Pump body structure, compressor and refrigeration equipment
By setting bypass cavities and through holes on the stationary scroll plate to control gas flow, the operation problem of scroll compressors under different load conditions is solved, achieving efficient and reliable compressor operation and reducing energy consumption and wear.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- GUANGDONG MIDEA ENVIRONMENTAL TECH CO LTD
- Filing Date
- 2025-05-13
- Publication Date
- 2026-04-28
AI Technical Summary
Existing scroll compressors cannot meet the selective operating requirements under full-load and partial-load conditions, resulting in insufficient operating efficiency and reliability.
By setting a bypass cavity and through hole on the stationary scroll plate, and controlling the gas flow through a control valve, the compressor can achieve variable capacity under different load conditions. The cross-sectional area of the bypass cavity is increased to optimize gas flow and reduce flow resistance and wear.
It enables stable operation of the compressor under full load and partial load conditions, reduces energy consumption and power loss, improves overall efficiency and reliability, and extends service life.
Smart Images
Figure CN224174258U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of compressor equipment technology, and more specifically, to a pump body structure, a compressor, and a refrigeration device. Background Technology
[0002] A scroll compressor is a mechanical device used to compress gases. It typically consists of a stationary scroll assembly and a moving scroll component. The relative revolution of the scroll teeth creates a continuous change in the closed volume, making the compression chamber volume smaller and smaller, thereby compressing the gas and increasing its pressure and temperature.
[0003] Currently, in related technologies, scroll compressors have helical scroll blades on one end face of the stationary scroll, and a concave area on the other side for sealing and venting the scroll. However, since the concave area is generally a circular plane, it cannot form a bypass cavity, preventing scroll compressors in related technologies from meeting the requirement of selective operation under full-load and partial-load conditions. Utility Model Content
[0004] The embodiments of this utility model are intended to at least solve one of the technical problems existing in the prior art.
[0005] Therefore, a first aspect of the embodiments of the present invention provides a pump body structure.
[0006] A second aspect of the embodiments of this utility model provides a compressor.
[0007] A third aspect of the embodiments of this utility model provides a refrigeration device.
[0008] In view of the above, according to a first aspect of the present invention, a pump body structure is provided, the pump body structure comprising: a moving volute; a stationary volute, the stationary volute comprising a connected disc body and a mounting portion, the disc body and the moving volute forming a compression cavity, the mounting portion being located on the side of the disc body away from the moving volute; a back pressure plate disposed within the mounting portion, forming a bypass cavity with the inner wall of the mounting portion and the disc body, the bypass cavity being able to communicate with the compression cavity; and a through hole disposed on at least one of the disc body and the mounting portion, one end of the through hole communicating with the bypass cavity, and the other end of the through hole penetrating the side wall of the stationary volute.
[0009] The pump body structure provided in this embodiment includes a moving scroll, a stationary scroll, a back pressure plate, and a through hole. Specifically, the stationary scroll includes a disc body and a mounting part. The disc body and the moving scroll form a compression chamber, and the compression chamber is connected to the suction chamber of the compressor. Specifically, during the operation of the compressor, gas enters the compression chamber from the suction chamber. Since the moving scroll can move relative to the stationary scroll, it can compress the gas entering the compression chamber during the movement of the moving scroll. When the pressure of the compressed gas reaches the exhaust pressure, the compressed high-temperature and high-pressure gas is discharged from the exhaust port on the stationary scroll.
[0010] A back pressure plate is disposed within the mounting section, and the back pressure plate, the inner wall of the mounting section, and the disc body enclose a bypass cavity, through which the compression chamber can communicate. A through hole is disposed on the mounting section, or on the disc body, or part of the through hole is disposed on the mounting section and the other part on the disc body; the specific configuration can be determined according to actual needs. Since one end of the through hole connects to the bypass cavity and the other end penetrates the side wall of the stationary volute disc, optionally, the pump body structure also includes a control valve, which can control the connection or disconnection between the other end of the through hole and the suction chamber.
[0011] Specifically, under partial load conditions, the compressor's compression chamber is connected to the bypass chamber, and the bypass chamber is connected to the suction chamber through a through-hole, thereby prematurely discharging some gas and reducing displacement, cooling capacity, and energy consumption. Under full load conditions, the compression chamber and bypass chamber are cut off, and the through-hole is also cut off from the suction chamber. This ensures that the bypass chamber is isolated from the suction chamber, and normal compression begins as the volume of gas in the compression chamber continuously decreases, thus achieving the compressor's variable capacity function. By forming the bypass chamber through the inner wall of the mounting section, the disc, and the back pressure plate, and by creating a through-hole on the stationary scroll plate, the compressor can selectively operate under both full load and partial load conditions.
[0012] Optionally, the pump body structure also includes a float assembly, which is disposed on the back pressure plate. The float assembly, the back pressure plate, and the inner wall of the mounting part enclose a back pressure cavity, which can communicate with the compression cavity. Thus, during compressor operation, intermediate pressure can be introduced into the back pressure cavity. This intermediate pressure can apply axial force to the stationary scroll in the axial direction to ensure reliable meshing between the stationary scroll and the moving scroll, prevent radial leakage between the stationary scroll and the moving scroll, and improve the reliability of the compressor.
[0013] Furthermore, when the compressor operates under full load, the bypass chamber can act as a second back pressure chamber, applying axial force to the stationary scroll to further ensure that the stationary scroll presses down on the moving scroll, thus preventing abnormal noise. Moreover, when the gas pressure in the compression chamber is too high, the bypass chamber can serve as a pressure relief channel, preventing scroll wear caused by excessive pressure and further improving the compressor's reliability.
