Scroll Compressor

Abstract

To restrain deterioration of rotation moment generated in a turning scroll.SOLUTION: A scroll type compressor 10 includes a fixed scroll 51, a turning scroll 52, a rotation prevention mechanism 300, and a back pressure chamber H5. A spiral turning lap 522 of the turning scroll 52 is meshed with a spiral fixed lap 512 of the fixed scroll 51. A first compression chamber C1 is formed by an inner wall surface 522a of the turning lap 522 and an outer wall surface 512b of the fixed lap 512. A second compression chamber C2 is formed by an inner wall surface 512a of the fixed lap 512 and an outer wall surface 522b of the turning lap 522. A turning base plate 521 of the turning scroll 52 includes a first through hole 701 which can communicate the first compression chamber C1 with the back pressure chamber H5, and a second through hole 702 which can communicate the second compression chamber C2 with the back pressure chamber H5. Before the second compression chamber C2 is communicated with the back pressure chamber H5 through the second through hole 702, the first compression chamber C1 is communicated with the back pressure chamber H5 through the first through hole 701.SELECTED DRAWING: Figure 8

Description

[Technical field]

[0001] The present invention relates to a scroll compressor for use in a vehicle air conditioner or the like. [Background technology]

[0002] The scroll compressor disclosed in Patent Document 1 includes a scroll unit in which a fixed scroll and an orbiting scroll (movable scroll) are provided with a spiral wrap standing on a base plate (bottom plate) and the center of the base plate and the center of the base circle of the wrap (spiral center) are eccentric to each other, and the wraps are meshed with each other to form an enclosed space, and a rotation prevention mechanism that prevents the rotation of the orbiting scroll, and the volume of the enclosed space is changed by causing the orbiting scroll to revolve around the axis of the fixed scroll while preventing the rotation of the orbiting scroll by the rotation prevention mechanism. Patent Document 1 discloses that the rotation prevention mechanism is composed of a circular hole formed on the back surface of the base plate of the orbiting scroll and a pin that protrudes from the housing wall facing the back surface of the base plate of the orbiting scroll and engages with the circular hole. Patent Document 1 also discloses that a rotation moment is generated in the orbiting scroll due to a compression reaction force associated with compression by the scroll compressor, and a load due to this rotation moment acts on the rotation prevention mechanism. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2015-059517 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, the present inventors have found that during operation of the scroll compressor as described above, the rotational moment is momentarily lost, and as a result, the pin momentarily separates from the inner circumferential surface of the circular hole and then collides with the inner circumferential surface of the circular hole again.

[0005] Therefore, an object of the present invention is to suppress a decrease in the rotational moment generated in the orbiting scroll. [Means for solving the problem]

[0006] According to one aspect of the present invention, there is provided a scroll-type compressor, which includes a fixed base having a discharge hole at its center, a fixed scroll having a spiral-shaped fixed wrap standing on the fixed base, an orbiting base, and an orbiting scroll having a spiral-shaped orbiting wrap standing on the orbiting base and meshing with the fixed wrap, a first compression chamber formed by an inner wall surface of the orbiting wrap and an outer wall surface of the fixed wrap, a second compression chamber formed by the inner wall surface of the fixed wrap and the outer wall surface of the orbiting wrap, a rotation prevention mechanism for preventing the orbiting scroll from rotating on its axis, and a back pressure chamber provided on the back side of the orbiting scroll, and while preventing the orbiting scroll from rotating on its axis by the rotation prevention mechanism, the orbiting scroll is caused to revolve around the axis of the fixed scroll to change the volumes of the first compression chamber and the second compression chamber, thereby compressing the fluids in the first compression chamber and the second compression chamber and discharging them together from the discharge hole to the discharge chamber. The pivot base plate has a first through hole that can communicate the first compression chamber and the back pressure chamber, and a second through hole that can communicate the second compression chamber and the back pressure chamber. Before the second compression chamber communicates with the back pressure chamber through the second through hole, the first compression chamber communicates with the back pressure chamber through the first through hole. Effect of the Invention

[0007] According to the present invention, the pressure in the first compression chamber can be made higher than the pressure in the second compression chamber, thereby increasing the rotational moment generated in the orbiting scroll and thereby suppressing a decrease in the rotational moment. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a cross-sectional view showing a schematic configuration of a scroll compressor according to an embodiment of the present invention. [Diagram 2] Plan view of the orbiting scroll [Diagram 3] An enlarged cross-sectional view of the rotation prevention portion that constitutes the rotation prevention mechanism. [Figure 4] Layout of the rotation prevention part of the rotation prevention mechanism on the rotating base plate [Diagram 5] FIG. 2 is a block diagram illustrating the flow of gas refrigerant and lubricating oil in the scroll compressor. [Figure 6] A diagram showing the relationship between the pressure in the compression chamber and the pressure in the back pressure chamber and the volute angle (crank angle) [Figure 7] A diagram showing the operating state of a scroll compressor. [Figure 8] A diagram showing the operating state of a scroll compressor. [Figure 9] A diagram showing the operating state of a scroll compressor. [Figure 10] A diagram showing the operating state of a scroll compressor. [Figure 11] A diagram showing the operating state of a scroll compressor. [Figure 12] A diagram showing the operating state of a scroll compressor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

[0010] Fig. 1 is a cross-sectional view showing a schematic configuration of a scroll compressor 10 according to an embodiment of the present invention. The scroll compressor 10 is incorporated in a refrigerant circuit of a vehicle air conditioner or the like, and is configured to receive low-pressure gas refrigerant from the refrigerant circuit, compress it, increase the pressure, and return it to the refrigerant circuit. The left side in Fig. 1 is the front side of the scroll compressor 10, the right side in Fig. 1 is the rear side of the scroll compressor 10, the upper side in Fig. 1 is the upper side of the scroll compressor 10, and the lower side in Fig. 1 is the lower side of the scroll compressor 10. The above-mentioned gas refrigerant is an example of a fluid in the present invention.

