Compressor pump body and compressor having the same

Abstract

This invention provides a compressor pump body and a compressor having the compressor pump body. The compressor pump body includes a cylinder; a secondary bearing disposed at the lower part of the cylinder; a main bearing disposed at the upper part of the cylinder; a crankshaft that passes through the main bearing, the cylinder, and the secondary bearing sequentially along its axial direction, so that the eccentric part of the crankshaft rotates in the cylinder; an oil pump groove formed in the inner wall of the main bearing, wherein the crankshaft rotation pumps refrigerant oil from the lower end of the main bearing through the oil pump groove to the upper end of the main bearing; and a first oil return groove formed in the inner wall of the main bearing, wherein the starting point of the first oil return groove is located at the upper end of the main bearing, and the end point of the first oil return groove is connected to the lower end of the main bearing, for transporting the refrigerant oil at the upper end of the main bearing to the lower end of the main bearing. By setting the oil pump groove and the first oil return groove in the inner wall of the main bearing, this invention can return excess oil to the lower end of the main bearing during high-frequency operation of the compressor, reducing the oil circulation rate, reducing system oil residue, and thus improving the reliability of compressor operation.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor pump body and a compressor having the compressor pump body. Background Technology

[0002] The compressor is the core power component of a refrigeration and air conditioning system. The pump body, as the core working mechanism of the compressor, mainly consists of a cylinder, main bearing, auxiliary bearing, crankshaft, rollers, and vanes. Its operational reliability directly determines the overall performance of the compressor. The main bearing and crankshaft form a critical friction pair, requiring stable and suitable oil lubrication to ensure reliable operation of the friction pair under high-speed rotation conditions. With the popularization of variable frequency compressor technology, compressors need to operate over a wide speed and frequency range, placing higher demands on the bearing lubrication and oil supply system.

[0003] Existing variable frequency rotary compressors generally employ a single-spiral oil groove supply structure for the pump body main bearing. Refrigeration oil is transported upwards through a single-spiral pumping path on the inner wall of the main bearing, relying on the centrifugal force generated by the crankshaft rotation, to lubricate the friction pair between the crankshaft and the main bearing. This structure has only a single upward pumping channel, and the pumping oil volume and height are positively correlated with the compressor speed; the higher the speed, the greater the pumping oil volume and height, and vice versa.

[0004] However, this single, unidirectional oil circuit has significant drawbacks. On the one hand, when the compressor operates at high frequency, the excessive oil volume and height lead to a high oil circulation rate. A large amount of refrigerant oil enters the system piping along with the refrigerant, condensing and remaining due to differences in physical properties. This reduces the effective heat exchange area of ​​the piping, decreasing the system's heat exchange efficiency and affecting overall energy efficiency. On the other hand, when the compressor operates at low frequency, the low speed, small oil volume, and insufficient oil height make the upper part of the main bearing prone to lubrication deficiency, increasing the risk of wear and failure. Summary of the Invention

[0005] One object of the present invention is to overcome at least one deficiency in the prior art and to provide a compressor pump body and a compressor having the compressor pump body.

[0006] A further objective of the present invention is to reduce the oil circulation rate when the compressor is operating at high frequency.

[0007] Another further object of the present invention is to increase the amount of refrigeration oil at the upper end of the main bearing when the compressor is running at low frequency.

[0008] Specifically, the present invention provides a compressor pump body, comprising: cylinder; A secondary bearing is located at the lower part of the cylinder; The main bearing is located at the top of the cylinder; The crankshaft passes through the main bearing, cylinder and auxiliary bearing in sequence along its axial direction, so that the eccentric part of the crankshaft rotates in the cylinder. The oil pump groove is located on the inner wall of the main bearing. When the crankshaft rotates, it pumps the refrigeration oil from the lower end of the main bearing to the upper end of the main bearing through the oil pump groove. The first oil return groove is located on the inner wall of the main bearing. The starting point of the first oil return groove is located at the upper end of the main bearing, and the end of the first oil return groove is connected to the lower end of the main bearing. The first oil return groove is used to transport the refrigeration oil from the upper end of the main bearing to the lower end of the main bearing.

