Scroll Compressor

Abstract

[Problem] To strike a balance between reducing the weight of an oscillating scroll and balancing weight. [Solution] A scroll compressor (10) comprises: a fixed scroll (70) and an oscillating scroll (80) housed within a housing (20); and a pin-and-ring rotation-blocking mechanism (90) for blocking the rotation of the oscillating scroll (80). The oscillating scroll (80) comprises an oscillating spiral element (82) that stands upright from a first plate face (81a) of a discoid oscillating plate (81) toward the fixed spiral element (73). The rotation-preventing mechanism (90) comprises: a plurality of circular recessions (91) provided in a second plate face (81b) of the oscillating plate (81); and a plurality of pins (93) that extend from the housing (20) into the plurality of recessions (91) and engage therewith. The moving head (81) comprises, in an outer circumferential surface (81c) thereof, at least one groove (111, 112) that does not communicate with the first plate face (81a) and the second plate face (81b).

Description

[Technical field]

[0001] The present invention relates to an improved technique for scroll compressors. [Background technology]

[0002] A scroll compressor is provided with a rotation prevention mechanism for preventing the rotation of the orbiting scroll (also called the orbiting scroll). Conventionally, an Oldham-type rotation prevention mechanism using an Oldham ring has been widely used as this rotation prevention mechanism. The Oldham-type rotation prevention mechanism is similar to the principle of the Oldham coupling, and an Oldham ring is interposed between the plate surface of the orbiting end plate of the orbiting scroll and the housing wall surface facing this plate surface. The Oldham ring is an annular member centered on a drive shaft that drives the orbiting scroll, and is provided so as to be able to reciprocate only in the direction of a first straight line perpendicular to the drive shaft. On the other hand, the orbiting scroll is provided so as to be able to reciprocate only in the direction of a second straight line perpendicular to the drive shaft relative to the Oldham ring. The direction of the first straight line is shifted by 90° from the direction of the second straight line. Therefore, the orbiting scroll can revolve around the axis of the drive shaft while being restricted from rotating.

[0003] Since the orbiting scroll and the Oldham ring have a certain mass, sufficient consideration must be given to the radial vibration caused by the revolution of the orbiting scroll. When the above-mentioned Oldham-type rotation prevention mechanism is adopted, the radial vibration force (centrifugal force) caused by the revolution of the orbiting scroll can be balanced by a counterweight provided on the drive shaft, but the vibration force caused by the reciprocating motion of the Oldham ring cannot be balanced by the counterweight. For this reason, there is a limit to the suppression of the radial vibration caused by the revolution of the orbiting scroll.

[0004] Therefore, in recent years, pin-and-ring type anti-rotation mechanisms have come to be adopted instead of Oldham type anti-rotation mechanisms. A scroll compressor equipped with this pin-and-ring type anti-rotation mechanism is known from Patent Document 1, for example.

[0005] The pin-and-ring type rotation prevention mechanism known in Patent Document 1 is composed of a plurality of pins provided on a fixed member and a plurality of circular recesses that individually engage with the plurality of pins. The plurality of recesses are arranged and formed in the circumferential direction with respect to the plate surface of the oscillating end plate of the oscillating scroll. The plurality of pins extend from a housing wall surface facing the plate surface of the oscillating end plate into the plurality of recesses. The oscillating scroll only revolves so that the inner peripheral surface of the recesses is always in contact with the pins, and does not use a member that reciprocates in the radial direction as in the Oldham type rotation prevention mechanism. This is advantageous in suppressing radial vibration of the oscillating scroll. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] International Publication No. 2018 / 003032 Summary of the Invention [Problem to be solved by the invention]

[0007] As mentioned above, even if a pin-and-ring type rotation prevention mechanism is adopted, the radial excitation force caused by the revolution of the orbiting scroll cannot be balanced unless a counterweight is provided on the drive shaft. Therefore, in order to reduce the size and weight of the counterweight and thus the weight of the entire compressor, it is preferable that the orbiting scroll is as light as possible.

[0008] An object of the present invention is to provide a technique capable of reducing the weight of an orbiting scroll in a scroll compressor employing a pin-and-ring type anti-rotation mechanism. [Means for solving the problem]

[0009] In the following description, reference numerals in the accompanying drawings are placed in parentheses to facilitate understanding of the present invention, but the present invention is not limited to the illustrated form.

