Device for transferring heat of a gaseous working medium
By setting a second partition layer in the heat pump equipment to achieve pressure balance, the problem of high material and structural requirements under high efficiency is solved, realizing a compact structure and efficient heat transfer, which is suitable for buildings and electric vehicles.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- RIMACOMP GMBH
- Filing Date
- 2022-01-12
- Publication Date
- 2026-06-19
AI Technical Summary
Existing heat pump equipment requires high operating pressure to achieve high efficiency, resulting in high requirements for materials and structures. Furthermore, the preheating medium, such as external air, is costly and requires a large space.
By setting a second partition layer between the heat exchange pipeline and the working pipeline, pressure balance is achieved, allowing the first section of the working pipeline to be coupled with the heat exchange pipeline. Heat transfer is carried out by utilizing the gap between the inner and outer walls and the channel structure, and a thin-wall design is achieved to improve efficiency.
It achieves a compact structure for high efficiency, improves the heat transfer efficiency between the working medium and the heat exchange medium, and can reduce the wall thickness by more than 50%. It is suitable for buildings and electric vehicles, with a COP value in the range of 5 to 8.
Smart Images
Figure CN116917682B_ABST
Abstract
Description
Technical Field
[0001] This invention relates to an apparatus for transferring heat from a gaseous working medium to a heat exchange medium by compressing a gaseous working medium, wherein the apparatus comprises: a working conduit, wherein a volume enclosed by the working conduit is divided into at least two sections, namely a first section and a second section, wherein the first section is configured to receive a pressure transmission medium, and the second section is configured to receive and output the gaseous working medium, wherein at least one inlet and outlet valve is provided for receiving and outputting the gaseous working medium, wherein a first volume defined by the first section and a second volume defined by the second section are separated by a movable first partition in the working conduit, wherein the first partition is configured such that the pressure difference between the first section and the second section of the working conduit is compensated by the movement of the first partition in the working conduit and the resulting change in the size ratio between the first volume and the second volume; and a heat exchange conduit for receiving the heat exchange medium. Background Technology
[0002] Heat pumps are known from existing technologies, for example, for delivering optionally preheated fresh air into the interior space of, for example, a building or vehicle compartment. Here, heat is transferred to a heat exchange medium by means of the compression of the working medium, and the efficiency of such a heat pump is largely related to the temperature of the working medium during its preparation and the pressure used. In conventional heat pumps used in home engineering, pressures of several bar can be present, for example. In principle, using higher operating pressures allows for higher efficiency. However, higher pressures also impose higher requirements on the materials used and the structures to be used. Therefore, to achieve good efficiency at lower pressures, it has been common to preheat the working medium, particularly in the form of external air, which can be achieved, for example, by using geothermal energy. However, this comes with considerable cost. Furthermore, this approach requires a correspondingly large space. Summary of the Invention
[0003] Therefore, the object of the present invention is to realize a device for heat transfer that overcomes the disadvantages mentioned at the beginning and achieves a compact construction while being highly efficient.
[0004] This objective is achieved by means of a device of the type mentioned at the beginning: According to the invention, a heat exchange pipeline is coupled to a first section of a working pipeline to achieve pressure balance, wherein the heat exchange pipeline and the first section of the working pipeline are connected and a second partition layer is provided between these pipelines to separate the pipelines from each other, wherein the second partition layer is configured and arranged such that a continuous pressure balance exists between the heat exchange pipeline and the first section of the working pipeline, wherein the second section of the working pipeline has a heat output section, the heat output section being surrounded from the outside and the inside by a two-piece heat absorption section of the heat exchange pipeline, wherein the working pipeline has an inner wall and a covering inner wall. An outer wall and a working medium gap are formed between the inner wall and the outer wall to guide the working medium. The inner wall surrounds the channel, through which a first part of the heat exchange pipeline is formed in the heat absorption section. The heat exchange pipeline in the heat absorption section also has an outer cover wall that encloses the outer wall of the working pipeline. The outer cover wall forms a second part of the heat exchange pipeline in the heat absorption section and defines it. A heat exchange medium gap is formed between the outer wall of the working pipeline and the outer cover wall of the heat exchange pipeline, which is connected in parallel with the channel. This allows the heat exchange medium guided in the heat absorption section of the heat exchange pipeline to flow around the working pipeline on the outside through the heat exchange medium gap and on the inside through the channel.
