Pump body assembly, compressor and refrigeration equipment

Abstract

The utility model discloses a pump body assembly, a compressor and refrigeration equipment, and relates to the technical field of compressors, the pump body assembly comprises an air cylinder, a piston, a crankshaft and a connecting rod; the piston is arranged in the air cylinder, and a piston pin is arranged on the piston in a penetrating mode. The crankshaft is provided with a crank which is eccentrically arranged; the connecting rod is provided with a first end part and a second end part, the crank is sleeved with the first end part, the second end part is inserted into the piston, and the piston pin penetrates through the piston and the second end part; a first oil groove is formed in the outer side wall of the crank in the axial direction of the crank, and / or a second oil groove is formed in the outer side wall of the piston pin in the axial direction of the piston pin. According to the technical scheme, friction loss and energy consumption of the compressor can be reduced, and the service life of the compressor is prolonged.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and particularly relates to a pump body assembly, a compressor and a refrigeration device. Background Art

[0002] The frictional loss of a reciprocating compressor is one of the important factors affecting its mechanical efficiency. When the compressor operates, the crankshaft drives the connecting rod, and the connecting rod drives the piston to reciprocate in the cylinder. This reciprocating motion causes a large friction between the large end of the connecting rod and the crank of the crankshaft, and between the small end of the connecting rod and the piston pin, thereby increasing the frictional loss and energy consumption of the compressor. At the same time, it will also accelerate the wear and aging of the compressor, reducing the service life of the compressor. Summary of the Utility Model

[0003] The main purpose of the utility model is to provide a pump body assembly, a compressor and a refrigeration device, aiming to reduce the frictional loss and energy consumption of the compressor to extend the service life of the compressor.

[0004] To achieve the above object, a pump body assembly proposed by the utility model includes:

[0005] A cylinder;

[0006] A piston disposed in the cylinder, and a piston pin is disposed through the piston;

[0007] A crankshaft provided with an eccentric crank;

[0008] A connecting rod provided with a first end and a second end, the first end is sleeved on the crank, the second end is inserted into the piston, and the piston pin is disposed through the piston and the second end;

[0009] Wherein, a first oil groove is provided along the axial direction of the crank on the outer side wall of the crank, and / or a second oil groove is provided along the axial direction of the piston pin on the outer side wall of the piston pin.

[0010] In an embodiment, the first oil groove is located on a side of the crank close to the central axis of the crankshaft;

[0011] and / or, the second oil groove is located on a side of the piston pin away from the crank.

[0012] In an embodiment, taking the direction from the central axis of the crankshaft towards the central axis of the crank as the first initial line, the included angle between the starting end of the first oil groove and the first initial line is d_e1, the included angle between the ending end of the first oil groove and the first initial line is d_s1, and the coverage angle of the first oil groove is d_s1 - d_e1;

[0013] And / or, with the direction of the central axis of the crankshaft towards the central axis of the crank defined as the first initial line, the included angle between the starting end of the second oil groove and the first initial line is d_e2, the included angle between the terminating end of the second oil groove and the first initial line is d_s2, and the coverage angle of the second oil groove is 360° - (d_s2 - d_e2).

[0014] In one embodiment, the coverage angle of the first oil groove satisfies: 120° ≤ d_e1 ≤ 150°, 210° ≤ d_s1 ≤ 240°;

[0015] And / or, the coverage angle of the second oil groove satisfies: 30° ≤ d_e2 ≤ 60°, 300° ≤ d_s2 ≤ 330°.

[0016] In one embodiment, the first oil groove includes at least two first groove bodies distributed along the axial direction of the crank;

[0017] And / or, the second oil groove includes at least two second groove bodies distributed along the axial direction of the piston pin.

[0018] In one embodiment, the spacing w1 between two adjacent first groove bodies > 2 mm;

[0019] And / or, the spacing w2 between two adjacent second groove bodies > 2 mm.

[0020] In one embodiment, defining the outer diameter of the crank as D1 and the depth of the first oil groove as d1, then it satisfies: D1 / 400 ≤ d1 ≤ D1 / 10;

[0021] And / or, defining the outer diameter of the piston pin as D2 and the depth of the second oil groove as d2, then it satisfies: D2 / 400 ≤ d2 ≤ D2 / 10.

