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

Abstract

The invention relates to a reversing valve, comprising: an electrically actuatable spindle drive (10) within a high-pressure fluid chamber (HDR), having a spindle nut (14) which is joined to a valve actuating body (16) with play and can be adjusted relative to the valve actuating body (16), wherein two fluid channels (K2, K3, K4) of a housing (2a) of the reversing valve can be fluidically connected to one another within the high-pressure fluid chamber (HDR) by means of the valve actuating body (16); the spindle nut (14) can be moved against a first or second stop (AS1, AS2) of the valve actuating body (16), the stop being used to bring the valve actuating body (16) into the respective actuating positions; and the valve actuating body (16) has at least two openings (34, 36) which are spaced apart from one another in an axial stroke direction (X - X) and via each of which the high-pressure fluid chamber (HDR) can be fluidically connected to a low-pressure fluid passage (FP) of the valve actuating body (16). When the valve actuating body (16) is adjusted, the reversing valve brings about a pressure equalization between the high-pressure fluid chamber (HDR) and the fluid passage (FP). The invention also relates to a heat pump valve unit, to a heat pump, and to a building.

Description

[0001] 202500015

[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, among other things, for heating or cooling 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] The proposed reversing valve facilitates electromechanical actuation of the spindle drive or adjustment of the valve actuator. Therefore, a lower actuating force or torque is required from the electric motor.

[0010] It is proposed that at least one spring be arranged between the spindle nut and the valve actuator, which clamps the valve actuator against a counter-sliding sealing surface of the housing, along which the valve actuator with its sliding sealing surface can be adjusted from the first to the second positioning position or vice versa.

[0011] This prevents the valve actuator from lifting off the counter-sliding sealing surface of the housing during a period of pressure equalization.

[0012] A heat pump valve unit with a reversing valve of the type described above is also proposed. 202500015

[0013] 2

[0014] In one embodiment, the heat pump valve unit has:

[0015] a housing with fluid inlets and fluid outlets, wherein the housing has a high-pressure housing section with the high-pressure fluid space, wherein the valve actuator with the high-pressure housing section and the fluid inlets and fluid outlets associated with the high-pressure housing section forms the reversing valve of the type described above;

[0016] wherein the high-pressure housing section is closed off with an associated housing cover, which forms the high-pressure fluid space;

[0017] wherein the housing cover contains at least one component in the form of a pressure sensor, temperature sensor, pressure and temperature sensor,

[0018] Service valve and / or pressure switch fluid-tight, which as such extends into the high-pressure fluid space.

[0019] The proposed heat pump valve unit represents a compact solution or module whose integrated components provide a correspondingly extended range of functions.

[0020] Thus, with at least one sensor in the form of a pressure and / or temperature sensor, a state variable of a conveyed refrigerant can be recorded, which allows a refrigerant circuit to be monitored.

[0021] The service valve allows such a refrigerant circuit to be filled or emptied. And the pressure switch allows the power supply to a compressor connected to the heat pump valve unit to be temporarily interrupted and then restored, if necessary.

[0022] In one embodiment, the fluid inlets and outlets associated with the high-pressure housing section are provided or formed in an associated housing base and opposite the housing cover. 202500015

[0023] 3

[0024] In a further embodiment, the housing also has a low-pressure housing section with a low-pressure fluid chamber, wherein the low-pressure housing section is closed off with an associated housing cover which forms the low-pressure fluid chamber;

[0025] wherein this housing cover also fluid-tightly accommodates at least one component in the form of a pressure sensor, temperature sensor, pressure and temperature sensor and / or service valve, which as such extends into the low-pressure fluid space.

[0026] In one embodiment, a fluid inlet and fluid outlet associated with the low-pressure housing section are provided or formed in an associated housing base and opposite the housing cover.

[0027] The two housing sections can be connected to each other via a jointly formed bridge section. This bridge section can be formed integrally with the two housing sections.

[0028] This bridge section can be arranged and oriented in such a way, at least in sections, that it connects the two housing sections and stiffens them against each other in the sense of a rib or rib section.

