Compressor and refrigeration apparatus

Abstract

The application discloses a compressor and a refrigeration device. The compressor comprises a crankshaft, a bearing, a dynamic scroll and an eccentric sleeve. The crankshaft comprises a main body section and an eccentric section which are connected. The outer peripheral wall of the main body section protrudes from the outer peripheral wall of the eccentric section. The outer peripheral wall of the eccentric section comprises a plurality of first matching surfaces which are arranged at intervals in the circumferential direction of the eccentric section. The inner peripheral wall of the eccentric sleeve is provided with a plurality of second matching surfaces. Each second matching surface is arranged opposite to one first matching surface. The first matching surface and the second matching surface are matched to limit the displacement of the eccentric sleeve relative to the crankshaft in the circumferential direction of the eccentric section. The inner peripheral wall of the eccentric sleeve and the outer peripheral wall of the eccentric section are in clearance fit. The structure of the compressor is reasonably arranged, the eccentricity of the compressor is adjustable, the scroll tooth of the compressor is protected, and the reliability and stability of the compressor in use are improved.

Description

Technical Field

[0001] This application belongs to the field of refrigeration equipment technology, specifically relating to a compressor and refrigeration equipment. Background Technology

[0002] A scroll compressor includes a crankshaft, an eccentric sleeve, bearings, and a moving scroll. The eccentric sleeve is fitted onto the eccentric section of the crankshaft, and the moving scroll is connected to the outer peripheral wall of the eccentric sleeve via the bearings. The crankshaft drives the moving scroll to rotate relative to the stationary scroll of the scroll compressor via the eccentric sleeve and bearings, thereby compressing the refrigerant in the compression chamber of the scroll compressor. The eccentricity of the compressor is not adjustable.

[0003] When a scroll compressor is in operation, if it encounters liquid slugging or impurities entering the compression chamber, the liquid and impurities are incompressible. Since the compressor's eccentricity is not adjustable, this can lead to bearing lubrication issues or even scroll gear breakage, which will reduce the reliability and stability of the scroll compressor. Utility Model Content

[0004] This application aims to address at least one of the technical problems existing in the prior art or related technologies.

[0005] Therefore, the first aspect of this application proposes a compressor.

[0006] The second aspect of this application proposes a refrigeration device.

[0007] In view of the above, the first aspect of this application provides a compressor, comprising: a crankshaft, along the axial direction of the crankshaft, the crankshaft including a main body section and an eccentric section connected together, the outer peripheral wall of the main body section protruding from the outer peripheral wall of the eccentric section, the outer peripheral wall of the eccentric section including a plurality of spaced first mating surfaces in the circumferential direction of the eccentric section; an eccentric sleeve, sleeved on the eccentric section, the inner peripheral wall of the eccentric sleeve having a plurality of second mating surfaces, each second mating surface being opposite to a first mating surface, the first mating surfaces and the second mating surfaces engaging to restrict the displacement of the eccentric sleeve relative to the crankshaft in the circumferential direction of the eccentric section; a bearing; a moving scroll, the moving scroll being connected to the outer peripheral wall of the eccentric sleeve via the bearing; wherein, the inner peripheral wall of the eccentric sleeve and the outer peripheral wall of the eccentric section are clearance-fitted.

[0008] The compressor provided in this application includes a crankshaft, an eccentric sleeve, a bearing, and a moving scroll.

[0009] The crankshaft consists of a main section and an eccentric section, which are connected. Along the axial direction of the crankshaft, the main section is located on one side of the eccentric section.

[0010] An eccentric sleeve is fitted onto the eccentric section, and the moving scroll is connected to the outer peripheral wall of the eccentric sleeve via a bearing.

[0011] The outer peripheral wall of the eccentric segment includes multiple first mating surfaces. These multiple first mating surfaces are arranged at intervals along the circumference of the eccentric segment.

[0012] The inner circumferential wall of the eccentric sleeve is provided with multiple second mating surfaces, which are arranged at intervals along the circumference of the eccentric section. These second mating surfaces cooperate with multiple first mating surfaces. Specifically, each second mating surface is positioned opposite a first mating surface. The cooperation of the first and second mating surfaces restricts the displacement of the eccentric sleeve relative to the crankshaft along the circumference of the eccentric section. This allows the crankshaft to drive the moving scroll to rotate relative to the stationary scroll of the compressor via the eccentric sleeve and bearings, thereby compressing the refrigerant in the compressor's compression chamber.

[0013] The inner circumferential wall of the eccentric sleeve and the outer circumferential wall of the eccentric section are in clearance fit, that is, there is a gap between the inner circumferential wall of the eccentric sleeve and the outer circumferential wall of the eccentric section along the radial direction of the eccentric section.

[0014] When the compressor is working under normal conditions, a second mating surface of the eccentric sleeve and a first mating surface of the crankshaft contact and limit the fit. The crankshaft rotates to apply a driving force to the second mating surface of the eccentric sleeve through the first mating surface of the eccentric section. Under the dual action of the driving force and the centrifugal force of the moving scroll, the moving scroll meshes with the stationary scroll, so that the compressor is in a fixed eccentricity state.

[0015] When liquid refrigerant or impurities enter the compressor's compression chamber, the eccentricity of the compressor is adjustable due to the clearance fit between the inner circumferential wall of the eccentric sleeve and the outer circumferential wall of the eccentric section. This means the eccentricity can be adaptively adjusted within a certain range. When the resultant force of the driving force and the centrifugal force of the moving scroll is less than the radial thrust on the moving scroll, the moving scroll will drive the eccentric sleeve to move radially along the eccentric section. This protects the scroll teeth of both the moving and stationary scrolls, preventing damage to the scroll teeth. By reducing frictional power consumption, this improves the stability and reliability of the compressor's operation, thus enhancing its performance and market competitiveness.

[0016] Understandably, the first and second mating surfaces work together to limit the fit dimensions of the crankshaft and eccentric sleeve. This restricts the displacement of the eccentric sleeve relative to the crankshaft along the circumferential direction of the eccentric section, indirectly limiting the fit dimensions of the moving scroll and the crankshaft. This provides reliable structural support for the moving scroll to perform translational rotation relative to the stationary scroll, ensuring the accuracy of the moving scroll's trajectory and not affecting volumetric efficiency or performance. Although the eccentric sleeve and crankshaft are circumferentially limited by the interaction of the first and second mating surfaces, they are also clearance-fitted radially within the eccentric section. Therefore, the eccentric sleeve can have slight floating or displacement relative to the eccentric section. When liquid refrigerant or impurities enter the compressor's compression chamber, the gap between the eccentric sleeve and the eccentric section absorbs some of the impact energy, preventing all impact forces from being directly transmitted to the bearings and the moving scroll, thus providing overload protection.

[0017] Understandably, when liquid refrigerant or impurities enter the compressor's compression chamber, the eccentric sleeve can float or shift slightly relative to the eccentric section, which can reduce the peak torque transmitted to the crankshaft and moving scroll, protect the lubricating film from damage, prevent shaft burnout or even tooth breakage, and improve the compressor's resistance to liquid slugging and impurities.

[0018] In some technical solutions, optionally, the first mating surface includes at least one of a plane and an arc surface; and / or the second mating surface includes at least one of a plane and an arc surface.

[0019] In this technical solution, the shapes of the first mating surface and the second mating surface are refined.

[0020] The first mating surface includes at least one of a plane and an arc surface; that is, the first mating surface includes a plane, or the first mating surface includes an arc surface, or the first mating surface includes both a plane and an arc surface. The structural design of the first mating surface facilitates processing and manufacturing, and helps to reduce production costs.

[0021] The second mating surface includes at least one of a plane and an arc surface. That is, the second mating surface includes a plane, or the second mating surface includes an arc surface, or the second mating surface includes both a plane and an arc surface. The structural design of the second mating surface facilitates processing and manufacturing, and helps to reduce production costs.

[0022] When the compressor is working under normal conditions, a second mating surface of the eccentric sleeve and a first mating surface of the crankshaft fit and limit each other in the circumferential direction of the eccentric section, so as to effectively limit the displacement of the eccentric sleeve relative to the crankshaft and provide reliable structural support to ensure the motion trajectory of the moving scroll.

[0023] When at least one of the first mating surface and the second mating surface includes a plane, the contact between the first mating surface and the second mating surface can be a line contact or a small area of ​​surface contact, which helps to improve the accuracy of the contact between the first mating surface and the second mating surface.

[0024] When at least one of the first and second mating surfaces includes a curved surface, the contact area between the first and second mating surfaces will be relatively large, resulting in a more uniform load distribution. This helps reduce stress concentration, improves the wear resistance of the structure, and ensures the product's service life. Simultaneously, it reduces the assembly precision requirements for the eccentric sleeve and crankshaft. Even with minor angular deviations, effective contact and limiting of the first and second mating surfaces can still be guaranteed, thus improving assembly efficiency.

