EP4585805A1

EP4585805A1 - Scroll compressor

Info

Publication number: EP4585805A1
Application number: EP23863079.2A
Authority: EP
Inventors: Imed Guitari; Yukio Kazahaya
Original assignee: Valeo Japan Co Ltd
Current assignee: Valeo Electrification SAS
Priority date: 2022-09-09
Filing date: 2023-08-31
Publication date: 2025-07-16
Also published as: WO2024053541A1; JPWO2024053541A1; CN119768612A

Abstract

[Problem] To prevent a phenomenon of tilting of a ring with respect to a ring fitting portion of a rotation prevention mechanism.

[Solution] A scroll compressor (10) comprises a rotation prevention mechanism (120) that prevents rotation of a movable scroll (80). The movable scroll (80) has an opposing surface (81b) that faces a flat surface (31a) of a partition member (30). The opposing surface (81b) has an annular sliding surface (111) capable of sliding on the flat surface (31a), and a retracted surface (112) on a radially inner side of the sliding surface (111). The rotation prevention mechanism (120) comprises: a ring fitting portion (130) recessed from the retracted surface (112); a ring (140) that is clearance-fitted in the ring fitting portion (130); and a rotation prevention pin (150) extending from the partition member (30) into the ring (140). The ring (140) has, on the second end surface (143) side of the inner circumferential surface (144), a retracted portion (145) that does not contact the pin (150).

Description

[Technical Field]

The present invention relates to a scroll compressor and in particular relates to an anti-rotation mechanism for preventing rotation of a movable scroll.

[Background Art]

There are known scroll compressors comprising an anti-rotation mechanism for preventing rotation of a movable scroll on itself, without impeding orbiting of the movable scroll in relation to a fixed scroll fixed to a housing.
Anti-rotation mechanisms furthermore include what are known as pin-and-ring anti-rotation mechanisms (pin & ring anti-rotation mechanisms), comprising multiple sets of anti-rotation pins (also referred to below simply as "pins") and restricting rings (also referred to below simply as "rings").
In the scroll compressor disclosed in Patent Document 1, a movable scroll comprises a disc-shaped end plate, and a spiral wall standing upright toward the fixed scroll from the end plate. An annular sliding face (referred to as a "rib" in Patent Document 1) sliding against a force receiving plate fixed to the housing is formed in the vicinity of the outermost circumference of an end face of the end plate on the opposite side to the spiral wall.
An axial clearance is formed between the force receiving plate and a face radially inward from the sliding face. In other words, the face radially inward from the sliding face (referred to below as a "retreat face") is positioned with a step that becomes lower from the sliding face to the spiral wall side. A plurality of bottomed recesses (corresponding to ring mating portions) disposed uniformly along a predetermined pitch circle are formed in this "retreat face". Rings engaging with pins fixed to the housing are mated in these recesses. A clearance sufficient to allow the movable scroll to orbit in a predetermined radius of revolution is present between outer circumferential surfaces of the plurality of pins and inner circumferential surfaces of the plurality of rings, and rotation (rotation on itself) of the movable scroll is prevented as a result of the plurality of pins engaging with the plurality of rings, and a known anti-rotation mechanism is constructed by this means.
When rotation of a drive shaft causes the movable scroll to orbit about the drive shaft in the predetermined radius of revolution, there is a reduction in the volume of compression chambers formed between the spiral wall of the movable scroll and the spiral wall of the fixed scroll. The pressure of a refrigerant enclosed within the compression chambers increases toward the center as a result, and a force in a thrust direction attempting to separate the movable scroll from the fixed scroll, and rotational torque causing rotation (rotation on itself) of the actual movable scroll act on the movable scroll because of this pressure. The former force is received by means of a thrust plate (force receiving plate). Meanwhile, the latter rotational torque is received by the pins via the rings, and rotation of the movable scroll is prevented by this means.
In the invention disclosed in Patent Document 1, the length of the rings is greater than the depth of the recesses. Furthermore, there is also a known configuration in which the length of the rings is smaller than the depth of the recesses, as can be seen as prior art in Patent Document 1.
In these conventional anti-rotation mechanisms, the mating between the rings and the recesses is preferably what is known as a clearance fit, with a slight clearance rather than a press-fit. In a configuration in which the rings are fitted in the recesses by means of a clearance fit, the rings are mated in the recesses without being press-fit, so it is possible to eliminate the risk of deformation of the movable scroll or the housing which would be caused by a press-fit.
While one side of the pin is press-fit into the housing, the other side engages with the ring, so the pin receives a load from the ring as a "cantilever". Consequently, the pin elastically deforms under the force from the ring, and a tip end side of the pin deforms so as to move away from the ring, whereas the side of the pin close to the portion press-fit into the housing only deforms by a small amount, and the force from the ring tends to be concentrated. It is also possible that contact between the rings and the pins will no longer be the ideal linear contact, and there may also be point contact between the pins and the near-side inner circumferential surface or far-side inner circumferential surface of the rings.

[Prior Art Documents]

[Patent Documents]

[Patent Document 1] JP 2017-532495 A

[Summary of the Invention]

[Problems to be Solved by the Invention]

In the conventional configuration described above, the length of the rings is greater than the depth of the recesses (ring mating portions), so the near-side end faces of the rings protrude from the surface of the retreat face in which the recesses are formed. Furthermore, even if the length of the rings is smaller than the depth of the recesses, the rings constituting the anti-rotation mechanism fit into the recesses with a clearance, so the rings may move in the axial direction of the recesses and protrude from the surface of the retreat face in which the recesses are formed due to vibration during compressor operation and friction with the pins, etc.
If the near side of the inner circumferential surface of the rings is pressed by the pins when the near-side end face of the rings protrudes from the recesses in this way, as stated above, the point of action of the load from the pins on the rings falls outside the recesses, so there is a risk of what is known as a phenomenon of tilting of the rings in relation to the recesses, where the rings tilt within the range of clearance with the recesses.
When this tilt phenomenon occurs, the orientation of the rings within the recesses becomes unstable, which risks producing vibration, and generating wear of the thrust plate and noise, as the rings and the thrust plate make one-sided contact.
The present invention has been devised to solve the problems above, and the objective thereof lies in providing technology to prevent the phenomenon of tilting of rings in relation to ring mating portions in a pin-and-ring anti-rotation mechanism.

