Patent Application
20210388836
This application claims the benefit of priorities to the following two Chinese patent applications, both of which are incorporated herein by reference in their entireties: Chinese Patent Application No. 201811245293.4, titled “OIL SUPPLY MECHANISM OF ROTATING MACHINERY AND ROTATING MACHINERY HAVING OIL SUPPLY MECHANISM”, filed with the China National Intellectual Property Administration on Oct. 24, 2018; and Chinese Patent Application No. 201821730366.4, titled “OIL SUPPLY MECHANISM OF ROTATING MACHINERY AND ROTATING MACHINERY HAVING OIL SUPPLY MECHANISM”; filed with the China National Intellectual Property Administration on Oct. 24, 2018.
The present disclosure relates to an oil supply mechanism of a rotating machinery and a rotating machinery having the oil supply mechanism.
The content in this section only provides background information related to the present disclosure, which may not constitute prior art.
In a rotating machinery (such as a scroll compressor), an oil supply mechanism (such as a compressor oil supply mechanism) is generally provided in order to lubricate and cool joining surfaces between various components. In the existing compressor oil supply mechanism, an oil pump is connected to one end of a rotating shaft of the compressor, lubricating oil in an oil sump of the compressor is pumped to an oil supply passage formed in the rotating shaft by the oil pump, and the lubricating oil is supplied through the oil supply passage from the other end of the rotating shaft to the joining surfaces to lubricate and cool corresponding components, for example, to lubricate and cool the joining surface in the compressor mechanism. The oil pump used in the existing compressor oil supply mechanism is generally, for example, a quantitative pump, the oil pump is driven by the rotating shaft of the compressor and pumps the lubricating oil as the rotating shaft of the compressor rotates. The pumping rate of the lubricating oil pumped by the oil pump is proportional to the rotation speed of the rotating shaft of the compressor. When the rotating shaft of the compressor rotates at a low speed, less lubricating oil is pumped from the end of the rotating shaft to the joining surfaces, and when the rotating shaft of the compressor rotates at a high speed, more lubricating oil is pumped from the end of the rotating shaft to the joining surfaces. As the rotation speed of the rotating shaft increases, the pumped lubricating oil continues to increase, so that an oil circulation rate of the lubricating oil is relatively high under a high-speed operating condition, which results in relatively low efficiency of the compressor, thereby resulting in the relatively low efficiency of the entire system. If the oil circulation rate under the high-speed operating condition is reduced by reducing the volume of the oil pump, the oil circulation under a low-speed operating condition may also be proportionally reduced, which may cause an insufficient lubrication and thereby causing a problem of wear of the compressor components.
Therefore, it is necessary to improve the existing oil supply mechanism of the rotating machinery, so that the oil supply mechanism can not only ensure the lubrication requirement under a low-speed operating condition, but also ensure a relatively low oil circulation rate under a high-speed operating condition, and improves the performance of the rotating machinery.
An object of the present disclosure is to solve or improve one or more of the above problems.
One aspect according to the present disclosure is to provide an oil supply mechanism of a rotating machinery including a rotating shaft. The oil supply mechanism includes a main oil supply passage formed in the rotating shaft substantially in an axial direction of the rotating shaft; and a bypass oil passage in communication with the main oil supply passage and allowing a part of lubricating oil in the main oil passage to flow out via the bypass oil passage. The bypass oil passage extends in a direction substantially transverse to the rotating shaft, and the bypass oil passage is configured such that a radial distance between an outlet of the bypass oil passage and an axis of the rotating shaft is greater than a radius of the rotating shaft.
In an embodiment, a ratio of the radial distance to the radius ranges from 2 to 5. Preferably, the ratio ranges from 2.5 to 4.
In an embodiment, the bypass oil passage includes a first passage portion and a second passage portion connected to each other, the first passage portion is in direct fluid communication with the main oil supply passage, and a cross-sectional area of the first passage portion is greater than a cross-sectional area of the second passage portion so that the bypass oil passage is formed as a stepped passage.
In an embodiment, the bypass oil passage is constructed by forming an integral radial protrusion at the rotating shaft, and/or the bypass oil passage is constructed by providing an additional oil passage member.
In an embodiment, a first through hole extending in a direction substantially transverse to the rotating shaft is formed in the rotating shaft, the additional oil passage member is provided with a second through hole extending in an axial direction of the additional oil passage member, the additional oil passage member is attached to the rotating shaft to allow the second through hole to be in direct communication with the main oil supply passage or be in indirect communication with the main oil supply passage via the first through hole, and at least a portion of the bypass oil passage is formed by the second through hole.
