Scroll compressor

Abstract

In the scroll compressor in the present disclosure, if the shortest distance (compression chamber sealing length) from the point at which the fixed scroll wrap (124b) and the orbiting scroll wrap (126b) contact at the outermost periphery to the inner periphery (124d) of the annular oil supply groove (124c) is set to Lα when the crank angle α is α > 0°, and the shortest distance from the point at which the fixed scroll wrap (124b) and the orbiting scroll wrap (126b) contact at the outermost periphery to the inner periphery (124d) of the annular oil supply groove (124c) and the shortest distance (suction portion sealing length) from the outer periphery (128f) of the suction portion (128c) to the inner periphery (124d) of the annular oil supply groove (124c) is set to Ls when the crank angle is 0°, Ls is greater than the smallest Lα. Thus, a scroll compressor that can achieve both suppression of reduction in compressor efficiency caused by leakage of refrigerant and oil and reduction in sliding loss is provided.

Description

Technical Field

[0001] This disclosure specifically relates to scroll compressors used in refrigeration equipment such as air conditioners and cold storage facilities for cooling and heating, or heat pump-type hot water supply devices. Background Technology

[0002] Patent Document 1 discloses a scroll compressor. Generally, when compressing refrigerant, this type of scroll compressor generates a force (hereinafter referred to as "reverse thrust") that attempts to separate the stationary scroll and the rotary scroll. When the two scrolls separate, refrigerant and oil leak from the compression chamber, resulting in a decrease in compressor efficiency due to deterioration in volumetric efficiency and compression efficiency. Therefore, a back pressure chamber is formed on the back side of either the stationary or rotary scroll. The back pressure chamber maintains a back pressure that generates a force (hereinafter referred to as "push force") that pushes the stationary or rotary scroll towards the opposite scroll. The pressure within the back pressure chamber is set to any pressure between the suction pressure and the discharge pressure. This push force suppresses the separation of the stationary and rotary scrolls, reducing the decrease in compressor efficiency caused by refrigerant and oil leakage. However, if the push force is too large, losses caused by sliding between the end plates of the stationary and rotary scrolls increase, leading to a decrease in compressor efficiency.

[0003] Therefore, the scroll compressor disclosed in Patent Document 1 forms an annular oil supply groove that communicates with the back pressure chamber on the sliding surface where the fixed scroll end plate and the rotary scroll end plate contact each other. Multiple oil grooves, each with an open end and composed of arc or straight lines, are arranged at approximately equal intervals within the annular oil supply groove. This reduces the sliding loss between the fixed scroll end plate and the rotary scroll end plate.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 7-208356 Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] This disclosure provides a scroll compressor that simultaneously suppresses compressor efficiency reduction caused by refrigerant and oil leakage and reduces sliding losses.

[0009] Methods for solving problems

[0010] The scroll compressor mechanism disclosed herein includes: a sealed container; and a compression mechanism section disposed within the sealed container for compressing a refrigerant. The compression mechanism section includes a fixed scroll member and a rotating scroll member. The fixed scroll member has a fixed scroll member end plate and scroll-shaped fixed scroll member teeth erected from the fixed scroll member end plate. The rotating scroll member has a rotating scroll member end plate and scroll-shaped rotating scroll member teeth erected from the rotating scroll member end plate. The fixed scroll member teeth mesh with the rotating scroll member teeth. A plurality of compression chambers are formed between the fixed scroll tooth and the rotary scroll tooth. Each compression chamber comprises: an outer compression chamber located outside the rotary scroll tooth; an inner compression chamber located inside the rotary scroll tooth; an intake section located at the outermost periphery of the compression chamber, guiding the intake refrigerant into the interior of the compression chamber; and a discharge section located at the innermost periphery of the compression chamber, discharging the discharge refrigerant from the interior of the compression chamber into the interior of the sealed container. The outer compression chamber is different from the inner compression chamber. The volume of the refrigerant after sealing is relatively large. An annular oil supply groove is formed on the sliding surface where the fixed scroll end plate and the rotary scroll end plate contact. The pressure in the annular oil supply groove is any pressure between the suction pressure and the discharge pressure. The scroll compressor includes a sealing part surrounded by the inner periphery of the annular oil supply groove, the outer compression chamber, and the outer periphery of the suction section. When the moment when the refrigerant sealing of the outer compression chamber is completed is set to a crank angle of 0°, if the crank angle α is α > 0°, the refrigerant from the fixed scroll... The shortest distance (compression chamber sealing length) from the point where the vortex teeth of the fixed vortex component and the vortex teeth of the rotary vortex component make contact at the outermost periphery to the inner periphery of the annular oil supply groove is set as Lα. When the crank angle is 0°, the shortest distance from the point where the vortex teeth of the fixed vortex component and the vortex teeth of the rotary vortex component make contact at the outermost periphery to the inner periphery of the annular oil supply groove and the shortest distance from the outer periphery of the suction part to the inner periphery of the annular oil supply groove (suction part sealing length) are set as Ls. Then, Ls is larger than the minimum Lα.

