JP4979473B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used in a refrigeration air conditioner, an air compressor, and the like.

  As a conventional scroll compressor, there is one disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2004-270599). A scroll compression mechanism and an electric motor are housed in the sealed container. The scroll compression mechanism unit includes a fixed scroll having a spiral wrap on a disk-shaped end plate, and a turning scroll having a spiral wrap formed on the disk-shaped end plate. The compression chamber is formed in a state where the fixed scroll wrap and the orbiting scroll wrap mesh with each other.

  The orbiting scroll includes an orbiting boss portion provided with an orbiting bearing portion that engages with an eccentric shaft portion of a main shaft that transmits rotational force on a surface (back surface) opposite to the end plate surface on which a wrap is provided. The fixed scroll is bolted to a frame having a main bearing, and the orbiting scroll orbits within them.

  The scroll compressor described in Patent Document 1 includes a sealing unit that seals the back pressure chamber formed in the rear plate portion of the orbiting scroll and the discharge space in the peripheral portion on the main bearing side. A concave groove is formed in the end face of the center of the frame facing the end face of the orbiting boss, and a seal ring and a leaf spring for bringing the seal ring into close contact with the end face of the orbiting scroll in the groove. And a sealing means in combination.

  The seal ring is provided with an abutment to absorb the effects of thermal expansion and tolerance of the seal ring itself, and the seal ring is deformed by frictional force when the end face of the swivel boss slides during compressor operation. there is a possibility. Further, the seal ring may be deformed due to a pressure difference between the back pressure chamber and the discharge space in the peripheral portion on the main bearing side. For this reason, the seal ring is prevented from being deformed by being incorporated in a groove having a margin for the width of the seal ring.

JP 2004-270599 A

  In the scroll compressor described in Patent Document 1, it is important to process the groove into which the seal ring is incorporated in order to ensure that the sealing performance functions. A relatively large compressor is unlikely to be dimensionally restricted. However, there are the following problems when trying to realize with a small and inexpensive compressor.

  In order to ensure the sealing performance in the sealing means and the reliability against wear due to sliding, it is necessary to increase the processing accuracy of the groove, particularly the surface roughness. However, when the above structure is adopted in a small compressor, the actual groove width is narrow and precision machining is difficult. In addition, there is a problem that workability is low, such as requiring processing time and frequent blade tool replacement. In addition, the orbiting boss part of the orbiting scroll and the Oldham ring and main shaft for preventing rotation must be arranged in a limited space in the frame. Since the thickness of the wall between the bearings must be secured, there is a problem that the degree of freedom in design is low.

  An object of the present invention is to provide a scroll compressor that solves the above-mentioned problems, is easy to machine, and can improve the sealing performance with a simple configuration.

In order to achieve the above object, the present invention is characterized by:
In a sealed container, a fixed scroll and the orbiting scroll spiral wrap is provided on the end plate, in the scroll compressor having a frame having a main bearing for supporting the spindle for pivoting said orbiting scroll,
A sealing part that seals the back pressure chamber on the back surface of the end plate of the orbiting scroll and the space around the main bearing, has a rectangular cross section perpendicular to the rotation direction of the main shaft, and contacts along the rotation direction of the main shaft Sealing means having a portion ;
A sealing means mounting portion provided on an upper surface of the frame so as to face an end surface of the orbiting boss portion of the orbiting scroll into which the main shaft is inserted;
And a seal support means for positioning said sealing means to said sealing means mounting portion,
The seal support means is located on the inner peripheral side with respect to the inner peripheral end of the seal means , and has a support portion having an upright portion that supports the inner peripheral side of the seal means; An elastic part for contacting the back part,
The seal means has an outer peripheral side supported by the frame by the seal means mounting portion and an inner peripheral side supported by the upright portion on the seal support means.

  According to the present invention, the sealing performance can be improved with a simple configuration, and the machining can be easily performed, so that it is possible to cope with downsizing.

