DE102014007853B3 - Method and device for controlling the temperature of a heat exchanger - Google Patents

Abstract

The invention relates to a method and a device for controlling the temperature of a heat exchanger in systems in which the energy flow provided by the compressor is used as a primary hot steam flow and in conditioned form as a primary refrigerant flow by from these two streams by means of a combination consisting of a throttle body, a with the throttle body parallel adjustable hot gas valve, a reducing tube and a capillary tube, through the interaction and their configurations and by the set values of the hot gas valve, a definable current is generated in which both the amount and the state of the substance can be determined as a refrigerant and at manipulated variables the hot gas valve adjusts either the primary refrigerant flow or a stream consisting of parts of the primary streams, these partial streams undergoing a heat exchange by one of the embodiments, or a hot steam Adjusting the flow or the primary hot steam flow, wherein the specific stream directly into a in the heat exchanger, which is designed for example as a finned meandering heat exchange tube (finned air heat exchanger), placed reducing tube with a longitudinal side with one or more identically shaped openings provided capillary tube is introduced and throttled by the nature of the Reduzierrohrs and by the degree of openings. Due to the throttling and thus resulting pressure equally large amounts of moles as refrigerant through the openings occur indirectly in the heat exchanger, resulting in a uniform distribution of material in the heat exchanger. This leads, on the one hand, in the interior of the heat exchanger to optimum wetting with the substance and, consequently, to uniform tempering of the heat exchange surface, and, on the other hand, the quantity of substance and the state of the substance and thus the temperature and the power at the heat exchanger are determined by means of the manipulated variable of the hot gas valve. In this case, carried out in the control range of the hot gas valve through the heat exchanger, both a cooling and a heating operation. With a heating demand that is greater than from the heat exchanger deliverable, the heat output of the heat exchanger is dependent on the manipulated variable of the hot gas valve, by means of further actuators and embodiments of the heat exchanger adapted to the manipulated variable of the hot gas valve extension of the heating power, this provides a control device, which operates the heat exchanger with its configurations, with load changes for an automatic temperature and power compensation.

Description

The invention relates to a method and a device for carrying out a method for controlling the temperature of a heat exchanger. The operation of chillers or heat pumps, application finds. The refrigeration processes and heat pump processes take into account the required state changes of a substance, whereby by means of the working substance - the refrigerant - a heat transport in a closed system is accompanied to transport the heat energy, which is supplied on the one hand to the system and on the other hand discharged from the system.

In this method, with this device, the working fluid is converted by means of a refrigerator or a heat pump in a state, wherein the energy-loaded working substance is then used to a combination of a throttle body, a parallel to the throttle body adjustable hot gas valve, a reducing tube and a capillary tube, to be converted by their interaction and their configurations and by the set values at the hot gas valve in a further determinable state with a determinable amount of material. In the course of this agent is introduced into an apparatus, a heat exchanger, and then transferred to another state. In the process, the energy-laden working substance effects the direct temperature control of the heat exchanger, which indirectly heats media or objects. Both a cooling and a heating by the heat exchanger takes place in a control range of the hot gas valve, with a uniform material distribution and material distribution in the heat exchanger ensures that at a heat demand change always its entire heat exchange surface is available, so that by an optimal utilization of the heat exchange surface a uniform and thus optimum energy drainage is ensured by the heat exchange surface.

By means of the method with the apparatus, the heat exchanger arranged in the material cycle of refrigeration or heat pump systems and the substance placed in the heat exchanger are uniformly distributed and divided at different states and quantities of the substance inside the heat exchanger, so that the entire internal heat exchange surface is completely filled with such The resulting material is wetted, resulting in a uniformly tempered heat exchange surface, with a temperature range of the heat exchanger, which is determined by the adjustment ranges of a hot gas valve and an expansion valve. This temperature range corresponds, on the one hand, to the two temperature ranges of the heat exchangers used in a refrigeration system and one heat pump system and, on the other hand, to a further temperature range connecting these two temperature ranges, wherein a change of use of the heat exchanger from cooling to heating and vice versa and a continuous temperature change are taken into account in the control range of the hot gas valve and in the temperature range of the heat exchanger, the performance of the heat exchanger is variable. In this case, the method of temperature compensation in the heat exchanger with a power balance of the machine can be combined, the power adjustment depending on the dissipated energy flow of the heat exchanger, which allows an energetic operation of the systems in a realized, uniformly tempered heat exchanger surface, which is an economical construction of the Apparatus is created. Furthermore, by means of the method and the device, thermal transmission losses are minimized by an always optimally used heat exchange surface and by an immediate temperature control.

The method with the device includes that at settings on the hot gas valve and / or on the expansion valve at the heat exchanger, an adjustable temperature and a net power that balances a heat load result. In a changing heat load, the temperature compensation is usually carried out by means of a control device which operates the heat exchanger with its configurations, which performs an automatic temperature and power compensation. The temperature is continuously recorded by a sensor. In the case of a required constant maintenance of the detected temperature, the controller compares the detected temperature with the user-specified setpoint, with a difference between the detected temperature and setpoint, the controller adjusts the hot gas valve and / or the expansion valve until the detected temperature is equalized to the desired value. The sensed temperature is usually a mixing temperature, such as that of a room, resulting from the cumulative temperatures of one or more heat exchangers with their net power and the heat load of a room.

The state of the art is that installations such as chillers or heat pumps are available in the application as direct evaporation systems, whose main components are a compressor, a condenser, at least one throttle body and an evaporator, often in addition, for better functionality, extended to a collector. The evaporator and the condenser are each heat exchangers, the z. B. is designed as a lamellar air heat exchanger and consists of several, held at a distance thermally conductive fins, the heat exchanger tube several times are penetrated and thermally connected to this, as a rule, the course of the heat exchanger tube through the disk set meandering. The components of the system are each connected to each other with an inlet and outlet pipe and thus form a closed system with one or more fabric circles. The dry superheated refrigerant vapor, also referred to as the suction gas, drawn in by the compressor at low pressure and low temperature is compressed and subsequently this, now under higher pressure, compressed and dry superheated refrigerant vapor, also as superheated steam and in this special form as a hot gas referred to, desized in the desuperheater and in the condenser, often referred to as a condenser, cooled, causing a phase change in the hot gas, which leads to a liquefaction, wherein the high-pressure refrigerant condensate collects in the collector. This part of the direct evaporation plant with compressor, condenser and collector forms the high pressure side. Subsequently, the high-pressure refrigerant condensate flows as a refrigerant mass flow via at least one throttle body, the z. B. is designed as a capillary tube or expansion valve, which causes the throttling of the high-pressure refrigerant condensate, in the evaporator. Due to a low pressure in the evaporator then again a phase change of the refrigerant is obtained and thus the specific heat of vaporization, here in the form of cold, free, the evaporation of the refrigerant is carried out at a constant pressure and thus at a constant temperature. From there, the vaporized refrigerant, the dry superheated refrigerant vapor, at low pressure and low temperature in turn sucked from the compressor. This part of the direct evaporation plant with throttle body and evaporator forms the low pressure side. The dry superheated refrigerant vapor drawn by the compressor at low pressure and low temperature is in turn compressed by the compressor, so that the process starts again. In this lying in systems such as refrigerators and heat pumps underlying cycle heat is supplied to the evaporator with its useful cooling heat, which is withdrawn from a medium, such as air in the refrigerator. During the liquefaction (condensation) of the refrigerant vapor, the specific heat of vaporization (heat of condensation) is released, which is composed of the heat supplied and the drive power of the compressor. This condensation heat is released by the condenser elsewhere in a medium again. In plants with low useful power is usually omitted for economic reasons on separate lubricant devices for the compressor, so that the working fluid - so the refrigerant - attached oil is transported with its additives from the refrigerant flow and / or from the refrigerant vapor stream and so is always circulating in the material cycle and ensures the lubrication of the compressor. Before and / or after the evaporator are one or more throttle bodies, such as the thermostatic expansion valve, the constant pressure valve, not quite correctly referred to as suction pressure valve, and others, with manifold interconnections.

The throttle bodies, which operate without auxiliary electric power and are referred to as self-regulating throttle bodies, such as the thermostatic expansion valve, the temperature-controlled evaporation pressure regulator and others, consist of a mechanical actuator and a mechanically constructed controller (setpoint adjuster and comparator), wherein the actuator with a mechanical Actuator is firmly connected which in turn is firmly connected to the controller, the controller is connected as required by means of a capillary tube with a sensor. The controller forms a mechanical control device together with the actuator and the thermostatic sensor acting on the comparator. Here, actuator and control device are housed in a common housing and form with or without the in or outside of the housing located sensor assembly, the throttle body. These throttling devices are independent regulators, which manage without auxiliary energy.

In comparison to the power supply without auxiliary throttle bodies is supplied with the auxiliary power throttle bodies, such as supplied with electrical power expansion valves, also referred to as throttle valves, the actuator (valve) is actuated by an electronic controller by means of the electrically operated actuator, the controller with a Comparator, an amplifier and a generator of the control signal is provided with time response. The one or more controlled variables, z. As temperature, pressure, etc., and adjustable in a range reference variable or adjustable in a range at the setpoint generator constant setpoint (user default) are routed to the controller, the controlled variable is detected by a consisting of a sensor and a transducer measuring device. The controller uses the comparator to check whether the controlled variable corresponds to the reference variable. With unequal sizes, a control deviation or a control difference arises. In a control difference, the amplifier causes a force acting on the actuator control signal, wherein the actuator modifies the manipulated variable on the actuator to adjust the controlled variable to the reference variable or to the desired value. In general, the signals from measuring devices, actuators, etc. are standardized, so that with a standardized output signal of the controller, also referred to as a standardized control signal of the controller, by means of an actuator (electric motor, pneumatic or hydraulic drive), which causes a hub or a rotation angle , the manipulated variable on the actuator (eg valve, cock) is influenced or adjusted, whereby the actuating current, z. B. the mass flow or the energy flow adjusts. With continuous control, the output signal of the controller and the manipulated variable of the actuator within the control range is continuous, while in unsteady control, the output signal of the controller, and thus the manipulated variable and the actuating current, is erratic.

The one or more self-regulating throttle bodies are selected according to the temperature and performance requirements of the evaporator and placed in this, with the setpoint adjuster (adjusting spindle), which is part of the setpoint device, which in turn is part of the throttle body, carried out an adaptation of the throttle body to the evaporator can be. The setpoint adjuster adjustable setpoint is provided for the adaptation of the throttle body to the evaporator, this setting after the respective occurrence of the thermally equilibrium equilibrium and thus after the settling of the cyclic process and interacting useful power of the evaporator and the heat load, here the cooling demand , should be done gradually in time intervals. In this respect, the setpoint adjuster is not suitable for different evaporator temperature settings in the independently controlling throttle bodies. The self-regulating throttling devices operated evaporator are designed primarily to the optimum operating point, so that the maximum evaporation capacity of the evaporator can be used. Based on the evaporator temperature and power is in the refrigeration system or the heat pump system to the tuned in the low-pressure system part evaporator valve combination consisting of an evaporator and at least one according to the evaporator data selected throttle body z. B. is designed as a thermostatic expansion valve, the high-pressure side part of the system, which is usually available as a standardized condenser unit and completes the system selected and added to the evaporator valve combination, which ensures a total economic utilization of the system. The condenser unit is a compact unit and usually consists of the components compressor, condenser, collector and condenser fan.

The available at the evaporator or condenser temperature and power are widely used, either they are directly to the object to be tempered or tempered Good, z. As gases such as air or other, delivered, or indirectly, by being transferred to a medium, which in turn emits the thermal energy to be tempered Good.

Based on the prior art, the problem is that the evaporator, which is operated with self-regulating throttle bodies, such as the thermostatic expansion valve, tuned with temperature and power to an operating point. Therefore, changes that emanate from the optimum operating point and that are made by means of the self-regulating throttle elements, such as the thermostatic expansion valve, lead to a lower utilization of the evaporator. When the optimum operating point setting is changed, for example, a lowering of the evaporator temperature carried out by the setpoint device of the thermostatic expansion valve results in unadapted and disadvantageous system properties, which leads to a shortened evaporation process alongside the evaporator tube or for draining the end of the evaporator tube, also referred to as an underfilled evaporator. This has the consequence that in the evaporator and thus at the evaporator heat exchange surface no uniform temperature and power distribution is given. In addition, this lowering of the evaporator temperature leads to a reduction of the mass flow, d. H. a reduction of the refrigerant oil flow, which can lead to a stagnation of the oil flow and thus to a blockage of the compressor. Accordingly, an increase in the evaporator temperature by means of the setpoint device of the thermostatic expansion valve to a disadvantageous flooding of the evaporator, also referred to as overfilled evaporator, resulting in that unvaporized refrigerant enters the compressor, which can lead to a defect in the compressor valves ,

The disadvantage is that when equipped with a self-regulating throttle body evaporator whose performance is not continuously adapts to the changing heat load, since the refrigeration systems are rated with their evaporator performance (net power) so that they can cope with the expected peak loads. This requires that the refrigeration system is operated at partial load, ie in low load operation, with undiminished performance. In order to adjust the temperature and the dissipated amount of heat flow (useful power) of the evaporator as a heat exchanger at a changing load, for example, due to a change in temperature and a subsequent change in cooling demand, more, user-operable control devices, such. As a room thermostat acting as a fixed value control required, the room thermostat is used to keep the room temperature and for thermal load adjustment needs the refrigeration system or the evaporator on and off. The disadvantage here is that a small switching difference between the on and off temperature damaging switching cycles in the compressor leads. In addition, it is disadvantageous that, when the refrigeration system or the evaporator is switched on and off, the power drain through the evaporator is discontinuous and, accordingly, the temperature profile fluctuates periodically.

For evaporators that are equipped with self-regulating throttle bodies, such. As the thermostatic expansion valve, is also a disadvantage that the throttle-evaporator combination only for cooling, but not for heating is available. In a change of use of the evaporator as a heat exchanger from the cooling to the heating and vice versa additional automation and additional technical equipment, such. As a heating-cooling switching valve, piping (transport routes), etc., required.

A disadvantage is in inverter systems, which are equipped with a heating-cooling switching valve and in which the heat exchanger is used both as an evaporator and as a condenser, that when switching from cooling to heating operation and vice versa a sudden and thus a discontinuous temperature transition occurs, and that for this construction, an additional cost of piping and control technology arises, which is unprofitable, especially for small systems. In addition, it is disadvantageous that the temperature profile fluctuates periodically when the refrigeration system or the evaporator or the refrigeration system or the liquefier is switched on and off.

A disadvantage of independently controlling throttle bodies are the time-consuming optimization measures whose goal is to optimize the adaptation of the throttle body, z. As the thermostatic expansion valve to obtain the evaporator, which should lead to the best possible refrigerant charge in the evaporator. Also disadvantageous are the settings deviating from the optimum operating point, which result in disadvantageous system properties which, inter alia, can lead to unstable control behavior. In addition, an optimal adaptation by means of the adjusting spindle of the setpoint device is usually feasible only by a person skilled in the art.

In the known electronic evaporator controls, the problem is that due to the large number of different measuring devices, such. As for measuring the evaporation temperature, the evaporator pressure and other variables, a considerable amount of structural and regulatory measures is required, which is unprofitable especially for refrigeration systems with low power. For this reason, the systems (cold rooms, refrigerators, chests, etc.) or the heat exchangers are usually operated by means of two-position controllers or three-position controllers.

It is known that serving as a transport medium fluid, z. As water, oil, glycol or others, is used to load the energy generated by chillers or heat pumps in a buffer memory. The so stored by a medium energy, also referred to as hot water or chiller, is adjusted when removed from the buffer memory to the setpoints of temperature and mass flow, with temperature and mass flow determine the heat flow. The heat quantity flow in turn serves for the uniform and thus gentle tempering of an object or medium.

According to this procedure, temperature control devices are in use, which transmit and store the useful power of the evaporator at very low temperature directly to a fluid serving as a transport medium, filled into a container by means of a refrigeration system as a direct evaporation system. The fluid is passed during removal from this container through a heat exchanger operated with a controllable electrothermal heater and adjusted to the target temperature, the heat flow is conveyed by means of a pump to the place of use, there z. For example, initiate and maintain an operation or process flow, or the heat flow is passed through a water-to-air heat exchanger to temper a medium, such as air.

