KR800000364B1 - Refrigeration heat recovery system - Google Patents

Abstract

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Description

Refrigeration Heat Regeneration System

1 is a diagram of the vapor compression refrigeration system of the present invention for the development of high temperature lift

2 is a relation chart of the high temperature lift thermal regeneration cycle of FIG.

3 is a view showing another embodiment of the present invention

TECHNICAL FIELD The present invention relates to a circulation system for high temperature temperatures in a steam pressure refrigeration system having a mechanical compressor. Typically, a large amount of energy is generated on the high pressure side in a steam pressure refrigeration system. However, due to the thermodynamic nature of most refrigerants, the temperature of the energy excreted in the system is relatively low. Therefore, this released energy cannot be recovered for application in domestic or industrial heat sources.

Therefore, it is an object of the present invention to improve the freezing process. Another object is to efficiently generate high temperature lift in steam compression refrigeration cycle. Furthermore, it is to use the high temperature lifted by the compressor in the refrigeration cycle without increasing the lift capacity of the compressor.

Another object is to combine the advantages of the vapor pressure refrigeration cycle with the benefits of an absorption refrigeration cycle in providing an efficient thermal regeneration system that can produce higher temperature energy than in each system.

Another aim is to efficiently develop high temperature lifts for regenerated heat source applications in refrigeration units using working fluids known in the art.

The above object is to include a high head circulation method connected to the refrigerating unit in order to act between the compressor discharge and the condenser inlet in a steam pressure freezer and a device for mixing at least some of the discharged refrigerant vapor into an absorbent concentrated solution and causing high temperature mixing. This is achieved by having a high head circulating system and a heat exchanger that transfers high temperature energy to the thermally regenerated material and separating the refrigerant from the solution and allowing the refrigerant to be used in the refrigeration cycle and having the solution reused in the high head circulating system.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The following detailed description will be given in conjunction with the accompanying drawings for the purposes of the foregoing and a more detailed understanding of the invention. Referring to FIG. 1, there is shown a steam pressure refrigeration system 10 in accordance with the present invention for the development of a high temperature lift, in which the energy released from the system can be immediately applied to industrial and domestic heat sources. Like most conventional vapor pressure refrigeration cycles, the apparatus comprises a condenser 11 and an evaporator 12 and is connected to a float valve 13 which expands as the refrigerant moves from high pressure to low pressure. More specifically, while the above-mentioned freezer element is shown enclosed in one fuselage 15, it is clear that each element can be developed indefinitely from the description of the present invention. In this cycle, the material to be cooled, such as water, enters the evaporator through inlet pipe 16 and passes through the evaporator conduit so that the contents discharge thermal energy to the refrigerant and exit the outlet pipe 17 out of the system.

The refrigerant in the vapor form leaves the evaporator and enters the inlet of the compressor 20 through the inlet channel 21. The compressor 20 of FIG. 1 is an electric drive and is a hermetically sealed centrifugal compressor. I technology can be used.

Although the present invention is described above with respect to a machine using R-11 as a refrigerant, any suitable refrigerant can be used if the selected refrigerant is absorbed and harmonized.

R-11 is maintained at about 7 psia on the low pressure side and 30 psia on the high pressure side. A damping adjustment mechanism 22 is provided to regulate the flow of refrigerant from the evaporator to the compressor inlet, the flow rate is regulated by a sensor 23, the sensor being usually operated by electricity or air and discharged from the evaporator. It is connected to a regulator that is arranged to sense the temperature of the cold material and is located on the damping plate.

At the commercial pressures mentioned above, the refrigerant R-11 is saturated below 120 ° F and the excreted energy limits the practical use. The work required for the compressor to raise the saturation temperature of the refrigerant to 120 ° F. increases as the temperature of the refrigerant increases. As a result, temperature rise by mechanical methods becomes economically impossible. In addition, the decomposition rate of most known refrigerants increases as the compressor discharge temperature increases, which further limits the mechanical method of performing high lift. As will be apparent from the discussion below, the present invention overcomes the long-standing technical shortcomings by providing a high lift circulation system that takes advantage of the absorbent principle of obtaining relatively high temperatures without the need to increase the high lift capacity of the compressor.

