CN111287963B

CN111287963B - Rotary compressor, gas compression system, refrigeration system and heat pump system

Info

Publication number: CN111287963B
Application number: CN201811489069.XA
Authority: CN
Inventors: 陈中贵
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2018-12-06
Filing date: 2018-12-06
Publication date: 2022-08-23
Anticipated expiration: 2038-12-06
Also published as: CN111287963A

Abstract

The invention discloses a rotary compressor, a gas compression system, a refrigeration system and a heat pump system, wherein the rotary compressor comprises: the air cylinder is provided with a slide sheet groove; the sliding sheet is arranged in the sliding sheet groove; a cam mechanism, a cam portion of which is rotatably provided in the cylinder; the sliding shoe comprises a sliding shoe head part and a sliding shoe end part which are connected, the sliding shoe head part is provided with a hinged surface, the front end of the sliding sheet is provided with an open slot, the hinged surface is hinged with the open slot so that the sliding shoe head part is connected with the sliding sheet in a swinging mode, the sliding shoe end part is pressed against the outer circular surface of the cam part, and a gap is formed in the hinged surface. The rotary compressor of the invention improves the lubrication state between the sliding vane and the cam part friction pair, greatly reduces the friction power consumption between the sliding vane and the cam part friction pair, has good lubrication effect between the sliding shoe and the sliding vane, and greatly improves the reliability of the rotary compressor.

Description

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

Technical Field

The invention belongs to the technical field of compressor manufacturing, and particularly relates to a rotary compressor, a gas compression system with the rotary compressor, a refrigeration system with the rotary compressor and a heat pump system with the rotary compressor.

Background

In the compressor mechanism, the friction loss between the front end of the slide sheet and the outer circular surface of the piston is large. In order to reduce this friction loss, in the related art, a needle roller is installed at a leading end of the vane, and the structure is intended to change sliding friction between the piston and the vane into rolling friction, so that friction power consumption is effectively reduced. However, the requirement of the needle roller structure on the reliability is extremely high, the contact stress between the needle roller and the piston is rapidly increased, the abrasion resistance of the needle roller material is challenged, the needle roller structure is easy to have the risk of needle roller rolling dead-locking failure, once the needle roller rolling failure occurs, the needle roller is rapidly worn until the compressor is dead-locked and failed, and an improvement space exists.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a rotary compressor, and friction power consumption of a sliding vane cam part friction pair of the rotary compressor is low.

The rotary compressor according to an embodiment of the present invention includes: the air cylinder is provided with a slide sheet groove; the sliding sheet is arranged in the sliding sheet groove; a cam mechanism, a cam portion of which is rotatably provided in the cylinder; the sliding shoe comprises a sliding shoe head part and a sliding shoe end part which are connected, the sliding shoe head part is provided with a hinged surface, the front end of the sliding sheet is provided with an open slot, the hinged surface is hinged with the open slot so that the sliding shoe head part is connected with the sliding sheet in a swinging mode, the sliding shoe end part is pressed against the outer circular surface of the cam part, and a gap is formed in the hinged surface.

According to the rotary compressor provided by the embodiment of the invention, the contact stress of the front end of the sliding vane and the outer circular surface of the cam part is greatly improved, the lubricating state between the sliding vane and the cam part friction pair is improved, the friction power consumption between the sliding vane and the cam part friction pair is greatly reduced, the lubricating effect between the sliding shoe and the sliding vane is good, the reliability of the rotary compressor is greatly improved, and the sliding shoe is simple in structure, low in cost and good in effect.

According to the rotary compressor of one embodiment of the present invention, an opening angle of the opening groove is γ, γ is less than 180 °, an angle between a line connecting one end of the notch close to the end of the slipper and the center of the head of the slipper and the center plane of the slipper is ω 1, and an angle between a line connecting one end of the notch far from the end of the slipper and the center of the head of the slipper and the center plane of the slipper is ω 2, which satisfies the following conditions: omega 1 is more than 0.5 gamma and less than 90 degrees, omega 2 is more than or equal to 60 degrees and less than 90 degrees.

