Scroll compressor

Abstract

Inhibition of reduction of the rotational torque generated in the orbiting scroll. A scroll compressor (10) has a fixed scroll (51), an orbiting scroll (52), a rotation prevention mechanism (300), and a back pressure chamber (H5). A scroll-like orbiting wrap (522) of the orbiting scroll (52) is engaged with a scroll-like fixed wrap (512) of the fixed scroll (51). A first compression chamber (C1) is formed by an inner wall surface (522a) of the orbiting wrap (522) and an outer wall surface (512b) of the fixed wrap (512). A second compression chamber (C2) is formed by an inner wall surface (512a) of the fixed wrap (512) and an outer wall surface (522b) of the orbiting wrap (522). An orbiting base plate (521) of the orbiting scroll (52) has a first through-hole (701) capable of communicating the first compression chamber (C1) with the back pressure chamber (H5) and a second through-hole (702) capable of communicating the second compression chamber (C2) with the back pressure chamber (H5). The first compression chamber (C1) is communicated with the back pressure chamber (H5) via the first through-hole (701) before the second compression chamber (C2) is communicated with the back pressure chamber (H5) via the second through-hole (702).

Description

Technical Field

[0001] This invention relates to a scroll compressor for use in vehicle air conditioning systems and the like. Background Technology

[0002] Patent Document 1 discloses a scroll compressor comprising: a scroll unit, wherein the scroll unit has a scroll-shaped surrounding member erected on a base plate (base plate), and a fixed scroll and a rotating scroll (movable scroll) are eccentrically positioned relative to each other at the center of the base circle (scroll center) of the surrounding member, forming a sealed space by their surrounding members facing and engaging with each other; and a rotation-stopping mechanism, which prevents the rotating scroll from rotating, thereby preventing the rotating scroll from rotating and causing the rotating scroll to revolve around the axis of the fixed scroll, thus changing the volume of the sealed space. Patent Document 1 discloses that the rotation-stopping mechanism consists of a circular hole formed on the back side of the base plate of the rotating scroll and a pin protruding from the outer casing wall opposite the back side of the base plate of the rotating scroll and engaging with the circular hole. In addition, Patent Document 1 discloses that a rotational torque is generated in the vortex disk by the compression reaction force accompanying the compression achieved by the scroll compressor, and the load generated by the rotational torque acts on the rotation-stopping mechanism.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2015-059517 Summary of the Invention

[0006] The technical problem that the invention aims to solve

[0007] However, the inventors have discovered that when the scroll compressor described above is operating, the aforementioned rotational torque will momentarily disappear. As a result, the pin will momentarily leave the inner circumferential surface of the circular hole and then collide with the inner circumferential surface of the circular hole again.

[0008] Therefore, the object of the present invention is to suppress the decrease in the rotational torque generated in the vortex disk.

[0009] Technical solutions adopted to solve technical problems

[0010] According to one aspect of the present invention, a scroll compressor is provided. The scroll compressor includes: a fixed scroll having a fixed base plate with a discharge hole in the center and a scroll-shaped fixed surrounding member erected on the fixed base plate; a rotating scroll having a rotating base plate and a scroll-shaped rotating surrounding member erected on the rotating base plate and engaging with the fixed surrounding member; a first compression chamber formed by the inner wall surface of the rotating surrounding member and the outer wall surface of the fixed surrounding member; a second compression chamber formed by the inner wall surface of the fixed surrounding member and the outer wall surface of the rotating surrounding member; a rotation-stopping mechanism to prevent the rotation of the rotating scroll; and a back pressure chamber disposed on the back side of the rotating scroll. The rotation-stopping mechanism prevents the rotation of the rotating scroll, and the rotating scroll revolves around the axis of the fixed scroll, causing the volumes of the first and second compression chambers to change respectively. This compresses the fluid in the first and second compression chambers respectively, and discharges them together from the discharge hole to the discharge chamber. The rotary substrate has a first through hole that connects a first compression chamber to a back pressure chamber and a second through hole that connects a second compression chamber to a back pressure chamber. Before the second compression chamber connects to the back pressure chamber via the second through hole, the first compression chamber connects to the back pressure chamber via the first through hole.

[0011] Invention Effects

[0012] According to the present invention, since the pressure in the first compression chamber can be made higher than the pressure in the second compression chamber, the rotational torque generated in the vortex disk can be increased accordingly, thereby suppressing the decrease in rotational torque. Attached Figure Description

[0013] Figure 1 This is a cross-sectional view illustrating the schematic structure of a scroll compressor according to an embodiment of the present invention.

[0014] Figure 2 This is a top view of the vortex disk.

[0015] Figure 3 This is an enlarged cross-sectional view of the rotation-stopping part that constitutes the rotation-stopping mechanism.

[0016] Figure 4 This is a configuration diagram of the rotation-stopping part of the rotation-stopping mechanism in a rotary substrate.

[0017] Figure 5 This is a block diagram illustrating the flow of gaseous refrigerant and lubricating oil in the aforementioned scroll compressor.

[0018] Figure 6 It is a graph showing the relationship between the pressure in the compression chamber and the pressure in the back pressure chamber and the vortex rotation angle (crank angle).

[0019] Figure 7 This is a diagram showing the working state of a scroll compressor.

[0020] Figure 8 This is a diagram showing the working state of a scroll compressor.

[0021] Figure 9 This is a diagram showing the working state of a scroll compressor.

[0022] Figure 10 This is a diagram showing the working state of a scroll compressor.

[0023] Figure 11 This is a diagram showing the working state of a scroll compressor.

[0024] Figure 12 This is a diagram showing the working state of a scroll compressor. Detailed Implementation

[0025] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0026] Figure 1 This is a cross-sectional view illustrating the schematic structure of a scroll compressor 10 according to an embodiment of the present invention. The scroll compressor 10 is assembled in the refrigerant circuit of a vehicle air conditioning system, etc., receiving low-pressure gaseous refrigerant from the refrigerant circuit, compressing it, and then pressurizing it before returning it to the refrigerant circuit. Furthermore, Figure 1 The left side of the image shows the front of the scroll compressor 10. Figure 1 The right side of the image shows the rear side of the scroll compressor 10. Figure 1 The upper part of the middle is the upper part of the scroll compressor 10. Figure 1 The lower side is the lower side of the scroll compressor 10. Furthermore, the aforementioned gaseous refrigerant is an example of a fluid in this invention.