The disadvantage here is that the fluid located in a container is first cooled by the refrigeration system to the lowest temperature and subsequently, when removed from this container, the mass flow is heated as required by an adjustable heating and is adjusted to the target temperature, which results in a high consumption of primary energy. In addition, with conventional construction of Temperierungsgeräte disadvantage that additional supplies, eg. As glycol, are required, which are needed for heat transport, which is an additional expense. Likewise, additional technical equipment is required, eg. B. equipment parts such as pumps, heating, pressure vessels, storage and others, as well as extensive automation, so that the operating costs of the equipment are high.

In the case of the systems operated with the conventional method, which serve for the precise temperature control of an object or medium, it is also disadvantageous that the heat quantity flow, the temperature and the mass flow are adjusted to the reference variable by means of one or more tempering devices. In this case, additional control valves and / or other apparatus are required to adjust the temperature in addition to the one or more heat exchangers. Through the use of one or more heat exchangers occur transmission losses and, due to the additional piping, heat losses, so that additional energy is needed, resulting in additional energy consumption. In addition, it is disadvantageous in these methods that liquid escapes in the event of a leak and thus great damage can occur, especially in sensitive areas.

Hot gas defrosting devices are generally known in which the melting of frost layers on the evaporator takes place by means of a hot gas bypass. The defrosting takes place cyclically or as needed, which is determined by the grown frost layer on the evaporator. In the defrosting process, the introduction of the refrigerant flow into the evaporator is throttled and instead the hot steam flow is introduced.

Air conditioners are known, which consist of peltier block aggregates stretched between heat sinks, wherein the heat sinks are flowed through by the air medium in order to temper this air ( DE 196 00 470 A1 ).

Also known is the method and device for controlling the temperature of a liquid bath located in a reaction vessel by means of a medium whose temperature can be adjusted by means of a heating circuit and a cooling circuit ( DE 198 52 735 A1 ).

A temperature control can also be done by means of a heating register and a cooling register, wherein the media temperature is monitored by a controller and accordingly the registers are thermally adjusted ( WO 98/09 730 A1 ).

Further clockwise cyclic processes go out DE 20 2006 014 246 U1 . DE 34 13 931 A1 and DE 10 2004 008 410 A1 out.

These methods are used in the known systems targeted temperature control such as heating, cooling or freezing of objects or liquids.

The object of the invention is to provide a method and an apparatus for carrying out the method for controlling the temperature of a heat exchanger in refrigeration or heat pump systems, wherein a heat exchanger as an evaporator or as a heat exchanger or condenser (evaporator-heat exchanger condenser) is operable, so that this heat exchanger is used both for heating purposes and for cooling purposes, wherein the temperature range of the heat exchanger is determined by the characteristics of the systems and by the characteristic characteristics of the refrigerant. In addition, it is an object of the invention that in a predetermined temperature range of the heat exchanger, the temperature is continuously variable, with a uniformly tempered heat exchange surface of the heat exchanger for a direct and uniform temperature control of media or objects.

A further object of the invention is the use of the energy flow provided by the compressor, firstly as superheated steam flow and secondly in the heated and cooled form as high-pressure refrigerant condensate or refrigerant mass flow, in order to determine by means of these flows the temperature and the output of the heat exchanger which directly determines the specific use Media or objects tempered. This method should lead to overcoming the disadvantages of common procedures compared to conventional methods in which a vaporizer / compressor / condenser set is in use and other cascaded heat exchangers with other material circuits for precise temperature control of media or objects.

The object of the invention is further that the introduced into the heat exchanger energy flow or the energy-loaded agent is distributed and divided evenly as a refrigerant in the heat exchanger so that when heat demand change or load change, the inner heat exchange surface is always optimally wetted with the working material, so that the inner heat exchange surface is completely usable for energy transfer, resulting in the medium or the object to an improved usability of the heat content of the substance, which in turn results in an improved quality of the process. Furthermore, a submerged or flooded heat exchanger, in particular in the operating mode of the heat exchanger as an evaporator, to avoid.

The object of the invention is further that in the control range of an actuator a continuous temperature change is performed by the heat exchanger and in this control range a continuous change of use of the heat exchanger from cooling to heating and vice versa is considered, also it is required that the performance of the heat exchanger is changeable ,

The object of the invention is furthermore to operate the refrigeration systems or heat pump systems in an energy-efficient manner, which has to take place by means of a drive power of the working machine which adjusts to the heat exchanger output.

Furthermore, it is an object of the invention that the refrigerant-oil mixture in the system cycle is continuously in flow to protect the compressor from dry running.

Another object of the invention is that the heat exchanger to compensate for a heat demand, the recovered heat energy uses, resulting in another task, namely the expandability of the heat exchanger to a condenser, so that, to compensate for a larger heating needs, respectively, to increase the heating power, in addition provided by the heat exchanger useful power of the condenser from the recovered heat energy further useful power provides.

A further object of the invention is that the heat exchanger can also be operated, inter alia, outside the temperature range predetermined by the inventive device, whereby the characteristic numbers of the refrigeration system or heat pump system, such as the maximum permissible temperature of the compressor and others, are taken into account in order to ensure safe operation ensure the system in this extended temperature range.

The object of the invention is further that in addition to the cost-effectiveness of the refrigeration system and the heat pump system and their reliability is guaranteed. In addition, it is required that in the event of a malfunction of the system, the heat exchanger must be kept within a specified temperature range. This gives rise to a further object, namely that a safety loop without auxiliary power is to be included, which has a direct protective effect on the system, eg. As in a defect of the electronic controller, so that the system is transferred to a safe operating condition and so indirectly the safety loop operates the heat exchanger in the specified temperature range.

The object of the invention is furthermore that the inventive device for controlling the temperature of the heat exchanger is to be kept in a compact, simple and inexpensive construction.

In addition, it is an object of the invention to provide a method and apparatus for carrying out the method for controlling a heat exchanger in refrigeration systems or heat pump systems, wherein the heat exchanger, which is temperature-controlled as a function of the device, to compensate for its low power consumption, and this with a low performance of the refrigeration systems or heat pump systems, resulting in a further object that for temperature control and performance of the heat exchanger, for which no standardized throttle bodies are available, a solution with a method according to the device for temperature control and performance determination of the heat exchanger serves, is brought about.

Accordingly, it is an object to compensate for low heat demand with a heat exchanger and its useful power, which should be accompanied by low energy consumption of the machine.

Furthermore, it is an object to ensure an uninterrupted operation of the refrigeration system or heat pump system.

It is also an object to efficiently feed the heat exchanger with a mass flow and / or a flow, the state and the amount of the substance can be determined and the material is evenly distributed and divided within the heat exchanger, resulting in a determinable, uniformly tempered heat exchange surface results.

Furthermore, it is an object that in the control range of an actuator by the heat exchanger, both cooling and heating takes place, and that the tuned to the heat exchanger and adapted to him device consisting of a throttle body is to keep in a compact design.

Furthermore, it is an object that the net power or the amount of heat flow removed by the heat exchanger automatically adapts to the momentary heat load of the objects or the media.

The above objects are achieved with the methods and the devices having the features according to claims 1 to 19 and 20 to 39, respectively. Advantageous embodiments and uses of the invention will become apparent from the claims.

The object is achieved by the inventive method in that the energy flow provided by the compressor is used as a compressed and dry superheated refrigerant vapor stream or as superheated steam flow in two respects, on the one hand, the superheated steam flow is available, on the other hand, the superheated steam flow or the compressed and dry superheated refrigerant vapor stream is entitzt, cooled and throttled, then he stands as a high-pressure refrigerant condensate, also referred to as refrigerant, in the system circuit available, the refrigerant is used as a refrigerant mass flow. The refrigerant mass flow and / or the hot steam volumetric flow supply a heat exchanger, wherein a stream, the Corresponds to the refrigerant mass flow or which consists of proportional proportions of the two merged streams, the two-phase stream, or from a proportionate hot steam volume flow or the hot steam volume flow, is introduced into the heat exchanger, the flow comes into direct effect in the heat exchanger and causes that temperature and power are provided by this. In this case, the smallest temperature of the temperature range of the heat exchanger is determined by a throttle body and a downstream reducer and this in turn downstream capillary tube, the high temperature is determined by an adjustable hot gas valve and the downstream reducer and this in turn downstream capillary tube, said high temperature on the predetermined maximum refrigerant vapor temperature or the maximum temperature of the compressor is limited. Throttling devices are used such as the thermostatic expansion valve or the automatic expansion valve, which act as robust, self-operating, functional regulators, or the electronic expansion valve or the capillary tube or others. The combined by the parallel connection of the throttle body with the adjustable hot gas valve by means of the connection of the outputs of the throttle body and the hot gas valve and set values of the hot gas valve current is introduced into a reducing tube, which is connected downstream of the outputs and in turn a capillary tube, wherein at least one or a plurality of reducing tubes and one or more capillary tubes are respectively placed in at least one heat exchanger, wherein the capillary tube is provided with at least one pressure-adjusting elastic opening. Both the reducing tube and the at least one pressure-adjusting elastic opening of the capillary tube restrict the flow. The throttling has the consequence that depending on the manipulated variable of the hot gas valve in each case sets a pressure in the reducing tube and in the capillary tube. The pressure in the inlet of the reducing pipe also influences the degree of throttling of the throttle body. Accordingly, the refrigerant mass flow is dependent on the manipulated variable of the hot gas valve. In addition, the pressure in the capillary tube functionally affects the degree of opening of the openings in the capillary tube and thus, in addition to the manipulated variable of the hot gas valve, the amount that emerges through the openings of the capillary tube is determined. Because of these coupled by the pressure actuators with the manipulated variable of the hot gas valve, the admixing of the superheated steam flow to the refrigerant mass flow can be determined, being tempered by a hot steam flow or by merging into different proportions streams or by a refrigerant mass flow of the heat exchanger. In addition, before the introduction of the refrigerant mass and / or the superheated steam flow into the reducing tube and the capillary tube, a heat exchange between the refrigerant mass flow and superheated steam flow optionally takes place by means of a thermal compensating accumulator. By actuation of the hot gas valve thus takes place a determinable introduction of refrigerant mass flow and / or superheated steam flow into the reducing tube and the capillary tube, wherein within the heat exchanger, which is usually designed as a lamellae equipped heat exchanger tube, by means of the capillary tube, a uniform distribution of the mass flow and / or volume flow takes place, is determined by the pressure in the capillary tube, the degree of opening of the at least one opening in the capillary tube, so that in each case a uniform distribution of the mass flow and / or the volume flow through the openings in the heat exchanger tube is carried out by these identically shaped openings, creating an optimal, uniform Temperature control of the heat exchanger is achieved, which z. B. leads in a laminar air heat exchanger to a uniformly tempered heat exchange surface. By this procedure, both cooling and heating takes place in the adjustment range of the hot gas valve by means of the heat exchanger. In case of temperature change or load change, a control device by temperature adjustment ensures that the heat demand is automatically compensated by the actuated by the controller hot gas valve from the heat exchanger operated therewith, both for a cooling and a heating demand.

The task of tempering a heat exchanger by means of a device according to the inventive method, is achieved in that the collector at least one throttle body, designed as a thermostatic expansion valve or as an automatic expansion valve or as an electronic expansion valve or capillary tube, is followed, the one actuated by the controller Hot gas valve, which is connected either as a hot gas bypass before the condenser or in a branch with him, connected in parallel. Here, the two merged and interconnected outputs of the throttle body and the hot gas valve are connected to the thermal balance memory, which is designed as a thermally conductive, long and preferably wound tube or container whose contents have good thermal conduction properties, this is the balance memory with at least one tube provided as outlet pipe. The outlet tube is extended with a reducer tube and a thermally-insulating capillary tube provided with one or more elastic apertures of similar shape closed at its end with the end of the outlet tube, the reducer tube and the capillary tube placed in the heat exchanger. The in the Heat exchanger introduced part of the outlet pipe is sealingly connected to the input of the heat exchanger. The suction pipe functioning as a connecting pipe between the outlet of the heat exchanger and the compressor is sealingly connected to the heat exchanger and the compressor.

In the inventive method and the device are with the combination consisting of a throttle body, a throttling organ connected in parallel adjustable hot gas valve, a reducing tube and a capillary tube, by their interaction and their configurations heat exchanger temperatures adjustable, in this combination, the specific heat of vaporization of the refrigerant and the specific heat capacity of the compressed and dry superheated refrigerant vapor and the superheated steam are usable by the heat exchanger.

A particular advantage of this invention is that in the control range of the hot gas valve at the smallest adjustable control variable, a refrigerant mass flow at the largest adjustable control variable adjusts a hot steam volume flow and result in either different refrigerant hot steam mass flows or a reduced hot steam volume flow at all intermediate values.

Another particular advantage of the invention is that in the control range of the hot gas valve through the heat exchanger both cooling and heating is possible, the lowest heat exchanger temperature is determined by the evaporation temperature, which is determined by means of the throttle body, the Reduzierrohrs and the capillary, the high heat exchanger temperature is determined by means of the hot gas valve, the Reduzierrohrs and the capillary tube, the largest temperature on the characteristic characteristics of the system, eg. As the maximum refrigerant vapor temperature or the maximum temperature of the compressor is limited.

A particular inventive advantage is that by an inventive combination, consisting of a throttle body, a parallel with the throttle body, adjustable hot gas valve whose two outputs are merged, and a downstream reducer and a downstream capillary, by their interaction and by the embodiments of this Combined by operating the hot gas valve temperature and power at the heat exchanger are adjustable and with a temperature control automatic temperature compensation, with continuous control by the heat exchanger, a continuous power compensation is performed, and a change of use of the heat exchanger from heating to cooling and vice versa is taken into account at a uniformly tempered heat exchange surface of the heat exchanger, which is operable as an evaporator or as a heat exchanger.

An inventive, significant advantage is that by the inventive combination, consisting of a throttle body, a throttling organ connected in parallel adjustable hot gas valve, a reducing tube and a capillary, through their interaction and by the embodiments of this combination, a mixing of the hot steam volume flow is made possible to the refrigerant mass flow , wherein in the adjustment range of the hot gas valve, a temperature range of the heat exchanger can be adjusted, which extends from the evaporation temperature to the hot steam temperature. In this way, in addition to the specific heat of vaporization of the refrigerant additionally the specific heat capacity of the compressed and dry superheated refrigerant vapor or the superheated steam is used for temperature control of the heat exchanger.

Another inventive advantage is that the inventive combination operates a heat exchanger and can be extended with further parallel throttle bodies, which are each equipped with a downstream reducer and a downstream capillary tube, these throttle bodies, the hot gas valve is connected in parallel to more parallel connected and in Depending on the hot gas valve to operate standing heat exchanger, the hot gas valve as a master and coupled by the pressure throttle bodies operate as a slave so as to operate several identically configured heat exchanger simultaneously or use multiple cold spots / hot spots in the network.

It is inventively advantageous that, instead of the throttling element designed without auxiliary energy, designed, for example, as a thermostatic expansion valve or capillary tube, an electric, hydraulic or pneumatic expansion valve actuated by the regulator with auxiliary power can be used. The two valves operated by the regulator, the expansion valve and the hot gas valve, are operated as master-slave, with the hot gas valve as master and the expansion valve as slave. It is advantageous that the master-slave mode is realized, for example, in that the electrical connection of the expansion valve for electrical connection of the hot gas valve is connected in parallel reversed or the signal output of the controller which actuates the hot gas valve, in parallel actuates the expansion valve.

A given by this invention advantage is that the cost of automation with control and regulation technology and for the production of hardware and the number of measurements are kept low.

An inventive advantage is that by a reducing tube as a connecting pipe and by the at least one elastic opening of the thermally insulating capillary tube, preferably made of materials such. B. plastic, the refrigerant mass flow and / or the hot steam volume flow are throttled. The throttling of the refrigerant mass flow and / or the hot steam volume flow through the reducing tube and the at least one opening of the capillary tube leads to a pressure in the reducing tube and in the capillary tube, wherein the pressure in the capillary tube determines the degree of opening of the at least one elastic opening of the capillary tube, d. H. as the pressure increases, the at least one orifice widens and as the pressure decreases, it narrows, thus the flow rate varies depending on the pressure and the degree of opening of the capillary tube orifices. The manipulated variable of the hot gas valve influences the pressure by means of the at least one elastic opening in the capillary tube and by means of the reducing tube, the pressure in the inlet of the reducing tube also having an influence on the degree of throttling of the throttle element, i. H. For example, in a throttle body, which is designed as a thermostatic expansion valve, the manipulated variable of the expansion valve is determined by means of the pressure, resulting in the quantitative ratio of the hot steam volume flow to the refrigerant mass flow, so that according to the settings of the hot gas valve, a hot steam volume flow or from different proportions of superheated steam flow and Refrigerant mass flow existing refrigerant hot steam mass flow or sets a refrigerant mass flow, wherein by means of the manipulated variable of the hot gas valve, the amount of substance and thus the heat exchanger performance is determined and the heat exchanger temperature is determined by the state of the substance. In addition, it is advantageous that an admixing of the hot steam volume flow to the refrigerant mass flow takes place by means of the hot gas valve, wherein an increasing hot steam volume flow leads to a decreasing refrigerant mass flow and vice versa.

