JP2017106423A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor including a driving shaft and an oil discharge pathway formed therein for oil in a crank chamber, capable of suppressing oil rising by preventing the leakage of oil from the lower part of a housing forming the crank chamber.SOLUTION: A compressor 10 includes a casing 20 in which an oil reservoir space 25 is formed, a motor 50, a driving shaft 60 connected to the motor, a compression mechanism 30 including a movable scroll 32, and an upper housing 33 forming the crank chamber in which a connection part between the driving shaft and the movable scroll is stored, an in-shaft oil supply pathway 63 for carrying oil O from the oil reservoir space to the crank chamber, an oil discharge pathway 90, and an upper shaft seal ring 41, the upper housing having an upper bearing part 332 arranged below the crank chamber and an upper shaft seal part 333 arranged below it, the oil discharge pathway including an oil discharge main pathway 64c extending through the inside of the driving shaft in the axial direction and an inflow pathway 67 communicating the oil discharge main pathway with the crank chamber, the upper shaft seal ring being arranged on the upper shaft seal part.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor. More specifically, the present invention relates to a compressor in which an oil discharge path for discharging oil accumulated in a crank chamber is formed in a drive shaft.

  Conventionally, as in Patent Document 1 (Japanese Patent Application Laid-Open No. 2013-177877), an oil supply path for supplying oil in an oil reservoir space at the bottom of a casing to a sliding portion such as a bearing and a housing of a compression mechanism are formed. 2. Description of the Related Art There is known a compressor in which an oil drain path for returning oil accumulated in a crank chamber to an oil reservoir space is formed in a drive shaft. In the compressor of Patent Document 1 (Japanese Patent Laid-Open No. 2013-177877), the oil drainage path extends in the drive shaft in the axial direction and extends from the main path in a direction intersecting the axial direction and opens into the crank chamber. Including suction holes.

  In the compressor having such a configuration, the oil is guided from the suction hole to the main path against the centrifugal force accompanying the rotation of the drive shaft. It is easy to accumulate. When oil is accumulated too much in the crank chamber, the crank chamber is sealed with oil, and the pressure in the crank chamber increases. For this reason, oil is likely to leak out from the lower part of the housing in which the crank chamber is formed, and oil rising that oil flows out of the compressor is likely to occur.

  An object of the present invention is a compressor in which a drain passage for discharging oil accumulated in a crank chamber formed in a housing is formed in a drive shaft, and the oil from the lower portion of the housing in which the crank chamber is formed. An object of the present invention is to provide a compressor that can prevent oil leakage and suppress oil rise.

  A compressor according to a first aspect of the present invention includes a casing, an electric motor, a drive shaft, a compression mechanism, an oil supply path, an oil discharge path, and an upper shaft seal ring. An oil reservoir space is formed at the bottom of the casing. The electric motor is accommodated in the casing. The drive shaft extends in the vertical direction and is connected to the electric motor. The compression mechanism is accommodated in the casing. The compression mechanism includes a movable part and an upper housing. The movable part is connected to a drive shaft and driven by an electric motor. The upper housing forms a crank chamber in which a connecting portion between the eccentric portion of the drive shaft and the movable portion is accommodated. The upper housing is disposed below the crank chamber and has an upper bearing portion that supports the drive shaft. The upper housing has an upper shaft seal portion disposed below the upper bearing portion. The oil supply path conveys oil in the oil reservoir space to the crank chamber. The oil supply path is formed inside the drive shaft. The oil drainage path includes a main oil drainage path and an inflow path. The oil drain main path extends in the axial direction inside the drive shaft. The inflow path communicates the oil drain main path and the crank chamber. The upper shaft seal ring is disposed on the upper shaft seal portion.

  In the compressor according to the first aspect of the present invention, the upper shaft seal ring is disposed on the upper shaft seal portion of the upper housing below the crank chamber formed in the upper housing. Therefore, in the compressor according to the first aspect of the present invention, even when the pressure in the crank chamber rises, oil leakage from the lower portion of the upper housing is prevented, and oil rise is suppressed.

  The compressor which concerns on the 2nd viewpoint of this invention is a compressor which concerns on a 1st viewpoint, Comprising: The lower housing arrange | positioned under the electric motor, and a lower shaft seal ring are further provided. The lower housing has a lower bearing portion and a lower shaft seal portion. The lower bearing portion pivotally supports the drive shaft. The lower shaft seal portion is disposed above the lower bearing portion. The lower shaft seal ring is disposed on the lower shaft seal portion.

  In the compressor according to the second aspect of the present invention, since the lower shaft seal ring is disposed in the lower shaft seal portion of the lower housing, oil leakage from above the lower housing can be prevented, and oil rising can be further suppressed.

  The compressor which concerns on the 3rd viewpoint of this invention is a compressor which concerns on a 2nd viewpoint, Comprising: An annular space is arrange | positioned under the lower shaft seal part. The annular space is formed so as to surround the drive shaft. The annular space communicates with the oil drain main path. An oil path that communicates the annular space and the oil reservoir space is formed in the lower housing.

  In the compressor according to the third aspect of the present invention, by providing the annular space and the oil path, it is easy to secure a flow path through which oil flows from the oil drain main path to the oil reservoir space. Therefore, the pressure increase in the crank chamber can be suppressed to be relatively low, and oil rising due to oil leakage from the lower portion of the upper housing can be suppressed.

  The compressor which concerns on the 4th viewpoint of this invention is a compressor which concerns on a 2nd viewpoint or a 3rd viewpoint, Comprising: The groove | channel by which a lower shaft seal ring is arrange | positioned is formed in the drive shaft.

  Since the compressor according to the fourth aspect of the present invention is provided with a groove for disposing the lower shaft seal ring on the drive shaft side, it is possible to assemble a compressor in which the lower shaft seal ring is disposed in the lower shaft seal portion. Easy.

  A compressor according to a fifth aspect of the present invention is the compressor according to any one of the second to fourth aspects, wherein the lower shaft seal ring has a height in the axial direction of the attachment portion of the lower shaft seal ring. The value of the ratio to the diameter of the drive shaft is 0.04 or more and less than 0.07.

  In the compressor according to the fifth aspect of the present invention, the lower shaft seal ring having a height satisfying the above conditions is used, so that oil is prevented from leaking from the upper portion of the lower housing. It can be prevented that the height of the compressor becomes unnecessarily high and the efficiency of the compressor decreases.

  The compressor which concerns on the 6th viewpoint of this invention is a compressor which concerns on either of the 1st viewpoint to the 5th viewpoint, Comprising: The groove | channel by which an upper shaft seal ring is arrange | positioned is formed in the drive shaft.

  In the compressor according to the sixth aspect of the present invention, since the groove for disposing the upper shaft seal ring is provided on the drive shaft side, it is easy to assemble a compressor in which the upper shaft seal ring is disposed in the upper shaft seal portion. It is.

  A compressor according to a seventh aspect of the present invention is the compressor according to any one of the first to sixth aspects, wherein the upper shaft seal ring is attached at the height in the axial direction of the upper shaft seal ring. The value of the ratio to the diameter of the drive shaft is 0.04 or more and less than 0.07.

  In the compressor according to the seventh aspect of the present invention, by using the upper shaft seal ring having a height that satisfies the above conditions, the upper shaft seal ring is prevented from leaking oil from the lower portion of the upper housing. It can be prevented that the height of the compressor becomes unnecessarily high and the efficiency of the compressor decreases.

  A compressor according to an eighth aspect of the present invention is the compressor according to any one of the first to seventh aspects, and further includes a series pump. The series pump is attached to the lower part of the drive shaft. The series pump supplies oil in the oil reservoir space to the oil supply path.

  In the compressor according to the eighth aspect of the present invention, the manufacturing cost of the compressor can be suppressed as compared with the case where oil supply to the crank chamber and oil discharge from the crank chamber are performed by separate pumps.

  A compressor according to a ninth aspect of the present invention is the compressor according to any one of the first to seventh aspects, and further includes a dual pump. The dual pump is attached to the lower part of the drive shaft. The double pump includes an oil supply pump and an oil discharge pump. The oil supply pump supplies oil in the oil reservoir space to the oil supply path. The oil discharge pump discharges the oil in the crank chamber to the oil reservoir space via the oil discharge path.

  In the compressor according to the ninth aspect of the present invention, the oil supply to the crank chamber is performed by the oil supply pump and the oil discharge from the crank chamber is performed by the oil discharge pump, respectively. is there.

  A compressor according to a tenth aspect of the present invention is the compressor according to the ninth aspect, and the oil discharge pump and the oil supply pump are positive displacement pumps. The volume of the oil pump is larger than the volume of the oil pump.

  In the compressor according to the tenth aspect of the present invention, since the volume of the oil discharge pump is larger than the volume of the oil supply pump, the increase in the pressure in the crank chamber can be suppressed relatively low, and the oil due to oil leakage from the lower part of the upper housing The rise can be suppressed.

  In the compressor according to the present invention, the upper shaft seal ring is disposed on the upper shaft seal portion of the upper housing below the crank chamber formed in the upper housing. Therefore, in the compressor according to the present invention, even when the pressure in the crank chamber rises, oil leakage from the lower portion of the upper housing is prevented, and oil rise is suppressed.

It is a schematic longitudinal cross-sectional view of the compressor which concerns on 1st Embodiment of this invention. It is a top view of the drive shaft of the compressor of FIG. The upper outflow path and the lower outflow path formed in the drive shaft are drawn with dotted lines. It is a schematic longitudinal cross-sectional view around the upper housing of the compressor of FIG. It is a schematic longitudinal cross-sectional view of the lower part of the drive shaft of the compressor of FIG. A cross-sectional view of the drive shaft cut along the S-C-T cross section of FIG. 2 is drawn. It is a schematic longitudinal cross-sectional view of the lower part of the drive shaft of the compressor which concerns on other embodiment. A cross-sectional view of the drive shaft cut along the S-C-T cross section of FIG. 2 is drawn. It is an enlarged view of the lower housing and oil pump periphery of the compressor of FIG. It is a disassembled perspective view of the oil pump of the compressor of FIG. FIG. 2 is a graph showing a change in an oil rising index with respect to an operating frequency of the compressor of FIG. 1 (with drained oil in the shaft and upper shaft seal ring). As a reference, in the case of draining oil in the shaft without the upper shaft seal ring, the case of draining off the shaft is also shown. It is a schematic sectional drawing about the upper housing, electric motor, drive shaft, and lower housing of the compressor concerning a 2nd embodiment of the present invention.

  Hereinafter, embodiments of the present invention will be described with examples. The following embodiments are merely examples, and can be appropriately changed without departing from the gist of the present invention.

<First Embodiment>
A compressor 10 according to a first embodiment of the present invention will be described with reference to the drawings.

(1) Overall Configuration The compressor 10 according to the present embodiment is a scroll compressor. The compressor 10 is connected to a refrigerant circuit of a refrigeration apparatus (not shown). In the refrigerant circuit, the refrigerant circulates to perform a vapor compression refrigeration cycle. Specifically, in the refrigerant circuit, the refrigerant compressed by the compressor 10 radiates heat by the condenser, is depressurized by the depressurization mechanism, absorbs heat by the evaporator, and is sucked by the compressor 10 again.

  As shown in FIG. 1, the compressor 10 mainly includes a casing 20, a compression mechanism 30, an electric motor 50, a drive shaft 60, a lower housing 70, and an oil pump 80. In the drive shaft 60, an in-shaft oil supply path 63 and an in-shaft oil discharge path 64 for supplying oil O (refrigeration oil) to the sliding portion of the compressor 10 are formed (FIG. 1). reference). The in-shaft oil discharge path 64 constitutes a part of the oil discharge path 90 for discharging the oil O from the crank chamber 35 described later (see FIG. 1).

(2) Detailed Configuration The configuration of the compressor 10 will be described in detail below. In the following description, the direction and position will be described with the direction of the arrow U in FIG.

