Patent Description:
At present, crankshaft lubrication for a pump body of a compressor in a related art is generally achieved by supplying oil through a spiral oil applying blade mounted in an inner hole in the lower part of an auxiliary shaft of a crankshaft. Lubrication for a main shaft part and the auxiliary shaft part of the crankshaft is mainly achieved by supplying oil through oil guide grooves formed in inner holes of a main bearing and an auxiliary bearing. The dimension and the position design of the oil guide grooves is an important factor that affects crankshaft lubrication; if the design is improper, insufficient oil supply to the main shaft part of the crankshaft will be caused when the compressor is running, thereby resulting in worsened wear of the crankshaft and main bearing. In several cases, the service life of the compressor even may be affected as a result of problems such as pump body blockage, crankshaft fracture and the like. <CIT> relates generally to a pump body assembly, a compressor and heat-exchange equipment. <CIT> relates generally to an electric compressor having high performance and reliability.

In the following, each of the described methods, apparatuses, embodiments, examples, and aspects, which do not fully correspond to the invention as defined in the claims is thus not according to the invention and is, as well as the whole following description, present for illustration purposes only or to highlight specific aspects or features of the claims. Embodiments not falling under the scope of the claims should be interpreted as examples useful for understanding the invention. The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

In view of this, according to a first aspect of the present invention, a pump body assembly according to claim <NUM> is provided.

According to a second aspect of the present invention, a compressor according to claim <NUM> is provided.

According to a third aspect of the present invention, an air conditioner according to claim <NUM> is provided.

In view of this, according to one aspect of the present invention, a pump body assembly is provided, comprising: a crankshaft including a main shaft part and an eccentric part connected with the main shaft part, wherein a distance between a center line of the main shaft part and a center line of the eccentric part is e; a main bearing including a hub part, wherein the main shaft part penetrates through a through hole in the hub part, and a first oil guide groove is formed in the hole wall of the through hole; and a cylinder body, wherein a sliding vane slot and a center hole are formed in the cylinder body, the crankshaft penetrates through the center hole, the main bearing is located at one side of the cylinder body, a radius of the center hole is R, and a difference value between R and e is r. A value range of an included angle formed of a first connection line between a center of the center hole and that of the sliding vane slot in the same projection plane and a second connection line between a termination point of the first oil guide groove at one end of the hub part away from the eccentric part and a center of the through hole is smaller than or equal to the sum of 17π/<NUM> and <MAT>, and greater than or equal to the sum of 5π/<NUM> and <MAT>. An included angle of the pump body assembly is a rotation angle corresponding to the rotation of the crankshaft from the first connection line to the second connection line.

The pump body assembly provided by the present invention includes a crankshaft, a main bearing and a cylinder body, wherein the crankshaft includes a main shaft part and an eccentric part connected with the main shaft part, and an eccentric distance e between a center line of the main shaft part and a center line of the eccentric part is provided; the main bearing includes a hub part with a through hole therein, wherein a first oil guide groove is formed in the hole wall of the through hole, the main shaft part penetrates through the through hole, and a center hole and a sliding vane slot in communication with the center hole are formed in the cylinder body, the crankshaft penetrates through the center hole of the cylinder body, the main bearing is arranged at one side of the cylinder body, a radius of the center hole is R, and a difference value between R and e is r. In the same projection plane in the axial direction of the center hole, the center of the center hole is connected with the center of the sliding vane slot to form a first connection line, and a termination point of the first oil guide groove at one end away from the eccentric part is connected with the center of the through hole in the hub part to form a second connection line; in the same projection plane in the axial direction of the center hole, the first connection line between the center of the center hole in the cylinder body and the center of the sliding vane slot is defined as a <NUM>-degree direction, and an angle increase direction is the same as a rotation direction of crankshaft; and a rotation angle corresponding to the rotation of the crankshaft from the first connection line to the second connection line is an included angle, which is greater than or equal to <MAT> and smaller than or equal to 17π/<NUM>+ <MAT>.

By defining a relationship among the included angle formed of the first connection line between the center of the center hole in the same projection plane in the axial direction of the center hole and the center of the sliding vane slot and the second connection line between the termination point of the first oil guide groove at one end of the hub part away from the eccentric part and the center of the through hole, crankshaft eccentricity e and the radius R of the center hole of the cylinder body, oil supply of the oil grooves is more sufficient and an oil film on each portion of the main shaft part of the crankshaft is more uniform when the crankshaft deforms under action of external load to be in contact with the main bearing, thereby effectively improving the problem of the abnormal wear of the main shaft part of the crankshaft, avoiding the problems such as pump body blockage, crankshaft fracture and the like, and prolonging the service life of the compressor.

In addition, the pump body assembly in the embodiment provided by the present invention further has the following additional technical features:.

In the embodiment, the pump body assembly is provided with one cylinder body, and the value range of the included angle is smaller than and equal to the sum of 8π/<NUM> and <MAT>, and greater than or equal to the sum of 2π/<NUM> and <MAT>.

In the embodiment, when the pump body assembly is a single-cylinder pump body assembly, the value range of the included angle meets the following formula: the included angle being greater than or equal to <MAT> and smaller than or equal to <MAT>. In such a manner, oil supply of the oil grooves is more sufficient when the crankshaft deforms under action of external load to be in contact with the main bearing.

In any of the embodiments, the pump body assembly is provided with at least two cylinder bodies, and the value range of the included angle is smaller than and equal to the sum of 7π/<NUM> and <MAT>, and greater than or equal to the sum of 2π/<NUM> and <MAT>.

