A compressor crankshaft with synergistic lubrication and a compressor

Abstract

The utility model provides a kind of compressor crankshaft and compressor of collaborative lubrication, it is related to compressor field, to the current crankshaft fan leaf flung out limited coverage of refrigerating machine oil, it is difficult to effectively lubricate the position of the active position of the position of fan leaf flush and below, fan leaf oil channel and auxiliary oil channel are set up on fan leaf, especially the first oil channel and the second oil channel and the orifice design of staggered distribution that intersect in auxiliary oil channel, change the flung out path and coverage of refrigerating machine oil, refrigerating machine oil can not only be flung out from fan leaf top end face, but also can be flung out from fan leaf side circumferential surface, and using staggered distribution increases its coverage along axial direction, so that refrigerating machine oil can more widely cover to the active component of the position of fan leaf flush and the position below fan leaf, such as piston and connecting rod small head end cooperation position, piston and cylinder wall etc., strengthen the lubrication of these parts, reduce the wear between piston ring and cylinder wall.

Description

Technical Field

[0001] This utility model relates to the field of compressors, specifically to a compressor crankshaft and compressor with synergistic lubrication. Background Technology

[0002] In a refrigerator compressor, the crankshaft converts the rotation of the motor into the reciprocating motion of the piston, and the cylinder block provides radial support for the crankshaft. The rotating surfaces between the cylinder block and the crankshaft require lubrication, as do the mating surfaces between the connecting rod and the piston pin, and between the connecting rod and the crankshaft eccentric shaft. Insufficient lubrication can lead to increased frictional power consumption.

[0003] Currently, crankshafts are equipped with a single main shaft oil passage, which delivers refrigerant oil from the crankshaft to the eccentric shaft and fan blade positions. At the eccentric shaft position, the refrigerant oil lubricates the mating position between the eccentric journal and the big end of the connecting rod. At the fan blade position, the fan blade oil passage extends to the top of the fan blade to form an opening. The refrigerant oil thrown out from the opening at the top of the fan blade lubricates the mating position between the small end of the connecting rod and the piston pin. However, the refrigerant oil thrown out from the top of the fan blade is mostly distributed above the top end face of the fan blade, with a limited coverage area. It is not easy to lubricate the moving positions flush with the fan blade and below the fan blade, resulting in insufficient lubrication at the mating position between the piston and the small end of the connecting rod, and between the piston and the cylinder wall, which aggravates the wear between the piston rings and the cylinder wall.

[0004] In addition, the mating position of the crankshaft main journal and the cylinder seat bore depends on the splash lubrication of the crankshaft main oil passage. A single crankshaft center oil passage is difficult to achieve continuous oil supply, and the oil film is prone to breakage, resulting in an increase in the metal contact area at the mating position and an increase in the wear rate. At the same time, the oil supply capacity of a single crankshaft main oil passage is insufficient, and the fan blade oil passage and the eccentric shaft position cannot obtain enough refrigeration oil, affecting the overall lubrication effect. Utility Model Content

[0005] The purpose of this invention is to address the deficiencies of existing technologies by providing a compressor crankshaft and compressor with synergistic lubrication. The invention features fan blade oil passages and auxiliary oil passages on the fan blades, particularly the intersecting first and second oil passages in the auxiliary oil passages and the staggered orifice design. This alters the path and coverage of the refrigeration oil, allowing it to be ejected not only from the top end face of the fan blades but also from the side circumference. The staggered distribution increases its axial coverage, enabling the refrigeration oil to more extensively cover moving parts flush with and below the fan blades, such as the piston and connecting rod small end mating area, and the piston and cylinder wall. This enhances lubrication in these areas and reduces wear between the piston rings and cylinder wall.

[0006] The primary objective of this invention is to provide a compressor crankshaft with synergistic lubrication, employing the following solution:

[0007] It includes an eccentric shaft, a fan blade, and a main shaft arranged in sequence. The outer circumference of the main shaft is provided with a spiral oil groove. The fan blade is provided with a fan blade oil passage and an auxiliary oil passage. The fan blade oil passage is connected to the spiral oil groove. The auxiliary oil passage includes a first oil passage and a second oil passage that intersect. The two ends of the first oil passage extend to the outer circumferential wall of the fan blade to form a first orifice and a second orifice, respectively. One end of the second oil passage is connected to the fan blade oil passage, and the other end extends to the outer circumferential wall of the fan blade to form a third orifice. The first orifice, the second orifice, and the third orifice are staggered in the axial direction of the main shaft.

