WO2019227842A1

WO2019227842A1 - Rotary compressor, gas compression system, refrigeration system and heat pump system

Info

Publication number: WO2019227842A1
Application number: PCT/CN2018/112737
Authority: WO
Inventors: 李盖敏; 李华明
Original assignee: 广东美芝精密制造有限公司
Priority date: 2018-06-01
Filing date: 2018-10-30
Publication date: 2019-12-05

Abstract

Disclosed are a rotary compressor, a gas compression system, a refrigeration system and a heat pump system, wherein the rotary compressor comprises: a cylinder (10), a cam mechanism (30), a sliding vane (40) and a swinging block (50). A cam portion of the cam mechanism (30) is rotatably arranged in the cylinder (10), the cylinder (10) is provided with a sliding vane groove (13), the sliding vane (40) is mounted in the sliding vane groove (13), the swinging block (50) and the front end of sliding vane (40) are hinged around a first axis, the first axis is parallel to the axis of the cylinder (10), and the swinging block (50) presses against the outer perimeter of the cam portion.

Description

Rotary compressors, gas compression systems, refrigeration systems and heat pump systems

Cross-reference to related applications

This application requires the Chinese patent application number "201810557430.1" and the name of the invention filed by Guangdong Meizhi Precision Manufacturing Co., Ltd. on June 1, 2018, with the invention name "rotary compressor, gas compression system, refrigeration system and heat pump system" The priority of the Chinese patent application number "201820852311.4" is "rotary compressor, gas compression system, refrigeration system and heat pump system", the entire contents of which are incorporated herein by reference.

Technical field

The present disclosure belongs to the technical field of compressor manufacturing, and in particular, relates to a rotary compressor, a gas compression system having the rotary compressor, a refrigeration system having the rotary compressor, and a heat pump having the rotary compressor. system.

Background technique

In the compressor mechanism, the friction loss between the tip of the sliding vane and the outer circular surface of the piston is large. In order to reduce this friction loss, in the related art, a needle is installed at the tip of the sliding plate. The purpose of this structure is to change the sliding friction between the piston and the sliding plate into rolling friction, and the friction power consumption is effectively reduced. However, the needle structure has extremely high requirements for reliability. As the contact stress between the needle and the piston increases sharply, the wear resistance of the needle material is challenged, and the needle structure is prone to needle roller failure. The risk that once the needle roller fails to roll, the needle will wear abruptly until the compressor jams and fails, and there is room for improvement.

Summary of the Invention

The present disclosure aims to solve at least one of the technical problems existing in the prior art. For this reason, the present disclosure proposes a rotary compressor having a small frictional power consumption of a friction pair of a sliding cam portion of the rotary compressor.

A rotary compressor according to an embodiment of the present disclosure includes an air cylinder, a cam mechanism, a sliding vane, and a rocker block. A cam portion of the cam mechanism is rotatably disposed in the air cylinder, and the air cylinder is provided with a sliding vane groove. The sliding plate is installed in the sliding plate groove, the rocker is hinged with the tip of the sliding plate about a first axis, the first axis is parallel to the axis of the cylinder, and the rocker presses against the The outer surface of the cam portion.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding blade and the outer surface of the cam portion is greatly improved, the lubrication state between the sliding pair and the friction pair of the cam portion is greatly improved, and the sliding cam is greatly reduced. The frictional power consumption between the friction pairs also greatly improves its reliability, and the structure of the rocker is simple, the cost is low, and the effect is good.

According to a rotary compressor according to an embodiment of the present disclosure, one of the tip of the sliding plate and the rocker is provided with an arc-shaped opening groove, and the other includes an arc-shaped hinge surface, and the hinge surface and the hinge Open slot articulated.

According to a rotary compressor according to an embodiment of the present disclosure, the opening groove is provided at the front end of the sliding plate and is open to the compression cavity of the cylinder. The sliding plate is further provided with a guide groove, and the guide groove and the The open ends of the open slot are connected, and two side walls of the guide slot extend from one end connected to the side wall of the open slot to the other end in a direction away from each other; the rocker includes a rocker connecting portion and In the hinged surface, a width of the rocker block connection portion is smaller than a diameter of the hinged surface.

According to a rotary compressor according to an embodiment of the present disclosure, a tip end of the sliding plate includes a sliding plate connection portion and the hinge surface, and a width of the sliding plate connection portion is smaller than a diameter of the hinge surface.

According to a rotary compressor according to an embodiment of the present disclosure, the arc of the open groove is greater than 180 °, and the arc of the hinge surface is greater than 180 °.

According to a rotary compressor according to an embodiment of the present disclosure, the rocker block has a pressing surface for pressing the cam portion, the pressing surface is arc-shaped, and at least a part of the pressing surface and the The outer surface of the cam portion is inscribed.

According to a rotary compressor according to an embodiment of the present disclosure, the rocker has a pressing surface for pressing the cam portion, and the pressing surface is a flat surface.

According to a rotary compressor of an embodiment of the present disclosure, the rocker is made of one of steel, cast iron, plastic, alloy, and ceramic.

The present disclosure also proposes a gas compression system having the rotary compressor according to any one of the above.

The present disclosure also proposes a refrigeration system having the rotary compressor according to any one of the above.

The present disclosure also proposes a heat pump system having the rotary compressor according to any one of the above.

The gas compression system, the refrigeration system, and the heat pump system have the same advantages as the above-mentioned rotary compressor over the prior art, and will not be repeated here.

Additional aspects and advantages of the present disclosure will be given in part in the following description, and part of them will become apparent from the following description, or be learned through the practice of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and / or additional aspects and advantages of the present disclosure will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

1 is a schematic structural diagram of a rotary compressor according to an embodiment of the present disclosure;

2 is an end view of a rotary compressor at a cylinder according to an embodiment of the present disclosure;

FIG. 3 is a partially enlarged view at A in FIG. 2; FIG.

4-7 are schematic structural diagrams of a rocker according to an embodiment of the present disclosure;

8-9 are schematic structural diagrams of a sliding sheet according to an embodiment of the present disclosure;

10 to 13 are schematic structural diagrams of cooperation between a sliding plate and a rocker according to an embodiment of the present disclosure;

14 is a cross-sectional view of a rotary compressor at a cylinder according to an embodiment of the present disclosure;

15 is a sectional view at X-X in FIG. 14;

16 is a cross-sectional view of a rotary compressor at a cylinder according to another embodiment of the present disclosure;

17 is a cross-sectional view of a rotary compressor at a cylinder according to still another embodiment of the present disclosure;

18 is a cross-sectional view of a rotary compressor at a cylinder according to still another embodiment of the present disclosure;

FIG. 19 is a partially enlarged view at B in FIG. 18; FIG.

