WO2020183605A1 - Compressor and refrigeration cycle device - Google Patents

Compressor and refrigeration cycle device Download PDF

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Publication number
WO2020183605A1
WO2020183605A1 PCT/JP2019/009961 JP2019009961W WO2020183605A1 WO 2020183605 A1 WO2020183605 A1 WO 2020183605A1 JP 2019009961 W JP2019009961 W JP 2019009961W WO 2020183605 A1 WO2020183605 A1 WO 2020183605A1
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WO
WIPO (PCT)
Prior art keywords
thrust bearing
pump case
refueling
pump
compressor
Prior art date
Application number
PCT/JP2019/009961
Other languages
French (fr)
Japanese (ja)
Inventor
龍扶 高野
ジョー ヒル
泰典 中野
佑介 上橋
Original Assignee
日立ジョンソンコントロールズ空調株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 日立ジョンソンコントロールズ空調株式会社 filed Critical 日立ジョンソンコントロールズ空調株式会社
Priority to PCT/JP2019/009961 priority Critical patent/WO2020183605A1/en
Publication of WO2020183605A1 publication Critical patent/WO2020183605A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to a compressor or the like.
  • Patent Document 1 describes a positive displacement compressor including a thrust bearing support portion that supports a thrust bearing.
  • Patent Document 2 describes a compressor provided with a damping mechanism for attenuating the vibration in the axial direction of the drive shaft in the thrust force transmission path transmitted from the drive shaft to the bearing portion via the thrust bearing member. Have been described.
  • a predetermined step is provided in the thrust bearing support portion in order to hold the thrust bearing. Since high dimensional accuracy is required for processing this step, the cost required for processing the thrust bearing support portion and the like increases. Further, in the technique described in Patent Document 1, a predetermined wall thickness for supporting the thrust bearing is required for the thrust bearing support portion, which leads to an increase in material cost and an increase in size of the compressor.
  • an object of the present invention is to provide a highly reliable compressor or the like with a simple configuration.
  • the coupling portion penetrates the pump case and the thrust bearing and is coupled to the fixing member to fix the thrust bearing, and the thrust bearing and the thrust bearing are fixed. It was decided that an axial gap was provided between the pump case and the pump case.
  • FIG. 5 is an exploded perspective view including a crankshaft, a subframe, a thrust bearing, a refueling pump, and a stepped bolt of the compressor according to the first embodiment of the present invention. It is a partially enlarged view which enlarged the Q part of FIG. 2 in the compressor which concerns on 1st Embodiment of this invention. It is a partially enlarged view of the vicinity of a refueling pump in the cross section of the compressor according to the second embodiment of the present invention.
  • FIG. 1 is a vertical sectional view of the compressor 100 according to the first embodiment.
  • the compressor 100 shown in FIG. 1 is a device that compresses a gaseous refrigerant in the compression chamber C between the fixed scroll 2a and the swivel scroll 2b.
  • the compressor 100 includes a closed container 1, a compression mechanism 2, a frame 3, a crankshaft 4 (drive shaft), a main bearing 5, a swivel bearing 6, and an electric motor 7. It has.
  • the compressor 100 includes an oldham joint 8, balancers 9a and 9b, a subframe 10 (fixing member), an auxiliary bearing 11 (radial bearing), a refueling pump 12, and a thrust bearing. 13 and a stepped bolt 14 (joint portion) are provided.
  • the closed container 1 is a shell-shaped container that houses the compression mechanism 2, the crankshaft 4, the electric motor 7, the refueling pump 12, and the like, and is substantially sealed.
  • Lubricating oil for improving the lubricity and sealing property of the compressor 100 is sealed in the closed container 1.
  • the lubricating oil is stored as an oil sump R at the bottom of the closed container 1.
  • the closed container 1 includes a cylindrical case 1a, an upper cap 1b welded to the upper part of the case 1a, and a lower cap 1c welded to the lower part of the case 1a.
  • the compression mechanism unit 2 is a mechanism that compresses the refrigerant (gas) in the compression chamber C as the crankshaft 4 rotates.
  • the compression mechanism unit 2 includes a fixed scroll 2a and a swivel scroll 2b, and is arranged in the upper space inside the closed container 1.
  • the fixed scroll 2a is a member fixed in the closed container 1, and has a base plate ia and a spiral wrap ib erected on the base plate ia.
  • the swivel scroll 2b is a member that forms a compression chamber C between the swivel scroll 2b and the fixed scroll 2a by its movement, and is arranged so as to swivel so as to face the fixed scroll 2a.
  • the swivel scroll 2b has a base plate ja, a spiral wrap jb erected on the base plate ja, and a boss portion jc fitted to the upper end portion of the crankshaft 4.
  • the wrap jb is provided on the upper side of the base plate ja
  • the boss portion jc is provided on the lower side of the base plate ja.
  • the compression chamber C is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the extension side of the lap jb of the swivel scroll 2b, respectively.
  • the frame 3 shown in FIG. 1 is a member that supports the swivel scroll 2b and fixes the main bearing 5, and is fastened to the fixed scroll 2a.
  • the frame 3 is provided with a hole (not shown) through which the crankshaft 4 is inserted.
  • the crankshaft 4 is a shaft that rotates integrally with the rotor 7b of the electric motor 7.
  • the crankshaft 4 includes a main shaft 4a, an eccentric portion 4b extending upward of the main shaft 4a, and a protrusion 4c extending downward of the main shaft 4a.
  • the spindle 4a is coaxially fixed to the rotor 7b of the electric motor 7 and rotates integrally with the rotor 7b.
  • the eccentric portion 4b is a shaft that rotates while being eccentric with respect to the main shaft 4a, and is fitted to the boss portion jc described above. Then, the eccentric portion 4b rotates while being eccentric, so that the swivel scroll 2b rotates.
  • the protrusion 4c has a cylindrical shape and extends downward from the center of the lower end of the main shaft 4a.
  • the outer diameter of the protrusion 4c is smaller than the outer diameter of the main shaft 4a.
  • An inner rotor 12a (see FIG. 2) of the refueling pump 12, which will be described later, is installed on the protrusion 4c.
  • a lubrication flow path 4d through which lubricating oil flows is provided inside the crankshaft 4.
  • the lubricating oil flowing through the oil supply flow path 4d is guided to the main bearing 5, the swivel bearing 6, the auxiliary bearing 11, and the like in addition to the compression mechanism portion 2.
  • the main bearing 5 rotatably supports the upper portion of the main shaft 4a with respect to the frame 3, and is fixed to the peripheral wall surface of the hole (reference numeral not shown) of the frame 3.
  • the swivel bearing 6 rotatably supports the eccentric portion 4b with respect to the boss portion jc, and is fixed to the inner peripheral wall of the boss portion jc.
  • a main bearing 5 and a swing bearing 6, for example, a slide bearing is used.
  • the electric motor 7 is a drive source for rotating the crankshaft 4.
  • the electric motor 7 includes a stator 7a and a rotor 7b, and is installed inside the closed container 1 (between the frame 3 and the subframe 10).
  • the stator 7a is fixed to the inner peripheral wall of the closed container 1 by press fitting or the like.
  • the rotor 7b is rotatably arranged with respect to the stator 7a.
  • the height position of the rotor 7b is slightly higher than that of the stator 7a.
  • a magnetic force is generated to move the rotor 7b downward so that the height positions of the stator 7a and the rotor 7b are aligned.
  • the crankshaft 4 presses the thrust bearing 13 downward, so that the vertical vibration of the crankshaft 4 is suppressed.
  • the Oldham joint 8 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 4b and rotates the swivel scroll 2b without rotating.
  • the oldham joint 8 is provided between the swivel scroll 2b and the frame 3.
  • the balancers 9a and 9b are members for suppressing the vibration of the compressor 100, and are provided at predetermined positions in the closed container 1.
  • the subframe 10 is a "fixing member" for fixing the auxiliary bearing 11.
  • the subframe 10 includes a cylindrical cylindrical portion 10a and three legs 10b (see also FIG. 3) extending radially outward from the cylindrical portion 10a.
  • An auxiliary bearing 11 is fixed to the inner peripheral wall of the cylindrical portion 10a.
  • the three legs 10b (see FIG. 3) are provided at intervals of about 120 ° in the circumferential direction and are integrally formed with the cylindrical portion 10a. The tips of the three legs 10b are fixed to the inner peripheral wall of the closed container 1, respectively.
  • each of these thick portions 10s is provided with one screw hole n for screwing the stepped bolt 14 described later from the lower side. That is, each screw hole n is opened downward.
  • the auxiliary bearing 11 shown in FIG. 1 is a "radial bearing” that supports the crankshaft 4 and receives a radial load from the crankshaft 4. As described above, the auxiliary bearing 11 is fixed to the inner peripheral wall of the cylindrical portion 10a by press fitting or the like. As such an auxiliary bearing 11, for example, a slide bearing is used.
  • the refueling pump 12 is a pump that sucks up lubricating oil from the oil sump R of the closed container 1 and supplies it to the refueling flow path 4d, and is installed at the lower end (end) of the crankshaft 4.
  • a refueling pump 12 for example, a trochoidal pump can be used.
  • the thrust bearing 13 is a bearing that receives a load in the axial direction (thrust direction) from the crankshaft 4, and is installed near the lower end of the crankshaft 4.
  • the stepped bolt 14 is a "joining portion" that connects the thrust bearing 13 to the subframe 10 (fixing member).
  • the suction pipe Pa is a pipe that guides the refrigerant to the compression chamber C via the suction chamber H, and is installed in the upper cap 1b of the closed container 1.
  • the gaseous refrigerant is guided to the suction chamber H via the suction pipe Pa. Then, the refrigerant is compressed by reducing the volume of the compression chambers C formed one after another as the swivel scroll 2b swivels. The compressed refrigerant is discharged into the closed container 1 through the discharge port N provided near the center of the fixed scroll 2a.
  • the discharge pipe Pb shown in FIG. 1 is a pipe through which the refrigerant discharged through the discharge port N passes, and is installed in the case 1a of the closed container 1.
  • the refrigerant discharged from the compressor 100 via the discharge pipe Pb sequentially passes through, for example, a condenser (not shown), an expansion valve (not shown), and an evaporator (not shown) in a refrigeration cycle (not shown). It circulates in a heat pump cycle) and is further returned to the compressor 100 via a suction pipe Pa.
  • FIG. 2 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100.
  • the refueling pump 12 includes an inner rotor 12a, an outer rotor 12b, a pump cover 12c, and a pump case 12d.
  • the inner rotor 12a is a rotor provided with trochoidal curved teeth on the outer peripheral side.
  • the inner rotor 12a is installed on the protrusion 4c of the crankshaft 4 and rotates integrally with the crankshaft 4.
  • the outer rotor 12b is arranged so as to surround the inner rotor 12a, and trochoidal curved teeth are provided on the inner peripheral side thereof.
  • the "lubricating section” that supplies lubricating oil to the lubricating flow path 4d as the crankshaft 4 rotates includes an inner rotor 12a and an outer rotor 12b.
  • the pump cover 12c is a cover that forms a space for pumping lubricating oil together with the inner rotor 12a and the outer rotor 12b, and is fixed to the pump case 12d.
  • the pump case 12d is a case for accommodating the inner rotor 12a and the outer rotor 12b (that is, the "refueling unit").
  • the pump case 12d includes a concave accommodating portion 121d in which the inner rotor 12a, the outer rotor 12b, and the like are accommodated, an immersion portion 122d extending downward from the accommodating portion 121d, and a flange 123d extending radially outward from the accommodating portion 121d. Is equipped with.
  • the immersion portion 122d is usually immersed in the oil sump R near the tip thereof.
  • the immersion portion 122d is provided with a flow path hd for guiding the lubricating oil into the space between the inner rotor 12a and the outer rotor 12b.
  • the flange 123d is a portion where the stepped bolt 14 is installed.
  • the flange 123d is provided with holes h4 (see FIG. 3) having a size corresponding to the intermediate portion 14b (see FIG. 3) of the stepped bolt 14 at three locations.
  • the thrust bearing 13 shown in FIG. 2 is a bearing that receives a load in the axial direction (thrust direction) from the crankshaft 4. More specifically, the thrust bearing 13 is installed at a position where there is a step between the main shaft 4a and the protrusion 4c of the crankshaft 4. Further, the thrust bearing 13 is interposed between the subframe 10 (fixing member) and the oil supply pump 12, and is fixed to the lower surface of the subframe 10 with a stepped bolt 14. The thrust bearing 13 is provided with a hole h2 through which a protrusion 4c of the crankshaft 4 (see also FIG. 3) is inserted.
  • the thrust bearing 13 has, for example, a thin disk shape, and has a configuration in which a predetermined porous sintered layer is provided on the sliding surface side of a base steel plate (called a back metal).
  • a back metal a base steel plate
  • FIG. 3 is an exploded perspective view including a crankshaft 4, a subframe 10, a thrust bearing 13, a refueling pump 12, and a stepped bolt 14.
  • a crankshaft 4 As shown in FIG. 3, one hole h2 through which the protrusion 4c at the lower end of the crankshaft 4 is inserted is provided in the central portion of the thrust bearing 13.
  • three holes h3 through which the threaded portion 14a of the stepped bolt 14 is inserted are provided at equal intervals in the circumferential direction.
  • a radial groove (not shown) for taking in lubricating oil is provided on the sliding surface (upper surface) with the crankshaft 4.
  • a predetermined groove may be provided on the sliding surface (lower end surface) of the crankshaft 4 with the thrust bearing 13.
  • the stepped bolt 14 is a "joining portion" that connects the thrust bearing 13 to the subframe 10 (fixing member).
  • the stepped bolt 14 also has a function of supporting the refueling pump 12.
