Piston, compressor and refrigeration device

Abstract

The application provides a piston, a compressor and a refrigeration device, the piston is used for the compressor, the compressor comprises a suction cavity, and the piston comprises: a body, the body comprises a first end and a second end arranged in an axial direction; a support groove is arranged at the first end of the body and / or the second end of the body, and the support groove is used for being in communication with the suction cavity. Compared with the piston without the support groove in the related art, the oil film thickness can be increased, the oil film carrying capacity is improved, the lubrication between the upper end surface and / or the lower end surface of the piston and the bearing or the partition plate is significantly improved, the wear of the piston is reduced, and the service life of the piston is prolonged. The local dynamic pressure is increased, the gas pressure cavity can support the crankshaft, and then the carrying capacity of the crankshaft can be improved, and the friction loss in the operation process of the compressor is reduced. The contact area between the piston and the upper bearing, the lower bearing or the partition plate is reduced, so that the input of the compressor can be improved, and the efficiency and reliability of the compressor are improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor pistons, in particular to a piston, a compressor and a refrigeration device. BACKGROUND

[0002] At present, rotary compressors are widely used in the field of refrigeration. Specifically, a crankshaft is driven to rotate by a motor, an eccentric part of the crankshaft is provided with a self-rotating piston, upper and lower end surfaces of the piston are in contact with upper and lower bearings, and the piston also rotates eccentrically when the motor drives the crankshaft to rotate. However, there is friction in the contact area between the piston and the upper and lower bearings, the lubrication state deteriorates, rough contact occurs, and wear is caused, thereby reducing the energy efficiency and reliability of the rotary compressor. SUMMARY

[0003] Embodiments of the present application aim to at least solve one of the technical problems existing in the prior art.

[0004] To this end, a first aspect of embodiments of the present application provides a piston.

[0005] A second aspect of embodiments of the present application provides a compressor.

[0006] A third aspect of embodiments of the present application provides a refrigeration device.

[0007] Therefore, according to a first aspect of embodiments of the present application, a piston is provided, the piston being used in a compressor, the compressor comprising a suction chamber, and the piston comprising: a body comprising a first end and a second end arranged in an axial direction; and a support groove provided at the first end of the body and / or the second end of the body, the support groove being configured to communicate with the suction chamber.

[0008] The piston provided by the embodiments of the present application comprises a body and a support groove. Specifically, the compressor comprises a suction chamber. It can be understood that if the compressor is a single-cylinder compressor, the compressor comprises a first cylinder, a piston, a sliding vane, a crankshaft and a motor part. The piston is located in the first cylinder, and a cavity is formed between an outer wall of the piston and an inner wall of the first cylinder. The sliding vane is movably arranged on the first cylinder and is connected to the piston to divide the cavity into a compression chamber and the suction chamber. The crankshaft is connected to the motor part and the piston. The compressor is also provided with a suction port, which communicates with the suction chamber. In detail, under the drive of the motor part, the crankshaft drives the piston to rotate in the first cylinder, and at the same time, the piston drives the sliding vane to move relative to the first cylinder, so as to compress the refrigerant in the compression chamber.

[0009] In addition, if the compressor is a double-cylinder compressor, the compressor comprises a first cylinder and a second cylinder, and a partition plate is arranged between the first cylinder and the second cylinder.

[0010] If the compressor is a single-cylinder compressor, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing and the lower bearing respectively, and if the compressor is a double-cylinder compressor, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing and the partition plate respectively, or the lower bearing and the partition plate.

[0011] It can be understood that in the related art, when the rotary compressor is running, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing or the lower bearing or the partition plate and there is friction between them, which increases the friction loss of the rotary compressor and reduces the service life of the piston.

[0012] The body includes a first end and a second end, wherein the first end and the second end are distributed in the axial direction of the body, that is, the first end of the body is the upper end face of the piston, and the second end of the body is the lower end face of the piston. The support groove is arranged on the first end of the body and / or the second end of the body, that is, the support groove can be arranged on the upper end face of the piston, or on the lower end face of the piston, or on both the upper and lower end faces of the piston. It can be arranged according to actual needs.

[0013] The support groove is in communication with the suction cavity, that is, when the compressor is running, the crankshaft drives the piston to rotate relative to the first cylinder, and the support groove can suck in refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the slot opening of the support groove, that is, an oil film is formed at the position of the support groove on the upper end face of the piston and / or the lower end face of the piston. Compared with the piston without the support groove in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end face of the piston and / or the lower end face of the piston and the bearing or the partition plate can be significantly improved, the wear of the piston can be reduced, and the service life of the piston can be prolonged.

[0014] In addition, since the oil film is formed at the position of the support groove, and the refrigerant is sucked into the support groove, a gas pressure cavity is formed between the support groove and the oil film, the local dynamic pressure is increased, the gas pressure cavity can support the crankshaft, and the carrying capacity of the crankshaft can be improved, and the friction loss during the operation of the compressor can be reduced.

[0015] Moreover, since the support groove is arranged on the upper end face of the piston and / or the lower end face of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, thereby improving the input of the compressor and the efficiency and reliability of the compressor.

[0016] In actual application, the number of support grooves is multiple, and the multiple support grooves are uniformly arranged in the circumferential direction of the body, so as to further reduce the wear of the contact area between the piston and the upper bearing, the lower bearing or the partition plate, prolong the service life of the piston, further reduce the friction loss during the operation of the compressor, reduce the input of the compressor, and improve the efficiency and reliability of the compressor.

[0017] It should be noted that the support groove can be arranged at the first end of the body and / or the second end of the body by using a chemical etching forming method, a laser processing forming method or a high-speed processing engraving forming method. The support groove can be arranged according to actual needs.

[0018] In addition, the piston provided by the technical scheme provided in the present application also has the following additional technical features.

[0019] In a possible technical scheme, the support groove comprises at least one bending portion.

[0020] In this technical scheme, the support groove comprises at least one bending portion, that is, the groove wall of the support groove does not extend along a straight line. For example, the support groove is a V-shaped groove, and the opening ends of the V-shaped grooves are arranged in a circumferential direction when there are a plurality of support grooves. In other words, the bending portion is located between the first portion of the support groove and the second portion of the support groove, and the first portion of the support groove is arranged closer to the center of the body than the second portion of the support groove.

[0021] By arranging at least one bending portion in the support groove, the gas and oil storage effect of the support groove can be improved, and the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, thereby prolonging the service life of the piston.

[0022] Moreover, since the gas and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, and the oil film and the gas pressure cavity formed by the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0023] In addition, since the support groove is arranged on the upper end surface of the piston and / or the lower end surface of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, thereby improving the input of the compressor and improving the energy efficiency and reliability of the compressor.

[0024] It should be noted that the number of bending portions can be multiple, that is, the support groove comprises a plurality of groove segments, and the connection between adjacent two groove segments forms a bending portion, that is, the groove wall of the support groove extends in a zigzag manner, thereby further improving the gas and oil storage effect of the support groove, increasing the thickness of the oil film and realizing the secondary lubrication of the piston.

[0025] In a possible technical scheme, the support groove comprises a first groove segment and a second groove segment, wherein the second groove segment is in communication with the first groove segment and the gas suction cavity, the second groove segment is arranged closer to the outer edge of the body than the first groove segment, and the connection between the first groove segment and the second groove segment forms at least one bending portion.

[0026] In the technical solution, the support groove includes a first groove segment and a second groove segment, specifically, the second groove segment is arranged closer to the outer edge of the body than the first groove segment, that is, the second groove segment is located on the outer side of the at least one bending part, and the first groove segment is located on the inner side of the at least one bending part. The second groove segment is connected with the first groove segment, and the second groove segment is communicated with the suction cavity. During the operation of the compressor, the second groove segment can suck in refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove, that is, an oil film is formed at the position of the upper end surface of the piston and / or the lower end surface of the piston where the support groove is located. Compared with the piston without the support groove in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end surface and / or the lower end surface of the piston and the bearing or the partition plate can be significantly improved, the wear of the piston can be reduced, and the service life of the piston can be prolonged.