20-21 are schematic structural diagrams of a sliding sheet according to an embodiment of the present disclosure;

22 to 23 are schematic structural diagrams of a secondary bearing according to an embodiment of the present disclosure;

24 to 33 are schematic diagrams of a connection process of a rocker block according to an embodiment of the present disclosure;

34 is a graph showing a relationship between COP and (r1-r2) / r2 of a rotary compressor according to an embodiment of the present disclosure;

FIG. 35 is a graph showing a relationship between COP and t2 / t1 of a rotary compressor according to an embodiment of the present disclosure.

Reference signs:

Cylinder 10, the projection of the exhaust hole of the main bearing on the end face of the cylinder 11, the notch 12, the sliding blade groove 13,

Main bearing 21, auxiliary bearing 22, oil supply channel 23,

Cam mechanism 30, crankshaft 31, piston 32, keyway 33, key 34, boss 35,

Slide 40, opening groove 41, guide groove 42, guide groove 43, slide plate connection portion 46,

Rocker 50, first sub rocker 51, hinge surface 52, first welding surface 53, second sub rocker 54, pressing surface 55, rocker connecting portion 56, second welding surface 57,

The rotor 61, the stator 62, the casing 71, the upper case 72, and the lower case 73.

Detailed ways

Hereinafter, embodiments of the present disclosure will be described in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present disclosure, and should not be construed as limiting the present disclosure.

Example one

The following describes a rotary compressor according to an embodiment of the present disclosure with reference to FIGS. 1 to 35. The rotary compressor includes a casing, a stator 62, a rotor 61, a cam mechanism 30, a cylinder 10, a main bearing 21, a sub-bearing 22, and a slide. Tablet 40 and shaking block 50.

Among them, referring to FIG. 1, the casing may include a casing 71, an upper casing 72, a lower casing 73, a stator 62, a rotor 61, a cam mechanism 30, a cylinder 10, a main bearing 21, a sub-bearing 22, a sliding plate 40 and a rocker. The block 50 may be installed in a cabinet.

The rotor 61 is connected to the cam mechanism 30 for driving the cam mechanism 30 to rotate. The main bearing 21 and the auxiliary bearing 22 are respectively provided on the upper and lower surfaces of the cylinder 10. A compression chamber is defined between the cylinder 10, the main bearing 21 and the auxiliary bearing 22 The cam portion of the cam mechanism 30 is rotatably provided in the cylinder 10.

As shown in FIG. 2, in an embodiment in which the cam mechanism 30 includes a crankshaft 31 and a piston 32, the piston 32 is sleeved outside the eccentric portion of the crankshaft 31. The cam portion of the cam mechanism 30 includes a piston 32, and the piston 32 is rotatably provided at In the cylinder 10, the piston 32 is rotatably fitted in the compression chamber under the driving of the crankshaft 31. Of course, the cam mechanism 30 may be integrated.

As shown in FIG. 2, the cylinder 10 is provided with a sliding blade groove 13, and the sliding blade 40 is installed in the sliding blade groove 13. The rocker 50 and the tip of the sliding blade 40 are hinged about a first axis, and the first axis is parallel to the axis of the cylinder 10. The rocking block 50 presses against the outer circular surface of the cam portion. During the operation of the rotary compressor, the rocking block 50 and the outer circular surface of the cam portion slide to cooperate to form a sliding friction pair.

It should be noted that the leading end of the sliding plate 40 refers to the end of the sliding plate 40 that extends into the compression chamber and is close to the outer circular surface of the cam portion (piston 32) of the cam mechanism 30. One end of the rocker block 50 abuts with the front end of the slider 40, and the other end of the rocker block 50 abuts against the outer circular surface of the cam portion (piston 32) of the cam mechanism 30. The rocker 50 has a pressing surface 55 that presses the outer circular surface of the cam portion. The width of the pressing surface 55 in the circumferential direction of the outer circular surface of the cam portion is larger than the width of the leading end of the slider 40.

During the operation of the rotary compressor, the sliding plate 40 reciprocates along the sliding plate groove 13. The rocker 50 is always pressed against the outer surface of the cam portion (piston 32). The rocker 50 is opposed to the sliding plate 40 about the first axis. The rocker 50 swings in a direction parallel to the end face of the cylinder 10.

It can be understood that by providing a rocker 50 between the sliding plate 40 and the cam portion, the contact stress between the sliding plate 40 and the cam portion can be greatly reduced, and the lubrication state is changed from the original boundary lubrication to the fluid dynamic pressure lubrication. Friction power consumption is effectively reduced, and the amount of cold leakage between the sliding plate 40 and the cam portion is also reduced.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pairs of the cam portion of the blade 40 also greatly improves its reliability, and the rocker 50 has a simple structure, low cost and good effect.

Example two

A self-lubricating coating is provided on at least one surface of the friction pair formed by the slider 40 and the rocker block 50 and the friction pair formed by the rocker block 50 and the outer circular surface of the cam portion. For example, the surface of the slider 40 that cooperates with the rocker 50 may be provided with a self-lubricating coating, or the surface of the slider 50 that cooperates with the slide 40 may be provided with a self-lubricating coating, or the outer surface of the slider 50 and the cam portion The surface of the round surface is provided with a self-lubricating coating, or the outer surface of the cam portion is provided with a self-lubricating coating. Among the four surfaces, one of the surfaces may be a self-lubricating coating, or two of the surfaces may be self-lubricating. Coatings, or three of them with a self-lubricating coating, or four of them with a self-lubricating coating. In a specific embodiment, both ends of the rocker 50 are provided with a self-lubricating coating, which can reduce the process of applying the self-lubricating coating and simplify the processing process.

The material of the self-lubricating coating is at least one of Teflon, molybdenum disulfide, tungsten disulfide, polyimide, and graphite. The process of the self-lubricating coating is at least one of spray coating, dipping, deposition, electroplating, and coating.