[Means for Solving the Problems]

The reference symbols used in the appended drawings are added in parentheses in the description below in order to make the present invention easier to understand, but this does not limit the present invention to the forms depicted.
The present invention provides a scroll compressor comprising: a housing (20); a partition member (30) fixed inside the housing (20); an accommodating space (25) defined by the partition member (30) inside the housing (20); a fixed scroll (70) and a movable scroll (80) accommodated in combination inside the accommodating space (25); and an anti-rotation mechanism (120) for preventing rotation of the movable scroll (80) on itself, characterized in that

the movable scroll (80) comprises a disc-shaped movable plate (81) and a movable spiral wall (82) standing upright from the movable plate (81),
a plate face (81b) on the opposite side of the movable plate (81) to the movable spiral wall (82) has an opposing face (81b) facing a flat face (31a) of the partition member (30),
the opposing face (81b) comprises: an annular sliding face (111) which is provided on the outermost circumference and is capable of sliding in relation to the flat face (31a) of the partition member (30); and a retreat face (112) positioned radially inside the sliding face (111) and at a predetermined depth from the sliding face (111),
the anti-rotation mechanism (120) comprises: ring mating portions (130) indented from the retreat face (112) along a direction orthogonal to the sliding face (111) of the movable scroll (80); cylindrical rings (140; 240; 340) mated with a clearance fit in relation to the ring mating portions (130); and anti-rotation pins (150) extending from the flat face (31a) of the partition member (30) into the rings (140; 240; 340) so as to be capable of contacting an inner circumferential surface (144) of the rings (140; 240; 340), and
the rings (140; 240; 340) have a first end face (142) disposed on a far side of the ring mating portions (130), and a second end face (143) on the opposite side to the first end face (142) in the axial direction, and a retreat portion (145, 245) that does not contact the anti-rotation pins (150) is provided along the whole circumference on at least the second end face (143) side of the inner circumferential surface (144).

The rings are thus mated with a clearance fit in relation to the inner circumferential surface of the ring mating portions. Consequently, there is a minute gap (clearance) between the inner circumferential surface of the ring mating portions and the outer circumferential surface of the rings. However, the retreat portion is formed on the inner circumferential surface of the rings. It is therefore possible to prevent the phenomenon of tilting of the rings in relation to the ring mating portions by setting the position at which force is transmitted between the anti-rotation pins and the rings away from the end face of the rings.
Preferably, the ring mating portions (130) have a bottom face (132) facing the first end face (142) of the rings (140; 240; 340),

the retreat portion (145, 245) is configured by a circumferential surface (145; 245) positioned radially outward from the inner circumferential surface (144) along the whole circumference of the inner circumferential surface (144) of the rings (140; 240; 340), and
in a state in which the first end face (142) of the rings (140; 240; 340) is touching the bottom face (132) of the ring mating portions (130), a boundary (145b) between the retreat portion (145; 245) and the inner circumferential surface (144) is positioned further to the bottom face (132) side of the ring mating portions (130) than an opening-side edge (135) of the inner circumferential surface (131) of the ring mating portions (130).

Also preferably, in a state in which the second end face (143) of the rings (140; 240; 340) is touching the flat face (31a) of the partition member (30), the boundary (145b) is positioned further to the bottom face (132) side of the ring mating portions (130) than the opening-side edge (135) of the inner circumferential surface (131) of the ring mating portions (130).
Preferably, the retreat portion (145) is configured by a tapering surface which decreases in diameter from the second end face (143) toward the far side of the rings (140).
As another preferred example, the retreat portion (245) is configured by a cylindrical surface (245a) of larger diameter than the inner circumferential surface (144) of the rings (240).
Preferably, the retreat portion (145; 245) is formed only on the second end face (143) side of the rings (140; 240).
Also preferably, the rings (140; 240) are provided with a reverse-assembly preventing portion (160) for preventing the rings (140) from being assembled the opposite way round with the ring mating portions (130).
As another preferred example, retreat portions (145, 245) are formed along the whole circumference of the inner circumferential surface (144) of the rings (340) on both axial end faces (142, 143) of the rings (340).

[Effects of the Invention]

The present invention makes it possible to prevent the phenomenon of tilting of rings in relation to ring mating portions in a pin-and-ring anti-rotation mechanism.

[Brief Description of the Drawings]

[Fig. 1] is a view in cross section of a scroll compressor according to example 1.
[Fig. 2] is an enlargement of the portion 2 in fig. 1.
[Fig. 3] is an oblique view in which a movable scroll illustrated in fig. 2 is seen from a fixed member side.
[Fig. 4] is an enlargement in cross section of an anti-rotation mechanism illustrated in fig. 2.
[Fig. 5] is an exploded view of the anti-rotation mechanism illustrated in fig. 4.
[Fig. 6] Fig. 6A is an illustrative diagram of the anti-rotation mechanism in a state in which a ring illustrated in fig. 2 is touching a bottom face of a ring mating portion; and fig. 6B is an illustrative diagram of the anti-rotation mechanism in a state in which the ring illustrated in fig. 2 is at a distance from the bottom face of the ring mating portion.
[Fig. 7] is a view in cross section of the ring in the anti-rotation mechanism of a scroll compressor according to example 2.
[Fig. 8] Fig. 8A is an illustrative diagram of a configuration in which tapered retreat portions are provided on both end faces of the ring in the anti-rotation mechanism of a scroll compressor according to example 3; fig. 8B is an illustrative diagram of a configuration in which cylindrical retreat portions are provided on both end faces of the ring in the anti-rotation mechanism of the scroll compressor according to example 3; fig. 8C is an illustrative diagram of a configuration in which a cylindrical retreat portion is provided on one end face and a tapered retreat portion is provided on the other end face of the ring in the anti-rotation mechanism of the scroll compressor according to example 3; and fig. 8D is an illustrative diagram of a configuration in which a tapered retreat portion is provided on one end face and a cylindrical retreat portion is provided on the other end face of the ring in the anti-rotation mechanism of the scroll compressor according to example 3.