[0027] The scroll compressor 10 includes: a housing 20; a rotating shaft 30; an electric motor 40 that rotates the rotating shaft 30; a scroll unit 50 driven by the rotating shaft 30 and compressing (low-pressure) gaseous refrigerant; and an inverter 60 that drives and controls the electric motor 40. The rotating shaft 30, the electric motor 40, the scroll unit 50, and the inverter 60 are housed within the housing 20. Furthermore, the scroll unit 50 includes a fixed scroll 51 and a rotating scroll 52 that rotates relative to the fixed scroll 51. The fixed scroll 51 and the rotating scroll 52 are arranged opposite each other along the central axis of the scroll compressor 10.

[0028] The housing 20 includes a front housing 21, a cover member 22, a middle housing 23, and a rear housing 24. Moreover, they are fastened together by fasteners (not shown) and constitute the housing 20 of the scroll compressor 10.

[0029] The front housing 21 has a cylindrical first peripheral wall portion 211 extending front to back and a first partition wall portion 212 that separates the interior of the first peripheral wall portion 211 from the front to the back. The front end face of the first peripheral wall portion 211 forms the front end face of the front housing 21, and the rear end face of the first peripheral wall portion 211 forms the rear end face of the front housing 21. In this embodiment, the interior of the first peripheral wall portion 211 (i.e., the interior space of the front housing 21) is divided by the first partition wall portion 212 into an inverter housing space for housing the front side of the inverter 60 and a motor housing space for housing the rear side of the motor 40. That is, the motor 40 and the inverter 60 are housed in the front housing 21.

[0030] A support portion 213 is provided on the first partition 212 to support the front end of the rotating shaft 30. Specifically, in this embodiment, the support portion 213 is configured to protrude cylindrically from the rear side of the first partition 212 toward the motor housing space, and rotatably supports the front end of the rotating shaft 30 via a first bearing 214 installed inside.

[0031] A cover member 22 is joined to the front end face of the front housing 21, thereby enclosing the inverter housing space (forming an inverter housing chamber). The front end face of the intermediate housing 23 is joined to the rear end face of the front housing 21. In addition, sealing members can be arranged between the front housing 21 and the cover member 22 and between the front housing 21 and the intermediate housing 23 as needed.

[0032] The intermediate outer shell 23 has a cylindrical second peripheral wall portion 231 extending front to back and a second partition wall portion 232 that separates the interior of the second peripheral wall portion 231 front to back. The front end face of the second peripheral wall portion 231 constitutes the front end face of the intermediate outer shell 23, and the rear end face of the second peripheral wall portion 231 constitutes the rear end face of the intermediate outer shell 23. In this embodiment, the interior of the second peripheral wall portion 231 (i.e., the interior space of the intermediate outer shell 23) is divided by the second partition wall portion 232 into a front connecting space that connects to the aforementioned motor housing space of the front outer shell 21 and a rear vortex housing space that houses the vortex unit 50. That is, the vortex unit 50 is housed in the intermediate outer shell 23.

[0033] The second partition wall portion 232 has a hollow protrusion 233 protruding towards the front outer casing 21 (motor housing space). The hollow protrusion 233 is disposed radially at the center of the second partition wall portion 232, opposite to the support portion 213 disposed on the first partition wall portion 212 of the front outer casing 21. A through hole 234 is formed on the top of the hollow protrusion 233, which communicates the inside and outside of the hollow protrusion 233 and allows the rear end side of the rotating shaft 30 to be inserted. In addition, a second bearing 235 that rotatably supports the rear end side of the rotating shaft 30 is installed inside the hollow protrusion 233. That is, in this embodiment, the rotating shaft 30 is rotatably supported by a first bearing 214 disposed on the front outer casing 21 side and a second bearing 235 disposed on the intermediate outer casing 23 side.

[0034] The rear end face of the rear end face of the intermediate end face 23 is joined to the rear end face of the intermediate end face 23. In this embodiment, a recess 236 is formed on the rear end face of the intermediate end face 23, i.e., the rear end face of the second peripheral wall portion 231, to receive the outer edge of the fixing base plate 511 of the fixing scroll 51 constituting the scroll unit 50. Furthermore, the outer edge of the fixing base plate 511 of the fixing scroll 51 is clamped between the intermediate end face 23 and the rear end face 24, thereby fixing the fixing scroll 51, and closing the opening on the rear side of the second peripheral wall portion 231 with the fixing base plate 511 of the fixing scroll 51. Additionally, a sealing member can be disposed between the intermediate end face 23 and the rear end face 24 as needed.

[0035] The rear outer shell 24 is formed into a bottomed cylindrical shape, having a cylindrical third peripheral wall portion 241 extending from front to back and a bottom wall portion 242 that closes the opening on the rear side of the third peripheral wall portion 241. Furthermore, the front end face of the third peripheral wall portion 241, which forms the front end face of the rear outer shell 24, is joined to the rear end face of the second peripheral wall portion 231, which forms the rear end face of the intermediate outer shell 23, thereby closing the opening on the front side of the third peripheral wall portion 241 by the fixing base plate 511 of the fixing volute 51.

[0036] The motor 40 is, for example, a three-phase AC motor, including a stator core unit 41 and a rotor 42.

[0037] The stator core unit 41 is fixed to the inner peripheral surface of the first peripheral wall portion 211 of the front housing 21. Direct current from a vehicle battery (not shown) or the like is converted into alternating current by the inverter 60 and supplied to the stator core unit 41.

[0038] The rotor 42 is configured with a predetermined gap to the radially inner side of the stator core unit 41. A permanent magnet is installed in the rotor 42. The rotor 42 is formed into a cylindrical shape and is fixed to the rotating shaft 30 with the rotating shaft 30 inserted through its hollow portion. That is, the rotor 42 and the rotating shaft 30 are integrated.

[0039] When the motor 40 generates a magnetic field in the stator core unit 41 through the power supply from the inverter 60, the rotational force acts on the permanent magnet of the rotor 42, causing the rotor 42 to rotate, thereby causing the rotating shaft 30 to rotate.

[0040] As described above, the scroll unit 50 includes a fixed scroll 51 and a rotating scroll 52 that rotates relative to the fixed scroll 51.

[0041] The fixed scroll 51 has a circular plate-shaped fixed base plate 511 and a scroll-shaped fixing and surrounding member 512 erected on one side of the fixed base plate 511. In the fixed scroll 51 of this embodiment, the scroll-shaped fixing and surrounding member 512 is integrally erected on the fixed base plate 511. The fixing roll 512 extends from the inner end (winding start end) on the radially inward side to the outer end (winding end end) on the aforementioned one side of the fixed base plate 511 (see reference). Figure 7 It extends in a vortex shape. Moreover, when the fixed vortex 51 is facing forward on the aforementioned one side of the fixed base plate 511 (the side on which the fixed surrounding member 512 is erected), the outer edge of the fixed base plate 511 is clamped and fixed by the intermediate outer shell 23 and the rear outer shell 24.

