CN211874956U - Main bearing seat and scroll compressor - Google Patents

Abstract

The present disclosure relates to a main bearing seat and a scroll compressor having the same, and in an aspect, provides a main bearing seat for a scroll compressor, including: a recess in which an orbiting scroll of the scroll compressor is engaged with a drive shaft; a thrust surface through which the main bearing housing supports the orbiting scroll; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to an outside of the main bearing housing such that the lubricant in the recess can be discharged from the oil discharge passage, and further comprising an oil supply passage formed in the main bearing housing and configured to extend from the recess to the thrust surface such that the lubricant in the recess can be supplied to the thrust surface via the oil supply passage. Thereby, better lubrication of the thrust surface is achieved, and a predetermined oil circulation rate is obtained by controlling the distribution of the lubricant in the oil supply passage and the oil discharge passage, achieving good lubrication of the inside of the compression mechanism and avoiding the excessive lubricant from entering the external system along with the exhaust gas to cause deterioration of the system efficiency and the like.

Description

Main bearing seat and scroll compressor

Technical Field

The present disclosure relates to a main bearing housing for a scroll compressor and a scroll compressor having the same.

Background

This section provides background information related to the present disclosure, but such information does not necessarily constitute prior art.

Scroll compressors typically include a compression mechanism, a oldham ring, a main bearing housing, a drive shaft, and the like. A main bearing housing supports a movable scroll of the compression mechanism by a thrust plate and the movable scroll is translationally rotated relative to a fixed scroll of the compression mechanism via an oldham ring to define a series of compression chambers between the movable and fixed scrolls for compressing fluid entering the scroll compressor.

In a scroll compressor, a thrust plate of a main bearing housing, specifically, a thrust surface of the thrust plate which contacts a movable scroll is easily worn by the translational rotation of the movable scroll. In addition, the keys of the oldham ring are also susceptible to wear due to the constant impact with the orbiting and non-orbiting scrolls.

In general, the above problem is solved by causing lubricant (e.g., lubricating oil) in a recess of a main bearing housing to be pushed to a thrust surface of the main bearing housing and a groove that receives the oldham ring. Fig. 1a to 4 relate to the above-described conventional lubrication manner, in which fig. 1a and 1b show a plan view of a compression mechanism and a main bearing seat portion of a conventionally used scroll compressor 100 and a longitudinal sectional view near the compression mechanism and the main bearing seat taken along line a-a of fig. 1a, respectively, fig. 2 shows a supply path of lubricant by an arrow on the basis of fig. 1b, and fig. 3 and 4 are a side perspective view and a plan view showing the main bearing seat fitted with a oldham ring, respectively, in which the supply path of lubricant is shown by an arrow. Specifically, as shown in fig. 1a to 4, lubricant in an oil reservoir at the bottom of the scroll compressor is pumped through the central hole 21 of the drive shaft 2 into the recess 11 of the main bearing housing 1, for example, by an oil pump (not shown), the lubricant is pushed in a gap between the recess 11 of the main bearing housing 1 and the boss 31 of the movable scroll 3 received in the recess 11 by the translational rotation of the movable scroll 3, so that a small portion of the lubricant is pushed out and reaches the thrust surface 12, and the remaining lubricant is discharged through the oil discharge passage 13 in the main bearing housing 1 and returned to the oil reservoir. A part of the lubricant reaching the thrust surface 12 is further pushed into the recess 14 receiving the oldham ring 4 by the translatory movement of the end plate of the orbiting scroll 3, whereby lubrication of the thrust surface 12 of the main bearing housing and the key 41 of the oldham ring 4 is simultaneously achieved.

However, in the oil supply path of the lubricant from entering the thrust surface 12 to leaving the thrust surface 12 (to the groove 14), the end plate of the orbiting scroll is in close contact with the thrust plate of the main bearing housing, and the clearance caused by the orbiting movement of the orbiting scroll 3 is very small, which means that most of the lubricant in the recess 11 is discharged through the oil discharge passage 13, and the amount of lubricant used to lubricate the thrust surface 12 is very limited, often causing wear of the thrust surface 12. Furthermore, since the keys 41 of the oldham ring 4 (especially the keys for engaging the fixed scroll 5) are higher than the oldham ring arms, the oil supply path from the entrance groove 14 to the keys 41 of the oldham ring 4 is restricted due to gravity. The lubricant remains mainly in the above-mentioned gap and the amount of lubricant that enters the groove 14 from the thrust surface 12 is also very limited.

