Scroll compressor, and refrigerator

Abstract

To solve the problem that there is the risk of difficulty for a lubricant to enter a gap, which is formed on a thrust slide surface if a height of a lap of a movable scroll is reduced for securing a strength in a scroll compressor.SOLUTION: A stationary-side lap 21b of a stationary scroll 21 includes a first region R1 and a second region R2. The first region R1 is a region from winding end 21e to a stationary-side reference point 21f. The second region R2 is a region from the stationary-side reference point 21f to winding start 21s. A movable-side lap 22b of a movable scroll 22 includes a third region R3 and a fourth region R4. The third region R3 is a region from winding end 22e to a movable-side reference point 22f. The fourth region R4 is a region from the movable-side reference point 22f to winding start 22s. A first dimension in the first region R1 is shorter than the first dimension in the second region R2 just by a first length h1. A second dimension in the third region R3 is shorter than the second dimension in the fourth region R4 just by a second length h2.SELECTED DRAWING: Figure 8

Description

[Technical Field]

[0001] The present invention relates to a scroll compressor and a refrigeration device. [Background technology]

[0002] Conventionally, as disclosed in Patent Document 1 (JP 2000-337276 A), a scroll compressor is known in which a floating member presses a movable scroll against a fixed scroll to prevent refrigerant from leaking from the compression chamber through the tip end surface of the scroll wrap. Summary of the Invention [Problem to be solved by the invention]

[0003] In the scroll compressor disclosed in Patent Document 1 (JP 2000-337276 A), a compressive load generated by the pressure of the refrigerant in the compression chamber acts on the wrap of the movable scroll during operation. The compressive load, a tangential gas load acting in the opposite direction to the direction of movement of the movable scroll, causes the movable scroll to tilt relative to the fixed scroll as it orbits. The tilt of the movable scroll forms a gap on the thrust sliding surface between the movable scroll and the floating member, and lubricating oil is supplied to this gap. However, if the height of the movable scroll wrap is reduced to ensure the strength of the wrap, the tangential gas load is reduced, and the tilt of the movable scroll during orbiting is also reduced. This makes it difficult for lubricating oil to enter the gap formed on the thrust sliding surface, potentially damaging the thrust bearing. [Means for solving the problem]

[0004] A scroll compressor according to a first aspect includes a compression mechanism, a floating member, and a housing. The compression mechanism includes a fixed scroll and a movable scroll. The fixed scroll includes a fixed end plate and a fixed wrap. The movable scroll includes a movable end plate and a movable wrap. The floating member is pressed toward the movable scroll by pressure in the back pressure space, thereby pressing the movable scroll toward the fixed scroll. The housing supports the floating member, and forms a back pressure space between the floating member and the floating member. The fixed wrap extends in a spiral shape from a first point, which is an end on the outer circumferential side, to a second point, which is an end on the inner circumferential side. The fixed wrap extends from a first main surface of the fixed end plate along a first direction with a predetermined first dimension. The movable wrap extends in a spiral shape from a third point, which is an end on the outer circumferential side, to a fourth point, which is an end on the inner circumferential side. The movable side wrap extends in the first direction from a second main surface of the movable side end plate opposite the first main surface, having a predetermined second dimension. The fixed side wrap has a first region and a second region. The first region is a region from the first point to a fifth point that contacts the third point during orbital movement of the movable scroll. The second region is a region from the fifth point to the second point. The movable side wrap has a third region and a fourth region. The third region is a region from the third point to a sixth point that contacts the first point during orbital movement of the movable scroll. The fourth region is a region from the sixth point to the fourth point. The first dimension in the first region is shorter than the first dimension in the second region by a first length. The second dimension in the third region is shorter than the second dimension in the fourth region by a second length.

[0005] In the scroll compressor of the first aspect, the moment that acts to suppress the tilt of the orbiting scroll during orbiting is reduced, and excessive reduction in the tilt of the orbiting scroll during orbiting is suppressed, thereby suppressing the occurrence of the problem of insufficient supply of lubricating oil between the orbiting scroll and the floating member.

[0006] A scroll compressor according to a second aspect includes a compression mechanism, a floating member, and a housing. The compression mechanism includes a fixed scroll and a movable scroll. The fixed scroll includes a fixed end plate and a fixed wrap. The movable scroll includes a movable end plate and a movable wrap. The floating member is pressed toward the movable scroll by the pressure in the back pressure space, thereby pressing the movable scroll toward the fixed scroll. The housing supports the floating member, and forms a back pressure space between the floating member and the floating member. The fixed wrap extends in a spiral shape from a first point, which is an end on the outer circumferential side, to a second point, which is an end on the inner circumferential side. The fixed wrap extends from a first main surface of the fixed end plate along a first direction with a predetermined first dimension. The movable wrap extends in a spiral shape from a third point, which is an end on the outer circumferential side, to a fourth point, which is an end on the inner circumferential side. The movable side wrap extends in the first direction and has a predetermined second dimension from the second main surface of the movable side end plate, which faces the first main surface. The fixed side wrap has a first region and a second region. The first region is the region from the first point to a fifth point that contacts the third point during orbital movement of the movable scroll. The second region is the region from the fifth point to the second point. The movable side wrap has a third region and a fourth region. The third region is the region from the third point to a sixth point that contacts the first point during orbital movement of the movable scroll. The fourth region is the region from the sixth point to the fourth point. The first main surface facing the tip end face of the third region is recessed by a first length in a direction away from the second main surface relative to the first main surface facing the tip end face of the fourth region. The second main surface facing the tip surface of the first region is recessed by a second length in a direction away from the first main surface relative to the second main surface facing the tip surface of the second region.

[0007] In the scroll compressor of the second aspect, the moment that acts to suppress the tilt of the orbiting scroll during orbiting is reduced, and excessive reduction in the tilt of the orbiting scroll during orbiting is suppressed, thereby suppressing the occurrence of the problem of insufficient supply of lubricating oil between the orbiting scroll and the floating member.

[0008] A scroll compressor according to a third aspect is the scroll compressor according to the first or second aspect, wherein the lower limit values ​​of the first length and the second length are displacement amounts in the first direction of the orbiting scroll.

[0009] A scroll compressor according to a fourth aspect is the scroll compressor according to the third aspect, wherein the lower limit values ​​of the first length and the second length are equal to or greater than 1 / 1000 of the first dimension in the third region.

[0010] A scroll compressor of a fifth aspect is the scroll compressor of any one of the first to fourth aspects, wherein the upper limit values ​​of the first length and the second length are the minimum values ​​of the distance in the first direction between the tip end surface of the movable side wrap and the first main surface when the movable scroll is not rotating.

[0011] A scroll compressor according to a sixth aspect is the scroll compressor according to the fifth aspect, wherein the upper limit values ​​of the first length and the second length are 150 μm to 250 μm.

[0012] A scroll compressor according to a seventh aspect is the scroll compressor according to the first aspect, wherein the first main surface facing the tip end face of the third region is recessed by a third length in a direction away from the second main surface relative to the first main surface facing the tip end face of the fourth region, and the second main surface facing the tip end face of the first region is recessed by a fourth length in a direction away from the first main surface relative to the second main surface facing the tip end face of the second region.