  • the stepped bolt 14 includes a screw portion 14a, an intermediate portion 14b, and a head portion 14c.
  • the screw portion 14a is provided with a screw groove m (see FIG. 4) for screwing into the screw hole n of the subframe 10.
  • the intermediate portion 14b is connected to the threaded portion 14a and has a larger diameter than the threaded portion 14a.
  • the head 14c is connected to the intermediate portion 14b and has a larger diameter than the intermediate portion 14b.
  • the stepped bolt 14 penetrates the pump case 12d and the thrust bearing 13 in the axial direction, and is coupled to the subframe 10 to fix the thrust bearing 13. That is, the stepped bolt 14 is screwed into the screw hole n provided in the subframe 10 (fixing member) from below.
  • FIG. 4 is a partially enlarged view of the Q portion shown in FIG. 2.
  • these gaps GD and GA are shown longer than they actually are in order to make it easier to understand the radial gap GD and the axial gap GA.
  • the diameter of the intermediate portion 14b of the stepped bolt 14 is larger than the diameter of the hole h3 of the thrust bearing 13, while being smaller than the diameter of the hole h4 of the pump case 12d.
  • the intermediate portion 14b is pressed against the lower surface of the thrust bearing 13, and the upper surface of the intermediate portion 14b and the thrust bearing are pressed against each other. It is in direct contact with the lower surface of 13. That is, the thrust bearing 13 is sandwiched and fixed by the intermediate portion 14b of the stepped bolt 14 and the subframe 10 (fixing member). Further, three stepped bolts 14 are installed corresponding to the three screw holes n of the subframe 10 (see FIG. 3). As a result, the movement of the thrust bearing 13 in the circumferential direction is restricted.
  • the diameter of the hole h4 in which the intermediate portion 14b of the stepped bolt 14 is installed is slightly larger than the diameter of the intermediate portion 14b. Therefore, in the state where the stepped bolt 14 is installed, a predetermined radial gap GD is provided between the intermediate portion 14b and the peripheral wall surface of the hole h4 of the pump case 12d.
  • the wall thickness (thickness in the vertical direction) of the flange 123d around the intermediate portion 14b is slightly thinner than the wall thickness (thickness in the vertical direction) of the intermediate portion 14b. Therefore, in the state where the stepped bolt 14 is installed, a predetermined axial gap GA is provided between the upper surface of the flange 123d of the pump case 12d and the thrust bearing 13.
  • a radial gap GD is provided between the intermediate portion 14b of the stepped bolt 14 and the pump case 12d, while an axial gap GA is provided between the thrust bearing 13 and the pump case 12d.
  • the refueling pump 12 is supported (suspended) by the head 14c of the three stepped bolts 14 (see FIG. 3). That is, the stepped bolt 14 is in direct contact with a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4).
  • the dimension L1 of the radial gap GD between the intermediate portion 14b of the stepped bolt 14 and the pump case 12d is the middle within the range in which the radial gap is formed. It is preferable that the shaft diameter of the portion 14b (joining portion) is 4% or more and 13% or less of the hole diameter of the hole h4 of the pump case 12d in the range of forming the above-mentioned radial gap. As a result, the runout of the crankshaft 4 is appropriately absorbed.
  • the dimension L2 of the axial clearance GA between the thrust bearing 13 and the pump case 12d (the length of the clearance GA: see FIG. 4) is the intermediate portion 14b (joint portion) in the range in which the axial clearance is formed. ) In the axial direction, or 1% or more and 6% or less of the vertical wall thickness of the flange 123d of the pump case 12d around the above-mentioned axial gap. As a result, the runout of the crankshaft 4 is appropriately absorbed.
  • the inner diameter of the cylindrical portion 10a is constant in the vicinity of the thrust bearing 13 in the axial direction of the cylindrical portion 10a of the subframe 10 (fixing member). As a result, high dimensional accuracy is rarely required when processing the subframe 10, so that the man-hours and costs required for processing can be reduced.
  • a step is provided in the lower part of the subframe 10 (near the thrust bearing 13) according to the size of the thrust bearing 13, and the rotation of the thrust bearing 13 in the circumferential direction is regulated without using screws.
  • the subframe 10 is formed on the surface, high processing accuracy is required.
  • the inner diameter of the cylindrical portion 10a is constant in the axial direction, and the rotation of the thrust bearing 13 in the circumferential direction is regulated by the three stepped bolts 14. (See Fig. 3). Therefore, the processing cost of the subframe 10 can be reduced.
  • the thrust bearing 13 is sandwiched in the vertical direction between the intermediate portion 14b of the stepped bolt 14 and the subframe 10 and is firmly fixed.
  • the three stepped bolts 14 also serve to prevent the thrust bearing 13 from rotating. Therefore, it is not necessary to adopt a detent shape such as a so-called D-cut shape for the thrust bearing 13, and it is not necessary to perform high-precision processing that requires a strict dimensional tolerance.
  • the thrust bearing 13 one with an inexpensive back metal in which a porous sintered layer or the like is provided only on one surface on the side receiving an axial load from the crankshaft 4 can be adopted.
  • the thrust bearing 13 is sandwiched between the intermediate portion 14b of the stepped bolt 14 and the subframe 10 to be firmly fixed, while the intermediate portion 14b is provided with a radial gap GD and an axial gap GA. Has been done. As a result, it is possible to prevent an excessive load from being applied to the inner rotor 12a and the outer rotor 12b of the refueling pump 12 when the crankshaft 4 swings around. As a result, it is possible to prevent problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12.
  • the thrust bearing 13 is arranged under the subframe 10. Therefore, it is not necessary to provide a predetermined step for holding the thrust bearing 13 in the subframe 10 or to secure a predetermined wall thickness to support the load of the thrust bearing 13. Therefore, it is possible to suppress an increase in the size of the subframe 10 and an increase in material cost.
  • the thrust bearing 13 is provided on the lower side of the crankshaft 4. Therefore, for example, as compared with a configuration in which a large-diameter flange portion (not shown) is provided at a predetermined position on the crankshaft 4 and a thrust bearing 13 is installed on the flange portion, the size of the crankshaft 4 is increased and the material cost is increased. Can be suppressed. Further, since the stepped bolt 14 serves both of fixing the thrust bearing 13 and supporting the refueling pump 12, the number of parts can be reduced.
  • the compressor 100A (see FIG. 5) according to the second embodiment has a bolt 15A (see FIG. 5) and a spacer 16A (see FIG. 5) in place of the stepped bolt 14 (see FIG. 2) described in the first embodiment. ) Is provided. Others are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.
  • FIG. 5 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100A according to the second embodiment.
  • the compressor 100A in addition to the crankshaft 4 (drive shaft) and the subframe 10 (fixing member), the auxiliary bearing 11 (radial bearing), the oil supply pump 12, the thrust bearing 13, and the thrust bearing 13 are included.
  • a bolt 15A (joint portion) and a spacer 16A (joint portion) are provided.
  • the bolt 15A has a screw portion 151A provided with a screw groove to be screwed into a screw hole of the subframe 10, and a head portion 152A having a diameter larger than that of the screw portion 151A.
  • the spacer 16A is a member (collar) that maintains a vertical distance between the head portion 152A of the bolt 15A and the thrust bearing 13, and has a cylindrical shape.
  • the axial length of the spacer 16A is longer than the wall thickness around the spacer 16A in the pump case 12d. Further, the threaded portion 151A of the bolt 15A is inserted through the spacer 16A.
  • the thrust bearing 13 is sandwiched and fixed by the spacer 16A and the subframe 10.
  • the diameter of the head 152A of the bolt 15A is larger than the outer diameter of the spacer 16A. Further, a radial gap is provided between the spacer 16A and the pump case 12d, while an axial gap is provided between the thrust bearing 13 and the pump case 12d.
  • the refueling pump 12 is supported by the head 152A of the bolt 15A. That is, the bolt 15A is in direct contact with a part (lower surface) of the pump case 12d.
  • the dimension of the radial gap between the spacer 16A and the pump case 12d is preferably 4% or more and 13% or less of the diameter of the spacer 16A (or the diameter of the hole h4 of the pump case 12d).
  • the dimension of the axial gap between the thrust bearing 13 and the pump case 12d is 1% or more and 6% or less of the axial length of the spacer 16A (or the vertical wall thickness of the flange 123d). It is preferable to have. As a result, the runout of the crankshaft 4 is appropriately absorbed.
  • the thrust bearing 13 is sandwiched between the spacer 16A and the subframe 10 and firmly fixed, while the spacer 16A is provided with gaps in the radial and axial directions. ..
  • problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12 can be prevented.
  • FIG. 6 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100B according to the third embodiment of the present invention.
  • the compressor 100B shown in FIG. 6 is the first except that the diameter of the head 152B of the bolt 15B (joining portion) is relatively small and the spacer 16B (joining portion) has the flange portion 162B. Since it is the same as that of the second embodiment (see FIG. 5), detailed description thereof will be omitted.
  • the spacer 16B includes a cylindrical cylindrical portion 161B and a flange portion 162B extending radially outward from the lower end portion (one end portion in the axial direction) of the cylindrical portion 161B.
  • the axial length of the cylindrical portion 161B is longer than the wall thickness around the cylindrical portion 161B in the pump case 12d. Further, the threaded portion 151B of the bolt 15B is inserted through the spacer 16B so that the head portion 152B of the bolt 15B abuts on the flange portion 162B of the spacer 16B.
  • the thrust bearing 13 is sandwiched and fixed by the spacer 16B and the subframe 10.
  • the diameter of the head 152B of the bolt 15B is larger than the inner diameter of the spacer 16B. Further, a radial gap is provided between the spacer 16B and the pump case 12d, while an axial gap is provided between the thrust bearing 13 and the pump case 12d.
  • the refueling pump 12 is supported by the head portion 152B of the bolt 15B via the flange portion 162B of the spacer 16B. That is, the bolt 15B is in direct contact with a part (lower surface) of the pump case 12d.
  • the dimension of the radial gap between the spacer 16B and the pump case 12d is preferably 4% or more and 13% or less of the diameter of the spacer 16B (or the diameter of the hole h4 of the pump case 12d).
  • the dimension of the axial gap between the thrust bearing 13 and the pump case 12d is 1% or more of the axial length of the cylindrical portion 161B of the spacer 16B (or the vertical wall thickness of the flange 123d). It is preferably 6% or less.
  • the thrust bearing 13 is sandwiched between the spacer 16B and the subframe 10 and firmly fixed, while the spacer 16B is provided with gaps in the radial and axial directions. ..
  • problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12 can be prevented.
  • FIG. 7 is a block diagram of the refrigerant circuit K of the air conditioner W.
  • the solid line arrow in FIG. 7 indicates the flow of the refrigerant during the heating operation. Further, the broken line arrow in FIG. 7 indicates the flow of the refrigerant during the cooling operation.
  • the air conditioner W is a device that performs air conditioning such as cooling and heating. As shown in FIG. 7, the air conditioner W includes a compressor 100, an outdoor heat exchanger Eo, an outdoor fan Fo, an expansion valve Ve, a four-way valve Vf, an indoor heat exchanger Ei, and an indoor fan Fi. And have.
  • the compressor 100, the outdoor heat exchanger Eo, the outdoor fan Fo, the expansion valve Ve, and the four-way valve Vf are provided in the outdoor unit Wo.
  • the indoor heat exchanger Ei and the indoor fan Fi are provided in the indoor unit Wi.
  • the compressor 100 is a device that compresses a gaseous refrigerant, and has the same configuration as that of the first embodiment (see FIG. 1).
  • the outdoor heat exchanger Eo is a heat exchanger in which heat exchange is performed between the refrigerant flowing through the heat transfer tube (not shown) and the outside air sent from the outdoor fan Fo.
  • the outdoor fan Fo is a fan that sends outside air to the outdoor heat exchanger Eo.
  • the outdoor fan Fo includes an outdoor fan motor Mo which is a drive source, and is installed near the outdoor heat exchanger Eo.
  • the indoor heat exchanger Ei is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the indoor air (air in the air-conditioned space) sent from the indoor fan Fi.
  • the indoor fan Fi is a fan that sends indoor air to the indoor heat exchanger Ei.
  • the indoor fan Fi includes an indoor fan motor Mi as a drive source, and is installed in the vicinity of the indoor heat exchanger Ei.
  • the expansion valve Ve is a valve that reduces the pressure of the refrigerant condensed by the "condenser" (one of the outdoor heat exchanger Eo and the indoor heat exchanger Ei).
  • the refrigerant decompressed by the expansion valve Ve is guided to an "evaporator" (the other of the outdoor heat exchanger Eo and the indoor heat exchanger Ei).
  • the four-way valve Vf is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner W. For example, during cooling operation (see the dashed arrow in FIG. 7), the compressor 100, the outdoor heat exchanger Eo (condenser), the expansion valve Ve, and the indoor heat exchanger Ei (evaporator) are the four-way valve Vf. In the refrigerant circuit K which is sequentially connected via the above, the refrigerant circulates in the refrigeration cycle.
  • the compressor 100, the indoor heat exchanger Ei (condenser), the expansion valve Ve, and the outdoor heat exchanger Eo (evaporator) are the four-way valve Vf.
  • the refrigerant circuit K which is sequentially connected via the above, the refrigerant circulates in the refrigeration cycle.
  • the refrigerant circulates in sequence through the compressor 100, the "condenser", the expansion valve Ve, and the “evaporator”.
  • Devices such as the compressor 100, the outdoor fan Fo, the expansion valve Ve, and the indoor fan Fi are driven based on a command from a control device (not shown).
  • the configuration in which the head portion 14c of the stepped bolt 14 (joining portion) is in direct contact with a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4) has been described. (See FIG. 4), but not limited to this.
