CROSS-REFERENCE TO RELATED APPLICATION
This application claims the priority benefit of Taiwan application serial no. 112130260, filed on Aug. 11, 2023. The entirety of the above-mentioned patent application is hereby incorporated by reference herein and made a part of this specification.
BACKGROUND
Technical Field
The disclosure relates to a compressor.
Description of Related Art
After the low-pressure gaseous fluid from the evaporator is sent to a 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 into high-pressure gaseous fluid, so that the efficiency of the refrigeration cycle may be improved. 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 orbiting scroll and a stationary scroll, and the motor drives the orbiting scroll to orbit relative to the stationary scroll through a driving shaft. As the orbiting scroll orbits, the orbiting scroll and the stationary scroll generate a plurality of contact points in the radial direction to form a plurality of compression spaces whose volumes gradually decrease from the outer periphery to the center, so that the gaseous fluid is continuously pressurized to transform into high-pressure gaseous fluid, which is discharged from the second compression chamber through the center of the stationary scroll.
Generally speaking, the end portion of the driving shaft is an eccentric shaft portion. The bushing is sleeved on the eccentric shaft portion, and the orbiting scroll is sleeved on the bushing through the bearing. Therefore, the inertial force generated by the orbiting scroll while orbiting will be transmitted to the eccentric shaft portion, which not only increases the load on the bearing, but also causes uneven stress on the bearing, thereby causing severe abrasion in specific areas of the bearing to affect the operating efficiency and the lifetime of the compressor.
On the other hand, the bushing is slidably sleeved on the eccentric shaft portion in the radial direction, and the orbiting scroll can slide synchronously with the bushing in the radial direction. Since the plurality of contact points between the orbiting 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 abnormally high pressure is generated in the plurality of compression spaces, the orbiting scroll and the bushing cannot easily slide in the radial direction. That is, the orbiting scroll and the bushing cannot easily retreat in the radial direction, resulting in the orbiting scroll being unable to smoothly orbit relative to the stationary scroll.
SUMMARY
The disclosure provides a compressor, which helps to improve the operating efficiency and the lifetime.
The disclosure proposes a compressor, which includes a housing, a motor, a driving shaft, a first compression mechanism, and a second compression mechanism. The housing has a first compression chamber and a second compression chamber that are communicated with each other. The motor is disposed in the housing. The driving shaft is connected to the motor. The driving shaft passes through the first compression chamber and extends into the second compression chamber. The first compression mechanism is disposed in the first compression chamber and connected to the driving shaft. The second compression mechanism is disposed in the second compression chamber and includes a stationary scroll, an orbiting scroll, a bushing seat, a bushing, and a bearing. The orbiting scroll is engaged with the stationary scroll, and there are a plurality of contact points between the orbiting scroll and the stationary scroll to form a plurality of compression spaces. The bushing seat is positioned at an end portion of the driving shaft and has a positioning protrusion. A main axis of the driving shaft passes through the positioning protrusion, and the positioning protrusion is deflected at an angle relative to a straight line connected by the plurality of contact points. 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 orbiting scroll is sleeved on the bearing.
The disclosure proposes another compressor, which includes a housing, a motor, a driving shaft, and a compression mechanism. The housing has a compression chamber. The motor is disposed in the housing. The driving shaft is connected to the motor. The driving shaft extends into the compression chamber. The compression mechanism is disposed in the compression chamber and includes a stationary scroll, an orbiting scroll, a bushing seat, a bushing, and a bearing. The orbiting scroll is engaged with the stationary scroll, and there are a plurality of contact points between the orbiting scroll and the stationary scroll to form a plurality of compression spaces. The bushing seat is positioned at an end portion of the driving shaft and has a positioning protrusion. A main axis of the driving shaft passes through the positioning protrusion, and the positioning protrusion is deflected at an angle relative to a straight line connected by the plurality of contact points. 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 orbiting scroll is sleeved on the bearing.
Based on the above, in the compressor of the disclosure, the bushing seat is positioned at the end portion of the driving shaft. The orbiting 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 driving shaft. Specifically, the plurality of contact points between the orbiting scroll and the stationary scroll form the plurality of closed spaces, and the positioning protrusion is deflected at an angle relative to the straight line connected by the plurality of contact points, so that the bearing can receive the force evenly when the orbiting scroll orbits, thereby preventing severe abrasion in specific areas of the bearing due to excessive force to improve the operating efficiency and the lifetime of the compressor.
In order to make the above-mentioned features and advantages of the disclosure clearer and easier to understand, the following embodiments are given and described in details with accompanying drawings as follows.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1A is a schematic view of a compressor according to an embodiment of the disclosure.
FIG. 1B is a schematic side view of the compressor of FIG. 1A.