[0010] According to the present invention, A housing (20); a compression mechanism (60) housed in the housing (20) and including a fixed scroll (70) and an orbiting scroll (80); a drive shaft (50) that is rotatably supported in the housing (20) and drives the orbiting scroll (80); a rotation prevention mechanism (90) that prevents the orbiting scroll (80) from rotating about its axis, The fixed scroll (70) includes a fixed end plate (71) supported in a manner not to rotate relative to the housing (20) and a fixed scroll body (73) having a spiral shape extending upright from one plate surface (71a) of the fixed end plate (71), the oscillating scroll (80) includes a disk-shaped oscillating end plate (81) positioned opposite the fixed scroll (73), and a spiral-shaped oscillating scroll (82) standing from a first plate surface (81a) of the oscillating end plate (81) toward the fixed scroll (73) and combining with the fixed scroll (73) to form a compression chamber (83); The oscillating end plate (81) is rotatably supported by an eccentric shaft (51) provided at one end of the drive shaft (50), The rotation prevention mechanism (90) is a plurality of circular recesses (91) provided on a second plate surface (81b) of the oscillating mirror plate (81) opposite to the first plate surface (81a) and arranged in a circumferential direction of the second plate surface (81b); a plurality of pins (93) extending from a wall portion (31a) of the housing (20) facing the second plate surface (81b) of the oscillating end plate (81) into the plurality of recesses (91) and individually engaging with inner circumferential surfaces (91a) of the plurality of recesses (91) directly or via ring members (92), The scroll compressor is characterized in that the oscillating mirror plate (81) has at least one groove portion (111, 112; 112A; 112B) on an outer circumferential surface (81c) that does not communicate with the first plate surface (81a) and the second plate surface (81b).

[0011] Preferably, the grooves (112; 112A; 112B) are provided between adjacent ones of the recesses (91).

[0012] Preferably, the grooves (112; 112A; 112B) are deepest at positions farthest from the adjacent recesses (91). Effect of the Invention

[0013] In the present invention, the weight of the orbiting scroll can be reduced by providing at least one groove portion on the outer peripheral surface of the orbiting end plate that does not communicate with the first plate surface and the second plate surface. Since the groove portion does not communicate with the first plate surface and the second plate surface, it does not affect the first plate surface and the second plate surface. Therefore, there is no interference with the orbiting scroll provided on the first plate surface, and the second plate surface can be used as a sliding surface up to the vicinity of the outermost periphery. [Brief description of the drawings]

[0014] [Figure 1] 1 is a cross-sectional view of a scroll compressor according to a first embodiment. [Diagram 2] FIG. 2 is a perspective view of the orbiting scroll shown in FIG. [Diagram 3] 3 is a cross-sectional view taken along the axis of the orbiting scroll shown in FIG. 2. [Figure 4] 4 is a view of the orbiting scroll shown in FIG. 3 as viewed from the first plate surface side of the orbiting end plate. [Diagram 5] 4 is a view of the orbiting scroll shown in FIG. 3 as viewed from the second plate surface side of the orbiting end plate. [Figure 6] 6 is a cross-sectional view taken along line 6-6 in FIG. [Figure 7] 7 is a cross-sectional view (corresponding to the cross-sectional position of FIG. 6) of the orbiting scroll of the scroll compressor according to the second embodiment, as viewed from the second plate surface side of the orbiting end plate. [Figure 8] 7 is a cross-sectional view (corresponding to the cross-sectional position of FIG. 6) of the orbiting scroll of the scroll compressor according to the third embodiment, as viewed from the second plate surface side of the orbiting end plate. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the accompanying drawings. Note that the embodiments shown in the accompanying drawings are merely examples of the present invention, and the present invention is not limited to these embodiments. <Example 1>

[0016] A scroll compressor 10 according to a first embodiment will be described with reference to Fig. 1 to Fig. 6. As shown in Fig. 1, the scroll compressor 10 is suitable for use in a refrigeration cycle in which a refrigerant is used as a working fluid, for example, in a refrigeration cycle of an automotive air conditioner. However, the use of the scroll compressor 10 is not limited.

[0017] The scroll compressor 10 is a so-called horizontally-mounted electric compressor having a horizontal housing 20, an electric motor 40 housed in the housing 20, a drive shaft 50 (including the output shaft of the electric motor 40) driven by the electric motor 40, and a compression mechanism 60 driven by the electric motor 40 via the drive shaft 50.

[0018] The housing 20 has a horizontal cylindrical first housing 21 and a second housing 22 that closes one opening of the first housing 21. The inside of the first housing 21 is divided into two in the longitudinal direction by an integral partition wall 23. One of the first housing 21 portions relative to the partition wall 23 is called a first cylindrical portion 24, and the other portion is called a second cylindrical portion 25. The open end of the first cylindrical portion 24 is closed by a lid 26. An inverter device (not shown) that supplies driving power to the electric motor 40 is accommodated inside the first cylindrical portion 24. The second housing 22 is fastened to the first housing 21 by fastening members (not shown) such as bolts so as to close the open end of the second cylindrical portion 25.