[0013] A refrigeration apparatus according to an eighth aspect includes the scroll compressor according to any one of the first to seventh aspects, and a refrigerant circuit through which refrigerant compressed by the scroll compressor flows. [Brief explanation of the drawings]

[0014] [Figure 1] 1 is a refrigerant circuit diagram of a refrigeration device 100 according to an embodiment. [Figure 2] FIG. 1 is a vertical cross-sectional view of a scroll compressor 101 according to an embodiment. [Figure 3] 3 is an enlarged view of the floating member 30 and its surroundings of the scroll compressor 101 in FIG. 2. FIG. [Figure 4] FIG. 2 is a plan view of a fixed scroll 21 according to the embodiment. [Figure 5] FIG. 2 is a plan view of the movable scroll 22 of the embodiment. [Figure 6A] 5B is a diagram showing the state in which the fixed scroll 21 and the movable scroll 22 are engaged with each other, as viewed from above with the fixed-side end plate 21a removed. It is a diagram showing the state at the time when the first compression chamber Sc1 and the second compression chamber Sc2 are formed. It is a diagram showing the state in which the phase is advanced by 90° from FIG. 5D. [Figure 6B] FIG. 6B is a diagram showing a state in which the phase is advanced by 90° from that of FIG. 6A. [Figure 6C] FIG. 6C is a diagram showing a state in which the phase is advanced by 90° from FIG. 6B. [Figure 6D] FIG. 6D is a diagram showing a state in which the phase is advanced by 90° from that of FIG. 6C. [Figure 7] 3A and 3B are schematic diagrams for explaining forces acting on a movable scroll 22 during orbiting. [Figure 8] 5 is a cross-sectional view of the fixed scroll 21 taken along line AA in FIG. 4. FIG. [Figure 9] 6 is a cross-sectional view of the movable scroll 22 taken along line BB in FIG. 5. [Figure 10] FIG. 2 is a vertical cross-sectional view of a compression mechanism 20 according to the embodiment. [Figure 11] FIG. 10 is a diagram for explaining a moment acting on a conventional movable scroll 22 as a comparative example. [Figure 12] FIG. 10 is a diagram for explaining a moment acting on a conventional movable scroll 22 as a comparative example. [Figure 13] 4A and 4B are diagrams for explaining a moment acting on a movable scroll 22 of the embodiment. [Figure 14] 4A and 4B are diagrams for explaining a moment acting on a movable scroll 22 of the embodiment. [Figure 15] FIG. 10 is a cross-sectional view of a fixed scroll 21 of a modified example A. [Figure 16] FIG. 10 is a cross-sectional view of a movable scroll 22 of a modified example A. [Figure 17]FIG. 4 is a vertical cross-sectional view of a compression mechanism 20 of a modified example A. [Figure 18] 10 is a diagram for explaining a moment acting on the movable scroll 22 of the modification A. FIG. [Figure 19] 10 is a diagram for explaining a moment acting on the movable scroll 22 of the modification A. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0015] (1) Overall structure As shown in FIG. 1 , a scroll compressor 101, which is one embodiment of the compressor of the present disclosure, is provided in a refrigeration system 100. The refrigeration system 100 utilizes a vapor compression refrigeration cycle. The refrigeration system 100 is, for example, an air conditioner or a hot water supply system. The refrigeration system 100 includes a refrigerant circuit 110 filled with a refrigerant. The refrigerant circuit 110 includes the scroll compressor 101, a radiator 102, a pressure reduction mechanism 103, and a heat absorber 104. The radiator 102 and the heat absorber 104 are heat exchangers. The pressure reduction mechanism 103 is, for example, an expansion valve.

[0016] The scroll compressor 101 is a hermetic compressor. The scroll compressor 101 draws in low-pressure refrigerant in a refrigeration cycle, compresses the drawn refrigerant, and discharges high-pressure refrigerant in the refrigeration cycle. The refrigerant discharged from the scroll compressor 101 flows through a refrigerant circuit 110 along the arrows shown in Figure 1 and is drawn in again.

[0017] As shown in FIG. 2, the scroll compressor 101 includes a casing 10, a compression mechanism 20, a floating member 30, an upper housing 40, a seal member 60, a motor 70, a crankshaft 80, and a lower bearing housing 90.

[0018] (2) Detailed configuration (2-1) Casing 10 The casing 10 has a substantially cylindrical shape. The casing 10 is disposed so that the longitudinal direction of the substantially cylindrical shape of the casing 10 is aligned with the vertical direction. In Fig. 2, the vertical direction (first direction) is indicated by an arrow D1.

[0019] The casing 10 accommodates a compression mechanism 20, a floating member 30, an upper housing 40, a seal member 60, a motor 70, a crankshaft 80, and a lower bearing housing 90.

[0020] The compression mechanism 20 is disposed at the top of the casing 10. The floating member 30 and the upper housing 40 are disposed below the compression mechanism 20. The motor 70 is disposed below the upper housing 40. The lower bearing housing 90 is disposed below the motor 70. An oil reservoir space 11 is formed at the bottom of the casing 10. Refrigeration oil for lubricating the compression mechanism 20 and the like is stored in the oil reservoir space 11.

[0021] The internal space of the casing 10 is divided into a first space S1 and a second space S2 by a partition plate 16. The first space S1 is the space below the partition plate 16 in the vertical direction. The second space S2 is the space above the partition plate 16 in the vertical direction. The partition plate 16 is fixed to the casing 10 and the compression mechanism 20 so as to maintain airtightness between the first space S1 and the second space S2.

[0022] The partition plate 16 is a plate-like member formed in an annular shape in a plan view. The inner peripheral side of the partition plate 16 is fixed over the entire circumference to an upper portion of the fixed scroll 21 of the compression mechanism 20. The outer peripheral side of the partition plate 16 is fixed over the entire circumference to the inner surface of the casing 10.

[0023] The first space S1 is a space in which the motor 70 is disposed. The first space S1 is a space into which refrigerant flows from the refrigerant circuit 110 before being compressed by the scroll compressor 101. The first space S1 is a space into which low-pressure refrigerant in the refrigeration cycle flows.

[0024] The second space S2 is a space into which the refrigerant discharged from the compression mechanism 20 (refrigerant compressed by the compression mechanism 20) flows. The second space S2 is a space into which high-pressure refrigerant in the refrigeration cycle flows.

[0025] A suction pipe 13, a discharge pipe 14, and an injection pipe 15 are attached to the casing 10 so as to communicate between the inside and outside of the casing 10.

[0026] The suction pipe 13 is attached near the center of the casing 10 in the longitudinal direction (vertical direction). Specifically, the suction pipe 13 is attached at a height position between the upper housing 40 and the motor 70. The suction pipe 13 communicates between the outside of the casing 10 and a first space S1 inside the casing 10. The refrigerant before compression (low-pressure refrigerant in the refrigeration cycle) passes through the suction pipe 13 and flows into the first space S1.

[0027] The discharge pipe 14 is attached to the upper part of the casing 10 at a height position above the partition plate 16. The discharge pipe 14 connects the outside of the casing 10 with a second space S2 inside the casing 10. The refrigerant compressed by the compression mechanism 20 and flowing into the second space S2 (high-pressure refrigerant in the refrigeration cycle) passes through the discharge pipe 14 and flows out of the scroll compressor 101.

[0028] The injection pipe 15 is attached to the upper part of the casing 10 at a height position below the partition plate 16. The injection pipe 15 is attached so as to penetrate the casing 10. As shown in FIG. 2, the end of the injection pipe 15 on the inside side of the casing 10 is connected to the fixed scroll 21 of the compression mechanism 20. The injection pipe 15 communicates with the compression chamber Sc in the middle of compression inside the compression mechanism 20 via a passage (not shown) formed in the fixed scroll 21. An intermediate-pressure refrigerant (refrigerant with a pressure intermediate between low pressure and high pressure in the refrigeration cycle) is supplied from the refrigerant circuit 110 through the injection pipe 15 to the compression chamber Sc in the middle of compression.

[0029] (2-2) Compression mechanism 20 The compression mechanism 20 has a fixed scroll 21 and a movable scroll 22. The fixed scroll 21 and the movable scroll 22 are combined with each other to form a compression chamber Sc. The compression mechanism 20 compresses the refrigerant in the compression chamber Sc and discharges the compressed refrigerant. The compression mechanism 20 has a symmetric wrap structure, as described below.

[0030] (2-2-1) Fixed Scroll 21 2, the fixed scroll 21 is mounted on the upper housing 40. The fixed scroll 21 and the upper housing 40 are fixed to each other by fixing means (for example, bolts) not shown.

[0031] The fixed scroll 21 has a disk-shaped fixed end plate 21a, a spiral-shaped fixed wrap 21b, and a peripheral edge portion 21c. The fixed wrap 21b and the peripheral edge portion 21c extend vertically from the lower surface of the fixed end plate 21a toward the movable scroll 22 (downward). When the fixed scroll 21 is viewed vertically from below, the fixed wrap 21b is formed in a spiral shape (involute shape) from near the center of the fixed end plate 21a toward the outer periphery. The peripheral edge portion 21c has a cylindrical shape. The peripheral edge portion 21c is arranged on the outer periphery of the fixed end plate 21a so as to surround the fixed wrap 21b.

