Compressor and heat management integrated device

Abstract

The invention provides a compressor which comprises a shell, an exhaust cover and a static vortex disc, at least part of the static vortex disc is located in a mounting cavity of the shell, the exhaust cover is connected with the shell, the compressor is provided with an exhaust cavity and an oil return channel, the exhaust cavity is located between the exhaust cover and the static vortex disc, and the exhaust cavity communicates with the oil return channel; the compressor is provided with a mounting gap, the static scroll plate comprises a fixed plate part, the mounting gap is located between the fixed plate part and the shell, the compressor further comprises a static plate sealing element, the static plate sealing element is connected with the fixed plate part and the shell, at least part of the static plate sealing element is located in the mounting gap, and the static plate sealing element comprises a first sealing ring and a second sealing ring; the oil return channel comprises a throttling oil return channel, and at least part of the throttling oil return channel is located between the first sealing ring and the second sealing ring. At least one part of the throttling oil return channel is formed by utilizing a part of the mounting gap between the first sealing ring and the second sealing ring, so that the processing difficulty of the throttling oil return channel can be reduced; the invention further provides a thermal management integration device.

Description

Technical Field

[0001] This application relates to the field of vehicle thermal management, and more particularly to a compressor and an integrated thermal management device. Background Technology

[0002] The main function of a compressor is to compress low-pressure, low-temperature refrigerant gas into high-pressure, high-temperature refrigerant gas. Related technology discloses a compressor including a moving scroll, a stationary scroll, and an exhaust cover. The compressor has a compression chamber, a high-pressure chamber, and a low-pressure chamber. The compression chamber is located between the moving scroll and the stationary scroll, and the high-pressure chamber is located between the stationary scroll and the exhaust cover. The compressor also has an oil return passage connecting the high-pressure chamber and the low-pressure chamber. Through the oil return passage, the oil separated in the high-pressure chamber is returned to the low-pressure chamber to lubricate the compressor's transmission components. The oil return passage includes a throttling oil return passage, which is arranged between the stationary scroll and the exhaust cover. However, this throttling oil return passage uses a throttling groove with a slender arc-shaped structure cut into the end face of the stationary scroll for throttling, making the machining of the compressor's throttling oil return passage quite difficult. Summary of the Invention

[0003] This application aims to provide a compressor and thermal management integrated device, which reduces the machining difficulty of the throttling oil return channel.

[0004] To achieve the above objectives, this application provides a compressor, including a housing, an exhaust cover, and a stationary scroll. The housing has a mounting cavity, and the stationary scroll is at least partially located in the mounting cavity. The exhaust cover is connected to the housing. The compressor has an exhaust chamber and an oil return passage. The exhaust chamber is located between the exhaust cover and the stationary scroll, and the exhaust chamber communicates with the oil return passage. The compressor has an installation gap. The stationary scroll includes a fixed plate portion, and the installation gap is located between the fixed plate portion and the housing. The compressor further includes a stationary scroll seal, which is connected to the fixed plate portion and the housing. The stationary scroll seal is at least partially located in the installation gap and includes a first sealing ring and a second sealing ring. The oil return passage includes a throttling oil return passage, which is at least partially located between the first sealing ring and the second sealing ring.

[0005] The compressor provided in this application includes a housing, an exhaust cover, a stationary scroll, and a stationary scroll seal. The stationary scroll seal includes a first sealing ring and a second sealing ring. The compressor has an installation gap located between the fixed portion of the stationary scroll and the housing. The stationary scroll seal is at least partially located within the installation gap. The compressor also has an oil return passage. The throttling oil return passage is at least partially located between the first and second sealing rings. Utilizing the portion of the installation gap between the first and second sealing rings to form at least a portion of the throttling oil return passage reduces the machining difficulty of the throttling oil return passage.

[0006] To achieve the above objectives, this application provides a thermal management integrated device, including a compressor. The compressor includes a housing, an exhaust cover, and a stationary scroll. The housing has a mounting cavity, and the stationary scroll is at least partially located in the mounting cavity. The exhaust cover is connected to the housing. The compressor has an exhaust chamber and an oil return channel. The exhaust chamber is located between the exhaust cover and the stationary scroll, and the exhaust chamber communicates with the oil return channel. The compressor has an installation gap. The stationary scroll includes a fixed plate portion. The installation gap is located between the fixed plate portion and the housing. The compressor also includes a stationary plate seal, which is connected to the fixed plate portion and the housing. The stationary plate seal is at least partially located in the installation gap. The stationary plate seal includes a first sealing ring and a second sealing ring. The oil return channel includes a throttling oil return channel, which is at least partially located between the first sealing ring and the second sealing ring.

[0007] The thermal management integrated device provided in this application includes a compressor, which includes a housing, an exhaust cover, a stationary scroll, and a stationary disk seal. The stationary disk seal includes a first sealing ring and a second sealing ring. The compressor has an installation gap located between the fixed portion of the stationary scroll and the housing, and the stationary disk seal is at least partially located within the installation gap. The compressor also has an oil return channel, and a throttling oil return channel is at least partially located between the first and second sealing rings. Utilizing the portion of the installation gap between the first and second sealing rings to form at least a portion of the throttling oil return channel reduces the machining difficulty of the throttling oil return channel. Attached Figure Description

[0008] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0009] Figure 1 This is a three-dimensional schematic diagram of a compressor provided in this application;

[0010] Figure 2 yes Figure 1 An explosion diagram;

[0011] Figure 3 yes Figure 1 Front view diagram;

[0012] Figure 4 yes Figure 3 A schematic diagram of the FF section;

[0013] Figure 5 yes Figure 4 Enlarged schematic diagram at point M;

[0014] Figure 6 yes Figure 3 Schematic diagram of the GG cross section;

[0015] Figure 7a yes Figure 1 A left-view diagram;

[0016] Figure 7b yes Figure 7a Schematic diagram of the HH-direction cross section;

[0017] Figure 8 yes Figure 7a A top-down view;

[0018] Figure 9 yes Figure 2 A three-dimensional schematic diagram of the compressor core assembly;

[0019] Figure 10 yes Figure 9 A diagram showing the view from the right.

[0020] Figure 11 yes Figure 10 Schematic diagram of the cross section in direction II;

[0021] Figure 12 yes Figure 2 A three-dimensional schematic diagram of the intermediate static scroll plate;

[0022] Figure 13 yes Figure 2 A schematic diagram of the middle shell from one perspective;

[0023] Figure 14 yes Figure 13 A schematic cross-sectional view along the JJ direction of one embodiment;

[0024] Figure 15 yes Figure 13 A cross-sectional view along the JJ direction of another embodiment;

[0025] Figure 16a yes Figure 9 A three-dimensional schematic diagram of the main bearing housing from one perspective;

[0026] Figure 16b yes Figure 9 A three-dimensional schematic diagram of the main bearing housing from another perspective;

[0027] Figure 17 yes Figure 11 A three-dimensional schematic diagram of the motor housing;

[0028] Figure 18 yes Figure 17 Front view diagram;

[0029] Figure 19 yes Figure 9 A partial structural diagram of the motor assembly;

[0030] Figure 20 yes Figure 19 A schematic diagram of the YY-direction cross-section;

[0031] Figure 21 This is a three-dimensional schematic diagram of another compressor provided in this application;

[0032] Figure 22 yes Figure 21 An exploded view of the compressor core assembly is omitted.

