WO2020004220A1 - Horizontal scroll compressor - Google Patents

Abstract

A horizontal scroll compressor in which, as lubricating oil passes through a decompression mechanism (42), a gas refrigerant separated from the lubricating oil is caused to flow from a mechanism accommodating compartment (34c) of a rotation-preventing mechanism into an entry opening portion (91), and the gas refrigerant that has flowed in is discharged through a discharge path (90, 130). When the uppermost area of the entry opening portion is an uppermost portion of the entry opening portion, an uppermost-positioned sliding portion among a plurality of sliding portions is an upper sliding portion, and the area of the upper sliding portion that is positioned on the lowermost side at the timing of the upper sliding portion being positioned at the lowermost area is a lowermost portion, the uppermost portion of the entry opening portion is positioned above the lowermost portion of the upper sliding portion.

Description

Horizontal scroll compressor Cross-reference to related application

This application is based on Japanese Patent Application No. 2018-124915 filed on June 24, 2018, the disclosure of which is incorporated herein by reference.

The present disclosure relates to a horizontal scroll compressor.

In the scroll compressor, a rotation preventing mechanism for preventing rotation of the orbiting scroll is disposed substantially perpendicularly to the axial direction of the orbiting scroll. For this reason, the lubricating oil to be supplied to the upper sliding portion (hereinafter referred to as the upper sliding portion) of the plurality of sliding portions constituting the rotation preventing mechanism is unlikely to rise upward due to gravity. .
For this reason, it is difficult to lubricate the upper sliding portion of the plurality of sliding portions of the rotation preventing mechanism, and the Oldham ring as the rotation preventing mechanism reciprocates, so that the speed becomes zero at the time of turning back. For this reason, it is generally known that it is difficult to form an oil film in the upper sliding portion.

ス ク ロ ー ル In the scroll compressor, a force (hereinafter, referred to as a thrust load) in a direction to separate the orbiting scroll from the fixed scroll in the axial direction is generated by the compression reaction force of the refrigerant.

To cope with this, in Patent Document 1, a bearing member having a thrust support surface that receives a thrust load from a sliding surface of the orbiting scroll is provided.

オ ル Here, the Oldham ring, which is a rotation preventing mechanism, is arranged radially inward of the sliding surface of the orbiting scroll. In this configuration, the lubricating oil separated from the high-pressure refrigerant discharged from the compression chamber by the oil separation mechanism is supplied to the inside of the sliding surface of the orbiting scroll via the high-pressure oil storage chamber and the pressure reduction control mechanism.

ス ラ The thrust support surface of the bearing member receives a thrust load from the sliding surface of the orbiting scroll. Therefore, the thrust support surface of the bearing member is pressed against the sliding surface of the orbiting scroll, so that the lubricating oil is prevented from flowing radially outward from between the thrust supporting surface and the sliding surface of the orbiting scroll.

Therefore, since the lubricating oil is held radially inward of the sliding surface of the orbiting scroll, sufficient lubricating oil is also supplied to the upper sliding portion of the Oldham ring.

JP 2008-138597 A

で は In the scroll compressor of Patent Document 1, as described above, the thrust support surface of the bearing member is pressed from the sliding surface of the orbiting scroll. For this reason, the lubricating oil from the high-pressure oil storage chamber is also supplied to the upper sliding portion of the Oldham ring disposed radially inward of the sliding surface of the orbiting scroll.

On the other hand, the lubricating oil from the high-pressure oil storage chamber is supplied to the inside of the sliding surface of the orbiting scroll via the pressure reduction control mechanism as described above. When the lubricating oil passes through the decompression control mechanism, the refrigerant in the lubricating oil (that is, the working fluid) undergoes decompression foaming. Further, when the sliding portion is lubricated, heat is transferred to the oil, and the oil is heated, thereby generating a heated shot. That is, the refrigerant dissolved in the lubricating oil is separated from the lubricating oil.

で は In the scroll compressor of Patent Document 1, the thrust support surface of the bearing member is pressed from the sliding surface of the orbiting scroll. For this reason, a region radially inside the sliding contact surface is defined by the bearing member and the orbiting scroll. For this reason, the lubricating oil is held in the radially inner region.

At this time, in the radially inner region, the gas refrigerant easily moves upward, and the lubricating oil easily moves downward.

As a result, since lubricating oil having a relatively high proportion of gas refrigerant is supplied to the vicinity of the upper sliding portion of the Oldham ring, the upper sliding portion of the Oldham ring may be poorly lubricated and wear may increase. is there.

The present disclosure has an object to provide a horizontal scroll compressor in which a rotation preventing mechanism is lubricated.

According to one aspect of the present disclosure, a fixed scroll,
When the direction in which the axis extends is the axial direction, the compression chamber is disposed on one side in the axial direction with respect to the fixed scroll, turns around the axis, and sucks, compresses, and discharges the refrigerant between the fixed scroll and the fixed chamber. Orbiting scroll formed in
A support portion that supports the orbiting scroll from one side in the axial direction,
The horizontal scroll compressor, which is arranged so that the axial direction intersects the vertical direction,
A lubricating oil separator that separates the lubricating oil from the refrigerant discharged from the compression chamber and discharges the separated refrigerant;
A rotation preventing mechanism that has a plurality of sliding portions that slide while being displaced with the rotation of the orbiting scroll, and that restricts the rotation of the orbiting scroll,
A storage chamber forming unit that forms a mechanism storage chamber that stores the rotation prevention mechanism,
A lubricating oil path forming unit that forms a lubricating oil path that guides the lubricating oil separated from the refrigerant by the lubricating oil separating unit to the mechanism housing chamber;
A pressure reducing mechanism that narrows the lubricating oil path,
A discharge path forming unit that forms a discharge path having an entrance opening that opens into the mechanism storage chamber,
A gas refrigerant separated from the lubricating oil as the lubricating oil passes through the pressure reducing mechanism flows into the inlet opening from the mechanism housing chamber, and the gas refrigerant that has flowed in is discharged through the discharge path,
The uppermost part of the inlet opening is the uppermost part of the inlet opening, the uppermost sliding part of the plurality of sliding parts is the upper sliding part, and the upper sliding part is the lowermost part. The lowermost part of the upper sliding portion at the timing of is located at the lowermost position, and the uppermost portion of the entrance opening is located above the lowermost portion of the upper sliding portion.

As described above, it is possible to discharge the gas refrigerant from the mechanism storage chamber and leave the lubricating oil in the mechanism storage chamber. For this reason, the anti-rotation mechanism can be lubricated by the lubricating oil in the mechanism storage chamber.

Note that reference numerals in parentheses attached to the respective components and the like indicate an example of the correspondence between the components and the like and specific components and the like described in the embodiments described later.

It is a figure showing the section composition of the horizontal scroll compressor in a 1st embodiment. FIG. 2A is a cross-sectional view of the horizontal scroll compressor shown in FIG. 1 cut along a cross section orthogonal to the axis S. Part (b) is a cross-sectional view taken along the line IIa-IIa of part (a). (A) part is the figure which looked at the orbiting scroll single body in FIG. 1 from the axial direction one side. Part (b) is a cross-sectional view taken along the line IIIa-IIIa of part (a). Part (a) is a schematic diagram showing that the center Sp of the orbiting scroll is located below the center Kp of the fixed scroll. Part (b) is a cross-sectional view showing the position of the rotation preventing mechanism when the center Sp of the orbiting scroll is located below the center Kp of the fixed scroll, and corresponds to the part (a) of FIG. It is. Part (c) is a cross-sectional view showing the position of the rotation preventing mechanism when the center Sp of the orbiting scroll is positioned below the center Kp of the fixed scroll, and corresponds to the part (b) of FIG. It is. (A) is a schematic diagram showing that the center Sp of the orbiting scroll is located above the center Kp of the fixed scroll. Part (b) is a cross-sectional view showing the position of the rotation preventing mechanism when the center Sp of the orbiting scroll is located above the center Kp of the fixed scroll, and is a view corresponding to the part (a) of FIG. is there. Part (c) is a cross-sectional view showing the position of the rotation preventing mechanism when the center Sp of the orbiting scroll is located above the center Kp of the fixed scroll, and is a view corresponding to the part (b) of FIG. is there. FIG. 2 is a diagram illustrating a second sliding surface of a second annular disk portion of the thrust bearing portion in FIG. 1. FIG. 7 is a sectional view taken along the line VII-VII in FIG. 6. It is sectional drawing of the thrust bearing part in FIG. FIG. 2 is an enlarged cross-sectional view of a part of a horizontal scroll compressor in FIG. 1 around a turning scroll and a fixed scroll. It is a partial surface composition of the horizontal scroll compressor in the 1st modification of a 1st embodiment. It is a partial surface composition of the horizontal scroll compressor in the 2nd modification of a 1st embodiment. It is a figure showing the section composition of the horizontal scroll compressor in a 2nd embodiment. FIG. 13 is a cross-sectional view of the horizontal scroll compressor of FIG. 12 cut along a cross section orthogonal to the axis, showing a compression step of compressing the refrigerant in a second compression chamber. FIG. 13 is a sectional view taken along the line XIII-XIII in FIG. 13. It is a figure showing the section composition of the horizontal scroll compressor in a 2nd embodiment, and is a figure showing a suction process in which refrigerant is sucked in the 2nd compression room. It is a figure showing the section composition of the horizontal scroll compressor in a 3rd embodiment. It is a figure showing the partial section composition of the horizontal scroll compressor in a 4th embodiment. It is XV-XV sectional drawing in FIG. It is a figure showing composition of a rotation prevention mechanism in a 5th embodiment. FIG. 20 is a diagram showing a configuration of an upper pin-ring mechanism in FIG. 19. It is a figure showing composition of an upper pin-hole mechanism of a rotation prevention mechanism in a 6th embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings for the sake of simplicity.

(1st Embodiment)
FIG. 1 is a longitudinal sectional view showing the internal configuration of a horizontally mounted scroll compressor 10 according to the present embodiment.

The horizontal scroll compressor 10 uses carbon dioxide as a refrigerant, and forms a supercritical refrigeration cycle in which the pressure of carbon dioxide discharged from the compression chamber exceeds the critical pressure. The horizontal scroll compressor 10 of the present embodiment is applied to a vehicle air conditioner that air-conditions a vehicle interior.

横 The horizontal scroll compressor 10 according to the present embodiment is a semi-hermetic electric compressor in which an electric motor section 20 and a compression mechanism section 30 are accommodated in an airtight container 11 to which containers are connected by bolts.

The sealed container 11 includes a comp case 11a as a cylindrical casing, and an electric motor side end case 11b and a compression mechanism side end case 11c disposed on one side and the other side in the axial direction of the comp case 11a. Have.

軸 The axial direction of the comp case 11a is a direction in which the axis of the comp case 11a extends. The axial direction is a direction crossing the vertical direction in a state where the horizontal scroll compressor 10 is mounted on the vehicle.

吸入 A suction port 11d is provided on one side in the axial direction of the comp case 11a on the side of the sky improvement area. The suction port 11d is an opening for sucking the refrigerant flowing from the evaporator constituting the vehicle air conditioner into the suction chamber 11e in the comp case 11a.

The suction chamber 11e is formed on one side in the axial direction with respect to the main bearing 27 of the comp case 11a, and houses the motor unit 20 and the like.

The motor unit 20 includes a stator 22 fixed to the inner peripheral surface of the comp case 11a and a rotor 26 fixed to the rotating shaft 24, and constitutes a three-phase AC motor. The stator 22 is configured by winding a three-phase stator coil around a stator core. The rotor 26 forms a plurality of magnetic poles arranged in the circumferential direction.

Here, the rotation shaft 24 is arranged so that its axis coincides with the axis of the comp case 11a. A crank mechanism 24a is provided on the other side of the rotating shaft 24 in the axial direction. The axis of the crank mechanism 24a is parallel to the axis of the rotating shaft 24.