[0032] During operation of the scroll compressor 101, the movable scroll 22 orbits relative to the fixed scroll 21. As a result, the refrigerant (low-pressure refrigerant in the refrigeration cycle) that flows from the first space S1 into the compression chambers Sc on the peripheral side is compressed as it moves toward the innermost (central) compression chamber Sc. A discharge port 21d that discharges the refrigerant compressed in the compression chambers Sc is formed near the center of the fixed-side end plate 21a. The discharge port 21d is a hole that penetrates the fixed-side end plate 21a in the thickness direction (vertical direction). The discharge port 21d communicates with the innermost compression chamber Sc. A discharge valve 23 that opens and closes the discharge port 21d is attached above the fixed-side end plate 21a. When the pressure in the innermost compression chamber Sc that communicates with the discharge port 21d becomes greater than the pressure in the space above the discharge valve 23 (second space S2) by a predetermined value or more, the discharge valve 23 opens, and the refrigerant flows from the compression chamber Sc into the second space S2 via the discharge port 21d.

[0033] A relief hole 21e is formed on the outer circumferential side of the discharge port 21d of the fixed side end plate 21a. The relief hole 21e is a hole that penetrates the fixed side end plate 21a in the thickness direction. The relief hole 21e communicates with a compression chamber Sc that is formed on the outer circumferential side of the innermost compression chamber Sc that communicates with the discharge port 21d. The relief hole 21e communicates with a compression chamber Sc that is in the middle of compression in the compression mechanism 20. A plurality of relief holes 21e may be formed in the fixed side end plate 21a. A relief valve 24 that opens and closes the relief hole 21e is attached above the fixed side end plate 21a. When the pressure of the compression chamber Sc that communicates with the relief hole 21e becomes higher than the pressure in the space above the relief valve 24 (second space S2) by a predetermined value or more, the relief valve 24 opens, and refrigerant flows from the compression chamber Sc into the second space S2 through the relief hole 21e.

[0034] (2-2-2) Movable Scroll 22 The movable scroll 22 has a disk-shaped movable end plate 22a, a spiral movable end wrap 22b, and a cylindrical boss portion 22c. The movable end wrap 22b extends vertically from the upper surface of the movable end plate 22a toward the fixed scroll 21 (upward). The boss portion 22c extends vertically from the lower surface of the movable end plate 22a toward the opposite side of the fixed scroll 21 (downward). When the movable scroll 22 is viewed from above in the vertical direction, the movable end wrap 22b is formed in a spiral shape (involute shape) from near the center of the movable end plate 22a toward the outer periphery.

[0035] The fixed-side wrap 21b of the fixed scroll 21 and the movable-side wrap 22b of the movable scroll 22 are fitted together to form a compression chamber Sc. The fixed scroll 21 and the movable scroll 22 are fitted together so that the lower surface of the fixed-side end plate 21a faces the upper surface of the movable-side end plate 22a. This forms a compression chamber Sc surrounded by the fixed-side end plate 21a, the fixed-side wrap 21b, the movable-side wrap 22b, and the movable-side end plate 22a.

[0036] In the compression mechanism 20 having a symmetrical wrap structure, a compression chamber Sc (first compression chamber Sc1 in FIGS. 6A to 6D) surrounded by the outer peripheral surface of the movable-side wrap 22b and the inner peripheral surface of the fixed-side wrap 21b, and a compression chamber Sc (second compression chamber Sc2 in FIGS. 6A to 6D) surrounded by the inner peripheral surface of the movable-side wrap 22b and the outer peripheral surface of the fixed-side wrap 21b, are formed symmetrically about a point when viewed in the vertical direction. The winding end angle of the movable-side wrap 22b is the same as the winding end angle of the fixed-side wrap 21b. The winding end angle of the movable-side wrap 22b is the angle in the spiral direction (circumferential direction) of the outer peripheral end (winding end) of the movable-side head 22a, when the end (winding start) of the center side of the movable-side head 22a is set as the base point (0°). The winding end angle of the fixed side wrap 21b is the angle in the spiral direction (circumferential direction) of the outer peripheral end (winding end) of the fixed side head 21a, when the center end (winding start) of the fixed side head 21a is set as the base point (0°). In the compression mechanism 20 having a symmetrical wrap structure, the refrigerant is compressed in the first compression chamber Sc1 and the refrigerant is compressed in the second compression chamber Sc2 at the same time. The fixed scroll 21 and the movable scroll 22 will be described in detail later.

[0037] The movable side end plate 22a is disposed above the floating member 30. During operation of the scroll compressor 101, the floating member 30 is pressed toward the movable scroll 22 by the pressure of a back pressure space B0 formed below the floating member 30. As a result, when the pressing portion 34 at the upper part of the floating member 30 comes into contact with the lower surface of the movable side end plate 22a, the floating member 30 presses the movable scroll 22 toward the fixed scroll 21. The force with which the floating member 30 presses the movable scroll 22 toward the fixed scroll 21 causes the movable scroll 22 to come into close contact with the fixed scroll 21. This suppresses refrigerant leakage from gaps between the tooth tips (tip end surface) of the fixed side wrap 21b and the bottom surface (main surface in contact with the tooth tips) of the movable side end plate 22a, and from gaps between the tooth tips of the movable side wrap 22b and the bottom surface of the fixed side end plate 21a.

[0038] The back pressure space B0 is a space formed between the floating member 30 and the upper housing 40. As shown in FIG. 3, the back pressure space B0 is formed on the rear side (lower side) of the floating member 30. Refrigerant from the compression chamber Sc of the compression mechanism 20 is guided into the back pressure space B0. The back pressure space B0 and the first space S1 surrounding the back pressure space B0 are sealed. During operation of the scroll compressor 101, the pressure in the back pressure space B0 is higher than the pressure in the first space S1.

[0039] An Oldham coupling 25 is disposed between the movable scroll 22 and the floating member 30. The Oldham coupling 25 slidably engages with both the movable scroll 22 and the floating member 30. The Oldham coupling 25 restricts the rotation of the movable scroll 22 and allows the movable scroll 22 to orbit relative to the fixed scroll 21.

[0040] The boss portion 22c is disposed in an eccentric space 38 surrounded by the inner surface of the floating member 30. A bearing metal 26 is disposed inside the boss portion 22c. The bearing metal 26 is, for example, press-fitted and fixed inside the boss portion 22c. An eccentric portion 81 of a crankshaft 80 is inserted into the bearing metal 26. By inserting the eccentric portion 81 into the bearing metal 26, the movable scroll 22 and the crankshaft 80 are connected.

[0041] (2-3) Floating member 30 The floating member 30 is disposed on the back side of the movable scroll 22 (the side opposite to the side on which the fixed scroll 21 is disposed). The floating member 30 is pressed toward the movable scroll 22 by the pressure in the back pressure space B0, thereby pressing the movable scroll 22 toward the fixed scroll 21. A portion of the floating member 30 also functions as a bearing that supports the crankshaft 80.

[0042] The floating member 30 has a cylindrical portion 30 a, a pressing portion 34 , and an upper bearing housing 31 .

[0043] The cylindrical portion 30a defines an eccentric space 38 surrounded by the inner surface of the cylindrical portion 30a. The boss portion 22c of the movable scroll 22 is disposed in the eccentric space 38.

[0044] The pressing portion 34 is a cylindrical member extending from the upper end of the cylindrical portion 30a toward the movable scroll 22. As shown in FIG. 3 , a thrust surface 34a at the upper end of the pressing portion 34 faces the back surface of the movable end plate 22a of the movable scroll 22. The thrust surface 34a is formed in an annular shape in a plan view. When the floating member 30 is pressed toward the movable scroll 22 by the pressure in the back pressure space B0, the thrust surface 34a comes into contact with the back surface of the movable end plate 22a, pressing the movable scroll 22 toward the fixed scroll 21.