  • a washer (washer: not shown) may be interposed between the head 14c of the stepped bolt 14 and a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4).
  • each embodiment can be applied to a configuration in which the compressor 100 is installed horizontally.
  • the case where the compressor 100 is a scroll type compressor has been described, but the present invention is not limited to this. That is, each embodiment can be applied to another type of compressor such as a rotary type compressor.
  • each embodiment can be combined as appropriate.
  • a compressor 100A second embodiment
  • a spacer 16A see FIG. 5
  • the third embodiment and the fourth embodiment may be combined.
  • the air conditioner W (refrigeration cycle device: see FIG. 7) including the compressor 100 has been described, but the present invention is not limited to this.
  • the fourth embodiment can be applied to other "refrigeration cycle devices" such as refrigerators, water heaters, air-conditioning hot water supply devices, and chillers.
  • each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the configurations described. Further, it is possible to appropriately add / delete / replace other configurations with respect to a part of the configurations of each embodiment.
  • the above-mentioned mechanism and configuration show what is considered necessary for explanation, and do not necessarily show all the mechanisms and configurations in the product.

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Abstract

Provided is a compressor and the like with a simple configuration and high reliability. A stepped bolt (14) of this compressor (100) is inserted through a pump case (12d) and a thrust bearing (13) to be engaged with a threaded hole provided in a subframe (10). The thrust bearing (13) is secured by being sandwiched between the stepped bolt (14) and the subframe (10). A radial gap is provided between the stepped bolt (14) and pump case (12d), an axial gap is provided between the thrust bearing (13) and the pump case (12d), and an oil feed pump (12) is supported by the stepped bolt (14).

Description

圧縮機及び冷凍サイクル装置Compressor and refrigeration cycle equipment
　本発明は、圧縮機等に関する。 The present invention relates to a compressor or the like.
　圧縮機のクランク軸から軸方向（スラスト方向）の荷重を受けるスラスト軸受の固定構造に関して、例えば、特許文献１，２に記載の技術が知られている。
　すなわち、特許文献１に、スラスト軸受を支持するスラスト軸受支持部を備える容積型圧縮機について記載されている。 Regarding the fixed structure of a thrust bearing that receives a load in the axial direction (thrust direction) from the crankshaft of a compressor, for example, the techniques described in Patent Documents 1 and 2 are known.
That is, Patent Document 1 describes a positive displacement compressor including a thrust bearing support portion that supports a thrust bearing.
　また、特許文献２には、駆動軸からスラスト軸受部材を経由して軸受部へ伝達されるスラスト力の伝達経路に、駆動軸の軸方向の振動を減衰させる減衰機構が設けられた圧縮機について記載されている。 Further, Patent Document 2 describes a compressor provided with a damping mechanism for attenuating the vibration in the axial direction of the drive shaft in the thrust force transmission path transmitted from the drive shaft to the bearing portion via the thrust bearing member. Have been described.
特開２００７－２７０６９６号公報JP-A-2007-270696 特開２０１２－９７５８１号公報Japanese Unexamined Patent Publication No. 2012-97581
　特許文献１に記載の技術では、スラスト軸受を保持するために、スラスト軸受支持部に所定の段差が設けられる。この段差の加工には高い寸法精度が求められるため、スラスト軸受支持部等の加工に要するコストが高くなる。さらに、特許文献１に記載の技術では、スラスト軸受を支えるための所定の肉厚がスラスト軸受支持部に必要になるため、材料費の増加や圧縮機の大型化を招く。 In the technique described in Patent Document 1, a predetermined step is provided in the thrust bearing support portion in order to hold the thrust bearing. Since high dimensional accuracy is required for processing this step, the cost required for processing the thrust bearing support portion and the like increases. Further, in the technique described in Patent Document 1, a predetermined wall thickness for supporting the thrust bearing is required for the thrust bearing support portion, which leads to an increase in material cost and an increase in size of the compressor.
　また、特許文献２に記載の技術では、駆動軸の軸方向の振動を減衰させる減衰機構が設けられるため、部品点数や製造コストの増加を招き、また、組立工程の複雑化を招く。さらに、特許文献２に記載の技術では、ゴム製である減衰機構の弾性変形に伴い、ラジアル軸受に対する駆動軸の片当たり（荷重の片寄り）が生じやすい。このように特許文献１，２に記載の技術は、圧縮機の構成の簡素化や信頼性の面において改善の余地がある。 Further, in the technique described in Patent Document 2, since a damping mechanism for damping the vibration in the axial direction of the drive shaft is provided, the number of parts and the manufacturing cost are increased, and the assembly process is complicated. Further, in the technique described in Patent Document 2, one-sided contact (shifting of the load) of the drive shaft with respect to the radial bearing is likely to occur due to the elastic deformation of the damping mechanism made of rubber. As described above, the techniques described in Patent Documents 1 and 2 have room for improvement in terms of simplification and reliability of the compressor configuration.
　そこで、本発明は、簡素な構成で信頼性の高い圧縮機等を提供することを課題とする。 Therefore, an object of the present invention is to provide a highly reliable compressor or the like with a simple configuration.
　前記した課題を解決するために、本発明に係る圧縮機は、結合部が、ポンプケース及びスラスト軸受を貫通し、固定部材に結合されて前記スラスト軸受を固定しており、前記スラスト軸受と前記ポンプケースとの間には軸方向の隙間が設けられていることとした。 In order to solve the above-mentioned problems, in the compressor according to the present invention, the coupling portion penetrates the pump case and the thrust bearing and is coupled to the fixing member to fix the thrust bearing, and the thrust bearing and the thrust bearing are fixed. It was decided that an axial gap was provided between the pump case and the pump case.
　本発明によれば、簡素な構成で信頼性の高い圧縮機等を提供できる。 According to the present invention, it is possible to provide a highly reliable compressor or the like with a simple configuration.
本発明の第１実施形態に係る圧縮機の縦断面図である。It is a vertical sectional view of the compressor which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係る圧縮機の断面における給油ポンプ付近の部分拡大図である。It is a partially enlarged view of the vicinity of a refueling pump in the cross section of the compressor according to the first embodiment of the present invention. 本発明の第１実施形態に係る圧縮機のクランク軸、サブフレーム、スラスト軸受、給油ポンプ、及び段付きボルトを含む分解斜視図である。FIG. 5 is an exploded perspective view including a crankshaft, a subframe, a thrust bearing, a refueling pump, and a stepped bolt of the compressor according to the first embodiment of the present invention. 本発明の第１実施形態に係る圧縮機において、図２のＱ部を拡大した部分拡大図である。It is a partially enlarged view which enlarged the Q part of FIG. 2 in the compressor which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係る圧縮機の断面における給油ポンプ付近の部分拡大図である。It is a partially enlarged view of the vicinity of a refueling pump in the cross section of the compressor according to the second embodiment of the present invention. 本発明の第３実施形態に係る圧縮機の断面における給油ポンプ付近の部分拡大図である。It is a partially enlarged view of the vicinity of a refueling pump in the cross section of the compressor according to the third embodiment of the present invention. 本発明の第４実施形態に係る空気調和機の冷媒回路の構成図である。It is a block diagram of the refrigerant circuit of the air conditioner which concerns on 4th Embodiment of this invention.
≪第１実施形態≫
　以下では、一例として、クランク軸４（図１参照）に給油ポンプ１２が設置されたスクロール式の圧縮機１００について説明する。 << First Embodiment >>
In the following, as an example, the scroll type compressor 100 in which the refueling pump 12 is installed on the crankshaft 4 (see FIG. 1) will be described.
＜圧縮機の構成＞
　図１は、第１実施形態に係る圧縮機１００の縦断面図である。
　図１に示す圧縮機１００は、固定スクロール２ａと旋回スクロール２ｂとの間の圧縮室Ｃにおいてガス状の冷媒を圧縮する機器である。
　図１に示すように、圧縮機１００は、密閉容器１と、圧縮機構部２と、フレーム３と、クランク軸４（駆動軸）と、主軸受５と、旋回軸受６と、電動機７と、を備えている。また、圧縮機１００は、前記した構成の他に、オルダム継手８と、バランサ９ａ，９ｂと、サブフレーム１０（固定部材）と、副軸受１１（ラジアル軸受）と、給油ポンプ１２と、スラスト軸受１３と、段付きボルト１４（結合部）と、を備えている。 <Compressor configuration>
FIG. 1 is a vertical sectional view of the compressor 100 according to the first embodiment.
The compressor 100 shown in FIG. 1 is a device that compresses a gaseous refrigerant in the compression chamber C between the fixed scroll 2a and the swivel scroll 2b.
As shown in FIG. 1, the compressor 100 includes a closed container 1, a compression mechanism 2, a frame 3, a crankshaft 4 (drive shaft), a main bearing 5, a swivel bearing 6, and an electric motor 7. It has. Further, in addition to the above-described configuration, the compressor 100 includes an oldham joint 8, balancers 9a and 9b, a subframe 10 (fixing member), an auxiliary bearing 11 (radial bearing), a refueling pump 12, and a thrust bearing. 13 and a stepped bolt 14 (joint portion) are provided.
　密閉容器１は、圧縮機構部２、クランク軸４、電動機７、給油ポンプ１２等を収容する殻状の容器であり、略密閉されている。この密閉容器１には、圧縮機１００の潤滑性やシール性を高めるための潤滑油が封入されている。なお、潤滑油は、密閉容器１の底部に油溜りＲとして貯留されている。密閉容器１は、円筒状のケース１ａと、このケース１ａの上部に溶接された上キャップ１ｂと、ケース１ａの下部に溶接された下キャップ１ｃと、を備えている。 The closed container 1 is a shell-shaped container that houses the compression mechanism 2, the crankshaft 4, the electric motor 7, the refueling pump 12, and the like, and is substantially sealed. Lubricating oil for improving the lubricity and sealing property of the compressor 100 is sealed in the closed container 1. The lubricating oil is stored as an oil sump R at the bottom of the closed container 1. The closed container 1 includes a cylindrical case 1a, an upper cap 1b welded to the upper part of the case 1a, and a lower cap 1c welded to the lower part of the case 1a.
　圧縮機構部２は、クランク軸４の回転に伴って、圧縮室Ｃで冷媒（ガス）を圧縮する機構である。圧縮機構部２は、固定スクロール２ａと、旋回スクロール２ｂと、を備え、密閉容器１内の上部空間に配置されている。 The compression mechanism unit 2 is a mechanism that compresses the refrigerant (gas) in the compression chamber C as the crankshaft 4 rotates. The compression mechanism unit 2 includes a fixed scroll 2a and a swivel scroll 2b, and is arranged in the upper space inside the closed container 1.
　固定スクロール２ａは、密閉容器１内に固定される部材であり、台板ｉａと、この台板ｉａに立設される渦巻状のラップｉｂと、を有している。
　旋回スクロール２ｂは、その移動によって固定スクロール２ａとの間に圧縮室Ｃを形成する部材であり、固定スクロール２ａに対向して旋回自在に配置されている。 The fixed scroll 2a is a member fixed in the closed container 1, and has a base plate ia and a spiral wrap ib erected on the base plate ia.
The swivel scroll 2b is a member that forms a compression chamber C between the swivel scroll 2b and the fixed scroll 2a by its movement, and is arranged so as to swivel so as to face the fixed scroll 2a.
　旋回スクロール２ｂは、台板ｊａと、この台板ｊａに立設される渦巻状のラップｊｂと、クランク軸４の上端部に嵌合するボス部ｊｃと、を有している。図１の例では、台板ｊａの上側にラップｊｂが設けられる一方、台板ｊａの下側にボス部ｊｃが設けられている。 The swivel scroll 2b has a base plate ja, a spiral wrap jb erected on the base plate ja, and a boss portion jc fitted to the upper end portion of the crankshaft 4. In the example of FIG. 1, the wrap jb is provided on the upper side of the base plate ja, while the boss portion jc is provided on the lower side of the base plate ja.
　そして、固定スクロール２ａのラップｉｂと、旋回スクロール２ｂのラップｊｂと、が噛み合うことで、ラップｉｂ，ｊｂの間に圧縮室Ｃが形成される。前記した圧縮室Ｃは、ガス状の冷媒を圧縮する空間であり、旋回スクロール２ｂのラップｊｂの外線側・内線側にそれぞれ形成される。 Then, the lap ib of the fixed scroll 2a and the lap jb of the swivel scroll 2b mesh with each other to form a compression chamber C between the laps ib and jb. The compression chamber C is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the extension side of the lap jb of the swivel scroll 2b, respectively.
　図１に示すフレーム３は、旋回スクロール２ｂを支持したり、主軸受５を固定したりする部材であり、固定スクロール２ａに締結されている。フレーム３には、クランク軸４が挿通される孔（符号は図示せず）が設けられている。
　クランク軸４は、電動機７の回転子７ｂと一体で回転する軸である。図１に示すように、クランク軸４は、主軸４ａと、この主軸４ａの上側に延びる偏心部４ｂと、主軸４ａの下側に延びる突起４ｃと、を備えている。 The frame 3 shown in FIG. 1 is a member that supports the swivel scroll 2b and fixes the main bearing 5, and is fastened to the fixed scroll 2a. The frame 3 is provided with a hole (not shown) through which the crankshaft 4 is inserted.
The crankshaft 4 is a shaft that rotates integrally with the rotor 7b of the electric motor 7. As shown in FIG. 1, the crankshaft 4 includes a main shaft 4a, an eccentric portion 4b extending upward of the main shaft 4a, and a protrusion 4c extending downward of the main shaft 4a.
