JP2016145522A - Scroll compressor and air conditioner using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor that make suction heating loss small by supplying oil locally at necessary timing.SOLUTION: A scroll compressor comprises: a closed container; a fixed scroll which is incorporated in the closed container, and has a fixed-side plate part and a fixed-side lap stood on a mirror plate plane side of a fixed-side plate part to stay spiral; and a swivel scroll which has a swivel-side plate part and a swivel-side lap stood on one surface of the swivel-side plate part to stay spiral, and forms a compression chamber as the fixed-side lap and swivel-side lap swivel relative to the fixed scroll while engaging each other. The fixed scroll has an oil supply hole penetrating the fixed scroll to supply oil to the compression chamber, and an oil supply groove not penetrating the fixed scroll, and the swivel scroll has an addendum groove provided to an addendum of the swivel-side lap, the oil supply hole and oil supply groove communicating with each other through the addendum groove within a range of a first crank angle.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a scroll compressor and an air conditioner using the same.

  Patent Document 1 discloses a scroll compressor that supplies oil to both the swirling outer line chamber and the extension chamber before the compression chamber is closed, and supplies oil from the fixed tooth bottom to the compression chamber after the compression chamber is closed. Have been described.

  According to the scroll compressor described in Patent Document 1, it is possible to disperse oil over a wider range and seal many gaps.

Japanese Patent No. 5548586

  However, in the scroll compressor described in Patent Document 1, the inlet (suction area communication path outlet) for refueling the suction chamber is located further away from the end of the orbiting scroll. The hot oil heats the low-temperature suction refrigerant until it reaches the suction chamber formed at the end of the orbiting scroll winding, causing loss.

  In addition, since oil passes through the space that extends from the inlet to the end of the orbiting scroll, it is not possible to guide the oil flow only to the gap between the outermost compression chamber and the suction chamber where oil is really needed. It is difficult, and in order to sufficiently fill the gap with oil, it is unavoidable to supply more than the necessary minimum amount, which causes more heating loss.

  Then, an object of this invention is to provide the scroll compressor which makes suction heat loss small by supplying oil locally at a required timing.

  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. To give an example, a sealed container and a built-in sealed container hold a spiral shape on the fixed side plate and the end plate surface side of the fixed side plate. A fixed scroll having a fixed side wrap, a revolving side plate portion, and a revolving side wrap that is erected while maintaining a spiral shape on one surface of the revolving side plate portion. And a revolving scroll that forms a compression chamber by revolving with respect to the fixed scroll while meshing with the orbiting side wrap, the fixed scroll penetrating the fixed scroll and refueling the compression chamber, and a fixed scroll The orbiting scroll has a tooth tip groove provided at the tooth tip of the orbiting side wrap, and the oil supply hole and the oil supply groove have a tooth tip groove in the range of the first crank angle. Communication through That is a scroll compressor.

  ADVANTAGE OF THE INVENTION According to this invention, the scroll compressor which makes suction heat loss small can be provided by supplying oil locally at a required timing.

1 is a cycle configuration diagram of an air conditioner according to Embodiment 1. FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1. FIG. 3 is a top view of a fixed scroll according to Embodiment 1. FIG. 3 is a top view of the orbiting scroll according to Embodiment 1. FIG. It is explanatory drawing of the oil supply method to the oil supply hole which concerns on Example 1. FIG. It is explanatory drawing of the oil supply method after the oil supply hole which concerns on Example 1. FIG. It is explanatory drawing of the oil supply method to the suction chamber from the tooth tip groove | channel which concerns on Example 1. FIG. It is explanatory drawing in case the oil supply groove | channel which concerns on Example 1 is a rectangular cross section. It is explanatory drawing which showed the state immediately before the turning outside line room which concerns on Example 1 completes a suction stroke. It is the figure which showed the crank angle and volume change which concern on Example 1. FIG. FIG. 6 is a structural diagram of a turning scroll and a fixed scroll according to a second embodiment. FIG. 6 is a structural diagram of a turning scroll and a fixed scroll according to a third embodiment.

  Examples will be described below with reference to the drawings.

  The first embodiment will be described with reference to FIGS. FIG. 1 is a cycle configuration diagram of an air conditioner according to the present embodiment. The air conditioner includes an indoor heat exchanger 101, an outdoor heat exchanger 102, a scroll compressor 1, an expansion valve 104, a four-way valve 105, an indoor blower fan 106, and an outdoor blower fan 107. The compressor 1, the outdoor heat exchanger 102, the outdoor blower fan (propeller fan) 107, and the expansion valve 104 are arranged in the outdoor unit 109 (see FIG. 2), and the indoor heat exchanger 101 and the indoor blower fan 106 are indoor units (see FIG. (Not shown).

