Cartridge ball valve with L-shaped flow path for operation with a refrigerant

Abstract

The invention relates to a cartridge ball valve (1) with an L-shaped flow path for operation with a refrigerant, comprising an actuator (3); a drive shaft (8) rotatable about a pivot axis (7); a valve ball (10) connected to the drive shaft (8); a valve housing (4) with a cavity (15) for receiving the valve ball (10) and two fluid connections connected to the cavity (15), wherein one of the fluid connections is formed in the form of a first side wall opening (18) in a side wall (19) of the valve housing (4) and a second refrigerant connection is formed in the form of a bottom wall opening (20) in a bottom wall (12) of the valve housing (4); a distributor (2) with flow lines (21, 22) which has a distributor pocket (6) into which the valve housing (4) is inserted, wherein the flow lines (21, 22) are aligned with the fluid connections of the valve housing (4);and internal sealing elements placed within the valve housing (4) for exerting pressure on the valve ball surface; wherein a flow channel (11) with a bottom opening (13) directed towards the bottom wall opening (20) of the valve housing (4) and with a side opening (14) extends through the valve ball (10), and wherein a pressure equalization opening (23) is placed as a further housing opening on the side of the valve housing (4) opposite the first side wall opening (18), and wherein the first side wall opening (18) and the pressure equalization opening (23) are in fluid communication with each other via a pressure equalization channel (24).

Description

[0001] The invention relates to a pressure-balanced cartridge ball valve with an L-shaped flow path for operation with a refrigerant, in particular for use within a motor vehicle air conditioning system.

[0002] Refrigerant valves typically provide three operating modes. When the refrigerant valve is in the open position, the refrigerant flows from the fluid inlet to the fluid outlet with a maximum flow path cross-section and minimal pressure drop. When the refrigerant valve is in the closed position, the refrigerant flow is kept below an upper limit defined for the closed state. In another operating mode, expansion, a variable, reduced flow path cross-section (expansion groove) is provided to ensure refrigerant expansion.

[0003] In refrigerant ball valves, the internal seal between the valve ball and the sealing elements—typically ball seats and O-rings—is ensured by a design that incorporates a floating ball. The valve ball and the drive shaft are generally two separate parts. The drive shaft allows the valve ball to move, but the ball can also move horizontally toward a ball seat. When the refrigerant ball valve is in the closed position, high pressure from one side of the valve ball can move it toward the opposite side, increasing the contact pressure between the valve ball and the seal. This ensures sufficient internal sealing performance and protection against internal leakage in the closed position.

[0004] German patent application DE 10 2020 211 278 A1 discloses a corresponding expansion valve for controlling a fluid flow with a linear flow path. This is a ball valve in which the aforementioned concept of the "floating" valve ball is applied.

[0005] However, some design applications require an L-shaped flow path instead of a linear one. In the L-topology, the ports are arranged at a 90° angle, for example, on the side and bottom of the valve body. The resulting flow path is L-shaped. Due to the floating ball and the unbalanced pressure on both sides of the valve ball, the sealing elements are not sufficiently compressed to seal on the high-pressure inlet side of the valve ball. The high-pressure fluid enters the cavity of the valve ball within the valve body. This is acceptable for a valve with a linear topology, but leads to internal leakage in a valve with an L-topology.

[0006] Furthermore, when using a valve design where the valve ball and shaft are formed as a single unit, the valve ball is unable to move horizontally, even under increased pressure. The challenge lies in ensuring sufficient contact pressure between the valve ball and the sealing elements, and ultimately, the correct sealing function of the valve design. If high pressure occurs at the side inlet when the valve is closed, high-pressure fluid enters the valve housing and pressurizes the valve ball from the side inlet direction. This situation could cause the drive shaft, which is formed as a single unit with the valve ball, to tilt, resulting in internal leaks at the sealing elements located at the side inlet, as well as external leaks at sealing elements of a shaft seal on the drive shaft, such as an X-ring.

[0007] The object of the invention is to provide a cartridge ball valve with L-topology in which, when a high pressure is applied, the sealing function on the high pressure inlet side is ensured even in the closed position of the cartridge ball valve and no high pressure fluid enters the cavity of the valve housing.

[0008] This problem of the invention is solved by a cartridge ball valve with the features according to claim 1. Further developments are specified in the dependent claims.

