JP5304285B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor for compressing refrigerant gas in a cooling device such as a cooling / heating air conditioner or a refrigerator, or a heat pump type hot water supply device.

  Conventionally, scroll compressors used in refrigeration air conditioners and refrigerators generally have fixed scrolls and swirl scrolls, in which spiral wraps rise from end plates, form compression chambers between the two, and orbiting scrolls are constrained by rotation. When rotating along a circular orbit under the restraint of rotation due to, the working fluid is sucked, compressed and discharged by moving while changing its volume.

  The working fluid is gradually compressed with the turning motion of the orbiting scroll, and becomes a high pressure state toward the center portion. Therefore, a separation force acts on the orbiting scroll in a direction away from the fixed scroll. As a result, a gap is generated between the orbiting scroll and the fixed scroll, so that leakage occurs during compression, resulting in performance deterioration. As a countermeasure, an intermediate pressure is applied to a back pressure chamber provided on the back surface of the orbiting scroll to prevent separation from the fixed scroll.

Furthermore, a path communicating from the back pressure chamber side opening end that opens to the back pressure chamber to the compression chamber side opening end that opens to the compression chamber is provided, and the compression chamber side opening end provided on the end plate of the orbiting scroll is the revolving scroll side opening end. Along with the orbiting motion, the compression chamber that communicates with the thrust surface of the fixed scroll and the suction port periodically moves, so that the compression chamber that does not communicate with the suction port and that is formed outside the orbiting scroll is intermittently refueled. It is possible, and the supplied oil plays a role of a seal of the compression chamber, the leakage of the working fluid is suppressed, and the reduction of the compression efficiency is suppressed (for example, see Patent Document 1).
JP 2007-270697 A

  However, in the above prior art, the compression chamber side opening end of the path connecting the back pressure chamber and the compression chamber is not opened in the compression chamber formed inside the orbiting scroll. It is difficult to supply the seal oil, and the compression efficiency may be reduced due to leakage of the working fluid.

  In particular, as shown in the above prior art, scroll compression having spiral wraps with different suction volumes of the outer compression chamber formed on the outer wall side of the spiral wrap of the orbiting scroll and the inner compression chamber formed on the inner wall side. In the compressor (hereinafter referred to as an asymmetric scroll compressor), the leakage from the inner compression chamber to the inner compression chamber on the one low pressure side is from the outer compression chamber on the lower pressure side. More than leakage into the outer compression chamber.

  In an asymmetric scroll compressor in which the suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber, the inner compression chamber having a smaller suction volume has a feature that the pressure increase rate with respect to the crank rotation angle is larger due to the suction volume difference. On the other hand, in both the outer and inner compression chambers, the formation of the next compression chamber at the time when the orbiting scroll makes one revolution from the completion of closing of each compression chamber is the same as in the symmetric scroll.

The above description will be further described with reference to the drawings. 18 and 19, the spiral wrap side surface gap D2 that partitions the second compression chamber 15b-1 and the second compression chamber 15b-2 formed thereafter, the first compression chamber 15a-1, and the subsequent compression chamber 15b-1. There is a spiral wrap side surface gap D1 that partitions the first compression chamber 15a-2. In FIG. 19, when the pressure increase speeds of the first compression chamber 15a and the second compression chamber 15b are compared, the pressure change is larger in the second compression chamber 15b having a smaller suction volume. Therefore, the spiral wrap side surface gap D2 that partitions the second compression chambers 15b is more likely to leak than the spiral wrap side surface gap D1 that partitions the first compression chambers 15b. Leakage through the spiral wrap side surface causes recompression of the refrigerant, resulting in a decrease in compression performance due to useless work.

  The present invention solves the above-mentioned conventional problems, and provides a scroll compressor that realizes an improvement in compressor efficiency by an oil supply path and an oil supply amount control in consideration of a compression chamber pressure distribution and a leakage path of an asymmetric scroll compressor. The purpose is to do.

  In order to solve the above-described problems, a scroll compressor according to the present invention includes a fixed scroll in which a spiral wrap rises from an end plate and a revolving scroll, and a compression chamber is provided between the both. And the inner compression chamber formed inside the orbiting scroll. The suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber. A chamber is formed, and the orbiting scroll revolves with a predetermined orbiting radius along a circular orbit, so that the compression chamber moves toward the center while changing the volume, and sucks the working fluid from the suction port formed in the fixed scroll. The scroll compressor performs a series of operations of compression and discharge after being confined in the compression chamber, and communicates with the first path connecting the high pressure region and the back pressure chamber, and the back pressure chamber and the suction port. A second path connecting the compression chambers not provided, the compression chamber side opening end of the second path intermittently opens to the outer compression chamber and the inner compression chamber, and the total amount of oil supplied to the inner compression chamber is compressed outside Increase the total amount of oil supplied to the room.

