RU105723U1 - ONE-SECTION OR MULTI-SECTION RADIATOR, AT LEAST, WITH TWO DIFFERENTLY COMPLETED SITES - Google Patents

Abstract

1. At least one-section, preferably two-section or multi-section radiator, in particular a flat radiator containing ! location (VL) of connection to the supply line, ! location (RL) of connection to the return line, ! a first flow-permeable and preferably space-facing section (1), and ! at least one other passing flow and preferably located behind the plot (1'), ! characterized in that the flow passes through the first section essentially evenly before the other sections, and only in the lower end zone of the first section (1) is provided at least one connection point with at least one other section (1'). ! 2. Radiator according to claim 1, characterized in that the first section (1) is designed so that more heat can be supplied to it, at least at a low thermal output, than to the remaining sections of the radiator. ! 3. Radiator according to claim 1 or 2, characterized in that the sections are made in the form of plates and are preferably formed from profiled plates or flat pipes, which are connected to each other through collector channels, in particular from a steel sheet, and ! the plates are profiled so that the sections (1, 1') include a plurality of flow channels, ! the total length of the flow channels in the first section (1) is greater than in the other sections, ! the flow resistance of the flow channels of the first section (1) is less than in the other sections, ! the sections are connected via one or more connecting pipe sections, preferably made of metal or plastic. ! 4. The radiator according to claim 1, characterized in that the place (VL) of the connection with the supply line and the place (RL) of the connection with the return

Description

2420-172247RU / 22

ONE-SECTION OR MULTI-SECTION RADIATOR, AT LEAST, WITH TWO DIFFERENTLY COMPLETED SITES

Description

A utility model relates to a two-section or multi-section radiator, in particular a flat radiator, according to the restrictive part of paragraph 1 of the utility model formula, to a single-section radiator made in the form of a plate, a heating body according to the restrictive part of paragraph 13 of the utility model, and also to an electric radiator according to the restrictive part of paragraph 28 of the utility model formula. In addition, the utility model relates to another radiator according to paragraph 40 of the utility model formula with a valve device for such radiators. In addition, the utility model relates to a thermostatic device that can be used with a valve device, respectively, a radiator according to the utility model in accordance with the restrictive part of paragraph 60 of the utility model formula.

Flat radiators are usually made of profiled, respectively, embossed half-shells, preferably of steel sheet, which are welded together, and horizontal and vertical flow channels can be formed. To increase thermal power, profiled steel sheets (convective profiles or sheets) are usually attached to the surface of the radiator, preferably with rectangular profiles. Flat radiators belong in their heating capacity to the most preferred types of radiators and are distinguished by their preferred decorative and hygienic properties, primarily due to the relatively small mass, which favorably affects the control parameters, in particular, taking into account energy-saving heating systems. As an alternative solution to the indicated design of flat radiators, it is possible to assemble the heating plates of flat radiators not from profiled half-pipes, but from separate flat pipes. This does not affect either the power attributed to the surface unit or the operating parameters, but only the appearance and cost of manufacture. Therefore, radiators of this design are not considered further.

Heating systems and thus also radiators are usually carried out taking into account the minimum possible external temperatures during the heating period (the so-called design parameters), at which a pleasant room temperature must still be ensured. The parameters for the radiator are, in particular, the amount of water passing through the radiator, the flow resistance, as well as the ratio of the radiator sections with predominantly convective and radiating heat transfer. Thus, these parameters are usually chosen for extreme heating conditions, while the so-called partial load range with a relatively lower required heat output, which prevails in most of the heating period, requires a different calculation and other parameters of the radiator.

To provide the required thermal power, the so-called single-section flat radiators have a single heating plate, the construction of which essentially consists of one part. In contrast, two-section flat radiators, i.e. radiators with a front plate facing the heated room and a plate located behind it usually have a symmetrical design, while a symmetrical flow always passes through the front and rear heating plates, i.e. with the same amount of water. This also applies, respectively, to both of the very front heating plates of a three-section or multi-section flat radiator.

With increasing awareness of the need to save heating energy, the requirements for the heat-insulating properties of buildings are being tightened, so that radiators even work on relatively cold days only in the partial load range, i.e. with low water temperature in the flow line of the heating network.

Just in the partial load range, i.e. at a relatively soft outside temperature, the indicated one-piece, respectively, symmetrical design detects disadvantages. In the partial load range, radiators should give only thermal power of several hundred watts, so that relatively little water passes through them. Due to the usually high proportion of convection in the total heat dissipation, the single or front portion of a single-section radiator with convective sheets facing the room will have a relatively low temperature. This negative effect is still amplified in multi-section radiators due to the symmetrical design, since not only the front section, but also the sections located behind it are used for heating. Thus, only part of the total heat is lost through the front heating plate. Thus, at low thermal power, the front heating plate remains relatively cold. However, the radiator surfaces that are cold in comparison with the body temperature negatively affect the microclimate of the room, since it is perceived as uncomfortable.

DE 196 14 330 C1 shows a radiator with two heating plates that are connected to each other through a connecting pipe to a valve. Both heating plates are made in the form of convectors, so that in this case both the above disadvantages and the disadvantages that will be indicated below are manifested.

DE 40 41 191 C2 refers to the junction with a multilayer plate radiator, consisting of a T-shaped connecting part located between two heating plates.

In addition, in the partial load range, it is added that suddenly added extraneous heat sources, such as uneven sunlight, suddenly switched on incandescent lamps, ceiling lights or computers, as well as additional people in the room, further reduce the required thermal voltage, which, with a high proportion of radiator convection, also very quickly leads to cold surfaces of the radiator. It should be borne in mind that with increasingly effective thermal insulation of buildings, radiators made earlier for high thermal capacities, even at extreme outdoor temperatures, should work almost exclusively in the range of partial loads.

Valve devices are also known in the art in which, using a relatively small travel range of the locking device, for example, a valve disc, a complete at least approximately linear range of flow cross-sectional control is provided.

Thus, the known valve devices are only suitable for relatively coarse control, which in thermostatic valves often leads to the fact that their control function essentially consists in frequently opening and closing the entire flow cross-section, which can lead to a relatively uneven change in room temperature accordingly regulated premises.

In addition, with the help of known valve devices, only one single connection point can be adjusted, which until now has not been a disadvantage with respect to known radiators.

Finally, mainly radiators are known from the prior art which have heating sections which are made uniformly for convection of heat and for radiating heat.

In the utility model DE 296 02 171 U1, a thermostatic valve is disclosed in which the valve body on the inlet side is tapered, respectively, in the form of a wedge. The narrow side of the wedge faces the hole, which forms the junction downstream of the front heating plate. Another hole, which is indicated by reference numerals, is provided on the wide side of the wedge. A heating medium is first directed into this opening when a wider area of the wedge-shaped valve body is manually or by means of a corresponding reduction in the thermostat capsule inside the thermostat valve and is retracted back a relatively large distance. Since two different locking devices are not provided, but only one wedge-shaped valve body, this valve body can only be moved uniformly.

DE 24 28 511 A1 shows a valve in which two valve springs are located on a valve pin, while one valve spring in a certain control range counteracts the other valve spring and, accordingly, can interact with it. Thus, the effect on the valve characteristics is realized, as is the case in the figurative sense also in the thermostat device according to the subject of a utility model, the description of which will be given below.

With an increasing understanding of the need to save heating energy, more stringent requirements are imposed on new buildings for thermal insulation properties. Whereas until now the room had, for example, a heat demand of 3000 W, and the heating surfaces in the corresponding room had to be designed for this maximum heat demand, the same room that is provided for in the building constructed in accordance with the regulation 95 for thermal insulation, may have a heat demand of 700 watts. In the heat demand of the corresponding room, which can be maximum and minimum, it is necessary to additionally take into account other influences. So, for example, in the corresponding room there may be additional sources of heat. For example, a computer may be in the room, audiovisual devices may be in operation or in standby mode, one or more persons may be in the room, sunlight may fall through one or more windows, etc. These effects can lead to the fact that the provided radiator must work with a decrease in power to 600 W or more, so that the room temperature does not increase excessively. In a radiator with a power of 3000 W, the difference of 600 W to be regulated determines the power fluctuation to be regulated in 20% of the total power of the corresponding radiator. With a radiator power of 700 watts, a power range of 600 watts causes a 86% difference to be regulated.

Thus, the following points of view follow from this:

1. The heat needed in the room can be provided, as a rule, with a radiator that gives off exclusively the heat of radiation, which is significantly more preferable for the health of the inhabitants of the room, since the air temperature can be lower, while the feeling of warmth and comfort among the inhabitants of the room improves. In addition, due to reduced convection, the air in the room is less loaded with dust particles.

2. The power range to be regulated is increased, so that the valve travel range used for regulation must be increased.

3. In the case of increased power requirements, taking into account the heat losses of the room, the radiating radiator is necessary at peak loads, for example, when the room is thoroughly ventilated or warms up again after a long cold period, it is possible to increase the power of the radiator. This power increase should be adjustable.

4. Due to the lower power consumption built according to the previous instructions for thermal insulation of the building, the corresponding valve devices, respectively, radiators can be controlled using a thermostat in a much narrower range, so it is desirable to have thermostats with faster, respectively, steeper and / or non-linear characteristics tripping, while such thermostatic devices should work without complex electronics, i.e. should work purely mechanically.

Given these problems, this utility model is based on the task of modifying the indicated at the beginning of single-section, respectively, multi-section radiators while maintaining the achieved heat output taking into account special conditions in the partial load range so that the room comfort, the surface facing the room, or at least , its large sections in the partial load range remain as warm as possible, in addition, the radiator in its design can be coordinated with the full and partial Booting, so that in general the preferred properties of planar radiators in all respects retained or even improved. In addition, the objective of the utility model is to solve all the problems posed by Resolution 95 on thermal insulation. In particular, there must be created: a valve device with improved response characteristics, respectively, with diversified transmission characteristics, and a corresponding radiator for the regular heat demand of the radiation with the possibility of increasing power, and a thermostatic device with nonlinear, respectively, fast response characteristics, in order to solve problems arising from a growing awareness of the need to save heating energy.

