Crankshaft and compressor with same

Abstract

The crankshaft comprises an eccentric section, a first oil storage groove and a first oil through hole are formed in the eccentric section, a first oil guide groove is formed in the peripheral wall of the eccentric section, and the first oil storage groove is communicated with the first oil guide groove through the first oil through hole. Lubricating oil accumulated in the first oil storage groove flows into the first oil guide groove through the first oil through hole under the action of centrifugal force. According to the invention, in the initial rotation stage of the crankshaft, namely, the initial operation stage of the compressor, lubricating oil accumulated in the first oil storage tank in the eccentric section flows into the first oil guide groove outside the eccentric section through the first oil through hole under the action of centrifugal force in the initial rotation stage of the crankshaft; therefore, the eccentric section friction pair of the crankshaft can be quickly lubricated in the initial operation stage of the compressor, so that the lubrication condition of the eccentric section friction pair in the initial starting stage of the compressor is greatly improved, the reliability of the crankshaft is greatly improved, and the power consumption is reduced.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and in particular relates to a crankshaft and a compressor having the same. Background Art

[0002] At present, the oil circuit design on the compressor crankshaft is mainly aimed at the delivery of lubricating oil during the operation of the compressor. However, during the initial startup of the compressor, the lubricating oil cannot be distributed to the parts with the most severe working conditions in time, resulting in poor local lubrication of the crankshaft, increased wear, and causing the compressor to jam. Summary of the Invention

[0003] Therefore, the present invention provides a crankshaft that can solve the technical problem that lubricating oil cannot be distributed to the most severe working condition parts in time during the initial startup of the compressor, resulting in poor local lubrication of the crankshaft and increased wear.

[0004] In order to solve the above problems, the present invention provides a crankshaft, including an eccentric section, wherein a first oil storage tank and a first oil hole are constructed in the eccentric section, and a first oil guide groove is constructed on the outer peripheral wall of the eccentric section. The first oil storage tank is connected to the first oil guide groove through the first oil hole. During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil storage tank flows into the first oil guide groove through the first oil hole under the action of centrifugal force.

[0005] In some embodiments, the first oil storage tank is located below the first oil hole, and the height of the first oil storage tank gradually decreases from the side of the first oil storage tank away from the first oil guide groove to the side of the first oil storage tank close to the first oil guide groove.

[0006] In some embodiments, a first oil supply channel is further constructed in the eccentric section, one end of the first oil hole leads to the first oil supply channel, and the other end of the first oil hole leads to the first oil guide groove. The first oil storage tank is located between the first oil supply channel and the first oil guide groove, and the first oil storage tank has a first groove wall away from the first oil guide groove, and the angle between the first groove wall and the horizontal plane is a, 0<a≤90°.

[0007] In some embodiments, the width of the first oil storage tank is W1, the diameter of the first oil hole is R1, and R1 / 4≤W1≤R1; and / or the maximum height of the first oil storage tank is H1, the diameter of the first oil hole is R1, and R1 / 4≤H1≤R1.

[0008] In some embodiments, the crankshaft also includes a main shaft section, a second oil storage tank and a second oil hole are constructed in the main shaft section, a second oil guide groove is constructed on the outer peripheral wall of the main shaft section, the second oil storage tank is connected to the second oil guide groove through the second oil hole, and in the initial rotation stage of the crankshaft, the lubricating oil accumulated in the second oil storage tank flows into the second oil guide groove through the second oil hole under the action of inertia force.

[0009] In some embodiments, the second oil storage tank is located below the second oil hole, the second oil storage tank extends spirally in the main shaft section, and the rotation direction of the second oil storage tank is opposite to the rotation direction of the crankshaft during rotation.

[0010] In some embodiments, the spiral radian of the second oil storage tank is L2, 0≤L2≤Π / 2; and / or the height of the second oil storage tank is H2, the spiral radian of the second oil storage tank is L2, and the radius of the main axis segment is r2, 0≤H2 / (L2·r2)≤0.5.

[0011] In some embodiments, the outer surface of the crankshaft is coated with a nitriding layer.

[0012] In some embodiments, the thickness of the nitrided layer is C, where C is ≥ 0.15 mm.

[0013] The present invention also provides a compressor comprising the aforementioned crankshaft.

