A bearing lubrication flow channel structure of a scroll compressor and a compressor

Abstract

The application discloses a kind of bearing lubrication flow channel structures of scroll compressor, comprising: drive shaft includes drive shaft body, drive shaft body is equipped with eccentric part, sixth flow channel is equipped in eccentric part, and sixth flow channel is communicated with the gap between dynamic disc and eccentric sleeve;Drive shaft body is located in the outer side of eccentric part far from the one end of eccentric sleeve and is equipped with inclined holeThe inclined hole is directed to the power mechanism of compressor;Dynamic disc is located in the one side of bearing frame and is equipped with extension, the sliding bearing is equipped in the extension, the fifth flow channel is equipped on sliding bearing, and fifth flow channel is communicated with the gap between dynamic disc and eccentric sleeve;The structure of entire compressor is optimized in the application, the structure of each mechanism is optimized, lubricating medium flows to the inside of drive shaft body by fifth flow channel and sixth flow channel, then is sprayed outward from inclined hole, in this process not only lubrication is carried out to the components, bearing and drive shaft on the way, but also the lubrication can be realized to the one side of first bearing far from eccentric sleeve, to realize sufficient lubrication effect.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, and specifically relates to a bearing lubrication channel structure for a scroll compressor. Background Technology

[0002] Scroll compressors, as a type of highly efficient fluid machinery, are widely used in new energy vehicle air conditioning, central air conditioning, and heat pump systems due to their compact structure and stable operation. A scroll compressor consists of a stationary disc and a moving disc meshing together. During operation, the moving disc rotates around the center of the stationary disc, gradually pushing the gas-liquid mixture towards the central space between the moving and stationary discs. The volume of the gas-liquid mixture continuously decreases, and the pressure continuously increases, eventually reaching a high-temperature, high-pressure state. Finally, it is discharged from the exhaust port at the center of the stationary disc and then exits through the exhaust channel on the casing to the outside of the compressor. However, existing scroll compressors still have the following problems during operation: 1. During the operation of a scroll compressor, lubrication is usually required for the components to operate better. However, due to the unreasonable lubrication channels in the existing compressor structure, some components may not be lubricated or may not be lubricated sufficiently during operation. This will seriously affect the working performance of the various components in the compressor and may even seriously affect the service life of the components. 2. During compressor operation, the temperature of the stator windings continuously rises. If the heat cannot be dissipated in time, the excessively high stator temperature may cause the insulation layer to age or even burn out the motor. Therefore, a good heat dissipation design is crucial for protecting the stator. Currently, most compressors use heat dissipation slots on the casing, but these slots are narrow and have a small heat dissipation area, which seriously affects the heat dissipation effect of the stator and even the entire compressor cavity. Therefore, solving the internal lubrication problem of the compressor is urgent. 3. During operation, the scroll compressor generates periodic gas pulsations and mechanical excitation forces due to the gas compression cycle between the moving and stationary scrolls. These excitation forces are transmitted to the compressor housing. The compressor housing and the internal stationary scroll assembly are typically made of metal and possess specific structural modes. When the frequency of the excitation force approaches or falls within a certain natural frequency of the housing / stationary scroll assembly, resonance occurs. During this process, the vibration amplitude of the structure is drastically amplified, causing severe vibration of the housing wall and radiating low-frequency "roaring" or mid-to-high-frequency "whistling" sounds into the surrounding environment, increasing noise pollution in the working environment. 4. During the exhaust process, the exhaust valve plate will be pushed open by the exhaust hole on the static plate. If the exhaust valve plate is opened too much, it is easy to deform or even break, which will seriously affect its service life. Therefore, a limiter is set above it. The airflow continuously pushes the exhaust valve plate open, and a popping noise will be generated between it and the limiter, which will affect the working environment. In conclusion, the heat dissipation and noise reduction issues of scroll compressors still need to be addressed. Summary of the Invention

[0003] Purpose of the invention: In order to overcome the above shortcomings, the purpose of this invention is to provide a bearing lubrication channel structure for a scroll compressor. Its structure is reasonably designed. By optimizing the structure of the entire compressor and the structure of each mechanism, a lubrication channel is formed, which can lubricate the components along the path, as well as the first bearing and the eccentric sleeve. This effectively solves the problem that many components cannot be lubricated in a timely manner in the prior art.

