Double valve plate motorized valve

Abstract

The application provides a double valve plate electric valve, which comprises a valve body, a first valve cover, a second valve cover and an electric actuator, the first valve cover and the second valve cover are respectively arranged at opposite ends of the valve body to form a first valve cavity and a second valve cavity with a middle partition plate of the valve body, a flow path switching valve plate and an expansion throttling valve plate are respectively arranged in the two valve cavities, an axial displacement sleeve is arranged in an axial through hole of the middle partition plate, the electric valve further comprises a first driving shaft for driving the flow path switching valve plate to move horizontally and rotate, a second driving shaft for driving the expansion throttling valve plate to move horizontally and rotate, the electric actuator is provided with an output rotating shaft which is drivingly connected with the axial displacement sleeve, the axial displacement sleeve is provided with a first position which is drivingly connected with the first driving shaft and a second position which is drivingly connected with the second driving shaft, and the rotation of the output rotating shaft can drive the axial displacement sleeve to switch between the two positions along the axial direction of the axial displacement sleeve. The application effectively reduces the number of system construction assembly components, reduces the occupation of the installation space and reduces the product manufacturing cost.

Description

Technical Field

[0001] This invention relates to the field of pipeline valve design technology, specifically to a dual-plate electric valve. Background Technology

[0002] In order to achieve throttling and flow path switching of refrigerant or other fluid media, air conditioning systems are equipped with corresponding electric throttling valves and electric multi-way valves (such as five-way valves). However, in the prior art, the aforementioned electric throttling valves and electric multi-way valves are mostly configured independently. On the one hand, this makes the structure less compact and requires more installation space. On the other hand, since the electric actuators need to be configured separately for the throttling valve and the multi-way valve, the product manufacturing cost is increased. Summary of the Invention

[0003] The dual-valve plate electric valve designed in this invention can at least partially solve the above problems.

[0004] The present invention aims to provide a dual-valve plate electric valve, comprising a valve body, a first valve cover, a second valve cover, and an electric actuator. The valve body has a partition plate. The first valve cover and the second valve cover are respectively disposed at opposite ends of the valve body to form a first valve cavity and a second valve cavity with the partition plate. A flow path switching valve plate is provided in the first valve cavity, and an expansion throttling valve plate is provided in the second valve cavity. An axial through hole is formed in the partition plate, and an axial displacement sleeve is provided in the axial through hole. The valve also includes a first drive shaft for driving the flow path switching valve plate to rotate translatively and a second drive shaft for driving the expansion throttling valve plate to rotate translatably. The electric actuator has an output external spline at the free end of its output shaft. The output external spline is driven to be connected to the internal spline of the axial displacement sleeve. The axial displacement sleeve has a first position driven to be connected to the first drive shaft and a second position driven to be connected to the second drive shaft. The rotation of the output shaft can drive the axial displacement sleeve to switch between the first position and the second position along the axial direction of the output shaft.

[0005] In some embodiments, the first valve cover is located between the valve body and the electric actuator, the first drive shaft has a central through hole, the output shaft passes through the central through hole, the output external spline is located between the first drive shaft and the second drive shaft, the first drive shaft, the second drive shaft and the output shaft are coaxially arranged, the first end of the first drive shaft is formed with a first external spline that can be matched and connected with the internal spline, and the first end of the second drive shaft is formed with a second external spline that can be matched and connected with the internal spline.

[0006] In some embodiments, the outer circular wall of the axial displacement sleeve is provided with a guide groove, the guide groove including a first guide groove and a second guide groove extending circumferentially along the output shaft, the first guide groove and the second guide groove being spaced apart along the axial direction of the output shaft, and their adjacent ends being connected via an inclined third guide groove, the valve body being provided with a limit assembly, the limit assembly including a guide limit pin, the free end of the guide limit pin being slidably located within the guide groove.

[0007] In some embodiments, the limiting assembly further includes a thrust spring and a sealing plug, the thrust spring being located between the sealing plug and the guide limiting pin, the sealing plug being detachably connected to the valve body; and / or, the outer circular wall surface of the axial displacement sleeve is further provided with a pressure balancing portion penetrating both ends of its axial direction.

[0008] In some embodiments, a first elastic thrust assembly is fitted radially outward of the first drive shaft, and the first elastic thrust assembly is clamped between the first valve cover and the flow path switching valve plate; and / or, a second elastic thrust assembly is fitted radially outward of the second drive shaft, and the second elastic thrust assembly is clamped between the valve body and the expansion throttling valve plate.

