JP7208364B2 - scroll compressor - Google Patents

Description

The present invention relates to scroll compressors.

2. Description of the Related Art As described in Patent Document 1, scroll compressors that are used in air conditioners, refrigerators, and the like and compress refrigerant are generally known. In this scroll compressor, the refrigerant is compressed by orbiting the orbiting scroll with respect to the fixed scroll.

At present, the use of non-Freon refrigerants is required from the viewpoint of environmental protection, and the demand for compressors using carbon dioxide, which is a natural refrigerant, is increasing.

JP 2009-030514 A

When carbon dioxide is used as the refrigerant, it is necessary to compress the refrigerant to a high pressure, so the components of the compressor must be compatible with high pressure. In addition, there is an increasing demand for large capacity compressors using natural refrigerants. However, simply trying to cope with high pressure and increase the capacity will increase the external dimensions and weight of each component, and the installation space may be restricted.

SUMMARY OF THE INVENTION Accordingly, the present invention provides a compact scroll compressor that can handle high pressures and has a large capacity.

A scroll compressor according to an aspect of the present invention includes a rotating shaft extending along an axis, a motor that rotates the rotating shaft, a scroll compression unit that compresses a refrigerant by rotation of the rotating shaft, the rotating shaft, the A fixed scroll comprising a motor and a housing that accommodates the scroll compression section, the scroll compression section having a fixed end plate fixed to the housing and a fixed wrap projecting from the fixed end plate in the direction of the axis. a swivel end plate provided on the rotating shaft and arranged to face the fixed end plate in the direction of the axis; and a coolant protruding from the swivel end plate toward the fixed end plate together with the fixed wrap. and the fixed end plate and the orbiting end plate to support the orbiting scroll so as to revolve around the axis without rotating on its own axis. an Oldham ring, wherein the Oldham ring comprises a ring body that is annular so as to surround the axis; and a plurality of keys respectively inserted into the grooves, wherein the fixed end plate is disposed radially outwardly of the fixed wrap, forms an annular shape centered on the axis, and rotates at the turning end in the direction of the axis. It has an annular groove recessed in a direction away from the plate, a part of the ring body is arranged in the annular groove, and the swivel end plate has the disk shape and the thickness provided with the swivel wrap. A thick portion is provided integrally with the thick portion radially outward of the thick portion to form an annular shape. and a thin portion having an end face facing the end plate side disposed at a position away from the fixed end plate, and the ring main body is placed on the end face of the thin portion.

According to such a scroll compressor, the fixed end plate is provided with an annular groove, and a part of the ring body is arranged in the annular groove. Therefore, even if the thickness dimension in the direction of the axis of the Oldham ring is increased in order to cope with high pressure and increase the capacity, the fixed end plate can be arranged close to the swivel end plate. Therefore, the scroll compression portion can be made compact in the axial direction.
In addition, when lubricating oil is introduced into the scroll compressing portion, the lubricating oil can be retained in the annular groove, and the operation of the scroll compressing portion can be made smoother, leading to an improvement in efficiency.
Further, the orbiting end plate of the orbiting scroll has a thick portion and a thin portion, and the ring body of the Oldham ring is provided between the annular groove of the fixed end plate and the thin portion of the orbiting end plate. Become. Therefore, even if the thickness dimension in the axial direction of the ring body of the Oldham ring is increased in order to improve the strength accompanying high pressure, the fixed end plate and the swivel end plate can be brought closer in the axial direction. Therefore, it is possible to make the scroll compressing portion even more compact in the axial direction.
Further, the thinned portion is provided radially outward of the swivel end plate. Therefore, the weight of the radially outer end portion of the turning end plate can be reduced, and the moment of inertia when the turning end plate turns around the axis of the rotating shaft can be reduced. Since the radially outer end of the swivel end plate is less affected by the compressive load than the center of the swivel end plate, even if the thin portion is provided, there is little problem in terms of strength. Therefore, vibration can be suppressed even if the orbiting end plate is increased in size in order to cope with high pressure and increase the capacity of the scroll compressor.

