US20210115917A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
US20210115917A1
US20210115917A1 US16/496,015 US201716496015A US2021115917A1 US 20210115917 A1 US20210115917 A1 US 20210115917A1 US 201716496015 A US201716496015 A US 201716496015A US 2021115917 A1 US2021115917 A1 US 2021115917A1
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United States
Prior art keywords
pressure
scroll
chamber
switching valve
pressure chamber
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Abandoned
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US16/496,015
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English (en)
Inventor
Hironobu Inaba
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Sanden Corp
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Sanden Holdings Corp
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Assigned to SANDEN HOLDINGS CORPORATION reassignment SANDEN HOLDINGS CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INABA, HIRONOBU
Publication of US20210115917A1 publication Critical patent/US20210115917A1/en
Abandoned legal-status Critical Current

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    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/025—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents the moving and the stationary member having co-operating elements in spiral form
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a scroll compressor that compresses fluid such as a gas refrigerant.
  • a scroll compressor includes a scroll unit having a fixed scroll and an orbiting scroll engaged with each other.
  • the orbiting scroll orbits about the axis of the fixed scroll to change the volume of the compression chamber defined by the fixed scroll and the orbiting scroll.
  • the scroll unit compresses the gas refrigerant and discharges the compressed gas refrigerant.
  • a back pressure is applied to the back surface of the orbiting scroll to press it against the fixed scroll so as to prevent or reduce the separation of the orbiting scroll from the fixed scroll during the compression operation, thereby minimizing the probability of compression failure.
  • the back pressure applied to the back surface of the orbiting scroll is adjusted using a back-pressure control valve disposed in a communication passage connecting the back-pressure chamber and the suction chamber in communication.
  • Patent Document 1 JP 2012-207606 A
  • the contamination In the back-pressure chamber, if contamination (foreign matter) is caused by, for example, abrasion of sliding portions, the contamination is introduced into the back-pressure control valve.
  • the contamination may, for example, clog a filter contained in the back-pressure control valve, and may disturb the functionality of the back-pressure control valve. As a result, the back-pressure control valve may become unable to properly adjust the back pressure.
  • an object of the present invention is to provide a scroll compressor in which functional disturbance of the back-pressure control valve caused by contamination can be reduced or prevented.
  • the scroll compressor includes: a scroll unit having a fixed scroll and an orbiting scroll; a discharge chamber into which fluid compressed by the scroll unit is discharged; a back-pressure chamber configured to apply a back pressure that presses the orbiting scroll against the fixed scroll; and a switching valve disposed at some midpoint of a communication passage connecting the discharge chamber and the back-pressure chamber in communication.
  • the switching valve is configured to switch between a first state in which the switching valve connects the discharge chamber with the back-pressure chamber in communication and a second state in which the switching valve connects the back-pressure chamber with a space external to the back-pressure chamber in communication, in accordance with an operational state of the scroll unit.
  • FIG. 1 is a vertical cross-sectional view of an example of a scroll compressor.
  • FIG. 2 is a block diagram for illustrating the flows of gas refrigerant and lubricating oil.
  • FIG. 3 is a cross-sectional view of a substantial part of a switching valve according to a first embodiment when the scroll compressor is in operation.
  • FIG. 4 is a cross-sectional view of the substantial part of the switching valve according to the first embodiment when the scroll compressor is not in operation.
  • FIG. 5 is a cross-sectional view of a substantial part of a switching valve according to a second embodiment when the scroll compressor is in operation.
  • FIG. 6 is a cross-sectional view of the substantial part of the switching valve according to the second embodiment when the scroll compressor is not in operation.
  • FIG. 7 is a cross-sectional view of a substantial part of a switching valve according to a third embodiment when the scroll compressor is in operation.
  • FIG. 8 is a cross-sectional view of the substantial part of the switching valve according to the third embodiment when the scroll compressor is not in operation.
  • FIG. 9 is a cross-sectional view of a substantial part of a switching valve according to a modification of the first embodiment.
  • FIG. 10 is a cross-sectional view of a substantial part of a switching valve according to a modification of the second embodiment.
  • FIG. 1 shows an example of a scroll compressor.
