Pump structure, compressor, air conditioner

Abstract

The present invention provides a pump body structure, a compressor, and an air conditioner, wherein the pump body structure includes a crankshaft and a lower flange, wherein the lower flange is provided with an axial hole, wherein the crankshaft is inserted into the axial hole, wherein the crankshaft has an eccentric portion and a thrust ring spaced from the eccentric portion, wherein the axial hole has a counterbore on the side facing the eccentric portion, wherein the thrust ring is located in the counterbore and the first lower thrust surface of the thrust ring contacts the bottom wall of the counterbore, wherein a bearing is also mounted on the crankshaft, wherein the bearing is located between the thrust ring and the second lower thrust surface of the eccentric portion. According to the present invention, by constructing the thrust ring on the crankshaft, the axial support area of ​​the crankshaft is increased without increasing the eccentric mass of the eccentric portion, thereby improving the stability and reliability of the crankshaft operation and reducing the vibration and noise of the miniaturized compressor.

Description

Technical Field

[0001] The invention belongs to the technical field of compressor manufacturing, and in particular relates to a pump body structure, a compressor and an air conditioner. Background Art

[0002] In recent years, within major air-conditioning industries at home and abroad, the research directions of compressors for 1-1.5HP household air-conditioning systems have been increasingly focused on miniaturization and high efficiency, and the core competitiveness of air-conditioning products in the domestic and foreign markets has been improved by reducing the material cost of compressors.

[0003] The pump structure of the compressor is mainly composed of a cylinder, a rolling piston, a crankshaft, a vane, a spring, and flanges mounted on both ends of the cylinder. For the current development of small-displacement single-cylinder compressors in the direction of miniaturization and high efficiency, there are mainly two bottleneck problems. The first is the low energy efficiency caused by the miniaturization of the compressor: the extreme design of the pump body parts of small-displacement models and the reduction of the stacking height of the motor stator and rotor will correspondingly cause the compressor's effective air intake to be small, gas leakage and clearance volume to be relatively large (which has a greater impact on the low-frequency operation of the compressor), relatively high friction power consumption, and relatively low motor efficiency. The problem ultimately leads to low energy efficiency of the compressor; the second is the problem of high noise and vibration caused by the miniaturization of the compressor: after the compressor is miniaturized, its overall height and the volume of the distributor are reduced, and the corresponding motor upper cavity volume and the distributor suction buffer volume will be reduced accordingly, causing the noise and vibration level of the compressor to seriously exceed the standard.

[0004] In the prior art, in order to reduce the impact of gas leakage and clearance volume on the volumetric efficiency of the small-displacement compressor pump body, the pump body as a whole will adopt a flattened design. When the inner diameter of the cylinder increases, the eccentricity of the eccentric part will also increase accordingly, thereby reducing the circumferential leakage of the gas refrigerant from the compression chamber to the suction chamber, and improving the low-frequency refrigeration capacity of the compressor. In general, in order to reduce the friction power consumption at the eccentric bearing and reduce the radial leakage of the gas refrigerant along the roller end face, the outer diameter of the crankshaft eccentric circle will be reduced and the roller thickness will be increased. However, the area of ​​the lower thrust surface of the crankshaft will also be reduced accordingly, thereby affecting the energy efficiency, vibration noise and operating reliability of the compressor. In addition, the increase in the mass of the roller will generate a larger inertial force, causing the vibration and noise of the compressor to further deteriorate. Summary of the invention

[0005] Therefore, the present invention provides a pump body structure, a compressor, and an air conditioner to overcome the shortcomings of the prior art in that the outer diameter of the crankshaft eccentric circle is reduced in the overall flattened design of the compressor pump body, which reduces the compressor energy efficiency and reliability and worsens the vibration and noise.

