Device for regulating the flow and expanding the fluid in a fluid circuit

Abstract

The invention relates to a device for regulating the throughflow and expanding a fluid, in particular a refrigerant in a refrigerant circuit of an air-conditioning system of a motor vehicle. The device (1) has a housing (2) and a valve element (6) arranged in the interior of the housing (2) and at least one sealing element (11, 11a).

Description

Technical Field

[0001] This invention relates to an apparatus for regulating flow and expanding a fluid in a fluid circuit, particularly a refrigerant circuit in an air conditioning system of a motor vehicle. The apparatus has a housing and a valve element disposed within the housing, as well as at least one sealing element. The valve element and the sealing element are oriented coaxially with a longitudinal axis. In the closed state, the valve element, movably arranged relative to the housing along the longitudinal axis, abuts against the sealing element. In the open state, at least one fully circumferential gap is formed between the valve element and the sealing element. Background Technology

[0002] A valve, particularly an expansion valve, used as a device for regulating flow and expanding refrigerant performs the following functions: sealing when closed, regulating mass flow rate or expanding refrigerant according to a characteristic curve, and allowing full-load flow when the flow cross-section is opened to its maximum. Operating the valve with its flow cross-section at its maximum allows refrigerant to flow with minimal or no significant pressure loss.

[0003] In addition to the functions mentioned above, the valve should meet other standards. In this case, the transition between the sealing function and the regulating or expanding function should be as continuous as possible, and therefore without jumps within the corresponding characteristic lines. Sealing must also be guaranteed when the valve, driven by an electric motor, is not energized; therefore, the valve should be self-sealing or self-inhibiting. The valve will be configured to withstand a pressure drop across its sides. In this case, the pressure difference can reach 100 bar. The valve should be usable in a temperature range from -40°C to +180°C.

[0004] Another requirement for valves is to avoid emitting noise in the form of flow noise and whistling noise during operation, specifically during valve flow. A particular challenge is that bidirectional flow valves may be charged in a first direction or a second direction opposite to the first direction, depending on the type of system operation. For example, when the system is operating in refrigeration system mode, the refrigerant valve used in the refrigerant circuit of a motor vehicle's air conditioning system flows in the first direction, while when the system is operating in heat pump mode, the refrigerant valve flows in the second direction.

[0005] DE 10 2016 013 492A1 discloses an electrically driven expansion valve and a shut-off valve for operation with refrigerant R744. The valve has a valve body disposed within a valve body chamber, a sealing seat, and a seal oriented within the valve along the axial direction of movement of the valve body. The valve is configured such that, in the closed state, a pressure bypass to the valve body chamber exists. In this case, the valve body is provided with a through opening extending substantially axially as part of the pressure bypass. The pressure bypass extends from a connection portion through the valve body to the valve body chamber. Summary of the Invention

[0006] Technical issues

[0007] It is known from the prior art that specific geometry in the sealing region of a valve can be used to respond to flow noise and whistling noise generated when flow passes through the valve. However, with the known geometry, noise emission can only be reduced when flow passes through the valve in the first flow direction, particularly at the valve seat or throttling point; noise is still emitted when flow passes through the valve in a second flow direction deviating from the first flow direction. Furthermore, a great deal of effort is required to avoid noise emitted throughout the entire characteristic operating field during operation due to the numerous possible operating points with different valve parameters and opening positions.

[0008] Solution to the problem

[0009] The object of this invention is to provide and improve upon a device for regulating flow and expanding fluid in a fluid circuit, particularly in a refrigerant circuit, specifically in the refrigerant circuit of an air conditioning system in a motor vehicle, to meet the aforementioned requirements. In this case, the device should minimize noise emissions, particularly those independent of the flow direction. Furthermore, production should be simple, and thus the production cost of the device should be minimized.

[0010] This objective is achieved through the subject matter having the features of the independent claim. Other improvements are described in the dependent claims.

[0011] This objective is achieved by a device for regulating flow and expanding a fluid in a fluid circuit, particularly a refrigerant in a refrigerant circuit. The device has a housing and a valve element disposed within the housing, as well as at least one sealing element. The valve element and the sealing element are oriented coaxially with a longitudinal axis.

[0012] In the closed state, the valve element, which is movably arranged relative to the housing along the longitudinal axis, abuts against the sealing element. In the open state, at least one fully circumferential gap is formed between the valve element and the sealing element.

[0013] According to the concept of the present invention, at least one sealing element forms a sealing seat portion associated with a valve element. In this case, the sealing element or valve element has at least two sealing surfaces arranged spaced apart from each other in the region of the sealing seat portion along a longitudinal axis. Corresponding grooves are formed between the sealing surfaces arranged adjacent to each other.

[0014] According to another improvement of the invention, the valve element is formed as a valve needle in a rotationally symmetrical manner about a longitudinal axis, the valve needle having a generally cylindrical shape, specifically a cylindrical shape.

[0015] According to a preferred embodiment of the invention, at least one sealing element has a circular annular shape with a circular opening for receiving a valve element. In this case, the sealing surface and the groove formed between corresponding sealing surfaces arranged adjacent to each other are preferably formed in a fully circumferential manner on the inner shell surface of at least one sealing element.