[0009] Optionally, the compressor pump body also includes: The second return oil groove is located on the inner wall of the main bearing. The starting point of the second return oil groove is located at the upper end of the main bearing, and the end of the second return oil groove is connected to the pump oil groove. The second return oil groove is used to transport the refrigeration oil at the upper end of the main bearing to the pump oil groove.

[0010] Optionally, the depth of the first and second return oil tanks gradually increases along the flow direction of the refrigeration oil.

[0011] Optionally, the depth at the end of the first return oil trough is less than a first preset multiple of the depth at the beginning of the first return oil trough.

[0012] Optionally, the depth at the end of the second return oil trough is less than a second preset multiple of the depth at the beginning of the second return oil trough.

[0013] Optionally, the depths of the first return oil sump and the second return oil sump are greater than or equal to the depth of the pump oil sump.

[0014] Optionally, the pump oil groove, the first return oil groove, and the second return oil groove are all spiral structures extending circumferentially and axially along the inner wall of the main bearing.

[0015] Optionally, the starting point of the second return oil tank coincides with the end point of the pump oil tank.

[0016] Optionally, the starting point of the first return oil tank coincides with the end point of the pump oil tank.

[0017] According to another aspect of the invention, a compressor is also provided, which includes the compressor pump body of any of the above.

[0018] The compressor pump body provided by this invention includes: a cylinder, a secondary bearing, a main bearing, a crankshaft, an oil pump groove, and a first oil return groove. The secondary bearing is located at the lower part of the cylinder, and the main bearing is located at the upper part of the cylinder. The crankshaft passes through the main bearing, the cylinder, and the secondary bearing sequentially along its axial direction, allowing the eccentric portion of the crankshaft to rotate within the cylinder. The oil pump groove is located on the inner wall of the main bearing. The crankshaft rotation pumps refrigerant oil from the lower end of the main bearing through the oil pump groove to the upper end of the main bearing. The first oil return groove is also located on the inner wall of the main bearing, with its starting point at the upper end of the main bearing and its end connected to the lower end of the main bearing. The first oil return groove is used to transport the refrigerant oil from the upper end of the main bearing to the lower end. By providing the oil pump groove and the first oil return groove on the inner wall of the main bearing, this invention allows excess oil to flow back to the lower end of the main bearing during high-frequency compressor operation, reducing the oil circulation rate, decreasing system oil residue, and thus improving the compressor's operational reliability and system heat exchange efficiency.

[0019] Furthermore, the compressor pump body provided by this invention also includes a second oil return groove. The second oil return groove is formed on the inner wall of the main bearing, with its starting point located at the upper end of the main bearing and its end connected to the pump oil groove. The second oil return groove is used to transport the refrigerant oil from the upper end of the main bearing to the pump oil groove. By adding a second oil return groove, this invention allows the oil accumulated at the upper end of the main bearing to flow directly back to the pump oil groove for circulation, thereby enhancing lubrication during low-frequency compressor operation. Simultaneously, in conjunction with the first oil return groove, it enables more precise refrigerant oil flow distribution within the compressor pump body under both high and low frequency operating conditions, resulting in a more balanced oil supply and return.

[0020] The above and other objects, advantages and features of this application will become more apparent to those skilled in the art from the following detailed description of specific embodiments of this application in conjunction with the accompanying drawings. Attached Figure Description

[0021] The following sections will describe some specific embodiments of this application in detail by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or components. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings: Figure 1 This is a schematic cross-sectional view of a compressor according to an embodiment of this application; Figure 2 yes Figure 1 A schematic 3D view of the main bearing in the diagram; Figure 3 yes Figure 1 A schematic cross-sectional view of the main bearing in the structure; Figure 4 yes Figure 1 Another schematic perspective view of the main bearing in the diagram. Detailed Implementation

[0022] Figure 1 This is a schematic cross-sectional view of a compressor 10 according to an embodiment of this application; Figure 2 yes Figure 1 A schematic perspective view of the main bearing 130 in the diagram; Figure 3 yes Figure 1 A schematic cross-sectional view of the main bearing 130 in the diagram; Figure 4 yes Figure 1 Another schematic perspective view of the main bearing 130.

