JP6488893B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor, and more particularly to a lubrication structure between two surfaces of a back surface of a turning scroll and a thrust plate disposed at a position facing the back surface of the turning scroll.

  In the scroll compressor, a compression chamber for compressing a refrigerant is formed between the fixed scroll and the orbiting scroll by meshing the plate-like spiral teeth provided on the base plates of the fixed scroll and the orbiting scroll. Yes. The refrigerant suction chamber is present at the outermost peripheral portion of the compression chamber, and the refrigerant discharge port is present at the innermost peripheral portion (central portion) of the compression chamber. The revolving motion of the orbiting scroll (orbiting motion and eccentric rotation operation) gradually reduces the volume of the compression chamber while moving the compression chamber from the outer peripheral portion toward the center portion, and from the refrigerant suction port to the suction chamber. The refrigerant sucked into the compressor is compressed at a predetermined ratio, and the compressed refrigerant is discharged from the discharge port to the discharge chamber in the compressor hermetic container.

  FIG. 7 is a cross-sectional side view illustrating a schematic configuration of the scroll compressor 50. The configuration and operation of the scroll compressor 50 will be described with reference to FIG.

  The scroll compressor 50 exemplified here sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high temperature and high pressure state. The scroll compressor 50 includes a compression mechanism unit that combines a fixed scroll 1 and an orbiting scroll 52 that revolves with respect to the fixed scroll 1 in a sealed container 6 (consisting of sealed containers 6a and 6b). Yes. The scroll compressor 50 also includes a drive unit 14 (for example, a rotary drive unit such as an electric motor or a clutch) that drives the main shaft 15 that pivotally supports the orbiting scroll 52.

  The fixed scroll 1 is composed of a base plate 1b and a plate-like spiral tooth 1a which is a spiral projection standing on one surface of the base plate 1b, and is fixed to the sealed container 6 (sealed container 6a) with a bolt or the like. Has been. The orbiting scroll 52 includes a base plate 52b and plate-like spiral teeth 52a that are erected on one surface of the base plate 52b and are substantially the same shape as the plate-like spiral teeth 1a. ing. By compressing the plate-like spiral teeth 1a of the fixed scroll 1 and the plate-like spiral teeth 52a of the orbiting scroll 52, a compression chamber 3 whose volume changes relatively is formed.

  And the sealed container 6 (sealed container 6b) which becomes the outer peripheral part of the compression chamber 3 formed by meshing the plate-like spiral teeth 1a of the fixed scroll 1 and the plate-like spiral teeth 52a of the orbiting scroll 52 with each other. A refrigerant inlet 11 for introducing the refrigerant into the compression chamber 3 and a lubricating oil inlet 13 for introducing the lubricating oil into the compressor are provided. A discharge port 4 is formed at the center of the base plate 1b of the fixed scroll 1 to discharge the compressed and high-pressure refrigerant. Then, the compressed high-pressure refrigerant is discharged into the discharge chamber 7 in the sealed container 6 via the discharge valve device 5 provided on the base plate 1 b of the fixed scroll 1. The refrigerant discharged into the discharge chamber 7 is discharged from the refrigerant discharge port 12 to the refrigeration cycle.

  The orbiting scroll 52 performs a revolving motion without rotating about the fixed scroll 1 by the rotation motion preventing mechanism 9 for preventing the rotating motion, and the orbiting scroll 52 (the plate-like spiral teeth 52a of the base plate 52b) An overturning load (thrust bearing pressing load, the position of which changes with the rotation of the orbiting scroll 52) F acting on the back surface 52c opposite to the forming surface is received by the thrust plate 8. A hollow cylindrical boss portion 52d is formed at a substantially central portion of the back surface 52c.

  Further, a balance weight 16 is attached to an eccentric shaft portion 15 a provided at one end portion of the main shaft 15. A drive bearing 17 is provided between the outer peripheral part of the balance weight 16 attached to the eccentric shaft part 15a and the inner peripheral part of the hollow cylindrical boss part 52d. The balance weight 16 cancels out the imbalance caused by the orbiting scroll 52 performing the orbiting motion (oscillating motion) via the eccentric shaft portion 15a of the main shaft 15, thereby maintaining the static balance and the dynamic balance. It is supposed to be.

  The main shaft 15 rotates with the rotation of the drive unit 14 to cause the orbiting scroll 52 to revolve. One of the main shafts 15 (near the eccentric shaft portion 15a) is rotatably supported by a main bearing 18 provided in the sealed container 6 (sealed container 6b), and the other of the main shafts 15 is supported by the sealed container 6 (sealed container 6). It is rotatably supported by a sub bearing 19 provided in 6b).

  The discharge valve device 5 regulates the thin plate-like discharge valve 5a that opens and closes the opening (refrigerant outlet) of the discharge port 4 and the opening degree (floating amount) of the discharge valve 5a and suppresses excessive deformation of the discharge valve 5a. And a fixing bolt 5c for fixing the valve pressing 5b to the base plate 1b of the fixed scroll 1 through the discharge valve 5a. The valve retainer 5b has a shape having a curved portion following the flat portion at the tip, and the height of the discharge valve 5a, that is, the opening degree is regulated by the height of the curved portion. The discharge valve 5 a allows the refrigerant flow to flow in one direction from the discharge port 4 to the discharge chamber 7 in the sealed container 6.

