CN217233803U - Exhaust bearing for rotary compressor, pump body assembly and rotary compressor - Google Patents

Abstract

The utility model discloses an exhaust bearing, a pump body component and a rotary compressor for the rotary compressor, the rotary compressor also comprises a cylinder and a piston matched in an inner hole of the cylinder, the exhaust bearing is arranged at one axial end of the cylinder, and one end surface of the exhaust bearing facing the cylinder in the axial direction is a bearing surface, the exhaust bearing is provided with a central shaft hole and an exhaust hole, the bearing surface is provided with a circular ring area coaxially arranged with the central shaft hole, the inner ring radius R1 of the circular ring area is the difference between the inner radius of the piston and the eccentricity of the piston, the outer ring radius R2 of the circular ring area is the difference between the outer radius of the piston and the eccentricity of the piston, the bearing surface is also provided with a sinking groove which is arranged around the central shaft hole, the sinking groove extends inwards to the central shaft hole to be communicated with the central shaft hole, the groove edge of the sinking groove is positioned in the circular ring area, and the exhaust hole is positioned outside the circular ring area. According to the utility model discloses an efficiency that is used for rotary compressor's exhaust bearing can promote rotary compressor.

Description

Exhaust bearing for rotary compressor, pump body assembly and rotary compressor

Technical Field

The utility model belongs to the technical field of the compressor technique and specifically relates to a discharge bearing, pump body subassembly and rotary compressor for rotary compressor are related to.

Background

In recent years, along with implementation of relevant energy efficiency policies, efficiency improvement of a compressor becomes a problem to be solved urgently in the industry, in the current efficiency improvement means, in order to improve the energy efficiency of the compressor, generally, a piston inner diameter chamfer is enlarged to reduce friction loss between a piston and a bearing, but when the piston is matched with an exhaust bearing, the inner diameter chamfer of the piston is limited by a sealing requirement between an exhaust hole of the exhaust bearing and the piston, so that the inner diameter chamfer of the piston cannot be enlarged, specifically, under the premise that the outer diameter of the piston is not changed, the wall thickness at the end part of the piston is reduced by enlarging the inner diameter chamfer of the piston, the sealing capacity between the piston and the exhaust bearing is insufficient, high-pressure gas in an exhaust cavity is easy to leak, and therefore, if the inner diameter chamfer of the piston is enlarged, the exhaust hole needs to be moved outwards relative to a central shaft hole to increase the distance between the exhaust hole and the central shaft hole. However, the outward movement of the discharge hole of the discharge bearing may cause the energy efficiency of the compressor to be lowered, and thus the energy efficiency of the compressor may still not be effectively improved.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides an exhaust bearing for rotary compressor, exhaust bearing can reduce the wearing and tearing between exhaust bearing and the piston under the condition that does not cause the exhaust hole to move outward, promotes rotary compressor's efficiency.

The utility model discloses still provide a pump body subassembly that has above-mentioned exhaust bearing.

The utility model discloses still provide a rotary compressor who has above-mentioned pump body subassembly.

The exhaust bearing for the rotary compressor according to the embodiment of the first aspect of the present invention further comprises a cylinder and a piston fitted in the inner hole of the cylinder, the exhaust bearing is disposed at one axial end of the cylinder, and an axial side end surface of the exhaust bearing facing the cylinder is a supporting surface, the exhaust bearing is provided with a central shaft hole and an exhaust hole, the supporting surface is provided with a ring region coaxially disposed with the central shaft hole, an inner ring radius R1 of the ring region is a difference between an inner radius of the piston and an eccentric amount of the piston, an outer ring radius R2 of the ring region is a difference between an outer radius of the piston and an eccentric amount of the piston, wherein the supporting surface is further provided with a sinking groove surrounding the central shaft hole, the sinking groove extends inwards to the central shaft hole to communicate with the central shaft hole, the edge of the sink groove is positioned in the circular ring area, and the exhaust hole is positioned outside the circular ring area.

According to the utility model discloses an efficiency that is used for rotary compressor can reduce the wearing and tearing between exhaust bearing and the piston under the condition that does not cause the exhaust hole to move outward, promotes rotary compressor.

In some embodiments, a ratio of a radial distance X between a groove edge of the sink groove and a hole wall of the central shaft hole to a wall thickness W of the piston is 0.3 or more.

In some embodiments, a radial distance X between a groove edge of the sink groove and a hole wall of the central shaft hole is 1mm or more.

In some embodiments, a radial distance L between a groove edge of the sink groove and an outer annular line of the annular region is greater than or equal to 0.5 mm.

In some embodiments, the depth H of the sink is 0.2mm to 1 mm.

