JP2014125959A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of maintaining the reliability of a pump by suppressing swinging rotation of the pump.SOLUTION: A compressor comprises: a compression mechanism 15; a drive motor 16; a casing 10 in which an oil reservoir space P storing lubrication oil is formed; a pump 80 including an inner rotor 82 and an outer rotor 83, and pumping up the lubrication oil in the oil reservoir space P; a crankshaft 17 including a main shaft portion 17a and an eccentric portion 17b; and an attachment member 70 attaching the pump 80 to a lower end of the crankshaft 17. Oil supply holes 61a, 61b, 61c, 61d, 62a, and 72a are formed within the crankshaft 17. The attachment member 70 is located on the lower end of the crankshaft 17 so that a rotational center of the inner rotor 82 is eccentric to a shaft center of the crankshaft 17.

Description

  The present invention relates to a compressor.

  2. Description of the Related Art Conventionally, some refrigeration apparatuses such as air conditioners employ a scroll compressor as disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. Hei 8-219062). This compressor accommodates a compression element, a drive shaft connected to the compression element and having an oil supply passage formed therein, a motor for driving the drive shaft, a compression element, the drive shaft, and the motor, and lubricating oil is contained at the bottom. And a stored casing. In this compressor, a positive displacement oil pump is further provided at the lower end of the drive shaft. The oil pump is attached to the drive shaft via a connecting body connected to the drive shaft. In this compressor, the rotational force of the drive shaft is transmitted to the oil pump and the oil pump acts, so that the lubricating oil stored at the bottom is pumped into the oil supply passage of the drive shaft.

  In a compressor as disclosed in Patent Document 1, the compression element usually includes a fixed scroll and a movable scroll that meshes with the fixed scroll. In this compressor, the drive shaft usually has a main shaft portion and an eccentric portion eccentric to the main shaft portion, so that the movable scroll rotates eccentrically with respect to the fixed scroll. moving.

  Here, in such a compressor, it is conceivable that the drive shaft is inclined by receiving the force of the gas refrigerant due to the compression in the compression element. For this reason, in a compressor provided with a drive shaft having an eccentric portion, it is considered that eccentric rotation may be performed with the drive shaft tilted. As a result, the connecting body connected to the drive shaft swings around at a position shifted from the original rotation center of the oil pump. Therefore, the load of the oil pump connected to the coupling body increases, and there is a possibility that the reliability of the oil pump cannot be maintained.

  Then, the subject of this invention is providing the compressor which can maintain the reliability of a pump by suppressing the whirling of a pump.

  The compressor which concerns on the 1st viewpoint of this invention accommodates the compression mechanism, the drive motor which drives a compression mechanism, the compression mechanism, and a drive motor, and the oil sump space which stores lubricating oil in the bottom part is formed. A casing, a pump, and a crankshaft are provided. The pump has an inner rotor and an outer rotor located on the outer peripheral side of the inner rotor. The pump is accommodated in the casing so as to suck up the lubricating oil in the oil sump space by the rotation of the inner rotor. The crankshaft has a main shaft portion whose axial center coincides with the rotation center of the drive motor when viewed in the axial direction, and an eccentric portion that is eccentric with respect to the main shaft portion, and compresses the driving force transmitted from the drive motor. It is accommodated in the casing so as to be transmitted to the mechanism. The crankshaft is formed with an oil supply hole through which lubricating oil sucked up by the pump flows. An attachment member for attaching the pump to the lower end portion of the crankshaft is connected to the lower end portion of the crankshaft by connecting the inner rotor. The attachment member is connected to the lower end portion of the crankshaft so that the rotation center of the inner rotor is eccentric with respect to the axis of the crankshaft.

  Here, in the compressor provided with the drive shaft having the eccentric portion as in the present invention, it is considered that eccentric rotation may be performed in a state where the drive shaft is inclined as described above. As a result, the pump swings around at a position deviated from the original center of rotation. For this reason, we are anxious about the load of a pump becoming large.

  Therefore, in the present invention, the mounting member is configured such that the rotation center of the inner rotor is eccentric with respect to the axis of the crankshaft. This makes it possible to rotate the inner rotor as much as possible at the original rotation center. That is, the swinging of the inner rotor can be suppressed. Therefore, contact between the outer rotor and the pump can be reduced, and reliability can be maintained.

  The compressor which concerns on the 2nd viewpoint of this invention is a compressor which concerns on the 1st viewpoint of this invention, Comprising: The lower main bearing which pivotally supports the part which is a lower end part of a crankshaft and is located above a pump is further provided Prepare. The amount of eccentricity of the rotation center of the inner rotor with respect to the axis of the crankshaft is a gap distance between the lower main shaft portion of the crankshaft and the lower main bearing. The lower main shaft portion of the crankshaft is supported by a lower main bearing.

  In the present invention, the rotational amount of the inner rotor can be reduced by decentering the rotation center of the inner rotor with respect to the axis of the crankshaft.

  The compressor which concerns on the 3rd viewpoint of this invention is a compressor which concerns on the 2nd viewpoint of this invention, Comprising: The internal peripheral surface and attachment member of an inner rotor are connected, The internal peripheral surface and attachment member of an inner rotor, The center of the connecting portion is eccentric with respect to the axis of the crankshaft.

  In this compressor, the center of the connecting portion between the inner peripheral surface of the inner rotor and the mounting member is decentered with respect to the axis of the crankshaft, so that the rotation center of the inner rotor is offset from the axis of the crankshaft. Are eccentric. As a result, the inner rotor can be rotated as much as possible at the original rotation center, and the whirling of the inner rotor can be suppressed.

  The compressor which concerns on the 4th viewpoint of this invention is a compressor which concerns on the 3rd viewpoint of this invention, Comprising: A mounting member is attached to the pump shaft part connected with the inner rotor of a pump, and the lower end part of a crankshaft. Mounting portion. The inner peripheral surface of the inner rotor and the pump shaft portion are connected, and the center of the connecting portion between the inner peripheral surface of the inner rotor and the pump shaft portion is eccentric with respect to the axis of the crankshaft.

  In the present invention, the center of the connecting portion between the inner peripheral surface of the inner rotor and the pump shaft portion is decentered with respect to the axis of the crankshaft. The rotation center of the inner rotor can be eccentric with respect to the axis of the crankshaft.

  A compressor according to a fifth aspect of the present invention is the compressor according to the second aspect or the third aspect of the present invention, wherein the mounting member includes a pump shaft portion connected to an inner rotor of the pump, and a crankshaft. And an attachment portion attached to the lower end portion. The center of the mounting portion is eccentric with respect to the axis of the crankshaft.

  In the present invention, the center of the mounting portion of the mounting member is decentered with respect to the axis of the crankshaft, so that the center of rotation of the inner rotor can be easily adjusted by simply connecting the inner rotor to the mounting member. It is possible to make the shaft eccentric.

