Compressors and refrigeration equipment

Abstract

The present invention provides a compressor and a refrigeration device, the compressor comprising: a crankshaft; a connecting structure, arranged on the crankshaft; wherein a evasion portion is arranged on the connecting structure and / or on the crankshaft, the evasion portion is located at the portion where the connecting structure and the crankshaft match, and the evasion portion is configured to be suitable for evading at least one of the connecting structure and the crankshaft. The compressor provided by the present invention comprises a crankshaft and a connecting structure connected to the crankshaft, the arrangement of the evasion portion can increase the gap between the crankshaft and the connecting structure, and then when the crankshaft is tilted and deformed, the evasion portion can evade the tilted crankshaft, so that the contact-maintaining surface of the crankshaft and the connecting structure is in contact, so that the oil film between the crankshaft and the connecting structure is not destroyed, thereby effectively ensuring the reliability of the compressor, and then a thinner shaft diameter and a shorter sleeve can be used to reduce the friction loss of the matching portion of the crankshaft and the connecting structure, thereby improving the performance of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a compressor and a refrigeration equipment. Background Art

[0002] Currently, if Figure 1 and Figure 2 As shown, the compressor 100' includes a crankshaft 102', the crankshaft 102' includes a main shaft portion 1020', a secondary shaft portion 1022' and an eccentric portion 1024', the main bearing 104' is sleeved on the main shaft portion 1020', the secondary bearing 106' is sleeved on the secondary shaft portion 1022', the cylinder 108' includes a cylinder cavity, the piston 114' is disposed in the cylinder cavity and the piston 114' is sleeved on the eccentric portion 1024', the rotor 110' is connected to the main shaft portion 1020', and the balance block 112' is disposed on the rotor 110'. Figure 2 As shown, the parts where the main shaft portion 1020' and the main bearing 104', the secondary shaft portion 1022' and the secondary bearing 106', and the eccentric portion 1024' and the piston 114' cooperate are most likely to cause reliability problems such as abnormal wear. Figure 2 The portion A' in the middle shows the part where the main shaft 1020' and the main bearing 104' are prone to wear. In order to ensure the reliability of the kinematic pair of the matching parts, the prior art can only use a thicker shaft diameter and a higher bearing, which leads to an increase in the volume of the compressor 100', an increase in cost and an increase in friction loss. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

[0004] To this end, a first aspect of the present invention provides a compressor.

[0005] A second aspect of the present invention further provides a refrigeration device.

[0006] In view of this, the first aspect of the present invention proposes a compressor, comprising: a crankshaft; a connecting structure, arranged on the crankshaft; wherein an avoidance portion is arranged on the connecting structure and / or the crankshaft, the avoidance portion is located at the part where the connecting structure cooperates with the crankshaft, and the avoidance portion is configured to be suitable for avoiding at least one of the connecting structure and the crankshaft.

[0007] The compressor provided by the present invention includes a crankshaft and a connecting structure connected to the crankshaft, wherein an avoidance portion is provided on the connecting structure and / or the crankshaft, and the avoidance portion is used to avoid at least one of the connecting structure or the crankshaft. The provision of the avoidance portion can increase the gap between the crankshaft and the connecting structure, and then when the crankshaft is tilted and deformed, the avoidance portion can avoid the tilted crankshaft so that the contact surfaces of the crankshaft and the connecting structure are in contact, so that the oil film between the crankshaft and the connecting structure is not destroyed, thereby effectively ensuring the reliability of the compressor, and then a thinner shaft diameter and a shorter shaft sleeve can be used, thereby reducing the volume and cost of the compressor, reducing the friction loss of the matching parts of the crankshaft and the connecting structure, and thus improving the performance of the compressor.

[0008] It can be understood that the avoidance portion avoids at least one of the connecting structure and the crankshaft, that is, the avoidance portion avoids the tilting deformation of the crankshaft to ensure that after the crankshaft tilts, the contact between the crankshaft and the connecting structure at the corresponding part of the avoidance portion is surface contact.

[0009] The above-mentioned compressor provided by the present invention may also have the following additional technical features:

[0010] In the above technical solution, further, there is a gap between the crankshaft and the connecting structure, and along the axial direction of the crankshaft, the gap corresponding to the avoidance portion increases toward the direction away from the middle of the connecting structure.

[0011] In this technical solution, there is a gap between the crankshaft and the connecting structure, and lubricating oil can be distributed in the gap. Among them, along the axial direction of the crankshaft, the gap corresponding to the avoidance portion increases toward the direction away from the middle of the connecting structure. Therefore, when the crankshaft is tilted and deformed, the gradually increasing gap can form an avoidance space for the crankshaft, so that the contact between the crankshaft and the connecting structure becomes surface contact, thereby ensuring the normal operation of the oil film, thereby avoiding wear between the crankshaft and the connecting structure and improving the reliability of the compressor.

[0012] In any of the above technical solutions, further, in the cross section of the compressor in the axial direction of the crankshaft, at the same axial height, the sum of the gaps on both sides of the axis of the crankshaft is defined as a double-sided gap; the minimum value of the double-sided gap corresponding to the avoidance portion is δ0, the difference between the maximum value of the double-sided gap corresponding to the avoidance portion and δ0 is δ, the diameter of the crankshaft corresponding to the part with the smallest double-sided gap corresponding to the avoidance portion is D, and the length of the avoidance portion along the axial direction of the crankshaft is h; wherein the quotient of δ and δ0, and the product of the quotient of D and h, is greater than or equal to 0.2, and less than or equal to 5.

[0013] In this technical solution, the avoidance portion gradually increases from the middle to the end of the connecting structure, so the bilateral gap corresponding to the avoidance portion has a minimum value and a maximum value. The minimum value of the bilateral gap corresponding to the avoidance portion is δ0, and the difference between the maximum value of the bilateral gap corresponding to the avoidance portion and δ0 is δ. The diameter of the crankshaft corresponding to the smallest part of the bilateral gap corresponding to the avoidance portion is D. Along the axial direction of the crankshaft, the length of the avoidance portion is h. The corresponding size of the avoidance portion affects the effect of improving the friction between the crankshaft and the connecting structure. Therefore, the quotient of δ and δ0 and the product of the quotient of D and h are set to be greater than or equal to 0.2 and less than or equal to 5. At this time, the avoidance portion has the best effect on improving the friction between the crankshaft and the connecting structure.

