Compressor and refrigeration apparatus

Abstract

The application discloses a compressor and a refrigeration equipment, and relates to the technical field of compressor structure, wherein the compressor comprises a crankcase, a crankshaft and a crankshaft matching cover; the crankcase comprises a piston cylinder and a crankshaft operation area located on one side of the piston cylinder; the crankshaft comprises a main shaft and an eccentric shaft located at the end of the main shaft; the eccentric shaft extends into the crankshaft operation area; and one end of the eccentric shaft away from the main shaft is further provided with a secondary shaft; the crankshaft matching cover is arranged on the crankshaft operation area; the crankshaft matching cover comprises a main body; the main body has opposite first and second sides; the first side of the main body faces the crankcase; the first side of the main body is provided with a rotating groove; and the rotating groove is rotationally matched with the secondary shaft arranged at one end of the crankshaft. The application aims to improve the poor running stability and large wear of the main shaft of the compressor crankshaft when the matching size of the main shaft and the motor is small.

Description

Technical Field

[0001] This invention relates to the field of compressor structure technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] Reciprocating compressors are widely used in refrigerators and freezers due to their excellent cooling performance. The overall size of the compressor significantly affects the volumetric efficiency of the refrigerator or freezer, which is closely related to its economic benefits. Therefore, current compressor designs often optimize the compressor structure to reduce its axial dimension. Optimizing the motor assembly size reduces the rotor component's mating area with the crankshaft, leading to increased crankshaft wear. This significantly impacts the compressor's operational stability and lifespan. Summary of the Invention

[0003] The main objective of this invention is to provide a compressor and refrigeration equipment that improves the poor crankshaft stability and high wear when the main shaft and motor of the compressor crankshaft have small mating dimensions.

[0004] To achieve the above objectives, the compressor includes:

[0005] A crankcase, including a piston cylinder and a crankshaft operating area located on one side of the piston cylinder;

[0006] A crankshaft includes a main shaft and an eccentric shaft located at the end of the main shaft, the eccentric shaft extending into the crankshaft's operating region, and a secondary shaft being provided at the end of the eccentric shaft furthest from the main shaft; and,

[0007] A crankshaft mating cover is provided on the crankshaft operating area. The crankshaft mating cover includes a main body, which has a first side and a second side facing each other. The first side of the main body faces the crankcase and is provided with a rotating groove. The rotating groove is rotatably engaged with a countershaft located at one end of the crankshaft.

[0008] In one embodiment, the rotating groove is configured as an annular groove, which provides rotational engagement with a secondary shaft coaxially arranged with the eccentric shaft of the crankshaft.

[0009] In one embodiment, a groove is provided on the first side of the main body, and a protrusion is provided in the middle of the groove, and the annular groove is defined between the protrusion and the inner side of the groove.

[0010] In one embodiment, a mounting portion is provided on the first side of the main body near the edge, and the mounting portion is mounted to the crankcase.

[0011] In one embodiment, the bottom of the rotating groove is provided with multiple oil storage tanks.

[0012] In one embodiment, a plurality of the oil storage tanks are distributed radially and / or circumferentially along the rotating groove.

[0013] In one embodiment, within a group of oil storage tanks arranged radially along the rotating groove, the center-to-center distance between adjacent oil storage tanks is a, where a ≤ 0.5 mm; and / or,

[0014] The depth of the oil storage tank is b, where b ≤ 0.5 mm; and / or,

[0015] The diameter of the oil storage tank is c, where c ≤ 0.5 mm.

[0016] In one embodiment, the secondary shaft is coaxially arranged with the eccentric shaft, and the rotating groove is an annular groove.

[0017] In one embodiment, the compressor further includes a piston movably disposed within the piston cylinder and a connecting rod that drivesly connects the piston and the eccentric shaft;

[0018] A groove is provided on the first side of the main body, and a protrusion is provided in the middle of the groove. The protrusion and the inner side of the groove define the annular groove.

[0019] The connecting rod has a first gap A between one end of the eccentric shaft and the free end of the protrusion, where A ≥ 1 mm.

[0020] In one embodiment, a second gap B is provided between the secondary shaft and the bottom of the rotating groove, such that 2mm≤B≤3mm.

