Four-way reversing valve for high-capacity reversible heat pump compressors

Abstract

The invention relates to a four-way reversing valve for high-capacity reversible heat pump compressors. The valve comprises a housing having four ports, namely a discharge port, a suction port, an evaporator port and a condenser port. The four-way reversing valve further comprises a conical rotor rotatably arranged inside the housing for changing the flow path between the four ports, wherein the large diameter face of the rotor comprises two separate openings, wherein a first opening fluidly connects the large diameter face to the small diameter face of the rotor via a first fluid conduit and a second opening fluidly connects the large diameter face to a radially outer portion of the rotor via a second fluid conduit. The invention also relates to a kit comprising two or more four-way reversing valves.

Description

[0001] This invention relates to a four-way reversing valve for a high-capacity reversible heat pump compressor. The valve includes a housing having four ports: a discharge port, a suction port, an evaporator port, and a condenser port. The four-way reversing valve further includes a conical rotor rotatably disposed within the housing to alter the flow path between the four ports. The rotor's large-diameter face includes two separate openings. A first opening fluidly connects the large-diameter face to the rotor's small-diameter face via a first fluid conduit, and a second opening fluidly connects the large-diameter face to the rotor's radially outer portion via a second fluid conduit. The invention also relates to an assembly comprising two or more four-way reversing valves.

[0002] Four-way reversing valves (4WRVs) are known to be used in reversible heat pumps. The known architecture typically uses differential pressure as the energy source for operating the valve, a small pilot-operated solenoid valve to actuate the valve's piston, and the piston to drive a slider mechanism to change the valve's position.

[0003] Most 4WRVs are used in combination with scroll compressors (in which trace amounts of oil are present in the exhaust gas) in small variable refrigerant flow (VRF) heat pump systems, and use, for example, R410A as the refrigerant.

[0004] The alternative 4WRV can be used with an oil-free compressor (where there is no oil and the valve mechanism should remain operational without any oil).

[0005] The fluid flowing through a valve operated by a reversible heat pump can vary significantly in terms of its density, volumetric velocity, and direction. One problem arising from these variations is that the valve cannot operate effectively under all possible flow conditions.

[0006] Prior art document WO 2021 / 037970A1 discloses a rotatable four-way directional valve, which is part of a common unit used in refrigerant gas handling systems. This common unit includes an accumulator, a check valve, and the directional valve. The check valve and the directional valve are arranged together in a first region, and the accumulator is arranged in a second region. The directional valve is connected to an actuator that rotates the directional valve to control the flow of refrigerant through the valve.

[0007] The object of this invention is to provide an improved four-way directional valve that overcomes this problem. This object is achieved by a combination of the four-way directional valve according to claim 1 and the corresponding four-way directional valve according to claim 19. Preferred embodiments are the subject of the dependent claims.

[0008] According to claim 1, a four-way reversing valve for a high-capacity reversible heat pump compressor is provided. The valve comprises: a housing having four ports, namely, a discharge port, a suction port, an evaporator port, and a condenser port; and a conical rotor rotatably disposed within the housing to change the flow path between the four ports, wherein a large-diameter face of the rotor includes two separate openings, wherein a first opening fluidly connects the large-diameter face to a small-diameter face of the rotor via a first fluid conduit, and a second opening fluidly connects the large-diameter face to a radially outer portion of the rotor via a second fluid conduit. According to the invention, the circular portion of the large-diameter face is exclusively composed of the two separate openings and at least a portion of the wall separating the openings, and the first and second openings are defined by at least one circular arc and one or more straight boundaries.

[0009] The two separate openings can be separated only by a wall and can represent most or the largest portion of a large-diameter surface. Most of the large-diameter surface, and particularly the central portion, can be occupied by these two separate openings. This yields a rotor with the maximum possible openings for a given size, thus providing minimum flow resistance or maximum Kv flow coefficient through said openings. Rotating the rotor 180° allows the two separate openings to be alternately connected to two different ports. The term "surface" is understood broadly and does not refer to a uniform solid portion of the rotor. Rather, it refers to the outer portion of the rotor, which can be planar and / or may include one or more openings.

[0010] In a preferred embodiment of the invention, the first opening and the second opening have the same size and shape, and / or the first opening and the second opening have a semi-circular shape. The exact shape of the opening can be selected to optimize the flow through the opening and the rotor.

[0011] In another preferred embodiment of the invention, the partition wall passes through the center of the large-diameter surface, and / or the circular portion is arranged concentrically with the large-diameter surface, and / or the radius of the circular portion is at least 50%, 66%, or 75% of the radius of the large-diameter surface, particularly the outer radius of the large-diameter surface.

