WO2022239678A1

WO2022239678A1 - Scroll compressor

Info

Publication number: WO2022239678A1
Application number: PCT/JP2022/019358
Authority: WO
Inventors: 将弘麻生; 義幸二上
Original assignee: パナソニックＩｐマネジメント株式会社
Priority date: 2021-05-11
Filing date: 2022-04-28
Publication date: 2022-11-17
Also published as: CN117295895A; JP2022174443A

Abstract

In a scroll compressor according to the present disclosure, when a crank angle of 0° is set to the time when refrigerant confinement is completed, the shortest distance Ls is greater than the minimum shortest distance Lα, Lα being, for the crank angle α > 0°, the shortest distance (compression chamber seal length) from a point where a fixed scroll wrap 124b and an orbiting scroll wrap 126b are in contact with each other on the outermost circumference to an inner circumferential edge 124d of an annular lubrication groove 124c, the shortest distance Ls being, for a crank angle of 0°, the shortest distance from the point where the fixed scroll wrap 124b and an orbiting scroll wrap 126b are in contact with each other on the outermost circumference to the inner circumferential edge 124d of the annular lubrication groove 124c and the shortest distance (intake part seal length) from an outer circumferential edge 128f of an intake part 128c to the inner circumferential edge 124d of the annular lubrication groove 124c. This arrangement provides a scroll compressor capable of both suppressing lowered compressor efficiency due to refrigerant and oil leakage and also reducing sliding loss.

Description

scroll compressor

The present disclosure particularly relates to scroll compressors used in refrigerating devices such as cooling and heating air conditioners and refrigerators, or heat pump water heaters.

Patent Literature 1 discloses a scroll compressor. In general, this type of scroll compressor generates a force (hereinafter referred to as "push-back force") that tends to pull the fixed scroll and the orbiting scroll apart from each other when compressing the refrigerant. When both scrolls are pulled apart, refrigerant or oil leaks from the compression chamber, which deteriorates the volumetric efficiency and compression efficiency, thereby lowering the efficiency of the compressor. Therefore, a back pressure chamber is formed on the back surface of the fixed scroll or the orbiting scroll. The back pressure chamber holds a back pressure for generating a force (hereinafter referred to as "pressing force") that presses the fixed scroll or the orbiting scroll against the mating scroll. The pressure in the back pressure chamber is set to an arbitrary pressure intermediate between the suction pressure and the discharge pressure. This pressing force prevents the fixed scroll and the orbiting scroll from being separated from each other, thereby reducing a decrease in compressor efficiency due to leakage of refrigerant or oil. However, if the pressing force becomes excessive, loss due to sliding between the fixed scroll end plate and the orbiting scroll end plate increases, and the efficiency of the compressor decreases.
Therefore, in the scroll compressor disclosed in Patent Document 1, an annular oil supply groove communicating with the back pressure chamber is formed in the sliding surface of the fixed scroll end plate in contact with the orbiting scroll end plate, and one end of the annular oil supply groove is open. A plurality of oil grooves having a shape or a linear shape are arranged at substantially equal pitches. By doing so, the sliding loss between the fixed scroll end plate and the orbiting scroll end plate is reduced.

JP-A-7-208356

The present disclosure provides a scroll compressor that achieves both suppression of compressor efficiency deterioration due to leakage of refrigerant and oil and reduction of sliding loss.