As shown in FIG. 1, a device representing a high lift circulation system is connected to the refrigeration system between the compressor discharge shaft and the inlet shaft of the conventional condenser 15. Therefore, the high lift circulation system can be conveniently refitted to the current application field device without any major element change or modification.

The high head circulating system includes a solution pump 36, an optional solution heat exchanger 38, a high temperature heat exchanger 25, a gravity type separator 30, and a solution concentrator 35. Starting at the solution pump 36, a strong solution of absorbent is exited from the concentrator 35 and is passed through any solution heat exchanger 38 to the injection nozzle 39 via the solution passage 55. Herein, the term "strong solution" refers to a solution having a strong absorbency to a refrigerant, and similarly, "weak solution" is a term used for a solution having a weak absorbency to the refrigerant.

The injection nozzle 39 is located in the compressor discharge pipe 41 and the nozzle is located near the inlet 40 of the high temperature heat exchanger 25 as shown in FIG. In operation, saturated or dense refrigerant vapor is discharged from the compressor and moved to the high temperature heat exchanger inlet where the steam is exposed to a "strong solution" from the injection nozzle. Since some refrigerant vapor in the mixed gas is absorbed by the solution, the temperature rise of the mixed gas is higher than the saturation temperature of the steam discharged from the compressor.

The heat exchanger 25 is generally a one-way heat exchanger having a group of tubes 42 that are vertically lined up to transport the hot mixture gas down through the body. The thermal regeneration material (which may be water) is transferred to the bottom of the fuselage by the inlet pipe 45 and the regenerated material is generally moved upwards through the fuselage and through the front and rear passages by a baffle 46 in pieces. Flows. The convection of the two fluids flowing on the heat transfer surface of the tube results in an effective exchange of energy between the two materials, and the temperature of the regeneration material is raised to approximately the temperature of the hot mixture gas.

Finally, the recycled material is discharged from the top of the exchanger through discharged 48. In practice, the absorber is absorbed by a strong solution when the amount of heat slightly less than half or half of the total discharge volume of the compressor is applied to the circulation system. This means that about 50% of the total energy of the refrigerant vapor discharged from the compressor is consumed by absorption, and 50% of the residue is conveyed through the mixer heat exchanger in the form of unabsorbed refrigerant vapor. As explained below, in the unabsorbed refrigerant, energy is used in a downward flow so that energy is reconcentrated from the exchanger 25 to the dilute solution. As the absorption process is essentially a reversible process, it is also required to reconcentrate the solution by the same amount of energy consumed for absorption. Since the internal energy is balanced in the above manner, there is always enough internal energy to reconcentrate the solution for all heat loads in the system.

The mixed gas out of the tube tube of the heat regeneration exchanger is passed directly through the gravity separator (30), and the weak liquid solution in the liquid phase is collected on the low water level (49) of the separator while the unabsorbed refrigerant vapor is evaporated to It passes through the tube tube 50 to be horizontally and straight line.

The weak solution collected in the reservoir 49 of the separator leaves any solution heat exchanger 38, passes through the concentrator 35, expands to low pressure and is quenched. In fact, weak solutions are throttled from the discharge pressure of the compressor to the compressor inlet pressure, and this object is ascertained from the following.

The pressure difference between the solution feed zone of the concentrator and the low water reservoir of the separator provides the necessary power to transport the weak solution through the solution heat exchanger. The supply of the solution contained in the concentrator is maintained to wet the tube surface in the tube tube (50).

The quenching of the weak solution causes the temperature of the solution to be much lower than the temperature of the unabsorbed refrigerant vapor passing through the concentrator tube tube 50. In conclusion, both materials are thermally flown in the concentrator and the unabsorbed refrigerant vapor in the tube condenses, giving thermal energy to the weak solution stored in the feed zone.