(2-1) Casing The compressor 10 has a vertically long cylindrical casing 20. As shown in FIG. 1, the casing 20 includes a cylindrical member 21 that is open at the top and bottom, and an upper lid 22 a and a lower lid 22 b that are respectively provided at the upper end and the lower end of the cylindrical member 21. The cylindrical member 21, and the upper lid 22a and the lower lid 22b are fixed by welding so as to keep airtightness.

  As shown in FIG. 1, the casing 20 accommodates components / components of the compressor 10 including the compression mechanism 30, the electric motor 50, the drive shaft 60, the lower housing 70, and the oil pump 80. An oil reservoir space 25 is formed at the bottom of the casing 20 as shown in FIG. In the oil reservoir space 25, oil O for lubricating the drive shaft 60 and the sliding portion of the compression mechanism 30 is stored.

  As shown in FIG. 1, a suction pipe (not shown) for sucking a refrigerant that is a compression target of the compression mechanism 30 is provided in the upper part of the casing 20 so as to penetrate the upper lid 22a. The lower end of the suction pipe is connected to a fixed scroll 31 of a compression mechanism 30 described later. The suction pipe communicates with a compression chamber Sc of the compression mechanism 30 described later. The compression chamber Sc is supplied with the low-pressure refrigerant in the refrigerant circuit via the suction pipe.

  A discharge pipe 24 through which a refrigerant discharged to the outside of the casing 20 passes is provided at an intermediate portion of the cylindrical member 21 of the casing 20 (see FIG. 1). The discharge pipe 24 is disposed such that an end of the discharge pipe 24 inside the casing 20 protrudes between an upper housing 33 of the compression mechanism 30 and an electric motor 50 which will be described later. High-pressure refrigerant in the refrigerant circuit compressed by the compression mechanism 30 is discharged from the discharge pipe 24.

(2-2) Compression mechanism The compression mechanism 30 is driven by the electric motor 50 and compresses the refrigerant. The compression mechanism 30 is arrange | positioned at the upper part in the casing 20 (refer FIG. 1). As shown in FIG. 1, the compression mechanism 30 mainly includes a fixed scroll 31, a movable scroll 32, an upper housing 33, and an Oldham coupling 34. The fixed scroll 31 is disposed above the upper housing 33. The movable scroll 32 is combined with the fixed scroll 31 to form the compression chamber Sc. The upper housing 33 forms a crank chamber 35 in which a pin bearing portion 323 of the movable scroll 32 described later is disposed. The upper housing 33 has an upper bearing portion 332 that supports the drive shaft 60 below the crank chamber 35 (see FIG. 1). The upper housing 33 has an upper shaft seal portion 333 below the upper bearing portion 332 (see FIG. 1). The Oldham coupling 34 prevents the movable scroll 32 from rotating.

(2-2-1) Fixed Scroll As shown in FIG. 1, the fixed scroll 31 mainly includes a fixed side end plate 311, a fixed side wrap 312, and a peripheral edge 313. The fixed side wrap 312 and the peripheral edge 313 protrude downward from the surface of the fixed side end plate 311 on the movable scroll 32 side, in other words, from the lower surface of the fixed side end plate 311. The fixed side wrap 312 is formed in a spiral shape.

  The fixed side end plate 311 is formed in a disc shape. The fixed side wrap 312 and the movable side wrap 322 of the movable scroll 32 to be described later are combined so that the lower surface of the fixed side end plate 311 and the upper surface of the movable side end plate 321 of the movable scroll 32 to be described later face each other. A compression chamber Sc in which the refrigerant is compressed is formed between 31 and the movable scroll 32 (see FIG. 1).

  A discharge port 311a is formed in the fixed side end plate 311 (see FIG. 1). The discharge port 311a is formed in the center of the fixed side end plate 311 so as to penetrate the fixed side end plate 311 in the thickness direction (see FIG. 1). Moreover, the recessed part 311b is formed in the stationary side end plate 311 (refer FIG. 1). The recess 311b is formed in the upper part of the fixed side end plate 311 so as to be recessed downward. A lid 37 is attached above the fixed side end plate 311. The recess 311b and the lid 37 form a discharge space 311c. The discharge space 311 c is a space surrounded by the recess 311 b and the lid body 37. The discharge space 311c communicates with the compression chamber Sc via the discharge port 311a (see FIG. 1). The discharge space 311 c communicates with a space below the upper housing 33 in the casing 20 via a refrigerant passage 314 formed in the fixed scroll 31 and a refrigerant passage 335 formed in the upper housing 33. The refrigerant compressed in the compression chamber Sc of the compression mechanism 30 passes through the refrigerant passage 314 and the refrigerant passage 335 and flows into the space below the upper housing 33. When the compressor 10 is operated, the space below the upper housing 33 is filled with the high-pressure refrigerant compressed by the compression mechanism 30.

  The peripheral edge 313 is formed in a thick ring shape and is disposed so as to surround the fixed side wrap 312 (see FIG. 1). When the movable scroll 32 turns with respect to the fixed scroll 31, the upper surface of the movable side end plate 321 of the movable scroll 32 described later comes into sliding contact with the lower surface of the peripheral edge portion 313.

(2-2-2) Movable Scroll The movable scroll 32 that is an example of the movable part is connected to the drive shaft 60. The movable scroll 32 is driven by an electric motor 50 connected to the drive shaft 60.

  As shown in FIG. 1, the movable scroll 32 mainly includes a movable side end plate 321, a movable side wrap 322, and a pin bearing portion 323.

  The movable side end plate 321 is formed in a disc shape.

  The movable side wrap 322 protrudes upward from the surface of the movable side end plate 321 on the fixed scroll 31 side, in other words, from the upper surface of the movable side end plate 321 (see FIG. 1). The movable side wrap 322 is formed in a spiral shape.

  The pin bearing portion 323 protrudes downward from the surface of the movable side end plate 321 on the electric motor 50 side, in other words, from the lower surface of the movable side end plate 321 (see FIG. 1). The pin bearing portion 323 is formed in a cylindrical shape, and the opening at the upper end of the cylinder is closed by the movable side end plate 321. The pin bearing portion 323 is accommodated in a crank chamber 35, which will be described later, formed by the upper housing 33. The movable scroll 32 and the drive shaft 60 are connected by inserting a pin shaft portion 61 of the drive shaft 60 described later into the pin bearing portion 323. A bearing metal 323 a is fitted inside the pin bearing portion 323. The pin shaft portion 61 inserted into the pin bearing portion 323 is rotatably supported by the bearing metal 323a. When the movable scroll 32 is connected to the drive shaft 60 in the pin bearing portion 323, when the electric motor 50 is operated, the drive shaft 60 connected to the electric motor 50 rotates and the movable scroll 32 is driven.

  An oil communication chamber 36 is provided between the upper end surface of the pin shaft portion 61 of the drive shaft 60 inserted into the pin bearing portion 323 and the lower surface of the movable side end plate 321 inside the cylindrical pin bearing portion 323. Is formed (see FIG. 1). The oil communication chamber 36 communicates with an in-shaft oil supply path 63 formed in a drive shaft 60 described later. The oil communication chamber 36 is supplied with oil O from the in-shaft oil supply path 63.

  A pin shaft channel 323b extending in the vertical direction is formed between the pin shaft portion 61 and the bearing metal 323a (see FIG. 1). The pin shaft channel 323 b has an upper end opened to the oil communication chamber 36 and a lower end opened to the crank chamber 35. Oil O flows from the oil communication chamber 36 into the pin shaft channel 323b. The oil O flowing into the pin shaft channel 323b is supplied to the sliding portion between the pin shaft portion 61 and the bearing metal 323a. The oil O that has been supplied to the sliding portion between the pin shaft portion 61 and the bearing metal 323 a flows into the crank chamber 35 formed by the upper housing 33.

  Inside the movable side end plate 321, an end plate oil path (not shown) is formed. The oil passage in the end plate extends from the opening on the lower surface of the movable side end plate 321 communicating with the oil communication chamber 36 to the inside of the disk-shaped movable end end plate 321 outward in the radial direction and further upwards to extend to the movable end end plate. Open on the upper surface of 321.

(2-2-3) Housing The upper housing 33 is a cylindrical member that extends vertically. The upper housing 33 is press-fitted into the cylindrical member 21, and the outer peripheral surface thereof is joined to the inner surface of the cylindrical member 21 over the entire circumferential direction (see FIG. 1). The fixed scroll 31 is fixed to the upper housing 33 with the lower surface of the peripheral edge 313 of the fixed scroll 31 and the upper end surface of the upper housing 33 facing each other (see FIG. 1). A drive shaft 60 is inserted into the cylindrical upper housing 33 (see FIG. 1).

  As shown in FIG. 1, the upper housing 33 is formed with a recess 331 formed to be recessed downward at the center of the upper surface. Further, as shown in FIG. 1, the upper housing 33 includes an upper bearing portion 332 disposed below the concave portion 331 and an upper shaft seal portion 333 disposed below the upper bearing portion 332.

  The concave portion 331 forms a crank chamber 35 in which the pin bearing portion 323 of the movable scroll 32 is disposed (see FIG. 1). Inside the crank chamber 35, a connecting portion between the pin shaft portion 61 of the drive shaft 60 inserted into the upper housing 33 and the movable scroll 32 is housed inside (see FIG. 1). That is, the crank chamber 35 accommodates the pin bearing portion 323 of the movable scroll 32 into which the pin shaft portion 61 of the drive shaft 60 is inserted (see FIG. 1). The crank chamber 35 also accommodates a balance weight 66 attached to the drive shaft 60 (see FIG. 1).

  In the concave portion 331 of the upper housing 33, that is, in the crank chamber 35, oil O after being supplied to the sliding portion between the pin shaft portion 61 of the drive shaft 60 and the bearing metal 323 a, or a drive shaft 60 described later. After being supplied to the sliding portion between the main shaft 62 and the bearing metal 332a, the oil O flows. The crank chamber 35 communicates with an oil drain main path 64 c of an in-shaft oil drain path 64 (described later) via an inflow path 67. The oil drain main path 64c extends in the axial direction inside the drive shaft 60. The inflow path 67 includes an in-weight inflow path 66a and an in-axis inflow path 64a of an in-shaft oil discharge path 64 described later (see FIG. 1). The in-weight inflow path 66 a is a path formed inside the balance weight 66. The in-axis inflow path 64a is a path that is formed inside the drive shaft 60 and communicates with the oil drain main path 64c. The oil O flowing into the crank chamber 35 flows into the in-shaft oil discharge path 64 through the in-weight inflow path 66 a and is finally discharged into the oil reservoir space 25 at the lower part of the casing 20. The discharge of the oil O from the crank chamber 35 will be described later.

  The upper bearing portion 332 is disposed below the crank chamber 35 (see FIG. 1). The upper bearing portion 332 supports the drive shaft 60. Specifically, a bearing metal 332a is provided inside the upper bearing portion 332 (see FIG. 1). The bearing metal 332 a rotatably supports the main shaft 62 of the drive shaft 60 inserted into the upper bearing portion 332 of the upper housing 33. The upper bearing portion 332 is formed with an upper bearing oil drain passage 332b extending in the vertical direction (see FIG. 1). The lower end of the upper bearing oil drain passage 332b communicates with an annular space 334 disposed around the upper bearing portion 332 (see FIG. 1). The upper end of the upper bearing oil drain passage 332 b communicates with the crank chamber 35 disposed above the upper bearing portion 332. The upper bearing oil drain path 332 b is a path for guiding the oil O after being supplied to the sliding portion between the bearing metal 332 a of the upper bearing portion 332 and the main shaft 62 of the drive shaft 60 to the crank chamber 35.

