compressor

Abstract

The compression mechanism (14) is arranged at a position close to one end of the housing (10), and the motor (6) is arranged at a position close to the other end. The suction pipe (18) opens between the compression mechanism (14) and the motor (6) in the housing (10). A gas flow path (91) is formed between the motor (6) and the housing (10) to communicate one end side and the other end side of the motor (6) in the housing (10) in the axial direction. The gas guide (80) has a first flow path arranged opposite to the open end (18A) of the suction pipe (18) in the housing (10) and to guide a part of the gas after passing through the suction pipe (18) to the compression mechanism (14) side, and a second flow path to guide the remaining part of the gas after passing through the suction pipe (18) to the gas flow path (91).

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a compressor. BACKGROUND

[0002] Hitherto, a compressor including a rectifying member for dividing a gas sucked into a casing has been known. Such a compressor is described in, for example, Patent Literature 1.

[0003] The compressor of Patent Literature 1 includes a hermetic container, an electric element, a compression mechanism portion driven by the electric element, a suction pipe that sucks a refrigerant into the hermetic container, and a rectifying plate that divides the refrigerant sucked from the suction pipe. And, one branch of the refrigerant divided by the rectifying plate passes through a first opening portion provided toward the compression mechanism portion side, and the other branch passes through a second opening portion provided toward the electric element side.

[0004] It can be considered that, according to the compressor of Patent Literature 1, not only the compression mechanism portion but also the electric element can be cooled.

[0005] PRIOR ART DOCUMENT

[0006] PATENT LITERATURE

[0007] Patent Literature 1: Japanese Laid-Open Patent Publication No. 2018-131910 (in particular, paragraphs 0012, 0030) SUMMARY

[0008] PROBLEMS TO BE SOLVED BY THE INVENTION

[0009] However, in the compressor of Patent Literature 1, the refrigerant from the second opening portion of the rectifying plate is sufficiently supplied to the region of the one end side in the axial direction of the electric element (the compression mechanism portion side), but the amount of supply to the region of the other end side in the axial direction of the electric element (the side opposite to the compression mechanism portion) can be insufficient. Therefore, the cooling of the other end side in the axial direction of the electric motor can be insufficient.

[0010] An object of the present disclosure is to improve the reliability of the electric motor by reducing the temperature difference between the one end side and the other end side in the axial direction of the electric motor.

[0011] TECHNICAL SOLUTION FOR SOLVING THE PROBLEMS

[0012] A first aspect of the present disclosure is directed to a compressor 1 including a cylindrical casing 10, a compression mechanism 14, an electric motor 6, a suction pipe 18, a gas flow path 91, and a gas guide 80. The compression mechanism 14 is arranged in the casing 10 at a position close to one end of the casing 10, and compresses gas. The electric motor 6 is arranged in the casing 10 at a position close to the other end of the casing 10, and drives the compression mechanism 14. The suction pipe 18 is opened between the compression mechanism 14 and the electric motor 6 in the casing 10. The gas flow path 91 is formed between the electric motor 6 and an inner peripheral surface of the casing 10, and communicates one end side and the other end side of the electric motor 6 in the casing 10 in the axial direction. The gas guide 80 is arranged opposite to an opened end 18A of the suction pipe 18 in the casing 10, and has a first flow path 83 and a second flow path 84. The first flow path 83 guides a part of the gas after passing through the suction pipe 18 to the compression mechanism 14 side. The second flow path 84 guides the remaining part of the gas after passing through the suction pipe 18 to the gas flow path 91.

[0013] In the first aspect, a part of the gas sucked from the suction pipe 18 is guided to the gas flow path 91 by the second flow path 84 of the gas guide 80, and is supplied to the other end side of the electric motor 6 in the axial direction through the gas flow path 91. The part of the electric motor 6 on the other end side in the axial direction is cooled by the gas after passing through the gas flow path 91. As a result, the temperature difference between the one end side and the other end side in the axial direction of the electric motor 6 is reduced, and the reliability of the electric motor 6 is improved.

[0014] A second aspect of the present disclosure is directed to the first aspect, in which a minimum flow path cross-sectional area of the first flow path 83 is larger than a minimum flow path cross-sectional area of the second flow path 84.

[0015] In the second aspect, the gas sucked from the suction pipe 18 is more easily guided to the compression mechanism 14 side than to the electric motor 6 side. As a result, adverse effects due to excessive flow of the gas to the electric motor 6 side can be prevented.

[0016] A third aspect of the present disclosure is directed to the first or second aspect, in which the second flow path 84 includes a narrowing portion 85 and an expanding portion 86. The flow path cross-sectional area of the narrowing portion 85 is reduced as it approaches an outlet side of the second flow path 84. The expanding portion 86 is located closer to the outlet side of the second flow path 84 than the narrowing portion 85, and the flow path cross-sectional area of the expanding portion 86 is increased as it approaches the outlet side of the second flow path 84.

