Device for regulating the flow and distribution of a refrigerant in a refrigerant circuit

Abstract

Device (10) for controlling the flow and distribution of a refrigerant in a refrigerant circuit, comprising: a cage (100) comprising at least one inlet (P), one first outlet (A) and one second outlet (B); a piston (200) which is designed to be movable in a cage interior (I) of the cage (100) in the direction of a cage longitudinal axis (L), wherein the piston (200) in a first position connects the inlet (P) with the first outlet (A) and in a second position connects the inlet (P) with the second outlet (B), wherein the piston (200) has a first guide section (210) and a second guide section (230), as well as an outlet section (220) arranged between the first and the second guide section (210, 230) for fluidically connecting the inlet (P) with the first outlet (A) and / or the second outlet (B); and a sealing unit (300, 300', 300'') which seals the piston (200) radially against the cage (100), wherein the sealing unit (300, 300', 300'') in the first position of the piston (200) seals the inlet (P) against the second outlet (B) and in the second position of the piston (200) seals the inlet (P) against the first outlet (A).

Description

Technical field

[0001] The invention relates to a device for controlling the flow and distribution of a refrigerant in a refrigerant circuit, in particular a refrigerant circuit of a vehicle.

[0002] It is already known that high demands are placed on the tightness of refrigerant valves. In refrigerant valves, a closing element of the valve unit exerts a translational movement within a valve housing between two positions to assume different switching positions. For this purpose, the valve unit can be connected to, or is connected to, an actuator unit of the refrigerant valve. The actuator unit is designed to generate a rotational movement of a drive shaft. The drive unit can include a rotor-stator arrangement. The drive shaft can be connected to, or is connected to, the rotor in a rotationally fixed manner. The rotational movement of the drive shaft is transmitted into the translational movement of the closing element via a transmission unit.To maintain the functionality of the refrigerant valve, care must be taken to ensure a safe and reliable seal between the valve unit and the environment, as well as between the connections of the valve unit itself.

[0003] For example, it is already known to use a so-called rod seal in a refrigerant valve with two ports, such as a radial inlet and an axial outlet, to ensure a seal between the closing element and the valve body of the valve unit. Such a rod seal consists of an O-ring and a sealing ring that slides on an outer surface of the closing element and is positioned in contact between the O-ring and the closing element. This enables a high radial sealing effect.

[0004] However, such a conventional rod seal requires a rigid functional frame to maintain the O-ring in its tensioned state. Furthermore, to ensure the rod seal's function, the outer surface of the sealing element must be continuous. This means that the outer diameter of the sealing element, at least in the section over which the rod seal's sealing ring slides, must be uninterrupted along the entire travel path. In other words, the rod seal's sealing ring is in contact with the outer surface of the sealing element throughout its entire travel path. This protects the O-ring from explosive decompression, which occurs during rapid pressure drops and is destructive.

[0005] The constant contact between the sealing ring and the outer surface of the valve body makes it difficult to use the rod seal in refrigerant valves with more than two ports. More precisely, due to the contact between the valve body and the sealing ring, the outer surface is closed, i.e., without openings, to prevent abrasive wear of the sealing ring during operation. Abrasive wear of the sealing ring reduces the service life of the rod seal and leads to frequent replacements, which are detrimental and necessary to maintain functionality. However, providing a functional area with a reduced diameter compared to the other areas of the valve body, as required for valves with more than two ports, significantly increases the risk of explosive decompression of the permanently pre-tensioned O-ring.Therefore, a uniform diameter of the outer surface of the locking element is necessary to counteract a release of the pre-tensioned O-ring, which would occur during a release, i.e., when passing through a section of the locking element with a smaller diameter outer surface, in order to avoid an explosive decompression of the O-ring. Description of the invention

[0006] There is therefore a need to create a device for regulating the flow and distribution of a refrigerant in a refrigerant circuit, especially for use in a vehicle, which avoids the aforementioned disadvantages of the known devices, meets high tightness requirements and is applicable with more than two connections.

[0007] In particular, it is an object of the present invention to provide a compact device for controlling the flow and distribution of a refrigerant in a refrigerant circuit, which ensures a reliable and secure seal both between the device and the environment and between the connections provided in the device. In particular, the service life of the device is to be increased.

[0008] This is achieved by a device having the features of claim 1. Advantageous embodiments are specified in the dependent claims.

[0009] To solve the problem, a device for regulating the flow and distribution of a refrigerant in a refrigerant circuit is specified. The device for regulating the flow and distribution of a refrigerant in a refrigerant circuit comprises a cage comprising at least one inlet, a first outlet, and a second outlet; a piston which is designed to be movable in a cage interior in the direction of a cage longitudinal axis, wherein the piston connects the inlet to the first outlet in a first position and connects the inlet to the second outlet in a second position, wherein the piston has a first guide section and a second guide section, as well as an outflow section arranged between the first and the second guide section for fluidically connecting the inlet to the first outlet and / or the second outlet;and a sealing unit which seals the piston radially against the cage, wherein in the first position of the piston the sealing unit seals the inlet against the second outlet and in the second position of the piston the inlet against the first outlet.

[0010] The advantages of the invention are obvious. Firstly, the device according to the invention results in an extremely compact device, which requires very little space, particularly along the longitudinal axis of the cage. This allows the axial installation space to be advantageously small, and the device can achieve high functionality even in confined spaces. As described above, such devices can be used, for example, in refrigerant valves of the refrigerant circuit, particularly in vehicles, especially in vehicles that are at least partially electrically powered. Space is extremely limited in such refrigerant valves. However, the demands on functionality are simultaneously increasing. This can be easily solved by the device according to the invention.