[0011] 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 that is driven by the rotating shaft 30 to compress a (low-pressure) gas 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 accommodated in the housing 20. The scroll unit 50 includes a fixed scroll 51 and an orbiting scroll 52 that orbits relative to the fixed scroll 51. The fixed scroll 51 and the orbiting scroll 52 are disposed opposite to each other in the central axial direction of the scroll compressor 10.

[0012] The housing 20 includes a front housing 21, a cover member 22, a center housing 23, and a rear housing 24. These are fastened together by fasteners (not shown) or the like to form the housing 20 of the scroll compressor 10.

[0013] The front housing 21 has a cylindrical first circumferential wall portion 211 extending in the front-rear direction, and a first partition portion 212 dividing the interior of the first circumferential wall portion 211 into front and rear portions. A front end surface of the first circumferential wall portion 211 constitutes a front end surface of the front housing 21, and a rear end surface of the first circumferential wall portion 211 constitutes a rear end surface of the front housing 21. In this embodiment, the interior of the first circumferential wall portion 211 (i.e., the internal space of the front housing 21) is divided by the first partition portion 212 into a front inverter accommodating space that accommodates the inverter 60, and a rear motor accommodating space that accommodates the electric motor 40. In other words, the electric motor 40 and the inverter 60 are accommodated in the front housing 21.

[0014] The first partition wall portion 212 is provided with a support portion 213 that supports a front end portion of the rotating shaft 30. Specifically, in this embodiment, the support portion 213 is formed to protrude cylindrically from the rear surface of the first partition wall portion 212 into the motor accommodating space, and is configured to rotatably support the front end portion of the rotating shaft 30 via a first bearing 214 mounted therein.

[0015] A cover member 22 is joined to the front end surface of the front housing 21, thereby closing off the inverter accommodating space (forming an inverter accommodating chamber). A front end surface of the center housing 23 is joined to the rear end surface of the front housing 21. Note that seal members may be disposed between the front housing 21 and the cover member 22 and between the front housing 21 and the center housing 23, as necessary.

[0016] The center housing 23 has a cylindrical second circumferential wall portion 231 extending in the front-rear direction, and a second partition portion 232 that divides the interior of the second circumferential wall portion 231 into front and rear portions. A front end surface of the second circumferential wall portion 231 constitutes a front end surface of the center housing 23, and a rear end surface of the second circumferential wall portion 231 constitutes a rear end surface of the center housing 23. In this embodiment, the interior of the second circumferential wall portion 231 (i.e., the internal space of the center housing 23) is divided by the second partition portion 232 into a front connection space connected to the motor accommodating space of the front housing 21, and a rear scroll accommodating space that accommodates the scroll unit 50. In other words, the scroll unit 50 is accommodated in the center housing 23.

[0017] The second partition wall portion 232 has a hollow protruding portion 233 protruding toward the front housing 21 (motor accommodating space). The hollow protruding portion 233 is provided at the radial center of the second partition wall portion 232 so as to face the support portion 213 provided in the first partition wall portion 212 of the front housing 21. At the top of the hollow protruding portion 233, an insertion hole 234 is formed that communicates the inside and outside of the hollow protruding portion 233 and through which the rear end side of the rotating shaft 30 is inserted. In addition, a second bearing 235 that rotatably supports a portion of the rear end side of the rotating shaft 30 is attached inside the hollow protruding portion 233. That is, in this embodiment, the rotating shaft 30 is rotatably supported by the first bearing 214 provided on the front housing 21 side and the second bearing 235 provided on the center housing 23 side.

[0018] The front end surface of the rear housing 24 is joined to the rear end surface of the center housing 23. In this embodiment, a recess 236 is formed in the rear end surface of the center housing 23, i.e., the rear end surface of the second peripheral wall portion 231, to accommodate an outer edge portion of a fixed base plate 511 of a fixed scroll 51 constituting the scroll unit 50. The outer edge portion of the fixed base plate 511 of the fixed scroll 51 is sandwiched between the center housing 23 and the rear housing 24, whereby the fixed scroll 51 is fixed and the rear opening of the second peripheral wall portion 231 is closed by the fixed base plate 511 of the fixed scroll 51. A seal member may be disposed between the center housing 23 and the rear housing 24 as necessary.

[0019] The rear housing 24 is formed in a cylindrical shape with a bottom, and has a cylindrical third circumferential wall portion 241 extending in the front-rear direction, and a bottom wall portion 242 closing an opening on the rear side of the third circumferential wall portion 241. The front end surface of the third circumferential wall portion 241 constituting the front end surface of the rear housing 24 is joined to the rear end surface of the second circumferential wall portion 231 which is the rear end surface of the center housing 23, so that the opening on the front side of the third circumferential wall portion 241 is closed by the fixed base plate 511 of the fixed scroll 51.

[0020] The electric motor 40 is, for example, a three-phase AC motor, and includes a stator core unit 41 and a rotor 42.

[0021] The stator core unit 41 is fixed to an inner circumferential surface of the first circumferential wall portion 211 of the front housing 21. A direct current from an in-vehicle battery (not shown) or the like is converted into an alternating current by an inverter 60 and supplied to the stator core unit 41.

[0022] The rotor 42 is disposed radially inside the stator core unit 41 with a predetermined gap therebetween. A permanent magnet is incorporated in the rotor 42. The rotor 42 is formed in a cylindrical shape, and is fixed to the rotating shaft 30 with the rotating shaft 30 inserted into its hollow portion. In other words, the rotor 42 is integrated with the rotating shaft 30.

[0023] When a magnetic field is generated in the stator core unit 41 by power supply from the inverter 60, a torque acts on the permanent magnet of the rotor 42, causing the rotor 42 to rotate, thereby rotating the rotary shaft 30.

[0024] As described above, the scroll unit 50 includes the fixed scroll 51 and the orbiting scroll 52 that orbits relative to the fixed scroll 51.