  Here, the operation of the scroll compressor 50 will be described. When the main shaft 15 is rotationally driven with the rotation of the drive unit 14, the orbiting scroll 52 whose rotation is suppressed by the rotation motion preventing mechanism 9 performs a revolving motion (turning motion, eccentric rotation operation). When the orbiting scroll 52 performs a revolving motion, the refrigerant flows from the refrigerant suction port 11 into the compression chamber 3, and the suction process is started. Further, since the plate-like spiral teeth 52a of the orbiting scroll 52 and the plate-like spiral teeth 1a of the fixed scroll 1 mesh with each other to form the compression chamber 3 therebetween, the refrigerant flowing into the compression chamber 3 is Since the volume of the compression chamber 3 is reduced with the revolution of the orbiting scroll 52, the compression is performed at a predetermined ratio.

  The refrigerant compressed in the compression chamber 3 is guided to the discharge port 4 provided at the center of the base plate 1b of the fixed scroll 1. A discharge valve device that allows refrigerant to flow in one direction from the discharge port 4 to the discharge chamber 7 in the sealed container 6 at the opening end of the discharge port 4 (the right end of the base plate 1b of the fixed scroll 1 in FIG. 7). 5, when the refrigerant pressure in the discharge port 4 becomes higher than the refrigerant pressure in the discharge chamber 7, the discharge valve device 5 opens and discharges the high-pressure refrigerant in the discharge port 4 into the discharge chamber 7. . Then, the refrigerant discharged into the discharge chamber 7 is discharged from the refrigerant discharge port 12 to the refrigeration cycle. In this way, the scroll compressor 50 continuously repeats refrigerant suction → compression → discharge.

  Then, when the main shaft 15 is rotationally driven with the rotation of the drive unit 14 and the orbiting scroll 52 whose rotation is suppressed by the rotation motion preventing mechanism 9 performs a revolving motion, the refrigerant enters the compression chamber 3 from the refrigerant suction port 11. The refrigerant suction process is started. Further, the refrigerant flowing into the compression chamber 3 formed by the plate-like spiral teeth 52 a of the orbiting scroll 52 and the plate-like spiral teeth 1 a of the fixed scroll 1 meshing with each other is caused to revolve around the orbiting scroll 52. Along with this, when the volume of the compression chamber 3 is reduced and compressed at a predetermined ratio, an overturning load (thrust bearing pressing load, the position of which changes with the rotation of the orbiting scroll 52) F is generated in the orbiting scroll 52. The rollover load F generated in the orbiting scroll 52 is received by the thrust plate 8 via the back surface 52c.

  The thrust bearing surface that receives the overturning load F generated in the orbiting scroll 52 with the thrust plate 8 is filled between the two surfaces of the thrust plate 8 disposed at a position facing the back surface 52c of the orbiting scroll 52 and the back surface 52c. It is composed of lubricated oil.

  As described above, when the orbiting scroll 52 revolves with respect to the fixed scroll 1 and the thrust plate 8, the sliding surface between the rear surface 52c of the orbiting scroll 52 and the thrust plate 8 (the rear surface 52c of the orbiting scroll 52, The rollover load F acts on the two surfaces of the orbiting scroll 52 and the thrust plate 8 disposed at a position facing the back surface 52c, and the sliding contact surface comes into contact, and wear occurs. In the worst case, seizure occurs. However, the slidable contact surface is lubricated by the mist-like lubricating oil contained in the refrigerant introduced from the refrigerant suction port 11 or the lubricating oil introduced from the lubricating oil suction port 13, so that the sliding surface is lubricated. It prevents wear and seizure on the contact surface.

  However, the overturning load F is supported by the pressure generated by the lubricating oil between the sliding contact surfaces of the thrust plate 8 and the back surface 52c of the orbiting scroll 52 between the thrust bearing surfaces. If the pressure cannot be generated, the back surface 52c of the orbiting scroll 52 and the surface of the thrust plate 8 come into contact with each other, wear occurs, and seizure occurs in the worst case.

  Therefore, for example, in Patent Document 1, lubricating oil is stored on at least one contact sliding surface with a counterpart member such as an end plate of a fixed scroll, an end plate of a turning scroll, a thrust bearing, and a rotation prevention mechanism. Many fine oil reservoirs (concave portions) that can be formed are provided to prevent seizure of the sliding portion when the operation is resumed after being stopped for a long time.

  For example, in Patent Document 2, a plurality of oil supply grooves are formed on the back surface of the scroll substrate of the movable scroll member from the radial center side to the outer peripheral side of the scroll substrate. The oil supply groove has a curved shape that inclines in the circumferential direction from the radial center side to the outer peripheral side of the scroll substrate, the inner end portion is set near the outer periphery of the cylindrical portion, and the outer end portion is the outer peripheral edge of the scroll substrate. To reach. A part of the refrigerant gas introduced from the refrigerant suction port passes through the suction passage between the front housing and the movable scroll member and sweeps the back surface of the scroll substrate, and the back surface of the scroll substrate is always in the refrigerant gas atmosphere. Yes, the mist-like lubricating oil in the refrigerant gas enters the oil supply groove. The mist-like lubricating oil in the refrigerant gas passing through the suction passage flows into the oil supply groove from the inner end portion of the oil supply groove, and the lubricating oil in the oil supply groove flows out from the outer end portion.