[0005] According to the design scheme of the present invention, a very wide operating range can be achieved with respect to the pressure present in the device. Because the working pipeline can be surrounded by the heat exchange medium on both sides in the heat output section, particularly efficient heat transfer to the heat exchange medium can be achieved.
[0006] Another significant advantage lies in the pressure balance that can be established through pressure coupling between the pressure transmission, heat exchange medium, and working medium. This allows for the design of significantly thinner walls in the heat output section of the working pipe compared to walls designed without such pressure balance. In fact, the walls only need to be designed to facilitate the proper guidance of the first partition layer and ensure the mechanical stability of the pipe, since the pressure is as uniform as possible on both the inner and outer sides of the working pipe wall. This means that the walls can be, for example, more than 50% thinner than possible without such pressure balance. This improves the heat transfer efficiency between the working and heat exchange media. In absolute terms, the wall thickness in the heat output or absorption section, excluding the outer casing wall of the heat exchange pipe, can be, for example, between 1 mm and 4 mm, and especially less than 10 mm.
[0007] With the device according to the invention, the device can be used, for example, in the form of a heat pump for buildings or vehicles, especially electric vehicles, and can achieve a COP value in the range of 5 to 8.
[0008] At least one inlet and outlet valve does not necessarily have to be a single piece. Of course, separate inlet and outlet valves can also be installed. Multiple valves can also be installed. Of course, the expression "pipeline pressure" refers to the pressure of the medium received in the pipeline; that is, pressure balance between two pipelines means pressure balance between the media received in the pipelines.
[0009] The pressure balancing is preferably performed so that there is essentially no tensile or compressive stress in the radial direction of the pipeline. As a result, the wall between the working medium and the heat exchange medium in the heat output section can be constructed to be extremely thin, thereby achieving better heat transfer.
[0010] For example, the device according to the invention can operate such that periodic pressure changes are transmitted via a pressure transmission medium to two partitions, wherein an increase in pressure causes at least the first partition to move such that the working medium received in the first section is compressed and thus heated. The heated working medium here transfers heat to a heat exchange medium. The pressure is increased until the first partition reaches its endpoint and, after sufficient heat transfer, the outlet valve is opened to release the working medium. Thereafter, the pressure of the pressure transmission medium decreases, causing the first partition to move back, and fresh working medium is drawn into the second section via the inlet valve to be opened.
[0011] In particular, it can be proposed that the heat exchange medium is at least partially gaseous. For example, it could be heated water vapor, and a mixture of gaseous and liquid states is also possible.
[0012] Furthermore, it can be stated that the heat exchange medium is a liquid medium, especially water. The condition description always refers to the thermal state during rated operation of the equipment according to the invention and to the rated values of the pressure and temperature range present in the medium.
[0013] In particular, it can be pointed out that the pressure transmission medium in the first section of the working pipeline is oil.
[0014] Of course, the device according to the invention can contain the corresponding medium, or it may have been filled accordingly upon delivery.
[0015] Furthermore, it can be proposed that the first separation layer can be formed directly through the interface formed by the surface tension of the liquid pressure transmission medium relative to the gaseous working medium.
[0016] The aforementioned separating layers, namely the first and second separating layers, can be simply provided by boundary layers, which are formed by two immiscible media relative to each other. Therefore, the separating layers can be formed, for example, by a transition between oil and air or oil and water. Here, the piping in the transition region can be oriented such that the different densities of the media used form a boundary surface, which extends transversely, and in particular orthogonally, to the respective pipe cross-sections, thereby separating the media from each other along a short path. Therefore, the piping in the transition region of the media can, for example, be vertically oriented and thus achieve, for example, a boundary between oil (as a pressure transmission medium) and air (as a working medium), such that oil, due to its higher density, tends to accumulate in the lower region of the vertical pipe section.
[0017] Alternatively, it can be proposed that the first separating layer can be constituted by a first separating mechanism provided for this purpose, which is preferably configured as a spatially movable first sealing element. For example, such a sealing element can be implemented as an O-ring or as a lip seal.
[0018] Furthermore, it can be proposed that, in the heat absorption section, the heat exchange pipelines are symmetrically arranged around the longitudinal axis.
[0019] In particular, it can be proposed that the working pipeline can be configured as a concentric double pipe in the heat output section, the double pipe being coaxially configured with the longitudinal axis of the heat exchange pipeline in the region of the heat absorption section, wherein the working medium gap is formed between the inner and outer walls of the double pipe and is limited by the inner and outer walls, wherein the outer wall of the heat exchange pipeline surrounds the double pipe and the channel is surrounded by the inner wall of the double pipe.