[0033] Figure 23 yes Figure 22 Front view of the middle shell;

[0034] Figure 24 yes Figure 23 A schematic cross-sectional view of the EE direction of one embodiment;

[0035] Figure 25 yes Figure 23 A schematic cross-sectional view of the EE direction of another embodiment;

[0036] Figure 26 This is a three-dimensional schematic diagram of a thermal management integrated device provided in this application. Detailed Implementation

[0037] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0038] It should be understood that the described embodiments are merely some embodiments of this application, and not all embodiments. All other technical solutions obtained by those skilled in the art based on the technical solutions in this application without inventive effort are within the scope of protection of this application.

[0039] To reduce the machining difficulty of the throttling return oil channel, this application proposes a compressor. Please refer to [link to relevant documentation]. Figures 1 to 5The compressor includes a housing 1, an exhaust cover 2, and a stationary scroll 41. The housing 1 has a mounting cavity 10, and the stationary scroll 41 is at least partially located in the mounting cavity 10. The exhaust cover 2 is connected to the housing 1. The compressor 100 has an exhaust chamber 110 and an oil return passage K. The exhaust chamber 110 is located between the exhaust cover 2 and the stationary scroll 41, and the exhaust chamber 110 communicates with the oil return passage K. The compressor 100 has an installation gap Q. The stationary scroll 41 includes a fixed plate portion 41a. The installation gap Q is located between the fixed plate portion 41a and the housing 1. The compressor 100 also includes a stationary plate seal 415, which is connected to the fixed plate portion 41a and the housing 1. The stationary plate seal 415 is at least partially located in the installation gap Q. The stationary plate seal 415 includes a first sealing ring 415a and a second sealing ring 415b. The oil return passage K includes a throttling oil return passage R, which is at least partially located between the first sealing ring 415a and the second sealing ring 415b. By utilizing the partial installation gap Q located between the first sealing ring 415a and the second sealing ring 415b to form at least a portion of the throttling return oil channel R, the machining difficulty of the throttling return oil channel can be reduced.

[0040] In some embodiments, the installation gap Q is a small gap between the outer peripheral wall of the fixed disk portion 41a and the inner peripheral wall of the housing 1. The throttling return oil channel R is formed by the installation gap Q between the fixed disk portion 41a and the housing 1 and the two stationary disk seals 415. That is, the narrow gap between the outer peripheral wall of the fixed disk portion 41a, the inner peripheral wall of the housing 1, the outer wall of the first sealing ring 415a, and the outer wall of the second sealing ring 415b forms the throttling return oil channel R. The throttling effect is achieved through the throttling return oil channel R, which can reduce the problem of poor lubrication of oil returning to the compressor via the return oil channel K due to the high flow rate of oil under high pressure. Furthermore, the throttling return oil channel R can extend the throttling path, achieving a pressure drop effect along the flow path.

[0041] Please see Figure 11 and Figure 12 In some embodiments, at least one of the stationary volute 41 and the housing 1 has a stationary volute sealing groove 416, and the stationary volute seal 415 is at least partially located in the stationary volute sealing groove 416. The stationary volute sealing groove 416 is located on at least one of the outer peripheral wall side of the fixed volute portion 41a and the inner peripheral wall of the housing 1. In some embodiments, the stationary volute sealing groove 416 is provided on the outer peripheral wall side of the fixed volute portion 41a. By using the stationary volute sealing groove 416 to limit the stationary volute seal 415, the reliability of the seal can be improved. Of course, in other embodiments, the stationary volute sealing groove 416 can also be provided on the inner peripheral wall of the housing 1. In some specific embodiments, the stationary volute sealing groove 416 is an annular groove, and the cross-sectional shapes of two adjacent annular grooves are similar. Of course, in other embodiments, two adjacent annular grooves can also be grooves with different cross-sectional shapes.

[0042] In a specific embodiment, the inner peripheral side of the stationary disc seal 415 contacts the inner peripheral wall of the housing 1, and the outer peripheral side of the stationary disc seal 415 contacts the outer peripheral wall of the fixed disc portion 41a. In some embodiments, there are two stationary disc seals 415, namely a first sealing ring 415a and a second sealing ring 415b, and a throttling oil return channel R is formed between the first sealing ring 415a and the second sealing ring 415b. The first sealing ring 415a and the second sealing ring 415b are arranged along the axial direction of the stationary volute 41. Of course, in other embodiments, there may be three or more stationary disc seals 415 arranged along the axial direction of the stationary volute 41, wherein a throttling oil return channel R is formed between two adjacent stationary disc seals 415. In this case, at least two throttling oil return channels R can be formed, further improving the throttling effect. The inner ring side of the stationary disc seal 415 abuts against and seals with the fixed disc portion 41a, and the outer ring side of the stationary disc seal 415 abuts against and seals with the fixed disc portion 41a and the housing 1.

[0043] In other embodiments, one of the stationary disc seals 415 may be axially arranged at one end of the fixed disc portion 41a and at the protrusion on the inner peripheral wall of the housing 1, with the protrusion facing the end face of the fixed disc portion 41a. That is, the fixed disc portion 41a, the stationary disc seal 415, and the protrusion on the inner peripheral wall of the housing 1 are arranged axially. The other stationary disc seal 415 may be arranged between the outer peripheral wall of the fixed disc portion 41a and the inner peripheral wall of the housing 1.

[0044] Please see Figure 4 , Figure 5 , Figures 9 to 12 In some embodiments, the return oil channel K further includes an oil inlet channel 413, which is at least partially located in the fixed disk portion 41a. The exhaust chamber 110 is connected to the oil inlet channel 413, and the oil inlet channel 413 is connected to the throttling return oil channel R.

[0045] And / or, please see Figure 4 , Figure 5 , Figures 9 to 12 In some embodiments, the oil return channel K further includes an oil drain channel 414, which is at least partially located in the fixed plate portion 41a. The compressor 100 also has an oil return chamber 120, and the throttling oil return channel R is connected to the oil drain channel 414, which is connected to the oil return chamber 120.

[0046] In some embodiments, the exhaust chamber 110 is connected to the inlet side of the throttling oil return channel R via the oil inlet channel 413, and the outlet side of the throttling oil return channel R is connected to the oil return chamber 120 via the oil discharge channel 414. When the compressor is operating, the refrigerant and lubricating oil mixture can undergo oil-gas separation in the exhaust chamber 110. The separated oil can enter the throttling oil return channel R through the oil inlet channel 413. After being throttled by the throttling oil return channel R, the oil returns to the oil return chamber 120 inside the compressor 100 through the oil discharge channel 414, thereby achieving oil return. In some embodiments, when the compressor 100 is operating, it employs... Figure 4 The installation configuration shown places the inlet of the oil inlet channel 413 in a position close to the bottom of the exhaust chamber 110 along the direction of gravity, which is more conducive to the smooth return of the oil stored in the exhaust chamber 110.

[0047] Please see Figure 4 , Figures 9 to 12 In some embodiments, the oil inlet channel 413 includes a first oil inlet channel 413a and a second oil inlet channel 413b. The exhaust chamber 110 is connected to the first oil inlet channel 413a, the first oil inlet channel 413a and the second oil inlet channel 413b are connected, and the second oil inlet channel 413b is connected to the throttling return oil channel R. The equivalent flow area of ​​the first oil inlet channel 413a is larger than that of the second oil inlet channel 413b. In this embodiment, the oil stored in the exhaust chamber 110 enters the throttling return oil channel R through the oil inlet channel 413. When the oil enters the second oil inlet channel 413b via the first oil inlet channel 413a, the second oil inlet channel 413b, which has a smaller equivalent flow area, is used to throttle the oil, which can further improve the throttling effect of the return oil channel R. The equivalent flow area of ​​the channel is the cross-sectional area perpendicular to the channel axis. In some embodiments, the axes of the first oil inlet channel 413a and the second oil inlet channel 413b intersect, which can bend the oil's path and further slow down the oil flow, thus achieving a throttling effect.

