WO2024053541A1

WO2024053541A1 - Scroll compressor

Info

Publication number: WO2024053541A1
Application number: PCT/JP2023/031727
Authority: WO
Inventors: イメドギタリ; 幸生風早
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2022-09-09
Filing date: 2023-08-31
Publication date: 2024-03-14

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

scroll compressor

The present invention relates to a scroll compressor, and particularly to an anti-rotation mechanism that prevents rotation of a movable scroll.

A scroll type compressor is known that is equipped with an anti-rotation mechanism that prevents rotation of the movable scroll without interfering with the orbital movement of the movable scroll relative to the fixed scroll fixed to the housing.

In addition, the rotation prevention mechanism has a plurality of sets of rotation prevention pins (hereinafter also simply referred to as pins) and regulation rings (hereinafter simply referred to as rings). An anti-rotation mechanism) is known.

In the scroll compressor disclosed in Patent Document 1, the movable scroll has a disk-shaped end plate and a spiral wall that stands up from the end plate toward the fixed scroll. An annular sliding surface (referred to as a rib in Patent Document 1) that slides into contact with a force receiving plate fixed to the housing is formed near the outermost periphery of the end surface on the opposite side of the spiral wall of the end plate. There is.

An axial clearance is formed between the surface radially inside this sliding surface and the force receiving plate. In other words, the surface radially inside the sliding surface (hereinafter referred to as the "retreat surface") is located with a step that becomes lower from the sliding surface toward the spiral wall. This "retreat surface" is formed with a plurality of bottomed recesses (corresponding to ring fitting parts) that are evenly arranged along a predetermined pitch circle. A ring that engages with a pin fixed to the housing fits into this recess. There is sufficient clearance between the outer circumferential surface of the plurality of pins and the inner circumferential surface of the plurality of rings so that the movable scroll can revolve at a predetermined turning radius, and the plurality of pins are connected to the plurality of rings. By engaging with the movable scroll, rotation (rotation) of the movable scroll is prevented, thereby forming a well-known rotation prevention mechanism.

When the movable scroll revolves around the center of the drive shaft at a predetermined turning radius due to rotation of the drive shaft, the volume of the compression chamber formed between the spiral wall of the movable scroll and the spiral wall of the fixed scroll becomes smaller. As a result, the pressure of the refrigerant trapped in the compression chamber increases as it gets closer to the center, and this pressure creates a force in the thrust direction that attempts to separate the movable scroll from the fixed scroll, and a rotational torque that causes the movable scroll to rotate (rotate) itself. Acts on movable scroll. The former force is received by a thrust plate (force receiving plate). On the other hand, the latter rotational torque is received by the pin via the ring, thereby preventing the movable scroll from rotating.

In the invention disclosed in Patent Document 1, the length of the ring is longer than the depth of the recess. Further, as mentioned in Patent Document 1 as a prior art, a configuration in which the length of the ring is shorter than the depth of the recess is also known.

In these conventional anti-rotation mechanisms, the fitting between the ring and the recess is preferably not a press fit but a so-called clearance fit with a slight clearance. According to the configuration in which the ring is mounted in the recess by a clearance fit, the ring is fitted into the recess without being press-fitted, and therefore, the possibility of deformation of the movable scroll or the housing due to press-fitting can be eliminated.

By the way, since one side of the pin is press-fitted into the housing and the other side is engaged with the ring, the pin receives the load from the ring as a so-called cantilever beam. For this reason, the pin is elastically deformed by the force from the ring, and the tip side of the pin deforms to escape from the ring, whereas the side of the pin near the press-fit part with the housing deforms less and the force from the ring is reduced. Easy to concentrate. Additionally, due to the accumulation of manufacturing errors in multiple mechanical parts, the contact between the ring and pin may not be an ideal line contact, and the inner circumferential surface on the near side or the inner circumferential side of the ring may come into point contact with the pin. .

Special Publication No. 2017-532495

In the conventional configuration described above, since the length of the ring is longer than the depth of the recess (ring fitting portion), the front end surface of the ring protrudes from the recess formation surface of the retraction surface. Furthermore, even if the length of the ring is shorter than the depth of the recess, the ring that constitutes the anti-rotation mechanism is loosely fitted into the recess, so vibrations from compressor operation or friction with the pin may cause the ring to move in the axial direction of the recess. It is possible that the retraction surface may move and protrude from the recess forming surface.

When the front end surface of the ring protrudes from the recess in this way, if the front end of the ring's inner peripheral surface is pushed by the pin as described above, the point of application of the load from the pin to the ring will be in the recess. Therefore, there is a risk that the ring will tilt within the range of the clearance with the recess, which is a so-called tilting phenomenon of the ring with respect to the recess.

When such a tilting phenomenon occurs, there is a risk that the posture of the ring within the recess becomes unstable, causing vibration, or that the ring and thrust plate come into partial contact, causing wear of the thrust plate and noise.

The present invention has been made in order to solve the above-mentioned problems, and aims to provide a technique that can prevent the occurrence of a tilting phenomenon of a ring with respect to a ring fitting part in a pin-and-ring type rotation prevention mechanism. Take it as a challenge.

In the following description, reference numerals in the accompanying drawings will be added in parentheses in order to facilitate understanding of the present invention, but the present invention is not thereby limited to the illustrated form.