[0042] Figure 2 This is a top view of the vortex disk 52. (See attached image.) Figure 1 and Figure 2 As shown, the rotary scroll (movable scroll) 52 has a circular plate-shaped rotary base plate (movable base plate) 521 and a rotary surrounding member (movable surrounding member) 522 erected on one side of the rotary base plate 521. In the rotary scroll 52 of this embodiment, the vortex-shaped rotary surrounding member 522 is integrally erected on the rotary base plate 521. The rotary surrounding member 522 extends in a vortex shape from the inner end (winding start portion) on the radially inward side to the outer end (winding end portion) 52c on the aforementioned one side of the rotary base plate 521. Moreover, the rotary scroll 52 is arranged such that the rotary surrounding member 522 engages with the fixed surrounding member 512 of the fixed scroll 51. That is, the rotary scroll 52 is arranged between the second partition 232 of the intermediate housing 23 and the fixed scroll 51 with the aforementioned one side of the rotary base plate 521 (the side where the rotary surrounding member 522 is erected) facing rearward. Here, the fixed scroll 51 and the rotating scroll 52 are arranged such that the fixed surrounding member 512 engages with the rotating surrounding member 522, the protruding end edge of the fixed surrounding member 512 contacts the rotating base plate 521, and the protruding end edge of the rotating surrounding member 522 contacts the fixed base plate 511. Furthermore, chip-shaped sealing members are provided on the protruding end edges of both the fixed surrounding member 512 and the rotating surrounding member 522.

[0043] In this embodiment, such as Figure 2As shown, the spiraling member 522 is formed along an involute curve (imaginary line) extending from the base circle (imaginary circle) 52a. Here, the extension angle of the spiraling member 522 refers to the angle around the center (fixed vortex center) 52b of the base circle 52a and is the angle from the reference point on the base circle 52a (the starting point of the aforementioned involute curve) to the winding end 52c of the spiraling member 522.

[0044] Although the illustration is omitted, similar to the spiraling member 522, the fixed member 512 is also formed along an involute curve (imaginary line) extending from the base circle (imaginary circle). Here, the extension angle of the fixed member 512 refers to the angle about the center of the base circle (fixed helix center) of the fixed member 512 and is from the reference point on the base circle (the starting point of the aforementioned involute curve) to the winding end 51c of the fixed member 512 (see reference). Figure 7 (angle)

[0045] In this embodiment, the extension angle of the fixed surrounding member 512 is the same as the extension angle of the rotating surrounding member 522. However, the extension angles of the fixed surrounding member 512 and the rotating surrounding member 522 may also be different.

[0046] In this embodiment, the fixed surrounding member 512 is formed by offsetting the center of its base circle relative to the center (not shown) of the fixed base plate 511. Similarly, the rotating surrounding member 522 is formed by offsetting the center 52b of its base circle 52a relative to the center (not shown) of the rotating base plate 521. This allows for a reduction in the outer diameter of the scroll unit 50 and a smaller main body diameter of the scroll compressor 10, thereby enabling miniaturization of the scroll compressor 10.

[0047] The vortex 52 is configured to be driven by the rotating shaft 30 via the crank mechanism 70 so as to rotate relative to the fixed vortex 51, in other words, to revolve around the axis of the fixed vortex 51.

[0048] The crank mechanism 70 is configured to connect the rotating shaft 30 to the rotary scroll 52 and convert the rotational motion of the rotating shaft 30 into the rotational motion of the rotary scroll 52. In this embodiment, the crank mechanism 70 is disposed inside the hollow protrusion 233 of the second partition wall portion 232 of the intermediate housing 23. The crank mechanism 70 includes: a crank pin 71 erected at the rear end of the rotating shaft 30; an eccentric bushing 72 mounted eccentrically relative to the crank pin 71; and a cylindrical portion 73 protruding from the back side of the rotary base plate 521 of the rotary scroll 52. The eccentric bushing 72 is rotatably supported on the inner circumferential surface of the cylindrical portion 73 by a bearing (not shown). In addition, a counterweight 74 is installed at the rear end of the rotating shaft 30 to counteract the centrifugal force generated by the rotational motion of the rotary scroll 52.

[0049] The scroll unit 50 is configured to draw in and compress low-pressure gaseous refrigerant by rotating the scroll 52 relative to the fixed scroll 51. Furthermore, an annular thrust plate 80 is disposed between the rotating base plate 521 of the scroll 52 and the second partition wall portion 232 of the intermediate housing 23, and the rear surface of the second partition wall portion 232 receives thrust from the scroll 52 via the thrust plate 80.

[0050] The rotation of the gyratory scroll 52 can be stopped by the rotation-stopping mechanism 300. Here, using Figure 3 and Figure 4 Explanation of the rotation-stopping mechanism 300.

[0051] Figure 3 This is an enlarged cross-sectional view of the rotation-stopping part 303 that constitutes the rotation-stopping mechanism 300. Figure 4 This is a configuration diagram of the rotation-stopping part 303 of the rotation-stopping mechanism 300 in the rotary base plate 521.

[0052] The self-rotation prevention mechanism 300 is designed to... Figure 4 As shown, multiple (five in this embodiment) rotation-stopping portions 303, consisting of rings 301 and pins 302, are arranged at equal intervals along the circumferential direction near the outer periphery of the back surface of the rotating substrate 521. Figure 3 As shown, the ring 301 is pressed into a circular hole formed on the back side of the rotating base plate 521, and the pin 302 protrudes from the second partition wall portion 232 of the intermediate outer shell 23 and passes through the thrust plate 80, fitting inside the ring 301. Furthermore, if there are at least three or more rotation-stopping portions 303, the rotating volute 52 can revolve around the axis of the fixed volute 51 without rotating on its own axis. Here, the second partition wall portion 232 is an example of the "outer shell wall" of the present invention.

[0053] return Figure 1 In this embodiment, the scroll compressor 10 includes: an intake chamber H1 into which a low-pressure gaseous refrigerant flows; a compression chamber H2 into which the low-pressure gaseous refrigerant is compressed; a discharge chamber H3 into which the gaseous refrigerant compressed in the compression chamber H2 is discharged; a gas-liquid separation chamber H4 into which lubricating oil is separated from the gaseous refrigerant compressed in the compression chamber H2; and a back pressure chamber H5 disposed on the back side of the scroll 52 (the back side of the scroll base plate 521).