[0008] Furthermore, one end of the fan blade oil passage extends to the top surface of the fan blade, and the other end extends to the main shaft and connects to the spiral oil groove.

[0009] Furthermore, along the axis of the main shaft from the main shaft to the fan blades, the flow direction of the refrigeration oil in the second oil passage forms an acute angle with the axis of the main shaft.

[0010] Furthermore, the axis of the first oil passage is inclined relative to the tip surface of the fan blade.

[0011] Furthermore, the axis of the second oil passage is radially coplanar with the main shaft at its location, and the axes of the first and second oil passages are perpendicular.

[0012] Furthermore, the sum of the diameters of the first, second, and third orifices is equal to the axial thickness of the fan blade, so that the refrigeration oil ejected from the auxiliary oil passage covers the axial thickness range of the fan blade.

[0013] Furthermore, an eccentric shaft oil passage is provided inside the eccentric shaft, and an annular oil groove is provided on the outer circumference of the eccentric shaft. The eccentric oil passage connects the annular oil groove and the spiral oil groove.

[0014] Furthermore, one end of the eccentric shaft oil passage extends to the outer circumferential surface of the eccentric shaft to connect with the annular oil groove, and the other end passes through the fan blade and extends into the main shaft to connect with the spiral oil groove.

[0015] Furthermore, the main shaft has two spiral oil grooves, which are staggered upwards along the outer circumference of the main shaft.

[0016] The second objective of this invention is to provide a compressor that utilizes a compressor crankshaft with synergistic lubrication as described in the first objective.

[0017] Compared with the prior art, the advantages and positive effects of this utility model are:

[0018] To address the current issue of limited coverage of refrigeration oil ejected from crankshaft fan blades, which makes it difficult to effectively lubricate moving parts flush with and below the fan blades, the design incorporates fan blade oil channels and auxiliary oil channels on the fan blades. In particular, the intersecting first and second auxiliary oil channels, along with the staggered orifice design, alter the oil ejection path and coverage area. Refrigeration oil can now be ejected not only from the top end face of the fan blades but also from the side circumference. The staggered distribution further increases its axial coverage, allowing for broader coverage of moving parts flush with and below the fan blades, such as the piston and connecting rod small end mating area and the piston-cylinder wall. This enhances lubrication in these areas and reduces wear between piston rings and cylinder walls. Furthermore, the synergistic effect of the spiral oil grooves with the fan blade oil channels and auxiliary oil channels improves overall oil supply capacity, ensuring that the eccentric shaft and fan blade oil channels receive more refrigeration oil. This further enhances the lubrication of the compressor crankshaft, ensuring normal compressor operation and extending its service life.

[0019] An annular oil groove is formed on the outer circumference of the eccentric shaft, and the eccentric oil passage connects the annular oil groove and the spiral oil groove. When the oil flows from the spiral oil groove through the eccentric shaft oil passage to the annular oil groove, the circumferential continuous structure of the annular oil groove allows the oil to be evenly distributed on the surface of the eccentric shaft journal.

[0020] Two staggered spiral oil grooves on the main shaft enhance the oil supply capacity through dual parallel paths. Each spiral oil groove independently generates a dynamic pressure oil film. The staggered distribution makes the oil supply areas of the two oil grooves complementary in the circumferential direction. At the same time, the spiral directions of the two oil grooves are the same, ensuring the consistency of the oil delivery direction and avoiding mutual interference of fluids. Attached Figure Description

[0021] The accompanying drawings, which form part of this specification, are used to provide a further understanding of this utility model. The illustrative embodiments of this utility model and their descriptions are used to explain this utility model and do not constitute an improper limitation of this utility model.

[0022] Figure 1 This is a schematic diagram of the oil passage inside the fan blades of a compressor crankshaft that provides synergistic lubrication in one or more embodiments of the present invention.

[0023] Figure 2 This is a schematic diagram of the eccentric shaft of the compressor crankshaft that provides synergistic lubrication in one or more embodiments of the present invention.

[0024] Figure 3 This is a schematic diagram of the main shaft of a compressor crankshaft that is synergistically lubricated in one or more embodiments of the present invention.

