EP3652005A1

EP3652005A1 - Valve assembly for a refrigerant circuit

Info

Publication number: EP3652005A1
Application number: EP18733849.6A
Authority: EP
Inventors: Jonathan Krost; Tobias Herrmann
Original assignee: Audi AG
Current assignee: Audi AG
Priority date: 2017-07-12
Filing date: 2018-06-21
Publication date: 2020-05-20
Also published as: WO2019011617A1; CN110914081B; CN110914081A; KR102343522B1; US12055229B2; US20200132204A1; DE102017211891A1; KR20200029004A; JP2020526450A; JP6998446B2

Abstract

The invention relates to a valve assembly (10) for a refrigerant circuit, comprising at least two ball valves (20, 30), each of which has a ball (24, 34) as a control element and an actuator (28, 38) for adjusting the associated ball (24, 34). The invention further relates to a refrigerant circuit having heat pump functionality for a vehicle having such a valve assembly (10). According to the invention, the at least two ball valves (20, 30) are each designed as a 3-way valve allowing bidirectional flow and having three connection points (A1, B1, C1, A2, B2, C2), wherein a first ball (24) of a first ball valve (20) has a T-shaped borehole, which permits selective flow through two connection points (A1, B1; A1, C1) of the three connection points (A1, B1, C1) and blocking of one connection point (B1, C1) of the three connection points (A1, B1, C1) or simultaneous flow through the three connection points (A1, B1, C1), and wherein a second ball (34) of a second ball valve (30) has an L-shaped borehole, which permits selective flow through two connection points (A2, B2; A2, C2) of the three connection points (A2, B2, C2) and blocking of one connection point (B2, C2) of the three connection points (A2, B2, C2) or blocking of the three connection points (A2, B2, C2).

Description

Valve arrangement for a refrigerant circuit

The invention relates to a valve arrangement for a cold ittelkreislauf GE measure the genus of claim 1 and a refrigerant circuit with heat pump functionality for a vehicle with such a valve assembly.

Valve arrangements for a refrigerant circuit in a vehicle are known in numerous variations. Such a valve arrangement may comprise, for example, at least two ball valves, each having a ball as an adjusting element and an actuator for adjusting the associated ball. The valve arrangement can be used, for example, in a heat pump system for a vehicle whose coolant circuit comprises a compressor, a condenser, an indirect condenser, a chiller, an evaporator and two expansion elements. Via the valve arrangement with at least two ball valves different operating modes of the refrigerant circuit can be adjusted in electrified vehicles heat pump systems can be used. These have the advantage that the refrigerant circuit can be used to heat the interior of the vehicle. Compared to a vehicle heating by means of an electric auxiliary heater so a heating can be achieved with less electrical power consumption. This results in a greater electrical range. In order to enable the switching between the different functions of the refrigeration circuit, shut-off valves are used. These are used for selective switching between a flow through the condenser for the purpose of cooling function or a flow through an indirect condenser for Heizfunkti- on. In these two operating modes, a sufficient amount of refrigerants To have tel in each active part of the refrigeration circuit available, also a Kältemittelabsaugfunktion is used. In this case, the refrigerant is withdrawn from the respective inactive heat exchanger and fed to the active region of the refrigerant circuit. In the cooling mode, the refrigerant condenser located at the front of the vehicle is flowed through.

