SCROLL COMPRESSOR

TECHNICAL FIELD

The present invention relates to a scroll compressor equipped with an Oldham coupling for preventing self-rotation of a movable scroll.

BACKGROUND ART

A scroll compressor used in a refrigeration system or the like is equipped with a fixed scroll and a movable scroll. The fixed scroll and the movable scroll each have a spiral portion. The spiral portion of the movable scroll interfits with the spiral portion of the fixed scroll, whereby compression chambers, which are spaces in which a fluid such as refrigerant gas is compressed, are formed. The scroll compressor compresses the fluid by causing the movable scroll to orbit to change the volumes of the compression chambers.

Ordinarily the scroll compressor is equipped with an Oldham coupling for preventing self-rotation of the movable scroll during operation. The Oldham coupling is installed between the movable scroll and a fixed member such as a housing. As disclosed in patent document 1 (JP-A No. 2011-510209), the Oldham coupling has an annular body portion and key portions that project in the vertical direction from the body portion. Each key portion has a surface that slides against the movable scroll or the fixed member.

SUMMARY OF INVENTION
Technical Problem

In the case of an Oldham coupling such as disclosed in patent document 1 (JP-A No. 2011-510209), the sliding lengths, which are the lengths of the sliding surfaces of the key portions along the sliding direction of the key portions, are constrained by the dimensions of the annular body portion. Specifically, it is necessary to shorten the sliding lengths of the key portions the shorter the difference is between the outer diameter and the inner diameter of the annular body portion. However, if the sliding lengths of the key portions are not sufficient, the surface pressure that acts on the sliding surfaces of the key portions becomes higher. Because of this, there is the concern that issues such as seizure of the sliding surfaces and damage to the key portions will arise, thereby reducing the reliability of the compressor.

It is an object of the present invention to provide a scroll compressor that has high reliability by sufficiently ensuring the sliding lengths of the key portions of the Oldham coupling.

Solution to Problem

A scroll compressor pertaining to a first aspect of the invention is equipped with a movable scroll, a stationary member, and an Oldham coupling. The movable scroll has first key grooves. The stationary member has second key grooves. The Oldham coupling is provided between the movable scroll and the stationary member. The Oldham coupling is relatively movable with respect to the stationary member along a first axis and is relatively movable with respect to the movable scroll along a second axis. The Oldham coupling has an annular body portion, two pairs of first key portions, and a pair of second key portions. The annular body portion has a first horizontal surface and a second horizontal surface that oppose each other. The first key portions project from the first horizontal surface and are fitted into the first key grooves. The second key portions project from the second horizontal surface and are fitted into the second key grooves. The first key portions are provided one each in four regions partitioned by the first axis and the second axis. The second key portions are provided on the first axis across the second axis. First inner peripheral edges, which are inner peripheral edges of the annular body portion between the two first key portions located on the same sides with respect to the first axis, have circular arc shapes. The first horizontal surface has inwardly positioned surfaces that are positioned more on a center of gravity side of the Oldham coupling than virtual extension lines of the circular arcs of the first inner peripheral edges. The first key portions have inwardly positioned portions that project from the inwardly positioned surfaces.

In this scroll compressor, the first key portions of the Oldham coupling have sliding surfaces that slide against the movable scroll. The sliding length, which is the length of the sliding surfaces of the first key portions in the sliding direction of the first key portions, can be lengthened an amount corresponding to the inwardly positioned portions of the first key portions. Because of this, the sliding length of the first key portions can be sufficiently ensured, so the surface pressure that acts on the sliding surfaces of the first key portions can be restrained. Consequently, this scroll compressor has high reliability by sufficiently ensuring the sliding lengths of the key portions of the Oldham coupling.

A scroll compressor pertaining to a second aspect of the invention is the scroll compressor pertaining to the first aspect, wherein second inner peripheral edges, which are inner peripheral edges of the annular body portion between the two first key portions located on the same sides with respect to the second axis, have circular arc shapes. The first inner peripheral edges and the second inner peripheral edges are interconnected via step portions.

In this scroll compressor, the annular body portion of the Oldham coupling has the first inner peripheral edges and the second inner peripheral edges that have circular arc shapes with mutually different radii. The first inner peripheral edges and the second inner peripheral edges form step portions at the positions of the inwardly positioned portions of the first key portions. Because of the step portions, one of the first inner peripheral edges and the second inner peripheral edges can be formed more outward in the radial direction of the annular body portion than the other. Because of this, the radial direction dimension of the annular body portion can be shortened in the ranges of the first inner peripheral edges or the second inner peripheral edges, Consequently, with this scroll compressor, the weight of the Oldham coupling can be reduced.

A scroll compressor pertaining to a third aspect of the invention is the scroll compressor pertaining to the first aspect or the second aspect, wherein the radius of the circular arcs of the first inner peripheral edges is longer than the radius of the circular arcs of the second inner peripheral edges.

In this scroll compressor, the annular body portion of the Oldham coupling has the first inner peripheral edges and the second inner peripheral edges that have circular arc shapes with mutually different radii. The first inner peripheral edges can be formed more outward in the radial direction of the annular body portion than the second inner peripheral edges. Because of this, the radial direction dimension of the annular body portion can be shortened in the ranges of the first inner peripheral edges. Consequently, with this scroll compressor, the weight of the Oldham coupling can be reduced. Furthermore, the radial direction dimension of the annular body portion can be ensured in the ranges of the second inner peripheral edges, so the sliding length of the second key portions can be lengthened by that amount. Because of this, the surface pressure that acts on the sliding surfaces of the second key portions can be restrained.

