Scroll, scroll compressor

Abstract

The application provides a scroll disc and scroll compressor, wherein the scroll disc comprises a scroll disc base body, one side of the scroll disc base body is a first side surface, the first side surface is provided with scroll teeth, and the first side surface is composed of a first area and a second area; the first area is an area adjacent to a discharge port of a compressor pump body, the second area is an area other than the first area on the first side surface, a first wear-resistant layer is coated on the first area, a second wear-resistant layer is coated on the second area, and the film thickness of the first wear-resistant layer is not equal to the film thickness of the second wear-resistant layer. According to the application, the film thickness of the wear-resistant layers corresponding to the first area and the second area is not equal, so that the difficulty of the process can be greatly reduced and the coating cost of the corresponding wear-resistant layer can be reduced under the premise of meeting the wear-resistant requirements of different areas.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of compressor manufacturing, and particularly relates to a scroll plate and scroll compressor. BACKGROUND

[0002] The scroll compressor is a volumetric compression compressor, and key working components include a fixed scroll plate and a dynamic scroll plate in meshing relative motion. The profile of the dynamic and static scroll plates is spiral (spiral tooth), the dynamic plate is eccentric to the static plate and is installed in opposition with a difference of 180 degrees, the end of the scroll plate profile is in contact with the bottom of the opposite scroll plate, and a series of crescent spaces are formed between the dynamic and static plates. The dynamic scroll plate rotates at a high speed without self-rotation with the center of the static plate as the rotation center and with a rotation radius p under the action of the crankshaft drive and anti-rotation mechanism, thereby forming continuous changes in the closed volume, so as to realize the purpose of gas suction, compression and discharge.

[0003] High reliability and high efficiency are important trends in the development of scroll compressors. In order to achieve high reliability or high efficiency, the dynamic and static scroll plates are usually made of light alloys (such as aluminum alloy, magnesium alloy and titanium alloy, etc.) in whole or in part, the main purpose of which is to reduce the centrifugal force acting on the dynamic scroll plate, reduce the vibration amplitude of the compressor and reduce the weight of the whole machine. The light alloy pump body without any treatment has poor wear resistance and cannot meet the demand for high reliability, so the pump body needs to be modified or treated on the surface. After the wear-resistant surface modification or surface treatment, the roughness of the hard wear-resistant layer is too large, the friction factor is too large when running with the counterpart, and the power consumption (i.e. power consumption) increases. In order to reduce the power consumption, a wear-resistant layer is usually plated on the wear-resistant layer to reduce the friction. The mismatched composite coating system or the mismatched film thickness ratio cannot maximize the effect of the wear-resistant coating and is prone to coating peeling.

[0004] Therefore, how to select a suitable composite coating system to play its due role while considering the process and cost is of great significance to the realization of high reliability and high energy efficiency of the compressor.

[0005] The wear-resistant layer and solid lubricating layer in the prior art often select the same film thickness value at different positions to pursue the uniformity of the film thickness value. This requirement is certainly beneficial to the wear resistance and lubricity of the whole scroll plate, but in the specific implementation process, the current density and other parameters are difficult to remain consistent at different positions due to the complexity of the scroll plate structure, which makes it difficult for the film thickness of the related coating to meet the design requirements through a single process, i.e. the technical implementability needs to be discussed, and the use of multiple different plating processes greatly increases the coating cost of the coating. SUMMARY

[0006] Therefore, the application provides a scroll disc and scroll compressor, which can overcome the problems of the prior art, such as the difficulty in realizing the process and the high cost of coating due to the uniform film thickness requirement of the wear-resistant layer at different positions of the scroll disc.

[0007] To solve the above problems, the application provides a scroll disc, comprising a scroll disc base body, a first side of the scroll disc base body facing a counterpart, a scroll tooth provided on the first side, and the first side being composed of a first region and a second region, wherein the first region is adjacent to an exhaust port of a compressor pump body, the second region is the region of the first side except the first region, a first wear-resistant layer is provided on the first region, and a second wear-resistant layer is provided on the second region, and the film thickness of the first wear-resistant layer is not equal to the film thickness of the second wear-resistant layer.

[0008] In some embodiments, the film thickness of the first wear-resistant layer is H1, the film thickness of the second wear-resistant layer is H2, and (1-3) x H1=(1-2) x H2.

[0009] In some embodiments, a third wear-resistant layer is provided on the side vertical wall of the scroll tooth, the film thickness of the third wear-resistant layer is H3, and (1-3) x H1=(1-2) x H3.