　主軸４ａは、電動機７の回転子７ｂに同軸で固定され、この回転子７ｂと一体で回転する。偏心部４ｂは、主軸４ａに対して偏心しながら回転する軸であり、前記したボス部ｊｃに嵌合している。そして、偏心部４ｂが偏心しながら回転することによって、旋回スクロール２ｂが旋回するようになっている。 The spindle 4a is coaxially fixed to the rotor 7b of the electric motor 7 and rotates integrally with the rotor 7b. The eccentric portion 4b is a shaft that rotates while being eccentric with respect to the main shaft 4a, and is fitted to the boss portion jc described above. Then, the eccentric portion 4b rotates while being eccentric, so that the swivel scroll 2b rotates.
　突起４ｃは、円筒状を呈し、主軸４ａの下端部中央から下側に延びている。なお、突起４ｃの外径は、主軸４ａの外径よりも小さい。突起４ｃには、後記する給油ポンプ１２のインナロータ１２ａ（図２参照）が設置されている。 The protrusion 4c has a cylindrical shape and extends downward from the center of the lower end of the main shaft 4a. The outer diameter of the protrusion 4c is smaller than the outer diameter of the main shaft 4a. An inner rotor 12a (see FIG. 2) of the refueling pump 12, which will be described later, is installed on the protrusion 4c.
　クランク軸４の内部には、潤滑油が通流する給油流路４ｄが設けられている。給油流路４ｄを介して通流する潤滑油は、圧縮機構部２の他、主軸受５や旋回軸受６、副軸受１１等に導かれる。 Inside the crankshaft 4, a lubrication flow path 4d through which lubricating oil flows is provided. The lubricating oil flowing through the oil supply flow path 4d is guided to the main bearing 5, the swivel bearing 6, the auxiliary bearing 11, and the like in addition to the compression mechanism portion 2.
　主軸受５は、フレーム３に対して主軸４ａの上部を回転自在に軸支するものであり、フレーム３の孔（符号は図示せず）の周壁面に固定されている。
　旋回軸受６は、ボス部ｊｃに対して偏心部４ｂを回転自在に軸支するものであり、ボス部ｊｃの内周壁に固定されている。このような主軸受５や旋回軸受６として、例えば、滑り軸受が用いられる。 The main bearing 5 rotatably supports the upper portion of the main shaft 4a with respect to the frame 3, and is fixed to the peripheral wall surface of the hole (reference numeral not shown) of the frame 3.
The swivel bearing 6 rotatably supports the eccentric portion 4b with respect to the boss portion jc, and is fixed to the inner peripheral wall of the boss portion jc. As such a main bearing 5 and a swing bearing 6, for example, a slide bearing is used.
　電動機７は、クランク軸４を回転させる駆動源である。この電動機７は、固定子７ａと、回転子７ｂと、を備え、密閉容器１の内部（フレーム３とサブフレーム１０との間）に設置されている。固定子７ａは、圧入等によって密閉容器１の内周壁に固定されている。回転子７ｂは、固定子７ａに対して回転自在に配置されている。 The electric motor 7 is a drive source for rotating the crankshaft 4. The electric motor 7 includes a stator 7a and a rotor 7b, and is installed inside the closed container 1 (between the frame 3 and the subframe 10). The stator 7a is fixed to the inner peripheral wall of the closed container 1 by press fitting or the like. The rotor 7b is rotatably arranged with respect to the stator 7a.
　ちなみに、図１の例では、固定子７ａよりも回転子７ｂのほうが、高さ位置が若干高くなっている。これによって、固定子７ａと回転子７ｂとの高さ位置を揃えるように回転子７ｂを下向きに移動させる磁力が発生する。その結果、クランク軸４がスラスト軸受１３を下向きに押圧するため、クランク軸４の上下方向の振動が抑制される。 By the way, in the example of FIG. 1, the height position of the rotor 7b is slightly higher than that of the stator 7a. As a result, a magnetic force is generated to move the rotor 7b downward so that the height positions of the stator 7a and the rotor 7b are aligned. As a result, the crankshaft 4 presses the thrust bearing 13 downward, so that the vertical vibration of the crankshaft 4 is suppressed.
　オルダム継手８は、偏心部４ｂの偏心回転を受けて、旋回スクロール２ｂを自転させることなく旋回させる輪状部材である。このオルダム継手８は、旋回スクロール２ｂとフレーム３との間に設けられている。
　バランサ９ａ，９ｂは、圧縮機１００の振動を抑制するための部材であり、密閉容器１内の所定箇所に設けられている。 The Oldham joint 8 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 4b and rotates the swivel scroll 2b without rotating. The oldham joint 8 is provided between the swivel scroll 2b and the frame 3.
The balancers 9a and 9b are members for suppressing the vibration of the compressor 100, and are provided at predetermined positions in the closed container 1.
　サブフレーム１０は、副軸受１１を固定する「固定部材」である。サブフレーム１０は、円筒状の円筒部１０ａと、この円筒部１０ａから径方向外側に延びる３本の脚１０ｂ（図３も参照）と、を備えている。円筒部１０ａの内周壁には、副軸受１１が固定されている。３本の脚１０ｂ（図３参照）は、周方向において約１２０°間隔で設けられ、円筒部１０ａと一体形成されている。３本の脚１０ｂの先端は、それぞれ、密閉容器１の内周壁に固定されている。 The subframe 10 is a "fixing member" for fixing the auxiliary bearing 11. The subframe 10 includes a cylindrical cylindrical portion 10a and three legs 10b (see also FIG. 3) extending radially outward from the cylindrical portion 10a. An auxiliary bearing 11 is fixed to the inner peripheral wall of the cylindrical portion 10a. The three legs 10b (see FIG. 3) are provided at intervals of about 120 ° in the circumferential direction and are integrally formed with the cylindrical portion 10a. The tips of the three legs 10b are fixed to the inner peripheral wall of the closed container 1, respectively.
　円筒部１０ａにおいて、３本の脚１０ｂの直下の部分１０ｓ（図３参照）は、それぞれ、肉厚に形成されている。これらの肉厚の部分１０ｓには、後記する段付きボルト１４を下側から螺合するためのネジ穴ｎがひとつずつ設けられている。すなわち、それぞれのネジ穴ｎは、下側に開口している。 In the cylindrical portion 10a, the portions 10s (see FIG. 3) directly below the three legs 10b are each formed to be thick. Each of these thick portions 10s is provided with one screw hole n for screwing the stepped bolt 14 described later from the lower side. That is, each screw hole n is opened downward.
　図１に示す副軸受１１は、クランク軸４を軸支し、クランク軸４から径方向の荷重を受ける「ラジアル軸受」である。副軸受１１は、前記したように、円筒部１０ａの内周壁に圧入等で固定されている。このような副軸受１１として、例えば、滑り軸受が用いられる。 The auxiliary bearing 11 shown in FIG. 1 is a "radial bearing" that supports the crankshaft 4 and receives a radial load from the crankshaft 4. As described above, the auxiliary bearing 11 is fixed to the inner peripheral wall of the cylindrical portion 10a by press fitting or the like. As such an auxiliary bearing 11, for example, a slide bearing is used.
　給油ポンプ１２は、密閉容器１の油溜りＲから潤滑油を吸い上げて、給油流路４ｄに供給するポンプであり、クランク軸４の下端部（端部）に設置されている。このような給油ポンプ１２として、例えば、トロコイドポンプを用いることができる。 The refueling pump 12 is a pump that sucks up lubricating oil from the oil sump R of the closed container 1 and supplies it to the refueling flow path 4d, and is installed at the lower end (end) of the crankshaft 4. As such a refueling pump 12, for example, a trochoidal pump can be used.
　スラスト軸受１３は、クランク軸４から軸方向（スラスト方向）の荷重を受ける軸受であり、クランク軸４の下端付近に設置されている。
　段付きボルト１４は、スラスト軸受１３をサブフレーム１０（固定部材）に結合する「結合部」である。 The thrust bearing 13 is a bearing that receives a load in the axial direction (thrust direction) from the crankshaft 4, and is installed near the lower end of the crankshaft 4.
The stepped bolt 14 is a "joining portion" that connects the thrust bearing 13 to the subframe 10 (fixing member).
　吸込パイプＰａは、吸込室Ｈを介して圧縮室Ｃに冷媒を導く管であり、密閉容器１の上キャップ１ｂに設置されている。 The suction pipe Pa is a pipe that guides the refrigerant to the compression chamber C via the suction chamber H, and is installed in the upper cap 1b of the closed container 1.
　電動機７の駆動によって旋回スクロール２ｂが旋回すると、吸込パイプＰａを介してガス状の冷媒が吸込室Ｈに導かれる。そして、旋回スクロール２ｂの旋回に伴って次々に形成される圧縮室Ｃの容積が縮小することで、冷媒が圧縮される。圧縮された冷媒は、固定スクロール２ａの中心付近に設けられた吐出口Ｎを介して、密閉容器１内に吐出される。 When the swivel scroll 2b is swiveled by the drive of the electric motor 7, the gaseous refrigerant is guided to the suction chamber H via the suction pipe Pa. Then, the refrigerant is compressed by reducing the volume of the compression chambers C formed one after another as the swivel scroll 2b swivels. The compressed refrigerant is discharged into the closed container 1 through the discharge port N provided near the center of the fixed scroll 2a.
　図１に示す吐出パイプＰｂは、吐出口Ｎを介して吐出された冷媒が通流する管であり、密閉容器１のケース１ａに設置されている。吐出パイプＰｂを介して圧縮機１００から吐出された冷媒は、例えば、凝縮器（図示せず）、膨張弁（図示せず）、及び蒸発器（図示せず）を順次に介して冷凍サイクル（ヒートポンプサイクル）で循環し、さらに、吸込パイプＰａを介して、圧縮機１００に戻される。
　次に、給油ポンプ１２、スラスト軸受１３、及び段付きボルト１４の構成について、詳細に説明する。 The discharge pipe Pb shown in FIG. 1 is a pipe through which the refrigerant discharged through the discharge port N passes, and is installed in the case 1a of the closed container 1. The refrigerant discharged from the compressor 100 via the discharge pipe Pb sequentially passes through, for example, a condenser (not shown), an expansion valve (not shown), and an evaporator (not shown) in a refrigeration cycle (not shown). It circulates in a heat pump cycle) and is further returned to the compressor 100 via a suction pipe Pa.
Next, the configurations of the refueling pump 12, the thrust bearing 13, and the stepped bolt 14 will be described in detail.
　図２は、圧縮機１００の断面における給油ポンプ１２付近の部分拡大図である。
　図２に示すように、給油ポンプ１２は、インナロータ１２ａと、アウタロータ１２ｂと、ポンプカバー１２ｃと、ポンプケース１２ｄと、を備えている。
　インナロータ１２ａは、外周側にトロコイド曲線状の歯が設けられたロータである。このインナロータ１２ａは、クランク軸４の突起４ｃに設置され、クランク軸４と一体で回転する。 FIG. 2 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100.
As shown in FIG. 2, the refueling pump 12 includes an inner rotor 12a, an outer rotor 12b, a pump cover 12c, and a pump case 12d.
The inner rotor 12a is a rotor provided with trochoidal curved teeth on the outer peripheral side. The inner rotor 12a is installed on the protrusion 4c of the crankshaft 4 and rotates integrally with the crankshaft 4.
　アウタロータ１２ｂは、インナロータ１２ａを囲むように配置され、その内周側にはトロコイド曲線状の歯が設けられている。なお、クランク軸４の回転に伴って給油流路４ｄに潤滑油を供給する「給油部」は、インナロータ１２ａと、アウタロータ１２ｂと、を含んで構成される。 The outer rotor 12b is arranged so as to surround the inner rotor 12a, and trochoidal curved teeth are provided on the inner peripheral side thereof. The "lubricating section" that supplies lubricating oil to the lubricating flow path 4d as the crankshaft 4 rotates includes an inner rotor 12a and an outer rotor 12b.
　そして、インナロータ１２ａ及びアウタロータ１２ｂが互いに噛合しながら回転することで、油溜りＲ（図１参照）の潤滑油が吸い上げられて給油流路４ｄに導かれるようになっている。
　ポンプカバー１２ｃは、潤滑油を圧送するための空間をインナロータ１２ａやアウタロータ１２ｂとともに形成するカバーであり、ポンプケース１２ｄに固定されている。 Then, the inner rotor 12a and the outer rotor 12b rotate while meshing with each other, so that the lubricating oil in the oil sump R (see FIG. 1) is sucked up and guided to the oil supply flow path 4d.
The pump cover 12c is a cover that forms a space for pumping lubricating oil together with the inner rotor 12a and the outer rotor 12b, and is fixed to the pump case 12d.
　ポンプケース１２ｄは、インナロータ１２ａやアウタロータ１２ｂ（つまり、「給油部」）を収容するケースである。ポンプケース１２ｄは、インナロータ１２ａやアウタロータ１２ｂ等が収容される凹状の収容部１２１ｄと、この収容部１２１ｄから下側に細長く延びる浸漬部１２２ｄと、収容部１２１ｄから径方向外側に延びるフランジ１２３ｄと、を備えている。 The pump case 12d is a case for accommodating the inner rotor 12a and the outer rotor 12b (that is, the "refueling unit"). The pump case 12d includes a concave accommodating portion 121d in which the inner rotor 12a, the outer rotor 12b, and the like are accommodated, an immersion portion 122d extending downward from the accommodating portion 121d, and a flange 123d extending radially outward from the accommodating portion 121d. Is equipped with.