A scroll compressor pertaining to a fourth aspect of the invention is the scroll compressor pertaining to any one of the first to third aspects, wherein the dimension of the first key portions along the second axis is longer than the dimension of the second key portions along the first axis.

In this scroll compressor, the sliding length of the first key portions can be made longer than the sliding length of the second key portions. Because of this, the surface pressure that acts on the sliding surfaces of the first key portions can be restrained.

Furthermore, the scroll compressor pertaining to the fifth aspect of the invention is equipped with a movable scroll, a stationary member, and an Oldham coupling. The movable scroll has first key grooves. The stationary member has second key grooves. The Oldham coupling is provided between the movable scroll and the stationary member. The Oldham coupling is relatively movable with respect to the stationary member along a first axis and is relatively movable with respect to the movable scroll along a second axis. The Oldham coupling has an annular body portion, at least two first key portions, and a pair of second key portions. The annular body portion has a first horizontal surface and a second horizontal surface that oppose each other. The first key portions project from the first horizontal surface and are fitted into the first key grooves. The second key portions project from the second horizontal surface and are fitted into the second key grooves. The first key portions are provided in any of four regions partitioned by the first axis and the second axis, and two or more of the first key portions are not provided in the same region. The second key portions are provided on the first axis across the second axis. The first horizontal surface has inwardly positioned surfaces that are positioned more on a center of gravity side of the Oldham coupling than virtual extension lines of first inner peripheral edges that are part of an inner peripheral edge of the annular body portion. The first key portions have inwardly positioned portions that project from the inwardly positioned surfaces.

Advantageous Effects of Invention

The scroll compressor pertaining to the invention has high reliability by sufficiently ensuring the sliding lengths of the key portions of the Oldham coupling.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a longitudinal sectional view of a scroll compressor pertaining to an embodiment.

FIG. 2 is a bottom view of a fixed scroll.

FIG. 3 is a top view of a movable scroll.

FIG. 4 is a bottom view of the fixed scroll in which a second wrap of the movable scroll and compression chambers are shown.

FIG. 5 is an enlarged view of the area around an Oldham coupling of FIG. 1.

FIG. 6 is a sectional view along line segment VI-VI of FIG. 5.

FIG. 7 is a perspective view of the Oldham coupling.

FIG. 8 is a top view of the Oldham coupling.

FIG. 9 is an enlarged view of the area around a first key portion at the upper left of

FIG. 8.

FIG. 10 is a top view of the Oldham coupling 39 of example modification C.

FIG. 11 is a top view of the Oldham coupling 39 of example modification C.

FIG. 12 is a top view of the Oldham coupling 39 of example modification D.

FIG. 13 is a top view of the Oldham coupling 39 of example modification D.

DESCRIPTION OF EMBODIMENT

A scroll compressor 101 pertaining to an embodiment of the invention will be described with reference to the drawings. The scroll compressor 101 is used in a refrigeration system such as an air conditioning system. The scroll compressor 101 compresses refrigerant gas that circulates through a refrigerant circuit of the refrigeration system.

(1) Configuration of Scroll Compressor

The scroll compressor 101 is a high/low pressure dome-type scroll compressor. The scroll compressor 101 compresses refrigerant using two scroll members having spiral-shaped wraps that interfit.

FIG. 1 is a longitudinal sectional view of the scroll compressor 101. In FIG. 1, arrow U indicates an upward direction along a vertical direction. The scroll compressor 101 is configured mainly from a casing 10, a compression mechanism 15, a housing 23, an Oldham coupling 39, a drive motor 16, a lower bearing 60, a crankshaft 17, a suction pipe 19, and a discharge pipe 20. Next, the constituent elements of the scroll compressor 101 will be described.

(1-1) Casing

The casing 10 is configured from an open cylinder-shaped barrel casing portion 11, a bowl-shaped top wall portion 12, and a bowl-shaped bottom wall portion 13. The top wall portion 12 is airtightly welded to the upper end portion of the barrel casing portion 11. The bottom wall portion 13 is airtightly welded to the lower end portion of the barrel casing portion 11.

The casing 10 is formed of a rigid member that does not easily become deformed or damaged when there is a change in pressure and/or temperature inside and outside the casing 10. The casing 10 is installed in such a way that the axial direction of the open cylindrical shape of the barrel casing portion 11 lies along the vertical direction.

Inside the casing 10 are housed mainly the compression mechanism 15, the housing 23, the Oldham coupling 39, the drive motor 16, the lower bearing 60, and the crankshaft 17. The suction pipe 19 and the discharge pipe 20 are airtightly welded to wall portions of the casing 10.

In the bottom portion of the casing 10 is formed an oil collection space 10a in which lubricating oil is stored. The lubricating oil is refrigerating machine oil that is used to well preserve the lubricity of sliding parts of the compression mechanism 15 and so forth during the operation of the scroll compressor 101.

(1-2) Compression Mechanism

The compression mechanism 15 is housed inside the casing 10. The compression mechanism 15 sucks in and compresses low-temperature low-pressure refrigerant gas and discharges high-temperature high-pressure refrigerant gas (hereinafter called “compressed refrigerant”), The compression mechanism 15 is configured mainly from a fixed scroll 24 and a movable scroll 26. The fixed scroll 24 is fixed with respect to the casing 10. The movable scroll 26 performs orbiting movement with respect to the fixed scroll 24. FIG. 2 is a bottom view of the fixed scroll 24 as seen along the vertical direction. FIG. 3 is a top view of the movable scroll 26 as seen along the vertical direction.

