Reversing valve, heat pump valve unit, heat pump, and building

Abstract

The invention relates to a reversing valve (100) having a valve actuating body (8) which is pivotable about an axis of rotation of an electric drive (14) and has a low-pressure fluid passage (FP), via which a low-pressure fluid inlet opening (46) into the low-pressure fluid passage (FP) is connectable to a low-pressure fluid outlet opening (40, 44) out of the low-pressure fluid passage (FP), and having a driving body (12) for pivoting the valve actuating body (8) about the axis of rotation. The driving body (12) is pivotable relative to the valve actuating body (8) against a first or second stop (30) of the valve actuating body (8), and at least one of at least two pressure equalizing openings (26) in the valve actuating body (8) is exposable and can be used to short-circuit the low-pressure fluid passage (FP) with a high-pressure fluid chamber (6). The invention also relates to a heat pump valve unit, to a heat pump, and to a building.

Description

[0001] 202500328

[0002] 1

[0003] Description

[0004] Reversing valve, heat pump valve unit, heat pump and building

[0005] The present invention relates to a reversing valve, a heat pump valve unit with such a reversing valve, a heat pump with such a heat pump valve unit and a building with such a heat pump.

[0006] Heat pumps are used to heat or cool buildings, for example in the form of a so-called air-to-water heat pump.

[0007] The object of the present invention is to improve such a heat pump.

[0008] This problem is solved by a reversing valve proposed and protected according to claim 1.

[0009] By short-circuiting a high-pressure fluid flow flowing through the high-pressure fluid chamber with a low-pressure fluid flow flowing through the low-pressure fluid passage – via at least one of the proposed pressure equalization openings – a high pressure difference existing between the two fluid flows – on the order of approximately 30 bar – is significantly reduced before the valve actuator is pivoted into a desired end position by the actuator.

[0010] The pressure equalization openings can also be referred to as short-circuit openings, short-circuit passages, or short-circuit fluid channels.

[0011] Due to the high pressure existing in the high-pressure fluid chamber, the valve actuator experiences such a strong contact or pressure against an associated sliding sealing surface of the reversing valve that the valve actuator 202500328

[0012] 2

[0013] with this sliding sealing surface, it interacts fluidically in a sealing manner. This also applies to the time or time period during which the two fluid flows, or the high-pressure fluid flow and the low-pressure fluid flow, are short-circuited.

[0014] And by significantly reducing this pressure, the frictional force that the electric drive has to overcome between the valve actuator and the sliding sealing surface is also significantly reduced.

[0015] Thus, the proposed reversing valve advantageously facilitates and simplifies the electromechanical actuation of the valve actuator. Consequently, a lower actuating force or torque is required from the electric motor to adjust the reversing valve.

[0016] Consequently, cheaper or less powerful electric motors can be used, thus advantageously reducing or minimizing the costs of such an electric drive for such a reversing valve.

[0017] In this arrangement, a high-pressure fluid inlet opening into the high-pressure fluid chamber can be connected to a high-pressure fluid outlet opening from the high-pressure fluid chamber.

[0018] In one embodiment, the high-pressure fluid inlet opening, the low-pressure fluid inlet opening, a first high-pressure or low-pressure fluid outlet opening and a second high-pressure or low-pressure fluid outlet opening are formed in a sliding sealing surface curved around the axis of rotation.

[0019] In addition, in another version the valve actuator is curved around the axis of rotation.

[0020] In addition, in another embodiment the low-pressure fluid passage is curved around the axis of rotation. 202500328

[0021] 3

[0022] In another embodiment, the sliding sealing surface is circularly shaped around the axis of rotation. This sliding sealing surface is enclosed by a circularly closed, circumferential projection of a housing section, which surrounds or encloses the valve actuator on a radial outer side.

[0023] In addition, in another embodiment the valve actuator is curved on a radial inner side around a hollow cylindrical projection section of a housing section, through which the axis of rotation extends and a drive shaft of the electric drive is supported.

[0024] In addition, in a further embodiment, a recess in the form of a groove with a flat sliding sealing surface with at least one first pressure equalization opening and at least one second pressure equalization opening is formed in the valve actuator body, wherein a projecting section of the actuator body with a flat counter-sliding sealing surface engages in the recess up to the stop against the sliding sealing surface.

[0025] In addition, in another version the groove of the valve actuator and the projecting section of the drive body are curved around the axis of rotation.

[0026] In addition, in another version the reversing valve is designed in the form of a 4 / 2-way valve.