  During the cooling operation, the high-temperature and high-pressure refrigerant discharged from the scroll compressor 1 flows into the outdoor heat exchanger 102 via the four-way valve 105. The refrigerant flowing into the outdoor heat exchanger 102 is condensed and becomes liquid refrigerant by exchanging heat with the outdoor air sent by the outdoor fan 107. The liquid refrigerant passes through the expansion valve 104 to become a low-temperature and low-pressure two-phase refrigerant and flows into the indoor heat exchanger 101. The low-temperature and low-pressure two-phase refrigerant that has flowed into the indoor heat exchanger 101 exchanges heat with indoor air sent by the indoor fan 106. At this time, the indoor air sent to the indoor heat exchanger 101 is cooled by the low-temperature and low-pressure two-phase refrigerant that has flowed into the indoor heat exchanger 101, and is discharged into the room through a blowout port (not shown). Since the air discharged into the room from the air outlet (not shown) is lower than the temperature of the air at the air inlet (not shown), the room temperature can be lowered. The refrigerant heat-exchanged in the indoor heat exchanger 101 returns to the scroll compressor 1 again through the four-way valve 105.

  During the heating operation, the high-temperature and high-pressure refrigerant discharged from the scroll compressor 1 flows into the indoor heat exchanger 101 via the four-way valve 105. Then, it passes through the four-way valve 105 and the outdoor heat exchanger 102 and returns to the scroll compressor 1 through the four-way valve 105.

  In this embodiment, R32 is used as the refrigerant, but it can also be used for other refrigerants such as R1234ze and R1234yf.

  FIG. 2 is a longitudinal sectional view of the scroll compressor according to this embodiment. The basic operation of the scroll compressor 1 will be described with reference to FIG. The scroll compressor 1 includes a compression mechanism unit 3 composed of an orbiting scroll 6 and a fixed scroll 5 provided with spiral wraps 6a and 5c, an electric motor 4 for driving the compression mechanism unit 3, and the compression mechanism unit 3 An airtight container 2 for storing the electric motor 4 is provided. A compression mechanism unit 3 is disposed in the upper part of the sealed container 2, and an electric motor 4 is disposed in the lower part. A lubricating oil 13 is stored at the bottom of the sealed container 2.

  The sealed container 2 is configured by welding a lid chamber 2b and a bottom chamber 2c up and down to a cylindrical case 2a. The lid chamber 2b is provided with a suction pipe 2d, and a discharge pipe 2e is provided on the side surface of the case 2a. The inside of the sealed container 2 is a discharge pressure chamber 2f.

  The compression mechanism unit 3 includes a fixed scroll 5 having a spiral wrap 5c on the end plate surface 5f side of the base plate 5d, a revolving scroll 6 having a spiral wrap 6a on the base plate 6b, and a bolt on the fixed scroll 5. 8 and a frame 9 that supports the orbiting scroll 6 integrated with each other.

  The frame 9 includes a main bearing 9a that rotatably supports the crankshaft 7. An eccentric portion 7 b of the crankshaft 7 is connected to the lower surface side of the orbiting scroll 6.

  An Oldham ring 12 is disposed between the lower surface side of the orbiting scroll 6 and the frame 9, and the Oldham ring 12 is attached to a groove formed on the lower surface side of the orbiting scroll 6 and a groove 9 c formed on the frame 9. ing. The Oldham ring 12 functions to revolve by receiving the eccentric rotation of the eccentric portion 7 b of the crankshaft 7 without rotating the orbiting scroll 6.

  The electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a is fastened to the sealed container 2 by press-fitting or welding. The rotor 4b is rotatably arranged in the stator 4a. A crankshaft 7 is fixed to the rotor 4b.

  The crankshaft 7 includes a main shaft 7 a and an eccentric portion 7 b and is supported by a main bearing 9 a and a lower bearing 17 provided on the frame 9. The eccentric portion 7 b is formed integrally with the main shaft 7 a of the crankshaft 7, and is fitted to a orbiting bearing 6 c provided on the back surface of the orbiting scroll 6. The crankshaft 7 is driven by the electric motor 4, and the eccentric portion 7b is eccentrically rotated with respect to the main shaft 7a, thereby causing the orbiting scroll 6 to orbit. The crankshaft 7 is provided with an oil supply passage 7c that guides the lubricating oil 13 to the main bearing 9a, the lower bearing 17 and the slewing bearing 6c.