The solution supply zone in the concentrator must be connected to the compressor inlet side by the inlet channet 52 so that the compressor maintains the pressure in the supply zone below the vapor pressure and the solution is heated due to concentration of the unabsorbed refrigerant vapor. When used to boil the refrigerant. The pure refrigerant vapor boiled in solution enters the compressor through the inlet channel 52 for reuse in the cycle.

The recondensed solution (ie, strong) exits the concentrator by means of a rotary pump 36 and the strong solution is transferred to the spray nozzle 39 from a warm dilute solution entering the concentrator 35 under the influence of the pump. Pass through any solution heat exchanger that delivers up to a cold, strong solution.

Control of the thermal regeneration process is maintained in response to the temperature of the regeneration material leaving the thermal regeneration exchanger in the high lift circulation system. The detector 57 is located in the outlet pipe 48 and is adapted to send the temperature value to a regulator operably connected to the valve 56 in the solution passage 55. When the temperature of the outgoing regenerated material is far from the proper value, The regulator operates a control valve installed to increase or decrease the amount of solution delivered to the main nozzle. However, it is obvious that any device of this type can also be used to adjust the flow of solution in the above manner.

As shown, the volume of the strong solution is adjusted to control the amount of refrigerant vapor absorbed in the inlet area of the exchanger 25, which in turn has a high head, not only the amount of steam energy to be consumed in the absorption process, but also the unabsorbed useful for reconcentration. Determine the amount of energy available in the refrigerant vapor.

As mentioned above, the high lift circulation system is designed so that sufficient energy is available to reconcentrate at the unabsorbed energy when operated under maximum heat load. In addition, an automatic adjustment balance is installed in the high lift circuit between the thermal regeneration exchanger 25 and the concentrator 35, for example, if more than the required amount of energy is consumed by the heat load already established in the absorption process. The condition of the solution leaving 25 will be too lean or weak.

As a result, the amount of energy contained in the unabsorbed refrigerant vapor passing through the concentrator 35 is reduced proportionally and lowers the amount of energy available to reconcentrate the extremely thin solution in the concentrator 35. The concentration of the solution exiting the concentrator 35 is therefore weaker since less energy is consumed for absorption during the next cycle. The evidence is that when the solution delivered to the exchanger 25 is relatively sparse, less refrigerant is absorbed and more energy is used for reconcentration in the unabsorbed vapor and the solution exiting the concentrator is hardened. This process continues until a properly balanced energy relationship is established between the concentrator 35 and the heat exchanger 25 for the required heat load.

The refrigerant moving through the concentrator tube is discharged to a chamber 61 included in the fuselage 15 of the refrigerator system. The state of the refrigerant entering the chamber will of course vary with the amount of refrigerant condensed in the concentrator. The liquid refrigerant exiting the concentrator enters the float valve chamber 63 directly. The refrigerant vapor leaving the concentrator, on the other hand, is sent to the diesel condenser via a conduit 64 where the vapor condenses to the liquid phase and returns to the float chamber 63. The condensation of the refrigerant vapor is divided between the condensers of the concentrator and the amount of work performed by each depends on the heat load imposed on the high lift circulation system.

From the float seal, refrigerant is used to pass through expansion valve 13 and to cool in evaporator 12. The evaporation gas from the evaporator is sent to the compressor by the inlet 21 and used once again in the cycle along with the refrigerant which has lost the weak solution.

2, the state of the solution as it passes through the high lift cycle of the high lift cycle is explained. Firstly it can be assumed that no solution heat exchanger 38 is in the circuit, and the cycle shown shows a diagram of a system using R-11 as refrigerant and lubricant with an absorbent such as Texaco URSA. The refrigerant concentration of the solution is along the chart abscissa and represents the percentage of concentration by weight. The left vertical axis represents the solution vapor pressure corresponding to the saturated concentration temperature of the refrigerant indicated along the right vertical axis. The saturation temperature of the solution is also shown in the diagram and is shown as an oblique line.