[0029] The two housing sections – excluding their respective covers – can each be shaped like a trough or a cuboid. A trough shape means that the inner and outer surfaces of both housing sections are at least partially concave or convex.

[0030] In a further embodiment, the proposed heat pump valve unit also features an electric motor, enclosed within the housing, for actuating the spindle drive.

[0031] 4

[0032] The valve actuator is adjusted purely electrically. No fluid control channels within the housing or high-pressure housing section, nor fluid control lines outside the housing or high-pressure housing section, are required to adjust or move the valve actuator.

[0033] It is proposed that the valve actuator has a flat sliding sealing surface, via which it interacts with a flat counter-sliding sealing surface of the high-pressure housing section in a planar sealing manner and can be adjusted along this counter-sliding sealing surface from the first to the second positioning position or vice versa.

[0034] The actuating force applied by the electric motor must overcome a resistance, or frictional force, which results from the pressure of the valve actuator against a corresponding running surface – or the counter-sealing surface – of the high-pressure housing section. This pressure, in turn, is determined, influenced, or caused by the pressure in the high-pressure fluid chamber and the pressure in the low-pressure fluid passage of the valve actuator.

[0035] A pressure in the high-pressure fluid chamber, reduced by the pressure prevailing in the low-pressure fluid passage, ultimately determines the actual contact pressure of the valve actuator against the running surface of the high-pressure housing section. This is also referred to as the differential pressure exerted on the valve actuator, which results in a normal force that presses the actuator against the running surface of the high-pressure housing section. And depending on the friction conditions between the

[0036] A corresponding frictional force develops between the valve actuator and the running surface, which the electric motor must overcome as a resistance. 202500015

[0037] 5

[0038] A drive spindle of the spindle drive can be formed as part of a rotor shaft of the electric motor or joined to this rotor shaft.

[0039] In one embodiment, the counter-sliding sealing surface is recessed or lowered relative to a surrounding housing base surface of the high-pressure housing section. This creates a groove by which the valve actuator is guided.

[0040] The valve actuator can be shaped, for example, in the form of a trough body or a trough-shaped or trough-like body, or essentially cuboid or cuboid-like, which is placed with its open side or a flat end sealing surface associated with the open side - or the sliding sealing surface - on the flat counter-sliding sealing surface of the high-pressure housing section and can be moved or adjusted along this counter-sliding sealing surface from the first to the second positioning position or vice versa.

[0041] A trough shape is understood to mean that the inner surface and / or the outer surface of the valve actuator (each) are at least partially concave or convex.

[0042] It is proposed that at least the surface forming the low-pressure fluid passage, or the outer surface, of the valve actuator should be shaped concavely, at least in sections. Furthermore, if the surface facing the high-pressure fluid chamber, or the outer surface, of the valve actuator is also shaped convexly, at least in sections, such a trough-like design minimizes the mass of the valve actuator, thus saving weight and costs. From a fluid dynamics perspective, the concave shape of the low-pressure fluid passage also reduces turbulence in the conveyed gaseous or vaporous refrigerant, which in itself represents a flow resistance.

[0043] 6

[0044] Furthermore, a heat pump with a heat pump valve unit of the type described above is proposed.

[0045] Furthermore, a building with a heat pump of the type described above is proposed.

[0046] Furthermore, the use of a heat pump of the type described above for heating or cooling a building is proposed.

[0047] 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, partly schematically:

[0048] Fig. 1 shows a proposed embodiment of a heat pump valve unit in a perspective or spatial representation.

[0049] Fig. 2 shows another proposed embodiment of a heat pump valve unit in a planar sectional view.

[0050] Fig. 3 shows an arrangement of a valve actuator and a spindle nut,

[0051] Fig. 4 shows different states of this arrangement according to Fig. 4.

[0052] Fig. 5 shows the operation of an electric motor, which exhibits the states shown in Fig. 4.