  Furthermore, for example, in Patent Document 3, an oil supply pump is provided between the back side of the orbiting scroll and the thrust receiver, and a discharge passage that discharges the pressure oil discharged from the oil supply pump toward the oil supply portion on the orbiting scroll side. And a relief valve that keeps the inside of the discharge passage at a pressure equal to or lower than a preset pressure is provided on one of the orbiting scroll and the thrust receiver. Thereby, the orbiting scroll is always in slidable contact with the thrust receiver in a stable manner, and the orbiting scroll is prevented from vibrating in the thrust direction between the fixed scroll and the thrust receiver. It is intended to prevent galling, wear, etc. from occurring in the orbiting scroll and the thrust receiver.

JP-A-8-35495 Japanese Patent Laid-Open No. 7-189946 JP 2002-13490 A

  However, as described above, between the sliding contact surface between the back surface 52c of the orbiting scroll 52 and the thrust plate 8 between the thrust bearing surfaces (at the position facing the back surface 52c of the orbiting scroll 52 and the back surface 52c of the orbiting scroll 52). As a means for increasing the pressure (dynamic pressure) of lubricating oil against the thrust plate 8 disposed between the two surfaces, the effect of the oil sump structure by dimples (concave portions) and grooves irrelevant to the rotation direction was weak. . Further, if an oil supply pump is provided between the back side of the orbiting scroll and the thrust receiver, there is a problem that the manufacturing cost is increased.

  The present invention has been made to solve the above-described problems, and provides excellent lubrication between the two surfaces of the orbiting scroll and the thrust plate disposed at a position opposite to the orbiting scroll. It is an object to provide a scroll compressor that can.

In order to achieve the above object, a scroll compressor according to claim 1 of the present invention forms a compression chamber by meshing plate-like spiral teeth provided on the base plate of each of the fixed scroll and the orbiting scroll. In the scroll compressor that compresses the refrigerant by moving to the center while reducing the volume of the compression chamber by revolving the orbiting scroll,
Lubricating oil is a mist-like lubricating oil contained in the refrigerant introduced from the refrigerant suction port, or a lubricating oil introduced from the lubricating oil suction port, and the flow direction of the lubricating oil on the back of the orbiting scroll A flow path groove that opens in the forward direction and is blocked by a groove wall surface is formed, and the flow path groove is moved to the center while reducing the volume of the compression chamber by revolving the orbiting scroll. By compressing the refrigerant, a rollover groove in the same direction as the operation direction of the orbiting scroll is formed at a position 90 degrees ahead of the maximum point of the orbiting scroll's overturning load. And provided over the entire surface in accordance with the progress of the maximum load point of the overturning load .

According to a second aspect of the present invention, there is provided a scroll compressor in which a compression chamber is formed by meshing plate-like spiral teeth provided on the base plate of each of the fixed scroll and the orbiting scroll to revolve the orbiting scroll. In the scroll compressor that compresses the refrigerant by moving to the center while reducing the volume of the compression chamber by
A flow path groove that is open in the direction and forward direction of the lubricating oil flow is formed on the back surface of the orbiting scroll and is closed by a groove wall surface, and the flow path groove on the inner peripheral side of the orbiting scroll is formed on the orbiting scroll. The orbiting scroll that is supplied from the center side and is dragged by the rotation of the balance weight to change the direction of the flow groove on the inner peripheral side to the forward direction with the flow of the lubricating oil flowing in the rotation direction of the balance weight. The channel groove on the outer peripheral side of the orbit is moved to the center while reducing the volume of the compression chamber by revolving the orbiting scroll and compressing the refrigerant, so that the overturning load acts on the orbiting scroll. wherein at a position becomes 90 degrees direction of travel away from the maximum point of overturning load of the orbiting scroll and the same direction of the flow channel and the direction of movement of the orbiting scroll, the maximum of the overturning load start Characterized in that provided on the entire surface according to the progress of the focus.

  A scroll compressor according to claim 3 of the present invention is the above-described scroll compressor according to claim 1 or 2, wherein a thrust plate is provided on the back surface of the orbiting scroll, and the orbiting scroll is caused to revolve. The overturning load that acts on the orbiting scroll when compressing the refrigerant by moving it to the center while reducing the volume of the chamber is caused by the flow groove between the back surface of the orbiting scroll and the sliding surface of the thrust plate. The thrust plate is supported by the lubricating oil film generated by the dynamic pressure of the lubricating oil generated when the lubricating oil collides with the groove wall surface.