  Examples of the present invention will be described below. FIG. 1 is a sectional view of a scroll compressor according to an embodiment of the present invention, and FIG. 2 is an enlarged view of a main part in FIG. In the sealed container 1, a scroll compression mechanism 2 and an electric motor 3 that drives the scroll compression mechanism 2 are housed. The scroll compression mechanism unit 2 includes a fixed scroll 10 and a turning scroll 20. The fixed scroll 10 includes a spiral wrap 11 raised from the bottom 12 as shown in FIGS. 1 and 6, and a flange 13 around the bottom 12 that is a flat surface having the same height as the tip of the wrap 11. Have As shown in FIGS. 1 and 7, the orbiting scroll 20 includes a disc-shaped end plate 21, a spiral-shaped wrap 22 that is raised from the end plate 21 and meshed with the wrap 11 of the fixed scroll 10, and the main shaft 4. And a boss portion 23 provided with an orbiting scroll bearing that engages with an eccentric shaft portion 5 that is provided continuously with the shaft. The tip end portion of the main shaft 4 is inserted into the boss portion 23.

  The frame 30 has a flat surface portion 31 provided around a space in which the orbiting scroll 20 orbits and a main bearing 32 through which the main shaft 4 passes. The frame 30 and the fixed scroll 10 are in contact with the flat portion 31 of the frame 30 and the flange portion 13 of the fixed scroll 10, and both are fastened by a plurality of bolts 24. The scroll compression mechanism unit 2 has an Oldham ring 6 between the frame 30 and the orbiting scroll 20 so that the orbiting scroll 20 does not rotate and orbits with respect to the fixed scroll 10.

  The electric motor 3 includes a stator 90 and a rotor 100 that is rotatably arranged on the inner peripheral side of the stator 90. The main shaft 4 is fixed to the rotor 100, and the driving force of the electric motor 3 is transmitted to the orbiting scroll 20 through the main shaft 4 by rotating the rotor 100.

  An oil sump 120 that is partitioned by a bearing support plate 110 is provided at the bottom of the sealed container 1. The oil reservoir 120 stores lubricating oil that lubricates the rotating portion. A bearing housing 111 is attached to the bearing support plate 110, and a spherical bearing 112 is disposed inside the bearing housing 111. The main shaft 4 is inserted into the cylindrical hole of the spherical bearing 112, and the main shaft 4 is rotatably supported. The oil sump portion 120 is provided with an oil supply pump 50 for supplying lubricating oil to the boss portion 23, the main bearing 32, and the like. The oil supply pump 50 is connected to the main shaft 4, and functions as a pump when the main shaft 4 is rotated by the electric motor 3.

  The main shaft 4 is formed with an oil supply passage 4a penetrating the main shaft 4 in the substantially axial direction and a lateral oil supply hole 4b communicating with the oil supply passage 4a. The lateral oil supply hole 4b opens to the outer peripheral surface of the main shaft 4, and communicates the opening with the oil supply path 4a. When driven by the electric motor 3 and the main shaft 4 rotates, the oil supply pump 50 operates to suck up the lubricating oil in the oil reservoir 120. Lubricating oil passes through the oil supply passage 4 a and is discharged from the lateral oil supply holes 4 b to lubricate the main shaft 4 and the main bearing 32. Further, the lubricating oil ascends the oil supply passage 4a and is discharged from the upper end of the main shaft 4 to lubricate the boss portion 23 provided with the orbiting scroll bearing.

  An oil drain pipe 60 bent in an L shape is attached to the frame 30. One end side of the oil draining pipe 60 attached to the frame 30 introduces lubricating oil that has lubricated the boss portion 23, the main bearing 32, etc., and the oil draining pipe 60 guides the introduced lubricating oil downward. The other end of the oil draining pipe 60 opens toward the stator 90, and guides the lubricating oil that has lubricated the boss portion 23, the main bearing 32, and the like to the upper portion of the stator 90. Since the stator 90 has a coil, it is preferable that at least the surface of the oil drainage pipe 60 and the end portion on the stator 90 side are made of an insulating material. In addition, since the refrigerant also adheres to the oil drain pipe 60, it is preferable to use a material that can withstand the refrigerant.