According to the present invention, there is provided a housing (20), a partition member (30) fixed within the housing (20), and a storage space defined within the housing (20) by the partition member (30). 25), a fixed scroll (70) and a movable scroll (80) that are housed in combination in the housing space (25), and a rotation prevention mechanism (120) that prevents rotation of the movable scroll (80). and
The movable scroll (80) includes a disc-shaped movable plate (81) and a movable spiral wall (82) standing from the movable plate (81),
A plate surface (81b) of the movable plate (81) opposite to the movable spiral wall (82) has an opposing surface (81b) that faces the flat surface (31a) of the partition member (30). ,
The opposing surface (81b) is provided at the outermost periphery and includes an annular sliding surface (111) that is slidable on the flat surface (31a) of the partition member (30), and the sliding surface (111). ) and a retraction surface (112) located on the radially inner side of the sliding surface (111) and at a predetermined depth from the sliding surface (111);
The rotation prevention mechanism (120) includes a ring fitting portion (130) recessed from the retraction surface (112) in a direction perpendicular to the sliding surface (111) of the movable scroll (80), and A cylindrical ring (140; 240; 340) fitted with a loose fit into the fitting part (130) and a ring (140; 240; 340) so as to be able to contact the inner peripheral surface (144) and an anti-rotation pin (150) extending from the flat surface (31a) of the partition member (30) into the ring (140; 240; 340),
The ring (140; 240; 340) has a first end surface (142) located on the back side of the ring fitting part (130), and a second end surface (142) that is axially opposite to the first end surface (142). a recessed portion (145, 245) having an end surface (143) and extending over the entire circumference at least on the second end surface (143) side of the inner peripheral surface (144) and not coming into contact with the rotation prevention pin (150); Provided is a scroll compressor characterized in that it is provided with.

In this way, the ring is loosely fitted to the inner circumferential surface of the ring fitting portion. Therefore, there is a small gap (clearance) between the inner circumferential surface of the ring fitting portion and the outer circumferential surface of the ring. However, a recessed portion is formed on the inner peripheral surface of the ring. Therefore, the force transmission position of the anti-rotation pin and the ring can be moved away from the end face of the ring, thereby preventing the ring from tilting relative to the ring fitting portion.

Preferably, the ring fitting part (130) has a bottom surface (132) facing the first end surface (142) of the ring (140; 240; 340),
The recessed portion (145; 245) extends over the entire circumference of the inner circumferential surface (144) of the ring (140; 240; 145; 245),
When the first end surface (142) of the ring (140; 240; 340) is in contact with the bottom surface (132) of the ring fitting portion (130), the recess portion (145; 245) and the inner The boundary (145b) with the circumferential surface (144) is closer to the opening side edge (135) of the inner circumferential surface (131) of the ring fitting portion (130) than the edge (135) on the opening side of the inner circumferential surface (131) of the ring fitting portion (130). It is located on the bottom (132) side.

More preferably, in a state where the second end surface (143) of the ring (140; 240; 340) is in contact with the flat surface (31a) of the partition member (30), the boundary (145b) is It is located closer to the bottom surface (132) of the ring fitting portion (130) than the edge (135) on the opening side of the inner peripheral surface (131) of the ring fitting portion (130).

Preferably, the recessed portion (145) is formed by a tapered surface of the ring (140) whose diameter decreases toward the back from the second end surface (143).

As another preferable example, the retraction portion (245) is configured by a cylindrical surface (245a) having a larger diameter than the inner circumferential surface (144) of the ring (240).

Preferably, the recessed portion (145; 245) is formed only on the second end surface (143) side of the ring (140; 240).

More preferably, the ring (140; 240) is provided with a reverse assembly prevention part (160) that prevents the ring (140) from being assembled in the opposite direction to the ring fitting part (130). There is.

As another preferable example, the recessed portion (145, 245) is provided on both end surfaces (142, 143) of the ring (340) in the axial direction, all around the inner peripheral surface (144) of the ring (340). It is formed over a period of time.

According to the present invention, it is possible to prevent the occurrence of a tilting phenomenon of the ring with respect to the ring fitting portion in a pin-and-ring type rotation prevention mechanism.

1 is a sectional view of a scroll compressor according to Example 1. FIG. FIG. 2 is an enlarged view of part 2 of FIG. 1; FIG. 3 is a perspective view of the movable scroll shown in FIG. 2 when viewed from the fixed member side. 3 is an enlarged sectional view of the rotation prevention mechanism shown in FIG. 2. FIG. 5 is an exploded view of the rotation prevention mechanism shown in FIG. 4. FIG. 6A is an explanatory diagram of the rotation prevention mechanism in a state where the ring shown in FIG. 2 is in contact with the bottom surface of the ring fitting portion, and FIG. 6B is an explanatory diagram of the rotation prevention mechanism in a state where the ring shown in FIG. 2 is separated from the bottom surface of the ring fitting portion. It is an explanatory view of a rotation prevention mechanism. FIG. 3 is a cross-sectional view of a ring of a rotation prevention mechanism of a scroll compressor according to a second embodiment. FIG. 8A is an explanatory diagram of a configuration in which a ring of a rotation prevention mechanism for a scroll compressor according to Embodiment 3 is provided with tapered recessed portions on both end surfaces, and FIG. 8B is an explanatory diagram of a configuration of a rotation prevention mechanism for a scroll compressor according to Example 3. An explanatory diagram of a configuration in which a ring has a cylindrical retraction portion on both end surfaces, and FIG. 8C is an explanatory diagram of a configuration in which a ring has a cylindrical retraction portion on one end surface and a tapered shape on the other end surface of the ring of a rotation prevention mechanism for a scroll compressor according to Example 3. FIG. 8D is an explanatory diagram of a configuration provided with a retraction portion, and FIG. 8D is a configuration in which a ring of a rotation prevention mechanism for a scroll compressor according to Embodiment 3 has a tapered retraction portion on one end surface and a cylindrical retraction portion on the other end surface. FIG.

Embodiments of the present invention will be described below based on the accompanying drawings. Note that the form shown in the attached drawings is an example of the present invention, and the present invention is not limited to this form.

<Example 1>
A scroll compressor 10 according to a first embodiment will be described with reference to FIGS. 1 to 6.

As shown in FIG. 1, the scroll compressor 10 is suitable for use in a refrigeration cycle that uses refrigerant as a working fluid, and is used, for example, in a refrigeration cycle of an automobile air conditioner. Note that the use of the scroll compressor 10 is not limited.

The scroll compressor 10 includes, for example, a housing 20 that can be installed horizontally, a motor 40 housed in the housing 20, an inverter 45 housed in the housing 20 to drive and control the motor 40, and an inverter 45 housed in the housing 20. and a scroll-type compression mechanism 60 driven by a motor 40.

The housing 20 includes, for example, a first housing 21 having a cylindrical shape with a bottom, and a second housing 22 (head member 22) that closes one opening of the first housing 21.