[Embodiments of the Invention]

Embodiments of the present invention will be described below with reference to the appended drawings. It should be noted that the forms depicted in the appended drawings are examples of the present invention, and the present invention is not limited to those forms.

A scroll compressor 10 according to example 1 will be described with reference to fig. 1-6.
As shown in fig. 1, the scroll compressor 10 is suitable for use in a refrigeration cycle employing a refrigerant as a working fluid, and is employed in the refrigeration cycle of an automotive air conditioning device, for example. It should be noted that there is no limitation to the purpose of use of the scroll compressor 10.
The scroll compressor 10 comprises, for example: a housing 20 which can be installed horizontally; a motor 40 accommodated in the housing 20; an inverter 45 which is accommodated in the housing 20 and drive-controls the motor 40; and a scroll compression mechanism 60 which is accommodated in the housing 20 and is driven by means of the motor 40.
The housing 20 is formed, for example, by: a bottomed cylindrical first housing 21; and a second housing 22 (head member 22) which closes off the opening on one side of the first housing 21.
One end of the first housing 21 is closed off by a bottom wall 23, while the other end is completely open. The opening is closed off by the openable/closable head member 22. A partition member 30 partitions the interior of the first housing 21 into a first accommodating chamber 24 on the bottom wall 23 side, and a second accommodating chamber 25 on the side of the opening which is closed off by the head member 22.
The first accommodating chamber 24 may also be referred to below as the "low-pressure chamber 24". The second accommodating chamber 25 constitutes an accommodating space defined by the housing 20 and the partition member 30 fixed inside the housing 20. The second accommodating chamber 25 may also be referred to below as the "accommodating space 25".
The partition member 30 is a disc-shaped member which restricts both relative rotation and relative movement in the axial direction with respect to the first housing 21. The partition member 30 may also be referred to below as the "fixed member 30".
The partition member 30 is configured by a disc-shaped partition plate portion 31, and a support portion 32 integrally provided in the center of the partition plate portion 31. The partition member 30 comprises a plurality of intake holes 33 providing communication between the first accommodating chamber 24 and the second accommodating chamber 25.
The motor 40 is housed in the first accommodating chamber 24. The scroll compression mechanism 60 (also referred to below simply as the compression mechanism 60) is housed in the second accommodating chamber 25. It should be noted that the partition member 30 may be considered as a component of the compression mechanism 60. That is to say, even if a partition wall 34 is considered as part of the compression mechanism 60, this does not depart from the essential point of the present invention.
The first housing 21 further comprises an intake port 26 for taking the refrigerant into the first accommodating chamber 24 from the outside. The head member 22 comprises: a discharge chamber 27 from which the refrigerant compressed by the compression mechanism 60 is discharged; an oil separation chamber 28 for separating oil from the refrigerant conducted from the discharge chamber 27; and a discharge port 29 for discharging to the outside the gaseous refrigerant from which the oil has been separated by means of the oil separation chamber 28. The first housing 21 further comprises an inverter chamber 21b for accommodating the inverter 45.
The motor 40 comprises: a rotor having a longitudinal direction of the housing 20 as its center of rotation, and an annular stator 42 enclosing the periphery of the rotor 52, the motor 41 driving the compression mechanism 60. The stator 42 is fixed to an inner circumferential surface 21a of the first housing 21.
A drive shaft 51 (output shaft 51) is fixed to the rotor 41. The drive shaft 51 also serves as an output shaft of the motor 40. The rotor 41 is rotatable about a center line CL1 of the drive shaft 51.
The drive shaft 51 runs through the partition member 30 from the first accommodating chamber 24 toward the second accommodating chamber 25, and is rotatably supported by means of a first bearing 52 provided in the support portion 32 of the partition member 30, and a second bearing 53 provided in the bottom wall 23 of the housing 20. The drive shaft 51 further comprises an eccentric shaft 54 on one end face penetrating the partition member 30. The eccentric shaft 54 extends from one end face of the drive shaft 51 toward the compression mechanism 60 and is parallel with the drive shaft 51. A center line CL2 of the eccentric shaft 54 is offset from the center line CL1 of the drive shaft 51. An annular bush 55 is rotatably mated with the eccentric shaft 54. A counterweight 56 protruding radially from the bush 55 is integrally provided with a portion of the bush 55.
The compression mechanism 60 comprises a pair of scroll members 70, 80 accommodated in the second accommodating chamber 25.
The fixed scroll 70 comprises a flat, disc-shaped fixed plate 71, a cylindrical outer circumferential wall 72, and a spiral-shaped fixed spiral wall 73. The fixed plate 71 comprises a discharge hole 74 in a central part thereof. The outer circumferential wall 72 is a cylindrical part standing upright integrally along the whole circumference of the fixed plate 71, from an outer edge of one plate face 71a (the face 71a facing the partition member 30 side) to the partition member 30 side. A refrigerant intake port 75 for taking the refrigerant from radially outward to inward is formed in the outer circumferential wall 72. The fixed spiral wall 73 stands upright integrally from said one plate face 71a of the fixed plate 71 toward the partition member 30 side. The fixed scroll 70 is supported between the head member 22 and the partition member 30 so as to be incapable of relative rotation, and so that the fixed plate 71 is oriented orthogonally to the center line CL2 of the eccentric shaft 54.
The movable scroll 80 comprises a flat, disc-shaped movable plate 81, and a spiral-shaped movable spiral wall 82. The outer diameter of the movable plate 81 is formed with a size that does not cause interference even when the movable scroll 80 orbits at a predetermined eccentric radius inside the outer circumferential wall 72 of the fixed scroll 70. The movable spiral wall 82 stands upright integrally from a face 81a (referred to below as the "first plate face 81a") of the movable plate 81 facing the plate face 71a of the fixed plate 71 toward the plate face 71a of the fixed plate 71. A third bearing 57 is fitted in the center of a plate face 81b (referred to below as the "second plate face 81b") opposite the first plate face 81a. An outer circumferential surface of the bush 55 mates with an inner circumferential surface of the third bearing 57.
Compression chambers 83 enclosed by the plates 71, 81 and the spiral walls 73, 82 are formed by engagement of the fixed spiral wall 73 and the movable spiral wall 82.
As shown in fig. 1 and 2, rotation of the drive shaft 51 enables the center of the movable scroll 80 to orbit with a preset eccentric radius (eccentric rotation) via the bush 55 and third bearing 57 mated with the eccentric shaft 54.
Here, the "preset eccentric radius" is not a fixed value and also includes values which are automatically adjusted so that the amount of eccentricity of the movable scroll 80 achieves a set ideal amount of eccentricity. For example, a self-centering function may be provided by mating of the eccentric shaft 54 and the bush 55 so that the spiral walls 73, 82 make optimum contact when the movable scroll 80 orbits.
As described above, rotation of the drive shaft 51 causes the movable scroll 80 to orbit. As a result, the refrigerant taken in from the intake port 26 passes through the gap in the motor 40 inside the low-pressure chamber 24, and is taken into the compression chambers 83 through the refrigerant intake port 75 of the fixed scroll 70 via the intake holes 33 in the partition member 30. As the movable scroll 80 orbits, the compression chambers 83 steadily move toward the center while the internal volume thereof decreases. The refrigerant inside the compression chambers 83 is compressed by this means. When the pressure inside the compression chambers 83 that have moved to the center rises to a pressure greater than the pressure inside the discharge chamber 27, a discharge valve 91 opens due to the pressure difference and the refrigerant inside the compression chambers 83 flows into the discharge chamber 27 through the discharge hole 74. The refrigerant inside the discharge chamber 27 is discharged to the outside from the discharge port 29 via the oil separation chamber 28.
The relationship between the partition plate portion 31 of the partition member 30 and the movable scroll 80 will be described in detail next.
As shown in fig. 1 and 2, one end face 31a of the partition plate portion 31 faces the second accommodating chamber 25 side. This one end face 31a is capable of supporting the sliding motion of the movable scroll 80. This one end face 31a may also be referred to below as the "flat face 31a" or the "sliding support face 31a". A center line CL3 of the movable scroll is orthogonal to the flat face 31a when a second end face 81b of the movable scroll 80 is touching the flat face 31a.
A thrust member 101 capable of receiving a thrust load resulting from a compression reaction force is preferably interposed between the flat face 31a of the partition plate portion 31 and the second plate face 81b of the movable scroll 80. The thrust member 101 is configured by a thin plate-shaped annular thrust race, for example. The thrust member 101 is also referred to below as the "thrust race 101", as appropriate. The thrust race 101 comprises a material having excellent wear resistance, and can be sandwiched between the flat face 31a of the partition plate portion 31 and a tip end face of the cylindrical outer circumferential wall 72 of the fixed scroll 70.
As shown in fig. 3 and 4, the second plate face 81b (opposing face 81b) comprises: an annular sliding face 111 which is provided on the outermost circumference and is capable of sliding in relation to the flat face 31a of the partition member 30; and a retreat face 112 positioned radially inside and at a predetermined depth from the sliding face 111. The "predetermined depth" as referred to here may be a specific fixed depth, or a depth spanning a specific range, but does not include zero.
