US20150098845A1 - Fluid Machinery - Google Patents
Fluid Machinery Download PDFInfo
- Publication number
- US20150098845A1 US20150098845A1 US14/399,456 US201314399456A US2015098845A1 US 20150098845 A1 US20150098845 A1 US 20150098845A1 US 201314399456 A US201314399456 A US 201314399456A US 2015098845 A1 US2015098845 A1 US 2015098845A1
- Authority
- US
- United States
- Prior art keywords
- refrigerant
- expander
- pump
- crank chamber
- fluid machinery
- 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.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
-
- 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
- F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
-
- 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
-
- 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
- F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
Definitions
- the present invention relates to a fluid machinery used by being incorporated into a Rankine cycle or the like, in particular, relates to a fluid machinery that is provided with an expander that generates power by expansion of a refrigerant, and a piston pump that pumps the refrigerant.
- the Rankine cycle 2 A recovers the exhaust heat (here, heat of the engine cooling water) of the engine 10 as an external heat source, and converts the exhaust heat into power and outputs the power.
- the pump unit 50 A includes a piston 51 housed in a pump cylinder 74 A formed to communicate with the crank chamber 72 A, and a connecting rod 52 which is connected to the piston 51 at one end and connected to the crank section 28 a of the rotating shaft 28 at the other end to convert rotational motion of the rotating shaft 28 into reciprocating linear motion of the piston 51 .
- the fixed scroll 61 and the orbiting scroll 62 are disposed so that the spiral wraps 61 b and 62 b are engaged with each other, and an expansion chamber 63 that expands the introduced refrigerant (gas-phase refrigerant) is formed between both wraps 61 b and 62 b . Furthermore, between a surface of the base portion 62 a of the orbiting scroll 62 on the opposite side to the fixed scroll 61 and a surface of the housing 70 facing thereto, an anti-rotation member 77 such as a ball coupling that prevents the rotation of the orbiting scroll 62 is disposed.
- FIG. 5 illustrates a schematic configuration of an exhaust heat recovery apparatus 1 B in the second embodiment to which the fluid machinery according to the present invention is applied.
- the crank chamber 72 B on the pump unit 50 B side and the refrigerant outlet chamber 78 B on the expander unit 60 B side are in communication with each other, via the bearing 131 b that supports the rotating shaft 105 , the generator motor unit 110 (especially, a gap space between the rotor 111 and the stator 112 ), the through hole 123 a formed in the connecting member 123 , and the anti-rotation member 77 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
- The present invention relates to a fluid machinery used by being incorporated into a Rankine cycle or the like, in particular, relates to a fluid machinery that is provided with an expander that generates power by expansion of a refrigerant, and a piston pump that pumps the refrigerant.
- As a fluid machinery incorporated into a Rankine cycle, a pump-integrated expander in which an expander that generates power by expansion of a refrigerant is integrally connected to a pump that pumps the refrigerant has been known (for example, see Patent Document 1). Inventors have considered adopting a piston pump, with high volumetric efficiency from a low rotational speed area to a high rotational speed area, as a pump of the fluid machinery of this type. In this case, a liquid-phase refrigerant drawn into the piston pump might flow into a crank chamber, and thus, there may be a concern over degradation of a lubrication state of each sliding section in the crank chamber.
- On this point, Patent Document 2 discloses, in a fluid machinery incorporated into a Rankine cycle, a technique of sufficiently lubricating a mechanical sliding section of a refrigerant pumping pump, by separating a lubricating oil from a gas-phase refrigerant, and by supplying the separated lubricating oil to a liquid-phase refrigerant drawn into the refrigerant pumping pump.
-
- Patent Document 1: Japanese Patent Application Laid-open Publication No. 2010-077827
- Patent Document 2: Japanese Patent No. 4725344
- However, the lubricating oil separated from the gas-phase refrigerant has a high temperature compared to the drawn refrigerant of the pump, and thus, as in the above-described related art, if the lubricating oil separated from the gas-phase refrigerant is supplied to the liquid-phase refrigerant drawn into the refrigerant pumping pump, a part of the drawn refrigerant of the pump is gasified (evaporated), and there may be a risk of a decrease in the volumetric efficiency of the pump.
- Therefore, an object of the present invention is to reduce a risk of a decrease in the volume efficiency of a piston pump, while reducing a decrease in lubrication performance of a mechanical sliding section in a crank chamber of the piston pump, in a fluid machinery including an expander that generates power by the expansion of the refrigerant, and the piston pump that pumps the refrigerant.
- A fluid machinery according to an aspect of the invention including: an expander that generates power by expansion of a refrigerant; and a piston pump that pumps the refrigerant, in which a refrigerant outlet chamber through which the refrigerant after expansion is discharged from the expander communicates with a crank chamber of the piston pump.
- According to the fluid machinery, since the interior of the crank chamber is set to a state in which the liquid-phase refrigerant is easily gasified, by allowing the refrigerant outlet section, through which the refrigerant after expansion is discharged from the expander, to communicate with the crank chamber of the piston pump, it is possible to reduce an amount of liquid-phase refrigerant that flows into the crank chamber and/or is stored in the crank chamber. Furthermore, there is little fear of gasification of the drawn refrigerant of the pump as in the above-described related arts. This can reduce the risk of a decrease in volumetric efficiency of the piston pump, while reducing a decrease in lubrication performance of the mechanical sliding section of the piston pump.