[0021] In one embodiment, a movable gap is provided between the secondary shaft and the wall of the rotating groove, and the movable gap is C, where 10μm≤C≤15μm.

[0022] In one embodiment, in the length direction of the crankshaft, the second side of the crankshaft mating cover is flush with the end face of the crankcase, or the second side of the crankshaft mating cover is lower than the end face of the crankcase.

[0023] In one embodiment, the crankcase is provided with two support portions, and the two support portions are respectively located on both sides of the crankshaft operating area. The first side of the main body is provided with two mounting portions near the edge, and the two mounting portions are respectively mounted to the two support portions.

[0024] In one embodiment, the compressor further includes a high-pressure chamber assembly disposed on the outside of the support portion, and the distance between the high-pressure chamber assembly and the support portion is D, where D≥3mm.

[0025] The present invention also proposes a refrigeration device, wherein the refrigeration device includes a compressor, the compressor comprising:

[0026] A crankcase, including a piston cylinder and a crankshaft operating area located on one side of the piston cylinder;

[0027] A crankshaft includes a main shaft and an eccentric shaft located at the end of the main shaft, the eccentric shaft extending into the crankshaft's operating region, and a secondary shaft being provided at the end of the eccentric shaft furthest from the main shaft; and,

[0028] A crankshaft mating cover is provided on the crankshaft operating area. The crankshaft mating cover includes a main body, which has a first side and a second side facing each other. The first side of the main body faces the crankcase and is provided with a rotating groove. The rotating groove is rotatably engaged with a countershaft located at one end of the crankshaft.

[0029] In the technical solution of this invention, the main shaft of the crankshaft is used to cooperate with the rotor of the motor, and the eccentric shaft is used to drive the piston through the connecting rod. Based on this, this application provides a secondary shaft at the end of the eccentric shaft away from the main shaft, and adds a crankshaft mating cover to the crankcase. By providing a rotating groove on the first side of the crankshaft mating cover facing the crankcase, and having the rotating groove rotatably engage with the secondary shaft, the engagement between the secondary shaft and the crankshaft mating cover is added to the existing engagement between the main shaft and the rotor of the crankshaft. This allows for the optimization of motor dimensions and reduction of rotor component dimensions, thereby reducing the mating area between the main shaft and the rotor component. The engagement between the secondary shaft and the rotating groove further increases the crankshaft positioning mating area, stabilizing the crankshaft, improving crankshaft operating stability, reducing crankshaft wear, and thus extending crankshaft service life. This meets the requirements of size optimization while minimizing the impact on the original compressor performance. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0031] Figure 1 A three-dimensional structural schematic diagram of a portion of the compressor provided by the present invention;

[0032] Figure 2 for Figure 1 A schematic diagram of the planar structure of the compressor;

[0033] Figure 3 for Figure 1 Another schematic diagram of the planar structure of the compressor;

[0034] Figure 4 for Figure 3 Schematic diagram of the cross section at point XX';

[0035] Figure 5 for Figure 3 A schematic diagram of the cross-section at point YY';

[0036] Figure 6 for Figure 1 A three-dimensional structural diagram of the crankcase in the image;

[0037] Figure 7 for Figure 1 A three-dimensional structural diagram of the crankshaft fitting cover;

[0038] Figure 8 for Figure 7 A schematic diagram of a planar structure of the crankshaft fitting cover;

[0039] Figure 9 for Figure 7 Another planar structural diagram of the crankshaft fitting cover;

[0040] Figure 10 for Figure 7 A cross-sectional schematic diagram of the crankshaft fitting cover.

[0041] Explanation of icon numbers:

[0042] 1000, Compressor; 100, Crankshaft mating cover; 1, Main body; 1a, First side; 1b, Second side; 11, Rotating groove; 11a, Annular groove; 111, Groove; 112, Protrusion; 113, Oil reservoir; 12, Mounting part; 200, Crankshaft case; 201, Piston cylinder; 202, Crankshaft operating area; 203, Piston; 204, Connecting rod; 205, Support part; 300, Crankshaft; 301, Main shaft; 302, Eccentric shaft; 303, Secondary shaft; 400, High-pressure chamber assembly.