[0009] The cartridge ball valve designed according to the invention is suitable for operation with a refrigerant and has an L-shaped flow path. It comprises a preferably electric actuator, a drive shaft rotatable about a pivot axis, a valve ball connected to the drive shaft, and a valve housing with a cavity for receiving the valve ball and two fluid ports connected to the cavity, preferably oriented at an angle of 90° to each other. One of the fluid ports is designed as a first side wall opening of the valve housing, while a second fluid port is designed as a bottom wall opening of the valve housing. The cartridge ball valve further comprises a distributor with flow lines, which has a distributor pocket into which the valve housing is inserted, the flow lines being aligned with the fluid ports of the valve housing.The cartridge ball valve further comprises internal sealing elements located within the valve housing for exerting pressure on the valve ball surface. A flow channel extends through the valve ball, with a bottom opening facing the bottom wall opening of the valve housing and a side opening, the position of which is adjustable by rotating the drive shaft about the axis of rotation relative to the first side wall opening. According to the invention, a second side wall opening of the valve housing, serving as a pressure equalization opening, is located on the side of the valve housing opposite the first side wall opening. The first side wall opening and the pressure equalization opening are in fluid communication with each other via a pressure equalization channel.

[0010] When using a cartridge ball valve of this design in an air conditioning system, particularly in a motor vehicle air conditioning system, it is necessary that the refrigerant circuit allows two opposite flow directions at certain components, so that the refrigerant flow direction is reversible, for example, during the transition between cooling and heat pump / heating operating modes. The cartridge ball valve according to the invention can also fulfill this function and allows flow in two opposite directions. That is, the first side wall opening and the bottom wall opening of the valve housing can each function as either a fluid inlet or a fluid outlet, depending on the flow direction. However, this only applies if the cartridge ball valve does not have a closing function in the specific application and therefore there is no need to prevent internal leaks.If the cartridge ball valve is required to perform a closing function, the configuration is such that the first side wall opening of the valve housing can only be the fluid inlet, and consequently, the bottom wall opening of the valve housing can only serve as the fluid outlet. Closing the cartridge ball valve then interrupts the fluid flow from the first side wall opening of the valve housing, which forms the fluid inlet, towards the bottom wall opening of the valve housing, which forms the fluid outlet.

[0011] The absence of a "floating valve ball" in a ball valve design where the drive shaft and valve ball are formed as a single unit is compensated for by the pressure-equalizing ball valve design according to the invention. When high pressure occurs at the lateral inlet in the closed state, high-pressure fluid enters the valve housing and pressurizes the valve ball from the lateral inlet direction. However, it can also flow around the valve housing through the pressure equalization channel and enter the valve housing at the opposite lateral opening, the pressure equalization port, thus pressurizing the valve ball from the opposite side as well. Therefore, the same pressure occurs on both sides of the valve ball, resulting in pressure equalization. The ball remains in the center of its cavity, and sealing elements are pressed against the ball surface by the pressure from both sides.Since an adequate contact pressure exists between the valve ball and the sealing elements, the internal sealing function is ensured. This provides a pressure-balanced cartridge ball valve, which solves the problem of internal leakage inherent in L-topology valves. The pressure equalization on both sides of the valve ball ensures that all sealing elements are sufficiently compressed, preventing the risk of internal leakage.

[0012] Preferably, the flow channel within the valve ball is also L-shaped, corresponding to the L-topology of the cartridge ball valve. The internal sealing elements typically include two ball seal seats located in the cavity inside the valve housing, between which the valve ball is positioned. Advantageously, each ball seal seat is mounted to the valve housing via a ball seal seat sealing ring, which is preferably located within a circumferential groove on the side of the ball seal seat facing away from the valve ball and bears against the valve housing. According to a particularly preferred embodiment of the invention, the two ball seal seats are located at the opposite housing openings, the first side wall opening and the pressure equalization opening, each positioned between the corresponding housing opening and the valve ball.In one embodiment, the mechanical support and correct positioning of the ball seal seats within the valve housing is achieved by positively engaging the ball seal seats within the valve housing. Alternatively, seal seat holders are arranged for the mechanical support and correct positioning of the ball seal seats within the valve housing, with each seal seat holder enclosing a ball seal seat on its circumference.

[0013] Advantageously, the pressure equalization channel extends in an annular shape around the valve housing. According to the invention, the cartridge ball valve further comprises a distributor having a distributor pocket into which the valve housing is inserted, the distributor preferably having two flow lines in accordance with the L-topology, which are oriented perpendicular to each other and are aligned with the fluid connections of the valve housing. According to a particularly preferred embodiment of the invention, the pressure equalization channel extending around the valve housing can be designed in the form of a space extending around the circumference of the valve housing between the valve housing and the distributor pocket.This space between the valve body and the manifold pocket, forming the pressure equalization channel, can be created, for example, by a stepped reduction in the outer circumference of the valve body and a stepped reduction in the inner circumference of the manifold pocket that is not axially complementary and is offset in position. Advantageously, the first side wall opening and the opposite pressure equalization opening can be sealed by two sealing rings extending around the circumference of the valve body. One sealing ring is positioned above and the other below the first side wall opening and the opposite pressure equalization opening, respectively, with the upper sealing ring between the valve body and the manifold providing a seal against external fluid leakage, and the lower sealing ring between the valve body and the manifold providing a seal against internal fluid leakage.

