compressor

Abstract

The application provides a compressor, which comprises a casing, a rotating shaft, a bearing and an oil-gas isolation cover, the bearing is at least partially located in the casing, the rotating shaft is connected with the bearing, the bearing comprises a main bearing seat, the oil-gas isolation cover is connected with the main bearing seat, the main bearing seat is provided with a gas supply channel, the bearing is provided with an oil return channel, the oil-gas isolation cover is located in the casing, and the oil-gas isolation cover is at least partially located between the gas supply channel and the oil return channel. The compressor provided by the application reduces the mixing of the air inlet and the oil return, thereby reducing the probability of the lubricating oil entering the gas supply channel, reducing the oil-gas entering the compression chamber and ensuring the volume rate of the compression chamber.

Description

Technical Field

[0001] This application belongs to the field of refrigerant compression, specifically, it relates to a compressor. Background Technology

[0002] The compressor is one of the important components of an air conditioning system. In related technologies, an isolation cover is installed between the motor and the working fluid intake to prevent the heat generated by the motor, which serves as the drive mechanism, from being transferred to the refrigerant being drawn in (i.e., intake air). However, if a large amount of oil and gas is drawn into the intake chamber and into the compression chamber during the compression process of the refrigerant, it will cause a decrease in the volume fraction of the compression chamber. Summary of the Invention

[0003] The technical problem to be solved by this application is to provide a compressor that can reduce the amount of lubricating oil entering the air supply passage.

[0004] This application provides a compressor, including a housing, a rotating shaft, a support member, and an oil-gas isolation cover. The support member is at least partially located inside the housing. The rotating shaft is connected to the support member. The support member includes a main bearing housing. The oil-gas isolation cover is connected to the main bearing housing. The main bearing housing is provided with an air supply channel. The support member has an oil return channel. The oil-gas isolation cover is located inside the housing, and at least partially located between the air supply channel and the oil return channel. The compressor has a housing cavity, which includes a first inner cavity, and the first inner cavity includes a first sub-cavity and a second sub-cavity. The oil-gas isolation cover is located between the first sub-cavity and the second sub-cavity. The air supply channel communicates with the first sub-cavity, and the oil return channel communicates with the second sub-cavity. The oil-gas isolation cover has an air inlet and an air outlet. The housing has an air inlet, which includes an opening located on the inner wall of the housing. The air inlet is directly opposite the opening. The air inlet communicates with the first sub-cavity and the second sub-cavity, and the air outlet communicates with the first sub-cavity and the second sub-cavity.

[0005] The compressor provided in this application has an air supply channel in the main bearing housing and an oil return channel in the support component. By setting an oil-gas isolation cover, the oil-gas isolation cover is located at least partially between the air supply channel and the oil return channel, which reduces the situation where lubricating oil returning from the oil return channel mixes with the refrigerant gas flowing to the air supply channel, thereby reducing the probability that lubricating oil enters the air supply channel and then enters the compression chamber. Attached Figure Description

[0006] 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.

[0007] Figure 1 A perspective view of a compressor provided in an embodiment of this application; Figure 2 An exploded view of a compressor provided in an embodiment of this application; Figure 3 A cross-sectional view of a compressor provided in an embodiment of this application; Figure 4 This is a diagram showing the fit between the fixed vortex and the moving vortex in one state in an embodiment of this application. Figure 5 for Figure 3 Enlarged view of center circle A; Figure 6 for Figure 3 Sectional view along direction D in the middle; Figure 7 This is a structural diagram of the wear-resistant plate and pump base in the separated state in the embodiments of this application; Figure 8 This is an exploded view of the oil pump in an embodiment of this application; Figure 9 This is a structural diagram of the oil pump with an oil suction pipe in an embodiment of this application; Figure 10 for Figure 3 A magnified view of center circle E; Figure 11 This is a structural diagram of the moving scroll plate with an oil passage hole in an embodiment of this application; Figure 12 This is a partial cross-sectional view of the compressor provided in an embodiment of this application; Figure 13 This is a perspective view of the moving vortex disk in the embodiments of this application; Figure 14 This is a diagram showing the distribution of the oil passages in the moving end plate in the embodiments of this application; Figure 15 for Figure 12 A magnified view of center circle F; Figure 16 A cross-sectional view of a compressor provided in an embodiment of this application; Figure 17 This is a structural diagram of the moving vortex disk in the embodiments of this application; Figure 18 This is a structural diagram of the main bearing housing in an embodiment of this application; Figure 19 A cross-sectional view of a compressor provided in an embodiment of this application; Figure 20 This is a structural diagram of the oil and gas isolation cover in the embodiments of this application; Figure 21 This is a cross-sectional view of the oil and gas isolation cover in an embodiment of this application; Figure 22 Another partial cross-sectional view of the compressor provided in an embodiment of this application; Figure 23 This is a cross-sectional view of the moving end plate in an embodiment of this application; Figure 24 This is an exploded view of the one-way valve and cover in an embodiment of this application; Figure 25 This is a perspective view of the moving vortex disk in the embodiments of this application; Figure 26 This is a diagram showing the engagement of the fixed vortex and the moving vortex in another state in an embodiment of this application. Figure 27 Another partial cross-sectional view of the compressor provided in an embodiment of this application; Figure 28 This is a structural diagram of the exhaust valve and the moving scroll plate in an exploded state, as provided in the embodiments of this application. Figure 29a This is a side view of the lift limiter in an embodiment of this application; Figure 29b This is a structural diagram of the lift limiter in the embodiments of this application; Figure 30 This is a cross-sectional view of the muffler in an embodiment of this application; Figure 31 This is another cross-sectional view of the muffler in the embodiments of this application; Figure 32 for Figure 19 A magnified view of circle B in the center. Detailed Implementation

[0008] 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.

[0009] It should be understood that the described embodiments are merely some, not all, of the embodiments in this application. All other embodiments obtained by those skilled in the art based on the embodiments in this application without inventive effort are within the scope of protection of this application.

[0010] like Figures 1 to 3As shown, this embodiment provides a compressor including a compressor housing, a support member, a compression mechanism, a drive mechanism 9, and a rotating shaft assembly. The compressor housing includes a casing 1 and a cover 7. The compression mechanism, drive mechanism 9, and rotating shaft are all located within the entire compressor housing. The support member is at least partially located within the casing 1, meaning the support member can be entirely located within the casing 1, in which case the casing 1 and the cover 7 are directly connected. Alternatively, the support member can be partially located within the casing 1 and partially located outside the casing 1, in which case the casing 1, the support member, and the cover 7 are connected, with the support member partially located between the casing 1 and the cover 7.

[0011] The compression mechanism includes a moving scroll 4 and a fixed scroll 5. The moving scroll 4 is supported by a support member and contacts the support member. The drive mechanism 9 is connected to the rotating shaft assembly. The rotating shaft assembly is connected to the moving scroll 4. The rotating shaft assembly includes a rotating shaft 3. The rotating shaft 3 is installed in conjunction with the support member. The compression mechanism is located at least partially between the support member and the cover 7. Specifically, the fixed scroll 5 is connected to the cover 7. The moving scroll 4 includes a moving end plate 41 and a moving scroll body 42, with the moving scroll body 42 located on one side of the moving end plate 41 along the thickness direction. The fixed scroll 5 includes a fixed end plate 51 and a fixed scroll body 52, with the fixed scroll body 52 located on one side of the fixed end plate 51 along the thickness direction. The fixed scroll body 52 meshes with the moving scroll body 42. The compressor has a compression chamber V, which is at least partially located between the moving scroll 4 and the fixed scroll 5. Specifically, the compression chamber V is at least partially located between the moving end plate 41 and the fixed end plate 51, and it is located between the fixed scroll body 52 and the moving scroll body 42. In other words, the moving scroll 4 and the fixed scroll 5 cooperate to form the compression chamber V. During the compression of the refrigerant, the fixed scroll body 52 meshes with the moving scroll body 42, driving the refrigerant to be gradually pushed towards the center and compressed within the compression chamber V. During the process of the compressor compressing the refrigerant, the support component supports the moving scroll 4. At least part of the end face of the moving end plate 41 on the side away from the moving scroll 42 slides in contact with the support component. The support component includes the main bearing seat 6.

[0012] The compression mechanism has an air intake chamber S and an oil storage chamber C3. The air intake chamber S is located on the periphery of the compression chamber V and is at least partially located between the cover 7 and the fixed scroll 5. The oil storage chamber C3 is located inside the housing 1 and is located close to the bottom plate of the housing 1.

[0013] In compressors, lubrication not only reduces friction and wear but also provides sealing, cooling, and noise reduction. In related technologies, magnets are used to attract metal debris by placing them on the filter screen of the oil sump. Although the filter screen is located outside the oil pump, metal powder generated during operation can still enter the pump's internal cavity and then, along with the lubricating oil, enter components such as bearings and motors, causing damage. Therefore, the compressor provided in this embodiment includes an oil pump 2, located inside the housing 1. The oil pump 2 pumps lubricating oil to the required parts within the housing 1 for lubrication. For key technical details of this embodiment, please refer to [link to relevant documentation]. Figures 5 to 9 The oil pump 2 has an inner cavity 20 and includes an adsorption element 21, which is at least partially located within the inner cavity 20. In this embodiment, the adsorption element 21 can be entirely located within the inner cavity 20, or partially located within and partially located outside the inner cavity 20 (e.g., partially outside the oil pump 2). The oil pump 2, as a power device, draws lubricating oil into the inner cavity 20 and then discharges it. During the pumping process, it relies on the movement of its moving parts to transport the lubricating oil. The adsorption element 21 has adsorption properties, capable of adsorbing substances in the lubricating oil that could damage or destructively harm the components in the compressor. In some embodiments, the adsorption element 21 is a magnet, possessing magnetic properties, capable of attracting metal powder or metal particles in the lubricating oil. This prevents the metal powder or metal particles from entering the compressor along with the lubricating oil, significantly reducing or even eliminating damage to components such as bearings and magnets on the drive mechanism 9 caused by the metal powder or metal particles.

[0014] If an adsorption element 21 is installed outside the oil pump 2, the adsorption element 21 can attract metal powder or metal particles contained in the lubricating oil outside the oil pump 2. However, the moving parts are usually inside the oil pump 2, generally in the inner cavity 20 of the oil pump. During the movement of the moving parts, they will generate metal powder or metal particles by running with other parts of the oil pump 2, causing the metal powder or metal particles to enter the inner cavity 20 of the oil pump. In this embodiment, by setting an adsorption element 21 in the inner cavity 20 of the oil pump, the metal powder or metal particles generated by the moving parts of the oil pump 2 during the movement can be attracted by the adsorption element 21 in time, preventing them from flowing to other parts of the compressor with the lubricating oil.

[0015] Furthermore, please refer again. Figure 7 and Figure 8 The oil pump 2 includes an oil pump housing 22 and an oil pump rotor 23. The oil pump cavity 20 is located in the oil pump housing 22, and the oil pump rotor 23 is located in the oil pump cavity 20. As the actuating component of the oil pump, the oil pump rotor 23 provides kinetic energy during the oil pumping process to realize the delivery of lubricating oil.