A scroll compressor according to the present disclosure includes a closed container and a compression mechanism section disposed in the closed container and compressing a refrigerant, the compression mechanism section including a fixed scroll and an orbiting scroll, and the fixed scroll has a fixed scroll end plate and a spiral fixed scroll wrap rising from the fixed scroll end plate, and the orbiting scroll has an orbiting scroll end plate and a spiral orbiting scroll wrap rising from the orbiting scroll end plate. a plurality of compression chambers are formed between the fixed scroll wrap and the orbiting scroll wrap by meshing the fixed scroll wrap and the orbiting scroll wrap, and the compression chambers are positioned outside the orbiting scroll wrap; an inner compression chamber positioned inside the orbiting scroll wrap; a suction portion positioned on the outermost periphery of the compression chamber for guiding suction pressure refrigerant into the compression chamber; a discharge portion located on the innermost circumference and discharging discharge pressure refrigerant from the inside of the compression chamber to the inside of the closed container, wherein the outer compression chamber closes the refrigerant more than the inner compression chamber; An annular oil groove is formed in the sliding surface of the fixed scroll end plate in contact with the orbiting scroll end plate, and the pressure in the annular oil groove is any pressure between the suction pressure and the discharge pressure. In the scroll compressor, the sealing portion surrounded by the inner peripheral edge of the annular oil supply groove, the outer compression chamber, and the outer peripheral edge of the suction portion is provided, and when the outer compression chamber completes the confinement of the refrigerant is a crank angle of 0°, the shortest distance from the point where the fixed scroll wrap and the orbiting scroll wrap are in contact at the outermost periphery to the inner peripheral edge of the annular oil supply groove when the crank angle α is greater than 0° (Compression chamber seal length) is Lα, and at the crank angle of 0°, the shortest distance from the point where the fixed scroll wrap and the orbiting scroll wrap are in contact at the outermost circumference to the inner peripheral edge of the annular oil supply groove; Assuming that the shortest distance (suction portion seal length) from the outer peripheral edge of the suction portion to the inner peripheral edge of the annular oil supply groove is Ls, the Ls is larger than the minimum Lα. .

The scroll compressor according to the present disclosure can reduce leakage of refrigerant and oil by ensuring a seal length at the suction portion where the pressure difference from the annular oil groove is large. For this reason, it is possible to achieve both suppression of reduction in compressor efficiency due to deterioration in volumetric efficiency and reduction in sliding loss.

Longitudinal sectional view of the scroll compressor in Embodiment 1 Enlarged vertical cross-sectional view of the main part of the scroll compressor A cross-sectional view of the fixed scroll and orbiting scroll in Embodiment 1 taken along line AA in FIG. Explanatory drawing of suction part seal length Ls Explanatory drawing of compression chamber seal length Lα A cross-sectional view of the fixed scroll and orbiting scroll in Embodiment 2 taken along the line AA in FIG.

(Knowledge, etc. on which this disclosure is based)
At the time when the inventors came up with the present disclosure, as described in Patent Document 1, a scroll compressor had a fixed scroll end plate and an orbiting scroll end plate in order to reduce sliding loss between the fixed scroll end plate and the orbiting scroll end plate. An annular oil groove communicating with the back pressure chamber is formed in the sliding surface of the orbiting scroll end plate, and a plurality of arc-shaped or linear oil grooves with one end open are arranged in the annular oil groove at substantially equal pitches. was set up. As a result, the sliding surface between the fixed scroll end plate and the orbiting scroll end plate is well lubricated, and the sliding area can be reduced.
However, no particular consideration has been given to leakage of refrigerant or oil from the back pressure chamber to the suction portion or from the back pressure chamber to the compression chamber on the sliding surface between the fixed scroll end plate and the orbiting scroll end plate. As a result, refrigerant and oil leak from the compression chamber, particularly at the suction section, which is located at the outermost periphery of the compression chamber and has a large pressure difference from the pressure inside the annular oil groove, and this may reduce the efficiency of the compressor. rice field.
The inventors found such problems and came to constitute the subject of the present disclosure.

Therefore, the present disclosure provides a scroll compressor that achieves both suppression of compressor efficiency deterioration due to leakage of refrigerant and oil and reduction of sliding loss.

Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed description than necessary may be omitted. For example, detailed descriptions of well-known matters or redundant descriptions of substantially the same configurations may be omitted.
It should be noted that the accompanying drawings and the following description are provided to allow those skilled in the art to fully understand the present disclosure and are not intended to limit the claimed subject matter thereby.

(Embodiment 1)
Embodiment 1 will be described below with reference to FIGS. 1 to 5. FIG.

[1-1. Constitution]
1 is a longitudinal sectional view of the scroll compressor 100, FIG. 2 is an enlarged longitudinal sectional view of the essential parts of the scroll compressor, and FIG. 4 is an explanatory diagram of the suction portion seal length Ls, and FIG. 5 is an explanatory diagram of the compression chamber seal length Lα.

As shown in FIG. 1, the scroll compressor 100 includes a closed container 110, a compression mechanism section 120 arranged in the closed container 110, and a motor section 130 that drives the compression mechanism section 120. Oil 140 is stored in the bottom of the .
A suction pipe 112 and a discharge pipe 114 are attached to the sealed container 110 . In this embodiment, suction pipe 112 is attached to the side surface of closed container 110 . The discharge pipe 114 is attached to the upper surface of the sealed container 110 .

