CN117514778A - Movable scroll assembly, scroll compressor and refrigeration equipment - Google Patents

Abstract

The invention discloses an orbiting scroll assembly, a scroll compressor and refrigeration equipment. The movable vortex plate assembly comprises an end plate, a movable vortex tooth, a hub part and a movable plate bearing; the movable vortex teeth are arranged at one axial end of the end plate, the hub part is arranged at one end of the end plate, which is away from the movable vortex teeth, the hub part is provided with a shaft hole, and the peripheral wall of the shaft hole is provided with at least one first groove; the movable disc bearing is arranged in the shaft hole and sleeved on the periphery of the eccentric shaft section. According to the technical scheme, the contact rigidity of the eccentric shaft section and the eccentric shaft section can be reduced, the contact deformation area of the eccentric shaft section and the eccentric shaft section is increased, the surface pressure is reduced, the thickness of an oil film between the eccentric shaft section and the eccentric shaft section is increased, and the purpose of effectively improving the abrasion between the eccentric shaft section and the eccentric shaft section is achieved.

Description

Movable scroll assembly, scroll compressor and refrigeration equipment

Technical Field

The invention relates to the technical field of compressors, in particular to an movable scroll assembly, a scroll compressor and refrigeration equipment.

Background

The scroll compressor comprises a fixed scroll, an movable scroll and a crankshaft, wherein the movable scroll is arranged on the crankshaft, the movable scroll is assembled with the fixed scroll in a matched manner and is movable relative to the fixed scroll, and when the scroll compressor works, the crankshaft rotates to drive the movable scroll to move, so that refrigerant can continuously operate in a compression cavity defined by the fixed scroll and the movable scroll in a matched manner, and the suction, compression and discharge processes of the compressor are realized.

In the scroll compressor of the related art, a certain inclination occurs between the crankshaft and the movable scroll during operation, and the cooperation between the crankshaft and the movable scroll assembly has a local stress concentration, which results in a large abrasion between the crankshaft and the movable scroll assembly.

Disclosure of Invention

The main object of the present invention is to propose an orbiting scroll assembly aimed at improving the wear between the crankshaft and the orbiting scroll assembly.

In order to achieve the above object, the present invention provides an orbiting scroll assembly applied to a scroll compressor including a crankshaft having an eccentric shaft section; the orbiting scroll assembly includes:

an end plate;

the movable vortex teeth are arranged at one axial end of the end plate;

the hub part is arranged at one end of the end plate, which is far away from the movable vortex teeth, and is provided with a shaft hole, and the peripheral wall of the shaft hole is provided with at least one first groove; and

the movable disc bearing is arranged in the shaft hole and sleeved on the periphery of the eccentric shaft section.

In an embodiment of the present application, the first groove is disposed annularly along a circumferential direction of the hub portion.

In an embodiment of the present application, the movable disc bearing is in interference fit with the shaft hole; the hole peripheral wall of the shaft hole has a first end close to the end plate and a second end distant from the end plate, at least one of the first end and the second end being provided with the first groove.

In an embodiment of the present application, the first end is provided with the first groove, the first groove has a first edge near the end plate, and a gap D1 is formed between the first edge and the end plate, so as to satisfy: d1 is more than or equal to 0.5mm and less than or equal to 1mm.

In an embodiment of the present application, in an axial direction, the dynamic disc bearing has a third end surface near the end plate, the third end surface being located at a side of the first edge facing away from the end plate; an axial distance D2 between the first edge and the third end face satisfies: d2 is more than or equal to 0.1mm and less than or equal to 1mm.

In an embodiment of the present application, an axial length of the hub portion is defined as L, and an axial depth dimension of the first groove is H1, satisfying 0< H1/L <1/3.

In an embodiment of the present application, the hub portion has a cylindrical structure, a radial thickness dimension of the hub portion is defined as T, and a radial depth dimension of the first groove is defined as B1, so as to satisfy 0< B1/T <1/2.

In an embodiment of the application, an axial gap D3 is formed between the movable disc bearing and the end plate, and the requirement that D3 is smaller than or equal to 1mm and smaller than or equal to 2mm is met.