An annular edge face 113 protruding from the retreat face 112 is further provided on a radial inner side of the retreat face 112.
The center line CL3 of the movable scroll 80 is in the center of the movable plate 81 and orthogonal to the sliding face 111.
As shown in fig. 4, the sliding face 111 of the movable scroll 80 is in close slidable contact with the thrust race 101. In a state in which the sliding face 111 is in close contact with the thrust race 101, a space portion 114 radially inside the location of close contact between the thrust race 101 and the sliding face 111 enables an oil reservoir space to be formed, and it is possible to retain lubricating oil supplied via a lubricating oil supply path (not depicted). The locations of sliding between the sliding face 111 of the movable scroll 80 and the thrust race 102, and the locations of contact between a ring 140 and a pin 150 (to be described later) can be lubricated by means of the lubricating oil retained in the space portion 114, making it possible to suppress sliding resistance and to suppress wear.
It should be noted that the thrust race 101 may or may not be present. This example 1 should be configured so that the sliding face 111 of the movable scroll 80 is in close slidable contact with the flat face 31a of the partition plate portion 31 either directly or indirectly through the thrust race 101. In the description of this example 1, when the sliding face 111 of the movable scroll 80 is referred to as being in sliding contact with the flat face 31a of the partition plate portion 31, this should be assumed to include a configuration of direct sliding contact with the flat face 31a, or indirect sliding contact through the thrust race 101.
As shown in fig. 3 and 4, the scroll compressor 10 comprises the anti-rotation mechanism 120 for preventing rotation of the movable scroll 80 on itself. The anti-rotation mechanism 120 comprises: a plurality of ring mating portions 130 indented from the retreat face 112 along the center line CL3 of the movable scroll 80 (along a direction orthogonal to the sliding face 111); a plurality of rings 140 (also referred to as restricting rings 140) respectively mated with the plurality of ring mating portions 130; and a plurality of pins 150 (also referred to as anti-rotation pins 150) respectively extending from the flat face 31a of the partition member 30 into the plurality of rings 140.
As shown in fig. 5, the ring mating portions 130 are in the form of bottomed holes formed by an inner circumferential surface 131 and a bottom face 132. The inner circumferential surface 131 of the ring mating portions 130 is formed in a circular shape orthogonal to the sliding face 111 and opens onto the retreat face 112. An opening end 133 of the ring mating portions 130 preferably comprises a tapered bevel portion 134 for easing insertion of the rings 140 into the ring mating portions 130. A corner 135 between the inner circumferential surface 131 and the bevel portion 134 of the ring mating portions 130 will be referred to as the "opening-side edge 135 of the inner circumferential surface 131".
It should be noted that the bevel portion 134 may or may not be present. When the bevel portion 134 is not present, the opening-side edge 135 of the inner circumferential surface 131 is aligned with the opening end 133 of the ring mating portions 130.
The bottom face 132 is a flat face parallel to the sliding face 111. A cavity portion 136 which is indented from the bottom face 132 and is smaller than the diameter of the inner circumferential surface 131 of the ring mating portions 130 may further be formed in order to reduce the weight of the movable scroll 80 and to reduce the number of places to be machined.
A depth (first depth) from the sliding face 111 to the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130 is D1. A depth (second depth) from the edge 135 to the bottom face 132 is D2, which is greater than the first depth D1.
As shown in fig. 5, the rings 140 are cylindrical members with a circular penetration which are mated with a "clearance fit" (mated with play) in relation to the ring mating portions 130. The extent of the clearance fit is preferably such that an outer circumferential surface 141 of the rings 140 mated with the inner circumferential surface 131 of the ring mating portions 130 is capable of axial sliding, rotational movement, and removal, and such that there is a small maximum gap (clearance). The thickness of the rings 140 is uniform over the circumferential direction thereof.
An end face 142 of the rings 140 on the side facing the bottom face 132 of the ring mating portions 130 when the rings 140 are mated with the ring mating portions 130 will be referred to as the "first end face 142", and an end face 143 on the opposite axial side to the first end face 142 will be referred to as the "second end face 143". The first end face 142 and the second end face 143 are parallel to each other and are also parallel to the bottom face 132 of the ring mating portions 130.
As shown in fig. 4, the pins 150 are configured by round columns having a circular cross section, and are positioned parallel to the inner circumferential surface 144 of the rings 140. One end portion 151 of the pins 150 is fixed by means of a press-fit in pin holes 34 formed in the partition member 30. That is to say, the pins 150 have one end portion 151 fixed to the partition member 30 while another end portion 152 thereof is a free end, having what is known as a cantilever structure.
The plurality of pins 150 are arranged so that the outer circumferential surface of the respective other end portions 152 thereof are capable of contacting the inner circumferential surface 144 of the corresponding rings 140. The clearance between the inner diameter of the rings 140 and the outer diameter of the other end portion 152 of the pins 150 is greater than the amount of mobility (double the eccentric radius) of the movable scroll 80. The plurality of rings 140 and the corresponding plurality of pins 150 successively make linear contact, thereby making it possible to permit orbiting along the center line CL3 while preventing rotation of the movable scroll 80 on itself.
As shown in fig. 4 and 5, a retreat portion 145 that does not contact the pins 150 is provided on the rings 140 along the whole circumference on at least one axial end 143 side (second end face 143 side) of the inner circumferential surface 144.
To give an example, the retreat portion 145 is formed only on the second end face 143 side of the rings 140, as shown in fig. 5. The retreat portion 145 is configured by a circumferential surface positioned radially outward from the inner circumferential surface 144 along the whole circumference of the inner circumferential surface 144 of the rings 140. The retreat portion 145 will also be referred to as the "circumferential surface 145", as appropriate.
The circumferential surface 145 (retreat portion 145) is a plane of rotation of a line connecting a predetermined start point 145a and end point 145b in the axial direction of the rings 140 along a center line RL of the rings 140. The start point 145a is positioned on the second end face 143 of the rings 140, radially outward by a predetermined amount from the inner circumferential surface 144 of the rings 140. The end point 145b is positioned on the inner circumferential surface 144 of the rings 140, a predetermined amount away from the second end face 143 to the first end face 142 side. The end point 145b is positioned at a boundary of the inner circumferential surface 144 and the circumferential surface 145 (retreat portion 145) of the rings 140. The end point 145b will also be referred to as the "boundary 145b", as appropriate.
More specifically, the circumferential surface 145 (retreat portion 145) is configured by a tapering surface which decreases in diameter from the axial end 143 (second end face 143) toward the far side (first end face 142 side) of the rings 140. The retreat portion 145 is thus configured by a circumferential surface (tapering surface) which is positioned radially outward from the inner circumferential surface 144 along the whole circumference of the inner circumferential surface 144 of the rings 140. When the rings 140 are viewed from the outer circumferential surface 141 side, an angle θ1 formed by the inner circumferential surface 144 and the retreat portion 145 is an obtuse angle.
An axial length from the start point 145a to the end point 145b (length of the retreat portion 145) is L1. An axial length from the end point 145b to the first end face 142 of the rings 140 (straight length) is L2, which is greater than the length L1 of the retreat portion 145. By making the straight length L2 greater, it is possible to achieve a state of stable linear contact of the pins 150 (see fig. 4) with the inner circumferential surface 144 of the rings 140.
As shown in fig. 6A, in a state in which the first end face 142 of the rings 140 is touching the bottom face 132 of the ring mating portions 130, the boundary 145b (end point 145b of the retreat portion 145) is positioned further to the bottom face 132 side of the ring mating portions 130 than the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130. That is to say, the distance L2 (straight length L2) from the bottom face 132 of the ring mating portions 130 to the boundary 145b is shorter than the distance D2 (second depth D2) from the bottom face 132 of the ring mating portions 130 to the opening-side edge 135 of the ring mating portions 130. In this state also, the second end face 143 of the rings 140 protrudes to the partition member 30 side from the ring mating portions 130.
As shown in fig. 6B, in a state in which the second end face 143 of the rings 140 is touching the flat face 31a of the partition member 30, the boundary 145b is positioned further to the bottom face 132 side of the ring mating portions 130 than the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130. That is to say, the distance L1 (length L1 of the retreat portion 145) from the flat face 31a to the boundary 145b is longer than the distance D1 (first depth D1) from the flat face 31a to the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130.
