WO2021103525A1 - 压缩机和制冷设备 - Google Patents

压缩机和制冷设备 Download PDF

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Publication number
WO2021103525A1
WO2021103525A1 PCT/CN2020/099160 CN2020099160W WO2021103525A1 WO 2021103525 A1 WO2021103525 A1 WO 2021103525A1 CN 2020099160 W CN2020099160 W CN 2020099160W WO 2021103525 A1 WO2021103525 A1 WO 2021103525A1
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WO
WIPO (PCT)
Prior art keywords
crankshaft
bearing
connecting structure
compressor
avoidance
Prior art date
Application number
PCT/CN2020/099160
Other languages
English (en)
French (fr)
Inventor
郑礼成
江波
Original Assignee
安徽美芝精密制造有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 安徽美芝精密制造有限公司 filed Critical 安徽美芝精密制造有限公司
Priority to EP20894567.5A priority Critical patent/EP3957857A4/en
Priority to JP2021571640A priority patent/JP7250961B2/ja
Publication of WO2021103525A1 publication Critical patent/WO2021103525A1/zh
Priority to US17/531,014 priority patent/US20220090596A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements

Definitions

  • This application relates to the technical field of refrigeration equipment, and specifically to a compressor and a refrigeration equipment.
  • the compressor 100' includes a crankshaft 102', the crankshaft 102' includes a main shaft portion 1020', a counter shaft portion 1022' and an eccentric portion 1024', and 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 arranged in the cylinder cavity and the piston 114' is sleeved on the eccentric portion 1024'
  • the parts 1020' are connected, and the balance weight 112' is arranged on the rotor 110'.
  • FIG. 2 shows the parts where the main shaft part 1020' and the main bearing 104', the counter shaft part 1022' and the auxiliary bearing 106', and the eccentric part 1024' and the piston 114' fit together.
  • A'in 2 shows the part where the main shaft part 1020' and the main bearing 104' are prone to wear.
  • the bearing of the compressor 100' has increased in volume, cost, and friction loss.
  • This application aims to solve at least one of the technical problems existing in the prior art or related technologies.
  • the first aspect of the present application provides a compressor.
  • the second aspect of the application also provides a refrigeration device.
  • the first aspect of the present application proposes a compressor, including: a crankshaft; a connecting structure arranged on the crankshaft; wherein the connecting structure and/or the crankshaft are provided with an avoiding portion, and the avoiding portion is located between the connecting structure and the crankshaft.
  • the avoiding portion is configured to be suitable for avoiding at least one of the connecting structure and the crankshaft.
  • the compressor provided in the present application includes a crankshaft and a connecting structure connected to the crankshaft.
  • the connecting structure and/or the crankshaft are provided with an avoiding portion, and the avoiding portion is used to avoid at least one of the connecting structure or the crankshaft.
  • the arrangement can increase the gap between the crankshaft and the connecting structure, and then when the crankshaft is tilted and deformed, the avoiding part can avoid the inclined crankshaft, so that the contact holding surface of the crankshaft and the connecting structure is in contact, so that the crankshaft and the connecting structure are in contact with each other.
  • the oil film is not destroyed, which effectively guarantees the reliability of the compressor, and can adopt a thinner shaft diameter and a shorter sleeve, which reduces the volume and cost of the compressor, and reduces the friction loss of the matching part of the crankshaft and the connecting structure. , Thereby improving compressor performance.
  • the avoidance part avoids at least one of the connecting structure and the crankshaft, that is, the avoidance part avoids tilting deformation of the crankshaft to ensure that after the crankshaft is tilted, the contact between the crankshaft and the connecting structure of the corresponding part of the avoidance part is surface contact.
  • the gap between the crankshaft and the connecting structure there is a gap between the crankshaft and the connecting structure, and the lubricating oil can be distributed in the gap.
  • the gap corresponding to the avoiding portion increases in the direction away from the middle of the connecting structure.
  • the gradually increasing clearance can form a 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 the wear between the crankshaft and the connecting structure.
  • the sum of the clearances on both sides of the crankshaft axis is defined as the bilateral clearance;
  • the bilateral clearance corresponding to the avoidance part The minimum value of is ⁇ 0
  • the difference between the maximum value of the bilateral clearance corresponding to the avoidance part and ⁇ 0 is ⁇
  • the diameter of the crankshaft corresponding to the part with the smallest bilateral clearance corresponding to the avoidance part is D, along the axis of the crankshaft, the avoidance part
  • the length of is h; where, the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.
  • 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 and a maximum value, and the minimum value of the bilateral gap corresponding to the avoidance portion is ⁇ 0 .
  • the difference between the maximum value of the corresponding bilateral clearance and ⁇ 0 is ⁇ .
  • the diameter of the crankshaft corresponding to the part with the smallest bilateral clearance corresponding to the avoidance part is D.
  • the length of the avoidance part is h, and the avoidance part corresponds to The size affects the effect of improving the friction between the crankshaft and the connecting structure. Therefore, the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is set to be greater than or equal to 0.2 and less than or equal to 5. The effect of improving the friction between the connecting structures is the best.
  • the avoidance portion includes a plurality of avoidance sections, which are sequentially connected along the axis of the crankshaft, wherein at least one avoidance section satisfies the quotient of ⁇ and ⁇ 0 , and D and h
  • the product of the quotient is greater than or equal to 0.2 and less than or equal to 5.
  • the avoidance section includes a plurality of avoidance sections, which are sequentially connected along the axial direction.
  • the size of at least one avoidance section satisfies the quotient of ⁇ and ⁇ 0 , and D and
  • the product of the quotient of h is a relational expression that is greater than or equal to 0.2 and less than or equal to 5.
  • the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is greater than or equal to 0.5 and less than or equal to 2.5.
  • h is greater than or equal to 2 mm and less than or equal to 20 mm.
  • the axial height h of the avoidance part is set to 2mm ⁇ h ⁇ 20mm, which is more convenient for the processing of the avoidance part and also helps reduce the wear between the crankshaft and the connecting structure.
  • the size of the gap corresponding to at least part of the avoiding portion changes linearly.
  • the size of the gap corresponding to at least part of the avoiding 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, it moves away from the middle part of the connecting structure.
  • the radial direction of the gap changes in direct proportion.
  • the wall surface formed by the avoiding portion includes a tapered surface.
  • the wall surface formed by the avoidance portion includes a tapered surface, so that the gap between the crankshaft and the connecting structure changes linearly in the axial direction, and at the same time, the processing of the avoidance portion is facilitated.
  • the tangent to the wall formed by at least part of the relief portion is the same as the direction perpendicular to the axis of the crankshaft. The acute angle between them gradually decreases.
  • the tangent to the wall surface formed by at least part of the avoidance part gradually tends to be horizontal, that is, the tangent to the wall surface formed by the avoidance part is perpendicular to the crankshaft
  • the acute angle in the axial direction is gradually reduced, so that the avoiding portion and the shape of the flexural deformation of the crankshaft are more matched, thereby further improving the wear improvement effect.
  • the wall surface formed by the avoiding portion includes a curved surface.
  • the wall surface formed by the avoiding portion includes a curved surface, so that the change of the gap corresponding to the avoiding portion is more matched with the shape of the flexural deformation of the crankshaft, thereby further improving the wear improvement effect.
  • the avoiding portion has a ring shape.
  • the avoiding part is annular, and the annular avoiding part can produce a good avoiding effect in 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
  • the improvement effect of, that is, the degree of wear can be reduced in all directions.
  • the crankshaft includes: a main body, the main body includes a first shaft portion and a second shaft portion coaxially arranged; an eccentric portion connected to the main body, and the main body and the eccentric portion are eccentrically arranged.
  • 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 with the rotor of the motor to drive the eccentric part to rotate
  • the eccentric part rotates to realize the suction of the compressor Exhaust process.
  • 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.
  • the connecting structure includes a first bearing, a second bearing, and a piston.
  • the first bearing is sleeved on the first shaft portion
  • the second bearing is sleeved on the second shaft portion.
  • the bearing realizes the fixation of the crankshaft
  • the piston is sleeved on the eccentric part
  • the movement of the piston is driven by the rotation of the eccentric part, thereby realizing the suction and discharge process of the compressor.
  • the avoidance part is arranged at the part of the first shaft part close to the second shaft part and/or the escape part is arranged at the first shaft part away from the second shaft part
  • the part of the eccentric part, and/or the avoiding part is arranged at the end of the eccentric part close to the first bearing and/or the avoiding part is arranged at the end of the eccentric part close to the second bearing, and/or the avoiding part is arranged at the end of the second shaft part close to the eccentric part .
  • the escape portion when the escape portion is provided on the crankshaft, the escape portion is provided at the portion of the first shaft portion close to the second shaft portion, the portion of the first shaft portion away from the second shaft portion, and the eccentric portion close to the first bearing.
  • the avoidance portion is provided at an end of the first bearing close to the second bearing and/or the escape portion is provided at an end of the first bearing away from the second bearing, And/or the avoidance part is arranged at the end of the piston close to the first bearing and/or the avoidance part is arranged at the end of the piston close to the second bearing, and/or the avoidance part is arranged at the end of the second bearing close to the first bearing.