[0014] The drive shaft is rotatably mounted about its axis of rotation in a shaft bearing, preferably within the valve housing, which has a shaft seal. Preferably, the shaft seal is designed as an X-ring seal.

[0015] In a valve design with an L-topology, the invention ensures the sealing function against internal leakage. The design according to the invention provides sufficient contact pressure between the valve ball and the seal without a "floating valve ball." Therefore, the valve ball and the drive shaft can be designed as a single part, resulting in a simpler construction. The described pressure configuration results in low torque on the valve ball. The low torque means lower power consumption and opens up the possibility of miniaturizing the valve actuator.

[0016] The cartridge ball valve according to the invention is particularly applicable as a refrigerant valve in a refrigerant circuit of an air conditioner, a heat pump, or a combination of an air conditioner and a heat pump. For example, the cartridge ball valve can be used as an expansion valve. A refrigerant circuit in which the cartridge ball valve according to the invention can be used can be operated with any refrigerant except R744 (CO2), in particular R1234yf, R1234a, R404a, R600 or R600a, R290, R152a, R32, or mixtures of the aforementioned refrigerants.

[0017] Further details, features, and advantages of embodiments of the invention will become apparent from the following description of exemplary embodiments with reference to the accompanying drawings. These show: Fig. 1: A side view of a cartridge ball valve with a distributor and an actuator, showing lines from subsequent sectional views I-I and II-II, Fig. 2: a sectional side view along a vertical plane corresponding to line I - I of the cartridge ball valve in a closed state, with a further line of a subsequent sectional view III - III shown, Fig. 3: a sectional side view along a vertical plane corresponding to line III - III of the cartridge ball valve in the closed state, Fig. 4: a sectional view from above along a horizontal plane corresponding to line II - II of the cartridge ball valve in the closed state, Fig. 5: a sectional side view along a vertical plane corresponding to line I - I of the cartridge ball valve in an open state, with a further line of a subsequent sectional view III - III shown, Fig. 6: a sectional side view along the vertical plane corresponding to line III - III of the cartridge ball valve in the open state, Fig. 7: a sectional view from above along a horizontal plane corresponding to line II - II of the cartridge ball valve in the open state, Fig. 8: an exploded view of the cartridge ball valve (without distributor); Fig. 9A: a schematic representation of the pressure equalization within a closed cartridge ball valve in a sectional view along the vertical plane III - III, Fig. 9B: a schematic representation of the pressure equalization within the closed cartridge ball valve in a sectional view from above along a horizontal plane corresponding to line II - II.

[0018] The Fig. Figure 1 shows a side view of a cartridge ball valve 1 with a distributor 2 and an electric actuator 3. The electric actuator 3 is mounted on a valve body 4, which is predominantly enclosed in a Fig. 1 is recorded in a non-visible pocket-shaped recess in distributor 2, wherein in Fig. 1 Only a flange 5 is visible at the upper axial end of the valve housing 4, which rests on the distributor 2 and on which the actuator 3 is also attached. Fig. In addition, lines I - I and II - II from subsequent section views are also shown.

[0019] In the Fig. Figure 2 is a sectional view of the cartridge ball valve 1 along a vertical plane according to the one shown in Fig. The line I-I shown in Figure 1 depicts the cartridge ball valve 1 in a closed state. The part of the valve body 4 located below the flange 5 is inserted into the previously mentioned pocket-shaped recess of the distributor 2, hereinafter referred to as distributor pocket 6. Fig. Figure 2 shows the electric actuator 3, to which a drive shaft 8 rotatable about a pivot axis 7 is coupled via an actuator coupling element 9, and a valve ball 10 formed integrally with the drive shaft 8. An L-shaped flow channel 11 runs through the valve ball 10, with a bottom opening 13 facing a bottom wall 12 of the valve housing 4 and a side opening 14. The valve housing 4 forms a cavity 15 inside for receiving the valve ball 10. According to the Fig. 2 ball sealing seats 16 and sealing seat holders 17 for mechanical support and correct positioning of the ball sealing seats 16 are arranged within the cavity 15.