-
FIG. 1 is a diagram illustrating a schematic configuration of an exhaust heat recovery apparatus according to a first embodiment of the present invention. -
FIG. 2 is a cross-sectional view of a fluid machinery (pump-integrated expander) according to the first embodiment. -
FIG. 3 is a diagram illustrating an example of a distribution passage of a gas-phase refrigerant in the fluid machinery (pump-integrated expander) according to the first embodiment. -
FIGS. 4A and 4B are diagrams illustrating modified examples of the fluid machinery (pump-integrated expander) according to the first embodiment. -
FIG. 5 is a diagram illustrating a schematic configuration of an exhaust heat recovery apparatus of a second embodiment of the present invention. -
FIG. 6 is a cross-sectional view of a fluid machinery (expander-pump-generator motor-integrated fluid machinery) according to the second embodiment. -
FIG. 7 is a diagram illustrating an example of the distribution passage of a gas-phase refrigerant in the fluid machinery (expander-pump-generator motor-integrated fluid machinery) according to the second embodiment. -
FIG. 8 is a diagram illustrating a modified example of a fluid machinery (expander-pump-generator motor-integrated fluid machinery) according to the second embodiment. - Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
-
FIG. 1 illustrates a schematic configuration of an exhaustheat recovery apparatus 1A to which a fluid machinery according to the present invention is applied in a first embodiment. The exhaustheat recovery apparatus 1A is mounted on a vehicle and recovers and uses exhaust heat of anengine 10 of the vehicle. - The exhaust
heat recovery apparatus 1A has a Rankinecycle 2A that recovers the exhaust heat of theengine 10 and converts it into power, atransmission mechanism 3 that performs the transmission of power between the Rankinecycle 2A and theengine 10, and acontrol unit 4A that controls the overall operation of the exhaust heat recovery apparatus 1. - The
engine 10 is a water-cooled internal combustion engine and is cooled by an engine cooling water that circulates in a coolingwater flow passage 11. Aheater 22 of the Rankinecycle 2A to be described later is disposed on the coolingwater flow passage 11, so that the engine cooling water that has absorbed heat from theengine 10 flows through theheater 22. - The Rankine
cycle 2A recovers the exhaust heat (here, heat of the engine cooling water) of theengine 10 as an external heat source, and converts the exhaust heat into power and outputs the power. - In a
refrigerant circulation passage 21 of the Rankinecycle 2A, theheater 22, anexpander 23, acondenser 24, and apump 25 are disposed in this order. Furthermore, between theheater 22 and thecondenser 24, abypass passage 26 that circulates the refrigerant while bypassing theexpander 23 is provided, and abypass valve 27 that opens and closes thebypass passage 26 is provided in thebypass passage 26. - The
heater 22 is a heat exchanger which heats the refrigerant to obtain superheated vapor, by performing heat exchange between the engine cooling water which has absorbed heat from theengine 10 and the refrigerant of the Rankinecycle 2A. Alternatively, although it is not illustrated, theheater 22 may be configured to perform heat exchange between the refrigerant and the exhaust gas of theengine 10, instead of the engine cooling water. - The
expander 23 is a scroll expander that generates power (driving force) by expanding the refrigerant (gas-phase refrigerant), which is the superheated vapor heated by theheater 22, and by converting it into rotational energy. - The
condenser 24 is a heat exchanger which cools and condenses (liquefies) the refrigerant, by performing the heat exchange between the refrigerant passed through theexpander 23 and the ambient air. - The
pump 25 is a mechanical type piston pump that pumps the refrigerant (liquid-phase refrigerant) liquefied by thecondenser 24. When thepump 25 draws and discharges the refrigerant (liquid-phase refrigerant) liquefied in thecondenser 24, the refrigerant circulates through each of the elements of the Rankinecycle 2A. - Here, the expander (scroll expander) 23 and the pump (piston pump) 25 are integrally connected to each other and is configured as a “pump-integrated expander” 29A having a common rotating
shaft 28. That is, the rotatingshaft 28 of the pump-integratedexpander 29A has a function as an output shaft of theexpander 23 and a function as a drive shaft of thepump 25. - The
transmission mechanism 3 has apulley 32 that is attached to the rotatingshaft 28 of the pump-integratedexpander 29A via anelectromagnetic clutch 31, acrank pulley 33 that is attached to acrankshaft 12 of theengine 10, and abelt 34 that is wrapped around thepulley 32 and thecrank pulley 33. - The
control unit 4A controls the operation of thebypass valve 27 and theelectromagnetic clutch 31. - When the
control unit 4A opens thebypass valve 27, the refrigerant circulates while bypassing theexpander 23. Furthermore, the control unit 4 controls to turn on (engage) and turn off (disengage) theelectromagnetic clutch 31, so that thetransmission mechanism 3 transfers and cuts off power between theengine 10 and the Rankinecycle 2A (more specifically, the pump-integrated expander 29A). - When starting up the Rankine
cycle 2A, thecontrol unit 4A opens thebypass valve 27 and drives thepump 25 by theengine 10 by turning on (engage) theelectromagnetic clutch 31. Thus, the refrigerant is circulated while bypassing theexpander 23. Then, for example, when a pressure difference before and after theexpander 23 becomes a predetermined value or more, thecontrol unit 4A closes thebypass valve 27 and causes the refrigerant to circulate via theexpander 23. Thereafter, when theexpander 23 generates sufficient driving force, a part of the driving force generated by theexpander 23 drives thepump 25, the remaining driving force is transmitted to theengine 10 via thetransmission mechanism 3 to assist the output (driving force) of theengine 10. - Furthermore, for example, by turning off (disengage) the
electromagnetic clutch 31, thecontrol unit 4A is able to stop the Rankinecycle 2A. - Next, a configuration of the pump-integrated
expander 29A (fluid machinery) will be described. -
FIG. 2 is a cross-sectional view of the pump-integratedexpander 29A. As described above, the pump-integratedexpander 29A is a fluid machinery in which theexpander 23 that generates power by the expansion of the refrigerant is integrally connected to thepump 25 that pumps the refrigerant, and is used by being incorporated into the Rankinecycle 2A. - The pump-integrated
expander 29A has apump unit 50A that configures the pump (piston pump) 25, anexpander unit 60A that configures the expander (scroll expander) 23, therotating shaft 28 that has a function as a drive shaft of thepump unit 50A and a function as an output shaft of theexpander unit 60A, and ahousing 70 that houses these elements. In addition, the pump-integratedexpander 29A is provided with theelectromagnetic clutch 31 and thepulley 32 that configure thetransmission mechanism 3. - The