The first housing 21 has one end closed by the bottom wall 23 and the other end completely open. This opening is closed by a head member 22 that can be opened and closed. The inside of the first housing 21 is partitioned by a partition member 30 into a first storage chamber 24 on the bottom wall 23 side and a second storage chamber 25 on the open side closed by the head member 22.

Hereinafter, the first storage chamber 24 may be referred to as the "low pressure chamber 24." The second storage chamber 25 is a storage space defined by the housing 20 and a partition member 30 fixed within the housing 20. Hereinafter, this second storage chamber 25 may be referred to as "storage space 25."

The partition member 30 is a disc-shaped member, and both relative rotation and relative movement in the axial direction with respect to the first housing 21 are restricted. Hereinafter, the partition member 30 may be referred to as the "fixing member 30."

This partition member 30 is composed of a disk-shaped partition plate portion 31 and a support portion 32 that is integrally provided at the center of this partition plate portion 31. The partition member 30 has a plurality of suction holes 33 that communicate the first storage chamber 24 and the second storage chamber 25.

A motor 40 is stored in the first storage chamber 24. A scroll type compression mechanism 60 (hereinafter also simply referred to as compression mechanism 60) is housed in the second storage chamber 25. Note that the partition member 30 can be considered as an element constituting the compression mechanism 60. That is, even if the partition wall 34 is considered to be part of the compression mechanism 60, it does not depart from the spirit of the present invention.

Furthermore, the first housing 21 has a suction port 26 that sucks refrigerant into the first storage chamber 24 from the outside. The head member 22 includes a discharge chamber 27 from which refrigerant compressed by the compression mechanism 60 is discharged, an oil separation chamber 28 which separates oil from the refrigerant led from the discharge chamber 27, and an oil separation chamber 28 which separates oil from the refrigerant introduced from the discharge chamber 27. It has a discharge port 29 for discharging the separated and removed gaseous refrigerant to the outside. Further, the first housing 21 includes an inverter chamber 21b that accommodates the inverter 45.

The motor 40 includes a rotor 41 whose rotation center is in the longitudinal direction of the housing 20 and an annular stator 42 surrounding the rotor 52, and drives the compression mechanism 60. The stator 42 is fixed to the inner peripheral surface 21a of the first housing 21.

A drive shaft 51 (output shaft 51) is fixed to the rotor 41. This drive shaft 51 also serves as the output shaft of the motor 40. The rotor 41 is rotatable with respect to the center line CL1 of the drive shaft 51.

The drive shaft 51 passes through the partition member 30 from the first storage chamber 24 to the second storage chamber 25 , and connects a first bearing 52 provided on the support portion 32 of the partition member 30 and the bottom wall 23 of the housing 20 . It is rotatably supported by a second bearing 53 provided in the. Further, the drive shaft 51 has an eccentric shaft 54 on one end surface passing through the partition member 30. The eccentric shaft 54 extends from one end surface of the drive shaft 51 toward the compression mechanism 60 and is parallel to the drive shaft 51 . The 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 fitted onto the eccentric shaft 54. A counterweight 56 is integrally provided in a part of the bush 55 and projects from the bush 55 in the radial direction.

The compression mechanism 60 has a pair of

scroll members

70 and 80 housed in the second storage chamber 25.

The fixed scroll 70 has a flat disk-shaped fixed plate 71, a cylindrical outer peripheral wall 72, and a spiral-shaped fixed spiral wall 73. The fixed plate 71 has a discharge hole 74 in the central portion. The outer peripheral wall 72 is a cylindrical portion that stands integrally over the entire circumference from the outer edge of one plate surface 71a (the surface 71a facing the partition member 30 side) of the fixed plate 71 toward the partition member 30 side. A refrigerant suction port 75 is formed in the outer peripheral wall 72 for sucking refrigerant from the radially outer side to the inner side. The fixed spiral wall 73 is integrally erected from one plate surface 71a of the fixed plate 71 toward the partition member 30 side. The fixed scroll 70 is supported so as not to be relatively rotatable between the head member 22 and the partition member 30 so that the fixed plate 71 is oriented orthogonal to the center line CL2 of the eccentric shaft 54.

The movable scroll 80 has a flat disk-shaped movable plate 81 and a spiral-shaped movable spiral wall 82. The outer diameter of the movable plate 81 is formed to a size that does not interfere with the movable scroll 80 inside the outer circumferential wall 72 of the fixed scroll 70 even if the movable scroll 80 revolves around a predetermined eccentric radius. The movable spiral wall 82 is integrally erected from a surface 81a (hereinafter referred to as "first plate surface 81a") opposite to the plate surface 71a of the fixed plate 71 of the movable plate 81 toward the plate surface 71a of the fixed plate 71. ing. A third bearing 57 is mounted at the center of a plate surface 81b (hereinafter referred to as "second plate surface 81b") opposite to the first plate surface 81a. The outer circumferential surface of the bush 55 described above is fitted into the inner circumferential surface of the third bearing 57 .

By meshing the fixed spiral wall 73 and the movable spiral wall 82, a compression chamber 83 surrounded by each

plate

71, 81 and each

spiral wall

73, 82 is formed.

As shown in FIGS. 1 and 2, as the drive shaft 51 rotates, the center of the movable scroll 80 is moved to a preset eccentric radius via the bush 55 fitted to the eccentric shaft 54 and the third bearing 57. It can revolve (eccentric rotation) at .

Here, the "preset eccentric radius" is not a fixed value, but includes one that is automatically adjusted so that the amount of eccentricity of the movable scroll 80 becomes the set ideal amount of eccentricity. For example, when the movable scroll 80 revolves, a self-aligning function can be provided by fitting the eccentric shaft 54 and the bush 55 so that the

spiral walls

73 and 82 are in optimal contact with each other.

