LT5575B - One-sectional or multisectional heater with at least two differently fitted segments - Google Patents

Abstract

The invention relates to two-sectional or multi sectional heater, especially to plane heater according to common part of claim (1) or to one sectional heater with plate shaped heating body according to common part of claim (28) and to electrical heater according to common part of claim (39). Furthermore the invention relates to method for producing such heaters according to common part of claim (40) and to another heater according to common part of claim (43), which comprises a valve device forsuch heaters. Furthermore the invention comprises a thermostatic device, which can be used with a valve device according to invention, according to common part of claim (63).

Description

The invention relates to a two-sectional or multi-sectional radiator, in particular a flat radiator according to the general part of claim 1, a single-section radiator with a plate-shaped heating body according to general part 20 of the invention and an electric radiator according to general part 28 of the invention. The invention further comprises a method of manufacturing such radiators according to claim 40 of the invention and another radiator according to claim 43 having a valve arrangement for such radiators. The invention further encompasses a thermostatic device which can be used with a valve device, namely a radiator according to the general paragraph of claim 63.

Flat radiators are usually manufactured from profiled half-shells with embossing, preferably steel sheet, which are welded to one another, and can thus form horizontal as well as vertical ducts. Profiled steel sheets (convection profiles or sheets) are best fitted with rectangular profiles to increase heating power on heating body surfaces.

Flat radiators are among the best types of radiators in terms of their heating capacity, along with valuable decorative and hygienic properties, relatively low weight, which positively influences their control parameters, especially with regard to energy efficient heating systems. As an alternative to the described design of flat panel radiators, flat panel radiator heating panels, not consisting of profiled semi-shells, but of individual flat tubes are available. This does not affect either specific power or operating parameters, only appearance and production costs. Therefore, radiators of this design will not be considered further.

Heating systems, and thus radiators, are usually calculated by estimating the lowest possible outside temperature (so-called calculation parameters) during the heating period, which still guarantees a comfortable room temperature.

Calculation parameters of the radiator include, for example, the amount of water passing through the radiator, the resistance to flow, and parts of the radiator having essentially convective and radiant heat transfer. These parameters are usually selected for extreme heating conditions, while the so-called partial load range with the relatively lower heating power that prevails most of the heating season requires different calculations and different radiator parameters.

For the required heat output, so-called single-section flat radiators have a single heating plate, the structure of which is essentially one-piece. In contrast, two-section flat radiators, i.e. radiators with a front facing a heated space, a plate and a plate behind it, generally have a symmetrical design, whereby a symmetrical flow is always passed through the front and rear heating plates, that is, an equal amount of water. This is also true for a three-sectional or multi-sectional flat radiator on both front heating panels.

With the increasing awareness of the need to save heating energy, the requirements for thermal insulation of buildings are tightened, so that even in relatively cold days, radiators work only at partial load, that is, at low inlet temperatures.

It is under partial load conditions, that is, at relatively mild external temperatures, that the symmetrical design of a single part, respectively, is negatively affected. Under partial load radiators only need to supply a few hundred watts of heating power so that relatively little water passes through them. Because of the generally high convection rate in the total heat transfer, the single or front, room-facing segment of a single-section radiator with convection steel sheets will have relatively low temperatures. This negative effect is exacerbated by the symmetrical design of the multi-sectional radiators, because not only the front segment but also the segments behind it serve for heating. In this way, only part of the heat is released through the front heating plate. At the same time, with low heating power, the front heating plate remains relatively cold. But relatively cold relative to body temperature radiator surfaces adversely affect the indoor microclimate, which is perceived as uncomfortable.

DE 19614330 Cl describes a radiator with two heating plates interconnected by a connecting pipe having a valve. Both heating panels are calculated as convectors, so in this case there are both the above mentioned drawbacks and the drawbacks that will be mentioned later.

DE 4041191 C2 relates to a connection to a multilayer paneled radiator comprising a T-shaped connection element located between two heating panels. In addition, unexpected extraneous heat sources, such as uneven sunlight, unexpected incandescent lamps, ceiling lights or computers, as well as people in a heated room, also contribute to a partial reduction in the required heating power. For a large part of the radiator convection, this is very quickly caused by the cooling of the radiator surfaces. It should be borne in mind that, with increasing thermal insulation in buildings, previous high-output radiators, even at extreme outside temperatures, must operate almost exclusively under partial loads.

Valve arrangements are also known in the art, which provide a full, at least approximately linear, passage cross-sectional adjustment range for a closing device, such as a valve plate.

Thus, known valve arrangements are only suitable for relatively coarse control, which in the case of thermostatic valves often results in their control function essentially leading to frequent opening and closing of the full cross-section, which can cause relatively uneven changes in room temperature.

In addition, known valve arrangements can only regulate a single junction, which has not been a drawback with prior art radiators.

After all, the most well known in the technical art are radiators that have heating segments made in the same way, convection and radiation combined.

A useful model according to DE 29602171 UI shows a thermostatic valve in which the valve body is made in the wedge-shaped manner on the entrance side. The narrow portion of the wedge is facing toward the opening formed in the direction of flow, with the first heating plate. The other opening, indicated by the indicated positions, is provided on the broad part of the wedge. This opening is initially directed to the heating medium by pushing back the widest part of the body of the wedge valve by a sufficiently large distance, either manually or by shrinking the thermostatic capsule inside the thermostatic valve. Since there are no two different shut-off devices and only one wedge valve body, this valve body can only be displaced in one way.

DE 2428511 A1 discloses a valve in which two valve springs are disposed on a valve plug, whereby one valve spring can act against the other valve spring, respectively, within a certain adjustment range, respectively.

In this way, the characteristics of the valve are affected where, in a sense, this also occurs in a thermostatic device according to the present invention, which will be described below.

With increasing awareness of the need for energy savings in heating, new homes are subject to stricter requirements for thermal insulation. While the heat requirement for a room to date was, for example, 3,000 W and the heating surfaces in the room in question had to be calculated for this maximum heat requirement, the same room in a building built under the respective heat insulation ordinance 95 may have a heat requirement of 700 W. Additional factors must be taken into account when estimating the heat demand of the room in question, which may be maximum and minimum. Thus, for example, additional heat sources may be available in the room in question. For example, a room may have a computer, work or standby audio-visual equipment, a room may have one or more persons, the sun may shine through one or more windows, etc. These factors may result in the intended radiator being reduced to 600 Watt. or more so that the room temperature does not increase excessively. In a radiator with 3000W adjustable power difference of 600W, a variable power variation of 20% of the total power of the respective radiator is achieved. At 700 W radiator power, the 600 W power change range results in an 86% adjustable power variation.

This leads to the following conclusions:

1. Providing the necessary room heat requires, as a rule, a radiator that provides exclusively radiant heat, which is most desirable to the health of those indoors, since, at lower air temperatures, the perception of indoor heat and comfort is improved. In addition, reduced convection results in less airborne dust particles.

2. The adjustable power range increases, so the valve stroke range used for adjustment must be increased.

3. When the requirements for the radiator power calculated for the heat loss of the room are increased, maximum capacity shall be provided, for example when the room is essentially ventilated or after a long cold period, to increase the capacity of the radiator. This power boost must be adjustable.

4. Because the power requirement of a building constructed in accordance with the previous thermal insulation instructions is reduced, the corresponding valve units, radiators, respectively, can be thermostatically controlled within a much narrower range. Therefore, it is desirable to have faster, respectively steeper and / or non-linear operating thermostats, and such thermostatic devices must operate without complicated electronics, i.e. y. must operate purely mechanically.

In view of these problems, it is a primary object of the present invention to modify the aforementioned single-section radiators, respectively, with multi-section radiators, while retaining attainable heating power under particular conditions within the partial load range so as to increase room comfort and at least stay as warm as possible in the partial load range. In addition, the design of the radiator could be adapted to operate in full or partial load mode, so that in general, the desirable properties of flat radiators would be preserved or even improved.

Furthermore, the object of the invention is to solve all the problems arising from thermal insulation regulation 95. Specifically, a valve device having improved performance characteristics, with diversified pass-through characteristics, and an appropriate radiator for regular, radiant heat demand that can be increased, and a thermostatic device with non-linear, respectively, quick-acting characteristics to solve problems should be provided. stemming from the growing awareness of the need to save heat energy.

High heating power at relatively low heating and production costs, as well as good control parameters, which are factors that directly influence the comfort and microclimate of the heated room, are considered to be the most suitable features.

This object is solved by the invention based on the features set forth in 1.12, 27, 39,

41, respectively, 58 of the claims.

The two-section or multi-section radiator according to the invention optimally has a single connection to a supply line which is connected only to the front heating panel, respectively, facing the room. The warm water flowing through the inlet connection is distributed as evenly as possible along the top longitudinal edge of the front heating plate itself and through the perpendicular and appropriately spaced ducts in the front, facing the room. In this way, regardless of whether the radiator is full load or partial, the front segment is supplied with warmer water than the other segments. This means that with the same heating output, the front segment will be warmer and at the same time more comfortable to touch than conventional systems. This positive effect is best reinforced by the fact that the front segment has a higher radiance than other radiator segments.

To allow water to flow from the forward segment to one or more of the segments behind it, at least one connection pipe is provided, which is optimally located in one of the lower angular areas of the radiator. The water flowing into the rear heating plate is preferably first directed upwards to the upper longitudinal edge, redistributed by a transverse channel therein, and fed through a perpendicular passage thereto to a return connection point in the lower angular area.