[0011] Invention Effects

[0012] The scroll compressor disclosed herein reduces refrigerant and oil leakage by ensuring a sealing length of the suction section with a large pressure difference from the annular oil supply groove. Therefore, it can simultaneously suppress compressor efficiency reduction caused by volumetric efficiency degradation and reduce sliding losses. Attached Figure Description

[0013] Figure 1 This is a longitudinal cross-sectional view of the scroll compressor in Embodiment 1.

[0014] Figure 2This is an enlarged longitudinal section view of the main parts of the scroll compressor.

[0015] Figure 3 The fixed scroll member and the rotating scroll member in embodiment 1 are along Figure 1 The axial view of the section cut by line AA.

[0016] Figure 4 This is an explanatory diagram of the sealing length Ls of the inhalation section.

[0017] Figure 5 This is an explanatory diagram of the compression chamber sealing length Lα.

[0018] Figure 6 The fixed scroll member and the rotating scroll member in embodiment 2 are along Figure 1 The axial view of the section cut by line AA. Detailed Implementation

[0019] (The knowledge and insights that form the basis of this disclosure, etc.)

[0020] The inventors conceived of a scroll compressor at the time of this disclosure, as described in Patent Document 1, which, in order to reduce the sliding loss between the fixed scroll end plate and the rotary scroll end plate, forms an annular oil supply groove communicating with the back pressure chamber on the sliding surface of the fixed scroll end plate and the rotary scroll end plate. Multiple oil grooves, each with an open end and composed of arc or straight lines, are arranged at approximately equal intervals in this annular oil supply groove. This improves the lubrication of the sliding surface between the fixed scroll end plate and the rotary scroll end plate and reduces the sliding area.

[0021] However, in the sliding surfaces of the fixed scroll end plate and the rotary scroll end plate, the leakage of refrigerant and oil from the back pressure chamber to the suction section or from the back pressure chamber to the compression chamber is not specifically considered. Therefore, in the suction section, which is located at the outermost periphery of the compression chamber and has a large pressure difference with the annular oil supply groove, leakage of refrigerant and oil from the compression chamber is particularly likely to occur, resulting in reduced compressor efficiency.

[0022] The inventors discovered this problem, which constitutes the subject of this disclosure.

[0023] Therefore, this disclosure provides a scroll compressor that achieves both suppression of compressor efficiency reduction caused by refrigerant and oil leakage and reduction of sliding losses.

[0024] The embodiments will now be described in detail with reference to the accompanying drawings. However, sometimes unnecessary detailed descriptions may be omitted. For example, there may be omissions of detailed descriptions of matters that are already known, or repeated descriptions of substantially the same structures.

[0025] Furthermore, the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the invention, and are not intended to limit the subject matter of the claims.

[0026] (Implementation Method 1)

[0027] The following uses Figures 1 to 5 Implementation method 1 will be described.