[0009] In some embodiments, the second elastic thrust assembly includes a sliding bearing, a first sliding plate, a first thrust plate, and a disc spring. The sliding bearing is fitted onto one end of the second drive shaft near the axial displacement sleeve. The first sliding plate, the first thrust plate, and the disc spring are sequentially fitted onto the radially outer side of the second drive shaft in a direction away from the axial displacement sleeve. The end of the second drive shaft away from the axial displacement sleeve is rotatably connected to the second valve cover via a shaft end sleeve.

[0010] In some embodiments, a first sealing ring is provided between the output shaft and the wall of the central through hole; and / or, a second sealing ring is provided within the rotational fit clearance between the first drive shaft and the middle partition.

[0011] In some embodiments, two third sealing rings are provided between the rotational fit clearance between the output shaft and the first valve cover. The two third sealing rings are spaced apart along the axial direction of the output shaft to form a lubrication annular gap between them. An oil storage cavity is formed inside the output shaft, and the oil storage cavity communicates with the lubrication annular gap.

[0012] In some embodiments, the valve body is provided with a plurality of flow path switching interfaces, each of the flow path switching interfaces being spaced apart around the output shaft, and each of the flow path switching interfaces being formed on the side of the partition plate facing the flow path switching valve plate; and / or, the second valve cover is provided with an expansion valve inlet and an expansion valve outlet on the side end face away from the valve body.

[0013] In some embodiments, a first limiting groove is formed on the top surface of the partition plate, and the flow path switching valve plate has a first limiting pin, the first limiting pin being slidably located within the first limiting groove; and / or, a second limiting groove is formed on the top surface of the second valve cover, and the expansion throttle valve plate has a second limiting pin, the second limiting pin being slidably located within the second limiting pin.

[0014] The dual-valve plate electric valve of the present invention, on the one hand, simultaneously equips the valve body with a flow path switching valve plate and an expansion throttling valve plate, enabling the electric valve to simultaneously possess flow path switching and fluid throttling functions, achieving a high degree of component integration, effectively reducing the number of components required for system assembly, and reducing the space occupied for installation. On the other hand, by equipping the valve body with an axial displacement sleeve and utilizing its position switching to achieve drive connection between the output shaft and one of the first drive shaft and the second drive shaft respectively, it achieves independent control of flow path switching and fluid throttling, meeting the different operating conditions of the system (e.g., an air conditioning system), greatly improving the structural compactness of the electric valve, and further reducing product manufacturing costs. Attached Figure Description

[0015] Figure 1 This is a three-dimensional structural diagram of a dual-valve plate electric valve according to an embodiment of the present invention, viewed from one perspective.

[0016] Figure 2 This is a three-dimensional structural schematic diagram of a dual-valve plate electric valve according to an embodiment of the present invention from another perspective;

[0017] Figure 3 yes Figure 1 A schematic diagram of the internal structure of the dual-valve plate electric valve in the image;

[0018] Figure 4 yes Figure 1 A three-dimensional structural diagram of the valve body in the diagram;

[0019] Figure 5 yes Figure 1 A structural disassembly diagram of the valve body and some of the components assembled on it;

[0020] Figure 6 yes Figure 1 A three-dimensional structural diagram of the second valve cover, showing the sealing sleeve;

[0021] Figure 7 yes Figure 3 A three-dimensional structural diagram of the axial displacement sleeve in the process;

[0022] Figure 8 yes Figure 7 Side view of the axial displacement sleeve in the middle;

[0023] Figure 9 yes Figure 2 A three-dimensional structural diagram of the flow path switching valve plate in the middle;

[0024] Figure 10 yes Figure 2 A three-dimensional structural diagram of the first drive shaft in the process;

[0025] Figure 11 yes Figure 2 A three-dimensional structural diagram of the expansion throttle valve plate in the diagram;

[0026] Figure 12 yes Figure 2 3D structural diagram of the second drive shaft

[0027] Figure 13 This is a schematic diagram showing the change in the rotation state of the flow path switching valve plate during the counterclockwise rotation of the output shaft of the dual-valve plate electric valve of the present invention by a preset angle.

[0028] Figure 14 This is a schematic diagram showing the change in the rotational state of the expansion throttle valve plate during the counterclockwise rotation of the output shaft of the dual-valve plate electric valve of the present invention by a preset angle.