In an embodiment of the present application, the outer peripheral wall of the hub portion is provided with a second groove, and the second groove extends along the circumferential direction of the hub portion.

In an embodiment of the present application, the axial length of the hub portion is L, the axial depth dimension of the first groove is H1, the axial depth dimension of the second groove is H2, the radial thickness dimension of the hub portion is T, the radial depth dimension of the first groove is B1, and the radial depth dimension of the second groove is B2, which satisfies the following conditions:

0<H1/L<1/3；

and/or 0< H2/L <1/3;

and/or 0< (B1+B2)/T <1/2.

In an embodiment of the present application, the second groove corresponds to the position of the first groove;

or the first groove is arranged on one side of the inner wall of the hub part, which is close to the end plate, and the second groove is arranged on one side of the outer wall of the hub part, which is far away from the end plate;

or, the first groove is arranged on one side of the inner wall of the hub part, which is far away from the end plate, and the second groove is arranged on one side of the outer wall of the hub part, which is near to the end plate.

In order to achieve the above object, the present application further provides a scroll compressor including the above movable scroll assembly; the orbiting scroll assembly includes:

an end plate;

the hub part is arranged at one axial end of the end plate and is provided with a shaft hole, and the peripheral wall of the shaft hole is provided with at least one first groove; and

the movable disc bearing is arranged in the shaft hole and sleeved on the periphery of the eccentric shaft section.

In order to achieve the above object, the present application further provides a refrigeration apparatus including the above scroll compressor.

In the movable vortex plate assembly, one axial end of the end plate is provided with a hub part, the hub part is provided with a shaft hole for installing a movable vortex plate bearing, and the movable vortex plate bearing is sleeved on the periphery of an eccentric shaft section of the crankshaft so as to realize the driving connection of the crankshaft and the movable vortex plate assembly. By arranging at least one first groove on the hole peripheral wall of the shaft hole, the contact rigidity of the eccentric shaft section and the movable disc bearing can be reduced, the contact deformation area of the eccentric shaft section and the movable disc bearing is increased, and the surface pressure is reduced, so that the thickness of an oil film between the eccentric shaft section and the movable disc bearing is increased, and the purpose of effectively improving the abrasion between the eccentric shaft section and the movable disc bearing is achieved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic view of an embodiment of an orbiting scroll assembly of the present invention;

FIG. 2 is an enlarged view of a portion of the M in FIG. 1;

FIG. 3 is a partial cross-sectional view of the embodiment of FIG. 1;

FIG. 4 is a schematic view of another embodiment of an orbiting scroll assembly of the present invention;

FIG. 5 is an enlarged view of a portion of N in FIG. 4;

FIG. 6 is a schematic view of an alternate embodiment of an orbiting scroll assembly of the present invention;

FIG. 7 is a schematic structural diagram of an embodiment of the present invention in which a first groove and a second groove are disposed correspondingly;

FIG. 8 is an enlarged view of a portion of the portion of FIG. 7 at K;

FIG. 9 is a partial cross-sectional view of the embodiment of FIG. 7;

FIG. 10 is a schematic structural view of an embodiment of the present invention in which a first groove and a second groove are staggered;

fig. 11 is a schematic structural diagram of another embodiment of the present invention in which the first groove and the second groove are staggered.

Reference numerals illustrate:

reference numerals	Name of the name	Reference numerals	Name of the name
				100	Movable vortex plate assembly	122	First groove
110	End plate	122a	A first edge
				120	Hub part	123	Second groove
1211	Hole peripheral wall	130	Movable plate bearing
				1211a	First end	130a	Third end face
1211b	Second end	140	Movable vortex tooth

The achievement of the objects, functional features and advantages of the present invention will be further described with reference to the accompanying drawings, in conjunction with the embodiments.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

It should be noted that, if directional indications (such as up, down, left, right, front, and rear … …) are included in the embodiments of the present invention, the directional indications are merely used to explain the relative positional relationship, movement conditions, etc. between the components in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indications are correspondingly changed.

Meanwhile, the meaning of "and/or" and/or "appearing throughout the text is to include three schemes, taking" a and/or B "as an example, including a scheme, or B scheme, or a scheme that a and B satisfy simultaneously.