[0014] In some technical solutions, the through hole may optionally include a body and a recess, wherein the body is disposed on at least one of the mounting part and the disc body and communicates with the bypass cavity, and the recess is disposed on the disc body and communicates with the bypass cavity and the body respectively.
[0015] In this technical solution, the through hole is defined to include a body and a recess. Specifically, the body is disposed on the mounting part, or the body is disposed on the disc body, or a part of the body is disposed on the mounting part and the other part is disposed on the disc body.
[0016] By creating grooves on the disc body, which are connected to both the bypass cavity and the main body, the cross-sectional area of the bypass cavity is increased. This satisfies the compressor's stable operation requirements under both full-load and partial-load conditions. When the compressor is operating under partial-load conditions, it optimizes the buffering effect of gas flow, reduces pressure loss and flow resistance, and ensures smooth gas flow. This, in turn, reduces power loss, improves the overall efficiency of the compressor under partial-load conditions, and also reduces compressor wear, thus extending the compressor's service life.
[0017] In some technical solutions, the settling tank may optionally include a first settling tank along the radial direction of the stationary vortex disk, and the first settling tank is located inside the body.
[0018] This technical solution specifies one design method for the through-hole. Specifically, along the radial direction of the stationary scroll, the first recess is located inside the body, meaning the first recess and the body are distributed radially along the stationary scroll. Since the first recess is connected to the bypass cavity, the cross-sectional area of the bypass cavity is increased, reducing the flow resistance of the compressor under partial load conditions and improving the overall efficiency.
[0019] In some technical solutions, optionally, the end of the first settling tank away from the main body is provided with a guide wall, and the end of the guide wall away from the back pressure plate extends outward at an angle.
[0020] In this technical solution, since a guide wall is provided at the end of the first settling tank away from the main body, and the guide wall extends at an incline, the guide wall can guide the gas entering the first settling tank and the main body through the bypass cavity when the compressor is running under partial load conditions. This is beneficial to further optimize the gas flow path and ensure smooth gas flow.
[0021] In some technical solutions, optionally, along the axial direction of the stationary vortex disk, the distance between the bottom wall of the first settling tank and the side of the disk body near the back pressure plate is equal to the distance between the side of the main body near the moving vortex disk and the side of the disk body near the back pressure plate.
[0022] In this technical solution, the distance between the bottom wall of the first settling tank and the top surface of the disc is equal to the distance between the lower wall of the body and the top surface of the disc. In other words, the bottom wall of the first settling tank and the lower wall of the body are located on the same plane. This can increase the cross-sectional area of the bypass cavity, reduce the gas flow resistance under partial load conditions, facilitate the processing of through holes, reduce the processing difficulty of through holes, and thus reduce the production cost of the compressor.
[0023] In some technical solutions, optionally, the body is disposed on the disk body, and the sinking groove includes a second sinking groove along the axial direction of the stationary vortex disk, with at least a portion of the second sinking groove opposite to the body.
[0024] This technical solution defines an alternative through-hole design. Specifically, the main body is mounted on the disc, and at least part of the second recess is opposite to the main body along the axial direction of the stationary scroll. In other words, the second recess and the main body are distributed along the axial direction of the stationary scroll. Since the second recess is connected to both the bypass cavity and the main body, the cross-sectional area of the bypass cavity is increased, reducing the flow resistance of the compressor under partial load conditions and improving the overall efficiency.
[0025] Furthermore, since both the main body and the second sink are located on the disc body, i.e., through holes are opened on the disc body, compared to setting the second sink in the mounting part, while ensuring the structural strength of the mounting part and ensuring the seal between the mounting part and the back pressure plate and float plate assembly, the axial depth of the second sink can be appropriately increased due to the thickness of the disc body. This allows for maximizing the cross-sectional area of the bypass cavity and reducing pressure loss and flow resistance of the compressor under partial load conditions.
[0026] In some technical solutions, optionally, along the radial direction of the static vortex disk, the second settling tank includes opposing first and second tank walls; wherein at least one of the first and second tank walls is configured as an arc-shaped wall.
[0027] In this technical solution, the second settling tank is defined as comprising a first tank wall and a second tank wall opposite to each other. Specifically, the first tank wall and the second tank wall are arranged radially along the stationary vortex disk. Specifically, the first tank wall is an arc-shaped wall, or the second tank wall is an arc-shaped wall, or both the first and second tank walls are arc-shaped walls. The specific configuration can be determined according to actual needs. That is, the second settling tank is an arc-shaped tank.
[0028] Understandably, since the area of the disc body away from the moving scroll, i.e., the top surface of the disc body is generally a circular plane, setting the first groove wall and / or the second groove wall as an arc wall can match the shape of the disc body, thereby maximizing the cross-sectional area of the bypass cavity. When the compressor is running under partial load conditions, it further optimizes the buffering effect of the gas flow process, reduces pressure loss and flow resistance, and improves the overall efficiency of the compressor.
[0029] In some technical solutions, optionally, based on the fact that the first groove wall is an arc-shaped wall, the length M of the first groove wall in the circumferential direction of the static vortex disk and the circumference N of the circle in which the first groove wall is located satisfy M≥N / 2.
[0030] In this technical solution, since the circumferential length of the first groove wall is greater than or equal to half the circumference of the circle in which the first groove wall is located, that is, the circumferential length of the arc groove is set to be relatively long, thereby further increasing the overall cross-sectional area of the bypass cavity, reducing the flow resistance of gas under partial load conditions of the compressor, reducing power loss, and improving the overall efficiency of the compressor under partial load conditions.
[0031] In some technical solutions, the body may optionally include a connecting port that communicates with a bypass cavity, and the width of the connecting port is greater than the width of the second settling tank along the radial direction of the stationary vortex disk.