SUMMERY OF THE UTILITY MODEL

This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.

It is an object of the present disclosure to provide a main bearing housing capable of directly lubricating a thrust surface of the main bearing housing and a oldham ring.

Another object of the present disclosure is to provide a main bearing housing capable of controlling an oil circulation rate by controlling distribution of lubricant between an oil supply passage and an oil discharge passage.

To achieve one or more of the above objects, according to an aspect of the present disclosure, there is provided a main bearing housing for a scroll compressor, the main bearing housing including: a recess in which an orbiting scroll of the scroll compressor engages a drive shaft of the scroll compressor; a thrust surface through which the main bearing housing supports the movable scroll; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to an outside of the main bearing housing such that the lubricant in the recess can be discharged from the oil discharge passage, the main bearing housing further including an oil supply passage formed in the main bearing housing and configured to extend from the recess to the thrust surface such that the lubricant in the recess can be supplied to the thrust surface via the oil supply passage.

In the above-described main bearing housing, the main bearing housing may further include a groove for receiving the rotation prevention device, and the main bearing housing may be further provided with an oil supply passage formed in the main bearing housing and configured to extend from the recess to the groove.

According to another aspect of the present disclosure, there is provided a main bearing housing for a scroll compressor, the main bearing housing including: a recess in which an orbiting scroll of the scroll compressor engages a drive shaft of the scroll compressor; a recess configured to receive an anti-rotation device; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to an outside of the main bearing housing such that the lubricant in the recess can be discharged from the oil discharge passage, the main bearing housing further including an oil supply passage formed in the main bearing housing and configured to extend from the recess to the groove such that the lubricant in the recess can be supplied to the groove via the oil supply passage.

In the above-described main bearing housing, the oil supply passage and the oil discharge passage may be configured so as to enable a predetermined oil circulation rate to be obtained by fitting each other, which may be achieved by controlling the distribution of lubricant between the oil supply passage and the oil discharge passage.

In the above-described main bearing housing, the control of the distribution may be achieved by controlling the value of n, where n is the distribution ratio of the lubricant supplied to the outlet of the oil supply passage to the lubricant entering the oil discharge passage and n is controlled by changing the following parameters according to the following formula:

wherein r is₁Is the radius of the inlet of the oil discharge passage, r₂Radius of the outlet of the oil supply passage, v₁Is the speed, v, of the lubricant at the inlet of the oil discharge channel₂Is the velocity of the lubricant at the outlet of the oil supply passage.

In the above main bearing housing, the value of n may be controlled to be between 0.5 and 1.5 so that the oil circulation rate is more than 1% and less than 2%.

In the above main bearing housing, the control of the distribution may be achieved by changing the number of oil supply passages and/or the number of oil discharge passages.

In the main bearing housing, the oil supply passage may be one or more oil supply passages.

In the above-described main bearing housing, the oil supply passage is a plurality of oil supply passages, at least one of the plurality of oil supply passages extends to the thrust surface and the remaining oil supply passages of the plurality of oil supply passages extend to the groove.

In the above-described main bearing housing, in the case where the oil supply passage is a plurality of oil supply passages, the plurality of oil supply passages may be arranged such that outlets of the plurality of oil supply passages are uniformly arranged on the thrust surface, or the plurality of oil supply passages may be arranged such that outlets of the plurality of oil supply passages extending into each groove are uniformly arranged in the groove.

In the main bearing housing, the oil supply passage and the oil discharge passage may be completely independent passages.

In the above-described main bearing housing, an inlet of the oil supply passage and an inlet of the oil discharge passage may be located at the same position of the circumferential wall of the recess.

In the main bearing housing, the oil supply passage may be a passage extending in a single direction.

In the main bearing housing, an outlet of the oil supply passage extending to the groove may be located at a boundary between a bottom surface and a side surface of the groove.

In the above-described main bearing housing, the main bearing housing may include a main bearing housing body and a thrust plate that are separate from each other, the thrust plate providing a thrust surface adapted to support the orbiting scroll, the oil supply passage extending substantially vertically through the thrust plate and opening into the groove, and the oil discharge passage extending substantially diagonally through the main bearing housing body and opening outside the main bearing housing.

According to yet another aspect of the present disclosure, a scroll compressor is provided which may have any of the main bearing housings described above.