[0014] In any of the above technical solutions, further, the avoidance portion includes multiple avoidance segments, and the multiple avoidance segments are connected in sequence along the axial direction of the crankshaft, wherein at least one avoidance segment satisfies the product of the quotient of δ and δ0 and the quotient of D and h, which is greater than or equal to 0.2 and less than or equal to 5.

[0015] In this technical solution, the avoidance portion includes multiple avoidance segments, and the multiple avoidance segments are connected in sequence along the axial direction. Among the multiple avoidance segments, the size of at least one avoidance segment satisfies the relationship that the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.

[0016] In any of the above technical solutions, further, the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.5 and less than or equal to 2.5.

[0017] In this technical solution, when the quotient of δ and δ0 and the product of the quotient of D and h are set to be greater than or equal to 0.5 and less than or equal to 2.5, the effect of improving the friction between the crankshaft and the connecting structure is better.

[0018] In any of the above technical solutions, further, h is greater than or equal to 2 mm and less than or equal to 20 mm.

[0019] In this technical solution, the axial height h of the avoidance portion is set to 2mm≤h≤20mm, which makes it easier to process the avoidance portion and also helps to reduce the wear between the crankshaft and the connecting structure.

[0020] In any of the above technical solutions, further, along the axial direction of the crankshaft, the size of the gap corresponding to at least part of the avoidance portion changes linearly.

[0021] In this technical solution, along the axial direction of the crankshaft, the size of the gap corresponding to at least part of the avoidance portion changes linearly, that is, in the cross-section of the compressor in the axial direction of the crankshaft, along the axial direction of the crankshaft, the radial size of the gap changes in a positive proportional relationship from the direction away from the middle of the connecting structure.

[0022] In any of the above technical solutions, further, the wall surface formed by the avoidance portion includes a conical surface.

[0023] In this technical solution, the wall surface formed by the avoidance portion includes a conical surface, so that the gap between the crankshaft and the connecting structure changes linearly along the axial direction, and the processing of the avoidance portion is also facilitated.

[0024] In any of the above technical solutions, further, on a cross section of the compressor in the axial direction of the crankshaft, along the direction away from the middle of the connecting structure, the acute angle between the tangent of the wall formed by at least part of the avoidance portion and the direction perpendicular to the axis of the crankshaft gradually decreases.

[0025] In this technical solution, in the axial direction of the crankshaft, along the direction away from the middle of the connecting structure, the tangent of at least part of the wall formed by the avoidance portion gradually tends to be horizontal, that is, the acute angle between the tangent of the wall formed by the avoidance portion and the direction perpendicular to the axial direction of the crankshaft gradually decreases, so that the shape of the avoidance portion and the flexural deformation of the crankshaft are more matched, thereby further enhancing the wear improvement effect.

[0026] In any of the above technical solutions, further, the wall surface formed by the avoidance portion includes a curved surface.

[0027] In this technical solution, the wall surface formed by the avoidance portion includes a curved surface, so that the change in the gap corresponding to the avoidance portion is more matched with the shape of the flexural deformation of the crankshaft, thereby further improving the wear improvement effect.

[0028] In any of the above technical solutions, further, in a cross section perpendicular to the axis of the crankshaft, the avoidance portion is annular.

[0029] In this technical solution, the avoidance portion is annular in shape, and the annular avoidance portion can produce a good avoidance effect on all directions of the crankshaft when the crankshaft is tilted and deformed, thereby improving the wear between the crankshaft and the connecting structure in all directions, that is, reducing the degree of wear in all directions.

[0030] In any of the above technical solutions, further, the crankshaft includes: a main body, the main body includes a first shaft portion and a second shaft portion that are coaxially arranged; an eccentric portion that is connected to the main body, and the main body and the eccentric portion are eccentrically arranged.

[0031] In this technical solution, the crankshaft includes a main body and an eccentric part. The main body includes a first shaft part and a second shaft part. The first shaft part is connected to the rotor of the motor to drive the eccentric part to rotate. The rotation of the eccentric part realizes the intake and exhaust process of the compressor.

[0032] In any of the above technical solutions, further, the connection structure includes: a first bearing, sleeved on the first shaft portion; a second bearing, sleeved on the second shaft portion; and a piston, sleeved on the eccentric portion.

[0033] In this technical solution, the connecting structure includes a first bearing, a second bearing and a piston. The first bearing is sleeved on the first shaft portion, and the second bearing is sleeved on the second shaft portion. The crankshaft is fixed by the first bearing and the second bearing. The piston is sleeved on the eccentric portion, and the rotation of the eccentric portion drives the piston to move, thereby realizing the suction and exhaust process of the compressor.

[0034] In any of the above technical solutions, further, based on the avoidance portion being arranged on the crankshaft, the avoidance portion is arranged at a portion of the first shaft portion close to the second shaft portion and / or the avoidance portion is arranged at a portion of the first shaft portion away from the second shaft portion, and / or the avoidance portion is arranged at an end of the eccentric portion close to the first bearing and / or the avoidance portion is arranged at an end of the eccentric portion close to the second bearing, and / or the avoidance portion is arranged at an end of the second shaft portion close to the eccentric portion.

[0035] In this technical solution, when the avoidance portion is provided on the crankshaft, the avoidance portion is provided on any one of a portion of the first shaft portion close to the second shaft portion, a portion of the first shaft portion far from the second shaft portion, an end of the eccentric portion close to the first bearing, an end of the eccentric portion close to the second bearing, and an end of the second shaft portion close to the eccentric portion, or a combination thereof.

[0036] In any of the above technical solutions, further, based on the avoidance portion being arranged on the connecting structure, the avoidance portion is arranged at an end of the first bearing close to the second bearing and / or the avoidance portion is arranged at an end of the first bearing away from the second bearing, and / or the avoidance portion is arranged at an end of the piston close to the first bearing and / or the avoidance portion is arranged at an end of the piston close to the second bearing, and / or the avoidance portion is arranged at an end of the second bearing close to the first bearing.

[0037] In this technical solution, when the avoidance portion is provided on the connecting structure, the avoidance portion is provided on any one of an end of the first bearing close to the second bearing, an end of the first bearing away from the second bearing, an end of the piston close to the first bearing, an end of the piston close to the second bearing, and an end of the second bearing close to the first bearing, or a combination thereof.

