Low-pressure-loss check valve, compressor and air conditioner

Abstract

The utility model provides a low-pressure-loss check valve, a compressor and an air conditioner, the low-pressure-loss check valve comprises a main valve body, the interior of the main valve body is divided into a main flow channel and a branch flow channel, and the section area of the branch flow channel is smaller than that of the main flow channel; the shape of the valve is matched with that of the main flow channel, and the valve is rotatably connected into the main flow channel; the driven piece is arranged in the branch flow channel and is connected to the valve; the shape of the piston is matched with that of the branch flow channel, and the piston can reciprocate along the branch flow channel along the flow direction of the fluid; and the driving piece is connected to the piston and can drive the driven piece and the valve to synchronously rotate forwards and backwards under the driving of reciprocating motion of the piston, so that the valve opens or closes the main flow channel. According to the low-pressure-loss check valve and the compressor and the air conditioner applying the low-pressure-loss check valve, opening and closing of the valve are achieved through the full pressure difference in the fluid flowing process, the check function of the low-pressure-loss check valve is guaranteed, meanwhile, the piston driving the valve to rotate and a transmission structure are mainly arranged in the branch flow channel, main flow loss is reduced, and the efficiency of an air conditioner system is improved.

Description

Low pressure loss check valves and compressors, air conditioners Technical Field

[0001] This utility model relates to the field of compressor check valve technology, and in particular to a low pressure loss check valve and a compressor and air conditioner that use it. Background Technology

[0002] In air conditioning systems that primarily use centrifugal compressors, backflow of fluid can damage the compressor shaft and electrical system during shutdown or other abnormal situations, affecting the safety of the air conditioning system. Therefore, a check valve must be installed to prevent backflow.

[0003] Traditional check valves are divided into piston type and flap type. They open the valve by consuming energy in the main flow channel, allowing the fluid in the main flow channel to flow in one direction. Their main structure is arranged in the main flow channel. For air conditioning systems that are sensitive to efficiency, this will cause an increase in the flow loss (pressure loss) in the main flow channel, resulting in a decrease in system efficiency.

[0004] Therefore, how to provide a check valve structure that can satisfy the check function of unidirectional fluid flow and minimize the pressure loss of the main flow channel is a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0005] This invention proposes a low-pressure-loss check valve and compressors and air conditioners using it, to solve the technical problem that the main structure of traditional check valves is located in the main flow channel, which causes increased pressure loss in the main flow channel.

[0006] To solve the above problems, the technical solution adopted by this utility model is as follows:

[0007] This utility model provides a low-pressure-loss check valve, comprising:

[0008] The main valve body is internally divided into a main flow channel and a branch flow channel with a smaller cross-sectional area than the main flow channel;

[0009] The valve is shaped to match the main channel and is rotatably connected to the main channel.

[0010] The driven component is located in the branch channel and connected to the valve;

[0011] The piston, whose shape matches the shape of the branch channel, can reciprocate along the branch channel with the direction of fluid flow;

[0012] The driving component is connected to the piston and can drive the driven component and valve to rotate synchronously in the forward and reverse directions under the drive of the piston's reciprocating motion, so as to open or close the main flow channel of the valve.

[0013] Preferably, the main valve body includes:

[0014] The first valve body is internally divided into a first main flow channel and a first branch flow channel with a cross-sectional area smaller than that of the first main flow channel;

[0015] The second valve body is connected to the first valve body. The interior of the second valve body is divided into a second main flow channel and a second branch flow channel that are respectively matched with the first main flow channel and the first branch flow channel. The second main flow channel is connected to the first main flow channel to form a main flow channel, and the second branch flow channel is connected to the first branch flow channel to form a branch flow channel.

[0016] Preferably, the first valve body has a first groove at the end of the first partition separating the first main channel and the first branch channel, and the second valve body has a second groove at the end of the second partition separating the second main channel and the second branch channel. The first groove and the second groove are joined together to form a hinge hole.

[0017] One end of the valve is provided with a hinge shaft passing through a hinge hole. The driven member is connected to the end of the hinge shaft that extends into the branch channel. The valve is rotatably connected to the junction of the first main channel and the second main channel through the hinge shaft and the hinge hole.

[0018] Preferably, the driven member is a driven gear, and the driving member is a driving rack that meshes with the driven gear.

[0019] Preferably, a first limiting structure is provided at one end of the drive rack facing the first valve body, and a second limiting structure is provided at the opposite end of the drive rack facing the second valve body. The first limiting structure is used to restrict the valve from rotating to an axis parallel to the main valve body when the piston moves toward the second branch channel, and the second limiting structure is used to restrict the valve from rotating to an axis perpendicular to the main valve body when the piston moves toward the first branch channel.

[0020] Preferably, the first valve body and the second valve body, the first main flow channel and the second main flow channel, and the first branch flow channel and the second branch flow channel are mirror images of each other.

[0021] Preferably, the cross-sections of the first and second main channels are circular, and the valve is a disc shape that matches the shape of the first and second main channels.

[0022] Preferably, the cross-sections of the first and second branch channels are crescent-shaped, and the piston is crescent-shaped to match the shapes of the first and second branch channels.

[0023] Preferably, the valve is provided with a first sealing ring around its periphery for engaging with the inner wall of the main flow channel, and the piston is provided with a second sealing ring around its periphery for engaging with the inner wall of the branch flow channel.

[0024] This utility model also provides a compressor, including the aforementioned low-pressure-loss check valve.

[0025] This utility model also provides an air conditioner, including the compressor described above.

[0026] Compared with the prior art, the present invention has the following beneficial effects:

[0027] The low-pressure-loss check valve and the compressors and air conditioners using it provided by this utility model utilize the total pressure difference during the fluid flow process to realize the opening and closing of the valve, ensuring the check function of the low-pressure-loss check valve (forward flow channel is open, reverse flow channel is closed). At the same time, the piston and transmission structure that drive the valve to rotate are mainly set in the branch channel, thereby reducing the main flow loss (pressure loss) and improving the efficiency of the air conditioning system. It is especially suitable for the flow channels of air conditioning systems and compressors that are sensitive to efficiency.

[0028] In addition, this low-pressure-loss check valve only requires that the piston rotate in the forward and reverse directions (the main flow channel must be fully open when the piston reaches the maximum forward stroke and the main flow channel must be fully closed when the piston reaches the maximum reverse stroke), and does not require that the valve rotation shaft remain vertical, making assembly flexible and convenient. Attached Figure Description

[0029] To more clearly illustrate the technical solution proposed by this utility model, the present utility model will be described in detail below with reference to the embodiments and accompanying drawings. It should be understood that the embodiments and accompanying drawings described in the following detailed description are merely some embodiments of this utility model, and those skilled in the art can make changes to these drawings under the concept of this utility model.

[0030] Figure 1 is a three-dimensional structural schematic diagram of an embodiment of the low pressure loss check valve provided by this utility model;

[0031] Figure 2 is a schematic diagram of the exploded structure of the low-pressure-loss check valve in Figure 1 when the valve is closed;

[0032] Figure 3 is a three-dimensional structural diagram of the first valve body of an embodiment of the low pressure loss check valve provided by this utility model;

[0033] Figure 4 is a three-dimensional structural diagram of the second valve body of an embodiment of the low pressure loss check valve provided by this utility model;

[0034] Figure 5 is a three-dimensional structural schematic diagram of an embodiment of the low pressure loss check valve provided by this utility model;

[0035] Figure 6 is a three-dimensional structural schematic diagram of the piston in an embodiment of the low pressure loss check valve provided by this utility model;

[0036] Figure 7 is a three-dimensional structural diagram of the valve and piston in the valve open state of the low pressure loss check valve provided by this utility model.

[0037] Figure 8 is a cross-sectional view of the low-pressure-loss check valve in Figure 1 in the open state along the UU direction.

[0038] Figure 9 is a cross-sectional view of the low-pressure-loss check valve in Figure 8 in the open state along the SS direction.

[0039] Figure 10 is a cross-sectional view of the low-pressure-loss check valve in Figure 8 along the TT direction.

[0040] Figure 11 is a three-dimensional structural diagram of the valve and piston in the valve open state of the low pressure loss check valve provided by this utility model.

[0041] Figure 12 is a cross-sectional view of the low-pressure-loss check valve in Figure 1 along the UU direction when the valve is closed.

[0042] Figure 13 is a cross-sectional view of the low-pressure-loss check valve in Figure 12 along the VV direction.

[0043] Figure 14 is a cross-sectional view of the low-pressure-loss check valve in Figure 12 along the WW direction;

[0044] The main markings in the attached figures are as follows:

[0045] 1. Main valve body; 11. First valve body; 111. First diversion section; 112. First transition section; 113. First connecting section; 12. Second valve body; 121. Second connecting section; 122. Second transition section; 123. Second diversion section; 2. Main flow channel; 21. First main flow channel; 22. Second main flow channel; 3. Branch flow channel; 31. First branch flow channel; 32. Second branch flow channel; 4. Valve; 41. Hinge shaft; 5. Driven component; 6. Piston; 7. Drive component; 71. Rectangular slot; 72. First limiting structure; 73. Second limiting structure; 8. First partition; 81. First dividing part; 82. Second dividing part; 83. Third dividing part; 84. First groove; 9. Second partition; 91. Fourth dividing part; 92. Fifth dividing part; 93. Sixth dividing part.

[0046] Other markings in the diagram include:

[0047] A. First manifold; B. First throttling cavity; C. Second manifold; D. Second throttling cavity; E. Hinge hole; F. Flow channel inlet; G. Flow channel outlet; H. Flow direction; X. First direction; Y. Second direction; Z. Third direction. Detailed Implementation

[0048] Please refer to Figures 1-14. The low-pressure-loss check valve provided by this utility model includes:

[0049] The main valve body 1 is internally divided into a main flow channel 2 and a branch flow channel 3 with a cross-sectional area smaller than that of the main flow channel 2; the valve 4 is shaped to match the main flow channel 2 and is rotatably connected to the main flow channel 2; the driven member 5 is located in the branch flow channel 3 and connected to the valve 4; the piston 6 is shaped to match the branch flow channel 3 and can reciprocate along the branch flow channel 3 (i.e., driven by the fluid in the direction of fluid flow) with the flow direction of the fluid; the driving member 7 is connected to the piston 6 and can drive the driven member 5 and the valve 4 to rotate synchronously in both directions under the drive of the reciprocating motion of the piston 6, so that the valve 4 can rotate to open (open the main flow channel 2) or close (close) the main flow channel 2.

[0050] Please refer to Figures 1-4 and 8-10. In this embodiment, the main valve body 1 includes:

[0051] A first valve body 11 is internally divided into a first main channel 21 and a first branch channel 31 with a cross-sectional area smaller than that of the first main channel 21. A second valve body 12 is connected to the first valve body 11 to form the main valve body 1. The second valve body 12 is internally divided into a second main channel 22 and a second branch channel 32 that match the first main channel 21 and the first branch channel 31, respectively. The second main channel 22 is connected to the first main channel 21 to form the main channel 2, and the second branch channel 32 is connected to the first branch channel 31 to form the branch channel 3.

[0052] Please refer to Figures 1-4 and 8-10. In a preferred embodiment of this example, the first valve body 11 has a first partition 8 inside that separates the first main channel 21 from the first branch channel 31. The end of the first partition 8 that is used to dock with the second valve body 12 has a first groove 84. The second valve body 12 has a second partition 9 inside that separates the second main channel 22 from the second branch channel 32. The end of the second partition 9 that is used to dock with the first partition 8 has a second groove (not shown in the figure). The first groove 84 and the second groove dock to form a closed hinge hole E.

[0053] Please refer to Figures 5-10. One end of the valve 4 is provided with a hinge shaft 41 that passes through the hinge hole E. The driven member 5 is connected to the end of the hinge shaft 41 that extends into the branch channel 3. The valve 4 is rotatably connected to the junction of the first main channel 21 and the second main channel 22 through the hinge shaft 41 and the hinge hole E. Driven by the reciprocating motion of the piston 6 along the branch channel 3, the driven member 5 and the valve 4 are driven to rotate synchronously in both directions at the junction of the first main channel 21 and the second main channel 22, so that the valve 4 rotates to the position of opening or closing the main channel 2 corresponding to the junction of the first main channel 21 and the second main channel 22.

[0054] In one embodiment of this invention, the hinge hole E can also be located near the second partition 9 of the first partition 8, so that the valve 4 is rotatably connected to the first main channel 21 near the second main channel 22 through the hinge shaft 41 cooperating with the hinge hole E. The piston 6 drives the valve 4 to rotate to open or close the position of the first main channel 21 near the second main channel 22.

[0055] In another embodiment of this invention, the hinge hole E may also be provided in the second partition 9 near the first partition 8, so that the valve 4 is rotatably connected to the second main channel 22 near the first main channel 21 through the hinge shaft 41 cooperating with the hinge hole E, and the piston 6 drives the valve 4 to rotate to open or close the position of the second main channel 22 near the first main channel 21.

[0056] In other embodiments of this example (not shown in the figure), the hinge hole E can also be provided in the middle section of the first partition 8, so that the valve 4 is rotatably connected to the middle section of the first main channel 21 through the hinge shaft 41 cooperating with the hinge hole E. The piston 6 drives the valve 4 to rotate to open or close the position of the main channel 2 corresponding to the middle section of the first main channel 21.

[0057] In other embodiments of this example (not shown in the figure), the hinge hole E can also be provided in the middle section of the second partition 9, so that the valve 4 can be rotatably connected to the middle section of the second main channel 22 through the hinge shaft 41 cooperating with the hinge hole E. The piston 6 drives the valve 4 to rotate to open or close the position of the main channel 2 corresponding to the middle section of the second main channel 22.

[0058] Please refer to Figures 5-10. In this embodiment, the driven member 5 is a driven gear, and the driving member 7 is a driving rack that meshes with the driven gear. By cooperating with the driven member 5 (driven gear) and the driving rack (driving member 7), the reciprocating linear motion of the piston 6 and the driving rack (driving member 7) is converted into the forward and reverse rotational motion of the driven member 5 (driven gear) and the valve 4.

[0059] Please refer to Figures 5-10. In a preferred embodiment of this example, a first limiting structure 72 is provided at one end of the drive rack (drive member 7) facing the first valve body 11, and a second limiting structure 73 is provided at the opposite end of the drive rack (drive member 7) facing the second valve body 12. The first limiting structure 72 is used to limit the valve 4 to rotate to the axial direction parallel to the main valve body 1 (i.e., parallel to the first direction X coaxial with the main valve body 1) when the piston 6 moves towards and close to the second branch channel 32 (away from and away from the first branch channel 31). The second limiting structure 73 is used to limit the valve 4 to rotate to the axial direction perpendicular to the main valve body 1 (i.e., perpendicular to the first direction X) when the piston 6 moves towards the first branch channel 31 (away from and away from the second branch channel 32) by limiting the valve 4 to rotate to the axial direction perpendicular to the main valve body 1 (i.e., perpendicular to the first direction X) when the piston 6 moves towards the first branch channel 31 (away from and away from the second branch channel 32).

[0060] Please refer to Figures 5-10. In a more preferred embodiment of this invention, a rectangular slot 71 extending axially is provided on one side of the middle section of the drive rack (drive member 7). The inner wall of the rectangular slot 71 is provided with a plurality of drive teeth (not shown in the figure). The inner end wall of the rectangular slot 71 facing the first valve body 11 forms the aforementioned first limiting structure 72, and the inner end wall of the rectangular slot 71 facing the opposite end of the second valve body 12 forms the aforementioned second limiting structure 73.

[0061] The driven member 5 (driven gear) is provided with a number of transmission teeth (not shown in the figure) that mesh with the aforementioned driving teeth. When the piston 6 moves forward toward and close to the second branch channel 32 (away from and away from the first branch channel 31), it makes a limiting contact with the driven member 5 (driven gear) through the first limiting structure 72 (the inner end wall of the rectangular slot 71 facing the first valve body 11). At this time, the driven member 5 (driven gear) rotates exactly 90 degrees forward, thereby limiting the valve 4 to rotate 90 degrees forward to the axial direction (first direction X) parallel to the main valve body 1, so as to maximize the opening of the main channel 2 and ensure its flow.

[0062] When the piston 6 moves in the opposite direction toward the first branch channel 31 (away from and away from the second branch channel 32), it makes a limiting contact with the driven member 5 (driven gear) through the second limiting structure 73 (the inner end wall of the rectangular slot 71 facing the opposite end of the second valve body 12). At this time, the driven member 5 (driven gear) rotates exactly 90 degrees in the opposite direction, thereby restricting the valve 4 to rotate 90 degrees in the opposite direction to the axial direction (first direction X) perpendicular to the main valve body 1, so as to completely close the main channel 2.

[0063] Please refer to Figures 1-4 and 8-10. In this embodiment, the first valve body 11 and the second valve body 12, the first main channel 21 and the second main channel 22, and the first branch channel 31 and the second branch channel 32 are mirror images of each other. The structures of the first valve body 11 and the second valve body 12 are completely identical and can be used interchangeably.

[0064] In other embodiments (not shown in the figures), the lengths of the first valve body 11 and the second valve body 12, the first main channel 21 and the second main channel 22, and the first branch channel 31 and the second branch channel 32 may be different.

[0065] Please refer to Figures 1-10. In this embodiment, both the first valve body 11 and the second valve body 12 are hollow, thin-walled cylindrical shapes. The cross-sections of the first main channel 21 and the second main channel 22 are circular. The valve 4 is a disc shape that matches the shape of the first main channel 21 and the second main channel 22.

[0066] Please refer to Figures 1 and 2. In a preferred embodiment of this example, the extension direction of the hinge shaft 41 is a third direction Z that is perpendicular to both the first direction X and the second direction Y. The first direction X, the second direction Y, and the third direction Z constitute the XYZ three-dimensional coordinate system.

[0067] Please refer to Figures 1 and 2. In one embodiment of this example, the first direction X and the second direction Y are both horizontal, and the third direction Z is vertical. That is, the axial direction (length direction) of the low-pressure-loss check valve and the flow direction H of the fluid are parallel to the first direction X. One of the radial directions (width direction) of the low-pressure-loss check valve is parallel to the second direction Y. The other radial direction (height direction) of the low-pressure-loss check valve and the rotation axis direction of the valve 4 are both parallel to the third direction Z.

[0068] In other embodiments of this example (not shown in the figure), the rotation axis direction of valve 4 may also form an angle greater than 0 degrees and less than or equal to 90 degrees with the third direction Z (when the angle is 90 degrees, the rotation axis direction of valve 4 is parallel to the second direction Y and perpendicular to the third direction Z and the first direction X).

[0069] Please refer to Figures 1-10. In this embodiment, the cross-sections of the first partition 8 and the second partition 9 are both arc-shaped. The two ends of the first partition 8 and the second partition 9 are respectively connected to the corresponding inner walls of the first valve body 11 and the second valve body 12. The cross-sections of the first branch channel 31 and the second branch channel 32 are crescent-shaped. The piston 6 is crescent-shaped, matching the shape of the first branch channel 31 and the second branch channel 32.

[0070] Please refer to Figures 1-2 and 6-8. In the preferred embodiment of this example, the drive rack (drive member 7) is connected to the side of the piston 6 with its crescent-shaped dome facing the first branch channel 31 (facing away from the second branch channel 32).

[0071] In other embodiments of this example (not shown in the figure), the drive rack (drive member 7) may also be connected to the opposite side of the crescent-shaped dome of the piston 6 facing the second branch channel 32 (away from the first branch channel 31).

[0072] In other embodiments (not shown in the figures), the cross-sections of the first main channel 21 and the second main channel 22 may be rectangular, the valve 4 may be rectangular in shape matching the shape of the first main channel 21 and the second main channel 22, the cross-sections of the first branch channel 31 and the second branch channel 32 may be U-shaped, and the piston 6 may be U-shaped in shape matching the shape of the first branch channel 31 and the second branch channel 32.

[0073] In this embodiment, the valve 4 is provided with a first sealing ring (not shown in the figure) for cooperating with the inner wall of the main flow channel 2, and the piston 6 is provided with a second sealing ring (not shown in the figure) for cooperating with the inner wall of the branch flow channel 3, so as to ensure the airtightness of the valve 4 periphery and the inner wall of the main flow channel 2, and the piston 6 periphery and the inner wall of the branch flow channel 3, respectively.

[0074] In a preferred embodiment of this invention, the first sealing ring and the second sealing ring are made of rubber or plastic.

[0075] In this embodiment, the second valve body 12 and the first valve body 11 are sealed together by a flange or welded structure to form the main valve body 1.

[0076] Please refer to Figures 1-4, 8, and 9. In this embodiment, the axial end of the first valve body 11 facing away from (away from) the second valve body 12 is the first drainage section 111. The end of the first drainage section 111 facing away from (away from) the second valve body 12 forms a flow channel inlet F. The axial end of the first valve body 11 facing (closer to) the second valve body 12 is the first connecting section 113. The axial end of the second valve body 12 facing away from (away from) the first valve body 11 is the second drainage section 123. The end of the second drainage section 123 facing away from (away from) the first valve body 11 forms a flow channel outlet G. The axial end of the second valve body 12 facing (closer to) the first valve body 11 is the second connecting section 121. The outer diameter of the first drainage section 111 is smaller than that of the first connecting section 113, and the outer diameter of the second drainage section 123 is smaller than that of the second connecting section 121.

[0077] Please refer to Figures 1-4, 8, and 9. In the preferred embodiment of this example, the first drainage section 111 is connected to the first connecting section 113 via a first transition section 112 with a gradually expanding and inclined outer diameter, and the second drainage section 123 is connected to the second connecting section 121 via a second transition section 122 with a gradually expanding and inclined outer diameter.

[0078] Please refer to Figures 1-4, 8, and 9. In a more preferred embodiment of this example, the outer diameter of the first connecting section 113 and the first transition section 112 is enlarged only at one end in the second direction Y relative to the first drainage section 111. The outer diameter of the second connecting section 121 and the second transition section 122 is enlarged only at one end in the second direction Y relative to the second drainage section 123. The first branch channel 31 and the second branch channel 32 are respectively disposed in the inner layer of the enlarged outer diameter ends of the first connecting section 113 and the second connecting section 121. That is, when the pressure difference between the upper and lower flow channels inside the low pressure loss check valve is large, the low pressure loss check valve can achieve normal operation by only setting a branch channel 3 and a piston 6 on one side (single side).

[0079] In one embodiment of this invention (not shown in the figure), the first connecting section 113 and the first transition section 112 simultaneously expand their outer diameters relative to the first guide section 111 at both ends in the second direction Y. The second connecting section 121 and the second transition section 122 simultaneously expand their outer diameters relative to the second guide section 123 at both ends in the second direction Y. A pair of first branch channels 31 and a pair of second branch channels 32 are respectively disposed in the inner layers of the first connecting section 113 and the second connecting section 121 at both ends in the second direction Y. That is, when the pressure difference between the upper and lower flow channels inside the low pressure loss check valve is small, the low pressure loss check valve simultaneously provides a pair of branch channels 3 and a pair of pistons 6 on both sides of the symmetrical double sides (both sides) to increase the area of ​​the piston 6 subjected to the fluid thrust, thereby increasing the driving force of the fluid on the piston 6 and avoiding the problem that the piston 6 cannot drive the valve 4 to fully open due to the small pressure difference between the upper and lower flow channels, or even cannot open the valve 4, causing the valve 4 to close and not work properly.

[0080] In other embodiments of this example (not shown in the figures), the cross-sections of the first partition 8 and the second partition 9 may also be circular, and the first partition 8 and the second partition 9 are respectively connected to the corresponding inner walls of the first valve body 11 and the second valve body 12 through a connecting structure. The cross-sections of the first branch channel 31 and the second branch channel 32 are annular, and the piston 6 is annular in shape matching the shape of the first branch channel 31 and the second branch channel 32.

[0081] The first connecting section 113 and the first transition section 112 simultaneously expand their outer diameters relative to the first guide section 111 in the entire circumference of the first valve body 11. The second connecting section 121 and the second transition section 122 simultaneously expand their outer diameters relative to the second guide section 123 in the entire circumference of the second valve body 12. A pair of first branch channels 31 and a pair of second branch channels 32 are respectively arranged in the inner layer of the first connecting section 113 and the second connecting section 121 in the entire circumference. That is, when the pressure difference between the upper and lower flow channels inside the low pressure loss check valve is too small, the low pressure loss check valve simultaneously arranges branch channels 3 and annular piston 6 around its circumference to maximize the area of ​​the piston 6 subjected to the fluid thrust, thereby maximizing the driving force of the fluid on the piston 6.

[0082] Please refer to Figures 1-4, 8, and 9. In a preferred embodiment of this example, the first partition 8 includes a first partition 81 extending in the first direction X and spaced apart from the first transition section 112 in a second direction Y perpendicular to the first direction X; a third partition 83 extending in the first direction X and spaced apart from the first connecting section 113 in the second direction Y; and a second partition 82 extending in the second direction Y, perpendicular to the second partition 81 and the third partition 83, and spaced apart from the first transition section 112 in the first direction X. The first drainage section 111, the first transition section 112, and the first connecting section 113 extend in the second direction Y. The first confluence cavity A, which is formed by the enlarged outer diameter of the first diversion section 111, the third partition 83, the second partition 82, and the first partition 81, connects the flow channel inlet F and the first branch channel 31. The first diversion section 111, the first transition section 112, and the first connecting section 113 are flush with the other end of the first diversion section 111 (with the same outer diameter) in the second direction Y, and together with the first partition 81, form the first throttling cavity B, which connects the flow channel inlet F and the first main flow channel 21. The cross-sectional area of ​​the first confluence cavity A is smaller than that of the first main flow channel 21 and larger than that of the first branch channel 31. The cross-sectional area of ​​the first throttling cavity B is smaller than that of the first main flow channel 21 and larger than that of the first branch channel 31.

[0083] Please refer to Figures 1-4, 8, and 9 together. In a more preferred embodiment of this example, the cross-sectional area of ​​the first throttling cavity B is equal to that of the first confluence cavity A.

[0084] Please refer to Figures 1-4, 8, and 9. In a preferred embodiment of this example, the second partition 9 includes a sixth partition 93 extending in the first direction X and spaced apart from the second transition section 122 in the second direction Y; a fourth partition 91 extending in the first direction X and spaced apart from the second connecting section 121 in the second direction Y; and a fifth partition 92 extending in the second direction Y, perpendicular to the section connecting the fourth partition 91 and the sixth partition 93, and spaced apart from the second transition section 122 in the first direction X. The second drainage section 123, the second transition section 122, and the second connecting section 121 are positioned relative to the second transition section 122 in the second direction Y. The enlarged outer diameter end of the diversion section 123, the sixth partition 93, the fifth partition 92, and the fourth partition 91 form a second confluence cavity C connecting the outlet G of the flow channel and the second branch flow channel 32. The second diversion section 123, the second transition section 122, and the second connecting section 121 are flush with the opposite end of the second diversion section 123 (with the same outer diameter) in the second direction Y, and together with the sixth partition 93, form a second throttling cavity D connecting the outlet G of the flow channel and the second main flow channel 22. The cross-sectional area of ​​the second confluence cavity C is smaller than that of the second main flow channel 22 and larger than that of the second branch flow channel 32. The cross-sectional area of ​​the second throttling cavity D is smaller than that of the second main flow channel 22 and larger than that of the second branch flow channel 32.

[0085] Please refer to Figures 1-4, 8, and 9. In a more preferred embodiment of this example, the cross-sectional area of ​​the second throttling cavity D is equal to that of the second confluence cavity C.

[0086] This utility model also provides a compressor (not shown in the figure) including the low pressure loss check valve installed in the compressor flow channel as described above.

[0087] This utility model also provides an air conditioner (not shown in the figure), which includes the compressor described above that uses the low pressure loss check valve.

[0088] Please refer to Figure 7-14. The working principle of the low-pressure-loss check valve provided by this utility model is as follows:

[0089] When the fluid flows forward from the inlet F through the first valve body 11 and the second valve body 12 to the outlet G (as shown in Figures 8 and 9, flowing from right to left along the first direction X), the upstream pressure of the low-pressure-loss check valve is greater than its downstream pressure. In the branch channel 3, the upstream side of the piston 6 is the total pressure of the fluid, and the downstream side is the static pressure of the fluid. Due to the sudden decrease in downstream pressure, the piston 6 moves rapidly from right to left along the flow direction H (in the same direction as the fluid) under the action of fluid thrust. This causes the valve 4 to rotate 90 degrees forward to be parallel to the first direction X, so that when the fluid flows forward, the valve 4 opens the main flow channel 2, ensuring that the compressor flow channel is unobstructed.

[0090] Similarly, when the fluid flows in the opposite direction from the outlet G of the flow channel through the second valve body 12 and the first valve body 11 to the inlet F of the flow channel (as shown in Figures 12 and 13, flowing from left to right along the first direction X), the upward and downward flow directions of the low-pressure loss check valve are reversed. Due to the sudden decrease in the downward pressure, the piston 6 moves rapidly from left to right against the flow direction H (opposite to the fluid) under the action of the fluid thrust, causing the valve 4 to rotate 90 degrees in the opposite direction to the first direction X, so that when the fluid flows in the opposite direction, the valve 4 closes the main flow channel 2, realizing the function of the low-pressure loss check valve to check (the forward flow channel is open and the reverse flow channel is closed).

[0091] The low-pressure-loss check valve provided by this utility model utilizes the total pressure difference during fluid flow to realize the opening and closing of valve 4, ensuring the check function of the low-pressure-loss check valve (forward flow channel is open, reverse flow channel is closed). At the same time, the piston 6 that drives the valve 4 to rotate and the transmission structure are mainly set in the branch channel 3, thereby reducing the main flow loss (pressure loss) and improving the efficiency of the air conditioning system. It is especially suitable for the flow channels of air conditioning systems and compressors that are sensitive to efficiency.

[0092] In addition, this low-pressure-loss check valve only requires the rotation direction of the piston 6 corresponding to valve 4 in both forward and reverse strokes (piston 6 must fully open the main flow channel 2 when it reaches the maximum stroke in the forward motion and fully close the main flow channel 2 when it reaches the maximum stroke in the reverse motion), and does not require the rotation axis of valve 4 to remain vertical, making assembly flexible and convenient.

[0093] The above are merely preferred embodiments of the present utility model and are not intended to limit the present utility model. Those skilled in the art should understand that any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A low-pressure-loss check valve, characterized in that, include: The main valve body (1) is divided into a main channel (2) and a branch channel (3) with a cross-sectional area smaller than that of the main channel (2); the valve (4) is shaped to match the main channel (2) and is rotatably connected to the main channel (2); the driven member (5) is located in the branch channel (3) and connected to the valve (4); the piston (6) is shaped to match the branch channel (3) and can reciprocate along the branch channel (3) with the flow direction of the fluid; the driving member (7) is connected to the piston (6) and can drive the driven member (5) and the valve (4) to rotate synchronously in the forward and reverse directions under the drive of the reciprocating motion of the piston (6) so that the valve (4) opens or closes the main channel (2).

2. The low-pressure-loss check valve as described in claim 1, characterized in that, The main valve body (1) includes: a first valve body (11), which is internally divided into a first main channel (21) and a first branch channel (31) with a cross-sectional area smaller than that of the first main channel (21); a second valve body (12), which is connected to the first valve body (11), and the second valve body (12) is internally divided into a second main channel (22) and a second branch channel (32) that are respectively matched with the first main channel (21) and the first branch channel (31), the second main channel (22) and the first main channel (21) are connected to form the main channel (2), and the second branch channel (32) and the first branch channel (31) are connected to form the branch channel (3).

3. The low pressure loss check valve as described in claim 2, characterized in that, The first valve body (11) has a first groove (84) at the end of the first partition (8) separating the first main channel (21) and the first branch channel (31). The second valve body (12) has a second groove at the end of the second partition (9) separating the second main channel (22) and the second branch channel (32). The first groove (84) and the second groove are connected to form a hinge hole (E). One end of the valve (4) is provided with a hinge shaft (41) passing through the hinge hole (E). The follower (5) is connected to the end of the hinge shaft (41) extending into the branch channel (3). The valve (4) is rotatably connected to the junction of the first main channel (21) and the second main channel (22) through the hinge shaft (41) and the hinge hole (E).

4. The low pressure loss check valve as described in claim 3, characterized in that, The driven member (5) is a driven gear, and the driving member (7) is a driving rack that meshes with the driven gear.

5. The low-pressure-loss check valve as described in claim 4, characterized in that, A first limiting structure (72) is provided at one end of the drive rack facing the first valve body (11), and a second limiting structure (73) is provided at the opposite end of the drive rack facing the second valve body (12). The first limiting structure (72) is used to restrict the valve (4) from rotating to an axis parallel to the main valve body (1) when the piston (6) moves toward the second branch channel (32). The second limiting structure (73) is used to restrict the valve (4) from rotating to an axis perpendicular to the main valve body (1) when the piston (6) moves toward the first branch channel (31).

6. The low-pressure-loss check valve as described in any one of claims 2-5, characterized in that, The first valve body (11) and the second valve body (12), the first main channel (21) and the second main channel (22), and the first branch channel (31) and the second branch channel (32) are mirror images of each other.

7. The low-pressure-loss check valve as described in claim 6, characterized in that, The first main channel (21) and the second main channel (22) have circular cross-sections, and the valve (4) is a disc shape that matches the shape of the first main channel (21) and the second main channel (22).

8. The low pressure loss check valve as described in claim 7, characterized in that, The cross-sections of the first branch channel (31) and the second branch channel (32) are crescent-shaped, and the piston (6) is crescent-shaped to match the shape of the first branch channel (31) and the second branch channel (32).

9. The low-pressure-loss check valve as described in any one of claims 1-6, characterized in that, The valve (4) is provided with a first sealing ring on its periphery for cooperating with the inner wall of the main channel (2), and the piston (6) is provided with a second sealing ring on its periphery for cooperating with the inner wall of the branch channel (3).

10. A compressor, characterized in that, Including the low pressure loss check valve as described in any one of claims 1-9.

11. An air conditioner, characterized in that, Includes the compressor as described in claim 10.

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