[0025] The fixed scroll 51 has a disk-shaped fixed base plate 511 and a spiral fixed wrap 512 standing on one surface of the fixed base plate 511. In the fixed scroll 51 of this embodiment, the spiral fixed wrap 512 is integrally standing on the fixed base plate 511. The fixed wrap 512 extends in a spiral shape on the one surface of the fixed base plate 511 from an inner end (a winding start end) on the radial inside to an outer end (a winding end) 51c (see FIG. 7) on the radial outside. The fixed scroll 51 is fixed by having an outer edge of the fixed base plate 511 sandwiched between the center housing 23 and the rear housing 24 with the one surface of the fixed base plate 511 (the surface on which the fixed wrap 512 is standing) facing forward.

[0026] FIG. 2 is a plan view of the orbiting scroll 52. As shown in FIG. 1 and FIG. 2, the orbiting scroll (movable scroll) 52 has a disk-shaped orbiting base plate (movable base plate) 521 and an orbiting wrap (movable wrap) 522 erected on one surface of the orbiting base plate 521. In the orbiting scroll 52 of this embodiment, a spiral orbiting wrap 522 is integrally erected on the orbiting base plate 521. The orbiting wrap 522 extends in a spiral shape on the one surface of the orbiting base plate 521 from an inner end (winding start portion) on the radial inner side to an outer end (winding end portion) 52c on the radial outer side. The orbiting scroll 52 is arranged so that the orbiting wrap 522 meshes with the fixed wrap 512 of the fixed scroll 51. That is, the orbiting scroll 52 is disposed between the second partition wall portion 232 of the center housing 23 and the fixed scroll 51 with the one surface of the orbiting base plate 521 (the surface on which the orbiting wrap 522 is erected) facing rearward. Here, the fixed scroll 51 and the orbiting scroll 52 are disposed such that the fixed wrap 512 and the orbiting wrap 522 are engaged with each other, the protruding edge of the fixed wrap 512 contacts the orbiting base plate 521, and the protruding edge of the orbiting wrap 522 contacts the fixed base plate 511. A tip seal is provided on each of the protruding edge of the fixed wrap 512 and the protruding edge of the orbiting wrap 522.

[0027] In this embodiment, the orbiting wrap 522 is formed to follow an involute curve (virtual line) extending from a base circle (virtual circle) 52a, as shown in Fig. 2. Here, the inflection angle of the orbiting wrap 522 is an angle around the center (fixed spiral center) 52b of the base circle 52a, and is the angle from a reference point (start point of the involute curve) on the base circle 52a to a winding end 52c of the orbiting wrap 522.

[0028] Although not shown, the fixed wrap 512 is also formed to follow an involute curve (virtual line) extending from a base circle (virtual circle) like the orbiting wrap 522. Here, the expansion angle of the fixed wrap 512 is the angle around the center of the base circle (fixed spiral center) of the fixed wrap 512, and is the angle from a reference point on the base circle (start point of the involute curve) to the winding end 51c of the fixed wrap 512 (see FIG. 7).

[0029] In this embodiment, the expansion angle of the fixed wrap 512 is the same as the expansion angle of the orbiting wrap 522. However, the expansion angle of the fixed wrap 512 and the expansion angle of the orbiting wrap 522 may be different.

[0030] In this embodiment, the fixed wrap 512 is formed with the center of its base circle eccentric with respect to the center (not shown) of the fixed substrate 511. Also, the orbiting wrap 522 is formed with the center 52b of its base circle 52a eccentric with respect to the center (not shown) of the orbiting substrate 521. This makes it possible to reduce the outer diameter of the scroll unit 50, reduce the body diameter of the scroll compressor 10, and reduce the size of the scroll compressor 10.

[0031] The orbiting scroll 52 is driven by the rotating shaft 30 via a crank mechanism 70 and configured to perform orbital motion relative to the fixed scroll 51 , in other words, to revolve around the axis of the fixed scroll 51 .

[0032] The crank mechanism 70 is configured to connect the rotary shaft 30 and the orbiting scroll 52 and convert the rotational motion of the rotary shaft 30 into the orbiting motion of the orbiting scroll 52. In this embodiment, the crank mechanism 70 is disposed inside the hollow protruding portion 233 of the second partition wall portion 232 of the center housing 23. The crank mechanism 70 includes a crank pin 71 erected on the rear end of the rotary shaft 30, an eccentric bush 72 eccentrically attached to the crank pin 71, and a cylindrical portion 73 protruding from the rear surface of the orbiting base plate 521 of the orbiting scroll 52. The eccentric bush 72 is rotatably supported on the inner circumferential surface of the cylindrical portion 73 via a bearing (not shown). A balancer weight 74 is attached to the rear end of the rotary shaft 30 to counter the centrifugal force generated by the orbiting motion of the orbiting scroll 52.

[0033] The scroll unit 50 is configured to take in and compress a low-pressure gaseous refrigerant by the orbiting scroll 52 orbiting relative to the fixed scroll 51. An annular thrust plate 80 is disposed between the orbiting base plate 521 of the orbiting scroll 52 and the second partition wall portion 232 of the center housing 23, and the rear surface of the second partition wall portion 232 receives a thrust force from the orbiting scroll 52 via the thrust plate 80.

[0034] The rotation of the orbiting scroll 52 can be prevented by a rotation-preventing mechanism 300. Here, the rotation-preventing mechanism 300 will be described with reference to FIGS.

[0035] Fig. 3 is an enlarged cross-sectional view of rotation-preventing portion 303 constituting rotation-preventing mechanism 300. Fig. 4 is a layout diagram of rotation-preventing portion 303 of rotation-preventing mechanism 300 on swivel base plate 521.

[0036] As shown in Fig. 3, the rotation prevention mechanism 300 is configured by arranging a plurality of rotation prevention parts 303 (five in this embodiment) at equal intervals along the circumferential direction near the outer periphery of the back surface of the orbiting base plate 521, the rotation prevention parts 303 being each composed of a ring 301 press-fitted into a circular hole formed in the back surface, which is the other surface of the orbiting base plate 521, and a pin 302 protruding from the second partition wall part 232 of the center housing 23, penetrating the thrust plate 80, and loosely fitting inside the ring 301, as shown in Fig. 4. Note that if there are at least three rotation prevention parts 303, the orbiting scroll 52 can make an orbital movement around the axis of the fixed scroll 51 without rotating on its axis. Here, the second partition wall part 232 is an example of the "housing wall" in the present invention.