[0023] See Figures 1 to 4 This application provides a compressor pump body 100, which may include: a cylinder 110, a secondary bearing 120, a main bearing 130, a crankshaft 140, a pump oil groove 131, and a first return oil groove 132.

[0024] The auxiliary bearing 120 can be located at the lower part of the cylinder 110 to form a support structure on the lower side of the pump body.

[0025] The main bearing 130 can be installed on the upper part of the cylinder 110, corresponding to the auxiliary bearing 120 above and below, together forming the axial support of the pump body.

[0026] The crankshaft 140 can pass sequentially through the main bearing 130, the cylinder 110, and the auxiliary bearing 120 along its axial direction, so that the eccentric portion 141 of the crankshaft 140 rotates in the cylinder 110. The eccentric portion 141 of the crankshaft 140 is confined inside the cylinder 110 and can rotate with the crankshaft 140 to perform eccentric motion, thereby completing the compression work of the compressor 10.

[0027] like Figure 2 As shown, the oil pump groove 131 can be opened on the inner wall of the main bearing 130. When the crankshaft 140 rotates, it generates an oil pumping action, which transports the refrigeration oil from the lower end of the main bearing 130 upward along the oil pump groove 131 to the upper end of the main bearing 130, providing basic lubrication for the friction pair between the crankshaft 140 and the main bearing 130.

[0028] like Figure 3 As shown, the first return oil groove 132 can be formed on the inner wall of the main bearing 130, with its starting point located in the upper end face area of ​​the main bearing 130 and its end connected to the lower end of the main bearing 130. This allows the refrigerant oil accumulated on the upper end of the main bearing 130 to flow back to the lower end of the main bearing 130. When the compressor 10 is running at high frequency, excess refrigerant oil in the pump oil circuit can circulate to the lower end of the bearing through the return oil circuit, reducing the amount of refrigerant oil participating in the refrigerant circulation and improving the oil circulation rate of the compressor 10. Due to the improved oil circulation, the residual refrigerant oil in the system is further reduced, the heat exchange area of ​​the system is further improved, and the heat exchange efficiency of the system is improved.

[0029] In some optional embodiments, high-frequency operation of compressor 10 refers to compressor 10 operating in a high-speed range above its rated speed. For example, operating conditions where the compressor 10 operates at a frequency greater than 60Hz and a speed greater than 3600r / min can be considered high-frequency operation. Under this condition, the crankshaft 140 rotates at a high speed, and the oil pump sump 131 is affected by centrifugal force, resulting in a significant increase in the oil pumping volume and oil pumping height, which can easily lead to excessive oil supply. Through the return flow in the first return oil sump 132, excess refrigerant oil can be promptly guided back to the lower end of the main bearing 130, improving the oil circulation rate of compressor 10.

[0030] In some alternative embodiments, such as Figure 4 As shown, the compressor pump body 100 also includes a second return oil groove 133, which can be formed on the inner wall of the main bearing 130. The starting point of the second return oil groove 133 is located at the upper end of the main bearing 130, and it is used to collect the refrigerant oil accumulated at the upper end. The end of the second return oil groove 133 is connected to the pump oil groove 131. The second return oil groove 133 is used to transport the refrigerant oil at the upper end of the main bearing 130 to the pump oil groove 131, forming a closed loop with the pump oil circuit. This allows the refrigerant oil accumulated on the upper end face and surrounding parts of the bearing to circulate back to the pump oil circuit through the return oil circuit when the compressor 10 is running at low frequency, further ensuring the lubrication of the friction pair between the main bearing 130 and the crankshaft 140.

