Compressor

Abstract

The invention provides a compressor. The compressor comprises a shell, a motor arranged in the shell, a driving shaft connected to the motor, a first compression mechanism and a second compression mechanism, wherein the first compression mechanism and the second compression mechanism are connected to the driving shaft. The driving shaft penetrates through the first compression cavity of the shell and extends to the second compression cavity of the shell. The first compression mechanism and the second compression mechanism are arranged in the first compression cavity and the second compression cavity respectively. The second compression mechanism comprises a static scroll, a dynamic scroll, a lining seat, a lining and a bearing, wherein the static scroll and the dynamic scroll are meshed with each other; the lining seat is positioned at the end part of the driving shaft; the main axis of the driving shaft passes through the positioning convex part of the bushing seat, and the positioning convex part deflects by an angle relative to a straight line formed by connecting a plurality of contact points between the movable scroll and the static scroll. The bushing is sleeved on the positioning convex part, and the center line of the bushing is eccentric to the main axis. The bearing is sleeved on the bushing, and the orbiting scroll is sleeved on the bearing.

Description

Technical Field

[0001] The present invention relates to a compressor. Background Art

[0002] After the low-pressure gaseous fluid of the evaporator is sent to the secondary compressor, it is compressed in the first compression chamber and the second compression chamber respectively by the first compression mechanism and the second compression mechanism to form a high-pressure gaseous fluid, so as to improve the efficiency of the refrigeration cycle. For example, the first compression mechanism can be a screw compression mechanism, and the second compression mechanism can be a scroll compression mechanism.

[0003] In detail, the scroll compression mechanism includes a movable scroll and a stationary scroll, and the motor drives the movable scroll to revolve relative to the stationary scroll through a driving shaft. As the movable scroll revolves, the movable scroll and the stationary scroll generate multiple contact points in the radial direction to form multiple compression spaces whose volumes gradually decrease from the periphery to the center, so that the gaseous fluid is continuously pressurized to be converted into a high-pressure gaseous fluid and discharged from the center of the stationary scroll into the second compression chamber.

[0004] Generally speaking, the end of the drive shaft is an eccentric shaft portion, wherein the bushing is sleeved on the eccentric shaft portion, and the movable scroll is sleeved on the bushing through a bearing. Therefore, the inertial force generated by the movable scroll during orbiting will be transmitted to the eccentric shaft portion, which not only increases the load on the bearing, but also causes uneven force on the bearing, causing serious wear in specific areas of the bearing, affecting the operating efficiency and service life of the compressor. On the other hand, the bushing is slidably sleeved on the eccentric shaft portion in the radial direction, and the movable scroll can slide synchronously with the bushing in the radial direction. Because the multiple contact points between the movable scroll and the static scroll are connected in a straight line in the radial direction and coincide with the radial sliding path and retreat path of the bushing, when abnormally high pressure is generated in multiple compression spaces, the movable scroll and the bushing are not easy to slide in the radial direction, that is, the movable scroll and the bushing are not easy to produce radial retreat, resulting in the movable scroll being unable to smoothly orbit relative to the static scroll. Summary of the invention

[0005] The present invention is directed to a compressor, which helps to improve operating efficiency and service life.

[0006] According to one embodiment of the present invention, the compressor includes a housing, a motor, a drive shaft, a first compression mechanism and a second compression mechanism. The housing has a first compression chamber and a second compression chamber that are connected. The motor is arranged in the housing. The drive shaft is connected to the motor. The drive shaft passes through the first compression chamber and extends to the second compression chamber. The first compression mechanism is arranged in the first compression chamber and is connected to the drive shaft. The second compression mechanism is arranged in the second compression chamber and includes a stationary scroll, a movable scroll, a bushing seat, a bushing and a bearing. The movable scroll is engaged with the stationary scroll and has a plurality of contact points with the stationary scroll to form a plurality of compression spaces. The bushing seat is positioned at the end of the drive shaft and has a positioning protrusion. The main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is deflected by an angle relative to the straight line formed by the plurality of contact points. The bushing is sleeved on the positioning protrusion, and the center line of the bushing is eccentric to the main axis. The bearing is sleeved on the bushing, and the movable scroll is sleeved on the bearing.