[0037] Returning to FIG. 1, in this embodiment, the scroll compressor 10 has a suction chamber H1 into which low-pressure gas refrigerant flows, a compression chamber H2 that compresses the low-pressure gas refrigerant, a discharge chamber H3 from which the gas refrigerant compressed in the compression chamber H2 is discharged, a gas-liquid separation chamber H4 that separates lubricating oil from the gas refrigerant compressed in the compression chamber H2, and a back pressure chamber H5 provided on the rear side of the rotating scroll 52 (the rear side of the rotating base plate 521).

[0038] The suction chamber H1 is defined by a first peripheral wall portion 211 of the front housing 21, a first partition wall portion 212 of the front housing 21, a second peripheral wall portion 231 of the center housing 23, and a second partition wall portion 232 of the center housing 23. That is, in this embodiment, the suction chamber H1 is defined by the motor accommodating space of the front housing 21 and the connecting space of the center housing 23. The first peripheral wall portion 211 is provided with a suction port P1. The suction port P1 is connected to the refrigerant circuit (the low pressure side of the refrigerant circuit) via a connecting pipe (not shown) or the like. Therefore, the low pressure refrigerant from the refrigerant circuit flows into the suction chamber H1 through the suction port P1. In addition, the center housing 23 is provided with a refrigerant passage L1 for guiding the low pressure gas refrigerant in the suction chamber H1 to a space H6 near the outer end of the scroll unit 50.

[0039] The compression chamber H2 is formed in the scroll unit 50, i.e., between the fixed scroll 51 and the orbiting scroll 52. The scroll unit 50 is configured to compress the low-pressure gaseous refrigerant by taking in the low-pressure gaseous refrigerant from the space H6 when the compression chamber H2 is formed.

[0040] In this embodiment, the fixed scroll 51 and the orbiting scroll 52 are disposed so that the wall surface of the fixed wrap 512 and the wall surface of the orbiting wrap 522 are partially in contact with each other with the fixed wrap 512 and the orbiting wrap 522 being offset from each other in the circumferential direction. Therefore, in this embodiment, as shown in FIG. 2 and FIG. 7 to FIG. 10, the inner wall surface 522a of the orbiting wrap 522 and the outer wall surface 512b of the fixed wrap 512 form a crescent-shaped first compression chamber C1, and the inner wall surface 512a of the fixed wrap 512 and the outer wall surface 522b of the orbiting wrap 522 form a crescent-shaped second compression chamber C2. Here, the final compression chamber C3 shown in FIG. 10 to FIG. 12 is formed by combining the first compression chamber C1 and the second compression chamber C2 into one body. In this embodiment, the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3 can constitute the above-mentioned compression chamber H2.

[0041] The orbiting scroll 52 is assembled so that the center (axial center) of the orbiting base plate 521 is eccentric to the center (axial center) of the fixed base plate 511, and while its rotation is prevented by the rotation prevention mechanism 300, it is caused to revolve around the center of the fixed base plate 511 via the crank mechanism 70 by the rotating shaft 30. The orbital radius of this orbital motion can be determined by the contact between the fixed wrap 512 and the orbiting wrap 522. By this orbital motion, the first compression chamber C1 and the second compression chamber C2 are moved from the winding end end 52c of the orbiting wrap 522 and the winding end end 51c of the fixed wrap 512 toward the center, and the volumes of the first compression chamber C1 and the second compression chamber C2 are each changed in a decreasing direction. Therefore, the gas refrigerant taken into the first compression chamber C1 from the winding end 52c side of the orbiting wrap 522 is compressed, and the gas refrigerant taken into the second compression chamber C2 from the winding end 51c side of the fixed wrap 512 is compressed. The gas refrigerant compressed in the first compression chamber C1 and the gas refrigerant compressed in the second compression chamber C2 are combined in the final compression chamber C3, which is formed by combining the first compression chamber C1 and the second compression chamber C2.

[0042] 1 is formed by the third peripheral wall portion 241 of the rear housing 24, the bottom wall portion 242 of the rear housing 24, and the fixed base plate 511 of the fixed scroll 51. That is, the inside of the third peripheral wall portion 241 of the rear housing 24 constitutes the discharge chamber H3. A discharge hole L2 is formed in the radial center of the fixed base plate 511 of the fixed scroll 51, which communicates the compression chamber H2 (final compression chamber C3) that has moved most inward (has the smallest volume) with the discharge chamber H3. Therefore, the gas refrigerant compressed in the compression chamber H2 (final compression chamber C3) of the scroll unit 50 is discharged through the discharge hole L2 into the discharge chamber H3. Furthermore, on the other surface of the fixed base plate 511 of the fixed scroll 51 facing the discharge chamber H3, a check valve 90, for example a reed valve, is attached which allows the flow of gaseous refrigerant 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).

[0043] The gas-liquid separation chamber H4 is provided in the rear housing 24. Specifically, in this embodiment, the gas-liquid separation chamber H4 is formed as a cylindrical space extending downward from the outer circumferential surface toward the inside of the bottom wall portion 242 of the rear housing 24. An oil separator 100 that separates lubricating oil contained in the gas refrigerant is disposed in the gas-liquid separation chamber H4. Here, a centrifugal separation type oil separator is used, but the present invention is not limited to this, and other types of oil separators may be used. A discharge port P2 is provided above the oil separator 100 in the gas-liquid separation chamber H4. The discharge port P2 is connected to the refrigerant circuit (the high pressure side) via a connecting pipe (not shown) or the like. In addition, a communication hole L3 that communicates the discharge chamber H3 and the gas-liquid separation chamber H4 is formed in the bottom wall portion 242 of the rear housing 24.

[0044] Therefore, the gas refrigerant in the discharge chamber H3, i.e., the gas refrigerant compressed in the compression chamber H2 (high-pressure gas refrigerant), flows into the gas-liquid separation chamber H4 through the communication hole L3, where the lubricating oil is separated by the oil separator 100, and then discharged to the high-pressure side of the refrigerant circuit from the discharge port P2. Meanwhile, the lubricating oil separated from the high-pressure gas refrigerant by the oil separator 100 is guided by gravity to the lower part of the gas-liquid separation chamber H4.