  • the avoidance part when the avoidance part is arranged on the connecting structure, the avoidance part is arranged at the end of the first bearing close to the second bearing, the end of the first bearing away from the second bearing, the end of the piston close to the first bearing, and the end of the piston close to the second bearing. Any one or a combination of one end of the second bearing and an end of the second bearing close to the first bearing.
  • the avoiding part can also be provided on the connecting structure and the crankshaft at the same time.
  • the compressor further includes: a cylinder, the cylinder includes a cylinder cavity, the piston is arranged in the cylinder cavity, the crankshaft is penetrated in the cylinder cavity, and the cylinder is provided with a sliding vane groove; the sliding vane is arranged In the sliding plate groove, it is connected with the piston in rolling motion; the rotor is connected with the first shaft part.
  • the compressor further includes a cylinder, a sliding vane and a rotor, the rotor is connected with the first shaft portion, the cylinder has a cylinder cavity, the piston is arranged in the cylinder cavity, and the crankshaft is penetrated in the cylinder cavity.
  • the cylinder is also provided with a sliding plate groove, and the sliding plate is arranged in the sliding plate groove and is rotatably connected with the piston, so as to realize the suction and discharge process of the compressor.
  • the compressor is an inverter compressor.
  • the compressor is an inverter compressor, and the reliability of the inverter compressor can be improved by arranging an escape part on the connecting structure or on the crankshaft.
  • the compressor may also be a fixed speed compressor.
  • the compressor is filled with a refrigerant, and the refrigerant is difluoromethane or propane.
  • the compressor is filled with a refrigerant, and the cooling or heating of the refrigeration equipment is realized through the process of heat absorption and heat release of the refrigerant.
  • the refrigerant is difluoromethane or propane.
  • the refrigerant can also be other Refrigerant.
  • a refrigeration equipment including: the compressor as proposed in any of the above technical solutions.
  • the refrigeration equipment provided in the second aspect of the present application includes the compressor proposed in any of the above technical solutions, and therefore has all the beneficial effects of the compressor.
  • the refrigeration equipment includes a heat exchanger, the heat exchanger and the compressor are connected through a pipeline, and the refrigerant can flow in the pipeline.
  • Figure 1 shows a schematic structural diagram of a compressor in the related art
  • Fig. 2 shows another structural schematic diagram of the compressor in the related art.
  • FIG. 3 shows a schematic diagram of the structure in which the avoiding portion of an embodiment of the present application is a conical surface
  • Fig. 4 shows the curve relationship between the avoidance portion and the minimum oil film thickness of an embodiment of the present application
  • FIG. 5 shows another schematic diagram of the structure in which the avoiding portion of an embodiment of the present application is a tapered surface
  • FIG. 6 shows a schematic diagram of a structure in which the avoiding portion is a curved surface according to an embodiment of the present application
  • FIG. 7 shows another schematic diagram of the structure in which the avoiding portion of an embodiment of the present application is a curved surface
  • Figure 8 shows a schematic structural diagram of a compressor according to a specific embodiment of the present application.
  • Fig. 9 shows a schematic structural diagram of a compressor according to another specific embodiment of the present application.
  • the present application proposes a compressor 100 including: a crankshaft 102 and a connecting structure 104.
  • the connecting structure 104 is arranged on the crankshaft 102; wherein, the connecting structure 104 and/or the crankshaft 102 is provided with an avoiding portion 106, the avoiding portion 106 is located at the part where the connecting structure 104 and the crankshaft 102 cooperate, and the avoiding portion 106 is configured It is suitable for avoiding at least one of the connecting structure 104 and the crankshaft 102.
  • the compressor 100 provided in the present application includes a crankshaft 102 and a connecting structure 104 connected to the crankshaft 102.
  • the connecting structure 104 and/or the crankshaft 102 are provided with an avoiding portion 106, and the avoiding portion 106 is used to avoid the connecting structure 104 or
  • the arrangement of the avoiding portion 106 can increase the gap 108 between the crankshaft 102 and the connecting structure 104, and when the crankshaft 102 is tilted and deformed, the avoiding portion 106 can avoid the inclined crankshaft 102.
  • crankshaft 102 and the connecting structure 104 contact and maintain surface 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 diameter can be used.
  • the shaft sleeve reduces the volume and cost of the compressor 100, reduces the friction loss of the mating part of the crankshaft 102 and the connecting structure 104, thereby improving the performance of the compressor 100.
  • the avoiding portion 106 avoids at least one of the connecting structure 104 and the crankshaft 102, that is, the avoiding portion 106 avoids the tilting deformation of the crankshaft 102 to ensure that after the crankshaft 102 is tilted, the avoiding portion 106 corresponds to the crankshaft 102 and the crankshaft 102.
  • the contact of the connection structure 104 is surface contact.
  • the avoiding portion 106 when the avoiding 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 a line contact, local oil film is broken, and the crankshaft 102 and the connecting structure 104 are in direct metal contact, which is likely to cause wear.
  • the avoidance portion 106 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 friction between the crankshaft 102 and the connecting structure 104.
  • the degree of wear improves the reliability of the compressor 100.
  • the shape of the avoidance portion 106 is adapted to the shape of the corresponding inclined outer side wall of the crankshaft 102; based on the avoidance portion 106 being arranged on the crankshaft 102, the crankshaft 102 is inclined Later, the shape of the avoiding portion 106 is adapted to the shape of the inner side wall of the connecting structure 104.
  • the avoiding portion 106 is provided at the end of the connecting structure 104 and/or at the part of the crankshaft 102 corresponding to the end of the connecting structure 104.
  • the avoiding portion 106 is provided in the circumferential direction of the end of the connecting structure 104 and/or provided in the circumferential direction of the portion of the crankshaft 102 corresponding to the end of the connecting mechanism.
  • the avoiding portion 106 when the avoiding portion 106 is disposed on the connecting structure 104, at least a part of the avoiding portion 106 is located on the inner side wall of the connecting structure 104.
  • FIG. 3 it includes the features defined in the above-mentioned embodiments, and further: there is a gap 108 between the crankshaft 102 and the connecting structure 104, and along the axis of the crankshaft 102, the relief portion 106 corresponds to The gap 108 increases in a direction away from the middle of the connection structure 104.
  • the lubricating oil can be distributed in the gap 108.
  • the gap 108 corresponding to the avoiding portion 106 is away from the middle of the connecting structure 104.
  • the direction increases, so that when the crankshaft 102 is tilted and deformed, the gradually increasing gap 108 can form an escape 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 Therefore, the abrasion between the crankshaft 102 and the connecting structure 104 is avoided, and the reliability of the compressor 100 is improved.
  • the connecting structure 104 can be divided into two end portions and a middle portion disposed between the two end portions.
  • the gap 108 corresponding to the avoiding portion 106 gradually increases in the direction away from the middle portion of the connecting structure 104 to adapt to the shape of the crankshaft 102 when the crankshaft 102 is tilted and deformed.
  • the avoiding portion 106 when the avoiding portion 106 is arranged on the connecting structure 104, the avoiding portion 106 is arranged at the end of the connecting structure 104. In the axial direction of the crankshaft 102, in the direction away from the middle of the connecting structure 104, the avoiding portion 106 is connected to The radial outer side of the structure 104 is obliquely arranged; when the avoiding portion 106 is arranged on the crankshaft 102, the avoiding portion 106 is located at the end of the crankshaft 102 corresponding to the connecting structure 104, in the axial direction of the crankshaft 102, along the distance away from the connecting structure 104 In the direction of the middle portion, the relief portion 106 is inclined to the axial direction of the crankshaft 102.
  • the present application includes the features defined in the above-mentioned embodiment, and further: in the cross section of the compressor 100 in the axial direction of the crankshaft 102, at the same axial height, the gap 108 on both sides of the axis of the crankshaft 102 The sum is defined as the bilateral gap 108; the minimum value of the bilateral gap 108 corresponding to the avoiding portion 106 is ⁇ 0 , the difference between the maximum value of the bilateral gap 108 corresponding to the avoiding portion 106 and ⁇ 0 is ⁇ , the bilateral gap 108 corresponding to the avoiding portion 106
  • the diameter of the crankshaft 102 corresponding to the smallest part is D
  • the length of the avoiding portion 106 is h; where the quotient of ⁇ and ⁇ 0 , 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.
  • the avoiding portion 106 gradually increases from the middle to the end of the connecting structure 104, so the bilateral gap 108 corresponding to the avoiding portion 106 has a minimum and a maximum value, and the minimum value of the bilateral gap 108 corresponding to the avoiding portion 106 Is ⁇ 0 , the difference between the maximum value of the bilateral gap 108 corresponding to the avoidance portion 106 and ⁇ 0 is ⁇ , the diameter of the crankshaft 102 corresponding to the smallest portion of the bilateral gap 108 corresponding to the avoidance portion 106 is D, along the axis of the crankshaft 102 , The length of the avoiding portion 106 is h, and the corresponding size of the avoiding portion 106 affects the effect of improving the friction between the crankshaft 102 and the connecting structure 104.
  • the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is set as If it is greater than or equal to 0.2 and less than or equal to 5, the avoidance portion 106 has the best effect on improving the friction between the crankshaft 102 and the connecting structure 104 at this time.
  • ⁇ 0 /2 is half of the bilateral gap 108 corresponding to the avoiding portion 106
  • ⁇ /2 is half of the difference between the maximum value of the bilateral gap 108 corresponding to the avoiding portion 106 and ⁇ 0.
