CN112628118A - Crankshaft mechanism of double-support piston compressor and piston compressor - Google Patents

Crankshaft mechanism of double-support piston compressor and piston compressor Download PDF

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Publication number
CN112628118A
CN112628118A CN202011212834.0A CN202011212834A CN112628118A CN 112628118 A CN112628118 A CN 112628118A CN 202011212834 A CN202011212834 A CN 202011212834A CN 112628118 A CN112628118 A CN 112628118A
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China
Prior art keywords
main shaft
oil
shaft
crankshaft
piston compressor
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CN202011212834.0A
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Chinese (zh)
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CN112628118B (en
Inventor
熊克强
魏会军
严耀宗
申婷
刘皓贤
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Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
    • 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
    • F04B39/14—Provisions for readily assembling or disassembling
    • 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
    • F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention discloses a crankshaft mechanism of a double-support piston compressor and the piston compressor, wherein the crankshaft mechanism comprises a crankshaft body, the crankshaft body comprises a main shaft, an auxiliary balance block, an eccentric shaft, an avoidance section and an auxiliary shaft which are fixedly connected from bottom to top in sequence, the axis of the main shaft is superposed with the axis of the auxiliary shaft, the avoidance section is cylindrical, the upper end of the avoidance section is fixedly connected with the lower end of the auxiliary shaft, and the lower end of the avoidance section is fixedly connected with the upper end of the eccentric shaft. This crankshaft mechanism adopts the cylindrical section of dodging, and its oilhole department minimum thickness is big, does not have the moment of overturning, and intensity promotes, and the operation is reliable, promotes crankshaft mechanism's life-span.

Description

Crankshaft mechanism of double-support piston compressor and piston compressor
Technical Field
The invention relates to the technical field of compressors, in particular to a crankshaft mechanism of a double-support piston compressor and the piston compressor.
Background
The piston compressor is a compressor which can pressurize gas and convey gas by means of reciprocating motion of a piston, and in order to enable the compressor to operate more efficiently and save energy, a double-support technology can be adopted, so that bearing stress can be effectively reduced. The piston compressor with the double-support structure is provided with the avoidance section on the crankshaft, but the avoidance section can cause the deformation of the crankshaft, the strength is reduced, and the service life is influenced. Meanwhile, thinning of the crankshaft is a common means for improving efficiency, but problems such as low-frequency oil supply are likely to occur.
The specific structure of the existing double-support compressor is shown in fig. 1, and the pump body part of the compressor comprises a cylinder block 1, a crankshaft 2, a connecting rod 3, a piston 4, an upper bearing plate 5, an oil guide groove 6, a piston pin 7, an oil pump 8 and the like. When the compressor is operated, the motor rotor 28 drives the crankshaft 2 to rotate at a high speed, and the connecting rod 3 converts the rotation motion of the crankshaft 2 into the reciprocating motion of the piston 4 to push the compressed gas to do work. The relative motion of the oil pump 8 and the crankshaft 2 generates shearing force on the surface of the oil pump 8, so that lubricating oil rises through a central hole of the crankshaft 2 and lubricates various friction components, and the lubricating oil rising to the top of the crankshaft 2 enters a friction pair consisting of the piston 4, the piston pin 7 and the small end of the connecting rod 3 through the oil guide groove 6 to lubricate various moving components. However, the existing double-support compressor has the following defects:
in the conventional crankshaft 2, as shown in fig. 2 to 3, an avoidance section 11 is arranged between an eccentric shaft 9 and an auxiliary shaft 10, the avoidance section 11 is small in thickness and thin in wall surface, and an offset distance exists between the avoidance section 11 and the axis of the auxiliary shaft 10, so that in the operation process of the crankshaft, the overturning moment of the avoidance section 11 is increased, the avoidance section 11 is easily fatigued and broken, and the service life of the crankshaft 2 is affected.
Disclosure of Invention
The invention aims to overcome the existing problems and provides a crankshaft mechanism of a double-support piston compressor, which adopts a cylindrical avoidance section, has large thickness, no overturning moment, improved strength, reliable operation and prolonged service life of the crankshaft mechanism.
