CN218177407U

CN218177407U - Sliding vane, pump body assembly and compressor

Info

Publication number: CN218177407U
Application number: CN202222778439.XU
Authority: CN
Inventors: 翟元彬; 黄英伟; 田树丹
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2022-10-21
Filing date: 2022-10-21
Publication date: 2022-12-30
Anticipated expiration: 2032-10-21

Abstract

The utility model provides a gleitbretter, pump body subassembly and compressor, gleitbretter are used for pump body subassembly, and pump body subassembly includes the cylinder, and the cylinder is equipped with the mounting groove, and the gleitbretter includes: the body is arranged in the mounting groove and can move in the mounting groove along a first direction; along the second direction, the body includes suction side and exhaust side, along the third direction, is equipped with first oil groove on the first terminal surface of body, and first oil groove is close to the suction side and sets up, and the second terminal surface of body is equipped with the second oil groove, and the second oil groove is close to the exhaust side and sets up.

Description

Sliding vane, pump body assembly and compressor

Technical Field

The utility model relates to a compressor technical field particularly, relates to a gleitbretter, pump body subassembly and compressor.

Background

At present, as shown in fig. 1, in a pump body assembly, a cylinder 1 'is provided with a vane slot, one end of a vane 4' close to the roller is matched with the outer circle of the roller, an air suction cavity is communicated with an air suction hole 10 'in the cylinder 1', an air exhaust cavity is communicated with an air exhaust hole 2', and the vane 4' separates the air suction cavity from the air exhaust cavity. The conventional exhaust hole 2 'is generally disposed on the bearing 2', and when the exhaust is about to end, the high-pressure refrigerant and the refrigerant oil at the lower part of the cylinder 1 'are extruded to the side of the sliding vane 4' close to the partition plate 3 'due to the failure of timely discharging, which may cause the exhaust side pressure of the sliding vane 4': the exhaust pressure Pd ' on the side close to the partition plate 3' is larger than the exhaust pressure Pd on the side close to the bearing 2 '. Therefore, the slide vane 4' may be inclined in the slide vane of the cylinder 1', the upper edge of the slide vane 4' near the suction side may be in metal contact with the end face of the bearing 2', and the lower edge near the discharge side may be in metal contact with the end face of the partition plate 3 '. Therefore, the friction power consumption of the sliding sheet 4' is increased, abnormal friction sound occurs, and the bearing 2' and the end surface of the partition plate 3' are seriously abraded abnormally, even the compressor fails.

SUMMERY OF THE UTILITY MODEL

The present invention aims at least solving one of the technical problems existing in the prior art or the related art.

To this end, a first aspect of the present invention provides a slider.

The second aspect of the utility model provides a pump body subassembly still.

The third aspect of the present invention also provides a compressor.

In view of this, the utility model discloses a first aspect provides a gleitbretter for pump body subassembly, pump body subassembly include the cylinder, and the cylinder is equipped with the mounting groove, and the gleitbretter includes: the body is arranged in the mounting groove and can move in the mounting groove along a first direction; along the second direction, the body includes suction side and exhaust side, along the third direction, is equipped with first oil groove on the first terminal surface of body, and first oil groove is close to the suction side and sets up, and the second terminal surface of body is equipped with the second oil groove, and the second oil groove is close to the exhaust side and sets up.

The utility model provides a gleitbretter, body setting are in the mounting groove to can follow the first direction motion in the mounting groove, so that the chamber of breathing in and the exhaust chamber of cylinder are separated. Wherein, along the second direction, the body includes suction side and exhaust side, along the third direction, be provided with first oil groove on the first terminal surface of body, first oil groove is close to the suction side and sets up, be provided with the second oil groove on the second terminal surface of body, the second oil groove is close to the exhaust side and sets up, and like this, can improve the lubricated effect of first terminal surface department and second terminal surface department, reduce the friction of gleitbretter in first terminal surface and second terminal surface department, and then reduce the friction consumption of first terminal surface and second terminal surface department of gleitbretter, reduce the noise that the gleitbretter friction arouses. Simultaneously, can dodge the at least part of the cylinder both ends parts that first terminal surface and second terminal surface correspond through first oil groove and second oil groove to, first oil groove is close to the side setting of breathing in, and the second oil groove is close to the side setting of exhausting, can balance the slope of gleitbretter, takes place wearing and tearing and abnormal noise after avoiding the gleitbretter to interfere with the part at cylinder both ends.

According to the utility model provides a gleitbretter can also have following additional technical characterstic:

in some possible designs, in the second direction, the thickness T of the vane and the width T1 of the first oil groove satisfy the following relation: 0 is less than or equal to 0.5T; the thickness T of the sliding piece and the width T2 of the second oil groove satisfy the following relational expression: 0T 2 is less than or equal to 0.5T.

In this design, along the second direction, the width of first oil groove is too wide can reduce sealed effect, and the width undersize of first oil groove then can reduce lubricated effect, consequently, sets up the width T1 of first oil groove for being greater than 0 and be less than or equal to 0.5 gleitbretter thickness T doubly. Correspondingly, the width of second oil groove is too wide and can reduce sealed effect, and the width undersize of second oil groove then can reduce to lubricated balanced effect, consequently, sets up the width T2 of second oil groove and be greater than 0 and be less than or equal to 0.5 gleitbretter thickness T doubly.

In some possible designs, the first oil groove and the second oil groove extend from one end of the body away from the center of the cylinder to the other end of the body in the first direction.

In this design, along first direction, cylinder center's one end is kept away from the body to the other end of body extension to first oil groove and second oil groove to avoid first oil groove or second oil groove and cylinder intercommunication, guaranteed the sealed of cylinder.

In some possible designs, the first oil groove and the second oil groove are arranged in central symmetry along the first direction.

In this design, along first direction, first oil groove and second oil groove are central symmetry and set up, like this, when the installation gleitbretter, need not distinguish the upper and lower terminal surface of gleitbretter, have reduced the degree of difficulty of assembly, manufacturing, simultaneously, are central symmetry setting with first oil groove and second oil groove, can also form central symmetry's oil film pressure to correct the slope of gleitbretter, and then avoid taking place the condition of friction and unusual noise.

In some possible designs, the length L1 of the first oil groove along the first direction and the depth h1 of the first oil groove along the third direction satisfy the following relation: h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1; the length L2 of the second oil groove along the first direction and the depth h2 of the second oil groove along the third direction satisfy the following relational expression: h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2.

In the design, the depth h1 of the first oil groove and the length L1 of the first oil groove meet the condition that h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1, and the oil film bearing capacity can be better. Correspondingly, the depth h2 of the second oil groove and the length L1 of the second oil groove meet the condition that h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2, and the oil film bearing capacity can be better.

In some possible designs, the cross-section of each of the first oil groove and the second oil groove is rectangular in cross-section perpendicular to the first direction.