[0027] In addition, since the oil film is formed at the position of the support groove, and the refrigerant is sucked into the support groove, an air pressure cavity is formed between the support groove and the oil film, the local dynamic pressure is increased, the air pressure cavity can support the crankshaft, and thus the carrying capacity of the crankshaft can be improved, and the friction loss during the operation of the compressor can be reduced.

[0028] Moreover, since the support groove is arranged on the upper end surface of the piston and / or the lower end surface of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and thus the input of the compressor can be improved, the energy efficiency and the reliability of the compressor can be improved.

[0029] The connection between the first groove segment and the second groove segment forms at least one bending part, that is, the groove wall of the support groove does not extend along a straight line, so that the gas storage and oil storage effect of the support groove can be improved, the oil film thickness can be increased, and thus the wear of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0030] Moreover, since the gas storage and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston can be realized, and the air pressure cavity formed by the oil film and the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0031] It is worth noting that one end of the second groove segment away from the first groove segment penetrates through the side wall of the body, so that the refrigerant and the lubricating oil can enter the support groove during the operation of the compressor.

[0032] In a possible technical solution, the first groove segment and / or the second groove segment is an arc-shaped groove.

[0033] In the technical solution, the first groove segment is an arc-shaped groove, or the second groove segment is an arc-shaped groove, or both the first groove segment and the second groove segment are arc-shaped grooves. The actual needs can be set.

[0034] By setting the first groove segment and / or the second groove segment as an arc-shaped groove, the effect of the support groove in storing gas and oil can be further improved, the oil film thickness can be increased, and thus the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0035] Moreover, since the effect of the support groove in storing gas and oil is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, and the air pressure cavity formed by the oil film and the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0036] It can be understood that the first groove segment is an arc-shaped groove, that is, the cross-sectional shape of the groove wall of the first groove segment is a segment of an arc or a plurality of segments of arcs connected in sequence. Similarly, the second groove segment is an arc-shaped groove, that is, the cross-sectional shape of the groove wall of the second groove segment is a segment of an arc or a plurality of segments of arcs connected in sequence. It can be understood that the cross-sectional shape of the groove wall of the first groove segment is a plurality of segments of arcs connected in sequence, and / or the cross-sectional shape of the groove wall of the second groove segment is a plurality of segments of arcs connected in sequence, which can improve the effect of the support groove in storing gas and oil.

[0037] In a possible technical solution, the first groove segment includes oppositely arranged first and second groove walls, and the first and second groove walls are distributed in the circumferential direction; wherein the first groove wall and / or the second groove wall extends along the first spiral line.

[0038] In this technical solution, the first groove segment includes the first and second groove walls, wherein the first and second groove walls are oppositely arranged, and the first and second groove walls are distributed in the circumferential direction. The first groove wall and / or the second groove wall extends along the first spiral line, specifically, the first groove wall extends along the first spiral line, or the second groove wall extends along the first spiral line, or both the first and second groove walls extend along the first spiral line. The specific arrangement is made according to actual needs.

[0039] By extending the first groove wall and / or the second groove wall along the first spiral line, the effect of the support groove in storing gas and oil can be further improved, the outflow of the refrigerant and the lubricating oil into the support groove can be reduced, the oil film thickness can be further increased, and thus the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0040] Moreover, since the effect of the support groove in storing gas and oil is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, and the air pressure cavity formed by the oil film and the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0041] In a possible technical solution, the rotation direction of the first spiral line is opposite to the rotation direction of the compressor.

[0042] In the technical solution, the rotation direction of the first spiral line is opposite to the rotation direction of the compressor, and the first groove wall and / or the second groove wall extends along the first spiral line, that is, the cross-sectional shape of the first groove wall and / or the second groove wall is a part of the first spiral line. That is, the rotation direction of the cross-sectional shape of the first groove wall and / or the second groove wall is opposite to the rotation direction of the compressor.

[0043] By making the rotation direction of the first spiral line opposite to the rotation direction of the compressor, the gas and oil storage effect of the support groove can be improved, and the outflow of the refrigerant and the lubricating oil entering the support groove from the support groove can be reduced. The oil film thickness is effectively increased, the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate is further improved, and the service life of the piston is prolonged.

[0044] Moreover, since the gas and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, the gas pressure cavity formed by the oil film and the support groove can support the crankshaft, and the wear loss of the compressor is reduced.

[0045] In a possible technical solution, the equation of the first spiral line is:

[0046] x = 10.906 * e (π×0.2773245×a / 180°) * sin(a); y = 10.906 * e (π×0.2773245×a / 180°) * cos(a); wherein

[0047] e is a constant, and a is the rotation angle of the first spiral line relative to the center of the body.

[0048] In the technical solution, the equation of the first spiral line is defined. e is a constant 10, and a is the rotation angle of the first spiral line relative to the center of the body.

[0049] By extending the first groove wall and / or the second groove wall along the first spiral line, the gas and oil storage effect of the support groove can be further improved, the outflow of the refrigerant and the lubricating oil entering the support groove from the support groove can be reduced, the oil film thickness can be further increased, and the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0050] Moreover, since the gas and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, the gas pressure cavity formed by the oil film and the support groove can support the crankshaft, and the wear loss of the compressor is reduced.

[0051] The equation of the first spiral line is an equation in an x, y rectangular coordinate system with the center of the body as the origin.

[0052] In a possible technical solution, the second groove section comprises a third groove wall and a fourth groove wall arranged oppositely, and the third groove wall and the fourth groove wall are distributed along the circumferential direction; wherein the third groove wall and / or the fourth groove wall extends along the second spiral line.

[0053] In the technical solution, the second groove section comprises the third groove wall and the fourth groove wall, wherein the third groove wall and the fourth groove wall are arranged oppositely and distributed along the circumferential direction. The third groove wall and / or the fourth groove wall extends along the second spiral line, specifically, the third groove wall extends along the second spiral line, or the fourth groove wall extends along the second spiral line, or both the third groove wall and the fourth groove wall extend along the second spiral line. The arrangement is specifically according to actual needs.

[0054] By extending the third groove wall and / or the fourth groove wall along the second spiral line, the effect of the support groove in storing gas and oil can be further improved, the outflow of the refrigerant and the lubricating oil into the support groove can be reduced, the oil film thickness can be further increased, and the wear of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, thereby prolonging the service life of the piston.

[0055] Moreover, the effect of the support groove in storing gas and oil is improved, thereby further increasing the layout dynamic pressure of the piston, realizing secondary lubrication of the piston, and reducing the wear loss of the compressor while the gas pressure cavity formed by the oil film and the support groove supports the crankshaft.

[0056] In a possible technical solution, the equation of the second spiral line is:

[0057] x=14.5171×e (π×0.2773245×b / 180°) ×cos(b); y=14.5171×e (π×0.2773245×b / 180°) ×sin(b);

[0058] wherein e is a constant, and b is a rotation angle of the second spiral line relative to the center of the body.

[0059] In the technical solution, the equation of the second spiral line is defined. e is a constant 10, and b is a rotation angle of the second spiral line relative to the center of the body.

[0060] By extending the third groove wall and / or the fourth groove wall along the second spiral line, the effect of the support groove in storing gas and oil can be further improved, the outflow of the refrigerant and the lubricating oil into the support groove can be reduced, the oil film thickness can be further increased, and the wear of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, thereby prolonging the service life of the piston.