[0011] In particular, the combination of the piston, which at least substantially fulfills the function of the closing element, with its guide sections, the outflow section, and the sealing unit advantageously ensures the device's versatility in various valve units. At the same time, the required space can be reduced or at least minimized. Furthermore, the device according to the invention, with the sealing unit in conjunction with the outflow section, can be used for configurations with more than two ports. The sealing unit can slide over the outflow section in such a way that explosive decompression of the sealing unit can be counteracted or avoided altogether. Thus, the device according to the invention can meet stringent sealing requirements while simultaneously offering a high degree of flexibility and functionality.

[0012] The term "outflow section" refers to a section of the piston that provides a functional flow path from a through-hole in the piston, extending radially through the piston's outer surface. In other words, the outflow section allows the refrigerant to flow radially outward from the through-hole, through the piston's outer surface, and into the surrounding air. The outflow section can incorporate an opening structure and a support structure. The opening structure can consist of multiple radial openings. The support structure is formed by the remaining outer surface of the outflow section between these radial openings. The opening structure is designed to allow refrigerant to flow through the piston's outer surface within the outflow section. The support structure provides support and protection for the sealing unit.In particular, when the outflow section is moved by a sealing unit, the support structure prevents the sealing unit from penetrating the opening structure. This reduces wear on the sealing unit and prevents pressure release and the associated explosive decompression of the sealing unit. This extends the service life of the sealing unit and reduces maintenance, repair, and replacement work, as well as the associated downtime. Overall, this results in a device that is more robust in operation, with high flexibility and functionality.

[0013] The arrangement and design of the sealing unit, in conjunction with the piston design, further ensures a long service life and reliable, secure compliance with stringent sealing requirements. This eliminates the need for maintenance and repair work, as well as premature component replacement, thus reducing unnecessary downtime.

[0014] According to a further aspect of the device according to the invention, the piston can, in a third position, connect the inlet to the first outlet and the second outlet. This allows for a switching state in which the inlet is simultaneously in fluid contact with the first outlet and the second outlet. This corresponds, in particular, to a mid-position of the piston between the first position and the second position.

[0015] Alternatively, according to a further aspect of the invention, the piston can, in a fourth position, close the inlet to both the first outlet and the second outlet. This allows for a switching state in which the inlet is simultaneously separated from a fluid connection to the first outlet and a fluid connection to the second outlet. Again, this corresponds in particular to the piston's mid-position between the first and second positions.

[0016] According to a further aspect of the device according to the invention, the inlet or at least one outlet can be configured in the direction of the cage's longitudinal axis. This can advantageously further reduce the axial extent of the device compared to a device in which all connections are radially arranged.

[0017] According to a further aspect of the device according to the invention, the sealing unit can comprise an elastomer ring and a sealing ring, wherein the elastomer ring is arranged in a permanent state of tension within a receptacle. This improves the radial sealing properties of the sealing unit. Simultaneously, the sealing ring, in conjunction with the piston and / or the receptacle, ensures that the permanent state of tension of the elastomer ring is maintained. This advantageously prevents explosive decompression of the elastomer ring. Explosive decompression is destructive to the elastomer ring. Thus, the safety and robustness of the device, as well as its overall service life, can be improved.

[0018] Preferably, the sealing ring can be in direct contact with the piston. In other words, the sealing ring slides directly on the piston throughout its entire travel. This prevents the sealing ring from becoming dislodged and thus prevents the elastomer ring from depressurizing. Particularly in the outflow section, it is important to ensure that sufficient surface area of ​​the piston remains to form a support structure for the support ring. This counteracts or prevents explosive decompression of the sealing unit and, in particular, of the elastomer ring.

[0019] According to a further aspect of the device according to the invention, the device can have a second sealing unit, which is assigned to the first guide section of the piston and seals the cage interior against a drive-side section of the device. This further improves the device's sealing performance. Furthermore, the individual sealing units can be slightly relieved of stress by distributing the radial support of the piston across several sealing units.

[0020] According to a further aspect of the device according to the invention, the device can have a third sealing unit, which is assigned to the second guide section of the piston and seals the cage interior against an inlet oriented in the direction of the cage's longitudinal axis or against the device itself. This results in an improvement in the device's sealing performance. Furthermore, the individual sealing units can also be slightly relieved of stress by distributing the radial support of the piston across several sealing units.

[0021] According to a further aspect of the device according to the invention, the device can have at least three sealing units, each of which has an identical inner diameter. This allows the device to be sealed particularly effectively against the environment or the installation space, as well as between the individual connections of the device. The identical inner diameters enable a distributed load bearing and better force distribution when supporting the piston. The assembly process can also be simplified, since the sealing units can be interchangeable or identical.

[0022] According to a further aspect of the device according to the invention, the piston can be cylindrical, with the first guide section, the second guide section, and the outflow section having an identical outer diameter. This makes it particularly easy to manufacture. The outer diameter of the piston is specifically chosen to match the inner diameter of the sealing units. "Matching" means that the piston can slide freely through the sealing units, while the sealing units simultaneously provide a sealing effect.