[0012] The center of the large-diameter surface can be the rotation center of the rotor. Since the wall can pass through the rotation center of the rotor, the wall or a portion thereof can be used to rotatably connect the rotor to the valve housing. Concentrically positioning the circular portion relative to the large-diameter surface allows for maximizing the cross-sectional area of ​​the openings provided within the circular portion. The radius of the circular portion can be maximized such that the cross-sectional area of ​​the openings is correspondingly maximized. The circular portion can be defined such that it comprises only the opening or portions of the opening and the wall or portions of the wall dividing the opening. The circular portion itself is not a component, but defines the area of ​​the large-diameter surface in which only the openings and walls exist.

[0013] In another preferred embodiment of the invention, the partition wall extends along the entire length of the rotor and separates the first fluid conduit from the second fluid conduit, and / or the partition wall has a straight cross section near the large diameter surface and / or a curved cross section near the small diameter surface.

[0014] The term "fluid conduit" can be understood broadly and can refer to long or short channels or openings through which fluid can flow during valve operation. The cross-section or shape of the wall can gradually change between a large-diameter surface and a small-diameter surface.

[0015] In another preferred embodiment of the invention, the rotor is supported against the housing by means of a pin disposed at the center of the wall, wherein the pin is preferably surrounded by a sliding ring and / or the size of the rotor is determined to balance the pressure generated at the first fluid conduit and the second fluid conduit.

[0016] Specifically, the surface area pointing towards or viewed from the rotor's axial direction can be selected such that the different pressures acting inside and outside the rotor do not generate a resultant force acting on the rotor. Since no resultant force acts on the rotor, the rotor seal can withstand constant or near-constant stress, independent of the pressure difference present at the rotor. Therefore, leakage of the seal is unlikely. Although the rotor may not experience a resultant force, torque may still be applied to the rotor due to the pressure gradient.

[0017] In another preferred embodiment of the invention, the radially outer portion of the large-diameter surface or the small-diameter surface includes a gear, and / or the large-diameter surface includes a chamfer at at least some of its inner edges.

[0018] Gears can be positioned on the outer circumference of the corresponding section. Gears can be used to rotate the rotor by means of actuators. Chamfers can be placed on the walls at large-diameter surfaces. Chamfers can facilitate rotor rotation, especially since the walls may have to move over some sealing components as the rotor rotates.

[0019] In a particularly preferred embodiment of the invention, the gear is made of a different material than the rest of the rotor. While the rest of the rotor may be made of aluminum or an aluminum alloy, the gear may be made of some steel or other alloy. The gear and the rest of the rotor may be connected to each other, for example, by screws. The screws may be screwed onto the rotor in a direction perpendicular to the large diameter face of the rotor (i.e., the axial direction of the rotor).

[0020] In another preferred embodiment of the invention, a first seal, particularly a V-shaped lip seal, is disposed at or near the small diameter surface, and / or an axial sliding ring pressed against the O-ring is disposed at or near the large diameter surface.

[0021] The first seal may contact the rotor or the outer circumference of its small-diameter surface. The axial sliding ring may contact the axial side of the rotor, that is, one side or part of the rotor, which is perpendicular to the axial direction of the rotor.

[0022] In another preferred embodiment of the invention, a spring and / or bearing is disposed at or near a small diameter surface, wherein the spring is configured to apply force to the rotor in the axial direction of the rotor.

[0023] The spring can apply force to the rotor via the bearing. These two components can be in close contact with each other. The force applied to the rotor by the spring can press the rotor against some sealing components located at or near the large diameter surface of the rotor.

[0024] In another preferred embodiment of the invention, the radially outer portion of the large-diameter surface or the small-diameter surface comprises a permanent magnet and / or a ferromagnetic material.

[0025] The magnetic component can be used in conjunction with a sensor to determine the angular position of the rotor relative to the rest of the valve.

[0026] In an example of a particularly preferred embodiment of the invention, sensors, particularly reed sensors, Hall sensors, and / or inductive sensors, are configured to interact with a permanent magnet.

[0027] The sensor can be installed together with the rest of the valve and / or can be permanently and / or integrally installed with the valve.

[0028] In a preferred embodiment of the invention, a motor, particularly a DC geared motor, is connected to the housing via gears for rotating the rotor. The motor may be at least partially located inside the housing or within a recess of the housing. The motor provides the driving force required to change the position of the valve (i.e., the rotational position of the rotor). The housing may be provided with an opening for connecting the motor output shaft to the rotor.

[0029] In a particularly preferred embodiment of the invention, the sensor is positioned close to the motor, such that it is included within the motor housing. The motor housing may be attached to the valve housing and may be a separate component from the valve housing. Since the sensor can be integrated into the motor housing, valve assembly is simplified. In particular, when the motor housing is attached to the valve housing, both the motor and the sensor can be assembled simultaneously.

[0030] In a preferred embodiment of the invention, the housing includes an inlet section and an outlet section, wherein the inlet section and the outlet section may be connected to each other via a first flange and / or may be connected to each other in different rotational positions relative to each other, and / or the housing is made of aluminum or an aluminum alloy.

[0031] The two mentioned sections of the housing allow the housing, and particularly the ports of the housing, to be oriented in different orientations. Therefore, the valve can be easily adapted to different geometries of the heat pump architecture.