In addition, if there is a description of "first", "second", etc. in the embodiments of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.

The present invention proposes an orbiting scroll assembly 100 for use in a scroll compressor. The scroll compressor comprises a motor, a crankshaft, a fixed scroll assembly, an auxiliary frame and a main frame, wherein the crankshaft is provided with an auxiliary shaft section matched with the auxiliary frame, a main shaft section matched with the main frame, a rotor section connected with the motor and an eccentric shaft section in driving connection with the movable scroll assembly 100, and the movable scroll assembly 100 and the fixed scroll assembly are mutually matched to define a compression cavity. When the compressor operates, the motor drives the crankshaft to rotate, and the eccentric shaft section drives the movable scroll assembly 100 to move relative to the fixed scroll assembly so as to realize the function of compressing the refrigerant.

However, the crankshaft is subjected to radial forces exerted by various components during rotation, and may oscillate or tilt. Meanwhile, as the movable scroll assembly 100 is driven to move through the eccentric shaft section, the movable scroll teeth 140 can be subjected to the pressure of gas in the compression cavity, so that the movable scroll assembly 100 can be subjected to the pressures at different axial positions, and the movable scroll assembly 100 can be inclined in the running process or even in a slight inclined state. Therefore, during operation of the compressor, the crankshaft and/or the orbiting scroll assembly 100 may be inclined, and thus local stress concentration may occur between the eccentric shaft section of the crankshaft and the orbiting disk bearing 130 in the orbiting scroll assembly 100, and surface pressure may be excessively increased, resulting in increased wear.

Based on this, referring to fig. 1, 4 and 6, the orbiting scroll assembly 100 in this embodiment includes an end plate 110, an orbiting scroll teeth 140, a hub portion 120 and an orbiting scroll bearing 130, where the orbiting scroll teeth 140 and the hub portion 120 are disposed at two axial ends of the end plate 110, the hub portion 120 has a shaft hole, the orbiting scroll bearing 130 is mounted in the shaft hole and is sleeved on the outer periphery of the eccentric shaft section, and by providing at least one first groove 122 on the hole peripheral wall 1211 of the shaft hole, a certain deformation space can be provided for the orbiting scroll bearing 130, and the contact rigidity of the orbiting scroll bearing 130 and the eccentric shaft section can be reduced to a certain extent, so that the orbiting scroll bearing 130 can deform to a certain extent when receiving the radial force of the eccentric shaft section, the contact area between the eccentric shaft section and the orbiting scroll bearing 130 is increased, the surface pressure is reduced, the stress impact between the eccentric shaft section and the orbiting scroll bearing 130 is reduced.

In addition, the first groove 122 also has the function of reducing the thickness of the hub 120, so that the rigidity of the hub 120 is reduced, and the hub 120 can correspondingly deform along with the swinging of the eccentric shaft section to a certain extent, thereby further improving the abrasion of the crankshaft.

In practical application, an oil supply channel is provided on the crankshaft to supply oil between the eccentric shaft section and the movable disc bearing 130, so as to form oil film lubrication. When the eccentric shaft section is inclined, the oil film between the eccentric shaft section and the movable disc bearing 130 may deviate, so that the oil film thickness between the eccentric shaft section and the movable disc bearing 130 is thinner or even no oil film exists at the stress concentration position of the eccentric shaft section and the movable disc bearing 130.

In practical application, the movable disk bearing 130 may be a cylindrical structure, the movable disk bearing 130 is in interference fit with the shaft hole, and the eccentric shaft section is inserted into the inner cavity of the movable disk bearing 130 and is in sliding fit with the inner wall of the movable disk bearing 130. That is, the dynamic disc bearing 130 is interposed between the eccentric shaft section and the hole peripheral wall 1211, so that the first groove 122 can increase the flexibility of the dynamic disc bearing 130.