[0038] Of course, the avoidance portion can also be provided on the connecting structure and the crankshaft at the same time.

[0039] In any of the above technical solutions, further, the compressor also includes: a cylinder, the cylinder includes a cylinder cavity, a piston is arranged in the cylinder cavity, a crankshaft is passed through the cylinder cavity, and a vane groove is arranged on the cylinder; the vane is arranged in the vane groove and is rollingly connected to the piston; and a rotor is connected to the first shaft portion.

[0040] In this technical solution, the compressor further includes a cylinder, a vane and a rotor, the rotor is connected to the first shaft portion, the cylinder has a cylinder cavity, the piston is arranged in the cylinder cavity, and the crankshaft is arranged in the cylinder cavity. Among them, the cylinder is also provided with a vane groove, the vane is arranged in the vane groove, and is rotatably connected to the piston, so as to realize the suction and exhaust process of the compressor.

[0041] In any of the above technical solutions, further, the compressor is a variable frequency compressor.

[0042] In this technical solution, the compressor is a variable frequency compressor. The reliability of the variable frequency compressor can be improved by arranging an avoidance portion on the connecting structure or the crankshaft. Of course, the compressor can also be a fixed speed compressor.

[0043] In any of the above technical solutions, further, the compressor is filled with a refrigerant, and the refrigerant is difluoromethane or propane.

[0044] In this technical solution, the compressor is filled with refrigerant, and the cooling or heating of the refrigeration equipment is achieved through the heat absorption and heat release process of the refrigerant. Specifically, the refrigerant is difluoromethane or propane. Of course, the refrigerant can also be other refrigerants.

[0045] According to a second aspect of the present invention, a refrigeration device is also proposed, comprising: a compressor as proposed in any of the above technical solutions.

[0046] The refrigeration equipment provided in the second aspect of the present invention comprises the compressor proposed in any of the above technical solutions and therefore has all the beneficial effects of the compressor.

[0047] Specifically, the refrigeration equipment includes a heat exchanger, the heat exchanger is connected to the compressor through a pipeline, and the refrigerant can flow in the pipeline.

[0048] Additional aspects and advantages of the present invention will become apparent from the following description or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0050] Figure 1 A schematic diagram of the structure of a compressor in the related art is shown;

[0051] Figure 2 Another structural schematic diagram of a compressor in the related art is shown.

[0052] in, Figure 1 and Figure 2 The corresponding relationship between the reference numerals and the component names is as follows:

[0053] 100' compressor, 102' crankshaft, 1020' main shaft portion, 1022' secondary shaft portion, 1024' eccentric portion, 104' main bearing, 106' secondary bearing, 108' cylinder, 110' rotor, 112' balance block, 114' piston.

[0054] Figure 3 A schematic diagram showing a structure in which the avoidance portion of an embodiment of the present invention is a conical surface;

[0055] Figure 4 A graph showing a curve relationship between a relief portion and a minimum oil film thickness according to an embodiment of the present invention is shown;

[0056] Figure 5 Another structural schematic diagram showing an embodiment of the present invention in which the avoidance portion is a conical surface;

[0057] Figure 6 A schematic diagram showing a structure in which the avoidance portion of an embodiment of the present invention is a curved surface;

[0058] Figure 7 Another structural schematic diagram showing an embodiment of the present invention in which the avoidance portion is a curved surface;

[0059] Figure 8 A schematic diagram showing the structure of a compressor according to a specific embodiment of the present invention is shown;

[0060] Fig. 9 A schematic structural diagram of a compressor according to another specific embodiment of the present invention is shown.

[0061] in, Figures 3 to 9 The corresponding relationship between the reference numerals and the component names is as follows:

[0062] 100 compressor, 102 crankshaft, 1020 first shaft portion, 1022 second shaft portion, 1024 eccentric portion, 104 connecting structure, 1040 first bearing, 1042 second bearing, 1044 piston, 106 avoidance portion, 108 gap, 110 cylinder, 112 vane, 114 rotor, 116 balance block. DETAILED DESCRIPTION

[0063] In order to more clearly understand the above-mentioned purpose, features and advantages of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0064] In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited to the specific embodiments disclosed below.

[0065] Refer to the following Figures 3 to 9 The compressor 100 and the refrigeration device according to some embodiments of the present invention are described.

[0066] Embodiment 1:

[0067] like Figure 3 As shown, according to one embodiment of the present invention, the present invention proposes a compressor 100 including: a crankshaft 102 and a connecting structure 104 .

[0068] Specifically, the connecting structure 104 is arranged on the crankshaft 102; wherein, an avoidance portion 106 is arranged on the connecting structure 104 and / or the crankshaft 102, and the avoidance portion 106 is located at the part where the connecting structure 104 cooperates with the crankshaft 102, and the avoidance portion 106 is configured to be suitable for avoiding at least one of the connecting structure 104 and the crankshaft 102.

[0069] The compressor 100 provided by the present invention includes a crankshaft 102 and a connecting structure 104 connected to the crankshaft 102, wherein an avoidance portion 106 is provided on the connecting structure 104 and / or the crankshaft 102, and the avoidance portion 106 is used to avoid at least one of the connecting structure 104 or the crankshaft 102. The setting of the avoidance portion 106 can increase the gap 108 between the crankshaft 102 and the connecting structure 104, and then when the crankshaft 102 is tilted and deformed, the avoidance portion 106 can avoid the tilted crankshaft 102, so that the contact holding surface of the crankshaft 102 and the connecting structure 104 is in contact, so that the oil film between the crankshaft 102 and the connecting structure 104 is not destroyed, thereby effectively ensuring the reliability of the compressor 100, and then a thinner shaft diameter and a shorter shaft sleeve can be used, thereby reducing the volume and cost of the compressor 100, reducing the friction loss of the matching part of the crankshaft 102 and the connecting structure 104, and improving the performance of the compressor 100.

[0070] It can be understood that the avoidance portion 106 avoids at least one of the connecting structure 104 and the crankshaft 102, that is, the avoidance portion 106 avoids the tilting deformation of the crankshaft 102 to ensure that after the crankshaft 102 tilts, the contact between the crankshaft 102 and the connecting structure 104 corresponding to the avoidance portion 106 is surface contact.