[0045] The back pressure chamber H5 is formed between the orbiting base plate 521 of the orbiting scroll 52 and the second partition wall portion 232 of the center housing 23. In this embodiment, the back pressure chamber H5 includes the internal space of the hollow protruding portion 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 center housing 23, the fixed base plate 511 of the fixed scroll 51, and the rear housing 24. An orifice (throttling portion) OL1 is disposed in the middle of the lubricating oil passage L4.

[0046] Therefore, in the gas-liquid separation chamber H4, the lubricating oil separated from the high-pressure gas 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.

[0047] In this embodiment, as shown in FIG. 2, a first through hole 701 and a second through hole 702 are formed in the orbiting base plate 521 of the orbiting scroll 52. The first through hole 701 is formed through the orbiting base plate 521 at a position that allows the first compression chamber C1 and the back pressure chamber H5 to communicate with each other. The second through hole 702 is formed through the orbiting base plate 521 at a position that allows the second compression chamber C2 and the back pressure chamber H5 to communicate with each other. The first through hole 701 opens near the inner wall surface 522a of the orbiting wrap 522 in the orbiting base plate 521. On the other hand, the second through hole 702 opens near the outer wall surface 522b of the orbiting wrap 522 in the orbiting base plate 521.

[0048] Next, the flow of the gas refrigerant and the lubricating oil in the scroll compressor 10 will be described with reference to Fig. 1 and Fig. 5. Fig. 5 is a block diagram for explaining the flow of the gas refrigerant and the lubricating oil in the scroll compressor 10. In Fig. 1, the flow of the gas refrigerant before the lubricating oil is mixed or after the lubricating oil is separated is indicated by hatched arrows, the flow of the gas refrigerant containing the lubricating oil is indicated by filled arrows, and the flow of the lubricating oil separated from the gas refrigerant is indicated by hollow arrows.

[0049] As shown in FIG. 1 and FIG. 5, the low-pressure gas refrigerant from the refrigerant circuit flows into the suction chamber H1 through the suction port P1, and is then guided to the space H6 near the outer end of the scroll unit 50 through the refrigerant passage L1. The low-pressure gas refrigerant guided to the space H6 is taken into the compression chamber H2 (the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3) of the scroll unit 50 along with the orbital motion of the orbiting scroll 52, and compressed. The gas refrigerant (high-pressure gas refrigerant) compressed in the compression chamber H2 is discharged to the discharge chamber H3 through the discharge hole L2 (and the check valve 90), and then flows into the gas-liquid separation chamber H4 through the communication hole L3. The lubricating oil contained in the gas refrigerant that flows into the gas-liquid separation chamber H4 is separated by the oil separator 100. The gas refrigerant from which the lubricating oil has been separated by the oil separator 100 is discharged to the refrigerant circuit from the discharge port P2. Meanwhile, the lubricating oil separated from the gas refrigerant by the oil separator 100 flows through the lubricating oil passage L4 from the lower part of the gas-liquid separation chamber H4 and is supplied to the back pressure chamber H5. The back pressure chamber H5 can be communicated with the compression chamber H2 (the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3) via the first through hole 701 and the second through hole 702.

[0050] Here, an orifice OL1 is disposed in the middle of the lubricating oil passage L4. Therefore, the lubricating oil separated from the gas refrigerant by the oil separator 100 is supplied to the back pressure chamber H5 with its pressure reduced from the pressure Pd in ​​the discharge chamber H3. The back pressure chamber H5 can also communicate with the compression chamber H2 (the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3) via the first through hole 701 and the second through hole 702. Therefore, the first through hole 701 and the second through hole 702, which can function as a throttle section, limit the flow rate of the fluid (lubricating oil and / or gas refrigerant) moving between the back pressure chamber H5 and the compression chamber H2 (the first compression chamber C1, the second compression chamber C2, and the final compression chamber C3). 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 the intermediate pressure (back pressure) Pm presses the orbiting scroll 52 toward the fixed scroll 51. In other words, the back pressure chamber H5 generates the back pressure Pm that presses the orbiting scroll 52 toward the fixed scroll 51.

[0051] The first through-hole 701 and the second through-hole 702 can function as back pressure control holes that control the back pressure Pm.

[0052] The operation of the scroll compressor 10 having such a configuration will be described with reference to Fig. 6 to Fig. 12. Fig. 6 is a diagram showing the relationship between the pressure in the first compression chamber C1, the pressure in the second compression chamber C2, and the pressure in the final compression chamber C3, the pressure in the back pressure chamber H5 (back pressure Pm), and the volute angle (crank angle) from the start of compression of the gas refrigerant in the compression chamber H2 (the first compression chamber C1 and the second compression chamber C2). Figs. 7 to 12 show the operating states of the scroll compressor 10.

[0053] The rotary shaft 30 is rotated by the rotary driving force from the electric motor 40, and the orbiting scroll 52 revolves around the axis of the fixed scroll 51 via the crank mechanism 70 while its rotation is prevented by the rotation-preventing mechanism 300. The orbiting motion of the orbiting scroll 52 causes the gaseous refrigerant to be 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 wrap 512 and the orbiting wrap 522 of the scroll unit 50.

[0054] In this embodiment, the expansion angle to the winding end 51c of the fixed wrap 512 is the same as the expansion angle to the winding end 52c of the orbiting wrap 522. Therefore, as shown in Fig. 7, the winding end 52c of the orbiting wrap 522 abuts against the outer wall surface 512b of the fixed wrap 512 to seal the first compression chamber C1, and at the same time, the winding end 51c of the fixed wrap 512 abuts against the outer wall surface 522b of the orbiting wrap 522 to seal the second compression chamber C2. Note that Fig. 7 corresponds to a crank angle of 0° in Fig. 6.

[0055] 6, the volume of the first compression chamber C1 decreases and the internal pressure increases due to the orbital motion of the orbiting scroll 52, and the volume of the second compression chamber C2 decreases and the internal pressure increases. During this period Z0, as shown in FIG 7, 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.

