Crankshaft and compressor having the same

Abstract

The application provides a crankshaft and a compressor with the same, wherein the crankshaft comprises an eccentric section, a first oil storage groove and a first oil through hole are arranged in the eccentric section, a first oil guide groove is arranged on the outer circumferential wall of the eccentric section, the first oil storage groove is communicated with the first oil guide groove through the first oil through hole, and the 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 in the initial rotating stage of the crankshaft. According to the application, in the initial rotating stage of the crankshaft, i.e. the initial operating stage of the compressor, the lubricating oil accumulated in the first oil storage groove 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, so that the eccentric section friction pair of the crankshaft can be quickly lubricated in the initial operating stage of the compressor, the lubricating condition of the eccentric section friction pair in the initial stage of the compressor start-up is greatly improved, the reliability of the crankshaft is greatly increased, and the power consumption is reduced.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically relating to a crankshaft and a compressor having the same. Background Technology

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

[0003] Therefore, the present invention provides a crankshaft that can solve the technical problem that the lubricating oil cannot be distributed to the most severely affected parts of the compressor in time during the initial start-up process, resulting in poor local lubrication of the crankshaft and increased wear.

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

[0005] In some embodiments, the first oil storage tank is located below the first oil passage, 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 channel to the side of the first oil storage tank closer to the first oil guide channel.

[0006] In some embodiments, a first oil supply channel is also constructed within the eccentric section. One end of the first oil passage leads to the first oil supply channel, and the other end of the first oil passage leads to the first oil guide groove. The first oil storage groove is located between the first oil supply channel and the first oil guide groove. The first oil storage groove has a first groove wall surface away from the first oil guide groove. The angle between the first groove wall surface and the horizontal plane is α, where 0 < α ≤ 90°.

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

[0008] In some embodiments, the crankshaft further includes a main shaft section, in which a second oil reservoir and a second oil passage are constructed. A second oil guide groove is constructed on the outer peripheral wall of the main shaft section. The second oil reservoir is connected to the second oil guide groove through the second oil passage. During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the second oil reservoir flows into the second oil guide groove through the second oil passage under the action of inertial force.

[0009] In some embodiments, the second oil reservoir is located below the second oil passage, the second oil reservoir extends spirally within the main shaft section, and the direction of rotation of the second oil reservoir is opposite to the direction of rotation of the crankshaft.

[0010] In some embodiments, the spiral radius of the second oil reservoir is L2, 0≤L2≤Π / 2; and / or, the height of the second oil reservoir is H2, the spiral radius of the second oil reservoir is L2, and the radius of the main shaft 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 ≥ 0.15 mm.

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

[0014] The present invention provides a crankshaft and a compressor having the same, which 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 section flows into the first oil guide groove outside the eccentric section through the first oil passage under the action of centrifugal force, thus achieving rapid lubrication of the eccentric section friction pair. This initial crankshaft rotation phase corresponds to the initial operation phase of the compressor. This allows the present application to achieve rapid lubrication of the eccentric section friction pair of the crankshaft during the initial operation phase of the compressor, thereby greatly improving the lubrication condition of the eccentric section friction pair during the initial startup of the compressor, significantly increasing the reliability of the crankshaft, and reducing power consumption. Attached Figure Description

[0016] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

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

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

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

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

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

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

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

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

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

[0026] The reference numerals in the attached figures are as follows:

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

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

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

[0031] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0032] See also Figures 1 to 9 As shown, according to an embodiment of the present invention, a crankshaft is provided, including an eccentric section 1. The eccentric section 1 has a first oil reservoir 2 and a first oil passage 3. The outer peripheral wall of the eccentric section 1 has a first oil guide groove 4. The first oil reservoir 2 is connected to the first oil guide groove 4 through the first oil passage 3. During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil reservoir 2 flows into the first oil guide groove 4 through the first oil passage 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 section 1 flows into the first oil guide groove 4 outside the eccentric section 1 through the first oil passage 3 under the action of centrifugal force, thus achieving rapid lubrication of the eccentric section friction pair. The initial rotation stage of the crankshaft is also the initial operation stage of the compressor. This allows the present application to achieve rapid lubrication of the eccentric section friction pair of the crankshaft during the initial operation stage of the compressor, thereby greatly improving the lubrication condition of the eccentric section friction pair in the initial stage of compressor startup, significantly increasing the reliability of the crankshaft, and reducing power consumption.

[0034] See Figure 2 As shown, the first oil storage tank 2 is located below the first oil passage 3. 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 towards the first oil guide groove 4, thereby making it easier for the lubricating oil accumulated in the first oil reservoir 2 to flow into the first oil guide groove 4 under the action of centrifugal force. Preferably, the bottom of the first oil reservoir 2 is an upward-curved arc shape. Specifically, the first oil passage 3 can extend radially along the eccentric section 1 or extend slightly downward.

