PROPORTIONAL VALVE ARRANGEMENT FOR REFRIGERANT

Description

Technical field

[0001] The invention relates to a proportional valve arrangement for refrigerants, comprising a valve housing having a valve body chamber, a valve body which is arranged within the valve body chamber and is designed to be transferable between a first position and a second position.

[0002] Such proportional valve arrangements are used, for example, in the fluid systems of at least partially electrically powered motor vehicles. These proportional valves are also called continuous valves or directional control valves, and high demands are placed on their performance, particularly in the automotive sector.

[0003] For example, the fluids can be in a liquid or gaseous state. Furthermore, very high internal tightness requirements apply, both in the liquid and gaseous states of the fluid. These tightness requirements also apply to the external environment. Consequently, the proportional valve arrangement must meet the constraints that there is no pressure-relieved connection at the valve and that no reliable pressure relief can occur.

[0004] With large piston diameters, particularly large pressure differentials in valves often result in large axial hydraulic or pneumatic forces acting on the piston. This necessitates large actuation forces to operate the valves. This is usually achieved by actuators of a corresponding size and corresponding force. <osten.

[0005] Proportional valve assemblies are described in the prior art, for example, in EP 2 700 853 A1, EP 0 907 045 A1, JP 2013 221578 A, EP 0 058 559 A1 (according to the preamble of claim 1), and US 2008 / 245428 A1. The valve bodies of these proportional valve assemblies are subject to high wear, which increases maintenance requirements. Description of the invention

[0006] The object of the invention is to provide a valve device belonging to the aforementioned technical field which at least partially overcomes the disadvantages of the prior art. In particular, the object of the invention is to propose a valve device which reduces the high actuating forces required for valves with large cross-sections.

[0007] The solution to the problem is defined by the features of claim 1. The invention relates to a proportional valve arrangement for refrigerants, comprising a valve housing having a valve body chamber, a valve body which is arranged within the valve body chamber and is designed to be movable between a first position and a second position, wherein the valve housing has a first sealing seat and a second sealing seat, and the valve body is movable between the first sealing seat and the second sealing seat.

[0008] Valves are generally used to shut off and / or control the flow of a fluid. Simpler valves can only be controlled discretely. This means they can only be switched on / off, i.e., only opened and closed. However, simply opening and closing the valve is no longer sufficient for many applications. For example, their use as expansion valves in battery cooling, air conditioning, or heat pump systems to create a defined and controllable pressure drop between the condenser (heat dissipation) and evaporator (cooling) often requires more continuous switching. Therefore, continuous switching is frequently required. Such continuous or steady switching can be achieved, for example, using proportional valves, which allow for a smooth transition between switching positions. This makes the fluid flow rate adjustable.Such proportional valves, with the help of a proportional magnet, not only allow discrete switching positions, but also a continuous transition of the valve opening.

[0009] A refrigerant within the meaning of the invention is to be understood as a fluid which is used for heat transfer in a refrigeration system and which absorbs heat at low temperature and low pressure and releases heat at higher temperature and higher pressure, usually involving changes in the state of the fluid.

[0010] This results, for example, in the technical advantage that the proportional valve assembly can precisely assume any position of the valve body between the first and second sealing seats. This leads to the further advantage that the proportional valve assembly can be switched continuously and the flow rate can be precisely controlled. In addition, a stepper motor, for example, is suitable as a drive for the proportional valve assembly, thus eliminating the need for a return spring or similar mechanism to close the proportional valve assembly.

[0011] According to the invention, the valve body has a spherical section which is arranged to move between the first and second sealing seats. This offers the technical advantage, for example, that optimal sealing is always ensured in both the first and second sealing seats. The symmetry of the spherical body results in operation with minimal wear, since the orientation of the valve body when entering the first or second sealing seat is independent of its function. In other words, the spherical seat ensures a seal even if the valve body is misaligned. For example, both the spherical section of the valve body and the sealing seat are made of a metallic material. Aluminum or stainless steel are suitable materials for both the sealing seat and the spherical valve body.An additional advantage is that there are only very small contact surfaces between the spherical valve body and the sealing seat. This further reduces wear and improves the tightness and sealing reliability of the proportional valve assembly.

[0012] In the invention, the valve body comprises a first guide section and a second guide section for guiding the valve body in the valve housing, with the spherical section arranged between the first and second guide sections. This achieves, for example, the technical advantage of enabling precise guidance of the valve body and preventing tilting of the valve body. This also leads to a further reduction in wear and thus to a longer service life of the proportional valve assembly.

[0013] In a particularly preferred embodiment, a first gap is formed between the first guide section and the spherical section. This gap is formed by making the diameter of the valve body in this section smaller than in the first guide section or in the spherical section. This reduced diameter creates a first gap that can accommodate fluid and facilitates flow around the valve body between two adjacent ports. Additionally, the first gap increases the pressure-bearing surface area of ​​the spherical section.