An advantage of this design is that the thermally insulating capillary tube placed in the heat exchanger and provided with at least one or more elastic openings at intervals provides a uniform material distribution and material distribution in the heat exchanger, which is usually designed as a heat exchanger tube. H. it is a uniform refrigerant mass flow and / or superheated steam volume flow distribution and division causes, resulting in a uniformly tempered heat exchange surface with low temperature gradients. It is also advantageous that the at least one opening in the capillary tube acts as a pressure-adjusting nozzle which atomizes the refrigerant mass flow in the heat exchanger or depressurizes the hot steam volume flow. Thus, the openings provide for the throttling of the flow and for the distribution and the division of refrigerant mass flow and / or superheated steam flow.

An advantage of the invention is that in the heat exchanger by the distribution and spraying of the pressurized refrigerant mass flow through the at least one elastic opening in the capillary tube improved utilization of the introduced into the heat exchanger energy flow is obtained compared to a refrigerant inlet into a heat exchanger, without the inventive Refrigerant distribution takes place, resulting in improved utilization of the heat exchange surface, especially in a part-load operation. In addition, reduce the throttling losses of the throttle body.

It is inventively advantageous that the commercially available, standardized and thus power-graded hot gas valve can be connected to it before the condenser or in the branch of the condenser, whereby the maximum hot steam temperature can be predetermined and a simple hydraulic connection of the hot gas valve is given.

The advantage here is that the mechanical and the electrical interconnection of the components in the refrigeration systems or heat pump systems held in a simplified, cost-effective, compact design with low volume and so the equipment cost is simplified.

A given by this invention advantage is that in systems in the application as direct evaporation systems by the inventive device no separate lubricant devices for the compressor are required, as by the combination consisting of a throttle body, a parallel with the throttle body adjustable hot gas valve, a Reduzierrohr and a capillary tube, through their interaction and the embodiments of this combination, the refrigerant-oil mixture is continuously in the flow or the superheated steam oil mixture flows continuously in the system circuit.

Another inventive advantage is that the thermally conductive, preferably wound, long tube or the container filled with ingredients with good thermal conductivity properties serves as a thermal compensating memory, wherein the different tempered refrigerant and superheated steam flows (two-phase flow) through the thermal balance memory undergo heat exchange, at the same time takes place in the thermal balance memory nebulization of the two-phase flow.

Another object is achieved by an embodiment of the device with an inventive method in that the specific heat of condensation of the compressed and dry superheated refrigerant vapor or the hot steam volume flow is used for heating purposes. In this case, the pressure in the heat exchanger is determined by the arranged at the entrance of the heat exchanger adjustable hot gas valve and arranged at the outlet of the heat exchanger adjustable expansion valve. The heat exchanger is thus functionally operated as an evaporator or as a heat exchanger or as a condenser (evaporator-heat exchanger condenser).

In this expedient embodiment of the inventive device, the combination consisting of a throttle body, a throttle valve connected in parallel with the adjustable hot gas valve, a reducer and a capillary tube, with their interaction and their designs expanded by a arranged at the output of the heat exchanger adjustable expansion valve.

The procedure includes that depending on the difference of the detected temperature to the reference variable, the hot gas valve and the expansion valve are operated sequentially by the controller by first the highest possible control variable of the expansion valve, the hot gas valve is actuated and then the expansion valve is operated with the largest possible manipulated variable of the hot gas valve. The heat exchanger is thus operated by the controller by means of the hot gas valve and by means of the throttle body influenced by the hot gas valve, the heat exchanger being used in this mode of operation as an evaporator or as a heat exchanger. When expanding the heat exchanger with an expansion valve, the heat exchanger is used by the regulator by means of the expansion valve in the operation of a condenser. The heat exchanger is thus operable with the inventive device and the embodiment as an evaporator-heat exchanger condenser.

In this inventive embodiment it is advantageous that by the inventive combination, consisting of the throttle body, the throttling member connected in parallel, adjustable hot gas valve and a throttle body and the hot gas valve downstream reducing tube and the reducer downstream capillary tube, by their interaction and their embodiments in addition, the pressure in the heat exchanger can be determined by means of an expansion valve arranged at the outlet of the heat exchanger, so that the heat exchanger can also be operated as a condenser. It is advantageous that at a heating demand that is greater than that provided by the heat exchanger by means of the specific heat of the compressed and dry superheated refrigerant vapor or hot steam heat output, the specific heat of condensation of hot steam from here operated as a condenser heat exchanger is available.

An object with a further embodiment of the inventive method is that the heating demand compensation, which is carried out by the means operated by a hot gas valve and / or an expansion valve heat exchanger and also by a three-way valve operated as a distribution valve condenser, wherein the condenser with the heat exchanger in combines a design or is arranged separately at the heat exchanger. If the heating demand is greater than the heat output that can be generated by the heat exchanger, the heat output of the condenser is switched on at this heat output. The connection of the heating power of the condenser takes place when the manipulated variable of the hot gas valve exceeds an upper threshold in the control range of the hot gas valve, and the shutdown of the heating power of the condenser takes place when the manipulated variable of the hot gas valve falls below a lower threshold in the control range of the hot gas valve. Thus, the switching on and off of the heating power is adjusted to the manipulated variable of the hot gas valve and thus adapted to the heat output of the heat exchanger, as evaporator heat exchanger condenser.

In this further embodiment, the inventive device is extended by a condenser and a three-way valve. In this case, the compressor is connected to a pressure line with the entry of preferably operated by the regulator three-way valve, wherein on the one hand, the two outlets of the three-way valve is connected to the condenser, which in turn is connected to the downstream collector, and on the other, the second outlet of the three-way valve is connected to the further condenser, which is an integral part of the heat exchanger or placed at the heat exchanger, said condenser is also connected to the inlet of the first condenser, which in turn is connected to the downstream collector.

The inventive embodiment has the advantage that to compensate for the heating demand in addition to the heat exchanger provided Useful heat, a further useful heat is provided by a condenser, which is switchable in coordination with the hot gas valve, ie the heat output of the condenser is connected as needed to the heat output of the heat exchanger as evaporator heat exchanger condenser. It can be z. B. these provided by the condenser useful heat by heat recovery, for example, from the heat flow of the exhaust air, the heat is removed, are obtained.

The solution to one of the aforementioned objects is brought about by a further supplementary embodiment with an extension of the inventive device in that the controllable heating, preferably an electrothermal converter, is arranged between the thermal compensation reservoir and the heat exchanger.

As a result, the superheated steam volume flow is overheated by the controllable heater before it enters the heat exchanger, the heat transfer being effected by means of the refrigerant as mass flow and / or volume flow. The resulting from the cumulative energy of the compressor and the controllable heat output energy flow is available as useful power at the heat exchanger.

An advantage of this further additional embodiment is that the heat demand is compensated by means of a single heat exchanger and thereby the amount of technical equipment, in particular of the piping system (working medium transport path) is reduced to a minimum, so that the temperature of the objects or media the heat exchange surface of a single heat exchanger takes place.

An advantage of this embodiment is also that the outgoing of the controllable heating energy flow, due to the design of a heat exchanger, transferred to a large heat exchange surface of the heat exchanger and due to the consideration of uniform material distribution and material distribution in the heat exchanger is a uniform heat transfer to a medium or an object in comparison with the energy flow transmitted by the controllable heater, which occurs at high temperature in the case of direct transmission due to the design of the electrothermal converter with a small heat exchange surface.

Another object is achieved by an extended expedient embodiment of the device by the inventive device is extended by a controllable heating, which is designed as an electrothermal transducer and integrated in the heat exchanger or according to the heat flow of the heat exchanger is connected downstream of this. In addition, the heat exchanger is preceded by a valve which is arranged after the merged outputs of the throttle body and the electric hot gas valve in front of the heat exchanger.

With this further designed device, the method is extended to extend the temperature range of the heat exchanger, wherein the characteristic characteristics of the system such as the maximum refrigerant vapor temperature or the maximum temperature of the compressor are taken into account in the extended temperature range of the heat exchanger. In this extended temperature range, heat exchanger temperatures are adjustable up to the maximum limit temperature of the oil mixed as refrigerant.

• – wobei bei einer erfassten Temperatur, die kleiner als die Führungsgröße ist, diese Temperaturdifferenz einem Heizbedarf entspricht, wobei der Regler die erfasste Temperatur mittels der von ihm betriebenen regelbaren Heizung an die Führungsgröße angleicht, und wobei der Wärmeaustauscher mittels des ihm zusätzlich vorgeschalteten geschlossenen Ventils durch den Verdichter evakuiert wird, der sich anschließend ausschaltet,
• – wobei bei einer erfassten Temperatur, die größer als die Führungsgröße ist, diese Temperaturdifferenz einem Kühlbedarf entspricht, wobei der Regler die erfasste Temperatur mittels des von ihm betriebenen Wärmeaustauschers an die Führungsgröße angleicht, indem mittels des vom Regler betätigten Heißgasventils bei geöffnetem und dem Wärmeaustauscher vorgeschalteten Ventil ein bestimmbarer Strom in den Wärmeaustauscher eingeleitet wird,
• – wobei bei geöffnetem Heißgasventil die erfasste Temperatur, die kleiner als die Führungsgröße ist, einer geringen Temperaturdifferenz mit einem geringen Kühlbedarf entspricht, wobei die erfasste Temperatur mittels des vom Regler betriebenen Wärmeaustauschers an die Führungsgröße angeglichen wird, indem der Regler, der in Abhängigkeit von der Temperaturdifferenz das dem Wärmeaustauscher vorgeschaltete Ventil taktet, einen bestimmbaren Strom in den Wärmeaustauscher einleitet.

The extended and complementary embodiments of the inventive combination are based on the extended inventive method in which the heat exchanger is operated at temperatures greater than or equal to the maximum refrigerant vapor temperature or the maximum temperature of the compressor, the maximum refrigerant vapor temperature being at the refrigerant vapor temperature when entering the compressor, the controller, z. B. a P-controller with a constant control deviation, between detected temperature and reference variable performs a balance and equalizes the detected temperature to the reference variable,

• - Wherein at a detected temperature, which is smaller than the reference variable, this temperature difference corresponds to a heating demand, wherein the controller equalizes the detected temperature by means of the controllable heater operated by it to the reference variable, and wherein the heat exchanger by means of the additional upstream valve closed by the compressor is evacuated, which then turns off,
• - Wherein at a detected temperature, which is greater than the reference variable, this temperature difference corresponds to a cooling demand, wherein the controller equalizes the detected temperature by means of the heat exchanger operated by it to the reference variable by means of the operated by the controller hot gas valve in the open and the heat exchanger upstream Valve a determinable stream is introduced into the heat exchanger,
• Wherein, with the hot gas valve open, the detected temperature, which is smaller than the reference variable, corresponds to a small temperature difference with a low cooling requirement, wherein the detected temperature is adjusted by means of the heat exchanger operated by the regulator to the reference variable by the controller operating in Depending on the temperature difference the valve upstream of the heat exchanger clocks, initiates a determinable flow into the heat exchanger.

In this inventive method, a monitoring and protection device with a corresponding method in addition to the existing device and the existing method is required to protect sensitive components of the system from overheating.

Such an arrangement of a monitoring and protection device is here, for example, the connection of a collector downstream, variable temperature throttle body with a valve, the valve outlet with an access of a heat exchanger, which is designed as a heat exchanger tube and part of the suction line is connected, wherein the throttle body consists of a capillary tube, which is preferably wound around a thermally conductive cylinder and thus mechanically connected to it and also thermally connected, wherein the cylinder is equipped with a controllable heating, preferably an electrothermal transducer. The designed as a heat exchanger tube heat exchanger, which is part of the suction line is equipped with the existing of a pipe access, which is introduced into the interior of the heat exchanger tube and sealingly connected to this, with a reducer tube is connected as a connecting tube to which a with one or more identically designed elastic openings provided, thermally insulating capillary tube, which preferably consists of a thermally insulating and elastic material is connected, wherein the end of the capillary tube is sealed.

Such monitoring and protection devices prevent, inter alia, temperature excesses, ie exceeding the maximum refrigerant vapor temperature or the maximum temperature of the compressor, whereby safe operation in the extended temperature range of the direct evaporation system is ensured.

The associated control method is discussed in more detail in the figures and in the dependent claims.

The advantage is that in this embodiment the heat exchanger can be operated up to the limit temperature of the oil admixed with the working substance as refrigerant.

In these additional embodiments, it is advantageous that the inventive combination, consisting of a throttle body, an adjustable hot gas valve connected in parallel with the throttling member, a reducing tube and a capillary tube, by their interaction and by the embodiments of this combination with a variably tempered throttle body with its embodiments expandable, which extends the temperature range of the heat exchanger. In this case, components of the refrigerators or heat pumps, z. As the compressor, by means of the variable-temperature throttle body needs-tempered and thus protected from overheating.

An advantage of these embodiments and embodiments is that in the inventive combination, consisting of a throttle body, connected in parallel with the throttle body, adjustable hot gas valve whose two outputs are merged, and a downstream reducer and a downstream capillary tube, by their interaction and by the configurations of this combination of heat exchangers with other apparatus, such as condenser and / or heating, can be extended while the components of the system are optionally protected by means of a variable-temperature throttle body against overheating.

Another object is achieved in that by a variable pressure in the capillary, the amount of material spent in the heat exchanger can be influenced and thus the performance of the heat exchanger can be determined, the openings of the capillary provide for uniform distribution and division of the substance. Accordingly, by means of the pressure, the flow rate of the refrigerant or of the superheated refrigerant steam or of the superheated steam can be determined through the at least one opening of the thermally insulating capillary tube.

It is advantageous in this extended advantageous embodiment that the inventive method of temperature control of a heat exchanger with a determinable pressure in the capillary tube, which affects the amount of heat spent in the amount of substance, which in turn affects the performance of the heat exchanger, can be combined. It is advantageous that with changing pressure through the capillary tube openings a uniform distribution and division of the substance takes place in the heat exchanger, whereby the heat exchange surface is always uniformly tempered.

To adjust the power consumption of the chiller or heat pump to the heat exchanger performance from an energy point of view, a regulation of the power of the compressor is required.

Another object is achieved by a further expedient and advantageous embodiment solved the inventive method in that the power of the compressor automatically adapts to the energy flow discharged from the heat exchanger. In this case, a method is used, in which the drive power of the compressor or the rotational speed of the compressor is determined as a function of the heat quantity flow discharged by the heat exchanger. Controlled variables for controlling the power of the compressor are usually the amount of heat removed by the heat exchanger, which is determined from the difference in the amount of heat before and after the heat treatment, for example a medium, or the enthalpy, which is determined from the difference in enthalpy before and after Heat treatment, for example, a medium. An advantage of this embodiment is that the inventive method of controlling the temperature of a heat exchanger with the method of power control of the compressor can be combined.

In addition to the combination of the two methods, the temperature and pressure of the refrigerant vapor drawn in by the compressor are monitored, so that a dry superheated refrigerant vapor is sucked in by the compressor. If the temperature detected at the suction line falls below the predetermined refrigerant vapor temperature or the pressure detected in the suction line, the controller determines a minimum actuating variable of the compressor drive power or a minimum compressor speed, the controller setting the speed to the minimum Manipulated variable limited or the lower speed range of the compressor regulatory limits.

It is taken into account in the combined process sequence that carried out by the heat exchanger temperature compensation takes place prior to the adjustment of the drive power of the compressor to the energy flow discharged from the heat exchanger by a lower response value of the manipulated variable of the actuator located in normal operation and when it falls below and at an upper Pickup value of the manipulated variable of the actuator located in the control mode and when it is exceeded successively the manipulated variable of the speed of the compressor is increased until the detected temperature is equalized to the reference variable.