In this case, preferred properties are understood, in particular, high thermal power at relatively low heating and manufacturing costs, as well as good control parameters, i.e. signs that directly affect the comfort and microclimate of the heated room.

This problem is solved according to the utility model using the features of paragraphs 1, 13, 28, 40, and 60 of the utility model formula.

For this, a two-section or multi-section radiator according to a utility model preferably has a single connection point to the supply line, which is connected only to the front, respectively, facing the room heating plate. The warm water that flows through this junction with the supply line is distributed as evenly as possible along the upper longitudinal edge of the very front heating plate and through flowing channels running perpendicular to it and appropriately made along the front section facing the room. Thus, regardless of whether the radiator is operating in full load mode or in partial load mode, warmer water is thereby supplied to the front section than to the other sections. Consequently, with equal thermal power, the front section will be warmer and, therefore, more comfortable to the touch than in conventional systems. This favorable effect is preferably further enhanced by the fact that the front portion has a higher proportion of heat of radiation than the remaining sections of the radiator.

In order for water to flow from the front section to one or more sections located behind it, at least one connecting pipe is provided, which is preferably located in one lower corner of the radiator. The water that flows into the rear of the heating plate is preferably first deflected upward in the direction of the upper longitudinal edge, again distributed by the transverse channel located there and through the flowing channels running perpendicular to it, is led to the junction with the return line in the lower corner zone.

If three or more heating plates are provided, then the direction of the water in the third and in all subsequent sections can be carried out accordingly, which, from the point of view of hydrodynamics, corresponds to the serial connection of three or more radiators. However, in a three-section radiator, it is also possible to connect both rear heating plates in parallel and to connect them in series with the front heating plate, for which it is advisable to connect the connecting pipe between the front and second heating plates to the very last heating plate.

The advantage is that in any case, the front radiator is first supplied with warm water, so that it, in partial load mode, has a higher surface temperature compared to conventional radiators, so that it can give the impression of a more comfortable indoor microclimate.

Since the first, respectively, front section of the radiator heats up relatively evenly on its full surface just in the partial load range, it is still possible to compensate for the radiation of a window located above the radiator even with a small thermal power. In conventional radiators, this is not possible due to the high proportion of convection.

Another advantage is that the radiator according to the utility model provides a more uniform temperature profile on the surfaces of the radiator. Namely, due to the fact that the inflowing water is first directed exclusively through the front heating plate facing the room, the temperature of the water after passing the front radiator, for example, in full load mode, has not yet reached the temperature in the return line, as is the case in ordinary systems, and takes on a value that lies approximately in the middle between the temperature in the flow line and the temperature in the return line. Thus, the temperature distribution on the surface of the radiator is more uniform, which facilitates the implementation of the radiator, and also simplifies its design. Particularly favorable is a more uniform temperature distribution just in the partial load range, which is illustrated by the example that when using the radiator thermostat the water flow rate is set so that the temperature of the water after passing the front radiator drops to almost room temperature, while at the same heat output in a conventional radiator with a symmetric flow, this would take place already in the middle of the radiator, so that its surface would be felt on most of the cold and not tnoj.

The two-section radiator is expediently equipped with convective profiles, for example, only on its rear heating plate, so that such a radiator according to the utility model has a relatively large fraction of the heat of radiation in the entire heat output in the direction of the room, and the rear convection section in the partial load range no longer heats up. If such a radiator is sufficient for the specified design case, which sets the maximum thermal power at a very low outside temperature, then just at relatively soft outside temperatures, which are most of the time, the radiator will have a relatively large fraction of the heat of radiation. In contrast, at lower outside temperatures, the rear heating plate is also heated, so that the proportion of convection increases.

The advantage is that the indicator of such a radiator is not constant over the entire temperature range, and in the partial load range it is less due to a much larger fraction of the heat of radiation than at higher heating capacities, where the proportion of convection is larger. Thus, in the partial load range, a lower flow temperature is preferably required to achieve a certain heat output. Thus, the radiator according to the utility model, just in the partial load range, which makes up most of the heating work, helps to save heating costs.

Another advantage is that according to a utility model, the heating plate facing the room is warmer, which, although it is desirable for each radiator, since it is not the back wall that should be heated, but first of all the room, but it is not realized with the symmetrical execution of conventional radiators. Thus, less heat is lost to the outside through the usually thinner wall insulation behind the radiators. The radiator according to a utility model is preferably further provided on its rear side with a radiating screen, namely, usually of aluminum with a multilayer structure in order to increase thermal insulation in the direction of the wall. Such a radiating screen is also expediently provided between the front and rear heating plate in order to insulate the front heating plate from the rear heating plate. Another advantage is that digital modeling is facilitated and thus the design of the radiator, since it is very difficult to simulate just the singularities, respectively, in this case, a very large local heat loss.

Other advantages arise in special applications, for example, in kindergartens or when used in central heating systems. Just in kindergartens, it is desirable, accordingly, is prescribed by law that the front heating plate under no circumstances reach higher temperatures than, for example, about 50 ° C. While in conventional radiators this is possible only by lowering the temperature in the supply line and thereby the heat output, according to the utility model, the radiator needs only to be turned so that the hotter heating plate does not face the room, but toward the back wall, so that with equal heat output there is no danger of burns. This arrangement is also preferably used in central heating systems, in particular in the countries of the former eastern block, where temperatures in the supply line are partially realized up to 130 ° C. In conventional radiator systems made symmetrically, the inhabitants of the houses are regularly fired, in particular, near the junction with the supply line. In this case, you just need to just turn the radiator, so that the heating plate located on the side of the room accepts relatively acceptable temperatures. If at a later time the thermal insulation or the central heating system is improved, then it is necessary at lower temperatures in the supply line to simply turn the radiator according to a utility model, so that the above preferred properties are fully manifested without the need for a new radiator.

Typically, both the junction with the feed line and the junction with the return line are on the same side edge of the radiator. However, just with longer radiators, it is preferable, according to another embodiment, the central location of the junction. In this case, it is advisable to supply warm water in the middle to the front heating plate, where it then branches into the left and right flow until it is withdrawn, in the case of a two-section or multi-section radiator, in the middle zone of the backmost heating plate again into the return water line. In this case, warm water is expediently supplied at the upper edge of the front radiator. However, in one preferred embodiment, both the inlet and the outlet are located at the lower edge of the radiator, for which it is necessary to direct the incoming warm water upward, as will be explained below. It is also necessary on the rear radiator after the water flows from the front to the rear radiator.

The advantage of the central location of the junction just in long radiators is, again, a very uniform temperature distribution, since warm water that flows through the radiator in partial load mode at a relatively low speed must pass only half the length of the radiator before it leaves the front radiator, so that the side edge sections of the radiator will also be warm to the touch. Another advantage of this variant of the connection point is that such a radiator is just at low outside temperatures, when cold glass surfaces above the radiator lead to the so-called shaft of cold air, swirls it along the entire length of the radiator due to the upward flow of warm air and can lead to overcompensation. Thus, both at the front and at the rear end of the radiator, you can not be afraid of the cold falling air in the legs, as would be the case when connected on the same side of the inlet and outlet.

The indicated solution principles can, however, be applied not only to multilayer, but also single-layer radiators. Due to this, with comparable configurations, a radiator with a large fraction of the heat of radiation is possible, which is preferable which, even at low heating capacities, has a radiator surface that is pleasantly warm to the touch, while at high heating capacities such a radiator has a rather high proportion of convection, so it is also sufficient for less frequent extremely cold winter days.

Such a single-section radiator according to the utility model has, according to paragraph 13 of the utility model formula, at least two differently calculated sections, of which the first section, which preferably faces the heated room, is located in the direction of flow in front of other sections.

In such a radiator, water first passes through a junction with a supply line to a first portion, which is preferably located in the upper zone of the radiator. If the connection with the supply line is provided for structural reasons on the lower edge of the radiator, then according to a utility model, the water is first deflected to the upper section, for example, using a specially made flow channel or using a support insert, respectively, a spacer device, as will be explained below. Then the water is distributed along the entire upper longitudinal edge of the radiator and deviates in the direction of the return line. The first section preferably does not have convective profiles, due to which a very high proportion of the heat of radiation in the heat removal is provided, which is equal to about 50% for this section. Then water through the second section, which is preferably provided with convective profiles and is usually located in the lower zone of the radiator, passes to the return line. Preferably, as well as for hygienic reasons, convective profiles in this section are located on the side of the radiator facing away from the room.

The advantage is that such a radiator due to the transverse distribution of the flowing means along its entire length, respectively, the width is warm to the touch, namely, due to the high proportion of radiation heat even in the partial load mode. Even if the lower section remains “cold” at low heating capacities, it is just compared to conventional single-section radiators that the especially warm upper section is perceived more pleasantly. Therefore, this section is preferably located at the height of the knees, in particular in radiators in office buildings.

A particularly preferred embodiment is provided when the radiation section is directly provided with insulation that extends over at least most of its rear side. In this embodiment, it is possible to further reduce the proportion of convection of the radiation section and, by reducing convective heat loss, increase the surface temperature, as well as the fraction of radiation heat, very significantly.

To enhance this action, it is also advisable to separate the ratio of flows in the first and second sections, which is achieved, for example, due to greater resistance to flow or longer flow paths, respectively, a larger heat transfer surface in the first section.

For this, the flow channels in the first section preferably extend in the horizontal direction, while in other sections they extend, as usual, in the vertical direction. The first section is preferably separated from the remaining sections by a dividing wall through which at least one connecting channel passes. Due to the passage of the flow in the first section in the form of a meander and due to the location of the connecting channel, preferably diametrically opposite to the connection with the supply line, a large heat exchange surface in the first section is advantageously provided in order to increase the proportion of radiation heat.

The advantage is that a single-section radiator, due to different ratios of the fraction of convection heat and the fraction of radiation heat in the partial load and full load modes, also has a non-linear indicator, which is preferably reduced even at low heating powers, which, as mentioned above, leads to cost savings for heating.

This preferred effect can be further enhanced in both single-section and multi-section radiators, due to the fact that by means of adjustable mechanics, in particular, at low heating capacities, closing sheets are pushed over the convective profiles, thereby preventing air convection and thereby increasing the fraction of heat that is given off through the radiation of heat, compared with the portion removed by convection.