[0007] According to another embodiment of the present invention, the compressor includes a housing, a motor, a drive shaft and a compression mechanism. The housing has a compression chamber. The motor is disposed in the housing. The drive shaft is connected to the motor. The drive shaft extends to the compression chamber. The compression mechanism is disposed in the compression chamber and includes a stationary scroll, a movable scroll, a bushing seat, a bushing and a bearing. The movable scroll is engaged with the stationary scroll and has a plurality of contact points with the stationary scroll to form a plurality of compression spaces. The bushing seat is positioned at the end of the drive shaft and has a positioning protrusion. The main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is deflected at an angle relative to a straight line formed by the plurality of contact points. The bushing is sleeved on the positioning protrusion, and the center line of the bushing is eccentric to the main axis. The bearing is sleeved on the bushing, and the movable scroll is sleeved on the bearing.

[0008] Based on the above, in the compressor of the present invention, the bushing seat is positioned at the end of the drive shaft, wherein the movable scroll is connected to the positioning protrusion of the bushing seat through the bearing and the bushing, and the center line of the bushing is eccentric to the main axis of the drive shaft. In detail, multiple contact points between the movable scroll and the stationary scroll form multiple closed spaces, and the positioning protrusion is deflected at an angle relative to the straight line connected by the multiple contact points, so that the bearing can be evenly stressed when the movable scroll revolves, preventing a specific area of ​​the bearing from being severely worn due to excessive force, thereby improving the operating efficiency and service life of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1A is a schematic diagram of a compressor according to an embodiment of the present invention;

[0010] Figure 1B yes Figure 1A A schematic side view of a compressor;

[0011] Figure 1C yes Figure 1A A schematic cross-sectional view of the compressor along line segment II;

[0012] Figure 1D yes Figure 1C A partial enlarged schematic diagram of the part A in FIG.

[0013] Figure 1E yes Figure 1A A schematic cross-section of the compressor along line segment JJ;

[0014] Figure 1F yes Figure 1E A partial enlarged schematic diagram of the part B in FIG.

[0015] Figure 2A It is a schematic diagram of the combination of a movable scroll and a bushing seat according to an embodiment of the present invention;

[0016] Figure 2B yes Figure 2A Explosion diagram of

[0017] Figure 2C yes Figure 2B A front view schematic diagram of a bearing, a bushing and a bushing seat;

[0018] Figure 2D and Figure 2E yes Figure 2C Schematic diagram of the bushing seat at two different viewing angles;

[0019] Figure 3A and Figure 3B is a schematic diagram of a bushing seat according to another embodiment of the present invention at two different viewing angles;

[0020] Figure 4A is a front view schematic diagram of a bearing, a bushing and a bushing seat according to another embodiment of the present invention;

[0021] Figure 4B yes Figure 4A A schematic diagram of a bushing seat;

[0022] Figure 5 It is a cross-sectional schematic diagram of a compressor according to another embodiment of the present invention. DETAILED DESCRIPTION

[0023] Reference will now be made in detail to exemplary embodiments of the present invention, examples of which are illustrated in the accompanying drawings. Whenever possible, the same reference numerals are used in the drawings and the description to refer to the same or like parts.

[0024] Figure 1A Schematic diagram of a compressor according to an embodiment of the present invention. Figure 1B yes Figure 1A Schematic side view of a compressor. Figure 1C yes Figure 1A Schematic diagram of the cross section of the compressor along line segment II. Figure 1D yes Figure 1CA partial enlarged schematic diagram of part A in FIG. Figures 1A to 1C In this embodiment, the compressor 10 may be a two-stage compressor, and includes a housing 11, a motor 12, a drive shaft 13, a first compression mechanism 14, and a second compression mechanism 100. In detail, the housing 11 has a first compression chamber 11a and a second compression chamber 11b that are connected, wherein the motor 12 is disposed in the housing 11, and the drive shaft 13 is connected to the motor 12. The first compression mechanism 14 and the second compression mechanism 100 are disposed in the first compression chamber 11a and the second compression chamber 11b, respectively, wherein the drive shaft 13 passes through the first compression chamber 11a and extends to the second compression chamber 11b.