[0022] In one embodiment, the depth d1 of the first oil groove and / or the depth d2 of the second oil groove is 10 μm to 1000 μm.

[0023] In one embodiment, the top end of the crank protrudes from the top end of the first end portion.

[0024] To achieve the above object, the present utility model further provides a compressor, including the pump body assembly as described above.

[0025] To achieve the above object, the present utility model further provides a refrigeration device, including the compressor as described above.

[0026] The technical solution of the present utility model is provided by arranging a first oil groove on the outer side wall of the crank and / or a second oil groove on the outer side wall of the piston pin. When the first end portion of the connecting rod is sleeved on the crank of the crankshaft, lubricating oil can be introduced into the first oil groove, which can effectively reduce the friction between the first end portion of the connecting rod and the crank of the crankshaft; and when the piston pin is inserted through the second end portion of the connecting rod, lubricating oil can be introduced into the second oil groove, which can effectively reduce the friction between the second end portion of the connecting rod and the piston pin; thus, the friction loss and energy consumption during the reciprocating motion of the compressor can be effectively reduced, so as to extend the service life of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present utility model. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.

[0028] Figure 1 The front view of an embodiment of the crankshaft provided by the present utility model;

[0029] Figure 2 The top view of an embodiment of the crankshaft provided by the present utility model;

[0030] Figure 3 The front view of an embodiment of the piston pin provided by the present utility model;

[0031] Figure 4 The top view of an embodiment of the piston pin provided by the present utility model.

[0032] Explanation of the reference numerals in the drawings:

[0033] Label Name Label Name 10 Crankshaft 20 Piston pin 11 Crank 21 Second oil groove 111 First oil groove 21a Second groove body 111a First groove body a First initial line

[0034] The realization of the object, functional features and advantages of the present utility model will be further described in conjunction with the embodiments with reference to the drawings. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0035] The following will clearly and completely describe the technical solutions in the embodiments of the present utility model in conjunction with the drawings in the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, rather than all embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts fall within the scope of protection of the present utility model.

[0036] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) involved in the embodiments of the present utility model, then such directional indications are only used to explain the relative positional relationship, movement conditions, etc. between components in a certain specific posture. If this specific posture changes, then the directional indications will also change accordingly.

[0037] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present utility model, then such descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first", "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning includes three parallel scenarios. Taking "A and / or B" as an example, it includes scenario A, or scenario B, or the scenario where both A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the fact that those of ordinary skill in the art can implement it. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the protection scope required by the present utility model.

[0038] The frictional loss of a reciprocating compressor is one of the important factors affecting its mechanical efficiency. When the compressor operates, the crankshaft drives the connecting rod, and the connecting rod drives the piston to reciprocate in the cylinder. This reciprocating motion causes a large friction between the large end of the connecting rod and the crank of the crankshaft, and between the small end of the connecting rod and the piston pin, thereby increasing the frictional loss and energy consumption of the compressor. At the same time, it will also accelerate the wear and aging of the compressor, reducing the service life of the compressor.

[0039] Based on the above problems, the present utility model proposes a pump body assembly, which is applied to a compressor, aiming to reduce the frictional loss and energy consumption of the compressor to extend the service life of the compressor. The compressor includes a stator, a rotor, and a pump body assembly. The rotor is disposed inside the stator, and the rotor is connected to the crankshaft 10 (specifically, the connection can be achieved by interference fit, screws, snap fasteners, etc.). The cylinder of the pump body assembly is installed on the stator. When the compressor operates, the rotor drives the crankshaft 10 to rotate, and drives the piston to reciprocate in the cylinder through the cooperation of the crank 11 and the connecting rod, and the cooperation of the connecting rod and the piston pin 20. The piston drives the valve group to complete processes such as suction, compression, and exhaust during the reciprocating motion. The structure of the present pump body assembly will be described below by way of embodiments.