According to the first aspect of the present invention, the compression chambers are formed by meshing the plate-like spiral teeth provided on the respective base plates of the fixed scroll and the orbiting scroll to form a compression chamber, and the orbiting scroll is caused to revolve. In the scroll compressor that compresses the refrigerant by moving it to the center while reducing the volume of the lubricant , the lubricating oil is supplied from the mist-like lubricating oil contained in the refrigerant introduced from the refrigerant inlet or the lubricating oil inlet. It is an introduced lubricating oil, and a flow channel is formed in the back surface of the orbiting scroll in the direction and forward direction of the lubricating oil, and is closed by a groove wall surface. the revolving disk to overthrow load to the orbiting scroll by compressing the while reducing the volume of the compression chamber is moved to the center portion refrigerant by revolving motion starts act In the position becomes the maximum point of overturning load Lumpur 90 degrees direction of travel destination the same direction of the flow channel and the direction of movement of the orbiting scroll, and provided over the entire surface according to the progress of the point of maximum load of the overthrow load By supporting the overturning load (thrust bearing pressing load, the position changes with the rotation of the orbiting scroll) with the dynamic pressure (pressure) due to the pumping action of the lubricating oil channel groove, the thrust bearing parts (the orbiting scroll and It is possible to provide a scroll compressor that can suppress contact between the thrust plates), reduce wear, increase the life of the device, and improve reliability. Compared with the static pressure effect, it is possible to increase the service life of the device and improve the reliability while reducing the product cost without forming parts by forming the lubricating oil flow channel with a mold. It is possible to provide a scroll compressor that can be used.

According to a second aspect of the present invention, the plate-like spiral teeth provided on the base plates of the fixed scroll and the orbiting scroll are meshed with each other to form a compression chamber, and the orbiting scroll is caused to revolve by revolving. In the scroll compressor that compresses the refrigerant by moving it to the center while reducing the volume of the compression chamber, the flow is closed in the direction and forward direction of the lubricating oil on the back of the orbiting scroll, and is blocked by the groove wall surface. A flow groove is formed, and the flow path groove on the inner peripheral side of the orbiting scroll is supplied from the center side of the orbiting scroll and is dragged by the rotation of the balance weight, whereby a flow in the rotation direction of the balance weight is obtained. and the flow of the lubricating oil in the forward direction, the flow path groove on the outer peripheral side of the orbiting scroll direction of the flow channels of the inner peripheral side is changed, the orbital motion of said orbiting scroll The 90-degree direction of travel away from the maximum point of overturning load of the orbiting scroll to overthrow load to the orbiting scroll begins to act by moved to compress the refrigerant to the center while decreasing the volume of the compression chamber by Rukoto The flow groove in the same direction as the operation direction of the orbiting scroll is provided at the position where it is located, and is provided over the entire surface in accordance with the progress of the maximum load point of the rollover load. It is possible to provide a scroll compressor that can suppress contact between thrust bearing components, reduce wear, increase the life of the device, and improve the reliability by supporting with dynamic pressure due to the action. Compared with the static pressure effect, it is possible to increase the service life of the device and improve the reliability while reducing the product cost without forming parts by forming the lubricating oil flow channel with a mold. It is possible to provide a scroll compressor that can be used.

  According to a third aspect of the present invention, a thrust plate is provided on the back of the orbiting scroll, and the orbiting scroll is revolved to move to the center while reducing the volume of the compression chamber. The overturning load that acts on the orbiting scroll when compressing is caused by the collision of the lubricating oil generated by the collision of the lubricating oil with the groove wall surface of the flow channel between the sliding surface of the orbiting scroll and the thrust plate. By supporting it with the thrust plate supported by the lubricating oil film due to dynamic pressure, the overturning load is supported by the dynamic pressure due to the pumping action of the lubricating oil flow channel groove, thereby suppressing contact between thrust bearing parts and reducing wear. Thus, it is possible to provide a scroll compressor that can achieve a longer device life and improved reliability. Also, a scroll compressor is provided that can increase the service life of the device and improve the reliability while reducing the product cost without forming parts by forming the flow channel of the lubricating oil with a mold or the like. It becomes possible.

It is a cross-sectional side view which shows schematic structure of the scroll compressor which is Embodiment 1 of this invention. It is a figure which shows the thrust bearing surface of the turning scroll of the scroll compressor shown in FIG. It is the figure which rotated the thrust bearing surface of the turning scroll shown in FIG. 2 20 degree | times. It is the figure which rotated the thrust bearing surface of the turning scroll shown in FIG. 3 60 degree | times. It is a figure which shows the thrust bearing surface of the turning scroll of a scroll compressor, and provided the opening groove | channel in the flow and the forward direction of lubricating oil. It is a figure which shows the thrust bearing surface of the turning scroll of the scroll compressor which is Embodiment 2 of this invention. It is a cross-sectional side view which shows schematic structure of the conventional scroll compressor.

Hereinafter, preferred embodiments of a scroll compressor according to the present invention will be described in detail with reference to the drawings. In addition, although the scroll compressor demonstrated here shows the example of a horizontal installation type, this invention is applicable also to a vertical installation type. In addition, the following drawings including FIG. 1 are schematically shown, and the relationship such as the size of each component may be different from the actual one, and the present invention is limited by this embodiment. Is not to be done. Further, the same reference numerals are used for the same configuration as the conventional one.
(Embodiment 1)
FIG. 1 is a cross-sectional side view showing a schematic configuration of a scroll compressor 20 according to Embodiment 1 of the present invention. Based on FIG. 1, the structure and operation | movement of the scroll compressor 20 are demonstrated.

  The scroll compressor 20 illustrated here becomes one of the elements which comprise the refrigerating cycle used for various apparatuses, such as an air conditioning apparatus, a hot-water supply apparatus, a refrigeration apparatus, a freezing apparatus, for example.