[0025] Please refer to Figure 1C and Figure 1D , the first compression mechanism 14 may be a screw compression mechanism, and the second compression mechanism 100 may be a scroll compression mechanism. The first compression mechanism 14 is connected to the drive shaft 13, and the second compression mechanism 100 is connected to the end 13a of the drive shaft 13 located in the second compression chamber 11b. The motor 12 can drive the first compression mechanism 14 and the second compression mechanism 100 to operate synchronously through the drive shaft 13, so that the low-pressure gaseous fluid is compressed by the first compression mechanism 14 and the second compression mechanism 100 in the first compression chamber 11a and the second compression chamber 11b respectively to form a high-pressure gaseous fluid, and then discharged from the second compression chamber 11b.

[0026] Figure 1E yes Figure 1A Schematic diagram of the cross section of the compressor along line segment JJ. Figure 1F yes Figure 1E This is a partial enlarged schematic diagram of part B in the figure. Please refer to Figure 1C to Figure 1F In this embodiment, the second compression mechanism 100 includes a stationary scroll 110, a movable scroll 120, a bushing seat 130, a bushing 140 and a bearing 150. The stationary scroll 110 is fixed in the second compression chamber 11b, and the movable scroll 120 is engaged with the stationary scroll 110. The movable scroll 120 can be driven by the driving shaft 13 to revolve relative to the stationary scroll 110. During the revolving of the movable scroll 120 relative to the stationary scroll 110, a plurality of contact points 101 are generated between the movable scroll 120 and the stationary scroll 110, and a plurality of compression spaces 102 whose volumes gradually decrease from the periphery to the center are formed, so that the gaseous fluid is continuously pressurized to be converted into a high-pressure gaseous fluid, and then discharged from the center of the stationary scroll 110 to the second compression chamber 11b.

[0027] Please refer to Figures 1D to 1F, the bushing seat 130 is positioned at the end 13a of the drive shaft 13, and has a positioning protrusion 131 protruding toward the fixed scroll 110. The main axis 13b of the drive shaft 13 passes through the positioning protrusion 131, and the positioning protrusion 131 is deflected by an angle α relative to a straight line 103 formed by a plurality of contact points 101. On the other hand, the movable scroll 120 is connected to the positioning protrusion 131 of the bushing seat 130 through a bearing 150 and a bushing 140, wherein the movable scroll 120 is sleeved on the bearing 150, and the bearing 150 is sleeved on the bushing 140. The bushing 140 is sleeved on the positioning protrusion 131, and the center line 141 of the bushing 140 is eccentric to the main axis 13b.

[0028] Therefore, when the drive shaft 13 drives the bushing seat 130 to rotate, the movable scroll 120, the bearing 150 and the bushing 140 can eccentrically revolve around the main axis 13b. Under the design of the deflection angle α of the positioning protrusion 131 relative to the straight line 103, the bearing 150 can be evenly stressed when the movable scroll 120 revolves, preventing a specific area of ​​the bearing 150 from being severely worn due to excessive stress, thereby improving the operating efficiency and service life of the compressor 100.

[0029] For example, the deflection angle α of the positioning protrusion 131 relative to the straight line 103 formed by the plurality of contact points 101 may be an acute angle. Preferably, the angle α may be between 5 degrees and 45 degrees. More preferably, the angle α may be equal to 15 degrees.

[0030] Please refer to Figures 1D to 1F In this embodiment, the bushing 140 has a through groove 142, wherein the positioning protrusion 131 is disposed in the through groove 142, and the height of the positioning protrusion 131 is less than the depth of the through groove 142. By means of the cooperation between the positioning protrusion 131 and the through groove 142, the bushing 140 can reciprocate or radially slide relative to the bushing seat 130 within a set stroke, and cannot rotate relative to the bushing seat 130. In terms of the main extension direction of the through groove 142, the through groove 142 deflects at an angle α relative to the straight line 103 formed by the plurality of contact points 101. Further, the positioning protrusion 131 has a positioning baseline 131a passing through the main axis 13b and parallel to the through groove 142, and an angle α is sandwiched between the positioning baseline 131a and the straight line 103 formed by the plurality of contact points 101.