[0014] The crankshaft and the compressor having the same provided by the present invention have the following beneficial effects:

[0015] During the initial rotation phase of the crankshaft, the lubricating oil accumulated in the first oil reservoir inside the eccentric segment flows into the first oil guide groove outside the eccentric segment through the first oil hole under the action of centrifugal force, thereby enabling rapid lubrication of the eccentric segment friction pair. The initial rotation phase of the crankshaft is the initial operation phase of the compressor, which enables the present application to rapidly lubricate the eccentric segment friction pair of the crankshaft during the initial operation phase of the compressor, thereby greatly improving the lubrication condition of the eccentric segment friction pair during the initial startup of the compressor, significantly increasing the reliability of the crankshaft, and reducing power consumption. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the embodiments or the description of the prior art. Obviously, the drawings described below are merely exemplary, and those skilled in the art can, without inventive effort, derive other implementation drawings based on the provided drawings.

[0017] Figure 1is a side view of a crankshaft according to an embodiment of the present invention;

[0018] Figure 2 for Figure 1 A cross-sectional view of a crankshaft according to an embodiment of the present invention taken along the DD direction;

[0019] Figure 3 A front view of a crankshaft according to an embodiment of the present invention;

[0020] Figure 4 for Figure 3 A cross-sectional view of a crankshaft according to an embodiment of the present invention taken along the AA direction;

[0021] Figure 5 A top view of a crankshaft according to an embodiment of the present invention;

[0022] Figure 6 for Figure 5 A cross-sectional view of a crankshaft according to an embodiment of the present invention taken along the BB direction;

[0023] Figure 7 for Figure 5 A cross-sectional view of a crankshaft according to an embodiment of the present invention taken along the CC direction;

[0024] Figure 8 for Figure 5 A cross-sectional view of a crankshaft according to an embodiment of the present invention taken along the EE direction;

[0025] Figure 9 for Figure 5 A cross-sectional view of the crankshaft of an embodiment of the present invention in the FF direction.

[0026] The reference numerals indicate:

[0027] 1. Eccentric section; 2. First oil storage tank; 3. First oil hole; 4. First oil guide groove; 5. Main shaft section; 6. Second oil storage tank; 7. Second oil hole; 8. Second oil guide groove; 9. First oil supply channel; 10. Second oil supply channel; 11. Third oil hole; 12. Balance block; 13. First groove wall. DETAILED DESCRIPTION

[0028] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0029] In the description of the present invention, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0030] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0031] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0032] See also Figures 1 to 9 As shown, according to an embodiment of the present invention, a crankshaft is provided, comprising an eccentric section 1, wherein a first oil storage tank 2 and a first oil through hole 3 are constructed in the eccentric section 1, a first oil guide groove 4 is constructed on the outer peripheral wall of the eccentric section 1, and the first oil storage tank 2 is connected to the first oil guide groove 4 through the first oil through hole 3. In the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil storage tank 2 flows into the first oil guide groove 4 through the first oil through hole 3 under the action of centrifugal force.

[0033] In this technical solution, during the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil reservoir 2 inside the eccentric segment 1 flows into the first oil guide groove 4 outside the eccentric segment 1 through the first oil hole 3 under the action of centrifugal force, thereby enabling rapid lubrication of the eccentric segment friction pair. The initial rotation stage of the crankshaft is the initial operation stage of the compressor, which enables the present application to achieve rapid lubrication of the eccentric segment friction pair of the crankshaft during the initial operation stage of the compressor, thereby greatly improving the lubrication condition of the eccentric segment friction pair during the initial startup of the compressor, significantly increasing the reliability of the crankshaft, and reducing power consumption.

[0034] See also Figure 2 As shown, the first oil storage tank 2 is located below the first oil through hole 3 , and the height of the first oil storage tank 2 gradually decreases from the side of the first oil storage tank 2 away from the first oil guide groove 4 to the side of the first oil storage tank 2 close to the first oil guide groove 4 .

[0035] In this embodiment, the height of the first oil reservoir 2 gradually decreases as it approaches the first oil guide groove 4, thereby allowing the lubricating oil accumulated in the first oil reservoir 2 to more easily flow into the first oil guide groove 4 under the action of centrifugal force. Preferably, the bottom of the first oil reservoir 2 is shaped like an upward arc. Specifically, the first oil hole 3 can extend radially along the eccentric segment 1 or slightly obliquely downward.