If three or more heating plates are provided, water control in the third and all other parts may be effected in an appropriate manner which, from a hydrodynamic point of view, is consistent with the connection of three or more radiators.

However, in the 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 this purpose it is advisable to run the connecting pipe between the front and second heating plates to the very last heating plate.

The advantage is that, in any case, warm water is primarily supplied to the front heating body, so it only has a higher surface temperature in partial load mode than conventional radiators, which is perceived as a more comfortable microclimate in the room.

Because the first, respectively front segment of the radiator heats relatively evenly over its entire surface, namely in the partial load range, even at low heating power, radiation compensation from the window above the radiator is still possible. In conventional radiators this is not possible due to the high proportion of convection.

Another advantage is that the radiator according to the present invention provides a more even temperature profile of the radiator surfaces. It is precisely because the incoming water is primarily directed exclusively through the front heating plate facing the room that, after passing through the front heating body, for example in full load mode, the water temperature does not yet reach the return temperature typically found in conventional systems; in the middle between the temperature in the feed line and the temperature in the return line. At the same time, the temperature distribution across the radiator surface is smoother, which simplifies the radiator calculation and simplifies the design. Particularly valuable is the fact that a more even temperature distribution is obtained within the partial load range. This is illustrated by the example where the radiator thermostat sets the water flow rate so that the temperature of the past front heating body drops to near room temperature, whereas at equal heating power this would occur in a conventional radiator with symmetrical flow already in the middle of the heating body. the area would feel cold and uncomfortable.

The dual-section radiator purposefully has convection profiles only on its rear heating plate, so such a radiator according to the invention has a relatively larger radiant portion at full heating power, and the rear convection segment no longer warms in the partial load range. If such a radiator is sufficient in the given calculated case for maximum heating power at very low outside temperatures, it will be at relatively mild outside temperatures, which last for a considerable period of time, that the radiator will have a relatively higher radiant exposure. Conversely, at lower outside temperatures, the posterior heating plane also warms, thus increasing the convection rate.

The advantage is that the heating body index of such a radiator is not constant over the entire temperature range, but is lower in the partial load range due to a much larger radiant output than at higher heating powers with a higher convection rate. Thus, under partial load conditions, a lower feed temperature is more desirable to obtain the set heating output. At the same time, the radiator according to the invention contributes to the saving of heating costs in the partial load range, which constitutes a greater part of the heating work.

Another advantage is that according to the invention, the heating panel facing the room is warmer, which is desirable for each radiator, since it is necessary to heat the room, not the back wall, but this is not achieved with the symmetrical construction of conventional radiators. In this way, less heat is lost to the outside through the generally thinner insulation of the radiator wall. It is good that the radiator according to the invention is provided on the back with an additional radiant screen, usually of a multi-layer aluminum construction, to increase the thermal insulation in the wall direction. It is expedient to provide such a radiation screen also between the front and rear heating plates in order to obtain thermal insulation of the front heating plane from the rear heating plane. Another advantage is that numerical modeling and thus the construction of the radiator becomes easier, since it is very difficult to model precisely the singularities, respectively, in this case very large local heat loss.

Other benefits occur when using radiators in special cases, such as kindergartens, or when using central heating systems. In kindergartens, it is desirable and provided for by law that the front heating plate should never, under any circumstances, reach temperatures higher than, for example, about 50 ° C. Whereas in conventional radiators this is possible only by reducing the inlet temperature and thus the heating power, and according to the invention it is sufficient to rotate the hotter heating plate not to the room but to the rear wall so that with the same heating power , there is no risk of burns. This arrangement is also best used in district heating systems, namely in the former Eastern Bloc, where inlet temperatures of up to 130 ° C can be achieved. In conventional radiator systems, built symmetrically, homeowners burn permanently, especially near the entrance. In this case, it is only necessary to turn the radiator so that the heating panel faces relatively well to the side of the room. If the thermal insulation or the central heating system were subsequently improved, then at lower inlet temperatures, it would only be necessary to turn the radiator, thus fully revealing the above advantages, without having to buy a new radiator.

Typically, the connection points at both the feed and return lines are on one corner of the radiator. However, in the case of longer radiators, it is preferable, according to another embodiment, where the connection point is centered. The warm water is then purposefully fed to the center of the front heating plate, where it then flows to the left and right streams until it is discharged into the center area of the two-section or multi-section radiator or back panel itself. In this way, the warm water is purposefully supplied to the upper edge of the front heating body. However, in one more preferred embodiment, both the inlet and outlet are at the bottom edge of the radiator, which necessitates an upward direction of incoming warm water, as will be explained below. It is also necessary in the rear heating body after water passes from the front to the rear heating body.

The advantage of the junction at the center of the long radiator is again the even temperature distribution, since the warm water flowing through the radiator at partial load mode at a relatively low speed only needs to pass half the length of the heater before leaving the front heater. the parts will also be warm to the touch. Another advantage of this variant is that such a radiator, especially at low outside temperatures, where cold glass surfaces above the radiator cause a so-called cold air wave, swirling along the entire length of the radiator due to the upward warm air flow and can cause overcompensation. At the same time, the front and rear ends of the radiator can not be afraid of the cold air falling to the base (towards the feet), as would be the case when connecting the inlet and outlet on the same side.

The above solution principles can be applied not only to multi-layer radiators, but also to single-layer radiators. Therefore, in comparable configurations, it is possible to have a radiator with preferably a greater amount of radiated heat which, at low heating capacities, has a pleasantly warm touch on the radiator surface, whereas at high heating capacities such a radiator has a sufficiently high convection heat output. for less frequent extreme cold winter days.

The single-section radiator according to claim 13 of the invention has at least two differently manufactured segments, of which the first segment, which is optimally turned back to the heated space, is disposed in the flow direction upstream.

In such a radiator, the water initially passes through the point of connection to the feed line to the first segment, which is optimally located in the upper area of the radiator. If the connection point to the feed line is provided at the bottom edge of the radiator due to constructional features, the water is first directed to the upper area according to the invention, for example by a specially constructed passageway or support liner, respectively. The water is then distributed through the entire upper longitudinal edge of the radiator and directed in the direction of the return line. Preferably, the first segment has no convective circuits, which provides a very high radiant heat transfer rate, which is about 50% in this segment. The water then passes through the second segment, which preferably has convective circuits and is, as usual, in the lower area of the radiator, towards the return line. It is desirable, also for hygienic reasons, that the convection profiles in this segment face away from the room on the radiator side.

The advantage of such a radiator is that it is warm to the touch due to the transverse distribution of the flow medium throughout its length, respectively its width, namely due to the high radiant heat even at partial load. Even if the lower zone remains "cold" at low heating power levels, the extremely warm upper zone is more easily perceived compared to conventional single-section radiators. Therefore, the best position for this area is at road height, especially in the radiators of office buildings.

A preferred embodiment is provided when the emitter segment is directly covered with insulation that extends at least substantially over its posterior side.

In this embodiment, it is possible to further reduce the convection portion of the radiation segment and to significantly increase the surface temperature as well as the radiation portion due to the reduction of convective heat losses.

In order to amplify this effect, it is also advisable to redistribute the flow rate in the first and second segments, which is achieved, for example, by higher flow resistance or longer flow passages in the first surface segment, respectively.

For this purpose, the passage channels of the first segment are optimally in the horizontal direction, whereas in the other segments they pass as usual in the vertical direction. Optimally, the first segment is separated from the remaining segments by a baffle through which at least one connection channel passes. Because of the flow of meander direction in the first segment and the arrangement of the interconnection channel, the diametrically opposite position of the interconnection with the feed line in the first segment provides a large heat exchange surface to increase the radiated portion.

The advantage of having a single-section radiator, due to the different ratios of the convection part to the radiator part in partial load and full load mode, has a non-linear index of the heating body, which decreases just at low heating power.

In both single-section and multi-section radiators, this desirable effect can be further enhanced by adjustable mechanics, especially at low heating capacities. The cover sheets are pushed over the convection circuits, thereby eliminating air convection and thereby increasing the amount of heat released by the heat emitted as compared to the convection directed heat portion.

Therefore, it is desirable to provide a temperature sensor in the segment of the radiator according to the present invention to which less heat is supplied in partial load mode. Usually this segment is located at the bottom end of the radiator. The temperature sensor is optimally connected to the expansion volume, which, due to the temperature-dependent shift in the setting, shifts the blinds that cover as described above. At the same time, the setting offset is controlled precisely so that the convective heat transfer at high heating capacities and at higher temperatures is increased in the sensor area.

The advantage is that the heating body index can be calculated as variable, so that even if the convective circuits are located over the entire radiator surface, it is possible to realize a heating body with optimum heating power in full load mode with optimum high radiant exposure in partial load mode.

Other advantages of a single-section radiator include the tilting of its lateral segments backwards, respectively, toward the wall, so that, when double and substantially rectangular, they are folded parallel to each other and at a certain distance from the front panel. This embodiment is very close to a two-section radiator. In such a radiator, the middle portion purposefully does not have convection profiles to maximize the radiant portion in this segment facing the room. Conversely, it is desirable to have convective contours on the folded-back side segments that extend optimally over the entire radiator surface.

If the rear surfaces of the radiator extend almost the entire width of the front surface, it is advisable to provide an entrance connection in the middle segment facing the room, whereas in the latter case there are two existing return connection points. At the same time, especially with an evenly heated front panel in partial load mode, this embodiment has the particular advantage that it essentially approaches a two-section radiator, where no connection of the two heating bodies to each other via interconnecting pipes is required, which would normally require higher production costs. Conversely, it is relatively easy to bend a single-layer radiator accordingly.