Further, in the above scroll compressor, the key groove in the fixed end plate is recessed from the annular groove in a direction away from the orbiting end plate in the direction of the axial line, and extends radially outward of the annular groove from the annular groove. It may be provided extending to.

For example, when drilling a hole in the fixed end plate at a radially outer position of the annular groove and inserting an end mill into the hole to form the key groove, the end mill machining start point follows the outline of the drill and forms an arc. will be formed. However, if the key groove is formed to the radially outer position of the annular groove, the side surface facing the circumferential direction of the key groove in the annular groove can be formed in a flat shape along the radial direction. can easily form a keyway having a side surface of
In addition, the thickness of the fixed end plate in the direction of the axis at the radially outer position of the annular groove, which is the starting point of machining the keyway, is greater than the thickness in the direction of the axis at the position where the annular groove is formed. big. Therefore, even if the key groove is formed so as to extend radially outward of the annular groove, the strength problem is unlikely to occur.

Further, in the scroll compressor described above, the bottom surface of the annular groove and the surface of the ring body may be spaced apart in the direction of the axis.

Such a configuration makes it difficult for the surface of the ring body to come into contact with the bottom surface of the annular groove. Therefore, friction loss between the Oldham ring and the fixed end plate can be reduced.

The scroll compressor described above can be made compact while supporting high pressure and increasing capacity.

1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the invention; FIG. It is a figure which expands and shows the scroll compression part in the scroll compressor which concerns on embodiment of this invention. It is a top view showing a fixed scroll in a scroll compressor concerning an embodiment of the present invention. 1 is a plan view showing an orbiting scroll in a scroll compressor according to an embodiment of the invention; FIG. It is a top view which shows the Oldham's ring in the scroll compressor which concerns on embodiment of this invention. FIG. 6 is a view showing the Oldham ring in the scroll compressor according to the embodiment of the present invention, and is a cross-sectional view taken along the line AA of FIG. 5; FIG. 6 is a view showing the Oldham ring in the scroll compressor according to the embodiment of the present invention, and is a cross-sectional view taken along the line BB of FIG. 5;

A scroll compressor 1 according to an embodiment of the present invention will be described below.
In this embodiment, a vertical hermetic two-stage compressor having two compression units 4 and 5 will be described as the scroll compressor 1, but the scroll compressor 1 is not limited to such a compressor. For example, it may be a single-stage compressor having only one compression section, or a horizontal type compressor.

The scroll compressor 1 includes a rotary shaft 2 , a motor 3 that rotates the rotary shaft 2 , and a rotary compression section 4 and a scroll compression section 5 that compress refrigerant by rotating the rotary shaft 2 . The scroll compressor 1 further includes a housing 6 that houses the rotating shaft 2, motor 3, rotary compressor 4, and scroll compressor 5 in a sealed manner.

The rotating shaft 2 has a cylindrical shape centered on an axis O1 extending in the vertical direction. The upper end of the rotating shaft 2 is integrally provided with a columnar eccentric shaft 8 centered on an axis O2 arranged at a position radially displaced from the axis O1.

The housing 6 has a tubular shape extending vertically along the axis O<b>1 of the rotating shaft 2 . The housing 6 is formed by casting, for example. The housing 6 has a cylindrical housing body 10 , an upper lid 11 closing an upper opening of the housing body 10 , and a lower lid 12 closing a lower opening of the housing body 10 . Thereby, the housing 6 has a sealed space S extending in the vertical direction. Oil (lubricating oil) is accumulated from the lower portion of the housing body 10 to the bottom portion of the lower lid 12, and an oil reservoir OL is formed at this position.

A suction pipe 13 for introducing a refrigerant into the space S from the outside is connected to the lower portion of the housing 6 . Furthermore, a discharge pipe 14 is connected to the upper portion of the housing 6 for discharging the refrigerant from the space S to the outside.

A rotary lower bearing 20 , a rotary upper bearing 21 , and a scroll bearing 22 that rotatably support the rotary shaft 2 with respect to the housing 6 are provided inside the housing 6 . A rotary lower bearing 20 and a rotary upper bearing 21 are provided in the rotary compression section 4 , and a scroll bearing 22 is provided in the scroll compression section 5 .

