CN117469129A

CN117469129A - Reciprocating compressor and refrigerating equipment

Info

Publication number: CN117469129A
Application number: CN202310510260.2A
Authority: CN
Inventors: 邓敦勇; 蔡顺; 殷田甜; 张巍; 陈新杰; 黄刚
Original assignee: Anhui Meizhi Compressor Co Ltd
Current assignee: Anhui Meizhi Compressor Co Ltd
Priority date: 2023-05-08
Filing date: 2023-05-08
Publication date: 2024-01-30

Abstract

The invention discloses a reciprocating compressor and refrigeration equipment, wherein the reciprocating compressor comprises a crank case, a crank shaft, a rotor assembly, a piston, a connecting rod and a piston pin, the crank case comprises a crank shaft seat and a cylinder seat, the crank shaft penetrates through the crank shaft seat, and a first friction pair which is contacted with each other is arranged between the crank shaft and the crank shaft seat; the rotor assembly is connected with the crankshaft, and a second friction pair which is contacted with each other is arranged between the rotor assembly and the crankshaft seat; the piston is movably arranged in the cylinder seat; one end of the connecting rod is connected with the crankshaft, the other end of the connecting rod is connected with the piston, and a third friction pair which is contacted with each other is arranged between the connecting rod and the piston; the piston pin penetrates through the piston, and a fourth friction pair which is contacted with each other is arranged between the piston pin and the connecting rod; at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair is provided with a lubricating structure. The technical scheme of the invention can effectively reduce the abrasion of the friction pair, and improve the performance and the service life of the reciprocating compressor.

Description

Reciprocating compressor and refrigerating equipment

Technical Field

The invention relates to the technical field of reciprocating compressors, in particular to a reciprocating compressor and refrigeration equipment.

Background

Key components of reciprocating compressors include the crankcase, cylinders, pistons, connecting rods, crankshafts, and the like. Since these components require high-speed friction during operation, lubrication is required to reduce friction loss and wear. Friction pairs between key parts of the reciprocating compressor, if insufficient lubrication, may cause an increase in friction between the friction pairs, thereby increasing friction loss and energy consumption of the machine, and also accelerating wear and aging of the machine, reducing the service life of the machine. In addition, insufficient lubrication of the friction pair can also lead to increased noise and vibration of the machine, affecting the stability and reliability of the machine, and possibly even causing machine failure and accidents. Therefore, insufficient lubrication of the friction pair of the reciprocating compressor is an important problem to be solved.

Disclosure of Invention

The invention aims to provide a reciprocating compressor, which aims to effectively reduce abrasion of a friction pair and improve the lubricating performance of the friction pair by arranging a lubricating structure on the friction pair of a key component, thereby reducing noise and vibration of the reciprocating compressor and improving the performance and service life of the reciprocating compressor.

To achieve the above object, the present invention provides a reciprocating compressor comprising:

A crankcase including a crankshaft seat and a cylinder seat;

the crankshaft penetrates through the crankshaft seat, and a first friction pair which is in contact with each other is arranged between the crankshaft and the crankshaft seat;

a rotor assembly connected to the crankshaft, the rotor assembly and the crankshaft seat having a second friction pair in contact with each other;

the piston is movably arranged in the cylinder seat;

one end of the connecting rod is connected with the crankshaft, the other end of the connecting rod is connected with the piston, and a third friction pair which is in contact with each other is arranged between the connecting rod and the piston; and

the piston pin penetrates through the piston, and a fourth friction pair which is in contact with each other is arranged between the piston pin and the connecting rod; and at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair is provided with a lubricating structure.

Optionally, the first friction pair is provided with the lubricating structure, the lubricating structure is configured as a self-lubricating gasket, the crankshaft seat is provided with a crankshaft hole, the crankshaft is provided with a shaft shoulder, the shaft shoulder is provided with a crankshaft thrust surface, the crankshaft penetrates through the crankshaft hole, and the self-lubricating gasket is arranged at the edge of the crankshaft hole and is in butt joint with the crankshaft thrust surface.

Optionally, the crankcase is equipped with the installation step in the border of bent axle hole, self-lubricating gasket cover is located the installation step, and at least part outstanding the installation step.

Optionally, the shaft shoulder is provided with a protrusion, the crankshaft thrust surface is formed on the surface of the protrusion facing the installation step, the installation step comprises a first annular step and a second annular step, and the self-lubricating gasket is sleeved on the first step and clamped between the protrusion and the second step.

Optionally, the crankshaft seat has a top surface and a bottom surface opposite to each other, the top surface has a shaft hole part for mounting the crankshaft, and part of the shaft hole part protrudes out of the bottom surface to form a crankshaft section;

the rotor assembly includes: the rotor iron core comprises a first iron core section and a second iron core section, wherein the first iron core section is provided with a first shaft hole connected with the crankshaft section, the second iron core section is provided with a second shaft hole connected with the crankshaft, and the aperture of the first shaft hole is larger than that of the second shaft hole;

the second friction pair is provided with a lubricating structure, the second iron core section is provided with an upper surface which is in contact with the lower end face of the crankshaft section, and the lubricating structure comprises a first oil storage structure arranged on the upper surface.

Optionally, the first oil storage structure includes a plurality of first oil storage holes provided on the upper surface.

Optionally, the rotor core further includes a third core segment, the second core segment is located between the first core segment and the third core segment, the first core segment the second core segment and the third core segment are a plurality of core lamination, the first oil storage hole runs through along the axial direction the second core segment, the third core segment is close to one side of the second core segment is sealed the first oil storage hole.

Optionally, the lubrication structure further includes an oil groove provided on a lower end surface of the crankshaft section, and the oil groove penetrates through the crankshaft section in a radial direction of the crankshaft section.

Optionally, the lower end face is divided into a first area far away from the cylinder seat and a second area close to the cylinder seat along a reference line, and the oil groove is formed in the first area, wherein the reference line is an auxiliary line passing through the center of the lower end face and perpendicular to the axis of the cylinder seat.

Optionally, the connecting rod includes the body of rod, is located the bent axle go-between of body of rod one end and be located the wrist pin go-between of body of rod other end, the wrist pin go-between have with the internal surface direct contact's of piston contact terminal surface, the third friction pair is equipped with lubricating structure, lubricating structure is including locating the second oil storage structure on at least part of contact terminal surface.

Optionally, the second oil storage structure includes a plurality of second oil storage holes provided on the contact end surface.

Optionally, the plurality of second oil storage holes are arranged on the contact end surface in an annular array with the center of the circle of the piston pin connecting ring as the center.

Optionally, the piston body has the inner chamber, and runs through the both sides of piston body and with the pinhole that the inner chamber is linked together, the pinhole supplies the wrist pin to pass and fixes the wrist pin go-between of connecting rod, the interior surface of inner chamber and the contact terminal surface direct contact of wrist pin go-between, lubrication structure still includes the third oil storage structure of locating on at least part of interior surface.

Optionally, the third oil storage structure includes a plurality of third oil storage holes provided on the inner surface.

Optionally, the plurality of third oil storage holes are arranged in an annular array with the center of the pin hole as the center on the inner surface.

Optionally, the piston pin includes the round pin body, the surface of round pin body has the cover and establishes the region, the piston pin go-between cover of connecting rod is located establish the region, fourth friction pair is equipped with lubricating structure, lubricating structure is including locating establish the fourth oil storage structure in region.

Optionally, the fourth oil storage structure is a plurality of fourth oil storage holes distributed in the sleeving area, and the fourth oil storage holes are arrayed along the circumferential direction and the axial direction of the pin body.

Optionally, the piston pin connecting ring is provided with an inner hole wall sleeved with the piston pin, and the lubricating structure further comprises a fifth oil storage structure arranged on the inner hole wall.

The invention also proposes a refrigeration device characterized by comprising a reciprocating compressor as described above.

The technical scheme of the invention is that a crank case, a crank shaft, a rotor assembly, a piston, a connecting rod and a piston pin are adopted, wherein the crank case comprises a crank shaft seat and a cylinder seat, the crank shaft penetrates through the crank shaft seat, and a first friction pair which is in contact with each other is arranged between the crank shaft and the crank shaft seat; the rotor assembly is connected with the crankshaft, and a second friction pair which is contacted with each other is arranged between the rotor assembly and the crankshaft seat; the piston is movably arranged in the cylinder seat; one end of the connecting rod is connected with the crankshaft, the other end of the connecting rod is connected with the piston, and a third friction pair which is in contact with each other is arranged between the connecting rod and the piston; the piston pin penetrates through the piston, and a fourth friction pair which is in contact with each other is arranged between the piston pin and the connecting rod; and at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair is provided with a lubricating structure. By arranging the lubrication structure in at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair, the lubrication structure forms a lubrication oil path, a lubrication oil film and the like between the friction pairs of the key components, so that compared with the prior art, the lubrication effect on the key components can be improved, the usage amount of lubricating oil can be reduced, the service life of the contact surface of the key components can be prolonged in a manner of coating high-hardness and high-wear-resistance materials, the cost can be reduced, and the cost performance of the machine can be improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic view showing the construction of an embodiment of a reciprocating compressor according to the present invention;

FIG. 2 is a schematic cross-sectional view of the reciprocating structure of FIG. 1;

FIG. 3 is an enlarged view of a portion of FIG. 2 at Q;

FIG. 4 is an enlarged view of a portion of FIG. 3 at T;

FIG. 5 is a schematic view of the structure of a self-lubricating pad;

FIG. 6 is a schematic diagram of an embodiment of the crank carrier of FIG. 1;

FIG. 7 is a schematic view of the structure of FIG. 6 from another view angle;

FIG. 8 is an enlarged view of a portion of FIG. 7 at A;

FIG. 9 is a schematic cross-sectional view of the structure C-C of FIG. 7;

FIG. 10 is a partial enlarged view at B in FIG. 9;

FIG. 11 is a schematic cross-sectional view of the structure of FIG. 7 at another view angle;

FIG. 12 is an enlarged view of a portion of FIG. 11 at C;

FIG. 13 is a schematic view of an embodiment of a rotor assembly according to the present invention;

FIG. 14 is a cross-sectional view taken at Z-Z in FIG. 13;

FIG. 15 is an enlarged view of a portion of the portion I of FIG. 14;

FIG. 16 is an exploded view of the rotor assembly of FIG. 13;

fig. 17 is a schematic view of the second core segment of fig. 16;

fig. 18 is a schematic structural view of the third core segment of fig. 16;

FIG. 19 is a schematic view of an embodiment of a piston rod of the present invention;

FIG. 20 is an enlarged view of a portion of FIG. 19 at E;

FIG. 21 is a schematic view of the structure of the section at D-D in FIG. 19;

FIG. 22 is an enlarged view of a portion of FIG. 21 at F;

FIG. 23 is a schematic view of an embodiment of a piston of the present invention;

FIG. 24 is a schematic view of the structure of FIG. 23 from another perspective;

FIG. 25 is a schematic view of the cross-sectional structure at N-N in FIG. 24;

FIG. 26 is a schematic view of a further embodiment of a piston according to the present invention;

FIG. 27 is a schematic view of the cross-sectional structure at M-M in FIG. 26;

fig. 28 is a partial enlarged view of G in fig. 27;

FIG. 29 is a schematic view of an embodiment of a wrist pin of the present invention;

fig. 30 is a partial enlarged view at Y in fig. 29.

