TWM651447U - Compressor - Google Patents

Abstract

A compressor including a housing, a motor disposed in the housing, a driving shaft connected to the motor, a first compression mechanism connected to the driving shaft and a second compression mechanism is provided. The driving shaft passes through a first compression chamber of the housing and extends into a second compression chamber of the housing. The first compression mechanism and the second compression mechanism are respectively disposed in the first compression chamber and the second compression chamber. The second compression mechanism includes a stationary scroll, a movable scroll engaged with the stationary scroll, a bushing seat positioned at an end portion of the driving shaft, a bushing and a bearing. A main axis of the driving shaft passes through a positioning protrusion of the bushing seat, and the positioning protrusion deviates from a straight line formed by a plurality of contact points between the movable scroll and the stationary scroll in an angle. The bushing is sleeved on the positioning protrusion, and a 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.

Description

compressor

The new invention relates to a compressor.

After the low-pressure gaseous fluid from the evaporator is sent to the two-stage 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 to improve the refrigeration cycle efficiency. For example, the first compression mechanism may be a screw compression mechanism, and the second compression mechanism may be a scroll compression mechanism.

Specifically, the scroll compression mechanism includes an movable scroll and a fixed scroll, and the motor drives the movable scroll to orbit relative to the fixed scroll through the drive 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 It is converted into high-pressure gaseous fluid and discharged from the second compression chamber through the center of the static scroll.

Generally speaking, the end of the driving shaft is an eccentric shaft part, wherein the bushing is sleeved on the eccentric shaft part, and the orbiting scroll is sleeved on the bushing through the bearing. Therefore, the inertial force generated by the orbiting scroll will be transmitted to the eccentric shaft, which not only increases the load on the bearing, but also causes uneven force on the bearing, causing severe wear in specific areas of the bearing, affecting the 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 stationary 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 abnormal high pressure is generated in multiple compression spaces, the movable scroll It is not easy for the movable scroll and the bushing to slide in the radial direction, that is, the movable scroll and the bushing are not easy to retreat in the radial direction, resulting in the movable scroll unable to smoothly rotate relative to the fixed scroll.

The new model provides a compressor that helps improve operating efficiency and service life.

This new invention proposes a compressor, which 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 disposed in the first compression chamber and connected to the drive shaft. The second compression mechanism is disposed in the second compression chamber and includes a fixed scroll, a movable scroll, a bushing seat, a bushing and a bearing. The movable scroll meshes with the fixed scroll and has multiple contact points with the fixed scroll to form multiple 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 connected by multiple 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.

This new creation proposes another compressor, including a casing, a motor, a drive shaft and compression mechanism. The housing has a compression chamber. The motor is arranged in the housing. The drive shaft is connected to the motor. The drive shaft extends into the compression chamber. The compression mechanism is arranged in the compression chamber and includes a fixed scroll, a moving scroll, a bushing seat, a bushing and a bearing. The movable scroll meshes with the fixed scroll and has multiple contact points with the fixed scroll to form multiple 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 connected by multiple 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.

Based on the above, in the compressor created by the present invention, the bushing seat is positioned at the end of the drive shaft, in which 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. Specifically, multiple contact points between the movable scroll and the fixed scroll form multiple closed spaces, and the positioning convex portion is deflected at an angle relative to the straight line connected by the multiple contact points, so that the bearing can When the movable scroll rotates, the force is evenly applied to prevent specific areas of the bearing from being severely worn due to excessive force, thereby improving the operating efficiency and service life of the compressor.

In order to make the above-mentioned features and advantages of the present invention more obvious and easy to understand, examples are given below and explained in detail with the accompanying drawings.

10, 20: Compressor

11, 21: Shell

11a: First compression chamber

11b: Second compression chamber

12, 22: Motor

13, 23: Drive shaft

13a: end

13b: Main axis

14:First compression mechanism

21a:Compression chamber

100: Second compression mechanism

100a: Compression mechanism

101:Contact point

102: Compressed space

103: straight line

110:Static Uzumaki

120: Moving scroll

130, 130a, 130b: bushing seat

131: Positioning convex part

131a: Positioning baseline

131b: First perforation

131c: Second perforation

1311, 1421: long side

1312, 1422: short side

132:First supporting surface

133:Second supporting surface

134: Supporting slope

140: Bushing

141: Center line

142:Through groove

150:Bearing

160: fixed block

170: Locking piece

A, B: parts

α, β: angle

I-I, J-J: line segments

Figure 1A is a schematic diagram of a compressor according to an embodiment of the present invention.

