Pump assembly, compressor and air conditioner

Abstract

This invention relates to the field of compressor technology, specifically to a pump body assembly, a compressor, and an air conditioner. The pump body assembly includes a cylinder and an oil guiding structure. A partition is fitted onto one side of the cylinder, and a cylinder head is fitted onto the other side. The cylinder has a vane groove for mounting a vane. A first oil groove extending axially along the cylinder is provided on the side wall of the vane groove. An oil hole is provided on the partition, opposite to the side of the vane away from the cylinder head, and the oil hole communicates with the first oil groove. The oil guiding structure guides lubricating oil to the oil hole, allowing the lubricating oil to flow into the first oil groove. A back pressure cavity is formed between the side of the vane away from the partition and the cylinder head. The oil guiding structure also guides lubricating oil into the back pressure cavity, providing a force to the vane relative to the partition. According to the technical solution of this invention, the back pressure cavity provides back pressure to the vane, balancing the axial impact of the lubricating oil in the oil hole on the vane, resulting in a more balanced axial force on the vane and thus reducing wear on the vane's end face.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a pump assembly, a compressor, and an air conditioner. Background Technology

[0002] In the global context of green, low-carbon, and environmentally friendly practices, improving the energy efficiency of air conditioning compressors has always been a hot topic in industry research. Compressor energy losses can be categorized into motor losses, friction losses, and indication losses, with friction losses consistently accounting for a significant portion of total compressor losses. Compressor friction losses are primarily caused by friction generated between compressor components during operation. These losses are mainly caused by friction from parts such as vanes, eccentric bearings, thrust surfaces, main and auxiliary bearings, rollers, and rotor balance weights. Research indicates that vane friction losses consistently constitute the largest portion of total compressor friction losses. Figure 1 As shown, this friction loss accounts for a larger proportion under high-frequency operation, reaching approximately 50% of the total friction loss. Therefore, reducing vane friction loss is one of the key paths to improving compressor energy efficiency.

[0003] During compressor operation, the vanes reciprocate within the vane slot under the action of the pump spring, following the rollers. This large-area contact between the vane side surface and the slot wall, as well as between the upper and lower end faces and the upper and lower planes, generates significant frictional losses. As the compressor frequency increases, especially during high-frequency operation, the oil discharge rate within the compressor increases substantially, leading to a significant drop in oil level and a substantial decrease in oil supply through the spring hole at the tail of the vane slot. This results in insufficient oil supply to the vane and the slot, causing a significant increase in vane frictional power consumption. In severe cases, dry friction between the vane and the slot, as well as the upper and lower end faces, can cause severe vane wear, leading to compressor reliability issues. To address vane wear, the industry commonly uses surface coatings to strengthen the vanes and mitigate wear. However, these coatings significantly increase compressor costs. Therefore, to avoid excessive vane wear and high costs, there is an urgent need to design a solution that ensures adequate oil supply to the vane area.

[0004] Based on the aforementioned issues of low energy efficiency and reliability caused by insufficient high-frequency oil supply to conventional compressor vanes, our company conducted a thorough comparative analysis of existing technologies and proposed an innovative patent proposal (patent number: 202210648504.9) for a sliding vane friction reduction system for a rolling rotor dual-cylinder compressor. This system supplies oil to the sliding vane slots on the cylinder by opening intersecting horizontal and vertical oil holes on the partition plate corresponding to the vane slots. This solution can significantly increase the lubrication of both sides of the vane, resulting in the beneficial effects of reducing frictional power consumption and improving reliability. However, in this solution, the vertical oil holes on the partition plate are opposite to the vanes, and the high-pressure lubricating oil in the vertical oil holes causes the upper vane to bear an upward axial force and the lower vane to bear a downward axial force. This leads to abnormal wear between the upper end face of the upper vane and the upper flange face, and between the lower end face of the lower vane and the lower flange face. This not only increases the power consumption of the vane end face but also brings new reliability problems. Therefore, it is urgent to solve this problem. Summary of the Invention

[0005] In view of this, the present invention provides a pump body assembly, a compressor and an air conditioner. The main technical problem to be solved is: how to improve the axial balance of the vane and reduce the wear of the vane end face.