In the embodiment, when the pump body assembly is a multi-cylinder pump body assembly, the value range of the included angle meets the following formula: the included angle being greater than or equal to <MAT> and smaller than or equal to <MAT>. In such a manner, oil supply of the oil grooves is more sufficient when the crankshaft deforms under action of external load to be in contact with the main bearing. Furthermore, in a process that a multi-cylinder compressor rotates around the crankshaft, gas force has a plurality of peak values, and there is greater difference between a direction (corresponding to a direction of centrifugal force) of a balance block and a single-cylinder compressor, so that the optimal range of the termination angle of the oil groove of the multi-cylinder compressor is not completely consistent with that of the single-cylinder compressor; and the positions of the oil grooves are different according to different numbers of the cylinder bodies, so that the best lubrication effect is achieved.

In any of the embodiments, the value range of the included angle formed of the first connection line in the same projection plane of the pump body assembly and a third connection line between a termination point at another end of the first oil guide groove and the center of the through hole is smaller than or equal to 2π and greater than or equal to 3π/<NUM>.

In the embodiment, the third connection line is formed by the termination point at another end of the first oil guide groove and the center of the through hole, and the included angle formed of the first connection line and the third connection line greatly affects the reliability of the crankshaft. By setting the value range of the included angle formed of the first connection line and the third connection line to be smaller than or equal to 2π and greater than or equal to 3π/<NUM>, oil supply of the oil grooves is more sufficient and the reliability of the main shaft part of the crankshaft is better when the crankshaft deforms under action of external load to be in contact with the main bearing.

In any of the embodiments, the pump body assembly further includes a first annular groove which is formed in the hole wall of the through hole, and the first oil guide groove is communicated with the first annular groove.

In the embodiment, the pump body assembly further includes a first annular groove formed in the hole wall of the through hole, and the first annular groove is communicated with the first oil guide groove; an annular groove is formed in the inner surface of the hub part of the main bearing, so that oil supply amount between the hub part of the main bearing and the main shaft part of the crankshaft may be further increased. In such a manner, a lubricating condition of the main shaft part of the crankshaft is improved. And meanwhile, contact area between the hub part of the main bearing and the main shaft part of the crankshaft is reduced through the first annular groove, so that viscous resistance and friction loss between the two are reduced, and the performance of the compressor is improved.

In any of the embodiments, the pump body assembly further includes an oil passing hole which is formed in the first annular groove, and the oil passing hole penetrates through the hub part in a radial direction.

In the embodiment, the oil passing hole is formed in the first annular groove, and penetrates through the hub part in the radial direction, so that circulating performance between lubricating oil on the inner surface of a hub and lubricating oil outside may be improved, and a temperature of the lubricating oil in the hub is reduced to certain extent. In such a manner, the lubricating reliability of the main shaft part of the crankshaft is further improved.

In any of the embodiments, a radial depth of the first annular groove of the pump body assembly is smaller than or equal to <NUM>.

In the embodiment, the radial depth of the first annular groove is limited to be not greater than <NUM>, such that the first annular groove slightly affects the rigidity of the whole pump body assembly.

In the embodiment, the pump body assembly further includes a second annular groove which is formed in the main shaft part and is located in an area where the main shaft part is matched with the hub part.

In the embodiment, a second annular groove is formed in the area where the main shaft part is matched with the hub part, such that oil supply amount between the hub part of the main bearing and the main shaft part of the crankshaft may be further increased. In such a manner, a lubricating condition of the main shaft part of the crankshaft is improved. And meanwhile, contact area between the hub part of the main bearing and the main shaft part of the crankshaft is reduced through the second annular groove, so that viscous resistance and friction loss between the two are reduced, and the performance of the compressor is improved.

In any of the embodiments, a radial depth of the second annular groove of the pump body assembly is smaller than or equal to <NUM>.

In the embodiment, the radial depth of the second annular groove is limited to be not greater than <NUM>, such that the integral rigidity of the crankshaft is guaranteed. In such a manner, the second annular groove is ensured to slightly affect the rigidity of the whole pump body assembly.

In any of the embodiments, the crankshaft of the pump body assembly further includes an auxiliary shaft part, and the eccentric part is located between the main shaft part and the auxiliary shaft part; the pump body assembly further includes an auxiliary bearing; the main bearing is sleeved on the main shaft part; the auxiliary bearing is sleeved on the auxiliary shaft part; the pump body assembly further comprises a second oil guide groove which is formed in a through hole of the auxiliary bearing.

In the embodiment, the crankshaft further includes an auxiliary shaft part which is connected with the eccentric part; bearings include a main bearing and an auxiliary bearing, which are respectively located at the two sides of the cylinder body; the main bearing is matched with the main shaft part, the auxiliary bearing is matched with the auxiliary shaft part, a first oil guide groove is formed in the main bearing and a second oil guide groove is formed in the through hole of the auxiliary bearing. The first oil guide groove is formed in the through hole of the main bearing, and the second oil guide groove is formed in the through hole of the auxiliary bearing, such that lubricating oil enters a position between the main bearing and the main shaft part and a position between the auxiliary bearing and the auxiliary shaft part. In such a manner, a lubricating condition between the main shaft part and the auxiliary shaft part of the crankshaft is improved.

In any of the embodiments, the pump body assembly further includes: the value range of the included angle formed of the first connection line between the center of the center hole in the same projection plane and the center of the sliding vane slot and a fourth connection line between a termination point of the second oil guide groove at one end of the hub part close to the eccentric part and the center of the through hole is smaller than or equal to 2π and greater than or equal to 3π/<NUM>.