(1-2-1) Fixed Scroll

The fixed scroll 24 has a first end plate 24a and a first wrap 24b that is spiral-shaped and formed upright on the first end plate 24a. A main suction hole 24c is formed in the first end plate 24a. The main suction hole 24c is a space that interconnects the suction pipe 19 and later-described compression chambers 40. The main suction hole 24c forms a suction space for introducing the low-temperature low-pressure refrigerant gas from the suction pipe 19 to the compression chambers 40. A discharge hole 41 is formed in the central portion of the first end plate 24a, and a broad recess portion 42 that communicates with the discharge hole 41 is formed in the upper surface of the first end plate 24a. The broad recess portion 42 is a space that is provided recessed in the upper surface of the first end plate 24a. A cover 44 is fixed by bolts 44a to the upper surface of the fixed scroll 24 in such a way as to close off the broad recessed portion 42. The fixed scroll 24 and the cover 44 are sealed via a gasket (not shown in the drawings). A muffler space 45 that muffles the operating sound of the compression mechanism 15 is formed as a result of the broad recessed portion 42 being covered with the cover 44. A first compressed refrigerant flow passage 46 that communicates with the muffler space 45 and opens to the lower surface of the fixed scroll 24 is formed in the fixed scroll 24. An oil groove 24e that is C-shaped as shown in FIG. 2 is formed in the lower surface of the first end plate 24a.

(1-2-2) Movable Scroll

The movable scroll 26 has a second end plate 26a that is disc-shaped and a second wrap 26b that is spiral-shaped and formed upright on the second end plate 26a. An upper end bearing 26c is formed in the central portion of the lower surface of the second end plate 26a. An oil feed pore 63 is formed in the movable scroll 26. The oil feed pore 63 allows the outer peripheral portion of the upper surface of the second end plate 26a and the space inside the upper end bearing 26c to communicate with each other.

The fixed scroll 24 and the movable scroll 26 form, as a result of the first wrap 24b and the second wrap 26b interfitting, compression chambers 40 that are spaces enclosed by the first end plate 24a, the first wrap 24b, the second end plate 26a, and the second wrap 26b. The volumes of the compression chambers 40 are gradually reduced by the orbiting movement of the movable scroll 26. During the orbiting of the movable scroll 26, the lower surfaces of the first end plate 24a and the first wrap 24b of the fixed scroll 24 slide against the upper surfaces of the second end plate 26a and the second wrap 26b of the movable scroll 26. Hereinafter, the surface of the first end plate 24a that slides against the movable scroll 26 will be called a thrust sliding surface 24d. FIG. 4 is a bottom view of the fixed scroll 24 in which the second wrap 26b of the movable scroll 26 and the compression chambers 40 are shown. In FIG. 4, the region with the hatching represents the thrust sliding surface 24d. In FIG. 4, the outer edge of the thrust sliding surface 24d represents the path of the outer edge of the second end plate 26a of the orbiting movable scroll 26. As shown in FIG. 4, the oil groove 24e of the fixed scroll 24 is formed in the lower surface of the first end plate 24a in such a way as to fit within the thrust sliding surface 24d.

Two pairs of first key grooves 26d are formed in the lower surface of the second end plate 26a. In FIG. 3, the positions of the first key grooves 26d are indicated by dashed lines. When the movable scroll 26 is seen along the vertical direction, the first key grooves 26d are formed in positions the same distance away from the center of the second end plate 26a. The first key grooves 26d are grooves into which first key portions 39b of the Oldham coupling 39 are fitted.

(1-3) Housing

The housing 23 is disposed under the compression mechanism 15. The outer peripheral surface of the housing 23 is airtightly joined to the inner peripheral surface of the barrel casing portion 11. Because of this, the inside space of the casing 10 is partitioned into a high-pressure space S1 under the housing 23 and an upper space S2 that is a space above the housing 23. The housing 23 has the fixed scroll 24 mounted on it and, together with the fixed scroll 24, sandwiches the movable scroll 26. A second compressed refrigerant flow passage 48 is formed in, so as to run through in the vertical direction, the outer peripheral portion of the housing 23. The second compressed refrigerant flow passage 48 communicates with the first compressed refrigerant flow passage 46 at the upper surface of the housing 23 and communicates with the high-pressure space S1 at the lower surface of the housing 23.

A crank chamber S3 is provided recessed in the upper surface of the housing 23. A housing through hole 31 is formed in the housing 23. The housing through hole 31 runs through the housing 23 in the vertical direction from the central portion of the bottom surface of the crank chamber S3 to the central portion of the lower surface of the housing 23. Hereafter, the portion that is part of the housing 23 and in which the housing through hole 31 is formed will be called an upper bearing 32. in the housing 23 is formed an oil return passageway 23a that allows the high-pressure space S1 in the neighborhood of the inner surface of the casing 10 and the crank chamber S3 to communicate with each other.

A pair of second key grooves 23d is formed in the upper surface of the housing 23. When the housing 23 is seen along the vertical direction, the second key grooves 23d are formed in positions the same distance away from the center of the housing through hole 31.

The second key grooves 23d are grooves into which second key portions 39c of the Oldham coupling 39 are fitted.