In this design, in the cross-section of following the first direction of perpendicular to, the cross-section of first oil groove and second oil groove all is the rectangle, the processing of the first oil groove of being convenient for and second oil groove.

In some possible designs, along the second direction, in a projection of a plane perpendicular to the second direction, the projection of the first oil groove and the projection of the second oil groove are both triangular.

In this design, along the second direction, in the projection of the plane of perpendicular to second direction, the projection of first oil groove and the projection of second oil groove are triangle-shaped, have promoted the lubricated effect of first oil groove and second oil groove.

In some possible designs, the first oil groove includes a first ramp and the second oil groove includes a second ramp; from one end close to the center of the cylinder to one end far away from the center of the cylinder, the first inclined surface is obliquely arranged towards the second end surface, and the second inclined surface is obliquely arranged towards the first end surface.

In this design, first oil groove includes first inclined plane, and the second oil groove includes the second inclined plane, by the one end that is close to the center of cylinder to the one end of keeping away from the center of cylinder, first inclined plane sets up to the slope of second terminal surface place orientation, by the one end that is close to the cylinder center, to the one end of keeping away from the cylinder center, the second inclined plane sets up to the slope of first terminal surface place orientation, has promoted lubricated effect, thereby the friction power consumption of first terminal surface and second terminal surface has been reduced, and the noise that the gleitbretter friction arouses.

In some possible designs, an angle between the first bevel and the first direction is greater than or equal to 0 ° and less than or equal to 3 °; an included angle between the second inclined surface and the first direction is greater than or equal to 0 degrees and less than or equal to 3 degrees.

In this design, the contained angle between first inclined plane and the first direction is too big, then can reduce the intensity of gleitbretter, if the contained angle undersize of first inclined plane and first direction, then can reduce lubricated effect, also can be unfavorable for reducing the friction consumption of first terminal surface simultaneously. Specifically, the included angle between the first inclined plane and the first direction is designed to be larger than or equal to 0 degrees and smaller than or equal to 3 degrees, so that the strength of the sliding sheet can be guaranteed, and the reduction of friction power consumption and the reduction of friction noise can be guaranteed.

Correspondingly, the strength of the sliding sheet can be reduced if the included angle between the second inclined surface and the first direction is too large, the lubricating effect can be reduced if the included angle between the second inclined surface and the first direction is too small, and the reduction of the friction power consumption of the second end face can be not facilitated. Specifically, the included angle between the second inclined plane and the first direction is designed to be larger than or equal to 0 degrees, and smaller than or equal to 3 degrees, so that the strength of the sliding sheet can be guaranteed, and the reduction of friction power consumption and the reduction of friction noise can be guaranteed.

In some possible designs, in a projection of a plane perpendicular to the first direction along the first direction, the projection of the first oil groove and the projection of the second oil groove are both triangular.

In this design, along the first direction, in the planar projection of the first direction of perpendicular to, the projection of first oil groove and the projection of second oil groove are triangle-shaped, can promote the improvement to lubricated effect of first oil groove and second oil groove, reduce the frictional force of first terminal surface and second terminal surface department, and then reduce the friction power dissipation of the first terminal surface and the second terminal surface department of gleitbretter, reduce the noise that gleitbretter friction brought.

In some possible designs, the first oil groove includes a third inclined surface, and the second oil groove includes a fourth inclined surface; the third inclined surface is inclined toward the second end surface from the side close to the exhaust side to the side close to the suction side, and the fourth inclined surface is inclined toward the first end surface from the side close to the suction side to the side close to the exhaust side.

In this design, first oil groove includes the third inclined plane, and the second oil groove includes the fourth inclined plane, and the third inclined plane inclines to the suction side by the exhaust side, also is the third inclined plane along the thickness direction slope of gleitbretter for the projection of first oil groove is triangle-shaped. The fourth inclined plane is inclined from the air suction side to the air exhaust side, so that the projection of the second oil groove is triangular, the lubrication conditions of the first end face and the second end face of the sliding sheet are improved, the friction power consumption is reduced, and abnormal noise caused by friction is reduced.

In some possible designs, the angle between the third bevel and the second direction is greater than or equal to 0 ° and less than or equal to 3 °; an included angle between the fourth inclined surface and the second direction is greater than or equal to 0 degrees and less than or equal to 3 degrees.

In this design, too big then can reduce the intensity of gleitbretter between third inclined plane and the second direction, and then reduce the life of gleitbretter. If the included angle between the third inclined plane and the second direction is too small, the depth of the first oil groove can be reduced, the lubricating effect is further reduced, and meanwhile, the friction power consumption of the first end face is not reduced. Therefore, the included angle between the third inclined plane and the second direction is designed to be larger than or equal to 0 degrees and smaller than or equal to 3 degrees, the strength and the service life of the sliding piece can be guaranteed, the lubricating effect of the first oil groove can be guaranteed, and abnormal friction between the sliding piece and the first end face is avoided.

The too big contained angle between fourth inclined plane and the second direction then can reduce the intensity of gleitbretter, and then reduces the life of gleitbretter. If the included angle between the fourth inclined plane and the second direction is too small, the depth of the second oil groove can be reduced, the lubricating effect is further reduced, and meanwhile, the friction power consumption of the first end face is not reduced. Therefore, the included angle between the fourth inclined plane and the second direction is designed to be larger than or equal to 0 degrees and smaller than or equal to 3 degrees, the strength and the service life of the sliding piece can be guaranteed, the lubricating effect of the second oil groove can be guaranteed, and abnormal friction between the sliding piece and the first end face is avoided.

According to the utility model discloses a second aspect still provides a pump body subassembly, include: the cylinder is provided with a mounting groove; the first supporting part is arranged at one end of the cylinder; the second supporting part is arranged at the other end of the air cylinder, and the air cylinder, the first supporting part and the second supporting part enclose a compression cavity; and a sliding piece as set forth in any one of the first to the second aspects, the sliding piece being disposed in the mounting groove and being capable of sliding in the mounting groove along a first direction, the first end face corresponding to the first support portion, the second end face corresponding to the second support portion.

The utility model discloses the pump body subassembly that the second aspect provided, which comprises a cylinder, first supporting part, second supporting part and gleitbretter, the gleitbretter sets up in the mounting groove, and first terminal surface corresponds with first supporting part, the second terminal surface corresponds with the second supporting part, through set up first oil groove on first terminal surface, set up the second oil groove on the second terminal surface, the lubricated effect between first terminal surface and the first supporting part has been promoted, lubricated effect between second terminal surface and the second oil groove, at the gliding in-process of gleitbretter, gleitbretter and first supporting part have been reduced, friction power consumption between the second supporting part, reduce unusual frictional noise.