The self-lubricating coating can improve the inadequate lubrication between the friction pairs, reduce frictional power consumption, and enhance the initial running-in effect of the friction pairs, greatly reducing the failure rate of the initial operation of the rotary compressor.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pairs of the cam portion of the blade 40 also greatly improves its reliability, and the self-lubricating coating is provided, which not only reduces the frictional power consumption of the rotary compressor, but also helps reduce the rotary compression. The initial failure rate of the machine, and the structure of the rocker block 50 is simple, the cost is low, and the effect is good.

Example three

The following describes a rotary compressor according to an embodiment of the present disclosure with reference to FIGS. 1 to 4, 6, 8 to 10, 12, and 14 to 35. The rotary compressor includes a casing, a stator 62, and a rotor. 61. The cam mechanism 30, the cylinder 10, the main bearing 21, the auxiliary bearing 22, the sliding plate 40 and the rocker 50.

As shown in FIG. 2 to FIG. 4, the cylinder 10 is provided with a sliding blade groove 13, and the sliding blade 40 is installed in the sliding blade groove 13. The rocker 50 and the leading end of the sliding blade 40 are hinged about a first axis. The axis is parallel. The rocker 50 has a pressing surface 55 that presses against the outer circular surface of the cam portion, and the pressing surface 55 is inscribed with the outer circular surface of the cam portion. During the operation of the rotary compressor, The pressing surface 55 and the outer circular surface of the cam portion are slidingly fitted to form a sliding friction pair.

It can be understood that by providing a rocker 50 between the sliding plate 40 and the cam portion, the contact stress between the sliding plate 40 and the cam portion can be greatly reduced. The contact between the sliding plate 40 and the cam portion is cut away from the original The contact becomes an inscribed contact, and the lubrication state is changed from the original boundary lubrication to the fluid dynamic pressure lubrication, the friction power consumption is effectively reduced, and the leakage of cold between the sliding plate 40 and the cam portion is also reduced.

Since the pressing surface 55 of the rocker block 50 is arc-shaped, and the pressing surface 55 is inscribed with the outer circular surface of the cam portion, in this way, it is easy to form between the pressing surface 55 of the rocker 50 and the outer circular surface of the cam portion. The oil film can maintain sufficient oil film thickness, which can effectively reduce the contact area between the rocker 50 and the outer circular surface of the cam portion, thereby effectively reducing the friction loss of the friction pair.

The pressing surface 55 is an arc surface with a radius r1, and the radius of the outer circular surface of the cam portion is r2.

The inventors have found through a large number of experiments that, for the rotary compressor of the embodiment of the present disclosure, when satisfying: 0.01% ≦ (r1-r2) / r2, between the pressing surface 55 of the rocker 50 and the outer circular surface of the cam portion It is easy to form an oil film, and a sufficient oil film thickness can be maintained, so that the contact area between the rocker 50 and the outer circular surface of the cam portion can be effectively reduced, thereby further reducing the friction loss of the friction pair.

The inventor found through a large number of experiments that the relationship curve between the COP of the rotary compressor and (r1-r2) / r2 is shown in FIG. 34. When (r1-r2) / r2 is too small, the rocker 50 and the outer circular surface of the cam portion The gap between them is too small, and it is difficult for the lubricating oil to enter the friction pair through this gap to generate an oil film, which adversely affects the COP. When (r1-r2) / r2 is too large, the bearing capacity of the oil film on the friction pair decreases, which will also cause the friction pair. Metal contact can have an adverse effect on COP.

When satisfying: 0.01% ≤ (r1-r2) / r2≤1%, such as (r1-r2) /r2=0.05%, or (r1-r2) /r2=0.1%, or (r1-r2) / r2 = 0.5%, an oil film is easy to form between the pressing surface 55 of the rocker 50 and the outer circular surface of the cam portion, and a sufficient oil film thickness can be maintained, thereby effectively reducing the distance between the rocker 50 and the outer circular surface of the cam portion. Contact area, which can effectively reduce the friction loss of the friction pair.

Increasing the area of the pressing surface 55 on the rocking block 50 can further reduce the surface pressure between the pressing surface 55 on the rocking block 50 and the outer circular surface of the cam portion, thereby increasing the thickness of the oil film and further reducing the rocking block. The contact area between the pressing surface 55 on the 50 and the outer circular surface of the cam portion reduces the friction loss of the friction pair.

In order to increase the area of the pressing surface 55 on the rocking block 50, the width of the pressing surface 55 needs to be increased. In order to avoid the interference between the rocker block 50 and the vane groove 13 of the cylinder 10 when the compressor is running, a gap 12 needs to be opened at the corresponding position of the vane groove 13 of the cylinder 10. If the gap 12 is opened at the corresponding vane groove of the exhaust side At 13, there will be a clearance volume. After the compression, the high-pressure refrigerant will remain in the avoidance tank, occupying the internal volume of the cylinder 10 after expansion, reducing the intake air volume, and thus reducing the energy efficiency of the compressor.

The wider the width of the pressing surface 55, the larger the volume of the notch 12 that needs to be opened on the exhaust vane slot 13 of the cylinder 10, the larger the clearance volume, and the greater the impact of the clearance energy on the compressor energy efficiency.

The wider the width of the pressing surface 55, the thicker the oil film thickness between the pressing surface 55 and the outer circular surface of the cam portion. The oil film thickness reaches a certain level, which is sufficient to completely avoid metal contact between the friction pair, and then further increase the resistance. On the contrary, the width of the pressing surface 55 will increase the viscosity loss of the oil film between the friction pairs and reduce the energy efficiency of the compressor.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the slider 40 and the outer surface of the cam portion is greatly improved, the lubrication state between the slider 40 and the friction pair of the cam portion is improved, and the resistance of the rocker 50 An oil film is easily formed between the pressing surface 55 and the outer circular surface of the cam portion, and a sufficient oil film thickness can be maintained, so that the contact area between the rocker 50 and the outer circular surface of the cam portion can be effectively reduced, thereby effectively reducing the friction. Friction loss of the pair.

In some embodiments, the thickness of the slider 40 is t1, and the width of the rocker 50 at the abutting surface 55 is t2. In other words, the width of the end of the rocker 50 that is in contact with the outer circular surface of the cam portion is t2.

The inventor found through a large number of experiments that the relationship curve between COP and t2 / t1 of the rotary compressor is shown in FIG. 35. For the rotary compressor of the embodiment of the present disclosure, when: 0.5≤t2 / t1≤3, the compression The machine has a large COP. For example, t2 / t1 = 1, or t2 / t1 = 1.5, or t2 / t1 = 2, or t2 / t1 = 2.5.