As the drive shaft 51 rotates as described above, the movable scroll 80 revolves. As a result, the refrigerant sucked from the suction port 26 passes through the gap between the motor 40 in the low-pressure chamber 24, passes through the suction hole 33 of the partition member 30, passes through the refrigerant suction port 75 of the fixed scroll 70, and enters the compression chamber. 83. As the movable scroll 80 revolves, the compression chamber 83 moves toward the center while gradually decreasing its internal volume. Thereby, the refrigerant in the compression chamber 83 is compressed. When the pressure in the compression chamber 83 that has moved to the center increases to exceed the pressure in the discharge chamber 27, the discharge valve 91 opens due to the pressure difference, and the refrigerant in the compression chamber 83 passes through the discharge hole 74 to the discharge chamber 27. flows into. The refrigerant in the discharge chamber 27 is discharged outward from the discharge port 29 via the oil separation chamber 28 .

Next, the relationship between the partition plate portion 31 of the partition member 30 and the movable scroll 80 will be described in detail.

As shown in FIGS. 1 and 2, one end surface 31a of the partition plate portion 31 faces the second storage chamber 25 side. This one end surface 31a can support the sliding movement of the movable scroll 80. Hereinafter, this one end surface 31a may be referred to as a "flat surface 31a" or a "sliding support surface 31a." When the second end surface 81b of the movable scroll 80 is in contact with the flat surface 31a, the center line CL3 of the movable scroll is perpendicular to the flat surface 31a.

It is preferable that a thrust member 101 capable of receiving a thrust load due to a compression reaction force is interposed between the flat surface 31a of the partition plate portion 31 and the second plate surface 81b of the movable scroll 80. This thrust member 101 is constituted by, for example, a thin plate-like annular thrust race. Hereinafter, the thrust member 101 will be referred to as "thrust race 101" as appropriate. The thrust race 101 is made of a material with excellent wear resistance, and can be sandwiched between the flat surface 31a of the partition plate portion 31 and the end surface of the cylindrical outer circumferential wall 72 of the fixed scroll 70.

As shown in FIGS. 3 and 4, the second plate surface 81b (opposing surface 81b) is provided at the outermost periphery and has an annular sliding surface 111 that is slidable on the flat surface 31a of the partition member 30. , has a retraction surface 112 located radially inside of this sliding surface 111 and at a predetermined depth. Here, the "predetermined depth" may be a specific constant depth or a depth spanning a specific range, but does not include zero.

Further, the retracting surface 112 has an annular edge surface 113 protruding from the retracting surface 112 on the radially inner side thereof.

The center line CL3 of the movable scroll 80 is the center of the movable plate 81 and is orthogonal to the sliding surface 111.

As shown in FIG. 4, the sliding surface 111 of the movable scroll 80 is in close sliding contact with the thrust race 101. When the sliding surface 111 is in close contact with the thrust race 101, the space 114 on the radially inner side of the place where the thrust race 101 and the sliding surface 111 are in close contact can be used as an oil sump space, and the space 114 can be used as an oil reservoir space. It is possible to retain lubricating oil supplied via a supply path (not shown). The lubricating oil retained in the space 114 lubricates the sliding area between the sliding surface 111 of the movable scroll 80 and the thrust race 102 and the contact area between the ring 140 and the pin 150, which will be described later, to suppress sliding resistance. It is possible to suppress wear and tear.

Note that the presence or absence of the thrust race 101 is optional. In the first embodiment, the sliding surface 111 of the movable scroll 80 is configured to be in close sliding contact with the flat surface 31a of the partition plate portion 31, either directly or indirectly via the thrust race 101. Bye. In the description of the first embodiment, when it is said that the sliding surface 111 of the movable scroll 80 is in sliding contact with the flat surface 31a of the partition plate part 31, it is said that the sliding surface 111 of the movable scroll 80 is in sliding contact with the flat surface 31a of the partition plate part 31 directly or through the thrust race 101. This shall include a structure in which there is indirect sliding contact.

As shown in FIGS. 3 and 4, the scroll compressor 10 includes a rotation prevention mechanism 120 that prevents the movable scroll 80 from rotating. This rotation prevention mechanism 120 includes a plurality of ring fitting portions 130 that are recessed from the retraction surface 112 along the center line CL3 of the movable scroll 80 (along the direction orthogonal to the sliding surface 111), and these plurality of rings. A plurality of rings 140 (also referred to as regulation rings 140) each fitted into the fitting portion 130, and a plurality of pins 150 (rotation prevention pins) each extending into the plurality of rings 140 from the flat surface 31a of the partition member 30. 150).

As shown in FIG. 5, the ring fitting portion 130 has a bottomed hole configuration, and is composed of an inner circumferential surface 131 and a bottom surface 132. An inner circumferential surface 131 of the ring fitting portion 130 is formed in a perfect circular shape orthogonal to the sliding surface 111 and is open to the retracting surface 112. It is preferable that the open end 133 of the ring fitting part 130 has a tapered chamfered part 134 for easily inserting the ring 140 into the ring fitting part 130. The corner 135 between the inner circumferential surface 131 of the ring fitting portion 130 and the chamfered portion 134 is referred to as the "opening side edge 135 of the inner circumferential surface 131."

Note that the presence or absence of the chamfered portion 134 is optional. If the chamfered portion 134 is not provided, the edge 135 on the opening side of the inner peripheral surface 131 will match the opening end 133 of the ring fitting portion 130.

The bottom surface 132 is a flat surface parallel to the sliding surface 111. Furthermore, in order to reduce the weight of the movable scroll 80 and the number of parts to be machined, a recessed portion 136 may be formed that is recessed from the bottom surface 132 and has a diameter smaller than the inner circumferential surface 131 of the ring fitting portion 130.

The depth (first depth) from the sliding surface 111 to the opening-side edge 135 of the inner circumferential surface 131 of the ring fitting portion 130 is D1. The depth from this edge 135 to the bottom surface 132 (second depth) is D2, which is greater than the first depth D1.

As shown in FIG. 5, the ring 140 is a perfectly circular cylindrical member that passes through the ring 140, and is fitted into the ring fitting portion 130 with a "loose fit" (loosely fitted). The degree of clearance fit is such that the outer circumferential surface 141 of the ring 140 fitted to the inner circumferential surface 131 of the ring fitting part 130 can be slid in the axial direction, rotated, and removed. ) is preferably small. The thickness of the ring 140 is uniform in the circumferential direction.