Reference numerals illustrate:

the achievement of the objects, functional features and advantages of the present invention will be further described with reference to the accompanying drawings, in conjunction with the embodiments.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

It should be noted that all directional indicators (such as up, down, left, right, front, and rear … …) in the embodiments of the present invention are merely used to explain the relative positional relationship, movement, etc. between the components in a particular posture (as shown in the drawings), and if the particular posture is changed, the directional indicator is changed accordingly.

Furthermore, the description of "first," "second," etc. in this disclosure is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.

Under the large background of global carbon peak and carbon neutralization, the reciprocating compressor is used as the most core energy consumption unit of the refrigeration system, and the reduction of energy consumption loss and the improvement of reliability are forever technical hot spots in the technical field of reciprocating compressors.

Key components of the reciprocating compressor include the crankcase, cylinders, pistons 50, connecting rods, crankshafts, and the like. Since these components require high-speed friction during operation, lubrication is required to reduce friction loss and wear. Friction pairs between key parts of the reciprocating compressor, if insufficient lubrication, may cause an increase in friction between the friction pairs, thereby increasing friction loss and energy consumption of the machine, and also accelerating wear and aging of the machine, reducing the service life of the machine. In addition, insufficient lubrication of the friction pair can also lead to increased noise and vibration of the machine, affecting the stability and reliability of the machine, and possibly even causing machine failure and accidents. Therefore, insufficient lubrication of the friction pair of the reciprocating compressor is an important problem to be solved.

The related art mainly adopts lubrication to reduce abrasion, and also adopts a mode of coating high-hardness and high-wear-resistance materials to prolong the service life of the contact end face, and adopts higher-hardness and higher-wear-resistance materials to reduce friction effect by adding lubricating oil, which is not ideal.

Therefore, the invention provides the reciprocating compressor, and aims to effectively reduce the abrasion of the friction pair and improve the lubricating performance of the friction pair by arranging the lubricating structure on the friction pair of the key component, thereby reducing the noise and vibration of the reciprocating compressor and improving the performance and the service life of the reciprocating compressor.

Referring to fig. 1, in an embodiment of the present invention, the twin compressor includes a crankcase 10, a crankshaft 20, a rotor assembly 30, a piston 50, a connecting rod 40, and a piston pin 60, wherein the crankcase 10 includes a crankshaft seat 11 and a cylinder seat 19, the crankshaft 20 is disposed through the crankshaft seat 11, and a first friction pair is disposed between the crankshaft 20 and the crankshaft seat 11 and is in contact with each other; the rotor assembly 30 is connected with the crankshaft 20, and a second friction pair contacted with each other is arranged between the rotor assembly 30 and the crankshaft seat 11; the piston 50 is movably arranged in the cylinder seat 19; one end of the connecting rod 40 is connected with the crankshaft 20, the other end of the connecting rod 40 is connected with the piston 50, and a third friction pair which is contacted with each other is arranged between the connecting rod 40 and the piston 50; the piston pin 60 penetrates the piston 50, and a fourth friction pair which is in contact with each other is arranged between the piston pin 60 and the connecting rod 40; and at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair is provided with a lubricating structure.

The reciprocating compressor 100 is composed of key components such as a crankcase 10, a crankshaft 20, a rotor, a connecting rod 40, a piston 50, a piston pin 60, and the like. The crankshaft seat 11 is an important component for bearing the crankshaft 20, the crankshaft 20 is a key component for converting the reciprocating motion of the piston 50 into the rotary motion, the rotor drives the reciprocating motion of the piston 50 through the crankshaft 20, and the connecting rod 40 connects the piston 50 with the crankshaft 20, so that the reciprocating motion of the piston 50 in the cylinder seat 19 can be converted into the rotary motion of the crankshaft 20. Meanwhile, the cooperation between the piston 50 and the piston pin 60 is also very important, and the piston pin 60 can enable the piston 50 to be kept stable in reciprocating motion, deviation is avoided, and therefore normal operation of the compressor is guaranteed. The coordination among these critical components is critical to the efficient and stable operation of reciprocating compressor 100.

According to the technical scheme, the lubrication structure is arranged in at least one of the first friction pair, the second friction pair, the third friction pair and the fourth friction pair, and forms a lubrication oil path, a lubrication oil film and the like between the friction pairs of the key parts, so that compared with the prior art, the lubrication effect on the key parts can be improved by increasing the lubrication oil quantity to reduce abrasion, the usage amount of the lubrication oil is reduced, the service life of the contact surface of the key parts can be prolonged by adopting a mode of coating high-hardness and high-wear-resistance materials, the cost can be reduced, and the cost performance of a machine is improved.

The key components of the reciprocating compressor 100, including the crankcase 10, cylinders, pistons 50, connecting rods 40, crankshaft 20, etc., are generally described above. Since these components require high-speed friction during operation, lubrication is required to reduce friction loss and wear. The present solution solves the lubrication problem of the reciprocating compressor 100 by providing a lubrication structure in at least one friction pair of these critical components. Thereby effectively reducing wear of the friction pair and improving lubrication performance of the friction pair, thereby improving performance and service life of the reciprocating compressor 100.

The following describes how the first friction pair is specifically disposed, and how the lubrication structure is disposed.

Referring to fig. 2 to 5 in combination, the first friction pair is provided with the lubricating structure, the lubricating structure is configured as a self-lubricating gasket 25, the crankshaft seat 11 is provided with a crankshaft hole 131, the crankshaft is provided with a shaft shoulder 21, the shaft shoulder 21 is provided with a crankshaft thrust surface 23, the crankshaft 20 penetrates through the crankshaft hole 131, and the self-lubricating gasket 25 is arranged at the edge of the crankshaft hole 131 and is abutted against the crankshaft thrust surface 23.

Specifically, the first friction pair refers to a situation that, between the crankshaft thrust surface 23 and the crankshaft thrust surface 23, in the existing reciprocating compressor 100, a bearing thrust form is adopted between the crankshaft thrust surface 23 and the crankshaft thrust surface 23 to reduce friction and shock, and the bearing thrust itself is composed of an upper supporting plate, a lower supporting plate and a retainer, both in terms of technology and cost, the retainer is relatively high, and the retainer may deform under high temperature conditions to cause the risk of falling of steel balls, thereby affecting the reliability of the whole machine and causing abnormal abrasion and failure of a sample machine.

Generally, the crankshaft 20 includes a main shaft, a shoulder 21 and an eccentric shaft, which are sequentially connected, the main shaft passes through a crankshaft hole 131 and is connected with an external driving motor, the shoulder 21 is disposed near the crankshaft seat 11, the eccentric shaft forms a revolute pair with the piston pin 60 through the connecting rod 40, and the piston 50 is fixedly connected with the piston pin 60 through a spring pin.

Referring to fig. 2 to 5, by providing the self-lubricating pad 25 at the edge of the crank hole 131, the self-lubricating pad 25 is abutted against the crankshaft thrust surface 23 of the shaft shoulder 21, so that the crankshaft thrust surface 23 of the shaft shoulder 21 and the crankshaft thrust surface 23 of the crankcase 10 are effectively separated, the contact area between the two is reduced, the friction between the crankshaft thrust surface 23 of the shaft shoulder 21 and the crankshaft thrust surface 23 is improved, and the crankshaft thrust surface 23 and the self-lubricating pad 25 have better lubrication, so that the abrasion between the crankshaft thrust surface 23 and the crankshaft thrust surface 23 is reduced, the noise of the reciprocating compressor 100 in the working process is reduced, and the energy efficiency applied to the reciprocating compressor 100 is improved. In addition, the self-lubricating gasket 25 is utilized to effectively replace bearing thrust commonly applied in the existing reciprocating compressor 100, so that the whole structure of the reciprocating compressor 100 is simpler, the assembly process is reduced, the cost is reduced, and the popularization and the application are convenient.

The self-lubricating gasket 25 has an inner annular surface and an outer annular surface, wherein the cross-sectional shape of the inner annular surface is circular, so that the inner annular surface can be conveniently matched with the crank hole 131, the cross-sectional shape of the outer annular surface can be in regular shapes such as circular, rectangular and the like, so that the self-lubricating gasket is convenient to process, and can also be in irregular shapes.

Optionally, in an embodiment, the self-lubricating pad 25 is configured as a polytetrafluoroethylene pad, and the self-lubricating pad 25 made of polytetrafluoroethylene has excellent high temperature resistance, can be used at a temperature of 260 ℃ and has excellent corrosion resistance, and is not hardened or softened in a refrigerant and lubricating oil environment, so that effective separation between the crankshaft thrust surface 23 and the crankshaft thrust surface 23 is ensured, and has excellent self-lubricating property, and good lubrication can be provided to reduce friction with the crankshaft thrust surface 23. However, the present application is not limited thereto, and in other embodiments, the self-lubricating pad 25 may be a graphite pad or a polyether ether ketone pad. A metal-based gasket containing polytetrafluoroethylene is also possible.

Optionally, in an embodiment, the friction coefficient μ of the self-lubricating pad 25 is greater than or equal to 0.05 and less than or equal to 0.1, and the self-lubricating pad 25 is made of a solid lubricating material, so that the friction coefficient of the self-lubricating pad 25 is set between 0.05 and 0.1, which is beneficial to reducing friction loss and improving compressor energy efficiency. Specifically, the friction coefficient of the self-lubricating pad 25 may have a specific value of 0.05, 0.06, 0.07, 0.08, 0.09, 0.1, or the like.

Referring to fig. 2 to 4, in an embodiment, the crankcase 10 is provided with a mounting step 14 at the edge of the crank hole 131, the self-lubricating gasket 25 is sleeved on the mounting step 14 and protrudes at least partially from the mounting step 14, so that the assembly is convenient, the contact between the crank thrust surface 23 and the mounting step 14 can be reliably avoided, the contact area between the crank thrust surface 23 and the mounting step 14 is reduced, and further, the unnecessary friction movement between the crank thrust surface 23 and the mounting step 14 is effectively prevented.

Specifically, referring to fig. 4, in an embodiment, the shoulder 21 is provided with a protrusion 22, the crankshaft thrust surface 23 is formed on a surface of the protrusion 22 facing the mounting step 14, the mounting step 14 includes a first step 151 and a second step 152 which are annular, the self-lubricating pad 25 is sleeved on the first step 151 and clamped between the protrusion 22 and the second step 152, it is understood that when the crankshaft 20 is assembled to the crankcase 10 through the crankshaft hole 131, the protrusion 22 on the shoulder 21 abuts against the self-lubricating pad 25 by using the crankshaft thrust surface 23 thereof, on one hand, the self-lubricating pad 25 is sleeved on the first step 151 and at least partially protrudes out of the first step 151, and the protrusion of the mating protrusion 22 facilitates the self-lubricating pad 25 to contact with the crankshaft 20, further increases the gap between the crankshaft thrust surface 23 and the crankcase 10, and reliably reduces the contact area between the crankshaft thrust surface 23 and the mounting step 14; on the other hand, the self-lubricating gasket 25 is sleeved with the first step 151 and clamped between the boss 22 and the second step 152, which is favorable for improving the assembly reliability of the self-lubricating gasket 25, and ensures that the self-lubricating gasket 25 can provide better lubrication to reduce friction loss. The protrusion 22 may be annular as a whole, or may be formed by a plurality of protrusions arranged at intervals.

Referring to fig. 4, in an embodiment, the outer peripheral surface of the first step 151 is in clearance fit with the inner hole of the self-lubricating pad 25, so as to facilitate the assembly of the self-lubricating pad 25.