[0040] Please refer to Figures 1 to 4, in an embodiment of the present utility model, the pump body assembly includes a cylinder, a piston, a crank 11 and a connecting rod; the piston is disposed in the cylinder, and a piston pin 20 is passed through the piston; the crankshaft 10 is provided with an eccentrically disposed crank 11; the connecting rod has a first end and a second end, the first end is sleeved on the crank 11, the second end is inserted into the piston, and the piston pin 20 is passed through the piston and the second end; wherein, a first oil groove 111 is provided on the outer side wall of the crank 11 along the axial direction of the crank 11, and / or a second oil groove 21 is provided on the outer side wall of the piston pin 20 along the axial direction of the piston pin 20.

[0041] In this embodiment, the cylinder includes a body part and a cylinder part. A first mounting hole with an axis extending vertically is formed on the body part, the crankshaft 10 is passed through the first mounting hole, the cylinder part is disposed on the top of the body part and defines a second mounting hole with an axis extending horizontally, and the piston is inserted into the second mounting hole.

[0042] It should be noted that the crank 11 is eccentrically disposed with respect to the crankshaft 10, that is, the central axis of the crank 11 is parallel to the central axis of the crank 11. And, the crank 11 is disposed above the crankshaft 10, and the connecting rod is disposed above the body part.

[0043] It can be understood that the connecting rod further includes a rod body connecting the first end and the second end. The rod body has a long bar-shaped structure with a first end and a second end disposed opposite to each other. The first end is in a ring-shaped structure, the first end is connected to the first end of the rod body, and the second end is also in a ring-shaped structure, and the second end is connected to the second end of the rod body. Among them, the first end is a large end, the second end is a small end, and the inner diameter of the first end is greater than the inner diameter of the second end. In this way, it is convenient for the first end to cooperate with the larger-diameter crank 11, and it is convenient for the second end to cooperate with the smaller-diameter piston pin 20.

[0044] In actual application, the first end can be an integrally formed structure with the rod body, or can be connected to the first end of the rod body by means of bonding, screw connection, snap connection, etc. And, the second end can be an integrally formed structure with the rod body, or can be connected to the second end of the rod body by means of bonding, screw connection, snap connection, etc.

[0045] In this embodiment, in order to improve the connection reliability between the first end and the rod body, a structure with an arc-shaped connection surface can be formed at the first end of the rod body, so that the arc-shaped connection surface cooperates with the outer arc surface of the first end, which can increase the connection area between the first end and the rod body, and thus improve the connection reliability between the first end and the rod body. Similarly, in order to improve the connection reliability between the second end and the rod body, a structure with an arc-shaped connection surface can be formed at the second end of the rod body, so that the arc-shaped connection surface cooperates with the outer arc surface of the second end, which can increase the connection area between the second end and the rod body, and thus improve the connection reliability between the second end and the rod body.

[0046] In actual application, the first oil groove 111 can penetrate through the end face of the crank 11 away from the crankshaft 10, so as to facilitate the introduction of lubricating oil into the first oil groove 111. Similarly, the second oil groove 21 can penetrate through at least one end face of the piston pin 20, so as to facilitate the introduction of lubricating oil into the second oil groove 21.

[0047] In summary, the technical solution of the present utility model is provided with a first oil groove 111 on the outer side wall of the crank 11, and / or a second oil groove 21 on the outer side wall of the piston pin 20. When the first end of the connecting rod is sleeved on the crank 11 of the crankshaft 10, lubricating oil can be introduced into the first oil groove 111, which can effectively reduce the friction between the first end of the connecting rod and the crank 11 of the crankshaft 10; and when the piston pin 20 penetrates through the second end of the connecting rod, lubricating oil can be introduced into the second oil groove 21, which can effectively reduce the friction between the second end of the connecting rod and the piston pin 20; thus, the friction loss and energy consumption during the reciprocating motion of the compressor can be effectively reduced, so as to extend the service life of the compressor.

[0048] Please refer to Figure 2 In an embodiment of the present utility model, the first oil groove 111 is located on the side of the crank 11 close to the central axis of the crankshaft 10. Since the first oil groove 111 on the crank 11 can be communicated with the oil groove on the crankshaft 10, so as to introduce the lubricating oil into the first oil groove 111 of the crank 11 through the oil groove on the crankshaft 10, therefore, by making the first oil groove 111 located on the side of the crank 11 close to the central axis of the crankshaft 10, it is more convenient for the oil groove on the crankshaft 10 to introduce the lubricating oil into the first oil groove 111 of the crank 11.