According to the rotary compressor of one embodiment of the present invention, the gap is provided to communicate with the outside of the open groove at least part of the time during the swing of the shoe.

According to the rotary compressor of one embodiment of the present invention, the notch is disposed at the non-load bearing region of the hinge surface.

According to the rotary compressor of one embodiment of the invention, the notch is arranged in the area of the sliding shoe head part close to the compression cavity side.

According to the rotary compressor provided by the embodiment of the invention, the notches are symmetrically arranged at two sides of the slipper head part.

According to the rotary compressor of one embodiment of the present invention, the gap is planar or groove-shaped.

The invention also provides a gas compression system which is provided with any one of the rotary compressors.

The invention also provides a refrigerating system which is provided with the rotary compressor.

The invention also provides a heat pump system which is provided with the rotary compressor.

The gas compression system, the refrigeration system, the heat pump system and the rotary compressor have the same advantages compared with the prior art, and are not described herein again.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 is a schematic structural view of a rotary compressor according to an embodiment of the present invention;

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

FIGS. 3 and 4 are enlarged partial views of FIG. 2 at A and respectively illustrate one form of relief groove;

FIG. 5 is a schematic structural diagram of a slider according to an embodiment of the present invention;

FIG. 6 is a schematic structural view of a slipper according to one embodiment of the invention;

FIG. 7 is a schematic structural diagram of a slider according to another embodiment of the present invention;

FIG. 8 is a schematic structural view of a slipper according to another embodiment of the invention;

fig. 9 is an end view of a rotary compressor according to still another embodiment of the present invention at a cylinder;

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

FIG. 11 is a partial schematic structure of a slider according to an embodiment of the present invention;

FIG. 12 is a schematic structural view of a slipper according to one embodiment of the invention;

fig. 13 is an end view of a rotary compressor according to still another embodiment of the present invention at a cylinder;

FIG. 14 is an enlarged view of a portion of FIG. 13 at C;

FIG. 15 is a partial schematic structure of a slider according to an embodiment of the present invention;

FIGS. 16 and 17 are schematic structural views of a slipper according to an embodiment of the invention;

FIG. 18 is a schematic diagram of the configuration of a slipper according to an embodiment of the invention as it moves to a position where the indentation communicates with the compression chamber.

Reference numerals:

a cylinder 10, a vane groove 13, an escape groove 14, a first inner wall surface 14a, a second inner wall surface 14b, a guide inner wall surface 14c,

a cam mechanism 30, a crankshaft 31, a piston 32,

the slide 40, the open slot 41,

a slipper 50, a slipper head 51, a hinge surface 52, a notch 53, a slipper end 54, a first outer wall surface 54a, a second outer wall surface 54b, a pressing surface 55, a slipper neck 56,

rotor 61, stator 62, main bearing 63, auxiliary bearing 64, shell 71, upper shell 72, lower shell 73.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention and are not to be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "center", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

Example one

A rotary compressor according to an embodiment of the present invention is described below with reference to fig. 1 to 18, and includes: the engine comprises a machine shell, a stator 62, a rotor 61, a cam mechanism 30, a cylinder 10, a main bearing 63, a secondary bearing 64, a sliding sheet 40 and a sliding shoe 50.

Referring to fig. 1, the casing may include a casing body 71, an upper casing 72, and a lower casing 73, and the stator 62, the rotor 61, the cam mechanism 30, the cylinder 10, the main bearing 63, the sub bearing 64, the vane 40, and the shoe 50 may be installed in the casing.

The rotor 61 is connected to the cam gear 30 for driving the cam gear 30 to rotate, a main bearing 63 and a sub bearing 64 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 63 and the sub bearing 64, and a cam portion of the cam gear 30 is rotatably provided in the cylinder 10.