[0019] Furthermore, the housing 20 has a suction port 27 that draws refrigerant into the housing 20 from the outside, and a discharge port 28 that discharges the refrigerant compressed by the compression mechanism 60 from the housing 20. The suction port 27 is provided in the second cylindrical portion 25. The discharge port 28 is provided in the second housing 22.

[0020] The electric motor 40, the drive shaft 50, and the compression mechanism 60 are housed in the second cylindrical portion 25 of the first housing 21. The compression mechanism 60 is located on the opening side of the second cylindrical portion 25. Inside the second cylindrical portion 25, a space 29 between the partition wall 23 and the compression mechanism 60 is hereinafter referred to as the "low pressure chamber 29." The electric motor 40 is located in the low pressure chamber 29. This low pressure chamber 29 is in communication with the suction port 27.

[0021] A support block 31 is provided inside the second cylindrical portion 25 between the electric motor 40 and the compression mechanism 60. Both the relative rotation and the relative axial movement of this support block 31 with respect to the second cylindrical portion 25 are restricted. Therefore, the support block 31 can be considered to constitute a part of the housing 20. Hereinafter, the support block 31 will be described as "a part of the housing 20" as appropriate.

[0022] The drive shaft 50 is located in the low pressure chamber 29, extends horizontally in the longitudinal direction of the second cylindrical portion 25, and penetrates the support block 31 toward the compression mechanism 60. The drive shaft 50 is rotatably supported by a first bearing 32 provided in the partition wall 23 and a second bearing 33 provided in the support block 31. As a result, the drive shaft 50 extends horizontally in the longitudinal direction of the housing 20, and is rotatably supported by the housing 20. Each of the bearings 32, 33 is preferably constituted by a rolling bearing.

[0023] Furthermore, the drive shaft 50 has an eccentric shaft 51 on one end surface penetrating the support block 31. This eccentric shaft 51 (eccentric pin 51) extends from one end surface of the drive shaft 50 toward the compression mechanism 60 and is parallel to the drive shaft 50. A center line CL2 of the eccentric shaft 51 is offset from a center line CL1 of the drive shaft 50, and an annular bush 52 is rotatably fitted to this eccentric shaft 51. A counterweight 53 (balance weight 53) is integrally provided on a part of the bush 52 and protrudes radially from the bush 52. Furthermore, a bearing 54 (third bearing 54) is fitted to the outer circumferential surface of the bush 52. The third bearing 54 is preferably constituted by a rolling bearing. The inner surface of the bush 52 that fits onto the eccentric shaft 51 and the outer surface of the bush 52 that fits onto the bearing 54 are not coaxial, thereby forming a well-known automatic centering mechanism that allows the center line CL3 of the oscillating scroll 80 to be positioned inside the rotational locus formed by the center line CL2 of the eccentric shaft 51.

[0024] The electric motor 40 has a rotor 41 fixed to a drive shaft 50 and a stator 42 surrounding the rotor 41. The stator 42 is fixed to the inner circumferential surface of the second cylindrical portion 25. The drive shaft 50 functions as an output shaft of the electric motor 40.

[0025] The compression mechanism 60 includes a fixed scroll 70 and an orbiting scroll 80 .

[0026] The fixed scroll 70 has a disk-shaped fixed end plate 71, a cylindrical outer peripheral wall 72, and a spiral-shaped fixed scroll body 73. The fixed end plate 71 (also called the fixed plate 71) is perpendicular to the center line CL2 of the eccentric shaft 51 and is supported by the housing 20 so as not to rotate relative to the housing 20. The outer peripheral wall 72 is a cylinder erected over the entire circumference from the outer edge of one plate surface 71a (the surface 71a facing the electric motor 40) of the fixed end plate 71. The fixed scroll body 73 is located inside the outer peripheral wall 72 and erected from one plate surface 71a of the fixed end plate 71. The fixed scroll body 73 is formed in, for example, an involute curved shape. The outer peripheral wall 72 of the fixed scroll 70 has a refrigerant suction port 74 formed therein for drawing the refrigerant from the radially outer side to the inner side.

[0027] The orbiting scroll 80 is combined with the fixed scroll 70 and revolves around the fixed scroll 70 .

[0028] 2 to 4, the orbiting scroll 80 has a disk-shaped orbiting end plate 81 positioned opposite the fixed scroll 73, and a scroll-shaped orbiting scroll 82.