[0010] In some embodiments, the scroll disc is a moving scroll disc, the scroll disc base body has a second side opposite to the first side, the second side has a contact ring surface in contact with a wear-resistant sheet, a fourth wear-resistant layer is provided on the contact ring surface, and the film thickness of the fourth wear-resistant layer is greater than any one of the first wear-resistant layer, the second wear-resistant layer and the third wear-resistant layer.

[0011] In some embodiments, the film thickness of the fourth wear-resistant layer is H4, and H4=(1-3) x H1.

[0012] In some embodiments, 1≤H4 / H1≤5; and / or, H4=(1.5-2.5) x H1=(1-1.5) x H2=(1-1.5) x H3.

[0013] In some embodiments, a first solid lubricating layer is provided on the outside of the first wear-resistant layer, a second solid lubricating layer is provided on the outside of the second wear-resistant layer, a third solid lubricating layer is provided on the outside of the third wear-resistant layer, and a fourth solid lubricating layer is provided on the outside of the fourth wear-resistant layer, the film thickness of the first solid lubricating layer is in positive proportion to the film thickness of the first wear-resistant layer, the film thickness of the second solid lubricating layer is in positive proportion to the film thickness of the second wear-resistant layer, the film thickness of the third solid lubricating layer is in positive proportion to the film thickness of the third wear-resistant layer, and the film thickness of the fourth solid lubricating layer is in positive proportion to the film thickness of the fourth wear-resistant layer.

[0014] In some embodiments, the film thickness of the first solid lubricating layer is h1, the film thickness of the second solid lubricating layer is h2, the film thickness of the third solid lubricating layer is h3, and the film thickness of the fourth solid lubricating layer is h4, h4=(1-3)×h1=(1-2)×h2=(1-2)×h3.

[0015] In some embodiments, the maximum peak-valley vertical distance of the first wear-resistant layer in a set evaluation length is Rt1, the maximum peak-valley vertical distance of the second wear-resistant layer in a set evaluation length is Rt2, the maximum peak-valley vertical distance of the third wear-resistant layer in a set evaluation length is Rt3, and the maximum peak-valley vertical distance of the fourth wear-resistant layer in a set evaluation length is Rt4, h1=(1-8)Rt1, h2=(1-8)Rt2, h3=(1-8)Rt3, h4=(1-8)Rt4; and / or, h4=(1.5-2.5)×h1=(1-1.5)×h2=(1-1.5)×h3.

[0016] In some embodiments, 2μm≤Rt1≤Rt3≤Rt2≤Rt4≤15μm.

[0017] In some embodiments, when the Vickers hardness N1 of the first wear-resistant layer, the second wear-resistant layer, the third wear-resistant layer, and the fourth wear-resistant layer is ≥500HV, h1=(2.5-5)Rt1, h2=(2.5-5)Rt2, h3=(1-3)Rt3, h4=(2.5-5)Rt4; or, when the Vickers hardness N1 of the first wear-resistant layer, the second wear-resistant layer, the third wear-resistant layer, and the fourth wear-resistant layer is ≥500HV, h1=(1.5-4)Rt1, h2=(1.5-4)Rt2, h3=(1-2.5)Rt3, h4=(1.5-4)Rt4.

[0018] The present application also provides a scroll compressor comprising the scroll described above.

[0019] The present application provides a scroll and a scroll compressor, the film thickness of the wear-resistant layer in the first region and the second region is not equal, thereby greatly reducing the difficulty of the process and the coating cost of the corresponding wear-resistant layer under the premise of meeting the wear-resistant requirements of different regions. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 It is a planar structure schematic diagram of the scroll of the embodiment of the present application (the first side, the shadow area in the figure only schematically partially shows the corresponding wear-resistant layer);

[0021] Figure 2 It is a three-dimensional structure schematic diagram of the scroll of the embodiment of the present application (the shadow area in the figure only schematically partially shows the corresponding wear-resistant layer);

[0022] Figure 3 Fig. 1 is a schematic diagram of the planar structure of the vortex disc (second side, the shaded area in the figure only schematically shows the corresponding wear-resistant layer in part);

[0023] Figure 4 Fig. 2 is a schematic diagram of the microstructure of the vortex disc base body, wear-resistant layer and solid lubricating layer in the embodiment of the present application;

[0024] Figure 5 Fig. 3 is a schematic diagram of the internal structure of the scroll compressor in the embodiment of the present application.

