Main bearing housing and scroll compressor

Abstract

This disclosure relates to a main bearing housing and a scroll compressor having the same main bearing housing. In one aspect, a main bearing housing for a scroll compressor is provided, comprising: a recess in which a moving scroll member of the scroll compressor engages with a drive shaft; a thrust surface through which the main bearing housing supports the moving scroll member; and an oil discharge passage formed in the main bearing housing and configured to extend from the recess to the outside of the main bearing housing, allowing lubricant in the recess to be discharged from the oil discharge passage; and an oil supply passage formed in the main bearing housing and configured to extend from the recess to the thrust surface, allowing lubricant in the recess to be supplied to the thrust surface via the oil supply passage. This achieves better lubrication of the thrust surface, and by controlling the distribution of lubricant in the oil supply and discharge passages, a predetermined oil circulation rate is obtained, resulting in good lubrication of the internal components of the compression mechanism and preventing excessive lubricant from entering the external system with the exhaust gas, thus avoiding system efficiency degradation.

Description

Technical Field

[0001] This disclosure relates to a main bearing housing for a scroll compressor and a scroll compressor having the main bearing housing. Background Technology

[0002] This section provides background information relating to this disclosure, but such information does not necessarily constitute prior art.

[0003] A scroll compressor typically includes a compression mechanism, a cross ring, a main bearing housing, and a drive shaft. The main bearing housing supports the moving scroll component of the compression mechanism via a thrust plate, and the moving scroll component rotates relative to the stationary scroll component of the compression mechanism via the cross ring to define a series of compression chambers between the moving and stationary scroll components for compressing the fluid entering the scroll compressor.

[0004] In scroll compressors, the thrust plate of the main bearing housing, specifically the thrust surface of the thrust plate that contacts the moving scroll, is prone to wear due to the translational rotation of the moving scroll. Additionally, the key of the cross-slip ring is also prone to wear due to its continuous collisions with both the moving and stationary scrolls.

[0005] The above problem is usually solved by pushing the lubricant (e.g., lubricating oil) in the recess of the main bearing housing to the thrust surface of the main bearing housing and the groove that receives the cross slip ring. Figures 1a to 4 Regarding the aforementioned conventional lubrication methods, among which, Figure 1a and Figure 1b Top and side views of the compression mechanism and main bearing housing of a conventionally used scroll compressor 100 are shown respectively. Figure 1a A longitudinal sectional view taken along line AA near the compression mechanism and main bearing housing. Figure 2 exist Figure 1b The supply path of the lubricant is shown by arrows, and... Figure 3 and Figure 4 The figures show a side perspective view and a top view of the main bearing housing equipped with a cross-shaped slip ring, with arrows indicating the lubricant supply path. Specifically, as... Figures 1a to 4As shown, lubricant in the oil reservoir at the bottom of the scroll compressor is pumped, for example, through the central hole 21 of the drive shaft 2 via an oil pump (not shown) into the recess 11 of the main bearing housing 1. Through the translational rotation of the moving scroll member 3, the lubricant is pushed in the gap between the recess 11 of the main bearing housing 1 and the hub 31 of the moving scroll member 3 received in the recess 11, causing a small portion of the lubricant to be pushed out and reach the thrust surface 12. The remaining lubricant is discharged through the oil drain channel 13 in the main bearing housing 1 and returns to the oil reservoir. A portion of the lubricant reaching the thrust surface 12 is further pushed into the groove 14 receiving the cross slip ring 4 by the translational movement of the end plate of the moving scroll member 3, thereby simultaneously achieving lubrication of the thrust surface 12 of the main bearing housing and the key 41 of the cross slip ring 4.

[0006] However, in the lubricant supply path from entering the thrust surface 12 to exiting the thrust surface 12 (reaching the groove 14), the end plate of the moving scroll member is in tight contact with the thrust plate of the main bearing housing. The clearance caused by the translational motion of the moving scroll member 3 is very small. This means that most of the lubricant in the groove 11 is discharged through the drain channel 13, and the amount of lubricant used to lubricate the thrust surface 12 is very limited, often causing wear on the thrust surface 12. Moreover, since the key 41 of the cross ring 4 (especially the key for engaging with the fixed scroll member 5) is higher than the cross ring arm, the lubricant supply path from entering the groove 14 to reaching the key 41 of the cross ring 4 is limited by gravity. The lubricant mainly remains in the aforementioned gap, and the amount of lubricant entering the groove 14 from the thrust surface 12 is also very limited. Summary of the Invention

[0007] This section provides a general overview of this disclosure, rather than a full disclosure of the entire scope or all features of this disclosure.