The crank mechanism 24a and the rotating shaft 24 constitute an integrally molded product. As a result, the crank mechanism 24a revolves around the axis of the rotating shaft 24 as the rotating shaft 24 rotates.

The rotating shaft 24 is provided with a lubricating oil path 24b and lubricating oil paths 24c, 24d, 24e. The lubricating oil path 24b and the lubricating oil path 24c constitute a first lubricating oil path.

The lubricating oil path 24b is a flow path for supplying the lubricating oil from the high-pressure lubricating oil chamber 40 described later to the main bearing 27, the bearing 29, and the crank mechanism housing chamber (that is, the bearing housing chamber) 38. The lubricating oil path 24b is provided to extend along the axis S of the rotating shaft 24. The lubricating oil passage 24b has an inlet formed on the other axial side of the rotary shaft 24. Hereinafter, the direction in which the axis S extends is referred to as the axial direction.

The lubricating oil path 24c is a flow path for supplying the lubricating oil from the lubricating oil path 24b to the main bearing 27 and the crank mechanism storage chamber 38. The lubricating oil path 24d is a flow path that supplies the lubricating oil from the lubricating oil path 24b to the crank bearing 32c. The lubricating oil path 24e is a flow path that supplies the lubricating oil from the lubricating oil path 24b to the bearing unit 29.

の う ち The other axial side of the rotary shaft 24 is rotatably supported by the main bearing 27 around the axis. The main bearing 27 is fixed to the inner peripheral surface of the comp case 11a. The main bearing 27 supports the orbiting scroll 32 from one axial side via a thrust bearing 100 so that the orbiting scroll 32 described later can be orbited.

の う ち One side of the rotating shaft 24 in the axial direction is supported by the bearing 29 so as to be rotatable about the axis. The bearing portion 29 is fixed to the comp case 11a using bolts 29a and the like.

The compression mechanism 30 is disposed on the other side in the axial direction with respect to the electric motor 20 in the comp case 11a. The compression mechanism 30 includes an orbiting scroll 32 and a fixed scroll 34.

The orbiting scroll 32 includes a base portion 32a that extends in a direction orthogonal to the axial direction, and a tooth portion 32b that protrudes from the base portion 32a to the other side in the axial direction and that is formed along an involute curve.

At the base 32a of the orbiting scroll 32, a pressure reduction control mechanism 42 is provided as a pressure reduction mechanism that narrows a lubricating oil path formed between the high-pressure lubricating oil chamber 40 and the lubricating oil path 24b. The lubricating oil path is constituted by lubricating oil paths 44 and 43.
The pressure reduction control mechanism 42 forms a lubricating oil path having a flow path cross-sectional area smaller than the flow path cross-sectional areas of the lubricating oil paths 44 and 43. A lubricating oil path 43 that allows the lubricating oil that has passed through the pressure reduction control mechanism 42 to flow through the lubricating oil path 24 b is provided at the base 32 a of the orbiting scroll 32.

The lubricating oil paths 44, 43 are constituted by the lubricating oil path 43 and the lubricating oil path 44. The lubricating oil path 44 is formed by a lubricating oil path forming part 44 a of the fixed scroll 34. The lubricating oil paths 24b and 24c are formed by lubricating oil path forming portions 24h and 24i of the rotating shaft 24. The lubricating oil path 120 is a second lubricating oil path formed by the lubricating oil path forming portion 120a of the main bearing 27.

The lubricating oil path 43 is intermittently connected to the lubricating oil path 44 as the orbiting scroll 32 turns. The lubricating oil path 44 is formed to guide the lubricating oil from the high-pressure lubricating oil chamber 40 to the pressure reduction control mechanism 42 in the fixed scroll 34.

The orbiting scroll 32 includes a crank bearing 32c that rotatably holds the crank mechanism 24a. The crank bearing portion 32c protrudes from the base portion 32a to one side in the axial direction of the crank mechanism 24a, and is formed in a cylindrical shape around the axis of the crank mechanism 24a.

ク ラ ン ク A crank mechanism housing chamber 38 for housing the crank mechanism 24a and the balancer weight 36 is provided between the base 32a of the orbiting scroll 32 and the main bearing 27.

The balancer weight 36 is supported by the rotating shaft 24. The balancer weight 36 rotates with the rotation shaft 24 and plays a role of canceling the weight imbalance in the orbiting scroll 32 with respect to the axis S.

In the balancer weight 36 of the present embodiment, a radially outer portion 36a around the axis S (see FIG. 9) overlaps a part of an inlet opening 120b of the lubricating oil path 120 described later so as to overlap. 36 and a main bearing 27 are arranged.

The fixed scroll 34 is arranged on the other side in the axial direction with respect to the orbiting scroll 32. The fixed scroll 34 is fixed to the main bearing 27.

The fixed scroll 34 includes a base portion 34a that extends in a direction orthogonal to the axial direction, and a tooth portion 34b that protrudes from the base portion 34a to one side in the axial direction and that is formed along an involute curve. The base 34 a of the fixed scroll 34 is arranged to face the base 32 a of the orbiting scroll 32.

圧 縮 Compression chambers 50a and 50b, which will be described later, are formed between the base portion 34a and the tooth portion 34b of the fixed scroll 34 and the base portion 32a and the tooth portion 32b of the orbiting scroll 32 according to the present embodiment. The compression chambers 50a and 50b suck the refrigerant sucked from the suction port 11d, compress it, and discharge it. The compression chamber 50a is disposed radially inward of the compression chamber 50b about the axis S. The compression chamber 50a corresponds to a first compression chamber, and the compression chamber 50b corresponds to a second compression chamber.

A high-pressure discharge channel 51 that discharges high-pressure refrigerant from the compression chamber 50 a to the discharge chamber 60 is provided at the base 34 a of the fixed scroll 34. A check valve 62 is provided on the discharge chamber 60 side of the high-pressure discharge channel 51.

The discharge chamber 60 is formed between the compression mechanism side end case 11c and the fixed scroll 34. A lubricating oil separating mechanism (that is, a lubricating oil separating section) 63 and a high-pressure lubricating oil chamber 40 are provided in the compression mechanism side end case 11c. The lubricating oil separating mechanism 63 separates the lubricating oil from the gas refrigerant that has passed through the discharge chamber 60.
The refrigerant is dissolved in the lubricating oil separated from the gas refrigerant by the lubricating oil separating mechanism 63. The high-pressure lubricating oil chamber 40 stores the lubricating oil separated from the gas refrigerant by the lubricating oil separating mechanism 63. Thus, the refrigerant is dissolved in the lubricating oil in the high-pressure lubricating oil chamber 40.

自 A rotation preventing mechanism 70 that regulates rotation of the orbiting scroll 32 is disposed between the orbiting scroll 32 and the fixed scroll 34. An Oldham ring is used as the rotation prevention mechanism 70 of the present embodiment. Details of the rotation prevention mechanism 70 will be described later.

In the suction chamber 11e of the present embodiment, the refrigerant flowing through the suction port 11d is radially outward with respect to the rotor 26 around the axis S and below the rotor 26 in the vertical direction. A refrigerant path 11f that leads to 50a and 50b is provided.

冷媒 In the comp case 11a, a coolant path 11g is provided radially outside the main bearing 27 around the axis S and below the main bearing 27 in the vertical direction. The refrigerant path 11g is a flow path that guides the refrigerant that has passed through the refrigerant path 11f to the compression chambers 50a and 50b. The refrigerant path 11g is disposed below the fixed scroll 34 and the orbiting scroll 32 in the vertical direction.

In the comp case 11a, a refrigerant path 11h is provided radially outside the fixed scroll 34 and the orbiting scroll 32 around the axis S and below the fixed scroll 34 and the orbiting scroll 32 in the vertical direction. ing.
The refrigerant path 11h is a flow path for guiding the refrigerant that has passed through the refrigerant path 11g to the compression chambers 50a and 50b. The refrigerant paths 11h and 11g are arranged radially outward with respect to the rotor 26 about the axis S and below the rotor 26 in the vertical direction.

The fixed scroll 34 is provided with a refrigerant path 11i as an internal refrigerant path for guiding the refrigerant that has passed through the refrigerant path 11h to the compression chambers 50a and 50b.

The refrigerant path 11g is formed by the refrigerant path forming part 12a of the main bearing 27. The refrigerant paths 11h and 11i are formed by fixed scrolls 12b and 12c.

In the present embodiment, a discharge path 90 described later (that is, a first discharge path) Path) is provided. The discharge path 90 is a path for discharging the gas refrigerant from the rotation prevention mechanism storage chamber (that is, the mechanism storage chamber) 34c to the suction chamber 11e. The discharge path 90 is formed by a discharge path forming portion 90a of the main bearing 27.

ス ラ A thrust bearing 100 is provided between the orbiting scroll 32 and the main bearing 27. The thrust bearing 100 is supported by the main bearing 27 and supports the orbiting scroll 32 from one side in the axial direction so as to be orbitable. Details of the thrust bearing 100 will be described later.

Next, details of the structure of the rotation preventing mechanism 70 of the present embodiment will be described with reference to FIGS.

The rotation preventing mechanism 70 is supported so as to be slidable in the vertical direction with respect to the fixed scroll 34.

The anti-rotation mechanism 70 includes a ring portion 71 and keys 72, 73, 74, and 75. The ring portion 71 is formed in a ring shape around the axis B. The axis B of the ring portion 71 is arranged parallel to the axis S of the rotating shaft 24.

The ring portion 71 is disposed in the rotation preventing mechanism storage chamber 34 c of the fixed scroll 34. The anti-rotation mechanism storage chamber 34c is formed by the anti-rotation mechanism storage chamber forming portion 34f (see FIG. 1) of the fixed scroll 34 so as to be recessed from one side in the axial direction to the other side. The rotation prevention mechanism storage chamber 34c is formed in a ring shape about the axis R. The axis R is arranged parallel to the axis B.

The key 72 is arranged at the lowermost side of the ring portion 71. The key 72 is formed to protrude from the ring portion 71 to the other side in the axial direction. The key 72 is housed in the key groove 80 of the fixed scroll 34.

The key groove portion 80 is disposed at the lowermost side of the rotation prevention mechanism storage chamber 34c. The key groove portion 80 is formed so as to be recessed from the bottom surface 34d (see FIG. 3) of the rotation preventing mechanism storage chamber 34c to the other axial side.

溝 The groove forming portion 80a of the fixed scroll 34 that forms the key groove portion 80 is configured such that the key 72 is movable in the vertical direction. On one side and the other side in the width direction of the key 72, sliding surfaces 72a and 72b which slide on the groove forming portion 80a are formed. The width direction is a direction orthogonal to the axial direction and parallel to the horizontal direction.

The key 73 is arranged at the uppermost position in the ring portion 71. The key 73 is formed so as to protrude from the ring portion 71 to the other side in the axial direction. The key 73 is housed in the key groove 81 of the fixed scroll 34. The key groove portion 81 is disposed at the uppermost position in the rotation prevention mechanism storage chamber 34c. The key groove portion 81 is formed so as to be recessed from the bottom surface 34d of the rotation preventing mechanism storage chamber 34c to the other axial side.

溝 The groove forming portion 81a of the fixed scroll 34, which forms the key groove portion 81, is configured such that the key 73 can move in the vertical direction. On one side and the other side in the width direction of the key 73, sliding surfaces 73a and 73b that slide on the groove forming portion 81a are formed.

The key 74 is arranged on the other side in the width direction of the ring portion 71. The key 74 is formed so as to protrude from the ring portion 71 to one side in the axial direction. The key 74 is housed in the key groove 82 of the orbiting scroll 32 (see FIG. 3). The key groove portion 82 is formed so as to be recessed to one side in the width direction in the orbiting scroll 32.

The groove forming portion 82a of the orbiting scroll 32 that forms the key groove portion 82 is configured to be movable in the width direction by the key 74. Sliding surfaces 74a and 74b which slide on the groove forming portion 82a are formed on the key region improving side and the lower side of the key 74.