  The scroll compressor 20 sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state. The scroll compressor 20 includes a revolving motion (a revolving motion and an eccentric revolving operation) with respect to the fixed scroll 1 and the fixed scroll 1 in the hermetic container 6 (comprising the hermetic containers 6a and 6b). The compression mechanism part which combined these is provided. The scroll compressor 20 also includes a drive unit 14 (for example, a rotary drive unit such as an electric motor or a clutch) that drives the main shaft 15 that supports the orbiting scroll 2.

  The fixed scroll 1 is composed of a base plate 1b and a plate-like spiral tooth 1a which is a spiral projection standing on one surface of the base plate 1b, and is fixed to the sealed container 6 (sealed container 6a) with a bolt or the like. Has been. The orbiting scroll 2 is composed of a base plate 2b and a plate-like spiral tooth 2a that is provided on one surface of the base plate 2b and is a spiral protrusion having substantially the same shape as the plate-like spiral tooth 1a. ing. By compressing the plate-like spiral teeth 1 a of the fixed scroll 1 and the plate-like spiral teeth 2 a of the orbiting scroll 2, a compression chamber 3 having a relatively variable volume is formed.

  And the sealed container 6 (sealed container 6b) which becomes the outer peripheral part of the compression chamber 3 formed by meshing the plate-like spiral teeth 1a of the fixed scroll 1 and the plate-like spiral teeth 2a of the orbiting scroll 2 with each other. A refrigerant inlet 11 for introducing the refrigerant into the compression chamber 3 and a lubricating oil inlet 13 for introducing the lubricating oil into the compressor are provided. A discharge port 4 is formed at the center of the base plate 1b of the fixed scroll 1 to discharge the compressed and high-pressure refrigerant. Then, the compressed high-pressure refrigerant is discharged into the discharge chamber 7 in the sealed container 6 via the discharge valve device 5 provided on the base plate 1 b of the fixed scroll 1. The refrigerant discharged into the discharge chamber 7 is discharged from the refrigerant discharge port 12 to the refrigeration cycle.

  The orbiting scroll 2 performs a revolving motion without rotating about the fixed scroll 1 by the rotation motion preventing mechanism 9 for preventing the rotating motion, and the orbiting scroll 2 (the plate-like spiral teeth 2a of the base plate 2b) An overturning load (thrust bearing pressing load, the position of which changes with the rotation of the orbiting scroll 2) F acting on the back surface 2c opposite to the forming surface is received by the thrust plate 8. Further, a hollow cylindrical boss 2d is formed at a substantially central portion of the back surface 2c.

  Further, a balance weight 16 is attached to an eccentric shaft portion 15 a provided at one end portion of the main shaft 15. A drive bearing 17 is provided between the outer peripheral portion of the balance weight 16 attached to the eccentric shaft portion 15a and the inner peripheral portion of the hollow cylindrical boss portion 2d. The balance weight 16 cancels out the unbalance caused when the orbiting scroll 2 orbits (oscillates) through the eccentric shaft portion 15a of the main shaft 15, thereby maintaining a static balance and a dynamic balance. It is like that.

  The main shaft 15 rotates with the rotation of the drive unit 14 to cause the orbiting scroll 2 to revolve. One of the main shafts 15 (near the eccentric shaft portion 15a) is rotatably supported by a main bearing 18 provided in the sealed container 6 (sealed container 6b), and the other of the main shafts 15 is supported by the sealed container 6 (sealed container 6). It is rotatably supported by a sub bearing 19 provided in 6b).

  The discharge valve device 5 regulates the thin plate-like discharge valve 5a that opens and closes the opening (refrigerant outlet) of the discharge port 4 and the opening degree (floating amount) of the discharge valve 5a and suppresses excessive deformation of the discharge valve 5a. And a fixing bolt 5c for fixing the valve pressing 5b to the base plate 1b of the fixed scroll 1 through the discharge valve 5a. The valve retainer 5b has a shape having a curved portion following the flat portion at the tip, and the height of the discharge valve 5a, that is, the opening degree is regulated by the height of the curved portion. The discharge valve 5 a allows the refrigerant flow to flow in one direction from the discharge port 4 to the discharge chamber 7 in the sealed container 6.

  Here, the operation of the scroll compressor 20 will be described. When the main shaft 15 is rotationally driven along with the rotation of the drive unit 14, the orbiting scroll 2 whose rotation is suppressed by the rotation motion preventing mechanism 9 performs a revolving motion (a turning motion, an eccentric rotation operation). When the orbiting scroll 2 performs a revolving motion, the refrigerant flows from the refrigerant suction port 11 into the compression chamber 3, and the suction process is started. Further, the plate-like spiral teeth 2a of the orbiting scroll 2 and the plate-like spiral teeth 1a of the fixed scroll 1 are engaged with each other to form a compression chamber 3 therebetween, so that the compression chamber 3 is moved from the outer peripheral portion to the central portion. The refrigerant flowing into the compression chamber 3 is compressed at a predetermined ratio by gradually reducing the volume of the compression chamber 3 while being moved toward the front.

  The refrigerant compressed in the compression chamber 3 is guided to the discharge port 4 provided at the center of the base plate 1b of the fixed scroll 1. A discharge valve device that allows refrigerant to flow in one direction from the discharge port 4 to the discharge chamber 7 in the sealed container 6 at the opening end of the discharge port 4 (the right end of the base plate 1b of the fixed scroll 1 in FIG. 1). 5, when the refrigerant pressure in the discharge port 4 becomes higher than the refrigerant pressure in the discharge chamber 7, the discharge valve device 5 opens and discharges the high-pressure refrigerant in the discharge port 4 into the discharge chamber 7. . Then, the refrigerant discharged into the discharge chamber 7 is discharged from the refrigerant discharge port 12 to the refrigeration cycle. In this way, the scroll compressor 20 continuously repeats refrigerant suction → compression → discharge.