Point "A" in the diagram represents the discharge pressure of the compressor entering the energy regeneration heat exchanger (25). As shown in a representative example of a system using R-11 as a refrigerant, the discharge pressure is about 30 psia or exactly 30.5 psia. At the discharge pressure, the saturation temperature of the refrigerant vapor is about 115 ° F and the strong solution injected into this area is exposed to the compressor discharge pressure and thus absorbs the refrigerant vapor.

As a result, the solution temperature rises to about 160 ° with a concentration of about 23%, and the hot mixture enters the heat exchanger 25 and raises the temperature of the recycled material to about the temperature of the solution and spits out heat into the recycled material. To start. As the solution enters the regenerator and the heat continues to diminish, the solution becomes thin and eventually causes the heat exchanger to stay on the "B" phase. At this point the solution is about 120 ° F. and has a concentration of about 76.6%.

The solution and unabsorbed refrigerant vapor exit the heat exchanger 25 in approximately saturated condition and are conveyed to a separator 30 where the components are separated.

The separated weak solution is quenched from the "B" state to the "C" state by passing the solution through some form of expansion device for this purpose. As described above, quenching is performed by discharging the pressure of the compressor to the inlet pressure of the compressor or

Achievement is achieved by lowering from about 30.5 psia to about 7 psia, and under these conditions quenching changes the concentration of the solution from 76.6% to 68% and reduces the temperature of the cross-section solution to 45 ° F. In this condition the solution enters concentrator 35.

In the concentrator 35, the solution is in thermal communication with the unabsorbed refrigerant through the tube tube, and the vapor is saturated or nearly saturated.

The cooled weak solution condenses the vapor and latent heat is released into the solution. The solution that is exposed to the compressor inlet and drives off the refrigerant comes to state "D". During reconcentration the solution fed to the concentrator is ideally at 10.5% in 67% refrigerant and the temperature rises to about 105 ° F.

The reconcentrated solution is transferred to the injection nozzle 39 by the circulation pump 36 in the " D " phase and exposed to the compressor discharge pressure. By spraying the state of the solution changes from "D" to "A" and the cycle is repeated again.

3 shows a diagram of a vapor compression refrigeration system using a screw compressor 126 of another apparatus of the present invention for the development of high temperature lifts. The refrigeration system includes a condenser 112 and an evaporator 113. The condenser and the evaporator are connected by the float chamber 116 and the expansion valve 115 device located in the refrigerant line 114. Cold material, such as water, is transferred to the evaporator through the inlet pipe 117 and heat passes through the evaporation tube tube, which is discharged from the hot material to the refrigerant, and is passed from the system by the outlet pipe 118 device. The refrigerant in the vapor state exits the evaporator and is delivered to the suction side of the compressor 120 by the inlet channel 121.

As shown in the figure, the compressor 120 is a conventional screw compressor driven by a suitable drive 122, for example an electric motor. While screw compressors may be ideally used in the present invention, it will be apparent from the following description that any mechanical compressor may be used in the practice of the present invention.

As shown in the figure, a high head, circulatory system includes an absorber 125 and a generator 140. The high lift circulation system is connected to the refrigeration system and the discharge side of the refrigerant evaporator 113 and the refrigerant condenser 112 in an operable way. The concentrated absorbent solution is conveyed by the solution suction pipe 123 to the refrigerant inlet channel 121 where the solution is exposed to the refrigerant vapor at the compressor inlet. The mixture of pure refrigerant vapor and concentrated solution passes through the compressor, the pressure of the mixture rises and carries the mixture to the high pressure side of the refrigeration system.

The solution is injected into the compressor directly below the inlet, where it is delivered to the exposed location of the refrigerant in the pressure gauge. Under the influence of the compressor, the mixture of solution and refrigerant is pumped down into the absorption-generator circulation system by the compressor discharge line 127, and as it passes through the compressor, the energy level in the mixture is sufficient to keep the refrigerant saturated or slightly overheated. Is increased to a degree.

Absorption unit 125 is a one-way heat exchanger having a vertically aligned tube tube 126 that is adapted to convey a high temperature mixture downward through an absorbent body that wets the tube inner side.