For countries with mild winters, another embodiment of a single-section radiator in accordance with the present invention, in which the return line is made as a pipe passing through a substantial part of its length at the rear of the radiator, is particularly important. This return line purposefully has a plurality of preferably circular or rectangular convection plates which, at cold outside temperatures, significantly increase the amount of heat released by body convection. However, on warmer days, especially at partial load, they barely warm up, as warm water at the front of the heating plane has already cooled to room temperature. In this embodiment, it is expedient to have no convection sheets on the front surface of the radiator.

The advantage is that this embodiment at a relatively low cost allows the construction of a radiator with sufficient thermal power and excellent control parameters. For this purpose, a tube with convection bodies, which is inexpensive and available for sale in meters, is best used. The diameter of this tube as well as the overall surface of the convection bodies can be matched to the design of the radiator. Such a radiator optimally has convectional contours on its front surface, which can be additionally covered by the aforementioned adjustable blinds.

In order to direct the aforementioned flow from the lower angular area upwards, the invention utilizes so-called support liners, respectively, expansion devices with a shaped discharge tube and a transverse hole. When transposed, the transverse aperture enters the extension of the connection element, that is, the connection points with the feed line, respectively, the connection points with the return line, or the extension pipe connecting the front and rear heating plates. In addition, the outlet pipe is located in one of the vertical passageways of the heating plane, so that the outlet may preferably be concentrated in a particular defined passageway.

An advantage of using a support liner, respectively, an expansion device according to the present invention, is that the inlet connection may be in the lower radiator area when it is not necessary to use a non-radiator tap with a stand to direct water upwards. This helps to further reduce production costs.

The valve assembly according to the invention, which is best used in a radiator according to claim 41 of the invention, has a housing as well as feed and return lines, in addition, a shut-off device such as a valve plate and valve saddle is provided. The valve device according to the invention has at least two feed lines and at least two return lines, and the shut-off device is connected to each of the two feed lines or to each of the two return lines. The shut-off device, respectively the valve plate, may be provided in a section of piping approximately the diameter of the valve plate, for example between the feed lines and the return lines, where both feed lines, respectively return lines, are arranged in a flow direction. the flow may initially pass through one feed line, respectively, with the return line, with increasing feed, and then gradually, and finally completely, flow through the other feed line, respectively, with the return line due to further displacement of the valve seat.

A certain amount of leakage through the part of the pipeline bypassing the partially opened valve pan is easily tolerated, since the corresponding, relatively small, leakage rate at low pressure used in district heating systems does not cause circulation in this area.

Appropriate valve arrangements for supplying the heating medium may be used, for example, to two different heating bodies, for example, a forward, indoors, radiating segment, and a convection segment behind it. On the other hand, this valve with both feed lines, respectively the return lines, can be arranged in the connecting pipe so that opening the first inlet, respectively the outlet opening, respectively, opens a longer first, essentially linear adjustment range, to which the second input, respectively the output, is connected to another linear control range. Conversely, corresponding linear adjustment ranges occur when the valve plates are closed, respectively.

In order to ensure that the inlets and outlets of the valve device according to the invention can be closed individually as well as completely without leakage, each of the two inlets or each of the two outlets may be associated with closures, namely a valve plate with a corresponding valve saddle. The opening of the first shut-off device, respectively the first valve plate, can then pass the heating medium flow first through the first radiator heating segment and then through the next radiator heating segment, or conversely, bypassing the heating medium flow. If both inlets, respectively, of the outlet openings are directed to a single pipeline, the linear characteristic of the valve according to the invention can be significantly extended.

The shut-off devices, respectively, of the valve shells, are preferably coaxially located, respectively, on one axis and, if necessary, one after the other. By controlling the shut-off device, by means of the valve fingers provided by the valve adjusting head or by the thermostatic head respectively, the valves can be opened at different temperatures to provide the correspondingly connected radiator output depending on the room temperature. It will be appreciated that the valve device of the invention can be operated in substantially the same manner. As a result, the corresponding two inputs, respectively the exits, need not necessarily be in the form of round holes, but they may also have grooved, oval or triangular holes. The valve body, respectively the valve body with inlets and outlets, may then be made of plastic, whereby the valve body may be mounted, if necessary, and pressed into a brass or copper housing as well as a plastic housing.

The long linear adjustment range of a single radiator is also in principle sufficient to allow a large, sweeping cross-section to be released in sequence, for example by lifting two valve plates in the same plane one after the other. One valve plate may then be provided movable in the center area of the other valve plate. Raising the inner valve plate first loosens a certain passage area, and then the next, annular valve seat surrounding the first valve seat can be raised, thereby increasing the free passage cross-section of the valve device while extending the linear adjustment range.

One of the two closing devices, respectively, one of the two valve plugs must be preloaded with respect to the other valve plate so that it will remain independently of it, at least, by pushing one closing device, preferably the valve plate, in an optimally adjustable transfer path, essentially in a closed position for subsequent displacement by providing flow control by a valve arrangement. One of the shut-off devices can then be directly connected to the valve finger, while the other shut-off devices may remain pressed against the respective valve saddle, such as a spring member. Then, one clamping device may optimally be provided with a clamp that engages the other clamping device, after transferring one valve disc to another valve disc after a certain period of time, even when the intended spring member still has to press another valve disc against the corresponding valve saddle.

Obviously, the grasping of the other closing device, respectively the other valve plate, may be accomplished in other ways. For example, a spring member pressing another valve disk against its respective valve saddle with respect to the spring stroke and spring force may be made such that the spring force at a certain adjustment decreases and, when fully restored, the spring engages the valve disk and consequently fully open the appropriate opening.

There are different mechanical realization possibilities which will be apparent to those skilled in the art in the context of the present invention and which also form part of the present invention.

In one embodiment of the valve assembly according to the invention, each of the closure devices, respectively, of the valve trays may be provided with a separate mechanical transfer device. However, due to the space required and the need for better control without the need to overcome synchronization difficulties, a single mechanical transfer device for both valve discs is optimal when the mechanical transfer device would actuate both valve disks but with some delay.

According to another particularly preferred embodiment of the invention, the valve device according to the general part of claim 41 has one shut-off device disposed in another shut-off device, wherein the other shut-off device has an opening and one shut-off device acts on a cross-section of the apertures. The aperture may have one axial region and one radial region, wherein one closure member may act on a cross-section of the apertures of the aperture, axis, and / or radial region. This alternative embodiment of the invention may be embodied with the additions set forth in other embodiments of the invention.

In an alternative embodiment of the invention, the inlet, and thus outlet, of the valve assembly may optimally enter one another such that, when both shut-off devices are open, an enlarged fluid cross-section is provided. For example, if necessary, the radial orifice area in the other shut-off device and the inlet of the valve device, respectively, can be arranged so that they both enter the same pipe so that when both shut-off devices are open, . In this embodiment, it is also possible to increase the linear range of control of the valve device according to the invention by providing more precise control, in particular of the radiator.

As stated above, a thermostatic device, respectively a thermostatic cartridge, which may comprise, for example, a wax or paraffin capsule, is connected to the actuating finger of the closing device of the valve device according to the actuator rod of the closing device, respectively.

In addition to the conventional radiator valve arrangements, the invention may be used to regulate a radiator of a particular invention. Such a radiator according to claim 41 of the present invention, which is also part of the present invention, has one mainly radiant segment, a heating segment and one mainly convection segment. As with a conventional radiator, at least one feed line and one return line are provided to supply the heating segments with heat medium, optimally water. Also provided is a valve, respectively, a thermostatic device, wherein the valve, respectively, a thermostatic device, has an element affecting the flow of a flow corresponding to the radiant heating segment and another valve, respectively, a thermostatic device having a second element affecting the flow of the flow. which corresponds to the convective heating segment.

It is to be understood that the valve thermostat units of the radiator according to the invention may be replaced by the valve unit according to the invention, wherein the thermostatic device may be provided optionally wherein said valve, respectively, the thermostatic device comprises a first element affecting the flow an element affecting the flow of the outlets.

If the two thermostatic devices of the valve, respectively, are separated from each other, the two thermostatic devices of the valve, respectively, must operate at different room temperatures due to the different performance characteristics of thermostatic elements, such as wax capsules, respectively. For each heating segment, the radiator may have one feed line and one return line, or one single supply line and one single return line may be provided. According to the present invention, the individual heating segments of this radiator can also be separated in space. Then, for example, the radiant heating segment may be provided as a ceiling heater, while the convective heating segment may be remote from the radiant heating segment, for example, in a wall recess.

To provide an accelerated operation of a conventional or radiator valve assembly, the invention provides a thermostatic capsule, such as a waxed capsule, respectively, with a paraffin wax, which comprises a housing containing a volume of a certain expandable material such as paraffin or wax. In addition, it is intended to accept an element (contour) which, in itself, is flexible, accepting the thermal expansion of the medium, respectively the contraction. This element actuates a setting device, such as a valve finger, for example, which can be applied to the closing devices of the valve device of the invention. Then, by accepting the thermal expansion of the medium, respectively the contraction, the element (contour) in the radial direction is made so that this contour can change its dimensions nonlinear when the volume changes in the expansion direction, respectively in the direction of contraction. Another advantage of this type of thermostatic capsule is that, by compensating for thermal expansion and consequently shrinkage, the circuit can provide a longer setting time.