  A compressor according to a sixth aspect of the present invention is the compressor according to any one of the second aspect to the fifth aspect of the present invention, wherein the attachment member has the rotation center of the inner rotor at the axis of the crankshaft. On the other hand, the crankshaft is connected to the lower end portion of the crankshaft so as to be eccentric in the direction opposite to the load direction with respect to the lower main bearing of the crankshaft.

  In the present invention, the rotation center of the inner rotor is eccentric with respect to the axis of the crankshaft in the direction opposite to the load direction with respect to the lower main bearing of the crankshaft. Thereby, the center of rotation of the inner rotor can be positioned in advance at a position where the whirling of the inner rotor is suppressed. Therefore, the amount of swinging of the inner rotor can be reduced.

  In the compressor according to the present invention, the reliability of the pump can be maintained by suppressing the swing of the pump.

The longitudinal cross-sectional view of the compressor which concerns on one Embodiment of this invention. The perspective view of the attachment member connected with a crankshaft. The schematic block diagram of the lower end part of a crankshaft. The schematic diagram which shows the eccentric direction with respect to the axial center of the crankshaft of the center of the attachment member connected with a crankshaft in an axial direction upper view. The longitudinal cross-sectional view of the compressor which concerns on the modification A. FIG. The perspective view of the attachment member concerning the modification A. FIG. The schematic diagram which shows the eccentric direction with respect to the axial center of the crankshaft of the center of the pump shaft part of a crankshaft in the axial direction upper view based on the modification A.

  Hereinafter, a compressor 1 according to an embodiment of the present invention will be described with reference to the drawings.

(1) Configuration of Compressor FIG. 1 is a longitudinal sectional view of a compressor 1 according to this embodiment. In the following description, a rotation center line OO passing through the rotation center of the drive motor 16 shown in FIG. The direction along the axis is the axial direction or the vertical (vertical) direction. A direction orthogonal to the axial direction is a radial direction, and a direction around the axial direction is a circumferential direction.

  The compressor 1 is used for compressing a refrigerant in a refrigerant circuit that performs a refrigeration cycle by circulating the refrigerant. The compressor 1 is a high-low pressure dome type scroll compressor, and compresses refrigerant by revolving at least one scroll of two scrolls meshing with each other without rotating.

  As shown in FIG. 1, the compressor 1 mainly includes a casing 10, a suction pipe 18, a discharge pipe 19, a compression mechanism 15, a drive motor 16, a lower main bearing housing 60, and an oil separation plate 65. A crankshaft 17, a gas guide 58, and a pump 80. The compressor 1 includes a suction pipe 18 and a part of a discharge pipe 19, a compression mechanism 15, an upper bearing 33, a drive motor 16, a lower main bearing housing 60, an oil separation plate 65, a crankshaft 17, in an internal space of the casing 10. It has a sealed structure in which the gas guide 58 and the pump 80 are accommodated. Hereinafter, the components of the compressor 1 will be described.

(1-1) Casing, Suction Pipe, and Discharge Pipe The casing 10 is a vertical cylindrical container that extends in the axial direction, and is mainly hermetically sealed with a substantially cylindrical tubular portion 11 and an upper end of the tubular portion 11. It is comprised from the bowl-shaped upper wall part 12 welded in the shape, and the bowl-shaped bottom wall part 13 welded to the lower end of the cylindrical part 11 airtightly.

  The internal space of the casing 10 is partitioned into a high-pressure space S1 that is a space below the compression mechanism 15 and a low-pressure space S2 that is a space above the compression mechanism 15.

  A suction pipe 18 and a discharge pipe 19 are connected to the casing 10. The suction pipe 18 is a tubular member that penetrates the upper wall portion 12, and is a member that sucks the refrigerant circulating in the refrigerant circuit from the outside of the casing 10 to the compression chamber 40 (described later) in the compression mechanism 15. . The lower end of the suction pipe 18 is fitted into a fixed scroll 24 (described later). The discharge pipe 19 is a tubular member that penetrates the cylindrical portion 11, and is a member that discharges the compressed refrigerant from the high-pressure space S <b> 1 to the outside of the casing 10.

  An oil sump space P, which is a space for storing lubricating oil, is formed at the bottom of the internal space of the casing 10. Lubricating oil is used in order to keep the lubricity of sliding parts, such as compression mechanism 15, favorable during operation of compressor 1.

(1-2) Compression mechanism The compression mechanism 15 sucks the low-temperature and low-pressure refrigerant, and discharges it after compressing the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant. The compression mechanism 15 is connected to the upper end of the crankshaft 17. The compression mechanism 15 mainly has an upper bearing housing 23, a fixed scroll 24, and a movable scroll 26.

(1-2-1) Upper Bearing Housing The upper bearing housing 23 is press-fitted into the inner peripheral side of the cylindrical portion 11 of the casing 10, and the outer peripheral surface thereof is in close contact with the inner peripheral surface of the cylindrical portion 11 of the casing 10. Yes. As described above, the outer peripheral surface of the upper bearing housing 23 and the inner peripheral surface of the cylindrical portion 11 of the casing 10 are in close contact with each other, so that the internal space of the casing 10 is divided into the above-described high-pressure space S1 and low-pressure space S2. Has been.

  The upper bearing housing 23 mounts the fixed scroll 24 by being fixed with bolts or the like, and sandwiches the movable scroll 26 together with the fixed scroll 24 via the Oldham joint 39. Here, the Oldham joint 39 is an annular member for preventing the movable scroll 26 from rotating. A hole penetrating in the axial direction is formed in the outer peripheral portion of the upper bearing housing 23, and this hole constitutes a second communication passage 48 through which the refrigerant flows. The second communication passage 48 communicates with the first communication passage 46 (described later) and the high-pressure space S1.

  Further, the upper bearing housing 23 is formed with a housing recess 31 that is recessed in the center portion of the upper surface, and a bearing holding portion 32 that extends downward from the center portion in the axial direction. A boss portion 26 c (described later) of the movable scroll 26 is located in the inner space of the housing recess 31. An upper bearing 33 (described later) is press-fitted into the bearing holding portion 32.

(1-2-2) Fixed Scroll The fixed scroll 24 is a disc-shaped first end plate 24a and a spiral shape (involute shape) connected to the lower surface of the first end plate 24a and orthogonal to the lower surface of the first end plate 24a. 1st wrap 24b.

  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 is a hole that communicates the internal space of the suction pipe 18 and a compression chamber 40 described later. The auxiliary suction hole is a hole that communicates the low pressure space S <b> 2 and the compression chamber 40.

