JP5771739B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor.

  As background art in this technical field, there is JP-A-9-228968 (Patent Document 1). According to this publication, “a hole having a high-pressure hydraulic chamber and a low-pressure chamber on the rear plate portion of the orbiting scroll through a seal portion and having a hole diameter equal to or smaller than the seal ring width of the seal portion on the rear plate portion of the orbiting scroll. As the orbiting scroll having the hole revolves, oil in the hydraulic chamber accumulates in the hole, and oil leakage means is configured to be discharged on the low pressure chamber side across the seal ring. (Refer to claim 1).

  There exists Unexamined-Japanese-Patent No. 2011-58439 (patent document 2) as another background art. In this publication, “a small hole is provided in the back part or frame of the orbiting scroll facing the sealing means, and this small hole straddles the sealing means with the orbiting movement of the orbiting scroll, on the high pressure hydraulic chamber side and the back pressure chamber side. It is provided on the orbiting scroll or frame so that the oil in the high pressure hydraulic chamber is supplied to the back pressure chamber side so as to open alternately, and the high pressure hydraulic chamber and the back pressure chamber are connected to each other to increase the pressure. The scroll compressor includes an oil supply passage that supplies oil in the hydraulic chamber to the back pressure chamber side (see claim 1).

JP-A-9-228968 JP 2011-58439 A

  Since both Patent Documents 1 and 2 supply oil to the back pressure chamber by the differential pressure between the back pressure chamber and the discharge pressure space, the pressure in the discharge pressure space becomes small under low pressure ratio conditions. There is a possibility that the back pressure and the discharge pressure become equal, and the oil supply from the discharge pressure space to the back pressure chamber cannot be performed. If oil cannot be supplied to the back pressure chamber in this way, the sliding part of the Oldham ring cannot be lubricated, the amount of oil required for sealing the compression chamber cannot be secured, leakage loss increases, and the compressor efficiency increases. descend. Therefore, an object of the present invention is to provide a highly reliable scroll compressor that can supply oil to the back pressure chamber even under low pressure ratio conditions.

In order to solve the above problems, for example, the configuration described in the claims is adopted.
The present application includes a plurality of means for solving the above-mentioned problems. For example, “a fixed side flat plate portion and a first lap that is erected while maintaining a spiral shape on one surface of the fixed side flat plate portion. And a second scroll and a first lap. The second wrap and the first lap And a revolving scroll that forms a compression chamber by revolving with respect to the fixed scroll, and presses the revolving scroll against the fixed scroll on the back side of the revolving scroll. In the scroll compressor in which the back pressure chamber is formed, the back pressure chamber or back pressure hole for adjusting the pressure of the back pressure chamber, and the back pressure chamber from the discharge pressure space from which the compressed refrigerant from the compression chamber is discharged First oil supply means for supplying oil and second oil supply means for supplying oil from the back pressure chamber to the compression chamber or a suction chamber formed on the suction side of the compression chamber are provided. It is characterized by.

  According to the present invention, it is possible to supply the back pressure chamber even under a low pressure ratio condition and to provide a highly reliable scroll compressor.

The longitudinal cross-sectional view of the scroll compressor of a present Example. The figure which shows the slit provided in the turning scroll boss | hub part. The figure which shows the oil hole provided in the turning scroll boss | hub part. The enlarged view of a back pressure valve. The enlarged view of a back pressure hole. The top view showing the meshing state of a fixed scroll and a turning scroll. The figure which shows the slit provided in the turning scroll end plate surface. The conceptual diagram of the refrigerating cycle which shows a present Example.

  Hereinafter, examples will be described with reference to the drawings.