[0054] The suction chamber H1 is formed by dividing the first peripheral wall portion 211 of the front outer shell 21, the first partition wall portion 212 of the front outer shell 21, the second peripheral wall portion 231 of the intermediate outer shell 23, and the second partition wall portion 232 of the intermediate outer shell 23. That is, in this embodiment, the suction chamber H1 is formed by the motor housing space of the front outer shell 21 and the connection space of the intermediate outer shell 23. An intake port P1 is formed in the first peripheral wall portion 211. The intake port P1 is connected to the refrigerant circuit (low-pressure side) via a connecting pipe (not shown) or the like. Therefore, low-pressure refrigerant from the refrigerant circuit flows into the suction chamber H1 through the intake port P1. In addition, a refrigerant passage L1 is formed in the intermediate outer shell 23 for guiding the low-pressure gaseous refrigerant in the suction chamber H1 to the space H6 near the outer end of the scroll unit 50.

[0055] Compression chamber H2 is formed within scroll unit 50, specifically between fixed scroll 51 and rotating scroll 52. Scroll unit 50 is configured to compress low-pressure gaseous refrigerant by drawing in low-pressure gaseous refrigerant from space H6 during the formation of compression chamber H2.

[0056] In this embodiment, the fixed scroll 51 and the rotating scroll 52 are arranged such that the wall surfaces of the fixed scroll 512 and the rotating scroll 522 are in partial contact with each other, with the circumferential angles of the fixed scroll 512 and the rotating scroll 522 offset from each other. Therefore, in this embodiment, as... Figure 2 and Figures 7-10 As shown, a crescent-shaped first compression chamber C1 is formed by the inner wall surface 522a of the rotating surround 522 and the outer wall surface 512b of the fixed surround 512, and a crescent-shaped second compression chamber C2 is formed by the inner wall surface 512a of the fixed surround 512 and the outer wall surface 522b of the rotating surround 522. Here, Figures 10-12 The final compression chamber C3 shown is formed by combining and integrating the first compression chamber C1 and the second compression chamber C2. In this embodiment, the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3 can constitute the aforementioned compression chamber H2.

[0057] The vortex 52 is assembled such that the center (axis) of the vortex substrate 521 is eccentrically positioned relative to the center (axis) of the fixed substrate 511, and is prevented from rotating by the rotation-stopping mechanism 300. It then revolves around the center of the fixed substrate 511 via the crank mechanism 70 through the rotation shaft 30. The radius of this revolving motion is defined by the contact between the fixed surrounding member 512 and the vortex surrounding member 522. Through this revolving motion, the first compression chamber C1 and the second compression chamber C2 move from the winding end 52c of the vortex surrounding member 522 and the winding end 51c of the fixed surrounding member 512 toward the center, thereby changing the volume of the first compression chamber C1 and the volume of the second compression chamber C2 in a decreasing direction. Therefore, the gaseous refrigerant introduced into the first compression chamber C1 from the winding end 52c side of the rotating coil 522 is compressed, and the gaseous refrigerant introduced into the second compression chamber C2 from the winding end 51c side of the fixed coil 512 is compressed. The gaseous refrigerant compressed in the first compression chamber C1 and the gaseous refrigerant compressed in the second compression chamber C2 are together in the final compression chamber C3, which combines the first compression chamber C1 and the second compression chamber C2 into one unit.

[0058] Figure 1 The discharge chamber H3 shown is formed by the third peripheral wall portion 241 of the rear outer casing 24, the bottom wall portion 242 of the rear outer casing 24, and the fixing base plate 511 for fixing the scroll 51. That is, the interior of the third peripheral wall portion 241 of the rear outer casing 24 constitutes the discharge chamber H3. A discharge hole L2 is formed at the radial center of the fixing base plate 511 of the fixing scroll 51, which communicates with the discharge chamber H3 through the compression chamber H2 (final compression chamber C3) that moves to the innermost side (where the volume becomes the smallest). Therefore, the gaseous refrigerant compressed in the compression chamber H2 (final compression chamber C3) of the scroll unit 50 is discharged to the discharge chamber H3 through the discharge hole L2. Additionally, a check valve 90, for example a reed valve, is installed on the other side of the fixed base plate 511 of the fixed scroll 51 facing the discharge chamber H3. The check valve 90 allows gaseous refrigerant to flow from the compression chamber H2 (final compression chamber C3) to the discharge chamber H3, but restricts the flow of gaseous refrigerant from the discharge chamber H3 to the compression chamber H2 (final compression chamber C3).

[0059] A gas-liquid separation chamber H4 is disposed within the rear outer casing 24. Specifically, in this embodiment, the gas-liquid separation chamber H4 is formed as a cylindrical space extending downward from the outer peripheral surface toward the interior through the bottom wall portion 242 of the rear outer casing 24. An oil separator 100 for separating lubricating oil contained in the gaseous refrigerant is disposed within the gas-liquid separation chamber H4. A centrifugal oil separator is used here, but it is not limited to this, and other types of oil separators may also be used. An outlet P2 is provided at the upper part of the oil separator 100 in the gas-liquid separation chamber H4. The outlet P2 is connected to the refrigerant circuit (high-pressure side) via a connecting pipe (not shown) or the like. In addition, a communication hole L3 is formed in the bottom wall portion 242 of the rear outer casing 24, which communicates the discharge chamber H3 with the gas-liquid separation chamber H4.

[0060] Therefore, the gaseous refrigerant in the discharge chamber H3, i.e., the gaseous refrigerant compressed in the compression chamber H2 (high-pressure gaseous refrigerant), flows into the gas-liquid separation chamber H4 through the connecting hole L3, and is separated from the lubricating oil by the oil separator 100. After that, it is discharged from the discharge port P2 to the high-pressure side of the aforementioned refrigerant circuit. On the other hand, the lubricating oil separated from the high-pressure gaseous refrigerant by the oil separator 100 is guided to the lower part of the gas-liquid separation chamber H4 under the action of gravity.

[0061] A back pressure chamber H5 is formed between the rotating base plate 521 of the rotating scroll 52 and the second partition wall portion 232 of the intermediate outer shell 23. In this embodiment, the back pressure chamber H5 includes the internal space of the hollow protrusion 233 of the second partition wall portion 232. A lubricating oil passage L4 connecting the back pressure chamber H5 and the gas-liquid separation chamber H4 is formed in the intermediate outer shell 23, the fixing base plate 511 of the fixed scroll 51, and the rear outer shell 24. A throttling orifice (throttling section) OL1 is disposed in the middle of the lubricating oil passage L4.

