WO2020183605A1 - Compresseur et dispositif à cycle de réfrigération - Google Patents

Compresseur et dispositif à cycle de réfrigération 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
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English (en)
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/fr
Publication of WO2020183605A1 publication Critical patent/WO2020183605A1/fr

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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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur et analogues présentant une configuration simple et une haute fiabilité. Un boulon à épaulement (14) du compresseur (100) est inséré dans un corps de pompe (12d) et un palier de butée (13) pour venir en prise avec un trou fileté ménagé dans un faux cadre (10). Le palier de butée (13) est fixé en étant pris en sandwich entre le boulon à épaulement (14) et le faux cadre (10). Un espace radial est ménagé entre le boulon à épaulement (14) et le corps de pompe (12d), un espace axial est prévu entre le palier de butée (13) et le corps de pompe (12d), et une pompe d'alimentation en huile (12) est supportée par le boulon à épaulement (14).
PCT/JP2019/009961 2019-03-12 2019-03-12 Compresseur et dispositif à cycle de réfrigération WO2020183605A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09112441A (ja) * 1995-10-23 1997-05-02 Hitachi Ltd 容積型ポンプ及び圧縮機
JP2004293530A (ja) * 2003-03-28 2004-10-21 Hitachi Ltd 流体圧縮機
JP2012097581A (ja) * 2010-10-29 2012-05-24 Daikin Industries Ltd 圧縮機
JP2018119503A (ja) * 2017-01-27 2018-08-02 パナソニックＩｐマネジメント株式会社 密閉型圧縮機
JP2019007382A (ja) * 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 スクロール圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09112441A (ja) * 1995-10-23 1997-05-02 Hitachi Ltd 容積型ポンプ及び圧縮機
JP2004293530A (ja) * 2003-03-28 2004-10-21 Hitachi Ltd 流体圧縮機
JP2012097581A (ja) * 2010-10-29 2012-05-24 Daikin Industries Ltd 圧縮機
JP2018119503A (ja) * 2017-01-27 2018-08-02 パナソニックＩｐマネジメント株式会社 密閉型圧縮機
JP2019007382A (ja) * 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 スクロール圧縮機

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