FIG. 1C is a schematic cross-sectional view of the compressor of FIG. 1B along a line segment I-I.
FIG. 1D is a partially enlarged schematic view of part A in FIG. 1C.
FIG. 1E is a schematic cross-sectional view of the compressor of FIG. 1B along a line segment J-J.
FIG. 1F is a partially enlarged schematic view of part B in FIG. 1E.
FIG. 2A is a schematic view of a combination of an orbiting scroll and a bushing seat according to an embodiment of the disclosure.
FIG. 2B is a schematic exploded view of FIG. 2A.
FIG. 2C is a schematic front view of the bearing, bushing, and bushing seat of FIG. 2B.
FIG. 2D and FIG. 2E are schematic views of the bushing seat of FIG. 2C from two different viewing angles.
FIG. 3A and FIG. 3B are schematic views of a bushing seat from two different viewing angles according to another embodiment of the disclosure.
FIG. 4A is a schematic front view of a bearing, a bushing, and a bushing seat according to another embodiment of the disclosure.
FIG. 4B is a schematic view of the bushing seat of FIG. 4A.
FIG. 5 is a schematic cross-sectional view of a compressor according to another embodiment of the disclosure.
DESCRIPTION OF THE EMBODIMENTS
FIG. 1A is a schematic view of a compressor according to an embodiment of the disclosure. FIG. 1B is a schematic side view of the compressor of FIG. 1A. FIG. 1C is a schematic cross-sectional view of the compressor of FIG. 1B along a line segment I-I. FIG. 1D is a partially enlarged schematic view of part A in FIG. 1C. Referring to FIG. 1A to FIG. 1C, in the embodiment, a compressor 10 may be a two-stage compressor and includes a housing 11, a motor 12, a driving 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 communicated with each other. The motor 12 is disposed in the housing 11, and the driving 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. The driving shaft 13 passes through the first compression chamber 11a and extends into the second compression chamber 11b.
Referring 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 driving shaft 13, and the second compression mechanism 100 is connected to an end portion 13a of the driving 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 driving shaft 13, so that the low-pressure gaseous fluid is successively 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 to form a high-pressure gaseous fluid, which is then discharged from the second compression chamber 11b.
FIG. 1E is a schematic cross-sectional view of the compressor of FIG. 1B along a line segment J-J. FIG. 1F is a partially enlarged schematic view of part B in FIG. 1E. Referring to FIG. 1C to FIG. 1F, in the embodiment, the second compression mechanism 100 includes a stationary scroll 110, an orbiting 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 orbiting scroll 120 is engaged with the stationary 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, a plurality of contact points 101 are generated between the orbiting scroll 120 and the stationary scroll 110, and a plurality of compression spaces 102 are formed whose volumes gradually decrease from the outer periphery to the center, so that the gaseous fluid is continuously pressurized to transform into high-pressure gaseous fluid, which is then discharged out of the second compression chamber 11b from a center of the stationary scroll 110.
Referring to FIG. 1D to FIG. 1F, the bushing seat 130 is positioned at the end portion 13a of the driving shaft 13 and has a positioning protrusion 131 protruding toward the stationary scroll 110. A main axis 13b of the driving shaft 13 passes through the positioning protrusion 131, and the positioning protrusion 131 is deflected at an angle α relative to a 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 a 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 orbiting scroll 120, the bearing 150, and the bushing 140 can orbit 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 orbiting scroll 120 orbits, thereby preventing severe abrasion in the specific area of the bearing 150 due to excessive force to improve the operating efficiency and the lifetime of the compressor 10.
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 may be equal to 15 degrees.
Referring to FIG. 1D to FIG. 1F, in the embodiment, the bushing 140 has a through groove 142. The positioning protrusion 131 is disposed in the through groove 142, and a height of the positioning protrusion 131 is less than a 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. In terms of the main extending direction of the through groove 142, the through groove 142 is deflected at the angle α relative to the straight line 103 connected by the plurality of contact points 101. Furthermore, the positioning protrusion 131 has a positioning reference line 131a passing through the main axis 13b and parallel to the through groove 142, and the angle α is included between the positioning reference line 131a and the straight line 103 connected by 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 orbiting scroll 120, and the sliding path and retreat path of the bushing 140 coincide with the positioning reference line 131a. Therefore, the angle α is included between the sliding path and the retreat path of the bushing 140 and the straight line 103 connected by the plurality of contact points 101.
Referring to FIG. 1F, the positioning protrusion 131 also has two long sides 1311 that are opposite to each other and two short sides 1312 that are opposite to each other, 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 at the angle α relative to the straight line 103 connected by the plurality of contact points 101 in the clockwise and counterclockwise directions respectively. 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. 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 at the angle α relative to the straight line 103 connected by the plurality of contact points 101 in the clockwise and counterclockwise directions respectively.