[0016] At least one sealing element preferably has an annular protrusion projecting from the inner shell surface. The annular protrusion projecting from the inner shell surface preferably has an end face with a sealing seat diameter D1 facing inwards in the radial direction. The end face is understood as a free surface or a free side. The sealing seat diameter D1 has a value ranging from 1 mm to 12 mm, specifically from 5 mm to 9 mm, and particularly 7 mm.

[0017] At least two sealing surfaces and a groove formed between corresponding sealing surfaces arranged adjacent to each other are preferably disposed on an end face oriented inward along the radial direction of an annular protrusion projecting from the inner shell surface of at least one sealing element.

[0018] According to an advantageous embodiment of the invention, on one hand, the inner shell surface of at least one sealing element has a first sealing element diameter D2 in a first region where it meets a protrusion projecting from the inner shell surface in the direction along the longitudinal axis; and on the other hand, the inner shell surface of at least one sealing element has a second sealing element diameter D3 in a second region where it meets a protrusion projecting from the inner shell surface in the direction along the longitudinal axis. In this case, the first sealing element diameter D2 can be in the range of 1.05·D1 to 1.50·D1, while the second sealing element diameter D3 can be in the range of 1.20·D1 to 4.00·D1.

[0019] The legs that connect the end face of the protrusion protruding from the inner shell surface of at least one sealing element to the inner shell surface are preferably oriented with opening angles α1 and α2 relative to the longitudinal axis, respectively. In this case, the first opening angle α1, which is the angle of the first leg relative to the longitudinal axis, can have a value in the range of 0° to 100°, while the second opening angle α2, which is the angle of the second leg relative to the longitudinal axis, can have a value in the range of 30° to 90°.

[0020] Another advantage of the invention is that at least two sealing surfaces, particularly in the direction of the longitudinal axis, are parallel to each other and oriented flush.

[0021] According to another preferred embodiment of the invention, at least two sealing surfaces are formed with different extensions L-1 and L-2 in the direction of the longitudinal axis, and the groove formed between the respective sealing surfaces arranged adjacent to each other is formed with an extension LN in the direction of the longitudinal axis and a depth DN in the radial direction. In this case, the first sealing surface may have an extension L-1 in the direction of the longitudinal axis ranging from 0.2 mm to 3.0 mm, while the second sealing surface may have an extension L-2 in the direction of the longitudinal axis ranging from 0.1 mm to 10.0 mm.

[0022] The groove provided between the corresponding sealing surfaces arranged adjacent to each other can be formed with an extension LN in the direction of the longitudinal axis ranging from 0.1 mm to 10.0 mm, and a depth DN in the radial direction ranging from 0.1 mm to 4.0 mm.

[0023] According to another improvement of the invention, in the open state of the device, at least one fully circumferential first annular gap and at least one fully circumferential second annular gap are formed in the region of the sealing seat portion between the valve element and at least one sealing element. The first annular gap has an extension L-1 of a first sealing surface in the direction of the longitudinal axis, and the second annular gap has an extension L-2 of a second sealing surface in the direction of the longitudinal axis. In this case, the at least two gaps formed in the region of the sealing seat portion preferably have different extensions L-1 and L-2 in the direction of the longitudinal axis.

[0024] According to another advantageous embodiment of the invention, the valve element is arranged to be guided and held within a valve seat element or a valve seat sealing element, which respectively allow linear movement of the valve element in the direction of the longitudinal axis.

[0025] According to a first alternative embodiment of the invention, at least one sealing element is preferably formed as a valve seat seal, thereby sealing the valve element against the housing and against the valve seat element.

[0026] The valve element is specifically arranged via two sealing elements to seal against the housing and against the valve seat element. In this case, advantageously, the first sealing element is formed as a valve seat seal, thereby sealing the valve element against the housing and against the valve seat element, while the second sealing element is formed as a sliding seal, thereby sealing the valve element against the housing.

[0027] According to a second alternative embodiment of the invention, at least one sealing element is formed as a valve seat sealing element, thereby sealing the valve element against the housing. The valve element is specifically arranged to seal against the housing via two sealing elements. In this case, advantageously, the first sealing element is formed as a valve seat sealing element and the second sealing element is formed as a sliding seal, thereby sealing the valve element against the housing.

[0028] Another advantage of the invention is that an actuating element and a transmission mechanism are arranged relative to the housing along the longitudinal axis, the transmission mechanism being used to transmit the rotational motion of the actuating element about the longitudinal axis to the linear motion of the valve element. In this case, the actuating element is preferably formed as a drive shaft. The drive shaft is preferably connected to an electric motor, particularly a stepper motor or servo motor that can be configured to rotate about the longitudinal axis. The drive shaft can be fixed within the housing along the longitudinal axis and thus axially.

[0029] The housing may have connections for connecting to fluid lines, which are connected to the interior of the housing via through openings. In this case, the axes of symmetry of the through openings of the housing connections may have a common intersection point for the valve elements to be arranged.

