Device for transferring heat from a gaseous working medium

Abstract

The invention relates to a device (1) for transferring heat from a gaseous working medium (M2) to a heat-exchanger medium (M3) by compressing the gaseous working medium (M2), wherein the device (1) comprises: an operating line (AL), wherein the volume (V) enclosed by the operating line (AL) is divided into at least two sections, namely a first (AL-V1) and a second section (AL-V2), wherein the first section (AL-V1) is set up to hold a pressure-transfer medium (M1) and the second section (AL-V2) is set up to hold and discharge the gaseous working medium (M2), wherein at least one inlet and outlet valve (2) is provided for holding and discharging the gaseous working medium (M2), wherein a first volume delimited by the first section (AL-V1) is separated from a second volume delimited by the second section (AL-V2) by a first separating layer (T12) that can be displaced within the operating line (AL), wherein the first separating layer (T12) is arranged in such a way that pressure differences between the first (AL-V1) and second sections (AL-V2) of the operating line (AL) are equalized by a displacement of the first separating layer (T12) in the operating line (AL) and an accompanying change in the proportion between the first volume and the second volume is equalized, and comprising a heat-exchanger line (WL) to hold the heat-exchanger medium (M3), wherein the heat-exchanger line (WL) is coupled to the first section (AL-V1) of the operating line (AL) to bring about pressure equalization.

Claims

1. A device (1) for transferring heat from a gaseous working medium (M2) to a heat-exchanger medium (M3) by compressing the gaseous working medium (M2), wherein the device (1) comprises: an operating line (AL), wherein the volume (V) enclosed by the operating line (AL) is divided into at least two sections, namely a first (AL-V1) and a second section (AL-V2), wherein the first section (AL-V1) is set up to hold a pressure-transfer medium (M1) and the second section (AL-V2) is set up to hold and discharge the gaseous working medium (M2), wherein at least one inlet and outlet valve (2) is provided to hold and discharge the gaseous working medium (M2), wherein a first volume delimited by the first section (AL-V1) is separated from a second volume delimited by the second section (AL-V2) by a first separating layer (T12) that can be displaced within the operating line (AL), wherein the first separating layer (T12) is arranged in such a way that pressure differences between the first (AL-V1) and second (AL-V2) sections of the operating line (AL) are equalized by a displacement of the first separating layer (T12) in the operating line (AL) and an accompanying change in the proportion between the first volume and the second volume is equalized; and a heat-exchanger line (WL) to hold the heat-exchanger medium (M3), wherein the heat-exchanger line (WL) is coupled to the first section (AL-V1) of the operating line (AL) in order to bring about pressure equalization by connecting the heat-exchanger line (WL) to the first section (AL-V1) of the operating line (AL) and a second separating layer (T13) is provided between these lines (WL, AL) for separating the lines (WL, AL) from each other, wherein the second separating layer (T13) is designed and arranged in such a way that there is a continuous pressure equalization between the heat-exchanger line (WL) and the first section (AL-V1) of the operating line (AL), and wherein the second section (AL-V2) of the operating line (AL) comprises a heat-emission section (AL-VT) enclosed by a two-part heat-absorption section (WL) of the heat-exchanger line (WL) on the outside and inside while the operating line (AL) comprises an inner wall (AL-IW) and an outer wall (AL-AW) encapsulating the inner wall (AL-IW), and, between the inner wall (AL-IW) and the outer wall (AL-AW), a working-medium gap (S-M2) is formed to guide the working medium (M2), wherein the inner wall (AL-IW) is enclosed by a channel (K) through which a first part of the heat-exchanger line (WL) is formed in the heat-absorption section (WL), and the heat-exchanger line (WL) in the heat-absorption section (WL) also comprises a shell wall (WL-M) enveloping the outer wall (AL-AW) of the operating line (AL), through which a second part of the heat-exchanger line (WL) is formed and delimited in the heat-absorption section (WL), wherein, between the outer wall (AL-AW) of the operating line (AL) and the shell wall (WL-M) of the heat-exchanger line, (WL), a heat-exchanger-medium gap (S-M3) connected in parallel with the channel (K) is formed so that a heat-exchanger medium (M3) conveyed in the heat-absorption section (WL) of the heat-exchanger line (WL) can flow around the operating line (AL) on the outside via the heat-exchanger-medium gap (S-M3) and on the inside via the channel (K).

2. The device (1) according to claim 1, wherein the heat-exchanger medium (M3) is at least partially gaseous.

3. The device (1) according to claim 1, wherein the heat-exchanger medium (M3) is a liquid medium.

4. The device (1) according to claim 1, wherein the pressure-transfer medium (M1) in the first section (AL-V1) of the operating line (AL) is an oil.

5. The device (1) according to claim 4, wherein the first separating layer (T12) is formed directly by the boundary surface formed on the basis of the surface tension of the liquid pressure-transfer medium (M1) with respect to the gaseous working medium (M2).