Referring to FIG. 1D to FIG. 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 slide synchronously relative to the bushing seat 130 and the stationary scroll 110 in the radial direction, and the radial sliding path and the retreat path of the bushing 140 are deflected at the angle α relative to the straight line 103 connected by the plurality of 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 plurality of 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 abnormally high pressure is generated in the plurality of compression spaces 102, the orbiting scroll 120, the bearing 150, and the bushing 140 can still slide in the radial direction or retreat radially to maintain the smoothness of the orbiting of the orbiting scroll 120 and help improve the operating efficiency of the compressor 10.
Referring to FIG. 1C and FIG. 1D, in the 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 to be locked into the end portion 13a of the driving shaft 13 so as to position the bushing seat 130 at the end portion 13a of the driving 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 131b, and the main axis 13b of the driving shaft 13 passes through the first through hole 131b. The locking member 170 first passes through the fixing block 160 and then through the first through hole 131b to be then locked into the end portion 13a of the driving shaft 13 so as to position the orbiting scroll 120, the bearing 150, the bushing 140, and the bushing seat 130 in the end portion 13a of the driving shaft 13.
On the other hand, the positioning protrusion 131 also has a second through hole 131c. A connection line between the first through hole 131b and the second through hole 131c coincides with the positioning reference line 131a, and is deflected at the angle α relative to the straight line 103 connected by the plurality of contact points 101. That is to say, the first through hole 131b is used to adjust the positioning protrusion 131 to produce the deflection angle α, and the connection line 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 reference line 131a) of the orbiting scroll 120, the bearing 150, and the bushing 140 avoids the plurality of contact points 101 or the straight line 103 between the orbiting scroll 120 and the stationary scroll 110. Therefore, a small acting force (which can be called a retreating force) can be used to cause the retreat to prevent severe abrasion in specific areas of the bearing 150 due to excessive force.
FIG. 2A is a schematic view of a combination of an orbiting scroll and a bushing seat according to an embodiment of the disclosure. FIG. 2B is a schematic exploded view of FIG. 2A. FIG. 2C is a schematic front view of the bearing, bushing, and bushing seat of FIG. 2B. Referring to FIG. 2A to FIG. 2C, In the 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 13b, and the angle β may be between 0.5 and 5 degrees.
As shown in FIG. 1F, FIG. 2A, and FIG. 2C, the bearing 150 is inclined along with the bushing 140 relative to the main axis 13b. However, the orbiting scroll 120 is not inclined relative to the main axis 13b. Therefore, the bearing 150 can receive the force evenly when the orbiting scroll 120 orbits, thereby preventing severe abrasion in specific areas of the bearing 150 due to excessive force to improve the operating efficiency and the lifetime 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 plurality of contact points 101 or the straight line 103 between the orbiting scroll 120 and the stationary scroll 110. Therefore, the centripetal force of the orbiting scroll 120 during orbiting is small, so that a small acting force (which can be called a retreating force) is used to cause the retreat in the radial direction, thereby preventing severe abrasion in specific areas of the bearing 150 due to excessive force.
FIG. 2D and FIG. 2E are schematic views of the bushing seat of FIG. 2C from two different viewing angles. Referring to FIG. 2C to FIG. 2E, the bushing seat 130 also has a first supporting surface 132 and a second supporting surface 133 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. In detail, the first supporting surface 132 is higher than the second supporting surface 133. The bushing 140 that is in contact with the first supporting surface 132 and the second supporting surface 133 may be inclined due to a height difference between the first supporting surface 132 and the second supporting surface 133 such 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 that is in contact with the first supporting surface 132 and the second supporting surface 133 is inclined on the bushing seat 130, an area of the first supporting surface 132 with the higher height is less than an area of the second supporting surface 133 with the lower height.
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, a 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 is between ½ of a side length of the short side 1312 and an entire side length.
FIG. 3A and FIG. 3B are schematic views of a bushing seat from two different viewing angles according to another embodiment of the disclosure. Referring to FIG. 3A and FIG. 3B, different from the bushing seat 130 shown in FIG. 2D and FIG. 2E, the second supporting surface 133 of a bushing seat 130a in the embodiment is higher than the first supporting surface 132, and the area of the second supporting surface 133 with the higher height is less than the area of the first supporting surface 132 with the lower height. Specifically, a 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 is between ½ of the side length of the short side 1312 and the entire side length, as shown in FIG. 3B.