Figure 1B is a schematic side view of the compressor of Figure 1A.

FIG. 1C is a schematic cross-sectional view of the compressor of FIG. 1A along line section I-I.

Figure 1D is a partially enlarged schematic view of part A in Figure 1C.

FIG. 1E is a cross-sectional view of the compressor of FIG. 1A along line section J-J.

Figure 1F is a partially enlarged schematic view of part B in Figure 1E.

Figure 2A is a schematic diagram of the combination of the movable scroll and the bushing seat according to an embodiment of the present invention.

Figure 2B is an exploded diagram of Figure 2A.

Figure 2C is a schematic front view of the bearing, bushing and bushing seat of Figure 2B.

FIG. 2D and FIG. 2E are schematic views of the bushing seat in FIG. 2C from two different viewing angles.

3A and 3B are schematic views of the bushing seat from two different angles according to another embodiment of the present invention.

Figure 4A is a schematic front view of a bearing, bushing and bushing seat according to another embodiment of the present invention.

Figure 4B is a schematic view of the bushing seat of Figure 4A.

Figure 5 is a schematic cross-sectional view of a compressor according to another embodiment of the present invention.

Figure 1A is a schematic diagram of a compressor according to an embodiment of the present invention. Figure 1B is a schematic side view of the compressor of Figure 1A. FIG. 1C is a schematic cross-sectional view of the compressor of FIG. 1A along line section I-I. Figure 1D is a partially enlarged schematic view of part A in Figure 1C. Please refer to FIGS. 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 compressor. Compression mechanism 100. In detail, the housing 11 has a first compression chamber 11 a and a second compression chamber 11 b that communicate with each other. 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 respectively disposed in the first compression chamber 11a and the second compression chamber 11b, wherein the drive shaft 13 passes through the first compression chamber 11a and extends to the second compression chamber 11b.

Please refer to FIG. 1C and FIG. 1D. The first compression mechanism 14 can be a screw compression mechanism, and the second compression mechanism 100 can 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 passes through the first compression mechanism 14 and the second compression chamber 11b respectively in the first compression chamber 11a and the second compression chamber 11b. The compression mechanism 100 compresses the high-pressure gaseous fluid and then discharges it from the second compression chamber 11b.

FIG. 1E is a cross-sectional view of the compressor of FIG. 1A along line section J-J. Figure 1F is a partially enlarged schematic view of part B in Figure 1E. Please refer to FIGS. 1C to 1F . In this embodiment, the second compression mechanism 100 includes a fixed scroll 110 , an orbiting scroll 120 , a bushing seat 130 , a bushing 140 and a bearing 150 . The fixed scroll 110 is fixed in the second compression chamber 11b, and the movable scroll 120 is meshed with the fixed scroll 110. The orbiting scroll 120 can be driven by the driving shaft 13 to orbit relative to the stationary scroll 110. During the orbiting process of the orbiting scroll 120 relative to the stationary scroll 110, multiple scrolls are generated between the orbiting scroll 120 and the stationary scroll 110. contact points 101, and form multiple compression spaces 102 whose volumes gradually decrease from the periphery to the center, so that the gaseous fluid is continuously pressurized to transform into a high-pressure gaseous fluid, and then is transformed into a high-pressure gaseous fluid by a static vortex. The center of the roll 110 discharges the second compression chamber 11b.

Referring to FIGS. 1D to 1F , the bushing seat 130 is positioned at the end 13 a of the drive shaft 13 and has a positioning protrusion 131 protruding toward the stationary scroll 110 . The main axis 13b of the driving shaft 13 passes through the positioning protrusion 131, and the positioning protrusion 131 is deflected by an angle α relative to the straight line 103 connected by the plurality of contact points 101. On the other hand, the orbiting scroll 120 is connected to the positioning protrusion 131 of the bushing seat 130 through the bearing 150 and the bushing 140 . The orbiting 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.

Therefore, when the driving shaft 13 drives the bushing seat 130 to rotate, the movable scroll 120, the bearing 150 and the bushing 140 can revolve eccentrically 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 receive the force evenly when the movable scroll 120 revolves, preventing a specific area of the bearing 150 from being severely worn due to excessive force. Accordingly, The operating efficiency and service life of the compressor 10 are improved.

For example, the deflection angle α of the positioning protrusion 131 relative to the straight line 103 connected by the plurality of contact points 101 may be an acute angle. Preferably, the angle α may be between 5 degrees and 45 degrees. Preferably, the angle α It can be equal to 15 degrees.

