Main bearing-crankshaft structure, pump body assembly, compressor and air conditioner

Abstract

The utility model belongs to the technical field of rotor type compressors, and discloses a main bearing-crankshaft structure, a pump body assembly, a compressor and an air conditioner, the main bearing-crankshaft structure comprises a crankshaft and a main bearing, a long shaft part of the crankshaft is sleeved in a main bearing inner hole of the main bearing in a matched and penetrating manner; the main bearing inner hole comprises a straight hole section and a micro taper hole section which are axially communicated, and the micro taper hole section is arranged far away from one side of the main bearing large end face of the main bearing; the diameter of an inlet of the micro taper hole section is the same as that of the straight hole section, and the diameter of an outlet of the micro taper hole section is larger than that of the inlet of the micro taper hole section; according to the utility model, a deformation avoiding space is formed between the long shaft part and the matched outer circle of the upper end part of the inner hole of the main bearing so as to accommodate the bending deformation of the long shaft part; and secondly, the oil film strength between the upper end part of the inner hole of the main bearing and the long shaft part is increased, the abrasion between the long shaft part and the upper end part of the inner hole of the main bearing is effectively reduced, and the operation reliability of the compressor pump body assembly is greatly improved.

Description

Technical Field

[0001] The utility model belongs to the technical field of rotary compressors, and particularly relates to a main bearing - crankshaft structure, a pump body assembly, a compressor and an air conditioner. Background Art

[0002] With the development of compressor technology, the requirement for the high efficiency of compressors is constantly increasing; among them, to improve the high - efficiency operation of compressors, the shaft diameter of the crankshaft is required to be smaller and smaller; after the shaft diameter of the crankshaft becomes smaller, the rigidity of the crankshaft becomes poor, and its ability to resist deformation decreases. During the operation of the compressor, when the motor drives the crankshaft to rotate eccentrically, the crankshaft is usually affected by the combined action of eccentric inertial force, motor magnetic pull force and gas force; especially when the compressor starts or the motor speed increases, due to the reduced ability of the crankshaft to resist deformation, the long shaft part of the crankshaft is prone to bending deformation under the action of the motor magnetic pull force, resulting in insufficient oil film thickness between it and the upper end part of the inner hole of the main bearing, which easily leads to metal - to - metal contact friction between the crankshaft and the main bearing, increasing the wear of the long shaft part and the upper end part of the inner hole of the main bearing. In severe cases, the friction temperature at this part can rise sharply, causing material adhesion, and further leading to the risk of failure of the compressor pump body assembly. Summary of the Utility Model

[0003] Aiming at the technical problems existing in the prior art, the utility model provides a main bearing - crankshaft structure, a pump body assembly, a compressor and an air conditioner to solve the technical problems that the long shaft part of the crankshaft is prone to bending deformation under the action of the motor magnetic pull force, resulting in insufficient oil film thickness between it and the upper end part of the inner hole of the main bearing, which easily leads to metal - to - metal contact friction between the crankshaft and the main bearing and increases the wear of the long shaft part and the upper end part of the inner hole of the main bearing.

[0004] To achieve the above - mentioned purpose, the technical solution adopted by the utility model is as follows:

[0005] The utility model provides a main bearing - crankshaft structure, including a crankshaft and a main bearing, and the long shaft part of the crankshaft is fitted and sleeved in the main bearing inner hole of the main bearing;

[0006] The main bearing inner hole includes an axially - connected straight hole section and a micro - tapered hole section, and the micro - tapered hole section is arranged on the side away from the main bearing large end face of the main bearing; wherein, the main bearing large end face is the end face of the main bearing facing the compressor cylinder;

[0007] The inlet diameter of the micro - tapered hole section is the same as the diameter of the straight hole section, and the outlet diameter of the micro - tapered hole section is larger than the inlet diameter of the micro - tapered hole section.

[0008] Furthermore, the relationship between the axial length of the straight hole section and the axial length of the micro - tapered hole section satisfies:

[0009] 3.5n2≥n1≥2.5n2

[0010] Among them, n1 is the axial length of the straight hole section; n2 is the axial length of the micro-cone hole section.