[0025] In some technical solutions, optionally, at least a portion of the shape of the first mating surface is the same as the shape of the second mating surface; or the shape of the first mating surface is different from the shape of the second mating surface.

[0026] In this technical solution, at least a portion of the shape of the first mating surface is the same as the shape of the second mating surface. That is, a portion of the shape of the first mating surface is the same as the shape of the second mating surface, or the shapes of the first and second mating surfaces are completely identical. This increases the contact area between the first and second mating surfaces. When the compressor operates under normal conditions, a first mating surface and a second mating surface are in contact. Specifically, the contact between the first and second mating surfaces, which are at least partially identical in shape, enables precise fitting of the first and second mating surfaces, improves the degree of contact fit, provides more stable circumferential positioning in the eccentric section, ensures contact stability, reduces shaking or relative displacement, and also helps reduce local contact stress between the eccentric section and the eccentric sleeve, thereby improving the wear resistance of the product and extending its service life.

[0027] The first mating surface has a different shape than the second mating surface. When the compressor is working under normal conditions, the first mating surface and the second mating surface with different shapes come into contact and fit together. The first mating surface and the second mating surface can achieve line contact or point contact locally, which helps to avoid stress concentration, optimize stress distribution, and achieve the purpose of stress buffering.

[0028] In some technical solutions, optionally, the first mating surface extends from the axial end face of the eccentric segment away from the main body segment to the connection between the main body segment and the eccentric segment; the second mating surface extends from one axial end face of the eccentric sleeve to the other axial end face of the eccentric sleeve.

[0029] In this technical solution, the arrangement positions of the first mating surface and the second mating surface are refined.

[0030] The first mating surface extends axially from the side of the eccentric segment away from the main body segment to the connection between the main body segment and the eccentric segment.

[0031] The eccentric sleeve has two opposing axial end faces, and the second mating surface extends from one axial end face of the eccentric sleeve to the other axial end face of the eccentric sleeve.

[0032] It is understandable that the crankshaft can drive the eccentric sleeve to rotate, but the eccentric sleeve cannot rotate relative to the crankshaft. Therefore, by reasonably setting the arrangement of the first mating surface and the second mating surface, it is possible to ensure that the first mating surface and the second mating surface have sufficient mating length in the axial direction of the crankshaft, which can ensure the stable force transmission area and effectively prevent the eccentric sleeve from rotating relative to the crankshaft.

[0033] Furthermore, by rationally setting the axial positions of the first and second mating surfaces on the crankshaft, it can be ensured that the eccentric sleeve is circumferentially limited in the axial direction of the crankshaft, further guaranteeing the stability and reliability of the overall structural fit. Simultaneously, the precise positioning of the first and second mating surfaces simplifies the assembly of the eccentric sleeve and crankshaft, facilitating mass production and reducing product manufacturing costs.

[0034] In some technical solutions, optionally, the outer peripheral wall of the eccentric section is provided with a first positioning part, and the inner peripheral wall of the eccentric sleeve is provided with a second positioning part; one of the first positioning part and the second positioning part is a groove, and the other is a convex part, the convex part is inserted into the groove, and the convex part and the groove are in clearance fit; the groove extends from the axial end face of one of the eccentric section and the eccentric sleeve along the axial direction of the eccentric section.

[0035] In this technical solution, the outer peripheral wall of the eccentric segment is provided with a first positioning part, and the inner peripheral wall of the eccentric sleeve is provided with a second positioning part. One of the first and second positioning parts is a groove, and the other is a protrusion. That is, the outer peripheral wall of the eccentric segment has a groove, and the inner peripheral wall of the eccentric sleeve has a protrusion. The protrusion is inserted into the groove, and the protrusion and groove are in a clearance fit. Alternatively, the outer peripheral wall of the eccentric segment has a protrusion, and the inner peripheral wall of the eccentric sleeve has a groove. The protrusion is inserted into the groove, and the protrusion and groove are in a clearance fit.

[0036] The groove extends axially from the axial end face of either the eccentric section or the eccentric sleeve along the axial direction of the eccentric section. When the groove is provided on the outer peripheral wall of the eccentric section, it extends axially from one side of the eccentric section's axial end face along the axial direction of the eccentric section, with the groove spaced apart from the other side's axial end face; or the groove extends from one side of the eccentric section's axial end face to the connection between the eccentric section and the main body section. When the groove is provided on the inner peripheral wall of the eccentric sleeve, it extends axially from one side of the eccentric sleeve's axial end face along the axial direction of the eccentric section, with the groove spaced apart from the other side's axial end face; or the groove extends from one side of the eccentric sleeve's axial end face to the other side's axial end face.

[0037] The first and second positioning parts work together to prevent misalignment and achieve directional assembly. They limit the assembly positions of the first and second mating surfaces, reducing the number of assembly steps required for their alignment. In other words, the first and second positioning parts work together to restrict the assembly positions of the crankshaft and eccentric sleeve, preventing compressor failure due to misalignment of the eccentric sleeve. This simplifies the compressor assembly process, reduces assembly difficulty, improves assembly efficiency and yield, ensures the compressor achieves the preset eccentricity during operation, guarantees smooth and effective operation, and enhances the compressor's performance and market competitiveness.

[0038] Understandably, the groove extends axially along the crankshaft from the axial end face of either the crankshaft or the eccentric sleeve. Therefore, when assembling the eccentric sleeve and crankshaft, the convex part can be inserted into the groove simply by fitting the eccentric sleeve onto one side of the crankshaft, providing ease of assembly. The cooperation between the convex part and the groove not only restricts the displacement of the eccentric sleeve relative to the crankshaft in the circumferential direction of the eccentric section, but also meets the requirement that the moving scroll will drive the eccentric sleeve to move radially along the eccentric section when liquid refrigerant or impurities enter the compressor's compression chamber.

[0039] In some technical solutions, optionally, the plurality of first mating surfaces include at least a first driving mating surface and a first non-driving mating surface; at least one of the first driving mating surface and the first non-driving mating surface is provided with a first positioning part.

[0040] In this technical solution, the types of multiple first mating surfaces are specified, and the multiple first mating surfaces include at least a first driving mating surface and a first non-driving mating surface.

[0041] The second mating surface that mates with the first driving mating surface is called the second driving mating surface, and the second mating surface that mates with the first non-driving mating surface is called the second non-driving mating surface.

[0042] When the compressor operates under normal conditions, the first driving mating surface and the second driving mating surface are positioned opposite each other, and the first non-driving mating surface and the second non-driving mating surface are positioned opposite each other. The second driving mating surface and the first driving mating surface are in contact and mutually restrictive engagement. The first non-driving mating surface and the second non-driving mating surface have a gap in the radial direction of the eccentric section. The crankshaft rotates to apply a driving force to the second driving mating surface of the eccentric sleeve through the first driving mating surface of the eccentric section. Under the combined action of the driving force and the centrifugal force of the moving scroll, the moving scroll meshes with the stationary scroll, keeping the compressor in a state of fixed eccentricity.

[0043] At least one of the first driving mating surface and the first non-driving mating surface is provided with a first positioning part. That is, the first driving mating surface is provided with a first positioning part, or the first non-driving mating surface is provided with a first positioning part, or both the first driving mating surface and the first non-driving mating surface are provided with a first positioning part. Therefore, at least one of the first driving mating surface and the first non-driving mating surface serves as the carrier of the first positioning part. The first positioning part and the second positioning part cooperate to function as positioning markers. When assembling the eccentric sleeve and the crankshaft, the positional relationship between the first driving mating surface and the second driving mating surface, as well as the positional relationship between the first non-driving mating surface and the second non-driving mating surface, can be indirectly defined by the alignment of the first positioning part and the second positioning part. This prevents situations where the first driving mating surface and the second non-driving mating surface are opposite each other, or where the first non-driving mating surface and the second driving mating surface are opposite each other. This reduces the assembly difficulty of the compressor, improves the assembly efficiency and yield rate of the compressor, ensures that the compressor can obtain the preset eccentricity during operation, guarantees the smoothness and effectiveness of the compressor's operation, and improves the compressor's performance and market competitiveness.

[0044] When only the first non-driving mating surface is provided with the first positioning part, it not only has the effect of preventing mistakes, but also does not encroach on the area of ​​the first driving mating surface and the second driving mating surface. When the compressor is working under normal conditions, it is beneficial to increase the contact area of ​​the first driving mating surface and the second driving mating surface, and provides reliable structural support for ensuring the stability and reliability of the compressor operation.