[0043] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0044] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0045] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0046] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0047] Reciprocating compressors are widely used in refrigerators and freezers due to their excellent cooling performance. The overall size of the compressor significantly affects the volumetric efficiency of the refrigerator or freezer, which is closely related to its economic benefits. Therefore, current compressor designs often optimize the compressor structure to reduce its axial dimension. Optimizing the motor assembly size reduces the rotor component's mating area with the crankshaft, leading to increased crankshaft wear. This significantly impacts the compressor's operational stability and lifespan.

[0048] In view of this, the present invention proposes a compressor, please refer to [link / reference]. Figures 1 to 10 The following is a detailed description of the compressor as described in this application, with reference to the accompanying drawings.

[0049] Please see Figures 1 to 10The compressor 1000 includes a crankcase 200, a crankshaft 300, and a crankshaft mating cover 100. The crankcase 200 includes a piston cylinder 201 and a crankshaft operating area 202 located on one side of the piston cylinder 201. The crankshaft 300 includes a main shaft 301 and an eccentric shaft 302 located at the end of the main shaft 301. The eccentric shaft 302 extends into the crankshaft operating area 202, and a secondary shaft 303 is provided at the end of the eccentric shaft 302 away from the main shaft 301. The crankshaft mating cover 100 covers the crankshaft operating area 202. The crankshaft mating cover 100 includes a main body 1. The main body 1 has a first side 1a and a second side 1b. The first side 1a of the main body 1 faces the crankcase 200, and a rotating groove 11 is provided on the first side 1a of the main body 1. The rotating groove 11 is rotatably engaged with the secondary shaft 303 located at one end of the crankshaft 300.

[0050] In the technical solution of this invention, the main shaft 301 of the crankshaft 300 is used to cooperate with the rotor of the motor, and the eccentric shaft 302 is used to drive the piston 203 through the connecting rod 204. Based on this, this application provides a secondary shaft 303 at the end of the eccentric shaft 302 away from the main shaft 301. Simultaneously, a crankshaft mating cover 100 is added to the crankcase 200. A rotating groove 11 is provided on the first side 1a of the crankshaft mating cover 100 facing the crankcase 200, and the rotating groove 11 is rotatably fitted to the secondary shaft 303, so that the crankshaft 300, from the main shaft 301 to the rotor… Based on the existing cooperation, the cooperation between the secondary shaft 303 and the crankshaft cooperation cover 100 is added. This allows for the optimization of motor size and reduction of rotor component size, thereby reducing the cooperation area between the main shaft 301 and the rotor component cooperation section. Through the cooperation between the secondary shaft 303 and the rotating groove 11, the positioning cooperation area of ​​the crankshaft 300 is additionally increased, which stabilizes the crankshaft 300, improves the operating stability of the crankshaft 300, improves the wear of the crankshaft 300, and thus increases the service life of the crankshaft 300. This meets the size optimization requirements while reducing the impact on the performance of the original compressor 1000.

[0051] Of course, the method of setting the crankshaft mating cover 100 on the crankcase 200 to increase the mating area with the crankshaft 300 can also be used in the existing compressor 1000. Increasing the mating area can also improve the stability of the crankshaft 300 operation and optimize the wear of the crankshaft 300. The specific application scenario depends on actual needs, aiming to expand the design feasibility of the compressor 1000 and meet the functional design requirements.