  In this way, when the main shaft 15 is rotationally driven in accordance with the rotation of the drive unit 14 and the orbiting scroll 2 whose rotation is suppressed by the rotation motion preventing mechanism 9 performs the revolving motion, the refrigerant is transferred from the refrigerant suction port 11 to the compression chamber. 3 and the refrigerant suction process is started. Further, the refrigerant flowing into the compression chamber 3 formed by the plate-like spiral teeth 2 a of the orbiting scroll 2 and the plate-like spiral teeth 1 a of the fixed scroll 1 meshing with each other is caused to revolve around the orbiting scroll 2. Along with this, when the volume of the compression chamber 3 is reduced and compressed at a predetermined ratio, a rollover load (thrust bearing pressing load, the position changes with the rotation of the orbiting scroll 2) F is generated. The rollover load F acting on 2c is received by the thrust plate 8.

  The thrust bearing surface that receives the overturning load F generated in the orbiting scroll 2 with the thrust plate 8 is filled between the two surfaces of the orbiting scroll 2 on the back surface 2c and the thrust plate 8 disposed at a position facing the back surface 2c. It is composed of lubricated oil.

  When the orbiting scroll 2 performs a revolving motion with respect to the thrust plate 8, the sliding contact surface between the rear surface 2 c of the orbiting scroll 2 and the thrust plate 8 (the rear surface 2 c of the orbiting scroll 2 and the rear surface 2 c of the orbiting scroll 2). Between the thrust plate 8 and the thrust plate 8 disposed at a position opposite to each other by the mist-like lubricating oil contained in the refrigerant introduced from the refrigerant suction port 11 or the lubricating oil introduced from the lubricating oil suction port 13. Lubricated to suppress contact between thrust bearing parts (orbiting scroll 2 and thrust plate 8) on the sliding contact surface (thrust bearing surface), reduce wear, increase the life of the device, and improve reliability. Yes.

  When the orbiting scroll 2 performs a revolving motion (orbiting motion and eccentric rotation operation) with respect to the fixed scroll 1 in this way, the volume of the compression chamber 3 is reduced and the refrigerant is compressed at a predetermined ratio. Due to the distribution of pressure generated in the compression operation, an overturning load F is generated that presses the orbiting scroll 2 in the direction of the thrust bearing surface (thrust plate 8) while the orbiting scroll 2 is tilted. The rollover load F moves in the rotation direction because the pressure distribution in the compression chamber 3 changes with the eccentric rotation operation. However, in the configuration of the scroll compressor 20, the position of the balance weight 16 in the traveling direction (rotation direction) is slightly ahead. In addition, the maximum load (the rollover load F maximum point) is always generated. The rollover load F is distributed at an angle of ± 90 degrees around the maximum load point (the maximum point of the rollover load F) (see the generation range of the rollover load F in FIG. 3).

  The overturning load F is between the sliding contact surfaces of the back surface 2c of the orbiting scroll 2 and the thrust plate 8 between the thrust bearing surfaces (the back surface 2c of the orbiting scroll 2 and the thrust plate 8 disposed at a position facing the back surface 2c). Is supported by the pressure generated by the lubricating oil filled between the two surfaces), and the generation of pressure forces the wedge effect, squeeze effect, dynamic pressure due to the pumping action, and the lubricating oil pressurized using a pump, etc. There is a method using static pressure to be supplied. If sufficient pressure cannot be generated, the back surface 2c of the orbiting scroll 2 and the surface of the thrust plate 8 come into contact with each other and wear occurs, and in the worst case, seizure occurs.

  Here, the pumping action will be explained. Spiral grooves, herringbone grooves, and the like are formed on the thrust bearing surface, and the working fluid such as lubricating oil is effectively guided into the groove by the groove shape. The working fluid is made to collide with the end face (the flow path is reduced) and compressed to generate pressure. In the conventional scroll compressor, the pumping effect cannot be used for the thrust bearing surface of the orbiting scroll. The reason is that the groove shape is designed to exhibit an effect at the time of shaft center rotation (spinning), and the eccentric rotation operation like the conventional scroll compressor cannot guide the flow of the lubricating oil well.

  Although it is difficult as described above to generate pressure in all grooves at all timings, the timing and grooves at which pressure is generated and the grooves are narrowed down. Specifically, the maximum point of the rollover load F always advances 90 degrees. The groove (lubricant flow channel groove 2e) at the position (direction where the rollover load begins to occur) ahead of the direction (rotation direction) generates pressure at that timing, so that the orbiting scroll 2 at that timing By setting the direction of the groove (lubricant flow channel 2e) to be the same as the operation direction, the flow velocity of the lubricating oil relative to the end of the groove is maximized (dynamic pressure generated by the groove: load capacity is proportional to the flow velocity. It is possible to effectively generate dynamic pressure (see FIGS. 2 and 3).