[0062] Therefore, in the gas-liquid separation chamber H4, the lubricating oil separated from the high-pressure gaseous refrigerant by the oil separator 100 (including the lubricating oil temporarily stored in the lower part of the gas-liquid separation chamber H4) is supplied to the back pressure chamber H5 via the lubricating oil passage L4.

[0063] In this embodiment, such as Figure 2 As shown, a first through hole 701 and a second through hole 702 are formed on the gyratory base plate 521 of the gyratory swivel disk 52. The first through hole 701 is formed through the gyratory base plate 521 at a position that allows the first compression chamber C1 to communicate with the back pressure chamber H5. The second through hole 702 is formed through the gyratory base plate 521 at a position that allows the second compression chamber C2 to communicate with the back pressure chamber H5. The first through hole 701 opens near the inner wall surface 522a of the gyratory surrounding member 522 in the gyratory base plate 521. In contrast, the second through hole 702 opens near the outer wall surface 522b of the gyratory surrounding member 522 in the gyratory base plate 521.

[0064] Next, refer to Figure 1 and Figure 5 The flow of gaseous refrigerant and lubricating oil in the scroll compressor 10 is explained. Figure 5 This is a block diagram illustrating the flow of gaseous refrigerant and lubricating oil in the scroll compressor 10. Additionally, in Figure 1 In the diagram, the flow of gaseous refrigerant before or after the lubricating oil is mixed is indicated by a slanted arrow; the flow of gaseous refrigerant containing lubricating oil is indicated by a black arrow; and the flow of lubricating oil separated from the gaseous refrigerant is indicated by a blank arrow.

[0065] like Figure 1 and Figure 5 As shown, low-pressure gaseous refrigerant from the aforementioned refrigerant circuit flows into the suction chamber H1 via the suction port P1, and then is introduced into the space H6 near the outer end of the scroll unit 50 via the refrigerant passage L1. The low-pressure gaseous refrigerant guided into space H6 is drawn into the compression chamber H2 (first compression chamber C1, second compression chamber C2, and final compression chamber C3) of the scroll unit 50 and compressed as the scroll unit 52 rotates. The compressed gaseous refrigerant (high-pressure gaseous refrigerant) in the compression chamber H2 is discharged into the discharge chamber H3 via the discharge port L2 (and check valve 90), and then flows into the gas-liquid separation chamber H4 via the connecting port L3. The gaseous refrigerant flowing into the gas-liquid separation chamber H4 is separated from the lubricating oil contained therein by the oil separator 100. Then, the gaseous refrigerant from which the lubricating oil has been separated by the oil separator 100 is discharged from the discharge port P2 back to the aforementioned refrigerant circuit. On the other hand, the lubricating oil separated from the gaseous refrigerant by the oil separator 100 flows from the lower part of the gas-liquid separation chamber H4 in the lubricating oil passage L4 and is supplied to the back pressure chamber H5. The back pressure chamber H5 can be connected to the compression chamber H2 (first compression chamber C1, second compression chamber C2 and final compression chamber C3) through the first through hole 701 and the second through hole 702.

[0066] Here, a throttling orifice OL1 is disposed midway through the lubricating oil passage L4. Therefore, the pressure of the lubricating oil separated from the gaseous refrigerant by the oil separator 100 is reduced from the pressure Pd in ​​the discharge chamber H3 and supplied to the back pressure chamber H5. Furthermore, the back pressure chamber H5 is connected to the compression chamber H2 (first compression chamber C1, second compression chamber C2, and final compression chamber C3) via the first through-hole 701 and the second through-hole 702. Therefore, the flow rate of fluid (lubricating oil and / or gaseous refrigerant) between the back pressure chamber H5 and the compression chamber H2 (first compression chamber C1, second compression chamber C2, and final compression chamber C3) is limited by the first through-hole 701 and the second through-hole 702, which function as throttling devices. As a result, the pressure in the back pressure chamber H5 is maintained at an intermediate pressure (back pressure) Pm between the pressure Ps in the suction chamber H1 and the pressure Pd in ​​the discharge chamber H3, and this intermediate pressure (back pressure) Pm presses the vortex 52 toward the fixed vortex 51. That is, the back pressure chamber H5 causes the back pressure Pm pressing towards the fixed scroll plate 51 to act on the rotating scroll plate 52. In other words, the back pressure chamber H5 can generate a back pressure Pm that presses the rotating scroll plate 52 towards the fixed scroll plate 51.

[0067] In addition, the first through hole 701 and the second through hole 702 can function as back pressure control holes for controlling back pressure Pm.

[0068] use Figures 6-12 The operation of the scroll compressor 10 with this structure will be explained. Figure 6 It is a graph showing the relationship between the pressure in the first compression chamber C1, the pressure in the second compression chamber C2, the pressure in the final compression chamber C3, the pressure in the back pressure chamber H5 (back pressure Pm), and the vortex rotation angle (crankshaft angle) of the gaseous refrigerant in the compression chamber H2 (first compression chamber C1 and second compression chamber C2) from the start of compression. Figures 7-12 This indicates the operating status of the scroll compressor 10.

[0069] The rotating shaft 30 rotates by the rotational driving force from the electric motor 40, and the rotary scroll 52 revolves around the axis of the fixed scroll 51 while being prevented from rotating by the rotation-stopping mechanism 300 via the crank mechanism 70. Through the rotary motion of the rotary scroll 52, the gaseous refrigerant is drawn from the suction port P1 through the suction chamber H1, the refrigerant passage L1 and the space H6 into the first compression chamber C1 and the second compression chamber C2 between the fixed surrounding member 512 and the rotary surrounding member 522 of the scroll unit 50.

[0070] In this embodiment, the extension angle up to the winding end 51c of the fixed winding member 512 is the same as the extension angle up to the winding end 52c of the rotating winding member 522. Therefore, as Figure 7As shown, while sealing the first compression chamber C1 by abutting the winding end 52c of the rotating coil 522 against the outer wall surface 512b of the fixed coil 512, sealing the second compression chamber C2 by abutting the winding end 51c of the fixed coil 512 against the outer wall surface 522b of the rotating coil 522. Furthermore, this... Figure 7 Corresponding to Figure 6 The crank angle is 0°.