[0023] According to a further aspect of the device according to the invention, the outflow section can have a plurality of radial openings, wherein the radial openings on a piston surface define an outflow area which is greater than 50%, in particular 70%, and in particular 90% of the total surface area of ​​the outflow section. This enables fluid communication between a through-hole of the piston extending along the longitudinal axis of the piston and an environment located radially outside the piston surface. The radial openings and the outflow area are designed such that the piston surface in the outflow section continues to form a support contour which supports the sealing unit in the radial direction.This prevents the sealing unit, and in particular a sealing ring of the sealing unit, from entering the radial openings, which would lead to a relaxation of the sealing unit, especially of an elastomer ring of the sealing unit. Such a relaxation of the sealing unit can quickly lead to explosive decompression, which is destructive to the sealing unit. Thus, the durability of the device can be improved and the preload of the sealing unit maintained in every position, resulting in excellent sealing properties. At the same time, supporting the sealing unit prevents abrasive wear of the sealing unit during piston movement.

[0024] In such a variant, the radial openings can be designed as slots oriented along the longitudinal axis of the piston. This allows the support structure to be oriented along the longitudinal axis of the piston, i.e., in the direction of piston movement. This further prevents abrasive wear and provides improved sliding properties.

[0025] Alternatively, the ratio of the length of the openings along the piston's longitudinal axis to the length of the openings in a circumferential direction can be at least two. This further improves the sliding properties and can reduce abrasive wear of the sealing unit.

[0026] Alternatively, the number of radial openings on the outflow section can be at least 4, in particular at least 8, in particular at least 12, and in particular at least 16. This allows for the creation of a maximum outflow area while maintaining the support structure. Advantageously, this maximizes the functionality of the outflow section and simultaneously prevents the sealing unit from being drawn into the radial openings due to the resulting support structure. This protects the sealing unit and thus leads to an extended service life and improved sealing performance of the device.

[0027] Alternatively, the radial openings can be arranged evenly spaced around the circumference. This also ensures that the piston's support structure is evenly distributed around the circumference in the outflow section, resulting in better support for the sealing unit. This effectively prevents the sealing unit from entering the radial openings, thus preventing wear and stress relaxation of the sealing unit.

[0028] In particular, the radial openings can be designed as a mesh or sieve. For this purpose, a multitude of small radial openings are arranged in the outflow section, distributed both along the longitudinal axis of the piston and circumferentially. Piston material remains between the individual openings, forming the support structure of the outflow section. As the piston's outflow section moves through a sealing unit, the support structure formed by many of the numerous small radial openings comes into contact with the inner circumferential surface of the sealing unit. This prevents the sealing unit from being drawn into the radial openings and simultaneously establishes a fluid connection via these openings. The sealing properties can thus be improved.

[0029] According to a further aspect of the device according to the invention, the cage can have radially external sealing elements to seal the inlet, the first outlet, and the second outlet against each other within a single installation space. This allows for simple assembly of the device into a single installation space while meeting the high sealing requirements.

[0030] This allows for the creation of a device that can be used with valves with more than two ports and is flexibly adaptable to the structural and functional requirements of the installation space. At the same time, damage to the sealing unit can be efficiently prevented, and excellent, particularly radial, sealing performance can be achieved. Functional flow paths, such as the outflow section, can be traversed, especially without loss of contact between the piston and the sealing unit. This ensures a high sealing effect and protects the sealing unit from explosive decompression. In particular, the permanent preload of the sealing unit can be maintained simply and reliably.

[0031] Another aspect of the present invention relates to a refrigerant valve with one of the devices described above, which is inserted into an installation space.

[0032] The various and exemplary features described above can be combined with one another according to the invention, insofar as this is technically sensible and suitable. Further advantageous embodiments and combinations of features of the invention will become apparent from the following detailed description and the entirety of the patent claims. Brief description of the drawings

[0033] The invention is explained in more detail below with reference to exemplary embodiments and the accompanying schematic drawings. These show: Fig. 1 a schematic representation of a device according to the invention in a first embodiment; Fig. 2A-2C schematic representations of the device according to the invention of the first embodiment in different positions of the piston; Fig. 3 a schematic representation of a device according to the invention in a second embodiment; Fig. 4A-4B schematic representations of the piston with differently designed outflow sections; and Fig. 5 a schematic representation of a device according to the invention in a further embodiment.

[0034] Basically, identical parts in the figures are marked with the same or similar reference symbols. Ways to implement the invention

[0035] The exemplary embodiments described below each show a device 10 for controlling the flow and distributing a refrigerant in a refrigerant circuit. The device 10 can, for example, be used in a refrigerant valve.

[0036] Fig. Figure 1 shows a schematic representation of the device 10 for controlling the flow and distributing a refrigerant in a refrigerant circuit according to a first embodiment. The device 10 comprises a cage 100 with a cage longitudinal axis L and a cage interior I. The cage 100 has three connections P, A, B: an inlet P, a first outlet A, and a second outlet B. The cage 100 further comprises three receptacles 150, 150', 150" for receiving and arranging three sealing units 300, 300', 300".

[0037] The cage 100 can be a single component or made up of several cage sections.

[0038] Sealing elements 160 are arranged on an outer side of the cage 100 to seal the connections P, A, B from one another when the cage is inserted into a mounting space 30. Each sealing element 160 can have an O-ring. In particular, one sealing element 160 can be provided between each pair of connections P, A, B.