Therefore, the radiator according to the utility model is preferably provided in the area to which less heat is supplied with a partial temperature sensor with a temperature sensor. Usually this section is at the lower end of the radiator. The temperature sensor is preferably connected to an expansion volume which, with the aid of a temperature-dependent installation movement, displaces, as mentioned above, the closing louvers. In this case, the installation movement is controlled just so that the convective heat dissipation at high heating capacities and thereby higher temperatures in the sensor zone increases.

The advantage is that the radiator index in this case can be made variable, so that even in the case when convective profiles pass over the entire surface of the radiator, the radiator can be realized with optimal thermal power in full load mode with an optimally high proportion of radiation heat in partial load mode .

Other advantages of a single-section radiator are provided when bending its side sections back, respectively, to the wall, so that with double and essentially rectangular bending, they pass on the back side in parallel and at a distance from the front plate. This embodiment is very close to a two-section radiator. In such a radiator, the middle section is expediently not provided with convective profiles in order to maximize the fraction of radiation heat in this section facing the room. In contrast, convective profiles that preferably extend over the entire surface of the radiator are preferably located on the backwardly folded side portions.

If the rear surfaces of the radiator extend over almost the entire width of the front surface, then the middle section facing the room is expediently equipped with an inlet connection, while on the rear side in this case two existing connection points converge with the return line. Along with, in particular, a uniformly heated front surface in the partial load mode, this embodiment has a particular advantage in that it actually approaches a two-section radiator without the need to connect two heating bodies to each other using connecting pipes, which usually leads to higher manufacturing costs. In contrast, suitable bending of a single-layer radiator is relatively simple.

Just for countries with mild winters, another embodiment of a single-section radiator according to a utility model is particularly preferable, in which the return line is made in the form of a pipe passing behind the radiator along a substantial part of its length. This return is expediently equipped with many preferably circular or rectangular convective plates, which at low outside temperatures significantly increase the proportion of heat removed by convection, which, however, is barely heated on less cold days and, in particular, in partial load mode, since warm water is already cooled on the front surface of the heating plate to room temperature. In this embodiment, the front surface of the radiator is expediently not provided with convective sheets at all.

The advantage is that in this embodiment, at a relatively low cost, it is possible to create a radiator with sufficient thermal power and excellent control parameters. For this purpose, a pipe, which is already equipped with convective bodies, is used, which is commercially available in the form of an inexpensive product sold per meter. The diameter of this pipe, as well as the total area of convective bodies, can be coordinated with the design of the radiator. Such a radiator is preferably further provided on its front surface with convective profiles, which can be further closed by the already mentioned adjustable closing louvers.

To ensure the above-mentioned flow deviations from the lower corner zone upwards, the so-called supporting inserts, respectively, spacers with a shaped drain pipe and a transverse hole are used in the utility model. With appropriate installation, the transverse hole is in the continuation of the connecting section, i.e. connection points with the feed line, respectively, the connection points with the return line, or in the continuation of the connecting pipe for connecting the front and rear heating plate. In addition, the drain pipe is located in one of the vertically extending flow channels of the heating plate, so that the drain can preferably be concentrated in a specific flow channel.

The advantage is that when using the support insert, respectively, of the spacer device according to the utility model, the connection with the supply line can be located in the lower zone of the radiator, without the need to use a valve device located outside the radiator with a riser for directing water upward. This helps to further reduce manufacturing costs.

A valve device according to a utility model, which can preferably be used in a radiator according to paragraph 40 of the formula for a utility model, has a housing as well as a supply and return line, and a locking device such as a valve disc and valve seat is provided between the supply line and the return line. According to a utility model, this valve device is provided with at least two supply lines and at least two return lines, wherein the locking device is connected to each of two supply lines or to each of two return lines. In this case, a locking device or valve plate can be provided in a pipe section having approximately the diameter of the valve plate, for example, between supply lines and return lines, while both supply lines, respectively return lines, are arranged in the flow direction one after another, so that due to the permutation of the valve disc, first the flow can pass through one supply line, respectively, the return line with increasing permutation, and then gradually, and ultimately fully In this case, the flow can pass through another supply line, respectively, a return line due to further rearrangement of the valve disc.

At the same time, a certain leakage flow through the pipeline section can be allowed without circumventing a partially open valve disc, since, accordingly, the low leakage rate at low pressures used in central heating systems does not lead to circulation in this zone.

Appropriate valve devices can be used to supply the heating medium, for example, into two different heating bodies, for example, into the front radiating section directed into the room and into the convective section behind it. On the other hand, this valve with both supply lines, respectively, return lines can be installed on the connecting pipe, so that when you open, respectively, release the first inlet or outlet, a longer first, essentially linear control range becomes available, to which then, when opening the second input, respectively, the output, another linear control range is connected. In accordance with this, with reverse regulation, respectively, closing the valve disc, the corresponding linear control ranges arise.

In order to be able to close the inputs and outputs of the valve device according to the utility model individually also completely without leakage, each of the two inputs or each of the two outputs can be connected to a locking device, in particular, a valve plate with a corresponding valve seat. In this case, by first opening the first locking device, respectively, of the first valve plate, it is possible to pass the flow of the heating medium first through one heating section of the radiator, and then through another heating section of the radiator, or vice versa, to prevent the flow of the heating medium through them. If both inlet, respectively, outlet openings are transferred to one pipeline, then the linear characteristic of the valve can be significantly extended, according to the utility model.

The locking devices, respectively, valve seats are preferably located coaxially, respectively, on the same axis and, if desired, one after another. When controlling locking devices, respectively valve plates, using the provided valve pushers of the adjusting head or the corresponding thermostat head, it is possible to open both valve plates at different temperatures in order to transfer power to a suitably connected radiator in accordance with the room temperature. In the same way, it is naturally possible to control the valve device according to the utility model, while the corresponding two inputs, respectively, the outputs do not have to be made in the form of circular holes, and slotted, oval or triangular holes can also be made. In this case, the valve body, respectively, the valve body with inputs and outputs can be made of plastic, while the valve body can, if necessary, be sealed, respectively, pressed into a brass or copper body, as well as into a plastic body.

In order to ensure a long linear control range for an individual radiator, it is also in principle sufficient when a large flow cross-section is sequentially released, for example, by lifting two valve plates located in the same plane. In this case, one valve disc may be provided movable in the middle zone of another valve disc. By raising the inner valve disc, a certain flow zone is first freed up, whereby a second, annular valve disc surrounding the first valve disc can then be lifted to increase due to this free flow cross section in the valve apparatus and thereby extend the linear control range.

One of the two locking devices, respectively, one of the two valve plates must be preloaded relative to the other valve plate, so that when moving one locking device, preferably the valve plate, it remains on its preferably at least adjustable switching path at least at least a substantially closed position, so as to subsequently move in order to control the flow through the valve device. In this case, one locking device can be directly connected to the valve pusher, and other locking devices can remain pressed against the corresponding valve seat, for example, using a spring device. In this case, a gripping device can be preferably provided on one locking device, which grips, after a certain degree of movement of one valve disk relative to the other valve plate, another locking device, even when the provided spring device must still press the other valve plate to its corresponding valve seat.

Naturally, the capture of another locking device, respectively, of another valve disc can be done differently. So, for example, the spring device pressing the other valve disc to the corresponding valve seat can be made relative to the spring travel and the spring force so that the spring force decreases with a certain regulation, and the spring returning completely to its resting position captures the valve disc, whereby gradually and in the end, the corresponding hole is completely released.

For this, there are various possibilities of mechanical implementation, which will be obvious to a person skilled in the art when viewing this disclosure, and which in accordance with this should also be included in the scope of this utility model.

In one possible embodiment of the valve device according to the utility model, for each of the locking devices used, respectively, of the valve plates, a separate mechanical switching device can be provided. However, for the reasons of the required space and to provide better adjustability without the need to overcome synchronization difficulties, one mechanical switching device for both valve plates is preferable, while this mechanical switching device is triggered relative to both valve plates only with a delay.

According to another particularly preferred embodiment, the valve device according to the restrictive part of paragraph 40 of the utility model formula with one locking device is located in another locking device, while the other locking device has a passage, and one locking device acts on the flowing cross section of this passage. The passage may have one axial and one radial section, and one locking element can act on the flowing cross section of the axial and / or radial section of the passage. Moreover, this alternative embodiment of the utility model can be implemented with the additions indicated for other embodiments.

In an alternative embodiment of the utility model, the input, respectively, the output of the valve device can preferably enter into each other, so that when both locking devices are open, an increased flow cross-section is provided. In particular, the optionally provided radial section of the passage in the other locking device and the input, respectively, the output of the valve device can be located so that they both enter the same pipe, so that when both locking devices are open, then the specified increased flowing cross section. Due to this embodiment, it is also possible to increase the linear control range of the valve device according to the utility model in order to provide finer control, in particular of the radiator.

As mentioned above, with the actuator pusher, or actuator rod of the locking device, respectively, the locking device of the valve device, according to the utility model, a thermostatic device, respectively, a thermostat cartridge, which may contain, for example, a capsule with wax or paraffin, is connected.

Along with conventional radiators, valve devices according to a utility model can be used to regulate a specially designed radiator according to a utility model. Such a radiator according to claim 40 of the utility model formula, which is also part of this utility model, has one at least a predominantly intended heating section for radiation, and one at least a predominantly intended section for convection. As with a conventional radiator, at least one supply line and one return line are provided to provide the heating sections with a heating medium, preferably water. A valve or thermostat device is also provided, the valve or thermostat device having a flow-influencing section that corresponds to the radiative heating section and has another valve or thermostatic device that has a second flow-influencing section that corresponds to convective heating section.

Naturally, the valve or thermostat devices provided in the radiator according to the utility model can be replaced by the valve device according to the utility model, and the thermostat device can be optionally provided, said valve or thermostat device having, as the first flow-influencing section, , and the second section affecting the flow stream.