  A discharge hole 41 is formed at the center of the first end plate 24a. The discharge hole 41 is a hole for discharging the refrigerant compressed in the compression chamber 40. In addition, an enlarged recess 42 communicating with the discharge hole 41 is formed on 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 fastened and fixed to the upper surface of the fixed scroll 24 with a bolt or the like so as to close the enlarged concave portion 42. And the muffler space 45 which consists of an expansion chamber which silences the driving | running sound of the compression mechanism 15 by covering the expansion recessed part 42 with the cover body 44 is formed. The fixed scroll 24 and the lid 44 are sealed by being brought into close contact with each other via a gasket (not shown). The fixed scroll 24 is formed with a first communication passage 46 that communicates with the muffler space 45 and opens on the lower surface of the fixed scroll 24.

(1-2-3) Movable Scroll The movable scroll 26 is connected to the upper surface of the second end plate 26a and the second end plate 26a, and a second wrap having a spiral shape (involute shape) perpendicular to the upper surface of the second end plate 26a. 26b. A boss portion 26c having a pin bearing 35 that supports the upper end portion of the crankshaft 17 (ie, an eccentric portion 17b described later) on the inner side 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 pores 63 communicate the outer peripheral portion of the upper surface of the second end plate 26a with the space inside the boss portion 26c. In addition, an elliptical key groove 26d into which a key portion (not shown) of the Oldham joint 39 is fitted is formed on the lower surface of the second end plate 26a.

  In the compression mechanism 15 having the above configuration, the first end plate 24a, the first end plate 24b, the second end plate 26a, and the second end plate 26a of the movable scroll 26 mesh with the first end plate 24b of the fixed scroll 24 and the second end plate 26a. A compression chamber 40, which is a space surrounded by the second wrap 26b, is formed. In the compression chamber 40, the refrigerant is compressed by reducing the volume by the revolving motion of the movable scroll 26.

(1-3) Upper Bearing The upper bearing 33 is a sliding bearing fitted to the bearing holding portion 32 of the upper bearing housing 23, and rotatably supports the upper portion (main shaft portion 17a described later) of the crankshaft 17. . The upper bearing 33 may be a rolling bearing.

(1-4) Drive Motor The drive motor 16 is connected to a crankshaft 17 that is connected to the compression mechanism 15, and is a brushless DC motor that drives the compression mechanism 15 via the crankshaft 17. The drive motor 16 is disposed below the compression mechanism 15.

  The drive motor 16 mainly includes a stator 51 that is fixed to the inner wall of the cylindrical portion 11 of the casing 10 and a rotor 52 that is rotatably disposed inside the stator 51 in the radial direction. An air gap, which is a slight gap, is formed between the inner peripheral surface of the stator 51 and the outer peripheral surface of the rotor 52.

  The stator 51 has a coil part (not shown) around which a copper wire is wound, and a coil end 53 formed above and below the coil part. In addition, a plurality of core cut portions (not shown) are formed on the outer peripheral surface of the stator 51 so as to extend from the upper end surface to the lower end surface of the stator 51 and at predetermined intervals in the circumferential direction. ing. The core cut portion forms a motor cooling passage 55 extending in the axial direction between the tubular portion 11 and the stator 51. The crankshaft 17 is fitted in the central portion of the rotor 52.

(1-5) Lower Main Bearing Housing The lower main bearing housing 60 is disposed below the drive motor 16. The lower main bearing housing 60 supports a lower main bearing 34 as a slide bearing that pivotally supports a lower end portion of the crankshaft 17 and a portion located above the pump 80. The outer surface of the lower main bearing housing 60 is joined to the inner wall of the cylindrical portion 11 of the casing 10. The lower main bearing 34 may be a rolling bearing.

(1-6) Oil Separation Plate The oil separation plate 65 is a flat plate-like member that separates the lubricating oil from the descending refrigerant. The oil separation plate 65 is fixed to the upper end surface of the lower main bearing housing 60.

(1-7) Crankshaft FIG. 2 is a schematic perspective view of the attachment member 70 connected to the crankshaft 17. FIG. 3 is a schematic configuration diagram of the lower end portion of the crankshaft 17. FIG. 4 is a schematic diagram showing an eccentric direction of the center AA of the mounting member 70 with respect to the axis of the crankshaft 17 when viewed in the axial direction.

  The crankshaft 17 connects the compression mechanism 15 and the drive motor 16. The crankshaft 17 includes a main shaft portion 17a, an eccentric portion 17b that constitutes the upper end portion of the crankshaft 17, a balance weight portion 17c that balances the mass of the crankshaft 17, a lower main shaft portion 17d, and a lower end of the crankshaft 17. And an attachment member 70 located in the section.

  As shown in FIG. 1, the crankshaft 17 has a hollow shape in which a longitudinal oil supply hole 61a extending in the axial direction is formed. The vertical oil supply hole 61 a communicates with the oil chamber 89. The oil chamber 89 is a space formed by the upper end surface of the crankshaft 17 (specifically, the eccentric portion 17b) and the lower surface of the second end plate 26a. The oil chamber 89 communicates with a sliding portion between the fixed scroll 24 and the movable scroll 26 (referred to as a sliding portion of the compression mechanism 15 in this embodiment as appropriate) through the oil supply hole 63 of the second end plate 26a. ing. The oil chamber 89 communicates with the low pressure space S <b> 2 via the compression chamber 40.

(1-7-1) Main shaft portion The main shaft portion 17a is a portion that rotates around the rotation center line OO of the drive motor 16. That is, the axis of the main shaft portion 17 a coincides with the rotation center line OO of the drive motor 16 in the axial direction view. The main shaft portion 17 a is located below the eccentric portion 17 b of the crankshaft 17 and is pivotally supported by the upper bearing 33. The main shaft portion 17a is formed therein with a first oil supply horizontal hole 61b that branches from the vertical oil supply hole 61a in the horizontal direction. The 1st oil supply horizontal hole 61b is formed so that lubricating oil can be supplied to the sliding part of the upper bearing 33 and the main-shaft part 17a.

(1-7-2) Eccentric portion The eccentric portion 17b is provided at the upper end of the main shaft portion 17a so that the shaft core S11 (see FIG. 4) is eccentric with respect to the axial center of the main shaft portion 17a. ing. The eccentric portion 17 b is pivotally supported by a pin bearing 35 that is fitted inside the boss portion 26 c of the movable scroll 26. Further, the eccentric portion 17b is formed with a second oil supply horizontal hole 61c that branches from the vertical oil supply hole 61a in the horizontal direction. The second oil supply lateral hole 61c is formed so that the lubricating oil can be supplied to the sliding portion between the pin bearing 35 and the eccentric portion 17b.

(1-7-3) Balance Weight Part The balance weight part 17c is a part that is fixed in close contact with the outer peripheral surface of the main shaft part 17a. The balance weight portion 17 c is fixed to the outer peripheral surface located above the drive motor 16. The balance weight portion 17c is provided so as to be positioned in a direction opposite to the eccentric direction of the eccentric portion 17b.