In the embodiment, in the same projection plane in the axial direction of the center hole, the termination point of the second oil guide groove at one end of the hub part close to the eccentric part and the center of the through hole define the fourth connection line; when the value range of the included angle formed of the first connection line and the fourth connection line is smaller than or equal to 2π and greater than or equal to 3π/<NUM>, oil supply of the oil groove is more sufficient and the integral reliability of the crankshaft is better when the crankshaft deforms under action of external load to be in contact with the auxiliary bearing.

In any of the embodiments, the first oil guide groove and the second oil guide groove of the pump body assembly are both spiral oil guide grooves.

In the embodiment, the first oil guide groove and the second oil guide groove are both spiral oil guide grooves; in a running process of the compressor, flowing of lubricating oil is facilitated, such that the inner wall surface of the main bearing and the inner wall surface of the auxiliary bearing supply lubricating oil to the main shaft part and the auxiliary shaft part of the crankshaft under action of the spiral oil guide grooves. In such a manner, the main shaft part and the auxiliary shaft part of the crankshaft are both lubricated.

In the embodiment, spiral directions of the first oil guide groove and the second oil guide groove of the pump body assembly are the same as a rotation direction of the crankshaft.

In the embodiment, the spiral direction of the first oil guide groove and the spiral direction of the second oil guide groove are the same as the rotation direction of the crankshaft, such that lubricating oil may enter the first oil guide groove and the second oil guide groove under action of centrifugal force, and oil supply amount between the hub of the main bearing and the shaft part of the crankshaft is increased; the spiral direction of the first oil guide groove is the same as that of the second oil guide groove, such that the lubricating oil enters each position wherein the crankshaft is in contact with the hub part.

In any of the embodiments, a value range of a width of the first oil guide groove of the pump body assembly is smaller than or equal to <NUM> and greater than or equal to <NUM>; and a value range of a depth of the first oil guide groove is smaller than or equal to <NUM> and greater than or equal to <NUM>.

In the embodiment, when the value range of the width of the first oil guide groove is greater than or equal to <NUM> and smaller than or equal to <NUM> and the value range of the depth of the first oil guide groove is greater than or equal to <NUM> and smaller than or equal to <NUM>, the lubricating reliability of the crankshaft is better.

According to a second aspect of the present invention, a compressor is provided, including the pump body assembly according to any of the embodiments. As a result, the compressor has all the beneficial effects of the pump body assembly, which will not be detailed here.

According to a third aspect of the present invention, an air conditioner is provided, including the pump body assembly or the compressor according to any of the embodiments. As a result, the air conditioner has all the beneficial effects of the pump body assembly or the compressor, which will not be detailed here.

The corresponding relationship between the reference signs and component names in <FIG> is as follows:
<NUM> pump body assembly; <NUM> crankshaft; <NUM> main shaft part; <NUM> eccentric part; <NUM> auxiliary shaft part; <NUM> main bearing; <NUM> first oil guide groove; <NUM> hub part; <NUM> flange part; <NUM> first connection line; <NUM> second connection line; <NUM> through hole; <NUM> cylinder body; <NUM> sliding vane slot; <NUM> center hole; <NUM> crankshaft rotation direction; <NUM> third connection line; <NUM> first annular groove; <NUM> oil passing hole; <NUM> piston; <NUM> sliding vane; and <NUM> second annular groove.

To understand above purposes, features and advantages of the present invention more clearly, the present invention is further detailed below in combination with drawings and specific embodiments. It should be explained that if there is no conflict, embodiments in the present invention and the features in the embodiments can be mutually combined.

In the following description, many specific details are set forth in order to fully understand the present invention. However, the present invention can also be implemented in other ways than described herein. Therefore, the protection scope of the present invention is not limited by the following specific embodiments disclosed.

A pump body assembly <NUM>, a compressor, and an air conditioner according to some embodiments of the present invention will be described below with reference to <FIG>.

According to an embodiment of the present invention, a pump body assembly <NUM> is provided, including: a crankshaft <NUM> including a main shaft part <NUM> and an eccentric part <NUM> connected with the main shaft part <NUM>, wherein a distance between a center line of the main shaft part <NUM> and a center line of the eccentric part <NUM> is e; a main bearing <NUM> including a hub part <NUM>, wherein the main shaft part <NUM> penetrates through a through hole <NUM> in the hub part <NUM>, and a first oil guide groove <NUM> is formed in the hole wall of the through hole <NUM>; and a cylinder body <NUM>, wherein a sliding vane slot <NUM> and a center hole <NUM> are formed in the cylinder body <NUM>, the crankshaft <NUM> penetrates through the center hole <NUM>, the main bearing <NUM> is located at one side of the cylinder body <NUM>, a radius of the center hole <NUM> is R, and a difference value between R and e is r. A value range of an included angle formed of a first connection line <NUM> between the center of the center hole <NUM> and that of the sliding vane slot <NUM> in the same projection plane and a second connection line <NUM> between a termination point of the first oil guide groove <NUM> at one end of the hub part <NUM> away from the eccentric part <NUM> and the center of the through hole <NUM> is smaller than or equal to sum of 17π/<NUM> and <MAT>, and greater than or equal to sum of 5π/<NUM> and <MAT>.