[0016] The oil pump cavity 20 includes a first cavity 20a and a second cavity 20b. The housing 1 has an oil storage cavity C3 located outside the oil pump 2 and communicating with the first cavity 20a. The oil pump rotor 23 is located in the first cavity 20a. The suction member 21 is located in the second cavity 20b, and the first cavity 20a and the second cavity 20b are connected. The compressor includes a rotating shaft 3, which is movably connected to the oil pump rotor 23. The rotating shaft 3 is provided with an oil supply through hole 30, which communicates with the second cavity 20b. During the rotation of the shaft 3, the oil pump rotor 23 is driven to move in the first chamber 20a, drawing the lubricating oil in the oil storage chamber C3 into the first chamber 20a, and then discharging it into the second chamber 20b with the adsorption element 21. The adsorption element 21 adsorbs the metal powder or metal particles contained in the lubricating oil passing through the second chamber 20b, thereby reducing or preventing the metal powder or metal particles from entering the oil supply through hole 30 of the shaft 3. Since the metal powder or metal particles have a certain hardness, they can prevent damage to other components (especially moving parts) inside the compressor, thus providing a protective function.

[0017] Furthermore, the oil pump housing 22 includes a pump base 221, which has a flat shoulder 22a. The bottom surface of the oil pump rotor 23 contacts the flat shoulder 22a, specifically the bottom surface of the oil pump rotor 23 contacts the top surface of the flat shoulder 22a. In other words, the first cavity 20a and the second cavity 20b are located on both sides of the top surface of the flat shoulder 22a. Compared to the first cavity 20a, the second cavity 20b is closer to the bottom plate of the housing 1. That is, compared to the oil pump rotor 23, the suction member 21 is closer to the inner bottom surface of the oil pump inner cavity 20. In addition, the oil pump housing 22 also includes a wear-resistant plate 222, which is connected to the pump base 221. The oil pump rotor 23 is located between the wear-resistant plate 222 and the flat shoulder 22a. The top surface of the oil pump rotor 23 contacts the wear-resistant plate 222, specifically the bottom surface of the wear-resistant plate 222. At least one of the oil pump rotor 23, the wear-resistant plate 222, and the pump base 221 is made of metal. In this embodiment, the wear-resistant plate 222 serves both as a cover for the oil pump 2 and as a wear-resistant material. The oil pump rotor 23, the wear-resistant plate 222, and the pump base 221 are all made of metal. The wear-resistant plate 222 and the flat shoulder 22a limit the oil pump rotor 23 in its thickness direction. During operation, the oil pump rotor 23 wears against the wear-resistant plate 222 and the flat shoulder 22a, generating metal powder or metal particles. The adsorption member 21 can effectively adsorb the generated metal powder or particles.

[0018] In this embodiment, the wear-resistant plate 222, the flat shoulder 22a and the peripheral wall of the pump base 221 together form the first cavity 20a, making the first cavity 20a a relatively closed cavity. In this way, the volume of the first cavity 20a changes during the operation of the oil pump rotor 23, thereby achieving the purpose of oil suction and oil discharge.

[0019] Please refer to it again. Figure 6 and Figure 7 The oil pump 2 includes a meshing part 24, through which the oil pump rotor 23 meshes with the pump base 221. During operation, the oil pump rotor 23 is always meshed with the pump base 221 through the meshing part 24, and the outer wall of the oil pump rotor 23 is in contact with the inner wall of the first cavity 20a, thus dividing the first cavity 20a into two chambers: an oil inlet chamber 20a1 and an oil outlet chamber 20a2. The volume of the oil inlet chamber 20a1 can cyclically increase and decrease, and the volume of the oil outlet chamber 20a2 can cyclically decrease and increase. When the volume of the oil inlet chamber 20a1 increases, the volume of the oil outlet chamber 20a2 decreases; when the volume of the oil inlet chamber 20a1 decreases, the volume of the oil outlet chamber 20a2 increases. As the volume of the oil inlet chamber 20a1 gradually increases, a vacuum is formed, and the lubricating oil in the oil storage chamber C3 is drawn into the oil inlet chamber 20a1. Meanwhile, as the volume of the oil outlet chamber 20a2 gradually decreases, the lubricating oil is compressed, its pressure increases, and it enters the second chamber 20b from the oil outlet chamber 20a2. In this embodiment, the oil pump 2 has an oil inlet channel 2b and an oil outlet channel 2c. The oil inlet channel 2b connects the oil inlet chamber 20a1 and the oil storage chamber C3, and the oil outlet channel 2c connects the oil outlet chamber 20a2 and the second chamber 20b. The oil inlet channel 2b and the oil outlet channel 2c are located on both sides of the meshing part 24. That is, during the operation of the oil pump rotor 23, the lubricating oil in the oil storage chamber C3 enters the oil inlet chamber 20a1 through the oil inlet channel 2b, and the lubricating oil in the oil outlet chamber 20a2 enters the second chamber 20b through the oil outlet channel 2c. The opening size of the oil outlet channel 2c can be set according to requirements, thereby ensuring that the pressure of the lubricating oil entering the second cavity 20b meets the usage requirements. The oil outlet channel 2c extends outward from the inner wall of the second cavity 20b.

[0020] Please refer to it again. Figure 3 and Figure 8 The second cavity 20b includes a countersunk hole 20b1, and the adsorption member 21 is at least partially installed in the countersunk hole 20b1. There is a gap between the top surface of the adsorption member 21 and the end face of the rotating shaft 3 (the end face of the section where the rotating shaft 3 mates with the oil pump rotor), which ensures that the lubricating oil can smoothly enter the oil supply through hole 30 from the second cavity 20b, and also reserves space for the adsorption of generated metal powder or metal particles.

[0021] In addition, the rotating shaft 3 is usually a metal part. In order to prevent the adsorbent 21 from slipping out of the countersunk hole 20b1 and adsorbing the rotating shaft 3, which would block the inlet of the oil supply through hole 30, the oil pump 2 includes a limiting part 25. Please refer to the figure. The limiting part 25 is connected to the pump base 221. The limiting part 25 is used to limit the adsorbent 21 in the direction of the rotating shaft 3. In this embodiment, the structure of the limiting part 25 is not specifically limited. It can be a limiting ring covering the edge of the adsorbent 21 and the limiting ring is connected to the pump base 221 (e.g., threaded connection). Alternatively, the inner wall opening of the countersunk hole 20b1 can be provided with a flange. The flange can be a continuous circle or an intermittent setting. After the adsorbent 21 is installed into the countersunk hole 20b1, this flange is set to limit the adsorbent 21.

[0022] Please refer to it again. Figure 6 and Figure 7 The pump base 221 is provided with a recess 20c, which extends outward from the inner wall of the first cavity 20a and connects the first cavity 20a and the oil inlet channel 2b. This ensures that during the operation of the oil pump rotor 23, the oil inlet channel 2b is always connected to the oil inlet chamber 20a1 of the first cavity 20a, and the oil pump rotor 23 will not cover the oil inlet channel 2b, thus ensuring the continuous delivery of lubricating oil.

[0023] Please see Figure 6 and Figure 7 In some embodiments, the engaging portion 24 includes a protrusion 24a and a groove 24b, with the protrusion 24a at least partially located in the groove 24b. One of the protrusion 24a and the groove 24b is located on the pump seat 221, and the other is located on the oil pump rotor 23. During operation, the outer peripheral wall of the protrusion 24a can engage with the peripheral wall of the groove 24b, thus ensuring that the oil inlet channel 2b and the oil outlet channel 2c are not connected.

[0024] Please see Figure 8 In this embodiment, the oil pump rotor 23 has a mounting hole 230, and the rotating shaft 3 is clearance-fitted with the mounting hole 230. The compressor includes a drive mechanism 9, which is connected to the rotating shaft 3. The centerline of the section of the rotating shaft 3 that mates with the drive mechanism 9 is eccentrically positioned relative to the centerline of the section of the rotating shaft 3 that mates with the oil pump rotor 23. The drive mechanism 9 drives the rotating shaft 3 to rotate. Because the rotating shaft 3 and the mounting hole 230 are clearance-fitted, the rotating shaft 3 will not drive the oil pump rotor 23 to rotate synchronously. Due to the eccentric positioning, the rotating shaft 3 can provide power to the oil pump rotor 23, enabling it to move within the first cavity 20a and engage with the inner wall of the first cavity 20a, thereby achieving oil pumping operation.

[0025] Please refer to it again. Figure 2 , Figure 3 and combined Figure 5In this embodiment, the compressor includes a secondary bearing housing 11, which is located inside the housing 1 and connected to the housing 1. A pump seat 221 is connected to the secondary bearing housing 11. A wear-resistant plate 222 is located between the pump seat 221 and the secondary bearing housing 11. This embodiment does not specifically limit the connection method between the pump seat 221 and the secondary bearing housing 11. In some embodiments, the pump seat 221 and the secondary bearing housing 11 are detachably connected to facilitate the cleaning of metal powder or particles adsorbed by the adsorption element 21. This can be achieved by providing threaded holes on the secondary bearing housing 11 and bolt holes on the pump seat 221 and the wear-resistant plate 222. Bolts pass through these bolt holes sequentially and engage with the threaded holes on the secondary bearing housing 11. The wear-resistant plate 222 is pressed between the pump seat 221 and the secondary bearing housing 11. The bolt holes on the pump seat 221 and the wear-resistant plate 222 can be round holes or open holes. Figure 7 and Figure 8 As shown. When using a threaded connection, the oil pump 2 can be at least partially housed in the secondary bearing housing 11, that is, the bottom of the secondary bearing housing 11 is provided with a pump seat mounting hole, and the pump seat 221 is at least partially installed in the pump seat mounting hole, as shown. Figure 5 As shown, this method can reduce the overall size and weight of the oil pump 2; alternatively, the oil pump 2 and the auxiliary bearing housing 11 can be distributed along the axial direction of the rotating shaft 3, as not shown in the figure. Alternatively, the pump housing 221 and the auxiliary bearing housing 11 can also be connected by snap-fit ​​or other methods.

[0026] Please see Figure 5 In this embodiment, the compressor includes a secondary bearing 12, and the rotating shaft 3 is connected to the secondary bearing housing 11 via the secondary bearing 12. The secondary bearing housing 11 is located inside the housing 1 and is connected to the housing 1. In this embodiment, the secondary bearing 12 is a sliding bearing. The secondary bearing 12 also requires lubrication during operation. When the lubricating oil in the oil reservoir C3 is insufficient to reach the bottom of the secondary bearing 12, the clearance fit between the rotating shaft 3 and the mounting hole 230 allows some lubricating oil to enter the area where the secondary bearing 12 is located through the clearance between the rotating shaft 3 and the mounting hole 230 for lubrication.

[0027] Please refer to it again. Figure 2 and Figure 3The oil pump 2 is installed at the bottom of the auxiliary bearing housing 11. For easy disassembly, cleaning, or maintenance, the housing 1 includes a cylinder 13 and a base plate 14, with the base plate 14 connected to the bottom end of the cylinder 13. Additionally, the compressor includes a seal 15, which is at least partially located between the cylinder 13 and the base plate 14. When disassembly, cleaning, or maintenance of the oil pump 2 is required, the base plate 14 can be removed for operation. Furthermore, the compressor includes connecting arms 111, with the auxiliary bearing housing 11 connected to the inner wall of the cylinder 13 via the connecting arms 111. The connecting arms 111 are spaced apart, with a large oil passage area between adjacent connecting arms 111, allowing oil to pass through without blockage.

[0028] Please refer to it again. Figure 6 The side wall of the cylinder 13 is provided with an oil sight glass 16, which can be used to check the amount of lubricating oil so that it can be replenished in time.