Please refer to FIGS. 1D to 1F . In this embodiment, the bushing 140 has a through groove 142 , in which 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 . Through the cooperation of the positioning protrusion 131 and the through groove 142, the bushing 140 can reciprocate or slide radially relative to the bushing seat 130 within a set stroke, and cannot rotate relative to the bushing seat 130. According to the main extension direction of the through groove 142, the through groove 142 is deflected relative to the straight line 103 formed by the plurality of contact points 101. α. Furthermore, the positioning protrusion 131 has a positioning reference line 131 a passing through the main axis 13 b and parallel to the through groove 142 , and there is an angle α between the positioning reference line 131 a and the straight line 103 connecting the plurality of contact points 101 .

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 reference line 131a. Therefore, there is an angle α between the sliding path and the retreat path of the bushing 140 and the straight line 103 connecting the plurality of contact points 101 .

Please refer to FIG. 1F , the 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 reference line 131a, the two long sides 1311 can be deflected by the angle α of the straight line 103 connected in the clockwise and counterclockwise directions relative to the plurality of contact points 101. . In addition, the positioning reference line 131a extends through the two short sides 1312.

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

Please refer to FIGS. 1D to 1F . During the orbiting process of the orbiting scroll 120 relative to the stationary scroll 110 , the orbiting scroll 120 , the bearing 150 and the bushing 140 can be synchronously radially rotated relative to the bushing seat 130 and the stationary scroll 110 . Scroll 110 slides and bushing 140 slides radially The path and the retreat path are deflected by an angle α relative to the straight line 103 connected by the 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 the multiple contact points 101), Since the direction of the straight line 103 is different from the retreat direction (parallel to the positioning reference line 131a), even if abnormal high pressure is generated in the multiple compression spaces 102, 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 scroll 120 and help improve the operating efficiency of the compressor 10 .

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

As shown in FIG. 1D and FIG. 1F , the positioning protrusion 131 also has a first through hole 131 b, and the main axis 13 b of the driving shaft 13 passes through the first through hole 131 b. The locking piece 170 first passes through the fixed block 160 and then through the first through hole 131b, and then is locked into the end 13a of the drive shaft 13 to position the movable scroll 120, the bearing 150, the bushing 140 and the bushing seat 130 in the drive shaft. End 13a of shaft 13.

On the other hand, the positioning protrusion 131 also has a second through hole 131c, wherein the connection line between the first through hole 131b and the second through hole 131c coincides with the positioning reference line 131a, and is relative to the straight line connected by the plurality of contact points 101. 103 Yaw angle α. That is to say, the first through hole 131b is used to adjust the positioning protrusion 131 to produce a deflection angle α, and the connection line between the first through hole 131b and the second through hole 131c is fixed. The positioning protrusion 131 is deflected by an angle α such that the retreat direction of the movable scroll 120 , the bearing 150 and the bushing 140 (parallel to the positioning reference line 131 a ) avoids multiple gaps between the movable scroll 120 and the fixed scroll 110 The contact point 101 or the straight line 103 can yield through a small force (which can be called a yield force), thereby preventing a specific area of the bearing 150 from being severely worn due to excessive force.

Figure 2A is a schematic diagram of the combination of the movable scroll and the bushing seat according to an embodiment of the present invention. Figure 2B is an exploded diagram of Figure 2A. Figure 2C is a schematic front view of the bearing, bushing and bushing seat of Figure 2B. Please refer to FIGS. 2A to 2C . In this embodiment, the bushing 140 is supported on the bushing seat 130 , and the centerline 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 to 5 degrees.

As shown in FIGS. 1F, 2A and 2C, the bearing 150 and the bushing 140 are tilted relative to the main axis 13b, but the movable scroll 120 is not tilted relative to the main axis 13b. Therefore, the bearing 150 can revolve around the movable scroll 120. The force is evenly applied at all times to prevent a specific area of the bearing 150 from being severely worn due to excessive force, thereby improving the operating efficiency and service life of the compressor 10 . In addition, when the orbiting scroll 120 orbits relative to the stationary scroll 110, the retreat direction of the orbiting scroll 120 is parallel to the long side 1311 of the positioning protrusion 131 or the positioning reference line 131a, and avoids the orbiting scroll 120 and the stationary scroll 110. Multiple contact points 101 or straight lines 103 between scrolls 110 . Therefore, the centripetal force of the movable scroll 120 when orbiting is small, so that a small force (which can be called a concession force) is used to generate concessions in the radial direction, thereby preventing a specific area of the bearing 150 from being overly stressed and causing damage. Severe wear and tear.