At the same time the indirect condenser is sucked through the compressor. In a heating mode, the indirect condenser flows through. At the same time the condenser is sucked through the compressor. To implement this, four shut-off valves are used. These are arranged in a circle and have cable outlets between the valves. The four valves are identical. They work according to a ball-valve principle. Each of the four valves has a ball that has a hole along one axis. The housing has two openings on opposite sides. The ball can be rotated by a servomotor. If the ball is rotated so that its bore is aligned with the openings of the housing, the medium can flow through the valve. If the ball is rotated so that the bore does not overlap the housing openings, the valve is closed; it can then not be flowed through. A disadvantage may be considered that four electric actuators are required to drive the four valves. The use of the four valves and their servomotors is costly. In addition, the weight of the four valves has a negative effect on vehicle consumption. Furthermore, the space required for the four valves is comparatively large. From DE 10 2014 105 097 A1 a generic valve block arrangement for a plurality of valves, in particular expansion and / or shut-off valves is known which comprises a valve block with a plurality of flow paths for fluids and a plurality of adjusting units with associated drive units. The valve block is formed in two parts from a flow path element with the flow paths and from a limiting element. The The boundary element acts as a cover and boundary of the flow paths and further cavities or recesses optionally provided in the flow path element toward the outside. Under an adjustment is a valve with valve body to understand, wherein the valve body is moved via a Ver adjusting element. As adjusting units ball valves are preferably used. In the embodiment of the adjusting units as ball valves, the respective valve body is thus designed as a ball and the adjusting element as a pin-like connection to the ball. The invention is based on the object to provide a valve assembly for a refrigerant circuit and a refrigerant circuit with heat pump functionality for a vehicle with such a valve assembly, the implementation of various functions, in particular functions of a heat pump, in a refrigeration cycle at significantly lower ren costs and lighter weight and smaller space allows.

According to the invention the object is achieved by providing a valve arrangement for a refrigerant circuit having the features of patent claim 1 and by a refrigerant circuit with heat pump functionality for a vehicle having the features of claim 13. Advantageous embodiments and further developments of the invention are specified in the dependent claims.

In order to provide a valve arrangement for a refrigerant circuit, which allows the implementation of various functions, in particular functions of a heat pump, in a refrigeration cycle at significantly lower cost and weight and smaller space, the at least two ball valves, each having a ball as an actuator and an actuator for adjusting the associated ball, in each case as bidirectionally permeable 3-way valve with three terminals ausge- leads. Here, a first ball of a first ball valve has a T-shaped bore, which allows an optional flow through two ports of the three ports and shut off a connection of the three ports or a simultaneous flow through the three ports. A second ball of a second ball valve has an L-shaped bore, which allows an optional passage of two ports of the three ports and a shut-off of a connection of the three ports or shutting off the three ports. In addition, a refrigerant circuit with heat pump functionality for a vehicle is proposed, which comprises a compressor, a condenser, an indirect condenser, a chiller, an evaporator, two expansion elements and a valve arrangement according to the invention with at least two ball valves, via which different operating modes of the refrigerant circuit are adjustable , By embodiments of the valve arrangement according to the invention, it is advantageously possible to represent the different functions of a heat pump with only two ball valves, so that only two actuators are required, which are preferably designed as electric actuators to switch between the various functions of the heat pump. Furthermore, embodiments of the valve arrangement according to the invention advantageously reduce the complexity of the refrigerant circuit. As a result, the refrigerant circuit for the implementation of the heat pump functions can be more robust. A chiller is understood below to mean a coolant-refrigerant heat exchanger which acts as a heat source during a heat pump mode and is used in air-conditioning mode for cooling units such as a battery. In an advantageous embodiment of the valve arrangement according to the invention, the ball valves may each have a valve block with flow channels in which the terminals are formed and the balls can be mounted rotatably. In addition, a first connection block having a first connector may connect a second port of the first ball valve to a second port of the second ball valve, and a second connection block having a second connector may connect a third port of the first ball valve to a third port of the second ball valve. By this arrangement of the ball valves, the various functions of the heat pump can be implemented particularly space-saving.

In a further advantageous embodiment of the valve arrangement according to the invention, the first connection block, the second connection block, the first valve block and the second valve block connected to each other, preferably screwed together. Alternatively, the first connection block, the second connection block, the first valve block and the second valve block can be completely or partially combined in a common fluid block, so that assembly steps can be advantageously saved.

In a further advantageous embodiment of the valve arrangement according to the invention, a first connection of the first ball valve with a first fluid connection of the valve arrangement and a first connection of the second ball valve can be connected to a second fluid connection of the valve arrangement. The first connector may have a third fluid port of the valve assembly and the second connector may have a fourth fluid port of the valve assembly. This results in four fluid connections for the valve arrangement, which are accessible via connection lines. can be connected to the other components of the Kaltel ittelkreislaufs.