As shown in fig. 2, in the embodiment where the cam mechanism 30 includes the crankshaft 31 and the piston 32, the piston 32 is disposed outside the eccentric portion of the crankshaft 31, the cam portion of the cam mechanism 30 includes the piston 32, the piston 32 is rotatably disposed in the cylinder 10, and the piston 32 is rotatably fitted in the compression cavity by the driving of the crankshaft 31. Of course, the cam mechanism 30 may be integrated.

As shown in fig. 3 and 4, the cylinder 10 is provided with a slide groove 13 and an escape groove 14, the slide sheet 40 is mounted in the slide groove 13, the slide groove 13 can extend in the radial direction of the cylinder 10, and the slide sheet 40 is movable in the slide groove 13.

Avoidance groove 14 is provided at one end of slider groove 13 connected to the compression chamber of cylinder 10, avoidance groove 14 is provided at the inner end of slider groove 13, avoidance groove 14 communicates with slider groove 13, in the embodiment shown in fig. 3 and 4, avoidance groove 14 may be open type, and the size of avoidance groove 14 gradually decreases from the end away from slider groove 13 to the end connected to slider groove 13. The avoiding groove 14 is used for accommodating the sliding shoe 50, and the structure of the avoiding groove 14 can be designed correspondingly according to the structure of the sliding shoe 50.

As shown in fig. 3, 4, 6, and 8, the slipper 50 includes a slipper head 51 and a slipper end 54, the slipper head 51 is connected to the slipper end 54, for example, the slipper head 51 and the slipper end 54 may be integrally formed, or connected by welding or the like.

The sliding shoe head part 51 is connected to the front end of the sliding sheet 40 in a swinging mode, the sliding shoe head part 51 is connected with the front end of the sliding sheet 40 in a swinging mode around a first axis, the first axis is parallel to the axis of the air cylinder 10, the sliding shoe head part 51 and the front end of the sliding sheet 40 form a sliding friction pair, the sliding shoe end part 54 presses against the outer circular surface of the cam part, and in the working process of the rotary compressor, the sliding shoe end part 54 is in sliding fit with the outer circular surface of the cam part to form the sliding friction pair.

The tip of the slide piece 40 means an end of the slide piece 40 which is inserted into the compression chamber and is close to the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe head 51 abuts against the tip of the slide 40, and the shoe end 54 abuts against the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe end 54 has a pressing surface 55, and the pressing surface 55 presses the outer circumferential surface of the cam portion.

During the operation of the rotary compressor, the sliding vane 40 reciprocates along the sliding vane groove 13, the sliding shoe 50 always presses against the outer circumferential surface of the cam portion (piston 32), the sliding shoe 50 swings relative to the sliding vane 40 about the first axis, and the sliding shoe 50 swings in a direction parallel to the end surface of the cylinder 10.

It can be understood that the contact stress between the slide piece 40 and the cam portion can be greatly reduced by providing the shoe 50 between the slide piece 40 and the cam portion, the lubrication state is basically changed from the original boundary lubrication to hydrodynamic lubrication, the frictional power consumption is effectively reduced, and the cold leakage between the slide piece 40 and the cam portion is also reduced.

As shown in fig. 3 and 4, when the sliding vane 40 is at the top dead center, the wall surface of the avoiding groove 14 is covered at least partially outside the sliding shoe end 54, that is, the shape of the wall surface of the avoiding groove 14 may be substantially similar to the shape of the outer wall surface of the sliding shoe end 54, so that when the sliding vane 40 moves to the top dead center position, the clearance between the avoiding groove 14 and the sliding shoe end 54 is small, the clearance volume of the compression cavity is reduced as much as possible, the ineffective compression is avoided, and the performance of the compressor is greatly improved.

