JP2013209965A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor, which has a gas guide capable of efficiently increasing spot welding strength.SOLUTION: A scroll compressor 101 has a gas guide 71 which is spot-welded to an inner surface 11a of a casing 10. The gas guide 71 has flow path forming surfaces R12 to R15 forming a gas flow path 72 together with the inner surface 11a of the casing 10. At least a part of the gas flow path 72 has a cross section shape such that a maximum value D1 of a distance in a direction vertical to a radial direction of the casing 10, as a distance between it and the flow path forming surface R12, and a maximum value D2 of a distance in a radial direction of the casing 10, as a distance between an inner surface 11a of the casing 10 and the flow path forming surface R13 satisfy a relation, D2/D1≥0.35.

Description

  The present invention relates to a compressor.

  Conventionally, a compressor including a gas guide that forms a gas flow path with an inner surface of a casing has been used. The gas guide is a member that guides the refrigerant gas compressed by the compression mechanism inside the compressor. For example, a compressor gas guide disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2010-106790) discharges a part of the compressed refrigerant along the circumferential direction of the casing. Lubricating oil contained in the refrigerant flowing along the circumferential direction of the casing is blown away by centrifugal force. Thereby, lubricating oil is isolate | separated from a refrigerant | coolant.

  Generally, in terms of mass production of compressors, it is suitable to join the gas guide and the casing by spot welding. However, the spot welded portion has a high strength against a load in the shear direction, but a low strength against a load in the tensile direction. Further, in the gas flow path formed by the gas guide, pressure pulsation of the refrigerant compressed by the compression mechanism occurs. Therefore, a pressure difference is generated between the gas flow path on the inner surface side of the casing and the space on the central side of the casing, so that the gas guide is likely to receive a force in the casing radial direction, that is, a load in the tensile direction. Therefore, it is desirable that the gas guide has a sufficient spot weld strength.

  However, in order to increase the spot welding diameter in order to improve the spot welding strength of the gas guide, equipment corresponding to high electrode pressure and welding current is used, and the plate thickness of the gas guide and casing is increased. There is a need. This may increase the cost.

  The objective of this invention is providing the compressor provided with the gas guide which can improve spot-welding intensity | strength efficiently.

  The compressor which concerns on the 1st viewpoint of this invention is equipped with the gas guide spot-welded to the inner surface of a casing. The gas guide has a flow path forming surface that forms a gas flow path together with the inner surface of the casing. At least some of the gas flow paths have a cross-sectional shape that is a distance between the flow path forming surfaces and is a maximum distance D1 in a direction perpendicular to the radial direction of the casing, and the inner surface of the casing and the flow path forming surface. And the maximum distance D2 in the radial direction of the casing satisfies the relationship D2 / D1 ≧ 0.35.

  In the compressor according to the first aspect, the gas guide that forms the gas flow path for guiding the refrigerant compressed by the compression mechanism is spot welded to the inner surface of the casing. The spot welded portion of the gas guide has a high strength against a load in the shear direction, which is the circumferential direction of the casing, and a low strength against a load in the tensile direction, which is the radial direction of the casing. The gas guide of the compressor of the present invention has a shape that reduces the load in the tensile direction.

  For example, the cross-sectional shape of the gas channel is substantially rectangular, and the ratio of the length of the rectangular side along the casing radial direction to the length of the rectangular side along the circumferential direction of the casing is 0.45 or more. Consider the case where a gas guide is designed. In this case, the load acting on the surface of the gas guide along the radial direction of the casing due to the pressure of the refrigerant flowing through the gas flow path is reduced. Therefore, the compressor according to the first aspect includes a gas guide that can efficiently improve the spot welding strength.

  The compressor which concerns on the 2nd viewpoint of this invention is a compressor which concerns on a 1st viewpoint, Comprising: The cross-sectional shape of a gas flow path is a substantially rectangular shape. The substantially rectangular cross-sectional shape is such that the length L1 of the long side that is a side along the inner surface of the casing and the length L2 of the short side that is a side orthogonal to the long side are L2 / L1 ≧ 0.45. Meet.

  The compressor which concerns on the 3rd viewpoint of this invention is a compressor which concerns on a 1st viewpoint, Comprising: The cross-sectional shape of a gas flow path is a substantially trapezoid. This substantially trapezoidal cross-sectional shape includes an outer base length L3 that is a side along the inner surface of the casing, an inner base length L4 that is a side parallel to the outer base side, and a distance between the outer base side and the inner base side. L5 satisfies the relationship of L4 / L3 <0.90 and L5 / L3 ≧ 0.50.

  The compressor which concerns on the 4th viewpoint of this invention is a compressor which concerns on a 1st viewpoint, Comprising: The cross-sectional shape of a gas flow path is a substantially triangle. In the substantially triangular cross-sectional shape, the other two sides form an angle of 45 degrees or more with respect to the bottom side which is the side along the inner surface of the casing.

  The compressor which concerns on the 5th viewpoint of this invention is a compressor which concerns on a 1st viewpoint, Comprising: The cross-sectional shape of a gas flow path is a substantially semicircle. In this substantially semicircular cross-sectional shape, the side along the inner surface of the casing has a diameter.

  A compressor according to a sixth aspect of the present invention is the compressor according to any one of the first to fifth aspects, wherein the gas guide includes an upper gas flow path, a lower gas flow path, and a side portion. A gas flow path is formed. In the upper gas flow path, the gas flowing in from above flows downward. In the lower gas channel, the gas flowing in from the upper gas channel further flows downward. In the side gas channel, the gas flowing in from the upper gas channel flows in the horizontal direction.

  In the compressor according to the sixth aspect, a part of the refrigerant compressed by the compression mechanism flows downward in the vertical direction, and the rest gradually descends while flowing along the casing circumferential direction. Lubricating oil contained in the refrigerant flowing along the circumferential direction of the casing is blown to the inner surface of the casing by centrifugal force and finally returned to the oil reservoir space at the bottom of the casing. Therefore, the compressor according to the second aspect can efficiently separate the lubricating oil from the refrigerant.

  The compressor concerning the 1st thru / or the 6th viewpoint of the present invention is provided with the gas guide which can improve spot welding strength efficiently.

  The compressor according to the sixth aspect of the present invention can efficiently separate the lubricating oil from the refrigerant.