Specifically, in an embodiment, the clearance between the outer peripheral surface of the first step 151 and the inner hole of the self-lubricating pad 25 is k, where k is greater than or equal to 0.05mm and less than or equal to 0.5mm. Specifically, when k is greater than 0.5mm, the self-lubricating pad 25 is easy to move in the radial direction, and further is easy to be staggered with the protrusion 22, so that the self-lubricating pad 25 is stressed unevenly, and the motion stability of the crankshaft 20 is influenced; when k is less than 0.05mm, smooth fitting of the self-lubricating pad 25 with the first step 151 is not facilitated. Therefore, the clearance k between the outer peripheral surface of the first step 151 and the inner hole of the self-lubricating pad 25 is set between 0.05mm and 0.5mm, which not only facilitates the assembly of the self-lubricating pad 25 and the first step 151, but also ensures the reliable contact between the self-lubricating pad 25 and the boss 22, the uniform stress of the self-lubricating pad 25 and the driving stability of the crankshaft 20.

Referring to fig. 4, in an embodiment, the height of the first step 151 is smaller than the thickness of the self-lubricating pad 25, so as to ensure that the crankshaft thrust surface 23 of the crankshaft 20 is not in direct contact with the crankcase 10, thereby facilitating the increase of the clearance between the crankshaft thrust surface 23 and the crankcase 10, reliably reducing the contact area between the crankshaft thrust surface 23 and the mounting step 14, preventing unnecessary friction movement between the crankshaft thrust surface 23 and the mounting step 14, and reducing wear between the crankshaft thrust surface 23 and the crankcase 10.

Optionally, in an embodiment, a process hole 153 is provided at the connection between the first step 151 and the second step 152, so as to facilitate the machining of the mounting step 14.

Optionally, in an embodiment, a first chamfer 154 is disposed on a side of the first step 151 near the crankshaft hole 131, so as to avoid abrasion of the crankshaft 20 caused by collision between the first step 151 and the crankshaft 20, and further facilitate the crankshaft 20 passing through the crankshaft hole 131.

Optionally, in an embodiment, a second chamfer structure 155 is disposed on a side of the first step 151 away from the crankshaft hole 131, so as to avoid abrasion caused by collision contact between the first step 151 and the self-lubricating pad 25, and further facilitate the first step 151 extending into the inner hole of the self-lubricating pad 25.

Optionally, in an embodiment, an oil channel is disposed in the crankshaft 20, and/or an oil groove 162 is disposed on an outer surface of a main shaft of the crankshaft 20, so that the crankshaft 20 and the crankcase 10 are always in a state of oil lubrication and oil contact, abrasion caused by friction between the crankshaft 20 and the crankcase 10 is reduced, and service life of a pump body assembly is prolonged.

With reference to fig. 6 to 18, how the second friction pair is provided, and how the lubrication structure is provided will be described in detail.

Referring to fig. 6 to 12, the crank base 11 has a top surface 111 and a bottom surface 112 opposite to each other, the top surface 111 has a shaft hole portion 13 for mounting the crankshaft 20, and a portion of the shaft hole portion 13 protrudes from the bottom surface 112 to form a crankshaft segment 16; referring to fig. 13 to 18, the rotor assembly 30 includes: a rotor core 31, the rotor core 31 including a first core segment 32 and a second core segment 33, the first core segment 32 having a first shaft hole 321 connected to the crankshaft segment 16, the second core segment 33 having a second shaft hole 331 connected to the crankshaft 20, the first shaft hole 321 having a larger aperture than the second shaft hole 331; wherein the second friction pair is provided with a lubrication structure, the second core segment 33 has an upper surface 332 contacting the lower end surface 161 of the crankshaft segment 16, and the lubrication structure includes a first oil storage structure 36 provided on the upper surface 332.

In the related art, the crank shaft section 16 of the crank case 10 is disposed in the rotor, a second friction pair exists between the lower end surface 161 of the crank shaft section 16 and the rotor, the lubrication condition between the crank case 10 and the rotor is relatively insufficient, and dry grinding is easy to occur.

Specifically, the rotor assembly 30 includes a rotor core 31, a permanent magnet 38, a rotor end plate 39, and a connector 37, the rotor core 31 is provided with a magnet slot 35, and the permanent magnet 38 is provided in the magnet slot 35; the rotor core 31 comprises a first core section 32 and a second core section 33, the first core section 32 is provided with a first shaft hole 321 used for being connected with the crankshaft section 16 of the crankshaft seat 11, the second core section 33 is provided with a second shaft hole 331 used for being connected with the crankshaft 20, the aperture of the first shaft hole 321 is larger than that of the second shaft hole 331, the second core section 33 is provided with an upper surface 332 contacted with the lower end surface 161 of the crankshaft section 16, and the upper surface 332 is provided with a first oil storage structure 36; the connector 37 passes through the rotor end plate 39 and the rotor core 31 to connect the rotor end plate 39, the rotor core 31, and the permanent magnets 38 together.

During assembly, the crankshaft section 16 of the crankshaft seat 11 extends into the first shaft hole 321 of the rotor core 31, the lower end surface 161 of the crankshaft section 16 contacts with the edge between the second shaft hole 331, i.e. the upper surface 332, and when the crankshaft drives the rotor core 31 to rotate at high speed, the lower end surface 161 of the crankshaft section 16 rubs with the upper surface 332 of the second core section 33, in addition, vibration is inevitably generated in the operation process of the reciprocating compressor 100, which can cause up-and-down movement of the rotor, and related technologies in the industry mainly reduce abrasion by increasing lubrication, and have high cost. Through arranging first oil storage structure 36 at the upper surface 332 of second iron core section 33, first oil storage structure 36 can store a certain amount of lubricating oil, and lubricating oil in the first oil storage structure 36 can splash in the rotation to can lubricate rotor and bent axle 20, rotor and crankcase 10, guarantee the lubrication condition between crankcase 10 and the rotor subassembly 30, reduce the unusual wearing and tearing that cause because the rotor beats, alleviate unusual wearing and tearing risk, guarantee compressor steady operation, the production of noise reduction, and then promote the complete machine efficiency of compressor.

The main function of rotor core 31 is to provide a magnetic flux path enabling the conversion of electrical energy into mechanical energy. The design and manufacture of rotor core 31 has a great impact on the efficiency, power and noise level of the motor. There are two ways of manufacturing rotor core 31: the monolithic core and the punched sheet are laminated to form the core.

The whole iron core is formed by casting or forging and the like. The magnetic circuit has the advantages of stable structure, good mechanical property, small magnetic circuit loss and the like, but the manufacturing cost is higher.

The lamination of the punching sheets to form the iron core is formed by superposing a plurality of thin iron sheets together, blanking the iron sheets into a required shape and then stacking the iron sheets. The magnetic circuit has the advantages of low manufacturing cost, high material utilization rate, small magnetic circuit loss and the like.

In one embodiment, the first core segment 32 and the second core segment 33 are formed of a plurality of monolithic cores, each monolithic core having a corresponding flange and slot for ease of assembly. This design may make rotor core 31 stronger and more durable, while also being easier to repair and replace. The first oil reservoir structure 36 is disposed on a monolithic core.

In another embodiment, the first core segment 32 and the second core segment 33 are each formed by stacking a plurality of silicon steel sheets, and the specific selection is comprehensively considered according to the application scenario and requirements.

A rotor end plate 39 and a connecting member 37 to connect the rotor end plate 39, the rotor core 31, and the permanent magnets 38 together to form a unit. When in installation, the permanent magnets 38 are arranged in the magnet grooves 35, and the rotor end plate 39 prevents the permanent magnets 38 from being separated from the magnet grooves 35 and ensures the overall stability of the rotor core 31.

The connection 37 is typically a plurality of rivets threaded through the clamping rotor core 31, end plates, and secure the permanent magnets 38 within the rotor core 31. In some arrangements the connection may also be secured using bolts and nuts.

In one embodiment, the rotor end plate 39 includes a first end plate 391, the magnet slots 35 of the second core segment 33 are closed at one end, the permanent magnets 38 are disposed in the magnet slots 35, the first end plate 391 is disposed over the first core segment 32, and the first end plate 391 and the second core segment 33 are clamped by the connector 37, thereby fixedly forming the entire rotor assembly 30.

Referring to fig. 14 and 16, in another embodiment, the rotor end plate 39 includes a first end plate 391 and a second end plate 392, the first end plate 391 and the second end plate 392 are respectively located at two ends of the rotor core 31 in the axial direction, the first end plate 391 is close to the first core segment 32, and the first end plate 391 and the second end plate 392 clamp and fix the rotor core 31 and the permanent magnets 38 through the connection members 37. The first end plate 391 and the second end plate 392 can fix the permanent magnet 38, thereby improving the reliability of fixing the permanent magnet 38, and ensuring the reliability and safety of assembling the rotor assembly 30, so as to reduce or avoid abnormal sound generated by shaking of the permanent magnet 38 during the operation of the compressor. And simultaneously, the permanent magnet 38 can be prevented from being broken due to shaking of the permanent magnet 38, so that the performance of the permanent magnet 38 is ensured.

Referring to fig. 13 and 17, in particular, the first oil storage structure 36 includes a plurality of first oil storage holes 361 provided on the upper surface 332. The plurality of first oil storage holes 361 are arranged at intervals, so that on one hand, the lubrication area is increased, on the other hand, the influence of the first oil storage holes 361 intersecting each other on the oil storage capacity is avoided, the reduction of the strength of a contact surface and the reduction of the bearing capacity of the contact surface are avoided, and the deformation is easy to occur.

Further, referring to fig. 14, 16 and 18, the rotor core 31 further includes a third core segment 34, the second core segment 33 is located between the first core segment and the third core segment 34, the first core segment 32, the second core segment 33 and the third core segment 34 are all formed by stacking a plurality of core laminations, the first oil storage hole 361 axially penetrates through the second core segment 33, and one side of the third core segment 34 close to the second core segment 33 is closed with the first oil storage hole 361.

In this scheme, first iron core section 32, second iron core section 33 and third iron core section 34 are a plurality of iron core punching lamination and form, have low in manufacturing cost, material utilization height, advantage such as magnetic circuit loss are little, first oil storage hole 361 runs through along the axial second iron core section 33, third iron core section 34 is close to one side of second iron core section 33 seals first oil storage hole 361.

In another aspect, the first core segment 32 and the second core segment 33 are formed by stacking a plurality of core laminations, the first oil storage hole 361 axially penetrates through the second core segment 33, and the second end plate 392 closes the first oil storage hole 361 at a side close to the second core segment 33.

In one embodiment, the plurality of first oil storage holes 361 are arranged in rows and columns, such as rectangular, circular, etc. rows and columns on a portion of the upper surface 332.

Specifically, the plurality of first oil storage holes 361 are arranged on the upper surface 332 in an annular array with the center of the second shaft hole 331 as the center. The plurality of first oil storage holes 361 are arranged in a single circle, a double circle, etc. on the upper surface 332.

Specifically, referring to fig. 17, the spacing angle θ between any adjacent two of the first oil storage holes 361 satisfies 15+.θ+.180 °. The too dense first oil storage holes 361 may not significantly improve the actual lubrication effect, in addition to the increase in the difficulty of processing, and the too sparsely distributed plurality of first oil storage holes 361 may not sufficiently uniform lubrication between the upper surface 332 and the lower end surface 161 of the crankcase 10, and the relative lubrication effect may be weak, so that the plurality of first oil storage structures 36 between the friction pairs at evenly spaced portions may be more convenient to process, and the lubrication effect may be relatively superior.

At 180 ° θ, the first oil storage holes 361 are symmetrically arranged on the diameter of the second shaft hole 331, and the symmetrical arrangement ensures uniformity of lubrication and uniform stress of the rotor on the upper surface 332 because the crankshaft 20 rotates in the axial direction.