[0048] Please see Figure 11 In some specific embodiments, the first oil inlet channel 413a extends axially along the fixed disk portion 41a, and one end of the first oil inlet channel 413a faces the exhaust chamber 110; the second oil inlet channel 413b extends radially along the fixed disk portion 41a, and one end of the second oil inlet channel 413b faces the throttling return oil channel R.

[0049] The inlet of the first oil inlet channel 413a is located on the end face of the fixed disk portion 41a facing the exhaust chamber 110, and the outlet of the second oil inlet channel 413b is located on the outer peripheral wall of the fixed disk portion 41a. The outlet of the first oil inlet channel 413a is connected to the inlet of the second oil inlet channel 413b. The use of an axially extending first oil inlet channel 413a and a radially extending second oil inlet channel 413b facilitates the opening of holes in the fixed disk portion 41a and reduces the processing difficulty. In some embodiments, the axes of the first oil inlet channel 413a and the second oil inlet channel 413b are perpendicular, which can bend the oil flow path and further slow down the oil flow speed, achieving a throttling effect.

[0050] Please see Figure 4 , Figures 9 to 11 In some embodiments, the oil discharge channel 414 includes a first oil discharge channel 414a and a second oil discharge channel 414b. The throttling return oil channel R is connected to the first oil discharge channel 414a, the first oil discharge channel 414a and the second oil discharge channel 414b are connected, and the second oil discharge channel 414b is connected to the return oil chamber 120. The equivalent flow area of ​​the first oil discharge channel 414a is larger than the equivalent flow area of ​​the second oil discharge channel 414b. In this embodiment, the oil stored in the exhaust chamber 110 enters the throttling return oil channel R through the oil inlet channel 413 and is then throttled, before returning to the return oil chamber 120 via the oil discharge channel 414. When the oil enters the second oil discharge channel 414b via the first oil discharge channel 414a, the throttling effect of the return oil channel K is further improved by utilizing the second oil discharge channel 414b, which has a smaller equivalent flow area. In some embodiments, the axes of the first oil discharge channel 414a and the second oil discharge channel 414b intersect, which can bend the oil's path and further slow down the oil flow, achieving a throttling effect.

[0051] Please see Figure 11 In some specific embodiments, the first oil discharge channel 414a extends radially along the fixed disk portion 41a and points towards the throttling return oil channel R, while the second oil discharge channel 414b extends axially along the fixed disk portion 41a and points towards the return oil channel T. The inlet of the first oil discharge channel 414a is located on the peripheral wall of the fixed disk portion 41a, and the outlet of the second oil discharge channel 414b is located on the end face of the fixed disk portion 41a facing away from the exhaust chamber 110. The outlet of the first oil discharge channel 414a communicates with the inlet of the second oil discharge channel 414b. The use of a radially extending first oil discharge channel 414a and an axially extending second oil discharge channel 414b facilitates the opening of holes in the fixed disk portion 41a and reduces the processing difficulty. In some embodiments, the axes of the first oil discharge channel 414a and the second oil discharge channel 414b are perpendicular, which can bend the oil's path and further slow down the oil flow, achieving a throttling effect.

[0052] Please see Figure 4 and Figure 11 In some specific embodiments, the compressor 100 further includes a moving scroll 42 and a main bearing housing 43, the oil return chamber 120 is located between the moving scroll 42 and the main bearing housing 43, the oil return channel K further includes an oil return flow channel T, the oil return flow channel T is at least partially located in the main bearing housing 43, the oil discharge channel 414 is connected to the oil return flow channel T, and the oil return flow channel T is connected to the oil return chamber 120.

[0053] In some embodiments, please refer to Figure 5 , Figure 6 and Figure 8 The compressor 100 also includes a drive shaft assembly 44, which is driven by the moving scroll 42. The housing 1 of the compressor 100 has a suction channel 12b and a low-pressure chamber connected to the suction channel 12b. When the compressor is working, the oil entering the oil return chamber 120 through the oil return channel T can lubricate the main bearing 430 between the main bearing housing 43 and the drive shaft assembly 44, and the drive bearing 440 between the drive shaft assembly 44 and the moving scroll 42. On the other hand, the oil can also enter the low-pressure chamber of the compressor 100 through the main bearing 430. After the oil mixes with the refrigerant entering through the suction channel 12b, it enters the compression chamber between the stationary scroll 41 and the moving scroll 42 through the second through groove 4300 of the main bearing housing 43 for lubrication.

[0054] Please see Figure 11 and Figure 16b In some embodiments, the return oil flow channel T includes a first return oil flow channel T1 and a second return oil flow channel T2. One end of the first return oil flow channel T1 is connected to the discharge oil flow channel 414, and the other end of the first return oil flow channel T1 is connected to the second return oil flow channel T2. The second return oil flow channel T2 is connected to the return oil chamber 120, and the axis of the first return oil flow channel T1 intersects the axis of the second return oil flow channel T2. Using two intersecting return oil flow paths can bend the oil's path, further slowing down the oil flow speed and achieving a throttling effect. In some embodiments, the angle between the axis of the first return oil flow channel T1 and the axis of the second return oil flow channel T2 is an acute angle; however, in other embodiments, the angle can also be a right angle or an obtuse angle.

[0055] Please see Figure 4 , Figure 5 and Figure 8In some specific embodiments, the exhaust chamber 110 includes a first chamber 110a and a second chamber 100b, the second chamber 100b being connected to the oil return channel K. The fixed disk portion 41a has a scroll exhaust port 410, which is connected to the first chamber 110a. The compressor 100 has an exhaust channel 12a, which is connected to the second chamber 100b. The compressor 100 includes a separation baffle portion S, which is at least partially located between the first chamber 110a and the second chamber 100b. The compressor 100 has a separation channel 110c, which is connected to the first chamber 110a and the second chamber 100b. When the high-pressure refrigerant and lubricating oil mixture enters the second chamber 100b through the separation channel 110c, the increased flow area can reduce the flow rate to a certain extent, which is beneficial for oil-gas separation.

[0056] In some embodiments, one end of the separation partition S is connected to one of the exhaust cover 2 and the fixed disk portion 41a, and the other end of the separation partition S has a gap L between it and the other of the exhaust cover 2 and the fixed disk portion 41a, forming at least a portion of the separation channel 110c. Using this gap L to form at least a portion of the separation channel 110c reduces the processing difficulty of the separation partition S. When the compressor is operating, the high-pressure refrigerant and lubricating oil mixture is discharged from the scroll exhaust port 410 of the stationary scroll 41 to the first chamber 110a, then enters the second chamber 100b via the gap L, and is then discharged through the exhaust channel 12a. In some embodiments, both the exhaust channel 12a and the suction channel 12b of the compressor 100 are arranged in the housing 1. Please refer to... Figure 4 and Figure 5 In some embodiments, taking the separation partition S connected to the exhaust cover 2 and forming a gap L between it and the fixed plate 41a as an example, when the high-pressure refrigerant and lubricating oil mixture enters the second chamber 100b through the gap L, the increased flow area reduces the flow velocity to a certain extent, which is beneficial for oil-gas separation. The separated oil can adhere to the outer wall of the separation partition S and the inner wall of the housing 1 where the second chamber 100b is located. The separated oil eventually drips off under the action of gravity and finally returns to the compressor 100 through the oil return channel K, thus realizing oil return. The compressor is arranged in the following manner during operation: Figure 4 As shown in the diagram, the oil inlet channel 413 is in a lower position in the direction of gravity, which is conducive to oil return.