[0020] Furthermore, it can be proposed that the cross-sections of the inner and outer walls form a multi-toothed star shape, which is particularly axially symmetric or point-symmetric, wherein the star shape formed by the outer wall is preferably an enlargement of the star shape formed by the inner wall. By forming a star shape, the surface area of the corresponding wall is significantly increased, thereby improving heat transfer between the working medium and the heat exchange medium. Typically, using such a structure in systems under high pressure is extremely difficult due to the bending stress that occurs in the corresponding tips. However, in this paper, the pressure balance between the media allows for the use of complex geometries with small wall thicknesses even in the presence of high ambient pressure. The enlargement is preferably achieved here such that the outer star shape has the same geometry as the inner star shape and is only a scaled-down version of the inner star shape. That is, when the outer star shape is scaled down, it can coincide with the inner star shape.
[0021] In particular, it can be proposed that the working piping in a region of the heat output section be configured such that the working medium gap tapers toward at least one inlet and outlet valve. Here, relative to the non-tapered region of the working piping, the gap width tapers by at least 20%, preferably 30%, and especially 50% or 80%. In this way, heat transfer can be further improved.
[0022] Furthermore, it can be proposed that the working pipeline be divided into parallel-connected branches at least within the heat output section.
[0023] In particular, it can be proposed that the device is designed for operating pressures between 6 bar and 1000 bar, preferably between 50 bar and 100 bar, in such a way that the working piping and heat exchange piping, as well as at least one inlet and outlet valve, are designed to withstand the rated operating pressure. A pressure of 1000 bar can be meaningful for hydrogen applications. If the device according to the invention is to be used as a heat pump, then the operating pressure is, for example, at least 10 bar (i.e., the pressure in the transmission medium or the first section, which is then transmitted to the remaining media), of which 50 bar to 100 bar is particularly meaningful for the purposes of the invention. The higher the pressure selected, the higher the efficiency of the device.
[0024] The device according to the invention can be sized in various ways. Therefore, for small installations, for example, a weight in the range of 10 kg and a size less than 30 cm can be proposed, thus making the device particularly suitable for use, for example, in vehicles. However, it can also be considered for large installations, such that the device can weigh several tons and have a structural height of approximately 3 meters. The device according to the invention has excellent scalability in terms of performance.
[0025] Furthermore, it can be proposed that the device also has a pump for transmitting pressure to a pressure transmission medium contained in a first section of the working pipeline, wherein the pump is preferably configured as a rotary pump, piston pump, gear pump or vane pump.
[0026] In particular, it can be pointed out that the device also has a heat exchanger, wherein heat exchange lines are connected to the heat exchanger to output heat.
[0027] Furthermore, it can be proposed that the second separating layer is composed of a second separating mechanism provided for this purpose, the second separating mechanism preferably being configured as a spatially movable second sealing element, the second sealing element being configured as an elastic membrane fixedly mounted on its edge or otherwise spatially movable. For example, the second sealing element can be designed as an O-ring or a lip seal.
[0028] This invention enables a structural form for near-isothermal compression of gases using a piston compressor. Here, the energy used for heat exchange can be reduced during gas compression, thereby improving efficiency. Essentially, two resistances must be overcome during gas compression:
[0029] 1. Resistance caused by reducing volume
[0030] 2. By reducing volume, the temperature continues to rise, thereby increasing the resistance to further compression.
[0031] If heat is successfully and continuously removed during compression (i.e., maintaining the temperature as constant as possible), then this means a significant reduction in energy consumption. In this configuration or the device according to the invention, it is possible to achieve almost continuous heat removal during the compression process based on the piston.
[0032] Furthermore, it should be mentioned that the compressed and cooled working medium can reach extremely low temperatures when depressurized through the outlet valve. The outflowing working medium is ideal for a variety of cooling purposes, suitable for indoor air conditioning, as well as applications in cold storage and the chemical industry. Attached Figure Description
[0033] The invention is described in detail below with reference to exemplary and non-limiting embodiments, which are illustrated in the accompanying drawings. The drawings show:
[0034] Figure 1 A schematic diagram of the device according to the present invention is shown, and
[0035] Figure 2 Showing the corresponding Figure 1 A cross-sectional view of the tangent AB. Detailed Implementation
[0036] In the following figures, (unless otherwise stated) the same reference numerals denote the same features. Figure 1 An embodiment of the device 1 according to the present invention is shown, the device being used to transfer heat from a gaseous working medium M2 to a heat exchange medium M3 by compressing a gaseous working medium M2. Here, the device 1 includes a working conduit AL, wherein a volume V surrounded by the working conduit AL is divided into at least two sections, namely a first section AL-V1 and a second section AL-V2. The first section AL-V1 is configured to receive the pressure transmission medium M1, while the second section AL-V2 is configured to receive and output the gaseous working medium M2. For receiving and outputting the gaseous working medium M2, at least one inlet and outlet valve 2 is provided, wherein a first volume defined by the first section AL-V1 and a second volume defined by the second section AL-V2 are separated by a movable first partition layer T12 in the working conduit AL.