  The upper shaft seal portion 333 is disposed below the upper bearing portion 332 (see FIG. 1). The upper shaft seal portion 333 is formed in a cylindrical shape. The inner diameter of the upper shaft seal portion 333 is substantially equal to the outer diameter of the main shaft 62 of the drive shaft 60 disposed inside the upper shaft seal portion 333. The inner diameter of the upper shaft seal portion 333 is slightly larger than the outer diameter of the main shaft 62 of the drive shaft 60 disposed inside the upper shaft seal portion 333. The upper shaft seal portion 333 prevents the oil O from leaking from the lower part of the gap between the upper housing 33 and the drive shaft 60.

  An upper shaft seal ring 41 is disposed on the upper shaft seal portion 333 (see FIG. 1). By disposing the upper shaft seal ring 41 in the upper shaft seal portion 333, even if the oil O accumulates in the crank chamber 35 and the pressure in the crank chamber 35 rises, the oil O leaks from the lower portion of the upper housing 33. Can be prevented and oil rise can be suppressed.

  Specifically, the upper shaft seal ring 41 is disposed between the upper shaft seal portion 333 and the drive shaft 60 below the upper shaft seal portion 333 (see FIG. 1). The upper shaft seal ring 41 is disposed in an annular seal ring groove 41a formed in a region of the main shaft 62 of the drive shaft 60 facing the upper shaft seal portion 333 (see FIG. 1). The upper shaft seal ring 41 is disposed in an annular seal ring groove formed in the upper shaft seal portion 333 instead of being disposed in the seal ring groove 41a formed in the main shaft 62 of the drive shaft 60. Also good.

  The upper shaft seal ring 41 is made of metal or resin. For the upper shaft seal ring 41, for example, a metal material or a resin material excellent in high temperature characteristics is used. The upper shaft seal ring 41 is formed in an annular shape and has a joint (not shown) (not shown). The shape of the joint is, for example, an angle cut shape. However, the shape of the joint is not limited to this, and may be, for example, a step cut shape. The shape of the joint may be determined as appropriate. The diameter A1 of the main shaft 62 of the drive shaft 60 of the portion to which the upper shaft seal ring 41 is attached at the height h1 (see FIG. 1) in the axial direction of the upper shaft seal ring 41 (see FIG. 1, see the seal ring groove 41a). The value of the ratio to the diameter of the portion not formed is 0.047, but is not limited thereto. In order to obtain sufficient sealing performance, the value of the ratio of the height h1 in the axial direction of the upper shaft seal ring 41 to the diameter A1 of the main shaft 62 of the drive shaft 60 in the portion where the upper shaft seal ring 41 is attached is 0.04 or more and less than 0.07. The value of the ratio of the radial thickness w1 (see FIG. 1) of the upper shaft seal ring 41 to the diameter A1 of the main shaft 62 of the drive shaft 60 in the portion where the upper shaft seal ring 41 is attached is 0.040. However, the present invention is not limited to this. In order to obtain sufficient sealing performance, the value of the ratio of the radial thickness w1 of the upper shaft seal ring 41 to the diameter A1 of the main shaft 62 of the drive shaft 60 in the portion where the upper shaft seal ring 41 is attached is 0. It is preferably 0.03 or more and less than 0.06.

(2-2-4) Oldham Joint The Oldham Joint 34 is provided on the upper surface of the upper housing 33 (see FIG. 1). The Oldham coupling 34 is slidably fitted into the movable side end plate 321 of the movable scroll 32 and the upper housing 33. The Oldham coupling 34 prevents the movable scroll 32 driven by the electric motor 50 from rotating. Due to the action of the Oldham coupling 34, the movable scroll 32 revolves with respect to the fixed scroll 31 without rotating.

(2-3) Electric motor The electric motor 50 is arrange | positioned under the upper housing 33 of the compression mechanism 30 (refer FIG. 1). The electric motor 50 includes a stator 51 fixed to the inner wall surface of the cylindrical member 21 and a rotor 53 that is rotatably accommodated with a slight gap (air gap) inside the stator 51 (see FIG. 1).

  The stator 51 has a cylindrical stator core 52 and windings (not shown) wound around the stator core 52. A core cut 52a extending in the vertical direction is formed on the outer peripheral surface of the stator core 52 (see FIG. 1). In the core cut 52 a portion, a gap is formed between the stator core 52 and the cylindrical member 21 of the casing 20.

  Unlike the compressor 10, a compressor of a type that returns oil accumulated in the crank chamber to the oil reservoir space through a gap in the core cut portion needs to have a large core cut. On the other hand, in the present compressor 10, since the in-shaft oil discharge path 64 for returning the oil O of the crank chamber 35 to the oil reservoir space 25 is formed in the drive shaft 60, the core cut 52 a is made relatively small. can do. Therefore, the compressor 10 can improve motor efficiency compared with the compressor of the type which returns the oil which accumulates in a crank chamber to an oil reservoir space through the clearance gap of a core cut part.

  The rotor 53 is formed in a cylindrical shape. The rotor 53 and the drive shaft 60 are connected by inserting the drive shaft 60 into the rotor 53. The drive shaft 60 is also connected to the movable scroll 32. That is, the rotor 53 is connected to the movable scroll 32 via the drive shaft 60. The electric motor 50 drives the movable scroll 32 by rotating the rotor 53.

(2-4) Drive shaft The drive shaft 60 extends in the vertical direction along the axial center of the cylindrical member 21 of the casing 20 (see FIG. 1). The drive shaft 60 is connected to the rotor 53 of the electric motor 50 and transmits the driving force of the electric motor 50 to the movable scroll 32.

  The drive shaft 60 includes a main shaft 62 whose center axis coincides with the central axis of the cylindrical member 21, and a pin shaft portion 61 that is eccentric with respect to the main shaft 62 (see FIG. 1). The pin shaft portion 61 is an example of an eccentric portion.

  The pin shaft portion 61 is formed with a diameter smaller than that of the main shaft 62. The pin shaft portion 61 is inserted into the pin bearing portion 323 of the movable scroll 32 as described above. The pin shaft portion 61 is rotatably supported by a bearing metal 323a disposed inside the pin bearing portion 323.

  The main shaft 62 is rotatably supported by a bearing metal 332a of the upper bearing portion 332 of the upper housing 33 and a bearing metal 71a of a lower bearing portion 71 of the lower housing 70 described later (see FIG. 1). The main shaft 62 is connected to the rotor 53 of the electric motor 50 between the upper bearing portion 332 and the lower bearing portion 71 (see FIG. 1). The drive shaft 60 rotates around the rotation center C in plan view (see FIG. 2). The rotation center C is the center position of the main shaft 62 in plan view.

  As shown in FIG. 1, an in-shaft oil supply path 63 for supplying oil O to the sliding portion of the compressor 10 is formed inside the drive shaft 60. Further, as shown in FIG. 1, an in-shaft oil discharge path 64 for discharging the oil O accumulated in the crank chamber 35 is formed inside the drive shaft 60. The in-shaft oil supply path 63 and the in-shaft oil discharge path 64 will be described later.

  An oil pump shaft receiver 65 is fixed to the lower end of the main shaft 62 of the drive shaft 60 (see FIG. 1). Specifically, an oil pump shaft receiver 65 is inserted and fixed in an opening of an inflow passage 63a of an in-shaft oil supply passage 63 described later formed at the lower end of the main shaft 62.

  The oil pump shaft receiver 65 is a hollow member. The oil pump shaft 84 of the oil pump 80 is inserted into the hollow portion of the oil pump shaft receiver 65 from the lower end side as described later (see FIG. 6). An axial relay path 84b is formed inside the oil pump shaft 84 as described later (see FIG. 6). The axial relay path 84b communicates with the inflow path 63a of the in-shaft oil supply path 63 into which the oil pump shaft receiver 65 is inserted (see FIG. 6).

  Three balance weights (balance weight 66, balance weight 68, and balance weight 69) are attached to the main shaft 62 (see FIG. 1). The balance weight 66 is disposed in the crank chamber 35. The balance weight 68 is disposed between the rotor 53 of the electric motor 50 and the upper housing 33. The balance weight 69 is disposed below the rotor 53. The balance weight 66, the balance weight 68, and the balance weight 69 are provided to balance the rotation of the drive shaft 60.

  In the balance weight 66 disposed in the crank chamber 35, an in-weight inflow path 66a that connects the crank chamber 35 and an in-shaft inflow path 64a of an in-shaft oil discharge path 64 described later is formed. (See FIG. 3). The in-weight inflow path 66a extends on the same straight line as the in-axis inflow path 64a extending in a direction orthogonal to the axial direction of the drive shaft 60 (see FIG. 3). The oil O in the crank chamber 35 flows into the in-shaft oil discharge path 64 through the in-weight inflow path 66a.

(2-5) Lower housing The lower housing 70 is arrange | positioned in the lower part in the casing 20 (refer FIG. 1). The lower housing 70 is disposed below the electric motor 50. The lower housing 70 is a cylindrical member extending vertically (see FIG. 7). A part of the outer peripheral surface of the lower housing 70 projects toward the cylindrical member 21 of the casing 20 (see FIG. 7), and is fixed to the cylindrical member 21. A drive shaft 60 is inserted into the cylindrical lower housing 70 (see FIG. 1).

  The lower housing 70 has a lower shaft seal portion 77 at the upper portion thereof (see FIG. 1). Further, the lower housing 70 has a lower bearing portion 71 below the lower shaft seal portion 77 (see FIG. 1). A recess 72 that is recessed upward is formed in the lower portion of the lower housing 70 (see FIG. 1). An oil pump 80 is fixed to the lower end surface of the lower housing 70 so as to close the opening at the bottom of the recess 72 (see FIG. 1).

  The lower bearing portion 71 supports the drive shaft 60. A bearing metal 71a is provided inside the lower bearing portion 71 (see FIG. 1). The bearing metal 71 a rotatably supports the main shaft 62 of the drive shaft 60 disposed in the lower bearing portion 71 of the lower housing 70.

  The lower shaft seal portion 77 is formed in a cylindrical shape. The inner diameter of the lower shaft seal portion 77 is substantially equal to the outer diameter of the main shaft 62 of the drive shaft 60 disposed inside the lower shaft seal portion 77. The inner diameter of the lower shaft seal portion 77 is slightly larger than the outer diameter of the main shaft 62 of the drive shaft 60 disposed inside the lower shaft seal portion 77. The lower shaft seal portion 77 prevents oil O from leaking from the upper part of the gap between the lower housing 70 and the drive shaft 60.

  An annular space is formed between the lower bearing portion 71 and the lower shaft seal portion 77 and between the lower housing 70 and the drive shaft 60 so as to surround the drive shaft 60 (see FIG. 6). ). Even if the annular space is formed between the main shaft 62 and the lower housing 70 by reducing the outer diameter of a part of the main shaft 62 of the drive shaft 60, the inner diameter of a part of the lower housing 70 is reduced. And may be formed between the main shaft 62 and the lower shaft seal portion 77. This space functions as an annular space 76 (see FIG. 1). The annular space 76 is a space adjacent to the bearing metal 71a of the lower bearing portion 71 (see FIG. 6). The annular space 76 communicates with an oil drain main path 64c of an in-shaft oil discharge path 64, which will be described later, and an outflow path 64d of an in-shaft oil drain path 64, which will be described later (see FIG. 6). Oil O that has flowed through the main oil drain path 64c and the outflow path 64d flows into the annular space 76. A part of the oil O after being supplied to the sliding portion between the bearing metal 71 a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60 flows into the annular space 76. The annular space 76 communicates with a lower housing oil drain path 74 formed in the lower housing 70. The lower housing internal oil discharge path 74 is an example of an oil path. The lower housing internal oil drain passage 74 communicates with a lower space 78 (see FIG. 6) surrounded by the recess 72 of the lower housing 70 and the oil pump 80. The oil O flowing into the annular space 76 flows into the lower space 78 through the lower housing drain oil passage 74. Further, a part of the oil O after being supplied to the sliding portion between the bearing metal 71a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60 is directly (without passing through the oil draining path 74 in the lower housing). It flows into the lower space 78. The oil O that has flowed into the lower space 78 is guided to an oil discharge pump portion 80B of an oil pump 80, which will be described later, and flows into the oil reservoir space 25. That is, the lower housing internal oil discharge path 74 communicates the annular space 76 and the oil reservoir space 25 via the lower space 78 and the oil discharge pump portion 80B.