[0014] According to a particularly preferred embodiment, in a state where the valve body rests against the first sealing seat, an axial projection surface of the first gap in the direction of the first guide section has the same size as an axial projection surface of the first gap in the direction of the spherical section. In other words, the diameter of the first sealing seat is identical to the diameter of the first guide section. This results, for example, in the technical advantage that the axial components of the projection surfaces are identical in this state, resulting in a balanced force equilibrium of the valve body in the axial direction under fluid pressure. This force equilibrium, in turn, simplifies the actuator's operation to move the valve body or to transfer it from a first position to a second position.

[0015] Another consequence arises in the event of a power failure or a defect in the actuator. In such a case, the valve body would remain in its position, as it would not be returned to a rest or closed position by a return spring.

[0016] In a further particularly preferred embodiment, a second space is formed between the second guide section and the spherical section. This space is also formed by making the diameter of the valve body in this section smaller than in the second guide section or in the spherical section. This reduced diameter creates a first space that can accommodate fluid and facilitates flow around the valve body between two adjacent ports. Additionally, the second space increases the pressure-bearing surface area of ​​the spherical section.

[0017] According to another embodiment, in a state in which the valve body rests against the second sealing seat, an axial projection surface of the second gap in the direction of the spherical section has the same size as an axial projection surface of the second gap in the direction of the second guide section.

[0018] In other words, the diameter of the first sealing seat is identical to the diameter of the second guide section. This offers the technical advantage, for example, that the axial components of the projection surfaces are identical in this state, resulting in a balanced force equilibrium of the valve body in the axial direction under fluid pressure. This force balance, in turn, simplifies the actuator's movement of the valve body or its transfer from a first position to a second position. In conjunction with a pressure bypass, pressure equalization can also occur within the proportional valve assembly. Overall, the proportional valve assembly is therefore pressure and <raftausgeglichen. Die Druckausgeglichenheit wird hierbei durch den Druckbypass und die druckbeaufschlagte Flächengleichheit erzielt, während sich die I<raftausgeglichenheit beispielsweise durch das nicht vorhandene Rückstellelement ergibt.

[0019] Even in this configuration, in the event of a power failure or a defect in the drive, the consequence is that the valve body would remain in its position, since it is not moved into a rest or closed position by a return spring.

[0020] In a particular embodiment, the valve body has an inlet port, a first outlet port, and a second outlet port. This offers the technical advantage, for example, of making the proportional valve arrangement more flexible and versatile. For instance, the proportional valve arrangement can be configured as a 3 / 2-way valve. In this case, the proportional valve arrangement would have, for example, three ports arranged side by side. By moving the valve body from the first sealing seat to the second sealing seat, fluid from the inlet port can flow into both the first outlet port and / or the second outlet port. Particularly in conjunction with the force-balanced configuration of the aforementioned embodiments, the additional advantage arises that the valve body can be easily actuated regardless of its position between the first and second sealing seats.This also applies regardless of the fluid pressure at the inlet and outlet ports. In other words, the valve body is force-balanced and therefore easily adjustable for an actuator, irrespective of the pressure at each inlet and outlet port. For example, this configuration of a 3 / 2-way valve can also be extended to other configurations.

[0021] To improve the force compensation of the valve piston, the proportional valve arrangement features a pressure bypass that connects the second outlet port to the valve body chamber. This achieves the technical advantage, for example, that pressure compensation through the piston is possible symmetrically and without an external bypass. This allows for a compact design and particularly simple manufacturing.

[0022] In another embodiment, the pressure bypass has a communication link through the valve body. For example, the communication link extends along the geometric longitudinal axis of the valve body. This achieves the technical advantage, for instance, that the refrigerant can flow directly through the valve body. This results in simple and symmetrical pressure equalization of the refrigerant, which in turn enables a force-balanced configuration of the valve piston. At the same time, this allows for simple and cost-effective manufacturing of the pressure bypass.

[0023] The proportional valve arrangement preferably features an electrically actuated drive for proportionally actuating the valve body. This offers the technical advantage, for example, of enabling continuous adjustment of the valve body. The drive may, for instance, include a stepper motor. The stepper motor does not require much force because of the force compensation provided by the valve piston. The use of an electric drive is also advantageous in the event of a defect or power failure. In such a case, the valve body remains in its last position and, due to the absence of a return spring and the prevailing self-locking mechanism, is not moved to an end position or a desired position.

[0024] According to another particular embodiment, the drive is at least partially arranged within the valve body chamber. For example, the rotor and the spindle driven by the rotor are located inside the valve body chamber. This achieves the technical advantage, for instance, of enabling a very compact design. Additionally, leakage and ingress can be effectively reduced because the rotor and spindle are integrated within the valve body chamber, thus requiring fewer seals and interfaces.

[0025] In a particular embodiment, the drive comprises a stepper motor connected to the valve body via a spindle. This achieves, for example, the technical advantage of enabling direct and precise adjustment of the valve body. If the power supply fails or the stepper motor malfunctions, the valve body remains in its last position.