[0027] Furthermore, a heat pump valve unit with a reversing valve of the type described above is proposed and placed under protection.

[0028] Such a heat pump valve unit can, in addition to the previously described reversing valve and its electric drive, also accommodate or include a variety of other components, such as at least one service valve, at least one pressure and / or temperature sensor, and / or at least 202500328

[0029] 4

[0030] a pressure switch and the like. All these components are fluidly sealed within an associated housing section of the heat pump valve unit and extend into an associated housing space or fluid channel.

[0031] A service valve like this allows a refrigerant circuit to be filled or emptied. A pressure switch like this allows the power supply to a compressor to be temporarily interrupted and then restored, if necessary.

[0032] And such a pressure and / or temperature sensor can be used to detect a state variable of a conveyed refrigerant, which allows a refrigerant circuit to be monitored.

[0033] At this point, it is clarified that the previously used notation of terms with brackets, such as refrigerant circuit(run), is intended to cover possible alternative designations that each describe the same thing (e.g. refrigerant circuit = refrigerant cycle).

[0034] Furthermore, a heat pump with a reversing valve of the type described above is proposed and placed under protection.

[0035] Furthermore, a building with a heat pump or a reversing valve of the type described above is proposed and placed under protection.

[0036] Furthermore, the use of a heat pump of the type described above for temperature control, i.e., for heating or cooling a building, is proposed and protected. 202500328

[0037] 5

[0038] The invention will now be explained in detail with reference to the figures. Further advantageous embodiments of the invention will become apparent from the dependent claims and the subsequent description of preferred embodiments. These are shown, in part schematically:

[0039] Fig. 1 shows a proposed embodiment of a reversing valve,

[0040] Fig. 2 shows a part of the reversing valve shown in Fig. 1 in a first perspective view,

[0041] Fig. 3 shows a part of the reversing valve shown in Fig. 1 in a second perspective view,

[0042] Fig. 4 shows a part of the reversing valve shown in Fig. 1 in a third perspective view,

[0043] Fig. 5 shows a part of the reversing valve shown in Fig. 1 in a fourth perspective view,

[0044] Fig. 6 shows a part of the reversing valve shown in Fig. 1 in a fifth perspective view,

[0045] Fig. 7 shows a part of the reversing valve shown in Fig. 1 in a sixth perspective view,

[0046] Fig. 8 shows a part of the reversing valve shown in Fig. 1 in a seventh perspective view,

[0047] Fig. 9 shows a part of the reversing valve shown in Fig. 1 in an eighth perspective view,

[0048] Fig. 10 shows a part of the reversing valve shown in Fig. 1 in a ninth perspective view. 202500328

[0049] 6

[0050] Fig. 1 shows a multi-way valve or reversing valve 100 in the form of a so-called

[0051] A 4 / 2-way valve, which as such forms a so-called heat pump valve unit. This heat pump valve unit has a number of other components, which are not shown in Figures 1 to 10.

[0052] The multi-way or reversing valve 100 has a housing 2, 4 forming a high-pressure fluid chamber 6. The housing section 2 can, for example, be formed as a stepped cylindrical, deep-drawn metal part, which is fluidically sealed to a housing section 4 with fluid channels – for example, in the form of a housing plate. The metal construction gives the housing section 2 a certain degree of structural stability. The housing section 4, on the other hand, can, for example, be made of a glass fiber reinforced plastic.

[0053] Within the high-pressure fluid chamber 6, a valve actuator 8, pivotable about a rotational axis R - R of an electric drive 14 and curved in a circumferential direction or pivoting direction about the rotational axis R - R, is arranged with a low-pressure fluid passage FP (visible or shown only in Fig. 2). The low-pressure fluid passage FP is also curved about the rotational axis R - R. The valve actuator 8 functions as a sliding seal, fluid guide, and fluid deflector.

[0054] The valve actuator 8 rests on its end-sealing face Sn with a flat, closed, circumferential end-sealing surface on a sliding sealing surface 11, which as such has a total of four openings, or in which a total of four openings are formed: a fluid drain opening 40, a high-pressure fluid inlet opening 42, a fluid drain opening 44, and a low-pressure fluid inlet opening 46. Depending on the position or orientation or end position of the valve actuator 8, the two fluid drain openings 40 and 44 are, on the one hand, a high-pressure fluid drain opening and, on the other hand, a low-pressure fluid drain opening. This will be further clarified below.