When the ring 140 is fitted into the ring fitting part 130, the end surface 142 facing the bottom surface 132 of the ring fitting part 130 is defined as a "first end surface 142", and the ring 140 has an axis relative to the first end surface 142. The end surface 143 on the opposite side is referred to as a "second end surface 143." The first end surface 142 and the second end surface 143 are parallel to each other and also parallel to the bottom surface 132 of the ring fitting part 130.

As shown in FIG. 4, the pin 150 is constituted by a cylinder with a perfect circular cross section, and is located parallel to the inner circumferential surface 144 of the ring 140. One end portion 151 of this pin 150 is fixed to a pin hole 34 formed in the partition member 30 by press fitting. That is, the pin 150 has a so-called cantilever structure in which one end 151 is fixed to the partition member 30 and the other end 152 is a free end.

The plurality of pins 150 are arranged such that the outer circumferential surface of the other end portion 152 of each pin can come into contact with the inner circumferential surface 144 of the corresponding ring 140. The clearance between the inner diameter of the ring 140 and the outer diameter of the other end 152 of the pin 150 is larger than the amount of movement of the movable scroll 80 (twice the eccentric radius). By linearly contacting the plurality of rings 140 and the corresponding plurality of pins 150 in sequence, it is possible to prevent the movable scroll 80 from rotating and allow it to swing along the center line CL3.

As shown in FIGS. 4 and 5, the ring 140 has a recessed portion 145 that does not come into contact with the pin 150 over the entire circumference at least on the one axial end 143 side (second end surface 143 side) of the inner peripheral surface 144. It is provided.

For example, as shown in FIG. 5, the recessed portion 145 is formed only on the second end surface 143 side of the ring 140. The retracting portion 145 extends over the entire circumference of the inner circumferential surface 144 of the ring 140 and is constituted by a circumferential surface located radially outward from the inner circumferential surface 144 . The recessed portion 145 will be referred to as "surrounding surface 145" as appropriate.

This circumferential surface 145 (retreat portion 145) is a surface obtained by rotating a line connecting a predetermined start point 145a and end point 145b of the ring 140 in the axial direction along the center line RL of the ring 140. The starting point 145a is on the second end surface 143 of the ring 140 and is a predetermined amount radially outward from the inner circumferential surface 144 of the ring 140. The end point 145b is on the inner circumferential surface 144 of the ring 140, and is located a predetermined distance away from the second end surface 143 toward the first side end surface 142. This end point 145b is located at the boundary between the inner circumferential surface 144 and the circumferential surface 145 (retreat portion 145) of the ring 140. This end point 145b is appropriately referred to as a "boundary 145b."

More specifically, this circumferential surface 145 (retreat portion 145) is tapered so that the diameter of the ring 140 decreases from the axial end 143 (second end surface 143) toward the back side (first end surface 142 side). Consists of a tapered surface. In this way, the retracting portion 145 is formed of a circumferential surface (a tapered surface) located radially outward from the inner circumferential surface 144 of the ring 140 over the entire circumference. When the ring 140 is viewed from the outer circumferential surface 141 side, the angle θ1 between the inner circumferential surface 144 and the recessed portion 145 is an obtuse angle.

The length in the axial direction from the starting point 145a to the ending point 145b (the length of the retracting portion 145) is L1. The axial length (straight length) from the end point 145b to the first end surface 142 of the ring 140 is L2, which is longer than the length L1 of the recessed portion 145. By setting the straight length L2 long, the pin 150 (see FIG. 4) can be stably brought into line contact with the inner peripheral surface 144 of the ring 140.

As shown in FIG. 6A, when the first end surface 142 of the ring 140 is in contact with the bottom surface 132 of the ring fitting part 130, the boundary 145b (the end point 145b of the retracted part 145) is inside the ring fitting part 130. It is located closer to the bottom surface 132 of the ring fitting portion 130 than the edge 135 of the peripheral surface 131 on the opening side. In other words, the distance L2 (straight length L2) from the bottom surface 132 of the ring fitting part 130 to the boundary 145b is the distance D2 ( the second depth D2). Even in this state, the second end surface 143 of the ring 140 protrudes from the ring fitting portion 130 toward the partition member 30 side.

As shown in FIG. 6B, when the second end surface 143 of the ring 140 is in contact with the flat surface 31a of the partition member 30, the boundary 145b is the edge 135 on the opening side of the inner peripheral surface 131 of the ring fitting part 130. It is located closer to the bottom surface 132 of the ring fitting portion 130 than the ring fitting portion 130 . In other words, the distance L1 from the flat surface 31a to the boundary 145b (the length L1 of the retracted portion 145) is the distance D1 from the flat surface 31a to the edge 135 on the opening side of the inner peripheral surface 131 of the ring fitting portion 130 (the first depth D1).

As shown in FIGS. 5 and 6A, the ring 140 is provided with a reverse assembly prevention portion 160 that prevents the ring 140 from being assembled in the opposite direction to the ring fitting portion 130. For example, the reverse assembly prevention portion 160 is constituted by a small protrusion 161 that protrudes radially outward from the outer peripheral surface 141 of the ring 140. This protrusion 161 includes a flange formed on the outer peripheral surface 141 over the entire circumference. When the first end surface 142 of the ring 140 is in contact with the bottom surface 132 of the ring fitting part 130, the protrusion 161 is located at a position where it does not contact the retraction surface 112 or the chamfered part 134, that is, the second end surface 142 of the ring 140. It is located near.

Therefore, as shown in FIG. 6A, when the ring 140 is properly assembled to the ring fitting part 130, the protrusion 161 does not interfere with the retraction surface 112 or the chamfered part 134. On the other hand, if an attempt is made to assemble the ring 140 in the opposite direction to the ring fitting portion 130, the protrusion 161 interferes with the retraction surface 112 or the chamfered portion 134, making it impossible to assemble the ring 140. Therefore, it is possible to prevent the ring 140 from being assembled in the opposite direction to the ring fitting part 130.

Next, the principle of preventing the occurrence of a tilting phenomenon of the ring 140 with respect to the ring fitting portion 130 when the movable scroll 80 makes a swinging motion will be explained.