As shown in <FIG>, the pump body assembly <NUM> provided by the present invention includes a crankshaft <NUM>, a main bearing <NUM> and a cylinder body <NUM>, wherein the crankshaft <NUM> includes a main shaft part <NUM> and an eccentric part <NUM> connected with the main shaft part <NUM>, and a distance between a center line of the main shaft part <NUM> and a center line of the eccentric part <NUM> is e; the main bearing <NUM> includes a hub part <NUM> with a through hole <NUM> therein and a flange part <NUM>, wherein a first oil guide groove <NUM> is formed in the hole wall of the through hole <NUM>, the main shaft part <NUM> penetrates through the through hole <NUM>, and a center hole <NUM> and a sliding vane slot <NUM> in communication with the center hole <NUM> are formed in the cylinder body <NUM>, the crankshaft <NUM> penetrates through the center hole <NUM> of the cylinder body <NUM>, the main bearing <NUM> is arranged at the one side of the cylinder body <NUM>, a radius of the center hole <NUM> is R, and a difference value between R and e is r. In the same projection plane in the axial direction of the center hole <NUM>, a first connection line <NUM> between the center of the center hole <NUM> in the cylinder body <NUM> and the center of the sliding vane slot <NUM> is defined as a <NUM>-degree direction, and the center of the center hole <NUM> is connected with the center of the sliding vane slot <NUM> to form the first connection line <NUM>; a termination point of the first oil guide groove <NUM> at one end away from the eccentric part <NUM> is connected with the center of the through hole <NUM> in the hub part <NUM> to form a second connection line <NUM>; an angle increase direction is the same as a crankshaft rotation direction <NUM>; and a rotation angle corresponding to the rotation of the crankshaft <NUM> from the first connection line <NUM> to the second connection line <NUM> is an included angle, which is greater than or equal to <MAT> and smaller than or equal to 17π/<NUM>+ <MAT>.

By defining a relationship among the included angle formed of the first connection line <NUM> between the center of the center hole <NUM> in the same projection plane in the axial direction of the center hole and the center of the sliding vane slot <NUM> and the second connection line <NUM> between the termination point of the first oil guide groove <NUM> at one end of the hub part <NUM> away from the eccentric part <NUM> and the center of the through hole <NUM>, crankshaft <NUM> eccentricity e and the radius R of the center hole <NUM> of the cylinder body <NUM>, oil supply of the oil grooves is more sufficient and an oil film on each portion of the main shaft part <NUM> of the crankshaft <NUM> is more uniform when the crankshaft <NUM> deforms under action of external load to be in contact with the main bearing <NUM>, thereby effectively improving the problem of the abnormal wear of the main shaft part <NUM> of the crankshaft <NUM>, avoiding the problems such as pump body blockage, crankshaft fracture and the like, and prolonging the service life of the compressor.

The lubrication principle and wear mechanism of the compressor crankshaft of the existing structure are briefly analyzed and explained below in conjunction with <FIG>:.

As shown in <FIG>, the compressor pump body assembly includes a crankshaft <NUM>', bearings and a cylinder body <NUM>'. The crankshaft <NUM>' includes a main shaft part <NUM>', an eccentric part <NUM>' and an auxiliary shaft part <NUM>'. The bearings include a main bearing and an auxiliary bearing, the main bearing includes a main bearing profile <NUM>' and a main bearing flange <NUM>', and the main shaft part <NUM>' is arranged at the main bearing profile <NUM>'; the auxiliary bearing includes an auxiliary bearing hub <NUM>' and an auxiliary bearing flange <NUM>', the auxiliary shaft part <NUM>' is arranged at the auxiliary bearing hub <NUM>', and a spiral oil applying blade <NUM>' mounted in an inner hole of the auxiliary shaft part <NUM>' of the crankshaft <NUM>' generally supplies oil to lubricate the crankshaft <NUM>'. When the crankshaft <NUM>' rotates, the oil applying blade <NUM>' upwards supplies lubricating oil on the bottom of a compressor oil tank, transmits the lubricating oil into an inner hole of the main bearing and an inner hole of the auxiliary bearing through the main shaft part <NUM>' of the crankshaft <NUM>' and the oil hole <NUM>' of the auxiliary shaft part <NUM>'; and then, under action of the spiral oil guide grooves in the inner wall surfaces of the main and auxiliary bearings, the lubricating oil is supplied to the main shaft part <NUM>' and the auxiliary shaft part <NUM>' of the crankshaft so as to achieve lubricating effect on the main shaft part <NUM>' and the auxiliary shaft part <NUM>' of the crankshaft <NUM>'. When the compressor is running, the crankshaft <NUM>' deforms to tilt under action force of gas pressure, radial magnetic tension and centrifugal force of a balance block, and then is in contact with the bearings to generate contact stress. If the contact stress is too great or positions of bearing oil guide grooves are unreasonable, the crankshaft will generate abnormal wear with the bearings due to insufficient oil supply.

The relationship among the termination point of the oil guide groove of the main bearing and the crankshaft eccentricity, the radius of the cylinder body <NUM> and the like is deeply analyzed and researched in combination with a stress condition of the crankshaft based on the lubricating principle and wear mechanism of the crankshaft so as to disclose a novel design structure adopting a main bearing <NUM> as a spiral oil guide groove, which is simple to implement and remarkable in effect. It should be noted that the structure of the present invention is applicable to compressors using different refrigerants and lubricating oils.

In one embodiment of the present invention, the pump body assembly <NUM> is provided with one cylinder body <NUM>, and the value range of the included angle is smaller than and equal to the sum of 8π/<NUM> and <MAT>, and greater than or equal to the sum of 2π/<NUM> and <MAT>.