[0052] Specifically, please refer to Figure 3The rotating groove 11 is configured as an annular groove 11a, which is used to allow the auxiliary shaft 303, which is coaxially arranged with the eccentric shaft 302 of the crankshaft 300, to rotate. It is understood that the specific position of the secondary shaft 303 located at one end of the eccentric shaft 302 is not limited. For example, it can be coaxially arranged with the main shaft 301 of the crankshaft 300, or coaxially arranged with the eccentric shaft 302, or even independently of the main shaft 301 and the eccentric shaft 302. It is only necessary that the rotating groove 11 on the crankshaft mating cover 100 can accommodate the secondary shaft 303. In this embodiment, the secondary shaft 303 is set to be coaxially arranged with the eccentric shaft 302. Therefore, the rotating groove 11 is correspondingly set as the annular groove 11a for rotational engagement with the secondary shaft 303. The coaxial arrangement of the secondary shaft 303 and the eccentric shaft 302 can be understood as axially extending the eccentric shaft 302, which is convenient for manufacturing and has a stable and strong connection. Furthermore, based on the coaxial arrangement of the eccentric shaft 302 and the secondary shaft 303, the diameters of the secondary shaft 303 and the eccentric shaft 302 do not actually need to be the same. As long as the secondary shaft 303 can fit with the annular groove 11a to increase the mating area, thereby improving the running stability of the crankshaft 300 and optimizing wear, it is sufficient. In this embodiment, the diameters of the eccentric shaft 302 and the secondary shaft 303 are set to be the same, which is also for ease of manufacturing and low cost.

[0053] Further reading Figure 3 The first side 1a of the main body 1 is provided with a groove 111, and a protrusion 112 is provided in the middle of the groove 111. The annular groove 11a is defined between the protrusion 112 and the inner side of the groove 111. There are several ways to provide the annular groove 11a on the main body 1. For example, an annular groove 11a can be directly opened on the first side 1a of the main body 1, that is, the height of the middle part and the outer edge are basically the same. Alternatively, a groove 111 can be opened on the first side 1a of the main body 1, and a columnar structure can be provided in the middle of the groove 111 to form the annular groove 11a. In this embodiment, a protruding post 112 is provided in the groove 111. The protruding post 112 can be integrally formed with the main body 1, or it can be independently set and assembled to the main body 1. However, the integrally formed structure obviously has higher strength. The structure of providing the protruding post 112 in the middle of the groove 111 is mainly used to adjust the height of the protruding post 112. That is, its height can have a height difference with the outer edge of the groove 111. When the structural dimensions are satisfied, increasing the height of the protruding post 112 can further increase the mating area between the sub-shaft 303 and the protruding post 112, thereby further improving the stability of the crankshaft 300 operation.

[0054] Furthermore, a mounting portion 12 is provided on the first side 1a of the main body 1 near its edge, and the mounting portion 12 is used to install it onto the crankcase 200. The method of fixing the crankshaft mating cover 100 to the crankcase 200 is not limited here, as long as it ensures that the crankshaft mating cover 100 is stably installed on the crankcase 200. In this embodiment, the mounting portion 12 is provided on the first side 1a of the main body 1 near its edge, so that it can be installed onto the crankcase 200. The structure is simple and easy to install.

[0055] In addition, please see Figure 9 The bottom of the rotating groove 11 is provided with multiple oil storage grooves 113. The crankshaft 300 requires lubrication during rotation to reduce rotational wear and extend its service life. In addition to the crankshaft mating cover 100, the auxiliary shaft 303 also requires lubrication when mating with the rotating groove 11. Therefore, in this embodiment, multiple oil storage grooves 113 are provided at the bottom of the rotating groove 11 to store lubricant, thereby ensuring lubricant coverage between the auxiliary shaft 303 and the rotating groove 11, meeting structural and functional requirements, and improving its service life.

[0056] Furthermore, the plurality of oil storage tanks 113 are distributed radially and / or circumferentially along the rotating groove 11. The arrangement of the plurality of storage tanks is not limited, as they all fulfill their liquid storage function. For example, they can be randomly arranged, arranged in an array, or arranged circumferentially. In this embodiment, the oil storage tanks 113 are arranged radially and circumferentially along the rotating groove 11 to form a structure radiating outwards from the center of the rotating groove 11. This arrangement makes the distribution of the plurality of oil storage tanks 113 more uniform, and the regular arrangement facilitates manufacturing and reduces costs.