In some possible designs, the pump body assembly further comprises: the roller is arranged in the cylinder; the length L of the slide sheet, the length L1 of the first oil groove and the eccentricity e of the roller satisfy the following relational expression: l1 is not more than L-2e-5mm; the length L of the slide sheet, the length L2 of the second oil groove and the eccentricity e of the roller satisfy the following relational expression: l2 is not more than L-2e-5mm.

In the design, the pump body assembly further comprises a roller arranged in the cylinder, and the compression of the medium in the compression cavity is realized through the eccentric motion of the roller. Wherein, under the condition that the gleitbretter stretches into in the cylinder longest, along first direction, the distance between the edge of first oil groove and cylinder internal wall face is sealing distance, in order to guarantee good sealed, need to make sealing distance L-2e-L1 be greater than or equal to 5mm, just promptly L1 is less than or equal to L-2e-5mm, correspondingly, the length L of gleitbretter, the length L2 of second oil groove, the eccentric value e of roller satisfy following relational expression: l2 is less than or equal to L-2e-5mm, so that the communication between the air suction cavity of the cylinder and the first oil groove is avoided, and the communication between the air exhaust cavity and the second oil groove is avoided.

In some possible designs, the cylinder includes a first cylinder and a second cylinder, the rollers include a first roller and a second roller, the first support portion includes a first bearing and a second bearing, and the second support portion includes a diaphragm; the first roller is arranged in the first cylinder, the second roller is arranged in the second cylinder, the first bearing is positioned on one side of the first cylinder, which is far away from the second cylinder, the second bearing is positioned on one side of the second cylinder, which is far away from the first cylinder, and the partition plate is arranged between the first cylinder and the second cylinder; the pump body subassembly still includes: the axial region wears to locate first cylinder and second cylinder, and first roller and second roller are connected with the axial region.

In this design, the cylinders include a first cylinder and a second cylinder, the rollers include a first roller and a second roller, and the bearings include a first bearing and a second bearing. The axial region is worn to establish on first cylinder, second cylinder, first bearing, second bearing, and first roller and second roller are connected with the axial region, realize eccentric motion under the drive of axial region.

Specifically, first cylinder and second cylinder set up along the axial interval of axial part, and first bearing setting deviates from one side of second cylinder at first cylinder, and the second bearing setting deviates from one side of first cylinder at the second cylinder, and the baffle setting is between first bearing and second bearing, and first bearing, baffle and first cylinder enclose out the compression chamber, and second bearing, baffle and second cylinder enclose out another compression chamber and realize the compression to the medium.

Furthermore, exhaust holes are respectively formed in the first bearing and the second bearing, air suction holes are respectively formed in the first air cylinder and the second air cylinder, and the shaft portion is a crankshaft.

According to the utility model discloses a third aspect still provides a compressor, include: the vane of any one of the first aspects, or the pump body assembly of any one of the second aspects.

The utility model discloses the compressor that the third aspect provided, because of gleitbretter or the pump body subassembly that proposes including above-mentioned arbitrary technical scheme, consequently have all beneficial effects of gleitbretter or pump body subassembly.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, 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 shows a schematic structural view of a pump body assembly of the related art.

The air cylinder comprises a 1 'air cylinder, a 10' air suction hole, a 2 'bearing, a 20' exhaust hole, a 3 'partition plate and a 4' sliding sheet.

Figure 2 shows one of the schematic structural views of a slider according to an embodiment of the present invention;

FIG. 3 shows a side view of the slider of the embodiment shown in FIG. 2;

fig. 4 shows a second schematic structural diagram of a sliding piece according to an embodiment of the present invention;

FIG. 5 shows a partial front view of the slider of the embodiment of FIG. 4;

fig. 6 shows a third schematic structural diagram of a sliding piece according to an embodiment of the present invention;

FIG. 7 shows a partial side view of the slider of the embodiment of FIG. 6;

FIG. 8 shows a force diagram of a slider according to an embodiment of the present invention;

FIG. 9 shows another force diagram for the slider of the embodiment of FIG. 8;

FIG. 10 illustrates one of the schematic structural views of the pump body assembly of one embodiment of the present invention;

fig. 11 shows a second schematic structural view of a pump body assembly according to an embodiment of the present invention;

fig. 12 is a schematic view illustrating a compressor according to an embodiment of the present invention;

fig. 13 is a graph showing a comparison of noise spectra of a compressor according to an embodiment of the present invention and a related art compressor;

fig. 14 is a schematic diagram showing the relationship between the oil film bearing capacity of the pump body assembly and the size of the first oil groove or the second oil groove according to an embodiment of the present invention;

fig. 15 shows a reynolds differential equation diagram.

Wherein, the correspondence between the reference numbers and the component names in fig. 2 to 12 is:

1 compressor, 10 motor, 100 rotor, 102 stator, 12 gas-liquid separator, 14 upper shell, 16 main shell, 18 lower shell, 2 pump body component, 20 cylinder, 200 mounting groove, 202 first cylinder, 204 second cylinder, 22 first roller, 23 second roller, 24 first bearing, 25 second bearing, 26 partition plate, 28 shaft part, 3 sliding sheet, 30 body, 31 suction side, 32 exhaust side, 33 first end surface, 34 first oil groove, 340 first inclined surface, 342 third inclined surface, 35 second end surface, 36 second oil groove, 360 second inclined surface, 362 fourth inclined surface.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention more clearly understood, the present invention will be described in further detail with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

The following describes a vane 3, a pump body assembly 2 and a compressor 1 proposed according to some embodiments of the present invention with reference to fig. 2 to 15.

As shown in fig. 2, fig. 10 and fig. 11, according to the first embodiment of the present invention, the present invention provides a sliding piece 3 for a pump body assembly 2, the pump body assembly 2 includes a cylinder 20, the cylinder 20 is provided with a mounting groove 200, the sliding piece 3 includes: the body 30 is disposed in the mounting groove 200.

Specifically, the body 30 is movable in a first direction within the mounting groove 200; along the second direction, body 30 includes suction side 31 and exhaust side 32, and along the third direction, is equipped with first oil groove 34 on the first terminal surface 33 of body 30, and first oil groove 34 is close to suction side 31 and sets up, and the second terminal surface 35 of body 30 is equipped with second oil groove 36, and second oil groove 36 is close to exhaust side 32 and sets up.