The motor 3 is provided above the rotary upper bearing 21 and below the scroll bearing 22 in the space S of the housing 6 so as to be surrounded by the housing body 10 . A power source (not shown) is connected to the motor 3 through terminals 15 provided on the housing 6 . The motor 3 rotates the rotary shaft 2 with electric power from the power supply.

The rotary compression section 4 is provided below the motor 3 and is sandwiched between a rotary lower bearing 20 and a rotary upper bearing 21 . More specifically, the rotary compression section 4 has a cylinder 30 arranged above the lower rotary bearing 20 and below the upper rotary bearing 21 . Cylinder 30 is arranged in oil sump OL. A suction pipe 13 is connected to the cylinder 30 . The cylinder 30 has a compression chamber C<b>1 inside which compresses the refrigerant introduced from the suction pipe 13 . A rotating shaft 2 is inserted through the compression chamber C1. A piston 31 is provided on the rotating shaft 2 . As the rotation shaft 2 rotates, the piston 31 rotates within the compression chamber C1, thereby compressing the refrigerant. The refrigerant compressed in the compression chamber C1 of the rotary compression unit 4 passes through the rotary upper bearing 21 and flows upward toward the motor 3 side.

The rotary compression unit 4 of this embodiment has, as an example, a twin rotary structure in which the cylinders 30 are provided in two stages vertically, but for example, it has a single rotary structure in which only one cylinder 30 is provided. may Also, the connecting position of the suction pipe 13 to the rotary compression unit 4 is not limited to that shown in FIG.

Next, the scroll compression section 5 will be described with reference to FIGS. 2 to 4. FIG.
The scroll compression unit 5 is arranged within the space S above the motor 3 . More specifically, as shown in FIG. 2, the scroll compression portion 5 is vertically sandwiched between a fixed scroll 40 fixed to the housing 6 above the scroll bearing 22 and the fixed scroll 40 and the scroll bearing 22 . and an orbiting scroll 43 provided.
Further, the scroll compression section 5 has an Oldham ring 50 that engages with the fixed scroll 40 and the orbiting scroll 43 .

The fixed scroll 40 has a fixed end plate 41 which is fixed to the housing 6 below the discharge pipe 14 and has a disc shape centered on the axis O1, and a spiral which protrudes downward from the fixed end plate 41 and has the axis O1 as a reference. and a securing wrap 42 having a shape.

As shown in FIG. 3 , the fixed end plate 41 has a mating surface 41 a facing downward in the direction of the axis O<b>1 on the radially outer side of the fixed wrap 42 and in surface contact with the scroll bearing 22 . An annular groove 41b having an annular shape around the axis O1 is provided between the fixing wrap 42 and the mating surface 41a. The annular groove 41b is recessed upward in the direction of the axis O1 with respect to the mating surface 41a and the cutting edge 42a at the tip of the fixed wrap 42. As shown in FIG. In this embodiment, the mating surface 41a of the fixed end plate 41 and the cutting edge 42a of the fixed wrap 42 are arranged on the same plane. However, since the fixing wrap 42 thermally expands during operation of the compressor 1, the mating surface 41a and the cutting edge 42a of the fixing wrap 42 are not arranged completely on the same plane so as to allow for this thermal expansion. The cutting edge 42a of 42 may be arranged above the mating surface 41a.

Further, the fixed end plate 41 is provided with a pair of fixed side key grooves 41c spaced apart by 180 degrees in the circumferential direction. The fixed-side keyway 41c radially extends from a position close to the fixed wrap 42 to a midway position on the mating surface 41a. Further, the fixed-side key groove 41c is recessed further upward in the direction of the axis O1 than the annular groove 41b. Each fixed side keyway 41c has a rectangular cross section perpendicular to the radial direction. Each fixed-side keyway 41c has key sliding surfaces 41d, which are a pair of flat surfaces that are arranged in parallel with each other at intervals in the circumferential direction and that extend along the direction of the axis O1 and the radial direction.