As shown in fig. 5 and 6A, the rings 140 are provided with a reverse-assembly preventing portion 160 for preventing the rings 140 from being assembled the opposite way round with the ring mating portions 130. For example, the reverse-assembly preventing portion 160 is configured by a small protrusion 161 protruding radially outward from the outer circumferential surface 141 of the rings 140. The protrusion 161 includes a flange which is formed along the whole circumference on the outer circumferential surface 141. In a state in which the first end face 142 of the rings 140 is touching the bottom face 132 of the ring mating portions 130, the protrusion 161 lies at a position that does not touch the retreat face 112 or the bevel portion 134, i.e., a position in the vicinity of the second end face 143 of the rings 140.
As shown in fig. 6A, the protrusion 161 therefore does not interfere with the retreat face 112 or the bevel portion 134 when the rings 140 are correctly assembled with the ring mating portions 130. On the other hand, if the rings 140 are assembled the opposite way round with the ring mating portions 130, the protrusion 161 interferes with the retreat face 112 or the bevel portion 134, and the rings 140 cannot be assembled. This makes it possible to prevent the rings 140 from being assembled the opposite way round with the ring mating portions 130.
A description will be given next of the principle of preventing the phenomenon of tilting of the rings 140 in relation to the ring mating portions 130 when the movable scroll 80 is orbiting.
As shown in fig. 4, the pins 150 have a cantilever structure with said one end portion 151 fixed to the partition member 30. For example, when the movable scroll 80 orbits in the direction of the arrow Ru, the inner circumferential surface 144 of the rings 140 makes linear contact with said other end portion 152 (free end 152) of the pins 150. Said other end portion 152 takes the load acting from the inner circumferential surface 144 of the rings 140.
Because of this load, said other end portion 152 of the pins 150 may elastically deform, as shown by the imaginary line, for example. When the pins 150 elastically deform, they touch only the boundary 145b (end point 145b of the retreat portion 145). The boundary 145b receives a reaction force fr from the pins 150. The reaction force fr has the opposite orientation to the direction of orbiting of the movable scroll 80 (the direction of the arrow Ru). The rings 140 that have received the reaction force fr attempt to collapse in the radial direction of the ring mating portions 130 (direction of the arrow Tr), with the opening-side edge 135 of the ring mating portions 130 as a support point. In this state, however, the outer circumferential surface 141 of the rings 140 is touching the inner circumferential surface 131 of the ring mating portions 130 in the direction in which the reaction force fr is exerted.
The rings 140 are capable of axially displacing in relation to the ring mating portions 130 in a range from the position of touching the bottom face 132 shown in fig. 6A to the position of touching the flat face 31a shown in fig. 6B. However, whatever the axial position of the rings 140 in relation to the ring mating portions 130, the boundary 145b is still positioned further to the bottom face 132 side of the ring mating portions 130 than the opening-side edge 135. That is to say, the position 145b (boundary 145b) at which force is transmitted between the pins 150 and the rings 140 is set away from the end face 143 (second end face 143) of the rings 140 to the bottom face 132 side. The rings 140 are supported by the inner circumferential surface 131 of the ring mating portions 130 so as not to collapse in the radial direction (the direction of the arrow Tr in fig. 4) of the ring mating portions 130. As a result, it is possible to prevent the phenomenon of tilting of the rings 140 in relation to the ring mating portions 130.
The description of example 1 above will be summarized as follows.
As shown in fig. 1, the scroll compressor 10 comprises: the housing 20; the partition member 30 fixed inside the housing 20; the accommodating space 25 (second accommodating chamber 25) defined by the partition member 30 inside the housing 20; the fixed scroll 70 and the movable scroll 80 accommodated in combination inside the accommodating space 25; and the anti-rotation mechanism 120 for preventing rotation of the movable scroll 80 on itself. The movable scroll 80 comprises the disc-shaped movable plate 81 and the movable spiral wall 82 standing upright from the movable plate 81. The plate face 81b (second plate face 81b) on the opposite side of the movable plate 81 to the movable spiral wall 82 has the opposing face 81b facing the flat face 31a of the partition member 30.
As shown in fig. 3 and 4, the opposing face 81b comprises: the annular sliding face 111 which is provided on the outermost circumference and is capable of sliding in relation to the flat face 31a of the partition member 30; and the retreat face 112 positioned radially inside the sliding face 111 and at a predetermined depth from the sliding face 111.
As shown in fig. 4, the anti-rotation mechanism 120 comprises: the ring mating portions 130 indented from the retreat face 112 along a direction orthogonal to the sliding face 111 of the movable scroll 80; the cylindrical rings 140 mated with a clearance fit in relation to the ring mating portions 130; and the anti-rotation pins 150 extending from the flat face 31a of the partition member 30 into the rings 140 so as to be capable of contacting the inner circumferential surface 144 of the rings 140. The rings 140 have the first end face 142 disposed on the far side of the ring mating portions 130, and the second end face 143 on the opposite side to the first end face 142 in the axial direction, and the retreat portion 145 that does not contact the anti-rotation pins 150 is provided along the whole circumference on at least the second end face 143 side of the inner circumferential surface 144.
The rings 140 are mated with a clearance fit in relation to the inner circumferential surface 131 of the ring mating portions 130. Consequently, there is a gap (clearance) between the inner circumferential surface 131 of the ring mating portions 130 and the outer circumferential surface 141 of the rings 140. However, the retreat portion 145 is formed on the inner circumferential surface 144 of the rings 140. It is therefore possible to prevent the phenomenon of tilting of the rings 140 in relation to the ring mating portions 130 by setting the position at which force is transmitted between the anti-rotation pins 150 and the rings 140 away from the end face 143 (second end face 143) of the rings 140.
As shown in fig. 4, the ring mating portions 130 have the bottom face 132 facing the first end face 142 of the rings 140. The retreat portion 145 is configured by a circumferential surface (corresponding to the circumferential surface 145) positioned radially outward from the inner circumferential surface 144 along the whole circumference of the inner circumferential surface 144 of the rings 140.
As shown in fig. 6A, in a state in which the first end face 142 of the rings 140 is touching the bottom face 132 of the ring mating portions 130, the boundary 145b between the retreat portion 145 and the inner circumferential surface 144 is positioned further to the bottom face 132 side of the ring mating portions 130 than the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130.
In a state in which the first end face 142 of the rings 140 is touching the bottom face 132 of the ring mating portions 130, the boundary 145b (end point 145b of the retreat portion 145) between the retreat portion 145 and the inner circumferential surface 144 is thus positioned further to the bottom face 132 side than the opening-side edge 135 of the ring mating portions 130. The anti-rotation pins 150 therefore make point contact only at the boundary 145b between the retreat portion 145 and the inner circumferential surface 144, so that even if the rings 140 are pressed by the anti-rotation pins 150, the point of action on the rings 140 from the anti-rotation pins 150 is inside the ring mating portions 130. It is possible to prevent the phenomenon known as tilting of the rings 140 in relation to the ring mating portions 130, where the rings 140 tilt in the range of clearance with the ring mating portions 130.
As shown in fig. 6B, in a state in which the second end face 143 of the rings 140 is touching the flat face 31a of the partition member 30, the boundary 145b between the retreat portion 145 and the inner circumferential surface 144 is positioned further to the bottom face 132 side of the ring mating portions 130 than the opening-side edge 135 of the inner circumferential surface 131 of the ring mating portions 130.
Even if the rings 140 are assumed to have exited to the maximum extent from the ring mating portions 130 and have exited to a position touching the flat face 31a of the partition member 30, the position 145b (boundary 145b) at which force is transmitted between the anti-rotation pins 150 and the rings 140 is still positioned on the far side of the ring mating portions 130. It is possible to prevent the phenomenon of tilting of the rings 140 in relation to the ring mating portions 130, even if a load is exerted at the boundary 145b from the anti-rotation pins 150.
As shown in fig. 5, the retreat portion 145 is configured by a tapering surface which decreases in diameter from the second end face 143 toward the far side (first end face 142 side) of the rings 140. The angle θ formed by the inner circumferential surface 144 and the retreat portion 145 of the rings 140 is therefore an obtuse angle. When the anti-rotation pins 150 make point contact at the corner 145b (boundary 145b) between the inner circumferential surface 144 and the retreat portion 145 of the rings 140, the contact pressure can be alleviated to a greater extent than when the angle θ is an acute angle. Moreover, by configuring the boundary 145b area with an arc-shaped cross section, contact pressure can be alleviated to an even greater extent because the boundary 145b is rounded.
The retreat portion 145 is formed only on the second end face 143 side of the rings 140, as shown in fig. 4. The retreat portion 145 therefore needs to be formed only on one side of the rings 140. The straight length L2 (see fig. 5) over which the rings 140 and the anti-rotation pins 150 make linear contact can therefore be increased, making it possible to reduce linear pressure as a result.
As shown in fig. 4, the rings 140 are provided with the reverse-assembly preventing portion 160 for preventing the rings 140 from being assembled the opposite way round with the ring mating portions 130. It is therefore possible to easily prevent the rings 140 from being assembled the opposite way round with the ring mating portions 130 as a result of human error.