[0057] Specifically, within a group of oil storage tanks 113 arranged radially along the rotating groove 11, the center-to-center distance between adjacent oil storage tanks 113 is 'a', where 'a' ≤ 0.5 mm; the depth of each oil storage tank 113 is 'b', where 'b' ≤ 0.5 mm; and the diameter of each oil storage tank 113 is 'c', where 'c' ≤ 0.5 mm. It is understood that the specific dimensions of the oil storage tanks 113 are primarily determined by actual needs, ensuring the liquid storage function is met without affecting the structural function of the crankshaft mating cover 100. In this embodiment, the center-to-center distance between two adjacent oil storage tanks 113 arranged radially along the rotating groove 11 is set to no more than 0.5 mm, and the diameter and depth of each oil storage tank are also set to no more than 0.5 mm to meet structural requirements. Specifically, the center-to-center distance between two adjacent oil storage tanks 113 arranged radially along the rotating groove 11, as well as the diameter and depth of each storage tank, are preferably set to 0.5 mm.

[0058] Specifically, the structure of the crankcase 200 is almost identical to that of the existing structure. It is provided with the piston cylinder 201 and the crankshaft operating area 202 located on one side of the piston cylinder 201. Correspondingly, the eccentric shaft 302 of the crankshaft 300 needs to extend into the crankshaft operating area 202 to drive the piston 203 to move within the piston cylinder 201. Based on this, the crankshaft mating cover 100 provided in this application can be set at the position of the crankcase 200 corresponding to the crankshaft operating area 202, and will not affect the operation of the compressor 1000 itself, thus meeting the structural and functional requirements.

[0059] Specifically, the secondary shaft 303 is coaxially arranged with the eccentric shaft 302, and the rotating groove 11 is an annular groove 11a. The coaxial arrangement of the secondary shaft 303 and the eccentric shaft 302 has been described in detail above and will not be repeated here. Similarly, the setting of the rotating groove 11 as an annular groove 11a has also been described above and will not be repeated here.

[0060] Further, please refer to Figure 4The compressor 1000 further includes a piston 203 movably disposed within the piston cylinder 201 and a connecting rod 204 drivingly connecting the piston 203 and the eccentric shaft 302; a groove 111 is provided on the first side 1a of the main body 1, and a protrusion 112 is provided in the middle of the groove 111, and the annular groove 11a is defined between the protrusion 112 and the inner side of the groove 111; a first gap A, A≥1mm, is formed between the end of the connecting rod 204 that connects to the eccentric shaft 302 and the free end of the protrusion 112. The above text describes the specific configuration of the annular groove 11a. Specifically, the first side 1a of the main body 1 has the groove 111, and the protrusion 112 is provided in the middle of the groove 111. The annular groove 11a is defined by the protrusion 112 and the inner surface of the groove 111. The height of the protrusion 112 can be set according to actual needs. Specifically, the height of the protrusion 112 can be increased to improve the mating area with the secondary shaft 303, thereby improving the running stability of the crankshaft 300. Based on this, in this embodiment, the secondary shaft 303 and the eccentric shaft 302 are coaxially arranged, and their diameters are similar for ease of manufacturing. Therefore, the connecting rod 204 sleeved on the eccentric shaft 302 may dynamically shift towards the secondary shaft 303 along the axial direction of the eccentric shaft 302. During the operation of the compressor 1000, there is a risk that the connecting rod 204 may contact the protrusion 112. Therefore, in this embodiment… The distance between the protrusion 112 and the connecting rod 204 is limited to 1mm or greater. If it is less than 1mm, wear or even collision may occur, affecting the normal operation of the compressor 1000. Conversely, a distance greater than 1mm can avoid contact problems. However, a larger distance requires increasing the height of the crankshaft mating cover 100 to ensure the mating area between the sub-shaft 303 and the protrusion 112, thus affecting the overall height of the compressor 1000 and consequently the spatial layout of the refrigeration equipment using the compressor 1000. On the other hand, reducing the height of the protrusion 112 requires decreasing the height of the crankshaft mating cover 100, which in turn affects the mating area between the sub-shaft 303 and the protrusion 112 and weakens the stability of the mating between the sub-shaft 303 and the annular groove 11a. Therefore, in this embodiment, the distance between the protrusion 112 and the connecting rod 204 is set to 1mm to avoid the above problems.

