WO2021098423A1 - 曲轴、压缩机及制冷设备 - Google Patents

曲轴、压缩机及制冷设备 Download PDF

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Publication number
WO2021098423A1
WO2021098423A1 PCT/CN2020/121597 CN2020121597W WO2021098423A1 WO 2021098423 A1 WO2021098423 A1 WO 2021098423A1 CN 2020121597 W CN2020121597 W CN 2020121597W WO 2021098423 A1 WO2021098423 A1 WO 2021098423A1
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WO
WIPO (PCT)
Prior art keywords
shaft
crank arm
oil passage
oil
axis
Prior art date
Application number
PCT/CN2020/121597
Other languages
English (en)
French (fr)
Inventor
王诚诚
Original Assignee
安徽美芝制冷设备有限公司
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 安徽美芝制冷设备有限公司 filed Critical 安徽美芝制冷设备有限公司
Priority to JP2022523350A priority Critical patent/JP7379693B2/ja
Priority to EP20889731.4A priority patent/EP4027013B1/en
Publication of WO2021098423A1 publication Critical patent/WO2021098423A1/zh

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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
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B39/02—Lubrication
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F25B31/002—Lubrication

Definitions

  • This application belongs to the technical field of refrigeration equipment, and specifically relates to a crankshaft, a compressor, and a refrigeration equipment.
  • the fixed-speed reciprocating compressor generally adopts casting molding.
  • the crankshaft In order to meet the needs of different reciprocating compressor displacement, the crankshaft needs to have different eccentricity and shaft diameter, but when planning the crankshaft with different eccentricity and shaft diameter, it is necessary to reopen the mold, resulting in low standardization and universality of the mold for casting crankshafts. Poor performance, increasing manufacturing costs.
  • the casted crankshaft needs to process the oil supply channel on the outer surface, which is complicated to process and has poor oiling effect.
  • This application aims to solve one of the technical problems existing in the prior art or related technologies.
  • the first aspect of this application proposes a crankshaft.
  • the second aspect of the application proposes a compressor.
  • the third aspect of the application proposes a refrigeration equipment.
  • an embodiment according to the first aspect of the present application proposes a crankshaft, which includes: a first shaft, a second shaft, a first crank arm, a second crank arm, and a recess; the first crank arm is arranged at the first One end of the shaft, the first crank arm is provided with a first oil passage, the first oil passage penetrates the first shaft; the second crank arm is provided at one end of the second shaft, the second crank arm is provided with a second oil passage, The two oil passages penetrate the second shaft; the recess is provided on the end surface of the first crank arm away from the first shaft or on the end surface of the second crank arm away from the second shaft, and the second crank arm is used to connect with the first crank arm , So that the recessed portion communicates with the first oil passage and the second oil passage.
  • the crankshaft provided by the embodiment of the present application includes a first shaft, a first crank arm, a second shaft, and a second crank arm.
  • a first oil passage is provided on the first crank arm and allowing the first oil passage to penetrate the first shaft,
  • a second oil passage is provided on the second crank arm, and the second oil passage penetrates the second shaft, so that after the second crank arm is connected with the first crank arm, the first oil passage is connected with the second oil passage, which realizes The lubricating oil enters the second oil passage to supply oil through the first oil passage.
  • a recessed part is formed between the first oil passage and the second oil passage,
  • the second shaft is eccentrically arranged with respect to the axis of the first shaft, the recessed part can communicate with the first oil passages that are displaced from each other. And the second oil passage, it is more convenient for lubricating oil to enter the second oil passage through the first oil passage, and the oil supply effect is improved.
  • the second crank arm is used to connect with the first crank arm, that is, the first crank arm and the second crank arm are independent of each other and subsequently assembled together, which facilitates the eccentric arrangement of the second shaft relative to the axis of the first shaft.
  • the eccentricity can be adjusted according to the actual displacement requirements of the compressor, and the relative position of the second shaft and the first shaft can be adjusted, so that the crankshaft can adapt to the displacement requirements of different compressors, such as fixing the first shaft and the first crank arm, The second crank arm and the second shaft are moved in the eccentric direction to obtain crankshafts with different eccentric amounts.
  • crankshaft in the above technical solution provided by this application may also have the following additional technical features:
  • the recessed portion is provided on the end surface of the first crank arm away from the first shaft, and the first oil passage penetrates part of the bottom wall of the recessed portion.
  • the recessed portion is specifically arranged on the end surface of the first crank arm away from the first shaft, and the first oil passage penetrates part of the bottom wall of the recessed portion.
  • the first oil passage and the recessed portion are fully Communication, on the other hand, can store oil through the part of the recessed part that is not penetrated, and supply oil to the second oil passage to improve the lubrication effect.
  • the recess is provided on the end surface of the second crank arm away from the second shaft, and the second oil passage penetrates part of the bottom wall of the recess.
  • the recessed portion is specifically arranged on the end surface of the second crank arm away from the second shaft, and the second oil passage penetrates part of the bottom wall of the recessed portion.
  • the second oil passage and the recessed portion are fully Communication, on the other hand, can store oil through the part of the recessed part that is not penetrated, and supply oil to the second oil passage to improve the lubrication effect.
  • the second shaft is eccentrically arranged in the first direction relative to the axis of the first shaft, and the recessed portion extends at least partially in the first direction.
  • the second shaft is eccentrically arranged in the first direction relative to the axis of the first shaft, that is, the axis of the second shaft is parallel to the axis of the first shaft and is spaced along the first direction.
  • the recessed portion is set to extend at least partially along the first direction, which facilitates the lubricating oil in the first oil passage to enter the second oil passage through the recessed portion, facilitates the supply of oil into the second oil passage, and improves the lubrication effect.
  • the opening of the recess is an ellipse, and the center of the ellipse is eccentrically arranged with respect to the axis of the first shaft in the first direction.
  • the opening of the recessed portion is specifically designed to be elliptical, and the recessed portion may have an elliptical sinking platform structure at this time.
  • the opening of the recessed portion may also be elongated or circular, etc., and is not limited to an elliptical shape.
  • the short axis of the ellipse extends in the first direction
  • the long axis of the ellipse corresponds to two short arc segments; among the two short arc segments located on the first crank arm, there is one short arc The segment is used to extend to the area where the second oil passage is located, or among the two short arc segments located on the second crank arm, there is a short arc segment to extend to the area where the first oil passage is located.
  • the short axis of the ellipse is extended in the first direction, and there is a short circle in the two short arc segments corresponding to the long axis.
  • the arc section extends to the area where the second oil passage is located, that is, the recessed portion can be at least partially connected to the second oil passage and directly communicates.
  • the oil can be stored through the recessed portion in the short axis direction.
  • the arc segment extends to the area where the second oil passage is located, facilitating oil supply to the second oil passage.
  • the short axis of the ellipse is extended in the first direction, and one of the two short arc segments corresponding to the long axis extends to The area where the first oil passage is located, that is, the recessed portion can be at least partially connected to the first oil passage, and directly communicates.
  • the oil can be stored through the recessed portion in the minor axis direction, and on the other hand, due to the extension of the short arc section To the area where the first oil passage is located, it is convenient for the first oil passage to supply oil into the second oil passage through the recessed portion.
  • the designed short arc segment can extend to the area where the second oil passage or the first oil passage is located under any eccentric condition of the crankshaft, so that the recessed portion is connected with the second oil passage or the first oil passage.
  • the first crank arm is integrally formed with the first shaft.
  • the second crank arm and the second shaft are integrally formed.
  • the first crank arm and the second crank arm are connected together.
  • first crank arm can also be welded to the first shaft
  • second crank arm can also be welded to the second shaft
  • the first crank arm and the first shaft are integrally forged and formed; and/or the second crank arm and the second shaft are integrally forged and formed.
  • the molding is simple, the processing and manufacturing technology is mature, the production efficiency and the material utilization rate are high, and the cost can be reduced while the quality of the crankshaft parts is guaranteed.
  • the first crank arm with a certain accuracy can be quickly realized.
  • the first shaft of the oil passage, the second crank arm and the second shaft with the second oil passage can directly forge the oil passage to improve production efficiency.
  • a set of forging dies can meet the needs of crankshafts with different eccentric amounts, making the dies have very good versatility, reducing development costs and manufacturing costs. In addition, it also avoids the environmental pollution caused by the metal casting hot forming process and the massive consumption of energy.
  • first crank arm and the first shaft can also be integrally formed by turning
  • second crank arm and the second shaft can also be integrally formed by turning
  • first crank arm and the second crank arm are welded together by resistance welding.
  • the first crank arm and the second crank arm are connected together by resistance welding. Because resistance welding can energize the welding band into the side of the first crank arm facing the second crank arm, the connection is convenient It is firm and will not cause the second crank arm to warp relative to the first crank arm, and it is convenient for the second crank arm to be firmly set in the proper position of the first crank arm, thereby adjusting the eccentricity of the second shaft relative to the first shaft .
  • the welding of the second crank arm needs to be able to be welded to the first crank arm under all eccentric conditions of the crankshaft, so as to ensure the versatility of the crankshaft components.
  • the end of the second crank arm away from the second shaft is provided with a welding band, and the welding band is used to surround the outer circumference of the recess; the second crank arm is welded to the first crank arm by resistance welding with the welding band.
  • the recess is provided on the first crank arm and the opening of the recess is elliptical, of the two short arc segments corresponding to the long axis of the ellipse, one short arc segment is used to extend to In the area where the second oil passage is located, another short arc segment and two long arc segments corresponding to the short axis of the ellipse surround the opening of the first oil passage, and are located inside the welding belt at any eccentric position.
  • first crank arm and the second crank arm are welded together by laser welding.
  • the connection is convenient and firm.
  • the wall thicknesses of the first oil passage are not completely the same.
  • the wall thickness of the first oil passage is not exactly the same, that is, there is a relatively thin wall between the outer surface of the first shaft
  • the cross-section of the first oil passage is not a circular hole, but a triangular hole, an oval hole or a gourd-shaped hole, etc., or the cross-section of the first oil passage is a circular hole, but its center Deviate from the axis of the first shaft.
  • the centrifugal force generated is not exactly the same, so that the lubricating oil can pass through the thinner wall under the action of centrifugal force.
  • the oil enters the first oil passage and the second oil passage for lubrication.
  • the oiling effect is good and the lubricating effect is good.
  • the diameter of the crankshaft is designed to be larger, so that the diameter of the oil passage can be made larger to ensure sufficient centrifugal force to ensure the oil capacity. While increasing the amount of oil on the crankshaft and ensuring the structural strength, a small-volume crankshaft is realized.
  • the first oil passage has an axisymmetric structure.
  • the first oil passage by designing the first oil passage to have an axisymmetric structure on any cross section of the first axis, such as an ellipse, a cross pattern, etc., the first oil passage can be conveniently processed while ensuring the upper The amount of oil.
  • the first oil passage has an axially symmetric special-shaped hole structure. It can ensure that the wall thickness of the first oil passage has a large variation range, thereby ensuring that the first shaft can generate sufficient centrifugal force to guide the lubricating oil to oil.