[0008] One object of this disclosure is to provide a main bearing housing that can directly lubricate the thrust surface of the main bearing housing and the cross slip ring.

[0009] Another object of this disclosure is to provide a main bearing housing that can control the oil circulation rate by controlling the distribution of lubricant between the oil supply channel and the oil discharge channel.

[0010] To achieve one or more of the above objectives, according to one aspect of the present disclosure, a main bearing housing for a scroll compressor is provided, the main bearing housing comprising: a recess in which a moving scroll member of the scroll compressor engages with a drive shaft of the scroll compressor; a thrust surface through which the main bearing housing supports the moving scroll member; and an oil drain passage formed in the main bearing housing and configured to extend from the recess to the outside of the main bearing housing, such that lubricant in the recess can be discharged from the oil drain passage, the main bearing housing 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 lubricant in the recess can be supplied to the thrust surface via the oil supply passage.

[0011] In the aforementioned main bearing housing, the main bearing housing may further include a groove for receiving an anti-rotation device, and the main bearing housing may also be provided with an oil supply channel formed in the main bearing housing and configured to extend from the recess to the groove.

[0012] According to another aspect of this disclosure, a main bearing housing for a scroll compressor is provided, the main bearing housing comprising: a recess in which a moving scroll of the scroll compressor engages with a drive shaft of the scroll compressor; a groove configured to receive an anti-rotation device; and an oil drain passage formed in the main bearing housing and configured to extend from the recess to the outside of the main bearing housing, such that lubricant in the recess can be discharged from the oil drain passage, the main bearing housing further comprising an oil supply passage formed in the main bearing housing and configured to extend from the recess to the groove, such that lubricant in the recess can be supplied to the groove via the oil supply passage.

[0013] In the aforementioned main bearing housing, the oil supply channel and the oil discharge channel can be configured to cooperate with each other to achieve a predetermined oil circulation rate. This cooperation can be achieved by controlling the distribution of lubricant between the oil supply channel and the oil discharge channel.

[0014] In the aforementioned main bearing housing, the distribution control 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 channel to lubricant entering the oil discharge channel, and n is controlled by changing the following parameters according to the following formula:

[0015]

[0016] Where r1 is the radius of the inlet of the oil drain channel, r2 is the radius of the outlet of the oil supply channel, v1 is the velocity of the lubricant at the inlet of the oil drain channel, and v2 is the velocity of the lubricant at the outlet of the oil supply channel.

[0017] In the aforementioned main bearing housing, the value of n can be controlled between 0.5 and 1.5 to ensure that the oil circulation rate is greater than 1% and less than 2%.

[0018] In the aforementioned main bearing housing, the distribution control can be achieved by changing the number of oil supply channels and / or the number of oil discharge channels.

[0019] In the aforementioned main bearing housing, the oil supply channel can be one or more oil supply channels.

[0020] In the aforementioned main bearing housing, there are multiple oil supply channels, at least one of which extends to the thrust surface and the remaining oil supply channels extend to the groove.

[0021] In the aforementioned main bearing housing, when there are multiple oil supply channels, the multiple oil supply channels can be arranged such that the outlets of the multiple oil supply channels are evenly distributed on the thrust surface, or the multiple oil supply channels can be arranged such that the outlets of the multiple oil supply channels extending into each groove are evenly distributed in the groove.

[0022] In the aforementioned main bearing housing, the oil supply channel and the oil discharge channel can be completely independent of each other.

[0023] In the aforementioned main bearing housing, the inlet of the oil supply channel and the inlet of the oil discharge channel can be located at the same position on the circumferential wall of the recess.

[0024] In the aforementioned main bearing housing, the oil supply channel can be a channel extending in a single direction.

[0025] In the aforementioned main bearing housing, the outlet of the oil supply channel extending into the groove can be located at the junction of the bottom surface and the side surface of the groove.

[0026] In the aforementioned 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 provides a thrust surface suitable for supporting the moving scroll member. The oil supply channel extends generally vertically through the thrust plate and opens into the groove. The oil discharge channel extends generally obliquely through the main bearing housing body and opens to the outside of the main bearing housing.

[0027] According to another aspect of this disclosure, a scroll compressor is provided, which may have any of the main bearing housings described above.