[0071] Specifically, when the avoidance portion 106 is not provided, if the crankshaft 102 is tilted and deformed, the contact between the crankshaft 102 and the connecting structure 104 is line contact, the oil film is partially ruptured, and the crankshaft 102 and the connecting structure 104 are in direct metal contact, which can easily lead to wear. After the avoidance portion 106 is provided, if the crankshaft 102 is tilted and deformed, the contact between the crankshaft 102 and the connecting structure 104 is still surface contact, which ensures the normal operation of the oil film, thereby reducing the degree of wear between the crankshaft 102 and the connecting structure 104 and improving the reliability of the compressor 100.

[0072] Specifically, based on the avoidance portion 106 being arranged on the connecting structure 104, the shape of the avoidance portion 106 is adapted to the shape of the outer side wall of the corresponding tilted crankshaft 102; based on the avoidance portion 106 being arranged on the crankshaft 102, after the crankshaft 102 is tilted, the shape of the avoidance portion 106 is adapted to the shape of the inner side wall of the connecting structure 104.

[0073] Specifically, the avoidance portion 106 is disposed at an end of the connection structure 104 and / or at a portion of the crankshaft 102 corresponding to the end of the connection structure 104 .

[0074] Specifically, the avoidance portion 106 is disposed in a circumferential direction of an end portion of the connection structure 104 and / or in a circumferential direction of a portion of the end portion of the crankshaft 102 corresponding to the connection mechanism.

[0075] Specifically, when the avoidance portion 106 is disposed on the connection structure 104 , at least a portion of the avoidance portion 106 is located on the inner side wall of the connection structure 104 .

[0076] Embodiment 2:

[0077] like Figure 3 As shown, according to an embodiment of the present invention, it includes the features defined in the above embodiments, and further: there is a gap 108 between the crankshaft 102 and the connecting structure 104, and along the axial direction of the crankshaft 102, the gap 108 corresponding to the avoidance portion 106 increases toward the middle direction away from the connecting structure 104.

[0078] In this embodiment, there is a gap 108 between the crankshaft 102 and the connecting structure 104, and lubricating oil can be distributed in the gap 108, wherein, along the axial direction of the crankshaft 102, the gap 108 corresponding to the avoidance portion 106 increases toward the middle direction away from the connecting structure 104, so that when the crankshaft 102 is tilted and deformed, the gradually increasing gap 108 can form an avoidance space for the crankshaft 102, so that the contact between the crankshaft 102 and the connecting structure 104 becomes surface contact, thereby ensuring the normal operation of the oil film, thereby avoiding wear between the crankshaft 102 and the connecting structure 104, and improving the reliability of the compressor 100.

[0079] Specifically, the connection structure 104 can be divided into two ends and a middle portion disposed between the two ends. The gap 108 corresponding to the avoidance portion 106 gradually increases in a direction away from the middle portion of the connection structure 104 to adapt to the shape of the crankshaft 102 when it is tilted and deformed.

[0080] Specifically, when the avoidance portion 106 is provided on the connecting structure 104, the avoidance portion 106 is provided at the end portion of the connecting structure 104, and in the axial direction of the crankshaft 102, along the direction away from the middle portion of the connecting structure 104, the avoidance portion 106 is inclined toward the radial outer side of the connecting structure 104; when the avoidance portion 106 is provided on the crankshaft 102, the avoidance portion 106 is located at the portion of the end portion of the crankshaft 102 corresponding to the connecting structure 104, and in the axial direction of the crankshaft 102, along the direction away from the middle portion of the connecting structure 104, the avoidance portion 106 is inclined toward the axial direction of the crankshaft 102.

[0081] Embodiment three:

[0082] According to an embodiment of the present invention, it includes the features defined in the above-mentioned embodiments, and further: in the cross section of the compressor 100 in the axial direction of the crankshaft 102, at the same axial height, the sum of the gaps 108 on both sides of the axis of the crankshaft 102 is defined as the double-sided gap 108; the minimum value of the double-sided gap 108 corresponding to the avoidance portion 106 is δ0, the difference between the maximum value of the double-sided gap 108 corresponding to the avoidance portion 106 and δ0 is δ, the diameter of the crankshaft 102 corresponding to the smallest part of the double-sided gap 108 corresponding to the avoidance portion 106 is D, and the length of the avoidance portion 106 along the axial direction of the crankshaft 102 is h; wherein, the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.

[0083] In this embodiment, the avoidance portion 106 gradually increases from the middle to the end of the connecting structure 104, so the bilateral gap 108 corresponding to the avoidance portion 106 has a minimum value and a maximum value. The minimum value of the bilateral gap 108 corresponding to the avoidance portion 106 is δ0, and the difference between the maximum value of the bilateral gap 108 corresponding to the avoidance portion 106 and δ0 is δ. The diameter of the crankshaft 102 corresponding to the smallest part of the bilateral gap 108 corresponding to the avoidance portion 106 is D. Along the axial direction of the crankshaft 102, the length of the avoidance portion 106 is h. The size corresponding to the avoidance portion 106 affects the effect of improving the friction between the crankshaft 102 and the connecting structure 104. Therefore, the quotient of δ and δ0 and the product of the quotient of D and h are set to be greater than or equal to 0.2 and less than or equal to 5. At this time, the avoidance portion 106 has the best effect of improving the friction between the crankshaft 102 and the connecting structure 104.

[0084] Specifically, δ0 / 2 is half of the bilateral gap 108 corresponding to the avoidance portion 106 , and δ / 2 is half of the difference between the maximum value of the bilateral gap 108 corresponding to the avoidance portion 106 and δ0.

[0085] Specifically, at the same axial height, the difference between the diameter of the inner side wall of the connection structure 104 and the diameter of the crankshaft 102 is a double-sided gap 108 .

[0086] Furthermore, the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.5 and less than or equal to 2.5.

[0087] In this embodiment, when the product of the quotient of δ and δ0 and the quotient of D and h is set to be greater than or equal to 0.5 and less than or equal to 2.5, the effect of improving the friction between the crankshaft 102 and the connecting structure 104 is better.

