CN222542648U - Compression components, refrigeration equipment and vehicles - Google Patents

Abstract

The utility model provides a compression assembly, a refrigeration device and a vehicle, wherein the compression assembly includes: a frame, a bearing and a crankshaft, the frame is provided with a groove, the bearing is connected to the frame, the groove is distributed along the circumference of the bearing, and the crankshaft is passed through the bearing. The radial thickness of the bearing is H1, the width of the groove along the radial direction of the bearing is H2, the radial spacing between the groove and the bearing is H3, and H1, H2 and H3 satisfy 0.5＜H2/(H1+H3)＜0.6. By arranging the groove on the frame, the effective contact area between the crankshaft and the bearing is increased, the local oil film thickness during the operation of the compression assembly is improved, and the contact surface pressure between the crankshaft and the bearing is reduced, which can effectively improve the eccentric wear problem of the bearing.

Description

Compression assembly, refrigeration equipment and vehicle

Technical Field

The utility model relates to the technical field of compressors, in particular to a compression assembly, refrigeration equipment and a vehicle.

Background

The slewing mechanism of the scroll compressor mainly comprises a crankshaft, a frame, a bearing and other parts, wherein the frame supports the crankshaft to rotate through the bearing, so that the scroll is driven to rotate for compression.

The crankshaft can generate larger elastic deformation when the compressor runs, and the abrasion loss of the bearing can be increased, so that the bearing is easy to damage.

Disclosure of utility model

The utility model aims to solve the technical problems that in the prior art or related technologies, a crankshaft can generate larger elastic deformation when the compressor runs, and the abrasion loss of a bearing can be increased.

In view of the above, the present utility model provides a compression assembly, comprising a frame, a bearing, a crankshaft, and a crankshaft, wherein the frame is provided with grooves, the bearing is connected with the frame, the grooves are distributed along the circumferential direction of the bearing, the crankshaft penetrates through the bearing, the radial thickness of the bearing is H1, the width of the groove is H2 along the radial direction of the bearing, the radial distance between the groove and the bearing is H3, H1, H2 and H3 are satisfied, and 0.5< H2/(H1+H23) <0.6.

According to the compression assembly provided by the utility model, the crankshaft is arranged on the bearing in a penetrating way, so that the crankshaft can rotate relative to the frame, and the rotating crankshaft is used for driving the movable vortex disc to rotate. When the crankshaft rotates, the crankshaft is deformed, and when the contact area between the crankshaft and the bearing is changed, the wear amount of the bearing is increased. Grooves are formed in the frame and distributed along the circumferential direction of the bearing, so that part of the frame near the bearing is easy to deform when stressed, the local rigidity of the frame is reduced, and the deformation capacity is increased. When the crankshaft is deformed, the bearing is stressed, the bearing can apply force to the frame, and the position of the bearing can be slightly changed because the frame is easy to deform. For the difficult condition that makes the bearing position change that takes place for frame non-deformable, the bearing position in this scheme can change because of the deformation of frame, and frame and bearing can resist the great elastic deformation that compression subassembly operation in-process bent axle produced, increase the effective area of contact between bent axle and the bearing, improve compression subassembly operation in-process local oil film thickness, reduce the contact surface pressure between bent axle and the bearing, can effectively improve the eccentric wear problem of bearing, reduce compression subassembly's damage rate, be favorable to improving compression subassembly operation in-process stability.

The interval between recess and the bearing can be to supporting compression assembly elastic deformation's effect influence, when considering the interval between recess and the bearing, still need consider the interval between recess and the bearing to need be correlated with compression assembly's size, therefore, with the width of recess, the thickness of bearing and the interval between recess and the bearing correlation in this embodiment, satisfy under H1, H2 and H3, 0.5< H2/(H2+H2) < 0.6's circumstances, the nearby part frame of bearing can effectively resist the deformation of bent axle when the atress to the eccentric wear problem between bent axle and the bearing is effectively improved.