The hole peripheral wall 1211 of the shaft hole is provided with at least one first groove 122, it is to be understood that the hole peripheral wall 1211 of the shaft hole may be provided with one first groove 122, two first grooves 122, or a plurality of first grooves 122, etc., and the specific number of the first grooves 122 may be determined according to the actual situation, which may not be limited herein. The specific position of the first recess 122 may also be determined according to the actual situation, for example, may be disposed in a region of the hole peripheral wall 1211 close to the end plate 110, or may be disposed in a region of the hole peripheral wall 1211 away from the end plate 110, or may be disposed in a region axially intermediate the hole peripheral wall 1211, or the like. In practical applications, the cross-sectional shape of the first groove 122 is not limited, and for example, the cross-sectional shape of the first groove 122 may be rectangular, semicircular, triangular, trapezoidal, or other special-shaped shapes. In practical applications, the extending shape of the first groove 122 may be an annular groove structure around the periphery of the hole peripheral wall 1211, or may be one or more circular arc groove structures, or may be a spiral groove structure around the hole peripheral wall 1211, or may be other irregularly extending structures, etc.

In the orbiting scroll assembly 100 according to the present invention, a hub 120 is disposed at one axial end of the end plate 110, the hub 120 has a shaft hole for mounting an orbiting disk bearing 130, and the orbiting disk bearing 130 is sleeved on the outer periphery of the eccentric shaft section of the crankshaft, so as to realize driving connection between the crankshaft and the orbiting scroll assembly 100. By arranging at least one first groove 122 on the hole peripheral wall of the shaft hole, the contact rigidity of the movable disc bearing 130 and the eccentric shaft section can be reduced, the contact deformation area of the eccentric shaft section and the movable disc bearing 130 is increased, and the surface pressure is reduced, so that the thickness of an oil film between the eccentric shaft section and the movable disc bearing 130 is increased, and the purpose of effectively improving the abrasion between the eccentric shaft section and the movable disc bearing 130 is achieved.

In an embodiment of the present application, referring to fig. 3, the first groove 122 is disposed annularly along the circumferential direction of the hub 120.

When the compressor is running, the eccentric shaft section of the crankshaft is in eccentric rotation, so that the eccentric shaft section rotates relative to the movable disc bearing 130, namely, during running, the eccentric shaft section may generate local stress impact with any area in the circumferential direction of the movable disc bearing 130, and according to the embodiment, the first groove 122 is annularly arranged along the circumferential direction of the hub part 120, so that the first groove 122 surrounds the whole circumferential edge of the movable disc bearing 130, the contact rigidity of the movable disc bearing 130 and the eccentric shaft section can be reduced in a larger range, and the condition that the contact stress between the eccentric shaft section and the movable disc bearing 130 is overlarge when the eccentric shaft section moves to a certain position in the circumferential direction is prevented.

In addition, in this embodiment, the first groove 122 is configured as a continuous annular groove, and since the first groove 122 is located in the shaft hole, compared with other intermittent grooves or a section of groove, the present embodiment is more beneficial to processing and manufacturing, and can improve production efficiency.

In an embodiment of the present application, referring to fig. 1 to 6, the movable disc bearing 130 is in interference fit with the shaft hole; the hole peripheral wall 1211 of the shaft hole has a first end 1211a close to the end plate 110 and a second end 1211b distant from the end plate 110, at least one of the first end 1211 and the second end 1211b being provided with the first recess 122.

It will be appreciated that, during operation of the compressor, when the eccentric shaft section or the orbiting scroll assembly 100 is inclined, the stress concentration portion between the orbiting disk bearing 130 and the eccentric shaft section is located at the axial end regions of the eccentric shaft section, and therefore, the first groove 122 is provided at the position of the hole peripheral wall 1211 near the first end 1211a of the end plate 110 and/or the second end 1211b away from the end plate 110, so that the portion of the orbiting disk bearing 130, which is greatly stressed, can deform in the direction of the first groove 122 when the radial force of the eccentric shaft section is applied, so as to buffer the impact of the eccentric shaft section on the orbiting disk bearing 130, so that the contact area between the orbiting disk bearing 130 and the eccentric shaft section is increased, and thus the surface pressure can be reduced.

In practical use, the first grooves 122 may be provided only at the first end 1211a of the hole peripheral wall 1211 (see fig. 1 to 3), or the first grooves 122 may be provided only at the second end 1211b of the hole peripheral wall 1211 (see fig. 4 to 5), or the first grooves 122 may be provided at both the first end 1211a and the second end 1211b (see fig. 6).