Said contour is preferably made such that in the axial direction, respectively, the volume compensation direction, it is geometrically designed such that a linear change in volume causes a non-linear change in the contour length in the axial direction.

A tapered or tapered shape can be used as the best geometric performance.

Alternatively, said contour may be tapered and / or tapered, circular, or any other geometric shape spaced in sequence, thereby providing certain switching characteristics that result in a nonlinear actuation, namely faster actuation.

It is worth noting that the thermostatic capsule described is suitable not only for heating or cooling, such as ceiling cooling, but also, for example, for automatic opening of the windows, respectively for automatic opening of the greenhouse windows, etc., and for other control purposes. Similarly, the valve device of the present invention may be used for other technical purposes not only in the heating field, where a linear extension of the pitch control is desired, whereby two or more volumes (e.g. radiator segments) in series to a closed loop are required closed outline.

Below is a detailed description of the subject matter of the invention, with reference to the accompanying drawings, which schematically illustrate optimal embodiments. At the same time, additional advantages and features of the invention are disclosed. The individual features according to the invention may also be combined in any other way. The drawings show:

FIG. 1 is an anterior isometric projection of a two-section flat panel radiator according to the invention;

FIG. 2 is a two-section radiator according to the invention with central connection points with feed and return lines;

FIG. 3 is a cross-sectional view of a two-section radiator where the convection sheets can be covered by expansion volume and blinds;

FIG. 4 is a diagram of a single-section radiator according to the present invention;

Fig. 5 is a single-section radiator according to the invention with backwardly folded lateral segments and central connecting members;

FIG. 6 is another single-section radiator according to the present invention having a rear tubular segment provided with convection bodies;

FIG. 7 is an expansion device (support insert) according to the invention for directing a fluid heating medium flowing through the radiator in a working position;

FIG. 8 is a schematic diagram of an electrical flat panel radiator according to the present invention;

FIG. 9 is a cross-sectional view of a radiator according to the present invention mounted in a front wall mounting space;

FIG. 10 is an embodiment wherein the convection segment is adjacent to the radiation segment;

FIG. 11A-11C is a cross-sectional view of a valve assembly according to a first embodiment of the present invention in several different positions;

FIG. 12A-12C is a cross-sectional view of a valve assembly according to an alternative embodiment of the present invention in several different positions;

FIG. 13 - characteristic of the valve with regard to its regulation and characteristic of the radiator in relation to the power of the radiator;

FIG. 14 is a transverse section of a thermostatic capsule, namely a wax capsule according to the present invention;

FIG. 15 is a cross-sectional view of another embodiment of a thermostatic capsule according to the present invention; FIG. 16 is an isometric projection of a two-layer vertical heating wall;

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

FIG. 18 is a horizontal sectional view of the lower area of the heating wall according to FIG. 17;

FIG. 19 is an expanded isometric projection of another embodiment of a two-layer vertical heating wall;

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

Fig. 21 is a horizontal sectional view of the lower area of the heating wall in accordance with Figs. 20;

FIG. 22 is an isometric projection of a two-layer horizontal heating wall;

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

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

FIG. 25 is an expanded isometric projection of another embodiment of a two-layer horizontal heating wall;

FIG. Fig. 26 is a view of the heating medium passage in the upper zone of the horizontal heating wall according to Figs. 25 partial horizontal incision;

FIG. 27 is a horizontal sectional view of the lower area of the heating wall according to FIG. 26;

FIG. 28 is a heating wall according to FIG. 26 vertical incision in the right lateral zone;

FIG. 29 is an expanded isometric projection of another embodiment of a two-layer horizontal heating wall;

FIG. 30 is a top view of the heating medium passage in the upper horizontal heating wall area of FIG. 29 partial horizontal section;

FIG. 31 is a lower area of the heating wall according to FIG. 29 horizontal section;

FIG. 32 is a heating wall according to FIG. 30 vertical incision in the right lateral area.

FIG. 1 shows a two-section radiator according to the invention with a so-called one-way connection, where the feed line connection (PD) is located in the upper corner area (a) of the front heating plate 1 and the return connection (GR) is located in the lower corner area of the rear heating plate. (d '). The hot water flowing through the connection to the feed line is distributed in an appropriate manner in the front heating plate before passing through the connecting element (c-c '), preferably through a metal or plastic pipe, to the rear heating plate Γ. The heating plate is purposefully made of two half-shell, respectively profiled plates, optimally made of steel sheet or plastic, which are welded, respectively connected to each other in such a way as to prevent water penetration. Each profile is formed so that the heating plate has a plurality of vertically spaced passageways (a-d) and a corresponding transverse passageway is provided on the upper and lower longitudinal edges (a-b, respectively, d-c) of the fluid to distribute the water optimally. For even distribution, the corresponding transverse passageways may expand in the form of a funnel in the longitudinal direction.

Water entering the lower corner area (c ') must first be directed to the upper corner area (b'). The self-heating of the warm water in this angular zone is purposefully supported by a special design of the rear heating plate Γ. For this purpose, a pipe connected to the coupling element (c-c ') may be provided in one of the upstream conduits, so that the incoming water is directed upwards. Alternatively, this tube may be discarded if the passage is separated from the lower transverse passage. A support liner according to the present invention may also be used for this purpose, as will be explained below.

In the upper angular zone (b '), water is diverted again in a horizontal longitudinal direction 10, as shown by the dashed arrows, until it flows again through vertical passageways toward the junction with the return line in the lower angular zone (d'). For ease of fabrication, the front and rear heating panels may be made the same, so that the point of connection to the feed line PD may also be in the lower corner area (d) of the front heating panel. For this purpose, the warm water flowing through the PD connection to the feed line must first be directed to the upper angular area (a), preferably by means already indicated.

In order to increase the proportion of heat radiated by convection, the heating plates may be provided with convection contours, respectively sheets 2, which may have a rectangular or wavy profile in the top view. In one optimal embodiment, both the front and rear heating panels have a predetermined corresponding convection profile. However, it is possible that only the rear heating plate has one or two convection profiles. To further increase the heating output, the radiator may also have a third heating plate which is located behind and connected to the second heating plate in parallel or in series.

Because of the use of a connection, such as a screw-on connection pipe (c-c '), there is no need for the heating panels to be rigidly connected to one another and can be adapted as modules to the existing conditions.

It is only in partial load mode, that is, at low heating capacities, respectively, at low flow rates, only the front heating plate 1, not the back plate, warms up, which gives a feeling of comfort in the microclimate of the room. If there is no convection profile on the front heating plate, it usually emits about 50% heat. In this case, the radiator has a relatively low heating body rate, so compared to a radiator with a high convection rate, it can be controlled to lower flow rates, which provides better control.

In the case of long radiators, which are necessary for large rooms, especially office premises, the radiator in the connection point to the feed line in area (a) may be warm to the touch, but long before the connecting element (c) - cold to the touch. This may allow the convection caused by the radiator far in front of the coupling member to no longer be sufficient to cause a vortex and to lift upwardly downward cold air coming from above the radiator window. As a result, someone near, for example, the radiator inlet connection will feel the heat at the feet while another person in the connection area will feel cold due to the descending cold air at the feet.

To avoid this unpleasant effect, in one optimal embodiment of the invention shown in FIGS. 2, there is provided a central arrangement of junctions with feed and return lines and optimally symmetric branching of incoming warm water to left and right flows. For this purpose, it is desirable to provide a transverse elevation after connection to the feed line location (PD), which is illustrated in FIG. 2 as a transverse line. Two connecting tubes (dd ', cc' respectively) are provided in the lower angular zones (d, cc) respectively, to direct flow to the rear heating plate, the ends having a respective tube, a support liner according to the invention or another suitable device for on the heating plate. After the impact of the flowing medium on the upper corner zones (a ', b, respectively) of the rear heating plate, the flow is directed to the middle (m). A separating baffle may be provided in the middle of the upper transverse passageway to divide the flow left and right, as shown in the vertical transverse line. The medium flowing through the vertical ducts as well as the transverse duct finally reaches the return connection (GR).

While the surface temperature of a single-sided radiator with feed and return lines drops across the entire width of the radiator, the central contour of the feed line is symmetrical and adds to the comfort of the user.

As the flow passes through the front heating plate in front of the rear heating plate, the heat output from both heating plates is different, especially in partial load mode. It depends on the individual production of heating panels. It is better to make both heating panels the same to reduce production costs. However, in order for the radiator to be able to have a warm front heating plate even with low heating power, the front heating plate must have a larger radiant portion, while the rear heating plate must have a large convection to provide the required heating power on cold days. Therefore, the front heating plate optimally has no convection circuit.

As a compromise between these two extreme cases, another embodiment of the invention provides adjustable blinds that regulate the flow of room air to convective circuits depending on the required heating power. FIG. 3 is a cross-sectional view of a two-section radiator with adjustable blinds for two convection circuits 2 according to the present invention.

To this end, the front heating plate 1, which faces the room, has a temperature sensor 6 as well as an expansion volume 3, which are used, for example, for the conversion of windows in greenhouses. A slidable valve finger across the heating plates 1, 1 'is connected to the expansion volume 3 on one side and to one of the cover sheets 7 on the other side to ensure the adjustment of the sheets as the temperature changes. For transferring the displacement shift to the second cover sheet, there are provided scissor-shaped guide links 5 with a fixed central pivot point, respectively, and two guide links, the respective one end of which is fixedly connected and the corresponding other end connected so that it slides with the cover sheet. Several spring elements 4 may be provided for reversible force such that the cover sheets 7, on the one hand, press the scissor-shaped guide rods 5 and, on the other hand, rest on the spring elements 4, which in turn rest on the support frame. If only one convection circuit is provided, it is sufficient to connect the valve finger directly to the cover sheet so that there is no need for guide guides.