  • the difference between the diameter of the inner side wall of the connecting structure 104 and the diameter of the crankshaft 102 is the bilateral gap 108.
  • the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is greater than or equal to 0.5 and less than or equal to 2.5.
  • FIG. 4 is a graph showing the influence of the size of the avoidance portion 106 on the minimum oil film thickness, where the horizontal axis adopts a logarithmic coordinate, and the oil film bearing capacity between the crankshaft 102 and the connecting structure 104 can be used
  • the minimum oil film thickness characterizes. The greater the minimum oil film thickness, the stronger the oil film carrying capacity, and the less likely to be abraded between the crankshaft 102 and the connecting structure 104.
  • h is greater than or equal to 2 mm and less than or equal to 20 mm.
  • the axial height h of the avoidance portion 106 is set to 2mm ⁇ h ⁇ 20mm, which is more convenient for processing the avoidance portion 106 and also helps reduce the wear between the crankshaft 102 and the connecting structure 104.
  • the avoiding portion 106 includes a plurality of avoiding sections, and the plurality of avoiding sections are sequentially opposite to each other along the axial direction of the crankshaft 102. Connection, where at least one avoidance segment satisfies the quotient of ⁇ and ⁇ 0 , 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.
  • the avoidance section 106 includes a plurality of avoidance sections, which are sequentially connected along the axial direction. Among the plurality of avoidance sections, at least one of the avoidance sections has a size that satisfies the above-mentioned quotient of ⁇ and ⁇ 0 , and D The product of the quotient of h is greater than or equal to 0.2 and less than or equal to 5.
  • the avoidance segment satisfies: the product of the quotient of ⁇ and ⁇ 0 , 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 segment is ⁇ 0 , the difference between the maximum value of the bilateral gap 108 corresponding to the avoiding section and ⁇ 0 is ⁇ , the diameter of the crankshaft 102 corresponding to the smallest part of the bilateral gap 108 corresponding to the avoiding section is D, along the axis of the crankshaft 102, the avoiding section
  • the length of is h, and the corresponding ⁇ , ⁇ 0 , D and h of the avoidance section satisfy the above-defined relational expression.
  • the avoiding portion 106 is provided at the end of the connecting structure 104, and the inclination angles of the plurality of avoiding sections may be the same or different. Further, the plurality of avoiding sections are smoothly connected.
  • the size of the gap 108 corresponding to at least part of the relief portion 106 changes linearly, that is, in the cross section of the compressor 100 in the axial direction of the crankshaft 102, along the axial direction of the crankshaft 102, From the direction away from the middle of the connecting structure 104, the radial size of the gap 108 changes in a proportional relationship.
  • the wall surface formed by the avoiding portion 106 includes a tapered surface.
  • the wall surface formed by the avoiding portion 106 includes a tapered surface, so that the gap 108 between the crankshaft 102 and the connecting structure 104 changes linearly in the axial direction, and at the same time, the processing of the avoiding portion 106 is facilitated.
  • Embodiment 6 is a diagrammatic representation of Embodiment 6
  • the compressor 100 is on the cross section of the crankshaft 102 in the axial direction along the distance away from the connecting structure 104 In the direction of the middle portion, the acute angle between the tangent to the wall formed by at least part of the relief portion 106 and the direction perpendicular to the axis of the crankshaft 102 gradually decreases.
  • the tangent of the wall formed by at least part of the avoiding portion 106 gradually becomes horizontal, that is, the tangent of the wall formed by the avoiding portion 106 and
  • the acute angle perpendicular to the axial direction of the crankshaft 102 is gradually reduced, so that the avoiding portion 106 and the shape of the flexural deformation of the crankshaft 102 are more matched, thereby further improving the wear improvement effect.
  • the speed at which the gap 108 corresponding to the avoiding portion 106 increases gradually increases.
  • the wall surface formed by the avoiding portion 106 includes a curved surface.
  • the wall formed by the avoiding portion 106 includes a curved surface, so that the change of the gap 108 corresponding to the avoiding portion 106 is more matched with the shape of the flexural deformation of the crankshaft 102, thereby further improving the wear improvement effect.
  • the avoiding portion 106 is provided on the crankshaft 102, and the avoiding portion 106 is realized by the change of the diameter of the crankshaft 102, that is, the diameter of the crankshaft 102 after the avoiding portion 106 is reduced, and the crankshaft 102 is formed at the avoiding portion 106
  • the tapered shape makes the gap 108 between the crankshaft 102 and the connecting structure 104 linearly change in the axial direction in the part where the avoiding portion 106 is provided.
  • the avoiding portion 106 is provided on the connecting structure 104, and the avoiding portion 106 is realized by the diameter change of the connecting structure 104, that is, the diameter of the inner side wall of the connecting structure 104 after the avoiding portion 106 is increased, and the avoiding portion 106 is
  • the inner side wall of the connecting structure 104 at 106 is tapered, so that the gap 108 between the crankshaft 102 and the connecting structure 104 changes linearly in the axial direction at the portion where the avoiding portion 106 is provided.
  • the avoiding portion 106 can be set as a curved surface, facing away from the center of the movement pair (away from the middle of the connecting structure 104) In the axial direction, the speed at which the gap 108 corresponding to the avoiding portion 106 increases gradually increases, that is, the tangent line of the avoiding portion 106 and the axis of the crankshaft 102 gradually become parallel, and the gap 108 corresponding to the avoiding portion 106 can be changed. It is more matched with the flexural deformation shape of the crankshaft 102, thereby further improving the wear improvement effect.
  • the avoiding portion 106 can also be provided on the crankshaft 102 and the connecting structure 104 at the same time.
  • the wall surface formed by the escape portion 106 includes a tapered surface and a curved surface.
  • the avoiding portion 106 in a cross section perpendicular to the axis of the crankshaft 102, the avoiding portion 106 has a ring shape.
  • the avoiding portion 106 has a ring shape, and the annular avoiding portion 106 can produce a good avoiding effect on the crankshaft 102 in all directions when the crankshaft 102 is tilted and deformed, and thus can improve the crankshaft 102 and the connection in all directions.
  • the improvement effect of the wear between the structures 104 that is, the degree of wear can be reduced in all directions.
  • Embodiment 8 is a diagrammatic representation of Embodiment 8
  • crankshaft 102 includes a main body, and the main body includes a first shaft portion 1020 and a first shaft portion 1020 and Two shaft parts 1022; an eccentric part 1024, which is connected to the main body, and the main body and the eccentric part 1024 are eccentrically arranged.
  • 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 with the rotor 114 of the motor to drive the eccentric portion 1024 to rotate.
  • the 1024 rotation realizes the suction and discharge process of the compressor 100.
  • the connecting 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.
  • 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.
  • the crankshaft 102 is fixed by the first bearing 1040 and the second bearing 1042
  • the piston 1044 is sleeved on the eccentric part 1024
  • the piston 1044 is driven to move through the rotation of the eccentric part 1024, thereby realizing the suction and discharge process of the compressor 100 .
  • the avoidance portion 106 is arranged on the portion of the first shaft portion 1020 close to the second shaft portion 1022 and/or the avoidance portion 106 is arranged on the first shaft portion 1020 away from the second shaft portion 1022
  • the part of the eccentric part 1024 and/or the avoiding part 106 is arranged at the end of the eccentric part 1024 close to the first bearing 1040 and/or the avoiding part 106 is arranged at the end of the eccentric part 1024 close to the second bearing 1042, and/or the avoiding part 106 is arranged at the second bearing 1042.
  • the shaft portion 1022 is close to one end of the eccentric portion 1024.
  • the escape portion 106 when the escape portion 106 is provided on the crankshaft 102, the escape portion 106 is provided at the portion of the first shaft portion 1020 close to the second shaft portion 1022, the portion of the first shaft portion 1020 away from the second shaft portion 1022, The eccentric portion 1024 is close to one end of the first bearing 1040, the eccentric portion 1024 is close to an end of the second bearing 1042, and the second shaft portion 1022 is close to any one or a combination of the end of the eccentric portion 1024.
  • the avoidance portion 106 is arranged on the end of the first bearing 1040 close to the second bearing 1042 and/or the avoidance portion 106 is arranged on the end of the first bearing 1040 away from the second bearing 1042, And/or the avoiding portion 106 is arranged at the end of the piston 1044 close to the first bearing 1040 and/or the avoiding portion 106 is arranged at the end of the piston 1044 close to the second bearing 1042, and/or the avoiding portion 106 is arranged at the second bearing 1042 close to the first bearing.
  • the avoiding portion 106 when the avoiding portion 106 is arranged on the connecting structure 104, the avoiding portion 106 is arranged on the end of the first bearing 1040 close to the second bearing 1042, the end of the first bearing 1040 away from the second bearing 1042, and the piston 1044 close to One end of the first bearing 1040, one end of the piston 1044 close to the second bearing 1042, and one end of the second bearing 1042 close to the first bearing 1040 or a combination thereof.
  • the avoiding portion 106 can also be provided on the connecting structure 104 and the crankshaft 102 at the same time.