  The fixed scroll 10 has a discharge port 14 that opens at the center of the spiral wrap 11, a suction port 15 that connects to the outside of the sealed container 1 and opens at the outer periphery of the wrap 11, and a compression space 7. And a relief hole 114 that communicates with the discharge-side pressure space 113 in the sealed container 1. A plurality of relief holes 114 are formed as shown in FIG. The fixed scroll 10 is provided with a relief valve 115 that opens and closes the relief hole 114. The relief valve 115 opens when the pressure in the compression space 7 becomes higher than the pressure in the discharge-side pressure space 113, prevents over compression of the refrigerant gas, and pulls the fixed scroll 10 and the orbiting scroll 20 away from each other. Reduce the release force.

  The scroll compression mechanism 2 sucks the refrigerant gas from the suction port 15 and confines the refrigerant gas in the compression space 7 formed by the wraps 11, 22, the bottom 12, and the flange 13 of both scrolls. The on-off valve 15 a is a valve that opens and closes the suction port 15. As the orbiting scroll 20 orbits, the compression space 7 gradually decreases in volume while moving to the center. As the volume of the compression space 7 decreases, the refrigerant gas confined in the compression space 7 is compressed, and finally, the compressed refrigerant gas is discharged from the discharge port 14 to the discharge side pressure space 113 in the sealed container 1.

  A back pressure chamber 33 is formed by the frame 30 and the orbiting scroll 20 on the back surface side opposite to the lap 22 side with respect to the disc-shaped end plate 21 of the orbiting scroll 20. When the refrigerant gas is compressed by the scroll compression mechanism 2, a pulling force that causes the fixed scroll 10 and the orbiting scroll 20 to separate is generated. The back pressure chamber 33 is provided to reduce the pulling force.

  An intermediate pressure between the discharge pressure discharged from the discharge port 14 and the suction pressure sucked from the suction port 15 is introduced into the back pressure chamber 33 to generate a pressing force that presses the orbiting scroll 20 toward the fixed scroll 10, It is reduced against the pulling force by the compressed gas in the compression space 7. In addition, the fixed scroll 10 is provided with a back pressure control valve 140 that is controlled to open when the difference between the pressure in the back pressure chamber 33 and the suction pressure exceeds a predetermined value so as to communicate with the back pressure chamber 33. When the back pressure control valve 140 is controlled to open, the pressure in the back pressure chamber 33 is introduced into the suction pressure region.

  Next, the pressure introduced into the back pressure chamber 33 will be described. The refrigerant gas discharged from the discharge port 14 to the discharge-side pressure space 113 contains high-pressure lubricating oil. The refrigerant gas discharged into the discharge side pressure space 113 passes through grooves (not shown) formed in the outer periphery of the fixed scroll 10 and the frame 30 and enters the electric motor 3 side. The refrigerant gas that has entered the electric motor 3 passes through a groove (not shown) formed in the stator 90, a coil of the stator 90, a gap between the stator 90 and the rotor 100, and the like. In the process, the refrigerant gas collides with each part of the electric motor 3 and separates the lubricating oil contained therein. The separated lubricating oil falls down while taking heat of each part, and enters the oil reservoir 120 through the vent hole 110a formed in the bearing support plate 110. In addition, the refrigerant gas that has entered the electric motor 3 exits from the discharge pipe 130 to the outside.

  In addition, the refrigerant gas flows into the oil reservoir 120 through the vent hole 110a, but the lubricating oil in the space in which the electric motor 3 is stored also flows into the oil reservoir 120 through the vent hole 110a.