[0026] In a further advantageous embodiment, the spindle is self-lockingly connected to a hollow shaft. In mechanics, self-locking describes the resistance caused by friction against slippage or rotation of two adjacent bodies. Self-locking is influenced by the angle of inclination, the surface roughness of the contact surfaces, the material pairing, the lubricant, and temperature. The hollow shaft is rigidly connected to the valve housing, with the spindle interacting with the hollow shaft via a thread. The rotation of the drive is transmitted to the spindle, thereby changing its axial position. The self-locking is achieved by the thread between the hollow shaft and the spindle, which, for example, provides the technical advantage that the valve body remains unaffected even under pressure differentials.

[0027] According to a further variant, the invention relates to a proportional valve arrangement for refrigerants with a valve housing having a valve body chamber, a valve body which is arranged within the valve body chamber and is designed to be transferable between a first sealing seat and a second sealing seat, an electrically actuated drive which is connected to the valve body via a spindle, wherein a closing device for generating an axial preload between the valve body and the first sealing seat when the valve body is in contact with the first sealing seat and an axial preload between the valve body and the second sealing seat when the valve body is in contact with the second sealing seat is arranged between the spindle and the valve body.

[0028] This results, for example, in the technical advantage that the proportional valve assembly can precisely assume any position of the valve body between the first and second sealing seats. This leads to the further advantage that the proportional valve assembly can be switched continuously and the flow rate can be precisely controlled. In addition, the closing device generates an axial preload both when the valve body is in contact with the first and second sealing seats, thus ensuring a high degree of closing reliability. A further advantage arises, particularly in conjunction with the spindle, when it moves the valve body into an end position. Here, the closing device prevents the valve body from jamming in the sealing seat in the end position. Thus, the closing device improves the function and service life of the proportional valve assembly.

[0029] In a preferred embodiment, the valve body has a stepped installation space for accommodating the spindle and the closing device. This achieves, for example, the technical advantage of a particularly compact proportional valve assembly. The spindle and closing device are at least partially integrated into the valve body. The stepped installation space is easy to manufacture, and the assembly of the proportional valve assembly is simplified.

[0030] According to a preferred embodiment, the closing device comprises a spring element arranged coaxially with respect to the spindle. This achieves, for example, the technical advantage of a more compact proportional valve arrangement. The spring element of the closing device performs a dual function. On the one hand, the spring element is designed to generate an axial preload between the valve body and the spindle when the valve body comes into contact with the first sealing seat. Simultaneously, the spring element is designed to generate an axial preload between the valve body and the spindle when the valve body comes into contact with the second sealing seat.

[0031] According to a further advantageous embodiment, the spring element is designed to create an axial preload between the spindle and a first stop of the stepped installation space. This achieves, for example, the technical advantage that the spindle can continue to move at least partially in the axial direction against the preload of the spring element even after the valve body has come into contact with the second sealing seat. This establishes a defined closing pressure of the valve body in the seat. Due to the coaxial arrangement of the spring element with the spindle, the axial movement of the spindle is dampened, thus preventing the valve body from jamming in its final position.

[0032] According to an additional embodiment, the spring element is designed to create an axial preload between the spindle and a second stop in the stepped installation space. This achieves, for example, the technical advantage that the spindle can continue to move at least partially in the axial direction against the preload of the spring element, even after the valve body has come into contact with the first sealing seat. Due to the coaxial arrangement of the spring element with the spindle, the axial movement of the spindle is also dampened in the opposite direction, thus preventing jamming in the opposite end position of the valve body and establishing a defined closing pressure of the valve body in the seat.

[0033] In a further advantageous embodiment, the spindle is self-lockingly connected to a hollow shaft. In mechanics, self-locking describes the resistance caused by friction against slippage or rotation of two adjacent bodies. Self-locking is influenced by the angle of inclination, the surface roughness of the contact surfaces, the material pairing, the lubricant, and temperature. The hollow shaft is rigidly connected to the valve housing, with the spindle interacting with the hollow shaft via a thread. The rotation of the drive is transmitted to the spindle, thereby changing its axial position.The self-locking mechanism is achieved through the thread between the hollow shaft and the spindle, which, for example, offers the technical advantage that even under pressure and I <raftunterschieden kein Verstellen des Ventilkörpers stattfindet, auch wenn der Antrieb in einer beliebigen Hubstellung unbestromt geschaltet wird.

[0034] According to an additional advantageous embodiment, the valve body has an inlet port and at least one outlet port. For example, the valve body has one inlet port and at least two outlet ports. Additional ports for inlet or outlet flow are also conceivable. This achieves, for example, the technical advantage of making the proportional valve arrangement more flexible and versatile. For example, the proportional valve arrangement is designed as a 3 / 2-way valve. Thus, the proportional valve arrangement would have, for example, three ports arranged side by side. By moving the valve body from the first sealing seat to the second sealing seat, fluid from the inlet port can flow into both the first outlet port and / or the second outlet port.This also applies regardless of the fluid pressure at the inlet and outlet ports. In other words, the valve body is force-balanced and therefore easily adjustable for an actuator, irrespective of the pressure at each inlet and outlet port. For example, this configuration of a 3 / 2-way valve can also be extended to other configurations.