  • a scroll compressor 100 is incorporated, for example, in a refrigerant circuit (external device) of a vehicle air conditioner.
  • the scroll compressor 100 compresses a gas refrigerant (fluid) drawn from the low-pressure side of the refrigerant circuit and then discharges the compressed gas refrigerant.
  • the scroll compressor 100 includes a housing 200 , a scroll unit 300 for compressing a low-pressure gas refrigerant, an electric motor 400 for driving the scroll unit 300 , an inverter 500 for controlling the electric motor 400 , and a support member 600 rotatably supporting one end of a drive shaft 420 of the electric motor 400 .
  • Examples of the refrigerant in the refrigerant circuit may include a CO 2 (carbon dioxide) refrigerant.
  • the scroll compressor 100 is described as an inverter-integrated compressor herein, this is merely an illustrative example. Alternatively, the scroll compressor 100 may be separated from the inverter.
  • the housing 200 includes a front housing 220 , a rear housing 240 , and an inverter cover 260 .
  • the front housing 220 houses the scroll unit 300 , the electric motor 400 , the inverter 500 , and the support member 600 .
  • the rear housing 240 is fastened to one end of the front housing 220 .
  • the inverter cover 260 is fastened to the other end of the front housing 220 .
  • the front housing 220 , the rear housing 240 , and the inverter cover 260 are integrally fastened by a plurality of fasteners 700 including, for example, bolts and washers, so as to constitute the housing 200 of the scroll compressor 100 .
  • the front housing 220 is configured to include a cylindrical peripheral wall portion 222 and a disk-shaped partition wall portion 224 that divides the internal space surrounded by the peripheral wall portion 222 into two in the axial direction.
  • the term “cylindrical” refers to a substantially and seemingly cylindrical shape.
  • any cylindrical shape herein may have, for example, one or more ribs for reinforcement and bosses for attachment, etc. in the outer peripheral surface (the same also applies to other shape-related terms below).
  • the internal space of the front housing 220 is divided by the partition wall portion 224 into a first space 220 A for housing the scroll unit 300 , the electric motor 400 , and the support member 600 , and a second space 220 B for housing the inverter 500 .
  • the opening at the one end of the peripheral wall portion 222 is closed by the disk-shaped rear housing 240 .
  • the opening at the other end of the peripheral wall portion 222 is closed by the inverter cover 260 .
  • a cylindrical support portion 224 A is formed extending from the partition wall portion 224 toward the one end of the peripheral wall portion 222 .
  • the other end of the drive shaft 420 of the electric motor 400 is rotatably supported by the support portion 224 A via a bearing 720 press-fitted onto the inner peripheral surface of the support portion 224 A.
  • a suction port P 1 for drawing in gas refrigerant is formed in the peripheral wall portion 222 .
  • the gas refrigerant from the low-pressure side of the refrigerant circuit is drawn into the first space 220 A of the front housing 220 through the suction port P 1 .
  • the first space 220 A of the front housing 220 functions as a suction chamber H 1 for drawing in gas refrigerant.
  • the gas refrigerant flows around the electric motor 400 , thereby cooling the electric motor 400 .
  • spaces on axially opposite sides of the electric motor 400 communicate with each other so as to constitute the single suction chamber H 1 .
  • the gas refrigerant flows in the form of a mixed fluid containing a small amount of lubricating oil.
  • the rear housing 240 is fastened by the plurality of fasteners 700 to an opening at the one end of the peripheral wall portion 222 of the front housing 220 .
  • the rear housing 240 closes the opening at the one end of the front housing 220 .
  • the rear housing 240 also has a discharge port P 2 for discharging the gas refrigerant compressed by the scroll unit 300 to the high-pressure side of the refrigerant circuit.
  • an oil separator 740 is incorporated in the rear housing 240 .
  • the oil separator 740 is configured to separate lubricating oil from the gas refrigerant compressed by the scroll unit 300 .
  • the gas refrigerant from which the lubricating oil has been separated by the oil separator 740 (although not necessarily completely; a small amount of lubricating oil may be left in such gas refrigerant) is discharged to the high-pressure side of the refrigerant circuit through the discharge port P 2 . Meanwhile, the lubricating oil separated by the oil separator 740 is introduced to a back-pressure supply passage L 1 , which will be described in detail later.