In the embodiment, when the pump body assembly <NUM> is a single-cylinder pump body assembly, the value range of the included angle meets the following formula: the included angle being greater than or equal to <MAT> and smaller than or equal to <MAT>. In such a manner, oil supply of the oil grooves is more sufficient when the crankshaft <NUM> deforms under action of external load to be in contact with the main bearing <NUM>.

In one embodiment of the present invention, the pump body assembly <NUM> is provided with at least two cylinder bodies <NUM>, and the value range of the included angle is smaller than and equal to the sum of 7π/<NUM> and <MAT>, and greater than or equal to the sum of 2π/<NUM> and <MAT>.

In the embodiment, when the pump body assembly <NUM> is a multi-cylinder pump body assembly, the value range of the included angle meets the following formula: the included angle being greater than or equal to <MAT> and smaller than or equal to <MAT>. In such a manner, oil supply of the oil grooves is more sufficient when the crankshaft <NUM> deforms under action of external load to be in contact with the main bearing <NUM>. Furthermore, in a process that a multi-cylinder compressor rotates around the crankshaft, gas force has a plurality of peak values, and there is greater difference between a direction (corresponding to a direction of centrifugal force) of a balance block and a single-cylinder compressor, so that the optimal range of the termination angle of the oil groove of the multi-cylinder compressor is not completely consistent with that of the single-cylinder compressor; and the positions of the oil grooves are different according to different numbers of the cylinder bodies, so that the best lubrication effect is achieved.

In one embodiment of the present invention, as shown in <FIG>, the value range of the included angle formed of the first connection line <NUM> in the same projection plane of the pump body assembly <NUM> and a third connection line <NUM> between a termination point of the first oil guide groove <NUM> at another end and the center of the through hole <NUM> is smaller than or equal to 2π and greater than or equal to 3π/<NUM>.

In the embodiment, the third connection line <NUM> is formed by the termination point at another end of the first oil guide groove <NUM> and the center of the through hole <NUM>, and the included angle formed of the first connection line <NUM> and the third connection line <NUM> greatly affects the reliability of the crankshaft <NUM>. By setting the value range of the included angle formed of the first connection line <NUM> and the third connection line <NUM> to be smaller than or equal to 2π and greater than or equal to 3π/<NUM>, oil supply of the oil grooves is more sufficient and the reliability of the main shaft part <NUM> of the crankshaft <NUM> is better when the crankshaft <NUM> deforms under action of external load to be in contact with the main bearing <NUM>.

In one embodiment of the present invention, as shown in <FIG>, the pump body assembly <NUM> further includes a first annular groove <NUM> which is formed in the hole wall of the through hole <NUM>, and the first oil guide groove <NUM> is communicated with the first annular groove <NUM>.

In the embodiment, the pump body assembly <NUM> further includes a first annular groove <NUM> formed in the hole wall of the through hole <NUM>, and the first annular groove <NUM> is communicated with the first oil guide groove <NUM>; an annular groove is formed in the inner surface of the hub part <NUM> of the main bearing, oil supply amount between the hub part <NUM> of the main bearing and the main shaft part <NUM> of the crankshaft <NUM> may be further increased, so that a lubricating condition of the main shaft part <NUM> of the crankshaft <NUM> is improved. And meanwhile, contact area between the hub part <NUM> of the main bearing <NUM> and the main shaft part <NUM> of the crankshaft <NUM> is reduced through the first annular groove <NUM>, so that viscous resistance and friction loss between the two are reduced, and the performance of the compressor is improved.

In one embodiment of the present invention, as shown in <FIG>, the pump body assembly <NUM> further includes an oil passing hole <NUM> which is formed in the first annular groove <NUM>, and the oil passing hole <NUM> penetrates through the hub part122 in a radial direction.

In the embodiment, the oil passing hole <NUM> is formed in the first annular groove <NUM>, and penetrates through the hub part <NUM> in the radial direction, so that circulating performance between lubricating oil on the inner surface of a hub and lubricating oil outside may be improved, and a temperature of the lubricating oil in the hub is reduced to certain extent. In such a manner, the lubricating reliability of the main shaft part <NUM> of the crankshaft <NUM> is further improved.

In one embodiment of the present invention, a radial depth of the first annular groove <NUM> of the pump body assembly <NUM> is smaller than or equal to <NUM>.

In the embodiment, the radial depth of the first annular groove <NUM> is limited to be not greater than <NUM>, such that the first annular groove <NUM> slightly affects the rigidity of the whole pump body assembly <NUM>.

In one embodiment of the present invention, as shown in <FIG>, the pump body assembly <NUM> further includes a second annular groove <NUM> which is formed in the main shaft part <NUM> and is located in an area wherein the main shaft part <NUM> is matched with the hub part <NUM>.

In the embodiment, a second annular groove <NUM> is formed in the area wherein the main shaft part <NUM> is matched with the hub part <NUM>, such that oil supply amount between the hub part <NUM> of the main bearing <NUM> and the main shaft part <NUM> of the crankshaft <NUM> may be further increased. In such a manner, a lubricating condition of the main shaft part <NUM> of the crankshaft <NUM> is improved. And meanwhile, contact area between the hub part <NUM> of the main bearing <NUM> and the main shaft part <NUM> of the crankshaft <NUM> is reduced through the second annular groove <NUM>, so that viscous resistance and friction loss between the two are reduced, and the performance of the compressor is improved.

In one embodiment of the present invention, a radial depth of the second annular groove <NUM> of the pump body assembly <NUM> is smaller than or equal to <NUM>.

In the embodiment, the radial depth of the second annular groove <NUM> is limited to be not greater than <NUM>, such that the integral rigidity of the crankshaft is guaranteed. In such a manner, the second annular groove <NUM> slightly affects the rigidity of the whole pump body assembly <NUM>.