The present embodiment relates to a scroll compressor suitable as a refrigerant compressor used in a refrigeration cycle for refrigeration or air conditioning, or a gas compressor for compressing air or other gas. First, the basic structure of the scroll compressor will be described.
FIG. 1 is a longitudinal sectional view of the scroll compressor of this embodiment. As shown in the figure, the fixed scroll (fixed scroll member) 7 includes a disk-shaped fixed-side flat plate portion 7a (base plate) and a first wrap erected in a spiral shape on the fixed-side flat plate portion 7a. 7b and a cylindrical support portion 7d that is located on the outer peripheral side of the fixed-side flat plate portion 7a, has a mirror plate surface that is continuous with the tip surface of the first wrap 7b, and surrounds the first wrap 7b.

  The surface of the fixed-side flat plate portion 7a on which the first wrap 7b is erected is called a tooth bottom 7c because it is between the first wrap 7b. The surface of the support portion 7 d that contacts the orbiting flat plate portion 8 a (end plate) of the orbiting scroll (orbiting scroll member) 8 is an end plate surface 7 e of the fixed scroll 7. The support portion 7d of the fixed scroll 7 is fixed to the frame 17 by bolts or the like, and the frame 17 integrated with the fixed scroll 7 is fixed to the case (sealed container) 9 by fixing means such as welding.

  The orbiting scroll 8 is disposed so as to face the fixed scroll 7, and the first scroll wrap 7 b and the second orbiting scroll second wrap 8 b are engaged with each other, and are provided in the frame 17 so as to be orbitable. The orbiting scroll 8 includes a disc-shaped orbiting side flat plate portion 8a, a second wrap 8b that stands upright from a tooth bottom 8c that is the surface of the orbiting side flat plate portion 8a, and an orbiting side flat plate portion 8a. And a boss portion 8d provided at the center of the back surface of the head. Further, the surface of the outer peripheral portion of the orbiting flat plate portion 8 a that contacts the fixed scroll 7 is the end plate surface 8 e of the orbiting scroll 8. The compression chamber 13 is formed by revolving with respect to the fixed scroll 7 while the second wrap 8b and the first wrap 7b mesh with each other.

  The case 9 has a sealed container structure in which a scroll unit including the fixed scroll 7 and the orbiting scroll 8, a motor unit 16 (16a: rotor, 16b: stator), lubricating oil, and the like are housed. A shaft (rotary shaft) 10 fixed integrally with the rotor 16 a of the motor unit 16 is rotatably supported by the frame 17 via the main bearing 5, and is coaxial with the central axis of the fixed scroll 7.

  A crank portion 10 a is provided at the tip of the shaft 10, and the crank portion 10 a is inserted into the orbiting bearing 11 provided on the boss portion 8 d of the orbiting scroll 8. The orbiting scroll 8 can be orbited as the shaft 10 rotates. It is configured. The center axis of the orbiting scroll 8 is decentered by a predetermined distance with respect to the center axis of the fixed scroll 7. The second wrap 8b of the orbiting scroll 8 is overlapped with the first wrap 7b of the fixed scroll 7 while being shifted by a predetermined angle in the circumferential direction. Reference numeral 12 denotes an Oldham ring for causing the orbiting scroll 8 to relatively rotate with respect to the fixed scroll 7 while restraining it from rotating.

  FIG. 6 is a plan view showing the meshing state of the fixed scroll and the orbiting scroll. As shown in the figure, a plurality of crescent-shaped compression chambers 13 (13a, 13b) are formed between the first wraps 7b, 8b. When the orbiting scroll 8 is orbited, the volume of each compression chamber is continuously reduced as it moves to the center. That is, the orbiting extension side compression chamber 13a and the orbiting outside line side compression chamber 13b are formed on the inner line side and the outer line side of the second wrap 8b of the orbiting scroll 8, respectively. Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 when the phase of the orbiting motion of the orbiting scroll 8 advances and the closing of the fluid is completed.

  As shown in FIGS. 1 and 6, the suction port 14 is provided in the fixed scroll 7. The suction port 14 is formed on the outer peripheral side of the fixed-side flat plate portion 7 a so as to communicate with the suction chamber 20. Further, the discharge port 15 is formed near the spiral center of the fixed-side flat plate portion 7a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost peripheral side.