In some embodiments, the depth H of the sink is gradually reduced from the center to the outside, or is constant and then gradually reduced.

In some embodiments, the bottom wall of the sink is a flat surface, or an inclined surface, or a curved surface.

In some embodiments, an end of the central shaft bore facing the cylinder is formed with a bore chamfer having a radial dimension a of less than 1mm, wherein the bore chamfer engages the counterbore, or the bore chamfer is flared outwardly to form the counterbore.

In some embodiments, the sink groove is formed as an annular groove concentric with the central shaft aperture, and an inner annular edge of the sink groove coincides with a hole edge of the central shaft aperture.

In some embodiments, the hole wall of the central shaft hole has an oil groove, and two ends of the oil groove respectively extend to two axial ends of the central shaft hole.

According to the utility model discloses pump body subassembly of second aspect embodiment, pump body subassembly is used for rotary compressor and includes: cylinder, piston, bent axle, first bearing and second bearing, the bent axle is worn to locate the cylinder, the piston bush is located the bent axle just cooperate in the hole of cylinder, first bearing with the second bearing is located respectively the axial both ends of cylinder, first bearing with at least one in the second bearing is for the basis the utility model discloses the exhaust bearing of first aspect embodiment.

According to the utility model discloses pump body subassembly, through setting up the exhaust bearing of the embodiment of the above-mentioned first aspect to rotary compressor's efficiency has been improved.

According to the utility model discloses third aspect embodiment's rotary compressor includes: pump body subassembly and drive assembly, pump body subassembly is according to the utility model discloses the pump body subassembly of the embodiment of aspect two, drive assembly with the bent axle links to each other in order to drive the bent axle rotates.

According to the utility model discloses rotary compressor through setting up the pump body subassembly of the embodiment of the aspect of above-mentioned second to rotary compressor's efficiency has been improved.

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

Drawings

Fig. 1 is a cross-sectional view of a pump body assembly according to an embodiment of the present invention;

FIG. 2 is a perspective view of the exhaust bearing shown in FIG. 1;

FIG. 3 is a cross-sectional view of the exhaust bearing shown in FIG. 2;

FIG. 4 is a graph of X/W ratio versus energy efficiency according to an embodiment of the present invention;

fig. 5 is a cross-sectional view of an exhaust bearing according to another embodiment of the present invention;

fig. 6 is a cross-sectional view of an exhaust bearing according to yet another embodiment of the present invention.

Reference numerals:

a pump body assembly 100;

a first bearing 1; an exhaust bearing 10; a bearing surface 11; a circular ring area 110; a central shaft hole 12; oil grooves 121; an exhaust hole 13; a sink tank 14; a slot edge 141; a bottom wall 142; a side wall 143;

a cylinder 2; an inner bore 21; a piston 3; a second bearing 4; a crankshaft 5; a base shaft 51; an eccentric portion 52.

Detailed Description

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

The following disclosure provides many different embodiments or examples for implementing different features of the invention. In order to simplify the disclosure of the present invention, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. In addition, the present disclosure provides examples of various specific processes and materials, but one of ordinary skill in the art may recognize the applicability of other processes and/or the use of other materials.

In recent years, along with implementation of relevant energy efficiency policies, efficiency improvement of a compressor becomes a problem to be solved urgently in the industry, in the current efficiency improvement means, in order to improve the energy efficiency of the compressor, generally, a piston inner diameter chamfer is enlarged to reduce friction loss between a piston and a bearing, but when the piston is matched with an exhaust bearing, the inner diameter chamfer of the piston is limited by a sealing requirement between an exhaust hole of the exhaust bearing and the piston, so that the inner diameter chamfer of the piston cannot be enlarged, specifically, under the premise that the outer diameter of the piston is not changed, the wall thickness at the end part of the piston is reduced by enlarging the inner diameter chamfer of the piston, the sealing capacity between the piston and the exhaust bearing is insufficient, high-pressure gas in an exhaust cavity is easy to leak, and therefore, if the inner diameter chamfer of the piston is enlarged, the exhaust hole needs to be moved outwards relative to a central shaft hole to increase the distance between the exhaust hole and the central shaft hole. However, the outward movement of the discharge hole of the discharge bearing may cause the energy efficiency of the compressor to be lowered, and thus the energy efficiency of the compressor may still not be effectively improved.

In order to solve at least one of the above problems, the present application provides an exhaust bearing 10, a pump body assembly 100 having the exhaust bearing 10, and a rotary compressor having the pump body assembly 100, so as to improve the energy efficiency of the rotary compressor without causing the exhaust hole 13 to move outward.

Next, with reference to the drawings, a gas bearing 10 according to an embodiment of the first aspect of the present invention is described.