It is a longitudinal section of the scroll compressor concerning a 1st embodiment of the present invention. It is a front view of the gas guide which concerns on 1st Embodiment of this invention. It is a top view of the gas guide seen from the arrow III of FIG. It is a bottom view of the gas guide seen from the arrow IV of FIG. It is sectional drawing of the gas guide in the VV line | wire of FIG. It is sectional drawing of the gas guide in the VI-VI line of FIG. It is sectional drawing of the gas guide in the VII-VII line of FIG. It is a front view of the gas guide which concerns on 2nd Embodiment of this invention. It is a top view of the gas guide seen from the arrow IX of FIG. It is a bottom view of the gas guide seen from the arrow X of FIG. It is sectional drawing of the gas guide in the XI-XI line of FIG. It is sectional drawing of the gas guide in the XII-XII line | wire of FIG. It is sectional drawing of the gas guide in the XIII-XIII line | wire of FIG. It is a front view of the gas guide which concerns on 3rd Embodiment of this invention. It is a top view of the gas guide seen from the arrow XV of FIG. It is a bottom view of the gas guide seen from the arrow XVI of FIG. It is sectional drawing of the gas guide in the XVII-XVII line of FIG. It is sectional drawing of the gas guide in the XVIII-XVIII line | wire of FIG. It is sectional drawing of the gas guide in the XIX-XIX line | wire of FIG. It is a front view of the gas guide which concerns on 4th Embodiment of this invention. It is a top view of the gas guide seen from the arrow XXI of FIG. It is a bottom view of the gas guide seen from arrow XXII of FIG. It is sectional drawing of the gas guide in the XXIII-XXIII line | wire of FIG. It is sectional drawing of the gas guide in the XXIV-XXIV line | wire of FIG. It is sectional drawing of the gas guide in the XXV-XXV line | wire of FIG. It is the same sectional view of a gas guide as FIG.

<First Embodiment>
A compressor according to a first embodiment of the present invention will be described with reference to the drawings. The compressor according to the present embodiment is a high and low pressure dome type scroll compressor. A scroll compressor is a compressor in which a refrigerant is compressed by changing the volume of a space formed by two scroll members having spiral wraps that mesh with each other.

(1) Configuration of Compressor FIG. 1 is a longitudinal sectional view of a scroll compressor 101 according to this embodiment. The scroll compressor 101 mainly includes a casing 10, a compression mechanism 15, a housing 23, a drive motor 16, a lower bearing 60, a crankshaft 17, a gas guide 71, a suction pipe 19, and a discharge pipe 20. Consists of The scroll compressor 101 plays a role of compressing refrigerant gas in a refrigerant circuit that repeats a refrigeration cycle for circulating refrigerant. Next, each component of the scroll compressor 101 will be described.

(1-1) Casing The casing 10 includes a substantially cylindrical trunk casing portion 11, a bowl-shaped upper wall portion 12 welded in an airtight manner to the upper end portion of the trunk casing portion 11, and the trunk casing portion 11. And a bowl-shaped bottom wall portion 13 which is welded in an airtight manner to the lower end portion of the base plate. The casing 10 is formed of a rigid member that is unlikely to be deformed or damaged when pressure or temperature changes inside or outside the casing 10. The casing 10 is installed so that the substantially cylindrical axial direction of the body casing portion 11 is along the vertical direction.

  Inside the casing 10, a compression mechanism 15, a housing 23 disposed below the compression mechanism 15, a drive motor 16 disposed below the housing 23, and a crankshaft 17 disposed to extend in the vertical direction. Etc. are housed. A suction pipe 19 and a discharge pipe 20 are welded to the wall portion of the casing 10 in an airtight manner.

  An oil sump space 10 a in which lubricating oil is stored is formed at the bottom of the casing 10. Lubricating oil is used to keep the lubricity of sliding parts such as the compression mechanism 15 good during the operation of the scroll compressor 101.

(1-2) Compression Mechanism The compression mechanism 15 is housed inside the casing 10, sucks and compresses low-temperature and low-pressure refrigerant gas, and discharges high-temperature and high-pressure refrigerant gas (hereinafter referred to as “compressed refrigerant”). . The compression mechanism 15 mainly includes a fixed scroll component 24 and a turning scroll component 26.

  The fixed scroll 24 includes a first end plate 24a and a first wrap 24b having a spiral shape (involute shape) formed upright on the first end plate 24a. The fixed scroll 24 is formed with a main suction hole (not shown) and an auxiliary suction hole (not shown) adjacent to the main suction hole. The main suction hole communicates the suction pipe 19 and a compression chamber 40 described later. The auxiliary suction hole communicates a low-pressure space S2 described later and the compression chamber 40. A discharge hole 41 is formed at the center of the first end plate 24a, and an enlarged recess 42 communicating with the discharge hole 41 is formed at the upper surface of the first end plate 24a. The enlarged recess 42 is a space that is recessed in the upper surface of the first end plate 24a and extends in the horizontal direction. A lid 44 is fixed to the upper surface of the fixed scroll 24 with bolts 44 a so as to close the enlarged recess 42. The fixed scroll 24 and the lid 44 are tightly sealed through a gasket (not shown). A muffler space 45 that silences the operation sound of the compression mechanism 15 is formed by covering the enlarged recess 42 with the lid 44. The fixed scroll 24 is formed with a first compressed refrigerant channel 46 that communicates with the muffler space 45 and opens on the lower surface of the fixed scroll 24.

  The orbiting scroll 26 has a second end plate 26a and a second wrap 26b having a spiral shape (involute shape) formed upright on the second end plate 26a. An upper end bearing 26c is formed at the center of the lower surface of the second end plate 26a. Oil supply pores 63 are formed in the second end plate 26a. The oil supply pore 63 communicates the outer peripheral portion of the upper surface of the second end plate 26a and the space inside the upper end bearing 26c.

  The fixed scroll 24 and the orbiting scroll 26 are surrounded by the first end plate 24a, the first wrap 24b, the second end plate 26a, and the second wrap 26b when the first wrap 24b and the second wrap 26b are engaged with each other. A compression chamber 40 that is a space is formed. The volume of the compression chamber 40 is changed by the revolving motion of the orbiting scroll 26.

(1-3) Housing The housing 23 is arrange | positioned under the compression mechanism 15, and the outer peripheral surface is joined to the inner surface of the casing 10 airtightly. Thereby, the internal space of the casing 10 is partitioned into a high-pressure space S <b> 1 below the housing 23 and a low-pressure section S <b> 2 above the housing 23. The housing 23 is mounted with a fixed scroll 24 by being fixed with a bolt or the like, and holds the turning scroll 26 together with the fixed scroll 24 via an Oldham joint 39. The Oldham joint 39 is an annular member for preventing the orbiting scroll 26 from rotating. A second compressed refrigerant channel 48 is formed through the outer periphery of the housing 23 in the vertical direction. The second compressed refrigerant channel 48 communicates with the first compressed refrigerant channel 46 at the upper end surface of the housing 23, and communicates with the high-pressure space S <b> 1 through the discharge port 49 at the lower end surface of the housing 23.