[0088] Specifically, Figure 4 As shown, Figure 4 This is a curve chart showing the influence of the size corresponding to the avoidance portion 106 on the minimum oil film thickness, wherein the horizontal axis uses logarithmic coordinates. The oil film bearing capacity between the crankshaft 102 and the connecting structure 104 can be characterized by the minimum oil film thickness. The larger the minimum oil film thickness, the stronger the oil film bearing capacity, and the less likely wear will occur between the crankshaft 102 and the connecting structure 104.

[0089] Furthermore, h is greater than or equal to 2 mm and less than or equal to 20 mm.

[0090] In this embodiment, the axial height h of the avoidance portion 106 is set to 2 mm≤h≤20 mm, which is more convenient for machining the avoidance portion 106 and also helps to reduce the wear between the crankshaft 102 and the connecting structure 104 .

[0091] Embodiment 4:

[0092] like Figure 5 and Figure 7 As shown, according to an embodiment of the present invention, it includes the features defined in the above embodiments, and further: the avoidance portion 106 includes a plurality of avoidance segments, and the plurality of avoidance segments are sequentially connected along the axial direction of the crankshaft 102, wherein at least one avoidance segment satisfies the product of the quotient of δ and δ0 and the quotient of D and h, which is greater than or equal to 0.2 and less than or equal to 5.

[0093] In this embodiment, the avoidance portion 106 includes a plurality of avoidance segments, and the plurality of avoidance segments are connected in sequence along the axial direction. A size of at least one of the plurality of avoidance segments satisfies the relationship that the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.

[0094] It can be understood that the avoidance section satisfies the relationship that the quotient of δ and δ0, and the product of the quotient of D and h, is greater than or equal to 0.2, and less than or equal to 5, that is, the minimum value of the bilateral gap 108 corresponding to the avoidance section is δ0, the difference between the maximum value of the bilateral gap 108 corresponding to the avoidance section and δ0 is δ, the diameter of the crankshaft 102 corresponding to the smallest part of the bilateral gap 108 corresponding to the avoidance section is D, and the length of the avoidance section along the axial direction of the crankshaft 102 is h, and δ, δ0, D and h corresponding to the avoidance section satisfy the above-defined relationship.

[0095] Specifically, along the axial direction of the crankshaft 102 , the avoidance portion 106 is disposed at the end of the connection structure 104 , and the inclination angles of the plurality of avoidance sections may be the same or different. Furthermore, the plurality of avoidance sections are smoothly connected.

[0096] Embodiment five:

[0097] like Figure 3 and Figure 5 As shown, according to an embodiment of the present invention, it includes the features defined in any of the above embodiments, and further: along the axial direction of the crankshaft 102, the size of the gap 108 corresponding to at least part of the avoidance portion 106 changes linearly.

[0098] In this embodiment, along the axial direction of the crankshaft 102, the size of the gap 108 corresponding to at least part of the avoidance portion 106 changes linearly, that is, in a cross-section of the compressor 100 in the axial direction of the crankshaft 102, along the axial direction of the crankshaft 102, the radial size of the gap 108 changes in a positive proportional relationship from the direction away from the middle of the connecting structure 104.

[0099] Furthermore, the wall surface formed by the avoidance portion 106 includes a tapered surface.

[0100] In this embodiment, the wall surface formed by the avoidance portion 106 includes a conical surface, so that the gap 108 between the crankshaft 102 and the connecting structure 104 changes linearly along the axial direction, and the processing of the avoidance portion 106 is also facilitated.

[0101] Embodiment six:

[0102] like Figure 6 and Figure 7 As shown, according to an embodiment of the present invention, it includes the features defined in any of the above embodiments, and further: on the cross-section of the compressor 100 in the axial direction of the crankshaft 102, along the direction away from the middle of the connecting structure 104, the acute angle between the tangent of the wall formed by at least part of the avoidance portion 106 and the direction perpendicular to the axis of the crankshaft 102 gradually decreases.

[0103] In this embodiment, in the axial direction of the crankshaft 102, along the direction away from the middle of the connecting structure 104, the tangent of at least part of the wall formed by the avoidance portion 106 gradually tends to be horizontal, that is, the acute angle between the tangent of the wall formed by the avoidance portion 106 and the axial direction perpendicular to the crankshaft 102 gradually decreases, so that the shape of the avoidance portion 106 and the flexural deformation of the crankshaft 102 are more matched, thereby further enhancing the wear improvement effect.

[0104] Specifically, the speed at which the gap 108 corresponding to the avoidance portion 106 increases gradually increases in the axial direction away from the middle of the connection structure 104 .

[0105] Furthermore, the wall surface formed by the avoidance portion 106 includes a curved surface.

[0106] In this embodiment, the wall surface formed by the avoidance portion 106 includes a curved surface, so that the change of the gap 108 corresponding to the avoidance portion 106 is more matched with the shape of the flexural deformation of the crankshaft 102, thereby further improving the wear improvement effect.

[0107] like Figure 3 As shown, the avoidance portion 106 is arranged on the crankshaft 102, and the avoidance portion 106 is realized by changing the diameter of the crankshaft 102, that is, the diameter of the crankshaft 102 becomes smaller after the avoidance portion 106 is arranged, and the crankshaft 102 forms a cone at the avoidance portion 106, so that the gap 108 between the crankshaft 102 and the connecting structure 104 in the part where the avoidance portion 106 is arranged changes linearly along the axial direction.

[0108] like Figure 5 As shown, the avoidance portion 106 is arranged on the connecting structure 104, and the avoidance portion 106 is realized by changing the diameter of the connecting structure 104, that is, the diameter of the inner wall of the connecting structure 104 after the avoidance portion 106 is arranged becomes larger, and the inner wall of the connecting structure 104 forms a cone at the avoidance portion 106, so that the gap 108 between the crankshaft 102 and the connecting structure 104 in the part where the avoidance portion 106 is arranged changes linearly along the axial direction.

[0109] like Figure 6 and Figure 7 As shown, when the flexural deformation of the crankshaft 102 is large, in order to further improve the wear improvement effect, the avoidance portion 106 can be set as a curved surface, and the speed of increasing the gap 108 corresponding to the avoidance portion 106 is gradually increased in the axial direction away from the center of the moving sub-center (away from the middle of the connecting structure 104), that is, the tangent of the avoidance portion 106 and the axis of the crankshaft 102 are gradually parallel to each other, so that the change of the gap 108 corresponding to the avoidance portion 106 can be more matched with the flexural deformation shape of the crankshaft 102, thereby further improving the wear improvement effect.