As shown in fig. 3 and 4, the wall of the escape slot 14 is spaced from the shoe end 54 when the slide 40 is at top dead centre. This can ensure that the shoe 50 does not interfere with the vane groove 13 of the cylinder 10, so that the reliability thereof is greatly improved. In some embodiments, the minimum clearance between the shoe end 54 and the wall of the avoidance slot 14 when the vane 40 is at top dead center is δ, satisfying: delta is more than or equal to 0.1mm, for example, delta is 0.2 mm.

According to the rotary compressor of the embodiment of the invention, the contact stress of the front end of the sliding vane 40 and the outer circular surface of the cam part is greatly improved, the lubrication state between the sliding vane 40 and the cam part friction pair is improved, the friction power consumption between the cam part friction pair of the sliding vane 40 is greatly reduced, on the premise of ensuring that the sliding shoe 50 does not interfere with the sliding vane groove 13, the clearance volume of a compression cavity is reduced as much as possible, the invalid compression is avoided, the performance of the compressor is greatly improved, the reliability of the rotary compressor is greatly improved, and the sliding shoe 50 has the advantages of simple structure, low cost and good effect.

In some embodiments, as shown in fig. 3 and 4, the wall surface of the avoiding groove 14 close to the compression cavity side (right side in fig. 3 and 4) includes a first inner wall surface 14a and a second inner wall surface 14b which are sequentially connected from the slide sheet groove 13 to the compression cavity, an end of the first inner wall surface 14a away from the second inner wall surface 14b is connected to the slide sheet groove 13, an end of the second inner wall surface 14b away from the first inner wall surface 14a extends to the compression cavity, when the slide sheet 40 is at the top dead center, an included angle between the first inner wall surface 14a and a central plane of the slide sheet groove 13 is α 1, and an included angle between the second inner wall surface 14b and a symmetrical plane of the slide sheet groove 13 is α 2, which satisfies: alpha 2 is more than alpha 1 and less than 90 degrees.

That is, the second inner wall surface 14b is contracted inward with respect to the first inner wall surface 14a, and the gap at the second side wall surface can be reduced. It can be understood that the compressed high-pressure refrigerant remains in the avoiding groove 14, particularly in a portion of the avoiding groove 14 close to the compression cavity side, and the high-pressure refrigerant occupies the internal volume of the cylinder 10 after expanding, so as to reduce the suction amount, thereby reducing the energy efficiency of the compressor, and the clearance volume of the compression cavity can be reduced by providing the avoiding groove 14 with the above structure.

As shown in fig. 3 and 4, the first inner wall surface 14a and the second inner wall surface 14b may be connected by a guide inner wall surface 14c, and since the inclination angle between the first inner wall surface 14a and the second inner wall surface 14b is large, the stress concentration at the position may be reduced by providing the guide inner wall surface 14c, which reduces the processing difficulty, the first inner wall surface 14a and the second inner wall surface 14b are both planar, and the guide inner wall surface 14c is arc-shaped.

As shown in fig. 3 and 4, the outer end of the shoe end 54 is connected to the shoe head 51, the inner end of the shoe end 54 has a pressing surface 55 which presses against the outer circumferential surface of the cam portion, and a first outer wall surface 54a and a second outer wall surface 54b which are connected in sequence are provided between the outer end and the inner end of the shoe end 54; the first inner wall surface 14a is spaced apart from and extends in the same direction as the first outer wall surface 54a, the first inner wall surface 14a and the first outer wall surface 54a may be parallel or substantially parallel, and the second inner wall surface 14b is spaced apart from and extends in the same direction as the second outer wall surface 54 b. This design reduces the compression chamber clearance volume and prevents the shoe 50 from interfering with the vane slot 13.

In the embodiment shown in fig. 3, the wall surface of the avoiding groove 14 on the compression chamber side (right side in fig. 3 and 4) and the wall surface of the avoiding groove 14 on the suction chamber side (left side in fig. 3 and 4) are symmetrically disposed about the center plane of the vane groove 13. That is to say, the avoiding grooves 14 are symmetrically arranged on two sides of the sliding sheet groove 13, so that the avoiding grooves 14 are simple in design and convenient to process.