  The scroll compressor according to the present invention increases the total oil supply amount to the inner compression chamber from the total oil supply amount to the outer compression chamber while supplying oil to the inner compression chamber and the outer compression chamber that do not communicate with the suction port. The leakage of the working fluid from the spiral wrap side surface gap between the same compression chambers can be effectively suppressed, and the compression efficiency can be improved. At the same time, by intermittently supplying oil to these compression chambers, it is possible to widen the range of oil supply control in the direction of reducing the amount of oil supply, and it is possible to suppress an increase in viscosity loss due to excessive oil supply, so highly efficient scrolling A compressor can be provided.

  According to a first aspect of the present invention, there is provided a fixed scroll in which a spiral wrap rises from an end plate and a revolving scroll, and a compression chamber is provided between the two, and the compression chamber is formed on the outer side of the revolving scroll wrap and the revolving scroll. The inner compression chamber is formed inside, the suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber, a high pressure region and a back pressure chamber are formed on the back of the orbiting scroll, and the orbiting scroll is a circular orbit. , The compression chamber moves toward the center while changing the volume, sucks the working fluid from the suction port formed in the fixed scroll, confines it in the compression chamber, and then compresses it. A scroll compressor that performs a series of discharge operations, and includes a first path connecting the high pressure region and the back pressure chamber, and a second path connecting the back pressure chamber and the compression chamber not communicating with the suction port, 2 The compression chamber side opening end of the path, the outer compression chamber intermittently opened inside the compression chamber, in which the total amount of oil to the inner compression chamber is more than the total amount of oil to the outer compression chambers. According to this configuration, in both the inner compression chamber and the outer compression chamber, the spiral wrap side surface gap between the compression chamber that previously closed the working fluid and the compression chamber that next closed the working fluid. The leakage of the working fluid can be effectively suppressed, and an increase in viscosity loss due to excessive oil supply can be suppressed.

According to a second aspect of the present invention, in particular, in the scroll compressor of the first aspect, the compression chamber side opening end of the second path is provided on the upper surface of the orbiting scroll wrap, and the opening end is fixed scroll in accordance with the orbiting movement of the orbiting scroll. It opens intermittently in a recess provided on the surface of the lap end plate. According to this configuration, since the oil supply amount can be controlled by the communication time depending on the diameter and length of the second path and the shape of the recess, the adjustment range of the oil supply amount into the compression chamber and the pressure adjustment of the back pressure chamber The range is expanded and the compressor efficiency and back pressure stability can be further improved.

  According to a third aspect of the invention, in the scroll compressor of the first aspect of the invention, in particular, a plurality of compression chamber side opening ends of the second path are provided on the wrap end plate surface of the orbiting scroll. By periodically moving the upper surface of the compression chamber and the wrap of the fixed scroll and the thrust surface of the compression chamber and the fixed scroll, the compression chamber is intermittently opened. According to this configuration, in addition to the effect of the second aspect, the second path can be formed only by drilling the end plate, so that the number of processing steps can be reduced.

  In a fourth aspect of the invention, in particular, in the scroll compressor according to any one of the first to third aspects of the invention, the back pressure chamber side opening end of the first path is provided with a high pressure region and a back pressure provided on the back of the orbiting scroll. A seal member for partitioning the chamber is passed. According to this configuration, since the amount of oil supplied to the compression chamber can be further reduced, the adjustment range of the oil supply amount to the compression chamber and the pressure adjustment range of the back pressure chamber are further expanded, and the efficiency and back pressure of the compressor are increased. Can be further improved. Further, even if the second path does not communicate with the back pressure chamber and the compression chamber, even if the crankshaft is rotating once, excessive back pressure rise can be suppressed by intermittently communicating the first path. . Furthermore, since the amount of oil flowing from the high pressure region into the back pressure chamber can be controlled by the communication time, there is no need to provide a throttle for adjusting the amount of oil in the first path, and the trouble of foreign matter getting caught in the throttle is avoided. And reliability can be improved.

  According to a fifth aspect of the invention, in particular, in the scroll compressor according to any one of the first to fourth aspects, a third path connecting the back pressure chamber and the compression chamber communicating with the suction port is provided. According to this configuration, the oil supplied from the back pressure chamber serves as a seal for the compression chamber communicating with the suction, can suppress the leakage of the working fluid in the suction stroke, can improve the volumetric efficiency, and the compressor efficiency Can be further improved.

