Compression pump of air conditioning system

Abstract

The utility model discloses a compression pump of an air conditioning system, which comprises a main shaft provided with a central channel extending along the axial direction of the main shaft; the inclined plate is provided with at least one channel, and the at least one channel is communicated with the central channel of the main shaft; the piston is provided with an outer surface which is in sliding fit with the inner wall of the pump body; the sliding shoe is provided with a first end and a second end, the first end is connected with the piston, and the second end and the inclined plate form a sliding contact surface; the pump body is provided with an inner wall, and the inner wall defines an air cylinder used for reciprocating motion of the piston; wherein the central channel of the main shaft and at least one channel of the swash plate jointly form a lubricating oil channel, and the lubricating oil channel is configured to guide lubricating oil to a sliding shoe between the piston and the swash plate. According to the utility model, the lubricating oil channel directly leading to the sliding contact surface of the sliding shoe and the inclined plate from the main shaft is constructed. Therefore, the lubricating oil can reach the key friction pair of the sliding shoe and the inclined plate more directly and efficiently.

Description

Technical Field

[0001] This utility model relates to the field of automotive air conditioning compressor technology, and in particular to an air conditioning system compressor pump. Background Technology

[0002] With the booming development of the automotive industry and the increasing demands for driving comfort, automotive air conditioning systems have become an indispensable and important component of modern automobiles. As the core component of the refrigeration system, the performance of the automotive air conditioning compressor directly affects the cooling efficiency, energy consumption, and overall reliability of the air conditioning system.

[0003] Currently, there are many types of automotive air conditioning compressors on the market. Based on their working principles, they can be mainly divided into reciprocating compressors, rotary compressors, and scroll compressors. Among them, axial piston compressors are widely used in mid-to-high-end cars and automotive air conditioning systems with high performance requirements due to their compact structure, stable operation, good high-speed performance, and relatively high cooling efficiency. An axial piston compressor mainly consists of key components such as a main shaft, swashplate or rocker plate, piston, sliding shoe or connecting rod, cylinder block, and distributor plate. Its working principle is that the rotation of the main shaft drives the rotation or oscillation of the swashplate or rocker plate, which in turn drives the piston to reciprocate within the cylinder, thus compressing the refrigerant.

[0004] During the operation of an axial reciprocating compressor, frequent relative movements and friction occur between various moving parts, such as between the main shaft and bearings, between the piston and cylinder wall, and between the sliding shoe or connecting rod and the piston, swashplate, or rocker plate. This friction generates heat, reduces mechanical efficiency, accelerates component wear, and may even lead to component failure, severely impacting the compressor's lifespan and reliability. Therefore, effective lubrication is crucial for ensuring the normal operation of an axial reciprocating compressor.

[0005] Traditional automotive air conditioning compressor lubrication primarily relies on refrigerant carrying lubricating oil. This involves adding a specific proportion of lubricating oil to the refrigerant, utilizing the refrigerant's circulation within the system to deliver the lubricating oil to various friction surfaces. While this lubrication method is simple in structure, it has some inherent limitations. First, the lubricating oil delivery efficiency is constrained by the refrigerant's flow rate and velocity, making it difficult to precisely control the time and amount of lubricating oil reaching each friction surface, especially during compressor startup or low-speed operation, where lubrication may be ineffective. Second, the lubricating performance of the lubricating oil may be affected to some extent after mixing with the refrigerant, such as reduced viscosity and weakened oil film strength. Furthermore, for some critical friction pairs, such as the contact surfaces between the sliding track or connecting rod and the swashplate or rocker plate, and the connection points between the piston pin and the sliding track or connecting rod, traditional lubrication methods often fail to provide sufficient and timely lubrication, easily leading to accelerated wear in these areas.

[0006] In existing technologies, the key friction pairs inside axial reciprocating compressors, especially the contact surface between the sliding shoe and the swashplate, often suffer from insufficient lubrication. During the operation of an axial reciprocating compressor, one end of the sliding shoe connects to the piston, while the other end slides against the inclined surface of the swashplate. As the main shaft rotates, the swashplate drives the sliding shoe to slide on its surface, converting rotational motion into reciprocating linear motion of the piston. Due to the significant pressure and relative sliding speed between the sliding shoe and the swashplate, this contact surface becomes one of the areas with the most intense friction inside the compressor. Traditional lubrication methods rely on lubricating oil mixed with the refrigerant. However, the lubricating oil needs to travel a long distance to reach the contact surface between the sliding shoe and the swashplate, and the oil quantity and oil film stability are difficult to guarantee.