Another object of the present invention is to provide a piston compressor comprising the above crank mechanism.
The purpose of the invention is realized by the following technical scheme:
the utility model provides a bent axle mechanism of double bracing piston compressor, includes the bent axle body, the bent axle body includes main shaft, vice balancing piece, eccentric shaft, dodges section and countershaft by fixed connection in proper order from bottom to top, the axis of main shaft with the axis coincidence of countershaft, wherein, dodge the section and be cylindrical, should dodge the upper end of section with countershaft lower extreme fixed connection, the lower extreme and the upper end fixed connection of eccentric shaft.
The working principle of the crankshaft mechanism of the double-support piston compressor is as follows:
the eccentric shaft and the connecting rod are assembled, the big end of the connecting rod penetrates through the auxiliary shaft in the assembling direction, and then the big end of the connecting rod downwards matches with the eccentric shaft through the avoiding section; when the device works, the main shaft and the auxiliary shaft rotate, and the eccentric shaft rotates around the rotation center to drive the connecting rod to move; because the cylindrical avoiding section is arranged between the eccentric shaft and the auxiliary shaft, the minimum thickness of the avoiding section is increased, the strength of the crankshaft body is greatly improved, and the bearing deformation is reduced; in addition, cylindrical dodge to comparing prior art's the section of dodging, thickness is bigger, and no overturning moment, the operation process is reliable, and then improves the running life of bent axle body.
According to a preferable scheme of the invention, an oil guide mechanism for guiding lubricating oil to lubricate the crankshaft body is arranged on the crankshaft body, and the oil guide mechanism comprises a central oil duct arranged inside a main shaft, a main shaft oil outlet hole arranged in the middle of the main shaft, a main shaft oil inlet hole arranged at the upper part of the main shaft, a top oil outlet hole arranged on the top end surface of an auxiliary shaft and an inclined oil duct arranged between the main shaft oil inlet hole and the top oil outlet hole; the main shaft oil outlet hole is communicated with the main shaft oil inlet hole, the lower end of the main shaft oil outlet hole is communicated with the main shaft oil outlet hole, the opening of the central oil duct is located at the bottom of the main shaft, the central oil duct extends upwards along the axis of the main shaft, the main shaft oil outlet hole is communicated with the central oil duct, the inclined oil duct is arranged in an upwards inclined mode, the lower end of the inclined oil duct is communicated with the main shaft oil inlet hole, and the upper end of the inclined oil duct is communicated with the top oil outlet hole. Through setting up above-mentioned mechanism, during operation, lubricating oil gets into from central oil duct, and partial lubricating oil flows out through main shaft oil outlet, lubricates main shaft and cylinder block, and another part lubricating oil upwards gets into the main shaft inlet port through the oil groove, then flows out to the top oil outlet through the centrifugal action of oblique oilhole, and partial lubricating oil is lubricated countershaft and bolster bearing plate from the countershaft oil outlet. The oil guide mechanism provided by the invention can ensure reliable oiling under the condition of low frequency by arranging the inclined oil duct, provides enough lubrication for the crankshaft body, and prolongs the service life of the crankshaft body.
Preferably, an eccentric shaft oil outlet is formed in the eccentric shaft and communicated with the inclined oil duct. This has the advantage that sufficient lubrication can be provided for the eccentric shaft.
Preferably, the axis of the main shaft oil outlet hole is perpendicular to the axial direction of the main shaft oil inlet hole.
Preferably, the oil groove is a spiral oil groove and extends spirally along the surface of the main shaft. Its benefit lies in, through setting up the spiral oil groove, at the in-process that oils, lubricating oil is under the effect of centrifugal force, upwards carries along the spiral oil groove, has guaranteed the reliability that the low frequency oiled.
Preferably, an annular groove is formed in the surface of the main shaft between the main shaft oil outlet and the main shaft oil inlet, and the annular groove is communicated with the oil groove. By providing an annular groove, the lubrication of the main shaft is further improved.
Preferably, the axis of the avoidance section coincides with the axis of the auxiliary shaft, and the lower end of the avoidance section is located on the top end face of the eccentric shaft. By adopting the structure, on one hand, the process difficulty can be reduced, and on the other hand, the lower end of the avoiding section is positioned on the top end face of the eccentric shaft, so that the rotating center of the crankshaft body penetrates through the eccentric shaft, and the overall strength of the crankshaft body can be improved.