[0006] To achieve the above objectives, the present invention mainly provides the following technical solutions:

[0007] In a first aspect, embodiments of the present invention provide a pump body assembly, including a cylinder and an oil guiding structure. A partition is covered on one side of the cylinder, and a cylinder cover is covered on the other side of the cylinder. The cylinder has a vane groove for mounting a vane. A first oil groove extending axially along the cylinder is provided on the side wall of the vane groove. An oil hole is provided on the partition. The oil hole is opposite to the side of the vane away from the cylinder cover and communicates with the first oil groove. The oil guiding structure is used to guide lubricating oil to the oil hole so that the lubricating oil flows into the first oil groove through the oil hole.

[0008] The side of the sliding vane away from the partition plate forms a back pressure cavity with the cylinder head. The oil guiding structure is also used to guide lubricating oil into the back pressure cavity, so that the back pressure cavity provides the sliding vane with a force relative to the partition plate.

[0009] In some embodiments, the back pressure chamber includes a second oil groove disposed on the cylinder head to receive lubricating oil from the oil guiding structure. The opening of the second oil groove is opposite to the side of the slide that is away from the partition. The back pressure chamber provides a force to the slide relative to the partition through the lubricating oil inside the second oil groove.

[0010] In some embodiments, the second oil groove is connected to the first oil groove, and the oil guiding structure guides the lubricating oil to the second oil groove through the first oil groove.

[0011] In some embodiments, one end of the first oil groove extends through the vane groove along the cylinder axis, and the opening of one end of the first oil groove is opposite to the opening of the second oil groove so that the two are connected.

[0012] In some embodiments, the shapes of the opening at one end of the first oil groove and the opening of the second oil groove are adapted to match, such that the projected outline of the opening at one end of the first oil groove on a plane perpendicular to the cylinder axis lies on the projected outline of the opening of the second oil groove on a plane perpendicular to the cylinder axis.

[0013] In some embodiments, the opening shape of the oil hole and the second oil groove are the same, and the projection contours of their openings on a plane perpendicular to the cylinder axis coincide.

[0014] In some embodiments, the opening of the second oil groove extends beyond both sides of the slide plate in the thickness direction.

[0015] In some embodiments, the pump assembly further includes an oil return structure for draining lubricating oil from the first oil sump and the back pressure chamber to an oil reservoir.

[0016] In some embodiments, when the back pressure chamber includes a second oil groove disposed on the cylinder head and the second oil groove is in communication with the first oil groove, the oil return structure includes an oil guide groove disposed on the side of the sliding vane groove near the cylinder head. One end of the oil guide groove extends to the intersection of the first oil groove and the second oil groove, so that the oil guide groove is in communication with both the first oil groove and the second oil groove. The oil return structure guides the lubricating oil in the first oil groove and the second oil groove to the oil sump through the other end of the oil guide groove.

[0017] In some embodiments, there are two cylinders, and the partition is located between the two cylinders; there are two cylinder heads, and they are arranged in a one-to-one correspondence with the two cylinders.

[0018] There are two back pressure chambers, and they are set up one-to-one with the two cylinders.

[0019] Secondly, embodiments of the present invention also provide a compressor that may include any of the pump body assemblies described above.

[0020] Thirdly, embodiments of the present invention also provide an air conditioner that may include any of the compressors described above.

[0021] By employing the above technical solutions, the pump assembly, compressor, and air conditioner of the present invention have at least the following beneficial effects:

[0022] 1. In the technical solution provided by this invention, the back pressure chamber can provide more lubricating oil to the end face of the slide plate away from the partition plate, thereby reducing frictional power consumption and improving compressor efficiency. In addition, the back pressure chamber can provide back pressure to the slide plate to counteract the axial impact of the lubricating oil in the oil hole on the slide plate, making the axial force on the slide plate more balanced, thereby reducing the wear of the end face of the slide plate;

[0023] 2. The end face and side face of the slider do not need to use slider coating technology, which reduces costs.

[0024] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0025] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram showing the percentage of frictional losses in different parts of the compressor;

[0027] Figure 2 This is a schematic diagram of the structure of a pump body assembly provided in an embodiment of the present invention;

[0028] Figure 3 yes Figure 2 A schematic diagram of the pump body assembly with the sliding vanes concealed.