[0004] Technical solution: In order to achieve the above objectives, the present invention provides a bearing lubrication channel structure for a scroll compressor, comprising: a drive shaft, the drive shaft comprising a drive shaft body, an eccentric portion provided on the drive shaft body, one end of the eccentric portion extending away from the drive shaft body into an eccentric sleeve, and a sixth flow channel provided in the eccentric portion, the sixth flow channel communicating with the gap between the moving disc and the eccentric sleeve; Furthermore, the drive shaft body has an oblique through hole on the outer side of the eccentric part away from the eccentric sleeve, and the outlet of the oblique through hole faces the first bearing side; It also includes a moving plate, which has an extension on one side of the bearing frame. The extension has a sliding bearing, and the sliding bearing has a fifth flow channel, which communicates with the gap between the moving plate and the eccentric sleeve. The lubricating medium after the gas-liquid mixture is separated enters from the fifth flow channel. After passing through the fifth flow channel, it enters the gap between the moving plate and the eccentric sleeve to lubricate both. During this process, the oil flows through the sixth flow channel to the interior of the drive shaft body and is sprayed outward from the oblique perforation. In this process, not only is the drive shaft lubricated, but oil can also be sprayed onto the side of the first bearing away from the eccentric sleeve to achieve sufficient lubrication.

[0005] Furthermore, it also includes a stationary disc, which has at least one exhaust hole. An end cover is located on the outer side of the stationary disc, and an inner ring frame is located inside the end cover. The inner ring frame divides the cavity between the end cover and the stationary disc into a first cavity and a second cavity. A bearing frame is located on the side of the stationary disc away from the end cover, and a first bearing is located within the bearing frame. The first bearing is mounted on a drive shaft, and an eccentric sleeve is located on the drive shaft on one side of the first bearing. The eccentric sleeve is connected to the moving disc. A lubrication channel for the movement of the lubricating medium is provided between the stationary disc, the end cover, and the bearing frame. After the mixture in the first cavity is separated into gas and liquid, the lubricating medium flows through the lubrication channel to the first bearing and the eccentric sleeve, lubricating the components along the path, as well as the first bearing and the eccentric sleeve. The scroll compressor bearing lubrication channel structure described in this invention optimizes the entire compressor structure and the structure of each mechanism to form a lubrication channel, enabling it to lubricate the components along the path, as well as the first bearing and the eccentric sleeve. This effectively solves the problem of many components not being lubricated in a timely manner or being insufficiently lubricated in the prior art.

[0006] The stationary plate has a first flow channel on one side of the end cap, and the outer side of the first flow channel communicates with the second cavity. The end face of the stationary plate has a second flow channel on the outer side of the second cavity, and the second flow channel communicates with the second cavity. The stationary plate also has a first lower flow channel hole on the second flow channel, and the first lower flow channel hole communicates with the third flow channel on the stationary plate.

[0007] Furthermore, the bearing bracket is provided with a second flow channel hole on one side of the stationary plate. The second flow channel hole communicates with the third flow channel, and the surface of the bearing bracket is provided with a fourth flow channel that communicates with the second flow channel hole. The fourth flow channel extends to the groove on the inner side of the bearing bracket, which can deliver lubricating gas to the first bearing and the eccentric sleeve for lubrication.

[0008] More preferably, the bearing housing is provided with a partition inside, with the first bearing and the eccentric sleeve located on both sides of the partition. After the lubricating medium flows into the interior of the bearing housing through the fourth flow channel, it is diverted to both sides by the partition to lubricate the first bearing and the eccentric sleeve respectively.

[0009] Furthermore, the first flow channel is inclined toward one side of the second cavity.

[0010] The compressor described in this invention has a power mechanism including a housing, the housing having at least one air inlet, the housing being divided into a first cavity and a second cavity by a partition, the partition in the second cavity having at least one flow channel guide for guiding airflow, the flow channel guide forming a flow channel with the partition sidewall and the mounting part, and the air inlet being located on the air inlet side of the flow channel. At least one heat dissipation component is provided on the partition plate at the air outlet end of the flow channel. The flow guide component inside the housing can effectively guide the gas entering through the air inlet, improving its heat dissipation effect. After passing through the flow channel, the gas from the air inlet reaches the heat dissipation component, which can simultaneously dissipate heat in the first and second cavities of the housing.

[0011] Furthermore, the heat dissipation assembly includes a first heat dissipation component and a second heat dissipation component, which are disposed front and rear on a partition; the height of the second heat dissipation component is higher than the height of the first heat dissipation component. The second heat dissipation component being higher than the first heat dissipation component allows it to not only meet the heat dissipation requirements but also to act as a flow deflector, preventing gas from directly blowing onto the three-phase terminals and thus preventing impact on the three-phase terminals, which could lead to insulation abnormalities.

[0012] Preferably, the housing has protrusions on its inner wall for contacting and engaging with the stator. Heat dissipation channels for the flow of heat dissipation medium are provided between the protrusions, and the area ratio of the heat dissipation channels to the protrusions is 1:4. By optimizing the structure of the inner wall of the housing, heat from the stator is transferred to the protrusions inside the housing during operation. The heat dissipation medium in the heat dissipation channels carries away the heat from the stator and the protrusions. By changing the area ratio of the protrusions contacting the stator to the heat dissipation channels, the stator mounting area is increased, effectively improving the heat dissipation effect on the stator, preventing excessive stator temperature, and ensuring its operating efficiency.