[0032] In a particularly preferred embodiment of the invention, the large-diameter surface of the rotor is at least partially disposed between the inlet section and the outlet section. The dimensions of the inlet and outlet sections can be determined such that the rotor can be inserted between the two sections without them being connected to each other. A gap or groove can be provided between the inlet and outlet sections to accommodate at least a portion of the large-diameter surface of the rotor when the two sections are connected to each other. The gap or groove between the two sections can accommodate bearings and / or other components required to provide a rotatable connection between the rotor and the housing.

[0033] In another particularly preferred embodiment of the invention, the remainder of the rotor is disposed within the inlet section. The remainder of the rotor includes the portion of the rotor excluding the large-diameter surface and / or may include additional structures for rotatably connecting the rotor to the housing.

[0034] In a preferred embodiment of the invention, the housing includes a valve section, particularly a ball valve section, which is connected to the inlet section via a second flange. The presence of the valve section does not change the number of ports provided in the housing. The suction port may be located at the inlet section, or, if the valve section is present, at the valve section. The valve section allows for fluid disconnection of the valve from the compressor, enabling maintenance of the compressor.

[0035] In a preferred embodiment of the invention, the discharge port and / or evaporator port are arranged at 90° ± 20°, particularly ± 10°, relative to the suction port. The suction port may be arranged along the axial direction of the valve and lead directly into the inlet port of the compressor connected to the valve. The axial direction of the valve may be parallel to the axis of rotation of the rotor.

[0036] The present invention also relates to a assembly comprising two or more of the four-way directional valves currently described. The valves are fluidly connected via at least one, and particularly exactly three or four, manifolds. The ports of the valves can be arranged such that two or more valves can be fluidly connected to each other, to a compressor, and / or to some heat exchanger architecture supplied by the compressor for heat transfer. Connecting multiple valves in this manner allows for the expansion of the performance of the valve assembly for heat exchanger architectures of different capacities. The capacity of the combined valve can be increased simply by adding the required number of identical valves to match a given heat exchanger architecture.

[0037] In a preferred embodiment of the invention, at least two identical manifolds are provided. Since the valve ports can be designed identically to each other, the same manifolds can be used to connect the various ports of the valves. This further simplifies the design of assemblies combining multiple valves as described herein.

[0038] Further advantages and details of the invention are described with reference to the accompanying drawings. In the drawings:

[0039] Figure 1 A general overview of the valve and compressor components of a reversible heat pump;

[0040] Figure 2a Longitudinal view of the valve;

[0041] Figure 2b : Cross-sectional view of the valve;

[0042] Figure 2c : Detailed view of the connection between the valve rotor and the motor;

[0043] Figure 3a Perspective view of the rotor;

[0044] Figure 3b : Longitudinal view of the rotor;

[0045] Figure 3c Plan view of the rotor

[0046] Figure 4a , Figure 4b Longitudinal views of valves in two different positions;

[0047] Figures 5a to 5d Different orientations from the entrance section to the exit section;

[0048] Figure 5e , Figure 5f : The internal arrangement of the rotor in one orientation of the inlet section;

[0049] Figure 6a A circuit diagram of a portion of a heat pump system;

[0050] Figure 6b : Schematic diagram of bypass function;

[0051] Figures 6c to 6f : Bypass and non-bypass positions of the rotor;

[0052] Figure 7 The graph shows the variation of the area between ports D, S, E, and C with the rotor angle.

[0053] Figure 8 Details of the motor's arrangement relative to the housing;

[0054] Figure 9 : Overall overview of the assembled valves;

[0055] Figure 10 Longitudinal cross-sectional view of the valve;

[0056] Figure 11 A longitudinal cross-sectional view of the valve showing the force distribution;

[0057] Figure 12 A sleeve of two valves; and

[0058] Figure 13 : A longitudinal cross-sectional view of the sleeve of two valves.

[0059] Figure 1 A general overview of the four-way reversing valve 100 and compressor 101 assembly of a reversible heat pump is shown. The compressor may be a centrifugal compressor, screw compressor, scroll compressor, or some other type of compressor. The structure of the reversible heat pump is only partially shown and is symbolically represented by two large-diameter pipes implied in the lower portion of the figure. Valve 100 is fluidly connected to compressor 101 via two fluid conduits and fluidly connected to the rest of the heat pump via two additional fluid conduits. The downward-facing 90° downward bend of the lower port of valve 100 towards the upper pipe avoids installation work and materials for additional bends and flanges.

[0060] Figure 2a This is a longitudinal view of a four-way reversing valve 100. Valve 100 is configured for a high-capacity reversible heat pump compressor 101 previously shown. Valve 100 includes a housing 1 having four ports D, S, E, and C, namely, a discharge port D, a suction port S connectable to the compressor 101, an evaporator port E, and a condenser port C.