FIG. 2D and FIG. 2E are schematic views of the bushing seat in FIG. 2C from two different viewing angles. Please refer to FIGS. 2C to 2E , the bushing seat 130 also has a first bearing surface 132 and a The second supporting surface 133 is connected to the first supporting surface 132 , and the positioning protrusion 131 protrudes from the first supporting surface 132 and the second supporting surface 133 . Specifically, 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 caused by the first bearing surface 132 and the second bearing surface 133 . The height difference between the surfaces 133 causes an inclination, so that the center line 141 of the bushing 140 is inclined 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 higher first bearing surface 132 is smaller than that of the lower one. The area of the second supporting surface 133.

As shown in FIG. 2D and FIG. 2E , the height difference between the first supporting surface 132 and the second supporting surface 133 is between 0.5 mm and 5 mm. In addition, the distribution range of the second supporting surface 133 extends along 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 1/1 of the length of the short side 1312. 2 to the entire side length.

3A and 3B are schematic views of the bushing seat from two different angles according to another embodiment of the present invention. Please refer to Figures 3A and 3B. Different from the bushing seat 130 shown in Figures 2D and 2E, the second supporting surface 133 of the bushing seat 130a of this embodiment is higher than the first supporting surface 132, and the height is relatively high. The area of the tall second supporting surface 133 is smaller than the area of the lower first supporting surface 132 . Specifically, the distribution range of the first supporting surface 132 extends along 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 the length of the short sides 1312. Between 1/2 and the entire side length, as shown in Figure 3B.

The height design of the two supporting surfaces of the bushing seat is based on the orbiting direction of the movable scroll. To determine, for example, the bushing seat 130 shown in FIG. 2D and FIG. 2E is suitable for the movable scroll that rotates clockwise, so that the movable scroll that starts to revolve first passes through the lower surface (ie, the second supporting surface). 133). In contrast, the bushing seat 130a shown in FIGS. 3A and 3B is suitable for the movable scroll that rotates counterclockwise, so that the movable scroll that starts to revolve first winds through the lower surface (ie, the first supporting surface 132), and then When the movable scroll 120 retreats, the second supporting surface 133 that the bottom of the bushing seat 130 rests on is a low surface instead of a high surface, so that the resistance to retreat is smaller, and the movable scroll 120 can pass through a smaller force (which can be called The setback force) can produce a setback to prevent a specific area of the bearing 150 from being severely worn due to excessive force.

Figure 4A is a schematic front view of a bearing, bushing and bushing seat according to another embodiment of the present invention. Figure 4B is a schematic view of the bushing seat of Figure 4A. Please refer to FIG. 4A and FIG. 4B. Different from the bushing seat 130 or the bushing seat 130a in the previous embodiment, the bearing surface of the bushing seat 130b in this embodiment is a bearing inclined surface 134. In detail, the bushing 140 contacts the supporting slope 134 so that the centerline 141 of the bushing 140 is inclined at an angle β relative to the main axis 13b, and the angle β may be between 0.5 degrees and 5 degrees.

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 high on the left and low on the right is suitable for a clockwise rotating scroll. Make the movable scroll that starts to revolve around the lower surface first. Correspondingly, a bushing seat with a supporting inclined surface that is higher on the right and lower on the left is suitable for the movable scroll that rotates counterclockwise, so that the movable scroll that starts to rotate first winds through the lower surface.

Figure 5 is a schematic cross-sectional view of a compressor according to another embodiment of the present invention. The compressor 10 of the previous embodiment is a two-stage compressor, and its two connected compression chambers are respectively provided with a screw compression mechanism and a scroll compression mechanism. In comparison, the compressor 10 shown in Figure 5 The compressor 20 is a single-stage compressor, and its casing 21 has a single compression chamber 21a, and a single compression mechanism 100a, such as a scroll compression mechanism, is configured in the compression chamber 21a.

As shown in FIG. 5 , the motor 22 and the drive shaft 23 are disposed in the housing 21 , where the drive shaft 23 is connected to the motor 22 and extends to the compression chamber 21 a to be connected to the compression mechanism 100 a. Specifically, 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, which is then discharged from the compression chamber 21a.