[0013] As can be seen from the above technical solution, the present invention has the following beneficial effects: 1. The scroll compressor bearing lubrication channel structure described in this invention optimizes the structure of each component to form a reasonable lubrication channel inside the compressor. After the mixture in the first cavity is separated into gas and liquid, the lubricating gas is located in the upper part of the first cavity and flows through the lubrication channel to the position of the first bearing and the eccentric sleeve. The lubricating medium enters from below the fifth channel, and after passing through the fifth channel, it enters the gap between the moving disc and the eccentric sleeve to lubricate both. During this process, the lubricating medium flows through the sixth channel to the interior of the moving shaft body and is sprayed outward from the oblique perforation. This allows it to not only lubricate the drive shaft during compressor operation but also spray oil onto the side of the first bearing away from the eccentric sleeve, achieving sufficient lubrication. This greatly improves the internal lubrication effect of the compressor, ensures its working performance, and avoids the impact of high temperature on its working performance or even damage to components.

[0014] 2. The flow channel guide described in this invention can effectively guide the gas entering through the air inlet. After passing through the flow channel, the gas reaches the heat dissipation component. The heat dissipation component can simultaneously dissipate heat in the first and second cavities of the housing, effectively improving its heat dissipation effect.

[0015] 3. The height of the second heat sink is higher than that of the first heat sink. The higher height of the second heat sink not only meets the heat dissipation requirements but also acts as a flow deflector, preventing gas from directly blowing onto the three-phase terminals and thus preventing impact on the terminals that could lead to insulation abnormalities.

[0016] 4. This invention improves the rigidity of the shell by setting cross-arranged reinforcing ribs on the rear cover, thereby increasing its natural frequency, which is different from the exhaust frequency, reducing resonance and achieving a good noise reduction effect; the setting of connecting ribs further strengthens the rigidity of the shell and increases its natural frequency.

[0017] 5. The present invention limits the opening position of the exhaust valve plate by setting a limiting member on the exhaust valve plate of the stationary disc, so as to avoid its deformation or bending. Furthermore, the noise reduction unit on the limiting member can reduce the noise during the exhaust process.

[0018] 6. The conical orifice is designed to gradually expand from bottom to top. As the gas flows out, the channel gradually widens, which helps to reduce the airflow speed, smooth the airflow, reduce eddies, and effectively reduce aerodynamic noise caused by high-speed airflow impact. Attached Figure Description

[0019] Figure 1 This is a partial structural schematic diagram of the bearing lubrication channel structure of the scroll compressor described in this invention; Figure 2 This is a partial schematic diagram of the lubrication flow channel in the drive shaft section of the present invention; Figure 3 This is a partial schematic diagram of the flow channel on the bearing bracket in this invention; Figure 4 This is a schematic diagram of the structure of the moving disk and the sliding bearing in this invention; Figure 5 This is a cross-sectional view of the drive shaft in this invention; Figure 6 This is a schematic diagram of the bearing lubrication channel structure of the scroll compressor in this invention; Figure 7 This is a schematic diagram of the compressor structure in this invention; Figure 8 This is a cross-sectional view of the compressor in this invention; Figure 9 This is a schematic diagram of the compressor stator heat dissipation structure in this invention. Figure 10 This is a schematic diagram of the stator installed inside the housing in this invention; Figure 11 This is a cross-sectional view of the interior of the shell in this invention; Figure 12 This is a top view of the housing in this invention; Figure 13This is a schematic diagram of the static disk in this invention; Figure 14 This is a schematic diagram of the vent hole on the stationary disk in this invention; Figure 15 This is a schematic diagram of the structure of the exhaust valve plate in this invention; Figure 16 This is a schematic diagram of the limiting component in this invention; Figure 17 This is a schematic diagram of the limiting component from another perspective in this invention; Figure 18 This is a schematic diagram of the noise reduction structure of the scroll compressor scroll housing in this invention; Figure 19 This is a schematic diagram of the internal structure of the vortex disk shell in this invention; Figure 20 This is a cross-sectional view of the vortex disk and the shell in this invention; Figure 21 In this invention Figure 20 A magnified view of a portion of point A in the middle. Detailed Implementation

[0020] The present invention will be further explained below with reference to the accompanying drawings and specific embodiments.