  According to a sixth aspect of the present invention, in the scroll compressor according to any one of the first to fourth aspects, a fourth path is provided to connect the high pressure region and the compression chamber communicating with the suction port. According to this configuration, since high-pressure oil is supplied to the compression chamber that communicates with suction, the lubrication performance during high-load operation with a large differential pressure can be improved, abnormal wear of the lap can be suppressed, and reliability can be improved. .

  A seventh aspect of the present invention is the scroll compressor according to any one of the fifth to sixth aspects, wherein the compression chamber side opening ends of the third and fourth paths are provided on the upper surface of the orbiting scroll wrap. It is. According to this configuration, the water hammer phenomenon due to opening and closing of the oil supply path does not occur, and noise caused by the working fluid can be reduced.

  According to an eighth aspect of the present invention, in the scroll compressor according to the fifth or sixth aspect, the compression chamber side opening ends of the third and fourth paths are provided on the wrap upper surface of the orbiting scroll, and the opening end is the orbiting scroll. As a result of the swiveling motion, the opening is intermittently opened in a recess provided on the lap end plate surface of the fixed scroll. According to this configuration, the oil supply amount can be controlled by the communication time depending on the diameters and lengths of the third and fourth paths and the shape of the recesses. Deterioration of volumetric efficiency due to heating can be suppressed, and the efficiency of the compressor can be improved.

According to a ninth aspect of the present invention, in the scroll compressor described in the fifth or sixth aspect, a plurality of compression chamber side opening ends of the third and fourth paths are provided on the wrap end plate surface of the orbiting scroll, and the orbiting scroll orbits. Accordingly, the opening end periodically opens in the compression chamber by periodically moving on the wrap upper surface of the compression chamber and the fixed scroll and the thrust surface of the compression chamber and the fixed scroll. According to this configuration, in addition to the effect of the eighth aspect, the third and fourth paths can be formed only by drilling the end plate, so that the number of processing steps can be reduced.

  According to a tenth aspect of the invention, in particular, in the scroll compressor according to any one of the first to ninth aspects, the working fluid is a high-pressure fluid, for example, carbon dioxide. According to this configuration, even when the working pressure of the working fluid is high, a stable back pressure is applied while effectively suppressing leakage of the working fluid from the spiral wrap side surface gap between the compression chambers. be able to.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention. 2 and 3 are enlarged cross-sectional views of the main part of the compression mechanism of FIG. 1, FIG. 2 shows internal communication, and FIG. 3 shows external communication.

  Hereinafter, the configuration, operation, and action of the scroll compressor according to the first embodiment will be described.

  As shown in FIG. 1, the scroll compressor of the present invention is configured to include a hermetic container 1 and a compression mechanism 2, a motor unit 3, and an oil storage unit 20 therein. The details of the compression mechanism will be described with reference to FIGS. 2 and 3. The main bearing member 11 of the shaft 4 fixed by welding or shrink fitting in the sealed container 1, and bolted on the main bearing member 11. A scroll-type compression mechanism 2 is configured by sandwiching a turning scroll 13 meshing with the fixed scroll 12 between the fixed scroll 12. Between the orbiting scroll 13 and the main bearing member 11, there is provided a rotation restraining mechanism 14 such as an Oldham ring that guides the orbiting scroll 13 so as to prevent the rotation of the orbiting scroll and move in a circular orbit, and an eccentric shaft at the upper end of the shaft 4. The orbiting scroll 13 is moved in a circular orbit by driving the orbiting scroll 13 eccentrically by the portion 4a. By using the fact that the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves while shrinking the volume from the outer peripheral side toward the center portion, the suction communicated outside the sealed container 1. The working fluid is sucked from the suction port 17 in the outer peripheral portion of the pipe 16 and the fixed scroll 12 and is compressed in the compression chamber 15 after being closed. The working fluid that has reached a predetermined pressure pushes the reed valve 19 through the discharge port 18 at the center of the fixed scroll 12 and is discharged into the sealed container 1.

  Further, a pump 25 is provided at one end of the shaft 4, and the suction port of the pump 25 is disposed in the oil storage unit 20. Since the pump 25 is driven simultaneously with the scroll compressor, the pump 25 can reliably suck up the oil 6 in the oil storage unit 20 provided at the bottom of the hermetic container 1 regardless of the pressure condition and the operation speed. The worry of running out of oil is also eliminated. The oil 6 sucked up by the pump 25 is supplied to the compression mechanism 2 through an oil supply hole 26 running vertically through the shaft 4. If foreign matter is removed from the oil 6 with an oil filter or the like before or after the oil 25 is sucked up by the pump 25, foreign matter can be prevented from entering the compression mechanism 2 and further reliability can be improved.