[0031] In some optional embodiments, low-frequency operation of compressor 10 refers to compressor 10 operating in an energy-saving range with low speed and low load. For example, the operating frequency of compressor 10 can be less than 30Hz. Operating conditions with a speed less than 1800 r / min can be considered low-frequency operation. Under these conditions, the crankshaft 140 rotates slowly, and the pumping volume and height of the oil pump sump 131 are significantly insufficient, making it difficult to stably deliver refrigerant oil to the upper end of the main bearing 130. This can easily lead to insufficient lubrication at the upper end and increased wear of the friction pair. Through the reflux effect of the second return oil sump 133, the refrigerant oil accumulated at the upper end of the main bearing 130 can be guided back to the pump oil sump 131, continuously replenishing the upper lubrication and ensuring the reliability and stability of bearing operation under low-frequency conditions.

[0032] In some optional embodiments, the compressor pump body 100 may include multiple pump oil grooves 131, a first return oil groove 132, and a second return oil groove 133. This application does not impose a specific limitation on the exact number of pump oil grooves 131, the first return oil groove 132, and the second return oil groove 133; the number of these three can be the same or different. Those skilled in the art can flexibly select and match them according to the actual displacement, rated speed range, load characteristics, and lubrication requirements of the compressor 10. For example, for a small-displacement, low-power fixed-frequency compressor 10, one set of pump oil grooves 131 paired with one set of first return oil grooves 132 and one set of second return oil grooves 133 can meet basic lubrication and return oil requirements. For a large-displacement, high-power wide-frequency variable-frequency compressor 10, two to four sets of pump oil grooves 131 can be set, with corresponding configurations of the same or different numbers of first return oil grooves 132 and second return oil grooves 133, to achieve a larger flow rate of pumping and returning oil. This design, which allows for flexible adjustment of the number of oil grooves, enables optimal parameter matching for the specific operating conditions of different models. While ensuring the reliability of lubrication and the effect of oil circulation control across the entire frequency band, it also takes into account the structural strength and manufacturing cost of the main bearing 130, significantly improving the versatility and applicability of this technical solution.

[0033] In some optional embodiments, the depths of the first return oil groove 132 and the second return oil groove 133 gradually increase along the flow direction of the refrigeration oil. This gradual increase in groove depth from top to bottom significantly optimizes the return oil dynamics, comprehensively improving return oil efficiency and lubrication effect under all operating conditions. The shallower initial depth at the upper end of the first return oil groove 132 and the second return oil groove 133 effectively collects a small amount of accumulated oil on the upper surface and surrounding area of ​​the main bearing 130, preventing refrigeration oil from stagnating on the end face and failing to enter the return oil groove. Especially during low-frequency operation, it maximizes the collection of limited upper accumulated oil for return replenishment. As the groove depth gradually increases from top to bottom, the flow cross-sectional area of ​​the first return oil groove 132 and the second return oil groove 133 gradually increases, effectively reducing the flow resistance of the refrigeration oil, increasing the return oil speed and flow rate, and ensuring that a large amount of excess refrigeration oil can quickly and smoothly return to the lower end of the main bearing 130 or the pump oil groove 131 during high-frequency operation, preventing excessive oil supply into the refrigerant circulation. In addition, the gradually changing groove depth structure can make full use of the centrifugal force generated by the crankshaft 140 rotation to guide the refrigeration oil to flow downward along the groove, further enhancing the oil return power. It can achieve efficient oil return without the need for additional power components, thus balancing the improvement of lubrication reliability and system energy efficiency.