[0061] Moreover, the gas and oil storage effect of the support groove is improved, so that the layout dynamic pressure of the piston is further increased, the secondary lubrication of the piston is realized, the gas pressure cavity formed by the oil film and the support groove can support the crankshaft, and the wear loss of the compressor is reduced.

[0062] The equation of the second spiral line is an equation in an x, y rectangular coordinate system with the center of the body as the origin.

[0063] In one possible technical solution, the first groove section further includes a support wall close to the center of the body, the support wall is connected with the first groove wall and the second groove wall, and the angle a between the line connecting one end of the support wall with the center of the body and the line connecting the other end of the support wall with the center of the body satisfies 3.5°≤a≤5°.

[0064] In this technical solution, it is specified that the first groove section further includes a support wall, the support wall is arranged close to the center of the body, and the support wall is connected with the first groove wall and the second groove wall. Further, the line connecting one end of the support wall with the center of the body is a first line, the line connecting the other end of the support wall with the center of the body is a second line, and the angle between the first line and the second line is between 3.5° and 5°, that is, the circumferential width of the support wall is specified, that is, the groove width of the support groove in the circumferential direction of the body is specified.

[0065] When the compressor is running, the support groove can suck in and store refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove, that is, an oil film is formed at the position where the support groove is located on the upper end surface of the piston and / or the lower end surface of the piston. Compared with the piston without the support groove in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end surface and / or the lower end surface of the piston and the bearing or the partition plate can be significantly improved, the wear of the piston can be reduced, and the service life of the piston can be prolonged.

[0066] In addition, since the groove width of the support groove in the circumferential direction is limited to the above range, the gas and oil storage effect of the support groove can be improved, so that the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0067] Moreover, since the gas and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, the gas pressure cavity formed by the oil film and the support groove can support the crankshaft, and the wear loss of the compressor is reduced.

[0068] In addition, since the support groove is arranged on the upper end surface of the piston and / or the lower end surface of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, so that the compressor input can be improved, and the energy efficiency and reliability of the compressor can be improved.

[0069] It can be understood that if the angle between the first line and the second line is too small, on the one hand, the air pressure cavity formed by the oil film and the support groove is too small to effectively increase the local dynamic pressure, and on the other hand, the thickness of the oil film is limited, which cannot effectively improve the lubrication condition of the contact area of the upper and lower end surfaces of the piston. If the angle between the first line and the second line is too large, the gas storage and oil storage effect of the support groove will be reduced.

[0070] In a possible technical solution, the distance d between the support wall and the center of the body, the inner diameter D1 of the body and the outer diameter D2 of the body satisfy d < (D1 + D2) / 4; and / or the distance d between the support wall and the center of the body, the inner diameter D1 of the body and the outer diameter D2 of the body satisfy D1 < 2d < D2.

[0071] In this technical solution, the distance between the support wall and the center of the body, the inner diameter of the body and the outer diameter of the body satisfy d < (D1 + D2) / 4. That is, compared with the outer edge of the body, the support groove is arranged close to the center of the body, so that the gas storage and oil storage effect of the support groove can be improved, and the wear condition of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0072] Moreover, since the gas storage and oil storage effect of the support groove is improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston is realized, and the air pressure cavity formed by the oil film and the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0073] The distance between the support wall and the center of the body, the inner diameter of the body and the outer diameter of the body satisfy D1 < 2d < D2, that is, the support wall has a certain distance from the inner wall of the piston, so that the refrigerant and lubricating oil sucked into the support groove can be prevented from leaking from the side of the support groove close to the center of the body, and it is ensured that the support groove can store part of the refrigerant and lubricating oil, so as to effectively support the crankshaft while reducing the wear of the piston.

[0074] In actual application, the distance m between the end of the second groove segment away from the first groove segment and the center of the body and the outer diameter D2 of the body satisfy 2m ≥ D2, so as to ensure that the end of the second groove segment away from the first groove segment can penetrate through the side wall of the body, and it is ensured that the support groove can smoothly suck in the refrigerant and lubricating oil.

[0075] In a possible technical solution, along the axial direction of the body, the depth H of the support groove satisfies 5 μm ≤ H ≤ 20 μm.

[0076] In the technical solution, the depth of the support groove is between 5 and 20 microns in the axial direction of the body, that is, the range of the depth of the support groove is limited. During the operation of the compressor, the support groove can suck and store refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the opening of the support groove, that is, an oil film is formed at the position where the upper end surface of the piston and / or the lower end surface of the piston is located. Compared with the piston without the support groove in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end surface and / or the lower end surface of the piston and the bearing or the partition plate can be significantly improved, the wear of the piston can be reduced, and the service life of the piston can be prolonged.

[0077] In addition, since the depth of the support groove is between 5 and 20 microns, the gas storage and oil storage effects of the support groove can be improved, and thus the wear of the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston can be prolonged.

[0078] Moreover, since the gas storage and oil storage effects of the support groove are improved, the layout dynamic pressure of the piston can be further increased, the secondary lubrication of the piston can be realized, and the oil film and the gas pressure cavity formed by the support groove can support the crankshaft while reducing the wear loss of the compressor.

[0079] In addition, since the support groove is arranged on the upper end surface of the piston and / or the lower end surface of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and thus the input of the compressor can be improved, and the energy efficiency and reliability of the compressor can be improved.

[0080] It can be understood that if the depth of the support groove is too small, on the one hand, the gas pressure cavity formed by the oil film and the support groove is too small, and the local dynamic pressure cannot be effectively increased, and on the other hand, the oil film thickness is limited, and the lubrication of the contact area of the upper and lower end surfaces of the piston cannot be effectively improved. If the depth of the support groove is too deep, the gas storage and oil storage effects of the support groove will be reduced.

[0081] In a possible technical solution, the number of support grooves is multiple, and the multiple support grooves are distributed at intervals in the circumferential direction of the body.

[0082] In the technical solution, the number of support grooves is multiple, and the multiple support grooves are arranged at intervals in the circumferential direction of the body, so that the area of the formed oil film can be increased, the wear of the contact area between the upper end surface and / or the lower end surface of the piston and the upper bearing, the lower bearing or the partition plate can be further reduced, the service life of the piston can be prolonged, and the mechanical loss of the compressor during operation can be reduced.

[0083] Moreover, by arranging multiple support grooves, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be further reduced, and thus the input of the compressor can be improved, and the energy efficiency and reliability of the compressor can be improved.

[0084] In addition, since the plurality of support grooves are arranged, a plurality of air pressure cavities can be formed, the support force on the crankshaft is further increased, and the energy efficiency and reliability of the compressor are improved.

[0085] It should be noted that the number n of support grooves satisfies 10≤n≤40. Specifically, the number of support grooves can be 10 or 20 or 30 or 40. The specific number can be set according to actual needs.

[0086] In one possible technical solution, the plurality of support grooves are uniformly distributed on the body.

[0087] In this technical solution, the plurality of support grooves are uniformly distributed on the body, so that the wear of the contact area between the piston and the upper bearing, the lower bearing, or the partition plate can be further reduced, the service life of the piston is prolonged, the friction loss during the operation of the compressor is reduced, the input of the compressor is reduced, and the energy efficiency and reliability of the compressor are improved.

[0088] According to a second aspect of the present application, a compressor is provided, which comprises the piston provided in any of the above technical solutions, and thus has all the beneficial technical effects of the piston, which will not be repeated here.

[0089] Further, the compressor further comprises a first cylinder, the piston is located in the first cylinder and forms a cavity with the first cylinder; a sliding vane is movably arranged in the first cylinder and connected with the piston, the sliding vane divides the cavity into a compression chamber and a suction chamber, the suction chamber is in communication with the support groove; a crankshaft is connected with the piston; and a motor part is connected with the crankshaft.