[0061] In addition, please continue to refer to Figure 4A second gap B is provided between the secondary shaft 303 and the bottom of the rotating groove 11, where 2mm ≤ B ≤ 3mm. Similar to the spacing between the protruding post 112 and the connecting rod 204, to avoid contact friction or even collision between the secondary shaft 303 and the bottom of the rotating groove 11, this embodiment also provides a second gap between the secondary shaft 303 and the bottom of the rotating groove 11. The size of the second gap is set between 2mm and 3mm. It can be understood that when the size of the second gap is less than 2mm, the distance between the secondary shaft 303 and the bottom of the rotating groove 11 is relatively close, posing the aforementioned risk of friction and collision. If the size of the second gap is set to be greater than 3mm, it will affect the overall height of the compressor 1000. In this embodiment, the size of the second gap is set to 3mm to meet the above requirements and avoid the aforementioned problems.

[0062] In addition, a movable gap is provided between the secondary shaft 303 and the groove wall of the rotating groove 11, and the movable gap is C, 10μm≤C≤15μm. The cooperation between the secondary shaft 303 and the rotating groove 11 requires a certain gap because the secondary shaft 303 needs to rotate within the rotating groove 11. However, to ensure proper support for the cooperation between the secondary shaft 303 and the rotating groove 11, the gap cannot be too large. Therefore, in this embodiment, the movable gap is set between 10μm and 15μm to ensure the aforementioned functional effect. It is understood that if the movable gap is less than 10μm, there may be significant contact friction between the secondary shaft 303 and the rotating groove 11, affecting the normal operation of the crankshaft 300 and causing wear that results in a shorter service life. Conversely, if the movable gap is greater than 15μm, the cooperation effect between the secondary shaft 303 and the groove wall of the rotating groove 11 is compromised, failing to provide stable support and affecting the rotational stability of the crankshaft 300. This also results in heavy wear between the secondary shaft 303 and the rotating groove 11. Therefore, in this embodiment, the movable gap is set to 15μm to meet the above requirements. Specifically, the rotating groove 11 is configured as the annular groove 11a as described above, and the annular groove 11a is formed by the combination of the groove 111 and the protrusion 112. The gap between the secondary shaft 303 and the groove wall of the groove 111 and the gap between the secondary shaft 303 and the outer wall of the protrusion 112 are both the movable gaps, and in this embodiment, they are all set to 15μm.

[0063] Furthermore, along the length of the crankshaft 300, the second side 1b of the crankshaft mating cover 100 is flush with the end face of the crankcase 200, or the second side 1b of the crankshaft mating cover 100 is lower than the end face of the crankcase 200. The crankshaft mating cover 100 covers the crankcase 200. Based on the structural requirement to reduce the height of the compressor 1000, the addition of the crankshaft mating cover 100 cannot increase the structural height of the crankcase 200. Therefore, in this embodiment, the end face of the second side 1b of the crankshaft mating cover 100 is limited to not being higher than the top end face of the crankcase 200, i.e., flush with or lower than the top end face of the crankcase 200, to meet the above requirements.

[0064] Furthermore, the crankcase 200 has two protruding support portions 205, which are located on both sides of the crankshaft operating area 202. Two mounting portions 12 are correspondingly provided on the first side 1a of the main body 1 near its edge, and these two mounting portions 12 are installed onto the two support portions 205. The mating structure between the crankshaft 300 mating portion and the crankcase 200 is not limited; it is sufficient that the crankshaft 300 mating portion can be fixed to the crankcase 200 through a corresponding connection structure. In this embodiment, two support portions 205 are provided on the crankcase 200, and two mounting portions 12 are correspondingly provided on the crankshaft 300 mating portion. The crankshaft mating cover 100 is positioned and installed on the crankcase 200 through the alignment of the support portions 205 and the mounting portions 12. The mounting portions 12 and the support portions 205 are connected by bolts, resulting in a simple structure, stable connection, and low cost.