[0028] According to this disclosure, by providing an oil supply channel in the main bearing housing leading to the thrust surface and / or groove of the main bearing housing, the thrust surface and the cross-slip ring received in the groove are directly lubricated. This allows for a larger amount of lubricant to be provided in the thrust surface and groove, thereby achieving better lubrication of the thrust surface and the cross-slip ring. Furthermore, by configuring the oil supply channel and the oil discharge channel to cooperate with each other, a predetermined oil circulation rate is obtained by controlling the distribution of lubricant in the oil supply channel and the oil discharge channel. This achieves good lubrication of the cross-slip ring in the groove and the thrust surface, as well as good lubrication of the internal components of the compression mechanism, and also prevents excessive lubricant from entering the external system with the exhaust gas, thus avoiding system efficiency degradation.

[0029] The above-described features and advantages, as well as other features and advantages, of this disclosure will become clearer from the following detailed description of exemplary embodiments of the disclosure in conjunction with the accompanying drawings. Attached Figure Description

[0030] The above and other objects, features, and advantages of this disclosure can be more readily understood by referring to the following detailed description of exemplary embodiments of the present disclosure in conjunction with the accompanying drawings. In all the drawings, the same or corresponding technical features or components will be indicated by the same or corresponding reference numerals. In the drawings:

[0031] Figure 1a This is a top view of the compression mechanism and main bearing housing of a conventionally used scroll compressor.

[0032] Figure 1b For along Figure 1a A longitudinal sectional view of the compression mechanism and the vicinity of the main bearing housing, taken by line AA;

[0033] Figure 2 The longitudinal cross-sectional view of the lubricant supply path is shown with arrows based on Figure 1;

[0034] Figure 3 A side perspective view of a main bearing housing fitted with a cross-shaped slip ring is shown, in which the supply path of the lubricant is indicated by arrows;

[0035] Figure 4 A top view of the main bearing housing equipped with a cross ring is shown, in which the supply path of the lubricant is indicated by arrows;

[0036] Figure 5a and Figure 5b The images show a side perspective view and a longitudinal sectional view of the main bearing housing according to an embodiment of the present disclosure.

[0037] Figure 6a and Figure 6bThe images show a side perspective view and a longitudinal sectional view of the main bearing housing according to another embodiment of the present disclosure;

[0038] Figure 7a and Figure 7b The images show, respectively, an exemplary side perspective view and a longitudinal sectional view of a main bearing housing equipped with four oil supply channels;

[0039] Figure 8a and Figure 8b The images show, respectively, an exemplary side perspective view and a longitudinal sectional view of a main bearing housing equipped with four oil supply channels;

[0040] Figure 9a A longitudinal sectional view of a main bearing housing with an oil supply channel according to this disclosure is shown; and

[0041] Figure 9b To show in Figure 9a The graph and corresponding curves show the relationship between the value of n obtained from the test and the oil circulation rate in the case of the main bearing housing. Detailed Implementation

[0042] The present disclosure will now be described in detail with reference to the accompanying drawings and exemplary embodiments. It should be noted that the following detailed description is for illustrative purposes only and is not intended to limit the scope of the disclosure. Furthermore, the same reference numerals are used to denote the same parts in the various drawings.

[0043] First, refer to Figures 1a to 4 A simplified description of the scroll compressor's structure is provided. Taking a low-pressure side compressor as an example, the scroll compressor 100 includes a housing, a top cover at one end of the housing, a bottom cover at the other end of the housing, and a partition between the top cover and the housing. The partition divides the internal space of the scroll compressor into a high-pressure side between the partition and the top cover, and a low-pressure side between the partition, the housing, and the bottom cover. The housing contains a compression mechanism consisting of a fixed scroll member 5 and a moving scroll member 3, a drive mechanism consisting of a stator and a rotor, and a drive shaft 2. The drive shaft 2 is driven to rotate by the drive mechanism, causing the moving scroll member 3 to rotate relative to the fixed scroll member 5, thereby defining a series of compression chambers between the moving scroll member 3 and the fixed scroll member 5 to compress the fluid entering the scroll compressor. The fixed scroll member 5 includes an end plate, a spiral scroll extending from one side of the end plate, and an exhaust port formed at approximately the center of the end plate. The moving scroll member 3 includes an end plate 32, a spiral scroll extending from one side of the end plate 32, and a hub 31 extending from the other side of the end plate 32.

[0044] like Figure 1b As shown, the scroll compressor also includes a cross slip ring 4 and a main bearing housing 1.