In a further advantageous embodiment of the invention Ventilanord- tion, the first ball can have two half-holes and a through hole. In this case, the axes of the two half-bores and the through-bore can preferably each be perpendicular to each other and meet in the center of the ball. Through this design of the first ball, the positioning movements about a rotation axis and the required sealing functions can be implemented particularly easily. Thus, in a first switching position of the first ball valve, which corresponds to a first rotational position of the first ball, the first ball can connect the first port to the second port and shut off the third port and in a second switching position of the first ball valve, which corresponds to a second rotational position corresponds to the first ball, connect the first terminal to the second terminal and to the third terminal and in a third switching position of the first ball valve, which corresponds to a third rotational position of the first ball, connect the first terminal to the third terminal and shut off the second terminal. In addition, the first ball valve can have compensation means, which provide a defined minimum flow cross-section for the fluid flow during a changeover operation between two shift positions. As a result, it is advantageously possible to perform a change of the operating mode of the refrigeration ittelkreislaufs without the compressor must be completely switched off.

In a further advantageous embodiment of the valve arrangement according to the invention, the second ball may have two half-bores. Here, the axes of the two half-holes can be perpendicular to each other and meet in the center of the ball. By this embodiment of the second ball, the adjusting movements about a rotation axis and the required sealing functions be implemented particularly easily. Thus, in a first switching position of the second ball valve, which corresponds to a first rotational position of the second ball, the second ball can connect the first port to the second port and shut off the third port and in a second switching position of the second ball valve, which corresponds to a second rotational position corresponds to the second ball, the first port and the second port and the third port shut off and in a third switching position of the second ball valve, which corresponds to a first rotational position of the second ball, connect the first port to the third port and shut off the second port.

In an advantageous embodiment of the invention Kaltem ittelkreislaufs the first fluid port of the valve assembly with a high-pressure side of the compressor, the second fluid port of the valve assembly can with a suction pressure side of the compressor, the third fluid port of the valve assembly can with the condenser and the fourth fluid port of the valve assembly can with the indirect Capacitor connected. Through this interconnection of the valve arrangement with the two ball valves, all required refrigerant flow directions in the refrigerant circuit can be set with additional heat pump functionality. Thus, for example, via a first combined switching position of the two ball valves, a cooling mode or a second combined switching position of the two ball valves a heating mode of Kältem ittelkreislaufs or via a third combined switching position of the two ball valves simultaneous flow through the capacitor and the indirect capacitor or other combined switching positions the two ball valves, a refrigerant charge or a flushing of different paths of the refrigerant circuit can be adjusted. In addition, the ball valves can be switched in a predetermined order to switch between the operating modes of the refrigeration ittelkreislaufs. Via the first ball valve with the T- shaped bore can be flowed through either the capacitor or the indirect capacitor or both at the same time. The second ball valve with the L-shaped bore allows the extraction of the refrigerant either from the condenser or the indirect condenser or is completely closed. The switching positions of the two ball valves are coordinated so that, for example, no combined switching position of the two ball valves is possible, in which flows through the first ball valve only the indirect capacitor and at the same time the indirect condenser is sucked through the second ball valve. This would cause a short circuit. In addition, a combined switching position of the two ball valves is prevented, in which flows through the first ball valve, only the condenser and at the same time the condenser is sucked through the second ball valve. This would also cause a short circuit. Embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description. In the drawing, like reference numerals designate components that perform the same or analog functions. 1 shows a schematic circuit diagram of an exemplary embodiment of a refrigerant circuit according to the invention for a vehicle with heat pump functionality,

2 shows a schematic circuit diagram of an exemplary embodiment of a valve arrangement according to the invention for the refrigerant circuit of FIG. 1,

3 is a schematic perspective view of the valve assembly according to the invention of FIG. 2 from above, a schematic perspective view of the inventive valve assembly of Figures 2 and 3 from below, a schematic perspective view of a first ball of a first ball valve of the valve assembly according to the invention of FIGS. 2 to 4, and a schematic perspective view of a second ball of a second ball valve Valve arrangement according to the invention from FIGS. 2 to 4.