The additional oil passage member is inserted into the first through hole so that the first through hole is completely occupied by the additional oil passage member, and the bypass oil passage is formed by the second through hole. Alternatively, the additional oil passage member is inserted into the first through hole so that the first through hole is partially occupied by the additional oil passage member, and the bypass oil passage is formed by the second through hole and a portion of the first through hole. Alternatively, the additional oil passage member is attached to an outer peripheral wall surface of the rotating shaft in a manner without being inserted into the first through hole, and the bypass oil passage is formed by the first through hole and the second through hole.
In an embodiment, a cross-sectional area of the first through hole is greater than a cross-sectional area of the second through hole, so that the bypass oil passage is formed as a stepped passage: and/or the first through hole and/or the second through hole are formed with a stepped portion, so that the bypass oil passage is formed as a stepped passage in which a passage portion in direct communication with the main oil supply passage has a larger cross-sectional area.
In an embodiment, the additional oil passage member is provided with a stop portion, and the stop portion is abutted against an outer peripheral wall surface of the rotating shaft when the additional oil passage member is attached to the rotating shaft.
In an embodiment, a portion of the outer peripheral wall surface of the rotating shaft abutting against the stop portion is formed as a plane portion.
In an embodiment, the additional oil passage member is a pin.
The oil supply mechanism further includes an oil pump device, and the oil pump device is coupled with the rotating shaft to pump the lubricating oil into the main oil supply passage.
A lower end portion of the rotating shaft is supported by a bottom bearing, and the main oil supply passage includes a central oil passage connected to the oil pump device and an eccentric oil passage extending upward from the central oil passage, the central oil passage is connected to and in communication with the eccentric oil passage in a joint area. The bypass oil passage is located below the joint area and above the bottom bearing in the axial direction of the rotating shaft, and the bypass oil passage is in communication with the central oil passage.
In an embodiment, the bypass oil passage is arranged on the same side as the eccentric oil passage in a circumferential direction of the rotating shaft.
An aspect of the present disclosure is to provide rotating machinery including the oil supply mechanism according to the present disclosure.
In an embodiment, the rotating machinery is a scroll compressor.
In the present disclosure, an elongated bypass oil passage is provided in an oil supply mechanism of a rotating machinery. The bypass oil passage has a relatively low drainage capacity under a low-speed operating condition, so as to ensure the oil supply amount under the low-speed operating condition, and meet the lubrication requirement. In addition, the bypass oil passage has a relatively high drainage capacity under a high-speed operating condition, so as to reduce the oil supply amount under the high-speed operating condition, reduce oil circulation rate, and improve the efficiency of the rotating machinery.
Hereinafter, the embodiments of the present disclosure will be described only by the way of examples with reference to the accompanying drawings, in which the same features or components are denoted by the same reference numerals and the accompanying drawings are not necessarily drawn to scale, and in the accompanying drawings:
The following description is merely exemplary in nature and is not intended to limit the present disclosure, the application and usage thereof. It should be noted that in all these drawings, similar reference numerals indicate the same or similar components and features. The drawings only schematically show the inventive concept and principle of the embodiments of the present disclosure, and do not necessarily show the specific dimensions and proportions of the various embodiments of the present disclosure. An exaggerated manner may be used in specific parts of the specific drawings to illustrate related details or structures of the embodiments of the present disclosure.
In this specification, a rotating machinery refers to a mechanical device or system having a rotating shaft, a crankshaft, or a rotating drive shaft. A compressor with a rotating shaft belongs to the rotating machinery described herein. Hereinafter, a compressor (such as a scroll compressor) is taken as an example of the rotating machinery to describe an oil supply mechanism of a rotating machinery of a comparative example and an oil supply mechanism of a rotating machinery according to the present disclosure, so as to illustrate the inventive concept of the present disclosure. However, it should be noted that the oil supply mechanism according to the present disclosure is also applicable to other rotating machinery including a rotating shaft, a crankshaft, or a rotating drive shaft and an oil pump device coupled with the rotating shaft, the crankshaft, or the rotating drive shaft.
The oil delivery rate or oil delivery amount of the lubricating oil pumped by the oil pump device 2 flowing out from the upper end portion of the rotating shaft 1 is proportional to the rotation speed of the rotating shaft 1.
As shown in
The inventor is aware of the above problems and proposes a compressor oil supply mechanism which is capable of solving the above technical problems. The oil supply mechanism according to the inventive concept of the present disclosure is provided with an elongated bypass oil passage, which can not only meet the lubrication requirement under the low-speed operating condition, but also reduce the oil circulation rate under the high-speed operating condition, and reduce the proportion of the lubricating oil contained in the compressor discharged gas. On one hand, it is beneficial to the capacity of the entire refrigeration/heating cycle, which improves the efficiency of the heat exchanger, and on the other hand, it is beneficial to maintaining the internal oil amount inside the compressor and improving the reliability of the compressor operation, which is beneficial to the management of the lubricating oil of the compressor, thereby improving the efficiency and reliability of the compressor, and improving the performance of the compressor. The compressor oil supply mechanism according to an embodiment of the present disclosure will be described below with reference to the accompanying drawings.