  • the scroll unit 300 is housed in a portion, closer to the one end, of the front housing 220 .
  • the scroll unit 300 includes a fixed scroll 320 fixed to one surface of the rear housing 240 , and an orbiting scroll 340 disposed on a side, opposite to the rear housing 240 , of the fixed scroll 320 .
  • the fixed scroll 320 includes a disk-shaped bottom plate 322 fixed to one surface of the rear housing 240 , and an involute curve-shaped wrap (spiral blade) 324 extending from one surface of the bottom plate 322 to the orbiting scroll 340 .
  • the orbiting scroll 340 includes a disk-shaped bottom plate 342 disposed facing the bottom plate 322 of the fixed scroll 320 , and an involute curve-shaped wrap 344 extending from one surface of the bottom plate 342 to the fixed scroll 320 .
  • a crescent-shaped closed space that is, a compression chamber H 2 for compressing the gas refrigerant, is defined between the fixed scroll 320 and the orbiting scroll 340 .
  • a discharge passage L 2 for discharging the gas refrigerant compressed by the compression chamber H 2 is formed.
  • a discharge chamber H 3 for temporarily storing the gas refrigerant discharged from the compression chamber H 2 through the discharge passage L 2 is formed.
  • the discharge chamber H 3 is formed of a columnar recess.
  • a one-way valve 326 is attached to the other surface of the bottom plate 322 .
  • the one-way valve 326 is formed of, for example, a reed valve, and configured to permit the flow of the gas refrigerant from the compression chamber H 2 to the discharge chamber H 3 and block the flow of the gas refrigerant from the discharge chamber H 3 to the compression chamber H 2 .
  • the electric motor 400 is, for example, a three-phase alternating current motor, and includes the drive shaft 420 , a rotor 440 , and a stator core unit 460 disposed radially outside the rotor 440 .
  • the stator core unit 460 of the electric motor 400 is supplied with an alternating current to which a direct current from, for example, an in-vehicle battery (not shown) is converted by the inverter 500 .
  • the drive shaft 420 is connected to the orbiting scroll 340 via a crank mechanism, which will be described later, and transmits the rotational driving force of the electric motor 400 to the orbiting scroll 340 .
  • One end, which is closer to the orbiting scroll 340 , of the drive shaft 420 passes through a through hole 600 A formed in the support member 600 and is rotatably supported on a bearing 760 fixed to the support member 600 .
  • the other end of the drive shaft 420 is rotatably supported on the bearing 720 press-fitted into the support portion 224 A of the front housing 220 , as described above.
  • the rotor 440 is disposed radially inside the stator core unit 460 and rotatably supported on the drive shaft 420 that is fitted (e.g., press-fitted) into a shaft hole formed at the radial center of the rotor 440 .
  • a current is supplied to the electric motor 400 from the inverter 500 , a magnetic field is generated in the stator core unit 460 and a torque acts on the rotor 440 to rotationally drive the drive shaft 420 .
  • the support member 600 has a bottomed cylindrical shape having the same outer diameter as the bottom plate 322 of the fixed scroll 320 .
  • the inner peripheral surface of the support member 600 has a stepped columnar shape with two inner diameters, the larger of which is closer to the opening and the smaller of which is closer to the bottom.
  • the orbiting scroll 340 of the scroll unit 300 is housed in the space defined by the larger diameter portion of the inner peripheral surface of the support member 600 .
  • the surface at the open end of the support member 600 is fastened to the one surface of the bottom plate 322 of the fixed scroll 320 with, for example, a fastener (not shown).
  • the opening of the support member 600 is closed by the fixed scroll 320 so that a back-pressure chamber H 4 for pressing the orbiting scroll 340 against the fixed scroll 320 is defined.
  • the bearing 760 is fitted on the smaller diameter portion of the inner peripheral surface of the support member 600 .
  • the one end of the drive shaft 420 of the electric motor 400 is rotatably supported on the bearing 760 .
  • the through hole 600 A is formed at a radially center portion of the bottom wall located at the deepest position of the support member 600 .