[0011] Furthermore, the relationship between the axial length of the micro-cone hole section and the axial height of the main bearing satisfies:

[0012] n2≥0.2n

[0013] Among them, n2 is the axial length of the micro-cone hole section; n is the axial height of the main bearing.

[0014] Furthermore, the relationship between the outlet diameter and the inlet diameter of the micro-cone hole section satisfies:

[0015] d2≥d1+0.01mm

[0016] Among them, d1 is the inlet diameter of the micro-cone hole section; d2 is the outlet diameter of the micro-cone hole section.

[0017] Furthermore, a central oil hole is provided at the axial center of the crankshaft, and an upper radial oil hole is provided at the long shaft portion of the crankshaft; among them, the diameter of the upper radial oil hole satisfies:

[0018] Ψ≥m-n≥0

[0019] Among them, Ψ is the diameter of the upper radial oil hole; m is the distance between the upper thrust surface of the crankshaft and the center line of the upper radial oil hole; n is the axial height of the main bearing.

[0020] Furthermore, the central oil hole includes an installation section and a lift section that are axially connected; among them, the inlet end of the installation section penetrates through the end surface of the short shaft portion of the crankshaft, and the lift section is a blind hole structure;

[0021] The upper radial oil hole is arranged close to the blind end bottom surface of the lift section; among them, the blind end bottom surface of the lift section is a conical surface structure, and the distance between the blind end bottom surface of the lift section and the center of the upper radial oil hole satisfies:

[0022] 1.5Ψ≥L≥0.5Ψ

[0023] Among them, Ψ is the diameter of the upper radial oil hole; L is the distance between the blind end bottom surface of the lift section and the center of the upper radial oil hole.

[0024] Furthermore, an oil suction piece is installed in the installation section; the oil suction piece is in interference fit with the installation section; a spiral oil groove is provided on the inner wall of the inner hole of the main bearing.

[0025] The present utility model also provides a compressor pump body assembly, including the main bearing-crankshaft structure described above.

[0026] The utility model also provides a compressor, comprising the main bearing-crankshaft structure or the compressor pump body assembly.

[0027] The utility model also provides an air conditioner, comprising the compressor.

[0028] Compared with the prior art, the beneficial effects of the utility model are:

[0029] The utility model provides a main bearing-crankshaft structure, by arranging a micro-conical hole section in the inner hole of the main bearing, and designing the outlet diameter of the micro-conical hole section to be larger than the inlet diameter, a deformation avoidance space is formed between the matching outer circles of the long axis portion and the upper end portion of the inner hole of the main bearing to accommodate the bending deformation of the long axis portion; secondly, by arranging the micro-conical hole section, the oil storage space between the long axis portion and the upper end portion of the inner hole of the main bearing is increased, so that more refrigeration oil is stored between the long axis portion and the upper end portion of the inner hole of the main bearing, thereby increasing the oil film strength between the upper end portion of the inner hole of the main bearing and the long axis portion, avoiding metal contact friction between the long axis portion and the upper end portion of the inner hole of the main bearing during the operation of the compressor, especially during the secondary start or when the motor speed increases, thereby effectively reducing the wear of the long axis portion and the upper end portion of the inner hole of the main bearing, and greatly improving the reliability of the operation of the compressor pump body assembly.

[0030] Furthermore, the relationship between the axial length n1 of the straight hole section and the axial length n2 of the micro-tapered hole section is designed according to 3.5n2≥n1≥2.5n2, or the relationship between the axial length n2 of the micro-tapered hole section and the axial height n of the main bearing is designed according to n2≥0.2n, so as to achieve the reliable support length of the crankshaft and avoidance of the maximum bending deformation space under the extreme operating pressure of the compressor.

[0031] Furthermore, the center oil hole is designed as a blind hole structure, which can ensure that the refrigeration oil in the oil pool at the bottom of the compressor passes through the center oil hole and enters the inner hole of the main bearing through the upper radial oil hole, thereby ensuring a continuous supply of refrigeration oil between the main bearing and the long shaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0033] Figure 1 It is a schematic diagram of the overall structure of the main bearing-crankshaft structure described in Example 1;

[0034] Figure 2Schematic structural diagram of the crankshaft in Embodiment 1;

[0035] Figure 3 Partial sectional view of the crankshaft in Embodiment 1;

[0036] Figure 4 Schematic structural diagram of the main bearing in Embodiment 1;

[0037] Figure 5 Sectional view of the main bearing in Embodiment 1;

[0038] Figure 6 Schematic structural diagram of the compressor pump body assembly in Embodiment 2;

[0039] Figure 7 Schematic structural diagram of the compressor in Embodiment 3.

