Scroll compressor with microgroove structure

Abstract

The invention relates to the field of scroll compressors, provides a scroll compressor with a microgroove structure, and aims to solve the problems that the effect of reducing leakage is poor by adding sealing strips between scroll teeth and end plates of a movable scroll plate and a static scroll plate, optimizing the molded line design of the scroll plates, improving the machining precision and the like in the prior art. And an annular sealing strip is arranged at the contact part of the movable scroll plate and the pin shaft plate, so that the leakage is reduced, and the effect is poor. Comprising a rack, a static scroll plate arranged on the rack and a movable scroll plate driven by an eccentric crankshaft and used for being meshed with the static scroll plate, the static scroll plate is provided with a plurality of first scroll teeth, the movable scroll plate is provided with a plurality of second scroll teeth, the top of each first scroll tooth is provided with a first annular microgroove, and the top of each second scroll tooth is provided with a second annular microgroove. A second annular microgroove is formed in the top of the second scroll wrap, and a third annular microgroove is formed in the contact face of the movable scroll plate and the pin shaft plate.

Description

Technical Field

[0001] The present application relates to the technical field of scroll compressors, and more specifically, to a scroll compressor with a micro-groove structure. Background Art

[0002] As an important equipment in the fields of refrigeration, air conditioning and air compression, the working stability and performance level of the scroll compressor are directly related to the operating efficiency and energy consumption of the entire system. During the operation of the scroll compressor, good meshing and sealing of the orbiting scroll and the stationary scroll are the key to ensuring its working stability and improving performance. However, affected by the axial gas force acting on the working chamber side of the orbiting scroll, the scroll teeth and the end plates of the orbiting scroll and the stationary scroll cannot fit tightly, forming a certain axial gap. This gap causes the exchange of gas mass between adjacent working chambers, that is, radial leakage, which reduces the efficiency of the compressor and increases energy consumption.

[0003] In order to solve this problem, the prior art generally adopts methods such as adding sealing strips, optimizing the scroll profile design, and improving the processing accuracy to reduce leakage. However, these methods often involve complex processing processes and high costs, and have limited effects on leakage control between the scroll teeth and the end plates of the orbiting scroll and the fixed scroll, and the contact parts between the orbiting scroll and the pin shaft disk. In particular, the leakage problem is particularly prominent in the annular part where the orbiting scroll and the pin shaft disk contact, due to the large contact area and high sealing requirements.

[0004] In order to ensure the stability of the axial back pressure of the movable scroll, an annular sealing strip is usually arranged at the contact point between the movable scroll and the pin shaft disk to isolate the suction chamber and the back pressure chamber of the compressor and prevent gas leakage between the back pressure chamber and the suction chamber. However, in actual operation, due to factors such as aging, wear and installation accuracy of the sealing strip, it is still difficult to completely avoid leakage problems. The leakage problem not only reduces the efficiency of the scroll compressor, but may also cause wear on the compressor components, affecting the stability and service life of the compressor. Especially in air-conditioning heat pump systems, due to space limitations and energy consumption requirements, higher requirements are placed on the performance and reliability of scroll compressors. How to effectively suppress refrigerant leakage between the vortex teeth and end plates of the movable scroll and the fixed scroll, and between the movable scroll and the pin shaft disk, while ensuring a good oil lubrication effect, has become an important direction for the technical improvement of scroll compressors.

[0005] Therefore, the prior art needs to be improved. Summary of the invention

[0006] The purpose of the present application is to provide a scroll compressor with a micro-groove structure to solve the problem that the existing methods of reducing leakage by adding sealing strips between the scroll teeth and the end plates of the orbiting scroll and the fixed scroll, optimizing the scroll profile design, and improving the processing accuracy are not effective, and the problem that the leakage is not reduced by arranging an annular sealing strip at the contact part between the orbiting scroll and the pin shaft disk is not effective.

[0007] To achieve the above purpose, the technical solution adopted in the embodiment of the present application is:

[0008] A scroll compressor with a micro-groove structure, comprising:

[0009] It includes a frame, a fixed scroll plate arranged on the frame, and a movable scroll plate driven by an eccentric crankshaft and used to engage with the fixed scroll plate, wherein the fixed scroll plate has a plurality of first scroll teeth, the movable scroll plate has a plurality of second scroll teeth, the top of the first scroll teeth is provided with a first annular microgroove, the top of the second scroll teeth is provided with a second annular microgroove, and the contact surface between the movable scroll plate and the pin shaft plate is provided with a third annular microgroove.