[0090] The compressor provided in the embodiments of the present application comprises a piston, a first cylinder, a sliding vane, a crankshaft, and a motor part. Specifically, it can be understood that the piston is located in the first cylinder, and a cavity is formed between the outer wall of the piston and the inner wall of the first cylinder. The sliding vane is movably arranged on the first cylinder and connected with the piston to divide the cavity into a compression chamber and a suction chamber. The crankshaft is connected with the motor part and the piston. The compressor is also provided with a suction port in communication with the suction chamber. In detail, under the driving of the motor part, the crankshaft drives the piston to rotate in the first cylinder, and at the same time, the piston drives the sliding vane to move relative to the first cylinder, so as to compress the refrigerant in the compression chamber. This is a single-cylinder compressor.

[0091] It can be understood that if the compressor is a double-cylinder compressor, the compressor comprises a first cylinder and a second cylinder, and a partition plate is arranged between the first cylinder and the second cylinder.

[0092] If the compressor is a single-cylinder compressor, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing and the lower bearing, respectively. If the compressor is a double-cylinder compressor, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing and the partition plate, or the lower bearing and the partition plate, respectively.

[0093] It can be understood that in the related art, when the rotary compressor is running, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing or the lower bearing or the partition plate and there is friction, which increases the friction loss of the rotary compressor and reduces the service life of the piston.

[0094] The support groove is arranged on the first end of the body and / or the second end of the body, that is, the support groove can be arranged on the upper end face of the piston, or arranged on the lower end face of the piston, or arranged on both the upper and lower end faces of the piston.

[0095] The support groove is in communication with the suction cavity, that is, when the compressor is running, the crankshaft drives the piston to rotate relative to the first cylinder, the support groove can suck in the refrigerant and the lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove, that is, an oil film is formed at the position of the support groove on the upper end face of the piston and / or the lower end face of the piston. Compared with the piston without the support groove in the related art, the thickness of the oil film can be increased, the oil film carrying capacity can be improved, the lubrication between the piston upper end face and / or lower end face and the bearing or the partition plate can be significantly improved, the wear of the piston can be reduced, and the service life of the piston can be prolonged.

[0096] In addition, since the oil film is formed at the position of the support groove, and the refrigerant is sucked into the support groove, a gas pressure cavity is formed between the support groove and the oil film, the local dynamic pressure is increased, the gas pressure cavity can support the crankshaft, and thus the carrying capacity of the crankshaft can be improved, and the friction loss during the operation of the compressor can be reduced.

[0097] Moreover, since the support groove is arranged on the upper end face of the piston and / or the lower end face of the piston, the contact area between the piston and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and thus the input of the compressor can be improved, the efficiency and reliability of the compressor can be improved.

[0098] The compressor includes but is not limited to a rotary compressor.

[0099] According to a third aspect of the present application, a refrigeration equipment is provided, which comprises the compressor provided in any of the above technical solutions, and thus has all the beneficial technical effects of the compressor, which will not be repeated here.

[0100] Additional aspects and advantages of the present application will be described in the following description part, some of which will become apparent from the following description, or will be understood by those skilled in the art through the practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0101] The above and / or additional aspects and advantages of the present application will become apparent and more readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings, in which:

[0102] Figure 1Fig. 1 shows one of structural schematic diagrams of a piston according to one embodiment of the present application;

[0103] Figure 2 Fig. 2 shows another one of structural schematic diagrams of a piston according to one embodiment of the present application;

[0104] Figure 3 Fig. 3 shows a third one of structural schematic diagrams of a piston according to one embodiment of the present application;

[0105] Figure 4 Fig. 4 shows a structural schematic diagram of a compressor according to one embodiment of the present application; Figure 3 Fig. 5 shows an enlarged view of the piston of the embodiment shown in Fig. 4 at A;

[0106] Figure 5 Fig. 6 shows another one of structural schematic diagrams of a compressor according to one embodiment of the present application;

[0107] Figure 6 Fig. 7 shows a third one of structural schematic diagrams of a compressor according to one embodiment of the present application;

[0108] Figure 7 Fig. 8 shows a schematic diagram of an efficiency improvement range of a compressor according to one embodiment of the present application.

[0109] Figure 8 Fig. 9 shows a schematic diagram of an efficiency improvement range of a compressor according to one embodiment of the present application.

[0110] In the drawings, Figures 1 to 7 Correspondence between reference signs and component names in the drawings is as follows:

[0111] 100 piston, 110 body, 111 first end, 112 second end, 120 support groove, 121 bent portion, 122 first groove segment, 1221 first groove wall, 1222 second groove wall, 1223 support wall, 123 second groove segment, 1231 third groove wall, 1232 fourth groove wall, 200 compressor, 210 first cylinder, 220 crankshaft, 230 motor portion, 240 second cylinder, 250 sliding vane, 260 cavity, 261 compression cavity, 262 suction cavity. DETAILED DESCRIPTION

[0112] In order to enable a more complete understanding of the above-mentioned objects, features and advantages of the present application, the present application will be described in further detail below with reference to the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict, if possible.

[0113] In the following description, a large number of specific details are set forth in order to facilitate a full understanding of the present application, but the present application can also be implemented in other ways different from those described herein, and therefore, the scope of protection of the present application is not limited by the specific embodiments disclosed below.

[0114] Some embodiments provided by the present application will be described below with reference to Figures 1 to 8 piston 100, compressor 200 and refrigeration equipment.

[0115] In an embodiment according to the present application, as Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 、 Figure 6 and Figure 7 shown, a piston 100 is proposed, the piston 100 being used in a compressor 200, the compressor 200 comprising a suction chamber 262, the piston 100 comprising: a body 110 comprising a first end 111 and a second end 112 arranged along an axial direction; and a support groove 120 provided at the first end 111 of the body 110 and / or the second end 112 of the body 110, the support groove 120 being configured to communicate with the suction chamber 262.

[0116] The piston 100 provided by the embodiments of the present application comprises a body 110 and a support groove 120. Specifically, the compressor 200 comprises a suction chamber 262. It can be understood that, if the compressor 200 is a single-cylinder compressor, the compressor 200 comprises a first cylinder 210, a piston 100, a sliding vane 250, a crankshaft 220 and a motor portion 230. The piston 100 is located in the first cylinder 210, and a cavity 260 is formed between the outer wall of the piston 100 and the inner wall of the first cylinder 210. The sliding vane 250 is movably arranged on the first cylinder 210 and is connected to the piston 100 to divide the cavity 260 into a compression chamber 261 and the suction chamber 262. The crankshaft 220 is connected to the motor portion 230 and the piston 100. The compressor 200 is further provided with a suction port, which communicates with the suction chamber 262. In detail, under the driving of the motor portion 230, the crankshaft 220 drives the piston 100 to rotate in the first cylinder 210, and at the same time, the piston 100 drives the sliding vane 250 to move relative to the first cylinder 210, so as to compress the refrigerant in the compression chamber 261.

[0117] In addition, if the compressor 200 is a double-cylinder compressor, the compressor 200 comprises a first cylinder 210 and a second cylinder 240, and a partition plate is arranged between the first cylinder 210 and the second cylinder 240.

[0118] If the compressor 200 is a single-cylinder compressor, the upper and lower end faces of the piston 100 along the axial direction respectively contact an upper bearing and a lower bearing. If the compressor 200 is a double-cylinder compressor, the upper and lower end faces of the piston 100 along the axial direction respectively contact an upper bearing and a partition plate, or a lower bearing and a partition plate.

[0119] It can be understood that in the related art, when the rotary compressor is running, the upper and lower end faces of the piston in the axial direction are in contact with the upper bearing or the lower bearing or the partition plate and there is friction, which increases the friction loss of the rotary compressor and reduces the service life of the piston.