  The oil 6 guided to the compression mechanism 2 is substantially equal to the discharge pressure of the scroll compressor and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with each other, and the predetermined compression function is stably exhibited. Further, a part of the oil 6 enters the bearing portion 66 between the shaft 4 and the main bearing member 11, the fitting portion between the eccentric shaft portion 4 a and the orbiting scroll 13 so as to obtain a clearance by the supply pressure and the own weight. Then, the respective parts are lubricated and then dropped and returned to the oil storage unit 20.

  The compression chamber 15 formed by the fixed scroll 12 and the orbiting scroll 13 includes an outer compression chamber 15a formed on the wrap outer wall side of the orbiting scroll 13 and an inner compression chamber 15b formed on the wrap inner wall side. The suction volume of the chamber 15a is larger than the suction volume of the inner compression chamber 15b. As a result, as shown in FIG. 19, the pressure increase rate of the inner compression chamber 15b with respect to the crank rotation angle becomes faster than the pressure increase rate of the outer compression chamber 15a. As a result, the spiral wrap side surface D2 shown in FIG. Since the pressure difference between the inner compression chamber 15b-1 partitioned by the inner compression chamber 15b-2 formed on the low pressure side and the inner compression chamber 15b-2 is larger than that of the outer compression chamber 15a, the spiral compression wrap side surface D2 of the inner compression chamber 15b is used. The working fluid is likely to leak.

  Therefore, in the scroll compressor of the present embodiment, the oil supply amount control path 55 that leads from the oil storage unit 20 to the inner compression chamber 15b is configured by the first path 55-1 and the second path 55-2, and the inner compression chamber. By setting the cross-sectional area of the communication recess 84 to be larger than the cross-sectional area of the outer compression chamber communication recess 85, the oil is positively supplied to the outer compression chamber 15b having a high pressure increase rate, thereby forming the inner side formed immediately before. The leakage of the working fluid from the compression chamber 15b-1 to the inner compression chamber 15b-2 formed next can be suppressed.

  The oil 6 flowing out from the oil supply hole 26 flows into the first path 55-1 from the high-pressure region side opening end 55-1 a of the first path 55-1, and the back pressure chamber of the first path 55-1. It flows out from the side opening end 55-1b. Further, since the high pressure region 30 and the back pressure chamber 29 are closely separated by the seal member 78, the oil 6 does not leak between the high pressure region 30 and the back pressure chamber 29.

  At the crank angle shown in FIG. 2 (the crank angle in FIG. 4A), the back pressure chamber side opening end 55-1b of the first path 55-1 is open to the high pressure region 30. Therefore, since there is no pressure difference between the high pressure region side opening end 55-1a and the back pressure chamber side opening end 55-1b of the first path 55-1, the movement of the oil 6 in the first path 55-1 is Absent.

  On the other hand, at the crank angle shown in FIG. 3 (the crank angles in FIGS. 4B, 4C, and 4D), the back pressure chamber side opening end 55-1b of the first path 55-1 is the seal member. The back pressure chamber 29 is opened across 78. Therefore, the oil 6 flows out into the back pressure chamber 29 having a pressure lower than that of the high pressure chamber 30 (= the back pressure chamber 29 is maintained at an intermediate pressure between the high pressure and the suction pressure) due to the pressure difference.

  That is, the back pressure chamber side opening end 55-1b of the first path 55-1 travels through the seal member 78 depending on the crank angle, so that the non-communication state and the communication state of the high pressure region 30 and the back pressure chamber 29 are changed. repeat. Therefore, since the amount of oil 6 supplied to the back pressure chamber 29 and thus to the inner compression chamber 15b can be reduced, the adjustment range of the oil supply amount to the inner compression chamber 15b can be widened. An increase in viscosity loss due to the excessive supply of oil 6 into the chamber 15b can be suppressed, and the efficiency of the compressor can be improved. In addition, since the adjustment range of the oil 6 flowing into the back pressure chamber 29 is widened and the back pressure can be reduced, the pressing force of the orbiting scroll 13 against the fixed scroll 12 can be reduced, and the thrust surface 13d of the orbiting scroll 13 and the orbiting can be reduced. The sliding loss at the wrap tip 13c of the scroll 13 can be alleviated, and the efficiency of the compressor can be improved. Further, even when the second path 55-2 does not communicate with the back pressure chamber 29 and the inner compression chamber 15b during the one rotation of the crankshaft, the first path 55-1 is intermittently communicated. Thus, an excessive increase in back pressure can be suppressed, and the reliability of the compression mechanism 2 can be improved. Further, since the amount of oil flowing from the high pressure region 30 into the back pressure chamber 29 can be controlled by the communication time, it is not necessary to provide a throttle portion for adjusting the oil amount in the first path 55-1 and foreign matter is present in the throttle portion. The trouble of biting can be avoided and the reliability of the compression mechanism 2 can be improved.