[0020] The Fig. Figure 3 shows a sectional view along a vertical plane corresponding to line III-III in the closed state of the cartridge ball valve 1. It can be seen that the valve housing 4 has two fluid ports connected to the cavity 15 and oriented at an angle of 90° to each other. A first fluid port is formed as a first side wall opening 18 in a side wall 19 of the valve housing 4. A second fluid port is formed as a bottom wall opening 20 in the bottom wall 12 of the valve housing 4. In the distributor 2, two flow lines 21, 22 are formed adjacent to the distributor pocket 6 into which the valve housing 4 is inserted. These flow lines are oriented perpendicular to each other such that each flow line 21, 22 is aligned with one of the fluid ports 18 and 20.A first, horizontally oriented flow line 21 is aligned with the first side wall opening 18 of the valve housing 4 and a second, vertical flow line 22 is aligned with the bottom wall opening 20 of the valve housing 4. As can be seen from the sectional views in the . Fig. 2 and the Fig. As can be seen from Figure 3, the flow channel 11 within the valve ball 10 is formed at right angles or in an L-shape, such that the lateral opening 14 of the valve ball 10 is oriented at a right angle to the bottom wall opening 20 in the bottom wall 12 of the valve housing 4. The flow channel 11 running through the valve ball 10 is oriented with its bottom opening 13 towards the bottom wall opening 20 of the valve housing 4 in every rotational position, while the position of the lateral opening 14 of the flow channel 11 is adjustable by rotating the drive shaft 8, which is formed as one part together with the valve ball 10, about the axis of rotation 7, relative to the first side wall opening 18. In the Fig. In the position shown in Figure 3, the lateral opening 14 of the flow channel 11 of the valve ball 10 is not directed towards the first side wall opening 18. The cartridge ball valve 1 is therefore located according to Fig. 3 in a closed state. On the side of the valve housing 4 opposite the first side wall opening 18, a pressure equalization opening 23 is formed as a further housing opening, wherein the first side wall opening 18 and the pressure equalization opening 23 are connected via a Fig. The pressure equalization channel 24, which is only partially visible, is in fluid communication with each other. This pressure equalization channel 24 is formed as an intermediate space extending around the circumference of the valve housing between the valve housing 4 and the distributor 2. The intermediate space forming the pressure equalization channel 24 between the valve housing 4 and the distributor 2 is created by a stepped reduction in the outer circumference of the valve housing 2 and, in the axial direction, a non-complementary stepped reduction in the inner circumference of the distributor pocket 6. Ball seal seats 16.1, 16.2 are mounted opposite each other inside the valve housing 4 as sealing elements for the valve ball 10, with the valve ball 10 being arranged between these opposing ball seal seats 16.1, 16.2. A first ball seal seat 16.1 is positioned inside the valve housing 4 at the first side wall opening 18, while the second ball seal seat 16.2 is located inside the valve housing 4 at the opposite pressure equalization opening 23. According to the . Fig. In the embodiment shown in Figure 3, the ball sealing seats 16.1, 16.2 are designed as hollow cylindrical rings, the inner surfaces of which at least partially have a spherical sealing surface corresponding to the valve ball 10. In the closed state of the cartridge ball valve 1, the flow channel 11 is arranged transversely to the flow direction of the cartridge ball valve 1, and the spherical sealing surface rests on the valve ball 10 in such a way that no fluid can pass through the corresponding surfaces between the valve ball 10 and the spherical sealing surface of the ball sealing seat 16.1; 16.2. As already mentioned, two sealing seat holders 17.1, 17.2 are arranged within the valve housing 4 to mechanically support the correct positioning of the ball sealing seats 16.1, 16.2, each enclosing a ball sealing seat 16.1; 16.2 around its circumference. The ball sealing seat 16.1; 16.2 ensures a dynamic seal of the rotating valve ball 10 against internal fluid leakage between the valve ball 10 and the respective ball seat 16.1; 16.2. Furthermore, in the . Fig. 3. In addition to the ball seals 16.1, 16.2, various other elements with a sealing function are identifiable. Each ball seal 16.1; 16.2 is associated with a ball seal sealing ring 25.1; 25.2 designed as an O-ring. A ball seal sealing ring 25.1; 25.2 prevents internal leakage between the valve housing 4 and the respective associated ball seal 16.1; 16.2. Furthermore, the ball seal sealing ring 25.1; 25.2 establishes a contact force for sufficient contact pressure between the valve ball 10 and the ball seal 16.1; 16.2. In the Fig. In the embodiment shown in Figure 3, the ball seat sealing rings 25.1, 25.2 are each positioned in a circumferential groove 26.1, 26.2 formed on the rear side of the ball seat 16.1, 16.2 facing the valve housing 4. The drive shaft 8 is coupled at its upper end to the electric actuator 3 via the actuator coupling element 9. The drive shaft 8 is rotatably mounted about its axis of rotation 7 in a shaft bearing 27, the shaft bearing 27 being located in an upper region of the valve housing 4, more precisely in a housing opening at the level of the flange 5 of the valve housing 4. The shaft bearing 27 has a shaft seal 28, which is advantageously designed as an X-ring seal and provides a dynamic seal of the drive shaft 8 against external fluid leakage between the drive shaft 8 and the valve housing 4.The X-ring seal arranged around the circumference of the drive shaft 8 seals the area between the drive shaft 8 and the shaft bearing 27 to prevent fluid from escaping from the interior of the valve housing 4 into the environment. A radially outwardly projecting shoulder 29 is formed on the drive shaft 8 below the position of the shaft bearing 27. This shoulder serves to abut an axial inner surface 30 located inside the valve housing 4 below the shaft bearing 27. As also in the... Fig. As can be seen in Figure 3, the electric actuator 3 is mounted and fastened to the valve housing 4. A radially open groove 32, extending around the entire circumference of an upper annular rim 31 of the valve housing 4, is formed in this groove. An O-ring, acting as a sealing ring 33, is received in this groove to seal the valve housing 4 and the actuator 3. This seal protects internal components from external contamination and corrosive media. Several additional sealing rings, also designed as O-rings, are positioned between the valve housing 4 and the distributor 2. For example, a sealing ring 34, located between the valve housing 4 and the distributor 2, is received in an upwardly open axial groove 35 of the distributor 2. This groove extends around the distributor pocket 6 on a surface outside the distributor pocket, thus sealing internal components against contamination and corrosive media.The first side wall opening 18, the opposite pressure equalization opening 23 and the pressure equalization channel 24 connecting the first side wall opening 18 and the pressure equalization opening 23 are sealed by two sealing rings 36, 37 extending around the circumference of the valve housing 4, of which - with respect to the axial direction - an upper sealing ring 36 is positioned above and a lower sealing ring 37 is positioned below the first side wall opening 18, the opposite housing opening 23 and the pressure equalization channel 24.The upper sealing ring 36 is an O-ring that is received in a circumferential, outwardly open radial groove 38 formed in the outer wall of a cylindrical part of the valve housing 4 above the first side wall opening 18, the opposite housing opening 23, and the pressure equalization channel 24. It provides a seal against external fluid leakage between the valve housing 4 and the distributor 2; that is, the upper sealing ring 36 serves to prevent refrigerant from flowing out of the system. The lower sealing ring 37 is an O-ring that is received in a circumferential, outwardly open radial groove 39, also formed in the outer wall of the cylindrical part of the valve housing 4, below the first side wall opening 18, the opposite housing opening 23, and the pressure equalization channel 24. It ensures a seal against internal fluid leakage between the valve housing 4 and the distributor 2.