Further, the fixed end plate 41 is formed with a pair of suction passages 41e communicating with a later-described compression chamber C2 formed by the fixed wrap 42. As shown in FIG. The pair of suction passages 41e are provided between the pair of fixed side key grooves 41c at positions that do not interfere with them. That is, each suction flow path 41e is provided one by one between the fixed side key grooves 41c at positions separated from the pair of fixed side key grooves 41c in the circumferential direction. Each suction passage 41e is recessed further upward than the annular groove 41b in the direction of the axis O1, extends from the fixed wrap 42 through the annular groove 41b to the mating surface 41a, and opens to the outer peripheral surface of the fixed end plate 41. are doing.

The orbiting scroll 43 includes an orbiting end plate 44 disposed below the fixed end plate 41 and opposed to the fixed end plate 41 in the direction of the axis O1, and a fixed end plate 44 extending upward from the orbiting end plate 44 in the direction of the axis O1. and a swivel wrap 45 projecting toward the plate 41 .

The swivel end plate 44 is disc-shaped around the axis O2 of the eccentric shaft 8 and attached to the eccentric shaft 8 . As shown in FIGS. 2 and 4, the turning end plate 44 includes a thick portion 44a having a disc shape centered on the axis O2 of the eccentric shaft 8, and a radially outward portion from the thick portion 44a integrally with the thick portion 44a. and a flange-like thin portion 44b projecting outward.

The thick portion 44 a is connected to the eccentric shaft 8 so as to be rotatable relative to the eccentric shaft 8 . Specifically, a cylindrical portion 46 that covers the eccentric shaft 8 from the outer periphery is integrally provided at the lower portion of the thick portion 44a. A bearing 46a is provided inside the cylindrical portion 46 as shown in FIG.

The thin portion 44b has an annular shape around the axis O2 of the eccentric shaft 8. As shown in FIG. The thin portion 44b has a smaller thickness in the direction of the axes O1 and O2 than the thick portion 44a, and the end surface (upper surface) facing the fixed end plate 41 side is smaller than the thick portion 44a. is located away from As a result, the turning end plate 44 has a surface facing the radial direction at the radially outer end, and a step is provided at the radially outer end of the turning end plate 44 .

The turning end plate 44 is provided with a pair of turning-side key grooves 44c spaced apart by 180 degrees in the circumferential direction. The orbiting-side key groove 44c opens to the outer peripheral surface of the thin portion 44b and extends radially inward from the outer peripheral surface of the thin portion 44b to the thick portion 44a. Therefore, the turning-side key groove 44c is provided between the thin portion 44b and the thick portion 44a. The turning-side keyway 44c penetrates the thin portion 44b in the direction of the axis O1, and has the same thickness dimension in the direction of the axis O1 as the thickness dimension of the thin portion 44b in the direction of the axis O1. It extends radially. Therefore, when the swivel end plate 44 is viewed from above, the swivel-side key groove 44c is provided so as to slip behind the thick portion 44a. Each turning-side keyway 44c has a rectangular cross section perpendicular to the radial direction. Each orbiting side keyway 44c has a key sliding surface 44d which is a pair of flat surfaces arranged in parallel with a space in the circumferential direction and extending along the direction of the axis O1 and the radial direction.

A thrust plate 47 is provided between the orbiting end plate 44 and the scroll bearing 22 to receive the load from the scroll compression portion 5 in the direction of the axis O1, that is, the thrust load. The thrust plate 47 has an annular shape surrounding the axis O1 of the rotating shaft 2 as shown in FIG. The thrust plate 47 is provided between the thin portion 44b and the thick portion 44a. That is, at least part of the thrust plate 47 is provided at a position supporting the thick portion 44a from below in the direction of the axis O1.

More specifically, when the inner diameter of the thrust plate 47 is din, the outer diameter is dout, and the outer diameter of the thick portion 44a is D, the relationship din<D≤dout is established.

The orbiting wrap 45 is radially overlapped with the fixed wrap 42 so as to face the fixed wrap 42 in the radial direction. A space between the orbiting wrap 45 and the fixed wrap 42 serves as a compression chamber C2 in which the refrigerant is compressed. Refrigerant flowing out from the compression chamber C1 of the rotary compression section 4 is introduced into the compression chamber C2 after passing around the motor 3 and the scroll bearing 22 .