  When the orbiting scroll 6 is turned through the crankshaft 7 driven by the electric motor 4, the refrigerant gas passes from the suction pipe 2d to the fixed scroll 5 through the suction port 5a provided coaxially with the suction pipe 2d, and then the orbiting scroll 6 The refrigerant gas is guided to the compression chamber 11 formed by the fixed scroll 5, and the refrigerant gas is compressed by reducing the volume of the compression chamber as it moves in the center direction of the scroll.

  Thereafter, the refrigerant gas in the compression chamber 11 is discharged from the discharge port 5e provided at the approximate center of the base plate 5d of the fixed scroll 5 to the discharge pressure chamber 2f in the sealed container 2, and flows out from the discharge pipe 2e to the outside. I will do it. However, under the so-called over-compression condition in which the pressure of the refrigerant gas in the compression chamber 11 reaches the discharge pressure before communicating with the discharge port 5e, the release valve 19 opens when the over-compression occurs, and the refrigerant gas flows from there. It is discharged into the discharge pressure chamber 2f.

  Lubricating oil 13 is supplied from the oil storage chamber at the bottom inside the compressor to the inside of the crankshaft 7 due to the pressure difference between the pressure inside the sealed container 2 (discharge pressure) and the pressure in the back pressure chamber 16 (back pressure). After flowing into the passage 7 c and lubricating the lower bearing 17, the main bearing 9 a and the slewing bearing 6 c, they flow into the back pressure chamber 16. Thereafter, the oil in the back pressure chamber 16 is supplied to the compression chamber (suction chamber) 11 through the back pressure control valve 10. This point will be described in detail below.

  FIG. 3 shows a fixed scroll according to the present embodiment. FIG. 4 shows the orbiting scroll 6 according to this embodiment. FIG. 5 is a cross-sectional view when these two scroll wraps mesh to form a compression chamber. As shown in FIG. 5, a back pressure chamber 16 is formed on the opposite side of the orbiting scroll 6, and the oil stored therein passes through a groove 5 i and a back pressure hole 5 b formed in the fixed scroll 5. After reaching the back pressure control valve 10, the oil is supplied to the lap from an oil supply hole 5 g provided at substantially the center of the fixed scroll tooth bottom 5 j.

  In addition, the black arrow of FIG. 5 shows the flow of oil. The back pressure control valve 10 includes a valve body 10e that is a circular thin plate, a spring 10d, and seal members 10b and 10c that isolate them from the external space of the fixed scroll. The spring 10d separates the valve body 10e from the back pressure hole 5b. The back pressure is controlled by urging with an elastic force in the direction of.

  The oil supply from the oil supply hole 5g will be described in detail. As a characteristic structure of the lap related to fuel supply, the fixed scroll 5 is provided with an oil supply groove 5h on the wrap winding end side (suction side) as shown in FIG. In the case of the present embodiment, the oil supply groove 5h is a circular depression and is provided in two places in total on the fixed scroll inner line side and the outer line side. On the other hand, as shown in FIG. 4, the orbiting scroll 6 is provided with a tooth tip groove 6d from the end of winding to the center along the spiral on the lap tooth tip.

  The oil supply method using these is demonstrated using FIG. 6 and FIG. FIG. 6 is a diagram showing the positional relationship between the fixed scroll wrap 5c and the orbiting scroll wrap 6a when the crank angle changes. Here, the discharge port 5e, the oil supply hole 5g, and the oil supply groove 5h are provided in the fixed scroll and are portions that are partially closed by the wrap 6a when viewed from the orbiting scroll side. Shown always visible to make the relationship clearer. FIG. 6 shows that the crank angle advances from (a) to (f) in the order indicated by the black arrows, rotates 360 °, and returns to the position (a) again.

  In the state shown in FIG. 6A, the oil supply hole 5g communicates with the swirling outer line chamber 11a to supply oil. Here, since the orbiting outer line chamber 11a moves to the wrap winding start side (center side) with the movement of the orbiting scroll wrap 6a, the oil supplied also moves to the center side downstream, and most of them. Does not reach the gap at the upstream end of the wrap winding (suction side). Therefore, as in the prior art, this method alone has a problem in that the sealing performance in the gap between the compression chamber and the suction side space is lowered, and the effect of suppressing the refrigerant leakage to the suction side is lowered.