[0040] Among them, 100 is the pump body assembly, 200 is the motor assembly, 300 is the housing, 400 is the liquid reservoir, 500 is the bottom oil sump; 1 is the crankshaft, 2 is the main bearing, 3 is the auxiliary bearing, 4 is the core rotor, 5 is the cylinder; 11 is the long shaft part, 12 is the short shaft part, 13 is the eccentric part, 14 is the central oil hole, 15 is the lower radial oil hole, 16 is the upper radial oil hole, 17 is the top thrust surface of the crankshaft; 141 is the installation section, 142 is the lift section; 21 is the inner hole of the main bearing, 22 is the spiral oil groove, 23 is the large end face of the main bearing; 211 is the straight hole section, 212 is the micro-conical hole section. Specific embodiments

[0041] In order to make the technical problems, technical solutions and beneficial effects solved by the present application clearer and more understandable, the technical solutions in the embodiments of the present application will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present application; obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative work belong to the scope of protection of the present application.

[0042] Embodiment 1

[0043] As shown in the attached Figure 1-4 figure, Embodiment 1 of the present application provides a main bearing-crankshaft structure, including a crankshaft 1 and a main bearing 2; the crankshaft 1 includes a long shaft part 11, an eccentric part 13 and a short shaft part 12 connected in sequence along the axis; the main bearing 2 has an end face facing the compressor cylinder, denoted as the large end face 23 of the main bearing; the main bearing 2 has an end face facing the compressor motor assembly, denoted as the small end face of the main bearing; a main bearing inner hole 21 is provided at the center of the main bearing 2, and the long shaft part 11 of the crankshaft 1 is fitted and sleeved in the main bearing inner hole 21.

[0044] A central oil hole 14 is provided at the axial center of the crankshaft 1. The central oil hole 14 includes an installation section 141 and a lift section 142 that are axially connected. Among them, the inlet section of the installation section 141 communicates with the end face of the short shaft portion 12, and the outlet section of the installation section 141 communicates with the inlet section of the lift section 142. An oil suction sheet is installed in the installation section 141, and the oil suction sheet is in interference fit with the installation section 141 to fix the oil suction sheet. The lift section 142 is a blind hole structure, and the blind end of the lift section 142 is located in the long shaft portion 11.

[0045] Lower radial oil holes 15 and upper radial oil holes 16 are provided on the surface of the long shaft portion 11. The lower radial oil holes 15 are arranged close to the eccentric shaft 13 and penetrate through the long shaft portion 11 in the radial direction. Among them, one end of the lower radial oil hole 15 communicates with the inner wall of the installation section 141, and the other end of the lower radial oil hole 15 communicates with the surface of the long shaft portion 11.

[0046] The upper radial oil holes 16 are arranged close to the bottom surface of the blind end of the lift section 142 and penetrate through the long shaft portion 11 in the radial direction. Among them, one end of the upper radial oil hole 16 communicates with the inner wall of the blind end of the lift section 142, and the other end of the upper radial oil hole 16 communicates with the surface of the long shaft portion 11. Specifically, the diameter Ψ of the upper radial oil hole 16 satisfies: Ψ≥m - n≥0; where Ψ is the diameter of the upper radial oil hole 16, m is the distance between the top thrust surface 17 of the crankshaft and the center line of the upper radial oil hole 16, and n is the axial height of the main bearing 2.

[0047] The bottom surface of the blind end of the lift section 142 is a conical bottom surface structure with a central angle of 150°. Among them, the distance L between the bottom surface of the blind end of the lift section 142 and the center line of the upper radial oil hole 16 satisfies: 1.5Ψ≥L≥0.5Ψ; where Ψ is the diameter of the upper radial oil hole.