[0061] Inside the housing 1, a conical rotor 2 is configured to alter and / or vary the flow path between the four ports D, S, E, and C. The rotor 2 can change the flow path by rotating relative to the housing 1 about its axis of rotation. Figure 2a The middle is horizontal. In Figure 2a In the position of rotor 2 shown, evaporator port E is connected to suction port S, and discharge port D is connected to condenser port C.

[0062] The housing 1 includes an inlet section 11 and an outlet section 12 connected to each other via a first flange 13. These sections 11, 12 can be connected to each other in different rotational positions relative to each other. The housing 1 can be made of aluminum or an aluminum alloy.

[0063] The two mentioned sections 11 and 12 of housing 1 allow housing 1 and, in particular, the ports D, S, E, and C of housing 1 to be arranged in different orientations. Figure 2a In this embodiment, the discharge port D points in the opposite direction to the evaporator port E. However, the inlet section 11 can be rotated relative to the outlet section 12, and the discharge port D points in the same direction as the evaporator port E (i.e., in...). Figure 2a (Vertically downward direction). Alternatively, the discharge port D can be oriented such that it is perpendicular to the drawing plane and points towards or indicates the drawing plane. Therefore, valve 100 can be easily adapted to different geometries of heat pump architectures.

[0064] Figure 2b A cross-sectional view of valve 100 is shown, with the large-diameter surface 21 of rotor 2 pointing towards the drawing plane. Rotor 2 is shown inside inlet section 11. Rotor 2 may be primarily arranged in inlet section 11; however, in the assembled state of valve 100, a small portion of the rotor may be arranged in outlet section 12. The radially outer portion of large-diameter surface 21 includes a gear 202 for meshing with a gear 31 or any other suitable gear. Gear 31 is driven by a motor 3, which will be shown in more detail in a separate figure. The circular portion 211 of large-diameter surface 21 is exclusively composed of separate openings 24, 26 and a wall 200 separating said openings 24, 26. In an alternative embodiment, gear 202 may be located at the small-diameter surface 22 of rotor 2. Gear 202 may be located on the outer circumference of the corresponding component.

[0065] Gear 202 can be made of a different material than the rest of rotor 2. While the rest of rotor 2 can be made of aluminum or an aluminum alloy, gear 202 can be made of some steel or other alloy. Gear 202 and the rest of rotor 2 can be connected to each other, for example, by screws. Screws can be screwed onto rotor 2 in a direction perpendicular to the large diameter surface 21 of rotor 2 (i.e., the axial direction of rotor 2).

[0066] Figure 2c This is a detailed view of the connection between the rotor 2 of valve 100 and the motor 3. A lip seal 32 and an O-ring 33 may be provided between the gear 31 and the motor 3.

[0067] Figure 3a This is a perspective view of rotor 2. Rotor 2 includes two separate openings 24 and 26, wherein the first opening 24 fluidly connects the large diameter surface 21 to the small diameter surface 22 of rotor 2 via a first fluid conduit 25, and the second opening 26 fluidly connects the large diameter surface 21 to the radially outer portion 23 of rotor 2 via a second fluid conduit 27.

[0068] The two separate openings 24, 26 may be separated only by wall 200 and may represent a large portion or the largest portion of the large-diameter surface 21. A large portion of the large-diameter surface 21, and particularly the central portion of the large-diameter surface 21, may be occupied by the two separate openings 24, 26. This results in a rotor 2 with the maximum possible number of openings 24, 26 for a given size, thereby providing minimum flow resistance or maximum flow coefficient Kv through said openings 24, 26. Rotating the rotor 2 by 180° allows the two separate openings 24, 26 to be alternately connected to two different ports. The term "surface" is understood broadly and does not refer to a uniform solid portion of the rotor 2. Rather, it refers to the outer portion of the rotor 2, which may be planar and / or may include one or more openings.

[0069] exist Figure 3a In this embodiment, the first opening 24 and the second opening 26 have the same size and shape. The two openings 24, 26 are defined by at least one arc 28 and one or more straight edges 29. The first opening 24 and the second opening 26 may have a semi-circular shape. The exact shape of the openings 24, 26 can be selected to optimize the flow through the openings 24, 26 and the rotor 2.

[0070] The large-diameter surface 21 may include chamfers at least some of its inner edges (particularly the straight edge 29). Therefore, the chamfer at the large-diameter surface 21 can be provided at the wall 200. The chamfer can facilitate the rotation of the rotor 2, especially since the wall 200 may have to move over some sealing components as the rotor 2 rotates.

[0071] Figures 3a to 3c It is shown that the partition wall 200 passes through the center of the large diameter surface 21, and / or the circular portion 211 is arranged concentrically with the large diameter surface 21, and / or the radius of the circular portion 211 is at least 50%, 66% or 75% of the radius of the large diameter surface 21, particularly the outer radius of the large diameter surface 21.