[0039] In Fig. Figure 1 also shows an axial sealing element 500, which is arranged on the drive side of the device 10 on a connecting housing 40. Instead of the axial sealing element 500, another radial sealing element 160 is also conceivable.

[0040] A piston 200 is mounted coaxially within the cage interior I of cage 100, allowing longitudinal displacement. In other words, the piston's longitudinal axis L corresponds to the cage's longitudinal axis L. The cage 100 is connected via the connecting housing 40 to a (in Fig. 1. (not shown) drive unit 20 can be connected. The drive unit 20 can have a rotor 21 and a rotor shaft 22, which can be connected to or is connected to the rotor 21 in a rotationally fixed manner, as well as a stator assembly. When the stator assembly is activated, a rotational movement of the rotor 21 and the rotor shaft 22 is generated. The rotational movement of the rotor shaft 22 is transmitted via a coupling arrangement into a rotational movement of a spindle 45.

[0041] The spindle 45 has a threaded section with an external thread at one end facing away from the drive unit 20. The threaded section is part of a transmission unit for translating the rotational movement of the spindle 45 into a translational axial movement of the piston 200.

[0042] The piston 200 has a through-hole along its longitudinal axis L. Within this through-hole, the piston 200 has a threaded section with an internal thread, which can be engaged with, or is engaged in, the threaded section of the spindle 45. Furthermore, at its end facing the drive unit 20, the piston 200 has a flanged section 250 with recesses 260, which together form an anti-rotation device for the piston 200. This anti-rotation device can be arranged to engage in a complementary opening in the connecting housing 40. The flanged section 250 with recesses 260, acting as an anti-rotation device for the piston 200, the complementary receiving opening in the connecting housing 45, and the threaded sections of the piston 200 and the spindle 45 form the transmission unit that converts the rotational movement of the spindle 45 into a translational movement of the piston 200.

[0043] The piston 200 further comprises a first guide section 210, a second guide section 230, and an outlet section 220 arranged between the first and second guide sections 210 and 230. The first guide section 210 has a first diameter D1. The second guide section 230 has a second diameter D2. The outlet section 220 has a third diameter D3. The first diameter D1, the second diameter D2, and the third diameter D3 can be at least substantially the same and correspond to an outer diameter Da of the piston 200.

[0044] As in Fig. As shown in Figure 1, the outflow section 220 has an opening structure and a support structure. The opening structure allows the refrigerant to flow from the through-hole of the piston 200, through the outer surface of the piston 200, in a radial direction to the outside in the direction of the piston's longitudinal axis L. The support structure is formed by a plurality of radial openings 240. The support structure is formed between the individual radial openings 240 of the outflow section 220. The support structure provides support for the sealing units 300, 300', 300" during translational movement and protects them from damage. The radial openings 240 are specifically shaped such that their transitions to the support structure have a geometry that protects the sealing units 300, 300', 300" from abrasive wear during axial movement of the outflow section 220 through the sealing units 300, 300', 300".The geometry can be formed, for example, by a rounded shape or a chamfer. In particular, sharp edges and abrupt contour changes of the radial openings 240 to the support structure should be avoided.

[0045] In the Fig. In the embodiment shown in Figure 1, the radial openings 240 are elongated slots extending along the longitudinal axis L of the piston. In particular, the length of the radial openings 240 in the direction of the longitudinal axis L of the piston is at least twice as long as the length of the radial opening 240 in the circumferential direction.

[0046] Alternative opening geometries for the radial openings 240 are also conceivable, provided that the outflow section 220 forms the support structure in such a way as to prevent the sealing units 300, 300', 300" from immersing into the radial openings 240. For example, a multitude of circular or oval openings with the same or different dimensions can also be provided. A mesh- or sieve-like opening structure with a multitude of small radial openings 240 is also conceivable.

[0047] Exemplary opening geometries of the opening structure are shown below in conjunction with Fig. Sections 4A to 5 are described in more detail.

[0048] According to the in Fig. In the device 10 shown in Figure 1, the inlet P is arranged axially in the direction of the cage's longitudinal axis P, while the first outlet A and the second outlet B are arranged radially. In other words, the through-hole of the piston 200 is in fluid communication with the inlet P.

[0049] Each sealing unit 300, 300', 300" is received in an associated receptacle 150, 150', 150" of the cage 100. A first sealing unit 300 is received in a first receptacle 150 and is arranged between the first outlet A and the second outlet B. A second sealing unit 300' is received in a second receptacle 150' and is arranged between a drive-side end of the cage 100 and the first outlet A and is associated with the first guide section 210. A third sealing unit 300" is received in a third receptacle 150" and is arranged between the second outlet B and the inlet P, or at an end of the cage 100 opposite the drive unit 20.

[0050] The first sealing unit 300 seals the inlet P against the second outlet B in a first position of the piston 200, as shown in Fig. 2A is shown. The first sealing unit 300 seals the inlet P against the first outlet A in a second position of the piston 200, as shown in Fig. 2C and Fig. Figure 1 is shown. In a third position of the piston 200, the inlet P is connected to both the first outlet A and the second outlet B, as shown in Figure 1. Fig. 2B is shown. In the third position, the outflow section 220 with the plurality of radial openings 240 connects the inlet P to both the first outlet A and the second outlet B.