Next, the oil 6 flowing into the back pressure chamber 29 is compressed in the second path 55-2 from the back pressure chamber side opening end 55-2a of the second path 55-2 through the second path 55-2. It reaches the chamber side opening end 55-2b. Further, the air flows through the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85 provided in the fixed scroll 12 and flows into the inner compression chamber 15b and the outer compression chamber 15a.

  At the crank angle shown in FIG. 2 (the crank angle in FIG. 5C), the compression chamber side opening end 55-2b of the second path 55-2 is in communication with the inner compression chamber communication recess 84, and the inner compression is performed. Oil 6 is supplied to the chamber 15b.

  On the other hand, at the crank angle shown in FIG. 3 (the crank angle in FIG. 5A), the compression chamber side opening end 55-2b of the second path 55-2 is in communication with the outer compression chamber communication recess 85. The oil 6 is supplied to the outer compression chamber 15a.

  Since the cross-sectional area of the inner compression chamber communication recess 84 is larger than the cross-sectional area of the outer compression chamber communication recess 85, the compression chamber side opening end 55-2b and the inner side of the second path 55-2 accompanying the turning of the orbiting scroll 13 are included. The opening time of the compression chamber communication recess 84 is longer than the opening time of the outer compression chamber communication recess 85. Therefore, the amount of oil supplied to the inner compression chamber 15b is larger than the amount of oil supplied to the outer compression chamber 15a, and oil can be positively supplied to the outer compression chamber 15b having a large pressure increase rate. The leakage of the working fluid from the chamber 15b-1 to the inner compression chamber 15b-2 formed next can be suppressed.

  Therefore, in both the inner compression chamber 15b and the outer compression chamber 15a, the spiral wrap side surface gap D2 between the compression chamber 15 that previously closed the working fluid and the compression chamber 15 that next closed the working fluid. It is possible to effectively suppress the leakage of the working fluid from the cylinder, and to suppress a decrease in compression efficiency due to recompression.

  The amount of oil supplied from the high pressure region 30 to the back pressure chamber 29 can be controlled by changing the cross-sectional area and the opening position of the back pressure chamber side opening end 55-1b of the first path 55-1, and the back pressure chamber. The amount of oil supply from 29 to the inner compression chamber 15b and the outer compression chamber 15a is the sectional area of the second path 55-2 and the sectional area of the compression chamber side opening end 55-2b of the second path 55-2. It can be controlled by changing.

  5B and 5D, the compression chamber side opening end 55-2b of the second path 55-2 communicates with the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85. Therefore, neither the inner compression chamber 15b nor the outer compression chamber 15a is refueled. Therefore, an increase in viscosity loss due to excessive oil supply can be suppressed, and the efficiency of the compressor can be improved.

  The amount of oil supply in the inner compression chamber 15b and the outer compression chamber 15a is controlled by the size of the cross-sectional areas of the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85. The amount of oil supply may be controlled by changing the depth and position of the outer compression chamber communication recess 85.

(Embodiment 2)
6 and 7 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the second embodiment of the present invention. 6 shows internal communication, and FIG. 7 shows external communication. 6 and 7, the oil supply to the compression chamber 15 is the same as that of the first embodiment except for the compression chamber side opening end of the second path 55-2, and therefore the same components as those in FIG. Only the description about the compression chamber side opening end of the second path 55-2 will be given, and the others will be omitted.

As shown in FIG. 6, in the present embodiment, the compression chamber side opening end of the second path 55-2 is constituted by an inner compression chamber side opening end 55-2c and an outer compression chamber side opening end 55-2d. ing. The oil 6 that has flowed into the back pressure chamber 29 passes through the second path 55-2 from the back pressure chamber side opening end 55-2a of the second path 55-2, and reaches the inner compression chamber side of the second path 55-2. It is distributed to the opening end 55-2c and the outer compression chamber side opening end 55-2d.

  At the crank angle shown in FIG. 6 (the crank angle in FIG. 8C), the inner compression chamber side opening end 55-2c of the second path 55-2 is in communication with the inner compression chamber 15b, and the inner compression chamber Oil 6 is supplied to 15b.