[0045] The upper bearing housing 31 is a cylindrical member disposed below the cylindrical portion 30a (below the eccentric portion space 38). A bearing metal 32 is disposed inside the upper bearing housing 31. The bearing metal 32 is, for example, press-fitted and fixed inside the upper bearing housing 31. The bearing metal 32 rotatably supports a main shaft 82 of the crankshaft 80.

[0046] (2-4) Upper housing 40 The upper housing 40 is a substantially cylindrical member disposed below the fixed scroll 21 and the floating member 30. The upper housing 40 supports the floating member 30. A back pressure space B0 is formed between the upper housing 40 and the floating member 30. The upper housing 40 is attached to the inner surface of the casing 10 by, for example, press fitting.

[0047] (2-5) Sealing member 60 The seal member 60 is a member for forming a back pressure space B0 between the floating member 30 and the upper housing 40. The seal member 60 is, for example, a gasket such as an O-ring. As shown in FIG. 3, the seal member 60 divides the back pressure space B0 into a first chamber B1 and a second chamber B2. The first chamber B1 and the second chamber B2 are spaces formed in a substantially annular shape in a plan view. The second chamber B2 is disposed inside the first chamber B1. In a plan view, the area of ​​the first chamber B1 is larger than the area of ​​the second chamber B2.

[0048] The first chamber B1 communicates with the compression chamber Sc in the middle of compression via a first flow path 64. The first flow path 64 is a flow path that guides the refrigerant in the middle of compression in the compression mechanism 20 (intermediate-pressure refrigerant) to the first chamber B1. The first flow path 64 is formed in the fixed scroll 21 and the upper housing 40.

[0049] The second chamber B2 communicates with the discharge port 21d of the fixed scroll 21 via a second flow path 65. The second flow path 65 is a flow path that guides the refrigerant (high-pressure refrigerant) discharged from the compression mechanism 20 to the second chamber B2. The second flow path 65 is formed in the fixed scroll 21 and the upper housing 40.

[0050] During operation of the scroll compressor 101, the pressure in the second chamber B2 is higher than the pressure in the first chamber B1. However, because the area of ​​the first chamber B1 is larger than the area of ​​the second chamber B2 in a plan view, the pressure in the back pressure space B0 does not easily exert an excessive pressing force on the movable scroll 22 against the fixed scroll 21. Because the second chamber B2 is located more inward than the first chamber B1, a balance is easily maintained between the force with which the movable scroll 22 is pressed downward by the pressure in the compression chamber Sc and the force with which the floating member 30 presses the movable scroll 22 upward.

[0051] (2-6) Motor 70 The motor 70 drives the movable scroll 22. The motor 70 has a stator 71 and a rotor 72. The stator 71 is an annular member fixed to the inner surface of the casing 10. The rotor 72 is a cylindrical member disposed inside the stator 71. A small gap (air gap) is formed between the inner peripheral surface of the stator 71 and the outer peripheral surface of the rotor 72.

[0052] A crankshaft 80 passes through the rotor 72 along its axial direction. The rotor 72 is connected to the movable scroll 22 via the crankshaft 80. The motor 70 drives the movable scroll 22 by rotating the rotor 72, causing the movable scroll 22 to orbit relative to the fixed scroll 21.

[0053] (2-7) Crankshaft 80 The crankshaft 80 connects the rotor 72 of the motor 70 and the movable scroll 22 of the compression mechanism 20. The crankshaft 80 extends in the vertical direction. The crankshaft 80 transmits the driving force of the motor 70 to the movable scroll 22.

[0054] The crankshaft 80 has an eccentric portion 81 and a main shaft 82 .

[0055] The eccentric portion 81 is disposed above the main shaft 82. The central axis of the eccentric portion 81 is eccentric with respect to the central axis of the main shaft 82. The eccentric portion 81 is connected to the bearing metal 26 disposed inside the boss portion 22c of the movable scroll 22.

[0056] The main shaft 82 is rotatably supported by a bearing metal 32 disposed in the upper bearing housing 31 of the floating member 30 and a bearing metal 91 disposed in the lower bearing housing 90. The main shaft 82 is connected to the rotor 72 of the motor 70 between the upper bearing housing 31 and the lower bearing housing 90. The main shaft 82 extends in the vertical direction.

[0057] An oil passage (not shown) is formed inside the crankshaft 80. The oil passage has a main path (not shown) and branch paths (not shown). The main path extends in the axial direction of the crankshaft 80 from the lower end to the upper end of the crankshaft 80. The branch paths extend from the main path in the radial direction of the crankshaft 80. Refrigeration oil in the oil reservoir space 11 is pumped up by a pump (not shown) provided at the lower end of the crankshaft 80, and is supplied through the oil passage to sliding parts between the crankshaft 80 and each bearing metal 26, 32, 91, sliding parts of the compression mechanism 20, etc.

[0058] (2-8) Lower bearing housing 90 The lower bearing housing 90 is fixed to the inner surface of the casing 10. The lower bearing housing 90 is disposed below the motor 70. A bearing metal 91 is disposed inside the lower bearing housing 90. The bearing metal 91 is, for example, press-fitted and fixed inside the lower bearing housing 90. The main shaft 82 of the crankshaft 80 passes through the bearing metal 91. The bearing metal 91 rotatably supports the lower side of the main shaft 82 of the crankshaft 80.

[0059] (3) Operation of the scroll compressor 101 The operation of the scroll compressor 101 in a normal state will be described below. The normal state is a state in which the pressure of the refrigerant discharged from the discharge port 21d of the compression mechanism 20 is higher than the pressure in the compression chamber Sc during compression.

[0060] When the motor 70 is driven, the rotor 72 rotates, and the crankshaft 80 connected to the rotor 72 also rotates. When the crankshaft 80 rotates, the Oldham coupling 25 causes the movable scroll 22 to orbit relative to the fixed scroll 21 without rotating on its own axis. Low-pressure refrigerant that flows into the first space S1 from the suction pipe 13 passes through a refrigerant passage (not shown) formed in the upper housing 40 and is drawn into the compression chamber Sc on the peripheral side of the compression mechanism 20. When the movable scroll 22 orbits, the first space S1 and the compression chamber Sc are no longer in communication, the volume of the compression chamber Sc decreases, and the pressure of the compression chamber Sc increases. Refrigerant is injected from the injection pipe 15 into the compression chamber Sc during compression. The pressure of the refrigerant increases as it moves from the compression chamber Sc on the peripheral side (outer side) to the compression chamber Sc on the central side (inner side), eventually reaching high pressure in the refrigeration cycle. The refrigerant compressed by the compression mechanism 20 is discharged from the discharge port 21d of the fixed side end plate 21a into the second space S2. The high-pressure refrigerant in the second space S2 is discharged from the discharge pipe .

[0061] (4) Detailed configuration of the fixed scroll 21 and the movable scroll 22 4, the fixed-side wrap 21b is formed to extend spirally from a winding start 21s (second point), which is the end on the center side (inner peripheral side) of the fixed-side end plate 21a, to a winding end 21e (first point), which is the end on the outer peripheral side, in a plan view. The fixed-side wrap 21b extends in the vertical direction (first direction) from a first main surface 21p, which is the lower main surface of the fixed-side end plate 21a, having a predetermined fixed-side dimension (first dimension). The fixed-side dimension is the vertical dimension of the fixed-side wrap 21b from the first main surface 21p, which is connected to the fixed-side wrap 21b, to the tip surface of the fixed-side wrap 21b.

[0062] As shown in FIG. 5, the movable-side wrap 22b is formed in a spiral shape extending from a winding start 22s (fourth point), which is the end on the center side (inner peripheral side) of the movable-side head plate 22a, to a winding end 22e (third point), which is the end on the outer peripheral side, in a plan view. The movable-side wrap 22b extends vertically from a second main surface 22p, which is the upper main surface of the movable-side head plate 22a, having a predetermined movable-side dimension (second dimension). The movable-side dimension is the vertical dimension of the movable-side wrap 22b from the second main surface 22p, which is connected to the lower end of the movable-side wrap 22b, to the tip surface of the movable-side wrap 22b. The second main surface 22p of the movable-side head plate 22a faces the first main surface 21p of the fixed-side head plate 21a.