[0021] Example 1 Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0022] like Figure 1 and Figure 2 The illustrated bearing lubrication channel structure of a scroll compressor includes a stationary disc 2 with at least one exhaust port 21. An end cover 5 is located on the outer side of the stationary disc 2, and an inner ring frame 5021 is located inside the end cover 5. The inner ring frame 5021 divides the cavity between the end cover 5 and the stationary disc 2 into a first cavity 5011 and a second cavity 5012. A bearing frame 3 is located on the side of the stationary disc 2 away from the end cover 5, and a first bearing 6 is located within the bearing frame 3. The first bearing 6 is mounted on a drive shaft 7, and an eccentric sleeve 8 is located on the side of the drive shaft 7 opposite to the first bearing 6. The eccentric sleeve 8 is connected to a moving disc 9. A lubrication channel for the movement of the lubricating medium is provided between the stationary disc 2, the end cover 5, and the bearing frame 3. After the mixture in the first cavity 5011 is separated into gas and liquid, the gas is located at the upper part of the first cavity 5011. The lubricating medium (separated lubricating oil) flows through the lubrication channel to the positions of the first bearing 6 and the eccentric sleeve 8, lubricating the components along the path and the first bearing 6 and the eccentric sleeve 8.

[0023] It should be noted that the first chamber 5011 contains a gas-liquid mixture (refrigeration oil and refrigerant), and the second chamber 5012 contains refrigeration oil. During operation... like Figures 1 to 3 as well as Figure 4 The illustrated scroll compressor bearing lubrication channel structure includes: a drive shaft 7, the drive shaft 7 including a drive shaft body, the drive shaft body having an eccentric portion 71, one end of the eccentric portion 71 away from the drive shaft body extending into an eccentric sleeve 8, and the eccentric portion 71 having a sixth flow channel 711, the sixth flow channel 711 communicating with the gap between the moving plate 9 and the eccentric sleeve 8; Furthermore, the drive shaft body is provided with an oblique through hole 701 on the outer side of the eccentric part 71 away from the eccentric sleeve 8, and the outlet of the oblique through hole 701 faces the first bearing 6. It also includes a moving plate 9, which has an extension on one side of the bearing frame 3. A sliding bearing 91 is provided in the extension. A fifth flow channel 911 is provided on the sliding bearing 91, and the fifth flow channel 911 communicates with the gap between the moving plate 9 and the eccentric sleeve 8. During operation, the drive shaft 7 drives the eccentric sleeve 8 to rotate continuously. During this process, the lubricating medium after the gas-liquid mixture is separated enters from the fifth flow channel 911 and enters the gap between the moving plate 9 and the eccentric sleeve 8 to lubricate both. During this process, the oil flows through the sixth flow channel 711 to the interior of the drive shaft body and flows outward from the oblique through hole 701. This process not only lubricates the drive shaft but also lubricates the first bearing 6.

[0024] In this embodiment, the tilt angle of the oblique through-hole 701 is preferably 30°~60° to ensure that the outlet of the oblique through-hole 701 faces the direction of the first bearing. Therefore, when the lubricating oil flows into the interior of the drive shaft body through the sixth flow channel 711 and is sprayed out from the oblique through-hole 701, it will be sprayed onto the first bearing 6, ensuring that the first bearing 6 is continuously lubricated by the lubricating oil. It should be noted that the tilt angle of the oblique through-hole 701 is less than 90° to ensure that the oil outlet direction is towards the first bearing 6. In actual use, the tilt angle can be adjusted according to the actual working conditions. Example 2 The bearing lubrication channel structure of the scroll compressor described in this embodiment is the same as that in Embodiment 1, such as... Figures 1 to 3The stationary disk 2 shown has a first flow channel 201 on one side of the end cap 5. The outer side of the first flow channel 201 communicates with the second cavity 5012. The end face of the stationary disk 2 has a second flow channel 202 on the outer side of the second cavity 5012, and the second flow channel 202 communicates with the second cavity 5012. Furthermore, the stationary disk 2 has a first lower flow channel hole on the second flow channel 202, and the first flow channel hole communicates with a third flow channel 203 on the stationary disk 2. Figure 14 As shown.

[0025] like Figure 3 The bearing housing 3 shown has a second flow channel hole 31 on one side of the stationary plate 2. The second flow channel hole 31 communicates with the third flow channel 203. The surface of the bearing housing 3 also has a fourth flow channel 32 communicating with the second flow channel hole 31. The fourth flow channel 32 extends to a groove on the inner side of the bearing housing 3, enabling the delivery of lubricating gas to the first bearing 6 and the eccentric sleeve 8 for lubrication. The aforementioned first flow channel 201, second flow channel 202, third flow channel 203, and fourth flow channel 32 constitute a lubrication channel for lubricating the components along the path, as well as the first bearing 6 and the eccentric sleeve 8.

[0026] The first flow channel 201, the second flow channel 202, the third flow channel 203, the fourth flow channel 32, the fifth flow channel 911, the sixth flow channel 711, and the oblique through hole 701 constitute a lubrication flow channel for lubricating the passing components and the other side of the first bearing 6 away from the eccentric sleeve 8.