Example 4

As shown in FIG. 2 to FIG. 3, the cylinder 10 is provided with a sliding blade groove 13, and the sliding blade 40 is installed in the sliding blade groove 13. As shown in FIG. 3 to FIG. 13, one of the sliding blade 40 and the rocker 50 is provided with an arc. The other one of the open slot 41, the sliding plate 40 and the rocker 50 includes an arc-shaped hinge surface 52. The hinge surface 52 and the open slot 41 are hinged about a first axis, and the first axis is parallel to the axis of the cylinder 10. 50 presses against the outer circular surface of the cam portion. During the operation of the rotary compressor, the rocker 50 and the outer circular surface of the cam portion slide to cooperate to form a sliding friction pair.

In the embodiments shown in FIGS. 3 to 5, 8, 10, and 11, the tip of the sliding plate 40 is provided with an arc-shaped opening groove 41, and the rocking block 50 includes an arc-shaped hinge surface 52 and the rocking block 50. It may include a cylindrical or fan-shaped hinge joint, the hinge surface 52 is a part of the peripheral wall of the hinge joint, and the hinge joint is hinged with the opening slot 41 at the front end of the sliding plate 40.

In the embodiment shown in FIGS. 6 to 7, 9, 12, and 13, the tip of the sliding plate 40 is provided with an arc-shaped hinge surface 52, and the rocking block 50 includes an arc-shaped hinge surface 52 and the slider 40. It may include a cylindrical or fan-shaped hinge joint, the hinge surface 52 is a part of the peripheral wall of the hinge joint, and the hinge joint is hinged with the opening groove 41 of the rocker 50.

During the operation of the rotary compressor, under the action of the pressure difference between the inside and outside of the cylinder 10, the above-mentioned hinge surface 52 and the inner wall of the opening groove 41 are closely abutted together to generate relative movement, and a friction pair is formed between the contact surfaces.

The radius of the hinge surface 52 is r3, and the radius of the opening groove 41 is r4. The inventor has found through a large number of experiments that, for the rotary compressor of the embodiment of the present disclosure, (r4-r3) / r3 is too small, and the rocker 50 and the cam portion The gap between the outer circular surfaces is too small, and it is difficult for the lubricant to enter the friction pair through this gap to produce an oil film, which adversely affects the COP; when (r4-r3) / r3 is too large, the bearing capacity of the oil film on the friction pair decreases, and Will cause direct contact of the friction pair, which will adversely affect the COP.

When satisfying: 0.1% ≤ (r4-r3) / r3≤2%, such as (r4-r3) /r3=0.5, or (r4-r3) /r3=0.5, or (r4-r3) / r3 = 1 Or (r4-r3) /r3=1.5, an oil film is easy to form between the surfaces of the friction pair, and a sufficient oil film thickness can be maintained, so that the contact area between the rocker 50 and the sliding plate 40 can be effectively reduced, and further The friction loss of the friction pair is effectively reduced.

According to the rotary compressor of the embodiment of the present disclosure, the stress of the tip of the sliding plate 40 contacting the outer surface of the cam portion is greatly improved, and the lubrication state between the sliding plate 40 and the friction pair of the cam portion is improved. An oil film is easily formed between the pieces 40, and a sufficient oil film thickness can be maintained, so that the contact area between the rocker 50 and the sliding plate 40 can be effectively reduced, and the friction loss of the friction pair can be effectively reduced.

Example 5

The following describes a rotary compressor according to an embodiment of the present disclosure with reference to FIGS. 1 to 35. The rotary compressor includes a casing, a stator 62, a rotor 61, a crankshaft 31, a piston 32, a cylinder 10, a main bearing 21, and a sub-bearing 22. ，滑片 40 和 Rocker 50.

Among them, referring to FIG. 1, the casing may include a casing 71, an upper casing 72, a lower casing 73, a stator 62, a rotor 61, a crankshaft 31, a piston 32, a cylinder 10, a main bearing 21, a sub-bearing 22, and a sliding plate 40. The swing block 50 may be installed in the cabinet.

As shown in Figs. 1-17, the rotor 61 is connected to the crankshaft 31 for driving the crankshaft 31 to rotate. The main bearing 21 and the auxiliary bearing 22 are provided on the upper and lower surfaces of the cylinder 10, the cylinder 10, the main bearing 21, and the auxiliary bearing, respectively. A compression cavity is defined between 22, the piston 32 is sleeved outside the eccentric part of the crankshaft 31, the piston 32 is rotatably disposed in the cylinder 10, and the piston 32 is rotatably fitted in the compression cavity under the driving of the crankshaft 31.

As shown in FIG. 14, FIG. 16 and FIG. 17, the air cylinder 10 is provided with a sliding blade groove 13, and a sliding blade 40 is installed in the sliding blade groove 13. The tip of the rocker 50 and the sliding blade 40 is hinged about a first axis. The axis of the cylinder 10 is parallel, and the rocker 50 presses against the outer surface of the piston 32. During the operation of the rotary compressor, the rocker 50 and the outer surface of the piston 32 slide to cooperate to form a sliding friction pair.

It should be noted that the leading end of the sliding plate 40 refers to an end of the sliding plate 40 protruding into the compression chamber near the outer circular surface of the piston 32. One end of the rocker block 50 abuts the front end of the sliding plate 40, and the other end of the rocker block 50 abuts the outer circular surface of the piston 32. The rocker 50 has a pressing surface 55 that presses the outer circular surface of the cam portion. The width of the pressing surface 55 in the circumferential direction of the outer circular surface of the cam portion is larger than the width of the leading end of the slider 40.

During the operation of the rotary compressor, the sliding plate 40 reciprocates along the sliding plate groove 13. The rocking block 50 always presses against the outer surface of the piston 32. The rocking block 50 swings relative to the sliding plate 40 about the first axis. 50 swings in a direction parallel to the end face of the cylinder 10.

It can be understood that by providing a rocker 50 between the sliding plate 40 and the piston 32, the contact stress between the sliding plate 40 and the piston 32 can be greatly reduced, and the lubrication state is changed from the original boundary lubrication to the fluid dynamic pressure lubrication. Friction power consumption is effectively reduced, and the amount of cold leakage between the sliding plate 40 and the piston 32 is also reduced.