In the embodiment shown in fig. 4, the avoiding groove 14 is asymmetrically disposed on both sides of the slide groove 13, and as shown in fig. 4, the width of the wall surface of the avoiding groove 14 on the side close to the compression chamber is smaller than the width of the wall surface of the avoiding groove 14 on the side close to the suction chamber, that is, the area of the avoiding groove 14 on the side close to the compression chamber is smaller, and the clearance volume of the compression chamber can be reduced.

Correspondingly, the shoe end 54 may be disposed asymmetrically, the inner end of the shoe end 54 has a pressing surface 55 pressed against the outer circumferential surface of the cam portion, and when the vane 40 is at the top dead center, the width of the portion of the pressing surface 55 close to the compression cavity side is smaller than the width of the portion of the pressing surface 55 close to the suction cavity side.

The abutting surface 55 may be arc-shaped, and at least a part of the abutting surface 55 is inscribed in the outer circular surface of the cam portion. Thus, the contact between the slide piece 40 and the cam portion is changed from the original circumscribed contact to the inscribed contact, the frictional power consumption is effectively reduced, and the leakage of the cooling energy between the slide piece 40 and the piston 32 is also reduced.

Of course, the pressing surface 55 may be a flat surface. In this way, the shoe 50 is easy to machine and can also reduce the contact stress to a greater extent than the needle roller structure of the related art.

As shown in fig. 4, the wall surface of the escape groove 14 on the side closer to the intake chamber is planar, and forms an obtuse angle with the inner wall of the escape groove 14 and the inner wall of the compression chamber, and the wall surface of the escape groove 14 on the side closer to the intake chamber is an inclined surface.

As shown in fig. 5 to 8, one of the front end of the slide piece 40 and the slide shoe head 51 is provided with an arc-shaped open slot 41, and the other thereof includes an arc-shaped hinge surface 52, and the hinge surface 52 is hinged to the open slot 41 to swing the slide shoe head 51 and the slide piece 40. In the embodiment shown in fig. 5 and 6, the front end of the sliding sheet 40 is provided with an arc-shaped open slot 41, and the sliding shoe head 51 comprises an arc-shaped hinge surface 52; in the embodiment shown in fig. 7 and 8, the shoe head 51 is provided with an arcuate slot 41 and the leading end of the slide 40 includes an arcuate hinge surface 52. The arc of the open slot 41 is greater than 180 deg., the arc of the hinge surface 52 is greater than 180 deg., and the arc of the hinge surface 52 is greater than the arc of the open slot 41. This prevents the slide 40 from being disengaged from the shoe 50.

Example two

As shown in fig. 9, in the embodiment where the cam mechanism 30 includes the crankshaft 31 and the piston 32, the piston 32 is disposed outside the eccentric portion of the crankshaft 31, the cam portion of the cam mechanism 30 includes the piston 32, the piston 32 is rotatably disposed in the cylinder 10, and the piston 32 is rotatably fitted in the compression cavity by the driving of the crankshaft 31. Of course, the cam mechanism 30 may be integrated.

As shown in fig. 10, the cylinder 10 is provided with a slide groove 13, the slide sheet 40 is mounted in the slide groove 13, the slide groove 13 can extend in the radial direction of the cylinder 10, and the slide sheet 40 is movable in the slide groove 13.

As shown in fig. 10-12, the slipper 50 includes a slipper head 51 and a slipper end 54, the slipper head 51 is connected to the slipper end 54, for example, the slipper head 51 and the slipper end 54 may be integrally formed or connected by welding or the like.

The sliding shoe head part 51 is connected to the front end of the sliding sheet 40 in a swinging mode, the sliding shoe head part 51 is connected with the front end of the sliding sheet 40 in a swinging mode around a first axis, the first axis is parallel to the axis of the cylinder 10, the sliding shoe head part 51 and the front end of the sliding sheet 40 form a sliding friction pair, the sliding shoe end part 54 presses against the outer circular surface of the cam part, and in the working process of the rotary compressor, the sliding shoe end part 54 is in sliding fit with the outer circular surface of the cam part to form the sliding friction pair.