Preferably, the length of the avoidance segment is greater than the length of the eccentric shaft. This has the advantage of facilitating the assembly of the connecting rod.
Preferably, the diameter of the eccentric shaft is larger than the diameter of the secondary shaft, which is larger than or equal to the diameter of the bypass section.
Preferably, the avoidance segment is eccentrically connected with the auxiliary shaft, and the eccentric direction faces the eccentric shaft. The avoidance section is eccentrically connected with the auxiliary shaft, namely the rotation center line of the crankshaft body is eccentric with the axis of the avoidance section, so that the thickness between the inclined oil duct and the avoidance section can be increased, the avoidance section is guaranteed to have high strength, the diameter of the eccentric shaft is reduced, and the power consumption of the crankshaft body during working is reduced.
Further, the inclined direction of the inclined oil passage is the same as the eccentric direction of the avoidance section. By adopting the structure, the inclination angle of the inclined oil duct can be further improved, and the low-frequency oiling is facilitated.
A piston compressor comprises the crankshaft mechanism and a connecting rod matched with the crankshaft mechanism.
Compared with the prior art, the invention has the following beneficial effects:
1. according to the crankshaft structure, the cylindrical avoiding section is arranged between the eccentric shaft and the auxiliary shaft, so that the minimum thickness of the avoiding section is increased, the strength of the crankshaft body is greatly improved, and the bearing deformation is reduced; in addition, compared with an avoidance section in the prior art, the cylindrical avoidance pair has no overturning moment and is reliable in operation process, and the operation life of the crankshaft mechanism is further prolonged.
2. In the preferred scheme of the invention, the oil guide mechanism is provided with the inclined oil duct, compared with the vertical oil duct in the prior art, the inclined oil duct can ensure that the oiling is more reliable under the condition of low frequency, so that enough lubrication is provided for the crankshaft body, and the service life of the crankshaft body is prolonged.
Drawings
Fig. 1 is an exploded view of a prior art dual support compressor.
Fig. 2 to 3 are schematic structural views of a crankshaft in the related art, in which fig. 2 is a perspective view, fig. 3 is a sectional view, and arrows in fig. 3 indicate the flow direction of lubricating oil.
Fig. 4-5 are schematic structural views of a first embodiment of a crankshaft mechanism of a double-support piston compressor in the present invention, wherein fig. 4 is a perspective view, fig. 5 is a sectional view, and arrows in fig. 5 indicate a flow direction of lubricating oil.
Fig. 6 is a partially enlarged view of fig. 5.
Fig. 7 is a schematic perspective view of a piston compressor according to the present invention.
Fig. 8-9 are schematic structural views of another embodiment of a crankshaft mechanism of a double-support piston compressor in the present invention, wherein fig. 8 is a perspective view, fig. 9 is a sectional view, and arrows in fig. 9 indicate the flow direction of lubricating oil.
Fig. 10 is a schematic structural diagram of a third embodiment of a crankshaft mechanism of a double-support piston compressor in the invention.
Detailed Description
In order to make those skilled in the art understand the technical solutions of the present invention well, the following description of the present invention is provided with reference to the embodiments and the accompanying drawings, but the embodiments of the present invention are not limited thereto.
Example 1
Referring to fig. 4-6, the present embodiment discloses a crankshaft mechanism of a dual-support piston compressor, which includes a crankshaft body and an oil guide mechanism disposed on the crankshaft body for guiding lubricating oil to lubricate the crankshaft body.
Referring to fig. 4 to 6, the crankshaft body includes a main shaft 13, an auxiliary balance block 14, an eccentric shaft 15, an avoidance section 16 and an auxiliary shaft 17, which are fixedly connected in sequence from bottom to top, an axis of the main shaft 13 coincides with an axis of the auxiliary shaft 17, the eccentric shaft 15 and the auxiliary balance block 14 are respectively located at two sides of a rotation center of the crankshaft body, wherein the avoidance section 16 is cylindrical, an upper end of the avoidance section 16 is fixedly connected with a lower end of the auxiliary shaft 17, and a lower end of the avoidance section is fixedly connected with an upper end of the eccentric shaft 15.