[0021] The Fig. Figure 4 shows a sectional view from above along a horizontal plane corresponding to line II-II of the cartridge ball valve 1 in the closed state. The valve body 4 has a circular cross-section and is inserted into the distributor pocket 6 of the distributor 2, which also has a circular cross-section. In the Fig. As shown in the sectional view 4, the first, horizontally oriented flow line 21 is aligned with the first side wall opening 18 of the valve housing 4. A further housing opening, the pressure equalization opening 23, is located on the side of the valve housing 4 opposite the first side wall opening 18. The first side wall opening 18 and the pressure equalization opening 23 are in fluid communication with each other via the pressure equalization channel 24. The pressure equalization channel 24 is formed as a space extending around the circumference of the valve housing 4 between the valve housing 4 and the distributor 2.Since both the valve housing 4 and the distributor pocket 6 have a circular cross-section, the space forming the pressure equalization channel 24 runs annularly around the valve housing 4 and, in its course, is tangent to both the first side wall opening 18 and the pressure equalization opening 23, thus providing two flow paths for the fluid connection between the first side wall opening 18 and the pressure equalization opening 23. The sectional view of the... Fig. Figure 4 shows the valve ball 10, which is positioned within the cavity 15 between the two ball seal seats 16.1, 16.2. A seal seat holder 17.1, 17.2, which surrounds the respective ball seal seat 16.1; 16.2, provides mechanical support for the correct positioning of the two annular ball seal seats 16.1, 16.2 at the first side wall opening 18 and the pressure equalization opening 23, respectively, such that the annular ball seal seats 16.1, 16.2 are aligned with the first side wall opening 18 and the pressure equalization opening 23. Furthermore, each ball seal seat 16.1; 16.2 is mounted to the valve housing 4 by means of a ball seal seat sealing ring 25.1; 25.2, which is located within a circumferential groove 26.1; 26.2 is located on the side of the respective ball seat 16.1; 16.2 facing away from the valve ball 10 and rests against the valve housing 4. In the Fig. In the closed state of the cartridge ball valve 1 shown in Figure 4, the lateral opening 14 of the flow channel 11 of the valve ball 10 is not directed towards the first side wall opening 18.