The slipper head part 51 is provided with a hinge surface 52, the front end of the sliding sheet 40 is provided with an opening groove 41, the hinge surface 52 is hinged with the opening groove 41 so that the slipper head part 51 is connected with the sliding sheet 40 in a swinging mode, and the slipper end part 54 is pressed against the outer circular surface of the cam part.

The tip of the slide piece 40 means an end of the slide piece 40 which is inserted into the compression chamber and is close to the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe head 51 abuts against the tip of the slide plate 40, and the shoe end 54 abuts against the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe end 54 has a pressing surface 55, and the pressing surface 55 presses the outer circumferential surface of the cam portion.

As shown in fig. 9 to 12, the limit pivot angle of the shoe 50 with respect to the central plane of the slide groove 13 is θ, the opening angle of the open groove 41 is γ, and the central angle of the hinge surface 52 is β, which satisfy: gamma- (360-beta) > 2 theta. Theta is the maximum swinging angle of the sliding shoe 50, the hinge surface 52 is smaller than 360 degrees, and the size relation of the angles is limited, so that the sliding shoe 50 can be prevented from interfering with the open slot 41 of the sliding sheet 40 in the swinging process, and the components are prevented from being locked with the open slot 41 of the sliding sheet 40, and even the compressor fails to function.

According to the rotary compressor of the embodiment of the invention, the contact stress of the front end of the sliding sheet 40 and the outer circular surface of the cam part is greatly improved, the lubrication state between the sliding sheet 40 and the cam part friction pair is improved, the friction power consumption between the sliding sheet 40 and the cam part friction pair is greatly reduced, the sliding shoe 50 and the sliding sheet groove 13 are ensured not to be interfered, the reliability of the rotary compressor is greatly improved, and the sliding shoe 50 has the advantages of simple structure, low cost and good effect.

In some embodiments, as shown in FIG. 12, the slipper 50 further comprises a slipper neck 56 connected between the slipper head 51 and the slipper end 54, the slipper neck 56 having a width less than the width of the slipper head 51 and the slipper end 54, the slipper neck 56 preventing the slipper head 51 from rotating with the slider 40. The opening angle at the junction of the slipper neck 56 and slipper head 51 is 360-beta.

As shown in fig. 11, the opening groove 41 is arc-shaped and satisfies: gamma is less than 180 deg. The central angle of the hinge surface 52 may be greater than that of the open groove 41, to prevent the shoe 50 from falling off,

as shown in fig. 9 and 10, the swing arm length of the sliding shoe 50 is L, i.e., the distance from the center of the head 51 of the sliding shoe to the center of the pressing surface 55 is L, the diameter of the hinge surface 52 is d, and the width of the slide piece 40 is T, which satisfies: l is more than or equal to d and less than or equal to T. By designing the structure of the shoe 50 in accordance with this requirement, the shoe 50 can be effectively prevented from being stuck.

As shown in fig. 9 and 10, the swing arm length of the shoe 50 is L, the inner diameter of the cylinder 10 is D, and the limit eccentric amount of the cylinder 10 is e, which satisfy: sin θ ═ e/(0.5D + L-e). By designing the structure of the slipper 50 in accordance with this requirement, the jamming of the slipper 50 can be effectively prevented.

The shoe end 54 has a pressing surface 55 for pressing the cam portion, and the pressing surface 55 is one of an arc-shaped surface and a flat surface.

As shown in fig. 10 and 12, the pressing surface 55 is a circular arc surface, and the pressing surface 55 is inscribed in the outer circular surface of the cam surface. Thus, the contact between the slide piece 40 and the cam portion is changed from the original circumscribed contact to the inscribed contact, the frictional power consumption is effectively reduced, and the leakage of the cooling energy between the slide piece 40 and the piston 32 is also reduced.