[0049] Please refer to Figure 4 In an embodiment of the present utility model, the second oil groove 21 is located on the side of the piston pin 20 away from the crank 11. With such a setting, the lubricating oil can be introduced into the second oil groove 21 from the side of the piston pin 20 away from the crank 11, which is more convenient for the introduction of the lubricating oil.

[0050] Please refer to Figure 2 In an embodiment of the present utility model, the direction from the central axis of the crankshaft 10 towards the central axis of the crank 11 is defined as the first initial line a, the included angle between the starting end of the first oil groove 111 and the first initial line a is d_e1, the included angle between the terminating end of the first oil groove 111 and the first initial line a is d_s1, and the covering angle of the first oil groove 111 is d_s1 - d_e1.

[0051] With such a setting, the first oil groove 111 can be an arc-shaped groove, rather than a complete annular groove, which can ensure that the crank 11 has sufficient supporting strength for the first end of the connecting rod, so as to ensure the reliability of the crank 11 driving the connecting rod to rotate.

[0052] It should be noted that the first initial line a is the 0° line. Along the counterclockwise direction of the crankshaft 10, the angle between the starting end of the first oil groove 111 and the first initial line a is d_e1, and the angle between the terminating end of the first oil groove 111 and the first initial line a is d_s1.

[0053] Please refer to Figure 4 , and define the direction from the central axis of the crankshaft 10 towards the central axis of the crank 11 as the first initial line a. The angle between the starting end of the second oil groove 21 and the first initial line a is d_e2, the angle between the terminating end of the second oil groove 21 and the first initial line a is d_s2, and the coverage angle of the second oil groove 21 is 360°-(d_s2-d_e2).

[0054] With such a setting, the second oil groove 21 can be an arc-shaped groove instead of a complete annular groove, which can ensure that the piston pin 20 has sufficient connection strength to the second end of the connecting rod, so as to ensure the installation reliability of the piston pin 20 to the piston and the second end.

[0055] It should be noted that the first initial line a is the 0° line. Along the counterclockwise direction of the piston pin 20, the angle between the starting end of the second oil groove 21 and the first initial line a is d_e2, and the angle between the terminating end of the second oil groove 21 and the first initial line a is d_s2.

[0056] It should be noted that when the coverage angle of the first oil groove 111 is too small, the amount of lubricating oil stored in the first oil groove 111 is too small to meet the lubrication effect between the crank 11 and the first end of the connecting rod, resulting in large friction between the crank 11 and the first end of the connecting rod; while when the coverage angle of the first oil groove 111 is too large, the strength of the crank 11 will decrease, thus affecting the support reliability of the crank 11 to the first end.

[0057] Based on this, please refer to Figure 2 , in an embodiment of the present invention, the coverage angle of the first oil groove 111 satisfies: 120°≤d_e1≤150°, 210°≤d_s1≤240°.

[0058] With such a setting, by controlling the angle between the starting end of the first oil groove 111 and the initial line, and the angle between the terminating end of the first oil groove 111 and the initial line, so as to control the coverage angle of the first oil groove 111, the friction between the first end and the crank 11 can be effectively reduced, and at the same time, the support reliability of the first end to the crank 11 can be ensured.

[0059] As some examples, the angle between the starting end of the first oil groove 111 and the first initial line a can specifically be 120°, 125°, 130°, 135°, 138°, 140°, 145°, 147°, 150°, etc.; the angle between the terminating end of the first oil groove 111 and the first initial line a can specifically be 210°, 216°, 220°, 223°, 225°, 230°, 232°, 235°, 238°, 240°, etc.

[0060] Similarly, it should be noted that when the coverage angle of the second oil groove 21 is too small, the amount of lubricating oil stored in the second oil groove 21 is too small to meet the lubrication effect between the piston pin 20 and the second end of the connecting rod, resulting in large friction between the piston pin 20 and the second end of the connecting rod; when the coverage angle of the second oil groove 21 is too large, the strength of the piston pin 20 will be reduced, thus affecting the installation reliability of the piston pin 20 on the piston and the second end.