It is inventively advantageous in this advantageous embodiment that the thermally insulating capillary tube placed in the heat exchanger and provided with at least one or more elastic apertures arranged at equal intervals along the capillary tubes is provided with changing pressure for a uniform material distribution and material distribution through the at least one opening in the heat exchanger ensures, so that at different load conditions and at a capacity of the heat exchanger adaptive drive power of the compressor a uniformly tempered heat exchange surface is ensured.

In this embodiment, it is furthermore advantageous that the method of the drive power of the compressor, which is adapted to the heat exchanger capacity, can be combined with the inventive method and its configurations for controlling the temperature of a heat exchanger. In addition, it is advantageous that, taking into account a uniformly tempered heat exchange surface, further energy savings can be achieved.

Another object is achieved by an expedient and advantageous supplementary embodiment with a device in that a tuned to the heat exchanger, variable temperature throttle body, consisting of a capillary tube, a thermally conductive cylinder and a controllable heater, the task of combining the parallel with a throttle body switched hot gas valve takes over. In this case, the capillary tube is wound around the thermally conductive cylinder, which is equipped with heating, and connected to it mechanically and thermally.

The inventive device is based on the method that a control device actuates an electronic valve, and thus the heating tempered the cylinder, which in turn tempered the capillary tube with the refrigerant mass flow therein, which is introduced into the heat exchanger and thus tempered and operated.

Advantage of this inventive complementary useful embodiment is that by means of a manipulated variable of the variable-temperature throttle body, the state of the actuating current is set.

The advantage of this additional expedient embodiment is also that followed by an electronic valve operated by the controller by means of the variable temperature throttle body, the temperature at the heat exchanger of the reference variable and corresponding automatic temperature compensation takes place, with continuous control, a continuous power compensation by the heat exchanger at a constant temperature change Heat exchanger or is carried out in a continuous change of use of the heat exchanger from cooling to heating and vice versa, with a uniformly tempered heat exchange surface of the heat exchanger, which in particular at low power range of the chiller or Heat pump is a cost-effective design with low volume.

An advantage of the inventive embodiments and embodiments is that a control device, which operates a heat exchanger by means of the hot gas valve and / or expansion valve, ensures that the heat demand is automatically compensated by the useful power of the heat exchanger or the heat exchanger performance automatically adjusts to the heat load. The same applies to the tuned to the heat exchanger and adapted variable temperature throttle body, which is actuated by a control device which operates a heat exchanger.

Another advantage of this additional embodiment of the invention is that the inventive method of temperature control of a heat exchanger with a capacity control of the compressor can be combined. The power control of the prime mover of the compressor affects the speed of the compressor and the pressure in the capillary tube, which pressure affects the amount of material spent in the heat exchanger, thereby determining the temperature and performance of the heat exchanger.

In this embodiment, the combinability of the inventive method of temperature control of a heat exchanger with the method of power control of the compressor is advantageous that the heat exchanger performance can be determined on the one hand by the state of the substance as a refrigerant and on the other hand by the determinable by the pressure in the capillary tube amount of substance. Conveniently, the thermally insulating capillary tube placed in the heat exchanger, which is provided with at least one or more spaced, identically designed openings, which ensure a uniform material distribution and material distribution, which has a uniformly tempered heat exchange surface result, so that the heat flow flows evenly from the heat exchanger. The adaptation of the drive power of the compressor to the discharged energy flow of the heat exchanger takes place as a function of a control variable, for example, the amount of heat removed by the heat exchanger or the heat exchanger from the enthalpy or other controlled variables.

An advantage of the invention is that the temperature range of the heat exchanger can be designed with embodiments and with designs and the performance of the heat exchanger with embodiments and configurations can be changed and the performance of the working machine can be adapted to the energy flow discharged by the heat exchanger.

In a fixed value control, the control device controls the detected controlled variable, here the temperature to keep the temperature of the objects or media constant by the heat exchanger, which is operable as an evaporator or as a heat exchanger or condenser, automatically compensates with its useful power the current heat demand, wherein the heat exchanger is expandable with one or more condensers and / or with one or more controllable heaters, wherein the condenser and / or controllable heaters also automatically compensate for the current heat demand with their useful power. In the case of a follow-up control, in which the variable command variable usually depends on further variables, the same applies to the temperature adjustment as with the fixed-value control. In addition, the control device monitors by means of the detected controlled variable, here the refrigerant vapor temperature (suction gas temperature), the temperature of the compressor and others, and protects the components such as the compressor from overheating.

In the case of reference variables which are smaller than the characteristic numbers of the system, such as the maximum refrigerant vapor temperature or the maximum temperature of the compressor, and with a heating requirement which is greater than that which can be achieved by the actuators of the hot gas valve, the expansion valve and the three-way valve, the controllable temperature can additionally be determined Heating be switched on. The control device operates the heat exchanger and, depending on the required power requirement, a condenser and / or a controllable heater.

The chiller or the heat pump comprises the apparatus operated by the control device (heat exchanger, condenser and heater), the actuators actuated by the control device (valves and variable-temperature throttle bodies), the machine switched by the control device (compressor) and the transport routes (piping) , The control device also ensures the automated operation of the system, whereby the variables to be controlled (controlled variables), in this case temperature and pressure, are recorded continuously by the measuring devices (temperature sensors and pressure sensors).

In the embodiments with the embodiments, the control device operates a heat exchanger as an evaporator or as a heat exchanger or as a condenser. Depending on the power requirement, the heat exchanger is extended by a condenser and / or a controllable heater as well as monitoring and protection devices that monitor components of the systems.

On the invention with its methods and their devices will be discussed in more detail in the embodiments and the claims.

Some applications and the resulting benefits are shown below.

It is inventively advantageous that in the systems that are equipped with the inventive combination, condensate formation on the condenser is avoided in heating operation, in contrast to inverter devices that are equipped with reversing valves for cooling and heating.

Another advantage given by this invention is that in systems used in the application as direct evaporation systems, the heat exchanger with continuous temperature control for sensitive cooling of a medium is available. With a continuous temperature control and with the uniformly tempered heat exchange surface of the heat exchanger, the medium to be treated, for. As air, precise and even tempering, with condensation on the heat exchanger in the application is avoided as an evaporator. Thus, it is possible to dispense with a condensate collecting tray, which also allows an installation independent of the condensate drain in the building. The dew point temperature is determined by the controller from humidity and air temperature.

It is an advantage of the invention that, by means of this method and the device for carrying out this method, among other things, the heat exchange surface, for example in the case of a lamellar air heat exchanger, is uniformly tempered and with constant regulation a precise, uniform temperature control of an object or medium, eg. As an aerosol, is made possible whereby specific liquid suspended matter from the aerosol are auskondensierbar.

Another advantage is that in case of a defect of a controller, z. As an electronic controller, operated hot gas valve, the throttle body, which is designed for example as a thermostatic expansion valve, acting as a self-operating regulator as a safety valve in its function, so that heat-sensitive substances such as milk, flavors and others are protected against overheating.

An inventive advantage is given by the fact that the system with the combination according to the invention, consisting of a throttle body, a throttle valve connected in parallel, adjustable hot gas valve whose two outputs are merged, and a downstream reducer and a downstream capillary tube, by their interaction and by the embodiments of this combination, the temperature and performance is determined at the heat exchanger. This inventive combination is expandable with other inventive combinations that determine temperature and performance in a heat exchanger, and / or the inventive combination is expandable with one or more heat exchanger throttle body combinations.

An advantage of the inventive method and the device is that evenly distributed in the heat exchanger and divided by the placed in the heat exchanger capillary tube of the refrigerant mass flow and / or the hot steam volume flow, so that, for example, when using the heat exchanger as lamellar air heat exchanger of the heat exchanger discharged heat flow, the Efficiency, even and thus with low thermal losses directly to the object or the medium is transferable. In comparison, in conventionally operated Temperierungsgeräten the cooling capacity is transferred to a fluid, which in turn tempered by means of another heat exchanger, the object or the medium, which has further transmission losses result. Thus, an improved efficiency is given by the invention evenly tempered heat exchange surface by the immediate precise temperature control of objects or media, resulting in a saving of energy and technical equipment, which improves the overall economy. The inventive method with its inventive devices are used to tools that z. B. in the piece pressing process, in milling centers or tunnel boring machines in use to temper, d. H. to preheat before starting the work process and to precisely temper it during the work process, usually to de-heat. The tool provided with meandering holes is equipped with the inventive device of Reduzierrohrs and capillary tube, whereby the tool is additionally upgraded with the inventive heat exchanger.

Another inventive advantage is that due to the uniform temperature of the heat exchanger in the function as a surface heat exchanger electronic components are temperature controlled directly and precisely, which is avoidable by dew point determination of the electronic components, among other things, the condensation on the same. In addition, by means of the capillary tube with its at least one opening, a spatially limited, precise temperature control of the hot spot (heat source) of the electronic component is provided. Accordingly, the method with the device, for example, in optoelectronics, z. As laser technology, applicable, where the components are precisely tempered to the component on the one hand condensate and on the other hand overheating avoid. In addition, the decommissioned component is always kept at operating temperature to allow a cyclic operation of the device, with on and off duration.

The inventions with their embodiments and embodiment are suitable for applications and applications such as the temperature of objects, eg. As tools and other goods, or media such as air, which can be found, for example, in object rooms such as chests, cells, showcases and others, and other media, such as hydrocarbons and other gases. Further applications in process technology are, for example, condensation of liquid suspended matter from an aerosol, such as, for example, the recovery of aroma substances that result from the fermentation of organic substances, or the condensation of gas components from the air. By means of continuous control is a continuous change of use of the heat exchanger from cooling to heating and vice versa, which makes the use of thermally sensitive objects, u. a. Also, food, and thus the invention is also suitable for medical and measuring technology and the food industry. Due to the precise and uniform air temperature control, the use in rooms with precision manufacturing systems, such. As CNC machining centers are equipped, also suitable. Consequently, the invention is not limited to specific applications, but the use of the inventive method and the inventive devices with their embodiments and embodiments for precise temperature control of a heat exchanger, which in turn tempered objects or media, varied.

The methods according to the invention and the devices according to the invention are explained in more detail below with reference to the accompanying schematic diagrams:

1 shows the structure of a system in which a heat exchanger is operable to the maximum refrigerant vapor temperature.

2 shows a capillary tube that acts as a distributor for the media stream.

3 shows the in 1 illustrated system in which the heat exchanger is additionally equipped with an expansion valve to increase the heating power provided by the hot gas valve through this expansion valve.

4 shows the in 1 shown system that is equipped with a condenser that can be added to the heating power of the heat exchange with its heating power.

5 shows the structure of the plant of 4 , which is equipped with a variable-temperature throttle body, which takes over the task of the throttle body with the parallel-connected hot gas valve.

6 shows the plant of 4 , in which the temperature of the heat exchanger is adjustable up to the limit temperature of the oil mixed with the refrigerant, while a characteristic number of the system, here the maximum refrigerant vapor temperature, is taken into account.

7 shows the additional heat exchanger introduced in the system circuit 6 in an enlarged view to clarify the details.

8th shows a further variant for extending the temperature range, in which the temperature of the compressor is monitored, compared to the arrangement in 6 monitors the refrigerant vapor temperature.

9 shows the thermal balance memory as a wound tube.

10 shows the thermal balance memory as a container.

1 shows the schematic structure of a system with a combination of throttle body and hot gas valve with their interaction and with the embodiments of this combination, wherein the reference variable w1 of the heat exchanger up to the maximum refrigerant vapor temperature w2, a characteristic index of the system is variable.

One at a collector 1 connected throttle body 2 , designed here as a thermostatic expansion valve, is a hot gas valve 3 at one of the branches 5 a condenser 4 is connected, connected in parallel, with an output 2 ' of the throttle body 2 and an exit 3 ' of the hot gas valve 3 in a common pipe 6 lead, this pipe 6 with a thermal balance memory 7 connected by means of a pipe 8th with an entrance 9 ' a heat exchanger 9 connected is. An exit 9 '' of the heat exchanger 9 is with a suction pipe acting as a connecting pipe 10 with a compressor 11 connected, the compressor 11 in turn by means of acting as a connecting pipe pressure line 12 with the liquefier 4 connected is. The condenser 4 is in turn with the collector 1 connected.

A temperature sensor 13 detects the temperature of the heat exchanger 9 flowing and the heat exchange surface comprising medium, for. B. air, by a fan 14 is encouraged. When passing through the temperature sensor 13 detected temperature is a mixing temperature, on the one hand to the temperature of the untreated medium, the heat load, and on the other to the temperature of the useful heat of the heat exchanger 9 , wherein the untreated medium by the treatment with the heat of the heat exchanger 9 becomes the treated medium. If the detected temperature deviates from the reference variable w1, this is done by a controller 15 operated heat exchanger 9 a temperature compensation and thus a heat demand balance by the controller 15 the hot gas valve 3 actuated. Exceeds the one on the suction line 10 applied temperature sensor 16 detected temperature the predetermined maximum refrigerant vapor temperature w2, limits the controller 15 by means of an actuator 17 the manipulated variable of the hot gas valve 3 , Due to this manipulated variable limitation, the upper setting range of the hot gas valve 3 regulated restricted. The throttle body 2 , designed here as a thermostatic expansion valve, is equipped with a sensor 18 equipped, which is also on the suction line 10 is created and also recorded the temperature. If this temperature falls below the evaporation temperature, the throttling device designed as a thermostatic expansion valve prevents it 2 among other things, that unvaporized refrigerant to the compressor 11 flowing back. A condenser fan 19 ensures the cooling of the condenser 4 and the compressor 11 ,

2 shows the in 1 in longitudinal section, in which in the meandering heat exchanger tube a reducing tube and a capillary tube are placed.

That in the heat exchanger input 9 ' inserted end of the tube 8th that seals with the heat exchanger inlet 9 ' is connected, is equipped with a reducing pipe serving as a connecting pipe 20 , which is designed as a capillary tube, on which a thermally insulating and elastic capillary tube 21 is attached. The capillary tube 21 has on its longitudinal side one or more elastic, identically designed openings 22 on and is sealed at its end and sealed with the reducer 20 in the heat exchanger 9 placed. The heat exchanger outlet 9 '' is with the suction line 10 connected.

• – drosseln den Strom, der durch das Drosselorgan 2 strömt,
• – oder drosseln den in Abhängigkeit von der Stellgröße des Heißgasventils 3 sich einstellenden Strom, der als Teilströme anteilig durch das Drosselorgan 2 und das Heißgasventil 3 strömt und im Anschluss zusammengeführt wird
• – oder drosseln den in Abhängigkeit von der Stellgröße des Heißgasventils 3 sich einstellenden Strom, der als Teilstrom durch das Heißgasventil 3 strömt,
• – oder drosseln den Strom, der durch das Heißgasventil 3 strömt.

The designed as a capillary reducing tube 20 and the at least one elastic opening 22 of the capillary tube 21

• - throttle the current passing through the throttle 2 flows,
• - Or throttle the function of the manipulated variable of the hot gas valve 3 adjusting current, which as part of streams proportionately through the throttle body 2 and the hot gas valve 3 flows and then merged
• - Or throttle the function of the manipulated variable of the hot gas valve 3 self-adjusting current, acting as a partial flow through the hot gas valve 3 flows,
• - or throttle the flow through the hot gas valve 3 flows.

Due to the throttling of the flow through the reducing tube 20 and on the other hand by the degree of opening of the at least one elastic opening 22 in the capillary tube 21 turns in the reducer tube 20 and in the capillary tube 21 a pressure. The refrigerant mass flow and / or the superheated steam flow through the reducing tube 20 in the thermally insulating capillary tube 21 initiated, the capillary tube 21 by means of the openings 22 which is alongside the capillary tube 21 are attached, for a uniform distribution of the refrigerant mass flow and / or the superheated steam flow in the heat exchanger 9 , designed here as a heat exchanger tube, ensures. In addition, the degree of at least one opening fits 22 the pressure caused by the throttling of the capillary tube 21 initiated, ie, the degrees of opening vary depending on the pressure, which ensures that in each case an equal amount of refrigerant or refrigerant superheated steam or superheated steam through the identically shaped openings 22 of the capillary tube 21 in the heat exchanger 9 exit. Accordingly, the refrigerant mass flow and / or the hot steam volume flow along the heat exchanger tube is evenly distributed and divided, resulting in a uniformly tempered heat exchange surface.

3 shows the in 1 illustrated plant, which is extended at the output of the heat exchanger to an expansion valve.