(1-4) Oldham Coupling

The Oldham coupling 39 is a member for preventing self-rotation of the orbiting movable scroll 26. FIG. 5 is an enlarged view of the area around the Oldham coupling 39 of FIG. 1. FIG. 6 is a sectional view along line segment VI-VI of FIG. 5. As shown in FIGS. 5 and 6, the Oldham coupling 39 is installed between the movable scroll 26 and the housing 23, FIG. 7 is a perspective view of the Oldham coupling 39. FIG. 8 is a top view of the Oldham coupling 39.

The Oldham coupling 39 is an annular member having mainly an annular body portion 39a, two pairs of first key portions 39b, and a pair of second key portions 39c.

The annular body portion 39a has a first horizontal surface 39d1 and a second horizontal surface 39d2 that oppose each other. The first horizontal surface 39d1 and the second horizontal surface 39d2 are surfaces parallel to the horizontal plane. The first horizontal surface 39d1 is positioned higher than the second horizontal surface 39d2. In

FIGS. 7 and 8, the second horizontal surface 39d2 is a surface on the reverse side of the first horizontal surface 39d1. On the first horizontal surface 39d1 are formed plural sliding raised portions 39e. The upper surfaces of the sliding raised portions 39e are parallel to the first horizontal surface 39d1.

The first key portions 39b are raised portions that project upward from the first horizontal surface 39d1. The first key portions 39b are fitted into the first key grooves 26d of the movable scroll 26.

The second key portions 39c are raised portions that project downward from the second horizontal surface 39d2. The second key portions 39c are fitted into the second key grooves 23d of the housing 23. In FIG. 8, the positions of the second key portions 39c are indicated by dashed lines.

FIG. 8 shows a first axis A1 and a second axis A2 that are parallel to the horizontal plane. The first axis A1 and the second axis A2 pass through a center of gravity O of the Oldham coupling 39 and are orthogonal to each other. The four first key portions 39b are formed one each in four regions partitioned by the first axis A1 and the second axis A2. The two second key portions are formed one each in two regions partitioned by the second axis A2. Hereinafter, as needed, the four first key portions 39b will be differentiated into a pair of first key portions 39b1 and a pair of first key portions 39b2 and described as shown in FIG. 7 and FIG. 8.

The pair of first key portions 39b1 are formed in symmetrical positions across the first axis A1. The pair of first key portions 39b2 are formed in symmetrical positions across the first axis A1. The pair of first key portions 39b1 and the pair of first key portions 39b2 are formed in symmetrical positions across the second axis A2. The pair of second key portions 39c are formed in symmetrical positions across the second axis A2. Each second key portion 39c is formed in a position on the first axis A1 in which it is symmetrical with respect to the first axis A1.

The first key portions 39b have first sliding surfaces 39h that are side surfaces parallel to the second axis A2. The first sliding surfaces 39h are the surfaces closer to the center of gravity O of the Oldham coupling 39 among the two side surfaces of each first key portion 39b that are parallel to the second axis A2. The first sliding surfaces 391i are surfaces that slide against the inner surfaces of the first key grooves 26d along the second axis A2. The first sliding surfaces 39h are surfaces that receive surface pressure from the movable scroll 26.

The second key portions 39c have second sliding surfaces 39i that are side surfaces parallel to the first axis A1. The second sliding surfaces 39i are the two side surfaces of each second key portion 39c that are parallel to the first axis A1. The second sliding surfaces 39i are surfaces that slide against the inner surfaces of the second key grooves 23d along the first axis A1. The second sliding surfaces 39i are surfaces that receive surface pressure from the housing 23.

The Oldham coupling 39 is relatively movable with respect to the housing 23 along the first axis A1 and is relatively movable with respect to the movable scroll 26 along the second axis A2. As the Oldham coupling 39 relatively moves with respect to the movable scroll 26, the upper surfaces of the sliding raised portions 39e of the Oldham coupling 39 slide against the lower surface of the second end plate 26a of the movable scroll 26.

In FIG. 8 are shown first inner peripheral edges IE1 and second inner peripheral edges IE2 that are inner peripheral edges of the annular body portion 39a when the Oldham coupling 39 is seen along the vertical direction. The first inner peripheral edges IE1 and the second inner peripheral edges IE2 correspond to inner peripheral surfaces of the annular body portion 39a. When the Oldham coupling 39 is seen along the vertical direction, the first inner peripheral edges IE1 and the second inner peripheral edges IE2 have circular arc shapes.

The first inner peripheral edges IE1 are inner peripheral edges of the annular body portion 39a between the two first key portions 39b located on the same sides with respect to the first axis A1. The second inner peripheral edges IE2 are inner peripheral edges of the annular body portion 39a between the two key portions 39h located on the same sides with respect to the second axis A2. In the radial direction of the annular body portion 39a, the first inner peripheral edges IE1 are positioned more outward in the radial direction than the second inner peripheral edges IE2. That is, as shown in FIG. 8, a first inner peripheral radius R1 that is the radius of the circular arcs of the first inner peripheral edges IE1 is longer than a second inner peripheral radius R2 that is the radius of the circular arcs of the second inner peripheral edges IE2.

In FIG. 8, virtual extension lines VL1 of the first inner peripheral edges IE1 are indicated by long-dashed short-dashed lines. The virtual extension lines VL1 are virtual circular arcs in which the circular arcs forming the first inner peripheral edges IE1 in FIG. 8 are extended from both ends of the first inner peripheral edges IE1. The first inner peripheral radius R1 is longer than the second inner peripheral radius R2, so in the radial direction of the annular body portion 39a the virtual extension lines VL1 are positioned more outward in the radial direction than the second inner peripheral edges IE2.