[0055] 7

[0056] The circularly shaped sliding sealing surface 11 is surrounded by a circularly closed circumferential projection section 10. acomprises a section which is integrally formed on housing section 4 and shaped around the axis of rotation R - R. This projecting section 10 a This projecting section 10 extends along the axis of rotation R - R or in a longitudinal direction X - X and closes off or borders the sliding sealing surface 11. a The valve actuator 8 is partially enclosed or encompassed on its radial outer side over an angular range.

[0057] A hollow cylindrical projection section 10j is formed around the axis of rotation R - R and integrally attached to the housing section 4. This projection section 10j supports the drive shaft 18. This projection section 10j is related to the projection section 10 aIt is arranged internally and concentrically and is also located between the individual openings 40, 42, 44, 46. These individual openings 40, 42, 44, 46 are formed in the sliding sealing surface 11 and are arranged or provided to be spaced apart from each other along the sliding sealing surface 11, for example at an angle of 90°.

[0058] A drive element 12 is connected to the valve actuator 8 in the longitudinal or axial direction X - X, over which the valve actuator 8 can pivot. A drive shaft 18 of the electric drive 14 extends through an eye or opening in the drive element 12 into the hollow cylindrical projection section 10j, which supports the drive shaft 18. The drive shaft 18 forms a shaft-hub connection with the drive element 12, approximately in the form of a hexagonal connection.

[0059] The valve actuator 8 is shaped in a curved form around the projecting section 10j, either sectionally or over an angular range, or encompasses it sectionally or over an angular range. 202500328

[0060] 8

[0061] The drive shaft 18 extends into the upper cylindrical section of the housing part or deep-drawn part 2, shown in Fig. 1. In this area, the drive shaft 12—also called the rotor shaft—carries a rotor 16 of the electric drive 14, which is arranged internally to a stator 20 of the electric drive 14. Between the rotor 16 and the stator 20 lies the housing section or deep-drawn part 2, which separates the high-pressure fluid chamber 6 from its surroundings. The drive shaft 18 is supported by a bearing 22 within the housing section or deep-drawn part 2. A dipole magnet is also arranged at the upper free end of the drive shaft 18. This magnet interacts with an associated Hall sensor (not shown) to precisely position the valve actuator 8.

[0062] The valve actuator 8 has a recess in the form of a groove 8N, also curved about the axis of rotation R - R, with a flat sliding sealing surface comprising a first pressure equalization opening 26 and a second pressure equalization opening 28. A projecting section 12v – or a lug 12v – of the actuator 12, also curved about the axis of rotation R - R, engages in this groove 8N with a flat counter-sliding sealing surface up to the stop against the sliding sealing surface of the groove 8N. The two pressure equalization openings 26, 28 are located in the circumferential direction, respectively.

[0063] The pivot direction is arranged at intervals across an angular range.

[0064] The drive element 12 is joined to the valve actuator 8 with play in the circumferential direction and pivoting direction about the axis of rotation R - R, so that the drive element 12 can pivot relative to the valve actuator 8 against a first stop 30 or a second stop 32 of the valve actuator 8, thereby exposing one of two pressure equalization openings 26, 28 in the valve actuator 8 to connect or short-circuit the low-pressure fluid passage FP with the high-pressure fluid chamber 6.

[0065] 9

[0066] Figure 2 shows the valve actuator 8 in a first end position. In this figure 2, the drive element 12 assumes a so-called mid-position, in which both pressure equalization openings 26, 28 are covered or closed. Figure 2 also illustrates one of two possible end positions of the valve actuator 8.

[0067] In the position of the valve actuator 8 - according to Fig. 2 - the high-pressure fluid inlet opening 42 into the high-pressure fluid chamber 6 - via the high-pressure fluid chamber 6 - is fluidically connected to the high-pressure fluid outlet opening 40 from the high-pressure fluid chamber 6, whereas through the low-pressure fluid passage FP the low-pressure fluid inlet opening 46 into the low-pressure fluid passage FP is connected to the low-pressure fluid outlet opening 44 from the low-pressure fluid passage FP.

[0068] In Fig. 3, however, the drive element 12 has moved against, or been struck against, the right stop 30 of the valve actuator 8. In this position, the pressure equalization opening 26 – i.e., the rear of the two pressure equalization openings 26, 28 in the pivoting direction – is exposed. The valve actuator 8 itself has not yet pivoted; it is still in its initial position or in the aforementioned first end position. As a result, a first pressure differential – of, for example, approximately 30 bar – between the high-pressure fluid flow and the low-pressure fluid flow can be reduced by the reversing valve 100 to approximately 20 bar.