In addition, the compression assembly in the technical scheme provided by the utility model can also have the following additional technical characteristics:

in some embodiments, optionally, H1 and H2 are satisfied, 0.8< H2/H1<0.9.

The radial width of recess can be to supporting compression subassembly elastic deformation's effect and influence, and the width of recess is bigger, and the frame is more easy to take place to warp, but under the too big circumstances of width of recess, the structural strength of frame is lower, causes the frame to damage easily, consequently, need inject the width scope of recess.

The width of the groove should be related to the size of the compression assembly, and the size of the bearing is generally increased when the size of the compression assembly is larger, so that in this embodiment, the radial width of the groove is related to the radial thickness of the bearing, and H1 and H2 are satisfied, and in the case that 0.8< H2/H1<0.9, the partial frame near the bearing can effectively resist the deformation of the crankshaft when being stressed, thereby effectively improving the eccentric wear problem between the crankshaft and the bearing.

In some embodiments, optionally, the length of the groove is L2, H2 and L2 are satisfied, 0.6< H2/L2<0.65, along the axial direction of the bearing.

The length of the groove and the width of the groove both have an influence on the effect of resisting the elastic deformation of the compression assembly, the effect of resisting the elastic deformation of the compression assembly is poor under the condition that the length of the groove is too large and the width of the groove is too small, and the effect of resisting the elastic deformation of the compression assembly is also poor under the condition that the length of the groove is too small and the width of the groove is too large, so that the length of the groove and the width of the groove need to be designed in a correlation mode. Under the condition that H2 and L2 are met and 0.6< H2/L2<0.65, the length of the groove is related to the width of the groove, and a part of the frame near the bearing can effectively resist the deformation of the crankshaft when being stressed, so that the eccentric wear problem between the crankshaft and the bearing is effectively improved.

In some embodiments, optionally, the axial length of the bearing is L1, L1 and L2 are satisfied, 0.12< L2/L1<0.17.

The axial length of recess can be to supporting compression subassembly elastic deformation's effect and influence, and the axial length of recess is bigger, and the frame is more easy to take place to warp, but under the too big circumstances of axial length of recess, the structural strength of frame is lower, causes the frame to damage easily, consequently, need to inject the axial length scope of recess.

The range of the axial length of the groove should be related to the size of the compression assembly, and the axial length of the bearing is generally increased when the size of the compression assembly is larger, so that in this embodiment, the axial length of the groove is related to the axial length of the bearing, and L1 and L2 are satisfied, and in the case of 0.12< L2/L1<0.17, the partial frame near the bearing can effectively resist the deformation of the crankshaft when being stressed, thereby effectively improving the eccentric wear problem between the crankshaft and the bearing.

In some embodiments, optionally, the bearing has an inner diameter D1, and the frame has a maximum width D2, D1 and D2 in the radial direction of the bearing, and 0.25< D1/D2<0.3.

In order to reduce the space occupied by the compression assembly, the compression assembly tends to be small in shell diameter, and when the maximum width of the frame is reduced, the size of the bearing is reduced, and the size of the bearing can influence the supporting effect of the crankshaft, so that the size of the bearing cannot be changed at will. In this embodiment, the maximum width of the frame is associated with the inner diameter of the bearing, and when D1 and D2 are satisfied and D1/D2 is 0.25< D1/D2<0.3, the compression assembly has the characteristic of "small shell diameter", and in the above range, the bearing can effectively support the crankshaft, so as to ensure the running stability of the compression assembly.

In some technical schemes, optionally, the crankshaft extends out of a first side of the frame, an oil groove is arranged on a second side of the frame, the first side and the second side of the frame are two sides of the frame, which are away from each other, a bearing chamber is arranged on the frame, the bearing is positioned in the bearing chamber, the groove and the bearing chamber are communicated with the oil groove, and the end part of the bearing is lower than the bottom wall of the oil groove based on the first side of the frame.