　浸漬部１２２ｄは、通常、その先端付近が油溜りＲに浸漬している。浸漬部１２２ｄには、インナロータ１２ａとアウタロータ１２ｂとの間の空間に潤滑油を導くための流路ｈｄが設けられている。
　フランジ１２３ｄは、段付きボルト１４が設置される部分である。このフランジ１２３ｄには、段付きボルト１４の中間部１４ｂ（図３参照）に対応する大きさの孔ｈ４（図３参照）が３箇所に設けられている。 The immersion portion 122d is usually immersed in the oil sump R near the tip thereof. The immersion portion 122d is provided with a flow path hd for guiding the lubricating oil into the space between the inner rotor 12a and the outer rotor 12b.
The flange 123d is a portion where the stepped bolt 14 is installed. The flange 123d is provided with holes h4 (see FIG. 3) having a size corresponding to the intermediate portion 14b (see FIG. 3) of the stepped bolt 14 at three locations.
　図２に示すスラスト軸受１３は、前記したように、クランク軸４から軸方向（スラスト方向）の荷重を受ける軸受である。より詳しく説明すると、クランク軸４の主軸４ａと突起４ｃとの間で段差になっている箇所にスラスト軸受１３が設置されている。また、スラスト軸受１３は、サブフレーム１０（固定部材）と給油ポンプ１２との間に介在し、サブフレーム１０の下面に段付きボルト１４で固定されている。なお、スラスト軸受１３には、クランク軸４の突起４ｃ（図３も参照）が挿通される孔ｈ２が設けられている。 As described above, the thrust bearing 13 shown in FIG. 2 is a bearing that receives a load in the axial direction (thrust direction) from the crankshaft 4. More specifically, the thrust bearing 13 is installed at a position where there is a step between the main shaft 4a and the protrusion 4c of the crankshaft 4. Further, the thrust bearing 13 is interposed between the subframe 10 (fixing member) and the oil supply pump 12, and is fixed to the lower surface of the subframe 10 with a stepped bolt 14. The thrust bearing 13 is provided with a hole h2 through which a protrusion 4c of the crankshaft 4 (see also FIG. 3) is inserted.
　スラスト軸受１３は、例えば、肉薄の円板状を呈し、ベースとなる鋼板（バックメタルという）の摺動面側に所定の多孔質焼結層が設けられた構成になっている。なお、前記した構成は一例であり、スラスト軸受１３の構成は、これに限定されるものではない。 The thrust bearing 13 has, for example, a thin disk shape, and has a configuration in which a predetermined porous sintered layer is provided on the sliding surface side of a base steel plate (called a back metal). The configuration described above is an example, and the configuration of the thrust bearing 13 is not limited to this.
　図３は、クランク軸４、サブフレーム１０、スラスト軸受１３、給油ポンプ１２、及び段付きボルト１４を含む分解斜視図である。
　図３に示すように、スラスト軸受１３の中央部には、クランク軸４の下端部の突起４ｃが挿通される１つの孔ｈ２が設けられている。一方、スラスト軸受１３の縁付近には、段付きボルト１４のネジ部１４ａが挿通される３つの孔ｈ３が周方向に等間隔で設けられている。 FIG. 3 is an exploded perspective view including a crankshaft 4, a subframe 10, a thrust bearing 13, a refueling pump 12, and a stepped bolt 14.
As shown in FIG. 3, one hole h2 through which the protrusion 4c at the lower end of the crankshaft 4 is inserted is provided in the central portion of the thrust bearing 13. On the other hand, near the edge of the thrust bearing 13, three holes h3 through which the threaded portion 14a of the stepped bolt 14 is inserted are provided at equal intervals in the circumferential direction.
　また、スラスト軸受１３においてクランク軸４との摺動面（上面）には、潤滑油を取り込むための径方向の溝（図示せず）が設けられている。なお、前記した溝に代えて、クランク軸４においてスラスト軸受１３との摺動面（下端面）に所定の溝（図示せず）を設けるようにしてもよい。 Further, in the thrust bearing 13, a radial groove (not shown) for taking in lubricating oil is provided on the sliding surface (upper surface) with the crankshaft 4. Instead of the groove described above, a predetermined groove (not shown) may be provided on the sliding surface (lower end surface) of the crankshaft 4 with the thrust bearing 13.
　段付きボルト１４は、前記したように、スラスト軸受１３をサブフレーム１０（固定部材）に結合する「結合部」である。その他に段付きボルト１４は、給油ポンプ１２を支える機能も有している。 As described above, the stepped bolt 14 is a "joining portion" that connects the thrust bearing 13 to the subframe 10 (fixing member). In addition, the stepped bolt 14 also has a function of supporting the refueling pump 12.
　図３に示すように、段付きボルト１４は、ネジ部１４ａと、中間部１４ｂと、頭部１４ｃと、を備えている。ネジ部１４ａには、サブフレーム１０のネジ穴ｎに螺合するネジ溝ｍ（図４参照）が設けられている。中間部１４ｂは、ネジ部１４ａに連なり、ネジ部１４ａよりも径が大きい。頭部１４ｃは、中間部１４ｂに連なり、中間部１４ｂよりも径がさらに大きい。段付きボルト１４は、ポンプケース１２ｄ及びスラスト軸受１３を軸方向に貫通し、サブフレーム１０に結合されてスラスト軸受１３を固定している。すなわち、段付きボルト１４は、サブフレーム１０（固定部材）に設けられたネジ穴ｎに下側から螺合している。 As shown in FIG. 3, the stepped bolt 14 includes a screw portion 14a, an intermediate portion 14b, and a head portion 14c. The screw portion 14a is provided with a screw groove m (see FIG. 4) for screwing into the screw hole n of the subframe 10. The intermediate portion 14b is connected to the threaded portion 14a and has a larger diameter than the threaded portion 14a. The head 14c is connected to the intermediate portion 14b and has a larger diameter than the intermediate portion 14b. The stepped bolt 14 penetrates the pump case 12d and the thrust bearing 13 in the axial direction, and is coupled to the subframe 10 to fix the thrust bearing 13. That is, the stepped bolt 14 is screwed into the screw hole n provided in the subframe 10 (fixing member) from below.
　図４は、図２に示すＱ部を拡大した部分拡大図である。
　なお、図４では、径方向の隙間ＧＤや軸方向の隙間ＧＡを分かりやすくするために、これらの隙間ＧＤ，ＧＡを実際よりも長めに図示している。
　図４に示すように、段付きボルト１４の中間部１４ｂの径は、スラスト軸受１３の孔ｈ３の径よりも大きく、その一方で、ポンプケース１２ｄの孔ｈ４の径よりも小さい。 FIG. 4 is a partially enlarged view of the Q portion shown in FIG. 2.
In FIG. 4, these gaps GD and GA are shown longer than they actually are in order to make it easier to understand the radial gap GD and the axial gap GA.
As shown in FIG. 4, the diameter of the intermediate portion 14b of the stepped bolt 14 is larger than the diameter of the hole h3 of the thrust bearing 13, while being smaller than the diameter of the hole h4 of the pump case 12d.
　そして、段付きボルト１４のネジ部１４ａがサブフレーム１０のネジ穴ｎに螺合すると、中間部１４ｂがスラスト軸受１３の下面に押し当てられるようになっており、中間部１４ｂの上面とスラスト軸受１３の下面とが直接接触している。すなわち、段付きボルト１４の中間部１４ｂとサブフレーム１０（固定部材）とによって、スラスト軸受１３が挟み込まれて固定されている。さらに、サブフレーム１０の３つのネジ穴ｎに対応して、３本の段付きボルト１４が設置されている（図３参照）。これによって、スラスト軸受１３の周方向の移動が規制される。 When the screw portion 14a of the stepped bolt 14 is screwed into the screw hole n of the subframe 10, the intermediate portion 14b is pressed against the lower surface of the thrust bearing 13, and the upper surface of the intermediate portion 14b and the thrust bearing are pressed against each other. It is in direct contact with the lower surface of 13. That is, the thrust bearing 13 is sandwiched and fixed by the intermediate portion 14b of the stepped bolt 14 and the subframe 10 (fixing member). Further, three stepped bolts 14 are installed corresponding to the three screw holes n of the subframe 10 (see FIG. 3). As a result, the movement of the thrust bearing 13 in the circumferential direction is restricted.
　また、ポンプケース１２ｄのフランジ１２３ｄにおいて、段付きボルト１４の中間部１４ｂが設置される孔ｈ４の径は、中間部１４ｂの径よりも若干大きくなっている。したがって、段付きボルト１４が設置された状態では、中間部１４ｂとポンプケース１２ｄの孔ｈ４の周壁面との間に径方向の所定の隙間ＧＤが設けられている。 Further, in the flange 123d of the pump case 12d, the diameter of the hole h4 in which the intermediate portion 14b of the stepped bolt 14 is installed is slightly larger than the diameter of the intermediate portion 14b. Therefore, in the state where the stepped bolt 14 is installed, a predetermined radial gap GD is provided between the intermediate portion 14b and the peripheral wall surface of the hole h4 of the pump case 12d.
　また、中間部１４ｂの周囲におけるフランジ１２３ｄの肉厚（上下方向の厚さ）は、中間部１４ｂの肉厚（上下方向の厚さ）よりも若干薄くなっている。したがって、段付きボルト１４が設置された状態では、ポンプケース１２ｄのフランジ１２３ｄの上面と、スラスト軸受１３と、の間に軸方向の所定の隙間ＧＡが設けられている。 Further, the wall thickness (thickness in the vertical direction) of the flange 123d around the intermediate portion 14b is slightly thinner than the wall thickness (thickness in the vertical direction) of the intermediate portion 14b. Therefore, in the state where the stepped bolt 14 is installed, a predetermined axial gap GA is provided between the upper surface of the flange 123d of the pump case 12d and the thrust bearing 13.
　このように、段付きボルト１４の中間部１４ｂとポンプケース１２ｄとの間には径方向の隙間ＧＤが設けられる一方、スラスト軸受１３とポンプケース１２ｄとの間には軸方向の隙間ＧＡが設けられている。そして、３本の段付きボルト１４（図３参照）の頭部１４ｃによって、給油ポンプ１２が支えられている（吊り下げられている）。すなわち、段付きボルト１４は、ポンプケース１２ｄの一部（ポンプケース１２ｄの孔ｈ４付近の下面）と直接接触している。 As described above, a radial gap GD is provided between the intermediate portion 14b of the stepped bolt 14 and the pump case 12d, while an axial gap GA is provided between the thrust bearing 13 and the pump case 12d. Has been done. The refueling pump 12 is supported (suspended) by the head 14c of the three stepped bolts 14 (see FIG. 3). That is, the stepped bolt 14 is in direct contact with a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4).
　これによって、クランク軸４で振れ回りが生じた場合でも、前記した径方向の隙間ＧＤや軸方向の隙間ＧＡによって、クランク軸４の振れ回りが吸収される。つまり、クランク軸４の振れ回りに伴って、給油ポンプ１２のインナロータ１２ａ（図２参照）が若干傾くと、径方向の隙間ＧＤや軸方向の隙間ＧＡの許容範囲内で、アウタロータ１２ｂ（図２参照）も若干傾く。したがって、給油ポンプ１２のインナロータ１２ａやアウタロータ１２ｂに過大な荷重が生じないため、クランク軸４の折損や給油ポンプ１２のかじり・焼付きといった不具合を防止できる。 As a result, even if the crankshaft 4 has a runout, the runout of the crankshaft 4 is absorbed by the radial gap GD and the axial gap GA described above. That is, when the inner rotor 12a (see FIG. 2) of the refueling pump 12 is slightly tilted with the swing of the crankshaft 4, the outer rotor 12b (FIG. 2) is within the allowable range of the radial gap GD and the axial gap GA. See) also tilts slightly. Therefore, since an excessive load is not generated on the inner rotor 12a and the outer rotor 12b of the refueling pump 12, problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12 can be prevented.
　なお、段付きボルト１４の中間部１４ｂとポンプケース１２ｄとの間の径方向の隙間ＧＤの寸法Ｌ１（隙間ＧＤの長さ：図４参照）は、この径方向の隙間を形成する範囲における中間部１４ｂ（結合部）の軸径、又は、前記した径方向の隙間を形成する範囲におけるポンプケース１２ｄの孔ｈ４の孔径の４％以上かつ１３％以下であることが好ましい。これによって、クランク軸４の振れ回りが適切に吸収される。 The dimension L1 of the radial gap GD between the intermediate portion 14b of the stepped bolt 14 and the pump case 12d (the length of the gap GD: see FIG. 4) is the middle within the range in which the radial gap is formed. It is preferable that the shaft diameter of the portion 14b (joining portion) is 4% or more and 13% or less of the hole diameter of the hole h4 of the pump case 12d in the range of forming the above-mentioned radial gap. As a result, the runout of the crankshaft 4 is appropriately absorbed.
　また、スラスト軸受１３とポンプケース１２ｄとの間の軸方向の隙間ＧＡの寸法Ｌ２（隙間ＧＡの長さ：図４参照）は、この軸方向の隙間を形成する範囲における中間部１４ｂ（結合部）の軸方向の長さ、又は、前記した軸方向の隙間の周囲におけるポンプケース１２ｄのフランジ１２３ｄの上下方向の肉厚の１％以上かつ６％以下であることが好ましい。これによって、クランク軸４の振れ回りが適切に吸収される。 Further, the dimension L2 of the axial clearance GA between the thrust bearing 13 and the pump case 12d (the length of the clearance GA: see FIG. 4) is the intermediate portion 14b (joint portion) in the range in which the axial clearance is formed. ) In the axial direction, or 1% or more and 6% or less of the vertical wall thickness of the flange 123d of the pump case 12d around the above-mentioned axial gap. As a result, the runout of the crankshaft 4 is appropriately absorbed.