  A lower shaft seal ring 42 is disposed in the lower shaft seal portion 77. Since the lower shaft seal ring 42 is disposed in the lower shaft seal portion 77, the leakage of the oil O from the upper portion of the lower housing 70 can be prevented, and oil rising can be suppressed.

  Specifically, a lower shaft seal ring 42 is disposed between the lower shaft seal portion 77 and the drive shaft 60 above the lower shaft seal portion 77 (see FIG. 6). The lower shaft seal ring 42 is disposed in an annular seal ring groove 42a formed in a region of the main shaft 62 of the drive shaft 60 facing the lower shaft seal portion 77 (see FIG. 6). The lower shaft seal ring 42 is disposed in an annular seal ring groove formed in the lower shaft seal portion 77 instead of being disposed in the seal ring groove 42a formed in the main shaft 62 of the drive shaft 60. Also good.

  The lower shaft seal ring 42 is made of metal or resin. For the lower shaft seal ring 42, for example, a metal material or a resin material excellent in high temperature characteristics is used. The lower shaft seal ring 42 is formed in an annular shape, and has a joint (not shown) (not shown). The shape of the joint is, for example, an angle cut shape. However, the shape of the joint is not limited to this, and may be, for example, a step cut shape. The shape of the joint may be determined as appropriate. The diameter A2 (see FIG. 6, of the seal ring groove 42a) of the main shaft 62 of the drive shaft 60 of the portion to which the lower shaft seal ring 42 is attached at the axial height h2 (see FIG. 6) of the lower shaft seal ring 42. The value of the ratio to the diameter of the non-formed portion is 0.053, but is not limited thereto. In order to obtain sufficient sealing performance, the value of the ratio of the axial height h2 of the lower shaft seal ring 42 to the diameter A2 of the main shaft 62 of the drive shaft 60 of the portion where the lower shaft seal ring 42 is attached is 0.04 or more and less than 0.07. The ratio of the radial thickness w2 (see FIG. 6) of the lower shaft seal ring 42 to the diameter A2 of the main shaft 62 of the drive shaft 60 in the portion where the lower shaft seal ring 42 is attached is 0.045. However, the present invention is not limited to this. In order to obtain sufficient sealing performance, the value of the ratio of the radial thickness w2 of the lower shaft seal ring 42 to the diameter A2 of the main shaft 62 of the drive shaft 60 in the portion where the lower shaft seal ring 42 is attached is 0. It is preferably 0.03 or more and less than 0.06.

(2-6) In-shaft oil supply path The in-shaft oil supply path 63 is an example of an oil supply path. The in-shaft oil supply path 63 is an oil path for supplying the oil O in the oil reservoir space 25 supplied by an oil supply pump part 80 </ b> A of the oil pump 80 described later to each sliding part of the compressor 10. The in-shaft oil supply path 63 is formed in the drive shaft 60 (see FIG. 1). The in-shaft oil supply path 63 conveys the oil O in the oil reservoir space 25 to the upper end of the pin shaft portion 61 of the drive shaft 60 disposed in the crank chamber 35. That is, the in-shaft oil supply path 63 carries the oil O in the oil reservoir space 25 to the crank chamber 35.

  As shown in FIGS. 1, 3, and 4, the in-shaft oil supply path 63 mainly includes an inflow path 63 a, an oil supply main path 63 b, an upper outflow path 63 c, and a lower outflow path 63 d. FIG. 3 is a cross-sectional view of the upper portion of the drive shaft 60 cut along the SCS ′ cross section in FIG. FIG. 4 is a cross-sectional view of the lower portion of the drive shaft 60 taken along the S-C-T cross section in FIG. C in FIG. 2 indicates the rotation center C of the drive shaft 60.

  The inflow path 63a is a recess opening at the lower end of the drive shaft 60 (see FIG. 4). The inflow path 63a is formed in the central portion of the drive shaft 60 so as to be recessed upward from the lower end (see FIG. 4). An oil pump shaft receiver 65 is inserted into the inflow path 63a from the lower end opening (see FIG. 6). Further, an oil pump shaft 84 of an oil pump 80 described later is inserted into the hollow oil pump shaft receiver 65 (see FIG. 6). The inflow path 63a communicates with an axial relay path 84b formed in the oil pump shaft 84 of the oil pump 80 (see FIG. 6). The oil O in the oil reservoir space 25 is supplied from the inflow path 63a to the in-shaft oil supply path 63 by the oil supply pump portion 80A of the oil pump 80.

  The oil supply main path 63b extends in the drive shaft 60 in the axial direction, that is, in the vertical direction. The lower end of the oil supply main path 63b communicates with the inflow path 63a. The upper end of the oil supply main path 63 b opens at the upper end surface of the pin shaft portion 61 of the drive shaft 60. The oil supply main path 63 b communicates with the oil communication chamber 36.

  The upper outflow path 63c extends in the drive shaft 60 from the oil supply main path 63b in a direction crossing the axial direction. In particular, here, the upper outflow path 63c extends in the drive shaft 60 from the oil supply main path 63b in a direction orthogonal to the axial direction (see FIG. 3). The upper outflow path 63c extends in the drive shaft 60 in the radial direction from the oil supply main path 63b (see FIG. 2). The upper outflow path 63 c opens at the outer peripheral surface of the drive shaft 60 in the upper bearing portion 332 of the upper housing 33. Oil O flowing out of the opening of the outer peripheral surface of the drive shaft 60 in the upper outflow path 63 c is supplied to the sliding portion between the bearing metal 332 a of the upper bearing portion 332 and the main shaft 62 of the drive shaft 60.

  The lower outflow path 63d extends in the drive shaft 60 from the oil supply main path 63b in a direction crossing the axial direction (see FIG. 4). In particular, here, the lower outflow path 63d extends in the drive shaft 60 from the oil supply main path 63b in a direction orthogonal to the axial direction (see FIG. 4). The lower outflow path 63d extends in the drive shaft 60 in the radial direction from the oil supply main path 63b (see FIG. 2). The lower outflow path 63 d opens at the outer peripheral surface of the drive shaft 60 in the lower bearing portion 71 of the lower housing 70. Oil O flowing out of the opening of the outer peripheral surface of the drive shaft 60 in the lower outflow path 63d is supplied to the sliding portion between the bearing metal 71a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60.

  Here, the opening on the outer peripheral surface of the drive shaft 60 in the upper outflow path 63c and the opening on the outer peripheral surface of the drive shaft 60 in the lower outflow path 63d are shifted by about 180 degrees with respect to the rotation center C of the drive shaft 60. (See FIG. 2). In other words, the upper outflow path 63c and the lower outflow path 63d generally extend on a straight line passing through the rotation center C of the drive shaft 60 in plan view. Referring to FIG. 2, the upper outflow path 63c and the lower outflow path 63d generally extend on a straight line ST extending through the rotation center C of the drive shaft 60 in plan view.

  In this way, the opening on the outer peripheral surface of the drive shaft 60 of the upper outflow path 63c and the opening on the outer peripheral surface of the drive shaft 60 of the lower outflow path 63d are arranged symmetrically with respect to the rotation center C of the drive shaft 60. This facilitates oil film generation at the sliding portion of the upper bearing portion 332 and the sliding portion of the lower bearing portion 71. The reason is as follows. In terms of mechanism, the upper bearing portion 332 and the lower bearing portion 71 receive a load in a direction (angle) that is generally opposite to the rotation center C of the drive shaft 60 (approximately 180 degrees different). The form in which the upper bearing portion 332 and the lower bearing portion 71 receive a load is a so-called rotational load in which the magnitude of the load is substantially constant and the load direction varies in synchronization with the shaft rotation. Therefore, if each of the upper bearing portion 332 and the lower bearing portion 71 is designed to provide an opening for the outflow path on the opposite side to the direction in which the load is supported (substantially the minimum oil film thickness position angle), the upper bearing portion 332 and the lower bearing portion The flow rate of the oil O supplied to the part 71 can be increased most.

  However, as shown in FIGS. 2 and 4, when the upper outflow path 63c and the lower outflow path 63d are branched from the same oil supply main path 63b, the oil O flowing through one of the oil supply main path 63b and the upper outflow path 63c is driven. The flow is against the centrifugal force caused by the rotation of the shaft 60. In the present embodiment, the flow of the oil O flowing through the lower outflow path 63d becomes a flow that opposes the centrifugal force, and it is difficult for the lower bearing portion 71 to be supplied with oil (see FIG. 4).

  Therefore, in another embodiment, as shown in FIG. 5, an oil supply main path 63 b that extends in the axial direction from the inflow path 63 a at an axially symmetrical position with respect to the rotation center C of the drive shaft 60. May be provided with another lower bearing dedicated path (vertical hole) 63e. In addition, the lower outflow path 63d may be connected to the lower bearing dedicated path 63e instead of the oil supply main path 63b, and the oil O may be supplied to the lower outflow path 63d via the lower bearing dedicated path 63e. With the configuration as shown in FIG. 5, the flow of the oil O flowing through the lower outflow path 63 d also becomes a flow along the centrifugal force, and the oil O is easily supplied to the lower bearing portion 71.

(2-7) Oil Discharge Route The oil discharge route 90 guides the oil O in the crank chamber 35 and the oil O after being supplied to the lower bearing portion 71 to the oil discharge pump portion 80B of the oil pump 80. It is. The oil drainage path 90 mainly includes an in-shaft oil drainage path 64, an annular space 76, a lower housing drainage oil path 74, and a lower space 78 surrounded by the recess 72 of the lower housing 70 and the oil pump 80. Included (see FIG. 1).

  The in-shaft oil discharge path 64 guides the oil O in the crank chamber 35 to the annular space 76 formed around the main shaft 62 of the drive shaft 60. The oil O in the annular space 76 is conveyed to the lower space 78 through the lower housing drain oil passage 74. The oil O collected in the crank chamber 35 includes the oil O after being supplied to the sliding portion between the pin shaft portion 61 of the drive shaft 60 and the bearing metal 323a of the pin bearing portion 323. The oil O accumulated in the crank chamber 35 is supplied to the sliding portion between the main shaft 62 of the drive shaft 60 and the bearing metal 332a of the upper bearing portion 332, and then passes through the upper bearing oil drain passage 332b. Oil O flowing into the The oil O flowing into the annular space 76 is supplied to the sliding portion between the oil O flowing through the in-shaft oil discharge path 64 and the main shaft 62 of the drive shaft 60 and the bearing metal 71a of the lower bearing portion 71. Part of oil O.

  The in-shaft oil discharge path 64 mainly has an in-shaft inflow path 64a, a main oil discharge path 64c, and an outflow path 64d (see FIGS. 1 and 6).

  The oil drain main path 64c is a hole that extends in the drive shaft 60 in the axial direction, that is, in the vertical direction. The oil drain main path 64c is formed in a circular shape in plan view. The oil drain main path 64 c extends from the upper end surface of the pin shaft portion 61 of the drive shaft 60 to the lower portion of the drive shaft 60. The opening at the upper end of the oil drain main path 64c is closed by a plug 64e (see FIG. 1). For this reason, the oil drain main path 64 c does not communicate with the oil communication chamber 36 formed above the pin shaft portion 61.