[0061] Based on this, please refer to Figure 4 , in an embodiment of the present invention, the coverage angle of the second oil groove 21 satisfies: 30° ≤ d_e2 ≤ 60°, 300° ≤ d_s2 ≤ 330°.

[0062] With such a setting, by controlling the angle between the starting end of the second oil groove 21 and the first initial line a, and the angle between the terminating end of the second oil groove 21 and the first initial line a to control the coverage angle of the second oil groove 21, the friction force between the piston pin 20 and the second end can be effectively reduced, and at the same time, the installation reliability of the piston pin 20 on the piston and the second end can be ensured.

[0063] As some examples, the angle between the starting end of the second oil groove 21 and the first initial line a can specifically be 30°, 35°, 40°, 45°, 48°, 50°, 55°, 57°, 60°, etc.; the angle between the terminating end of the second oil groove 21 and the first initial line a can specifically be 300°, 306°, 310°, 313°, 315°, 320°, 322°, 325°, 328°, 330°, etc.

[0064] Please refer to Figure 1 , in an embodiment of the present invention, the first oil groove 111 includes at least two first groove bodies 111a distributed along the axial direction of the crank 11.

[0065] With such a setting, by arranging the first oil groove 111 into at least two first groove bodies 111a, it is more convenient to machine the first oil groove 111 on the outer side wall of the crank 11.

[0066] In actual application, two adjacent first groove bodies 111a can be connected to each other or not.

[0067] Please refer to Figure 3 , in an embodiment of the present utility model, the second oil groove 21 includes at least two sections of second groove bodies 21a distributed along the axial direction of the piston pin 20.

[0068] With such a setting, by setting the second oil groove 21 as at least two sections of second groove bodies 21a, it is more convenient to machine the second oil groove 21 on the outer side wall of the piston pin 20.

[0069] In actual application, two adjacent sections of the second groove bodies 21a may be interconnected or may not be interconnected.

[0070] It should be noted that when the distance between two adjacent sections of the first groove bodies 111a is too small, it indicates that the height of the first groove bodies 111a is too high, which will result in insufficient strength of the crank 11 and also cause relatively large lubricating oil loss in the first oil groove 111.

[0071] Based on this, please refer to Figure 1 , in an embodiment of the present utility model, the distance w1 between two adjacent sections of the first groove bodies 111a > 2 mm.

[0072] With such a setting, it is possible to avoid the height of the first groove bodies 111a being too high, so as to ensure the strength of the first end portion and reduce the loss of lubricating oil.

[0073] As some examples, the distance between two adjacent sections of the first groove bodies 111a may specifically be 2 mm, 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, 3 mm, etc.

[0074] Similarly, it should be noted that when the distance between two adjacent sections of the second groove bodies 21a is too small, it indicates that the height of the second groove bodies 21a is too high, which will result in insufficient strength of the piston pin 20 and also cause relatively large lubricating oil loss in the second oil groove 21.

[0075] Please refer to Figure 3 , in an embodiment of the present utility model, the distance w2 between two adjacent sections of the second groove bodies 21a > 2 mm.

[0076] With such a setting, it is possible to avoid the height of the second groove bodies 21a being too high, so as to ensure the strength of the second end portion and reduce the loss of lubricating oil.

[0077] As some examples, the distance between two adjacent sections of the second groove bodies 21a may specifically be 2 mm, 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, 3 mm, etc.

[0078] It should be noted that when the depth of the first oil sump 111 is too shallow, the amount of lubricating oil stored in the first oil sump 111 is also too small, which cannot meet the lubrication effect between the crank 11 and the first end, resulting in large friction between the crank 11 and the first end of the connecting rod; and when the depth of the first tank body 111a is too deep, the strength of the crank 11 is insufficient, which will instead affect the lubrication effect between the crank 11 and the first end.

[0079] Based on this, please refer to Figure 2 , in an embodiment of the present utility model, the outer diameter of the crank 11 is defined as D1, and the depth of the first oil sump 111 is defined as d1, then: D1 / 400 ≤ d1 ≤ D1 / 10.