[0029] The oscillating end plate 81 is perpendicular to the center line CL3 of the oscillating scroll 80 and is located inside the outer peripheral wall 72 of the fixed scroll body 73. Of the oscillating end plate 81, the plate surface 81a facing one plate surface 71a of the fixed end plate 71 is referred to as the "first plate surface 81a," and the surface 81b opposite to the first plate surface 81a is referred to as the "second plate surface 81b."

[0030] The oscillating scroll 82 stands upright from the first plate surface 81a of the oscillating end plate 81 toward the fixed scroll 73, and is combined with the fixed scroll 73 to form a plurality of compression chambers 83. The oscillating scroll 82 is configured, for example, in an involute curved shape (see FIG. 4).

[0031] On the other hand, a circular supported recess 84 is formed on the second plate surface 81b of the oscillating end plate 81 at the center CL3 of the oscillating end plate 81. The outer peripheral surface of the third bearing 54 (see FIG. 1) is fitted into this supported recess 84. The oscillating end plate 81 is rotatably supported via the third bearing 54 by an eccentric shaft 51 provided on the drive shaft 50. As a result, the oscillating scroll 80 is driven by the drive shaft 50. When the drive shaft 50 rotates, the oscillating scroll 80 can revolve (rotate eccentrically) around the axis CL2 of the drive shaft 50.

[0032] 1, scroll compressor 10 has a rotation prevention mechanism 90 that prevents rotation of oscillating scroll 80. This rotation prevention mechanism 90 is a pin-and-ring type rotation prevention mechanism consisting of a plurality of recesses 91 provided in oscillating end plate 81 and a plurality of anti-rotation pins 93 provided in housing 20. Hereinafter, recesses 91 will be referred to as "pin engagement recesses 91," and pins 93 will be referred to as "anti-rotation pins 93."

[0033] 2, 3 and 5, the multiple (e.g., six) pin engagement recesses 91 are arranged at equal pitches along the circumferential direction on the second plate surface 81b of the oscillating mirror plate 81. In other words, the multiple pin engagement recesses 91 are circular depressions positioned at equal pitches on concentric circles with the center CL3 of the oscillating mirror plate 81 as the reference.

[0034] The multiple anti-rotation pins 93 are configured as round bars parallel to the drive shaft 50, and extend from a wall portion 31a facing the second plate surface 81b of the oscillating end plate 81 in the housing 20 (e.g., support block 31) into the multiple pin engagement recesses 91. These multiple anti-rotation pins 93 are individually engaged with the inner circumferential surfaces 91a of the multiple pin engagement recesses 91 directly or via a ring member 92 (member 92 shown by imaginary lines in FIG. 3). Therefore, the oscillating scroll 80 can move relative to the housing 20 only within the range of the inner circumferential surfaces 91a of the multiple circular pin engagement recesses 91.

[0035] As the drive shaft 50 rotates, the orbiting scroll 80 attempts to rotate on its axis, but the rotation is restricted by the pin engagement recess 91 and the anti-rotation pin 93. In this manner, the rotation prevention mechanism 90 can prevent the orbiting scroll 80 from rotating on its axis while allowing the orbiting scroll 80 to revolve.

[0036] In this way, in the pin-and-ring type rotation prevention mechanism 90, the rotation of the orbiting scroll 80 can be prevented by engaging the multiple anti-rotation pins 93 with the inner peripheral surfaces 91a of the multiple pin engagement recesses 91, and there is no need to consider vibrations resulting from the reciprocating member since there is no member (Oldham ring) that reciprocates in the radial direction as in the Oldham type rotation prevention mechanism. Meanwhile, since the orbiting scroll 80 has a predetermined mass, a radial excitation force is generated as the orbiting scroll 80 revolves, but this radial excitation force as the orbiting scroll 80 revolves is balanced by the counterweight 53 provided on the eccentric shaft 51.

[0037] Further, as shown in Figs. 2 and 5, the oscillating end plate 81 of the oscillating scroll 80 has an annular sliding contact portion 101 and a plurality of recesses 102 for adjusting the center of gravity on a second plate surface 81b.

[0038] The annular sliding portion 101 is a flat annular surface of a constant width that protrudes slightly from the outer circumferential edge of the second plate surface 81b. This annular sliding portion 101 can be in sliding contact with the wall surface of the wall portion 31a of the support block 31 (i.e., the wall surface of the housing 20) when the orbiting scroll 80 revolves.