(1-7-4) Lower Main Shaft Portion The lower main shaft portion 17d is positioned below the drive motor 16 and is pivotally supported by the lower main bearing 34. The lower main shaft portion 17d is formed therein with a third oil supply horizontal hole 61d branched in a horizontal direction from the vertical oil supply hole 61a. The third oil supply lateral hole 61d is formed so that lubricating oil can be supplied to the sliding portion between the lower main bearing 34 and the lower main shaft portion 17d.

(1-7-5) Mounting Member The mounting member 70 has a convex shape protruding downward as shown in FIGS. 2 and 3, and is mainly a disk that is press-fitted into the groove 71 a of the crankshaft 17. A mounting portion 73 that is a large-diameter portion and a pump shaft portion 74 that is a disk-shaped small-diameter portion that protrudes downward from the lower surface of the mounting portion 73. The mounting portion 73 is press-fitted into the groove 71a so that the outer peripheral surface thereof is in close contact with the inner peripheral surface of the groove 71a. The attaching portion 73 is press-fitted into the groove 71a so that the center AA (see FIG. 2) of the attaching member 70 coincides with the center of the groove 71a in the axial direction. The pump shaft portion 74 is formed so that its outer diameter is smaller than the outer diameter of the mounting portion 73 so as to be fitted into a through hole 82a (described later) formed in an inner rotor 82 (described later) of the pump 80. Yes. An inner rotor of the pump 80 is attached to the pump shaft portion 74 so that the inner peripheral surface of the inner rotor 82 of the pump 80 is in contact with the outer peripheral surface thereof. Thus, in this embodiment, the pump 80 is attached to the lower end portion of the crankshaft 17 by the inner rotor 82 of the pump 80 being attached to the lower end portion of the crankshaft 17 via the attachment member 70. ing.

  Further, the attachment member 70 is formed with a through-hole 72a penetrating in the axial direction at the center thereof. The diameter of the through hole 72a is smaller than the diameter of the vertical oil supply hole 61a, and communicates with the vertical oil supply hole 61a. In addition, the through hole 72 a communicates with the discharge port of the pump 80. Thus, the through-hole 72a formed in the attachment member 70 communicates with the vertical oil supply hole 61a and the discharge port of the pump 80, so that when the pump 80 is operated, it is stored in the oil sump space P. The lubricating oil is sucked into the pump chamber 86 (described later) through the suction port 81a (described later), and the lubricating oil flowing into the pump chamber 86 passes through the through-hole 72a communicating with the discharge port. It is supposed to flow through. In this case, the vertical oil supply hole 61a, the first oil supply horizontal hole 61b, the second oil supply horizontal hole 61c, the third oil supply horizontal hole 61d, and the through hole 72a flow through the lubricating oil sucked up by the pump 80. Is formed.

  Here, the center AA of the attachment member 70 coincides with the center of the groove 71a of the crankshaft 17 in the axial view. Accordingly, the center AA of the mounting member 70 is eccentric with respect to the axis of the crankshaft 17. Specifically, the groove 71a of the crankshaft 17 is such that the center AA of the mounting member 70 is in the load direction DI1 with respect to the lower main bearing 34 of the crankshaft 17 as viewed in the axial direction with respect to the axis of the crankshaft 17. It is formed so as to be eccentric in the direction DI2 (see FIG. 4) opposite to (see FIG. 4). That is, as viewed in the axial direction, the direction from the axis of the crankshaft 17 toward the center AA of the mounting member 70 of the crankshaft 17 coincides with the direction DI2. More specifically, the load direction DI1 with respect to the lower main bearing 34 of the crankshaft 17 is 110 ° to 200 ° when the eccentric direction of the eccentric portion 17b of the crankshaft 17 is 90 ° as shown in FIG. Direction. Therefore, since the direction DI2 is a direction opposite to the direction DI1, the direction DI2 is a direction of 290 ° to 20 °. The above-mentioned angle is a counterclockwise angle with reference to the reference line STL1 shown in FIG.

  Further, the groove 71a of the crankshaft 17 is such that the eccentric amount of the center AA of the mounting member 70 with respect to the axis of the crankshaft 17 is a gap distance D1 between the crankshaft 17 and the lower main bearing 34 (FIG. 3). For example). The gap distance D1 between the lower main shaft portion 17d of the crankshaft 17 and the lower main bearing 34 is such that the axis of the crankshaft 17 and the center of the lower main bearing 34 overlap each other. This is the distance of the gap between the outer peripheral surface and the inner peripheral surface of the lower main bearing 34, that is, the radial clearance of the lower main bearing 34. The gap distance D1 is 25 μm, for example.

  As described above, the crankshaft 17 is connected to the compression mechanism 15 (specifically, the movable scroll 26) and the drive motor 16 (specifically, the rotor 52) from the drive motor 16. The transmitted driving force is transmitted to the compression mechanism 15. Specifically, when a current flows through the drive motor 16, first, the rotor 52 rotates counterclockwise as viewed from above around the rotation center line OO, and this rotational driving force is transmitted to the crankshaft 17. Then, the crankshaft 17 rotates counterclockwise as viewed from above. When the crankshaft 17 rotates, the driving force of the rotor 52 (drive motor 16) is transmitted to the movable scroll 26 (compression mechanism 15) connected to the crankshaft 17, and the movable scroll 26 is driven. . At this time, the crankshaft 17 has the eccentric portion 17b that is eccentric with respect to the rotation center line OO of the drive motor 16, so that the movable scroll 26 performs eccentric rotation.

(1-8) Pump As shown in FIG. 1 and FIG. 3, the pump 80 is a positive displacement pump connected to the lower end of the crankshaft 17 via an attachment member 70 located at the lower end of the crankshaft 17. It is a trochoid pump. The pump 80 is fixed to the lower surface of the lower main bearing housing 60.

  The pump 80 mainly includes a pump casing 81, a rotatable inner rotor 82, an outer rotor 83 positioned on the outer peripheral side of the inner rotor 82, and a lid 84. The rotor 82, the outer rotor 83, and the lid 84 are accommodated.

  The pump casing 81 is formed with a suction port 81a, a plurality of bolt holes 81b, and a discharge port (not shown). The suction port 81a is formed to face the lubricating oil stored in the oil reservoir space P. The suction port 81 a communicates with a pump chamber 86 formed between the outer peripheral surface of the inner rotor 82 and the inner peripheral surface of the outer rotor 83. The bolt hole 81 b is a hole through which a bolt passes in order to fix the pump 80 to the lower surface of the lower main bearing housing 60. The discharge port communicates with the vertical oil supply hole 61 a through the through hole 72 a formed in the attachment member 70 and also communicates with the pump chamber 86. The discharge port discharges the lubricating oil sucked from the suction port 81a and flowing into the pump chamber 86 into the vertical oil supply hole 61a through the through hole 72a.