FIG. 9 is an enlarged view of the area around the first key portion 39b at the upper left of FIG. 8. Hereinafter, the regions that are part of the first horizontal surface 39d1 and are located between the virtual extension lines VL1 and the second inner peripheral edges IE2 as shown in FIGS. 8 and 9 will be called inwardly positioned surfaces 39d3. The inwardly positioned surfaces 39d3 are surfaces positioned more on the center of gravity O side of the Oldham coupling 39 than the virtual extension lines VL1. In FIG. 9, the inwardly positioned surface 39d3 is indicated as a region with hatching.

As shown in FIG. 9, the first key portions 39b have inwardly positioned portions 39g that project upward from the inwardly positioned surfaces 39d3 of the first horizontal surface 39d1. That is, the first key portions 39h have inwardly positioned portions 39g that are positioned more on the center of gravity O side of the Oldham coupling 39 than the virtual extension lines VL1.

As shown in FIG. 9, a dimension L1 of the first key portions 39b along the second axis A2 is longer than a dimension L2 of the second key portions 39c along the first axis A1. That is, a first sliding length L1 that is the sliding direction dimension of the first sliding surfaces 39h is longer than a second sliding length L2 that is the sliding direction dimension of the second sliding surfaces 39i.

As shown in FIG. 9, the first inner peripheral edges IE1 and the second inner peripheral edges IE2 are interconnected via step portions 39f. The step portions 39f correspond to inner peripheral edges of the annular body portion 39a that interconnect the first inner peripheral edges IE1 and the second inner peripheral edges IE2. The step portions 39f are parallel to the first sliding surfaces 39h of the first key portions 39b.

(1-5) Drive Motor

The drive motor 16 is a brushless DC motor disposed under the housing 23. The drive motor 16 has mainly a stator 51 and a rotor 52. The stator 51 is an open cylinder-shaped member fixed to the inner peripheral surface of the casing 10. The rotor 52 is a solid cylinder-shaped member disposed inside the stator 51. An air gap is formed between the inner peripheral surface of the stator 51 and the outer peripheral surface of the rotor 52. Plural core cuts are formed in the outer peripheral surface of the stator 51. The core cuts are grooves formed in the vertical direction ranging from the upper end surface to the lower end surface of the stator 51. The core cuts are formed at predetermined intervals along the circumferential direction of the stator 51. The core cuts form motor cooling passageways 55 that extend in the vertical direction between the barrel casing portion 11 and the stator 51.

The rotor 52 is coupled to the crankshaft 17. The crankshaft 17 runs in the vertical direction through the rotational center of the rotor 52. The rotor 52 is connected via the crankshaft 17 to the compression mechanism 15.

(1-6) Lower Bearing

The lower bearing 60 is disposed under the drive motor 16. The outer peripheral surface of the lower hearing 60 is airtightly joined to the inner peripheral surface of the casing 10. The lower bearing 60 supports the crankshaft 17. An oil separation plate 73 is attached to the lower bearing 60. The oil separation plate 73 is a fiat plate-shaped member housed inside the casing 10. The oil separation plate 73 is fixed to the upper end surface of the lower bearing 60.

(1-7) Crankshaft

The crankshaft 17 is housed inside the casing 10. The crankshaft 17 is disposed in such a way that its axial direction lies along the vertical direction. The axial center of the upper end portion of the crankshaft 17 is slightly eccentric with respect to the axial center of the portion excluding the upper end portion. The crankshaft 17 has a counterweight 18. The counterweight 18 is tightly fixed to the crankshaft 17 at a height position under the housing 23 and above the drive motor 16.

The crankshaft 17 runs in the vertical direction through the rotational center of the rotor 52 and is coupled to the rotor 52. The upper end portion of the crankshaft 17 is fitted into the upper end bearing 26c, whereby the crankshaft 17 is connected to the movable scroll 26. The crankshaft 17 is supported by the upper bearing 32 and the lower bearing 60.

The crankshaft 17 has inside a main oil feed passage 61 that extends in the axial direction of the crankshaft 17. The upper end of the main oil feed passage 61 communicates with an oil chamber 83 formed by the upper end surface of the crankshaft 17 and the lower surface of the second end plate 26a. The oil chamber 83 communicates with the thrust sliding surface 24d and the oil groove 24e via the oil feed pore 63 in the second end plate 26a and finally communicates with the low-pressure space S2 via the compression chambers 40. The lower end of the main oil feed passage 61 is immersed in the lubricating oil in the oil collection space 10a.

The crankshaft 17 has a first auxiliary oil feed passage 61a, a second auxiliary oil feed passage 61b, and a third auxiliary oil feed passage 61c that branch from the main oil feed passage 61. The first auxiliary oil feed passage 61a, the second auxiliary oil feed passage 61b, and the third auxiliary oil feed passage 61c extend in the horizontal direction. The first auxiliary oil feed passage 61a opens to the sliding surfaces of the crankshaft 17 and the upper end bearing 26c of the movable scroll 26. The second auxiliary oil feed passage 61b opens to the sliding surfaces of the crankshaft 17 and the upper bearing 32 of the housing 23. The third auxiliary oil feed passage 61b opens to the sliding surfaces of the crankshaft 17 and the lower bearing 60.