[0031] In other words, the cooperation between the positioning protrusion 131 and the through groove 142 determines the sliding path and retreat path of the bushing 140 and the movable scroll 120, and the sliding path and retreat path of the bushing 140 coincide with the positioning baseline 131a. Therefore, the sliding path and retreat path of the bushing 140 and the straight line 103 formed by the plurality of contact points 101 form an angle α.

[0032] Please refer to Figure 1FThe positioning protrusion 131 also has two opposite long sides 1311 and two opposite short sides 1312, and the two short sides 1312 are connected between the two long sides 1311. Specifically, since the two long sides 1311 are parallel to the positioning baseline 131a, the two long sides 1311 can be deflected by an angle α in the clockwise and counterclockwise directions relative to the straight line 103 connected by the plurality of contact points 101. In addition, the positioning baseline 131a extends through the two short sides 1312.

[0033] Correspondingly, the through slot 142 has two long sides 1421 facing the two long sides 1311 respectively and two short sides 1422 facing the two short sides 1312 respectively, wherein the two long sides 1421 are parallel to the positioning baseline 131a, and the positioning baseline 131a extends through the two short sides 1422. Since the two long sides 1421 are parallel to the positioning baseline 131a, the two long sides 1421 can be deflected by an angle α in the clockwise and counterclockwise directions respectively relative to the straight line 103 formed by the plurality of contact points 101.

[0034] Please refer to Figures 1D to 1F In the process of the movable scroll 120 orbiting relative to the stationary scroll 110, the movable scroll 120, the bearing 150 and the bushing 140 can slide synchronously in the radial direction relative to the bushing seat 130 and the stationary scroll 110, and the radial sliding path and the retreat path of the bushing 140 are deflected by an angle α relative to the straight line 103 connected by multiple contact points 101 (that is, the radial sliding path and the retreat path of the bushing 140 do not coincide with the straight line 103 connected by multiple contact points 101). Since the direction of the straight line 103 is different from the retreat direction (parallel to the positioning baseline 131a), even if the multiple compression spaces 102 generate abnormally high pressures, the movable scroll 120, the bearing 150 and the bushing 140 can still slide in the radial direction or produce radial retreat to maintain the smoothness of the orbiting of the movable scroll 120, which helps to improve the operating efficiency of the compressor 100.

[0035] Please refer to Figure 1C and Figure 1D In this embodiment, the second compression mechanism 100 further includes a fixing block 160 and a locking member 170. The fixing block 160 is disposed in the bushing 140 and abuts against the positioning protrusion 131. On the other hand, the locking member 170 passes through the fixing block 160 and the positioning protrusion 131 and is locked into the end 13a of the driving shaft 13 to position the bushing seat 130 at the end 13a of the driving shaft 13. For example, the locking member 170 may be a bolt.

[0036] like Figure 1D and Figure 1FAs shown, the positioning protrusion 131 also has a first through hole 131b, and the main axis 13b of the drive shaft 13 passes through the first through hole 131b. The locking member 170 first passes through the fixing block 160 and then passes through the first through hole 131b, and then is locked into the end 13a of the drive shaft 13, so as to position the movable scroll 120, the bearing 150, the bushing 140 and the bushing seat 130 into the end 13a of the drive shaft 13.

[0037] On the other hand, the positioning protrusion 131 further has a second through hole 131c, wherein the connection between the first through hole 131b and the second through hole 131c coincides with the positioning baseline 131a, and deflects at an angle α relative to the straight line 103 formed by the plurality of contact points 101. In other words, the first through hole 131b is used to adjust the positioning protrusion 131 to produce a deflection angle α, and the connection between the first through hole 131b and the second through hole 131c fixes the deflection angle α of the positioning protrusion 131, so that the retreat direction (parallel to the positioning baseline 131a) of the movable scroll 120, the bearing 150 and the bushing 140 avoids the plurality of contact points 101 or the straight line 103 between the movable scroll 120 and the stationary scroll 110, so that retreat can be produced by a relatively small force (which can be called retreat force), thereby preventing a specific area of ​​the bearing 150 from being seriously worn due to excessive force.