　また、図２に示すように、サブフレーム１０（固定部材）の円筒部１０ａの軸方向において、スラスト軸受１３の付近では、円筒部の１０ａの内径が一定であることが好ましい。これによって、サブフレーム１０を加工する際に高い寸法精度が求められることがほとんどないため、加工に要する工数やコストを削減できる。 Further, as shown in FIG. 2, it is preferable that the inner diameter of the cylindrical portion 10a is constant in the vicinity of the thrust bearing 13 in the axial direction of the cylindrical portion 10a of the subframe 10 (fixing member). As a result, high dimensional accuracy is rarely required when processing the subframe 10, so that the man-hours and costs required for processing can be reduced.
　なお、仮に、スラスト軸受１３の大きさに合わせて、サブフレーム１０の下部（スラスト軸受１３の付近）に段差を設け、さらに、スラスト軸受１３の周方向の回転をねじを使わずに規制するようにサブフレーム１０を形成すると、高い加工精度が求められる。これに対して本実施形態では、前記したように、円筒部の１０ａの内径が軸方向で一定であり、また、スラスト軸受１３の周方向の回転が３個の段付きボルト１４で規制されている（図３参照）。したがって、サブフレーム１０の加工コストを削減できる。 Temporarily, a step is provided in the lower part of the subframe 10 (near the thrust bearing 13) according to the size of the thrust bearing 13, and the rotation of the thrust bearing 13 in the circumferential direction is regulated without using screws. When the subframe 10 is formed on the surface, high processing accuracy is required. On the other hand, in the present embodiment, as described above, the inner diameter of the cylindrical portion 10a is constant in the axial direction, and the rotation of the thrust bearing 13 in the circumferential direction is regulated by the three stepped bolts 14. (See Fig. 3). Therefore, the processing cost of the subframe 10 can be reduced.
＜効果＞
　第１実施形態によれば、段付きボルト１４の中間部１４ｂとサブフレーム１０との間でスラスト軸受１３が上下方向で挟み込まれて強固に固定される。また、３個の段付きボルト１４が、スラスト軸受１３の回り止めの機能も担っている。したがって、スラスト軸受１３に関して、いわゆるＤカット形状といった回り止めの形状を採用する必要がないため、厳しい寸法公差が求められる高精度な加工を行う必要がない。さらに、スラスト軸受１３として、クランク軸４から軸方向の荷重を受ける側の片面のみに多孔質焼結層等が設けられた安価なバックメタル付きのものを採用できる。 <Effect>
According to the first embodiment, the thrust bearing 13 is sandwiched in the vertical direction between the intermediate portion 14b of the stepped bolt 14 and the subframe 10 and is firmly fixed. In addition, the three stepped bolts 14 also serve to prevent the thrust bearing 13 from rotating. Therefore, it is not necessary to adopt a detent shape such as a so-called D-cut shape for the thrust bearing 13, and it is not necessary to perform high-precision processing that requires a strict dimensional tolerance. Further, as the thrust bearing 13, one with an inexpensive back metal in which a porous sintered layer or the like is provided only on one surface on the side receiving an axial load from the crankshaft 4 can be adopted.
　また、段付きボルト１４の中間部１４ｂとサブフレーム１０との間にスラスト軸受１３が挟み込まれて強固に固定される一方、中間部１４ｂには径方向の隙間ＧＤや軸方向の隙間ＧＡが設けられている。これによって、クランク軸４の振れ回りが生じたとき、給油ポンプ１２のインナロータ１２ａやアウタロータ１２ｂに過大な荷重がかかることを防止できる。その結果、クランク軸４の折損や給油ポンプ１２のかじり・焼付きといった不具合を防止できる。 Further, the thrust bearing 13 is sandwiched between the intermediate portion 14b of the stepped bolt 14 and the subframe 10 to be firmly fixed, while the intermediate portion 14b is provided with a radial gap GD and an axial gap GA. Has been done. As a result, it is possible to prevent an excessive load from being applied to the inner rotor 12a and the outer rotor 12b of the refueling pump 12 when the crankshaft 4 swings around. As a result, it is possible to prevent problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12.
　また、第１実施形態では、サブフレーム１０の下側にスラスト軸受１３が配置されている。したがって、サブフレーム１０において、スラスト軸受１３を保持するための所定の段差を設けたり、スラスト軸受１３の荷重を支えるために所定の肉厚を確保したりする必要がない。したがって、サブフレーム１０の大型化や材料費の増加を抑制できる。 Further, in the first embodiment, the thrust bearing 13 is arranged under the subframe 10. Therefore, it is not necessary to provide a predetermined step for holding the thrust bearing 13 in the subframe 10 or to secure a predetermined wall thickness to support the load of the thrust bearing 13. Therefore, it is possible to suppress an increase in the size of the subframe 10 and an increase in material cost.
　また、第１実施形態では、クランク軸４の下側にスラスト軸受１３が設けられる。したがって、例えば、クランク軸４の所定箇所に大径の鍔部（図示せず）を設け、この鍔部にスラスト軸受１３を設置する構成に比べて、クランク軸４の大型化や材料費の増加を抑制できる。さらに、段付きボルト１４が、スラスト軸受１３の固定と、給油ポンプ１２の支持と、の両方の役割を兼ねているため、部品点数を削減できる。 Further, in the first embodiment, the thrust bearing 13 is provided on the lower side of the crankshaft 4. Therefore, for example, as compared with a configuration in which a large-diameter flange portion (not shown) is provided at a predetermined position on the crankshaft 4 and a thrust bearing 13 is installed on the flange portion, the size of the crankshaft 4 is increased and the material cost is increased. Can be suppressed. Further, since the stepped bolt 14 serves both of fixing the thrust bearing 13 and supporting the refueling pump 12, the number of parts can be reduced.
　このように本実施形態によれば、給油ポンプ１２に過大な荷重が発生しにくく、信頼性の高い圧縮機１００を提供できる。また、部品点数が少なく簡素な構成で、加工性や組立性に優れた安価な圧縮機１００を提供できる。 As described above, according to the present embodiment, it is possible to provide a highly reliable compressor 100 in which an excessive load is unlikely to be generated in the refueling pump 12. Further, it is possible to provide an inexpensive compressor 100 having excellent workability and assembling property with a simple configuration with a small number of parts.
≪第２実施形態≫
　第２実施形態に係る圧縮機１００Ａ（図５参照）は、第１実施形態で説明した段付きボルト１４（図２参照）に代えて、ボルト１５Ａ（図５参照）及びスペーサ１６Ａ（図５参照）を備える構成になっている。なお、その他については、第１実施形態と同様である。したがって、第１実施形態とは異なる部分について説明し、重複する部分については説明を省略する。 << Second Embodiment >>
The compressor 100A (see FIG. 5) according to the second embodiment has a bolt 15A (see FIG. 5) and a spacer 16A (see FIG. 5) in place of the stepped bolt 14 (see FIG. 2) described in the first embodiment. ) Is provided. Others are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.
　図５は、第２実施形態に係る圧縮機１００Ａの断面における給油ポンプ１２付近の部分拡大図である。
　図５に示すように、圧縮機１００Ａは、クランク軸４（駆動軸）やサブフレーム１０（固定部材）の他に、副軸受１１（ラジアル軸受）と、給油ポンプ１２と、スラスト軸受１３と、ボルト１５Ａ（結合部）と、スペーサ１６Ａ（結合部）と、を備えている。 FIG. 5 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100A according to the second embodiment.
As shown in FIG. 5, in the compressor 100A, in addition to the crankshaft 4 (drive shaft) and the subframe 10 (fixing member), the auxiliary bearing 11 (radial bearing), the oil supply pump 12, the thrust bearing 13, and the thrust bearing 13 are included. A bolt 15A (joint portion) and a spacer 16A (joint portion) are provided.
　ボルト１５Ａは、サブフレーム１０のネジ穴に螺合するネジ溝が設けられたネジ部１５１Ａと、このネジ部１５１Ａよりも径が大きい頭部１５２Ａと、を有している。
　スペーサ１６Ａは、ボルト１５Ａの頭部１５２Ａとスラスト軸受１３との間の上下方向の距離を保持する部材（カラー）であり、円筒状を呈している。なお、スペーサ１６Ａの軸方向の長さは、ポンプケース１２ｄにおけるスペーサ１６Ａの周囲の肉厚よりも長くなっている。また、スペーサ１６Ａには、ボルト１５Ａのネジ部１５１Ａが挿通されている。 The bolt 15A has a screw portion 151A provided with a screw groove to be screwed into a screw hole of the subframe 10, and a head portion 152A having a diameter larger than that of the screw portion 151A.
The spacer 16A is a member (collar) that maintains a vertical distance between the head portion 152A of the bolt 15A and the thrust bearing 13, and has a cylindrical shape. The axial length of the spacer 16A is longer than the wall thickness around the spacer 16A in the pump case 12d. Further, the threaded portion 151A of the bolt 15A is inserted through the spacer 16A.
　そして、スペーサ１６Ａとサブフレーム１０とによって、スラスト軸受１３が挟み込まれて固定されている。なお、ボルト１５Ａの頭部１５２Ａの径は、スペーサ１６Ａの外径よりも大きい。
　また、スペーサ１６Ａとポンプケース１２ｄとの間には径方向の隙間が設けられる一方、スラスト軸受１３とポンプケース１２ｄとの間には軸方向の隙間が設けられている。そして、ボルト１５Ａの頭部１５２Ａによって、給油ポンプ１２が支えられている。つまり、ボルト１５Ａは、ポンプケース１２ｄの一部（下面）と直接接触している。 The thrust bearing 13 is sandwiched and fixed by the spacer 16A and the subframe 10. The diameter of the head 152A of the bolt 15A is larger than the outer diameter of the spacer 16A.
Further, a radial gap is provided between the spacer 16A and the pump case 12d, while an axial gap is provided between the thrust bearing 13 and the pump case 12d. The refueling pump 12 is supported by the head 152A of the bolt 15A. That is, the bolt 15A is in direct contact with a part (lower surface) of the pump case 12d.
　なお、スペーサ１６Ａとポンプケース１２ｄとの間の径方向の隙間の寸法は、スペーサ１６Ａの径（又は、ポンプケース１２ｄの孔ｈ４の径）の４％以上かつ１３％以下であることが好ましい。また、スラスト軸受１３とポンプケース１２ｄとの間の軸方向の隙間の寸法は、スペーサ１６Ａの軸方向の長さ（又は、フランジ１２３ｄの上下方向の肉厚）の１％以上かつ６％以下であることが好ましい。これによって、クランク軸４の振れ回りが適切に吸収される。 The dimension of the radial gap between the spacer 16A and the pump case 12d is preferably 4% or more and 13% or less of the diameter of the spacer 16A (or the diameter of the hole h4 of the pump case 12d). The dimension of the axial gap between the thrust bearing 13 and the pump case 12d is 1% or more and 6% or less of the axial length of the spacer 16A (or the vertical wall thickness of the flange 123d). It is preferable to have. As a result, the runout of the crankshaft 4 is appropriately absorbed.
＜効果＞
　第２実施形態によれば、スペーサ１６Ａとサブフレーム１０との間にスラスト軸受１３が挟み込まれて強固に固定され、その一方で、スペーサ１６Ａには径方向・軸方向の隙間が設けられている。これによって、クランク軸４の振れ回りが生じた場合でも、クランク軸４の折損や給油ポンプ１２のかじり・焼付きといった不具合を防止できる。 <Effect>
According to the second embodiment, the thrust bearing 13 is sandwiched between the spacer 16A and the subframe 10 and firmly fixed, while the spacer 16A is provided with gaps in the radial and axial directions. .. As a result, even if the crankshaft 4 swings around, problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12 can be prevented.
≪第３実施形態≫
　第３実施形態は、ボルト１５Ｂ（図６参照）やスペーサ１６Ｂ（図６参照）の形状が第２実施形態とは異なっているが、その他については第２実施形態と同様である。したがって、第２実施形態とは異なる部分について説明し、重複する部分については説明を省略する。 << Third Embodiment >>
In the third embodiment, the shapes of the bolt 15B (see FIG. 6) and the spacer 16B (see FIG. 6) are different from those of the second embodiment, but the other aspects are the same as those of the second embodiment. Therefore, a part different from the second embodiment will be described, and a description of the overlapping part will be omitted.
　図６は、本発明の第３実施形態に係る圧縮機１００Ｂの断面における給油ポンプ１２付近の部分拡大図である。
　なお、図６に示す圧縮機１００Ｂは、ボルト１５Ｂ（結合部）の頭部１５２Ｂの径が比較的小さい点と、スペーサ１６Ｂ（結合部）が鍔部１６２Ｂを有している点以外は、第２実施形態（図５参照）と同様であるから、詳細な説明は省略する。 FIG. 6 is a partially enlarged view of the vicinity of the refueling pump 12 in the cross section of the compressor 100B according to the third embodiment of the present invention.
Note that the compressor 100B shown in FIG. 6 is the first except that the diameter of the head 152B of the bolt 15B (joining portion) is relatively small and the spacer 16B (joining portion) has the flange portion 162B. Since it is the same as that of the second embodiment (see FIG. 5), detailed description thereof will be omitted.
　スペーサ１６Ｂは、円筒状の円筒部１６１Ｂと、この円筒部１６１Ｂの下端部（軸方向の一方側の端部）から径方向外側に延びる鍔部１６２Ｂと、を備えている。なお、円筒部１６１Ｂの軸方向の長さは、ポンプケース１２ｄにおける円筒部１６１Ｂの周囲の肉厚よりも長くなっている。また、ボルト１５Ｂの頭部１５２Ｂがスペーサ１６Ｂの鍔部１６２Ｂに当接するように、ボルト１５Ｂのネジ部１５１Ｂがスペーサ１６Ｂに挿通されている。 The spacer 16B includes a cylindrical cylindrical portion 161B and a flange portion 162B extending radially outward from the lower end portion (one end portion in the axial direction) of the cylindrical portion 161B. The axial length of the cylindrical portion 161B is longer than the wall thickness around the cylindrical portion 161B in the pump case 12d. Further, the threaded portion 151B of the bolt 15B is inserted through the spacer 16B so that the head portion 152B of the bolt 15B abuts on the flange portion 162B of the spacer 16B.