[0007] Specifically, lubricating oil typically needs to enter the cylinder through the intake process before it can reach the contact area between the slide and the swashplate. This lubrication path is relatively indirect, and the supply of lubricating oil is easily affected by the compressor's operating conditions. For example, at high speeds, the lubricating oil may have difficulty reaching the slide contact surface in the center of the swashplate due to centrifugal force; at low speeds or during startup, the supply of lubricating oil may be insufficient to form a stable oil film. Furthermore, lubricating oil mixed with refrigerant may have its viscosity and lubricating properties affected by the refrigerant. Under high pressure and high temperature conditions, the oil film strength may decrease, making it difficult to effectively isolate the friction surfaces, leading to direct contact and wear.

[0008] Insufficient lubrication increases the coefficient of friction between the sliding track and the swashplate, generating significant frictional heat and raising the temperature in that area. High temperatures not only accelerate the oxidation and deterioration of the lubricating oil, further reducing its lubricating performance and creating a vicious cycle, but also cause thermal deformation of components, affecting fit accuracy and sealing performance. Prolonged operation under insufficient lubrication conditions can lead to wear, scratches, and even spalling on the contact surfaces of the sliding track and swashplate. The resulting metal particles further exacerbate the wear of other moving parts, shortening the compressor's lifespan. Furthermore, increased friction leads to energy loss, reducing the compressor's cooling efficiency and increasing energy consumption. Severe lubrication problems can also generate abnormal noise and vibration, affecting the vehicle's NVH performance (noise, vibration, and harshness), reducing ride comfort. To improve compressor durability and reliability, some high-end compressors may employ more complex lubrication supply systems, such as independent oil pumps and oil passages, but this undoubtedly increases the compressor's structural complexity and manufacturing costs.

[0009] Therefore, effectively delivering lubricating oil to the key friction pairs inside an axial reciprocating compressor, especially the contact surface between the sliding shoe and the swashplate, and ensuring the timeliness and stability of lubricating oil supply, has been a technical challenge that those skilled in the art have been working to solve. Addressing the aforementioned problems with existing lubrication methods, there is an urgent need for a novel lubrication system that is simple in structure, highly efficient, and reliable, in order to improve the service life and performance of axial reciprocating compressors. Utility Model Content

[0010] Based on the above background, this utility model aims to provide a compressor pump for an air conditioning system that optimizes the delivery path of lubricating oil to achieve more effective lubrication of key friction pairs, thereby solving the problem of insufficient lubrication in the prior art and improving the working efficiency and service life of the compressor.

[0011] To achieve the above objectives, this utility model discloses a compressor pump for an air conditioning system, comprising: a main shaft having a central channel extending axially thereon; an inclined plate having at least one channel communicating with the central channel of the main shaft; a piston having an outer surface that slides in contact with the inner wall of the pump body; a slipper having a first end and a second end, the first end being connected to the piston and the second end forming a sliding contact surface with the inclined plate; and a pump body having an inner wall defining a cylinder for reciprocating motion of the piston; wherein the central channel of the main shaft and at least one channel of the inclined plate together form a lubricating oil channel, the lubricating oil channel being configured to guide lubricating oil to the slipper between the piston and the inclined plate.

[0012] Preferably, the central channel of the spindle is a through hole extending along the spindle axis, and the cross-section of the through hole is circular. This designation of the central channel as a through hole ensures that lubricating oil can be smoothly delivered from one end to the other, laying the foundation for subsequent lubricating oil flow into the inclined plate channel. This feature enhances the reliability of lubricating oil delivery.

[0013] Preferably, at least one channel of the inclined plate is an oil passage formed within the inclined plate body, and the oil passage extends along a predetermined path. This defines the specific structure of the inclined plate channel as an internal oil passage, distinct from the external structure, providing a physical channel for the directional flow of lubricating oil within the inclined plate, and facilitating the lubricating oil to reach the contact surfaces requiring lubrication.