[0048] The inner hole 21 of the main bearing includes a straight hole section 211 and a micro - conical hole end 212 that are axially connected, that is, the inner hole 21 of the main bearing is divided into a straight hole section 211 and a micro - conical hole section 212 along the axial direction from the large end face 23 of the main bearing to the small end face of the main bearing. Among them, the straight hole section 211 is arranged on the side close to the large end face 23 of the main bearing, and the micro - conical hole end 212 is arranged on the side close to the small end face of the main bearing, that is, the micro - conical hole section 212 is arranged on the side far from the large end face 23 of the main bearing.

[0049] The inlet diameter of the straight hole section 211 is the same as the outlet diameter of the straight hole section 211. The inlet diameter of the micro-cone hole end 212 is the same as the outlet diameter of the straight hole section 211. The outlet diameter of the micro-cone hole section 212 is larger than the inlet diameter of the micro-cone hole section 212. Among them, the transition from the inlet to the outlet of the micro-cone hole section 212 is smooth. Preferably, the relationship between the outlet diameter d2 and the inlet diameter d1 of the micro-cone hole section 212 satisfies: d2 ≥ d1 + 0.01 mm. Wherein, d1 is the inlet diameter of the micro-cone hole section; d2 is the outlet diameter of the micro-cone hole section.

[0050] Between the axial length n1 of the straight hole section 211 and the axial length n2 of the micro-cone hole section 212, it satisfies: 3.5n2 ≥ n1 ≥ 2.5n2. Wherein, n1 is the axial length of the straight hole section; n2 is the axial length of the micro-cone hole section. The relationship between the axial length n2 of the micro-cone hole section 212 and the axial height n of the main bearing 2 satisfies: n2 ≥ 0.2n. Wherein, n2 is the axial length of the micro-cone hole section; n is the axial height of the main bearing.

[0051] A spiral oil groove 22 is provided on the inner wall of the inner hole 21 of the main bearing. The starting end of the spiral oil groove 22 starts from the large end face 23 of the main bearing and spirally arranges upward along the inner wall of the inner hole 21 of the main bearing until it terminates at the small end face of the main bearing.

[0052] Oil supply principle:

[0053] In this Embodiment 1, by providing a central oil hole 14 at the axial center of the crankshaft 1, the central oil hole 14 is formed by a combination of an axially connected installation section 141 and a lift section 142. The oil suction piece is press-fitted into the installation section 141, and the lift section 142 is set as a blind hole structure. When the compressor operates, the oil suction piece in the installation section 141 can suck the refrigeration oil in the bottom oil sump of the compressor into the central oil hole 14. The refrigeration oil continuously flows upward in the central oil hole 14. When the oil level reaches the lower radial oil hole 15 provided on the long shaft portion 11, a part of the refrigeration oil flows out along the lower radial oil hole 15 and flows into the spiral oil groove 22, and the remaining part of the refrigeration oil continues to flow upward and flows out through the upper radial oil hole 16 provided on the long shaft portion 11 and flows into the micro-cone hole section 212. Among them, setting the lift section 142 as a blind hole structure can increase the oil pressure of the refrigeration oil in the central oil hole 14, ensure that the refrigeration oil in the bottom oil sump of the compressor enters the inner hole of the main bearing through the central oil hole and the upper radial oil hole, and thus ensure the continuous supply of refrigeration oil between the main bearing and the long shaft portion.

[0054] Secondly, by providing a micro-tapered hole section 212 in the main bearing inner hole 21, and designing the outlet diameter of the micro-tapered hole section 212 to be larger than the inlet diameter, on the one hand, a deformation avoidance space can be formed between the matching outer circles of the long axis portion 11 and the upper end of the main bearing inner hole 21 to accommodate the bending deformation of the long axis portion; on the other hand, compared with the straight hole section 211, the micro-tapered hole section 212 can store more refrigeration oil, increase the oil film strength between the upper end of the main bearing inner hole 21 and the long axis portion 11, effectively solve the problem of insufficient oil film thickness between the long axis portion 11 and the main bearing inner hole 21, avoid metal contact friction between the long axis portion 11 and the upper end of the main bearing inner hole 21 during the operation of the compressor, especially during the secondary start or when the motor speed increases, thereby effectively reducing the wear of the long axis portion 11 and the upper end of the main bearing inner hole 21, and greatly improving the reliability of the operation of the compressor pump body assembly.