If both valve, respectively, thermostatic devices are separated from each other, then both valve, respectively, thermostatic devices should operate at different room temperatures, using thermostatic sections, such as wax capsules, or paraffin capsules with different response characteristics. The radiator may have one supply line and one return line for each heating section, or one common supply line and one common return line may be provided. Separate heating sections of this radiator according to a utility model can also be divided in space. In this case, for example, the radiative heating section can be provided as ceiling heating, while the convective heating section is located at a distance from the radiative heating section, for example, in a wall niche.

To ensure accelerated actuation of the valve device according to a utility model, respectively, of a conventional or corresponding utility model of a radiator, a thermostat capsule is proposed according to a utility model, in particular, a capsule with wax, respectively, with paraffin, which has a body, and the body has a volume subjected to thermal expansion medium, in particular paraffin or wax. In addition, there is provided a thermal expansion sensing, respectively, reduction of a region subjected to thermal expansion of the medium, which itself is movable. This section drives a mounting device, for example, a valve pusher, such as, for example, which can be used in locking devices of the valve device according to a utility model. Moreover, according to a utility model, the thermal expansion sensing, respectively, reduction of the medium subjected to thermal expansion is made in the radial direction so that this section can change its size non-linearly when the volume changes in the expansion direction, respectively, of the reduction. Another advantage of this type of thermostat capsule is that the compensating thermal expansion, respectively, the reduction of the area can provide an increased installation path.

Moreover, this section is preferably made so that it is in the axial direction, respectively, in the direction of volume compensation geometrically made so that a linear change in volume leads to a nonlinear change in the length of the section in the axial direction.

As a preferred geometric embodiment, a conically tapering or conically expanding shape can be used.

As an alternative solution, this section can be performed with a conically decreasing and / or conically increasing circle, or any other geometric shapes arranged in series can be used to provide certain switching characteristics that cause non-linear operation, respectively, faster operation.

It should be noted that the opened thermostat capsule is suitable not only for heating or cooling, for example, ceiling cooling, but also, for example, for automatically opening windows, respectively, for automatically actuating windows of greenhouses, etc., as well as for various other regulatory objectives. Similarly, the valve device proposed according to the utility model can be used not only in the field of heating, but also for various other technical purposes, where it is desirable to extend the linear range of flow control, respectively, where it is necessary to include two or more volumes (for example, radiator sections) in series in a closed contour, respectively, to exclude from the closed loop.

The following is a detailed description of the subject matter of the utility model with reference to the accompanying drawings, in which preferred embodiments are schematically shown. At the same time, additional advantages and features of the utility model are disclosed. According to a utility model, individual features can also be combined in any other way. In this case, the drawings show:

FIG. 1 - two-section flat radiator according to a utility model in an isometric projection in front;

FIG. 2 - a two-section radiator according to a utility model, with a central location of the junction with the supply or return lines;

FIG. 3 is a cross-sectional view of a two-section radiator in which convective sheets can be closed using an expansion volume and closing shutters;

FIG. 4 is a diagram of a single-section radiator according to a utility model;

FIG. 5 - a single-section radiator according to a utility model with back sections bent back and central connecting sections;

FIG. 6 - another single-section radiator according to a utility model with a rear pipe section, which is equipped with convective bodies;

FIG. 7 is a spacer device (support insert) according to a utility model for deflecting a heating fluid flowing through a radiator, namely, in the operating position;

FIG. 8 is a connection diagram of an electric flat radiator according to a utility model;

FIG. 9 is a cross-sectional view of a radiator according to a utility model installed in a front mounting space of a wall;

FIG. 10 is an embodiment in which a convective portion is located adjacent to a radiation portion;

FIG. 11A-11C is a longitudinal section of a first embodiment of a valve device according to a utility model in several different positions;

FIG. 12A-12C is a cross-sectional view of an alternative embodiment of a valve device according to a utility model in various positions;

FIG. 13 is a characteristic of a valve with respect to its regulation and a characteristic of a radiator with respect to the power parameters of a radiator;

FIG. 14 is a cross-sectional view of a thermostat capsule or wax capsule according to a utility model;

FIG. 15 is a cross-sectional view of another embodiment of a thermostatic capsule according to a utility model;

FIG. 16 - two-layer vertical heating wall in a separate isometric view;

FIG. 17 is a partial horizontal section through a passage for a heating medium in the upper zone of a vertical heating wall;

FIG. 18 is a horizontal section through the lower zone of the heating wall of FIG. 17;

FIG. 19 is another embodiment of a two-layer vertical heating wall in an exploded isometric view;

FIG. 20 is a partial horizontal section through the passage for the heating medium in the upper zone of the vertical heating wall of FIG. 19;

FIG. 21 is a horizontal section through the lower zone of the heating wall of FIG. twenty;

FIG. 22 - two-layer horizontal heating wall in a separate isometric view;

FIG. 23 is a vertical section through a portion of a horizontal heating wall in the area of the left dividing wall;

FIG. 24 is a vertical section through a portion of a horizontal heating wall to the right in the area of the guide sheets;

FIG. 25 is another embodiment of a two-layer horizontal heating wall in an exploded isometric view;

FIG. 26 is a partial horizontal section through the passage for the heating medium in the upper zone of the horizontal heating wall of FIG. 25;

FIG. 27 is a horizontal section through the lower zone of the heating wall of FIG. 26;

FIG. 28 is a vertical section through the heating wall of FIG. 26 in the right side zone;

FIG. 29 is another embodiment of a two-layer horizontal heating wall in an exploded isometric view;

FIG. 30 is a partial horizontal section through a passage for a heating medium in the upper zone of the horizontal heating wall of FIG. 29;

FIG. 31 is a horizontal section through the lower zone of the heating wall of FIG. 29;

FIG. 32 is a vertical section through the heating wall of FIG. 30 in the right side zone.

In FIG. 1 shows a two-section radiator according to a utility model with a so-called one-way connection, in which the place VL of the connection with the supply line is in the upper corner zone a of the front heating plate 1, and the place RL of the connection with the return line is in the lower corner zone d 'of the back heating plate 1 '. The warm water flowing through the junction with the feed line is appropriately distributed in the front heating plate before being directed through the connecting section c-c ', preferably a metal or plastic pipe, into the rear heating plate 1'. The heating plate is expediently made of two half-shells, respectively, of profiled plates, preferably of steel sheet or plastic, which are welded, respectively, connected to each other impervious to water. In order to evenly distribute the flowing means, preferably water, each profile is configured such that there are several flow channels extending in the vertical direction a-d in the heating plate, and a corresponding transverse flow channel is located on the upper and lower longitudinal edges a-b, respectively d-c. For uniform distribution, the corresponding transverse flow channels can expand funnel-shaped in the longitudinal direction.

Water that flows into the lower corner zone from the 'back heating plate must first be diverted to the upper corner zone b'. The natural tendency of warm water to rise up is expediently supported by a special embodiment of the rear heating plate 1 'in this corner zone. For this, a tube can be provided in one of the flowing channels extending in the vertical direction, which is connected to the connecting section c-c ', so that the inflowing water deviates upward. This tube can be discarded when this flow channel is separated from the lower transverse flow channel. However, for this purpose, a support insert according to a utility model can also be used, as will be explained below.

In the upper corner zone b ', the water again deviates in the horizontal longitudinal direction, as indicated by dashed arrows, before it again flows through the vertical flow channels in the direction of the junction with the return line in the lower corner zone d'. For ease of manufacture, the front and rear heating plates can be the same, so that the place VL of the connection to the feed line can also be in the lower corner zone d of the front heating plate. To do this, the warm water flowing through the connection point VL to the supply line must first be diverted to the upper corner zone, and preferably using the above measures.

To increase the fraction of heat removed due to convection on the heating plates, convective profiles can be located, respectively, sheets 2, which in the top view can have a rectangular or wave profile. In one preferred embodiment, both the front and rear heating plates are provided with a corresponding convective profile. However, it is also possible that only the rear heating plate is provided with one or two convective profiles. To further increase the thermal power, the radiator may also have a third heating plate, which is located behind the second heating plate and connected with it in parallel or in series.

Due to the use of an attachable, for example, screw-in connecting pipe c-c ', there is no need for a rigid connection of the heating plates to each other, and they can be adapted in the form of modules to the existing conditions.

Just in the partial load mode, i.e. at low heating capacities, respectively, at low flow rates of the flowing means, only the front heating plate 1 but not the rear plate is heated, which contributes to the comfort of the indoor microclimate. If convective profiles are not located on the front heating plate, then usually about 50% of the heat is removed from it through radiation. In this case, the radiator has a relatively small indicator, so that compared to a radiator with a large proportion of convection, it can be adjusted to lower flow rates, which provides better adjustability.

Just with long radiators, which are necessary for large rooms, in particular, office premises, the radiator in the area (a) of the connection to the supply line can be warm to the touch, but long before the connecting section (c) it is cold to the touch. This can lead to the fact that convection caused by the radiator far in front of the connecting section is no longer sufficient for the swirl and upward direction of the cold air falling downward, which comes from the window above the radiator. As a result of this, a person who is, for example, near the junction with the radiator feed line, feels heat near the legs, while another person in the area of the connecting section, on the basis of lowering cold air, will feel cold near the legs.

To eliminate this undesirable effect, in one preferred embodiment of the utility model shown in FIG. 2, a central arrangement of the connection points with the supply and return lines is provided, and preferably the symmetrical branching of the flowing warm water into the left and right flows. For this purpose, preferably, a transverse protrusion is provided below the connection point VL to the supply line, as shown in FIG. 2 as a cross-section. To transfer the flow to the rear heating plate in the lower corner zones (d, respectively, c), two connecting pipes are provided (d-d ', respectively, c-c'), at the ends of each of which there is a corresponding tube, a support insert according to the useful models or other suitable device for deflecting the flow in the rear heating plate up. After impact of the flowing medium into the upper corner zones (a ', respectively, b') of the rear heating plate, the flow deviates towards the middle (m). In the middle of the upper transverse flow channel, a partition can be made to separate the left and right flow, as shown by a vertical transverse line. Through the vertical flow channels, as well as the transverse flow channel, the fluid finally enters the place RL of the connection to the return line.