  When the shaft 10 is rotationally driven by the motor unit 16, it is transmitted from the crank portion 10 a of the shaft 10 to the orbiting scroll 8 via the orbiting bearing 11, and the orbiting scroll 8 has a turning radius of a predetermined distance around the center axis of the fixed scroll 7. Rotate with. It is restrained by the Oldham ring 12 so that the turning scroll 8 does not rotate during this turning movement.

  By the orbiting motion of the orbiting scroll 8, the compression chamber 13 formed between the first wrap 7b and the second wrap 8b continuously moves to the center, and the volume of the compression chamber 13 is continuously reduced according to the movement. As a result, the fluid sucked from the suction port 14 (for example, refrigerant gas circulating in the refrigeration cycle) is sequentially compressed in each compression chamber 13, and the compressed fluid is discharged from the discharge port 15 to the discharge space 54 above the case. Is done. The discharged fluid enters the motor chamber 52 in the case 9 from the discharge space 54 and is supplied from the discharge pipe 6 to the outside of the compressor, for example, to the refrigeration cycle.

  Lubricating oil is stored at the bottom of the case 9, and a positive displacement or centrifugal oil pump 21 is provided at the lower end of the shaft 10. The oil pump 21 is also rotated with the rotation of the shaft, and the lubricating oil is sucked from the lubricating oil suction port 25 provided in the oil pump case 22 and discharged from the discharge port 28 of the oil pump. The discharged lubricating oil is supplied to the upper portion through a through hole 3 provided in the shaft. A portion of the lubricating oil lubricates the auxiliary bearing 23 through the lateral hole 24 provided in the shaft 10 and returns to the oil reservoir 53 at the bottom of the case. Most of the other lubricating oil passes through the through hole 3 and reaches the upper portion of the crank portion 10a of the shaft 10, and lubricates the slewing bearing 11 through an oil groove 57 provided in the crank portion 10a. And after lubricating the main bearing 5 provided in the lower part of the slewing bearing 11, it returns to a case bottom part through the oil drain hole 26a and the oil drain pipe 26b. Here, the space formed by the oil groove 57 and the orbiting bearing 11 and the space for housing the main bearing 5 (the frame 17, the shaft 10, the frame seal 56, the collar-shaped orbiting boss provided on the boss portion 8d of the orbiting scroll 8). The space formed by the member 34 and the seal member 32) will be collectively referred to as a first space 33. The first space 33 is a space having a pressure close to the discharge pressure. Most of the lubricating oil flowing into the first space 33 for lubrication of the main bearing 5 and the slewing bearing 11 returns to the bottom of the case through the oil drain hole 26a and the oil drain pipe 26b. The minimum amount necessary for lubrication of the Oldham ring 12 and lubrication and sealing of the sliding portion between the fixed scroll 7 and the orbiting scroll 8 is the first amount between the upper end surface of the seal member 32 and the end surface of the orbiting boss member 34. Enters the back pressure chamber 18 as the second space through the oil supply means.

The seal member 32 is inserted into an annular groove 31 provided in the frame 17 together with a wave spring (not shown), and has a first space 33 serving as a discharge pressure and an intermediate between the suction pressure and the discharge pressure. It partitions the back pressure chamber 18 that is in pressure.
As shown in FIG. 2, the first oil supply means is composed of one or a plurality of first slits 60 provided in the turning boss member 34 and the seal member 32, and the first slit 60 is a seal member. 32 so as to straddle 32. That is, the first oil supply means is constituted by a first slit provided on the surface of the orbiting scroll 8 opposite to the fixed scroll 7, and the first slit is connected to the discharge pressure space (54, 52, 33) and the back. The pressure chamber 18 is always in communication. As a result, due to the pressure difference between the first space 33 and the back pressure chamber 18, oil flows from the first space 33 into the back pressure chamber 18 through the first slit 60 that is a minute gap.