[0057] To further improve the oil-gas separation effect, please refer to some specific embodiments. Figure 5The separation partition S consists of two parts, including a first partition 411 and a second partition 21. The first partition 411 is connected to the fixed disk 41a. Along the axial direction of the fixed disk 41a, the first partition 411 and the exhaust cover 2 have a first gap L1. The second partition 21 is connected to the exhaust cover 2. Along the axial direction of the fixed disk 41a, the second partition 21 and the fixed disk 41a have a second gap L2. Along the radial direction of the stationary vortex disk 41, the first partition 411 and the second partition 21 are arranged radially along the stationary vortex disk 41. A third gap L3 is formed between the first partition 411 and the second partition 21. The first gap L1, the second gap L2 and the third gap L3 are connected and form at least a portion of the separation channel 110c. The first gap L1, the second gap L2, and the third gap L3 can form a separation channel 110c with a folding structure. The high-pressure refrigerant and lubricating oil mixture in the exhaust chamber 110 experiences reduced flow velocity through the separation channel 110c, facilitating oil-gas separation. Specifically, in... Figure 5 In the illustrated embodiment, the first partition 411 and the second partition 21 are one; of course, in other embodiments, the number of either the first partition 411 or the second partition 21 may be two or more, to form a separation channel 110c with multiple folding structures.

[0058] In some embodiments, the equivalent flow area of ​​any one of the first gap L1, the second gap L2, and the third gap L3 is greater than the equivalent flow area of ​​the exhaust inlet 121a of the exhaust passage 12a, to prevent excessive pressure drop.

[0059] In some embodiments, please refer to Figure 10 and Figure 12 The stationary scroll 41 also includes a scroll portion 41b, which is connected to the fixed disk portion 41a and is located on the side of the fixed disk portion 41a facing the moving scroll 42. The stationary scroll 41 also has a first hole 417, which is located on the side of the fixed disk portion 41a facing the exhaust chamber 110. The depth of the first hole 417 is less than the thickness of the fixed disk portion 41a, that is, the first hole 417 does not penetrate the fixed disk portion 41a. In some embodiments, there are two first holes 417, which are symmetrically arranged, and the first holes 417 are threaded holes. The first holes 417 serve as process holes and can be used for disassembling and assembling the compressor core assembly 4.

[0060] Please see Figure 7a , Figure 7b and Figure 9In some embodiments, the compressor further includes an exhaust valve 401 and an exhaust valve limiting member 402, the exhaust valve 401 and the exhaust valve limiting member 402 being at least partially located in the first chamber 110a, the exhaust valve 401 and the exhaust valve limiting member 402 being connected to the stationary scroll plate 41, the exhaust valve 401 being located between the stationary scroll plate 41 and the exhaust valve limiting member 402, and the exhaust valve 401 being capable of blocking or opening the scroll plate exhaust port 410.

[0061] Please see Figure 2 In some embodiments, the compressor 100 further includes a limiting part 22, one end of which is connected to one of the stationary scroll 41 and the exhaust cover 2, and the other end of which is in contact with the other of the stationary scroll 41 and the exhaust cover 2.

[0062] The limiting portion 22 extends axially along the housing 1 and is at least partially integral with one of the stationary vortex disk 41 and the exhaust cover 2. In some specific embodiments, the limiting portion 22 is connected to the exhaust cover 2, and the limiting portion 22 and the exhaust cover 2 are at least partially integral with each other. The limiting portion 22 is further away from the axis of the housing 1 than the separating partition portion S. The limiting portion 22 facilitates the installation and positioning of the exhaust cover 2.

[0063] Please see Figure 6 In some embodiments, the compressor 100 includes a compressor core assembly 4. The compressor core assembly 4 can be first assembled as an integral part, and then assembled with the housing 1 as an integral part. Specifically, the compressor core assembly 4 includes a stationary scroll 41, a moving scroll 42, a main bearing housing 43, a drive shaft assembly 44, a motor assembly 45, a first connector 46, and an anti-rotation mechanism 400. The stationary scroll 41, the main bearing housing 43, and the motor assembly 45 are connected by the first connector 46. One end of the drive shaft assembly 44 is rotatably connected to the main bearing housing 43 via a main bearing 430, and the other end of the drive shaft assembly 44 is driven by the moving scroll 42 via a drive bearing 440. The motor assembly 45 includes a stator 451, a rotor 452, and a motor housing 453. The first connector 46 is connected to the motor housing 453 of the motor assembly 45, and the drive shaft assembly 44 is connected to the rotor 452 of the motor assembly 45. In some embodiments, a gasket 47 is further arranged between the moving scroll 42 and the main bearing housing 43 to improve the wear resistance between them. The motor housing 453 has a stator mounting cavity 450, and the stator 451 is at least partially located in the stator mounting cavity 450. The stator 451 is connected to the motor housing 453, and the motor housing 453 is connected to the main bearing housing 43. Positioning the stator 451 using the stator mounting cavity 450 improves the axial positioning accuracy of the stator.

[0064] Please see Figures 17 to 20In some embodiments, the motor housing 453 includes a first protruding positioning portion 4531 that extends from the inner wall of the motor housing 453 toward the axis of the motor housing 453.

[0065] The first protruding positioning part 4531 includes a first connecting arc surface 4531c, which is located on the side of the first protruding positioning part 4531 facing the axis of the motor housing 453, and the first connecting arc surface 4531c is in contact with the outer peripheral wall of the stator 451.

[0066] In some embodiments, the first protruding positioning part 4531 is interference-fitted with the stator 451 via a first connecting arc surface 4531c. Of course, in other embodiments, the two can also be connected in other ways, such as welding, assembly, etc.

[0067] Please see Figure 14 In some embodiments, a plane perpendicular to the axial direction of the motor housing 453 is defined as the first projection plane, and the projection of the first connecting arc surface 4531c on the first projection plane is an arc. The circles of the arcs projected by each first connecting arc surface 4531c coincide to fit the outer peripheral wall contour of the stator 451.

[0068] Please see Figure 16a , Figure 16b , Figure 17 and Figure 18 In some embodiments, there are at least two first protruding positioning portions 4531, which are arranged circumferentially at intervals. The motor housing 453 has a first through groove 4530 located between adjacent first protruding positioning portions 4531. Refrigerant entering the mounting cavity 10 through the intake channel 12b can enter the compression cavity through the first through groove 4530 of the motor housing 453 and the second through groove 4300 on the main bearing seat 43. In addition, the first through groove 4530 between the first protruding positioning portions 4531 can provide a receiving space for the protruding portion on the outer periphery of the stator 451.

[0069] Please see Figures 17 to 20 In some embodiments, the motor housing 453 further includes a limiting step portion 4531a, which extends from the inner wall of the first protruding positioning portion 4531 toward the axis of the motor housing 453, and the end of the stator 451 contacts the limiting step portion 4531a. The limiting step portion 4531a can be used to axially limit the stator 451.

[0070] In some embodiments, the limiting step portion 4531a is located at one end of the length direction of the first protruding positioning portion 4531, and the length direction of the first protruding positioning portion 4531 is the same as the axial direction of the motor housing 453. In a specific embodiment, the limiting step portion 4531a is located at one end of the first protruding positioning portion 4531 facing the bearing seat portion 4533 of the motor housing 453, and the limiting step portion 4531a contacts one end of the stator 451, which can axially limit the stator 451.

[0071] In some embodiments, the first protrusion positioning part 4531 further includes a first guide slope 4531b, which is located at the other end of the length direction of the first protrusion positioning part 4531. The guiding function of the first guide slope 4531b facilitates the assembly of the stator 451 and the motor housing 453.