In the 1 shown system is extended by one from the controller 15 actuated expansion valve 23 that is between the outlet of the heat exchanger 9 and the compressor 11 is arranged, and a pressure sensor 24 who is between the collector 1 and designed as a thermostatic expansion valve throttle body 2 is arranged. Part of the suction line 10 is designed here as a heat exchanger in the form of a heat exchanger tube.

By the hot gas valve 3 in the heat exchanger 9 introduced hot steam volume flow, the heat of the superheated superheated steam from the heat exchanger 9 provided as heating power. With open hot gas valve 3 and by closing the expansion valve 23 will the pressure in the heat exchange 9 influenced, which the heat exchanger 9 can also be operated in the operation of a condenser, so that in addition to the specific heat capacity of the superheated steam flow rate, the specific heat of condensation of the hot steam flow rate can be used by the heat exchanger. The heat exchanger 9 is thus extended by the operation of a condenser, so that it can be used in the operation either as an evaporator or as a heat exchanger or as a condenser. By the heat exchanger 9 placed capillary tube 21 with its at least one elastic opening 22 During cooling and heating operation, a uniform distribution and distribution of the refrigerant mass flow and / or superheated steam flow is ensured, which in the heating operation, which takes place by means of the heat of the superheated steam, to a uniformly tempered heat exchange surface of the heat exchanger 9 leads.

By means of the regulator 15 operated hot gas valve 3 and also from the regulator 15 actuated expansion valve 23 is the heat exchanger 9 operable as evaporator-heat exchanger condenser. In case of deviation from the temperature sensor 13 detected temperature to the reference variable w1 takes place through the heat exchanger 9 by means of the regulator 15 a temperature compensation by the controller 15 sequentially the hot gas valve 3 and the expansion valve 23 operated, ie at the largest possible manipulated variable of the expansion valve 23 First, the hot gas valve 3 actuated and subsequently with the largest possible manipulated variable of the hot gas valve 3 the expansion valve 23 operated and vice versa, if necessary, the control sense reverses and the sequence of actuation of the manipulated variables of the hot gas valve 3 and the expansion valve 23 takes place in reverse order.

To the in 1 described functions or tasks occur further tasks, by the controller 15 be taken over. Below that of the temperature sensor 16 detected temperature in the normal operation located expansion valve 23 and with the largest possible manipulated variable of the hot gas valve 3 a once pre-determined evaporation temperature w3, determines the controller 15 a minimum manipulated variable of the expansion valve 23 for the regulatory restriction of the lower actuating range of the expansion valve 23 , Because of the temperature sensor 16 detected evaporation temperature is paired with the evaporation pressure, the task of limiting the expansion valve 23 additionally carried out by the detection of a pressure and a once predetermined evaporation pressure w3 '. Below that of another on the suction line 10 arranged pressure sensor detected pressure the predetermined evaporation pressure w3 'determines the controller 15 a minimum manipulated variable of the expansion valve 23 , Which means by means of this specific manipulated variable of the lower actuating range of the expansion valve 23 additionally regulated. Below the pressure sensor 24 detected pressure a once predetermined condensing pressure w4, determines the controller 15 a further minimum manipulated variable of the hot gas valve 3 to the manipulated variable of the hot gas valve 3 that from the regulator 15 by means of the maximum refrigerant steam temperature w2 and that of the temperature sensor 16 detected temperature is determined, the controller 15 from the two manipulated variables of the hot gas valve 3 uses the smaller manipulated variable to limit the same to the upper control range of the hot gas valve 3 regulate restricting.

A further embodiment for operating and thus for controlling the temperature of the heat exchanger 9 both by pressing the hot gas valve 3 as well as by operating the expansion valve 23 through the regulator 15 provides that if a previously set upper threshold value is exceeded, w5 _{OE will be} in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 and in case of deviation by the temperature sensor 16 detected temperature at the pre-determined evaporation temperature w3, the controller 15 the manipulated variable of the expansion valve 23 changed until the detected temperature is equalized to the evaporation temperature w3. The regulator 15 adjusts the expansion valve 23 depending on the temperature sensor 16 detected temperature and the once predetermined evaporation temperature w3, since the evaporation temperature w3 with the evaporation pressure w3 'is paired, the controller adjusts 15 the expansion valve 23 in addition, depending on the one by another on the suction line 10 arranged pressure sensor detected pressure and the once predetermined vaporizing pressure w3 '. In addition, continue to be from the controller 15 limited manipulated variables of the hot gas valve 3 effective, wherein one of the control variables is determined when the temperature sensor 16 detected temperature exceeds the maximum refrigerant temperature w2, another variable is determined when the pressure from the sensor 24 detected pressure falls below a condensing pressure w4, wherein the controller 15 from the two specific variables of the hot gas valve 3 the smaller manipulated variable for manipulated variable limiting uses the upper setting range of the hot gas valve 3 regulate restricting.

If a previously set lower response value w5 _{UE is} fallen below in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 the reset of the expansion valve takes place 23 through the regulator 15 ,

4 shows the in 1 illustrated plant, which is extended with a condenser.

A liquefier 25 is either part of the heat exchanger 9 or is, as here, the heat exchanger 9 placed. A three-way valve used as a distribution valve 26 that from the regulator 15 is pressed, is with the compressor 11 , the hot gas valve 3 also from the regulator 15 is actuated, the condenser 4 and the liquefier 25 connected. A three-way valve entry 26 ' and the hot gas valve 3 are by means of the pressure line 12 to the compressor 11 connected. The condenser 25 is on the one hand with a three-way valve outlet 26 '' and on the other hand with the inlet to the condenser 4 and a three-way valve exit 26 ''' connected. The condenser 25 is like the heat exchanger 9 equipped with a capillary tube provided with at least one opening, for a uniform distribution of material or current distribution in the condenser 25 provides.

The extension is also included 3 applicable.

Is the heating demand greater than the heating power, by means of the manipulated variable of the actuator from the hot gas valve 3 and / or the manipulated variable of the actuator from the expansion valve 23 through the heat exchanger 9 is achievable, ie is the once set in advance upper threshold w5 _OD in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 exceeded, the controller switches 15 the three-way valve 26 around, thereby providing additional heating power through the condenser 25 is switched, it is the three-way valve entry 26 ' to the three-way valve outlet 26 '' opened and thus this flow path switched through and the three-way valve inlet 26 ' to the three-way valve outlet 26 ''' is closed and thus blocked this flow path.

In addition, the controller compares 15 from the pressure sensor 24 detected pressure with the once predetermined condensing pressure w4 _D , which is greater than the condensing pressure w4. If the detected pressure falls below the condensing pressure w4 _D , the controller changes 15 the manipulated variable of the three-way valve 26 and thus limits the upper range of the three-way valve 26 one.

If the value falls below a previously set lower threshold w5 _UD in the setting range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 the provision of the three-way valve takes place 26 through the regulator 15 , this is the three-way valve entry 26 ' to the three-way valve outlet 26 '' closed and thus this flow path blocked and the three-way valve inlet 26 ' to the three-way valve outlet 26 ''' is opened and thus the flow path switched through, so that is the heat output from the condenser 25 off.

The hot steam volume flow flows when connecting the condenser 25 through the liquefier 25 and in the course of the condenser 4 , The temperature compensation takes place with the condenser switched on and off 25 through the regulator 15 by pressing the hot gas valve 3 and / or the expansion valve 23 operated heat exchanger 9 , Through that into the condenser 25 introduced capillary tube is a uniformly tempered heat exchange surface of the condenser 25 given. Functions of 1 and 3 are also effective.

Another embodiment with a further control concept for operating the condenser 25 through the regulator 15 provides that the regulator 15 the manipulated variable of the three-way valve 26 successively gradual changes by clocks, resulting in a gradual increase or decrease of the condenser 25 guided stream and thus to a constantly similar heating power through the condenser 25 leads. The condenser 25 is from a three-way valve 26 from the flow path from the three-way valve inlet 26 ' to the three-way valve outlet 26 ''' is operated, operated in such a way that when exceeding the once set upper threshold value w5 _OD in the control range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 the regulator 15 the three-way valve 26 Pressed with a clock, causing the flow through the condenser 25 increased by one level. Thereafter, the temperature compensation is carried out by the controller 15 by means of the hot gas valve 3 and / or the expansion valve 23 operated heat exchanger 9 , Is after an interval that of the temperature sensor 13 detected temperature of heat exchanger 9 , Liquefier 25 thermally settled, and is the upper threshold w5 _OD in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 permanently below the cycle, or are the cycles completed, otherwise the process continues until the upper response value w5 _OD in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 permanently undercut or the three-way valve 26 converted. If, due to the carried out temperature compensation, the once predetermined lower response value w5 _{UD is} in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 falls below, it comes from the regulator 15 operated three-way valve 26 to a reversal of the sense of action, this is continued at alternating clock and interval, this reversal until the lower threshold w5 _UD in the adjustment range of the hot gas valve 3 through the hot gas valve 3 permanently exceeded or the three-way valve 26 is returned to the original position. In this control by successive switching is the mentioned function of the control variable limit of the three-way valve 26 or the limitation of its opening degree also effective. Functions of 1 and 3 are also effective here.

A further extended embodiment with a further expedient control concept for operating the liquefier 25 through the regulator 15 is that the regulator 15 from the pressure sensor 24 detected pressure compared with the once predetermined condensing pressure w4 _D , in case of deviation of the detected pressure by the controller 15 adapted to the condensing pressure w4 _D by the controller 15 the manipulated variable of the three-way valve 26 modifies and so performs a pressure equalization. The condenser 25 is from the regulator 15 operated in such a way that when exceeding the once predetermined upper threshold value w5 _OD in the control range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 the regulator 15 from the pressure sensor 24 the pressure measured adjusts to the condensing pressure w4 _D and thus regulates the pressure, thus the connection is the heating capacity of the condenser 25 to the heat output of the heat exchanger 9 Voted. Here, the condensing pressure w4 _{D is} greater than the condensing pressure w4. In case of deviation from the temperature sensor 13 detected temperature of heat exchanger 9 , Liquefier 25 and heat load to the reference variable w1, the temperature compensation by the controller 15 operated heat exchanger 9 by actuating the hot gas valve 3 and / or the expansion valve 23 , If the lower response value of the manipulated variable w5 _{UD is not reached} in the adjustment range of the hot gas valve 3 by the manipulated variable of the hot gas valve 3 the pressure control is taken out of service, the regulator 15 the three-way valve 26 in the original position with through-flow path from the three-way valve inlet 26 ' to the three-way valve outlet 26 ''' returns. In this scheme of keeping constant from the pressure sensor 24 detected pressure with the condensing pressure w4 _D is the mentioned function of the manipulated variable limiting the three-way valve 26 or the limitation of its opening degree already taken into account. In addition, the functions of 1 and 3 effective.

5 shows in another embodiment the in 4 shown heat exchanger, which is tempered by means of a variable-temperature throttle body.

One from the regulator 15 actuated variable-temperature throttle element 27 occurs in place of 4 shown parallel connection of the designed as a thermostatic expansion valve throttle body 2 with the regulator 15 operated hot gas valve 3 , and takes over the task of these two parallel organs. That on the heat exchanger 9 coordinated variable-temperature throttle body 27 consists of one from the regulator 15 operated, adjustable heating 28 , preferably an electrothermal transducer, in a thermally conductive cylinder 29 is placed, and from a capillary tube 30 that around the thermally conductive cylinder 29 is wound, preferably soldered, and is so thermally connected to it.

The entrance of the temperable capillary tube 30 is with the collector 1 connected, the outlet is with the reducer tube 20 ( 2 ), wherein the reducing tube 20 ( 2 ) with the thermally insulating capillary tube 21 ( 2 ), both in the heat exchanger 9 are placed, the end of the capillary tube 30 is with the heat exchanger input 9 ' sealingly connected. The evaporation temperature is controlled by the variably temperature-controllable throttle 27 , the reducer tube 20 and the one or more openings 22 of the capillary tube 21 certainly. Their condition leads to a temperature and a power, which on the heat exchanger 9 are tuned, also be determined by determining the degree of throttling of the variable-temperature throttle body 27 and by determining the nature of the Reduzierrohrs 20 and by determining the degree of opening of the one or more openings 22 of the capillary tube 21 these to the heat exchanger 9 customized.

The capillary tube 30 and the refrigerant mass flow flowing through this are provided by the controllable heating 28 tempered, with the heating 28 through the regulator 15 is preferably operated with continuous control, which is a continuous change in performance of the heat exchanger 9 causes. The tempered refrigerant mass flow is in the heat exchanger 9 placed thermally insulating capillary tube 21 ( 2 ) and there by means of the capillary tube 21 ( 2 ) located, at least one elastic opening 22 ( 2 ) in the heat exchanger 9 distributed and split, ie sprayed. The controller monitors this 15 by means of the temperature sensor 16 the detected temperature. If the detected temperature exceeds the maximum refrigerant steam temperature w2, the controller limits 15 the manipulated variable of the heating 28 or the heating power.

In addition, the functions of 4 effective.

In 6 will the in 4 shown plant extended by a device, so that the reference variable w1 to the limit temperature w6 of the refrigerant mixed foreign mixture, here oil, is variable, while a key figure of the system, the maximum refrigerant vapor temperature w2, is taken into account.

• – ein variabel temperierbares Drosselorgan 31, bestehend aus einem Kapillarrohr 32, das um einen thermisch leitenden Zylinder 33 gewickelt und mechanisch und thermisch mit ihm verbunden ist, wobei im Zylinder 33 eine regelbare Heizung 34, vorzugsweise ein elektrothermischer Wandler, platziert ist,
• – ein Ventil 35,
• – einen Wärmeaustauscher 36, der als Wärmeaustauscherrohr ausgestaltet im Stoffkreislauf der Saugleitung 10 angeordnet ist. Der Wärmeaustauscher 36 (7) verfügt über einen weiteren Zugang, der als ein Rohr 37 (7) ausgestaltet ist. Das Rohr 37 führt einerseits in das Innere des Wärmeaustauschers 36 (7) und ist mit diesem abdichtend verbunden, und ist andererseits mit dem Ventil 35 verbunden. Im Innern des Wärmeaustauschers 36 (7) ist am Rohr 37 (7) als Verbindungsrohr ein als Kapillarrohr ausgestaltetes Reduzierrohr 38 (7) angeschlossen, an dem ein mit ein oder mehreren elastischen, gleich gestalteten Öffnungen 39 (7) versehenes, thermisch isolierendes und elastisches Kapillarrohr 40 (7) angeschlossen ist, dessen Ende dichtend verschlossen ist,
• – ein Ventil 41 und
• – eine regelbare Heizung 42, vorzugsweise ein elektrothermischer Wandler, die entweder im Wärmeaustauscher 9 platziert oder, wie hier in 6 dargestellt, separat angeordnet ist.

In the 4 shown plant is extended to

• - A variably temperature-adjustable throttle body 31 consisting of a capillary tube 32 that is a thermally conductive cylinder 33 wound and mechanically and thermally connected to it, being in the cylinder 33 a controllable heating 34 , preferably an electrothermal transducer, is placed,
• - a valve 35 .
• - a heat exchanger 36 , which is designed as a heat exchanger tube in the material cycle of the suction line 10 is arranged. The heat exchanger 36 ( 7 ) has another access, which acts as a pipe 37 ( 7 ) is configured. The pipe 37 On the one hand leads into the interior of the heat exchanger 36 ( 7 ) and is sealingly connected thereto, and on the other hand with the valve 35 connected. Inside the heat exchanger 36 ( 7 ) is on the pipe 37 ( 7 ) as a connecting tube designed as a capillary Reduzierrohr 38 ( 7 ) connected to the one with one or more elastic, identically designed openings 39 ( 7 ) provided, thermally insulating and elastic capillary tube 40 ( 7 ) is connected, whose end is sealed,
• - a valve 41 and
• - a controllable heating 42 , preferably an electrothermal transducer, either in the heat exchanger 9 placed or, as here in 6 shown, is arranged separately.

The entrance of the capillary tube 32 , the part of the regulator 15 actuated variable-temperature throttle body 31 is, is at the exit of the collector 1 connected, the output of the capillary tube 32 is on from the regulator 15 operated valve 35 connected, which in turn with the pipe 37 connected is. Between pipe 6 and pipe 8th is the thermal balance memory 7 , the one from the regulator 15 operated valve 41 on the one hand on the pipe 6 and on the other hand with a pipe 43 at the thermal balance memory 7 connected. The monitoring of the refrigerant vapor temperature is carried out by the controller 15 by means of two temperature sensors 16 ' and 16 '' , which on the suction line 10 are attached. The extension is also included 3 applicable.