[0030] The through opening of the first connection of the housing can preferably be oriented in a radial direction relative to the longitudinal axis, while the through opening of the second connection of the housing can be arranged on the side of the actuating element opposite to the valve element.

[0031] Furthermore, the axis of symmetry of the through opening of the second connection of the housing can be coaxially oriented with the longitudinal axis.

[0032] Advantageous embodiments of the present invention enable the use of devices for regulating flow and expanding fluid in the refrigerant circuit of an air conditioning system in a motor vehicle. The device according to the invention can be used in refrigerant circuits with different refrigerants such as R1234yf, R134A, propane, and R744.

[0033] The device of the present invention for regulating flow and expanding fluid in a fluid circuit can thus be configured as a refrigerant expansion valve, which can be flowed through in both directions and can operate without noise. Grooves additionally provided between the sealing surfaces along the longitudinal axis allow the gas to undergo pre-expansion or post-expansion, which respectively interfere with the formation of turbulence and thus prevent the development of harmonic noise.

[0034] The special geometry of the sealing seat, sealing area, or regulating area results in an overlap of positive effects, such as reduced or eliminated noise development and noise emission in the corresponding flows in both flow directions when flowing in or out.

[0035] In summary, the device according to the invention for regulating flow and expanding fluid in a fluid circuit also has the following advantages:

[0036] - The sealing area, particularly the sealing seat, of the refrigerant expansion shut-off valve is formed in a prescribed manner and with prescribed measures to avoid any kind of noise unrelated to the flow direction.

[0037] - Reliable operation over a wide temperature and pressure range, and

[0038] - To carry out simple production with the lowest possible production cost.

[0039] When the device according to the invention is used in the refrigerant circuit of the air conditioning system of a motor vehicle, particularly in a system capable of operating in heat pump mode, a significant amount of energy is used as heating energy. Besides direct energy savings, the scope and therefore acceptance can be increased, especially in the case of motor vehicles driven by electric motors. Attached Figure Description

[0040] Further details, features, and advantages of embodiments of the present invention will become apparent from the following description of exemplary embodiments with reference to the accompanying drawings. As follows:

[0041] Figure 1a and Figure 1b : A device for regulating flow and expanding fluid in a fluid circuit, shown in a transverse cross-section and in the closed state. The device has a housing, a valve element disposed inside the housing, and an actuating element with a belt drive.

[0042] Figure 1c and Figure 1d The valve element and the actuator with a transmission mechanism located within the housing are shown in detailed sectional perspective and plan view, respectively.

[0043] Figure 1e : A detailed view of the arrangement of valve elements within the valve seat or sealing elements.

[0044] Figure 2a and Figure 2b The fluid in the corresponding cross-section of the device passes through a channel used to regulate the flow and make... Figures 1a to 1e The flow direction of the flow expansion device,

[0045] Figure 2c and Figure 2d : Figure 2a and Figure 2b The embodiments shown in the diagram represent alternative implementations of the prior art sealing regions formed between the valve element and the sealing element, respectively.

[0046] Figures 3a to 3c : Figures 2a to 2d A schematic view of a prior art sealing seat portion formed between a valve element and a sealing element.

[0047] Figure 4a and Figure 4b Detailed views of the sealing areas formed between the valve element and the sealing element that forms the valve seat sealing element.

[0048] Figure 5 The different shapes and orientations of the grooves formed in the sealing seat, and their combinations, and

[0049] Figure 6 Compared to Figure 4b A detailed view of another embodiment of a sealing region with a different number of grooves formed in the sealing seat portion between the valve element and the sealing element. Detailed Implementation

[0050] exist Figure 1a and Figure 1b The diagram shows a device 1, specifically a valve 1, in the closed state of the device 1, for regulating flow and expanding fluid in a fluid circuit, specifically in the refrigerant circuit of the air conditioning system of a motor vehicle. The device 1 has a housing 2 and a valve element 6 arranged within the housing 2, as well as an actuating element 4 with a belt drive 5. The device 1, and particularly the valve element 6, is driven by an electric motor 3. The electric motor 3 places the drive shaft, which forms the actuating element 4, in a rotational motion 4a.

[0051] By means of a transmission device 5, specifically a thread, or more specifically a so-called motion thread, oriented axially on the drive shaft 4, the rotational motion 4a of the drive shaft 4 is transmitted around the longitudinal axis of the drive shaft 4 into a translational stroke motion of the valve element 6, preferably formed as a valve needle. The translational stroke motion thus corresponds to a linear motion 6a of the valve element 6 in the axial direction and therefore in the direction of the longitudinal axis of the drive shaft 4.

[0052] The threaded pair of the transmission device 5 is provided between the drive shaft 4 and the valve element 6. In this case, the free end of the drive shaft 4, which is generally cylindrical, particularly a cylindrical rod with a cross-section of different diameters, is inserted into the opening 6b formed in the valve element 6. The free end of the drive shaft 4 is located at the distal end of the end connected to the electric motor 3. The drive shaft 4 therefore has an external thread on its free end, which is the first element of the threaded pair, and an internal thread, which is the second element of the threaded pair, is formed in the opening 6b of the valve element 6.