[0028] [1-1. Structure]

[0029] Figure 1 This is a longitudinal section view of a scroll compressor 100. Figure 2 This is an enlarged longitudinal section view of the main components of the scroll compressor. Figure 3 It is to move the fixed scroll member 124 and the rotating scroll member 126 along... Figure 1 The sagittal section view cut by line AA. Figure 4 This is an explanatory diagram of the inhalation section sealing length Ls. Figure 5 This is an explanatory diagram of the sealing length Lα of the compression chamber.

[0030] like Figure 1 As shown, the scroll compressor 100 includes a sealed container 110, a compression mechanism 120 disposed within the sealed container 110, and a motor 130 for driving the compression mechanism 120. Oil 140 is stored at the bottom of the sealed container 110.

[0031] A suction pipe 112 and a discharge pipe 114 are installed in a sealed container 110. In this embodiment, the suction pipe 112 is installed on the side of the sealed container 110. The discharge pipe 114 is installed on the upper surface of the sealed container 110.

[0032] like Figure 2 As shown, the compression mechanism 120 includes a main bearing component 122, a fixed scroll component 124, and a rotating scroll component 126.

[0033] The main bearing assembly 122 is fixed within the sealed container 110 by welding and hot pressing. The fixed scroll member 124 includes a fixed scroll member end plate 124a and scroll-shaped fixed scroll member scroll teeth 124b rising from the fixed scroll member end plate 124a, and is fixed to the main bearing assembly 122 by bolts. The rotary scroll member 126 includes a rotary scroll member end plate 126a and scroll-shaped rotary scroll member scroll teeth 126b rising from the rotary scroll member end plate 126a, and is arranged on the upper part of the main bearing assembly 122 opposite to the fixed scroll member 124. Multiple compression chambers 128 are formed by meshing the fixed scroll member scroll teeth 124b and the rotary scroll member scroll teeth 126b. A silencer 121 is provided on the back side of the fixed scroll member 124, and a discharge pressure chamber 127 is formed between the silencer 121 and the back side of the fixed scroll member 124. Inside the gyratory scroll member 126, there are a connection path 126c and a supply path 126d that guide oil 140 from the bottom of the sealed container 110 to the compression chamber 128. A sealing member 116 is provided on the back side of the end plate 126a of the gyratory scroll member. Thus, a high-pressure region 118 that maintains the discharge pressure is formed inside the sealing member 116, and a back pressure chamber 129 that maintains the back pressure that pushes the gyratory scroll member 126 against the fixed scroll member 124 is formed outside the sealing member 116. A rotation limiting mechanism 123, such as a cross slip ring, is provided between the main bearing member 122 and the gyratory scroll member 126 to prevent the gyratory scroll member 126 from rotating and to guide it in a circular track motion.

[0034] like Figure 1 As shown, the motor unit 130 includes: a stator 132, which is fixed to the sealed container 110 by welding and hot pressing; and a rotor 134, which has a permanent magnet disposed on the inner circumference of the stator 132. A crankshaft 136 is fixed to the rotor 134.

[0035] The crankshaft 136 is supported by a main bearing assembly 122 and a secondary bearing assembly 138 located near the bottom of the sealed container 110. The crankshaft 136 includes a main shaft portion 136a and an eccentric shaft portion 136b formed eccentrically relative to the main shaft portion 136a. The eccentric shaft portion 136b engages with a swivel bearing 126f located on a boss portion 126e on the back side of the swivel scroll member 126. The crankshaft 136 has an axially penetrating oil supply hole 136c inside, and the main shaft portion 136a is engaged with an oil pump 142 that is bolted to the secondary bearing assembly 138.

[0036] The oil pump 142 is positioned at the suction port to reliably enter the oil 140.