[0072] Please see Figure 17 In some embodiments, the motor housing 453 further includes a second protruding positioning portion 4532, which extends from the outer wall of the motor housing 453 away from the axis of the motor housing 453. The second protruding positioning portion 4532 includes a second connecting arc surface 4532b, which is located on the side of the second protruding positioning portion 4532 away from the axis of the motor housing 453. The second connecting arc surface 4532b contacts the inner peripheral wall of the housing 1.

[0073] There are at least two second protruding positioning portions 4532, which are arranged circumferentially at intervals. In some embodiments, the second protruding positioning portions 4532 are interference-fitted to the housing 1 via a second connecting arc surface 4532b. Of course, in other embodiments, the two can also be connected in other ways, such as welding, assembly, etc. In some embodiments, at least one end of the second protruding positioning portion 4532 includes a second guide slope 4532a, which has a guiding function to facilitate the assembly of the motor housing 453 and the housing 1. In a specific embodiment, the second guide slope 4532a is located at both ends of the second protruding positioning portion 4532.

[0074] When the compressor 100 is working, after the stator 451 of the motor assembly 45 is energized, the rotor 452 can drive the drive shaft assembly 44 to rotate synchronously. Under the constraint of the anti-rotation mechanism 400, the moving scroll 42 is driven by the drive shaft assembly 44 to perform eccentric rotary translation. It does not rotate on its own axis, but only revolves around the sun. As the moving scroll 42 moves, the gas in the crescent-shaped outer ring chamber formed by the moving scroll 42 and the stationary scroll 41 is continuously pushed towards the center, the volume continuously shrinks, the pressure gradually increases, and the compression work begins.

[0075] Please see Figure 2In some embodiments, the compressor 100 further includes an end cover 3 connected to the housing 1, and the exhaust cover 2, the compressor core assembly 4, and the end cover 3 are arranged along the axial direction of the housing 1; in some embodiments, at least one of the exhaust cover 2 and the end cover 3 is welded to the housing 1. Assembling the compressor core assembly 4 with the housing 1 and then welding the exhaust cover 2 and the end cover 3 to the housing 1 can reduce the number of leakage points in the compressor. Compared to the method of connecting via pipelines, the method of welding the exhaust cover 2 and the end cover 3 has a lower risk of leakage.

[0076] Please see Figure 2 In some embodiments, the compressor 100 further includes a controller assembly 50 and a three-phase terminal 30 electrically connected to the motor assembly 45, the three-phase terminal 30 being mounted on the end cover 3 and connected to the controller assembly 50.

[0077] In some embodiments, the compressor 100 employs Figures 1 to 3 The housing 1, exhaust cover 2, and end cover 3 are shown, and the compressor 100 also includes a... Figure 6 , Figure 9 The compressor core assembly 4 is shown. Of course, in some other embodiments, the compressor 100 may also employ... Figures 21 to 22 The housing 1, exhaust cover 2, and end cover 3 are shown. At this time, the compressor core assembly 4 of the compressor 100 can be adopted. Figure 6 , Figure 9 The structure shown indicates that the compressor core assembly 4 can be first assembled as a single unit, and then the compressor core assembly 4, as a single unit, is then combined with... Figures 1 to 3 Assemble the housing 1 shown, or with Figures 22 to 25 Assemble the housing 1 shown.

[0078] exist Figure 22 In the embodiment shown, the housing 1 can be an extruded part, and the length direction of the mounting cavity 10 is consistent with the length direction of the housing 1, which can reduce the processing difficulty.

[0079] Please see Figure 22 In some embodiments, the end cap 3 includes a flange 31 located at the end of the end cap 3 facing the exhaust cover 2, and the housing 1 has a stepped limiting groove 13, with the flange 31 at least partially located in the stepped limiting groove 13, which facilitates the limiting of the end cap 3. In some embodiments, the compressor 100 further includes a three-phase terminal 30 electrically connected to the motor assembly 45, the three-phase terminal 30 being mounted on the end cap 3.

[0080] Please see Figure 24 and Figure 25In some embodiments, the motor housing 453 is connected to the housing 1. The housing 1 includes a first limiting surface 14 located in the mounting cavity 10, and one end of the motor housing 453 contacts the first limiting surface 14. The first limiting surface 14 is used to axially limit the motor housing 453, facilitating the limited installation of the motor housing 453. In some specific embodiments, the motor housing 453 is connected to the housing 1 by an interference fit.

[0081] To reduce the risk of compressor leakage due to damage to the stationary disc seal, this application also provides a compressor, please refer to [link to relevant documentation]. Figure 1 , Figure 4 , Figure 5 , Figure 14 and Figure 15 The compressor includes a housing 1, an exhaust cover 2, and a stationary scroll 41. The exhaust cover 2 is connected to the housing 1. The housing 1 has a stationary scroll mounting cavity 10a. The stationary scroll 41 is at least partially located in the stationary scroll mounting cavity 10a. The stationary scroll 41 includes a fixed disk portion 41a and a stationary scroll seal 415. The stationary scroll seal 415 is connected to the fixed disk portion 41a. The compressor 100 has an installation gap Q, which is located between the fixed disk portion 41a and the housing 1. The stationary scroll seal 415 is at least partially located in the installation gap Q. The housing 1 has a cavity W and an exhaust passage 12a. The cavity W is closer to the exhaust cover 2 than the stationary scroll 41. The cavity W includes a clearance cavity W10. The inner diameter of the clearance cavity W10 is larger than the inner diameter of the stationary scroll mounting cavity 10a. The exhaust passage 12a has an exhaust inlet 121a. The housing 1 includes a groove wall surface W1. The wall forming the clearance cavity W10 includes the groove wall surface W1. The exhaust inlet 121a is at least partially located on the groove wall surface W1. When installing the stationary scroll plate, the problem of scraping between the stationary scroll seal 415 and the exhaust inlet 121a at the clearance cavity W10 can be reduced to a certain extent, thereby reducing the risk of compressor leakage caused by damage to the stationary scroll seal 415.

[0082] In some embodiments, when the stationary scroll plate 41 is not installed in the stationary plate mounting cavity 10a, the outer diameter of the stationary plate seal 415 disposed on its outer periphery is defined as Z. In some embodiments, the inner diameter of the clearance cavity W10 is larger than the outer diameter Z of the stationary plate seal 415, which can further reduce the risk of the stationary plate seal 415 scraping against the exhaust inlet 121a when the stationary scroll plate 41 is installed. Wherein, when the stationary scroll plate 41 is disposed of with two or more stationary plate seals 415, the inner diameter of the clearance cavity W10 is larger than the outer diameter Z of the stationary plate seal 415 with the largest outer diameter.

[0083] Please see Figure 14 , Figure 15 , Figure 24 and Figure 25At least one side of the recessed cavity W is provided with a chamfered structure. Specifically, in some embodiments, the recessed cavity W includes a first guide cavity W20, and the wall forming the first guide cavity W20 includes a first inclined wall surface W2, which is located on the side of the groove wall surface W1 near the stationary scroll plate 41. Along the axial direction of the housing 1, the inner diameter of the first guide cavity W20 gradually decreases from the side away from the stationary scroll plate 41 to the side near the stationary scroll plate 41. During the installation of the stationary scroll plate 41, the first inclined wall surface W2 has a guiding function and can mitigate the sudden change in the inner diameter of the housing 1, thereby reducing the risk of damage to the stationary scroll seal 415 caused by the sudden change in the inner diameter of the housing 1. In some embodiments, the first guide cavity W20 is located between the clearance cavity W10 and the stationary scroll mounting cavity 10a. The taper of the first inclined wall surface W2 can be 15°-20°, which can better mitigate the sudden change in the inner diameter of the cavity and facilitate the installation of the stationary scroll seal 415.