  A crank chamber S <b> 3 is recessed in the upper surface of the housing 23. Further, a housing through hole 31 is formed in the housing 23. The housing through-hole 31 is a space formed through the housing 23 in the vertical direction from the center of the bottom surface of the crank chamber S3 to the center of the lower end surface of the housing 23. Hereinafter, a portion that is a part of the housing 23 and in which the housing through hole 31 is formed is referred to as an upper bearing 32. The housing 23 is formed with an oil return passage 23a that connects the high-pressure space S1 near the inner surface of the casing 10 and the crank chamber S3.

(1-4) Drive Motor The drive motor 16 is a brushless DC motor housed in the casing 10 and disposed below the housing 23. The drive motor 16 mainly includes a stator 51 that is fixed to the inner surface of the casing 10 and a rotor 52 that is rotatably accommodated by providing an air gap inside the stator 51.

  The stator 51 mainly includes a stator core 51a, an insulator 51b, and a coil 51c. The insulator 51b is attached to both end surfaces of the stator core 51a in the axial direction, and is wound around the stator core 51a by a coil 51c. The insulator 51b is a member that electrically insulates the stator core 51a and the coil 51c. The outer peripheral surface of the stator 51 is provided with a plurality of core cut portions (not shown) that are notched from the upper end surface to the lower end surface of the stator 51 and at predetermined intervals in the circumferential direction. . The core cut portion forms a motor cooling passage 55 that extends in the vertical direction between the body casing portion 11 and the stator 51.

  The rotor 52 is connected to the crankshaft 17 that passes through the center of rotation in the vertical direction. The rotor 52 is connected to the compression mechanism 15 via the crankshaft 17.

(1-5) Lower Bearing The lower bearing 60 is a member that is disposed below the drive motor 16 and is airtightly joined to the inner surface of the casing 10 on the outer peripheral surface thereof. The lower bearing 60 rotatably supports the crankshaft 17. The lower bearing 60 has an oil separation plate 73 attached to the upper end thereof.

(1-6) Crankshaft The crankshaft 17 is accommodated in the casing 10, and the axial direction thereof is arranged along the vertical direction. The crankshaft 17 has a shape in which the shaft center of the upper end portion thereof is slightly eccentric with respect to the shaft center of the portion excluding the upper end portion. The crankshaft 17 has a balance weight 18. The balance weight 18 is fixed in close contact with the crankshaft 17 at a height position below the housing 23 and above the drive motor 16.

  The crankshaft 17 passes through the rotation center of the rotor 52 in the vertical direction and is connected to the rotor 52. The upper end portion of the crankshaft 17 is fitted into the upper end bearing 26 c of the orbiting scroll 26. The crankshaft 17 is supported by the upper bearing 32 and the lower bearing 60.

  The crankshaft 17 has a main oil supply passage 61 extending in the axial direction. The upper end of the main oil supply passage 61 communicates with an oil chamber 83 formed by the upper end surface of the crankshaft 17 and the lower surface of the second end plate 26a. The oil chamber 83 communicates with a thrust bearing surface 24c, which is a surface in which the first end plate 24a and the second end plate 26a are in sliding contact with each other at the outer peripheral portion, through an oil supply hole 63 of the second end plate 26a. The lower end of the main oil supply passage 61 communicates with the oil sump space 10a of the high pressure space S1.

  Further, the crankshaft 17 has a first sub oil supply path 62 a, a second sub oil supply path 62 b, and a third sub oil supply path 62 c that branch from the main oil supply path 61. The first sub oil supply passage 62a, the second sub oil supply passage 62b, and the third sub oil supply passage 62c extend in the horizontal direction. The first sub oil supply passage 62 a is open to the sliding contact surface between the crankshaft 17 and the upper end bearing 26 c of the orbiting scroll 26. The second sub oil supply passage 62 b opens in the sliding contact surface between the crankshaft 17 and the upper bearing 32 of the housing 23. The third sub oil supply passage 62 c is open to the sliding contact surface between the crankshaft 17 and the lower bearing 60.

(1-7) Gas Guide The gas guide 71 is disposed in the high-pressure space S <b> 1 between the housing 23 and the drive motor 16. The gas guide 71 is formed of a metal plate, and is fixed to the inner surface of the body casing portion 11 of the casing 10 by spot welding. The gas guide 71 and the inner surface of the casing 10 form a refrigerant guide channel 72 through which the compressed refrigerant passes. The upper end of the refrigerant guide channel 72 communicates with the second compressed refrigerant channel 48 of the housing 23.

  FIG. 2 is a front view of the gas guide 71 when the gas guide 71 fixed to the inner surface of the casing 10 is viewed from the inside of the casing 10. A dotted arrow shown in FIG. 2 represents the flow of the compressed refrigerant passing through the refrigerant guide channel 72. The seven points WP shown in FIG. 2 are spot welding parts WP that are parts where the gas guide 71 is spot-welded to the inner surface of the casing 10. FIG. 3 is a top view of the gas guide 71 as viewed from the arrow III in FIG. FIG. 4 is a bottom view of the gas guide 71 viewed from the arrow IV in FIG. FIG. 5 is a cross-sectional view of the gas guide 71 taken along the line VV in FIG. 6 is a cross-sectional view of the gas guide 71 taken along line VI-VI in FIG. FIG. 7 is a cross-sectional view of the gas guide 71 taken along line VII-VII in FIG. In addition, the cross section of the casing 10 (body | casing part casing part 11) is also shown by FIGS.

  As shown in FIGS. 3 to 5, the gas guide 71 is in close contact with the inner surface of the casing 10 to form a horizontal channel 72 a and a vertical channel 72 b between the gas guide 71 and the inner surface of the casing 10. The vertical flow path 72b includes an upper vertical flow path 72b1 on the upper side and a lower vertical flow path 72b2 on the lower side, and communicates with the horizontal flow path 72a in the central portion in the vertical direction. As shown in FIG. 6, the horizontal cross-sectional area of the vertical flow path 72b gradually decreases from the top to the bottom. As shown in FIG. 7, the surface that forms the upper vertical flow path 72 b 1 of the gas guide 71 is a contact surface R <b> 11 that is in contact with the inner surface of the casing 10, and a radial direction that is a surface substantially along the radial direction of the casing 10. A surface R12, a circumferential surface R13 which is a surface spaced apart from the inner surface of the casing 10 and substantially along the circumferential direction of the casing 10, an outer curved surface R14 connecting the contact surface R11 and the radial surface R12, and a radial surface It is comprised from inner curved surface R15 which connects R12 and circumferential direction surface R13. The spot welding part WP shown in FIG. 7 is located on the contact surface R11 of the gas guide 71.