[0029] Figure 4 yes Figure 3 Enlarged view of point A in the middle;

[0030] Figure 5 It is a schematic diagram showing the cooperation between the sliding vane on the pump body assembly and the first and second oil grooves;

[0031] Figure 6 yes Figure 5 Enlarged view of point B in the middle;

[0032] Figure 7 This is a structural diagram of the upper flange;

[0033] Figure 8 This is a top view of the upper cylinder;

[0034] Figure 9 It is a bottom view of the upper cylinder;

[0035] Figure 10 This is a schematic diagram of the partition structure;

[0036] Figure 11 This is a cross-sectional view of the partition;

[0037] Figure 12 This is a top view of the lower cylinder;

[0038] Figure 13 It is a bottom view of the lower cylinder;

[0039] Figure 14 This is a structural diagram of the lower flange.

[0040] Reference numerals: 1. Crankshaft; 2. Upper flange; 3. Upper muffler; 4. Cylinder; 5. Diaphragm; 6. Cylinder head; 7. Upper roller; 8. Lower roller; 9. Lower flange; 10. Lower muffler; 11. Oil guide plate; 12. Oil suction pipe; 13. Upper screw; 14. Lower screw; 15. Oil plug; 16. Sliding vane; 101. Upper eccentric oil hole; 102. Upper eccentric oil groove; 103. Lower eccentric oil hole; 104. Lower eccentric oil groove; 201. Second oil groove; 401. First oil groove; 402. Oil guide groove; 403. Spring vertical hole; 404. Spring horizontal hole; 405. Bevel cut; 406. Sliding vane groove; 501. Horizontal hole; 502. Oil hole; 503. Diaphragm center hole; 504. Oil plug hole. Detailed Implementation

[0041] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0042] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0043] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0044] like Figure 2 and Figure 3 As shown, an embodiment of the present invention provides a pump body assembly including a cylinder 4 and an oil guide structure. A partition 5 is fitted onto one side of the cylinder 4, and a cylinder head 6 is fitted onto the other side of the cylinder 4. There are two or more cylinders 4, and a partition 5 is provided between adjacent cylinders 4. Both the uppermost cylinder 4 and the lowermost cylinder 4 have cylinder heads 6. The cylinder head 6 of the uppermost cylinder 4 can be integrally formed on the upper flange 2, and the cylinder head 6 of the lowermost cylinder 4 can be integrally formed on the lower flange 9.

[0045] The cylinder 4 has a vane groove 406 for mounting the vane 16. A first oil groove 401 extending axially along the cylinder is provided on the side wall of the vane groove 406, and this first oil groove 401 can penetrate both ends of the cylinder axially. An oil hole 502 is provided on the partition 5, and this oil hole 502 can be a vertical oil hole. The oil hole 502 is opposite to the side of the vane 16 away from the cylinder head 6, and the oil hole 502 communicates with the first oil groove 401. Preferably, the oil hole 502 is opposite to the side opening of the first oil groove 401 near the partition 5, so that the oil hole 502 communicates with the first oil groove 401.

[0046] The aforementioned oil guiding structure is used to guide lubricating oil to the oil hole 502, allowing the lubricating oil to flow into the first oil groove 401 through the oil hole 502. The structure of guiding lubricating oil into the oil hole 502 is prior art and will not be described in detail here. Since the oil hole 502 is opposite to the side of the sliding vane 16 away from the cylinder head 6, the lubricating oil in the oil hole 502 can flow into the sliding vane groove 406, lubricating the side of the sliding vane 16 away from the cylinder 4. After flowing into the first oil groove 401, the lubricating oil can also lubricate the side of the sliding vane 16. In a specific application example, such as... Figure 8 and Figure 9 As shown, there are two first oil grooves 401, which are respectively set on two opposite side walls of the slide groove 406. The lubricating oil in the two first oil grooves 401 can lubricate the two sides of the slide 16.

[0047] Among them, the side of the sliding vane 16 away from the partition 5 forms a back pressure cavity with the cylinder head 6. The oil guiding structure is also used to guide the lubricating oil into the back pressure cavity, so that the back pressure cavity provides the sliding vane 16 with a force relatively close to the partition 5.

[0048] In the above example, the back pressure chamber provides more lubricating oil to the end face of the vane 16 facing away from the partition 5, reducing frictional power consumption and improving compressor efficiency. Additionally, the back pressure chamber provides back pressure to the vane 16 to counteract the axial impact of the lubricating oil in the oil hole 502 on the vane 16, resulting in a more balanced axial force on the vane 16 and thus reducing end face wear.