[0039] The plurality of center-of-gravity adjusting recesses 102 are recessed from the second plate surface 81b so as to adjust the center-of-gravity position of the swing scroll 80, and are located radially inward from the annular sliding contact portion 101. These center-of-gravity adjusting recesses 102 are arranged in a range from the winding end 82a (base point Sp) of the swing scroll 82 shown in FIG. 4 to a winding angle θ (about 180°) before that, and in the middle between the pin engaging recesses 91 and the adjacent pin engaging recesses 91. By providing the plurality of center-of-gravity adjusting recesses 102, the mass of the swing scroll 80 in the region θ corresponding to the winding end side of the swing scroll 82 can be made to approach the mass of the swing scroll 80 in the other region. As a result, the center of gravity of the swing scroll 80 can be made to coincide with the center CL3 of the swing mirror plate 81.

[0040] Here, as shown in Fig. 5, when the oscillating scroll 80 is viewed from the second plate surface 81b side of the oscillating mirror plate 81, a number of straight lines L1 and a number of straight lines L2 extending radially from the center CL3 of the oscillating mirror plate 81 are considered. Hereinafter, the multiple straight lines L1 and the multiple straight lines L2 will be described by distinguishing them into multiple first straight lines L1 and multiple second straight lines L2. The multiple first straight lines L1 are straight lines that pass through the centers of the pin engagement recesses 91. The multiple second straight lines L2 are straight lines that pass through the middle between adjacent pin engagement recesses 91, 91. All of the straight lines L1 and the straight lines L2 are arranged at equal angles.

[0041] The inner peripheral surface 91a of the pin engagement recess 91 and the inner peripheral surface of the annular sliding contact portion 101 coincide with each other at the position of the first straight line L1. The plurality of center-of-gravity adjustment recesses 102 are located on the second straight line L2. The surface 102b of the inner peripheral surface 102a of each center-of-gravity adjustment recess 102 that is closer to the annular sliding contact portion 101 is linear and perpendicular to the second straight line L2, and is close to the annular sliding contact portion 101.

[0042] 6, on the first straight line L1, the thickness (first thickness) from the outer circumferential surface 81c of the oscillating mirror plate 81 to the inner circumferential surface 91a of the pin engagement recess 91 is Th1. On the second straight line L2, the thickness (second thickness) from the surface 102b of the inner circumferential surface 102a of the center-of-gravity adjusting recess 102, which is closer to the annular sliding contact portion 101, to the outer circumferential surface 81c of the oscillating mirror plate 81 is Th2, which is thicker than the first thickness Th1 (Th2>Th1).

[0043] 2, 3 and 6, the oscillating mirror plate 81 has at least one groove 111 and / or groove 112, for example, the first groove 111 and / or the second groove 112, on the outer peripheral surface 81c, which does not communicate with the first plate surface 81a and the second plate surface 81b. The first groove 111 and the second groove 112 have a U-shaped cross section (see FIG. 3) that is open on the outer peripheral surface 81c side of the oscillating mirror plate 81. The first groove 111 consists of a groove bottom surface 111a on the center CL3 side of the oscillating mirror plate 81 and a pair of flat groove side surfaces 111b and groove side surfaces 111b extending from the groove bottom surface 111a toward the outer peripheral surface 81c. Similarly, the second groove portion 112 is composed of a groove bottom surface 112a on the center CL3 side of the oscillating mirror plate 81, and a pair of flat groove side surfaces 112b extending from the groove bottom surface 112a toward the outer circumferential surface 81c.

[0044] The first grooves 111 are located in the outer peripheral surface 81c of the oscillating mirror plate 81 at positions facing the pin engagement recesses 91, i.e., on the first straight lines L1. Each of the first grooves 111 is an arc-shaped groove that runs along the outer peripheral surface 81c. Therefore, the groove bottom surface 111a is an arc-shaped surface that runs along the outer peripheral surface 81c.

[0045] 6, when the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each first groove portion 111 is recessed close to the pin engagement recess 91. As described above, on the first straight line L1, the first thickness Th1 from the outer peripheral surface 81c of the oscillating mirror plate 81 to the inner peripheral surface 91a of the pin engagement recess 91 is relatively small. Therefore, on the first straight line L1, the depth De1 (first groove depth De1) from the outer peripheral surface 81c of the oscillating mirror plate 81 to the groove bottom surface 111a of each first groove portion 111 is relatively small.

[0046] On the other hand, the second grooves 112 are provided between the pin engagement recesses 91 adjacent to each other on the outer peripheral surface 81c of the oscillating mirror plate 81. Preferably, the second grooves 112 are arranged in the middle between the pin engagement recesses 91 adjacent to each other. More specifically, when the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each of the second grooves 112 is located on the second straight line L2 and is a linear groove perpendicular to the second straight line L2. Therefore, the groove bottom surface 112b is a linear surface perpendicular to the second straight line L2.