[0017] In the third aspect of the invention, the second flow path 84 has a throttle portion 88 at a portion where the reduced portion 85 and the enlarged portion 86 are connected, thereby restricting the amount of refrigerant gas flowing toward the motor 6 side. The gas after passing through the throttle portion 88 spreads along the surface of the gas guide 80, whereby the flow rate of the refrigerant gas is slowed down. As a result, it is possible to slow down the flow rate of the gas flowing toward the motor 6 side, for example, in a case where the oil reservoir is arranged at a position closer to the other end of the housing 10 than the motor 6 of the compressor 1, and so on, and it is possible to suppress the scattering of oil in the oil reservoir due to the flow of gas.

[0018] The fourth aspect of the invention of the present disclosure is, on the basis of any one of the above-mentioned first to third aspects of the invention, the outlet of the second flow path 84 is opposed to the first open end 91A of the gas flow path 91 on the side close to the gas guide 80.

[0019] In the fourth aspect of the invention, it is possible to cause the gas flowing through the second flow path 84 to flow toward the gas flow path 91 with good efficiency.

[0020] The fifth aspect of the invention of the present disclosure is, on the basis of the above-mentioned fourth aspect of the invention, the outlet of the second flow path 84 coincides with the entire first open end 91A of the gas flow path 91 when viewed in the axial direction of the housing 10.

[0021] In the fifth aspect of the invention, it is possible to suppress the gas after flowing through the second flow path 84 from excessively flowing into the gas flow path 91. As a result, it is possible to prevent adverse effects due to the excessive flow of gas toward the motor 6 side. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure;

[0023] Figure 2 is a perspective view of a gas guide;

[0024] Figure 3 is a view of the gas guide as viewed from the radially outer side;

[0025] Figure 4 is a longitudinal sectional view of a gas guide;

[0026] Figure 5A is a sectional view taken along the VA-VA line of Figure 3 ;

[0027] Figure 5B is a sectional view taken along the VB-VB line of Figure 3 ;

[0028] Figure 5C is a sectional view taken along the VC-VC line of Figure 3 ;

[0029] Figure 6 is a view showing the positional relationship between the outlet of the second flow path of the gas guide and the first gas flow path when viewed in the axial direction. DETAILED DESCRIPTION

[0030] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that the following embodiments are merely illustrative of the preferred examples in essence, and have no intention of limiting the present invention, the application target of the present invention, or the range of use of the present invention.

[0031] EMBODIMENT

[0032] <1. Overall structure>

[0033] The scroll compressor 1 according to the embodiment of the present disclosure is connected to a refrigerant circuit in which a refrigerant gas is circulated to perform a refrigeration cycle, and compresses a refrigerant as a working fluid. The scroll compressor 1 is used, for example, in an air conditioning device, a refrigeration device.

[0034] Figure 1 is a longitudinal sectional view of the scroll compressor 1. As shown in Figure 1 , the scroll compressor 1 is a hermetic compressor of a full-closed type, and mainly includes a housing 10, a compression mechanism 14, a motor 6, a drive shaft 7, a lower bearing portion 21, a partition plate 26, a suction pipe 18, and a discharge pipe 19.

[0035] The housing 10 is a closed container having both ends closed. The housing 10 is a cylinder having a longitudinal length, and has a length in the axial direction. The housing 10 has a trunk portion 11, an upper end plate 12, and a lower end plate 13. The trunk portion 11 is a cylinder having an axis in the vertical direction. The upper end plate 12 has a convex surface protruding in a bowl shape toward the upper side. The upper end plate 12 is integrally combined with the trunk portion 11 by being welded to the upper end portion of the trunk portion 11 in a gas-tight manner. The lower end plate 13 has a convex surface protruding in a bowl shape toward the lower side. The lower end plate 13 is integrally combined with the trunk portion 11 by being welded to the lower end portion of the trunk portion 11 in a gas-tight manner.

[0036] The compression mechanism 14, the motor 6, the lower bearing portion 21, and the partition plate 26 are arranged in the housing 10. The compression mechanism 14 is arranged at a position near the upper end in the housing 10. The motor 6 is arranged at a position near the lower end in the housing 10. The lower bearing portion 21 is arranged at a position lower than the motor 6 in the housing 10. The partition plate 26 is arranged radially outward of the lower bearing portion 21 in the housing 10. The partition plate 26 is arranged below the motor 6 in the housing 10. The drive shaft 7 is housed in the housing 10 in a state in which the axis direction coincides with the axis direction of the trunk portion 11.