[0053] depicts,

[0054] Fig. 6 shows a pressure equalization curve achieved with the proposed heat pump valve unit,

[0055] Fig. 7 shows a heat pump system with such a proposed heat pump valve unit, 202500015

[0056] 7

[0057] Fig. 8 schematic representation of switching states of connections of the proposed heat pump valve unit,

[0058] Fig. 9 shows another representation of an arrangement of a valve actuator and a spindle nut in a perspective or spatial view,

[0059] Fig. 10 shows the arrangement shown in Fig. 9 in a first top view,

[0060] Fig. 11 shows the arrangement shown in Fig. 9 in a second top view and

[0061] Fig. 12 shows the valve actuator shown in Fig. 9 in a bottom view.

[0062] The heat pump valve unit 100 (see e.g. Fig. 1) has a housing 2 which is divided into a high-pressure housing section 2a and a low-pressure housing section 2b.

[0063] This housing 2 accommodates a large number of components.

[0064] At the right end of this housing 2, an electric motor 4 is flanged via its housing G or its housing flange to a flange 2F of the high-pressure housing section 2a. The high-pressure housing section 2a also accommodates a service valve SV2, a pressure switch PS, and a pressure and temperature sensor PT2.

[0065] The low-pressure housing section 2b, however, accommodates a service valve SV1 and a pressure and temperature sensor PT1.

[0066] The service valves SV1, SV2, the pressure and temperature sensors PT1, PT2, and the pressure switch PS extend through an associated housing cover Di, D2, which fluidically seals the respective components and forms an associated housing space in which the respective components extend or in which these components 202500015

[0067] 8

[0068] protrude into (see Fig. 2). The two housing covers Di , D2 can be welded to the respective associated housing section or - alternatively - screwed on.

[0069] The two service valves SV1 and SV2 allow the refrigerant circuit to be filled or emptied. The pressure switch PS allows the power supply to a compressor connected to the high-pressure housing section 2a to be temporarily interrupted and then restored, if necessary.

[0070] The two housing sections 2a, 2b are each shaped like a trough or trough and are closed off by their respective housing covers Di, D2. The high-pressure housing section 2a forms a high-pressure fluid chamber HDR and the low-pressure housing section 2b a low-pressure fluid chamber NDR (see Fig. 2).

[0071] The housing 2 is described as tub-shaped or tub-like because this shape results in material and cost savings in the forming of these two housing sections 2a, 2b, for example, compared to a cuboid or cuboid-like shape for these two housing sections 2a, 2b. Alternatively, such a cuboid shape could also be used for forming the housing 2 or the two housing sections 2a, 2b.

[0072] To save weight, it is proposed to use as much plastic as possible, or even exclusively, for the construction of the housing 2, 2a, 2b. The same applies at least to the housing G of the electric motor 4.

[0073] The high-pressure housing section 2a has fluid inlets or fluid inlet channels as well as fluid outlets or fluid outlet channels. These channels K1, K2, K3, K4, which are assigned to the high-pressure housing section 2a, are formed or provided in an associated housing base and opposite the housing cover Di. 202500015

[0074] 9

[0075] The channel Ki is always a high-pressure inlet channel that can be connected to or is connected to a compressor K (see Fig. 7).

[0076] Channel K*, on the other hand, is always a low-pressure drain channel that can be connected to or is connected to a collection tank or accumulator A, in which a liquid portion of a conveyed, evaporated refrigerant or liquid refrigerant accumulates (see Fig. 7).

[0077] Depending on the first or second position of a valve actuator 16 within the high-pressure fluid chamber HDR, one of the two channels K2, K3 is connected to the high-pressure fluid chamber HDR and the other channel is connected via a low-pressure fluid passage FP of the valve actuator 16 to the channel K4 or low-pressure drain channel.

[0078] In Fig. 2, channel K2 functions as a high-pressure outlet channel and is connected to an internal heat exchanger (not shown), to which a compressed refrigerant is supplied. Channel K3, on the other hand, functions as a low-pressure inlet channel in Fig. 2 and is connected to an external heat exchanger (not shown), from which evaporated refrigerant is supplied to channel K3.

[0079] The positioning position of the valve actuator 16 shown in Fig. 2 can be defined as the first of two positioning positions in which the fluid passage FP connects the channel K3 with the channel K4.

[0080] In the second position - not shown - the fluid passage FP connects channel K2 with channel K4, in which channel K2 functions as a low-pressure inlet channel, whereas channel K3 functions as a high-pressure outlet channel.