[0025] The reference signs are as follows:

[0026] 1, vortex disc base body; 11, vortex tooth; 21, first wear-resistant layer; 22, second wear-resistant layer; 23, third wear-resistant layer; 24, fourth wear-resistant layer; 31, first solid lubricating layer; 32, second solid lubricating layer; 33, third solid lubricating layer; 34, fourth solid lubricating layer; 10, upper cover of the shell; 20, static scroll disc; 30, compression cavity; 40, dynamic scroll disc; 50, wear-resistant sheet; 60, lower cover of the shell; 70, upper support; 80, crankshaft. DETAILED DESCRIPTION

[0027] For reference Figures 1 to 5 As shown in the figure, according to the embodiment of the present application, a vortex disc is provided, which comprises a vortex disc base body 1, one side of the vortex disc base body 1 towards a counterpart (specifically, when the vortex disc base body 1 is the base body of a dynamic scroll disc, the counterpart is a static scroll disc, and vice versa) is a first side, the first side is provided with vortex teeth 11, and the first side is composed of a first area and a second area, wherein the first area is an area adjacent to the exhaust port of the compressor pump body, and the second area is an area other than the first area on the first side, the first area is coated with a first wear-resistant layer 21, and the second area is coated with a second wear-resistant layer 22, and the film thickness of the first wear-resistant layer 21 is not equal to the film thickness of the second wear-resistant layer 22. In this technical solution, the film thickness of the wear-resistant layers corresponding to the first area and the second area is not equal, so that the process difficulty can be greatly reduced and the coating cost of the corresponding wear-resistant layer can be reduced on the premise of meeting the wear-resistant requirements (satisfying the wear-resistant effect) of different areas.

[0028] As mentioned before, the first area is an area adjacent to the exhaust port of the compressor pump body, and the second area can be understood as an area adjacent to the suction port of the compressor pump body, and the first area and the second area together constitute the side of the vortex disc base body 1 towards the counterpart (excluding the area occupied by the vortex teeth 11 thereon), for reference Figure 1As shown, the boundary between the first region and the second region is the position where the scroll teeth 11 of the orbiting scroll plate close to the suction side begin to mesh. At this time, the film thickness of the first wear-resistant layer is less than the film thickness of the second wear-resistant layer, and further, the film thickness of the first wear-resistant layer 21 is H1, the film thickness of the second wear-resistant layer 22 is H2, (1-3) x H1 = (1-2) x H2. The side wall of the scroll teeth 11 is covered with a third wear-resistant layer 23, and the film thickness of the third wear-resistant layer 23 is H3, (1-3) x H1 = (1-2) x H3. It should be noted that the side wall of the scroll teeth 11 includes the entire side wall inside and outside, and the film thickness of the wear-resistant layer of the end portion thereof towards the counterpart is not particularly limited, and the thickness is moderate.

[0029] In some embodiments, the orbiting scroll plate is an orbiting scroll plate, the orbiting scroll plate base 1 has a second side surface opposite to the first side surface, the second side surface has a contact ring surface in contact with the wear-resistant sheet, and the contact ring surface is covered with a fourth wear-resistant layer 24, and the film thickness of the fourth wear-resistant layer 24 is greater than any one of the first wear-resistant layer 21, the second wear-resistant layer 22 and the third wear-resistant layer 23. In this technical solution, the second side surface of the base 1 of the orbiting scroll plate is relatively flat, and the contact wear risk between the second side surface and the wear-resistant sheet is relatively large, so the film thickness thereof is designed to be relatively large, which is beneficial to improve the overall wear resistance of the orbiting scroll plate. As a preferred implementation manner, the film thickness of the fourth wear-resistant layer 24 is H4, and H4 = (1-3) x H1.

[0030] In some embodiments, 1≤H4 / H1≤5, so as to ensure that the film thicknesses of the wear-resistant layers of the orbiting scroll plate are within a reasonable range, and prevent the film thicknesses of some regions from being too small to cause wear of the base in a short time and reduce the service life of the orbiting scroll plate, and prevent the film thicknesses of some regions from being too large to cause cost waste.

[0031] In some embodiments, H4 = (1.5-2.5) x H1 = (1-1.5) x H2 = (1-1.5) x H3, so that the wear-resistant layers corresponding to the regions are more matched in film thickness, and the wear-resistant layers corresponding to the regions have relatively consistent wear time, and the service life of the orbiting scroll plate is relatively optimal.