(1-8) Suction Pipe

The suction pipe 19 is a pipe for introducing the refrigerant in the refrigerant circuit from the outside of the casing 10 to the compression mechanism 15. The suction pipe 19 is airtightly fitted into the top wall portion 12 of the casing 10. The suction pipe 19 runs in the vertical direction through the upper space S2, and its inner end portion is fitted into the main suction hole 24c in the fixed scroll 24.

(1-9) Discharge Pipe

The discharge pipe 20 is a pipe for discharging the compressed refrigerant from the high-pressure space S1 to the outside of the casing 10. The discharge pipe 20 is airtightly fitted into the barrel casing portion 11 of the casing 10. The discharge pipe 20 runs in the horizontal direction through the high-pressure space S1. Inside the casing 10, an open portion 20a of the discharge pipe 20 is positioned in the neighborhood of the housing 23.

(2) Operation of Scroll Compressor

The operation of the scroll compressor 101 will be described. First, the flow of the refrigerant circulating through the refrigerant circuit equipped with the scroll compressor 101 will be described. Next, the flow of the lubricating oil inside the scroll compressor 101 will be described.

(2-1) Flow of Refrigerant

When the driving of the drive motor 16 starts, the rotor 52 begins to rotate and the crankshaft 17 fixed to the rotor 52 begins axially rotating. The axial rotational movement of the crankshaft 17 is transmitted via the upper end bearing 26c to the movable scroll 26. The axial center of the upper end portion of the crankshaft 17 is eccentric with respect to the axial center of the axial rotational movement of the crankshaft 17.

The movable scroll 26 is engaged with the housing 23 via the Oldham coupling 39. When the crankshaft 17 rotates, the first key portions 39b of the Oldham coupling 39 slide along the second axis A2 inside the first key grooves 26d of the movable scroll 26, and the second key portions 39c of the Oldham coupling 39 slide along the first axis A1 inside the second key grooves 23d of the housing 23. Because of this, the movable scroll 26 performs orbiting movement with respect to the fixed scroll 24 without self-rotating.

The low-temperature low-pressure refrigerant before being compressed is supplied from the suction pipe 19 via the main suction hole 24c to the compression chambers 40 of the compression mechanism 15. Because of the orbiting movement of the movable scroll 26, the compression chambers 40 move from the outer peripheral portion to the central portion of the fixed scroll 24 while their volumes are gradually decreased. As a result, the refrigerant in the compression chambers 40 is compressed and becomes compressed refrigerant. The compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45 and thereafter is discharged via the first compressed refrigerant flow passage 46 and the second compressed refrigerant flow passage 48 to the high-pressure space S1. Thereafter, the compressed refrigerant descends through a motor cooling passageway 55 and reaches the high-pressure space S1 under the drive motor 16. Thereafter, the compressed refrigerant reverses its flow direction and ascends through another motor cooling passageway 55 and the air gap in the drive motor 16. Finally, the compressed refrigerant is discharged from the discharge pipe 20 to the outside of the scroll compressor 101.

(2-2) Flow of Lubricating Oil

When the driving of the drive motor 16 starts, the rotor 52 begins to rotate and the crankshaft 17 fixed to the rotor 52 begins axially rotating. When the compression mechanism 15 is driven by the axial rotation of the crankshaft 17 and the compressed refrigerant is discharged to the high-pressure space S1. the pressure inside the high-pressure space S1 increases. The lower end of the main oil feed passage 61 communicates with the oil collection space 10a inside the high-pressure space S1. The upper end of the main oil feed passage 61 communicates with the low-pressure space S2 via the oil chamber 83 and the oil feed pore 63. Because of this, differential pressure occurs between the upper end and the lower end of the main oil feed passage 61. As a result, the lubricating oil stored in the oil collection space 10a is sucked by the differential pressure from the lower end of the main oil feed passage 61 and ascends through the inside of the main oil feed passage 61 to the oil chamber 83.

Most of the lubricating oil ascending through the main oil feed passage 61 is sequentially distributed to the third auxiliary oil feed passage 61c, the second auxiliary oil feed passage 61b, and the first auxiliary oil feed passage 61a. The lubricating oil flowing through the third auxiliary oil feed passage 61c lubricates the sliding surfaces of the crankshaft 17 and the lower bearing 60 and thereafter flows into the high-pressure space S and returns to the oil collection space 10a. The lubricating oil flowing through the second auxiliary oil feed passage 61b lubricates the sliding surfaces of the crankshaft 17 and the upper bearing 32 of the housing 23 and thereafter flows into the high-pressure space S1 and the crank chamber S3. The lubricating oil that has flowed into the high-pressure space S1 returns to the oil collection space 10a. The lubricating oil that has flowed into the crank chamber S3 flows via the oil return passageway 23a in the housing 23 to the high-pressure space S1 and returns to the oil collection space 10a. The lubricating oil flowing through the first auxiliary oil feed passage 61a lubricates the sliding surfaces of the crankshaft 17 and the upper end bearing 26c of the movable scroll 26 and thereafter flows into the crank chamber S3 and returns via the high-pressure space S1 to the oil collection space 10a.