As shown in
In the illustrated exemplary embodiment, a first through hole 13 is provided in the rotating shaft 1. The first through hole 13 extends through a wall of the rotating shaft 1 in a radial direction of the rotating shaft 1, so that the central oil passage 11 is in communication with an outside of the rotating shaft 1. In the axial direction of the rotating shaft 1, the first through hole 13 is arranged below a joint area D for the central oil passage 11 and the eccentric oil passage 12, and is in direct fluid communication with the central oil passage 11, and is as far away from the joint area D as possible, so as to ensure that the first through hole 13 is arranged as low as possible while the first through hole 13 is located above the bottom bearing. In a circumferential direction of the rotating shaft 1, the first through hole 13 is arranged on the same side with the eccentric oil passage 12. Alternatively, the first through hole 13 may be away from the eccentric oil passage 12 in the circumferential direction, so as to ensure a stable oil supply.
The compressor oil supply mechanism 200 further includes an additional oil passage member. In this exemplary embodiment, a pin 5 is used as the additional oil passage member, and is attached to the rotating shaft 1. A second through hole 54 is formed in the pin 5, and extends in an axial direction of the pin 5 through an entire axial length of the pin 5. In the illustrated exemplary embodiment, the first through hole 13 is a threaded hole and has a uniform cross-sectional area over an entire length of the first through hole 13. A first end 53 of the pin 5 is threaded into the first through hole 13. It should be noted that the present disclosure is not limited to this. In other possible embodiments of the present disclosure, the pin 5 may be inserted into the first through hole 13 in other ways. For example, the first through hole 13 may be formed as an unthreaded hole, and the pin 5 may be interference-fitted in the first through hole 13. The first end 53 of the pin 5 extends into substantially half of the length of the first through hole 13, and does not reach an inner peripheral wall surface S1 of the rotating shaft 1, so that a portion of the first through hole 13 does not engage with the pin 5. That is, the first through hole 13 is partially occupied by the pin 5. It should be noted here that the additional oil passage member according to the present disclosure may also be implemented as other suitable members with through holes (for example, a circular pipe).
The first passage portion 41 of the bypass oil passage 40 is formed by a portion of the first through hole 13 which does not engage with the pin 5. and the second passage portion 42 is formed by the second through hole 54 in the pin 5. This arrangement allows a radial distance between an outlet of the bypass oil passage 40 and an axis (longitudinal axis O) of the rotating shaft 1 to be greater than a radius of the rotating shaft 1, so that the bypass oil passage 40 is constructed as an elongated bypass oil passage. In addition, the cross-sectional area of the first through hole 13 that is, a cross-section area of the first passage portion 41 in this embodiment) is greater than a cross-sectional area of the second through hole 54 (that is, the second passage portion 42 in this embodiment), so that the bypass oil passage 40 is formed as a stepped passage. This configuration allows a part of the lubricating oil in the central oil passage 11 to be stored in the first passage portion 41 with a relatively larger cross-sectional area during the rotation of the rotating shaft 1, so as to ensure that the lubricating oil is able to be stably and reliably discharged from the bypass oil passage 40 at different rotation speeds of the rotating shaft 1.
As shown in
The inventor further discovers that the length of the pin 5 or the radial dimension of the bypass oil passage 40 may affect the relationship characteristics between the oil delivery rate of the compressor oil supply mechanism 200 and the rotation speed of the rotating shaft 1.
As shown in
The compressor oil supply mechanism according to the preferred embodiment of the present disclosure is shown above. In the embodiment shown above, in order to facilitate processing, the first through hole 13 is a threaded hole having the uniform diameter and extends in the axial direction of the rotating shall 1. The first end portion 53 of the pin 5 is threaded with the first through hole 13 on a portion of the length of the first through hole 13, without being inserted to reach the inner peripheral wall surface S1 of the rotating shaft 1 (that is, the pin 5 is inserted so as to not allow an end surface of the first end portion 53 to reach the inner peripheral wall surface S1 to be flush with the inner peripheral wall surface S1, so that the first through hole 13 is partially occupied by the pin 5), the first passage portion 41 of the bypass oil passage 40 is formed by a portion of the first through hole 13 which is not engaged with the pin 5, and the second passage portion 42 is formed by the second through hole 54 in the pin 5. In addition, the first through hole 13 in the rotating shaft 1 is arranged below the joint area D for the central oil passage 11 and the eccentric oil passage 12, and the first through hole 13 is arranged close to the eccentric oil passage 12 in the circumferential direction. However, the present disclosure is not limited to this.