[0084] Please see Figure 15 and Figure 25 In some embodiments, the housing 1 includes a housing end face 19 located at the end of the housing 1 facing the exhaust cover 2, and a clearance cavity W10 located on the side of the stationary disk mounting cavity 10a facing the exhaust cover 2. The end of the clearance cavity W10 away from the stationary scroll 41 penetrates through the housing end face 19. The clearance cavity W10 with an end-through structure allows the end of the housing 1 to have a larger inner diameter, facilitating the smooth installation of the stationary scroll 41 into the stationary disk mounting cavity 10a.

[0085] In some embodiments, the housing 1 further includes a transition wall W4 located at both ends of the first guide cavity W20 along the axial direction. Along the axial direction of the housing 1, the transition wall W4 is located on both sides of the first inclined wall W2. The transition wall W4 can mitigate the abrupt change in inner diameter at the connection between the first inclined wall W2 and the housing 1 walls on both sides, reducing the risk of damage to the stationary disc seal 415 caused by the abrupt change in the inner diameter of the housing 1's inner cavity. Along the axial direction of the housing 1, the inner diameter of the cavity enclosed by the transition wall W4 gradually decreases from the side away from the stationary scroll 41 to the side closer to the stationary scroll 41.

[0086] Please see Figure 14 and Figure 24In some embodiments, both sides of the recessed cavity W are chamfered, resulting in higher strength for the housing 1 compared to the structure where the end of the clearance cavity W10 away from the stationary volute 41 penetrates the end face 19 of the housing. Specifically, the recessed cavity W also includes a second guide cavity W30, the wall forming the second guide cavity W30 including a second inclined wall surface W3, which is located on the side of the groove wall surface W1 away from the stationary volute 41. Along the axial direction of the housing 1, the inner diameter of the second guide cavity W30 gradually decreases from the side near the stationary volute 41 to the side away from the stationary volute 41. Since the second guide cavity W30 is located on the side of the clearance cavity W10 away from the stationary volute 41, the second inclined wall surface W3 can also mitigate the abrupt change in the inner diameter of the housing 1, thereby reducing the risk of damage to the stationary volute seal 415 caused by the abrupt change in the inner diameter of the housing 1. The taper of at least one of the first inclined wall surface W2 and the second inclined wall surface W3 can be 15°-20°, which can better reduce the sudden change in the inner diameter of the cavity and facilitate the installation of the static disc seal 415.

[0087] Please see Figure 14 and Figure 24 In some embodiments, a rounded chamfer is used to reduce scratch damage to the stationary disc seal 415 caused by abrupt changes in the inner diameter at the corner of the inner wall of the housing 1. Specifically, the housing 1 also includes a transition wall surface W4, which is located on both sides of the first inclined wall surface W2 along the axial direction of the housing 1, and / or, on both sides of the second inclined wall surface W3 along the axial direction of the housing 1. By using the transition wall surface W4 to transition at the abrupt change in the inner diameter of the housing 1, damage to the stationary disc seal 415 caused by the abrupt change in the inner diameter of the housing 1 can be further reduced.

[0088] The transition walls W4 at both ends of the first guide cavity W20 can mitigate the abrupt change in inner diameter at the connection between the first inclined wall W2 and the walls of the housing 1 on both sides. Along the axial direction of the housing 1, the inner diameter of the cavity enclosed by the transition walls W4 gradually decreases from the side away from the stationary volute 41 to the side closer to the stationary volute 41. Similarly, the transition walls W4 at both ends of the second guide cavity W30 can mitigate the abrupt change in inner diameter at the connection between the second inclined wall W3 and the walls of the housing 1 on both sides. Along the axial direction of the housing 1, the inner diameter of the cavity enclosed by the transition walls W4 gradually increases from the side away from the stationary volute 41 to the side closer to the stationary volute 41. In one specific embodiment, the transition walls W4 can be rounded chamfered surfaces to make the corners of the housing walls smoother.

[0089] In some embodiments, along the axial direction of the housing 1, the width of the cavity W is not less than the diameter of the exhaust inlet 121a, the exhaust inlet 121a is located on the wall forming the cavity W, and in some embodiments, the exhaust inlet 121a is partially located on the groove wall surface W1 and partially located on at least one of the first inclined wall surface W2 and the second inclined wall surface W3.

[0090] Please see Figure 24 and Figure 25 In some embodiments, along the axial direction of the housing 1, the width of the groove wall surface W1 is greater than or equal to the diameter of the exhaust inlet 121a, and the exhaust inlet 121a is at least partially located on the groove wall surface W1. In some embodiments, the exhaust inlet 121a is entirely located on the groove wall surface W1, which better avoids the stationary disc seal 415, such as... Figure 24 , 25 As shown, avoiding the stationary disc seal 415 is more effective. Of course, in some other embodiments, the exhaust inlet 121a may also be partially located on the groove wall surface W1 and partially located on at least one of the first inclined wall surface W2 and the second inclined wall surface W3, such as... Figure 14 , 15 As shown.

[0091] In one specific embodiment, within the allowable error range, the cross section of the clearance cavity W10 perpendicular to its axis is circular, and the inner diameter of the clearance cavity W10 remains unchanged along the axial direction. The exhaust inlet 121a is located on the groove wall surface W1.

[0092] Please see Figure 5 , Figure 14 and Figure 15 In some embodiments, the housing 1 has a pressure relief hole 17, which has a pressure relief inlet 17a and a pressure relief outlet 17b. The pressure relief inlet 17a is at least partially located on the groove wall surface W1. When installing the stationary scroll plate, this reduces the risk of scraping between the stationary scroll plate seal 415 and the pressure relief inlet 17a at the clearance cavity W10, thereby reducing the risk of compressor leakage. In some specific embodiments, the pressure relief inlet 17a is entirely located on the groove wall surface W1, resulting in better clearance.

[0093] In some embodiments, at least one of the pressure relief hole 17 and the exhaust channel 12a extends radially along the housing 1; this facilitates the processing of the pressure relief hole 17 and the exhaust channel 12a.

[0094] The compressor 100 also includes a pressure relief valve assembly 16, which is connected to the housing 1, and the pressure relief port 17 communicates with the pressure relief valve assembly 16. When the pressure in the high-pressure discharge chamber 110 of the compressor exceeds the design value of the pressure relief valve assembly 16, the pressure relief valve assembly 16 will open to prevent the compressor from bursting. In some specific embodiments, the pressure relief valve assembly 16 is connected to the housing 11, the pressure relief port 17 is located in the housing 11, the pressure relief valve assembly 16 is at least partially located in the pressure relief port 17, and a sealing ring is provided on the outer periphery of the pressure relief valve assembly 16.

[0095] Please see Figure 8 , Figure 14 and Figure 15In some embodiments, the compressor 100 has an exhaust chamber 110 located between the exhaust cover 2 and the stationary volute 41. The exhaust chamber 110 is connected to the exhaust inlet 121a. The exhaust passage 12a also has an exhaust outlet 122a located on the outer wall side of the housing 1. The exhaust inlet 121a is connected to the exhaust outlet 122a.

[0096] Please see Figure 2 , Figure 14 and Figure 15 In some embodiments, the housing 1 includes an outer shell 11 and a support portion 15 connected to the outer shell 11. The support portion 15 includes a first support body 15a and a second support body 15b, which are located at opposite ends of the axial direction of the outer shell 11. At least a portion of at least one of the exhaust channel 12a, the pressure relief hole 17, and the cavity W is located in the first support body 15a. And / or, the housing 1 also has an intake channel 12b, which is at least partially located in the second support body 15b. The thickness of the support portion 15 is at least partially greater than the thickness of the outer shell 11.