  The inner rotor 82 is rotatably accommodated in the pump casing 81. The inner rotor 82 has a plurality of external teeth (not shown) formed on the outer peripheral edge thereof. Further, the inner rotor 82 has a through hole 82a penetrating in the axial direction at the center thereof, and by fitting the pump shaft portion 74 of the mounting member 70 of the crankshaft 17 into the through hole 82a, It is connected to the lower end of the crankshaft 17. The inner peripheral surface of the inner rotor 82 is in close contact with the outer peripheral surface of the pump shaft portion 74 of the mounting member 70 of the crankshaft 17. Thus, when the crankshaft 17 rotates, the inner rotor 82 rotates as the crankshaft 17 rotates. That is, in this embodiment, the attachment member 70 of the crankshaft 17 functions as a pump drive shaft that operates the pump 80 by transmitting the driving force of the drive motor 16 to the inner rotor 82.

  Here, the center AA of the mounting member 70 is eccentric with respect to the axis of the crankshaft 17. Therefore, the rotation center of the inner rotor 82 whose inner peripheral surface is attached in close contact with the outer peripheral surface of the attachment member 70 (specifically, the pump shaft portion 74) is a center line passing through the center AA of the attachment member 70. It is on L1 and is eccentric with respect to the axis of the crankshaft 17.

  The outer rotor 83 is rotatably accommodated in the pump casing 81, and has a plurality of internal teeth (not shown) that mesh with a plurality of external teeth formed on the inner rotor 82. The number of external teeth formed on the inner rotor 82 and the number of internal teeth formed on the outer rotor 83 are different.

  The lid 84 is a plate-like lid member that is fixed to the upper surfaces of the inner rotor 82 and the outer rotor 83 by caulking so as to cover the pump chamber 86 from above. The lid 84 prevents the lubricating oil in the pump chamber 86 from flowing to the outside.

(1-9) Gas Guide The gas guide 58 is a member for distributing the compressed refrigerant flowing through the second communication passage 48 in the lateral direction and the downward direction in the high-pressure space S1. The reason for guiding in the lateral direction is to perform cyclone separation of the lubricating oil, and the reason for guiding in the downward direction is for cooling the drive motor 16.

(2) Operation Hereinafter, the flow of the refrigerant and the lubricating oil in the compressor 1 having the above configuration 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 performs shaft rotation motion. The driving force of the crankshaft 17 is transmitted to the movable scroll 26 through the boss portion 26c, and the movable scroll 26 performs a revolving motion.

  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 18 via the main suction hole or from the low-pressure space S2 via the auxiliary suction hole. Due to the orbiting motion of the movable scroll 26, the volume of the compression chamber 40 is gradually reduced while moving from the outer peripheral portion to the center portion of the fixed scroll 24. As a result, the refrigerant in the compression chamber 40 is compressed into a compressed refrigerant. After the compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45, the compressed refrigerant passes through the first communication passage 46 and the second communication passage 48, and the high-pressure space S <b> 1 (specifically, the compression mechanism 15, the drive motor 16, and the like). To the space in the axial direction). Then, it is discharged to the outside of the casing 10 through the discharge pipe 19. A part of the compressed refrigerant discharged to the high-pressure space S1 flows downward in the space between the gas guide 58 and the cylindrical portion 11 of the casing 10. The compressed refrigerant further descends through the motor cooling passage 55 and reaches the space below the drive motor 16. Thereafter, the compressed refrigerant reverses the flow direction, moves up the motor cooling passage 55 and the air gap, and flows again into the space between the compression mechanism 15 and the drive motor 16 in the axial direction. Then, it is discharged from the discharge pipe 19 to the outside of the casing 10.

(2-2) Flow of lubricating oil First, when the drive motor 16 is driven, the rotor 52 rotates. As a result, the crankshaft 17 fixed to the rotor 52 performs shaft rotation motion. When the crankshaft 17 rotates, the inner rotor 82 of the pump 80 rotates using the mounting member 70 connected to the crankshaft 17 as a drive shaft. As the inner rotor 82 rotates, the outer rotor 83 having inner teeth that mesh with the plurality of outer teeth of the inner rotor 82 rotates. Here, the outer teeth of the inner rotor 82 and the inner teeth of the outer rotor 83 are different in number, so that when the inner rotor 82 and the outer rotor 83 rotate, they are formed between the inner rotor 82 and the outer rotor 83. The volume of the pump chamber 86 is changed. As a result, when the inner rotor 82 and the outer rotor 83 are rotated and the volume of the pump chamber 86 is increased, a suction action occurs, and the lubricating oil in the oil reservoir space P enters the pump chamber 86 via the suction port 81a. Inhaled. As the rotation of the inner rotor 82 and the outer rotor 83 proceeds, the volume of the pump chamber 86 gradually decreases, and the lubricating oil in the pump chamber 86 is discharged into the through hole 72a of the mounting member 70 through the discharge port. become. The lubricating oil discharged to the through hole 72a of the mounting member 70 rises as it is and rises through the vertical oil supply hole 61a. In addition, the rising of the lubricating oil in the vertical oil supply hole 61a is caused by the influence of suction based on the pressure difference between both ends in the axial direction of the vertical oil supply hole 61a in addition to the delivery of the lubricating oil by the pump 80. Specifically, when the compression mechanism 15 is driven by the rotation of the crankshaft 17 and the compressed refrigerant is discharged into the high-pressure space S1, the pressure in the high-pressure space S1 increases. Here, the vertical oil supply hole 61 a communicates with the low pressure space S <b> 2 through the oil chamber 89 and the oil supply hole 63. Thereby, a pressure difference is generated between the upper end portion and the lower end portion of the vertical oil supply hole 61a. As a result, the vertical oil supply hole 61a itself acts as a differential pressure pump and ascends the vertical oil supply hole 61a.

  The lubricating oil that has moved up the vertical oil supply hole 61 a and reached the oil chamber 89 is supplied to the sliding portion of the compression mechanism 15 via the oil supply hole 63. The lubricating oil that has lubricated the sliding portion of the compression mechanism 15 leaks into the low pressure space S <b> 2 and the compression chamber 40. And it discharges from the compression chamber 40 to the high pressure space S1 through the same path as the compressed refrigerant. Thereafter, the lubricant oil collides with the oil separation plate 65 after descending the motor cooling passage 55 together with the compressed refrigerant. At this time, the lubricating oil adhering to the oil separation plate 65 drops in the high pressure space S1 and is stored in the oil sump space P. On the other hand, most of the lubricating oil rising through the vertical oil supply hole 61a is diverted to the first oil supply horizontal hole 61b, the second oil supply horizontal hole 61c, and the third oil supply horizontal hole 61d. Part of the lubricating oil branched into the second oil supply lateral hole 61 c and the lubricating oil in the oil chamber 89 lubricates the sliding portion between the eccentric portion 17 b of the crankshaft 17 and the pin bearing 35. Further, the lubricating oil divided into the first oil supply lateral hole 61 b lubricates the sliding portion between the main shaft portion 17 a of the crankshaft 17 and the upper bearing 33. Further, the lubricating oil divided into the third oil supply lateral hole 61 d lubricates the sliding portion between the lower main shaft portion 17 d of the crankshaft 17 and the lower main bearing 34. And the lubricating oil which lubricated each sliding part will be returned to the oil pool space P from the high pressure space S1.