[0032] In this technical solution, since the radial width of the connecting port is greater than the radial width of the second sink, that is, the flow cross-sectional area of the connecting port is increased, when the compressor is running under partial load conditions, the gas in the compression chamber enters the bypass chamber and enters the main body through the connecting port from the bypass chamber, and then flows into the suction chamber. This process can further reduce flow resistance and power loss, which is beneficial to improving the overall efficiency of the compressor under partial load conditions.
[0033] In some technical solutions, the body may optionally include a first segment and a second segment that are connected. Along the radial direction of the stationary vortex disk, the second segment is located outside the first segment; wherein, along the axial direction of the stationary vortex disk, the width of the second segment is greater than the width of the first segment.
[0034] In this technical solution, the body is defined to include a first section and a second section, with the second section located outside the first section. Since the axial width of the second section is greater than the axial width of the first section, that is, the axial width of the second section located outside is greater than the axial width of the first section located inside, the flow resistance of the gas can be further reduced when the compressor is running under partial load conditions.
[0035] In some technical solutions, optionally, at least a portion of the settling tank extends circumferentially along the stationary vortex disk; and / or along the circumferential direction of the stationary vortex disk, the settling tank includes a first end and a second end, with a gap between the first end and the second end.
[0036] In this technical solution, since at least part of the settling groove extends circumferentially along the stationary volute, the overall cross-sectional area of the bypass cavity can be further increased. When the compressor is running under partial load conditions, the buffering effect of the gas flow process can be optimized, pressure loss and flow resistance can be reduced, and smooth gas flow can be ensured.
[0037] The trough includes a first end and a second end. Specifically, there is a gap between the first end and the second end along the circumference of the stationary vortex disk, that is, the trough is a semi-circular trough. This allows the overall cross-sectional area of the bypass cavity to be increased as much as possible while avoiding interference between the trough and other structures, thereby further improving the reliability of the pump body structure.
[0038] In some technical solutions, the disc body is optionally provided with a bypass hole, through which the compression chamber can communicate with the bypass cavity; along the radial direction of the stationary vortex disc, the sink is located outside the bypass hole.
[0039] In this technical solution, the disc body is also equipped with a bypass hole. Specifically, under partial load conditions, the compression chamber is connected to the bypass chamber through the bypass hole, and the bypass chamber is connected to the suction chamber through a through hole, thereby prematurely discharging some gas and reducing displacement, cooling capacity, and energy consumption. Under full load conditions, the bypass hole and bypass chamber are cut off, thus cutting off the compression chamber from the bypass chamber, and the through hole and suction chamber are cut off, thus cutting off the bypass chamber from the suction chamber. As the volume of gas in the compression chamber continuously decreases, normal compression begins, thereby realizing the variable capacity function of the compressor.
[0040] Since the trough is located radially outside the bypass hole, that is, the trough is set closer to the outer edge of the disc than the bypass hole, the circumferential length of the trough can be increased when at least a part of the trough extends circumferentially, thereby increasing the overall volume of the bypass cavity. This optimizes the buffering effect during gas flow and reduces flow resistance. When the compressor is running under full load, the bypass cavity, as a second back pressure cavity, can increase the axial force applied to the stationary scroll plate, prevent leakage, and help improve the overall efficiency of the compressor.
[0041] In some technical solutions, optionally, the back pressure plate has a recess on the side near the moving scroll, and the inner wall of the recess, the inner wall of the mounting part, and the disk body enclose a bypass cavity.
[0042] In this technical solution, a recess is provided on the side of the back pressure plate near the moving scroll, and the inner wall of the recess, the inner wall of the mounting part, and the plate body enclose a bypass cavity. This ensures that the compressor operates stably under full load and partial load conditions, while further increasing the cross-sectional area of the bypass cavity, improving the flow resistance of the gas under partial load conditions, optimizing the buffering effect, and reducing compressor wear.
[0043] According to a second aspect of the present invention, a compressor is provided, comprising a pump body structure as provided in any of the above technical solutions, and thus possessing all the beneficial technical effects of the pump body structure, which will not be repeated here.
[0044] According to a third aspect of this utility model, a refrigeration device is provided, including a pump body structure or compressor as provided in any of the above technical solutions, and thus possesses all the beneficial technical effects of the pump body structure or compressor, which will not be repeated here.
[0045] Additional aspects and advantages of the present invention will be set forth in the description which follows, in part will be obvious from the description, or may be learned by practice of the present invention. Attached Figure Description
[0046] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:
[0047] Figure 1 One of the structural schematic diagrams of a stationary vortex disk according to an embodiment of the present invention is shown;
[0048] Figure 2 A second schematic diagram of the structure of a stationary vortex disk according to an embodiment of the present invention is shown;
[0049] Figure 3 A partial structural schematic diagram of a pump body structure according to another embodiment of the present invention is shown;
[0050] Figure 4 One of the structural schematic diagrams of a stationary vortex disk according to another embodiment of the present invention is shown;
[0051] Figure 5 A second schematic diagram of the structure of a stationary vortex disk according to another embodiment of the present invention is shown;
[0052] Figure 6 A partial exploded view of a pump body structure according to an embodiment of the present invention is shown;
[0053] Figure 7 A schematic diagram of the structure of a compressor according to an embodiment of the present invention is shown.