[0053] Valve element 6 is arranged in valve seat element 7. In this case, valve element 6, which moves linearly in the axial direction and extends substantially in the axial direction, is held by anti-slip rotation device 8, which prevents the valve element 6 from rotating about the axial direction or about the longitudinal axis of the valve element 6, and allows linear movement 6a in the axial direction.

[0054] The valve element 6 has a shaped portion 6c located within the housing 2 in a region that slides along the housing 2. The shaped portion 6c is formed on the end of the valve element 6 near the oriented end of the electric motor 3 and protrudes from the valve element 6 in an opposite manner. The shaped portion 6c is particularly... Figure 1c and Figure 1d As seen in the diagram. Therefore, valve element 6 has a T-shape in the cross-section passing through the longitudinal axis. Figure 1c and Figure 1d In the figure, valve element 6 and actuating element 4 are shown together with transmission device 5 inside housing 2 in detailed sectional perspective view and plan view, respectively.

[0055] In the region of the formed portion 6c of the valve element 6, the housing 2 is formed with notch-shaped or groove-shaped recesses 2a. These recesses 2a are arranged opposite to each other about the longitudinal axis of the valve element 6, and the shapes of the recesses 2a correspond to the formed portion 6c of the valve element 6. In this case, the shapes of the recesses 2a of the housing 2 correspond to the outer shape of the formed portion 6c of the valve element 6 plus the clearance used for the sliding movement of the valve element 6 in the axial direction within the housing 2.

[0056] By arranging the T-shaped forming portion 6c of the valve element 6 within the recessed or grooved portion 2a of the housing 2, rotational movement of the valve element 6 driven by the actuating element 4 rotating around the longitudinal axis is avoided. Therefore, the valve element 6 is moved into linear motion 6a by the rotational motion 4a of the actuating element 4, without rotating itself around the longitudinal axis.

[0057] The device 1 also includes a first connecting portion 9 and a second connecting portion 10. The through opening 9a of the first connecting portion is oriented radially relative to the valve element 6, while the through opening 10a of the second connecting portion 10 is oriented axially relative to the valve element 6. The through opening 9a of the first connecting portion 9 is filled with refrigerant at a first pressure p1, such that pressure p1 acts on the valve element 6 approximately radially. The through opening 10a of the second connecting portion 10 is filled with refrigerant at a second pressure p2, such that pressure p2 acts on the valve element 6 approximately axially. All pressure surfaces of the valve element 6 are adjusted so that the valve element 6 is arranged in a nearly isostatic state. The pressure acting on the valve element 6 is balanced. The section 5a, which is formed into a flat area in the region of the thread that was originally a circular cross-section, ensures pressure balance in the axial direction regarding the second pressure p2 within the valve 1 when the flow opening and the opening 6b of the valve element 6 are combined to form a through hole.

[0058] Furthermore, the valve element 6 is arranged to seal against the housing 2 and against the valve seat element 7 via two sealing elements 11 and 12, specifically the first static sealing element 11 and the second dynamic sealing element 12, which are arranged to seal against the housing 2. The first sealing element 11 is formed as a seat seal, particularly as a valve seat seal, while the second sealing element 12 is formed as a sliding seal, particularly as a rod seal in the shape of an axial seal or an annular seal. Therefore, the first sealing element 11 is arranged between the housing 2, the valve element 6, and the valve seat element 7.

[0059] Figure 1e Detailed views of the arrangement of valve element 6 within valve seat element 7 or within first sealing element 11 are shown respectively.

[0060] When the device 1 is closed, the valve element 6 abuts against the first sealing element 11 in the sealing area 13. When the device 1 is open, the valve element 6 is displaced axially relative to the first sealing element 11, so that a completely circumferential gap is formed between the valve element 6 and the first sealing element 11.

[0061] The sealing region 13 has a sealing surface extending circumferentially around the first sealing element 11 and a sealing surface extending circumferentially around the valve element 6. These two sealing surfaces are tapered in a similar manner relative to the longitudinal axis and are related to each other. In the closed state of the device 1, the sealing surfaces of the first sealing element 11, which are also connected to the housing 2 and the valve seat element 7 in a sealing manner, and the sealing surfaces of the valve element 6 are supported against each other in a fluid-tight manner.

[0062] The tapered sealing surface of valve element 6 extends 0.05 mm along the longitudinal axis of valve element 6 in sealing region 13 at an angle δ ranging from 3° to 10°, particularly from 3° to 6°, relative to the longitudinal axis. Due to the tapered design of the sealing surface, valve element 6 can be inserted into the first sealing element 11 in a centered manner when device 1 is being closed.

[0063] With device 1 in the open state, the sealing surfaces of valve element 6 and sealing element 11 are arranged spaced apart from each other. Next to sealing region 13, valve element 6 has adjusting region 14, which are arranged adjacent to each other in the axial direction. The adjusting surface of adjusting region 14 is tapered, like the sealing surface of sealing region 13, and is oriented at an angle γ relative to the longitudinal axis of sealing region 13 at a 6 mm extension along the longitudinal axis of valve element 6, ranging from 0.5° to 2°, particularly from 1° to 2°.