[0029] Please combine Figure 2 and Figure 9 To prevent insufficient lubricating oil in the oil reservoir C3 from reaching the pump base 221 and thus preventing oil suction, the oil pump 2 in this embodiment also includes an oil suction pipe 26. The oil suction pipe 26 is installed on the pump base 221 and has an oil inlet channel 2b. The oil suction pipe 26 extends toward the bottom plate 14 of the housing 1. Furthermore, the end of the oil suction pipe 26 facing the bottom plate of the housing 1 has a through groove 26a. The through groove 26a penetrates the peripheral sidewall of the oil suction pipe 26 and communicates with the oil inlet channel 2b. The side of the through groove 26a facing the bottom plate of the housing 1 is open. With this design, when the amount of lubricating oil is small, the lubricating oil can enter the oil inlet channel 2b of the oil suction pipe 26 through the through groove 26a, and then enter the oil inlet chamber 20a1.

[0030] Please refer to it again. Figure 3 and Figure 5The compressor includes a filter screen 27, which is connected to at least one of the oil pump housing 22 and the auxiliary bearing housing 11. The filter screen 27 has a filter screen cavity 27a, and the oil suction pipe 26 is located in the filter screen cavity 27a. Since many components in the compressor are in operation, such as shafts, bearings, and moving scrolls, these components will generate powder or particulate matter through friction with other components. These substances will enter the oil storage chamber C3 along with the lubricating oil. By setting up the filter screen 27 for filtration, the powder or particles in the oil storage chamber C3 can be reduced or prevented from entering the oil pump cavity 20, thereby improving the cleanliness of the lubricating oil entering the oil pump cavity 20. In addition, by setting up the adsorption element 21, and with the adsorption element 21 at least partially located in the inner cavity 20 of the oil pump, it is possible to ensure that the metal powder or metal particles generated by the oil pump itself during operation can be adsorbed by the adsorption element 21, thereby ensuring the cleanliness of the lubricating oil entering the oil supply through hole 30 of the rotating shaft 3, preventing the lubricating oil from being delivered to other operating parts in the compressor, causing damage to the operating parts and their mating parts, and improving the protection effect.

[0031] Please see Figure 3 and Figure 10 and combined Figure 11 In this embodiment, the moving scroll 4 is connected to the end of the rotating shaft 3. Specifically, the moving scroll 4 includes an assembly part 44, which is located on the side of the moving end plate 41 away from the moving scroll body 42. The assembly part 44 is provided with an assembly hole 44a. The compressor includes a bearing component 43. The rotating shaft 3 is connected to the assembly hole 44a through the bearing component 43. The center line of the assembly hole 44a is eccentrically set with the center line of the section of the rotating shaft 3 that is connected to the drive mechanism 9. During the rotation of the rotating shaft 3, it drives the moving scroll 4 to move horizontally, causing the moving scroll body 42 to mesh with the fixed scroll body 52. ​​This causes the refrigerant to be continuously compressed under the meshing motion of the moving scroll body 42 and the fixed scroll body 52. ​​More specifically, the compressor includes an eccentric part 31, which is connected to the end of the rotating shaft 3. The eccentric part 31 is connected to the assembly hole 44a through the bearing component 43. In this embodiment, the eccentric part 31, the bearing component 43, etc., are all located in the bearing housing cavity 60 of the main bearing housing 6.

[0032] During the refrigerant compression process, the moving scroll 4, bearing 43, eccentric part 31, and rotating shaft 3 all operate at high speeds. These components require lubrication to reduce friction and wear, and also to reduce noise. Please refer to [link / reference]. Figure 11 In the first embodiment, the assembly part 44 has an oil passage hole 40, which is connected to the outlet of the oil supply hole 30. Lubricating oil pumped by the oil pump 2 enters the oil supply hole 30 and then enters the assembly hole 44a from the outlet of the oil supply hole 30, lubricating the bearing part 43, the rotating shaft, the eccentric part 31, etc., in the assembly hole 44a. This embodiment does not specifically limit the number of oil passage holes 40; they can be designed according to requirements.

[0033] During the refrigerant compression process, excessively high temperatures within the compression chamber can reduce intake efficiency and lead to power loss. To minimize this, in the second embodiment, the lubricating oil flowing from the oil supply hole 30 can enter the moving end plate 41 of the moving scroll 4. During refrigerant compression, since the temperature of the lubricating oil flowing from the oil supply hole 30 is relatively lower than that of the moving end plate 41, some of the heat within the moving end plate 41 is transferred to the lubricating oil as it flows in and out of the plate. The lubricating oil then carries the heat out of the plate. The specific design is as follows: Please refer to... Figure 10 and combined Figures 12 to 14 The moving end plate 41 is provided with an oil passage 4a, which is at least partially located inside the moving end plate 41. The moving end plate 41 has an oil inlet hole 4a1 and an oil outlet hole 4a2. The oil passage 4a communicates with the oil inlet hole 4a1 and the oil outlet hole 4a2. The oil inlet hole 4a1 and the oil outlet hole 4a2 penetrate the end face of the moving end plate 41 opposite to the moving scroll body 42. By providing the oil passage 4a, lubricating oil can flow in the oil passage 4a. The heat concentrated in the middle of the compressor during the compression process can be carried away by the lubricating oil in the oil passage 4a, avoiding the situation where the temperature is too high, causing the parts to expand and wear more aggravated. In related technologies, oil passages are typically provided on the end face of the moving scroll plate or penetrate its side wall, usually for lubrication but with poor heat dissipation. In this embodiment, the oil inlet and outlet holes penetrate the end face of the moving end plate away from the moving scroll body, allowing lubricating oil to flow on the back side of the end face where the moving end plate meets the moving scroll body. This achieves the purpose of cooling the moving end plate of the moving scroll plate. At the same time, the lubricating oil will not flow out from the side wall of the moving end plate, ensuring that a large amount of lubricating oil does not enter the intake chamber and then the compression chamber. This achieves heat dissipation of the moving scroll plate while preventing a large amount of lubricating oil from entering the compression chamber, which helps to improve intake efficiency and thus improve the compression efficiency of the compressor.

[0034] Please refer to it again. Figure 14 In this embodiment, there are multiple oil passages 4a, each extending along a direction perpendicular to the thickness of the moving end plate 41. An oil inlet 4a1 is located at the center of the moving end plate 41, and one end of each oil passage 4a is connected to the oil inlet 4a1. Each oil passage 4a is also connected to at least one oil outlet 4a2. In other words, multiple oil passages 4a share the same oil inlet 4a1, and each oil passage 4a is equipped with at least one oil outlet 4a2. The oil supply through-hole 30 is connected to the oil inlet 4a1. By providing multiple oil passages 4a, the heat dissipation performance of the moving end plate 41 is improved. Specifically, the multiple oil passages 4a are radially distributed and evenly distributed on the moving end plate 41, achieving a uniform heat dissipation effect.

[0035] To facilitate the machining of the oil passage 4a, the end of each oil passage 4a away from the oil inlet hole 4a1 passes through the peripheral side of the moving end plate 41, and the hole is machined from the peripheral side of the moving end plate 41, which is quick and effective. In addition, the compressor includes a plug 47, which is used to block the end of the oil passage 4a away from the oil inlet hole 4a1, so as to prevent the lubricating oil entering the oil passage 4a from flowing out from the peripheral side of the moving end plate 41 and then into the suction chamber.

[0036] Similarly, for ease of processing, both the oil inlet hole 4a1 and the oil outlet hole 4a2 are arranged along the thickness direction of the moving end plate 41. The cross-sections of the oil passage 4a, the oil inlet hole 4a1, and the oil outlet hole 4a2 are all circular; in other words, the oil passage 4a, the oil inlet hole 4a1, and the oil outlet hole 4a2 are all circular holes. Since each oil passage 4a is connected to the oil inlet hole 4a1, the diameter of the oil inlet hole 4a1 is larger than the diameter of the oil passage 4a.

[0037] Furthermore, please refer again. Figure 12 and combined Figure 15 The end face of the moving end plate 41 facing away from the moving scroll body 42 has a first plane 41a. The first plane 41a is at least partially in contact with the main bearing housing 6, which provides support for the moving scroll 4. During operation, the moving scroll 4 slides in contact with the main bearing housing 6. In this embodiment, the contact can be direct or indirect. For example, the compressor includes a wear-resistant part 46. At least one of the first plane 41a and / or the end face of the main bearing housing 6 that contacts the first plane 41a is provided with the wear-resistant part 46. The wear-resistant part 46 has wear-resistant properties, so that the moving scroll 4 does not directly contact the main bearing housing 6, which helps to extend the service life of the moving scroll 4 and the main bearing housing 6.

[0038] Furthermore, the end face of the moving end plate 41 facing away from the moving scroll body 42 has a second plane 41b. The outlet end of the oil outlet 4a2 passes through the second plane 41b, and there is a first gap CL1 between the second plane 41b and the end face of the main bearing housing 6. This ensures that the outlet of the oil outlet 4a2 remains unobstructed and is not blocked by the end face of the bearing housing 6 during the operation of the moving scroll 4, which helps the lubricating oil to flow and discharge smoothly and improves the heat dissipation effect of the moving scroll 4. In addition, the outlet end of the oil outlet 4a2 is close to the first plane 41a, so that the lubricating oil flowing out of the outlet of the oil outlet 4a2 can flow to the surface of the wear-resistant part 46 for lubrication during the planar movement of the moving scroll 4. In addition, the compressor includes an anti-rotation part 800, such as Figure 16As shown, the anti-rotation part 800 is connected between the moving scroll 4 and the main bearing housing 6. The anti-rotation part 800 includes a pin 801 and a pin ring 802. One of the pin 801 and the pin ring 802 is located in the moving scroll 4, and the other is located in the main bearing housing 6. The pin 801 and the pin ring 802 are clearance-fitted. The central hole of the pin ring 802 is connected to the first gap CL1. The lubricating oil flowing out from the outlet of the oil outlet 4a2 can enter the pin ring 802 through the first gap, thereby lubricating the pin 801 and the pin ring 802.

[0039] Please refer to it again. Figure 10 The moving end plate 41 has a third plane 41c on its end face away from the moving vortex body 42. An oil inlet hole 4a1 penetrates the third plane 41c. A second gap CL2 exists between the third plane 41c and the bearing component 43. A third gap CL3 exists between the outlet of the oil supply through hole 30 and the inlet of the oil inlet hole 4a1. The second gap CL2 and the third gap CL3 are connected, allowing some of the lubricating oil flowing from the outlet of the oil supply through hole 30 to enter the second gap CL2 from the third gap CL3, and then enter the bearing component 43. The bearing component 43 is a sliding bearing, and the lubricating oil can lubricate the mating parts between the bearing component 43 and the rotating shaft 3, and / or the mating parts between the bearing component 43 and the assembly part 44. In this embodiment, the third plane 41c, the second plane 41b, and the first plane 41a are distributed from the inside to the outside along the radial direction of the moving end plate 41.

[0040] Please refer to it again. Figure 10 The inner wall of the assembly hole 44a is provided with a limiting shoulder 44b, and the top surface of the bearing part 43 abuts against the limiting shoulder 44b.