[0022] The Fig. Figure 5 shows a sectional side view along a vertical plane corresponding to line I - I of the cartridge ball valve 1 in an open state, as already shown in Fig. 2, the line of a subsequent section view III - III is shown. Unlike the one in Fig. In the closed position of the cartridge ball valve 1 shown in Figure 2, the lateral opening 14 of the L-shaped flow channel 11 of the valve ball 10 is oriented towards the first side wall opening, wherein in Fig. 5 the first side wall opening and as a result of the orientation of the side opening 14 also the L-shape of the flow channel 11 are not visible.

[0023] The Fig. Figure 6 shows a sectional view along a vertical plane corresponding to line III-III in the open state of the cartridge ball valve 1. The only difference to the otherwise corresponding sectional view of the Fig. 3 consists in the alignment of the lateral opening 14 of the passage channel 11 by the valve ball 10, which is aligned towards the first side wall opening 18, while the passage channel 11, as in every rotational position of the drive shaft 8, which is formed in one piece with the valve ball 10, is also aligned in the rotational position of the drive shaft 8 according to the open state of the cartridge ball valve 1 with its bottom opening 13 towards the bottom wall opening 20 of the valve housing 4.

[0024] The Fig. Figure 7 shows a sectional view from above along a horizontal plane corresponding to line II-II of the cartridge ball valve 1 in the open state, in which, unlike the one in Fig. In the open state of the cartridge ball valve 1 shown in Figure 4, the side opening 14 of the flow channel 11 of the valve ball 10 is aligned towards the first side wall opening 18.

[0025] The Fig. Figure 8 shows an exploded view of the individual components of the cartridge ball valve 1, with the exception of the distributor. Fastening elements 40 in the form of screws or bolts are provided for attaching the electric actuator 3 to the valve housing. These elements can be inserted into or passed through cylindrical sleeves 41 of the actuator 3 and correspond to bores 42 formed in the flange 5 of the valve housing 4. The sealing between the valve housing 4 and the actuator 3 is achieved by the sealing ring 33, which can be inserted into the outwardly open radial groove 32 formed in the upper annular rim 31 of the valve housing 4. A cover plate 44 is provided to cover a central opening 43 in the flange 5 of the valve housing 4. This cover plate has bores 45 for receiving and passing through fastening elements 46, as well as a central opening 47 for the passage of the drive shaft 8.The actuator coupling element 9 couples the drive shaft 8, which is formed integrally with the valve ball 10, to the actuator 3. A shaft bearing is provided for the rotatable mounting of the drive shaft 8 within the valve housing 4. This bearing comprises a shaft seal 28, advantageously designed as an X-ring seal, and two axial bearing washers 48, between which the shaft seal 28 is positioned with respect to the axial direction. The radially outwardly projecting shaft shoulder 29 is formed on the drive shaft 8. A spacer ring 49 can be placed on this shoulder, with the shaft shoulder 29, fitted with the spacer ring 49, bearing against the axial inner surface located within the valve housing 4. Fig. 8 is therefore not visible. In the perspective view of the valve housing 4, the first side wall opening 18 is visible. Above the first side wall opening 18, the circumferential, outwardly open radial groove 38 is formed in the outer wall of the cylindrical part of the valve housing 4, which is provided for receiving the upper sealing ring 36, designed as an O-ring. Below the first side wall opening 18, the circumferential, outwardly open radial groove 39 is formed in the outer wall of the cylindrical part of the valve housing 4, which serves to receive the lower sealing ring 37. In the exploded view of the Fig. Figure 8 also shows the individual ball seal seats 16.1, 16.2, which are designed as hollow cylindrical rings, the inner surfaces of which at least partially have a spherical sealing surface corresponding to the valve ball 10. Two seal seat holders 17.1, 17.2 are provided to mechanically support the correct positioning of the ball seal seats 16.1, 16.2 within the valve housing 4. The seal seat holders 17.1, 17.2 each have a rectangular outer contour and a central circular opening. The circular openings of the seal seat holders 17.1, 17.2 each correspond to the outer diameter of one of the annular ball seal seats 16.1, 16.2, such that both ball seal seats 16.1, 16.2 can each be received into a circular opening of a seal seat holder 17.1; 17.2. As already mentioned, each ball seat 16.1, 16.2 has a ball seat sealing ring 25.1; 25.2 assigned, which is intended to prevent internal leakage between the valve housing 4 and the ball seal seat 16.1; 16.2 and, furthermore, to establish a contact force for sufficient contact pressure between the valve ball 10 and the ball seal seat 16.1; 16.2.