[0056] Next, at the time when the period Z0 in FIG. 6 is changed to the period Z1, the first through hole 701 is released from the end edge of the protruding side of the fixed wrap 512 that had been blocking the first through hole 701, and the first through hole 701 is opened. Then, at this time, the first compression chamber C1 and the back pressure chamber H5 start to communicate with each other through the first through hole 701 (see FIG. 8). The open state of the first through hole 701 continues in the periods Z1 and Z2 in FIG. 6. On the other hand, in the period Z1, the second through hole 702 is located away from the second compression chamber C2. Here, in the period Z1, the pressure in the back pressure chamber H5 (back pressure Pm) is higher than the pressure in the first compression chamber C1. Therefore, the fluid in the back pressure chamber H5 flows from the back pressure chamber H5 through the first through hole 701 into the first compression chamber C1, and the pressure in the first compression chamber C1 becomes higher than the pressure in the second compression chamber C2. Incidentally, during this period Z1, the volume of the first compression chamber C1 decreases and the internal pressure increases due to the orbital motion of the orbiting scroll 52, and the volume of the second compression chamber C2 decreases and the internal pressure increases.

[0057] In the period Z1, the pressure in the first compression chamber C1 is higher than the pressure in the second compression chamber C2. Therefore, it is possible to increase the rotation moment generated in the orbiting scroll 52. The direction of this rotation moment coincides with the direction of the orbital motion of the orbiting scroll 52.

[0058] 6, the second through hole 702 is released from the protruding edge of the fixed wrap 512 that had been blocking the second through hole 702, and the second through hole 702 opens. At this point, communication between the second compression chamber C2 and the back pressure chamber H5 begins via the second through hole 702 (see FIG. 9). The open state of the second through hole 702 continues during periods Z2 and Z3 in FIG.

[0059] At a crank angle of 360° in the middle of this period Z2, the gas refrigerant compressed by the volumetric reduction change of the first compression chamber C1 due to the revolution orbital motion of the orbiting scroll 52 and the gas refrigerant compressed by the volumetric reduction change of the second compression chamber C2 are mixed in the final compression chamber C3 as shown in Fig. 10. From the start of period Z2 to a crank angle of 360°, the magnitude relationship between the pressure in the first compression chamber C1 and the pressure in the second compression chamber C2 during period Z1 is maintained. It goes without saying that from the start of period Z2 to a crank angle of 360°, the volume of the first compression chamber C1 is reduced and the internal pressure increases due to the revolution orbital motion of the orbiting scroll 52, and the volume of the second compression chamber C2 is reduced and the internal pressure increases. Therefore, even during the period from the start of the period Z2 to a crank angle of 360°, the pressure in the first compression chamber C1 is higher than the pressure in the second compression chamber C2, so that it is possible to increase the rotational moment generated in the orbiting scroll 52 by that amount. The direction of this rotational moment coincides with the direction of the orbital revolution of the orbiting scroll 52.

[0060] During the period from the start of period Z2 to a crank angle of 360°, the pressure in the back pressure chamber H5 (back pressure Pm) is higher than the pressure in the second compression chamber C2. Therefore, the fluid in the back pressure chamber H5 flows from the back pressure chamber H5 through the second through hole 702 into the second compression chamber C2, and the pressure in the second compression chamber C2 increases accordingly. This also applies to the first compression chamber C1.

[0061] After the crank angle reaches 360° in the period Z2, the volume of the final compression chamber C3 decreases due to the orbital motion of the orbiting scroll 52, and the internal pressure increases.

[0062] 6, the first through hole 701 is blocked by the protruding edge of the fixed wrap 512. That is, at this point, communication between the final compression chamber C3 and the back pressure chamber H5 via the first through hole 701 is blocked (see FIG. 11). After this, the first through hole 701 is located away from the final compression chamber C3. Meanwhile, in period Z3, the second through hole 702 remains open, so communication between the final compression chamber C3 and the back pressure chamber H5 via the second through hole 702 continues.

[0063] 6, the second through hole 702 is blocked by the protruding edge of the fixed wrap 512. That is, at this point, communication between the final compression chamber C3 and the back pressure chamber H5 via the second through hole 702 is blocked (see FIG. 12). After this, the second through hole 702 is located away from the final compression chamber C3.

[0064] Here, during period Z2, when the pressure in the final compression chamber C3 is higher than the pressure in the backpressure chamber H5 (backpressure Pm), the fluid in the final compression chamber C3 can flow into the backpressure chamber H5 through both the first through-hole 701 and the second through-hole 702. Also, during period Z3, since the pressure in the final compression chamber C3 is higher than the pressure in the backpressure chamber H5 (backpressure Pm), the fluid in the final compression chamber C3 can flow into the backpressure chamber H5 through the second through-hole 702.

[0065] 6, in the period Z1, the first compression chamber C1 communicates with the back pressure chamber H5 through the first through hole 701, but the second compression chamber C2 and the back pressure chamber H5 do not communicate with each other. From the start of the period Z2 to the crank angle of 360°, the first compression chamber C1 communicates with the back pressure chamber H5 through the first through hole 701, and the second compression chamber C2 communicates with the back pressure chamber H5 through the second through hole 702. From the crank angle of 360° to the end of the period Z2, the final compression chamber C3 communicates with the back pressure chamber H5 through the first through hole 701 and the second through hole 702. In the period Z3, the final compression chamber C3 communicates with the back pressure chamber H5 through the second through hole 702, but the first compression chamber C1 and the back pressure chamber H5 do not communicate with each other.

[0066] When the volume of the final compression chamber C3 decreases due to the orbital motion of the orbiting scroll 52 and the pressure in the final compression chamber C3 reaches the discharge pressure, the check valve 90 opens and the gas refrigerant in the final compression chamber C3 is discharged through the discharge hole L2 to the discharge chamber H3.