  • the first oil passage on any cross section of the first shaft, has a circular hole structure, and the center of the circular hole structure is deviated from the axis of the first shaft. Any cross section of the first oil passage is set in a round hole shape, which is convenient for processing.
  • the first oil passage has a thin-walled section and a thick-walled section; the second shaft is arranged eccentrically with respect to the axis of the first shaft in a direction away from the thin-walled section.
  • the design has a thin-walled section and a thick-walled section on any cross-section of the first shaft, wherein the thin-walled section is the thinnest section by default, and the thick-walled section is the thickest-walled section. That is, the thickness of any thin-walled section is less than the thickness of any thick-walled section.
  • the number of thin-walled sections can be one or multiple, and the number of thick-walled sections can be one or multiple.
  • the second shaft and the thin-walled section are not located in the same orientation of the axis of the first shaft, which can avoid the problems caused by the second shaft.
  • Centrifugal force affects the thin-walled section of the first shaft, avoids rupture and damage of the thin-walled section, and ensures the structural strength of the thin-walled section, thereby further achieving a small-volume crankshaft with a higher oil volume.
  • the central angle of the second shaft and the thin-walled section relative to the axis of the first shaft is greater than or equal to 90°.
  • the central angle of the second shaft and the thin-walled section relative to the axis of the first shaft is greater than or equal to 90°, that is, the second shaft and the thin-walled section are in any cross section of the first shaft.
  • the orthographic projection on the center angle corresponding to the axis of the first axis is at least 90°.
  • the central angle of the second shaft and the thin-walled section relative to the axis of the first shaft is 90°, so that the thin-walled section is perpendicular to the direction of movement of the piston of the reciprocating compressor.
  • the central angle of the second shaft and the thin-walled section relative to the axis of the first shaft may also be 120° or 180°. It can be determined according to the thickness and position of the thin-walled section.
  • the inner contour of the thin-walled section is a first circular arc
  • the inner contour of the thick-walled section is a second circular arc
  • the opening directions of the first circular arc and the second circular arc face the axis of the first shaft.
  • the inner contour of the thin-walled section is the first arc
  • the inner contour of the thick-walled section is the second arc
  • the first oil passage has a larger space, which facilitates more lubricating oil to enter the first oil passage and improves the lubrication effect. It is also convenient for the processing of the first oil passage.
  • the wall thickness of the thin-walled section is greater than or equal to 0.3mm; and/or the arc length of the first arc ranges from 3mm to 5mm; and/or the radius corresponding to the first arc is the same as that of the second arc.
  • the range of the difference of the radius corresponding to the arc is 0mm to 2mm.
  • the wall thickness of the thin-walled section is made greater than or equal to 0.3 mm, such as 0.4 mm to 0.5 mm, it is ensured that the thin-walled section has sufficient structural strength.
  • the arc length of the first arc is made greater than 0 mm, such as between 3 mm and 5 mm, it is ensured that the thin-walled section has a sufficient amount of oil.
  • the first oil is a circular hole structure, and is eccentrically arranged with respect to the axis of the first shaft, so that sufficient centrifugal force can be generated during the rotation of the first shaft to guide the lubricating oil to oil.
  • the first oil passage further has a transition section connecting the thin-walled section and the thick-walled section. Further, the inner contour of the transition section has a first straight line.
  • it is set on any cross section of the first shaft, with a transition section to connect the thin-walled section and the thick-walled section, which can buffer the thickness change of the first shaft and improve the structural strength of the first shaft .
  • the transition section includes a first straight line, such as being tangent to the first arc and the second arc, or of course it may not be tangent; the transition section may also include a fifth arc through which the first straight line passes The fifth arc connects the first arc and the second arc.
  • the first tangent is made at the intersection of the first arc and the first straight line
  • the second tangent is made at the intersection of the second arc and the first straight line
  • the first tangent faces the second tangent.
  • the angle inside the first shaft is greater than 90°. Ensure that there is enough space inside the first oil passage to ensure the amount of oil.
  • the included angle between the first tangent line and the second tangent line facing the inside of the first shaft may also be less than 90°.
  • the inner contour of the thin-walled section is a third circular arc
  • the inner contour of the thick-walled section is a fourth circular arc
  • the opening direction of the third circular arc and the fourth circular arc faces the axis of the first shaft, The other opening direction is away from the axis of the first shaft.
  • the outer contour of the welding band is the same shape as the outer contour of the second crank arm; and/or the cross-section of the welding band is trapezoidal or wedge-shaped.
  • the second crank arm by setting the outer contour of the welding band to be the same shape as the outer contour of the second crank arm, it is convenient for the second crank arm to be tightly connected to the first crank arm without the second crank arm relative to The first crank arm is partially tilted.
  • the welding belt is located at the edge of the second crank arm and connected with the edge of the second crank arm with a rounded corner, or the welding belt is at a certain distance from the edge of the second crank arm, wherein the welding belt surrounds one end of the fourth oil passage by default Open up.
  • the cross section of the welding belt a trapezoid or wedge shape
  • the side of the welding belt facing the axis of the second shaft is set in an outward wedge shape, which facilitates energization and melting into the side of the first crank arm close to the second crank arm , The first crank arm and the second crank arm are firmly connected.
  • the width of the end surface of the welding belt facing the first crank arm is greater than or equal to 0.2 mm.
  • the width of the end face of the welding band facing the first crank arm not less than 0.2 mm, such as 0.5 mm to 0.8 mm, it is ensured that the welding band can firmly connect the first crank arm and the second crank arm.
  • an end of the first crank arm close to the first shaft is provided with a boss.
  • a boss is formed at one end of the first crank arm close to the first shaft, which facilitates the installation and positioning of the washer, thereby facilitating the placement of the bearing in the compressor, and ensuring the perpendicularity of the bearing to the first shaft.
  • the boss and the groove are opposed to each other, and the inner surface of the groove also has a circular arc surface, and may also have an edge.
  • the height of the boss is greater than 0.5 mm; and/or the depth of the groove is less than or equal to 0.8 mm.
  • the height of the boss may be 1 mm, 2 mm, etc., and the depth of the groove may be between 0.2 mm and 0.4 mm. So that the boss has enough structural strength to support the bearing and the rotor, and the groove can ensure the precision grinding of the first shaft.
  • a first oil hole is provided on the first shaft, and the first oil hole communicates with the first oil passage;
  • a second oil hole is provided on the second shaft, and the second oil hole is connected with the second oil passage through.
  • the first oil hole communicating with the first oil passage is provided on the first shaft, and the second oil hole communicating with the second oil passage is provided on the second shaft, so that the lubricating oil can pass through The first oil hole and the second oil hole flow out to lubricate the compressor rotor and other structures.
  • the number of the first oil hole is one or at least two; the number of the second oil hole is one or at least two.
  • the diameter of the first oil hole is greater than or equal to 1.5 mm; the diameter of the second oil hole is greater than or equal to 1.5 mm. Such as 2mm to 4mm. Ensure that the lubricating oil flows out smoothly.
  • the first shaft and the second shaft are both low carbon steel shafts or alloy steel shafts. Such as low-carbon alloy steel, with high structural strength and wear resistance.
  • the embodiment of the second aspect of the present application proposes a compressor, including: a crankshaft as in any one of the above technical solutions.
  • the compressor further includes: a housing, a motor, a bearing, and a piston.
  • the bottom of the shell has an oil pool; the motor is arranged in the shell, and the rotor of the motor is sleeved on the first shaft; the bearing is sleeved on the first shaft and is located between the rotor and the first crank arm; One end is connected, and the other end of the connecting rod is connected with the second shaft.
  • the first shaft can extend into the oil sump, so that the lubricating oil enters the second shaft through the first shaft to realize the lubrication of the crankshaft, thereby realizing the lubrication of the rotor and connecting rod, improving the lubrication effect of the compressor and reducing wear , Improve the service life of the compressor.
  • the diameter of the boss of the crankshaft is larger than the diameter of the raceway of the bearing, such as 1mm to 2mm larger, which helps to stably support the bearing and avoid the bearing from moving greatly.
  • a chamfer is provided at one end of the first shaft away from the second shaft, and the width of the chamfer is smaller than the wall thickness of any part of the first oil passage, so as to guide the rotor to be installed on the first shaft.
  • An embodiment of the third aspect of the present application proposes a refrigeration device, including: a compressor as in any one of the above technical solutions.
  • the refrigeration equipment further includes a condenser, a pressure reducing member, and an evaporator.
  • the outlet of the compressor is communicated with the inlet of the condenser; the inlet of the pressure reducing element is communicated with the outlet of the condenser; the inlet of the evaporator is communicated with the outlet of the pressure reducing element, and the outlet of the evaporator is communicated with the inlet of the compressor.
  • Fig. 1 shows a schematic cross-sectional view of a crankshaft according to an embodiment of the present application
  • Figure 2 shows a cross-sectional view in the direction of A-A in Figure 1;
  • FIG. 3 shows a schematic diagram of the structure of the first shaft and the first crank arm of an embodiment of the present application
  • FIG. 4 shows another structural schematic diagram of the first shaft and the first crank arm of an embodiment of the present application
  • FIG. 5 shows another structural schematic diagram of the first shaft and the first crank arm of an embodiment of the present application
  • Fig. 6 shows a schematic structural view of the second shaft and the second crank arm of an embodiment of the present application
  • FIG. 7 shows another structural schematic diagram of the second shaft and the second crank arm of an embodiment of the present application.
  • Fig. 8 shows another structural schematic diagram of the second shaft and the second crank arm of an embodiment of the present application.
  • crankshaft 110 first shaft, 111 first oil passage, 112 thin section, 113 thick section, 114 transition section, 115 first oil hole, 120 first crank arm, 121 recess, 122 boss, 130 Two shafts, 131 second oil passage, 132 second oil hole, 140 second crank arm, 141 welding belt.
  • crankshaft 100 according to some embodiments of the present application will be described with reference to FIGS. 1 to 8.
  • a crankshaft 100 includes: a first shaft 110, a second shaft 130, a first crank arm 120, a second crank arm 140, and a recess 121; the first crank arm 120 is arranged on the first shaft 110 One end of the first crank arm 120 is provided with a first oil passage 111, and the first oil passage 111 penetrates the first shaft 110; the second crank arm 140 is provided at one end of the second shaft 130, and the second crank arm 140 is provided with The second oil passage 131, the second oil passage 131 penetrates the second shaft 130; the recess 121 is provided on the end surface of the first crank arm 120 away from the first shaft 110, and the second crank arm 140 is used to connect with the first crank arm 120 , So that the recessed portion 121 communicates with the first oil passage 111 and the second oil passage 131.
  • the recess 121 is provided at the end of the first crank arm 120 away from the first shaft 110, or the recess 121 is provided at the end of the second crank arm 140 away from the second shaft 130, so that the first oil passage 111 There is a recess 121 between the second oil passage 131 and the recess 121. On the one hand, it is beneficial to store lubricating oil through the recess 121 to ensure sufficient oil in the second oil passage 131.