As shown in fig. 1, the exhaust bearing 10 is used for a rotary compressor, the rotary compressor comprises a cylinder 2 and a piston 3, the piston 3 is fitted in an inner hole 21 of the cylinder 2, the exhaust bearing 10 is arranged at one axial end of the cylinder 2, in combination with fig. 2-3, one axial end surface of the exhaust bearing 10 facing the cylinder 2 is a bearing surface 11, the bearing surface 11 is used for realizing sealing fit with the piston 3, and the exhaust bearing 10 is provided with a central shaft hole 12 and an exhaust hole 13.

Specifically, as shown in fig. 1, the rotary compressor further includes a crankshaft 5, the crankshaft 5 includes a base shaft 51 and an eccentric portion 52, the base shaft 51 is inserted into the central shaft hole 12 of the exhaust bearing 10 and is supported by the central shaft hole 12 to rotate smoothly, the eccentric portion 52 is located in the inner hole 21 of the cylinder 2 and rotates synchronously with the base shaft 51, and the piston 3 is located in the inner hole 21 of the cylinder 2 and is sleeved outside the eccentric portion 52 to roll along the inner hole 21 of the cylinder 2 along with the rotation of the eccentric portion 52. The end surface of the piston 3 facing the exhaust bearing 10 is in sealing fit with the bearing surface 11 to prevent the refrigerant in the cylinder 2 from leaking, and the refrigerant in the cylinder 2 is compressed and then discharged through the exhaust hole 13 of the exhaust bearing 10.

As shown in fig. 1 and 2, in the exhaust bearing 10 according to the embodiment of the present invention, the supporting surface 11 has the annular region 110 disposed coaxially with the central shaft hole 12, the inner ring radius R1 of the annular region 110 is the difference between the inner radius R3 of the piston 3 and the eccentricity E of the piston 3, i.e., R1R 3-E d3/2-E, and the outer ring radius R2 of the annular region 110 is the difference between the outer radius R1 of the piston 3 and the eccentricity E of the piston 3, i.e., R2R 1-E d1/2-E, wherein the eccentricity E of the piston 3 is the distance between the central axis of the piston 3 and the central axis of the central shaft hole 12 of the exhaust shaft hole.

Referring to fig. 1 to 3, the support surface 11 further has a sink groove 14, the sink groove 14 is disposed around the central axis hole 12, and the sink groove 14 extends inward to the central axis hole 12 to communicate with the central axis hole 12, that is, the sink groove 14 directly communicates with the central axis hole 12 without indirect communication via an oil guide groove or the like, so that the structure can be simplified. Moreover, the sink groove 14 is communicated with the central shaft hole 12, so that the sink groove 14 can be communicated with an oil supply system of the rotary compressor, heat generated by mutual friction between the piston 3 and the exhaust bearing 10 can be rapidly taken away, and the sink groove 14 can be used as an oil storage groove to play a role in improving oil film bearing capacity and storing lubricating oil, so that sufficient lubricating oil is provided for a friction pair of the piston 3 and the exhaust bearing 10, and friction loss is reduced.

Referring to fig. 1 to 3, the groove edge 141 of the sink groove 14 is located in the circular ring region 110, and the exhaust holes 13 are located outside the circular ring region 110. Herein, "inner" refers to a side close to the central axis of the central axial hole 12, and "outer" refers to a side away from the central axis of the central axial hole 12. Thus, by disposing the groove edge 141 of the sink groove 14 between the outer ring and the inner ring of the annular region 110, the friction loss between the piston 3 and the exhaust bearing 10, specifically, the contact area between the bearing surface 11 of the exhaust bearing 10 and the shaft end surface of the piston 3, can be effectively reduced, thereby reducing the friction loss when the rotary compressor is in operation.

In addition, the groove edge 141 of the sinking groove 14 is arranged on the inner side of the outer ring of the circular ring area 110, so that in the rotating process of the piston 3, the sealing fit between the piston 3 and the exhaust bearing 10 can be ensured, the leakage of the refrigerant from the sinking groove 14 is avoided, and the exhaust hole 13 is arranged outside the circular ring area 110, so that the leakage of the refrigerant is further avoided, and the smooth exhaust is ensured. Also, since the groove edge 141 of the sink groove 14 is disposed outside the inner ring of the circular ring region 110, it can be said that the sink groove 14 is not a hole chamfer formed at the end of the central shaft hole 12, friction can be reduced more effectively and a more sufficient oil reserving capacity can be provided.