[0071] exist Figure 6 During the period Z0 shown, through the revolution and rotation of the vortex disk 52, the volume of the first compression chamber C1 decreases and the internal pressure increases, and the volume of the second compression chamber C2 decreases and the internal pressure increases. During this period Z0, as... Figure 7 As shown, the first through hole 701 is located away from the first compression chamber C1, and the second through hole 702 is located away from the second compression chamber C2.

[0072] Next, from Figure 6 At the moment when period Z0 transitions to period Z1, the first through hole 701 deviates from the protruding end edge of the fixed surrounding member 512 that closes the first through hole 701, thereby opening the first through hole 701. Furthermore, at this moment, communication begins between the first compression chamber C1 and the back pressure chamber H5 via the first through hole 701 (see reference). Figure 8 The opening state of the first through hole 701 is as follows: Figure 6 This continues during periods Z1 and Z2. On the other hand, during period Z1, the second through hole 702 is located away from the second compression chamber C2. Here, during period Z1, the pressure (back pressure Pm) in the back pressure chamber H5 is higher than the pressure in the first compression chamber C1. Therefore, since the fluid in the back pressure chamber H5 flows into the first compression chamber C1 from the back pressure chamber H5 through the first through hole 701, the pressure in the first compression chamber C1 correspondingly becomes higher than the pressure in the second compression chamber C2. In addition, during this period Z1, it goes without saying that the volume of the first compression chamber C1 decreases and the internal pressure increases due to the revolution and rotation of the vortex disk 52, and the volume of the second compression chamber C2 decreases and the internal pressure increases.

[0073] During period Z1, the pressure in the first compression chamber C1 is higher than the pressure in the second compression chamber C2. Therefore, the rotational torque generated in the vortex disk 52 can be increased accordingly. In addition, the direction of this rotational torque is consistent with the direction of the vortex disk 52's revolution and rotational motion.

[0074] Next, from Figure 6At the moment when period Z1 transitions to period Z2, the second through hole 702 deviates from the protruding end edge of the fixed surrounding member 512 that closes the second through hole 702, thereby opening the second through hole 702. Furthermore, at this moment, communication begins between the second compression chamber C2 and the back pressure chamber H5 via the second through hole 702 (see reference). Figure 9 The opening state of the second through hole 702 is as follows: Figure 6 It continues during periods Z2 and Z3.

[0075] During this period, at a crank angle of 360° midway through Z2, the gaseous refrigerant compressed due to the volume reduction change of the first compression chamber C1 caused by the revolution and rotation of the vortex disk 52, and the gaseous refrigerant compressed due to the volume reduction change of the second compression chamber C2, are as follows: Figure 10 The mixture is shown to be mixed in the final compression chamber C3. During the period from the beginning of period Z2 to the crank angle 360°, the pressure relationship between the first compression chamber C1 and the second compression chamber C2 during period Z1 is maintained. It goes without saying that during the period from the beginning of period Z2 to the crank angle 360°, the volume of the first compression chamber C1 decreases and its internal pressure increases due to the revolution and rotation of the rotary scroll 52, and the volume of the second compression chamber C2 also decreases and its internal pressure increases. Therefore, during the period from the beginning of period Z2 to the crank angle 360°, the pressure in the first compression chamber C1 is also higher than the pressure in the second compression chamber C2, thus correspondingly increasing the rotational torque generated in the rotary scroll 52. Furthermore, the direction of this rotational torque is consistent with the direction of the revolution and rotation of the rotary scroll 52.

[0076] Furthermore, during the period from the start of period Z2 to the crank angle 360°, the pressure (back pressure Pm) in the back pressure chamber H5 is higher than the pressure in the second compression chamber C2. Therefore, as fluid flows from the back pressure chamber H5 into the second compression chamber C2 through the second through-hole 702, the pressure in the second compression chamber C2 increases accordingly. The same applies to the first compression chamber C1.

[0077] After the crank angle reaches 360° in Z2, the volume of the compression chamber C3 decreases and the internal pressure increases due to the revolution and rotation of the vortex disk 52.

[0078] Next, from Figure 6 At the moment when period Z2 transitions to period Z3, the first through hole 701 is closed by the protruding end edge of the fixed surround 512. That is, at this moment, the communication between the final compression chamber C3 and the back pressure chamber H5 via the first through hole 701 is cut off (see reference). Figure 11Subsequently, the first through hole 701 is located away from the final compression chamber C3. On the other hand, since the second through hole 702 remains open during Z3, the communication between the final compression chamber C3 and the back pressure chamber H5 continues via the second through hole 702.

[0079] Next, from Figure 6 At the moment when period Z3 transitions to period Z4, the second through hole 702 is closed by the protruding end edge of the fixed surround 512. That is, at this moment, the communication between the final compression chamber C3 and the back pressure chamber H5 via the second through hole 702 is cut off (see reference). Figure 12 ). Thereafter, the second through-hole 702 is located away from the final compression chamber C3.

[0080] Here, during period Z2, when the pressure in the final compression chamber C3 is higher than the pressure (back pressure Pm) in the back pressure chamber H5, the fluid in the final compression chamber C3 can flow into the back pressure chamber H5 through both the first through hole 701 and the second through hole 702. Furthermore, during period Z3, since the pressure in the final compression chamber C3 is higher than the pressure (back pressure Pm) in the back pressure chamber H5, the fluid in the final compression chamber C3 can flow into the back pressure chamber H5 through the second through hole 702.

[0081] Therefore, in Figure 6 In the process, during period Z1, the first compression chamber C1 is connected to the back pressure chamber H5 via the first through hole 701, but the second compression chamber C2 is not connected to the back pressure chamber H5. During the period from the beginning of period Z2 until the crankshaft angle reaches 360°, the first compression chamber C1 is connected to the back pressure chamber H5 via the first through hole 701, and the second compression chamber C2 is connected to the back pressure chamber H5 via the second through hole 702. During the period from the crankshaft angle reaching 360° until the end of period Z2, the final compression chamber C3 is connected to the back pressure chamber H5 via both the first through hole 701 and the second through hole 702. In period Z3, the final compression chamber C3 is connected to the back pressure chamber H5 via the second through hole 702, but the first compression chamber C1 is not connected to the back pressure chamber H5.

[0082] When the volume of the final compression chamber C3 is reduced by the revolution and rotation of the vortex 52, so that the pressure in the final compression chamber C3 reaches the discharge pressure, the check valve 90 opens, and the gaseous refrigerant in the final compression chamber C3 is discharged through the discharge port L2 and into the discharge chamber H3.