In one embodiment of the present invention, the crankshaft <NUM> of the pump body assembly <NUM> further includes an auxiliary shaft part <NUM>, and the eccentric part <NUM> is located between the main shaft part <NUM> and the auxiliary shaft part <NUM>; the pump body assembly <NUM> further includes an auxiliary bearing; the main bearing is sleeved on the main shaft part <NUM>;the auxiliary bearing is sleeved on the auxiliary shaft part <NUM>; and the pump body assembly <NUM> further comprises a second oil guide groove (not shown in the figure) which is formed in a through hole <NUM> of the auxiliary bearing.

In the embodiment, as shown in <FIG>, the crankshaft <NUM> further includes an auxiliary shaft part <NUM> which is connected with the eccentric part <NUM>; the bearings include a main bearing <NUM> and an auxiliary bearing, which are respectively located at the two sides of the cylinder body <NUM>; the main bearing <NUM> is matched with the main shaft part <NUM>, the auxiliary bearing is matched with the auxiliary shaft part <NUM>, the first oil guide groove <NUM> is formed in the through hole of the main bearing and the second oil guide groove is formed in the through hole of the auxiliary bearing. The first oil guide groove <NUM> is formed in the through hole of the main bearing, and the second oil guide groove is formed in the through hole of the auxiliary bearing, such that lubricating oil enters a position between the main bearing and the main shaft part <NUM> and a position between the auxiliary bearing and the auxiliary shaft part <NUM>. In such a manner, a lubricating condition between the main shaft part <NUM> and the auxiliary shaft part <NUM> of the crankshaft <NUM> is improved.

In one embodiment of the present invention, the pump body assembly <NUM> further includes: the value range of the included angle formed of the first connection line <NUM> between the center of the center hole <NUM> in the same projection plane and the center of the sliding vane slot <NUM> and a fourth connection line between a termination point of the second oil guide groove at one end of the hub part <NUM> close to the eccentric part <NUM> and the center of the through hole <NUM> is smaller than or equal to 2π and greater than or equal to 3π/<NUM>.

In the embodiment, in the same projection plane in the axial direction of the center hole <NUM>, the termination point of the second oil guide groove at one end of the hub part <NUM> close to the eccentric part <NUM> and the center of the through hole <NUM> define the fourth connection line; when the value range of the included angle formed of the first connection line <NUM> and the fourth connection line is smaller than or equal to 2π and greater than or equal to 3π/<NUM>, oil supply of the oil groove is more sufficient and integral reliability of the crankshaft is better when the crankshaft <NUM> deforms under action of external load to be in contact with the auxiliary bearing.

In one embodiment of the present invention, the first oil guide groove <NUM> and the second oil guide groove of the pump body assembly <NUM> are both spiral oil guide grooves.

In the embodiment, the first oil guide groove <NUM> and the second oil guide groove are both spiral oil guide grooves; in a running process of the compressor, flowing of lubricating oil is facilitated, such that the inner wall surface of the main bearing <NUM> and the inner wall surface of the auxiliary bearing supply lubricating oil to the main shaft part <NUM> and the auxiliary shaft part <NUM> of the crankshaft <NUM> under action of the spiral oil guide grooves. In such a manner, the main shaft part <NUM> and the auxiliary shaft part <NUM> of the crankshaft <NUM> are both lubricated.

In one embodiment of the present invention, spiral directions of the first oil guide groove <NUM> and the second oil guide groove of the pump body assembly <NUM> are the same as the rotation direction of the crankshaft <NUM>.

In the embodiment, the spiral direction of the first oil guide groove <NUM> and the spiral direction of the second oil guide groove are the same as the rotation direction of the crankshaft <NUM>, such that lubricating oil may enter the first oil guide groove <NUM> and the second oil guide groove under action of centrifugal force, and oil supply amount between the hub of the main bearing <NUM> and the shaft part of the crankshaft <NUM> is increased; the spiral direction of the first oil guide groove <NUM> is the same as that of the second oil guide groove, such that the lubricating oil enters each position wherein the crankshaft <NUM> is in contact with the hub part <NUM>.

In one embodiment of the present invention, the value range of the width of the first oil guide groove <NUM> of the pump body assembly <NUM> is smaller than or equal to <NUM> and greater than or equal to <NUM>; and the value range of the depth of the first oil guide groove <NUM> is smaller than or equal to <NUM> and greater than or equal to <NUM>.

In the embodiment, as shown in <FIG>, when the value range of the width a of the first oil guide groove <NUM> is greater than or equal to <NUM> and smaller than or equal to <NUM>, the value range of the depth b of the first oil guide groove <NUM> is greater than or equal to <NUM> and smaller than or equal to <NUM>, lubricating reliability of the crankshaft <NUM> is better.

In a specific embodiment, a direction that a connection line of the center of the cylinder body <NUM> of the gas cylinder and the center of the sliding vane slot <NUM> points to the sliding vane slot <NUM> is defined as a <NUM>-degree direction; as shown in <FIG>, the angle increase direction is the same as the crankshaft rotation direction <NUM>. Unless otherwise specified, all angles are based on this. In the embodiment, a piston <NUM> is sleeved outside the eccentric part <NUM> of the crankshaft <NUM>, and the outer radius dimension of the piston <NUM> is r equal to R-e.