From this, according to the utility model discloses exhaust bearing 10 is through setting up above-mentioned heavy groove 14 to need not to increase the internal diameter chamfer of piston 3, can not lead to exhaust hole 13 relative central shaft hole 12 to move outward, and then guaranteed that rotary compressor's efficiency can not reduce, promptly according to the utility model discloses exhaust bearing 10 through setting up above-mentioned heavy groove 14, can not receive exhaust hole 13 sealing width's of exhaust bearing 10 restriction, can reduce the friction loss simultaneously again, and the reinforcing is lubricated, and then promotes compressor's efficiency effectively.

In some embodiments of the present invention, the sink groove 14 may be formed as a circular ring groove concentric with the central shaft hole 12. That is, the outer ring and the outer ring of the sinking groove 14 are both circular, wherein the outer ring of the sinking groove 14 is the groove edge 141 of the sinking groove 14, and the inner ring of the sinking groove 14 coincides with the hole edge of the central shaft hole 12, so as to correspond to the situation that the sinking groove 14 extends inwards to the central shaft hole 12 to communicate with the central shaft hole 12. Therefore, in the rough machining process of the exhaust bearing 10, the sink groove 14 and the bearing surface 11 can be machined and formed by clamping a lathe at one time, the structure is simple, the production change of a design scheme is facilitated, the machining difficulty is reduced, the machining efficiency is improved, and the rigidity and the reliability of the exhaust bearing 10 can be improved.

Moreover, the sink groove 14 is a circular groove, and the area of the circular groove can be increased as much as possible on the premise of ensuring that the sizes meet the requirements, so that the abrasion is further reduced, and the oil storage capacity is improved. Of course, the present invention is not limited thereto, and in other embodiments of the present invention, the sinking groove 14 may also be configured in other forms, for example, an oval shape, a polygonal shape groove, a special-shaped groove, etc., which will not be described herein.

Further, it is to be noted that, when the end of the central shaft hole 12 facing the cylinder 2 is formed with a hole chamfer, the "hole edge of the central shaft hole 12" refers to the outer edge of the hole chamfer, whereas if the end of the central shaft hole 12 facing the cylinder 2 is not formed with a hole chamfer, the end edge of the central shaft hole 12 is the "hole edge of the central shaft hole 12".

For example, in some alternative examples, as shown in fig. 1-3, the radial distance X between the slot edge 141 of the sink slot 14 and the wall of the central axial bore 12 is greater than or equal to 1mm, e.g., X is 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, etc. Thereby, the friction loss between the piston 3 and the exhaust bearing 10, specifically, the contact area between the bearing surface 11 of the exhaust bearing 10 and the shaft end surface of the piston 3, can be more effectively reduced when the rotary compressor is operated, thereby reducing the friction loss. Moreover, the sink groove 14 can better improve the oil film bearing capacity and store lubricating oil, so that more sufficient lubricating oil is provided for the friction pair of the piston 3 and the exhaust bearing 10, and the friction loss is further reduced.

Further, it is to be noted that the radial distance X between the groove edge 141 of the sinker 14 and the hole wall of the central axial hole 12 is not necessarily equal everywhere depending on the difference in the shape of the sinker 14, and therefore, in the present example, any radial distance X between the groove edge 141 of the sinker 14 and the hole wall of the central axial hole 12 satisfies the above-mentioned value range.

For example, when the sink 14 is a circular ring and is disposed coaxially with the central axis hole 12, it is set that: the radius of the sinking groove 14 is r2, the diameter is d2, the radius of the central shaft hole 12 is r4, the diameter is d4, in this case, X is r2-r4 (d2-d4)/2, therefore, (d2-d4)/2 is larger than or equal to 1mm, namely, d2-d4 is larger than or equal to 2 mm. Thereby, the friction loss between the piston 3 and the exhaust bearing 10, specifically, the contact area between the bearing surface 11 of the exhaust bearing 10 and the shaft end surface of the piston 3, can be more effectively reduced when the rotary compressor is operated, thereby reducing the friction loss. Moreover, the sink groove 14 can better improve the oil film bearing capacity and store lubricating oil, so that more sufficient lubricating oil is provided for the friction pair of the piston 3 and the exhaust bearing 10, and the friction loss is further reduced.

For example, in some alternative examples, as shown in fig. 1-3, a radial distance L between a groove edge 141 of the sink groove 14 and an outer circumferential line of the annular region 110 is greater than or equal to 0.5mm, e.g., L is 0.5mm, 0.6mm, 0.7mm, 0.8mm, 1mm, 2mm, 3mm, 4mm, etc. Therefore, a certain distance is ensured between the sinking groove 14 and the outer ring line of the circular ring area 110, and the sealing between the piston 3 and the supporting surface 11 is enough, so that the problem that the high-pressure gas in the cylinder 2 leaks outwards through the sinking groove 14 to influence the energy efficiency of the rotary compressor can be effectively avoided. In other words, the parameter setting can effectively avoid the problem that the volumetric efficiency is reduced due to leakage, so that the energy efficiency of the rotary compressor is reduced.