[0049] In a specific application example, such as Figures 4 to 6 As shown, the aforementioned back pressure chamber may include a second oil groove 201 disposed on the cylinder head 6. The back pressure chamber receives lubricating oil from the oil guiding structure through the second oil groove 201. The opening of the second oil groove 201 is opposite to the side of the slide plate 16 away from the partition plate 5. The back pressure chamber provides the slide plate 16 with a force relative to the partition plate 5 through the lubricating oil inside the second oil groove 201.

[0050] In the above example, the back pressure chamber receives lubricating oil through the second oil groove 201 and provides back pressure to the slide plate 16. The second oil groove 201 is located on the side of the cylinder head 6 near the slide plate 16, which has the advantage of being easy to process.

[0051] The aforementioned second oil groove 201 can be connected to the first oil groove 401, and the oil guiding structure guides the lubricating oil to the second oil groove 201 through the first oil groove 401. Preferably, one end of the first oil groove 401 passes through the vane groove 406 along the cylinder axis, and the opening of one end of the first oil groove 401 is opposite to the opening of the second oil groove 201 so that the two are connected.

[0052] In the above example, the first oil tank 401 can serve as part of the oil guiding structure to guide oil to the second oil tank 201, without the need to separately open an oil passage to guide oil to the second oil tank 201. This has the advantage of simplifying the structure and making the overall oil guiding structure more compact.

[0053] In a specific application example, such as Figure 7 and Figure 8As shown, the shapes of the opening at one end of the first oil groove 401 and the opening of the second oil groove 201 are adapted to match, such that the projected outline of the opening at one end of the first oil groove 401 on a plane perpendicular to the cylinder axis lies on the projected outline of the opening of the second oil groove 201 on the same plane. For example, if the projected outline of the opening of the second oil groove 201 on the same plane is waist-shaped, and the projected outline of the opening at one end of the first oil groove 401 on the same plane is arc-shaped, the arc-shaped outline coincides with the arc segment on the waist-shaped outline. This design is mainly to facilitate the smooth flow of lubricating oil from the first oil groove 401 into the second oil groove 201, thereby reducing the flow resistance of the lubricating oil.

[0054] In a specific application example, such as Figure 7 and Figure 10 As shown, the opening shapes of the aforementioned oil hole 502 and the second oil groove 201 are identical, and the projected outlines of their openings on a plane perpendicular to the cylinder axis coincide. For example, the projected outlines of their openings on a plane perpendicular to the cylinder axis are both waist-shaped and coincide. This design is mainly to ensure that the lubricating oil in both the oil hole 502 and the second oil groove 201 can provide approximately equal axial force to the slide plate 16, thereby balancing the axial force on the slide plate 16.

[0055] Preferred, such as Figure 6 As shown, the opening of the aforementioned second oil groove 201 extends beyond both sides of the thickness direction of the slide plate 16. Since the opening shape of the oil hole 502 and the second oil groove 201 are the same, the opening of the oil hole 502 also extends beyond both sides of the thickness direction of the slide plate 16. This design is mainly to enable the oil hole 502 and the second oil groove 201 to provide more sufficient lubricating oil to the upper and lower end faces of the slide plate 16, thereby improving the lubrication effect of the end face of the slide plate 16 and further reducing frictional power consumption.

[0056] The aforementioned pump body assembly may also include an oil return structure, which is used to guide the lubricating oil in the aforementioned first oil sump 401 and back pressure chamber to the oil sump to form an oil circuit circulation. This circulation oil circuit can not only ensure the lubrication state of both sides of the slide vane 16 under the reciprocating motion of the slide vane 16, but also ensure the lubrication state of the upper and lower end faces of the slide vane 16, greatly reducing the frictional power consumption of the slide vane 16, and at the same time avoiding the wear problem of the slide vane 16 caused by the compressor under high frequency oil shortage state and the wear problem of the end of the slide vane 16 caused by the axial force of the slide vane 16.