[0041] Please refer to it again. Figures 12 to 14 The compressor also has an oil inlet 4a4, which penetrates the end face of the moving end plate 41 facing the moving scroll 42 and is connected to the oil passage 4a. The compressor has a compression chamber V, and the oil inlet 4a4 is connected to the compression chamber V. By providing the oil inlet 4a4, during the meshing process of the moving scroll 42 and the fixed scroll 52, the oil inlet 4a4 is intermittently connected to the compression chamber V. When connected, some lubricating oil in the oil passage 4a can enter the compression chamber V through the oil inlet 4a4 to lubricate the mating parts of the moving scroll 4 and the fixed scroll 5. In this embodiment, the diameter of the oil inlet 4a4 is smaller than the diameter of the oil passage 4a to avoid excessive lubricating oil entering the compression chamber V and reducing compression efficiency. In addition, the number of oil inlets 4a4 is at least one. When there are multiple oil inlets 4a4, the multiple oil inlets 4a4 can be connected to the same oil passage 4a or to different oil passages 4a.

[0042] In this embodiment, the compression mechanism has a main outlet 510. Specifically, the fixed end plate 51 has a main outlet 510. The surface perpendicular to the thickness direction of the fixed end plate 51 is defined as the projection surface. The projection of the moving vortex body 42 on the projection surface includes the inner profile line 421 and the outer profile line 422 of the moving vortex. Please refer to [link / reference]. Figure 4 and Figure 13 and combined Figure 17 The inner profile 421 of the moving vortex includes a free end O1 and a profile start end O2. Compared to the free end O1, the profile start end O2 is closer to the main discharge outlet 510. Compared to the profile start end O2, the oil inlet 4a4 is closer to the free end O1. Similarly, compared to the outer profile 522 of the fixed vortex, the inner profile 521 of the fixed vortex is closer to the main discharge outlet 510. In this embodiment, "closer" means closer along the profile, not closer in a straight line. By setting the oil inlet 4a4 closer to the free end O1, during the meshing of the fixed vortex body 52 and the moving vortex body 42, the location of the oil inlet 4a4 is in the low-pressure area of ​​the compression chamber. The lubricating oil can smoothly enter the compression chamber to effectively lubricate the mating parts between the fixed vortex 5 and the moving vortex 4, avoiding the oil inlet 4a4 being affected by the relative high pressure in the compression chamber V, which would prevent the lubricating oil from smoothly entering the compression chamber V.

[0043] During the compression process of the refrigerant, the fixed scroll 52 and the moving scroll 42 mesh, driving the refrigerant gradually towards the center within the compression chamber V and compressing it. The pressure gradually increases. When the pressure reaches a certain level but does not reach the discharge pressure, the fixed scroll 5 and the moving scroll 4 may separate, causing pressure leakage and significantly reducing the compressor's compression efficiency. For this reason, please refer to [link / reference needed]. Figure 13 The compressor in this embodiment includes a moving disc tooth top seal 45, which is located at the end of the moving scroll 42 facing the fixed end plate 51. The moving scroll 42 is in sealing contact with the fixed end plate 51 through the moving disc tooth top seal 45. The compressor also includes a stationary disc tooth top seal 53, which is located at the end of the fixed scroll 52 facing the moving end plate 41. The fixed scroll 52 is in sealing contact with the moving end plate 41 through the stationary disc tooth top seal 53. The sealing contact is in the thickness direction of the fixed end plate 51. Because the moving disc tooth top seal 45 and the stationary disc tooth top seal 53 are elastic, when the pressure of the compressed refrigerant causes the scroll body of the fixed scroll 5 and the moving scroll 4 to separate from the end plate, the elasticity of the moving disc tooth top seal 45 and the stationary disc tooth top seal 53 still maintains a sealed connection with the end plate, ensuring the sealing performance of the compression chamber and improving the compression performance of the compressor.

[0044] In both the first and second embodiments described above, the lubricating oil flows through the bearing housing cavity 60 of the bearing seat in the support member during the oil return process. This lubricates various components within the bearing housing cavity 60, including the eccentric portion, bearing components, and the parts where the moving scroll 4 mates with the support member, reducing wear and improving the service life of each component. Furthermore, the support member has an oil return path L, through which the lubricating oil flowing through the bearing housing cavity 60 returns to the oil storage chamber C3 within the housing 1, and is then pumped by the oil pump 2. This ensures continuous circulation of the lubricating oil during the refrigerant compression process. In the above embodiments, the main bearing housing 6 is provided with an air supply channel 6a. The refrigerant enters the suction chamber from the air supply channel 6a and then enters the compression chamber from the suction chamber for compression. In related technologies, an isolation cover is installed between the motor and the working fluid inlet to prevent heat generated by the motor, which serves as the drive mechanism, from being transferred to the refrigerant being drawn in. Although the isolation cover effectively isolates heat transfer and prevents the drawn-in refrigerant from being heated, the refrigerant is affected by the lubricating oil returning from the oil return path. This causes the refrigerant gas to carry a large amount of lubricating oil from the air supply channel 6a into the suction chamber, resulting in the refrigerant entering the compression chamber carrying a large amount of lubricating oil. This leads to low volumetric efficiency and reduces the compressor's compression efficiency. Therefore, in this embodiment, the compressor includes an oil-gas isolation cover 8, which is located inside the housing 1 and is at least partially located between the air supply channel 6a and the oil return path L. The oil-gas isolation cover 8 is connected to the main bearing seat 6, and has a central hole for installation. In this embodiment, by setting an oil-gas isolation cover 8 to separate the gas supply channel 6a and the oil return channel L, the mixing of lubricating oil returning from the oil return channel with the refrigerant gas flowing into the gas supply channel can be greatly reduced. This reduces the amount of oil carried by the refrigerant entering the suction chamber from the gas supply channel 6a, and prevents a large amount of lubricating oil from being sucked into the compression chamber, which would cause a decrease in volumetric efficiency. This helps to improve the compression efficiency of the compressor.

[0045] Further, please refer to Figure 2 , Figure 3 , Figure 16 and Figure 18The housing 1 has an air inlet 10, an air supply channel 6a connected to the air inlet 10, an air intake chamber S connected to the air supply channel 6a, and an oil return line L connected to the oil storage chamber C3. An oil-gas isolation cover 8 is provided between the air inlet 10 and the oil return line L. The air intake chamber S and the oil storage chamber C3 are located on opposite sides of the oil-gas isolation cover 8, specifically on opposite sides of the oil-gas isolation cover 8 along the axial direction of the rotating shaft 3. In this way, the refrigerant entering the housing 1 from the air inlet 10 will flow upward, i.e., towards the main bearing seat 6, while the lubricating oil flows downward from the inner cavity 60 of the bearing seat towards the bottom plate of the housing 1. The flow direction of the refrigerant and the flow direction of the lubricating oil are opposite, and the oil-gas isolation cover 8 is located between the flow paths of the refrigerant and the lubricating oil, which greatly reduces or even avoids the lubricating oil entering the air intake chamber S. In this embodiment, there are multiple air supply channels 6a, which are arranged in a circular array around the center line of the main bearing seat 6. The phase difference between the moving vortex body 42 and the fixed vortex body 52 is 180 degrees. Therefore, after the moving vortex body 42 and the fixed vortex body 52 mesh, the crescent-shaped compression chamber is formed as a pair. The multiple air supply channels 6a are evenly distributed, which is conducive to the refrigerant gas being drawn into the compression chamber evenly and fully for compression, thereby improving the volumetric efficiency.

[0046] Please refer to it again. Figure 19 The compressor has a housing cavity C, which includes a first cavity C1 and a second cavity C2. The first cavity C1 is connected to the second cavity C2. Compared to the second cavity C2, the first cavity C1 is closer to the support member. The first cavity C1 includes a first sub-cavity C11 and a second sub-cavity C12. The oil-gas isolation cover 8 is located between the first sub-cavity C11 and the second sub-cavity C12. The air inlet 10 and the air supply channel 6a are both connected to the first sub-cavity C11, and the oil return channel L is connected to the second sub-cavity C12. The first sub-cavity C11 and the second sub-cavity C12 are both connected to the second cavity C2. In other words, the first sub-cavity C11 is the outer peripheral space of the oil-gas isolation cover 8, and the second sub-cavity C12 is the inner peripheral space of the oil-gas isolation cover 8. The second cavity C2 includes an oil storage cavity C3, which is located at the bottom of the second cavity C2. Refrigerant enters the first sub-cavity C11 (i.e., the outer peripheral space of the oil-gas isolation cover 8) from the inlet 10, and then enters the suction chamber S from the supply passage 6a. Oil returning from the bearing housing cavity 60 to the oil storage chamber C3 enters the second sub-cavity C12 (i.e., the inner peripheral space of the oil-gas isolation cover 8) through the return oil passage L, and then flows into the oil storage chamber C3. Further, the housing 1 includes a base plate 14, the inlet 10 includes an opening 101 located on the inner wall of the housing 1, and the vertical distance from the bottom end face of the oil-gas isolation cover 8 to the inner end face of the base plate 14 is... l 1 is less than the minimum vertical distance from opening 101 to the inner end face of base plate 14. l2. In other words, the bottom surface of the oil-gas isolation cover 8 is closer to the bottom plate 14 than the opening 101, which ensures that the refrigerant entering from the opening 101 is separated and blocked by the oil-gas isolation cover 8 and can flow towards the gas supply channel 6a.

[0047] Please see Figure 20 and Figure 21 The oil-gas isolation cover 8 has an inlet 84 and an outlet 85. The inlet 84 is directly opposite the opening 101 and connects the first sub-cavity C11 and the second sub-cavity C12. The outlet 85 also connects the first sub-cavity C11 and the second sub-cavity C12. The outlet 85 and the inlet 84 are spaced apart along the circumference of the oil-gas isolation cover 8, allowing the refrigerant gas to have a certain flow path from the inlet 84 to the outlet 85. Part of the refrigerant entering from the opening 101 will enter the inner circumferential space of the oil-gas isolation cover 8 (i.e., the second sub-cavity C12) through the inlet 84. During the flow of the refrigerant gas in the second sub-cavity C12, it can dissipate heat and cool the lubricating oil returning in the second sub-cavity C12. When the refrigerant flows to the outlet 85, part of the refrigerant can flow from the outlet 85 to the outer circumferential space of the oil-gas isolation cover 8 (i.e., the first sub-cavity C11), and then enter the suction chamber through the gas supply channel 6a. In this embodiment, the oil-gas isolation cover 8 is set to achieve the function of oil-gas separation, preventing a large amount of lubricating oil from entering the compression chamber, reducing the risk of liquid slugging, and also cooling the lubricating oil returning to the oil.

[0048] Please refer to it again. Figure 19 The oil-gas isolation cover 8, located away from the main bearing housing 6, has a gap CL between its end and the inner wall of the housing 1, and this gap CL communicates with the oil storage chamber C3. There is a distance between the air inlet 10 and the air supply channel 6a, specifically a distance between the opening 101 and the air supply channel 6a. When the refrigerant gas flowing in from the air inlet 10 contains liquid (such as liquid refrigerant, liquid lubricating oil, etc.), the liquid mixed in the refrigerant gas, after entering the housing 1, is drawn together by gravity due to the distance between the opening 101 and the air supply channel 6a, flowing from the gap CL to the oil storage chamber C3. This reduces or prevents liquid from entering the compression chamber, lowering the risk of liquid slugging. Furthermore, the liquid is also resisted by the oil-gas isolation cover 8, clinging to the outer wall of the oil-gas isolation cover 8 and flowing along the outer wall of the oil-gas isolation cover 8 towards the oil storage chamber C3.