As can be seen from FIG. 1, a refrigerant circuit 1 for a vehicle with heat pump functionality in the exemplary embodiment shown has a compressor 3, a condenser 5, an indirect condenser 7, a chiller 8, an evaporator 9, two expansion elements EO1, EO2 and a valve arrangement according to the invention 10 with at least two ball valves 20, 30, over which various modes of the refrigerant circuit 1 are adjustable. The individual components of the refrigerant circuit 1 are interconnected as shown.

As can be seen from FIGS. 1 to 6, the valve arrangement 1 0 for the refrigerant circuit 1 in the exemplary embodiment shown has two ball valves 20, 30, which each have a ball 24, 34 as adjusting element and an actuator 28, 38 for adjusting the associated ball 24 34. According to the invention, two ball valves 20, 30 are each designed as a bidirectionally flow-through 3-way valve with three connections A1, B1, C1, A2, B2, C2. Here, a first ball 24 of a first ball valve 20 has a T-shaped bore 26, which is an optional flow through two ports A1, B1; A1, C1 of the three connections A1, B1, C1 and a blocking of a connection B1, C1 of the three connections A1, B1, C1 or a simultaneous one Flow through the three ports A1, B1, C1 allowed. A second ball 34 of a second ball valve 30 has an L-shaped bore 36, which an optional flow through two ports A2, B2; A2, C2 of the three connections A2, B2, C2 and a blocking of a connection B2, C2 of the three connections A2, B2, C2 or a blocking of the three connections A2, B2, C2.

As can be further seen in particular from FIGS. 3 and 4, the ball valves 20, 30 each have a valve block 22, 32 with flow channels, in which the connections A1, B1, C1, A2, B2, C2 are formed and the balls 24, 34 are rotatably mounted. A first connection block 12 with a first T-shaped connection piece 12.1 connects a second connection B1 of the first ball valve 20 to a second connection B2 of the second ball valve 30. In addition, a second connection block 14 connects to a second T-shaped connection piece 14.1 a third connection C1 of FIG first ball valve 20 with a third port C2 of the second ball valve 30. In the illustrated embodiment, the first connecting block 12, the second connecting block 14, the first valve block 22 and the second valve block 32 are bolted together via screw not shown. In alternative embodiments, not shown, the first connection block 12, the second connection block 14, the first valve block 22 and the second valve block 32 may alternatively be completely or partially combined in a common fluid block. As is further apparent from FIGS. 3 and 4, the actuators 28, 38 are designed as servomotors, which are coupled to the balls 24, 34 via shafts (not shown). About the waves of the respective actuator 28, 38, the associated ball 24, 34 rotate about its axis of rotation in the various switching positions. As can also be seen in particular from FIG. 2, in the illustrated exemplary embodiment of the valve arrangement 10, a first connection A1 of the first ball valve 20 is connected to a first fluid connection P1 of the valve arrangement 10. A first connection A2 of the second ball valve 30 is connected to a second fluid connection P2 of the valve arrangement 10. In addition, the first T-shaped connecting piece 12.1 has a third fluid port P3 of the valve arrangement 10, and the second T-shaped connecting piece 14.1 has a fourth fluid port P4 of the valve arrangement 10.

As can also be seen from FIG. 5, the first ball 24 has two half-bores 26.1, 26.2 and a through-bore 26.3. The axes of the two half-bores 26.1, 26.2 and the through-hole 26.3 are each perpendicular to each other and meet in the center of the ball.

As can also be seen from FIG. 6, the second ball 34 has two half-bores 36.1, 36.2. The axes of the two half-bores 36.1, 36.2 are perpendicular to each other and meet in the ball center. As can also be seen from FIG. 2, in a first switching position of the first ball valve 20, the first ball 24 connects the first port A1 to the second port B1 and blocks the third port C1. In a current second switching position of the first ball valve 20, the first ball 24 connects the first port A1 to the second port B1 and to the third port C1. In a third switching position of the first ball valve 20, the first ball 24 connects the first port A1 to the third port C1 and blocks the second port B1. Thus, the first port A1 acts as an intake port, and the second port B1 and the third port C1 each act as an exhaust port. Here, the first port A1 is independent of the switching position with an opening of a first ten half-bore 26.1 connected. The second connection B1 is connected in the first switching position with an opening of a second half-bore 26.2 and in the second switching position with an opening of the through-bore 26.3. The third terminal C1 is connected in the third switching position with the opening of the second half-bore 26.2 and in the second switching position with an opening of the through-bore 26.3.