  The arrangement of the first slit 60 does not always straddle the seal member 32 but may straddle intermittently with the orbiting motion of the orbiting scroll 8. That is, the first slit 60 may be configured to intermittently communicate the discharge pressure space (54, 52, 33) and the back pressure chamber 18 with the turning of the orbiting scroll 8.

  As shown in FIG. 3, another first oil supply means includes, for example, a plurality of holes 30 provided in the orbiting boss member 34 and the seal member 32, and the plurality of holes 30 are formed in the orbiting scroll 8. A circular motion across the seal member 32 is performed along with the swivel motion, and the space moves between the first space 33 and the back pressure chamber 18. As a result, the lubricating oil in the first space 33 is accumulated in the hole 30, intermittently transferred to the back pressure chamber 18 and discharged, whereby the minimum necessary oil can be guided to the back pressure chamber 18.

  When the back pressure increases, the lubricating oil that has entered the back pressure chamber 18 passes through the back pressure valve 61 that connects the back pressure chamber 18 and the suction chamber 20 (or the compression chamber 13), and then the suction chamber 20 (or the compression chamber 13). And discharged from the discharge port 15. Part of the oil discharged from the discharge port 15 is discharged together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, for example, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 at the bottom of the case.

  As described above, by providing the first space 33, the back pressure chamber 18 and the first oil supply means, the amount of oil required for each bearing portion and the amount of oil required for the compression chamber can be independently set. Since it can be controlled, the amount of oil supplied to the compression chamber can be optimized, and a highly efficient compressor can be obtained. Further, as another configuration, the oil supply pump 21, the first space 33, and the first oil supply means are not provided, and the oil in the oil reservoir 53, which is the discharge pressure, is used by using the restriction in the minute gap of the bearing portion. The structure may be such that the pressure is reduced and introduced into the back pressure chamber. In this case, since all of the oil that has passed through the bearing portion enters the back pressure chamber, the amount of oil supplied to the bearing portion and the compression chamber cannot be controlled independently, but components such as the oil pump 21 and the seal member 32 are not required. Thus, a compressor having a simple structure and a low cost can be provided.

  Next, the details of the back pressure will be described. In the scroll compressor, an axial force for separating the fixed scroll 7 and the orbiting scroll 8 from each other is generated by the compression action. If the so-called orbiting scroll 8 separation phenomenon occurs in which both scrolls are separated by this axial force, the sealing performance of the compression chamber deteriorates and the efficiency of the compressor decreases. Therefore, a back pressure chamber 18 serving as a pressure between the discharge pressure and the suction pressure is provided on the back side of the orbiting flat plate portion of the orbiting scroll 8, the separation force is canceled by the back pressure, and the orbiting scroll 8 is fixedly scrolled. 7 to press. At this time, if the pressing force is too large, sliding loss between the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 increases, and the compressor efficiency decreases. That is, there is an optimum value for the back pressure, and if it is too small, the sealing performance of the compression chamber deteriorates and the thermal fluid loss increases, and if it is too large, the sliding loss increases. Therefore, maintaining the back pressure at an optimum value is important in improving the performance and reliability of the compressor.

In order to obtain this optimum back pressure value, the scroll compressor of FIG. 1 includes a back pressure valve 61.
As shown in FIG. 4, the back pressure valve 61 includes a space 61 a that communicates with the back pressure chamber 18 and a space 61 c that communicates with the suction chamber 20 (or the compression chamber 13) through a communication path 61 b provided in the fixed scroll 7. The valve 61d is arranged so as to partition the two spaces. The valve 61d is pressed against the opening communicating with the space 61a by a spring 61f which is an elastic body fixed by a stopper 61e. The valve 61d has a pressure corresponding to the pressure in the suction chamber 20 (or the compression chamber 13) in the space 61c into which the pressure in the space 61a, that is, the back pressure is introduced through the communication passage 61b, and the pressing force of the spring 61f. When higher than the total, the space 61a and the space 61c are communicated by moving upward. That is, when the pressure in the back pressure chamber 18 becomes higher than a certain value, the back pressure valve 61 releases the fluid in the back pressure chamber 18 to the suction chamber 20 or the compression chamber 13, thereby setting the back pressure to an appropriate value. To be adjusted. The back pressure value in the back pressure valve 61 is “suction pressure + α (pressure corresponding to the pressing force of the spring 61 f)”.