[0037] The first partition layer T12 is configured such that movement through the first partition layer T12 in the working conduit AL (exemplarily in...) Figure 1 The pressure difference between the first section AL-V1 and the second section AL-V2 of the working pipeline AL is balanced by the change in the size ratio between the first and second volumes (indicated by the arrows) and the accompanying change, which allows the working medium M2 to be compressed and heated.
[0038] In addition, the device 1 also includes a heat exchange pipeline WL for receiving the heat exchange medium M3. Here, the heat exchange pipeline WL is coupled to the first section AL-V1 of the working pipeline AL to achieve pressure balance, in such a way that the heat exchange pipeline WL is connected to the first section AL-V1 of the working pipeline AL and a second partition layer T13 is provided between these pipelines (i.e., the working pipeline AL and the heat exchange pipeline WL) to separate the pipelines from each other.
[0039] The second partition layer T13 is configured and arranged to provide a continuous pressure balance between the heat exchange pipe WL and the first section AL-V1 of the working pipe AL. The second section AL-V2 of the working pipe AL has a heat output section AL-V2' (for better overview, this heat output section is only shown on one side of the x-axis symmetrical structure and is provided with a reference numeral), which is surrounded on the outside and inside by a two-piece heat absorption section WL' of the heat exchange pipe WL, such that the working pipe AL has an inner wall AL-IW and an outer wall AL-AW that covers the inner wall AL-IW (see also...). Figure 2 A working medium gap S-M2 is formed between the inner wall AL-IW and the outer wall AL-AW to guide the working medium M2. The inner wall AL-IW surrounds the channel K, through which the first part of the heat exchange pipeline WL is formed in the heat absorption section WL'. In addition, the heat exchange pipeline WL also has an outer casing wall WL-M in the heat absorption section WL' that surrounds the outer wall AL-AW of the working pipeline AL, through which the second part of the heat exchange pipeline WL is formed in the heat absorption section and is defined thereto. A heat exchange medium gap S-M3 is formed between the outer wall AL-AW of the working pipeline AL and the outer casing wall WL-M of the heat exchange pipeline WL, and is connected in parallel with the channel K, such that the heat exchange medium M3 guided in the heat absorption section WL' of the heat exchange pipeline WL can cause the working pipeline AL to flow around the heat exchange medium gap S-M3 on the outside and through the channel K on the inside.
[0040] In addition, Figure 1Pump 3 is shown, by means of which pressure is applied to the pressure transmission medium M1. If this pressure increases, the separator T12 moves toward valve 2, and with the valve closed, the working medium M2 is compressed and thus heated. After a predetermined duration and / or after compression and successful heat transfer to the heat exchange medium M3, outlet valve 2 is opened, reducing the pressure acting on the pressure transmission medium M1, allowing separator 12 to move further downward, and fresh working medium M2 can flow into the second section AL-V2 via inlet valve 2, where it is subsequently compressed and heated again by increasing the pressure. For example, in Figure 1 The pump 3 shown is a hydraulic pump, and the hydraulic fluid 6 received in the container 5 is shown.
[0041] The heat exchange medium M3 can be a liquid medium, especially water. Furthermore, it can be proposed that the pressure transmission medium M1 in the first section AL-V1 of the working pipeline AL can be oil. Depending on the medium used, the first partition layer T12 can be formed directly through an interface based on the surface tension of the liquid pressure transmission medium M1 relative to the gaseous working medium M2. Alternatively, the first partition layer T12 can be formed by a first partition mechanism T12, preferably configured as a spatially movable first sealing element. Similarly, the second partition layer T13 can be formed by a second partition mechanism, preferably configured as a spatially movable second sealing element, which is either an elastic membrane fixedly mounted on its edge or spatially movable in its entirety. The first partition layer T12 and / or the second partition layer T13 can also be formed by the surface of a partition column, which can be movably held in the working pipeline AL.