The key 75 is arranged on the other side in the width direction of the ring portion 71. The key 75 is formed so as to project from the ring portion 71 to one side in the axial direction. The key 75 is housed in a key groove 83 (see FIG. 3) of the orbiting scroll 32. The key groove portion 83 is formed so as to be recessed on one side in the width direction in the orbiting scroll 32.

溝 The groove forming portion 83a of the orbiting scroll 32 which forms the key groove portion 83 is configured to be movable in the width direction by the key 75. Sliding surfaces 75a and 75b which slide on the groove forming portion 83a are formed on the key region improving side and the lower side of the key 75.

In the rotation preventing mechanism 70 configured as described above, the ring portion 71 reciprocates in the vertical direction with the ring portion 71 being supported by the groove forming portions 80a and 81a with the turning of the orbiting scroll 32 (FIGS. 4 and 5). reference). At this time, the sliding surfaces 72a and 72b slide vertically with respect to the groove forming portion 80a. The sliding surfaces 73a and 73b slide vertically with respect to the groove forming portion 81a.

FIG. 4 shows the anti-rotation mechanism 70 at the timing when the anti-rotation mechanism 70 is located at the lowest position. FIG. 5 shows the rotation prevention mechanism 70 at the timing when the rotation prevention mechanism 70 is located at the uppermost position.

FIG. 4 shows that the distance between the lowermost part of the sliding surfaces 73a and 73b (hereinafter, referred to as the lowermost part) and the lowermost part of the fixed scroll 34 is L. I have. FIG. 5 shows that the distance between the lowermost part of the sliding surfaces 73a and 73b and the lowermost part of the fixed scroll 34 is (L + α). α is a distance where α> 0 holds.

に In addition, the orbiting scroll 32 reciprocates in the width direction while the ring portion 71 is supported by the groove forming portions 82a and 83a. At this time, the sliding surfaces 74a and 74b slide in the width direction with respect to the groove forming portion 82a. The sliding surfaces 75a and 75b slide in the width direction with respect to the groove forming portion 83a.

The uppermost part (hereinafter referred to as the uppermost part) of the entrance opening 91 of the discharge path 90 of the present embodiment, which opens into the rotation prevention mechanism storage chamber 34c, is located below the lowermost part of the key 73 as the upper sliding part. Located on the Tenchi improvement side. The lowermost part of the entrance opening 91 (hereinafter, referred to as the lowermost part) is located on the side of the sky region higher than the lowermost part of the key 73 as the upper sliding part. The key 73 constitutes the uppermost sliding portion of the keys 72, 73, 74, 75.

Next, the structure of the thrust bearing 100 of the present embodiment will be described with reference to FIGS.

The thrust bearing 100 is arranged on one axial side with respect to the lubricating oil path 120. The thrust bearing 100 includes annular disk portions 100a and 100b. The annular disk portions 100a and 100b are each formed in a ring shape with the axis S as a center. The annular disk portion 100a corresponds to the first annular disk portion, and the annular disk portion 100b corresponds to the second annular disk portion.

The annular disk portion 100a is a fixed bearing portion supported by the main bearing 27. On the other side in the axial direction of the annular disk portion 100a, a sliding surface 101a that slides on the annular disk portion (that is, the swivel bearing portion) 100b is formed. The sliding surface 101a corresponds to a first sliding surface.

The annular disk portion 100b is supported by the orbiting scroll 32. A sliding surface 101b that slides on the annular disk portion 100a is formed on one side of the annular disk portion 100b in the axial direction. The sliding surface 101b corresponds to the second sliding surface.

凹 部 A concave portion 103 is formed on the inner side in the radial direction about the axis S of the sliding surface 101b so as to be concave on the other side in the axial direction. The recess 103 is opened radially inward of the sliding surface 101 about the axis S.

複数 A plurality of protrusions 104 are arranged in the recess 103. The plurality of protrusions 104 are formed in a columnar shape protruding from the bottom in the recess 103 to one side in the axial direction. A pressure-receiving surface (that is, a pressure-receiving portion) 104a that receives a force from the sliding surface 101a of the annular disk portion 100a is provided on one axial side of each of the plurality of protrusions 104. The plurality of protrusions 104 are dispersedly arranged in the recess 103. The recess 103 plays a role of retaining the lubricating oil. Therefore, each of the plurality of protrusions 104 is surrounded by the lubricating oil in the recess 103.

(4) Each of the pressure receiving surfaces 104a of the plurality of protrusions 104 slides on the slide surface 101a of the annular disk portion 100a in a state where the lubricating oil in the concave portion 103 is supplied and lubricated. A blocking portion 102 for blocking the lubricating oil in the recess 103 is formed radially outward of the sliding surface 101 with respect to the concave portion 103 around the axis S.

の う ち The radially inner end portion 110 of the annular disk portion 100a of the present embodiment constitutes a protruding portion of the main bearing 27 that projects radially inward from the inner peripheral surface 27a. The radially inner tip portion 110 is formed in an annular shape about the axis S. The inner peripheral surface 27a of the main bearing 27 is formed in an annular shape about the axis S. The inner peripheral surface 27a forms a bearing storage forming portion that forms the crank mechanism storage chamber 38 radially inward of the inner peripheral surface 27a.

Specifically, the diameter of the inner peripheral surface 27a centered on the axis S is φDb, and the diameter of the annular disk portion 100a centered on the axis S is φDp. The inner peripheral surface 27a and the annular disk portion 100a of the thrust bearing 100 are configured so that φDb> φDp is satisfied.

潤滑 A lubricating oil path 120 is provided on one side of the main bearing 27 in the axial direction with respect to the annular disk portion 100a and on the lower side in the vertical direction with respect to the crank bearing portion 32c. The lubricating oil path 120 is a flow path that guides the lubricating oil in the crank mechanism housing chamber 38 to the rotation prevention mechanism housing chamber 34c.

Specifically, the lubricating oil path 120 has an inlet opening 120b that opens into the crank mechanism housing chamber 38. The inlet opening 120b (see FIG. 9) is formed in the inner peripheral surface 27a.

Next, the operation of the horizontal scroll compressor 10 of the present embodiment will be described.

First, when three-phase AC power is supplied to the stator coil of the stator 22, a rotating magnetic field is generated in the rotor 26 from the stator coil. The rotor 26 is synchronized with the rotating magnetic field. Accordingly, the rotation shaft 24 rotates about the axis S. Therefore, the balancer weight 36 rotates together with the rotating shaft 24.

At this time, the rotating shaft 24 applies a turning force to the orbiting scroll 32 via the crank mechanism 24a. Therefore, the orbiting scroll 32 orbits about the axis S with respect to the fixed scroll 34. Accordingly, compression chambers 50a and 50b are formed between the orbiting scroll 32 and the fixed scroll 34. The compression chambers 50a and 50b suck, compress, and discharge the refrigerant.

Specifically, the compression chamber 50b sucks, compresses, and discharges low-pressure refrigerant through the suction port 11d, the suction chamber 11e, and the refrigerant paths 11f, 11g, 11h, and 11g. The refrigerant discharged from the compression chamber 50b becomes a low-pressure low-temperature refrigerant in the refrigeration cycle. The low-pressure low-temperature refrigerant is sucked again by the compression chamber 50a, compressed, and discharged.

高 圧 The high-pressure gas refrigerant discharged from the compression chamber 50 a flows to the discharge chamber 60 through the high-pressure discharge channel 51. The lubricating oil of the high-pressure gas refrigerant from the discharge chamber 60 is separated by the lubricating oil separating mechanism 63.

The high-pressure refrigerant from which the lubricating oil has been removed by the lubricating oil separating mechanism 63 is discharged toward the condenser from the discharge port 63a. On the other hand, the lubricating oil separated from the high-pressure refrigerant from the discharge chamber 60 by the lubricating oil separating mechanism 63 is stored in the high-pressure lubricating oil chamber 40.

At this time, the orbiting scroll 32 orbits with respect to the fixed scroll 34. Therefore, the pressure reduction control mechanism 42 intermittently communicates with the lubricating oil path 44. Therefore, the lubricating oil in the high-pressure lubricating oil chamber 40 is introduced into the depressurizing control mechanism 42 in a state where the depressurizing control mechanism 42 communicates with the lubricating oil path 44.

Thereby, the lubricating oil that has passed through the pressure reduction control mechanism 42 flows through the lubricating oil path 43 to the lubricating oil path 24b. The lubricating oil from the lubricating oil path 24b is supplied to the main bearing 27, the bearing part 29, the crank mechanism storage chamber 38, and the crank bearing part 32c through the lubricating oil paths 24c, 24d, and 24e. Therefore, the main bearing 27, the bearing portion 29, and the crank bearing portion 32c are each lubricated by the lubricating oil.

Here, as the orbiting scroll 32 orbits with respect to the fixed scroll 34, the orbiting scroll 32 reciprocates in the width direction with respect to the rotation preventing mechanism 70. At this time, the rotation prevention mechanism 70 reciprocates in the vertical direction with respect to the fixed scroll 34 while receiving the rotation force of the orbiting scroll 32.

At this time, the sliding surfaces 72a and 72b of the key 72 slide vertically with respect to the groove forming portion 80a. The sliding surfaces 73a and 73b of the key 73 slide vertically with respect to the groove forming portion 81a. The sliding surfaces 74a and 74b of the key 74 slide in the width direction with respect to the groove forming portion 82a. The sliding surfaces 75a and 75b of the key 75 slide in the width direction with respect to the groove forming portion 83a.

Here, at the timing when the uppermost key 73 among the keys 72, 73, 74, and 75 (that is, the plurality of sliding portions) is located at the lowermost position in the vertical direction, the sliding surfaces 73a and 73b of the keys 73 Of the lowermost portion is referred to as the lowermost portion of the upper sliding portion.

(4) The uppermost part (hereinafter, referred to as the uppermost part) of the entrance opening 91 of the discharge path 90 is disposed closer to the sky region than the lowermost part of the upper sliding part. Further, the lowermost part of the entrance opening 91 (hereinafter, referred to as the lowermost part) is disposed on the upper side of the upper side of the upper sliding part on the upper side of the sky region.

On the other hand, when the lubricating oil from the high-pressure lubricating oil chamber 40 is depressurized by the depressurization control mechanism 42, the refrigerant dissolved in the lubricating oil generates depressurized foam. In the rotation prevention mechanism storage chamber 34c, it is separated into lubricating oil and gas refrigerant. Therefore, the gas refrigerant flows from the rotation prevention mechanism storage chamber 34c into the suction chamber 11e through the discharge path 90.

伴 い Accordingly, lubricating oil having a small amount of gas refrigerant component and excellent in sliding characteristics remains in the rotation preventing mechanism storage chamber 34c. For this reason, the sliding surfaces 72a and 72b of the key 72, the sliding surfaces 73a and 73b of the key 73, the sliding surfaces 74a and 74b of the key 74, and the sliding surfaces 75a and 75b of the key 75 are formed in the rotation preventing mechanism storage chamber 34c. Lubricated by the lubricating oil inside. Thereby, the reliability of the rotation prevention mechanism 70 can be reliably ensured.

The amount of gas refrigerant discharged from the rotation prevention mechanism storage chamber 34c into the suction chamber 11e through the discharge path 90 is extremely smaller than the amount of gas refrigerant drawn into the suction chamber 11e from the suction port 11d. For this reason, the gas refrigerant from the discharge path 90 flows into the refrigerant path 11f located on the lower side in the vertical direction in the suction chamber 11e in a short time.

Therefore, there is no heat effect such as the temperature of the electric motor unit 20 being raised due to the gas refrigerant from the discharge path 90. Thus, the electric motor unit 20 is cooled by the gas refrigerant drawn into the suction chamber 11e from the suction port 11d, and can be operated in a highly efficient state without an increase in copper loss.