[0081] The outer heat exchanger (not shown) represents a thermal connection or interface to an environment, whereas the inner heat exchanger (not shown) represents a thermal connection or interface to 202500015

[0082] 10

[0083] at least one room which, as such, can be heated by means of a heat pump 200 (see Fig. 7) either (external heat exchanger)

[0084]

[0085] Acting as an evaporator; internal heat exchanger

[0086]

[0087] (acting as a condenser) or to cool (external heat exchanger)

[0088]

[0089] acting as a condenser; internal heat exchanger

[0090]

[0091] (acting as an evaporator).

[0092] The low-pressure housing section 2b has a fluid inlet or fluid inlet channel Ks and a fluid outlet or fluid outlet channel Ke. Channel Ks is connectable to or connected with the collection tank or accumulator A (see Fig. 7), from which evaporated refrigerant is supplied to channel Ks, whereas channel Ke is directly or indirectly connected to the compressor K via a separator S (see Fig. 7).

[0093] These two channels Ks, Ke are formed or provided in an associated housing base of the low-pressure housing section 2b and opposite the housing cover Di.

[0094] Each of the channels Ki , K2, K3, K4, Ks, Ke shown in Fig. 2 has an associated fluid or connection hose or fluid line in the form of a hose or connection hose Ai, A2, A3, A4, As, Ae that can be connected or is connected.

[0095] The two housing sections 2a, 2b are connected to each other via a jointly formed web section 2st, which extends both into and out of the image plane in Fig. 2. This web section 2st can lead into or extend into a jointly formed rib section between the two housing sections 2a, 2b (not shown in Fig. 2), which also connects the two housing sections 2a, 2b and stiffens them against each other due to its orientation parallel to the image plane. Alternatively, this rib section can be omitted to create an air gap LSp between the two housing sections 2a, 2b.

[0096] 11

[0097] The valve actuator 16 forms a so-called reversing valve RV in the form of a 4 / 2-way valve (see Fig. 2 and Fig. 7), which can be operated in a first or second position and via which a cold central circuit can be reversed or operated in a first or second mode (see Fig. 7).

[0098] The valve actuator 16 is shaped as a body functioning as a sliding sealing body, fluid guide and fluid deflection body with a low-pressure fluid passage FP that connects the channel K4 (or low-pressure inlet channel) either with the channel K3 or the channel K2, depending on the actuating position or position of the valve actuator 16.

[0099] The valve actuator 16 has a flat sliding sealing surface 20 on its open side, via which it can be adjusted from the first to the second position or vice versa along a flat counter-sliding sealing surface 22 of the housing section 2a - thereby sealing in a flat manner with the counter-sliding sealing surface 22.

[0100] The counter-sliding sealing surface 22 can be slightly lowered, recessed, offset, or deepened relative to a surrounding base surface, housing base surface, or tray base.

[0101] This counter-sliding sealing surface 22 thus forms a groove or shallow groove with the surrounding wall, through which the valve actuator 16 is guided. This proposed recess of the counter-sliding sealing surface 22 can be produced, for example, by machining. A suitable surface finish can be achieved on the counter-sliding sealing surface 22 to ensure a sufficiently effective seal in conjunction with the sliding sealing surface 20 of the valve actuator 16. The sliding sealing surface 20 also has a suitable surface finish.

[0102] 12

[0103] Furthermore, at least one guide rail 24 can be formed in this base surface or in this basin base and project from it. This guide rail 24 extends lengthwise or along the counter-sliding sealing surface 22 and thus flanks the valve actuator 16 on one side, supporting its axial stroke or movement in the X-X direction. Alternatively, two such guide rails 24 spaced apart from each other can be formed or provided in the base surface, thus supporting the valve actuator 16 on both sides. This completely prevents any deviation of the valve actuator 16 from its intended axial stroke in the X-X direction.

[0104] In addition to or as an alternative to such a guide rail 24 or such guide rails 24, the said groove with the counter-sliding sealing surface 22 could also be formed deeper.