[0014] Preferably, the inclined plate has two or more oil passages, which are spaced apart along the circumference of the inclined plate. By providing multiple channels, the supply of lubricating oil can be increased, the contact surface between the slide and the inclined plate can be lubricated more evenly, the risk of local overheating and wear can be reduced, and the lubrication effect can be improved.

[0015] Preferably, the lubricating oil is configured to flow sequentially through the central channel of the main shaft and at least one channel of the inclined plate, and ultimately reach the sliding contact surface between the slide and the inclined plate. This clarifies the flow path of the lubricating oil within the channels of the main shaft and the inclined plate, emphasizes the process by which the lubricating oil ultimately reaches the sliding contact surface between the critical friction pair, the slide and the inclined plate, and directly reflects the purpose of this invention to improve the lubrication effect of key components.

[0016] Preferably, the cross-section of at least one channel of the inclined plate is circular or selected from elliptical and polygonal shapes. This defines the specific shape of the inclined plate channel; different shapes may affect the flow rate, pressure, and distribution of the lubricating oil. A suitable orifice shape can be selected according to actual needs to further optimize the lubrication effect.

[0017] Preferably, it also includes an oil inlet, which is located at the end of the spindle and communicates with the central channel of the spindle. This adds a necessary structural feature—the oil inlet—clearly defines the entry point for lubricating oil into the entire lubrication system, ensuring the integrity of the lubrication system and making the entry of lubricating oil more controllable and stable.

[0018] In summary, this invention constructs a lubricating oil channel directly from the main shaft to the sliding contact surface between the slide and the inclined plate by setting a central channel inside the main shaft and at least one channel on the inclined plate that communicates with the central channel of the main shaft. This design changes the traditional method of compressors relying on refrigerant to carry lubricating oil, allowing the lubricating oil to reach the key friction pair between the slide and the inclined plate more directly and efficiently. This effectively solves the technical problem of accelerated wear in this part due to insufficient lubricating oil supply in the prior art, and improves the operating reliability and service life of the compressor. Attached Figure Description

[0019] Figure 1 This is a cross-sectional structural schematic diagram of the air conditioning system compressor pump according to one embodiment of the present invention. Detailed Implementation

[0020] The present invention will be described more clearly and completely below through embodiments and in conjunction with the accompanying drawings.

[0021] Figure 1 A cross-sectional structural schematic diagram of an air conditioning system compressor pump according to a specific embodiment of the present invention is shown. Figure 1 As shown, the compressor pump of this air conditioning system mainly includes: main shaft 1, inclined plate 2, piston 3, pump body 4, and sliding shoe 5.

[0022] The main shaft 1 is the core rotating component of the compression pump, typically made of high-strength alloy steel to withstand high-speed rotation and transmit torque. The main shaft 1 has a central channel 11 extending along its axial direction. This central channel 11 is a through-hole extending along the axis of the main shaft 1, preferably with a circular cross-section to facilitate smooth flow of lubricating oil and reduce flow resistance. For example, the diameter of the central channel 11 can be set to 2-5 mm, and the specific dimensions can be adjusted according to the model of the compression pump and lubrication requirements. The central channel 11 provides an efficient delivery path for the lubricating oil and is a key structure for achieving the lubrication objective of this invention.

[0023] The inclined plate 2 is mounted on the main shaft 1 and rotates with the main shaft 1. The inclined plate 2 has at least one channel 21, which communicates with the central channel 11 of the main shaft 1. In this embodiment, the inclined plate 2 has multiple channels 21, such as three. The multiple oil channels 21 are formed within the body of the inclined plate 2 and extend along a predetermined path. For example, they can be inclined oil channels extending from the area near the central channel 11 of the main shaft towards the outer edge of the inclined plate 2. Preferably, the multiple oil channels 21 are evenly spaced along the circumference of the inclined plate 2, for example, at 120-degree intervals, to ensure that the lubricating oil can be more evenly distributed to each slide 5. The cross-section of at least one channel 21 of the inclined plate can be a circular hole or selected from elliptical, polygonal (such as triangular, rectangular), etc. The specific shape can be designed according to the flow requirements and flow characteristics of the lubricating oil. For example, circular holes are simple to design and process and have low flow resistance; elliptical or polygonal holes can change the flow direction and pressure distribution of the lubricating oil to more accurately lubricate the target area.