When the rotation preventing mechanism housing chamber 34c is filled with the lubricating oil, the lubricating oil can be discharged from the rotation preventing mechanism housing chamber 34c to the suction chamber 11e through the discharge path 90. Thus, it is possible to suppress the temperature of the lubricating oil from being increased by the lubricating oil separating mechanism 63.

伴 い Accordingly, the temperature rise of the compression chambers 50a and 50b can be suppressed, which is effective for forming the compression chambers 50a and 50b, and the compressor efficiency is improved. Further, it is possible to suppress the seizure of the sliding part due to the temperature rise of the lubricating oil. Then, the lubricating oil can be returned to the inside of the suction chamber 11e, and can be returned to the compression chambers 50a and 50b together with the refrigerant gas.

According to the above-described embodiment, the horizontal scroll compressor 10 includes the fixed scroll 34 and the orbiting scroll 32, and is arranged so that the axial direction intersects (for example, orthogonally) with the vertical direction.

When the direction in which the axis S extends is defined as the axial direction, the orbiting scroll 32 is disposed on one side in the axial direction with respect to the fixed scroll 34, orbits around the axis S, sucks in the refrigerant, compresses and discharges the refrigerant. The compression chambers 50 a and 50 b are formed between the compression chambers 50 a and 50 b. The main bearing 27 constitutes a supporting portion that supports the orbiting scroll 32 from one side in the axial direction.

The lubricating oil separating mechanism 63 forms a lubricating oil separating unit that separates the lubricating oil from the high-pressure gas refrigerant discharged from the compression chambers 50a and 50b and discharges the gas refrigerant from which the lubricating oil has been separated. The rotation preventing mechanism 70 has keys (that is, sliding portions) 72, 73, 74, and 75 that slide while being displaced in the vertical direction in accordance with the rotation of the orbiting scroll 32, and regulate the rotation of the orbiting scroll 32. I do.

The fixed scroll 34 includes a rotation preventing mechanism storage chamber forming part 34f that forms a rotation preventing mechanism storage chamber 34c that stores the rotation preventing mechanism 70.

A lubricating oil path 44, a lubricating oil path 24b of the rotating shaft 24, a lubricating oil path 24c, and a lubricating oil path 120 are provided to guide the lubricating oil separated from the refrigerant by the lubricating oil separating mechanism 63 to the rotation prevention mechanism storage chamber 34c. Have been. The horizontal scroll compressor 10 includes a decompression control mechanism 42 that narrows a lubricating oil path through which lubricating oil flows from the lubricating oil separating mechanism 63 to the rotation prevention mechanism storage chamber 34c.

The fixed scroll 34 has an entrance opening 91 that opens into the rotation prevention mechanism storage chamber 34c, and forms a discharge path 90 through which the lubricating oil in the rotation prevention mechanism storage chamber 34c is discharged to the suction chamber 11e. And a discharge path forming unit 90a.

The key 73 located at the uppermost position among the keys 72 and 73 is an upper sliding portion. At the timing when the upper sliding portion is located at the lowermost portion, the lowermost portion of the upper sliding portion is defined as the lowermost portion.

(4) The uppermost uppermost portion of the entrance openings 91 located on the upper side of the upper part of the entrance opening 91 is located on the upper side of the Tenri district rather than the lowermost portion of the upper sliding portion. Specifically, the lowermost part located at the lowermost part of the entrance openings 91 of the discharge path 90 is formed on the upper side of the upper part of the upper sliding part on the side of the sky region.

Therefore, when the lubricating oil from the high-pressure lubricating oil chamber 40 is depressurized by the depressurizing control mechanism 42, the lubricating oil is separated into the lubricating oil and the gas refrigerant in the rotation prevention mechanism storage chamber 34c. Therefore, the gas refrigerant flows from the rotation prevention mechanism storage chamber 34c into the suction chamber 11e through the discharge path 90.

潤滑 Accordingly, lubricating oil remains in the rotation prevention mechanism storage chamber 34c. For this reason, the sliding surfaces 72a and 72b of the key 72, the sliding surfaces 73a and 73b of the key 73, the sliding surfaces 74a and 74b of the key 74, and the sliding surfaces 75a and 75b of the key 75 are formed in the rotation preventing mechanism storage chamber 34c. Lubricated by the lubricating oil inside. Thereby, abrasion can be prevented and sliding resistance can be reduced. As a result, it is possible to prevent a decrease in the reliability and performance of the rotation preventing mechanism 70.

In the present embodiment, since the lubricating oil from the high-pressure lubricating oil chamber 40 passes through the pressure reduction control mechanism 42 and is reduced to a predetermined pressure before being supplied to each sliding portion, the reliability of each sliding portion is ensured. be able to.

In the present embodiment, the lubricating oil and the refrigerant gas are discharged from the rotation preventing mechanism storage chamber 34c to the suction chamber 11e through the discharge path 90, and the entire amount of the lubricating oil and the refrigerant gas is supplied to the compression chambers 50a and 50b and utilized for forming the compression chamber. It is possible to reduce leakage loss during compression.

で は In the present embodiment, the motor efficiency can be expected to be improved by reliably cooling the electric motor unit 20 by the low-pressure refrigerant sucked through the inlet 11d. Therefore, the reliability of the sliding portion can be improved at low cost, and an improvement in efficiency can be expected as a side effect.

In the present embodiment, the mist-like lubricating oil flowing into the suction chamber 11e from the suction port 11d is formed into droplets by collision with the inner wall of the comp case 11a and the electric motor unit 20 (particularly, the winding unit), and the gravity is reduced. Moves to the lower side of the comp case 11a. Then, the refrigerant moves to the refrigerant paths 11g and 11h flowing from the rotation preventing mechanism storage chamber 34c into the suction chamber 11e through the discharge path 90.

As a result, the lubricating oil accumulated on the lower side of the comp case 11a can be quickly supplied to the compression chambers 50a and 50b by utilizing the flow of the gas refrigerant, and only a very small amount of lubricating oil remains inside the comp case 11a. Become. Therefore, the accumulation of the lubricating oil in the comp case 11a can be suppressed, and the required amount of lubricating oil of the refrigeration and air conditioning equipment for maintaining the reliability and the compressor efficiency can be controlled.

In the present embodiment, the lubricating oil in the high-pressure lubricating oil chamber 40 is supplied to various sliding parts using the pressure difference between the high-pressure lubricating oil chamber 40 and the suction chamber 11e. By utilizing the refrigerant pressure difference to supply the lubricating oil in this way, a costly positive displacement lubricating oil pump is not required, and the reliability of each sliding portion and cost response can be simultaneously achieved.

In the present embodiment, when the balancer weight 36 approaches the inlet opening 120b of the lubricating oil path 120, the radially outer side 36a of the balancer weight 36 overlaps a part of the inlet opening 120b of the lubricating oil path 120. .

As a result, the lubricating oil having a high density is conveyed to the outer peripheral side of the crank mechanism storage chamber 38 by the centrifugal force of the balancer weight 36, and is quickly moved into the inlet opening 120 b of the lubricating oil path 120 by the rotational force of the balancer weight 36. Can be flowed into. Therefore, the lubricating oil in the crank mechanism housing chamber 38 can be supplied to the anti-rotation mechanism housing chamber 34c through the lubricating oil path 120 at an early stage.

In addition to this, the gas refrigerant and the lubricating oil in the crank mechanism storage chamber 38 are stirred by the rotation of the balancer weight 36, so that the lubricating oil is quickly transferred to the rotation preventing mechanism storage chamber 34c through the lubricating oil path 120 by the flow of the gas refrigerant. Can be supplied to

In the present embodiment, the diameter of the inner peripheral surface 27a forming the crank mechanism housing chamber 38 around the axis S is φDb, and the diameter of the annular disk portion 100a of the thrust bearing 100 around the axis S is φDp. And The inner peripheral surface 27a and the annular disk portion 100a of the thrust bearing 100 are configured so that φDb> φDp is satisfied.

Accordingly, since a weir having a height of (φDb−φDp) / 2 can be provided in the crank mechanism housing chamber 38, the lubricating oil in the crank mechanism housing chamber 38 can be blocked. Therefore, the lubricating oil in the crank mechanism housing chamber 38 can be supplied to the rotation preventing mechanism housing chamber 34c through the lubricating oil path 120 at an early stage.

In the present embodiment, the refrigerant pressure in the anti-rotation mechanism housing chamber 34c in which the sliding surfaces 72a, 72b, 73a, 73b... 74a, 74b and the like are arranged is substantially the same as the pressure in the suction chamber 11e. For this reason, a pressure reducing valve is not required between the rotation prevention mechanism storage chamber 34c and the suction chamber 11e.

For example, a differential pressure actuated valve or the like operates when a certain differential pressure is reached and discharges lubricating oil.However, in the time until operation, discharge cannot be performed, and when lubricating oil is discharged to a compression chamber, The performance may be degraded due to insufficient formation of the compression chamber or increased leakage, or the sliding part inside the compression may be worn. On the other hand, in the present embodiment, as described above, it is possible to supply oil to various sliding parts installed in a place where the refrigerant pressure is low by utilizing the refrigerant pressure difference, so that early refueling becomes possible.

In the present embodiment, the lubricating oil path 120 is provided on one axial side of the thrust bearing 100.

Here, when the lubricating oil path 120 is not provided, it is necessary to supply the lubricating oil in the crank mechanism housing chamber 38 to the rotation preventing mechanism housing chamber 34c through a small gap where the pressure loss in the thrust bearing 100 is large. .

On the other hand, in the present embodiment, as described above, the lubricating oil path 120 is provided on one axial side of the thrust bearing 100. For this reason, pressure loss can be reduced, and early lubrication to the anti-rotation mechanism storage chamber 34c becomes possible.

In the present embodiment, the discharge path 90 is provided above the main bearing 27 in the comp case 11a. The lubricating oil path 120 is disposed below the crank mechanism housing chamber 38 in the comp case 11a.

Therefore, when the motor unit 20 is stopped, a slight amount of lubricating oil is left on each sliding part, and the surplus lubricating oil accumulates on the lower side in the rotation prevention mechanism storage chamber 34c.

Therefore, the discharge path 90 is disposed below the crank mechanism storage chamber 38 as described above. Therefore, after the electric motor unit 20 is started, the lubricating oil mixed with the gas refrigerant is supplied from the crank mechanism housing chamber 38 to the lubricating oil sump below the rotation prevention mechanism housing chamber 34c through the discharge path 90.

Therefore, the lubricating oil accumulated under the rotation-preventing mechanism housing chamber 34c can be stirred, and the lubricating oil can be carried to the inlet opening 91 of the discharge path 90 together with the gas refrigerant. As a result, the lubricating oil can be supplied to the sliding surfaces 72a,.

In the present embodiment, a lubricating oil path for flowing the lubricating oil from the high-pressure lubricating oil chamber 40 to the rotation prevention mechanism storage chamber 34c and a refrigerant path for flowing the refrigerant from the suction port 11d to the compression chambers 50a and 50b are provided. Are provided independently.

Here, if the lubricating oil path and the refrigerant path are connected, the amount of gas refrigerant contained in the lubricating oil supplied to the rotation prevention mechanism storage chamber 34c increases.

On the other hand, in the present embodiment, as described above, the lubricating oil path and the refrigerant path are provided independently. For this reason, the amount of gas refrigerant contained in the lubricating oil supplied to the rotation prevention mechanism storage chamber 34c can be reduced. With this, it is possible to suppress a decrease in the viscosity of the lubricating oil supplied to the rotation prevention mechanism storage chamber 34c.

横 In addition, the horizontal scroll compressor 10 is heavy among functional components constituting a refrigeration cycle for a vehicle air conditioner, and is difficult to cool down to warm. Therefore, when the temperature is lower than that of other devices due to a change in the outside air temperature, the refrigerant gas is likely to aggregate and the liquid refrigerant is likely to accumulate. Therefore, by separating the lubrication path from the suction path, it is possible to suppress the liquid refrigerant from entering the sliding portions and taking out the lubricating oil from each sliding portion.