[0037] As will be described later, the compression mechanism 14 compresses refrigerant gas that has been introduced into the casing 10. The electric motor 6 drives the compression mechanism 14. Specifically, the electric motor 6 rotates the drive shaft 7, which rotates the orbiting scroll 5, which will be described later, thereby driving the compression mechanism 14.

[0038] An oil reservoir portion 15, which stores lubricating oil, is formed in the bottom of the casing 10. The partition plate 26 covers the lubricating oil stored in the bottom of the casing 10 from above.

[0039] An intake pipe 18 is provided on the trunk portion 11 of the casing 10. The intake pipe 18 introduces refrigerant gas in a refrigerant circuit into the casing 10. The intake pipe 18 opens in the casing 10 between the compression mechanism 14 and the electric motor 6. The intake pipe 18 communicates the inside and outside of the trunk portion 11.

[0040] An exhaust pipe 19 is provided on the top of the casing 10. The exhaust pipe 19 sends out refrigerant gas compressed by the compression mechanism 14 to the refrigerant circuit. The exhaust pipe 19 communicates the inside and outside of the upper end plate 12.

[0041] The drive shaft 7 has a main shaft portion 71, an eccentric portion 72, and a counterweight portion 73. The eccentric portion 72 is shorter than the main shaft portion 71. The eccentric portion is provided so as to extend in the axial direction from the upper end surface of the main shaft portion 71. The axis of the eccentric portion 72 is offset from the axis of the main shaft portion 71 by a prescribed distance. In order to maintain dynamic balance with the eccentric portion 72, the orbiting scroll 5, and the like, which will be described later, the counterweight portion 73 is provided on the radially outer side of the main shaft portion 71. An oil supply passage 74 is formed in the inside of the drive shaft 7 so as to extend from the upper end to the lower end of the drive shaft 7. The lower end portion of the drive shaft 7 is immersed in the oil reservoir portion 15.

[0042] The electric motor 6 is arranged below the compression mechanism 14 in the casing 10. The electric motor 6 has a stator 61 and a rotor 62. The stator 61 is fixed to the inner peripheral surface of the trunk portion 11 of the casing 10 by shrinkage fitting or the like. The rotor 62 is arranged on the radially inner side of the stator 61 and is fixed to the main shaft portion 71 of the drive shaft 7. The rotor 62 is arranged substantially coaxially with the main shaft portion 71. The rotor 62 is coupled to the compression mechanism 14 via the drive shaft 7.

[0043] The partition plate 26 is fixed to the inner peripheral surface of the trunk portion 11 of the casing 10 at a position between the electric motor 6 and the oil reservoir portion 15. The partition plate 26 is approximately circular in shape when viewed in the axial direction. The lower bearing portion 21 is fixed to the through hole in the central portion of the partition plate 26 by a screw or the like fastening member. The lower bearing portion 21 is substantially cylindrical and is arranged substantially coaxially with the partition plate 26. The lower bearing portion 21 rotatably supports the lower end portion of the drive shaft 7.

[0044] <2. Structure of the compression mechanism>

[0045] The compression mechanism 14 has a fixed member 3, a stationary scroll 4, and an orbiting scroll 5. The fixed member 3 is fixed to the upper portion of the trunk portion 11 of the housing 10. The stationary scroll 4 is fixed to the upper end portion of the trunk portion 11 of the fixed member 3. The orbiting scroll 5 is disposed between the stationary scroll 4 and the fixed member 3. The central portion of the fixed member 3 is recessed in a disc shape from the upper end side toward the lower end side. The fixed member 3 has an annular portion 31 on the outer peripheral side and a recessed portion 32 on the inner peripheral side.

[0046] A first gap 8 extending in the axial direction is formed between the outer peripheral surface of the fixed member 3 and the inner peripheral surface of the trunk portion 11 of the housing 10 at the angular position at which the suction pipe 18 is arranged. The first gap 8 communicates the space above the fixed member 3 with the space below the fixed member 3. A second gap 9 extending in the axial direction is formed between the outer peripheral surface of the fixed member 3 and the inner peripheral surface of the trunk portion 11 of the housing 10 at the angular position which is 180° rotationally symmetrical to the first gap 8. The gap 9 communicates the space above the fixed member 3 with the space below the fixed member 3. If the gaps 8, 9 are ignored, the fixed member 3 divides the internal space of the housing 10 into an upper space 16 and a lower space 17.

[0047] A through-hole 33 penetrating from the bottom of the recessed portion 32 to the lower end is formed in the fixed member 3. A bearing bush (omitted from illustration) is inserted in the through-hole 33. The drive shaft 7 is inserted in the bearing bush. In this way, the fixed member 3 constitutes an upper bearing which rotatably supports the upper end portion of the drive shaft 7. An oil discharge passage 38 extending from the recessed portion 32 toward the outer peripheral surface and opening at the second gap 9 is formed in the fixed member 3.