rotating shaft 28 extends in an axial direction (horizontal direction in the drawings) of thehousing 70, and has acrank section 28 a, an axis of which is shifted (offset) from a rotational center of therotating shaft 28, and a large-diameter end section 28 b. - In addition,
bearings shaft 28 are disposed within thehousing 70. Thebearing 71 a is disposed in acylindrical section 70 a formed to project from the one end side (here, a left end side) of thehousing 70 to rotatably support the vicinity of an end portion opposite to the large-diameter end section 28 b of the rotatingshaft 28. The bearing 71 b is disposed in a substantially center in the axial direction of thehousing 70 to rotatably support the large-diameter section 28 b of the rotatingshaft 28. - The
crank section 28 a of therotating shaft 28 is housed in acrank chamber 72A formed in thehousing 70. Furthermore, in thecylindrical section 70 a of thehousing 70 at a position on thecrank chamber 72A side from the bearing 71 a, ashaft seal 73 that seals a space between an outer peripheral surface of therotating shaft 28 and an inner peripheral surface of thecylindrical section 70 a is provided. - An
armature plate 81 is attached to the end portion (leading end portion) of therotating shaft 28 protruding outward from thecylindrical section 70 a, and thepulley 32 is rotatably attached to the outer peripheral surface of thecylindrical section 70 a via abearing 82. Also, aclutch coil 83 is housed in anannular groove 32 a formed on the end surface of thepulley 32. Theelectromagnetic clutch 31 includes thearmature plate 81 and theclutch coil 83, thearmature plate 81 is magnetically attracted to the end surface of thepulley 32 by energizing theclutch coil 83, and theelectromagnetic clutch 31 is engaged. - Next, the
pump unit 50A will be described. - The
pump unit 50A includes apiston 51 housed in apump cylinder 74A formed to communicate with thecrank chamber 72A, and a connectingrod 52 which is connected to thepiston 51 at one end and connected to thecrank section 28 a of therotating shaft 28 at the other end to convert rotational motion of therotating shaft 28 into reciprocating linear motion of thepiston 51. - An open end of the
pump cylinder 74A is covered by acylinder cover 75. Thecylinder cover 75 is formed with asuction port 75 a that intakes the refrigerant (liquid-phase refrigerant) liquefied in thecondenser 24 into thepump cylinder 74A, and adischarge port 75 b that discharges the drawn refrigerant. Thesuction port 75 a is provided with acheck valve 76 a that only allows the intake of refrigerant, and thedischarge port 75 b is provided with acheck valve 76 b that only allows the discharge of the refrigerant. - The
pump unit 50A repeats the intake and the discharge of the refrigerant (liquid-phase refrigerant) by reciprocating motion of thepiston 51 within thepump cylinder 74A along with the rotation of therotating shaft 28, thereby pumping the refrigerant. - Next, the
expander unit 60A will be described. - The
expander unit 60A includes a fixedscroll 61 fixed to an end portion (right end portion in the drawings) on the opposite side of thecylindrical section 70 a of thehousing 70, and anorbiting scroll 62. - The fixed
scroll 61 has a disk-shapedbase portion 61 a, and aspiral wrap 61 b uprightly provided on one surface (left side in the drawings) of thebase portion 61 a. Anintroduction port 61 c of the refrigerant is formed to penetrate through a substantially central portion of thebase portion 61 a of the fixedscroll 61. Also, the orbitingscroll 62 has a substantially disk-shapedbase portion 62 a, and aspiral wrap 62 b uprightly provided on the surface of thebase portion 62 a on the fixedscroll 61 side. - The fixed
scroll 61 and the orbitingscroll 62 are disposed so that the spiral wraps 61 b and 62 b are engaged with each other, and anexpansion chamber 63 that expands the introduced refrigerant (gas-phase refrigerant) is formed between bothwraps base portion 62 a of the orbitingscroll 62 on the opposite side to the fixedscroll 61 and a surface of thehousing 70 facing thereto, ananti-rotation member 77 such as a ball coupling that prevents the rotation of the orbitingscroll 62 is disposed. - In the
expander unit 60A, when the refrigerant (gas-phase refrigerant) introduced into theexpansion chamber 63 via theintroduction port 61 c is expanded within theexpansion chamber 63, the orbitingscroll 62 performs orbiting motion with respect to the fixedscroll 61. Theexpansion chamber 63 moves to the peripheral portion from the central portion, while increasing the volume along with the orbiting motion of the orbitingscroll 62, and the refrigerant (gas-phase refrigerant) after expansion is discharged to arefrigerant outlet chamber 78A of thehousing 70. Therefrigerant outlet chamber 78A is, for example, a space formed on the radially outer side of the orbitingscroll 62 in thehousing 70. - In the
housing 70, thepump unit 50A and theexpander unit 60A are connected to each other via a drivencrank mechanism 80. Specifically, the large-diameter section 28 b of therotating shaft 28 is connected to theorbiting scroll 62 via the driven crankmechanism 80. - The driven
crank mechanism 80 has aflange section 81 fixed to the end surface of the large-diameter section 28 b of therotating shaft 28, acrank pin 82 which is uprightly provided at a position shifted from the rotation center of therotating shaft 28 of the end surface of theflange section 81 and which is parallel to therotating shaft 28, and aneccentric bush 83 provided on theorbiting scroll 62 side. Theeccentric bush 83 is disposed in ahollow boss section 62 c formed on the surface of thebase portion 62 a of the orbitingscroll 62 on the opposite side to the fixedscroll 61 via abearing 84. - The
crank pin 82 is inserted into aninsertion hole 83 a formed in theeccentric bush 83. Theinsertion hole 83 a is formed at a position shifted from the center of the bush, and theeccentric bush 83 is configured to oscillate with respect to the crankpin 82. Thus, in the driven crankmechanism 80, the orbiting motion of thecrank pin 82 becomes orbiting motion of theeccentric bush 83 as it is, and conversely, the orbiting motion of theeccentric bush 83 becomes orbiting motion of thecrank pin 82 as it is. - By the driven crank
mechanism 80, the rotational motion of therotating shaft 28 is converted into the orbiting motion of the orbitingscroll 62, or the orbiting motion of the orbitingscroll 62 is converted into the rotational motion of therotating shaft 28. Moreover, as described above, the pump unit 50 is driven by the rotation of therotating shaft 28 to pump the liquid-phase refrigerant. - Since the balance between the
eccentric bush 83 and the orbitingscroll 62 is kept to reduce an occurrence of vibration or the like in theexpander unit 60A, a counterweight (balance weight) 85 is fixed to theeccentric bush 83. In addition, an oscillating range of theeccentric bush 83 with respect to the crankpin 82 is regulated by engagement between a regulatinghole 81 a provided in theflange section 81 and a regulatingprojection 83 b provided in theeccentric bush 83. - Here, in the