The compression mechanism 100a of this embodiment is the same scroll compression mechanism as the second compression mechanism 100 of the previous embodiment, and has the same structural design, such as the cooperation between the fixed scroll and the movable scroll and the structural design of the bushing seat. , the fit of the bushing seat and the drive shaft, the structural design of the bushing, the fit of the bushing and the bushing seat, the relative relationship between the centerline of the bushing and the main axis of the drive shaft (such as eccentricity and inclination), and the relationship between the bushing and the bushing , bearings and the coordination of the movable scroll are all the same, and will not be repeated here.

To sum up, in the compressor of the present invention, the bushing seat is positioned at the end of the drive shaft, and the movable scroll is connected to the positioning protrusion of the bushing seat through the bearing and the bushing, and the bushing can be The height difference between the first bearing surface and the second bearing surface (or bearing slope) causes the center line of the bushing to be eccentric to the main axis of the drive shaft. Specifically, multiple contact points between the movable scroll and the stationary scroll form multiple closed spaces, and the positioning convex portion is deflected at an angle relative to the straight line connected by the multiple contact points, so that the retreat direction is consistent with the straight line formed by the multiple contact points. The directions of the straight lines are different, and the supporting surface (or supporting slope) is a low surface when the movable scroll retreats. The retreat resistance of the movable scroll is small, so the retreat can be caused by a small force, so that the bearing can move in the The scrolls are evenly stressed when they rotate, preventing specific areas of the bearing from being stressed. If it is too large, it will cause serious wear and tear, thereby improving the operating efficiency and service life of the compressor.

On the other hand, during the orbiting process of the movable scroll relative to the fixed scroll, the movable scroll, bearings and bushings can slide synchronously relative to the fixed scroll in the radial direction. Due to the radial sliding path or retreat of the bushing, The path deviates at an angle relative to the straight line connected by multiple contact points (that is, the radial sliding path or retreat path of the bushing does not coincide with the straight line connected by multiple contact points), even if multiple compression spaces generate abnormally high pressure , the movable scroll, bearings and bushings can still slide in the radial direction or yield radially to maintain the smoothness of the movable scroll and help improve the operating efficiency of the compressor.

Although the embodiments of the present invention have been disclosed above, they are not intended to limit the invention. Anyone with ordinary knowledge in the technical field can make some modifications and changes without departing from the spirit and scope of the invention. Therefore, the scope of protection of this new creation shall be determined by the appended patent application scope.

10:Compressor

11: Shell

11a: First compression chamber

11b: Second compression chamber

12: Motor

13: Drive shaft

14:First compression mechanism

100: Second compression mechanism

A: Part

Claims (30)