[0048] The stationary scroll 4 has a stationary side end plate portion 41, a stationary side scroll wrap 42, and an outer peripheral wall portion 43. The stationary side scroll wrap 42 is formed in a scroll wall shape which traces an involute curve and protrudes from the lower end surface of the stationary side end plate portion 41. The stationary scroll 4 is fixed to the trunk portion 11 of the housing 10.

[0049] The orbiting scroll 5 has an orbiting side end plate portion 51, an orbiting side scroll wrap 52, and a flange portion 53. The orbiting side end plate portion 51 is formed in a flat plate shape which is approximately circular when viewed in the axial direction. The orbiting side scroll wrap 52 is formed in a scroll wall shape which traces an involute curve and protrudes from the upper end surface of the orbiting side end plate portion 51. The flange portion 53 is formed in a cylindrical shape extending in the axial direction and is disposed at the central portion of the lower end surface of the orbiting side end plate portion 51.

[0050] The orbiting side scroll wrap 52 of the orbiting scroll 5 is engaged with the stationary side scroll wrap 42 of the stationary scroll 4. Also, a compression chamber 50 is formed in the compression mechanism 14, the compression chamber 50 being surrounded by the stationary side end plate portion 41 and the stationary side scroll wrap 42 of the stationary scroll 4 and the orbiting side end plate portion 51 and the orbiting side scroll wrap 52 of the orbiting scroll 5.

[0051] An outlet 44, penetrating the stationary end plate portion 41, opens at the center of the stationary vortex disk 4's stationary end plate portion 41. A high-pressure chamber 45 is formed on the upper end surface of the stationary end plate portion 41. The outlet 44 opens toward the high-pressure chamber 45. This high-pressure chamber 45 constitutes a high-pressure space. The high-pressure chamber 45 communicates with the space within the upper end plate 12.

[0052] The crosshead coupling 55 engages with the keyway formed on the lower end face of the moving side end plate portion 51 of the moving scroll plate 5 and the keyway formed on the annular portion 31 of the fixed member 3, thereby restricting the rotation of the moving scroll plate 5.

[0053] In the compression mechanism 14 described above, when the motor 6 is energized, the moving scroll 5 rotates under the action of the drive shaft 7. The rotation of the moving scroll 5 is restricted by the crosshead coupling 55, so the moving scroll 5 only revolves around the center. As the moving scroll 5 revolves, the volume between the two scrolls 42 and 52 contracts towards the center, thereby compressing the refrigerant gas flowing towards the center. The compressed refrigerant gas is then supplied to the refrigerant circuit through the nozzle 44 and the high-pressure chamber 45 from the nozzle pipe 19.

[0054] <3. Detailed Structure of the Gas Guide>

[0055] The scroll compressor 1 of this embodiment also includes a gas guide 80. Hereinafter, refer to... Figures 1-5C The structure of the gas guide 80 will be described in detail. It should be noted that in the following description, the orientation is defined using the axial, radial, and circumferential directions of the scroll compressor 1, based on the posture of the gas guide 80 after it is mounted on the scroll compressor 1.

[0056] The gas guide 80 is a component used to divert (rectify) the refrigerant gas drawn in from the suction pipe 18. For example... Figure 1 and Figure 3 As shown, the gas guide 80 is arranged opposite to the open end 18A of the suction tube 18 within the housing 10. The gas guide 80 includes a first curved surface 81, a second curved surface 82, a first flow path 83, and a second flow path 84.

[0057] Viewed from the axial upper end, the first curved surface 81 is a curved portion whose two ends in the circumferential direction are depicted as an imaginary arc. Specifically, the first curved surface 81 has a curvature extending along the inner circumferential surface of the body 11 of the housing 10.

[0058] Viewed from the lower axial side, the second curved surface 82 is a surface-shaped portion whose two ends are depicted as imaginary arcs in the circumferential direction. Specifically, the second curved surface 82 has the same curvature as the first curved surface 81. The second curved surface 82 and the first curved surface 81 are integrally connected, and together they form an imaginary curved surface. Figure 2 andFigure 3 As shown, the circumferential width W2 of the second curved portion 82 is longer than the circumferential width Wl of the first curved portion 81 (Wl < W2). The center line of the second curved portion 82 in the circumferential direction coincides with the center line of the first curved portion in the circumferential direction.