As shown in FIGS. 14-17, a locking structure is provided between the eccentric portion of the crankshaft 31 and the piston 32. The locking structure is used to limit the circumferential relative movement between the crankshaft 31 and the piston 32, thereby avoiding the eccentricity of the crankshaft 31. Friction loss occurs between the portion and the piston 32.

It can be understood that at this time, the relative movement between the outer circular surface of the piston 32 and the tip of the sliding plate 40 will increase, and the friction loss between the outer circular surface of the piston 32 and the tip of the sliding plate 40 will increase. With the above-mentioned rocker 50, the friction loss between the outer circular surface of the piston 32 and the tip of the sliding plate 40 has become very small. On this basis, a clamping structure is further installed to prevent the eccentric portion of the crankshaft 31 and the relativeness of the piston 32. Motion is still very advantageous for reducing the total friction loss of the rotary compressor.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pair of the cam portion of the blade 40 and the friction loss between the eccentric portion of the crankshaft 31 and the piston 32 can be effectively reduced.

The latching structure can be in a variety of structural forms.

In some embodiments, the latching structure includes a boss 35 that extends into the groove, one of the inner peripheral wall of the piston 32 and the outer peripheral wall of the eccentric portion of the crankshaft 31 is provided with a groove, and the inner peripheral wall of the piston 32 and the crankshaft The other of the outer peripheral walls of the eccentric portion of 31 is provided with a boss 35.

As shown in FIG. 16, a boss 35 is provided on the inner peripheral wall of the piston 32, and a groove is provided on the outer peripheral wall of the eccentric portion of the crankshaft 31. The boss 35 protrudes into the groove, and the boss 35 and the groove can be fitted with a clearance.

As shown in FIG. 17, the inner peripheral wall of the piston 32 is provided with a groove, and the outer peripheral wall of the eccentric portion of the crankshaft 31 is provided with a boss 35, the boss 35 projects into the groove, and the boss 35 and the groove can be fitted with a clearance.

In other embodiments, the latching structure includes a key slot 33 and a key 34. The key 34 is mounted on the key slot 33. The key slot 33 is provided on the outer peripheral wall of the eccentric portion of the crankshaft 31 and the inner peripheral wall of the piston 32. The key groove 33 and the key 34 are more manufacturable. The key 34 may be a rectangular parallelepiped, and the cross section of the key 34 may be a square to facilitate installation.

As shown in FIG. 15, at least one of the key groove 33 in the piston 32 and the crankshaft 31 is a blind hole. In other words, at least one of the key groove 33 in the piston 32 and the key groove 33 in the crank shaft 31 is a blind hole, and The distance from the lower end of the blind hole portion of the key groove 33 to the lower end surface of the piston 32 is h1, which satisfies: h1 ≧ 1 mm. In this way, when the rotary compressor is in operation, it is possible to effectively prevent the key 34 from expanding due to heat, or tilting, or contact with the upper end surface of the lower bearing under the action of gravity to generate friction loss.

As shown in FIG. 15, the upper end face of the key 34 is lower than the upper end face of the piston 32, and the distance between the upper end face of the key 34 and the upper end face of the piston 32 is h1, which satisfies: h1 ≥ 0.005 mm, and further, h1 ≥ 0.02 mm . In this way, it is possible to effectively prevent the key 34 from being thermally expanded or tilted during the operation of the rotary compressor, resulting in friction loss caused by contact with the lower end surface of the upper bearing.

As shown in FIG. 14, the maximum distance between the key groove 33 and the main axis of the crankshaft 31 is L1, and L1 is the distance from the farthest point of the key groove 33 relative to the main axis of the crankshaft 31 to the main axis of the crankshaft 31. The main bearing 21 The closest projection 11 of the exhaust hole on the end face of the cylinder 10 to the major axis of the crankshaft 31 is L2, and L2 is the projection 11 of the exhaust hole on the end face of the cylinder 10 of the main bearing 21 relative to the main axis of the crankshaft 31 The distance from the nearest point to the main shaft axis of the crankshaft 31 satisfies: L2-L1≥0.2mm.

It can be understood that after the key groove 33 is opened on the piston 32, the seal width of the end face of the piston 32 is reduced. In order to ensure the seal width between the exhaust hole and the end face of the piston 32, by setting the value range of L2-L1, when the crankshaft When the eccentric part 31 and the piston 32 rotate around the main axis of the crankshaft 31 as the rotation center until the key groove 33 on the piston 32 falls into the exhaust hole area, the seal width between the exhaust hole and the end face of the piston 32 is ensured to be 0.2 mm or more. Avoid affecting sealing performance.

The key groove 33 and the key 34 have a clearance fit, and the total gap between the key groove 33 and the key 34 in the radial direction of the piston 32 is S1, and the total gap between the eccentric portion of the crankshaft 31 and the piston 32 is S2, which satisfies the relationship S1> S2.

It can be understood that there is a radial gap between the outer circle of the eccentric portion of the crankshaft 31 and the inner circle of the piston 32. When the rotary compressor is running, the piston 32 is pressed against the eccentric portion of the crankshaft 31 under the action of gas to ensure the outer circle of the piston 32. Radial clearance from the inner circle of the cylinder 10. By setting S1> S2, it is possible to prevent the key 34 and the key groove 33 from affecting the radial clearance between the outer circle of the piston 32 and the inner circle of the cylinder 10 during the operation of the rotary compressor, that is, the presence of the key 34 will not affect the operation of the compressor. The gap between the outer circle of the piston 32 and the inner circle of the cylinder 10.

Example Six

As shown in FIG. 18, in an embodiment in which the cam mechanism 30 includes a crankshaft 31 and a piston 32, the piston 32 is sleeved outside the eccentric portion of the crankshaft 31, and the cam portion of the cam mechanism 30 includes a piston 32, and the piston 32 is rotatably provided at In the cylinder 10, the piston 32 is rotatably fitted in the compression chamber under the driving of the crankshaft 31. Of course, the cam mechanism 30 may be integrated.

As shown in FIG. 18 and FIG. 19, the cylinder 10 is provided with a sliding blade groove 13, and the sliding blade 40 is installed in the sliding blade groove 13. The rocker 50 and the tip of the sliding blade 40 are hinged about a first axis. The axis is parallel, and the rocker 50 presses against the outer surface of the cam portion. During the operation of the rotary compressor, the rocker 50 and the outer surface of the cam portion slide to form a sliding friction pair.