[0072] The center of the large-diameter surface 21 can be the rotation center of the rotor 2. Since the wall 200 can pass through the rotation center of the rotor 2, the wall 200 or a portion thereof can be used to rotatably connect the rotor 2 to the housing 1 of the valve 100. Positioning the circular portion 211 concentrically relative to the large-diameter surface 21 maximizes the cross-sectional area of ​​the openings 24, 26 provided in the circular portion 211. The radius of the circular portion 211 can be maximized such that the cross-sectional area of ​​the openings 24, 26 is correspondingly maximized. The circular portion 211 can be defined such that it includes only the openings 24, 26 or portions thereof, and the wall 200 or portions thereof that divide the openings 24, 26. The wall 200 can be understood to include a central support 212 for supporting the rotor 2 against the housing 1. The circular portion 211 itself is not a component, but defines an area of ​​the large-diameter surface 21 in which only the two openings 24, 26 and the wall 200 are present.

[0073] Figure 3b The diagram shows a partition wall 200 extending along the entire or nearly entire length of the rotor 2 and separating the first fluid conduit 25 from the second fluid conduit 27. According to... Figure 3a and Figure 3c The partition wall 200 has a straight cross-section near the large-diameter surface 21. Near the small-diameter surface 22, the wall 200 may have a curved cross-section, such as... Figure 3a As indicated. The radially outward portion of wall 200 can form the radially outward portion 23 of rotor 2.

[0074] The term "fluid conduit" can be understood in a broad sense and can refer to long or short channels or openings through which fluid can flow during the operation of valve 100. The cross-section or shape of wall 200 can gradually change between a large-diameter surface 21 and a small-diameter surface 22.

[0075] The rotor 2 is conical in the following sense: the large diameter surface 21 and the small diameter surface 22 are arranged concentrically to each other, and the central portion between the large diameter surface 21 and the small diameter surface 22 at least partially and gradually changes its cross-sectional area and shape from approximately the area and shape of the small diameter surface 22 to at least part of the area and shape of the large diameter surface 21.

[0076] Figure 4a and Figure 4b Valve 100 is shown in two different positions. Figure 4a In the process, rotor 2 rotates so that evaporator port E is connected to suction port S. Figure 4b In the middle, the rotor 2 rotates so that the condenser port C is connected to the suction port S.

[0077] In each diagram, two arrows indicate the flow of the intake gas. Since the density of the intake gas at intake port S may be one-sixth the density of the intake gas in the discharge line connected to exhaust port D, the gas velocity at intake port S may be six times greater for the same mass flow rate. This means that Kv towards intake port S should be maximized to avoid excessive energy loss. To maximize Kv in the intake section of 4WRV, the cross-sectional area in valve 100 is designed from, for example... The diameter changes stably at the suction port S of compressor 101. to This restores most of the dynamic pressure to static pressure. Figure 4a , Figure 4b In the diagram, the left arrow indicates the valve 100 section where the fluid accelerates, and the right arrow indicates the fluid deceleration section.

[0078] Apart from entrance section 11 and exit section 12, Figure 4a The embodiments include a valve section 14, particularly a ball valve section, which can be connected to the inlet section 11 via a second flange 15.

[0079] The presence of valve section 14 does not change the number of ports provided at housing 1. The suction port S can be located at inlet section 11, or, if valve section 14 is present, at said valve section 14. Valve section 14 allows for fluid disconnection of valve 100 from compressor 101, enabling maintenance of compressor 101 to be performed.

[0080] The discharge port D and evaporator port E are arranged at an angle of 90° ± 20°, specifically ± 10°, relative to the suction port S. The suction port S can be arranged along the axial direction of valve 100 and directly leads to the inlet port of compressor 101 connected to valve 100. The axial direction of valve 100 can be parallel to the rotation axis of rotor 2.

[0081] Figures 5a to 5d Different orientations of inlet section 11 to outlet section 12 are shown. Emission port D is part of inlet section 11, and the orientation of emission port D depends on the orientation of inlet section 11. Inlet section 11 and outlet section 12 can be connected relative to each other in four different orientations.

[0082] Figure 5e and Figure 5f The internal arrangement of rotor 2 within valve 100 is shown. Valve 100 is shown in a configuration where the discharge port D points upwards, as... Figure 5a Like in the middle.

[0083] Figure 6aThis is the circuit diagram for the 4WRV valve 100. The four ports C, E, D, and S can be connected to each other in two alternating ways. Motor 3 rotates the previously described rotor 2, causing the heat pump's condenser, evaporator, and compressor to be connected in the desired manner. Motor 3 can be controlled by some external or internal controller. Discharge port D can always be connected to the outlet port of compressor 101, and suction port S is connected to the inlet port of compressor 101.

[0084] Figure 6b This is a schematic diagram of the bypass function of valve 100. The four ports C, E, D, and S can be connected to provide a bypass between the discharge port D and the intake port S.