  • the compressor 100 further includes: a cylinder 110, the cylinder 110 includes a cylinder cavity, the piston 1044 is arranged in the cylinder cavity, the crankshaft 102 is inserted in the cylinder cavity, and the cylinder 110 is provided with a sliding plate 112 groove; the sliding plate 112 is arranged In the groove of the sliding plate 112, it is connected to the piston 1044 in rolling motion; the rotor 114 is connected to the first shaft portion 1020.
  • the compressor 100 further includes a cylinder 110, a sliding 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 arranged in the cylinder cavity, and the crankshaft 102 penetrates. Set in the cylinder cavity.
  • the cylinder 110 is also provided with a sliding plate 112 groove, the sliding plate 112 is arranged in the sliding plate 112 groove, and is rotatably connected with the piston 1044, so as to realize the suction and discharge process of the compressor 100.
  • the compressor 100 is an inverter compressor.
  • the compressor 100 is an inverter compressor, and the reliability of the inverter compressor can be improved by arranging the avoidance portion 106 on the connecting structure 104 or the crankshaft 102.
  • the compressor 100 may also be a fixed speed compressor.
  • the compressor 100 is filled with a refrigerant, and the refrigerant is difluoromethane or propane.
  • the compressor 100 is filled with refrigerant, and the cooling or heating of the refrigeration equipment is realized through the process of heat absorption and heat release of the refrigerant.
  • the refrigerant is difluoromethane or propane.
  • the refrigerant can also be Other refrigerants.
  • the compressor 100 includes a crankshaft 102, a first bearing 1040, a second bearing 1042, a cylinder 110, a piston 1044, a sliding vane 112, and a rotor 114.
  • the above-mentioned components form a suction chamber and a compression chamber.
  • the rotor 114 of the motor drives the crankshaft 102 to rotate, which increases the volume of the suction chamber and reduces the volume of the compression chamber to realize the suction 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 of the sliding bearing (the first shaft portion 1020, the second shaft portion 1022 or the eccentric shaft) and the connecting structure 104 (the first bearing 1040, the second bearing 1042 or the piston 1044), Full of lubricating oil during normal operation.
  • the three sliding bearings mentioned above often experience abnormal wear. Specifically, due to the centrifugal force generated during the rotation of the rotor 114 and the magnetic pulling force of the motor itself, the center of the rotor 114 will deviate from the motor axis and yaw.
  • crankshaft 102 will be flexed and deformed, resulting in the first part of the crankshaft 102.
  • the shaft portion 1020 is in line contact with the upper end of the first bearing 1040, and the oil film is partially broken.
  • the first shaft portion 1020 of the crankshaft 102 and the first bearing 1040 are in direct metal contact and cause wear.
  • the eccentric shaft of the crankshaft 102 will be flexed and deformed under the action of the air 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 second bearing 1042
  • the edges, the eccentric shaft, and the upper and lower edges of the piston 1044 may be in direct metal contact and cause abnormal wear. Therefore, due to the inclination and 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. As shown in FIG.
  • the connecting structure 104 or the part where the crankshaft 102 matches the connecting structure 104 is provided with an avoiding portion 106, and there is a gap 108 between the connecting structure 104 and the crankshaft 102, and the avoiding portion 106
  • the gap 108 between the corresponding connecting structure 104 and the crankshaft 102 part increases toward the axial direction away from the center of the movement pair, so that the original metal contact parts can still maintain surface contact after the crankshaft 102 is flexed and deformed, and a normal oil film is established, thereby avoiding Wear and tear greatly improves the reliability of the compressor 100.
  • crankshaft 102 or the connecting structure 104 can be removed by turning or the like to form the avoiding portion 106, or the crankshaft 102 and the avoiding portion 106 provided on the crankshaft 102 can be manufactured integrally, or the connecting structure 104 It is manufactured integrally with the avoiding portion 106 provided on the connecting structure 104.
  • the minimum value of the bilateral gap 108 corresponding to the avoiding portion 106 is ⁇ 0
  • the difference between the maximum value of the bilateral gap 108 corresponding to the avoiding portion 106 and ⁇ 0 is ⁇
  • the minimum bilateral gap 108 corresponding to the avoiding portion 106 corresponds to
  • the diameter of the crankshaft 102 is D.
  • the length of the avoiding portion 106 is h.
  • the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.
  • Figure 4 it is a graph showing the influence of the size of the sliding bearing avoidance portion 106 on the minimum oil film thickness.
  • the horizontal axis adopts a logarithmic coordinate.
  • the oil film carrying capacity of the sliding bearing can be characterized by the minimum oil film thickness. The greater the minimum oil film thickness , The stronger the oil film bearing capacity, the less prone to wear of the sliding bearing. It can be seen from Fig. 4 that the size of the avoiding part 106 meets: the quotient of ⁇ and ⁇ 0 , the product of the quotient of D and h, is greater than or equal to 0.2 and less than or equal to At 5 o'clock, the effect of improving wear is the best.
  • the product of the quotient of ⁇ and ⁇ 0 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.
  • 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, which are connected
  • the 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
  • the piston 1044 is sleeved on the eccentric Department 1024.
  • the avoiding portion 106 is provided on the crankshaft 102.
  • the first shaft portion 1020 corresponds to the upper end and the lower end portion of the first bearing 1040
  • the second shaft portion 1022 corresponds to the upper end portion of the second bearing 1042.
  • the upper and lower parts of the piston 1044 corresponding to the eccentric shaft are provided with avoiding parts 106.
  • the shape of the avoiding parts 106 is a conical surface.
  • the specific dimensions of any avoiding part 106 satisfy: the quotient of ⁇ and ⁇ 0 , and D and The product of the quotient of h is greater than or equal to 0.2 and less than or equal to 5.
  • h1, h2, h3, h4, and h5 in FIG. 8 are the axial heights of the avoiding portion 106, respectively.
  • Embodiment 11 is a diagrammatic representation of Embodiment 11:
  • 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, which are connected
  • the 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
  • the piston 1044 is sleeved on the eccentric Department 1024.
  • the avoiding portion 106 is provided on the connecting structure 104.
  • the avoiding portion 106 is provided on the upper and lower ends of the first bearing 1040, the upper end of the second bearing 1042, the upper and lower ends of the piston 1044, and the avoiding portion 106.
  • the shape of is a curved surface, and the specific dimensions of any avoidance portion 106 respectively satisfy: the product of the quotient of ⁇ and ⁇ 0 and the quotient of D and h is greater than or equal to 0.2 and less than or equal to 5.
  • h1, h2, h3, h4, and h5 in FIG. 9 are the axial heights of the avoiding portion 106, respectively.
  • Embodiment 12 is a diagrammatic representation of Embodiment 12
  • a refrigeration equipment including: the compressor 100 as proposed in any of the above embodiments.
  • the refrigeration equipment provided in the second aspect of the present application includes the compressor 100 proposed in any of the above embodiments, and therefore has all the beneficial effects of the compressor 100.
  • the refrigeration equipment 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.
  • the term “plurality” refers to two or more than two, unless specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed”, etc. should be understood in a broad sense.
  • “connected” can be a fixed connection, a detachable connection, or an integral connection;
  • “connected” can be Directly connected, or indirectly connected through an intermediary.