[0045] The cross-slip ring 4 is annular in shape and mounted on the main bearing housing 1. The cross-slip ring 4 includes an annular body and two pairs of keys disposed on the body. One pair of keys engages with a pair of keyways on the moving scroll member 3 and can reciprocate linearly along the keyways. The other pair of keys engages with a pair of keyways on the fixed scroll member 5 and can reciprocate linearly along the keyways. During operation, the cross-slip ring reciprocates linearly relative to the fixed main bearing housing 1 and the fixed scroll member 5 under the drive of the moving scroll member 3. Simultaneously, the moving scroll member 3 reciprocates linearly in a direction approximately perpendicular to the direction of movement of the cross-slip ring, thus causing the moving scroll member 3 to rotate translatively relative to the fixed scroll member 5 via the cross-slip ring 4, but preventing it from rotating on its own axis. It should be noted that the cross-slip ring is merely one example of a feasible anti-rotation device. For example, an anti-rotation device without an annular body but only keys can also be used. In this case, insufficient lubrication of the keys also exists.

[0046] The main bearing housing 1 is configured to support the compression mechanism, particularly the moving scroll member 3, and to rotatably support the drive shaft 2. The main bearing housing 1 includes: a recess 11, located approximately at the center of the upper portion of the main bearing housing 1 and configured to receive the hub 31 of the moving scroll member 3, allowing the hub 31 to rotate translationally within the recess 11; a groove 14, located radially outward of the recess 11 and configured to receive a cross-slip ring 4 (particularly the annular body of the cross-slip ring 4), allowing the cross-slip ring 4 to move within the groove 14; and a thrust surface 12, the surface of the thrust plate of the main bearing housing 1 that interacts with the end plate 32 of the moving scroll member 3. The contact surface includes a thrust plate, which may be integral with the main bearing housing 1 or separate from it. The main bearing housing 1 supports the end plate 32 of the driven scroll member 3 via the thrust surface 12. A central hole 15 is located approximately at the center of the lower portion of the main bearing housing 1 and is configured to receive and rotatably support the drive shaft 2. An oil drain channel 13 is formed in the main bearing housing 1 and is configured to extend from the circumferential wall 16 of the recess 11 to the outside of the main bearing housing 1. It should be noted that, according to this disclosure, in addition to the circumferential wall 16, the oil drain channel 13 may also extend from other parts of the recess 11 (e.g., the lower portion).

[0047] During the operation of the scroll compressor, the lubricant stored in the oil reservoir at the bottom of the scroll compressor housing can be pumped through the central hole 21 of the drive shaft 2 and into the recess 11 of the main bearing housing 1 via a lubricant supply device such as an oil pump located at the bottom of the housing. Part of the lubricant in the recess 11 is used to lubricate the thrust surface 32 and the cross slip ring 4 received in the groove 14, while the remainder of the lubricant in the recess 11 is discharged from the recess 11 and returned to the oil reservoir through the oil drain channel 13, which extends radially from the recess 11 through the main bearing housing 1 and to the outside of the main bearing housing 1.

[0048] This disclosure improves the main bearing housing based on a commonly used scroll compressor, specifically by improving the lubricant supply method for the thrust surface and the cross slip ring. In addition to the existing oil drain channel, a lubricant supply channel for directly lubricating the thrust surface is added to the main bearing housing, and / or a lubricant supply channel for directly lubricating the cross slip ring in the groove is added to the main bearing housing, thereby providing better lubrication.

[0049] Therefore, the following description will focus only on the main bearing housing according to this disclosure and will omit further description of the other components and parts mentioned above.

[0050] Figure 5a and Figure 5b A main bearing housing 1 according to one embodiment of the present disclosure is shown, wherein, Figure 5a A side perspective view of the main bearing housing 1 according to this embodiment of the present disclosure is shown, and Figure 5b A longitudinal sectional view of the main bearing housing 1 according to this embodiment of the present disclosure is shown.