[0051] As from Fig. As can be seen in Figure 2A, the second outlet B is fluidically sealed from the inlet P via the first sealing unit 300, which is arranged between the first outlet A and the second outlet B (viewed along the piston's longitudinal axis L), the piston 200, and the third sealing unit 300, which is arranged between the second outlet B and the inlet P (viewed along the piston's longitudinal axis L). The inlet P is in fluid communication with the first outlet A via the through-hole in the piston 200 and the radial openings 240 formed in the outflow section 220.

[0052] According to the representation in Fig. In position 2B, the piston 200 is in a central position. In this position, the radial openings 240 in the outflow section 220 can extend along the piston's longitudinal axis L beyond both sides of the first sealing unit 300. Thus, the inlet P can be in fluid communication with both the first outlet A and the second outlet B via the radial openings 240 of the outflow section 220. Therefore, the piston 200 assumes a third position, defined by the fact that the inlet P is fluidically connected to both the first outlet A and the second outlet B.

[0053] In the second position of piston 200, which is in Fig. As shown in Figure 2C, the first sealing unit 300 seals inlet P against the first outlet A. The second outlet B is in fluid contact with inlet P via the radial openings 240 in the outflow section 220.

[0054] The sealing units 300, 300', 300'' each have an elastomer ring 310 and a sealing ring 320 arranged radially between the elastomer ring 310 and the piston 200. The elastomer ring 310 is in a permanent state of tension. This allows for excellent radial sealing. The sealing ring 320 contacts the elastomer ring 310 on one side, and on the opposite side, the sealing ring 320 is in sealing and / or sliding contact with the piston 200. Specifically, the sealing ring 320 is in direct contact with a surface of the piston 200. In other words, the sealing ring 320 contacts the surface of the piston 200 in every position (and translational position) of the piston 200. This ensures that the permanent stress state of the elastomer ring 310 is maintained extremely reliably, thus protecting it from destructive explosive decompression.At the same time, the sealing ring 320 can be easily protected from damage, such as abrasive wear and penetration into the opening structure, due to the design of the outflow section 220 with the support structure.

[0055] The sealing units 300, 300', 300'' can all have an identical inner diameter Di, which is designed to fit the outer diameter Da of the piston 200 in the first guide section 210, the outflow section 220, and the guide section 230. "Fits" means that translational movement of the piston 200 through the sealing units 300, 300', 300'' is permitted, while simultaneously ensuring support of the sealing units 300, 300', 300'' against the piston 200. Thus, the sealing units 300, 300', 300'' can be interchanged, which simplifies the assembly process.

[0056] When one of the sealing units 300, 300', 300'' passes through the outlet section 220, the sealing unit 300, 300', 300'' being passed through can be flushed with refrigerant passing through the opening structure. This improves the sliding properties when passing over the outlet section 220. The sealing unit 300, 300', 300'' can thus be further protected from damage.

[0057] The Fig. Figure 3 now shows the device 10 according to a second embodiment of the invention. The device 10 of the second embodiment corresponds at least substantially to the device 10 of the first embodiment. Repeating descriptions are omitted, and reference is made to the preceding and following sections. The features of the first embodiment can be combined, interchanged, or otherwise assembled with those of the second embodiment, provided they do not contradict each other technically.

[0058] The device 10 according to Fig. 3 has an axial inlet P in the direction of the piston's longitudinal axis L, a radial first outlet A, and a radial second outlet B. The second outlet B is arranged along the piston's longitudinal axis L between the first outlet A and the inlet P. The device 10 of the second embodiment also has three sealing units 300, 300', 300''. Each sealing unit 300, 300', 300'' is received in an associated receptacle 150, 150', 150'' of the cage 100. A first sealing unit 300 is received in a first receptacle 150 and is arranged between the first outlet A and the second outlet B. A second sealing unit 300' is received in a second receptacle 150' and is arranged between a drive-side end of the cage 100 and the first outlet A and is associated with the first guide section 210.A third sealing unit 300'' is received in a third receptacle 150'' and arranged between the first sealing unit 300 and the second outlet B. Specifically, the first receptacle 150 and the third receptacle 150'' are arranged in a continuous section of the cage 100. In other words, in the direction of the cage's longitudinal axis L, the cage 100 is closed between the first receptacle 150 and the third receptacle 150''. Specifically, no connection is provided in the direction of the cage's longitudinal axis L between the first receptacle 150 and the third receptacle 150''.

[0059] An axial distance in the direction of the cage longitudinal axis L between the first opening 150 and the third opening 150'' is preferably greater than the length of the outflow section 220 of the piston 200 as seen in the direction of the piston longitudinal axis L. The axial distance in the direction of the cage longitudinal axis L between the first opening 150 and the third opening 150'' can be greater than or equal to 1.2 times, in particular greater than or equal to 1.5 times, in particular greater than or equal to 2 times, greater than the length of the outflow section 220 of the piston 200 as seen in the direction of the piston longitudinal axis L.

[0060] Here too, the first sealing unit 300, the second sealing unit 300', and the third sealing unit 300'' are at least substantially identical in construction. This simplifies assembly. The sealing units 300, 300', 300' essentially correspond to the sealing units 300, 300', 300'' described previously in relation to the first embodiment.

[0061] In contrast to the first embodiment, there is no connection of the device 10 between the first sealing unit 300 and the third sealing unit 300''. In other words, the cage 100 is closed in the section between the first sealing unit 300 and the third sealing unit 300'', as described above. The axial distance in the direction of the cage's longitudinal axis L between the first receptacle 150 and the third receptacle 150'' is greater than the length of the outflow section 220 in the direction of the piston's longitudinal axis L.