[0085] Figures 6c to 6f The physical orientation of the rotor 2, used to provide both bypass and non-bypass configurations of valve 100, is shown. Figure 6c In this configuration, rotor 2 is set to 0°, and no bypass is provided between the exhaust port D and the intake port S. Figure 6d At the 45° position shown, a bypass is provided between the exhaust port D and the intake port S. Figure 6e A bypass still exists at the 135° position shown. No bypass is shown at the inverted position of rotor 2 at 180°. From... Figure 6c The position shown is converted to Figure 6e In the indicated position, valve 100 connects all ports C, E, D, and S. Bypass positions can be advantageous during compressor 101 startup because they effectively reduce the load on compressor 101. Furthermore, bypass positions can be used in situations requiring only the minimum performance of the heat pump. The bypass position effectively reduces the efficiency of valve 100, which can be useful when less heat pump performance than the minimum deliverable setting of compressor 101 is needed.

[0086] Figure 7 The bottom lines in the middle show that Figures 6c to 6f The area between the discharge port D and the intake port S increases and decreases accordingly during the rotation of rotor 2 as indicated in the figure.

[0087] Figure 8 More details of the arrangement of the motor 3 relative to the housing 1 are shown. The rotor 2 is attached to the inlet section 11 and connected to the rotor 2 via a gear 31 and a gear 202. The gear 202 may extend at 180° or 360° around the circumference of the rotor 2.

[0088] The radially outer portion of the large-diameter surface 21 of rotor 2 includes at least one permanent magnet 206 and / or some ferromagnetic material. The magnetic component can be used in conjunction with a sensor 209 for determining the angular position of rotor 2 relative to the rest of valve 100.

[0089] The purpose of valve sensor 209 is to provide position feedback when valve 100 has fully rotated rotor 2. Sensor 209 may be of the reed type, which includes mechanical contacts that close when subjected to a magnetic field. The cooling and heating positions of valve 100 can be detected by two permanent magnets 206 in the moving rotor 2, each magnet spaced 180° apart from each other. To ensure that the magnetic field of magnets 206 is strong enough to penetrate the solid aluminum wall of valve 100 and reach sensor 209, no metal parts that would affect the magnetic field are arranged near the field. The position of magnets 206 is chosen such that they are closer to motor 3 so that sensor 209 can be included in actuator housing.

[0090] Sensor 209 may be a reed sensor, a Hall sensor, and / or an inductive sensor. Sensor 209 may be configured to interact with permanent magnet 206. Sensor 209 may be configured together with the rest of valve 100 and / or may be permanently and / or integrally configured with valve 100.

[0091] Sensor 209 can be positioned close to motor 3, such that the sensor is included within the housing of motor 3. The housing of motor 3 can be attached to the housing 1 of valve 100. Since the sensor can be integrated into the housing of motor 3, the assembly of valve 100 is simplified. In particular, when attaching the housing of motor 3 to the housing 1 of valve 100, both motor 3 and sensor 209 can be assembled simultaneously.

[0092] The motor 3 may be at least partially located inside the housing 1 or inside a recess of the housing 1 of the valve 100. The motor 3 provides the driving force required to change the position of the valve 100 (i.e., the rotational position of the rotor 2). The housing 1 may be provided with an opening for connecting the output shaft of the motor 3 to the rotor 2.

[0093] Figure 9 This is an overall overview of the assembled valve 100. A motor 3 for rotating the concealed rotor 2 is connected to the housing 1, and the valve 100 is ready to be connected to the compressor 101 and to piping arranged in the heat pump configuration. The housing 1 includes an inlet section 11, an outlet section 12, and a valve section 14.

[0094] Figure 10 This is a longitudinal sectional view of valve 100. Detailed enlarged views of the main image are provided above and below it. The large-diameter surface 21 of rotor 2 is at least partially disposed between inlet section 11 and outlet section 12. Specifically, the outermost radial portion of the large-diameter surface 21 may be a portion on one side facing outlet section 12 and a portion on the opposite side facing inlet section 11.

[0095] The dimensions of the inlet section 11 and the outlet section 12 can be determined such that the rotor 2 can be inserted between the two sections 11 and 12 without them being connected to each other. A gap or groove can be provided between the inlet section 11 and the outlet section 12 to accommodate at least a portion of the large-diameter surface 21 of the rotor 2 when the two sections 11 and 12 are connected to each other. The gap or groove between the two sections 11 and 12 can accommodate bearings and / or other components required to provide a rotatable connection between the rotor 2 and the housing 1.

[0096] Apart from the large-diameter surface 21, the rest of the rotor 2 is disposed inside the inlet section 11. The rest of the rotor 2 includes the portion of the rotor 2 excluding the large-diameter surface 21 and / or may include additional structures for rotatably connecting the rotor 2 to the housing 1.

[0097] The rotor 2 is supported against the housing 1 by means of a pin 201 located at the center of the wall 200. The pin 201 is surrounded by a sliding ring 208.

[0098] The first seal 203, particularly the V-shaped lip seal, is located at or near the small diameter surface 22. The axial sliding ring 204, which presses against the O-ring 205, is located at or near the large diameter surface 21.

[0099] The first seal 203 can contact the outer circumference of the rotor 2 or its small diameter surface 22. The axial sliding ring 204 can contact the axial side of the rotor 2, that is, one side or part of the rotor 2, which is perpendicular to the axial direction of the rotor 2.