[0051] like Figure 5a and Figure 5b As shown, the main bearing housing 1 includes an oil supply channel 101 formed in the main bearing housing 1 and configured to extend from the circumferential wall 16 of the recess 11 through the main bearing housing 1 to the thrust surface 12, thereby communicating between the recess 11 and the thrust surface 12. Thus, lubricant in the recess 11 can be supplied to the thrust surface 12 via the oil supply channel 101. Furthermore, the remaining portion of the lubricant in the recess 11 can be discharged from the recess 11 through the oil drain channel 13 provided in the main bearing housing 1 as described above, returning to the oil reservoir. Figure 5bAs shown, the lubricant in the recess 11 enters the oil supply channel 101 from the inlet on the circumferential wall 16 of the recess 11 by means of the kinetic energy generated by the translational motion of the hub 31 of the moving vortex member 3 (if a counterweight is provided in the recess 11, the counterweight can also agitate the lubricant in the recess into the oil supply channel 101), and then exits through the oil supply channel 101 from the outlet on the thrust surface 12 of the oil supply channel 101, as shown. Figure 5b As indicated by the arrow in the oil supply channel 101, the lubricant leaving the oil supply channel 101 enters between the thrust surface 12 of the main bearing housing 1 and the end plate 32 of the moving scroll member 3, thereby lubricating the thrust surface 12 of the main bearing housing 1, and thus lubricating the surface of the end plate 32 of the moving scroll member 3 that contacts the thrust surface 12. Subsequently, as the end plate 32 of the moving scroll member 3 rotates, a portion of the lubricant located between the thrust surface 12 and the end plate 32 of the moving scroll member 3 is further pushed into the groove 14, and with the movement of the cross slip ring 4 received in the groove 14, the lubricant is pushed to the key of the cross slip ring 4, thereby lubricating the key of the cross slip ring 4.

[0052] Compared to the lubrication of the thrust surface and cross slip ring of the main bearing housing in conventional scroll compressors, in the embodiments of this disclosure, by providing an oil supply channel 101 that leads directly to the thrust surface 12, a larger amount of lubricant is provided to the thrust surface 12, and with the movement of the moving scroll 3, a larger amount of lubricant is provided to the groove 14 that receives the cross slip ring 4, so that both the thrust surface 12 and the cross slip ring 4 are better lubricated.

[0053] Figure 6a and Figure 6b It shows the relationship with Figure 5a and Figure 5b Another embodiment similar to the main bearing housing 1 shown herein, wherein, Figure 6a A side perspective view of the main bearing housing 1 according to another embodiment of the present disclosure is shown, and Figure 6b A longitudinal sectional view of the main bearing housing 1 according to another embodiment of this disclosure is shown.

[0054] It is conceivable that the main bearing housing 1 may include an oil supply channel 102 formed in the main bearing housing 1 and configured to extend from the circumferential wall 16 of the recess 11 through the main bearing housing 1 to the groove 14, thereby communicating between the recess 11 and the groove 14. Thus, lubricant in the recess 11 can be supplied to the groove 14 via the oil supply channel 102. Furthermore, the remainder of the lubricant in the recess 11 can be discharged from the recess 11 through the oil drain channel 13 to return to the oil reservoir. Similarly, as... Figure 6bAs shown, the lubricant in the recess 11 enters the oil supply channel 102 through an inlet at the circumferential wall 16 of the recess 11 by means of kinetic energy, and then exits through the oil supply channel 102 through an outlet in the groove 14 of the oil supply channel 102, as... Figure 6b As indicated by the arrow in the oil supply channel 102. The lubricant leaving the oil supply channel 102 enters the groove 14 to lubricate the cross-shaped slip ring 4 received in the groove 14.

[0055] Figure 6a and Figure 6b The location of the outlet of the oil supply channel 102 is shown. Specifically, the groove 14 is shown to include a bottom surface 141 and a side surface 142 extending upward from the bottom surface 141 to the thrust surface 12. The outlet of the oil supply channel 102 is located at the junction of the bottom surface 141 and the side surface 142 of the groove 14. With this arrangement, the lubricant leaving from the outlet of the oil supply channel 102 can better contact and be agitated by the annular body of the cross-shaped slip ring 4 as it moves in the groove 14, thereby achieving better lubrication of the cross-shaped slip ring 4.

[0056] Furthermore, it is conceivable that the main bearing housing 1 may include multiple oil supply channels. Figure 7a and Figure 7b The following are exemplary side perspective views and longitudinal sectional views of a main bearing housing 1 equipped with four oil supply channels 101. Figure 8a and Figure 8b The side perspective view and longitudinal sectional view of the main bearing housing 1, which is provided with four oil supply channels 102, are shown respectively, as examples.

[0057] By setting multiple oil supply channels, more lubricant can be supplied to the thrust surface 12 or the groove 14, and the lubricant can be supplied more evenly, thereby achieving better lubrication of the cross-shaped slip ring 4 in the thrust surface 12 or the groove 14. Figure 7a and Figure 7b as well as Figure 8a and Figure 8b As shown, the four oil supply channels 101 can be arranged such that their outlets are evenly distributed on the thrust surface 12, and the four oil supply channels 102 can be arranged such that their outlets are evenly distributed and correspondingly distributed in the grooves 14, so that the same number of oil supply channels 102 are arranged in each groove. It is conceivable that when multiple oil supply channels 102 are provided, the multiple oil supply channels can be arranged such that the outlets of the multiple oil supply channels extending into each groove are evenly distributed in the groove, thereby achieving more uniform lubrication of the cross slip ring 4 in the thrust surface 12 and the groove 14.

[0058] It is conceivable that the main bearing housing 1 may include both oil supply channel 101 and oil supply channel 102. When the main bearing housing 1 includes multiple oil supply channels, these multiple oil supply channels may include both oil supply channel 101 and oil supply channel 102. That is, at least one of the multiple oil supply channels is an oil supply channel 101 extending to the thrust surface 12, and the remaining oil supply channels are oil supply channels 102 extending to the groove 14. Thus, direct lubrication of the cross-shaped slip ring 4 in both the thrust surface 12 and the groove 14 can be achieved simultaneously, resulting in better lubrication.

[0059] In addition, such as Figure 5b or Figure 6b As shown, the inlet of the oil supply passage 101 or 102 and the inlet of the oil discharge passage 13 can be arranged at the same location on 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 can also be located at a different location on the circumferential wall 16 than the inlet of the oil discharge passage 13.

[0060] The control over oil circulation rate (OCR) and / or lubrication effect that can be achieved by means of the main bearing housing according to this disclosure will be described in detail below.

[0061] In general, in this disclosure, the oil supply passage and the oil discharge passage can be configured to cooperate with each other to achieve the optimal oil circulation rate, thereby achieving better lubrication of the thrust surface 12 and the cross slip ring 4, while also ensuring proper lubrication inside the compression mechanism and preventing excessive lubricant from entering the external system with the exhaust gas, which would lead to system efficiency degradation.

[0062] Specifically, the cooperation between the aforementioned oil supply channel and oil discharge channel is achieved by controlling the distribution of lubricant in the recess 11 between the oil supply channel and the oil discharge channel. Since the amount of lubricant that the lubricant supply device, such as an oil pump, can pump to the recess 11 is constant, the distribution percentage of lubricant can be controlled by controlling the amount of lubricant entering the oil supply channel and / or the amount of lubricant entering the oil discharge channel. This ensures both lubrication of the thrust surface 12 and the cross slip ring 4 and control of the oil circulation rate.

[0063] Now combine Figure 9a To elaborate further. Figure 6b similar, Figure 9a A longitudinal sectional view of the main bearing housing 1 with an oil supply channel 102 according to this disclosure is shown, wherein the oil supply path and the oil discharge path are indicated by arrows. Figure 9aIn the example shown, the main bearing housing 1 is a split type, comprising a main bearing housing body adapted to support the drive shaft and a thrust plate providing a thrust surface adapted to support the moving scroll member. The oil supply channel 102 extends generally vertically through the thrust plate and opens into the groove 14. The oil discharge channel 13 extends generally obliquely through the main bearing housing body and opens to the outside of the main bearing housing 1. With this configuration, the oil supply and discharge channels can be machined more easily, and the oil circulation rate can be flexibly controlled in different ways to achieve proper lubrication of the relevant moving parts. Figure 9a In this diagram, there is one oil supply channel 102 and one oil discharge channel 13, for ease of explanation. It should be noted that the following description can also be applied to the case where the main bearing housing 1 is provided with an oil supply channel 101, or both or more oil supply channels 101 and / or 102.

[0064] exist Figure 9a In the main bearing housing 1 according to this disclosure, the distribution of lubricant between the oil supply channel 102 and the oil discharge channel 13 can be controlled by controlling the value of n, where n is the distribution ratio of lubricant supplied to the outlet of the oil supply channel 102 to lubricant entering the oil discharge channel 13, and n is controlled by changing the following parameters according to the following formula:

[0065]

[0066] In the above formula, r1 is the radius of the inlet of the oil drain channel 13, r2 is the radius of the outlet of the oil supply channel 102, v1 is the velocity of the lubricant at the inlet of the oil drain channel 13, and v2 is the velocity of the lubricant at the outlet of the oil supply channel 102. The magnitudes of v1 and v2 are respectively related to the height positions of the inlet of the oil drain channel 13 and the outlet of the oil supply channel 102 in the axial direction of the main bearing housing 1. It should be noted that, as... Figure 9a As shown, the oil drain channel 13 can be a uniform circular hole, and the oil supply channel 102 can also be a uniform circular hole.

[0067] Therefore, the value of n can be controlled by controlling at least one of the radius of the inlet of the oil drain channel 13, the radius of the outlet of the oil supply channel 102, the speed of the lubricant at the inlet of the oil drain channel 13, and the speed of the lubricant at the outlet of the oil supply channel 102. By controlling the value of n, the oil circulation rate is made to be at a predetermined oil circulation rate, that is, the optimal oil circulation rate corresponding to the predetermined application conditions, thereby achieving better lubrication effect while controlling the oil circulation rate.

[0068] It is understood that, for the main bearing housing 1 provided with an oil supply channel 101 according to this disclosure, r2 in the above formula is the radius of the outlet of the oil supply channel 101 and v2 is the velocity of the lubricant at the outlet of the oil supply channel 101, and wherein the magnitude of v2 is related to the height position of the outlet of the oil supply channel 101 in the axial direction of the main bearing housing 1.

[0069] Furthermore, in the application of the above formula, the number of oil drain channels and / or oil supply channels is not limited, but can be multiple. When there are multiple oil drain channels and oil supply channels, the corresponding radii r1 and r2 can be obtained by converting the radii to equivalent radii. Additionally, it is understood that when the outlets of multiple oil supply channels are not at the same longitudinal height or the inlets of multiple oil drain channels are not at the same longitudinal height, the corresponding velocities v1 and v2 can also be obtained by converting the velocities to equivalent velocities.

[0070] Figure 9b To show in Figure 9a The graph and corresponding curves show the relationship between the value of n obtained from the test and the oil circulation rate under the condition of main bearing housing 1.

[0071] In this test, such as Figure 9b As shown in the diagram, the value of n is changed simply by altering the radius of the oil supply passage 102, thereby controlling the distribution ratio of lubricant between the oil supply passage 102 and the oil discharge passage 13 to obtain the optimal oil circulation rate. In a certain scroll compressor, the optimal oil circulation rate is less than 2% and simultaneously greater than 1%.

[0072] from Figure 9b As can be seen from the curve, when the oil circulation rate is within the above range, the corresponding value of n is between 0.5 and 1.5. Therefore, by controlling only the radius of the oil inlet channel 102, the value of n can be controlled between 0.5 and 1.5, resulting in an oil circulation rate greater than 1% and less than 2%. Within this oil circulation rate range, good lubrication can be achieved for the cross-shaped slip ring 4 in the groove 14 and the thrust surface, as well as for the internal components of the compression mechanism. Furthermore, excessive lubricant entering the external system with the exhaust gas can be avoided, preventing system efficiency degradation.

[0073] Preferably, the oil supply channels 101 and 102 can be configured as channels extending in a single direction, thereby making it easier to control the lubricant entering the oil discharge channels 101 and 102, and thus easier to control the distribution of lubricant between the oil supply channels and the oil discharge channels. However, it is understood that the oil supply channels 101 and 102 can also be configured as other types of channels, such as bent channels.

[0074] It is conceivable that the distribution of the lubricant between the oil supply channel and the oil discharge channel can be achieved by changing the number of oil supply channels and / or the number of oil discharge channels. Specifically, the amount of lubricant supplied to the thrust surface 12 and / or groove 14 can be changed by changing the number of oil supply channels and / or the amount of lubricant discharged can be changed by changing the number of oil discharge channels, thereby controlling the distribution of lubricant between the oil supply channel and the oil discharge channel to obtain the optimal oil circulation rate, while achieving proper lubrication of the thrust surface 12 and the cross slip ring 4.

[0075] Furthermore, according to this disclosure, the oil supply channel and the oil discharge channel are either completely independent channels or independent channels that share an inlet only in the recess. Compared with related technical solutions where the oil supply channel and the oil discharge channel share a portion of the channel or are in an upstream-downstream relationship, since the oil supply channel and the oil discharge channel are independent, the distribution of lubricant between the oil supply channel and the oil discharge channel can be effectively controlled, thereby effectively controlling the oil circulation rate while ensuring proper lubrication of the relevant moving parts.

[0076] Although this disclosure has been described with reference to exemplary embodiments, it should be understood that this disclosure is not limited to the specific embodiments described and shown herein. Various changes can be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the claims of this disclosure.