[0034] In some optional embodiments, the depth at the end of the first return oil groove 132 is less than a first preset multiple of the depth at the starting point of the first return oil groove 132. Limiting the maximum increase in the depth at the end of the first return oil groove 132 relative to the starting point depth allows for a balance between return oil efficiency, structural strength, processing feasibility, and oil supply stability while maintaining a gradual change in groove depth. Limiting the maximum increase in the depth at the end of the first return oil groove 132 relative to the starting point depth avoids excessive reduction in the effective wall thickness of the main bearing 130 due to an excessively large depth at the end of the first return oil groove 132, ensuring the radial load-bearing capacity and fatigue life of the main bearing 130, and preventing the risk of deformation, cracking, and other failures during long-term operation. Simultaneously, the gradual increase in groove depth results in a linear and slow increase in the cross-sectional area of ​​the first return oil groove 132, leading to a stable change in the refrigerant oil flow rate. This ensures smooth return of excess oil under high-frequency operating conditions while avoiding oil stagnation, eddies, and interference from return oil flow fluctuations caused by a sudden increase in cross-sectional area, thus achieving a dynamic balance between oil supply and return.

[0035] Furthermore, the design that the depth of the end of the first oil return groove 132 is less than a first preset multiple of the depth of the starting point of the first oil return groove 132 can be adapted to conventional CNC machining processes, without the need for special tools or multiple processes, which can reduce machining difficulty and production costs, and improve the parameter consistency of mass production. More importantly, the reasonable groove depth increase limits the oil return capacity, only removing excess refrigeration oil that exceeds lubrication requirements. This ensures the basic oil film thickness of the friction pair between the crankshaft 140 and the main bearing 130, while effectively reducing the oil circulation rate, thus balancing the operational reliability of the compressor 10 and the system heat exchange efficiency.

[0036] In some optional embodiments, the depth at the end of the second return oil groove 133 is less than a second preset multiple of the depth at the starting point of the second return oil groove 133. Limiting the maximum increase in the depth at the end of the second return oil groove 133 relative to the starting point allows for an optimal balance between stability, lubrication reliability, and structural performance in the closed-loop oil circulation, while maintaining a gradual change in groove depth, taking into account the unique loop characteristic of the second return oil groove 133 directly connecting to the pump oil groove 131. Limiting the maximum increase in the depth at the end of the second return oil groove 133 relative to the starting point also prevents excessive reduction of the effective wall thickness of the main bearing 130 due to an excessively large depth at the end of the return oil groove, ensuring the radial load-bearing capacity and fatigue life of the main bearing 130, and preventing the risk of deformation, cracking, and other failures during long-term operation. Since the end of the second return oil groove 133 is directly connected to the pump oil groove 131, the gradual increase in groove depth allows for stable and controllable return oil flow. This avoids oil stagnation, eddies, and drastic fluctuations in return oil flow caused by a sudden increase in cross-sectional area, preventing return oil impact from interfering with the normal pumping pressure and flow of the pump oil groove 131. This ensures stable operation of the closed-loop system, especially under low-frequency conditions, allowing the accumulated oil at the top to be smoothly replenished to the pump oil groove 131, continuously improving the pumping oil level and lubrication effect. Simultaneously, a reasonable increase in groove depth limits the return oil capacity, guiding only excess refrigerant oil exceeding lubrication requirements back to the pump oil groove 131. This ensures the basic oil film thickness of the upper friction pair between the crankshaft 140 and the main bearing 130 while avoiding upper lubrication loss due to excessive return oil.

[0037] In addition, the design of limiting the maximum increase in the depth of the end of the second return oil groove 133 relative to the starting depth can be adapted to conventional CNC milling and grinding processes without the need for special tools or multiple processes, reducing the processing difficulty and production cost, improving the parameter consistency of mass production, and working in synergy with the corresponding design of the first return oil groove 132 to achieve precise oil supply and return control of the variable frequency compressor 10 across the entire frequency band.

[0038] In some optional embodiments, the first preset multiple and the second preset multiple can be 1.2 to 1.3 times, preferably 1.25 times. The above-mentioned values ​​of the first preset multiple and the second preset multiple are merely examples, and those skilled in the art can select appropriate values ​​of the first preset multiple and the second preset multiple according to specific application scenarios and requirements.