The lubricating oil that has ascended through the inside of the main oil feed passage 61 to the upper end and has reached the oil chamber 83 flows through the oil feed pore 63 and is supplied to the oil groove 24e by the differential pressure. Some of the lubricating oil that has been supplied to the oil groove 24e leaks out to the low-pressure space S2 and the compression chambers 40 while sealing the thrust sliding surface 24d. At this time, the high-temperature lubricating oil that has leaked out heats the low-temperature refrigerant gas present in the low-pressure space S2 and the compression chambers 40. Furthermore, the lubricating oil that has leaked out to the compression chambers 40 becomes mixed in, as minute oil droplets, with the compressed refrigerant. The lubricating oil that has been mixed in with the compressed refrigerant travels the same path as the compressed refrigerant and is discharged from the compression chambers 40 to the high-pressure space S1. Thereafter, the lubricating oil descends together with the compressed refrigerant through the motor cooling passageways 55 and thereafter hits the oil separation plate 73. The lubricating oil sticking to the oil separation plate 73 falls through the high-pressure space S and returns to the oil collection space 10a.

(3) Characteristics of Scroll Compressor

In the scroll compressor 101, the Oldham coupling 39 has the first key portions 39b that slide against the movable scroll 26 and the second key portions 39c that slide against the housing 23. The first key portions 39b have the first sliding surfaces 39h that slide along the second axis A2 against the inner surfaces of the first key grooves 26d of the movable scroll 26. When the Oldham coupling 39 is seen along the vertical direction, as shown in FIGS. 8 and 9, the first inner peripheral edges IE1 of the Oldham coupling 39 are positioned more outward in the radial direction than the second inner peripheral edges IE2. Additionally, the first key portions 39b have the inwardly positioned portions 39g that are positioned more on the center of gravity O side of the Oldham coupling 39 than the virtual extension lines VL1 of the first inner peripheral edges IE1. For that reason, the first sliding length L1 that is the sliding direction dimension of the first sliding surfaces 39h can be lengthened an amount corresponding to the inwardly positioned portions 39g of the first key portions 39b.

The sliding length of the key portions of an Oldham coupling is constrained by the dimensions of the Oldham coupling specifically, the radial direction dimension of the annular body portion of the Oldham coupling. In the conventional Oldham coupling, the key portions corresponding to the first key portions 39b of the embodiment do not have portions corresponding to the inwardly positioned portions 39g. For that reason, in the conventional Oldham coupling, sometimes the sliding length of the key portions cannot be sufficiently ensured. When the sliding length of the key portions is not sufficient, there is the concern that the surface pressure that acts on the sliding surfaces of the key portions will become higher and that issues such as seizure of the sliding surfaces and damage to the key portions will arise, thereby reducing the reliability of the compressor.

In contrast, the Oldham coupling 39 of the scroll compressor 101 of the embodiment can sufficiently ensure, with the inwardly positioned portions 39g of the first key portions 39b, the first sliding length L1 of the first key portions 39b. Because of this, the surface pressure that acts on the first sliding surfaces 39h of the first key portions 39b from the movable scroll 26 is restrained, For that reason, the occurrence of issues such as seizure of the first sliding surfaces 39h of the first key portions 39b and damage to the first key portions 39b is inhibited. Consequently, the scroll compressor 101 has high reliability by sufficiently ensuring the first sliding length L1 of the first key portions 39b of the Oldham coupling 39.

Furthermore, the annular body portion 39a of the Oldham coupling 39 has the first inner peripheral edges IE1 and the second inner peripheral edges IE2 that have circular arc shapes with mutually different radii when seen along the vertical direction. The first inner peripheral edges IE1 and the second inner peripheral edges IE2 form the step portions 39f at the positions of the inwardly positioned portions 39g of the first key portions 39b. Because of the step portions 39f, the first inner peripheral edges IE1 are formed more outward in the radial direction of the annular body portion 39a than the second inner peripheral edges IE2. For that reason, the radial direction dimension of the annular body portion 39a can be shortened in the ranges of the first inner peripheral edges IE1 in the circumferential direction of the annular body portion 39a. Consequently, with the scroll compressor 101, the weight of the Oldham coupling 39 can be reduced.

Furthermore, by forming, the second inner peripheral edges IE2 more inward in the radial direction of the annular body portion 39a than the first inner peripheral edges IE1, the radial direction dimension of the annular body portion 39a can be ensured in the ranges of the second inner peripheral edges IE2 in the circumferential direction of the annular body portion 39a. Because of this, the second sliding length L2 of the second key portions 39c can be lengthened. For that reason, the occurrence of issues such as seizure of the second sliding surfaces 39i of the second key portions 39c and damage to the second key portions 39c is inhibited.

(4) Example Modifications

An embodiment of the invention has been described above, but the specific configurations of the invention can be changed in a range that does not depart from the spirit of the invention. Example modifications applicable to the embodiment of the invention will be described below.

(4-1) Example Modification A

In the embodiment, the movable scroll 26 has the first key grooves 26d that slide against the first key portions 39h of the Oldham coupling 39. The first sliding surfaces 39h of the first key portions 39b slide against the inner surfaces of the first key grooves 26d. However, the movable scroll 26 may also have, instead of the first key grooves 26d, cutouts having surfaces that slide against the first sliding surfaces 39h of the first key portions 39b.

(4-2) Example Modification B

In the embodiment, the first sliding length L1 that is the sliding direction dimension of the first sliding surfaces 39h is longer than the second sliding length L2 that is the sliding direction dimension of the second sliding surfaces 39i. However, the first sliding length L does not need to be longer than the second sliding length L2 as long as the first sliding length L1 and the second sliding length L2 are sufficiently ensured.