[0110] Specifically, the avoidance portion 106 may also be provided on both the crankshaft 102 and the connection structure 104. The wall surface formed by the avoidance portion 106 includes a conical surface and a curved surface.

[0111] Embodiment seven:

[0112] According to an embodiment of the present invention, the present invention includes the features defined in any one of the above embodiments, and further: in a cross section perpendicular to the axis of the crankshaft 102 , the avoidance portion 106 is annular.

[0113] In this embodiment, the avoidance portion 106 is annular, and the annular avoidance portion 106 can produce a good avoidance effect on all directions of the crankshaft 102 when the crankshaft 102 is tilted and deformed, thereby improving the wear between the crankshaft 102 and the connecting structure 104 in all directions, that is, reducing the degree of wear in all directions.

[0114] Embodiment eight:

[0115] like Figure 8 and Fig. 9 As shown, according to an embodiment of the present invention, it includes the features defined in any of the above embodiments, and further: the crankshaft 102 includes: a main body, the main body includes a first shaft portion 1020 and a second shaft portion 1022 arranged coaxially; an eccentric portion 1024, which is connected to the main body, and the main body and the eccentric portion 1024 are eccentrically arranged.

[0116] In this embodiment, the crankshaft 102 includes a main body and an eccentric portion 1024 , the main body includes a first shaft portion 1020 and a second shaft portion 1022 , the first shaft portion 1020 is connected to the rotor 114 of the motor to drive the eccentric portion 1024 to rotate, and the rotation of the eccentric portion 1024 realizes the intake and exhaust process of the compressor 100 .

[0117] Furthermore, the connection structure 104 includes: a first bearing 1040 sleeved on the first shaft portion 1020 ; a second bearing 1042 sleeved on the second shaft portion 1022 ; and a piston 1044 sleeved on the eccentric portion 1024 .

[0118] In this embodiment, the connecting structure 104 includes a first bearing 1040, a second bearing 1042 and a piston 1044. The first bearing 1040 is sleeved on the first shaft portion 1020, and the second bearing 1042 is sleeved on the second shaft portion 1022. The crankshaft 102 is fixed by the first bearing 1040 and the second bearing 1042. The piston 1044 is sleeved on the eccentric portion 1024, and the rotation of the eccentric portion 1024 drives the piston 1044 to move, thereby realizing the intake and exhaust process of the compressor 100.

[0119] Further, based on the avoidance portion 106 being arranged on the crankshaft 102, the avoidance portion 106 is arranged at a portion of the first shaft portion 1020 close to the second shaft portion 1022 and / or the avoidance portion 106 is arranged at a portion of the first shaft portion 1020 away from the second shaft portion 1022, and / or the avoidance portion 106 is arranged at an end of the eccentric portion 1024 close to the first bearing 1040 and / or the avoidance portion 106 is arranged at an end of the eccentric portion 1024 close to the second bearing 1042, and / or the avoidance portion 106 is arranged at an end of the second shaft portion 1022 close to the eccentric portion 1024.

[0120] In this embodiment, when the avoidance portion 106 is provided on the crankshaft 102, the avoidance portion 106 is provided on any one of a portion of the first shaft portion 1020 close to the second shaft portion 1022, a portion of the first shaft portion 1020 away from the second shaft portion 1022, an end of the eccentric portion 1024 close to the first bearing 1040, an end of the eccentric portion 1024 close to the second bearing 1042, and an end of the second shaft portion 1022 close to the eccentric portion 1024, or a combination thereof.

[0121] Further, based on the avoidance portion 106 being arranged on the connecting structure 104, the avoidance portion 106 is arranged at an end of the first bearing 1040 close to the second bearing 1042 and / or the avoidance portion 106 is arranged at an end of the first bearing 1040 away from the second bearing 1042, and / or the avoidance portion 106 is arranged at an end of the piston 1044 close to the first bearing 1040 and / or the avoidance portion 106 is arranged at an end of the piston 1044 close to the second bearing 1042, and / or the avoidance portion 106 is arranged at an end of the second bearing 1042 close to the first bearing 1040.

[0122] In this embodiment, when the avoidance portion 106 is provided on the connecting structure 104, the avoidance portion 106 is provided on any one of an end of the first bearing 1040 close to the second bearing 1042, an end of the first bearing 1040 away from the second bearing 1042, an end of the piston 1044 close to the first bearing 1040, an end of the piston 1044 close to the second bearing 1042, and an end of the second bearing 1042 close to the first bearing 1040, or a combination thereof.

[0123] Of course, the avoidance portion 106 can also be provided on both the connection structure 104 and the crankshaft 102 .

[0124] Furthermore, the compressor 100 also includes: a cylinder 110, the cylinder 110 includes a cylinder cavity, the piston 1044 is arranged in the cylinder cavity, the crankshaft 102 is passed through the cylinder cavity, and a sliding vane 112 groove is provided on the cylinder 110; the sliding vane 112 is arranged in the sliding vane 112 groove and is rollingly connected to the piston 1044; the rotor 114 is connected to the first shaft portion 1020.

[0125] In this embodiment, the compressor 100 further includes a cylinder 110, a vane 112 and a rotor 114, the rotor 114 is connected to the first shaft portion 1020, the cylinder 110 has a cylinder cavity, the piston 1044 is disposed in the cylinder cavity, and the crankshaft 102 is disposed in the cylinder cavity. Among them, the cylinder 110 is also provided with a vane 112 groove, the vane 112 is disposed in the vane 112 groove, and is rotatably connected to the piston 1044, thereby realizing the suction and exhaust process of the compressor 100.

[0126] Furthermore, the compressor 100 is a variable frequency compressor.

[0127] In this embodiment, the compressor 100 is a variable frequency compressor. The reliability of the variable frequency compressor can be improved by providing an avoidance portion 106 on the connection structure 104 or the crankshaft 102. Of course, the compressor 100 can also be a fixed speed compressor.

[0128] Furthermore, the compressor 100 is filled with a refrigerant, and the refrigerant is difluoromethane or propane.

[0129] In this embodiment, the compressor 100 is filled with refrigerant, and the refrigeration or heating of the refrigeration equipment is achieved through the heat absorption and heat release process of the refrigerant. Specifically, the refrigerant is difluoromethane or propane. Of course, the refrigerant can also be other refrigerants.