[0038] Figure 2A It is a schematic diagram of the combination of a movable scroll and a bushing seat according to an embodiment of the present invention. Figure 2B yes Figure 2A Explosion diagram. Figure 2C yes Figure 2B See the front view of the bearing, bushing and bushing seat. FIG. 2A to FIG. 2C In the present embodiment, the bushing 140 is supported on the bushing seat 130 , and the center line 141 of the bushing 140 is inclined at an angle β relative to the main axis 13 b , and the angle β may be between 0.5 and 5 degrees.

[0039] like Figure 1F , Figure 2A and Figure 2CAs shown, the bearing 150 is tilted with the bushing 140 relative to the main axis 13b, but the movable scroll 120 is not tilted relative to the main axis 13b, so the bearing 150 can be evenly stressed when the movable scroll 120 revolves, preventing a specific area of ​​the bearing 150 from being severely worn due to excessive stress, thereby improving the operating efficiency and service life of the compressor 100. In addition, when the movable scroll 120 revolves relative to the stationary scroll 110, the retreat direction of the movable scroll 120 is parallel to the long side 1311 of the positioning protrusion 131 or the positioning baseline 131a, and avoids the multiple contact points 101 or straight lines 103 between the movable scroll 120 and the stationary scroll 110. Therefore, the centripetal force of the movable scroll 120 during the revolving is small, so that retreat is generated in the radial direction through a small force (which can be called retreat force), preventing a specific area of ​​the bearing 150 from being severely worn due to excessive stress.

[0040] Figure 2D and Figure 2E yes Figure 2C Schematic diagram of the bushing seat at two different viewing angles. Please refer to FIG. 2C to FIG. 2E , the bushing seat 130 also has a first bearing surface 132 and a second bearing surface 133 connected to the first bearing surface 132, and the positioning protrusion 131 protrudes from the first bearing surface 132 and the second bearing surface 133. In detail, the first bearing surface 132 is higher than the second bearing surface 133, and the bushing 140 contacting the first bearing surface 132 and the second bearing surface 133 can be tilted due to the height difference between the first bearing surface 132 and the second bearing surface 133, so that the center line 141 of the bushing 140 is tilted relative to the main axis 13b. On the other hand, in order to ensure that the bushing 140 contacting the first bearing surface 132 and the second bearing surface 133 is tilted on the bushing seat 130, the area of ​​the first bearing surface 132 with a higher height is smaller than the area of ​​the second bearing surface 133 with a lower height.

[0041] like Figure 2D and Figure 2E As shown, the height difference between the first bearing surface 132 and the second bearing surface 133 is between 0.5 mm and 5 mm. In addition, the distribution range of the second bearing surface 133 extends from one of the long sides 1311 to the two short sides 1312, and extends to at least half of each short side 1312, that is, the distribution range is between 1 / 2 of the length of the short side 1312 and the entire length.

[0042] Figure 3A and Figure 3B Schematic diagram of a bushing seat according to another embodiment of the present invention at two different viewing angles. Figure 3A and Figure 3B , different from Figure 2D and Figure 2EIn the bushing seat 130 shown in the figure, the second bearing surface 133 of the bushing seat 130a of this embodiment is higher than the first bearing surface 132, and the area of ​​the second bearing surface 133 with a higher height is smaller than the area of ​​the first bearing surface 132 with a lower height. In detail, the distribution range of the first bearing surface 132 extends from one of the long sides 1311 to the two short sides 1312, and extends to at least half of each short side 1312, that is, the distribution range is between 1 / 2 of the side length of the short side 1312 and the entire side length, such as Figure 3B shown.