In some cases, a check valve or the like may be provided in the discharge port 63a or the suction port 11d, but this is not recommended because it leads to an increase in size and cost.

Here, the refrigerant path is constituted by refrigerant paths 11f, 11g, 11h, and 11i. The lubricating oil path includes a lubricating oil path 44, a lubricating oil path 43, a lubricating oil path 24b of the rotating shaft 24, a lubricating oil path 24c, and a lubricating oil path 120.

When the lubricating oil path 120 is not provided and the gap between the annular disc portions 100a and 100b of the thrust bearing 100 is extremely small, the lubrication flowing from the crank mechanism housing chamber 38 to the rotation prevention mechanism housing chamber 34c is provided. The fluidity of the oil decreases. As a result, the temperature of the lubricating oil increases due to the sliding heat, the viscosity of the lubricating oil decreases, and seizure may occur.

On the other hand, in the present embodiment, since the lubricating oil path 120 is provided as described above, the fluidity of the lubricating oil flowing from the crank mechanism housing chamber 38 to the rotation prevention mechanism housing chamber 34c can be increased. As a result, a decrease in the viscosity of the lubricating oil is suppressed, and the occurrence of seizure can be suppressed.

In the present embodiment, carbon dioxide is used as the refrigerant, and the pressure of carbon dioxide discharged from the compression chamber 50a exceeds the critical pressure.

二 酸化 炭素 Here, carbon dioxide has a higher pressure during operation and a rotation torque as high as about 1.5 times that of a CFC-based refrigerant (refrigerant), so that a large load also acts on the rotation prevention mechanism 70. Therefore, in order to secure reliability and performance, formation of an oil film and removal of sliding heat can be realized by creating a favorable lubricating environment. As a result, wear can be suppressed, and sliding loss can be reduced due to low friction.

In the present embodiment, the refrigerant paths 11g and 11h are arranged below the fixed scroll 34 and the orbiting scroll 32. The refrigerant paths 11g and 11h are arranged radially outward with respect to the rotor 26 about the axis S, and are arranged below the rotor 26.

Accordingly, since a positive displacement lubricating oil pump or the like is not used, the lubricating oil accumulated on the lower side of the comp case 11a is supplied to the compression chambers 50a and 50b early by utilizing the flow of the gas refrigerant without increasing the power. Therefore, only a very small amount of lubricating oil is left inside the comp case 11a.

Therefore, it is possible to suppress the accumulation of the lubricating oil inside the comp case 11a, and it is possible to control the amount of the lubricating oil necessary for the refrigeration and air-conditioning equipment for maintaining the reliability and the compressor efficiency.

In addition, loss due to stirring resistance during rotation of the rotor 26 and loss of efficiency are suppressed, and lubrication oil depletion at the sliding portion due to depletion of lubrication oil, seizure, and increase in cost due to enlargement of the lubricating oil separator. Can be suppressed.

凹 部 A concave portion 103 is formed on the sliding surface 101 of the annular disk portion 100b of the thrust bearing 100 of the present embodiment, which is recessed toward the other side in the axial direction on the radially inner side centered on the axis S. The recess 103 is opened radially inward of the sliding surface 101 about the axis S (that is, the crank mechanism housing chamber 38).

The lubricating oil is drawn into the concave portion 103 from all directions on the inner peripheral surface of the annular disk portion 100b by the orbiting movement of the orbiting scroll 32, and an oil film can be formed on the pressure receiving surfaces 104a of the plurality of projections 104. In particular, since the orbiting scroll 32 revolves, the sliding speed when the thrust bearing 100 is used for a scroll-type compressor is smaller than the sliding speed when the thrust bearing 100 is used for a device that rotates.

From the above, the lubricating oil can be drawn from all directions of the inner peripheral surface of the thrust bearing 100 to form an oil film, so that wear and seizure can be suppressed.

In the present embodiment, the compression mechanism 30 is mounted on a scroll compressor for a vehicle air conditioner. Therefore, in order to prioritize the traveling performance of the vehicle, the power supply to the vehicle air-conditioning compressor is temporarily stopped, and even in the case where intermittent operation in which the vehicle is quickly returned to frequently occurs, the effect of the present embodiment that realizes the early refueling is achieved. Is big.

潤滑 In the present embodiment, a lubricating oil having a compatibility of 1% or more with the refrigerant at room temperature is used. Lubricating oils (ie, compatible oils) that are compatible with the refrigerant, such as carbon dioxide and PAG, HFC, HFO and PVE, are used. The compatible oil has good solubility with the refrigerant, is easily dissolved in the refrigerant, and has high oil fluidity. Therefore, the lubricating oil discharged from the compression chambers 50a and 50b is likely to return to the compression chambers 50a and 50b. Therefore, the amount of the compatible oil discharged from the compression chambers 50a and 50b remaining in the refrigerant circuit (that is, the amount of the compatible oil flowing out of the horizontal scroll compressor 10 into the refrigerant circuit) can be reduced. Circuit design becomes easy.

However, when a lubricating oil that is compatible with the gas refrigerant is used, the decompressed foaming phenomenon of the dissolved gas occurs in the lubricating oil in the course of flowing through the lubrication path. In that case, the gas has a volume ten times that of the lubricating oil alone.

Therefore, the rotation of the balancer weight 36 stirs the gas refrigerant and the lubricating oil in the crank mechanism housing chamber 38, thereby conveying the lubricating oil by the flow of the gas refrigerant and quickly moving the lubricating oil to the rotation preventing mechanism housing chamber 34 c through the lubricating oil path 120. Can be supplied to
(Modification)
In the above-described first embodiment, the example in which the discharge path 90 is formed between the comp case 11a and the main bearing 27 has been described. Instead, as shown in FIGS. The bearing 27 may be provided.

(A) As shown in FIG. 10, when the outlet opening 92 of the discharge path 90 that opens to the suction chamber 11 e is located below the inlet opening 91, the lowest part of the inlet opening 91 is the upper side. The key 73 serving as a sliding portion is arranged on the side of the sky improvement area below the lowermost portion of the key 73. The lowermost part is the lowermost part of the entrance opening 91.

In FIG. 10, the uppermost portion of the entrance opening 91 is located closer to the sky region than the lowermost portion of the key 73 as the upper sliding portion.

(B) As shown in FIG. 11, when the outlet opening 92 of the discharge path 90 is located above the inlet opening 91, the uppermost portion of the inlet opening 91 that is located at the uppermost position is defined as an upper sliding portion. The key 73 is located on the side of the Tenchi area that is higher than the lowermost part.

In FIG. 11, the lowermost part of the entrance opening 91 is located closer to the sky region than the lowermost part of the key 73 as the upper sliding part.

(2nd Embodiment)
In the first embodiment, an example in which the gas refrigerant from the rotation prevention mechanism storage chamber 34c is discharged to the suction chamber 11e has been described. Instead, the gas refrigerant from the rotation prevention mechanism storage chamber 34c is transferred to the compression chamber 50b. The second embodiment for discharging will be described with reference to FIGS.

The present embodiment is different from the first embodiment only in the discharge flow path for discharging the gas refrigerant from the rotation prevention mechanism storage chamber 34c, and the other configurations are the same. Therefore, hereinafter, the discharge flow path for discharging the gas refrigerant from the rotation prevention mechanism storage chamber 34c will be mainly described, and the description of the other components will be omitted.

横 The horizontal scroll compressor 10 of the present embodiment is provided with a discharge path 130 (see FIGS. 12, 13, and 14) instead of the discharge path 90. The discharge path 130 is a second discharge path formed in the fixed scroll 34.

The discharge path 130 includes an inlet opening 140 opening in the key groove 81 and an outlet opening 121 opening in the working chamber 53. The working chamber 53 is an area surrounded by the base 34a and the teeth 34b of the fixed scroll 34 and the base 32a and the teeth 32b of the orbiting scroll 32. Part of the working chamber 53 constitutes the compression chambers 50a and 50b. The discharge path 130 is formed by the discharge path forming section 130a of the fixed scroll 34.

Here, the uppermost part (hereinafter, referred to as the uppermost part) of the inlet opening 140 is arranged on the side of the upper part of the upper side than the lowermost part of the upper sliding part. The lowermost part of the inlet opening 140 (hereinafter, referred to as the lowermost part) is disposed closer to the sky region than the lowermost part of the upper sliding part.

吸入 A suction port 123 and a discharge port 125 are opened in the working chamber 53 of the present embodiment. The suction port 123 communicates with the refrigerant path 11i (see FIG. 12). The discharge port 125 communicates with the high-pressure discharge flow path 51 (see FIG. 12).

The horizontal scroll compressor 10 of the present embodiment is different from the horizontal scroll compressor 10 of the first embodiment in the discharge operation for discharging the gas refrigerant from the rotation prevention mechanism storage chamber 34c.

Therefore, the discharging operation of the horizontal scroll compressor 10 of the present embodiment will be described below.
First, with the rotation of the rotor 26, the rotating shaft 24 applies a rotating force to the orbiting scroll 32 via the crank mechanism 24a. Therefore, the orbiting scroll 32 orbits about the axis S with respect to the fixed scroll 34. Accordingly, between the orbiting scroll 32 and the fixed scroll 34, the compression chambers 50a and 50b draw in the refrigerant, compress it, and discharge it.

As shown in FIG. 15, in a state where the space between the suction port 123 and the compression chamber 50b is opened by the orbiting scroll 32 and the fixed scroll 34, the low-pressure refrigerant flows from the suction chamber 11e to the refrigerant paths 11g, 11h, 11i, and the suction port. 123 is sucked into the compression chamber 50b through the working chamber 53.

At this time, the gas refrigerant from the rotation prevention mechanism storage chamber 34c passes through the discharge path 130 in a state where the space between the outlet opening 121 of the discharge path 130 and the compression chamber 50b is opened by the orbiting scroll 32 and the fixed scroll 34. It is sucked into the compression chamber 50b.

Then, as the orbiting scroll 32 orbits, the teeth 32b of the orbiting scroll 32 and the teeth 34b of the fixed scroll 34 come into contact at points P1 and P2. At this time, the space between the suction port 123 and the compression chamber 50b is closed by the orbiting scroll 32 and the fixed scroll 34. The space between the outlet opening 121 of the discharge path 130 and the compression chamber 50b is closed by the orbiting scroll 32 and the fixed scroll 34.

At this time, the compression chamber 50b is hermetically closed by the orbiting scroll 32 and the fixed scroll 34.

Thereafter, as the orbiting scroll 32 turns, the refrigerant in the compression chamber 50b is compressed, and the compressed refrigerant is discharged to the compression chamber 50a. The compression chamber 50 a into which the refrigerant has been discharged compresses the refrigerant and discharges the compressed high-pressure refrigerant from the discharge port 125 to the lubricating oil separation mechanism 63 through the high-pressure discharge flow path 51 and the discharge chamber 60. The subsequent operation is the same as in the first embodiment, and a description thereof will be omitted.

According to the present embodiment described above, the discharge path 130 is formed in the fixed scroll 34 so as to communicate between the rotation prevention mechanism storage chamber 34c and the compression chamber 50b.

(4) When the compression chamber 50b compresses the refrigerant, the fixed scroll 34 and the orbiting scroll 32 close the space between the discharge path 130 and the compression chamber 50b.

Before the compression chamber 50b starts compressing the refrigerant, the gas refrigerant in the anti-rotation mechanism storage chamber 34c is discharged in a state where the space between the discharge path 130 and the compression chamber 50b is opened by the fixed scroll 34 and the orbiting scroll 32. It is sucked into the compression chamber 50b through the passage 130.

As described above, while the lubricating oil passes through the pressure reduction control mechanism 42, the gas refrigerant separated from the lubricating oil is discharged from the rotation prevention mechanism storage chamber 34c to the compression chamber 50b, and the excess lubrication in the rotation prevention mechanism storage chamber 34c is discharged. Oil can be supplied to the compression chamber 50b.