The second side of the frame is provided with the oil groove, and the bearing chamber is communicated with the oil groove, so that oil in the oil groove can flow into the bearing chamber, lubrication can be carried out between the bearing and the crankshaft by the oil, and abrasion of the crankshaft and the bearing is reduced. The crankshaft extends out of the frame in a direction away from the second side of the frame, the second side of the frame is generally provided with components such as a movable scroll, the first side of the frame is used as a reference, the end part of the bearing is lower than the bottom wall of the oil groove, namely, the bearing does not extend into the oil groove, other components in the compression assembly can be possibly installed in the oil groove, and the bearing does not extend into the oil groove in order to avoid interference between the bearing and the other components in the oil groove, so that the running stability of each component in the compression assembly is ensured.

The end of the bearing is not easy to be flush with the bottom wall of the oil groove due to the influence of the machining precision, in order to avoid the bearing extending into the oil groove due to the influence of the machining precision, the height difference is arranged between the end of the bearing and the bottom wall of the oil groove in the embodiment, and the bearing is ensured not to interfere with other parts in the oil groove.

In some technical schemes, optionally, the rack comprises a main rack, a groove and an oil groove are formed in the main rack, the extending rack is connected with the main rack, the extending rack is located on one side of the main rack along the axial direction of the crankshaft, one part of a bearing is connected with the main rack, the other part of the bearing is connected with the extending rack, the groove is formed in the bottom wall of the oil groove, and the bearing chamber is adjacent to the first side of the rack relative to the oil groove.

The oil groove can occupy the space in the frame, in order to make the bearing dodge the oil groove, extends the direction of deviating from the oil groove with a part of frame, forms and extends the frame, extends the frame and is used for installing the bearing. By extending a portion of the frame to form an extended frame, rather than integrally thickening the frame, this may reduce the footprint of the frame and may reduce the weight of the frame.

One part of the bearing is arranged on the main frame, the other part of the bearing is arranged on the extension frame, namely, the bearing chamber extends to the main frame from the extension frame, and the main frame has higher structural strength.

In some embodiments, the grooves may optionally include annular grooves extending circumferentially of the bearing, or a plurality of grooves spaced circumferentially of the bearing.

The groove can be of an annular structure, the annular groove extends along the circumferential direction of the bearing, and when the bearing receives the acting force of crankshaft deformation, part of the frame in the circumferential direction of the bearing can be correspondingly deformed.

Or a plurality of grooves can be arranged around the bearing, and two adjacent grooves are distributed at intervals, so that part of the frame in the circumferential direction of the bearing can be deformed due to the acting force of the crankshaft.

In a second aspect, the present utility model provides a refrigeration appliance including a compression assembly as in the first aspect.

In a third aspect, the utility model provides a vehicle comprising a compression assembly as in the first aspect, or a refrigeration apparatus as in the second aspect.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, or may be learned by practice of the utility model.

Drawings

The foregoing and/or additional aspects and advantages of the utility model will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 shows one of the schematic structural diagrams of a compression assembly in an embodiment of the utility model;

FIG. 2 shows a second schematic diagram of a compression assembly in an embodiment of the utility model;

Fig. 3 shows an enlarged view at a in fig. 2.

Reference numerals:

100 frames, 110 grooves, 120 oil grooves, 130 bearing chambers, 140 main frames, 150 extension frames, 200 bearings, 300 crankshafts.

Detailed Description

In order that the above-recited objects, features and advantages of the present utility model will be more clearly understood, a more particular description of the utility model will be rendered by reference to the appended drawings and appended detailed description. It should be noted that, without conflict, the embodiments of the present utility model and features in the embodiments may be combined with each other.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present utility model, but the present utility model may be practiced in other ways than those described herein, and therefore the scope of the present utility model is not limited to the specific embodiments disclosed below.