The expansion volume is a thermostat capsule with a volume of liquid that expands upon heating and shrinks on cooling, respectively. Usually uses media such as wax or paraffin. The expansion volume is made in such a way that the thermal expansion of the volume turns into a valve finger displacement movement. The corresponding displacement movement can be linear or temperature dependent, or approach the jump function at a predicted jump temperature. Due to the scissor-shaped mechanics, the movement of the valve finger turns into the transverse movement of the covering sheets. They are best made so that at relatively high temperatures in the lower part of the front heating plate, that is, when the radiator has to deliver high heating power, the cover sheets expose the convection circuits so that air at the convection circuits can flow freely. In this case, the radiator gives off its heat mainly by convection. The corresponding heating body index for a convection radiator is relatively high, for example 1.5. As the temperature decreases in the lower rear part of the front heating plate, the cover sheets 7 are displaced and cover the convection circuits so that the amount of radiated heat is increased and the total heating power is reduced. The increased radiant exposure reduces the corresponding heating body index, for example, by 1.25, which positively affects the control parameters at partial load. In a particular embodiment of the invention, memory alloys or bimetallic springs may be provided to provide switching.

Further, such control parameters can be selected for control using a thermostat valve which can regulate the flow in the radiation segment and the convection segment independently of one another, or regulate the radiation section and the convection section independently so that, with low room heating load, the radiant segment is most heavily loaded, and the convection segment is additionally loaded at higher room heating loads.

The solution of the present invention can be used not only in multi-sectional radiators but also in single-sectional radiators. For this, FIG. 4 shows a single-section radiator according to the present invention having a first segment 8, which is preferably located in the upper radiator area, and a second segment 9. The inlet is in the first segment 8, so that a hot water flow passes therethrough. For optimum distribution of warm water at the upper longitudinal edge (ab), a transverse passageway is provided, with other transverse passageways in the form of a meander or a few vertical passageways (not shown) that can continue in the lower passageways (shown by thick vertical lines) . In addition, a separating baffle 10 is provided between the first and second segments so that the incoming warm water initially concentrates in the upper zone to release heat therein before entering the lower zone through one or more connection channels 11.

The upper zone is optimally devoid of convective circuits, so the upper zone forms a flat radiator with a high radiance and low body warmth. The lower zone usually has a convection circuit 2, so much of the heat in the lower zone is provided by convection. If a separating baffle is placed between the first segment and the second segment, a consistent connection of the radiant and convective heating bodies is obtained.

When warm water flows at low heating rates and at the same low flow rate into the upper zone, the water cools in the upper zone before entering the second segment, so that a significant part of the radiator surface feels warm and at the same time comfortable. For a uniform temperature distribution over the surface, especially when the radiators are very long, a central location of the connection to the feed line may be provided as above.

When the radiators are very long or high heating capacities are required, it may be expedient to fold back the side parts (a, b) of the radiator, so that in the extreme case, as shown in Figs. 5, an almost two-section radiator is obtained in which the lateral portions optimally run parallel to a substantial portion of the front surface of the heating body. In this case, it is appropriate to choose the central arrangement of the connection points with the feed and return lines shown above. Contrary to the two-section radiator initially described in this embodiment, there is no longer any need to connect the front and rear heating panels to one another through the connecting pipes, which greatly reduces production costs. The necessary bending of the radiator can be performed both before and during the welding of both radiator semiconductors 20a, 20b. Convection sheets 2 are purposefully located only on the rear heating plate Γ or pass only a relatively small part of the height of the radiator. segment and convection segment.

FIG. Fig. 6 shows another embodiment of a single-section radiator with a forward radius segment 8 and a rear convection segment 9, respectively. For this purpose, a single-section radiator according to the invention or other planar radiators through a generally flexible connecting pipe 13 made of plastic, metal or the like, connected to a radial tubular segment 14. To increase the convection part, the at least posterior tubular segment has a plurality of circular or rectangular , the surface of which is selected according to the required total heating power. Because such pipes will be a very cheap item in the future, sold in meters, it will be possible to realize a radiator that is very cheap on the one hand and provides the benefits of a two-section radiator according to the present invention.

Such a radiator can be used, for example, in warm regions, where winters are relatively mild, where a very high proportion of radiation is required, but only a very small number of days also require a high degree of convection. Consistent coupling of the radiation segment and the convection segment allows both conditions to be satisfied evenly. To further increase the convection rate, the front heating plate can also be partially foreseen with convection sheets, as shown by the dashed wavy line.

FIG. 9 is a cross-sectional view of an embodiment of the radiator installed in the wall mounting space of the present invention as an exemplary embodiment. Wall mounting space is usually left to sanitize bathrooms as a plinth retaining wall 26 against the wall. The holding stand is used to attach equipment such as a washbasin 28 or the like. At the end of the rescue work, the support stand is covered with plates and used as a practical additional surface 25.

This wall-to-wall mounting space can be used to save space when installing a radiator. In this case, it is optimal to install the single-sectional or multi-sectional radiator according to the invention so that the radiating segment 1 faces the room while the convection segment 1 'is in the air box 27. discharge grate 29, 30. The radiating segment 1 optimally terminates at the anterior upper surface. The convection segment can be made as convection sheets or tubes with convection bodies as shown in FIG. 6. This saves space by creating a wall heating surface which, due to the construction of one or more elements of the radiator, particularly at low temperatures in the supply line, feels warm and comfortable.

FIG. 10 illustrates another suitable embodiment of a multi-part radiator according to the present invention, in which the emitter segment 1 and one or more convection segments are arranged side by side. The radiant segment 1 is optimally located under the window 31 and is of such a size that its surface, on the one hand, can compensate for the cold radiating surface of the window 31 above it and, on the other, due to its convection portion , to compensate for falling cold air. The convection segment 1 'is laterally, above or below the radiant segment, is consistently engaged in the direction of flow and is preferably positioned along the baseboard. For this purpose, the convection segment is optimally made as a tube with convection bodies, as in Figs. 6, and may in turn be trimmed due to external visual and indoor hygiene requirements.

In all of the above-mentioned multi-section radiators, the front, optimally facing the heating panel, is the warmest, while the wall panels from the side may be relatively cold. As a result, less heat is lost through the walls of the house. To further prevent such heat loss, all radiators of the present invention may be provided with a wall-side radiation screen 12, which is optimally made of multilayer aluminum and is used for both radiation insulation and thermal insulation in the wall direction. Such a radiation screen can be used for insulation between the front heating panel itself and the heating panels arranged outside.

As stated above, the heating medium flowing through the interconnecting tubular member (cc ', respectively, dd') into the lower connection area (c ', respectively, d') of the heating plate must be directed upwards (b ', respectively, a '). Where this is purposefully achieved by a suitably arranged vertical duct, it is best to use an expansion device, respectively a support liner, as further explained in relation to FIGS.

7th

In the upper part of Figs. Part 7 shows the part of the semicircle, respectively, a front view of the plate, that is to say, prior to joining this semiconductor with another semiconductor made in an appropriate manner. As noted above, this semi-shell is profiled, respectively, with indentations 21, 22a, 22b, so that a plurality of passageways 21 according to the present invention pass in an optimally vertical direction. Also on the lower, respectively, upper longitudinal edge (not shown) is a substantially perpendicular transverse passageway 23. In the lower left, respectively, Fig. 7 is a top plan view of the radiator part according to the invention, respectively. In this embodiment, the connection point 18 with the feed line is located in the middle and on the lower longitudinal edge of the radiator, as provided for long radiators according to the present invention.

For channeling the water flowing through the inlet connection 18 to the water supply, the vertical passageway adjacent to the inlet passageway may be separated from the rest of the lower transverse passageway, for example by a baffle. However, it is preferable to insert a specially made bearing insert into one of the half shells before expanding the two shells, respectively. FIG. In the embodiment shown in Fig. 7, the support insert has a transverse hole 19a in its lower part which is optimally made as a transition hole and also has a hole 19b extending perpendicular thereto. In its working position, the perpendicular hole 19b is located in one of the vertically extending passageways 21, and the transverse hole 19a is at the height and extension of the connection 18 with the feed line. This arrangement ensures the desired flow upward deviation. While the flow deflection is best executed through only one passage, the support liner may also be constructed so that the flow passes through several passageways.

The support liner is preferably symmetrical in shape to occupy the specified working position. In the shown Fig. In the embodiment 7, the outer contour of the support liner is aligned with the semicircular indentation, respectively, of the semicircular profiling, so that the vertically extending hole 19b is in the passageway 21. When the support liner is substantially annular, it may have a recess 19c in working position it fits to the lower longitudinal edge. The symmetrical shape facilitates the automated installation of the support liners, for example by using a robot or by easily shaking one of the half-shells.

To produce the heating plate, they first make imprints 22a, 22b on two plates of plastic-deformable material, preferably steel sheet or plastic. The plate thus profiled forms one semiconductor 20a, 20b. Each half shell has one or more openings for accommodating valve parts and connection points PD, GR, respectively, connecting elements (c-c '). In these locations, the support liners are optimally housed between the two semiconductors to accommodate the very high forces resulting from joining the two semiconductors by welding the joints together to prevent undesirable deformation of the semiconductors. Where additional flow deflection is to occur, a support plate is provided with a directional flow outlet according to the present invention.