As is further apparent from FIG. 2, in a first switching position of the second ball valve 30, the second ball 34 connects the first port A2 to the second port B2 and blocks the third port C2. In a current second switching position of the second ball valve 30, the second ball 34 blocks the first port A2 and the second port B2 and the third port C2. In a third switching position of the second ball valve 30, the second ball 34 connects the first port A2 to the third port C2 and blocks the second port B2.

As can also be seen from FIG. 1, the first fluid connection P1 of the valve arrangement 10 is connected to a high-pressure side of the compressor 3. The second fluid port P2 of the valve arrangement 10 is provided with a suction pressure side of the compressor 3, wherein a check valve RSV is arranged between the second fluid port P2 and the compressor 3. The third fluid port P3 of the valve assembly 10 is connected to a first port of the condenser 5. The fourth fluid connection P4 of the valve arrangement 10 is connected to a first connection of the indirect capacitor 7. As can also be seen from FIG. 1, a second connection of the capacitor 5 is connected via a check valve RSV to a first connection of the expansion element EO, which is designed as an expansion valve. A second connection of the indirect capacitor 5 is likewise connected via a check valve RSV to the first connection of the expansion element EO. A second connection of the expansion organ EO is with connected to a first port of the evaporator. A second port of the evaporator 9 is connected to the suction pressure side of the compressor 3.

Via a first combined switching position of the two ball valves 20, 30, in which the first ball valve 20 is in its first switching position, and the second ball valve 30 is in its third switching position, a cooling mode of the Kaltem ittelkreislaufs 1 is set. Therefore, in the cooling mode, the first port of the condenser 5 is connected to and flows through the high pressure side of the compressor 3. At the same time, the first port of the indirect condenser 7 is connected to the suction pressure side of the compressor 3 and exhausted by this compressor. Alternatively, via a second combined switching position of the two ball valves 20, 30, in which the first ball valve 20 is in its third switching position, and the second ball valve 30 is in its first switching position, a heating mode of the Kaltem ittelkreislaufs 1 set. Therefore, in the heating mode, the first port of the indirect condenser 7 is connected to and flows through the high-pressure side of the compressor. At the same time, the first port of the condenser 5 is connected to the suction pressure side of the compressor 3 and exhausted by the same. Via a third combined switching position of the two ball valves 20, 30, in which the first ball valve 20 is in its second switching position, and the second ball valve 30 is also in its second switching position, a simultaneous flow through the capacitor 5 and the indirect capacitor. 7 set. By means of further combined switching positions of the two ball valves 20, 30, it is possible to set a refrigerant charge or a flushing of different paths of the cold-off-line circuit 1. In order to avoid unwanted combined switching states of the two ball valves 20, 30, the ball valves 20, 30 are switched in a predetermined order in order to switch between the operating modes of the refrigeration ittelkreislaufs 1. Preferably, the combined Switch positions of the two ball valves 20, 30 so matched to each other, for example, that no combined switching position of the two ball valves 20, 30 is possible, in which flows through the first ball valve 20, only the indirect capacitor 7 and at the same time the indirect condenser 7 sucked off via the second ball valve 30 is, or in which via the first ball valve 20, only the capacitor 5 flows through and at the same time the condenser 5 is sucked off via the second ball valve 30. In an advantageous manner, embodiments of the cold-pressing circuit 1 make it possible to change the operating mode without the compressor 3 having to be switched off. For this purpose, the first ball valve 20 balancing means not shown in detail, which provide a defined minimum flow cross-section for the fluid flow during a switching between two switching positions available. Thus, the first ball 24, for example, between the opening of the second half-bore 26.2 and the openings of the through hole 26.3 have bypass channels, which are introduced as grooves and / or notches in a jacket of the first ball 24. As a result, at least one defined minimum flow cross-section for the fluid flow is ensured during the ball rotation from the first switching position via the second switching position to the third switching position and vice versa at each instant. The bypass channels in this case fluidly connect the two openings of the through hole 26.3 with the opening of the second half-bore 26.2. By varying the depth and / or width of the bypass channels, the effective minimum flow cross-section during the rotation process can be influenced. Additionally or alternatively, at least the openings of the through-bore 26.3 and the opening of the second half-bore 26.2 each have a larger diameter than the second terminal B1 and the third terminal C1. In addition to the two constructional measures just described, from the system point of view instead of a complete shutdown of the compressor 3, it is possible to reduce the power of the compressor 3 when the compressor 3 is switched off. To limit switching operations and thus despite narrowed flow cross section with the compressor running 3 no inadmissible high pressure peaks in the system to produce. Now, the change from the cooling mode to the heating mode will be described by way of example. As already stated above, is located in the cooling mode of the refrigeration ittel circuit 1, the first ball valve 20 in its first switching position and the second ball valve 30 is in its third switching position. As a result, the condenser 5 flows through and the indirect condenser 7 is sucked off. Now, the second ball valve 30 is switched to its second switching position, in which all ports A2, B2, C2 of the second ball valve are shut off, so that no further refrigerant is sucked. Then, the first ball valve 20 is switched to its second switching position, in which the capacitor 5 and the indirect capacitor 7 can be flowed through. Subsequently, the first ball valve 20 is switched to its third switching position, in which only the indirect capacitor 7 is flowed through. Then, the second switching valve 30 is switched to its first switching position, in which the condenser 5 is sucked off.