[0029] In the picture:

[0030] 1. Valve body; 11. Middle partition plate; 111. First limiting groove; 12. Limiting assembly; 121. Guide limiting pin; 122. Thrust spring; 123. Sealing plug; 124. Third sealing ring; 2. First valve cover; 21. Flow path switching valve plate; 211. Flow passage; 212. First drive connection hole; 213. First pin hole; 22. First drive shaft; 221. Second sealing ring; 222. First external spline; 223. First drive connection part; 231. Second sliding plate; 232. Second thrust plate; 233. Compression spring; 24. Third sealing ring; 3. Second valve cover; 31. Expansion throttle valve plate; 311. Flow hole; 312. Second drive connection hole; 313. Second pin hole; 32. Second drive shaft; 321. Shaft end sleeve; 322. Second external spline; 323. Second drive connection part; 331. Sliding bearing; 332. First sliding plate; 333. First thrust plate; 334. Disc spring; 34. Second limiting groove; 4. Electric actuator; 41. Output shaft; 411. Output external spline; 412. First sealing ring; 413. Oil reservoir; 414. Oil plug; 5. Axial displacement sleeve; 51. Internal spline; 52. Guide groove; 521. First guide groove; 522. Second guide groove; 523. Third guide groove; 53. Pressure balance part; 101. First interface; 1011. First port; 102. Second interface; 1021. Second port; 103. Third interface; 1031. Third port; 104. Fourth interface; 1041. Fourth port; 105. Fifth interface; 1051. Fifth port; 201. Expansion valve inlet; 202. Expansion valve outlet; 300. Sealing seat; 301. Throttling groove. Detailed Implementation

[0031] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, they are provided so that the invention will be thorough and complete, and the concept of the exemplary embodiments will be fully conveyed to those skilled in the art. In the drawings, for clarity, the thickness of regions and layers is exaggerated. The same reference numerals in the drawings denote the same or similar structures, and therefore their detailed descriptions will be omitted.

[0032] The described features, structures, or characteristics can be combined in any suitable manner in one or more embodiments. Numerous specific details are provided in the following description to give a full understanding of embodiments of the invention. However, those skilled in the art will recognize that the invention can be practiced without one or more of the specific details described, or other methods, components, materials, etc. In other instances, well-known structures, materials, or operations are not shown or described in detail to avoid obscuring aspects of the invention.

[0033] The following example describes the dual-valve plate electric valve of the present invention. This example is only a part of the embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. All other embodiments obtained by those skilled in the art without inventive effort should be covered within the scope of protection of the present invention.

[0034] Please refer to the reference. Figures 1 to 14 As shown, according to an embodiment of the present invention, a dual-valve plate electric valve is provided, including a valve body 1, a first valve cover 2, a second valve cover 3, and an electric actuator 4. The valve body 1 has a partition plate 11, which specifically forms two relatively independent grooves at both axial ends of the valve body 1. These grooves specifically serve as the main structure of the first valve cavity and the second valve cavity, as described later. The first valve cover 2 and the second valve cover 3 are respectively disposed at opposite ends of the valve body 1 to form the first valve cavity (not labeled in the figure) and the second valve cavity (not labeled in the figure) with the partition plate 11, respectively. A flow path switching valve plate 21 is provided in the first valve cavity, and an expansion throttling valve plate 31 is provided in the second valve cavity. An axial through hole (not labeled in the figure) is formed on the partition plate 11. See details below. Figure 9 As shown, corresponding flow channels 211 are formed on the flow path switching valve plate 21, so that different interfaces can be connected or disconnected by adjusting its translational rotation angle. This makes the valve body 1 corresponding to the first valve cavity objectively form a flow path switching valve structure. The number of flow channels 211 is matched with the specific requirements of flow path switching and the corresponding number of interfaces. See [link to details]. Figure 11As shown, two flow holes 311 are formed on the expansion throttling valve plate 31, so that the connection, cut-off and throttling of different interfaces can be realized by adjusting its translational rotation angle, so that the valve body 1 corresponding to the second valve cavity objectively forms an expansion throttling valve structure. An axial displacement sleeve 5 is provided in the axial through hole. It also includes a first drive shaft 22 for driving the flow path switching valve plate 21 to translate rotation and a second drive shaft 32 for driving the expansion throttling valve plate 31 to translate rotation. Specifically, the first drive shaft 22 has a first drive connection part 223, which can be a flat opening structure. The flow path switching valve plate 21 has a corresponding first drive connection hole 212. The first drive connection part 223 is inserted into the first drive connection hole 212. The second drive shaft 32 has a second drive connection part 323, which can also be a flat opening structure. The expansion throttling valve plate 31 has a corresponding second drive connection hole 312. The second drive connection part 323 is inserted into the second drive connection hole 212. The drive connection hole 312 is inserted and fitted. The free end of the output shaft 41 of the electric actuator 4 has an output external spline 411. The electric actuator 4 specifically uses electromagnetic force to drive the output shaft 41 to rotate. As is well known in the industry, the present invention does not improve the specific structure of the electric actuator 4, and will not be described in detail here. The output external spline 411 is driven to connect with the internal spline 51 of the axial displacement sleeve 5. The axial displacement sleeve 5 has a first position driven to connect with the first drive shaft 22 (at this time, the axial displacement sleeve 5 is not driven to connect with the second drive shaft 32) and a second position driven to connect with the second drive shaft 32 (at this time, the axial displacement sleeve 5 is not driven to connect with the first drive shaft 22). The rotation of the output shaft 41 can drive the axial displacement sleeve 5 to switch between the first position and the second position along the axial direction of the output shaft 41. It is understood that the aforementioned axial displacement sleeve 5 always maintains spline connection with the output shaft 41 during the switching process between the first position and the second position.