[0039] In some optional embodiments, the depths of the first return oil groove 132 and the second return oil groove 133 are greater than or equal to the depth of the pump oil groove 131. Having the first return oil groove 132 and the second return oil groove 133 at a depth greater than or equal to the depth of the pump oil groove 131 ensures that the first return oil groove 132 and the second return oil groove 133 have a larger flow cross-sectional area and lower flow resistance, significantly improving return oil efficiency and oil supply stability under all operating conditions.

[0040] During high-frequency operation, the larger return oil groove can quickly drain excess refrigerant oil from the upper end of the main bearing 130, allowing it to flow back to the lower end of the main bearing 130 via the first return oil groove 132, thus preventing excess oil from overflowing into the refrigerant circulation and effectively reducing the oil circulation rate.

[0041] During low-frequency operation, the deeper return oil groove has a stronger oil accumulation and gathering capacity, which can fully collect the small amount of refrigeration oil dispersed at the upper end of the main bearing 130 and guide it back, preventing the oil from stagnating and evaporating on the end face, providing continuous replenishment to the pump oil circuit, and improving the reliability of low-frequency lubrication.

[0042] Furthermore, the design that the depth of the first return oil groove 132 and the second return oil groove 133 is greater than or equal to the depth of the pump oil groove 131 can achieve efficient oil return without deepening the pump oil groove 131. This avoids the problem of excessively deep pump oil groove 131 weakening the structural strength of the main bearing 130. Moreover, the depth difference between the return oil groove and the pump oil groove can ensure the unidirectional flow of return oil, preventing the oil in the pump oil groove 131 from flowing back into the return oil groove and interfering with normal pumping, thus further optimizing the operational stability of the oil circuit system.

[0043] In some optional embodiments, the pump oil groove 131, the first return oil groove 132, and the second return oil groove 133 are all helical structures extending circumferentially and axially along the inner wall of the main bearing 130. Designing the pump oil groove 131, the first return oil groove 132, and the second return oil groove 133 as helical structures extending synchronously circumferentially and axially along the inner wall of the main bearing 130 can fully utilize the centrifugal force generated by the rotation of the crankshaft 140 and the viscous shear force of the refrigeration oil, comprehensively enhancing the pumping and return oil dynamics of the oil circuit system, and achieving more efficient and stable lubrication and oil control effects under all operating conditions.

[0044] The spiral structure can be adapted to the rotation direction of the crankshaft 140, which can significantly enhance the active oil pumping capacity of the oil sump 131, improve the delivery efficiency and pumping height of the refrigeration oil, especially under low frequency and low speed conditions, it can effectively compensate for the decrease in pumping capacity caused by insufficient centrifugal force, and ensure the basic oil supply at the upper end of the main bearing 130.

[0045] For the first return oil groove 132 and the second return oil groove 133, the spiral structure can not only utilize gravity, but also guide the refrigeration oil to flow in a directional manner along the groove by means of the circumferential driving force generated by the rotation of the crankshaft 140, providing additional power for the return oil process, accelerating the return oil speed, avoiding oil stagnation at the upper end of the main bearing 130, and making the return oil flow more stable and controllable, reducing the impact and interference on the pump oil circuit.

[0046] Furthermore, the continuous spiral oil grooves can form a more uniform and continuous oil film distribution on the friction pair surfaces of the crankshaft 140 and the main bearing 130, covering a larger contact area and avoiding local dry friction, thereby improving lubrication reliability. The spiral structure has a more uniform stress distribution and does not produce the stress concentration problem common in straight grooves, effectively ensuring the structural strength and fatigue life of the main bearing 130. Moreover, this structure is compatible with conventional CNC machining processes and can be formed in one pass, with high machining accuracy and good batch consistency. Together with the technical features such as gradually changing groove depth and the return oil groove being deeper than the pump oil groove, it works to achieve precise oil supply and return control of the variable frequency compressor 10 across the entire frequency range.