[0100] Spring 210 and / or bearing 207 are disposed at or near the small diameter surface 22. Spring 210 is configured to apply force to rotor 2 in the axial direction of rotor 2. Spring presses rotor 2 against axial sliding ring 204 and O-ring 205.

[0101] Spring 210 can apply force to rotor 2 via bearing 207. Spring 210 and bearing 207 can be in close contact with each other. The force applied to rotor 2 by spring 210 can press rotor 2 against other sealing components located at or near the large diameter surface 21 and / or against pin 201 and / or sliding ring 208 of rotor 2.

[0102] Figure 11 This is a longitudinal cross-sectional view of valve 100, showing the pressure distribution within valve 10. Since the intake pressure and discharge pressure typically differ by a considerable amount, the net force may be caused by the pressure difference acting on rotor 2.

[0103] During the rotation of rotor 2, valve 100 must handle the pressure difference between the intake and discharge sections. To minimize the impact of the differential pressure on drive and transmission, a pressure balance principle is implemented to counteract any resultant force acting on rotor 2. However, the pressure balance region is off-center, meaning there is a torque that generates a lateral force, which is absorbed by two radial bearings on either side of rotor 2 to keep the rotor centered. The black frame around the wall of the inclined rotor 2 illustrates how the balance region is off-center. The dimensions and shape of rotor 2 are determined to balance the pressures present at the first fluid conduit 25 and the second fluid conduit 27.

[0104] Specifically, the surface area pointing towards or viewed from the axial direction of rotor 2 can be selected such that the different pressures acting on the inside and outside of rotor 2 do not generate a resultant force acting on rotor 2 along its axial direction. Since no resultant force acts on rotor 2, the seal of rotor 2 can withstand constant or near-constant stress, independent of the pressure difference occurring at rotor 2. Therefore, leakage of the seal is unlikely. Although the rotor may not experience a resultant force, a torque may still be applied to the rotor due to the pressure gradient.

[0105] Figure 12 A set comprising two four-way directional valves 100 is shown. The valves are fluidly connected to each other via four manifolds 5 and to other components of the heat pump, not shown in the figure. Since the ports D, S, E, and C of the valves 100 can be designed identically, the same manifolds 5 can be used to connect the individual ports D, S, E, and C of the valves 100. This further simplifies the design of sets combining multiple valves 100 as described herein. The ports D, S, E, and C of the valves 100 can be arranged such that two or more valves 100 can be fluidly connected to each other, to the compressor 101, and / or to some heat exchanger architecture supplied by the compressor for heat transfer. Connecting multiple valves 100 in this manner allows for the expansion of the performance of sets of valves 100 with heat exchanger architectures of different capacities. The capacity of the combined valves 100 can be increased simply by adding the required number of identical valves 100 to match a given heat exchanger architecture. Figure 13 This is a longitudinal cross-sectional view of the assembly of two valves 100. The geometry of rotor 2 ensures that the pressure drop across valve 100 is minimized.

[0106] Figure Labels

[0107] 1. Shell

[0108] 2 rotors

[0109] 3 motors

[0110] 5 manifold

[0111] 11. Entrance Section

[0112] 12 Exit Section

[0113] 13 First flange

[0114] 14 Valve Section

[0115] 21 large diameter surface

[0116] 22 Small Diameter Surfaces

[0117] 23 Radial outer portion of rotor 2

[0118] 24 First Opening

[0119] 25 First fluid conduit

[0120] 26 Second opening

[0121] 27 Second fluid conduit

[0122] 28. Arc

[0123] 29 Straight edge

[0124] 100 Four-way Reversing Valve

[0125] 101 Compressor

[0126] 200 wall

[0127] 201 sales

[0128] 202 Gear

[0129] 203 First Seal

[0130] 204 Axial Sliding Ring

[0131] 205 O-ring

[0132] 206 permanent magnet

[0133] 207 bearing

[0134] 208 Sliding Ring

[0135] 209 Sensor

[0136] 210 Spring

[0137] 211 Circular section

[0138] D emission port

[0139] S Inhalation Port

[0140] E Evaporator Port

[0141] C Condenser Port

Claims

1. A four-way reversing valve (100) for a high-capacity reversible heat pump compressor (101), the four-way reversing valve comprising: A housing (1) having four ports (D, S, E, C), namely, a discharge port (D), a suction port (S), an evaporator port (E), and a condenser port (C); a conical rotor (2) rotatably disposed inside the housing (1) to change the flow path between the four ports (D, S, E, C), wherein the large diameter surface (21) of the rotor (2) includes two separate openings (24, 26), wherein the first opening (24) fluidly connects the large diameter surface (21) to the small diameter surface (22) of the rotor (2) via a first fluid conduit (25), and the second opening (26) fluidly connects the large diameter surface (21) to the radially outer portion (23) of the rotor (2) via a second fluid conduit (27). The feature is that the circular portion (211) of the large-diameter surface (21) is exclusively composed of at least a portion of the two separate openings (24, 26) and the partition wall (200) separating the openings (24, 26), and the first opening and the second opening (24, 26) are defined by at least one arc (28) and one or more straight edges (29), and The circular portion (211) is arranged concentrically with the large diameter surface (21), and / or the radius of the circular portion (211) is at least 50%, 66% or 75% of the radius of the large diameter surface (21).