  Since the maximum point of the overturning load F is rotating relative to the axis of the orbiting scroll 2 (main shaft 15) as a relative motion, for example, if the maximum load point advances 60 degrees, a groove 90 degrees ahead (see FIG. 4), if the maximum load point advances 180 degrees, the groove 90 degrees ahead always has the same relationship and generates dynamic pressure.

The reason why the pressure generation timing is 90 degrees ahead of the maximum point of the overturning load F is that it is slow to generate dynamic pressure simultaneously with the generation of the overturning load F (the back surface 2c of the orbiting scroll 2 and the thrust plate 8 are in contact with each other). Have occurred in advance). The numerical value “90 degrees” is a value set in order to cover the entire generation region of the rollover load F in consideration of the distribution of the rollover load F, but is not limited and may be “30 degrees”. It may be “45 degrees”.
(Embodiment 2)
FIG. 5 shows the thrust bearing surface of the orbiting scroll of the scroll compressor, and an opening groove is provided in the forward direction with the flow of the lubricating oil. FIG. 6 shows a thrust bearing surface of the orbiting scroll of the scroll compressor according to the second embodiment of the present invention.

  The method of supplying the lubricating oil to the thrust bearing portion (between the two surfaces of the orbiting scroll 2 and the thrust plate 8) differs depending on the scroll compressor, but in the second embodiment, the lubricant is supplied from the center side (inside) of the orbiting scroll 2, By being dragged by the rotation of the balance weight 16, a flow in the rotation direction of the balance weight 16 occurs.

  Here, as shown in FIG. 5, by providing grooves (flow channel grooves) in the direction and forward direction of the flow of the lubricating oil, the inhalability of the lubricating oil is improved.

  Therefore, in the second embodiment, as shown in FIG. 6, the opening of the groove (lubricant flow channel groove 2f) is in the forward direction with respect to the flow direction of the lubricating oil, and the groove (lubricant flow channel groove 2g) The end portion always has a direction that coincides with the operation direction of the orbiting scroll 2 at a position 90 degrees ahead of the maximum point of the rollover load (position where the rollover load starts to occur).

  Thus, the improvement of the suction property and the generation of the dynamic pressure at the timing when the rollover load F is generated are compatible, and the grooves (the lubricating oil flow groove 2f and the lubricating oil flow groove 2g are similar to the herringbone groove). In the position where the direction of () changes, the lubricating oil collides with the groove wall surface, so that dynamic pressure is generated and the lubricating effect can be further enhanced.

  As described above, according to the present invention, the compression spiral chamber 3 is formed by meshing the plate-like spiral teeth 1a and 2a provided on the base plates 1b and 2b of the fixed scroll 1 and the orbiting scroll 2, respectively, In the scroll compressor 20 that compresses the refrigerant by moving the scroll 2 to the center while reducing the volume of the compression chamber 3 by revolving, the revolving motion of the orbiting scroll 2 on the back surface 2c of the orbiting scroll 2 is performed. The position of the orbiting scroll 2 coincides with the operation direction of the orbiting scroll 2 at the position where the overturning load F starts to act on the orbiting scroll 2 by compressing the refrigerant by moving to the center while reducing the volume of the compression chamber 3. The flow channel 2e of the lubricating oil facing is provided on the entire surface in accordance with the change in position of the overturning load F, so that the overturning load (thrust bearing pressing load, turning The thrust bearing parts (the orbiting scroll 2 and the thrust plate 8) are in contact with each other by supporting F with the dynamic pressure (pressure) generated by the pumping action of the lubricating oil passage groove 2e. Thus, it is possible to provide the scroll compressor 20 that can reduce the wear, increase the life of the apparatus, and improve the reliability. Compared with the static pressure effect, it is possible to increase the service life of the device and improve the reliability while reducing the product cost without forming parts by forming the lubricating oil flow channel with a mold. It is possible to provide a scroll compressor 20 that can be used.

  Further, the compression scroll 3 is formed by meshing the plate-like spiral teeth 1a and 2a provided on the base plates 1b and 2b of the fixed scroll 1 and the orbiting scroll 2 respectively, and the orbiting scroll 2 is compressed by revolving. In the scroll compressor 20 that compresses the refrigerant by moving to the center while reducing the volume of the chamber 3, the opening is on the back surface 2c of the orbiting scroll 2 and the forward direction of the flow of the lubricating oil, The revolving motion of the orbiting scroll 2 reduces the volume of the compression chamber 3 and moves it to the center to compress the refrigerant, thereby compressing the refrigerant. The flow passage grooves 2f and 2g of the lubricating oil having a direction coinciding with the operation direction of the roller are provided on the entire surface in accordance with the position change of the rollover load F. Is supported by the dynamic pressure generated by the pumping action of the lubricating oil passage groove 2g, so that the contact between thrust bearing parts can be suppressed, wear can be reduced, the life of the device can be extended, and the reliability can be improved. The machine 20 can be provided. Compared with the static pressure effect, forming the flow grooves 2f and 2g for lubricating oil with a mold or the like realizes longer device life and improved reliability while reducing product costs without increasing the number of parts. It becomes possible to provide the scroll compressor 20 which can do.