  • the specific meanings of the above-mentioned terms in this application can be understood according to specific circumstances.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Applications Or Details Of Rotary Compressors (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

一种压缩机(100)和制冷设备，压缩机(100)包括：曲轴(102)；连接结构(104)，设置在曲轴(102)上；其中，连接结构(104)上和/或曲轴(102)上设置有避让部(106)，避让部(106)位于连接结构(104)与曲轴(102)相配合的部分，避让部(106)被配置为适于避让连接结构(104)和曲轴(102)中的至少一个。该压缩机，包括曲轴(102)和与曲轴(102)相连接的连接结构(104)，避让部(106)的设置能够使得曲轴(102)与连接结构(104)之间的间隙增大，进而在曲轴(102)发生倾斜变形时，避让部(106)能够对倾斜的曲轴(102)进行避让，以使得曲轴(102)与连接结构(104)的接触保持面接触，使得曲轴(102)与连接结构(104)之间的油膜不被破坏，从而有效保证压缩机(100)的可靠性，进而可以采用更细的轴径、更短的轴套，减少曲轴(102)与连接结构(104)配合部分的摩擦损失，提升了压缩机性能。

Description

压缩机和制冷设备
本申请要求于2019年11月29日提交到中国国家知识产权局、申请号为“2019112016855”、申请名称为“压缩机和制冷设备”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及制冷设备技术领域，具体而言，涉及一种压缩机、一种制冷设备。
背景技术
目前，如图1和图2所示，压缩机100’包括曲轴102’，曲轴102’包括主轴部1020’、副轴部1022’和偏心部1024’，主轴承104’套设在主轴部1020’上，副轴承106’套设在副轴部1022’上，气缸108’包括气缸腔，活塞114’设置在气缸腔内且活塞114’套设在偏心部1024’上，转子110’与主轴部1020’相连接，平衡块112’设置在转子110’上。如图2所示，主轴部1020’与主轴承104’、副轴部1022’与副轴承106’、偏心部1024’与活塞114’相配合的部位最容易导致异常磨损等可靠性问题，图2中A’处所示为主轴部1020’与主轴承104’容易发生磨损的部分，为了保证相配合部位的运动副的可靠性，现有技术中只能采用较粗的轴径、更高的轴承，从而导致压缩机100’体积的增大、成本的上升以及摩擦损失的增大。
发明内容
本申请旨在至少解决现有技术或相关技术中存在的技术问题之一。
为此，本申请的第一方面提供了一种压缩机。
本申请的第二方面还提供了一种制冷设备。
有鉴于此，本申请的第一方面提出了一种压缩机，包括：曲轴；连接结构，设置在曲轴上；其中，连接结构上和/或曲轴上设置有避让部，避让 部位于连接结构与曲轴相配合的部分，避让部被配置为适于避让连接结构和曲轴中的至少一个。
本申请提供的压缩机，包括曲轴和与曲轴相连接的连接结构，其中，连接结构上和/或曲轴上设置有避让部，避让部用于避让连接结构或曲轴中的至少一个，避让部的设置能够使得曲轴与连接结构之间的间隙增大，进而在曲轴发生倾斜变形时，避让部能够对倾斜的曲轴进行避让，以使得曲轴与连接结构的接触保持面接触，使得曲轴与连接结构之间的油膜不被破坏，从而有效保证压缩机的可靠性，进而可以采用更细的轴径、更短的轴套，降低了压缩机的体积以及成本，减少曲轴与连接结构配合部分的摩擦损失，从而提升压缩机性能。
可以理解的是，避让部避让连接结构和曲轴中的至少一个，也即避让部对曲轴的倾斜变形进行避让，以保证曲轴倾斜后，避让部对应部分的曲轴和连接结构的接触为面接触。
根据本申请提供的上述的压缩机，还可以具有以下附加技术特征：
在上述技术方案中，进一步地，曲轴与连接结构之间具有间隙，沿曲轴的轴线方向，避让部对应的间隙向远离连接结构的中部方向增大。
在该技术方案中，曲轴与连接结构之间具有间隙，间隙内能够供润滑油分布，其中，沿曲轴的轴线方向，避让部对应的间隙向远离连接结构的中部方向增大，从而在曲轴发生倾斜变形时，逐渐增大的间隙可对曲轴形成避让空间，使得曲轴与连接结构之间的接触变为面接触，进而保证了油膜的正常工作，从而避免了曲轴与连接结构之间的磨损，提升了压缩机的可靠性。
在上述任一技术方案中，进一步地，压缩机在曲轴的轴线方向的截面中，在同一轴向高度上，将曲轴的轴线两侧的间隙之和定义为双边间隙；避让部对应的双边间隙的最小值为δ 0，避让部对应的双边间隙的最大值与δ 0之差为δ，避让部对应的双边间隙最小的部分所对应的曲轴的直径为D，沿曲轴的轴线方向，避让部的长度为h；其中，δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。
在该技术方案中，避让部由连接结构的中部至端部方向逐渐增大，因此避让部对应的双边间隙具有最小值和最大值，避让部对应的双边间隙的 最小值为δ 0，避让部对应的双边间隙的最大值与δ 0之差为δ，避让部对应的双边间隙最小的部分所对应的曲轴的直径为D，沿曲轴的轴线方向，避让部的长度为h，避让部对应的尺寸影响着曲轴与连接结构的摩擦改善的效果，因此，将δ与δ 0之商，与D与h之商的乘积，设置为大于等于0.2，且小于等于5，此时避让部对曲轴与连接结构之间的摩擦的改善效果最好。
在上述任一技术方案中，进一步地，避让部包括多个避让段，沿曲轴的轴线方向多个避让段依次相连接，其中，至少一个避让段满足δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。
在该技术方案中，避让部包括多个避让段，多个避让段沿轴向依次相连接，在多个避让段中至少有一个避让段的尺寸满足上述δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5的关系式。
在上述任一技术方案中，进一步地，δ与δ 0之商，与D与h之商的乘积，大于等于0.5，且小于等于2.5。
在该技术方案中，δ与δ 0之商，与D与h之商的乘积，设置在大于等于0.5，且小于等于2.5之间时，对曲轴与连接结构之间的摩擦的改善效果较好。
在上述任一技术方案中，进一步地，h大于等于2mm，且小于等于20mm。
在该技术方案中，避让部的轴向高度h设置为2mm≤h≤20mm，更便于避让部的加工，同时也利于降低曲轴与连接结构之间的磨损情况。
在上述任一技术方案中，进一步地，沿曲轴的轴线方向，至少部分避让部对应的间隙的大小呈线性变化。
在该技术方案中，沿曲轴的轴线方向，至少部分避让部对应的间隙的大小呈线性变化，也就是压缩机在曲轴的轴线方向的截面中，沿曲轴的轴线方向，由远离连接结构的中部的方向，间隙的径向大小呈正比例关系变化。
在上述任一技术方案中，进一步地，避让部所形成的壁面包括锥面。
在该技术方案中，避让部形成的壁面包括锥面，从而使曲轴与连接结构之间的间隙沿轴向呈线性变化，同时也便于避让部的加工。
在上述任一技术方案中，进一步地，压缩机在曲轴的轴线方向的截面上，沿远离连接结构的中部的方向，至少部分避让部所形成的壁面的切线， 与垂直于曲轴的轴线的方向之间的锐角逐渐减小。
在该技术方案中，在曲轴的轴线方向上，沿远离连接结构的中部的方向，至少部分避让部形成的壁面的切线逐渐趋于水平，也即避让部形成的壁面的切线与垂直于曲轴的轴线方向的锐角逐渐减小，以使得避让部与曲轴的挠曲变形的形状更加匹配，从而进一步提升磨损改善效果。
在上述任一技术方案中，进一步地，避让部所形成的壁面包括曲面。
在该技术方案中，避让部形成的壁面包括曲面，使得避让部对应的间隙的变化与曲轴的挠曲变形的形状更加匹配，从而进一步提升磨损改善效果。
在上述任一技术方案中，进一步地，在垂直于曲轴的轴线的截面上，避让部呈环形。
在该技术方案中，避让部呈环形，环形的避让部能够在曲轴发生倾斜形变时对曲轴的各个方向均产生很好的避让效果，进而在各个方向均能提升曲轴与连接结构之间的磨损的改善效果，也即在各个方向均能减轻磨损程度。
在上述任一技术方案中，进一步地，曲轴包括：主体，主体包括同轴设置的第一轴部和第二轴部；偏心部，与主体相连接，主体与偏心部偏心设置。
在该技术方案中，曲轴包括主体与偏心部，主体包括第一轴部和第二轴部，第一轴部与电机的转子相连接从而带动偏心部转动，偏心部转动实现压缩机的吸气排气过程。
在上述任一技术方案中，进一步地，连接结构包括：第一轴承，套设在第一轴部上；第二轴承，套设在第二轴部上；活塞，套设在偏心部上。
在该技术方案中，连接结构包括第一轴承、第二轴承和活塞，第一轴承套设在第一轴部上，第二轴承套设在第二轴部上，通过第一轴承和第二轴承实现对曲轴的固定，活塞套设在偏心部上，通过偏心部转动带动活塞运动，进而实现压缩机的吸气和排气过程。
在上述任一技术方案中，进一步地，基于避让部设置在曲轴上，避让部设置在第一轴部靠近第二轴部的部分和/或避让部设置在第一轴部远离第二轴部的部分，和/或避让部设置在偏心部靠近第一轴承的一端和/或避让部设置在 偏心部靠近第二轴承的一端，和/或避让部设置在第二轴部靠近偏心部的一端。
在该技术方案中，当避让部设置在曲轴上时，避让部设置在第一轴部靠近第二轴部的部分、第一轴部远离第二轴部的部分、偏心部靠近第一轴承的一端，偏心部靠近第二轴承的一端、第二轴部靠近偏心部的一端中的任一个或其组合上。