As shown in <FIG>, M is a center point of the cylinder body <NUM> of the gas cylinder, N is a center point of the piston <NUM>, A is a point of tangency of the piston <NUM> and the sliding vane <NUM> (for the sake of simplicity, swing of the point A of tangency is neglected in the following calculation with smaller errors), B is a point of tangency of the piston <NUM> and the cylinder body <NUM> of the gas cylinder, θ is a rotation angle of the crankshaft, α is a directional angle of resultant force of gas force, β is an included angle between AM and AN, δ is an included angle between AN and AB, r is an outer radius of the piston <NUM>, and e is crankshaft eccentricity, wherein the angle dimensions above meet the following geometric relations:
<MAT>.

By combining formulas (<NUM>), (<NUM>) and (<NUM>), get:
<MAT>.

According to related calculation for lubrication of the main bearing <NUM>, an angle, in a practical direction of motion under action of gas force, of the crankshaft <NUM> may advance by about π/<NUM> relative to the direction angle α of the gas force, and thus, the angle, in the practical direction of motion, of the crankshaft <NUM> is as follows:
<MAT>.

For existing compressor types including refrigerants such as R22, R410A, R32, R290, R134a and the like, a gas exhaust angle (a rotation angle of the crankshaft <NUM> when gas exhaust is just started after refrigerants are compressed) is generally about 7π/<NUM>, which is substituted into θ in the formula (<NUM>) to obtain an angle, in the direction of motion of the crankshaft, corresponding to the gas exhaust angle as follows:
<MAT>.

The gas force on the crankshaft <NUM> is the maximum value during gas exhaust, and radial motion of the crankshaft <NUM> is maximal, such that influences on lubrication of the main shaft part <NUM> are also maximal. According to a large number of experimental studies, there is a great relation specifically as shown in following <FIG> among wear extent of the main shaft part <NUM> of the crankshaft <NUM>, a termination angle σ of the oil groove of the main bearing away from the gas cylinder <NUM>, and a practical motion angle d of the crankshaft <NUM> during gas exhaust. When a difference value of σ-d ranges from -7π/<NUM> to 7π/<NUM>, the wear extent of the main shaft part <NUM> of the crankshaft <NUM> is smaller and the reliability of the crankshaft <NUM> is higher; -7π/<NUM>≤σ-d≤7π/<NUM> is substituted into the formula (<NUM>) to obtain an optimal range of the termination angle σ of the oil groove of the main bearing <NUM> away from the gas cylinder as follows:
<MAT>.

Furthermore, for the single-cylinder pump body assembly and the single-cylinder compressor, the optimal range of the difference value of σ-d is greater than -π/<NUM> and smaller than 5π/<NUM>, and the range of the termination angle σ of the oil groove is as follows:
<MAT>.

Furthermore, for the multi-cylinder pump body assembly and the multi-cylinder compressor, as shown in <FIG>, the optimal range of the difference value of σ-d is greater than - π/<NUM> and smaller than π/<NUM>, and the range of the termination angle σ of the oil groove is as follows:
<MAT>.

In a process that the multi-cylinder compressor rotates around the crankshaft <NUM>, gas force has a plurality of peak values, and there is greater difference between a direction (corresponding to a direction of centrifugal force) of a balance block and the single-cylinder compressor, so that the optimal range of the termination angle of the oil groove of the multi-cylinder compressor is not completely consistent with that of the single-cylinder compressor.

In a specific embodiment, the first oil guide groove <NUM> of the main bearing <NUM> is a spiral oil guide groove, and the rotation direction of the spiral oil guide groove is consistent with the rotation direction of the crankshaft <NUM>.

In a specific embodiment, as shown in <FIG>, the range of the angle σ0 of the termination point of the first oil guide groove <NUM> of the main bearing <NUM> close to the gas cylinder <NUM> also greatly affects the reliability of the main shaft part <NUM> of the crankshaft <NUM>. Based on the study, when σ0 is greater than or equal to 3π/<NUM> and smaller than or equal to 2π, the reliability of the main shaft part <NUM> of the crankshaft <NUM> is better; similarly, when a starting angle ϕ of the second oil guide groove of the auxiliary bearing close to the gas cylinder <NUM> is greater than or equal to 3π/<NUM> and smaller than or equal to 2π, the reliability of the auxiliary shaft part <NUM> is better.

The width a and the depth b of the first oil guide groove <NUM> also greatly affect the lubricating reliability; and when the range of the width a of the first oil guide groove <NUM> is greater than or equal to <NUM> and smaller than or equal to <NUM> and the range of the depth b is greater than or equal to <NUM> and smaller than or equal to <NUM>, the integral reliability of the crankshaft <NUM> is better.

It should be noted that the angles of the oil grooves mentioned in the embodiment are all an included angle between the connection line of the termination point of the first oil guide groove <NUM> and the center of the main bearing <NUM>, and the <NUM>-degree angle.

In one embodiment of the present invention, as shown in <FIG>, a first annular groove <NUM>, a radial depth of which is not greater than <NUM>, is formed in the inner surface of the hub of the main bearing <NUM>. The first annular groove <NUM> is formed in the inner surface of the hub of the main bearing <NUM>, so that oil supply amount between the hub of the main bearing <NUM> and the shaft part of the crankshaft <NUM> may be further increased. In such a manner, a lubricating condition of the shaft part of the crankshaft <NUM> is improved. And meanwhile, contact area between the hub part <NUM> of the main bearing and the shaft part of the crankshaft <NUM> is reduced through the first annular groove <NUM>, so that viscous resistance and friction loss between the two are reduced, and the performance of the compressor is improved. The radial depth dimension of the first annular groove <NUM> is limited to be not greater than <NUM>, such that the first annular groove <NUM> is ensured to slightly affect the rigidity of the whole pump body assembly <NUM>.