Thus, the inlet opening 140 of the discharge path 130 is set at a height position at which the upper sliding portion of the rotation preventing mechanism 70 can be refueled. This allows the lubricating oil to be reliably supplied to the sliding surfaces 72a, 72b,... 75a, 75b of the rotation preventing mechanism 70, and allows the refrigerant gas to be discharged from the compression chamber 50b.

(4) Accordingly, the lubricating oil can be circulated without staying even after the lubricating oil is supplied to the rotation prevention mechanism storage chamber 34c, and an increase in the temperature of the lubricating oil due to sliding heat can be suppressed. Further, the lubricating oil can be returned into the compression chamber 50b, which can be utilized for forming the compression chamber, and the leakage loss during compression can be reduced. Further, the lubricating oil discharged from the rotation prevention mechanism storage chamber 34c is supplied to the compression chambers 50a and 50b earlier than when the lubricating oil is returned to the inside of the comp case 11a and supplied to the compression chambers 50a and 50b. it can.

In the present embodiment, the space between the outlet opening 121 of the discharge path 130 and the compression chamber 50b is opened before the compression chamber 50b is closed by the orbiting scroll 32 and the fixed scroll 34.

As a result, lubricating oil having a higher temperature than the refrigerant gas flowing into the compression chamber 50b from the suction port 123 heats the refrigerant gas before binding into the compression chamber 50b, thereby reducing the density and suppressing an increase in power. can do. Further, since the path length of the flow path of the lubricating oil from the rotation preventing mechanism storage chamber 34c to the compression chamber 50b can be minimized, the lubricating oil can be supplied to the compression chamber 50b at an early stage.

(Third embodiment)
In the second embodiment, the example in which the discharge path 130 that discharges the gas refrigerant from the rotation prevention mechanism storage chamber 34c to the compression chamber 50b is described. However, instead of this, the third embodiment in which the discharge path 90 in the first embodiment and the discharge path 130 in the second embodiment are combined will be described with reference to FIG.

In FIG. 16, the same reference numerals as those in FIGS. 1 and 15 denote the same components, and a description thereof will be omitted.

排出 The horizontal scroll compressor 10 of the present embodiment is provided with a discharge path 90 and a discharge path 130. The discharge route 90 is arranged on the side of the Tenchi district better than the discharge route 130.

Here, as in the second embodiment, the uppermost portion of the entrance opening 140 is located closer to the sky region than the lowermost portion of the upper sliding portion. The lowermost part of the inlet opening 140 is located on the side of the upper part of the sky above the lowermost part of the upper sliding part.

In the present embodiment configured as described above, a difference is provided between the positions (that is, the height positions) of the discharge path 90 and the discharge path 130 in the vertical direction. Here, in the rotation prevention mechanism storage chamber 34c, the lubricating oil having a high density of the gas refrigerant moves toward the sky region better than the lubricating oil having a low density of the gas refrigerant.

Therefore, the density of the lubricating oil on the upper side in the rotation prevention mechanism storage chamber 34c is reduced, and the density of the lubrication oil on the lower side in the rotation prevention mechanism storage chamber 34c in the top and bottom direction is increased.

Therefore, the gas refrigerant (or lubricating oil having a high refrigerant gas density) is mainly discharged to the suction chamber 11e from the discharge path 90 communicating from the rotation prevention mechanism storage chamber 34c to the suction chamber 11e. On the other hand, lubricating oil having a low density of the gas refrigerant is supplied into the compression chamber 50b through the discharge path 130.

For example, when the temperature of the gas refrigerant separated from the lubricating oil by the depressurized firing is higher than the temperature of the refrigerant gas sucked into the compression chamber 50b through the suction port 123, the gas refrigerant separated from the lubricating oil is sucked. When sucked into the compression chamber 50b through the port 123, the following problem occurs.

That is, since the gas refrigerant separated from the lubricating oil by the above-described depressurized firing in the compression chamber 50b heats the refrigerant gas drawn into the compression chamber 50b through the suction port 123, the volume efficiency is reduced.

On the other hand, in the present embodiment, as described above, lubricating oil having a low density of the gas refrigerant is supplied into the compression chamber 50b through the discharge path 130. Accordingly, it is possible to suppress heating of the refrigerant gas sucked into the compression chamber 50b through the suction port 123, and to suppress a decrease in volumetric efficiency.

On the other hand, the lubricating oil having a high density of the gas refrigerant is discharged from the discharge path 90 to the suction chamber 11e. Therefore, lubricating oil having a low density of gas refrigerant (that is, lubricating oil having a high density of the lubricating oil itself) can be used for lubricating the sliding portion of the anti-rotation mechanism 70 in the anti-rotation mechanism storage chamber 34c. .

Further, since the surplus lubricating oil can be supplied to the compression chamber 50b at an early stage, the formation and leakage of the compression chambers 50a and 50b are suppressed without lowering the volumetric efficiency as described above. Can be lubricated.

(Fourth embodiment)
In the first, second, and third embodiments, an example has been described in which the lubricating oil path 120 is disposed below the rotating shaft 24 in the vertical direction. However, instead of this, a fourth embodiment in which the lubricating oil path 120 is arranged on the side of the upper side with respect to the rotating shaft 24 will be described with reference to FIGS. 17 and 18, the same reference numerals as those in FIG. 1 denote the same components, and a description thereof will be omitted.

The arrangement of the lubricating oil path 120 is mainly different between the present embodiment and the above-described third to third embodiments.

Therefore, the arrangement relationship between the lubricating oil path 120, the discharge path 90, and the keys 73 and 72 of the rotation preventing mechanism 70 will be described.

旋回 The orbiting scroll 32 is disposed adjacent to the anti-rotation mechanism 70 on one side in the axial direction with respect to the anti-rotation mechanism 70.

Therefore, during the operation, the orbiting scroll 32 performs the orbiting motion adjacent to the rotation preventing mechanism 70. Therefore, the lubricating oil and the gas refrigerant in the rotation prevention mechanism storage chamber 34 c orbit in the same direction as the orbital movement of the orbiting scroll 32.

Particularly, in a high-speed rotation region where the orbiting speed of the orbiting scroll 32 is high, it becomes remarkable that the lubricating oil and the gas refrigerant flow as a orbital flow. Utilizing the characteristics, the following arrangement relation is also effective.

Hereinafter, for convenience of explanation, the opposite direction to the turning direction of the orbiting scroll 32 will be referred to as the anti-turning direction. When the orbiting scroll 32 orbits in the orbiting direction and advances from the lubricating oil path 120 toward the discharge path 90, the length of the path through which the orbiting scroll 32 passes is referred to as a first path length.

When the orbiting scroll 32 orbits in the anti-orbiting direction and advances from the lubricating oil path 120 toward the discharge path 90, the length of the path through which the orbiting scroll 32 passes is referred to as a second path length. In the present embodiment, the discharge path 90 is arranged at a position where the second path length is shorter than the first path length.

When the range formed between the lubricating oil path 120 and the discharging path 90 between the lubricating oil path 120 and the discharging path 90 is defined as a prohibited range, the sliding surfaces 73a, 73b, 72a, and 72b are provided in the rotation preventing mechanism storage chamber. 34c is arranged so as to avoid the prohibited range.

Here, the lubricating oil and the gas refrigerant flowing from the lubricating oil path 120 into the rotation prevention mechanism storage chamber 34c flow in the turning direction as shown by the arrow G in FIG. For this reason, the lubricating oil and the gas refrigerant flow from the lubricating oil path 120 in the rotation direction in the rotation prevention mechanism storage chamber 34c, and then flow to the suction chamber 11e through the discharge path 90. For this reason, in the above-mentioned prohibited range, there is a possibility that the lubricating oil is insufficient.

Therefore, in the present embodiment, as described above, the sliding surfaces 73a, 73b, 72a, 72b are arranged so as to avoid the prohibited range in the rotation prevention mechanism storage chamber 34c.

In other words, when the orbiting scroll 32 moves in the counterclockwise direction in FIG. 18 in the forward direction, the rotational position H of the lubricating oil path 120 with respect to the discharge path 90 (tentatively, the rotational direction 0 ° position). > 0 °. Therefore, the sliding surfaces 73a, 73b, 72a, 72b can be lubricated with the lubricating oil.

In addition, since the discharge path 90 is on the more retarded side than the lubricating oil path 120 and downstream of the swirling flow, it is possible to prevent the lubricating oil supplied to the rotation preventing mechanism 70 from being discharged early. it can.

(Fourth embodiment)
In the above-described first to third embodiments, an example in which an Oldham ring is used as the rotation preventing mechanism 70 has been described. However, instead of this, a fourth embodiment in which a pin-ring mechanism is used as the rotation preventing mechanism 70 is shown in FIG. This will be described with reference to FIG.

自 The anti-rotation mechanism 70 of the present embodiment includes pin- ring mechanisms 70a, 70b, 70c, 70d as shown in FIG. The pin- ring mechanisms 70a, 70b, 70c, 70d are arranged vertically and horizontally.

The pin-ring mechanism 70a includes a pin 200 and a ring 210 as shown in FIG. One side of the pin 200 is inserted into a hole of the fixed scroll 34. The other side of the pin 200 is inside the ring 210. The ring 210 is fitted in a hole of the orbiting scroll 32.

Pin- ring mechanisms 70b, 70c, 70d each include a pin 200 and a ring 210, similarly to pin-ring mechanism 70a.

リ ン グ In the rotation prevention mechanism 70 of the present embodiment configured as described above, the ring 210 rotates in accordance with the rotation of the orbiting scroll 32. Therefore, the inner peripheral surface of the ring 210 slides on the pin 200 while rotating.

In the present embodiment, the pin-ring mechanism 70a is the pin-ring mechanism located at the uppermost position among the pin- ring mechanisms 70a, 70b, 70c, 70d. Then, as shown in FIG. 20, at the timing when the lowermost part of the outer peripheral surface of the pin 200 contacts the lowermost part of the inner peripheral surface of the ring 210, The lower part is the lowermost part of the upper sliding part.

(Fifth embodiment)
In the fourth embodiment, an example in which a pin-ring mechanism is used as the rotation preventing mechanism 70 has been described. However, instead of this, a fifth embodiment using a pin-hole mechanism as the rotation preventing mechanism 70 will be described with reference to FIG. This will be described with reference to FIG.

The rotation preventing mechanism 70 of the present embodiment includes a plurality of pin-hole mechanisms and a plate 70A disposed between the orbiting scroll 32 and the fixed scroll 34. FIG. 21 shows only one pin-hole mechanism. The plurality of pin-hole mechanisms are dispersedly arranged in the vertical and horizontal directions, as in the case of the pin-ring mechanism of the fourth embodiment.

Hereinafter, for convenience of explanation, the uppermost pin-hole mechanism among the plurality of pin-hole mechanisms is referred to as a pin-hole mechanism 70e.

The pin-hole mechanism 70e includes pins 200a and 200b as shown in FIG. One of the pins 200 a is inserted into a hole of the fixed scroll 34. The other side of the pin 200a is in the hole of the plate 70A. One side of the pin 200b is in the hole of the plate 70A. The other side of the pin 200b is inserted into a hole of the orbiting scroll 32.

の う ち The remaining pin-hole mechanisms other than the pin-hole mechanism 70e among the plurality of pin-hole mechanisms are configured similarly to the pin-hole mechanism 70e.

で は In the rotation preventing mechanism 70 of the present embodiment configured as described above, the plate 70A is displaced in the vertical direction and the width direction (that is, in the direction perpendicular to the plane of FIG. 21) with the turning of the turning scroll 32.

Therefore, the pin 200a slides on the inner peripheral surface in the hole of the fixed scroll 34. At this time, the outer peripheral surface of the pin 200b slides on the inner peripheral surface in the hole of the orbiting scroll 32 while the pin 200b is displaced in the vertical direction and the width direction.