　そして、スペーサ１６Ｂとサブフレーム１０とによって、スラスト軸受１３が挟み込まれて固定されている。なお、ボルト１５Ｂの頭部１５２Ｂの径は、スペーサ１６Ｂの内径よりも大きい。
　また、スペーサ１６Ｂとポンプケース１２ｄとの間には径方向の隙間が設けられる一方、スラスト軸受１３とポンプケース１２ｄとの間には軸方向の隙間が設けられている。そして、スペーサ１６Ｂの鍔部１６２Ｂを介して、ボルト１５Ｂの頭部１５２Ｂによって、給油ポンプ１２が支えられている。つまり、ボルト１５Ｂは、ポンプケース１２ｄの一部（下面）と直接接触している。 The thrust bearing 13 is sandwiched and fixed by the spacer 16B and the subframe 10. The diameter of the head 152B of the bolt 15B is larger than the inner diameter of the spacer 16B.
Further, a radial gap is provided between the spacer 16B and the pump case 12d, while an axial gap is provided between the thrust bearing 13 and the pump case 12d. The refueling pump 12 is supported by the head portion 152B of the bolt 15B via the flange portion 162B of the spacer 16B. That is, the bolt 15B is in direct contact with a part (lower surface) of the pump case 12d.
　なお、スペーサ１６Ｂとポンプケース１２ｄとの間の径方向の隙間の寸法は、スペーサ１６Ｂの径（又は、ポンプケース１２ｄの孔ｈ４の径）の４％以上かつ１３％以下であることが好ましい。また、スラスト軸受１３とポンプケース１２ｄとの間の軸方向の隙間の寸法は、スペーサ１６Ｂの円筒部１６１Ｂの軸方向の長さ（又は、フランジ１２３ｄの上下方向の肉厚）の１％以上かつ６％以下であることが好ましい。これによって、クランク軸４の振れ回りが適切に吸収される。 The dimension of the radial gap between the spacer 16B and the pump case 12d is preferably 4% or more and 13% or less of the diameter of the spacer 16B (or the diameter of the hole h4 of the pump case 12d). The dimension of the axial gap between the thrust bearing 13 and the pump case 12d is 1% or more of the axial length of the cylindrical portion 161B of the spacer 16B (or the vertical wall thickness of the flange 123d). It is preferably 6% or less. As a result, the runout of the crankshaft 4 is appropriately absorbed.
＜効果＞
　第３実施形態によれば、スペーサ１６Ｂとサブフレーム１０との間にスラスト軸受１３が挟み込まれて強固に固定され、その一方で、スペーサ１６Ｂには径方向・軸方向の隙間が設けられている。これによって、クランク軸４の振れ回りが生じた場合でも、クランク軸４の折損や給油ポンプ１２のかじり・焼付きといった不具合を防止できる。 <Effect>
According to the third embodiment, the thrust bearing 13 is sandwiched between the spacer 16B and the subframe 10 and firmly fixed, while the spacer 16B is provided with gaps in the radial and axial directions. .. As a result, even if the crankshaft 4 swings around, problems such as breakage of the crankshaft 4 and galling / seizure of the refueling pump 12 can be prevented.
≪第４実施形態≫
　第４実施形態では、第１実施形態で説明した圧縮機１００（図１参照）を備える空気調和機Ｗ（冷凍サイクル装置：図７参照）について説明する。 << Fourth Embodiment >>
In the fourth embodiment, the air conditioner W (refrigeration cycle device: see FIG. 7) including the compressor 100 (see FIG. 1) described in the first embodiment will be described.
　図７は、空気調和機Ｗの冷媒回路Ｋの構成図である。
　なお、図７の実線矢印は、暖房運転時における冷媒の流れを示している。
　また、図７の破線矢印は、冷房運転時における冷媒の流れを示している。
　空気調和機Ｗは、冷房や暖房等の空調を行う機器である。図７に示すように、空気調和機Ｗは、圧縮機１００と、室外熱交換器Ｅｏと、室外ファンＦｏと、膨張弁Ｖｅと、四方弁Ｖｆと、室内熱交換器Ｅｉと、室内ファンＦｉと、を備えている。 FIG. 7 is a block diagram of the refrigerant circuit K of the air conditioner W.
The solid line arrow in FIG. 7 indicates the flow of the refrigerant during the heating operation.
Further, the broken line arrow in FIG. 7 indicates the flow of the refrigerant during the cooling operation.
The air conditioner W is a device that performs air conditioning such as cooling and heating. As shown in FIG. 7, the air conditioner W includes a compressor 100, an outdoor heat exchanger Eo, an outdoor fan Fo, an expansion valve Ve, a four-way valve Vf, an indoor heat exchanger Ei, and an indoor fan Fi. And have.
　図７に示す例では、圧縮機１００、室外熱交換器Ｅｏ、室外ファンＦｏ、膨張弁Ｖｅ、及び四方弁Ｖｆが、室外機Ｗｏに設けられている。一方、室内熱交換器Ｅｉ及び室内ファンＦｉは、室内機Ｗｉに設けられている。 In the example shown in FIG. 7, the compressor 100, the outdoor heat exchanger Eo, the outdoor fan Fo, the expansion valve Ve, and the four-way valve Vf are provided in the outdoor unit Wo. On the other hand, the indoor heat exchanger Ei and the indoor fan Fi are provided in the indoor unit Wi.
　圧縮機１００は、ガス状の冷媒を圧縮する機器であり、第１実施形態（図１参照）と同様の構成を備えている。
　室外熱交換器Ｅｏは、その伝熱管（図示せず）を通流する冷媒と、室外ファンＦｏから送り込まれる外気と、の間で熱交換が行われる熱交換器である。
　室外ファンＦｏは、室外熱交換器Ｅｏに外気を送り込むファンである。室外ファンＦｏは、駆動源である室外ファンモータＭｏを備え、室外熱交換器Ｅｏの付近に設置されている。 The compressor 100 is a device that compresses a gaseous refrigerant, and has the same configuration as that of the first embodiment (see FIG. 1).
The outdoor heat exchanger Eo is a heat exchanger in which heat exchange is performed between the refrigerant flowing through the heat transfer tube (not shown) and the outside air sent from the outdoor fan Fo.
The outdoor fan Fo is a fan that sends outside air to the outdoor heat exchanger Eo. The outdoor fan Fo includes an outdoor fan motor Mo which is a drive source, and is installed near the outdoor heat exchanger Eo.
　室内熱交換器Ｅｉは、その伝熱管（図示せず）を通流する冷媒と、室内ファンＦｉから送り込まれる室内空気（空調対象空間の空気）と、の間で熱交換が行われる熱交換器である。
　室内ファンＦｉは、室内熱交換器Ｅｉに室内空気を送り込むファンである。室内ファンＦｉは、駆動源である室内ファンモータＭｉを備え、室内熱交換器Ｅｉの付近に設置されている。 The indoor heat exchanger Ei is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the indoor air (air in the air-conditioned space) sent from the indoor fan Fi. Is.
The indoor fan Fi is a fan that sends indoor air to the indoor heat exchanger Ei. The indoor fan Fi includes an indoor fan motor Mi as a drive source, and is installed in the vicinity of the indoor heat exchanger Ei.
　膨張弁Ｖｅは、「凝縮器」（室外熱交換器Ｅｏ及び室内熱交換器Ｅｉの一方）で凝縮した冷媒を減圧する弁である。なお、膨張弁Ｖｅによって減圧された冷媒は、「蒸発器」（室外熱交換器Ｅｏ及び室内熱交換器Ｅｉの他方）に導かれる。 The expansion valve Ve is a valve that reduces the pressure of the refrigerant condensed by the "condenser" (one of the outdoor heat exchanger Eo and the indoor heat exchanger Ei). The refrigerant decompressed by the expansion valve Ve is guided to an "evaporator" (the other of the outdoor heat exchanger Eo and the indoor heat exchanger Ei).
　四方弁Ｖｆは、空気調和機Ｗの運転モードに応じて、冷媒の流路を切り替える弁である。例えば、冷房運転時（図７の破線矢印を参照）には、圧縮機１００、室外熱交換器Ｅｏ（凝縮器）、膨張弁Ｖｅ、及び室内熱交換器Ｅｉ（蒸発器）が、四方弁Ｖｆを介して順次接続されてなる冷媒回路Ｋにおいて、冷凍サイクルで冷媒が循環する。 The four-way valve Vf is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner W. For example, during cooling operation (see the dashed arrow in FIG. 7), the compressor 100, the outdoor heat exchanger Eo (condenser), the expansion valve Ve, and the indoor heat exchanger Ei (evaporator) are the four-way valve Vf. In the refrigerant circuit K which is sequentially connected via the above, the refrigerant circulates in the refrigeration cycle.
　一方、暖房運転時（図７の実線矢印を参照）には、圧縮機１００、室内熱交換器Ｅｉ（凝縮器）、膨張弁Ｖｅ、及び室外熱交換器Ｅｏ（蒸発器）が、四方弁Ｖｆを介して順次接続されてなる冷媒回路Ｋにおいて、冷凍サイクルで冷媒が循環する。 On the other hand, during the heating operation (see the solid line arrow in FIG. 7), the compressor 100, the indoor heat exchanger Ei (condenser), the expansion valve Ve, and the outdoor heat exchanger Eo (evaporator) are the four-way valve Vf. In the refrigerant circuit K which is sequentially connected via the above, the refrigerant circulates in the refrigeration cycle.
　このように、圧縮機１００、「凝縮器」、膨張弁Ｖｅ、及び「蒸発器」を順次に介して冷媒が循環するようになっている。なお、圧縮機１００、室外ファンＦｏ、膨張弁Ｖｅ、室内ファンＦｉ等の機器は、不図示の制御装置からの指令に基づいて駆動される。 In this way, the refrigerant circulates in sequence through the compressor 100, the "condenser", the expansion valve Ve, and the "evaporator". Devices such as the compressor 100, the outdoor fan Fo, the expansion valve Ve, and the indoor fan Fi are driven based on a command from a control device (not shown).
＜効果＞
　第４実施形態によれば、簡素な構成で信頼性の高い圧縮機１００を備えた空気調和機Ｗを提供できる。 <Effect>
According to the fourth embodiment, it is possible to provide an air conditioner W having a highly reliable compressor 100 with a simple configuration.
≪変形例≫
　以上、本発明に係る圧縮機１００や空気調和機Ｗ等について各実施形態で説明したが、本発明はこれらの記載に限定されるものではなく、種々の変更を行うことができる。
　例えば、第１実施形態では、圧縮機１００（図１参照）のクランク軸４と給油ポンプ１２とが直接的に接続された構成について説明したが、これに限らない。すなわち、クランク軸４と給油ポンプ１２との間に所定の接続部（図示せず）が別体で設けられていてもよい。このような構成でも、第１実施形態と同様の効果が奏される。 ≪Modification≫
Although the compressor 100, the air conditioner W, and the like according to the present invention have been described above in each embodiment, the present invention is not limited to these descriptions, and various modifications can be made.
For example, in the first embodiment, the configuration in which the crankshaft 4 of the compressor 100 (see FIG. 1) and the refueling pump 12 are directly connected has been described, but the present invention is not limited to this. That is, a predetermined connection portion (not shown) may be separately provided between the crankshaft 4 and the refueling pump 12. Even with such a configuration, the same effect as that of the first embodiment is obtained.
　また、第１実施形態では、サブフレーム１０の脚１０ｂが３本設けられ（図３参照）、また、段付きボルト１４が３本設けられる構成について説明したが（図３参照）、これに限らない。すなわち、サブフレーム１０の脚１０ｂや段付きボルト１４は、複数設けられていればよく、その個数は適宜に変更可能である。 Further, in the first embodiment, a configuration in which three legs 10b of the subframe 10 are provided (see FIG. 3) and three stepped bolts 14 are provided (see FIG. 3) has been described, but the present invention is limited to this. Absent. That is, a plurality of legs 10b and stepped bolts 14 of the subframe 10 may be provided, and the number thereof can be appropriately changed.
　また、第１実施形態では、段付きボルト１４（結合部）の頭部１４ｃが、ポンプケース１２ｄの一部（ポンプケース１２ｄの孔ｈ４付近の下面）と直接接触している構成について説明したが（図４参照）、これに限らない。例えば、段付きボルト１４の頭部１４ｃと、ポンプケース１２ｄの一部（ポンプケース１２ｄの孔ｈ４付近の下面）と、の間にワッシャー（座金：図示せず）が介在していてもよい。 Further, in the first embodiment, the configuration in which the head portion 14c of the stepped bolt 14 (joining portion) is in direct contact with a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4) has been described. (See FIG. 4), but not limited to this. For example, a washer (washer: not shown) may be interposed between the head 14c of the stepped bolt 14 and a part of the pump case 12d (the lower surface of the pump case 12d near the hole h4).
　また、各実施形態では、圧縮機１００が縦置きで設置される構成について説明したが、これに限らない。例えば、圧縮機１００が横置きで設置される構成にも各実施形態を適用できる。
　また、各実施形態では、圧縮機１００がスクロール式の圧縮機である場合について説明したが、これに限らない。すなわち、各実施形態は、ロータリ式等の別タイプの圧縮機にも適用できる。 Further, in each embodiment, the configuration in which the compressor 100 is installed vertically has been described, but the present invention is not limited to this. For example, each embodiment can be applied to a configuration in which the compressor 100 is installed horizontally.