[0083] In the scroll compressor 10 of this embodiment, as described above, the center of the rotating base plate 521 is offset from the center 52b of the base circle 52a of the rotating surround 522. In this case, during one rotation of the rotating scroll 52, the distance α (not shown) between the center of the compressive reaction force acting on the rotating scroll 52 and the center of the rotating base plate 521 varies. If the first compression chamber C1 and the second compression chamber C2 have the same pressure, the center of the compressive reaction force acting on the rotating scroll 52 is located at the midpoint between the center of the base circle of the fixed surround 512 and the center 52b of the base circle 52a of the rotating surround 522. The higher the pressure in the first compression chamber C1 is than the pressure in the second compression chamber C2, the farther the center of the compressive reaction force is from the center of the rotating base plate 521 (i.e., the aforementioned distance α increases), and vice versa. Here, the aforementioned rotational torque is the torque about the center of the gyratory base plate 521, and is the product of the compressive reaction force and the aforementioned distance α. The compressive reaction force varies during one rotation of the gyratory vortex disk 52, for example, in... Figure 6 The crank angle shown is minimized around 360°. Therefore, in order to suppress the decrease in rotational torque around the crank angle of 360° where the compression reaction force is minimized, it is preferable to make the pressure in the first compression chamber C1 higher than the pressure in the second compression chamber C2 around the crank angle of 360°, so as to increase the aforementioned distance α around the crank angle of 360°.

[0084] Therefore, the following countermeasures were adopted in this embodiment [1].

[0085] [1] such as Figures 6-9 As shown, before the second compression chamber C2 connects to the back pressure chamber H5 via the second through hole 702, the first compression chamber C1 connects to the back pressure chamber H5 via the first through hole 701. Thus, for example, when from... Figure 6 During the period from the start of the periods Z1 and Z2 shown to the crank angle of 360°, the pressure difference between the first compression chamber C1 and the second compression chamber C2 can be increased, thereby suppressing the decrease in rotation torque.

[0086] By taking this countermeasure, for example, it is possible to suppress Figure 6 The crank angle shown is around 360°, which reduces the rotational torque, thus ensuring good contact between pin 302 and the inner circumferential surface of ring 301. Therefore, collision between pin 302 and ring 301 can be prevented, thereby suppressing vibration and noise generation in the rotation-stopping mechanism 300.

[0087] In addition, the following additional countermeasures may also be adopted in this embodiment [2].

[0088] [2] The opening angle up to the winding end 51c of the fixed winding member 512 is smaller than the opening angle up to the winding end 52c of the swirling winding member 522. Thus, after sealing the first compression chamber C1 by abutting the winding end 52c of the swirling winding member 522 against the outer wall surface 512b of the fixed winding member 512, the second compression chamber C2 is sealed by abutting the winding end 51c of the fixed winding member 512 against the outer wall surface 522b of the swirling winding member 522. Therefore, since the first compression chamber C1 always compresses the gaseous refrigerant before the second compression chamber C2, the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2, resulting in an increase in the generated rotational torque.

[0089] According to this embodiment, the scroll compressor 10 includes: a fixed scroll 51, which has a fixed base plate 511 having a discharge hole L2 at its center and a scroll-shaped fixed surrounding member 512 erected on the fixed base plate 511; a rotating scroll 52, which has a rotating base plate 521 and a scroll-shaped rotating surrounding member 522 erected on the rotating base plate 521 and engaging with the fixed surrounding member 512; a first compression chamber C1, which is formed by the inner wall surface 522a of the rotating surrounding member 522 and the outer wall surface 512b of the fixed surrounding member 512; and a second compression chamber C2, which is formed by the inner wall surface 512a of the fixed surrounding member 512 and the outer wall surface 512b of the fixed surrounding member 512. The outer wall surface 522b of the swirling coil member 522 is formed; a rotation-stopping mechanism 300 is formed to prevent the swirling coil member 52 from rotating; and a back pressure chamber H5 is provided on the back side of the swirling coil member 52. The rotation-stopping mechanism 300 prevents the swirling volute 52 from rotating, and the swirling volute 52 revolves around the axis of the fixed volute 51, causing the volumes of the first compression chamber C1 and the second compression chamber C2 to change respectively. This compresses the fluid (e.g., gaseous refrigerant) in the first compression chamber C1 and the fluid (e.g., gaseous refrigerant) in the second compression chamber C2 respectively, and they are discharged together from the discharge port L2 to the discharge chamber H3. The swirling base plate 521 has a first through hole 701 that connects the first compression chamber C1 and the back pressure chamber H5 and a second through hole 702 that connects the second compression chamber C2 and the back pressure chamber H5. Before the second compression chamber C2 is connected to the back pressure chamber H5 via the second through hole 702, the first compression chamber C1 is connected to the back pressure chamber H5 via the first through hole 701. Therefore, since the pressure in the first compression chamber C1 can be made higher than the pressure in the second compression chamber C2, the rotation torque generated in the vortex disk 52 can be increased accordingly, thereby suppressing the decrease in rotation torque.

[0090] According to this embodiment, such as Figure 6As shown, during the period when the pressure in the back pressure chamber H5 is higher than the pressure in the first compression chamber C1 and higher than the pressure in the second compression chamber C2, after the first compression chamber C1 and the back pressure chamber H5 begin to connect via the first through hole 701 (i.e., after the start period Z1), the second compression chamber C2 and the back pressure chamber H5 begin to connect via the second through hole 702 (i.e., during the start period Z2). Thus, the state in which the pressure in the first compression chamber C1 is higher than the pressure in the second compression chamber C2 can be maintained.

[0091] Furthermore, according to this embodiment, the rotation-stopping mechanism 300 includes: a ring 301, which is pressed into a circular hole formed in either the back surface of the rotary substrate 521 or the outer casing wall (e.g., the second partition wall portion 232) opposite to the back surface; and a pin 302, which protrudes from the other side and is fitted inside the ring 301. This structure can suppress the generation of vibration and noise in the rotation-stopping mechanism 300.

[0092] Furthermore, according to this embodiment, the fixed surrounding member 512 can be formed from an involute curve based on the base circle of the fixed surrounding member 512. The swirling surrounding member 522 can be formed from an involute curve based on the base circle 52a of the swirling surrounding member 522. The extension angle from the reference point on the base circle of the fixed surrounding member 512 to the winding end 51c of the fixed surrounding member 512 is the same as the extension angle from the reference point on the base circle 52a of the swirling surrounding member 522 to the winding end 52c of the swirling surrounding member 522. Therefore, as Figure 7 As shown, the first compression chamber C1 can be sealed by abutting the winding end 52c of the rotating member 522 against the outer wall surface 512b of the fixed member 512, while the second compression chamber C2 can be sealed by abutting the winding end 51c of the fixed member 512 against the outer wall surface 522b of the rotating member 522.