Referring to fig. 4-6, the axis of the avoidance segment 16 coincides with the axis of the auxiliary shaft 17, that is, the center of the avoidance segment coincides with the rotation center of the crankshaft body, and the lower end of the avoidance segment 16 is located on the top end face of the eccentric shaft 15. By adopting the structure, on one hand, the process difficulty can be reduced, and on the other hand, the lower end of the avoiding section 16 is positioned on the top end surface of the eccentric shaft 15, so that the rotation center of the crankshaft body penetrates through the eccentric shaft 15, and the overall strength of the crankshaft body can be improved.
Referring to fig. 4, the length of the bypass section 16 is greater than that of the eccentric shaft 15, i.e., H1 > H2, wherein H1 is the length of the bypass section 16, and H2 is the length of the eccentric shaft 15. This has the advantage of facilitating the assembly of the connecting rod.
Referring to FIG. 6, the diameter of the eccentric shaft 15 is larger than that of the auxiliary shaft 17, and the diameter of the auxiliary shaft 17 is larger than or equal to that of the avoidance section 16, i.e. D3 > D1 ≧ D2, where D3 is the diameter of the eccentric shaft 15, D1 is the diameter of the auxiliary shaft 17, and D2 is the diameter of the avoidance section 16.
Referring to fig. 4-6, an oil guiding mechanism for guiding lubricating oil to lubricate the crankshaft body is disposed on the crankshaft body, and the oil guiding mechanism includes a central oil passage 18 disposed inside the main shaft 13, a main shaft oil outlet 19 disposed in the middle of the main shaft 13, a main shaft oil inlet 20 disposed on the upper portion of the main shaft 13, a top oil outlet 21 disposed on the top end surface of the auxiliary shaft 17, and an inclined oil passage 22 disposed between the main shaft oil inlet 20 and the top oil outlet 21; an oil groove 23 is formed in the surface of the main shaft 13 between the main shaft oil outlet 19 and the main shaft oil inlet 20, the upper end of the oil groove 23 is communicated with the main shaft oil inlet 20, the lower end of the oil groove 23 is communicated with the main shaft oil outlet 19, the opening of the central oil passage 18 is located at the bottom of the main shaft 13, the central oil passage 18 extends upwards along the axis of the main shaft 13, the main shaft oil outlet 19 is communicated with the central oil passage 18, the inclined oil passage 22 is obliquely arranged upwards, the lower end of the inclined oil passage 22 is communicated with the main shaft oil inlet 20, and the upper end of the inclined oil passage 22 is communicated with the top oil. By the arrangement of the mechanism, when the lubricating oil lubricating mechanism works, lubricating oil enters from the central oil passage 18, part of the lubricating oil flows out through the main shaft oil outlet 19 to lubricate the main shaft 13 and the cylinder block, the other part of the lubricating oil upwards enters the main shaft oil inlet 20 through the oil groove 23 and then flows out to the top oil outlet 21 through the centrifugal action of the inclined oil hole, and part of the lubricating oil lubricates the auxiliary shaft 17 and the upper bearing plate from the auxiliary shaft oil outlet 25. As shown in fig. 3, the oil passage 12 of the conventional crankshaft 2 is vertically disposed upward along the crankshaft 2, and when the frequency is low, the oil supply to the upper bearing plate 5 and the piston 4 is insufficient, which affects the lubrication of the crankshaft 2 and the piston 4, thereby reducing the service life of the crankshaft 2 and the piston 4 and increasing the energy consumption. The oil guide mechanism of the invention can ensure reliable oiling under the condition of low frequency by arranging the inclined oil duct 22, provides enough lubrication for the crankshaft body and prolongs the service life of the crankshaft body.
Referring to fig. 4 to 6, the axis of the top oil outlet hole 21 coincides with the axis of the oblique oil passage 22. This has the advantage of facilitating the transport of the lubricating oil.
Referring to fig. 6, the inclined oil passage 22 is inclined at an angle θ of 1 to 10 °; the minimum thickness h1 between the avoidance section 16 and the inclined oil passage 22 is more than or equal to 1 mm.
Referring to fig. 4 and 5, the eccentric shaft 15 is provided with an eccentric shaft oil outlet hole 24, and the eccentric shaft oil outlet hole 24 is communicated with the inclined oil passage 22. This has the advantage that sufficient lubrication can be provided for the eccentric shaft 15.
Further, the middle portion of the auxiliary shaft 17 is provided with an auxiliary shaft oil outlet hole 25, and the auxiliary shaft oil outlet hole 25 is communicated with the inclined oil passage 22, which is beneficial to providing sufficient lubrication for the auxiliary shaft 17 and the upper bearing plate.
Referring to fig. 4 and 5, the axis of the spindle oil outlet 19 is perpendicular to the axial direction of the spindle oil inlet 20; the oil groove 23 is a spiral oil groove and extends spirally along the surface of the main shaft 13. Its benefit lies in, through setting up spiral oil groove, at the in-process that oils, lubricating oil is under the effect of shearing force, upwards carries along spiral oil groove, has guaranteed the reliability that the low frequency oiled.
Referring to fig. 4 and 5, the surface of the main shaft 13 is provided with an annular groove 26 between the main shaft oil outlet hole 19 and the main shaft oil inlet hole 20, and the annular groove 26 communicates with the oil groove 23. By providing the annular groove 26, the fitting area is reduced, thereby reducing frictional power consumption.
Referring to fig. 4 to 6, the working principle of the crankshaft mechanism of the double-support piston compressor is as follows:
the eccentric shaft 15 is assembled with the connecting rod, the big end of the connecting rod penetrates through the auxiliary shaft 17 in the assembling direction, and then the big end of the connecting rod downwards matches with the eccentric shaft 15 through the avoiding section 16; when the device works, the main shaft 13 and the auxiliary shaft 17 rotate, and the eccentric shaft 15 rotates around the rotation center to drive the connecting rod to move; because the cylindrical avoiding section 16 is arranged between the eccentric shaft 15 and the auxiliary shaft 17, and the rotating center is superposed with the center of the avoiding section, the minimum thickness of the thin wall of the oil hole of the avoiding section 16 is increased, the strength of the crankshaft body is greatly improved, and the bearing deformation is reduced; in addition, cylindrical dodge to comparing prior art's the section of dodging, oilhole department minimum thickness is bigger, and no overturning moment, the operation process is reliable, and then improves the running life of bent axle body.
Referring to fig. 7, the present embodiment further discloses a piston compressor, which includes the above-mentioned crankshaft mechanism and a connecting rod, wherein the connecting rod is connected with the eccentric shaft in a matching manner.
Example 2
Referring to fig. 8 to 9, the other structure of the present embodiment is the same as that of embodiment 1, except that the bypass section 16 is eccentrically connected to the secondary shaft 17, and an eccentricity h3 exists between the bypass section 16 and the secondary shaft 17, and the eccentricity is toward the eccentric shaft 15. Because the avoidance section 16 is eccentrically connected with the auxiliary shaft 17, namely the rotation center line of the crankshaft body is eccentric to the axis of the avoidance section 16, the thickness between the inclined oil passage 22 and the avoidance section 16 can be increased, so that the avoidance section 16 has high strength, and the diameter D30 of the eccentric shaft 15 is reduced under the condition that the eccentricity h3 is not changed, so that the requirement that D30 is D3-2 × h3 is met, and the reduction of the power consumption of the crankshaft body during working is facilitated.
Further, the inclined direction of the inclined oil passage 22 is the same as the eccentric direction of the avoidance segment 16. By adopting the structure, the inclination angle of the inclined oil channel 22 can be further improved, and the low-frequency oiling is more facilitated.
Example 3
Referring to fig. 10, the other structure of the present embodiment is the same as that of embodiment 1, except that the auxiliary shaft 17 is directly fixedly connected with the eccentric shaft 15, i.e., the avoidance segment 16 is eliminated. Therefore, the connecting rod is very simple to assemble, the strength of the crankshaft is high, the low-frequency oiling is reliable, the height H3 of the crankshaft body is reduced, and the compressor can be more miniaturized.