In order to obtain an optimal back pressure value, the back pressure hole 35 may be used instead of the back pressure valve 61.
As shown in FIG. 5, the back pressure hole 35 is a U-shaped passage, and communicates the compression chamber 13 and the back pressure chamber 18 to introduce pressure corresponding to the compression chamber pressure into the back pressure chamber 18. The pressure in the compression chamber 13 increases as the crankshaft rotates. The back pressure value is determined depending on which section of the compression chamber 13 in the middle of compression communicates with the back pressure chamber 18. Therefore, the optimal back pressure value can be set by adjusting the communication section. The back pressure value in the back pressure hole 35 is “suction pressure × β (compression ratio determined by the communication section with the compression chamber 13)”.

  The above is the basic structure of the scroll compressor. A demerit of this structure is that oil cannot be supplied to the back pressure chamber 18 when the back pressure becomes equal to or higher than the discharge pressure under low pressure ratio conditions. Under the low pressure ratio condition, the difference between the discharge pressure and the suction pressure is small. The value of the back pressure is determined by the back pressure valve 61 or the back pressure hole 35 as described above, and is represented by “suction pressure + α” and “suction pressure × β”, respectively. When the difference between the discharge pressure and the suction pressure under the low pressure ratio condition is small, the back pressure value represented by these equations may be equal to or greater than the discharge pressure. At this time, there is no oil supply differential pressure between the first space 33 and the back pressure chamber 18, and oil supply to the back pressure chamber 18 through the first slit 60 or the oil transfer hole 30 becomes impossible.

  If the back pressure chamber 18 cannot be refueled, the reliability decreases due to poor lubrication of the sliding portion of the Oldham ring 12. Moreover, since there is no oil supplied to the compression chamber 13 via the back pressure chamber 18, the sealing property of the compression chamber 13 is lowered, leakage loss is increased, and the efficiency of the compressor is lowered.

  Therefore, as shown in FIG. 7, in the present embodiment, one or a plurality of second slits 62 are provided on the end plate surface 8e of the orbiting scroll or the end plate surface 7e of the fixed scroll to serve as the second oil supply means. That is, in addition to the first oil supply means (first slit 60) for supplying oil from the discharge pressure space (54, 52, 33) from which the compressed refrigerant from the compression chamber 13 is discharged to the back pressure chamber 18, A second oil supply means (second slit 62) for supplying oil from the back pressure chamber 18 to the position of the compression chamber 13 at the initial stage of compression or to the suction chamber 20 formed on the suction side to the compression chamber 13; Is provided.

  More specifically, the second oil supply means is configured by a second slit 62 provided on one surface of the turning-side flat plate portion 8a or one surface of the fixed-side flat plate portion 7a, and the second slit 62 is a back pressure chamber. 18 and the compression chamber 13 at the initial compression position or the suction chamber are always in communication. Alternatively, the second slit 62 may be provided so as to intermittently communicate the back pressure chamber 18 and the compression stage 13 position of the compression chamber 13 or the suction chamber 20 with the turning of the orbiting scroll 8. By being configured in this way, it is arranged so as to communicate with the suction chamber 20 constantly or intermittently, and the oil is allowed to flow from the back pressure chamber 18 to the suction chamber 20 (or the position of the compression chamber 13 in the initial stage of compression). As a result, the back pressure decreases, and the oil flows into the back pressure chamber 18 from the first space 33 by the amount of the oil flowing into the suction chamber 20. Instead of the second slit 62, a hole for oil transfer may be provided.