[0062] According to the second embodiment, the piston 200 is also axially displaceable within the cage interior I of the cage 100.

[0063] The design of piston 200 is essentially the same as that of the piston of the first embodiment. Therefore, a repeated description of this is omitted.

[0064] In the first position of the piston 200, the first sealing unit 300 seals the inlet P against the second outlet B. A fluid connection between the inlet P and the first outlet A is enabled via the outflow section 220.

[0065] In the second position of the piston 200, the third sealing unit 300'' seals the inlet P against the first outlet A. A fluid connection between the inlet P and the second outlet B is enabled via the outflow section 220.

[0066] In the intermediate position between the first and second positions of the piston 200, the inlet P is fluidically separated from both the first outlet A by means of the first sealing unit 300 and the second outlet B by means of the third sealing unit 300''. In other words, the first sealing unit 300, the third sealing unit 300'', as well as the first guide section 210 and the second guide section 230 of the piston 200, close the inlet P to both the first outlet A and the second outlet B. This corresponds to a fourth position.

[0067] The in Fig. The devices shown in 1 to 3 can, for example, be used in 3 / 3-way valves.

[0068] Even if in Fig. Since the inlet P is arranged axially in the direction of the cage's longitudinal axis L (1 to 3), it is also conceivable that all connections are arranged radially. For this, the number of sealing units (300) and the cage design (100) must be adjusted accordingly.

[0069] It is also conceivable that the inlet P is arranged radially and an outlet A, B is arranged axially.

[0070] Fig. 4A and Fig. Figure 4B shows various embodiments of the piston 200. Individual features of the described pistons 200 can be combined with one another as desired. For example, the flange area 250 together with the recesses 260 can be used as an anti-rotation device. Fig. 4A with the outflow section of the Fig. 4B etc. can be combined. Each of the illustrated or recombined pistons 200 can be used accordingly in one of the devices 10 of the first or second embodiment.

[0071] Fig. Figure 4A shows an embodiment of the piston 200. The piston 200 is at least substantially cylindrical. The piston 200 has a through-opening in the direction of the piston's longitudinal axis L.

[0072] A first end of the piston 200, extending along the longitudinal axis L of the piston, has a flange region 250 with two projections spaced apart from each other by two opposing recesses 260, which are arranged essentially opposite one another. The flange region 250 with the recesses 260 forms an anti-rotation device for the piston 200. In particular, a receiving opening, shaped complementarily to the anti-rotation device for the piston 200, is formed in a connecting housing 40 of the valve unit for receiving and guiding the piston 200 in sections. Specifically, the projections of the flange region 250 can engage in correspondingly complementary grooves in the receiving opening of the connecting housing 40. This forms part of the transmission unit that converts the rotational movement of the spindle 45 into the translational movement of the piston 200.

[0073] Starting from the end of the piston 200 which has the flange area 250, the piston 200 further has a first guide section 210, an outflow section 220 and a second guide section 230 in the direction of the piston longitudinal axis L.

[0074] According to the representation in Fig. 4A the piston 200 ends in piston longitudinal axis L with the guide section 230.

[0075] As in Fig. As can be seen in Figure 4A, the outer diameters in the first guide section 210, the outflow section 220, and the second guide section 230 are the same. This enables permanent contact between the shell surface of the piston 200 and the sealing units 300, 300', 300''.

[0076] The outflow section 220 has an opening structure with a plurality of radial openings 240 and a support structure formed between the radial openings 240. The plurality of radial openings 240 can preferably be arranged uniformly distributed in the circumferential direction. In this context, a plurality of radial openings 240 means 2 or more radial openings 240, in particular at least 4 radial openings 240, in particular at least 8 radial openings 240, in particular at least 12 radial openings 240, and in particular at least 16 radial openings 240.

[0077] The radial openings 240 can define an outflow area on the outer surface of the piston 200 in the outflow section 220. In particular, the outflow area is at least 40%, in particular at least 45%, in particular at least 50%, in particular at least 70%, in particular at least 75%, in particular at least 90%, of the total outer surface of the outflow section 220, but less than the total outer surface of the outflow section 220, in particular less than 95%, in particular less than or equal to 90%. This ensures a sufficient support structure for supporting the sealing units 300, 300', 300''.

[0078] The multitude of radial openings 240 features a chamfer surrounding each radial opening 240 at the transition to the support structure. This protects the sealing units 300, 300', 300'' from abrasive wear as they pass through, thus preventing damage. Alternatively, the edge at the transition between the radial openings 240 and the support structure could also be rounded or have a different edge contour that prevents abrasive wear of the sealing units 300, 300', 300''.

[0079] In the Fig. In the embodiment shown in Figure 4A, the radial openings 240 are designed as elongated holes or slots. The elongated holes or slots are oriented in the direction of the piston's longitudinal axis L. In other words, the length of the elongated holes or slots in the direction of the piston's longitudinal axis L is greater than the length of the elongated holes or slots in the circumferential direction. In particular, the ratio of the length of the elongated holes or slots in the direction of the piston's longitudinal axis L to the length of the elongated holes or slots in the circumferential direction can be at least 2:1.

[0080] The elongated holes or slots in Fig. 4A are arranged in a circumferential row in the direction of the piston longitudinal axis L.