  The in-axis inflow path 64a extends in the drive shaft 60 from the oil drain main path 64c in a direction crossing the axial direction. In particular, here, the in-axis inflow path 64a extends in the drive shaft 60 from the oil drain main path 64c in a direction orthogonal to the axial direction. The in-shaft passage 64a extends in the drive shaft 60 in the radial direction from the oil drain main passage 64c. The in-shaft inflow path 64 a communicates with an in-weight inflow path 66 a formed in a balance weight 66 that is disposed in the crank chamber 35 and attached to the drive shaft 60. The in-weight inflow path 66 a has one end communicating with the in-shaft inflow path 64 a and the other end communicating with the crank chamber 35. The oil O in the crank chamber 35 passes through the in-weight inflow path 66a and flows into the in-axis inflow path 64a. The in-weight inflow path 66 a and the in-shaft inflow path 64 a function as an inflow path 67 that connects the oil drain main path 64 c and the crank chamber 35.

  The outflow path 64d extends in the drive shaft 60 from the lower end of the oil drain main path 64c in a direction crossing the axial direction. Particularly, here, the outflow path 64d extends in the drive shaft 60 from the lower end of the oil drain main path 64c in a direction orthogonal to the axial direction. The outflow path 64d extends in the drive shaft 60 in the radial direction from the lower end of the oil drain main path 64c. The outflow path 64 d is open to the outer peripheral surface of the main shaft 62 of the drive shaft 60 in an annular space 76 formed between the lower housing 70 and the main shaft 62 of the drive shaft 60. That is, the outflow path 64 d communicates with the annular space 76. The oil O that has flowed into the annular space 76 is discharged to a lower space 78 surrounded by the recess 72 of the lower housing 70 and the oil pump 80 via a lower housing drain oil passage 74 formed in the lower housing 70. The

  Oil O discharged from the in-shaft oil discharge path 64 flows into the lower space 78. In the lower space 78, the oil O after being supplied to the sliding portion between the bearing metal 71a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60 is directly or directly, or the annular space 76 and the lower housing. It flows in through the internal oil discharge path 74. The oil O that has flowed into the lower space 78 is guided to a drain oil pump portion 80B of the oil pump 80 through a discharge port 73a (see FIG. 1) formed in a thrust plate 73 of the oil pump 80 described later.

(2-8) Oil Pump The oil pump 80 is a so-called double trochoidal positive displacement pump.

  The oil pump 80 is fixed to the lower end surface of the lower housing 70 with bolts 83 as shown in FIG. The oil pump 80 is attached to the lower part of the drive shaft 60. Specifically, the oil pump shaft 84 of the oil pump 80 is inserted into the oil pump shaft receiver 65 attached to the inflow path 63 a below the drive shaft 60, so that the oil pump 80 is connected to the drive shaft 60. It is attached. The oil pump 80 mainly includes a thrust plate 73, a pump body 81, a pump cover 82, an oil pump shaft 84, a lower outer rotor 85, a lower inner rotor 86, an upper outer rotor 87, and an upper inner rotor 88.

  The oil pump 80 includes an oil supply pump portion 80A that supplies the oil O in the oil reservoir space 25 to the in-shaft oil supply path 63, and a drain that discharges the oil O in the crank chamber 35 to the oil reservoir space 25 through the oil discharge path 90. Oil pump unit 80B (see FIG. 6). Oil supply pump unit 80A is an example of an oil supply pump. The oil discharge pump unit 80B is an example of an oil discharge pump.

  The oil supply pump portion 80A includes a lower outer rotor 85 and a lower inner rotor 86 (see FIG. 6). The oil discharge pump unit 80B includes an upper outer rotor 87 and an upper inner rotor 88 (see FIG. 6). A driving force is transmitted by the oil pump shaft 84 to the lower inner rotor 86 of the oil supply pump portion 80A and the upper inner rotor 88 of the oil discharge pump portion 80B. The oil pump shaft 84 is connected to the lower part of the drive shaft 60, and when the drive shaft 60 rotates, the oil pump shaft 84 also rotates. As a result of the rotation of the oil pump shaft 84, the lower inner rotor 86 and the upper inner rotor 88 are driven, the oil supply pump portion 80A is a positive displacement oil pump, and the oil discharge pump portion 80B is a positive displacement oil pump. Function.

  Hereinafter, the oil pump 80 will be described in detail.

  The thrust plate 73 is formed in a disc shape (see FIG. 7). The thrust plate 73 is attached to the lower housing 70 so as to close the recess 72 formed in the lower housing 70 (see FIGS. 6 and 7). The lower end surface of the oil pump shaft receiver 65 attached to the lower end of the drive shaft 60 is in sliding contact with the thrust plate 73 (see FIG. 6). The thrust plate 73 receives the thrust force of the drive shaft 60.

  An insertion hole 73b for inserting the lower portion of the oil pump shaft 84 is formed in the central portion in the radial direction of the thrust plate 73 (see FIGS. 6 and 7). Further, a discharge port 73a for guiding the oil O in the lower space 78 above the thrust plate 73 to the oil discharge pump portion 80B is formed in the outer peripheral portion of the thrust plate 73 (see FIGS. 6 and 7). . The upper end of the discharge port 73a communicates with the lower space 78, and the lower end communicates with an in-body upper flow path 81b of the pump body 81 described later.

  The pump body 81 is a substantially cylindrical member that extends in the vertical direction. An oil pump shaft 84, a lower outer rotor 85, a lower inner rotor 86, an upper outer rotor 87, and an upper inner rotor 88 are accommodated in the pump body 81 (see FIG. 6). An outer peripheral edge 81a protruding upward is formed on the periphery of the upper portion of the pump body 81 (see FIG. 6). The pump body 81 is fixed to the lower housing 70 with the thrust plate 73 fitted inside the outer peripheral edge 81a (see FIG. 6).

  In the central portion of the upper surface of the pump body 81, an in-body upper flow path 81b that is recessed downward is formed (see FIGS. 6 and 7). In the central portion of the lower surface of the pump body 81, an in-body lower flow path 81c that is recessed upward is formed (see FIGS. 6 and 7). The in-body lower flow path 81c is formed in a circular shape in plan view. Furthermore, an inner peripheral hole 81d into which the oil pump shaft 84 is inserted is formed at the center of the pump body 81 (see FIGS. 6 and 7).

  The pump body 81 is formed with a discharge passage 81e extending in the horizontal direction and penetrating the inside and the outside (see FIGS. 6 and 7). One end (end on the inner side) of the discharge passage 81e opens to the upper flow passage 81b in the body, and the other end (end on the outer side) opens to the outer peripheral surface of the pump body 81 (see FIG. 6). ). A pump outlet pipe 89 is attached to the discharge flow path 81e (see FIG. 6). The pump outlet pipe 89 is formed in an L shape. The pump outlet pipe 89 extends in the horizontal direction along the discharge flow path 81e, and then changes the direction by 90 degrees and extends downward. The lower end of the pump outlet pipe 89 is disposed below the lower end of the oil pump 80. Further, the lower end of the pump outlet pipe 89 is disposed in the lower part of the oil reservoir space 25. The pump outlet pipe 89 guides the oil O that has flowed from the oil discharge pump unit 80B through the discharge flow path 81e to the lower part of the oil reservoir space 25.

  The pump cover 82 is formed in a substantially disc shape (see FIG. 7). The pump cover 82 is fixed to the lower surface of the pump body 81 (see FIGS. 6 and 7).

  An oil pump shaft 84 is rotatably supported at the center of the pump cover 82 (see FIGS. 6 and 7). The pump cover 82 is formed with an arc-shaped suction port 82a on the outer peripheral side of the oil pump shaft 84 supported by the pump cover 82 in plan view (see FIGS. 6 and 7). The suction port 82a is formed so as to penetrate the pump cover 82 in the vertical direction. The lower end of the suction port 82 a is open to the oil reservoir space 25. The upper end of the suction port 82 a opens into a lower body flow path 81 c formed in the pump body 81. When the oil pump shaft 84 rotates and the oil supply pump portion 80A is driven, the oil O in the oil reservoir space 25 passes through the suction port 82a and flows into the lower flow path 81c in the body.

  The oil pump shaft 84 is formed in a cylindrical shape and extends in the vertical direction (see FIG. 6). The lower part of the oil pump shaft 84 is rotatably supported by the pump cover 82 (see FIGS. 6 and 7). The oil pump shaft 84 is inserted into an inner peripheral hole 81d formed in the pump body 81, and is rotatably supported by the pump body 81 (see FIGS. 6 and 7). The oil pump shaft 84 is inserted into the insertion hole 73b of the thrust plate 73 disposed on the upper portion of the pump body 81 (see FIGS. 6 and 7). Further, the oil pump shaft 84 is inserted from below into an oil pump shaft receiver 65 attached to an inflow path 63 a formed at the lower end portion of the main shaft 62 of the drive shaft 60, and is fitted to the oil pump shaft receiver 65. (See FIG. 6 and FIG. 7). Specifically, the upper end portion of the oil pump shaft 84 formed in a hexagonal shape is inserted into a hexagonal hole provided in the inner diameter portion of the oil pump shaft receiver 65. That is, the oil pump shaft 84 is connected to the lower portion of the drive shaft 60 via the oil pump shaft receiver 65. By connecting the oil pump shaft 84 and the drive shaft 60, the oil pump shaft 84 rotates integrally with the drive shaft 60.

  A radial relay path 84a and an axial relay path 84b are formed inside the oil pump shaft 84 (see FIGS. 6 and 7). The radial relay path 84a penetrates the oil pump shaft 84 in the radial direction (see FIG. 6). The radial relay path 84 a opens to the body lower flow path 81 c of the pump body 81. The axial relay path 84b extends in the axial direction (vertical direction) through the oil pump shaft 84. The axial relay path 84b opens at the upper end surface of the oil pump shaft 84 and communicates with an inflow path 63a of an in-shaft oil supply path 63 formed inside the drive shaft 60 (see FIG. 6). The lower end of the axial relay path 84b communicates with the radial relay path 84a (see FIG. 6). When the oil pump shaft 84 rotates, the oil O in the lower flow path 81c in the body passes through the radial relay path 84a and the axial relay path 84b and is supplied to the in-shaft oil supply path 63 (see FIG. 6). ).

  The lower outer rotor 85 is fitted in the lower flow path 81c in the body. The lower outer rotor 85 is formed in an annular shape, and a plurality of outer teeth 85a having an arc shape (more precisely, a trochoidal curve shape) are formed on the inner peripheral surface thereof (see FIG. 7). The plurality of outer teeth 85a are arranged at equal intervals in the circumferential direction and bulge out toward the lower inner rotor 86 disposed inside the lower outer rotor 85.

  The lower inner rotor 86 is formed in an annular shape (see FIG. 7). The lower inner rotor 86 is disposed inside the lower outer rotor 85 (see FIG. 6). The lower inner rotor 86 is fitted to the outside of the oil pump shaft 84. Specifically, a D-shaped holding hole 86a is formed inside the lower inner rotor 86 (see FIG. 7). By inserting the oil pump shaft 84 into the holding hole 86a, the lower inner rotor 86 and the oil pump shaft 84 are connected, and the lower inner rotor 86 rotates integrally with the oil pump shaft 84. A plurality of inner teeth 86b are formed on the outer peripheral surface of the lower inner rotor 86 so as to correspond to the outer teeth 85a of the lower outer rotor 85 (see FIG. 7). The lower inner rotor 86 is disposed inside the lower outer rotor 85 so that the inner tooth portion 86b and the outer tooth portion 85a mesh with each other, so that the inner tooth portion 86b and the outer tooth portion 85a are interposed between each other. A volume chamber V1 for conveying the oil O is formed (see FIG. 6).

  The lower portion of the oil pump 80 including the lower inner rotor 86 and the lower outer rotor 85 constitutes an oil supply pump portion 80A. In the oil supply pump portion 80A, the oil O in the oil reservoir space 25 flows from the suction port 82a of the pump cover 82, and between the lower inner rotor 86 and the lower outer rotor 85 in the lower flow path 81c in the body. After passing through the volume chamber V1, it passes through the radial relay path 84a and the axial relay path 84b and is supplied to the in-shaft oil supply path 63.