A scroll compressor 200 according to example 2 will be described with reference to fig. 7. Fig. 7 corresponds to fig. 5 above.
The feature of the scroll compressor 200 according to example 2 lies in that the rings 140 of example 1 shown in fig. 1-6 described above have been changed to the rings 240 shown in fig. 7. The other basic components are common to those of the scroll compressor 10 according to example 1. The parts in common with the scroll compressor 10 according to example 1 bear the same reference symbols and will not be described in detail again.
The feature of the rings 240 of example 2 lies in a retreat portion 245, and the other components are the same as those of the rings 140 according to example 1. The retreat portion 245 corresponds to the retreat portion 145 of example 1 shown in fig. 5.
The retreat portion 245 is configured by a circumferential surface positioned radially outward from the inner circumferential surface 144 along the whole circumference of the inner circumferential surface 144 of the rings 240. The retreat portion 245 will also be referred to as the "circumferential surface 245", as appropriate. The position of the start point 145a and the position of the end point 145b (boundary 145b) of the circumferential surface 245 are the same as the respective positions of the start point 145a and the end point 145b of the circumferential surface 145 of example 1 shown in fig. 5. The circumferential surface 245 (retreat portion 245) is a plane of rotation of a line connecting a predetermined start point 145a and end point 145b in the axial direction of the rings 240 along a center line RL of the rings 140.
The retreat portion 245 is configured by a cylindrical surface 245a of larger diameter than the inner circumferential surface 144 of the rings 240. A boundary between the cylindrical surface 245a and the inner circumferential surface 144 is directly or indirectly connected. For example, the retreat portion 245 is formed by the cylindrical surface 245a, and a step surface 245b at the boundary of the inner circumferential surface 144 and the cylindrical surface 245a.
The start point 145a of the cylindrical surface 245a is positioned at the second end face 143 of the rings 240. The step surface 245b (end face 245b) is an annular face. The inner circumference of the step surface 245b is positioned at a dividing line 145b (boundary 145b) with the inner circumferential surface 144 of the rings 240. This dividing line 145b constitutes the end point 145b. The length L1 of the retreat portion 145 and the straight length L2 are the same as those of the rings 140 of example 1.
The retreat portion 245 is thus configured by the cylindrical surface 245a of larger diameter than the inner circumferential surface 144 of the rings 240. The dimensions are easily managed because the retreat portion 245 is simply formed into the cylindrical surface 245a.
The scroll compressor 200 according to example 2 is capable of demonstrating the same effects as the scroll compressor 10 of example 1 above, in addition to the effects of example 2.
A summary of the circumferential surface 245 of example 2 will be described here. As shown in fig. 7, let us assume that a line segment in the axial direction along the cylindrical surface 245a is a "first line segment", and a line segment in the radial direction along the step surface 245b is a "second line segment". We will now imagine a "line" connecting the first line segment and the second line segment, and connecting one end of each of the line segments to the start point 145a and the endpoint 145b. This line is rotated along the center line RL of the rings 140, thereby forming the circumferential surface 245 based on this center line RL.
The "line" connected to the start point 145a and the end point 145b is thus not limited to a straight line and also includes curves. The start point 145a and the end point 145b may also be connected by a curve. In summary, the feature of examples 1 and 2 lies in the fact that the boundary 145b between the inner circumferential surface 144 and the circumferential surfaces 145, 245 is provided on the rings 140, 240, as shown in fig. 5 and 7.