  As shown in FIG. 7, the horizontal cross section of the upper vertical flow path 72b1 has a substantially rectangular shape. Hereinafter, the horizontal cross section of the upper vertical flow path 72b1 will be described as being approximate to the rectangle C1. The rectangle C1 includes a long side E11 that is a side along the inner surface 11a of the casing 10 and a short side E12 that is a side orthogonal to the long side E11. As shown in FIG. 7, the rectangle C1 includes two points P11 where the extended surfaces of the two radial surfaces R12 intersect the inner surface 11a of the casing 10, and the extended surfaces of the two radial surfaces R12 are the circumferential surfaces R13. It has four vertices consisting of two points P12 intersecting with the extended surface. The long side E11 of the rectangle C1 is a side connecting the two points P11 and a side connecting the two points P12. The short side E12 of the rectangle C1 is a side connecting one point P11 and one point P12 located on the extended surface of the radial surface R12. The outer curved surface R14 is located outside the rectangle C1, and the inner curved surface R15 is located inside the rectangle C1. In the present embodiment, the ratio L2 / L1 between the length L2 of the short side E12 and the length L1 of the long side E11 of the rectangle C1 is 0.45 or more, preferably 0.50 or more.

  In addition, the rectangle C1 that approximates the horizontal section of the upper vertical flow path 72b1 satisfies the following condition including the condition represented by the above ratio L2 / L1. A rectangle C1 is a distance D between the flow path forming surfaces R12 to R15 that form the upper vertical flow path 72b1 and is perpendicular to the radial direction of the casing 10, and the inner surface 11a of the casing 10 and the flow path The maximum distance D2 between the forming surfaces R12 to R15 and the radial distance of the casing 10 satisfies the relationship D2 / D1 ≧ 0.35. Specifically, the distance D1 is a distance between two points PA where the two outer curved surfaces R14 are in contact with the inner surface 11a of the casing 10 with reference to FIG. The distance D2 is the maximum value of the distance between the inner surface 11a of the casing 10 and the circumferential surface R13.

  As shown in FIGS. 4 and 5, the horizontal cross section of the lower vertical flow path 72b2 and the vertical cross section of the horizontal flow path 72a are also substantially rectangular, similar to the horizontal cross section of the upper vertical flow path 72b1. It has the shape of

(1-8) Suction Pipe The suction pipe 19 is a pipe for introducing the refrigerant of the refrigerant circuit from the outside of the casing 10 to the compression mechanism 15. The suction pipe 19 is fitted into the upper wall portion 12 of the casing 10 in an airtight manner. The suction pipe 19 penetrates the low pressure space S2 in the vertical direction. An end portion of the suction pipe 19 in the casing 10 is fitted into a fixed scroll 24.

(1-9) Discharge Pipe The discharge pipe 20 is a pipe for discharging the compressed refrigerant from the high-pressure space S1 to the outside of the casing 10. The discharge pipe 20 is fitted in the body casing part 11 of the casing 10 in an airtight manner. The discharge pipe 20 penetrates the high-pressure space S1 in the horizontal direction. The opening 20 a at the end of the discharge pipe 20 in the casing 10 is located in the vicinity of the housing 23.

(2) Operation of Compressor The operation of the scroll compressor 101 according to this embodiment will be described. Initially, the flow of the refrigerant | coolant which circulates through a refrigerant circuit provided with the scroll compressor 101 is demonstrated. Next, the flow of the lubricating oil inside the scroll compressor 101 will be described.

(2-1) Flow of refrigerant First, when the drive motor 16 is driven, the rotor 52 rotates. As a result, the crankshaft 17 fixed to the rotor 52 rotates. The rotational movement of the crankshaft 17 is transmitted to the orbiting scroll 26 via the upper end bearing 26c. The shaft center of the upper end portion of the crankshaft 17 is eccentric with respect to the shaft rotational movement center of the crankshaft 17. The orbiting scroll 26 is prevented from rotating by the Oldham joint 39. As a result, the orbiting scroll 26 performs a revolving motion with respect to the fixed scroll 24 without rotating.

  The low-temperature and low-pressure refrigerant before compression is sucked into the compression chamber 40 of the compression mechanism 15 from the suction pipe 19 via the main suction hole or from the low-pressure space S2 via the auxiliary suction hole. By the revolving motion of the orbiting scroll 26, the compression chamber 40 moves from the outer peripheral portion of the fixed scroll 24 toward the center portion while gradually decreasing the volume. As a result, the refrigerant in the compression chamber 40 is compressed to become a compressed refrigerant. The compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45, and then discharged from the discharge port 49 to the high-pressure space S1 via the first compressed refrigerant channel 46 and the second compressed refrigerant channel 48. The compressed refrigerant passes through the refrigerant guide passage 72 that is a space between the gas guide 71 and the body casing portion 11, and then descends the motor cooling passage 55, and the high-pressure space S <b> 1 below the drive motor 16. To reach. Then, the compressed refrigerant reverses the flow direction and raises the air gap between the other motor cooling passage 55 and the drive motor 16. Finally, the compressed refrigerant is discharged from the discharge pipe 20 to the outside of the scroll compressor 101.

  In the present embodiment, a part of the compressed refrigerant passing through the refrigerant guide channel 72 passes through the vertical channel 72b and is sent to the high-pressure space S1 downward in the vertical direction, as shown in FIG. The remaining compressed refrigerant passes through the horizontal flow path 72a branched from the vertical flow path 72b and is sent to the high-pressure space S1 along the circumferential direction of the casing 10. Lubricating oil contained in the compressed refrigerant flowing in the high-pressure space S <b> 1 along the circumferential direction of the casing 10 is blown toward the inner surface of the casing 10 by centrifugal force. The lubricating oil adhering to the inner surface of the casing 10 falls toward the oil reservoir space 10a.

(2-2) Flow of lubricating oil First, the drive motor 16 is driven to rotate the rotor 52. As a result, the crankshaft 17 fixed to the rotor 52 rotates. When the compression mechanism 15 is driven by the rotational movement of the crankshaft 17 and the compressed refrigerant is discharged into the high-pressure space S1, the pressure in the high-pressure space S1 rises. On the other hand, the compression chamber 40 of the compression mechanism 15 communicating with the oil chamber 83 through the thrust bearing surface 24c and the oil supply hole 63 of the compression mechanism 15 is under a lower pressure than the high-pressure space S1. Therefore, the main oil supply passage 61 of the drive motor 16 communicating with the oil reservoir space 10a and the oil chamber 83 functions as a differential pressure pump. Thereby, the lubricating oil stored in the oil sump space 10a rises in the main oil supply passage 61.