[0059] The first flow path 83 is a flow path for guiding a portion of the gas after passing through the suction pipe 18 toward the compression mechanism 14 side. As shown in FIG. 2, the first flow path 83 is recessed toward the radially inner side at the midway portion in the circumferential direction of the first curved portion 81. As shown in FIG. 3, the first flow path 83 has a rectangular shape when viewed in the radial direction. The first flow path 83 is provided in the entire axial range of the first curved portion 81. The first flow path 83 is recessed toward the radially inner side by a constant depth Dl at any portion. When the gas guide 80 is mounted on the scroll compressor 1, the central portion of the first flow path 83 is opposed to the open end 18A of the suction pipe 18 when viewed in the radial direction. Figure 5A Figure 3 As shown in FIG. 2, the first flow path 83 is recessed toward the radially inner side at the midway portion in the circumferential direction of the first curved portion 81. As shown in FIG. 3, the first flow path 83 has a rectangular shape when viewed in the radial direction. The first flow path 83 is provided in the entire axial range of the first curved portion 81. The first flow path 83 is recessed toward the radially inner side by a constant depth Dl at any portion. When the gas guide 80 is mounted on the scroll compressor 1, the central portion of the first flow path 83 is opposed to the open end 18A of the suction pipe 18 when viewed in the radial direction.

[0060] The second flow path 84 is a flow path for guiding the remaining portion of the gas after passing through the suction pipe 18 toward the motor 6 side. As shown in FIG. 4, the second flow path 84 is recessed toward the radially inner side at the midway portion in the circumferential direction of the second curved portion 82. In detail, the second flow path 84 has a reduced portion 85, an enlarged portion 86, and a wide portion 87. Further, the second flow path 84 has a throttling portion 88 between the reduced portion 85 and the enlarged portion 86. Figure 5B Figure 5C As shown in FIG. 4, the second flow path 84 is recessed toward the radially inner side at the midway portion in the circumferential direction of the second curved portion 82. In detail, the second flow path 84 has a reduced portion 85, an enlarged portion 86, and a wide portion 87. Further, the second flow path 84 has a throttling portion 88 between the reduced portion 85 and the enlarged portion 86.

[0061] The reduced portion 85 is a portion in which the flow path cross-sectional area is reduced as it is closer to the axial lower end side. As shown in FIG. 5, the reduced portion 85 has a shape of an approximately isosceles trapezoid when viewed in the radial direction. As shown in FIG. 6, the bottom of the flow path of the reduced portion 85 is formed to be gradually shallower as it is closer to the lower side. In other words, the face on the radially inner side of the reduced portion 85 is inclined with respect to the axial direction in such a manner that it is closer to the radially outer side as it is closer to the lower side. Figure 3 Figure 2 As shown in FIG. 5, the reduced portion 85 has a shape of an approximately isosceles trapezoid when viewed in the radial direction. As shown in FIG. 6, the bottom of the flow path of the reduced portion 85 is formed to be gradually shallower as it is closer to the lower side. In other words, the face on the radially inner side of the reduced portion 85 is inclined with respect to the axial direction in such a manner that it is closer to the radially outer side as it is closer to the lower side. Figure 4 As shown in FIG. 5, the reduced portion 85 has a shape of an approximately isosceles trapezoid when viewed in the radial direction. As shown in FIG. 6, the bottom of the flow path of the reduced portion 85 is formed to be gradually shallower as it is closer to the lower side. In other words, the face on the radially inner side of the reduced portion 85 is inclined with respect to the axial direction in such a manner that it is closer to the radially outer side as it is closer to the lower side.

[0062] Figure 3 As shown in FIG. 5, the reduced portion 85 has a shape of an approximately isosceles trapezoid when viewed in the radial direction. As shown in FIG. 6, the bottom of the flow path of the reduced portion 85 is formed to be gradually shallower as it is closer to the lower side. In other words, the face on the radially inner side of the reduced portion 85 is inclined with respect to the axial direction in such a manner that it is closer to the radially outer side as it is closer to the lower side. Figure 4 As shown in FIG. 5, the reduced portion 85 has a shape of an approximately isosceles trapezoid when viewed in the radial direction. As shown in FIG. 6, the bottom of the flow path of the reduced portion 85 is formed to be gradually shallower as it is closer to the lower side. In other words, the face on the radially inner side of the reduced portion 85 is inclined with respect to the axial direction in such a manner that it is closer to the radially outer side as it is closer to the lower side.