[0035] In a further particularly advantageous embodiment, the proportional valve arrangement features a pressure bypass that connects the outlet port to the valve body chamber. This achieves, for example, the technical advantage that pressure equalization through the piston is possible symmetrically and without an external bypass. This allows for a compact design and enables the particularly simple and cost-effective manufacture of a force-balanced proportional valve arrangement. The effective pressurized surfaces on the valve body are designed such that the surfaces that move the actuator to the right are the same size as the surfaces that pressurize it to the left. The bypass results in the same pressure (pressure-balanced) on the surfaces on both sides, thus achieving force equilibrium on the actuator.This design, in conjunction with a stepper motor and therefore the absence of a return element, results in a completely force-balanced system, so that the self-locking mechanism has to withstand no or only very slight forces.

[0036] According to a further embodiment, the pressure bypass has a communication link through the valve body. For example, the communication link extends along the geometric longitudinal axis of the valve body. This achieves, for instance, the technical advantage that the refrigerant can flow directly through the valve body. This results in simple and symmetrical pressure equalization of the refrigerant, which overall enables the force-balanced configuration of the valve piston.

[0037] According to a further preferred embodiment, the stepped installation space for accommodating the spindle and the closing device is arranged in the communication link of the valve body. This offers, for example, the technical advantage that the proportional valve arrangement is particularly compact and space-saving. An additional advantage is that the stepped installation space is part of the communication link for pressure equalization, whereby at least part of the spindle and the closing device are directly integrated into the bypass and can flow around the fluid.

[0038] According to an additional embodiment, the valve body has a spherical section that is positioned to move between the first and second sealing seats. This offers the technical advantage, for example, that optimal sealing is always ensured in both the system at the first and second sealing seats. The symmetry of the spherical body results in operation with minimal wear, since the orientation of the valve body when entering the first or second sealing seat is independent of its function. In other words, the spherical seat ensures a seal even if the valve body is misaligned. For example, both the spherical section of the valve body and the sealing seat are made of a metallic material. Aluminum or stainless steel are suitable materials for both the sealing seat and the spherical valve body.An additional advantage is that there are only very small contact surfaces between the spherical valve body and the sealing seat. This further reduces wear and improves the tightness and sealing reliability of the proportional valve assembly.

[0039] To achieve the most precise adjustment of the valve body, the drive is designed for proportional actuation of the valve body. This offers the technical advantage, for example, of enabling continuous adjustment of the valve body. The drive typically incorporates a stepper motor. The stepper motor requires minimal force due to the force compensation provided by the valve piston. The use of an electric drive is also advantageous in the event of a malfunction or power outage. In such a case, the valve body remains in its last position and, due to the lack of a return spring and the inherent self-locking mechanism, is not moved to an end position or a desired position. This results in the additional benefit that energy can be saved by switching off the stepper motor at any stroke position.This is advantageous, for example, compared to solutions operated with a proportional magnet, because a proportional magnet requires a constant energy supply to maintain a specific position of the valve body. Therefore, using a stepper motor saves energy, which is particularly important in electromobility.

[0040] In an additional embodiment, the drive is at least partially arranged within the valve body chamber. For example, the rotor and the spindle driven by the rotor are located inside the valve body chamber. This achieves the technical advantage of enabling a very compact design. Furthermore, leakage and ingress can be effectively reduced because the rotor and spindle are integrated within the valve body chamber, thus requiring fewer seals and interfaces.

[0041] According to an additional embodiment, the drive includes a stepper motor. This achieves, for example, the technical advantage of enabling direct and precise adjustment of the valve body. For instance, the stepper motor is directly connected to the valve body via a spindle.

[0042] Another variant relates to a directional control valve, preferably for refrigerants, with at least two switching positions, comprising a valve housing and a valve piston axially displaceable within the valve housing along a longitudinal axis, as well as an actuator axially moving the valve piston. The valve housing has radial ports, with two working ports provided, between which a pressure port is arranged, and the valve piston is pressure-balanced.

[0043] A first embodiment relates to a directional control valve, preferably for refrigerants, with at least two switching positions, comprising a valve housing and a valve piston axially displaceable in the valve housing along a longitudinal axis, as well as an actuator axially moving the valve piston, wherein the valve housing has radial connections, wherein two working connections are provided, between which a pressure connection is arranged, wherein the valve piston is designed to be pressure-balanced.

[0044] According to an advantageous embodiment, the valve piston has a spherical section, wherein the spherical section can be applied to the valve housing to seal the respective, unpressurized working port against the pressure port.

[0045] According to another embodiment, a second seal is provided for mutual sealing of the working connections.

[0046] According to another embodiment, the second seal is provided as a double-acting rod seal or comprises two single-acting rod seals.

[0047] According to a further embodiment, an assembly acting in both directions of actuation of the valve piston is provided in a stepped installation space, wherein the assembly comprises a coil spring which can be applied to two abutments.

[0048] According to another embodiment, a stop geometry is provided to limit the stroke of the directional control valve to a predetermined number of revolutions.