Next, the Oldham ring 50 will be described with reference to FIGS. 5 to 7. FIG.
The Oldham ring 50 has an annular ring body 51 surrounding the axis O<b>1 of the rotating shaft 2 , and a pair of fixed side keys 52 and a pair of orbiting side keys 53 provided on the ring body 51 .

The ring body 51 has a substantially constant thickness, that is, a substantially constant dimension in the direction of the axis O1. The ring body 51 is mounted on the end surface (upper surface) of the thin portion 44b of the turning end plate 44 facing the fixed end plate 41 side. When the ring body 51 is placed on the thin portion 44b of the turning end plate 44, the surface (upper surface) of the ring body 51 facing the fixed end plate 41 side is the surface (upper surface) of the thick portion 44a facing the fixed end plate 41 side. Since the ring body 51 is located above the upper surface), part of the ring main body 51 protrudes upward from the thick portion 44a.

A portion of the ring body 51 protruding upward from the thick portion 44 a is arranged in the annular groove 41 b of the fixed end plate 41 . A minute gap SS is provided between the surface (upper surface) of the ring body 51 facing the fixed end plate 41 side and the bottom surface of the annular groove 41b. are spaced apart from each other.

The pair of fixed-side keys 52 are members having a rectangular cross-section and protruding upward from the upward-facing surface of the ring body 51 at intervals of 180 degrees in the circumferential direction. Each fixed-side key 52 has a radial dimension equivalent to the radial width dimension of the ring main body 51, and is provided integrally with the ring main body 51 so as not to protrude from the ring main body 51 in the radial direction. ing. The pair of fixed-side keys 52 are respectively inserted into and engaged with the pair of fixed-side key grooves 41 c provided in the fixed end plate 41 . Each fixed key 52 has planar side surfaces 52a on both sides in the circumferential direction that slide against the key sliding surface 41d of the fixed key groove 41c. The fixed-side key 52 reciprocates in the radial direction within the fixed-side key groove 41c.

The pair of orbiting side keys 53 are spaced 180 degrees apart in the circumferential direction and are positioned 90 degrees apart from the fixed side keys 52 in the circumferential direction, and project downward from the downward facing surface of the ring body 51 in cross section. It is a rectangular member. Each orbiting-side key 53 has a radial dimension larger than the radial width dimension of the ring body 51 , and is provided integrally with the ring body 51 in a state protruding radially inward from the ring body 51 . . The radially outer end face of each turning-side key 53 and the radially outer end face of the ring body 51 are arranged at substantially the same position. Therefore, each turning-side key 53 is provided on the ring main body 51 so as not to protrude radially outward from the ring main body 51 . The pair of turning-side keys 53 are inserted into and engaged with a pair of turning-side key grooves 44c provided in the turning end plate 44, respectively. Each turning-side key 53 has planar side surfaces 53a on both sides in the circumferential direction that slide against the key sliding surface 44d of the turning-side key groove 44c. The turning-side key 53 reciprocates in the radial direction within the turning-side key groove 44c.

The reciprocating motion between the orbiting key 53 and the orbiting key groove 44c and the reciprocating motion between the fixed key 52 and the fixed key groove 41c cause the orbiting scroll 43 to revolve around the axis O1 of the rotary shaft 2 without rotating. The relative movement between the stationary wrap 42 and the orbiting wrap 45 compresses the refrigerant in the compression chamber C2.

In the scroll compressor 1 of the present embodiment described above, the Oldham ring 50 is provided so that the ring body 51 protrudes in the direction of the axis O1 from the end surface of the thick portion 44a facing the fixed end plate 41 side. A portion of the ring body 51 is arranged in the annular groove 41b. Therefore, even if the thickness dimension of the Oldham ring 50 in the direction of the axis O1 is increased in order to cope with high pressure and increase the capacity, the fixed end plate 41 can be arranged close to the swivel end plate 44 . Therefore, the scroll compressor 5 can be made compact in the direction of the axis O1, and the entire scroll compressor 1 can be made compact.