[0064] The sealing surface of sealing region 14 and the adjusting surface of adjusting region 14 are oriented in a similar conical manner. Due to the conical shape of the adjusting surface of adjusting region 14 in the direction of the longitudinal axis of valve element 6, the flow cross-section of the fluid being guided through device 1 continuously changes with the linear axial movement 6a of valve element 6 until valve element 6 is completely removed from first sealing element 11 or device 1 is closed, and valve element 6 is supported against first sealing element 11 in a fluid-tight manner. The mass flow rate of the fluid passing through device 1 is adjusted by means of the linear movement 6a of valve element 6 relative to first sealing element 11, combined with the adjusting surface of adjusting region 14.

[0065] Figure 2a and Figure 2b The cross-sectional representations of device 1 are shown respectively, using the method of... Figures 1a to 1e The flow directions 15-1 and 15-2 are determined by the flow direction of the fluid through the device 1 used to regulate the flow and expand the fluid. Figure 2c and Figure 2d It shows in Figure 2a and Figure 2b The device shown in Figure 2A represents an alternative embodiment of the prior art sealing regions formed between valve element 6 and sealing element 11a'. This is in contrast to the embodiment shown in Figure 2A. Figure 2b In one embodiment, the sealing element 11a' combines the functions of the first sealing elements 11, 11' and the valve seat element 7. In this case, the valve seat element 7 and the first sealing elements 11, 11' are formed as an integral part as the sealing element 11a', particularly as the so-called valve seat element.

[0066] According to the flow direction 15-1, 15-2 of the fluid through the device, the sealing area of ​​the device known from the prior art has sealing surfaces formed in different ways, especially on the sealing elements 11', 11a'.

[0067] according to Figure 2a and Figure 2c The fluid flows along the first flow direction 15-1, enters the device through the through opening 9a of the first connecting portion 9 (serving as an inlet), and exits the device through the valve seat element 7 and the first sealing element 11', or through the sealing element 11a' formed as a valve seat sealing element, and through the through opening 10a of the second connecting portion 10 (serving as an outlet). In contrast, according to Figure 2b and Figure 2d The fluid flows in the opposite direction to the first flow direction 15-1, through the through opening 10a of the second connection 10 as an inlet, into the device, and flows out of the device through the first sealing element 11' and the valve seat element 7, or through the sealing element 11a' formed as a valve seat sealing element and through the through opening 9a of the first connection 9 as an outlet.

[0068] Fluid flows between the sealing surfaces formed on the sealing elements 11' and 11a' and the housing surface of the valve element 6, respectively. Figures 2a to 2d In the flow directions 15-1 and 15-2 indicated in the diagram, the fluid flows through the device with essentially no noise. However, when the fluid flows in the corresponding flow direction opposite to the flow directions 15-1 and 15-2, noise is generated and emitted, particularly flow noise, specifically whistling noise.

[0069] In this case, the corresponding length of the gap formed between the sealing surfaces of the sealing elements 11', 11a' and the housing surface of the valve element 6, which extends as a free gap in the direction of the longitudinal axis, is a decisive factor in the generation and emission of noise.

[0070] Figures 3a to 3c It shows Figures 2a to 2d The schematic view of the device formed in the sealing seat portion 16' between the valve element 6 and the sealing elements 11', 11a'.

[0071] The sealing seat portion 16' has a sealing seat surface 17' oriented in the direction of the longitudinal axis, corresponding to the sealing surface of the first sealing element 11' or the sealing element 11a' formed as a valve seat sealing element. The sealing seat surface 17' is arranged completely circumferentially around the rotationally symmetric valve element 6, thereby forming a gap, in particular annular gap, with a completely constant extension in the radial direction and therefore a constant flow cross-section.

[0072] The sealing seat surface 17', which defines the annular gap on the outer side, has extensions L', La', Lb' and a sealing seat diameter D1' in the direction of the longitudinal axis. The sealing seat surface 17' is formed as an annular protrusion on the inner shell surface of the sealing elements 11' and 11a'. In this case, on the one hand, the inner shell surface of the sealing elements 11' and 11a' has a first sealing element diameter D2' in a first region that is in contact with the protrusion in the direction of the longitudinal axis, and on the other hand, the inner shell surface of the sealing elements 11' and 11a' has a second sealing element diameter D3' in a second region that is in contact with the protrusion in the direction of the longitudinal axis.

[0073] The protrusion is formed in a generally trapezoidal shape in the cross-section of a plane extending along the longitudinal axis. In this case, the sealing seat surface 17' is arranged as a free side, end face, or surface on one of two parallel sides. With the second side of the side oriented parallel to each other with the sealing seat surface 17'—also called the base of the trapezoidal portion—the protrusion connects to the inner shell surface of the sealing elements 11', 11a'.

[0074] The legs connecting the parallel sides of the trapezoidal cross-section of the protrusion are arranged relative to the longitudinal axis with opening angles α1' and α2' adjacent to the sealing seat surface 17'.