[0049] According to another embodiment, a reduction gear is provided for sensing an axial position of a drive spindle of the drive.

[0050] Further advantageous embodiments and combinations of features of the invention can be derived from the following detailed description and the entirety of the patent claims. Brief description of the drawings

[0051] The drawings used to illustrate the exemplary embodiment show: Fig. 1 a side view of a directional control valve according to the present invention; Fig. 2 a longitudinal section of the directional control valve according to Fig. 1 Fig. 3 shows a longitudinal section of a directional control valve according to a second embodiment; Fig. 4 shows a longitudinal section of a partial view of a proportional valve arrangement; Fig. 5 shows an enlarged partial view of a proportional valve arrangement; and Figs. 6A, 6B, 6C show further partial views of a proportional valve in various switching positions.

[0052] Basically, identical parts in the figures are marked with the same reference symbols. Ways to implement the invention

[0053] Figure 1Figure 1 shows a 3 / 2-way valve 1 according to the invention in a side view. The directional control valve 1 is used, for example, as a refrigerant valve in a fluid system of a vehicle that is at least partially electrically powered. The directional control valve 1 has two switching positions and comprises a valve housing 2 and a valve piston 3 that is axially displaceable in the valve housing 2 along a longitudinal axis, as well as an actuator 4 that moves the valve piston axially. This actuator 4 is, for example, formed by a motor 5 and has a hollow shaft 6 in which a central drive spindle 7 is arranged. The hollow shaft 6 is arranged in a drive housing 8, which is sealedly connected to the valve housing 2. The drive spindle 7 is driven by a rotor 9 of the motor 5, so that a rotational movement of the drive spindle 7 enables an axial movement of the valve piston 3.The valve body 2, which is arranged in a housing 10, has three radial ports B, A, and C, with two working ports B and C being provided, between which a pressure port A is arranged. With large piston diameters, valves often experience large axial hydraulic / pneumatic forces acting on the valve piston 3, especially under large pressure differentials. This necessitates large actuation forces, which in turn must be provided by a correspondingly large actuator. Since none of the working ports B and C can be pressure-relieved, it must be ensured that the resulting forces on the valve piston 3, which move it in a first actuation direction, are equal to the forces that move it in a second, opposite actuation direction. The valve piston 3 is therefore pressure-balanced.This makes it possible to move the valve piston 3 with minimal force, regardless of the pressure requirements in the valve. This is achieved through the shape of the valve piston 3 and an internal connection between its two end faces. Pressure equalization of the valve piston 3 is realized through a nested bushing design. This allows the use of a valve piston 3 with a larger diameter in the central area (A-port). Its symmetry allows it to form a seat in each direction of actuation. This ensures that a force equilibrium (pressure equalization) exists both when the valve piston is in contact with seat A / B and seat A / C.

[0054] As can be seen in particular from the longitudinal section according to Figure 2As can be seen, the valve piston 3 has a spherical section 11, which can be applied to the valve housing 2 to seal the respective, unpressurized working port B or C against the pressure port A. In other words, the directional control valve 1 has a ball seat to provide the required high level of tightness. The spherical sealing element (section 11) reliably seals its respective seat on the valve housing 2, even if geometric defects are present or the valve piston 3 is misaligned due to play. Since the valve piston 3 is pressure-balanced, a second seal is required on the valve piston 3 to separate the two working ports B and C, preventing any medium from flowing from the first working port B to the second working port C via the pressure-balanced connection of the valve piston 3.This seal is a double-acting rod seal 12 or two single-acting rod seals arranged accordingly. The rod seal 12, which is characterized by minimal leakage and low actuation forces when moving the valve piston 3, may additionally have a plastic ring. A defined preload (axial force) in the seat is required for the reliable closing of the two valve seats. Since the drive via the drive spindle 7 inherently provides no elasticity during insertion into the seat, and this can lead to system preload, an additional assembly 13 acting in both directions of actuation is provided. This assembly is characterized by a coil spring 14 and a stepped installation space 15. The stepped installation space 15 allows for the creation of two abutments against which the installed assembly 13 can be supported.This results in the same axial force acting on the respective valve seat in both actuation directions, depending on the spindle pitch of spindle 8 and the spring constant, after the valve piston 3 is in contact with the seat surface. Additionally, this can reduce the cost of individual components, as the elastic component compensates for cost-relevant influences such as component tolerances.

[0055] Figure 3Figure 1 shows a longitudinal section of a second embodiment of a directional control valve 1 according to the invention. This embodiment is fundamentally identical in construction to the first embodiment. Therefore, only the differences are described. To limit the stroke of the directional control valve 1 to a defined number of revolutions, a stop geometry is used, which is implemented by two interlocking spiral bodies 16, 17. To sensing the axial position of the drive spindle 8, a reduction gear (cycloidal gear 18) is provided. This gear is characterized by a very high reduction ratio. Thus, with the correct selection of the reduction ratio, the total number of revolutions can be reduced to exactly one revolution (max. 360°) on a roller disc 19 (output disc).The absolute position can now be detected by means of a 2-pole magnetic target 20 mounted on the roller disc 19 and a 360° measuring Hall element positioned at the front, which is not shown. The cycloidal gear 18 also includes a cam disc 21, an eccentric 22, a cycloidal disc 23 and a spring 24.