[0069] The drive body 12 can remain in this stop position or position until the pressure difference has been reduced to a second pressure difference level.

[0070] The pressure prevailing in the high-pressure fluid chamber 6 can be significantly reduced by the exposed pressure equalization opening 26, thus considerably facilitating the pivoting of the valve actuator 8. The pressure in the high-pressure fluid chamber 6 acts on the valve actuator 8 via its end face Si.

[0071] 10

[0072] presses or compresses it with its end sealing surface Sn - or via its closed circumferential end sealing surface on the end sealing surface Sn - against the sliding sealing surface 11.

[0073] The higher the pressure in the high-pressure fluid chamber 6, the greater the contact pressure that the valve actuator 8 experiences against the sliding sealing surface 11. And the greater the frictional force at the contact point, which the electric drive 14 must overcome.

[0074] The pressure in the high-pressure fluid chamber 6 also acts on the front side of the drive body 12, so that it is pressed or pushed against the valve actuator body 8.

[0075] In Fig. 4, the valve actuator 8 is pivoted slightly compared to Fig. 3 and is shown covering the openings 44, 40 and the opening 46.

[0076] In Fig. 5, the valve actuator 8 is shown in a second end position, in which the high-pressure fluid inlet 42 is connected to the high-pressure fluid outlet 40 from the high-pressure fluid chamber 6 via the high-pressure fluid chamber 6, while the low-pressure fluid inlet 46 is connected to the low-pressure fluid outlet 44 from the low-pressure fluid chamber FP via the low-pressure fluid passage FP. However, the pressure equalization port 26 is still open.

[0077] In Fig. 6, the drive body 12 has moved in the opposite pivoting direction to the central position, in which the two pressure equalization openings 26, 28 are again covered or closed, so that the pressures in the two fluid flows (high-pressure fluid flow FSHD and low-pressure fluid flow FSND) can readjust or return to their previous levels or diverge from each other. 202500328

[0078] 11

[0079] In Figs. 7 to 10, however, the pivoting process from the second end position back to the first end position is illustrated.

[0080] In this process, the drive body 12 is moved - in an analogous manner but in the opposite direction of pivoting - against the left stop 32 of the valve actuator 8 and the pressure equalization opening 28 is exposed to facilitate the pivoting of the valve actuator 8 accordingly.

[0081] And in the second end position - according to Fig. 10 - the drive body 12 is pivoted again into the central position in an analogous manner, in which it covers or closes both pressure equalization openings 26, 28.

[0082] In Figs. 2, 3, 5, 6, 7, 9 and 10, a high-pressure fluid flow FSHD and a low-pressure fluid flow FSHD are indicated by arrows in relation to the respective end position of the valve actuator 8 shown in them.

[0083] If a room in a building is to be temperature-controlled using a heat pump that has such a reversing valve 100, then this room can be heated or cooled.

[0084] In the case of heating, a hot refrigerant flow (or high-pressure fluid flow FSHD) from a compressor must be routed through an internal heat exchanger, through which the heat of the pressurized, hot refrigerant can be transferred to the room as required. In this case, the internal heat exchanger functions as a condenser. This hot refrigerant flow (high-pressure fluid flow FSHD) is routed from the compressor through the high-pressure fluid inlet 42 shown in Fig. 2 into the high-pressure fluid chamber 6 and through the high-pressure fluid outlet 40 out of the high-pressure fluid chamber 6.

[0085] 12

[0086] In this process, a low-pressure refrigerant flow (or low-pressure fluid flow FSND) originating from an external heat exchanger is fed into the low-pressure fluid passage FP via the low-pressure fluid inlet opening 46 and out of the low-pressure fluid passage FP via the low-pressure fluid outlet opening 44. In this case, the external heat exchanger acts as an evaporator.

[0087] Therefore, the end position of the valve actuator 8 shown in Fig. 2 describes a heating mode of the associated heat pump.

[0088] In the case of cooling, however, the hot refrigerant flow (high-pressure fluid flow FSHD) coming from the compressor must be routed through the external heat exchanger so that the heat from the pressurized, hot refrigerant can be released to the building's surroundings as needed. In this case, the external heat exchanger acts as a condenser. This hot refrigerant flow (high-pressure fluid flow FSHD) is routed from the compressor through the high-pressure fluid inlet 42 shown in Fig. 6 into the high-pressure fluid chamber 6 and through the high-pressure fluid outlet 44 out of the high-pressure fluid chamber 6.