  • the one end of the drive shaft 420 passes through the through hole 600 A.
  • a sealing member 780 is disposed between the bearing 760 and the bottom wall to ensure the airtightness of the back-pressure chamber H 4 .
  • annular thrust plate 800 is disposed between the bottom plate 342 of the orbiting scroll 340 and the step portion at which the smaller diameter portion and the larger diameter portion meet with each other.
  • the step portion of the support member 600 receives a thrust force from the orbiting scroll 340 via the thrust plate 800 .
  • Sealing members 820 for ensuring the airtightness of the back-pressure chamber H 4 are disposed at the step portion of the support member 600 and at a portion, in contact with the thrust plate 800 , of the bottom plate 342 of the orbiting scroll 340 .
  • the back-pressure supply passage L 1 is formed to extend through the rear housing 240 , the fixed scroll 320 , and the support member 600 .
  • the back-pressure supply passage L 1 Through the back-pressure supply passage L 1 , the lubricating oil separated by the oil separator 740 that is incorporated in the rear housing 240 is supplied to the back-pressure chamber H 4 that is defined by the support member 600 .
  • the lubricating oil supplied from the oil separator 740 to the back-pressure chamber H 4 is used as a back pressure that presses the orbiting scroll 340 against the fixed scroll 320 .
  • An orifice 840 for limiting the flow rate of the lubricating oil is disposed at some midpoint of the back-pressure supply passage L 1 .
  • the back-pressure supply passage L 1 is an example of a communication passage connecting the discharge chamber H 3 and the back-pressure chamber H 4 in communication.
  • a back-pressure control valve 860 is attached to the smaller inner diameter portion of the support member 600 .
  • the back-pressure control valve 860 operates in accordance with the back pressure Pm in the back-pressure chamber H 4 and the suction pressure Ps in the suction chamber H 1 so as to adjust the back pressure Pm in the back-pressure chamber H 4 accordingly.
  • the back-pressure control valve 860 opens and discharges the lubricating oil in the back-pressure chamber H 4 to the suction chamber H 1 .
  • the back pressure Pm in the back-pressure chamber H 4 decreases.
  • the back-pressure control valve 860 closes and stops discharging the lubricating oil from the back-pressure chamber H 4 to the suction chamber H 1 .
  • the back pressure Pm in the back-pressure chamber H 4 increases.
  • the back-pressure control valve 860 adjusts the back pressure Pm in the back-pressure chamber H 4 to the target pressure.
  • a refrigerant introduction passage L 3 is defined between the inner peripheral surface of the peripheral wall portion 222 of the front housing 220 and the outer peripheral surface of the support member 600 .
  • the refrigerant introduction passage L 3 connects the suction chamber H 1 and a space H 5 located in an outer peripheral portion of the scroll unit 300 in communication.
  • the gas refrigerant is introduced from the suction chamber H 1 to the space H 5 .
  • the pressure in the space H 5 is equal to the pressure in the suction chamber H 1 .
  • the crank mechanism has a cylindrical boss portion 880 , a crank pin 882 , an eccentric bushing 884 , and a slide bearing 886 .
  • the boss portion 880 is formed protruding from the other surface of the bottom plate 342 of the orbiting scroll 340 .
  • the crank pin 882 is eccentrically erected on the one end surface of the drive shaft 420 .
  • the eccentric bushing 884 is eccentrically mounted to the crank pin 882 .
  • the slide bearing 886 is fitted into the boss portion 880 .
  • the eccentric bushing 884 is supported by the boss portion 880 via the slide bearing 886 so as to be rotatable relative to the boss portion 880 .
  • a balancer weight 888 for balancing the centrifugal force of the orbiting scroll 340 is attached.
  • an anti-rotation mechanism that prevents the rotation of the orbiting scroll 340 is also provided. Accordingly, the orbiting scroll 340 is orbitable about the axis of the fixed scroll 320 via the crank mechanism in a state in which the rotation of the orbiting scroll 340 is prevented.
  • FIG. 2 is a block diagram for illustrating the flows of gas refrigerant and lubricating oil.