Further, it should be noted that, depending on the shape difference of the sinker 14, the radial distance L between the groove edge 141 of the sinker 14 and the outer circumferential line of the annular region 110 is not necessarily equal everywhere, and therefore, in the present example, any radial distance L between the groove edge 141 of the sinker 14 and the outer circumferential line of the annular region 110 satisfies the above-mentioned value range.

For example, when the sink 14 is a circular ring and is disposed coaxially with the central axis hole 12, it is set that: the radius of the sinking groove 14 is r2, the diameter is d2, the outer radius of the piston 3 is r1, the outer diameter is d1, the eccentric amount of the piston 3 is E, and at this time, L is r1-r2-E is (d1-d2)/2-E, so that (d1-d2)/2-E is more than or equal to 0.5 mm. Therefore, a certain distance is ensured between the sinking groove 14 and the outer ring line of the circular ring area 110, and the sealing between the piston 3 and the supporting surface 11 is enough, so that the problem that the high-pressure gas in the cylinder 2 leaks outwards through the sinking groove 14 to influence the energy efficiency of the rotary compressor can be effectively avoided. In other words, the parameter setting can effectively avoid the problem that the volumetric efficiency is reduced due to leakage, so that the energy efficiency of the rotary compressor is reduced.

For example, in some alternative examples, as shown in fig. 1-3, the ratio of the radial distance X between the groove edge 141 of the sink groove 14 to the hole wall of the central shaft hole 12 to the wall thickness W of the piston 3 is equal to or greater than 0.3, e.g., X/W is 0.3, 0.4, 0.5, 0.6, 0.7, etc. Therefore, according to experimental verification, the energy efficiency of the rotary compressor can be effectively improved. Furthermore, according to experimental verification, when the ratio of the radial distance X between the groove edge 141 of the sink groove 14 and the hole wall of the central shaft hole 12 to the wall thickness W of the piston 3 is greater than or equal to 0.5, the energy efficiency of the rotary compressor is improved more significantly.

Further, it is worth mentioning that the radial distance X between the groove edge 141 of the sink groove 14 and the hole wall of the central shaft hole 12 is not necessarily equal everywhere according to the difference in shape of the sink groove 14, and therefore, in the present example, the ratio of any radial distance X between the groove edge 141 of the sink groove 14 and the hole wall of the central shaft hole 12 to the wall thickness W of the piston 3 satisfies the above-described ratio.

For example, when the sink 14 is a circular ring and is disposed coaxially with the central axis hole 12, it is set that: the diameter of the sinking groove 14 is d2, the diameter of the central shaft hole 12 is d4, the outer diameter of the piston 3 is d1, the inner diameter of the piston 3 (i.e. the diameter of the eccentric part 52) is d3, and at this time, X is (d2-d4)/2, and W is (d1-d 3/2), so X/W is (d2-d4)/d1-d3 is not less than 0.3. From this, according to experimental verification, can improve rotary compressor's energy efficiency comparatively effectively. Also, according to experimental verification, when the ratio of the radial distance X between the groove edge 141 of the sink groove 14 and the hole wall of the central shaft hole 12 to the wall thickness W of the piston 3 is equal to or greater than 0.5, the energy efficiency of the rotary compressor is improved more significantly. The X/W is a ratio of the width of the sink 14 to the wall thickness of the piston 3, and tests show that when the ratio is less than 0.3, the energy efficiency improvement effect is not obvious, when the ratio is greater than or equal to 0.3, the energy efficiency improvement effect begins to appear, and when the ratio is greater than or equal to 0.5, the energy efficiency improvement effect reaches a relatively ideal state, for example, as shown in fig. 4.

In addition, it is worth noting that the units of the above-mentioned parameters, such as d1, d2, d3, d4, E, etc., are all mm, and are not repeated herein.

For example, in some alternative examples, as shown in fig. 2-3, the depth H of the sink 14 is 0.2mm to 1 mm. For example, the depth H of the sink 14 may be 0.2mm, 0.4mm, 0.6mm, 0.8mm, 1mm, and so forth. Thereby, energy efficiency and reliability of the rotary compressor can be further improved. Specifically, if the depth of the sink 14 is less than 0.2mm, the oil storage capacity is insufficient, so that the structure has a reduced function of supplying sufficient lubricating oil to the friction pair, and if the depth of the sink 14 is greater than 1mm, the rigidity of the exhaust bearing 10 is affected, which results in increased deformation of the exhaust bearing 10 after being subjected to a force, increased wear between the central shaft hole 12 of the exhaust bearing 10 and the crankshaft 5, and increased friction loss between the bearing surface 11 of the exhaust bearing 10 and the shaft end surface of the piston 3, which easily causes reliability problems.