According to the present disclosure, by providing an oil supply channel in the main bearing housing leading to the thrust surface and/or the groove of the main bearing housing for directly lubricating the thrust surface and the oldham ring received in the groove, a greater amount of lubricant can be provided in the thrust surface and the groove, thereby achieving better lubrication of the thrust surface and the oldham ring. Further, by configuring the oil supply passage and the oil discharge passage to cooperate with each other, a predetermined oil circulation rate is obtained by controlling the distribution of the lubricant in the oil supply passage and the oil discharge passage, so that while good lubrication of the oldham ring and the thrust surface in the groove can be achieved, good lubrication of the interior of the compression mechanism can also be achieved and deterioration of system efficiency and the like due to excessive lubricant entering into an external system along with exhaust gas can also be avoided.

The above features and advantages and other features and advantages of the present disclosure will become more apparent from the following detailed description of exemplary embodiments thereof, which is to be read in connection with the accompanying drawings.

Drawings

The above and other objects, features and advantages of the present disclosure will be more readily understood by reference to the following detailed description of exemplary embodiments thereof taken in conjunction with the accompanying drawings. Throughout the drawings, identical or corresponding technical features or components will be denoted by identical or corresponding reference numerals. In the drawings:

FIG. 1a is a top view of a compression mechanism and main bearing housing portion of a conventionally used scroll compressor;

FIG. 1b is a longitudinal cross-sectional view taken along line A-A of FIG. 1a near the compression mechanism and main bearing housing;

fig. 2 is a longitudinal sectional view showing a supply path of lubricant by an arrow on the basis of fig. 1;

FIG. 3 is a side perspective view showing a main bearing housing fitted with a oldham ring, wherein the lubricant supply path is shown by arrows;

FIG. 4 is a top view showing a main bearing housing fitted with an oldham ring, wherein the supply path of lubricant is shown by arrows;

figures 5a and 5b are side perspective and longitudinal cross-sectional views, respectively, illustrating a main bearing housing according to an embodiment of the present disclosure;

fig. 6a and 6b are a side perspective view and a longitudinal sectional view, respectively, illustrating a main bearing housing according to another embodiment of the present disclosure;

fig. 7a and 7b are a side perspective view and a longitudinal sectional view, respectively, exemplarily showing a main bearing housing provided with 4 oil supply passages;

fig. 8a and 8b are a side perspective view and a longitudinal sectional view, respectively, exemplarily showing a main bearing housing provided with 4 oil supply passages;

fig. 9a is a longitudinal sectional view illustrating a main bearing housing provided with an oil supply passage according to the present disclosure; and

fig. 9b is a graph and corresponding graph showing the relationship between the value of n and the oil circulation rate obtained from the test in the case of the main bearing housing of fig. 9 a.

Detailed Description

The disclosure is described in detail below with the aid of exemplary embodiments with reference to the accompanying drawings. It is to be noted that the following detailed description of the present disclosure is intended for purposes of illustration only and is not intended to limit the present disclosure in any way. Moreover, like reference numerals are used to refer to like elements throughout the various figures.

First, the construction of the scroll compressor will be briefly described with reference to fig. 1a to 4. Taking a low pressure side compressor as an example, the scroll compressor 100 includes a housing, a top cover disposed at one end of the housing, a bottom cover disposed at the other end of the housing, and a partition plate disposed between the top cover and the housing, the partition plate dividing an internal space of the scroll compressor into a high pressure side between the partition plate and the top cover and a low pressure side between the partition plate, the housing, and the bottom cover. A compression mechanism formed by a fixed scroll 5 and a movable scroll 3, a drive mechanism formed by a stator and a rotor, and a drive shaft 2 are provided in the housing, and the drive shaft 2 is driven to rotate by the drive mechanism so that the movable scroll 3 makes translational motion relative to the fixed scroll 5 to define a series of compression chambers between the movable scroll 3 and the fixed scroll 5 to compress fluid entering the scroll compressor. The fixed scroll 5 includes an end plate, a spiral wrap extending from one side of the end plate, and a discharge port formed at a substantially central position of the end plate, and the movable scroll 3 includes an end plate 32, a spiral wrap extending from one side of the end plate 32, and a hub 31 extending from the other side of the end plate 32.

As shown in fig. 1b, the scroll compressor further includes an oldham ring 4 and a main bearing housing 1.