[0055] Example 2

[0056] As attached Figure 5 As shown, this embodiment 2 provides a compressor pump body assembly, including a crankshaft 1, a main bearing 2, a secondary bearing 3, a movement rotor 4 and a cylinder 5.

[0057] The main bearing 1 is sealed on the upper end surface of the cylinder 5, and the secondary bearing 3 is sealed on the lower end surface of the cylinder 5; the crankshaft 1 is concentrically assembled in the working chamber of the cylinder 5; wherein the long axis portion of the crankshaft 1 is inserted into the main bearing inner hole of the main bearing 2, and the short axis portion of the crankshaft 1 is inserted into the secondary bearing inner hole of the secondary bearing 3; the movement rotor 4 is arranged in the working chamber of the cylinder 5, and is sleeved on the outside of the eccentric portion of the crankshaft 1.

[0058] It should be noted that the crankshaft 1 adopts the crankshaft in the main bearing-crankshaft structure described in the above embodiment 1, and the main bearing 2 adopts the main bearing in the main bearing-crankshaft structure described in the above embodiment 1; the specific structures of the crankshaft 1 and the main bearing 2 are detailed in the description of the above embodiment 1 and will not be repeated here.

[0059] Example 3

[0060] As attached Figure 6 As shown, this embodiment 3 provides a compressor, including a pump body assembly 100, a motor assembly 200, a shell 300 and a liquid reservoir 400; the pump body assembly 100 and the motor assembly 200 are assembled inside the shell 300, and the liquid reservoir 400 is fixed on the outside of the shell 300; wherein, the pump body assembly 100 adopts the compressor pump body assembly described in the above embodiment 2, or the pump body assembly 100 includes the main bearing-crankshaft structure described in the above embodiment 1; wherein, a bottom oil pool 500 is provided at the bottom of the shell 300.

[0061] Under the condition of the maximum heating operating mode and running at a frequency of 110 Hz, the performance test of the compressor described in Embodiment 3 of the present invention was carried out. The test results showed that: compared with the existing ordinary rotary compressor, the cooling capacity per unit of the compressor described in Embodiment 3 of the present invention increased by 0.5%, the power consumption decreased by 1%, the exhaust temperature decreased by 2 °C, and the energy efficiency level increased by 1.5%; thus, it can be seen that the high-frequency performance of the compressor described in Embodiment 3 of the present invention has been significantly improved.

[0062] Embodiment 4

[0063] Embodiment 4 of the present invention provides an air conditioner, including the compressor described in Embodiment 3 above; by arranging the compressor described in Embodiment 3 above in the air conditioner, the refrigeration effect and energy efficiency level of the air conditioner are effectively improved.

[0064] In the main bearing - crankshaft structure, pump body assembly, compressor and air conditioner of the present invention, in order to solve the problem of insufficient oil film thickness between the long shaft part of the crankshaft and the inner hole of the main bearing, the central oil hole of the crankshaft is set as a blind hole to increase the oil pressure, and it communicates with the lower radial oil hole and the upper radial oil hole on the surface of the long shaft; when the compressor operates, the suction oil sheet sucks the refrigeration oil in the bottom oil sump into the central oil hole, and the refrigeration oil continuously flows upward in the central oil hole; when the oil level reaches the lower radial oil hole, a part of the refrigeration oil in the central oil hole flows out along the lower radial oil hole and enters the spiral oil groove in the inner hole of the main bearing, and the remaining part continues to flow upward and flows out through the upper radial oil hole and into the micro - taper hole section.

[0065] In the present invention, the upper end part of the inner hole of the main bearing is set as a micro - taper hole section. The micro - taper hole section with a micro - taper structure can, on the one hand, provide a certain space for avoidance when the long shaft of the crankshaft bends and deforms, and on the other hand, compared with the straight hole section, it can store more refrigeration oil and increase the oil film strength between the upper end part of the inner hole of the main bearing and the long shaft part; especially during the operation of the compressor, especially during the second start or when the motor speed increases, it can effectively reduce the wear between the long shaft of the crankshaft and the upper end part of the inner hole of the main bearing and improve the reliability of the operation of the pump body assembly.