  The lubricating oil that rises in the main oil supply path 61 is sequentially divided into the third auxiliary oil supply path 62c, the second auxiliary oil supply path 62b, and the first auxiliary oil supply path 62a. The lubricating oil flowing through the third auxiliary oil supply passage 62c lubricates the sliding contact surface between the crankshaft 17 and the lower bearing 60, and then is supplied to the high-pressure space S1 and falls toward the oil reservoir space 10a. The lubricating oil flowing through the second sub oil supply passage 62b is supplied to the high pressure space S1 and the crank chamber S3 after lubricating the sliding contact surface between the crankshaft 17 and the upper bearing 32 of the housing 23. The lubricating oil supplied to the high pressure space S1 falls toward the oil reservoir space 10a. The lubricating oil supplied to the crank chamber S3 is supplied to the high-pressure space S1 via the oil return passage 23a of the housing 23, and falls toward the oil reservoir space 10a. The lubricating oil flowing through the first auxiliary oil supply passage 62a is supplied to the crank chamber S3 after lubricating the sliding contact surface between the crankshaft 17 and the upper end bearing 26c of the orbiting scroll 26. The lubricating oil supplied to the crank chamber S3 is supplied to the high-pressure space S1 via the oil return passage 23a and falls toward the oil sump space 10a.

  The lubricating oil that has moved up the main oil supply passage 61 and reached the oil chamber 83 is supplied to the thrust bearing surface 24 c of the compression mechanism 15 through the oil supply holes 63. The lubricating oil supplied to the thrust bearing surface 24 c flows into the compression chamber 40. At this time, the high-temperature lubricating oil heats the low-temperature refrigerant before being compressed existing in the compression chamber 40 and is mixed into the refrigerant in the form of minute oil droplets. The lubricating oil mixed in the compressed refrigerant in the compression chamber 40 is supplied to the high-pressure space S1 through the same path as the compressed refrigerant. The lubricant oil collides with the oil separation plate 73 after descending the refrigerant guide passage 72 and the motor cooling passage 55 together with the compressed refrigerant. The lubricating oil adhering to the oil separation plate 73 falls toward the oil reservoir space 10a.

(3) Features of Compressor In the scroll compressor 101 according to the present embodiment, the refrigerant compressed by the compression mechanism 15 passes through the refrigerant guide flow path 72 formed by the gas guide 71 and is supplied to the high-pressure space S1. The The gas guide 71 is spot-welded to the inner surface of the casing 10 at the spot welding site WP. The spot welded portion WP of the gas guide 71 has a high strength against the load CL in the shear direction, which is a force applied along the circumferential direction of the casing 10, and is against the load RL in the tensile direction, which is a force applied along the radial direction of the casing 10. The strength is small. Further, the pressure of the refrigerant guide channel 72 through which the compressed refrigerant passes is higher than the pressure of the high pressure space S1 located on the opposite side of the refrigerant guide channel 72 with the gas guide 71 interposed therebetween. A force is applied from the guide channel 72 side toward the high-pressure space S1 side.

  In the present embodiment, the gas guide 71 of the scroll compressor 101 has a shape in which the tensile load RL due to the pressure of the refrigerant flowing through the refrigerant guide channel 72 is reduced. Specifically, as shown in FIG. 7, when the horizontal cross section of the upper vertical flow path 72b1 that is a part of the refrigerant guide flow path 72 is approximated to the rectangle C1, the length of the short side E12 of the rectangle C1 The shape of the gas guide 71 is designed so that the ratio L2 / L1 between L2 and the length L1 of the long side E11 is at least 0.45. Here, the shorter the length L1 of the long side E11 of the rectangle C1, the smaller the area of the circumferential surface R13 of the gas guide 71, so the load RL in the tensile direction acting in the radial direction of the casing 10 is also smaller. Further, as the length L2 of the short side E12 of the rectangle C1 is longer, the area of the radial surface R12 of the gas guide 71 is larger, so that the load CL in the shear direction acting in the circumferential direction of the casing 10 is larger. When the area of the rectangle C1 is constant, the shorter the length L1 of the long side E11 is, the longer the length L2 of the short side E12 is, so the ratio L2 / L1 is also large.

  That is, when the cross-sectional shape of the refrigerant guide channel 72 is the rectangle C1, the shape of the gas guide 71 is designed so that the ratio L2 / L1 between the length L2 of the short side E12 and the length L1 of the long side E11 is large. By doing so, the load RL in the tensile direction acting on the gas guide 71 can be reduced. Since the spot welded portion WP of the gas guide 71 has a low strength against the load RL in the tensile direction, the strength of the spot welded portion WP of the gas guide 71 is reduced by reducing the load RL in the tensile direction acting on the gas guide 71. Can be improved. Therefore, the scroll compressor 101 according to the present embodiment includes the gas guide 71 that can efficiently improve the spot welding strength.

Second Embodiment
A scroll compressor according to a second embodiment of the present invention will be described. Since the basic configuration, operation, and features of the present embodiment are the same as those of the scroll compressor according to the first embodiment, differences from the first embodiment will be mainly described. The same reference numerals are used for elements having the same structure and function as in the first embodiment.

(1) Configuration of Compressor The gas guide 171 in the present embodiment has a shape different from that of the gas guide 71 in the first embodiment. FIG. 8 is a front view of the gas guide 171 when the gas guide 171 fixed to the inner surface of the casing 10 is viewed from the inside of the casing 10. FIG. 9 is a top view of the gas guide 171 viewed from the arrow IX in FIG. FIG. 10 is a bottom view of the gas guide 171 viewed from the arrow X in FIG. FIG. 11 is a cross-sectional view of the gas guide 171 taken along the line XI-XI in FIG. 12 is a cross-sectional view of the gas guide 171 taken along the line XII-XII in FIG. 13 is a cross-sectional view of the gas guide 171 taken along line XIII-XIII in FIG.

  As shown in FIGS. 9 to 11, the gas guide 171 is in close contact with the inner surface of the casing 10 to form a horizontal channel 72 a and a vertical channel 72 b between the gas guide 171 and the inner surface of the casing 10. The vertical flow path 72b includes an upper vertical flow path 72b1 on the upper side and a lower vertical flow path 72b2 on the lower side, and communicates with the horizontal flow path 72a in the central portion in the vertical direction. As shown in FIG. 12, the horizontal sectional area of the vertical flow path 72b gradually decreases from the top to the bottom. As shown in FIG. 13, the surface that forms the upper vertical flow path 72 b 1 of the gas guide 171 is a contact surface R <b> 21 that is in contact with the inner surface of the casing 10, and a radial direction that is a surface substantially along the radial direction of the casing 10. A surface R22, a circumferential surface R23 which is a surface spaced apart from the inner surface of the casing 10 and substantially along the circumferential direction of the casing 10, an outer curved surface R24 connecting the contact surface R21 and the radial surface R22, and a radial surface It is comprised from inner curved surface R25 which connects R22 and circumferential direction surface R23. The spot welding site WP shown in FIG. 13 is located on the contact surface R21 of the gas guide 171.