[0049] Please refer to it again. Figure 20 and Figure 21In this embodiment, the oil-gas isolation cover 8 has a ring-shaped structure and includes a connecting portion 81 and an extension portion 82. The extension portion 82 is connected to the connecting portion 81, and the connecting portion 81 is connected to the main bearing seat 6. In order to allow the liquid hanging on the outer wall of the oil-gas isolation cover 8 to flow smoothly to the oil storage chamber C3, the diameter of the extension portion 82 is increased in at least a portion from the main bearing seat 6 toward the base plate 14. The increase can be incremental or staged, reducing the accumulation of liquid on the outer wall of the oil-gas isolation cover 8. In addition, the extension portion 82 has an end bend portion 83, which extends toward the drive mechanism 9. The lubricating oil flowing along the wall of the oil-gas isolation cover 8 can flow to the drive mechanism 9 to lubricate and cool the drive mechanism 9.

[0050] The drive mechanism 9 has an oil passage 90 that connects to the oil storage chamber C3. Lubricating oil flows out from the return oil passage L, passes through the second sub-chamber C12, and then enters the drive mechanism 9 located in the second inner chamber C2. After passing through the drive mechanism 9, it returns to the oil storage chamber C3. Please refer to [link / reference]. Figure 16 The drive mechanism 9 is a motor, including a stator assembly 91 and a rotor assembly 92. The stator assembly 91 and the rotor assembly 92 cooperate, and the rotor assembly 92 is connected to the rotating shaft 3. When the drive mechanism 9 is energized, the magnetic field generated by the stator assembly 91 interacts with the magnetic field generated by the rotor assembly 92, causing the rotor assembly 92 to rotate and drive the rotating shaft 3 to rotate. In this embodiment, the oil passage 90 includes a first oil passage 90a and a second oil passage 90b. The first oil passage 90a passes through the rotor assembly 92 from the main bearing seat 6 toward the base plate 14, and the second oil passage 90b passes through the stator assembly 91 from the main bearing seat 6 toward the base plate 14. The second oil passage 90b is located close to the inner wall of the housing 1. By opening oil passages in both the stator and rotor assemblies, the lubricating oil can be cooled and dissipated as it flows through the drive mechanism 9.

[0051] Please refer to it again. Figure 19In this embodiment, the support also includes a main bearing 61, and the rotating shaft 3 is installed in conjunction with the main bearing housing 6 via the main bearing 61. At least one of the main bearing housing 6 and the main bearing 61 has an oil return passage L, which connects the inner cavity 60 of the bearing housing and the second sub-cavity C12. The oil return passage L includes a channel L1 located in the main bearing housing 6 and connecting the inner cavity 60 of the bearing housing and the second sub-cavity C12. There are multiple channels L1, which are arranged in a circular array around the centerline of the main bearing housing 6. The channels L1 are located on the outer side of the main bearing 61 along the radial direction of the rotating shaft 3. The main bearing 61 is a rolling bearing, and the oil return passage L also includes a gap L2 between the rolling elements in the main bearing 61. During the compression of refrigerant, the compressor shaft 3 rotates, and the rolling elements in the main bearing 61 also rotate at high speed. Although there are gaps between the rolling elements, during the operation of the main bearing 61, the rolling elements may throw up the lubricating oil flowing through the gaps between the rolling elements, causing liquid slugging and damaging the moving plate, the main bearing housing 6, the eccentric part 31, etc. To address this, a channel L1 is provided on the main bearing housing 6, and the channel L1 is located radially outside the main bearing 61. In this way, the lubricating oil in the bearing housing cavity 60, especially the lubricating oil flowing out of the oil passage 4a of the driven end plate 41 in the above embodiment, can first reach the channel L1 and return to the oil storage cavity C3 through the channel L1, thereby reducing the large amount of lubricating oil approaching the main bearing 61 and causing liquid slugging. A small amount of lubricating oil entering between the rolling elements of the main bearing 61 can play a lubricating role, thereby extending the service life of the main bearing 61.

[0052] When a scroll compressor operates at low evaporation temperatures, it experiences problems such as increased suction volume, increased pressure ratio, and a rapid rise in discharge temperature. This leads to a sharp decline in compressor performance, insufficient heating capacity, and difficulty in operation. To address this issue and improve the efficiency of the compression mechanism during refrigerant compression, the compressor in this embodiment features an enthalpy-increasing channel 100. This channel enables simultaneous compression and refrigerant injection for mixing and cooling, thereby increasing the compressor's discharge capacity. Please refer to [reference needed]. Figures 22 to 23 The enthalpy-increasing channel 100 includes a cover channel 101 and a fixed scroll channel 102, which are connected. The cover channel 101 is located in the cover 7. The compressor has an enthalpy-increasing channel inlet 70a and at least one cover channel outlet 70b. The cover channel 101 connects the enthalpy-increasing channel inlet 70a and the cover channel outlet 70b. The fixed scroll channel 102 is located in the fixed end plate 51. At least a portion of the fixed scroll channel 102 has an angle θ with the thickness direction of the fixed end plate 51, wherein the angle θ is greater than 0° and less than 180°. In other words, at least a portion of the fixed scroll channel 102 is non-vertically arranged.

[0053] In this embodiment, there is at least one cover channel outlet 70b; in the following embodiments, it will be described as having only one cover channel outlet 70b. Specifically, please refer to... Figure 16 , Figure 22 and Figure 23 The fixed end plate 51 has a stationary disk channel inlet 50a and an enthalpy-increasing channel outlet 50b. The fixed scroll channel 102 connects the stationary disk channel inlet 50a and the enthalpy-increasing channel outlet 50b. The cover channel outlet 70b and the stationary disk channel inlet 50a are connected. The enthalpy-increasing channel outlet 50b is connected to the compression chamber V. During the compression of the refrigerant, the enthalpy-increasing channel 100 is used to receive refrigerant outside the compressor. In this embodiment, it receives refrigerant gas outside the compressor. The refrigerant gas enters the cover channel 101 from the enthalpy-increasing channel inlet 70a, then flows out of the cover channel 101 from the cover channel outlet 70b, and then enters the fixed scroll channel 102 from the stationary disk channel inlet 50a. Finally, it flows out of the fixed scroll channel 102 from the enthalpy-increasing channel outlet 50b and enters the compression chamber V, realizing simultaneous compression and spraying of refrigerant gas for mixing and cooling, thereby increasing the compressor's discharge capacity.

[0054] Furthermore, the stationary disk channel inlet 50a and the enthalpy-increasing channel outlet 50b are located on opposite sides of the fixed end plate 51 along its thickness direction. The surface perpendicular to the thickness direction of the fixed end plate 51 is defined as the projection surface. The projections of the stationary disk channel inlet 50a and the enthalpy-increasing channel outlet 50b on this projection surface do not overlap at least partially. In other words, the stationary disk channel inlet 50a and the enthalpy-increasing channel outlet 50b are not located in the same through hole along the thickness direction of the fixed end plate 51. Please refer again. Figure 23 In this embodiment, the fixed end plate 51 has a main outlet 510, and the enthalpy-increasing channel outlet 50b is located on the outer side of the main outlet 510 in the radial direction. The main outlet 510 is connected to the compression chamber V. In other words, the enthalpy-increasing channel outlet 50b and the main outlet 510 are not connected to the same compression chamber. In addition, since the crescent-shaped compression chambers are usually in pairs, there are two fixed scroll channels 102 and two enthalpy-increasing channel outlets 50b. Each fixed scroll channel 102 is connected to one enthalpy-increasing channel outlet 50b. That is, the refrigerant flowing out from the cover channel outlet 70b for enthalpy increase is divided into two streams and enters the corresponding fixed scroll channel 102, and then enters the two pairs of compression chambers for gas replenishment and enthalpy increase.

[0055] Further, please refer to Figure 22 and combined Figure 16 The fixed scroll channel 102 includes a first channel segment 102a, which is located inside the fixed end plate 51. The first channel segment 102a is at least partially arranged along a direction perpendicular to the thickness of the fixed end plate 51. In other words, the first channel segment 102a is at least partially arranged in the fixed end plate 51 along a horizontal direction.

[0056] During the compression of refrigerant by the compressor, the fixed scroll 52 and the moving scroll 42 mesh with each other, which makes the moving scroll 4 and the fixed scroll 5 have very high precision requirements. They are usually machined. In order to facilitate the machining of the first channel section 102a, at least one end of the first channel section 102a extends out of the peripheral sidewall of the fixed end plate 51. The compressor includes a head 54. The head 54 is provided at the end of the first channel section 102a near the outer wall of the fixed end plate 51. That is, the first channel section 102a is machined by drilling from the peripheral sidewall of the fixed end plate 51, and then the head 54 is used for sealing. Furthermore, the fixed scroll channel 102 includes a second channel section 102b, which connects the first channel section 102a and the stationary disk channel inlet 50a. The second channel section 102b is arranged along the thickness direction of the fixed end plate 51. The fixed scroll channel 102 also includes a third channel section 102c, which connects the first channel section 102a and the enthalpy-increasing channel outlet 50b. The third channel section 102c is also arranged along the thickness direction of the fixed end plate 51. Both the second channel section 102b and the third channel section 102c are arranged vertically for ease of processing. The refrigerant used for enthalpy increase is injected into the compression chamber from the stationary disk channel inlet 50a, passing sequentially through the second channel section 102b, the first channel section 102a, and the third channel section 102c, and then from the enthalpy-increasing channel outlet 50b. In this embodiment, the first channel segment 102a and the second channel segment 102b are connected, and there is an included angle between the first channel segment 102a and the second channel segment 102b. The second channel segment 102b is connected to the cover channel outlet 70b, and the second channel segment 102b is arranged along the thickness direction of the fixed end plate 51, so that the drill bit can process the second channel segment connecting the fixed scroll channel to the cover channel outlet in a positive direction relative to the fixed end plate during processing, which facilitates processing. In the absence of gas replenishment, the enthalpy-increasing channel 100 is equivalent to the clearance volume, which will inevitably reduce the volumetric efficiency of the compressor. To reduce the clearance volume of the compressor, please refer to [reference needed]. Figure 22 and combined Figure 24 , Figure 25 The compressor includes a one-way valve 200, which is at least partially located in the enthalpy-increasing channel 100. The one-way valve 200 can open the enthalpy-increasing channel 100 from the inlet 70a to the outlet 50b, and close it from the outlet 50b to the inlet 70a, so as to reduce the clearance caused by this part of the enthalpy-increasing channel 100 and ensure the volumetric efficiency of the compressor.

[0057] Please refer to it again. Figure 22 and Figure 24In some embodiments, the one-way valve 200 includes a valve plate 201, a limiter 202, and a fastener 203. The valve plate 201 and the limiter 202 are connected to the cover 7 via the fastener 203. The valve plate 201 is located between the surface of the cover channel outlet 70b and the limiter 202, and there is a lift gap between the limiter 202 and the surface of the cover channel outlet 70b. To facilitate the installation of the one-way valve 200, the enthalpy-increasing channel 100 also includes a connecting cavity 103, which is located between the cover 7 and the fixed scroll 5. The cover channel outlet 70b can communicate with the connecting cavity 103 via the one-way valve 200, and the stationary scroll channel inlet 50a communicates with the connecting cavity 103. The one-way valve 200 is located in the connecting cavity 103 and is fixed to the cover 7. In the replenishment state, refrigerant gas is introduced from the system circuit outside the compressor, entering the fixed scroll channel 102 through the enthalpy-increasing channel inlet 70a. When the pressure of this refrigerant gas increases to a certain level, it will push open the valve plate 201 and enter the connecting cavity 103. Then, it enters the fixed scroll channel 102 through the stationary plate channel inlet 50a, and finally enters the compression chamber through the enthalpy-increasing channel outlet 50b. In this embodiment, the cover 7 has an annular groove 70c, which is located outside the cover channel outlet 70b. By setting the annular groove 70c, the influence of end face unevenness on the closing and sealing performance of the valve plate 201 is reduced.