[0063] 6A to 6D show the transition of states while the movable scroll 22 makes one revolution (360°) relative to the fixed scroll 21. Each of FIGS. 6A to 6D shows a state where the phase is advanced by 90° from the previous state. In other words, each of FIGS. 6A to 6D shows a state where the movable scroll 22 has made a 90° revolution from the previous state. In FIGS. 6A to 6D, the fixed side wrap 21b and the movable side wrap 22b are indicated by hatched areas.

[0064] As shown in Figures 6A to 6D, the fixed scroll 21 and the movable scroll 22 form a first compression chamber Sc1 and a second compression chamber Sc2 while the movable scroll 22 orbits. Figure 6A shows a state in which the outer peripheries of the fixed side wrap 21b and the movable side wrap 22b are closed and the refrigerant suction process is completed. In other words, Figure 6A shows a state at a first point in time when the first compression chamber Sc1 and the second compression chamber Sc2 are formed.

[0065] As shown in Fig. 4, the fixed-side wrap 21b has a fixed-side reference point 21f (fifth point) in a plan view. As shown in Fig. 6A, at a first point in time, the fixed-side reference point 21f is in a position where it contacts the winding end 22e of the movable-side wrap 22b. The fixed-side reference point 21f is located approximately 0.5 turns from the winding end 21e toward the winding start 21s.

[0066] Here, a point one revolution from a specified point means a point one revolution (360°) from the specified point along the direction in which the spiral of the wrap extends when the fixed side wrap 21b and the movable side wrap 22b are viewed in a plane.

[0067] As shown in Fig. 5, the movable side wrap 22b has a movable side reference point 22f (sixth point) in a plan view. As shown in Fig. 6A, at a first point in time, the movable side reference point 22f is in a position where it contacts the winding end 21e of the fixed side wrap 21b. The movable side reference point 22f is located approximately 0.5 turns from the winding end 22e toward the winding start 22s.

[0068] The fixed-side wrap 21b has a first region R1 and a second region R2 along the direction in which the spiral extends in a plan view. The first region R1 extends from the winding end 21e to the fixed-side reference point 21f. The second region R2 extends from the fixed-side reference point 21f to the winding start 21s. In Figure 4, the first region R1 is shown hatched.

[0069] The movable-side wrap 22b has a third region R3 and a fourth region R4 along the direction in which the spiral extends in a plan view. The third region R3 extends from the end of the spiral 22e to the movable-side reference point 22f. The fourth region R4 extends from the movable-side reference point 22f to the start of the spiral 22s. In Figure 5, the third region R3 is shown hatched.

[0070] During normal operation of the scroll compressor 101, a compressive load caused by the pressure of the refrigerant in the first compression chamber Sc1 and the second compression chamber Sc2 acts on the movable-side wrap 22b, causing the movable-side end plate 22a to tilt relative to the horizontal plane. Therefore, during operation of the scroll compressor 101, the movable scroll 22 orbits while tilting relative to the fixed scroll 21.

[0071] FIG. 7 shows the forces acting on the orbiting orbiting scroll 22 when the orbiting side wrap 22b is viewed from above in the vertical direction. FIG. 7 shows the state at the moment when the orbiting scroll 22 is eccentric to the right side of the page. In FIG. 7, arrow 22r indicates the orbiting direction of the orbiting scroll 22. A centrifugal force Fc, a radial gas load Fgr, and a tangential gas load Fgt act on the orbiting scroll 22. The centrifugal force Fc acts in the eccentric direction of the orbiting scroll 22. The radial gas load Fgr acts in the opposite direction to the eccentric direction of the orbiting scroll 22 due to a compressive load. The tangential gas load Fgt acts in the opposite direction to the advancing direction of the orbiting scroll 22 (the tangential direction of the orbiting motion) due to a compressive load. The tangential gas load Fgt acts in a direction perpendicular to the radial gas load Fgr. A tangential gas load is applied to the side surface of the movable side wrap 22b in a substantially horizontal direction, causing the movable scroll 22 to tilt during orbiting.

[0072] The fixed side dimension (first dimension) of the fixed scroll 21 and the movable side dimension (second dimension) of the movable scroll 22 are set so as to satisfy the following first and second conditions.

[0073] First condition: As shown in FIG. 8, the fixed side dimension in the first region R1 is shorter than the fixed side dimension in the second region R2 by a first length h1.

[0074] Second condition: As shown in FIG. 9, the movable side dimension in the third region R3 is shorter than the movable side dimension in the fourth region R4 by a second length h2.

[0075] Appropriate values ​​for the fixed side dimensions and the movable side dimensions are determined in consideration of various factors, such as the type of scroll compressor 101, the dimensions of the fixed scroll 21 and the movable scroll 22, the temperature of the refrigerant, and the pressure of the refrigerant, etc. Therefore, the fixed side dimensions and the movable side dimensions cannot be uniquely determined.

[0076] The lower limit values ​​of the first length h1 and the second length h2 are the vertical displacement amount of the orbiting scroll 22. Specifically, the lower limit values ​​of the first length h1 and the second length h2 are equal to or greater than 1 / 1000 of the fixed-side dimension in the third region R3. The lower limit values ​​of the first length h1 and the second length h2 may be set to values ​​greater than the vertical displacement amount of the orbiting scroll 22. For example, if the actual measured value of the displacement amount of the orbiting scroll 22 is 24 μm, the lower limit values ​​of the first length h1 and the second length h2 may be set to 30 μm. The displacement amount of the orbiting scroll 22 is measured, for example, by a sensor attached to the lower main surface of the orbiting scroll 22. The lower limit values ​​of the first length h1 and the second length h2 may be set independently.

[0077] The upper limits of the first length h1 and the second length h2 are the minimum vertical distance between the tip end surface of the orbiting side wrap 22b and the first main surface 21p when the orbiting scroll 22 is not orbiting. In other words, the upper limits of the first length h1 and the second length h2 are the maximum vertical movement distances of the floating member 30 during operation of the scroll compressor 101. Specifically, the upper limits of the first length h1 and the second length h2 are 150 μm to 250 μm. The upper limits of the first length h1 and the second length h2 may be set independently.

[0078] Fig. 10 shows a state in which the fixed scroll 21 shown in Fig. 8 and the movable scroll 22 shown in Fig. 9 form a first compression chamber Sc1 and a second compression chamber Sc2. Due to the first condition, the distance between the tip end face of the fixed-side wrap 21b and the second main surface 22p in the first region R1 is longer than the distance between the tip end face of the fixed-side wrap 21b and the second main surface 22p in the second region R2. Similarly, due to the second condition, the distance between the tip end face of the movable-side wrap 22b and the first main surface 21p in the third region R3 is longer than the distance between the tip end face of the movable-side wrap 22b and the first main surface 21p in the fourth region R4.

[0079] (5) Features The moment acting on the movable scroll 22 that is inclined relative to the fixed scroll 21 during operation of the scroll compressor 101 will be described.

[0080] 11 and 12 are diagrams illustrating, as a comparative example, the moment acting on a conventional movable scroll 22. In the comparative example, the fixed side dimension of the fixed scroll 21 and the movable side dimension of the movable scroll 22 do not satisfy the first and second conditions. In other words, the fixed side dimension of the fixed scroll 21 is approximately constant from the winding start 21s to the winding end 21e, and the movable side dimension of the movable scroll 22 is approximately constant from the winding start 22s to the winding end 22e.

[0081] In the comparative example, a tilting moment M1 and an anti-tilting moment M2 act on the orbiting movable scroll 22. The tilting moment M1 is a moment that tends to tilt the orbiting movable scroll 22 due to a tangential gas load Fgt acting on the movable side wrap 22b. Figures 11 and 12 show only one tangential gas load Fgt as a representative example. Figures 11 and 12 also show a central axis 22h that passes through the center of the main surface of the movable side end plate 22a.