Note that, the depth H of the sinker 14 is not necessarily equal everywhere depending on the shape of the sinker 14, and therefore, in this example, the depth H at any position of the sinker 14 satisfies the above-described range.

Specifically, the depth of the sink groove 14 may be equal everywhere or may be different everywhere, for example, in some embodiments, as shown in fig. 5 and fig. 6, the depth H of the sink groove 14 may gradually decrease from the center to the outside, so that the oil storage amount may be sufficient on the premise that the outer diameter of the sink groove 14 meets the requirement, thereby achieving a better lubrication effect, and ensuring that the rigidity of the exhaust bearing 10 is better to some extent. For another example, in some other embodiments, as shown in fig. 1-3, the depth H of the sink 14 may be constant from the center to the outside and then gradually decreases. Therefore, the processing is convenient, the processing difficulty is reduced, and the rigidity of the exhaust bearing 10 can be better ensured.

Specifically, the inner wall of the sink tank 14 is not limited in form, and the inner wall of the sink tank 14 may specifically include only the bottom wall 142, or may further include the bottom wall 142 of the sink tank 14 and the side wall 143 of the sink tank 14. For example, the bottom wall 142 and the side wall 143 may be flat, curved, or a combination of flat surfaces at different angles, or a combination of flat surfaces and curved surfaces, or a combination of curved surfaces and curved surfaces, and so on. For example, in some embodiments, the bottom wall 142 of the sink 14 can be flat (e.g., as shown in fig. 3), or sloped (e.g., as shown in fig. 5), or curved (e.g., as shown in fig. 6), etc. For example, when the depth H of the sink 14 is constant from the center to the outside and then gradually decreases, the bottom wall 142 of the sink 14 may be a flat surface and the side wall 143 of the sink 14 may be an inclined surface, and for example, when the depth H of the sink 14 is gradually decreased from the center to the outside, the bottom wall 142 of the sink 14 may be a curved surface or an inclined surface and the sink 14 does not include the side wall 143. Thereby, a flexible design and machining of the sinker 14 can be achieved.

In some embodiments of the present invention, as shown in fig. 3, the end of the central shaft hole 12 facing the cylinder 2 may be formed with a hole chamfer having a radial dimension a smaller than 1 mm. Alternatively, the bore chamfer may engage the counter sink 14 as shown in FIG. 3, or alternatively, the bore chamfer may be flared outwardly to form the counter sink 14 as shown in FIGS. 5 and 6, such that the radial distance X between the slot edge 141 of the counter sink 14 and the wall of the bore 12 may be greater than or equal to 1 mm. Therefore, the processing and the forming are convenient. Of course, the present invention is not limited thereto, and in the other embodiments of the present invention, the end of the central shaft hole 12 facing the cylinder 2 may not have a hole chamfer, for example, the hole chamfer shown in fig. 3 may be eliminated, and the description thereof is omitted.

In some embodiments of the present invention, as shown in fig. 2 and 3, the hole wall of the central shaft hole 12 may have an oil groove 121 thereon, and both ends of the oil groove 121 extend to both axial ends of the central shaft hole 12 respectively. For example, when the axial direction of the central shaft hole 12 is the up-down direction, one end of the oil groove 121 extends to the upper end of the central shaft hole 12, and the other end of the oil groove 121 may extend to the lower end of the central shaft hole 12, thereby increasing the amount of the lubricating oil, improving the lubricating effect better, reducing the friction loss between the crankshaft 5 and the exhaust bearing 10, and further improving the energy efficiency of the rotary compressor. Moreover, due to the communication between the sink groove 14 and the central shaft hole 12, the two ends of the oil groove 121 can be utilized to extend to the two axial ends of the central shaft hole 12 respectively, so that the lubricating oil in the oil groove 121 can be supplied to the sink groove 14 sufficiently without providing other oil supply channels, and the design and the processing can be simplified.

Alternatively, oil groove 121 may extend along a spiral line, so that the length of oil groove 121 may be further increased, thereby increasing the amount of oil stored and the lubrication effect. Of course, the present invention is not limited thereto, and in other embodiments of the present invention, the oil groove 121 may also extend along a straight line, etc., so as to simplify the processing.

Next, a pump body assembly 100 according to an embodiment of the second aspect of the present invention is described with reference to the drawings.