As an example, in an embodiment of the present application, it may be preferable to provide the first groove 122 at the first end 1211a, considering that the contact stress of the free end portion thereof with the movable disc bearing 130 is greater when the eccentric shaft section is inclined. As shown in fig. 1 to 3, in this embodiment, the first groove 122 has a first edge 122a near the end plate 110, and a gap D1 is provided between the first edge 122a and the end plate 110, so that: d1 is more than or equal to 0.5mm and less than or equal to 1mm.

The axial end surfaces of the hub 120 and the end plate 110 are connected with each other by an included angle, the hub 120 extends along the axial direction, and the end plate 110 extends along the radial direction, it can be understood that the gap D1 between the first groove 122 and the end plate 110 should not be too small or too large, if too small, the first groove 122 is too close to or even may be directly opened at the connection position of the hub 120 and the end plate 110, so that the structural strength of the connection position is affected, and the connection position of the hub 120 and the end plate 110 is easily broken; if too large, the first groove 122 is too close to the axially middle region of the movable disk bearing 130, and may not function to well reduce the abrasion of the movable disk bearing 130 and the eccentric shaft section. Based on this, the gap D1 between the first edge 122a and the end plate 110 is set to satisfy 0.5 mm.ltoreq.D1.ltoreq.1 mm in this embodiment, so that not only the connection reliability of the hub 120 and the end plate 110 can be ensured, but also the abrasion between the movable disc bearing 130 and the eccentric shaft section can be reduced well.

By way of example, the gap D1 may be selected from 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, etc.

In an embodiment of the present application, referring to fig. 2, in the axial direction, the movable disc bearing 130 has a third end surface 130a near the end plate 110, and the third end surface 130a is located on a side of the first edge 122a facing away from the end plate 110; the axial distance D2 between the first edge 122a and the third end face 130a satisfies: d2 is more than or equal to 0.1mm and less than or equal to 1mm.

It will be appreciated that the movable disc bearing 130 is inserted in the shaft hole, the eccentric shaft section is matched with the inner wall of the movable disc bearing 130, and the crankshaft may axially move during operation, so that a moving space is provided for the crankshaft by arranging the movable disc bearing 130 and the end plate 110 in a clearance manner, and impact abrasion of the crankshaft and the end plate 110 is prevented. Further, in the present embodiment, the third end surface 130a of the movable disc bearing 130 is located at the side of the first edge 122a away from the end plate 110, so that the projection of the end portion of the movable disc bearing 130 falls into the first groove 122, which can make the deformation of the movable disc bearing 130 smoother, and prevent the contact friction between the third end surface 130a of the movable disc bearing 130 and the inner wall of the hub 120.

In practical application, the axial distance D2 between the first edge 122a and the third end surface 130a should not be too small, or should not be too large, and if too small, the third end surface 130a of the movable disc bearing 130 is easily in contact friction with the inner wall of the hub 120; if too large, the spacing between the orbiting plate bearing 130 and the end plate 110 is too large, the driving function of the crankshaft and orbiting scroll assembly 100 may be affected. Based on this, the axial distance D2 between the first edge 122a and the third end surface 130a is set to satisfy 0.1 mm+.d2+.1mm, so that the deformation of the movable disc bearing 130 can be smoother, and the transmission function of the crankshaft and the movable scroll assembly 100 can be ensured.

By way of example, the axial distance D2 may be selected from 0.1mm, 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, etc.

In one embodiment, referring to FIG. 2, the axial gap D3 between the rotor bearing 130 and the end plate 110 satisfies 1mm < D3 < 2mm.

By providing clearance between the rotor bearing 130 and the end plate 110, an axial floating space is provided for the crankshaft, preventing impact wear of the crankshaft and the end plate 110. It will be appreciated that the axial clearance D3 between the rotor bearing 130 and the end plate 110 should not be too small nor too large, if too small, to provide insufficient axial float space for the crankshaft; if too large, the gearing of the crankshaft and orbiting scroll assembly 100 may be affected. Based on this, the present embodiment sets the axial gap D3 between the movable disk bearing 130 and the end plate 110 to satisfy 1mm D3 2mm. By way of example, the axial gap D3 may be selected from 1mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm, 1.6mm, 1.7mm, 1.8mm, 1.9mm, 2mm, etc.