[0032] In some embodiments, the outer side of the first wear-resistant layer 21 is covered with a first solid lubricating layer 31, the outer side of the second wear-resistant layer 22 is covered with a second solid lubricating layer 32, the outer side of the third wear-resistant layer 23 is covered with a third solid lubricating layer 33, and the outer side of the fourth wear-resistant layer 24 is covered with a fourth solid lubricating layer 34. The film thickness of the first solid lubricating layer 31 is in direct proportion to the film thickness of the first wear-resistant layer 21, the film thickness of the second solid lubricating layer 32 is in direct proportion to the film thickness of the second wear-resistant layer 22, the film thickness of the third solid lubricating layer 33 is in direct proportion to the film thickness of the third wear-resistant layer 23, and the film thickness of the fourth solid lubricating layer 34 is in direct proportion to the film thickness of the fourth wear-resistant layer 24. That is, the thickness of the solid lubricating layer in the area with larger film thickness is also larger. The surface of the scroll body 1 is treated by the composite coating of wear resistance (i.e., the aforementioned wear-resistant layers) and friction reduction (i.e., the aforementioned solid lubricating layers), so as to simultaneously improve the wear resistance and friction reduction of the pump body, ensure the highest reliability of the two friction pairs of the moving disc and the stationary disc and the moving disc and the wear-resistant sheet, and minimize the power loss. Specifically, the film thickness of the first solid lubricating layer 31 is h1, the film thickness of the second solid lubricating layer 32 is h2, the film thickness of the third solid lubricating layer 33 is h3, and the film thickness of the fourth solid lubricating layer 34 is h4, h4 = (1-3) x h1 = (1-2) x h2 = (1-2) x h3. In matching with the aforementioned wear-resistant layers, h4 = (1.5-2.5) x h1 = (1-1.5) x h2 = (1-1.5) x h3.

[0033] The maximum peak-valley vertical distance of the first wear-resistant layer 21 in a set evaluation length is Rt1, the maximum peak-valley vertical distance of the second wear-resistant layer 22 in a set evaluation length is Rt2, the maximum peak-valley vertical distance of the third wear-resistant layer 23 in a set evaluation length is Rt3, and the maximum peak-valley vertical distance of the fourth wear-resistant layer 24 in a set evaluation length is Rt4, h1 = (1-8) Rt1, h2 = (1-8) Rt2, h3 = (1-8) Rt3, and h4 = (1-8) Rt4. The solid lubricating layer can completely cover the side of the corresponding wear-resistant layer facing the counter part, fully play the lubricating effect of the solid lubricating layer, and reduce the wear between the two parts in relative motion. In a specific embodiment, 2 μm ≤ Rt1 ≤ Rt3 ≤ Rt2 ≤ Rt4 ≤ 15 μm. It should be noted that the maximum peak-valley vertical distance (i.e., Rt) of the wear-resistant layer in the set evaluation length should not be too small. If it is too small, the mechanical embedding effect between the wear-resistant layer and the escalator lubricating coating will be weak.

[0034] The setting evaluation length is selected according to the roughness parameter evaluation procedure in the industry, and the position and the number of sampling lengths are selected flexibly according to actual requirements, which are not particularly limited in the application. The inventors find that the solid lubricating layer has different degrees of shedding due to different surface states, film thicknesses and surface activation states of the corresponding attached wear-resistant layer. In some embodiments, when the Vickers hardness N1 of the first wear-resistant layer 21, the second wear-resistant layer 22, the third wear-resistant layer 23 and the fourth wear-resistant layer 24 is greater than or equal to 500 HV, h1=(2.5-5)Rt1, h2=(2.5-5)Rt2, h3=(1-3)Rt3, and h4=(2.5-5)Rt4; or when the Vickers hardness N1 of the first wear-resistant layer 21, the second wear-resistant layer 22, the third wear-resistant layer 23 and the fourth wear-resistant layer 24 is greater than or equal to 500 HV, h1=(1.5-4)Rt1, h2=(1.5-4)Rt2, h3=(1-2.5)Rt3, and h4=(1.5-4)Rt4. According to different hardness of the wear-resistant layer, the maximum peak-valley vertical distance Rt value in the setting evaluation length of the wear-resistant layer is used to limit the film thickness of the wear-resistant layer, and the Rt value is limited in a range, so that the bonding force between the wear-resistant layer and the wear-resistant layer substrate is in an optimal range, the solid lubricating layer can play the maximum effect, and the problem of easy shedding of the solid lubricating layer is solved.