The above principle is that the first segment with a high radiant output is supplied with more heat than other radiator segments, especially at low heating power. This principle can be applied not only to radiators passing through the heating medium stream, but also to electric radiators as shown in Figs. 8. Thus, in said single-section radiators, respectively, the multi-section radiators, the radiating segment 8 can be arranged, for example, above or before the convection segment 9.

For this purpose, the relevant segments of the present invention are provided with a plurality of electric heating elements (Ri ... R _n , Ri ... r _n ) which are inserted directly into the radiator or into the respective passageways with metal bushings. Such an electric radiator may be provided with a water, paraffin or similar closed flow circuit, where flow convection is caused by the heating elements themselves or by an additional actuator. The heating elements of the respective parts are usually connected in parallel.

In an electric radiator according to the present invention shown in FIG. 8, the parallel impedance of the first segment 8 is lower than that of the second or other segments 9, thus providing more heat to the first segment. It is appropriate to provide for control of the individual heating elements of the segments, either individually or in cascades, by means of a control device such that the total heating power, and in particular the heat output due to radiation and convection, can be adjusted individually and correspondingly to room conditions. For example, in a two-section radiator, with the desired low heating output, it is preferable to disconnect the panel heating elements on the wall side, leaving the heating body with a large radiant portion on the room side. Therefore, a relay 16 is provided between the two radiator segments 8, 9.

In another optimum embodiment, the first, respectively, front heating segment 8 has a self-adjusting, and accordingly self-limiting, resistor, which is also used in so-called self-heating heating pipes. The self-limiting impedance consists, preferably, of ferrites embedded in a basic material such as an elastomer. This results in a temperature-dependent resistance which increases with increasing temperature. In this way, an almost leap in temperature change can be achieved, which causes the electrical resistance to be limited by itself, for example at low temperatures.

If the first, respectively, the front segment 8 of the electric radiator has a self-heating heater according to the present invention, it can be ensured, without complicated adjustment, that the resistance of the first, respectively, front segment 8 is lower at lower temperatures than the other segments. Thus, in the partial load mode, when the radiator surface is relatively cold, the radiator radiator segment heats up more, thus increasing the comfort of the room. At average radiator temperatures, the resistance of both radiator segments is the same, whereas at high heating temperatures, i.e. high heating plate temperatures, the surface temperature of the first segment remains at a set temperature due to cell self-tension.

Due to the above-mentioned separation of the radiator according to the present invention, non-linear control parameters can be optimally ensured in the radiator segment and in the convection segment behind the radiator segment: at low heating demand, heat is radiated at substantially higher heat demand. part of it is delivered through convection.

The required thermal output in rooms with good thermal insulation and partial load ranges can change significantly, for example, when the required heating power is only 400 W, the 300 W ceiling halogen lighting suddenly turns on or off. Therefore, for further improvement of the control parameters according to the present invention, it is desirable that the radiator operate with a thermostatic valve having a nonlinear, e.g., progressive or regressive control characteristic. In addition, the control valve is optimally constructed so that flow through the conventional segment can be fully or partially stopped, respectively, independently of the radiation segment control.

The foregoing description of the invention is applicable to a radiator passing through a flow of warm fluid, but the principle of differential loading of spaced radiator segments can also be applied to cooling bodies such as ceiling coolers passing through a cold flow of fluid. In this way, in a two-compartment cooling body, the first segment is facing toward the room, at which time the posterior segment is placed on the side of the wall or connected to another heat exchanger. For example, in a single-sectional cooling body, it may be desirable for the initially skipping segment to be in the middle or edge of the cooling body while the remaining segments are disposed in a complementary manner.

In some special applications, such as kindergartens or central heating systems in the former Eastern Bloc, multi-sectional radiators of the present invention may also be used in the opposite configuration such that the heating panel facing toward the heated room is colder than the panel placed behind it. This way, the front heating plate cannot burn your fingers, which is already required by law in some countries in kindergartens. If the building conditions, such as the thermal insulation or the purposes of use, change, the multi-section radiators of the present invention can simply be rotated so that the warmer heating panel faces the room, thereby providing the above advantages. This adjustment can be done without replacing or buying new radiators.

In the following description of embodiments of the invention shown in Figs. 11-15, the same features, i.e. having identical functions, denoted by equal positions shifted by 10 (i.e. 014 corresponds to 114, 250 corresponds to 350 and 1.1).

Figures 11A-11C show a first embodiment of a valve assembly according to the present invention. It is to be noted that the part associated with the setting head, respectively the thermostatic capsule, is not shown in these figures, since that part can be made in a known manner. As the conventional valve is known to those skilled in the art, it is not described in detail herein.

FIG. 11A illustrates a valve assembly 010 having a housing 012 having an inlet port 014 and two exit ports 016a, 016b. Adjoining the inlet port is an entrance pre-chamber 020 to which a connection chamber 022 is connected. The entrance pre-chamber in the closed position of the valve is separated from the entrance 014 by a valve plate 018a which sits on the valve seat 018b. The entrance pre-chamber 020 may also be closed relative to the chamber 022, namely, another valve plate 024 which fits against the respective valve saddle 024b.

The valve plate 018a is pushed by a finger 028 with which a setting head, respectively a thermostatic head, may be connected on the opposite side. The finger 028 is connected to the front valve plate 018a via a plug nozzle 029 which, at the other end, is provided with a gripper 030 for delaying engagement of the finger with the valve plate 024 a. Valve plate 024a is preloaded relative to its corresponding valve saddle 024b with spring 026 disposed separately inside housing 032 relative to chamber 022.

As long as the path S through which finger 028 can move freely relative to valve plate 024 is prevented by the adjusting motion of finger 028, only valve plate 018a moves, while valve 026 remains overloaded by spring 026.

In the other setting position shown in Fig. 11B, the heating medium, respectively water, enters only through the entrance 014 to the entrance pre-chamber 020 and from there through the outlet 016a to the radiator, i. y. radiator segment (not shown). With this setting, the valve plate 024a is in the closed position, so that the heating medium cannot enter the connection chamber 22. As shown in the position 10 of the valve 10 in Fig. 11B, the free path S of the finger 028 is passed.

The spring 026 is maintained in the closed position, and the valve plate 024a, by further movement of the finger 028, is grasped and loosens the opening corresponding to the valve seat 024b into the connection chamber 022.

FIG. 11c, valve device 010 connects, for example, another radiator or other radiator segment to the central heating system input.

If both outlet holes 016a, 016b are connected to one common pipe, it is possible at the same time to extend the linear control characteristic of the valve, but only one connected volume, 1.1, one radiator can be controlled in relation to the flow.

FIG. 12a-12c show another embodiment of a valve assembly according to the invention in various positions of the assembly.

In this case, the housing 112 has only one input 114, e.g. from the central heating, respectively, the cooling system, and one outlet 116 to the radiator, respectively, to the cooling body. Another outlet 116a is provided in one of the valve plates, which in this case may be referred to as a valve body 124a rather than a valve plate. The sleeve body 124a of the valve is contained within the valve body 112 and includes the valve plate 118a.

The sleeve body 124a of the valve opposite its entrance 114 is sealed at the other end with a circular cross-section relative to the body 112 of the valve assembly 100. The sealing portion 141 in the lower portion of the valve sleeve body 124a also passes through a sealed annular seal 140 of a circular cross-section 140; the sleeve body 124a of the valve is preloaded with a spring 126 relative to its saddle 124b.

The valve sleeve body has an inlet portion 114a fitted to the inlet 114, to which the entrance pre-chamber 120 is connected to a radially extending outlet 116a in the valve sleeve body, and further to the body 112 outlet 116. 124a, corresponds to the connecting chamber 22. 11A-11C, when Figs. 11 A-11C is connected to a common pipeline with its two outlets 16a, 16b.

Both Figs. 12A-12C in both Figs. In embodiments 11A-11C, the valve plate 118 and its control inside the sleek body 124a of the valve operate in the same manner and are reflected in the same positions and are therefore not repeated.

When, as shown in Figs. 12B, the valve plate 118a is retracted by the finger 128, then the valve plate 118a loosens the opening corresponding to the valve saddle 118b so that fluid may flow through the inlet port 114 and the inlet connecting port 114a, the inlet pre-chamber 120, and the port 116a, 116.

This embodiment also provides a freewheel path S between valve plate 118a and valve sleeve body 124a path S. As soon as the freewheel path S is selected by finger 128 displacement, gripper 130 rests on body 124 and further moves finger 128 to grip the entire valve sleeve body 124a. As a result, body 124a rises from its respective valve saddle 124b, thereby causing the connection chamber 122 to become accessible as a free-flowing cross-section for the flow of heating medium to flow through the valve assembly 100 according to the invention. This device is shown in Figs. 12C.

Such an embodiment allows the heating medium to be regulated by a mechanical setting device, i. y. synchronous control using a thermostatic capsule with a set control characteristic which, for example, has a much longer range compared to conventional valve units.

If, in a variant of the valve assembly 100 according to FIG. 12A-12C connecting chamber 122 closes e.g. in front of the outlet opening 116, and another entrance opening 116b is provided, as shown in Fig. 12C, which is essentially again possible to implement the valve assembly 010 according to Figs. 11A-11C.