(3) Features Conventionally, in a refrigeration apparatus such as an air conditioner, for example, there is one in which a scroll compressor as disclosed in Patent Document 1 (Japanese Patent Laid-Open No. Hei 8-219062) is employed. This compressor accommodates a compression element, a drive shaft connected to the compression element and having an oil supply passage formed therein, a motor for driving the drive shaft, a compression element, the drive shaft, and the motor, and lubricating oil is contained at the bottom. And a stored casing. In this compressor, a positive displacement oil pump is further provided at the lower end of the drive shaft. The oil pump is attached to the drive shaft via a connecting body connected to the drive shaft. In this compressor, the rotational force of the drive shaft is transmitted to the oil pump and the oil pump acts, so that the lubricating oil stored at the bottom is pumped into the oil supply passage of the drive shaft.

  Here, in the scroll compressor as disclosed in Patent Document 1, it is conceivable that the drive shaft having the eccentric portion is inclined by receiving the force of the gas refrigerant due to the compression in the compression element. For this reason, in a compressor provided with a drive shaft having an eccentric portion, it is considered that eccentric rotation may be performed with the drive shaft tilted. As a result, the connecting body connected to the drive shaft swings around at a position shifted from the original rotation center of the oil pump. Therefore, the load of the oil pump connected to the coupling body increases, and there is a possibility that the reliability of the oil pump cannot be maintained.

  Therefore, in the present embodiment, the attachment member 70 for attaching the pump 80 to the crankshaft 17 is configured such that the center AA is eccentric with respect to the axis of the crankshaft 17. More specifically, in this embodiment, the attachment member 70 has a center AA in a direction DI2 opposite to the load direction DI1 with respect to the lower main bearing 34 of the crankshaft 17 with respect to the axis of the crankshaft 17. It is configured to be eccentric. In the present embodiment, the attachment member 70 can be configured so that its center AA is eccentric with respect to the axis of the crankshaft 17 at the lower end of the crankshaft 17. This is because the formed groove 71 a for press-fitting the attachment member 70 is formed so that the center thereof is eccentric with respect to the axis of the crankshaft 17. Therefore, in this embodiment, the center AA of the mounting member 70 is easily eccentric with respect to the axis of the crankshaft 17 simply by press-fitting the mounting member 70 into the groove 71a. Is done.

  In this way, the center AA of the attachment member 70 is eccentric with respect to the axis of the crankshaft 17, so that the rotation center of the inner rotor 82 attached to the attachment member 70 is preliminarily set to the crankshaft 17. It can be eccentric with respect to the shaft core. More specifically, the rotation center of the inner rotor 82 can be eccentric with respect to the axis DI of the crankshaft 17 in a direction DI2 opposite to the load direction DI1 with respect to the lower main bearing 34 of the crankshaft 17. Yes.

  As described above, in this embodiment, it is possible to predict the swing of the inner rotor 82 in advance, and position the rotation center of the inner rotor 82 at a position where the swing can be suppressed as much as possible. Therefore, it is possible to suppress the inner rotor 82 from swinging out of the original rotation center, and the sliding portion of the inner rotor 82 can be reduced. Therefore, damage to the pump 80 can be suppressed, and the reliability of the pump 80 can be maintained. In the present embodiment, since the center AA of the mounting member 70 is eccentric with respect to the axis of the crankshaft 17 in advance, only by attaching the inner rotor 82 of the pump 80 to the mounting member 70, The rotation center of the inner rotor 82 can be easily decentered with respect to the axis of the crankshaft 17.

(4) Modification (4-1) Modification A
FIG. 5 is a longitudinal sectional view of the compressor 101 according to Modification A. FIG. 6 is a schematic perspective view of the attachment member 170 according to Modification A. FIG. 7 is a schematic diagram showing the eccentric direction of the center aa of the pump shaft portion 174 of the mounting member 170 with respect to the axis of the crankshaft 117 when viewed from above in the axial direction.

  In the above embodiment, the mounting member 70 formed on the crankshaft 17 has been described as being configured such that its center AA is eccentric with respect to the axis of the crankshaft 17, It is not limited. For example, the attachment member 70 only needs to be formed so that the rotation center of the inner rotor 82 is eccentric with respect to the axis of the crankshaft 17, and instead of the compressor 1 of the above-described embodiment, this modification example is provided. A compressor 101 can be used. Hereinafter, the compressor 101 according to Modification A will be described with reference to FIGS. In addition, about the component similar to the said embodiment, the same number is attached | subjected and description is abbreviate | omitted.

  The compressor 101 is a high and low pressure dome type scroll compressor as in the above embodiment. As shown in FIG. 5, the compressor 101 includes a casing 10, a suction pipe 18, a discharge pipe 19, a compression mechanism 15, an upper bearing 33, a drive motor 16, a lower main bearing housing 60, and oil separation. A plate 65, a crankshaft 117, a gas guide 58, and a pump 80 are included. The compressor 1 includes a suction pipe 18 and a part of the discharge pipe 19, a compression mechanism 15, an upper bearing 33, a drive motor 16, a lower main bearing housing 60, an oil separation plate 65, a crankshaft 117, in an internal space of the casing 10. It has a sealed structure in which the gas guide 58 and the pump 80 are accommodated. Hereinafter, components of the compressor 101 will be described.

(4-1-1) Crankshaft The crankshaft 117 has a hollow shape and connects the compression mechanism 15 and the drive motor 16. The crankshaft 117 includes a main shaft portion 117a, an eccentric portion 117b that constitutes the upper end portion of the crankshaft 117, a balance weight portion 117c that balances the mass of the crankshaft 117, a lower main shaft portion 117d, and a lower end of the crankshaft 117. And a mounting member 170 located in the section.

  As shown in FIG. 5, the crankshaft 117 has a hollow shape in which a longitudinal oil supply hole 161a extending in the axial direction is formed. The vertical oil supply hole 161 a communicates with the oil chamber 89. The oil chamber 89 is a space formed by the upper end surface of the crankshaft 117 (eccentric portion 117b) and the lower surface of the second end plate 26a.