housing 70, thecrank chamber 72A on thepump unit 50A side and therefrigerant outlet chamber 78A on theexpander unit 60A side are in communication with each other via thebearing 71 b that supports the large-diameter section 28 b of therotating shaft 28, a housing space of the driven crankmechanism 80, and theanti-rotation member 77, in other words, via a gap space between thepump unit 50A and theexpander unit 60A in thehousing 70. In addition, anoutlet port 79A through which the refrigerant after expansion discharged to therefrigerant outlet chamber 78A from theexpander unit 60A flows out to thecondenser 24 is open to the crankchamber 72A. - It is preferable that the
outlet port 79A be formed to open to the bottom (a lower portion in the vertical direction of the pump-integratedexpander 29A) of thecrank chamber 72A. - Thus, in the pump-integrated
expander 29A, as illustrated by arrows inFIG. 3 , the gas-phase refrigerant (of high temperature after expansion), which has been discharged to therefrigerant outlet chamber 78A from theexpander unit 60A, enters thecrank chamber 72A via theanti-rotation member 77, the housing space of the driven crankmechanism 80, and thebearing 71 b, and then, flows out of theoutlet port 79A that is open to the crankchamber 72A (that is, flows out through the crank chamber 72). The gas-phase refrigerant, which has flowed out of theoutlet port 79A, is liquefied by thecondenser 24, and then is pumped by thepump unit 50A. - According to the above-described pump-integrated
expander 29A (fluid machinery), since therefrigerant outlet chamber 78A through which the gas-phase refrigerant after expansion is discharged from theexpander unit 60A (expander) is in communication with thecrank chamber 72A of thepump unit 50A (piston pump), the interior of thecrank chamber 72A can be set to a state in which the liquid-phase refrigerant is easily gasified, and it is possible to reduce the amount of the liquid-phase refrigerant that flows into thecrank chamber 72A and/or is stored in thecrank chamber 72A. Thus, in particular, a decrease in lubrication performance of the mechanical sliding section in thecrank chamber 72A of thepump unit 50A and an increase in stirring resistance of the liquid-phase refrigerant due to the rotating shaft 28 (cranksection 28 b) can be reduced, durability of the mechanical sliding section can be improved, and the mechanical loss can be small. - Furthermore, since the
outlet port 79A is open to the bottom (lower portion) of thecrank chamber 72A, even if the liquid-phase refrigerant flows into thecrank chamber 72A, the flowed-in liquid-phase refrigerant can be discharged from theoutlet port 79A, and thus, the storage of the refrigerant in thecrank chamber 72A can be reduced. - Furthermore, since the gas-phase refrigerant after expansion of the relatively high temperature flows to the outside (the
condenser 24 side) through thecrank chamber 72A, even when the liquid-phase refrigerant is stored in thecrank chamber 72A, it is possible to cause the liquid-phase refrigerant to flow (discharge) out of theoutlet port 79A as a gas-phase refrigerant, by gasifying the majority of the liquid-phase refrigerant. This makes it possible to further reduce a decrease in the lubrication performance of the mechanical sliding section of thepump unit 50A and an increase in the stirring resistance of the liquid-phase refrigerant due to therotating shaft 28. - In addition, by allowing the
crank chamber 72A and therefrigerant outlet chamber 78A to communicate with each other via thebearing 71 b that rotatably supports therotating shaft 28 and via theanti-rotation member 77 that prevents rotation of the orbitingscroll 62, there is no need to form, in thehousing 70, a new dedicated communication passage or the like for allowing thecrank chamber 72A and therefrigerant outlet chamber 78A to communicate with each other. This makes it possible to reduce an increase in size of the pump-integratedexpander 29A and an increase in production cost. - Incidentally, the pump-integrated
expander 29A is configured so that theoutlet port 79A through which the refrigerant after expansion flows toward thecondenser 24 is open to the crankchamber 72A and the gas-phase refrigerant after expansion discharged from the expander 60 flows to the outside (thecondenser 24 side) via thecrank chamber 72A. However, thecrank chamber 72A and therefrigerant outlet chamber 78A may have any configuration that enables communication with each other, and the position at which theoutlet port 79A is formed is not limited to the configuration according to the above-described embodiment. - For example, as illustrated in
FIG. 4A , theoutlet port 79A may be open to therefrigerant outlet chamber 78A. In addition, as illustrated inFIG. 4B , acommunication passage 91 through which thecrank chamber 72A and the space on theexpander unit 60A side such as the housing space of the driven crankmechanism 80 are in communication with each other may be formed in thehousing 70. Also in this case, since thecrank chamber 72A can be set to a state in which the liquid-phase refrigerant is easily gasified, it is possible to reduce an amount of liquid-phase refrigerant that flows into thecrank chamber 72A and/or is stored in thecrank chamber 72A. - Furthermore, in a case in which the
outlet port 79A is open to therefrigerant outlet chamber 78A, the refrigerant gasified in thecrank chamber 72A is supplied to therefrigerant outlet chamber 78A via thebearing 71 b, the housing space of theanti-rotation member 77, and theanti-rotation member 77, and flows to the outside (condenser 24 side) from theoutlet port 79A along with the gas-phase refrigerant after expansion, as illustrated by arrows inFIG. 4A . - Furthermore, when the
communication passage 91 through which thecrank chamber 72A communicates with the space on theexpander unit 60A side such as the housing space of the driven crankmechanism 80 is formed in thehousing 70, the refrigerant after expansion, which has passed through theanti-rotation member 77 and the housing space of the driven crankmechanism 80, enters thecrank chamber 72A via thebearing 71 b and thecommunication passage 91, and then flows out of theoutlet port 79A that is open to the crankchamber 72A, as illustrated inFIG. 4B . - Furthermore, a communication passage through which the
crank chamber 72A and therefrigerant outlet chamber 78A directly communicate with each other may be formed in thehousing 70, and a communication passage through which theoutlet port 79A and therefrigerant outlet chamber 78A in the configuration illustrated inFIGS. 2 and 3 communicate with each other may be formed in thehousing 70. Furthermore, these communication passages may be provided outside thehousing 70. Also in this case, since the interior of thecrank chamber 72A can be set to a state in which the liquid-phase refrigerant is easily gasified, it is possible to reduce an amount of liquid-phase refrigerant that flows into thecrank chamber 72A and/or is stored in thecrank chamber 72A. - Next, a second embodiment of the present invention will be described.
FIG. 5 illustrates a schematic configuration of an exhaustheat recovery apparatus 1B in the second embodiment to which the fluid machinery according to the present invention is applied. - The exhaust
heat recovery apparatus 1A of the first embodiment drives thepump 25 that circulates the refrigerant of theRankine cycle 2A by the driving force generated by theexpander 23, and assists the output of theengine 10. Moreover, the pump-integratedexpander 29A is incorporated into theRankine cycle 2A. - In contrast, the exhaust
heat recovery apparatus 1B of the second embodiment has agenerator motor 100 and converts exhaust heat of anengine 10 into electrical energy to use it, by driving thegenerator motor 100 by the driving force generated by anexpander 23. Moreover, an expander-pump-generator motor-integratedfluid machinery 29B is incorporated into aRankine cycle 2B. In addition, in the present embodiment, thetransmission mechanism 3 in the first embodiment is not provided, and apump 25 is driven by thegenerator motor 100. Also, inFIG. 5 , the same elements as those ofFIG. 1 are denoted by the same reference numbers, and the functions thereof are the same. - In
FIG. 5 , the exhaustheat recovery apparatus 1B includes theRankine cycle 2B, thegenerator motor 100, and acontrol unit 4B. - In a
refrigerant circulation passage 21 of theRankine cycle 2B, aheater 22, theexpander 23, acondenser 24, and thepump 25 are disposed in this order. Furthermore, abypass passage 26 that circulates the refrigerant while bypassing theexpander 23 is provided between theheater 22 and thecondenser 24, and in thebypass passage 26, abypass valve 27 that opens and closes thebypass passage 26 is provided. - The
generator motor 100 is connected to apower storage apparatus 102 via a power converter 101 (such as a rectifier and an inverter). Thegenerator motor 100 is disposed between theexpander 23 and thepump 25, is driven by the power supplied from thepower storage apparatus 102, or is driven by the driving force generated by theexpander 23. - The
control unit 4B controls the operation of thebypass valve 27 and controls power supply and/or stop of power supply to thegenerator motor 100 from thepower storage apparatus 102. When power is supplied to thegenerator motor 100 from thepower storage apparatus 102, thegenerator motor 100 is operated as a motor to drive thepump 25. Meanwhile, when the power supply to thegenerator motor 100 from thepower storage apparatus 102 is stopped, thegenerator motor 100 is operated as a generator, and is driven by the driving force generated by theexpander 23 to generate power. - When the
Rankine cycle 2B is started up, thecontrol unit 4B opens thebypass valve 27 and supplies the power to thegenerator motor 100 from thepower storage apparatus 102 to operate thegenerator motor 100 as a motor, thereby driving thepump 25. Thus, the refrigerant is circulated while bypassing theexpander 23. Moreover, for example, when the pressure difference before and after theexpander 23 becomes equal to or greater than a predetermined value, thecontrol unit 4B closes thebypass valve 27 and causes the refrigerant to circulate via theexpander 23. Thereafter, when theexpander 23 generates sufficient driving force, thecontrol unit 4B stops the power supply to thegenerator motor 100 from thepower storage apparatus 102, to operate thegenerator motor 100 as a generator. Thus, the driving force generated by theexpander 23 drives thepump 25 and drives thegenerator motor 100, and thus, thegenerator motor 100 generates electric power. The electric power generated by thegenerator motor 100 is supplied to thepower storage apparatus 102 via thepower converter 101. - In this embodiment, the
expander 23, the pump (piston pump) 25, and thegenerator motor 100 are integrally connected and configured as afluid machinery 29B having a commonrotating shaft 105. That is, therotating shaft 105 of thefluid machinery 29B has a function as an output shaft of theexpander 23, a function as a drive shaft of thepump 25, and a function as a drive shaft of thegenerator motor 100. - Next, the configuration of the
fluid machinery 29B in which theexpander 23, the pump (piston pump) 25, and thegenerator motor 100 are integrally connected will be described. -
FIG. 6 is a cross-sectional view of thefluid machinery 29B. - As illustrated in
FIG. 6 , thefluid machinery 29B has apump unit 50B that configures the pump (piston pump) 25, agenerator motor unit 110 that configures thegenerator motor 100, anexpander unit 60B that configures the expander (scroll expander) 23, therotating shaft 105 that has a function as a drive shaft of thepump unit 50B, a function as a drive shaft of thegenerator motor unit 110, and a function as an output shaft of theexpander unit 60B, and ahousing 120 that houses these elements. - The
housing 120 has afirst housing 121 that houses thepump unit 50B and thegenerator motor unit 110, asecond housing 122 that houses theexpander unit 60B, and a connectingmember 123 that connects thefirst housing 121 and thesecond housing 122. Specifically, thefirst housing 121 is fitted and fixed to one side (left side in the drawings) of the connectingmember 123, and thesecond housing 122 is fitted and fixed to the other side (right side in the drawings) of the connectingmember 123. - A through
hole 123 a is formed in the connectingmember 123, and the internal space of thefirst housing 121 and the internal space of thesecond housing 122 are in communication with each other by the throughhole 123 a. - The
rotating shaft 105 extends in thefirst housing 121 in an axial direction (horizontal direction in the drawings), and has acrank section 105 a having an axial center shifted (offset) from a rotation center of therotating shaft 105 at one end side thereof (left end side in the drawings). Therotating shaft 105 is rotatably supported by a bearing 131 a disposed in thefirst housing 121 and abearing 131 b held by the connectingmember 123. Furthermore, thecrank section 105 a of therotating shaft 105 is housed in acrank chamber 72B formed in thefirst housing 121. - The
pump unit 50B includes apiston 51 housed in apump cylinder 74B that is formed to communicate with thecrank chamber 72B, and a connectingrod 52 that is connected to thepiston 51 at one end and is connected to thecrank section 105 a of therotating shaft 105 at the other end to convert rotational motion of therotating shaft 105 into reciprocating linear motion of thepiston 51. Furthermore, similar to the first embodiment, an open end of thepump cylinder 74B is covered by acylinder cover 75 that is formed with asuction port 75 a and adischarge port 75 b. Thesuction port 75 a and thedischarge port 75 b are provided withcheck valves - The
pump unit 50B repeats the intake and discharge of the refrigerant (liquid-phase refrigerant) by reciprocating motion of thepiston 51 within thepump cylinder 74B along with the rotation of therotating shaft 105, thereby pumping the refrigerant. - The
generator motor unit 110 is disposed in a space (housing space) adjacent to the crankchamber 72B via the bearing 131 a within thefirst housing 121. - The
generator motor unit 110 has arotor 111 including, for example, a permanent magnet fixed to therotating shaft 105, and astator 112 fixed to the inner peripheral surface of thefirst housing 121 so as to surround therotor 111. - The
stator 112 has ayoke 112 a, and, for example, three sets ofcoils 112 b wound around theyoke 112 a. Thecoil 112 b generates a magnetic field that rotates therotor 111 by being supplied with three-phase alternating current from thepower storage apparatus 102 via thepower converter 101, whereby therotating shaft 105 rotates and thepump unit 50B is driven. Furthermore, thecoil 112 b generates the three-phase alternating current along with the rotation of therotor 111, and the generated three-phase alternating current is supplied to thepower storage apparatus 102 via thepower converter 101. Thus, thepower storage apparatus 102 is charged. - Similar to the first embodiment, the
expander unit 60B includes a fixedscroll 61, and anorbiting scroll 62. The fixedscroll 61 is fixed within thesecond housing 122, and thesecond housing 122 is formed with anintroduction hole 122 a for introducing the refrigerant into thesecond housing 122. - The fixed
scroll 61 has a disk-shapedbase portion 61 a, and aspiral wrap 61 b uprightly provided on one surface (left surface in the drawings) of thebase portion 61 a. Anintroduction port 61 c of the refrigerant is formed to penetrate through a substantially central portion of thebase portion 61 a of the fixedscroll 61. Furthermore, the orbitingscroll 62 has a substantially disk-shapedbase portion 62 a, and aspiral wrap 62 b uprightly provided on the surface of thebase portion 62 a on the fixedscroll 61 side. - The fixed
scroll 61 and the orbitingscroll 62 are disposed so that the spiral wraps 61 b and 62 b are engaged with each other, and anexpansion chamber 63 that expands the introduced gas-phase refrigerant is formed between thewraps space 122 b having a relatively large volume is formed on the rear side (opposite side of the orbitingscroll 61 side) of the fixedscroll 61 of thesecond housing 122, and thus, for example, even when the refrigerant introduced from theintroduction hole 122 a contains the liquid-phase refrigerant (that is, a gas-liquid mixed state), introduction of the liquid-phase refrigerant into theintroduction port 61 c formed at thebase portion 61 a of the fixedscroll 61, and ultimately into theexpansion chamber 63 can be suppressed. - Furthermore, between the surface of the
base portion 62 a of the orbitingscroll 62 on the opposite side to the fixedscroll 61 and the surface of the connectingmember 123 facing thereto, ananti-rotation member 77 such as a ball coupling that prevents rotation of the orbitingscroll 62 is disposed. - In the
expander unit 60B, the gas-phase refrigerant is introduced into theexpansion chamber 63 via theintroduction hole 122 a formed in thesecond housing 122, thespace 122 b on the rear side of the fixedscroll 61, and theintroduction port 61 c formed in thebase portion 61 a of the fixedscroll 61. Moreover, when the introduced gas-phase refrigerant expands within theexpansion chamber 63, the orbitingscroll 62 performs the orbiting motion with respect to the fixedscroll 61. Theexpansion chamber 63 moves while increasing the volume to the peripheral portion from the central portion along with the orbiting motion of the orbitingscroll 62, and the refrigerant after expansion (gas-phase refrigerant) is discharged to arefrigerant outlet chamber 78B in thesecond housing 122. Therefrigerant outlet chamber 78B is, for example, a space formed on the radially outer side of the orbitingscroll 62 in thesecond housing 122. - Furthermore, the
rotating shaft 105 extending in thefirst housing 121 in the axial direction is connected to theorbiting scroll 62 via a drivencrank mechanism 80. - Similar to the first embodiment, the driven crank
mechanism 80 includes aflange section 81 fixed to the end surface of therotating shaft 105, acrank pin 82 which is uprightly provided at a position shifted from the rotation center of therotating shaft 28 of the end surface of theflange section 81 and which is parallel to therotating shaft 28, and aneccentric bush 83 provided on theorbiting scroll 62 side. - The
eccentric bush 83 is disposed in ahollow boss section 62 c formed on the surface of thebase portion 62 a of the orbitingscroll 62 on the opposite side to the fixedscroll 61 via abearing 84. Thecrank pin 82 is inserted into theinsertion hole 83 a formed in theeccentric bush 83. Theinsertion hole 83 a is formed at a position shifted from the center of the bush, and theeccentric bush 83 is configured to oscillate with respect to the crankpin 82. - Furthermore, in order to keep a balance between the
eccentric bush 83 and the orbitingscroll 62 to reduce an occurrence of vibration or the like in theexpander unit 60B, a counterweight (balance weight) 85 is fixed to theeccentric bush 83. In addition, an oscillating range of theeccentric bush 83 with respect to the crankpin 82 is regulated by engagement between a regulatinghole 81 a provided in theflange section 81 and a regulatingprojection 83 b provided in theeccentric bush 83. - By the driven crank
mechanism 80, the rotational motion of therotating shaft 105 is converted into the orbiting motion of the orbitingscroll 62, or the orbiting motion of the orbitingscroll 62 is converted into the rotational motion of therotating shaft 105. Furthermore, as described above, thepump unit 50B is driven by the rotation of therotating shaft 105 to pump the liquid-phase refrigerant, thegenerator motor unit 110 is driven to generate electric power, and thepower storage apparatus 102 is charged. - Here, in the
housing 120, thecrank chamber 72B on thepump unit 50B side and therefrigerant outlet chamber 78B on theexpander unit 60B side are in communication with each other, via thebearing 131 b that supports therotating shaft 105, the generator motor unit 110 (especially, a gap space between therotor 111 and the stator 112), the throughhole 123 a formed in the connectingmember 123, and theanti-rotation member 77. - In addition, an
outlet port 79B that causes the refrigerant after expansion to flow toward thecondenser 24 is open to the crankchamber 72B. It is preferable that theoutlet port 79B be formed to open to the bottom (lower portion in the vertical direction of thefluid machinery 29B) of thecrank chamber 72B. - Thus, in the
fluid machinery 29B according to this embodiment, as illustrated by arrows inFIG. 7 , the gas-phase refrigerant (after expansion), which has been discharged to therefrigerant outlet chamber 78B from theexpander unit 60B, enters thecrank chamber 72B via theanti-rotation member 77, the throughhole 123 a formed in the connectingmember 123, the generator motor unit 110 (the gap space between therotor 111 and the stator 112), and thebearings 131 a, and then flows out of theoutlet port 79B that is open to the crankchamber 72B. Moreover, the gas-phase refrigerant, which has flowed out of theoutlet port 79B, is liquefied by thecondenser 24, and then is pumped by thepump unit 50B. - Also in the
fluid machinery 29B according to the second embodiment, since therefrigerant outlet chamber 78B through which the refrigerant (gas-phase refrigerant) after expansion is discharged from theexpander unit 60B (expander) is in communication with thecrank chamber 72B of thepump unit 50B (piston pump), it is possible to obtain the same effects as that of the fluid machinery (pump-integratedexpander 29A) according to the first embodiment. - That is, since the interior of the
crank chamber 72B can be set to a state in which the liquid-phase refrigerant is easily gasified, it is possible to reduce the amount of liquid-phase refrigerant that flows into thecrank chamber 72B and/or is stored in thecrank chamber 72B. Furthermore, even if the liquid-phase refrigerant flows into thecrank chamber 72B, the flowed-in liquid-phase refrigerant can be discharged from theoutlet port 79B, and thus, the storage of the refrigerant in thecrank chamber 72B can be reduced. Furthermore, since the gas-phase refrigerant after expansion of relatively high temperature flows to the outside through thecrank chamber 72B, even when the liquid-phase refrigerant is stored in thecrank chamber 72B, it is possible to cause the liquid-phase refrigerant to flow (discharge) out ofoutlet port 79B as the gas-phase refrigerant, by gasifying the majority of the liquid-phase refrigerant. - In the
fluid machinery 29B of the above-described embodiment, theoutlet port 79B through which the refrigerant after expansion flows out toward thecondenser 24 is open to the crankchamber 72B, but is not limited thereto. Thecrank chamber 72B and therefrigerant outlet chamber 78B may have any configuration that enables communication with each other, and for example, as illustrated inFIG. 8 , theoutlet port 79B may be open to the housing space of thegenerator motor unit 110 of thefirst housing 121. Furthermore, theoutlet port 79B may be open to therefrigerant outlet chamber 72B, or a communication passage through which the housing space of the generator motor 90 communicates with thecrank chamber 72B may be formed in thefirst housing 121. - Furthermore, a communication passage through which the
crank chamber 72B and therefrigerant outlet chamber 78B directly communicate with each other may be formed in the housing 120 (thefirst housing 121, thesecond housing 122, and the connecting member 123), or a communication passage through which theoutlet port 79B and therefrigerant outlet chamber 78B in the configuration illustrated inFIG. 6 communicate with each other may be formed in thehousing 120. Furthermore, these communication passages may be provided outside thehousing 120. Also in this case, since the interior of thecrank chamber 72B can be set to a state in which the liquid-phase refrigerant is easily gasified, it is possible to reduce the amount of liquid-phase refrigerant that flows into thecrank chamber 72A and/or is stored in thecrank chamber 72B. - Moreover, in the
fluid machinery 29B of the above-described embodiment, theexpander 23, the pump (piston pump) 25, and thegenerator motor 100 are integrally connected, but thegenerator motor 100 may be used as a generator. In this case, it is preferable that the exhaustheat recovery apparatus 1B have atransmission mechanism 3 similar to the exhaustheat recovery apparatus 1A according to the first embodiment, and be configured to be able to drive thepump 25 by theengine 10. - The fluid machinery has been described above which is applied to the Rankine cycle and has the expander that generates power by expanding the gas-phase refrigerant and the piston pump that pumps the liquid-phase refrigerant. However, it is also possible to apply the technical concept of the present invention to a case in which the expander and the piston pump are separately provided. In this case, in the Rankine cycle, a communication passage through which the crank chamber of the piston pump that pumps the liquid-phase refrigerant communicates with a portion that is on the outlet side of the expander, for example, the communication passage through which the crank chamber of the piston pump communicates with the refrigerant flow passage leading to the condenser from the expander may be provided.
-
- 1A, 1B Exhaust heat recovery apparatus
- 2A, 2B Rankine cycle
- 10 Engine
- 21 Refrigerant circulating passage
- 22 Heater
- 23 Expander
- 24 Condenser
- 25 Pump (piston pump)
- 28 Rotating shaft
- 29A Pump-integrated expander (fluid machinery)
- 29B Expander-pump-generator motor-integrated fluid machinery
- 50A, 50B Pump unit
- 51 Piston
- 52 Connecting rod
- 60A, 60B Expander unit
- 61 Fixed scroll
- 62 Orbiting scroll
- 71 a, 71 b Bearing (bearing section)
- 70 Housing
- 72A, 72B Crank chamber
- 77 Anti-rotation member
- 78A, 78B Refrigerant outlet chamber
- 79A, 79B Outlet port
- 80 Driven crank mechanism
- 91 Communication passage
- 100 Generator motor
- 105 Rotating shaft
- 110 Generator motor unit
- 111 Rotor
- 112 Stator
- 120 Housing
Claims (8)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012-106428 | 2012-05-08 | ||
JP2012106428A JP5984492B2 (en) | 2012-05-08 | 2012-05-08 | Fluid machinery |
PCT/JP2013/062786 WO2013168682A1 (en) | 2012-05-08 | 2013-05-02 | Fluid machinery |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150098845A1 true US20150098845A1 (en) | 2015-04-09 |
Family
ID=49550719
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/399,456 Abandoned US20150098845A1 (en) | 2012-05-08 | 2013-05-02 | Fluid Machinery |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150098845A1 (en) |
JP (1) | JP5984492B2 (en) |
CN (1) | CN104271951A (en) |
DE (1) | DE112013002403T5 (en) |
WO (1) | WO2013168682A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150047351A1 (en) * | 2011-09-30 | 2015-02-19 | Takayuki Ishikawa | Waste heat utilization apparatus |
US11454116B2 (en) | 2018-06-08 | 2022-09-27 | Sanden Automotive Components Corporation | Scroll expander with exhaust path thru bearings and a partition plate |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR102170132B1 (en) * | 2014-11-12 | 2020-10-27 | 한온시스템 주식회사 | Power generation system using heat source in vehicles |
JP2018115580A (en) * | 2017-01-17 | 2018-07-26 | いすゞ自動車株式会社 | Rankine cycle |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20010004387A1 (en) * | 1999-12-17 | 2001-06-21 | Barkaroe Stefan | Arrangement for reducing power dissipation in a line driver |
US20010026764A1 (en) * | 2000-03-30 | 2001-10-04 | Takashi Ogawa | Freon compressor |
US20040253133A1 (en) * | 2003-03-31 | 2004-12-16 | Hiroyuki Gennami | Scroll compressor |
US20060196204A1 (en) * | 2005-03-02 | 2006-09-07 | Denso Corporation | Fluid pump and fluid machine |
US20070160482A1 (en) * | 2006-01-12 | 2007-07-12 | Anest Iwata Corporation | Combined compressing apparatus |
US20070245732A1 (en) * | 2006-04-17 | 2007-10-25 | Denso Corporation | Fluid machine, rankine cycle and control method |
US20080232992A1 (en) * | 2004-03-17 | 2008-09-25 | Tetsuya Okamoto | Fluid Machine |
US20090104060A1 (en) * | 2007-10-19 | 2009-04-23 | Mitsubishi Heavy Industries, Ltd. | Compressor |
US20090139262A1 (en) * | 2006-05-17 | 2009-06-04 | Panasonic Corporation | Expander-compressor unit |
US20100003147A1 (en) * | 2007-01-15 | 2010-01-07 | Panasonic Corporation | Expander-integrated compressor |
US20100254844A1 (en) * | 2007-11-21 | 2010-10-07 | Panasonic Corporation | Expander-compressor unit |
US20100263404A1 (en) * | 2007-11-21 | 2010-10-21 | Panasonic Corporation | Expander-compressor unit |
US8192185B2 (en) * | 2007-11-21 | 2012-06-05 | Panasonic Corporation | Expander-compressor unit |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4042417B2 (en) * | 2002-01-28 | 2008-02-06 | 株式会社日立製作所 | Positive displacement machine |
JP4014583B2 (en) * | 2003-06-20 | 2007-11-28 | 株式会社デンソー | Fluid machinery |
JP2008175496A (en) * | 2007-01-22 | 2008-07-31 | Matsushita Electric Ind Co Ltd | Expander integrated compressor and refrigerating cycle device including it |
JP2008215212A (en) * | 2007-03-05 | 2008-09-18 | Matsushita Electric Ind Co Ltd | Expander integrated type compressor and refrigerating cycle device |
JP2009013798A (en) * | 2007-07-02 | 2009-01-22 | Panasonic Corp | Expander-integrated compressor |
JP5389608B2 (en) * | 2009-11-02 | 2014-01-15 | サンデン株式会社 | Fluid machinery and waste heat utilization system for automobiles using fluid machinery |
-
2012
- 2012-05-08 JP JP2012106428A patent/JP5984492B2/en active Active
-
2013
- 2013-05-02 DE DE112013002403.9T patent/DE112013002403T5/en active Pending
- 2013-05-02 WO PCT/JP2013/062786 patent/WO2013168682A1/en active Application Filing
- 2013-05-02 US US14/399,456 patent/US20150098845A1/en not_active Abandoned
- 2013-05-02 CN CN201380024200.4A patent/CN104271951A/en active Pending
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20010004387A1 (en) * | 1999-12-17 | 2001-06-21 | Barkaroe Stefan | Arrangement for reducing power dissipation in a line driver |
US20010026764A1 (en) * | 2000-03-30 | 2001-10-04 | Takashi Ogawa | Freon compressor |
US20040253133A1 (en) * | 2003-03-31 | 2004-12-16 | Hiroyuki Gennami | Scroll compressor |
US20080232992A1 (en) * | 2004-03-17 | 2008-09-25 | Tetsuya Okamoto | Fluid Machine |
US20060196204A1 (en) * | 2005-03-02 | 2006-09-07 | Denso Corporation | Fluid pump and fluid machine |
US20070160482A1 (en) * | 2006-01-12 | 2007-07-12 | Anest Iwata Corporation | Combined compressing apparatus |
US20070245732A1 (en) * | 2006-04-17 | 2007-10-25 | Denso Corporation | Fluid machine, rankine cycle and control method |
US20090139262A1 (en) * | 2006-05-17 | 2009-06-04 | Panasonic Corporation | Expander-compressor unit |
US8186179B2 (en) * | 2006-05-17 | 2012-05-29 | Panasonic Corporation | Expander-compressor unit |
US20100003147A1 (en) * | 2007-01-15 | 2010-01-07 | Panasonic Corporation | Expander-integrated compressor |
US20090104060A1 (en) * | 2007-10-19 | 2009-04-23 | Mitsubishi Heavy Industries, Ltd. | Compressor |
US20100254844A1 (en) * | 2007-11-21 | 2010-10-07 | Panasonic Corporation | Expander-compressor unit |
US20100263404A1 (en) * | 2007-11-21 | 2010-10-21 | Panasonic Corporation | Expander-compressor unit |
US8192185B2 (en) * | 2007-11-21 | 2012-06-05 | Panasonic Corporation | Expander-compressor unit |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150047351A1 (en) * | 2011-09-30 | 2015-02-19 | Takayuki Ishikawa | Waste heat utilization apparatus |
US9441503B2 (en) * | 2011-09-30 | 2016-09-13 | Sanden Holdings Corporation | Waste heat utilization apparatus |
US11454116B2 (en) | 2018-06-08 | 2022-09-27 | Sanden Automotive Components Corporation | Scroll expander with exhaust path thru bearings and a partition plate |
Also Published As
Publication number | Publication date |
---|---|
CN104271951A (en) | 2015-01-07 |
DE112013002403T5 (en) | 2015-01-29 |
JP2013234585A (en) | 2013-11-21 |
WO2013168682A1 (en) | 2013-11-14 |
JP5984492B2 (en) | 2016-09-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2143880B1 (en) | Fluid machine, rankine circuit, and system for utilizing waste heat from vehicle | |
EP2412935A1 (en) | Fluid machine | |
US20060073050A1 (en) | Complex fluid machine | |
US20200102964A1 (en) | Centrifugal compressor | |
US20150098845A1 (en) | Fluid Machinery | |
CN101042094A (en) | Waste heat collecting system having expansion device | |
US9546656B2 (en) | Fluid machine | |
US20150033743A1 (en) | Fluid Machine | |
US20150033744A1 (en) | Fluid Machine | |
JP5291782B2 (en) | Rankine circuit and vehicle waste heat utilization system | |
JP2012026452A (en) | Fluid machine, rankine circuit using the fluid machine, and waste heat utilization system for vehicle | |
US20040247458A1 (en) | Fluid machine | |
US6707204B2 (en) | Rotational unit | |
US20150023824A1 (en) | Scroll-Type Expander And Fluid Machine Provided With Same | |
CN105840513B (en) | A kind of double rolling-piston-type motor compressors | |
KR102071233B1 (en) | Compressor, power generating system and method thereof | |
JP2010038120A (en) | Fluid machine | |
KR101273325B1 (en) | Hydraulic pump integrated electric motor | |
CN103781994B (en) | Fluid device | |
JP2013151941A (en) | Waste heat utilization system | |
JP2004340027A (en) | Fluid machinery | |
JP2013223405A (en) | Starter generator | |
JP2008180148A (en) | Fluid machine | |
JP2005273452A (en) | Fluid machine | |
EP2551449A1 (en) | Fluid machine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SANDEN CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:NAKAMURA, SHINJI;REEL/FRAME:034147/0580 Effective date: 20141014 |
|
AS | Assignment |
Owner name: SANDEN HOLDINGS CORPORATION, JAPAN Free format text: CHANGE OF NAME;ASSIGNOR:SANDEN CORPORATION;REEL/FRAME:038489/0677 Effective date: 20150402 |
|
AS | Assignment |
Owner name: SANDEN HOLDINGS CORPORATION, JAPAN Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE PROPERTY NUMBERS PREVIOUSLY RECORDED AT REEL: 038489 FRAME: 0677. ASSIGNOR(S) HEREBY CONFIRMS THE ASSIGNMENT;ASSIGNOR:SANDEN CORPORATION;REEL/FRAME:047208/0635 Effective date: 20150402 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
|
AS | Assignment |
Owner name: SANDEN HOLDINGS CORPORATION, JAPAN Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE TYPOGRAPHICAL ERRORS IN PATENT NOS. 6129293, 7574813, 8238525, 8083454, D545888, D467946, D573242, D487173, AND REMOVE 8750534 PREVIOUSLY RECORDED ON REEL 047208 FRAME 0635. ASSIGNOR(S) HEREBY CONFIRMS THE CHANGE OF NAME;ASSIGNOR:SANDEN CORPORATION;REEL/FRAME:053545/0524 Effective date: 20150402 |