  • the gas refrigerant from the low-pressure side of the refrigerant circuit is introduced into the suction chamber H 1 through the suction port P 1 , and it is then introduced into the space H 5 located in the outer peripheral portion of the scroll unit 300 through the refrigerant introduction passage L 3 .
  • the gas refrigerant is then taken into the compression chamber H 2 of the scroll unit 300 , and compressed as the volume of the compression chamber H 2 changes.
  • the gas refrigerant is discharged into the discharge chamber H 3 through the discharge passage L 2 and the one-way valve 326 , and it is then introduced into the oil separator 740 .
  • the gas refrigerant from which the lubricating oil has been separated by the oil separator 740 is discharged to the high-pressure side of the refrigerant circuit through the discharge port P 2 . Meanwhile, the lubricating oil separated by the oil separator 740 is supplied to the back-pressure chamber H 4 through the back-pressure supply passage L 1 at a flow rate restricted by the orifice 840 . After being supplied to the back-pressure chamber H 4 , the lubricating oil is discharged into the suction chamber H 1 via the back-pressure control valve 860 .
  • the lubricating oil supplied to the back-pressure chamber H 4 is used as a back pressure that presses the orbiting scroll 340 against the fixed scroll 320 as well as to lubricate sliding portions in the back-pressure chamber H 4 and the like.
  • contamination caused by, for example, abrasion of such sliding portions may be mixed in the lubricating oil present in the back-pressure chamber H 4 .
  • the contamination may clog the filter contained in the back-pressure control valve 860 for adjusting the back pressure Pm in the back-pressure chamber H 4 . This may disturb the functionality of the back-pressure control valve 860 , and the back-pressure control valve 860 may become unable to properly adjust the back pressure.
  • a switching valve 900 is disposed at some midpoint of a portion, downstream of the orifice 840 , of the back-pressure supply passage L 1 .
  • the switching valve 900 is configured to discharge the lubricating oil in the back-pressure chamber H 4 into the suction chamber H 1 when the scroll unit 300 of the scroll compressor 100 stops its operation.
  • the switching valve 900 autonomously switches between a first state and a second state in accordance with the suction pressure Ps in the suction chamber H 1 , the discharge pressure Pd in the discharge chamber H 3 , and the back pressure Pm in the back-pressure chamber H 4 .
  • the switching valve 900 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication.
  • the switching valve 900 connects the back-pressure chamber H 4 with the suction chamber H 1 in communication.
  • the switching valve 900 switches to the first state and permits the supply of a back pressure to the back-pressure chamber H 4 .
  • the switching valve 900 switches to the second state and discharges the lubricating oil present in the back-pressure chamber H 4 to the suction chamber H 1 . This reduces an absolute amount of contamination introduced into the back-pressure control valve 860 and prevents or reduces functional disturbance of the back-pressure control valve 860 .
  • the back-pressure supply passage L 1 is bent at an acute angle at a point downstream of the orifice 840 , and the downstream end of the back-pressure supply passage L 1 opens to the back-pressure chamber H 4 .
  • a larger diameter hole 600 B is formed in a portion, facing the bend of the back-pressure supply passage L 1 , of the outer surface of the support member 600 .
  • the larger diameter hole 600 B has a diameter larger than that of the back-pressure supply passage L 1 and extends to the bend of the back-pressure supply passage L 1 .
  • An annular valve seat 600 C is formed at the deepest portion, through which the back-pressure supply passage L 1 extends, of the larger diameter hole 600 B.
  • FIGS. 3 and 4 show a first embodiment of the switching valve 900 .
  • the switching valve 900 is housed in the larger diameter hole 600 B formed in the support member 600 .
  • the switching valve 900 includes a holder 920 , a valve member 940 , a compression coil spring 960 , and an O-ring 980 .
  • the holder 920 has a bottomed cylindrical shape with an opening at one end in the axial direction.
  • the valve member 940 is disposed axially displaceably with respect to the holder 920 .
  • the compression coil spring 960 is disposed between the bottom wall of the holder 920 A and the valve member 940 .
  • the holder 920 is press-fitted and fixed into the larger diameter hole 600 B so that its bottom wall partially closes the opening of the larger diameter hole 600 B.