[0045] Specifically, when the compressor is working under normal operating conditions, the second driving mating surface and the first driving mating surface contact and limit the mating, the first non-driving mating surface and the second non-driving mating surface have a gap in the radial direction of the eccentric section, and the portion of the outer peripheral wall of the eccentric section located between the first driving mating surface and the first non-driving mating surface has a gap with the portion of the inner peripheral wall of the eccentric sleeve located between the second driving mating surface and the second non-driving mating surface.

[0046] In some technical solutions, optionally, the plurality of first mating surfaces include at least a first driving mating surface and a first non-driving mating surface; the portion of the outer peripheral wall of the eccentric segment located between the first driving mating surface and the first non-driving mating surface is provided with a first positioning part.

[0047] In this technical solution, the types of multiple first mating surfaces are specified, and the multiple first mating surfaces include at least a first driving mating surface and a first non-driving mating surface.

[0048] The second mating surface that mates with the first driving mating surface is called the second driving mating surface, and the second mating surface that mates with the first non-driving mating surface is called the second non-driving mating surface.

[0049] The portion of the outer peripheral wall of the eccentric segment located between the first driving mating surface and the first non-driving mating surface is provided with a first positioning part. That is, the portion of the outer peripheral wall of the eccentric segment located between the first driving mating surface and the first non-driving mating surface serves as the carrier of the first positioning part. Since the first positioning part and the second positioning part are used in conjunction, the portion of the inner peripheral wall of the eccentric sleeve located between the second driving mating surface and the second non-driving mating surface is provided with a second positioning part.

[0050] The first and second positioning parts cooperate to serve as positioning markers. When assembling the eccentric sleeve and crankshaft, the alignment of the first and second positioning parts indirectly limits the positional relationship between the first and second driving mating surfaces, as well as the positional relationship between the first and second non-driving mating surfaces. This prevents situations where the first driving mating surface and the second non-driving mating surface are opposite each other, or where the first non-driving mating surface and the second driving mating surface are opposite each other. This reduces the assembly difficulty of the compressor, improves the assembly efficiency and yield rate of the compressor, ensures that the compressor can obtain the preset eccentricity during operation, guarantees the smoothness and effectiveness of the compressor's operation, and helps improve the compressor's performance and market competitiveness.

[0051] In some technical solutions, optionally, the first driving mating surface and the first non-driving mating surface are arranged opposite each other along the radial direction of the eccentric segment.

[0052] In this technical solution, the positional relationship between the first driving mating surface and the first non-driving mating surface is refined. Specifically, along the radial direction of the eccentric segment, the first driving mating surface and the first non-driving mating surface are arranged opposite to each other. The first driving mating surface and the first non-driving mating surface bear radial force components in opposite directions, which can cancel each other out or reduce bending moment, making the force distribution more uniform and helping to reduce eccentric loading and deformation.

[0053] Along the radial direction of the eccentric section, the first driving mating surface and the first non-driving mating surface are arranged opposite each other, which makes the contact reaction force between the eccentric sleeve and the crankshaft symmetrical in the radial direction of the eccentric section. This can reduce the tilting or vibration of the moving scroll caused by force imbalance, and make the compressor run more smoothly, which is beneficial to reducing operating noise and mechanical wear.

[0054] In some technical solutions, optionally, the second mating surface corresponding to the first driving mating surface is denoted as the second driving mating surface, and the second mating surface corresponding to the first non-driving mating surface is denoted as the second non-driving mating surface; when the first non-driving mating surface is provided with a groove, on the longitudinal section of the compressor, the outline of the groove is "L" shaped, the distance from the outline of the portion of the first non-driving mating surface located on the periphery of the groove to the outline of the first driving mating surface is A, the distance from the outline of the first driving mating surface to the outline of the groove is B, the length of the outline of the portion of the first non-driving mating surface located between the groove and the main body section is C, the distance from the outline of the portion of the second non-driving mating surface located on the periphery of the convex part to the outline of the second driving mating surface is A1, the minimum distance from the outline of the second driving mating surface to the outline of the convex part is B1, and the length of the outline of the portion of the second non-driving mating surface located between the convex part and the main body section is C1; wherein, A1 > A, B1 > B, C1 > C, and the axis of the eccentric section is located on the plane of the longitudinal section of the compressor.

[0055] In this technical solution, the second mating surface corresponding to the first driving mating surface is denoted as the second driving mating surface, and the second mating surface corresponding to the first non-driving mating surface is denoted as the second non-driving mating surface. The mating structure of the groove, the first driving mating surface, the first non-driving mating surface, the second driving mating surface, and the second non-driving mating surface is further refined.

[0056] When the first non-driving mating surface has a groove, on the longitudinal section of the compressor, the axis of the eccentric section is located on the plane where the longitudinal section of the compressor is located, and the outline of the groove is "L" shaped. That is, the groove and the protrusion mate to form an "L" shaped overlock.

[0057] Along the radial direction of the eccentric section, there is a gap between the groove and the convex part, and a gap between the outer peripheral wall of the eccentric section and the inner peripheral wall of the eccentric sleeve. Specifically, in the longitudinal section of the compressor, the distance from the outline of the portion of the first non-driving mating surface located on the periphery of the groove to the outline of the first driving mating surface is denoted as A. In the longitudinal section of the compressor, the distance from the outline of the first driving mating surface to the outline of the groove is denoted as B. In the longitudinal section of the compressor, the length of the outline of the portion of the first non-driving mating surface located between the groove and the main body section is denoted as C. In the longitudinal section of the compressor, the distance from the outline of the portion of the second non-driving mating surface located on the periphery of the convex part to the outline of the second driving mating surface is denoted as A1. In the longitudinal section of the compressor, the minimum distance from the outline of the second driving mating surface to the outline of the convex part is denoted as B1. In the longitudinal section of the compressor, the length of the outline of the portion of the second non-driving mating surface located between the convex part and the main body section is denoted as C1. Wherein, A1>A, B1>B, C1>C.

[0058] This ensures smoother assembly of the crankshaft and eccentric assembly, avoids interference, improves assembly efficiency, reduces the requirements for parts machining precision, and meets the stability and reliability requirements of the compressor under different operating conditions.

[0059] In some technical solutions, optionally, a clearance groove is provided at the connection between the axial end face of the eccentric sleeve facing the main body section and the inner peripheral wall of the eccentric sleeve. The clearance groove is arranged around the eccentric section, and the connection between the main body section and the eccentric section is arranged opposite to the clearance groove.

[0060] In this technical solution, the mating structure of the crankshaft and the eccentric sleeve is refined.

[0061] The outer wall of the main body protrudes beyond the outer wall of the eccentric section. That is, the outer diameter of the main body is larger than the outer diameter of the eccentric sleeve, and the main body and the eccentric section enclose a stepped structure.

[0062] An avoidance groove is provided at the connection between the axial end face of the eccentric sleeve facing the main body section and the inner peripheral wall of the eccentric sleeve. The connection between the main body section and the eccentric section is opposite to the avoidance groove. The avoidance groove is used to avoid the structure of the connection between the main body section and the eccentric section to avoid interference, so that after the eccentric sleeve is fitted onto the eccentric section, the eccentric sleeve can abut against the axial end face of the main body section.

[0063] The clearance groove is set around the eccentric section. The clearance groove can avoid the structure at the connection between the main body section and the eccentric section in all directions, ensuring the effective fit size between the eccentric sleeve and the crankshaft, and providing structural support for the stable operation of the compressor.

[0064] In addition, by setting up a clearance groove, a small amount of lubricating oil and impurities can enter the clearance groove when the compressor is running, and the clearance groove can serve as a storage space for lubricating oil and impurities.

[0065] In some technical solutions, optionally, a chamfer is provided at the connection between the main body section and the eccentric section; on the longitudinal section of the compressor, the outline of the chamfer is located between the two endpoints of the outline of the clearance groove; wherein, the axis of the eccentric section is located on the plane of the longitudinal section of the compressor.

[0066] In this technical solution, the mating structure of the main body section, the eccentric section, and the eccentric sleeve is refined.

[0067] A chamfer is provided at the connection between the main body section and the eccentric section. On the longitudinal section of the compressor, the axis of the eccentric section lies on the plane containing the compressor's longitudinal section, and the contour line of the chamfer lies between the two endpoints of the contour line of the clearance groove. That is, the positional relationship between the chamfer and the clearance groove is defined, ensuring that the chamfer is located within the space enclosed by the clearance groove, and that the clearance groove completely avoids the chamfer at the connection between the main body section and the eccentric section, preventing interference. This allows the eccentric sleeve, after being fitted onto the eccentric section, to abut against the axial end face of the main body section, ensuring an effective fit between the eccentric sleeve and the crankshaft.

[0068] In addition, a chamfer is provided at the connection between the main body section and the eccentric section. The chamfer structure allows for a smooth transition at the connection between the main body section and the eccentric section, reducing stress concentration, which helps to improve the service life of the product and reduce operating noise and mechanical wear.