[0024] The piston 3 reciprocates inside the pump body 4 to compress the refrigerant. The piston 3 is typically made of a lightweight, high-strength material, such as aluminum alloy. The piston 3 has an outer surface 31 that slides against the inner wall 41 of the pump body 4, forming the working chamber of the cylinder. To ensure good sealing, the piston 3 is usually also equipped with piston rings (not shown in the diagram).

[0025] The sliding shoe 5 transmits power between the piston 3 and the inclined plate 2, converting the rotational motion of the inclined plate 2 into the reciprocating linear motion of the piston 3. The sliding shoe 5 has a first end and a second end. The first end is connected to the piston 3, for example, via a piston pin, allowing for a certain degree of rotational freedom. The second end forms a sliding contact surface with the inclined plate 2. The second end of the sliding shoe 5 is typically designed as an arc or a plane that matches the surface of the inclined plate 2 to reduce contact stress and improve wear resistance.

[0026] The pump body 4 is the main structure of the compression pump, typically made of cast iron or aluminum alloy, and possesses high strength and rigidity. The pump body 4 has an inner wall 41 that defines a cylinder for the reciprocating motion of the piston 3. The inner wall 41 is precision-machined to achieve a high surface finish, thereby reducing frictional resistance during piston 3 movement.

[0027] In this invention, the central channel 11 of the main shaft 1 and at least one channel 21 of the inclined plate 2 together form a lubricating oil channel, which is configured to guide lubricating oil to the sliding shoe 5 between the piston 3 and the inclined plate 2. The specific lubricating oil flow path is as follows: the lubricating oil first enters the central channel 11 of the main shaft 1 through an inlet (not shown in the diagram). Since the central channel 11 of the main shaft 1 is a through hole extending along the axis of the main shaft 1, the lubricating oil can flow smoothly within the central channel 11. Then, the lubricating oil flows from the central channel 11 of the main shaft 1 into at least one channel 21 of the inclined plate 2. Since at least one channel 21 of the inclined plate 2 is an oil passage formed within the body of the inclined plate 2, the lubricating oil is confined within the oil passage and reaches the sliding contact surface between the sliding shoe 5 and the inclined plate 2 along a predetermined path.

[0028] This lubrication method allows the lubricating oil to directly and efficiently reach the sliding contact surface between the slide 5 and the inclined plate 2, forming an oil film on this surface. This reduces friction and wear, effectively protecting key components and extending the service life of the compressor pump. Compared to traditional lubrication methods that rely on refrigerant to carry the lubricating oil, this invention provides a more timely and sufficient supply of lubricating oil, especially under conditions with high lubrication requirements such as compressor start-up and low-speed operation, where its advantages are even more pronounced.

[0029] In a preferred embodiment, the oil inlet is located at the end of the spindle 1 and communicates with the central channel 11 of the spindle 1. This arrangement allows lubricating oil to directly enter the central channel 11 of the spindle 1, simplifying the lubricating oil supply path and improving lubrication efficiency. The oil inlet can be designed as a threaded connection or a press-fit connection for easy connection to external lubricating oil pipelines.

[0030] For example, during operation, lubricating oil, under the action of an oil pump (not shown in the diagram), enters the central channel 11 of the main shaft 1 through the oil inlet. As the main shaft 1 rotates, the lubricating oil, under the action of centrifugal force, is further thrown into the oil passage 21 of the swashplate 2, and finally reaches the sliding contact surface between the slide shoe 5 and the swashplate 2, effectively lubricating this contact surface. The lubricating oil forms an oil film between the contact surfaces, which can significantly reduce the coefficient of friction, reduce the generation of frictional heat, thereby lowering the operating temperature and improving the operating efficiency and reliability of the compressor.

[0031] Furthermore, because this invention employs an independent lubricating oil channel, the appropriate lubricating oil type and viscosity can be selected according to actual needs, unaffected by refrigerant characteristics, thus better meeting the lubrication requirements of critical friction pairs. Simultaneously, the independent lubricating oil channel also reduces the mixing of lubricating oil and refrigerant, mitigating potential adverse effects on refrigerant circulation.