[0047] In some optional embodiments, the starting point of the second return oil groove 133 coincides with the end of the pump oil groove 131. The starting point of the first return oil groove 132 coincides with the end of the pump oil groove 131. Setting the starting points of both the first return oil groove 132 and the second return oil groove 133 at the end of the pump oil groove 131 allows for precise alignment between the pump oil endpoint and the return oil starting point. This maximizes the oil collection efficiency, flow response speed, and lubrication stability of the oil circuit system, representing an optimized design for the full-condition oil supply needs of the variable frequency compressor 10.

[0048] After the oil pump sump 131 pumps the refrigeration oil from the lower end of the main bearing 130 to the upper end, it will form an oil collection area at its end. The starting points of the first return oil sump 132 and the second return oil sump 133 are directly aligned with this collection area, which can collect the excess refrigeration oil that has just been pumped out in time, and prevent the oil from spreading and stagnating on the upper surface of the main bearing 130 or overflowing with the refrigerant. Especially when operating at low frequency, it can collect the limited oil accumulation at the upper end to the maximum extent, ensuring that all oil that has not participated in lubrication can enter the return oil circulation, significantly improving the oil utilization rate.

[0049] Meanwhile, setting the starting points of both the first return oil groove 132 and the second return oil groove 133 at the end of the pump oil groove 131 enables immediate diversion of the pump oil at the end. Excess oil can flow back through two paths simultaneously: one path flows quickly back to the lower end of the main bearing 130 via the first return oil groove 132, meeting the high-frequency, high-flow return oil requirements; the other path flows directly back to the inlet of the pump oil groove 131 via the second return oil groove 133, forming a partial closed-loop circulation. This continuously replenishes the oil volume in the pump oil circuit at low frequencies, eliminating the need to wait for the oil to flow back to the lower end before pumping again. This significantly shortens the oil circulation cycle and effectively improves the low-frequency pump oil level and lubrication continuity.

[0050] Furthermore, the oil pump groove 131, the first return oil groove 132, and the second return oil groove 133 intersect at the same node, which avoids opening multiple dispersed return oil inlets on the upper end face of the main bearing 130, reduces damage to the bearing end face structure, optimizes stress distribution, simplifies the machining and positioning process, improves the accuracy and batch consistency of oil circuit machining, and ensures that oil is taken only from the end of the pump where the oil film is thickest, without damaging the continuous oil film in other areas of the friction pair, ensuring that the crankshaft 140 and the main bearing 130 always maintain a stable lubrication state.

[0051] This application also provides a compressor 10, such as Figure 1 As shown, the compressor 10 includes the compressor pump body 100 of any of the above embodiments, used to compress low-pressure gaseous refrigerant in an air conditioning or heat pump system and deliver it to the condenser to complete the core work process of the refrigeration cycle. The compressor 10 may also include a sealed housing 200 and a refrigerant oil sump 300. The sealed housing 200 is a closed pressure-bearing structure that encapsulates the compressor pump body 100 entirely inside, forming a high-pressure working chamber isolated from the outside world, achieving a two-phase seal between the refrigerant and the refrigerant oil, and preventing leakage of the system working fluid. The refrigerant oil sump 300 is formed at the bottom of the sealed housing 200 and stores a sufficient amount of refrigerant oil inside, serving as a medium reserve for the entire compressor 10 lubrication system, providing a continuous lubrication source for the crankshaft 140 and various friction pairs such as the main bearing 130 and the auxiliary bearing 120. When the compressor 10 is running, the crankshaft 140 rotates, driving the oil pump sump 131 to pump the refrigerant oil in the refrigerant oil pool 300 from the lower end of the main bearing 130 upwards. After lubricating the friction pair at the upper end of the main bearing 130, excess refrigerant oil flows directly back to the refrigerant oil pool 300 at the bottom of the sealing housing 200 through the first return oil sump 132, or flows back to the oil pump sump 131 through the second return oil sump 133 to participate in local circulation, forming a complete and efficient oil circulation system. The compressor 10 with the above structure can achieve precise control of lubrication and oil circulation over a wide frequency operating range, effectively reducing friction loss and oil circulation rate, significantly improving the operational reliability and system energy efficiency of the compressor 10, and is suitable for various variable frequency air conditioning and heat pump systems.