[0080] With such a setting, by reasonably designing the depth of the first tank body 111a according to the outer diameter of the crank 11, the friction force between the crank 11 and the first end can be effectively reduced, and at the same time, the strength and lubrication effect of the crank 11 can be ensured.

[0081] It should be noted that when the depth of the second tank body 21a is too shallow, the amount of lubricating oil stored in the second oil sump 21 is also too small, which cannot meet the lubrication effect between the piston pin 20 and the second end of the connecting rod, resulting in large friction between the piston pin 20 and the second end of the connecting rod; and when the depth of the second tank body 21a is too deep, the strength of the piston pin 20 is insufficient, which will instead affect the installation reliability and lubrication effect between the piston pin 20 and the second end.

[0082] Based on this, please refer to Figure 4 , in an embodiment of the present utility model, the outer diameter of the piston pin 20 is defined as D2, and the depth of the second oil sump 21 is defined as d2, then: D2 / 400 ≤ d2 ≤ D2 / 10.

[0083] With such a setting, by reasonably designing the depth of the second tank body 21a according to the outer diameter of the piston pin 20, the friction force between the piston pin 20 and the second end can be effectively reduced, and at the same time, the strength and lubrication effect of the piston pin 20 can be ensured.

[0084] Please refer to Figure 2 , Figure 4 , in an embodiment of the present utility model, the depth d1 of the first oil sump 111 and / or the depth d2 of the second oil sump 21 is 10 μm to 1000 μm; in this way, the situation that the depth of the first oil sump 111 and / or the second oil sump 21 is too shallow or too deep can be avoided, and the strength and lubrication effect of the crank 11 and the piston pin 20 can be effectively ensured.

[0085] As some examples, the depth of the first oil groove 111 and / or the depth of the second oil groove 21 can specifically be 10μm, 20μm, 30μm, 40μm, 50μm, 60μm, 70μm, 80μm, 90μm, 100μm, 150μm, 200μm, 250μm, 300μm, 350μm, 400μm, 450μm, 500μm, 550μm, 600μm, 650μm, 700μm, 800μm, 900μm, 1000mm, etc.

[0086] In practical applications, the depth of the first oil groove 111 and the depth of the second oil groove 21 can be the same or different.

[0087] Please refer to Figure 1 , in an embodiment of the present utility model, the top end of the crank 11 protrudes from the top end of the first end portion.

[0088] With such a setting, when the first end portion of the connecting rod is sleeved on the crank 11, the top end of the crank 11 will protrude from the top end of the first end portion. In this way, during the process of the crank 11 driving the connecting rod to rotate, it can be avoided that the first end portion of the connecting rod is disengaged from the crank 11; in addition, since the first oil groove 111 is provided on the crank 11, by making the top end of the crank 11 protrude from the top end of the first end portion, the contact area between the first oil groove 111 and the first end portion can also be increased to improve the lubrication effect between the crank 11 and the first end portion.

[0089] The present utility model also proposes a compressor, which includes a pump body assembly. The specific structure of the pump body assembly refers to the above embodiment. Since this compressor adopts all the technical solutions of the above all embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, and will not be elaborated here one by one.

[0090] In this embodiment, the compressor may further include a stator and a rotor. The rotor is disposed inside the stator, and the rotor is connected to the crankshaft 10 (specifically, the connection can be achieved by interference fit, screws, snap fasteners, etc.). The cylinder of the pump body assembly is installed on the stator; when the compressor operates, the rotor drives the crankshaft 10 to rotate, and drives the piston to reciprocate in the cylinder through the cooperation of the crank 11 and the connecting rod, and the cooperation of the connecting rod and the piston pin 20. During the reciprocating movement of the piston, the valve group is driven to complete processes such as suction, compression, and exhaust.

[0091] As an example, this compressor can be a reciprocating compressor.