[0054] in, Figures 1 to 7 The correspondence between the reference numerals and component names in the attached drawings is as follows:
[0055] 100 Pump body structure, 110 Moving scroll, 120 Stationary scroll, 121 Bypass hole, 122 Through hole, 123 Connecting port, 124 Disc body, 125 Mounting part, 126 Body, 127 Settling tank, 128 First settling tank, 129 Guide wall, 130 Back pressure plate, 131 Recess, 140 Bypass cavity, 150 Second settling tank, 151 First tank wall, 152 Second tank wall, 153 First end, 154 Second end, 160 Compression chamber, 170 Control valve, 180 Check valve, 190 Float assembly, 200 Compressor, 210 Suction chamber, 220 First section, 230 Second section, 240 Bottom wall. Detailed Implementation
[0056] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.
[0057] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.
[0058] The following reference Figures 1 to 7 This invention describes a pump body structure 100, a compressor 200, and a refrigeration device provided according to some embodiments of the present invention.
[0059] In one embodiment according to this application, such as Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, a pump body structure 100 is proposed, which includes: a moving volute 110; a stationary volute 120, the stationary volute 120 including a connected disc body 124 and a mounting part 125, the disc body 124 and the moving volute 110 forming a compression cavity 160, the mounting part 125 being located on the side of the disc body 124 away from the moving volute 110; a back pressure plate 130, disposed in the mounting part 125, and forming a bypass cavity 140 with the inner wall of the mounting part 125 and the disc body 124, the bypass cavity 140 being able to communicate with the compression cavity 160; and a through hole 122, disposed on the stationary volute 120, one end of the through hole 122 communicating with the bypass cavity 140, and the other end of the through hole 122 penetrating through the side wall of the stationary volute 120.
[0060] The pump body structure 100 provided in this embodiment of the present invention includes a moving scroll 110, a stationary scroll 120, a back pressure plate 130, and a through hole 122. Specifically, the stationary scroll 120 includes a disc body 124 and a mounting part 125. The disc body 124 and the moving scroll 110 form a compression chamber 160, and the compression chamber 160 is connected to the suction chamber 210 of the compressor 200. Specifically, during the operation of the compressor 200, gas enters the compression chamber 160 from the suction chamber 210. Since the moving scroll 110 can move relative to the stationary scroll 120, the gas entering the compression chamber 160 can be compressed during the movement of the moving scroll 110. When the pressure of the compressed gas reaches the exhaust pressure, the compressed high-temperature and high-pressure gas is discharged from the exhaust port on the stationary scroll 120.
[0061] A back pressure plate 130 is disposed within the mounting portion 125, and the back pressure plate 130, the inner wall of the mounting portion 125, and the disc body 124 enclose a bypass cavity 140, through which the compression cavity 160 can communicate. Optionally, a through hole 122 is disposed on the mounting portion 125, or a through hole 122 is disposed on the disc body 124, or a portion of the through hole 122 is disposed on the mounting portion 125 and the other portion is disposed on the disc body 124, which can be configured according to actual needs. Since one end of the through hole 122 communicates with the bypass cavity 140 and the other end of the through hole 122 penetrates the side wall of the stationary vortex disc 120, the pump body structure 100 may optionally include a control valve 170, which can control the communication or disconnection between the other end of the through hole 122 and the suction chamber 210.
[0062] Specifically, under partial load conditions, the compressor 200 connects the compression chamber 160 to the bypass chamber 140, and the bypass chamber 140 connects to the suction chamber 210 through the through hole 122, thereby prematurely discharging some gas and reducing displacement, cooling capacity, and energy consumption. Under full load conditions, the compression chamber 160 and the bypass chamber 140 are disconnected, and the through hole 122 is also disconnected from the suction chamber 210. This disconnection allows normal compression to begin as the volume of gas in the compression chamber 160 continuously decreases, thus achieving the variable capacity function of the compressor 200. By forming the bypass chamber 140 by the inner wall of the mounting part 125, the disc 124, and the back pressure plate 130, and by opening the through hole 122 on the stationary scroll 120, the compressor 200 can selectively operate under both full load and partial load conditions.
[0063] Optionally, the pump body structure 100 also includes a float assembly 190, which is disposed on the back pressure plate 130. The float assembly 190, the back pressure plate 130, and the inner wall of the mounting part 125 enclose a back pressure cavity. The back pressure cavity can communicate with the compression cavity 160, so that during the operation of the compressor 200, intermediate pressure can be introduced into the back pressure cavity. This intermediate pressure can apply axial force to the stationary scroll 120 in the axial direction to ensure reliable meshing between the stationary scroll 120 and the moving scroll 110, prevent radial leakage between the stationary scroll 120 and the moving scroll 110, and improve the reliability of the compressor 200.
[0064] Furthermore, when the compressor 200 is operating under full load, the bypass chamber 140 can serve as a second back pressure chamber, applying axial force to the stationary scroll 120 to further ensure that the stationary scroll 120 presses down on the moving scroll 110, thus preventing abnormal noise. Moreover, when the gas pressure in the compression chamber 160 is too high, the bypass chamber 140 can act as a pressure relief channel, thereby preventing scroll wear caused by excessive pressure and further improving the reliability of the compressor 200.
[0065] like Figure 1, Figure 3 , Figure 4 and Figure 5 As shown, in some embodiments, optionally, the through hole 122 includes a body 126 and a recess 127, wherein the body 126 is disposed on at least one of the mounting portion 125 and the disc body 124 and communicates with the bypass cavity 140, and the recess 127 is disposed on the disc body 124 and communicates with the bypass cavity 140 and the body 126 respectively.
[0066] In this embodiment, the through hole 122 is defined to include a body 126 and a recess 127. Specifically, the body 126 is disposed on the mounting part 125, or the body 126 is disposed on the disk body 124, or a part of the body 126 is disposed on the mounting part 125 and another part is disposed on the disk body 124.