  Here, when the back pressure hole 35 is adopted as the pressure adjusting means of the back pressure chamber 18, the back pressure hole 35 is formed on the back pressure chamber 18 and the compression chamber 13 or the suction side of the compression chamber as shown in FIG. The suction chamber 20 is communicated constantly or intermittently, and the optimum back pressure value is set by adjusting the communication section as described above. However, under the low pressure ratio condition, as described above, the pressure “suction pressure × β (compression ratio determined by the communication section with the compression chamber 13)” of the back pressure chamber 18 becomes high and becomes equal to the discharge pressure space. For this reason, there is a possibility that oil cannot be supplied to the back pressure chamber by the first oil supply means (first slit 60).

  Therefore, in this embodiment, the position where the oil is supplied to the compression chamber 13 or the back pressure chamber 18 by the second oil supply means (second slit 62) is the position where the oil is communicated with the compression chamber 13 or the back pressure chamber 18 by the back pressure hole 35. Since the pressure in the back pressure chamber 18 can be relieved by setting it to the outer peripheral side (suction side), the pressure in the back pressure chamber 18 is lowered thereby, and the back pressure by the first oil supply means (first slit 60) is reduced. Allows oil supply to the chamber. The cross-sectional area of the oil supply flow path of the second oil supply means (second slit 62) is preferably smaller than the cross-sectional area of the oil supply flow path of the back pressure hole 35.

  In general, a minute gap exists between the fixed scroll end plate surface 7e and the orbiting scroll end plate surface 8e, and oil leakage from the back pressure chamber 18 to the suction chamber 20 or the compression chamber 13 occurs in this flow path. ing. In consideration of oil leakage on the end plate surface, the flow resistance of the second slit 62 or the oil transfer hole is equal to the flow resistance of the first slit 60 or the oil transfer hole 30 provided in the swivel boss member 34. It is better to make it larger, and in this case, problems such as abnormal reduction in back pressure can be suppressed. Since the flow path resistance is greatly influenced by the depth of the slit, for example, the depth of the second slit 62 provided on the orbiting scroll end plate surface 8e is greater than the depth of the first slit 60 provided on the orbiting boss member 34. What is necessary is just to set so that it may become shallow.

  Further, the first slit 60 of the orbiting boss member 34 is provided so as to intermittently communicate the first space 33 and the back pressure chamber 18 with the orbiting motion of the orbiting scroll 8, and the second slit of the orbiting scroll end plate surface 8e. 62 is also provided intermittently so that the back pressure chamber 18 and the suction chamber 20 (or the compression chamber 13) communicate with each other, and the sections where the slits communicate with each other are preferably equalized. In other words, the intermittent communication timings of the first slit 60 and the second slit 62 are made the same. For example, when the orbiting scroll 8 is orbitally rotated 360 degrees, the slit depth can be deepened with respect to the slits that always communicate with 360 degrees by providing each of the slits to communicate with each space only 90 degrees. This makes it possible to suppress clogging of foreign matter in the slit and to simplify the processing. Furthermore, in the above example, if the communication start angle (phase) when the first slit 60 and the second slit 62 communicate with each other by 90 degrees is matched, the oil flows into and out of the back pressure chamber 18 almost simultaneously. Therefore, it is possible to keep back pressure fluctuations small.

  In addition, when using the back pressure hole 35 as a back pressure adjusting mechanism, when the back pressure is reduced by providing the second slit 62, in addition to the oil flowing into the back pressure chamber 18 from the first space 33, Since the pressure difference between the compression chamber 13 and the back pressure chamber 18 also increases and the refrigerant gas and oil flow into the back pressure chamber 18 through the back pressure hole 35, the effect of this embodiment uses the back pressure valve 61. Smaller than if When the back pressure valve 61 is used, even when the back pressure is reduced, the back pressure valve 61 serves as a check valve. Therefore, the back pressure is increased only by the inflow of oil from the first space 33 to the back pressure chamber 18. As a result, the effect of the present embodiment is increased.