  On the other hand, at the crank angle shown in FIG. 7 (the crank angle in FIG. 8A), the outer compression chamber side opening end 55-2d of the second path 55-2 is in communication with the outer compression chamber 15a, and the outer side Oil 6 is supplied to the compression chamber 15a.

  Since the sectional area of the inner compression chamber side opening end 55-2c is larger than the sectional area of the outer compression chamber side opening end 55-2d, the amount of oil supplied to the inner compression chamber 15b becomes larger than the amount of oil supplied to the outer compression chamber 15a. The oil can be positively supplied to the outer compression chamber 15b having a large pressure increase speed, and the working fluid can be transferred from the inner compression chamber 15b-1 formed one before to the inner compression chamber 15b-2 formed next. Leakage can be suppressed.

  Therefore, in both the inner compression chamber 15b and the outer compression chamber 15a, the spiral wrap side surface gap D2 between the compression chamber 15 that previously closed the working fluid and the compression chamber 15 that next closed the working fluid. It is possible to effectively suppress the leakage of the working fluid from the cylinder, and to suppress a decrease in compression efficiency due to recompression.

  The amount of oil supplied from the back pressure chamber 29 to the inner compression chamber 15b and the outer compression chamber 15a depends on the cross-sectional area of the second path 55-2 and the inner compression chamber side opening end 55-2c of the second path 55-2. It is possible to control by changing the cross-sectional area of the outer compression chamber side opening end 55-2d.

  8B and 8D, the inner compression chamber side opening end 55-2c and the outer compression chamber side opening end 55-2d of the second path 55-2 are wrapped with the fixed scroll 12. Since it is blocked by the tip, it does not communicate with the inner compression chamber 15b or the outer compression chamber 15a, so that neither the inner compression chamber 15b nor the outer compression chamber 15a is refueled. Therefore, an increase in viscosity loss due to excessive oil supply can be suppressed, and the efficiency of the compressor can be improved.

(Embodiment 3)
9 and 10 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the third embodiment of the present invention. FIG. 9 shows internal communication and FIG. 10 shows external communication. 9 and 10, the oil supply to the suction chamber 86 is the same as that of the first embodiment except for the third path 55-3. Therefore, the same reference numerals are used for the same components as in FIG. Only the route 55-3 will be described and the others will be omitted.

  As shown in FIG. 9, in the present embodiment, a third path 55-3 is provided. One end of the third path 55-3 is a back pressure chamber side opening end 55-3 a and always faces the back pressure chamber 29. The other end is a suction chamber side opening end 55-3b, which is provided on the upper surface of the orbiting scroll 13 and faces the suction chamber 86 through a counterbore 87 at all times.

  The oil 6 that has flowed into the back pressure chamber 29 passes from the back pressure chamber side opening end 55-3a of the third path 55-3 through the third path 55-3, and then into the suction chamber side of the third path 55-3. It flows into the suction chamber 86 through the counterbore 87 from the open end 55-3b.

Also in FIGS. 9 and 10, that is, at all crank angles shown in FIGS. 11A to 11D, the suction chamber side open end 55-3b of the third path 55-3 is always in communication with the suction chamber 86. The oil 6 is always supplied to the suction chamber 86. Therefore, the oil 6 is always in the suction chamber 86.
Since the oil 6 serves as a seal and the leakage of the working fluid in the suction stroke of the compression chamber (= suction chamber 86) communicating with the suction can be reduced and the volumetric efficiency can be improved, Efficiency can be improved.

  The amount of oil supplied from the back pressure chamber 29 to the suction chamber 86 depends on the cross-sectional area of the third path 55-3, the cross-sectional area of the back pressure chamber-side opening end 55-3a, and the cross-sectional area of the suction chamber-side opening end 55-3b. Further, it can be controlled by changing the opening position and the cross-sectional area and depth of the counterbore 87. The counterbore 87 may be eliminated.

  Further, as shown in FIG. 12 and FIG. 13, the suction chamber side opening end 55-3b of the third path passes through the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1, and enters the suction chamber 86. It is good also as a structure made to open. In this case, the outer suction chamber 86-2 or the inner suction chamber 86- only at the crank angle at which the suction chamber side open end 55-3b faces the outer suction chamber communication recess 88-2 or the inner suction chamber communication recess 88-1. Since oil 6 is supplied to 1, intermittent oil supply is possible.

  Therefore, the diameter and length of the third path 55-3, the cross-sectional area and opening position of the suction chamber side opening end 55-3b, and the shape of the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 recess. Therefore, the amount of oil supplied to the suction chamber 86 can be controlled by the communication time, so that the adjustment range of the amount of oil 6 supplied to the suction chamber 86 can be expanded, and deterioration of volumetric efficiency due to suction heating can be suppressed. Can be improved.