While the surface temperature in the radiator with the connection points with the supply and return lines located on one side falls across the entire width of the radiator, with the central location of the connection point with the supply line, the corresponding temperature profile is symmetrical and increases the user's comfort.

Since the flow passes through the front heating plate in front of the rear heating plate, the amount of heat generated by both heating plates is different, in particular in the partial load mode. It depends on the individual performance of the heating plates. Namely, to reduce the cost of manufacture, both heating plates tend to be the same. However, so that the radiator, even at low heating powers, can still have a warm front heating plate, the front plate should preferably have a higher proportion of heat of radiation, while the rear heating plate, in order to provide the necessary heat output on cold days, preferably has a high proportion of convection. Therefore, the front heating plate preferably does not have a convective profile.

As a compromise solution between these two extreme cases, in another embodiment of the utility model, adjustable closing louvers are provided which, depending, in particular, on the necessary heat output, regulate the flow of room air at convective profiles. In FIG. 3 shows in cross section a two-section radiator according to a utility model with adjustable louvers for two convective profiles 2.

For this, the front heating plate 1 facing the room is equipped with a temperature sensor 6, as well as an expansion volume 3, which is used, for example, to rearrange windows in greenhouses. Movable across the heating plates 1, 1 ', the valve pusher is connected on one side with an expansion volume 3 and on the other hand with one of the cover sheets 7 to allow the cover sheet to move when the temperature changes. To transfer the permutation movement to the second closing sheet, scissor-shaped guide rods 5 with a fixed middle or pivot point and two guide rods are provided, the corresponding one end of which is fixedly connected, and the corresponding other end is slidably connected with the cover sheet. In order to provide a return force, several spring elements 4 can be provided, so that the cover sheets 7, on the one hand, press on the scissor-shaped guide rods 5, and on the other hand, abut against the spring elements 4, which, in turn, abut against the holding frame . If only one convective profile is provided, then it is enough to connect the valve pusher directly to the cover sheet, so that there is no need for guide rods.

The expansion volume is a thermostatic capsule with a volume of liquid that expands when heated, and accordingly contracts when cooled. Media such as wax or paraffin are commonly used. The expansion volume is designed so that the thermal expansion of the volume is converted into a permutation movement of the valve follower. The corresponding permutation motion can be linear or depend on temperature, or approach a jump function at a given jump temperature. Using scissor-like mechanics, the permutation movement of the valve pusher is transformed into the transverse movement of the cover sheets. They are preferably designed such that at relatively high temperatures in the lower portion of the front heating plate, i.e. when the radiator must give off high thermal power, the cover sheets 7 open the convective profiles of the HF, so that air can pass unhindered at the convective profiles. In this case, the radiator gives off its heat mainly due to convection. The corresponding radiator index for a convective radiator is relatively large, for example, 1.5. When the temperature drops in the lower end portion of the front heating plate, the closing sheets 7 are rearranged and the convective profiles are closed, so that the proportion of heat given off by the radiation increases, and the total thermal power as a whole decreases. Due to the increased share of radiation heat, the corresponding radiator index becomes less, for example, 1.25, which favorably affects the control parameters in the partial load mode. In order to provide a switching action, in a particular embodiment of the utility model, memory alloys or bimetallic springs can be provided.

In addition, such regulation parameters can be achieved due to the fact that a thermostatic valve is used for regulation, which can regulate the flow in the radiation section and in the convection section independently of each other, or by adjusting the radiation section and the convection section independently of each other so that with a small heating load of the room, the radiation section is preferably loaded, and with a higher heating load of the room, the convection section is additionally loaded .

The solution according to the utility model can be applied not only in multi-section, but also in single-section radiators. For this, in FIG. 4 shows a one-section radiator according to a utility model with a first section 8, which is preferably located in the upper zone of the radiator, and a second section 9. The inlet is located on the first section 8, so that a stream of warm water passes through it in front of the second section. For a more even distribution of warm water, a transverse flow channel is preferably located on the upper longitudinal edge (a-b), to which other transverse flow channels or several vertically extending flow channels (not shown) are adjacent in the form of a meander, which can extend into the lower flow channels (indicated by thick vertical lines). However, between the first and second sections it is advisable to have a dividing wall 10, so that the flowing warm water is first concentrated in the upper section to give off heat in it, before entering through one or more connecting channels 11 into the lower section.

The upper section preferably does not have convective profiles, so that the upper section represents a flat radiator with a high proportion of radiation heat and a small radiator. The lower section usually has a convective profile 2, so that in the lower section most of the heat is removed by convection. If a dividing wall is made between the first section and the second section, then we are talking about the sequential inclusion of radiating and convective radiators.

When warm water flows at low heating capacities and thereby a low flow rate to the upper section, the water cools in the upper section before entering the lower section, so that a significant part of the radiator surface feels warm and thereby comfortable. In order to evenly distribute the temperature over the surface, it can be provided, in particular with very long radiators, that the connection to the supply line is centrally located, as indicated above.

With very long radiators or at high required heating capacities, it may be advisable to bend the side sections (a, b) of the radiator backwards, so that in an extreme case, as shown in FIG. 5, an almost two-section radiator is obtained in which the side portions preferably extend in parallel along a substantial portion of the front surface of the radiator. In this case, it is advisable to choose the above central connection points with the feed line and with the return line. In contrast to the initially indicated two-section radiator, in this embodiment, there is no longer any need to connect the front and rear heating plates to each other via connecting pipes, which leads to a significant reduction in manufacturing cost. The necessary bending of the radiator can be performed both before the connection, respectively, by welding both half-chambers (20a, 20b) of the radiator with each other, and after it.

Convective sheets 2 are expediently located only on the rear heating plate (1 ') or pass in the front section only along a relatively small part of the height of the radiator, so that this radiator also forms a radiation section and a convection section.

In FIG. 6 shows another embodiment of a single-section, respectively, two-section radiator with a front radiating section 8 and a rear convective section 9. For this, a single-section radiator according to a utility model or other flat radiator is connected through a usually flexible connecting pipe 13 made of plastic, metal or the like. with the pipe section 14 located behind the radiator. To increase the convection fraction, at least the rear pipe section is provided with a plurality of circular or rectangular convective bodies, respectively, plates 15, the surface of which is selected depending on the required total heat output. Since such pipes in the future will be offered in the form of very cheap goods sold per meter, it is possible to realize a radiator, which, on the one hand, is very cheap and, on the other hand, provides the advantages of a two-section radiator according to a utility model.

Such a radiator can be used, in particular, in southern countries with relatively mild winters, where a very high proportion of heat of radiation is usually required, but a very high proportion of convection is also required in a very small number of days. Due to the serial connection of the radiation section and the convection section, both conditions can be uniformly fulfilled. To further increase the proportion of convection, it is also possible to partially equip the front heating plate with convective sheets, as indicated by an intermittent wavy line.

In FIG. 9 is a cross-sectional view showing, as an example, a radiator structure according to a utility model in a mounting space in front of a wall. The installation space in front of the wall is often carried out when the bathrooms are being renovated in the form of a basement support column 26 in front of the wall. The support column serves to secure equipment, such as a washbasin 28 or the like. After the completion of the rehabilitation works, the support column is tiled and serves as a practical auxiliary surface 25.

This mounting space in front of the wall can be used for compact installation of the radiator. For this, it is preferable to install a single-section or multi-section radiator according to the utility model so that the radiating section 1 is located on the side of the room, while the convective section 1 'is located in the air duct 27. To ensure air convection, the mounting space in front of the wall is provided on its lower, respectively , the upper side of the intake and exhaust grilles (29, 30). The radiating portion 1 preferably ends flush with the front upper surface. The convective section can be made in the form of convective sheets or pipes with convective bodies of FIG. 6. Thus, a preferably compact wall heating surface is created which, due to the radiator structure consisting of one or more structural elements, just at low temperatures in the flow line, is preferably felt warm and comfortable.

In FIG. 10 shows another preferred embodiment of a multi-element radiator according to a utility model in which the radiating section 1 and one or more convective sections are adjacent to each other. The radiating section 1 is preferably located under the window 31 and is dimensioned so that its surface even on cold days, on the one hand, can compensate for the cold radiating surface of the window 31 above it and, on the other hand, due to its share of convection heat, can compensate for falling cold air. The convective section 1 'is adjacent, behind or under the radiating section with sequential inclusion in the direction of flow and preferably runs along the floor plinth. For this, the convective section is preferably made in the form of a pipe equipped with convective bodies, as described with reference to FIG. 6, and may, for reasons of appearance and hygiene of the room, in turn, be provided with a cladding.

In all of the above multi-section radiators, the front-most, preferably facing the room, heating plate is the warmest, while the heating plates located on the side of the wall can be relatively cold. This leads to the fact that less heat is uselessly lost through the wall of the house. To further prevent such heat loss in all radiators according to a utility model, a radiating screen 12 can be provided on the wall side, which is preferably made of multilayer aluminum and serves both for radiation insulation and thermal insulation in the direction of the wall. Such a radiating screen can also serve as insulation between the front heating plate and the heating plates located behind it.

As mentioned above, the heating medium, which flows through the connecting pipe section (c-c ', respectively, d-d') into the lower connecting zone (c ', respectively, d') of the heating plate 1 ', should be directed upward (b' , respectively, a '). While this can be expediently achieved using a suitably designed vertical flow channel, it is preferable to use a spacer device or a support insert for this, as explained below with reference to FIG. 7.

At the top of FIG. 7 shows a part of a half-shell, respectively, of a plate in a front view, namely, in front of the junction of this half-shell with a correspondingly made second half-shell. As mentioned above, this half-shell is profiled, respectively, provided with impressions 21, 22a, 22b, so that several flow channels 21 preferably pass in the heating plate according to the utility model, preferably in the vertical direction, as well as on the lower or upper longitudinal edge (not shown) essentially transverse flow channel 23 perpendicular to them. In the lower, respectively, left part of FIG. 7 shows a part of a radiator according to a utility model in a top view, respectively, in a transverse section, and in this embodiment, the connection point 18 to the supply line is located in the middle and on the lower longitudinal edge of the radiator, as is provided according to the utility model for long radiators.