[0006] In order to solve the above problems, the present invention provides a pump body structure, including a crankshaft and a lower flange, wherein the lower flange is provided with an axial hole, the crankshaft is inserted into the axial hole, the crankshaft has an eccentric portion and a thrust ring spaced apart from the eccentric portion, the axial hole has a countersunk hole on the side facing the eccentric portion, the thrust ring is located in the countersunk hole and the first lower thrust surface of the thrust ring is in contact with the bottom wall of the countersunk hole, the crankshaft is also provided with a bearing, and the bearing is located between the thrust ring and the second lower thrust surface of the eccentric portion.

[0007] Preferably, a thrust area of ​​the first lower thrust surface is Sa, a thrust area of ​​the second lower thrust surface is Sb, and 0.6≤Sa / Sb≤2.

[0008] Preferably, the axial depth of the counterbore is H, the axial height of the bearing is h1, the axial height of the thrust ring is h2, and 0≤H-(h1+h2)≤0.05mm.

[0009] Preferably, the lower flange is provided with an oil through hole extending in its radial direction, and the oil through hole can connect the counterbore with the outside of the pump body structure.

[0010] Preferably, the lower flange is also provided with an oil storage hole extending in its radial direction.

[0011] Preferably, there are multiple oil through holes, and an angle α is formed between any two adjacent oil through holes, 15°≤α≤30°; and / or, there are multiple oil storage holes, and an angle β is formed between any two adjacent oil storage holes, 15°≤β≤30°; and / or, an angle γ is formed between adjacent oil through holes and oil storage holes, 120°≤γ≤150°.

[0012] Preferably, the flow diameter of the oil through hole is d1, the flow diameter of the oil storage hole is d2, 0.8≤d2 / d1≤1.1; and / or, the oil through hole has N1, the oil storage hole has N2, 0≤N1-N2≤1.

[0013] Preferably, the wall of the counterbore has a positioning groove extending along its axial direction, and the outer peripheral wall of the bearing has a positioning boss extending along its axial direction, and the positioning boss can be accommodated in the positioning groove; and / or, the bearing includes a first ring body and a second ring body, and the first ring body and the second ring body are assembled to form the bearing.

[0014] Preferably, a vibration-damping and damping chamber is further constructed on the lower flange, and the vibration-damping and damping chamber is arranged around the outer circumference of the shaft hole.

[0015] Preferably, the volume of the vibration damping chamber is V1, the total volume of the lower flange is V2, 0.2≤V1 / V2≤0.5; and / or, an annular groove is constructed on the end face of the lower flange away from the eccentric portion, a cover plate is sealedly connected to the opening of the annular groove, and the annular groove and the cover plate together constitute the vibration damping chamber.

[0016] Preferably, the vibration damping cavity is filled with lubricating oil; and / or, the cover plate has a first sealing ring and a second sealing ring on one side facing the annular groove, and the first sealing ring and the second sealing ring are respectively located on both radial sides of the opening wall of the annular groove.

[0017] Preferably, an annular boss is provided between the first sealing ring and the second sealing ring.

[0018] Preferably, a roller is sleeved on the outer periphery of the eccentric portion, and the roller is a split structure, and / or the roller is made of a ceramic material; and / or the bearing is made of a ceramic material.

[0019] The present invention also provides a compressor, comprising the above-mentioned pump body structure.

[0020] The present invention also provides an air conditioner, comprising the above-mentioned compressor.

[0021] The present invention provides a pump body structure, a compressor, and an air conditioner. By constructing the thrust ring on the crankshaft, the axial support area of ​​the crankshaft is increased without increasing the eccentric mass of the eccentric part, thereby improving the stability and reliability of the crankshaft operation and reducing the overall vibration and noise of the miniaturized compressor. The lower flange and the bearing together constitute the support structure of the crankshaft. Compared with conventional secondary bearings, the bearing of this technical solution increases the effective support length of the crankshaft (short shaft), effectively improves the axial trajectory of the crankshaft operation, reduces the friction power consumption between the bearing and the crankshaft, and improves the overall energy efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 A schematic diagram of the internal structure of a pump body structure according to an embodiment of the present invention;

[0023] Figure 2 for Figure 1 A schematic diagram of the partial structure of the crankshaft;

[0024] Figure 3 for Figure 1 A schematic diagram of the top view structure of the bearing in FIG.