  The gas guide 171 in the present embodiment differs from the gas guide 71 in the first embodiment in the cross-sectional shape of the refrigerant guide channel 72. Specifically, as shown in FIG. 13, the horizontal cross section of the upper vertical flow path 72b1 has a substantially trapezoidal shape. Hereinafter, the horizontal section of the upper vertical flow path 72b1 will be described by approximating the trapezoid C2. The trapezoid C2 includes an outer base E21 which is a side along the inner surface 11a of the casing 10, an inner base E22 which is a side parallel to the outer base E21, and a pair of side E23 which connects the outer base E21 and the inner base E22. Consists of. As shown in FIG. 13, the trapezoid C2 includes two points P21 where the extended surfaces of the two radial surfaces R22 intersect the inner surface 11a of the casing 10, and the extended surfaces of the two radial surfaces R22 are the circumferential surfaces R23. It has four vertices consisting of two points P22 intersecting with the extended surface. The outer bottom side E21 of the trapezoid C2 is a side connecting the two points P21. The inner base E22 of the trapezoid C2 is a side connecting the two points P22. The side E23 of the trapezoid C2 is a side connecting one point P21 and one point P22 located on the extended surface of the radial surface R22. The outer curved surface R24 is located outside the trapezoid C2, and the inner curved surface R25 is located inside the trapezoid C2. The trapezoid C2 is symmetric with respect to the perpendicular bisector of the outer base E21 or the inner base E22. In the present embodiment, the ratio L4 / L3 of the length L4 of the inner base E22 and the length L3 of the outer base E21 of the trapezoid C2 is less than 0.90, preferably less than 0.85. Further, the ratio L5 / L3 between the distance L5 between the outer base E21 and the inner base E22, which is the height of the trapezoid C2, and the length L3 of the outer base E21 is 0.50 or more, preferably 0. 55 or more.

  FIG. 13 also shows a straight line WL that connects the center CP of the horizontal cross section of the spot welded part WP and the center (not shown) of the horizontal cross section of the casing 10 (body casing portion 11). In the present embodiment, it is preferable that the angle between the side E23 of the trapezoid C2 and the straight line WL closest to the side E23 is 45 degrees or less.

  As shown in FIGS. 10 and 11, the horizontal cross section of the lower vertical flow path 72b2 and the vertical cross section of the horizontal flow path 72a are also substantially trapezoids similar to the horizontal cross section of the upper vertical flow path 72b1. It has the shape of

(2) Features of the Compressor In this embodiment, the gas guide 171 of the scroll compressor 101 has a reduced load in the tensile direction due to the pressure of the refrigerant flowing through the refrigerant guide channel 72, as in the first embodiment. It has a shape. Specifically, as shown in FIG. 13, when the horizontal cross section of the upper vertical flow path 72b1 that is a part of the refrigerant guide flow path 72 is approximated to a trapezoid C2, the height L5 of the trapezoid C2 and the outer base side The shape of the gas guide 171 is designed so that the ratio L5 / L3 with the length L3 of E21 is at least 0.50. Here, as the length L3 of the outer base E21 of the trapezoid C2 is shorter, the length L4 of the inner base E22 is shorter and the area of the circumferential surface R23 of the gas guide 171 is smaller, so that the tension acting in the radial direction of the casing 10 is reduced. The direction load RL is also small. Moreover, since the side E23 is longer as the height L5 of the trapezoid C2 is longer, the load CL in the shear direction acting in the circumferential direction of the casing 10 is larger. When the area of the trapezoid C2 is constant, the shorter the length L3 of the outer base E21 is, the longer the height L5 is, so the ratio L5 / L3 is also large.

  That is, when the cross-sectional shape of the refrigerant guide channel 72 is a trapezoid C2, the shape of the gas guide 171 is designed so that the ratio L5 / L3 between the height L5 and the length L3 of the outer base E21 is increased. The load RL in the tensile direction acting on the gas guide 171 can be reduced. Thereby, the intensity | strength of the spot welding site | part WP of the gas guide 171 can be improved. Therefore, the scroll compressor 101 according to the present embodiment includes the gas guide 171 that can efficiently improve the spot welding strength.

<Third Embodiment>
A scroll compressor according to a third embodiment of the present invention will be described. Since the basic configuration, operation, and features of the present embodiment are the same as those of the scroll compressor according to the first embodiment, differences from the first embodiment will be mainly described. The same reference numerals are used for elements having the same structure and function as in the first embodiment.

(1) Configuration of Compressor The gas guide 271 in the present embodiment has a shape different from that of the gas guide 71 in the first embodiment. FIG. 14 is a front view of the gas guide 271 when the gas guide 271 fixed to the inner surface of the casing 10 is viewed from the inside of the casing 10. FIG. 15 is a top view of the gas guide 271 as viewed from the arrow XV in FIG. FIG. 16 is a bottom view of the gas guide 271 as viewed from the arrow XVI in FIG. 17 is a cross-sectional view of the gas guide 271 taken along the line XVII-XVII in FIG. FIG. 18 is a cross-sectional view of the gas guide 271 taken along the line XVIII-XVIII in FIG. FIG. 19 is a cross-sectional view of the gas guide 271 taken along the line XIX-XIX in FIG.

  As shown in FIGS. 15 to 17, the gas guide 271 is in close contact with the inner surface of the casing 10, and forms a horizontal flow path 72 a and a vertical flow path 72 b between the inner surface of the casing 10. The vertical flow path 72b includes an upper vertical flow path 72b1 on the upper side and a lower vertical flow path 72b2 on the lower side, and communicates with the horizontal flow path 72a in the central portion in the vertical direction. As shown in FIG. 18, the horizontal cross-sectional area of the vertical flow path 72b gradually decreases from the top to the bottom. As shown in FIG. 19, the surface forming the upper vertical flow path 72 b 1 of the gas guide 271 is along a contact surface R 31 in contact with the inner surface of the casing 10 and a direction that forms a predetermined angle with the radial direction of the casing 10. A pair of inclined surfaces R32, which is a curved surface, an outer curved surface R33 that connects the contact surface R31 and the inclined surface R32, and an inner curved surface R34 that connects the pair of inclined surfaces R32 to each other. The spot welding part WP shown in FIG. 19 is located on the contact surface R31 of the gas guide 271.