  The upper outer rotor 87 is fitted in the body upper flow path 81b. The upper outer rotor 87 is formed in an annular shape, and a plurality of arcuate (more strictly speaking, trochoidal curve) outer teeth 87a are formed on the inner peripheral surface thereof (see FIG. 7). The plurality of outer teeth 87a are arranged at equal intervals in the circumferential direction and bulge toward the upper inner rotor 88 disposed inside the upper outer rotor 87.

  The upper inner rotor 88 is formed in an annular shape (see FIG. 7). The upper inner rotor 88 is disposed inside the upper outer rotor 87 (see FIG. 6). The upper inner rotor 88 is fitted to the outside of the oil pump shaft 84. Specifically, a D-shaped holding hole 88a is formed inside the upper inner rotor 88 (see FIG. 7). By inserting the oil pump shaft 84 into the holding hole 88a, the upper inner rotor 88 and the oil pump shaft 84 are connected, and the upper inner rotor 88 rotates integrally with the oil pump shaft 84. A plurality of inner teeth 88b are formed on the outer peripheral surface of the upper inner rotor 88 so as to correspond to the outer teeth 87a of the upper outer rotor 87 (see FIG. 7). The upper inner rotor 88 is disposed inside the upper outer rotor 87 so that the inner tooth portion 88b and the outer tooth portion 87a mesh with each other, so that oil is provided between the inner tooth portion 88b and the outer tooth portion 87a. A volume chamber V2 for conveying O is formed (see FIG. 6). The volume chamber V <b> 2 between the upper inner rotor 88 and the upper outer rotor 87 is larger than the volume chamber V <b> 1 between the lower inner rotor 86 and the lower outer rotor 85.

  The upper portion of the oil pump 80 including the upper inner rotor 88 and the upper outer rotor 87 constitutes an oil discharge pump portion 80B. In the oil discharge pump part 80B, the oil O flows from the lower space 78 constituting a part of the oil discharge path 90 through the discharge port 73a of the thrust plate 73 into the body upper flow path 81b, and the body upper flow path After passing through the volume chamber V <b> 2 between the upper inner rotor 88 and the upper outer rotor 87 in 81 b, the oil reservoir space at the bottom of the casing 20 passes through the discharge passage 81 e formed on the side surface of the pump body 81. To 25.

  As described above, the volume chamber V2 between the upper inner rotor 88 and the upper outer rotor 87 is larger than the volume chamber V1 between the lower inner rotor 86 and the lower outer rotor 85. The discharge amount of the pump unit 80B is larger than the discharge amount of the oil supply pump unit 80A. Here, the discharge amount means the theoretical discharge amount of the oil supply pump unit 80A and the oil discharge pump unit 80B. The actual discharge amount of the oil discharge pump unit 80B may be smaller than the actual discharge amount of the oil supply pump unit 80A.

  How much the capacity of the volume chamber V2 is made larger than the capacity of the volume chamber V1 (how much the discharge amount of the oil discharge pump unit 80B is made larger than the discharge amount of the oil supply pump unit 80A) is oil in the crank chamber 35. It is determined appropriately so that O does not accumulate excessively.

(3) Operation Operation A basic operation operation of the compressor 10 will be described.

  When the compressor 10 is in operation, the electric motor 50 is operated and the rotor 53 rotates. When the rotor 53 rotates, the drive shaft 60 connected to the rotor 53 also rotates. When the drive shaft 60 rotates, the pin shaft portion 61 rotates eccentrically. As a result, the movable scroll 32 in which the pin shaft portion 61 is inserted into the pin bearing portion 323 turns. The movable scroll 32 revolves with respect to the fixed scroll 31 without rotating due to the action of the Oldham coupling 34. As the movable scroll 32 revolves, low-pressure refrigerant in the refrigerant circuit is sucked into the casing 20 through a suction pipe (not shown). More specifically, the low-pressure refrigerant in the refrigerant circuit passes through the suction pipe and is sucked from the peripheral side of the fixed side wrap 312 to the compression chamber Sc. As the movable scroll 32 revolves, the suction pipe and the compression chamber Sc no longer communicate with each other. And compression chamber Sc approaches the center part from the peripheral side, reducing the volume. Thereby, the pressure of the refrigerant in the compression chamber Sc increases. The high-pressure refrigerant compressed by the compression mechanism 30 is discharged into the discharge space 311c through the discharge port 311a formed near the center of the fixed side end plate 311. High-pressure refrigerant in the refrigerant circuit discharged into the discharge space 311 c flows into the space below the upper housing 33 through the refrigerant passage 314 formed in the fixed scroll 31 and the refrigerant passage 335 formed in the upper housing 33. To do. The high-pressure refrigerant flowing into the space below the upper housing 33 is discharged from the discharge pipe 24 and sent to the refrigerant circuit.

(4) Oil Supply / Discharge Operation The oil O supply / discharge operation in the compressor 10 will be described.

  First, the oil supply operation of the oil O will be described.

  When the compressor 10 is operated and the drive shaft 60 rotates, the oil supply pump unit 80A of the oil pump 80 is driven. Specifically, when the oil pump shaft 84 connected to the drive shaft 60 rotates, the lower inner rotor 86 rotates inside the lower outer rotor 85. As a result, the volume of the volume chamber V <b> 1 expands and contracts, and the oil O in the oil reservoir space 25 is sucked into the oil supply pump portion 80 </ b> A of the oil pump 80.

  More specifically, the oil O in the oil reservoir space 25 is sucked into the volume chamber V1 in the lower flow path 81c in the body via the suction port 82a of the pump cover 82. The oil O discharged from the volume chamber V <b> 1 flows through the radial relay path 84 a and the axial relay path 84 b and flows into the inflow path 63 a of the in-shaft oil supply path 63.

  The oil O that has flowed into the inflow path 63a of the in-shaft oil supply path 63 rises in the oil supply main path 63b. Further, when the lower bearing dedicated path 63e is provided as in the embodiment of FIG. 5, the oil O that has flowed into the inflow path 63a ascends the oil supply main path 63b and the lower bearing dedicated path 63e.

  When the lower outflow path 63d communicates with the oil supply main path 63b as in the embodiment of FIG. 4, a part of the oil O that rises in the oil supply main path 63b is supplied to the lower bearing portion 71 through the lower outflow path 63d. Is done. In the case where the lower bearing dedicated path 63e is provided as in the embodiment of FIG. 5, the oil O that moves up the lower bearing dedicated path 63e is supplied to the lower bearing portion 71 through the lower outflow path 63d. The oil O supplied to the lower bearing portion 71 lubricates the sliding portion between the bearing metal 71 a and the main shaft 62 of the drive shaft 60. Thereafter, the oil O flows out into the annular space 76 formed below the lower shaft seal portion 77 of the lower housing 70 or the lower space 78 surrounded by the recess 72 of the lower housing 70. The oil O that has flowed into the annular space 76 flows out to the lower space 78 via the lower housing drain oil passage 74.

  A part of the oil O that rises in the oil supply main path 63b is supplied to the upper bearing portion 332 through the upper outflow path 63c. The oil O supplied to the upper bearing portion 332 lubricates the sliding portion between the bearing metal 332a and the main shaft 62 of the drive shaft 60. Thereafter, the oil O passes through the upper bearing oil drain passage 332 b and flows into the crank chamber 35 formed by the upper housing 33.

  A part of the oil O that rises in the oil supply main path 63 b rises up to the upper end of the oil supply main path 63 b and flows into the oil communication chamber 36. Part of the oil O that has flowed into the oil communication chamber 36 flows into an oil path (not shown) formed in the movable scroll 32, and the rest flows into a pin shaft channel 323b (not shown). The oil O that has flowed into the oil path formed in the movable scroll 32 is supplied to a thrust surface between the fixed scroll 31 and the movable scroll 32, a gap between the fixed wrap 312 and the movable wrap 322, or the like. On the other hand, the oil O flowing into the pin shaft channel 323b is supplied to the sliding portion between the bearing metal 323a in the pin bearing portion 323 and the pin shaft portion 61 of the drive shaft 60, and lubricates the sliding portion. Thereafter, the oil O flows out into the crank chamber 35 formed by the upper housing 33.

  Next, the oil O discharging operation will be described.

  When the compressor 10 is operated and the drive shaft 60 rotates, the oil discharge pump unit 80B of the oil pump 80 is also driven. Specifically, when the oil pump shaft 84 connected to the drive shaft 60 rotates, the upper inner rotor 88 rotates inside the upper outer rotor 87. As a result, the volume of the volume chamber V2 of the oil discharge pump unit 80B is expanded and contracted, and the oil O in the crank chamber 35 passes through the inflow path 67 (the inflow path 66a in the weight and the inflow path 64a in the shaft), and the main oil discharge path 64c. The oil O that has flowed into the drained oil main path 64c from the inflow path 67 moves downward in the drained oil main path 64c, passes through the outflow path 64d, and flows out into the annular space 76. The oil O that has flowed into the annular space 76 passes through the lower housing drain oil passage 74 and flows into the lower space 78 surrounded by the recess 72 of the lower housing 70. The oil O in the lower space 78 flows through the discharge port 73 a formed in the thrust plate 73 and flows into the oil discharge pump portion 80 </ b> B of the oil pump 80. More specifically, the oil O that has passed through the discharge port 73a flows into the in-body upper flow path 81b and is sucked into the volume chamber V2 in the in-body upper flow path 81b. The oil O discharged from the volume chamber V <b> 2 passes through the discharge flow path 81 e formed inside the pump body 81, and is discharged to the oil reservoir space 25 at the bottom of the casing 20 through the pump outlet pipe 89.

  This time, by arranging the upper shaft seal ring 41 in the upper shaft seal portion 333, the oil rising index (a value representing the degree of oil rising with respect to a predetermined reference) with respect to the operating frequency of the compressor 10 is shown in FIG. It changes as indicated by the solid line and black circle (refer to the graph with oil drain in the shaft and upper shaft seal ring). On the other hand, when the upper shaft seal ring 41 is not disposed in the upper shaft seal portion 333, the oil rising index changes as shown by white circles and broken lines in FIG. (Refer to the graph without internal oil drain and upper shaft seal ring). In either case, as the operating frequency of the compressor 10 increases, the pressure in the crank chamber 35 increases and the oil increase index increases. However, as shown in FIG. 8, when the upper shaft seal part 333 is provided with the upper shaft seal ring 41, the oil rise is greatly suppressed compared to the case where the upper shaft seal part 333 is not provided with the upper shaft seal ring 41. it can.

  In FIG. 8, for reference, an oil drain path is not provided in the shaft, and the oil with respect to the operating frequency of the compressor when the oil in the crank chamber is returned to the oil sump space through the core cut portion of the electric motor. The change in the rising index is indicated by a black square and a two-dot chain line (off-axis drain oil). By arranging the upper shaft seal ring 41 in the upper shaft seal portion 333, it is possible to reduce the oil rise to the same level or less even when compared with a conventional compressor in which the pressure increase in the crank chamber is relatively low.

(5) Features (5-1)
The compressor 10 of this embodiment includes a casing 20, an electric motor 50, a drive shaft 60, a compression mechanism 30, an in-shaft oil supply path 63 as an example of an oil supply path, an oil discharge path 90, and an upper shaft seal ring. 41. The casing 20 has an oil reservoir space 25 formed at the bottom. The electric motor 50 is accommodated in the casing 20. The drive shaft 60 extends in the vertical direction and is connected to the electric motor 50. The compression mechanism 30 is accommodated in the casing 20. The compression mechanism 30 includes a movable scroll 32 as an example of a movable part, and an upper housing 33. The movable scroll 32 is connected to the drive shaft 60 and is driven by the electric motor 50. The upper housing 33 forms a crank chamber 35 in which a connecting portion between the pin shaft portion 61 of the drive shaft 60 and the movable scroll 32 (pin bearing portion 323 of the movable scroll 32) is accommodated. The pin shaft portion 61 is an example of an eccentric portion of the drive shaft 60. The upper housing 33 is disposed below the crank chamber 35 and has an upper bearing portion 332 that supports the drive shaft 60. The upper housing 33 has an upper shaft seal portion 333 disposed below the upper bearing portion 332. The in-shaft oil supply path 63 carries the oil O in the oil reservoir space 25 to the crank chamber 35. The in-shaft oil supply path 63 is formed inside the drive shaft 60. The oil discharge path 90 includes a main oil discharge path 64 c and an inflow path 67. The oil drain main path 64c extends in the axial direction inside the drive shaft 60. The inflow path 67 communicates the oil drain main path 64 c with the crank chamber 35. The upper shaft seal ring 41 is disposed on the upper shaft seal portion 333.