[0035] In this technical solution, on the one hand, by simultaneously configuring a flow path switching valve plate 21 and an expansion throttling valve plate 31 within the valve body 1, the electric valve simultaneously possesses both flow path switching and fluid throttling functions, achieving a high degree of component integration. This effectively reduces the number of components required for system assembly and minimizes the space occupied during installation. On the other hand, by configuring an axial displacement sleeve 5 within the valve body 1 and utilizing its position switching, the output shaft 41 is connected to one of the first drive shaft 22 and the second drive shaft 32, thereby achieving independent control of flow path switching and fluid throttling. This meets the different operating conditions required by the system (e.g., an air conditioning system), greatly improves the structural compactness of the electric valve, and further reduces product manufacturing costs.

[0036] In some embodiments, the first valve cover 2 is located between the valve body 1 and the electric actuator 4. The first drive shaft 22 has a central through hole, through which the output shaft 41 passes (not shown in the figure). The output external spline 411 is located between the first drive shaft 22 and the second drive shaft 32. The first drive shaft 22, the second drive shaft 32, and the output shaft 41 are coaxially arranged. The first end of the first drive shaft 22 has a first external spline 222 that can be matched and connected (i.e., spline meshing) with the internal spline 51. The first end of the second drive shaft 32 has a first external spline 222 that can be matched and connected (i.e., spline meshing) with the internal spline 51. The second external spline 322 of the 51-matching connection (i.e. spline engagement) is understood to mean that, in order to ensure that the output external spline 411 can mate with the internal spline 51 while also achieving the matching connection between the internal spline 51 and the aforementioned first external spline 222 and second external spline 322, the outer diameter of the aforementioned output external spline 411 should be consistent with the outer diameter of the first external spline 222 and second external spline 322. In order to ensure the passage assembly of the output shaft 41, the output external spline 411 should pass through the free end of the output shaft 41 and extend out of the central through hole before being assembled on the free end of the output shaft 41. This can be done by welding or interference fit.

[0037] In this technical solution, the output shaft 41 passes through the central through hole of the first drive shaft 22 and is coaxially arranged with the first drive shaft 22 and the second drive shaft 32, which can greatly simplify the structural design and further improve the structural compactness of the electric valve.

[0038] In some embodiments, the outer circular wall of the axial displacement sleeve 5 is provided with a guide groove 52. The guide groove 52 includes a first guide groove 521 and a second guide groove 522 extending circumferentially along the output shaft 41. The first guide groove 521 and the second guide groove 522 are spaced apart along the axial direction of the output shaft 41, and their adjacent ends are connected via an inclined third guide groove 523, so that the guide groove 52 is approximately Z-shaped. A limit assembly 12 is provided on the valve body 1. The limit assembly 12 includes a guide limit pin 121, the free end of which slides in the guide groove. Within 52, it is understood that the circumferential extension length of the aforementioned first guide groove 521 and second guide groove 522 is specifically adapted to the magnitude of the translational rotation angle of the corresponding flow path switching valve plate 21 and expansion throttling valve plate 31. The axial extension length of the aforementioned third guide groove 523 along the output rotating shaft 41 is specifically related to the meshing length of the axial displacement sleeve 5 with the first drive shaft 22 and the second drive shaft 32. In principle, under the premise that the axial displacement sleeve 5 is completely disengaged from the second drive shaft 32 when it is in the first position and completely disengaged from the first drive shaft 22 when it is in the second position, the shorter the better, which is beneficial to improving the response rate of the electric valve.