(4-1-1-1) Main shaft portion The main shaft portion 117 a is a portion that rotates around the rotation center line OO of the drive motor 16. That is, the axis of the main shaft portion 117 a coincides with the rotation center line OO of the drive motor 16 in the axial direction view. The main shaft portion 117 a is located below the eccentric portion 117 b of the crankshaft 117 and is pivotally supported by the upper bearing 33. The main shaft portion 117a is formed therein with a first oil supply lateral hole 161b that branches in the horizontal direction from the vertical oil supply hole 161a. The first oil supply lateral hole 161b is formed so that lubricating oil can be supplied to the sliding portion between the upper bearing 33 and the main shaft portion 117a.

(4-1-1-2) Eccentric part The eccentric part 117b is arranged at the upper end of the main shaft part 117a so that its axis S21 (see FIG. 7) is eccentric with respect to the axis of the main shaft part 117a. Is provided. Further, the eccentric portion 117b is pivotally supported by the boss portion 26c by being fitted into the space inside the boss portion 26c of the movable scroll 26. That is, the crankshaft 117 is connected to the movable scroll 26 by fitting the eccentric portion 117 b of the crankshaft 117 into the boss portion 26 c of the movable scroll 26. The eccentric portion 117b is formed with a second oil supply lateral hole 161c that branches from the vertical oil supply hole 161a in the horizontal direction. The second oil supply lateral hole 161c is formed so that the lubricating oil can be supplied to the sliding portion between the pin bearing 35 and the eccentric portion 17b.

(4-1-1-3) Balance Weight Part The balance weight part 117c is a part that is in close contact with and fixed to the outer peripheral surface of the main shaft part 117a. The balance weight portion 117 c is fixed to the outer peripheral surface located above the drive motor 16. The balance weight portion 117c is provided so as to be located in a direction opposite to the eccentric direction of the eccentric portion 117b.

(4-1-1-4) Lower Main Shaft Portion The lower main shaft portion 117d is located below the drive motor 16 and is pivotally supported by the lower main bearing 34. The lower main shaft portion 117d is formed therein with a third oil supply lateral hole 161d that branches in the horizontal direction from the vertical oil supply hole 161a. The third oil supply lateral hole 161d is formed so that lubricating oil can be supplied to the sliding portion between the lower main bearing 34 and the lower main shaft portion 117d.

(4-1-1-5) Mounting portion As shown in FIG. 6, the mounting member 170 has a convex shape protruding downward, and is mainly a disk-shaped large-diameter portion that is press-fitted into the groove 171a. And a pump shaft portion 174 that is a disk-shaped small-diameter portion that protrudes downward from the lower surface of the attachment portion 173. The mounting portion 173 is press-fitted into the groove 171a so that the outer peripheral surface thereof is in close contact with the inner peripheral surface of the groove 171a. The outer diameter of the pump shaft portion 174 is smaller than the outer diameter of the mounting portion 173 so as to be fitted into a through hole 82 a formed in the inner rotor 82 of the pump 80. Here, in the present modification, the attachment portion 173 is configured such that the center thereof coincides with the rotation center line OO in the axial view, but the pump shaft portion 174 has a center aa. The crankshaft 117 is configured to be eccentric with respect to the axis of the crankshaft 117. An inner rotor of the pump 80 is attached to the pump shaft portion 174 such that the inner peripheral surface of the inner rotor 82 of the pump 80 is in contact with the outer peripheral surface thereof. Therefore, in this modification, the center of the coupling portion 175 (see FIG. 5) between the outer peripheral surface of the mounting member 170 (specifically, the pump shaft portion 174) and the inner peripheral surface of the inner rotor 82 is the pump shaft portion. It coincides with the center aa of 174 when viewed in the axial direction. That is, the center of the coupling portion 175 between the mounting member 170 (specifically, the pump shaft portion 174) and the inner peripheral surface of the inner rotor 82 is eccentric with respect to the axis of the crankshaft 117. .

  Note that the center aa of the pump shaft portion 174 is opposite to the load direction DI11 (see FIG. 7) with respect to the lower main bearing 34 of the crankshaft 17 when viewed in the axial direction with respect to the axis of the crankshaft 117. It is formed so as to be eccentric in the side direction DI12 (see FIG. 7). That is, as viewed in the axial direction, the direction from the axial center of the crankshaft 117 toward the center aa of the pump shaft portion 174 of the mounting member 170 of the crankshaft 117 coincides with the direction DI12. More specifically, the load direction DI11 with respect to the lower main bearing 34 of the crankshaft 117 is 110 ° to 200 ° when the eccentric direction of the eccentric portion 117b of the crankshaft 117 is 90 ° as shown in FIG. Direction. Therefore, since the direction DI12 is a direction opposite to the direction DI11, the direction DI12 is a direction of 290 ° to 20 °. The above-mentioned angle is a counterclockwise angle with reference to the reference line STL11 shown in FIG.

  Further, the mounting member 170 has a gap distance (not shown) between the crankshaft 117 and the lower main bearing 34 such that the eccentric amount of the center aa of the pump shaft portion 174 with respect to the axis of the crankshaft 117 is. It is formed so that. The clearance distance between the lower main shaft portion 117d of the crankshaft 117 and the lower main bearing 34 is the lower portion of the crankshaft 117 in a state where the axis of the crankshaft 117 and the center of the lower main bearing 34 are overlapped. The distance between the outer peripheral surface of the main shaft portion 117d and the inner peripheral surface of the lower main bearing 34, that is, the radial clearance of the lower main bearing 34. This gap distance is, for example, 25 μm.

  Further, the attachment member 170 is formed with a through hole 172a penetrating in the axial direction. The diameter of the through hole 172a is smaller than that of the vertical oil supply hole 161a, and communicates with the vertical oil supply hole 161a. Further, the through hole 172 a communicates with the discharge port of the pump 80. The through hole 172a is formed such that the center thereof coincides with the center aa of the pump shaft portion 174 in the axial direction. Thus, the through-hole 172a formed in the attachment member 170 communicates with the vertical oil supply hole 161a and the discharge port of the pump 80, so that when the pump 80 is operated, the oil is stored in the oil sump space P. The lubricating oil is sucked into the pump chamber 86 through the suction port 81a, and the lubricating oil flowing into the pump chamber 86 flows into the vertical oil supply hole 161a through the through hole 72a communicating with the discharge port. Here, the vertical oil supply hole 161a, the first oil supply horizontal hole 161b, the second vertical oil supply hole 162a, the third oil supply horizontal hole 161d, and the through hole 172a are “oil supply holes through which the lubricating oil sucked up by the pump 80 flows. Is formed.