[0105] The axial stroke or axial movement of the valve actuator 16 in the X - X direction is effected by a spindle drive 10 in the high-pressure fluid chamber HDR, which converts a rotary movement of the electric motor 4 into this axial movement of the

[0106] converts valve actuator 16.

[0107] A spindle nut 14 of the spindle drive 10 is partially inserted into the valve actuator 16, i.e., positively connected to it. The valve actuator 16 has a corresponding shape with a kind of pocket or receptacle 18 in its outer surface (see Fig. 3), into which the spindle nut 14 is inserted with play, i.e., with clearance in the X-X direction or axial stroke direction relative to a first and second stop ASi, AS2 of the valve actuator 16 (see distances 30, 32). This spindle nut 14, which is movable along a spindle or drive spindle 12 of the spindle drive 10, moves the valve actuator 16 accordingly and thereby causes its axial stroke.

[0108] The valve actuator 16 has two openings or through-openings or channels 34,202500015 spaced apart from each other in one of the axial stroke directions X - X.

[0109] 13

[0110] 36, via which the high-pressure fluid space HDR can be fluidically connected to the low-pressure fluid passage FP.

[0111] These two openings or channels 34, 36 serve the purpose of pressure equalization between the high-pressure fluid chamber HDR and the low-pressure fluid passage FP, even before the valve actuator 16 is moved by the spindle nut 14 in one of the two axial stroke directions X - X, after the spindle nut 14 has traveled a distance 30 or 32 from the valve actuator 16. This is because, until the respective stop ASi, AS2 is reached, the rearmost of the two openings 34, 36 in the respective axial stroke direction is exposed by the spindle nut 14, and consequently the high-pressure fluid chamber HDR is fluidically connected to the fluid passage FP. This is intended to simplify adjustment of the valve actuator 16.

[0112] The representation or embodiment according to Fig. 3 is schematic. In this embodiment, the lower part or section of the spindle nut 14, which is movable and can be stopped against the respective stops AS1, AS2, is wider than the upper part or section of the spindle nut 14, which has an internal thread (not shown) that interacts with an external thread of the drive spindle 12. This lower part or section of the spindle nut 14 is encompassed or enclosed by the pocket or receptacle 18 both vertically Y-Y and axially X-X. Two sections of the actuating element 16 extend axially and in the X-X direction such that they partially overlap this lower part or section of the spindle nut 14 and consequently partially enclose or enclose it axially and in the X-X direction.

[0113] Fig. 4 illustrates this proposed pressure equalization mechanism schematically and qualitatively. Fig. 4 shows an adjustment of the

[0114] Valve actuator 16 from the second to the first position. 202500015

[0115] 14

[0116] The illustration on the far right in Fig. 4 shows the first position of the valve actuator 16. And the illustration on the far left in Fig. 4, on the other hand, shows the second position of the valve actuator 16.

[0117] In these first and second positions, the two openings or channels 34, 36 are closed and the spindle nut 14 has the corresponding distances 30, 32 relative to the two stops AS-i, AS2 (see also Fig. 3).

[0118] When the valve actuator 16 is moved from the second to the first position (see the sequence of figures in Fig. 4 from left to right), the spindle nut 14, in conjunction with the drive spindle 12, is initially moved against the right stop AS2. Until the right stop AS2 is reached, the opening 34, i.e., the rear of the two openings in the axial stroke direction X - X, is exposed. This allows compressed refrigerant to flow from the high-pressure fluid chamber HDR into the fluid passage FP. The pressure in the high-pressure fluid chamber is reduced, and the pressure in the fluid passage is increased. The two pressures approach each other. Fig. 6 qualitatively illustrates such pressure equalization.

[0119] The two distances 30, 32 of the valve actuator 16 to the respective stops AS1, AS2 can be designed such that pressure equalization via the respective openings 34, 36 occurs completely until the respective stops AS1, AS2 are reached. Otherwise, the rotary movement of the drive spindle 12 is briefly interrupted to bring about or achieve complete pressure equalization.

[0120] In the second illustration from the left – in Fig. 4 – this stop AS2 has been reached. Pressure equalization via opening 34 occurs accordingly or can be established. The valve actuator 16 is still stationary or in one of its second actuating positions until this point.