[0010] According to the scroll compressor with a microgroove structure described above, a plurality of first annular microgrooves are provided.

[0011] According to the scroll compressor with a microgroove structure described above, the depth of the first annular microgroove is set at 0.1-0.5 mm, and the width of the first annular microgroove is set at 0.2-1 mm.

[0012] According to the scroll compressor with a microgroove structure described above, the outer shape of the first annular microgroove is set to be rectangular, triangular, circular or a combination thereof.

[0013] According to the scroll compressor with a microgroove structure described above, there are multiple second annular microgrooves.

[0014] According to the scroll compressor with a microgroove structure described above, the depth of the second annular microgroove is set at 0.1-0.5 mm, and the width of the first annular microgroove is set at 0.2-1 mm.

[0015] According to the scroll compressor with a microgroove structure described above, the outer shape of the second annular microgroove is set to be rectangular, triangular, circular or a combination thereof.

[0016] According to the scroll compressor with a microgroove structure described above, there are multiple third annular microgrooves.

[0017] According to the scroll compressor with a microgroove structure described above, the outer shape of the third annular microgroove is set to be rectangular, triangular, circular or a combination thereof.

[0018] According to the scroll compressor with a micro-groove structure described above, the first scroll tooth and the second scroll tooth are arranged 180 degrees relative to each other and mesh with each other, and form one or more relatively closed working chambers with the orbiting scroll and the fixed scroll.

[0019] The scroll compressor with a microgroove structure provided by the present application has at least the following beneficial effects:

[0020] The present application respectively arranges the first annular microgroove, the second annular microgroove and the third annular microgroove at the top of the first scroll tooth, the top of the second scroll tooth and the contact surface between the movable scroll plate and the pin shaft plate, thereby changing the flow path of the refrigerant in these parts and increasing the flow resistance, thereby effectively suppressing the leakage of the refrigerant, which not only improves the axial sealing level of the scroll compressor, but also reduces the waste of refrigerant and environmental pollution; and the arrangement of the third annular microgroove can also serve as an oil lubrication channel and oil storage tank, which can guide the lubricating oil to flow to the contact surface between the movable scroll plate and the pin shaft plate to form a stable oil film lubrication, which can not only reduce the friction loss between the movable scroll plate and the pin shaft plate, but also improve the mechanical efficiency and service life of the scroll compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0022] Figure 1 A schematic structural diagram of a scroll compressor with a microgroove structure provided in an embodiment of the present application.

[0023] Figure 2 A schematic diagram of the connection structure between a first scroll tooth and a second scroll tooth in a scroll compressor with a microgroove structure provided in an embodiment of the present application.

[0024] Figure 3 A schematic structural diagram of a scroll compressor with a microgroove structure provided in an embodiment of the present application, in which the annular microgroove is arranged in a circular shape.

[0025] Figure 4 A schematic structural diagram of a scroll compressor with a microgroove structure provided in an embodiment of the present application, in which the annular microgrooves are arranged in a combined shape.

[0026] Among them, the reference numerals in the figure are:

[0027] 1. Frame; 21. First scroll tooth; 22. First annular microgroove; 23. Exhaust hole; 3. Moving scroll plate; 31. Second scroll tooth; 32. Second annular microgroove; 33. Third annular microgroove; 34. Back pressure hole; 4. Eccentric crankshaft; 5. Pin plate; 6. Main shaft; 7. Main shaft bearing; 8. Cross slip ring. DETAILED DESCRIPTION

[0028] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0029] It should be noted that when a component is referred to as being "fixed on" or "disposed on" another component, it may be directly or indirectly located on the other component. When a component is referred to as being "connected to" another component, it may be directly or indirectly connected to the other component. The directions or positions indicated by the terms "upper", "lower", "left", "right", "front", "back", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc. are based on the directions or positions shown in the accompanying drawings and are only for the convenience of description and cannot be understood as limitations on the present technical solution. The terms "first" and "second" are only used for the convenience of description and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features. "Multiple" means two or more, unless otherwise clearly and specifically defined.

[0030] As an important equipment in the fields of refrigeration, air conditioning and air compression, the working stability and performance level of the scroll compressor are directly related to the operating efficiency and energy consumption of the entire system. During the operation of the scroll compressor, good meshing and sealing of the orbiting scroll and the stationary scroll are the key to ensuring its working stability and improving performance. However, affected by the axial gas force acting on the working chamber side of the orbiting scroll, the scroll teeth and the end plates of the orbiting scroll and the stationary scroll cannot fit tightly, forming a certain axial gap. This gap causes the exchange of gas mass between adjacent working chambers, that is, radial leakage, which reduces the efficiency of the compressor and increases energy consumption.