[0025] Figure 4 for Figure 1 A schematic diagram of the cross-sectional structure of the cover plate in FIG.

[0026] Figure 5for Figure 1 Schematic diagram of the cross-sectional structure of the lower flange;

[0027] Figure 6 for Figure 5 Cross-section of the middle AA;

[0028] Figure 7 This is a comparison diagram of the vibration acceleration of the compressor housing using the technical solution of the present invention and the compressor housing in the prior art;

[0029] Figure 8 The figure is a comparison chart of energy efficiency between a compressor adopting the technical solution of the present invention and a compressor in the prior art.

[0030] The reference numerals are as follows:

[0031] 1. Crankshaft; 11. Eccentric part; 111. Second lower thrust surface; 12. Thrust ring; 121. First thrust surface; 2. Lower flange; 21. Oil through hole; 22. Oil storage hole; 23. Countersunk hole; 231. Positioning groove; 24. Vibration damping chamber; 3. Bearing; 31. Positioning boss; 32. First ring body; 33. Second ring body; 4. Cover plate; 41. First sealing ring; 42. Second sealing ring; 43. Annular boss; 5. Roller; 6. Upper flange; 7. Cylinder body; 8. Sliding vane. DETAILED DESCRIPTION

[0032] See also Figures 1 to 8As shown, according to an embodiment of the present invention, a pump body structure is provided, including a crankshaft 1, a lower flange 2, an upper flange 6, a cylinder body 7, a roller 5, and a sliding plate 8. The upper flange 6 and the lower flange 2 are respectively provided with shaft holes, and the long axis and the short axis of the crankshaft 1 are respectively inserted into the shaft holes. The cylinder body 7 is located between the upper flange 6 and the lower flange 2. The cylinder body 7 is provided with a roller 5. The crankshaft 1 has an eccentric portion 11 and a thrust ring 12 spaced apart from the eccentric portion 11. The roller 5 is sleeved on the eccentric portion 11. The roller 5, the slide 8 abuts against the outer circumferential surface of the roller 5 to separate the internal space of the cylinder body 7 into an independent intake chamber and an exhaust chamber, the axial hole has a countersunk hole 23 on the side facing the eccentric part 11, the thrust ring 12 is in the countersunk hole 23 and the first lower thrust surface 121 of the thrust ring 12 is in contact with the bottom wall of the countersunk hole 23, and the crankshaft 1 is also provided with a bearing 3, and the bearing 3 is between the thrust ring 12 and the second lower thrust surface 111 of the eccentric part 11. In this technical solution, by constructing the thrust ring 12 on the crankshaft 1, the axial support area of ​​the crankshaft 1 is increased without increasing the eccentric mass of the eccentric portion 11, thereby improving the stability and reliability of the operation of the crankshaft 1 and reducing the overall vibration and noise of the miniaturized compressor. The lower flange 2 and the bearing 3 together constitute the support structure of the crankshaft 1. Compared with the conventional auxiliary bearing, the bearing 3 of this technical solution increases the effective support length of the crankshaft 1 (short shaft), effectively improves the axial trajectory of the crankshaft 1, reduces the friction power consumption between the bearing 3 and the crankshaft 1, and improves the overall energy efficiency of the compressor.

[0033] In some embodiments, the thrust area of ​​the first lower thrust surface 121 is Sa, the thrust area of ​​the second lower thrust surface 111 is Sb, and 0.6≤Sa / Sb≤2. In this technical solution, the ratio of the thrust areas of the first lower thrust surface 121 to the second lower thrust surface 111 is limited to the aforementioned range to ensure that the crankshaft 1 has sufficient support area without axial movement and can further reduce the area of ​​the second lower thrust surface 111 and further reduce the eccentric mass of the crankshaft, so that the crankshaft can run smoothly and improve its vibration and noise.