  As shown in FIG. 8, the scroll compressor 1 described above includes a condenser 40 that condenses the refrigerant compressed by the scroll compressor 1, and a decompression unit (expansion) that decompresses the refrigerant condensed by the condenser 40. By adopting a refrigeration cycle apparatus comprising a valve 41), an evaporator 42 for evaporating the refrigerant depressurized by the depressurizing means (expansion valve 41), and an air blowing means for blowing air to the evaporator 42. Therefore, it is possible to provide an easy-to-use air conditioner with low power consumption throughout the year and a wide operation range.

3 through hole 5 main bearing 6 discharge pipe 7 fixed scroll (7a: fixed flat plate portion, 7b: first lap, 7c: tooth bottom, 7d: support portion, 7e: end plate surface)
8 orbiting scroll (8a: orbiting side flat plate portion, 8b: second lap, 8c: tooth bottom, 8d: boss portion, 8e: end plate surface)
9 Case (sealed container)
10 Shaft (Rotating shaft) (10a: Crank part)
DESCRIPTION OF SYMBOLS 11 Rotating bearing 12 Oldham ring 13 Compression chamber (13a: Turning inner line side compression chamber, 13b: Turning outer line side compression chamber)
14 Suction port 15 Discharge port 16 Motor part (16a: rotor, 16b: stator)
17 Frame 18 Back pressure chamber 20 Suction chamber 21 Oil pump 23 Sub bearing 30 Hole 32 Seal member 33 First space 34 Revolving boss member 35 Back pressure hole 52 Motor chamber 53 Oil reservoir 54 Discharge space 60 Provided in the orbiting scroll boss portion First slit 61 Back pressure valve (61a: space communicating with back pressure chamber, 61b: communication path, 61c: space communicating with suction chamber or compression chamber, 61d: valve, 61e: stopper, 61f: spring)
62 Second slit provided on orbiting scroll end plate

Claims (11)