The utility model provides a gleitbretter 3, body 30 set up in mounting groove 200 to can follow the first direction motion in mounting groove 200, so that the chamber of breathing in and the exhaust chamber of cylinder 20 are separated. Wherein, along the second direction, body 30 includes suction side 31 and exhaust side 32, along the third direction, be provided with first oil groove 34 on the first terminal surface 33 of body 30, first oil groove 34 is close to suction side 31 and sets up, be provided with second oil groove 36 on the second terminal surface 35 of body 30, second oil groove 36 is close to exhaust side 32 and sets up, like this, can improve the lubrication of first terminal surface 33 department and second terminal surface 35 department, reduce the friction of gleitbretter 3 in first terminal surface 33 and second terminal surface 35 department, and then reduce the friction power consumption of first terminal surface 33 and second terminal surface 35 department of gleitbretter 3, reduce the noise that the friction of gleitbretter 3 arouses. Meanwhile, at least parts of the two end parts of the cylinder 20 corresponding to the first end surface 33 and the second end surface 35 can be avoided through the first oil groove 34 and the second oil groove 36, the first oil groove 34 is arranged close to the air suction side 31, the second oil groove 36 is arranged close to the air exhaust side 32, the inclination of the sliding sheet 3 can be balanced, and abrasion and abnormal noise can be avoided after the sliding sheet 3 interferes with the parts at the two ends of the cylinder 20.

In specific application, pump body subassembly 2 includes cylinder 20, bearing and baffle 26, be provided with mounting groove 200 on the cylinder 20, and cylinder 20, bearing and baffle 26 surround out the compression chamber, gleitbretter 3 separates the compression chamber for low-pressure chamber and high-pressure chamber, gleitbretter 3 is under the huge pressure differential in side 31 and the exhaust side 32 both sides of breathing in, can lead to gleitbretter 3 to take place to incline or twist reverse in mounting groove 200, consequently, through the gleitbretter 3 that this application provided, can avoid gleitbretter 3 and baffle 26 and bearing to take place the metal friction, and then avoid wearing and tearing and abnormal noise.

The suction side 31 is disposed close to the suction hole of the pump body assembly 2, and the exhaust side 32 is disposed close to the exhaust hole of the pump body assembly 2.

In specific application, the first direction is a movement direction of the sliding vane 3, the second direction is a thickness direction of the sliding vane 3, and the third direction is an axial direction of the pump body assembly 2.

According to the second embodiment of the present invention, on the basis of the above-mentioned embodiments, further: in the second direction, the thickness T of the vane 3 and the width T1 of the first oil groove 34 satisfy the following relation: 0 is less than or equal to 0.5T; the thickness T of the vane 3 and the width T2 of the second oil groove 36 satisfy the following relation: 0T 2 is less than or equal to 0.5T.

In this design, too wide the width of the first oil groove 34 in the second direction may reduce the sealing effect, and too small the width of the first oil groove 34 may reduce the lubricating effect, and thus, the width T1 of the first oil groove 34 is set to be greater than 0 and less than or equal to 0.5 times the thickness T of the vane 3. Accordingly, too wide a width of the second oil groove 36 may reduce a sealing effect, and too small a width of the second oil groove 36 may reduce a lubrication balancing effect, and thus, the width T2 of the second oil groove 36 is set to be greater than 0 and less than or equal to 0.5 times the thickness T of the vane 3.

In a specific application, T1 is equal to any of 0.1T, 0.2T, 0.3T, and 0.4T. T2 is equal to any of 0.1T, 0.2T, 0.3T, 0.4T.

According to the third embodiment of the present invention, on the basis of the second embodiment, further: in the first direction, the first oil groove 34 and the second oil groove 36 extend from one end of the body 30, which is away from the center of the cylinder 20, to the other end of the body 30.

In this design, along the first direction, first oil groove 34 and second oil groove 36 extend from the one end of body 30 that is far away from the cylinder 20 center to the other end of body 30 to avoid first oil groove 34 or second oil groove 36 to communicate with cylinder 20, guaranteed the sealed of cylinder 20.

As shown in fig. 2, fig. 4 and fig. 6, according to a fourth embodiment of the present invention, on the basis of any of the above embodiments, further: in the first direction, the first oil groove 34 and the second oil groove 36 are arranged in a central symmetry.

In this design, along first direction, first oil groove 34 and second oil groove 36 are central symmetry and set up, like this, when installation gleitbretter 3, need not distinguish the upper and lower terminal surface of gleitbretter 3, have reduced the degree of difficulty of assembly, manufacturing, simultaneously, be central symmetry with first oil groove 34 and second oil groove 36 and set up, can also form central symmetry's oil film pressure to correct the slope of gleitbretter 3, and then avoid taking place the condition of friction and unusual noise.

In a specific application, the first oil groove 34 and the second oil groove 36 are arranged in 180 ° centrosymmetry along the first direction.

As shown in fig. 3 and 14, according to a fifth embodiment of the present invention, on the basis of any of the above embodiments, further: the length L1 of the first oil groove 34 in the first direction and the depth h1 of the first oil groove 34 in the third direction satisfy the following relation: h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1; the length L2 of the second oil groove 36 in the first direction and the depth h2 of the second oil groove 36 in the third direction satisfy the following relation: h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2.

In the design, the depth h1 of the first oil groove 34 and the length L1 of the first oil groove 34 satisfy that h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1, and the oil film bearing capacity can be ensured to be better. Correspondingly, the depth h2 of the second oil groove 36 and the length L1 of the second oil groove 36 satisfy that h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2, and the oil film bearing capacity can be ensured to be better.

It should be noted that, according to the wedge oil film theory reynolds differential equation model:

wherein dp is oil film bearing capacity, dx is oil film shear direction displacement, h ₀ Is the minimum oil film thickness, and h is the oil film thickness at displacement dx. Mu is dynamic viscosity of the oil film, and U is relative movement speed of two side surfaces of the oil film.

As shown in fig. 15, according to the schematic diagram of the reynolds differential equation model, as the displacement dx increases, the oil film thickness h gradually increases, and the oil film bearing capacity dp is a trend of increasing first and then decreasing; therefore, there is a relatively high oil film thickness h1 (i.e., the first oil groove depth h 1) over the total oil film length L1 (i.e., the length L1 of the first oil groove 34), so that the oil film bearing capacity dp is relatively high near the oil film thickness h 1.

As shown in fig. 14, according to the relationship between oil film bearing capacity and the size of the first oil groove 34 or the second oil groove 36, the ratio of the depth h1 of the first oil groove 34 to the length L1 of the first oil groove 34 satisfies: when h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1, the oil film bearing capacity is better. The ratio of the depth h2 of the second oil groove 36 to the length L2 of the second oil groove 36 satisfies: when h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2, the oil film bearing capacity is better.

As shown in fig. 2 and fig. 3, according to the sixth embodiment of the present invention, on the basis of the fifth embodiment, further: in a cross section perpendicular to the first direction, the first oil groove 34 and the second oil groove 36 each have a rectangular cross section.

In this design, in a cross section perpendicular to the first direction, the cross sections of the first oil groove 34 and the second oil groove 36 are both rectangular, which facilitates the machining of the first oil groove 34 and the second oil groove 36.