在上述任一技术方案中，进一步地，基于避让部设置在连接结构上，避让部设置在第一轴承靠近第二轴承的一端和/或避让部设置在第一轴承远离第二轴承的一端，和/或避让部设置在活塞靠近第一轴承的一端和/或避让部设置在活塞靠近第二轴承的一端，和/或避让部设置在第二轴承靠近第一轴承的一端。
在该技术方案中，当避让部设置在连接结构上时，避让部设置在第一轴承靠近第二轴承的一端、第一轴承远离第二轴承的一端、活塞靠近第一轴承的一端、活塞靠近第二轴承的一端、第二轴承靠近第一轴承的一端中的任一个或其组合上。
当然，避让部还能够同时设置在连接结构和曲轴上。
在上述任一技术方案中，进一步地，压缩机还包括：气缸，气缸包括气缸腔，活塞设于气缸腔内，曲轴穿设在气缸腔内，气缸上设置有滑片槽；滑片，设置在滑片槽内，与活塞滚动连接；转子，与第一轴部相连接。
在该技术方案中，压缩机还包括气缸、滑片和转子，转子与第一轴部相连接，气缸具有气缸腔，活塞设置在气缸腔内，且曲轴穿设在气缸腔内。其中，气缸上还设置有滑片槽，滑片设置在滑片槽内，且与活塞转动连接，从而实现压缩机的吸气排气过程。
在上述任一技术方案中，进一步地，压缩机为变频压缩机。
在该技术方案中，压缩机为变频压缩机，通过在连接结构上或曲轴上设置避让部能够提高变频压缩机的可靠性，当然压缩机也可以为定速压缩机。
在上述任一技术方案中，进一步地，压缩机内充注有冷媒，冷媒为二氟甲烷或丙烷。
在该技术方案中，压缩机内充注有冷媒，通过冷媒的吸热、放热过程实 现制冷设备的制冷或制热，具体地，冷媒为二氟甲烷或丙烷，当然，冷媒也可以为其他冷媒。
根据本申请的第二方面，还提出了一种制冷设备，包括：如上述任一技术方案提出的压缩机。
本申请第二方面提供的制冷设备，因包括上述任一技术方案提出的压缩机，因此具有压缩机的全部有益效果。
具体地，制冷设备包括换热器，换热器与压缩机通过管道相连通，冷媒能够在管道中流动。
本申请的附加方面和优点将在下面的描述部分中变得明显，或通过本申请的实践了解到。
附图说明
本申请的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1示出了相关技术中的压缩机的结构示意图；
图2示出了相关技术中的压缩机的另一结构示意图。
其中，图1和图2中附图标记与部件名称之间的对应关系为：
100’压缩机，102’曲轴，1020’主轴部，1022’副轴部，1024’偏心部，104’主轴承，106’副轴承，108’气缸，110’转子，112’平衡块，114’活塞。
图3示出了本申请一个实施例的避让部为锥面的结构示意图；
图4示出了本申请一个实施例的避让部与最小油膜厚度之间的曲线关系图；
图5示出了本申请一个实施例的避让部为锥面的另一结构示意图；
图6示出了本申请一个实施例的避让部为曲面的结构示意图；
图7示出了本申请一个实施例的避让部为曲面的另一结构示意图；
图8示出了本申请一个具体实施例的压缩机的结构示意图；
图9示出了本申请另一个具体实施例的压缩机的结构示意图。
其中，图3至图9中附图标记与部件名称之间的对应关系为：
100压缩机，102曲轴，1020第一轴部，1022第二轴部，1024偏心部， 104连接结构，1040第一轴承，1042第二轴承，1044活塞，106避让部，108间隙，110气缸，112滑片，114转子，116平衡块。
具体实施方式
为了能够更清楚地理解本申请的上述目的、特征和优点，下面结合附图和具体实施方式对本申请进行进一步的详细描述。需要说明的是，在不冲突的情况下，本申请的实施例及实施例中的特征可以相互组合。
在下面的描述中阐述了很多具体细节以便于充分理解本申请，但是，本申请还可以采用其他不同于在此描述的其他方式来实施，因此，本申请的保护范围并不受下面公开的具体实施例的限制。
下面参照图3至图9描述根据本申请一些实施例所述的压缩机100和制冷设备。
实施例一：
如图3所示，根据本申请的一个实施例，本申请提出了一种压缩机100，包括：曲轴102和连接结构104。
具体地，连接结构104设置在曲轴102上；其中，连接结构104上和/或曲轴102上设置有避让部106，避让部106位于连接结构104与曲轴102相配合的部分，避让部106被配置为适于避让连接结构104和曲轴102中的至少一个。
本申请提供的压缩机100，包括曲轴102和与曲轴102相连接的连接结构104，其中，连接结构104上和/或曲轴102上设置有避让部106，避让部106用于避让连接结构104或曲轴102中的至少一个，避让部106的设置能够使得曲轴102与连接结构104之间的间隙108增大，进而在曲轴102发生倾斜变形时，避让部106能够对倾斜的曲轴102进行避让，以使得曲轴102与连接结构104的接触保持面接触，使得曲轴102与连接结构104之间的油膜不被破坏，从而有效保证压缩机100的可靠性，进而可以采用更细的轴径、更短的轴套，降低了压缩机100的体积以及成本，减少曲轴102与连接结构104配合部分的摩擦损失，从而提升压缩机100性能。
可以理解的是，避让部106避让连接结构104和曲轴102中的至少一个， 也即避让部106对曲轴102的倾斜变形进行避让，以保证曲轴102倾斜后，避让部106对应部分的曲轴102和连接结构104的接触为面接触。
具体地，未设置避让部106时，若曲轴102发生倾斜变形时，曲轴102与连接结构104之间的接触为线接触，局部油膜破裂，曲轴102与连接结构104直接发生金属接触从而容易导致磨损，在设置避让部106以后，若曲轴102发生倾斜变形时，曲轴102与连接结构104之间的接触仍然为面接触，保证了油膜的正常工作，从而降低了曲轴102与连接结构104之间的磨损程度，提升了压缩机100的可靠性。
具体地，基于避让部106设置在连接结构104上，避让部106的形状与相对应的倾斜后的曲轴102的外侧壁的形状相适配；基于避让部106设置在曲轴102上，曲轴102倾斜后，避让部106的形状与连接结构104的内侧壁的形状相适配。
具体地，避让部106设置在连接结构104的端部和/或设置在曲轴102对应连接结构104的端部的部分。
具体地，避让部106设置在连接结构104的端部的周向和/或设置在曲轴102对应连接机构的端部的部分的周向。
具体地，避让部106设置在连接结构104上时，至少部分避让部106位于连接结构104的内侧壁上。
实施例二：
如图3所示，根据本申请的一个实施例，包括上述实施例限定的特征，以及进一步地：曲轴102与连接结构104之间具有间隙108，沿曲轴102的轴线方向，避让部106对应的间隙108向远离连接结构104的中部方向增大。
在该实施例中，曲轴102与连接结构104之间具有间隙108，间隙108内能够供润滑油分布，其中，沿曲轴102的轴线方向，避让部106对应的间隙108向远离连接结构104的中部方向增大，从而在曲轴102发生倾斜变形时，逐渐增大的间隙108可对曲轴102形成避让空间，使得曲轴102与连接结构104之间的接触变为面接触，进而保证了油膜的正常工作，从而避免了曲轴102与连接结构104之间的磨损，提升了压缩机100的可靠性。
具体地，连接结构104可以分为两个端部以及设置在两个端部之间的中部。避让部106对应的间隙108沿远离连接结构104的中部的方向逐渐增大，以适应曲轴102倾斜变形时的形状。
具体地，当避让部106设置在连接结构104上时，避让部106设置在连接结构104的端部，在曲轴102的轴线方向上，沿远离连接结构104的中部的方向，避让部106向连接结构104的径向外侧倾斜设置；当避让部106设置在曲轴102上时，避让部106位于曲轴102对应连接结构104的端部的部分，在曲轴102的轴线方向上，沿远离连接结构104的中部的方向，避让部106向曲轴102的轴线方向倾斜。
实施例三：
根据本申请的一个实施例，包括上述实施例限定的特征，以及进一步地：压缩机100在曲轴102的轴线方向的截面中，在同一轴向高度上，将曲轴102的轴线两侧的间隙108之和定义为双边间隙108；避让部106对应的双边间隙108的最小值为δ 0，避让部106对应的双边间隙108的最大值与δ 0之差为δ，避让部106对应的双边间隙108最小的部分所对应的曲轴102的直径为D，沿曲轴102的轴线方向，避让部106的长度为h；其中，δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。
在该实施例中，避让部106由连接结构104的中部至端部方向逐渐增大，因此避让部106对应的双边间隙108具有最小值和最大值，避让部106对应的双边间隙108的最小值为δ 0，避让部106对应的双边间隙108的最大值与δ 0之差为δ，避让部106对应的双边间隙108最小的部分所对应的曲轴102的直径为D，沿曲轴102的轴线方向，避让部106的长度为h，避让部106对应的尺寸影响着曲轴102与连接结构104的摩擦改善的效果，因此，将δ与δ 0之商，与D与h之商的乘积，设置为大于等于0.2，且小于等于5，此时避让部106对曲轴102与连接结构104之间的摩擦的改善效果最好。
具体地，δ 0/2为避让部106对应的双边间隙108的一半，δ/2为避让部106对应的双边间隙108的最大值与δ 0之差的一半。
具体地，在同一轴向高度上，连接结构104的内侧壁的直径与曲轴102的直径之差为双边间隙108。
进一步地，δ与δ 0之商，与D与h之商的乘积，大于等于0.5，且小于等于2.5。
在该实施例中，δ与δ 0之商，与D与h之商的乘积，设置在大于等于0.5，且小于等于2.5之间时，对曲轴102与连接结构104之间的摩擦的改善效果较好。
具体地，如图4所示，图4为避让部106对应的尺寸对最小油膜厚度的影响曲线图，其中横轴采用了对数坐标，曲轴102与连接结构104之间的油膜承载能力可以用最小油膜厚度表征，最小油膜厚度越大，油膜承载能力越强，曲轴102与连接结构104之间越不容易发生磨损。
进一步地，h大于等于2mm，且小于等于20mm。