In other possible embodiments of the present disclosure, the first through hole 13 may extend not in the radial direction of the rotating shaft 1, but in a direction tangent to the central oil passage 11. In addition, in other possible embodiments of the present disclosure, the first through hole 11 may be formed not in a plane perpendicular to the axis O of the rotating shaft 1, but may be formed to be slightly inclined upward or downward relative to the plane perpendicular to the axis O of the rotating shaft 1. Here, the expression “the bypass oil passage or the first through hole is substantially transverse to the rotating shaft” used in the specification can be used to mean that: the bypass oil passage 40 or the first through hole 13 extends in the radial direction of the rotating shaft 1 (extending in the radial direction away from the axis of the rotating shaft); the bypass oil passage 40 or the first through hole 13 extends in the direction tangent to the central oil passage 11; and the bypass oil passage 40 or the first through hole 13 extends slightly inclined upward or downward relative to the plane perpendicular to the axis O of the rotating shaft 1. Here, the bypass oil passage 40 or the first through hole 13 extends slightly inclined upward or downward relative to the plane perpendicular to the axis O of the rotating shaft 1″ means that the bypass oil passage 40 or the first through hole 13 does not have to be strictly perpendicular to the axis O of the rotating shaft 1, but may, for example, be inclined relative to the plane perpendicular to the axis O of the rotating shall 1 within the allowable range of machining error.
In other possible embodiments of the present disclosure, the first through hole 13 may also be formed as a stepped through hole, and a portion thereof with a relative larger cross-sectional area is close to the central oil passage 11. And in a case that the wall of the rotating shaft 1 is thick enough (for example, an integral radial protruding portion is provided at the axial portion and the circumferential portion of the rotating shaft 1), the pin 5 can even be omitted.
In other possible embodiments of the present disclosure, the first end portion 53 of the pin 5 may engage with the first through hole 13 on the entire length of the first through hole 13 and be flush with the inner peripheral wall surface S1 of the rotating shaft 1, so that the first through hole 13 is completely occupied by the pin 5. In this embodiment, the first passage portion 41 and the second passage portion 42 of the bypass oil passage 40 are respectively formed by the corresponding portions of the second through hole 54 in the pin 5. The second through hole 54 may be a through hole with a constant cross-sectional area, so that the first passage portion 41 and the second passage portion 42 may have the same cross-sectional area (that is, the bypass oil passage 40 is not formed as a stepped passage). However, preferably, the second through hole 54 is formed as a stepped hole, so that the cross-sectional area of the first passage portion 41 is greater than the cross-sectional area of the second passage portion 42, so as to ensure that the lubricating oil is stably and reliably discharged from the bypass oil passage 40 at different rotation speeds.
In other possible embodiments of the present disclosure, the first end portion 53 of the pin 5 may not be inserted into the first through hole 13, but be sealingly abutted against the outer peripheral wall surface S2 of the rotating shaft 1, and the second through hole 54 in the pin 5 is aligned with the first through hole 13. In this case, the first passage portion 41 of the bypass oil passage 40 is formed by the first through hole 13 or is formed by the first through hole 13 and a portion of the second through hole 54 together, and the second passage portion 42 of the bypass oil passage 40 is formed by the second through hole 54 or is formed by a portion of the second through hole 54. Preferably, the cross-sectional area of the first through hole 13 is greater than the cross-sectional area of the second through hole 54. Preferably, the second through hole 54 is formed as a stepped hole, and the cross-sectional area of the first through hole 13 is greater than or equal to the cross-sectional area of the portion of the second through hole 54 with relative larger cross-sectional area.
In other possible embodiments of the present disclosure, the first through hole 13 is arranged below the joint area D, and is arranged at any position in the circumferential direction of the rotating shaft 1, and is not limited to being arranged close to the eccentric oil passage 12 in the circumferential direction.
In other possible embodiments of the present disclosure, the first through hole 13 may also be arranged close to the joint area D. In this case, due to the arrangement of the eccentric oil passage 12, the first through hole 13 is provided to avoid a position that is close to the joint area D and 180 degrees away from the eccentric oil passage 12 in the circumferential direction. That is, in this case, the first through hole 13 needs to be arranged close to the eccentric oil passage 12 in the circumferential direction.
The exemplary embodiments of the present disclosure have been described in detail here. It should be understood that the present disclosure is not limited to the specific embodiments described and shown in detail herein, and other modifications and variations may be implemented by those skilled in the art without departing from the spirit and scope of the present disclosure. All these modifications and variations fall within the scope of the present disclosure. Moreover, all the components described herein can be replaced by other technically equivalent components.
| Number | Date | Country | Kind |
|---|---|---|---|
| 201811245293.4 | Oct 2018 | CN | national |
| 201821730366.4 | Oct 2018 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2019/112754 | 10/23/2019 | WO | 00 |