[0047] When the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each second groove portion 112 is recessed close to the center of gravity adjustment recess 102. Therefore, each second groove portion 112 is deepest at a position P1 far from the pin engagement recess 91 adjacent to the pin engagement recess 91, that is, at a position P1 intersecting the second straight line L2. In other words, each second groove portion 112 has a depth De2 (second groove depth De2) from the outer peripheral surface 81c of the oscillating mirror plate 81 to the groove bottom surface 112a on the second straight line L2 that is the largest. This second groove depth De2 is larger than the first groove depth De1 (De2>De1).

[0048] The operation of the scroll compressor 10 is generally as follows. As shown in FIG. 1, the driving shaft 50 is driven by the electric motor 40, so that the swing scroll 80 revolves. As a result, the refrigerant sucked from the suction port 27 and the refrigerant in the low pressure chamber 29 enter the compression chamber 83 through the refrigerant suction port 74 of the fixed scroll 70. As the swing scroll 80 revolves, the compression chamber 83 moves toward the center while gradually reducing its internal volume, so that the refrigerant in the compression chamber 83 is compressed. As the pressure in the compression chamber 83 increases, the check valve 121 opens, and the compressed refrigerant flows into the discharge chamber 122 in the second housing 22 and enters the adjacent gas-liquid separation chamber 123. The gaseous refrigerant from which the oil has been separated by the gas-liquid separation chamber 124 is discharged to the outside from the discharge port 28.

[0049] The above-described description of the scroll compressor 10 according to the first embodiment can be summarized as follows. As shown in Figs. 2, 3 and 6, the weight of the orbiting scroll 80 can be reduced by providing at least one groove 111 and / or groove 112 on the outer peripheral surface 81c of the orbiting end plate 81. The weight and size of the counterweight 53 for balancing the excitation force caused by the revolution of the orbiting scroll 80 can also be reduced. Furthermore, the grooves 111 and 112 do not communicate with the first plate surface 81a and the second plate surface 81b, and therefore do not affect the first plate surface 81a or the second plate surface 81b. Therefore, the grooves 111 and 112 do not interfere with the orbiting scroll 82 erected on the first plate surface 81a. Moreover, the second plate surface 81b can be used as a sliding surface (annular sliding portion 101) against the wall surface of the housing 20 up to the vicinity of the outermost periphery.

[0050] 6, the groove portion 112 (second groove portion 112) is provided between adjacent pin engagement recesses 91, 91 (pin engagement recess 91 and adjacent pin engagement recess 91). By disposing the groove portion 112 between adjacent pin engagement recesses 91, 91, it is possible to form a deeper groove having a second groove depth De2 while avoiding interference with each pin engagement recess 91. As a result, the weight of the orbiting scroll 80 can be further reduced.

[0051] Moreover, each groove portion 112 can be disposed at an optimal position in the orbiting scroll 80. Also, each groove portion 112 can be freely disposed only in a necessary portion at a position where it does not interfere with the pin engagement recess 91. Therefore, it is easy to balance the weight of the orbiting scroll 80 itself by using the groove portion 112. The orbiting scroll 80 does not need to be made larger in order to balance the weight. Therefore, the degree of freedom in designing each groove portion 112 can be increased. In this way, it is possible to achieve both a reduction in the weight of the orbiting scroll 80 and a balance in the weight of the orbiting scroll 80 itself.

[0052] Furthermore, the groove 112 (second groove 112) is deepest at a position P1 farthest from the adjacent pin engagement recesses 91 (pin engagement recesses 91 adjacent to each other). The farther the position on the outer peripheral surface 81c of the oscillating end plate 81 is from the adjacent pin engagement recesses 91, 91, the less the groove bottom surface 112a of each groove 112 interferes with each pin engagement recess 91, 91. In light of this, the depth De2 (second groove depth De2) of each groove 112 is made largest at a position P1 farthest from the position of the recess 91. Therefore, the weight of the oscillating scroll 80 can be further reduced.

[0053] Furthermore, when cutting the orbiting scroll 80, the orbiting scroll 80 is fixed (held) to a fixed base of a processing machine by a fixed claw such as a chuck or a clamper (not shown). By hooking the fixed claw to any of the multiple grooves 111 or 112, the orbiting scroll 80 can be easily and reliably fixed to a fixed base such as a bed or a table. Moreover, the groove 111 or 112 is located in a position (on the second straight line L2) that avoids the recess 91 in the outer circumferential surface 81c of the orbiting end plate 81. By effectively utilizing the groove side surface 111b or groove side portion 112b of the groove 111 or 112 to hook the fixed claw, the orbiting scroll 80 can be fixed in the orbiting axis direction. Therefore, the fixed claw can be hooked without causing distortion in the orbiting scroll 80, which has a relatively low rigidity.