[0082] The magnitude of the tilting moment M1 is the product of the magnitude of the tangential gas load Fgt and the first distance L1. The first distance L1 is the distance, in the direction along the central axis 22h, between a gas load position P1, where the tangential gas load Fgt acts, and a boss center position P2. The gas load position P1 is a position in the direction along the central axis 22h, and is the center position of the movable-side wrap 22b, where the tangential gas load Fgt acts. The boss center position P2 is located on the central axis 22h, and is the center position of the boss portion 22c in the direction along the central axis 22h.

[0083] The direction of the tilting moment M1 is the direction in which the tangential gas load Fgt acts around the boss center position P2. In Figure 11, the direction of the tilting moment M1 is clockwise. In Figure 12, the direction of the tilting moment M1 is counterclockwise.

[0084] The counter-tilt moment M2 is a moment that acts to suppress tilt of the orbiting scroll 22. Therefore, the counter-tilt moment M2 acts in the opposite direction to the tilt moment M1. In FIG. 11, the direction of the counter-tilt moment M2 is counterclockwise. In FIG. 12, the direction of the counter-tilt moment M2 is clockwise.

[0085] 11, the movable side dimension of the movable scroll 22 is constant. When the movable scroll 22 tilts, the outermost tip surface 22i of the movable side wrap 22b comes into contact with the first main surface 21p. Therefore, a downward tooth tip load Ftt acts on the outermost tip surface 22i of the movable side wrap 22b from the first main surface 21p. The direction of the tooth tip load Ftt is parallel to the central axis 22h.

[0086] In Figure 12, the fixed side dimension of the fixed scroll 21 is constant. When the movable scroll 22 tilts, the outermost tip surface 21i of the fixed side wrap 21b comes into contact with the second main surface 22p. Therefore, a downward tooth tip load Ftt acts on the second main surface 22p from the outermost tip surface 21i of the fixed side wrap 21b. The direction of the tooth tip load Ftt is parallel to the central axis 22h.

[0087] The magnitude of the counter tilt moment M2 is the product of the magnitude of the tooth tip load Ftt and the second distance L2. The second distance L2 is the distance between the tooth tip load position P3, where the tooth tip load Ftt acts, and the central axis 22h. In FIG. 11, the tooth tip load position P3 is on the outermost tip face 22i of the movable side wrap 22b. In FIG. 12, the tooth tip load position P3 is on the second main surface 22p, which faces the outermost tip face 21i of the fixed side wrap 21b.

[0088] Because the magnitude of the tilting moment M1 is greater than the magnitude of the anti-tilting moment M2, the orbiting movable scroll 22 tilts in the direction of the tilting moment M1. As a result, as shown in Figures 11 and 12, a thrust gap 35 is formed on the thrust sliding surface between the movable-side end plate 22a and the floating member 30, and lubricating oil is supplied to the thrust gap 35 from the eccentric portion space 38.

[0089] However, if the overall movable side dimension of the movable side wrap 22b is shortened in order to ensure the strength of the compression mechanism 20, the tangential gas load Fgt will be reduced, and the inclination of the orbiting movable scroll 22 will be reduced. This will make it difficult for lubricating oil to enter the thrust gap 35, which could result in damage to the movable side end plate 22a and the floating member 30 due to seizure.

[0090] 13 and 14 are diagrams illustrating the moment acting on the movable scroll 22 of this embodiment. In this embodiment, the fixed side dimension of the fixed scroll 21 and the movable side dimension of the movable scroll 22 satisfy the first and second conditions.

[0091] As shown in FIG. 13, due to the second condition, the third tip surface 22j, which is the tip surface of the movable side wrap 22b in the third region R3, does not contact the first main surface 21p. Therefore, a downward tooth tip load Ftt is not applied to the third tip surface 22j from the first main surface 21p. Instead, as shown in FIG. 13, the second tip surface 21k of the fixed side wrap 21b contacts the second main surface 22p. The fixed side wrap 21b having the second tip surface 21k is located on the inner circumferential side of the movable side wrap 22b having the third tip surface 22j and contacts the movable side wrap 22b having the third tip surface 22j during orbiting of the movable scroll 22. A downward tooth tip load Ftt is applied to the second main surface 22p from the second tip surface 21k of the fixed side wrap 21b. The direction of the tooth tip load Ftt is parallel to the central axis 22h. In FIG. 13, the tooth tip load position P3 is the second main surface 22p that faces the second tip face 21k of the fixed side wrap 21b.

[0092] As shown in FIG. 14, due to the first condition, the first tip surface 21j, which is the tip surface of the fixed-side wrap 21b in the first region R1, does not contact the second main surface 22p. Therefore, a downward tooth tip load Ftt is not applied to the second main surface 22p from the first tip surface 21j. Instead, as shown in FIG. 14, the fourth tip surface 22k of the movable-side wrap 22b contacts the first main surface 21p. The movable-side wrap 22b having the fourth tip surface 22k is located on the inner circumferential side of the fixed-side wrap 21b having the first tip surface 21j and contacts the fixed-side wrap 21b having the first tip surface 21j during orbital movement of the movable scroll 22. A downward tooth tip load Ftt is applied to the fourth tip surface 22k of the movable-side wrap 22b from the first main surface 21p. The direction of the tooth tip load Ftt is parallel to the central axis 22h. In FIG. 14, the tooth tip load position P3 is the fourth tip face 22k of the movable side wrap 22b.

[0093] 11 to 14, the position at which the tooth tip load Ftt acts is different in this embodiment from the comparative example. Specifically, the second distance L2 in this embodiment is shorter than the second distance L2 in the comparative example. Therefore, the magnitude of the counter-tilt moment M2 acting on the movable scroll 22 in this embodiment is smaller than the magnitude of the counter-tilt moment M2 acting on the movable scroll 22 in the comparative example.

[0094] As described above, in this embodiment, the counter-tilt moment M2, which acts to suppress the tilt of the orbiting scroll 22 during orbit, is reduced, and excessive reduction in the tilt of the orbiting scroll 22 is suppressed. Therefore, in this embodiment, the tilt of the orbiting scroll 22 becomes larger compared to the comparative example, making it easier for lubricating oil to enter the thrust gap 35.

[0095] Therefore, the scroll compressor 101 of this embodiment has the effect of suppressing the occurrence of a problem in which the movable side end plate 22a and the floating member 30 are damaged due to seizure caused by an insufficient supply of lubricating oil to the thrust gap 35.

[0096] (6) Variations (6-1) Variation A In the scroll compressor 101 of the embodiment, the fixed side dimensions and the movable side dimensions are set so as to satisfy the first and second conditions.

[0097] In this modified example, the fixed-side dimensions and the movable-side dimensions do not satisfy the first and second conditions. Instead, in this modified example, the vertical positions of the first main surface 21p, which is the lower main surface of the fixed-side mirror plate 21a, and the second main surface 22p, which is the upper main surface of the movable-side mirror plate 22a, are set so as to satisfy the following third and fourth conditions.

[0098] Third condition: As shown in FIG. 15, the first main surface 21p facing the tip face of the third region R3 is recessed by a first length h1 in a direction away from the second main surface 22p with respect to the first main surface 21p facing the tip face of the fourth region R4.

[0099] Fourth condition: As shown in FIG. 16, the second main surface 22p facing the tip surface of the first region R1 is recessed by a second length h2 in the direction away from the first main surface 21p relative to the second main surface 22p facing the tip surface of the second region R2.

[0100] 15, the first main surface 21p facing the tip face of the third region R3 is indicated by the reference symbol 21p1, and the first main surface 21p facing the tip face of the fourth region R4 is indicated by the reference symbol 21p2. The "direction away from the second main surface 22p" in the third condition refers to the direction away from the tip face of the fixed side wrap 21b, which is the direction indicated by the arrow U in FIG.

[0101] 16, the second main surface 22p facing the tip surface of the first region R1 is indicated by the reference symbol 22p1, and the second main surface 22p facing the tip surface of the second region R2 is indicated by the reference symbol 22p2. The "direction away from the first main surface 21p" in the fourth condition refers to the direction away from the tip surface of the movable-side wrap 22b, which is the direction indicated by arrow D in FIG.