As shown in fig. 1, the pump body assembly 100 is for a rotary compressor, and may include: cylinder 2, piston 3, bent axle 5, first bearing 1 and second bearing 4, bent axle 5 wears to locate cylinder 2, and bent axle 5 and cooperation are located in the hole 21 of cylinder 2 to 3 covers of piston, and first bearing 1 and second bearing 4 are located the axial both ends of cylinder 2 respectively, and at least one in first bearing 1 and the second bearing 4 is according to the utility model discloses exhaust bearing 10 in the embodiment of the first aspect. From this, according to the utility model discloses pump body subassembly 100, owing to be provided with according to the utility model discloses the exhaust bearing 10 of embodiment to rotary compressor's efficiency can be improved.

In addition, the pump body assembly 100 according to an embodiment of the present invention is not limited thereto, and may further include a slide, an elastic member, a bolt, and the like, for example. In addition, according to the utility model discloses pump body subassembly 100 can be for the single cylinder form that cylinder 2 quantity is one, also can be for the multi-cylinder form that cylinder 2 quantity is a plurality of, does not limit here and give unnecessary detail. For simplicity of description, the pump block assembly 100 will be described in a single cylinder format as an example, and it will be apparent to those skilled in the art from the following description that the pump block assembly 100 is a multi-cylinder format.

As shown in fig. 1, the first bearing 1 and the second bearing 4 are supported at both ends of the eccentric portion 52 of the crankshaft 5 in the axial direction, respectively, so that the crankshaft 5 rotates stably. The piston 3 is sleeved on the eccentric part 52 of the crankshaft 5, one end of the sliding sheet is abutted to the peripheral surface of the piston 3, the other end of the sliding sheet is inserted into the sliding sheet groove of the cylinder 2, and one end of the sliding sheet, which is far away from the piston 3, is provided with an elastic piece, so that the sliding sheet is always abutted to the peripheral surface of the piston 3. And a compression cavity is defined between the first bearing 1, the cylinder 2, the piston 3 and the second bearing 4, the compression cavity is positioned between the first bearing 1 and the second axial direction and between the peripheral surface of the piston 3 and the hole wall of the inner hole 21 of the cylinder 2, and the sliding sheet is matched with the piston 3 so as to further divide the compression cavity into a suction cavity and an exhaust cavity which are positioned on two sides of the sliding sheet. When the rotary compressor works, the driving assembly drives the crankshaft 5 to rotate, the piston 3 is driven by the eccentric part 52 of the crankshaft 5 to rotate, and the sliding sheet reciprocates in the sliding sheet groove under the action of the piston 3 and the elastic part, so that air suction of an air suction cavity and air exhaust of an air exhaust cavity are realized.

The axial end face of the first bearing 1 facing the cylinder 2 is a first supporting end face, the axial end face of the second bearing 4 facing the cylinder 2 is a second supporting end face, and in the movement process of the piston 3, the end faces on two axial sides of the piston 3 are respectively matched with the first supporting end face and the second supporting end face so as to prevent refrigerants in the air suction cavity and the air exhaust cavity from leaking to the inner ring area of the piston 3. Because of the sealing fit, when the piston 3 is in operation, friction is formed between the two axial end faces of the piston 3 and the first and second bearing end faces, respectively.

In the present embodiment, the first bearing 1 is set as the exhaust bearing 10, and therefore, the first supporting end surface is the supporting surface 11 of the exhaust bearing 10, and the present application reduces the contact area between the first supporting end surface and the piston 3 by providing the sunk groove 14 on the supporting surface 11, thereby reducing the friction loss, and moreover, the provision of the sunk groove 14 can be used as an oil storage groove, thereby improving the oil film bearing capacity and storing the lubricating oil, thereby reducing the wear. In addition, the sink groove 14 may be communicated with the oil supply system through the central shaft hole 12, so that heat generated by mutual friction between the piston 3 and the first supporting end surface may be rapidly taken away, thereby more effectively improving energy efficiency and reliability of the rotary compressor.

Next, a rotary compressor according to an embodiment of a third aspect of the present invention is described.

In an embodiment of the present invention, the rotary compressor may include: pump body subassembly 100 and drive assembly, pump body subassembly 100 is according to the utility model discloses the pump body subassembly 100 of second aspect embodiment, and drive assembly links to each other with bent axle 5 in order to drive bent axle 5 and rotate. From this, according to the utility model discloses rotary compressor, owing to be provided with according to the utility model discloses the pump body subassembly 100 to rotary compressor's efficiency can be improved.