The thermal regeneration material is a material having a high coefficient of water or thermal conductivity and is carried by the inlet pipe 128 to the bottom of the absorbing body, and generally moves upward through the body. The flow is brought forward and backward with respect to the outer surface of the exchanger tube by the baffle 129 to establish a sufficient reverse flow heat transfer relationship between the recycled material and the hot mixture and the regenerated material moving down the tube. The thermal regeneration material is discharged from the absorber by pipe 130 and transported to a suitable downward device for the release of contained energy.

As the mixture enters the absorber from the compressor, the solution concentrated in the mixture begins to absorb the saturated refrigerant. As it enters the absorption unit, the mixture moves downwards through a tube tube in heat transfer relationship with the thermal regeneration material where energy (heat) is dumped into the regeneration material.

As energy is discharged from the mixture, the absorption rate increases. By design, the high lift circulation system is configured to absorb the concentrated solution in a circuit in which less than one-half or one-half of the total refrigerant flow volume passing through the compressor when operated under maximum heat load. Thus, 50% or more of the useful energy of the refrigerant vapor discharged from the compressor remains pure or unabsorbed on the discharge side of the absorber.

The refrigerant discharged from the remaining 50% or less of the compressor condenses in the solution necessary to increase the temperature of the mixture to a temperature higher than the saturation temperature of the pure refrigerant. As described below, the energy retained in the unabsorbed refrigerant vapor is applied downwards to reconcentrate the lean solution from the absorber. Since the absorption process is essentially a reversible process, nearly the same amount of energy is consumed in the absorption process as needed for reconcentration. By maintaining the energy balance described above, there is sufficient internal energy included in the system to reconcentrate the solution for all heat loads.

The mixture exiting the tube tube of the heat regeneration exchanger is passed directly to the separation chamber (131). In the separator unabsorbed refrigerant is separated by gravity from the lean solution.

The liquid solution is collected in the chamber bottom reservoir, while the unabsorbed frozen steam is passed through the channel 132 to the downstream generator 140. Generator 141 is configured to have the function of reconcentrating the lean solution to the second heat exchanger and at least partially condensing the unabsorbed refrigerant vapor exiting the absorber.

As for the generator installation, it can be clearly seen that the unit is separated into a low pressure section including a high pressure section 441 located at the center and a high pressure chamber 143 and 144 in which fluid flows with each other, and the advanced chamber is a tube passing through the high pressure side. And a low pressure portion of the generator is operatively connected at the suction side of the compressor by line 123 to maintain this portion at the compressor inlet pressure.

The low pressure portion is separated from the low inlet portion by the tip walls 147 and 148 and is always maintained at the discharge pressure of the compressor.

The lean solution collected in the separator is conveyed via line 135 to the low pressure side of the generator. Prior to entering the generator, the lean solution is quenched by passing the fluid through expansion valve 137. As a result, the solution is throttled from the high pressure side to the low pressure side.

The quench solution enters the generator in chamber 143 and immediately rises through tube 146 under the influence of the compressor inlet. The unabsorbed refrigerant vapor is relatively hot and high pressure than the solution and enters the high pressure section of the generator from the separator and moves up relative to the heat exchanger tube outer surface.

As a result, the vapor condenses or partially condenses on the tube surface and the heat of condensation passes through the solution in the tube. The vapor pressure of the solution in the tube is the compressor inlet pressure and is relatively low, as a result of which the refrigerant is easily sent out of the solution. The mixture containing the free refrigerant and the condensed solution is conveyed to the compressor for reuse in the cycle.

Pure unabsorbed refrigerant vapor passing through the generator high pressure portion enters the discharge chamber 150 where the condensed refrigerant, which is still liquid, flows directly into the float chamber 116. The uncondensed vapor exiting the generator is conveyed above the refrigerated condenser 112 circulated through the condenser coil 151 by the inlet pipe 152 and the outlet pipe 153.

Condensate generated in the condenser 112 also goes to the float chamber 116 and is condensed and collected from the generator 140. As shown, the generator 140 and the condenser 112 are condensed with each other, and the amount of work done in each unit depends on the heating and cooling demands located in the system.