[0067] Because a groove 127 is opened on the disc 124 and the groove 127 is connected to the bypass cavity 140 and the main body 126 respectively, the cross-sectional area of the bypass cavity 140 is increased. This meets the requirements for stable operation of the compressor 200 under full load and partial load conditions. When the compressor 200 is running under partial load conditions, it can optimize the buffering effect of gas flow, reduce pressure loss and flow resistance, ensure smooth gas flow, thereby reducing power loss and improving the overall efficiency of the compressor 200 under partial load conditions. In addition, it can also reduce the wear of the compressor 200 and help extend the service life of the compressor 200.
[0068] like Figure 1 As shown, in some embodiments, optionally, the sink 127 includes a first sink 128 along the radial direction of the stationary vortex disk 120, and the first sink 128 is located inside the body 126.
[0069] In this embodiment, one design of the through hole 122 is defined. Specifically, along the radial direction of the stationary scroll 120, the first recess 128 is located inside the body 126, that is, the first recess 128 and the body 126 are distributed along the radial direction of the stationary scroll 120. Since the first recess 128 is connected to the bypass cavity 140, the cross-sectional area of the bypass cavity 140 is increased, reducing the flow resistance of the compressor 200 under partial load conditions and improving the overall efficiency.
[0070] like Figure 1 As shown, in some embodiments, optionally, the first settling tank 128 is provided with a guide wall 129 at the end away from the body 126, and the guide wall 129 extends outward at the end away from the back pressure plate 130.
[0071] In this embodiment, since a guide wall 129 is provided at the end of the first settling tank 128 away from the main body 126, and the guide wall 129 extends at an incline, when the compressor 200 is running under partial load conditions, the guide wall 129 can guide the gas entering the first settling tank 128 and the main body 126 from the bypass cavity 140, which is beneficial to further optimize the gas flow path and ensure smooth gas flow.
[0072] like Figure 1 As shown, in some embodiments, optionally, along the axial direction of the stationary vortex 120, the distance between the bottom wall 240 of the first sink 128 and the side of the disk body 124 near the back pressure plate 130 is equal to the distance between the side of the body 126 near the moving vortex 110 and the side of the disk body 124 near the back pressure plate 130.
[0073] In this embodiment, the distance between the bottom wall 240 of the first sink 128 and the top surface of the disc 124 is equal to the distance between the lower wall of the body 126 and the top surface of the disc 124. That is, the bottom wall 240 of the first sink 128 and the lower wall of the body 126 are located on the same plane. This allows for an increase in the cross-sectional area of the bypass cavity 140 and a reduction in gas flow resistance under partial load conditions. It also facilitates the processing of the through hole 122, which helps to reduce the processing difficulty of the through hole 122 and thus reduces the production cost of the compressor 200.
[0074] like Figure 3 , Figure 4 and Figure 5 As shown, in some embodiments, optionally, the body 126 is disposed on the disk 124, and the sink 127 includes a second sink 150 along the axial direction of the stationary vortex disk 120, at least a portion of the second sink 150 being opposite to the body 126.
[0075] In this embodiment, another design for the through hole 122 is defined. Specifically, the body 126 is disposed on the disc 124, and at least part of the second recess 150 is opposite to the body 126 along the axial direction of the stationary scroll 120. That is, the second recess 150 and the body 126 are distributed along the axial direction of the stationary scroll 120. Since the second recess 150 is connected to both the bypass cavity 140 and the body 126, the cross-sectional area of the bypass cavity 140 is increased, reducing the flow resistance of the compressor 200 under partial load conditions and improving the overall efficiency.
[0076] Furthermore, since both the main body 126 and the second sink 150 are located on the disc 124, i.e., through holes 122 are opened on the disc 124, compared to setting the second sink 150 on the mounting part 125, while ensuring the structural strength of the mounting part 125 and ensuring the seal between the mounting part 125 and the back pressure plate 130 and the float assembly 190, the axial depth of the second sink 150 can be appropriately increased due to the greater thickness of the disc 124. This allows for maximizing the cross-sectional area of the bypass cavity 140 and reducing the pressure loss and flow resistance of the compressor 200 under partial load conditions.
[0077] like Figure 4 As shown, in some embodiments, optionally, along the radial direction of the stationary vortex disk 120, the second sink 150 includes opposing first sink wall 151 and second sink wall 152; wherein at least one of the first sink wall 151 and the second sink wall 152 is configured as an arcuate wall.
[0078] In this embodiment, the second settling tank 150 is defined as including a first tank wall 151 and a second tank wall 152, specifically, the first tank wall 151 and the second tank wall 152 are arranged radially along the stationary vortex disk 120. Specifically, the first tank wall 151 is an arc-shaped wall, or the second tank wall 152 is an arc-shaped wall, or both the first tank wall 151 and the second tank wall 152 are arc-shaped walls. The specific configuration can be adjusted according to actual needs. That is, the second settling tank 150 is an arc-shaped tank.
[0079] It is understandable that, since the area of the disc 124 away from the moving scroll 110, i.e., the top surface of the disc 124 is generally a circular plane, setting the first groove wall 151 and / or the second groove wall 152 as arc-shaped walls can match the shape of the disc 124, thereby maximizing the cross-sectional area of the bypass cavity 140. When the compressor 200 is running under partial load conditions, it further optimizes the buffering effect of the gas during the flow process, reduces pressure loss and flow resistance, and improves the overall efficiency of the compressor 200.
[0080] In some embodiments, optionally, based on the fact that the first groove wall 151 is an arc-shaped wall, the length M of the first groove wall 151 in the circumferential direction of the stationary vortex disk 120 and the circumference N of the circle in which the first groove wall 151 is located satisfy M≥N / 2.