[0081] However, it is also conceivable to arrange two or more rows of elongated holes or slots in the outflow section 220. The two or more rows are spaced apart from each other in the direction of the piston's longitudinal axis L. The radial openings 240 of the first of the two or more rows can be offset in the direction of the piston's longitudinal axis L and / or circumferentially relative to the radial openings 240 of the second of the two or more rows. Alternatively, the radial openings 240 of the first of the two or more rows can be aligned in the piston's longitudinal axis L with the radial openings 240 of the second of the two or more rows.

[0082] In Fig. Figure 4B shows a further embodiment of an exemplary piston 200. The flange area 250 and the recesses 260 are shaped differently than in Figure 4B. Fig. 4A. The flange area 250 extends essentially circumferentially, with recesses 260 formed as flattened surfaces arranged on two diametrically opposite sides. This fulfills the same function as the flange area 250 and the recesses 260 of the Fig. 4A, namely an anti-rotation device as part of the transmission unit, which converts the rotational movement of the spindle 45 into the translational movement of the piston 200. In particular, a receiving opening, shaped complementarily to the anti-rotation device of the piston 200, is formed in a connecting housing 40 of the valve unit for the partial receiving and guiding of the piston 200. In particular, the recesses 260, which are designed as flattened surfaces, can engage with correspondingly complementary shaped surfaces in the receiving opening of the connecting housing 40, which prevents a rotational movement of the piston 200 about the piston's longitudinal axis L.

[0083] The outflow section 220 is also Fig. 4B differs from the outflow section 220 of the Fig. 4A is shown. Fig. In the embodiment of the outflow section 220 shown in Figure 4B, a plurality of radial openings 240 are arranged in three circumferential rows spaced apart from one another in the direction of the piston's longitudinal axis L. The radial openings 240 are bores with a circular cross-section. The radial openings 240 of the first row can have bores with a first diameter, the radial openings 240 of the second row can have bores with a second diameter, and the radial openings 240 of the third row can have bores with a third diameter. The first diameter differs from the second diameter and / or the third diameter. The second diameter, in turn, differs from the first diameter and / or the third diameter. In particular, the first diameter can be larger than the second diameter and the second diameter larger than the third diameter, as shown in Figure 4B. Fig. 4B is shown.

[0084] The radial openings 240 of the first row can be aligned with radial openings 240 of the second row in the direction of the piston's longitudinal axis L, and the radial openings 240 of the second row can be aligned with radial openings 240 of the third row in the direction of the piston's longitudinal axis L. Alternatively, it is also conceivable that, for example, the radial openings 240 of the second row are arranged circumferentially offset from the radial openings 240 of the first and / or third row. It is also conceivable to arrange further rows of radial openings 240.

[0085] Unlike the piston 200 of the Fig. 4A shows the piston 200 of the Fig. 4B, in the direction of the piston longitudinal axis L, adjacent to the second guide section 230 on a side opposite the outflow section 220, additionally features a conical section 270, the axial end of which defines the second end of the piston 200. The conical section 270 can, for example, enable self-centering and / or be used to close an axial valve seat.

[0086] Also in the design of the piston 200 of the Fig. 4B the outer diameters of the first guide section 210, the outflow section 220 and the second guide section 230 are of the same size.

[0087] The individual in Fig. 4A and Fig. The features described in 4B can be combined, exchanged, and assembled into further variants of the piston 200. The features described in 4B can also be combined with each other and exchanged to create further variants of the piston 200. Fig. 5. Indicated design of the outflow section 220 and its features corresponding to the features of the Fig. 4A and Fig. 4B can be combined.

[0088] Fig. Figure 5 shows an exemplary refrigerant valve with a device 10 according to the invention in a further embodiment. In the device 10 in the Fig. 5 corresponds at least substantially to the devices 10 of the first embodiment, although the outflow section 220 of the piston 200 has a further variant of the opening structure.

[0089] The in Fig. The outflow section 220 shown in Figure 5 has a plurality of radial openings 240 that define a net-like or sieve-like opening structure. In other words, a plurality of very small openings 204 are arranged in at least six rows spaced apart from one another in the direction of the piston's longitudinal axis, in particular at least eight rows, and in particular at least ten rows. This allows the outflow area to be increased simultaneously, and the support structure to be designed in such a way as to achieve a particularly good support effect on the sealing units 300, 300', 300''.

[0090] Fig. Figure 5 further shows the drive unit 20 with a stator arrangement (not shown) radially surrounding a rotor 21. A rotor shaft 22 is rotationally fixed to, or connected to, the rotor 21. The rotor 21 and the rotor shaft can be arranged in a containment shell, which is connected to, or connected to, a connecting housing 40. The connecting housing 40 also has a receiving opening for partially receiving the piston 200. Furthermore, a spindle 45 is mounted in the connecting housing 40, in particular by means of a fixed bearing.

[0091] The spindle 45 can be connected to the rotor shaft 22 via a coupling unit in a rotationally fixed manner, so that a rotational movement of the rotor shaft 22 is transmitted to the spindle 45.

[0092] An end of the spindle 45 opposite the drive unit 20 has a threaded section with an external thread, which engages in a threaded section with an internal thread in the through-hole of the piston 200. The anti-rotation device formed by the flange section 250 and recess 260 of the piston 200, together with the complementary receiving opening, which receives the flange section 250 and recess 260 axially displaceably, and the threaded sections on the spindle 45 and piston 200, form a transmission unit that converts the rotational movement of the spindle 45 into a translational movement of the piston 200.