[0025] Among them, 1. Eccentric shaft; 2. Annular oil groove; 3. Fan blade; 4. Third orifice; 5. First orifice; 6. Main shaft; 7. Spiral oil groove; 8. Second orifice. Detailed Implementation

[0026] Example 1

[0027] In a typical embodiment of this utility model, such as Figures 1-3 As shown, a compressor crankshaft with synergistic lubrication is presented.

[0028] Existing refrigerator compressor crankshafts have a single main shaft with six oil passages. The refrigerant oil ejected from the top of the fan blades (3) is distributed only above the top surface of the fan blades (3), resulting in limited coverage. This makes it difficult to effectively lubricate the moving parts flush with and below the fan blades (3), leading to insufficient lubrication at the piston and connecting rod small end mating area and between the piston and cylinder wall, thus exacerbating wear between the piston rings and cylinder wall. Therefore, this embodiment provides a compressor crankshaft with synergistic lubrication. The fan blades (3) have their own oil passages and auxiliary oil passages. In particular, the intersecting first and second oil passages in the auxiliary oil passages, along with the staggered orifice design, change the ejection path and coverage of the refrigerant oil, allowing it to more broadly cover the moving parts flush with and below the fan blades (3).

[0029] like Figures 1-3 As shown, the compressor crankshaft with synergistic lubrication includes an eccentric shaft 1, a fan blade 3, and a main shaft 6 arranged sequentially. A spiral oil groove 7 is provided on the outer circumference of the main shaft 6, and the fan blade 3 has an oil passage and an auxiliary oil passage. The oil passage of the fan blade 3 connects to the spiral oil groove 7, and the auxiliary oil passage consists of an intersecting first oil passage and a second oil passage. The first oil passage extends to the outer circumferential wall of the fan blade 3 at both ends, forming a first orifice 5 and a second orifice 8, respectively. One end of the second oil passage connects to the oil passage of the fan blade 3, and the other end extends to the outer circumferential wall of the fan blade 3, forming a third orifice 4. The first orifice 5, the second orifice 8, and the third orifice 4 are staggered upwards along the main shaft 6.

[0030] By setting a spiral oil groove 7 on the outer circumferential surface of the main shaft 6, the centrifugal force during crankshaft rotation and the guiding effect of the spiral structure can be used to more effectively transport refrigeration oil, increase the oil supply and continuity, thereby improving the lubrication of the crankshaft main shaft 6 journal and the cylinder seat shaft hole mating position, reducing direct metal contact caused by oil film breakage, and reducing the wear rate.

[0031] The oil passages and auxiliary oil passages on the fan blade 3, especially the intersecting first and second oil passages in the auxiliary oil passages and the staggered orifice design, change the ejection path and coverage of the refrigeration oil.

[0032] Specifically, such as Figure 1As shown, the oil passage of fan blade 3 adopts a through structure, directly connecting to the spiral oil groove 7 of the main shaft 6, forming the main oil supply path from the main shaft 6 to fan blade 3. The auxiliary oil passage has a cross structure, with the first oil passage and the second oil passage intersecting perpendicularly to form a three-dimensional oil network. The first oil passage serves as a transverse through channel, with its two ends of orifices staggered on the outer peripheral wall of fan blade 3. The refrigerant oil in the first oil passage can be supplied through the second oil passage, and the oil is thrown out in a fan shape from the two orifices by the centrifugal force of the crankshaft rotation. The second oil passage serves as a longitudinal drainage channel, with one end connected to the oil passage of fan blade 3, and the third orifice 4 at the other end set on the outer peripheral wall of the middle part of fan blade 3, forming an axial height difference with the orifice of the first oil passage. The spatial staggered layout breaks the limitation of the traditional single opening at the top of fan blade 3, and forms a three-dimensional lubrication coverage area through multi-directional oil injection.

[0033] The oil passage of the fan blade 3 divides the oil into two paths. One path is directly thrown out from the third orifice 4 through the second oil passage. Since the orifice is lower than the top of the fan blade 3, the oil is thrown out and, due to the combined effect of gravity and centrifugal force, it covers the piston pin and connecting rod small end mating surface below the fan blade 3. The other path is thrown out from the two orifices through the first oil passage, forming a horizontal fan-shaped oil curtain that covers the piston and cylinder wall area that is flush with the fan blade 3.