In addition, when lubricating oil is introduced into the scroll compressing portion 5, the lubricating oil can be retained in the annular groove 41b, and the operation of the scroll compressing portion 5 can be smoothed, leading to further improvement in efficiency.

The fixed-side key groove 41c is provided so as to extend from the annular groove 41b to the radially outer side of the annular groove 41b of the fixed end plate 41. As shown in FIG. Therefore, for example, when a hole is drilled in the fixed end plate 41 at a radially outer position of the annular groove 41b and an end mill is inserted into the hole to form the fixed side key groove 41c, the processing start point of the end mill is It is formed in an arc shape following the outer shape of the drill. However, if the fixed-side key groove 41c is formed to a radially outer position of the annular groove 41b, the key sliding surface 41d of the fixed-side key groove 41c can be formed in a planar shape along the radial direction in the annular groove 41b. . Therefore, the planar key sliding surface 41d can be easily formed in the annular groove 41b.

At a position radially outside of the annular groove 41b, which is the starting point for machining the fixed-side keyway 41c, the thickness of the fixed end plate 41 in the direction of the axis O1 is the same as in the direction of the axis O1 at the position where the annular groove 41b is formed. larger than the thickness of Therefore, even if the fixed-side key groove is formed to extend radially outward of the annular groove 41b, a strength problem is unlikely to occur.

The bottom surface of the annular groove 41b and the surface of the ring body 51 are spaced apart in the direction of the axis O1. Therefore, the surface of the ring main body 51 is less likely to come into contact with the bottom surface of the annular groove 41b during operation of the scroll compressor 1 . Therefore, friction loss between the Oldham ring 50 and the fixed end plate 41 can be reduced.

In addition, since the mating surface 41a of the fixed end plate 41 and the cutting edge 42a of the fixed wrap 42 are arranged on the same plane, machining of them is facilitated.

The orbiting end plate 44 of the orbiting scroll 43 has a thick portion 44a and a thin portion 44b. The thin portion 44b is provided radially outward of the turning end plate 44. As shown in FIG. Therefore, the weight of the radially outer end portion of the turning end plate 44 can be reduced, and the moment of inertia when the turning end plate 44 turns around the axis O1 of the rotating shaft 2 can be reduced. Therefore, even if the orbiting end plate 44 is increased in size in order to make the scroll compressor 1 compatible with high pressure and increase in capacity, vibration can be suppressed. As a result, the efficiency can be improved while the scroll compressor 1 can cope with high pressure and have a large capacity.

Here, the radially outer end portion of the turning end plate 44 is less affected by the compressive load than the central portion of the turning end plate 44 . Therefore, even if the turning end plate 44 is provided with the thin portion 44b, there is little problem in terms of strength.

Further, in order to make the scroll compressor 1 compatible with high pressure and to have a large capacity, it is necessary to increase the strength of the Oldham ring 50 . At this time, even if the thickness dimension of the Oldham ring 50 in the direction of the axis O1 is increased, the ring main body 51 of the Oldham ring 50 is mounted on the thin portion 44b of the swivel end plate 44 so that the Oldham ring 50 can be reduced by the amount of projection from the orbiting end plate 44 to the fixed scroll 40 side. Therefore, the fixed end plate 41 can be brought closer to the turning end plate 44 . Therefore, the dimension of the scroll compressing portion 5 in the direction of the axis O1 can be further reduced while ensuring strength by increasing the thickness of the Oldham ring 50, so that the scroll compressing portion 5 can be made compact. Therefore, it is possible to achieve further compactness of the scroll compressor 1 as a whole while achieving high pressure support and large capacity.

Further, since at least a part of the thrust plate 47 is provided at a position supporting the thick portion 44a of the turning end plate 44, the thrust plate 47 supports the thick portion 44a which receives more thrust load due to the compressive load. can do. Therefore, even if the turning end plate 44 is provided with the thin portion 44b, the load does not act only on the thin portion 44b, and the compressive load can be sufficiently handled.