  • the second shaft 130 will be relative to the first shaft
  • the axis of the 110 is eccentrically arranged, and the first oil passage 111 and the second oil passage 131 that are displaced from each other can be connected through the recess 121, which facilitates the entry of lubricating oil into the second oil passage 131 through the first oil passage 111 and improves the oil supply effect.
  • the second crank arm 140 is used to connect with the first crank arm 120, that is, the first crank arm 120 and the second crank arm 140 are independent of each other, and subsequently assembled together, which facilitates the second shaft 130 relative to the first shaft.
  • the axis of the 110 is set eccentrically, and the eccentricity can be adjusted according to the actual displacement of the compressor, such as fixing the first shaft 110 and the first crank arm 120, and moving the second crank arm 140 and the second shaft 130 in the eccentric direction ,
  • crankshaft 100 with different eccentricity which improves the versatility of crankshaft 100 parts. It does not require processing equipment with complex functions or diverse structures to process the oil supply channel and process the crankshaft 100 with different eccentricity requirements. The processing is simple and the production is reduced. cost.
  • the recess 121 is provided on the end surface of the first crank arm 120 away from the first shaft 110, and the first oil passage 111 penetrates part of the bottom wall of the recess 121.
  • the first oil passage 111 By allowing the first oil passage 111 to penetrate a part of the bottom wall of the recessed portion 121, on the one hand, it is advantageous for the first oil passage 111 to be fully connected with the recessed portion 121, and on the other hand, the portion of the recessed portion 121 that is not penetrated can be used to store oil, and Oil is supplied into the second oil passage 131 to improve the lubrication effect.
  • the second shaft 130 is eccentrically arranged in the first direction relative to the axis of the first shaft 110, and the recessed portion 121 extends at least partially along the first direction.
  • the first direction is the eccentric direction shown by the arrow in the cross-sectional view in FIG. 1.
  • the opening of the recess 121 is elliptical, and the center of the ellipse is eccentrically arranged with respect to the axis of the first shaft 110 in the first direction.
  • the short axis of the ellipse extends in the first direction, and the long axis of the ellipse corresponds to two short arc segments, and there is a short arc segment that can extend to the area where the second oil passage 131 is located.
  • the short axis of the ellipse is extended in the first direction, and one of the two short arc segments corresponding to the long axis extends to the area where the second oil passage 131 is located, that is, at least the recess 121 is Part of it is directly connected to the second oil passage 131.
  • oil can be stored through the recess 121 in the short axis direction.
  • the short arc section extends to the area where the second oil passage 131 is located, which is convenient for the first oil passage 131.
  • the oil passage 111 uses the recess 121 to supply oil to the second oil passage 131.
  • the designed short arc segment can extend to the area where the second oil passage 131 is located under any eccentric condition of the crankshaft 100.
  • the opening of the recess 121 may also be elongated or circular, etc., and is not limited to an elliptical shape.
  • the recessed portion 121 is provided on the end surface of the second crank arm 140 away from the second shaft 130.
  • the recessed portion 121 is provided on the end surface of the second crank arm 140 away from the second shaft 130, and the second oil passage 131 penetrates part of the bottom wall of the recessed portion 121.
  • the second oil passage 131 By allowing the second oil passage 131 to penetrate a part of the bottom wall of the recessed portion 121, on the one hand, it is advantageous for the second oil passage 131 to be fully communicated with the recessed portion 121, and on the other hand, oil can be stored through the portion of the recessed portion 121 that is not penetrated, and Oil is supplied into the second oil passage 131 to improve the lubrication effect.
  • the second shaft 130 is eccentrically arranged in the first direction relative to the axis of the first shaft 110, that is, the axis of the second shaft 130 is parallel to the axis of the first shaft 110 and is spaced apart along the first direction.
  • the recessed portion 121 extends at least partially along the first direction, which facilitates the lubricating oil in the first oil passage 111 to enter the second oil passage 131 through the recessed portion 121, facilitates the supply of oil into the second oil passage 131, and improves the lubrication effect.
  • the opening of the recessed portion 121 is an ellipse, and the center of the ellipse is eccentrically arranged with respect to the axis of the first shaft 110 in the first direction.
  • the short axis of the ellipse extends in the first direction, and the long axis of the ellipse corresponds to two short arc segments, and there is a short arc segment that can extend to the area where the first oil passage 111 is located.
  • the recess 121 can at least partially It is connected to the first oil passage 111 and directly communicates with it.
  • the oil can be stored through the recess 121 in the short axis direction.
  • the short arc section extends to the area where the first oil passage 111 is located, which is convenient for the first oil passage 111.
  • the oil passage 111 supplies oil into the second oil passage 131 through the recess 121.
  • the designed short arc segment can extend to the first oil passage 111 under any eccentric condition of the crankshaft 100, so that the recessed portion 121 is communicated with the first oil passage 111.
  • the opening of the recess 121 may also be elongated or circular, etc., and is not limited to an elliptical shape.
  • first crank arm 120 and the first shaft 110 are integrally formed.
  • the second crank arm 140 and the second shaft 130 are integrally formed.
  • the first crank arm 120 and the second crank arm 140 are connected together.
  • first crank arm 120 and the first shaft 110 are integrally forged and formed; and/or the second crank arm 140 and the second shaft 130 are integrally forged and formed.
  • the molding is simple, the processing and manufacturing process is mature, the production efficiency and the material utilization rate are high, and the cost can be reduced while the quality of the crankshaft 100 parts is guaranteed.
  • the forging process to process the crankshaft 100 by using the forging process to process the crankshaft 100, the first crank arm 120 and the first crank arm 120 with certain precision can be quickly realized.
  • the first shaft 110 with the first oil passage 111, the second crank arm 140 and the second shaft 130 with the second oil passage 131 can directly forge the oil passages to improve production efficiency.
  • a set of forging dies can meet the needs of crankshaft 100 with different eccentric amounts, which makes the dies have very good versatility and reduces development costs and manufacturing costs. In addition, it also avoids the environmental pollution caused by the metal casting hot forming process and the massive consumption of energy.
  • the end of the second crank arm 140 away from the second shaft 130 is provided with a welding band 141, the welding band 141 is used to surround the outer circumference of the recess 121; the second crank arm 140 passes The welding belt 141 is resistance welded to the first crank arm 120.
  • one of the two short arc segments corresponding to the long axis of the ellipse can extend To the area where the second oil passage 131 is located, another short arc segment and two long arc segments corresponding to the oval minor axis surround the opening of the first oil passage 111, and are located at the welding zone 141 at any eccentric position. internal.
  • the outer contour of the welding band 141 has the same shape as the outer contour of the second crank arm 140; and/or the cross-section of the welding band 141 is trapezoidal or wedge-shaped.
  • the welding belt 141 is located at the edge of the second crank arm 140, and is connected with the edge of the second crank arm 140 in a rounded corner, or the welding belt 141 is at a certain distance from the edge of the second crank arm 140, where the welding belt 141 is surrounded by default One end of the fourth oil passage is open.
  • the cross-section of the welding band 141 is made a trapezoid or wedge shape, for example, the welding band 141 is set in an outward wedge shape toward the axis of the second shaft 130, which facilitates energization and melting into the first crank arm 120 close to the second crank.
  • One side of the arm 140 is firmly connected to the first crank arm 120 and the second crank arm 140.
  • the width of the end surface of the welding band 141 facing the first crank arm 120 is greater than or equal to 0.2 mm.
  • the width of the end surface of the welding band 141 facing the first crank arm 120 is less than 0.2 mm, such as 0.5 mm to 0.8 mm, it is ensured that the welding band 141 can firmly connect the first crank arm 120 and the second crank arm 140.
  • first crank arm 120 and the second crank arm 140 are welded together by laser welding.
  • the connection is convenient and firm.
  • the wall thicknesses of the first oil passage 111 are not completely the same.
  • the wall thicknesses of the first oil passage 111 are not completely the same, that is to say, the outer surface of the first shaft 110 is relatively different from each other.
  • the cross section of the first oil passage 111 is not a circular hole, but a triangular hole, an oval hole or a gourd-shaped hole, etc., or the cross section of the first oil passage 111 is a circle Hole, but its center deviates from the axis of the first shaft 110.
  • the centrifugal force generated is not exactly the same, so that the lubricating oil can pass through the thinner wall under the action of the centrifugal force. After oiling, it enters the first oil passage 111 and the second oil passage 131 for lubrication.
  • the oiling effect is good, and the lubricating effect is good.
  • the diameter of the crankshaft 100 is designed to be larger, so that the diameter of the oil passage can be made larger to ensure sufficient centrifugal force to ensure the amount of oil.
  • the crankshaft 100 with a small volume can be realized while increasing the amount of oil on the crankshaft 100 and ensuring the structural strength.
  • the first oil passage 111 has an axisymmetric structure.
  • the first oil passage 111 can be conveniently processed while ensuring the amount of oil.
  • the first oil passage 111 has a circular hole structure, and the center of the circular hole structure is deviated from the axis of the first shaft 110.
  • Any cross section of the first oil passage 111 is set in a circular hole shape, which is convenient for processing.
  • the first oil passage 111 has an axially symmetric special-shaped hole structure, such as a cross pattern. It can be ensured that the wall thickness of the first oil passage 111 has a large variation range, thereby ensuring that the first shaft 110 can generate sufficient centrifugal force to guide the lubricating oil to be oiled.
  • the first oil passage 111 has a thin-walled section 112 and a thick-walled section 113; the second shaft 130 is far away from The direction in which the thin-walled section 112 is located is eccentrically arranged with respect to the axis of the first shaft 110.
  • the design has a thin-walled section 112 and a thick-walled section 113 on any cross-section of the first shaft 110, wherein the thin-walled section 112 is the thinnest section by default, and the thick-walled section 113 is the thickest section by default.
  • a thick section That is, the thickness of any thin-walled section 112 is smaller than the thickness of any thick-walled section 113.
  • the number of the thin-walled section 112 may be one or multiple, and the number of the thick-walled section 113 may be one or multiple.
  • the second shaft 130 and the thin-walled section 112 are not located in the same orientation of the axis of the first shaft 110, which can avoid the first shaft.
  • the centrifugal force brought by the second shaft 130 affects the thin-walled section 112 of the first shaft 110, avoids rupture and damage of the thin-walled section 112, ensures the structural strength of the thin-walled section 112, and further realizes that the small-sized crankshaft 100 has a higher structure. ⁇ The amount of oil.
  • the central angle of the second shaft 130 and the thin-walled section 112 relative to the axis of the first shaft 110 is greater than or equal to 90°. That is, the orthographic projection of the second shaft 130 and the thin-walled section 112 on any cross section of the first shaft 110 has a central angle corresponding to the axis of the first shaft 110 of at least 90°.
  • the second shaft 130 is separated from the thin-walled section 112 by a sufficient distance, which effectively prevents the eccentric movement of the second shaft 130 relative to the first shaft 110 from affecting the thin-walled section 112 of the first shaft 110 and ensures that the second shaft 130 is thin-walled
  • the structural strength of the section 112 meets the requirements of the crankshaft 100.