Referring to fig. 14 and 17, in order to prevent the edge of the second shaft hole 331 from being easily deformed and to reduce the strength of the bearing edge, the distance Z between the center of the first oil storage hole 361 and the edge of the second shaft hole 331 is 0.5mm < Z < 8mm. Alternatively, the wall thickness N between the first oil storage hole 361 and the second shaft hole 331 satisfies N being 1mm and 13mm.

If Z is smaller than 0.5mm, the strength between the second shaft hole 331 and the first oil storage hole 361 is insufficient, and the core punched sheet of the second core segment 33 is easily broken there, and the quality is not ensured.

If Z is greater than 8mm, although the strength is secured, the oil storage amount and effective lubrication area of the first oil storage hole 361 are also reduced, and it is understood that the ring width between the first shaft hole 321 and the second shaft hole 331 is such that the larger s the upper surface 332, the closer the first oil storage hole 361 is to the inner wall of the first shaft hole 321.

Specifically, referring to FIGS. 14 and 15, the diameter D of the first oil storage hole 361 satisfies 1 mm.ltoreq.D.ltoreq.5 mm, and the depth T of the first oil storage hole 361 satisfies 2 mm.ltoreq.T.ltoreq.21 mm.

When the first oil storage hole 361 is a non-circular hole, the diameter d refers to an equivalent diameter of the first oil storage hole 361, and the equivalent diameter refers to a diameter of the first oil storage hole 361 that is similar in shape and size to a sphere of the same volume.

The excessively large or small first oil storage hole 361 as described above does not enhance the oil storage effect, and the first oil storage hole 361 acts microscopically, and by defining the diameter d and the depth h of the first oil storage hole 361, the second core segment 33 is not excessively adversely affected while improving the friction problem between the upper surface 332 and the crankcase 10. In order to ensure the machining precision, the friction pair, that is, the relative movement of the second shaft hole 331 and the crankcase 10, is prevented from being affected by the residual sharp edges, burrs, etc. after machining, and the first oil storage hole 361 is configured as a laser etched hole, an ultrasonic etched hole, an electrochemical etched hole, or an electric spark machined hole.

It will be appreciated that since the rotor core 31 is formed by laminating core laminations, the first oil storage hole 361 penetrates the second core segment 33 when the core laminations are processed.

In this embodiment, for convenience of manufacturing, the shapes and sizes of the plurality of first oil storage holes 361 are the same. Specifically, the cross-sectional shape of the first oil storage hole 361 is a regular planar geometry. Such as circular, triangular, rectangular, star-shaped, etc.

In other embodiments, the shape and size of the plurality of first oil storage holes 361 may be different.

If multiple groups of different first oil storage holes 361 are arranged in different areas of the upper surface 332, the shapes and sizes of the multiple first oil storage holes 361 in each area are different.

Specifically, referring to fig. 14, in order to avoid magnetic leakage and to avoid abnormal sounds generated by the shaking of the permanent magnets 38 during the operation of the compressor, the height H1 of the rotor core 31 and the height H2 of the permanent magnets 38 satisfy 0.90.ltoreq.h1/h2.ltoreq.0.99. The situation that the permanent magnets 38 are not tightly riveted after the rotor assembly 30 is assembled can be avoided, and abnormal sounds generated in the operation process of the rotor assembly 30 are avoided.

Further, the height H1 of the rotor core 31 and the thickness B1 of the first end plate 391 satisfy b1+. 0.015H1, and the height H1 of the rotor core 31 and the thickness B2 of the second end plate 392 satisfy b2+. 0.015H1. Thereby facilitating assembly of the components within the rotor assembly 30, ensuring reliability and safety of assembly of the rotor assembly 30 to reduce or avoid abnormal sounds generated by the wobble of the permanent magnets 38 during operation of the compressor.

Further, the total length K of the connecting member 37 satisfies 1.05.ltoreq.K/(H1+B1+B2). Ltoreq.1.2.

Wherein the total length of the connecting piece 37 is the total length of the connecting piece 37 before riveting. Thereby facilitating the connection of the first end plate 391, the rotor core 31, and the second end plate 392 by the connection member 37, ensuring reliability and safety of the rotor assembly to reduce or avoid abnormal sounds generated by the shaking of the permanent magnet 38 during the operation of the compressor.

In one embodiment, the tail of the connector 37 is provided with a groove. After the rotor assembly 30 is assembled, the tail portions of the connector 37 may be swaged to deform the tail portions and effectively bring the parts of the rotor assembly 30 together.

Further, in order to avoid the wobbling of the permanent magnets 38, in one embodiment, the magnet slots 35 are provided in the rotor core 31, and the rotor core 31 is higher than the permanent magnets 38 are provided in the magnet slots 35. The first end plate 391 and the second end plate 392 are respectively clamped at two ends of the rotor core 31, and the first end plate 391 is provided with a limiting boss for stopping the permanent magnet 38 so as to realize axial limiting of the permanent magnet 38, thereby preventing the permanent magnet 38 from shaking in the magnet groove 35, improving the reliability of fixing the permanent magnet 38, reducing the noise of the rotor assembly 30, reducing the noise of the compressor, preventing the permanent magnet 38 from being broken due to shaking of the permanent magnet 38, and ensuring the performance of the permanent magnet 38.

In summary, the second core segment 33 has an upper surface 332 that contacts the end surface of the crankshaft segment 16, and the upper surface 332 is provided with a first oil storage structure 36; the connector 37 passes through the rotor end plate 39 and the rotor core 31 to connect the rotor end plate 39, the rotor core 31, and the permanent magnets 38 together. In the related art, the crank tube section 16 of the crank case 10 is disposed in the rotor, a friction pair exists between the lower end surface 161 of the crank tube section 16 and the rotor, the lubrication condition between the crank case 10 and the rotor is relatively insufficient, and dry grinding is easy to occur. Through arranging first oil storage structure 36 at the upper surface 332 of second iron core section 33, first oil storage structure 36 can store a certain amount of lubricating oil, lubricating oil in the first oil storage structure 36 can splash in the rotation, or because the rotor beats and throws away, thereby can lubricate rotor and bent axle 20, rotor and crankcase 10, guarantee the lubrication condition between crankcase 10 and rotor subassembly 30, reduce the friction between rotor subassembly 30 and the crankcase 10, optimize the lubrication effect between the two, can effectively reduce the friction loss of compressor, alleviate abnormal wear risk, guarantee that the compressor operates steadily, and then promote the complete machine efficiency of compressor.

Referring to fig. 6 to 12, the crankcase 10, which is one of the core members that are engaged with the crankshaft 20 for high-speed rotation, reduces the penetration of wear debris into the engagement surface thereof, which is one of the key indexes for improving the compressor.

Further, the lubrication structure further comprises an oil groove 162 arranged on the lower end surface 161 of the crankshaft section 16, the oil groove 162 penetrates through the crankshaft section 16 along the radial direction of the crankshaft section 16, and the arrangement of the oil groove 162 can effectively reduce the probability that rotor runout is easy to generate abnormal abrasion and large-particle abrasive dust enters a shaft hole gap, so that the occurrence of compressor blocking is reduced, and the reliability of the compressor is improved.

The crankcase 10 comprises a crankshaft seat 11, the crankshaft seat 11 is provided with a top surface 111 and a bottom surface 112 which are opposite, the top surface 111 is provided with a shaft hole part 13 for installing a crankshaft 20, part of the shaft hole part 13 protrudes out of the bottom surface 112 to form a crankshaft section 16, when the crankshaft 20 is installed, the neck of the crankshaft 20 is positioned on the top surface 111, the neck of the crankshaft 20 is connected with a crankshaft connecting ring 411 of a connecting rod 40, the driving connecting rod 40 moves, the crankshaft section 16 stretches into the shaft hole of a rotor core 31, the crankshaft 20 enters the shaft hole of the rotor through the crankshaft section 16 and is connected with the rotor core 31, the lower end surface 161 of the crankshaft section 16 is provided with an oil groove 162, the lower end surface 161 is contacted with an upper surface 332 between a rotating shaft hole of the rotor and the shaft hole, the oil groove 162 penetrates through the crankshaft section 16 along the radial direction of the crankshaft section 16, and when the crankshaft 20 drives the rotor to rotate, abrasive dust generated by friction between the lower end surface 161 and the crankshaft 20, abrasive dust generated by high friction between the crankcase 10 and the crankshaft 20 flows out along with lubricating oil through the oil groove 162 arranged on the lower end surface 161, so that the probability of the crankcase 10/20, the crankcase 10/the crankcase 10 and the rotor can be effectively reduced from entering the shaft hole due to abnormal and the abnormal probability of the clamping probability of the rotor and the compressor.

Specifically, referring to fig. 6 and 9, the crankcase 10 further includes a cylinder block 19 disposed on the top surface 111, the cylinder block 19 having a cylinder bore 191 in which the piston 50 is mounted, the shaft hole 13 being located in the middle of the top surface 111, the cylinder block 19 being located at an edge of the top surface 111, and a portion of the cylinder block 19 protruding from the top surface 111 in a direction from the bottom surface 112 to the top surface 111. The compressor is the heart of the refrigeration cycle and is also the most central component of the refrigerator. The crankcase 10 is a critical support assembly component of the compressor, and its design determines the overall size of the compressor. In the related art, the height of the crankcase 10 is higher, which results in a larger overall size of the compressor, and thus increases the occupancy rate of the compressor to the internal space of the refrigerator, and the overall refrigerator cannot be thinned. Through rationally setting up the cooperation structure of bent axle seat 11 and cylinder block 19, make the part of cylinder block 19 follow the direction of bottom surface 112 to top surface 111 protrusion in top surface 111, like this, reduced the overall dimension of crankcase 10 main part and cylinder body, and then be favorable to reducing the complete machine height dimension who uses the compressor of crankcase 10, and then can reduce the occupation rate of compressor to refrigeration plant's inner space, so under the certain circumstances of complete machine size of refrigeration plant, can correspondingly increase refrigeration plant's refrigerating chamber and/or freezing chamber's volume, and then be favorable to increasing refrigeration plant's volume, under the certain circumstances of refrigeration plant's volume, be favorable to reducing refrigeration plant overall dimension, be favorable to realizing refrigeration plant's light, thinness.

In one embodiment, the cylinder block 19 and the crankshaft block 11 are integrally formed, for example, the cylinder block 19 and the crankshaft block 11 are integrally formed as an iron casting.

In another embodiment, the cylinder block 19 and the crankshaft block 11 are provided separately. The cylinder seat 19 is arranged on the crank seat 11 through a bracket, which is beneficial to the assembly of the compressor and can reduce the processing difficulty and the processing cost of the compressor and parts thereof.

Specifically, referring to fig. 7, the lower end surface 161 is divided into a first area 181 far from the cylinder block 19 and a second area 182 near to the cylinder block 19 along a reference line, and the oil groove 162 is provided in the first area 181, wherein the reference line is an auxiliary line passing through the center of the lower end surface 161 and perpendicular to the axis of the cylinder bore 191.

The stress of the first area 181 is weaker than that of the second area 182, the top surface 111 of the crankshaft seat 11 is provided with a cylinder seat 19 positioned at one side, two ends of the connecting rod 40 are respectively connected with the crankshaft 20 and the piston 50, the crankshaft 20 rotates to drive the connecting rod 40, the connecting rod 40 drives the piston 50 to reciprocate in the cylinder seat 19, because the stress is different, the contact pressure between the lower end surface 161 of the crankshaft section 16 and the upper surface 332 of the rotating shaft hole of the rotor is different, in order to avoid that the strength of the lower end surface 161 is influenced by the opening of the oil groove 162, the oil groove 162 is opened in the first area 181 with weaker stress of the lower end surface 161, and the problems of deformation and abrasion of the lower end surface 161 in the operation process are avoided.