[0075] Figure 3b The sealing seat portion 16' is shown according to Figure 2c It has a sealing seat face 17' extending La' in the direction of the longitudinal axis. When the fluid flows along according to Figure 2a or Figure 2c When the flow direction 15-1 flows through the device, especially through the annular gap formed between the sealing seat surface 17' and the valve element 6, the flow is essentially noiseless. Figure 3c The sealing seat portion 16' is also shown according to Figure 2b or Figure 2d It has a sealing seat face 17' extending Lb' in the direction of the longitudinal axis. Fluid flows along according to... Figure 2b or Figure 2d The flow direction 15-2 flows through the device with virtually no noise, particularly through the annular gap formed between the sealing seat surface 17' and the valve element 6.

[0076] The extensions La' and Lb' of the sealing face 17' along the longitudinal axis are key factors influencing noise generation and emission. The optimal values ​​of the extensions La' and Lb' for achieving the lowest possible noise level through the device depend on the fluid flow directions 15-1 and 15-2. In this case, the extension La' is less than the extension Lb'. However, with the extensions La' and Lb', noise emission is suppressed only when the fluid flows through the device along the first flow directions 15-1 and 15-2, while noise is emitted when the fluid flows through the device along the corresponding opposite flow directions 15-1 and 15-2.

[0077] It is impossible to form extensions La' and Lb' on the sealing seat surface 17' that suppress noise development when both 15-1 and 15-2 flow through the device in the flow direction.

[0078] Figure 4a and Figure 4b Detailed views of the sealing region 13 formed between the valve element 6 and the sealing element 11a formed as a valve seat sealing element are shown.

[0079] The sealing seat portion 16 has two sealing surfaces 17-1 and 17-2 oriented radially inward, which are parallel and flush with each other. The sealing surfaces 17-1 and 17-2 are separated from each other by a groove 18 formed in an annular protrusion on the inner shell surface of the sealing element 11a. The sealing surfaces 17-1 and 17-2 and the groove 18 are formed completely circumferentially and thus completely closed in the circumferential direction.

[0080] Therefore, the sealing seat portion 16 represents a combination of two sealing surfaces 17-1 and 17-2, which have different extensions L-1 and L-2 in the direction of the longitudinal axis. The sealing surfaces 17-1 and 17-2 are formed on a groove 18 that has an extension LN in the direction of the longitudinal axis and a specific depth DN in the radial direction.

[0081] With this geometry of the sealing seat 16, noise development and emission are eliminated because the flow passes through the device in two flow directions that are oriented in opposite directions.

[0082] When a groove 18 is provided in the sealing seat portion 16 between the sealing surfaces 17-1 and 17-2 along the longitudinal axis, a first annular gap extending L-1 in the longitudinal axis direction and a second annular gap extending L-2 in the longitudinal axis direction are formed between the valve element 6 and the sealing element 11a. These two gaps have different lengths in the longitudinal axis direction corresponding to the extensions L-1 and L-2 of the sealing surfaces 17-1 and 17-2. In this case, the first gap with extension L-1 is longer than the second gap with extension L-2.

[0083] The periodic gas vibration disturbance is caused by the gap in the longitudinal axis direction, particularly the local flow characteristics of the different extensions L-1 and L-2 of the sealing surfaces 17-1 and 17-2, and the resulting turbulence. This is due to the gap in the longitudinal axis direction, particularly the local pre-expansion and local post-expansion of the gaseous fluid, and the resulting turbulence. This causes a variable flow toward the sealing seat 16, which avoids the generation and emission of noise caused by the variable flow passing through the device 1.

[0084] The geometry of the sealing seat portion 16 may have the following parameters related to the diameter D1 of the sealing seat portion:

[0085] - Diameter of the first sealing element D2: (1.05~1.50)·D1,

[0086] - The diameter of the second sealing element, D3: (1.20~4.00)·D1,

[0087] - Extension L-1 of the first sealing surface 17-1: (0.2~3.0)mm,

[0088] - Extension L-2 of the second sealing surface 17-2: (0.1~10.0)mm,

[0089] - Extension LN of groove 18: (0.1~10.0)mm,

[0090] - The depth DN of groove 18 is (0.1~4.0) mm.

[0091] - First opening angle α1: 0~100°, and

[0092] - Second opening angle α2: 30°~90°.

[0093] In this case, the diameter D1 of the sealing seat is in the range of 1 mm to 12 mm, specifically in the range of 5 mm to 9 mm, and especially 7 mm.

[0094] like Figure 5 and Figure 6 What we see in Figure 5 and Figure 6 The different shapes and orientations of the grooves 18, 18-1, 18-2 formed in the sealing seat portion 16 are shown, as well as their combinations, compared to those according to Figure 4b Another detailed view of an embodiment of the sealing region 13 formed between the valve element 6 and the sealing elements 11, 11a, showing different numbers of grooves 18-1, 18-2 and sealing surfaces 17-1, 17-2, 17-3 of the sealing seat portion 16, allows for the consideration of different embodiments of the sealing seat portion 16 having multiple grooves 18, 18-1, 18-2, corresponding shapes and orientations of the grooves 18, or shapes and orientations of the grooves 18-1, 18-2. In this case, the grooves 18, 18-1, 18-2 can have any shape and orientation and combination thereof. Figure 5 and Figure 6 The embodiments shown are not limited to the total possible range of variations in the embodiments.