The oldham ring 4 is annular in shape and is mounted on the main bearing housing 1. The oldham ring 4 includes an annular body and two pairs of keys provided on the body, one of which is fitted with and capable of reciprocating linear motion along a pair of key grooves of the orbiting scroll 3, and the other of which is fitted with and capable of reciprocating linear motion along a pair of key grooves of the non-orbiting scroll 5. In operation, the oldham ring is driven by the movable scroll 3 to reciprocate linearly with respect to the fixed main bearing housing 1 and the fixed scroll 5, and the movable scroll 3 reciprocates linearly in a direction substantially perpendicular to the movement direction of the oldham ring, so that the movable scroll 3 makes translational movement but cannot rotate with respect to the fixed scroll 5 via the oldham ring 4. Here, it should be noted that the oldham ring is only one example of a possible rotation preventing device, and for example, a rotation preventing device having no ring body but only keys may be adopted, and in this case, there is also a problem that lubrication of the keys is insufficient.

The main bearing housing 1 is configured to support a compression mechanism, particularly, an orbiting scroll 3, and rotatably support a drive shaft 2. The main bearing housing 1 includes: a recess 11, the recess 11 being provided at a substantially center of an upper portion of the main bearing housing 1 and configured to receive a boss portion 31 of the orbiting scroll 3 such that the boss portion 31 is capable of translational rotation in the recess 11; a groove 14, the groove 14 being provided at a radially outer side of the recess 11 and being configured for receiving the oldham ring 4 (in particular the annular body of the oldham ring 4) such that the oldham ring 4 is movable in the groove 14; a thrust surface 12, the thrust surface 12 being a surface of a thrust plate of the main bearing housing 1 that contacts a surface of the end plate 32 of the movable scroll 3, wherein the thrust plate may be a portion integral with the body of the main bearing housing 1 or may be a portion separate from the body of the main bearing housing 1, and the main bearing housing 1 supports the end plate 32 of the movable scroll 3 via the thrust surface 12; a center hole 15, the center hole 15 being provided at substantially the center of a lower portion of the main bearing housing 1 and configured to receive and rotatably support the drive shaft 2; and an oil drain passage 13, the oil drain passage 13 being formed in the main bearing housing 1 and configured to extend from a circumferential wall 16 of the recess 11 to the outside of the main bearing housing 1. Here, it should be noted that, according to the present disclosure, the oil drain passage 13 may extend from other portions (e.g., a lower portion) of the recess 11 in addition to the circumferential wall 16.

During operation of the scroll compressor, lubricant stored in an oil reservoir at the bottom of the housing of the scroll compressor may be pumped through the central bore 21 of the drive shaft 2 until into the recess 11 of the main bearing housing 1 via a lubricant supply device, such as an oil pump, provided at the bottom of the housing. A portion of the lubricant in recess 11 is used to lubricate thrust surface 32 and oldham ring 4 received in groove 14, while the remaining portion of the lubricant in recess 11 is discharged from recess 11 to return to the oil reservoir by oil discharge passage 13 extending from recess 11 through main bearing housing 1 in the radial direction of main bearing housing 1 to the outside of main bearing housing 1.

The present disclosure improves a main bearing seat on the basis of a general scroll compressor, that is, a lubricant supply manner to a thrust surface and a oldham ring, and particularly, a lubricant supply passage for directly lubricating the thrust surface is added in the main bearing seat and/or a lubricant supply passage for directly lubricating the oldham ring in a groove is added in the main bearing seat on the basis of an oil discharge passage, thereby providing a better lubricating effect.

In view of this, the following description will be made only with respect to the main bearing housing according to the present disclosure and the re-description of the above-described other components and parts will be omitted.

Fig. 5a and 5b illustrate a main bearing housing 1 according to an embodiment of the present disclosure, wherein fig. 5a is a side perspective view illustrating the main bearing housing 1 according to the embodiment of the present disclosure, and fig. 5b is a longitudinal sectional view illustrating the main bearing housing 1 according to the embodiment of the present disclosure.