[0037] like Figure 3As shown, the compression chamber 128 is formed by a fixed scroll member with scroll teeth 124b and a rotating scroll member with scroll teeth 126b. The compression chamber 128 includes an outer compression chamber 128a located outside the rotating scroll member with scroll teeth 126b and an inner compression chamber 128b located inside the rotating scroll member with scroll teeth 126b. An intake section 128c is provided at the outermost periphery of the compression chamber 128 to guide the intake of compressed refrigerant into the interior of the compression chamber 128. A discharge section 128d is provided at the innermost periphery of the compression chamber 128 to discharge compressed refrigerant from the interior of the compression chamber 128 into the interior of the sealed container 110.

[0038] Compared to the inner compression chamber 128b, the outer compression chamber 128a has a larger volume when the refrigerant is fully sealed.

[0039] An annular oil supply groove 124c is provided on the outer periphery of the fixed scroll member 124, which supplies refrigerant and oil 140 through communication with the back pressure chamber 129.

[0040] Within the area of ​​the fixed scroll member 124 surrounded by the inner periphery 124d of the annular oil supply groove 124c and the outer periphery 128e of the compression chamber 128, a sealing portion 125 is formed that slides in contact with the end plate 126a of the swirling scroll member.

[0041] The inner periphery 124d of the annular oil supply groove 124c is formed by a circle. For example, as... Figure 4 As shown, when the refrigerant is sealed in the outer compression chamber 128a at the center 124f of the inner periphery 124d of the annular oil supply groove 124c, the crank angle is 0°. When the crank angle is 0°, the shortest distance from the point of contact between the fixed scroll tooth 124b and the rotating scroll tooth 126b at their outermost periphery to the inner periphery 124d of the annular oil supply groove 124c, and the shortest distance from the outer periphery 128f of the suction section 128c to the inner periphery 124d of the annular oil supply groove 124c (suction section sealing length) are set as Ls. Furthermore, as... Figure 5 As shown, when the crank angle α is α > 0°, the shortest distance (compression chamber sealing length) from the point where the fixed scroll tooth 124b and the rotating scroll tooth 126b contact at their outermost periphery to the inner periphery 124d of the annular oil supply groove 124c is set as Lα. In this case, the center 124f of the inner periphery 124d of the annular oil supply groove 124c is eccentric from the center 124e of the fixed scroll to the suction section 128c, with Ls being larger than the minimum Lα (Lαmin).

[0042] [1-2. Actions]

[0043] The following describes the operation and function of the scroll compressor 100 as described above.

[0044] When the motor section 130 is energized, the rotor 134 rotates together with the crankshaft 136 through the magnetic field generated by the stator 132.

[0045] As the crankshaft 136 rotates, the oil pump 142 drives the oil 140 stored at the bottom of the sealed container 110 to be reliably drawn up regardless of pressure conditions or operating speed. This eliminates concerns about oil depletion. The oil 140 drawn up by the oil pump 142 is supplied to the compression unit 120 through the oil supply port 136c. Furthermore, by using an oil filter or similar means to remove foreign matter from the oil 140 before and after it is drawn up by the oil pump 142, foreign matter can be prevented from entering the compression unit 120, thereby improving reliability.

[0046] The pressure of the oil 140 supplied to the compression unit 120 is approximately equal to the pressure of the refrigerant discharged from the scroll compressor 100, thus becoming a back pressure source for the rotary scroll member 126. When the connection path 126c faces the outer side of the sealing member 116 (back pressure chamber 129), a portion of the oil 140 is guided into the back pressure chamber 129 due to the pressure difference. Conversely, when the connection path 126c faces the inner side of the sealing member 116 (high pressure region 118), no pressure difference is generated, and the oil 140 does not flow into the back pressure chamber 129. The oil 140 guided into the back pressure chamber 129 lubricates the sliding surfaces of the fixed scroll member end plate 124a and the rotary scroll member end plate 126a through the annular oil supply groove 124c. The remaining oil 140 flows into the mating part of the eccentric shaft 136b and the rotary bearing 126f, and the mating part of the main shaft 136a and the main bearing component 122, lubricating each part before returning to the bottom of the sealed container 110.