The sliding plate 40 is provided with a guide groove 43 on a side parallel to the end surface of the cylinder 10. The guide groove 43 is a sink groove or a through groove. The guide groove 43 extends to the front end of the sliding plate 40. For example, the front end of the sliding plate 40 is provided with The arc-shaped opening groove 41, the rocker 50 includes an arc-shaped hinge surface 52, the hinge surface 52 is hinged with the opening groove 41, the deflection groove 43 communicates with the opening groove 41, and one of the main bearing 21 and the auxiliary bearing 22 is provided with The oil passage 23, the oil supply passage 23 and the flow guide groove 43 penetrate through at least a part of the time during the movement of the sliding plate 40.

It can be understood that a lubricating oil channel is formed when the oil supply channel 23 and the guide groove 43 communicate with each other. Under high pressure, the lubricating oil flows from the oil supply channel 23 into the guide groove 43 on the side of the leading end of the sliding plate 40 for the sliding plate 40. Lubrication between the tip and the rocker 50. The reliability of the rocker block 50 and the sliding plate 40 is improved, at the same time the friction area between the sliding plate 40 and the bearing is reduced, the frictional power consumption is reduced, and the performance of the compressor is effectively improved.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pairs of the cam portion of the blade 40 also greatly improves its reliability, and lubricating oil is introduced between the slider 40 and the rocker 50 to improve the reliability of the rocker 50 and the slider 40. At the same time, the friction area between the sliding plate 40 and the bearing is reduced, and frictional power consumption is reduced.

In some embodiments, as shown in FIG. 20, the projection of the guide groove 43 on the plane where the end surface of the cylinder 10 is located is fan-shaped, the guide groove 43 is fan-shaped, and the arc of the guide groove 43 is greater than 180 °.

In some embodiments, as shown in FIG. 21, the projection of the guide groove 43 on the plane where the end surface of the cylinder 10 is located is an oval, the guide groove 43 is an oval, and the guide groove 43 includes an elongated section and a semicircular section. One end of the long section extends to the front end of the sliding plate 40. For example, one end of the long section extends to communicate with the opening groove 41 on the sliding plate 40, and the other end of the long section is connected to the semi-circular section. The oblong guide groove 43 penetrates the oil supply passage 23 more easily during the movement of the sliding plate 40, or the oblong guide groove 43 penetrates the oil supply passage 23 longer during the movement of the slide 40.

As shown in FIGS. 18 and 19, when the sliding plate 40 moves farthest from the center of the cylinder 10, the maximum distance of the guide groove 43 from the center of the cylinder 10 is L3, and L3 is the moving distance of the sliding plate 40 away from the cylinder 10. When the center of the cylinder is the farthest, the distance from the farthest point of the guide groove 43 relative to the center of the cylinder 10 to the center of the cylinder 10 satisfies: L3> D / 2, where D is the inner diameter of the cylinder 10. In this way, it is possible to ensure that the flow guide groove 43 has a chance to penetrate the oil supply channel 23 during the movement of the sliding plate 40.

As shown in FIGS. 22 and 23, the minimum distance between the fuel supply channel 23 and the center of the cylinder 10 is L4, and L4 is the distance from the closest point of the fuel supply channel 23 to the center of the cylinder 10 to the center of the cylinder 10, which meets: D / 2 <L4 <L3. In this way, it is possible to ensure that the flow guide groove 43 has a chance to penetrate the oil supply channel 23 during the movement of the sliding plate 40.

In some embodiments, as shown in FIG. 22, an end of the oil supply channel 23 facing away from the flow guide groove 43 penetrates the oil pool at the outer diameter of the main bearing 21 or the auxiliary bearing 22, and the oil supply channel 23 may be elongated.

In other embodiments, as shown in FIG. 23, the oil supply passage 23 penetrates the other surface in the thickness direction of the main bearing 21 or the auxiliary bearing 22, and the oil supply passage 23 may penetrate the main bearing 21 or the auxiliary bearing 22 in the axial direction.

In a specific embodiment, the oil supply channel 23 is provided on the auxiliary bearing 22, and a side of the sliding plate 40 facing the auxiliary bearing 22 is provided with a guide groove 43.

Example Seven

The following describes a rotary compressor according to an embodiment of the present disclosure with reference to FIGS. 1 to 33. The rotary compressor includes a casing, a stator 62, a rotor 61, a crankshaft 31, a piston 32, a cylinder 10, a main bearing 21, and a sub-bearing 22. ，滑片 40 和 Rocker 50.

As shown in FIGS. 1 and 2, the rotor 61 is connected to the crankshaft 31 and is used to drive the crankshaft 31 to rotate. The main bearing 21 and the auxiliary bearing 22 are respectively provided on the upper and lower surfaces of the cylinder 10, and the cylinder 10, the main bearing 21 and the auxiliary bearing A compression cavity is defined between 22, the piston 32 is sleeved outside the eccentric part of the crankshaft 31, the piston 32 is rotatably disposed in the cylinder 10, and the piston 32 is rotatably fitted in the compression cavity under the driving of the crankshaft 31.

As shown in FIG. 2, the cylinder 10 is provided with a sliding blade groove 13, and the sliding blade 40 is installed in the sliding blade groove 13. The rocker 50 and the tip of the sliding blade 40 are hinged about a first axis, and the first axis is parallel to the axis of the cylinder 10 The rocking block 50 presses against the outer circular surface of the cam portion. During the operation of the rotary compressor, the rocking block 50 and the outer circular surface of the cam portion slide to cooperate to form a sliding friction pair.

The piston 32 may be made of plastic or graphite. For example, the piston 32 is made of one of polyphenylene sulfide, liquid crystal polymer, polyether ether ketone, ABS engineering plastic, and Teflon.

The sliding plate 40 may be made of one of ceramic, aluminum-silicon alloy, light steel, and Teflon.

The inventor has found through a large number of experiments that by adding the above-mentioned rocker 50, the stress between the tip of the sliding plate 40 and the piston 32 can be reduced from several hundred megapascals to several megapascals. The stress on the tip of the sheet 40 and the side of the slider 40 is reduced.