[0069] The second aspect of this application provides a refrigeration device, comprising: the compressor described in the first aspect.

[0070] The refrigeration equipment provided in this application includes a compressor as described in the first aspect, and therefore has all the beneficial effects of the compressor, which will not be described in detail here.

[0071] For example, refrigeration equipment includes air conditioners, refrigerators, or freezers.

[0072] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0073] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0074] Figure 1 This invention provides a schematic diagram of the first part of the structure of a compressor from a first perspective, representing an embodiment of the present application.

[0075] Figure 2 A schematic diagram of the first part of the compressor structure from a second perspective of one embodiment of this application is shown;

[0076] Figure 3 A partial structural schematic diagram of a crankshaft according to an embodiment of this application is shown from a first-view perspective.

[0077] Figure 4 A partial structural schematic diagram of a crankshaft from a second perspective of one embodiment of this application is shown;

[0078] Figure 5 This invention provides a first-view structural schematic diagram of an eccentric sleeve according to an embodiment of the present application.

[0079] Figure 6 This invention provides a schematic diagram of the structure of an eccentric sleeve from a second perspective, representing an embodiment of the present application.

[0080] Figure 7 A third-view structural schematic diagram of an eccentric sleeve according to an embodiment of this application is shown;

[0081] Figure 8A schematic diagram of the second part of the compressor according to an embodiment of this application is shown;

[0082] Figure 9 A schematic diagram of the structure of a refrigeration device according to an embodiment of this application is shown.

[0083] Figure label:

[0084] 10 Compressor, 12 Longitudinal section of compressor, 100 Crankshaft, 110 Main body section, 120 Eccentric section, 122 First mating surface, 122a First driving mating surface, 122b First non-driving mating surface, 124 Axis of eccentric section, 130 First positioning part, 140 Chamfer, 200 Eccentric sleeve, 210 Second mating surface, 210a Second driving mating surface, 210b Second non-driving mating surface, 220 Second positioning part, 230 Clearance groove, 300 Bearing, 400 Moving scroll, 50 Refrigeration equipment, 510 Detection module, 520 Mode switching module, 530 Controller. Detailed Implementation

[0085] The embodiments of this utility model will now be described in detail. Examples of these embodiments are shown 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 are only used to explain this utility model, and should not be construed as limiting this utility model. All other embodiments obtained by those skilled in the art based on the embodiments in this application without inventive effort are within the scope of protection of this application.

[0086] The terms "first" and "second" in the specification and claims of this application may explicitly or implicitly include one or more of the features. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0087] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0088] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0089] The following is combined Figures 1 to 9 The compressor 10 and refrigeration equipment 50 of this utility model are described in an embodiment.

[0090] like Figure 1 , Figure 2 , Figure 3 , Figure 5 and Figure 8 As shown, the compressor 10 according to some embodiments of the present invention includes: a crankshaft 100, along the axial direction of the crankshaft 100, the crankshaft 100 includes a main body section 110 and an eccentric section 120 connected to each other, the outer peripheral wall of the main body section 110 protrudes from the outer peripheral wall of the eccentric section 120, the outer peripheral wall of the eccentric section 120 includes a plurality of spaced first mating surfaces 122 in the circumferential direction of the eccentric section 120; an eccentric sleeve 200, sleeved on the eccentric section 120, the inner peripheral wall of the eccentric sleeve 200 having... Multiple second mating surfaces 210, each second mating surface 210 is disposed opposite to a first mating surface 122, the first mating surface 122 and the second mating surface 210 are mated to limit the displacement of the eccentric sleeve 200 relative to the crankshaft 100 along the circumferential direction of the eccentric segment 120; bearing 300; moving scroll 400, the moving scroll 400 is connected to the outer peripheral wall of the eccentric sleeve 200 through the bearing 300; wherein, the inner peripheral wall of the eccentric sleeve 200 and the outer peripheral wall of the eccentric segment 120 are clearance-fitted.

[0091] According to an embodiment of the present invention, the compressor 10 includes a crankshaft 100, an eccentric sleeve 200, a bearing 300, and a moving scroll 400.

[0092] The crankshaft 100 includes a main body section 110 and an eccentric section 120, which are connected. Along the axial direction of the crankshaft 100, the main body section 110 is located on one side of the eccentric section 120.

[0093] The eccentric sleeve 200 is fitted onto the eccentric section 120, and the moving scroll 400 is connected to the outer peripheral wall of the eccentric sleeve 200 through the bearing 300.

[0094] The outer peripheral wall of the eccentric segment 120 includes a plurality of first mating surfaces 122. The plurality of first mating surfaces 122 are arranged at intervals along the circumference of the eccentric segment 120.

[0095] The inner circumferential wall of the eccentric sleeve 200 is provided with a plurality of second mating surfaces 210, which are arranged at intervals along the circumference of the eccentric section 120. The plurality of second mating surfaces 210 and a plurality of first mating surfaces 122 cooperate with each other. Specifically, each second mating surface 210 is opposite to a first mating surface 122. The first mating surfaces 122 and the second mating surfaces 210 cooperate to limit the displacement of the eccentric sleeve 200 relative to the crankshaft 100 along the circumference of the eccentric section 120, so that the crankshaft 100 drives the driven scroll 400 to rotate relative to the stationary scroll of the compressor 10 through the eccentric sleeve 200 and the bearing 300, thereby compressing the refrigerant in the compression chamber of the compressor 10.

[0096] The inner peripheral wall of the eccentric sleeve 200 and the outer peripheral wall of the eccentric section 120 are in clearance fit, that is, there is a gap between the inner peripheral wall of the eccentric sleeve 200 and the outer peripheral wall of the eccentric section 120 along the radial direction of the eccentric section 120.

[0097] When the compressor 10 is working under normal operating conditions, a second mating surface 210 of the eccentric sleeve 200 and a first mating surface 122 of the crankshaft 100 come into contact and are in a limiting fit. The crankshaft 100 rotates to apply a driving force to the second mating surface 210 of the eccentric sleeve 200 through the first mating surface 122 of the eccentric section 120. Under the dual action of the driving force and the centrifugal force of the moving scroll 400, the moving scroll 400 meshes with the stationary scroll, so that the compressor 10 is in a fixed eccentricity state.

[0098] When liquid refrigerant or impurities enter the compression chamber of compressor 10, the eccentricity of compressor 10 is adjustable due to the clearance fit between the inner circumferential wall of eccentric sleeve 200 and the outer circumferential wall of eccentric section 120. This means the eccentricity can be adaptively adjusted within a certain range. When the resultant force of the driving force and the centrifugal force of the moving scroll 400 is less than the radial thrust on the moving scroll 400, the moving scroll 400 will drive the eccentric sleeve 200 to move radially along the eccentric section 120. This protects the scroll teeth of both the moving scroll 400 and the stationary scroll, preventing damage to the scroll teeth. By reducing frictional power consumption, this improves the stability and reliability of compressor 10 operation, thus enhancing its performance and market competitiveness.

[0099] It is understandable that the first mating surface 122 and the second mating surface 210 cooperate to limit the mating dimensions of the crankshaft 100 and the eccentric sleeve 200. This restricts the displacement of the eccentric sleeve 200 relative to the crankshaft 100 along the circumferential direction of the eccentric segment 120, indirectly limiting the mating dimensions of the moving scroll 400 and the crankshaft 100. This provides reliable structural support for the moving scroll 400 to perform translational rotation relative to the stationary scroll, ensuring the accuracy of the moving scroll 400's motion trajectory without affecting volumetric efficiency and performance. Although the eccentric sleeve 200 and the crankshaft 100 can be limited circumferentially by the interaction of the first mating surface 122 and the second mating surface 210, the eccentric sleeve 200 and the eccentric segment 120 have a clearance fit in the radial direction of the eccentric segment 120. Therefore, the eccentric sleeve 200 can have slight floating or displacement relative to the eccentric segment 120. When liquid refrigerant or impurities enter the compression chamber of compressor 10, the gap between eccentric sleeve 200 and eccentric section 120 can absorb some of the impact energy, preventing all impact forces from being directly transmitted to bearing 300 and moving scroll 400, thus providing overload protection.

[0100] Understandably, when liquid refrigerant or impurities enter the compression chamber of compressor 10, the eccentric sleeve 200 can float or shift slightly relative to the eccentric section 120, which can reduce the peak torque transmitted to crankshaft 100 and moving scroll 400, protect the lubricating film from damage, avoid shaft burnout or even tooth breakage, and improve the compressor 10's resistance to liquid slugging and impurities.

[0101] It is understandable that when the compressor 10 is in a fixed eccentricity state, the relative positions of the eccentric sleeve 200 and the eccentric section 120 are fixed.