[0034] Preferably, the axial depth of the counterbore 23 is H, the axial height of the bearing 3 is h1, the axial height of the thrust ring 12 is h2, and 0≤H-(h1+h2)≤0.05mm. This ensures that the upper shaft end surface of the bearing 3 does not protrude from the counterbore 23, thereby reducing the friction between it and the eccentric portion 11.

[0035] In some embodiments, the lower flange 2 is provided with an oil hole 21 extending in the radial direction thereof, and the oil hole 21 can connect the counterbore 23 with the outside of the pump body structure, for example, the first end of the oil hole 21 can be connected with the bottom oil pool of the compressor, and the second end of the oil hole 21 is connected with the counterbore 23, so that the external lubricating oil can be guided into the counterbore 23 to effectively lubricate the bearing 23. Preferably, the lower flange 2 is also provided with an oil storage hole 22 extending in the radial direction thereof, which is used to store excessive lubricating oil, prevent excessive oil supply and increase power consumption, and maintain oil supply balance.

[0036] In some embodiments, the oil through hole 21 has a plurality of holes, and any two adjacent oil through holes 21 have an angle α, 15°≤α≤30°; and / or, the oil storage holes 22 have a plurality of holes, and any two adjacent oil storage holes 22 have an angle β, 15°≤β≤30°; and / or, adjacent oil through holes 21 and oil storage holes 22 have an angle γ, 120°≤γ≤150°; and / or, the oil through hole 21 has N1 holes, and the oil storage holes 22 have N2 holes, 0≤N1-N2≤1. In this technical solution, the oil through holes 21 and the oil storage holes 22 are distributed at a certain angle and number to ensure balanced oil supply and uniform lubrication in the circumferential direction during the rotation of the crankshaft 1.

[0037] The aperture sizes of the oil through hole 21 and the oil storage hole 22 are directly related to the oil supply and oil storage capacities, so they should be limited within a certain range (the diameter should be determined based on the specific model). In order to avoid excessive oil supply, the diameter of the oil through hole 21 should be equivalent to or smaller than the aperture size of the oil storage hole 22. Specifically, the flow diameter of the oil through hole 21 is d1, and the flow diameter of the oil storage hole 22 is d2, and 0.8≤d2 / d1≤1.1.

[0038] Preferably, the wall of the counterbore 23 has a positioning groove 231 extending along its axial direction, and the outer peripheral wall of the bearing 3 has a positioning boss 31 extending along its axial direction, and the positioning boss 31 can be accommodated in the positioning groove 231, so that the rotation of the bearing 3 in the circumferential direction is limited by the cooperation between the positioning boss 31 and the positioning groove 231; and / or, the bearing 3 includes a first ring body 32 and a second ring body 33, and the first ring body 32 and the second ring body 33 are assembled to form the bearing 3, which is beneficial to the assembly of the bearing 3 and the crankshaft 1 and reduces the restrictions on the radial direction size of the crankshaft 1 on the structural design. For example, a snap-fit ​​structure can be used to achieve a snap-fit ​​connection between the first ring body 32 and the second ring body 33.

[0039] Preferably, a vibration damping chamber 24 is also constructed on the lower flange 2. The vibration damping chamber 24 is arranged around the outer periphery of the shaft hole. On the one hand, it can reduce the weight of the parts. On the other hand, the arrangement of the chamber can prevent the vibration at the eccentric part 11 from being transmitted toward the lower side of the lower flange 2, thereby improving the vibration and noise of the whole machine. Furthermore, a plurality of weight-reducing grooves are constructed on the outer peripheral wall of the lower flange 2 to further reduce the mass of the parts. The vibration damping chamber 24 is filled with lubricating oil. By utilizing the incompressibility and damping properties of the fluid, the damping effect of the lower flange 2 on the noise and vibration propagation path is enhanced without reducing the rigidity of the lower flange 2, thereby improving the vibration and noise level of the miniaturized compressor.