EXAMPLE III

As shown in fig. 13, in the embodiment where the cam mechanism 30 includes the crankshaft 31 and the piston 32, the piston 32 is disposed outside the eccentric portion of the crankshaft 31, the cam portion of the cam mechanism 30 includes the piston 32, the piston 32 is rotatably disposed in the cylinder 10, and the piston 32 is rotatably fitted in the compression cavity by the driving of the crankshaft 31. Of course, the cam mechanism 30 may be integrated.

As shown in fig. 14, the cylinder 10 is provided with a slide groove 13, the slide 40 is mounted in the slide groove 13, the slide groove 13 can extend in the radial direction of the cylinder 10, and the slide 40 is movable in the slide groove 13.

As shown in fig. 14-18, the slipper 50 includes a slipper head 51 and a slipper end 54, the slipper head 51 is connected to the slipper end 54, for example, the slipper head 51 and the slipper end 54 may be integrally formed or connected by welding or the like.

The tip of the vane 40 is an end of the vane 40 that extends into the compression chamber and is close to the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe head 51 abuts against the tip of the slide 40, and the shoe end 54 abuts against the outer circumferential surface of the cam portion (piston 32) of the cam mechanism 30. The shoe end 54 has a pressing surface 55, and the pressing surface 55 presses the outer circumferential surface of the cam portion.

During the operation of the rotary compressor, the sliding vane 40 reciprocates along the sliding vane groove 13, the sliding shoe 50 always presses against the outer circumferential surface of the cam portion (piston 32), the sliding shoe 50 swings relative to the sliding vane 40 around the first axis, and the sliding shoe 50 swings in a direction parallel to the end surface of the cylinder 10.

As shown in fig. 14, 16-18, the articulation surface 52 is provided with a notch 53, as shown in fig. 18, the notch 53 being arranged to communicate with the exterior of the open slot 41 at least part of the time during which the slipper 50 oscillates.

It can be understood that, in the working process of the compressor, by providing the notch 53 on the hinge surface 52 of the sliding shoe 50, the lubricating oil can be brought into the open slot 41 of the sliding sheet 40 through the swing of the sliding shoe 50, and on the premise of ensuring the reliability of the sliding sheet 40 and the sliding shoe 50, the oil supply between the open slot 41 of the sliding sheet 40 and the sliding shoe 50 in the left-right swing process of the sliding shoe 50 is effectively solved, so that the lubrication of the sliding sheet is ensured to be improved, the friction power consumption between the sliding sheet 40 and the sliding shoe 50 is reduced, and the performance of the compressor is greatly improved.

According to the rotary compressor of the embodiment of the invention, the contact stress of the front end of the sliding vane 40 and the outer circular surface of the cam part is greatly improved, the lubrication state between the sliding vane 40 and the cam part friction pair is improved, the friction power consumption between the cam part friction pair of the sliding vane 40 is greatly reduced, the lubrication effect between the sliding shoe 50 and the sliding vane 40 is good, the reliability of the rotary compressor is greatly improved, and the sliding shoe 50 has the advantages of simple structure, low cost and good effect.

In some embodiments, the opening angle of the open slot 41 is γ, an angle between a line connecting one end of the notch 53 close to the slipper end 54 and the center of the slipper head 51 and the central plane of the slipper 50 is ω 1, an angle between a line connecting one end of the notch 53 far from the slipper end 54 and the center of the slipper head 51 and the central plane of the slipper 50 is ω 2, that is, the starting angle of the notch 53 is ω 1, and the ending angle is ω 2, which satisfies the following condition: omega 1 is more than 0.5 gamma and less than 90 degrees, omega 2 is more than or equal to 60 degrees and less than 90 degrees. Therefore, the size and the arrangement position of the notch 53 can meet the requirement of oil supply, and the movement of the sliding friction pair is not influenced. The notches 53 are provided with hinged surfaces 52 on either side, and positioning the notches 53 in the above-mentioned positions also prevents the boot neck 56 from breaking.