[0121] 15

[0122] In the third illustration from the left – in Fig. 4 – the valve actuator 16 is moved into its first position. However, the left opening 34 is still exposed. Therefore, the spindle nut 14 is now moved in the opposite direction to a central position, which it also holds in the second position (see illustration on the far left).

[0123] Only after reaching this central position (or mid-position), in which the two openings 34, 36 are closed or covered by the spindle nut 14, can the respective pressures, i.e., the pressure in the high-pressure fluid chamber HDR on the one hand and the pressure in the fluid passage FP on the other, readjust accordingly. That is, the common pressure level achieved (according to Fig. 6) is dissolved and the two pressures diverge.

[0124] Fig. 5 qualitatively illustrates the operation of the electric motor 4 to achieve or effect a change of position, such as the one described in Fig. 4.

[0125] Based on Figs. 3 and 4, starting from the second position of the valve actuator 16, the electric motor 4 or its drive shaft 6 (and consequently also the drive spindle 12) is initially rotated clockwise CW for as long as necessary.

[0126] (CW = Clockwise) is operated until the spindle nut 14 reaches the stop AS2 at time ti. At this time ti, the opening or channel 34 is exposed. If necessary, a time interval is then waited until time t2 so that the previously described pressure equalization can occur accordingly or completely.

[0127] From time t2 the valve actuator 16 is driven by the spindle nut 14, whereby the valve actuator 16 reaches its first position at time ts.

[0128] After a short switching period of the electric motor 4, during which no drive is provided by the electric motor 4 until time t4, the drive shaft 6202500015

[0129] 16

[0130] (and consequently also the drive spindle 12) now operates in the opposite direction of rotation CCW (CCW = Counter Clockwise) until time ts, when the spindle nut 14 reaches its central position again, in which the two openings or channels 34, 36 are once again closed or covered by the spindle nut 14. The aforementioned pressure equalization is thereby resolved or reversed.

[0131] The drive spindle 12 can be formed as part of a rotor shaft 6 or joined to such a rotor shaft 6.

[0132] This drive shaft 6 extends from the high-pressure fluid chamber HDR to the electric motor 4, where it carries the motor's rotor. The rotor is located inside a stator and within a containment shell that separates the wet chamber of the electric motor 4 from the dry chamber. The electric motor 4 can be contacted and controlled via the connector socket StB.

[0133] By means of a so-called dipole magnet at one end of the drive shaft 6, which interacts with an associated Hall sensor, the valve actuator 16 can be precisely positioned by counting the revolutions of the drive shaft 6. In conjunction with a given gear ratio of the spindle drive 10, an axial stroke X - X of the valve actuator 16 can be precisely set. With a gear ratio of, for example, 1 mm / revolution, thirty revolutions result in a total stroke of 30 mm. The drive shaft 6 is supported within the drive unit or the electric motor 4 by a fixed bearing on one side and a floating bearing on the other.

[0134] The heat pump 200 shown schematically in Fig. 7 - which can also be referred to as a heat pump system - has a heat pump valve unit 100 of the type described above.

[0135] All previously introduced or described components are shown. 202500015

[0136] 17

[0137] The rectangle shown with dashed lines represents the system boundary of the heat pump valve unit 100 and its housing 2 with the various components accommodated by the housing 2 and the channels Ki , K2, K3, K4, K5, K6.

[0138] The collection tank or accumulator A, the separator S and the compressor K, all of which are located outside this system boundary, are connected to the associated channels of the housing 2 via assigned, separate refrigerant lines.

[0139] Outside this system boundary lie the aforementioned heat exchangers – not shown – which must be imagined. The inner heat exchanger should be visualized as connected to channel K2, while the outer heat exchanger should be visualized as connected to channel K3.

[0140] The heat pump 200 is used to heat a room in a so-called...

[0141] The system operates in heating mode, in which the reversing valve RV assumes a first position (corresponding to the first position of the valve actuator 16). In this mode, a refrigerant coming from the compressor K – and under high pressure – is routed through channels K1 and K2 and the internal heat exchanger. Simultaneously, an evaporated refrigerant coming from the external heat exchanger is routed through channels K3 and K4.