[0034] The three orifices are staggered axially, configured such that the first orifice 5, the third orifice 4, and the second orifice 8 are sequentially distributed along the axial direction, resulting in different spray angles and ranges when the oil is ejected. The oil from the first orifice 5 and the third orifice 4, being positioned higher, primarily covers the sides and upper areas of the fan blade 3; the oil from the second orifice 8, being positioned lower, extends its spray trajectory downwards, filling the lubrication blind spot below the fan blade 3 in traditional designs, achieving full coverage from the top of the fan blade 3 to the cylinder wall. This axial staggered arrangement of the three orifices achieves "space-for-coverage," utilizing the superposition effect of fluid spray trajectories to expand the coverage range without increasing the kinetic energy loss of individual orifices. It transforms the concentrated weakening effect of large orifices into the dispersed weakening effect of multiple small orifices, while simultaneously maintaining structural rigidity through the supporting effect of the material between the orifices.

[0035] This allows the refrigeration oil to more widely cover the moving parts flush with and below the fan blade 3, such as the piston and connecting rod small end mating area, and the piston and cylinder wall, enhancing lubrication in these areas and reducing wear between the piston rings and cylinder wall. The synergistic effect of the spiral oil groove 7 with the oil passages and auxiliary oil passages of the fan blade 3 improves the overall oil supply capacity, ensuring that the eccentric shaft 1 and the oil passages of the fan blade 3 receive more refrigeration oil, further enhancing the lubrication of the compressor crankshaft, ensuring the normal operation of the compressor, and extending its service life.

[0036] It should be noted that, compared to directly opening large-diameter auxiliary oil channels on the fan blade 3, this embodiment uses three staggered small holes, namely the first hole 5, the second hole 8, and the third hole 4. Through spatial topology reconstruction, the "fan-shaped jet" of a single hole is transformed into a "three-dimensional matrix jet" of three holes. Traditional large-diameter openings cover the axial range by expanding the jet angle of a single hole. However, due to the limitations of fluid diffusion laws, the larger the hole diameter, the faster the kinetic energy of the oil is thrown out. The actual coverage length has a non-linear relationship with the hole diameter. The small-diameter design allows for a higher flow velocity of the oil when it is thrown out, reducing kinetic energy loss.

[0037] Furthermore, considering structural strength, if a large hole of diameter D is opened as an auxiliary oil passage, the reduction in the axial cross-sectional area of ​​fan blade 3 will be related to D. 2 Proportional to the thickness of the blade, when D exceeds 1 / 3 of the blade thickness, its bending strength may decrease by more than 40%. The total cross-sectional area of ​​the three staggered holes is typically only 1 / 2 to 2 / 3 of the area of ​​the large hole (e.g., the total area of ​​three φ1mm holes is 2.36mm²). 2 3.14mm, smaller than a φ2mm hole 2 The weakening of the 3-section of the fan blade is significantly reduced.

[0038] The staggered arrangement of the three small holes avoids stress concentration. Traditional large holes form a ring-shaped high-stress zone around them, while the dispersed small holes make the stress distribution more uniform. According to the theory of elasticity, the stress concentration coefficient of multiple small holes is much lower than that of a single large hole, which can increase the fatigue life of the fan blade by more than 50%.

[0039] One end of the oil passage in fan blade 3 extends to the top surface of fan blade 3, and the other end extends to the main shaft 6 and connects to the spiral oil groove 7, forming a direct channel from the spiral oil groove 7 to the top of fan blade 3. Utilizing the centrifugal force gradient during crankshaft rotation, the oil at the main shaft 6 experiences less centrifugal force, while the top of fan blade 3 experiences the greatest centrifugal force, creating a natural pressure difference that drives the oil flow. When the oil reaches the top surface from the spiral oil groove 7 through the oil passage in fan blade 3, the centrifugal force causes it to be thrown out radially, forming a three-dimensional supplement with the multi-directional spray from the auxiliary oil passage. This solves the problem of the traditional fan blade 3 oil passage relying solely on the top opening for oil throwing, achieving bidirectional oil supply through axial penetration, i.e., top surface throwing combined with auxiliary oil passage spray.