[0042] In addition, Figure 1 Chinese combination Figure 2 As can be seen, in the region of the heat absorption section WL', the heat exchange pipe WL is symmetrically arranged around the longitudinal axis x. More precisely, the working pipe AL can be configured as a concentric double pipe in the heat output section AL-V2', which is coaxially arranged with the longitudinal axis x of the heat exchange pipe WL in the region of the heat absorption section WL'. The working medium gap S-M2 is formed between the inner wall AL-IW and the outer wall AL-AW of the double pipe and is limited by the inner and outer walls. The outer casing wall WL-M of the heat exchange pipe WL surrounds the double pipe, and the channel K is surrounded by the inner wall AL-IW of the double pipe (see also...). Figure 2 The inner wall AL-IW can be fitted with heat sinks that extend into channel K to improve heat exchange. Figure 2 Other heat sinks are also shown, which extend from the outer wall AL-AW into the heat exchange medium gap S-M3 to improve heat exchange.
[0043] Unlike what is shown in the accompanying drawings, the inner wall AL-IW and the outer wall AL-AW can form a multi-toothed star shape in cross-section, the star shape being particularly axially or point-symmetric, wherein the star shape formed by the outer wall AL-AW is preferably an enlargement of the star shape formed by the inner wall AL-IW.
[0044] exist Figure 1 It can also be seen that the working pipeline AL is configured in a region of the heat output section AL-V2' such that the working medium gap S-M2 gradually narrows toward at least one inlet and outlet valve 2. This region is marked with the reference numeral S-M2v.
[0045] It can also be proposed that the working pipeline AL is divided into parallel-connected branches at least within the heat output section WL'AL-V2'. Here, the term "parallel connection" is understood to mean that the media guided in parallel can be mixed again after being connected in parallel.
[0046] exist Figure 1 The diagram also shows a heat exchanger 4, which can be a component of the device 1, wherein a heat exchange line WL is connected to the heat exchanger 4 to output heat.
[0047] This invention is not limited to the embodiments shown, but is defined by the entire scope of the claims. Various aspects of the invention or its embodiments can also be considered and combined with each other. Any reference numerals in the claims are exemplary and are used only to facilitate reading the claims, and are not intended to be limiting.
Claims
1. A device (1) for transferring heat from a gaseous working medium (M2) to a heat exchange medium (M3) by compressing a gaseous working medium (M2), wherein the device (1) comprises: - A working conduit (AL), wherein a volume (V) enclosed by the working conduit (AL) is divided into at least two sections, namely a first section (AL-V1) and a second section (AL-V2), wherein the first section (AL-V1) is provided for receiving a pressure transmission medium (M1) and the second section (AL-V2) is provided for receiving and outputting the gaseous working medium (M2), wherein at least one inlet and outlet valve (2) is provided for receiving and outputting the gaseous working medium (M2), wherein a first volume defined by the first section (AL-V1) and a second volume defined by the second section (AL-V2) are separated by a movable first partition (T12) in the working conduit (AL), wherein the first partition (T12) is configured such that movement of the first partition (T12) in the working conduit (AL) and a change in the size ratio between the first volume and the second volume thereunder balance the pressure difference between the first section (AL-V1) and the second section (AL-V2) of the working conduit (AL). - Heat exchange piping (WL) for receiving the heat exchange medium (M3). Its features are, The heat exchange pipe (WL) is coupled to the first section (AL-V1) of the working pipe (AL) to induce pressure balance, wherein the heat exchange pipe (WL) is connected to the first section (AL-V1) of the working pipe (AL), and a second partition layer (T13) is provided between the heat exchange pipe (WL) and the working pipe (AL) to separate the heat exchange pipe (WL) and the working pipe (AL) from each other, wherein the second partition layer (T13) is configured to maintain a continuous pressure balance between the heat exchange pipe (WL) and the first section (AL-V1) of the working pipe (AL). The second section (AL-V2) of the working pipe (AL) has a heat output section (AL-V2'), which is surrounded on the inner and outer sides by a two-piece heat absorption section (WL') of the heat exchange pipe (WL). The working pipe (AL) has an inner wall (AL-IW) and an outer wall (AL-AW) covering the inner wall (AL-IW), and a working medium gap (S-M2) is formed between the inner wall (AL-IW) and the outer wall (AL-AW) to guide the working medium (M2). The inner wall (AL-IW) surrounds a channel (K), through which the first part of the heat exchange pipe (WL') is formed in the heat absorption section, and the heat exchange pipe ( The heat absorption section (WL') also has an outer casing wall (WL-M) that surrounds the outer wall (AL-AW) of the working pipe (AL). The outer casing wall forms a second part of the heat exchange pipe (WL) in the heat absorption section (WL') and defines it. A heat exchange medium gap (S-M3) is formed between the outer wall (AL-AW) of the working pipe (AL) and the outer casing wall (WL-M) of the heat exchange pipe (WL) and is connected in parallel with the channel (K). This allows the heat exchange medium (M3) guided in the heat absorption section (WL') of the heat exchange pipe (WL) to flow around the working pipe (AL) on the outside through the heat exchange medium gap (S-M3) and on the inside through the channel (K).