[0102] It is understandable that the adjustable eccentricity of compressor 10 refers to the fact that the relative positions of eccentric sleeve 200 and eccentric section 120 can be adjusted.

[0103] It is understandable that a compression cavity is formed between the stationary volute and the moving volute 400.

[0104] According to some embodiments of the present invention, the first mating surface 122 includes at least one of a plane and an arc surface; and / or the second mating surface 210 includes at least one of a plane and an arc surface.

[0105] Specifically, the shapes of the first mating surface 122 and the second mating surface 210 are refined.

[0106] The first mating surface 122 includes at least one of a plane and an arc surface; that is, the first mating surface 122 includes a plane, or the first mating surface 122 includes an arc surface, or the first mating surface 122 includes both a plane and an arc surface. The structural design of the first mating surface 122 facilitates processing and manufacturing, and helps to reduce production costs.

[0107] The second mating surface 210 includes at least one of a plane and an arc surface. That is, the second mating surface 210 includes a plane, or the second mating surface 210 includes an arc surface, or the second mating surface 210 includes both a plane and an arc surface. The structural configuration of the second mating surface 210 facilitates processing and manufacturing, and helps to reduce production costs.

[0108] When the compressor 10 is working under normal conditions, a second mating surface 210 of the eccentric sleeve 200 and a first mating surface 122 of the crankshaft 100 fit and limit each other in the circumferential direction of the eccentric section 120, so as to effectively limit the displacement of the eccentric sleeve 200 relative to the crankshaft 100 and provide reliable structural support for ensuring the motion trajectory of the moving scroll 400.

[0109] When at least one of the first mating surface 122 and the second mating surface 210 includes a plane, the contact between the first mating surface 122 and the second mating surface 210 can be a line contact or a small area of ​​surface contact, which is beneficial to improving the accuracy of the contact between the first mating surface 122 and the second mating surface 210.

[0110] When at least one of the first mating surface 122 and the second mating surface 210 includes an arc surface, the contact area of ​​the first mating surface 122 and the second mating surface 210 will be relatively large, which can make the load distribution more uniform, reduce stress concentration, improve the wear resistance of the structure, and ensure the service life of the product. At the same time, it can also reduce the assembly accuracy requirements of the eccentric sleeve 200 and the crankshaft 100. Even with a small angular deviation, the first mating surface 122 and the second mating surface 210 can still be effectively contacted and limited, which is conducive to improving assembly efficiency.

[0111] According to some embodiments of the present invention, at least a portion of the shape of the first mating surface 122 is the same as the shape of the second mating surface 210; or the shape of the first mating surface 122 is different from the shape of the second mating surface 210.

[0112] Specifically, at least a portion of the shape of the first mating surface 122 is the same as the shape of the second mating surface 210. That is, a portion of the shape of the first mating surface 122 is the same as the shape of the second mating surface 210, or the shapes of the first mating surface 122 and the second mating surface 210 are completely identical. This increases the contact area between the first mating surface 122 and the second mating surface 210. When the compressor 10 operates under normal conditions, one first mating surface 122 and one second mating surface 210 are in contact. Specifically, the contact of at least a portion of the first mating surface 122 and the second mating surface 210 with the same shape enables precise fitting of the first mating surface 122 and the second mating surface 210, improves the degree of contact fit, provides more stable positioning in the circumferential direction of the eccentric segment 120, ensures contact stability, reduces shaking or relative displacement, and also helps reduce the local contact stress between the eccentric segment 120 and the eccentric sleeve 200, which is beneficial for improving the wear resistance of the product and extending its service life.

[0113] The shape of the first mating surface 122 is different from that of the second mating surface 210. When the compressor 10 is working under normal conditions, the first mating surface 122 and the second mating surface 210 with different shapes come into contact and fit together. The first mating surface 122 and the second mating surface 210 can achieve line contact or point contact in some areas, which helps to avoid stress concentration, optimize stress distribution, and achieve the purpose of stress buffering.

[0114] According to some embodiments of the present invention, the first mating surface 122 extends from the axial end face of the eccentric segment 120 away from the main body segment 110 to the connection between the main body segment 110 and the eccentric segment 120; the second mating surface 210 extends from one axial end face of the eccentric sleeve 200 to the other axial end face of the eccentric sleeve 200.

[0115] Specifically, the arrangement of the first mating surface 122 and the second mating surface 210 is refined.

[0116] The first mating surface 122 extends from the axial end face of the eccentric segment 120 away from the main body segment 110 to the connection between the main body segment 110 and the eccentric segment 120.

[0117] The eccentric sleeve 200 has two opposing axial end faces, and the second mating surface 210 extends from one axial end face of the eccentric sleeve 200 to the other axial end face of the eccentric sleeve 200.

[0118] It is understandable that the crankshaft 100 can drive the eccentric sleeve 200 to rotate, but the eccentric sleeve 200 cannot rotate relative to the crankshaft 100. Therefore, by reasonably setting the arrangement of the first mating surface 122 and the second mating surface 210, it can be ensured that the first mating surface 122 and the second mating surface 210 have sufficient mating length in the axial direction of the crankshaft 100, which can ensure the stable force transmission area and effectively prevent the eccentric sleeve 200 from rotating relative to the crankshaft 100.

[0119] Furthermore, by rationally setting the axial positions of the first mating surface 122 and the second mating surface 210 on the crankshaft 100, the eccentric sleeve 200 can be circumferentially limited in the axial direction of the crankshaft 100, further ensuring the stability and reliability of the overall structural fit. Simultaneously, the positional arrangement of the first mating surface 122 and the second mating surface 210 simplifies the assembly of the eccentric sleeve 200 and the crankshaft 100, facilitating mass production and reducing product manufacturing costs.

[0120] According to some embodiments of the present invention, such as Figure 1 , Figure 3 , Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, the outer peripheral wall of the eccentric section 120 is provided with a first positioning part 130, and the inner peripheral wall of the eccentric sleeve 200 is provided with a second positioning part 220; one of the first positioning part 130 and the second positioning part 220 is a groove, and the other is a protrusion. The protrusion is inserted into the groove, and the protrusion and the groove are in clearance fit; the groove extends from the axial end face of one of the eccentric section 120 and the eccentric sleeve 200 along the axial direction of the eccentric section 120.

[0121] Specifically, the outer peripheral wall of the eccentric segment 120 is provided with a first positioning part 130, and the inner peripheral wall of the eccentric sleeve 200 is provided with a second positioning part 220. One of the first positioning part 130 and the second positioning part 220 is a groove, and the other is a protrusion. That is, the outer peripheral wall of the eccentric segment 120 is provided with a groove, and the inner peripheral wall of the eccentric sleeve 200 is provided with a protrusion. The protrusion is inserted into the groove, and the protrusion and the groove are in clearance fit. Alternatively, the outer peripheral wall of the eccentric segment 120 is provided with a protrusion, and the inner peripheral wall of the eccentric sleeve 200 is provided with a groove. The protrusion is inserted into the groove, and the protrusion and the groove are in clearance fit.

[0122] In this configuration, the groove extends axially from the axial end face of either the eccentric segment 120 or the eccentric sleeve 200 along the axial direction of the eccentric segment 120. When the groove is provided on the outer peripheral wall of the eccentric segment 120, the groove extends axially from one side of the eccentric segment 120 along the axial direction of the eccentric segment 120, and the groove is spaced apart from the other side of the eccentric segment 120; alternatively, the groove extends from one side of the eccentric segment 120 to the connection between the eccentric segment 120 and the main body segment 110. When the groove is provided on the inner peripheral wall of the eccentric sleeve 200, the groove extends axially from one side of the eccentric sleeve 200 along the axial direction of the eccentric segment 120, and the groove is spaced apart from the other side of the eccentric sleeve 200; alternatively, the groove extends from one side of the eccentric sleeve 200 to the other side of the eccentric sleeve 200.

[0123] The first positioning part 130 and the second positioning part 220 cooperate to prevent mistaken assembly and achieve directional assembly. They limit the assembly position of the first mating surface 122 and the second mating surface 210, reducing the assembly steps required to align the first mating surface 122 and the second mating surface 210. In other words, the cooperation of the first positioning part 130 and the second positioning part 220 restricts the assembly position of the crankshaft 100 and the eccentric sleeve 200, preventing the compressor 10 from failing due to misalignment of the eccentric sleeve 200 assembly direction. This simplifies the assembly steps of the compressor 10, reduces the assembly difficulty of the compressor 10, and helps improve the assembly efficiency and yield of the compressor 10. It also ensures that the compressor 10 can obtain the preset eccentricity during operation, ensuring the smoothness and effectiveness of the compressor 10's operation, and ultimately improving the performance and market competitiveness of the compressor 10.