  In addition, you may comprise an intermittent oil supply path | route by the method shown in Embodiment 2 demonstrated using FIGS.

(Embodiment 4)
14 and 15 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the fourth embodiment of the present invention. FIG. 14 shows internal communication and FIG. 15 shows external communication. 14 and 15, the oil supply to the suction chamber 86 is the same as that of the first embodiment except for the fourth path 55-4. Therefore, the same reference numerals are used for the same components as in FIG. Only the route 55-4 will be described, and the others will be omitted.

  As shown in FIG. 14, in the present embodiment, a fourth path 55-4 is provided. One end of the fourth path 55-4 is a high-pressure region side opening end 55-4 a and always faces the high-pressure region 30. The other end is the suction chamber side opening end 55-4 b, which is provided on the upper surface of the orbiting scroll 13 and faces the suction chamber 86 through the counterbore 87.

  The oil 6 that has flowed into the high pressure region 30 passes through the fourth route 55-4 from the high pressure region side open end 55-4a of the fourth route 55-4 and passes through the suction chamber side open end of the fourth route 55-4. From 55-4b, it flows into the suction chamber 86 through the counterbore 87.

  14 and 15, that is, at all crank angles shown in FIGS. 11A to 11D, the suction chamber side opening end 55-4 b of the fourth path 55-4 is always in communication with the suction chamber 86. The high-pressure oil 6 is always supplied to the suction chamber 86.

  Therefore, by constantly supplying the high-pressure oil 6 to the suction chamber 86, the lubrication performance at the time of high load operation with a large differential pressure is improved, and abnormal wear on the upper surface and side surfaces of the orbiting scroll 13 and the fixed scroll 12 is suppressed. And the reliability of the compressor can be improved.

The amount of oil supplied from the high pressure region 30 to the suction chamber 86 is the cross sectional area of the fourth path 55-4, the cross sectional area of the high pressure region side opening end 55-4a, and the cross sectional area or opening of the suction chamber side opening end 55-4b. Position, counterbore 8
It is controllable by changing the cross-sectional area and depth of 7. The counterbore 87 may be eliminated.

  Further, as shown in FIGS. 16 and 17, the suction chamber side opening end 55-4 b of the fourth path passes through the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 to the suction chamber 86. It is good also as a structure made to open. In this case, the outer suction chamber 86-2 or the inner suction chamber 86- is only at the crank angle at which the suction chamber side opening end 55-4b faces the outer suction chamber communication recess 88-2 or the inner suction chamber communication recess 88-1. Since oil 6 is supplied to 1, intermittent oil supply is possible.

  Therefore, the diameter and length of the fourth path 55-4, the cross-sectional area and opening position of the suction chamber side opening end 55-4b, the shape of the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 recess. Therefore, the amount of oil supplied to the suction chamber 86 can be controlled by the communication time, so that the adjustment range of the amount of oil 6 supplied to the suction chamber 86 can be expanded, and deterioration of volumetric efficiency due to suction heating can be suppressed. Can be improved.

  In addition, you may comprise an intermittent oil supply path | route by the method shown in Embodiment 2 demonstrated using FIGS.

  Finally, when the working fluid is a high-pressure refrigerant, such as carbon dioxide, the operating pressure is particularly high, so the differential pressure during operation also increases, and the working fluid is more likely to leak from the side gaps of the spiral wrap. That is, it is possible to provide a scroll compressor in which the effect of the present invention appears remarkably and achieves high efficiency and high reliability.

  As described above, the scroll compressor according to the present invention effectively and minimally supplies oil to each of the spiral wrap side surface and the wrap tip leakage path in consideration of the leakage path between the compression chambers. Therefore, it is possible to achieve high-efficiency operation with oil sealing suppressed while ensuring sealing performance. Scroll fluid such as air scroll compressor, vacuum pump, scroll type expander, etc. is not limited to refrigerant. It can also be applied to machine applications.

Sectional drawing of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 1 of this invention Sectional drawing in the state which meshed the fixed scroll and turning scroll of the scroll compressor in Embodiment 1 of this invention Sectional drawing in the state which meshed the fixed scroll and turning scroll of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 2 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 2 of this invention Sectional drawing in the state which meshed the fixed scroll and turning scroll of the scroll compressor in Embodiment 2 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 3 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 3 of this invention Sectional drawing in the state which meshed the fixed scroll and turning scroll of the scroll compressor in Embodiment 3 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 3 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 3 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional view of a compression chamber formed with a conventional asymmetric spiral wrap Characteristic diagram showing pressure rise in compression chamber formed by conventional asymmetric spiral wrap