As shown in fig. 4 and 5, according to a seventh embodiment of the present invention, on the basis of the fifth embodiment, further: in a projection of a plane perpendicular to the second direction along the second direction, the projection of the first oil groove 34 and the projection of the second oil groove 36 are both triangular.

In this design, along the second direction, in the projection of the plane perpendicular to the second direction, the projection of first oil groove 34 and the projection of second oil groove 36 are both triangles, which improves the lubricating effect of first oil groove 34 and second oil groove 36.

In some possible designs, first oil groove 34 includes a first ramp 340, and second oil groove 36 includes a second ramp 360; the first inclined surface 340 is inclined toward the second end surface 35, and the second inclined surface 360 is inclined toward the first end surface 33 from an end near the center of the cylinder 20 to an end far from the center of the cylinder 20.

In this design, the first oil groove 34 includes the first inclined surface 340, the second oil groove 36 includes the second inclined surface 360, from one end close to the center of the cylinder 20 to one end far away from the center of the cylinder 20, the first inclined surface 340 is inclined toward the direction of the second end surface 35, from one end close to the center of the cylinder 20 to one end far away from the center of the cylinder 20, the second inclined surface 360 is inclined toward the direction of the first end surface 33, so as to improve the lubricating effect, thereby reducing the friction power consumption of the first end surface 33 and the second end surface 35, and the noise caused by the friction of the sliding vane 3.

In some possible designs, the included angle between the first bevel 340 and the first direction is greater than or equal to 0 °, and less than or equal to 3 °; the angle between the second slope 360 and the first direction is greater than or equal to 0 ° and less than or equal to 3 °.

In this design, if the included angle between the first inclined surface 340 and the first direction is too large, the strength of the sliding plate 3 will be reduced, and if the included angle between the first inclined surface 340 and the first direction is too small, the lubrication effect will be reduced, and it will be not beneficial to reduce the friction power consumption of the first end surface 33. Specifically, the included angle between the first inclined plane 340 and the first direction is designed to be greater than or equal to 0 ° and less than or equal to 3 °, which not only can ensure the strength of the sliding blade 3, but also can ensure the reduction of friction power consumption and reduce friction noise.

Correspondingly, the strength of the sliding blade 3 is reduced if the included angle between the second inclined surface 360 and the first direction is too large, and the lubricating effect is reduced if the included angle between the second inclined surface 360 and the first direction is too small, and the reduction of the friction power consumption of the second end surface 35 is also not facilitated. Specifically, the included angle between the second inclined plane 360 and the first direction is designed to be greater than or equal to 0 degrees and less than or equal to 3 degrees, so that the strength of the sliding piece 3 can be guaranteed, and the reduction of friction power consumption and the reduction of friction noise can be guaranteed.

It is understood that the first oil groove 34 and the second oil groove 36 have the same shape and size on the basis that the first oil groove 34 and the second oil groove 36 are arranged in central symmetry along the first direction.

As shown in fig. 6 and 7, according to the eighth embodiment of the present invention, on the basis of the fifth embodiment, further: in a projection along the first direction onto a plane perpendicular to the first direction, the projection of the first oil groove 34 and the projection of the second oil groove 36 are both triangular.

In this design, along first direction, in the projection of the plane of perpendicular to first direction, the projection of first oil groove 34 and the projection of second oil groove 36 are triangle-shaped, can promote the improvement to lubricated effect of first oil groove 34 and second oil groove 36, reduce the frictional force of first terminal surface 33 and second terminal surface 35 department, and then reduce the friction power consumption of first terminal surface 33 and second terminal surface 35 department of gleitbretter 3, reduce the noise that the gleitbretter 3 friction brought.

In some possible designs, first oil groove 34 includes third angled surface 342, and second oil groove 36 includes fourth angled surface 362; the third inclined surface 342 is inclined toward the second end surface 35 from the side closer to the exhaust side 32 to the side closer to the intake side 31, and the fourth inclined surface 362 is inclined toward the first end surface 33 from the side closer to the intake side 31 to the side closer to the exhaust side 32.

In this design, the first oil groove 34 includes a third inclined surface 342, the second oil groove 36 includes a fourth inclined surface 362, and the third inclined surface 342 is inclined from the exhaust side 32 to the suction side 31, that is, the third inclined surface 342 is inclined in the thickness direction of the vane 3, so that the projection of the first oil groove 34 is triangular. The fourth inclined plane 362 is inclined from the suction side 31 to the discharge side 32, so that the projection of the second oil groove 36 is triangular, and the lubrication condition of the first end surface 33 and the second end surface 35 of the sliding vane 3 is further improved, thereby reducing the friction power consumption and reducing the abnormal noise caused by friction.

In some possible designs, the angle between the third incline 342 and the second direction is greater than or equal to 0 °, and less than or equal to 3 °; the angle between the fourth inclined surface 362 and the second direction is greater than or equal to 0 ° and less than or equal to 3 °.

In this design, an excessively large included angle between the third inclined surface 342 and the second direction may reduce the strength of the sliding piece 3, thereby reducing the service life of the sliding piece 3. If the included angle between the third inclined surface 342 and the second direction is too small, the depth of the first oil groove 34 is reduced, and the lubrication effect is reduced, and the friction power consumption of the first end surface 33 is not reduced. Therefore, the included angle between the third inclined surface 342 and the second direction is designed to be greater than or equal to 0 ° and less than or equal to 3 °, so that the strength and the service life of the sliding piece 3 can be ensured, the lubricating effect of the first oil groove 34 can be ensured, and abnormal friction between the sliding piece 3 and the first end surface 33 can be avoided.

The too large included angle between the fourth inclined plane 362 and the second direction may reduce the strength of the sliding blade 3, and further reduce the service life of the sliding blade 3. If the included angle between the fourth inclined plane 362 and the second direction is too small, the depth of the second oil groove 36 is reduced, so as to reduce the lubricating effect, and meanwhile, the friction power consumption of the first end surface 33 is not facilitated to be reduced. Therefore, the included angle between the fourth inclined plane 362 and the second direction is designed to be greater than or equal to 0 ° and less than or equal to 3 °, so that the strength and the service life of the sliding vane 3 can be ensured, the lubricating effect of the second oil groove 36 can also be ensured, and abnormal friction between the sliding vane 3 and the first end face 33 is avoided.

As shown in fig. 10 and 11, according to a ninth embodiment of the present invention, there is also provided a pump body assembly 2, including: the air cylinder 20, the air cylinder 20 has mounting grooves 200; a first support part provided at one end of the cylinder 20; the second supporting part is arranged at the other end of the air cylinder 20, and the air cylinder 20, the first supporting part and the second supporting part enclose a compression cavity; and a sliding piece 3 as set forth in any one of the first to third aspects, the sliding piece 3 being disposed in the mounting groove 200 and being capable of sliding in a first direction in the mounting groove 200, the first end face 33 corresponding to the first supporting portion, and the second end face 35 corresponding to the second supporting portion.