Further, by providing the orbiting side key groove 44c over the thin portion 44b and the thick portion 44a of the orbiting end plate 44, the length dimension of the orbiting side key 53 in the radial direction can be increased. Therefore, the surface pressure of the side surface 53a of the turning-side key 53 that slides against the key sliding surface 44d of the turning-side key groove 44c can be reduced, and the strength of the Oldham ring 50 can be improved. In the present embodiment, the orbiting-side keyway 44c extends to the thick portion 44a, but since the thickness dimension of the thick portion 44a in the direction of the axis O1 is larger than that of the thin portion 44b, strength problems are unlikely to occur. .

As described above, the embodiments of the present invention have been described in detail with reference to the drawings. , substitutions, and other modifications are possible. Moreover, the present invention is not limited by the embodiments, but only by the claims.

For example, the ring main body 51 of the Oldham ring 50 may have dimensions that do not protrude above the thick portion 44a in the direction of the axis O1.

The turning-side keyway 44c may be formed only in the thin portion 44b.

The fixed-side key groove may be formed only within the annular groove.

According to the above-mentioned scroll compressor, it is possible to achieve compactness while achieving high pressure compatibility and large capacity.

1 scroll compressor
2 Axis of rotation
3 motor
4 rotary compressor
5 Scroll Compressor
6 housing
8 Eccentric shaft
10 housing body
11 Upper lid
12 lower lid
13 suction pipe
14 discharge pipe
15 terminals
20 Rotary lower bearing
21 rotary upper bearing
22 scroll bearing
30 cylinder
31 Piston
40 fixed scroll
41 fixed end plate
41a mating surface
41b annular groove
41c fixed side keyway
41d Key sliding surface 41e Discharge channel 42 Fixed wrap
42a cutting edge
43 orbiting scroll
44 swivel end plate
44a thick part
44b thin portion
44c swivel side keyway
44d key sliding surface 45 swivel wrap
46 Cylindrical portion 46a Bearing 47 Thrust plate
50 oldham ring
51 ring body
52 fixed side key
52a Side 53 Turning side key
53a side S space
SS Small gap OL Oil pool
O1 axis
O2 axis
C1 compression chamber
C2 compression chamber

Claims (3)

a rotating shaft extending along the axis;
a motor that rotates the rotating shaft;
a scroll compression unit that compresses a refrigerant by rotation of the rotating shaft;
a housing that accommodates the rotating shaft, the motor, and the scroll compression section;
with
The scroll compression section is
a fixed scroll having a fixed end plate fixed to the housing and a fixed wrap projecting from the fixed end plate in the direction of the axis;
a swivel end plate provided on the rotating shaft and arranged to face the fixed end plate in the direction of the axis; an orbiting scroll having an orbiting wrap forming a chamber;
an Oldham ring interposed between the fixed end plate and the orbiting end plate to support the orbiting scroll so as to orbit around the axis without rotating;
has
The Oldham ring is
a ring body that is annular so as to surround the axis;
a plurality of keys protruding from the surface of the ring body and inserted into key grooves provided in the swivel end plate and the fixed end plate;
has
The fixed end plate is disposed radially outwardly of the fixed wrap, has an annular shape centered on the axis, and has an annular groove recessed in a direction away from the turning end plate in the direction of the axis,
A portion of the ring body is disposed within the annular groove ,
The swivel end plate is
the disk-shaped thick portion provided with the swirl wrap;
It is integrally provided on the radially outer side of the thick portion to form an annular shape, has a smaller thickness dimension in the axial direction than the thick portion, and is closer to the fixed end plate than the thick portion. a thin-walled portion having an end surface facing away from the fixed end plate;
has
A scroll compressor in which the ring body is placed on the end surface of the thin portion . 3. The key groove in the fixed end plate is recessed from the annular groove in the direction of the axial line in a direction away from the swivel end plate, and extends from the annular groove to a radially outer side of the annular groove. 2. The scroll compressor according to 1. The scroll compressor according to claim 1 or 2, wherein the bottom surface of the annular groove and the surface of the ring body are spaced apart in the direction of the axis.

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