[0032] Specifically, such as Figure 1 As shown, the air conditioning system compressor pump of this utility model also includes a front cover 6, a rear cover 7, an intake valve plate 8, an exhaust valve plate 9, a rear valve plate assembly 10, a thrust bearing assembly 12, a shaft seal 13, a front valve plate assembly 14, and a clutch 15.

[0033] The front cover 6 is located at the front end of the pump body 4 and is fixedly connected to the pump body 4 by bolts or other means, forming the cavity inside the compressor pump together with the pump body 4.

[0034] The rear end cover 7 is located at the rear end of the pump body 4 and is also fixedly connected to the pump body 4 by bolts or other means, forming the cavity inside the compressor pump together with the pump body 4.

[0035] The intake valve plate 8 is disposed on the rear valve plate assembly 10 and is used to control the intake of refrigerant vapor.

[0036] The exhaust valve plate 9 is disposed on the rear valve plate assembly 10 and is used to control the discharge of compressed refrigerant vapor.

[0037] The rear valve plate assembly 10 is installed on the rear end face of the pump body 4, and has an air intake port and an air exhaust port. It is also equipped with an air intake valve plate 8 and an air exhaust valve plate 9 to control the intake and exhaust of refrigerant.

[0038] The thrust bearing assembly 12 is disposed between the main shaft 1 and the pump body 4 to support the main shaft 1 and withstand the axial thrust generated when the main shaft 1 is running, thereby ensuring the smooth rotation of the main shaft 1.

[0039] The shaft seal 13 is located at the point where the main shaft 1 passes through the pump body 4, and is used to prevent refrigerant and lubricating oil leakage inside the compressor pump.

[0040] The front valve plate assembly 14 is installed on the front end face of the pump body 4. Its structure and function are similar to the rear valve plate assembly 10, and it is used to control the refrigerant intake and discharge of another part of the cylinder.

[0041] The clutch 15 is mounted on the outside of the main shaft 1 and is used to control the start and stop of the compression pump. It is usually connected to the automobile engine and is engaged and disengaged by electromagnetic control.

[0042] These components work together with the main shaft 1, swashplate 2, piston 3, pump body 4, and slide 5 to complete the refrigerant intake, compression, and discharge processes, thereby realizing the cooling function of the automotive air conditioning system.

[0043] Through the above structural design, the automotive air conditioning compressor pump of this utility model not only has a highly efficient internal lubrication system, but also has good shock absorption performance, which can effectively reduce vibration during operation and improve the ride comfort of the car.

Claims

1. An air conditioning system compressor pump, characterized by, The application relates to a pump body, comprising: a pump body having a cylinder with an inner wall; a main shaft having a central passage extending along an axial direction thereof; a swash plate having at least one passage in communication with the central passage of the main shaft; a piston having an outer surface in sliding fit with the inner wall of the cylinder; a shoe having a first end connected with the piston and a second end in sliding contact with the swash plate; wherein the central passage of the main shaft and the at least one passage of the swash plate jointly form a lubricating oil passage configured to guide lubricating oil to the shoe between the piston and the swash plate.

2. The air conditioning system compression pump of claim 1, wherein, The central passage of the main shaft is a through hole extending along the axial direction of the main shaft, and the cross section of the through hole is circular.

3. The air conditioning system compression pump of claim 2, wherein, The at least one passage of the swash plate is an oil channel formed in the swash plate body and extending along a preset path.

4. The air conditioning system compression pump of claim 3, wherein, The swash plate has two or more oil channels distributed along the circumferential direction of the swash plate.

5. The air conditioning system compression pump of claim 1, wherein, The lubricating oil is configured to flow through the central passage of the main shaft and the at least one passage of the swash plate in sequence and finally reach the sliding contact surface of the shoe and the swash plate.

6. The air conditioning system compression pump of claim 5, wherein, The cross section of the at least one passage of the swash plate is circular or selected from one of an ellipse and a polygon.

7. The air conditioning system compression pump of claim 1, wherein, The application further comprises an oil inlet arranged at the end of the main shaft and in communication with the central passage of the main shaft.

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