The utility model provides a pump body subassembly 2, including cylinder 20, first supporting part, second supporting part and gleitbretter 3, gleitbretter 3 sets up in mounting groove 200, and first terminal surface 33 corresponds with first supporting part, second terminal surface 35 corresponds with the second supporting part, through set up first oil groove 34 on first terminal surface 33, set up second oil groove 36 on second terminal surface 35, the lubricated effect between first terminal surface 33 and the first supporting part has been promoted, lubricated effect between second terminal surface 35 and the second oil groove 36, at the gliding in-process of gleitbretter 3, gleitbretter 3 and first supporting part have been reduced, frictional power dissipation between the second supporting part, reduce unusual frictional noise.

Further, an exhaust hole is provided in the first support portion, and an intake hole is provided in the cylinder 20.

According to a tenth embodiment of the present invention, on the basis of the ninth embodiment, further: the pump body assembly 2 further comprises: a roller provided in the cylinder 20; the length L of the vane 3, the length L1 of the first oil groove 34 and the eccentricity e of the roller satisfy the following relational expression: l1 is not more than L-2e-5mm; the length L of the slide sheet 3, the length L2 of the second oil groove 36 and the eccentricity e of the roller satisfy the following relational expression: l2 is not more than L-2e-5mm.

In this design, the pump body assembly 2 further comprises a roller disposed within the cylinder 20, and compression of the medium within the compression chamber is achieved by eccentric movement of the roller. Wherein, under the condition that gleitbretter 3 stretches into in the cylinder 20 longest, along first direction, the distance between the edge of first oil groove 34 and cylinder 20 internal face is sealing distance, for guaranteeing good sealed, needs to make sealing distance L-2e-L1 be more than or equal to 5mm, promptly: l1 is not more than L-2e-5mm, and correspondingly, the length L of the sliding vane 3, the length L2 of the second oil groove 36 and the eccentric amount e of the roller satisfy the following relational expression: l2 is not more than L-2e-5mm.

In some possible designs, the cylinder 20 comprises a first cylinder 202 and a second cylinder 204, the rollers comprise a first roller 22 and a second roller 23, the first support comprises a first bearing 24 and a second bearing 25, the second support comprises a bulkhead 26; the first roller 22 is arranged in the first cylinder 202, the second roller 23 is arranged in the second cylinder 204, the first bearing 24 is positioned on one side of the first cylinder 202, which is far away from the second cylinder 204, the second bearing 25 is positioned on one side of the second cylinder 204, which is far away from the first cylinder 202, and the partition 26 is arranged between the first cylinder 202 and the second cylinder 204; the pump body assembly 2 further comprises: the shaft 28 is inserted into the first cylinder 202 and the second cylinder 204, and the first roller 22 and the second roller 23 are connected to the shaft 28.

In this design, the cylinder 20 includes a first cylinder 202 and a second cylinder 204, the rollers include a first roller 22 and a second roller 23, and the bearings include a first bearing 24 and a second bearing 25. The shaft part 28 is arranged on the first cylinder 202, the second cylinder 204, the first bearing 24 and the second bearing 25 in a penetrating mode, the first roller 22 and the second roller 23 are connected with the shaft part 28, and eccentric motion is achieved under the driving of the shaft part 28.

Specifically, the first cylinder 202 and the second cylinder 204 are arranged at intervals along the axial direction of the shaft portion 28, the first bearing 24 is arranged on one side of the first cylinder 202, which is far away from the second cylinder 204, the second bearing 25 is arranged on one side of the second cylinder 204, which is far away from the first cylinder 202, the partition plate 26 is arranged between the first bearing 24 and the second bearing 25, the first bearing 24, the partition plate 26 and the first cylinder 202 enclose a compression cavity, and the second bearing 25, the partition plate 26 and the second cylinder 204 enclose another compression cavity to realize compression of media.

Further, the first bearing 24 and the second bearing 25 are respectively provided with an exhaust hole, the first cylinder 202 and the second cylinder 204 are respectively provided with an intake hole, and the shaft portion 28 is a crankshaft.

It is understood that the number of the sliding pieces 3 is two, one sliding piece 3 is disposed in the mounting groove 200 of the first cylinder 202, the other sliding piece 3 is disposed in the mounting groove 200 of the second cylinder 204, the first end face 33 of the sliding piece 3 disposed on the first cylinder 202 is in contact with the first bearing 24, the second end face 35 is in contact with the partition 26, the first end face 33 of the sliding piece 3 disposed on the second cylinder 204 is in contact with the second bearing 25, and the second end face 35 is in contact with the partition 26.

As shown in fig. 12, according to the eleventh embodiment of the present invention, there is also provided a compressor 1 including: a vane 3 as set forth in any of the above embodiments, or a pump block assembly 2 as set forth in any of the above embodiments.

The utility model discloses the compressor 1 that the third aspect provided, because of gleitbretter 3 or the pump body subassembly 2 that provide including above-mentioned arbitrary embodiment, consequently have all beneficial effect of gleitbretter 3 or pump body subassembly 2.

Specifically, as shown in fig. 12, the rotary compressor 1 includes a gas-liquid separator 12, and an upper casing 14, a main casing 16, and a lower casing 18 together constitute a closed space; also included are a rotor 100 and a stator 102, and a pump block assembly 2. The rotor 100 of the motor 10 is connected to a crankshaft to rotate the crankshaft. The stator 102 is fixed in the main casing 16, the pump body assembly 2 is also fixed in the main casing 16, the gas-liquid separator 12 provides refrigerant for the pump body assembly 2, the pump body assembly 2 is driven by the motor 10 to rotate to complete the processes of air suction, compression and exhaust, and the refrigerant is discharged through the exhaust pipe of the upper casing 14 and then enters the cycle of the refrigerating device.

According to the twelfth embodiment of the present invention, as shown in fig. 10 and fig. 11, for the present invention, the pump body assembly 2 is schematically shown, including: crankshaft, bearings (including first bearing 24 and second bearing 25), cylinder 20 (including first cylinder 202 and second cylinder 204), and partition 26. In the pump body assembly 2, the upper end surface of the first cylinder 202 is matched with the first bearing 24, the lower end surface of the second cylinder 204 is matched with the second bearing 25, and the first cylinder 202 and the second cylinder 204 are separated by the partition plate 26 and are sequentially connected to form two independent compression cavities. The cylinder device also comprises a first roller 22 and a second roller 23 which are respectively sleeved on the crankshaft and do eccentric rotation motion relative to the center of the cylinder 20, so that the working volume is changed periodically.