  In the state shown in FIG. 6B in which the crank angle has advanced, oil supply to the orbiting outer line chamber 11a continues, and in the state shown in FIG. 6C in which the crank angle has further advanced, the oil supply hole 5g is connected to the orbiting scroll wrap 6a. By overlapping, refueling to the swirling outer line chamber 11a is completed.

  At this time, the oil supply hole 5g communicates with the tooth tip groove 6d, and further, the tooth tip groove 6d communicates with the oil supply groove 5h, so that the swivel extension chamber passes from the oil supply hole 5g via the tooth tip groove 6d and the oil supply groove 5h. Oil is locally supplied to the side gap immediately before 11b is closed, and the gap is sealed.

  FIG. 7 is a partially enlarged view of the AA cross section of FIG. 6C regarding the oil supply from the tooth tip groove 6d through the oil supply groove 5h in the state shown in FIG. 6C. The tooth tip groove 6d has a V-shaped cross section, and the oil supply groove 5h communicates with the swivel extension chamber 11b so as to straddle the wrap 6a, and oil supply is performed in the direction indicated by the black arrow.

  At this time, the oil supplied to the suction side space from the oil supply groove 5h is cooled when passing through the tooth tip groove 6d. Therefore, the suction heating loss can be reduced as compared with the case where oil is directly supplied from the oil supply hole 5g directly to the suction side space.

  In addition, the cross-sectional shape of the tooth tip groove 6d is not limited to the V-shape, and may be a rectangle as shown in FIG.

  Returning to FIG. 6, when the crank angle advances from the state shown in FIG. 6C to the state shown in FIG. 6D, the oil supply hole 5 g directly communicates with the turning extension chamber 11 b and supplies oil. Since this space is a space that is closed after the suction is completed, it is possible to improve the gap sealing performance on the wrap winding start side (center side) without generating suction heating loss. In the state shown in FIG. 6 (d), the oil supply groove 5h is closed by the wrap 6a of the orbiting scroll 6, and the oil supply from the tooth tip groove 6d is not performed.

  In the state shown in FIG. 6E in which the crank angle is advanced, the lap 6a is partially detached from the oil supply groove 5h, and the tooth tip groove 6d and the newly formed suction chamber 11c communicate with each other. If oil is supplied from the tooth tip groove 6d to the suction chamber 11c at this time, high-temperature oil is injected into the suction chamber 11c whose volume is increased, and suction heat is generated to reduce volumetric efficiency.

  However, in the structure of the present embodiment, the oil in the back pressure chamber 16 is not supplied to the oil supply groove 6d because the oil supply hole 5g is not already in communication with the tooth tip groove 6d in the state shown in FIG. Therefore, refueling to the suction chamber 11c is not performed.

  In this way, by adjusting the timing at which the oil supply hole 5g, the tooth tip groove 6d, and the oil supply groove 5h communicate with each other according to their positions, while locally supplying oil to the side gap in the suction chamber immediately before the completion of closing, The newly formed suction chamber can be refueled and the amount of oil supplied to the suction side can be minimized to effectively improve the sealing performance in the side gap while suppressing heating loss. Can be made.

  Similarly to the state shown in FIG. 6E, in the state shown in FIG. 6B, the tooth tip groove 6d is prevented from communicating with the oil supply hole 5g, so that the newly formed suction chamber 11d is oiled. Without heating loss.

  After the state shown in FIG. 6 (e), the state shown in FIG. 6 (f) is followed, and the crank angle rotates 360 ° to return to the state shown in FIG. 6 (a) again.

  Thus, in the scroll compressor according to the present embodiment, the fixed scroll 5 has the oil supply hole 5g that penetrates the fixed scroll 5 and supplies oil to the compression chamber, and the oil supply groove 5h that does not penetrate the fixed scroll 5, The orbiting scroll 6 has an addendum groove 6d provided at the addendum of the orbiting side wrap, and the oil supply hole 5g and the oil supply groove 5h are within the range of the first crank angle (FIGS. 6C and 6F). It communicates through the tooth tip groove 6d. Therefore, since refueling is performed locally at a necessary timing, the suction heating loss due to refueling can be reduced.

  In addition to the above-described oil supply path, the orbiting outer line chamber, which is a compression chamber formed on the outer line side of the orbiting scroll 6, and the oil supply hole 5g communicate directly with each other at the second crank angle (FIGS. 6A and 6B). The orbiting extension chamber, which is a compression chamber formed on the inner side of the orbiting scroll 6, and the oil supply hole 5g are in direct communication with each other at the third crank angle (FIGS. 6D and 6E). Therefore, it is possible to disperse the position of refueling and improve the sealing performance.