[0031] In order to solve this problem, the prior art generally adopts methods such as adding sealing strips, optimizing the scroll profile design, and improving the processing accuracy to reduce leakage. However, these methods often involve complex processing processes and high costs, and have limited effects on leakage control between the scroll teeth and the end plates of the orbiting scroll and the fixed scroll, and the contact parts between the orbiting scroll and the pin shaft disk. In particular, the leakage problem is particularly prominent in the annular part where the orbiting scroll and the pin shaft disk contact, due to the large contact area and high sealing requirements.

[0032] In order to ensure the stability of the axial back pressure of the movable scroll, an annular sealing strip is usually arranged at the contact point between the movable scroll and the pin shaft disk to isolate the suction chamber and the back pressure chamber of the compressor and prevent gas leakage between the back pressure chamber and the suction chamber. However, in actual operation, due to factors such as aging, wear and installation accuracy of the sealing strip, it is still difficult to completely avoid leakage problems. The leakage problem not only reduces the efficiency of the scroll compressor, but may also cause wear on the compressor components, affecting the stability and service life of the compressor. Especially in air-conditioning heat pump systems, due to space limitations and energy consumption requirements, higher requirements are placed on the performance and reliability of scroll compressors. How to effectively suppress refrigerant leakage between the vortex teeth and end plates of the movable scroll and the fixed scroll, and between the movable scroll and the pin shaft disk, while ensuring a good oil lubrication effect, has become an important direction for the technical improvement of scroll compressors.

[0033] For this purpose, see Figure 1 A scroll compressor with a microgroove structure provided in an embodiment of the present application includes a frame 1, a fixed scroll (not shown in the figure) and a movable scroll 3, wherein the fixed scroll is arranged on the frame 1, and the movable scroll 3 is driven by an eccentric crankshaft 4 and is used to engage with the fixed scroll to achieve gas suction, compression and discharge. Among them, the fixed scroll has a plurality of first scroll teeth 21, and the movable scroll 3 has a plurality of second scroll teeth 31. The top of the first scroll 21 (the position of the first scroll 21 close to the end plate) is provided with a first annular microgroove 22, and the top of the second scroll 31 (the position of the second scroll 31 close to the end plate) is provided with a second annular microgroove 32, and the contact surface between the movable scroll 3 and the pin disk 5 (the back of the movable scroll 3) is provided with a third annular microgroove 33.

[0034] The present embodiment provides the first annular microgroove 22, the second annular microgroove 32 and the third annular microgroove 33 at the top of the first scroll tooth 21, the top of the second scroll tooth 31 and the contact surface between the movable scroll plate 3 and the pin shaft plate 5, respectively, so as to change the flow path of the refrigerant in these parts and increase the flow resistance, thereby effectively suppressing the leakage of the refrigerant, which not only improves the axial sealing level of the scroll compressor, but also reduces the waste of refrigerant and environmental pollution; and the setting of the third annular microgroove 33 can also serve as an oil lubrication channel and oil storage tank, which can guide the lubricating oil to flow to the contact surface between the movable scroll plate 3 and the pin shaft plate 5 to form a stable oil film lubrication, which can not only reduce the friction loss between the movable scroll plate 3 and the pin shaft plate 5, but also improve the mechanical efficiency and service life of the scroll compressor.

[0035] It is worth mentioning that in actual engineering applications, due to the processing errors between the second scroll tooth 31 of the movable scroll 3 and the first scroll tooth 21 of the fixed scroll, and the inconsistent pressure on the thrust bearing oil film at each corner during machine operation, there is an axial gap between the vortex end face of the movable scroll 3 and the vortex end face of the fixed scroll. Therefore, along the vortex end face, there is leakage of the working fluid gas from the high-pressure chamber to the low-pressure chamber. Because the pressure difference makes this leakage radially in the vortex in the shape of a ray, this leakage mode is called radial leakage.