[0130] Embodiment nine:

[0131] According to a specific embodiment of the present invention, Figure 8 and Fig. 9 As shown, the compressor 100 includes a crankshaft 102, a first bearing 1040, a second bearing 1042, a cylinder 110, a piston 1044, a vane 112, a balancing block 116 arranged on a rotor 114 and other components. The above components form an intake chamber and a compression chamber. The rotor 114 of the motor drives the crankshaft 102 to rotate, so that the volume of the intake chamber increases and the volume of the compression chamber decreases, thereby realizing the intake and exhaust process. The crankshaft 102 includes a first shaft portion 1020, a second shaft portion 1022 and an eccentric portion 1024. The first shaft portion 1020 and the first bearing 1040, the second shaft portion 1022 and the second bearing 1042, and the eccentric portion 1024 and the piston 1044 respectively form three sliding bearings. There is a gap 108 between the shaft portion (the first shaft portion 1020, the second shaft portion 1022 or the eccentric shaft) of the sliding bearing and the connecting structure 104 (the first bearing 1040, the second bearing 1042 or the piston 1044), which is filled with lubricating oil during normal operation. The above three sliding bearings often suffer abnormal wear. Specifically, due to the centrifugal force generated during the rotation of the rotor 114 and the magnetic pull of the motor itself, the center of the rotor 114 will deviate from the axis of the motor and thus yaw. Accordingly, the upper end of the crankshaft 102 will bend and deform, causing the first shaft portion 1020 of the crankshaft 102 to form a line contact with the upper end of the first bearing 1040, and the local oil film will rupture. The first shaft portion 1020 of the crankshaft 102 and the first bearing 1040 will directly come into metal contact and cause wear. Similarly, the eccentric shaft of the crankshaft 102 will also bend and deform under the action of the gas force of the suction chamber and the compression chamber, so that the first shaft portion 1020 and the lower edge of the first bearing 1040, the second shaft portion 1022 and the upper edge of the second bearing 1042, and the eccentric shaft and the upper and lower edges of the piston 1044 may all come into direct metal contact and cause abnormal wear. Therefore, due to the tilted deformation of the crankshaft 102, it is difficult for the edges of each sliding bearing to establish a normal oil film, thereby forming local metal contact and causing wear. Figure 3As shown, in the embodiment proposed in the present application, an avoidance portion 106 is provided at the connecting structure 104 or the portion where the crankshaft 102 cooperates with the connecting structure 104, and a gap 108 is provided between the connecting structure 104 and the crankshaft 102. The gap 108 between the connecting structure 104 and the crankshaft 102 corresponding to the avoidance portion 106 increases in the axial direction away from the center of the moving sub-center, so that after the crankshaft 102 is flexurally deformed, the original metal contact portion can still maintain surface contact, establish a normal oil film, thereby avoiding wear and greatly improving the reliability of the compressor 100.

[0132] Specifically, a portion of the crankshaft 102 or the connecting structure 104 may be removed by turning or the like to form the avoidance portion 106, or the crankshaft 102 and the avoidance portion 106 disposed on the crankshaft 102 may be manufactured integrally, or the connecting structure 104 and the avoidance portion 106 disposed on the connecting structure 104 may be manufactured integrally.

[0133] Specifically, the minimum value of the bilateral gap 108 corresponding to the avoidance portion 106 is δ0, the difference between the maximum value of the bilateral gap 108 corresponding to the avoidance portion 106 and δ0 is δ, the diameter of the crankshaft 102 corresponding to the minimum portion of the bilateral gap 108 corresponding to the avoidance portion 106 is D, the length of the avoidance portion 106 along the axis of the crankshaft 102 is h, and the quotient of δ and δ0, and the product of the quotient of D and h, are greater than or equal to 0.2 and less than or equal to 5. Figure 4 As shown, it is a curve diagram showing the effect of the size of the sliding bearing avoidance portion 106 on the minimum oil film thickness, wherein the horizontal axis uses a logarithmic coordinate. The oil film load-bearing capacity of the sliding bearing can be characterized by the minimum oil film thickness. The larger the minimum oil film thickness, the stronger the oil film load-bearing capacity, and the less likely the sliding bearing is to wear. Figure 4 It can be seen that when the size of the avoidance portion 106 satisfies: when the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5, the wear improvement effect is best.

[0134] Furthermore, the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.5 and less than or equal to 2.5, and h is greater than or equal to 2 mm and less than or equal to 20 mm.

[0135] Embodiment ten:

[0136] like Figure 8As shown, according to a specific embodiment of the present invention, the compressor 100 proposed in the present application includes a crankshaft 102 and a connecting structure 104, the crankshaft 102 includes a first shaft portion 1020, a second shaft portion 1022 and an eccentric portion 1024, the connecting structure 104 includes a first bearing 1040, a second bearing 1042 and a piston 1044, the first bearing 1040 is sleeved on the first shaft portion 1020, the second bearing 1042 is sleeved on the second shaft portion 1022, and the piston 1044 is sleeved on the eccentric portion 1024. In this embodiment, the avoidance portion 106 is provided on the crankshaft 102. Specifically, the portion of the first shaft portion 1020 corresponding to the upper and lower ends of the first bearing 1040, the portion of the second shaft portion 1022 corresponding to the upper end of the second bearing 1042, and the portion of the eccentric shaft corresponding to the upper and lower ends of the piston 1044 are all provided with the avoidance portion 106. The avoidance portion 106 is in the shape of a cone. The specific dimensions of any avoidance portion 106 respectively satisfy: the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5. Among them, Figure 8 Here, h1, h2, h3, h4, and h5 are the axial heights of the avoidance portion 106, respectively.

[0137] Embodiment eleven:

[0138] like Fig. 9 As shown, according to a specific embodiment of the present invention, the compressor 100 proposed in the present application includes a crankshaft 102 and a connecting structure 104, the crankshaft 102 includes a first shaft portion 1020, a second shaft portion 1022 and an eccentric portion 1024, the connecting structure 104 includes a first bearing 1040, a second bearing 1042 and a piston 1044, the first bearing 1040 is sleeved on the first shaft portion 1020, the second bearing 1042 is sleeved on the second shaft portion 1022, and the piston 1044 is sleeved on the eccentric portion 1024. In this embodiment, the avoidance portion 106 is arranged on the connection structure 104. Specifically, the avoidance portion 106 is arranged at the upper end and the lower end of the first bearing 1040, the upper end of the second bearing 1042, and the upper end and the lower end of the piston 1044. The avoidance portion 106 is in the shape of a curved surface. The specific dimensions of any avoidance portion 106 respectively satisfy: the product of the quotient of δ and δ0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5. Among them, Fig. 9 Here, h1, h2, h3, h4, and h5 are the axial heights of the avoidance portion 106, respectively.