  • the central angle of the second shaft 130 and the thin-walled section 112 relative to the axis of the first shaft 110 is 90°, so that the thin-walled section 112 is perpendicular to the direction of movement of the piston of the reciprocating compressor.
  • the central angle of the second shaft 130 and the thin-walled section 112 relative to the axis of the first shaft 110 may also be 120° or 180°. It can be determined according to the wall thickness and position of the thin-walled section 112.
  • the inner contour of the thin-walled section 112 is a first arc
  • the inner contour of the thick-walled section 113 is a second arc
  • the opening directions of the first and second arcs face the first arc.
  • the axis of the shaft 110 Convenient processing and quick lubricating oil.
  • the first oil passage 111 has a larger space, which facilitates more lubricating oil to enter the first oil passage 111 and improves The lubrication effect also facilitates the processing of the first oil passage 111.
  • the inner profile of the thin-walled section 112 is a third circular arc
  • the inner profile of the thick-walled section 113 is a fourth circular arc
  • the opening direction of the third circular arc and the fourth circular arc is toward the axis of the first shaft 110
  • the other opening direction is away from the axis of the first shaft 110.
  • the wall thickness of the thin-walled section 112 is greater than or equal to 0.3mm; and/or the arc length of the first arc ranges from 3mm to 5mm; and/or the radius corresponding to the first arc is the same as that of the second arc The range of the difference of the corresponding radius is 0mm to 2mm.
  • the thin-walled section 112 has a sufficient amount of oil.
  • the difference between the radius corresponding to the first arc and the radius corresponding to the second arc is a circular hole structure, and is arranged eccentrically with respect to the axis of the first shaft 110, so that sufficient centrifugal force can be generated during the rotation of the first shaft 110 to guide the lubricating oil to be oiled.
  • the first oil passage 111 further has a transition section 114 connecting the thin-walled section 112 and the thick-walled section 113.
  • the thin-walled section 112 and the thick-walled section 113 are connected by the transition section 114, which can buffer the thickness change of the first shaft 110 and improve the structural strength of the first shaft 110.
  • transition section 114 includes a first straight line, such as tangent to the first arc and the second arc, of course, it may not be tangent; or the transition section 114 includes the first straight line and the fifth arc, the first The straight line connects the first arc and the second arc through the fifth arc.
  • a first tangent is made at the intersection of the first arc and the first straight line
  • a second tangent is made at the intersection of the second arc and the first straight line.
  • the first tangent and the second tangent face the first axis.
  • the angle inside 110 is greater than 90°. Ensure that there is enough space inside the first oil passage 111 to ensure the amount of oil.
  • the angle between the first tangent line and the second tangent line facing the inside of the first shaft 110 may also be less than 90°.
  • Embodiment 6 is a diagrammatic representation of Embodiment 6
  • an end of the first crank arm 120 close to the first shaft 110 is provided with a boss 122.
  • a boss 122 By forming a boss 122 at one end of the first crank arm 120 close to the first shaft 110, it is convenient to install and locate the gasket, thereby facilitating the placement of the bearing in the compressor, and ensuring the perpendicularity of the bearing to the first shaft 110.
  • the boss 122 exists opposite to the groove, and the inner surface of the groove also has a circular arc surface, and may also have an edge.
  • the height of the boss 122 is greater than 0.5 mm; and/or the depth of the groove is less than or equal to 0.8 mm.
  • the height of the boss 122 may be 1 mm, 2 mm, etc., and the depth of the groove may be between 0.2 mm and 0.4 mm.
  • the boss 122 has sufficient structural strength to support the bearing and the rotor, and the groove can ensure the fine grinding of the first shaft 110.
  • a first oil hole 115 is provided on the first shaft 110, and the first oil hole 115 is in communication with the first oil passage 111; the second shaft 130 is provided with a second oil hole 132.
  • the second oil hole 132 communicates with the second oil passage 131.
  • the first oil hole 115 communicating with the first oil passage 111 is provided on the first shaft 110, and the second oil hole 132 communicating with the second oil passage 131 is provided on the second shaft 130, so that the lubricating oil can pass through
  • the first oil hole 115 and the second oil hole 132 flow out to lubricate the compressor rotor and other structures.
  • the number of the first oil hole 115 is one or at least two; the number of the second oil hole 132 is one or at least two.
  • the diameter of the first oil hole 115 is greater than or equal to 1.5 mm; the diameter of the second oil hole 132 is greater than or equal to 1.5 mm. Such as 2mm to 4mm. Ensure that the lubricating oil flows out smoothly.