[0027] It should be noted that a gas-liquid mixture (refrigeration oil and refrigerant) is provided in the cavity between the compressor stationary plate 2 and the rear cover 5. During operation, the gas and liquid in the cavity will be separated. The gas will rise and the liquid will be at the bottom. The oil is pressed upward by the high pressure located at the bottom of the second flow channel 202, and the lubricating oil is pressed to the upper part of the second flow channel 202. It flows into the third flow channel 203 through the first lower flow channel hole located at the top of the second flow channel 202. After passing through the second flow channel hole 31, the lubricating oil flows into the fourth flow channel 32 through the third flow channel 203. After flowing into the interior of the bearing bracket 3 through the fourth flow channel 32, the lubricating medium is divided to both sides by the separator 301 to lubricate the first bearing 6 and the eccentric sleeve 8 respectively. The lubricating medium passing through the eccentric sleeve 8 enters through the oil inlet side of the fifth flow channel 911. After passing through the fifth flow channel 911, it enters the gap between the moving plate 9 and the eccentric sleeve 8 to lubricate both. During this process, the lubricating medium flows through the sixth flow channel 711 to the interior of the moving shaft body and flows outward from the oblique through hole 701. In this process, not only is the drive shaft lubricated, but the lubricating oil can also be sprayed onto the side of the first bearing 6 away from the eccentric sleeve 8 to lubricate the first bearing 6, thereby ensuring sufficient lubrication of the first bearing 6.

[0028] As shown in the figure, the first flow channel 201 is inclined toward the second cavity 5012, and the cross-sections of the first flow channel 201 and the second flow channel 202 are not on the same plane. With the first flow channel 201 inclined toward the second cavity 5012 and facing inward toward the second cavity 5012, during operation, the direction of the high-speed mixture impacting the refrigeration oil will change along the inclined direction of the first flow channel 201, which is more conducive to the refrigeration oil flowing out from the second flow channel 202.

[0029] The bearing housing 3 is provided with a partition 301 inside. The first bearing 6 and the eccentric sleeve 8 are located on both sides of the partition 301. After the lubricating medium flows into the interior of the bearing housing 3 through the fourth flow channel 32, it is divided to both sides by the partition 301 to lubricate the first bearing 6 and the eccentric sleeve 8 respectively.

[0030] In a further preferred embodiment, the first flow channel 201 is inclined toward the side of the second cavity 5012.

[0031] Example 3 like Figures 8 to 12 The power mechanism 1 shown includes a housing 11, which has at least one air inlet 111. The housing 11 is divided into a third cavity and a fourth cavity by a partition 13. The partition 13 located in the second cavity has at least one flow channel guide 131 for guiding airflow. The flow channel guide 131 forms a flow channel with the side wall of the partition 13 and the mounting part. The air inlet 111 is located on the air inlet side of the flow channel. At least one heat dissipation component 132 is provided on the air outlet end of the flow channel on the partition 13. During operation, after the gas enters the fourth cavity of the housing 11 from the air inlet 111, it smoothly turns and is blown onto the heat dissipation component 132 after passing through the flow channel guide 131, the side wall of the partition 13, and the mounting part to form a flow channel. The heat dissipation component 132 dissipates heat from the fourth cavity. Since the heat dissipation component 132 is located on the partition 13, it also dissipates heat from the partition 13 and the third cavity during the heat dissipation process.

[0032] A further preferred embodiment is as follows: Figure 10 and Figure 11 The heat dissipation assembly 132 shown includes a first heat dissipation component 1321 and a second heat dissipation component 1322, which are disposed on the partition 13 one after the other; the height of the second heat dissipation component 1322 is higher than the height of the first heat dissipation component 1321.

[0033] A further preferred embodiment is as follows: Figure 9The housing 11 shown has a protrusion 1101 on its inner wall for contacting and engaging with the stator 4. A heat dissipation channel 1102 for the flow of heat dissipation medium is provided between the protrusions 1101. The area ratio of the heat dissipation channel 1102 to the protrusion 1101 is 1:4.

[0034] In addition, it includes three-phase terminals 14, which are mounted on the partition 13. The three-phase terminals are an essential component inside the compressor. In existing compressors, the gas entering through the inlet blows directly onto the three-phase terminals, easily causing dust and other contaminants in the gas to be blown towards and accumulate on the surface of the terminals. If the temperature of the airflow blowing onto the terminals is much lower than the temperature of the terminals, condensation may also occur on the surface, directly leading to a sharp drop in insulation resistance and causing insulation abnormalities.

[0035] A further preferred embodiment is as follows: Figure 11 The height of the second heat sink 1322 is higher than that of the first heat sink 1321. The second heat sink 1322 not only provides excellent heat dissipation, but also effectively blocks airflow, preventing airflow from directly blowing onto the three-phase terminals 14 and affecting their insulation.