[0139] Embodiment 12:

[0140] According to a second aspect of the present invention, a refrigeration device is further provided, comprising: a compressor 100 as provided in any of the above embodiments.

[0141] The refrigeration device provided in the second aspect of the present invention comprises the compressor 100 provided in any one of the above embodiments, and therefore has all the beneficial effects of the compressor 100.

[0142] Specifically, the refrigeration device includes a heat exchanger, and the heat exchanger is connected to the compressor 100 through a pipeline, and the refrigerant can flow in the pipeline.

[0143] In the present invention, the term "plurality" refers to two or more than two, unless otherwise clearly defined. The terms "installed", "connected", "connected", "fixed", etc. should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0144] In the description of this specification, the description of the terms "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0145] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A compressor, characterized in that: include: Crankshaft; A connecting structure, arranged on the crankshaft; Wherein, a relief portion is provided on the connecting structure and / or the crankshaft, the relief portion is located at a portion where the connecting structure matches the crankshaft, and the relief portion is configured to be suitable for avoiding at least one of the connecting structure and the crankshaft; There is a gap between the crankshaft and the connecting structure, and along the axial direction of the crankshaft, the gap corresponding to the avoidance portion increases in a direction away from the middle of the connecting structure; In the cross section of the compressor in the axial direction of the crankshaft, at the same axial height, the sum of the gaps on both sides of the axis of the crankshaft is defined as a double-sided gap; The minimum value of the bilateral gap corresponding to the avoidance portion is δ0, the difference between the maximum value of the bilateral gap corresponding to the avoidance portion and δ0 is δ, the diameter of the crankshaft corresponding to the portion with the smallest bilateral gap corresponding to the avoidance portion is D, and the length of the avoidance portion along the axial direction of the crankshaft is h; wherein the product of the quotient of the δ and the δ0 and the quotient of the D and the h is greater than or equal to 0.2 and less than or equal to 5; When the avoidance portion is arranged on the connecting structure, the shape of the avoidance portion is adapted to the shape of the outer side wall of the corresponding tilted crankshaft; when the avoidance portion is arranged on the crankshaft, after the crankshaft is tilted, the shape of the avoidance portion is adapted to the shape of the inner side wall of the connecting structure.

2. The compressor according to claim 1, characterized in that The avoidance portion includes a plurality of avoidance segments, which are sequentially connected along the axial direction of the crankshaft, wherein at least one of the avoidance segments satisfies that the product of the quotient of the δ and the δ0 and the quotient of the D and the h is greater than or equal to 0.2 and less than or equal to 5.

3. The compressor according to claim 1, characterized in that The product of the quotient of the δ and the δ0 and the quotient of the D and the h is greater than or equal to 0.5 and less than or equal to 2.

5.

4. The compressor according to claim 1, characterized in that The h is greater than or equal to 2 mm and less than or equal to 20 mm.

5. The compressor according to any one of claims 1 to 4, characterized in that Along the axial direction of the crankshaft, the size of the gap corresponding to at least part of the avoidance portion changes linearly.

6. The compressor according to claim 5, characterized in that The wall surface formed by the avoidance portion includes a tapered surface.

7. The compressor according to any one of claims 1 to 4, characterized in that In the cross section of the compressor in the axial direction of the crankshaft, along the direction away from the middle of the connecting structure, the acute angle between the tangent of the wall formed by at least part of the avoidance portion and the direction perpendicular to the axis of the crankshaft gradually decreases.

8. The compressor according to claim 7, characterized in that The wall surface formed by the avoidance portion includes a curved surface.

9. The compressor according to any one of claims 1 to 4, characterized in that The escape portion is annular in shape in a cross section perpendicular to the axis of the crankshaft.

10. The compressor according to any one of claims 1 to 4, characterized in that The crankshaft comprises: A main body, the main body comprising a first shaft portion and a second shaft portion arranged coaxially; The eccentric part is connected to the main body, and the main body and the eccentric part are eccentrically arranged.

11. The compressor according to claim 10, characterized in that The connection structure comprises: A first bearing, sleeved on the first shaft portion; A second bearing, sleeved on the second shaft portion; The piston is sleeved on the eccentric part.

12. The compressor according to claim 11, characterized in that Based on the avoidance portion being arranged on the crankshaft, the avoidance portion is arranged at a portion of the first shaft portion close to the second shaft portion and / or the avoidance portion is arranged at a portion of the first shaft portion away from the second shaft portion, and / or the avoidance portion is arranged at an end of the eccentric portion close to the first bearing and / or the avoidance portion is arranged at an end of the eccentric portion close to the second bearing, and / or the avoidance portion is arranged at an end of the second shaft portion close to the eccentric portion; and / or Based on the fact that the avoidance portion is arranged on the connecting structure, the avoidance portion is arranged at an end of the first bearing close to the second bearing and / or the avoidance portion is arranged at an end of the first bearing away from the second bearing, and / or the avoidance portion is arranged at an end of the piston close to the first bearing and / or the avoidance portion is arranged at an end of the piston close to the second bearing, and / or the avoidance portion is arranged at an end of the second bearing close to the first bearing.

13. The compressor according to claim 11, characterized in that The compressor also includes: A cylinder, wherein the cylinder comprises a cylinder cavity, the piston is arranged in the cylinder cavity, the crankshaft is passed through the cylinder cavity, and a sliding vane groove is arranged on the cylinder; A sliding vane, disposed in the sliding vane groove and in rolling connection with the piston; The rotor is connected to the first shaft portion.

14. The compressor according to any one of claims 1 to 4, characterized in that The compressor is a variable frequency compressor; and / or The compressor is filled with a refrigerant, and the refrigerant is difluoromethane or propane.

15. A refrigeration device, characterized in that: include: A compressor as claimed in any one of claims 1 to 14.

Images