  Here, the upper shaft seal ring 41 is disposed on the upper shaft seal portion 333 of the upper housing 33 below the crank chamber 35 formed in the upper housing 33. Therefore, even when the pressure in the crank chamber 35 rises, leakage of the oil O from the lower part of the upper housing 33 is prevented, and oil rise is suppressed.

(5-2)
The compressor 10 of this embodiment includes a lower housing 70 disposed below the electric motor 50 and a lower shaft seal ring 42. The lower housing 70 has a lower bearing portion 71 and a lower shaft seal portion 77. The lower bearing portion 71 supports the drive shaft 60. The lower shaft seal portion 77 is disposed above the lower bearing portion 71. The lower shaft seal ring 42 is disposed on the lower shaft seal portion 77.

  Here, since the lower shaft seal ring 42 is disposed in the lower shaft seal portion 77 of the lower housing 70, leakage of the oil O from above the lower housing 70 can be prevented, and oil rising is easily suppressed.

(5-3)
In the compressor 10 of the present embodiment, the annular space 76 is disposed below the lower shaft seal portion 77. The annular space 76 is formed so as to surround the drive shaft 60. The annular space 76 communicates with the oil drain main path 64c. The lower housing 70 is formed with a lower housing drain oil passage 74 that allows the annular space 76 and the oil reservoir space 25 to communicate with each other.

  Here, by providing the annular space 76 and the lower housing drain oil passage 74, it is easy to secure a flow path through which the oil O flows from the drain main oil passage 64 c to the oil reservoir space 25. Therefore, the pressure rise in the crank chamber 35 can be suppressed relatively low, and the oil rise due to the leakage of the oil O from the lower portion of the upper housing 33 can be suppressed.

(5-4)
In the compressor 10 of the present embodiment, the drive shaft 60 is formed with a seal ring groove 42a in which the lower shaft seal ring 42 is disposed.

  Here, since the seal ring groove 42 a for disposing the lower shaft seal ring 42 is provided on the drive shaft 60 side, it is easy to assemble the compressor 10 in which the lower shaft seal ring 42 is disposed in the lower shaft seal portion 77. is there.

(5-5)
In the compressor 10 of the present embodiment, the ratio of the axial height h2 of the lower shaft seal ring 42 to the diameter A2 of the drive shaft 60 of the mounting portion of the lower shaft seal ring 42 is 0.04 or more and 0.00. Is less than 07.

  Here, by using the lower shaft seal ring 40 having a height h2 that satisfies the above conditions, it is possible to prevent the oil O from leaking from the upper portion of the lower housing 70. Further, by using the lower shaft seal ring 40 having the height h2 that satisfies the above conditions, the height h2 of the lower shaft seal ring 42 becomes unnecessarily high, and the efficiency of the compressor 10 decreases. Can be prevented.

(5-6)
In the compressor 10 of the present embodiment, the drive shaft 60 is formed with a seal ring groove 41a in which the upper shaft seal ring 41 is disposed.

  Here, since the seal ring groove 41a in which the upper shaft seal ring 41 is disposed is provided on the drive shaft 60 side, it is easy to assemble the compressor 10 in which the upper shaft seal ring 41 is disposed in the upper shaft seal portion 333. is there.

(5-7)
In the compressor 10 of the present embodiment, the ratio of the axial height h1 of the upper shaft seal ring 41 to the diameter A1 of the drive shaft 60 of the mounting portion of the upper shaft seal ring 41 is 0.04 or more and 0.00. Is less than 07.

  Here, by using the upper shaft seal ring 41 having a height h1 that satisfies the above conditions, the oil O can be prevented from leaking from the lower portion of the upper housing 33, and the height that satisfies the above conditions can be prevented. By using the upper shaft seal ring 41 having the length h1, it is possible to prevent the height h1 of the upper shaft seal ring 41 from becoming unnecessarily high and the efficiency of the compressor 10 from being lowered.

(5-8)
The compressor 10 of this embodiment includes an oil pump 80 as an example of a dual pump. The oil pump 80 is attached to the lower part of the drive shaft 60. Oil pump 80 includes an oil supply pump portion 80A and an oil discharge pump portion 80B. Oil supply pump unit 80A is an example of an oil supply pump. The oil discharge pump unit 80B is an example of an oil discharge pump. The oil supply pump unit 80 </ b> A supplies the oil O in the oil reservoir space 25 to the in-shaft oil supply path 63. The oil discharge pump unit 80 </ b> B discharges the oil O in the crank chamber 35 to the oil reservoir space 25 through the oil discharge path 90.

  Here, since oil supply to the crank chamber 35 is performed by the oil supply pump unit 80A and oil discharge from the crank chamber 35 is performed by the oil discharge pump unit 80B, it is easy to perform oil supply and oil discharge appropriately.

(5-9)
In the compressor 10 of the present embodiment, the oil discharge pump unit 80B and the oil supply pump unit 80A are positive displacement pumps. The volume of the volume chamber V2 of the oil discharge pump unit 80B is larger than the volume of the volume chamber V1 of the oil supply pump unit 80A.

  Here, since the volume of the oil discharge pump portion 80B is larger than the volume of the oil supply pump portion 80A, the pressure increase in the crank chamber 35 can be suppressed relatively low, and the oil rise due to the leakage of the oil O from the lower portion of the upper housing 33 Can be suppressed.

Second Embodiment
The compressor 110 according to the second embodiment will be described below. Since the compressor 110 has many points similar to those of the compressor 10 of the first embodiment, differences will be mainly described.

(1) Overall Overview FIG. 9 is a schematic longitudinal sectional view of the upper housing 33, the electric motor 50, the drive shaft 60, the lower housing 170, and the oil supply pump 180 of the compressor 110. In FIG. 9, the same reference numerals are assigned to the same components as those of the compressor 10 of the first embodiment. In addition, the structure similar to the compressor 10 of 1st Embodiment includes the structure where a shape and a function are the same in addition to the structure where a shape and a function correspond completely. The casing, the fixed scroll of the compression mechanism, the movable scroll, and the Oldham coupling, which are not shown, are the same as the casing 20, the fixed scroll 31, the movable scroll 32, and the Oldham coupling 34 of the compressor 10 of the first embodiment.

  The main differences between the compressor 110 of the second embodiment and the compressor 10 of the first embodiment are as follows.

  The compressor 10 of 1st Embodiment is provided with the oil pump 80 which is an example of the double pump which has the oil supply pump part 80A and the waste oil pump part 80B. On the other hand, the compressor 110 of 2nd Embodiment is provided with the oil supply pump 180 which is an example of a series pump.

(2) Detailed Configuration Hereinafter, the lower housing 170, the oil discharge path 190, and the oil supply pump 180 will be described in detail. Since the casing 20, the compression mechanism 30, the electric motor 50, the drive shaft 60, and the in-shaft oil supply path 63 have the same configuration as in the first embodiment, description thereof is omitted.

(2-1) Lower Housing The lower housing 170 is different from the lower housing 70 of the first embodiment in the following points.

  In the first embodiment, the lower housing drain oil passage 74 communicates with a lower space 78 surrounded by the recess 72 of the lower housing 70 and the oil pump 80 (see FIG. 6). On the other hand, the lower housing internal oil drainage path 174 formed in the lower housing 170 of the second embodiment communicates directly with the oil reservoir space 25 (see FIG. 9). The oil O flowing into the annular space 76 flows directly into the oil reservoir space 25 via the lower housing drain oil passage 174.

  Further, after being supplied to the sliding portion between the bearing metal 71 a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60, it flows into the lower space 178 surrounded by the recess 72 of the lower housing 170 and the oil supply pump 180. The oil O flows into the oil reservoir space 25 through a path (not shown) formed in the lower housing 170.

  Since the lower housing 170 and the lower housing 70 of the first embodiment are the same in other respects, the description thereof is omitted.

(2-2) Oil Drain Path The oil drain path 190 is an oil path that guides the oil O in the crank chamber 35 and part of the oil O after being supplied to the lower bearing portion 71 to the oil reservoir space 25. . The oil drainage path 190 mainly includes an in-shaft oil drainage path 64, an annular space 76, a lower housing drainage oil path 174, and a lower space 178 surrounded by the recess 72 of the lower housing 70 and the oil pump 80. Included (see FIG. 9).

  The oil drainage path 190 is mainly different from the oil drainage path 90 of the first embodiment in that the oil drainage path 174 and the lower space 178 in the lower housing communicate directly with the oil reservoir space 25. That is, the oil O that has flowed into the lower housing drain oil passage 174 and the lower space 178 flows into the oil reservoir space 25 without passing through the drain pump as in the first embodiment.

  About the other point, since the structure of the oil drain path 190 and the oil drain path 90 of 1st Embodiment is the same, description is abbreviate | omitted.

(2-3) Oil Pump Oil supply pump 180 is an example of a series pump. The oil supply pump 180 does not have the oil supply pump part 80A and the oil discharge pump part 80B like the oil pump 80 of the first embodiment, but functions only as an oil supply pump. The oil supply pump 180 is a pump that supplies the oil O in the oil reservoir space 25 to the in-shaft oil supply path 63.

  The oil supply pump 180 mainly includes a pump body 181, an oil pump shaft 184, an outer rotor 185, and an inner rotor 186 (see FIG. 9).

  The pump body 181 is fixed to the lower end of the lower housing 170. The pump body 181 is disposed so as to close the opening at the lower end of the recess 72 of the lower housing 70 (see FIG. 9). A suction path 181a and a rotor arrangement space 181b are formed inside the pump body 181 (see FIG. 9). The rotor arrangement space 181b is a space formed in the upper part of the pump body 181. An outer rotor 185 and an inner rotor 186 are arranged in the rotor arrangement space 181b (see FIG. 9). The suction path 181a extends upward from the lower end of the pump body 181 to the rotor arrangement space 181b (see FIG. 9). The suction path 181a is formed so that the flow path area gradually decreases upward. The pump body 181 is designed so that at least the lower end thereof is disposed in the oil O stored in the oil reservoir space 25.

  The oil pump shaft 184 is a hollow member extending in the vertical direction. An oil passage 184a extending in the vertical direction is formed inside the oil pump shaft 184 (see FIG. 9). The oil passage 184a extends through the oil pump shaft 184 from the lower end to the upper end of the oil pump shaft 184. The oil pump shaft 184 is connected to the lower part of the drive shaft 60. Specifically, the upper part of the oil pump shaft 184 is inserted into the inflow path 63 a below the drive shaft 60 and connected to the drive shaft 60. The oil pump shaft 184 is inserted through a hole (not shown) formed at the upper end of the pump body 181. The lower part of the oil pump shaft 184 is arranged inside the rotor arrangement space 181b. Specifically, the lower part of the oil pump shaft 184 is inserted into the inner rotor 186 arranged in the rotor arrangement space 181b (see FIG. 9). A D cut is provided on the outer peripheral side of the lower part of the oil pump shaft 184 so that the rotational force of the drive shaft 60 can be transmitted to the inner rotor 186. That is, the outer peripheral side cross section of the lower part of the oil pump shaft 184 is formed in a D shape. The lower part of the oil pump shaft 184 is inserted into a D-shaped holding hole (not shown) formed inside the inner rotor 186.