  As described above, the crankshaft 117 is separated from the drive motor 16 by connecting the compression mechanism 15 (specifically, the movable scroll 26) and the drive motor 16 (specifically, the rotor 52). The transmitted driving force is transmitted to the compression mechanism 15. Specifically, when a current flows through the drive motor 16, first, the rotor 52 rotates counterclockwise as viewed from above around the rotation center line OO, and this rotational driving force is transmitted to the crankshaft 17. Then, the crankshaft 17 rotates counterclockwise as viewed from above. When the crankshaft 17 rotates, the driving force of the rotor 52 (drive motor 16) is transmitted to the movable scroll 26 (compression mechanism 15) connected to the crankshaft 17, and the movable scroll 26 is driven. . At this time, since the crankshaft 117 has the eccentric part 117b, the movable scroll 26 performs eccentric rotation.

  In this modification, the mounting member 170 is configured such that the center aa of the pump shaft portion 174 is eccentric with respect to the axis of the crankshaft 117. Therefore, the rotation center of the inner rotor 82 whose inner peripheral surface is attached in close contact with the outer peripheral surface of the pump shaft portion 174 of the attachment member 170 is a center line L2 passing through the center aa of the pump shaft portion 174 of the attachment member 170. (Refer to FIG. 5) and is eccentric with respect to the axis of the crankshaft 117.

(4-1-2) Features Unlike the above-described embodiment in which the center of the groove 71a for press-fitting the attachment member 70 is eccentric with respect to the axis of the crankshaft 17, in this modification, the attachment member 170 is The center of the groove 171 a for press-fitting overlaps the axis of the crankshaft 117. And in this modification, the pump 80 is attached to the lower end part of the crankshaft 117 by the inner rotor 82 of the pump 80 being attached to the lower end part of the crankshaft 117 via the attachment member 170. The center (here, the center aa) of the portion (here, the pump shaft portion 174) to which the inner rotor 82 is connected is eccentric with respect to the axis of the crankshaft 117. And make up. That is, the mounting member 170 is configured such that the center of the coupling portion 175 between the outer peripheral surface thereof and the inner peripheral surface of the inner rotor 82 of the pump 80 is eccentric with respect to the axial center of the crankshaft 117.

  Thereby, the rotation center of the inner rotor 82 can be easily decentered with respect to the axis of the crankshaft 117 simply by attaching the inner rotor 82 to the attachment member 170. That is, in this modified example, as in the above embodiment, the runout of the inner rotor 82 is predicted in advance, and the inner rotor 82 is placed at a position where the rotation center of the inner rotor 82 is suppressed. Thus, the mounting member 170 can be configured. Thereby, it is possible to suppress the inner rotor 82 from swinging out of the original rotation center, and the sliding portion of the inner rotor 82 can be reduced. Therefore, damage to the pump 80 can be suppressed, and the reliability of the pump 80 can be maintained.

(4-2) Modification B
In the said embodiment, although the scroll compressor 1 was mentioned as an example and demonstrated as a compressor which concerns on this invention, it is not restricted to this. For example, a compressor having a drive shaft having an eccentric portion that is eccentric with respect to the rotation center of the drive motor (for example, a rotary compressor) is applicable.

  The present invention can be variously applied to a compressor including a drive shaft having a main shaft portion and an eccentric portion eccentric to the main shaft portion, and a pump attached to the drive shaft.

DESCRIPTION OF SYMBOLS 1,101 Compressor 10 Casing 15 Compression mechanism 16 Drive motor 17, 117 Crankshaft 17a, 117a Main shaft part 17b, 117b Eccentric part 17d, 117d Lower main shaft part 34 Lower main bearing 61a, 61b, 61c, 61d, 62a,
72a, 161a, 161b, 161c,
161d, 162a, 172a Oil supply hole 70, 170 Mounting member 73, 173 Mounting portion 74, 174 Pump shaft portion 80 Pump 82 Inner rotor 83 Outer rotor 175 Joint portion between inner peripheral surface of inner rotor and mounting member D1 Lower part of crankshaft Clearance distance between main shaft and lower main bearing AA, aa Rotation center of inner rotor P Oil reservoir space

Japanese Patent Application Laid-Open No. 8-21962

Claims (6)

A compression mechanism (15);
A drive motor (16) for driving the compression mechanism;
A casing (10) that accommodates the compression mechanism and the drive motor, and in which an oil sump space (P) for storing lubricating oil is formed at the bottom;
An inner rotor (82) and an outer rotor (83) positioned on the outer peripheral side of the inner rotor, and accommodated in the casing so as to suck up lubricating oil in the oil reservoir space by rotation of the inner rotor. A pump (80),
The main shaft portion (17a, 117a) whose axial center coincides with the rotation center of the drive motor in the axial direction, and the eccentric portion (17b, 117b) eccentric to the main shaft portion, Oil supply holes (61a, 61b, 61c, 61d, 62a, 72a, 161a, 161b, 161c, 161d, 162a, 172a) through which the lubricating oil sucked up by the pump flows are formed and transmitted from the drive motor A crankshaft (17, 117) housed in the casing to transmit driving force to the compression mechanism;
With
An attachment member (70, 170) for attaching the pump to the lower end portion of the crankshaft by connecting the inner rotor to the lower end portion of the crankshaft is connected,
The attachment member is connected to a lower end portion of the crankshaft so that the rotation center (AA, aa) of the inner rotor is eccentric with respect to the axis of the crankshaft.
Compressor (1). A lower main bearing (34) that pivotally supports a lower end portion of the crankshaft and located above the pump;
The amount of eccentricity of the rotation center of the inner rotor with respect to the axis of the crankshaft is a gap distance (D1) between the lower main shaft portion (17d, 117d) of the crankshaft and the lower main bearing.
The compressor according to claim 1. The inner peripheral surface of the inner rotor and the mounting member are connected,
The center (aa) of the connecting portion (175) between the inner peripheral surface of the inner rotor and the mounting member is eccentric with respect to the axis of the crankshaft.
The compressor according to claim 2. The attachment member has a pump shaft portion (74) connected to the inner rotor of the pump, and an attachment portion (73) attached to a lower end portion of the crankshaft.
The inner peripheral surface of the inner rotor and the pump shaft portion are connected,
The center of the connecting portion between the inner peripheral surface of the inner rotor and the pump shaft portion is eccentric with respect to the axis of the crankshaft.
The compressor according to claim 3. The attachment member has a pump shaft portion connected to the inner rotor of the pump, and an attachment portion attached to a lower end portion of the crankshaft,
The center (A-A) of the mounting portion is eccentric with respect to the axis of the crankshaft.
The compressor according to claim 2 or 3. In the mounting member, the rotation center of the inner rotor is in a direction (DI2, DI12) opposite to the load direction (DI1, DI11) of the crankshaft with respect to the lower main bearing with respect to the axis of the crankshaft. It is connected to the lower end of the crankshaft so as to be eccentric,
The compressor according to any one of claims 2 to 5.

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