Compression assemblies, refrigeration devices, and vehicles provided according to some embodiments of the present utility model are described below with reference to fig. 1-3.

In an embodiment of the present utility model, as shown in fig. 1 and 2, a compression assembly is provided, which includes a frame 100, a bearing 200, and a crankshaft 300, wherein the frame 100 is provided with grooves 110, the bearing 200 is connected to the frame 100, the grooves 110 are distributed along a circumferential direction (indicated by an arrow at B in fig. 1) of the bearing 200, and the crankshaft 300 is penetrated through the bearing 200. Wherein the radial direction (arrow at C in fig. 2) of the bearing 200 has a thickness H1, the width of the groove 110 is H2 along the radial direction of the bearing 200, the radial distance between the groove 110 and the bearing 200 is H3, H1, H2 and H3 satisfy, 0.5< H2/(h1+h3) <0.6.

In the compression assembly provided in this embodiment, the crankshaft 300 is disposed through the bearing 200, so that the crankshaft 300 can rotate relative to the frame 100, and the rotating crankshaft 300 is used for driving the orbiting scroll to rotate. When the crankshaft 300 rotates, the crankshaft 300 is deformed, and when the contact area between the crankshaft 300 and the bearing 200 is changed, the wear amount of the bearing 200 increases. The grooves 110 are formed in the frame 100, and the grooves 110 are distributed along the circumferential direction of the bearing 200, so that a part of the frame 100 near the bearing 200 is easy to deform when being stressed, the local rigidity of the frame 100 is reduced, and the deformation capacity is increased. When the crankshaft 300 is deformed, the bearing 200 is forced to the frame 100, and the position of the bearing 200 is slightly changed since the frame 100 is easily deformed. For the difficult condition that makes the bearing 200 position change that makes of frame 100 non-deformable, the bearing 200 position in this scheme can change because of the deformation of frame 100, and frame 100 and bearing 200 can resist the great elastic deformation that compression assembly operation in-process bent axle 300 produced, increase the effective area of contact between bent axle 300 and the bearing 200, improve compression assembly operation in-process local oil film thickness, reduce the contact surface pressure between bent axle 300 and the bearing 200, can effectively improve the eccentric wear problem of bearing 200, reduce compression assembly's damage rate, be favorable to improving compression assembly operation in-process stability.

The spacing between the groove 110 and the bearing 200 affects the effect of resisting the elastic deformation of the compression assembly, and when considering the spacing between the groove 110 and the bearing 200, the spacing between the groove 110 and the bearing 200 needs to be related to the size of the compression assembly, so in this embodiment, the width of the groove 110, the thickness of the bearing 200, and the spacing between the groove 110 and the bearing 200 are related, and in the case where H1, H2, and H3 satisfy 0.5< H2/(h1+h3) <0.6, the portion of the frame 100 near the bearing 200 can effectively resist the deformation of the crankshaft 300 when being stressed, thereby effectively improving the eccentric wear problem between the crankshaft 300 and the bearing 200.

As shown in connection with fig. 1 and 2, in some embodiments, optionally, H1 and H2 are satisfied, 0.8< H2/H1<0.9.

The radial width of the groove 110 may affect the effect of resisting the elastic deformation of the compression assembly, and the larger the width of the groove 110, the more easily the frame 100 is deformed, but in the case that the width of the groove 110 is too large, the structural strength of the frame 100 is low, and the frame 100 is easily damaged, so that the width range of the groove 110 needs to be limited.

The width of the groove 110 should be in a range related to the size of the compression assembly, and the size of the bearing 200 is generally increased as the size of the compression assembly is increased, so that the radial width of the groove 110 is related to the radial thickness of the bearing 200 in this embodiment, H1 and H2 are satisfied, and in the case of 0.8< H2/H1<0.9, the partial frame 100 near the bearing 200 can effectively resist the deformation of the crankshaft 300 when being stressed, thereby effectively improving the eccentric wear problem between the crankshaft 300 and the bearing 200.