[0089] The refrigerant flow (low-pressure fluid flow FSND) coming from the internal heat exchanger and operating at low pressure is guided or conveyed via the low-pressure fluid inlet opening 46 into the low-pressure fluid passage FP and via the low-pressure fluid outlet opening 40 out of the low-pressure fluid passage FP. In this case, the internal heat exchanger functions as an evaporator.

[0090] Therefore, the end position of the valve actuator 8 shown in Fig. 6 describes a cooling mode of the associated heat pump.

[0091] Although the preceding description explains exemplary versions, it should be noted that a large number of variations exist.202500328

[0092] 13

[0093] This is possible. Furthermore, it should be noted that the exemplary embodiments are merely examples and are not intended to restrict the scope of protection, applications, or structure in any way. Rather, the preceding description provides the skilled person with a guideline for implementing at least one exemplary embodiment, whereby various modifications, particularly with regard to the function and arrangement of the described components, can be made without departing from the scope of protection as defined by the claims and these equivalent combinations of features.

Claims

202500328 14 Patent claims 1. Reversing valve (100) with a valve actuator (8) pivotable about a rotation axis (R - R) of an electric actuator (14) with a low-pressure fluid passage (FP) through which a low-pressure fluid inlet opening (46) can be connected to the low-pressure fluid passage (FP) with a low-pressure fluid outlet opening (40, 44) from the low-pressure fluid passage (FP), and a drive element (12) for pivoting the valve actuator (8) about the rotation axis (R - R), wherein the drive element (12) is pivotable relative to the valve actuating element (8) against a first or second stop (30, 32) of the valve actuating element (8) and thereby at least one of at least two pressure equalization openings (26, 28) in the valve actuating element (8) is exposed, through which the low-pressure fluid passage (FP) can be short-circuited with a high-pressure fluid chamber (6).

2. Reversing valve (100) according to claim 1, wherein a high-pressure fluid inlet opening (42) into the high-pressure fluid chamber (6) can be connected to a high-pressure fluid outlet opening (40, 44) from the high-pressure fluid chamber (6).

3. Reversing valve (100) according to claim 2, wherein the high-pressure fluid inlet opening (42), the low-pressure fluid inlet opening (46), a first high-pressure or low-pressure fluid outlet opening (40, 44) and a second high-pressure or low-pressure fluid outlet opening (40, 44) are formed in a sliding sealing surface (11) curved about the axis of rotation (R - R).

4. Reversing valve (100) according to one of claims 1 to 3, wherein the valve actuating element (8) is curved about the axis of rotation R - R.

5. Reversing valve (100) according to one of the preceding claims, wherein the low-pressure fluid passage (FP) is curved about the axis of rotation R - R. 202500328 15 6. Reversing valve (100) according to one of claims 3 to 5, wherein the sliding sealing surface (11) is formed circularly around the axis of rotation (R - R) and is surrounded by a circularly closed circumferential projection section (10). a ) of a housing section (4) which surrounds the valve actuator (8) on a radial outer side.

7. Reversing valve (100) according to one of the preceding claims, wherein the valve actuating element (8) is curved on a radial inner side around a hollow cylindrical projection section (10j) of a housing section (4) through which the axis of rotation (R - R) extends and a drive shaft (18) of the electric drive (14) is supported.

8. Reversing valve (100) according to one of the preceding claims, wherein a recess in the form of a groove (9) with a flat sliding sealing surface with at least one first pressure equalization opening (26) and at least one second pressure equalization opening (28) is formed in the valve actuating body (8), wherein a projecting section (13) of the drive body (12) with a flat counter sliding sealing surface engages in the recess (9) up to the stop against the sliding sealing surface.

9. Reversing valve (100) according to claim 8, wherein the groove (9) of the valve actuating body (8) and the projecting section (13) of the drive body (12) are curved about the axis of rotation (R - R).

10. Reversing valve (100) according to one of the preceding claims, wherein the reversing valve (100) is designed in the form of a 4 / 2-way valve.

11. Heat pump valve unit with a reversing valve (100) according to one of the preceding claims.

12. Heat pump with a reversing valve (100) according to any one of the preceding claims 1 to 10. 202500328 16 13. Building with a heat pump according to claim 12.

14. Use of a heat pump according to claim 12 for temperature control of a building.

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