As shown in fig. 5a and 5b, the main bearing housing 1 includes an oil supply passage 101, the oil supply passage 101 being formed in the main bearing housing 1 and configured to extend through the main bearing housing 1 from the circumferential wall 16 of the recess 11 to the thrust surface 12 to communicate the recess 11 with the thrust surface 12. Thereby, the lubricant in the recess 11 can be provided to the thrust surface 12 via the oil supply channel 101. In addition, the remaining portion of the lubricant in recess 11 can be discharged from recess 11 through oil discharge passage 13 provided in main bearing housing 1 as described above to return to the oil reservoir. As shown in fig. 5b, the lubricant in the recess 11 enters the oil supply passage 101 from an inlet of the oil supply passage 101 on the circumferential wall 16 of the recess 11 by means of kinetic energy generated by the translational movement of the boss portion 31 of the orbiting scroll 3 (in the case where a weight located in the recess 11 is provided, the lubricant in the recess may also be whipped into the oil supply passage 101 by the weight), and then exits from an outlet of the oil supply passage 101 on the thrust surface 12 through the oil supply passage 101 as shown by an arrow in the oil supply passage 101 in fig. 5 b. The lubricant leaving the oil supply passage 101 enters between the thrust surface 12 of the main bearing housing 1 and the end plate 32 of the movable scroll 3 to lubricate the thrust surface 12 of the main bearing housing 1, that is, to lubricate the surface of the end plate 32 of the movable scroll 3 which is in contact with the thrust surface 12. After that, as the end plate 32 of the movable scroll 3 is rotated in the translational movement, a part of the lubricant between the thrust surface 12 and the end plate 32 of the movable scroll 3 is further pushed into the groove 14, and as the oldham 4 received in the groove 14 is moved, the lubricant is pushed to the key of the oldham 4, thereby achieving lubrication of the key of the oldham 4.

In the embodiment of the present disclosure, by providing the oil supply passage 101 directly leading to the thrust surface 12, a larger amount of lubricant is supplied to the thrust surface 12 and further to the recess 14 receiving the oldham ring 4 as the movable scroll 3 moves, so that both the thrust surface 12 and the oldham ring 4 are lubricated better than the case of lubricating the thrust surface and the oldham ring of the main bearing housing in the conventionally used scroll compressor.

Fig. 6a and 6b illustrate another embodiment similar to main bearing housing 1 illustrated in fig. 5a and 5b, wherein fig. 6a is a side perspective view illustrating main bearing housing 1 according to the another embodiment of the present disclosure, and fig. 6b is a longitudinal sectional view illustrating main bearing housing 1 according to the another embodiment of the present disclosure.

It is contemplated that main bearing housing 1 may include an oil supply passage 102 formed in main bearing housing 1 and configured to extend through main bearing housing 1 from circumferential wall 16 of recess 11 to groove 14 to communicate recess 11 with groove 14. Thereby, the lubricant in the recess 11 can be supplied to the groove 14 via the oil supply passage 102. Also, the remaining portion of the lubricant in the recess 11 can be discharged from the recess 11 through the oil discharge passage 13 to return to the oil reservoir. Similarly, as shown in fig. 6b, the lubricant in the recess 11 enters the oil supply passage 102 from an inlet of the oil supply passage 102 at the circumferential wall 16 of the recess 11 by means of kinetic energy, and then passes through the oil supply passage 102 to exit from an outlet of the oil supply passage 102 in the groove 14, as shown by the arrow in the oil supply passage 102 in fig. 6 b. The lubricant leaving the oil supply channel 102 enters the groove 14 to effect lubrication of the oldham ring 4 received in the groove 14.

The location of the outlet of the oil supply channel 102 is shown in fig. 6a and 6 b. Specifically, the groove 14 is shown to include a bottom surface 141 and a side surface 142 extending upwardly from the bottom surface 141 to the thrust surface 12. The outlet of the oil supply passage 102 is located at the intersection of the bottom surface 141 and the side surface 142 of the groove 14. By this arrangement, the lubricant exiting from the outlet of the oil supply passage 102 can be better brought into contact with and whipped by the annular body of the oldham ring 4 with the movement of the oldham ring 4 in the groove 14, thereby achieving better lubrication of the oldham ring 4.

Further, it is contemplated that main bearing housing 1 may include a plurality of oil supply passages. Fig. 7a and 7b are a side perspective view and a longitudinal sectional view, respectively, exemplarily showing main bearing housing 1 provided with 4 oil supply passages 101, and fig. 8a and 8b are a side perspective view and a longitudinal sectional view, respectively, exemplarily showing main bearing housing 1 provided with 4 oil supply passages 102.