[0081] In this embodiment, since the circumferential length of the first groove wall 151 is greater than or equal to half of the circumference of the circle in which the first groove wall 151 is located, that is, the circumferential length of the arc groove is set to be longer, thereby increasing the overall cross-sectional area of the bypass cavity 140, reducing the flow resistance of the gas in the compressor 200 under partial load conditions, reducing power loss, and improving the overall efficiency of the compressor 200 under partial load conditions.
[0082] like Figure 3 and Figure 4As shown, in some embodiments, the body 126 optionally includes a communication port 123, which communicates with the bypass cavity 140. Along the radial direction of the stationary vortex disk 120, the width of the communication port 123 is greater than the width of the second settling groove 150.
[0083] In this embodiment, since the radial width of the connecting port 123 is greater than the radial width of the second sink 150, that is, the flow cross-sectional area of the connecting port 123 is increased, when the compressor 200 is running under partial load conditions, the gas in the compression chamber 160 enters the bypass chamber 140, and enters the body 126 through the connecting port 123 from the bypass chamber 140, and then flows into the suction chamber 210. This process can further reduce flow resistance and power loss, which is beneficial to improving the overall efficiency of the compressor 200 under partial load conditions.
[0084] like Figure 3 As shown, in some embodiments, optionally, the body 126 includes a first segment 220 and a second segment 230 that are connected. Along the radial direction of the stationary volute 120, the second segment 230 is located outside the first segment 220; wherein, along the axial direction of the stationary volute 120, the width of the second segment 230 is greater than the width of the first segment 220.
[0085] In this embodiment, the body 126 is defined to include a first segment 220 and a second segment 230, and the second segment 230 is located outside the first segment 220. Since the axial width of the second segment 230 is greater than the axial width of the first segment 220, that is, the axial width of the second segment 230 located on the outside is greater than the axial width of the first segment 220 located on the inside, the flow resistance of the gas can be further reduced when the compressor 200 is running under partial load conditions.
[0086] like Figure 4 As shown, in some embodiments, optionally, at least a portion of the sink 127 extends circumferentially along the stationary vortex disk 120; and / or along the circumferential direction of the stationary vortex disk 120, the sink 127 includes a first end 153 and a second end 154, with a gap between the first end 153 and the second end 154.
[0087] In this embodiment, since at least part of the sink 127 extends circumferentially along the stationary volute 120, the overall cross-sectional area of the bypass cavity 140 can be further increased. When the compressor 200 is running under partial load conditions, the buffering effect of the gas during the flow process can be optimized, pressure loss and flow resistance can be reduced, and smooth gas flow can be ensured.
[0088] The settling groove 127 includes a first end 153 and a second end 154. Specifically, there is a gap between the first end 153 and the second end 154 along the circumference of the stationary vortex disk 120, that is, the settling groove 127 is a semi-circular groove. This can increase the overall cross-sectional area of the bypass cavity 140 as much as possible while avoiding interference between the settling groove 127 and other structures, thereby further improving the reliability of the pump body structure 100.
[0089] like Figure 3 and Figure 4 As shown, in some embodiments, optionally, the disk body 124 is also provided with a bypass hole 121, through which the compression cavity 160 can communicate with the bypass cavity 140; along the radial direction of the stationary vortex disk 120, the sink 127 is located outside the bypass hole 121.
[0090] In this embodiment, the disc body 124 is further provided with a bypass hole 121. Specifically, under partial load conditions, the compressor 200's compression chamber 160 is connected to the bypass chamber 140 through the bypass hole 121, and the bypass chamber 140 is connected to the suction chamber 210 through the through hole 122, thereby prematurely discharging some gas and achieving the purpose of reducing displacement, cooling capacity, and energy consumption. Under full load conditions, the bypass hole 121 and the bypass chamber 140 are closed, thus closing the compression chamber 160 and the bypass chamber 140, and the through hole 122 and the suction chamber 210 are closed, thus closing the bypass chamber 140 and the suction chamber 210. As the volume of gas in the compression chamber 160 continuously decreases, normal compression begins, thereby realizing the variable capacity function of the compressor 200.
[0091] Since the recess 127 is located radially outside the bypass hole 121, that is, the recess 127 is located closer to the outer edge of the disc 124 than the bypass hole 121, the circumferential length of the recess 127 can be increased when at least a part of the recess 127 extends circumferentially, thereby increasing the overall volume of the bypass cavity 140. This optimizes the buffering effect during gas flow and reduces flow resistance. When the compressor 200 is running under full load, the bypass cavity 140, as a second back pressure cavity, can increase the axial force applied to the stationary scroll 120, prevent leakage, and improve the overall efficiency of the compressor 200.
[0092] Optionally, the pump body structure 100 also includes a one-way valve 180, which is disposed on the disc body 124 and located at one end of the bypass hole 121 near the bypass cavity 140, for opening or closing the bypass hole 121 so that the bypass hole 121 is connected to or cut off the bypass cavity 140.
[0093] Optionally, there are two bypass holes 121, one of which is configured near the first end 153 and the other near the second end 154. Specifically, when the compressor 200 is operating under partial load, the two bypass holes 121 are opened, and the compression chamber 160 is connected to the bypass chamber 140 through the two bypass holes 121 respectively. Since one bypass hole 121 is near the first end 153 of the settling tank 127 and the other bypass hole 121 is near the second end 154 of the settling tank 127, when the gas in the compression chamber 160 enters the bypass chamber 140 through the two bypass holes 121, it approaches the area of the bypass chamber 140 with an increased cross-sectional area, further optimizing the buffering effect of the gas during the flow process, reducing pressure loss and flow resistance, and ensuring smooth gas flow.