As shown in connection with fig. 1 and 2, in some embodiments, the groove 110 may optionally have a length L2, H2 and L2 along the axial direction of the bearing 200 (indicated by the arrow at D in fig. 2), with 0.6< H2/L2<0.65.

Both the length of the groove 110 and the width of the groove 110 will affect the effect of resisting the elastic deformation of the compression assembly, and in the case that the length of the groove 110 is too large and the width of the groove 110 is too small, the effect of resisting the elastic deformation of the compression assembly is poor, and in the case that the length of the groove 110 is too small and the width of the groove 110 is too large, the effect of resisting the elastic deformation of the compression assembly is also poor, so that the length of the groove 110 and the width of the groove 110 need to be designed in a correlated manner. In the case where H2 and L2 are satisfied, 0.6< H2/L2<0.65, the length of the groove 110 is associated with the width of the groove 110, and the portion of the frame 100 near the bearing 200 can effectively resist deformation of the crankshaft 300 when being stressed, thereby effectively improving the problem of eccentric wear between the crankshaft 300 and the bearing 200.

As shown in connection with fig. 1 and 2, in some embodiments, optionally, the axial length of the bearing 200 is L1, L1 and L2 are satisfied, 0.12< L2/L1<0.17.

The axial length of the groove 110 may affect the effect of resisting the elastic deformation of the compression assembly, and the larger the axial length of the groove 110, the more easily the frame 100 is deformed, but in the case that the axial length of the groove 110 is too large, the structural strength of the frame 100 is lower, and the frame 100 is easily damaged, so that the axial length range of the groove 110 needs to be limited.

The range of the axial length of the groove 110 should be related to the size of the compression assembly, and the axial length of the bearing 200 is generally increased as the size of the compression assembly is larger, so that in this embodiment, the axial length of the groove 110 is related to the axial length of the bearing 200, and L1 and L2 satisfy, where 0.12< L2/L1<0.17, the portion of the frame 100 near the bearing 200 can effectively resist deformation of the crankshaft 300 when being stressed, thereby effectively improving the problem of eccentric wear between the crankshaft 300 and the bearing 200.

As shown in fig. 2, in some embodiments, optionally, the bearing 200 has an inner diameter D1, and the maximum widths of the frame 100 along the radial direction of the bearing 200 are D2, D1 and D2 satisfying 0.25< D1/D2<0.3.

In order to reduce the space occupied by the compression assembly, the compression assembly is moved toward a smaller shell diameter, and the size of the bearing 200 should be reduced when the maximum width of the frame 100 is reduced, and the size of the bearing 200 may affect the supporting effect of the crankshaft 300, so that the size of the bearing 200 cannot be arbitrarily changed. In this embodiment, the maximum width of the frame 100 is associated with the inner diameter of the bearing 200, and when D1 and D2 are satisfied and D1/D2 is 0.25< D1/D2<0.3, the compression assembly has the characteristic of "small shell diameter", and in the above range, the bearing 200 can effectively support the crankshaft 300, so as to ensure the running stability of the compression assembly.

As shown in connection with fig. 2 and 3, in some embodiments, optionally, the crankshaft 300 extends out of a first side of the frame 100, an oil groove 120 is provided on a second side of the frame 100, the first side and the second side of the frame 100 are opposite sides of the frame 100, a bearing chamber 130 is provided on the frame 100, the bearing 200 is located in the bearing chamber 130, and the groove 110 and the bearing chamber 130 are both in communication with the oil groove 120. Wherein, based on the first side of the frame 100, the end of the bearing 200 is lower than the groove bottom wall of the oil groove 120.