[0102] The appropriate vertical positions of the first main surface 21p and the second main surface 22p are determined in consideration of various factors, such as the type of scroll compressor 101, the dimensions of the fixed scroll 21 and the movable scroll 22, the temperature of the refrigerant, and the pressure of the refrigerant, etc. Therefore, the appropriate vertical positions of the first main surface 21p and the second main surface 22p cannot be uniquely determined.

[0103] The lower limit values ​​of the first length h1 and the second length h2 are set in the same manner as in the embodiment. The lower limit values ​​of the first length h1 and the second length h2 may be set independently.

[0104] The upper limit values ​​of the first length h1 and the second length h2 are set in the same manner as in the embodiment. The upper limit value of the first length h1 and the upper limit value of the second length h2 may be set independently.

[0105] Fig. 17 shows a state in which the fixed scroll 21 shown in Fig. 15 and the movable scroll 22 shown in Fig. 16 form a first compression chamber Sc1 and a second compression chamber Sc2. Due to the third condition, the distance between the tip end face of the movable-side wrap 22b in the third region R3 and the first main surface 21p is longer than the distance between the tip end face of the movable-side wrap 22b in the fourth region R4 and the first main surface 21p. Similarly, due to the fourth condition, the distance between the tip end face of the fixed-side wrap 21b in the first region R1 and the second main surface 22p is longer than the distance between the tip end face of the fixed-side wrap 21b in the second region R2 and the second main surface 22p.

[0106] 18 and 19 are diagrams illustrating the moment acting on the movable scroll 22 of this modified example. In this modified example, the vertical positions of the first main surface 21p and the second main surface 22p satisfy the third and fourth conditions.

[0107] As shown in FIG. 18, due to the third condition, the third tip surface 22j, which is the tip surface of the movable side wrap 22b in the third region R3, does not contact the first main surface 21p. Therefore, a downward tooth tip load Ftt is not applied to the third tip surface 22j from the first main surface 21p. Instead, as shown in FIG. 18, the second tip surface 21k of the fixed side wrap 21b contacts the second main surface 22p. The fixed side wrap 21b having the second tip surface 21k is located on the inner circumferential side of the movable side wrap 22b having the third tip surface 22j and contacts the movable side wrap 22b having the third tip surface 22j during orbiting of the movable scroll 22. A downward tooth tip load Ftt is applied to the second main surface 22p from the second tip surface 21k of the fixed side wrap 21b. The direction of the tooth tip load Ftt is parallel to the central axis 22h. In FIG. 18, the tooth tip load position P3 is the second main surface 22p that faces the second tip face 21k of the fixed side wrap 21b.

[0108] As shown in FIG. 19 , due to the fourth condition, the first tip surface 21j, which is the tip surface of the fixed-side wrap 21b in the first region R1, does not contact the second main surface 22p. Therefore, a downward tooth tip load Ftt is not applied to the second main surface 22p from the first tip surface 21j. Instead, as shown in FIG. 19 , the fourth tip surface 22k of the movable-side wrap 22b contacts the first main surface 21p. The movable-side wrap 22b having the fourth tip surface 22k is located on the inner circumferential side of the fixed-side wrap 21b having the first tip surface 21j and contacts the fixed-side wrap 21b having the first tip surface 21j during orbital movement of the movable scroll 22. A downward tooth tip load Ftt is applied to the fourth tip surface 22k of the movable-side wrap 22b from the first main surface 21p. The direction of the tooth tip load Ftt is parallel to the central axis 22h. In FIG. 19, the tooth tip load position P3 is the fourth tip face 22k of the movable side wrap 22b.

[0109] In this way, the third condition of this modification produces the same effect as the second condition of the embodiment, and the fourth condition of this modification produces the same effect as the first condition of the embodiment.

[0110] As described above, in this modification, similarly to the embodiment, the counter-tilt moment M2, which acts to suppress the tilt of the orbiting scroll 22, is reduced, and excessive reduction in the tilt of the orbiting scroll 22 is suppressed. Therefore, in this modification, the tilt of the orbiting scroll 22 is greater than in the comparative example, making it easier for lubricating oil to enter the thrust gap 35.

[0111] Therefore, the scroll compressor 101 of this modified example has the effect of suppressing the occurrence of a problem in which the movable side end plate 22a and the floating member 30 are damaged due to seizure caused by an insufficient supply of lubricating oil to the thrust gap 35.

[0112] (6-2) Variation B In the scroll compressor 101 of the embodiment, the vertical positions of the first main surface 21p, which is the lower main surface of the fixed-side end plate 21a, and the second main surface 22p, which is the upper main surface of the movable-side end plate 22a, may be set so as to satisfy the third and fourth conditions of Modification A. In other words, the scroll compressor 101 may be configured so as to satisfy the first to fourth conditions.

[0113] In this case, the first length (third length) of the third condition may be set independently of the first length h1 of the first condition, and the second length (fourth length) of the fourth condition may be set independently of the second length h2 of the second condition.

[0114] (6-3) Variation C In the embodiment, the vertical position of the first main surface 21p is uniform as shown in Fig. 8. However, as long as the fixed side dimension and the movable side dimension satisfy the first condition and the second condition, the vertical position of the first main surface 21p does not have to be uniform.

[0115] In the embodiment, the vertical position of second main surface 22p is uniform as shown in Fig. 9. However, as long as the fixed side dimension and the movable side dimension satisfy the first and second conditions, the vertical position of second main surface 22p does not have to be uniform.

[0116] (6-4) Variation D In Modifications A and B, the vertical position of the first main surface 21p (surface indicated by reference symbol 21p2 in FIG. 15 ) facing the front end face of the fourth region R4 is uniform. However, as long as the vertical positions of the first main surface 21p and the second main surface 22p satisfy the third and fourth conditions, the vertical position of the first main surface 21p facing the front end face of the fourth region R4 does not have to be uniform. In this case, for example, the "first main surface 21p facing the front end face of the fourth region R4" in the third condition is replaced with "the surface of the first main surface 21p facing the front end face of the fourth region R4 that is farthest from the front end face of the fixed-side wrap 21b" or "the average plane of the first main surface 21p facing the front end face of the fourth region R4." Here, the "average plane" refers to a virtual plane located at the average position in the direction of arrow U in FIG. 15 .

[0117] In Modifications A and B, the vertical position of the second main surface 22p (surface indicated by reference symbol 22p2 in FIG. 16 ) facing the tip surface of the second region R2 is uniform. However, as long as the vertical positions of the first main surface 21p and the second main surface 22p satisfy the third and fourth conditions, the vertical position of the second main surface 22p facing the tip surface of the second region R2 does not have to be uniform. In this case, for example, the "second main surface 22p facing the tip surface of the second region R2" in the fourth condition is replaced with "the surface of the second main surface 22p facing the tip surface of the second region R2 that is farthest from the tip surface of the movable-side wrap 22b" or "the average plane of the second main surface 22p facing the tip surface of the second region R2." Here, the "average plane" refers to a virtual plane located at the average position in the direction of arrow D in FIG. 16 .

[0118] (6-5) Variation E In this embodiment, the fixed side dimensions in the second region R2 are uniform as shown in Fig. 8. However, as long as the fixed side dimensions and the movable side dimensions satisfy the first and second conditions, the fixed side dimensions in the second region R2 do not have to be uniform. In this case, for example, the "fixed side dimensions in the second region R2" in the first condition is replaced with "the shortest value of the fixed side dimensions in the second region R2" or "the average value of the fixed side dimensions in the second region R2."

[0119] In this embodiment, the movable-side dimensions in the fourth region R4 are uniform, as shown in Fig. 9. However, as long as the fixed-side dimensions and the movable-side dimensions satisfy the first and second conditions, the movable-side dimensions in the fourth region R4 do not have to be uniform. In this case, for example, the "movable-side dimensions in the fourth region R4" in the second condition is replaced with "the shortest value among the movable-side dimensions in the fourth region R4" or "the average value of the movable-side dimensions in the fourth region R4."

[0120] (6-6) Variation F 15, in Modifications A and B, the position of the tip end surface of the fixed side wrap 21b is uniform in the direction of arrow U. However, as long as the vertical positions of the first main surface 21p and the second main surface 22p satisfy the third and fourth conditions, the position of the tip end surface of the fixed side wrap 21b in the direction of arrow U does not have to be uniform.