[0056] The Figure 4 shows a longitudinal section of a partial view of a proportional valve arrangement 100, which corresponds to the directional control valve 1 according to the Figure 1 , 2 and 3The proportional valve assembly 100 is suitable for use with refrigerants and comprises a valve housing 110 with a valve body chamber 105 for receiving a valve body 3, 120. The valve body 120 is designed to move continuously within the valve body chamber 105 – like a proportional valve. An electrically actuated actuator 160 in the form of a stepper motor is provided for proportionally actuating the valve body 120 of the proportional valve assembly 100. The rotor 9, 161 of the stepper motor is arranged in the valve body chamber 105, while the stator 162 is arranged outside the valve body chamber 105.

[0057] The actuator 160 drives a spindle 7, 170, which is connected to a hollow shaft 164 via a self-locking thread. The hollow shaft 164, in turn, is connected to the valve body 120 and guides the valve body 120 translationally. The valve body 120 has a spherical section 11, 122, which can be moved between a first sealing seat 112 and a second sealing seat 114. The valve body 120 has a first guide section 124 and a second guide section 126, which enables translational guidance of the valve body 120 in the valve housing 110. The spherical section 122 is located between the first guide section 124 and the second guide section 126.

[0058] The valve body 120 is guided within a cage-shaped bushing 176, which is located within the housing 10. The cage-shaped bushing 176 has several radial passages to allow a fluidic connection with the inlet and outlet ports (130, 135, 140). Seals 177 are arranged between the components of the cage-shaped bushing 176 and the housing 10. The valve housing 110 comprises an inlet port A, 130, a first outlet port B, 135, and a second outlet port C, 140.

[0059] Thus, the proportional valve arrangement 100 is designed as a 3 / 2-way valve, with ports 130, 135, and 140 arranged directly next to each other. By moving the valve body 120 from the first sealing seat 112 to the second sealing seat 114, fluid from the inlet port 130 can flow into either the first outlet port 135 and / or the second outlet port 140. Particularly in conjunction with the force-balanced arrangement, the valve body 120 can be easily actuated regardless of its position between the first sealing seat 112 and the second sealing seat 114. This also applies regardless of the fluid pressure at ports 130, 135, and 140.

[0060] In the housing 10 of the proportional valve assembly 100, a first sealing seat 112 and a second sealing seat 114 are arranged on the cage-shaped bushing 176. The first sealing seat 112 and the second sealing seat 114 are located upstream and downstream of the spherical section 122 of the valve body 120, respectively, resulting in two end positions of the proportional valve assembly 100. The first sealing seat 112 and the second sealing seat 114 are each located on a first and a second component of the cage-shaped bushing 176, which are arranged coaxially to each other. The components of the cage-shaped bushing 176 can be inserted into one another for assembly of the proportional valve assembly 100, with the spherical section 122 positioned between them.

[0061] The valve body 120 forms a first gap 123 within the cage-shaped bushing 176 between the first guide section 124 and the spherical section 122. This gap is characterized by a smaller diameter of the valve body 120 compared to the first guide section 124. The spherical section 122, on the other hand, has a diameter that is slightly larger than the diameter of the first guide section 124. Additionally, the valve body 120 forms a second gap 125 within the cage-shaped bushing 176 between the second guide section 126 and the spherical section 122. This second gap is characterized by a smaller diameter of the valve body 120 compared to the second guide section 126. The spherical section 122, however, has a diameter that is also slightly larger than the diameter of the second guide section 126.

[0062] The valve body 120 has a pressure bypass 150 to provide a communication link 152 between the second outlet port 140 and the valve body chamber 105. This communication link 152 extends directly through the valve body 120 along its longitudinal axis.

[0063] Within the communication channel 152 of the valve body 120, a stepped installation space 174 is located on the actuator side. The stepped installation space 174 partially accommodates the spindle 170. Additionally, a closing device 180 is located in the stepped installation space 174. The closing device 180 is arranged between the spindle 170 and the valve body 120, and serves to generate an axial preload between the valve body 120 and the first sealing seat 112 when the valve body 120 comes into contact with the first sealing seat 112. Simultaneously, the closing device 180 serves to generate an axial preload between the valve body 120 and the second sealing seat 114 when the valve body 120 comes into contact with the second sealing seat 114.The closing device 180 thus creates an axial preload both when the valve body 120 is in contact with the first sealing seat 112 and when the valve body 120 is in contact with the second sealing seat 114, thereby ensuring a high degree of closing reliability for the proportional valve arrangement 100. When the spindle 170 is moved into an end position, the closing device 180 prevents the valve body 120 from jamming in the sealing seats 112 and 114 in the end position.