The reference variable w1 here is greater than the respective characteristic number of the system, here the maximum refrigerant vapor temperature w2, whereby, however, the characteristics of the system for the protection of the system are taken into account in the inventive method. The reference variable w1 is variable up to the limit temperature w6 of the oil mixed with the refrigerant, wherein the temperature of the in the suction line 10 to the compressor 11 flowing refrigerant vapor from the controller 15 by means of the temperature sensor 16 ' and 16 '' monitored and possibly limited, so that the maximum refrigerant vapor temperature w2 is not exceeded.

• – die vom Regler 15 ermittelte Differenz zwischen der vom Temperaturfühler 13 erfassten Temperatur, die kleiner als die Führungsgröße w1 ist, und der Führungsgröße w1, wobei aus dieser Temperaturdifferenz ein Heizbedarf resultiert, durch die vom Regler 15 betriebene regelbare Heizung 42 ausgeglichen wird, wobei der Verdichter 11 bei geschlossenen Ventilen 35 und 41 den Kältemitteldampf absaugt und sich anschließend automatisch abschaltet,
• – die vom Regler 15 ermittelte geringe Differenz zwischen der vom Temperaturfühler 13 erfassten Temperatur, die größer als die Führungsgröße w1 ist, und der Führungsgröße w1, wobei aus dieser Temperaturdifferenz ein geringer Kühlbedarf resultiert, durch den vom Regler 15 betriebenen Wärmeaustauscher 9 ausgeglichen wird, indem der Regler 15 bei maximal geöffnetem Heißgasventil 3, hierbei ist bei größtmöglicher Stellgröße des Heißgasventils 3 die erfasste Temperatur sodann kleiner als die Führungsgröße w1, in Abhängigkeit von der Temperaturdifferenz das Ventil 41 mittels Pulsbreitensteuerung mit variabler Einschaltdauer oder Pulsfolgensteuerung mit variabler Periodendauer betätigt,
• – die vom Regler 15 ermittelte Differenz zwischen der vom Temperaturfühler 13 erfassten Temperatur, die größer als die Führungsgröße w1 ist, und der Führungsgröße w1, wobei aus dieser Temperaturdifferenz ein Kühlbedarf resultiert, durch den vom Regler 15 betriebenen Wärmeaustauscher 9 mittels des Heißgasventils 3 ausgeglichen wird, dies bei einem Pulsbreitenverhältnis, bei welchem die Einschaltdauer der Pulsbreitensteuerung gleich der Periodendauer ist, oder einem Pulsfolgenverhältnis, bei welchem die Periodendauer der Pulsfolgensteuerung gleich der Einschaltdauer ist, so dass folglich das Ventil 41 andauernd geöffnet ist.

The regulator 15 selects the appropriate apparatus or devices as needed, such as the heat exchanger 9 and / or the liquefier 25 and / or the heating 40 , and operates these, the control, here as a P-controller with a permanent control deviation, is shown here. In the case of a reference variable w1, in this extended temperature range, the temperature compensation and consequently the power compensation are regulated in such a way that

• - from the regulator 15 determined difference between the temperature sensor 13 detected temperature, which is smaller than the reference variable w1, and the reference variable w1, resulting from this temperature difference, a heating demand, by the controller 15 operated controllable heating 42 is compensated, the compressor 11 with closed valves 35 and 41 sucks the refrigerant vapor and then automatically shuts off,
• - from the regulator 15 determined small difference between that of the temperature sensor 13 detected temperature, which is greater than the reference variable w1, and the reference variable w1, resulting from this temperature difference low cooling demand, by the controller 15 operated heat exchanger 9 is compensated by the regulator 15 at maximum open hot gas valve 3 , this is the largest possible manipulated variable of the hot gas valve 3 the detected temperature then smaller than the reference variable w1, depending on the temperature difference, the valve 41 operated by means of variable duty cycle pulse width control or variable cycle duration pulse train control,
• - from the regulator 15 determined difference between the temperature sensor 13 detected temperature, which is greater than the reference variable w1, and the reference variable w1, resulting from this temperature difference, a cooling demand, by the controller 15 operated heat exchanger 9 by means of the hot gas valve 3 is balanced, this at a pulse width ratio in which the duty cycle of the pulse width control is equal to the period duration, or a pulse train ratio at which the period of the pulse train control is equal to the duty cycle, so that consequently the valve 41 is constantly open.

Another embodiment with a control concept to compensate for a low cooling demand by a Nutzkälte provides that when the valve is open 41 and with the largest possible control variable of the hot gas valve 3 those from the heat exchanger 9 provided power, here a cooling capacity, by the adjustable heating 42 provided heating power thermally balanced or on the low cooling requirement is adjusted, resulting in a thermal equilibrium between cooling capacity, heating capacity and the cooling demand, with the controllable heating 42 the temperature compensation and thus the power compensation is performed.

The control device is equipped with a device for monitoring the predetermined maximum refrigerant steam temperature w2, which is based on the refrigerant vapor temperature when entering the compressor 11 refers. Exceeds that of the temperature sensor 16 ' detected temperature, the maximum refrigerant vapor temperature w2, the controller opens 15 on the one hand the valve 35 , second, the regulator takes 15 the temperature control of the heat exchanger 36 in operation by the regulator 15 in case of deviation from the temperature sensor 16 '' detected temperature to the maximum refrigerant vapor temperature w2 variable-temperature throttle body 31 actuated and equalizes the detected temperature to the maximum refrigerant vapor temperature w2. The heat exchanger 36 tempered in the compressor 11 inflowing refrigerant vapor, ie in the present case, the in the compressor 11 incoming refrigerant vapor cooled, so that from the temperature sensor 16 '' detected temperature is equal to the maximum refrigerant vapor temperature w2. The main components of variable-temperature throttle body 31 are the adjustable heating 34 as well as with the adjustable heating 34 thermally coupled capillary tube 32 , where the adjustable heating 34 the refrigerant mass flow in the capillary tube 32 tempered. At the same time, the regulator 15 operated open valve 35 the temperature-controlled refrigerant mass flow through the pipe 37 ( 7 ) and the reducing tube 38 ( 7 ) in the thermally insulating capillary tube 40 ( 7 ) and through the at least one elastic opening 39 ( 7 ) in the heat exchanger 36 ( 7 ) sprayed, while in the heat exchanger 36 ( 7 ) spent refrigerant evaporated. At the same time the heat exchanger 9 in the heat exchanger 36 ( 7 ) inflowing refrigerant vapor is added to this evaporating refrigerant, whereby the refrigerant vapor of the heat exchanger 9 in the heat exchanger 36 ( 7 ) is tempered. The mixed refrigerant vapor then flows into the compressor 11 one. Below that of the temperature sensor 16 ' detected temperature, the maximum refrigerant vapor temperature w2, the controller decreases 15 the temperature control of the heat exchanger 36 , in which the inflowing refrigerant vapor is tempered, out of operation by the controller 15 the valve 35 closes and the variable temperature throttle body 31 decommissioned. This process for controlling the temperature of the refrigerant vapor does not exceed the maximum refrigerant steam temperature w2, so that the parameters of the system for protecting the system are taken into account. So that of the temperature sensor 16 ' If the temperature detected does not exceed the limit temperature w6, then the manipulated variable in control mode is also limited.

The functions mentioned in the other figures, such as the manipulated variable limit of the three-way valve 26 , the manipulated variable limit of the valve 23 ( 3 ) and others are also effective.

8th shows a further embodiment with embodiments in addition to 6 in which a characteristic number, the predetermined maximum compressor temperature w7, is taken into account and the reference variable w1 is variable up to the limit temperature w7 of the compressor.

The predetermined maximum compressor temperature w7 determines the maximum temperature of the compressor 11 , The pipe end 37 ( 7 ), the reducer tube 38 ( 7 ) and the capillary tube 40 ( 7 ) are in the oil of the compressor 11 placed.

Is the maximum compressor temperature w7 from that of a temperature sensor 44 detected temperature exceeded, the controller operates 15 for balancing and limiting the detected temperature, the variable-temperature throttle body 31 , where the adjustable heating 34 the capillary tube 32 and thus the refrigerant mass flow in the capillary tube 32 tempered. At the same time the controller opens 15 the valve 35 , so that the tempered refrigerant mass flow means of the tube 37 and the reducing tube 38 ( 7 ) in the capillary tube 40 ( 7 ) is introduced and through the at least one opening 39 ( 7 ) of the capillary tube 40 ( 7 ) directly into the oil of the compressor 11 leaking, which has the consequence that the oil immediately and the compressor 11 tempered indirectly or cooled here. In this case, the amount and temperature of the introduced refrigerant mass flow are kept constant to the evaporation performance of the variable-temperature throttle body 31 for cooling the oil is dimensioned such that liquid blows to the compressor 11 be avoided to keep constant.

Is the maximum temperature w7 from that of the temperature sensor 44 detected temperature, the controller deactivates 15 the temperature-controllable throttle body 31 and closes the valve 35 , So that of the temperature sensor 44 ' If the temperature detected does not exceed the limit temperature w7, the manipulated variable in control mode is also limited.

The in the 1 . 3 . 4 . 6 and 8th shown schematically thermal compensation memory are in 9 as a wrapped tube and in 10 shown as a container.

The in 9 outlined thermal equalization memory 7 , designed as a tube 45 , preferably made of a material with a favorable thermal thermal conductivity, such as copper, has by its length a large contact surface and thus provides a thermal balance between hot steam volume and refrigerant mass flow. This as a thermal compensation memory 7 space-saving wound pipe 45 is how in 1 . 3 and 4 shown with the tube 6 or as in 6 and 8th shown with the tube 43 and the tube 8th connected.

In 10 is the thermal equalization memory 7 as a container 46 configured with a small volume of space, wherein the container 46 with a content material 47 is filled, which consists of a material with a favorable thermal thermal conductivity, the amount of which is such that it ensures the thermal balance between hot steam volume and refrigerant mass flow. The container 46 is how in 1 . 3 and 4 shown on the pipe 6 or as in 6 and 8th shown on the pipe 43 and on the pipe 8th connected, wherein the permeable for the refrigerant superheated steam mass flow gauze 48 the emptying of the content material 47 from the container 46 in the pipe 6 or in the pipe 43 as well as in the pipe 8th prevented.

LIST OF REFERENCE NUMBERS

1

collector

2

throttle member

2 '

Output of the throttle body

3

Hot gas valve

3 '

Output of the hot gas valve

4

condenser

5

junction

6

pipe

7

Thermal equalization memory

8th

pipe

9

heat exchangers

9 '

Wärmeaustauschereingang

9 ''

Wärmeaustauscherausgang

10

suction

11

compressor

12

pressure line

13

temperature sensor

14

fan

15

regulator

16

temperature sensor

16 '

temperature sensor

16 ''

temperature sensor

17

actuator

18

sensor

19

Condenser

20

reducing tube

21

capillary

22

opening

23

expansion valve

24

pressure sensor

25

condenser

26

Three-way valve

26 '

Dreiwegventileintritt

26 ''

Dreiwegventilaustritt

26 '' '

Dreiwegventilaustritt

 27

throttle member

28

heater

29

cylinder

30

capillary

31

throttle member

32

capillary

33

cylinder

34

heater

35

Valve

36

heat exchangers

37

pipe

38

reducing tube

39

opening

40

capillary

41

Valve

42

heater

43

pipe

44

temperature sensor

44 '

temperature sensor

45

pipe

46

container

47

content material

48

gauze

Claims (39)