[0036] See also Figure 2 As shown, a first oil supply channel 9 is further constructed in the eccentric section 1, one end of the first oil hole 3 leads to the first oil supply channel 9, and the other end of the first oil hole 3 leads to the first oil guide groove 4. The first oil storage tank 2 is located between the first oil supply channel 9 and the first oil guide groove 4. The first oil storage tank 2 has a first groove wall surface 13 away from the first oil guide groove 4, and the angle between the first groove wall surface 13 and the horizontal plane is a, 0<a≤90°.

[0037] In this technical solution, because the angle between the first groove wall 13 and the horizontal plane is greater than zero degrees but less than or equal to 90 degrees, the first groove wall 13 has a blocking effect. This prevents the lubricating oil accumulated in the first oil reservoir 2 from flowing back into the first oil supply channel 9 through the first oil hole 3 under the influence of inertia. Instead, it helps the lubricating oil flow completely to the first oil guide groove 4, thereby ensuring the lubrication of the eccentric segment friction pair during the initial operation of the compressor. Specifically, one end of the first oil supply channel 9 opens to the top end face of the eccentric segment 1. Lubricating oil entering the first oil supply channel 9 is divided into two paths: one path is delivered to the top end face of the eccentric segment 1, and the other path flows into the first oil guide groove 4 through the first oil hole 3. Furthermore, the first oil guide groove 4 extends obliquely on the outer peripheral wall of the eccentric segment 1. This ensures that the first oil guide groove 4 has a larger area and a larger span, thereby ensuring that the first oil guide groove 4 can accommodate more lubricating oil, thereby ensuring the lubrication of the eccentric segment friction pair.

[0038] See also Figure 5 and Figure 8 As shown, the width of the first oil storage tank 2 is W1, the diameter of the first oil hole 3 is R1, R1 / 4≤W1≤R1; and / or, the maximum height of the first oil storage tank 2 is H1, the diameter of the first oil hole 3 is R1, R1 / 4≤H1≤R1.

[0039] In this embodiment, the first oil reservoir 2 is connected to the first oil through hole 3. If the volume of the first oil reservoir 2 is too large, the first oil supply passage 9 will affect the delivery of lubricating oil to the first oil guide groove 4 through the first oil through hole 3 during stable operation of the compressor. If the volume of the first oil reservoir 2 is too small, the oil storage effect will be poor. By limiting the width W1 of the first oil reservoir 2 to R1 / 4 ≤ W1 ≤ R1 and the maximum height H1 of the first oil reservoir 2 to R1 / 4 ≤ H1 ≤ R1, the first oil reservoir 2 can be made to have an appropriate volume relative to the first oil through hole 3. This ensures that the first oil reservoir 2 has a good oil storage effect while not affecting the delivery of lubricating oil from the first oil supply passage 9 to the first oil guide groove 4 through the first oil through hole 3.

[0040] See also Figure 3 、 Figure 4 、 Figure 5 and Figure 9 As shown, the crankshaft also includes a main shaft section 5, in which a second oil storage tank 6 and a second oil through hole 7 are constructed. A second oil guide groove 8 is constructed on the outer peripheral wall of the main shaft section 5. The second oil storage tank 6 is connected to the second oil guide groove 8 through the second oil through hole 7. During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the second oil storage tank 6 flows into the second oil guide groove 8 through the second oil through hole 7 under the action of inertia force.

[0041] In this technical solution, during the initial crankshaft rotation phase, the lubricating oil accumulated in the second oil reservoir 6 inside the main shaft section 5 flows into the second oil guide groove 8 outside the main shaft section 5 through the second oil hole 7 under the action of inertia, thereby quickly lubricating the main shaft section friction pair. This allows the present application to quickly lubricate the main shaft section friction pair during the initial operation of the compressor, thereby greatly improving the lubrication condition of the main shaft section friction pair during the initial startup of the compressor, further increasing the reliability of the crankshaft, and further reducing power consumption.

[0042] See also Figure 4 and Figure 9 As shown, the second oil storage tank 6 is located below the second oil through hole 7 , and the second oil storage tank 6 extends spirally in the main shaft section 5 , and the rotation direction of the second oil storage tank 6 is opposite to the rotation direction of the crankshaft when it rotates.