In an embodiment of the present application, referring to fig. 1 and 2, defining the axial length of the hub 120 as L, the axial depth dimension of the first groove 122 as H1, 0< H1/L <1/3 is satisfied.

In this embodiment, by limiting the axial depth H1 of the first groove 122 and the axial length L of the hub 120, the hub 120 can be ensured to have sufficient structural strength, and breakage caused by overlong axial depth of the first groove 122 can be prevented.

In an embodiment of the present application, referring to fig. 1 and 2, the hub 120 has a cylindrical structure, the radial thickness dimension of the hub 120 is defined as T, the radial depth dimension of the first groove 122 is defined as B1, and 0< B1/T <1/2 is satisfied.

In this embodiment, by limiting the radial depth B1 of the first groove 122, the wall thickness at the first groove 122 is ensured, and the wall thickness at the first groove 122 is prevented from being broken due to too thin wall thickness at the first groove 122 caused by too large radial depth of the first groove 122.

In an embodiment of the present application, referring to fig. 7 to 9, the outer peripheral wall of the hub 120 is provided with a second groove 123, and the second groove 123 extends along the circumferential direction of the hub 120.

In this embodiment, the second groove 123 is provided on the outer peripheral wall of the hub portion 120, so that the thickness of the hub portion 120 can be further reduced, and the rigidity of the hub portion 120 is reduced, so that the hub portion 120 can be correspondingly deformed along with the swing of the eccentric shaft section to a certain extent, and the wear of the crankshaft is further improved.

It will be appreciated that the specific location of the second recess 123 may be dependent on the actual situation, such as may be located in the region of the hub 120 near the end plate 110, or may be located in the region of the hub 120 remote from the end plate 110, or may be located in the axially intermediate region of the hub 120, etc. In practical applications, the cross-sectional shape of the second groove 123 is not limited, and for example, the cross-sectional shape of the second groove 123 may be rectangular, semicircular, triangular, trapezoidal, or other irregular shapes.

The shape and structure of the second groove 123 of the present embodiment may be the same as or different from the structure and shape of the first groove 122.

In an embodiment of the present application, referring to fig. 7 to 11, the axial length of the hub 120 is L, the axial depth dimension of the first groove 122 is H1, the axial depth dimension of the second groove 123 is H2, the radial thickness dimension of the hub 120 is T, the radial depth dimension of the first groove 122 is B1, and the radial depth dimension of the second groove 123 is B2, which satisfies the following conditions: 0< H1/L <1/3; and/or 0< H2/L <1/3; and/or 0< (B1+B2)/T <1/2.

In order to ensure that the hub 120 has sufficient structural strength, the axial depth dimension H1 of the first groove 122 and the axial depth dimension H2 of the second groove 123 are defined such that 0< H1/L <1/3,0< H2/L <1/3 to prevent the hub 120 from breaking.

Accordingly, in order to ensure that the hub 120 has sufficient structural strength, the radial depth dimension B1 of the first groove 122 and the radial depth dimension B2 of the second groove 123 are defined such that 0< (b1+b2)/T <1/2 to prevent the hub 120 from being broken.

In an embodiment of the present application, referring to fig. 7 to 9, the second groove 123 corresponds to the first groove 122. So arranged, the effect of the corresponding deformation of the hub 120 with the oscillation of the eccentric shaft section is better. In practical application, the second groove 123 and the first groove 122 may be disposed at the portion of the hub 120 near the end plate 110, considering that the contact stress between the free end portion and the movable disc bearing 130 is greater when the eccentric shaft section is inclined.

In some other embodiments of the present application, referring to fig. 10, the first groove 122 is disposed on a side of the inner wall of the hub 120 near the end plate 110, and the second groove 123 is disposed on a side of the outer wall of the hub 120 far from the end plate 110. Alternatively, as shown in fig. 11, the first groove 122 may be formed on a side of the inner wall of the hub 120 away from the end plate 110, and the second groove 123 may be formed on a side of the outer wall of the hub 120 close to the end plate 110.