[0063] Figure 3 ​​​​​As shown, the wide portion 87 is provided below the enlarged portion 86 and is continuous with the enlarged portion 86. The wide portion 87 has a rectangular shape when viewed in the radial direction. As shown in FIG. 6, the wide portion 87 is recessed toward the radial inner side by a constant depth D2 at any portion. That is, the face of the wide portion 87 on the radial inner side forms a circular arc face continuous with the face of the enlarged portion 86 on the radial inner side. Figure 4

[0064] As shown, the throttle portion 88 is provided at the boundary portion between the reduced portion 85 and the enlarged portion 86. The throttle portion 88 is a portion in which the flow path cross-sectional area is reduced. The upper end of the throttle portion 88 is continuous with the lower end of the reduced portion 85, and the lower end of the throttle portion 88 is continuous with the upper end of the enlarged portion 86. Figure 3

[0065] Since the flow path cross-sectional area of the first flow path 83 is constant, the minimum flow path cross-sectional area is the area of the region shown by the double-dot chain line. On the other hand, the flow path cross-sectional area of the second flow path 84 varies in the axial direction, and thus the minimum flow path cross-sectional area is the area of the region (throttle portion) shown by the double-dot chain line. Figure 5A Figure 5B

[0066] <4. Detailed structure of stator>

[0067] Hereinafter, the detailed structure of the stator 61 according to the present embodiment will be described with reference to FIGS. 5 and 6. Figure 1 Figure 6 The detailed structure of the stator 61 according to the present embodiment will be described below.

[0068] Four core cutout portions are provided at regular intervals (90° intervals in the present embodiment) on the outer peripheral surface of the stator 61. Each core cutout portion is formed by cutting a portion of the outer peripheral surface of the stator 61 as if the portion were shaved from the stator 61 in the range from the upper end to the lower end of the stator 61. Each core cutout portion of the present embodiment forms a plane parallel to the axial direction. By arranging the core cutout portions between the outer peripheral surface of the stator 61 and the inner peripheral surface of the trunk portion 11 of the housing 10, a plurality of flow paths extending in the up-down direction are formed between the trunk portion 11 and the stator 61. The plurality of flow paths communicate one end side and the other end side of the motor 6 in the axial direction within the housing 10.

[0069] ​​​​​One of the plurality of flow passages, i.e., a first gas flow passage 91, is arranged at an angle position (specifically, substantially directly below) at which the suction pipe 18 is connected, for flowing the sucked refrigerant gas as a descending flow. Another one of the plurality of flow passages, i.e., an oil discharge passage 95, is arranged at an angle position that is 180° rotationally symmetrical to the first gas flow passage 91, for flowing the lubricating oil that has lubricated the bearing portion and the like within the drive shaft 7 to the oil reservoir portion 15. In the present embodiment, a guide member 57 for guiding the lubricating oil is arranged from the second gap 9 to the axial middle portion of the oil discharge passage 95. At least one of the remaining two flow passages, i.e., a second gas flow passage and a third gas flow passage, among the plurality of flow passages is for flowing a gas flow as an ascending flow, which is a gas flow that has become a swirling flow due to the rotation of the motor 6 after the aforementioned descending flow has collided with the partition plate 26.

[0070] The gas guide 80 is installed so that the first flow passage 83 opposes the open end 18A of the suction pipe 18, and the outlet (upper end) of the first flow passage 83 faces the compression mechanism 14 side, and the outlet (lower end) of the second flow passage 84 faces the motor 6 side, with the curved portions 81, 82 extending along the inner circumferential surface of the trunk portion 11. The installation can be performed using various known methods, such as screwing, welding, brazing, and the like. As shown in FIG. 6, when the gas guide 80 is installed on the scroll compressor 1, the outlet of the second flow passage 84 opposes the first open end 91A, which is the upper end of the first gas flow passage 91. The outlet of the second flow passage 84 encompasses the first open end 91A when viewed in the axial direction. That is, the first open end 91A is surrounded by the outlet of the second flow passage 84. Figure 6

[0071] <5. SUMMARY>

[0072] As described above, the scroll compressor 1 according to the present embodiment has the gas guide 80 that includes the first flow passage 83 for guiding a portion of the gas that has passed through the suction pipe 18 to the compression mechanism 14 side, and the second flow passage 84 for guiding the remaining portion of the gas that has passed through the suction pipe 18 to the gas flow passage 91. Therefore, a portion of the gas that has been sucked from the suction pipe 18 can be used to cool the motor 6 in the axial direction. As a result, the temperature difference between the one end side and the other end side of the motor 6 in the axial direction is reduced, and the temperature of each portion of the motor 6 tends to be uniform. Therefore, the temperature of the entire motor 6 can be accurately detected by the temperature sensor that is installed at one location of the motor 6. Furthermore, the temperature of the motor 6 can be accurately detected by one temperature sensor for detecting abnormal conditions such as excessive temperature rise, and the reliability of the motor 6 can be improved by taking appropriate measures based on the detection result.