Further, in each embodiment, the case where the compressor 100 is a scroll type compressor has been described, but the present invention is not limited to this. That is, each embodiment can be applied to another type of compressor such as a rotary type compressor.
　また、各実施形態は、適宜に組み合わせることが可能である。例えば、第２実施形態と第４実施形態とを組み合わせ、ボルト１５Ａ（図５参照）及びスペーサ１６Ａ（図５参照）を備える圧縮機１００Ａ（第２実施形態）を空気調和機に搭載してもよい（第４実施形態）。同様に、第３実施形態と第４実施形態とを組み合わせてもよい。 In addition, each embodiment can be combined as appropriate. For example, even if the second embodiment and the fourth embodiment are combined and a compressor 100A (second embodiment) including a bolt 15A (see FIG. 5) and a spacer 16A (see FIG. 5) is mounted on the air conditioner. Good (4th embodiment). Similarly, the third embodiment and the fourth embodiment may be combined.
　また、第４実施形態では、圧縮機１００を備える空気調和機Ｗ（冷凍サイクル装置：図７参照）について説明したが、これに限らない。例えば、冷蔵庫、給湯機、空調給湯装置、チラーといった他の「冷凍サイクル装置」にも、第４実施形態を適用可能である。 Further, in the fourth embodiment, the air conditioner W (refrigeration cycle device: see FIG. 7) including the compressor 100 has been described, but the present invention is not limited to this. For example, the fourth embodiment can be applied to other "refrigeration cycle devices" such as refrigerators, water heaters, air-conditioning hot water supply devices, and chillers.
　また、各実施形態は本発明を分かりやすく説明するために詳細に記載したものであり、必ずしも説明した全ての構成を備えるものに限定されない。また、各実施形態の構成の一部について、他の構成の追加・削除・置換を適宜に行うことが可能である。
　また、前記した機構や構成は説明上必要と考えられるものを示しており、製品上必ずしも全ての機構や構成を示しているとは限らない。 Further, each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the configurations described. Further, it is possible to appropriately add / delete / replace other configurations with respect to a part of the configurations of each embodiment.
In addition, the above-mentioned mechanism and configuration show what is considered necessary for explanation, and do not necessarily show all the mechanisms and configurations in the product.
　１００，１００Ａ，１００Ｂ　圧縮機
　１　密閉容器
　２　圧縮機構部
　３　フレーム
　４　クランク軸（駆動軸）
　４ｄ　給油流路
　５　主軸受
　６　旋回軸受
　７　電動機
　７ａ　固定子
　７ｂ　回転子
　１０　サブフレーム（固定部材）
　１０ａ　円筒部
　１０ｂ　脚
　１１　副軸受（ラジアル軸受）
　１２　給油ポンプ
　１２ａ　インナロータ（給油部）
　１２ｂ　アウタロータ（給油部）
　１２ｃ　ポンプカバー
　１２ｄ　ポンプケース
　１３　スラスト軸受
　１４　段付きボルト（結合部）
　１４ａ　ネジ部
　１４ｂ　中間部
　１４ｃ　頭部
　１５Ａ，１５Ｂ　ボルト（結合部）
　１５１Ａ，１５１Ｂ　ネジ部
　１５２Ａ、１５２Ｂ　頭部
　１６Ａ，１６Ｂ　スペーサ（結合部）
　Ｃ　圧縮室
　Ｅｉ　室内熱交換器（蒸発器／凝縮器）
　Ｅｏ　室外熱交換器（凝縮器／蒸発器）
　ＧＡ　隙間（軸方向の隙間）
　ＧＤ　隙間（径方向の隙間）
　Ｋ　冷媒回路
　Ｒ　油溜り
　Ｖｅ　膨張弁
　Ｗ　空気調和機（冷凍サイクル装置）
　ｎ　ネジ穴
　ｍ　ネジ溝 100, 100A, 100B Compressor 1 Sealed container 2 Compression mechanism 3 Frame 4 Crankshaft (drive shaft)
4d Refueling flow path 5 Main bearing 6 Swivel bearing 7 Electric motor 7a Stator 7b Rotor 10 Subframe (fixing member)
10a Cylindrical part 10b Leg 11 Sub-bearing (radial bearing)
12 Refueling pump 12a Inner rotor (refueling section)
12b Outer rotor (refueling section)
12c Pump cover 12d Pump case 13 Thrust bearing 14 Stepped bolt (joint)
14a Threaded part 14b Intermediate part 14c Head 15A, 15B Bolt (joint part)
151A, 151B Threaded part 152A, 152B Head 16A, 16B Spacer (joining part)
C Compression chamber Ei Indoor heat exchanger (evaporator / condenser)
Eo outdoor heat exchanger (condenser / evaporator)
GA gap (axial gap)
GD gap (diameter gap)
K Refrigerant circuit R Oil sump Ve Expansion valve W Air conditioner (refrigeration cycle device)
n screw hole m screw groove

Claims (7)

  1. 　潤滑油が通流する給油流路が設けられた駆動軸と、
    　前記駆動軸の回転に伴って、ガスを圧縮する圧縮機構部と、
    　前記駆動軸を軸支するラジアル軸受と、
    　前記ラジアル軸受を固定する固定部材と、
    　前記駆動軸の端部に設置される給油ポンプと、を備えるとともに、
    　前記固定部材と前記給油ポンプとの間に介在するスラスト軸受と、
    　前記スラスト軸受を前記固定部材に結合する結合部と、を備え、
    　前記給油ポンプは、前記給油流路に潤滑油を供給する給油部と、前記給油部を収容するポンプケースと、を少なくとも有し、
    　前記結合部は、前記ポンプケース及び前記スラスト軸受を貫通し、前記固定部材に結合されて前記スラスト軸受を固定しており、
    　前記スラスト軸受と前記ポンプケースとの間には軸方向の隙間が設けられている圧縮機。     A drive shaft provided with a lubrication flow path through which lubricating oil flows,
    A compression mechanism that compresses gas as the drive shaft rotates,
    Radial bearings that support the drive shaft and
    A fixing member for fixing the radial bearing and
    It is equipped with a refueling pump installed at the end of the drive shaft, and
    A thrust bearing interposed between the fixing member and the refueling pump,
    A joint portion for connecting the thrust bearing to the fixing member is provided.
    The refueling pump has at least a refueling unit that supplies lubricating oil to the refueling flow path and a pump case that houses the refueling unit.
    The coupling portion penetrates the pump case and the thrust bearing, and is coupled to the fixing member to fix the thrust bearing.
    A compressor in which an axial gap is provided between the thrust bearing and the pump case.
  2. 　前記結合部は、
    　前記固定部材のネジ穴に螺合するネジ溝が設けられたネジ部と、
    　前記ネジ部に連なり、前記ネジ部よりも径が大きい中間部と、
    　前記中間部に連なり、前記中間部よりも径がさらに大きい頭部と、を有する段付きボルトであり、
    　前記中間部と前記固定部材とによって、前記スラスト軸受が挟み込まれて固定されており、
    　前記スラスト軸受と前記ポンプケースとの間には前記軸方向の隙間が設けられ、
    　前記頭部によって、前記給油ポンプが支えられていること
    　を特徴とする請求項１に記載の圧縮機。     The joint
    A screw portion provided with a screw groove to be screwed into the screw hole of the fixing member, and a screw portion.
    An intermediate portion connected to the threaded portion and having a diameter larger than that of the threaded portion,
    A stepped bolt having a head connected to the intermediate portion and having a diameter larger than that of the intermediate portion.
    The thrust bearing is sandwiched and fixed by the intermediate portion and the fixing member.
    An axial gap is provided between the thrust bearing and the pump case.
    The compressor according to claim 1, wherein the refueling pump is supported by the head.
  3. 　前記結合部は、
    　前記固定部材のネジ穴に螺合するネジ溝が設けられたネジ部、及び、前記ネジ部よりも径が大きい頭部を有するボルトと、
    　円筒状のスペーサと、を含み、
    　前記スペーサには、前記ネジ部が挿通され、
    　前記スペーサと前記固定部材とによって、前記スラスト軸受が挟み込まれて固定されており、
    　前記スラスト軸受と前記ポンプケースとの間には前記軸方向の隙間が設けられ、
    　前記頭部によって、前記給油ポンプが支えられていること
    　を特徴とする請求項１に記載の圧縮機。     The joint
    A screw portion provided with a screw groove to be screwed into a screw hole of the fixing member, and a bolt having a head having a diameter larger than that of the screw portion.
    Includes a cylindrical spacer,
    The threaded portion is inserted through the spacer.
    The thrust bearing is sandwiched and fixed by the spacer and the fixing member.
    An axial gap is provided between the thrust bearing and the pump case.
    The compressor according to claim 1, wherein the refueling pump is supported by the head.
  4. 　前記結合部は、前記ポンプケースの一部と直接接触していること
    　を特徴とする請求項１から請求項３のいずれか一項に記載の圧縮機。     The compressor according to any one of claims 1 to 3, wherein the coupling portion is in direct contact with a part of the pump case.
  5. 　前記結合部と前記ポンプケースとの間には径方向の隙間が設けられていること
    　を特徴とする請求項１から請求項３のいずれか一項に記載の圧縮機。     The compressor according to any one of claims 1 to 3, wherein a gap in the radial direction is provided between the joint portion and the pump case.
  6. 　前記結合部と前記ポンプケースとの間の前記径方向の隙間の長さは、前記径方向の隙間を形成する範囲における前記結合部の軸径、又は、前記径方向の隙間を形成する範囲における前記ポンプケースの孔径の４％以上かつ１３％以下であり、
    　前記スラスト軸受と前記ポンプケースとの間の前記軸方向の隙間の長さは、前記軸方向の隙間を形成する範囲における前記結合部の軸方向の長さ、又は、前記軸方向の隙間の周囲における前記ポンプケースの上下方向の肉厚の１％以上かつ６％以下であること
    　を特徴とする請求項５に記載の圧縮機。     The length of the radial gap between the joint portion and the pump case is the shaft diameter of the joint portion in the range in which the radial gap is formed, or the range in which the radial gap is formed. 4% or more and 13% or less of the hole diameter of the pump case.
    The length of the axial gap between the thrust bearing and the pump case is the axial length of the coupling portion in the range forming the axial gap, or the circumference of the axial gap. The compressor according to claim 5, wherein the wall thickness in the vertical direction of the pump case is 1% or more and 6% or less.
  7. 　圧縮機、凝縮器、膨張弁、及び蒸発器を順次に介して冷媒が循環する冷媒回路を備え、
    　前記圧縮機は、
    　潤滑油が通流する給油流路が設けられた駆動軸と、
    　前記駆動軸の回転に伴って、ガス状の冷媒を圧縮する圧縮機構部と、
    　前記駆動軸を軸支するラジアル軸受と、
    　前記ラジアル軸受を固定する固定部材と、
    　前記駆動軸の端部に設置される給油ポンプと、を備えるとともに、
    　前記固定部材と前記給油ポンプとの間に介在するスラスト軸受と、
    　前記スラスト軸受を前記固定部材に結合する結合部と、を備え、
    　前記給油ポンプは、前記給油流路に潤滑油を供給する給油部と、前記給油部を収容するポンプケースと、を少なくとも有し、
    　前記結合部は、前記ポンプケース及び前記スラスト軸受を貫通し、前記固定部材に結合されて前記スラスト軸受を固定しており、
    　前記スラスト軸受と前記ポンプケースとの間には軸方向の隙間が設けられている冷凍サイクル装置。     It is equipped with a refrigerant circuit in which the refrigerant circulates sequentially through a compressor, a condenser, an expansion valve, and an evaporator.
    The compressor
    A drive shaft provided with a lubrication flow path through which lubricating oil flows,
    A compression mechanism that compresses the gaseous refrigerant as the drive shaft rotates,
    Radial bearings that support the drive shaft and
    A fixing member for fixing the radial bearing and
    It is equipped with a refueling pump installed at the end of the drive shaft, and
    A thrust bearing interposed between the fixing member and the refueling pump,
    A joint portion for connecting the thrust bearing to the fixing member is provided.
    The refueling pump has at least a refueling unit that supplies lubricating oil to the refueling flow path and a pump case that houses the refueling unit.
    The coupling portion penetrates the pump case and the thrust bearing, and is coupled to the fixing member to fix the thrust bearing.
    A refrigeration cycle device in which an axial gap is provided between the thrust bearing and the pump case.
PCT/JP2019/009961 2019-03-12 2019-03-12 Compressor and refrigeration cycle device WO2020183605A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09112441A (en) * 1995-10-23 1997-05-02 Hitachi Ltd Positive displacement pump and compressor
JP2004293530A (en) * 2003-03-28 2004-10-21 Hitachi Ltd Fluid compressor
JP2012097581A (en) * 2010-10-29 2012-05-24 Daikin Industries Ltd Compressor
JP2018119503A (en) * 2017-01-27 2018-08-02 パナソニックＩｐマネジメント株式会社 Hermetic compressor
JP2019007382A (en) * 2017-06-22 2019-01-17 日立ジョンソンコントロールズ空調株式会社 Scroll compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09112441A (en) * 1995-10-23 1997-05-02 Hitachi Ltd Positive displacement pump and compressor
JP2004293530A (en) * 2003-03-28 2004-10-21 Hitachi Ltd Fluid compressor
JP2012097581A (en) * 2010-10-29 2012-05-24 Daikin Industries Ltd Compressor
JP2018119503A (en) * 2017-01-27 2018-08-02 パナソニックＩｐマネジメント株式会社 Hermetic compressor
JP2019007382A (en) * 2017-06-22 2019-01-17 日立ジョンソンコントロールズ空調株式会社 Scroll compressor

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