[0043] The height design of the two bearing surfaces of the bushing seat is determined by the orbiting direction of the movable scroll. For example, Figure 2D and Figure 2E The bushing seat 130 shown is suitable for a clockwise rotating orbiting scroll, so that the orbiting scroll that starts to orbit first passes through the lower surface (i.e., the second bearing surface 133). Figure 3A and Figure 3B The bushing seat 130a shown is suitable for a movable scroll that rotates counterclockwise, so that the movable scroll that begins to rotate first passes through the lower surface (i.e., the first bearing surface 132). When the movable scroll 120 retreats, the second bearing surface 133 supported by the bottom of the bushing seat 130 is a low surface rather than a high surface, so that the retreat resistance is smaller. The movable scroll 120 can retreat with a smaller force (which can be called a retreat force), thereby preventing a specific area of ​​the bearing 150 from being severely worn due to excessive force.

[0044] Figure 4A It is a front view schematic diagram of a bearing, a bushing and a bushing seat according to another embodiment of the present invention. Figure 4B yes Figure 4A Please refer to the schematic diagram of the bushing seat. Figure 4A and Figure 4B Different from the bushing seat 130 or the bushing seat 130a of the previous embodiment, the bearing surface of the bushing seat 130b of this embodiment is a bearing inclined surface 134. In detail, the bushing 140 contacts the bearing inclined surface 134, so that the center line 141 of the bushing 140 is inclined at an angle β relative to the main axis 13b, and the angle β can be between 0.5 degrees and 5 degrees.

[0045] The height design of the supporting slope of the bushing seat is determined by the orbiting direction of the movable scroll. For example, a bushing seat with a supporting slope that is higher on the left and lower on the right is suitable for a movable scroll that orbits clockwise, so that the movable scroll that begins to orbit first orbits the lower surface. Conversely, a bushing seat with a supporting slope that is higher on the right and lower on the left is suitable for a movable scroll that orbits counterclockwise, so that the movable scroll that begins to orbit first orbits the lower surface.

[0046] Figure 51 is a cross-sectional schematic diagram of a compressor of another embodiment of the present invention. The compressor 10 of the previous embodiment is a two-stage compressor, in which a screw compression mechanism and a scroll compression mechanism are respectively provided in two connected compression chambers. Figure 5 The compressor 20 shown is a single-stage compressor, wherein the housing 21 has a single compression chamber 21 a , and a single compression mechanism 100 a , such as a scroll compression mechanism, is disposed in the compression chamber 21 a .

[0047] like Figure 5 As shown, the motor 22 and the drive shaft 23 are disposed in the housing 21, wherein the drive shaft 23 is connected to the motor 22 and extends to the compression chamber 21a to be connected to the compression mechanism 100a. In detail, the motor 22 can drive the compression mechanism 100a to operate through the drive shaft 23, so that the low-pressure gaseous fluid in the compression chamber 21a is compressed by the compression mechanism 100a to form a high-pressure gaseous fluid, and then discharged from the compression chamber 21a.

[0048] The compression mechanism 100a of this embodiment is the same as the second compression mechanism 100 of the previous embodiment, which is a scroll compression mechanism and has the same structural design, such as the coordination between the stationary scroll and the movable scroll, the structural design of the bushing seat, the coordination between the bushing seat and the drive shaft, the structural design of the bushing, the coordination between the bushing and the bushing seat, the relative relationship between the center line of the bushing and the main axis of the drive shaft (such as the eccentric relationship and the inclined relationship), and the coordination between the bushing, the bearing and the movable scroll, etc., which will not be elaborated here.

[0049] In summary, in the compressor of the present invention, the bushing seat is positioned at the end of the drive shaft, wherein the movable scroll is connected to the positioning protrusion of the bushing seat through the bearing and the bushing, and the bushing can make the center line of the bushing eccentric to the main axis of the drive shaft due to the height difference between the first bearing surface and the second bearing surface (or the bearing inclined surface). In detail, multiple contact points between the movable scroll and the static scroll form multiple enclosed spaces, and the positioning protrusion is deflected at an angle relative to the straight line connected by the multiple contact points, so that the retreat direction is different from the direction of the straight line, and the bearing surface (or the bearing inclined surface) is a low surface when the movable scroll retreats, and the retreat resistance of the movable scroll is small, so retreat can be generated by a smaller force, so that the bearing can be evenly stressed when the movable scroll revolves, preventing a specific area of ​​the bearing from being severely worn due to excessive force, thereby improving the operating efficiency and service life of the compressor.

