US20140033710A1 - Rankine cycle system - Google Patents

Rankine cycle system Download PDF

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Publication number
US20140033710A1
US20140033710A1 US13/948,461 US201313948461A US2014033710A1 US 20140033710 A1 US20140033710 A1 US 20140033710A1 US 201313948461 A US201313948461 A US 201313948461A US 2014033710 A1 US2014033710 A1 US 2014033710A1
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US
United States
Prior art keywords
shaft portion
shaft
pump
cycle system
rankine cycle
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
Application number
US13/948,461
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English (en)
Inventor
Hidefumi Mori
Masao Iguchi
Fuminobu Enokijima
Hiroyuki Takei
Kojiro TAMARU
Fumihiko Ishiguro
Kazuo Katayama
Tomonori Sasaki
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Toyota Industries Corp
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Toyota Industries 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
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISHIGURO, FUMIHIKO, SASAKI, TOMONORI, TAMARU, Kojiro, ENOKIJIMA, FUMINOBU, IGUCHI, MASAO, KATAYAMA, KAZUO, MORI, HIDEFUMI, TAKEI, HIROYUKI
Publication of US20140033710A1 publication Critical patent/US20140033710A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants

Definitions

  • the present invention relates to a Rankine cycle system.
  • the Rankine cycle system of this type includes a pump, a boiler, an expansion machine, a condenser, and pipes.
  • the pipes are configured to allow working fluid to circulate from the pump, through the boiler and the expansion machine, and to the condenser.
  • This Rankine cycle system employs a fluid machine including the pump and the expansion machine coupled in a tandem manner.
  • the fluid machine includes a housing, a rotary shaft axially rotatably supported by the housing, and a pump mechanism and an expansion mechanism configured in the housing.
  • the pump mechanism is configured to be capable of sucking working fluid from a first intake port by the rotation of the rotary shaft, and discharging the working fluid from a first outlet port.
  • the expansion mechanism is configured to be capable of rotating the rotary shaft by causing expandable working fluid to flow into a second inlet port and to flow out from a second outlet port after expansion.
  • a power generating mechanism is also provided between the pump mechanism and the expansion mechanism.
  • a pulley of an electromagnetic clutch is fixed to the rotary shaft projecting partly from the housing. This pulley is driven by an engine.
  • the rotary shaft consists a first shaft portion, a second shaft portion, and a one-way clutch.
  • the first shaft portion drives the pump mechanism and the power generating mechanism.
  • the second shaft portion is provided concentrically with the first shaft portion.
  • the second shaft portion is driven by the expansion mechanism.
  • the one-way clutch is provided between the first shaft portion and the second shaft portion.
  • the first outlet port of the pump mechanism of the fluid machine is connected to the boiler by the pipe, and the boiler is connected to the second inlet port of the expansion mechanism by the pipe.
  • the second outlet port of the expansion mechanism is connected to the condenser by the pipe, and the condenser is connected to the first inlet port of the pump mechanism by the pipe.
  • the working fluid circulates from the pump mechanism via the boiler and the expansion mechanism to the condenser by turning the electromagnetic clutch ON and driving the pump mechanism of the fluid machine by the engine.
  • the working fluid is heated by waste heat of the engine in the boiler.
  • the heated working fluid drives the expansion mechanism.
  • the working fluid flowing through the expansion mechanism is heat-discharged by the condenser.
  • the one-way clutch blocks power transmission between the second shaft portion and the first shaft portion. Therefore, when the high-low pressure difference of the Rankine cycle system is small at the time of start of the engine or the like, there is a merit that a drag loss does not occur.
  • the one-way clutch allows power transmission between the second shaft portion and the first shaft portion, and hence the second shaft portion and the first shaft portion rotate integrally. Therefore, the electromagnetic clutch is turned OFF and the power generating mechanism is driven by the first shaft portion. In this manner, in this Rankine cycle system, waste heat may be effectively utilized.
  • a Rankine cycle system which is, in a configuration in which a first shaft portion configured to drive a pump mechanism and a second shaft portion configured to drive an expansion mechanism are coupled to each other, capable of continuing the circulation of working fluid by the expansion mechanism even when the pump mechanism is locked.
  • a Rankine cycle system of the invention comprises:
  • the pipes are connecting the pump to the condenser via the boiler and the expansion machine for circulating the working fluid, wherein
  • the pump includes a first shaft portion coupled to a drive source, and a pump mechanism capable of being rotated by the first shaft portion,
  • the expansion machine includes a second shaft portion coupled to the first shaft portion, and an expansion mechanism rotatable by the second shaft portion, and
  • a pump torque limiter is provided between the first shaft portion and the pump mechanism.
  • FIG. 1 is a schematic structure drawing illustrating a Rankine cycle system of Embodiment 1 to Embodiment 4.
  • FIG. 2 illustrates the Rankine cycle system of Embodiment 1 and is a cross-sectional view of a fluid machine.