在该实施例中，避让部106的轴向高度h设置为2mm≤h≤20mm，更便于避让部106的加工，同时也利于降低曲轴102与连接结构104之间的磨损情况。
实施例四：
如图5和图7所示，根据本申请的一个实施例，包括上述实施例限定的特征，以及进一步地：避让部106包括多个避让段，沿曲轴102的轴线方向多个避让段依次相连接，其中，至少一个避让段满足δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。
在该实施例中，避让部106包括多个避让段，多个避让段沿轴向依次相连接，在多个避让段中至少有一个避让段的尺寸满足上述δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5的关系式。
可以理解的是，避让段满足：δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5的关系式，也就是避让段对应的双边间隙108的最小值为δ 0，避让段对应的双边间隙108的最大值与δ 0之差为δ，避让段对应的双边间隙108最小的部分所对应的曲轴102的直径为D，沿曲轴102的轴线方向，避让段的长度为h，避让段对应的δ、δ 0、D与h满足上述限定的关系式。
具体地，沿曲轴102的轴线方向，避让部106设置在连接结构104的端部，多个避让段的倾斜角度可以相同也可以不同，进一步地，多个避让段之间光滑连接。
实施例五：
如图3和图5所示，根据本申请的一个实施例，包括上述任一实施例限定的特征，以及进一步地：沿曲轴102的轴线方向，至少部分避让部106对应的间隙108的大小呈线性变化。
在该实施例中，沿曲轴102的轴线方向，至少部分避让部106对应的间隙108的大小呈线性变化，也就是压缩机100在曲轴102的轴线方向的截面中，沿曲轴102的轴线方向，由远离连接结构104的中部的方向，间隙108的径向大小呈正比例关系变化。
进一步地，避让部106所形成的壁面包括锥面。
在该实施例中，避让部106形成的壁面包括锥面，从而使曲轴102与连接结构104之间的间隙108沿轴向呈线性变化，同时也便于避让部106的加工。
实施例六：
如图6和图7所示，根据本申请的一个实施例，包括上述任一实施例限定的特征，以及进一步地：压缩机100在曲轴102的轴线方向的截面上，沿远离连接结构104的中部的方向，至少部分避让部106所形成的壁面的切线，与垂直于曲轴102的轴线的方向之间的锐角逐渐减小。
在该实施例中，在曲轴102的轴线方向上，沿远离连接结构104的中部的方向，至少部分避让部106形成的壁面的切线逐渐趋于水平，也即避让部106形成的壁面的切线与垂直于曲轴102的轴线方向的锐角逐渐减小，以使得避让部106与曲轴102的挠曲变形的形状更加匹配，从而进一步提升磨损改善效果。
具体地，朝远离连接结构104的中部的轴向方向，使避让部106对应的间隙108增大的速度逐渐加大。
进一步地，避让部106所形成的壁面包括曲面。
在该实施例中，避让部106形成的壁面包括曲面，使得避让部106对应的间隙108的变化与曲轴102的挠曲变形的形状更加匹配，从而进一步提升磨损改善效果。
如图3所示，避让部106设置在曲轴102上，避让部106通过曲轴102 的直径的变化实现，也就是使得曲轴102设置避让部106后的直径变小，在避让部106处曲轴102形成锥形，使得设置避让部106的部分，曲轴102与连接结构104之间的间隙108沿轴向线性变化。
如图5所示，避让部106设置在连接结构104上，避让部106通过连接结构104的直径变化实现，也就是使连接结构104的内侧壁设置避让部106后的直径变大，在避让部106处连接结构104的内侧壁形成锥形，使得设置避让部106的部分，曲轴102与连接结构104之间的间隙108沿轴向线性变化。
如图6和图7所示，在曲轴102的挠曲变形较大时，为了进一步提升磨损改善效果，可以将避让部106设置为曲面，朝远离运动副中心(远离连接结构104的中部)的轴向方向，使避让部106对应的间隙108增大的速度逐渐加大，也就是使得避让部106的切线与曲轴102的轴线之间逐渐趋于平行，可以使避让部106对应的间隙108变化与曲轴102的挠曲变形形状更加匹配，从而进一步提升磨损改善效果。
具体地，也可以同时在曲轴102和连接结构104上设置避让部106。避让部106形成的壁面中包括锥面和曲面。
实施例七：
根据本申请的一个实施例，包括上述任一实施例限定的特征，以及进一步地：在垂直于曲轴102的轴线的截面上，避让部106呈环形。
在该实施例中，避让部106呈环形，环形的避让部106能够在曲轴102发生倾斜形变时对曲轴102的各个方向均产生很好的避让效果，进而在各个方向均能提升曲轴102与连接结构104之间的磨损的改善效果，也即在各个方向均能减轻磨损程度。
实施例八：
如图8和图9所示，根据本申请的一个实施例，包括上述任一实施例限定的特征，以及进一步地：曲轴102包括：主体，主体包括同轴设置的第一轴部1020和第二轴部1022；偏心部1024，与主体相连接，主体与偏心部1024偏心设置。
在该实施例中，曲轴102包括主体与偏心部1024，主体包括第一轴部 1020和第二轴部1022，第一轴部1020与电机的转子114相连接从而带动偏心部1024转动，偏心部1024转动实现压缩机100的吸气排气过程。
进一步地，连接结构104包括：第一轴承1040，套设在第一轴部1020上；第二轴承1042，套设在第二轴部1022上；活塞1044，套设在偏心部1024上。
在该实施例中，连接结构104包括第一轴承1040、第二轴承1042和活塞1044，第一轴承1040套设在第一轴部1020上，第二轴承1042套设在第二轴部1022上，通过第一轴承1040和第二轴承1042实现对曲轴102的固定，活塞1044套设在偏心部1024上，通过偏心部1024转动带动活塞1044运动，进而实现压缩机100的吸气和排气过程。
进一步地，基于避让部106设置在曲轴102上，避让部106设置在第一轴部1020靠近第二轴部1022的部分和/或避让部106设置在第一轴部1020远离第二轴部1022的部分，和/或避让部106设置在偏心部1024靠近第一轴承1040的一端和/或避让部106设置在偏心部1024靠近第二轴承1042的一端，和/或避让部106设置在第二轴部1022靠近偏心部1024的一端。
在该实施例中，当避让部106设置在曲轴102上时，避让部106设置在第一轴部1020靠近第二轴部1022的部分、第一轴部1020远离第二轴部1022的部分、偏心部1024靠近第一轴承1040的一端，偏心部1024靠近第二轴承1042的一端、第二轴部1022靠近偏心部1024的一端中的任一个或其组合上。
进一步地，基于避让部106设置在连接结构104上，避让部106设置在第一轴承1040靠近第二轴承1042的一端和/或避让部106设置在第一轴承1040远离第二轴承1042的一端，和/或避让部106设置在活塞1044靠近第一轴承1040的一端和/或避让部106设置在活塞1044靠近第二轴承1042的一端，和/或避让部106设置在第二轴承1042靠近第一轴承1040的一端。
在该实施例中，当避让部106设置在连接结构104上时，避让部106设置在第一轴承1040靠近第二轴承1042的一端、第一轴承1040远离第二轴承1042的一端、活塞1044靠近第一轴承1040的一端、活塞1044靠近第二轴承1042的一端、第二轴承1042靠近第一轴承1040的一端中的任一 个或其组合上。
当然，避让部106还能够同时设置在连接结构104和曲轴102上。
进一步地，压缩机100还包括：气缸110，气缸110包括气缸腔，活塞1044设于气缸腔内，曲轴102穿设在气缸腔内，气缸110上设置有滑片112槽；滑片112，设置在滑片112槽内，与活塞1044滚动连接；转子114，与第一轴部1020相连接。
在该实施例中，压缩机100还包括气缸110、滑片112和转子114，转子114与第一轴部1020相连接，气缸110具有气缸腔，活塞1044设置在气缸腔内，且曲轴102穿设在气缸腔内。其中，气缸110上还设置有滑片112槽，滑片112设置在滑片112槽内，且与活塞1044转动连接，从而实现压缩机100的吸气排气过程。
进一步地，压缩机100为变频压缩机。
在该实施例中，压缩机100为变频压缩机，通过在连接结构104上或曲轴102上设置避让部106能够提高变频压缩机的可靠性，当然压缩机100也可以为定速压缩机。
进一步地，压缩机100内充注有冷媒，冷媒为二氟甲烷或丙烷。
在该实施例中，压缩机100内充注有冷媒，通过冷媒的吸热、放热过程实现制冷设备的制冷或制热，具体地，冷媒为二氟甲烷或丙烷，当然，冷媒也可以为其他冷媒。
实施例九：
根据本申请的一个具体实施例，如图8和图9所示，压缩机100包括曲轴102、第一轴承1040、第二轴承1042、气缸110、活塞1044、滑片112、设置在转子114上的平衡块116等部件，上述部件形成吸气腔和压缩腔，电机的转子114带动曲轴102旋转，使吸气腔容积增大，压缩腔容积减小，实现吸排气过程。曲轴102包括第一轴部1020、第二轴部1022和偏心部1024，第一轴部1020与第一轴承1040、第二轴部1022与第二轴承1042，偏心部1024与活塞1044分别形成了三个滑动轴承，滑动轴承的轴部(第一轴部1020、第二轴部1022或偏心轴)与连接结构104(第一轴承1040、第二轴承1042或活塞1044)之间存在间隙108，正常运行时充满润滑油。 上述三个滑动轴承经常发生异常磨损。具体地，由于转子114旋转过程中产生的离心力以及电机本身的磁拉力作用，转子114的中心会偏离电机轴线从而发生偏摆，相应地，曲轴102上端发生挠曲变形，造成曲轴102的第一轴部1020与第一轴承1040上端形成线接触，局部油膜破裂，曲轴102的第一轴部1020与第一轴承1040直接发生金属接触并导致磨损。类似地，曲轴102的偏心轴受到吸气腔及压缩腔气体力作用也会发生挠曲变形，使得第一轴部1020与第一轴承1040下边缘、第二轴部1022与第二轴承1042上边缘、偏心轴与活塞1044上下边缘均可能直接发生金属接触并导致异常磨损。因此，由于曲轴102的倾斜变形，各滑动轴承边缘难以建立正常的油膜，从而形成局部金属接触并导致磨损。如图3所示，本申请提出的实施例中，在连接结构104或曲轴102与连接结构104相配合的部分设置有避让部106，连接结构104与曲轴102之间具有间隙108，避让部106对应的连接结构104和曲轴102部分的间隙108朝远离运动副中心的轴向方向增大，从而使得曲轴102发生挠曲变形之后原金属接触部位仍能保持面接触，建立正常的油膜，从而避免磨损，大大提高压缩机100可靠性。