[0036] When the working fluid gas flows from the high-pressure chamber to the low-pressure chamber and radial leakage occurs, the first annular microgroove 22 and the second annular microgroove 32 can rely on the resistance generated by the flow channel to reduce the fluid leakage, and finally achieve the purpose of reducing pressure and preventing leakage. The gas flow through the radial gap with annular microgroove seal can be equivalent to a number of isentropic flows of gradually contracting-expanding nozzles. Under the action of pressure difference, the leaking gas passes through the first microgroove, and the process is a process of gradually contracting and then expanding. Except for a small part of the gas directly entering the next microgroove along the axial gap, most of the gas produces a vortex effect in the first microgroove, the gas pressure in the microgroove decreases, the gas flow rate increases, and the gas after decompression enters the second microgroove along the axial gap until it enters the next level compression chamber after passing through the last microgroove, but at this time the leaking gas pressure is already very small. Its thermodynamic principle is explained as follows: the working fluid gas leaks outward through the radial gap, and the fluid pressure energy is converted into kinetic energy during the process, the temperature is reduced, the high-speed fluid enters the microgroove cavity, the flow area suddenly increases, resulting in a decrease in flow rate, and a vortex is formed in the tooth cavity due to the effect of fluid viscosity, the energy is continuously dissipated, and the pressure is continuously reduced. The pressure drop generated when flowing through the throttle is equal. In addition, the impact of the jet on the groove wall will also cause the loss of fluid kinetic energy, which plays a certain role in preventing fluid leakage.

[0037] Optional, see Figure 2 In one embodiment, the first scroll tooth 21 and the second scroll tooth 31 are arranged at 180 degrees relative to each other and mesh with each other, and form one or more relatively closed working chambers with the orbiting scroll 3 and the fixed scroll.

[0038] Optional, see Figure 1 In one embodiment, the scroll compressor also includes a main shaft 6, which is rotatably arranged on the frame 1 through a main shaft bearing 7, an eccentric crankshaft 4 is arranged on the main shaft 6, a movable scroll plate 3 is arranged on the eccentric crankshaft 4, an exhaust hole 23 is opened on the fixed scroll plate, and a back pressure hole 34 is arranged on the movable scroll plate 3.

[0039] When the scroll compressor is working, the motor drives the main shaft 6 and the eccentric crankshaft 4 to rotate, and the movable scroll 3 rotates and translates driven by the main shaft 6 and the eccentric crankshaft 4. The relative movement of the meshing point of the first scroll tooth 21 on the fixed scroll and the meshing point of the second scroll tooth 31 on the movable scroll 3 causes the volume of each working chamber to change periodically, and the working fluid gas is compressed. The cross slip ring 8 is used to prevent the movable scroll 3 from rotating. When the working fluid gas is compressed to a given pressure, the working fluid gas pushes open the exhaust valve plate and is discharged from the scroll compressor through the exhaust hole 23.

[0040] Optional, see Figure 1 In one embodiment, the first annular microgrooves 22 are provided in a plurality, and the plurality of first annular microgrooves 22 are evenly provided at the top of the first scroll gear 21. Compared with only providing one first annular microgrooves 22, the provision of the plurality of first annular microgrooves 22 in this embodiment has a significantly better flow control effect. Increasing the number of the first annular microgrooves 22 is equivalent to prolonging the energy dissipation process, thereby reducing the negative impact of radial leakage and improving the sealing performance. Under normal circumstances, the provision of 4 to 6 first annular microgrooves 22 is sufficient to control radial leakage.

[0041] Optionally, in one embodiment, the shape of the first annular microgroove 22 can be set to be rectangular, triangular, circular or a combination thereof, the depth of the first annular microgroove 22 can be set to be 0.1-0.5 mm, and the width of the first annular microgroove 22 can be set to be 0.2-1 mm.

[0042] Optional, see Figure 1 In one embodiment, the second annular microgrooves 32 are provided in a plurality, and the plurality of second annular microgrooves 32 are evenly provided at the top of the second volute 31. Compared with only one second annular microgrooves 32, the provision of the plurality of second annular microgrooves 32 in this embodiment has a significantly better flow control effect. Increasing the number of the second annular microgrooves 32 is equivalent to prolonging the energy dissipation process, thereby reducing the negative impact of radial leakage and improving the sealing performance. Under normal circumstances, the provision of 4 to 6 second annular microgrooves 32 is sufficient to control radial leakage.

[0043] Optionally, in one embodiment, the shape of the second annular microgroove 32 can be set to be rectangular, triangular, circular or a combination thereof, the depth of the second annular microgroove 32 can be set to be 0.1-0.5 mm, and the width of the second annular microgroove 32 can be set to be 0.2-1 mm.

[0044] Optionally, in one embodiment, the shape of the third annular microgroove 33 can be set to be rectangular, triangular, circular or a combination thereof.