In order to reject the water flowing through the VL, 18 connection to the water supply line, the vertical flow channel adjacent to the connection point to the supply line can be separated from the remainder of the lower transverse flow channel, for example, by a dividing wall. However, it is preferable to add both half-shells to one of the half-shells and place a specially made support insert, respectively, a spacer device. As shown in FIG. 7 of the embodiment, the support insert has a transverse hole 19a in its lower portion, which is preferably made in the form of a passage hole, as well as a hole 19b extending perpendicular to it. In its operating position, the perpendicular opening 19b is located in one of the vertically extending flow channels 21, while the transverse hole 19a is at a height and in continuation of the connection point 18 with the supply line. Due to this arrangement, the desired upward flow deviation is provided. While the deviation of the flow is preferably carried out through only one flow channel, the support insert can also be configured so that the flow passes through several flow channels.

In order for the support insert to occupy its predetermined working position, it preferably has an asymmetric shape. As shown in FIG. 7 of the embodiment, the outer contour of the support insert is aligned with embossing, respectively, profiling half, so that the vertically extending hole 19b lies in the flow channel 21. If the support insert is essentially ring-shaped, it can be provided in one place of the circumference with a flat 19c, which in a given working position is adjacent to the lower longitudinal edge. Due to the asymmetric execution, the automated installation of the support inserts is facilitated, for example, by means of a robot or by lightly shaking one half-piece.

For the manufacture of a heating plate, two plates of plastically deformable material, preferably a steel sheet or plastic, are first provided with embossments 22a, 22b. The profiled in this way the plate forms one half-pot 20a, 20b. Each half-chamber is equipped with one or more openings for accommodating valve portions and connecting portions VL, RL, respectively, connecting portions (c-c '). In these places, between the two half-shells, support inserts are preferably installed in order to perceive the very large forces that arise when connecting the two half-shells, respectively, when fastening the connecting sections, so that they do not lead to undesirable deformation of the half-shells. Where an additional flow deflection should occur, a support insert is used according to a utility model with directional flow output.

The above principle, according to which more heat is supplied to the first section with a high proportion of radiation heat, in particular, at low heating powers, than to the other sections of the radiator, can, however, be applied not only to radiators through which the flow of heating medium passes, but also for electric radiators, as shown in FIG. 8. Thus, in accordance with the indicated single-section, respectively, multi-section radiators, the radiating section 8 can be arranged, for example, above or in front of the convective section 9.

For this, according to the utility model, the respective sections are supplied with a number of electric heating elements (R ₁ ... R _n , r ₁ ... r _n ), which are installed directly in the radiator in the metal bushings or in the corresponding flow channels, as indicated above. Such an electric radiator can be equipped with a closed flow path with water, paraffin or the like, while convection of the flow is caused by the heating elements themselves or by using additional drive means. The heating elements of the respective sections are usually included in parallel.

As shown in FIG. 8 in an electric radiator according to a utility model, the parallel resistance of the first section 8 is less than the resistance of the second or other sections 9, so that more heat is supplied to the first section. It is advisable to control the individual heating elements of the sections individually or in cascades by means of an adjusting device, so that it is possible to coordinate the total heat output and, in particular, the fraction of heat given off by radiation and convection, individually and in accordance with indoor conditions. In particular, in a two-section radiator, it is preferable to turn off the heating elements of the plate on the wall side at the desired low thermal power, so that a radiator with a high proportion of radiation heat remains from the room side. For this, a relay 16 is additionally provided between both sections 8, 9 of the radiator.

In another preferred embodiment, the first, respectively, front heating section 8 is provided exclusively or additionally with self-regulating, respectively, self-limiting resistance, which is also used in so-called self-limiting pipe heaters. Self-limiting resistance preferably consists of ferrites which are embedded in a carrier material, such as, for example, an elastomer. Due to this, a temperature-dependent resistance is formed, which increases with increasing temperature, while an almost abrupt change in temperature can be provided, due to which the electrical resistance, for example, at low temperatures is independently limited.

If the first, respectively, front section 8 of the electric radiator according to a utility model is equipped with a self-limiting heating element, then it is possible without complicated regulation to ensure that the resistance of the first, respectively, front section 8 at low temperatures is less than the resistance of the remaining sections. Thus, in the partial load mode, when the surface of the radiator is relatively cold, the radiating portion of the radiator heats up more, so that the comfort of the room is improved. At medium temperatures of the radiator, the resistance of both sections of the radiator is the same, while at high heating powers, i.e. high temperatures of the heating plate, the surface temperature of the first section due to the self-limiting resistance element remains at a predetermined temperature, so that there is no danger of burns in the first, respectively, front section of the radiator.

Due to the aforementioned separation of the radiator according to the utility model into the first radiating section that passes through the stream and the convection section located downstream of it, it is possible to provide non-linear control parameters: with a low demand for heating, heat is transferred mainly through heat radiation, while with a large demand for When heated, most of the heat is transferred through convection.

Just in rooms with good thermal insulation and in the range of partial loads, the necessary thermal power can vary significantly, for example, when at the required thermal power of only 400 W, 300 W ceiling halogen lighting suddenly turns on or off. Therefore, to further improve the control parameters, the radiator according to a utility model preferably operates with a thermostatic valve with a non-linear, for example, progressive or regressive control characteristic. In this case, the control valve is preferably made so that the flow through the convection section can be completely or partially and independently of the regulation of the radiating section, respectively, to regulate.

While the utility model was described above with reference to the radiator through which the flow of warm flowing medium passes, the principle of different loading of the radiator zones separated in space can also be applied to cooling bodies, such as, for example, ceiling coolers through which the flow of cold flowing means. Thus, in a two-section cooling body, the first section is facing the room, while the rear section is located on the side of the wall or connected to another heat exchanger. In particular, in a single-section cooling body, it may be appropriate that the first transmission section is located in the middle or on the edge of the cooling body, while the remaining sections are arranged in a complementary manner.

In some very special applications, in particular in kindergartens or in central heating systems in the countries of the former eastern bloc, multi-section radiators according to the utility model can also be used with the opposite inclusion, so that the heating plate facing the heated room is colder than the one located behind her plate. Thus, fingers cannot be burned on the front heating plate, which is already required by law in some countries in kindergartens. If the building conditions, such as, for example, thermal insulation, or the purpose of the application are then changed, then the multi-section radiators according to the utility model can simply be turned so that the warmer heating plate faces the room, thereby providing the above advantages. Thus, coordination can be made without replacing or acquiring a new radiator.

In the following description of embodiments of the utility model shown in FIG. 11-15, the same, respectively, having the same functions features are indicated by the corresponding identical reference positions, which are shifted by one ten (i.e., 014 corresponds to 114, 250 corresponds to 350, etc.).

In FIG. 11A-11C show a first embodiment of a valve device according to this utility model. It should be noted that the section associated with the installation head, respectively, of the thermostat capsule is not shown in these figures, since this section can be performed in the usual way. Since the typical implementation of the valve is known to specialists in this field of technology, its detailed description is not given here.

Shown in FIG. 11A, an embodiment of a valve device 010 according to a utility model has a housing 012 that has an inlet 014 and two outlet openings 0.16a, 016b. Adjacent to the inlet 014 is an inlet pre-chamber 020, to which the connecting chamber 022 is connected. Inlet pre-chamber 020 is closed relative to the inlet 014 in the closed state of the valve by means of the valve disc 018a, which is adjacent to the valve seat 018b. The inlet chamber pre-chamber 020 may also be closed by chamber 022, namely, by means of another valve disc 024, which is adjacent to its corresponding valve seat 024b.

The valve plate 018a is rearranged by means of a pusher 028, to which an installation head or a thermostat head can be connected on the opposite side. The pusher 028 is connected to the front valve disc 018a through the insert shoe 029, the insert shoe at its opposite end having a gripping portion 030, through which the pusher 028 can be delayed to engage with the valve plate 024a. In this case, the valve disc 024a is preloaded with respect to its corresponding valve seat 024b by means of a spring 026, which is provided separately inside the housing 032 relative to the chamber 022.

As long as the path S along which the plunger 028 can move freely relative to the valve disc 024 is not traversed by the adjusting movement of the plunger 028, only the valve disc 018a moves, while the valve disc 024a loaded by the spring 026 remains in its closed position.

In the indicated last mounting position shown in FIG. 11B, the medium, respectively, the heating water, passes only through the inlet 014 to the inlet chamber 020 and out of it through the outlet 016a to the radiator, respectively, a portion of the radiator (not shown). With this installation, valve disc 024a is in its closed state so that the heating medium cannot enter the connecting chamber 022. As shown in FIG. 11B, with the valve 010 shown, the freewheeling path S of the pusher 028 is passed, so that the gripper 030 acts on another valve disc 024a.

The valve disc 024a held by the spring 026 in the closed position is gripped by further movement of the plunger 028 and releases a hole corresponding to the valve seat 024b in the connecting chamber 022.

In the latter, shown in FIG. 11C, a valve device 010 according to a utility model connects, for example, another radiator or another portion of a radiator to an input of a central heating system.

If both outlet openings 016a, 016b are connected to one common pipeline, then the linear characteristic of the valve regulation can be lengthened, however, only one connected volume, respectively, one radiator can be adjusted relative to the duct.

In FIG. 12A-12C show another embodiment of a valve device according to a utility model in various plant conditions.

In this case, the housing 112 has only one inlet 114, for example, from a central heating or cooling system, and one outlet 116 to a radiator, respectively, a cooling body. Another outlet 116a is provided in one of the valve plates, which in this case can be called not a valve plate, but rather a valve and streamlined body 124a.

The valve and streamlined body 124a is located in the valve body 112 and includes a valve disc 118a.

The valve and streamlined body 124a at its opposite end 114 end is sealed relative to the housing 112 of the valve device 100 with an O-ring seal. A valve follower 128 also sealed with an O-ring 140 and passes through the sealing portion 141 in the lower portion of the valve and streamlined body 124a, while the valve and streamlined body 124a is preloaded by a spring device 126 relative to its seat 124b.