A compressor including: A shell having a first compression chamber and a second compression chamber that are connected; A motor is provided 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; and A second compression mechanism is provided in the second compression chamber and includes: A still scroll; A moving scroll is engaged with the stationary scroll and has multiple contact points with the stationary scroll to form multiple compression spaces; A bushing seat is positioned at one end of the drive shaft and has a positioning protrusion, wherein a main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is relative to the contact points connected to each other. A straight line deflects by an angle; A bushing is sleeved on the positioning protrusion, and a center line of the bushing is eccentric to the main axis; and A bearing is sleeved on the bushing, and the orbiting scroll is sleeved on the bearing. The compressor of claim 1, wherein the bushing has a through groove, and the positioning protrusion is disposed in the through groove, and the through groove is deflected by the angle relative to the straight line connected by the contact points. . The compressor according to claim 2, wherein the positioning protrusion has a positioning reference line passing through the main axis and parallel to the through groove, and between the positioning reference line and the straight line connecting the contact points This angle is included. The compressor of claim 1, wherein the bushing is adapted to slide back and forth relative to the bushing seat along a sliding path, and the sliding path and the straight line connected by the contact points include the angle. . The compressor of claim 4, wherein the positioning convex portion has a positioning reference line passing through the main axis, and the positioning reference line coincides with the sliding path, and the positioning reference line is connected with the contact points. The angle is between the straight lines. The compressor of claim 1, wherein the angle is an acute angle. The compressor of claim 6, wherein the angle is between 5 degrees and 45 degrees. The compressor of claim 7, wherein the angle is equal to 15 degrees. The compressor of claim 1, wherein the positioning protrusion has a long side and a short side connected to the long side, and the long side is deflected at the angle relative to the straight line connected by the contact points. The compressor according to claim 1, wherein the second compression mechanism further includes: A fixed block is disposed in the bushing and contacts the positioning protrusion; and A locking piece passes through the fixing block and the positioning protrusion and locks into the end of the driving shaft. The compressor of claim 10, wherein the positioning protrusion has a first through hole, and the main axis of the drive shaft passes through the first through hole, and the locking piece passes through the first through hole and is locked into the drive shaft. of that end. The compressor of claim 11, wherein the positioning protrusion further has a second through hole, and a connecting line between the first through hole and the second through hole is relative to the straight line connecting the contact points. deflect this angle. The compressor of claim 1, wherein the bushing seat further 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. There is a height difference between the supporting surface and the second supporting surface, the first supporting surface and the second supporting surface, the bushing contacts the first supporting surface and the second supporting surface, and The centerline of the bushing is inclined relative to the main axis. The compressor of claim 13, wherein the center line of the bushing is inclined from 0.5 to 5 degrees relative to the main axis. The compressor of claim 13, wherein one of the first bearing surface and the second bearing surface is higher than the other of the first bearing surface and the second bearing surface, and the The area of the higher one of the first supporting surface and the second supporting surface is smaller than the area of the lower one of the first supporting surface and the second supporting surface. The compressor of claim 13, wherein the height difference between the first bearing surface and the second bearing surface is between 0.05 mm and 0.5 mm. The compressor of claim 13, wherein 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, and the first bearing The distribution range of the back surface extends from one long side to the two short sides, and extends to at least half of each short side. The compressor of claim 1, wherein the bushing seat also has a supporting slope, and the positioning protrusion protrudes from the supporting slope, the bushing contacts the supporting slope, and the bushing The centerline is tilted relative to this main axis. The compressor of claim 18, wherein the center line of the bushing is inclined from 0.5 to 5 degrees relative to the main axis. The compressor of claim 1, wherein the first compression mechanism is a screw compression mechanism. A compressor including: A shell with a compression chamber; A motor is provided in the housing; a drive shaft connected to the motor, wherein the drive shaft extends to the compression chamber; and A compression mechanism is provided in the compression chamber and includes: A still scroll; A moving scroll is engaged with the stationary scroll and has multiple contact points with the stationary scroll to form multiple compression spaces; A bushing seat is positioned at one end of the drive shaft and has a positioning protrusion, wherein a main axis of the drive shaft passes through the positioning protrusion, and the positioning protrusion is relative to the contact points connected to each other. A straight line deflects by an angle; A bushing is sleeved on the positioning protrusion, and a center line of the bushing is eccentric to the main axis; and A bearing is sleeved on the bushing, and the orbiting scroll is sleeved on the bearing. The compressor of claim 21, wherein the bushing has a through groove, and the positioning protrusion is disposed in the through groove, and the through groove is deflected by the angle relative to the straight line connected by the contact points. , the positioning protrusion has a positioning reference line passing through the main axis and parallel to the through groove, and the angle is sandwiched between the positioning reference line and the straight line connecting the contact points. The compressor of claim 21, wherein the bushing is adapted to slide back and forth relative to the bushing seat along a sliding path, and the sliding path and the straight line connected by the contact points include the angle. , the positioning convex portion has a positioning reference line passing through the main axis, and the positioning reference line coincides with the sliding path, and the angle is sandwiched between the positioning reference line and the straight line connected by the contact points. The compressor of claim 21, wherein the angle is between 5 degrees and 45 degrees. The compressor according to claim 21, wherein the bushing seat further 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. There is a height difference between the supporting surface and the second supporting surface, the first supporting surface and the second supporting surface, the bushing contacts the first supporting surface and the second supporting surface, and The centerline of the bushing is inclined relative to the main axis. The compressor of claim 25, wherein the center line of the bushing is inclined from 0.5 to 5 degrees relative to the main axis. The compressor of claim 25, wherein one of the first bearing surface and the second bearing surface is higher than the other of the first bearing surface and the second bearing surface, and the The area of the higher one of the first supporting surface and the second supporting surface is smaller than the area of the lower one of the first supporting surface and the second supporting surface. The compressor of claim 25, wherein the height difference between the first bearing surface and the second bearing surface is between 0.05 mm and 0.5 mm. The compressor according to claim 21, wherein the bushing seat also has a supporting slope, and the positioning protrusion protrudes from the supporting slope, the bushing contacts the supporting slope, and the bushing The centerline is tilted relative to this main axis. The compressor of claim 29, wherein the centerline of the bushing is inclined from 0.5 to 5 degrees relative to the main axis.

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