An oil sump 120 is provided at the second side of the frame 100, and the bearing chamber 130 is in communication with the oil sump 120, so that oil in the oil sump 120 can flow into the bearing chamber 130, so that the oil can lubricate between the bearing 200 and the crankshaft 300, and wear of the crankshaft 300 and the bearing 200 is reduced. The crankshaft 300 extends out of the frame 100 in a direction away from the second side of the frame 100, where the second side of the frame 100 is typically provided with a moving scroll or the like, and based on the first side of the frame 100, the end of the bearing 200 is lower than the bottom wall of the oil sump 120, i.e. the bearing 200 does not extend into the oil sump 120, and since other components in the compression assembly may be installed in the oil sump 120, in order to avoid interference between the bearing 200 and other components in the oil sump 120, the bearing 200 is not extended into the oil sump 120, thereby ensuring the operation stability of each component in the compression assembly.

The end of the bearing 200 is not easy to be flush with the bottom wall of the oil groove 120 due to the influence of the machining precision, in order to avoid the bearing 200 extending into the oil groove 120 due to the influence of the machining precision, in this embodiment, a height difference is arranged between the end of the bearing 200 and the bottom wall of the oil groove 120, so that the bearing 200 is ensured not to interfere with other components in the oil groove 120.

As shown in FIG. 2, in some embodiments, the frame 100 optionally includes a main frame 140 and an extension frame 150, the recess 110 and the sump 120 being provided on the main frame 140, the extension frame 150 being connected to the main frame 140, the extension frame 150 being located on one side of the main frame 140 in an axial direction of the crankshaft 300, a portion of the bearing 200 being connected to the main frame 140, another portion of the bearing 200 being connected to the extension frame 150, wherein the recess 110 is provided on a bottom wall of the sump 120, and the bearing chamber 130 being adjacent to a first side of the frame 100 relative to the sump 120.

The oil sump 120 occupies a space on the frame 100, and in order to avoid the oil sump 120 by the bearing 200, a portion of the frame 100 is extended in a direction away from the oil sump 120 to form an extension frame 150, and the extension frame 150 is used for installing the bearing 200. By extending a portion of the frame 100 to form the extension frame 150, rather than integrally thickening the frame 100, this may reduce the footprint of the frame 100 and may reduce the weight of the frame 100.

A part of the bearing 200 is mounted on the main frame 140, and another part of the bearing 200 is mounted on the extension frame 150, that is, the bearing housing 130 extends from the extension frame 150 to the main frame 140, and the main frame 140 has high structural strength, so that the bearing 200 can effectively support the crankshaft 300.

The bearing chamber 130 is communicated with the bottom of the oil sump 120, in this case, the groove 110 is disposed at the bottom wall of the oil sump 120, so that the groove 110 is located at the side of the bearing chamber 130, ensuring that the groove 110 can effectively reduce the local rigidity of the frame 100 and improve the deformability of the local frame 100.

In some embodiments, the grooves 110 optionally include annular grooves that extend in the circumferential direction of the bearing 200, or the number of grooves 110 is a plurality of grooves 110 spaced apart in the circumferential direction of the bearing 200.

The groove 110 may have an annular structure, and the annular groove extends along the circumferential direction of the bearing 200, so that when the bearing 200 receives the force of deforming the crankshaft 300, a part of the frame 100 in the circumferential direction of the bearing 200 can be deformed accordingly.

Alternatively, a plurality of grooves 110 may be provided around the bearing 200, and two adjacent grooves 110 may be spaced apart, so that a part of the frame 100 in the circumferential direction of the bearing 200 may be deformed by the force of the crankshaft 300.

The bearing 200 is located at the end of the machine frame 100 along the axial direction, the main shaft part of the crankshaft 300 and the bearing 200 are coaxial and slide relatively, the groove 110 is located at one side of the bottom of the oil groove 120 of the machine frame 100 close to the bearing 200 and extends downwards to form an evenly distributed annular groove wall structure, so that the local rigidity of the structure can be effectively reduced, the local deformation can be increased, the thickness of an oil film of the main shaft can be improved, the contact area between the crankshaft 300 and the bearing 200 can be further increased, the contact pressure can be reduced, the effect of improving local eccentric wear can be achieved, and the running reliability of the compressor can be further effectively improved.