[0120] The body 110 includes a first end 111 and a second end 112, wherein the first end 111 and the second end 112 are distributed along the axial direction of the body 110, that is, the first end 111 of the body 110 is the upper end face of the piston 100, and the second end 112 of the body 110 is the lower end face of the piston 100. The support groove 120 is arranged on the first end 111 of the body 110 and / or the second end 112 of the body 110, that is, the support groove 120 can be arranged on the upper end face of the piston 100, or on the lower end face of the piston 100, or on both the upper and lower end faces of the piston 100. It can be arranged according to actual needs.

[0121] The support groove 120 communicates with the suction chamber 262, that is, when the compressor 200 is running, the crankshaft 220 drives the piston 100 to rotate relative to the first cylinder 210, the support groove 120 can suck in refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the slot opening of the support groove 120, that is, an oil film is formed at the position where the support groove 120 is located on the upper end face of the piston 100 and / or the lower end face of the piston 100. Compared with the piston without the support groove 120 in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the piston 100 and the bearing or the partition plate can be significantly improved, the wear of the piston 100 can be reduced, and the service life of the piston 100 can be prolonged.

[0122] In addition, since the oil film is formed at the position of the support groove 120, and the refrigerant is sucked into the support groove 120, a gas pressure chamber is formed between the support groove 120 and the oil film, the local dynamic pressure is increased, the gas pressure chamber can support the crankshaft 220, and the carrying capacity of the crankshaft 220 can be improved, and the friction loss during the operation of the compressor 200 can be reduced.

[0123] Moreover, since the support groove 120 is arranged on the upper end face of the piston 100 and / or the lower end face of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, so that the input of the compressor 200 can be improved, the energy efficiency and reliability of the compressor 200 can be improved.

[0124] In practical applications, the number of support grooves 120 is multiple, and the multiple support grooves 120 are uniformly arranged in the circumferential direction of the body 110, so as to further reduce the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate, prolong the service life of the piston 100, further reduce the friction loss of the compressor 200 during operation, reduce the input of the compressor 200, improve the energy efficiency and reliability of the compressor 200.

[0125] It is worth noting that the support grooves 120 can be formed on the first end 111 of the body 110 and / or the second end 112 of the body 110 by using a chemical etching forming method, a laser processing forming method or a high-speed processing engraving forming method. Specifically, the support grooves 120 can be arranged according to actual needs.

[0126] Figure 8 In order to arrange the support grooves 120 on the first end 111 of the body 110 and the second end 112 of the body 110, the energy efficiency of the compressor 200 is improved at different operating frequencies. By Figure 8 It can be seen that arranging the support grooves 120 on the body 110 can significantly improve the energy efficiency of the compressor 200.

[0127] As shown in Figure 1 and Figure 2 , on the basis of the above embodiments, further, the support grooves 120 include at least one bending portion 121.

[0128] In this embodiment, it is defined that the support grooves 120 include at least one bending portion 121, that is, the groove wall of the support grooves 120 is not extended along a straight line, for example, the support grooves 120 are V-shaped grooves, and when the support grooves 120 are multiple, the opening ends of the V-shaped grooves are arranged in the circumferential direction. In other words, the bending portion 121 is located between the first part of the support groove 120 and the second part of the support groove 120, and the first part of the support groove 120 is arranged closer to the center of the body 110 than the second part of the support groove 120.

[0129] By arranging at least one bending portion 121 in the support grooves 120, the gas and oil storage effect of the support grooves 120 can be improved, and thus the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0130] Moreover, since the gas and oil storage effect of the support grooves 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 is realized, and the oil film and the gas pressure cavity formed by the support grooves 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0131] In addition, since the support groove 120 is arranged at the upper end surface of the piston 100 and / or the lower end surface of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, so that the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0132] It should be noted that the number of the bending portions 121 can be multiple, that is, the support groove 120 includes multiple groove segments, and the connection between two adjacent groove segments forms a bending portion 121, that is, the groove wall of the support groove 120 extends in a zigzag manner, so that the gas storage and oil storage effects of the support groove 120 can be further improved, the oil film thickness can be increased, and the secondary lubrication of the piston 100 can be realized.

[0133] As shown in FIGS. 1, 2 and 3, the support groove 120 is arranged at the upper end surface of the piston 100 and / or the lower end surface of the piston 100. Figure 1 and Figure 2 As shown in FIGS. 1, 2 and 3, the support groove 120 is arranged at the upper end surface of the piston 100 and / or the lower end surface of the piston 100.

[0134] In this embodiment, it is defined that the support groove 120 includes the first groove segment 122 and the second groove segment 123, specifically, the second groove segment 123 is arranged closer to the outer edge of the body 110 than the first groove segment 122, that is, the second groove segment 123 is located on the outer side of the at least one bending portion 121, and the first groove segment 122 is located on the inner side of the at least one bending portion 121. The second groove segment 123 is connected with the first groove segment 122, and the second groove segment 123 communicates with the suction chamber 262. Thus, during the operation of the compressor 200, the second groove segment 123 can suck in the refrigerant and the lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove 120, that is, an oil film is formed at the position of the support groove 120 on the upper end surface of the piston 100 and / or the lower end surface of the piston 100. Compared with the piston without the support groove 120 in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end surface and / or the lower end surface of the piston 100 and the bearing or the partition plate can be significantly improved, the wear of the piston 100 can be reduced, and the service life of the piston 100 can be prolonged.

[0135] In addition, since the oil film is formed at the position of the support groove 120, and the refrigerant is sucked into the support groove 120, so that an air pressure cavity is formed between the support groove 120 and the oil film, the local dynamic pressure is increased, the air pressure cavity can support the crankshaft 220, so that the carrying capacity of the crankshaft 220 can be improved, and the friction loss during the operation of the compressor 200 can be reduced.

[0136] Moreover, since the support groove 120 is arranged at the upper end surface of the piston 100 and / or the lower end surface of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, so that the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0137] The connection between the first groove segment 122 and the second groove segment 123 forms at least one bending part 121, that is, the groove wall of the support groove 120 is not extended along a straight line, so that the gas storage and oil storage effect of the support groove 120 can be improved, the oil film thickness can be increased, and the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0138] Moreover, since the gas storage and oil storage effect of the support groove 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 can be realized, and the gas pressure cavity formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0139] It is worth noting that the end of the second groove segment 123 away from the first groove segment 122 penetrates the side wall of the body 110, so that the refrigerant and the lubricating oil can enter the support groove 120 when the compressor 200 is running.

[0140] In a specific embodiment, further, the first groove segment 122 and / or the second groove segment 123 is an arc-shaped groove.

[0141] In this embodiment, the first groove segment 122 is an arc-shaped groove, or the second groove segment 123 is an arc-shaped groove, or both the first groove segment 122 and the second groove segment 123 are arc-shaped grooves. The specific setting can be made according to actual needs.

[0142] By setting the first groove segment 122 and / or the second groove segment 123 as an arc-shaped groove, the gas storage and oil storage effect of the support groove 120 can be further improved, the oil film thickness can be increased, and the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0143] Moreover, since the gas storage and oil storage effect of the support groove 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 can be realized, and the gas pressure cavity formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0144] It is understandable that the first groove segment 122 is an arc-shaped groove, meaning that the cross-sectional shape of the groove wall of the first groove segment 122 is an arc-shaped line, or multiple arc-shaped lines connected in sequence. Similarly, the second groove segment 123 is an arc-shaped groove, meaning that the cross-sectional shape of the groove wall of the second groove segment 123 is an arc-shaped line, or multiple arc-shaped lines connected in sequence. It is understandable that having the cross-sectional shape of the groove wall of the first groove segment 122 as multiple arc-shaped lines connected in sequence, and / or having the cross-sectional shape of the groove wall of the second groove segment 123 as multiple arc-shaped lines connected in sequence, can improve the gas and oil storage effect of the support groove 120.