[0142] For cooling the room, the heat pump 200 is operated in a so-called cooling mode, in which the reversing valve RV assumes a second position (corresponding to the second position of the valve actuator 16). In this mode, the refrigerant coming from the compressor K – and under high pressure – is routed through channels K1 and K3 and the external heat exchanger. The evaporated refrigerant coming from the internal heat exchanger is routed through channels K2 and K4.

[0143] 18

[0144] Fig. 8 describes, on the one hand – in the left half – a first state of the heat pump valve unit 100, in which – by the position of the reversing valve RV – the two connections or channels Ki and K2 are connected to each other, and the two connections or channels K3 and K4 are connected to each other. The valve actuator 16 assumes the aforementioned first position.

[0145] Position set. This switching state therefore describes the heating mode of the heat pump 200.

[0146] Fig. 8, on the other hand, describes – in the right half – a state of the heat pump valve unit 100 in which – by the position of the reversing valve RV – the two connections or channels K1 and K3 are connected on the one hand, and the two connections or channels K2 and K* are connected on the other. In this state, the valve actuator 16 assumes the aforementioned second position.

[0147] Position set. This switching state therefore describes the cooling mode of the heat pump 200.

[0148] The proposed heat pump valve unit represents a compact solution or module whose integrated components provide a correspondingly extended range of functions.

[0149] Fig. 9 shows an embodiment of an arrangement of the valve actuator 16 and the spindle nut 14, which is abutted along the counter-sliding sealing surface 22 of the valve actuator 16 against the stop AS2 of the valve actuator 16. In this position of the spindle nut 14, the opening or through-opening or channel 34 is exposed.

[0150] In Fig. 10, however, the spindle nut 14 is in its central position, in which the spindle nut 14 is spaced apart from the stops AS1, AS2 and in which both openings 34, 36 are closed or covered by the spindle nut 14.

[0151] 19

[0152] In Fig. 11, however, the spindle nut 14 is against the ASi of the

[0153] Valve actuator 16 is struck and the opening 36 is exposed or open or exposed.

[0154] Fig. 12 shows the valve actuator 16 viewed from below. Visible are the fluid passage FP and the two openings 34 and 36 of the valve actuator 16.

[0155] 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).

[0156] Although the preceding description explains exemplary embodiments, it should be noted that a multitude of variations are possible. Furthermore, it should be emphasized 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

202500015 20 Patent claims 1. Reversing valve, comprising: a housing (2a) with fluid inlets and fluid outlets (Ki, K2, K3, K4) and a high-pressure fluid chamber (HDR); a valve actuator (16) adjustable within the high-pressure fluid space (HDR) - in an axial stroke (X - X) to a first or second position in the form of a body functioning as a sliding sealing body, fluid guide and fluid deflection body with a low-pressure fluid passage (FP); wherein the low-pressure fluid passage (FP) in these two positioning positions connects a low-pressure fluid inlet (K2, K3) of the housing (2a) with a low-pressure fluid outlet (K4) of the housing (2a); and an electrically actuated spindle drive (10) - in the high-pressure fluid chamber (HDR) - with a spindle nut (14) which is joined with the valve actuator (16) with clearance and is adjustable relative to the valve actuator (16); wherein the spindle nut (14) can be moved against a first or second stop (AS1, AS2) of the valve actuator (16), and the valve actuator (16) can be moved into the respective positioning positions; wherein the valve actuator (16) has at least two openings (34, 36) spaced apart from each other in an axial stroke direction (X - X), through which the high pressure fluid space (HDR) can be fluidically connected to the low pressure fluid passage (FP); wherein these two openings (34, 36) are closed by the spindle nut (14) in the first and second positioning positions, wherein in these two positioning positions the spindle nut (14) is spaced away from the two stops (AS1, AS2); wherein until the respective stop (AS1, AS2) is reached, the rear of the two openings (34, 36) in the respective axial stroke direction can be exposed by the spindle nut (14) - for the purpose of pressure equalization between the high-pressure fluid chamber (HDR) and the low-pressure fluid passage (FP).