Method for controlling the temperature of a heat exchanger ( 9 ) with uniformly tempered heat exchange surface in the application in direct evaporation plants, in which the temperature and the power through a hot gas valve ( 3 ), wherein a hot steam volume flow, which after an adjustable hot gas valve ( 3 ) is available, and a mass flow of refrigerant, which after a throttle body ( 2 ) are used, by means of a combination consisting of the throttle body ( 2 ), with the throttle body ( 2 ) parallel, adjustable hot gas valve ( 3 ) and a throttle body ( 2 ) and the hot gas valve ( 3 ) downstream reducing tube ( 20 ) and a reducing tube ( 20 ) downstream capillary tube ( 21 ), by means of their interaction and their configurations and at setting values of the hot gas valve, to generate a determinable current which determines the temperature and the output of a heat exchanger ( 9 ), wherein the generated current as a function of the manipulated variable of the hot gas valve ( 3 ), this dependency is established by means of the combination, by combining an output ( 2 ' ) of the throttle body ( 2 ) with an output ( 3 ' ) of the hot gas valve ( 3 ) and with manipulated variables of the Hot gas valve ( 3 ) adjusts the current, which in a thermal balance memory ( 7 ) and in the course in the to the throttle body ( 2 ) and the hot gas valve ( 3 ) tuned capillary tube ( 21 ) with its at least one elastic opening ( 22 ) to which the reducing tube ( 20 ) is introduced, wherein the reducing tube ( 20 ) and the capillary tube ( 21 ) ensure that the flow is throttled, due to this throttling, a pressure in the reducing tube ( 20 ) and in the capillary tube ( 21 ), so this pressure is functionally dependent on the manipulated variable of the hot gas valve ( 3 ), whereas the one at the output ( 2 ' ) of the throttle body ( 2 ) occurring pressure also functionally the degree of throttling of the throttle body ( 2 ), so that, depending on the manipulated variables of the hot gas valve ( 3 ) adjusts a current that consists of either a refrigerant mass flow, or a current that results from the mixing of the hot steam volume flow to the refrigerant mass flow, these two streams are united by the pressure, optionally takes place between these two streams by means of the thermal compensating memory ( 7 ) a heat exchange, or a stream consisting of a hot steam volume flow, accordingly varies by changing the manipulated variable of the hot gas valve ( 3 ) the current, with closed hot gas valve ( 3 ), the largest possible refrigerant mass flow occurs, with constant opening of the hot gas valve ( 3 ), the hot steam volume flow increases continuously, which leads to the continuous decrease of the refrigerant mass flow up to the stagnation of the same, with continued continuous opening of the hot gas valve ( 3 ), after the refrigerant mass flow is already interrupted, the hot steam volume flow continues to increase continuously, with fully open hot gas valve ( 3 ) sets the largest possible hot steam volume flow, this process behaves accordingly inversely with the continuous closing of the hot gas valve ( 3 ), the reducing tube ( 20 ) and the capillary tube ( 21 ) are in the heat exchanger ( 9 ), whereby the length of the capillary tube ( 21 ) largely the tube length of the heat exchanger ( 9 ), which is designed as a meandering tube corresponds, which by the manipulated variable of the hot gas valve ( 3 ) adjusting current is through the reducing tube ( 20 ) in the heat exchanger ( 9 ) placed capillary tube ( 21 ), through which long side in the capillary tube ( 21 ) arranged at intervals, identically designed elastic openings ( 22 ) enter equally large partial flows in the heat exchanger ( 9 ), so that the current in the heat exchanger ( 9 ) is distributed uniformly along the heat exchanger tube, moreover, the pressure influences the degree of opening of the at least one opening ( 22 ) in the capillary tube ( 21 ), so that these openings ( 22 ) act as pressure-adjusting nozzles, so that upon entry of the refrigerant mass flow or the superheated steam flow into the heat exchanger ( 9 ) through the one or more identically designed openings ( 22 ) is caused, that this a current in the states with equal amounts in the heat exchanger ( 9 ) as mass flow parts through the openings ( 22 ) and thereby atomized, or that this is a stream as volume flow parts through the openings ( 22 ) flows and thereby relaxes, thus ensures the capillary tube ( 21 ) due to its uniformly shaped openings ( 22 ) at different sized currents, which depends on the manipulated variable of the hot gas valve ( 3 ) for a uniform and thus optimal current distribution through these openings ( 22 ) with a correspondingly uniform and thus optimal distribution of power in the heat exchanger ( 9 ), resulting in a uniform temperature of the heat exchanger tube and consequently a uniformly tempered heat exchange surface of the heat exchanger ( 9 ), wherein the manipulated variable of the hot gas valve ( 3 ) Influence on the condition and quantity of the reducer ( 20 ) and the capillary tube ( 21 ) and subsequently into the heat exchanger ( 9 ) introduced stream, so that in addition to a uniform temperature of the heat exchanger ( 9 ) the temperature and the capacity of the heat exchanger ( 9 ) are determinable, whereby in the case of deviation, the continuous flow of a temperature sensor ( 13 ) to a reference variable w1 the detected temperature is adjusted to the reference variable w1 by a controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) performs the temperature and power compensation, whereby by the adjustment range of the hot gas valve ( 3 ) resulting temperature range of the heat exchanger ( 9 ) extends from the evaporation temperature as the lowest temperature to the maximum refrigerant steam temperature w2 as a high temperature, wherein the evaporation temperature is determined by the throttle body ( 2 ), the reducing tube ( 20 ) and the one or more openings ( 22 ) of the capillary tube ( 21 ), the nature of which leads to a temperature and a power acting on the heat exchanger ( 9 ), and by determining the degree of throttling of the throttle body ( 2 ) and by determining the nature of the reducing tube ( 20 ) and by determining the degree of opening of the one or more openings ( 22 ) of the capillary tube ( 21 ) to the heat exchanger ( 9 ), wherein the maximum refrigerant vapor temperature w2 is determined by the hot gas valve ( 3 ), the reducing tube ( 20 ) and the one or more openings ( 22 ) of the capillary tube ( 21 ), whose temperature and performance resulting from their nature are applied to the heat exchanger ( 9 ), in addition, the temperature of the compressor ( 11 ) sucked refrigerant vapor to the maximum refrigerant vapor temperature w2 limiting adapted by one hand, the hot gas valve ( 3 ) in front of a condenser ( 4 ) or with a branch ( 5 ) of the liquefier ( 4 ) and on the other hand, the manipulated variable of the hot gas valve ( 3 ) through the regulator ( 15 ) is adjusted by the controller ( 15 ) with another, on the suction line ( 10 ) arranged temperature sensor ( 16 ) continuously detects the temperature, the detected temperature exceeds the maximum refrigerant vapor temperature w2, the controller is similar ( 15 ) the detected temperature to the maximum refrigerant vapor temperature w2 by the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) and thus the upper adjustment range of the hot gas valve ( 3 ) regulating restricts, thus is in the adjustment range of the hot gas valve ( 3 ) the heat exchanger ( 9 ) can be used both for cooling and for heating, whereby the 15 ) actuated hot gas valve ( 3 ) with continuous temperature control a continuous change in performance with change of use of the heat exchanger ( 9 ) from cooling to heating and vice versa, resulting in a uniform, precise temperature control of the heat exchanger ( 9 ) leads. Method according to the preceding claim 1, wherein the object of the throttle body ( 2 ), the throttling is done by a thermostatic expansion valve. Method according to the preceding claim 1, wherein the object of the throttle body ( 2 ), the throttling is done by an automatic expansion valve. Method according to the preceding claim 1, wherein the object of the throttle body ( 2 ), the throttling, through a capillary tube. Method according to the preceding claim 1, wherein the object of the throttle body ( 2 ), the throttling, by one from the regulator ( 15 ) operated electronic expansion valve, wherein the expansion valve to also from the controller ( 15 ) actuated hot gas valve ( 3 ) is operated inversely. Method according to one of the preceding claims 1 to 5, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 of the controller ( 15 ) operated heat exchangers ( 9 ) adjusts the detected temperature to the reference variable w1, the controller ( 15 ) the actuators, the hot gas valve ( 3 ) and an expansion valve ( 23 ), operated in sequence, so that the temperature compensation either by the manipulated variable modification of the hot gas valve ( 3 ) or by the manipulated variable modification of the expansion valve ( 23 ), wherein at the largest possible manipulated variable of the hot gas valve ( 3 ) and the normally open expansion valve ( 23 ) the regulator ( 15 ) through the temperature sensor ( 16 ) compares detected temperature with an evaporation temperature w3, the detected temperature falls below the evaporation temperature w3, the controller is similar ( 15 ) the detected temperature to the evaporation temperature w3 by the controller ( 15 ) the manipulated variable of the expansion valve ( 23 ) and thus the lower adjustment range of the expansion valve ( 23 ) regulates, falls below that of a pressure sensor ( 24 ) detected pressure condensing pressure w4, determines the controller ( 15 ) a further minimum manipulated variable of the hot gas valve ( 3 ) to the manipulated variable of the hot gas valve ( 3 ), by the controller ( 15 ) by means of the maximum refrigerant vapor temperature w2 and the temperature sensor ( 16 ) is determined, wherein the controller ( 15 ) from the two manipulated variables, the smaller manipulated variable of the hot gas valve ( 3 ) to limit it by the controller ( 15 ) by means of the smaller manipulated variable, the manipulated variable of the hot gas valve ( 3 ) and thus the upper adjustment range of the hot gas valve ( 3 ) regulatory limits. Method according to one of the preceding claims 1 to 5, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) adjusts the detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein - when exceeding an upper threshold value w5 _OE in the control range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) through the temperature sensor ( 16 ) compares detected temperature with an evaporation temperature w3, with a difference between the detected temperature and the evaporation temperature w3, the controller is similar ( 15 ) by manipulated variable modification of the expansion valve ( 23 ) the detected temperature to the evaporation temperature w3, wherein when falling below a condensing pressure w4 by the pressure sensor ( 24 ) detected pressure of the controller ( 15 ) the upper adjustment range of the hot gas valve ( 3 ) and thus another manipulated variable of the hot gas valve ( 3 ), in addition to that of the controller ( 15 ) by means of the maximum refrigerant vapor temperature w2 and the temperature sensor ( 16 ) detected temperature specific manipulated variable of the hot gas valve ( 3 ), whereby the controller ( 15 ) from the two manipulated variables of the hot gas valve ( 3 ) uses the smaller manipulated variable as a limit to the manipulated variable of the hot gas valve ( 3 ) and thus the upper setting range of the hot gas valve ( 3 ) to regulate, - when a lower response value w5 _{UE is} fallen below in the adjustment range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the return of the expansion valve ( 23 ) through the regulator ( 15 ) he follows. Method according to claims 6 and 7, wherein the controller ( 15 ) a pressure from another at the suction line ( 10 ) pressure sensor is detected, with an evaporation pressure w3 'compares and in deviation from the evaporation pressure w3' by means of actuation of the expansion valve ( 23 ) adjusts the pressure to the evaporation pressure w3 ', in addition to regulation by the controller ( 15 ) of the temperature sensor ( 16 ) detected temperature, the controller ( 15 ) with the evaporation temperature w3, and in deviation from the evaporation temperature w3 by means of actuation of the expansion valve ( 23 ) to the evaporation temperature w3. Method according to one of the preceding claims 1 to 8, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) adjusts the detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein - when exceeding an upper threshold value w5 _OD in the control range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) the manipulated variable of the three-way valve ( 26 ) modifies and thus the one flow path, from the three-way valve inlet ( 26 ' ) to the three-way valve outlet ( 26 '' ), on the other flow path, from the three-way valve inlet ( 26 ' ) to the three-way valve outlet ( 26 '' ) and thus a condenser ( 25 ), the controller ( 15 ) to the control task of limiting the manipulated variable of the hot gas valve ( 3 ) by means of the pressure sensor ( 24 ) and the condensing pressure w4 is performed by means of the pressure sensor ( 24 ) performs another control task by the controller ( 15 ) when falling below the pressure sensor ( 24 ) detected pressure to a further condensing pressure w4 _D , which is greater than the condensing pressure w4, the detected pressure equal to the condensing pressure w4 _D by the controller ( 15 ) the manipulated variable of the three-way valve ( 26 ) modifies and thus the upper Umstellbereich the three-way valve ( 26 ) regulates - falls below a lower threshold w5 _UD in the adjustment range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) the return of the three-way valve ( 26 ) and the condenser ( 25 ) decommissioned. Method according to one of the preceding claims 1 to 8, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ), whereby the controller ( 15 ) operated Heat exchanger ( 9 ) adjusts the detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein - when exceeding an upper threshold value w5 _OD in the control range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) the manipulated variable of a three-way valve ( 26 ) in steps, and thus the one flow path, from the three-way valve inlet ( 26 ' ) to the three-way valve outlet ( 26 ''' ), on the other flow path, from the three-way valve inlet ( 26 ' ) to the three-way valve outlet ( 26 '' ), and thus a condenser ( 25 ), whereby this change in each case after the thermal settling of the temperature sensor ( 13 ) is continued until the detected temperature is equalized to the reference variable w1 and until the upper threshold value w5 _{OD of} the manipulated variable of the hot gas valve (FIG. 3 ) or the three-way valve ( 26 ), the controller ( 15 ) fulfills the task of limiting the hot gas valve ( 3 ) depending on the pressure sensor ( 24 ) and the condensing pressure w4 another control task by the controller ( 15 ) falls below by the pressure sensor ( 24 ) detected pressure to a further condensing pressure w4 _D , which is greater than the condensing pressure w4, the detected pressure equal to the condensing pressure w4 _D , and thus the manipulated variable of the three-way valve ( 26 ) regulating limited and the upper Umstellbereich the three-way valve ( 26 ) is restricted, - falls below a lower threshold w5 _UD in the adjustment range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) at the regulator ( 15 ) in steps carried out control variable change of the three-way valve ( 26 ) the direction of action reverses, this manipulated variable change is in each case after the thermal settling of the by the temperature sensor ( 13 ) detected temperature is continued until the detected temperature of the reference variable w1 is adjusted and until a lower threshold value w5 _{UD of} the manipulated variable of the hot gas valve ( 3 ) is permanently exceeded or the controller ( 15 ) the three-way valve ( 26 ) returns to the original position and the condenser ( 25 ) decommissioned. Method according to one of the preceding claims 1 to 8, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) adjusts the detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein - when exceeding an upper threshold value w5 _OD in the control range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) and in case of deviation from the pressure sensor ( 24 ) pressure to a further condensing pressure w4 _D , which is greater than the condensing pressure w4, the detected pressure is adjusted to the condensing pressure w4 _D by the controller ( 15 ) the manipulated variable of a three-way valve ( 26 ) changes, and thereby by means of the flow path from the three-way valve inlet ( 26 ' ) to the three-way valve outlet ( 26 '' ) a liquefier ( 25 ) in control mode, so that the controller ( 15 ) another control task through to the control task, in which the controller ( 15 ) from the pressure sensor ( 24 ) compares detected pressure with the condensing pressure w4 and in the case of a deviation of the pressure from the condensing pressure w4 the detected pressure by actuation of the hot gas valve (FIG. 3 ) adjusts to the condensing pressure w4 and thus the manipulated variable of the hot gas valve ( 3 ), - falls below a lower response value w5 _UD in the adjustment range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) the three-way valve ( 26 ) returns to the original position and the condenser ( 25 ) decommissioned. Method according to one of the preceding claims 1 to 11, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) adjusts the detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein - when exceeding an upper threshold value w5 _OD in the control range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) the regulator ( 15 ) the commissioning of the condenser ( 25 ), when a further upper threshold value is exceeded in the adjustment range of the hot gas valve ( 3 ), which is greater than the upper threshold value w5 _OD , by the manipulated variable of the hot gas valve ( 3 ), the controller switches ( 15 ) a heater ( 42 ), - falls below a further lower response value in the adjustment range of the hot gas valve ( 3 ), which is greater than the lower response value w5 _UD in the adjustment range of the hot gas valve ( 3 ) is, by the manipulated variable of the hot gas valve ( 3 ), the regulator ( 15 ) the heating system ( 42 ), falls below the lower threshold w5 _UD in the adjustment range of the hot gas valve ( 3 ) by the manipulated variable of the hot gas valve ( 3 ) takes the controller ( 15 ) the liquefier ( 25 ) out of order. Method according to one of the preceding claims 1 to 11, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) for the purpose of temperature and power compensation, as required, the heat exchanger ( 9 ), the liquefier ( 25 ) and a controllable heating ( 42 ) operates. Method according to one of the preceding claims 1 to 13, wherein the object of the combination with the throttle body ( 2 ) in parallel, from the controller ( 15 ) actuated hot gas valve ( 3 ) also from the controller ( 15 ) actuated variable-temperature throttle element ( 27 ) which is applied to the controller ( 15 ) operated heat exchanger ( 9 ), wherein with continuous temperature control by the controller ( 15 ) this by changing the manipulated variable of the temperature-controllable throttle body ( 27 ) with its tempering element, the adjustable heating ( 28 ), continuously the performance of the heat exchanger operated by it ( 9 ), whereby by means of heating ( 28 ) the capillary tube ( 30 ) and the refrigerant mass flow therein is tempered, in the in the heat exchanger ( 9 ) placed capillary tube ( 21 ) and uniformly distributed there and by means of at least one elastic, in the capillary tube ( 21 ) opening ( 22 ) in the heat exchanger ( 9 ), which causes a uniformly tempered heat exchange surface, wherein continuously the temperature of the temperature sensor ( 16 ) and from the controller ( 15 ) is compared with the maximum refrigerant vapor temperature w2 and, if exceeded, equalized by the controller ( 15 ) the manipulated variable of the variable-temperature throttle element ( 27 ) and thus the upper setting range of the variable-temperature throttle element ( 27 ) regulates, wherein the evaporation temperature is determined by the variable temperature throttle body ( 27 ), the reducing tube ( 20 ) and the one or more openings ( 22 ) of the capillary tube ( 21 ), the nature of which leads to a temperature and a power acting on the heat exchanger ( 9 ) are tuned, also be determined by determining the degree of throttling in variable-temperature throttle body ( 27 ) and the reducing tube ( 20 ) and by determining the degree of opening at the one or more openings ( 22 ) of the capillary tube ( 21 ) to the heat exchanger ( 9 ) customized. Method according to one of claims 1 to 13, wherein the reference variable w1, which is greater than the maximum refrigerant vapor temperature w2, is variable up to the limit temperature w6 of the oil mixed with the refrigerant, wherein in this extended temperature range, a temperature compensation takes place in such a way - by the temperature sensor ( 13 ) detected temperature, which is smaller than the reference variable w1, by means of the of the controller ( 15 ) operated controllable heating ( 42 ) is adjusted to the reference variable w1, wherein in the heat exchanger ( 9 ) located refrigerant vapor by means of the valves ( 35 . 