[0036] In a further preferred embodiment, the air inlet 111 is located on the side of the housing 11 away from the three-phase terminal 14 to prevent the air intake of the flow channel from directly blowing onto the three-phase terminal 14.

[0037] In a further preferred embodiment of this invention, a set of grooves 1103 are provided on the protrusion 1101 inside the housing 11. The grooves 1103 are arranged perpendicularly to the heat dissipation channel 1102 and cooperate with the outer wall of the stator 4.

[0038] A further preferred embodiment is as follows: Figure 12 The flow guide 131 shown is arc-shaped. The arc-shaped flow guide 131 can guide the airflow to smoothly change direction, lower the flow group, and guide the airflow to the heat dissipation component 132, thereby improving its heat dissipation efficiency.

[0039] In the preferred embodiment, the flow channel guide 131 is made of aluminum alloy. It serves both as a flow guide and a heat dissipation component, further improving the overall heat dissipation effect.

[0040] The partition 1 has a groove, and the heat dissipation component 132 is disposed in the groove. The groove further optimizes its structure.

[0041] In a further preferred embodiment of this example, the partition 1 has a groove, and the heat dissipation assembly 132 is disposed within the groove. The groove further optimizes the structure.

[0042] In a further preferred embodiment, the partition 13 is provided with a heat sink 12 for heat dissipation of the controller SIC module on the side away from the fourth cavity. It should be noted that the heat sink 12 and the heat dissipation assembly 132 are disposed opposite each other on both sides of the partition 13. In this embodiment, the heat sink 12 is preferably a silicone thermal pad. When the gas used for heat dissipation enters the cavity and dissipates heat from the fourth cavity and the partition, the silicone thermal pad can effectively dissipate the heat, thereby achieving a better heat dissipation effect. It should be noted that other heat sinks 12 that can meet the heat dissipation requirements can also be selected according to actual needs.

[0043] like Figure 8 As shown, the housing 11 is equipped with a fan in the third cavity, which can powerfully exhaust the heat inside the housing from the outlet when it is working.

[0044] During operation, gas enters the second cavity of the housing 11 through the air inlet 111, smoothly changes direction after passing through the flow channel guide 131, the side wall of the partition 13, and the mounting part, and is then blown onto the heat dissipation assembly 132. The heat dissipation assembly 132 dissipates heat from the fourth cavity. Since the heat dissipation assembly 132 is located on the partition 13, heat dissipation is simultaneously transferred to the heat dissipation component 12 located in the third cavity for further cooling. The heat dissipation component 12 provides timely heat dissipation for the controller SIC module, enabling efficient operation and preventing overheating that could lead to performance degradation or even device damage.

[0045] Example 4 like Figures 13 to 17 An exhaust valve plate 22 is provided on one side of the exhaust port 21 on the static plate 2 shown. A limiting member 23 is provided on the outer side of the exhaust valve plate 22. The exhaust valve plate 22 and the limiting member 23 are connected to the static plate 2 via a connector 24, and a noise reduction unit 25 is provided on the limiting member 23. In this embodiment, the noise reduction unit 25 can be selected according to actual needs. Preferably, the noise reduction unit 25 is a sound-insulating pad with sound insulation effect. When the gas in the cavity blows open the exhaust valve plate 22, the sound-insulating pad can effectively reduce the popping sound generated by the contact between the exhaust valve plate 22 and the limiting member 23.

[0046] Further preferred embodiments in the examples, such as Figure 14 The exhaust valve plate 22 includes a valve plate connecting part 221, the valve plate connecting part 221 is provided with a first mounting hole, and at least one extended valve plate 222 is provided on one side of the connecting rib 221. The extended valve plate 222 is provided in a one-to-one correspondence with the exhaust hole 21, and the two cooperate with each other.

[0047] Further preferred embodiments in the examples, such as Figure 15 ,16 The limiting member 23 shown includes a limiting connection part 231, which has a second mounting hole, and at least one limiting piece 232 is provided on one side of the limiting connection part 231. The limiting piece 232 is provided in a one-to-one correspondence with the extension valve piece 222. The connecting member 24 passes through the second mounting hole on the limiting connection part 231 and the first mounting hole on the valve piece connection part 221 in sequence and then connects to the mounting hole on the stationary plate 2.