As shown in FIG. 2 , the compression mechanism section 120 includes a main bearing member 122 , a fixed scroll 124 and an orbiting scroll 126 .
The main bearing member 122 is fixed in the sealed container 110 by welding or shrink fitting. The fixed scroll 124 includes a fixed scroll end plate 124a and a spiral fixed scroll wrap 124b rising from the fixed scroll end plate 124a, and is bolted onto the main bearing member 122. As shown in FIG. The orbiting scroll 126 includes an orbiting scroll end plate 126 a and a spiral orbiting scroll wrap 126 b rising from the orbiting scroll end plate 126 a , and is arranged above the main bearing member 122 so as to face the fixed scroll 124 . A plurality of compression chambers 128 are formed by meshing the fixed scroll wrap 124b and the orbiting scroll wrap 126b. A muffler 121 is provided on the back surface of the fixed scroll 124 , and a discharge pressure chamber 127 is formed between the muffler 121 and the back surface of the fixed scroll 124 . Inside the orbiting scroll 126, there are provided a connection path 126c and a supply path 126d for guiding the oil 140 from the bottom of the sealed container 110 to the compression chamber 128. As shown in FIG. A sealing member 116 is provided on the back surface of the orbiting scroll end plate 126a. As a result, a high-pressure region 118 that retains the discharge pressure is formed inside the seal member 116 , and a back pressure chamber 129 that retains the back pressure that presses the orbiting scroll 126 against the fixed scroll 124 is formed outside the seal member 116 . formed. Between the main bearing member 122 and the orbiting scroll 126, a rotation restraining mechanism 123 such as an Oldham's ring is provided to prevent the orbiting scroll 126 from rotating and to guide the orbiting scroll.

As shown in FIG. 1, the motor unit 130 includes a stator 132 fixed to the sealed container 110 by welding or shrink fitting, and a rotor 134 containing permanent magnets arranged on the inner peripheral side of the stator 132 . I have it. A crankshaft 136 is fixed to the rotor 134 .
Crankshaft 136 is supported by main bearing member 122 and sub-bearing member 138 provided near the bottom of sealed container 110 . The crankshaft 136 includes a main shaft portion 136a and an eccentric shaft portion 136b formed eccentrically with respect to the main shaft portion 136a. The eccentric shaft portion 136b is fitted in a turning bearing 126f provided on a boss portion 126e on the back surface of the turning scroll 126. As shown in FIG. The crankshaft 136 has an oil supply hole 136c extending therethrough in the axial direction.
The oil pump 142 is arranged at a position where the suction port surely enters the oil 140 .

As shown in FIG. 3, compression chamber 128 is formed by fixed scroll wrap 124b and orbiting scroll wrap 126b. The compression chamber 128 includes an outer compression chamber 128a located outside the orbiting scroll wrap 126b and an inner compression chamber 128b located inside the orbiting scroll wrap 126b. The outermost periphery of the compression chamber 128 has a suction portion 128 c that guides the suction pressure refrigerant into the compression chamber 128 . The innermost circumference of the compression chamber 128 has a discharge portion 128 d that discharges the discharge pressure refrigerant from the inside of the compression chamber 128 to the inside of the sealed container 110 .
The outer compression chamber 128a has a larger volume than the inner compression chamber 128b when the refrigerant is completely confined.
An annular oil supply groove 124 c is provided in the outer peripheral portion of the fixed scroll 124 to communicate with the back pressure chamber 129 to supply the coolant and the oil 140 .
A seal portion 125 is formed in a range of the fixed scroll 124 surrounded by the inner peripheral edge 124d of the annular oil supply groove 124c and the outer peripheral edge 128e of the compression chamber 128 so as to be in sliding contact with the orbiting scroll end plate 126a.