LIST OF REFERENCE NUMBERS

1 refrigerant circuit with heat pump functionality

3 compressors

5 capacitor

7 indirect capacitor

8 chillers

9 evaporator

10 valve arrangement

12 first connection block

12.1 first connector

14 second connection block

14.1 second connector

20 first ball valve

22 first valve block

24 first ball

26 T-shaped bore

26.1 first half hole

26.2 second half-bore

26.3 Through hole

28 first actuator

A1, B1, C1 valve connection

30 second ball valve

32 second valve block

34 second ball

36 L-shaped bore

36.1 first half-hole

36.2 second half hole

38 second actuator A2, B2, C2 Valve connection P1, P2, P3, P4 Fluid connection EO1, EO2 Expansion element RSV Check valve

Claims

claims

1 . Valve arrangement (10) for a refrigerant circuit (1), with at least two ball valves (20, 30), each having a ball (24, 34) as an adjusting element and an actuator (28, 38) for adjusting the associated ball (24, 34 ), characterized in that the at least two ball valves (20, 30) each have a bidirectionally flowable 3-way valve with three connections (A1, B1, C1, A2, B2,

C2), wherein a first ball (24) of a first ball valve (20) has a T-shaped bore (36), which allows an optional flow through two ports (A1, B1; A1, C1) of the three ports (A1, B1, C1) and a shut-off of one terminal (B1, C1) of the three terminals (A1, B1, C1) or a simultaneous passage of the three terminals (A1, B1, C1), and wherein a second ball (34) of a second Ball valve (30) has an L-shaped bore (36), which is an optional flow through two terminals (A2, B2, A2, C2) of the three terminals (A2, B2, C2) and a shut-off of a terminal (B2, C2) the three connections (A2, B2,

C2) or shutting off the three connections (A2, B2, C2).

2. Valve arrangement (10) according to claim 1, characterized in that the ball valves (20, 30) each comprise a valve block (22, 32) with flow channels, in which the connections (A1, B1, C1,

A2, B2, C2) are formed and the balls (24, 34) are rotatably mounted.

Valve arrangement (10) according to claim 1 or 2, characterized in that a first connection block (12) with a first connection connecting piece (12.1) connects a second connection (B1) of the first ball valve (20) with a second connection (B2) of the second ball valve (30), and a second connection block (14) with a second connection piece (14.1) connects a third connection (C1 ) of the first ball valve (20) connects to a third port (C2) of the second ball valve (30).