(4-3) Example Modification C

In the embodiment, when the Oldham coupling 39 is seen along the vertical direction, the inner peripheral surface of the annular body portion 39a has a circular arc shape. FIG. 3 shows the first inner peripheral edges IE1 and the second inner peripheral edges IE2 that are the inner peripheral edges of the annular body portion 39a when the Oldham coupling 39 of the embodiment is seen along the vertical direction. When the Oldham coupling 39 is seen along the vertical direction, the first inner peripheral edges IE1 and the second inner peripheral edges IE2 have circular arc shapes.

However, the inner peripheral surface of the annular body portion 39a may also have an arbitrary shape. Specifically, the second inner peripheral edges IE2 do not need to have circular arc shapes as long as the first key portions 39b have the inwardly positioned portions 39g. Here, the inwardly positioned portions 39g are, as shown in FIG. 9, portions that are part of the first key portions 39b and are positioned more on the center of gravity O side of the Oldham coupling 39 than the virtual extension lines VL1 of the first inner peripheral edges IE1.

FIG. 10 and FIG. 11 are top views of the Oldham coupling 39 of the present example modification. In FIG. 10, the second inner peripheral edges IE2 positioned between the pair of first key portions 39b1 and between the pair of first key portions 39b2 include linear portions IE3 that are parallel to the second axis A2. In FIG. 11, the second inner peripheral edges IE2 positioned between the pair of first key portions 39b1 and between the pair of first key portions 39b2 include linear portions IE3 that are not parallel to the second axis A2. In FIG. 10 and FIG. 11, when the Oldham coupling 39 is seen along the vertical direction, the second inner peripheral edges IE2 are positioned more on the center of gravity O side of the Oldham coupling 39 than the virtual extension lines VL1 of the first inner peripheral edges IE1.

In this example modification also, the first sliding length L1 that is the sliding direction dimension of the first sliding surfaces 39h can be lengthened an amount corresponding to the inwardly positioned portions 39g of the first key portions 39b. Because of this, the surface pressure that acts on the first sliding surfaces 39h of the first key portions 39b from the movable scroll 26 is restrained. For that reason, the occurrence of issues such as of seizure of the first sliding surfaces 39h of the first key portions 39b and damage to the first key portions 39b is inhibited.

(4-4) Example Modification D

In the embodiment, as shown in FIG. 8, the Oldham coupling 39 has mainly the annular body portion 39a, the two pairs of first key portions 39b, and the pair of second key portions 39c. The two pairs of first key portions 39h comprise the pair of first key portions 39b1 and the pair of first key portions 39b2. The pair of first key portions 39b 1 are formed in symmetrical positions across the first axis A1. The pair of first key portions 39b2 are famed in symmetrical positions across the first axis A1. The pair of first key portions 39b1 and the pair of first key portions 39b2 are formed in symmetrical positions across the second axis A2.

However, the Oldham coupling 39 may also, instead of having the two pairs of first key portions 39b, have just one of the pair of first key portions 39b1 and just one of the pair of first key portions 39b2. That is, the first key portions 39b of the Oldham coupling 39 may be configured from just one first key portion 39b1 and one first key portion 39b2.

As examples, FIG. 12 and. FIG. 13 are top views of the Oldham coupling 39 of the present example modification. In FIG. 12 and FIG. 13, the Oldham coupling 39 has one first key portion 39b1 and one first key portion 39b2. In the Oldham coupling 39 shown in FIG. 12, the two first key portions 39b1 and 39b2 are formed in symmetrical positions with respect to the center of gravity O of the Oldham coupling 39. In the Oldham coupling 39 shown in FIG. 13, the two first key portions 39b1 and 39b2 are formed in symmetrical positions across the second axis A2. Furthermore, the two first key portions 39b1 and 39b2 may be formed in symmetrical positions across the first axis A1 from the positions shown in FIG. 12 and FIG. 13.

Furthermore, in this example modification, it suffices for the Oldham coupling 39 to have at least two first key portions 39b among the four first key portions 39b shown in FIG. 8.

That is, the Oldham coupling 39 may also have two or three first key portions 39b. In this case, the first key portions 39b are provided in any of the four regions partitioned by the first axis A1 and the second axis A2, and two or more of the first key portions 39b are not provided in the same region.

It will be noted that, in this example modification, as long as the first key portions 39b have the inwardly positioned portions 39b, when the Oldham coupling 39 is seen along the vertical direction the first inner peripheral edges IE1 and the second inner peripheral edges IE2 may also have arbitrary shapes as in example modification A.

INDUSTRIAL APPLICABILITY

The scroll compressor pertaining to the invention has high reliability by sufficiently ensuring the sliding lengths of key portions of an Oldham coupling.

REFERENCE SIGNS LIST

23 Housing (Stationary Member)

23
d Second Key Grooves

26 Movable Scroll

26
d First Key Grooves

39 Oldham Coupling

39
a Annular Body Portion

39
b First Key Portions

39
c Second Key Portions

39
d
1 First Horizontal Surface

39
d
2 Second Horizontal Surface

39
d
3 Inwardly Positioned Surfaces

39
f Step Portions

39
g Inwardly Positioned Portions

101 Scroll Compressor

A1 First Axis

A2 Second Axis

IE1 First Inner Peripheral Edges

IE2 Second Inner Peripheral Edges

R1 Radius of Circular Arcs of First Inner Peripheral Edges

R2 Radius of Circular Arcs of Second Inner Peripheral Edges

VL1 Virtual Extension Lines

CITATION LIST
<Patent Literature>

Patent Document 1: JP-A No. 2011-510209

SCROLL COMPRESSOR

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CPC

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