[0073] As​Figure 5A and Figure 5B As shown in FIG. 8, the minimum flow passage sectional area of the first flow passage 83 is larger than the minimum flow passage sectional area of the second flow passage 84. Therefore, the gas sucked from the suction pipe 18 is more likely to flow toward the compression mechanism 14 side than the motor 6 side. As a result, it is possible to prevent adverse effects caused by excessive flow of the gas to the motor 6.

[0074] Specifically, since the gas flowing toward the motor 6 side absorbs heat from the motor 6, the temperature thereof rises, and the density thereof decreases. Therefore, the more the flow rate of the gas flowing toward the motor 6 side, the lower the density of the gas sucked into the compression mechanism 14, and as a result, the less the mass of the refrigerant sucked into the compression mechanism 14 per one revolution of the orbiting scroll 5. In contrast, in the present embodiment, by making the minimum flow passage sectional area of the first flow passage 83 larger than the minimum flow passage sectional area of the second flow passage 84, the flow rate of the gas flowing toward the motor 6 is limited. Therefore, according to the present embodiment, it is possible to suppress the decrease in the density of the gas sucked into the compression mechanism 14 to suppress the decrease in the efficiency of the scroll compressor 1, and it is possible to reduce the temperature difference between the one end side and the other end side of the motor 6 in the axial direction.

[0075] In the scroll compressor 1 according to the present embodiment, the second flow passage 84 of the gas guide 80 includes the reduced portion 85 and the enlarged portion 86. Therefore, the second flow passage 84 has the throttling portion 88 at the connection portion of the reduced portion 85 and the enlarged portion 86, thereby limiting the amount of the refrigerant gas flowing toward the motor 6 side. The refrigerant gas after the throttling portion 88 spreads along the surface of the enlarged portion 86, and as a result, the flow rate of the refrigerant gas is slowed down. As a result, it is possible to slow down the flow rate of the gas flowing toward the motor 6 side, and as described in the present embodiment, it is possible to prevent the decrease in the oil amount in the case where the oil reservoir 15 is arranged at a position closer to the lower end of the housing 10 than the motor 6 of the compression mechanism 14, or the like.

[0076] Specifically, if the flow rate of the refrigerant gas guided by the gas guide 80 to flow downward in the first gas flow path 91 is excessively high, it is possible that the lubricating oil of the oil reservoir portion 15 is kicked up by the gas ejected from the first gas flow path 91. The kicked-up lubricating oil flows together with the refrigerant gas and is sucked into the compression mechanism 14, and flows out to the outside of the scroll compressor 1 together with the refrigerant gas compressed in the compression mechanism 14 through the ejection pipe 19. Therefore, if the amount of the lubricating oil kicked up by the refrigerant gas after passing through the first gas flow path 91 increases, the amount of the lubricating oil flowing out to the outside of the scroll compressor 1 increases and the amount of the lubricating oil of the oil reservoir portion 15 decreases, as a result of which it is possible that the compression mechanism 14 and the like are damaged due to poor lubrication. In contrast, in the present embodiment, the flow rate of the gas flowing through the first gas flow path 91 is suppressed to be low by providing the enlarged portion 86 on the gas guide 80. Therefore, according to the present embodiment, it is possible to suppress the amount of the lubricating oil flowing out from the scroll compressor 1 to be small, and thus it is possible to ensure the reliability of the scroll compressor 1.

[0077] In the scroll compressor 1 according to the present embodiment, the outlet of the second flow path 84 of the gas guide 80 opposes the first open end 91A of the first gas flow path 91 on the gas guide side. Therefore, it is possible to efficiently cause the gas flowing through the second flow path 84 to flow to the first gas flow path 91.

[0078] In the scroll compressor 1 according to the present embodiment, the outlet of the second flow path 84 coincides with the entire first open end 91A of the first gas flow path 91 when viewed in the axial direction of the housing 10. Therefore, it is possible to prevent the refrigerant gas flowing through the second flow path 84 from flowing to the first gas flow path 91 entirely. That is, it is possible to suppress the gas flowing through the second flow path 84 from flowing excessively into the first gas flow path 91. As a result, it is possible to prevent adverse effects due to excessive flow of the gas to the motor 6 side.

[0079] In the scroll compressor 1 according to the present embodiment, the bottom of the reduced portion 85 of the gas guide 80 is inclined so as to be closer to the radially outer side as it is closer to the axial direction lower end side. In this way, the minimum flow path cross-sectional area of the first flow path 83 is made larger than the minimum flow path cross-sectional area of the second flow path 84 with a simple structure. As a result, it is possible to cause the refrigerant gas sucked in from the suction pipe 18 to flow more easily to the compression mechanism 14 side than to the motor 6 side with a simple structure.

[0080] The above describes an illustrative embodiment of the present application, but the present application is not limited to the above-described embodiment.