Referring to fig. 12, in an embodiment, an inner wall of the crankshaft segment 16 at the lower end surface 161 is provided with an inner chamfer 171, and a height distance from a bottom of the oil groove 162 to an intersection line between the inner chamfer 171 and the inner wall is M, where M satisfies: m is less than or equal to 1.5mm.

In the present embodiment, the outer wall of the crankshaft segment 16 at the lower end surface 161 is provided with an outer chamfer 172, and the inner wall of the crankshaft segment 16 at the lower end surface 161 is provided with an inner chamfer 171. The inner chamfer 171 and the outer chamfer 172 can remove sharp edges, reduce the generation of abrasive dust and damage the rotor; the inner chamfer 171 and the outer chamfer 172 have a certain guiding function, which is beneficial to assembly; the inner chamfer 171 and the outer chamfer 172 also release stress to redistribute internal tissue structures during heat treatment of the material, and thus cracking is less likely to occur and deformation is reduced. In order to avoid the deformation of the lower end surface 161 easily caused by the arrangement of the oil groove 162, to reduce the strength of the edge of the oil groove 162, and to make the abrasive dust better flow out of the oil groove 162 with the lubricant, M.ltoreq.1.5 mm. First, in the direction from top surface 111 to bottom surface 112, the height distance between the bottom of oil groove 162 and the intersection of inner chamfer 171 and the side wall of crankshaft segment 16 is no more than 1.5mm; secondly, in the direction from the bottom surface 112 to the top surface 111, the height distance between the bottom of the oil groove 162 and the intersection point of the inner chamfer 171 and the side wall of the crankshaft segment 16 is not more than 1.5mm.

Specifically, referring to fig. 10, in order to secure the strength of the lower end surface 161, deformation is avoided in the vicinity of the oil groove 162, the groove depth of the oil groove 162 is V, where V satisfies: v is more than or equal to 0.6mm and less than or equal to 3.2mm.

When the groove depth is smaller than 0.6mm, the abrasion dust is not easy to discharge along with the lubricant; when the groove depth is greater than 3.2mm, the strength of the lower end face 161 cannot be ensured.

Specifically, referring to fig. 8 and 12, because of the relationship of the inner chamfer 171 and the outer chamfer 172, in order to ensure that the oil groove 162 communicates with the inner wall of the crank tube segment 16, the lower end surface 161 is not easily deformed, and the strength of the edge of the oil groove 162 is reduced, the length of the oil groove 162 in the penetrating direction is F, and the wall thickness of the crank tube segment 16 is Z, wherein the relationship between F and Z satisfies: F/Z is more than or equal to 0.45 and less than or equal to 1.

Specifically, referring to fig. 10, in order to enable the swarf to flow out of the oil groove 162 with the lubricant well, the strength of the lower end surface 161 is ensured, the width of the groove bottom of the oil groove 162 is W1, where L satisfies: w1 is more than or equal to 0.8mm and less than or equal to 3.6mm, the width of the notch of the oil groove 162 is W2, wherein W satisfies: w2 is more than or equal to 1.0mm and less than or equal to 7.2mm.

The width of the groove bottom of the oil groove 162 and the width of the notch of the oil groove 162 are different to form a transverse slope such as the trapezoid-shaped oil groove 162, i.e., the groove bottom is small and the notch is large, so that disturbance occurs to facilitate the discharge of the abrasive dust when the lubricant flows through the oil groove 162. The width of the groove bottom is too small, which is not beneficial to the discharge of abrasive dust along with the lubricant; the width of the groove bottom is too large, and the strength of the lower end surface 161 near the oil groove 162 is reduced; the width of the notch is the same.

In summary, by providing the oil groove 162 in the crankshaft segment 16, the oil groove 162 penetrates the crankshaft segment 16 in the radial direction of the crankshaft segment 16. The abrasion dust generated by abnormal abrasion of the crank case 10, the crank shaft 20 and the crank case 10/the rotor flows out along with the lubricating oil through the oil groove 162 formed in the lower end face 161, so that the conditions of easy abnormal abrasion and large particle abrasion dust generated by rotor jumping can be effectively reduced, the probability of the occurrence of compressor jamming can be reduced when the engine is applied to a compressor, and the running reliability of the compressor is improved.

The following describes how the third friction pair is provided, and how the lubrication structure is provided.

The third friction pair is a friction pair in which the contact end surface 42 of the piston pin connecting ring 412 of the connecting rod 40 and the inner surface 52 of the piston 50 have a plane-to-plane relationship, and since the relative movement of the piston pin connecting ring 412 and the piston 50 is a swing motion around the piston pin 60, the lubrication condition between the lower end surface 161 of the piston pin connecting ring 412 and the inner surface 52 of the piston 50 is relatively insufficient, and a dry grinding phenomenon is liable to occur.

Referring to fig. 19 to 22, the connecting rod 40 includes a rod body 41, a crankshaft connecting ring 411 at one end of the rod body 41, and a wrist pin connecting ring 412 at the other end of the rod body 41, the wrist pin connecting ring 412 having a contact end surface 42 in direct contact with an inner surface 52 of the piston 50, and the third friction pair being provided with a lubrication structure including a second oil storage structure 43 provided on at least a portion of the contact end surface 42.

The connecting rod 40 comprises a rod body 41, a crankshaft connecting ring 411 positioned at one end of the rod body 41 and a piston pin connecting ring 412 positioned at the other end of the rod body 41, wherein the piston pin connecting ring 412 is provided with a contact end surface 42 for directly contacting with the inner surface 52 of the piston 50, and at least part of the contact end surface 42 is provided with a second oil storage structure 43.

The relative movement of the piston pin connection ring 412 and the piston 50 is a swing motion around the piston pin 60, the piston pin connection ring 412 has a contact end surface 42 directly contacting the inner surface 52 of the piston 50, and the contact end surface 42 and the inner surface 52 of the piston 50 are in surface-to-surface contact, so that during the continuous movement of the connecting rod 40, the amount of lubricating oil is insufficient, and after a long period of operation, the piston 50 and the cylinder are often worn, thereby affecting the service life thereof. By arranging the second oil storage structure 43 at least on part of the contact end surface 42 of the piston pin connection ring 412, part of lubricating oil is stored in the second oil storage structure 43, so that the stored oil can lubricate a friction pair between the piston 50 and the piston pin connection ring 412 in the relative motion of the piston pin connection ring 412 and the piston 50, the lubrication effect between the piston 50 and the piston pin connection ring 412 is optimized, the friction loss of the compressor can be effectively reduced, and the energy efficiency ratio of the compressor is improved.

The contact end face 42 of the piston pin connection ring 412 is a ring width between an inner ring and an outer ring of the piston pin connection ring 412, the relative movement of the piston pin connection ring 412 and the piston 50 is swinging around the piston pin 60, and at least part of the contact end face 42 is provided with the second oil storage structure 43, which may be in a partial area of the circumference of the piston pin connection ring 412, such as 1/4 of the circumference, 1/6 of the circumference, etc.; or may be circumferentially around the contact end face 42 along the circumference of the wrist pin connection ring 412.

The contact end face 42 is in direct contact with the inner surface 52 of the piston 50 due to gravity, and the contact end face 42 is in surface-to-surface contact with the inner surface 52 of the piston 50, so that the lubrication oil quantity is insufficient, and the piston runs for a long time; or in the initial operation process, the lubricating oil is insufficient, friction loss is easy to occur due to dry grinding, part of the lubricating oil is stored in the second oil storage structure 43, and the stored lubricating oil can lubricate during the relative movement process of the contact end face 42 and the inner surface 52 of the piston 50, so that the lubrication effect between the contact end face 42 and the piston 50 is optimized, the friction loss between the contact end face and the piston 50 is reduced, and the energy efficiency ratio of the compressor is improved.

Referring to fig. 19 and 20, in particular, the second oil storage structure 43 includes a plurality of second oil storage holes 431 provided on the contact end surface 42. The plurality of second oil storage holes 431 are arranged at intervals, so that on one hand, the lubrication area is increased, on the other hand, the influence of the second oil storage holes 431 crossing each other on the oil storage capacity is avoided, and the reduction of the strength of the contact surface and the reduction of the bearing capacity of the contact surface are avoided.

In one embodiment, the plurality of second oil storage holes 431 are arranged in rows and columns, such as rectangular, circular, etc. rows and columns on the portion of the contact end face 42.

In another embodiment, the plurality of second oil storage holes 431 are arranged on the contact end surface 42 in an annular array with the center of the piston pin connection ring 412 as the center. The plurality of second oil storage holes 431 are arranged in an array along the center of the piston pin connection ring 412 on the contact end surface 42, for example, the plurality of second oil storage holes 431 are arranged in a single circle, a double circle, or the like.

Specifically, the diameter d1 of the second oil storage hole 431 does not exceed the ring width of the piston pin connection ring 412. On the one hand, the excessively large or small second oil storage hole 431 does not improve the oil storage effect; on the other hand, the excessively large second oil storage hole 431 is manifested in a macroscopic smoothness or a decrease in flatness, which tends to increase wear between the contact end surface 42 and the inner surface 52 of the piston 50, and may cause a problem of weakening the strength of the piston pin connection ring 412 or the like.

Referring to fig. 21 to 22, specifically, in the present embodiment, the diameter d1 of the second oil storage hole 431 satisfies 0.5mm < d1 < 0.8mm, and the depth t1 of the second oil storage hole 431 satisfies 0.001mm < t1 < 0.1mm.

When the second oil storage hole 431 is a non-circular hole, the diameter d1 refers to an equivalent diameter of the second oil storage hole 431, and the equivalent diameter refers to a diameter of the second oil storage hole 431 similar in shape and size to a sphere of the same volume.

The second oil reservoir hole 431 excessively large or excessively small as described above does not enhance the effect of oil reservoir, and the second oil reservoir hole 431 acts microscopically, and by defining the diameter d1 and the depth t1 of the second oil reservoir hole 431, the piston pin connection ring 412 is not excessively adversely affected while improving the friction problem between the contact end surface 42 and the inner surface 52 of the piston 50. Specifically, when d1 is smaller than 0.5mm, the second oil storage hole 431 occupies a smaller area on the contact end surface 42, which is easy to affect the collection effect of the second oil storage hole 431 on the lubricating oil, that is, the lubricating oil cannot smoothly flow into or out of the second oil storage hole 431, so that the friction pair cannot be lubricated well; when d1 is greater than 0.8mm, the second oil storage hole 431 occupies a larger area on the contact end surface 42, so that the loss of lubricating oil in the second oil storage hole 431 is easy to cause, and the amount of lubricating oil of the friction pair is reduced, so that a friction area cannot be well lubricated; therefore, the opening diameter d1 of the second oil storage hole 431 is set between 0.5mm and 0.8mm, which is favorable for better storing and lubricating the friction area of the second oil storage hole 431, so that the piston 50 and the connecting rod 40 have better lubricating effect, the friction between the piston 50 and the connecting rod 40 in the moving process is reduced, the service lives of the piston 50 and the connecting rod 40 are prolonged, the friction loss of the compressor provided with the piston pin 60 can be further reduced, meanwhile, the vibration noise is reduced, and the overall performance of the compressor is improved.

Specifically, the opening diameter d1 of the second oil storage hole 431 may have a specific value of 0.5mm, 0.55mm, 0.6mm, 0.65mm, 0.7mm, 0.75mm, 0.8mm, and the like.