[0058] Please see Figure 24 and Figure 25 The compressor has an exhaust chamber 300, which is at least partially located between the cover 7 and the compression mechanism. Specifically, the exhaust chamber 300 is at least partially located between the cover 7 and the fixed scroll 5. The main discharge outlet 510 can directly communicate with the exhaust chamber 300. In this embodiment, the exhaust chamber 300 is located between the cover 7 and the fixed scroll 5. Since both the exhaust chamber 300 and the connecting chamber 103 are located between the cover 7 and the fixed scroll 5, in order to ensure that the exhaust chamber 300 and the connecting chamber 103 are not connected, the compressor includes a seal. The seal isolates the exhaust chamber 300 and the connecting chamber 103, preventing the high-pressure refrigerant gas in the exhaust chamber 300 from mixing with the refrigerant gas used for replenishment in the connecting chamber 103. The sealing element includes a sealing ring 400, which is located between the cover 7 and the fixed scroll 5. The sealing ring 400 abuts against the fixed end plate 51 on one side along its thickness direction, and against the cover 7 on the other side along its thickness direction. The sealing ring 400 includes an outer sealing portion 401 and a blocking portion 402. The outer sealing portion 401 is located around the exhaust chamber 300 and the connecting chamber 103, and the blocking portion 402 is located between the exhaust chamber 300 and the connecting chamber 103. In other words, the sealing ring 400 is an irregularly shaped sealing ring, with an overall figure-eight structure. Of course, in other embodiments, two sealing rings can be combined to seal the exhaust chamber 300 and the connecting chamber 103 respectively.

[0059] To facilitate the installation of the sealing ring 400, the cover 7 has a first flat portion 71, and the fixed scroll 5 has a second flat portion 55. The first flat portion 71 and the second flat portion 55 are arranged opposite each other along the thickness direction of the fixed end plate 51. At least one of the first flat portion 71 and the second flat portion 55 has a sealing groove 403, and the sealing ring 400 is at least partially located in the sealing groove 403. By providing the sealing groove 403, during the compressor assembly process, the sealing ring 400 is first installed into the sealing groove 403, preventing the sealing ring 400 from slipping out of the sealing groove and causing misalignment of the sealing ring 400, which would lead to sealing failure.

[0060] In addition to isolating the exhaust chamber 300 and the connecting chamber 103, the aforementioned sealing element also isolates the space between the intake chamber S and the exhaust chamber 300, and between the intake chamber S and the exhaust chamber 300. Specifically, the sealing element is at least partially located between the exhaust chamber 300 and the intake chamber S, and at least partially located between the connecting chamber 103 and the intake chamber S. The compressor includes a housing wall 72, which is located on the outer periphery of the outer wall of the fixed scroll 5. The intake chamber S is at least partially located between the housing wall 72 and the outer wall of the fixed scroll 5. In this embodiment, the housing wall 72 is part of the cover 7, or the housing wall 72 and the cover 7 are separate structures connected to each other.

[0061] In addition, the sealing element also includes a sealing gasket 500, which is located between the first flat portion 71 and the second flat portion 55, and is located around the sealing ring 400. The sealing gasket 500 further enhances the sealing performance between the cover 7 and the fixed scroll 5, preventing the intake chamber S from communicating with the exhaust chamber 300 and the connecting chamber 103.

[0062] In related technologies, the stationary scroll plate is equipped with both venting holes and enthalpy-increasing holes. These venting holes and enthalpy-increasing channels have different openings, meaning they are not shared. This increases the number of openings on the stationary scroll plate's end plate, not only increasing the processing steps for the stationary scroll plate but also reducing its structural strength. Therefore, please refer to [further details needed]. Figure 16 , Figure 22 and Figure 23In this embodiment, the fixed end plate 51 has a connecting hole 512 that extends through the fixed end plate 51 along its thickness direction. The connecting hole 512 communicates with the compression chamber V and the exhaust chamber 300. Additionally, the connecting hole 512 can also communicate with the enthalpy-increasing channel 100. That is, the connecting hole can communicate with the compression chamber, the exhaust chamber, and the enthalpy-increasing channel, allowing the enthalpy-increasing channel and the connecting hole (i.e., the unloading hole) to be shared. This simplifies the structure and reduces the number of openings in the fixed end plate. In this embodiment, the connecting hole 512 and the main exhaust outlet 510 are spaced apart; in other words, the connecting hole 512 and the main exhaust outlet 510 are not the same hole. In this embodiment, the compression chamber V and the exhaust chamber 300 are connected through the connecting hole 512. This can meet the auxiliary exhaust function of unloading and regulating the compressor during the refrigerant compression process. It can also connect the enthalpy-increasing channel 100 and the compression chamber V, so that the gas replenishment enthalpy-increasing hole and the auxiliary unloading hole share the same hole. This avoids the need to open additional holes on the fixed end plate 51, reduces the structural damage to the fixed end plate 51, helps to improve the structural strength of the fixed end plate 51, and at the same time reduces the number of hole processing steps, which helps to improve the processing efficiency of the fixed scroll 5.

[0063] In this embodiment, since the connecting hole 512 can communicate with the enthalpy-increasing channel 100, a bypass port 512a is provided on the hole wall of the connecting hole 512, and the bypass port 512a communicates with the enthalpy-increasing channel 100.

[0064] In the gas replenishment state, medium-pressure gas is replenished in the intermediate chamber of the compressor; therefore, the location of the connecting hole 512 cannot be in the high-pressure chamber. Please refer again. Figure 4 The surface perpendicular to the thickness direction of the fixed end plate 51 is defined as the projection surface. The projection of the fixed vortex body 52 on the projection surface includes the inner profile 521 and the outer profile 522 of the fixed vortex. The projection of the moving vortex body 42 on the projection surface includes the inner profile 421 and the outer profile 422 of the moving vortex. When the free end O1 of the inner profile 421 of the moving vortex contacts the outer profile 522 of the fixed vortex, the inner profile 421 of the moving vortex and the outer profile 522 of the fixed vortex have multiple contact points (P1, P2, etc.) along the line direction from the free end O1 to the starting end O2 of the profile. The projection of the connecting hole 512 on the projection surface is close to the second contact point P2. At this time, the free end O1 coincides with the first contact point P1. When the free end O1 of the inner profile 421 of the moving vortex contacts the outer profile 522 of the fixed vortex, the volume of the compression chamber is at its maximum, and the outermost compression chamber in the maximum volume state has just been formed. At this time, the pressure in the outermost compression chamber is equivalent to the pressure in the intake chamber S. The design of placing the projection of the connecting hole 512 on the projection plane close to the second contact point P2 ensures that the connecting hole 512 is in a low-to-medium pressure position in the compression chamber. Among them, the starting end O2 of the profile is closer to the main exhaust outlet 510 than the free end O1.

[0065] As the moving scroll 42 further engages with the fixed scroll 52, the volume of the outermost compression chamber begins to decrease, and the pressure gradually increases. If the free end O of the inner profile 421 of the moving scroll contacts the outer profile 522 of the fixed scroll, the connecting hole 512 is exposed in the outermost compression chamber. When gas is supplied to the compression chamber through the enthalpy-increasing channel 100, due to the movable nature of the moving scroll 4, some of the refrigerant gas drawn into the outermost compression chamber will be squeezed out of the compression chamber and return to the suction chamber due to the gas supply from the enthalpy-increasing channel 100, reducing the compressor's discharge volume and compression efficiency. Therefore, when the free end O1 of the inner profile 421 of the moving scroll, away from the main discharge outlet 510, contacts the outer profile 522 of the fixed scroll, the projection of the connecting hole 512 on the projection surface is covered by the projection of the passive scroll 42 on the projection surface. Figure 4 As shown, only after the moving vortex body 42 and the fixed vortex body 52 further engage will the connecting hole 512 be exposed in the outermost compression cavity, as shown. Figure 26 As shown, even if the enthalpy-increasing channel 100 replenishes gas into the compression chamber, the amount of gas originally drawn into the outermost compression chamber will not decrease due to leakage into the suction chamber because of the replenishment of gas into the enthalpy-increasing channel 100. This increases the exhaust volume. Furthermore, during the entire refrigerant compression process, replenishment of gas through the connecting hole 512 reduces the exhaust temperature and improves the heating capacity. In this embodiment, compared to the fixed vortex outer profile 522, the projection of the connecting hole 512 on the projection plane is closer to the fixed vortex inner profile 521, which helps to extend the service time of the connecting hole 512 during the engagement process between the moving vortex body 42 and the fixed vortex body 52.

[0066] In addition, when the compressor starts to compress the refrigerant, if there is liquid in the compression chamber, the liquid can be discharged to the exhaust chamber 300 in time through the connecting hole 512 to reduce liquid slugging. This avoids the problem of reduced structural strength caused by high-pressure liquid slugging during the subsequent compression of refrigerant by the moving scroll 4 and the fixed scroll 5. Therefore, the connecting hole 512 can realize the functions of gas replenishment and enthalpy increase, auxiliary unloading and liquid slugging prevention.

[0067] Please see Figure 16 and Figure 26In this embodiment, the fixed end plate 51 also has a secondary outlet 511, which communicates with the compression chamber V. The secondary outlet 511 is located radially outside the main outlet 510 and is located between the main outlet 510 and the connecting hole 512. In other words, on the projection plane, the distance L1 from the projection center of the connecting hole 512 to the projection center of the main outlet 510 is greater than the distance L2 from the projection center of the secondary outlet 511 to the projection center of the main outlet 510. The secondary outlet 511 penetrates the fixed end plate 51 along its thickness direction. Furthermore, the center of the secondary outlet 511 on the projection plane and the center of the connecting hole 512 on the projection plane are located on the same straight line, which facilitates the processing of the connecting hole 512 and the secondary outlet 511, eliminates the need for repeated positioning, and improves the processing efficiency of the fixed volute 5. In this embodiment, there are two connecting holes 512 and two secondary discharge outlets 511. The crescent-shaped compression cavities are formed in pairs. One of the connecting holes 512 is connected to one of the two compression cavities in the pair, and the other connecting hole 512 is connected to the other compression cavity in the pair. Similarly, one of the secondary discharge outlets 511 is connected to one of the two compression cavities in the pair, and the other secondary discharge outlet 511 is connected to the other compression cavity in the pair.

[0068] Please see Figure 22 and combined Figure 27 In this embodiment, the enthalpy-increasing channel 100 includes a fixed vortex channel 102, which is located within the fixed end plate 51. The fixed vortex channel 102 is at least partially arranged along a direction perpendicular to the thickness of the fixed end plate 51. The fixed vortex channel 102 includes a first channel segment 102a, at least one end of which extends beyond the outer wall surface of the fixed end plate 51, i.e., at least one end of the first channel segment 102a penetrates the outer wall surface of the fixed end plate 51. In this embodiment, there are two connecting holes 512 and two fixed vortex channels 102, with each connecting hole 512 connecting to one fixed vortex channel 102.