The valve and streamlined body has an input section 114a adjacent to the input 114, to which an input pre-chamber 120 is connected in the valve and streamlined body, which is connected to a radially extended exit 116a in the valve and streamlined body, and then to the output 116 in the housing 112. Marked by 122 the region which is provided in the circumferential direction between the outer circumference of the valve body and the streamlined body 124a and the valve body 112 corresponds, in particular, to the connecting chamber 22 of FIG. 11A-11C when the embodiment of FIG. 11A-11C are connected to a common conduit by both of their outlets 16a, 16b.

The valve disc 118 and its control inside the valve and streamlined body 124a is carried out in the embodiment of FIG. 12A-12C, as in the embodiment of FIG. 11A-11C, which is also symbolized by the same reference numbers, so that a second description is not given.

When, as shown in FIG. 12B, the valve disc 118a is pushed back using the pusher 128, then the valve disc 118a releases an opening corresponding to the valve seat 118b, so that liquid can flow through the valve device 100 through the inlet 114 and the inlet connecting hole 114a, the inlet chamber 120 and the openings 116a, 116. .

In this embodiment, a freewheeling path S is also provided between the valve disc 118a and the valve and streamlined body 124a. Once the freewheel path S is selected by moving the plunger 128, the gripper 130 abuts against the body 124a, and with further movement of the plunger 128, the entire valve and streamlined body 124a is captured, whereby the body 124a rises from its corresponding valve seat 124b, which leads to the fact that the connecting chamber 122 also becomes available as a free flowing cross-section for the passage of the heating medium through the valve device 100 according to a utility model. This setting is shown in FIG. 12C.

Due to this embodiment, it is possible to regulate the heating medium by means of an installation mechanical device, i.e. synchronously controlled by a thermostat capsule, with a certain regulation characteristic, which has, for example, a relatively elongated range with respect to conventional valve devices.

If in the embodiment of the valve device 100 of FIG. 12A-12C, the connecting chamber 122 is closed, for example, in the area in front of the outlet 116, and another outlet is provided in the zone 116b of FIG. 12C, then, in principle, the valve device 010 of FIG. 11A-11C.

From the above explanations it follows that the valve device 10, respectively, 100 according to the utility model can be performed very differently to provide the desired characteristics, respectively, properties. Therefore, this description may lead one skilled in the art to make various equivalent decisions regarding a valve device according to a utility model, which should all fall within the protection scope of this utility model.

To illustrate this utility model in FIG. 13 is a graph of valve performance versus radiator performance. In this case, the valve characteristic reflects the regulation characteristic, and the radiator characteristic reflects the valve power characteristic, respectively, of the radiator.

As you know, a conventional radiator at about 50% of the flow of the heating medium, already due to the used heating medium, preferably water, has almost full thermal power. However, in this range the valve has only a small control range, so, in particular, in radiators of low power with conventional valves it is difficult to provide appropriate control. Valve devices 010, 100 and their modifications are able to provide a control range that is significantly improved relative to the valve characteristic shown, which displays the control characteristic of conventional valves, since due to the time-coordinated, respectively temperature-controlled movement of two locking devices, respectively, valve plates, favorable regulation ranges adjacent to each other are provided, so that the adverse return properties t pla known radiators.

In FIG. 14 shows a thermostat capsule 200 according to a utility model, which has a housing 250 that spans a volume 252. Volume 252 is filled with a medium that expands when exposed to heat, or compresses when exposed to cold. Commonly used materials are wax, paraffin or the like. Compensation section 254 extends into housing 250. Compensation section 254 has an opening 258 through which an actuator, such as a valve follower or the like, can pass to come into contact with surface 256 at the opposite end of section 254. As the temperature rises, the medium in volume 252 expands, and the flexible zone of section 254 is compressed in accordance with this thermally determined increase in volume, due to which section 254 is shortened in the axial direction and pushes the actuator in the axial direction, respectively respectively, a valve pusher.

This usual function of conventional thermostat capsules is modified in that the compressible zone 254 in this case is made conically tapering in the axial direction, so that at first a small change in volume leads to the fact that the installation device, or valve pusher, first moves along a long path. With a further increase in volume, the drive path of the installation device, respectively, of the valve follower is proportional to the conically expanding cross section of section 254.

This ensures non-linear thermal response of the thermostat capsule according to the utility model.

The modification shown in FIG. 14 of the thermostat capsule 200 is shown as a modified thermostat capsule 300 in FIG. 15. In this case, the section 354 is made in the form of an opposite trapezoid or cone, however, with the corresponding geometric design, it basically has the same non-linear control characteristic as in the embodiment of FIG. fourteen.

Regarding the valve device according to the utility model, it follows from the above description that, according to the utility model, either inputs or outputs can be made, because depending on which end of the radiator the corresponding valve device is connected, the radiator can have either one input and two output, or two inputs and one output, respectively, two inputs and two outputs. If the valve device according to the utility model has only one supply line and one return line on the housing, then the corresponding valve device can be located both at the input of the radiator and at the output of the radiator, so it is necessary to appropriately adapt the function of the valve device according to the utility model.

Since design measures for fitting the valve device are known to those skilled in the art, there is no need for further explanation in this description.

In FIG. 16-32 show preferred applications of the utility model for so-called heating walls, which consist of vertical and horizontal flat heating pipes that are connected to each other with the possibility of fluid flowing through vertical or vertical manifold pipes or channels.

In FIG. 16 shows a two-section vertical heating wall with a so-called one-way connection, in which the place VL of the connection to the supply line is in the upper corner zone of the front heating plate 1, and the place of the RL connection to the return line is in the lower corner zone of the rear heating plate 1 '. The warm water flowing through the junction with the feed line is appropriately distributed in the upper heating plate before it is guided through the connecting section, preferably a metal or plastic pipe, into the rear heating plate 1 ′. The passage of water in the upper zone is shown in FIG. 17, and in the lower zone - in FIG. 18. The connecting pipes are designed so that the heating medium can enter the rear heating plate only in the upper right zone. For this, tools are used in accordance with the above options for performing a utility model, which specialists can simply transfer to heating walls. In FIG. 19 shows a vertical heating wall in which the heating plates are connected to each other by T-elements in the upper and lower corner zones. The flow of the heating medium is regulated as shown in FIG. 20 and 21, through the T-shaped elements, while they are made closed or passing fluid, so that always the front heating plate receives the flow of heating medium sequentially in front of the rear heating plate.

In FIG. 22-32 show various embodiments of horizontal heating walls, i.e. heating pipes are arranged horizontally and connected to each other from the side by collector pipes in a compact design. The flow of the heating medium is regulated as shown in FIG. 23 and 24, through the guide sheets in the side zones, which are configured so that the front heating plate always receives a flow sequentially in front of the rear heating plate.

In FIG. 25-32, other embodiments of horizontal heating walls are shown, and the flow of the heating medium is regulated similarly to the above embodiments for vertical heating walls, i.e. through suitably made connecting pipes or T-shaped elements. In order to avoid repetitions, a description thereof is not given and reference is made to the above embodiments.

Claims (63)