[0036] See Figure 2 As shown, a first oil supply channel 9 is also constructed in the eccentric section 1. One end of the first oil passage 3 is connected to the first oil supply channel 9, and the other end of the first oil passage 3 is connected 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 13 that is far away from the first oil guide groove 4. The angle between the first groove wall 13 and the horizontal plane is α, where 0 < α ≤ 90°.

[0037] In this technical solution, since the angle between the first groove wall 13 and the horizontal plane is greater than zero degrees and less than or equal to 90°, the first groove wall 13 has a blocking effect. This prevents the lubricating oil accumulated in the first oil storage groove 2 from flowing back into the first oil supply channel 9 through the first oil passage 3 under the influence of inertial force. Instead, it helps the lubricating oil flow entirely to the first oil guide groove 4, thus ensuring the lubrication effect of the eccentric section friction pair during the initial operation of the compressor. Specifically, one end of the first oil supply channel 9 leads to the top end face of the eccentric section 1. The 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 section 1, and the other path flows into the first oil guide groove 4 through the first oil passage 3. Furthermore, the first oil guide groove 4 extends obliquely on the outer peripheral wall of the eccentric section 1, ensuring that the first oil guide groove 4 has a large area and a large span, thereby ensuring that the first oil guide groove 4 can hold more lubricating oil and thus ensuring the lubrication effect of the eccentric section 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 passage 3 is R1, and R1 / 4≤W1≤R1; and / or, the maximum height of the first oil storage tank 2 is H1, and the diameter of the first oil passage 3 is R1, and R1 / 4≤H1≤R1.

[0039] In this embodiment, the first oil storage tank 2 is connected to the first oil passage 3. If the volume of the first oil storage tank 2 is too large, it will affect the stable operation of the compressor. The first oil supply channel 9 will deliver lubricating oil to the first oil guide tank 4 through the first oil passage 3. If the volume of the first oil storage tank 2 is too small, the oil storage effect will be poor. By limiting the width W1 of the first oil storage tank 2 to R1 / 4≤W1≤R1 and the maximum height H1 of the first oil storage tank 2 to R1 / 4≤H1≤R1, the first oil storage tank 2 can have a suitable volume relative to the first oil passage 3. In this way, the first oil storage tank 2 can have a good oil storage effect without affecting the first oil supply channel 9's delivery of lubricating oil to the first oil guide tank 4 through the first oil passage 3.

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

[0041] In this technical solution, during the initial rotation stage of the crankshaft, 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 passage 7 under the action of inertial force, thus achieving rapid lubrication of the friction pair of the main shaft section. This allows the present application to also achieve rapid lubrication of the friction pair of the crankshaft main shaft section during the initial operation stage of the compressor, thereby greatly improving the lubrication condition of the friction pair of the main shaft section during the initial start-up 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 reservoir 6 is located below the second oil passage 7. The second oil reservoir 6 extends spirally within the main shaft section 5, and the direction of rotation of the second oil reservoir 6 is opposite to the direction of rotation of the crankshaft.

[0043] In this embodiment, because the lubricating oil in the second oil reservoir 6 flows rapidly to the second oil guide groove 8 through the second oil passage 7 under the action of inertial force during the initial startup of the compressor, 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 so that the lubricating oil accumulated in the second oil reservoir 6 can flow into the second oil guide groove 8 more quickly. Specifically, the second oil guide groove 8 extends spirally on 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 is also constructed with a second oil supply channel 10 and a third oil passage 11. One end of the third oil passage 11 leads to the second oil supply channel 10, and the other end of the third oil passage 11 leads to the second oil guide groove 8. The third oil passage 11 is located below the second oil passage 7. The second oil guide groove 8 extends from the third oil passage 11 to the second oil passage 7. The end of the first oil supply channel 9 away from the top end face of the eccentric section 1 leads to the second oil passage 7. The crankshaft also includes a balance block 12, with the eccentric section 1 and the main shaft section 5 located on the upper and lower sides of the balance block 12, respectively. The second oil supply channel 10 extends all the way to the top end face of the balance block 12. During compressor operation, 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 paths for delivery. One path is delivered all the way to the top end face of the balance block 12 under the action of centrifugal force, while the other path is delivered to the second oil guide groove 8 through the third oil passage 11, and then along the second oil guide groove 8 to the second oil passage 7. Finally, it enters the first oil supply channel 9 through the second oil passage 7, thereby realizing the delivery of lubricating oil throughout the entire oil circuit. Furthermore, the second oil supply channel 10 is a three-stage stepped channel with an inner diameter that decreases sequentially. The second oil supply channel 10 is designed in this way because, on the one hand, the stepped structure with an inner diameter that decreases sequentially will accelerate the fluid flow through continuous shrinkage of the cross section, and achieve efficient fluid delivery 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 towards the pipe wall.