Therefore, as shown in FIG. 21A, in the pin-hole mechanism 70e, at the timing when the pin 200b is located at the lowermost position, the lowermost part of the outer peripheral surface of the pin 200b is slid upward. The lowermost part of the moving part. Alternatively, at the timing when the pin 200b is located at the lowermost position, the lowermost portion of the inner peripheral surface in the hole of the orbiting scroll 32 is set as the lowermost portion of the upper sliding portion.

(Other embodiments)
(1) In the first to fifth embodiments, an example was described in which a supercritical refrigeration cycle in which carbon dioxide was used as a refrigerant and the refrigerant pressure exceeded the critical pressure was configured. You may comprise the refrigeration cycle which becomes below a pressure.

(2) In the second and third embodiments, the example in which the discharge path 130 is provided inside the fixed scroll 34 has been described. Instead, the discharge path 130 is provided at the boundary surface between the fixed scroll 34 and the orbiting scroll 32. It may be provided. Alternatively, the same effect can be obtained even if the discharge path 130 is provided inside the orbiting scroll 32.

(3) In the first to fifth embodiments, examples in which the concave portion 103 and the plurality of protrusions 104 are provided in the annular disk portion 100b of the thrust bearing 100 have been described. However, instead of this, the recess 103 and the plurality of protrusions 104 may be provided in the annular disk portion 100a of the thrust bearing 100.

(4) In the first to fifth embodiments, the example has been described in which the radially inner end portion 110 of the annular disk portion 100a is projected radially inward from the inner peripheral surface 27a of the main bearing 27. However, instead of this, the radially inner end portion of the annular disk portion 100b may project radially inward from the inner peripheral surface 27a of the main bearing 27.

(5) In the first to fifth embodiments, the example in which the horizontal scroll compressor 10 is applied to the vehicle air conditioner has been described. However, instead of this, the horizontal scroll compressor 10 may be applied to a stationary air conditioner, a stationary refrigeration device, and the like.

Alternatively, the horizontal scroll compressor 10 may be applied to an air conditioner for a moving object such as a train, a train, an airplane, a ship, or a refrigeration device for a moving object.

(6) In the first to fifth embodiments, the anti-rotation mechanism 70 is disposed between the fixed scroll 34 and the orbiting scroll 32. Instead, the anti-rotation mechanism 70 is disposed between the main bearing 27 and the orbiting scroll 32. May be arranged.

(7) In the first to fifth embodiments, the example in which the discharge path 90 is provided above the rotation prevention mechanism 70 has been described. However, if the uppermost part of the entrance opening of the discharge path 90 is located higher than the lowermost part of the upper sliding part of the rotation prevention mechanism 70, the discharge path 90 is moved to a position other than the upper side of the rotation prevention mechanism 70. May be provided.

Thus, lubrication of the sliding portion of the anti-rotation mechanism 70 can be ensured. That is, the inlet opening 120b of the lubricating oil path 120 to be supplied to the rotation preventing mechanism 70 is configured to be directly supplied to each sliding portion of the rotation preventing mechanism 70. Thereby, lubricating oil can be supplied reliably and stably.

(9) In the first to fifth embodiments, the example in which the inner peripheral surface 27a forming the crank mechanism housing chamber 38 is formed in an arc shape centering on the axis S has been described.

However, the present invention is not limited to this. If the radially inner end portion 110 of the annular disk portion 100a protrudes radially inward of the inner peripheral surface 27a of the main bearing 27, the inner peripheral surface 27a is circular. It does not have to be formed in an arc shape.

(10) In the first to fifth embodiments, the example in which the annular disk portion 100a of the thrust bearing 100 is formed in an arc shape centered on the axis S has been described.

However, the present invention is not limited to this. If the radially inner end portion 110 of the annular disk portion 100a protrudes radially inward of the inner peripheral surface 27a of the main bearing 27, the annular disk portion 100a is It does not have to be formed in an arc shape.

(11) In the first to fifth embodiments, examples in which the Oldham ring, the pin-ring mechanism, and the pin-hole mechanism are used as the rotation preventing mechanism 70 have been described. However, a mechanism other than the Oldham ring, the pin-ring mechanism, and the pin-hole mechanism may be used as the rotation preventing mechanism 70.
(12) The present disclosure is not limited to the above-described embodiment, and can be appropriately modified. In addition, the above embodiments are not irrelevant to each other, and can be appropriately combined unless a combination is clearly impossible. In each of the above embodiments, it is needless to say that elements constituting the embodiments are not necessarily essential, unless otherwise clearly indicated as essential or in principle considered to be clearly essential. No. In each of the above embodiments, when a numerical value such as the number, numerical value, amount, range, or the like of the constituent elements of the exemplary embodiment is mentioned, it is particularly limited to a specific number when it is clearly stated that it is essential and in principle The number is not limited to the specific number unless otherwise specified. Further, in each of the above embodiments, when referring to the shape of components and the like, the positional relationship, and the like, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc., the shape, It is not limited to a positional relationship or the like. Further, in each of the above embodiments, when the acquisition of the external environment information of the vehicle (for example, the humidity outside the vehicle) from the sensor is described, the sensor is abolished, and the external environment information is obtained from the server or the cloud outside the vehicle. It is also possible to receive. Alternatively, it is also possible to abolish the sensor, obtain related information related to the external environment information from a server or a cloud outside the vehicle, and estimate the external environment information from the obtained related information.
(Summary)
According to the first aspect described in the first to fourth embodiments and some or all of the other embodiments, the horizontal scroll compressor includes a fixed scroll and an orbiting scroll.

The orbiting scroll is disposed on one side in the axial direction with respect to the fixed scroll when the direction in which the axis extends is the axial direction, and orbits around the axis to fix the compression chamber that sucks in the refrigerant, compresses and discharges the refrigerant. Formed between the scroll.

The horizontal scroll compressor includes a support portion that supports the orbiting scroll from one side in the axial direction, and is arranged so that the axial direction intersects the vertical direction.

The horizontal scroll compressor includes a lubricating oil separation unit that separates lubricating oil from the refrigerant discharged from the compression chamber and discharges the refrigerant from which the lubricating oil has been separated.

The horizontal scroll compressor has a plurality of sliding portions that slide while being displaced with the turning of the orbiting scroll, and includes a rotation preventing mechanism that regulates the rotation of the orbiting scroll.

The horizontal scroll compressor includes a storage chamber forming part that forms a mechanism storage chamber that stores the rotation prevention mechanism, and a lubricating oil that forms a lubricating oil path that guides the lubricating oil separated from the refrigerant by the lubricating oil separating unit to the mechanism storing chamber. A path forming unit.

The horizontal scroll compressor includes a pressure reducing mechanism for narrowing the lubricating oil path, and a discharge path forming unit for forming a discharge path having an inlet opening that opens into the mechanism storage chamber.

(4) As the lubricating oil passes through the pressure reducing mechanism, the gas refrigerant separated from the lubricating oil flows into the inlet opening from the mechanism storage chamber, and the gas refrigerant that has flowed in is discharged through the discharge path.

The uppermost part of the inlet opening is the uppermost part of the inlet opening, the uppermost sliding part of the plurality of sliding parts is the upper sliding part, and the upper sliding part is the lowermost part. In the timing at which the uppermost sliding portion is located at the lowermost position, the lowermost portion is defined as the lowermost portion. The uppermost part of the entrance opening is located above the lowermost part of the upper sliding part.

According to a second aspect, a horizontal scroll compressor includes a casing that forms a suction port, a suction chamber that communicates with the suction port, and a refrigerant path that forms a refrigerant path that communicates between the suction chamber and the compression chamber. And a forming unit.

(4) With the turning of the orbiting scroll, the compression chamber sucks the refrigerant through the suction port, the suction chamber, and the refrigerant path, and compresses the sucked refrigerant. The discharge path communicates between the mechanism storage chamber and the suction chamber.

Thereby, the gas refrigerant can be discharged from the mechanism storage chamber to the suction chamber through the discharge path.

According to the third aspect, the discharge path communicates between the mechanism housing chamber and the compression chamber.

Thereby, the gas refrigerant can be discharged from the mechanism storage chamber to the suction chamber through the compression chamber.

According to a fourth aspect, a horizontal scroll compressor includes a casing that forms a suction port, a suction chamber that communicates with the suction port, and a refrigerant path that forms a refrigerant path that communicates between the suction chamber and the compression chamber. Forming part.

(4) With the turning of the orbiting scroll, the compression chamber sucks the refrigerant through the suction port, the suction chamber, and the refrigerant path, and compresses the sucked refrigerant. The horizontal scroll compressor includes a discharge path forming unit that forms a second discharge path when the discharge path is a first discharge path.

The first discharge path communicates between the mechanism storage chamber and the suction chamber, the second discharge path communicates between the mechanism storage chamber and the compression chamber, and the first discharge path is located above the second discharge path. To position.

Therefore, the gas refrigerant can be discharged from the mechanism storage chamber to the suction chamber through the first discharge path, and the lubricating oil can be discharged from the mechanism storage chamber to the compression chamber through the second discharge path.

According to the fifth aspect, when the compression chamber compresses the refrigerant, the space between the second discharge path and the compression chamber is closed by the fixed scroll and the orbiting scroll. Before the compression chamber starts compressing the refrigerant, the lubricating oil in the mechanism storage chamber is sucked into the compression chamber through the second discharge path in a state where the space between the second discharge path and the compression chamber is opened by the fixed scroll and the orbiting scroll. Is done.

According to the sixth aspect, the horizontal scroll compressor includes a crank mechanism that is disposed on one side in the axial direction with respect to the orbiting scroll, and turns around the axis to apply a turning force to the orbiting scroll.

The horizontal scroll compressor includes a bearing storage forming part that forms a bearing storage chamber that stores the crank mechanism. The lubricating oil path includes a first lubricating oil path that guides the lubricating oil that has passed through the pressure reducing mechanism to the bearing storage chamber, and a second lubricating oil path that guides the lubricating oil in the bearing storing chamber to the mechanism storing chamber.

This makes it possible to guide the lubricating oil that has passed through the pressure reducing mechanism to the mechanism storage chamber in a short time.

According to the first aspect, a direction opposite to the turning direction of the orbiting scroll is defined as a counter turning direction,
When the orbiting scroll orbits in the orbiting direction and proceeds from the second lubricating oil path to the discharge path, the length of the path through which the orbiting scroll passes is referred to as a first path length.

経 路 When the orbiting scroll orbits in the anti-orbiting direction and proceeds from the second lubricating oil path to the discharge path, the length of the path through which the orbiting scroll passes is referred to as a second path length. The discharge path is arranged at a position where the second path length is shorter than the first path length.

When a range formed between the discharge path and the second lubricating oil path in a direction opposite to the turning direction from the second lubricating oil path is defined as a prohibited range, the plurality of sliding portions are arranged avoiding the prohibited range. .

Thereby, lubricating oil can be supplied to a plurality of sliding parts.

According to the eighth aspect, the horizontal scroll compressor includes a rotating shaft that rotates about an axis and applies a rotating force to the orbiting scroll through the crank mechanism.

The horizontal scroll compressor includes a balancer weight that is disposed in the bearing storage chamber and that rotates with the rotating shaft to offset the imbalance in weight of the orbiting scroll with respect to the axis. The second lubricating oil path has an inlet opening that opens into the bearing storage chamber.

バ The balancer weight and the inlet opening are arranged so that the outer peripheral side of the balancer weight centered on the axis approaches the inlet opening, so that the outer peripheral side of the balancer weight partially overlaps the inlet opening.

Thus, the lubricating oil having a high density is conveyed to the outer peripheral side by the centrifugal force of the balancer weight, and can quickly flow into the inlet opening of the second lubricating oil path by the rotational force of the balancer weight.