  • first shaft 110 and the second shaft 130 are both low-carbon steel shafts or alloy steel shafts.
  • a compressor includes: the crankshaft 100 according to any one of the above-mentioned embodiments. Since the compressor proposed in this embodiment has the crankshaft 100 of any one of the above embodiments, it further has the beneficial effects of any one of the above embodiments, so it will not be repeated here.
  • the compressor further includes: a housing, a motor, a bearing and a piston.
  • the bottom of the casing has an oil pool; the motor is arranged in the casing, and the rotor of the motor is sleeved on the first shaft 110; the bearing is sleeved on the first shaft 110 and is located between the rotor and the first crank arm 120; One end of the connecting rod is connected, and the other end of the connecting rod is connected with the second shaft 130.
  • the first shaft 110 can extend into the oil sump, so that the lubricating oil enters the second shaft 130 through the first shaft 110 to realize the lubrication of the crankshaft 100, thereby realizing the lubrication of the rotor and connecting rod, and improving the lubrication effect of the compressor , Reduce wear and improve the service life of the compressor.
  • the diameter of the boss 122 of the crankshaft 100 is larger than the diameter of the raceway of the bearing, such as 1mm to 2mm larger, which is beneficial for stably supporting the bearing and avoiding the bearing from moving greatly.
  • an end of the first shaft 110 away from the second shaft 130 is provided with a chamfer, and the width of the chamfer is smaller than the wall thickness of any part of the first oil passage 111 to facilitate the installation of the rotor on the first shaft 110.
  • Embodiment 8 is a diagrammatic representation of Embodiment 8
  • a refrigeration equipment includes: the compressor as in any one of the above embodiments. Since the refrigeration equipment provided in this embodiment has the compressor of any one of the above embodiments, it further has the beneficial effects of any one of the above embodiments, and will not be repeated here.
  • the refrigeration equipment also includes a condenser, a pressure reducing component and an evaporator.
  • the outlet of the compressor is communicated with the inlet of the condenser; the inlet of the pressure reducing element is communicated with the outlet of the condenser; the inlet of the evaporator is communicated with the outlet of the pressure reducing element, and the outlet of the evaporator is communicated with the inlet of the compressor.
  • the refrigeration equipment is a refrigerator or an air conditioner.
  • the term “plurality” refers to two or more than two, unless specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense.
  • “connected” can be a fixed connection, a detachable connection, or an integral connection;
  • “connected” can be It is 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.

Abstract

一种曲轴（100），包括：第一轴（110）、第二轴（130）、第一曲柄臂（120）、第二曲柄臂（140）和凹陷部（121）；第一曲柄臂（120）设置在第一轴（110）的一端，第一曲柄臂（120）上设有第一油道（111），第一油道（111）贯穿第一轴（110）；第二曲柄臂（140）设置在第二轴（130）的一端，第二曲柄臂（140）上设有第二油道（131），第二油道（131）贯穿第二轴（130）；凹陷部（121）设置在第一曲柄臂（120）远离第一轴（110）的端面上或设置在第二曲柄臂（140）远离第二轴（130）的端面上，第二曲柄臂（140）用于与第一曲柄臂（120）连接，以使凹陷部（121）连通第一油道（111）和第二油道（131）。通过凹陷部（121）存储润滑油及向第二油道（131）供油，可提高供油效果。可根据压缩机的实际排量需要，调节第二轴（130）与第一轴（110）的相对位置从而调节偏心量，使得曲轴能够适应不同压缩机的排量需求，易于加工制造。还涉及包括曲轴的压缩机以及包括压缩机的制冷设备。

Description

曲轴、压缩机及制冷设备
本申请要求于2019年11月22日提交中国专利局、申请号为“201911158486.0”、发明创造名称为“曲轴、压缩机及制冷设备”的中国专利申请的优先权，上述申请全部内容通过引用结合在本申请中。
技术领域
本申请属于制冷设备技术领域，具体而言，涉及一种曲轴、一种压缩机及一种制冷设备。
背景技术
目前定速往复式压缩机普遍采用铸造成型。为满足不同往复式压缩机排量需求，曲轴需要具有不同的偏心量和轴径，但在规划不同偏心量和轴径的曲轴时均需重新开模，导致铸造曲轴的模具标准化程度低、通用性差，增加制造成本。而且，铸造成型的曲轴需在外表面上加工供油通道，加工复杂，上油效果差。
发明内容
本申请旨在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出了一种曲轴。
本申请的第二方面提出了一种压缩机。
本申请的第三方面提出了一种制冷设备。
有鉴于此，根据本申请的第一方面实施例提出了一种曲轴，包括：第一轴、第二轴、第一曲柄臂、第二曲柄臂和凹陷部；第一曲柄臂设置在第一轴的一端，第一曲柄臂上设有第一油道，第一油道贯穿第一轴；第二曲柄臂设置在第二轴的一端，第二曲柄臂上设有第二油道，第二油道贯穿第二轴；凹陷部设置在第一曲柄臂远离第一轴的端面上或设置在第二曲柄臂远离第二轴的端面上，第二曲柄臂用于与第一曲柄臂连接，以使凹陷部连通第一油道和第二油道。
本申请实施例提供的曲轴包括第一轴、第一曲柄臂、第二轴和第二曲柄臂，通过在第一曲柄臂上设置第一油道，并使第一油道贯穿第一轴，在第二曲柄臂上设置第二油道，并使第二油道贯穿第二轴，使得第二曲柄臂与第一曲柄臂连接后，第一油道与第二油道相连通，实现了润滑油经第一油道进入第二油道内供油。而且，通过在第一曲柄臂远离第一轴的一端设置凹陷部，或者在第二曲柄臂远离第二轴的一端设置凹陷部，使得第一油道和第二油道之间具有凹陷部，一方面有利于通过凹陷部存储润滑油，确保第二油道内油量充足，另一方面由于第二轴会相对于第一轴的轴线偏心设置，可通过凹陷部连通相互错位的第一油道和第二油道，更方便润滑油经第一油道进入第二油道，提高供油效果。
而且，第二曲柄臂用于与第一曲柄臂连接，也即第一曲柄臂与第二曲柄臂彼此独立，后续装配在一起，有利于使第二轴相对于第一轴的轴线偏心设置，可根据压缩机的实际排量需要，来调节偏心量，调节第二轴与第一轴的相对位置，使得曲轴能够适应不同压缩机的排量需求，如固定第一轴与第一曲柄臂，而在偏心方向上移动第二曲柄臂和第二轴，来得到不同偏心量的曲轴。与相关技术中第一轴、第二轴一体铸造成型、需在曲轴外表面加工供油通道相比，提高了曲轴零部件的通用性，无需功能复杂或结构多样的加工设备来加工供油通道、加工具有不同偏心量要求的曲轴，加工简单，降低生产成本。
另外，根据本申请提供的上述技术方案中的曲轴，还可以具有如下附加技术特征：
在一些实施例中，凹陷部设置在第一曲柄臂远离第一轴的端面上，第一油道贯穿凹陷部的部分底壁。
在这些实施例中，具体将凹陷部设置在第一曲柄臂远离第一轴的端面上，通过使第一油道贯穿凹陷部的部分底壁，一方面有利于第一油道与凹陷部充分连通，另一方面可通过凹陷部未被贯穿的部分进行存油，以及向第二油道内供油，提高润滑效果。
在一些实施例中，凹陷部设置在第二曲柄臂远离第二轴的端面上，第二油道贯穿凹陷部的部分底壁。
在这些实施例中，具体将凹陷部设置在第二曲柄臂远离第二轴的端面上，通过使第二油道贯穿凹陷部的部分底壁，一方面有利于第二油道与凹陷部充分连通，另一方面可通过凹陷部未被贯穿的部分进行存油，以及向第二油道内供油，提高润滑效果。
在一些实施例中，第二轴相对第一轴的轴线在第一方向上偏心设置，凹陷部至少部分沿第一方向延伸。
在这些实施例中，具体设定第二轴相对于第一轴的轴线在第一方向偏心设置，也即第二轴的轴线与第一轴的轴线相平行并沿第一方向间隔分布，通过设定凹陷部至少部分沿第一方向延伸，有利于第一油道内的润滑油经凹陷部进入第二油道，方便向第二油道内供油，提高润滑效果。
在一些实施例中，凹陷部的开口呈椭圆形，椭圆形的圆心在第一方向上相对于第一轴的轴线偏心设置。
在这些实施例中，具体设计凹陷部的开口呈椭圆形，此时凹陷部可为椭圆形沉台结构。通过使椭圆形的圆心在第一方向上相对于第一轴的轴线偏心设置，进一步确保润滑油能够经凹陷部大量进入第二油道，提高润滑效果。