An inner peripheral edge 124d of the annular oil supply groove 124c is formed as a circle. For example, the center 124f of the inner peripheral edge 124d of the annular oil supply groove 124c has a crank angle of 0° when the outer compression chamber 128a has completely confined the refrigerant, as shown in FIG. When the crank angle is 0°, the shortest distance from the contact point of the fixed scroll wrap 124b and the orbiting scroll wrap 126b at the outermost periphery to the inner peripheral edge 124d of the annular oil supply groove 124c, and the annular oil supply from the outer peripheral edge 128f of the suction portion 128c. Let Ls be the shortest distance (suction portion seal length) to the inner peripheral edge 124d of the groove 124c. Further, as shown in FIG. 5, the center 124f of the inner peripheral edge 124d of the annular oil supply groove 124c is located at a crank angle α of α>0° because the fixed scroll wrap 124b and the orbiting scroll wrap 126b are in contact at the outermost periphery. Let Lα be the shortest distance (compression chamber seal length) to the inner peripheral edge 124d of the annular oil supply groove 124c. In this case, it is eccentric from the fixed scroll center 124e toward the intake portion 128c so that Ls is larger than the minimum Lα (Lαmin).

[1-2. motion]
The operation and effects of the scroll compressor 100 configured as described above will be described below.
When the motor section 130 is energized, the magnetic field generated in the stator 132 causes the rotor 134 to rotate together with the crankshaft 136 .
As the crankshaft 136 rotates, the oil pump 142 is driven, and the oil 140 stored in the bottom of the sealed container 110 is reliably sucked up regardless of pressure conditions and operating speed. This eliminates the worry of running out of oil. Oil 140 sucked up by oil pump 142 is supplied to compression mechanism portion 120 through oil supply hole 136c. By removing foreign matter from the oil 140 with an oil filter or the like before and after the oil pump 142 sucks up the oil 140, it is possible to prevent foreign matter from entering the compression mechanism portion 120, thereby improving reliability. .
The pressure of the oil 140 supplied to the compression mechanism portion 120 is substantially the same as the pressure of the refrigerant discharged from the scroll compressor 100 and also serves as a back pressure source for the orbiting scroll 126 . A part of the oil 140 is guided to the back pressure chamber 129 by the pressure difference when the connection path 126c faces the outside of the seal member 116 (back pressure chamber 129). Conversely, when the connection path 126 c faces the inner side of the seal member 116 (high pressure area 118 ), no pressure difference occurs and the oil 140 does not flow into the back pressure chamber 129 . The oil 140 led to the back pressure chamber 129 lubricates the sliding surfaces of the fixed scroll end plate 124a and the orbiting scroll end plate 126a through the annular oil supply groove 124c. The remaining oil 140 flows into the fitting portion between the eccentric shaft portion 136b and the orbiting bearing 126f and the fitting portion between the main shaft portion 136a and the main bearing member 122, lubricates each portion, and then flows to the bottom portion of the closed container 110. return.

As the crankshaft 136 rotates, the eccentric shaft portion 136b rotates eccentrically with respect to the main shaft portion 136a, causing the orbiting scroll 126 to orbit.
The orbiting scroll 126 is eccentrically driven by the eccentric shaft portion 136 b and orbitally moved by the rotation restraint mechanism 123 , thereby changing the volume of the compression chamber 128 .

Refrigerant sucked from the suction pipe 112 is guided to the compression chamber 128 via the suction portion 128c. The refrigerant sucked into the compression chamber 128 moves from the outer circumference toward the center while reducing its volume, and is pressurized. At this time, in order to reduce the sliding area between the fixed scroll end plate 124a and the orbiting scroll end plate 126a, the annular oil supply groove 124c is enlarged. As a result, leakage of the refrigerant or oil 140 is likely to occur at the suction portion 128c, which is located on the outermost periphery of the compression chamber 128 and has a large pressure difference with the inside of the annular oil groove 124c. May result in reduced efficiency.

In the present embodiment, the center 124f of the inner peripheral edge 124d of the annular oil supply groove 124c is eccentric from the fixed scroll center 124e toward the intake portion 128c so that Lαmin<Ls. Therefore, Lαmin exists in a region opposite to the eccentric direction where the difference between the pressure in annular oil groove 124c and the pressure in compression chamber 128 is small. That is, the seal length is large in the suction portion 128c where the difference between the pressure in the annular oil groove 124c and the pressure in the compression chamber 128 is small, and the seal length is becomes smaller. The leakage amount of refrigerant or oil 140 is proportional to the pressure difference and inversely proportional to the seal length. As a result, leakage of the refrigerant and oil 140 from the suction portion 128 c can be reduced without increasing the amount of leakage of the refrigerant and oil 140 from the compression chamber 128 .