1. At least a one-section, preferably two-section or multi-section radiator, in particular a flat radiator comprising  the place (VL) of the connection to the feed line,  return line connection (RL),  the first passing stream and preferably facing the heated room area (1), and  at least one other transmissive flow and preferably a rear portion (1 ′), characterized in that through the first section flows substantially uniformly in front of other sections, and only in the lower end zone of the first section (1) is provided at least one junction with at least one other section (1 '). 2. A radiator according to claim 1, characterized in that the first section (1) is designed so that more heat can be supplied to it, at least at low thermal power, than to the rest of the radiator sections. 3. The radiator according to claim 1 or 2, characterized in that the sections are made in the form of plates and are preferably formed from profiled plates or flat pipes that are connected to each other through collector channels, in particular from a steel sheet,  the plates are profiled so that the sections (1, 1 ') include many flow channels,  the total length of the flow channels in the first section (1) is greater than in the remaining sections,  the resistance to flow of the flow channels of the first section (1) is less than in other sections,  sections connected through one or more connecting pipe sections, preferably of metal or plastic. 4. The radiator according to claim 1, characterized in that the place (VL) of the connection to the supply line and the place (RL) of the connection to the return line are located respectively on one vertical longitudinal edge of the radiator, or in the middle of the corresponding horizontal length of the radiator. 5. The radiator according to claim 1, characterized in that the first section (1) is located above, respectively, under the second section (1 '), and preferably both sections are made in the same radiator, respectively, one heating plate. 6. Radiator according to claim 1, characterized in that the surfaces of the sections (1, 1 ') are provided with convective profiles (2), which preferably have a rectangular or wave profile. 7. The radiator according to claim 1, characterized in that the first section (1) does not have a convective profile. 8. A radiator according to claim 6, characterized in that adjustable closing louvers (7) are provided for changing the cross section of the flow around convective profiles (2), moreover, the closing louvers (7) are designed to change depending on the temperature so that at low temperature the supply line in the first section (1) closing the blinds (7) essentially close the convective profiles (2). 9. A radiator according to claim 8, characterized in that a thermal sensor (6) is provided, which is located in the first section (1). 10. A radiator according to claim 8 or 9, characterized in that for the rearrangement of the closing blinds (7) a temperature-dependent compensating volume (3) or an alloy with memory or bimetal for the rearrangement of the closing blinds (7) is provided. 11. The radiator according to claim 1, characterized in that an insulating layer is provided, preferably of single-layer or multilayer aluminum, between the first section and at least one section located behind it, preferably in the first section. 12. The radiator according to claim 1, characterized in that it is provided on the side of the wall with a radiating screen, preferably made of multilayer aluminum. 13. Single-section, in particular, a flat radiator containing  the place (VL) of the connection to the feed line,  return line connection (RL) and  made in the form of a plate-shaped and flow-through heating body, characterized in that at least two differently made sections (8, 9) are provided, the first section (8) in the direction of flow being located in front of the remaining sections, and more heat can be supplied to it at least at low heat output than the rest of the sites. 14. The radiator according to claim 13, characterized in that at least on the surface of the radiator are convective profiles (2), which, when viewed from above, preferably have a rectangular or wave profile. 15. A radiator according to claim 14, characterized in that the total surface of the convective profiles of the first section (8) is smaller than the surface of the remaining sections. 16. The radiator according to item 13, wherein the first section (8) does not have convective profiles. 17. The radiator according to any one of paragraphs.13-16, characterized in that the radiator is made of profiled plate material, preferably steel sheet, with the formation of many flow channels or flat pipes that are connected to each other using collector channels, and the flow resistance flow channels of the first section (8) is less than the resistance of the remaining sections. 18. A radiator according to claim 13, characterized in that the radiator is profiled so that at least the first section (8) contains several flow channels that extend horizontally and in the form of a meander up or down, and / or, at least the second section (9) is profiled so that it contains several flowing channels extending in the vertical direction, the first section (8) being separated from the remaining sections by at least one partition (10). 19. The radiator according to claim 18, characterized in that only one connecting channel (11) passes through the partition (10). 20. The radiator according to claim 19, characterized in that the connecting channel (11) is located on one vertical longitudinal edge of the radiator. 21. A radiator according to claim 18, characterized in that several connecting channels (11) pass through the partition (10). 22. The radiator according to claim 13, characterized in that the place (VL) of the connection to the supply line is located on one vertical longitudinal edge of the radiator or in the middle of the horizontal length of the radiator. 23. The radiator according to claim 13, characterized in that the radiator, at least on one longitudinal edge, is bent back to form a rear, preferably facing the wall, surface of the radiator, which extends substantially parallel to the front surface of the radiator, the feed line being located on the front preferably facing the heated room surface of the radiator. 24. The radiator according to item 13, wherein the return line (RL) is made in the form of a pipe and passes behind the radiator along a substantial part of its length. 25. A radiator according to claim 24, characterized in that the pipe return line (14) is provided with a plurality of circular or rectangular convective bodies (15). 26. A radiator according to claim 13, characterized in that when executed with two sections, the first section (8) is located in the middle between the remaining sections (9). 27. A radiator according to claim 13, characterized in that it is provided on the side of the wall with a radiating screen (12) preferably made of multilayer aluminum. 28. A single-section or multi-section electric radiator, preferably a flat radiator, containing at least two different sections (8, 9), each of which is equipped with a plurality of heating elements (R ₁ ... R _n , r ₁ ... r _m ), and an adjustment device, characterized in that the adjustment device is designed so that the electrical resistance of the sections is independently adjustable, and more heat is supplied to the first section, at least at low thermal power, than to the remaining sections. 29. Radiator according to claim 28, characterized in that when performing single-section and generally with two sections, the first section (8) is located above the second section (9), or the first section (8) is preferably facing the heated room and is located in front of the others sections (9). 30. The radiator according to claim 28, characterized in that the total electrical resistance of the first section is less than the corresponding total resistance of each of the remaining sections. 31. A radiator according to any one of paragraphs 28-30, characterized in that the first section (8) is equipped with a self-regulating, respectively, self-limiting resistance, preferably ferrites embedded in the elastomer. 32. A radiator according to claim 28, characterized in that the sections are made of profiled plate material, preferably steel sheet, with the formation of many flow channels (21, 23), or of flat pipes that are connected to each other by collector channels. 33. The radiator according to claim 32, characterized in that it forms at least one hollow space through which the flowing means, preferably water or paraffin, flows. 34. A radiator according to claim 28 or 33, characterized in that the heating elements are integrated directly into one or more flowing hollow spaces (21), or the heating elements are integrated into metal bushings, and the bushings are integrated into flowing hollow spaces (21). 35. A radiator according to claim 28, characterized in that at least one spacer device (19) is located between the plates (20a, 20b), respectively, by the half-shells of the heating plate (1, 1 '). 36. A radiator according to claim 35, characterized in that at least one of the spacer devices (19) has at least one flow channel (19b), which provides a predetermined directional deviation of the heating medium. 37. A radiator according to claim 35 or 36, characterized in that the spacer device (19) comprises means (19b, 19c) that provide a predetermined direction when the spacer device is installed between half-cups, respectively, plates of a heating plate that contain a pipeline (VL). 38. A radiator according to claim 37, characterized in that the guiding means (19b) comprise at least one flow channel (19b), respectively, consisting of it. 39. Radiator according to claim 38, characterized in that the guiding means (19b) have an outer contour, which at least approximately corresponds to the contour (21, 22a, 22b) between half-cups, respectively, plates for improving, respectively, providing orientation . 40. A radiator, in particular a plate radiator, is preferred for central heating systems, comprising the following features: a heating section intended primarily for radiation, intended mainly for convection heating section, one supply line and one return line, valve, respectively, thermostat device, and valve, respectively, thermostat device has a first, affecting the passage of the flow section, which corresponds to the radiative heating section, and another valve, respectively, thermostatic device, which has a second affecting the passage of the flow section, which corresponds to the convective heating section, characterized in that radiative and convective heating sections are both operable by means of a valve device comprising case containing at least two inputs (014, 114), respectively, two supply lines or at least two outputs (016a, 016b; 116, 116a, 116b), respectively, two return lines, a locking device (018a, 018b, 024a, 024b; 118a, 118b, 124f, 124b), which is connected to each of the two inputs or to each of the two outputs, moreover each of the two inputs (014) or each of the two outputs (106a, 016b) corresponds to one locking device (018a, 024a), and at least one of the locking devices (018a, 024a; 118a, 124a) is movable in certain areas, independently of others. 41. The radiator according to claim 40, characterized in that the locking devices (018a, 024a; 118a, 124a) are preferably located on the same line in the axial direction, in particular, one after another, and are differently triggered, in particular, at different temperatures, or the locking device (018a), due to axial movement, opens or, accordingly, closes one after another two inputs (014) or two outputs (016a, 016b; 116a, 116b). 42. The radiator according to paragraph 41, wherein one locking device, in particular a valve disc, is preloaded relative to another valve disc using a spring device (026; 126), so that the preloaded valve disc when rearranging an unloaded pre-valve disc along a preferably adjustable path, it remains, independently, in its at least substantially closed position for gripping, preferably by means of a gripping device, when the permutation path is traveled . 43. Radiator according to any one of paragraphs.40-42, characterized in that for each locking device, respectively, each valve plate corresponds to a separate permutation mechanical device. 44. Radiator according to claim 40, characterized in that one locking device (118a) is located in another locking device (124a), the other locking device having a passage (114a, 120, 116a), which preferably has an axial section and a radial section, moreover, one locking device acts on the flowing cross section of the passage. 45. The radiator according to claim 40, characterized in that the other locking device (018a; 118a) is triggered before the first locking device (024a; 124a). 46. The radiator according to claim 40, characterized in that the valve pusher (028; 128) acts on one locking mechanism, while the other locking mechanism (024a; 124a) is preloaded with a spring device, so that when moving the valve pusher (028; 128 ) first, one locking mechanism (018a; 118a) is triggered, and the other locking mechanism (024a; 124a) only works when the gripper (030; 130) on one locking device (018a; 118a), respectively, the valve pusher (028; 128) captures another locking mechanism (024a; 124a). 47. A radiator according to claim 41, characterized in that preferably the radial passage (114a, 120, 116a) in another locking device and the input, respectively, the output in the housing (112) enter into each other, so that when both locks (124a; 118a) open, an enlarged flow cross-section is provided. 48. The radiator according to claim 47, characterized in that its inputs, respectively, the outputs (114, 116b, 116, 116a, 114a, 120) have flow cross sections aligned with each other, so that when all the inputs and outputs are open, the cross section of the inputs essentially corresponds to the cross section of the outputs, respectively, vice versa. 49. The radiator according to claim 40, characterized in that two inlets, respectively, two outlets are included in one inlet pipe, respectively, one outlet pipe. 50. The radiator according to claim 49, characterized in that a thermostatic device is connected to the valve pusher, which comprises a thermostat capsule, in particular a capsule with wax, respectively, with paraffin. 51. The radiator according to claim 40, characterized in that the locking devices are at least two valve plates that are movable relative to each other, and preferably, using a predetermined stroke range, first one valve plate releases a flowing cross-section, and then another valve plate moves for additional release of flowing cross-section. 52. The radiator according to item 46, wherein the rod, respectively, the valve pusher (028; 128) first captures the first valve disc and delayed captures the second valve disc. 53. A radiator according to claim 51 or 52, characterized in that one of the valve plates is preloaded relative to the other valve plate using, for example, a spring device (026; 126). 54. The radiator according to claim 42, characterized in that the valve seats corresponding to the valve plates are in the same plane, respectively, valve plates in the closed state of the valve are in the same plane. 55. The radiator according to claim 40, characterized in that the valve, respectively, thermostat device (010; 100) has both a first section that affects the flow stream and a second section that affects the flow stream. 56. The radiator according to claim 40 or 55, characterized in that both valve, respectively, thermostatic devices (010; 100) operate at different room temperatures. 57. The radiator according to claim 40, characterized in that each heating section has one input and one output. 58. Radiator according to 56, characterized in that both valve or thermostat devices (010; 100) have a common housing, the housing having one inlet and one outlet for each of both heating sections, or one outlet and for each of both heating sections, one inlet. 59. The radiator according to claim 40, characterized in that the convective heating section and / or the radiative heating section are divided into partial sections, which are connected, respectively, are turned off manually and / or automatically, for example, by means of manual valves, thermostatic valves or the like. P. 60. Thermostatic capsule, in particular a capsule with wax, respectively, with paraffin, containing case the volume of the medium undergoing thermal expansion, in particular paraffin, or wax, contained in the housing, compensating for thermal expansion, respectively, reducing the area, which in itself is preferably mobile, characterized in that the section (254; 354) in the radial, respectively, axial direction is made so that this section when changing the volume (252; 352) in its axial direction non-linearly changes its length. 61. The thermostat capsule according to claim 60, characterized in that the section in the axial direction, respectively, in the direction of volume compensation is geometrically configured such that a linear change in volume leads to a nonlinear change in the length of the section in the axial direction. 62. Thermostatic capsule according to claim 60 or 61, characterized in that the section is made tapered or tapered with an axially increasing circumference. 63. The thermostatic capsule according to claim 60 or 61, characterized in that the area (254; 354) has at least one zone that narrows conically and / or conically expands.