6. The device (1) according to claim 1, wherein the first separating layer (T12) is formed by a first separating means provided for this purpose, which is preferably formed as a first seal element that can be spatially displaced.

7. The device (1) according to claim 1, wherein the heat-exchanger line (WL) is formed symmetrically around a longitudinal axis (x) in the region of the heat-absorption section (WL).

8. The device (1) according to claim 7, wherein the operating line (AL) in the heat-emission section (AL-V2) is formed as a concentric double pipe formed coaxially to the longitudinal axis (x) of the heat-exchanger line (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 pipe and delimited by them, wherein the shell wall (WL-M) of the heat-exchanger line (WL) is the double pipe and the channel (K) is enclosed by the inner wall (AL-IW) of the double pipe.

9. The device according to claim 1, wherein the inner wall (AL-IW) and the outer wall (AL-AW) form a multi-toothed star in a cross-section, which multi-toothed star is, in particular, axially or point-symmetrically formed.

10. The device (1) according to claim 1, wherein the operating line (AL) in one area of the heat-emission section (AL-V2) is designed in such a way that the working-medium gap (S-M2) tapers towards at least one inlet and outlet valve (2).

11. The device (1) according to claim 1, wherein the operating line (AL) is distributed at least within the heat-emission section on branches connected in parallel.

12. The device (1) according to claim 1, wherein the device (1) is designed for a nominal operating pressure between 6 bar and 1000 bar by designing the operating line (AL) and the heat-exchanger line (WL) as well as the at least one inlet and outlet valve (2) to withstand the nominal operating pressure.

13. The device (1) according to claim 1, further comprising a pump (3) for transferring pressure to a pressure-transfer medium (M1) contained in the first section (AL-V1) of the operating line (AL).

14. The device (1) according to claim 1, further comprising a heat exchanger (4), wherein the heat-exchanger line (WL) is connected to the heat exchanger (4) for dissipating heat.

15. The device (1) according to claim 1, wherein the second separating layer (T13) is formed by a second separating means provided for this purpose, which is preferably designed as a spatially displaceable second seal element, which is designed as an elastic membrane firmly mounted at its edges or designed to be spatially displaceable in its entirety.

16. The device (1) according to claim 3, wherein the liquid medium is water.

17. The device according to claim 9, wherein the star formed by the outer wall (AL-AW) is an enlargement of the star formed by the inner wall (AL-IW).

18. The device according to claim 12, wherein the device (1) is designed for a nominal operating pressure between 50 bar and 100 bar.

19. The device according to claim 13, wherein the pump (3) is a rotary piston pump, a piston pump, a gear pump or a vane pump.

Description

(1) The invention is explained in more detail below by means of an exemplary and non-limiting embodiment, which is illustrated in the figures. The figure show:

(2) FIG. 1 a schematic illustration of a device according to the invention, and

(3) FIG. 2 a cross-sectional illustration corresponding to the section line A-B of FIG. 1.

(4) In the following figures, unless otherwise stated, the same reference numbers denote the same features. FIG. 1 shows an embodiment of a device according to the invention 1 for transferring heat from a gaseous working medium M2 to a heat-exchanger medium M3 by compressing the gaseous working medium M2. Herein, device 1 comprises a operating line AL, wherein the volume V enclosed by the operating line AL is divided into at least two sections, namely a first AL-V1 and a second section AL-V2. The first section AL-V1 is set up to hold a pressure-transfer medium M1 and the second section AL-V2 to hold and release the gaseous working medium M2. At least one inlet and outlet valve 2 is provided for the absorption and discharge of the gaseous working medium M2, wherein a first volume delimited by the first section AL-V1 is separated from a second volume delimited by the second section AL-V2 by a first separating layer T12 which can be displaced in the operating line AL.

(5) The first separating layer T12 is arranged in such a way that pressure differences between the first AL-V1 and the second section AL-V2 of the operating line AL are equalized by a displacement of the first separating layer T12 in the operating line AL (the displacement is indicated by arrows in FIG. 1 as an example) and a accompanying change in the proportion between the first volume and the second volume is equalized, wherein the working medium M2 can thus be compressed and thus heated.

(6) Furthermore, device 1 includes a heat-exchanger line WL to hold the heat-exchanger medium M3. In this case, the heat-exchanger line WL is coupled to the first section AL-V1 of the operating line AL in order to bring about pressure equalization while the heat-exchanger line WL is connected to the first section AL-V1 of the operating line AL and a second separating layer T13 is provided between these lines (i.e., the operating line AL and the heat-exchanger line WL) to separate the lines from each other.