It should be noted that, the specific configuration of the driving assembly is not limited, and for example, the driving assembly may be a driving motor, and the driving motor may be an inner rotor type motor or an outer rotor type motor, wherein the inner rotor type motor may include a rotor and a stator disposed outside the rotor, the rotor is connected to the crankshaft 5, wherein the outer rotor type motor may include a rotor and a stator disposed inside the rotor, and the rotor is connected to the crankshaft 5, which is not described herein again.

Of course, the rotary compressor according to the embodiment of the present invention is not limited to this, and for example, may further include a housing assembly, and the pump body assembly 100 and the driving assembly are both disposed in the housing assembly, wherein, the specific configuration of the housing assembly is also not limited, and for example, may be composed of multiple sections of housings, which is not described herein. Further, it is understood that other configurations and operations of the rotary compressor according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.

In a specific embodiment of the utility model, adopt the rotary compressor of 48cc discharge capacity (model AT 480), R410A is selected for the refrigerant, 380V 50Hz is adopted to the power, under the ASH operating mode, test exhaust bearing 10 to the influence of efficiency, in the experiment one, exhaust bearing 10 is last not to set up heavy groove 14, in the experiment two, exhaust bearing 10 is last to set up heavy groove 14, and the radial distance L between the outer loop line of groove edge 141 to the ring region 110 of heavy groove 14 is 0.8mm, the degree of depth H of heavy groove 14 is 0.5mm, the test result is as follows, after setting up heavy groove 14, rotary compressor's energy efficiency has promoted 3.4pts, the noise slightly improves, the efficiency promotion effect is obvious.

In the description of the present invention, it is to be understood that the terms "axial," "radial," "circumferential," and the like refer to an orientation or positional relationship based on that shown in the drawings, which is merely for convenience of description and simplicity of description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims (12)

1. An exhaust bearing for a rotary compressor, the rotary compressor further comprising a cylinder and a piston fitted in an inner hole of the cylinder, the exhaust bearing being provided at an axial end of the cylinder, and an axial side end surface of the exhaust bearing facing the cylinder being a bearing surface, the exhaust bearing having a central shaft hole and an exhaust hole, characterized in that,

the bearing surface is provided with an annular area which is coaxial with the central shaft hole, the inner ring radius R1 of the annular area is the difference between the inner radius of the piston and the eccentric amount of the piston, the outer ring radius R2 of the annular area is the difference between the outer radius of the piston and the eccentric amount of the piston,

still have heavy groove on the holding surface, heavy groove encircles center shaft hole sets up, heavy inslot extends extremely center shaft hole in order with center shaft hole intercommunication, the groove edge that sinks the groove is located in the ring region, the exhaust hole is located outside the ring region.

2. The exhaust bearing of claim 1, wherein a ratio of a radial distance X between a groove edge of the sink groove and a wall of the central shaft hole to a wall thickness W of the piston is 0.3 or more.

3. The exhaust bearing of claim 1, wherein a radial distance X between a groove edge of the sink groove and a hole wall of the central shaft hole is 1mm or more.

4. The exhaust bearing of claim 1, wherein a radial distance L between a groove edge of the sink groove and an outer annular line of the annular region is 0.5mm or greater.

5. The exhaust bearing according to claim 1, wherein the depth H of the sink groove is 0.2mm to 1 mm.

6. The exhaust bearing of claim 1, wherein the depth H of the sink groove is gradually reduced from the center to the outside, or is constant and then gradually reduced.

7. The exhaust bearing of claim 1, wherein the bottom wall of the sink is planar, or beveled, or curved.

8. The exhaust bearing of claim 1, wherein an end of the central shaft bore facing the cylinder is formed with a bore chamfer having a radial dimension a of less than 1mm, wherein the bore chamfer engages the counter sink or the bore chamfer is flared outwardly to form the counter sink.

9. The exhaust bearing of claim 1, wherein the counter sink is formed as an annular groove concentric with the central shaft bore, and an inner annular edge of the counter sink coincides with a bore edge of the central shaft bore.

10. The exhaust bearing according to any one of claims 1 to 9, wherein the hole wall of the central shaft hole has an oil groove, and both ends of the oil groove extend to both axial ends of the central shaft hole, respectively.

11. A pump body assembly for a rotary compressor, comprising: the exhaust bearing comprises a cylinder, a piston, a crankshaft, a first bearing and a second bearing, wherein the crankshaft penetrates through the cylinder, the piston is sleeved on the crankshaft and is matched in an inner hole of the cylinder, the first bearing and the second bearing are respectively positioned at two axial ends of the cylinder, and at least one of the first bearing and the second bearing is the exhaust bearing according to any one of claims 1-10.

12. A rotary compressor, comprising: the pump body assembly according to claim 11, and a drive assembly connected to the crankshaft for driving the crankshaft to rotate.

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