[0039] In this technical solution, a Z-shaped guide groove 52 is provided on the outer circular wall of the axial displacement sleeve 5, and a limiting component 12 is provided on the valve body 1. The free end of the guide limiting pin 121 of the limiting component 12 is slidably disposed in the guide groove 52. When the output shaft 41 drives the axial displacement sleeve 5 to rotate and the guide limiting pin 121 is in the third guide groove 523, the guide limiting pin 121 remains fixed to the valve body 1 (fixed in the circumferential direction). Since the inner spline 51 of the axial displacement sleeve 5 and the output outer spline 411 only limit each other in the circumferential direction, the axial displacement sleeve 5 remains fixed to the valve body 1. With upward sliding freedom, the axial displacement sleeve 5 will move rapidly along the axial direction of the output shaft 41 toward the first drive shaft 22 or the second drive shaft 32, thereby realizing the drive connection between the axial displacement sleeve 5 and the first drive shaft 22 or the second drive shaft 32. That is, the electric actuator 4 realizes the translational rotation drive of the flow path switching valve plate 21 or the expansion throttle valve plate 31. It can be understood that the movement direction of the axial displacement sleeve 5 along its axial direction is specifically determined according to the rotation direction of the output shaft 41 and the matching position of the guide limit pin 121 with the first guide groove 521 or the second guide groove 522.

[0040] In this technical solution, a sliding assembly relationship is adopted between the guide limiting pin 121, which is fixed in the circumferential direction relative to the valve body 1, and the Z-shaped guide groove 52 on the outer circular wall of the axial displacement sleeve 5. The axial sliding of the axial displacement sleeve 5 is achieved by the relative rotation drive of the output shaft 41, thereby achieving the purpose of switching between the first position and the second position. The structure is simple and novel.

[0041] In some embodiments, the limiting assembly 12 further includes a thrust spring 122 and a sealing plug 123. The thrust spring 122 is located between the sealing plug 123 and the guide limiting pin 121. The sealing plug 123 is detachably connected to the valve body 1. In order to prevent fluid leakage, in a preferred embodiment, a third sealing ring 124 is provided between the sealing plug 123 and the valve body 1.

[0042] In this technical solution, the axial assembly of the thrust spring 122 and the guide limit pin 121 is limited by the sealing plug 123. The thrust spring 122 can achieve elastic compensation of the guide limit pin 121 and the axial displacement sleeve 5, which can ensure the smooth switching of the position of the axial displacement sleeve 5 while reducing the wear between the two.

[0043] In some embodiments, the outer circular wall of the axial displacement sleeve 5 is further provided with a pressure balancing part 53 that penetrates both ends of its axial direction. Specifically, the pressure balancing part 53 can be a through hole structure that penetrates both ends of the axial direction of the axial displacement sleeve 5. In a specific embodiment of the present invention, the pressure balancing part 53 is achieved by cutting a part of the solid on the outer circular wall of the axial displacement sleeve 5 to form a notch.

[0044] In this technical solution, by setting a pressure balancing part 53 on the axial displacement sleeve 5, the smoothness of its axial switching position can be further ensured, and the axial sliding position switching can be prevented from being incomplete due to the formation of high pressure at both ends of the fluid when the fluid slides axially on the axial displacement sleeve 5.

[0045] In some embodiments, a first elastic thrust assembly is fitted radially outward of the first drive shaft 22. This first elastic thrust assembly is clamped between the first valve cover 2 and the flow path switching valve plate 21 to ensure that the flow path switching valve plate 21 can be reliably attached to the top surface of the aforementioned partition plate 11, thereby achieving reliable sealing or connection of each port on the top surface of the partition plate 11 and ensuring smooth rotation of the flow path switching valve plate 21. In one specific embodiment, the aforementioned first elastic thrust assembly specifically includes a second sliding plate 231, a second thrust plate 232, and a compression spring 233 arranged sequentially near the flow path switching valve plate 21. Similarly, a second elastic thrust assembly is fitted radially outward of the second drive shaft 32, and the second elastic thrust assembly is clamped between the valve body 1 and... Between the expansion throttle valve plates 31, it is ensured that the expansion throttle valve plates 31 can be reliably attached to the top surface of the aforementioned second valve cover 3, thereby achieving reliable sealing, connection or throttling of each port on the top surface of the second valve cover 3. Specifically, the second elastic thrust assembly includes a sliding bearing 331, a first sliding plate 332, a first thrust plate 333 and a disc spring 334. The sliding bearing 331 is fitted on one end of the second drive shaft 32 near the axial displacement sleeve 5. The first sliding plate 332, the first thrust plate 333 and the disc spring 334 are sequentially fitted on the radial outer side of the second drive shaft 32 in a direction away from the axial displacement sleeve 5. The end of the second drive shaft 32 away from the axial displacement sleeve 5 is rotatably connected to the second valve cover 3 via the shaft end sleeve 321.