[0057] like Figure 4As shown, when the back pressure chamber includes a second oil groove 201 disposed on the cylinder head 6, and the second oil groove 201 is connected to the first oil groove 401, the aforementioned oil return structure may include an oil guide groove 402 disposed on the side of the sliding vane groove 406 near the cylinder head 6. One end of the oil guide groove 402 extends to the junction of the first oil groove 401 and the second oil groove 201, so that the oil guide groove 402 is connected to both the first oil groove 401 and the second oil groove 201, allowing the lubricating oil in both the first oil groove 401 and the second oil groove 201 to flow into the oil guide groove 402. The oil return structure guides the lubricating oil in the first oil groove 401 and the second oil groove 201 to the oil sump through the other end of the oil guide groove 402.

[0058] In the above example, by providing an oil guide groove 402 extending to the intersection of the first oil groove 401 and the second oil groove 201 on one side of the slide groove 406, it has the advantage of convenient processing.

[0059] In a specific application example, there are two cylinders 4, namely an upper cylinder and a lower cylinder. A partition 5 is located between the two cylinders 4. There are two cylinder heads 6, each corresponding to one of the two cylinders 4. The two cylinder heads 6 are an upper cylinder head and a lower cylinder head, with the upper cylinder head integrally formed on the upper flange 2 and the lower cylinder head integrally formed on the lower flange 9. There are two back pressure chambers, each corresponding to one of the two cylinders 4. In this example, the two back pressure chambers provide back pressure to the sliding vanes 16 in both the upper and lower cylinders to balance the axial forces on the two sliding vanes 16.

[0060] An embodiment of the present invention also provides a compressor that may include any of the pump body assemblies described above. Due to the pump body assembly, the compressor's back pressure chamber can provide back pressure to the vane 16 to counteract the axial impact of the lubricating oil in the oil hole 502 on the vane 16, making the axial force on the vane 16 more balanced, thereby reducing end face wear of the vane 16.

[0061] An embodiment of the present invention also provides an air conditioner that may include any of the compressors described above. Due to the compressor, the air conditioner's back pressure chamber can provide back pressure to the vane 16 to counteract the axial impact of the lubricating oil in the oil hole 502 on the vane 16, making the axial force on the vane 16 more balanced, thereby reducing end face wear of the vane 16.

[0062] The working principle and preferred embodiments of the present invention are described below.

[0063] This invention relates to the design of a pump body assembly that can be used in a compressor, which in turn can be used in an air conditioner. In a specific application example, such as... Figures 2 to 14As shown, the pump body assembly includes cylinders 4 and cylinder heads 6. There can be two cylinders 4, one upper and one lower. There are also two cylinder heads 6, one upper and one lower. The upper cylinder head is integrally formed on the upper flange 2, and the lower cylinder head is integrally formed on the lower flange 9. The pump body assembly also includes a crankshaft 1, which has an upper eccentric portion and a lower eccentric portion. The upper eccentric portion is located inside an upper roller 7, which is fitted into the inner circle of the upper cylinder. The upper flange 2 and the upper muffler 3 are installed on the upper part of the upper cylinder, and are locked together using upper screws 13. The lower eccentric portion is located inside a lower roller 8, which is fitted into the inner circle of the lower cylinder. The lower flange 9 and the lower muffler 10 are installed on the lower part of the lower cylinder. The partition 5 is installed between the lower cylinder and the upper cylinder, and the lower muffler 10, lower flange 9, lower cylinder, partition 5, and upper cylinder are locked together by the lower screw 14. The crankshaft 1 passes through the center holes of the above-mentioned parts. The crankshaft 1 has a crankshaft center oil hole in its center, and an oil guide plate 11 is installed in the crankshaft center oil hole. An oil suction pipe 12 is installed at the lower end of the crankshaft center oil hole. Sliding plates 16 are installed in the sliding plate grooves 406 of both the upper and lower cylinders, and a pump spring is installed at the tail end of each sliding plate 16.