One end of the sliding sheet 3 close to the roller is matched with the excircle of the roller, an air suction cavity is communicated with the air suction hole in the cylinder 20, an exhaust cavity is communicated with the exhaust hole, and the air suction cavity and the exhaust cavity are separated by the sliding sheet 3. The conventional exhaust hole is generally disposed on the first bearing 24, and at the end stage of the exhaust, the high-pressure refrigerant and the refrigerant oil in the lower part of the cylinder 20 are pressed to the side of the sliding vane 3 close to the partition plate 26 due to the failure of timely discharging, which may cause the pressure on the exhaust side 32 of the sliding vane 3: the exhaust gas pressure Pd' on the side close to the partition plate 26 is larger than the exhaust gas pressure Pd on the side close to the first bearing 24. Therefore, the slide plate 3 may be inclined in the mounting groove 200 of the cylinder 20, an upper edge of the slide plate 3 near the suction side 31 may be in metal contact with an end surface of the first bearing 24, and a lower edge near the discharge side 32 may be in metal contact with an end surface of the partition plate 26. Therefore, the friction power consumption of the sliding sheet 3 is increased, abnormal sliding sheet 3 friction sound occurs, and the end surface of the bearing partition plate 26 is seriously abraded abnormally, even the compressor 1 fails.

In order to solve the above problem, the present invention provides a first oil groove 34 at the first end surface 33 of the sliding blade 3, and a second oil groove 36 at the second end surface 35. The oil groove is an avoiding sink groove designed according to the inclined direction of the sliding sheet 3, and can avoid the contact with the bearing and the end face of the partition plate 26 when the sliding sheet 3 is inclined. To achieve the relief effect, the first oil groove 34 of the vane 3 is provided on the first end surface 33 near the suction side 31, and the second oil groove 36 is provided on the second end surface 35 near the discharge side 32. The first oil groove 34 and the second oil groove 36 are 180 ° centrosymmetric with respect to the moving direction of the vane 3. At the same time, the advantage is that the first end face 33 and the second end face 35 are not specially distinguished during the assembly process of the sliding sheet 3, and the process complexity of assembly and manufacture is not caused.

As shown in fig. 11, when the vane 3 extends into the cylinder 20 to the maximum, in order to prevent the suction air of the cylinder 20 from communicating with the first oil groove 34 and the second oil groove 36 of the vane 3, a certain sealing distance is required, and the sealing distance is greater than or equal to 5mm. Therefore, the sealing distance from the inner circle of the cylinder 20 to the first oil groove 34: l-2e-L1 is more than or equal to 5mm, wherein L is the length of the slide sheet 3, e is the eccentric amount, and L1 is the length of the first oil groove 34. Therefore, the length L1 of the first oil groove 34 of the sliding sheet 3 is less than or equal to L-2e-5mm. Correspondingly, the length L2 of the second oil groove 36 is less than or equal to L-2e-5mm.

Centrosymmetric oil film pressures can be formed using wedge-shaped oil films of the first oil grooves 34 and the second oil grooves 36 to correct the inclination of the vane 3, the width T1 of the first oil grooves 34 is set to be not more than the width T of the vane 3, and the width T2 of the second oil grooves 36 is set to be not more than the width T of the vane 3, specifically, 0< -T1 > or less than 0.5T, and 0< -T2 > or less than 0.5T.

As shown in fig. 2 and 3, the first oil groove 34 and the second oil groove 36 are designed as sink grooves having a rectangular cross-sectional shape in order to facilitate the machining of the vane 3. According to a wedge oil film theory Reynolds differential equation model:

where dp is oil film bearing capacity, dx is oil film shearing direction displacement, h ₀ Is the minimum oil film thickness, and h is the oil film thickness at displacement dx. Mu is dynamic viscosity of oil film, and U is relative movement speed of two side surfaces of the oil film.

As shown in fig. 15, according to the schematic diagram of the reynolds differential equation model, as the displacement dx increases, the oil film thickness h gradually increases, and the oil film bearing capacity dp is a trend of increasing first and then decreasing; therefore, a relatively high oil film thickness h1 (i.e., the first oil groove depth h 1) exists over the total oil film length L1 (i.e., the length L1 of the first oil groove 34), so that the oil film bearing capacity dp is relatively high near the oil film thickness h 1.

According to theoretical calculation and experimental verification, as shown in fig. 14, the ratio of the depth h1 of the first oil groove 34 to the length L1 of the first oil groove 34 satisfies: when h1 is not less than 0.005L1 and not more than 0.05L1, the ratio of the depth h2 of the second oil groove 36 to the length L2 of the second oil groove 36 satisfies: the oil film bearing capacity is better when h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2.

According to the thirteenth embodiment of the present invention, as shown in fig. 4 and fig. 5, a schematic structural diagram of the sliding piece 3 is provided for this embodiment. Similarly to the vane 3 of the twelfth embodiment, the first oil groove 34 is provided in the first end surface 33 of the vane 3, and the second oil groove 36 is provided in the second end surface 35.

The difference between the thirteenth embodiment and the twelfth embodiment is that the first oil groove 34 and the second oil groove 36 have a triangular shape in a projection perpendicular to the moving direction of the vane 3, and the first oil groove 34 or the second oil groove has an inclination angle θ in a direction toward the tail of the vane 3. According to the ratio of the depth h1 of the first sink groove to the length L1 of the oil groove in the first embodiment, the inclination angle in the thirteenth embodiment:

according to the results of example one: tan theta is more than or equal to 0.005 and less than or equal to 0.05, namely theta is more than 0 and less than or equal to 3 degrees.

As shown in fig. 6 and 7, according to a fourteenth embodiment of the present invention, a first oil groove 34 is provided on the first end surface 33 of the vane 3, and a second oil groove 36 is provided on the second end surface 35.

The difference between the fourteenth embodiment and the sliding vane 3 in the thirteenth embodiment is that the direction of the inclination angle of the first oil groove 34 or the second oil groove 36 of the fourteenth embodiment is perpendicular to the moving direction of the sliding vane 3, specifically, the direction of the inclination of the first oil groove 34 or the second oil groove 36 is inclined to the side of the sliding vane 3, and the inclination angle α is the same as the requirement of the second inclination angle θ of the second embodiment, that is, 0< α ≦ 3 °

Fig. 8 and 9 show schematic diagrams of force analysis of the side surface of the slider 3, and the force analysis is as follows:

F _r1 ×sinα＝F _r2 x sin α (the gravity of the slide 3 and the supporting force are offset);

wherein F _r1 Is the oil film bearing capacity of the upper end of the sliding vane 3, F _r2 For the oil film bearing capacity at the lower end of the sliding vane 3, because the first oil groove 34 and the second oil groove 36 have the same structural size and are symmetrical along the center, therefore:

F _S +F _ps +F _r1 cosα＝F _pd +F _pd′ +F _r2 cosα

wherein, F _s Supporting force for the suction side 31 of the mounting groove 200, F _ps For suction pressure, F _pd To discharge pressure, F, near the bearing end _pd’ The discharge pressure is near the end of the separator 26.