[0069] In one embodiment, the enthalpy-increasing channel 100 includes a cover channel 101 located on the cover 7. The enthalpy-increasing channel 100 also includes a connecting cavity 103 located between the cover 7 and the fixed scroll 5. Both the cover channel 101 and the fixed scroll channel 102 are connected to the connecting cavity 103. The compressor has an enthalpy-increasing channel inlet 70a, and the cover channel 101 is connected to the enthalpy-increasing channel inlet 70a. The enthalpy-increasing channel inlet 70a is located on the top wall of the cover 7, and the connecting cavity 103 is located between the end face of the fixed end plate 51 away from the compression cavity V and the cover 7; the fixed scroll channel 102 includes a first channel section 102a, which is at least partially arranged along a direction perpendicular to the thickness of the fixed end plate 51, and at least one end of the first channel section 102a extends out of the peripheral sidewall of the fixed end plate 51; the compressor includes a head 54, and the end of the first channel section 102a near the peripheral sidewall of the fixed end plate 51 is provided with a head 54; the fixed scroll channel 102 includes a second channel section 102b, which connects the first channel section 102a and the connecting cavity 103, and the second channel section 102b is arranged along the thickness direction of the fixed end plate 51. The compressor includes a one-way valve 200, which is at least partially located in the enthalpy-increasing channel 100. The one-way valve 200 allows the enthalpy-increasing channel 100 to be open from the inlet 70a to the connecting hole 512. In this embodiment, the arrangement of the enthalpy-increasing channel 100, the one-way valve 200, and the seal are the same as those in this embodiment. Figure 22 The implementation method shown is the same, and will not be described in detail here. In this implementation method, the opening of the connecting hole 512 facing the compression chamber is the enthalpy increase channel outlet 50b.

[0070] In another implementation, please refer to Figure 27The difference from the previous embodiment is that the enthalpy-increasing channel inlet 70a is located on the peripheral sidewall of the cover 7, and the connecting cavity 103 is located between the peripheral sidewall of the fixed end plate 51 and the cover 7. In the gas replenishment state, gas enters from the enthalpy-increasing channel inlet 70a into the connecting cavity 103 between the peripheral sidewall of the fixed end plate 51 and the cover 7, and then enters from the fixed vortex channel 102 into the connecting hole 512, and enters the compression chamber through the connecting hole 512 for gas replenishment. The first channel section 102a includes a first flow channel 102d and a second flow channel 102e. The first flow channel 102d connects the second flow channel 102e and the connecting hole 512, and the second flow channel 102e connects the first flow channel 102d and the connecting cavity 103. The cross-sectional area of ​​the first flow channel 102d is smaller than the cross-sectional area of ​​the second flow channel 102e. The cross-sectional area is defined as the area obtained by cutting off each flow channel with a surface perpendicular to the centerline direction of each flow channel. By reducing the cross-sectional area of ​​the first flow channel 102d, a throttling effect is achieved. In this embodiment, a sealing element is also provided. The sealing element is located between the cover 7 and the fixed vortex 5 (not shown in the figure). A sealing element is provided between the connecting cavity 103 and the exhaust cavity 300, and a sealing element is provided between the intake cavity S and the connecting cavity 103. The sealing elements isolate the connecting cavity 103 from the exhaust cavity 300 and from the intake cavity S, preventing the make-up gas used for enthalpy increase from mixing with the exhaust cavity 300 and the intake cavity S.

[0071] Please refer to it again. Figure 16 and Figure 25 and combined Figure 28 , Figure 29a and Figure 29b In this embodiment, the compressor includes a valve 700c, which is mounted on a fixed end plate 51 and is at least partially located in the exhaust chamber 300, covering the connecting hole 512. Additionally, the compressor includes a main exhaust valve 700a, which is mounted on the fixed end plate 51 and is at least partially located in the exhaust chamber 300, covering the main discharge outlet 510. The valve 700c and the main exhaust valve 700a are at least partially integral. Furthermore, the compressor includes a secondary exhaust valve 700b, which is mounted on the fixed end plate 51 and is at least partially located in the exhaust chamber 300, covering the secondary discharge outlet 511. The secondary exhaust valve 700b and the main exhaust valve 700a are at least partially integral.

[0072] In the above embodiments, valve 700c, main exhaust valve 700a, and auxiliary exhaust valve 700b can share the same exhaust valve 700, which is located in the exhaust chamber 300. Figure 25 and Figure 28As shown; they can also be independently configured. The exhaust valve 700 includes a lift limiter 701, a resilient valve plate 702, and a valve seat. The resilient valve plate 702 is located between the lift limiter 701 and the valve seat. The lift limiter 701 is at least partially a powder metallurgy part. In this embodiment, the valve seat is located on the fixed scroll 5. Further, the material of the lift limiter 701 is metal powder, which is processed by powder metallurgy. This embodiment also provides a lift limiter processing technology, including the following steps: providing metal powder and a mold; loading the metal powder into the mold; pressing the metal powder into a part with the shape of a lift limiter; and sintering the part in a closed furnace. The mold has the outline shape of a lift limiter, including a limiting surface forming surface for forming the limiting surface 705. The side opposite the limiting surface forming surface has an open structure to facilitate the loading of metal powder and pressing. After pressing, the side of the metal powder near the open surface forms a flat plane, and after sintering, a limiter end face 708 with a planar structure is obtained. Because powder metallurgy can press into a blank of the final size, it can be formed in one step with little or no secondary processing. The process is simple and convenient, saving processing time and costs, greatly saving metal materials, and reducing product costs.

[0073] In this embodiment, the exhaust valve also includes a positioning element 708. Both the lift limiter 701 and the elastic valve plate 702 have through holes 709, and the valve seat has a positioning hole 710. The positioning element 708 passes through the through hole 709 and connects to the valve seat, and the positioning element 708 is engaged with the positioning hole 710. Specifically, the positioning element 708 is a screw, and the positioning hole 710 is a threaded countersunk hole, with the positioning element 708 threadedly engaged with the positioning hole 710.

[0074] Furthermore, the lift limiter 701 includes a fixing part 703 and at least one limiting part 704, with the limiting part 704 and the fixing part 703 being an integral structure. The limiting part 704 has a limiting surface 705, which faces the elastic valve plate 702. There is a valve gap flow gap 706 between the limiting surface 705 and the valve seat. When the pressure in the compression chamber reaches a certain pressure, it will push open the elastic valve plate 702, and the refrigerant gas in the compression chamber will enter the exhaust chamber 300 through the valve gap flow gap 706. Furthermore, the thickness of the limiting portion 704 decreases in the direction away from the fixed portion 703. The limiting portion 704 includes a head 707, which is located at the end of the limiting portion 704 away from the fixed portion 703. The radius of curvature of the limiting surface 705 at the head 707 portion is ≥40mm. The limiting surface 705 adopts an arc-shaped design with a radius of curvature ≥40mm, which makes the elastic valve plate 702 have better motion characteristics and adapts to the motion law when the elastic valve plate 702 moves and hits the lift limiter 701. This results in low contact stress and a long service life of the elastic valve plate 702, so that the elastic valve plate 702 is in normal working condition during the compressor's refrigerant compression process, maintaining timely opening and closing to ensure the volumetric efficiency of the compressor, thereby improving the compressor's economy and reliability.

[0075] Furthermore, the lift limiter 701 includes a limiter end face 708, which is planar. The limiter end face 708 and the limiting surface 705 are opposite sides of the lift limiter 701 along the thickness direction. In this embodiment, the limiter end face 708 is designed as a planar surface, which facilitates processing and increases the thickness of the fixing part 703, thereby improving the structural strength of the lift limiter 701 on the side near the fixing part 703.

[0076] Furthermore, the lift limiters of valve 700c, main exhaust valve 700a, and auxiliary exhaust valve 700b are integrated into a single structure. Specifically, the limiting part 704 includes a first limiting part 704a, which defines a surface perpendicular to the thickness direction of the fixed end plate 51 as a projection surface. The projection of the first limiting part 704a on the projection surface covers the projection of the main exhaust outlet 510 on the projection surface. The limiting part 704 also includes a second limiting part 704b, whose projection on the projection surface covers the projection of the auxiliary exhaust outlet 511 on the projection surface. Finally, the limiting part 704 includes a third limiting part 704c, whose projection on the projection surface covers the projection of the connecting hole 512 on the projection surface.

[0077] Similarly, the elastic valve plates of valve 700c, main exhaust valve 700a, and auxiliary exhaust valve 700b are also an integral structure. Elastic valve plate 702 includes a first elastic plate 702a, located between the first limiting part 704a and the fixed end plate 51. The projection of the first limiting part 704a on the projection surface covers the projection of the main exhaust outlet 510 on the projection surface. Elastic valve plate 702 also includes a second elastic plate 702b, located between the second limiting part 704b and the fixed end plate 51. The projection of the second elastic plate 702b on the projection surface covers the projection of the auxiliary exhaust outlet 511 on the projection surface. Elastic valve plate 702 further includes a third elastic plate 702c, located between the third limiting part 704c and the fixed end plate 51. The projection of the third elastic plate 702c on the projection surface covers the projection of the connecting hole 512 on the projection surface.

[0078] By designing the lift limiters of valve 700c, main exhaust valve 700a, and auxiliary exhaust valve 700b into an integrated structure, and designing the elastic valve plates of valve 700c, main exhaust valve 700a, and auxiliary exhaust valve 700b into an integrated structure, the assembly of the exhaust valves is facilitated. The three exhaust valves only need to share the same set of positioning holes, avoiding the need to open too many positioning holes on the fixed end plate 51. The assembly is convenient and quick, while reducing structural damage to the fixed end plate 51 and ensuring the overall structural strength of the fixed end plate 51.

[0079] In this embodiment, on the projection plane, the projection center of the secondary outlet 511 and the projection center of the connecting hole 512 are on the same straight line. l Above, the projection center of the main exhaust outlet 510 is spaced L3 from the straight line l, and the projection center of the main exhaust outlet 510 is farther from the fixed part 703 than the projection center of the secondary exhaust outlet 511. As the main exhaust port, the valve clearance 706 at the location of the main exhaust outlet 510 directly affects the degree of exhaust pressure loss. If the projection center of the main exhaust outlet 510 is on the straight line l... l If the valve gap 706 at the main outlet 510 position is small, the valve gap flow area is small, and the pressure loss is large. However, by designing the length of the first limiting part 704a to be longer, the valve gap flow gap 706 can be guaranteed, thereby reducing the pressure loss.

[0080] In addition, to avoid the elastic valve plate being affected by factors such as the unevenness of the end face of the fixed end plate 51, and to prevent the elastic valve plate from being pushed up due to the protrusion of the end face and causing it to discharge before reaching a certain pressure, in this embodiment, the fixed end plate 51 is provided with an annular groove 51a on the end face facing the lift limiter 701. The main discharge outlet 510, the secondary discharge outlet 511, and the connecting hole 512 are all provided with an annular groove 51a on their radial outer sides, which helps to improve the closing degree of the elastic valve plate and ensure the volume ratio of the compressor.