[0045] Optionally, in one embodiment, for the processing of the first annular microgroove 22, the second annular microgroove 32 and the third annular microgroove 33, high-precision processing methods such as precision machining, laser cutting, wire cutting, and electrochemical processing can be used, and during the processing, the processing accuracy and surface quality need to be strictly controlled to avoid adverse effects on the overall structure of the scroll compressor. At the same time, in order to ensure the durability and stability of the first annular microgroove 22, the second annular microgroove 32 and the third annular microgroove 33, all the annular microgrooves after processing need to be subjected to necessary surface treatment and strengthening treatment.

[0046] In one of the practical specific application embodiments, the shape of the first annular microgroove 22 and the shape of the second annular microgroove 32 are both set to be rectangular, the depth of the first annular microgroove 22 and the second annular microgroove 32 are both 0.3mm, the width is 0.5mm, the number is several, and they are evenly distributed on the top of the first scroll tooth 21 and the second scroll tooth 31, respectively, and the shape of the third annular microgroove 33 is also set to be rectangular, the depth is 0.2mm, the width is 0.4mm, the number is several, and they are evenly distributed on the contact surface of the movable scroll plate 3 and the pin shaft plate 5. The setting of the rectangular microgroove in this embodiment can significantly reduce the refrigerant leakage, improve the mechanical efficiency of the scroll compressor, and reduce the friction loss between the movable scroll plate 3 and the pin shaft plate 5. The scroll compressor with rectangular microgrooves significantly reduces the leakage of the working fluid gas by optimizing the gas flow path and improving the sealing. In addition, the rectangular microgroove can guide the working fluid gas to flow along a specific path, reducing the flow unevenness and leakage. The depth and width of the rectangular microgrooves are precisely controlled, effectively enhancing the sealing of the working chamber and preventing the working fluid gas in the high-pressure area from leaking into the low-pressure area. At the same time, the rectangular microgroove design also reduces the wear between the working fluid gas and the orbiting scroll 3 and the fixed scroll by reducing the friction of the contact surface, thereby extending the service life of the scroll compressor.

[0047] In another practical specific application embodiment, the shape of the first annular microgroove 22 and the shape of the second annular microgroove 32 are both set to a triangle, the depth of the first annular microgroove 22 and the second annular microgroove 32 are both 0.4mm, the bottom width is 0.6mm, and the number is a plurality of strips, which are evenly distributed on the top of the first scroll gear 21 and the second scroll gear 31, respectively, and the shape of the third annular microgroove 33 is set to a circle, see Figure 3, with a depth of 0.3 mm, a diameter of 0.5 mm, and a number of them, which are evenly distributed on the contact surface between the movable scroll plate 3 and the pin shaft plate 5. Compared with the rectangular microgrooves, in this embodiment, the setting of the triangular microgrooves of the first annular microgrooves 22 and the second annular microgrooves 32 has a weaker leakage control ability for the working gas, because its structural characteristics will reduce the turbulence and airflow separation of the working gas flowing through the radial gap, but its processing process is simpler, and the triangular microgrooves have higher structural strength, can withstand greater pressure differences and mechanical stresses, and extend the service life. In addition, the triangular microgrooves help to improve the heat exchange efficiency, optimize the thermal performance of the scroll compressor, and significantly improve the overall efficiency. The circular microgrooves of the third annular microgrooves 33 can better store lubricating oil on the contact surface between the movable scroll plate 3 and the pin shaft plate 5, and its shape is conducive to the accumulation and distribution of lubricating oil, thereby improving the oil lubrication effect. The design of the circular microgrooves also helps to reduce the direct contact area between the movable scroll plate 3 and the pin shaft plate 5, reduce the friction coefficient, and further reduce the wear and overheating of components caused by dry friction.