当然，在其他实施例中，凹陷部的开口也可呈长条形或圆形等等，不限于椭圆形。
在一些实施例中，椭圆形的短轴沿第一方向延伸，椭圆形的长轴对应两个短圆弧段；位于第一曲柄臂上的两个短圆弧段中，存在一个短圆弧段用于延伸至第二油道所在区域，或位于第二曲柄臂上的两个短圆弧段中，存在一个短圆弧段用于延伸至第一油道所在区域。
在这些实施例中，在凹陷部设置在第一曲柄臂上的情况下，通过使椭圆形的短轴沿第一方向延伸，并使长轴对应的两个短圆弧段中存在一个短圆弧段延伸至第二油道所在区域，也即凹陷部至少部分能够与第二油道相对接，而直接连通，一方面可通过短轴方向的凹陷部来进行存油，另一方面由于短圆弧段延伸至第二油道所在区域，方便向第二油道供油。另外，在凹陷部设置在第二曲柄臂上的情况下，通过使椭圆形的短轴沿第一方向延伸，并使长轴对应的两个短圆弧段中存在一个短圆弧段延伸至第一油道 所在区域，也即凹陷部至少部分能够与第一油道相对接，而直接连通，一方面可通过短轴方向的凹陷部来进行存油，另一方面由于短圆弧段延伸至第一油道所在区域，方便第一油道通过该凹陷部向第二油道内供油。其中，设计短圆弧段在曲轴的任何偏心条件下，均能够延伸至第二油道或第一油道所在区域，以使凹陷部与第二油道或第一油道相连通。
在一些实施例中，第一曲柄臂与第一轴一体成型。第二曲柄臂与第二轴一体成型。第一曲柄臂与第二曲柄臂连接在一起。通过使第一曲柄臂与第一轴一体成型，使第二曲柄臂与第二轴一体成型，而后将第一曲柄臂与第二曲柄臂连接在一起，实现曲轴的装配，加工简单，模块化的同时，也满足不同压缩机的排量需求，尤其是第二曲柄臂在很多排量需求下均能够连接在第一曲柄臂上的情况下，提高曲轴的生产效率。
当然，第一曲柄臂也可与第一轴焊接连接，第二曲柄臂也可与第二轴焊接连接。
在一些实施例中，第一曲柄臂与第一轴一体锻压成型；和/或第二曲柄臂与第二轴一体锻压成型。成型简单，加工制造工艺成熟，生产效率及材料利用率高，可在保证曲轴零件质量的情况下，降低成本。与相关技术中采用铸造工艺加工曲轴，而需在曲轴的外表面后续加工供油油道相比，通过采用锻压工艺加工曲轴，可快速地实现具有一定精度的第一曲柄臂与带有第一油道的第一轴，以及第二曲柄臂与带有第二油道的第二轴，可使油道直接锻压成型，提高生产效率。而且，一套锻压模具可以满足不同偏心量曲轴需求，使得模具具有非常好的通用性，降低开发费用及制造费用。另外，也免除了采用金属铸造热成型工艺所带来的对环境的污染，对能源的大量消耗。
当然，第一曲柄臂与第一轴也可通过车削等一体成型，同样第二曲柄臂与第二轴也可通过车削一体成型。
在一些实施例中，第一曲柄臂和第二曲柄臂通过电阻焊焊接在一起。
在这些实施例中，采用电阻焊的方式将第一曲柄臂和第二曲柄臂连接在一起，由于电阻焊能够将焊接带通电熔入第一曲柄臂朝向第二曲柄臂的一侧，连接方便牢固，不会导致第二曲柄臂相对于第一曲柄臂发生翘起的 情况，方便第二曲柄臂牢固地设置在第一曲柄臂适当的位置，从而调节第二轴相对第一轴的偏心量。其中，第二曲柄臂的焊接需满足曲轴所有偏心条件下均能够焊接在第一曲柄臂上，从而确保曲轴零部件的通用性。
在一些实施例中，第二曲柄臂远离第二轴的一端设有焊接带，焊接带用于围设在凹陷部的外周；第二曲柄臂通过焊接带电阻焊焊接在第一曲柄臂上。其中，在凹陷部设置在第一曲柄臂上，以及凹陷部的开口呈椭圆形的情况下，椭圆形的长轴所对应的两个短圆弧段中，一个短圆弧段用于延伸至第二油道所在区域，另一个短圆弧段以及椭圆形的短轴所对应的两个长圆弧段包围第一油道的开口，并在任何偏心位置时均位于焊接带的内部。
在另一些实施例中，第一曲柄臂和第二曲柄臂通过激光焊焊接在一起。连接方便牢固。
在一些实施例中，在第一轴的任一横截面上，第一油道各处的壁厚不完全相同。
在这些实施例中，通过设定在第一轴的任一截面上，第一油道各处的壁厚不完全相同，也即与第一轴的外表面之间具有相对而言的薄壁处和厚壁处，第一油道的横截面并非圆形孔，而是如三角形孔、椭圆形孔或葫芦形孔等等，或者第一油道的横截面为圆形孔，但其圆心偏离第一轴的轴线。在曲轴转动的过程中，由于第一油道在周向上各处壁厚不完全相同，所产生的离心力也不完全相同，使得润滑油能够在离心力的作用下通过壁厚较薄的地方进行上油，进入第一油道、第二油道而进行润滑，上油效果好，润滑效果好。与相关技术中为保证上油量和曲轴的结构强度，将曲轴的直径设计的较大，从而才能够使油道直径较大，以保证足够的离心力，进而保证上油量相比，可在提高曲轴上油量和保证结构强度的同时，实现小体积的曲轴。
在一些实施例中，在第一轴的任一横截面上，第一油道呈轴对称结构。
在这些实施例中，通过设计第一油道在第一轴的任一横截面上呈轴对称结构，如椭圆形、十字花型等等，可在方便加工第一油道的同时，保证上油量。
在一些实施例中，在第一轴的任一横截面上，第一油道呈轴对称的异形 孔结构。可确保第一油道壁厚的变化幅度较大，从而确保第一轴能够产生足够的离心力，引导润滑油上油。
在一些实施例中，在第一轴的任一横截面上，第一油道呈圆孔结构，圆孔结构的圆心偏离第一轴的轴线。将第一油道的任一横截面设置为圆孔状，加工方便。
在一些实施例中，在第一轴的任一横截面上，第一油道具有薄壁段和厚壁段；第二轴远离薄壁段所在方向相对于第一轴的轴线偏心设置。
在这些实施例中，设计在第一轴的任一横截面上均具有薄壁段和厚壁段，其中薄壁段默认为最薄的一段，厚壁段为壁厚最厚的一段。也即任一薄壁段的厚度小于任一厚壁段的厚度。薄壁段的数量可为一个，也可为多个，同样厚壁段的数量可为一个，也可为多个。通过使第二轴远离薄壁段所在方向相对于第一轴的轴线偏心设置，也即第二轴与薄壁段不位于第一轴的轴线的同一方位，可避免第二轴所带来的离心力对第一轴的薄壁段造成影响，避免薄壁段破裂损坏等，保证薄壁段的结构强度，从而进一步实现小体积的曲轴具有较高的上油量。
在一些实施例中，第二轴、薄壁段相对于第一轴的轴线的圆心角大于等于90°。
在这些实施例中，进一步设定第二轴、薄壁段相对于第一轴的轴线的圆心角大于或等于90°，也即第二轴、薄壁段在第一轴的任一横截面上的正投影，相对于第一轴的轴线所对应的圆心角至少为90°。使得第二轴与薄壁段相隔足够的距离，有效避免第二轴相对于第一轴的偏心运动对第一轴的薄壁段造成影响，确保第二轴薄壁段的结构强度满足曲轴的要求。
具体地，第二轴、薄壁段相对于第一轴的轴线的圆心角为90°，以使薄壁段垂直于往复式压缩机活塞的运动方向。当然，第二轴、薄壁段相对于第一轴的轴线的圆心角也可为120°或180°等。可依据薄壁段的壁厚及位置而定。
在一些实施例中，薄壁段的内轮廓为第一圆弧，厚壁段的内轮廓为第二圆弧，第一圆弧和第二圆弧的开口方向朝向第一轴的轴线。
在这些实施例中，限定在第一轴的任一横截面上，薄壁段的内轮廓为 第一圆弧，厚壁段的内轮廓为第二圆弧，方便加工，便于润滑油快速上油。另外，通过使第一圆弧和第二圆弧的开口方向朝向第一轴的轴线，使得第一油道具有较大的空间，便于更多的润滑油进入第一油道，提高润滑效果，也方便第一油道的加工。
在一些实施例中，薄壁段的壁厚大于等于0.3mm；和/或第一圆弧的弧长的取值范围为3mm至5mm；和/或第一圆弧所对应的半径与第二圆弧所对应的半径的差值的取值范围为0mm至2mm。
在这些实施例中，通过使薄壁段的壁厚大于等于0.3mm，如0.4mm至0.5mm，确保薄壁段具有足够的结构强度。另外，通过使第一圆弧的弧长大于0mm，如在3mm至5mm之间，确保薄壁段具有足够的上油量。另外，通过使第一圆弧所对应的半径与第二圆弧所对应的半径的差值大于等于0mm，如在1mm至2mm之间，其中若两个半径差值为0，则第一油道的横截面呈圆孔结构，相对于第一轴的轴线偏心设置，使得第一轴转动过程中能够产生足够的离心力引导润滑油上油。
在一些实施例中，第一油道还具有连接薄壁段和厚壁段的过渡段。进一步地，过渡段的内轮廓具有第一直线。
在这些实施例中，设定在第一轴的任一横截面上，具有过渡段来连接薄壁段和厚壁段，可对第一轴的薄厚变化进行缓冲，提高第一轴的结构强度。
在一些实施例中，过渡段包括第一直线，如分别与第一圆弧和第二圆弧相切，当然也可不相切；过渡段还可包括第五圆弧，第一直线通过第五圆弧连接第一圆弧和第二圆弧。
在一些实施例中，在第一圆弧与第一直线相交处作第一切线，在第二圆弧与第一直线相交处作第二切线，第一切线与第二切线面向第一轴内部的夹角大于90°。确保第一油道内部具有足够的空间，保证上油量。
当然，第一切线与第二切线面向第一轴内部的夹角也可小于90°。
在一些实施例中，薄壁段的内轮廓为第三圆弧，厚壁段的内轮廓为第四圆弧；第三圆弧和第四圆弧中一个开口方向朝向第一轴的轴线，另一个开口方向背离第一轴的轴线。
在一些实施例中，焊接带的外轮廓与第二曲柄臂的外轮廓的形状相同；和/或焊接带的横截面呈梯形或楔形。
在这些实施例中，通过设定焊接带的外轮廓与第二曲柄臂的外轮廓形状相同，便于第二曲柄臂紧密地连接在第一曲柄臂上，而不会发生第二曲柄臂相对于第一曲柄臂局部翘起的情况。例如，焊接带位于第二曲柄臂的边缘处，与第二曲柄臂的边缘圆角连接，或焊接带距离第二曲柄臂的边缘具有一定间距，其中，默认焊接带包围第四油道的一端开口。另外，通过使焊接带的横截面呈梯形或楔形，如焊接带朝向第二轴的轴线的一侧设置为向外的楔形状，便于通电熔入第一曲柄臂靠近第二曲柄臂的一侧，牢固连接第一曲柄臂和第二曲柄臂。
在一些实施例中，焊接带面向第一曲柄臂的端面的宽度大于等于0.2mm。
在这些实施例中，通过使焊接带面向第一曲柄臂的端面的宽度不小于0.2mm，如0.5mm至0.8mm，确保焊接带能够牢固连接第一曲柄臂和第二曲柄臂。
在一些实施例中，第一曲柄臂靠近第一轴的一端设有凸台。
在这些实施例中，通过在第一曲柄臂靠近第一轴的一端形成有凸台，便于垫圈的安装定位，进而便于压缩机中轴承的安放，保证轴承与第一轴的垂直度。
在一些实施例中，通过使凸台围绕在第一轴四周，并在凸台与第一轴的外轮廓相交处形成有凹槽，便于稳定支撑轴承，而且凹槽的存在一方面有利于后续对第一轴进行精加工，可对刀具进行让位，另一方面与凸台与第一轴之间不具有凹槽相比，减小了凸台的精磨面积，方便凸台的精磨，节约成本。具体地，凸台与凹槽相对存在，凹槽的内表面也具有圆弧面，也可具有棱边。
在一些实施例中，凸台的高度大于0.5mm；和/或凹槽的深度小于等于0.8mm。具体地，凸台的高度可为1mm、2mm等，凹槽的深度可在0.2mm至0.4mm之间。使得凸台具有足够的结构强度支撑轴承及转子，凹槽可确保第一轴的精磨。
在一些实施例中，第一轴上设有第一油孔，第一油孔与第一油道相连通；第二轴上设有第二油孔，第二油孔与第二油道相连通。
在这些实施例中，通过在第一轴上设置与第一油道相连通的第一油孔，在第二轴上设置与第二油道相连通的第二油孔，使得润滑油能够经第一油孔与第二油孔流出，润滑压缩机的转子等结构。
其中，第一油孔的数量为一个或至少两个；第二油孔的数量为一个或至少两个。
在一些实施例中，第一油孔的直径大于等于1.5mm；第二油孔的直径大于等于1.5mm。如2mm至4mm。确保润滑油顺利流出。
在一些实施例中，第一轴、第二轴均为低碳钢轴或合金钢轴。如低碳合金钢，结构强度高，耐磨损。
本申请的第二方面实施例提出了一种压缩机，包括：如上述技术方案中任一项的曲轴。
本申请提出的压缩机，由于具有上述任一技术方案的曲轴，进而具有上述任一技术方案的有益效果，在此不一一赘述。
在一些实施例中，压缩机还包括：壳体、电机、轴承及活塞。壳体的底部具有油池；电机设置在壳体内，电机的转子套设在第一轴上；轴承套设在第一轴上，并位于转子与第一曲柄臂之间；活塞与连杆的一端连接，连杆的另一端与第二轴相连接。其中，第一轴能够伸入到油池内，从而润滑油经第一轴进入第二轴，实现对曲轴的润滑，进而实现对转子、连杆的润滑，提高压缩机的润滑效果，减小磨损，提高压缩机的使用寿命。
在一些实施例中，曲轴的凸台的直径大于轴承的滚道直径，如大1mm至2mm，有利于稳定支撑轴承，避免轴承大幅度窜动。
在一些实施例中，第一轴远离第二轴的一端设置倒角，倒角的宽度小于第一油道任一处的壁厚，便于引导转子安装到第一轴上。
本申请的第三方面实施例提出了一种制冷设备，包括：如上述技术方案中任一项的压缩机。
本申请提供的制冷设备，由于具有上述任一技术方案的压缩机，进而具有上述任一技术方案的有益效果，在此不一一赘述。
在一些实施例中，制冷设备还包括冷凝器、降压件和蒸发器。压缩机的出口与冷凝器的入口相连通；降压件的入口与冷凝器的出口相连通；蒸发器的入口与降压件的出口相连通，蒸发器的出口与压缩机的入口相连通。实现制冷、制热循环，由于压缩机具有较高的使用寿命，从而有利于保证制冷系统的使用寿明。