By providing a plurality of oil supply channels, more lubricant can be supplied to the thrust surface 12 or the groove 14 and more evenly, thereby achieving better lubrication of the oldham ring 4 in the thrust surface 12 or the groove 14. As shown in fig. 7a and 7b and fig. 8a and 8b, the 4 oil supply channels 101 may be arranged such that their outlets are evenly arranged on the thrust surface 12, and the 4 oil supply channels 102 may be arranged such that their outlets are evenly and respectively correspondingly arranged in the grooves 14 such that the same number of oil supply channels 102 are arranged in each groove, it is envisaged that, where a plurality of oil supply channels 102 are provided, the plurality of oil supply channels may be arranged such that the outlets of the plurality of oil supply channels extending into each groove are evenly arranged in the groove, thereby achieving a more even lubrication of the thrust surface 12 and the oldham ring 4 in the groove 14.

It is contemplated that main bearing housing 1 may include both oil supply passage 101 and oil supply passage 102. In the case where main bearing housing 1 includes a plurality of oil supply passages, the plurality of oil supply passages may include both oil supply passages 101 and 102, i.e., at least one of the plurality of oil supply passages is oil supply passage 101 extending to thrust surface 12, and the remaining oil supply passages of the plurality of oil supply passages are oil supply passages 102 extending to groove 14. Thereby, a direct lubrication of the thrust surface 12 and the oldham ring 4 in the groove 14 can be achieved simultaneously and a better lubrication result is obtained.

Further, as shown in fig. 5b or fig. 6b, the inlet of the oil supply passage 101 or 102 and the inlet of the oil discharge passage 13 may be arranged to be located at the same position of the circumferential wall 16 of the recess 11. This arrangement is advantageous in terms of the machining of the oil discharge passage and the oil supply passage. However, it is understood that the inlet of the oil supply passage 101 or 102 may also be located at a position of the circumferential wall 16 different from the position of the inlet of the oil discharge passage 13.

Control that can be achieved in terms of Oil Circulation Rate (OCR) and/or lubrication effect by the main bearing housing according to the present disclosure will be described in detail below.

In general, in the present disclosure, the oil supply passage and the oil discharge passage may be configured to enable an optimum oil circulation rate to be obtained by cooperating with each other, thereby ensuring proper lubrication of the inside of the compression mechanism and avoiding system efficiency deterioration or the like due to excessive lubricant entering into the external system along with the exhaust gas while achieving better lubrication of the thrust surface 12 and the oldham ring 4.

Specifically, the above-described interfitting of the oil supply passage and the oil discharge passage is achieved by controlling the distribution of the lubricant in the recess 11 between the oil supply passage and the oil discharge passage. Since the amount of lubricant that the lubricant supply means such as an oil pump can pump the lubricant supplied to the recess 11 is constant, the distribution percentage of the lubricant can be controlled by controlling the amount of lubricant entering the oil supply passage and/or the amount of lubricant entering the oil discharge passage, so that both lubrication of the thrust surface 12 and the oldham ring 4 can be ensured and the oil circulation rate can be controlled.

Further description will now be made in conjunction with fig. 9 a. Fig. 9a is a longitudinal sectional view showing main bearing housing 1 provided with oil supply passage 102 according to the present disclosure, in which an oil supply path and an oil discharge path are shown by arrows, respectively, similar to fig. 6 b. In the example shown in figure 9a it can be seen that the main bearing housing 1 is of split type and comprises a main bearing housing body adapted to support the drive shaft and a thrust plate providing a thrust surface adapted to support the orbiting scroll member, which are separate from one another. The oil supply passage 102 extends substantially vertically through the thrust plate and opens into the groove 14. The oil drain passage 13 extends through the main bearing housing body in a substantially oblique direction and opens to the outside of the main bearing housing 1. According to this configuration, the oil supply passage and the oil discharge passage can be more easily processed, and control of the oil circulation rate while achieving appropriate lubrication of the relevant movable parts can be flexibly achieved in different ways. In fig. 9a, the number of the oil supply passage 102 and the oil discharge passage 13 is one for convenience of description. It is to be noted that the following description is also applicable to the case of the main bearing housing 1 provided with the oil supply passage 101 or both the oil supply passages 101 and 102 or a plurality of the oil supply passages 101 and/or 102.

In main bearing housing 1 according to the present disclosure shown in fig. 9a, control of the distribution of lubricant between oil supply channel 102 and oil drain channel 13 can be achieved by controlling the value of n, where n is the distribution ratio of lubricant supplied to the outlet of oil supply channel 102 to lubricant entering oil drain channel 13 and n is controlled by varying the following parameters according to the following equation:

in the above formula, r₁Is the radius of the inlet of the oil discharge channel 13, r₂Is the radius of the outlet of the oil supply passage 102, v₁The velocity of the lubricant at the inlet of the oil discharge channel 13, v₂Is the velocity of the lubricant at the outlet of the oil supply passage 102. Wherein v is₁And v₂Are respectively associated with the height positions of the inlet of the oil discharge passage 13 and the outlet of the oil supply passage 102 in the axial direction of the main bearing housing 1. Here, as shown in fig. 9a, the oil discharge passage 13 may be a uniform circular hole, and the oil supply passage 102 may also be a uniform circular hole.