[0035] The material of the scroll base 1 of the scroll is preferably at least one of an aluminum alloy, a titanium alloy and a magnesium alloy. The wear-resistant layer (i.e., the first wear-resistant layer 21, the second wear-resistant layer 22, the third wear-resistant layer 23 and the fourth wear-resistant layer 24) is at least one of an aluminum oxide (anodic oxidation, hard anodic oxidation, micro-arc oxidation), a titanium oxide, a zirconium oxide and a cermet coating such as WC-Co, a Ni-P binary or ternary alloy and a Ni-B binary or ternary alloy. The preparation process of the wear-resistant layer can be at least one of chemical plating, chemical oxidation, thermal spraying, electroplating and PVD / CVD / PECVD. The solid lubricating layer can be at least one of a soft metal solid lubricant (Sn, Pb, etc.), a metal compound solid lubricant (oxide, sulfide, halide, borate, etc.), an inorganic solid lubricant (including graphite and fluorinated graphite) and an organic adhesive solid lubricating dry film (polymer doped MoS2 / PTFE / graphite or a combination thereof).

[0036] The following gives several specific embodiments to evaluate the energy efficiency of the compressor adopting the technical scheme of the application.

[0037] The material of the vortex disc base 1, the wear-resistant layer, the film thickness of the corresponding area, the solid lubricating layer and the film thickness range of the corresponding area used in the embodiments 1 to 4 are shown in Table 1, wherein it can be seen that the material of the vortex disc base 1 in the embodiment 2 is selected as an aluminum alloy of the aluminum-silicon series, the wear-resistant layer is a micro-arc oxidation coating, and the solid lubricating layer is selected as an organic adhesive solid lubricating dry film containing a MoS2 / PTFE / graphite solid lubricating particle combination; the material of the vortex disc base 1 in the embodiment 4 is selected as a TC4 titanium alloy, the wear-resistant coating is a titanium dioxide coating, and the solid lubricating coating is selected as an organic adhesive solid lubricating dry film containing a MoS2 / PTFE / graphite solid lubricating particle combination.

[0038] Table 1: Technical parameters used in the scheme

[0039]

[0040]

[0041] The compressor is tested at the rated frequency (60 Hz) according to the new national standard, and the test results are shown in Table 2.

[0042] Table 2: Test results

[0043]

[0044] As can be seen from Table 2, when the hardness of the wear-resistant layer is > 500 HV, under the rated working condition, the energy efficiency of the solid lubricating layer in the embodiment 1 is only 3.3 when the film thickness is thinner than that of the embodiment 2. The energy efficiency of the embodiment 2 is as high as 3.48, and the COP is improved by 5.32%. When the hardness of the wear-resistant layer is < 500 HV, under the rated working condition, the energy efficiency of the embodiment 4 is 4.9, and the COP is improved by 4.9%. The embodiment 3 is a technical scheme in which the film thickness of the solid lubricating layer is thicker than that of the embodiments 1, 2 and 4. The energy efficiency at 60 Hz is 3.39, which is improved by 2.69% compared with the embodiment 1, but the coating has a serious peeling problem.

[0045] According to the embodiments of the present application, a scroll compressor is also provided, which comprises the vortex disc described above. Specifically, as shown in Figure 5 The scroll compressor comprises a shell upper cover 10, a static scroll disc 20, a compression chamber 30, a dynamic scroll disc 40, a wear-resistant sheet 50, a shell lower cover 60, an upper support 70 and a crankshaft 80, wherein the static scroll disc 20 and the dynamic scroll disc 40 can adopt the vortex disc. When the compressor is running, the crankshaft 80 drives the vortex disc 40 and makes the dynamic scroll disc 40 move in a certain trajectory, cooperates with the static scroll disc 20 according to the designed gap and forms a relative revolution to form a periodically changing compression chamber, so that the refrigerant gas completes the processes of suction, compression and exhaust in the compression chamber, thereby achieving the purpose of compressing the gas.

[0046] When the compressor is running, the orbiting scroll 40 forms a friction pair with the fixed scroll 20 and the wear plate 50 under the action of gas force.

[0047] Those skilled in the art can understand that the above-mentioned advantageous modes can be freely combined and superimposed without conflict.

[0048] The above is only the preferred embodiment of the present application, and should be noted that for ordinary skilled in the art, without departing from the technical principles of the present application, can also make a number of improvements and variations, these improvements and variations should be considered as the protection scope of the present application.