[0043] In this embodiment, because the lubricating oil in the second oil reservoir 6 flows rapidly through the second oil hole 7 to the second oil guide groove 8 during the initial startup of the compressor due to inertial force, and the direction of inertial force is opposite to the direction of centrifugal force, the spiral direction of the second oil reservoir 6 is designed to be opposite to the direction of crankshaft rotation, thereby allowing the lubricating oil accumulated in the second oil reservoir 6 to flow more quickly into the second oil guide groove 8. Specifically, the second oil guide groove 8 spirally extends along the outer peripheral wall of the main shaft section 5, and the spiral direction of the second oil guide groove 8 is the same as the direction of crankshaft rotation. The main shaft section 5 also has a second oil supply channel 10 and a third oil hole 11. One end of the third oil hole 11 opens into the second oil supply channel 10, and the other end of the third oil hole 11 opens into the second oil guide groove 8. The third oil hole 11 is located below the second oil hole 7. The second oil guide groove 8 extends from the third oil hole 11 to the second oil hole 7. The end of the first oil supply channel 9, away from the top end surface of the eccentric section 1, opens into the second oil hole 7. The crankshaft also includes a balance weight 12, with the eccentric section 1 and the main shaft section 5 located on the upper and lower sides of the balance weight 12, respectively. The second oil supply channel 10 extends all the way to the top end surface of the balance weight 12. During operation of the compressor, the lubricating oil in the bottom oil sump of the compressor rises along the second oil supply channel 10. The lubricating oil entering the second oil supply channel 10 is divided into two routes for transportation. One route is transported to the top end surface of the balance weight 12 under the action of centrifugal force, and the other route is transported to the second oil guide groove 8 through the third oil hole 11, and then travels along the second oil guide groove 8 to the second oil hole 7. Finally, it enters the first oil supply channel 9 through the second oil hole 7, thus completing the lubricating oil transportation of the entire oil circuit. Furthermore, the second oil supply channel 10 is a three-stage stepped channel with successively decreasing inner diameters. The second oil supply channel 10 is designed in this way. On the one hand, the stepped structure with successively decreasing inner diameters will accelerate the flow of fluid by continuously shrinking the cross-section, and achieve efficient fluid transportation or energy conversion through staged acceleration; on the other hand, in the spiral centrifugal oil circuit, the fluid is subjected to centrifugal force during rotation, and impurities in the lubricating oil will be thrown toward the pipe wall.

[0044] It is understandable that after each shutdown of the compressor, lubricating oil will be accumulated in the first oil storage tank 2 and the second oil storage tank 6 .

[0045] See also Figure 4 and Figure 9 As shown, the spiral arc of the second oil storage tank 6 is L2, 0≤L2≤Π / 2; and / or, the height of the second oil storage tank 6 is H2, the radius of the main shaft section 5 is r2, 0≤H2 / (L2·r2)≤0.5.

[0046] In this technical solution, the helical curvature of the second oil reservoir 6 is limited to limit the length of the second oil reservoir 6 extending into the crankshaft. If the length is too large, the lubricating oil in the second oil reservoir 6 may not fully flow into the second oil guide groove 8 during the initial operation of the compressor, resulting in long-term deposition of high-temperature lubricating oil and poor heat dissipation. If the length is too small, the oil storage effect is poor. A more suitable condition is when 0≤L2≤Π / 2. The helical curvature and longitudinal height of the second oil reservoir 6 are associated with the radius of the main shaft section 5 of the crankshaft to limit the helical slope of the second oil reservoir 6. If the slope is too large, the lubricating oil in the second oil reservoir 6 may be difficult to transport to the second oil guide groove 8 under the action of inertia during the initial operation of the compressor, affecting the lubrication effect of the compressor in the early stage of operation. If the slope is too small, the oil storage effect is poor. A more suitable condition is when 0≤H2 / (L2·r2)≤0.5. Among them, H2 / (L2·r2) is derived from the mathematical expression formula of the spiral: tanα=L / (2Π·R). The tangent value of the inclination angle α determines the steepness of the spiral, which is derived as follows: L is the height that the spiral rises along the axis when it rotates around the cylinder once (i.e., rotates 2Π radians). When the spiral rotates around the cylinder by an radian of L2, the height that the axis rises is H2. Substituting this into the formula, we get tanα=H2 / (L2·r2).

[0047] It should be noted that, in addition to being able to store lubricating oil, the second oil storage tank 6 is also one-way connected and has a certain depth. Therefore, impurities remaining in the lubricating oil due to wear can also be deposited at the bottom of the second oil storage tank 6. This can reduce the impurities in the lubricating oil from re-entering the oil circulation, reduce the wear caused by impurities, and reduce the possibility of oil circuit blockage and crankshaft seizure.