[0095] List of reference numerals

[0096] 1. Device, valve

[0097] 2 shells

[0098] 2a Recess of housing 2

[0099] 3 electric motors

[0100] 4 Actuating elements and drive shafts

[0101] Rotational motion of actuator 4a

[0102] 5. Transmission device

[0103] 5a section

[0104] 6 valve components

[0105] Linear motion of valve element 6a

[0106] 6b valve element 6 opening

[0107] The forming part of valve element 6c

[0108] 7 Valve seat components

[0109] 8 Anti-slip rotation device

[0110] 9 First connecting part

[0111] 9a Through opening of the first connecting part 9

[0112] 10 Second connecting part

[0113] 10a Through opening of the second connecting part 10

[0114] 11, 11a, 11', 11a' (first) sealing elements

[0115] 12 Second sealing element

[0116] 13 Sealing Area

[0117] 14 adjustment zones

[0118] 15-1, 15-2 Flow direction

[0119] 16, 16' Sealing Seat

[0120] 17' Sealing Seat Section

[0121] 17-1 First sealing surface

[0122] 17-2 Second sealing surface

[0123] 17-3 Third sealing surface

[0124] 18 grooves

[0125] 18-1 First Groove

[0126] 18-2 Second Groove

[0127] D1, D1' Sealing seat diameter

[0128] D2, D2' Diameter of the first sealing element

[0129] D3, D3' Diameter of the second sealing element

[0130] Extensions of the L', La', and Lb' sealing seat surfaces

[0131] Extension of L-1 first sealing surface 17-1

[0132] Extension of L-2 second sealing surface 17-2

[0133] Extension of LN groove 18

[0134] Depth of DN Groove 18

[0135] p1, p2 pressure

[0136] α1, α1' first opening angle

[0137] α2, α2' second opening angle

[0138] Angular surface of δ sealing area 13

[0139] Angular surface of γ adjustment region 14

Claims

1. An apparatus for regulating flow and expanding fluid in a fluid circuit, the apparatus having a housing (2) and a valve element (6) disposed inside the housing (2), and at least one sealing element (11, 11a), the valve element (6) being movably arranged relative to the housing (2) along a longitudinal axis, wherein, The valve element (6) and the at least one sealing element (11, 11a) are oriented coaxially with the longitudinal axis, and The valve element (6) is arranged to abut against the at least one sealing element (11, 11a) in the closed state of the device, and in the open state of the device, at least one fully circumferential gap is formed between the valve element (6) and the at least one sealing element (11, 11a). The feature is that the at least one sealing element (11, 11a) forms a sealing seat portion (16) in relation to the valve element (6), and the sealing element (11, 11a) or the valve element (6) has at least two sealing surfaces (17-1, 17-2, 17-3) arranged spaced apart from each other in the region of the sealing seat portion (16) along the direction of the longitudinal axis, wherein corresponding grooves (18, 18-1, 18-2) are formed between the sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other, and the at least one sealing element (11, 11a) has an annular protrusion protruding from the inner shell surface, the groove being arranged on the annular protrusion.

2. The apparatus according to claim 1, characterized in that, The valve element (6) is formed in a rotationally symmetrical manner around the longitudinal axis.

3. The apparatus according to claim 2, characterized in that, The valve element (6) has a generally cylindrical shape.

4. The apparatus according to any one of claims 1 to 3, characterized in that, The at least one sealing element (11, 11a) has the form of a circular ring with a circular opening for receiving the valve element (6).

5. The apparatus according to claim 4, characterized in that, The sealing surfaces (17-1, 17-2, 17-3) and the grooves (18, 18-1, 18-2) formed between the respective sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other are formed in a fully circumferential manner on the inner shell surface of the at least one sealing element (11, 11a).

6. The apparatus according to claim 1, characterized in that, The annular protrusion protruding from the inner shell surface of the at least one sealing element (11, 11a) has an end face oriented radially toward the interior, the end face having a sealing seat diameter D1.

7. The apparatus according to claim 6, characterized in that, The at least two sealing surfaces (17-1, 17-2, 17-3) and the grooves (18, 18-1, 18-2) formed between the respective sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other are formed on the end face oriented toward the interior along the radial direction of the annular protrusion protruding from the inner shell surface of the at least one sealing element (11, 11a).

8. The apparatus according to claim 6 or 7, characterized in that, The diameter D1 of the sealing seat has a value ranging from 1 mm to 12 mm.

9. The apparatus according to claim 8, characterized in that, The diameter D1 of the sealing seat has a value ranging from 5 mm to 9 mm.

10. The apparatus according to claim 9, characterized in that, The diameter D1 of the sealing seat is 7 mm.

11. The apparatus according to claim 8, characterized in that, On one hand, the inner shell surface of the at least one sealing element (11, 11a) has a first sealing element diameter D2 in a first region where it meets the annular protrusion protruding from the inner shell surface in the direction along the longitudinal axis, and on the other hand, the inner shell surface of the at least one sealing element (11, 11a) has a second sealing element diameter D3 in a second region where it meets the annular protrusion protruding from the inner shell surface in the direction along the longitudinal axis.