[0040] Along the axis of the main shaft 6 from the fan blade 3, the flow direction of the refrigeration oil in the second oil passage forms an acute angle with the axis of the main shaft 6. When the oil flows out of the third orifice 4 along the acute angle, its velocity vector can be decomposed into an axial component and a radial component. The axial component gives the oil downward jetting kinetic energy, covering the piston pin area below the fan blade 3; the radial component maintains the centrifugal diffusion tendency of the oil, ensuring that the oil can effectively adhere to the cylinder wall. This angle range can be configured to 30°-45°. In other optional embodiments, an angle range of less than 30° or greater than 45° can also be used to achieve the best balance between the two components, avoiding insufficient oil jet range due to an excessively large angle or weakened downward coverage due to an excessively small angle.

[0041] The first oil passage axis is inclined relative to the top surface of the fan blade 3, so that the first orifice 5 and the second orifice 8 are naturally axially misaligned at both ends, and the trajectory of the oil ejection can also be controlled. The top surface is defined as the reference plane. The inclined first oil passage will cause the oil to be ejected from the first and second orifices 8 to have a pitch angle, forming a parabolic spray coverage area. This breaks the limitations of traditional vertical openings. When the oil is ejected at an inclined angle, its coverage area in the axial direction of the fan blade 3 is significantly extended. It can simultaneously cover the small end of the connecting rod above the fan blade 3 and the transition area of ​​the cylinder wall below. Especially when the crankshaft rotates at high speed, the inclined sprayed oil maintains a longer flight trajectory due to inertia, enhancing the dynamic lubrication effect.

[0042] The first oil passage is perpendicular to the axis of the second oil passage, and the second oil passage is radially coplanar with the main shaft 6. The second oil passage is distributed radially along the main shaft 6 to maximize the radial kinetic energy of the oil when it is thrown out of the third orifice 4, so that it can effectively penetrate the gap between the piston and the cylinder wall. The first oil passage, which is perpendicular to the second oil passage, provides a lateral injection component. The combined injection vector of the two forms a cross-shaped coverage area. The spatial orthogonal distribution allows the oil in the auxiliary oil passage to simultaneously form a lubrication coverage in the radial direction (cylinder wall), axial direction (piston pin), and circumferential direction (side of fan blade 3), which is an upgrade in coverage dimension compared to the one-dimensional injection of the traditional single oil passage.

[0043] The sum of the diameters of the first orifice 5, the second orifice 8, and the third orifice 4 is equal to the axial thickness of the fan blade 3. Assuming the thickness of the fan blade 3 is H, and the sum of the total diameters of the three orifices is H, when the oil is thrown out from the orifices, its coverage length in the axial direction of the fan blade 3 is approximately equal to H (ignoring the oil diffusion angle), which just covers the entire axial thickness range of the fan blade 3. This avoids the problem of insufficient coverage due to the total diameter of the orifices being too small, or the problem of excessive oil spraying and weakened kinetic energy due to the total diameter of the orifices being too large. The oil thrown out from the auxiliary oil passage can form a continuous oil curtain in the axial direction of the fan blade 3, ensuring that the piston is always within the lubrication coverage range when it is moving.

[0044] Furthermore, the mating position between the crankshaft main shaft journal 6 and the cylinder seat bore relies on splash lubrication from a single crankshaft main shaft oil passage 6. This method makes continuous oil supply difficult, and the oil film is prone to breakage, leading to an increase in the metal-to-metal contact area at the mating position and a higher wear rate. Based on this, if... Figure 2 As shown, an oil passage is provided inside the eccentric shaft 1, and an annular oil groove 2 is provided on the outer circumference of the eccentric shaft 1. The eccentric oil passage connects the annular oil groove 2 and the spiral oil groove 7. When the oil flows from the spiral oil groove 7 through the oil passage of the eccentric shaft 1 to the annular oil groove 2, the continuous circumferential structure of the annular oil groove 2 allows the oil to be evenly distributed on the surface of the eccentric shaft 1 neck. The main oil supply path of the spiral oil groove 7 and the branch paths of the oil passage of the eccentric shaft 1 form a parallel oil supply network, increasing the oil supply to the mating surface between the eccentric shaft 1 neck and the big end of the connecting rod. At the same time, the annular oil groove 2 uses centrifugal force to evenly throw the oil out along the circumference, avoiding the local lubrication blind spots caused by traditional single-point oil supply.