[0050] On the other hand, during the process of the movable scroll orbiting relative to the stationary scroll, the movable scroll, the bearing and the bushing can slide synchronously in the radial direction relative to the stationary scroll. Since the radial sliding path or the retreat path of the bushing is deflected at an angle relative to the straight line formed by multiple contact points (that is, the radial sliding path or the retreat path of the bushing does not coincide with the straight line formed by multiple contact points), even if abnormally high pressure is generated in multiple compression spaces, the movable scroll, the bearing and the bushing can still slide in the radial direction or produce radial retreat to maintain the smoothness of the orbiting of the movable scroll, which helps to improve the operating efficiency of the compressor.

[0051] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A compressor, characterized in that: include: The housing has a first compression chamber and a second compression chamber that are connected to each other; A motor is disposed in the housing; a drive shaft connected to the motor, wherein the drive shaft passes through the first compression chamber and extends to the second compression chamber; a first compression mechanism, disposed in the first compression chamber and connected to the drive shaft; as well as The second compression mechanism is disposed in the second compression chamber and comprises: static vortex; A movable scroll meshed with the stationary scroll and having a plurality of contact points with the stationary scroll to form a plurality of compression spaces; A bushing seat is positioned at the end of the drive shaft and has a positioning protrusion, wherein the main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is deflected by an angle relative to a straight line formed by the plurality of contact points; a bushing, sleeved on the positioning protrusion, wherein the center line of the bushing is eccentric to the main axis; and The bearing is sleeved on the bushing, and the movable scroll is sleeved on the bearing.

2. The compressor according to claim 1, characterized in that The bushing has a through groove, and the positioning protrusion is arranged in the through groove, and the through groove is deflected by the angle relative to the straight line formed by the multiple contact points.

3. The compressor according to claim 2, characterized in that The positioning protrusion has a positioning base line passing through the main axis and parallel to the through groove, and the positioning base line and the straight line formed by connecting the plurality of contact points form the angle.

4. The compressor according to claim 1, characterized in that The bushing is suitable for reciprocatingly sliding relative to the bushing seat along a sliding path, and the sliding path and the straight line formed by connecting the plurality of contact points form the angle.

5. The compressor according to claim 4, characterized in that The positioning protrusion has a positioning baseline passing through the main axis, and the positioning baseline coincides with the sliding path. The positioning baseline and the straight line formed by connecting the plurality of contact points form an angle.

6. The compressor according to claim 1, characterized in that The angle is an acute angle.

7. The compressor according to claim 6, characterized in that The angle is between 5 degrees and 45 degrees.

8. The compressor according to claim 7, characterized in that Said angle is equal to 15 degrees.

9. The compressor according to claim 1, characterized in that The positioning protrusion has a long side and a short side connecting the long side, and the long side is deflected by the angle relative to the straight line formed by the plurality of contact points.

10. The compressor according to claim 1, characterized in that The second compression mechanism also includes: a fixing block, disposed in the bushing and abutting against the positioning protrusion; and A locking piece passes through the fixing block and the positioning protrusion and is locked into the end of the driving shaft.

11. The compressor according to claim 10, characterized in that The positioning protrusion has a first through hole, and the main axis of the driving shaft passes through the first through hole. The locking piece passes through the first through hole and is locked into the end of the driving shaft.

12. The compressor according to claim 11, characterized in that The positioning protrusion further has a second through hole, and the connection between the first through hole and the second through hole is deflected by the angle relative to the straight line formed by the plurality of contact points.

13. The compressor according to claim 1, characterized in that The bushing seat also has a first bearing surface and a second bearing surface connected to the first bearing surface, and the positioning protrusion protrudes from the first bearing surface and the second bearing surface, there is a height difference between the first bearing surface and the second bearing surface, the bushing contacts the first bearing surface and the second bearing surface, and the center line of the bushing is inclined relative to the main axis.

14. The compressor according to claim 13, characterized in that The centerline of the bushing is inclined by 0.5 to 5 degrees relative to the main axis.