12. The apparatus according to claim 11, characterized in that, The diameter D2 of the first sealing element has a value in the range of 1.05·D1 to 1.50·D1.

13. The apparatus according to claim 11 or 12, characterized in that, The diameter D3 of the second sealing element has a value ranging from 1.20·D1 to 4.00·D1.

14. The apparatus according to any one of claims 6 to 13, characterized in that, The end face of the annular protrusion protruding from the inner shell surface of the at least one sealing element (11, 11a) is connected to the leg of the inner shell surface and oriented relative to the longitudinal axis at corresponding opening angles α1, α2.

15. The apparatus according to claim 14, characterized in that, The first opening angle α1 has a value in the range of 0° to 100°.

16. The apparatus according to claim 14 or 15, characterized in that, The second opening angle α2 has a value in the range of 30° to 90°.

17. The apparatus according to any one of claims 1 to 16, characterized in that, The at least two sealing surfaces (17-1, 17-2, 17-3) are arranged parallel to each other and flush in orientation.

18. The apparatus according to any one of claims 1 to 17, characterized in that, The at least two sealing surfaces (17-1, 17-2, 17-3) are formed to have different extensions L-1, L-2 in the direction of the longitudinal axis, and the grooves (18, 18-1, 18-2) formed between the respective sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other are formed to have an extension LN in the direction of the longitudinal axis and a depth DN in the radial direction.

19. The apparatus according to claim 18, characterized in that, The first sealing surface (17-1) has an extension L-1 in the direction of the longitudinal axis ranging from 0.2 mm to 3.0 mm.

20. The apparatus according to claim 18 or 19, characterized in that, The second sealing surface (17-2) has an extension L-2 in the direction of the longitudinal axis ranging from 0.1 mm to 10.0 mm.

21. The apparatus according to any one of claims 18 to 20, characterized in that, The grooves (18, 18-1, 18-2) formed between the respective sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other have an extension LN in the direction of the longitudinal axis ranging from 0.1 mm to 10.0 mm.

22. The apparatus according to any one of claims 18 to 21, characterized in that, The grooves (18, 18-1, 18-2) formed between the respective sealing surfaces (17-1, 17-2, 17-3) arranged adjacent to each other have a depth DN in the radial direction ranging from 0.1 mm to 4.0 mm.

23. The apparatus according to any one of claims 1 to 22, characterized in that, In the open state of the device, at least one fully circumferential first annular gap and a fully circumferential second annular gap are formed in the region of the sealing seat (16) between the valve element (6) and the at least one sealing element (11, 11a), the at least one fully circumferential first annular gap having an extension L-1 of a first sealing surface (17-1) in the direction of the longitudinal axis, and the fully circumferential second annular gap having an extension L-2 of a second sealing surface (17-2) in the direction of the longitudinal axis.

24. The apparatus according to claim 23, characterized in that, At least two of the gaps formed in the region of the sealing seat (16) have different extensions L-1 and L-2 in the direction of the longitudinal axis.

25. The apparatus according to any one of claims 1 to 24, characterized in that, The valve element (6) is arranged inside the valve seat element (7) or inside the valve seat sealing element.

26. The apparatus according to claim 25, characterized in that, The at least one sealing element (11) is formed as a valve seat seal, thereby sealing the valve element (6) against the housing (2) and against the valve seat element (7).

27. The apparatus according to claim 25 or 26, characterized in that, The valve element (6) is arranged to be sealed against the housing (2) and against the valve seat element (7) via two sealing elements (11, 12).

28. The apparatus according to claim 27, characterized in that, The first sealing element (11) is formed as a valve seat seal, thereby sealing the valve element (6) against the housing (2) and against the valve seat element (7), and the second sealing element (12) is formed as a sliding seal, thereby sealing the valve element (6) against the housing (2).

29. The apparatus according to claim 25, characterized in that, The at least one sealing element (11a) is formed as a valve seat sealing element, thereby sealing the valve element (6) against the housing (2).

30. The apparatus according to claim 29, characterized in that, The valve element (6) is arranged in a sealed manner against the housing (2) via two sealing elements (11a, 12).

31. The apparatus according to claim 30, characterized in that, The first sealing element (11a) is formed as the valve seat sealing element and the second sealing element (12) is formed as a sliding seal, thereby sealing the valve element (6) against the housing (2).

32. The apparatus according to any one of claims 1 to 31, characterized in that, An actuating element (4) and a transmission device (5) are formed relative to the housing (2) along the direction of the longitudinal axis. The transmission device (5) is used to transmit the rotational motion (4a) of the actuating element (4) about the longitudinal axis to the linear motion (6a) of the valve element (6).

33. The apparatus according to claim 32, characterized in that, The actuating element (4) is formed as a drive shaft.

34. The apparatus according to claim 33, characterized in that, The drive shaft (4) is formed in a manner that connects to the electric motor (3).

35. Use of a device according to any one of claims 1 to 34 for regulating flow and expanding fluid in a fluid circuit in a refrigerant circuit of an air conditioning system of a motor vehicle.

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