[0046] See also Figure 4 and Figure 5As shown, the valve body 1 is provided with multiple flow path switching interfaces (not labeled in the figure), such as the first interface 101, the second interface 102, the third interface 103, the fourth interface 104, and the fifth interface 105 shown in the figure. Each of the flow path switching interfaces is spaced around the output shaft 41, and each of the flow path switching interfaces is formed on the side of the partition plate 11 facing the flow path switching valve plate 21, so as to make the structural layout of the electric valve more reasonable. The top surface of the aforementioned partition plate 11 has a first port 1011, a second port 1021, a third port 1031, a fourth port 1041, and a fifth port 105. 51. The aforementioned ports are spaced apart around the aforementioned central through hole. In some embodiments, each of the aforementioned ports is provided with a corresponding sealing seat 300. The sealing seat 300 is made of plastic or rubber, which can ensure the sealing of each port during the rotation of the flow path switching valve plate 21. It is understood that the aforementioned first interface 101 is connected to the first port 1011, the second interface 102 is connected to the second port 1021, the third interface 103 is connected to the third port 1031, the fourth interface 104 is connected to the fourth port 1041, and the fifth interface 105 is connected to the fifth port 1051.

[0047] The second valve cover 3 has an expansion valve inlet 201 and an expansion valve outlet 202 on the side of the valve body 1 away from the valve body 1. A corresponding sealing seat 300 is provided on the expansion valve outlet 202. In order to achieve its throttling effect on the fluid, a corresponding throttling groove 301 is provided on the top surface of the sealing seat 300. In this way, different throttling areas can be adjusted by adjusting the blocking area of ​​the expansion throttling valve plate 31 on the throttling groove 301. It can be understood that the aforementioned adjustment of the throttling area is essentially achieved by the size of the rotational driving angle of the second drive shaft 32 on the expansion throttling valve plate 31.

[0048] In some embodiments, a first sealing ring 412 is provided between the output shaft 41 and the wall of the central through hole to prevent fluid in the first valve chamber and the second valve chamber from flowing through the central through hole.

[0049] In some embodiments, a second sealing ring 221 is provided in the rotational fit gap between the first drive shaft 22 and the middle partition 11 to ensure the sealing between the first valve chamber and the second valve chamber, and further prevent the fluid from flowing between the two valve chambers.

[0050] In some embodiments, a first limiting groove 111 is formed on the top surface of the partition plate 11, and the flow path switching valve plate 21 has a first limiting pin (not shown in the figure). The first limiting pin is slidably located within the first limiting groove 111. In a specific embodiment, the aforementioned flow path switching valve plate 21 is provided with a first pin hole 213, and the aforementioned first limiting pin is interference-fitted into the first pin hole 213; and / or, a second limiting groove 34 is formed on the top surface of the second valve cover 3, and the expansion throttling valve plate 31 has a second limiting pin (not shown in the figure). The second limiting pin is slidably located within the second limiting pin. In a specific embodiment, the aforementioned expansion throttling valve plate 31 is provided with a second pin hole 313, and the aforementioned second limiting pin is interference-fitted into the second pin hole 313.

[0051] In this technical solution, by setting a first limiting pin and a first limiting groove 111 and a second limiting pin and a second limiting groove 34 that match each other between the flow path switching valve plate 21 and the middle partition plate 11 and between the expansion throttling valve plate 31 and the second valve cover 3 respectively, the rotational limiting of the flow path switching valve plate 21 and the expansion throttling valve plate 31 can be realized, ensuring the accuracy of the position.

[0052] In some embodiments, two third sealing rings 24 are provided between the rotational fit clearance between the output shaft 41 and the first valve cover 2. The two third sealing rings 24 are spaced apart along the axial direction of the output shaft 41 to form a lubrication annular gap between them. An oil storage cavity 413 is formed inside the output shaft 41, and the oil storage cavity 413 communicates with the lubrication annular gap. In this way, the lubricating oil stored in the oil storage cavity 413 can be used to achieve sufficient lubrication between the output shaft 41 and the first valve cover 2 to reduce friction. At the same time, the lubricating oil can also form an oil seal on the third sealing rings 24, effectively preventing fluid in the first valve cavity from entering the electric actuator 4.