[0045] Meanwhile, the insufficient oil supply capacity of the single crankshaft main shaft 6 makes it difficult for the fan blade 3 oil passage and the eccentric shaft 1 to obtain enough refrigeration oil, affecting the overall lubrication effect. Two staggered spiral oil grooves 7 on the main shaft 6 improve the oil supply capacity through dual parallel paths. Each spiral oil groove 7 independently generates a dynamic pressure oil film. The staggered distribution makes the oil supply areas of the two oil grooves complementary in the circumferential direction. At the same time, the spiral direction of the two oil grooves is the same, ensuring the consistency of the oil delivery direction and avoiding mutual interference of fluids.

[0046] In this embodiment, the crankshaft is forged from ductile iron (QT500-7), which has high strength (tensile strength ≥500MPa) and good wear resistance (hardness HB170~230). The oil passage diameter of the fan blade 3 is φ3mm, and the pitch of the spiral oil groove 7 is 24mm and the groove depth is 0.5mm.

[0047] Example 2

[0048] In another typical embodiment of this utility model, such as Figures 1-3 As shown, a compressor is presented.

[0049] The compressor utilizes the synergistic lubrication of the compressor crankshaft as described in Example 1. The synergistically lubricated compressor crankshaft serves as the core hub of the power transmission and lubrication system, constructing a full-path lubrication system for the crankshaft, cylinder, and piston. The compressor's body structure and the crankshaft's spiral oil grooves 7 and auxiliary oil passages form a systematic fit.

[0050] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor crankshaft with synergistic lubrication, characterized in that, It includes an eccentric shaft, a fan blade, and a main shaft arranged in sequence. The outer circumference of the main shaft is provided with a spiral oil groove. The fan blade is provided with a fan blade oil passage and an auxiliary oil passage. The fan blade oil passage is connected to the spiral oil groove. The auxiliary oil passage includes a first oil passage and a second oil passage that intersect. The two ends of the first oil passage extend to the outer circumferential wall of the fan blade to form a first orifice and a second orifice, respectively. One end of the second oil passage is connected to the fan blade oil passage, and the other end extends to the outer circumferential wall of the fan blade to form a third orifice. The first orifice, the second orifice, and the third orifice are staggered in the axial direction of the main shaft.

2. The compressor crankshaft with synergistic lubrication as described in claim 1, characterized in that, One end of the fan blade oil passage extends to the top surface of the fan blade, and the other end extends to the main shaft and connects to the spiral oil groove.

3. The compressor crankshaft with synergistic lubrication as described in claim 2, characterized in that, Along the axis of the main shaft from the main shaft to the fan blades, the flow direction of the refrigeration oil in the second oil passage forms an acute angle with the axis of the main shaft.

4. The compressor crankshaft with synergistic lubrication as described in claim 1, 2, or 3, characterized in that, The first oil passage axis is inclined relative to the tip surface of the fan blade.

5. The compressor crankshaft with synergistic lubrication as described in claim 4, characterized in that, The axis of the second oil passage is radially coplanar with the main shaft at its location, and the axes of the first and second oil passages are perpendicular.

6. The compressor crankshaft with synergistic lubrication as described in claim 1, characterized in that, The sum of the diameters of the first, second, and third orifices is equal to the axial thickness of the fan blade, so that the refrigeration oil thrown out by the auxiliary oil passage covers the axial thickness range of the fan blade.

7. The compressor crankshaft with synergistic lubrication as described in claim 1, characterized in that, An eccentric shaft oil passage is provided inside the eccentric shaft, and an annular oil groove is provided on the outer circumference of the eccentric shaft. The eccentric oil passage connects the annular oil groove and the spiral oil groove.

8. The compressor crankshaft with synergistic lubrication as described in claim 7, characterized in that, One end of the eccentric shaft oil passage extends to the outer circumference of the eccentric shaft to connect with the annular oil groove, and the other end passes through the fan blade and extends into the main shaft to connect with the spiral oil groove.

9. The compressor crankshaft with synergistic lubrication as described in claim 1, characterized in that, The main shaft has two spiral oil grooves, which are staggered upwards along the outer circumference of the main shaft.

10. A compressor, characterized in that, A compressor crankshaft using the synergistic lubrication as described in any one of claims 1-9.

Images