In this way, the wear between the sliding plate 40 and the piston 32 is greatly reduced, which can reduce the input force of the compressor, and the wear resistance, rigidity, and processing accuracy requirements of the sliding plate 40 and the piston 32 are reduced, thereby widening the selection criteria of the material of the piston 32. Under the structural conditions of the related technology, although the density of the plastic is small, its processing accuracy and abrasion resistance cannot meet its working requirements, which also limits the development of the plastic piston 32. However, the rotary compressor in the embodiment of the present disclosure reduces the requirements on the wear resistance, rigidity, and processing accuracy of the sliding plate 40 and the piston 32, so that the plastic piston 32 can be freed from restrictions.

The common raw material of the piston 32 is nickel-chromium-molybdenum cast iron (FC300) with a density of 7.3 g / cm3, respectively; and the density of the plastic is about 1 to 2 g / cm3. Using this material can greatly reduce the quality of the piston 32. As the weight of the piston 32 is reduced, on the one hand, the rotation speed of the piston 32 will increase, and the relative speed between the piston 32 and the rocker 50 will decrease, resulting in a decrease in the input force; on the other hand, according to the torque balance on the crankshaft 31, the weight of the balance block can be reduced. As a result, the input force is further reduced, and the energy efficiency of the compressor is improved.

As the moving part, the sliding plate 40 is reduced correspondingly after weight reduction, and the input force is also reduced.

In other words, due to the use of the above-mentioned rocker 50, the contact stress between the piston 32 and the sliding plate 40 is reduced, so that the material selection of the piston 32 and the sliding plate 40 is more abundant. According to the conventional design common sense, materials that cannot be used can be applied For the piston 32 and the sliding plate 40, the use of the above materials can reduce the weight of the piston 32 and the sliding plate 40 and realize a lightweight design. The wear between the sliding plate 40 and the piston 32 is greatly reduced, which can reduce the input force of the rotary compressor, and The sliding plate 40 and the piston 32 have reduced requirements for wear resistance, rigidity, and processing accuracy, thereby broadening the selection criteria for the material of the piston 32.

Secondly, the piston 32 and the weight are reduced. On the one hand, the rotation speed of the piston 32 will increase, and the relative speed between the piston 32 and the rocker 50 will decrease, resulting in a decrease in the input force. On the other hand, according to the torque balance on the crankshaft 31, the balance weight will also correspond. The weight is reduced, thereby further reducing the input force. In addition, the piston 32 and the sliding plate 40 are used as moving parts, and the replacement of the lightweight material can also effectively reduce the input force, thereby improving the energy efficiency of the compressor.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pairs of the cam portion of the plate 40 and the material selection criteria of the piston 32 and the sliding plate 40 is widened. The rotary compressor has a high level of weight reduction and high energy efficiency.

Example eight

As shown in FIG. 24-33, the rocker 50 includes a first sub-rocker 51 and a second sub-rocker 54 which are connected, the first sub-rocker 51 and the tip of the slider 40 are hinged about a first axis, and the second sub-rocker The rocker 54 presses against the outer circular surface of the cam portion.

The first sub-rocker 51 and the second sub-rocker 54 may be connected by welding. For example, the first sub-rocker 51 and the second sub-rocker 54 are welded by laser welding, resistance welding, or brazing in a furnace.

The first sub-rocker 51 and the second sub-rocker 54 are made of one of steel, cast iron or alloy for welding.

It should be noted that the volume of the rocker 50 is small. The rocker 50 has two mating surfaces that need to be processed. These two mating surfaces are respectively used to form a friction pair with the sliding plate 40 and the cam portion. It is 2 sub-components for easy processing.

According to the rotary compressor of the embodiment of the present disclosure, the contact stress between the tip of the sliding plate 40 and the outer circular surface of the cam portion is greatly improved, the lubrication state between the sliding plate 40 and the friction pair of the cam portion is greatly improved, and the sliding is greatly reduced. The frictional power consumption between the friction pairs of the cam portion of the blade 40 also greatly improves its reliability, and the structure of the rocker block 50 is simple, easy to process, low in cost, and good in effect.

As shown in FIG. 10 and FIG. 11, an arc-shaped opening groove 41 is provided at the front end of the sliding plate 40. The first sub rocker 51 has an arc-shaped hinge surface 52, and the hinge surface 52 presses against the wall surface of the opening groove 41, as shown in FIG. 24- As shown in FIG. 33, the first sub-rocker 51 may be a cylinder, or at least a part of the outer peripheral surface of the first sub-rocker 51 is arc-shaped,

As shown in FIG. 3, the second sub-rocker 54 has an arc-shaped pressing surface 55, and at least a portion of the pressing surface 55 is inscribed with an outer circular surface of the cam portion. As shown in FIG. 24-33, the pressing surface 55 of the second sub rocker 54 is a part of the outer peripheral wall of the cylinder.

As shown in FIG. 24-26, the first sub-rocker 51 has a first welding surface 53, and the first welding surface 53 is arc-shaped.

As shown in FIGS. 27-31, the first sub rocker 51 has a first welding surface 53, and the first welding surface 53 is planar.

As shown in FIG. 32-33, the first sub-rocker 51 has a first welding surface 53, and the first welding surface 53 is a polygonal line shape. For example, the first welding surface 53 includes three consecutive sections and two adjacent sections. Between vertical.

As shown in FIG. 24, the second sub-rocker 54 has a second welding surface 57, and the second welding surface 57 is arc-shaped.

As shown in FIGS. 25-31, the second sub-rocker 54 has a second welding surface 57, and the second welding surface 57 is planar.

As shown in FIGS. 32-33, the second sub-rocker 54 has a second welding surface 57 which is a polygonal line shape. For example, the second welding surface 57 includes three consecutively connected segments and two adjacent segments. Between vertical.

Of course, when the shapes of the first welding surface 53 and the second welding surface 57 are the same, the welding area of the first sub-rocker 51 and the second sub-rocker 54 is large, and the welding is stronger.

The technical features of the first embodiment to the eighth embodiment described above can be combined with each other to form a new embodiment without conflict.

The above-mentioned first embodiment to eighth embodiment may further include the following technical features to form a new embodiment without conflict.

As shown in FIGS. 3 to 13, one of the front end of the sliding plate 40 and the rocker block 50 is provided with an arc-shaped opening groove 41, and the other includes an arc-shaped hinge surface 52, and the hinge surface 52 is hinged with the opening groove 41.