F _t1 ＝μ ₁ ×F _r1 ，F _t2 ＝μ ₂ ×F _r2

F _t1 Is the friction force of the upper end face of the sliding vane 3, F _t2 Is the friction force of the lower end face of the slide 3, mu ₁ 、μ ₂ The coefficients of friction are respectively. Because the oil grooves on the upper end surface and the lower end surface of the sliding sheet 3 improve the lubrication, the friction coefficients mu 1 and mu 2 on the end surfaces of the sliding sheet 3 are reduced, and the friction force F _t1 、F _t2 And accordingly, frictional power consumption in contact with the first oil groove 34, the second oil groove 36 and the roller during the reciprocating motion of the vane 3 is reduced,

and the noise caused by the friction of the slide 3 is also reduced. As shown in FIG. 13, the experiment verifies that the sliding blade 3 of the present invention can reduce 5dB at 1250Hz noise frequency band of the compressor 1.

The sliding vane 3 provided by the present application is provided with a first oil groove 34 and a second oil groove 36 which are centrosymmetric at a first end surface 33 and a second end surface 35. First oil groove 34 of first end surface 33 is provided near suction side 31, and second oil groove 36 is provided at discharge side 32. By utilizing the dynamic pressure lubrication principle, the problem that the axial clearance is reduced due to the inclination or deformation of the sliding vane 3 can be effectively solved, the lubrication effect of the end face of the sliding vane 3 is improved, the friction noise of the end face of the sliding vane 3 is reduced, meanwhile, the abnormal abrasion of the end faces of the bearing and the partition plate 26 is prevented, and the reliability of the compressor 1 is improved.

In the present application, the term "plurality" is intended to mean two or more, unless explicitly defined otherwise. The terms "mounted," "connected," "secured," and the like are to be construed broadly and include, for example, connections that may be fixed or removable or integral; "connected" may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the description of the present specification, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The utility model provides a gleitbretter for pump body subassembly, pump body subassembly includes the cylinder, the cylinder is equipped with the mounting groove, its characterized in that, the gleitbretter includes:

the body is arranged in the mounting groove and can move in the mounting groove along a first direction;

along the second direction, the body includes suction side and exhaust side, along the third direction, be equipped with first oil groove on the first terminal surface of body, first oil groove is close to the suction side sets up, the second terminal surface of body is equipped with the second oil groove, the second oil groove is close to the exhaust side sets up.

2. The slider according to claim 1,

along the second direction, the thickness T of the sliding sheet and the width T1 of the first oil groove satisfy the following relational expression: 0 is less than or equal to 0.5T;

the thickness T of the sliding sheet and the width T2 of the second oil groove satisfy the following relational expression: 0T 2 is less than or equal to 0.5T.

3. The vane of claim 2, wherein the first oil groove and the second oil groove extend from one end of the body away from a center of the cylinder to the other end of the body along the first direction.

4. The sliding vane as claimed in any one of claims 1 to 3, wherein along the first direction, the first oil groove and the second oil groove are arranged in central symmetry.

5. The slider according to claim 4,

the length L1 of the first oil groove along the first direction and the depth h1 of the first oil groove along the third direction satisfy the following relational expression: h1 is more than or equal to 0.005L1 and less than or equal to 0.05L1;

the length L2 of the second oil groove along the first direction and the depth h2 of the second oil groove along the third direction satisfy the following relational expression: h2 is more than or equal to 0.005L2 and less than or equal to 0.05L2.

6. The slider of claim 5, wherein said first oil channel and said second oil channel each have a rectangular cross-section in a cross-section perpendicular to said first direction.

7. The slider of claim 5, wherein in a projection of a plane perpendicular to said second direction along said second direction, said projection of said first oil groove and said projection of said second oil groove are both triangular.

8. The slider according to claim 7,

the first oil groove comprises a first inclined surface, and the second oil groove comprises a second inclined surface;

the first inclined plane is arranged towards the second end face in an inclined mode, and the second inclined plane is arranged towards the first end face in an inclined mode.

9. The slider of claim 8,

an included angle between the first inclined surface and the first direction is greater than or equal to 0 degree and less than or equal to 3 degrees;

an included angle between the second inclined surface and the first direction is greater than or equal to 0 degrees and less than or equal to 3 degrees.

10. The slider of claim 5, wherein along said first direction, in a projection of a plane perpendicular to said first direction, a projection of said first oil channel and a projection of said second oil channel are both triangular.

11. The slider according to claim 10,

the first oil groove comprises a third inclined surface, and the second oil groove comprises a fourth inclined surface;

the third inclined surface is inclined toward the second end surface from a side close to the exhaust side to a side close to the suction side,

the fourth slope is inclined toward the first end surface from a side close to the suction side to a side close to the discharge side.

12. The slider of claim 11,

an included angle between the third inclined plane and the second direction is greater than or equal to 0 degree and less than or equal to 3 degrees;

an included angle between the fourth inclined surface and the second direction is greater than or equal to 0 degrees and less than or equal to 3 degrees.

13. A pump body assembly, comprising:

the air cylinder is provided with a mounting groove;

a first supporting part provided at one end of the cylinder;

the second supporting part is arranged at the other end of the air cylinder, and the air cylinder, the first supporting part and the second supporting part enclose a compression cavity; and

the sliding piece as claimed in any one of claims 1 to 12, wherein the sliding piece is disposed in the mounting groove and can slide in the mounting groove along a first direction, the first end face corresponds to the first supporting portion, and the second end face corresponds to the second supporting portion.

14. The pump body assembly of claim 13, further comprising:

the roller is arranged in the cylinder;

the length L of the slide sheet, the length L1 of the first oil groove and the eccentricity e of the roller satisfy the following relational expression: l1 is less than or equal to L-2e-5mm;

the length L of the slide sheet, the length L2 of the second oil groove and the eccentric amount e of the roller satisfy the following relational expression: l2 is less than or equal to L-2e-5mm.

15. The pump body assembly of claim 14,

the cylinder comprises a first cylinder and a second cylinder, the rollers comprise a first roller and a second roller, the first supporting part comprises a first bearing and a second bearing, and the second supporting part comprises a clapboard;

the first roller is arranged in the first cylinder, the second roller is arranged in the second cylinder, the first bearing is positioned on one side of the first cylinder, which is far away from the second cylinder, the second bearing is positioned on one side of the second cylinder, which is far away from the first cylinder, and the partition plate is arranged between the first cylinder and the second cylinder;

the pump body assembly further includes:

the shaft part is arranged in the penetrating mode in the first cylinder and the second cylinder, and the first roller and the second roller are connected with the shaft part.

16. A compressor, comprising:

the vane of any one of claims 1 to 12, or the pump body assembly of any one of claims 13 to 15.