A scroll compressor 300 according to example 3 will be described with reference to fig. 8A-8D. Fig. 8A-8D correspond to fig. 5 above.
The feature of the scroll compressor 300 according to example 3 lies in that the rings 140 of example 1 shown in fig. 1-6 and the rings 240 of example 2 described in example 2 shown in fig. 7 have been changed to the rings 340 shown in fig. 8A-8D. The other basic components are common to those of the scroll compressors 10, 200 according to examples 1 and 2. The parts in common with the scroll compressors 10, 200 according to examples 1 and 2 bear the same reference symbols and will not be described in detail again.
The ring 340 shown in fig. 8A comprises retreat portions 145 of example 1 shown in fig. 5 on both axial end faces 142, 143.
The ring 340 shown in fig. 8B comprises retreat portions 245 of example 2 shown in fig. 7 on both axial end faces 142, 143.
The ring 340 shown in fig. 8C comprises the retreat portion 245 of example 2 shown in fig. 7 on the first end face 142, and also comprises the retreat portion 145 of example 1 shown in fig. 5 on the second end face 143.
The ring 340 shown in fig. 8D comprises the retreat portion 145 of example 1 shown in fig. 5 on the first end face 142, and also comprises the retreat portion 245 of example 2 shown in fig. 7 on the second end face 143.
The retreat portions 145, 245 are thus formed along the whole circumference of the inner circumferential surface 144 of the rings 340 on both axial end faces 142, 143 of the rings 340. It is therefore possible to prevent the phenomenon of tilting of the rings 340 in relation to the ring mating portions 130, even if the rings 340 are assembled in the opposite direction in relation to the ring mating portions 130 (see fig. 5).
The scroll compressor 300 according to example 3 is capable of demonstrating the same effects as the scroll compressor 10 of example 1 above, in addition to the effects of examples 2 and 3.
It should be noted that the present invention is not limited to the examples, provided that the actions and effects of the present invention are demonstrated.
For example, the scroll compressors 10, 200, 300 are not limited to horizontal electric compressors, and may equally be configured so that the drive shaft 51 is driven by means of an external motive power source. For example, it is also possible to employ a belt-driven scroll compressor in which engine power is transmitted by a belt to a pulley provided on the drive shaft 51.
The exemplary scroll compressors 10, 200, 300 from any two or more of the examples may be combined.