[0064] The Figure 5Figure 1 shows an enlarged partial view of a proportional valve assembly 100. The valve body 120 is arranged within the cage-shaped bushing 176, and the spherical section 122 of the valve body 120 is located between the first sealing seat 112 and the second sealing seat 114, thus forming the two end positions of the proportional valve assembly 100. The first sealing seat 112 and the second sealing seat 114 are each located on a first and second component of the cage-shaped bushing 176, respectively, and are arranged coaxially with each other. The valve body 120 comprises the first guide section 124 and the second guide section 126, which enables the valve body 120 to be guided within the cage-shaped bushing 176 in the valve housing 110. The spherical section 122 is located between the first guide section 124 and the second guide section 126. The valve body 120 rests against the second sealing seat 114.

[0065] When the valve body 120 rests against the first sealing seat 112, an axial projection surface (B) of the valve body 120 from the first gap 123 towards the first guide section 124 has the same size as an axial projection surface (A) from the first gap 123 towards the spherical section 122, bounded radially by the first sealing seat 112. This results in a force equilibrium in that the axial components of the projection surfaces (A, B) have the same size in this state. For example, if fluid pressure from outside the proportional valve arrangement 100 is applied to the first outlet port B, 135, this results in an axially balanced force equilibrium of the valve body 120 within the proportional valve arrangement 100. This greatly simplifies the process for the electric actuator 160 to move the valve body 120 or to transfer it from a first position to a second position.

[0066] On the opposite side of the spherical section 122 of the valve body 120, a second space 125 is formed between the second guide section 126 and the spherical section 122. When the valve body 120 rests against the second sealing seat 114, the axial projection surface of the valve body 120 from the second space 125 towards the spherical section 122, limited in the radial direction by the second sealing seat 114, and the end face projection surface 127 onto the second guide section 126, corresponds to the size of an axial projection surface from the second space 125 towards the second guide section 126 and the axial projection surface from the valve body chamber 105 towards the first guide section 124.For example, if fluid pressure from outside the proportional valve arrangement 100 is applied to the second outlet port C, 140, a force equilibrium also results because the sum of the axial components of the projection areas is identical. At fluid pressure, this results in an axially balanced force equilibrium of the valve body 120, which greatly simplifies the process for the electric actuator 160 to move the valve body 120 or to transfer it from a first position to a second position.

[0067] The Figures 6A, 6B and 6CFigure 1 shows further partial views of a proportional valve assembly 100 in various switching positions. The valve body 120 is arranged within the cage-shaped bushing 176, and the spherical section 122 of the valve body 120 is located between the first sealing seat 112 and the second sealing seat 114, resulting in two end positions of the proportional valve assembly 100. The first sealing seat 112 and the second sealing seat 114 are each located on a first and second component of the cage-shaped bushing 176, respectively, and are arranged coaxially with each other. The valve body 120 comprises the first guide section 124 and the second guide section 126, which enables translational guidance of the valve body 120 within the cage-shaped bushing 176 in the valve housing 110.

[0068] The Figure 6AFigure 1 shows the valve body 120 in contact with the first sealing seat 112, thus enabling a fluid connection from the inlet port 130 to the second outlet port 140. The valve body 120 has a stepped installation space 174 for receiving the spindle 170 and the closing device 180. The spindle 170 is self-lockingly connected to the hollow shaft 164 (not shown) and transmits axial movement to the valve body 120. Due to the self-locking connection between the hollow shaft 164 and the spindle 170, the position of the valve body 120 cannot change independently, for example, due to pressure fluctuations in the fluid or other external influences. The closing device 180 comprises a spring element 172, which is arranged coaxially with respect to the spindle 170 and is located within the stepped installation space 174. The spring element 172 is arranged between two disc bodies 181, 182.The stepped installation space 174 has a main diameter which serves to accommodate the two disk bodies 181, 182, including the spring element 172 arranged between them. The stepped installation space 174 also includes a section with a secondary diameter smaller than the main diameter. The two disk bodies 181, 182 cannot enter the section with the secondary diameter but are pressed by the spring force of the spring element 172 against a first stop 175A, which defines the transition step from the main diameter to the secondary diameter within the stepped installation space 174. At the spindle-side end of the stepped installation space 174, there is a second stop 175B in the form of a spacer sleeve, which, analogous to the first stop 175A, defines the main diameter and the smaller secondary diameter.The two disc bodies 180, 182 cannot enter the section with the secondary diameter at the spacer sleeve either, but are pressed against a second stop 175B by the spring force of the spring element 172.

[0069] In the Figure 6A The spindle 170 is in a retracted position, with the valve body 120 being axially preloaded against the first sealing seat 112 by the spring force of the spring element 172 when the first disc body 181 abuts the second stop 175B in the form of the spacer sleeve. The spindle 170 can therefore continue to move at least partially in the axial direction against the preload of the spring element 172 even after the valve body 120 has already come into contact with the first sealing seat 112. This dampens the axial movement of the spindle 170, thus preventing the valve body 120 from jamming in its end position.