  As described above, the lubricating oil in which the refrigerant gas is dissolved passes through the oil supply passage 4a in the main shaft 4 by the pumping action of the oil supply pump 50, exits the lateral oil supply hole 4b, and lubricates the main shaft 4 and the main bearing 32. Further, the lubricating oil ascends the oil supply passage 4a and is discharged from the upper end of the main shaft 4 to lubricate the boss portion 23 provided with the orbiting scroll bearing. The lubricating oil that has lubricated the orbiting scroll bearing in the boss portion 23 flows from between the outer periphery of the main shaft 4 and the orbiting scroll bearing on the inner periphery of the boss portion 23 to the upper surface 30a of the frame 30, and the lower end portion of the boss portion 23 and the frame 30. The upper surface 30a is lubricated. Further, the lubricating oil moves to the outer peripheral side of the upper surface 30 a and flows into the back pressure chamber 33. Since the space between the outer periphery of the main shaft 4 and the inner periphery of the boss portion 23 is narrow, the pressure of the lubricating oil flowing into the back pressure chamber 33 is reduced due to pressure loss. The pressure of the refrigerant gas separated from the lubricating oil flowing into the back pressure chamber 33 is lower than the discharge pressure.

  Next, a structure for sealing the space around the upper periphery of the main bearing 32 provided in the frame 30 and the back pressure chamber 33 will be described with reference to FIGS.

  3 is an external perspective view of the seal ring 70 and the seal support means 80, FIG. 4 is a plan view of the seal support means 80, and FIG. 5 is a perspective view showing a state in which the seal support means 80 is inserted into the groove 34. It is.

  A seal means mounting portion that is a groove-like space recessed from the surface of the frame 30 is formed in the upper peripheral portion of the main bearing 32 provided in the frame 30. In this embodiment, the groove 34 provided by boring the frame 30 is a sealing means attachment portion. The groove 34 is provided with a seal ring 70 that seals the space around the upper portion of the main bearing 32 provided in the frame 30 and the back pressure chamber 33. As shown in FIG. 3, the seal ring 70 is a joint portion 70 a in which the joint portion is formed in a stepped shape, and is in close contact with the end portion of the boss portion 23 along the rotational axis direction of the main shaft 4. The outer peripheral portion of the seal ring 70 is in close contact with the outer peripheral wall of the groove 34 so that no gap is generated in the radial direction of the rotation shaft.

  The seal ring 70 (seal means) is supported by a seal support means 80. As shown in FIG. 2, the seal support means 80 includes a support portion 80a having an L-shaped cross section, and an elastic portion 80b bent downward from the support portion 80a (the side inserted into the groove 34). Have. As shown in FIGS. 3 and 4, the support portion 80 a has a flat portion 81 and an upright portion 82 rising from the flat portion 81, and the cross-sectional shape is L-shaped. The elastic portion 80b is cut out from the flat portion 81 and is bent downward (on the side inserted into the groove 34) by the rising portion 82.

  The lower side of the seal ring 70 is placed on the flat portion 81 of the support portion 80a, and the inner peripheral side is supported by the upright portion 82 of the support portion 80a. The upper side of the seal ring 70 is in contact with the boss part 23 (end part) of the orbiting scroll 20 to seal the space around the upper part of the main bearing 32 and the back pressure chamber 33. For this reason, the upright portion 82 of the support portion 80 a has a dimensional structure lower than the height dimension of the seal ring 70. That is, as shown in FIG. 2, “the height of the support portion 80a (the height of the upright portion) h <the height H of the seal ring 70”. Further, in the radial direction, the flat portion 81 of the support portion 80 a has a dimensional structure that is narrower than the width of the seal ring 70. That is, “the width of the support portion 80a (the width of the flat portion 81) w <the seal ring 70 width W”. Further, when the seal support means 80 is inserted into the groove 34, the upper end portion of the support portion 80 a does not protrude from the upper surface 30 a of the frame 30 as shown in FIGS. 2 and 5. By doing so, the seal support means 80 is not in direct contact with the frame 30 or the orbiting scroll 20, and therefore, wear can be prevented.

  As described above, the elastic portion 80b for bringing the seal ring 70 into close contact with the boss portion 23 on the back side of the swivel end plate is cut out from the flat portion 80c and bent downward (side inserted into the groove 34). ing. Since the elastic portion 80 b is inserted into the groove 34, the shape of the elastic portion 80 b matches the shape of the groove 34. That is, the length of the elastic portion 80b in the radial direction is formed in consideration of the length of the groove 34 in the radial direction, and the bending angle is determined by the depth of the groove 34 and the seal ring 70 and the boss portion 23. Consider the contact state. In this embodiment, the seal support means 80 is formed according to the shape of the groove 34, so that the positional deviation of the seal ring 70 is less likely to occur.