2. The device (1) according to claim 1, wherein the heat exchange medium (M3) is at least partially gaseous.
3. The device (1) according to claim 1, wherein the heat exchange medium (M3) is a liquid medium.
4. The device (1) according to claim 3, wherein the heat exchange medium (M3) is water.
5. The device (1) according to any one of claims 1 to 4, wherein the pressure transmission medium (M1) in the first section (AL-V1) of the working pipeline (AL) is oil.
6. The device (1) according to claim 5, wherein the first separation layer (T12) is formed directly by an interface formed by the surface tension of the liquid pressure transmission medium (M1) relative to the gaseous working medium (M2).
7. The device (1) according to any one of claims 1 to 4, wherein the first partition layer (T12) is constituted by a first partition mechanism provided for this purpose.
8. The device (1) according to claim 7, wherein the first separating mechanism is configured as a spatially movable first sealing element.
9. The device (1) according to any one of claims 1 to 4, wherein the heat exchange pipeline (WL) is symmetrically configured about the longitudinal axis (x) in the region of the heat absorption section (WL').
10. The device (1) according to claim 9, wherein the working conduit (AL) is configured as a concentric double tube in the heat output section (AL-V2'), the double tube being coaxially configured with the longitudinal axis (x) of the heat exchange conduit (WL) in the region of the heat absorption section (WL'), wherein the working medium gap (S-M2) is formed between the inner wall (AL-IW) and the outer wall (AL-AW) of the double tube and is limited by the inner and outer walls, wherein the outer casing wall (WL-M) of the heat exchange conduit (WL) surrounds the double tube, and the channel (K) is surrounded by the inner wall (AL-IW) of the double tube.
11. The device according to any one of claims 1 to 4, wherein the inner wall (AL-IW) and the outer wall (AL-AW) form a multi-toothed star shape in cross-section.
12. The device according to claim 11, wherein the star shape is configured to be axially or point-symmetrical.
13. The device according to claim 11, wherein the star shape formed by the outer wall (AL-AW) is an enlargement of the star shape formed by the inner wall (AL-IW).
14. The device (1) according to any one of claims 1 to 4, wherein the working conduit (AL) in the region of the heat output section (AL-V2') is configured such that the working medium gap (S-M2) tapers toward at least one inlet and outlet valve (2).
15. The device (1) according to any one of claims 1 to 4, wherein the working conduit (AL) is divided into parallel branches at least within the heat output section.
16. The device (1) according to any one of claims 1 to 4, wherein the device (1) is designed for a rated operating pressure between 6 bar and 1000 bar, in such a way that the working line (AL) and the heat exchange line (WL) and the at least one inlet and outlet valve (2) are designed to withstand the rated operating pressure.
17. The device (1) according to claim 16, wherein the device (1) is designed for a rated operating pressure between 50 bar and 100 bar.
18. The device (1) according to any one of claims 1 to 4, wherein the device (1) further comprises a pump (3) for transmitting pressure to a pressure transmission medium (M1) contained in a first section (AL-V1) of the working line (AL).
19. The device (1) according to claim 18, wherein the pump (3) is configured as a rotor pump, piston pump, gear pump or vane pump.
20. The device (1) according to any one of claims 1 to 4, wherein the device (1) further comprises a heat exchanger (4), wherein the heat exchange line (WL) is connected to the heat exchanger (4) to output heat.
21. The device (1) according to any one of claims 1 to 4, wherein the second partition layer (T13) is constituted by a second partition mechanism provided for this purpose.
22. The device (1) according to claim 21, wherein the second separating mechanism is configured as a spatially movable second sealing element, the second sealing element being configured as an elastic membrane fixedly mounted on its edge or as a whole being spatially movable.