[0145] like Figure 1 and Figure 2 As shown, based on the above embodiment, the first groove segment 122 further includes a first groove wall 1221 and a second groove wall 1222 disposed opposite to each other, the first groove wall 1221 and the second groove wall 1222 being distributed in the circumferential direction; wherein, the first groove wall 1221 and / or the second groove wall 1222 extend along a first spiral line.

[0146] In this embodiment, the first groove segment 122 is defined as including a first groove wall 1221 and a second groove wall 1222, wherein the first groove wall 1221 and the second groove wall 1222 are disposed opposite to each other, and the first groove wall 1221 and the second groove wall 1222 are distributed in the circumferential direction. The first groove wall 1221 and / or the second groove wall 1222 extend along a first spiral line. Specifically, the first groove wall 1221 extends along the first spiral line, or the second groove wall 1222 extends along the first spiral line, or both the first groove wall 1221 and the second groove wall 1222 extend along the first spiral line. The specific configuration is determined according to actual needs.

[0147] By extending the first groove wall 1221 and / or the second groove wall 1222 along the first spiral line, the gas and oil storage effect of the support groove 120 can be further improved, the refrigerant and lubricating oil entering the support groove 120 can be reduced from flowing out of the support groove 120, the oil film thickness can be further increased, and the wear of the contact area between the piston 100 and the upper bearing, lower bearing or partition can be further improved, thus extending the service life of the piston 100.

[0148] Moreover, by improving the gas and oil storage effect of the support groove 120, the dynamic pressure of the piston 100 can be further increased, and the piston 100 can be lubricated in a secondary manner. The air pressure chamber formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0149] In one specific embodiment, the first helix rotates in the opposite direction to the rotation of the compressor 200.

[0150] In this embodiment, the direction of rotation of the first helix is ​​opposite to the rotation direction of the compressor 200. Since the first groove wall 1221 and / or the second groove wall 1222 extends along the first helix, that is, the cross-sectional shape of the first groove wall 1221 and / or the second groove wall 1222 is a part of the first helix. In other words, the rotation direction of the cross-sectional shape of the first groove wall 1221 and / or the second groove wall 1222 is opposite to the rotation direction of the compressor 200.

[0151] like Figure 1 As shown, the cross-sectional shape of the first groove wall 1221 and / or the second groove wall 1222 rotates counterclockwise, and the rotation direction of the compressor 200 should be clockwise.

[0152] like Figure 2 As shown, the rotation direction of the cross-sectional shape of the first groove wall 1221 and / or the second groove wall 1222 is clockwise. At this time, the rotation direction of the compressor 200 should be counterclockwise.

[0153] By rotating the first helix in the opposite direction to the compressor 200, the gas and oil storage capacity of the support groove 120 can be improved, reducing the outflow of refrigerant and lubricating oil that enter the support groove 120. This effectively increases the oil film thickness, further improving the wear condition of the contact area between the piston 100 and the upper bearing, lower bearing, or partition, and extending the service life of the piston 100.

[0154] Moreover, by improving the gas and oil storage effect of the support groove 120, the dynamic pressure of the piston 100 can be further increased, and the piston 100 can be lubricated in a secondary manner. The air pressure chamber formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200 and improving the energy efficiency and reliability of the compressor 200.

[0155] like Figure 2 As shown, in another specific embodiment, the equation of the first helix is ​​further: x = 10.906 × e (π×0.2773245×a / 180°) ×sin(a); y=10.906×e (π×0.2773245×a / 180°) ×cos(a); where e is a constant and a is the rotation angle of the first helix relative to the center of the body 110.

[0156] In this embodiment, the equation of the first helix is ​​defined. e is a constant 10, and a is the rotation angle of the first helix relative to the center of the body 110.

[0157] By extending the first groove wall 1221 and / or the second groove wall 1222 along the first spiral line, the effect of the support groove 120 on gas and oil storage can be further improved, the outflow of the refrigerant and the lubricating oil entering the support groove 120 from the support groove 120 can be reduced, the oil film thickness can be further increased, and thus the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0158] Moreover, as the gas and oil storage effect of the support groove 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 is realized, and the oil film and the gas pressure cavity formed by the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0159] The equation of the first spiral line is an equation in an x, y rectangular coordinate system with the center of the body as the origin, and in addition, Figure 2 In the embodiment, the rotation angle a is 71 degrees, and the specific rotation angle can be set according to actual needs.

[0160] As shown in Figure 1 and Figure 2 On the basis of the above embodiment, further, the second groove segment 123 includes oppositely arranged third groove walls 1231 and fourth groove walls 1232, and the third groove walls 1231 and the fourth groove walls 1232 are distributed in the circumferential direction; wherein the third groove walls 1231 and / or the fourth groove walls 1232 extend along the second spiral line.

[0161] In this embodiment, the second groove segment 123 includes the third groove walls 1231 and the fourth groove walls 1232, wherein the third groove walls 1231 and the fourth groove walls 1232 are oppositely arranged and distributed in the circumferential direction. The third groove walls 1231 and / or the fourth groove walls 1232 extend along the second spiral line, specifically, the third groove walls 1231 extend along the second spiral line, or the fourth groove walls 1232 extend along the second spiral line, or the third groove walls 1231 and the fourth groove walls 1232 both extend along the second spiral line. The specific setting can be made according to actual needs.

[0162] By extending the third groove wall 1231 and / or the fourth groove wall 1232 along the second spiral line, the effect of the support groove 120 on gas and oil storage can be further improved, the outflow of the refrigerant and the lubricating oil entering the support groove 120 from the support groove 120 can be reduced, the oil film thickness can be further increased, and thus the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0163] Moreover, the gas and oil storage effect of the support groove 120 is improved, so that the layout dynamic pressure of the piston 100 is further increased, the secondary lubrication of the piston 100 is realized, and the air pressure cavity formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0164] As shown in Figure 2 the equation of the second spiral line is x=14.5171×e (π×0.2773245×b / 180°) ×cos(b); y=14.5171×e (π×0.2773245×b / 180°) ×sin(b); where e is a constant, and b is the rotation angle of the second spiral line relative to the center of the body 110.

[0165] In this embodiment, the equation of the second spiral line is defined. e is a constant 10, and b is the rotation angle of the second spiral line relative to the center of the body 110.

[0166] By extending the third groove wall 1231 and / or the fourth groove wall 1232 along the second spiral line, the gas and oil storage effect of the support groove 120 can be further improved, the refrigerant and lubricating oil entering the support groove 120 can be reduced from flowing out of the support groove 120, the oil film thickness can be further increased, and thus the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing, or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0167] Moreover, the gas and oil storage effect of the support groove 120 is improved, so that the layout dynamic pressure of the piston 100 is further increased, the secondary lubrication of the piston 100 is realized, and the air pressure cavity formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0168] The equation of the second spiral line is the equation in the x, y rectangular coordinate system with the center of the body as the origin, and in addition, Figure 2 b is 23 degrees in the above embodiment, and the specific rotation angle can be set according to actual needs.

[0169] As shown in Figure 1 on the basis of the above embodiment, further, the first groove segment 122 further comprises a support wall close to the center of the body 110, the support wall is connected with the first groove wall 1221 and the second groove wall 1222, the angle a between the line connecting one end of the support wall with the center of the body 110 and the line connecting the other end of the support wall with the center of the body 110 satisfies 3.5°≤a≤5°.