Claims

1. A main bearing housing (1) for a scroll compressor, the main bearing housing comprising: The recess (11) is where the moving scroll component of the scroll compressor engages with the drive shaft of the scroll compressor. Thrust surface (12), the main bearing housing supports the moving scroll member through the thrust surface; And an oil drain channel (13), which is formed in the main bearing housing and configured to extend from the recess to the outside of the main bearing housing, so that the lubricant in the recess can be discharged from the oil drain channel. The main bearing housing is characterized in that it further includes: An oil supply passage (101) is 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. The oil supply channel and the oil discharge channel are configured to cooperate to achieve a predetermined oil circulation rate. This cooperation is achieved by controlling the distribution of lubricant between the oil supply channel and the oil discharge channel. The distribution control 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 channel to lubricant entering the oil discharge channel, and n is controlled by changing the following parameters according to the following formula: Where r1 is the radius of the inlet of the oil drain channel, r2 is the radius of the outlet of the oil supply channel, v1 is the velocity of the lubricant at the inlet of the oil drain channel, and v2 is the velocity of the lubricant at the outlet of the oil supply channel. The value of n can be controlled between 0.5 and 1.5 so that the oil circulation rate is greater than 1% and less than 2%.

2. The main bearing housing according to claim 1, characterized in that, The main bearing housing also includes a groove (14) for receiving an anti-rotation device, and the main bearing housing is also provided with an oil supply channel (102) formed in the main bearing housing and configured to extend from the recess to the groove.

3. The main bearing housing according to claim 2, characterized in that, The oil supply channels are multiple, at least one of the multiple oil supply channels extends to the thrust surface and the remaining oil supply channels extend to the groove.

4. A main bearing housing (1) for a scroll compressor, the main bearing housing comprising: The recess (11) is where the moving scroll component of the scroll compressor engages with the drive shaft of the scroll compressor. A groove (14) configured to receive an anti-rotation device; And an oil drain channel (13), which is formed in the main bearing housing and configured to extend from the recess to the outside of the main bearing housing, so that the lubricant in the recess can be discharged from the oil drain channel. The main bearing housing is characterized in that it further includes: An oil supply passage (102) is 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. The oil supply channel and the oil discharge channel are configured to cooperate to achieve a predetermined oil circulation rate. This cooperation is achieved by controlling the distribution of lubricant between the oil supply channel and the oil discharge channel. The distribution control 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 channel to lubricant entering the oil discharge channel, and n is controlled by changing the following parameters according to the following formula: Where r1 is the radius of the inlet of the oil drain channel, r2 is the radius of the outlet of the oil supply channel, v1 is the velocity of the lubricant at the inlet of the oil drain channel, and v2 is the velocity of the lubricant at the outlet of the oil supply channel. The value of n can be controlled between 0.5 and 1.5 so that the oil circulation rate is greater than 1% and less than 2%.

5. The main bearing housing according to any one of claims 1, 2, and 4, characterized in that, The allocation can be controlled by changing the number of the oil supply channels and / or the number of the oil discharge channels.

6. The main bearing housing according to claim 1 or 4, characterized in that, The oil supply channel is one or more oil supply channels.

7. The main bearing housing according to claim 6, characterized in that, When there are multiple oil supply channels, the multiple oil supply channels are arranged such that the outlets of the multiple oil supply channels are evenly distributed on the thrust surface, or the multiple oil supply channels are arranged such that the outlets of the multiple oil supply channels extending into each groove are evenly distributed in the groove.

8. The main bearing housing according to any one of claims 1, 2, and 4, characterized in that, The oil supply channel and the oil discharge channel are completely independent of each other.

9. The main bearing housing according to any one of claims 1, 2, and 4, characterized in that, The inlet of the oil supply channel and the inlet of the oil discharge channel are located at the same position on the circumferential wall of the recess.

10. The main bearing housing according to any one of claims 1, 2, and 4, characterized in that, The oil supply channel is a channel that extends in a single direction.

11. The main bearing housing according to claim 2 or 4, characterized in that, The outlet of the oil supply channel extending into the groove is located at the junction of the bottom surface (141) and the side surface (142) of the groove.

12. The main bearing housing according to claim 2 or 4, characterized in that, The main bearing housing (1) includes a main bearing housing body and a thrust plate that are separate from each other. The thrust plate provides a thrust surface suitable for supporting the moving scroll member. The oil supply channel (102) extends generally vertically through the thrust plate and opens into the groove (14). The oil discharge channel (13) extends generally obliquely through the main bearing housing body and opens into the outside of the main bearing housing (1).

13. A scroll compressor, characterized in that, The scroll compressor includes the main bearing housing according to any one of claims 1 to 12.

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