  The outer rotor 185 is fitted in the rotor arrangement space 181b (see FIG. 9). The outer rotor 185 is formed in an annular shape, and a plurality of outer teeth (not shown) having an arc shape (more precisely, a trochoid curve shape) are formed on the inner peripheral surface thereof. The plurality of outer teeth are arranged at equal intervals in the circumferential direction, and bulge toward the inner rotor 186 disposed inside the outer rotor 185.

  The inner rotor 186 is formed in an annular shape. The inner rotor 186 is disposed inside the outer rotor 185 (see FIG. 9). The inner rotor 186 is fitted on the outside of the oil pump shaft 184. Specifically, a D-shaped holding hole (not shown) is formed inside the inner rotor 186. By inserting the oil pump shaft 184 provided with the D cut into the holding hole, the inner rotor 186 and the oil pump shaft 184 are connected. The inner rotor 186 connected to the oil pump shaft 184 rotates integrally with the oil pump shaft 184. A plurality of inner teeth (not shown) are formed on the outer peripheral surface of the inner rotor 186 so as to correspond to the outer teeth (not shown) of the outer rotor 185. The inner rotor 186 is disposed inside the outer rotor 185 so that the inner teeth of the inner rotor 186 and the outer teeth of the outer rotor 185 are engaged with each other, so that the inner teeth of the inner rotor 186 and the outer rotor A volume chamber for conveying oil O is formed between the outer teeth of 185.

  When the drive shaft 60 rotates and the oil pump shaft 184 attached to the drive shaft 60 rotates, the inner rotor 186 of the oil supply pump 180 rotates while meshing with the outer rotor 185 so that the inside of the pump body 181 extends vertically. The oil O in the oil reservoir space 25 is sucked up from the lower end of the suction path 181a formed in the above. The oil O sucked up through the suction path 181a flows into the inflow path 63a of the in-shaft oil supply path 63 through the oil path 184a formed in the oil pump shaft 184.

(3) Oil Supply / Discharge Oil The oil O supply / discharge oil in the compressor 110 will be described. In addition, about the basic driving | operation operation | movement (compression operation of a refrigerant | coolant) of the compressor 110, since it is the same as the compressor 10 of 1st Embodiment, description is abbreviate | omitted.

  First, refueling of oil O will be described.

  When the compressor 10 is operated and the drive shaft 60 rotates, the inner rotor 186 and the outer rotor 185 of the oil supply pump 180 are engaged with each other and rotated, so that the oil O in the oil reservoir space 25 enters the pump body 181 from the lower end of the suction path 181a. Sucked into. The oil O sucked into the pump body 181 flows through the oil passage 184 a formed in the oil pump shaft 184 and flows into the inflow passage 63 a of the in-shaft oil supply passage 63.

  The subsequent supply of the oil O to each part to the compressor 110 is the same as that in the first embodiment, and thus the description thereof is omitted.

  Next, the drainage of the oil O will be described.

  The oil O in the crank chamber 35 is discharged to the oil reservoir space 25 by the differential pressure. Specifically, when the pressure in the crank chamber 35 rises, the oil O in the crank chamber 35 passes through the inflow path 67 (the in-weight inflow path 66a and the in-shaft inflow path 64a) and is discharged to the oil drain main path 64c. Is done. The oil O discharged from the inflow path 67 to the drained oil main path 64c moves downward in the drained oil main path 64c, passes through the outflow path 64d, and flows out into the annular space 76. The oil O that has flowed into the annular space 76 passes through the lower housing drain oil passage 74 and flows into the oil reservoir space 25. The oil O supplied to the sliding portion between the bearing metal 71 a of the lower bearing portion 71 and the main shaft 62 of the drive shaft 60 and flowing into the lower space 78 flows through a path (not shown) formed in the lower housing 170. And flows into the oil reservoir space 25.

(4) Features The compressor 110 according to the second embodiment also has the same features as (5-1) to (5-7) described with respect to the compressor 10 of the first embodiment. Furthermore, the compressor 110 according to the second embodiment has the following characteristics.

(4-1)
The compressor 110 according to the present embodiment includes an oil supply pump 180 as an example of a series pump. The oil pump 180 is attached to the lower part of the drive shaft 60. The oil supply pump 180 supplies the oil O in the oil reservoir space 25 to the in-shaft oil supply path 63.

  Here, oil supply to the crank chamber 35 and oil discharge from the crank chamber 35 are performed by a series of pumps. In other words, the oil O is supplied to the crank chamber 35 by the oil supply pump 180, and the oil O accumulates in the crank chamber 35. And discharged. Here, the manufacturing cost of the compressor can be suppressed as compared with the case where oil supply and oil discharge are performed by separate pumps.

<Modification>
The modification of the said embodiment is shown below. Note that a plurality of modified examples may be combined within a consistent range.

(1) Modification A
In the first embodiment, the compressor 10 includes the positive displacement oil pump 80 as an example of a dual pump, but is not limited thereto.

  For example, the oil supply pump and the oil discharge pump may not be a dual pump. However, the compressor 10 can be reduced in size by using a double pump as the oil supply pump and the oil discharge pump, rather than using separate pumps.

  Further, for example, a pump of a type other than the positive displacement type may be used for the oil supply pump and / or the oil discharge pump. For example, a differential pressure pump or a centrifugal pump may be used for the oil supply pump and / or the oil discharge pump.

  Moreover, in the said 2nd Embodiment, although the compressor 110 has the positive displacement oil pump 180, it is not limited to this. As the oil supply pump 180, a pump of a type other than the positive displacement type may be used.

(2) Modification B
In the first embodiment, the oil drain passage 90 includes the lower housing drain oil passage 74 formed in the lower housing 70, but is not limited thereto.

  For example, the outflow path 64d of the in-shaft oil discharge path 64 may be formed to open to the outer peripheral surface of the main shaft 62 below the lower bearing portion 71 (bearing metal 71a). The oil O discharged from the outflow path 64d may be configured to directly flow into the lower space 78.

(3) Modification C
In the said 1st Embodiment, although the lower space 78 is guide | induced to the oil drainage pump part 80B via the discharge port 73a, it is not limited to this. For example, the oil O in the lower space 78 may be configured such that the oil O flows into the oil discharge pump portion 80B from the insertion hole 73b formed in the thrust plate 73.

(4) Modification D
In the first embodiment, the oil O in the crank chamber 35 flows into the oil exhaust main path 64c through the in-weight inflow path 66a and the in-shaft inflow path 64a, but is not limited to this. For example, the oil O inflow path may not be formed in the balance weight 66, and the oil O may be directly introduced from the crank chamber 35 into the in-shaft inflow path 64 a formed in the drive shaft 60.

(5) Modification E
In the above embodiment, the lower shaft seal ring 42 is disposed in the lower shaft seal portion 77, but the lower shaft seal ring 42 may be omitted. Even when the upper shaft seal ring 41 is arranged only in the upper shaft seal portion 333, the oil O leakage from the lower portion of the upper housing 33 is prevented and the oil rise is suppressed as compared with the case where the upper shaft seal ring 41 is not provided. can do. However, in order to further suppress oil rising, it is preferable to dispose the lower shaft seal ring 42 also in the lower shaft seal portion 77.

(6) Modification F
In the above embodiment, the number of the upper shaft seal ring 41 and the number of the lower shaft seal rings 42 is one, but the present invention is not limited to this. If necessary, two or more upper shaft seal rings 41 and / or lower shaft seal rings 42 may be disposed in the upper shaft seal portion 333 and / or the lower shaft seal portion 77.

  The present invention is a compressor in which an oil drain path for oil in a crank chamber is formed in a drive shaft, and the compression that prevents oil leakage from the lower portion of the housing in which the crank chamber is formed and suppresses oil rising. It is useful as a machine.

DESCRIPTION OF SYMBOLS 10,110 Compressor 20 Casing 25 Oil reservoir space 30 Compression mechanism 32 Movable scroll (movable part)
33 Upper housing 35 Crank chamber 41 Upper shaft seal ring 41a Seal ring groove (groove)
42 Lower shaft seal ring 42a Seal ring groove (groove)
50 Electric motor 60 Drive shaft 61 Pin shaft part (eccentric part)
63 In-shaft oil supply route (oil supply route)
64c Oil drain main path 67 Inflow path 70 Lower housing 71 Lower bearing portion 74 Lower housing oil drain path (oil path)
76 Annular space 77 Lower shaft seal 80 Oil pump (double pump)
80A Oil supply pump (oil supply pump)
80B Oil drain pump (oil drain pump)
90, 190 Oil drainage path 180 Oil supply pump (series pump)
332 Upper bearing portion 333 Upper shaft seal portion 334 Annular space A1 Diameter of drive shaft of mounting portion of upper shaft seal ring A2 Diameter of drive shaft of mounting portion of lower shaft seal ring Oil h1 Height of upper shaft seal ring h2 Lower portion Shaft seal ring height

JP 2013-177877 A

Claims (10)

A casing (20) having an oil reservoir space (25) formed at the bottom;
An electric motor (50) housed in the casing;
A drive shaft (60) extending in the vertical direction and connected to the electric motor;
A movable part (32) connected to the drive shaft and driven by the electric motor, and a crank chamber (35) in which a connecting part between the eccentric part (61) of the drive shaft and the movable part is accommodated are formed. And an upper housing (33) having an upper bearing portion (332) disposed below the crank chamber and supporting the drive shaft and an upper shaft seal portion (333) disposed below the upper bearing portion; A compression mechanism (30) housed in the casing,
An oil supply path (63) formed inside the drive shaft for conveying oil (O) in the oil reservoir space to the crank chamber;
An oil discharge path (90) including an oil discharge main path (64c) extending in the axial direction inside the drive shaft, and an inflow path (67) communicating the oil discharge main path and the crank chamber;
An upper shaft seal ring (41) disposed in the upper shaft seal portion;
A compressor (10, 110). A lower housing (70) having a lower bearing portion (71) for supporting the drive shaft and a lower shaft seal portion (77) disposed above the lower bearing portion, and disposed below the electric motor;
A lower shaft seal ring (42) disposed in the lower shaft seal portion;
Further comprising
The compressor according to claim 1. An annular space that is formed so as to surround the drive shaft and communicates with the oil drain main path is disposed below the lower shaft seal portion,
The lower housing is formed with an oil path (74) communicating the annular space (76) and the oil reservoir space.
The compressor according to claim 2. A groove (42a) in which the lower shaft seal ring is disposed is formed in the drive shaft.
The compressor according to claim 2 or 3. The ratio of the axial height (h2) of the lower shaft seal ring to the diameter (A2) of the drive shaft of the mounting portion of the lower shaft seal ring is 0.04 or more and less than 0.07.
The compressor according to any one of claims 2 to 4. A groove (41a) in which the upper shaft seal ring is disposed is formed in the drive shaft.
The compressor according to any one of claims 1 to 5. The ratio of the axial height (h1) of the upper shaft seal ring to the drive shaft diameter (A1) of the mounting portion of the upper shaft seal ring is 0.04 or more and less than 0.07.
The compressor according to any one of claims 1 to 6. A series of pumps (180) attached to the lower part of the drive shaft and supplying oil in the oil reservoir space to the oil supply path;
Further comprising
The compressor (110) according to any one of the preceding claims. An oil supply pump (80A) for supplying oil in the oil reservoir space to the oil supply passage; and an oil discharge pump (80B) for discharging oil in the crank chamber to the oil reservoir space through the oil discharge passage. A dual pump (80) attached to the lower part of the drive shaft,
Further comprising
A compressor (10) according to any one of the preceding claims. The oil discharge pump and the oil supply pump are positive displacement pumps,
A volume of the oil pump is larger than a volume of the oil pump;
The compressor according to claim 9.

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