[0094] Optionally, since at least part of the connecting port 123 is opposite to the second sink 150 along the axial direction of the stationary scroll 120, and one of the bypass holes 121 is close to the first end 153 of the second sink 150 and the other bypass hole 121 is close to the second end 154 of the second sink 150, that is, along the circumference of the stationary scroll 120, the connecting port 123 is located between the two bypass holes 121. When the compressor 200 is running under partial load conditions, the gas flow path can be optimized, the gas flow resistance can be further reduced, the power loss can be reduced, and the efficiency of the compressor 200 can be improved.
[0095] Optionally, the two bypass holes 121 are symmetrically arranged about the central axis of the stationary scroll 120, which can avoid uneven wear caused by uneven compression, thus extending the service life of the compressor 200 and ensuring the reliable operation of the compressor 200.
[0096] like Figure 3 As shown, in some embodiments, optionally, the back pressure plate 130 is provided with a recess 131 on the side near the moving scroll 110, and the inner wall of the recess 131, the inner wall of the mounting part 125 and the disk body 124 surround to form a bypass cavity 140.
[0097] In this embodiment, a recess 131 is provided on the side of the back pressure plate 130 near the moving scroll 110, and the inner wall of the recess 131, the inner wall of the mounting part 125 and the plate body 124 surround to form a bypass cavity 140. This ensures that the compressor 200 operates stably under full load and partial load conditions, while further increasing the cross-sectional area of the bypass cavity 140, improving the flow resistance of the gas in the compressor 200 under partial load conditions, optimizing the buffering effect, and reducing the wear of the compressor 200.
[0098] Optionally, the disk body 124 and the mounting part 125 are an integral structure.
[0099] Optionally, the pump body structure 100 also includes a control valve 170, located at the other end of the through hole 122. The control valve 170 can control the connection or disconnection between the through hole 122 and the suction chamber 210. Specifically, under partial load conditions, the compression chamber 160 is connected to the bypass chamber 140 through the bypass hole 121, and the control valve 170 is opened to allow the bypass chamber 140 to connect to the suction chamber 210 through the through hole 122, thereby prematurely discharging some gas and reducing displacement, cooling capacity, and energy consumption. Under full load conditions, the bypass hole 121 is closed, meaning the compression chamber 160 and bypass chamber 140 are disconnected, and the control valve 170 is closed, cutting off the connection between the through hole 122 and the suction chamber 210. As the volume of gas in the compression chamber 160 continuously decreases, normal compression begins, thus realizing the variable capacity function of the compressor 200.
[0100] Optionally, control valve 170 includes a solenoid valve.
[0101] According to a second aspect of the present invention, a compressor 200 is provided, including a pump body structure 100 as provided in any of the above embodiments, and thus possesses all the beneficial technical effects of the pump body structure 100, which will not be repeated here.
[0102] like Figure 3 , Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, optionally, a static scroll structure (pump body structure 100) of a variable displacement scroll compressor (compressor 200) includes a moving scroll component (moving scroll 110), a static scroll component (static scroll 120), and a bypass device. The moving scroll component (moving scroll 110) includes a moving scroll end face on one side and helical moving scroll blades formed on the moving scroll end face. The stationary scroll component (stationary scroll 120) includes a stationary scroll end face on one side and a spiral stationary scroll blade formed on the stationary scroll end face. The other side has a concave region. The concave region is connected to one of the compression chambers 160 formed between the spiral blades of the stationary scroll component (stationary scroll 120) and the spiral blades of the moving scroll component. The concave region has a downward semi-circular groove (second recess 150) forming a bypass chamber with the other compression chamber 160 and the intake chamber 210. By opening and closing the bypass chamber, the connection between one compression chamber 160 and the intake chamber 210 is determined, thereby realizing the variable volume of the compressor 200.
[0103] The bypass device includes a bypass cavity 140, a control valve 170, and a bypass valve (one-way valve 180). One end of the bypass cavity 140 is connected to one or more compression chambers 160 through the bypass valve (one-way valve 180). The bypass cavity 140 is sealed by a back pressure plate 130. The other end is connected to the suction chamber 210 through a solenoid valve (control valve 170). The bypass valve (one-way valve 180) is located in the bypass cavity 140. Because a semi-circular groove (second recess 150) is opened on the concave plane of the stationary scroll 120, which is semi-circular in shape, the cross-sectional area of the bypass cavity 140 is increased, and the refrigerant flow path is optimized.
[0104] The bypass device is located in the recessed area of the stationary vortex component (stationary vortex disk 120). The bypass device includes a proximal end (bypass hole 121), a cavity part (bypass cavity 140), and a distal end (through hole 122). The proximal end is fluidly connected to a compression cavity 160, which is the high-pressure side. The cavity part is a sealed cavity (bypass cavity 140) formed by the stationary vortex disk (disc body 124), the mounting part 125, and the back pressure plate 130, which is the pressure-changing side. The distal end extends from the receiving section (connection port 123) and is fluidly connected to the low-pressure area (intake cavity 210), which is the low-pressure side.
[0105] The fixed vortex component (pump body structure 100) includes a stationary vortex component main body (stationary vortex 120) and a back pressure plate 130 that are detachably connected. The proximal end (bypass hole 121), the cavity part (bypass cavity 140) and the distal end (through hole 122) are all disposed in the back pressure plate 130 and / or the fixed vortex main body (stationary vortex 120).