[0047] Furthermore, as the crankshaft 136 rotates, the eccentric shaft portion 136b rotates eccentrically relative to the main shaft portion 136a, causing the vortex member 126 to rotate.

[0048] The vortex component 126 is eccentrically driven by the eccentric shaft 136b and moves in a circular orbit through the rotation limiting mechanism 123, thereby changing the volume of the compression chamber 128.

[0049] The refrigerant drawn in through the suction pipe 112 is guided into the compression chamber 128 via the suction section 128c. The refrigerant in the compression chamber 128 moves and pressurizes while decreasing in volume from the outer periphery towards the center. At this time, to reduce the sliding area between the fixed scroll end plate 124a and the rotating scroll end plate 126a, the annular oil supply groove 124c is enlarged. Therefore, in the suction section 128c, located at the outermost periphery of the compression chamber 128 and with a large pressure difference from the annular oil supply groove 124c, refrigerant and oil 140 leakage is likely to occur, sometimes leading to a decrease in compressor efficiency due to deterioration in volumetric efficiency and compression efficiency.

[0050] In this embodiment, the center 124f of the inner periphery 124d of the annular oil supply groove 124c is eccentrically positioned from the center 124e of the fixed scroll member toward the suction section 128c, with Lαmin < Ls. Therefore, Lαmin exists on the side opposite to the eccentric direction, in a region where the pressure difference between the annular oil supply groove 124c and the compression chamber 128 is small. That is, in the suction section 128c where the pressure difference with the annular oil supply groove 124c is large, the sealing length is large; in the region where the pressure difference between the annular oil supply groove 124c and the compression chamber 128 is small, the sealing length is small. The leakage of refrigerant and oil 140 is directly proportional to the pressure difference and inversely proportional to the sealing length. Thus, the leakage of refrigerant and oil 140 in the compression chamber 128 is not increased, and the leakage of refrigerant and oil 140 at the suction section 128c is reduced.

[0051] Furthermore, the refrigerant that has reached the discharge pressure is discharged from the discharge section 128d at the innermost periphery of the compression chamber 128 to the discharge pressure chamber 127. The refrigerant discharged into the discharge pressure chamber 127 fills the interior of the sealed container 110 and is discharged to the outside of the sealed container 110 through the discharge pipe 114.

[0052] [1-3. Effects, etc.]

[0053] As described above, in this embodiment, the scroll compressor 100 is eccentrically positioned from the center 124e of the inner periphery 124d of the annular oil supply groove 124c towards the suction section 128c. This allows for an increased sealing length in the suction section 128c, located at the outermost periphery of the compression chamber 128 and with a large pressure difference from the annular oil supply groove 124c, and a decreased sealing length in areas with a small pressure difference between the annular oil supply groove 124c and the compression chamber 128. Furthermore, to reduce the sliding area between the fixed scroll end plate 124a and the swirling scroll end plate 126a, even with an enlarged annular oil supply groove 124c, reliably reduced refrigerant and oil 140 leakage can be achieved. Consequently, it is possible to both suppress compressor efficiency reduction caused by deterioration in volumetric efficiency and compression efficiency, and reduce sliding losses.

[0054] (Implementation Method 2)

[0055] The following uses Figure 6 Implementation method 2 will be described.

[0056] [2-1. Structure]

[0057] Figure 6 When the pressure in the outermost compression chamber 228a of the compression chamber 228 is equal to the pressure in the annular oil supply groove 224c, the fixed scroll member 224 and the rotating scroll member 126 move along... Figure 1 The axial view of the section cut by line AA.

[0058] like Figure 6 As shown, the scroll compressor 200 of Embodiment 2 differs from the scroll compressor 100 of Embodiment 1 only in the fixed scroll member 224; otherwise, its structure, function, and effects are the same as in Embodiment 1, and therefore its description is omitted. Furthermore, the fixed scroll member scroll teeth 124b, inner compression chamber 128b, suction section 128c, and outer periphery 128f of the suction section described in Embodiment 1 are shown in Embodiment 2 as the fixed scroll member scroll teeth 224b, inner compression chamber 228b, suction section 228c, and outer periphery 228f of the suction section.