  The gas guide 271 in the present embodiment differs from the gas guide 71 in the first embodiment in the cross-sectional shape of the refrigerant guide channel 72. Specifically, as shown in FIG. 19, the cross section in the horizontal direction of the upper vertical flow path 72b1 has a substantially triangular shape. Hereinafter, the horizontal cross section of the upper vertical flow path 72b1 will be described by approximating the triangle C3. The triangle C3 is an isosceles triangle composed of a base E31 that is a side along the inner surface 11a of the casing 10 and a pair of oblique sides E32 other than the base E31. As shown in FIG. 19, the triangle C3 includes two points P31 where the extended surfaces of the two inclined surfaces R32 intersect the inner surface 11a of the casing 10, and one point P32 where the extended surfaces of the two inclined surfaces R32 intersect. Have three vertices. The base E31 of the triangle C3 is a side connecting the two points P31. The hypotenuse E32 of the triangle C3 is an edge connecting one point P31 and the point P32. The outer curved surface R33 is located outside the triangle C3, and the inner curved surface R34 is located inside the triangle C3. In the present embodiment, the angle θ between the base E31 and the hypotenuse E32 of the triangle C3 is 45 degrees or more, preferably 50 degrees or more.

  As shown in FIGS. 16 and 17, the horizontal cross section of the lower vertical flow path 72b2 and the vertical cross section of the horizontal flow path 72a are also substantially triangular, similar to the horizontal cross section of the upper vertical flow path 72b1. It has the shape of

(2) Features of the Compressor In this embodiment, the gas guide 271 of the scroll compressor 101 has a reduced load in the tensile direction due to the pressure of the refrigerant flowing through the refrigerant guide channel 72, as in the first embodiment. It has a shape. Specifically, as shown in FIG. 19, when the horizontal cross section of the upper vertical flow path 72b1 that is a part of the refrigerant guide flow path 72 is approximated to the triangle C3, the base E31 and the hypotenuse E32 of the triangle C3 The shape of the gas guide 271 is designed so that the angle θ between them is at least 45 degrees. When the load acting on the inclined surface R32 is broken down into the radial load component of the casing 10 and the circumferential load component of the casing 10, the angle θ between the base E31 and the hypotenuse E32 of the triangle C3 is large. As the load component in the circumferential direction of the casing 10 increases. In this case, the load CL in the shear direction acting in the circumferential direction of the casing 10 is increased with respect to the inclined surface R32, and the load RL in the tensile direction acting in the radial direction of the casing 10 is decreased.

  That is, when the cross-sectional shape of the refrigerant guide channel 72 is a triangle C3, the shape of the gas guide 271 is designed so that the angle θ between the base E31 and the hypotenuse E32 is increased, thereby acting on the gas guide 271. The load RL in the tensile direction can be reduced. Thereby, the intensity | strength of the spot welding site | part WP of the gas guide 271 can be improved. Therefore, the scroll compressor 101 according to the present embodiment includes the gas guide 271 that can efficiently improve the spot welding strength.

<Fourth embodiment>
A scroll compressor according to a fourth embodiment of the present invention will be described. Since the basic configuration, operation, and features of the present embodiment are the same as those of the scroll compressor according to the first embodiment, differences from the first embodiment will be mainly described. The same reference numerals are used for elements having the same structure and function as in the first embodiment.

(1) Configuration of Compressor The gas guide 371 in the present embodiment has a shape different from that of the gas guide 71 in the first embodiment. FIG. 20 is a front view of the gas guide 371 when the gas guide 371 fixed to the inner surface of the casing 30 is viewed from the inside of the casing 10. FIG. 21 is a top view of the gas guide 371 as viewed from the arrow XXI in FIG. FIG. 22 is a bottom view of the gas guide 371 as viewed from the arrow XXII in FIG. FIG. 23 is a cross-sectional view of the gas guide 371 taken along the line XXIII-XXIII in FIG. 24 is a cross-sectional view of the gas guide 371 taken along the line XXIV-XXIV in FIG. 25 is a cross-sectional view of the gas guide 371 taken along the line XXV-XXV in FIG.

  As shown in FIGS. 21 to 23, the gas guide 371 is in close contact with the inner surface of the casing 10, and forms a horizontal flow path 72 a and a vertical flow path 72 b between the inner surface of the casing 10. The vertical flow path 72b includes an upper vertical flow path 72b1 on the upper side and a lower vertical flow path 72b2 on the lower side, and communicates with the horizontal flow path 72a in the central portion in the vertical direction. As shown in FIG. 24, the horizontal sectional area of the vertical flow path 72b gradually decreases from the top to the bottom. As shown in FIG. 25, the surface forming the upper vertical flow path 72b1 of the gas guide 371 protrudes inward in the radial direction from the contact surface R41 in contact with the inner surface of the casing 10 and the inner surface of the casing 10. The surface is composed of a curved surface R42 and an outer curved surface R43 connecting the contact surface R41 and the curved surface R42. The spot welding part WP shown in FIG. 25 is located on the contact surface R41 of the gas guide 371.

  The gas guide 371 in the present embodiment differs from the gas guide 71 in the first embodiment in the cross-sectional shape of the refrigerant guide channel 72. Specifically, as shown in FIG. 25, the horizontal cross section of the upper vertical flow path 72b1 has a substantially semicircular shape. Hereinafter, the horizontal cross section of the upper vertical flow path 72b1 will be described as being approximated by a semicircle C4. The diameter E41 of the semicircle C4 corresponds to a side along the inner surface 11a of the casing 10. As shown in FIG. 25, the diameter E41 is a straight line connecting two points P41 where the extended surfaces on both sides of the curved surface R42 intersect the inner surface 11a of the casing 10. The outer curved surface R43 is located outside the semicircle C4.

  As shown in FIGS. 22 and 23, the horizontal cross section of the lower vertical flow path 72b2 and the vertical cross section of the horizontal flow path 72a are also substantially the same as the horizontal cross section of the upper vertical flow path 72b1. It has a circular shape.

(2) Features of the Compressor In this embodiment, the gas guide 371 of the scroll compressor 101 has a reduced load in the tensile direction due to the pressure of the refrigerant flowing through the refrigerant guide channel 72, as in the first embodiment. It has a shape. Specifically, as shown in FIG. 25, the shape of the gas guide 371 is designed so that the horizontal cross section of the upper vertical flow path 72b1, which is a part of the refrigerant guide flow path 72, approximates a semicircle C4. Has been. The load acting on the curved surface R42 is decomposed into a tensile load RL acting in the radial direction of the casing 10 and a shearing load CL acting in the circumferential direction of the casing 10.

  That is, by designing the shape of the gas guide 371 so that the cross-sectional shape of the refrigerant guide channel 72 approximates the semicircle C4, the load RL in the tensile direction acting on the gas guide 371 can be reduced. Thereby, the intensity | strength of the spot welding site | part WP of the gas guide 371 can be improved. Therefore, the scroll compressor 101 according to the present embodiment includes the gas guide 371 that can efficiently improve the spot welding strength.