According to the ninth aspect, the horizontal scroll compressor includes the thrust bearing portion supported by the support portion and supporting the orbiting scroll from one side in the axial direction so that the orbiting scroll can be turned.

The bearing housing forming section has an inner peripheral surface centered on the axis, and the bearing housing chamber is formed radially inward of the inner peripheral surface centered on the axis.

入口 The inlet opening of the second lubricating oil passage is formed on the inner peripheral surface. The thrust bearing is disposed on the other side in the axial direction from the inlet opening of the second lubricating oil passage. Further, the thrust bearing portion is formed with a protruding portion that protrudes radially inward with respect to the axis from the inner peripheral surface over the circumferential direction with the axis as the center.

Thus, the lubricating oil flowing to the other side in the axial direction along the inner peripheral surface is blocked by the projection, so that the lubricating oil can flow into the inlet opening of the second lubricating oil passage.

According to the tenth aspect, the thrust bearing unit includes the fixed bearing unit supported by the support unit, and the turning bearing unit supported by the orbiting scroll, turning with the orbiting scroll, and sliding on the fixed bearing unit.

One of the fixed bearing portion and the slewing bearing portion has a concave portion that is recessed on the opposite side to the other bearing portion to hold the lubricating oil from the bearing storage chamber, and that the bottom portion of the concave portion faces the other bearing portion. A plurality of protruding portions are provided.

圧 A pressure receiving portion that receives a force from the other bearing portion is provided on the tip end side of each of the plurality of protrusions.

(4) With the turning of the orbiting scroll, the respective pressure receiving portions of the plurality of protrusions slide on the other bearing in a state of being lubricated by the lubricating oil in the concave portion.

According to the eleventh aspect, the lubricating oil path and the refrigerant path are formed independently.

Thus, it is possible to prevent the viscosity of the lubricating oil supplied to the plurality of sliding portions from being reduced by mixing the refrigerant flowing through the refrigerant path with the lubricating oil flowing through the lubricating oil path.

According to the twelfth aspect, the refrigerant path has an internal refrigerant path formed inside the fixed scroll and communicating with the compression chamber.

According to a thirteenth aspect, the horizontal scroll compressor is disposed in the suction chamber, and is disposed in a radial direction about the axis with respect to the rotor supported by the rotating shaft and the rotor in the suction chamber. A stator for applying a rotating magnetic field to the rotor to rotate the rotor.

The refrigerant path is disposed below the fixed scroll and the orbiting scroll,
Further, the coolant path is disposed radially outward with respect to the rotor with respect to the axis, and disposed below the rotor.

Thereby, when the gas refrigerant is discharged from the mechanism storage chamber to the suction chamber through the discharge path, the gas refrigerant can be caused to flow in a short time from the suction chamber to the compression chamber through the refrigerant path.

According to the fourteenth aspect, the fixed scroll and the orbiting scroll constitute a scroll compressor for a vehicle air conditioner.

According to the fifteenth aspect, the lubricating oil has a compatibility of 1% or more with the refrigerant at room temperature.

According to a sixteenth aspect, the refrigerant is carbon dioxide,
The pressure of carbon dioxide discharged from the compression chamber exceeds the critical pressure.

Claims (16)

1. Fixed scroll (34),
   When the direction in which the axis (S) extends is defined as the axial direction, the compression chamber is disposed on one side in the axial direction with respect to the fixed scroll, orbits around the axis, and sucks, compresses, and discharges the refrigerant ( Orbiting scroll (32) forming the fixed scroll with the orbiting scroll (32);
   A support portion (27) for supporting the orbiting scroll from one side in the axial direction,
   A horizontal scroll compressor arranged so that the axial direction intersects the vertical direction,
   A lubricating oil separator (63) for separating lubricating oil from the gas refrigerant discharged from the compression chamber and discharging the refrigerant from which the lubricating oil has been separated;
   A rotation preventing mechanism (70) having a plurality of sliding portions (72, 73, 74, 75) that slide while being displaced with the turning of the orbiting scroll, and that restricts rotation of the orbiting scroll;
   A storage chamber forming part (34f) for forming a mechanism storage chamber (34c) for storing the rotation preventing mechanism;
   A lubricating oil path forming part (44a, 24h, 24i, and a lubricating oil path forming part (44a, 24b, 24c, 120)) for guiding the lubricating oil separated from the gas refrigerant by the lubricating oil separating part to the mechanism housing chamber. 120a);
   A pressure reducing mechanism (42) for narrowing the lubricating oil path;
   A discharge path forming section (90a, 130a) for forming a discharge path (90, 130) having an entrance opening (91) opening into the mechanism storage chamber;
   As the lubricating oil passes through the pressure reducing mechanism, the gas refrigerant separated from the lubricating oil flows into the inlet opening from the mechanism housing chamber, and the gas refrigerant flows through the discharge path. Discharged,
   The uppermost part of the inlet opening is the uppermost part of the inlet opening, the uppermost sliding part of the plurality of sliding parts is the upper sliding part, and the upper sliding part is the uppermost sliding part. At the timing located at the lower part, the lowermost part of the upper sliding part is the lowermost part,
   A horizontal scroll compressor in which the uppermost part of the inlet opening is located above the lowermost part of the upper sliding part.
2. A casing (11a) forming a suction port (11d) and a suction chamber (11e) communicating with the suction port;
   A refrigerant path forming part (12a, 12b, 12c) that forms a refrigerant path (11g, 11h, 11i) communicating between the suction chamber and the compression chamber;
   With the orbiting of the orbiting scroll, the compression chamber sucks the refrigerant through the suction port, the suction chamber, and the refrigerant path and compresses the sucked refrigerant,
   The horizontal scroll compressor according to claim 1, wherein the discharge path (90) communicates between the mechanism housing chamber and the suction chamber.
3. The horizontal scroll compressor according to claim 1, wherein the discharge path (130) communicates between the mechanism housing chamber and the compression chamber.
4. A casing (11a) forming a suction port (11d) and a suction chamber (11e) communicating with the suction port;
   A refrigerant path forming part (12a, 12b, 12c) that forms a refrigerant path (11g, 11h, 11i) communicating between the suction chamber and the compression chamber;
   With the orbiting of the orbiting scroll, the compression chamber sucks the refrigerant through the suction port, the suction chamber, and the refrigerant path and compresses the sucked refrigerant,
   When the discharge path is a first discharge path (90), the discharge path forming unit (130a)
   Forming a second discharge path (130);
   The first discharge path communicates between the mechanism housing chamber and the suction chamber,
   The second discharge path communicates between the mechanism housing chamber and the compression chamber,
   The horizontal scroll compressor according to claim 1, wherein the first discharge path is located above the second discharge path.
5. When the compression chamber compresses the refrigerant, the fixed scroll and the orbiting scroll close the space between the second discharge path and the compression chamber,
   Before the compression chamber starts compressing the refrigerant, in a state where the space between the second discharge path and the compression chamber is opened by the fixed scroll and the orbiting scroll, the lubricating oil in the mechanism storage chamber is The horizontal scroll compressor according to claim 4, wherein the compressor is sucked into the compression chamber through a second discharge path.
6. A crank mechanism (24a) arranged on one side in the axial direction with respect to the orbiting scroll, and orbiting about the axis to apply a turning force to the orbiting scroll;
   A bearing housing forming section (27a) for forming a bearing housing chamber (38) for housing the crank mechanism;
   The lubricating oil path includes:
   A first lubricating oil path (24b, 24c) for guiding the lubricating oil that has passed through the pressure reducing mechanism to the bearing storage chamber;
   A second lubricating oil path (120) for guiding the lubricating oil in the bearing storage chamber to the mechanism storage chamber;
   The horizontal scroll compressor according to claim 5, comprising:
7. The opposite direction to the orbiting direction of the orbiting scroll is defined as an anti-orbiting direction,
   When the orbiting scroll orbits in the orbiting direction and proceeds from the second lubricating oil path toward the discharge path, the length of the path through which the orbiting scroll passes is defined as a first path length,
   When the orbiting scroll orbits in the anti-orbiting direction and proceeds from the second lubricating oil path toward the discharge path, the length of the path through which the orbiting scroll passes is defined as a second path length,
   The discharge path is arranged at a position where the second path length is shorter than the first path length,
   When a range formed between the discharge path and the second lubricating oil path from the second lubricating oil path in the anti-swirl direction is a prohibited range,
   The horizontal scroll compressor according to claim 6, wherein the plurality of sliding portions are arranged so as to avoid the prohibited range.
8. A rotating shaft (24) that rotates about the axis to apply a rotating force to the orbiting scroll through the crank mechanism;
   A balancer weight (36) disposed in the bearing storage chamber, the balancer weight rotating with the rotating shaft to offset the weight imbalance with respect to the axis in the orbiting scroll;
   The second lubricating oil path has an inlet opening (120b) that opens into the bearing storage chamber,
   The balancer weight and the inlet opening are arranged such that an outer peripheral side of the balancer weight around the axis approaches the inlet opening, so that the outer peripheral side of the balancer weight partially overlaps the inlet opening. The horizontal scroll compressor according to claim 6 or 7, wherein
9. A thrust bearing portion (100) supported by the support portion and supporting the orbiting scroll from one side in the axial direction such that the orbiting scroll can be turned;
   The bearing housing forming portion has an inner peripheral surface centered on the axis, and forms the bearing housing chamber radially inward centered on the axis than the inner peripheral surface,
   The inlet opening of the second lubricating oil path is formed on the inner peripheral surface,
   The thrust bearing portion is disposed on the other side in the axial direction from the inlet opening of the second lubricating oil path,
   9. The thrust bearing portion further includes a protruding portion (110) that protrudes radially inward from the inner peripheral surface about the axis along the circumferential direction about the axis. Horizontal scroll compressor according to 1.
10. The thrust bearing portion,
    A fixed bearing portion (100a) supported by the support portion;
    A revolving bearing (100b) supported by the revolving scroll and revolving with the revolving scroll to slide on the fixed bearing.
    One of the fixed bearing portion and the slewing bearing portion has a concave portion (103) recessed on the opposite side to the other bearing portion to hold the lubricating oil from the bearing storage chamber, and a bottom portion of the concave portion. And a plurality of projections (104) projecting toward the other bearing from
    A pressure receiving portion (104a) that receives a force from the other bearing portion is provided on a tip side of each of the plurality of protrusions,
    The revolving scroll according to claim 9, wherein the pressure receiving portions of the plurality of protrusions slide with respect to the other bearing portion in a state where the pressure receiving portions are lubricated by the lubricating oil in the concave portion with the turning of the orbiting scroll. Horizontal scroll compressor.
11. The horizontal scroll compressor according to any one of claims 4 to 10, wherein the lubricating oil path and the refrigerant path are formed independently.
12. The horizontal scroll according to any one of claims 4 to 11, wherein the refrigerant path has an internal refrigerant path (11i) formed inside the fixed scroll and communicating with the compression chamber. compressor.
13. A rotor (22) disposed in the suction chamber and supported by the rotating shaft;
    A stator (26) that is arranged in the suction chamber in a radial direction about the axis with respect to the rotor and applies a rotating magnetic field to the rotor to rotate the rotor;
    The refrigerant paths (11g, 11h) are disposed below the fixed scroll and the orbiting scroll,
    The said refrigerant | coolant path | route is arrange | positioned radially outside centering on the said axial line with respect to the said rotor, and is arrange | positioned at the lower side with respect to the said rotor. Horizontal scroll compressor.
14. The horizontal scroll compressor according to any one of claims 1 to 13, wherein the fixed scroll and the orbiting scroll constitute a scroll compressor for a vehicle air conditioner.
15. The horizontal scroll compressor according to any one of claims 1 to 14, wherein the lubricating oil has a compatibility of 1% or more with the refrigerant at room temperature.
16. The refrigerant is carbon dioxide,
    The horizontal scroll compressor according to any one of claims 1 to 15, wherein a pressure of the carbon dioxide discharged from the compression chamber exceeds a critical pressure.

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