Then, the refrigerant that reaches the discharge pressure is discharged from the innermost discharge portion 128 d of the compression chamber 128 into the discharge pressure chamber 127 . The refrigerant discharged into the discharge pressure chamber 127 fills the inside of the sealed container 110 and is discharged out of the sealed container 110 through the discharge pipe 114 .

[1-3. effects, etc.]
As described above, in the present embodiment, in scroll compressor 100, center 124f of inner peripheral edge 124d of annular oil supply groove 124c is eccentric from fixed scroll center 124e toward suction portion 128c. As a result, the seal length is increased at the suction portion 128c, which is located on the outermost periphery of the compression chamber 128 and has a large pressure difference with the annular oil groove 124c, and the pressure difference between the annular oil groove 124c and the compression chamber 128 is small. The seal length can be reduced in areas. Further, even if the annular oil supply groove 124c is enlarged in order to reduce the sliding area between the fixed scroll end plate 124a and the orbiting scroll end plate 126a, leakage of refrigerant and oil 140 can be reliably reduced. As a result, it is possible to achieve both suppression of deterioration in compressor efficiency due to deterioration in volumetric efficiency and compression efficiency, and reduction in sliding loss.

(Embodiment 2)
Embodiment 2 will be described below with reference to FIG.

[2-1. Constitution]
FIG. 6 is an arrow cut through the fixed scroll 224 and orbiting scroll 126 along line AA in FIG. It is a cross-sectional view.
As shown in FIG. 6, a scroll compressor 200 according to the second embodiment differs from the scroll compressor 100 according to the first embodiment only in a fixed scroll 224, and other configurations and functions are different. And the effects are the same as those of the first embodiment, so the description thereof is omitted. Note that the fixed scroll wrap 124b, the inner compression chamber 128b, the suction portion 128c, and the outer peripheral edge 128f of the suction portion described in the first embodiment are replaced by the fixed scroll wrap 224b, the inner compression chamber 228b, and the suction portion in the second embodiment. 228c, shown as outer peripheral edge 228f of the inlet.
An annular oil supply groove 224 c is provided in the outer peripheral portion of the fixed scroll 224 to communicate with the back pressure chamber 129 to supply the coolant and the oil 140 .
A seal portion 225 is formed in a range surrounded by an inner peripheral edge 224d of the annular oil supply groove 224c of the fixed scroll 224 and an outer peripheral edge 228e of the compression chamber 228 so as to be in sliding contact with the orbiting scroll end plate 226a.
An inner peripheral edge 224d of the annular oil supply groove 224c is composed of a plurality of arcs having different curvatures, and Lαmin<Ls. Further, in a range in which the pressure in the annular oil groove 224c is higher than the pressure in the compression chamber 228, Lα gradually decreases as the crank angle α advances (increases). Further, in a range in which the pressure in the annular oil supply groove 224c is lower than the pressure in the compression chamber 228, Lα gradually increases as the crank angle α advances (increases).

[2-2. effects, etc.]
As described above, in the scroll compressor 200, in the range where the pressure in the annular oil groove 224c is higher than the pressure in the compression chamber 228, Lα gradually decreases as the crank angle α progresses (increases). do. Further, in a range in which the pressure in the annular oil supply groove 224c is lower than the pressure in the compression chamber 228, Lα gradually increases as the crank angle α advances (increases). Like the scroll compressor 100 according to the first embodiment, the scroll compressor 200 as described above reliably suppresses the leakage of the refrigerant and the oil 140 while reducing the sliding area between the fixed scroll end plate 224a and the orbiting scroll end plate 126a. can be reduced. For this reason, it is possible to achieve both suppression of reduction in compressor efficiency due to deterioration in volumetric efficiency and compression efficiency, and reduction in sliding loss.
Further, in scroll compressor 200, inner peripheral edge 224d of annular oil supply groove 224c is composed of a plurality of arcs having different curvatures. Therefore, over the entire compression chamber 228, in a range where the pressure difference between the annular oil groove 224c and the compression chamber 228 is large, the seal length is increased so that the pressure difference between the annular oil groove 224c and the compression chamber 228 is increased. In a small range, the seal length can be reduced. Therefore, the scroll compressor 200 reliably suppresses leakage of the refrigerant and the oil 140, and further increases the sliding area between the fixed scroll end plate 224a and the orbiting scroll end plate 126a as compared with the scroll compressor 100 according to the first embodiment. can be reduced. Therefore, scroll compressor 200 can further reduce sliding loss than scroll compressor 100 according to the first embodiment.