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Compression mechanism 3 Motor part 4 Shaft 4a Eccentric shaft part 6 Oil 11 Main bearing member 12 Fixed scroll 13 Orbiting scroll 13c Orbiting scroll lap tip 13d Orbiting scroll thrust surface 13e Orbiting scroll back surface 14 Rotation restraint mechanism 15 Compression chamber 15a Outer compression chamber 15b Inner compression chamber 16 Suction pipe 17 Suction port 18 Discharge port 19 Reed valve 20 Oil reservoir 25 Pump 26 Oil supply hole 29 Back pressure chamber 30 High pressure region 55-1 First path 55-1a First path High pressure region side open end 55-1b Back pressure chamber side open end of first path 55-2 Second path 55-2a Back pressure chamber side open end of second path 55-2b Compression of second path Chamber side opening end 55-2c Inner compression chamber side opening end 55-2d Outer compression chamber side opening end 55-3 Third path 55 3a Back pressure chamber side opening end 55-3b Suction chamber side opening end 55-4 Fourth path 55-4a High pressure region side opening end 55-4b Suction chamber side opening end 66 Bearing portion 78 Seal member 84 Inner compression chamber communication recess 85 Outer compression chamber communication recess 86 Suction chamber 87 Counterbore 88-1 Inner suction chamber communication recess 88-2 Outer suction chamber communication recess

Claims (10)

A fixed scroll where a spiral wrap rises from the end plate, and a revolving scroll are meshed with each other, and a compression chamber is provided between the both, and the compression chamber is formed outside the revolving scroll wrap and inside the revolving scroll. The inner compression chamber is formed, the suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber, a high pressure region and a back pressure chamber are formed on the back of the orbiting scroll, and the orbiting scroll is circular. By turning with a predetermined turning radius along the trajectory, the compression chamber moves toward the center while changing the volume, sucks the working fluid from the suction port formed in the fixed scroll, and is confined in the compression chamber. After that, the scroll compressor performs a series of operations of compression and discharge, and is connected to the first path connecting the high pressure region and the back pressure chamber, the back pressure chamber and the suction port. A second path connecting the compression chambers not to be opened, and the compression chamber side opening end of the second path is intermittently opened to the outer compression chamber and the inner compression chamber, and the total oil supply to the inner compression chamber A scroll compressor whose amount is larger than the total amount of oil supplied to the outer compression chamber. The compression chamber side opening end of the second path is provided on the wrap upper surface of the orbiting scroll, and the compression chamber side opening end is intermittently provided in a recess provided on the wrap end plate surface of the fixed scroll in accordance with the orbiting motion of the orbiting scroll. The scroll compressor according to claim 1, wherein the scroll compressor is opened. A plurality of compression chamber-side opening ends of the second path are provided on the wrap end plate surface of the orbiting scroll, and the compression chamber-side opening end corresponds to the wrap upper surface of the compression chamber and the fixed scroll and the compression as the orbiting scroll turns. The scroll compressor according to claim 1, wherein the chamber is intermittently opened to the compression chamber by periodically moving between the chamber and a thrust surface of the fixed scroll. The back pressure chamber side opening end of the first path is a high pressure region provided on the back surface of the orbiting scroll and a seal member that partitions the back pressure chamber. 4. Scroll compressor. The scroll compressor according to any one of claims 1 to 4, further comprising a third path that connects the back pressure chamber and a compression chamber communicating with the suction port. The scroll compressor according to any one of claims 1 to 4, further comprising a fourth path connecting the high-pressure region and a compression chamber communicating with the suction port. The scroll compressor according to claim 5 or 6, wherein the compression chamber side opening ends of the third and fourth paths are provided on the upper surface of the orbiting scroll wrap. The compression chamber side opening ends of the third and fourth paths are provided on the upper surface of the orbiting scroll wrap, and the compression chamber side opening ends are provided on the wrap end plate surface of the fixed scroll in accordance with the orbiting motion of the orbiting scroll. The scroll compressor according to claim 5 or 6, wherein the scroll compressor is intermittently opened. A plurality of compression chamber side opening ends of the third and fourth paths are provided on the wrap end plate surface of the orbiting scroll, and the compression chamber side opening end is the upper surface of the wrap between the compression chamber and the fixed scroll in accordance with the orbiting motion of the orbiting scroll. The scroll compressor according to claim 5 or 6, wherein the compressor is intermittently opened to the compression chamber by periodically moving the thrust surfaces of the compression chamber and the fixed scroll. The scroll compressor according to any one of claims 1 to 9, wherein the working fluid is a high-pressure fluid such as carbon dioxide.