[0170] In this embodiment, the first groove section 122 further comprises a support wall, which is arranged close to the center of the body 110 and connected with the first groove wall 1221 and the second groove wall 1222. Further, one end of the support wall is connected with the first line of the center of the body 110, and the other end of the support wall is connected with the second line of the center of the body 110, and the angle between the first line and the second line is between 3.5° and 5°, that is, the circumferential width of the support wall is limited, that is, the groove width of the support groove 120 in the circumferential direction of the body 110 is limited.

[0171] When the compressor 200 is running, the support groove 120 can suck in and store refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove 120, that is, an oil film is formed at the position where the support groove 120 is arranged on the upper end surface of the piston 100 and / or the lower end surface of the piston 100. Compared with the piston without the support groove 120 in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the piston 100 and the bearing or the partition plate can be significantly improved, the wear of the piston 100 can be reduced, and the service life of the piston 100 can be prolonged.

[0172] In addition, since the groove width of the support groove 120 in the circumferential direction is limited in the above range, the gas storage and oil storage effect of the support groove 120 can be improved, and thus the wear of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0173] Furthermore, since the gas storage and oil storage effect of the support groove 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 can be realized, and the oil film and the gas pressure cavity formed by the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0174] In addition, since the support groove 120 is arranged on the upper end surface of the piston 100 and / or the lower end surface of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and thus the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0175] It can be understood that if the angle between the first line and the second line is too small, on the one hand, the gas pressure cavity formed by the oil film and the support groove 120 is too small, which cannot effectively increase the local dynamic pressure, and on the other hand, the oil film thickness is limited, which cannot effectively improve the lubrication of the contact area of the upper and lower end surfaces of the piston 100. If the angle between the first line and the second line is too large, the gas storage and oil storage effect of the support groove 120 will be reduced.

[0176] As Figure 1As shown, in a specific embodiment, further, the distance d between the support wall and the center of the body 110, and the distance between the inner diameter D1 and the outer diameter D2 of the body 110, satisfy d < 1 / 2.

[0177] (D1+D2) / 4; and / or the distance d between the support wall and the center of the body 110, and the distance between the inner diameter D1 and the outer diameter D2 of the body 110, satisfying D1<2d<D2.

[0178] In this embodiment, the distance between the support wall and the center of the body 110, and the distance between the inner diameter and the outer diameter of the body 110, satisfy d < (D1 + D2) / 4. That is, by positioning the support groove 120 closer to the center of the body 110 than its outer edge, the gas and oil storage capacity of the support groove 120 can be improved. This further improves the wear condition of the contact area between the piston 100 and the upper bearing, lower bearing, or partition, extending the service life of the piston 100.

[0179] Moreover, by improving the gas and oil storage effect of the support groove 120, the dynamic pressure of the piston 100 can be further increased, and the piston 100 can be lubricated in a secondary manner. The air pressure chamber formed by the oil film and the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0180] The distance between the support wall and the center of the body 110, the inner diameter of the body 110 and the outer diameter of the body 110 satisfy D1 < 2d < D2. That is, there is a certain distance between the support wall and the inner wall of the piston 100, which can prevent the refrigerant and lubricating oil sucked into the support groove 120 from leaking from the side of the support groove 120 near the center of the body 110. This ensures that the support groove 120 can store some refrigerant and lubricating oil, reduce the wear of the piston 100 and effectively support the crankshaft 220.

[0181] In practical applications, the distance m between the end of the second groove segment 123 away from the first groove segment 122 and the center of the body 110 is such that 2m≥D2 is satisfied with the outer diameter D2 of the body 110. This ensures that the end of the second groove segment 123 away from the first groove segment 122 can penetrate the side wall of the body 110, and that the support groove 120 can smoothly draw in refrigerant and lubricating oil.

[0182] like Figure 3 As shown, in another specific embodiment, the depth H of the support groove 120 along the axial direction of the body 110 satisfies 5μm≤H≤20μm.

[0183] In this embodiment, the depth of the support groove 120 is between 5 μm and 20 μm in the axial direction of the body 110, i.e. the range of the groove depth of the support groove 120 is defined. When the compressor 200 is running, the support groove 120 can suck in and store the refrigerant and the lubricating oil, and then the sucked lubricating oil can form an oil film at the groove opening of the support groove 120, i.e. at the position where the upper end surface of the piston 100 and / or the lower end surface of the piston 100 is located, compared with the piston without the support groove 120 in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the piston 100 and the bearing or the partition plate can be significantly improved, the wear of the piston 100 can be reduced, and the service life of the piston 100 can be prolonged.

[0184] In addition, since the groove depth of the support groove 120 is between 5 μm and 20 μm, the gas storage and oil storage effect of the support groove 120 can be improved, and then the wear of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further improved, and the service life of the piston 100 can be prolonged.

[0185] Moreover, since the gas storage and oil storage effect of the support groove 120 is improved, the layout dynamic pressure of the piston 100 can be further increased, the secondary lubrication of the piston 100 can be realized, and the oil film and the gas pressure cavity formed by the support groove 120 can support the crankshaft 220 while reducing the wear loss of the compressor 200.

[0186] In addition, since the support groove 120 is arranged on the upper end surface of the piston 100 and / or the lower end surface of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and then the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0187] It can be understood that if the depth of the support groove 120 is too small, on the one hand, the gas pressure cavity formed by the oil film and the support groove 120 is too small, and the local dynamic pressure cannot be effectively increased, and on the other hand, the oil film thickness is limited, and the lubrication of the contact area of the upper and lower end surfaces of the piston 100 cannot be effectively improved. If the depth of the support groove 120 is too deep, the gas storage and oil storage effect of the support groove 120 will be reduced.

[0188] As shown in Figure 1 , Figure 2 , Figure 3 and Figure 4 , on the basis of any of the above embodiments, further, the number of the support grooves 120 is multiple, and the multiple support grooves 120 are distributed along the circumference of the body 110.

[0189] In this embodiment, the number of support grooves 120 is multiple, and the multiple support grooves 120 are arranged at intervals in the circumferential direction of the body 110, so that the area of the formed oil film can be increased, the wear condition of the contact area between the upper and / or lower end surface of the piston 100 and the upper bearing, the lower bearing or the partition plate can be further reduced, the service life of the piston 100 can be prolonged, and the mechanical loss during the operation of the compressor 200 can be reduced.

[0190] Moreover, by arranging the multiple support grooves 120, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further reduced, so that the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0191] In addition, since the multiple support grooves 120 are arranged, multiple air pressure cavities can be formed, the support force on the crankshaft 220 can be further increased, and the energy efficiency and reliability of the compressor 200 can be improved.

[0192] It is worth noting that the number n of support grooves 120 satisfies 10≤n≤40. Specifically, the number of support grooves 120 can be 10 or 20 or 30 or 40. The specific number can be set according to actual needs.

[0193] On the basis of the above-mentioned embodiments, further, the multiple support grooves 120 are uniformly distributed on the body 110.

[0194] In this embodiment, the multiple support grooves 120 are uniformly distributed on the body 110, so that the wear condition of the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be further reduced, the service life of the piston 100 can be prolonged, the friction loss during the operation of the compressor 200 can be further reduced, the input of the compressor 200 can be reduced, and the energy efficiency and reliability of the compressor 200 can be improved.

[0195] According to a second aspect of the present application, a compressor 200 is provided, which comprises the piston 100 provided in any of the above-mentioned embodiments, thus having all the beneficial technical effects of the piston 100, which will not be described herein again.

[0196] As shown in FIGS. Figure 5 , Figure 6 and Figure 7 Figure 8 , further, the compressor 200 further comprises a first cylinder 210, the piston 100 is located in the first cylinder 210 and forms a cavity 260 with the first cylinder 210; a sliding vane 250 is movably arranged in the first cylinder 210 and connected with the piston 100, the sliding vane 250 divides the cavity 260 to form a compression chamber 261 and a suction chamber 262, the suction chamber 262 is in communication with the support groove 120; a crankshaft 220 is connected with the piston 100; and a motor part 230 is connected with the crankshaft 220.