[0054] Second Embodiment Next, a scroll compressor 10A according to a second embodiment will be described with reference to FIG. <Example 2>

[0055] FIG. 7 shows a cross-sectional configuration of an orbiting scroll 80A of a scroll compressor 10A according to the second embodiment, as viewed from the second plate surface 81b side of the orbiting end plate 81, and corresponds to the cross-sectional position of FIG.

[0056] The scroll compressor 10A of the second embodiment is characterized in that the second groove portion 112 of the first embodiment shown in Figs. 1 to 6 is changed to a second groove portion 112A shown in Fig. 7. The other basic configurations are common to the scroll compressor 10 of the first embodiment. The same reference numerals are used for the parts common to the scroll compressor 10 of the first embodiment, and detailed descriptions thereof will be omitted.

[0057] The second groove portion 112A of the second embodiment is configured to open the outer peripheral surface 81c side of the oscillating mirror plate 81 as in the first embodiment, and is composed of a groove bottom surface 112a on the center CL3 side of the oscillating mirror plate 81 and a pair of flat groove side surfaces 112b extending from the groove bottom surface 112a toward the outer peripheral surface 81c. More specifically, as shown in Fig. 7, when the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each second groove portion 112A is recessed in an arc shape from the outer peripheral surface 81c of the oscillating mirror plate 81. Therefore, the groove bottom surface 112b is also an arc-shaped surface recessed in an arc shape from the outer peripheral surface 81c of the oscillating mirror plate 81.

[0058] When the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each second groove portion 112A is recessed close to the center-of-gravity adjustment recess 102. Therefore, each second groove portion 112A is deepest at a position P1 far from the pin engagement recess 91 adjacent to the multiple pin engagement recesses 91, that is, at a position P1 intersecting the second straight line L2. In other words, each second groove portion 112A has a depth De2A (second groove depth De2A) from the outer peripheral surface 81c of the oscillating mirror plate 81 to the groove bottom surface 112a on the second straight line L2 that is the largest.

[0059] The scroll compressor 10A according to the second embodiment can achieve the same effects as those of the first embodiment.

[0060] In the second embodiment, the surface 102b of the inner peripheral surface 102a of each of the center-of-gravity adjusting recesses 102, which is closer to the annular sliding portion 101, may be an arc-shaped surface along the groove bottom surface 112a of the second groove portion 112A. In that case, the second groove depth De2A can be set to be larger than the second groove depth De2 of the first embodiment shown in FIG.

[0061] Next, a scroll compressor 10B according to a third embodiment will be described with reference to FIG. <Example 3>

[0062] Fig. 8 shows a cross-sectional configuration of an oscillating scroll 80B of a scroll compressor 10B according to the third embodiment, as viewed from the second plate surface 81b side of the oscillating end plate 81, and corresponds to the cross-sectional position of Fig. 6. The scroll compressor 10B of the third embodiment is characterized in that the second groove portion 112 of the first embodiment shown in Figs. 1 to 6 is changed to a second groove portion 112B shown in Fig. 8. The other basic configuration is common to the scroll compressor 10 according to the first embodiment. The same reference numerals are used for the parts common to the scroll compressor 10 according to the first embodiment, and detailed description thereof will be omitted.

[0063] The second groove 112B of the third embodiment is configured to be open on the outer peripheral surface 81c side of the oscillating mirror plate 81 as in the first embodiment, and is composed of a groove bottom surface 112a on the center CL3 side of the oscillating mirror plate 81 and a pair of flat groove side surfaces 112b extending from the groove bottom surface 112a toward the outer peripheral surface 81c. More specifically, as shown in Fig. 8, when the oscillating mirror plate 81 is viewed from the center CL1 direction (the second plate surface 81b side), each second groove 112B is recessed in a rectangular shape from the outer peripheral surface 81c of the oscillating mirror plate 81. Therefore, the groove bottom surface 112b is a linear surface perpendicular to the second straight line L2.

[0064] When the oscillating mirror plate 81 is viewed from the center CL3 direction (the second plate surface 81b side), each second groove portion 112B is recessed close to the center-of-gravity adjustment recess 102. For this reason, each second groove portion 112B is deepest at a position P1 far from the pin engagement recess 91 adjacent to the multiple pin engagement recesses 91, that is, at the position P1 where the second groove portion 112B intersects with the second straight line L2.