[0093] In this embodiment, the extension angle from the reference point on the base circle of the fixed surrounding member 512 to the winding end 51c of the fixed surrounding member 512 can be smaller than the extension angle from the reference point on the base circle 52a of the rotating surrounding member 522 to the winding end 52c of the rotating surrounding member 522. In this case, after sealing the first compression chamber C1 by abutting the winding end 52c of the rotating surrounding member 522 against the outer wall surface 512b of the fixed surrounding member 512, the second compression chamber C2 is sealed by abutting the winding end 51c of the fixed surrounding member 512 against the outer wall surface 522b of the rotating surrounding member 522. Therefore, since the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2, a rotational torque can always be generated in the rotating scroll 52, thereby suppressing the decrease of the rotational torque.

[0094] Furthermore, according to this embodiment, the center of the fixed substrate 511 is eccentric to the center of the base circle of the fixed surrounding member 512. Additionally, the center of the rotating substrate 521 is eccentric to the center 52b of the base circle 52a of the rotating surrounding member 522. In this structure of the scroll compressor 10, the generation of vibration and noise in the rotation-stopping mechanism 300 can be suppressed.

[0095] The drive source for driving the scroll compressor 10 of this embodiment is not limited to the electric motor 40, but may also be, for example, a vehicle engine.

[0096] Alternatively, the aforementioned scroll unit 50 (fixed scroll 51 and rotating scroll 52) can also be applied to a scroll expander. This scroll expander can, for example, be assembled in the refrigerant circuit of a vehicle steam circulation device, and cause the refrigerant introduced from the refrigerant circuit to expand and generate power (recovering power from the refrigerant).

[0097] The embodiments of the present invention have been described above. However, the present invention is not limited to the above embodiments, and modifications and alterations can be made based on the technical concept of the present invention, which is to be expected.

[0098] Symbol Explanation

[0099] 10…Scroll compressor, 20…Casing, 21…Front casing, 23…Intermediate casing, 24…Rear casing, 50…Scroll unit, 51…Fixed scroll, 51c…Winding end, 52…Rotating scroll, 52a…Base circle, 52b…Center, 52c…Winding end, 100…Oil separator, 232…Second partition (casing wall), 300…Rotation prevention mechanism, 301…Ring, 302…Pin, 303…Rotation prevention part, 511…Fixed base plate, 512…Fixed surrounding member, 512a… Inner wall surface, 512b…outer wall surface, 521…rotating base plate, 522…rotating surround, 522a…inner wall surface, 522b…outer wall surface, 701…first through hole, 702…second through hole, C1…first compression chamber, C2…second compression chamber, C3…final compression chamber, H1…suction chamber, H2…compression chamber, H3…discharge chamber, H4…gas-liquid separation chamber, H5…back pressure chamber, H6…space, L1…refrigerant passage, L2…discharge hole, L3…connecting hole, L4…lubricating oil passage, OL1…throttling hole.

Claims

1. A scroll compressor, comprising: A fixed scroll plate having a fixed base plate with a discharge hole in the center and a vortex-shaped fixed surround member erected on the fixed base plate. A swirling scroll, the swirling scroll having a swirling base plate and a swirling, spiral-shaped spiraling member erected on the swirling base plate and engaging with the fixed spiral member; The first compression chamber is formed by the inner wall surface of the swirling ring and the outer wall surface of the fixed ring; The second compression chamber is formed by the inner wall surface of the fixed surrounding member and the outer wall surface of the rotating surrounding member; A rotation-stopping mechanism, which prevents the rotation of the gyratory scroll; and A back pressure chamber is located on the back side of the vortex disk. The rotation-stopping mechanism prevents the rotation of the vortex disk, and causes the vortex disk to revolve around the axis of the fixed vortex disk, thereby changing the volumes of the first and second compression chambers. This compresses the fluids in the first and second compression chambers respectively, and the fluids are then discharged together from the discharge port into the discharge chamber. The rotary substrate has a first through hole that connects the first compression chamber to the back pressure chamber and a second through hole that connects the second compression chamber to the back pressure chamber. Before the second compression chamber is connected to the back pressure chamber via the second through hole, the first compression chamber is connected to the back pressure chamber via the first through hole, thereby suppressing the decrease in the rotation torque generated in the vortex disk due to the compression reaction force.

2. The scroll compressor as described in claim 1, characterized in that, During a period when the pressure in the back pressure chamber is higher than the pressure in the first compression chamber and higher than the pressure in the second compression chamber, after the communication between the first compression chamber and the back pressure chamber via the first through hole begins, the communication between the second compression chamber and the back pressure chamber via the second through hole begins.

3. The scroll compressor as described in claim 1 or 2, characterized in that, The rotation-stopping mechanism includes: a ring pressed into a circular hole formed on either the back side of the gyroscopic substrate or on the outer casing wall opposite the back side; and a pin protruding from the other side and fitting inside the ring.

4. The scroll compressor as described in any one of claims 1 to 3, characterized in that, The extension angle from the reference point on the base circle of the fixed surround to the winding end of the fixed surround is the same as the extension angle from the reference point on the base circle of the rotary surround to the winding end of the rotary surround.

5. The scroll compressor as described in any one of claims 1 to 4, characterized in that, While sealing the first compression chamber by abutting the winding end of the swirling member against the outer wall surface of the fixed member, the second compression chamber is sealed by abutting the winding end of the fixed member against the outer wall surface of the swirling member.

6. The scroll compressor as described in any one of claims 1 to 3, characterized in that, The spread angle from the reference point on the base circle of the fixed surround to the winding end of the fixed surround is smaller than the spread angle from the reference point on the base circle of the rotary surround to the winding end of the rotary surround.

7. The scroll compressor as described in any one of claims 1 to 3, characterized in that, After sealing the first compression chamber by abutting the end of the winding of the swirling member against the outer wall of the fixed member, the second compression chamber is sealed by abutting the end of the winding of the fixed member against the outer wall of the swirling member.

8. The scroll compressor as described in any one of claims 1 to 7, characterized in that, The center of the fixed base plate is off-center from the center of the base circle of the fixed surround. The center of the swivel substrate is off-center from the center of the base circle of the swivel surround.

Images