Valve arrangement (10) according to claim 3, characterized in that the first connecting block (12), the second connecting block (14), the first valve block (22) and the second valve block (32) connected to each other or completely or partially in a common fluid block are summarized.

Valve arrangement (10) according to claim 3 or 4, characterized in that a first connection (A1) of the first ball valve (20) with a first fluid port (P1) of the valve assembly (10) and a first port (A2) of the second ball valve (30 ) is connected to a second fluid port (P2) of the valve assembly (10), and the first connector (12.1) has a third fluid port (P3) of the valve assembly (10) and the second connector (14.1) has a fourth fluid port (P4) of the valve assembly (14). 10).

Valve arrangement (10) according to one of claims 1 to 5, characterized in that the first ball (24) has two half-bores (26.1, 26.2) and a through-bore (26.3).

Valve arrangement (10) according to claim 6, characterized in that the axes of the two half-bores (26.1, 26.2) and the through hole (26.3) each perpendicular to each other and meet in the middle of the ball.

8. Valve arrangement (10) according to claim 6 or 7, characterized in that the first ball (24) in a first switching position of the first ball valve (20) connects the first port (A1) with the second port (B1) and the third terminal (C1) shuts off and connects in a second switching position of the first ball valve (20) the first port (A1) with the second port (B1) and with the third port (C1) and in a third switching position of the first ball valve (20) connecting the first terminal (A1) to the third terminal (C1) and shutting off the second terminal (B1).

9. Valve arrangement (10) according to claim 8, characterized in that the first ball valve (20) has compensation means, which provide a defined minimum flow cross section for the fluid flow during a switching between two switching positions. O.Valve arrangement (10) according to one of claims 1 to 9, characterized in that the second ball (34) has two half-bores (36.1, 36.2).

1 1 .Ventilanordnung (10) according to claim 10, characterized in that the axes of the two half-bores (36.1, 36.2) are perpendicular to each other and meet in the ball center.

12. Valve arrangement (10) according to claim 10 or 1 1, characterized in that the second ball (34) in a first switching position of the second ball valve (30) connects the first port (A2) with the second port (B2) and the third Port (C2) shuts off and in a second switching position of the second ball valve (30) the first ten terminal (A2) and the second terminal (B2) and the third terminal (C2) shuts off and in a third switching position of the second ball valve (30) connects the first terminal (A2) to the third terminal (C2) and the second terminal ( B2) shut off.

13. A refrigerant circuit (1) with heat pump functionality for a vehicle, comprising a compressor (3), a condenser (5), an indirect condenser (7), a chiller (8), an evaporator (9), two expansion elements (EO1, EO2 ) and a valve arrangement (10) with at least two ball valves (20, 30), via which different operating modes of the refrigerant circuit (1) are adjustable, characterized in that the valve arrangement (10) according to at least one of the claims 1 to 12 is formed.

14. refrigerant circuit (1) according to claim 13, characterized in that the first fluid port (P1) of the valve assembly (10) with a high pressure side of the compressor (3), the second fluid port (P2) of the valve assembly (10) with a suction pressure side of the compressor (3), the third fluid port (P1) of the valve assembly (10) to the condenser (5) and the fourth fluid port (P4) of the valve assembly (10) is connected to the indirect capacitor (7).

15. Refrigerant circuit (1) according to claim 14, characterized in that via a first combined switching position of the two ball valves (20, 30) a cooling mode or a second combined switching position of the two ball valves (20, 30) a heating mode of the refrigerant circuit (1 ) or via a third combined switching position of the two ball valves (20, 30) a simultaneous flow through the condenser (5) and the indirect condenser (7) or via further combined switching positions of the two ball valves (20, 30) a cold filling or flushing of different ways of the refrigeration ittel circulation (1) is adjustable.

16. cold ittel circuit (1) according to claim 15, characterized in that the ball valves (20, 30) are switchable in a predetermined order in order to switch between the operating modes of the refrigeration ittel circuit (1).