[0121] 16, in Modifications A and B, the position of the tip end surface of the movable-side wrap 22b is uniform in the direction of arrow D. However, as long as the vertical positions of the first main surface 21p and the second main surface 22p satisfy the third and fourth conditions, the position of the tip end surface of the movable-side wrap 22b in the direction of arrow D does not have to be uniform.

[0122] (6-7) Variation G In the embodiment and Modification A, as shown in Fig. 13 and Fig. 18, a downward tooth tip load Ftt acts from the second tip surface 21k of the fixed side wrap 21b to the second main surface 22p. However, the position where the tooth tip load Ftt acts is not limited to this as long as the second distance L2 is shorter than the second distance L2 shown in Fig. 11. For example, in Fig. 13 and Fig. 18, the downward tooth tip load Ftt may act from the first main surface 21p on the tip surface of the movable side wrap 22b in the fourth region, which is located adjacent to the movable side wrap 22b in the third region R3.

[0123] In the embodiment and Modification A, as shown in Fig. 14 and Fig. 19, a downward tooth tip load Ftt acts on the fourth tip face 22k of the movable side wrap 22b from the first main surface 21p. However, as long as the second distance L2 is shorter than the second distance L2 shown in Fig. 12, the position where the tooth tip load Ftt acts is not limited to this. For example, in Fig. 14 and Fig. 19, the downward tooth tip load Ftt may act on the second main surface 22p from the tip face of the fixed side wrap 21b in the second region that is located adjacent to the fixed side wrap 21b in the first region R1.

[0124] (6-8) Variation H The scroll compressor 101 of the embodiment includes a floating member 30 for pressing the movable scroll 22 against the fixed scroll 21. However, the scroll compressor 101 may be a compressor of a type that does not include the floating member 30.

[0125] (6-9) Variation I The compression mechanism 20 of the scroll compressor 101 of the embodiment has a symmetric wrap structure. However, the compression mechanism 20 may have an asymmetric wrap structure. In the compression mechanism 20 having the asymmetric wrap structure, the number of turns of the stationary wrap 21b and the moving wrap 22b are different from each other. In the compression mechanism 20 having the asymmetric wrap structure, a compression chamber (first compression chamber Sc1) surrounded by the outer circumferential surface of the moving wrap 22b and the inner circumferential surface of the stationary wrap 21b and a compression chamber (second compression chamber Sc2) surrounded by the inner circumferential surface of the moving wrap 22b and the outer circumferential surface of the stationary wrap 21b are not formed point-symmetrically when viewed in the vertical direction (first direction). In the compression mechanism 20 having the asymmetric wrap structure, the refrigerant is compressed in the first compression chamber Sc1 and the refrigerant is compressed in the second compression chamber Sc2 at different times.

[0126] Although the embodiments of the present disclosure have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the present disclosure as defined in the claims. [Explanation of symbols]

[0127] 20: Compression mechanism 21: Fixed scroll 21a: Fixed side head plate 21b: Fixed side wrap 21e: End of fixed wrap (first point) 21f: Fixed side reference point (5th point) 21p: Lower main surface of the fixed head (first main surface) 21s: Start of wrapping the fixed side wrap (second point) 22: Movable scroll 22a: Movable side mirror plate 22b: Movable side wrap 22e: End of moving wrap (third point) 22f: Movable side reference point (6th point) 22p: Lower main surface of the movable head (second main surface) 22s: Beginning of wrapping on the movable side (4th point) 30: Floating member 40: Upper housing (housing) 100: Refrigeration equipment 101:Scroll compressor 110: Refrigerant circuit B0: Back pressure space D1: 1st direction R1: 1st area R2: 2nd area R3: 3rd area R4: 4th area h1: First length h2: Second length [Prior art documents] [Patent documents]

[0128] [Patent Document 1] Japanese Patent Application Laid-Open No. 2000-337276

Claims

1. a compression mechanism (20) having a fixed scroll (21) having a fixed side end plate (21a) and a fixed side wrap (21b), and a movable scroll (22) having a movable side end plate (22a) and a movable side wrap (22b); a floating member (30) that is pushed toward the movable scroll by the pressure in the back pressure space (B0) to press the movable scroll toward the fixed scroll; a housing (40) that supports the floating member and forms the back pressure space between the floating member and the housing; Equipped with The fixed side wrap extends spirally from a first point (21e) which is an end on the outer circumferential side to a second point (21s) which is an end on the inner circumferential side, and extends from a first main surface (21p) of the fixed side end plate along a first direction (D1) with a predetermined first dimension, The movable-side wrap extends spirally from a third point (22e) which is an end on the outer circumferential side to a fourth point (22s) which is an end on the inner circumferential side, and extends along the first direction from a second main surface (22p) of the movable-side head plate which faces the first main surface, with a predetermined second dimension; The fixed side wrap is a first region (R1) from the first point to a fifth point (21f) that contacts the third point during orbital movement of the movable scroll; a second region (R2) from the fifth point to the second point; and The movable side wrap is a third region (R3) from the third point to a sixth point (22f) that contacts the first point during orbital movement of the movable scroll; a fourth region (R4) from the sixth point to the fourth point; and The first dimension in the first region is shorter than the first dimension in the second region by a first length (h1); The second dimension in the third region is shorter than the second dimension in the fourth region by a second length (h2). Scroll compressor (101).

2. a compression mechanism (20) having a fixed scroll (21) having a fixed side end plate (21a) and a fixed side wrap (21b), and a movable scroll (22) having a movable side end plate (22a) and a movable side wrap (22b); a floating member (30) that is pushed toward the movable scroll by the pressure in the back pressure space (B0) to press the movable scroll toward the fixed scroll; a housing (40) that supports the floating member and forms the back pressure space between the floating member and the housing; Equipped with The fixed side wrap extends spirally from a first point (21e) which is an end on the outer circumferential side to a second point (21s) which is an end on the inner circumferential side, and extends from a first main surface (21p) of the fixed side end plate along a first direction (D1) with a predetermined first dimension, The movable-side wrap extends spirally from a third point (22e) which is an end on the outer circumferential side to a fourth point (22s) which is an end on the inner circumferential side, and extends along the first direction from a second main surface (22p) of the movable-side head plate which faces the first main surface, with a predetermined second dimension; The fixed side wrap is a first region (R1) from the first point to a fifth point (21f) that contacts the third point during orbital movement of the movable scroll; a second region (R2) from the fifth point to the second point; and The movable side wrap is a third region (R3) from the third point to a sixth point (22f) that contacts the first point during orbital movement of the movable scroll; a fourth region (R4) from the sixth point to the fourth point; and the first main surface facing the front end surface of the third region is recessed by a first length (h1) in a direction away from the second main surface relative to the first main surface facing the front end surface of the fourth region, the second main surface facing the tip surface of the first region is recessed by a second length (h2) in a direction away from the first main surface relative to the second main surface facing the tip surface of the second region; Scroll compressor (101).

3. The lower limit values ​​of the first length and the second length are the displacement amounts of the orbiting scroll in the first direction. The scroll compressor according to claim 1 or 2.

4. the lower limit value is equal to or greater than 1 / 1000 of the first dimension in the third region; The scroll compressor according to claim 3.

5. the upper limit values ​​of the first length and the second length are the minimum values ​​of the distance between the tip end surface of the movable side wrap and the first main surface in the first direction when the movable scroll is not orbiting. The scroll compressor according to claim 1 or 2.

6. The upper limit is 150 μm to 250 μm. The scroll compressor according to claim 5.

7. the first main surface facing the tip surface of the third region is recessed by a third length in a direction away from the second main surface relative to the first main surface facing the tip surface of the fourth region, the second main surface facing the tip surface of the first region is recessed by a fourth length in a direction away from the first main surface relative to the second main surface facing the tip surface of the second region; The scroll compressor according to claim 1 .

8. A scroll compressor (101) according to any one of claims 1, 2 and 7; a refrigerant circuit (110) through which the refrigerant compressed by the scroll compressor flows; Equipped with A refrigeration device (100).

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