[0048] As a specific embodiment, the outer surface of the crankshaft is coated with a nitriding layer, that is, the surface of the crankshaft is nitrided, which can improve the hardness and wear resistance of the crankshaft and further increase the reliability of the crankshaft.

[0049] More specifically, the nitriding layer must have a certain thickness to achieve better results. The thickness of the nitriding layer is C. When C ≥ 0.15 mm, the surface hardness of the crankshaft is greater than or equal to 450 HV, which can make the surface of the crankshaft have better hardness. Compared with the crankshaft that has not been nitrided, the surface hardness of the crankshaft of the present application is increased by 58%. At the same time, the roughness Ra of the eccentric section 1 after wear is measured to be reduced by 48%-66%, and the roughness Ra of the main shaft section 5 after wear is reduced by 27%-40%. In other words, when the crankshaft of the present application is nitrided and the thickness of the nitriding layer is greater than or equal to 0.15 mm, it can reduce the friction between rotating parts and reduce the wear of the parts, thereby improving the energy efficiency of the compressor and extending its service life.

[0050] The present invention also provides a compressor comprising the aforementioned crankshaft.

[0051] It is easy for those skilled in the art to understand that, under the premise of no conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0052] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that those skilled in the art may make various improvements and variations without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. A crankshaft, characterized in that: The invention comprises an eccentric section (1), wherein a first oil storage tank (2) and a first oil through hole (3) are constructed in the eccentric section (1), and a first oil guide groove (4) is constructed on the outer peripheral wall of the eccentric section (1). The first oil storage tank (2) is connected to the first oil guide groove (4) through the first oil through hole (3). In the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil storage tank (2) flows into the first oil guide groove (4) through the first oil through hole (3) under the action of centrifugal force.

2. The crankshaft according to claim 1, characterized in that The first oil storage tank (2) is located below the first oil through hole (3), and the height of the first oil storage tank (2) gradually decreases in a direction from a side of the first oil storage tank (2) away from the first oil guide groove (4) to a side of the first oil storage tank (2) close to the first oil guide groove (4).

3. The crankshaft according to claim 2, characterized in that A first oil supply channel (9) is also constructed in the eccentric section (1); one end of the first oil hole (3) leads to the first oil supply channel (9); the other end of the first oil hole (3) leads to the first oil guide groove (4); the first oil storage groove (2) is located between the first oil supply channel (9) and the first oil guide groove (4); the first oil storage groove (2) has a first groove wall surface (13) away from the first oil guide groove (4); the angle between the first groove wall surface (13) and the horizontal plane is a, 0<a≤90°.

4. The crankshaft according to claim 2, characterized in that The width of the first oil storage tank (2) is W1, the diameter of the first oil hole (3) is R1, and R1 / 4≤W1≤R1; and / or the maximum height of the first oil storage tank (2) is H1, the diameter of the first oil hole (3) is R1, and R1 / 4≤H1≤R1.

5. The crankshaft according to claim 1, characterized in that The invention also includes a main shaft section (5), wherein a second oil storage tank (6) and a second oil through hole (7) are constructed in the main shaft section (5), and a second oil guide groove (8) is constructed on the outer peripheral wall of the main shaft section (5). The second oil storage tank (6) is connected to the second oil guide groove (8) through the second oil through hole (7). In the initial rotation stage of the crankshaft, the lubricating oil accumulated in the second oil storage tank (6) flows into the second oil guide groove (8) through the second oil through hole (7) under the action of inertia force.

6. The crankshaft according to claim 5, characterized in that The second oil storage tank (6) is located below the second oil hole (7), and the second oil storage tank (6) extends spirally in the main shaft section (5). The rotation direction of the second oil storage tank (6) is opposite to the rotation direction of the crankshaft when it rotates.

7. The crankshaft according to claim 6, characterized in that The spiral radian of the second oil storage tank (6) is L2, 0≤L2≤Π / 2; and / or the height of the second oil storage tank (6) is H2, the spiral radian of the second oil storage tank (6) is L2, and the radius of the main shaft section (5) is r2, 0≤H2 / (L2·r2)≤0.

5.

8. The crankshaft according to any one of claims 1 to 7, characterized in that The outer surface of the crankshaft is coated with a nitriding layer.

9. The crankshaft according to claim 8, characterized in that The thickness of the nitriding layer is C, where C is ≥ 0.15 mm.

10. A compressor, characterized in that: A crankshaft comprising the crankshaft according to any one of claims 1 to 9.

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