As shown in FIG. 4, the pin 150 has a cantilever structure with one end 151 fixed to the partition member 30. For example, when the movable scroll 80 rotates in the direction of arrow Ru, the inner peripheral surface 144 of the ring 140 comes into line contact with the other end 152 (free end 152) of the pin 150. The other end 152 receives the load acting from the inner peripheral surface 144 of the ring 140.

Due to this load, the other end 152 of the pin 150 can be elastically deformed, for example, as shown by the imaginary line. By elastically deforming, the pin 150 contacts only the boundary 145b (the end point 145b of the retracted portion 145). Boundary 145b receives reaction force fr from pin 150. The direction of this reaction force fr is opposite to the direction in which the movable scroll 80 rotates (the direction of the arrow Ru). The ring 140 that has received this reaction force fr tends to fall in the radial direction of the ring fitting part 130 (in the direction of the arrow Tr) using the edge 135 on the opening side of the ring fitting part 130 as a fulcrum. However, in this state, the outer circumferential surface 141 of the ring 140 is in contact with the inner circumferential surface 131 of the ring fitting portion 130 in the direction in which the reaction force fr acts.

The ring 140 can be displaced in the axial direction with respect to the ring fitting part 130 in a range from a position in contact with the bottom surface 132 shown in FIG. 6A to a position in contact with the flat surface 31a shown in FIG. 6B. However, no matter where the ring 140 is located in the axial direction with respect to the ring fitting part 130, the boundary 145b is located closer to the bottom surface 132 of the ring fitting part 130 than the edge 135 on the opening side. . That is, the force transmission position 145b (boundary 145b) between the pin 150 and the ring 140 is away from the end surface 143 (second end surface 143) of the ring 140 toward the bottom surface 132 side. The ring 140 is supported by the inner circumferential surface 131 of the ring fitting part 130 so as not to fall in the radial direction of the ring fitting part 130 (in the direction of arrow Tr in FIG. 4). As a result, it is possible to prevent the ring 140 from tilting relative to the ring fitting portion 130.

The description of Example 1 above is summarized as follows.

As shown in FIG. 1, the scroll compressor 10 includes a housing 20, a partition member 30 fixed within the housing 20, and a storage space 25 (a second A storage chamber 25), a fixed scroll 70 and a movable scroll 80 that are combined and housed in the storage space 25, and a rotation prevention mechanism 120 that prevents the movable scroll 80 from rotating. The movable scroll 80 includes a disk-shaped movable plate 81 and a movable spiral wall 82 erected from the movable plate 81. A plate surface 81b (second plate surface 81b) of the movable plate 81 opposite to the movable spiral wall 82 side has an opposing surface 81b that faces the flat surface 31a of the partition member 30.

As shown in FIGS. 3 and 4, the opposing surface 81b includes an annular sliding surface 111 that is provided on the outermost periphery and is slidable on the flat surface 31a of the partition member 30, and a diameter of the sliding surface 111. It has a retraction surface 112 located on the inside in the direction and at a predetermined depth from the sliding surface 111.

As shown in FIG. 4, the rotation prevention mechanism 120 has a ring fitting portion 130 that is recessed from the retraction surface 112 in a direction perpendicular to the sliding surface 111 of the movable scroll 80, and A cylindrical ring 140 fitted with a loose fit and an anti-rotation pin 150 extending into the ring 140 from the flat surface 31a of the partition member 30 so as to be able to contact the inner peripheral surface 144 of the ring 140. We are prepared. The ring 140 has a first end surface 142 disposed on the back side of the ring fitting part 130 and a second end surface 143 that is axially opposite to the first end surface 142. A recessed portion 145 that does not come into contact with the anti-rotation pin 150 is provided on the second end surface 143 side over the entire circumference.

The ring 140 is fitted into the inner circumferential surface 131 of the ring fitting part 130 in a loose fit. Therefore, there is a gap (clearance) between the inner peripheral surface 131 of the ring fitting part 130 and the outer peripheral surface 141 of the ring 140. However, a recessed portion 145 is formed on the inner circumferential surface 144 of the ring 140. Therefore, the force transmission position of the anti-rotation pin 150 and the ring 140 can be moved away from the end surface 143 (second end surface 143) of the ring 140, thereby preventing the ring 140 from tilting relative to the ring fitting portion 130.

As shown in FIG. 4, the ring fitting part 130 has a bottom surface 132 facing the first end surface 142 of the ring 140. The retracting portion 145 extends over the entire circumference of the inner circumferential surface 144 of the ring 140 and is constituted by a circumferential surface (corresponding to the circumferential surface 145) located radially outward from the inner circumferential surface 144.

As shown in FIG. 6A, when the first end surface 142 of the ring 140 is in contact with the bottom surface 132 of the ring fitting part 130, the boundary 145b between the recessed part 145 and the inner peripheral surface 144 It is located closer to the bottom surface 132 of the ring fitting portion 130 than the edge 135 on the opening side of the inner circumferential surface 131 of the ring fitting portion 130 .

In this way, with the first end surface 142 of the ring 140 in contact with the bottom surface 132 of the ring fitting part 130, the boundary 145b between the recessed part 145 and the inner peripheral surface 144 (the end point 145b of the retracted part 145) It is located closer to the bottom surface 132 than the edge 135 on the opening side of the fitting portion 130 . Therefore, since the rotation prevention pin 150 makes point contact only with the boundary 145b between the retracted portion 145 and the inner circumferential surface 144, even if it is pushed by the rotation prevention pin 150, the rotation prevention pin 150 does not reach the ring 140. The point of action is inside the ring fitting part 130. It is possible to prevent the ring 140 from tilting within the clearance range with the ring fitting portion 130, which is a so-called tilting phenomenon of the ring 140 with respect to the ring fitting portion 130.

As shown in FIG. 6B, when the second end surface 143 of the ring 140 is in contact with the flat surface 31a of the partition member 30, the boundary 145b between the recessed portion 145 and the inner circumferential surface 144 is It is located closer to the bottom surface 132 of the ring fitting portion 130 than the edge 135 of the inner peripheral surface 131 on the opening side.