[0081] In the above-described embodiment, the compressor is a scroll compressor, but is not limited thereto. The compressor can be, for example, a rotary compressor, a screw compressor, a sliding vane type compressor, or the like, instead of the above-described compressor.

[0082] In the above-described embodiment, the axial direction of the housing 10 is the vertical direction, i.e., a so-called vertical arrangement, but is not limited thereto. The compressor can also be arranged horizontally instead of the above-described arrangement.

[0083] In the above-described embodiment, the line demarcating the boundary between the gas guide and the curved surface portion is a straight line, but is not limited thereto. Instead of the above-described arrangement, the boundary between the gas guide and the curved surface portion can be curved, thereby making the flow of the working fluid smoother, for example, from the narrowing portion to the throttling portion, or from the throttling portion to the expanding portion.

[0084] In the above-described embodiment, the shape of the core cutout portion of the stator 61 is planar as if a portion of the outer periphery of the stator 61 is shaved, but is not limited thereto. Instead of the above-described arrangement, the core cutout portion can have a shape as if a portion of the outer periphery of the stator is cut into a circular arc shape.

[0085] The elements appearing in the above-described embodiments and modified examples can be appropriately combined without causing contradiction.

[0086] - Industrial Applicability -

[0087] The present disclosure is useful for a compressor.

[0088] - Symbol Explanation -

[0089] 1 Scroll Compressor (Compressor)

[0090] 3 Fixed Member

[0091] 4 Static Scroll

[0092] 5 Dynamic Scroll

[0093] 6 Motor

[0094] 7 Drive Shaft

[0095] 8 First Gap

[0096] 9 Second Gap

[0097] 10 Housing

[0098] 11 Body

[0099] 14 Compression Mechanism

[0100] 18 Suction Pipe

[0101] 19 Discharge Pipe

[0102] 38 Oil Discharge Passage

[0103] 41 Static Side End Plate Portion

[0104] 42 static side scroll

[0105] 44 discharge port

[0106] 45 high-pressure chamber

[0107] 50 compression chamber

[0108] 51 dynamic side end plate portion

[0109] 52 dynamic side scroll

[0110] 53 flange portion

[0111] 57 guide member

[0112] 61 stator

[0113] 62 rotor

[0114] 71 shaft portion

[0115] 72 eccentric portion

[0116] 73 counterweight portion

[0117] 74 oil supply passage

[0118] 80 gas guide

[0119] 81 first curved surface portion

[0120] 82 second curved surface portion

[0121] 83 first flow path

[0122] 84 second flow path

[0123] 85 narrowing portion

[0124] 86 expanding portion

[0125] 87 wide portion

[0126] 88 throttle portion

[0127] 91 first gas flow path

[0128] 91A first open end

[0129] 95 oil discharge passage

Claims

1. A compressor (1), characterized in that: It includes a cylindrical housing (10), a compression mechanism (14), an electric motor (6), an intake pipe (18), a gas flow path (91), and a gas guide (80). The compression mechanism (14) is located inside the housing (10) near one end of the housing (10) to compress the gas. The electric motor (6) is located inside the housing (10) near the other end of the housing (10) and drives the compression mechanism (14). The suction tube (18) opens between the compression mechanism (14) and the motor (6) within the housing (10). The gas flow path (91) is formed between the inner circumferential surface of the motor (6) and the housing (10), so that one axial end of the motor (6) inside the housing (10) is connected to the other axial end. The gas guide (80) is arranged opposite to the open end (18A) of the suction tube (18) within the housing (10). The gas guide (80) has a first flow path (83) and a second flow path (84). The first flow path (83) guides a portion of the gas following the intake pipe (18) toward the compression mechanism (14). The second flow path (84) guides the remaining portion of the gas after passing through the suction tube (18) into the gas flow path (91). The second flow path (84) includes a shrinking section (85) and an enlarging section (86). The cross-sectional area of ​​the flow path of the reduced section (85) decreases as it approaches the outlet side of the second flow path (84). The enlarged portion (86) is located closer to the outlet side of the second flow path (84) than the reduced portion (85), and the flow path cross-sectional area of ​​the enlarged portion (86) increases as it approaches the outlet side of the second flow path (84).

2. The compressor according to claim 1, characterized in that: The minimum cross-sectional area of ​​the first flow path (83) is larger than the minimum cross-sectional area of ​​the second flow path (84).

3. The compressor according to claim 1 or 2, characterized in that: The outlet of the second flow path (84) is opposite to the first opening end (91A) of the gas flow path (91) near the gas guide (80).

4. The compressor according to claim 3, characterized in that: When viewed along the axial direction of the housing (10), the outlet of the second flow path (84) coincides with the entire first opening end (91A) of the gas flow path (91).

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