[0093] The cage 100 of the device 10 is inserted into a mounting space 30. The cage 100 can be divided into several cage sections 110, 120, 130 or be a single-piece component. Radially attached sealing elements 160 on the outside of the cage seal the cage 100 against the mounting space 30 between two adjacent connections P, A, B, and thus seal the connections P, A, B against each other.

[0094] Between the connecting housing 40 and the installation space 30, a Fig. 5 axial seals 500 (not shown) may be arranged. Alternatively, a further radially external sealing element 160 may also be provided between the drive-side end of the cage 100 and the first outlet A.

[0095] Further variations of the invention are known to those skilled in the art. Reference symbol list 10 Device 20 drive unit 21 Rotor 22 Rotor shaft 30 construction space 40 connection housings 45 spindle 100 cage 150-150'' recording 160 sealing elements 200 pistons 210 first section of the guide 220 Outflow section 230 second section of the guide 240 radial openings 250 Flange area of ​​the piston 260 exceptions 270 conical end section 300-300'' sealing unit 310 Elastomer ring 320 sealing ring 500 axial seal L cage longitudinal axis or piston longitudinal axis I Cage interior The inner diameter of the sealing unit Since the outer diameter of the piston D1 first piston diameter D2 second piston diameter D3 third piston diameter P Entrance A first outlet B second outlet

Claims

[1] Device (10) for controlling the flow and distribution of a refrigerant in a refrigerant circuit, comprising: a cage (100) comprising at least one inlet (P), one first outlet (A) and one second outlet (B); a piston (200) which is designed to be movable in a cage interior (I) of the cage (100) in the direction of a cage longitudinal axis (L), wherein the piston (200) in a first position connects the inlet (P) with the first outlet (A) and in a second position connects the inlet (P) with the second outlet (B), wherein the piston (200) has a first guide section (210) and a second guide section (230), as well as an outlet section (220) arranged between the first and the second guide section (210, 230) for fluidically connecting the inlet (P) with the first outlet (A) and / or the second outlet (B); and a sealing unit (300, 300', 300'') which seals the piston (200) radially against the cage (100), wherein the sealing unit (300, 300', 300'') in the first position of the piston (200) seals the inlet (P) against the second outlet (B) and in the second position of the piston (200) seals the inlet (P) against the first outlet (A). [2] Device (10) according to claim 1, characterized by , that the piston (200) in a third position connects the inlet (P) with the first outlet (A) and the second outlet (B). [3] Device (10) according to claim 1, characterized by , that the piston (200) in a fourth position closes the inlet (P) both in relation to the first outlet (A) and in relation to the second outlet (B). [4] Device (10) according to any one of the preceding claims, characterized by that the inlet (P) or at least an outlet (A, B) is formed in the direction of the cage longitudinal axis (L). [5] Device (10) according to any one of the preceding claims, characterized by , that the sealing unit (300, 300', 300'') comprises an elastomer ring (310) and a sealing ring (320), wherein the elastomer ring (310) is arranged in a permanent stress state in a receptacle (150, 150', 150''). [6] Device (10) according to claim 5, characterized by , that the sealing ring (320) is in direct contact with the piston (200). [7] Device (10) according to any one of the preceding claims, characterized by , that the device (10) has a second sealing unit (300') which is assigned to the first guide section (210) of the piston (200) and seals the cage interior (I) against a drive-side section of the device (10). [8] Device (10) according to any one of the preceding claims, characterized by, that the device (10) has a third sealing unit (300'') which is assigned to the second guide section (230) of the piston (200) and seals the cage interior (I) against an inlet (P) or the device (10) oriented in the direction of the cage longitudinal axis (L). [9] Device (10) according to any one of the preceding claims, characterized by , that the device (10) has at least three sealing units (300, 300', 300''), each of the three sealing units (300, 300', 300'') having an identical inner diameter (Di). [10] Device (10) according to any one of the preceding claims, characterized by , that the piston (200) is cylindrical, wherein the first guide section (210), the second guide section (230) and the outflow section (220) have an identical outer diameter (Da). [11] Device (10) according to any one of the preceding claims, characterized by, that the outflow section (220) has a plurality of radial openings (240), wherein the radial openings (240) on a shell surface of the piston (200) define an outflow area which is greater than 50%, in particular than 70%, in particular than 90% of the total shell surface of the outflow section (220). [12] Device (10) according to claim 11, characterized by , that the radial openings (240) are oriented in a slot-like manner in the direction of the longitudinal axis (L) of the piston. [13] Device (10) according to claim 11 or 12, characterized by , that the ratio of the length of the radial openings (240) in the direction of the piston longitudinal axis (L) to the length of the radial openings (240) in a circumferential direction is at least two. [14] Device (10) according to any one of claims 11 to 13, characterized by, that the number of radial openings (240) on the outflow section (220) is at least 4, in particular at least 8, in particular at least 12, in particular at least 16. [15] Device (10) according to any one of claims 11 to 14, characterized by , that the radial openings (240) are arranged evenly distributed in the circumferential direction. [16] Device (10) according to claim 15, characterized by , that the radial openings (240) are formed in a net-like pattern. [17] Device (10) according to any one of the preceding claims, characterized by , that the cage (100) has radially external sealing elements (160) to seal the inlet (P), the first outlet (A) and the second outlet (B) into a space (30) from each other.

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