Even if the ring 140 comes out of the ring fitting part 130 to the maximum extent and comes into contact with the flat surface 31a of the partition member 30, the force transmission position 145b (boundary 145b) between the rotation prevention pin 150 and the ring 140 is It is located on the back side of the fitting part 130. Therefore, even if a load is applied from the anti-rotation pin 150 to the boundary 145b, it is possible to prevent the ring 140 from tilting relative to the ring fitting portion 130.

As shown in FIG. 5, the retraction portion 145 is constituted by a tapered surface of the ring 140 whose diameter decreases from the second end surface 143 toward the back side (first end surface 142 side). Therefore, the angle θ formed between the inner circumferential surface 144 of the ring 140 and the recessed portion 145 becomes an obtuse angle. Compared to the case where the angle θ is an acute angle, the contact pressure is reduced when the anti-rotation pin 150 makes point contact with the corner 145b (boundary 145b) between the inner circumferential surface 144 of the ring 140 and the recessed portion 145. be able to. Note that by configuring the boundary 145b to have an arc-shaped cross section, the boundary 145b has a roundness, so that the contact pressure can be further alleviated.

As shown in FIG. 4, the recessed portion 145 is formed only on the second end surface 143 side of the ring 140. Therefore, the recessed portion 145 only needs to be formed on one side of the ring 140. Correspondingly, the straight length L2 (see FIG. 5) at which the ring 140 and the anti-rotation pin 150 are in line contact can be set longer, and as a result, the linear pressure can be reduced.

As shown in FIG. 4, the ring 140 is provided with a reverse assembly prevention part 160 that prevents the ring 140 from being assembled in the opposite direction to the ring fitting part 130. Therefore, it is possible to easily prevent the ring 140 from being attached to the ring fitting portion 130 in the wrong direction due to human error.

<Example 2>
A scroll compressor 200 according to a second embodiment will be described with reference to FIG. 7. FIG. 7 corresponds to FIG. 5 above.

The scroll compressor 200 of the second embodiment is characterized in that the ring 140 of the first embodiment shown in FIGS. 1 to 6 above is replaced with a ring 240 shown in FIG. 7. Other basic configurations are the same as the scroll compressor 10 according to the first embodiment. For parts common to the scroll compressor 10 according to the first embodiment, the reference numerals are used and detailed explanations are omitted.

The ring 240 of the second embodiment is characterized by a recessed portion 245, and the other configuration is the same as the structure of the ring 140 of the first embodiment. The retracting section 245 corresponds to the retracting section 145 of the first embodiment shown in FIG.

This retracting portion 245 extends over the entire circumference of the inner circumferential surface 144 of the ring 240 and is constituted by a circumferential surface located radially outward from the inner circumferential surface 144. The recessed portion 245 may be referred to as a "surrounding surface 245" as appropriate. The position of the start point 145a and the position of the end point 145b (boundary 145b) of this circumferential surface 245 are the same as the positions of the start point 145a and the end point 145b of the circumferential surface 145 of Example 1 shown in FIG. 5 above. This peripheral surface 245 (retreat portion 245) is a surface obtained by rotating a line connecting a predetermined start point 145a and end point 145b of the ring 240 in the axial direction along the center line RL of the ring 140.

The retraction portion 245 is constituted by a cylindrical surface 245a having a larger diameter than the inner circumferential surface 144 of the ring 240. The boundary between the cylindrical surface 245a and the inner circumferential surface 144 is connected directly or indirectly. For example, the retraction portion 245 is configured by a cylindrical surface 245a and a stepped surface 245b at the boundary between the cylindrical surface 245a and the inner circumferential surface 144.

The starting point 145a of the cylindrical surface 245a is the position of the second end surface 143 of the ring 240. The stepped surface 245b (end surface 245b) is an annular surface. The inner periphery of this stepped surface 245b is located at the boundary 145b (boundary 145b) with the inner peripheral surface 144 of the ring 240. This Sakai 145b is the end point 145b. The length L1 and the straight length L2 of the retracted portion 145 are the same as those of the ring 140 of the first embodiment.

In this way, the retraction portion 245 is constituted by a cylindrical surface 245a having a larger diameter than the inner circumferential surface 144 of the ring 240. Since the retraction portion 245 is simply formed into a cylindrical surface 245a, dimensional control is easy.

In addition to the effects of the second embodiment, the scroll compressor 200 according to the second embodiment can exhibit the same effects as the scroll compressor 10 of the first embodiment.

Here, the concept of the peripheral surface 245 of Example 2 will be explained. As shown in FIG. 7, a line segment in the axial direction along the cylindrical surface 245a is referred to as a "first line segment", and a line segment in the radial direction along the stepped surface 245b is referred to as a "second line segment". A "line" is assumed in which a first line segment and a second line segment are connected, and one end of each line segment is connected to a starting point 145a and an ending point 145b. By rotating this line along the center line RL of the ring 140, a peripheral surface 245 with this center line RL as a reference is formed.

In this way, the "line" connecting the starting point 145a and the ending point 145b is not limited to a straight line, but includes a curved line. The starting point 145a and the ending point 145b may be connected by a curve. In short, the feature of the first and second embodiments is that the

rings

140, 240 are provided with a boundary 145b between the inner circumferential surface 144 and the

circumferential surfaces

145, 245, as shown in FIGS. 5 and 7.

<Example 3>
A scroll compressor 300 according to a third embodiment will be described with reference to FIGS. 8A to 8D. 8A to 8D correspond to FIG. 5 above.

The scroll type compressor 300 of the third embodiment includes the ring 140 of the first embodiment shown in FIGS. 1 to 6 and the ring 240 of the second embodiment shown in the second embodiment shown in FIG. It is characterized by being changed to a ring 340 shown in 8D. Other basic configurations are the same as those of the

scroll compressors

10 and 200 according to the first and second embodiments. For parts common to the

scroll type compressors

10 and 200 according to Examples 1 and 2, reference numerals are used and detailed explanations are omitted.