[0106] Control valve 170 and exhaust valve (check valve 180) selectively introduce high-pressure or low-pressure fluid into the cavity section (bypass chamber 140). During stable operation of compressor 200, the pressure on the transformer side is intermediate between the medium-pressure side and the low-pressure side. When the connecting cavity (bypass chamber 140) is open, the pressure on the transformer side is the same as the pressure on the low-pressure side; when the connecting cavity (bypass chamber 140) is closed, the pressure on the transformer side is the same as the pressure in one of the compression chambers 160. Control valve 170 is an electromagnetic control valve, with one end mounted to the stationary scroll assembly (stationary scroll 120) and the other end welded to the housing.
[0107] A semi-circular groove (second recess 150) is formed downwards in the concave plane of the stationary volute 120. One end of the bypass cavity 140 is connected to the compression cavity 160, and its opening and closing are controlled by the pre-exhaust valve (one-way valve 180). The other end is connected to the intake cavity 210, and is equipped with a solenoid valve (control valve 170) to control whether the connection is made. This allows the compression cavity 160 to communicate with the intake cavity 210, while also increasing the cross-sectional area of the bypass cavity 140, reducing the resistance during gas flow, and ensuring smooth flow. In addition, the bypass cavity 140 can also serve as a second back pressure cavity, further ensuring that the stationary volute 120 presses down on the moving volute 110 to avoid abnormal noise. It can also ensure that there is a leakage channel when the pressure in the compression cavity 160 is very high, preventing volute wear caused by excessive pressure.
[0108] The back pressure plate 130 consists of a back pressure plate body, a back pressure plate gasket, and fasteners. The pump body structure 100 also includes a pressure relief valve assembly, which consists of a pressure relief valve plate, a limiter, and fasteners to relieve pressure during overcompression. The bypass valve assembly (one-way valve 180) consists of a bypass valve plate, a limiter, and fasteners to connect the compression chamber 160 and the bypass chamber 140.
[0109] According to a third aspect of the present invention, a refrigeration device is provided, including a pump body structure 100 or a compressor 200 as provided in any of the above embodiments, and thus possessing all the beneficial technical effects of the pump body structure 100 or the compressor 200, which will not be repeated here.
[0110] Alternatively, the refrigeration equipment may include air conditioners, refrigerators, or freezers.
[0111] In the description of this specification, the terms "connection," "installation," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.
[0112] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.
[0113] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.
Claims
1. A pump body structure, characterized in that, include: Moving scroll plate; A stationary scroll plate, comprising a connected plate body and a mounting portion, wherein the plate body and the moving scroll plate form a compression cavity, and the mounting portion is located on the side of the plate body opposite to the moving scroll plate; A back pressure plate is disposed in the mounting part and forms a bypass cavity with the inner wall of the mounting part and the disc body. The bypass cavity can communicate with the compression cavity. A through hole is provided on the stationary vortex disk, one end of which communicates with the bypass cavity, and the other end of which penetrates the side wall of the stationary vortex disk.
2. The pump body structure according to claim 1, characterized in that, The through hole includes: The main body is disposed on at least one of the mounting portion and the disk body, and communicates with the bypass cavity; A settling trough is provided in the disc body and is connected to the bypass cavity and the main body respectively.
3. The pump body structure according to claim 2, characterized in that, The settling tank includes a first settling tank along the radial direction of the stationary vortex disk, and the first settling tank is located inside the body.
4. The pump body structure according to claim 3, characterized in that, The first settling tank has a guide wall at the end away from the main body, and the guide wall extends outward at the end away from the back pressure plate.
5. The pump body structure according to claim 3, characterized in that, Along the axial direction of the stationary vortex, the distance between the bottom wall of the first settling tank and the side of the disc body near the back pressure plate is equal to the distance between the side of the main body near the moving vortex and the side of the disc body near the back pressure plate.
6. The pump body structure according to claim 2, characterized in that, The body is disposed on the disk body, and the sinking groove includes a second sinking groove along the axial direction of the static vortex disk, with at least a portion of the second sinking groove opposite to the body.
7. The pump body structure according to claim 6, characterized in that, Along the radial direction of the static vortex disk, the second settling tank includes opposing first tank walls and second tank walls; In this configuration, at least one of the first and second trench walls is constructed as an arc-shaped wall.
8. The pump body structure according to claim 7, characterized in that, Since the first groove wall is an arc-shaped wall, the length M of the first groove wall in the circumferential direction of the static vortex disk and the circumference N of the circle in which the first groove wall is located satisfy M≥N / 2.
9. The pump body structure according to claim 6, characterized in that, The body includes a connecting port that communicates with the bypass cavity. Along the radial direction of the stationary vortex disk, the width of the connecting port is greater than the width of the second settling tank.
10. The pump body structure according to claim 6, characterized in that, The body includes a first segment and a second segment that are connected along the radial direction of the static vortex disk, with the second segment located outside the first segment; Along the axial direction of the stationary vortex disk, the width of the second segment is greater than the width of the first segment.
11. The pump body structure according to any one of claims 2 to 10, characterized in that, At least a portion of the settling trough extends circumferentially along the stationary vortex disk; and / or along the circumferential direction of the stationary vortex disk, the settling trough includes a first end and a second end, with a gap between the first end and the second end.
12. The pump body structure according to any one of claims 2 to 10, characterized in that, The disc body is also provided with a bypass hole, and the compression chamber can communicate with the bypass chamber through the bypass hole; Along the radial direction of the stationary vortex disk, the sink is located outside the bypass hole.
13. The pump body structure according to any one of claims 1 to 10, characterized in that, The back pressure plate has a recess on the side near the moving scroll, and the inner wall of the recess, the inner wall of the mounting part, and the disk body together form the bypass cavity.
14. A compressor, characterized in that, Includes the pump body structure as described in any one of claims 1 to 13.
15. A refrigeration device, characterized in that, include: Pump body structure as described in any one of claims 1 to 13; or The compressor as described in claim 14.