Claims

1. A scroll, characterized by, The volute base (1) is provided with a first side surface on the side facing the counterpart, the first side surface is provided with a scroll tooth (11), the first side surface is composed of a first area and a second area, the first area is adjacent to the exhaust port of the compressor pump body, the second area is the area of the first side surface except the first area, the first area is provided with a first wear-resistant layer (21), the second area is provided with a second wear-resistant layer (22), the film thickness of the first wear-resistant layer (21) is not equal to the film thickness of the second wear-resistant layer (22); the side wall of the scroll tooth (11) is provided with a third wear-resistant layer (23); the volute is a movable scroll, the volute base (1) has a second side surface opposite to the first side surface, the second side surface has a contact ring surface in contact with the wear-resistant sheet, the contact ring surface is provided with a fourth wear-resistant layer (24), the film thickness of the fourth wear-resistant layer (24) is greater than any one of the first wear-resistant layer (21), the second wear-resistant layer (22) and the third wear-resistant layer (23).

2. The scroll of claim 1 wherein, The film thickness of the first wear-resistant layer (21) is H1, the film thickness of the second wear-resistant layer (22) is H2, (1~3)×H1=(1~2)×H2 and H1≠H2.

3. The scroll volute of claim 2, wherein, The film thickness of the third wear-resistant layer (23) is H3, (1~3)×H1=(1~2)×H3.

4. The scroll of claim 1 wherein, The film thickness of the fourth wear-resistant layer (24) is H4, H4=(1~3)×H1 and H4>H1.

5. The scroll of claim 4 wherein, H4=(1.5~2.5)×H1=(1~1.5)×H2=(1~1.5)×H3 and H4>H2, H4>H3.

6. The scroll of claim 1 wherein, The outer side of the first wear-resistant layer (21) is provided with a first solid lubricating layer (31), the outer side of the second wear-resistant layer (22) is provided with a second solid lubricating layer (32), the outer side of the third wear-resistant layer (23) is provided with a third solid lubricating layer (33), the outer side of the fourth wear-resistant layer (24) is provided with a fourth solid lubricating layer (34), the film thickness of the first solid lubricating layer (31) is proportional to the film thickness of the first wear-resistant layer (21), the film thickness of the second solid lubricating layer (32) is proportional to the film thickness of the second wear-resistant layer (22), the film thickness of the third solid lubricating layer (33) is proportional to the film thickness of the third wear-resistant layer (23), and the film thickness of the fourth solid lubricating layer (34) is proportional to the film thickness of the fourth wear-resistant layer (24).

7. The scroll of claim 6 wherein, The film thickness of the first solid lubricating layer (31) is h1, the film thickness of the second solid lubricating layer (32) is h2, the film thickness of the third solid lubricating layer (33) is h3, and the film thickness of the fourth solid lubricating layer (34) is h4, h4=(1~3)×h1=(1~2)×h2=(1~2)×h3.

8. The scroll volute of claim 6 wherein, The maximum peak-valley vertical distance of the first wear-resistant layer (21) in a set evaluation length is Rt1, the maximum peak-valley vertical distance of the second wear-resistant layer (22) in a set evaluation length is Rt2, the maximum peak-valley vertical distance of the third wear-resistant layer (23) in a set evaluation length is Rt3, the maximum peak-valley vertical distance of the fourth wear-resistant layer (24) in a set evaluation length is Rt4, h1=(1~8)Rt1, h2=(1~8)Rt2, h3=(1~8)Rt3, h4=(1~8)Rt4; and / or, h4=(1.5~2.5)×h1=(1~1.5)×h2=(1~1.5)×h3.

9. The scroll volute of claim 8, wherein, 2μm≤Rt1≤Rt3≤Rt2≤Rt4≤15μm.

10. The scroll circle according to claim 8 or 9, wherein When the Vickers hardness N1 of the first wear-resistant layer (21), the second wear-resistant layer (22), the third wear-resistant layer (23), and the fourth wear-resistant layer (24) is greater than or equal to 500HV, h1=(2.5~5)Rt1, h2=(2.5~5)Rt2, h3=(1~3)Rt3, h4=(2.5~5)Rt4.

11. The scroll circle according to claim 8 or 9, wherein When the Vickers hardness N1 of the first wear-resistant layer (21), the second wear-resistant layer (22), the third wear-resistant layer (23), and the fourth wear-resistant layer (24) is greater than or equal to 500HV, h1=(1.5~4)Rt1, h2=(1.5~4)Rt2, h3=(1~2.5)Rt3, h4=(1.5~4)Rt4.

12. A scroll compressor characterized by, The scroll.

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