In this embodiment, the shape and the size of the plurality of second oil storage holes 431 are the same for convenience of manufacturing. Specifically, the cross-sectional shape of the second oil storage hole 431 is a regular planar geometry. Such as circular, triangular, rectangular, star-shaped, etc.

In other embodiments, the shape and size of the plurality of second oil storage holes 431 may be different.

If multiple groups of different second oil storage holes 431 are arranged in different areas of the contact end surface 42, the shapes and sizes of the multiple second oil storage holes 431 in each area are different.

Specifically, the center distance n1 between any two adjacent second oil storage holes 431 satisfies: d1 is less than or equal to n1 is less than or equal to 10d1.

The too dense second oil storage holes 431 may not significantly improve the actual lubrication effect, in addition to the increase in the processing difficulty, and the relatively sparsely distributed plurality of second oil storage holes 431 may not sufficiently uniform lubrication between the contact end surface 42 and the inner surface 52 of the piston 50, and the relatively weak lubrication effect may be achieved, so that the plurality of second oil storage structures 43 between the friction pairs at uniformly spaced portions may be more convenient to process, and the lubrication effect may be relatively superior.

Specifically, n1 may have specific values d1, 2d1, 5d1, 7d1, 10d1, and so on.

In order to ensure the machining precision, the friction pair, that is, the relative movement of the plug pin connecting ring and the piston 50, is prevented from being influenced by the residual sharp edges, burrs and the like after machining, which is to swing around the piston pin 60, the second oil storage hole 431 is configured as a laser etched hole, an ultrasonic etched hole, an electrochemical etched hole or an electric spark machined hole.

As described above, the inner surface 52 of the piston pin connection ring 412, which contacts the piston 50, is a plane-to-plane friction pair, so as to reduce friction between the piston rod 40 and the piston 50, optimize lubrication therebetween, effectively reduce friction loss of the compressor, and improve energy efficiency ratio of the compressor.

Referring to fig. 23 to 28, the plug body 51 has an inner cavity 511, and a pin hole 512 penetrating both sides of the plug body 51 and communicating with the inner cavity 511, the pin hole 512 is provided for the piston pin 60 to pass through to fix the piston pin connection ring 412 of the connecting rod 40, the inner surface 52 of the inner cavity 511 is in direct contact with the contact end surface 42 of the piston pin connection ring 412, and the lubrication structure further includes a third oil storage structure 53 provided on at least a portion of the inner surface 52. The piston 50 is matched with the connecting rod 40, so that friction between the piston 50 and the piston pin connecting ring 412 of the connecting rod 40 can be reduced better, the lubrication effect between the piston 50 and the piston pin connecting ring 412 is optimized, and the energy efficiency ratio of the compressor is further improved.

Referring to fig. 23, in an embodiment of the present invention, the piston 50 includes a piston body 51, the piston body 51 has an inner cavity 511, and a pin hole 512 penetrating through both sides of the piston body 51 and communicating with the inner cavity 511, the pin hole 512 is used for passing a piston pin 60 therethrough to fix a piston pin connection ring 412 of the connecting rod 40, an inner surface 52 of the inner cavity 511 is in direct contact with a contact end surface 42 of the piston pin connection ring 412, and at least a portion of the inner surface 52 is provided with a third oil storage structure 53.

The piston 50 and the connecting rod 40 in the refrigeration apparatus are two important mechanical components that are commonly used in compressors for compressing gas into high pressure gas, thereby enabling the refrigeration cycle to operate. The piston 50 is a cylindrical member, typically made of metal, that can move up and down within the cylinder. In the compressor, a piston 50 is connected to a crankshaft 20 through a connecting rod 40, and when the crankshaft 20 rotates, the piston 50 moves up and down. During the up and down movement of the piston 50, the gas is compressed into a high pressure gas, which is then piped to other components in the refrigeration cycle. Connecting rod 40 is a component that connects piston 50 and crankshaft 20, and is typically made of steel. The crankshaft connecting ring 411 of the connecting rod 40 is connected with the crankshaft 20, the piston pin connecting ring 412 of the connecting rod 40 extends into the inner cavity 511 and is fixed by the piston pin 60, so that the relative motion of the piston pin connecting ring 412 of the connecting rod 40 and the piston 50 is swinging around the piston pin 60, the inner surface 52 of the piston 50 and the contact end surface 42 of the piston pin connecting ring 412 of the connecting rod 40 are matched friction pairs under the action of gravity, the inner surface 52 and the contact end surface 42 of the connecting rod 40 are in surface-to-surface contact, and in the continuous motion process of the connecting rod 40, the lubricating oil quantity is insufficient, after long-time operation, the piston 50 and a cylinder are always worn, and the service life of the piston is affected.

Friction of the contact end face 42 between the connecting rod 40 and the piston 50 is an important issue in internal combustion engines. In the related art, in order to reduce friction loss and wear, lubricating oil is generally used to reduce friction coefficient and improve lubricating performance. In addition, there is also a mode of coating high-hardness and high-wear-resistant materials to prolong the service life of the contact end face 42, the friction effect is not ideal due to the adoption of lubricating oil, and the cost of the material with higher hardness and higher wear resistance is relatively higher.

Specifically, the third oil storage structure 53 is disposed on the inner surface 52 near the pin hole 512, and the third oil storage structure 53 is near the pin hole 512. When the piston pin connecting ring 412 of the connecting rod 40 is arranged in the inner cavity 511 of the plug body 51, the piston pin 60 passes through the pin hole 512 to fix the piston pin connecting ring 412, the contact end surface 42 of the piston pin connecting ring 412 of the connecting rod 40 is directly contacted with the inner surface 52 due to gravity, the inner surface 52 is in surface-to-surface contact with the contact end surface 42 of the piston pin connecting ring 412 of the connecting rod 40, and after the lubricating oil quantity is insufficient and the piston pin connecting ring works for a long time; or in the initial operation process, the lubricating oil is insufficient, friction is easily generated by dry grinding, the service lives of the piston 50 and the connecting rod 40 are influenced, part of the lubricating oil is stored in the third oil storage structure 53, a layer of lubricating film is formed between the piston 50 and the connecting rod 40 in the relative movement process of the inner surface 52 and the inner surface 52 of the piston 50, and when in movement, the piston pin connecting ring 412 of the connecting rod 40 swings around the piston pin 60, so that the stored oil can lubricate, the friction loss of the piston 50 and the connecting rod is reduced, the dry grinding is prevented, and meanwhile, the oil can also take away heat, and the normal working temperature is kept. The third oil reservoir 53 is thus located adjacent the pin aperture 512 to reduce friction and wear.

Referring to fig. 25 to 28, the third oil storage structure 53 includes a plurality of third oil storage holes 531 provided on the inner surface 52. The third oil storage holes 531 increase the lubrication area, and ensure the strength of the inner surface 52, so as to avoid deformation and influence the quality of the piston 50.

In one embodiment, the plurality of third oil storage holes 531 are arranged in rows and columns, such as rectangular, circular, etc. rows and columns on a portion of the inner surface 52.

Further, the third oil storage holes 531 are arranged in an annular array on the inner surface 52 with the center of the pin hole 512 as the center.

Specifically, the annular array includes at least two rings of third oil storage holes 531. The plurality of third oil reservoir holes 531 are arranged in a single circle, a double circle, or the like on the inner surface 52.

Referring to FIG. 25, in one embodiment, a circle of the third oil storage holes 531 closest to the pin hole 512 has a radius R1 of 3 mm.ltoreq.R1.ltoreq.10 mm in the ring; the plurality of third oil storage holes 531 include a first array, and the first array is centered on the center of the pin hole 512 and is arranged on the inner surface 52 in an annular array with a radius R1, where R1 satisfies: r1 is more than or equal to 3mm and less than or equal to 10mm. On the one hand, the excessively large or small third oil reservoir 531 does not enhance the oil reservoir effect; on the other hand, the excessively large third oil reservoir hole 531 is manifested in a macroscopic smoothness or a decrease in flatness, which tends to increase wear between the inner surface 52 and the contact end surface 42 of the connecting rod 40, and may cause problems such as weakening of the strength of the piston 50.

In another embodiment, the radius difference of any adjacent two circles of the third oil storage holes 531 is 1mm < DeltaR < 6mm. The plurality of third oil storage holes 531 further includes a second array, which is centered on the center of the pin hole 512 and is arranged on the inner surface 52 in an annular array with a radius R2, where the relationship between R1 and R2 satisfies: deltaR=R2-R1 is more than or equal to 1mm and less than or equal to 6mm. The arrangement of the second array increases the lubrication area on one hand and ensures the lubrication effect; on the other hand, the expansion of the third oil reservoir hole 531 is avoided, resulting in a decrease in strength of the inner surface 52.

Referring to fig. 25, specifically, the spacing angle a of any adjacent two third oil storage holes 531 in the same array satisfies: a is more than or equal to 10 degrees and less than or equal to 30 degrees. The third oil storage holes 531 are arranged at intervals to increase the lubrication area on one hand, and on the other hand, the third oil storage holes 531 which are intersected with each other are prevented from affecting the oil storage capacity, so that the strength of the bearing area is weakened, and the friction loss is increased. The too dense third oil storage holes 531 may not significantly improve the actual lubrication effect, in addition to the increase in the processing difficulty, and the relative, too sparsely distributed third oil storage holes 531 may not sufficiently uniform lubrication between the inner surface 52 and the inner surface 52 of the piston 50, and the relative lubrication effect may be weak, so that the processing is more convenient and the lubrication effect may be relatively superior, as well as the uniformly spaced portions of the third oil storage structures 53 between the friction pairs.

In this embodiment, the shape and the size of the plurality of third oil storage holes 531 are the same for convenience of manufacturing. Specifically, the cross-sectional shape of the third oil storage hole 531 is a regular planar geometry. Such as circular, triangular, rectangular, star-shaped, etc.

In other embodiments, the shape and size of the plurality of third oil reservoir holes 531 may be different.

If multiple groups of different third oil storage holes 531 are arranged in different areas of the inner surface 52, the shapes and sizes of the multiple third oil storage holes 531 in each area are different.

Referring to fig. 26 to 28, the diameter d2 of the third oil storage hole 531 satisfies 0.5mm < d2 < 0.8mm, and the depth t2 and the diameter d2 of the third oil storage hole 531 satisfy the relationship: t2/d2 is more than or equal to 0.002 and less than or equal to 0.1.

The third oil reservoir hole 531, which is excessively large or small as described above, does not enhance the effect of oil reservoir, and the third oil reservoir hole 531 acts microscopically, and by defining the diameter d2 and the depth t2 of the third oil reservoir hole 531, the strength of the inner surface 52, friction pair are not adversely affected excessively while improving the problem of friction between the inner surface 52 and the contact end surface 42 of the wrist pin connecting ring 412 of the connecting rod 40. Specifically, when d2 is less than 0.5mm, the third oil storage hole 531 occupies a smaller area on the contact end surface 42, which easily affects the collection effect of the third oil storage hole 531 on the lubricating oil, that is, the lubricating oil cannot smoothly flow into or out of the third oil storage hole 531, so that the friction pair cannot be lubricated well; when d2 is greater than 0.8mm, the third oil storage hole 531 occupies a larger area on the contact end surface 42, which is easy to cause the loss of lubricating oil in the third oil storage hole 531, so as to reduce the amount of lubricating oil of the friction pair, and thus the friction area cannot be well lubricated; therefore, the opening diameter d2 of the third oil storage hole 531 is set between 0.5mm and 0.8mm, which is favorable for better storing and lubricating the friction area of the third oil storage hole 531, thereby having better lubricating effect between the piston 50 and the connecting rod 40, reducing the friction between the piston 50 and the connecting rod 40 in the moving process, prolonging the service lives of the piston 50 and the connecting rod 40, further reducing the friction loss of the compressor provided with the piston pin 60, reducing the vibration noise and improving the overall performance of the compressor.