  • FIG. 3 illustrates the Rankine cycle system of Embodiment 2 and is a cross-sectional view of a fluid machine.
  • FIG. 4 illustrates the Rankine cycle system of Embodiment 2 and is an enlarged partial plan view of a one-way clutch.
  • FIG. 5 illustrates the Rankine cycle system of Embodiment 2 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 6 illustrates the Rankine cycle system of Embodiment 2 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 7 illustrates the Rankine cycle system of Embodiment 2 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 8 illustrates the Rankine cycle system of Embodiment 3 and is an enlarged partial plan view of a one-way clutch.
  • FIG. 9 illustrates the Rankine cycle system of Embodiment 3 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 10 illustrates the Rankine cycle system of Embodiment 3 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 11 illustrates the Rankine cycle system of Embodiment 3 and is an enlarged partial cross-sectional view of the one-way clutch.
  • FIG. 12 illustrates the Rankine cycle system of Embodiment 4 and is a cross-sectional view of a fluid machine.
  • a Rankine cycle system of Embodiment 1 includes a pump 1 , a boiler 3 , an expansion machine 5 , a condenser 7 , and pipes 9 a to 9 d as illustrated in FIG. 1 .
  • This Rankine cycle system is configured to circulate refrigerant as working fluid by these members.
  • This Rankine cycle system employs a fluid machine 11 including the pump 1 and the expansion machine 5 coupled in a tandem manner.
  • the fluid machine 11 includes a housing 23 having a front housing 13 , a first fixed block 15 , a second fixed block 17 , a fixed scroll 19 , and a rear housing 21 as illustrated in FIG. 2 .
  • the front housing 13 is formed with a block chamber 13 a and a main shaft hole 13 b .
  • the main shaft hole 13 b communicates the outside and the block chamber 13 a .
  • the first fixed block 15 and the second fixed block 17 are fixed.
  • the block chamber 13 a is partitioned into a gear pump chamber 13 c , a storage chamber 13 d , and a hollow chamber 13 e .
  • the gear pump chamber 13 c is defined by the front housing 13 and the first fixed block 15 .
  • the storage chamber 13 d is formed in the interior of the second fixed block 17 .
  • the hollow chamber 13 e is defined by the front housing 13 and the second fixed block 17 for reducing the weight.
  • a bearing apparatus 25 and a shaft seal apparatus 27 are provided in the interior of the main shaft hole 13 b .
  • a rotary shaft 29 is axially rotatably supported by the bearing apparatus 25 and the shaft seal apparatus 27 .
  • the rotary shaft 29 corresponds to a first shaft portion and a second shaft portion.
  • the rotary shaft 29 extends orthogonally to the gear pump chamber 13 c and extends into the storage chamber 13 d .
  • a pulley 33 is fixed to the rotary shaft 29 projecting from the front housing 13 .
  • the front housing 13 is provided with a bearing apparatus 35 .
  • the pulley 33 is configured to be rotatable about the main shaft hole 13 b by the bearing apparatus 35 .
  • the pulley 33 is configured to be driven by an engine by a belt, not illustrated.
  • the engine corresponds to a drive source.
  • the engine is supplied with compressed air by a turbocharger.
  • the front housing 13 and the first fixed block 15 are formed with a secondary shaft hole 13 f parallel to the main shaft hole 13 b .
  • Two bearing apparatuses 37 are provided in the interior of the secondary shaft hole 13 f .
  • a secondary shaft 39 is axially rotatably supported by the bearing apparatuses 37 .
  • the secondary shaft 39 extends orthogonally to the gear pump chamber 13 c.
  • a main gear 41 is provided on the rotary shaft 29 by a pump torque limiter 43 .
  • the main gear 41 is configured to be rotatable by the rotary shaft 29 .
  • the main gear 41 corresponds to a pump mechanism.
  • the pump torque limiter 43 is configured not to transmit power between the rotary shaft 29 and the main gear 41 when the rotary shaft 29 generates torque equal to or higher than a predetermined value with respect to the main gear 41 .
  • a secondary gear 45 is provided on the secondary shaft 39 .
  • the secondary gear 45 is press-fitted onto the secondary shaft 39 .
  • the main gear 41 and the secondary gear 45 engage with each other.
  • the pump 1 is composed of the rotary shaft 29 , the secondary shaft 39 , the main gear 41 , the secondary gear 45 , the front housing 13 , and the first fixed block 15 .
  • the front housing 13 is formed with a first inlet port 13 g and a first outlet port 13 h both communicating with the gear pump chamber 13 c.
  • the rotary shaft 29 integrally includes a large diameter portion 29 a formed into a column shape having a large diameter at a portion behind the gear pump chamber 13 c .
  • Two bearing apparatuses 47 are provided in the interior of the second fixed block 17 .
  • the large diameter portion 29 a is axially rotatably supported by the bearing apparatuses 47 .