[0048] In another practical specific application embodiment, the shape of the first annular microgroove 22 and the shape of the second annular microgroove 32 are both set to a combined shape, that is, the shape of the first annular microgroove 22 and the shape of the second annular microgroove 32 are set to a combination of rectangular and triangular microgrooves to form a staggered composite microgroove structure, see Figure 4 , wherein the rectangular microgroove has a depth of 0.2 mm and a width of 0.4 mm; the triangular microgroove has a depth of 0.3 mm and a bottom width of 0.5 mm; the first annular microgroove 22 and the second annular microgroove 32 have a depth of 0.4 mm and a width of 0.6 mm, and the number of the microgroove is several, which are evenly distributed on the top of the first scroll tooth 21 and the second scroll tooth 31, respectively; the shape of the third annular microgroove 33 is set as a double-layer ring, the inner microgroove of which is rectangular, with a depth of 0.1 mm and a width of 0.3 mm; the outer microgroove is circular, with a depth of 0.2 mm and a diameter of 0.4 mm, and the number of the microgroove is several, which are evenly distributed on the contact surface between the movable scroll plate 3 and the pin shaft plate 5. In this embodiment, the first annular microgroove 22 and the second annular microgroove 32 are both arranged in a composite microgroove structure. Taking into account the sealing effect and structural strength of the microgroove, the rectangular microgroove has a stronger ability to hinder the leaking fluid, which will form turbulence and air flow diversion in the annular cavity, and the sealing effect is better; the triangular microgroove has a higher structural strength and can withstand greater pressure differences and mechanical stresses. The combination of the two meets the requirements for sealing ability and structural strength at the same time. The double-layer ring setting is intended to improve the oil lubrication effect, while increasing the contact area between the movable scroll plate 3 and the pin shaft plate 5 to reduce friction loss.

[0049] In summary, the present application provides a scroll compressor with a microgroove structure, including a frame 1, a fixed scroll plate and a movable scroll plate 3, wherein the fixed scroll plate is arranged on the frame 1, and the movable scroll plate 3 is driven by an eccentric crankshaft 4 and is used to engage with the fixed scroll plate to achieve gas suction, compression and discharge. Among them, the top of the first scroll tooth 21 (the position of the first scroll tooth 21 close to the end plate) is provided with a first annular microgroove 22, the top of the second scroll tooth 31 (the position of the second scroll tooth 31 close to the end plate) is provided with a second annular microgroove 32, and the contact surface between the movable scroll plate 3 and the pin plate 5 (the back of the movable scroll plate 3) is provided with a third annular microgroove 33. The present application respectively arranges the first annular microgroove 22, the second annular microgroove 32 and the third annular microgroove 33 at the top of the first scroll tooth 21, the top of the second scroll tooth 31 and the contact surface between the movable scroll plate 3 and the pin shaft plate 5, thereby changing the flow path of the refrigerant in these parts and increasing the flow resistance, thereby effectively suppressing the leakage of the refrigerant, which not only improves the axial sealing level of the scroll compressor, but also reduces the waste of refrigerant and environmental pollution; and the arrangement of the third annular microgroove 33 can also serve as an oil lubrication channel and oil storage tank, which can guide the lubricating oil to flow to the contact surface between the movable scroll plate 3 and the pin shaft plate 5 to form a stable oil film lubrication, which can not only reduce the friction loss between the movable scroll plate 3 and the pin shaft plate 5, but also improve the mechanical efficiency and service life of the scroll compressor.

[0050] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present application should be included in the protection scope of the present application.

Claims

1. A scroll compressor with a micro-groove structure, comprising a frame, a fixed scroll disposed on the frame, and a movable scroll driven by an eccentric crankshaft and used to engage with the fixed scroll, wherein: The fixed scroll plate has a plurality of first scroll teeth, and the movable scroll plate has a plurality of second scroll teeth, and is characterized in that a first annular microgroove is arranged on the top of the first scroll tooth, a second annular microgroove is arranged on the top of the second scroll tooth, and a third annular microgroove is arranged on the contact surface between the movable scroll plate and the pin shaft plate.

2. The scroll compressor with a microgroove structure according to claim 1, characterized in that: A plurality of the first annular microgrooves are provided.

3. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The depth of the first annular microgroove is set at 0.1-0.5 mm, and the width of the first annular microgroove is set at 0.2-1 mm.

4. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The first annular microgroove has an outer shape of a rectangle, a triangle, a circle or a combination thereof.

5. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The second annular microgrooves are multiple.

6. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The depth of the second annular microgroove is set at 0.1-0.5 mm, and the width of the first annular microgroove is set at 0.2-1 mm.

7. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The second annular microgroove has an outer shape of a rectangle, a triangle, a circle or a combination thereof.

8. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The third annular microgrooves are multiple.

9. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The outer shape of the third annular microgroove is set to be rectangular, triangular, circular or a combination thereof.

10. The scroll compressor with a microgroove structure according to claim 1, characterized in that: The first scroll tooth and the second scroll tooth are arranged at an angle of 180 degrees relative to each other and mesh with each other, and form one or more relatively closed working chambers with the orbiting scroll and the fixed scroll.

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