[0064] The aforementioned rolling rotor twin-cylinder pump body assembly mainly involves components such as crankshaft 1, oil suction pipe 12, oil guide plate 11, partition plate 5, oil plug 15, upper cylinder, lower cylinder, sliding vane 16, upper flange 2, and lower flange 9. By creating new lubrication oil passages for these components, the side and end faces of the sliding vane 16 are lubricated. By adding an oil suction pipe 12 at the bottom of crankshaft 1 and setting an oil guide plate 11 in the crankshaft center oil hole, it can be ensured that lubricating oil can still be pumped into the pump body even when the high-frequency oil level is very low. The lubricating oil flows through the crankshaft center oil hole to the upper eccentric oil groove 102 and the lower eccentric oil groove 104 through the upper eccentric oil hole 101 and the lower eccentric oil hole 103, respectively. The upper eccentric oil groove 102 is connected to the lower end face of the upper eccentric part, and the lower eccentric oil groove 104 is connected to the upper end face of the lower eccentric part. Both the upper eccentric oil groove 102 and the lower eccentric oil groove 104 are connected to the central hole 503 of the partition plate, so the lubricating oil can be directly pumped into the central hole 503 of the partition plate. A horizontal hole 501 and a vertical hole are formed at the position corresponding to the sliding plate groove 406 on the partition plate 5; the vertical hole is the aforementioned oil hole 502. The inner side of the horizontal hole 501 is connected to the central hole 503 of the partition plate, and the outer side of the horizontal hole 501 is connected to the oil plug hole 504, which is sealed with an oil plug 15. Figure 4As shown, the lubricating oil in the central hole 503 of the partition can be pumped to the vane groove 406 area of ​​the upper and lower cylinders. Vertical oil grooves are provided on both side walls of the vane groove 406 of the upper and lower cylinders; these vertical oil grooves are the aforementioned first oil groove 401. These vertical oil grooves communicate with the vertical holes (i.e., the aforementioned oil holes 502) on the partition 5. The vertical holes on the partition 5 are preferably circular, and the vertical oil grooves (i.e., the aforementioned first oil groove 401) on the upper and lower cylinders are preferably semi-circular. To prevent gas leakage from the vertical oil grooves of each cylinder 4, the closest distance d between the first oil groove 401 on the cylinder 4 and the oblique cut 405 of the cylinder 4 should not be less than 1 mm. To prevent lubricating oil leakage from the spring transverse hole 404, the first oil groove 401 on the cylinder 4 and the spring transverse hole 404 should not be interconnected.

[0065] Each cylinder 4 has an oil guide groove 402 on its side facing away from the partition plate 5, extending from the first oil groove 401 to the spring vertical hole 403. This allows the lubricating oil in the oil holes 502 on the partition plate 5 to flow back to the compressor oil sump through the first oil groove 401 on the upper cylinder, the upper end face oil guide groove 402, and the upper cylinder spring vertical hole 403, and also through the first oil groove 401 on the lower cylinder and the lower end face oil guide groove 402. Furthermore, the upper flange 2 has an end face oil groove corresponding to the first oil groove 401 on the upper cylinder; this end face oil groove is the aforementioned second oil groove 201. Thus, the first oil grooves 401 on both sides of the upper cylinder vane groove 406 can be connected through the second oil groove 201 on the upper flange 2. The lower flange 9 also has an end face oil groove corresponding to the first oil groove 401 on the lower cylinder; this end face oil groove is the aforementioned second oil groove 201. In this way, the first oil grooves 401 on both sides of the lower cylinder vane groove 406 can be connected through the second oil groove 201 on the lower flange 9. This circulating oil circuit can not only ensure the lubrication of both sides of the vane 16 under the reciprocating motion of the vane 16, but also ensure the lubrication of the upper and lower end faces of the vane 16, which greatly reduces the frictional power consumption of the vane 16, and avoids the wear problem of the vane 16 in the compressor under high-frequency oil shortage state, as well as the wear problem of the end of the vane 16 caused by the axial force of the vane 16.

[0066] The vertical oil holes on the aforementioned partition plate 5 (i.e., the aforementioned oil holes 502), the vertical oil grooves on each cylinder 4 (i.e., the aforementioned first oil groove 401), and the end face oil grooves on each flange (i.e., the aforementioned second oil groove 201) can be circular, oblong, elliptical, or a combination of shapes, with circular being the most favorable for processing.

[0067] The technical solution of the present invention can solve the following technical problems: 1. The problem of low compressor energy efficiency caused by excessive friction loss of the vane 16; 2. Solve the problem of axial force balance of the vane 16 and avoid wear caused by the up-and-down tilting of the vane 16; 3. Solve the reliability problem of severe wear on the end face of the vane 16 caused by lack of oil in the vane groove 406.

[0068] The technical solution of the present invention has the following beneficial effects: 1. The oil supply between the friction pairs of the compressor is more sufficient, the friction power consumption is reduced, and the compressor energy efficiency is improved; 2. The axial force of the vane 16 is more balanced, and the end face of the vane 16 is more lubricated, which solves the problem of wear on the end face of the vane 16; 3. The end face and side face of the vane 16 do not need to use the vane 16 coating technology, which reduces the cost of the compressor.