[0040] Furthermore, the volume of the vibration damping chamber 24 is V1, the total volume of the lower flange 2 is V2, 0.2≤V1 / V2≤0.5, that is, the volume V1 of the vibration damping chamber 24 should be appropriate and not too large. If it is too large, the stiffness of the lower flange 2 will be greatly reduced, which is not conducive to assembly and the vibration noise of the compressor. If it is too small, the volume of the refrigeration oil contained is too small and the effect of damping and absorbing vibration and noise energy cannot be achieved.

[0041] An annular groove is formed on the end surface of the lower flange 2 away from the eccentric part 11, and a cover plate 4 is sealed and connected to the opening of the annular groove. The annular groove and the cover plate 4 together constitute the vibration damping chamber 24. Furthermore, the cover plate 4 has a first sealing ring 41 and a second sealing ring 42 on one side facing the annular groove. The first sealing ring 41 and the second sealing ring 42 are respectively located on the radial sides of the opening wall of the annular groove. Furthermore, an annular boss 43 is provided between the first sealing ring 41 and the second sealing ring 42. In this technical solution, the vibration damping chamber 24 is formed by the annular groove and the cover plate 4 together, which simplifies its construction process. The first sealing ring 41 and the second sealing ring 42 can seal the lubricating oil in the vibration damping chamber 24, and the annular boss 43 can determine the relative position of the first sealing ring 41 and the second sealing ring 42. Corresponding through holes can be constructed on the cover plate 4 to realize the detachable connection between the cover plate 4 and the lower flange 2.

[0042] In some embodiments, a roller 5 is mounted on the outer periphery of the eccentric portion 11. The roller 5 is a split structure, that is, the roller 5 is formed by two separate rollers that are assembled together, which is beneficial to the assembly of the roller 5 and the eccentric portion 11 of the crankshaft 1 and reduces the restrictions on the radial dimension of the crankshaft on the structural design.

[0043] In some embodiments, the roller 5 and the bearing 3 are made of ceramic materials with low density and surface friction coefficient (such as alumina ceramic materials) through high-temperature sintering and other processes. Generally speaking, the density of ceramic materials is only 1 / 2 of the density of conventional materials, so that the mass of the roller 5 is reduced by at least 50%, effectively reducing the inertial force generated by the eccentric part of the crankshaft with a large eccentricity when rotating, and improving the vibration and noise problems of the compressor. It can be understood that the surface friction coefficient of the roller 5 and the bearing 3 is small and the surface finish is good, which can effectively reduce the friction and wear between the eccentric part 11 of the crankshaft 1 and the inner hole of the roller 5 and the second lower thrust surface 111 and the upper shaft end face of the bearing 3, and reduce the friction power consumption between the surfaces of each moving pair. In addition, the ceramic material has a large hardness and good wear resistance, so it can improve the operating reliability of the compressor to a certain extent.

[0044] Figure 7 and Figure 8 The comparison diagrams of the shell vibration acceleration and energy efficiency of the compressor using the technical solution of the present invention and the compressor of the prior art are respectively given. It can be seen from the figure that the vibration acceleration of the compressor using the technical solution is significantly lower than the vibration acceleration of the compressor of the prior art and is reduced by an average of 5m / s 2 On the other hand, it can be seen from the figure that compared with the existing technical solution, the energy efficiency of the whole machine is improved by about 5% due to the reduction of the friction power consumption of the pump body in this technical solution.

[0045] According to an embodiment of the present invention, a compressor is also provided, including the above-mentioned pump body structure. The compressor can specifically be a rotor compressor, or a rotary fluid machinery with a similar structure, such as a rotary expander, a vane compressor, a vane expander, etc.

[0046] According to an embodiment of the present invention, there is also provided an air conditioner, comprising the above-mentioned compressor.