  Further, a thrust plate 8 is provided on the back surface 2c of the orbiting scroll 2, and the orbiting scroll 2 is moved when the orbiting scroll 2 is revolved to move to the center while reducing the volume of the compression chamber 3 to compress the refrigerant. 2 is a dynamic pressure of the lubricating oil generated when the lubricating oil collides with the groove wall surfaces of the channel grooves 2e and 2g between the sliding contact surface between the back surface 2c of the orbiting scroll 2 and the thrust plate 8. Is supported by the thrust oil film supported by the lubricating oil film, and the overturning load F is supported by the dynamic pressure due to the pumping action of the lubricating oil passage grooves 2e and 2g, thereby suppressing contact between the thrust bearing parts and wear. Thus, it is possible to provide the scroll compressor 20 capable of realizing a longer device life and improved reliability. Also, by forming the lubricating oil flow grooves 2e, 2f, and 2g with a mold or the like, a scroll that can increase the life of the device and improve the reliability while suppressing the product cost without increasing the number of parts. The compressor 20 can be provided.

  Further, the lubricating oil flowing through the flow grooves 2e, 2f, 2g of the lubricating oil provided on the back of the orbiting scroll 2 is a mist-like lubricating oil contained in the refrigerant introduced from the refrigerant suction port 11, By supporting the overturning load F with the dynamic pressure due to the pumping action of the channel grooves 2e and 2g of the mist-like lubricating oil contained in the refrigerant introduced from the refrigerant suction port 11, the contact between the thrust bearing parts is suppressed, It is possible to provide the scroll compressor 20 capable of reducing the wear and extending the life of the apparatus and improving the reliability.

  Further, the lubricating oil flowing in the lubricating oil flow grooves 2e, 2f, 2g provided on the back surface 2c of the orbiting scroll 2 is the lubricating oil introduced from the lubricating oil suction port 13, so that the rollover load F is reduced to the lubricating oil. By supporting with the dynamic pressure by the pumping action of the lubricating oil flow channel 2e, 2g introduced from the suction port 13, the contact between the thrust bearing parts is suppressed, the wear is reduced, the life of the device is extended, and the reliability is improved. It becomes possible to provide the scroll compressor 20 which can implement | achieve.

DESCRIPTION OF SYMBOLS 1 Fixed scroll 1a Plate-shaped spiral tooth 1b Base plate 2 Orbiting scroll 2a Plate-shaped spiral tooth 2b Base plate 2c Back surface 2e Flow path groove (groove) of lubricating oil
2f Lubricating oil flow channel (groove)
2g Lubricating oil channel groove (groove)
DESCRIPTION OF SYMBOLS 3 Compression chamber 4 Discharge port 5 Discharge valve apparatus 6 Sealed container 7 Discharge chamber 8 Thrust plate 9 Rotation motion prevention mechanism 11 Refrigerant suction port 12 Refrigerant discharge port 13 Lubricating oil suction port 14 Drive part 15 Main shaft 16 Balance weight 20 Scroll compressor

Claims (3)

A compression chamber is formed by meshing plate-like spiral teeth provided on the base plate of each of the fixed scroll and the orbiting scroll, and the orbiting scroll is revolved to reduce the volume of the compression chamber to the center. In a scroll compressor that compresses the refrigerant by moving
Lubricating oil is a mist-like lubricating oil contained in the refrigerant introduced from the refrigerant inlet, or a lubricating oil introduced from the lubricating oil inlet,
Opening in the forward direction and the flow direction of the lubricating oil on the back of the orbiting scroll, and has a flow path groove closed by a groove wall surface,
The orbiting scroll starts to apply a capsizing load to the orbiting scroll by compressing the refrigerant by moving the orbiting scroll to the center while revolving the orbiting scroll and reducing the volume of the compression chamber. In the position 90 degrees ahead of the maximum point of the overturning load, a flow path groove in the same direction as the operation direction of the orbiting scroll is provided, and provided on the entire surface in accordance with the change in position of the overturning load. Scroll compressor. A compression chamber is formed by meshing plate-like spiral teeth provided on the base plate of each of the fixed scroll and the orbiting scroll, and the orbiting scroll is revolved to reduce the volume of the compression chamber to the center. In a scroll compressor that compresses the refrigerant by moving
Opening in the direction and forward direction of the flow of the lubricating oil on the back of the orbiting scroll, and has a channel groove closed by the groove wall surface,
The flow path groove on the inner peripheral side of the orbiting scroll is supplied from the center side of the orbiting scroll and is dragged by the rotation of the balance weight so that the flow of the lubricating oil in the rotation direction of the balance weight is in order. The flow path groove on the outer peripheral side of the orbiting scroll changes in direction and the direction of the flow groove on the inner peripheral side changes to the center while reducing the volume of the compression chamber by revolving the orbiting scroll. By moving and compressing the refrigerant, a capsizing load begins to act on the orbiting scroll. A scroll compressor characterized in that it is a road groove and is provided on the entire surface in accordance with a change in position of the overturning load. A thrust plate is provided on the back surface of the orbiting scroll, and acts on the orbiting scroll when the orbiting scroll is revolved to move to the center while reducing the volume of the compression chamber to compress the refrigerant. The overturning load is supported by the lubricating oil film by the dynamic pressure of the lubricating oil generated when the lubricating oil collides with the groove wall surface of the flow path groove between the sliding contact surface of the orbiting scroll and the thrust plate. The scroll compressor according to claim 1, wherein the scroll compressor is received by a plate.

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