[0044] It is understandable that lubricating oil will accumulate in both the first oil reservoir 2 and the second oil reservoir 6 after each compressor shutdown.

[0045] See also Figure 4 and Figure 9 As shown, the spiral radius 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, and the radius of the main shaft segment 5 is r2, 0≤H2 / (L2·r2)≤0.5.

[0046] In this technical solution, limiting the spiral arc of the second oil reservoir 6 is to limit the length of the second oil reservoir 6 entering the crankshaft. If the length is too large, the lubricating oil in the second oil reservoir 6 may not be able to flow completely to 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 will be poor. When 0≤L2≤Π / 2 is satisfied, it is more suitable. Corresponding the spiral arc and longitudinal height of the second oil reservoir 6 to the radius of the main shaft section 5 of the crankshaft is to limit the spiral slope of the second oil reservoir 6. If the slope is too large, the lubricating oil in the second oil reservoir 6 will be difficult to be delivered to the second oil guide groove 8 under the action of inertial force during the initial operation of the compressor, affecting the lubrication effect during the initial operation of the compressor. If the slope is too small, the oil storage effect will be poor. When 0≤H2 / (L2·r2)≤0.5 is more suitable, it is more suitable. H2 / (L2·r2) is derived from the mathematical expression of the spiral, tanα=L / (2Π·R). The tangent of the tilt angle α determines the steepness of the spiral. The derivation is as follows: L is the height 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 radians L2, the height the axis rises is H2. Substituting into the formula, we get tanα=H2 / (L2·r2).

[0047] It should be noted that, in addition to storing lubricating oil, the second oil reservoir 6 is unidirectionally 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 reservoir 6. This can reduce the re-entry of impurities in the lubricating oil into the oil circuit, reduce wear caused by impurities, and reduce the possibility of oil circuit blockage and crankshaft seizure.

[0048] As a specific implementation method, 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, a certain thickness of nitriding layer is necessary for better results. Let the thickness of the nitriding layer be C. When C ≥ 0.15 mm, the surface hardness of the crankshaft is greater than or equal to 450 HV, thus achieving better surface hardness. Compared to a crankshaft without nitriding treatment, the surface hardness of the crankshaft in this application is increased by 58%. Simultaneously, measured roughness Ra after wear of the eccentric section 1 is 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 this application undergoes nitriding treatment, 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 decrease the wear of these parts, thereby improving the compressor's energy efficiency and extending its service life.

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

[0051] It will be readily understood by those skilled in the art that, without 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 should be included within the protection scope of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A crankshaft, characterized in that, The crankshaft includes an eccentric section (1), which has a first oil reservoir (2) and a first oil passage (3). The outer peripheral wall of the eccentric section (1) has a first oil guide groove (4). The first oil reservoir (2) is connected to the first oil guide groove (4) through the first oil passage (3). During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the first oil reservoir (2) flows into the first oil guide groove (4) through the first oil passage (3) under the action of centrifugal force. The first oil storage tank (2) is located below the first oil passage (3). 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). The width of the first oil storage tank (2) is W1, the diameter of the first oil passage (3) is R1, and R1 / 4≤W1≤R1; and / or, the maximum height of the first oil storage tank (2) is H1, and the diameter of the first oil passage (3) is R1, and R1 / 4≤H1≤R1.

2. The crankshaft according to claim 1, characterized in that, The eccentric section (1) is also equipped with a first oil supply channel (9). One end of the first oil passage (3) is connected to the first oil supply channel (9), and the other end of the first oil passage (3) is connected 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 (13) that is far away from the first oil guide groove (4). The angle between the first groove wall (13) and the horizontal plane is a, and 0 < a ≤ 90°.

3. The crankshaft according to claim 1, characterized in that, It also includes a main shaft section (5), in which a second oil reservoir (6) and a second oil passage (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 reservoir (6) is connected to the second oil guide groove (8) through the second oil passage (7). During the initial rotation stage of the crankshaft, the lubricating oil accumulated in the second oil reservoir (6) flows into the second oil guide groove (8) through the second oil passage (7) under the action of inertial force.

4. The crankshaft according to claim 3, characterized in that, The second oil reservoir (6) is located below the second oil passage (7). The second oil reservoir (6) extends spirally within the main shaft section (5), and the direction of rotation of the second oil reservoir (6) is opposite to the direction of rotation of the crankshaft.

5. The crankshaft according to claim 4, characterized in that, The spiral radius 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 radius of the second oil storage tank (6) is L2, and the radius of the main shaft segment (5) is r2, 0≤H2 / (L2·r2)≤0.

5.

6. The crankshaft according to any one of claims 1 to 5, characterized in that, The outer surface of the crankshaft is coated with a nitriding layer.

7. The crankshaft according to claim 6, characterized in that, The thickness of the nitrided layer is C, where C ≥ 0.15 mm.

8. A compressor, characterized in that, Includes the crankshaft as described in any one of claims 1 to 7.

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