  Since the seal ring 70 is supported by the seal support means 80, the seal ring 70 is lifted from the bottom of the groove 34. Conventionally, since the seal ring has been directly inserted into the groove, the processing accuracy of the groove has been required in order to ensure sealing performance. In particular, in a small compressor, since the groove is small, it is difficult to increase the processing accuracy of the groove. In this embodiment, since it is not necessary to increase the groove processing accuracy, it is possible to cope with downsizing of the compressor by making machining easy. Since the seal support means 80 can be manufactured by sheet metal processing, parts can be manufactured at an overwhelmingly low cost compared to machining the groove 34.

  Furthermore, although the elastic part 80b is provided with planar legs, it may be provided with an arc part 84 having an arcuate end as shown in FIG. 4 in order to suppress wear. In the present embodiment, the number of elastic portions 80b is five, but the number of elastic portions 80b is not limited to five and may be set as appropriate. The elastic force can be adjusted by the number of elastic portions 80b.

  Further, in the present embodiment, the support portion 80a is provided over the entire circumference, but it may not be provided for the entire circumference. As long as the seal ring 70 can be supported, the structure may be divided into a plurality of parts in the circumferential direction. Further, the joint portion of the seal ring 70 may be shaped so as not to be deformed so as to have an angle with respect to the radial direction or the axial direction so as to prevent deformation of the seal ring.

  As described above, according to the present embodiment, machining can be easily performed, and the sealing performance can be improved with a simple configuration.

It is sectional drawing of the scroll compressor which is one Example of this invention. It is a principal part enlarged view in FIG. 2 is an external perspective view of a seal ring 70 and seal support means 80. FIG. 4 is a plan view of a seal support means 80. FIG. FIG. 5 is a perspective view showing a state in which a seal support means 80 is inserted into a groove 34. 3 is a plan view of the fixed scroll 10. FIG. 3 is a plan view of the orbiting scroll 20. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Scroll compression mechanism part 3 Electric motor 4 Main axis | shaft 5 Eccentric shaft part 6 Oldham ring 7 Compression space 10 Fixed scroll 11, 22 Wrap 12 Bottom part 13 Ridge part 14 Outlet 15 Inlet 20 Revolving scroll 21 Disc-shaped end plate 23 Boss Part 30 Frame 31 Flat part 32 Main bearing 33 Back pressure chamber 34 Groove 50 Oil supply pump 60 Oil drain pipe 70 Seal ring 80 Seal support means 80a Support part 80b Elastic part 90 Stator 100 Rotor

Claims (3)

In a sealed container, a fixed scroll and the orbiting scroll spiral wrap is provided on the end plate, in the scroll compressor having a frame having a main bearing for supporting the spindle for pivoting said orbiting scroll,
A sealing part that seals the back pressure chamber on the back surface of the end plate of the orbiting scroll and the space around the main bearing, has a rectangular cross section perpendicular to the rotation direction of the main shaft, and contacts along the rotation direction of the main shaft Sealing means having a portion ;
A sealing means mounting portion to which the main shaft is provided on an upper surface of the frame so as to face the end surface of the pivot boss portion of the orbiting scroll to be inserted, a seal support means for positioning said sealing means to said sealing means mounting portion With
The seal support means is located on the inner peripheral side with respect to the inner peripheral end of the seal means , and has a support portion having an upright portion that supports the inner peripheral side of the seal means; An elastic part for contacting the back part,
The scroll means is a scroll compressor whose outer peripheral side is supported on the frame by the sealing means mounting portion and whose inner peripheral side is supported on the seal supporting means by the upright portion. The scroll compressor according to claim 1, wherein
A scroll compressor in which the height of the support portion is lower than the height of the sealing means. The scroll compressor according to claim 1, wherein
A scroll compressor in which the width of the support portion is narrower than the width of the sealing means.

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