[Industrial Applicability]

The scroll compressors 10, 200, 300 according to the present invention are suitable for use in a refrigeration cycle of a vehicle air conditioning device.

[Description of Reference Symbols]

10, 200, 300... Scroll compressor
20... Housing
30... Partition member
31a... Flat face (sliding support face)
60... Scroll compression mechanism
70... Fixed scroll
80... Movable scroll
81... Movable plate
81b... Plate face on opposite side to movable spiral wall
82... Movable spiral wall
111... Sliding face
112... Retreat face
120... Anti-rotation mechanism
130... Ring mating portion
131... Inner circumferential surface
132... Bottom face
133... Opening end of ring mating portion
140, 240, 340... Ring
141... Outer circumferential surface
142... First end face
143... Second end face (one axial end of inner circumferential surface)
144... Inner circumferential surface
145, 245... Retreat portion (circumferential surface)
145b... Boundary
150... Anti-rotation pin
160... Reverse-assembly preventing portion
245a... Cylindrical surface

Claims

A scroll compressor comprising: a housing (20); a partition member (30) fixed inside the housing (20); an accommodating space (25) defined by the partition member (30) inside the housing (20); a fixed scroll (70) and a movable scroll (80) accommodated in combination inside the accommodating space (25); and an anti-rotation mechanism (120) for preventing rotation of the movable scroll (80) on itself, characterized in that
the movable scroll (80) comprises a disc-shaped movable plate (81) and a movable spiral wall (82) standing upright from the movable plate (81),

a plate face (81b) on the opposite side of the movable plate (81) to the movable spiral wall (82) has an opposing face (81b) facing a flat face (31a) of the partition member (30),

the opposing face (81b) comprises: an annular sliding face (111) which is provided on the outermost circumference and is capable of sliding in relation to the flat face (31a) of the partition member (30); and a retreat face (112) positioned radially inside the sliding face (111) and at a predetermined depth from the sliding face (111),

the anti-rotation mechanism (120) comprises: ring mating portions (130) indented from the retreat face (112) along a direction orthogonal to the sliding face (111) of the movable scroll (80); cylindrical rings (140; 240; 340) mated with a clearance fit in relation to the ring mating portions (130); and anti-rotation pins (150) extending from the flat face (31a) of the partition member (30) into the rings (140; 240; 340) so as to be capable of contacting an inner circumferential surface (144) of the rings (140; 240; 340), and

the rings (140; 240; 340) have a first end face (142) disposed on a far side of the ring mating portions (130), and a second end face (143) on the opposite side to the first end face (142) in the axial direction, and a retreat portion (145, 245) that does not contact the anti-rotation pins (150) is provided along the whole circumference on at least the second end face (143) side of the inner circumferential surface (144).
The scroll compressor as claimed in claim 1, characterized in that the ring mating portions (130) have a bottom face (132) facing the first end face (142) of the rings (140; 240; 340),
the retreat portion (145, 245) is configured by a circumferential surface (145; 245) positioned radially outward from the inner circumferential surface (144) along the whole circumference of the inner circumferential surface (144) of the rings (140; 240; 340), and

in a state in which the first end face (142) of the rings (140; 240; 340) is touching the bottom face (132) of the ring mating portions (130), a boundary (145b) between the retreat portion (145; 245) and the inner circumferential surface (144) is positioned further to the bottom face (132) side of the ring mating portions (130) than an opening-side edge (135) of the inner circumferential surface (131) of the ring mating portions (130).
The scroll compressor as claimed in claim 2, characterized in that, in a state in which the second end face (143) of the rings (140; 240; 340) is touching the flat face (31a) of the partition member (30), the boundary (145b) is positioned further to the bottom face (132) side of the ring mating portions (130) than the opening-side edge (135) of the inner circumferential surface (131) of the ring mating portions (130).
The scroll compressor as claimed in claim 1, characterized in that the retreat portion (145) is configured by a tapering surface which decreases in diameter from the second end face (143) toward the far side of the rings (140).
The scroll compressor as claimed in claim 1, characterized in that the retreat portion (245) is configured by a cylindrical surface (245a) of larger diameter than the inner circumferential surface (144) of the rings (240).
The scroll compressor as claimed in claim 1, characterized in that the retreat portion (145; 245) is formed only on the second end face (143) side of the rings (140; 240).
The scroll compressor as claimed in claim 6, characterized in that the rings (140; 240) are provided with a reverse-assembly preventing portion (160) for preventing the rings (140) from being assembled the opposite way round with the ring mating portions (130).
The scroll compressor as claimed in claim 1, characterized in that retreat portions (145; 245) are formed along the whole circumference of the inner circumferential surface (144) of the rings (340) on both axial end faces (142, 143) of the rings (340).