[0069] The above description is merely a preferred embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A pump body assembly comprising a cylinder (4) and an oil guiding structure, one side of the cylinder (4) being covered by a partition plate (5), the other side of the cylinder (4) being covered by a cylinder head (6), the cylinder (4) having a vane slot (406) for mounting a vane (16), a first oil groove (401) extending along the axial direction of the cylinder (4) being provided on the side wall of the vane slot (406), an oil hole (502) being provided on the partition plate (5), the oil hole (502) being opposite to the side of the vane (16) facing away from the cylinder head (6), and the oil hole (502) being in communication with the first oil groove (401), the oil guiding structure being configured to guide lubricating oil to the oil hole (502) so that the lubricating oil flows into the first oil groove (401) through the oil hole (502), characterized in that, a back pressure cavity is formed between the side of the vane (16) facing away from the partition plate (5) and the cylinder head (6), and the oil guiding structure is further configured to guide lubricating oil into the back pressure cavity so that the back pressure cavity provides a force for the vane (16) to relatively approach the partition plate (5). The back pressure cavity comprises a second oil groove (201) provided on the cylinder head (6) to receive lubricating oil from the oil guiding structure through the second oil groove (201), the opening of the second oil groove (201) being opposite to the side of the vane (16) facing away from the partition plate (5), and the back pressure cavity providing the force for the vane (16) to relatively approach the partition plate (5) through the lubricating oil inside the second oil groove (201). The second oil groove (201) is in communication with the first oil groove (401), and the oil guiding structure guides lubricating oil to the second oil groove (201) through the first oil groove (401).

2. The pump body assembly according to claim 1, characterized in that, one end of the first oil groove (401) penetrates the vane slot (406) along the axial direction of the cylinder (4), and the opening of the one end of the first oil groove (401) is opposite to the opening of the second oil groove (201) to make them in communication.

3. The pump body assembly according to claim 2, characterized in that, the shape of the opening of the one end of the first oil groove (401) is adapted to the shape of the opening of the second oil groove (201), and the projection profile of the opening of the one end of the first oil groove (401) on a plane perpendicular to the axial direction of the cylinder (4) is located on the projection profile of the opening of the second oil groove (201) on the plane perpendicular to the axial direction of the cylinder (4).

4. The pump body assembly according to any one of claims 1 to 3, characterized in that, the opening of the oil hole (502) is consistent with the opening of the second oil groove (201), and the projection profiles of the openings of the oil hole (502) and the second oil groove (201) on a plane perpendicular to the axial direction of the cylinder (4) are coincident.

5. The pump body assembly according to claim 4, characterized in that, the opening of the second oil groove (201) exceeds both sides of the vane (16) in the thickness direction. Further comprising an oil return structure configured to guide the lubricating oil in the first oil groove (401) and the back pressure cavity out to an oil pool.

7. The pump body assembly according to claim 6, characterized in that, ​ ​ ​ 6. The pump body assembly of any one of claims 1 to 3, 5, wherein, ​ ​ When the back pressure cavity comprises a second oil groove (201) arranged on the cylinder head (6) and the second oil groove (201) communicates with the first oil groove (401), the oil return structure comprises an oil guide groove (402) arranged on the side of the sliding vane groove (406) close to the cylinder head (6), one end of the oil guide groove (402) extends to the intersection of the first oil groove (401) and the second oil groove (201), so that the oil guide groove (402) communicates with the first oil groove (401) and the second oil groove (201), and the oil return structure guides the lubricating oil in the first oil groove (401) and the second oil groove (201) out of the oil pool through the other end of the oil guide groove (402).

8. The pump body assembly of any one of claims 1 to 3, 5, 7, wherein, The number of the cylinders (4) is two, and the partition plate (5) is located between the two cylinders (4); the number of the cylinder heads (6) is two, and the two cylinder heads (6) are arranged in one-to-one correspondence with the two cylinders (4); The number of the back pressure cavities is two, and the two back pressure cavities are arranged in one-to-one correspondence with the two cylinders (4).

9. A compressor characterized by, The pump body assembly of any one of claims 1 to 8.

10. An air conditioner characterized by comprising: The compressor of claim 9.

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