[0026] In the different sectional views of the figures Fig. 9A and Fig. Figure 9B schematically depicts the flow path of the fluid, for example a refrigerant, and the pressure equalization in the closed state of the cartridge ball valve 1. If the cartridge ball valve 1 must perform a closing function, the configuration is defined such that the first side wall opening 18 of the valve housing 4 can only be the fluid inlet, and the bottom wall opening 20 of the valve housing 4 can consequently only be the fluid outlet. Closing the cartridge ball valve 1 then interrupts the fluid flow from the first side wall opening 18 of the valve housing 4, which forms the fluid inlet, towards the bottom wall opening 20 of the valve housing 4, which forms the fluid outlet.

[0027] When high pressure occurs at the first side wall opening 18 in the closed state, a high-pressure fluid, for example refrigerant fluid, enters the valve housing 4 and pressurizes the valve ball 10 from the lateral inlet direction, as shown in the figures. Fig. 9A and Fig. 9B is indicated by an arrow passing through the first side wall opening 18. Thus, the valve ball is pressurized from the direction of the first side wall opening 18. Without pressure equalization, this situation could lead to tilting of the drive shaft 8, which is formed as a single unit with the valve ball 10, and consequently to internal leaks at the sealing elements positioned at the first side wall opening 18, i.e., to internal leaks at the ball seal seat 16.1 and at the ball seal seat sealing ring 25.1.

[0028] Due to the existing pressure equalization channel 24, the high-pressure fluid, as in Fig. 9B, indicated by arrows, flow in two directions through the pressure equalization channel 24 around the valve housing 4 and at the opposite pressure equalization opening 23, as shown in the figures. Fig. 9A and Fig.As indicated by another arrow 9B, the valve ball 10 enters the valve housing 4. In this way, the valve ball 10 can also be pressurized from the side opposite the first side wall opening 18. Therefore, the same pressure occurs on both sides of the valve ball 10, resulting in pressure equalization. There is neither displacement of the valve ball nor tilting of the drive shaft. The valve ball 10 remains in the center of its cavity 15, and the ball sealing seats 16.1, 16.2 are pressed against the spherical surface of the valve ball 10 by the pressure from both sides. Since there is adequate contact pressure between the valve ball 10 and the ball sealing seats 16.1, 16.2, and thus the sealing elements are properly compressed, the internal sealing function is ensured and there is no risk of internal leaks. Reference symbol list 1 cartridge ball valve 2 distributors 3 actuators 4 Valve housings 5 Flange of the valve housing 6 distribution pockets 7 axis of rotation 8 Drive shaft 9 Actuator coupling element 10 valve balls 11 Flow channel through the valve ball 12 Bottom wall of the valve housing 13 Bottom opening of the flow channel 14 lateral opening of the flow channel 15 cavities in the valve housing 16 Ball seal seat 16.1 Ball seal seat at the first side wall opening 16.2 Ball seal seat at the pressure equalization opening 17 Sealing seat holders 17.1 Sealing seat holder at the first side wall opening 17.2 Sealing seat holder at the pressure equalization opening 18 First side wall opening of the valve housing; housing opening 19 Side wall of the valve housing 20 Floor wall opening; Fluid connection 21 First flow line of the distributor 2 22 second flow line of the distributor 2 23 Pressure equalization opening; housing opening 24 Pressure equalization channel 25.1 Ball seat sealing ring 25.2 Ball seat sealing ring 26.1 circumferential groove for the ball seal seat sealing ring 25.1 26.2 circumferential groove for the ball seal seat sealing ring 25.2 27 shaft bearings 28 Shaft seal 29 wave step 30 axial inner surface in the valve housing 31 ring-shaped edge 32 radial groove 33 Sealing ring between the valve housing 4 and the actuator 3 34 Sealing ring between the valve housing 4 and the distributor 2 35 axial groove of the distributor 2 for the sealing ring 34 36 upper sealing ring 37 lower sealing ring 38 radial groove for the upper sealing ring 36 39 radial groove for the lower sealing ring 37 40 fasteners 41 cylindrical sleeves on the actuator 3 42 holes in the flange 5 of the valve housing 4 43 middle opening 43 in the flange 5 of the valve housing 4 44 Cover plate 45 holes in the cover plate 44 for receiving and passing fasteners 46 Fasteners 47 middle opening in the cover plate 44 for the passage of the drive shaft 8 48 axial bearing washers 49 spacer ring QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2020 211 278 A1

[0004]