Specifically, the opening diameter d2 of the third oil reservoir hole 531 may have a specific value of 0.5mm, 0.55mm, 0.6mm, 0.65mm, 0.7mm, 0.75mm, 0.8mm, or the like.

In summary, by adopting the plug body 51, the plug body 51 has an inner cavity 511, and a pin hole 512 penetrating through both sides of the piston body 51 and communicating with the inner cavity 511, the pin hole 512 is used for the piston pin 60 to pass through and fix the piston pin connection ring 412 of the connecting rod 40, the inner cavity 511 has an inner surface 52 directly contacting with the contact end surface 42 of the piston pin connection ring 412 of the connecting rod 40, and at least part of the inner surface 52 is provided with a third oil storage structure 53. The relative movement of the piston pin connection ring 412 of the connecting rod 40 and the piston 50 is a swing around the piston pin 60, the inner surface 52 of the piston 50 has an inner surface 52 in direct contact with the piston pin connection ring 412 of the connecting rod 40, and the inner surface 52 is in surface-to-surface contact with the contact end surface 42 of the connecting rod 40, so that during the continuous movement of the connecting rod 40, the amount of lubrication oil is insufficient, and during the continuous movement of the connecting rod 40, the piston 50 and the cylinder are often worn after a long period of operation, thereby affecting the service life thereof. By arranging the third oil storage structure 53 on at least part of the inner surface 52, part of lubricating oil is stored in the third oil storage structure 53, so that when the contact end surface 42 of the connecting rod 40 and the inner surface 52 of the piston 50 relatively move, the stored oil can lubricate a friction pair between the piston 50 and the connecting rod 40, the lubrication effect between the piston 50 and the connecting rod 40 is optimized, the friction loss of the compressor can be effectively reduced, and the energy efficiency ratio of the compressor is improved.

With reference to fig. 29 and 30, a description will be given below of how the fourth friction pair is specifically provided, and how the lubrication structure is provided.

Referring to fig. 29 and 30, the wrist pin 60 includes a pin body 61, an outer surface of the pin body 61 has a sleeved area 62, the wrist pin connection ring 412 of the connecting rod 40 is sleeved on the sleeved area 62, the fourth friction pair is provided with a lubrication structure, and the lubrication structure includes a fourth oil storage structure provided on the sleeved area 62.

The wrist pin 60 is a key connecting member of the reciprocating compressor 100 connecting the crankshaft 20 and the piston 50, and the wrist pin 60 is tied to the piston 50 and engaged with the wrist pin connecting ring 412 of the connecting rod 40. After the reciprocating compressor 100 is started, the crank shaft 20 drives the piston pin 60 and the piston 50 to reciprocate. In order to reduce friction loss and ensure operational reliability, lubrication is required between the moving friction pair, and the movement between the piston pin connecting ring 412 of the connecting rod 40 and the piston pin 60 is of a wobble type and cannot be directly supplied with oil, so that the friction pair is mostly in a rough contact stage during the whole operation process, and considerable friction idle work is easily generated between the pin hole 512 of the connecting rod 40 and the piston pin 60, and abrasion is deteriorated.

The piston pin 60 is a key connecting component for connecting the crankshaft 20 and the piston 50 in the reciprocating compressor 100, the piston pin 60 is bound with the piston 50 through a positioning pin hole 611, and a sleeved area 62 matched with the connecting rod 40 is arranged on the outer surface, so that after the reciprocating compressor 100 is started, the piston pin 60 and the piston 50 reciprocate under the driving of the crankshaft 20, wherein in order to reduce friction loss and ensure the reliability of operation, the fourth oil storage structure is a plurality of fourth oil storage holes 63 distributed in the sleeved area 62, and the fourth oil storage holes 63 are distributed along the circumferential direction and the axial direction of the pin body 61. Through establish regional 62 setting up a plurality of fourth oil storage holes 63 at the cover, utilize the function of the storage lubricating oil of fourth oil storage hole 63, at the operation in-process, lubricating oil can more effectively lubricate the cover and establish regional 62, and then strengthen the lubrication between connecting rod 40 and the piston pin 60, reduce the friction of piston pin 60 and connecting rod 40 in the motion process, thereby can prolong the life of piston pin 60 and connecting rod 40, also can further reduce the friction loss of the compressor that is equipped with this piston pin 60 from this, reduce vibration noise simultaneously, promote compressor wholeness ability.

In addition, the fourth oil storage hole 63 is formed in the pin body 61, so that the implementation process is simple, the universality is high, and mass production and popularization are facilitated.

In the technical scheme of the invention, the outer surface of the pin body 61 of the piston pin 60 is provided with the sleeved region 62 for the connecting rod 40 to rotate and sleeved, the sleeved region 62 is provided with a plurality of fourth oil storage holes 63, and by utilizing the function of the fourth oil storage holes 63 for storing lubricating oil, the lubricating oil can more effectively lubricate the sleeved region 62 in the running process, so that the lubrication between the connecting rod 40 and the piston pin 60 is enhanced, the friction between the piston pin 60 and the connecting rod 40 in the running process is reduced, and the service lives of the piston pin 60 and the connecting rod 40 are prolonged, so that the friction loss of a compressor provided with the piston pin 60 is further reduced, meanwhile, the vibration noise is reduced, and the integral performance of the compressor is improved.

Referring to fig. 29 and 30, in an embodiment, the fourth oil storage holes 63 are arranged along the circumferential direction and the axial direction of the pin body 61, and it can be appreciated that, according to the size of the sleeved area 62, the fourth oil storage holes 63 are uniformly distributed on the outer surface of the pin body 61, which can be arranged in a single row, and multiple rows and multiple columns, so as to be beneficial to collecting lubricating oil in multiple directions, and effectively perform better lubrication on the sleeved area 62, enhance lubrication between the connecting rod 40 and the piston pin 60, and thus effectively reduce the service life reduction of the piston pin 60 and the connecting rod 40 caused by friction. However, in other embodiments, the plurality of fourth oil storage holes 63 may be arranged in a radial manner, or the plurality of fourth oil storage holes 63 may be irregularly arranged in the sleeved area 62, which is not limited herein.

Referring to fig. 29 and 30, in an embodiment, at least two rows of the fourth oil storage holes 63 are offset; and/or, at least two rows of the fourth oil storage holes 63 are arranged in a staggered manner, so that each fourth oil storage hole 63 can store lubricating oil well and lubricate the sleeved area 62, thereby having good lubrication effect between the piston pin 60 and the connecting rod 40.

Referring to fig. 30 in combination, in an embodiment, the opening diameter of the fourth oil storage hole 63 is d3, d3 is greater than or equal to 0.5mm and less than or equal to 0.8mm, where the cross-sectional shape of the fourth oil storage hole 63 may be a regular shape or an irregular shape, and the opening diameter is the equivalent diameter of the corresponding shape.

Specifically, when d3 is less than 0.5mm, the fourth oil storage hole 63 occupies a small area on the outer wall surface of the pin body 61, which easily affects the collection effect of the fourth oil storage hole 63 on the lubricating oil, that is, the lubricating oil cannot smoothly flow into or out of the fourth oil storage hole 63, so that the sliding sleeve region 62 cannot be well lubricated, and friction idle work is generated between the piston pin 60 and the connecting rod 40, and wear is deteriorated; when d3 is greater than 0.8mm, the fourth oil storage hole 63 occupies a larger area on the outer wall surface of the pin body 61, which is easy to cause the loss of lubricating oil in the fourth oil storage hole 63, thereby reducing the amount of lubricating oil in the sleeved region 62, failing to lubricate the sleeved region 62 well, causing friction idle work between the piston pin 60 and the connecting rod 40 and causing deterioration of wear; therefore, the opening diameter d3 of the fourth oil storage hole 63 is set between 0.5mm and 0.8mm, which is favorable for better storing and lubricating the sleeved area 62 of each fourth oil storage hole 63, so that the piston pin 60 and the connecting rod 40 have better lubricating effect, the friction between the piston pin 60 and the connecting rod 40 in the moving process is reduced, the service lives of the piston pin 60 and the connecting rod 40 are prolonged, the friction loss of the compressor provided with the piston pin 60 can be further reduced, the vibration noise is reduced, and the overall performance of the compressor is improved.

Specifically, the opening diameter d3 of the fourth oil reservoir hole 63 may have a specific value of 0.5mm, 0.55mm, 0.6mm, 0.65mm, 0.7mm, 0.75mm, 0.8mm, and so on.

Referring to fig. 30, in an embodiment, the relationship between the distance n2 between two centers corresponding to two fourth oil storage holes 63 in two adjacent columns and the opening diameter d3 of the fourth oil storage holes 63 satisfies: d3.ltoreq.n2.ltoreq.10d3, so that the fourth oil storage holes 63 are independent of each other and do not overlap with each other, and the opening diameter d3 of each fourth oil storage hole 63 is ensured to be in a certain size range, for example, d3 is more than or equal to 0.5mm and less than or equal to 0.8mm, so that the fourth oil storage holes 63 store lubricating oil well and lubricate the sleeved area 62, thereby ensuring good lubrication effect between the piston pin 60 and the connecting rod 40.

The specific values of the distances n2 between the two centers corresponding to the two adjacent rows of the fourth oil storage holes 63 may be d3, 2d3, 3d3, 4d3, 5d3, 6d3, 7d3, 8d3, 9d3, and 10d3, and when the plurality of fourth oil storage holes 63 are arranged in multiple rows, the distances between the two centers corresponding to the two adjacent rows of the fourth oil storage holes 63 may be equal or unequal, which is not limited herein.

Referring to fig. 30, in an embodiment, the relationship between the distance n3 between two centers corresponding to two fourth oil storage holes 63 in two adjacent rows and the opening diameter d3 of the fourth oil storage holes 63 satisfies: d3 is less than or equal to n3 is less than or equal to 10d3. By such arrangement, the fourth oil storage holes 63 are independent of each other and do not overlap with each other, so that the opening diameter d3 of each fourth oil storage hole 63 is ensured to be within a certain size range, for example, d3 is greater than or equal to 0.5mm and less than or equal to 0.8mm, so that the fourth oil storage holes 63 store lubricating oil well and lubricate the sleeved area 62, thereby providing a good lubrication effect between the piston pin 60 and the connecting rod 40.

The specific values of the distances n3 between the two centers corresponding to the two adjacent rows of the fourth oil storage holes 63 may be d3, 2d3, 3d3, 4d3, 5d3, 6d3, 7d3, 8d3, 9d3, and 10d3, and when the plurality of fourth oil storage holes 63 are arranged in a plurality of rows, the distances between the two centers corresponding to the two adjacent rows of the fourth oil storage holes 63 may be equal or unequal, which is not limited herein.

Alternatively, in an embodiment, in the radial direction of the pin body 61, the groove depth of the fourth oil storage hole 63 is t3, where t3 is greater than or equal to 0.001mm and less than or equal to 0.1mm, so as to ensure the oil collecting effect of the fourth oil storage hole 63.