In one embodiment of the present invention, as shown in <FIG>, a second annular groove <NUM> is formed in the main shaft part <NUM> of the crankshaft <NUM>, and the area which is in contact with the hub part <NUM> of the main bearing also guarantees the depth of the second annular groove <NUM> to be not greater than <NUM>; and the principle is similar with the principle of forming the annular groove in the inner surface of the hub part <NUM> of the main bearing <NUM>, which is not further described here.

In one embodiment of the present invention, as shown in <FIG>, a radial oil passing hole <NUM> is additionally formed in the hub of the main bearing <NUM>, and the oil passing hole <NUM> penetrates through inner and outer surfaces of the hub part <NUM> and is located in the area of the first annular groove <NUM>. The oil passing hole <NUM> which penetrates through in the radial direction is formed, so that circulating performance between lubricating oil on the inner surface of the hub part <NUM> and lubricating oil outside may be improved, and the temperature of the lubricating oil in the hub is reduced to certain extent. In such a manner, lubricating reliability of the shaft part of the crankshaft <NUM> is further improved.

In the above embodiments, application on a rolling piston type compressor of the present invention is described in detail, and the present invention is not limited to the rolling piston type compressor. For example, for a piston sliding vane integrated swing type structure (as shown in <FIG>) or a piston <NUM> and sliding vane <NUM> hinged structure (as shown in <FIG>), the present invention still may be applied with no great difference in implementation way, which takes a direction that the connection line of the center of the cylinder body <NUM> of the gas cylinder and the center of the sliding vane slot <NUM> points to the sliding vane slot <NUM> as a <NUM>-degree direction; if the center of the sliding vane slot <NUM> cannot be obviously determined, the rotation angle of the crankshaft <NUM> when a gas suction cavity and a gas exhaust cavity of the gas cylinder are combined into one cavity is defined as a <NUM>-degree angle. The angle increase direction is the same as the crankshaft rotation direction <NUM>, and the optimal range of the termination angle σ of the main bearing <NUM> away from the gas cylinder is still as follows:
<MAT>.

According to an embodiment of a second aspect of the present invention, a compressor is provided, including the pump body assembly <NUM> according to any of the embodiments. As a result, the compressor has all the beneficial effects of the pump body assembly <NUM>, which will not be detailed here.

According to an embodiment of a third aspect of the present invention, an air conditioner is provided, including the pump body assembly <NUM> or the compressor according to any of the embodiments. As a result, the air conditioner has all the beneficial effects of the pump body assembly <NUM> or the compressor, which will not be detailed here.

In the present invention, the term "a plurality of" means two or more, unless otherwise specifically regulated. Terms such as "installation", "connected", "connecting", "fixation" and the like shall be understood in broad sense, and for example, "connecting" may refer to fixed connection or detachable connection or integral connection, and "connected" may refer to direct connection or indirect connection through an intermediate medium. For those ordinary skilled in the art, the specific meanings of the above terms in the present invention may be understood according to concrete conditions.

In the illustration of this description, the illustration of terms of "one embodiment", "some embodiments", "specific embodiments", etc. means that specific features, structures, materials or characteristics illustrated in combination with the embodiment or example are included in at least one embodiment or example of the present invention. In this description, exemplary statements for the above terms shall not necessarily refer to the same embodiment or example. Moreover, the described specific features, structures, materials or characteristics can be combined appropriately in any one or more embodiments or examples.

Claim 1:
A pump body assembly (<NUM>), comprising:
a crankshaft (<NUM>), comprising a main shaft part (<NUM>) and an eccentric part (<NUM>) connected with the main shaft part (<NUM>), wherein a distance between the center line of the main shaft part and the center line of the eccentric part (<NUM>) is e;
a main bearing (<NUM>), comprising a hub part (<NUM>), wherein the main shaft part (<NUM>) penetrates through a through hole (<NUM>) in the hub part (<NUM>), and a first spiral oil guide groove (<NUM>) is formed in a hole wall of the through hole (<NUM>); and
a cylinder body (<NUM>), wherein a sliding vane slot (<NUM>) and a center hole (<NUM>) are formed in the cylinder body (<NUM>), the crankshaft (<NUM>) penetrates through the center hole (<NUM>), the main bearing (<NUM>) is located at one side of the cylinder body (<NUM>), a radius of the center hole (<NUM>) is R, and a difference value between R and e is r; and
a first annular groove (<NUM>) which is formed in the hole wall of the through hole (<NUM>), and the first spiral oil guide groove (<NUM>) is communicating with the first annular groove (<NUM>);
wherein the first spiral oil guide groove (<NUM>) is provided such that the rotation angle (σ) corresponding to the rotation of the crankshaft (<NUM>) from a first connection line (<NUM>) between the center of the center hole (<NUM>) and that of the sliding vane slot (<NUM>) in the same projection plane to a second connection line (<NUM>) between a termination point of the first spiral oil guide groove (<NUM>) at one end of the hub part (<NUM>) away from the eccentric part (<NUM>) is within a first range of value and that the rotation angle (σ0) corresponding to the rotation of the crankshaft (<NUM>) from a third connection line (<NUM>) between a termination point at the other end of the first spiral oil guide groove (<NUM>) and the center of the through hole (<NUM>) to the first connection line (<NUM>) is within a second range of value;
characterised in that the first range of value is comprised between 5π/<NUM> + <MAT> and <MAT>, and that the second range of value is comprised between 3π/<NUM> and 2π.