[0048] Further preferred embodiments in the examples, such as Figure 14 The exhaust port 21 shown includes a first exhaust port 211, a second exhaust port 212, and a third exhaust port 213, all of which are located on the stationary plate 2. The first exhaust port 211 is a conical hole with a boss 2111 on its upper part and an annular groove 2112 on the outer side of the boss 2111. The second exhaust port 212 and the third exhaust port 213 have countersunk holes on their outer sides. The first exhaust port 211, the second exhaust port 212, and the third exhaust port 213 can improve the exhaust effect. The first exhaust port 211 adopts a conical hole design, which is gradually expanding from bottom to top. The channel gradually widens as the gas flows out, which helps to reduce the airflow velocity, smooth the airflow, reduce turbulence, and effectively reduce the aerodynamic noise generated by the impact of high-speed airflow. The boss and the annular groove can provide good support for the exhaust valve plate, reduce its contact area with the exhaust port, and effectively reduce the opening resistance of the exhaust valve plate during the exhaust process. It is conceivable that other suitable exhaust ports can be selected according to actual needs, as long as they can meet the exhaust requirements.

[0049] In a further preferred embodiment, a recess 2011 is provided on the stationary disc 2 on one side of the exhaust port. The recess 2011 reduces the contact area between the exhaust valve plate and the stationary disc 2.

[0050] In a further preferred embodiment, the width of the boss 2111 is 1~2mm. The taper of the first vent 211 is preferably in the range of 45°~65°. It is conceivable that the width of the boss 2111 and the taper of the first vent 211 can be adjusted according to actual needs.

[0051] Example 5 like Figures 18 to 21The end cap 5 shown has reinforcing ribs 51 on its outer side, which are arranged in a crisscross pattern. A set of connecting ribs 52 is provided on the end cap 5, positioned between adjacent sets of reinforcing ribs 51, with the ribs crossing at an angle of 120°~150°. The reinforcing ribs 51 and connecting ribs 52 on the end cap 5 effectively improve its stiffness and strength, increasing the natural frequency of the shell and making it different from the exhaust frequency, thereby reducing resonance and achieving a good noise reduction effect. It should be noted that stiffness is the material's ability to resist elastic deformation, characterized in engineering by Young's modulus of elasticity E; the higher the value, the smaller the deformation under the same force. The changed natural frequencies are 1700Hz (1st order) to 7800Hz (10th order), while the exhaust frequency is 800Hz to 1700Hz; the goal is to ensure that the natural frequency of the shell is not the same as the exhaust frequency. Furthermore, even in extreme situations during use, the presence of other components can further prevent resonance between the two.

[0052] One preferred embodiment is shown in the examples. Figure 18 The end cap 5 shown includes a first housing 501 and a second housing 502. The second housing 502 is located above the first housing 501, and the two have different diameters. A second reinforcing rib 503 is provided at the connection between the second housing 502 and the first housing 501. The provision of the second reinforcing rib 503 further improves the overall strength and rigidity of the end cap, further increases its natural frequency, and further enhances its noise reduction effect.

[0053] Further preferred embodiments are as follows: Figures 20 to 21 The connection between the second housing 502 and the first housing 501 shown has a step inside, the end face of the step matches the outer end face of the stationary plate 2, and a sealing element 504 is provided between the two.

[0054] Further preferred embodiments are described in the examples, such as... Figures 19 to 21 The second housing 502 shown has a reinforcing ring 5021 on the inner side of its top, and an inner ring frame 5022 is provided between the reinforcing ring 5021 and the inner wall. A third reinforcing rib 505 is provided between the inner ring frame 5022 and the reinforcing ring 5021 and the side wall of the second housing 502.

[0055] The addition of reinforcing ring 5021, inner ring frame 5022, and third reinforcing rib 505 further enhances the strength and rigidity of the end cap, increases its natural frequency, and thus further improves its noise reduction effect.

[0056] The stationary disk 2 is provided with a gas flow channel, and the lower part of the inner ring frame 5022 is located within the gas flow channel. The cooperation between the inner ring frame 5022 and the stationary disk 2 effectively improves the stability of the installation of the stationary disk 2 and the end cover, and reduces resonance.

[0057] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements can be made without departing from the principle of the present invention, and these improvements should also be considered within the scope of protection of the present invention.

Claims

1. A bearing lubrication channel structure for a scroll compressor, characterized in that: include: The drive shaft (7) includes a drive shaft body, on which an eccentric part (71) is provided. One end of the eccentric part (71) away from the drive shaft body extends into the eccentric sleeve (8), and a sixth flow channel (711) is provided in the eccentric part (711). The sixth flow channel (711) communicates with the gap between the moving plate (9) and the eccentric sleeve (8). Furthermore, the drive shaft body is provided with an oblique through hole (701) on the outer side of the eccentric part (71) away from the eccentric sleeve (8), and the outlet of the oblique through hole (701) faces the first bearing (6). It also includes a moving plate (9), which has an extension on one side of the bearing frame (3). The extension has a sliding bearing (91) and a fifth flow channel (911) on the sliding bearing (91). The fifth flow channel (911) communicates with the gap between the moving plate (9) and the eccentric sleeve (8). The lubricating medium after the gas-liquid mixture is separated enters through the fifth flow channel (911). After passing through the fifth flow channel (911), it enters the gap between the moving plate (9) and the eccentric sleeve (8) to lubricate both. During this process, the oil flows through the sixth flow channel (711) to the interior of the drive shaft body and flows outward from the oblique through hole (701). In this process, not only is the drive shaft lubricated, but the side of the first bearing (6) away from the eccentric sleeve (8) is also lubricated.