2. The four-way directional valve (100) according to claim 1, characterized in that, The first opening and the second opening (24, 26) have the same size and shape and / or the first opening and the second opening (24, 26) have a semi-circular shape.

3. The four-way directional valve (100) according to claim 1, characterized in that, The partition wall (200) passes through the center of the large diameter surface (21).

4. The four-way directional valve (100) according to claim 3, characterized in that, The partition wall (200) extends along the entire length of the rotor (2) and separates the first fluid conduit (25) from the second fluid conduit (27), and / or the partition wall (200) has a straight cross section near the large diameter surface (21) and / or has a curved cross section near the small diameter surface (22).

5. The four-way directional valve (100) according to claim 1, characterized in that, The rotor (2) is supported against the housing (1) by means of a pin (201) located at the center of the partition wall (200), wherein the pin (201) is surrounded by a sliding ring (208) and / or the size of the rotor (2) is determined to balance the pressure generated at the first fluid conduit (25) and the second fluid conduit (27).

6. The four-way directional valve (100) according to claim 1, characterized in that, The radially outer portion of the large-diameter surface (21) or the small-diameter surface (22) includes a gear (202), and / or the large-diameter surface (21) includes a chamfer at at least some of its inner edges.

7. The four-way directional valve (100) according to claim 6, characterized in that, The gear (202) is made of a different material than the rest of the rotor (2).

8. The four-way directional valve (100) according to claim 1, characterized in that, The first seal (203) is located at or near the small diameter surface (22), and / or the axial sliding ring (204) pressed against the O-ring (205) is located at or near the large diameter surface (21).

9. The four-way directional valve (100) according to claim 1, characterized in that, A spring (210) and / or a bearing (207) are disposed at or near the small diameter surface (22), wherein the spring (210) is configured to apply force to the rotor (2) in the axial direction of the rotor (2).

10. The four-way directional valve (100) according to claim 6 or 7, characterized in that, The radially outer portion of the large-diameter surface (21) or the small-diameter surface (22) includes a permanent magnet (206) and / or a ferromagnetic material.

11. The four-way directional valve (100) according to claim 10, characterized in that, The sensor (209) is configured to interact with the permanent magnet (206).

12. The four-way directional valve (100) according to claim 11, characterized in that, The motor (3) is connected to the housing (1) via the gear (202) for rotating the rotor (2).

13. The four-way directional valve (100) according to claim 12, characterized in that, The sensor (209) is positioned close to the motor (3) such that the sensor is included in the housing of the motor (3).

14. The four-way directional valve (100) according to claim 1, characterized in that, The housing (1) includes an inlet section (11) and an outlet section (12), wherein the inlet section (11) and the outlet section (12) can be connected to each other via a first flange (13) and / or can be connected to each other in different rotational positions relative to each other, and / or the housing (1) is made of aluminum or an aluminum alloy.

15. The four-way directional valve (100) according to claim 14, characterized in that, The large-diameter surface (21) of the rotor (2) is at least partially disposed between the inlet section (11) and the outlet section (12).

16. The four-way directional valve (100) according to claim 15, characterized in that, The remainder of the rotor (2) is located inside the inlet section (11).

17. The four-way directional valve (100) according to claim 14, characterized in that, The housing (1) includes a valve section (14) which is connected to the inlet section (11) via a second flange (15).

18. The four-way directional valve (100) according to claim 1, characterized in that, The discharge port (D) and / or the evaporator port (E) are arranged at 90° ± 20° relative to the intake port (S).

19. The four-way directional valve (100) according to claim 8, characterized in that, The first seal (203) is a V-shaped lip seal.

20. The four-way directional valve (100) according to claim 11, characterized in that, The sensor (209) is a reed sensor, a Hall sensor, or an inductive sensor.

21. The four-way directional valve (100) according to claim 12, characterized in that, The motor (3) is a DC gear motor.

22. The four-way directional valve (100) according to claim 17, characterized in that, This valve section (14) is the ball valve section.

23. The four-way directional valve (100) according to claim 18, characterized in that, The discharge port (D) and / or the evaporator port (E) are arranged at 90° ± 10° relative to the intake port (S).

24. A set comprising two or more four-way directional valves (100) according to any one of the preceding claims, characterized in that, These four-way directional valves are fluidly connected via at least one manifold (5).

25. The set according to claim 24, characterized in that, At least two identical manifolds were installed (5).

26. The set according to claim 24, characterized in that, These four-way directional valves are fluidly connected via three or four manifolds (5).

Images