[0059] An annular oil supply groove 224c is provided on the outer periphery of the fixed scroll member 224, which supplies refrigerant and oil 140 through communication with the back pressure chamber 129.

[0060] A sealing portion 225 is formed in the area surrounded by the inner periphery 224d of the annular oil supply groove 224c of the fixed scroll member 224 and the outer periphery 228e of the compression chamber 228, which is in sliding contact with the end plate 226a of the swirling scroll member.

[0061] The inner periphery 224d of the annular oil supply groove 224c is composed of multiple arcs with different curvatures, where Lαmin < Ls. Furthermore, in the range where the pressure within the annular oil supply groove 224c is higher than the pressure within the compression chamber 228, Lα gradually decreases as the crank angle α advances (increases). Conversely, in the range where the pressure within the annular oil supply groove 224c is lower than the pressure within the compression chamber 228, Lα gradually increases as the crank angle α advances (increases).

[0062] [2-2. Effects, etc.]

[0063] As described above, in this embodiment, the range in which the pressure in the annular oil supply groove 224c of the scroll compressor 200 is higher than the pressure in the compression chamber 228 gradually decreases as the crank angle α advances (increases). Furthermore, the range in which the pressure in the annular oil supply groove 224c is lower than the pressure in the compression chamber 228 gradually increases as the crank angle α advances (increases). This scroll compressor 200, like the scroll compressor 100 of Embodiment 1, can reliably suppress refrigerant and oil 140 leakage and reduce the sliding area between the fixed scroll end plate 224a and the rotating scroll end plate 126a. Therefore, it is possible to simultaneously suppress the reduction in compressor efficiency caused by deterioration in volumetric efficiency and compression efficiency, and reduce sliding losses.

[0064] Furthermore, the inner periphery 224d of the annular oil supply groove 224c of the scroll compressor 200 is composed of multiple arcs with different curvatures. Therefore, throughout the entire region of the compression chamber 228, the sealing length can be increased in areas where the pressure difference between the annular oil supply groove 224c and the compression chamber 228 is large, and decreased in areas where the pressure difference is small. Therefore, the scroll compressor 200 can reliably suppress refrigerant and oil 140 leakage, and compared to the scroll compressor 100 of Embodiment 1, further reduces the sliding area between the fixed scroll end plate 224a and the rotating scroll end plate 126a. Therefore, the scroll compressor 200 can further reduce sliding losses compared to the scroll compressor 100 of Embodiment 1.

[0065] Industrial availability

[0066] The scroll compressor of the present invention can both suppress the reduction of compressor efficiency and reduce sliding losses, and is useful for refrigeration cycle devices such as air conditioning devices, heat pump water heaters, hot water heating devices, and refrigerators.