Therefore, the value of n can be controlled by controlling at least one of the radius of the inlet of the oil discharge passage 13, the radius of the outlet of the oil supply passage 102, the speed of the lubricant at the inlet of the oil discharge passage 13, and the speed of the lubricant at the outlet of the oil supply passage 102, and the oil circulation rate is made to be at a predetermined oil circulation rate, that is, an optimum oil circulation rate corresponding to a predetermined application case, by controlling the value of n, thereby controlling the oil circulation rate while achieving a better lubrication effect.

It can be understood that, for the main bearing housing 1 provided with the oil supply passage 101 according to the present disclosure, r in the above formula₂Is the radius of the outlet of the oil supply passage 101 and v₂Is the velocity of the lubricant at the outlet of the oil supply passage 101, and wherein v₂Is associated with the height position of the outlet of the oil supply passage 101 in the axial direction of the main bearing housing 1.

Also, in the application of the above formula, the number of the oil discharge passage and/or the oil supply passage is not limited, but may be plural. In the case where the number of oil discharge passages and oil supply passages is plural, the corresponding radius r₁And r₂Can be obtained by converting the radius to an equivalent radius. In addition, it will be understood that in the case where the outlets of the plurality of oil supply passages are not at the same longitudinal level or the inlets of the plurality of oil discharge passages are not at the same longitudinal level, the corresponding velocities v₁And v₂It can also be obtained by converting the speed to an equivalent speed.

Fig. 9b is a graph and corresponding graph showing the relationship between the value of n and the oil circulation rate obtained in the test in the case of the main bearing housing 1 of fig. 9 a.

In this test, as shown in the graph in fig. 9b, the value of n was changed only by changing the radius of the oil supply passage 102, thereby controlling the distribution ratio of the lubricant between the oil supply passage 102 and the oil discharge passage 13 to obtain the optimum oil circulation ratio. In a certain scroll compressor, the optimum oil circulation rate is less than 2% and at the same time more than 1%.

As can be seen from the graph of fig. 9b, when the oil circulation rate is within the above range, the corresponding value of n is between 0.5 and 1.5. Thus, the oil circulation rate can be made greater than 1% and less than 2% by controlling only the radius of the oil intake passage 102 to control the value of n between 0.5 and 1.5. In this oil circulation rate range, good lubrication of the oldham ring 4 and the thrust surface in the groove 14 can be achieved, while also achieving good lubrication of the interior of the compression mechanism and also avoiding excessive lubricant entering the external system with the exhaust gas leading to deterioration of the system efficiency and the like.

Preferably, the oil supply passages 101 and 102 may be configured as passages extending in a single direction, whereby it is easier to control the lubricant entering the oil discharge passages 101 and 102, and thus to control the distribution of the lubricant between the oil supply passage and the oil discharge passage. However, it is understood that the oil supply passages 101 and 102 may be configured as other types of passages, such as a bent-shaped passage.

It is envisaged that the above-described distribution of lubricant between the oil supply passage and the oil discharge passage may be achieved by varying the number of oil supply passages and/or the number of oil discharge passages. In particular, the amount of lubricant provided to the thrust surface 12 and/or the groove 14 may be varied by varying the number of oil supply channels and/or the amount of lubricant drained by varying the number of oil drain channels, and thereby controlling the distribution of lubricant between the oil supply channels and the oil drain channels to obtain an optimum oil circulation rate while achieving proper lubrication of the thrust surface 12 and the oldham 4.

In addition, according to the present disclosure, the oil supply passage and the oil discharge passage are completely independent passages or independent passages sharing an inlet only in the recess. Compared with the related technical scheme that the oil supply channel and the oil discharge channel share a part of channels or the oil supply channel and the oil discharge channel are in an upstream-downstream relationship, the lubricant distribution between the oil supply channel and the oil discharge channel can be effectively controlled because the oil supply channel and the oil discharge channel are independent, so that the oil circulation rate can be effectively controlled, and the proper lubrication of related movable parts can be ensured.