[0124] It is understandable that the groove extends axially along the crankshaft 100 from the axial end face of either the crankshaft 100 or the eccentric sleeve 200. Therefore, when assembling the eccentric sleeve 200 and the crankshaft 100, the convex part can be inserted into the groove simply by fitting the eccentric sleeve 200 onto one side of the crankshaft 100, which provides convenient assembly. The cooperation between the convex part and the groove not only restricts the displacement of the eccentric sleeve 200 relative to the crankshaft 100 in the circumferential direction along the eccentric section 120, but also meets the requirement that the moving scroll 400 will drive the eccentric sleeve 200 to move radially along the eccentric section 120 when liquid refrigerant or impurities enter the compression chamber of the compressor 10.

[0125] For example, when a groove is provided on the outer peripheral wall of the eccentric section 120, the protrusion extends from one axial end face of the eccentric sleeve 200 along the axial direction of the eccentric section 120, and the protrusion is spaced apart from the other axial end face of the eccentric sleeve 200.

[0126] For example, when a groove is provided on the outer peripheral wall of the eccentric section 120, the protrusion is located between the two axial end faces of the eccentric sleeve 200.

[0127] For example, when a groove is provided on the inner peripheral wall of the eccentric sleeve 200, the protrusion extends from one axial end face of the eccentric section 120 along the axial direction of the eccentric section 120, and the protrusion is spaced apart from the connection between the eccentric section 120 and the main body section 110.

[0128] For example, when a groove is provided on the inner peripheral wall of the eccentric sleeve 200, the protrusion is located between the axial end face of the eccentric section 120 and the connection between the eccentric section 120 and the main body section 110.

[0129] According to some embodiments of the present invention, the plurality of first mating surfaces 122 include at least a first driving mating surface 122a and a first non-driving mating surface 122b; at least one of the first driving mating surface 122a and the first non-driving mating surface 122b is provided with a first positioning part 130.

[0130] Specifically, the types of the plurality of first mating surfaces 122 are further refined, and the plurality of first mating surfaces 122 include at least a first driving mating surface 122a and a first non-driving mating surface 122b.

[0131] The second mating surface 210 used in conjunction with the first driving mating surface 122a is denoted as the second driving mating surface 210a, and the second mating surface 210 used in conjunction with the first non-driving mating surface 122b is denoted as the second non-driving mating surface 210b.

[0132] When the compressor 10 is operating under normal conditions, the first driving mating surface 122a and the second driving mating surface 210a are positioned opposite each other, and the first non-driving mating surface 122b and the second non-driving mating surface 210b are positioned opposite each other. The second driving mating surface 210a and the first driving mating surface 122a are in contact and mutually restrictive fit. The first non-driving mating surface 122b and the second non-driving mating surface 210b have a gap in the radial direction of the eccentric section 120. The crankshaft 100 rotates to apply a driving force to the second driving mating surface 210a of the eccentric sleeve 200 through the first driving mating surface 122a of the eccentric section 120. Under the combined action of the driving force and the centrifugal force of the moving scroll 400, the moving scroll 400 meshes with the stationary scroll, so that the compressor 10 is in a state of fixed eccentricity.

[0133] At least one of the first driving mating surface 122a and the first non-driving mating surface 122b is provided with a first positioning part 130. That is, the first driving mating surface 122a is provided with a first positioning part 130, or the first non-driving mating surface 122b is provided with a first positioning part 130, or both the first driving mating surface 122a and the first non-driving mating surface 122b are provided with a first positioning part 130. Therefore, at least one of the first driving mating surface 122a and the first non-driving mating surface 122b serves as the carrier of the first positioning part 130. The first positioning part 130 and the second positioning part 220 cooperate to serve as positioning markers. When assembling the eccentric sleeve 200 and the crankshaft 100, the positional relationship between the first driving mating surface 122a and the second driving mating surface 210a, as well as the positional relationship between the first non-driving mating surface 122b and the second non-driving mating surface 210b, can be indirectly limited by the alignment of the first positioning part 130 and the second positioning part 220. This prevents the first driving mating surface 122a from being opposite to the second non-driving mating surface 210b, and the first non-driving mating surface 122b from being opposite to the second driving mating surface 210a. This reduces the assembly difficulty of the compressor 10, improves the assembly efficiency and yield of the compressor 10, ensures that the compressor 10 can obtain the preset eccentricity during operation, and ensures the smoothness and effectiveness of the compressor 10's operation. This is beneficial to improving the performance and market competitiveness of the compressor 10.

[0134] When only the first non-driving mating surface 122b is provided with the first positioning part 130, it not only has the effect of preventing mistakes, but also does not encroach on the area of ​​the first driving mating surface 122a and the second driving mating surface 210a. When the compressor 10 is working under normal operating conditions, it is beneficial to increase the contact area of ​​the first driving mating surface 122a and the second driving mating surface 210a, and provides reliable structural support for ensuring the stability and reliability of the compressor 10 operation.

[0135] Specifically, when the compressor 10 is operating under normal conditions, the second driving mating surface 210a and the first driving mating surface 122a contact and limit the mating, the first non-driving mating surface 122b and the second non-driving mating surface 210b have a gap in the radial direction of the eccentric section 120, and the portion of the outer peripheral wall of the eccentric section 120 located between the first driving mating surface 122a and the first non-driving mating surface 122b has a gap with the portion of the inner peripheral wall of the eccentric sleeve 200 located between the second driving mating surface 210a and the second non-driving mating surface 210b.

[0136] For example, there is one first driving mating surface 122a and one second driving mating surface 210a.

[0137] For example, the number of first non-driving mating surfaces 122b is at least one, and the number of second non-driving mating surfaces 210b is at least one.

[0138] According to some embodiments of the present invention, the plurality of first mating surfaces 122 include at least a first driving mating surface 122a and a first non-driving mating surface 122b; the portion of the outer peripheral wall of the eccentric segment 120 located between the first driving mating surface 122a and the first non-driving mating surface 122b is provided with a first positioning portion 130.

[0139] Specifically, the types of the plurality of first mating surfaces 122 are further refined, and the plurality of first mating surfaces 122 include at least a first driving mating surface 122a and a first non-driving mating surface 122b.

[0140] The second mating surface 210 used in conjunction with the first driving mating surface 122a is denoted as the second driving mating surface 210a, and the second mating surface 210 used in conjunction with the first non-driving mating surface 122b is denoted as the second non-driving mating surface 210b.

[0141] The portion of the outer peripheral wall of the eccentric segment 120 located between the first driving mating surface 122a and the first non-driving mating surface 122b is provided with a first positioning part 130. That is, the portion of the outer peripheral wall of the eccentric segment 120 located between the first driving mating surface 122a and the first non-driving mating surface 122b serves as the carrier of the first positioning part 130. Since the first positioning part 130 and the second positioning part 220 are used in conjunction, the portion of the inner peripheral wall of the eccentric sleeve 200 located between the second driving mating surface 210a and the second non-driving mating surface 210b is provided with a second positioning part 220.

[0142] The first positioning part 130 and the second positioning part 220 cooperate to serve as positioning markers. When assembling the eccentric sleeve 200 and the crankshaft 100, the alignment of the first positioning part 130 and the second positioning part 220 indirectly limits the positional relationship between the first driving mating surface 122a and the second driving mating surface 210a, as well as the positional relationship between the first non-driving mating surface 122b and the second non-driving mating surface 210b. This prevents the first driving mating surface 122a from being opposite to the second non-driving mating surface 210b, and the first non-driving mating surface 122b from being opposite to the second driving mating surface 210a. This reduces the assembly difficulty of the compressor 10, improves the assembly efficiency and yield of the compressor 10, ensures that the compressor 10 can obtain the preset eccentricity during operation, and guarantees the smoothness and effectiveness of the compressor 10's operation. This also helps to improve the performance and market competitiveness of the compressor 10.

[0143] For example, along the circumferential direction of the eccentric segment 120, the first positioning part 130 is closer to the first driving mating surface 122a than the first non-driving mating surface 122b.

[0144] For example, along the circumferential direction of the eccentric segment 120, the first positioning part 130 is closer to the first non-driving mating surface 122b than the first driving mating surface 122a.

[0145] For example, there is one first driving mating surface 122a and one second driving mating surface 210a.

[0146] For example, the number of first non-driving mating surfaces 122b is at least one, and the number of second non-driving mating surfaces 210b is at least one.

[0147] According to some embodiments of the present invention, the first driving mating surface 122a and the first non-driving mating surface 122b are arranged opposite to each other along the radial direction of the eccentric segment 120.