[0197] The compressor 200 provided by the embodiment of the present application comprises a piston 100, a first cylinder 210, a sliding vane 250, a crankshaft 220 and a motor part 230. Specifically, it can be understood that the piston 100 is located in the first cylinder 210, and a cavity 260 is formed between the outer wall of the piston 100 and the inner wall of the first cylinder 210. The sliding vane 250 is movably arranged on the first cylinder 210, and the sliding vane 250 is connected with the piston 100 to divide the cavity 260 into a compression cavity 261 and a suction cavity 262. The crankshaft 220 is connected with the motor part 230 and the piston 100. The compressor 200 is further provided with a suction port which is in communication with the suction cavity 262. In detail, under the driving of the motor part 230, the crankshaft 220 drives the piston 100 to rotate in the first cylinder 210, and at the same time, the piston 100 drives the sliding vane 250 to move relative to the first cylinder 210, so as to compress the refrigerant in the compression cavity 261. This is a single-cylinder compressor.

[0198] It can be understood that if the compressor 200 is a double-cylinder compressor, the compressor 200 comprises the first cylinder 210 and a second cylinder 240, and a partition plate is arranged between the first cylinder 210 and the second cylinder 240.

[0199] If the compressor 200 is a single-cylinder compressor, the upper and lower end faces of the piston 100 along the axial direction respectively contact an upper bearing and a lower bearing. If the compressor 200 is a double-cylinder compressor, the upper and lower end faces of the piston 100 along the axial direction respectively contact an upper bearing and a partition plate, or a lower bearing and a partition plate.

[0200] It can be understood that in the related art, when the rotary compressor is running, the upper and lower end faces of the piston along the axial direction contact and rub against the upper bearing or the lower bearing or the partition plate, which increases the friction loss of the rotary compressor and reduces the service life of the piston.

[0201] The support groove 120 is arranged on the first end 111 of the body 110 and / or the second end 112 of the body 110, that is, the support groove 120 can be arranged on the upper end face of the piston 100, or on the lower end face of the piston 100, or on both the upper and lower end faces of the piston 100.

[0202] The support groove 120 is in communication with the suction cavity 262, that is, when the compressor 200 is in operation, the crankshaft 220 drives the piston 100 to rotate relative to the first cylinder 210, the support groove 120 can suck in refrigerant and lubricating oil, so that the sucked lubricating oil can form an oil film at the groove opening of the support groove 120, that is, an oil film is formed at the position where the support groove 120 is located on the upper end surface of the piston 100 and / or the lower end surface of the piston 100, compared with the piston without the support groove 120 in the related art, the oil film thickness can be increased, the oil film carrying capacity can be improved, the lubrication between the upper end surface and / or the lower end surface of the piston 100 and the bearing or the partition plate can be significantly improved, the wear of the piston 100 can be reduced, and the service life of the piston 100 can be prolonged.

[0203] In addition, since the oil film is formed at the position of the support groove 120, and the support groove 120 sucks in refrigerant, a gas pressure cavity is formed between the support groove 120 and the oil film, the local dynamic pressure is increased, the gas pressure cavity can support the crankshaft 220, and thus the carrying capacity of the crankshaft 220 can be improved, and the friction loss during the operation of the compressor 200 can be reduced.

[0204] Moreover, since the support groove 120 is arranged on the upper end surface of the piston 100 and / or the lower end surface of the piston 100, the contact area between the piston 100 and the upper bearing, the lower bearing or the partition plate can be effectively reduced, and thus the input of the compressor 200 can be improved, and the energy efficiency and reliability of the compressor 200 can be improved.

[0205] The compressor 200 includes but is not limited to a rotary compressor.

[0206] According to a third aspect of the present application, a refrigeration device is provided, which comprises the compressor 200 provided in any of the above embodiments, and thus has all the beneficial technical effects of the compressor 200, which will not be described herein.

[0207] In the description of the present application, the terms "connection", "mounting", "fixing" and the like should be understood in a broad sense, for example, "connection" can be fixed connection, detachable connection or integral connection, and can be direct connection or indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the present application according to the specific circumstances.

[0208] In the description of the present application, the terms "one embodiment", "some embodiments", "a specific embodiment" and the like mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present application, the illustrative description of the above terms does not necessarily mean the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0209] The above merely provides preferred embodiments of the present application, and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the principles and technical scope of the present application shall fall into the scope of the present application.

Claims

1. A piston characterized by, The piston is used in a compressor, the compressor comprising a suction cavity, the piston comprising: a body comprising a first end and a second end arranged along an axial direction; a support groove provided at the first end of the body and / or the second end of the body, the support groove being configured to communicate with the suction cavity; the support groove comprises a first groove segment and a second groove segment; the second groove segment is in communication with the first groove segment and the suction cavity, and the second groove segment is arranged closer to an outer edge of the body than the first groove segment; the first groove segment comprises oppositely arranged first and second groove walls, the first and second groove walls being distributed along a circumferential direction; wherein the first groove wall and / or the second groove wall extends along a first helix line; an equation of the first helix line is: x = 10.906 x e (π×0.2773245×a / 180°) x = 10.906 x e y = 10.906 x e (π×0.2773245×a / 180°) x cos(a); wherein e is a constant, and a is a rotation angle of the first helix line relative to a center of the body; the second groove segment comprises oppositely arranged third and fourth groove walls, the third and fourth groove walls being distributed along a circumferential direction; wherein the third groove wall and / or the fourth groove wall extends along a second helix line; an equation of the second helix line is: x = 14.5171 x e (π×0.2773245×b / 180°) x = 14.5171 x e y = 14.5171 x e (π×0.2773245×b / 180°) x sin(b); wherein e is a constant, and b is a rotation angle of the second helix line relative to the center of the body.

2. The piston according to claim 1, wherein: the support groove comprises at least one bending portion.

3. The piston of claim 2 wherein, a junction of the first groove segment and the second groove segment forms the at least one bending portion.

4. The piston according to claim 3, wherein: the first groove segment and / or the second groove segment is an arc-shaped groove.

5. The piston according to claim 3, wherein: a rotation direction of the first helix line is opposite to a rotation direction of the compressor.

6. The piston according to claim 3, wherein: the first groove segment further comprises a support wall close to the center of the body, the support wall being connected to the first groove wall and the second groove wall, and an angle a between a line connecting one end of the support wall to the center of the body and a line connecting another end of the support wall to the center of the body satisfies 3.5°≤a≤5°.

7. The piston according to claim 6, wherein: a distance d between the support wall and the center of the body, an inner diameter D1 of the body and an outer diameter D2 of the body satisfy d<(D1+D2) / 4; and / or the distance d between the support wall and the center of the body, the inner diameter D1 of the body and the outer diameter D2 of the body satisfy D1<2d<D2.

8. The piston according to any one of claims 1 to 7, wherein: a depth H of the support groove along the axial direction of the body satisfies 5μm≤H≤20μm.

9. The piston according to any one of claims 1 to 7, wherein: a number of the support grooves is plural, and the plural support grooves are distributed along a circumferential direction of the body.

10. The piston according to claim 9, wherein: the plural support grooves are uniformly distributed on the body.

11. A compressor characterized by, comprising: the piston according to any one of claims 1 to 10; a first cylinder, the piston being located in the first cylinder and forming a cavity with the first cylinder; a sliding plate movably arranged in the first cylinder and connected to the piston, the sliding plate separating the cavity into a compression chamber and a suction chamber, the suction chamber being in communication with the support groove; a crankshaft connected to the piston; a motor portion connected to the crankshaft.

12. A refrigeration appliance characterized by, A compressor comprising the compressor of claim 11.

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