While the present disclosure has been described with reference to exemplary embodiments, it is to be understood that the disclosure is not limited to the specific embodiments described and illustrated in detail herein. Various modifications may be made to the exemplary embodiments by those skilled in the art without departing from the scope of the disclosure as defined in the claims.

Claims (16)

1. A main bearing housing for a scroll compressor, the main bearing housing comprising:

a recess in which an orbiting scroll of the scroll compressor engages with a drive shaft of the scroll compressor; a thrust surface through which the main bearing housing supports the orbiting scroll; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to an outside of the main bearing housing such that the lubricant in the recess can be discharged from the oil discharge passage,

characterized in that, main bearing seat still includes:

an oil supply passage formed in the main bearing housing and configured to extend from the recess to the thrust surface such that the lubricant in the recess can be provided to the thrust surface via the oil supply passage.

2. The main bearing housing of claim 1 further comprising a groove for receiving an anti-spin device, and wherein the main bearing housing is further provided with an oil supply passage formed therein and configured to extend from the recess to the groove.

3. The main bearing housing of claim 2 wherein the oil supply passage is plural, at least one of the plural oil supply passages extending to the thrust surface and the remaining of the plural oil supply passages extending to the recess.

4. A main bearing housing for a scroll compressor, the main bearing housing comprising:

a recess in which an orbiting scroll of the scroll compressor engages with a drive shaft of the scroll compressor; a recess configured to receive an anti-rotation device; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to an outside of the main bearing housing such that the lubricant in the recess can be discharged from the oil discharge passage,

characterized in that, main bearing seat still includes:

an oil supply passage formed in the main bearing housing and configured to extend from the recess to the groove such that the lubricant in the recess can be supplied to the groove via the oil supply passage.

5. The main bearing housing according to any one of claims 1 to 4 wherein the oil supply passage and the oil discharge passage are configured to enable a predetermined oil circulation rate to be achieved by interfitting, wherein the interfitting is achieved by controlling the distribution of the lubricant between the oil supply passage and the oil discharge passage.

6. The main bearing housing according to claim 5 wherein the control of the distribution can be achieved by controlling the value of n, where n is the distribution ratio of lubricant supplied to the outlet of the oil supply passage to lubricant entering the oil discharge passage and n is controlled by varying the following parameters according to:

wherein r is₁Is the radius of the inlet of the oil discharge passage, r₂Is the radius of the outlet of the oil supply passage, v₁Is the speed, v, of the lubricant at the inlet of the oil discharge channel₂Is the speed of the lubricant at the outlet of the oil supply passage.

7. The main bearing housing according to claim 6 wherein the value of n can be controlled between 0.5 and 1.5 to provide the oil circulation rate greater than 1% and less than 2%.

8. The main bearing housing according to claim 5, wherein the control of the distribution can be achieved by varying the number of the oil supply passages and/or the number of the oil discharge passages.

9. The main bearing housing according to claim 1 or 4 wherein the oil supply passage is one or more oil supply passages.

10. The main bearing housing according to claim 9 wherein, where the oil supply passage is a plurality of oil supply passages, the plurality of oil supply passages are arranged such that outlets of the plurality of oil supply passages are evenly arranged on the thrust surface or the plurality of oil supply passages are arranged such that outlets of the plurality of oil supply passages extending into each groove are evenly arranged in the groove.

11. The main bearing housing according to any one of claims 1 to 4 wherein the oil supply passage and the oil drain passage are entirely independent passages from each other.

12. The main bearing housing according to any one of claims 1 to 4 wherein an inlet of the oil supply passage and an inlet of the oil discharge passage are located at the same position of the circumferential wall of the recess.

13. The main bearing housing according to any one of claims 1 to 4 wherein the oil supply passage is a passage extending in a single direction.

14. The main bearing housing according to any one of claims 2 to 4 wherein an outlet of the oil supply passage extending to the groove is located at an intersection of a bottom surface and a side surface of the groove.

15. The main bearing housing according to any one of claims 2 to 4 including a main bearing housing body and a thrust plate separate from one another, the thrust plate providing a thrust surface adapted to support the orbiting scroll, the oil supply passage extending generally vertically through the thrust plate and opening into the recess, the oil discharge passage extending generally diagonally through the main bearing housing body and opening out of the main bearing housing.

16. A scroll compressor, characterized in that it comprises a main bearing housing according to any one of claims 1 to 15.

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