具体地，可在曲轴102上或连接结构104上通过车削等方式去掉一部分，以形成避让部106，或将曲轴102与设置在曲轴102上的避让部106一体制造而成，或将连接结构104与设置在连接结构104上的避让部106一体制造而成。
具体地，避让部106对应的双边间隙108的最小值为δ 0，避让部106对应的双边间隙108的最大值与δ 0之差为δ，避让部106对应的双边间隙108最小的部分所对应的曲轴102的直径为D，沿曲轴102的轴线方向，避让部106的长度为h，δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。如图4所示，为滑动轴承避让部106的尺寸对最小油膜厚度的影响曲线图，其中横轴采用了对数坐标，滑动轴承的油膜承载能力可以用最小油膜厚度表征，最小油膜厚度越大，油膜承载能力越强，滑动轴承越不容易发生磨损，由图4可见，避让部106的尺寸满足：δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5时，磨损改善的效果最好。
进一步地，δ与δ 0之商，与D与h之商的乘积，大于等于0.5，且小于等于2.5，h大于等于2mm，且小于等于20mm。
实施例十：
如图8所示，根据本申请的一个具体实施例，本申请提出的压缩机100包括曲轴102和连接结构104，曲轴102包括第一轴部1020、第二轴部1022和偏心部1024，连接结构104包括第一轴承1040、第二轴承1042和活塞1044，第一轴承1040套设在第一轴部1020上，第二轴承1042套设在第二轴部1022上，活塞1044套设在偏心部1024上。在本实施例中，避让部106设置在曲轴102上，具体地，第一轴部1020对应第一轴承1040的上端和下端的部分、第二轴部1022对应第二轴承1042的上端的部分，和偏心轴对应活塞1044的上端和下端的部分均设置了避让部106，避让部106的形状呈锥面，任一避让部106的具体尺寸均分别满足：δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。其中，图8中的h1、h2、h3、h4、h5分别为避让部106的轴向高度。
实施例十一：
如图9所示，根据本申请的一个具体实施例，本申请提出的压缩机100包括曲轴102和连接结构104，曲轴102包括第一轴部1020、第二轴部1022和偏心部1024，连接结构104包括第一轴承1040、第二轴承1042和活塞1044，第一轴承1040套设在第一轴部1020上，第二轴承1042套设在第二轴部1022上，活塞1044套设在偏心部1024上。在本实施例中，避让部106设置在连接结构104上，具体地，避让部106设置在第一轴承1040的上端和下端，第二轴承1042的上端，活塞1044的上端和下端，避让部106的形状呈曲面，任一避让部106的具体尺寸均分别满足：δ与δ 0之商，与D与h之商的乘积，大于等于0.2，且小于等于5。其中，图9中的h1、h2、h3、h4、h5分别为避让部106的轴向高度。
实施例十二：
根据本申请的第二方面，还提出了一种制冷设备，包括：如上述任一实施例提出的压缩机100。
本申请第二方面提供的制冷设备，因包括上述任一实施例提出的压缩 机100，因此具有压缩机100的全部有益效果。
具体地，制冷设备包括换热器，换热器与压缩机100通过管道相连通，冷媒能够在管道中流动。
在本申请中，术语“多个”则指两个或两个以上，除非另有明确的限定。术语“安装”、“相连”、“连接”、“固定”等均应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或一体地连接；“相连”可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本说明书的描述中，术语“一个实施例”、“一些实施例”、“具体实施例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或实例。而且，描述的具体特征、结构、材料或特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
以上所述仅为本申请的优选实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (17)

  1. 一种压缩机，其中，包括：
    曲轴；
    连接结构，设置在所述曲轴上；
    其中，所述连接结构上和/或所述曲轴上设置有避让部，所述避让部位于所述连接结构与所述曲轴相配合的部分，所述避让部被配置为适于避让所述连接结构和所述曲轴中的至少一个。
  2. 根据权利要求1所述的压缩机，其中，
    所述曲轴与所述连接结构之间具有间隙，沿所述曲轴的轴线方向，所述避让部对应的所述间隙向远离所述连接结构的中部方向增大。
  3. 根据权利要求2所述的压缩机，其中，
    所述压缩机在所述曲轴的轴线方向的截面中，在同一轴向高度上，将所述曲轴的轴线两侧的所述间隙之和定义为双边间隙；
    所述避让部对应的所述双边间隙的最小值为δ 0，所述避让部对应的所述双边间隙的最大值与所述δ 0之差为δ，所述避让部对应的所述双边间隙最小的部分所对应的所述曲轴的直径为D，沿所述曲轴的轴线方向，所述避让部的长度为h；
    其中，所述δ与所述δ 0之商，与所述D与所述h之商的乘积，大于等于0.2，且小于等于5。
  4. 根据权利要求3所述的压缩机，其中，
    所述避让部包括多个避让段，沿所述曲轴的轴线方向多个所述避让段依次相连接，其中，至少一个所述避让段满足所述δ与所述δ 0之商，与所述D与所述h之商的乘积，大于等于0.2，且小于等于5。
  5. 根据权利要求3所述的压缩机，其中，
    所述δ与所述δ 0之商，与所述D与所述h之商的乘积，大于等于0.5，且小于等于2.5。
  6. 根据权利要求3所述的压缩机，其中，
    所述h大于等于2mm，且小于等于20mm。
  7. 根据权利要求2至6中任一项所述的压缩机，其中，
    沿所述曲轴的轴线方向，至少部分所述避让部对应的所述间隙的大小呈线性变化。
  8. 根据权利要求7所述的压缩机，其中，
    所述避让部所形成的壁面包括锥面。
  9. 根据权利要求1至6中任一项所述的压缩机，其中，
    所述压缩机在所述曲轴的轴线方向的截面上，沿远离所述连接结构的中部的方向，至少部分所述避让部所形成的壁面的切线，与垂直于所述曲轴的轴线的方向之间的锐角逐渐减小。
  10. 根据权利要求9所述的压缩机，其中，
    所述避让部所形成的壁面包括曲面。
  11. 根据权利要求1至6中任一项所述的压缩机，其中，
    在垂直于所述曲轴的轴线的截面上，所述避让部呈环形。
  12. 根据权利要求1至6中任一项所述的压缩机，其中，所述曲轴包括：
    主体，所述主体包括同轴设置的第一轴部和第二轴部；
    偏心部，与所述主体相连接，所述主体与所述偏心部偏心设置。
  13. 根据权利要求12所述的压缩机，其中，所述连接结构包括：
    第一轴承，套设在所述第一轴部上；
    第二轴承，套设在所述第二轴部上；
    活塞，套设在所述偏心部上。
  14. 根据权利要求13所述的压缩机，其中，
    基于所述避让部设置在所述曲轴上，所述避让部设置在所述第一轴部靠近所述第二轴部的部分和/或所述避让部设置在所述第一轴部远离所述第二轴部的部分，和/或所述避让部设置在所述偏心部靠近所述第一轴承的一端和/或所述避让部设置在所述偏心部靠近所述第二轴承的一端，和/或所述避让部设置在所述第二轴部靠近所述偏心部的一端；和/或
    基于所述避让部设置在所述连接结构上，所述避让部设置在所述第一轴承靠近所述第二轴承的一端和/或所述避让部设置在所述第一轴承远离所述第二轴承的一端，和/或所述避让部设置在所述活塞靠近所述第一轴承的一端和/或 所述避让部设置在所述活塞靠近所述第二轴承的一端，和/或所述避让部设置在所述第二轴承靠近所述第一轴承的一端。
  15. 根据权利要求13所述的压缩机，其中，所述压缩机还包括：
    气缸，所述气缸包括气缸腔，所述活塞设于所述气缸腔内，所述曲轴穿设在所述气缸腔内，所述气缸上设置有滑片槽；
    滑片，设置在所述滑片槽内，与所述活塞滚动连接；
    转子，与所述第一轴部相连接。
  16. 根据权利要求1至6中任一项所述的压缩机，其中，
    所述压缩机为变频压缩机；和/或
    所述压缩机内充注有冷媒，所述冷媒为二氟甲烷或丙烷。
  17. 一种制冷设备，其中，包括：
    如权利要求1至16中任一项所述的压缩机。
PCT/CN2020/099160 2019-11-29 2020-06-30 压缩机和制冷设备 WO2021103525A1 (zh)

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