[0148] Specifically, the positional relationship between the first driving mating surface 122a and the first non-driving mating surface 122b is refined. Specifically, along the radial direction of the eccentric segment 120, the first driving mating surface 122a and the first non-driving mating surface 122b are arranged opposite to each other. The first driving mating surface 122a and the first non-driving mating surface 122b bear radial force components in opposite directions, which can cancel each other out or reduce bending moments, resulting in a more uniform force distribution and helping to reduce eccentric loading and deformation.

[0149] Along the radial direction of the eccentric section 120, the first driving mating surface 122a and the first non-driving mating surface 122b are arranged opposite each other, which enables the contact reaction force between the eccentric sleeve 200 and the crankshaft 100 to be symmetrical in the radial direction of the eccentric section 120. This can reduce the tilting or vibration of the moving scroll 400 caused by force imbalance, and the compressor 10 can run more smoothly, which is beneficial to reducing operating noise and mechanical wear.

[0150] According to some embodiments of the present invention, such as Figure 3 and Figure 5As shown, the second mating surface 210 corresponding to the first driving mating surface 122a is denoted as the second driving mating surface 210a, and the second mating surface 210 corresponding to the first non-driving mating surface 122b is denoted as the second non-driving mating surface 210b. When the first non-driving mating surface 122b is provided with a groove, the outline of the groove is "L"-shaped on the longitudinal section 12 of the compressor. The distance from the outline of the portion of the first non-driving mating surface 122b located on the periphery of the groove to the outline of the first driving mating surface 122a is A, and the distance from the outline of the first driving mating surface 122a to the outline of the groove is B. The length of the outline of the portion of the non-driving mating surface 122b located between the groove and the main body section 110 is C. The distance from the outline of the portion of the second non-driving mating surface 210b located on the periphery of the protrusion to the outline of the second driving mating surface 210a is A1. The minimum distance from the outline of the second driving mating surface 210a to the outline of the protrusion is B1. The length of the outline of the portion of the second non-driving mating surface 210b located between the protrusion and the main body section 110 is C1. Wherein, A1 > A, B1 > B, C1 > C, and the axis 124 of the eccentric section is located on the plane of the longitudinal section 12 of the compressor.

[0151] Specifically, the second mating surface 210 corresponding to the first driving mating surface 122a is denoted as the second driving mating surface 210a, and the second mating surface 210 corresponding to the first non-driving mating surface 122b is denoted as the second non-driving mating surface 210b. The mating structure of the groove, the first driving mating surface 122a, the first non-driving mating surface 122b, the second driving mating surface 210a, and the second non-driving mating surface 210b is further refined.

[0152] When the first non-driving mating surface 122b is provided with a groove, on the longitudinal section 12 of the compressor, the axis 124 of the eccentric section is located on the plane where the longitudinal section 12 of the compressor is located, and the outline of the groove is "L" shaped. That is, the groove and the protrusion mate to form an "L" shaped overlock.

[0153] Along the radial direction of the eccentric section 120, there is a gap between the groove and the convex part, and a gap between the outer peripheral wall of the eccentric section 120 and the inner peripheral wall of the eccentric sleeve 200. Specifically, in the longitudinal section 12 of the compressor, the distance from the outline of the portion of the first non-driving mating surface 122b located on the periphery of the groove to the outline of the first driving mating surface 122a is denoted as A. In the longitudinal section 12 of the compressor, the distance from the outline of the first driving mating surface 122a to the outline of the groove is denoted as B. In the longitudinal section 12 of the compressor, the length of the outline of the portion of the first non-driving mating surface 122b located between the groove and the main body section 110 is denoted as C. In the longitudinal section 12 of the compressor, the distance from the outline of the portion of the second non-driving mating surface 210b located on the periphery of the convex part to the outline of the second driving mating surface 210a is denoted as A1. In the longitudinal section 12 of the compressor, the minimum distance from the outline of the second driving mating surface 210a to the outline of the convex part is denoted as B1. On the longitudinal section 12 of the compressor, the length of the outline of the portion of the second non-driving mating surface 210b located between the protrusion and the main body section 110 is denoted as C1. Wherein, A1>A, B1>B, C1>C.

[0154] This ensures smoother assembly of the crankshaft 100 and the eccentric sleeve 200, avoids interference, improves assembly efficiency, reduces the requirements for the machining accuracy of parts, and meets the stability and reliability requirements of the compressor 10 under different operating conditions.

[0155] According to some embodiments of the present invention, such as Figure 1 , Figure 5 and Figure 6 As shown, an avoidance groove 230 is provided at the connection between the axial end face of the eccentric sleeve 200 facing the main body section 110 and the inner peripheral wall of the eccentric sleeve 200. The avoidance groove 230 is arranged around the eccentric section 120, and the connection between the main body section 110 and the eccentric section 120 and the avoidance groove 230 are arranged opposite to each other.

[0156] Specifically, the mating structure of crankshaft 100 and eccentric sleeve 200 is refined.

[0157] The outer peripheral wall of the main body section 110 protrudes beyond the outer peripheral wall of the eccentric section 120. That is, the outer diameter of the main body section 110 is larger than the outer diameter of the eccentric sleeve 200. The main body section 110 and the eccentric section 120 enclose a stepped structure.

[0158] An avoidance groove 230 is provided at the connection between the axial end face of the eccentric sleeve 200 facing the main body section 110 and the inner peripheral wall of the eccentric sleeve 200. The connection between the main body section 110 and the eccentric section 120 and the avoidance groove 230 are arranged opposite to each other. The avoidance groove 230 is used to avoid the structure of the connection between the main body section 110 and the eccentric section 120 to avoid interference, so that after the eccentric sleeve 200 is fitted onto the eccentric section 120, the eccentric sleeve 200 can abut against the axial end face of the main body section 110.

[0159] The clearance groove 230 is arranged around the eccentric section 120. The clearance groove 230 can avoid the structure at the connection between the main body section 110 and the eccentric section 120 in all directions, ensuring the effective fit size between the eccentric sleeve 200 and the crankshaft 100, and providing structural support for the stable operation of the compressor 10.

[0160] In addition, by setting the clearance groove 230, a small amount of lubricating oil and impurities can enter the clearance groove 230 when the compressor 10 is running, and the clearance groove 230 can be used as a storage space for lubricating oil and impurities.

[0161] If the eccentric sleeve is not provided with a clearance groove, the connection between the axial end face of the eccentric sleeve facing the main body section and the inner circumferential wall of the eccentric sleeve will come into contact with the connection between the main body section and the eccentric section, which can easily cause stress concentration, increase mechanical wear, and increase the operating noise of the compressor.

[0162] According to some embodiments of the present invention, such as Figure 1 As shown, a chamfer 140 is provided at the connection between the main body section 110 and the eccentric section 120; on the longitudinal section 12 of the compressor, the outline of the chamfer 140 is located between the two endpoints of the outline of the clearance groove 230; wherein, the axis 124 of the eccentric section is located on the plane of the longitudinal section 12 of the compressor.

[0163] Specifically, the mating structure of the main body section 110, the eccentric section 120, and the eccentric sleeve 200 is refined.

[0164] A chamfer 140 is provided at the connection between the main body section 110 and the eccentric section 120. On the longitudinal section 12 of the compressor, the axis 124 of the eccentric section lies on the plane containing the longitudinal section 12, and the outline of the chamfer 140 lies between the two endpoints of the outline of the clearance groove 230. That is, the positional relationship between the chamfer 140 and the clearance groove 230 is defined, ensuring that the chamfer 140 is located within the space enclosed by the clearance groove 230, and that the clearance groove 230 completely avoids the chamfer 140 at the connection between the main body section 110 and the eccentric section 120, preventing interference. This allows the eccentric sleeve 200, after being fitted onto the eccentric section 120, to abut against the axial end face of the main body section 110, ensuring the effective fit dimensions between the eccentric sleeve 200 and the crankshaft 100.

[0165] In addition, a chamfer 140 is provided at the connection between the main body section 110 and the eccentric section 120. The chamfer 140 structure allows the connection between the main body section 110 and the eccentric section 120 to be smoothly transitioned, reducing stress concentration, which is beneficial to improving the service life of the product and reducing operating noise and mechanical wear.

[0166] For example, the connection between the main body segment 110 and the eccentric segment 120 is provided with a chamfer.

[0167] For example, the connection between the main body segment 110 and the eccentric segment 120 is provided with a rounded corner.

[0168] The refrigeration device 50 according to some embodiments of the present invention includes: the compressor 10 in any of the above embodiments.

[0169] The refrigeration equipment 50 provided in this application includes the compressor 10 as described in any of the above embodiments, and therefore has all the beneficial effects of the compressor 10, which will not be described in detail here.

[0170] For example, the refrigeration equipment 50 includes an air conditioner, a refrigerator, or a freezer.