Specifically, when t3 is less than 0.001mm, the fourth oil storage hole 63 occupies a small volume on the pin body 61, which easily affects the collection effect of the fourth oil storage hole 63 on the lubricating oil, i.e., a certain amount of lubricating oil cannot be stored, the amount of lubricating oil in the sleeved area 62 is reduced, the sleeved area 62 cannot be well lubricated, and friction idle work is generated between the piston pin 60 and the connecting rod 40, and wear is deteriorated; when t3 is greater than 0.1mm, the fourth oil storage hole 63 occupies a larger volume on the pin body 61, which is easy to cause the loss of lubricating oil in the fourth oil storage hole 63, thereby reducing the amount of lubricating oil in the sleeved area 62, so that the sleeved area 62 cannot be well lubricated, the piston pin 60 and the connecting rod 40 generate friction idle work, abrasion is deteriorated, and meanwhile, the structural strength of the pin body 61 is easy to be influenced, and the connection reliability of the pin body 61 and the connecting rod 40 is easy to be influenced; therefore, the groove depth t3 of the fourth oil storage hole 63 is set between 0.001mm and 0.1mm, which is favorable for ensuring the oil collecting effect of the fourth oil storage hole 63, further ensuring better lubrication effect between the piston pin 60 and the connecting rod 40, reducing friction between the piston pin 60 and the connecting rod 40 in the moving process, prolonging the service lives of the piston pin 60 and the connecting rod 40, simultaneously, being favorable for improving the structural strength of the pin body 61, ensuring the connection reliability of the pin body 61 and the connecting rod 40, further reducing friction loss of the compressor provided with the piston pin 60, reducing vibration noise and improving the integral performance of the compressor.

Specifically, the groove depth t3 of the fourth oil storage hole 63 may have a specific value of 0.001mm, 0.005mm, 0.01mm, 0.015mm, 0.02mm, 0.025mm, 0.03mm, 0.035mm, 0.04mm, 0.045mm, 0.05mm, 0.055mm, 0.06mm, 0.065mm, 0.07mm, 0.075mm, 0.08mm, 0.085mm, 0.09mm, 0.095mm, 0.1mm, and the like.

Referring to fig. 29, in an embodiment, the connecting rod 40 has a mating section contacting with the sleeving area 62, in the axial direction of the pin body 61, the height of the sleeving area 62 is greater than or equal to the height of the mating section, where the height of the sleeving area 62 is G, and the specific value needs to be greater than or equal to the height of the mating section of the connecting rod 40, so as to ensure the effective contact area between the sleeving area 62 and the mating section, effectively avoid the lack of lubrication in place caused by the condition that the fourth oil storage hole 63 is not arranged between the sleeving area 62 and the mating section, be beneficial to reducing friction between the connecting rod 40 and the piston pin 60 in the moving process, prolonging the service lives of the piston pin 60 and the connecting rod 40, further reducing friction loss of the compressor provided with the piston pin 60, reducing vibration noise, and improving the overall performance of the compressor.

Alternatively, in an embodiment, the cross-sectional shape of the fourth oil storage hole 63 may be a circle, triangle, rectangle or star, or may be an irregular shape, so long as the opening diameter d3 is ensured to be between 0.5mm and 0.8mm, and the groove depth t3 is ensured to be between 0.001mm and 0.1 mm. The preferred embodiment of the present application adopts a circular cross-section shape, which is convenient for processing.

Alternatively, in an embodiment, the fourth oil storage hole 63 is configured as a laser etched hole, an ultrasonic etched hole, an electrochemical etched hole, or an electric spark machined hole, that is, the fourth oil storage hole 63 may be formed by any one of laser, ultrasonic, electrochemical etching, and electric spark machining.

The piston pin 60 is fixedly connected with the piston 50 through a spring pin, wherein, according to the connection position of the piston pin 60 and the piston 50, referring to fig. 29 and 30, in an embodiment, the positioning pin hole 611 is configured as a first pin hole 612, and the first pin hole 612 is provided at an end of the pin body 61 and extends along the axial direction of the pin body 61; and/or, the positioning pin hole 611 is configured as a second pin hole 613, the second pin hole 613 is provided at an end of the pin body 61, and is disposed along a radial direction of the pin body 61 and penetrates the pin body 61, in other words, according to a connection position of the piston pin 60 and the piston 50, the piston pin 60 may be connected with the piston 50 through any one of the first pin hole 612 and the second pin hole 613, so that the connecting rod 40 forms a rotational connection pair with the piston 50 through the piston pin 60, and further drives the piston pin 60 and the piston 50 to reciprocate through the connecting rod 40.

Further, the piston pin connection ring 412 is provided with an inner hole wall sleeved on the piston pin 60, and the lubrication structure further comprises a fifth oil storage structure arranged on the inner hole wall. The piston pin connecting ring 412 of the connecting rod 40 is provided with an inner hole wall sleeved with the piston pin 60, and the fifth oil storage structure comprises a plurality of fifth oil storage holes arranged on the inner hole wall. The hole wall of the inner hole is provided with a fifth oil storage structure, and it can be understood that the hole wall of the inner hole is a matching section on the connecting rod 40, which is contacted with the sleeved region 62 of the piston pin 60, wherein the oil storage structure is arranged to play a role in storing lubricating oil, so that lubricating oil is provided for lubricating the piston pin connecting ring 412 and the piston pin 60 in the operation process, the lubrication between the connecting rod 40 and the piston pin 60 is enhanced, the friction between the piston pin 60 and the connecting rod 40 in the movement process is reduced, and the service lives of the piston pin 60 and the connecting rod 40 can be prolonged, so that the friction loss of a compressor provided with the piston pin 60 can be further reduced, the vibration noise is reduced, and the integral performance of the compressor is improved.

Specifically, in an embodiment, the fifth oil storage structure may be configured as a plurality of fifth oil storage holes, where the plurality of fifth oil storage holes are disposed on the wall of the inner hole, and the relevant layout rules, layout parameters and processing manners may be set with reference to the relevant embodiments of the fourth oil storage hole 63 on the piston pin 60. In other embodiments, the oil storage structure may be configured as an annular oil sump 162, and may also be configured as a grating-type oil sump 162.

The present invention also proposes a refrigeration device, which includes a motor, a crank case 10, and a piston rod group, where the piston rod group includes a piston 50, a piston pin 60, a connecting rod 40, etc., and the specific structures of the piston 50, the connecting rod 40, the crank case 10, a rotor, etc. refer to the above embodiments, and since the refrigeration device adopts all the technical solutions of all the embodiments, at least has all the advantages brought by the technical solutions of the embodiments, which are not described in detail herein, the crank connecting ring 411 of the connecting rod 40 is connected with the crank shaft 20 of the crank case 10, the piston pin connecting ring 412 of the connecting rod 40 is disposed in the cavity 511 of the piston 50, the piston pin 60 passes through the pin hole 512 of the piston 50 to fix the piston pin connecting ring 412 of the connecting rod 40 and the piston 50, and the connecting rod 40 drives the piston 50 to reciprocate in the cylinder under the driving of the crank shaft 20. The reciprocating compressor 100 according to the present invention has advantages of high efficiency, low vibration noise, high reliability, etc.

The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all equivalent structural changes made by the description of the present invention and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the invention.

Claims

1. A reciprocating compressor, comprising:

a crankcase including a crankshaft seat and a cylinder seat;

the piston is movably arranged in the cylinder seat;

2. The reciprocating compressor of claim 1, wherein the first friction pair is provided with the lubrication structure, the lubrication structure is configured as a self-lubricating gasket, the crankshaft seat is provided with a crankshaft hole, the crankshaft is provided with a shaft shoulder, the shaft shoulder is provided with a crankshaft thrust surface, the crankshaft penetrates through the crankshaft hole, and the self-lubricating gasket is arranged at the edge of the crankshaft hole and is abutted with the crankshaft thrust surface.

3. The reciprocating compressor of claim 2, wherein the crankcase is provided with a mounting step at an edge of the crank hole, and the self-lubricating gasket is sleeved on the mounting step and at least partially protrudes out of the mounting step.

4. The reciprocating compressor of claim 3, wherein the shoulder is provided with a protrusion, the crankshaft thrust surface is formed on a surface of the protrusion facing the mounting step, the mounting step includes a first step and a second step having a ring shape, and the self-lubricating gasket is sleeved on the first step and clamped between the protrusion and the second step.

5. The reciprocating compressor of claim 1, wherein said crank carrier has opposite top and bottom surfaces, said top surface having an axial bore for mounting said crankshaft, a portion of said axial bore protruding from said bottom surface to form a crankshaft segment;

6. The reciprocating compressor of claim 5, wherein the first oil storage structure includes a plurality of first oil storage holes provided at the upper surface.

7. The reciprocating compressor of claim 6, wherein the rotor core further comprises a third core segment, the second core segment is located between the first core segment and the third core segment, the first core segment, the second core segment and the third core segment are all stacked with a plurality of core laminations, the first oil storage hole penetrates through the second core segment along the axial direction, and one side of the third core segment close to the second core segment closes the first oil storage hole.

8. The reciprocating compressor of claim 5, wherein the lubrication structure further comprises an oil groove provided on a lower end surface of the crank tube section, the oil groove penetrating the crank tube section in a radial direction of the crank tube section.

9. The reciprocating compressor of claim 8, wherein the lower end surface is divided into a first region distant from the cylinder block and a second region close to the cylinder block along a reference line, and the oil groove is provided in the first region, wherein the reference line is an auxiliary line passing through a center of the lower end surface and perpendicular to an axis of the cylinder block.

10. The reciprocating compressor of claim 1, wherein the connecting rod comprises a rod body, a crank connecting ring at one end of the rod body, and a piston pin connecting ring at the other end of the rod body, the piston pin connecting ring having a contact end surface in direct contact with an inner surface of the piston, the third friction pair being provided with a lubrication structure including a second oil storage structure provided on at least a portion of the contact end surface.

11. The reciprocating compressor of claim 10, wherein the second oil storage structure includes a plurality of second oil storage holes provided on the contact end surface.

12. The reciprocating compressor of claim 11, wherein the plurality of second oil storage holes are arranged in an annular array on the contact end surface centering on a center of the piston pin connection ring.

13. The reciprocating compressor of claim 10, wherein the plug body has an inner cavity, and a pin hole penetrating both sides of the piston body and communicating with the inner cavity, the pin hole being passed through by a piston pin to fix a piston pin connection ring of the connecting rod, an inner surface of the inner cavity being in direct contact with a contact end surface of the piston pin connection ring, the lubrication structure further comprising a third oil storage structure provided on at least a portion of the inner surface.

14. The reciprocating compressor of claim 13, wherein the third oil storage structure includes a plurality of third oil storage holes provided on the inner surface.

15. The reciprocating compressor of claim 14, wherein a plurality of the third oil storage holes are arranged in an annular array centered on a center of the pin hole on the inner surface.

16. The reciprocating compressor of claim 1, wherein the piston pin comprises a pin body, an outer surface of the pin body has a sleeved region, a piston pin connection ring of the connecting rod is sleeved on the sleeved region, the fourth friction pair is provided with a lubrication structure, and the lubrication structure comprises a fourth oil storage structure arranged on the sleeved region.

17. The reciprocating compressor of claim 16, wherein the fourth oil storage structure is a plurality of fourth oil storage holes arranged in the sheathing region, the plurality of fourth oil storage holes being arranged in an array in a circumferential direction and an axial direction of the pin body.

18. The reciprocating compressor of claim 16, wherein said piston pin connection ring is provided with an inner bore wall surrounding said piston pin, said lubrication structure further comprising a fifth oil reservoir provided in said inner bore wall.

19. A refrigeration apparatus comprising a reciprocating compressor as claimed in any one of claims 1 to 17.