  • a through hole 920 A is formed in a center portion of the bottom wall of the holder 920 , so that the discharge chamber H 3 and the suction chamber H 1 can communicate with each other through the through hole 920 A and the back-pressure supply passage L 1 .
  • the valve member 940 is a kind of so-called poppet valve, and includes a truncated conical head portion 940 A and a columnar stem portion 940 B disposed coaxially with the head portion 940 A.
  • the stem portion 940 B of the valve member 940 is inserted into the holder 920 with an annular gap between the stem portion 940 B and the inner peripheral surface of the holder 920 .
  • the valve member 940 Being axially displaceable with respect to the holder 920 , the valve member 940 is capable of coming into contact with and separating from the valve seat 600 C located at the deepest portion of the larger diameter hole 600 B.
  • the compression coil spring 960 biases the valve member 940 toward the valve seat 600 C.
  • the O-ring 980 is fitted into a circumferential groove formed in the outer peripheral surface of the stem portion 940 B of the valve member 940 .
  • the O-ring 980 ensures the airtightness between the inner peripheral surface of the holder 920 and the outer peripheral surface of the stem portion 940 B when the switching valve 900 is switched to the first state in which the switching valve 900 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication.
  • the scroll unit 300 When the scroll unit 300 is in operation, it is necessary to supply the lubricating oil separated by the oil separator 740 to the back-pressure chamber H 4 .
  • the valve member 940 of the switching valve 900 when the scroll unit 300 is in operation, the valve member 940 of the switching valve 900 is moved away from the valve seat 600 C of the support member 600 , as shown in FIG. 3 .
  • the switching valve 900 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication and blocks communication between the suction chamber H 1 and the discharge chamber H 3 and between the suction chamber H 1 and the back-pressure chamber H 4 .
  • the suction pressure Ps in the suction chamber H 1 , the discharge pressure Pd in the discharge chamber H 3 , and the back pressure Pm in the back-pressure chamber H 4 satisfy the relationship: suction pressure Ps ⁇ back pressure Pm ⁇ discharge pressure Pd.
  • the valve member 940 is biased by a valve closing biasing force of the compression coil spring 960 , and pressed by a valve closing force caused by the suction pressure Ps as well as a valve opening force caused by the back pressure supplied from the orifice 840 .
  • the spring coefficient and natural length of the compression coil spring 960 , the suction pressure Ps applied to the valve member 940 , and the pressure receiving area of the back pressure supplied from the orifice 840 , etc. may be appropriately determined in consideration of the operation characteristics of the scroll compressor 100 . Thus, these factors may be appropriately determined so that when the scroll unit 300 is in operation, the switching valve 900 is switched to the first state in which the switching valve 900 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication.
  • the lubricating oil present in the back-pressure chamber H 4 is to be discharged to the suction chamber H 1 so as to ensure that contamination mixed in the lubricating oil is not introduced into the back-pressure control valve 860 .
  • the valve member 940 of the switching valve 900 is in contact with the valve seat 600 C of the support member 600 so as to block communication between the discharge chamber H 3 and the back-pressure chamber H 4 while providing communication between the back-pressure chamber H 4 and the suction chamber H 1 , as shown in FIG. 4 .
  • the spring coefficient and natural length of the compression coil spring 960 may be appropriately determined in consideration of the operation characteristics of the scroll compressor 100 so that when the scroll unit 300 is not in operation, the switching valve 900 is switched to the second state in which the switching valve 900 connects the back-pressure chamber H 4 with the suction chamber H 1 in communication.
  • the contamination mixed in the lubricating oil that is present in the back-pressure chamber H 4 settles as a precipitate by gravity.
  • disposing the switching valve 900 vertically below the back-pressure chamber H 4 facilitates discharging the contamination that has settled in the back-pressure chamber H 4 into the suction chamber H 1 together with the lubricating oil. This reduces the absolute amount of contamination remaining in the back-pressure chamber H 4 , and thus, for example, minimizes the probability that the contamination can be introduced into the back-pressure control valve 860 and can clog the filter contained in the back-pressure control valve 860 when the scroll unit 300 is restarted.