<Modification>
As mentioned above, although embodiment of this invention was described referring drawings, the concrete structure of this invention can be changed in the range which does not deviate from the summary of this invention. Hereinafter, modifications applicable to the compressor according to the embodiment of the present invention will be described.

(1) Modification A
In 1st thru | or 4th embodiment, although the scroll compressor 101 provided with the compression mechanism 15 comprised from the fixed scroll component 24 and the turning scroll component 26 is used as a compressor, other types of compression mechanisms are used. A compressor provided may be used. For example, a rotary compressor or a reciprocating compressor may be used.

(2) Modification B
In the first to fourth embodiments, the horizontal cross section of the upper vertical flow path 72b1 formed by the gas guides 71, 171, 271 and 371, the horizontal cross section of the lower vertical flow path 72b2, and the horizontal flow path 72a. Each of the vertical cross sections has a shape of any one of a rectangle C1, a trapezoid C2, a triangle C3, and a semicircle C4. However, at least one of the horizontal cross section of the upper vertical flow path 72b1, the horizontal cross section of the lower vertical flow path 72b2, and the vertical cross section of the horizontal flow path 72a is a rectangle C1, a trapezoid C2, a triangle C3, and It suffices to have any one shape of the semicircle C4.

  For example, in the gas guide 71 in the first embodiment, the horizontal cross section of the upper vertical flow path 72b1, the horizontal cross section of the lower vertical flow path 72b2, and the vertical cross section of the horizontal flow path 72a are the length of the short side E12. The ratio L2 / L1 between the length L2 and the length L1 of the long side E11 is at least 0.45, but the ratio L2 / L1 of the rectangle C1 that is a horizontal section of the upper vertical flow path 72b1 is at least If it is 0.45, the ratio L2 / L1 of the rectangle C1 that is the horizontal cross section of the lower vertical flow path 72b2 and the vertical cross section of the horizontal flow path 72a may be less than 0.45.

(3) Modification C
In the first to fourth embodiments, the conditions to be satisfied by the horizontal cross-sectional shapes C1, C2, C3, and C4 of the upper vertical flow path 72b1 formed by the gas guides 71, 171, 271, and 371 have been described. For example, in the first embodiment, the rectangle C1 approximating the horizontal cross section of the upper vertical flow path 72b1 has a ratio L2 / L1 between the length L2 of the short side E12 and the length L1 of the long side E11 of at least 0. 45.

  However, these cross-sectional shapes C1, C2, C3, and C4 are distances between the flow path forming surfaces R12 to R15, R22 to R25, R32 to R34, R42, and R43 that form the upper vertical flow path 72b1, and the casing 10 The distance D between the maximum value D1 in the direction perpendicular to the radial direction and the inner surface 11a of the casing 10 and the flow path forming surfaces R12 to R15, R22 to R25, R32 to R34, R42 and R43. The maximum distance D2 in the radial direction may satisfy the relationship D2 / D1 ≧ 0.35, and more preferably satisfy the relationship D2 / D1 ≧ 0.40. As an example, FIG. 26 shows the distances D1 and D2 in the rectangular cross-sectional shape C1 in the first embodiment. The distance D1 is a distance between two points PA where the two outer curved surfaces R14 are in contact with the inner surface 11a of the casing 10. The distance D2 is the maximum value of the distance between the inner surface 11a of the casing 10 and the circumferential surface R13. The rectangle C1, trapezoid C2, triangle C3, and semicircle C4, which are specific cross-sectional shapes in the first to fourth embodiments, satisfy the condition of the distance ratio D2 / D1.

  The compressor according to the present invention includes a gas guide that can efficiently improve the spot welding strength.

DESCRIPTION OF SYMBOLS 10 Casing 11a Inner surface of casing 71 Gas guide 72 Refrigerant guide flow path (gas flow path)
72a Horizontal channel (side gas channel)
72b1 Upper vertical flow path (upper gas flow path)
72b2 Lower vertical flow path (lower gas flow path)
101 Scroll compressor (compressor)
171 gas guide 271 gas guide 371 gas guide C1 substantially rectangular cross-sectional shape C2 substantially trapezoidal cross-sectional shape C3 substantially triangular cross-sectional shape C4 substantially semi-circular cross-sectional shape E11 rectangular long side E12 rectangular short side E21 trapezoidal outer base E22 Trapezoid inner base E31 Triangular base E32 Two sides other than triangular base E41 Diameter of semicircle R12 to R15 Channel forming surface R22 to R25 Channel forming surface R32 to R34 Channel forming surface R42, R43 Channel forming surface

JP 2010-106790 A

Claims (6)

A flow path forming surface (R12 to R15, R22 to R25, R32 to R34, R42, R43) spot welded to the inner surface of the casing (10) and forming a gas flow path (72) with the inner surface (11a) of the casing. A compressor (101) comprising a gas guide (71,171,271,371) having
At least some of the gas flow paths have a cross-sectional shape (C1, C2, C3, C4) that is a distance between the flow path forming surfaces and a maximum distance D1 in a direction perpendicular to the radial direction of the casing. And the maximum value D2 of the distance in the radial direction of the casing between the inner surface of the casing and the flow path forming surface satisfies the relationship of D2 / D1 ≧ 0.35.
Compressor. The cross-sectional shape (C1) of the gas flow path is substantially rectangular, a length L1 of a long side (E11) that is a side along the inner surface of the casing, and a short side (side that is orthogonal to the long side) The length L2 of E12) satisfies the relationship of L2 / L1 ≧ 0.45.
The compressor according to claim 1. The cross-sectional shape (C2) of the gas flow path is substantially trapezoidal, and includes a length L3 of an outer bottom side (E21) that is a side along the inner surface of the casing, and an inner base side that is a side parallel to the outer bottom side ( The length L4 of E22) and the distance L5 between the outer base and the inner base satisfy the relationship of L4 / L3 <0.90 and L5 / L3 ≧ 0.50.
The compressor according to claim 1. The cross-sectional shape (C3) of the gas channel is substantially triangular, and the other two sides (E32) form an angle of 45 degrees or more with respect to the base (E31) that is a side along the inner surface of the casing. ,
The compressor according to claim 1. The cross-sectional shape (C4) of the gas flow path is a substantially semicircle, and the side along the inner surface of the casing has a diameter (E41).
The compressor according to claim 1. In the gas guide,
An upper gas flow path (72b1) in which the gas flowing in from above flows downward;
A lower gas channel (72b2) through which the gas flowing in from the upper gas channel flows further downward;
A side gas passage (72a) through which the gas flowing in from the upper gas passage flows in a horizontal direction;
Is formed,
The compressor according to any one of claims 1 to 5.

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