Claims

[1] Cartridge ball valve (1) with L-shaped flow path for operation with a refrigerant, comprising ➣ an actuator (3), ➣ a drive shaft (8) rotatable about a pivot axis (7), ➣ a valve ball (10) connected to the drive shaft (8), ➣ a valve housing (4) with a cavity (15) for receiving the valve ball (10) and two fluid connections connected to the cavity (15), wherein one of the fluid connections is formed in the form of a first side wall opening (18) in a side wall (19) of the valve housing (4) and a second fluid connection is formed in the form of a bottom wall opening (20) in a bottom wall (12) of the valve housing (4), ➣ a distributor (2) with flow lines (21, 22) which has a distributor pocket (6) into which the valve housing (4) is inserted, wherein the flow lines (21, 22) are aligned with the fluid connections of the valve housing (4), and ➣ internal sealing elements placed within the valve housing (4) for exerting pressure on the valve ball surface, wherein a flow channel (11) with a bottom opening (13) directed towards the bottom wall opening (20) of the valve housing (4) and with a side opening (14) extends through the valve ball (10), and wherein a pressure equalization opening (23) is placed as a further housing opening on the side of the valve housing (4) opposite the first side wall opening (18), and wherein the first side wall opening (18) and the pressure equalization opening (23) are in fluid communication with each other via a pressure equalization channel (24). [2] Cartridge ball valve (1) according to claim 1, characterized by , that the two fluid connections connected to the cavity (15) are oriented at an angle of 90° to each other. [3] Cartridge ball valve (1) according to claim 1 or 2, characterized by, that the flow channel (11) inside the valve ball (10) is L-shaped. [4] Cartridge ball valve (1) according to any one of claims 1 to 3, characterized by , that the sealing elements include two ball sealing seats (16.1, 16.2) placed in the cavity (15) inside the valve housing (4), between which the valve ball (10) is arranged. [5] Cartridge ball valve (1) according to claim 4, characterized by , that each ball seat (16.1; 16.2) is mounted to the valve housing (4) in a sealed manner via a ball seat sealing ring (25.1; 25.2), which is placed within a circumferential groove (26.1; 26.2) in the side of the ball seat (16.1; 16.2) facing away from the valve ball (10) and bears against the valve housing (4). [6] Cartridge ball valve (1) according to claim 4 or 5, characterized by, that the two ball sealing seats (16.1, 16.2) are located at the opposite housing openings, the first side wall opening (18) and the pressure equalization opening (23), each between the housing opening (18; 23) and the valve ball (10). [7] Cartridge ball valve (1) according to any one of claims 4 to 6, characterized by , that for the mechanical support and correct positioning of the ball sealing seats (16.1, 16.2) within the valve housing (4) the ball sealing seats (16.1, 16.2) are positively engaged within the valve housing (4). [8] Cartridge ball valve (1) according to any one of claims 4 to 6, characterized by , that for the mechanical support and correct positioning of the ball sealing seats (16.1, 16.2) within the valve housing (4) sealing seat holders (17.1, 17.2) are arranged, each sealing seat holder (17.1; 17.2) enclosing a ball sealing seat (16.1; 16.2) on its circumference. [9] Cartridge ball valve (1) according to any one of claims 1 to 8, characterized by , that the pressure equalization channel (24) runs in a ring shape around the valve housing (4). [10] Cartridge ball valve (1) according to any one of claims 1 to 9, characterized by , that the distributor (2) has two flow lines (21, 22) which are oriented perpendicular to each other and are aligned with the fluid connections of the valve housing (4). [11] Cartridge ball valve (1) according to any one of claims 1 to 10, characterized by , that the pressure equalization channel (24) is formed by a space extending around the circumference of the valve housing (4) between the valve housing (4) and the distributor pocket (6). [12] Cartridge ball valve (1) according to claim 11, characterized by, that the space forming the pressure equalization channel (24) between the valve housing (4) and the distributor pocket (6) is created by a step-like reduction of the outer circumference of the valve housing (4) and a step-like reduction of the inner circumference of the distributor pocket (6) that is not complementary in the axial direction and is offset. [13] Cartridge ball valve (1) according to any one of claims 1 to 12, characterized by , that the first side wall opening (18) and the opposite pressure equalization opening (23) are sealed by two sealing rings (36, 37) extending over the circumference of the valve housing (4), of which - with respect to the axial direction - one sealing ring (36) is placed above and one sealing ring (37) is placed below the first side wall opening (18) and the opposite pressure equalization opening (23). [14] Cartridge ball valve (1) according to any one of claims 1 to 13, characterized by, that the drive shaft (8) is mounted so as to rotate about its axis of rotation (7) in a shaft bearing (27) inside the valve housing (4), which has a shaft seal (28). [15] Cartridge ball valve (1) according to claim 14, characterized by , that the shaft bearing (27) has a shaft seal (28) which is designed as an X-ring seal. [16] Cartridge ball valve (1) according to any one of claims 1 to 15, characterized by , that the drive shaft (8) and the valve ball (10) are formed together as one part. [17] Use of a cartridge ball valve (1) according to any one of claims 1 to 16 in a refrigerant circuit with a refrigerant selected from the refrigerants R1234yf, R1234a, R404a, R600, R600a, R290, R152a, R32 or mixtures of the aforementioned refrigerants.

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