2. The scroll compressor bearing lubrication channel structure according to claim 1, characterized in that: It also includes a stationary plate (2), which has at least one vent hole (21). An end cap (5) is provided on the outer side of the stationary plate (2). An inner ring frame (5021) is provided inside the end cap (5). The inner ring frame (5021) divides the cavity between the end cap (5) and the stationary plate (2) into a first cavity (5011) and a second cavity (5012). A bearing frame (3) is provided on the side of the stationary plate (2) away from the end cap (5). The moving plate (9) is located on the side of the bearing frame (3) located on the stationary plate (2) and cooperates with the stationary plate (2). A first bearing (6) is provided inside the bearing frame (3). An eccentric sleeve (8) is provided on the drive shaft (7) and on the side of the first bearing (6) on the drive shaft (7). The eccentric sleeve (8) is connected to the moving disk (9). A lubrication channel for medium movement is provided between the stationary disk (2), the end cover (5) and the bearing bracket (3). When the gas-liquid mixture in the first cavity (5011) passes through the narrow channel, the oil will separate from the gas under the action of gravity due to its higher specific gravity. The gas is located in the upper part of the first cavity (5011) and flows through the lubrication channel to the position of the first bearing (6) and the eccentric sleeve (8) to lubricate the components along the way as well as the first bearing (6) and the eccentric sleeve (8).

3. The scroll compressor bearing lubrication channel structure according to claim 1, characterized in that: The stationary plate (2) is provided with a first flow channel (201) on one side of the end of the end cap (5). The outer side of the first flow channel (201) is connected to the second cavity (5012). The end face of the stationary plate (2) is provided with a second flow channel (202) on the outer side of the second cavity (5012). The second flow channel (202) is connected to the second cavity. The stationary plate 2 is provided with a first lower flow channel hole on the second flow channel 202. The first lower flow channel hole is connected to the third flow channel 203 on the stationary plate 2.

4. The scroll compressor bearing lubrication channel structure according to claim 2, characterized in that: The bearing bracket (3) is provided with a second flow channel hole (31) on one side of the stationary plate (2). The second flow channel hole (31) communicates with the third flow channel (203). The surface of the bearing bracket (3) is provided with a fourth flow channel (32) that communicates with the second flow channel hole (31). The fourth flow channel (32) extends to the groove on the inner side of the bearing bracket (3) and can deliver lubricating oil to the first bearing (6) and the eccentric sleeve (8) for lubrication.

5. The scroll compressor bearing lubrication channel structure according to claim 3, characterized in that: The bearing frame (3) is provided with a partition (301) inside. The first bearing (6) and the eccentric sleeve (8) are located on both sides of the partition (301). After the lubricating medium flows into the interior of the bearing frame (3) through the fourth flow channel (32), it is divided into two sides by the partition (301) to lubricate the first bearing (6) and the eccentric sleeve (8) respectively.

6. The scroll compressor bearing lubrication channel structure according to claim 3, characterized in that: The first flow channel (201) is inclined toward the side of the second cavity (5012).

7. A compressor, characterized in that: The scroll compressor bearing lubrication channel structure according to any one of claims 1 to 6 further includes: the power mechanism (1) includes a housing (11), the housing (11) is provided with at least one air inlet (111), the housing (11) is divided into a first cavity and a second cavity by a partition (13), the partition (13) located in the second cavity is provided with at least one flow channel guide (131) for guiding airflow, the flow channel guide (131) forms a flow channel with the side wall of the partition (13) and the mounting part, and the air inlet (111) is located on the air inlet side of the flow channel.

8. The compressor according to claim 7, characterized in that: At least one heat dissipation component (132) is provided on the air outlet end of the flow channel on the partition (13).

9. The compressor according to claim 7, characterized in that: The heat dissipation component (132) includes a first heat dissipation component (1321) and a second heat dissipation component (1322), which are arranged on the partition (13) in front and behind; the height of the second heat dissipation component (1322) is higher than the height of the first heat dissipation component (1321).

10. The compressor according to claim 7, characterized in that: The housing (11) has a protrusion (1101) on its inner wall for contacting and engaging with the stator (4). A heat dissipation channel (1102) for the flow of heat dissipation medium is provided between the protrusions (1101). The area ratio of the heat dissipation channel (1102) to the protrusion (1101) is 1:4.

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