  • This technical concept is also applicable to the second and third embodiments of the switching valve 900 described below.
  • FIGS. 5 and 6 show a second embodiment of the switching valve 900 .
  • the reference numeral “ 1000 ” will be assigned to the switching valve of the second embodiment.
  • the same features as those of the switching valve 900 according to the first embodiment will be described briefly to avoid duplicate description. Please also refer to the description for the first embodiment, if necessary.
  • the switching valve 1000 is housed in the larger diameter hole 600 B formed in the support member 600 .
  • the switching valve 1000 includes a holder 1020 , a valve member 1040 , a compression coil spring 1060 , and an O-ring 1080 .
  • the holder 1020 has a bottomed cylindrical shape with an opening at one end in the axial direction.
  • the valve member 1040 is disposed axially displaceably with respect to the holder 1020 .
  • the compression coil spring 1060 is disposed between the bottom wall of the holder 1020 and the valve member 1040 .
  • the valve member 1040 has a stepped columnar shape with two diameters, the larger of which is closer to the valve seat 600 C of the support member 600 in order, for example, to facilitate the manufacture of the valve member 1040 .
  • the valve member 1040 is adapted such that the free end surface of the larger diameter portion can come into contact with and separate from the valve seat 600 C.
  • the valve member 1040 provides operational advantages and effects similar to those described in the first embodiment. Thus, description therefor will be omitted.
  • FIGS. 7 and 8 show a third embodiment of the switching valve 900 .
  • the reference numeral “ 1100 ” will be assigned to the switching valve of the third embodiment.
  • the same features as those of the switching valve 900 according to the first embodiment will be described briefly to avoid duplicate description. Please also refer to the description for the first embodiment, if necessary.
  • the switching valve 1100 is housed in the larger diameter hole 600 B formed in the support member 600 .
  • the switching valve 1100 includes a holder 1120 , a valve member 1140 , a compression coil spring 1160 , and an O-ring 1180 .
  • the holder 1120 has a bottomed cylindrical shape with an opening at one end in the axial direction.
  • the valve member 1140 has a columnar shape and is disposed axially displaceably with respect to the holder 1020 .
  • the compression coil spring 1160 is disposed between the bottom wall of the holder 1120 and the valve member 1140 .
  • the scroll unit 300 When the scroll unit 300 is in operation, it is necessary to supply the lubricating oil separated by the oil separator 740 to the back-pressure chamber H 4 .
  • the valve member 1140 of the switching valve 1100 when the scroll unit 300 is in operation, the valve member 1140 of the switching valve 1100 is moved away from the valve seat 600 C of the support member 600 , as shown in FIG. 7 .
  • the switching valve 1100 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication and blocks communication between the suction chamber H 1 and the discharge chamber H 3 and between the suction chamber H 1 and the back-pressure chamber H 4 .
  • the suction pressure Ps in the suction chamber H 1 , the discharge pressure Pd in the discharge chamber H 3 , and the back pressure Pm in the back-pressure chamber H 4 satisfy the relationship: suction pressure Ps ⁇ back pressure Pm ⁇ discharge pressure Pd.
  • the valve member 1140 is biased by a valve closing biasing force of the compression coil spring 1160 , and pressed by a valve closing force caused by the suction pressure Ps as well as a valve opening force caused by the back pressure supplied from the orifice 840 .
  • the spring coefficient and natural length of the compression coil spring 1160 , the suction pressure Ps applied to the valve member 1140 , and the pressure receiving area of the back pressure supplied from the orifice 840 , etc. may be appropriately determined in consideration of the operation characteristics of the scroll compressor 100 . Thus, these factors may be appropriately determined so that when the scroll unit 300 is in operation, the switching valve 1100 is switched to the first state in which the switching valve 1100 connects the discharge chamber H 3 with the back-pressure chamber H 4 in communication.
  • the lubricating oil present in the back-pressure chamber H 4 is to be discharged to the suction chamber H 1 so as to ensure that contamination mixed in the lubricating oil is not introduced into the back-pressure valve 860 .