[0047] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0048] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the present invention. The above are only preferred embodiments of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention, and these improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A pump body structure, It is characterized in that The invention comprises a crankshaft (1) and a lower flange (2). The lower flange (2) is provided with an axial hole. The crankshaft (1) is inserted into the axial hole. The crankshaft (1) has an eccentric portion (11) and a thrust ring (12) spaced apart from the eccentric portion (11). The axial hole has a counterbore (23) on the side facing the eccentric portion (11). The thrust ring (12) is located in the counterbore (23) and a first lower thrust surface (121) of the thrust ring (12) contacts the bottom wall of the counterbore (23). The crankshaft (1) is also provided with a bearing (3). The bearing (3) is located between the thrust ring (12) and a second lower thrust surface (111) of the eccentric portion (11).

2. The pump structure according to claim 1, It is characterized in that The thrust area of ​​the first lower thrust surface (121) is Sa, the thrust area of ​​the second lower thrust surface (111) is Sb, and 0.6≤Sa / Sb≤2.

3. The pump body structure according to claim 1, It is characterized in that The axial depth of the counterbore (23) is H, the axial height of the bearing (3) is h1, the axial height of the thrust ring (12) is h2, and 0≤H-(h1+h2)≤0.05mm.

4. The pump structure according to claim 1, It is characterized in that The lower flange (2) is provided with an oil through hole (21) extending in its radial direction, and the oil through hole (21) can connect the counterbore (23) with the outside of the pump body structure.

5. The pump structure according to claim 4, It is characterized in that The lower flange (2) is also provided with an oil storage hole (22) extending in its radial direction.

6. The pump structure according to claim 5, It is characterized in that The oil through holes (21) are provided in plurality, and an angle α is formed between any two adjacent oil through holes (21), and the angle β is 15°≤α≤30° between any two adjacent oil storage holes (22) and the angle γ is 120°≤γ≤150° between adjacent oil through holes (21) and adjacent oil storage holes (22).

7. The pump structure according to claim 5, It is characterized in that The flow diameter of the oil through hole (21) is d1, the flow diameter of the oil storage hole (22) is d2, 0.8≤d2 / d1≤1.1; and / or, the oil through hole (21) has N1 holes, the oil storage hole (22) has N2 holes, 0≤N1-N2≤1.

8. The pump structure according to claim 1, It is characterized in that The counterbore (23) has a positioning groove (231) extending along its axial direction on its hole wall, and the outer peripheral wall of the bearing (3) has a positioning boss (31) extending along its axial direction, and the positioning boss (31) can be accommodated in the positioning groove (231); and / or, the bearing (3) includes a first ring body (32) and a second ring body (33), and the first ring body (32) and the second ring body (33) are assembled to form the bearing (3).

9. The pump structure according to claim 1, It is characterized in that A vibration reduction and damping chamber (24) is also constructed on the lower flange (2), and the vibration reduction and damping chamber (24) is arranged around the outer periphery of the shaft hole.

10. The pump structure according to claim 9, It is characterized in that The volume of the vibration damping chamber (24) is V1, the total volume of the lower flange (2) is V2, 0.2≤V1 / V2≤0.5; and / or, an annular groove is configured on the end surface of the lower flange (2) away from the eccentric portion (11), a cover plate (4) is sealedly connected to the opening of the annular groove, and the annular groove and the cover plate (4) together constitute the vibration damping chamber (24).

11. The pump structure according to claim 10, It is characterized in that The vibration damping cavity (24) is filled with lubricating oil; and / or the cover plate (4) has a first sealing ring (41) and a second sealing ring (42) on one side facing the annular groove, and the first sealing ring (41) and the second sealing ring (42) are respectively located on two radial sides of the opening wall of the annular groove.

12. The pump structure according to claim 11, It is characterized in that An annular boss (43) is also provided between the first sealing ring (41) and the second sealing ring (42).

13. The pump structure according to claim 1, It is characterized in that The outer periphery of the eccentric portion (11) is sleeved with a roller (5), the roller (5) is a split structure, and / or the material of the roller (5) is a ceramic material; and / or the material of the bearing (3) is a ceramic material.

14. A compressor comprising a pump body structure, It is characterized in that The pump body structure is the pump body structure according to any one of claims 1 to 13.

15. An air conditioner comprising a compressor, It is characterized in that The compressor is the compressor according to claim 14.

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