By the arrangement, the flexible effect of the movable disc bearing 130 is improved, enough interference fit area of the movable disc bearing 130 and the hub 120 can be ensured, the holding force of the movable disc bearing 130 is left, and the movable disc bearing 130 is prevented from falling off.

The present invention also proposes a scroll compressor, which includes an orbiting scroll assembly 100, and the specific structure of the orbiting scroll assembly 100 refers to the above embodiment, and since the scroll compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, and will not be described in detail herein.

The invention also provides a refrigeration device which comprises a scroll compressor, wherein the specific structure of the scroll compressor refers to the embodiment, and as the refrigeration device adopts all the technical schemes of all the embodiments, the refrigeration device at least has all the beneficial effects brought by the technical schemes of the embodiments, and the description is omitted.

Alternatively, the refrigeration device includes an air conditioner, a refrigerator, or a cold chain transporter, or the like.

The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all equivalent structural changes made by the description of the present invention and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the invention.

Claims (13)

1. An orbiting scroll assembly for use with a scroll compressor, said scroll compressor including a crankshaft having an eccentric shaft section; the orbiting scroll assembly includes:

an end plate;

the movable vortex teeth are arranged at one axial end of the end plate;

the hub part is arranged at one end of the end plate, which is away from the movable vortex teeth, and is provided with a shaft hole, and the peripheral wall of the shaft hole is provided with at least one first groove; and

the movable disc bearing is arranged in the shaft hole and sleeved on the periphery of the eccentric shaft section.

2. The orbiting scroll assembly of claim 1 wherein said first recess is annularly disposed about said hub.

3. The orbiting scroll assembly of claim 2 wherein said orbiting bearing is an interference fit with said shaft bore; the hole peripheral wall of the shaft hole has a first end close to the end plate and a second end distant from the end plate, at least one of the first end and the second end being provided with the first groove.

4. The orbiting scroll assembly of claim 3 wherein said first end is provided with said first recess having a first edge adjacent said end plate, said first edge having a gap D1 with said end plate, said gap being such that: d1 is more than or equal to 0.5mm and less than or equal to 1mm.

5. The orbiting scroll assembly of claim 4 wherein said orbiting bearing has a third end surface adjacent said end plate in an axial direction, said third end surface being on a side of said first edge facing away from said end plate; an axial distance D2 between the first edge and the third end face satisfies: d2 is more than or equal to 0.1mm and less than or equal to 1mm.

6. The orbiting scroll assembly of any one of claims 2 to 5, wherein an axial length of said hub is defined as L and an axial depth dimension of said first recess is H1, satisfying 0< H1/L <1/3.

7. The orbiting scroll assembly of any one of claims 2 to 5 wherein said hub is of cylindrical configuration defining a radial thickness dimension T of said hub and said first recess has a radial depth dimension B1 satisfying 0< B1/T <1/2.

8. The orbiting scroll assembly of any one of claims 1 to 5 wherein an axial gap D3 is provided between said orbiting bearing and said end plate satisfying 1mm +.d3 +.2 mm.

9. The orbiting scroll assembly according to any one of claims 1 to 5, wherein the outer peripheral wall of the hub is provided with a second groove extending in the circumferential direction of the hub.

10. The orbiting scroll assembly of claim 9 wherein said hub has an axial length L, said first recess has an axial depth dimension H1, said second recess has an axial depth dimension H2, said hub has a radial thickness dimension T, said first recess has a radial depth dimension B1, and said second recess has a radial depth dimension B2, satisfying:

0<H1/L<1/3；

and/or 0< H2/L <1/3;

and/or 0< 1/2.

11. The orbiting scroll assembly of claim 9 wherein said second recess corresponds to the location of said first recess;

or the first groove is arranged on one side of the inner wall of the hub part, which is close to the end plate, and the second groove is arranged on one side of the outer wall of the hub part, which is far away from the end plate;

or, the first groove is arranged on one side of the inner wall of the hub part, which is far away from the end plate, and the second groove is arranged on one side of the outer wall of the hub part, which is near to the end plate.

12. A scroll compressor comprising an orbiting scroll assembly according to any one of claims 1 to 11.

13. A refrigeration apparatus comprising the scroll compressor of claim 12.