2. Reversing valve according to claim 1, wherein at least one spring is arranged between the spindle nut (14) and the valve actuator (16), which 21 Valve actuator (16) is clamped against a counter sliding sealing surface (22) of the housing (2), along which the valve actuator (16) with its sliding sealing surface (20) can be adjusted from the first to the second position or vice versa.

3. Heat pump valve unit (100) with a reversing valve according to claim 1 or 2.

4. Heat pump valve unit (100) according to claim 3, comprising: a housing (2) with fluid inlets and fluid outlets (Ki, K2, K3, K4, Ks, Ke), wherein the housing (2) includes a high-pressure housing section (2a) with the features a high-pressure fluid space (HDR), wherein the valve actuator (16) together with the high-pressure housing section (2a) and the fluid inlets and fluid outlets (Ki, K2, K3, K4) associated with the high-pressure housing section (2a) forms the reversing valve (RV) according to the preceding claims 1 or 2; wherein the high-pressure housing section (2a) is closed off with an associated housing cover (D2), which forms the high-pressure fluid space (HDR); wherein the housing cover (D2) fluid-tightly accommodates at least one component in the form of a pressure sensor, temperature sensor, pressure and temperature sensor (PT2), service valve (SV2) and / or pressure switch (PS), which as such extends into the high-pressure fluid space (HDR).

5. Heat pump valve unit (100) according to claim 4, wherein the fluid inlets and fluid outlets (K1 , K2, K3, K4) associated with the high pressure housing section (2a) are formed in an associated housing base and opposite the housing cover (Di).

6. Heat pump valve unit (100) according to claim 4 or 5, wherein the housing (2) further comprises a low-pressure housing section (2b) with a low-pressure fluid chamber (NDR), wherein the low-pressure housing section (2b) is closed with an associated housing cover (Di) which forms the low-pressure fluid chamber (NDR); 202500015 22 wherein the housing cover (Di) fluid-tightly accommodates at least one component in the form of a pressure sensor, temperature sensor, pressure and temperature sensor (PTi) and / or service valve (SVi), which as such extends into the low-pressure fluid space (NDR).

7. Heat pump valve unit (100) according to claim 6, wherein a fluid inlet and fluid outlet (Ks, Ke) associated with the low-pressure housing section (2b) are formed in an associated housing base and opposite the housing cover (Di).

8. Heat pump valve unit (100) according to claim 6 or 7, wherein these two housing sections (2a, 2b) are connected to each other via a jointly formed web section (2st).

9. Heat pump valve unit (100) according to claim 8, wherein this web section (2st, 8) is at least partially arranged and oriented such that it connects the two housing sections (2a, 2b) to each other and stiffens them in the sense of a rib.

10. Heat pump valve unit (100) according to one of claims 6 to 9, wherein the two housing sections (2a, 2b) are each shaped in a trough or cuboid shape.

11. Heat pump valve unit (100) according to any one of the preceding claims 3 to 10, further comprising: an electric motor (4) received through the housing (2) for actuating the spindle drive (14).

12. Heat pump valve unit (100) according to one of the preceding claims 3 to 11, wherein the valve actuator (16) has a planar sliding sealing surface (20) via which it interacts with a planar counter-sliding sealing surface (22) of the high-pressure housing section (2a) in a planar sealing manner and thereby 202500015 23 along this counter-sliding sealing surface (22) is adjustable from the first to the second position or vice versa.

13. Heat pump valve unit (100) according to any one of the preceding claims 3 to 12, wherein a drive spindle (12) of the spindle drive (10) is formed as part of a rotor shaft (6) of an electric motor (4) or joined to the rotor shaft (6).

14. Heat pump valve unit (100) according to claim 12 or 13, wherein the counter sliding sealing surface (22) is recessed relative to a housing bottom surface of the high pressure housing section (2a) surrounding it.

15. Heat pump valve unit (100) according to any one of the preceding claims 3 to 14, wherein the valve actuator (16) is shaped in a trough or cuboid shape.

16. Heat pump (200) with a heat pump valve unit (100) according to any one of the preceding claims 3 to 15.

17. Building with a heat pump according to claim 16.

18. Use of a heat pump according to claim 16 for heating or cooling a building.

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