The scroll compressor according to the present disclosure can achieve both suppression of reduction in compressor efficiency and reduction in sliding loss, and can useful for

Reference Signs List 100, 200 scroll compressor 110 sealed container 112 suction pipe 114 discharge pipe 116 seal member 118 high pressure region 120 compression mechanism portion 121 muffler 122 main bearing member 123 rotation restraint mechanism 124, 224 fixed scroll 124a, 224a fixed

scroll end plate

124b, 224b fixed

Scroll wrap

124c, 224c

Annular oil groove

124d, 224d Inner peripheral edge of annular oil groove 124e Fixed scroll center 124f Center of inner peripheral edge of

annular oil groove

125, 225 Seal portion 126 Orbiting scroll 126a, 226a Orbiting scroll end plate 126b Orbiting scroll wrap 126c Connection Path 126d Supply path 126e Boss portion 126f Orbital bearing 127

Discharge pressure chambers

128, 228 Compression chambers 128a, 228a

Outer compression chambers

128b, 228b

Inner compression chambers

128c, 228c Suction portion 128d Discharge portions 128e, 228e Peripheral edges of

compression chambers

128f, 228f Outer peripheral edge of intake portion 129 Back pressure chamber 130 Motor portion 132 Stator 134 Rotor 136 Crankshaft 136a Main shaft portion 136b Eccentric shaft portion 136c Oil supply hole 138 Sub-bearing member 140 Oil 142 Oil pump

Claims

A closed container, and a compression mechanism arranged in the closed container for compressing a refrigerant,
The compression mechanism includes a fixed scroll and an orbiting scroll,
The fixed scroll has a fixed scroll end plate and a spiral fixed scroll wrap rising from the fixed scroll end plate,
The orbiting scroll has an orbiting scroll end plate and a spiral orbiting scroll wrap rising from the orbiting scroll end plate,
A plurality of compression chambers are formed between the fixed scroll wrap and the orbiting scroll wrap by meshing the fixed scroll wrap and the orbiting scroll wrap,
The compression chambers include an outer compression chamber positioned outside the orbiting scroll wrap, an inner compression chamber positioned inside the orbiting scroll wrap, and an inner compression chamber positioned on the outermost periphery of the compression chamber and extending into the compression chamber. a suction section for guiding suction pressure refrigerant; and a discharge section positioned at the innermost periphery of the compression chamber for discharging discharge pressure refrigerant from the inside of the compression chamber to the inside of the closed container. The chamber has a volume larger than that of the inner compression chamber when the refrigerant is completely confined, and
A scroll compressor in which an annular oil groove is formed in a sliding surface of the fixed scroll end plate in contact with the orbiting scroll end plate, and the pressure in the annular oil groove is an arbitrary pressure between suction pressure and discharge pressure,
a seal portion surrounded by the inner peripheral edge of the annular oil supply groove, the outer compression chamber, and the outer peripheral edge of the suction portion;
When the crank angle α is 0° when the outer compression chamber completes confinement of the refrigerant, the fixed scroll wrap and the orbiting scroll wrap are in contact with each other at the outermost periphery when the crank angle α is >0°. Lα is the shortest distance (compression chamber seal length) from the point where the oil supply groove is located to the inner peripheral edge of the annular oil supply groove. Ls is the shortest distance from the point to the inner peripheral edge of the annular oil supply groove and the shortest distance (suction portion seal length) from the outer peripheral edge of the suction portion to the inner peripheral edge of the annular oil supply groove. A scroll compressor, wherein the Ls is larger than the Lα.
The inner peripheral edge of the annular oil groove is formed in a circle, and the center of the inner peripheral edge of the annular oil groove is eccentric from the center of the end plate of the fixed scroll,
The scroll compressor according to claim 1.
The inner peripheral edge of the annular oil supply groove is composed of a plurality of arcs with different curvatures,
The scroll compressor according to claim 1.
In a range in which the pressure in the annular oil supply groove is higher than the pressure in the compression chamber,
characterized in that the Lα gradually decreases as the crank angle α progresses (increases),
The scroll compressor according to claim 1 or 3.
In a range in which the pressure in the annular oil groove is lower than the pressure in the compression chamber,
characterized in that the Lα gradually increases as the crank angle α progresses (increases),
The scroll compressor according to claim 1, claim 3, or claim 4.