The ring 340 shown in FIG. 8A has the recessed portions 145 of the first embodiment shown in FIG. 5 on both end surfaces 142 and 143 in the axial direction.
The ring 340 shown in FIG. 8B has the recessed portions 245 of the second embodiment shown in FIG. 7 on both end surfaces 142 and 143 in the axial direction.
The ring 340 shown in FIG. 8C has the recessed part 245 of the second embodiment shown in FIG. 7 on the first end face 142, and the retracted part 145 of the first embodiment shown in FIG. have.
The ring 340 shown in FIG. 8D has the retraction portion 145 of the first embodiment shown in FIG. 5 on the first end surface 142, and the retraction portion 245 of the second embodiment shown in FIG. have.

In this way, the recessed

portions

145 and 245 are formed on both end surfaces 142 and 143 of the ring 340 in the axial direction over the entire circumference of the inner peripheral surface 144 of the ring 340. Therefore, even if the ring 340 is assembled in the opposite direction to the ring fitting part 130 (see FIG. 5), it is possible to prevent the ring 340 from tilting relative to the ring fitting part 130.

In addition to the effects of Examples 2 and 3, the scroll compressor 300 according to the third embodiment can exhibit the same effects as the scroll compressor 10 of the first embodiment.

Note that the present invention is not limited to each embodiment as long as the functions and effects of the present invention are achieved.
For example, the

scroll compressors

10, 200, and 300 are not limited to horizontally mounted electric compressors, and may have a configuration in which the drive shaft 51 is driven by an external power source. For example, it is possible to use a belt-driven scroll compressor that transmits engine power to a pulley provided on the drive shaft 51 via a belt.
The scroll compressors 10, 200, and 300 of each embodiment can be combined with any two or more embodiments.

The

scroll compressor

10, 200, 300 of the present invention is suitable for use in a refrigeration cycle of a vehicle air conditioner.

10,200,300 Scroll compressor 20 Housing 30 Partition member 31a Flat surface (sliding support surface)
60 Scroll compression mechanism 70 Fixed scroll 80 Movable scroll 81 Movable plate 81b Plate surface opposite to the movable scroll wall 82 Movable scroll wall 111 Sliding surface 112 Evacuation surface 120 Rotation prevention mechanism 130 Ring fitting portion 131 Inner peripheral surface 132 Bottom surface 133 Open end of ring

fitting part

140, 240, 340 Ring 141 Outer peripheral surface 142 First end surface 143 Second end surface (one end in the axial direction of the inner peripheral surface)
144 Inner

peripheral surface

145, 245 Retraction part (peripheral surface)
145b Boundary 150 Rotation prevention pin 160 Reverse assembly prevention part 245a Cylindrical surface

Claims

a housing (20); a partition member (30) fixed within the housing (20); a storage space (25) defined within the housing (20) by the partition member (30); It includes a fixed scroll (70) and a movable scroll (80) that are combined and housed in the space (25), and a rotation prevention mechanism (120) that prevents rotation of the movable scroll (80),
The movable scroll (80) includes a disc-shaped movable plate (81) and a movable spiral wall (82) standing from the movable plate (81),
A plate surface (81b) of the movable plate (81) opposite to the movable spiral wall (82) has an opposing surface (81b) that faces the flat surface (31a) of the partition member (30). ,
The opposing surface (81b) is provided at the outermost periphery and includes an annular sliding surface (111) that is slidable on the flat surface (31a) of the partition member (30), and the sliding surface (111). ) and a retraction surface (112) located on the radially inner side of the sliding surface (111) and at a predetermined depth from the sliding surface (111);
The rotation prevention mechanism (120) includes a ring fitting portion (130) recessed from the retraction surface (112) in a direction perpendicular to the sliding surface (111) of the movable scroll (80), and A cylindrical ring (140; 240; 340) fitted with a loose fit into the fitting part (130) and a ring (140; 240; 340) so as to be able to contact the inner peripheral surface (144) and an anti-rotation pin (150) extending from the flat surface (31a) of the partition member (30) into the ring (140; 240; 340),
The ring (140; 240; 340) has a first end surface (142) located on the back side of the ring fitting part (130), and a second end surface (142) that is axially opposite to the first end surface (142). a recessed portion (145, 245) having an end surface (143) and extending over the entire circumference at least on the second end surface (143) side of the inner peripheral surface (144) and not coming into contact with the rotation prevention pin (150); is provided,
A scroll compressor characterized by:
The ring fitting part (130) has a bottom surface (132) facing the first end surface (142) of the ring (140; 240; 340),
The recessed portion (145; 245) extends over the entire circumference of the inner circumferential surface (144) of the ring (140; 240; 145; 245),
When the first end surface (142) of the ring (140; 240; 340) is in contact with the bottom surface (132) of the ring fitting portion (130), the recess portion (145; 245) and the inner The boundary (145b) with the circumferential surface (144) is closer to the opening side edge (135) of the inner circumferential surface (131) of the ring fitting portion (130) than the edge (135) on the opening side of the inner circumferential surface (131) of the ring fitting portion (130). The scroll compressor according to claim 1, wherein the scroll compressor is located on the bottom (132) side.
When the second end surface (143) of the ring (140; 240; 340) is in contact with the flat surface (31a) of the partition member (30), the boundary (145b) is located at the ring fitting portion. Claim (130) characterized in that it is located closer to the bottom surface (132) of the ring fitting part (130) than the edge (135) on the opening side of the inner circumferential surface (131). Scroll compressor according to item 2.
2. The retracting portion (145) is configured by a tapered surface of the ring (140) whose diameter decreases toward the back from the second end surface (143). The scroll type compressor described.
The scroll type according to claim 1, wherein the retracting portion (245) is constituted by a cylindrical surface (245a) having a larger diameter than the inner circumferential surface (144) of the ring (240). compressor.
The scroll compressor according to claim 1, wherein the recessed portion (145; 245) is formed only on the second end surface (143) side of the ring (140; 240).
The ring (140; 240) is provided with a reverse assembly prevention part (160) that prevents the ring (140) from being assembled in the opposite direction to the ring fitting part (130). The scroll compressor according to claim 6.
The recessed portion (145; 245) is formed on both axial end surfaces (142, 143) of the ring (340) over the entire circumference of the inner peripheral surface (144) of the ring (340). The scroll compressor according to claim 1, characterized in that: