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WO2011118562A1 - Machine hydraulique - Google Patents

Machine hydraulique Download PDF

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Publication number
WO2011118562A1
WO2011118562A1 PCT/JP2011/056757 JP2011056757W WO2011118562A1 WO 2011118562 A1 WO2011118562 A1 WO 2011118562A1 JP 2011056757 W JP2011056757 W JP 2011056757W WO 2011118562 A1 WO2011118562 A1 WO 2011118562A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
drive shaft
rotating body
fluid machine
unit
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2011/056757
Other languages
English (en)
Japanese (ja)
Inventor
中村　慎二
和田　博文
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
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.)
Filing date
Publication date
Priority claimed from JP2010067991A external-priority patent/JP2010249130A/ja
Application filed by Sanden Corp filed Critical Sanden Corp
Priority to CA2792544A priority Critical patent/CA2792544A1/fr
Priority to CN2011800154983A priority patent/CN102812207A/zh
Priority to US13/636,987 priority patent/US20130017114A1/en
Priority to EP11759367.3A priority patent/EP2551449A4/fr
Priority to KR1020127025858A priority patent/KR20120139770A/ko
Publication of WO2011118562A1 publication Critical patent/WO2011118562A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0215—Rotary-piston machines or engines 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • 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
    • F04C23/005—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 of dissimilar working principle
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors

Definitions

  • the present invention relates to a fluid machine, and more particularly, to a fluid machine suitable for use in a Rankine circuit of a vehicle waste heat utilization device.
  • a Rankine circuit constituting a waste heat utilization system of an internal combustion engine such as a vehicle engine has a circulation path through which a working fluid (heat medium) circulates, and the circulation path includes a pump, an evaporator (heat exchanger), An expander and a condenser are sequentially inserted.
  • the pump is driven by, for example, an electric motor and circulates the working fluid.
  • the working fluid passes through the evaporator, it receives waste heat and expands in the expander.
  • the thermal energy of the working fluid is converted into torque and output to the outside, and is used, for example, to rotate a fan for air-cooling the condenser.
  • Patent Document 1 discloses a fluid machine in which a pump, an expander, and a motor share one drive shaft as a fluid machine suitable for such a Rankine circuit.
  • the fluid machine in which a plurality of fluid units described above are connected tends to become longer and larger in the axial direction of the drive shaft.
  • special consideration is given to promoting the downsizing of the fluid machine. Absent.
  • the present invention has been made based on the above-described circumstances, and an object of the present invention is to provide a fluid machine capable of improving production efficiency and maintainability while also ensuring performance and realizing downsizing. It is in.
  • the fluid machine of the present invention has a rotating body, a plurality of fluid units for flowing in and out of working fluid as the rotating body rotates, and a drive shaft to which the rotating bodies of the plurality of fluid units are coupled.
  • an Oldham coupling is provided at a shaft portion between the rotating bodies of the drive shaft.
  • the Oldham coupling includes a slider including a locking portion with respect to the shaft portion and a main body portion on which the locking portion is formed, and the slider is formed in a receiving hole formed in the shaft portion. Be contained.
  • each of the plurality of fluid units includes a first rotating body, and receives the working fluid while expanding the first rotating body, expands the received working fluid, and then delivers the working fluid.
  • the plurality of fluid units include a second rotating body, sucks the working fluid as the second rotating body rotates, boosts the sucked working fluid, and then discharges the working fluid. including.
  • each of the plurality of fluid units includes a third rotating body, sucks the working fluid as the third rotating body rotates, compresses the sucked working fluid, and sends the compressed working fluid.
  • a power generation unit that has a fourth rotating body coupled to the drive shaft and generates electric power as the fourth rotating body rotates.
  • it has a fifth rotating body connected to the drive shaft, and generates electric power with the rotation of the fifth rotating body, while rotating the fifth rotating body with external electric power, And a power generation drive unit that drives the drive shaft in accordance with the rotation of the rotary body 5.
  • a power transmission unit connected to the drive shaft and transmitting power between the drive shaft and the outside is provided.
  • the Oldham coupling is provided in the shaft portion between the rotating bodies of the drive shaft, so that each fluid unit is separated and independent by the Oldham coupling at the time of manufacturing the fluid machine, and the operation evaluation of the fluid unit is performed individually.
  • the production efficiency can be improved while ensuring the performance of the fluid machine.
  • the Oldham coupling is a simple structure as compared with a fastening structure using a spline or the like, and therefore, the centering operation at the time of evaluating the operation of the fluid unit can be performed relatively easily. This contributes to further improvement in production efficiency of the fluid machine.
  • the Oldham coupling allows a displacement in the radial direction of the shaft, while reducing a rotation angle error caused by a shaft misalignment (eccentricity, declination), and can transmit the rotation angle with high accuracy. Since the shaft misalignment at the time of integrating a plurality of fluid units is allowed, the performance of the fluid machine can be ensured. Further, according to the present invention, it is possible to prevent the slider from dropping off when assembling the shaft portion opposed to the shaft portion via the slider, thereby deteriorating workability when the fluid machine is assembled. Specifically, the slider can be effectively prevented from falling off during the centering operation during the fluid unit operation evaluation, and the centering operation can be more easily performed. Can be improved.
  • the slider can be embedded in the shaft after the fluid machine is assembled, the length of the shaft, and hence the length of the drive shaft, can be shortened by the length of the slider. The size can be reduced.
  • FIG. 1 It is a figure showing roughly composition of a waste heat utilization device of vehicles provided with a fluid machine concerning a 1st embodiment. It is a schematic longitudinal cross-sectional view of the fluid machine applied to the apparatus of FIG. It is a schematic longitudinal cross-sectional view of the fluid machine which concerns on 2nd Embodiment. It is a schematic longitudinal cross-sectional view of the fluid machine which concerns on 3rd Embodiment. It is a schematic longitudinal cross-sectional view of the fluid machine which concerns on 4th Embodiment. It is the perspective view which showed the accommodation hole of FIG. It is the perspective view which showed the slider of FIG. It is the perspective view which showed the end surface of the to-be-driven shaft part of FIG.
  • FIG. 10 is a plan view illustrating a state in which the hub is slightly rotated in the circumferential direction of the shaft portion when the fluid machine is assembled in FIG. 9.
  • FIG. 1 shows a waste heat utilization device 1 for using a fluid machine 14 according to the first embodiment.
  • the waste heat utilization device 1 is, for example, an exhaust gas discharged from an engine (internal combustion engine) 10 of a vehicle. Recover heat.
  • the waste heat utilization apparatus 1 includes a Rankine circuit 12, and the Rankine circuit 12 has a circulation path 13 through which a working fluid (heat medium) circulates.
  • the circulation path 13 is constituted by, for example, a pipe or a pipe.
  • a pump unit (fluid unit) 16 of a fluid machine 14 is inserted in the circulation path 13 to cause the working fluid to flow. Further, a heater 18 is disposed downstream of the pump unit 16 in the direction in which the working fluid flows.
  • the expansion unit (fluid unit) 20 and the condenser 22 of the fluid machine 14 are sequentially inserted. That is, the pump unit 16 sucks the working fluid on the condenser 22 side, boosts the sucked working fluid, and then discharges the working fluid toward the heater 18.
  • the working fluid discharged from the pump unit 16 is in a low-temperature and high-pressure liquid state.
  • the heater 18 is a heat exchanger, and includes a low-temperature channel 18a constituting a part of the circulation path 13 and a high-temperature channel 18b capable of exchanging heat between the low-temperature channel 18a.
  • the high temperature flow path 18b is inserted in an exhaust pipe 24 extending from the engine 10, for example. Accordingly, when passing through the heater 18, the low-temperature and high-pressure liquid working fluid receives the heat of the exhaust gas generated by the engine 10. As a result, the working fluid is heated to a high-temperature and high-pressure superheated steam state.
  • the expansion unit 20 of the fluid machine 14 expands the working fluid that has been in a superheated steam state, and thereby the working fluid is in a high-temperature and low-pressure superheated steam state.
  • the condenser 22 is a heat exchanger, which condenses the working fluid that has flowed out of the expansion unit 20 by heat exchange with the outside air to form a low-temperature and low-pressure liquid state.
  • an electric fan (not shown) is disposed in the vicinity of the condenser 22, and the working fluid is cooled by wind from the front of the vehicle or wind from the electric fan.
  • the working fluid cooled by the condenser 22 is again sucked into the pump unit 16 and circulates in the circulation path 13.
  • the expansion unit 20 described above can not only expand the working fluid but also convert the thermal energy of the working fluid into torque (rotational force) and output it.
  • a power generation unit 26 is connected to the expansion unit 20 so that torque output from the expansion unit 20 can be used.
  • the power generation unit 26 is appropriately connected with an electrical load 28 such as a battery that uses or stores the generated power.
  • the fluid machine 14 has a power transmission unit 30 for inputting and outputting torque, and the power transmission unit 30 is, for example, an electromagnetic clutch.
  • the electromagnetic clutch is operated by an ECU (electronic control unit) 31 and can transmit torque intermittently. More specifically, as shown in FIG. 2, the expansion unit 20, the power generation unit 26, and the pump unit 16 are connected in series in this order via the drive shaft 72, and the drive shaft 72 is connected to the power generation unit 26 and the expansion unit.
  • a drive shaft portion 72A on the unit 20 side, a driven shaft portion 72B on the pump unit 16 side, and a slider 87 disposed between the shaft portions 72A and 72B are provided.
  • the expansion unit 20 is a scroll type expander having the turning mechanism 21 as a drive unit.
  • the opening of the cup-shaped casing 32 (expansion unit casing) of the expansion unit 20 is substantially covered by the partition wall 34, and a through hole is formed at the center of the partition wall 34.
  • a fixed scroll 36 is fixed in the expansion unit casing 32, and a high-pressure chamber 38 is defined on the back side of the fixed scroll 36.
  • the high pressure chamber 38 communicates with the heater 18 via an inlet port formed in the expansion unit casing 32 and a part of the circulation path 13 connected to the inlet port.
  • a movable scroll (rotating body, first rotating body) 40 is arranged on the front side of the fixed scroll 36 so as to be engaged.
  • An expansion chamber 42 for expanding the working fluid is defined between the fixed scroll 36 and the movable scroll 40, and the periphery of the movable scroll 40 is defined as a low pressure chamber 44 for receiving the expanded working fluid.
  • An introduction hole 46 is formed through substantially the center of the substrate of the fixed scroll 36, and the expansion chamber 42 and the high-pressure chamber 38 located at the center in the radial direction of the fixed and movable scrolls 36 and 40 communicate with each other through the introduction hole 46. To do.
  • the volume of the expansion chamber 42 increases and the expansion chamber 42 moves radially outward along the spiral walls of the fixed and movable scrolls 36 and 40.
  • the expansion chamber 42 finally communicates with the low pressure chamber 44, and the expanded working fluid flows into the low pressure chamber 44.
  • the low pressure chamber 44 communicates with the condenser 22 through an outlet port (not shown) and a part of the circulation path 13 connected to the outlet port.
  • the orbiting scroll 40 With the expansion of the working fluid, the orbiting scroll 40 is caused to make a revolving orbiting motion with respect to the fixed scroll 36, and this orbiting orbiting motion is converted into a rotational motion by the orbiting mechanism 21. That is, a boss is integrally formed on the rear surface of the substrate of the movable scroll 40, and an eccentric bush 50 is disposed in the boss via the needle bearing 48 so as to be relatively rotatable. A crankpin 52 is inserted into the eccentric bush 50, and the crankpin 52 protrudes eccentrically from the disk-shaped disk 54.
  • a shaft portion 56 is coaxially projected integrally, and the shaft portion 56 is rotatably supported by the partition wall 34 via a radial bearing 58 such as a ball bearing, and is one-way.
  • the drive shaft 72A is connected via a clutch 95. That is, the movable scroll 40 is rotatably supported by the partition wall 34, and the revolving turning motion of the movable scroll 40 is converted into the rotational motion of the shaft portion 56, and the rotational motion is transmitted to the drive shaft portion 72A.
  • the turning mechanism 21 has, for example, a ball coupling 60 to prevent the rotation of the movable scroll 40 during the revolution turning motion and to receive a thrust pressure.
  • the ball coupling 60 is an outer periphery of the substrate of the movable scroll 40. Between the portion and the portion of the partition wall 34 facing the outer peripheral portion.
  • the fixed and movable scrolls 36 and 40 are in sliding contact with each other with a slight gap.
  • the fixed and movable scrolls 36 and 40 are configured by substrates 36a and 40a and spiral wraps 36b and 40b provided integrally on the inner surfaces of the substrates 36a and 40a, respectively.
  • Tip seals 37 are respectively provided at the tips of the spiral wraps 36b and 40b, and the spiral wraps 36b and 40b and the substrates 40a and 36a disposed to face the spiral seals 36b and 40b, respectively, are provided via the tip seals 37.
  • An expansion chamber 42 having a spiral shape around the axis of the substrates 36a, 40a is formed by causing the spiral walls of the spiral wraps 36b, 40b to slidably contact each other with a slight gap therebetween.
  • the gaps between the spiral wraps 36b, 40b and the substrates 40a, 36a arranged opposite to each other, that is, the gaps between the fixed and movable scrolls 36, 40 are the coupling surfaces of the expansion unit casing 32 and the partition wall 34. Secured by between.
  • Each coupling surface is constituted by an end wall 32a of the expansion unit casing 32 and an end wall 34a of the partition wall 34.
  • a shim 39 which is a metal annular sandwich plate Is pinched.
  • the gap length between the fixed and movable scrolls 36 and 40 is adjusted by changing the thickness and quantity of the shim 39, so that the expansion unit During the operation of 20, the pressing force in the axial direction of the drive shaft 72 against the fixed scroll 36 of the movable scroll 40 is evenly and reliably received on the expansion unit casing 32 side.
  • the adjustment of the gap length between the fixed and movable scrolls 36 and 40 is performed for the purpose of evaluating the operation of the expansion unit 20 as to whether or not the movable scroll 36 smoothly revolves around the fixed scroll 40.
  • the clearance length is adjusted when the fixed and movable scrolls 36 and 40 are temporarily attached to each other, and a torque sensor (evaluator) such as a motor (not shown) is connected to the drive shaft 72A to rotate the drive shaft 72A.
  • the load torque of the fixed and movable scrolls 36 and 40 is estimated from this load torque. If the gap length between the fixed and movable scrolls 36 and 40 estimated from the load torque measurement value is within the clearance allowable range defined by the upper limit value and the lower limit value, the fixed and movable scrolls 36 and 40 are fully installed. To do.
  • the gap length between the fixed and movable scrolls 36 and 40 is managed by the load torque inspection process which is one of the manufacturing processes of the fluid machine 14.
  • the pump unit 16 is a trochoid pump, for example, but may be a circumscribed gear pump.
  • the pump unit 16 has a cylindrical casing (pump unit casing 62) that is open at both ends, and a pair of annular covers 64 are arranged in the pump unit casing 62 at a predetermined interval. Yes. Between these covers 64, an inner tooth (rotating body, second rotating body) 66 is rotatably arranged, and an outer tooth 68 is fixedly disposed so as to surround the inner tooth 66.
  • a pump chamber 70 is formed between the internal teeth 66 and the external teeth 68 to boost the working fluid as the internal teeth 66 rotate.
  • the pump chamber 70 is connected to a suction port (not shown) and the suction port.
  • the working fluid is sucked from the condenser 22 through a part of the circulation path 13.
  • the working fluid pressurized in the pump chamber 70 is discharged toward the heater 18 through a discharge port (not shown) and a part of the circulation path 13 connected to the discharge port.
  • the internal teeth 66 are fixed to the driven shaft portion 72B so as to be integrally rotatable.
  • An electromagnetic clutch as a power transmission unit 30 described later is connected to one end of the driven shaft portion 72B, and a shaft portion 56 of the turning mechanism 21 is connected to the other end of the drive shaft 72 via a one-way clutch 95 described later. Has been.
  • the drive shaft 72 is provided with an Oldham coupling 85 at the shaft portion between the movable scroll 40 and the internal teeth 66.
  • the Oldham joint 85 is a well-known joint capable of transmitting a rotational driving force while sliding a fitting portion between the protrusion and the groove.
  • a hub 72a is integrally formed or joined as a protrusion on the end surface of the drive shaft 72A of the drive shaft 72A on the power generation unit 26 and expansion unit 20 side of the drive shaft 72, and on the other hand, on the pump unit 16 side of the drive shaft 72
  • a hub 72b is integrally formed or joined as a protrusion on the end surface of the driven shaft portion 72B on the slider 87 side.
  • a slider 87 is disposed between the hubs 72a and 72b.
  • the slider 87 has groove portions (locking portions) 87a and 87b recessed in directions perpendicular to the radial direction of the drive shaft 72 on the end surfaces of the cylindrical body portion 91 facing the hubs 72a and 72b. Yes.
  • the torque sensor used in evaluating the operation of the expansion unit 20 is connected to the hub 72a.
  • the Oldham coupling 85 is configured such that the slider 87 is disposed so that the grooves 87a and 87b are fitted to the hubs 72a and 72b, respectively, so that the drive shaft 72 between the drive shaft 72A and the driven shaft 72B is disposed.
  • the drive shaft 72 having such an Oldham coupling 85 passes through the cover 64 and the pump unit casing 62, and also passes through the cover members 74 and 75 fixed to the opening end of the pump unit casing 62.
  • the lid member 74 includes a cylindrical portion 76 and a flange portion 78.
  • the lid member 75 includes a cylindrical portion 77 and a flange portion 79. The flange portions 78 and 79 are joined to the opening end of the pump unit casing 62. Yes.
  • Radial bearings 79 and 80 are disposed on the inner side of the cylindrical part 76 at both ends thereof, and radial bearings 89 are disposed on the inner side of the cylindrical part 77.
  • the cylindrical parts 76 and 77 are provided with radial bearings.
  • the drive shaft 72 is rotatably supported via bearings 79, 80, and 89.
  • a shaft sealing member 81 such as a lip seal is disposed inside the cylinder portion 76, and the shaft sealing member 81 partitions the inside of the cylinder portion 76 in an airtight manner.
  • An electromagnetic clutch as the power transmission unit 30 is connected to one end of the drive shaft 72 protruding from the cylindrical portion 76.
  • the power transmission unit 30 includes a rotor 83 disposed on the outside of the cylindrical portion 76 via a radial bearing 82, and a pulley 84 is fixed to the outer peripheral surface of the rotor 83.
  • a belt 86 indicated by a one-dot chain line is bridged between the pulley 84 and the pulley of the engine 10, and the pulley 84 and the rotor 83 are rotatable by receiving power supply from the engine 10, for example.
  • a solenoid 97 is disposed inside the rotor 83, and the solenoid 97 generates a magnetic field by feeding power from the ECU 31.
  • An annular armature 88 is disposed in the vicinity of the end face of the rotor 83, and the armature 88 is connected to a boss 92 via an elastic member 90 such as a leaf spring.
  • the boss 92 is splined to one end of the drive shaft 72, so that the armature 88 can rotate integrally with the drive shaft 72.
  • the armature 88 can be attracted to the end face of the rotor 83 while resisting the biasing force of the elastic member 90 by the magnetic field of the solenoid 97, and thus power can be transmitted between the rotor 83 and the armature 88.
  • a cylindrical casing (power generation unit casing) 93 of the power generation unit 26 is sandwiched between the partition wall 34 and the pump unit casing 62.
  • the expansion unit casing 32, the partition wall 34, and the power generation unit casing 93 are sandwiched between the partition wall 34 and the pump unit casing 62.
  • the pump unit casing 62 and the lid member 74 constitute a single housing for the fluid machine 14 by being connected to each other.
  • the other end of the drive shaft 72 reaches the through hole of the partition wall 34, and the other end of the drive shaft 72 is rotatably supported by the partition wall 34 via a needle bearing 94.
  • a one-way clutch 95 as a connecting member is fixed inside the other end of the drive shaft 72, and the other end of the drive shaft 72 and the shaft portion 56 of the turning mechanism 21 are connected via the one-way clutch 95. Yes.
  • the one-way clutch 95 is between the shaft 56 and the drive shaft 72. Shut off the power transmission.
  • the one-way clutch 95 permits power transmission between the shaft portion 56 and the drive shaft 72 when the rotational speed of the shaft portion 56 is higher than the rotational speed of the drive shaft 72, and the shaft portion 56 and the drive shaft 72 And rotate together.
  • a rotor (fourth rotating body) 96 is fixed to a portion of the drive shaft 72 extending in the power generation unit casing 93, and the rotor 96 is made of a permanent magnet, for example. Therefore, the rotor 96 is arranged coaxially with the shaft portion 56 and the internal teeth 66.
  • a stator is fixed to the inner peripheral surface of the power generation unit casing 93 so as to surround the rotor 96.
  • the stator includes a yoke 98 and, for example, three sets of coils 100 wound around the yoke 98.
  • the coil 100 is wired so as to generate a three-phase alternating current as the rotor 96 rotates, and the generated alternating current is supplied to an external load 28 through a lead wire (not shown).
  • the power generation unit 26 does not have a function as an electric motor, the shape of the yoke 98, the number of turns of the coil 100, and the like are configured to increase power generation efficiency.
  • a method of using the above-described vehicle waste heat utilization apparatus 1 will be described focusing on the operations of the fluid machine 14 and the Rankine circuit 12.
  • the working fluid circulates in the circulation path 13, and the working fluid is heated by the heater 18 and expanded by the expansion unit 20.
  • the rotational speed of the movable scroll 40 in other words, the rotational speed of the shaft portion 56 of the turning mechanism 21 is the rotational speed of the drive shaft 72.
  • the one-way clutch 95 blocks power transmission between the shaft portion 56 and the drive shaft 72.
  • the ECU 31 turns off the power transmission unit 30 and cuts off the power supply from the engine 10. Thereby, the fluid machine 14 shifts to an autonomous operation in which the pump unit 16 is operated using the torque generated in the expansion unit 20.
  • the rotor 96 of the power generation unit 26 rotates, and the power generation unit 26 generates an alternating current.
  • the alternating current is supplied to the load 28 and appropriately stored or consumed by the load 28.
  • the load 28 may include a rectifier that converts alternating current into direct current.
  • the ECU 31 may turn on the power transmission unit 30, that is, connect an electromagnetic clutch.
  • the fluid machine 14 functions as a regenerative brake, and not only an auxiliary load for deceleration is applied to the engine 10, but also the power generation unit 26 generates power, and the kinetic energy of the vehicle is converted into electric power.
  • the torque of the fluid machine 14 may be supplied to the engine 10 without shifting the fluid machine 14 to autonomous operation. That is, a portion of the torque generated by the expansion unit 20 that exceeds the torque consumed by the pump unit 16 and the power generation unit 26 may be output to the engine 10 via the power transmission unit 30.
  • the movable scroll 40 is connected to the drive shaft 72 via the shaft portion 56, and the internal teeth 66 of the pump unit 16 are connected.
  • An Oldham coupling 85 is provided at the shaft portion between the movable scroll 40 and the inner teeth 66.
  • the expansion unit 20 is separated and independent by the pump unit 16 and the Oldham coupling 85, and the operation of the expansion unit 20 is individually evaluated, thereby appropriately evaluating the operation of the expansion unit 20. Therefore, production efficiency can be improved while ensuring the performance of the fluid machine 14.
  • the internal teeth 66 of the pump unit 16 are rotated along with the rotation of the drive shaft 72, and the rotation of the internal teeth 66 is performed. Therefore, it is possible to appropriately evaluate the expansion unit 20.
  • a failure occurs in the pump unit 16 it is possible to repair and replace only the pump unit 16 with the Oldham coupling 85, and the fluid machine 14 is used for repair and replacement of the pump unit 16. It is possible to avoid disassembling the whole and improve the maintainability of the fluid machine 14.
  • the Oldham coupling 85 has a relatively simple structure, the centering operation when connecting the torque sensor to the hub 72a can be performed relatively easily in the operation evaluation of the expansion unit 20. Contributes to further improvement in machine production efficiency. Furthermore, the Oldham coupling 85 allows the displacement of the shaft in the radial direction, reduces the rotation angle error caused by the shaft misalignment (eccentricity, declination), and can transmit the rotation angle with high accuracy. , 20 is allowed to be offset when the two are integrated, the performance of the fluid machine 14 can be ensured.
  • FIG. 3 shows a fluid machine 102 according to the second embodiment.
  • symbol is attached
  • the fluid machine 102 does not include the power transmission device 30, and an internal tooth 66 (not shown in FIG. 3) of the pump unit 16 is connected to one end of the drive shaft 72B opposite to the Oldham coupling 85 side.
  • the fluid machine 102 does not include the pump unit casing 62, and the pump unit 16 is fastened to the open end of the power generation unit casing 93 by two through bolts 104 through a pair of covers 64, and each through bolt is 104 is screwed from the outside of the fluid machine 102 at a position that forms a diagonal of the cover 64.
  • the covers 64 are fastened by two connecting bolts 106, and each connecting bolt 106 is screwed from the outside of the fluid machine 102 at a position that forms a diagonal different from each through bolt 104. That is, the expansion unit casing 32, the partition wall 34, the power generation unit casing 93, and the cover 64 are connected to each other to constitute one housing for the fluid machine 102.
  • the Oldham coupling 85 is disposed closer to the pump unit 16 than the radial bearing 89 of the drive shaft 72.
  • the housing of the fluid machine 102 without the power transmission device 30 can be easily configured.
  • the pump unit 16 is fixed by fastening the through bolt 104 from the outside of the fluid machine 102, and the through bolt 104 can be fastened in the same direction as the fastening of the connecting bolt 106. Efficiency can be further improved.
  • FIG. 4 shows a fluid machine 108 according to the third embodiment.
  • symbol is attached
  • the fluid machine 108 does not include the power generation unit 26, and accordingly, the pump unit casing 62 is fastened to the expansion unit casing 32 via the partition wall 34.
  • the fluid machine 108 does not include the lid member 74, and instead, the pump unit casing 62 is extended to a position where the lid member 74 should exist, that is, the expansion unit casing 32, the partition wall 34, the pump The unit casing 62 is connected to each other to form one housing for the fluid machine 108, and the Oldham coupling 85 is positioned in the pump unit casing 62.
  • the pump unit 16 is fastened to the pump unit casing 62 with a plurality of through bolts 109 via a lid member 75, and each through bolt 109 is screwed from the inside of the pump unit casing 62.
  • the housing of the fluid machine 108 without the power generation unit 26 can be simply configured, and the production efficiency of the fluid machine 108 can be further improved.
  • the pump unit 16 is fastened to the pump unit casing 62 from the inside of the pump unit casing 62, that is, from the inside of the fluid machine 108, and the seal portion of the housing of the fluid machine 108 is 1 as compared to the case of the first embodiment. Since the number of locations is reduced, the risk of the working fluid leaking out of the housing can be reduced, and the reliability of the fluid machine 108 can be further improved.
  • FIG. 5 shows a fluid machine 110 according to the fourth embodiment.
  • symbol is attached
  • an Oldham coupling 112 is embedded in a shaft portion 56 that is integrally projected coaxially with the disk 54 from the opposite side of the drive shaft 72 to the crankpin 52.
  • a hub 72b is integrally formed or joined as a protrusion to the end surface of the driven shaft 72B on the pump unit 16 side of the drive shaft 72 (see FIG. 6). 8)
  • a housing hole 116 of the slider 114 of the present embodiment is recessed in the end surface of the shaft portion 56 opposite to the crank pin 52 (FIG. 6).
  • the slider 114 is formed with a hub (locking portion) 114a protruding from the end surface of the cylindrical main body 111 on the side of the receiving hole 116, while the end surface of the main body 111 on the hub 72b side of the drive shaft 72 is formed.
  • a groove (locking portion) 114b is recessed in a direction perpendicular to the hub 114a in the radial direction (FIG. 7).
  • a groove 116b is formed at the bottom 116a of the receiving hole 116, and the hub 114a is fitted into the groove 116b, and the slider 114 is arranged so that the hub 72b is fitted into the groove 114b.
  • 56 that is, the rotational angle error of the drive shaft 72A is reduced while the radial displacement of the drive shaft 72 between the drive shaft portion 72A and the driven shaft portion 72B is allowed. Is transmitted to the driven shaft portion 72B with high accuracy.
  • the hole depth D of the receiving hole 116 is substantially the same as the axial length L of the slider 114 in the axial direction excluding the hub 114a portion, so that the slider 114 includes not only the groove 114b but also the main body 111. It is accommodated in the accommodation hole 116.
  • the radial movement of the slider 114 is restricted by the wall surface 116c of the accommodation hole 116. That is, the hole diameter d1 of the accommodation hole 116 is slightly larger than the axial diameter d2 of the slider 114 in the radial direction, and the slider 114 can hardly move in the radial direction in the accommodation hole 116 when the fluid machine 110 is assembled.
  • the slider 114 is locked to the shaft portion 56 via the receiving hole 116 not only by the groove portion 114b but also by the main body portion 111.
  • the slider 114 when the driven shaft portion 72B is assembled to the drive shaft portion 72A via the slider 114, the slider 114 is prevented from dropping, and workability at the time of assembly of the fluid machine 110 can be prevented from being deteriorated. it can. Specifically, the slider 114 can be effectively prevented from falling off during the centering operation when evaluating the operation of the fluid units 16 and 20, and the centering operation can be performed more easily. The production efficiency of 110 can be further improved.
  • FIG. 9 is a perspective view of the receiving hole 120 constituting the Oldham coupling 118 according to the fifth embodiment, and FIGS. It is the top view which showed.
  • symbol is attached
  • the groove portion 116b of the fourth embodiment has two pairs of side surfaces 117a, 117c, and 117b, 117d, and the adjacent side surfaces 117a, 117b, and 117c, 117d are processed into R-shaped surfaces.
  • the corners 119 are connected smoothly.
  • the groove 120 b of the present embodiment is formed by connecting adjacent side surfaces 122 a, 122 b and 122 c, 122 d with a stepped portion by a corner 124.
  • the corner portion 124 is formed into an arcuate surface by, for example, indenting both ends of a pair of side surfaces 122a and 122c extending in the longitudinal direction of the groove 120b among the side surfaces 122a to 122d.
  • the corner portion 126 of the hub 114a can be brought into non-contact with the corner portion 124, and the groove portion 120b has a clearance space that allows slight movement of the hub 114a in the longitudinal direction thereof. 128 is formed. If such a relief space 128 is formed, the corner 124 is not limited to the shape described above.
  • a clearance space 128 is formed at the corner 124 of the groove 120b. Therefore, as shown by an arrow in FIG. 11, the hub 114a moves in the longitudinal direction of the groove 120b, that is, the shaft during the assembly operation of the fluid machine 110. It is possible to move slightly in the radial direction of the portion 56, and the deviation of the axis of the drive shaft 72 between the drive shaft portion 72A and the driven shaft portion 72B caused by the dimensional error or assembly error of each fluid unit 16, 20 is eliminated. Since it can be effectively tolerated, it is not necessary to strictly manage the dimensional error and assembly error of the fluid machine 110, and the production efficiency of the fluid machine 110 can be further improved.
  • an Oldham coupling 85 may be provided on the shaft portion of the drive shaft 72 between the expansion unit 20 and the power generation unit 26. Further, the partition wall 34 is eliminated, and the expansion unit casing 32 is directly joined to the pump unit casing 62 to expand the volume in the expansion unit casing 32, so that the working fluid in the low pressure chamber 44 exists. An Oldham coupling 85 may be disposed in the casing 32. In this case, the partition wall 34 and the radial bearing 58 are not required, and the configuration of the fluid machine is simplified, so that the production efficiency of the fluid machine can be further improved.
  • the Oldham joint 85 it is preferable to subject the Oldham joint 85 to a surface hardening treatment such as nitriding, because the durability of the Oldham joint 85 can be improved and the reliability of the fluid machine can be improved.
  • a compression unit fluid unit that sucks the working fluid as the orbiting scroll (rotating body, first rotating body) revolves and compresses the sucked working fluid and sends it out is used as the expansion unit 20 or the pump unit.
  • a fluid machine connected to 16 may be configured.
  • the swivel mechanism of both the compression unit and the expansion unit 20 can be separated by the Oldham coupling 85, and the operation can be individually evaluated, thereby further improving the production efficiency of the fluid machine. be able to.
  • an oil supply passage through which lubricating oil for lubricating the turning mechanism flows may be provided in the drive shaft 72, and particularly when the above-described compression unit is connected to the expansion unit 20, the compression unit and the expansion unit 20 It is preferable that the lubricating oil can be circulated between the two, and both the turning mechanisms can be lubricated more smoothly.
  • the pump unit 16 is a trochoid type, but the type of the pump unit is not particularly limited.
  • the arrangement of the units such as the pump unit 16, the power generation unit 26, and the expansion unit 20 is not particularly limited.
  • a motor generator power generation drive unit in which the power generation unit 26 has a function as a motor may be used.
  • This motor generator has a rotor (fifth rotor) and has a power generation function for generating electric power with the rotation of the rotor, while the rotor is rotated by external electric power and is driven with the rotation of the rotor. It can also function as a motor that drives the shaft 72.
  • the structure in which the slider 114 is embedded in the shaft portion 56 of the drive shaft 72 as in the fourth embodiment can be applied to the fluid machine of the first or second embodiment other than the third embodiment.
  • the fluid machine of the present invention is not limited to the Rankine circuit 12 of the vehicle waste heat utilization apparatus 1, but can be applied to any refrigerant circuit in which a working fluid circulates.
  • Fluid machine 16 Pump unit (fluid unit) 20 Expansion unit (fluid unit) 26 power generation unit 30 power transmission unit 40 movable scroll (rotating body, first rotating body) 66 Internal teeth (rotating body, second rotating body) 72 Drive shaft 85, 112 Oldham coupling 96 Rotor (fourth rotating body) 56 Shaft part 87,114 Slider 91,111 Main body part 114a Hub (locking part) 114b Groove (locking part) 116 receiving hole

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

Abstract

La présente invention concerne une machine hydraulique (14, 102, 108) équipée d'unités hydrauliques (16, 20) qui comportent des corps rotatifs (40, 66) et vers lesquelles et à partir desquelles un fluide actif circule au fur et à mesure que les corps rotatifs (40, 66) tournent ; et d'un arbre d'entraînement (72) auquel sont raccordés les corps rotatifs (40, 66) des unités hydrauliques (16, 20). Un coupleur Oldham (85) est disposé sur une section de l'arbre d'entraînement (72) située entre les corps rotatifs (40, 66).
PCT/JP2011/056757 2009-03-27 2011-03-22 Machine hydraulique Ceased WO2011118562A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CA2792544A CA2792544A1 (fr) 2010-03-24 2011-03-22 Machine hydraulique
CN2011800154983A CN102812207A (zh) 2010-03-24 2011-03-22 流体机械
US13/636,987 US20130017114A1 (en) 2009-03-27 2011-03-22 Fluid Machine
EP11759367.3A EP2551449A4 (fr) 2010-03-24 2011-03-22 Machine hydraulique
KR1020127025858A KR20120139770A (ko) 2010-03-24 2011-03-22 유체기계

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010067991A JP2010249130A (ja) 2009-03-27 2010-03-24 流体機械
JP2010-067991 2010-03-24

Publications (1)

Publication Number Publication Date
WO2011118562A1 true WO2011118562A1 (fr) 2011-09-29

Family

ID=44673924

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PCT/JP2011/056757 Ceased WO2011118562A1 (fr) 2009-03-27 2011-03-22 Machine hydraulique

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EP (1) EP2551449A4 (fr)
KR (1) KR20120139770A (fr)
CN (1) CN102812207A (fr)
CA (1) CA2792544A1 (fr)
WO (1) WO2011118562A1 (fr)

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JPS60164118U (ja) * 1984-04-10 1985-10-31 関西電力株式会社 エキスパンダ駆動圧縮機
JPH0323223U (fr) * 1989-07-19 1991-03-11
JPH06213241A (ja) * 1992-10-05 1994-08-02 Carl Schenck Ag ねじり剛性の継手
JP2005030386A (ja) 2003-06-20 2005-02-03 Denso Corp 流体機械
JP2007187153A (ja) * 2005-12-13 2007-07-26 Matsushita Electric Ind Co Ltd 流体機械
WO2008139877A1 (fr) * 2007-04-27 2008-11-20 Sanden Corporation Machine à fluide, circuit de rankine et système pour utiliser de la chaleur résiduelle provenant d'un véhicule
WO2010109875A1 (fr) * 2009-03-27 2010-09-30 サンデン株式会社 Machine à fluide

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JPS5728890A (en) * 1980-07-30 1982-02-16 Hitachi Ltd Non lubricating scroll type fluid machine
JPH07269478A (ja) * 1994-03-31 1995-10-17 Toshiba Corp 流体圧縮機
JP3567341B2 (ja) * 1995-01-27 2004-09-22 アネスト岩田株式会社 ツイン型全系回転スクロール流体機械
JPH09126168A (ja) * 1995-11-01 1997-05-13 Toshiba Corp 流体機械
JPH10196563A (ja) * 1997-01-07 1998-07-31 Kimie Nakamura スクロール流体機械
JP3918277B2 (ja) * 1998-02-20 2007-05-23 株式会社日立製作所 スクロール圧縮機
US6231324B1 (en) * 2000-02-02 2001-05-15 Copeland Corporation Oldham coupling for scroll machine
JP2001295776A (ja) * 2000-04-11 2001-10-26 Shin Meiwa Ind Co Ltd スクロール型流体機械
EP1918510B8 (fr) * 2005-06-29 2012-03-14 Panasonic Corporation Machine à fluide et dispositif de cycle de réfrigération

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60164118U (ja) * 1984-04-10 1985-10-31 関西電力株式会社 エキスパンダ駆動圧縮機
JPH0323223U (fr) * 1989-07-19 1991-03-11
JPH06213241A (ja) * 1992-10-05 1994-08-02 Carl Schenck Ag ねじり剛性の継手
JP2005030386A (ja) 2003-06-20 2005-02-03 Denso Corp 流体機械
JP2007187153A (ja) * 2005-12-13 2007-07-26 Matsushita Electric Ind Co Ltd 流体機械
WO2008139877A1 (fr) * 2007-04-27 2008-11-20 Sanden Corporation Machine à fluide, circuit de rankine et système pour utiliser de la chaleur résiduelle provenant d'un véhicule
WO2010109875A1 (fr) * 2009-03-27 2010-09-30 サンデン株式会社 Machine à fluide

Non-Patent Citations (1)

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Title
See also references of EP2551449A4 *

Also Published As

Publication number Publication date
EP2551449A1 (fr) 2013-01-30
CN102812207A (zh) 2012-12-05
EP2551449A4 (fr) 2014-04-02
KR20120139770A (ko) 2012-12-27
CA2792544A1 (fr) 2011-09-29

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