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示出了本申请的一个实施例的曲轴的剖视示意图；
图2示出了图1中的A-A方向的剖视图；
图3示出了本申请的一个实施例的第一轴与第一曲柄臂的一个结构示意图；
图4示出了本申请的一个实施例的第一轴与第一曲柄臂的另一个结构示意图；
图5示出了本申请的一个实施例的第一轴与第一曲柄臂的再一个结构示意图；
图6示出了本申请的一个实施例的第二轴与第二曲柄臂的一个结构示意图；
图7示出了本申请的一个实施例的第二轴与第二曲柄臂的另一个结构示意图；
图8示出了本申请的一个实施例的第二轴与第二曲柄臂的再一个结构示意图。
其中，图1至图8中附图标记与部件名称之间的对应关系为：
100曲轴，110第一轴，111第一油道，112薄壁段，113厚壁段，114过渡段，115第一油孔，120第一曲柄臂，121凹陷部，122凸台，130第二轴，131第二油道，132第二油孔，140第二曲柄臂，141焊接带。
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1至图8描述根据本申请一些实施例所述的曲轴100。
实施例一：
如图1所示，一种曲轴100，包括：第一轴110、第二轴130、第一曲柄臂120、第二曲柄臂140和凹陷部121；第一曲柄臂120设置在第一轴110的一端，第一曲柄臂120上设有第一油道111，第一油道111贯穿第一轴110；第二曲柄臂140设置在第二轴130的一端，第二曲柄臂140上设有第二油道131，第二油道131贯穿第二轴130；凹陷部121设置在第一曲柄臂120远离第一轴110的端面上，第二曲柄臂140用于与第一曲柄臂120连接，以使凹陷部121连通第一油道111和第二油道131。
在该实施例中，通过在第一曲柄臂120远离第一轴110的一端设置凹陷部121，或者在第二曲柄臂140远离第二轴130的一端设置凹陷部121，使得第一油道111和第二油道131之间具有凹陷部121，一方面有利于通过凹陷部121存储润滑油，确保第二油道131内油量充足，另一方面由于第二轴130会相对于第一轴110的轴线偏心设置，可通过凹陷部121连通相互错位的第一油道111和第二油道131，更方便润滑油经第一油道111进入第二油道131，提高供油效果。而且，第二曲柄臂140用于与第一曲柄臂120连接，也即第一曲柄臂120与第二曲柄臂140彼此独立，后续装配在一起，有利于使第二轴130相对于第一轴110的轴线偏心设置，可根据压缩机的实际排量需要，来调节偏心量，如固定第一轴110与第一曲柄臂120，而在偏心方向上移动第二曲柄臂140和第二轴130，来得到不同偏心量的曲轴100，提高了曲轴100零部件的通用性，无需功能复杂或结构多样的加工设备来加工供油通道、加工具有不同偏心量要求的曲轴100， 加工简单，降低生产成本。
进一步地，如图1、图4和图5所示，凹陷部121设置在第一曲柄臂120远离第一轴110的端面上，第一油道111贯穿凹陷部121的部分底壁。通过使第一油道111贯穿凹陷部121的部分底壁，一方面有利于第一油道111与凹陷部121充分连通，另一方面可通过凹陷部121未被贯穿的部分进行存油，以及向第二油道131内供油，提高润滑效果。
进一步地，如图1所示，第二轴130相对第一轴110的轴线在第一方向上偏心设置，凹陷部121至少部分沿第一方向延伸。第一方向即图1中在该剖视下的箭头所示的偏心方向，通过设定凹陷部121至少部分沿第一方向延伸，有利于第一油道111内的润滑油经凹陷部121进入第二油道131，方便向第二油道131内供油，提高润滑效果。
进一步地，如图5所示，凹陷部121的开口呈椭圆形，椭圆形的圆心在第一方向上相对于第一轴110的轴线偏心设置。椭圆形的短轴沿第一方向延伸，椭圆形的长轴对应两个短圆弧段中，存在一个短圆弧段能够延伸至第二油道131所在区域。通过使椭圆形的短轴沿第一方向延伸，并使长轴对应的两个短圆弧段中存在一个短圆弧段延伸至第二油道131所在区域，也即使得凹陷部121的至少部分与第二油道131相对接而直接连通，一方面可通过短轴方向的凹陷部121来进行存油，另一方面由于短圆弧段延伸至第二油道131所在区域，方便第一油道111借用凹陷部121向第二油道131供油。其中，设计短圆弧段在曲轴100的任何偏心条件下，均能够延伸至第二油道131所在区域。
当然，在其他实施例中，凹陷部121的开口也可呈长条形或圆形等等，不限于椭圆形。
实施例二：
与上述实施例一不同的是，凹陷部121设置在第二曲柄臂140远离第二轴130的端面上。
进一步地，凹陷部121设置在第二曲柄臂140远离第二轴130的端面上，第二油道131贯穿凹陷部121的部分底壁。通过使第二油道131贯穿凹陷部121的部分底壁，一方面有利于第二油道131与凹陷部121充分连 通，另一方面可通过凹陷部121未被贯穿的部分进行存油，以及向第二油道131内供油，提高润滑效果。
进一步地，第二轴130相对于第一轴110的轴线在第一方向偏心设置，也即第二轴130的轴线与第一轴110的轴线相平行并沿第一方向间隔分布，通过设定凹陷部121至少部分沿第一方向延伸，有利于第一油道111内的润滑油经凹陷部121进入第二油道131，方便向第二油道131内供油，提高润滑效果。
进一步地，凹陷部121的开口呈椭圆形，椭圆形的圆心在第一方向上相对于第一轴110的轴线偏心设置。椭圆形的短轴沿第一方向延伸，椭圆形的长轴对应两个短圆弧段中，存在一个短圆弧段能够延伸至第一油道111所在区域。通过使椭圆形的短轴沿第一方向延伸，并使长轴对应的两个短圆弧段中存在一个短圆弧段延伸至第一油道111所在区域，也即凹陷部121至少部分能够与第一油道111相对接，而直接连通，一方面可通过短轴方向的凹陷部121来进行存油，另一方面由于短圆弧段延伸至第一油道111所在区域，方便第一油道111通过该凹陷部121向第二油道131内供油。其中，设计短圆弧段在曲轴100的任何偏心条件下，均能够延伸至第一油道111，以使凹陷部121与第一油道111相连通。
或者进一步地，凹陷部121的开口也可呈长条形或圆形等等，不限于椭圆形。
实施例三：
在上述实施例一或实施例二的基础上，如图1所示，进一步限定第一曲柄臂120与第一轴110一体成型。第二曲柄臂140与第二轴130一体成型。第一曲柄臂120与第二曲柄臂140连接在一起。通过使第一曲柄臂120与第一轴110一体成型，使第二曲柄臂140与第二轴130一体成型，而后将第一曲柄臂120与第二曲柄臂140连接在一起，实现曲轴100的装配，加工简单，模块化的同时，也满足不同压缩机的排量需求，尤其是第二曲柄臂140在很多排量需求下均能够连接在第一曲柄臂120上的情况下，提高曲轴100的生产效率。
进一步地，第一曲柄臂120与第一轴110一体锻压成型；和/或第二曲 柄臂140与第二轴130一体锻压成型。成型简单，加工制造工艺成熟，生产效率及材料利用率高，可在保证曲轴100零件质量的情况下，降低成本。与相关技术中采用铸造工艺加工曲轴100，而需在曲轴100的外表面后续加工供油油道相比，通过采用锻压工艺加工曲轴100，可快速地实现具有一定精度的第一曲柄臂120与带有第一油道111的第一轴110，以及第二曲柄臂140与带有第二油道131的第二轴130，可使油道直接锻压成型，提高生产效率。而且，一套锻压模具可以满足不同偏心量曲轴100需求，使得模具具有非常好的通用性，降低开发费用及制造费用。另外，也免除了采用金属铸造热成型工艺所带来的对环境的污染，对能源的大量消耗。
进一步地，如图7和图8所示，第二曲柄臂140远离第二轴130的一端设有焊接带141，焊接带141用于围设在凹陷部121的外周；第二曲柄臂140通过焊接带141电阻焊焊接在第一曲柄臂120上。
其中，在凹陷部121设置在第一曲柄臂120，以及凹陷部121的开口呈椭圆形的情况下，椭圆形的长轴所对应的两个短圆弧段中，一个短圆弧段能够延伸至第二油道131所在区域，另一个短圆弧段以及椭圆形的短轴所对应的两个长圆弧段包围第一油道111的开口，并在任何偏心位置时均位于焊接带141的内部。
具体地，如图7和图8所示，焊接带141的外轮廓与第二曲柄臂140的外轮廓的形状相同；和/或焊接带141的横截面呈梯形或楔形。通过设定焊接带141的外轮廓与第二曲柄臂140的外轮廓形状相同，便于第二曲柄臂140紧密地连接在第一曲柄臂120上，而不会发生第二曲柄臂140相对于第一曲柄臂120局部翘起的情况。例如，焊接带141位于第二曲柄臂140的边缘处，与第二曲柄臂140的边缘圆角连接，或焊接带141距离第二曲柄臂140的边缘具有一定间距，其中，默认焊接带141包围第四油道的一端开口。另外，通过使焊接带141的横截面呈梯形或楔形，如焊接带141朝向第二轴130的轴线的一侧设置为向外的楔形状，便于通电熔入第一曲柄臂120靠近第二曲柄臂140的一侧，牢固连接第一曲柄臂120和第二曲柄臂140。
具体地，焊接带141面向第一曲柄臂120的端面的宽度大于等于0.2mm。 通过使焊接带141面向第一曲柄臂120的端面的宽度不小于0.2mm，如0.5mm至0.8mm，确保焊接带141能够牢固连接第一曲柄臂120和第二曲柄臂140。
或者进一步地，第一曲柄臂120和第二曲柄臂140通过激光焊焊接在一起。连接方便牢固。
实施例四：
在上述任一实施例的基础上，如图2所示，在第一轴110的任一横截面上，第一油道111各处的壁厚不完全相同。
在该实施例中，通过设定在第一轴110的任一截面上，第一油道111各处的壁厚不完全相同，也即与第一轴110的外表面之间具有相对而言的薄壁处和厚壁处，第一油道111的横截面并非圆形孔，而是如三角形孔、椭圆形孔或葫芦形孔等等，或者第一油道111的横截面为圆形孔，但其圆心偏离第一轴110的轴线。在曲轴100转动的过程中，由于第一油道111在周向上各处壁厚不完全相同，所产生的离心力也不完全相同，使得润滑油能够在离心力的作用下通过壁厚较薄的地方进行上油，进入第一油道111、第二油道131而进行润滑，上油效果好，润滑效果好。与相关技术中为保证上油量和曲轴100的结构强度，将曲轴100的直径设计的较大，从而才能够使油道直径较大，以保证足够的离心力，进而保证上油量相比，可在提高曲轴100上油量和保证结构强度的同时，实现小体积的曲轴100。
进一步地，在第一轴110的任一横截面上，第一油道111呈轴对称结构。通过设计第一油道111在第一轴110的任一横截面上呈轴对称结构，如椭圆形、十字花型等等，可在方便加工第一油道111的同时，保证上油量。
例如，在第一轴110的任一横截面上，第一油道111呈圆孔结构，圆孔结构的圆心偏离第一轴110的轴线。将第一油道111的任一横截面设置为圆孔状，加工方便。
进一步地，如图2所示，在第一轴110的任一横截面上，第一油道111呈轴对称的异形孔结构，如十字花型等。可确保第一油道111壁厚的变化幅度较大，从而确保第一轴110能够产生足够的离心力，引导润滑油上油。
实施例五：
在上述实施例四的基础上，如图2所示，进一步限定在第一轴110的任一横截面上，第一油道111具有薄壁段112和厚壁段113；第二轴130远离薄壁段112所在方向相对于第一轴110的轴线偏心设置。
在该实施例中，设计在第一轴110的任一横截面上均具有薄壁段112和厚壁段113，其中薄壁段112默认为最薄的一段，厚壁段113为壁厚最厚的一段。也即任一薄壁段112的厚度小于任一厚壁段113的厚度。薄壁段112的数量可为一个，也可为多个，同样厚壁段113的数量可为一个，也可为多个。通过使第二轴130远离薄壁段112所在方向相对于第一轴110的轴线偏心设置，也即第二轴130与薄壁段112不位于第一轴110的轴线的同一方位，可避免第二轴130所带来的离心力对第一轴110的薄壁段112造成影响，避免薄壁段112破裂损坏等，保证薄壁段112的结构强度，从而进一步实现小体积的曲轴100具有较高的上油量。
进一步地，第二轴130、薄壁段112相对于第一轴110的轴线的圆心角大于等于90°。也即第二轴130、薄壁段112在第一轴110的任一横截面上的正投影，相对于第一轴110的轴线所对应的圆心角至少为90°。使得第二轴130与薄壁段112相隔足够的距离，有效避免第二轴130相对于第一轴110的偏心运动对第一轴110的薄壁段112造成影响，确保第二轴130薄壁段112的结构强度满足曲轴100的要求。