[0092] In one embodiment, the compressor provided by the present solution can reduce the frictional losses related to the crank 11. The coverage angles of the first oil groove 111 and the second oil groove 21 corresponding to the crank 11 and the piston pin 20 respectively are shown in Table 1 below. The simulation results of the frictional losses of the crank 11 and the piston pin 20 are shown in Table 2 below:

[0093] Table 1 Coverage Angles of the First Oil Groove and the Second Oil Groove Corresponding to the Crank and the Piston Pin Respectively

[0094]

[0095] Table 2 Simulation Calculation Results of Crank Frictional Losses

[0096]

[0097] In summary, according to the simulation results in Table 2, when the film thickness is comparable, the frictional loss of the crank 11 provided with the first oil groove 111 is reduced by up to 0.03 W compared to the crank 11 without the first oil groove 111; when the film thickness is comparable, the frictional loss of the piston pin 20 provided with the second oil groove 21 is reduced by up to 0.182 W compared to the piston pin 20 without the second oil groove 21, which reflects the effect of the first oil groove 111 on reducing the frictional loss of the connecting rod crank 11 and the second oil groove 21 on the piston pin 20.

[0098] The present utility model also proposes a refrigeration device, which includes a compressor. The specific structure of the compressor refers to the above embodiment. Since this refrigeration device adopts all the technical solutions of the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated here one by one.

[0099] Exemplarily, the refrigeration device can be a refrigerator.

[0100] The above description is only an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformation made under the technical concept of the present utility model by using the content of the specification and drawings of the present utility model, or any direct / indirect application in other related technical fields is included in the patent protection scope of the present utility model.

Claims

1. A pump assembly, characterized in that: include: cylinder; A piston is disposed in the cylinder and a piston pin is provided on the piston; A crankshaft having an eccentrically arranged crank; A connecting rod, comprising a first end and a second end, wherein the first end is sleeved on the crank, the second end is inserted into the piston, and the piston pin penetrates the piston and the second end; Wherein, the outer side wall of the crank is provided with a first oil groove along the axial direction of the crank, and / or the outer side wall of the piston pin is provided with a second oil groove along the axial direction of the piston pin.

2. The pump assembly according to claim 1, characterized in that: The first oil groove is located on a side of the crank close to the center axis of the crankshaft; And / or, the second oil groove is located on a side of the piston pin away from the crank.

3. The pump assembly according to claim 1, characterized in that: The direction from the center axis of the crankshaft toward the center axis of the crank is defined as a first initial line, the angle between the starting end of the first oil groove and the first initial line is d_e1, the angle between the ending end of the first oil groove and the first initial line is d_s1, and the coverage angle of the first oil groove is d_s1-d_e1; And / or, the direction from the center axis of the crankshaft toward the center axis of the crank is defined as the first initial line, the angle between the starting end of the second oil groove and the first initial line is d_e2, the angle between the ending end of the second oil groove and the first initial line is d_s2, and the coverage angle of the second oil groove is 360°-(d_s2-d_e2).

4. The pump assembly according to claim 3, characterized in that: The coverage angle of the first oil groove satisfies: 120°≤d_e1≤150°, 210°≤d_s1≤240°; And / or, the coverage angle of the second oil groove satisfies: 30°≤d_e2≤60°, 300°≤d_s2≤330°.

5. The pump assembly according to any one of claims 1 to 4, characterized in that: The first oil groove comprises at least two first groove bodies distributed along the axial direction of the crank; And / or, the second oil groove includes at least two sections of second groove bodies distributed along the axial direction of the piston pin.

6. The pump assembly according to claim 5, characterized in that: The distance w1 between two adjacent sections of the first slot body is greater than 2 mm; And / or, the distance w2 between two adjacent sections of the second groove body is greater than 2 mm.

7. The pump assembly according to any one of claims 1 to 4, characterized in that: The outer diameter of the crank is defined as D1, and the depth of the first oil groove is defined as d1, then: D1 / 400≤d1≤D1 / 10; And / or, the outer diameter of the piston pin is defined as D2, and the depth of the second oil groove is defined as d2, then: D2 / 400≤d2≤D2 / 10 is satisfied.

8. The pump assembly according to claim 7, characterized in that: The depth d1 of the first oil groove and / or the depth d2 of the second oil groove is 10 μm to 1000 μm.

9. The pump assembly according to any one of claims 1 to 4, characterized in that: The top end of the crank protrudes from the top end of the first end.

10. A compressor, characterized in that: The invention comprises a pump body assembly as claimed in any one of claims 1 to 9.

11. A refrigeration device, characterized in that: Comprising the compressor of claim 10.

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