[0066] The above - mentioned embodiments are only one of the implementation manners that can realize the technical solution of the present invention. The scope of protection required by the present invention is not only limited by these embodiments, but also includes any changes, substitutions and other implementation manners that are easily conceivable by any person skilled in the art within the technical scope disclosed by the present invention.

Claims

1. A main bearing - crankshaft structure, characterized in that, It includes a crankshaft (1) and a main bearing (2), and the long shaft portion (11) of the crankshaft (1) is fitted and sleeved in the main bearing inner hole (21) of the main bearing (2). The main bearing inner hole (21) includes an axially connected straight hole section (211) and a micro-conical hole section (212), and the micro-conical hole section (212) is arranged on the side away from the main bearing large end face (23) of the main bearing (2); wherein, the main bearing large end face (23) is the end face of the main bearing (2) facing the compressor cylinder. The inlet diameter of the micro-conical hole section (212) is the same as the diameter of the straight hole section (211), and the outlet diameter of the micro-conical hole section (212) is larger than the inlet diameter of the micro-conical hole section (212).

2. The main bearing - crankshaft structure according to claim 1, characterized in that, The relationship between the axial length of the straight hole section (211) and the axial length of the micro-conical hole section (212) satisfies:[[]] 3.5n2≥n1≥2.5n2 Wherein, n1 is the axial length of the straight hole section; n2 is the axial length of the micro-conical hole section.

3. The main bearing - crankshaft structure according to claim 1, characterized in that, The relationship between the axial length of the micro-conical hole section (212) and the axial height of the main bearing (2) satisfies:[[]] n2≥0.2n Wherein, n2 is the axial length of the micro-conical hole section; n is the axial height of the main bearing.

4. A main bearing - crankshaft structure according to claim 1, wherein, The relationship between the outlet diameter and the inlet diameter of the micro-conical hole section (212) satisfies:[[]] d2≥d1+0.01mm Wherein, d1 is the inlet diameter of the micro-conical hole section; d2 is the outlet diameter of the micro-conical hole section.

5. A main bearing - crankshaft structure according to claim 1, characterized in that, A central oil hole (14) is arranged at the axial center of the crankshaft (1), and an upper radial oil hole (16) is arranged on the long shaft portion (11) of the crankshaft (1); Among them, the diameter of the upper radial oil hole (16) satisfies:[[]] Ψ≥m-n≥0 Wherein, Ψ is the diameter of the upper radial oil hole; m is the distance between the upper thrust surface of the crankshaft and the center line of the upper radial oil hole; n is the axial height of the main bearing.

6. The main bearing - crankshaft structure according to claim 5, characterized in that, The central oil hole (14) includes an axially connected installation section (141) and a lift section (142); wherein, the inlet end of the installation section (141) is communicated with the end face of the short shaft portion (12) of the crankshaft (1), and the lift section (142) is a blind hole structure; The upper radial oil hole (16) is arranged close to the blind end bottom surface of the lift section (142); wherein, the blind end bottom surface of the lift section (142) is a conical surface structure, and the distance between the blind end bottom surface of the lift section (142) and the center of the upper radial oil hole (16) satisfies:[[]] 1.5Ψ≥L≥0.5Ψ Wherein, Ψ is the diameter of the upper radial oil hole; L is the distance between the blind end bottom surface of the lift section and the center of the upper radial oil hole.

7. A main bearing - crankshaft structure according to claim 6, characterized in that An oil suction piece is installed in the installation section (141); the oil suction piece is in interference fit with the installation section (141); a spiral oil groove (22) is arranged on the hole wall of the main bearing inner hole (21).

8. A pump body assembly, characterized in that, It includes the main bearing-crankshaft structure according to any one of claims 1-7.

9. A compressor, characterized in that, It includes the main bearing-crankshaft structure according to any one of claims 1-7, or includes the pump body assembly according to claim 8.

10. An air conditioner, characterized in that, It includes the compressor according to claim 9.

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