[0065] In addition, the compressor 1000 also includes a high-pressure chamber assembly 400, which is disposed on the outside of the support portion 205, and the distance between the high-pressure chamber assembly 400 and the support portion 205 is D, where D≥3mm. The compressor 1000 also includes a high-pressure chamber assembly 400 disposed on the side of the crankcase 200. The existing crankcase 200 has a certain clearance space corresponding to the position of the high-pressure chamber assembly 400, facilitating the avoidance of the high-pressure chamber assembly 400. After the support portion 205 is provided on the crankcase 200, the high-pressure chamber assembly 400 and the support portion 205 are disposed opposite each other. Therefore, to avoid collision between the high-pressure chamber assembly 400 and the support portion 205 during compressor 1000 operation, this embodiment limits the installation distance between the high-pressure chamber assembly 400 and the support portion 205 to not less than 3mm. Specifically, in this embodiment, 4mm is preferred, to ensure the anti-collision clearance while avoiding increasing the space occupied by the crankcase 200 and the high-pressure chamber assembly 400 after combined installation.

[0066] The present invention also proposes a refrigeration device, which includes the compressor 1000. The specific structure of the compressor 1000 is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The refrigeration device includes refrigerators, freezers, and other devices that use the compressor 1000 as a refrigeration system component. In this embodiment, the refrigeration device is mainly a refrigerator.

[0067] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A compressor, characterized in that, include: A crankcase, including a piston cylinder and a crankshaft operating area located on one side of the piston cylinder; A crankshaft includes a main shaft and an eccentric shaft located at the end of the main shaft, the eccentric shaft extending into the crankshaft's operating region, and a secondary shaft being provided at the end of the eccentric shaft furthest from the main shaft; and... A crankshaft mating cover is provided on the crankshaft operating area. The crankshaft mating cover includes a main body, which has a first side and a second side facing each other. The first side of the main body faces the crankshaft housing and is provided with a rotating groove. The rotating groove is rotatably engaged with a countershaft located at one end of the crankshaft. The rotating groove is configured as an annular groove, which allows a secondary shaft coaxially arranged with the eccentric shaft of the crankshaft to rotate and engage. A second gap B is provided between the secondary shaft and the bottom of the rotating groove, and multiple oil storage grooves are provided at the bottom of the rotating groove. Along the length of the crankshaft, the second side of the crankshaft mating cover is flush with the end face of the crankcase, or the second side of the crankshaft mating cover is lower than the end face of the crankcase. A groove is provided on the first side of the main body, and a protrusion is provided in the middle of the groove. The protrusion and the inner side of the groove define the annular groove; the diameter of the eccentric shaft and the secondary shaft are set to be the same.

2. The compressor as described in claim 1, characterized in that, A mounting part is provided on the first side of the main body near the edge, and the mounting part is installed to the crankcase.

3. The compressor as described in claim 1, characterized in that, The plurality of oil storage tanks are distributed radially and / or circumferentially along the rotating groove.

4. The compressor as described in claim 3, characterized in that, In a group of oil storage tanks arranged radially along the rotating groove, the center-to-center distance between adjacent oil storage tanks is a, where a ≤ 0.5 mm; and / or, The depth of the oil storage tank is b, where b ≤ 0.5 mm; and / or, The diameter of the oil storage tank is c, where c ≤ 0.5 mm.

5. The compressor as described in claim 1, characterized in that, The compressor also includes a piston movably disposed within the piston cylinder and a connecting rod that drives the piston and the eccentric shaft; A groove is provided on the first side of the main body, and a protrusion is provided in the middle of the groove. The protrusion and the inner side of the groove define the annular groove. The connecting rod has a first gap A between one end of the eccentric shaft and the free end of the protrusion, where A ≥ 1 mm.

6. The compressor as claimed in claim 1, characterized in that, 2mm≤B≤3mm.

7. The compressor as claimed in claim 1, characterized in that, A movable gap is provided between the secondary shaft and the wall of the rotating groove, and the movable gap is C, where 10μm≤C≤15μm.

8. The compressor as claimed in claim 1, characterized in that, The crankcase has two protruding support parts, and the two support parts are respectively located on both sides of the crankshaft operating area. The first side of the main body is provided with two mounting parts near the edge, and the two mounting parts are respectively installed to the two support parts.

9. The compressor as claimed in claim 8, characterized in that, The compressor further includes a high-pressure chamber assembly, which is disposed on the outside of the support portion, and the distance between the high-pressure chamber assembly and the support portion is D, where D≥3mm.

10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.

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