[0097] Please see Figure 2 In some embodiments, both the first support 15a and the second support 15b include mounting feet 151, which can be used to fix the compressor 100 in place. The mounting feet 151 have openings for easy engagement with mounting connectors. The support portion 15 extends radially outward along the outer casing 11, increasing the thickness of the end of the casing 1. This strengthens the support and, by arranging the cavity W, exhaust channel 12a, and intake channel 12b at the thicker end of the casing 1, reduces the impact of the cavity W, exhaust channel 12a, and intake channel 12b on the strength of the casing 1.

[0098] Please see Figure 13 In some embodiments, the housing 1 further includes a third support 15c, which extends from the inner wall of the housing 1 toward the axis of the housing 1. The side of the third support 15c facing the end cover 3 has a plurality of small holes for cooperating with and connecting the end cover 3. The other side of the third support 15c contacts the compressor core assembly 4 and can limit the compressor core assembly 4.

[0099] Please see Figure 2 and Figure 14 In some embodiments, the compressor 100 further includes an exhaust cover 2, the housing 1 has a connection hole 18, and the exhaust cover 2 is connected to the housing 1 via a cover connector 20, the cover connector 20 being at least partially located in the connection hole 18. The connection hole 18 is arranged in the first support 15a, which can reduce the impact of the connection hole 18 on the strength of the housing 1.

[0100] Please see Figures 21 to 25 In some other embodiments, the housing 1 can also be an extruded part, with the length direction of the mounting cavity 10 aligned with the length direction of the housing 1, which can reduce processing difficulty. In this case, both the exhaust channel 12a and the suction channel 12b are arranged in the housing 1.

[0101] Please see Figures 21 to 25 In some embodiments, at least one of the exhaust cover 2 and the end cover 3 is welded to the housing 1. In some embodiments, assembling the compressor core assembly 4 with the housing 1 and then welding the exhaust cover 2 and the end cover 3 to the housing 1 can reduce the number of leakage points of the compressor. Compared with the pipeline connection method, the welding method of exhaust cover 2 and end cover 3 has a lower risk of leakage.

[0102] Please see Figure 18 , Figure 19 , Figure 24 and Figure 25 In some embodiments, the housing 1 has a mounting cavity 10, which includes a motor mounting cavity 10b and a stationary disk mounting cavity 10a. The stationary scroll 41 is at least partially located in the stationary disk mounting cavity 10a, and the motor assembly 45 is at least partially located in the motor mounting cavity 10b. The motor assembly 45 is interference-fitted to the housing 1 at the motor mounting cavity 10b. In some specific embodiments, the inner diameter of the motor mounting cavity 10b is smaller than the inner diameter of the stationary disk mounting cavity 10a. When assembling the compressor core assembly 4 into the housing 1, the larger inner diameter of the stationary disk mounting cavity 10a facilitates smoother assembly of the compressor core assembly 4.

[0103] Please see Figure 6 and Figure 9 In some embodiments, the compressor 100 includes a compressor core assembly 4, which includes a stationary scroll 41, a moving scroll 42, a main bearing housing 43, a drive shaft assembly 44, and a motor assembly 45. The motor assembly 45 includes a rotor 452, which is connected to the drive shaft assembly 44. One end of the drive shaft assembly 44 is rotatably connected to the main bearing housing 43, and the other end of the drive shaft assembly 44 is rotatably connected to the moving scroll 42.

[0104] The compressor core assembly 4 also includes a first connecting member 46. The stationary scroll 41, the main bearing housing 43, and the motor assembly 45 are arranged axially along the housing 1, and the stationary scroll 41, the main bearing housing 43, and the motor assembly 45 are connected to the first connecting member 46. In some embodiments, the compressor core assembly 4 is pre-assembled, then the compressor core assembly 4 is interference-fitted to the housing 1, and finally the exhaust cover 2 and the end cover 3 are welded to the housing 1, which can reduce the leakage points of the compressor. Of course, the exhaust cover 2 and the end cover 3 can also be connected to the housing 1 with bolts and sealed by the housing sealing component.

[0105] In some embodiments, a plurality of spaced-apart first connectors 46 are used to connect the motor housing 453, the main bearing housing 43, and the stationary scroll 41, and the same first connector 46 can connect all three at the same time. The motor housing 453, the main bearing housing 43, and the stationary scroll 41 are each provided with mounting holes 460 for engaging with the first connectors 46.

[0106] In some embodiments, the compressor core assembly 4 further includes a first positioning pin, wherein one end of the first positioning pin is located in the first pin hole 4534 of the motor housing 453, and the other end of the first positioning pin is located in the second pin hole 4301 of the main bearing seat 43. The first positioning pin can be used to position the motor housing 453 and the main bearing seat 43, so that the first connector 46 can connect the motor housing 453, the main bearing seat 43 and the stationary scroll 41.

[0107] In some embodiments, the compressor core assembly 4 further includes a second positioning pin, wherein one end of the second positioning pin is located in the third pin hole of the stationary scroll 41, and the other end of the second positioning pin 49 is located in the second pin hole 4301 of the main bearing housing 43. The second positioning pin 49 can be used to limit the stationary scroll 41 and the main bearing housing 43, so that the first connecting member 46 can connect the motor housing 453, the main bearing housing 43 and the stationary scroll 41.

[0108] In some embodiments, the second pin hole 4301 extends through the main bearing housing 43 along its length, and the pin holes at both ends of the main bearing housing 43 coincide, such that the first locating pin 48 and the second locating pin 49 are arranged axially along the second pin hole 4301. Of course, in other embodiments, the two ends of the main bearing housing 43 may also use staggered pin holes, which are used for the mating installation of the first locating pin 48 and the second locating pin 49, respectively.

[0109] In a specific embodiment, one end of the drive shaft assembly 44 is rotatably connected to the main bearing housing 43 via a main bearing 430. Specifically, the inner ring of the main bearing 430 is connected to the drive shaft assembly 44, and the outer ring of the main bearing 430 is connected to the main bearing housing 43. The other end of the drive shaft assembly 44 is rotatably connected to the moving scroll 42 via a drive bearing 440. Specifically, the inner ring of the drive bearing 440 is connected to the drive shaft assembly 44, and the outer ring of the drive bearing 440 is connected to the moving scroll 42. The motor housing 453 includes a bearing housing portion 4533, which is located at the end of the motor housing 453 facing away from the moving scroll 42. The compressor 100 also includes a secondary bearing 454, which is at least partially located between the drive shaft assembly 44 and the bearing housing portion 4533. In some embodiments, a plurality of support ribs 4533a are arranged circumferentially on the bearing housing portion 4533. Within the allowable range of machining error, the axis of the bearing housing portion 4533 coincides with the axis of the motor housing 453. The motor housing 453, stator 451, and rotor 452 are arranged in a direction perpendicular to the axis of the motor assembly 45.

[0110] Please see Figures 1 to 5 , Figure 21 and Figure 26 This application also proposes a thermal management integrated device. In some embodiments, the thermal management integrated device includes a compressor as described in any one or more of the above embodiments to reduce the processing difficulty of the throttling oil return channel. Specifically, the thermal management integrated device includes a compressor 100, which includes a housing 1, an exhaust cover 2, and a stationary scroll 41. The housing 1 has a mounting cavity 10, and the stationary scroll 41 is at least partially located in the mounting cavity 10. The exhaust cover 2 is connected to the housing 1. The compressor 100 has an exhaust cavity 110 and an oil return channel K. The exhaust cavity 110 is located between the exhaust cover 2 and the stationary scroll 41, and the exhaust cavity 110 communicates with the oil return channel K. The compressor 100 has an installation gap Q, and the stationary scroll 41 includes a fixed disk portion 41a. The installation gap Q... Located between the fixed plate portion 41a and the housing 1, the compressor 100 also includes a stationary plate seal 415. The stationary plate seal 415 is connected to the fixed plate portion 41a and the housing 1. The stationary plate seal 415 is at least partially located in the installation gap Q. The stationary plate seal 415 includes a first sealing ring 415a and a second sealing ring 415b. The oil return channel K includes a throttling oil return channel R. The throttling oil return channel R is at least partially located between the first sealing ring 415a and the second sealing ring 415b, which can reduce the machining difficulty of the throttling oil return channel.