[0053] It is understandable that, in order to ensure the sealing of the entire electric valve, corresponding sealing rings are also provided at the assembly surfaces of components such as the first valve cover 2, valve body 1, and second valve cover 3, which will not be described in detail here.

[0054] The following combination Figure 13 and Figure 14 The translational rotation states of the flow path switching valve plate and the expansion throttling valve plate during the counterclockwise rotation of the output shaft at a preset angle in this invention are described, along with the correspondence between each port:

[0055] See details Figure 13As shown, with position 1 in the figure as the initial position of the output shaft 41, the flow channel 211a connects the second port 1021 and the third port 1031, and the flow channel 211b connects the fourth port 1041 and the fifth port 1051. That is, at this time, the second interface 102 is connected to the third interface 103, and the fourth interface 104 is connected to the fifth interface 105. Correspondingly, the axial displacement sleeve 5 is driven to connect to the first drive shaft 22 (during this process, the guide limit pin 121 is in the first guide groove 521). At this time, the electric actuator 4 is powered on and runs, and the output shaft 41 is driven to rotate counterclockwise (from the top view) by a first angle. The flow path switching valve plate 21 is rotated counterclockwise synchronously by an angle of 72° (72° in a specific embodiment) to position 2 in the figure. At this position, the flow channel 211a connects the third port 1031 and the fourth port 1041, and the flow channel 211b connects the fifth port 1051 and the first port 1011. That is, at this time, the third port 103 is connected to the fourth port 104, and the fifth port 105 is connected to the first port 101. This realizes the translational rotation switching of the flow path switching valve plate 21 between position 1 and position 2, thereby achieving the purpose of flow path switching. The output shaft 41 continues to be driven counterclockwise. Rotating by a second angle (38° in one specific embodiment), the guide limit pin 121 will enter the second guide groove 522 via the third guide groove 523. Thus, the axial displacement sleeve 5 will slide along the axial direction of the output shaft 41 towards the second drive shaft 32 and disengage from the first drive shaft 22 while being driven by the second drive shaft 32. Within this rotation angle range, only the axial displacement of the axial displacement sleeve 5 is achieved. The flow path switching valve plate 21 remains in a fixed position (at position 2) due to the spline guide angle design. At this time, the output shaft 41 continues to rotate counterclockwise. Within this angle range, due to the axial displacement sleeve 5 and... The second drive shaft 32 is in a drive connection state (i.e., spline engagement). As the output shaft 41 rotates counterclockwise, the through-flow holes 311a and 311b partially intersect with the throttling grooves 301 of the expansion valve inlet 201 and the expansion valve outlet 202, respectively, thereby achieving the purpose of throttling the fluid. When the output shaft 41 rotates to the maximum limiting angle (182° in a specific embodiment, i.e., the central angle corresponding to the second guide groove 522 is equal to the central angle corresponding to the first guide groove 521, both being 72°), the expansion throttling valve plate 31 stops rotating under the action of the second limiting pin and the second limiting groove 34. Figure 14 Position 4 in the middle, at this time the expansion valve inlet 201 and expansion valve outlet 202 are fully connected, and there is no throttling function. Further combined with... Figure 13 and Figure 14As shown, when the flow path switching valve plate 21 switches between position 1 and position 2, the expansion throttle valve plate 31 remains at position 3, that is, it does not rotate. When the expansion throttle valve plate 31 switches between position 3 and position 4, the flow path switching valve plate 21 remains at position 2, that is, it does not rotate. This realizes the independent rotation control of the two valve plates by the output shaft 41, and realizes the sharing of the same output shaft 41 and electric actuator 4 by the two valve plates, thus achieving the core purpose of simplifying the structure, saving space and reducing costs.

[0056] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0057] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A dual-valve plate electric valve, characterized in that, The device includes a valve body (1), a first valve cover (2), a second valve cover (3), and an electric actuator (4). The valve body (1) has a partition plate (11). The first valve cover (2) and the second valve cover (3) are respectively located at opposite ends of the valve body (1) to form a first valve chamber and a second valve chamber with the partition plate (11). A flow path switching valve plate (21) is provided in the first valve chamber, and an expansion throttling valve plate (31) is provided in the second valve chamber. An axial through hole is formed on the partition plate (11), and an axial displacement sleeve (5) is provided in the axial through hole. The device also includes a first drive shaft (22) for driving the flow path switching valve plate (21) to rotate translatively, and a drive shaft (4) for... The second drive shaft (32) drives the expansion throttle valve plate (31) to rotate linearly. The electric actuator (4) has an output external spline (411) at the free end of its output shaft (41). The output external spline (411) is driven to connect with the internal spline (51) of the axial displacement sleeve (5). The axial displacement sleeve (5) has a first position driven to connect with the first drive shaft (22) and a second position driven to connect with the second drive shaft (32). The rotation of the output shaft (41) can drive the axial displacement sleeve (5) to switch between the first position and the second position along the axial direction of the output shaft (41).