The present invention is not limited to the above embodiments, and any other changes, modifications, substitutions, combinations, and simplifications which do not depart from the spirit and principle of the present invention should be construed as equivalents and are included in the scope of the present invention.

Claims (10)

1. The crankshaft mechanism of the double-support piston compressor comprises a crankshaft body, wherein the crankshaft body comprises a main shaft, an auxiliary balance block, an eccentric shaft, an avoiding section and an auxiliary shaft which are sequentially and fixedly connected from bottom to top, the axis of the main shaft is overlapped with the axis of the auxiliary shaft, and the crankshaft mechanism is characterized in that the avoiding section is cylindrical, the upper end of the avoiding section is fixedly connected with the lower end of the auxiliary shaft, and the lower end of the avoiding section is fixedly connected with the upper end of the eccentric shaft.
2. The crankshaft mechanism of a dual supporting piston compressor as claimed in claim 1, wherein the crankshaft body is provided with an oil guiding mechanism for guiding a lubricating oil to lubricate the crankshaft body, the oil guiding mechanism includes a central oil passage provided inside the main shaft, a main shaft oil outlet provided in the middle of the main shaft, a main shaft oil inlet provided in the upper portion of the main shaft, a top oil outlet provided in the top end surface of the auxiliary shaft, and an inclined oil passage provided between the main shaft oil inlet and the top oil outlet; the main shaft oil outlet hole is communicated with the main shaft oil inlet hole, the lower end of the main shaft oil outlet hole is communicated with the main shaft oil outlet hole, the opening of the central oil duct is located at the bottom of the main shaft, the central oil duct extends upwards along the axis of the main shaft, the main shaft oil outlet hole is communicated with the central oil duct, the inclined oil duct is arranged in an upwards inclined mode, the lower end of the inclined oil duct is communicated with the main shaft oil inlet hole, and the upper end of the inclined oil duct is communicated with the top oil outlet hole.
3. The crank mechanism of a dual supporting piston compressor as claimed in claim 2, wherein the axis of the main shaft oil outlet is perpendicular to the axial direction of the main shaft oil inlet; the oil groove is a spiral oil groove and extends spirally along the surface of the main shaft.
4. The crank mechanism of a double-supported piston compressor as claimed in claim 2 or 3, wherein the surface of the main shaft is provided with an annular groove between the main shaft oil outlet hole and the main shaft oil inlet hole, the annular groove communicating with the oil groove.
5. A crank mechanism of a double-support piston compressor as claimed in any one of claims 1 to 3, wherein the axis of the bypass section coincides with the axis of the secondary shaft, and the lower end of the bypass section is located on the top end surface of the eccentric shaft.
6. The crankshaft mechanism of a dual support piston compressor as claimed in claim 5, wherein the length of the bypass section is greater than the length of the eccentric shaft.
7. The crank mechanism of a dual support piston compressor of claim 5, wherein the diameter of the eccentric shaft is larger than the diameter of the secondary shaft, which is larger than or equal to the diameter of the bypass section.
8. A crank mechanism of a double-support piston compressor according to any one of claims 1 to 3, characterized in that the bypass section is eccentrically connected to the secondary shaft, and the eccentric direction is toward the eccentric shaft.
9. The crank mechanism of a dual supporting piston compressor as claimed in claim 8, wherein the inclined direction of the inclined oil passage is the same as the eccentric direction of the bypass section.
10. A piston compressor, characterized by comprising a crank mechanism according to any one of claims 1 to 9 and a connecting rod cooperating with the crank mechanism.
CN202011212834.0A 2020-11-03 2020-11-03 Crankshaft mechanism of double-support piston compressor and piston compressor Active CN112628118B (en)

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CN112628118B CN112628118B (en) 2022-07-29

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113700634A (en) * 2021-09-18 2021-11-26 珠海格力节能环保制冷技术研究中心有限公司 Cam crankshaft mechanism and piston compressor
CN117847197A (en) * 2024-03-05 2024-04-09 浙江安吉华意科技有限公司 Crankshaft transmission structure and processing method

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