[0067] In the scroll compressor 10 of this embodiment, as described above, the center of the orbiting base plate 521 and the center 52b of the base circle 52a of the orbiting wrap 522 are eccentric to each other. In this case, the distance α (not shown) between the center of the compression reaction force acting on the orbiting scroll 52 and the center of the orbiting base plate 521 varies during one revolution of the orbiting scroll 52. If the first compression chamber C1 and the second compression chamber C2 are at the same pressure, the center of the compression reaction force acting on the orbiting scroll 52 is at the midpoint between the center of the base circle of the fixed wrap 512 and the center 52b of the base circle 52a of the orbiting wrap 522. The higher the pressure in the first compression chamber C1 is than the pressure in the second compression chamber C2, the further away the center of the compression reaction force is from the center of the orbiting base plate 521 (i.e., the above-mentioned distance α becomes larger), and in the opposite case, the center of the compression reaction force approaches the center of the orbiting base plate 521 (i.e., the above-mentioned distance α becomes smaller). Here, the rotation moment is the moment around the center of the orbiting base plate 521, and is the product of the compression reaction force and the distance α. The compression reaction force varies during one revolution of the orbiting scroll 52, and is minimum, for example, near a crank angle of 360° as shown in FIG. 6. Therefore, in order to suppress a decrease in the rotation moment near a crank angle of 360° where the compression reaction force is minimum, it is preferable to make the pressure in the first compression chamber C1 higher than the pressure in the second compression chamber C2 near a crank angle of 360° in order to increase the distance α near the crank angle of 360°.

[0068] Therefore, in this embodiment, the following measure [1] is taken.

[0069] 6 to 9, before the second compression chamber C2 communicates with the back pressure chamber H5 through the second through hole 702, the first compression chamber C1 communicates with the back pressure chamber H5 through the first through hole 701. This makes it possible to increase the difference in pressure between the first compression chamber C1 and the second compression chamber C2 during the period Z1 and the period Z2 shown in FIG. 6 from the start of the period to a crank angle of 360°, thereby suppressing a decrease in the rotation moment.

[0070] By taking this measure, for example, a decrease in the rotational moment near a crank angle of 360° as shown in Fig. 6 is suppressed, so that pin 302 can be satisfactorily abutted against the inner circumferential surface of ring 301. Therefore, pin 302 can be prevented from colliding with ring 301, so that the generation of vibrations and noise in rotation-preventing mechanism 300 can be suppressed.

[0071] In addition, in this embodiment, the following additional measure [2] may be taken.

[0072] [2] The expansion angle to the winding end 51c of the fixed wrap 512 is set smaller than the expansion angle to the winding end 52c of the orbiting wrap 522. As a result, the winding end 52c of the orbiting wrap 522 abuts against the outer wall surface 512b of the fixed wrap 512 to seal the first compression chamber C1, and then the winding end 51c of the fixed wrap 512 abuts against the outer wall surface 522b of the orbiting wrap 522 to seal the second compression chamber C2. Therefore, the first compression chamber C1 always compresses the gas refrigerant before the second compression chamber C2, so the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2, and as a result, the rotation moment generated can be raised.

[0073] According to this embodiment, the scroll compressor 10 includes a fixed scroll 51 having a fixed base plate 511 having a discharge hole L2 at the center and a spiral-shaped fixed wrap 512 standing on the fixed base plate 511, a rotating base plate 521 and an orbiting scroll 52 having a spiral-shaped orbiting wrap 522 standing on the orbiting base plate 521 and meshing with the fixed wrap 512, a first compression chamber C1 formed by an inner wall surface 522a of the orbiting wrap 522 and an outer wall surface 512b of the fixed wrap 512, and a second compression chamber C2 formed by the inner wall surface 512a of the fixed wrap 512 and the outer wall surface 522b of the orbiting wrap 522. The rotary scroll 521 includes a second compression chamber C2, a rotation prevention mechanism 300 that prevents the rotary scroll 52 from rotating on its axis, and a back pressure chamber H5 provided on the back side of the rotary scroll 52. While the rotary scroll 52 is prevented from rotating on its axis by the rotation prevention mechanism 300, the rotary scroll 52 is caused to revolve around the axis of the fixed scroll 51 to change the volumes of the first compression chamber C1 and the second compression chamber C2, thereby compressing 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 and discharging them together from the discharge hole L2 to the discharge chamber H3. The rotary base plate 521 has a first through hole 701 that can communicate between the first compression chamber C1 and the back pressure chamber H5, and a second through hole 702 that can communicate between the second compression chamber C2 and the back pressure chamber H5. Before the second compression chamber C2 communicates with the back pressure chamber H5 through the second through hole 702, the first compression chamber C1 communicates with the back pressure chamber H5 through the first through hole 701. Therefore, the pressure in the first compression chamber C1 can be made higher than the pressure in the second compression chamber C2, so that the rotation moment generated in the orbiting scroll 52 can be increased accordingly, and thus the decrease in the rotation moment can be suppressed.

[0074] 6, 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, the first compression chamber C1 and the back pressure chamber H5 start communicating with each other through the first through hole 701 (i.e., after the period Z1 starts), and then the second compression chamber C2 and the back pressure chamber H5 start communicating with each other through the second through hole 702 (i.e., the period Z2 starts). This allows the pressure in the first compression chamber C1 to continue to be higher than the pressure in the second compression chamber C2.

[0075] Furthermore, according to this embodiment, rotation-preventing mechanism 300 includes ring 301 that is press-fitted into a circular hole formed in either the back surface of swivel base plate 521 or a housing wall (e.g., second partition portion 232) facing this back surface, and pin 302 that protrudes from the other and is loosely fitted inside ring 301. The generation of vibrations and noise in rotation-preventing mechanism 300 configured in this way can be suppressed.

[0076] According to this embodiment, the fixed wrap 512 can be formed by an involute curve based on the base circle of the fixed wrap 512. The orbiting wrap 522 can be formed by an involute curve based on the base circle 52a of the orbiting wrap 522. The expansion angle from the reference point on the base circle of the fixed wrap 512 to the winding end 51c of the fixed wrap 512 is the same as the expansion angle from the reference point on the base circle 52a of the orbiting wrap 522 to the winding end 52c of the orbiting wrap 522. Therefore, as shown in FIG. 7, the winding end 52c of the orbiting wrap 522 and the outer wall surface 512b of the fixed wrap 512 come into contact with each other to seal the first compression chamber C1, and at the same time, the winding end 51c of the fixed wrap 512 and the outer wall surface 522b of the orbiting wrap 522 come into contact with each other to seal the second compression chamber C2.