具体地，第二轴130、薄壁段112相对于第一轴110的轴线的圆心角为90°，以使薄壁段112垂直于往复式压缩机活塞的运动方向。当然，第二轴130、薄壁段112相对于第一轴110的轴线的圆心角也可为120°或180°等。可依据薄壁段112的壁厚及位置而定。
进一步地，如图2所示，薄壁段112的内轮廓为第一圆弧，厚壁段113的内轮廓为第二圆弧，第一圆弧和第二圆弧的开口方向朝向第一轴110的轴线。方便加工，便于润滑油快速上油。另外，通过使第一圆弧和第二圆弧的开口方向朝向第一轴110的轴线，使得第一油道111具有较大的空间，便于更多的润滑油进入第一油道111，提高润滑效果，也方便第一油道111的加工。
或者进一步地，薄壁段112的内轮廓为第三圆弧，厚壁段113的内轮 廓为第四圆弧；第三圆弧和第四圆弧中一个开口方向朝向第一轴110的轴线，另一个开口方向背离第一轴110的轴线。
具体地，薄壁段112的壁厚大于等于0.3mm；和/或第一圆弧的弧长的取值范围为3mm至5mm；和/或第一圆弧所对应的半径与第二圆弧所对应的半径的差值的取值范围为0mm至2mm。通过使薄壁段112的壁厚大于等于0.3mm，如0.4mm至0.5mm，确保薄壁段112具有足够的结构强度。另外，通过使第一圆弧的弧长大于0mm，如在3mm至5mm之间，确保薄壁段112具有足够的上油量。另外，通过使第一圆弧所对应的半径与第二圆弧所对应的半径的差值大于等于0mm，如在1mm至2mm之间，其中若两个半径差值为0，则第一油道111的横截面呈圆孔结构，相对于第一轴110的轴线偏心设置，使得第一轴110转动过程中能够产生足够的离心力引导润滑油上油。
进一步地，如图2所示，第一油道111还具有连接薄壁段112和厚壁段113的过渡段114。通过过渡段114来连接薄壁段112和厚壁段113，可对第一轴110的薄厚变化进行缓冲，提高第一轴110的结构强度。
进一步地，过渡段114包括第一直线，如分别与第一圆弧和第二圆弧相切，当然也可不相切；或者过渡段114包括第一直线和第五圆弧，第一直线通过第五圆弧连接第一圆弧和第二圆弧。
具体地，在第一圆弧与第一直线相交处作第一切线，在第二圆弧与第一直线相交处作第二切线，第一切线与第二切线面向第一轴110内部的夹角大于90°。确保第一油道111内部具有足够的空间，保证上油量。
当然，第一切线与第二切线面向第一轴110内部的夹角也可小于90°。
实施例六：
在上述任一实施例的基础上，如图3所示，进一步限定第一曲柄臂120靠近第一轴110的一端设有凸台122。通过在第一曲柄臂120靠近第一轴110的一端形成有凸台122，便于垫圈的安装定位，进而便于压缩机中轴承的安放，保证轴承与第一轴110的垂直度。
进一步地，通过使凸台122围绕在第一轴110四周，并在凸台122与第一轴110的外轮廓相交处形成有凹槽(图中未示出)，便于稳定支撑轴 承，而且凹槽的存在一方面有利于后续对第一轴110进行精加工，可对刀具进行让位，另一方面与凸台122与第一轴110之间不具有凹槽相比，减小了凸台122的精磨面积，方便凸台122的精磨，节约成本。具体地，凸台122与凹槽相对存在，凹槽的内表面也具有圆弧面，也可具有棱边。
进一步地，凸台122的高度大于0.5mm；和/或凹槽的深度小于等于0.8mm。具体地，凸台122的高度可为1mm、2mm等，凹槽的深度可在0.2mm至0.4mm之间。使得凸台122具有足够的结构强度支撑轴承及转子，凹槽可确保第一轴110的精磨。
进一步地，如图4和图6所示，第一轴110上设有第一油孔115，第一油孔115与第一油道111相连通；第二轴130上设有第二油孔132，第二油孔132与第二油道131相连通。通过在第一轴110上设置与第一油道111相连通的第一油孔115，在第二轴130上设置与第二油道131相连通的第二油孔132，使得润滑油能够经第一油孔115与第二油孔132流出，润滑压缩机的转子等结构。
具体地，第一油孔115的数量为一个或至少两个；第二油孔132的数量为一个或至少两个。
具体地，第一油孔115的直径大于等于1.5mm；第二油孔132的直径大于等于1.5mm。如2mm至4mm。确保润滑油顺利流出。
具体地，第一轴110、第二轴130均为低碳钢轴或合金钢轴。如低碳合金钢，结构强度高，耐磨损。
实施例七：
一种压缩机，包括：如上述实施例中任一项的曲轴100。本实施例提出的压缩机，由于具有上述任一实施例的曲轴100，进而具有上述任一实施例的有益效果，在此不一一赘述。
进一步地，压缩机还包括：壳体、电机、轴承及活塞。壳体的底部具有油池；电机设置在壳体内，电机的转子套设在第一轴110上；轴承套设在第一轴110上，并位于转子与第一曲柄臂120之间；活塞与连杆的一端连接，连杆的另一端与第二轴130相连接。其中，第一轴110能够伸入到油池内，从而润滑油经第一轴110进入第二轴130，实现对曲轴100的润 滑，进而实现对转子、连杆的润滑，提高压缩机的润滑效果，减小磨损，提高压缩机的使用寿命。
进一步地，曲轴100的凸台122的直径大于轴承的滚道直径，如大1mm至2mm，有利于稳定支撑轴承，避免轴承大幅度窜动。
进一步地，第一轴110远离第二轴130的一端设置倒角，倒角的宽度小于第一油道111任一处的壁厚，便于引导转子安装到第一轴110上。
实施例八：
一种制冷设备，包括：如上述实施例中任一项的压缩机。本实施例提供的制冷设备，由于具有上述任一实施例的压缩机，进而具有上述任一实施例的有益效果，在此不一一赘述。
进一步地，制冷设备还包括冷凝器、降压件和蒸发器。压缩机的出口与冷凝器的入口相连通；降压件的入口与冷凝器的出口相连通；蒸发器的入口与降压件的出口相连通，蒸发器的出口与压缩机的入口相连通。实现制冷、制热循环，由于压缩机具有较高的使用寿命，从而有利于保证制冷系统的使用寿明。
具体地，制冷设备为冰箱或空调器等。
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”等术语均应做广义理解，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 (25)

  1. 一种曲轴，其中，所述曲轴包括：
    第一轴；
    第二轴；
    第一曲柄臂，设置在所述第一轴的一端，所述第一曲柄臂上设有第一油道，所述第一油道贯穿所述第一轴；
    第二曲柄臂，设置在所述第二轴的一端，所述第二曲柄臂上设有第二油道，所述第二油道贯穿所述第二轴；
    凹陷部，设置在所述第一曲柄臂远离所述第一轴的端面上或设置在所述第二曲柄臂远离所述第二轴的端面上，所述第二曲柄臂用于与所述第一曲柄臂连接，以使所述凹陷部连通所述第一油道和所述第二油道。
  2. 根据权利要求1所述的曲轴，其中，
    所述凹陷部设置在所述第一曲柄臂远离所述第一轴的端面上，所述第一油道贯穿所述凹陷部的部分底壁。
  3. 根据权利要求1所述的曲轴，其中，
    所述凹陷部设置在所述第二曲柄臂远离所述第二轴的端面上，所述第二油道贯穿所述凹陷部的部分底壁。
  4. 根据权利要求1至3中任一项所述的曲轴，其中，
    所述第二轴相对所述第一轴的轴线在第一方向上偏心设置，所述凹陷部至少部分沿所述第一方向延伸。
  5. 根据权利要求4所述的曲轴，其中，
    所述凹陷部的开口呈椭圆形，所述椭圆形的圆心在所述第一方向上相对于所述第一轴的轴线偏心设置。
  6. 根据权利要求5所述的曲轴，其中，
    所述椭圆形的短轴沿所述第一方向延伸，所述椭圆形的长轴对应两个短圆弧段；
    位于所述第一曲柄臂上的所述两个短圆弧段中，存在一个所述短圆弧段用于延伸至所述第二油道所在区域，或
    位于所述第二曲柄臂上的所述两个短圆弧段中，存在一个所述短圆弧段用于延伸至所述第一油道所在区域。
  7. 根据权利要求1至3中任一项所述的曲轴，其中，
    所述第一曲柄臂与所述第一轴一体成型；
    所述第二曲柄臂与所述第二轴一体成型；
    所述第一曲柄臂与所述第二曲柄臂连接在一起。
  8. 根据权利要求7所述的曲轴，其中，
    所述第一曲柄臂与所述第一轴一体锻压成型；
    所述第二曲柄臂与所述第二轴一体锻压成型；
    所述第一曲柄臂与所述第二曲柄臂电阻焊焊接在一起。
  9. 根据权利要求8所述的曲轴，其中，
    所述第二曲柄臂远离所述第二轴的一端设有焊接带，所述焊接带用于围设在所述凹陷部的外周；
    所述第二曲柄臂通过所述焊接带电阻焊焊接在所述第一曲柄臂上。
  10. 根据权利要求1至3中任一项所述的曲轴，其中，
    在所述第一轴的任一横截面上，所述第一油道各处的壁厚不完全相同。
  11. 根据权利要求10所述的曲轴，其中，
    在所述第一轴的任一横截面上，所述第一油道呈轴对称的异型孔结构；或
    在所述第一轴的任一横截面上，所述第一油道呈圆孔结构，所述圆孔结构的圆心偏离所述第一轴的轴线。
  12. 根据权利要求10所述的曲轴，其中，
    在所述第一轴的任一横截面上，所述第一油道具有薄壁段和厚壁段；
    所述第二轴远离所述薄壁段所在方向相对于所述第一轴的轴线偏心设置。
  13. 根据权利要求12所述的曲轴，其中，
    所述第二轴、所述薄壁段相对于所述第一轴的轴线的圆心角大于等于90°。
  14. 根据权利要求12所述的曲轴，其中，
    所述薄壁段的内轮廓为第一圆弧，所述厚壁段的内轮廓为第二圆弧，所述第一圆弧和所述第二圆弧的开口方向朝向所述第一轴的轴线。
  15. 根据权利要求14所述的曲轴，其中，
    所述薄壁段的壁厚大于等于0.3mm；和/或
    所述第一圆弧的弧长的取值范围为3mm至5mm；和/或
    所述第一圆弧所对应的半径与所述第二圆弧所对应的半径的差值的取值范围为0mm至2mm。
  16. 根据权利要求14所述的曲轴，其中，
    所述第一油道还具有连接所述薄壁段和所述厚壁段的过渡段，所述过渡段的内轮廓具有第一直线；
    在所述第一圆弧与所述第一直线相交处作第一切线，在所述第二圆弧与所述第一直线相交处作第二切线，所述第一切线与所述第二切线面向所述第一轴内部的夹角大于90°。
  17. 根据权利要求12所述的曲轴，其中，
    所述薄壁段的内轮廓为第三圆弧，所述厚壁段的内轮廓为第四圆弧；
    所述第三圆弧和所述第四圆弧中一个开口方向朝向所述第一轴的轴线，另一个开口方向背离所述第一轴的轴线。
  18. 根据权利要求9所述的曲轴，其中，
    所述焊接带的外轮廓与所述第二曲柄臂的外轮廓的形状相同；和/或
    所述焊接带的横截面呈梯形或楔形。
  19. 根据权利要求9所述的曲轴，其中，
    所述焊接带面向所述第一曲柄臂的端面的宽度大于等于0.2mm。
  20. 根据权利要求1至3中任一项所述的曲轴，其中，
    所述第一曲柄臂靠近所述第一轴的一端设有凸台；
    所述凸台围绕在所述第一轴四周，所述凸台与所述第一轴之间形成有凹槽。
  21. 根据权利要求20所述的曲轴，其中，
    所述凸台的高度大于0.5mm；和/或
    所述凹槽的深度小于等于0.8mm。
  22. 根据权利要求1至3中任一项所述的曲轴，其中，
    所述第一轴上设有第一油孔，所述第一油孔与所述第一油道相连通；
    所述第二轴上设有第二油孔，所述第二油孔与所述第二油道相连通。
  23. 根据权利要求22所述的曲轴，其中，
    所述第一油孔的直径大于等于1.5mm；
    所述第二油孔的直径大于等于1.5mm。
  24. 一种压缩机，其中，包括：
    如权利要求1至23中任一项所述的曲轴；
    壳体，所述壳体的底部具有油池；
    电机，设置在所述壳体内，所述电机的转子套设在所述第一轴上；
    轴承，套设在所述第一轴上，并位于所述转子与所述第一曲柄臂之间；
    活塞，所述活塞与连杆的一端相连，所述连杆的另一端与所述第二轴相连接。
  25. 一种制冷设备，其中，包括：
    如权利要求24所述的压缩机；
    冷凝器，所述压缩机的出口与所述冷凝器的入口相连通；
    降压件，所述降压件的入口与所述冷凝器的出口相连通；
    蒸发器，所述蒸发器的入口与所述降压件的出口相连通，所述蒸发器的出口与所述压缩机的入口相连通。
PCT/CN2020/121597 2019-11-22 2020-10-16 曲轴、压缩机及制冷设备 WO2021098423A1 (zh)

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