41 ), by the controller ( 15 ) are closed by the compressor ( 11 ) is sucked off and the controller ( 15 ) the compressor ( 11 ) after the evacuation of the heat exchanger ( 9 ), - the temperature sensor ( 13 ) detected temperature, which is greater than the reference variable w1, by means of the controller ( 15 ) operated heat exchanger ( 9 ) is adjusted to the reference variable w1 by the controller ( 15 ) the hot gas valve ( 3 ) with the valve open ( 41 ), - with the largest possible manipulated variable of the hot gas valve ( 3 ) from the temperature sensor ( 13 ) detected temperature, which is smaller than the reference variable w1, by means of the controller ( 15 ) operated heat exchanger ( 9 ) is adjusted to the reference variable w1 by the controller equipped with a variable duty cycle pulse width control or variable cycle duration pulse train control ( 15 ), which depends on the difference between the temperature sensor ( 13 ) and the reference variable w1 determines the duty cycle or the period duration, the valve ( 41 ), whereby - when exceeding the maximum refrigerant vapor temperature w2 by the temperature sensor ( 16 ' ) detected temperature of the controller ( 15 ) on the one hand by means of the actuated by him variable-temperature throttle body ( 31 ) the heat exchanger ( 36 ) and on the other hand the valve ( 35 ), whereby in the case of deviation from the temperature sensor ( 16 '' ) detected temperature to the maximum refrigerant vapor temperature w2 this is adjusted to the maximum refrigerant vapor temperature w2 by the controller ( 15 ) operated heat exchangers ( 36 ) by means of a regulator ( 15 ) carried out modification of the manipulated variable of the variable temperature throttle body ( 31 ) carries out the temperature compensation, so that the tempered refrigerant mass flow in the in the heat exchanger ( 36 ) placed capillary tube ( 40 ) and here through the at least one elastic opening ( 39 ) in the capillary tube ( 40 ) and thus in the heat exchanger ( 36 ) is evenly distributed and divided, so this refrigerant is the heat exchanger ( 9 ) in the heat exchanger ( 36 ) inflowing refrigerant vapor, and also by the temperature sensor ( 16 ' ) is limited, provided that the detected temperature exceeds the limit temperature w6, by limiting the control variable in control operation, - and falls below the maximum refrigerant vapor temperature w2 by the temperature sensor ( 16 ' ) detected refrigerant vapor temperature on the one hand the controller ( 15 ) by means of the actuated by him variable-temperature throttle body ( 31 ) the heat exchanger ( 36 ) and on the other hand the valve ( 35 ), wherein the temperature range of the heat exchanger extends from the determined evaporation temperature over the maximum refrigerant vapor temperature w2 to the limit temperature w6 of the oil in the refrigerant. Method according to one of claims 1 to 13, wherein the reference variable w1, which is greater than the maximum refrigerant vapor temperature w2, to the maximum temperature w7 of the compressor ( 11 ) is variable, wherein in this extended temperature range, a temperature compensation takes place in such a way by - by the temperature sensor ( 13 ) detected temperature, which is smaller than the reference variable w1, by means of the controller ( 15 ) operated controllable heating ( 42 ) is adjusted to the reference variable w1, wherein in the heat exchanger ( 9 ) located refrigerant vapor by means of the valves ( 35 . 41 ), by the controller ( 15 ) are closed by the compressor ( 11 ) is sucked, the controller ( 15 ) the compressor ( 11 ) after the evacuation of the heat exchanger ( 9 ), - the temperature sensor ( 13 ) detected temperature, which is greater than the reference variable w1, by means of the controller ( 15 ) operated heat exchanger ( 9 ) is adjusted to the reference variable w1 by the controller ( 15 ) the hot gas valve ( 3 ) with the valve open ( 41 ), - with the largest possible manipulated variable of the hot gas valve ( 3 ) from the temperature sensor ( 13 ) detected temperature, which is smaller than the reference variable w1, by means of the controller ( 15 ) operated heat exchanger ( 9 ) is adjusted to the reference variable w1 by the controller equipped with a variable duty cycle pulse width control or variable cycle duration pulse train control ( 15 ), which depends on the difference between the temperature sensor ( 13 ) and the reference variable w1 the duty cycle or the period of operation of the valve ( 41 ), wherein when exceeding the maximum temperature w7 of the compressor ( 11 ) by the temperature sensor ( 44 ) detected compressor temperature of the controller ( 15 ) on the one hand the valve ( 35 ) opens and on the other hand, the variably tempered throttle body ( 31 ) is actuated and put into operation, whereby the variable-temperature throttle element ( 31 ) at the compressor ( 11 ) performs a temperature compensation by the variably tempered throttle body ( 31 ) a constant tempered refrigerant mass flow in the in the oil of the compressor ( 11 ) placed capillary tube ( 40 ), wherein here the refrigerant mass flow through the at least one elastic opening ( 39 ) in the capillary tube ( 40 ) and in the oil of the compressor ( 11 ) evenly distributed and divided is what causes the oil of the compressor ( 11 ) directly and the compressor ( 11 ) are tempered indirectly and also the temperature sensor ( 44 ' ) is limited when the limit temperature w6 is exceeded, by limiting the control variable in control mode, and - when falling below the maximum temperature w7 of the compressor ( 11 ) by the temperature sensor ( 44 ) detected compressor temperature of the controller ( 15 ) to a variable-temperature throttle body ( 31 ) shut down and on the other hand the valve ( 35 ), thereby extending the temperature range of the heat exchanger ( 9 ) from the determined evaporation temperature over the maximum refrigerant steam temperature w2 to the maximum temperature w7 of the compressor ( 11 ). Method according to one of claims 15 and 16, wherein at an extended temperature range, the task of temperature compensation from that of the controller ( 15 ) operated heating ( 42 ) at the largest possible manipulated variable of the hot gas valve ( 3 ), rather than the task of temperature compensation from the controller ( 15 ) by means of a pulse width control or pulse sequence control by the controller ( 15 ) at the largest possible manipulated variable of the hot gas valve ( 3 ) the valve ( 41 ) operated with variable duty cycle or variable period. Method according to one of the preceding claims, wherein in case of deviation from the temperature sensor ( 13 ) detected temperature to the reference variable w1 the controller ( 15 ) the manipulated variable of the hot gas valve ( 3 ) or the manipulated variables of hot gas valve ( 3 ) and temperable throttle body ( 31 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ) or the manipulated variables of hot gas valve ( 3 ) and expansion valve ( 23 ) and temperable throttle body ( 31 ) or the manipulated variable of the variable-temperature throttle element ( 27 ), whereby the controller ( 15 ) operated heat exchangers ( 9 ) from the temperature sensor ( 13 ) adjusts detected temperature to the reference variable w1 and thus performs a temperature and power compensation, wherein the controller ( 15 ) the drive power of the compressor ( 11 ) to the heat exchanger ( 9 ) adjusted heat flow rate by depending on the heat exchanger ( 9 ) dissipated amount of heat flow, the speed of the compressor ( 11 ) is controlled, wherein when falling below a predetermined refrigerant vapor temperature by the controller ( 15 ) on the suction line ( 10 ) detected temperature or below a predetermined refrigerant vapor pressure by the controller ( 15 ) in the suction line ( 10 ), the regulator ( 15 ) each have a minimum speed of the compressor ( 11 ) and from the two speeds the larger minimum speed for limiting the speed of the compressor ( 11 ) is used to regulate the lower speed range of the compressor ( 11 ), passing through the heat exchanger ( 9 ) carried out prior to adjusting the drive power of the compressor ( 11 ) to the heat exchanger ( 9 ) discharged energy flow takes place in the respective adjustment range at a lower response value of the manipulated variable of the actuator located in the control mode and when it falls below and in the respective control range at an upper threshold value of the manipulated variable of the actuator located in the control mode and when it exceeds the controller ( 15 ) successively the manipulated variable of the speed of the compressor ( 11 ) is increased until the detected temperature is equalized to the command value w1. Method according to one of the preceding claims 1 to 13 or 15 to 18, wherein in the interior of the thermal compensating accumulator ( 7 ) the surface ensures that a thermal balance between refrigerant mass flow and hot steam volume flow and the mixing and atomizing of the refrigerant mass flow with the superheated steam flow occurs. Apparatus for carrying out the method according to one of the preceding claims 1 to 13 and 15 to 19, wherein one with the outlet of a condenser ( 4 ) associated collectors ( 1 ) at least one throttle element ( 2 ) is connected downstream and one of a controller ( 15 ) actuated hot gas valve ( 3 ) is connected in parallel with these, which by means of a pressure line ( 12 ) with the inlet of the condenser ( 4 ) and a compressor ( 11 ), an output ( 2 ' ) of the throttle body ( 2 ) and an output ( 3 ' ) of the hot gas valve ( 3 ) are joined together and connected by means of a tube ( 6 ) with a thermal compensation memory ( 7 ) connected to at least one pipe ( 8th ) is provided as a drain pipe, while the end of the tube ( 8th ) with a connecting tube serving as a capillary tube Reduzierrohr ( 20 ), to which a capillary tube ( 21 ) is connected, which consists of a thermally insulating and elastic material, here are the reducing tube ( 20 ) and the capillary tube ( 21 ) in a heat exchanger ( 9 ) and the capillary tube ( 21 ) is on its longitudinal side with one or more elastic, identically shaped openings ( 22 ), while its end is closed, the end of the tube ( 8th ) is in a heat exchanger input ( 9 ' ) and connecting with it sealed, a heat exchanger outlet ( 9 '' ) is by means of a suction pipe acting as a connecting pipe ( 10 ) with the compressor ( 11 ), wherein a temperature sensor ( 16 ) on the suction line ( 10 ) is attached and another Temperature sensor ( 13 ) in the flow direction after the heat exchanger ( 9 ) is arranged. Device according to the preceding claim 20, wherein the throttle member ( 2 ) is designed as a thermostatic expansion valve. Device according to the preceding claim 20, wherein the throttle member ( 2 ) is designed as an automatic expansion valve. Device according to the preceding claim 20, wherein the throttle member ( 2 ) is designed as a capillary tube. Device according to the preceding claim 20, wherein the throttle member ( 2 ) as one from the controller ( 15 ) operated expansion valve is configured. Device according to one of the preceding claims 20 to 24, wherein in the suction line ( 10 ) between the heat exchanger ( 9 ) and the compressor ( 11 ) after the heat exchanger ( 9 ) an expansion valve ( 23 ) and that in the connecting tube between the collector ( 1 ) and the throttle body ( 2 ) after the collector ( 1 ) a pressure sensor ( 24 ) is arranged connecting and on the suction line ( 10 ) between the expansion valve ( 23 ) and the compressor ( 11 ) after the expansion valve ( 23 ) the temperature sensor ( 16 ) and another pressure sensor in the suction line ( 10 ) is arranged connecting. Device according to one of the preceding claims 20 to 25, wherein a condenser ( 25 ) and the heat exchanger ( 9 ) form a design or the liquefier ( 25 ) as part of the heat exchanger ( 9 ) is placed at this, wherein immediately after the connection of the inlet pipe from the condenser ( 25 ) is placed as a funnel configured connecting pipe, wherein the edge of the funnel with the interior of the inlet pipe from the condenser ( 25 ) is sealingly connected and the funnel mouth is sealingly connected to a capillary tube, which is provided on its longitudinal side with one or more elastic, identically shaped openings, consists of a thermally insulating and elastic material and is closed at its end, wherein a three-way valve inlet ( 26 ' ) with the input of the hot gas valve ( 3 ) and the output of the compressor ( 11 ) and a three-way valve outlet ( 26 '' ) with the inlet of the condenser ( 25 ) and a three-way valve outlet ( 26 ''' ) with the outlet of the condenser ( 25 ) and the condenser inlet ( 4 ) connected is. Device according to one of the preceding claims 20 to 26, wherein a controllable heating ( 42 ), preferably an electrothermal transducer, either in the heat exchanger ( 9 ) is integrated and forms an assembly with this or at the heat exchanger ( 9 ) is arranged. Device according to one of the preceding claims 20 to 27, wherein a controllable heating ( 42 ), preferably an electrothermal transducer, between the thermal balance memory ( 7 ) and the heat exchanger ( 9 ) is arranged. Device according to one of the preceding claims 20 to 28, wherein after the merger of output ( 2 ' ) of the throttle body ( 2 ) and output ( 3 ' ) of the hot gas valve ( 3 ) a valve ( 41 ) in front of the thermal equalization memory ( 7 ) is arranged. Device according to one of the preceding claims 20 to 29, wherein one of the controller ( 15 ) actuated variably temperature-controllable throttle element ( 31 ) from a capillary tube ( 32 ), a thermally conductive cylinder ( 33 ) and a controllable heating ( 34 ), whereby the capillary tube ( 32 ) around the thermally conductive cylinder ( 33 ) and mechanically and thermally connected to it and in the thermally conductive cylinder ( 33 ) from the controller ( 15 ) operated controllable heating ( 34 ), an electrothermal transducer is placed, here is the entrance of the capillary tube ( 32 ) with the output of the collector ( 1 ) and the output of the capillary tube ( 32 ) with one from the controller ( 15 ) actuated valve ( 35 ), in turn by means of a tube ( 37 ) with a heat exchanger ( 36 ), the heat exchanger ( 36 ) is by means of the suction line ( 10 ) with the compressor ( 11 ), the heat exchanger ( 9 ) and the pipe ( 37 ), which enters the interior of the heat exchanger ( 36 ) and is sealingly connected thereto, wherein in the heat exchanger ( 36 ) with the pipe ( 37 ) designed as a capillary reducing tube ( 38 ), on which in turn a capillary tube ( 40 ), which is closed at its end, wherein the consisting of a thermally insulating and elastic material capillary tube ( 40 ) on its longitudinal side with one or more elastic, identically designed openings ( 39 ) is provided. Device according to the preceding claim 30, wherein instead of the insertion of the end of the tube ( 37 ) in the heat exchanger ( 36 ) this in the compressor ( 11 ) and sealingly connected thereto, and that instead of the placement of the reducing tube ( 38 ) and the capillary tube ( 40 ) in the heat exchanger ( 36 ) these in the compressor ( 11 ) are placed. Device according to the preceding claim 20, wherein the hot gas valve ( 3 ) instead of as a hot gas bypass with the compressor ( 11 ) with a branch ( 5 ) of the liquefier ( 4 ) connected is. Apparatus for carrying out the method according to the preceding claim 14 and one of the preceding claims 20 to 32, wherein instead of with the throttle body ( 2 ) in parallel, from the controller ( 15 ) actuated hot gas valve ( 3 ) one from the controller ( 15 ), on the heat exchanger ( 9 ) tuned, variably temperature-controllable throttle body ( 27 ), wherein the throttle member ( 27 ) from a capillary tube ( 30 ), a thermally conductive cylinder ( 29 ) and a controllable heating ( 28 ), here is the capillary tube ( 30 ) around the thermally conductive cylinder ( 29 ) and mechanically and thermally connected to it, wherein in the thermally conductive cylinder ( 29 ) from the controller ( 15 ), adjustable heating ( 28 ), an electrothermal transducer is placed, here is the entrance of the capillary tube ( 30 ) at the output of the collector ( 1 ) and the exit of the capillary tube ( 30 ) on the reducing tube ( 20 ) connected. Device according to the preceding claims 20 to 32, wherein the heat exchangers ( 9 ) and adapted to it, consisting of at least one throttle body ( 2 ), with the at least one throttle body ( 2 ) parallel, adjustable hot gas valve ( 3 ) and a the at least one throttle body ( 2 ) and the hot gas valve ( 3 ) downstream reducing tube ( 20 ) and a reducing tube ( 20 ) downstream capillary tube ( 21 ), by their interaction and their configurations, the temperature and the performance of the heat exchanger ( 9 ), the combination is expandable - around the adjustable expansion valve ( 23 ), which determines the temperature and performance of the heat exchanger ( 9 ), - about the adjustable three-way valve ( 26 ), which determines the temperature and the performance of the condenser ( 25 ), - about the adjustable variable temperature throttle body ( 31 ), which determines the temperature and performance of the heat exchanger ( 36 ), - about the adjustable electronic valve, the temperature and the power of the adjustable heating ( 42 ) - another adjustable electronic valve which determines the temperature and the power of another controllable heater to be connected between the thermal compensating accumulator ( 7 ) and the heat exchanger ( 9 ) is arranged in the material cycle, - to further parallel throttle bodies, which in each case a reducing tube and a capillary tube is connected, the throttle body are associated with its reducing tube and its capillary each a further heat exchanger and the reducing tube and the capillary tube are each placed in the corresponding heat exchanger , the outputs of the other throttle bodies are also connected to the output ( 3 ' ) of the hot gas valve ( 3 ), the heat exchangers each an expansion valve is connected downstream; where the controller ( 15 ) actuates the actuators and the temperature and the performance of the other heat exchangers to the temperature and the performance of the heat exchanger ( 9 ) co-determined in the composite. Device according to one of the preceding claims 20 to 34, wherein the thermal compensation memory ( 7 ) from a wound tube ( 45 ) is designed, the material is copper, which has a favorable thermal conductivity. Device according to one of the preceding claims 20 to 34, wherein the thermal compensation memory ( 7 ) as a thermal container ( 46 ) whose content material ( 47 ) consists of a thermally low-conductive material, wherein between the content material ( 47 ) and the inlet and outlet of the container ( 46 ) in its interior a gauze ( 48 ) is attached. Device according to one of the preceding claims 20 to 36, wherein a control device is used, wherein the controller ( 15 ) - by pressing the hot gas valve ( 3 ) the heat exchanger ( 9 ) operates, - by pressing the hot gas valve ( 3 ) and / or the expansion valve ( 23 ) the heat exchanger ( 9 ) operates by means of actuating the three-way valve ( 26 ) the liquefier ( 25 ) operates, - by means of variable-temperature throttle body ( 31 ) the heat exchanger ( 36 ) operates, - by actuating an electronic valve, the controllable heating ( 42 ) operates by means of actuating an electronic valve another controllable heating, which between the thermal balance memory ( 7 ) and the heat exchanger ( 9 ) - the drive power of the compressor ( 11 ) to the discharged heat flow rate of the heat exchanger ( 9 ), or - by actuating the variable-temperature throttle body ( 27 ) the heat exchanger ( 9 ) operates, or - by pressing the variable-temperature throttle body ( 27 ) operates a further heat exchanger, thereby continuously the temperatures of the temperature sensors ( 13 . 16 . 16 ' . 16 '' . 44 . 44 ' ) and to the controller ( 15 ), in addition, the pressure from the pressure sensor ( 24 ) and another pressure sensor in the suction line ( 10 ) is detected, and to the controller ( 15 ) transfer. Use of a method according to one or more of the preceding claims 1 to 19 for a refrigeration system or heat pump. Use of a device according to one or more of the preceding claims 20 to 37 for a refrigeration system or heat pump.

Images