[0111] Please see Figure 26 In some embodiments, the thermal management integrated device further includes at least one of a flow channel plate 6, a first heat exchanger 7a, a second heat exchanger 7b, a first valve 8a, a second valve 8b, and a gas-liquid separator 9. The flow channel plate 6 has flow channels for connecting at least two of the components: the compressor 100, the first heat exchanger 7a, the second heat exchanger 7b, the first valve 8a, the second valve 8b, and the gas-liquid separator 9.

[0112] Please see Figure 26 In some embodiments, the flow channel plate 6 and the housing 1 can be a single piece, manufactured through casting, forging, stamping, extrusion, metal injection molding, or metal powder metallurgy. In some specific embodiments, the flow channel plate 6 and the housing 1 can be simultaneously extruded as a single unit. In this case, the length directions of the flow channel plate 6 and the housing 1 are aligned, reducing processing and assembly requirements and thus lowering processing difficulty. Alternatively, the flow channel plate 6 and the housing 1 can be extruded separately and then welded together to form a single unit. In other embodiments, the flow channel plate 6 and the housing 1 can also be extruded separately and then assembled. Figure 26 In the embodiment shown, the flow channel plate 6 is connected to the mounting body 12 of the housing 1, for example, the flow channel plate 6 is welded to the mounting surface 121 of the mounting body 12.

[0113] Please see Figure 26 In some embodiments, the housing 1 includes an outer shell 11 and a mounting body 12. The mounting body 12 has a mounting surface 121, which is planar in some embodiments to facilitate the assembly or welding connection between the housing 1 and the flow channel plate 6. In this case, both the exhaust passage 12a and the intake passage 12b of the compressor 100 are located in the mounting body 12, serving as inlet and outlet ports connecting the compressor 100 and the flow channel plate 6, thus reducing the use of piping.

[0114] Some of the technical features in the above embodiments can be combined or replaced.

[0115] The technical principles of this application have been described above with reference to specific embodiments. However, it should be noted that these descriptions are merely for explaining the principles of this application and should not be construed as limiting the scope of protection of this application in any way. Other specific technical solutions or equivalent substitutions that can be conceived by those skilled in the art without creative effort will fall within the scope of protection of this application.

Claims

1. A compressor characterized by, The compressor comprises a shell, an exhaust cover and a static volute, the shell has a mounting cavity, the static volute is at least partially located in the mounting cavity, the exhaust cover is connected with the shell, the compressor has an exhaust cavity and an oil return channel, the exhaust cavity is located between the exhaust cover and the static volute, and the exhaust cavity communicates with the oil return channel; The compressor has a mounting gap, the static volute comprises a fixed disc part, the mounting gap is located between the fixed disc part and the shell, the compressor further comprises a static disc seal, the static disc seal is connected with the fixed disc part and the shell, the static disc seal is at least partially located in the mounting gap, the static disc seal comprises a first sealing ring and a second sealing ring, the oil return channel comprises a throttling oil return channel, and the throttling oil return channel is at least partially located between the first sealing ring and the second sealing ring.

2. The compressor of claim 1, wherein, At least one of the static volute and the shell has a static disc sealing groove, the static disc seal is at least partially located in the static disc sealing groove, and the static disc sealing groove is located at least one of an outer peripheral wall side of the fixed disc part and an inner peripheral wall of the shell.

3. The compressor of claim 1, wherein, The oil return channel further comprises an oil inlet flow channel, the oil inlet flow channel is at least partially located in the fixed disc part, the exhaust cavity communicates with the oil inlet flow channel, and the oil inlet flow channel communicates with the throttling oil return channel. And / or, the oil return channel further comprises an oil outlet flow channel, the oil outlet flow channel is at least partially located in the fixed disc part, the compressor further has an oil return cavity, the throttling oil return channel communicates with the oil outlet flow channel, and the oil outlet flow channel communicates with the oil return cavity.

4. The compressor of claim 3, wherein, The oil inlet flow channel comprises a first oil inlet channel and a second oil inlet channel, the exhaust cavity communicates with the first oil inlet channel, the first oil inlet channel and the second oil inlet channel communicate, the second oil inlet channel communicates with the throttling oil return channel, and the equivalent flow area of the first oil inlet channel is greater than that of the second oil inlet channel.

5. The compressor of claim 4, wherein, The first oil inlet channel extends along the axial direction of the fixed disc part, and the second oil inlet channel extends along the radial direction of the fixed disc part. The channel inlet of the first oil inlet channel is located on the end face of the fixed disc part towards the exhaust cavity, and the channel outlet of the second oil inlet channel is located on the outer peripheral wall surface of the fixed disc part.

6. The compressor of claim 3, wherein, The oil outlet flow channel comprises a first oil outlet channel and a second oil outlet channel, the throttling oil return channel communicates with the first oil outlet channel, the first oil outlet channel and the second oil outlet channel communicate, the second oil outlet channel communicates with the oil return cavity, and the equivalent flow area of the first oil outlet channel is greater than that of the second oil outlet channel.

7. The compressor of claim 6, wherein, The first oil outlet channel extends along the radial direction of the fixed disc part, and the second oil outlet channel extends along the axial direction of the fixed disc part. The channel inlet of the first oil outlet channel is located on the peripheral wall surface of the fixed disc part, and the channel outlet of the second oil outlet channel is located on the end face of the fixed disc part away from the exhaust cavity.

8. The compressor according to any one of claims 3 to 7, characterized in that The compressor further includes a moving scroll and a main bearing seat, the oil return cavity is located between the moving scroll and the main bearing seat, the oil return passage further includes an oil return flow channel, the oil return flow channel is at least partially located in the main bearing seat, the oil discharge flow channel is in communication with the oil return flow channel, and the oil return flow channel is in communication with the oil return cavity.

9. The compressor according to any one of claims 1 to 7, characterized in that The exhaust cavity includes a first cavity and a second cavity, the second cavity is in communication with the oil return passage, the fixed disc portion has a scroll exhaust port, the scroll exhaust port is in communication with the first cavity, the compressor has an exhaust passage, the exhaust passage is in communication with the second cavity, the compressor includes a separation barrier, the separation barrier is at least partially located between the first cavity and the second cavity, and the compressor has a separation passage, the separation passage is in communication with the first cavity and the second cavity.

10. A thermal management integrated device, comprising: A compressor includes a housing, an exhaust cover and a stationary scroll, the housing has a mounting cavity, the stationary scroll is at least partially located in the mounting cavity, the exhaust cover is connected with the housing, the compressor has an exhaust cavity and an oil return passage, the exhaust cavity is located between the exhaust cover and the stationary scroll, and the exhaust cavity is in communication with the oil return passage. The compressor has a mounting gap, the stationary scroll includes a fixed disc portion, the mounting gap is located between the fixed disc portion and the housing, the compressor further includes a stationary disc seal, the stationary disc seal is connected with the fixed disc portion and the housing, the stationary disc seal is at least partially located in the mounting gap, the stationary disc seal includes a first sealing ring and a second sealing ring, the oil return passage includes a throttling oil return passage, and the throttling oil return passage is at least partially located between the first sealing ring and the second sealing ring.

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