Control of the thermal regeneration process is maintained in the high head circulation system corresponding to the temperature of the regeneration material exiting the thermal regeneration exchanger (125). The sensing unit 157 is arranged to sense the temperature of the regeneration material adjacent to the outlet pipe 130 and exiting the absorption unit. The temperature value is sent to regulator 158 connected to expansion valve 137 which in turn regulates the flow of the lean solution. If the temperature of the regeneration material exiting the absorber is outside the optimum value, the signal is sent to a regulator that regulates the expansion valve equipped to increase or decrease the amount of solution transported to the generator and return the temperature to the optimum value.

This regulates the flow rate of the solution through the generator and in effect controls the solution passing through the absorber 125. It also determines the amount of refrigerant energy consumed in the high head absorption process and the amount of energy available to reconcentrate the lean solution in the unabsorbed refrigerant vapor.

This absorber-generator installation allows the high lift circuit to balance the work performed by the two units and maintain the system at the proper load. For example, if a large amount of required energy is used in the absorption process, the state of the solution exiting the absorber will be too sparse, resulting in a proportional decrease in the amount of energy contained in the unabsorbed refrigerant vapor passing through the generator. The amount of energy available to reconstitute the solution will drop. Therefore, reconcentration of the solution leaving the generator weakens the refrigerant absorption capacity.

Therefore, in the next cycle, the energy consumed in the absorption process is reduced. In the same way, when the solution delivered to the absorber is relatively moist, less refrigerant is absorbed and more energy is available for reconcentration in the unabsorbed steam. Again the result is to harden the solution out of the concentrator during the next cycle. In fact, this balancing process continues until the proper energy relationship is established for the heat load required between the absorber and generator.

The refrigeration capacity of the refrigeration system is controlled by a damping valve 160 or similar device adapted to regulate the amount of refrigerant flow through the inlet 121 connected to the outlet upon evaporation with the compressor inlet. The position of the damping valve is sensed by the sensing unit 161 in the cooling material discharge part and adjusted in response to the temperature of the cold material exiting the evaporator.

In operation, the screw compressor always rotates at its maximum operating speed (open enough) to operate the generator so that the compression filter produces the highest concentration possible at maximum heat load. This method avoids conventional slide valve adjustments that would counterbalance the generator. A relatively simple control system is provided here to allow independent control of the heating and cooling loads.

As can be seen in the second unit, the compressor transports the mixture through a high lift circulation system like a pump, thus eliminating the need for a solution pump. When refrigerants such as R-11 are used, lubricants such as Texaco URSA are used as absorbents.

This combination of working fluids is ideally suited for use with screw compressors when the solution has been exposed to the refrigerant prior to entering the compressor or if injected directly into the compressor. Under these conditions, the solution provides the compressor with the required lubrication, so that the seed necessarily eliminates the need for an auxiliary lubricator required in this environment.

While the claims describe the structures of the invention, they do not need to be limited to the description, and this application may have any application or transformation possible within the scope of the following claims.

Claims (1)

In the refrigeration system of the type comprising a condenser 11, an evaporator 12, an expansion mechanism 13 for controlling the refrigerant between the evaporator of the condenser and a vapor compressor 20 for raising the state of the refrigerant vapor leaving the evaporator, Injector 39 exposing steam to the absorbing solution through a compressor to form a high temperature mixture, a heat exchanger 25 transferring heat energy from the mixture to regenerated material, and separating unabsorbed refrigerant vapor from the concentrated solution leaving the exchanger. Quenching the condenser (11) and the concentrated concentrated solution disposed between the condenser (11) and the separator (30) through which the unabsorbed steam passes from the separator to the condenser in a heat transfer relationship with the separator (30) and the included feed solution. The solution is supplied to the concentrator whereby thermal energy is transferred to vaporize the refrigerant from the vapor to the quenched solution and from there to an expansion device 38 which reconcentrates the solution. Freezing heat recovery system, characterized by the combination.

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