  The first crank angle (FIGS. 6C and 6F), the second crank angle (FIGS. 6A and 6B), and the third crank angle (FIGS. 6D and 6E) are: Different crank angles.

  Further, in the scroll compressor according to the present embodiment, the fixed scroll 5 has two or more oil supply grooves 5h, and the oil supply groove in a predetermined range (FIG. 6C) within the first crank angle range. At least one of 5h is located on the outer diameter side of the tooth tip groove 6d, and in a predetermined range (FIG. 6 (f)) within the first crank angle range, at least one of the oil supply grooves 5h is a tooth tip. It is located on the inner diameter side of the groove 6d.

  Next, sealing the side gap at the end of the orbiting scroll wrap winding of the suction chamber immediately before the completion of suction will be described in more detail below. FIG. 9 is an explanatory view showing a state immediately before the swirling outer line chamber 11a shown in gray completes the suction stroke.

  In the scroll compressor, the suction chamber formed on the inner / outer line side of the orbiting scroll wrap 6a expands to suck in the refrigerant, and finally the gap between the end of the orbiting scroll winding and the side of the fixed scroll wrap is reduced and closed. The process is complete.

  The volume change with respect to the crank angle of the suction chamber (compression chamber) is shown in FIG. Since the asymmetric wrap is used in this embodiment, the suction start timing and the suction completion timing of the outer chamber and the inner chamber are shifted from each other, but as a common feature, the volume is not maximized at the completion of the suction, The volume becomes maximum immediately before. Therefore, the suction chamber swells once immediately before closing, and then the suction is completed by closing the side gap while reducing the volume.

  At this time, the refrigerant in the suction chamber flows backward until the side surface gap is closed after the volume is maximized, which causes a reduction in volume efficiency.

  According to the oil supply method according to the present embodiment, the volumetric efficiency is improved by supplying oil to the side gap in accordance with the moment of maximum volume immediately before closing, and suppressing the backflow of the refrigerant due to the volume reduction by the supplied oil. be able to.

  Further, at least one of the oil supply hole 5g and the oil supply groove 5h is separated by 180 degrees or more in the turning direction. With such a structure, it is possible to disperse the oil supply positions. According to such a present Example, the position of oil supply can further be disperse | distributed and a sealing performance can be improved. The turning direction means, for example, the clockwise direction in the rotation direction in the scroll compressor shown in FIG.

  Further, as a leakage path from the compression chamber, there is a tooth tip clearance in addition to the side surface clearance, but the tooth tip of the orbiting scroll wrap 6a is always filled with oil by the tooth tip groove 6d as shown in FIG. Therefore, the refrigerant leakage from the tooth tip gap can be similarly suppressed.

  Furthermore, when R32 is used as the refrigerant, there is more leakage from the compression chamber than other refrigerants such as R410A, and the oil sealing effect according to this embodiment is particularly great.

  In this embodiment, the oil supply hole 5g and the oil supply groove 5h are provided in the fixed scroll 5 and the tooth tip groove 6d is provided in the orbiting scroll 6. However, the tooth scroll is provided in the fixed scroll 5 and oil is supplied to the orbiting scroll. You may make it provide the hole 5g and the oil supply groove | channel 5h.

  That is, the fixed scroll which has the airtight container 2, the fixed side board | plate part 5d incorporated in the airtight container 2, and the fixed side wrap 5c standing upright and maintaining the spiral shape in the end plate surface side of the fixed side board part 5d. 5, a turning side plate 6 b, and a turning side wrap 6 a erected while holding a spiral shape on one surface of the turning side plate 6 b, and the fixed side wrap 5 c and the turning side wrap 6 c are engaged with each other, A revolving scroll 6 that forms a compression chamber by revolving with respect to the fixed scroll 5. The revolving scroll 6 penetrates the revolving scroll 6 and supplies oil to the compression chamber, and an oil supply groove that does not penetrate the revolving scroll. The fixed scroll 5 has a tooth tip groove provided at the tooth tip of the fixed side wrap 5, and the oil supply hole and the oil supply groove pass through the tooth tip groove in the range of the first crank angle. To communicate It may be.

  A scroll compressor according to the present embodiment will be described with reference to FIG. Since the basic configuration of the scroll compressor in the present embodiment is the same as that in the first embodiment, only the differences will be described here.