[0070] The Figure 6BThe figure shows the valve body 120 spaced from both the first sealing seat 112 and the second sealing seat 114, thereby enabling a fluid connection from the inlet port 130 to the first outlet port 135 and to the second outlet port 140.

[0071] The Figure 6CFigure 1 shows the valve body 120 in contact with the second sealing seat 114, thus enabling a fluid connection from the inlet port 130 to the first outlet port 135. The spindle 170 is in a position extended towards the stepped installation space 174. The valve body 120 is axially biased against the second sealing seat 114 by the spring force of the spring element 172 when the second disc body 182 abuts the first stop 175A. Therefore, the spindle 170 can move at least partially further in the axial direction against the bias of the spring element 172 – i.e., penetrate deeper into the stepped installation space 174 – even when the valve body 120 is already in contact with the second sealing seat 114. This dampens the axial movement of the spindle 170, preventing the valve body 120 from jamming in its final position.

[0072] The stepped installation space 174 is an integral part of the communication link 152, which extends longitudinally through the valve body 120. Thus, the pressure bypass 150 runs through the valve body 120, through the stepped installation space 174, and therefore through the closing device 180, resulting in a compact design and simple, symmetrical pressure equalization of the fluid, which overall enables the force-balanced configuration of the valve body 120. Reference symbol list

[0073] 1 Directional control valve 2 Valve housing 3, 120 Valve piston 4 drive 5 Motor 6, 164 Hollow shaft 7, 170 drive spindle 8 drive housing 9 rotor 10 Housing 11, 122 Spherical section 12 Rod seal 13 module 14 coil spring 15 Installation space 16, 17 spiral body 18 Cycloid gear 19 rolling disc 20 Magnetic target 21 cam disc 22 eccentric 23 Cycloid disk 100 Proportional valve arrangement 105 Valve body chamber 110 Valve housing 112 First sealing seat 114 Second sealing seat 3. 120 Valve body 11, 122 Spherical section 123 First space 124 First guided tour section 125 Second space 126 Second guided tour section 127 Front projection surface A, 130 Inflow connection B, 135 First outlet connection C, 140 Second outlet 150 Pressure bypass 152 Communication link 160 Electric drive 161 rotor 162 stator 6, 164 Hollow shaft 170 spindle 172 spring element 174 Stepped installation space 175A First attack 175B Second attack 176 socket 177 Seals 180 locking device 181 First disc body 182 Second disc body

Claims

1. Proportional valve arrangement (100) for refrigerant, comprising: a valve housing (110) comprising a valve body chamber (105), a valve body (120) which is arranged within the valve body chamber (105) and is configured to be transferable between a first position and a second position, wherein the valve housing (110) comprises a first sealing seat (112) and a second sealing seat (114), and the valve body (120) is transferable between the first sealing seat (112) and the second sealing seat (114), characterized in that the valve body (120) comprises a spherical section (122) which is arranged to be transferable between the first sealing seat (112) and the second sealing seat (114), wherein the valve body (120) comprises a first guide section (124) and a second guide section (126) for guiding the valve body (120) in the valve housing (110), and wherein the spherical section (122) is arranged between the first guide section (124) and the second guide section (126).

2. Proportional valve arrangement (100) according to claim 1, wherein a first interspace (123) is formed between the first guide section (124) and the spherical section (122).

3. Proportional valve arrangement (100) according to claim 2, wherein in a state in which the valve body (120) bears against the first sealing seat (112), an axial projection area of the first interspace (123) in the direction of the first guide section (124) comprises the same size as an axial projection area of the first interspace (123) in the direction of the spherical section (122).

4. Proportional valve arrangement (100) according to claim 1 or 2, wherein a second interspace (126) is formed between the second guide section (126) and the spherical section (122).

5. Proportional valve arrangement (100) according to claim 4, wherein in a state in which the valve body (120) bears against the second sealing seat (114), an axial projection area of the second interspace (125) in the direction of the spherical section (122) comprises the same size as an axial projection area of the second interspace (125) in the direction of the second guide section (126).

6. Proportional valve arrangement (100) according to one of the preceding claims, wherein the valve housing (110) comprises an inflow port (130), a first outflow port (135) and a second outflow port (140).

7. Proportional valve arrangement (100) according to one of the preceding claims, wherein the proportional valve arrangement (100) comprises a pressure bypass (150) which connects the second outflow port (140) to the valve body chamber (105).

8. Proportional valve arrangement (100) according to claim 7, wherein the pressure bypass (150) comprises a communication connection (152) through the valve body (120).

9. Proportional valve arrangement (100) according to one of the preceding claims, wherein the proportional valve arrangement (100) comprises an electrically actuable drive (160) for the proportional actuation of the valve body (120).

10. Proportional valve arrangement (100) according to claim 9, wherein the drive (160) is arranged at least partially in the valve body chamber (105).

11. Proportional valve arrangement (100) according to claim 9 or 10, wherein the drive (160) comprises a stepper motor which is connected to the valve body (120) via a spindle (170).

12. Proportional valve arrangement (100) according to claim 11, wherein the spindle (170) is connected to a hollow shaft (164) in a self-locking manner.