  • the valve member 1140 of the switching valve 1100 is in contact with the valve seat 600 C of the support member 600 so as to block communication between the discharge chamber H 3 and the back-pressure chamber H 4 while providing communication between the back-pressure chamber H 4 and the suction chamber H 1 , as shown in FIG. 8 .
  • the spring coefficient and natural length of the compression coil spring 1160 may be appropriately determined in consideration of the operation characteristics of the scroll compressor 100 so that when the scroll unit 300 is not in operation, the switching valve 1100 is switched to the second state in which the switching valve 1100 connects the back-pressure chamber H 4 with the suction chamber H 1 in communication.
  • recesses 940 C and 1040 A may be formed in the free end surfaces of the valve members 940 and 1040 , respectively.
  • each of the recesses 940 C and 1040 A may be formed so as to extend internally from the end surface at a position facing the back-pressure supply passage L 1 . This allows the switching valve 900 and 1000 to receive the lubricating oil having passed through the orifice 840 , and thus, to receive an increased valve opening force caused by the discharge pressure Pd.
  • the scroll compressor 100 may be configured such that an externally supplied force is used to drive the drive shaft 420 .
  • each of the switching valves 900 , 1000 , and 1100 does not have to be disposed in a portion, downstream of the orifice 840 , of the back-pressure supply passage L 1 , and may alternatively be disposed in a portion, upstream of the orifice 840 , of the back-pressure supply passage L 1 .
  • the switching valves 900 , 1000 , and 1100 need not necessarily be configured to provide communication between the back-pressure chamber H 4 and the suction chamber H 1 when the scroll unit 300 is not in operation.
  • the switching valves 900 , 1000 , and 1100 may be configured to provide communication between the back-pressure chamber H 4 and the space H 5 , which is located in the outer peripheral portion of the scroll unit 300 , when the scroll unit 300 is not in operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US16/496,015 2017-03-22 2017-02-13 Scroll compressor Abandoned US20210115917A1 (en)

Applications Claiming Priority (3)

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JP2017-055566 2017-03-22
JP2017055566A JP2018159285A (ja) 2017-03-22 2017-03-22 スクロール型圧縮機
PCT/JP2018/004815 WO2018173543A1 (ja) 2017-03-22 2018-02-13 スクロール型圧縮機

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US20210115917A1 true US20210115917A1 (en) 2021-04-22

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US16/496,015 Abandoned US20210115917A1 (en) 2017-03-22 2017-02-13 Scroll compressor

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US (1) US20210115917A1 (de)
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CN (1) CN110462217A (de)
DE (1) DE112018001526T5 (de)
WO (1) WO2018173543A1 (de)

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JP2022052828A (ja) * 2020-09-24 2022-04-05 サンデン・オートモーティブコンポーネント株式会社 スクロール型圧縮機
DE102020129864A1 (de) * 2020-11-12 2022-05-12 Hanon Systems Vorrichtung zum Verdichten eines gasförmigen Fluids

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Publication number Priority date Publication date Assignee Title
JPS58176489A (ja) * 1982-04-09 1983-10-15 Hitachi Ltd 電動圧縮機
JPH0350308Y2 (de) * 1986-01-13 1991-10-28
JP2816209B2 (ja) * 1989-11-29 1998-10-27 株式会社日立製作所 スクロール圧縮機
JP3252495B2 (ja) * 1992-12-01 2002-02-04 株式会社日立製作所 スクロール圧縮機
JPH08296570A (ja) * 1995-04-25 1996-11-12 Hitachi Ltd スクロール型液冷媒ポンプ
JP2000314382A (ja) * 1999-05-06 2000-11-14 Hitachi Ltd スクロール圧縮機
JP2010096040A (ja) * 2008-10-15 2010-04-30 Toyota Industries Corp スクロール型圧縮機
JP5551644B2 (ja) 2011-03-30 2014-07-16 日立アプライアンス株式会社 スクロール圧縮機
JP2014070588A (ja) * 2012-09-28 2014-04-21 Daikin Ind Ltd スクロール圧縮機

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WO2018173543A1 (ja) 2018-09-27
DE112018001526T5 (de) 2019-12-05
JP2018159285A (ja) 2018-10-11

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