(7) The second separating layer T13 is designed and arranged in such a way that there is a continuous pressure equalization between the heat-exchanger line WL and the first section AL-V1 of the operating line AL. The second section AL-V2 of the operating line AL comprises a heat-emission section AL-V2 (for a better overview, this is marked only on one side of the x-axis symmetrical structure and provided with reference numbers), which is enclosed on the outside and inside by a two-part heat-absorption section WL of the heat-exchanger line WL while the operating line AL comprises an inner wall AL-IW and an outer wall AL-AW encapsulating the inner wall AL-IW (see also FIG. 2), and, between the inner wall AL-IW and the outer wall AL-AW, a working-medium gap S-M2 is formed to guide the working medium M2. The inner wall AL-IW encloses a channel K, through which a first part of the heat-exchanger line WL is formed in the heat-absorption section WL. In addition, the heat-exchanger line WL in the heat-absorption section WL also comprises a shell wall WL-M enveloping the outer wall AL-AW of the operating line AL, through which a second part of the heat-exchanger line WL is formed and delimited in the heat-absorption section. A heat-exchanger-medium gap S-M3 connected in parallel with channel K is formed between the outer wall AL-AW of the operating line AL and the shell wall WL-M of the heat-exchanger line WL so that a heat-exchanger medium M3 conveyed in the heat-absorption section WL of the heat-exchanger line WL can flow around the operating line AL on the outside via the heat-exchanger-medium gap S-M3 and on the inside via the channel K.

(8) In addition, in FIG. 1 shows a pump 3 by means of which the pressure-transfer medium M1 can be pressurized. If the pressure is increased, the separating layer T12 is moved in the direction of the valves 2, and in the case of closed valves, the working medium M2 is compressed and thus heated. After a predetermined time period and/or compression and heat transfer to the heat-exchanger medium M3, the outlet valve 2 is opened, the pressure on the pressure-transfer medium M1 is lowered so that the separating layer 12 can move downwards again and fresh working medium M2 can flow into the second section AL-V2 via the inlet valve 2, which can subsequently be compressed and heated again by increasing the pressure. In the case of the pump 3 shown in FIG. 1, it is, for example, a hydraulic pump in which hydraulic fluid 6 held in a container 5 is shown.

(9) For example, the heat-exchanger medium M3 can be a liquid medium, in particular, water. In addition, it can be provided that the pressure-transfer medium M1 in the first section AL-V1 of the operating line AL is an oil. Depending on the media used, the first separating layer T12 can be formed directly by the boundary surface formed on the basis of the surface tension of the liquid pressure-transfer medium M1 in relation to the gaseous working medium M2.

(10) Alternatively, the first separating layer T12 can be formed by a first separating means T12 provided for this purpose, which is preferably designed as a spatially displaceable first seal element. Similarly, the second separating layer T13 can be formed by a second separating means provided for this purpose, which is preferably designed as a spatially displaceable second seal element, which is designed as an elastic membrane permanently mounted at its edges or designed to be spatially displaceable in its entirety. The first separating layer T12 and/or the second separating layer T13 can also each be formed by the surface of a separating cylinder, which can be kept displaceable in the operating line AL.

(11) In addition, in FIG. 1 in conjunction with FIG. 2 shows that the heat-exchanger line WL is symmetrically formed around a longitudinal axis x in the area of the heat-absorption section WL. More precisely, the operating line AL in the heat-emission section AL-V2 can be designed as a concentric double pipe, which is formed coaxially to the longitudinal axis x of the heat-exchanger line WL in the area 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 pipe and is delimited by them, wherein the shell wall WL-M of the heat-exchanger line WL encloses the double pipe and the channel K is separated from the inner wall AL-IW of the double pipe (see also FIG. 2). On the inner wall AL-IW, cooling fins projecting into channel K can be provided to improve heat exchange. In FIG. 2, further cooling fins are also shown, which project from the outer wall AL-AW into the heat-exchanger-medium gap S-M3 to improve heat exchange.

(12) Contrary to what is depicted in the figures, the inner wall AL-IW and the outer wall AL-AW can form a multi-toothed star in cross-section, which is, in particular, axially or point-symmetrical, wherein the star formed by the outer wall AL-AW is preferably an enlargement of the star formed by the inner wall AL-IW.

(13) In addition, it is evident in FIG. 1 that the operating line AL in an area of the heat-emission section AL-V2 is designed in such a way that the working-medium gap S-M2 tapers towards at least one inlet and outlet valve 2. This area is marked with the reference S-M2v.

(14) It can also be provided that the operating line AL is distributed to branches connected in parallel, at least within the heat-emission section WL AL-V2. The term connected in parallel means that the medium guided in parallel can mix again after the parallel connection.

(15) In FIG. 1, a heat exchanger 4 is also shown, which can be part of the device 1, wherein the heat-exchanger line WL is connected to the heat exchanger 4 for the emission of heat.

(16) The invention is not limited to the embodiments shown but is defined by the entire scope of protection of the claims. Also, individual aspects of the invention or the embodiments can be held and combined with each other. Any reference numbers in the claims are exemplary and serve only to make the claims easier to read without limiting them.