A height design of the two supporting surfaces of the bushing seat is determined by the orbiting direction of the orbiting scroll. For example, the bushing seat 130 shown in FIG. 2D and FIG. 2E is suitable for the orbiting scroll that orbits clockwise such that the orbiting scroll that starts to orbit first passes through the lower surface (i.e., the second supporting surface 133). In contrast, the bushing seat 130a shown in FIG. 3A and FIG. 3B is suitable for the orbiting scroll that orbits counterclockwise such that the orbiting scroll that starts to orbit first passes through the lower surface (i.e., the first supporting surface 132). When the orbiting scroll 120 retreats, the second supporting surface 133 on which the bottom of the bushing seat 130 rests is a low surface instead of a high surface, so that the retreat resistance is smaller. The orbiting scroll 120 can retreat through a small acting force (which can be called a retreating force), thereby preventing severe abrasion in specific areas of the bearing 150 due to excessive force.
FIG. 4A is a schematic front view of a bearing, a bushing, and a bushing seat according to another embodiment of the disclosure. FIG. 4B is a schematic view of the bushing seat of FIG. 4A. Referring to FIG. 4A and FIG. 4B, different from the bushing seat 130 or the bushing seat 130a in the previous embodiments, a supporting surface of a bushing seat 130b in the embodiment is a supporting slope 134. In detail, the bushing 140 is in contact with the supporting slope 134 such that the center line 141 of the bushing 140 is inclined at the angle β relative to the main axis 13b, and the angle β may be between 0.5 degrees and 5 degrees.
A height design of the supporting slope of the bushing seat is determined by the orbiting direction of the orbiting scroll. For example, the bushing seat with the supporting slope that is high on the left and low on the right is suitable for the orbiting scroll that orbits clockwise such that the orbiting scroll that starts to orbit first passes through the lower surface. Correspondingly, the bushing seat with the supporting slope that is high on the right and low on the left is suitable for the orbiting scroll that orbits counterclockwise such that the orbiting scroll that starts to orbit first passes through the lower surface.
FIG. 5 is a schematic cross-sectional view of a compressor according to another embodiment of the disclosure. The compressor 10 of the previous embodiment is a two-stage compressor, and its two compression chambers that are communicated with each other are respectively disposed with the screw compression mechanism and the scroll compression mechanism. In comparison, a compressor 20 shown in FIG. 5 is a single-stage compressor, and its housing 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, a motor 22 and a driving shaft 23 are disposed in the housing 21. The driving shaft 23 is connected to the motor 22 and extends into the compression chamber 21a to be connected to the compression mechanism 100a. Specifically, the motor 22 can drive the compression mechanism 100a to operate through the driving 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 the embodiment is a scroll compression mechanism and has the same structural design as the second compression mechanism 100 of the previous embodiment. For example, the cooperation between the stationary scroll and the orbiting scroll, the structural design of the bushing seat, the cooperation between the bushing seat and the driving shaft, the structural design of the bushing, the cooperation between the bushing and the bushing seat, the relative relationship between the center line of the bushing and the main axis of the driving shaft (such as eccentricity and inclination), and the cooperation of the bushing, the bearing, and the orbiting scroll are all the same, and therefore will not be repeated here.
In summary, in the compressor of the disclosure, the bushing seat is positioned at the end portion of the driving shaft. The orbiting 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 driving shaft due to the height difference between the first supporting surface and the second supporting surface (or supporting slope). Specifically, the plurality of contact points between the orbiting scroll and the stationary scroll form a plurality of closed spaces, and the positioning protrusion is deflected at an angle relative to the straight line connected by the plurality of contact points such that the retreat direction is different from the direction of the straight line. In addition, the supporting surface (or supporting slope) is a low surface when the orbiting scroll retracts, and the retreat resistance of the orbiting scroll is small. Therefore, a small acting force can be used to cause the retreat, so that the bearing can receive the force evenly when the orbiting scroll orbits, thereby preventing severe abrasion in specific areas of the bearing due to excessive force to improve the operating efficiency and the lifetime of the compressor.
On the other hand, during the orbiting process of the orbiting scroll relative to the stationary scroll, the orbiting scroll, the bearing, and the bushing can slide relative to the stationary scroll synchronously in the radial direction. Since the radial sliding path or retreat path of the bushing is deflected at an angle relative to the straight line connected by the plurality of contact points (that is, the radial sliding path or retreat path of the bushing does not coincide with the straight line connected by the plurality of contact points), even if abnormally high pressure is generated in the plurality of compression spaces, the orbiting scroll, the bearing, and the bushing can still slide in the radial direction or retreat radially to maintain the smoothness of the orbiting of the orbiting scroll and help improve the operating efficiency of the compressor.
Although the disclosure has been described with reference to the embodiments above, the embodiments are not intended to limit the disclosure. Any person skilled in the art can make some changes and modifications without departing from the spirit and scope of the disclosure. Therefore, the scope of the disclosure will be defined in the appended claims.
Patent Application
20250052239