[0081] The compressor provided in this embodiment can be used in air conditioning systems in various applications, such as automotive air conditioning systems. NVH (Noise, Vibration, Harshness) is a key indicator for measuring in-vehicle comfort and is increasingly valued by private car owners and automotive manufacturers. As a core component of the automotive air conditioning system, the compressor is a significant source of noise and vibration when it is running. The exhaust pulsation problem of scroll compressors is prominent, especially at low speeds and high loads. Vehicle idling NVH issues are often caused by exhaust pulsation, which is the main cause of scroll compressor noise. Related technologies incorporate mufflers within the compressor; however, installing the muffler requires additional components for fixation, complicating the installation process. To improve installation convenience, please refer to [link to relevant documentation]. Figure 3 and Figure 19 and combined Figures 30 to 32 In this embodiment, a muffler 600 is provided inside the cover 7. The cover 7 has an exhaust port 73. The muffler 600 is partially located in the exhaust port 73 and partially located in the exhaust chamber 300. The muffler 600 has a silencing chamber 601, which communicates with both the exhaust port 73 and the exhaust chamber 300. Specifically, the muffler 600 has at least one vent 602, which connects the silencing chamber 601 and the exhaust chamber 300. In this embodiment, the refrigerant gas discharged from the main outlet 510 directly enters the exhaust chamber 300. Since the amount of oil mixed in this part of the refrigerant gas is very small, oil separation is not required, therefore the compressor does not need to be equipped with an oil separation chamber. In this embodiment, by installing a muffler 600 in the exhaust chamber 300, the high-pressure refrigerant airflow from the compression chamber to the exhaust chamber 300 changes its acoustic impedance when passing through the muffler 600, and some of the sound energy is reflected back to the sound source. This reduces the transmitted sound energy and blocks the transmission of sound waves of some frequencies. By installing the muffler, exhaust pulsation noise is greatly reduced, and driving comfort is improved.

[0082] Furthermore, the muffler 600 has at least one vent 602, which connects the muffler cavity 601 and the exhaust cavity 300. High-pressure refrigerant gas flows through the vent 602 and enters the muffler cavity 601. In this embodiment, the total cross-sectional area of ​​the vents 602 is greater than or equal to the cross-sectional area of ​​the muffler cavity 601. The cross-sectional area is defined as the area obtained by cutting off each hole with a surface perpendicular to its centerline. Both the muffler cavity 601 and the vent 602 are circular holes. The muffler 600 and the exhaust cavity 300 form an internal Helmholtz muffler.

[0083] Furthermore, the exhaust valve 700 is located between the main exhaust outlet 510 and the vent hole 602. The high-pressure refrigerant gas discharged from the main exhaust outlet 510 enters the exhaust chamber 300 after passing through the exhaust valve 700, and then enters the silencer chamber 601 through the vent hole 602.

[0084] In this embodiment, the vent 602 is located on the wall of the muffler 600. At least one vent 602 is located on the end wall of the muffler 600, and / or, at least one vent 602 is located on the peripheral wall of the muffler 600. In some embodiments, the vent 602 is located on the end wall of the muffler 600, such as... Figure 3 and Figure 30 As shown, in order to ensure that the total cross-sectional area of ​​the vents 602 is greater than or equal to the cross-sectional area of ​​the silencer cavity 601, the number of vents 602 is one, and the diameter of the vent 602 is the same as the diameter of the silencer cavity 601. Airflow enters the silencer cavity 601 through the vent 602, and the airflow interacts within the cavity, reducing exhaust noise. In other embodiments, the peripheral wall of the muffler 600 has several vents 602, or both the peripheral wall and end wall of the muffler 600 have vents 602, such as... Figure 19 and Figure 31 As shown, the diameter of the vent 602 is much smaller than the diameter of the silencer 601. The silencer 600 itself forms a perforated silencer. When the airflow passes through the vent 602, the gas flows through this small hole, dispersing the gas resistance and reducing noise.

[0085] To facilitate the installation of the muffler 600, in this embodiment, one end of the exhaust port 73 penetrates the outer wall of the cover 7, and the other end of the exhaust port 73 penetrates the cavity wall of the exhaust chamber 300. In other words, before the muffler 600 is installed, the exhaust port 73 is connected to the exhaust chamber 300. When installing the muffler 600, it is simply pressed into the outer opening of the exhaust port 73. After installation, the center line of the exhaust port 73 coincides with the center line of the muffler 600. To facilitate the fixing of the muffler 600, at least a portion of the muffler 600 is press-fitted with the exhaust port 73, thereby achieving a tight connection between the muffler 600 and the cover 7. To facilitate the positioning of the muffler 600 during assembly and ensure proper installation, the inner wall of the exhaust port 73 has a shoulder 731. The muffler 600 includes a body 604 and a boss 605, with the boss 605 abutting against the shoulder 731. During assembly, the end of the main body 604 away from the boss 605 is pressed in through the outer opening of the exhaust port 73. When the boss 605 comes into contact with the shoulder 731, it indicates that the muffler 600 has been installed in place, thus avoiding problems of incomplete or over-assembly. Furthermore, one end of the body portion 604 is connected to the boss portion 605, and the body portion 604 extends to the exhaust chamber 300. A chamfer 603 is provided on the outer periphery of the end of the body portion 604 away from the boss portion 605. In this embodiment, by providing the chamfer 603, interference between the end of the body portion 604 and the outer opening of the exhaust port 73 is avoided during the assembly of the muffler 600, which would prevent the body portion 604 from being pressed in. This helps to improve the assembly efficiency of the muffler 600. In this embodiment, the chamfer 603 can be a rounded corner or a beveled corner.

[0086] In this embodiment, one end of the exhaust port 73 penetrates the outer wall of the cover 7, and the centerline of the exhaust port 73 is perpendicular to the centerline of the main exhaust outlet 510. In other words, the centerline of the muffler 600 is horizontally positioned. This allows full utilization of the horizontal space of the exhaust chamber 300, and the installation requirements of the muffler 600 can be met without increasing the lateral (horizontal) dimension of the cover 7, resulting in a compact structure. Of course, in other embodiments, one end of the exhaust port 73 can penetrate the top wall of the cover 7, that is, the centerline of the exhaust port 73 is parallel or collinear with the centerline of the main exhaust outlet 510. In other words, the centerline of the muffler 600 is vertically positioned.

[0087] In this embodiment, the compressor is arranged vertically, that is, the axis of the rotating shaft is along the vertical direction. Since most of the lubricating oil circulates in the space between the casing and the back of the moving scroll 4, only a small part will enter the compression chamber on the front of the moving scroll 4 to lubricate the mating parts between the moving scroll 4 and the fixed scroll 5. Therefore, there is no need to consider the oil separation problem. Thus, the compressor provided in this embodiment does not need to be equipped with an oil separator to separate the lubricating oil and refrigerant gas.

[0088] The compressor discharges high-pressure refrigerant gas from the exhaust port 73. To facilitate connection with external components (such as pipes connecting to a heat exchanger), the compressor includes an exhaust adapter 74, which comprises a pipe section 741 and a pressure plate section 742. The pipe section 741 is at least partially located within the exhaust port 73. The compressor also includes a sealing section 75, located between the outer wall of the pipe section 741 and the inner wall of the exhaust port 73. The pressure plate section 742 is connected to the outer wall of the cover 7. In this embodiment, the connection method is not specifically limited; it can be one or any combination of welding, fastener connection, snap-fit, adhesive, etc.

[0089] Some of the technical implementation methods described above can be combined or replaced.

[0090] The technical principles of this application have been described above in conjunction with 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. Based on this explanation, other specific embodiments or equivalent substitutions of this application 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 in that: The device includes a housing, a rotating shaft, a support component, and an oil-gas isolation cover. The support component is at least partially located inside the housing. The rotating shaft is connected to the support component. The support component includes a main bearing housing. The oil-gas isolation cover is connected to the main bearing housing. The main bearing housing is provided with an air supply channel. The support component has an oil return channel. The oil-gas isolation cover is located inside the housing. At least part of the oil-gas isolation cover is located between the air supply channel and the oil return channel. The compressor has a housing cavity, which includes a first inner cavity, and the first inner cavity includes a first sub-cavity and a second sub-cavity. The oil-gas isolation cover is located between the first sub-cavity and the second sub-cavity. The air supply channel communicates with the first sub-cavity, and the oil return channel communicates with the second sub-cavity. The oil-gas isolation cover has an air inlet and an air outlet. The housing has an air inlet, which includes an opening located on the inner wall of the housing. The air inlet is directly opposite the opening. The air inlet communicates with the first sub-cavity and the second sub-cavity, and the air outlet communicates with the first sub-cavity and the second sub-cavity.

2. The compressor according to claim 1, characterized in that: The air supply channel is connected to the air inlet, and there is a gap between the air inlet and the air supply channel; The compressor has a compression chamber, an intake chamber, and an oil storage chamber. The air supply channel is connected to the intake chamber, and the oil return channel is connected to the oil storage chamber. The intake chamber and the oil storage chamber are located on opposite sides of the oil-gas isolation cover along the axial direction of the rotating shaft. The compressor includes a moving scroll and a fixed scroll, the compression chamber is at least partially located between the moving scroll and the fixed scroll, the compressor includes a cover, the suction chamber is located around the compression chamber, and the suction chamber is at least partially located between the cover and the fixed scroll; the oil storage chamber is located inside the housing, and the oil storage chamber is disposed close to the bottom plate of the housing; The gas supply channels are multiple, and the multiple gas supply channels are distributed in a circular array with the center line of the main bearing housing as the center.

3. The compressor according to claim 2, characterized in that: The housing includes a base plate, and the vertical distance from the bottom end face of the oil and gas isolation cover to the inner end face of the base plate is less than the minimum vertical distance from the opening to the inner end face of the base plate. The oil-gas isolation cover has a gap between the end away from the main bearing seat and the inner wall of the housing, and the gap communicates with the oil storage chamber; the opening has a distance between it and the air supply channel. The oil and gas isolation cover has a ring-shaped structure and includes a connecting part and an extension part. The extension part is connected to the connecting part, and the connecting part is connected to the main bearing seat. In the direction from the main bearing housing toward the base plate, the diameter of at least a portion of the extension increases.

4. The compressor according to claim 3, characterized in that: The housing cavity includes a second cavity, and the first cavity communicates with the second cavity; the first cavity is closer to the support member than the second cavity. Both the first sub-cavity and the second sub-cavity are connected to the second inner cavity.

5. The compressor according to claim 4, characterized in that: The air outlet and the air inlet are spaced apart along the circumferential direction of the oil and gas isolation cover.

6. The compressor according to claim 4, characterized in that: The support includes a main bearing, and the rotating shaft is installed in conjunction with the main bearing housing through the main bearing; at least one of the main bearing housing and the main bearing has the oil return passage, the main bearing housing has a bearing housing cavity, and the oil return passage connects the bearing housing cavity and the second sub-cavity.

7. The compressor according to claim 6, characterized in that: The oil return path includes a channel located in the main bearing housing, which connects the inner cavity of the bearing housing and the second sub-cavity. Multiple channels are arranged in a circular array around the centerline of the main bearing housing. The channels are located on the outer side of the main bearing along the radial direction of the shaft. The main bearing is a rolling bearing, and the oil return path also includes the gap between the rolling elements in the main bearing.

8. The compressor according to claim 6, characterized in that: The compressor includes an eccentric part and a bearing component. The eccentric part is connected to the top of the rotating shaft. The eccentric part is installed in conjunction with the moving scroll through the bearing component. Both the eccentric part and the bearing component are located in the inner cavity of the bearing housing.

9. The compressor according to claim 6, characterized in that: The compressor includes a drive mechanism located in the second inner cavity and connected to a rotating shaft; The extension has an end bend that extends toward the drive mechanism; The second inner cavity includes an oil storage chamber located at the bottom of the second inner cavity, and the drive mechanism has an oil passage that communicates with the oil storage chamber.

10. The compressor according to claim 9, characterized in that: The drive mechanism includes a stator assembly and a rotor assembly. The oil passage includes a first oil passage and a second oil passage. The first oil passage passes through the rotor assembly from the main bearing housing toward the base plate. The second oil passage passes through the stator assembly from the main bearing housing toward the base plate. The second oil passage is located close to the inner wall of the housing.

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