[0067] Explanation of reference numerals in the attached figures

[0068] 100, 200 scroll compressors

[0069] 110 Closed Container

[0070] 112 Inhalation tube

[0071] 114 Discharge pipe

[0072] 116 Sealing components

[0073] 118 High-voltage area

[0074] 120 Compression Mechanism Department

[0075] 121 Muffler

[0076] 122 Main bearing assembly

[0077] 123 Rotation Restriction Agency

[0078] 124, 224 Fixed scroll components

[0079] 124a, 224a Fixed scroll end plate

[0080] 124b, 224b fixed scroll components scroll teeth

[0081] 124c and 224c annular oil supply grooves

[0082] Inner periphery of 124d and 224d annular oil supply grooves

[0083] 124e Fixed Scroll Center

[0084] The center of the inner periphery of the 124f annular oil supply groove

[0085] 125, 225 sealing parts

[0086] 126 gyratory scroll component

[0087] 126a and 226a vortex end plates

[0088] 126b Scroll component scroll teeth

[0089] 126c Connection Path

[0090] 126d supply path

[0091] 126e Boss section

[0092] 126F swivel bearing

[0093] 127 Discharge from the pressure chamber

[0094] Compression chambers 128 and 228

[0095] 128a, 228a outer compression chamber

[0096] 128b and 228b inner compression chambers

[0097] 128c, 228c inhalation unit

[0098] 128d Discharge Section

[0099] The outer periphery of the 128e and 228e compression chambers

[0100] The outer periphery of the 128f and 228f inhalation section

[0101] 129 Back pressure chamber

[0102] 130 Motor Department

[0103] 132 Stator

[0104] 134 rotor

[0105] 136 crankshaft

[0106] 136a Main Spindle Section

[0107] 136b Eccentric Shaft

[0108] 136c oil supply port

[0109] 138 Auxiliary bearing components

[0110] 140 oil

[0111] 142 Oil pump.

Claims

1. A scroll compressor, characterized in that, include: Sealed container; and The compression mechanism, disposed within the sealed container, compresses the refrigerant. The compression mechanism includes a fixed scroll member and a rotating scroll member. The fixed scroll component has a fixed scroll component end plate and scroll-shaped fixed scroll component scroll teeth that stand upright from the fixed scroll component end plate. The swirling scroll component has a swirling scroll component end plate and swirling scroll component vortex teeth that stand upright from the swirling scroll component end plate. By engaging the vortex teeth of the fixed vortex component with those of the rotary vortex component, multiple compression chambers are formed between the vortex teeth of the fixed vortex component and the rotary vortex component. The compression chamber comprises: an outer compression chamber located outside the vortex teeth of the vortex member; an inner compression chamber located inside the vortex teeth of the vortex member; an intake section located at the outermost periphery of the compression chamber, which guides the intake refrigerant into the interior of the compression chamber; and a discharge section located at the innermost periphery of the compression chamber, which discharges the discharge refrigerant from the interior of the compression chamber into the interior of the sealed container. The outer compression chamber has a larger volume when the refrigerant is fully sealed compared to the inner compression chamber. An annular oil supply groove is formed on the sliding surface where the fixed scroll end plate contacts the rotating scroll end plate. The pressure within the annular oil supply groove is any pressure between the suction pressure and the discharge pressure. The scroll compressor includes a sealing portion surrounded by the inner periphery of the annular oil supply groove, the outer compression chamber, and the outer periphery of the suction section. When the moment when the refrigerant is completely sealed in the outer compression chamber is set as the crank angle of 0°, if the compression chamber sealing length from the contact point where the fixed scroll tooth and the rotary scroll tooth meet at the outermost periphery of the compression chamber to the inner periphery of the annular oil supply groove is set as Lα when the crank angle α is α > 0°, and the compression chamber sealing length from the contact point where the fixed scroll tooth and the rotary scroll tooth meet at the outermost periphery of the compression chamber to the inner periphery of the annular oil supply groove and the suction section sealing length from the outer periphery of the suction section to the inner periphery of the annular oil supply groove are set as Ls when the crank angle is 0°, then Ls is larger than the minimum Lα.

2. The scroll compressor according to claim 1, characterized in that: The inner periphery of the annular oil supply groove is formed by a circle, and the center of the inner periphery of the annular oil supply groove is off-center from the center of the end plate of the fixed vortex component.

3. The scroll compressor according to claim 1, characterized in that: The inner periphery of the annular oil supply groove is composed of multiple arcs with different curvatures.

4. The scroll compressor according to claim 1 or 3, characterized in that: Within the range where the pressure in the annular oil supply groove is higher than the pressure in the compression chamber. As the crank angle α increases, Lα gradually decreases.

5. The scroll compressor according to claim 1 or 3, characterized in that: Within the range where the pressure in the annular oil supply groove is lower than the pressure in the compression chamber, As the crank angle α increases, Lα gradually increases.

6. The scroll compressor according to claim 4, characterized in that: Within the range where the pressure in the annular oil supply groove is lower than the pressure in the compression chamber, As the crank angle α increases, Lα gradually increases.

Images