[0077] In this embodiment, the extension angle from the reference point on the base circle of the fixed wrap 512 to the winding end 51c of the fixed wrap 512 may be smaller than the extension angle from the reference point on the base circle 52a of the orbiting wrap 522 to the winding end 52c of the orbiting wrap 522. In this case, the winding end 52c of the orbiting wrap 522 abuts against the outer wall surface 512b of the fixed wrap 512 to seal the first compression chamber C1, and then the winding end 51c of the fixed wrap 512 abuts against the outer wall surface 522b of the orbiting wrap 522 to seal the second compression chamber C2. Therefore, the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2, so that the rotation moment can always be generated in the orbiting scroll 52, and thus the decrease in the rotation moment can be suppressed.

[0078] According to this embodiment, the center of the fixed base plate 511 and the center of the base circle of the fixed wrap 512 are eccentric to each other. Also, the center of the orbiting base plate 521 and the center 52b of the base circle 52a of the orbiting wrap 522 are eccentric to each other. In the scroll compressor 10 having such a configuration, the generation of vibrations and noise in the rotation-preventing mechanism 300 can be suppressed.

[0079] The drive source for driving the scroll compressor 10 of the present embodiment is not limited to the electric motor 40, and may be, for example, a vehicle engine or the like.

[0080] The scroll unit 50 (the fixed scroll 51 and the orbiting scroll 52) can also be applied to a scroll type expander. This scroll type expander can be incorporated in a refrigerant circuit of a Rankine cycle device for a vehicle, for example, and configured to expand a refrigerant introduced from the refrigerant circuit to generate power (recover power from the refrigerant).

[0081] Although the embodiment of the present invention has been described above, the present invention is not limited to the above-described embodiment, and it is needless to say that modifications and changes can be made based on the technical concept of the present invention. [Explanation of symbols]

[0082] 10...Scroll type compressor, 20...Housing, 21...Front housing, 23...Center housing, 24...Rear housing, 50...Scroll unit, 51...Fixed scroll, 51c...End of winding, 52...Orbiting scroll, 52a...Base circle, 52b...Center, 52c...End of winding, 100...Oil separator, 232...Second partition wall (housing wall), 300...Rotation prevention mechanism, 301...Ring, 302...Pin, 303...Rotation prevention part, 51 1...fixed base plate, 512...fixed wrap, 512a...inner wall surface, 512b...outer wall surface, 521...swivel base plate, 522...swivel wrap, 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...communication hole, L4...lubricating oil passage, OL1...orifice

Claims

1. a fixed scroll having a fixed base plate having a discharge hole at a central portion thereof and a spiral-shaped fixed wrap provided upright on the fixed base plate; a rotating base plate; and an orbiting scroll having a spiral-shaped orbiting wrap that is provided upright on the orbiting base plate and engages with the fixed wrap; a first compression chamber defined by an inner wall surface of the orbiting wrap and an outer wall surface of the fixed wrap; a second compression chamber formed by an inner wall surface of the fixed wrap and an outer wall surface of the orbiting wrap; a rotation prevention mechanism that prevents the orbiting scroll from rotating on its axis; A back pressure chamber provided on the back side of the orbiting scroll; a rotation-preventing mechanism for preventing rotation of the orbiting scroll, and a revolving motion of the orbiting scroll about an axis of the fixed scroll to change a volume of the first compression chamber and a volume of the second compression chamber, respectively, thereby compressing a fluid in the first compression chamber and a fluid in the second compression chamber, and discharging the fluid together from the discharge hole to a discharge chamber, the rotating base plate has a first through hole capable of communicating between the first compression chamber and the back pressure chamber, and a second through hole capable of communicating between the second compression chamber and the back pressure chamber, a first compression chamber communicating with the back pressure chamber through the first through hole before the second compression chamber communicating with the back pressure chamber through the second through hole;

2. 2. The scroll compressor according to claim 1, wherein, at a time when the pressure in the back pressure chamber is higher than the pressure in the first compression chamber and is also higher than the pressure in the second compression chamber, communication between the first compression chamber and the back pressure chamber via the first through hole is started, and then communication between the second compression chamber and the back pressure chamber via the second through hole is started.

3. 3. The scroll compressor according to claim 1, wherein the rotation-preventing mechanism includes a ring press-fitted into a circular hole formed in either the back surface of the rotating base plate or a housing wall facing the back surface, and a pin protruding from the other of the ring and loosely fitted inside the ring.

4. 4. The scroll compressor according to claim 1, wherein an expansion angle from a reference point on a base circle of the fixed wrap to a winding end of the fixed wrap is equal to an expansion angle from a reference point on a base circle of the orbiting wrap to a winding end of the orbiting wrap.

5. The scroll compressor according to any one of claims 1 to 4, wherein the first compression chamber is sealed by abutting the winding end end of the orbiting wrap against an outer wall surface of the fixed wrap, and the second compression chamber is sealed by abutting the winding end end of the fixed wrap against the outer wall surface of the orbiting wrap.

6. 4. The scroll compressor according to claim 1, wherein an expansion angle from a reference point on a base circle of the fixed wrap to a winding end of the fixed wrap is smaller than an expansion angle from a reference point on a base circle of the orbiting wrap to a winding end of the orbiting wrap.

7. The scroll compressor according to any one of claims 1 to 3 and claim 6, wherein the first compression chamber is sealed by abutting the winding end end of the swirl wrap against the outer wall surface of the fixed wrap, and then the second compression chamber is sealed by abutting the winding end end of the fixed wrap against the outer wall surface of the swirl wrap.

8. a center of the fixed substrate and a center of a base circle of the fixed wrap are eccentric to each other, 8. The scroll compressor according to claim 1, wherein a center of the orbiting base plate and a center of a base circle of the orbiting wrap are eccentric to each other.

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