It follows from the above explanations that the valve assembly 10, respectively 100, according to the invention can be implemented in very different ways to obtain the desired characteristic properties. Therefore, the description given to a person skilled in the art may lead to a variety of equivalent technical solutions for a valve assembly, all of which are within the scope of the present invention.

To illustrate the present invention, FIG. 13 is a graph of the valve characteristic relative to the radiator characteristic. Here, the characteristic of the valve reflects the control characteristic, and the characteristic of the radiator represents the power characteristic of the valve, respectively, of the radiator.

It is known that a conventional radiator already reaches almost full thermal capacity by about 50% of the heating medium flow due to the heating medium used, usually water. However, within this range, the valve has only a small adjustment range, which makes it difficult to achieve proper adjustment in low-power radiators with conventional valves. Valve units 010, 100 and their modifications enable the control range to be achieved much better than that of conventional valves, because the coordinated, time-dependent, temperature-dependent movement of the two shut-off valves, the valve plates, provides better control over the desired range. undesirable heat transfer properties of known radiators.

FIG. 14 illustrates a thermostatic capsule 200 according to the invention having a housing 250 which comprises a volume 252. The volume 252 is filled with a medium which expands when exposed to heat and shrinks when exposed to cold. Common materials used are wax, paraffin and the like. Compensation circuit 254 passes into housing 250. Compensation circuit 254 has an opening through which the actuating member may pass, e.g. valve finger or the like to touch surface 256 at the opposite end of contour 254. As the temperature rises, the volume in the volume 252 expands and the flexible area of the contour 254 is compressed correspondingly to this thermally induced volume increase, causing the contour 254 to shorten and push the actuator in that direction. y. valve finger.

This conventional function of conventional thermostatic capsules is modified by the fact that in this case the compression zone 254 is made tapered in the axial direction, so that a small change in volume initially forces the setting device, i.e. y. the valve finger to initially move a longer path. As the volume increases further, the setting device, i.e. y. valve finger stroke (stroke) in proportion to cross-section 254 of conically widening contour.

This ensures non-linear thermal action of the thermostatic capsule according to the invention.

FIG. 14 shows a modification of the thermostatic capsule 200 shown in FIG. 15 as a modified thermostatic capsule 300. In this case, the contour 354 is made as an inverted trapezoid or cone, but it has substantially the same nonlinear adjustment characteristic as the embodiment according to FIG. 14th

From the above description, it is clear that the valve device according to the invention may have either inputs or outputs, depending on which end of the radiator the valve device is connected to, the radiator may have either one inlet and two outputs or two inputs and one outlet, or respectively 2 inputs and 2 outputs. If the valve device according to the invention has only one feed line and one return line in the housing, the corresponding valve device may be provided at both the inlet and outlet of the radiator, and the function of the valve device according to the invention needs to be adapted accordingly.

Since the design of the valve unit alignment is known to those skilled in the art, no further explanation is required in this description.

FIG. Figures 16-32 illustrate the most valuable embodiments of the invention for so-called heating walls, which consist of vertical and horizontal flat heating pipes interconnected so that the medium can flow through vertical or vertical manifolds or ducts.

FIG. 16 shows a two-section vertical heating wall with so-called one-way connection, where the connection PD to the feed line is in the upper corner area of the front heating plate 1 and the return connection GR to the lower corner area of the rear heating plate 1 '. The warm water entering through the inlet connection is distributed in an appropriate manner in the upper heating plate before being directed to the rear heating plate 1 'by a switching member, preferably through a pipe made of metal or plastic. The flow of water in the upper zone is shown in Figs. 17, and in the lower zone of Figs. 18. The connecting pipes are made in such a way that the heating medium can reach the rear heating plate only in the upper right area. For this purpose, means are employed in accordance with the above embodiments of the invention, which can be readily applied by those skilled in the art to heating walls. FIG. Fig. 19 shows a vertical heating wall in which the heating plates are connected to each other in the upper and lower corner zones by T-elements. Flow control of the heating medium is carried out as shown in Figs. 20 and 21, T-shaped members made of a closed or permeable fluid such that the front heating plate always receives the flow of heating medium prior to entering the rear heating plate.

FIG. 22-32 illustrate different embodiments of horizontal heating walls, wherein the heating pipes are arranged horizontally and connected to one another by collector pipes of compact construction. Flow control of the heating medium proceeds as shown in Figs. 23 and 24, through guide plates in the side zones, which are arranged so that the front heating plate receives flow always in front of the rear heating plate.

FIG. 25-32 illustrate other embodiments of horizontal heating walls, wherein the flow of the heating medium is controlled analogously to the above embodiments of vertical heating walls, that is, through the correspondingly formed connecting pipes or T-shaped members. In order to avoid duplicates, a duplicate description thereof is not provided and reference is made to the previous description of embodiments.

Claims (65)