15. The compressor according to claim 13, characterized in that One of the first supporting surface and the second supporting surface is higher than the other of the first supporting surface and the second supporting surface, and an area of ​​the higher one of the first supporting surface and the second supporting surface is smaller than an area of ​​the lower one of the first supporting surface and the second supporting surface.

16. The compressor according to claim 13, characterized in that The height difference between the first bearing surface and the second bearing surface is between 0.05 mm and 0.5 mm.

17. The compressor according to claim 13, characterized in that The positioning protrusion has two opposite long sides and two opposite short sides, and the two short sides are connected between the two long sides. The distribution range of the first bearing surface extends along one of the long sides toward the two short sides and extends to at least half of each of the short sides.

18. The compressor according to claim 1, characterized in that The bushing seat also has a bearing inclined surface, and the positioning protrusion protrudes from the bearing inclined surface. The bushing contacts the bearing inclined surface, and the center line of the bushing is inclined relative to the main axis.

19. The compressor according to claim 18, characterized in that The centerline of the bushing is inclined by 0.5 to 5 degrees relative to the main axis.

20. The compressor according to claim 1, characterized in that The first compression mechanism is a screw compression mechanism.

21. A compressor, characterized in that: include: A housing having a compression chamber; A motor is disposed in the housing; a drive shaft connected to the motor, wherein the drive shaft extends to the compression chamber; as well as A compression mechanism is disposed in the compression chamber and comprises: static vortex; A movable scroll meshed with the stationary scroll and having a plurality of contact points with the stationary scroll to form a plurality of compression spaces; A bushing seat is positioned at the end of the drive shaft and has a positioning protrusion, wherein the main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is deflected by an angle relative to a straight line formed by the plurality of contact points; a bushing, sleeved on the positioning protrusion, wherein the center line of the bushing is eccentric to the main axis; and The bearing is sleeved on the bushing, and the movable scroll is sleeved on the bearing.

22. The compressor according to claim 21, characterized in that The bushing has a through groove, and the positioning protrusion is arranged in the through groove, the through groove is deflected by the angle relative to the straight line formed by the multiple contact points, the positioning protrusion has a positioning baseline passing through the main axis and parallel to the through groove, and the angle is sandwiched between the positioning baseline and the straight line formed by the multiple contact points.

23. The compressor according to claim 21, characterized in that The bushing is suitable for reciprocating sliding relative to the bushing seat along a sliding path, and the sliding path and the straight line formed by the multiple contact points have the angle, the positioning protrusion has a positioning baseline passing through the main axis, and the positioning baseline coincides with the sliding path, and the positioning baseline and the straight line formed by the multiple contact points have the angle.

24. The compressor according to claim 21, characterized in that The angle is between 5 degrees and 45 degrees.

25. The compressor according to claim 21, characterized in that The bushing seat also has a first bearing surface and a second bearing surface connected to the first bearing surface, and the positioning protrusion protrudes from the first bearing surface and the second bearing surface, there is a height difference between the first bearing surface and the second bearing surface, the bushing contacts the first bearing surface and the second bearing surface, and the center line of the bushing is inclined relative to the main axis.

26. The compressor according to claim 25, characterized in that The centerline of the bushing is inclined by 0.5 to 5 degrees relative to the main axis.

27. The compressor according to claim 25, characterized in that One of the first supporting surface and the second supporting surface is higher than the other of the first supporting surface and the second supporting surface, and an area of ​​the higher one of the first supporting surface and the second supporting surface is smaller than an area of ​​the lower one of the first supporting surface and the second supporting surface.

28. The compressor according to claim 25, characterized in that The height difference between the first bearing surface and the second bearing surface is between 0.05 mm and 0.5 mm.

29. The compressor according to claim 21, characterized in that The bushing seat also has a bearing inclined surface, and the positioning protrusion protrudes from the bearing inclined surface. The bushing contacts the bearing inclined surface, and the center line of the bushing is inclined relative to the main axis.

30. The compressor according to claim 29, characterized in that The centerline of the bushing is inclined by 0.5 to 5 degrees relative to the main axis.

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