[0171] For example, the compressor 10 includes a crankshaft 100, an eccentric sleeve 200, a bearing 300, and a moving scroll 400. The crankshaft 100 includes a main body section 110 and an eccentric section 120 connected to each other. The eccentric sleeve 200 includes an outer peripheral wall that mates with the bearing 300 and an inner peripheral wall that mates with the eccentric section 120. The inner peripheral wall of the eccentric sleeve 200 has a protrusion, and the eccentric section 120 of the crankshaft 100 has a groove. The protrusion and the groove form an oriented assembly structure to prevent compressor 10 failure caused by incorrect assembly direction of the eccentric sleeve 200. The inner peripheral wall of the eccentric sleeve 200 also has a second driving mating surface 210a and a second non-driving mating surface 210b, and the outer peripheral wall of the eccentric section 120 has a first driving mating surface 122a and a first non-driving mating surface 122b. The first driving mating surface 122a and the second driving mating surface 210a mate with each other. When the compressor 10 is working, a driving force is applied to the second driving mating surface 210a of the eccentric sleeve 200 through the eccentric section 120 of the crankshaft 100. Under the combined action of the driving force and the centrifugal force of the moving scroll 400, the moving scroll 400 is kept in a constant eccentricity state. In the event of liquid slugging or impurities entering the compression chamber of the compressor 10, the eccentricity of the moving scroll 400 can be adjusted to protect the scroll teeth from damage. This application has a reasonable structure for the compressor 10, which not only improves the stability of the compressor 10 and reduces the frictional power consumption between the moving scroll 400 and the stationary scroll, but also ensures assembly reliability.

[0172] For example, the inner peripheral wall of the eccentric sleeve 200 is provided with a protrusion, specifically, the protrusion is provided on one of the second driving mating surface 210a and the second non-driving mating surface 210b. The eccentric segment 120 is provided with a groove, specifically, the groove is provided on one of the first driving mating surface 122a and the first non-driving mating surface 122b. The protrusion and the groove are positioned to match, the protrusion is inserted into the groove, the protrusion and the groove are fitted with a clearance, and the groove and the protrusion are fitted to form an "L" shaped overlock.

[0173] For example, the outer surface of the protrusion includes at least one of a plane and an arcuate surface.

[0174] For example, the groove wall includes at least one of a plane and an arcuate surface.

[0175] For example, the second driving mating surface 210a of the eccentric sleeve 200 includes at least one of a plane and an arcuate surface. For example, the second driving mating surface 210a is a plane. For example, the second driving mating surface 210a is a combination of a plane and an axial inclined surface. For example, the second driving mating surface 210a is an axial arched surface.

[0176] For example, a clearance groove 230 is provided at the connection between the inner peripheral wall of the eccentric sleeve 200 and the axial end face of the eccentric sleeve 200 facing the main body section 110. A chamfer 140 is provided at the connection between the main body section 110 and the eccentric section 120. The size of the clearance groove 230 is larger than the size of the chamfer 140. This can prevent interference between the eccentric sleeve 200 and the root chamfer 140 of the eccentric section 120, ensuring the reliability of the assembly of the eccentric sleeve 200 and the eccentric section 120, and preventing the compressor 10 from failing due to assembly errors.

[0177] Exemplarily, the first driving mating surface 122a of the eccentric segment 120 is a plane. Exemplarily, the first driving mating surface 122a of the eccentric segment 120 is an axial inclined surface. Exemplarily, as... Figure 2 As shown, the drive angle is α, where α = (SF - UF) / R. When the compressor 10 is working, along the first direction, the distance from the second drive mating surface 210a of the eccentric sleeve 200 to the axis of the crankshaft 100 is SF, and the distance from the second drive mating surface 210a of the eccentric sleeve 200 to the axis 124 of the eccentric section is UF. R is the vortex eccentricity.

[0178] For example, on the axial end face of the crankshaft 100, the axial end face of the eccentric segment 120 is double semicircular or semicircular. The contour line of the eccentric segment 120 includes double circular arc edges and double straight edges, or the contour line of the eccentric segment 120 includes a single arc edge and a straight edge.

[0179] For example, such as Figure 9 As shown, the refrigeration equipment 50 includes a detection module 510, a compressor 10, a mode switching module 520, and a controller 530. The detection module 510 is used to detect the operating parameters of the refrigeration equipment 50. The controller 530 is used to control the operation of the mode switching module 520 to adjust the operating mode of the refrigeration equipment 50. The controller 530 is also used to control the operation of the compressor 10 according to the operating parameters detected by the detection module 510, etc., which will not be listed here.

[0180] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0181] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: A crankshaft, along the axial direction of the crankshaft, the crankshaft includes a main body section and an eccentric section connected to each other, the outer peripheral wall of the main body section protruding from the outer peripheral wall of the eccentric section, and the outer peripheral wall of the eccentric section including a plurality of spaced first mating surfaces in the circumferential direction of the eccentric section; An eccentric sleeve is fitted onto the eccentric segment. The inner circumferential wall of the eccentric sleeve is provided with a plurality of second mating surfaces. Each second mating surface is disposed opposite to a first mating surface. The first mating surface and the second mating surface cooperate to restrict the displacement of the eccentric sleeve relative to the crankshaft along the circumferential direction of the eccentric segment. Bearings; A moving scroll plate, wherein the moving scroll plate is connected to the outer peripheral wall of the eccentric sleeve via the bearing; The inner peripheral wall of the eccentric sleeve and the outer peripheral wall of the eccentric segment are in clearance fit.

2. The compressor according to claim 1, characterized in that, The first mating surface includes at least one of a plane and an arc surface; and / or The second mating surface includes at least one of a plane and an arc surface.

3. The compressor according to claim 1 or 2, characterized in that, At least a portion of the shape of the first mating surface is the same as the shape of the second mating surface; or The shape of the first mating surface is different from the shape of the second mating surface.

4. The compressor according to claim 1 or 2, characterized in that, The first mating surface extends axially from the side of the eccentric segment away from the main body segment to the connection between the main body segment and the eccentric segment; The second mating surface extends from one axial end face of the eccentric sleeve to the other axial end face of the eccentric sleeve.

5. The compressor according to claim 1 or 2, characterized in that, The outer peripheral wall of the eccentric section is provided with a first positioning part, and the inner peripheral wall of the eccentric sleeve is provided with a second positioning part; One of the first positioning part and the second positioning part is a groove, and the other is a protrusion. The protrusion is inserted into the groove, and the protrusion and the groove are in clearance fit. The groove extends axially from the axial end face of one of the eccentric segment and the eccentric sleeve along the axial direction of the eccentric segment.

6. The compressor according to claim 5, characterized in that, The plurality of first mating surfaces include at least a first driving mating surface and a first non-driving mating surface; At least one of the first driving mating surface and the first non-driving mating surface is provided with the first positioning part; or The portion of the outer peripheral wall of the eccentric segment located between the first driving mating surface and the first non-driving mating surface is provided with the first positioning part.

7. The compressor according to claim 6, characterized in that, Along the radial direction of the eccentric segment, the first driving mating surface and the first non-driving mating surface are arranged opposite to each other.

8. The compressor according to claim 7, characterized in that, The second mating surface corresponding to the first driving mating surface is denoted as the second driving mating surface, and the second mating surface corresponding to the first non-driving mating surface is denoted as the second non-driving mating surface; When the first non-driving mating surface is provided with the groove, the outline of the groove is "L" shaped on the longitudinal section of the compressor. The distance from the outline of the portion of the first non-driving mating surface located on the periphery of the groove to the outline of the first driving mating surface is A. The distance from the outline of the first driving mating surface to the outline of the groove is B. The length of the outline of the portion of the first non-driving mating surface located between the groove and the main body segment is C. The distance from the outline of the portion of the second non-driving mating surface located on the periphery of the protrusion to the outline of the second driving mating surface is A1. The minimum distance from the outline of the second driving mating surface to the outline of the protrusion is B1. The length of the outline of the portion of the second non-driving mating surface located between the protrusion and the main body segment is C1. Where A1 > A, B1 > B, C1 > C, and the axis of the eccentric segment is located on the plane of the longitudinal section of the compressor.

9. The compressor according to claim 1 or 2, characterized in that, An avoidance groove is provided at the connection between the axial end face of the eccentric sleeve facing the main body section and the inner peripheral wall of the eccentric sleeve. The avoidance groove is arranged around the eccentric section, and the connection between the main body section and the eccentric section is arranged opposite to the avoidance groove.

10. The compressor according to claim 9, characterized in that, The connection between the main body segment and the eccentric segment is chamfered; On the longitudinal section of the compressor, the contour line of the chamfer is located between the two endpoints of the contour line of the clearance groove; The axis of the eccentric section is located on the plane of the longitudinal section of the compressor.

11. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 10.

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