DEFINITION OF INVENTION 1. At least one-sectional, preferably two-sectional or multi-sectional radiator, in particular a flat radiator, comprising: - feed line connection (PD) location, - return connection point (GR), - a first segment (1) imparting flow and optimally directed towards the heated space, and - at least one transient flow and an optimally positioned posterior segment (ε), characterized in that the flow of the first segment is substantially uniformly ahead of the other segments, and that only the lower end zone of the first segment (1) provides at least one connection with at least one by another segment (1 '). 2. A radiator according to claim 1, characterized in that the first segment (1) is made so that a higher amount of heat can be supplied to it than to the rest of the radiator segments, at least at low heating power. 3. A radiator according to claim 1 or 2, characterized in that the segments are made in the form of plates and are preferably formed of profiled plates or flat tubes which are connected to one another through manifolds, preferably of sheet steel, where the plates are profiled so that 1, 1 ') comprises a plurality of passageways having a passage in the first segment (1) longer than the rest of the segments, the flow resistance of the passageways of the first segment (1) being lower than in the other segments, and segmented by one or more tubular connections; preferably of metal or plastic. 4. A radiator as claimed in any one of claims 1 to 3, wherein the feed line connection (PD) and the return line connection (GR) are each disposed on one vertical longitudinal edge of the radiator or each at the center of a horizontal radiator. A radiator according to any one of claims 1 to 4, characterized in that the first segment (1) is placed above or below the second segment (Γ), moreover, both segments are made in one heating body, respectively, in one heating plate. 6. A radiator according to any one of claims 1 to 5, characterized in that the surfaces of the segments (1, Γ) are provided with convective contours (2), which optimally have a rectangular or wavy profile. 7. A radiator according to claim 6, characterized in that the first segment (1) has no convective contour. 8. A radiator according to any one of claims 1 to 7, characterized in that it comprises adjustable blinds (7) for changing the cross section of convective circuits (2), whereby the blinds (7) can be displaced depending on the temperature so that: at low inlet temperatures in the first segment (1), the shutters (7) essentially cover the convection circuits (2). 9. A radiator according to claim 8, characterized in that it comprises a heat sensor (6) mounted in the first segment (1). 10. A radiator according to any one of claims 8 to 9, characterized in that a temperature dependent volume expansion (3) or a memory alloy or bimetal is provided for changing the position of the blinds (7). 11. A radiator according to any one of claims 1 to 10, characterized in that an insulating layer is provided, preferably of monolayer or multilayer aluminum, between the first segment and at least behind the segment, preferably in the first segment. 12. A radiator according to any one of claims 1 to 11, characterized in that it has a radiating screen on the side of the wall, preferably of laminated aluminum. 13. Single-section, optimally flat radiator or heating wall comprising: - feed line connection (PD) location, the return link point (GR), and - a flow-through heating body made in the form of a plate, characterized in that at least two differently calculated segments (8, 9) are provided, whereby the first segment (8) is located upstream of the remaining segments and can supply more heat than the remaining segments. segments, at least at low heating power. 14. A radiator according to claim 13, characterized in that at least the convective contours (2) are arranged on the surface of the heating body, which, in the top view, have an optimally rectangular or wavy profile. 15. A radiator according to claim 14, characterized in that the total surface of the convective circuits of the first segment (8) is smaller than the surface of the remaining sections. 16. The radiator of claim 14, wherein the first segment (8) has no convective contours. 17. A radiator according to any one of claims 13 to 16, characterized in that the heating body is made of a profiled sheet material, preferably a sheet of steel, forming a plurality of passageways, or of flat tubes interconnected with manifold ducts, wherein the first segment (8) the flow resistance of the flow channels is lower than that of the remaining segments. 18. A radiator according to any one of claims 13 to 17, characterized in that the heating body is profiled such that at least the first segment (8) has a plurality of passageways extending horizontally and in the form of a meander up or down, and / or at least the second segment (9) being profiled so as to have a plurality of vertically extending passageways, the first segment (8) being separated from the remaining segments by at least one partition (10). 19. A radiator as claimed in claim 18, characterized in that only one connection channel (11) passes through the separating baffle (10). 20. A radiator according to claim 19, characterized in that the connection channel (11) is located on one vertical longitudinal edge of the heating body. 21. A radiator according to claim 18, characterized in that a plurality of connecting channels (11) pass through the separating baffle (10). 22. A radiator as claimed in any one of claims 13 to 21, wherein the point of connection (PD) to the feed line is located on one vertical longitudinal edge of the heating body or at the center of the horizontal length of the heating body. 23. A radiator according to any one of claims 13 to 22, wherein the heating body is tilted back on at least one of its longitudinal edges to form a rear, optimally facing toward the wall, a heating body surface which extends parallel to the front surface of the heating body. in addition, the entrance is on the front, optimally facing the heated surface of the heated room. 24. A radiator as claimed in any one of claims 13 to 23, wherein the return connection (GR) is tubular and extends through a major portion of its length at the rear of the heating body. 25. A radiator according to claim 24, wherein the tubular return line (14) comprises a plurality of circular or rectangular convection bodies (15). 26. A radiator according to any one of claims 13 to 23, characterized in that it has two segments and the first segment (8) is midway between the remaining portions of the segment (9). 27. A radiator according to any one of claims 13 to 26, characterized in that it has a radiating screen (12) on the side of the wall, preferably made of multilayer aluminum. 28. Single-section or multi-section electric radiator, preferably a flat radiator comprising at least two differently calculated segments (8, 9) each having a plurality of heating elements (R _t ..... R _n , η ...... r _m ) and a control unit, characterized in that the control unit is constructed such that the electrical resistance of the segments is independently regulated from each other, and to the first segment at least more heat is fed than to the remaining segments, at least at low heating power. The radiator according to claim 28, characterized in that it is made in one section and combined with two segments, in which the first segment (8) is positioned above the second segment (9) or the first segment (8) is optimally facing towards the heated room and segments (9). 30. A radiator according to any one of claims 28 to 29, wherein the total electrical resistance of the first segment is less than the corresponding impedance of the other segments. 31. A radiator according to any one of claims 28 to 29, characterized in that the first segment (8) is provided with a self-adjusting, accordingly self-limiting resistance, optimally with elastomeric ferrites. 32. A radiator according to any one of claims 28 to 31, characterized in that the segments are made of profiled flat material, preferably of sheet steel, forming a plurality of passageways (21, 23), or of flat tubes interconnected by manifold channels. 33. A radiator according to claim 32, characterized in that at least one hollow space is formed therein for the passage of a fluid medium, preferably water or paraffin. 34. A radiator according to claim 33, wherein the heating elements are mounted directly in one or more hollow passageways (21) or the heating elements are mounted in metal bushings and the bushings are mounted in hollow passageways (21). 35. A radiator according to any one of claims 1 to 34, characterized in that at least one expansion device (19) is arranged between the semicircular, respectively, heating segment (1, Γ) plates (20a, 20b). 36. The radiator of claim 35, wherein at least one of the expansion devices (19) has at least one passage channel (19b) for providing a defined tolerance of the heating medium. 36. A radiator according to claim 35 or 36, characterized in that the expansion device (19) comprises means (19b, 19c) for securing the intended direction of installation of the expansion device between the semicircular, respectively, panels of the heating plate comprising the feed line pipe (PD). ). 38. The radiator of claim 37, wherein the guide means (19b) comprises at least one passageway (19b), respectively, formed therefrom. 39. A radiator according to claim 37 or 38, wherein the guide means (19b) has an outer contour which at least approximately corresponds to the contour (21, 22a, 22b) between the hemispheres, respectively, between the slabs for improving orientation, respectively. A method of manufacturing a radiator according to any one of claims 1 to 39, wherein - provides at least two semicircular, respectively, plates, preferably one or more pairs of plates of plastic deformable material, - at least one of these paired panels provides a guide structure for deflecting the heating medium, - the plates are joined to one another by extending the expansion devices at the intended locations between the panels, with at least one passage channel, characterized in that the expansion device is oriented as directed so that the heating medium is directed to the radiator. 41. The method of claim 40, wherein the expansion means comprises guiding means for guiding them. A method of manufacturing a radiator according to any one of claims 1 to 39, wherein the at least one heating plate consisting of flat tubes provides a guiding structure for directing the heating medium, wherein the guiding structure provides a directional feeding of the heating medium to separate segments. 43. Radiator, optimally paneled radiator, optimally applicable to central heating systems, characterized by having: - a heating segment mainly dedicated to radiant heat, - heating segment, mainly convection, - one feed line and one return line, - a valve, respectively, a thermostatic device, wherein the valve, respectively, of the thermostatic device, has a first flow-affecting segment corresponding to a heat-emitting segment, - another valve, respectively, a thermostatic device having a second flow-affecting segment corresponding to a conventional heating segment, characterized in that: - the radiating and convective segments both being provided with means for controlling a valve device comprising a housing having at least two inlets (014, 114), respectively, two feed lines or at least two outlets (016a, 016b; 116, 116a, 116b), respectively return lines, - a closing device (018a, 018b; 024a, 024b; 118a, 118b, 124a, 124b) belonging to each of the two inputs or to each of the two outputs, characterized in that each of the two inputs (014) or each of the two outputs (014); 016a, 016b) corresponds to one closing device (018a, 024a), in addition, at least one of the closing devices (018a, 024a; 118a, 124a) is provided with the possibility of transfer in separate zones, independently of the others. 44. A radiator according to claim 43, characterized in that the closing devices (018a, 024a; 118a, 124a) are optimally aligned in the axial direction, namely, one after the other, and are actuated differently, namely at different temperatures, or the closing device (018a). ) opens, closes, respectively, two inputs (014) or two outputs (016a, 016b; 116a, 116b). 45. The radiator of claim 44, wherein one closing device, namely, a valve disc, is preloaded with a spring member (026; 126) relative to the other valve disc such that, by moving the unloaded valve disc in an optimally adjustable path, the valve is preloaded. the plate would nevertheless remain in its at least substantially closed position so as to be optimally gripped by the gripper when the displacement path is crossed. 46. A radiator according to any one of claims 43 to 45, wherein a separate mechanical transfer device is provided for each closing device, respectively for each valve disc. 47. A radiator according to claim 43, wherein one closing device (018a) is disposed within the other closing device (124a), wherein the other closing device has an opening (114a, 120, 116a) which optimally has an axis region and a radial region, wherein the closing device affects the cross-section of the opening. 48. A radiator according to any one of claims 43 to 47, wherein the other closing device (018a; 118a) is operable against the first closing device (024a; 124a). 49. A radiator according to any one of claims 43 to 47, wherein the valve finger (028; 128) acts on one of the shut-off devices, the other shut-off device (024a; 124a) being preloaded with a spring member such that the valve finger ( 028; 128) is initially actuated by one closing device (018a; 118a) and the other closing device (024a; 124a) is actuated only when the clamp (030; 130) in one closing device (018a; 118a), respectively, in the valve plate (018a; 028; 128) grasps another closing device (024a; 124a). A radiator according to any one of claims 47 or 48 or 49, in so far as it is dependent on claim 46, wherein the other closure device has an optimally radial opening (114a, 120, 116a) and an inlet, respectively, in the housing (112). enters into one another such that when the other closure device (124a) and the one closure device (118a) are both open, it is provided with an enlarged passage cross section. 51. The radiator of claim 50, wherein its inputs, respectively, the outlets (114, 116b, 116, 116a, 114a, 120) have a mutually aligned cross-section of the outlets such that, when all inputs and outputs are open, the inputs substantially the cross-section of the outputs and vice versa. 52. A radiator as claimed in any one of claims 43 to 48, wherein the two inlets, respectively, the two inlets are in a single feed pipe, respectively, an outlet pipe. 53. A radiator according to any one of claims 43 to 51, wherein the valve finger is connected to a thermostat device comprising a thermostatic capsule, preferably a wax capsule, respectively. 54. A radiator as claimed in any one of claims 43 to 47, wherein the closing devices are at least two valve valves which are movable relative to one another, wherein, within an optimum stroke range, one valve plate initially loosens the cross-section of the passageways. for loosening the cross-section. 55. The radiator of claim 54, wherein the rod, respectively, of the valve finger (028; 128) initially grasps the first valve plate and retards the second valve plate. 56. A radiator according to claim 54 or 55, wherein one of the valve plugs is preloaded with respect to the other valve plate, such as a spring member (026; 126). 57. A radiator according to any one of claims 54 to 56, wherein the valve pads corresponding to the valve discs are disposed in a single plane, the valve discs being disposed in a single plane in the closed position of the valve. 58. The radiator of claim 43, wherein the valve device (010; 100), respectively, of the valve, comprises a first affecting flow segment and a second affecting flow segment. 59. A radiator according to claim 43 or 58, wherein the two valve units (010; 100) respectively operate at different room temperatures. 60. The radiator of claim 58 or 59, wherein each heating segment has a single inlet and a single outlet. 61. A radiator according to any one of claims 58 to 60, characterized in that the two valve units (010; 100) respectively have a common housing, wherein the housing has one entrance opening and one outlet opening for each of the heating segments, or one exit opening and one entrance opening for each of the heating segments. 62. A radiator according to any one of claims 58 to 61, characterized in that the convection heating segment and / or radiant heating segment is subdivided into sub-segments which are respectively disconnected manually and / or automatically, for example by hand valves, thermostatic valves and so on. 63. Thermostatic capsule, preferably a wax capsule containing paraffin, respectively - casing, - the volume of the medium exposed to thermal expansion in the housing, preferably paraffin wax, respectively, - thermal expansion, respectively contraction, compensating for the contour, which is optimally self-flexible, characterized in that the contour (254; 354) is radially, respectively, axially shaped so that when the volume changes (252; 352) this contour changes its axis nonlinearly. length. 64. The thermostatic capsule of claim 63, wherein the contour in the axial direction, respectively, in the volume compensation direction, is geometrically such that the linear expansion of the volume causes a non-linear change of the contour length in the axial direction. 65. A thermostatic capsule according to claim 63 or 64, characterized in that the contour is formed by a tapered or axially increasing circle. 66. The thermostatic capsule of claim 63 or 64, wherein the contour (254; 354) has at least one area that is tapered or tapered.