As shown in fig. 16 and 17, the notch 53 is provided in the non-load bearing area of the hinge surface 52, it being noted that the shoe 50 is clamped between the cam portion and the slide 40, and the load bearing area of the hinge surface 52 is mainly located at the top of the hinge surface 52, i.e. the end of the hinge surface 52 facing away from the shoe end 54.

The notch 53 is provided at least on one side, and the notch 53 is provided in a region of the slipper head 51 near a compression chamber side (right side in fig. 14) which is a high pressure side for facilitating suction of high pressure oil lubrication.

Of course, as shown in fig. 16 and 17, the notches 53 are symmetrically provided on both sides of the slipper head 51.

As shown in fig. 16, the notch 53 may be planar, and the planar notch 53 is easy to process.

As shown in FIG. 17, the indentations 53 may also be groove-shaped, including but not limited to arcuate grooves, rectangular grooves, and the like.

The invention also discloses a gas compression system which comprises the rotary compressor of any one of the embodiments. According to the gas compression system provided by the embodiment of the invention, the rotary compressor has high energy efficiency and is not easy to wear.

The invention also discloses a refrigerating system which comprises the rotary compressor of any one of the embodiments. According to the refrigeration system provided by the embodiment of the invention, the rotary compressor has high energy efficiency and is not easy to wear.

The invention also discloses a heat pump system, which comprises the rotary compressor in any embodiment. According to the heat pump system provided by the embodiment of the invention, the rotary compressor has high energy efficiency and is not easy to wear.

Claims

1. A rotary compressor, comprising:

the air cylinder is provided with a slide sheet groove and an avoidance groove;

the sliding sheet is arranged in the sliding sheet groove;

a cam mechanism, a cam portion of which is rotatably provided in the cylinder;

the sliding shoe comprises a sliding shoe head part and a sliding shoe end part which are connected, the sliding shoe head part is provided with a hinged surface, the front end of the sliding sheet is provided with an open slot, the hinged surface is hinged with the open slot so that the sliding shoe head part is connected with the sliding sheet in a swinging mode, the sliding shoe end part is pressed against the outer circular surface of the cam part, the hinged surface is provided with a notch, and lubricating oil is brought into the open slot of the sliding sheet through the swinging of the sliding shoe;

the width of the wall surface of the avoiding groove close to the compression cavity side is smaller than the width of the wall surface of the avoiding groove close to the suction cavity.

2. The rotary compressor of claim 1, wherein an opening angle of the opening groove is γ, γ is less than 180 °, an angle between a line connecting one end of the gap close to the end of the slipper and the center of the head of the slipper and the center plane of the slipper is ω 1, and an angle between a line connecting one end of the gap far from the end of the slipper and the center of the head of the slipper and the center plane of the slipper is ω 2, and the following relationship is satisfied: omega 1 is more than 0.5 gamma and less than 90 degrees, omega 2 is more than or equal to 60 degrees and less than 90 degrees.

3. The rotary compressor of claim 1, wherein the gap is configured to communicate with an outside of the open groove at least a portion of the time during the wobble of the shoe.

4. The rotary compressor of claim 1, wherein the notch is disposed in a non-load bearing region of the hinge surface.

5. The rotary compressor of claim 1, wherein the notch is provided at a region of the shoe head portion near a compression chamber side.

6. The rotary compressor of claim 1, wherein the notches are symmetrically disposed on both sides of the slipper head portion.

7. The rotary compressor of claim 1, wherein the gap is planar or groove-shaped.

8. A gas compression system having a rotary compressor according to any one of claims 1 to 7.

9. A refrigerating system having the rotary compressor of any one of claims 1 to 7.

10. A heat pump system characterized by having a rotary compressor according to any one of claims 1 to 7.