[0052] Therefore, those skilled in the art should recognize that although many exemplary embodiments of this application have been shown and described in detail herein, many other variations or modifications conforming to the principles of this application can be directly determined or derived from the disclosure of this application without departing from the spirit and scope of this application. Thus, the scope of this application should be understood and construed as covering all such other variations or modifications.

[0053] In the description of this disclosure, it should be understood that the terms "front", "rear", "left", "right", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and 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 of this application.

[0054] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," and "setting," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art should be able to understand the specific meaning of the above terms in this application based on the specific circumstances.

[0055] Unless otherwise specified, all terms used in the description of this disclosure (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0056] In the description of this disclosure, references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0057] Those skilled in the art should understand that the embodiments described below are merely a part of the embodiments of this application, and not all of the embodiments of this application. These partial embodiments are intended to explain the technical principles of this application and are not intended to limit the scope of protection of this application. Based on the embodiments provided in this application, all other embodiments obtained by those skilled in the art without creative effort should still fall within the scope of protection of this application.

Claims

1. A compressor pump body, characterized in that, include: cylinder; A secondary bearing is located at the lower part of the cylinder; The main bearing is located on the upper part of the cylinder; A crankshaft that passes sequentially along its axial direction through the main bearing, the cylinder, and the auxiliary bearing, such that the eccentric portion of the crankshaft rotates in the cylinder; An oil pump groove is formed on the inner wall of the main bearing. The rotation of the crankshaft pumps the refrigeration oil from the lower end of the main bearing to the upper end of the main bearing through the oil pump groove. The first oil return groove is formed on the inner wall of the main bearing. The starting point of the first oil return groove is located at the upper end of the main bearing, and the end of the first oil return groove is connected to the lower end of the main bearing. The first oil return groove is used to transport the refrigeration oil at the upper end of the main bearing to the lower end of the main bearing.

2. The compressor pump body according to claim 1, characterized in that, Also includes: The second return oil groove is formed on the inner wall of the main bearing. The starting point of the second return oil groove is located at the upper end of the main bearing, and the end of the second return oil groove is connected to the pump oil groove. The second return oil groove is used to transport the refrigeration oil at the upper end of the main bearing to the pump oil groove.

3. The compressor pump body according to claim 2, characterized in that, The depths of the first and second return oil tanks gradually increase along the flow direction of the refrigeration oil.

4. The compressor pump body according to claim 3, characterized in that, The depth at the end of the first return oil trough is less than a first preset multiple of the depth at the beginning of the first return oil trough.

5. The compressor pump body according to claim 3, characterized in that, The depth at the end of the second return oil trough is less than a second preset multiple of the depth at the beginning of the second return oil trough.

6. The compressor pump body according to claim 2, characterized in that, The depths of the first return oil sump and the second return oil sump are greater than or equal to the depth of the pump oil sump.

7. The compressor pump body according to claim 2, characterized in that, The pump oil groove, the first return oil groove, and the second return oil groove are all spiral structures extending circumferentially and axially along the inner wall of the main bearing.

8. The compressor pump body according to claim 2, characterized in that, The starting point of the second return oil tank coincides with the end point of the pump oil tank.

9. The compressor pump body according to claim 1, characterized in that, The starting point of the first return oil tank coincides with the end point of the pump oil tank.

10. A compressor, characterized in that, Includes the compressor pump body as described in any one of claims 1-9.

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