  The difference of the present embodiment from the first embodiment is that the number of oil supply grooves 5h provided in the fixed scroll 5 is larger than the two in the first embodiment. For example, in the example of FIG. 11, two oil supply grooves 5 h are provided on each of the turning inner line side and the outer line side, and the oil flow path when the tooth tip groove 6 d and the turning outer (inner) line chamber 11 communicate with each other is widened. It is possible to improve the sealing performance from the gap by increasing the amount of oil supply, and to realize a highly efficient scroll compressor.

  A scroll compressor according to the present embodiment will be described with reference to FIG. Since the basic configuration of the scroll compressor in the present embodiment is the same as that in the first embodiment, only the differences will be described here.

  This embodiment is characterized in that the oil supply groove 5h is a long groove along the wrap spiral shape. Thereby, the amount of oil supply to the suction chamber can be increased, and a highly efficient scroll compressor can be realized by improving the sealing performance in the gap. Thus, the oil supply groove 5h may be a non-circular recess, and the amount of oil supply may be adjusted according to the shape of the groove.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 2 Sealed container 2a Case 2b Cover chamber 2c Bottom chamber 2d Suction pipe 2e Discharge pipe 2f Discharge pressure chamber 3 Compression mechanism part 4 Electric motor 4a Stator 4b Rotor 5 Fixed scroll 5a Suction port 5c Lap 5d Base plate 5e Discharge Exit 5f End plate surface 5g Oil supply hole 5h Oil supply groove 5i Groove 6 Orbiting scroll 6a Wrap 6b Base plate 6c Orbiting bearing 6d Tooth groove 6e End plate surface 7 Crankshaft 7a Main shaft 7b Eccentric part 7c Oil supply passage 8 Bolt 9 Frame 9a Main bearing 10 Back Pressure valve 11 Compression chamber 12 Oldham ring 13 Lubricating oil 14 Balance weight 16 Back pressure chamber 17 Lower bearing 19 Release valve 19h Release port

Claims (7)

A sealed container;
A fixed scroll that is incorporated in the closed container and has a fixed side plate portion, and a fixed side wrap that stands upright while maintaining a spiral shape on the end plate surface side of the fixed side plate portion;
A revolving side plate portion, and a revolving side wrap that is erected while maintaining a spiral shape on one surface of the revolving side plate portion, and the fixed side wrap and the revolving side wrap are engaged with each other while the fixed scroll is engaged with the fixed scroll. And a revolving scroll that forms a compression chamber by revolving,
The fixed scroll includes an oil supply hole that penetrates the fixed scroll and supplies oil to the compression chamber, and an oil supply groove that does not penetrate the fixed scroll,
The orbiting scroll has a tooth groove provided at the tooth tip of the orbiting side wrap,
The oil supply hole and the oil supply groove communicate with each other via the tooth tip groove in a first crank angle range. The orbiting outer line chamber, which is a compression chamber formed on the outer line side of the orbiting scroll, and the oil supply hole communicate at a second crank angle,
2. The scroll compressor according to claim 1, wherein the orbiting extension chamber, which is a compression chamber formed on the extension side of the orbiting scroll, and the oil supply hole communicate with each other at a third crank angle.   The scroll compressor according to claim 2, wherein the first crank angle, the second crank angle, and the third crank angle are different crank angles.   The scroll compressor according to claim 1, wherein at least one of the oil supply hole and the oil supply groove is separated by 180 degrees or more in the turning direction.   The scroll compressor according to any one of claims 1 to 4, wherein the oil supply groove is non-circular. A sealed container;
A fixed scroll that is incorporated in the closed container and has a fixed side plate portion, and a fixed side wrap that stands upright while maintaining a spiral shape on the end plate surface side of the fixed side plate portion;
A revolving side plate portion, and a revolving side wrap that is erected while maintaining a spiral shape on one surface of the revolving side plate portion, and the fixed side wrap and the revolving side wrap are engaged with each other while the fixed scroll is engaged with the fixed scroll. And a revolving scroll that forms a compression chamber by revolving,
The orbiting scroll has an oil supply hole that penetrates the orbiting scroll and supplies oil to the compression chamber, and an oil supply groove that does not penetrate the orbiting scroll,
The fixed scroll has a tooth groove provided on a tooth tip of the fixed side wrap,
The oil supply hole and the oil supply groove communicate with each other via the tooth tip groove in a first crank angle range. The scroll compressor according to any one of claims 1 to 6, comprising:
An air conditioner using R32 as a refrigerant.

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