In the embodiments shown in FIGS. 3 to 5, 8, 10, and 11, an arc-shaped opening groove 41 is provided at the tip of the sliding plate 40. The opening groove 41 opens toward the compression cavity of the cylinder 10, and the sliding plate 40 A guide groove 42 is also provided. The guide groove 42 is connected to the open end of the opening groove 41. The two side walls of the guide groove 42 extend from one end connected to the side wall of the opening groove 41 to the other end in a direction away from each other. 50 includes a rocker connecting portion 56 and an arc-shaped hinge surface 52. The rocker 50 may include a cylindrical or fan-shaped hinge joint. The hinge surface 52 is a part of the peripheral wall of the hinge joint. 41 hinged, the width of the rocker connecting portion 56 is smaller than the diameter of the hinged surface 52. The cooperation of the guide groove 42 and the rocker connecting portion 56 can prevent the rocker 50 from interfering with the air cylinder 10 when the rocker 50 swings. The arc of the opening groove 41 is greater than 180 °, the arc of the hinge surface 52 is greater than 180 °, and the arc of the hinge surface 52 is greater than the arc of the opening groove 41. This can prevent the sliding plate 40 from detaching from the rocker 50.

In the embodiments shown in FIGS. 6 to 7, 9, 12, and 13, the tip end of the slider 40 is provided with an arc-shaped hinge surface 52, and the tip of the slider 40 includes a slider connection portion 46 and a hinge surface. 52. The width of the slider connection portion 46 is smaller than the diameter of the hinge surface 52. The rocker 50 includes an arc-shaped opening groove 41. The slider 40 may include a cylindrical or fan-shaped hinge joint, and the hinge surface 52 is part of the hinge joint. The peripheral wall and the hinge joint are hinged with the opening groove 41 of the rocker 50. The vane connecting portion 46 can prevent the rocker 50 from interfering with the air cylinder 10 when the rocker 50 swings. The arc of the opening groove 41 is greater than 180 °, the arc of the hinge surface 52 is greater than 180 °, and the arc of the hinge surface 52 is greater than the arc of the opening groove 41. This can prevent the sliding plate 40 from detaching from the rocker 50.

As shown in FIG. 3, FIG. 4, FIG. 6, FIG. 10, and FIG. 12, the rocker 50 has a pressing surface 55 for pressing the cam portion, the pressing surface 55 is arc-shaped, and at least part of the pressing surface 55 Inscribed with the outer circular surface of the cam portion. In this way, the contact between the sliding plate 40 and the cam portion is changed from the original inscribed contact to the inscribed contact, the frictional power consumption is effectively reduced, and the leakage of cold between the sliding plate 40 and the piston 32 is also reduced.

As shown in FIGS. 5, 7, 11, and 13, the rocker 50 has a pressing surface 55 for pressing the cam portion, and the pressing surface 55 is a flat surface. In this way, the rocker 50 is easy to process, and compared with the needle roller structure in the related art, the contact stress can also be greatly reduced.

The rocker 50 may be made of one of steel, cast iron, plastic, alloy, and ceramic.

As shown in FIG. 2, one end of the sliding blade groove 13 connected to the compression chamber of the air cylinder 10 includes an open-type notch 12. In this way, the sliding blade groove 13 and the rocker 50 can be prevented from interfering with each other.

The present disclosure also discloses a gas compression system. The gas compression system of the present disclosure includes the rotary compressor of any one of the above embodiments. According to the gas compression system of the embodiment of the present disclosure, the rotary compressor has high energy efficiency and is not easy to wear.

The present disclosure also discloses a refrigeration system. The refrigeration system of the present disclosure includes a rotary compressor of any one of the above embodiments. According to the refrigeration system of the embodiment of the present disclosure, the rotary compressor has high energy efficiency and is not easy to wear.

The present disclosure also discloses a heat pump system. The heat pump system of the present disclosure includes the rotary compressor of any one of the above embodiments. According to the heat pump system of the embodiment of the present disclosure, the rotary compressor has high energy efficiency and is not easy to wear.

Although the embodiments of the present disclosure have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, replacements and variations can be made to these embodiments without departing from the principles and spirit of the present disclosure, The scope of the present disclosure is defined by the claims and their equivalents.

Claims

A rotary compressor is characterized by comprising a cylinder, a cam mechanism, a sliding vane and a rocker block, a cam portion of the cam mechanism is rotatably provided in the cylinder, and the cylinder is provided with a sliding vane groove. The sliding plate is installed in the sliding plate groove, the rocker is hinged with the tip of the sliding plate about a first axis, the first axis is parallel to the axis of the cylinder, and the rocker presses against the The outer surface of the cam portion.
The rotary compressor according to claim 1, wherein one of the tip of the sliding plate and the rocker is provided with an arc-shaped opening groove, and the other includes an arc-shaped hinge surface, and the hinge The surface is hinged with the open slot.
The rotary compressor according to claim 2, wherein the opening groove is provided at the front end of the sliding vane and is open to the compression cavity of the cylinder, and the sliding vane is further provided with a guide groove. The guide groove is connected to the open end of the opening groove, and two side walls of the guide groove extend from one end connected to the side wall of the opening groove to the other end in a direction away from each other;

The rocker block includes a rocker block connecting portion and the hinge surface, and a width of the rocker block connecting portion is smaller than a diameter of the hinge surface.
The rotary compressor according to claim 2 or 3, wherein a tip of the sliding plate includes a sliding plate connection portion and the hinge surface, and a width of the sliding plate connection portion is smaller than a diameter of the hinge surface. .
The rotary compressor according to any one of claims 2-4, wherein the arc of the opening groove is greater than 180 °, and the arc of the hinge surface is greater than 180 °.
The rotary compressor according to any one of claims 1 to 5, wherein the rocker has a pressing surface for pressing the cam portion, the pressing surface is arc-shaped, and At least a part of the pressing surface is inscribed with an outer circular surface of the cam portion.
The rotary compressor according to any one of claims 1-6, wherein the rocker has a pressing surface for pressing the cam portion, and the pressing surface is a flat surface.
The rotary compressor according to any one of claims 1 to 7, wherein the rocker is made of one of steel, cast iron, plastic, alloy, and ceramic.
A gas compression system comprising the rotary compressor according to any one of claims 1-8.
A refrigeration system comprising the rotary compressor according to any one of claims 1-8.
A heat pump system comprising the rotary compressor according to any one of claims 1-8.