2. The dual-valve plate electric valve according to claim 1, characterized in that, The first valve cover (2) is located between the valve body (1) and the electric actuator (4). The first drive shaft (22) has a central through hole. The output shaft (41) passes through the central through hole. The output external spline (411) is located between the first drive shaft (22) and the second drive shaft (32). The first drive shaft (22), the second drive shaft (32) and the output shaft (41) are coaxially arranged. The first end of the first drive shaft (22) is formed with a first external spline (222) that can be matched and connected with the internal spline (51). The first end of the second drive shaft (32) is formed with a second external spline (322) that can be matched and connected with the internal spline (51).

3. The dual-valve plate electric valve according to claim 2, characterized in that, The outer circular wall of the axial displacement sleeve (5) is provided with a guide groove (52). The guide groove (52) includes a first guide groove (521) and a second guide groove (522) extending circumferentially along the output shaft (41). The first guide groove (521) and the second guide groove (522) are spaced apart along the axial direction of the output shaft (41), and their adjacent ends are connected by an inclined third guide groove (523). A limit component (12) is provided on the valve body (1). The limit component (12) includes a guide limit pin (121), and the free end of the guide limit pin (121) slides within the guide groove (52).

4. The dual-valve plate electric valve according to claim 3, characterized in that, The limiting assembly (12) also includes a thrust spring (122) and a sealing plug (123). The thrust spring (122) is located between the sealing plug (123) and the guide limiting pin (121). The sealing plug (123) is detachably connected to the valve body (1). And / or, the outer circular wall of the axial displacement sleeve (5) is also provided with a pressure balance part (53) that passes through both ends of its axial direction.

5. The dual-valve plate electric valve according to claim 2, characterized in that, A first elastic thrust assembly is fitted on the radial outer side of the first drive shaft (22), and the first elastic thrust assembly is clamped between the first valve cover (2) and the flow path switching valve plate (21); and / or, a second elastic thrust assembly is fitted on the radial outer side of the second drive shaft (32), and the second elastic thrust assembly is clamped between the valve body (1) and the expansion throttle valve plate (31).

6. The dual-valve plate electric valve according to claim 5, characterized in that, The second elastic thrust assembly includes a sliding bearing (331), a first sliding plate (332), a first thrust plate (333), and a disc spring (334). The sliding bearing (331) is fitted onto one end of the second drive shaft (32) near the axial displacement sleeve (5). The first sliding plate (332), the first thrust plate (333), and the disc spring (334) are sequentially fitted onto the radial outer side of the second drive shaft (32) in a direction away from the axial displacement sleeve (5). The end of the second drive shaft (32) away from the axial displacement sleeve (5) is rotatably connected to the second valve cover (3) via a shaft end sleeve (321).

7. The dual-valve plate electric valve according to claim 2, characterized in that, A first sealing ring (412) is provided between the output shaft (41) and the wall of the central through hole; and / or, a second sealing ring (221) is provided in the rotational fit gap between the first drive shaft (22) and the middle partition (11).

8. The dual-valve plate electric valve according to claim 2, characterized in that, Two third sealing rings (24) are provided between the output shaft (41) and the first valve cover (2) in rotational fit clearance. The two third sealing rings (24) are spaced apart along the axial direction of the output shaft (41) to form a lubrication ring gap between them. An oil storage cavity (413) is formed inside the output shaft (41), and the oil storage cavity (413) is connected to the lubrication ring gap.

9. The dual-valve plate electric valve according to claim 2, characterized in that, The valve body (1) is provided with multiple flow path switching interfaces, each of which is arranged at intervals around the output shaft (41), and each of which is formed on the side of the partition plate (11) facing the flow path switching valve plate (21); and / or, the second valve cover (3) is provided with an expansion valve inlet (201) and an expansion valve outlet (202) on the side end face away from the valve body (1).

10. The dual-valve plate electric valve according to claim 1, characterized in that, A first limiting groove (111) is formed on the top surface of the partition plate (11), and the flow path switching valve plate (21) has a first limiting pin, which is slidably located in the first limiting groove (111); and / or, a second limiting groove (34) is formed on the top surface of the second valve cover (3), and the expansion throttle valve plate (31) has a second limiting pin, which is slidably located in the second limiting pin.

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