The compression assembly in this embodiment may be a scroll compressor.

In the embodiment of the utility model, a refrigeration device is provided, which includes the compression assembly in any of the above embodiments, and can achieve the same technical effects, and will not be described herein.

Illustratively, the refrigeration appliance is an air conditioner.

In the embodiment of the utility model, a vehicle is provided, which comprises the compression assembly in any embodiment, or the refrigeration equipment in any embodiment, and can achieve the same technical effects, and the description is omitted herein.

The vehicle can be a traditional fuel vehicle or a new energy vehicle. The new energy automobile comprises a pure electric automobile, a range-extended electric automobile, a hybrid electric automobile, a fuel cell electric automobile, a hydrogen engine automobile and the like.

In the present utility model, the term "plurality" means two or more, unless explicitly defined otherwise. The terms "mounted," "connected," "secured," and the like are to be construed broadly, as they are used in a fixed or removable connection, or as they are integral with one another, as they are directly or indirectly connected through intervening media. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the description of the present specification, the terms "one embodiment," "some embodiments," "particular embodiments," and the like, mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only of the preferred embodiments of the present utility model and is not intended to limit the present utility model, but various modifications and variations can be made to the present utility model by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.

Claims (10)

1. A compression assembly, comprising: A frame, wherein a groove is provided on the frame; A bearing connected to the frame, wherein the grooves are distributed along the circumference of the bearing; A crankshaft, wherein the crankshaft passes through the bearing; The radial thickness of the bearing is H1, the width of the groove in the radial direction of the bearing is H2, the radial spacing between the groove and the bearing is H3, and H1, H2 and H3 satisfy 0.5＜H2/(H1+H3)＜0.6. 2. The compression assembly according to claim 1, characterized in that H1 and H2 satisfy 0.8＜H2/H1＜0.9. 3. The compression assembly according to claim 1 is characterized in that the axial length of the bearing is L1, the length of the groove along the axial direction of the bearing is L2, and L1 and L2 satisfy 0.12＜L2/L1＜0.17. 4. The compression assembly according to claim 3, characterized in that H2 and L2 satisfy 0.6＜H2/L2＜0.65. 5. The compression assembly according to any one of claims 1 to 4, characterized in that the inner diameter of the bearing is D1, the maximum width of the frame along the radial direction of the bearing is D2, and D1 and D2 satisfy 0.25＜D1/D2＜0.3. 6. The compression assembly according to any one of claims 1 to 4, characterized in that the crankshaft extends out of the first side of the frame, the second side of the frame is provided with an oil groove, the first side and the second side of the frame are two opposite sides of the frame, a bearing chamber is provided on the frame, the bearing is located in the bearing chamber, and the groove and the bearing chamber are both connected to the oil groove; Wherein, based on the first side of the frame, the end of the bearing is lower than the bottom wall of the oil groove. 7. The compression assembly according to claim 6, wherein the frame comprises: A main frame, the groove and the oil groove are arranged on the main frame; An extension frame connected to the main frame, and along the axial direction of the crankshaft, the extension frame is located on one side of the main frame, a part of the bearing is connected to the main frame, and another part of the bearing is connected to the extension frame; Wherein, the groove is arranged on the bottom wall of the oil groove; the bearing chamber is adjacent to the first side of the frame relative to the oil groove. 8. The compression assembly according to any one of claims 1 to 4, characterized in that the groove comprises an annular groove extending along the circumference of the bearing; or There are multiple grooves, and the multiple grooves are distributed at intervals along the circumference of the bearing. 9. A refrigeration device, comprising: A compression assembly as claimed in any one of claims 1 to 8. 10. A vehicle, comprising: A compression assembly as claimed in any one of claims 1 to 8; or The refrigeration device as claimed in claim 9.