[0065] The scroll compressor 10B according to the third embodiment can achieve the same effects as those of the first embodiment.

[0066] The scroll compressors 10, 10A, and 10B according to the present invention are not limited to the embodiments as long as they provide the functions and effects of the present invention. The scroll compressors 10, 10A, and 10B are not limited to horizontally-mounted electric compressors, and may be configured such that the drive shaft 50 is driven by an external power source. For example, the scroll compressors may be belt-driven scroll compressors in which engine power is transmitted to a pulley provided on the drive shaft 50 by a belt.

[0067] Further, the orbiting scroll 80 is not limited to a configuration having the annular sliding contact portion 101 and the recessed portion 102 for adjusting the center of gravity. Moreover, the shapes and sizes of the grooves 111, 112, 112A, and 112B are not limited to those in the first to third embodiments, but can be set arbitrarily. Moreover, it is sufficient that the outer peripheral surface 81c of the oscillating mirror plate 81 has at least one of the grooves 111, 112; 112A; 112B. [Industrial Applicability]

[0068] The scroll compressors 10, 10A, and 10B of the present invention are suitable for use in the refrigeration cycle of a vehicle air conditioner. [Explanation of symbols]

[0069] 10 Scroll Compressor (Example 1) 10A Scroll Compressor (Example 2) 10B Scroll compressor (Example 3) 20. Housing 31a Wall section 50 Drive shaft 51 Eccentric shaft 60 Compression Mechanism 70 Fixed Scroll 71 Fixed Head Plate 71a One side of the board 73 Fixed Spiral Body 80 Swinging Scroll (Example 1) 80A Swing Scroll (Example 2) 80B Swing scroll (Example 3) 81 Swinging Head Plate 81a 1st plate surface 81b 2nd plate surface 81c Outer surface 82 Swinging Spiral Body 83 Compression Chamber 90 Anti-rotation mechanism 91 Recess (pin engagement recess) 91a Inner surface 92 Ring member 93 Pin (anti-rotation pin) 111 First Groove 112 Second groove portion (Example 1) 112A Second groove portion (Example 2) 112B Second groove portion (Example 3)

Claims

1. A housing (20); a compression mechanism (60) that is housed in the housing (20) and that is composed of a fixed scroll (70) and an orbiting scroll (80); a drive shaft (50) that is rotatably supported in the housing (20) and drives the orbiting scroll (80); a rotation prevention mechanism (90) that prevents the orbiting scroll (80) from rotating about its axis, The fixed scroll (70) has a fixed end plate (71) supported in a manner not to rotate relative to the housing (20), and a fixed scroll body (73) in a spiral shape standing upright from one plate surface (71 a) of the fixed end plate (71), The orbiting scroll (80) has a disk-shaped oscillating head (81) positioned opposite the fixed scroll (73), and a spiral-shaped oscillating scroll (82) standing from a first plate surface (81a) of the oscillating head (81) toward the fixed scroll (73) and combined with the fixed scroll (73) to form a compression chamber (83), The oscillating mirror plate (81) is rotatably supported by an eccentric shaft (51) provided at one end of the drive shaft (50), The rotation prevention mechanism (90) is A plurality of circular recesses (91) are provided on a second plate surface (81b) of the oscillating mirror plate (81) opposite to the first plate surface (81a) and are arranged in a circumferential direction of the second plate surface (81b); a plurality of pins (93) extending from a wall portion (31a) in the housing (20) facing the second plate surface (81b) of the oscillating mirror plate (81) into the interior of the plurality of recesses (91) and individually engaging with inner circumferential surfaces (91a) of the plurality of recesses (91) directly or via ring members (92), The oscillating mirror plate (81) has a plurality of first grooves (111) and a plurality of second grooves (112; 112A; 112B) on an outer peripheral surface (81c) that do not communicate with the first plate surface (81a) and the second plate surface (81b), The plurality of first grooves (111) are provided at positions facing the plurality of recesses (91), The second grooves (112; 112A; 112B) are provided between adjacent recesses (91), A scroll compressor characterized in that a depth De2 from the outer peripheral surface (81c) of the oscillating mirror plate (81) to a groove bottom surface (112a) of the plurality of second groove portions (112; 112A; 112B) is greater than a depth De1 from the outer peripheral surface (81c) of the oscillating mirror plate (81) to a groove bottom surface (111a) of the plurality of first groove portions (111).

2. The scroll compressor according to claim 1, wherein the second grooves (112; 112A; 112B) are deepest at positions farthest from the adjacent recesses (91).

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