A fixed scroll having a fixed-side flat plate portion, and a first wrap that is erected while maintaining a spiral shape on one surface of the fixed-side flat plate portion;
The fixed scroll includes a revolving-side flat plate portion and a second lap that is erected while maintaining a spiral shape on one surface of the revolving-side flat plate portion, and the second wrap and the first wrap are engaged with each other. A revolving scroll that forms a compression chamber by revolving with respect to,
In the scroll compressor in which a back pressure chamber for pressing the orbiting scroll against the fixed scroll is formed on the back side of the orbiting scroll with respect to the fixed scroll,
A back pressure valve or a back pressure hole for adjusting the pressure of the back pressure chamber;
First oil supply means for supplying oil from a discharge pressure space from which the compressed refrigerant from the compression chamber is discharged to the back pressure chamber;
A second oil supply means for supplying oil from the back pressure chamber to the compression chamber or a suction chamber formed on the suction side of the compression chamber;
The second oil supply means is configured by a second slit provided on the one surface of the turning-side flat plate portion or the one surface of the fixed-side flat plate portion,
The scroll compressor is characterized in that the second slit is provided so as to always communicate the back pressure chamber and the compression chamber at the initial compression position or the suction chamber. The scroll compressor according to claim 1, wherein
The back pressure valve communicates the back pressure chamber and a suction chamber formed on the suction side of the compression chamber or the compression chamber when a predetermined condition is satisfied. The scroll compressor according to claim 2,
The back pressure valve has an elastic body,
The scroll compressor according to claim 1, wherein the predetermined condition is when the pressure in the back pressure chamber is higher than the sum of the pressing force of the elastic body and the pressure in the compression chamber or the suction chamber. The scroll compressor according to claim 1, wherein
The back pressure hole communicates the back pressure chamber and the compression chamber or the suction chamber formed on the suction side of the compression chamber constantly or intermittently,
The position where oil is supplied to the compression chamber or the suction chamber by the second oil supply means is on the outer peripheral side than the position communicating with the compression chamber or the suction chamber by the back pressure hole. Compressor. The scroll compressor according to claim 1, wherein
The back pressure hole communicates the back pressure chamber and the compression chamber or the suction chamber formed on the suction side of the compression chamber constantly or intermittently,
The scroll compressor characterized in that a cross-sectional area of the oil supply passage of the second oil supply means is configured to be smaller than a cross-sectional area of the oil supply passage of the back pressure hole. The scroll compressor according to claim 1, wherein
The first oil supply means includes a first slit provided on a surface of the orbiting scroll opposite to the fixed scroll, and the first slit always connects the discharge pressure space and the back pressure chamber. A scroll compressor provided to communicate with each other. The scroll compressor according to claim 1, wherein
The first oil supply means is configured by a first slit or a plurality of holes provided on a surface of the orbiting scroll opposite to the fixed scroll, and the first slit or the plurality of holes is formed by the orbiting scroll. A scroll compressor characterized in that the discharge pressure space and the back pressure chamber are intermittently communicated with each other. A fixed scroll having a fixed-side flat plate portion, and a first wrap that is erected while maintaining a spiral shape on one surface of the fixed-side flat plate portion;
The fixed scroll includes a revolving-side flat plate portion and a second lap that is erected while maintaining a spiral shape on one surface of the revolving-side flat plate portion, and the second wrap and the first wrap are engaged with each other. A revolving scroll that forms a compression chamber by revolving with respect to,
In the scroll compressor in which a back pressure chamber for pressing the orbiting scroll against the fixed scroll is formed on the back side of the orbiting scroll with respect to the fixed scroll,
A back pressure valve or a back pressure hole for adjusting the pressure of the back pressure chamber;
First oil supply means for supplying oil from a discharge pressure space from which the compressed refrigerant from the compression chamber is discharged to the back pressure chamber;
A second oil supply means for supplying oil from the back pressure chamber to the compression chamber or a suction chamber formed on the suction side of the compression chamber;
The scroll compressor characterized in that the flow path resistance of the second oil supply means is larger than the flow path resistance of the first oil supply means. The scroll compressor according to claim 10, wherein
A scroll compressor characterized in that the depth of the slit constituting the second oil supply means is shallower than the depth of the slit constituting the first oil supply means. A fixed scroll having a fixed-side flat plate portion, and a first wrap that is erected while maintaining a spiral shape on one surface of the fixed-side flat plate portion;
The fixed scroll includes a revolving-side flat plate portion and a second lap that is erected while maintaining a spiral shape on one surface of the revolving-side flat plate portion, and the second wrap and the first wrap are engaged with each other. A revolving scroll that forms a compression chamber by revolving with respect to,
In the scroll compressor in which a back pressure chamber for pressing the orbiting scroll against the fixed scroll is formed on the back side of the orbiting scroll with respect to the fixed scroll,
A back pressure valve or a back pressure hole for adjusting the pressure of the back pressure chamber;
First oil supply means for supplying oil from a discharge pressure space from which the compressed refrigerant from the compression chamber is discharged to the back pressure chamber;
A second oil supply means for supplying oil from the back pressure chamber to the compression chamber or a suction chamber formed on the suction side of the compression chamber;
The first oil supply means is configured by a first slit provided on a surface of the orbiting scroll opposite to the fixed scroll, and the first slit is provided in the discharge pressure space along with the orbiting of the orbiting scroll. And the back pressure chamber are provided so as to communicate intermittently,
The second oil supply means is configured by a second slit provided on the one surface of the orbiting side flat plate portion or the one surface of the fixed side flat plate portion, and the second slit is accompanied by the orbiting of the orbiting scroll, A back pressure chamber and the compression chamber or the suction chamber are provided so as to communicate intermittently;
A scroll compressor characterized in that the timing of intermittent communication between the first slit and the second slit is the same. A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
Decompression means for decompressing the refrigerant condensed by the condenser;
An evaporator for evaporating the refrigerant decompressed by the decompression means;
In a refrigeration cycle apparatus comprising a blowing means for blowing air to the evaporator,
A refrigeration cycle apparatus using the scroll compressor according to any one of claims 1 to 7 as the compressor.

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