  • An eccentric pin 29 b deviated with respect to the rotary shaft 29 is formed behind the large diameter portion 29 a .
  • the large diameter portion 29 a and the eccentric pin 29 b both function as the second shaft portion together with the rotary shaft 29 .
  • the fixed scroll 19 has a fixed base plate 19 a , a fixed peripheral wall 19 b , and a fixed spiral wall 19 c .
  • the fixed base plate 19 a is orthogonal to the rotary shaft 29 .
  • the fixed peripheral wall 19 b extends cylindrically in the axial direction around a peripheral edge of the fixed base plate 19 a .
  • the fixed peripheral wall 19 b is fixed to the front housing 13 .
  • the fixed spiral wall 19 c extends spirally in the axial direction toward the eccentric pin 29 b on the inside of the fixed base plate 19 a.
  • a movable scroll 49 is stored between the fixed scroll 19 and the second fixed block 17 .
  • the movable scroll 49 has a movable base plate 49 a , a boss portion 49 b , and a movable spiral wall 49 c .
  • the movable base plate 49 a is orthogonal to the rotary shaft 29 .
  • the boss portion 49 b extends cylindrically at a center of the movable base plate 49 a in the axial direction toward the eccentric pin 29 b .
  • the fixed spiral wall 49 c extends spirally and protrudes in the axial direction toward the fixed scroll 19 on the inside of the movable base plate 49 a .
  • the fixed scroll 19 and the movable scroll 49 engage each other whereby an expansion chamber 51 is defined.
  • the movable scroll 49 corresponds to an expansion mechanism.
  • a bush balancer 53 is provided between the large diameter portion 29 a of the rotary shaft 29 and the movable scroll 49 .
  • the bush balancer 53 is formed with a pin hole 53 a extending in the axial direction.
  • the eccentric pin 29 b is inserted through the pin hole 53 a .
  • a bearing apparatus 55 is provided in the interior of the boss portion 49 b of the movable scroll 49 .
  • the bush balancer 53 is axially rotatably supported by the bearing apparatus 55 .
  • a plurality of rotation preventing pins 57 a are fixed to a back surface of the second fixed block 17 .
  • the respective rotation preventing pins 57 a extend toward the movable base plate 49 a of the movable scroll 49 .
  • a plurality of rotation preventing holes 57 b are formed so as to be depressed on a front surface of the movable base plate 49 a .
  • Distal end portions of the rotation preventing pins 57 a are loosely fitted into the respective rotation preventing holes 57 b .
  • Cylindrical rings 57 c are loosely fitted into the respective rotation preventing holes 57 b .
  • the fixed base plate 19 a of the fixed scroll 19 is formed with an intake port 19 d communicating with the expansion chamber 51 at a center thereof.
  • the fixed scroll 19 and the rear housing 21 define an intake chamber 59 which communicates with the intake port 19 d .
  • the rear housing 21 is formed with a second inlet port 21 a communicating with the intake chamber 59 .
  • the fixed scroll 19 is formed with a second outlet port 19 e communicating with the expansion chamber 51 on the outer peripheral side.
  • the expansion machine 5 includes the fixed scroll 19 , the rear housing 21 , the movable scroll 49 , the second fixed block 17 , the bush balancer 53 , the large diameter portion 29 a , the eccentric pin 29 b , the respective rotation preventing pins 57 a , and the respective rings 57 c , or the like.
  • the first outlet port 13 h of the pump 1 of the fluid machine 11 is connected to the boiler 3 by the pipe 9 a and the boiler 3 is connected to the second inlet port 21 a of the expansion machine 5 by the pipe 9 b .
  • the second outlet port 19 e of the expansion mechanism 5 is connected to the condenser 7 by the pipe 9 c
  • the condenser 7 is connected to the first inlet port 13 g of the pump 1 by the pipe 9 d.
  • the rotary shaft 29 is rotated. If the main gear 41 is not subjected to seizure or the like, and the pump torque limiter 43 transmits the power from the rotary shaft 29 to the main gear 41 , the pump 1 is driven.
  • the pump 1 sucks refrigerant from the first inlet port 13 g and discharges the refrigerant from the first outlet port 13 h . Accordingly, the refrigerant is supplied from the pump 1 to the boiler 3 .
  • the refrigerant is heated by heat of compressed air supplied to the engine.
  • the refrigerant may be heated by a back-flow exhaust air or the like flowing back to the engine, as a heat source.
  • the refrigerant expandable by being heated flows from the second inlet port 21 a of the expansion machine 5 , and the refrigerant after the expansion flows out from the second outlet port 19 e . Accordingly, the rotary shaft 29 is rotated.
  • the rotation of the rotary shaft 29 may be regenerated for the engine or the like or may be provided for power generation for a power generator or the power generating mechanism.
  • Heat of the refrigerant passing through the expansion machine 5 is radiated by the condenser 7 . In this manner, in this Rankine cycle system, waste heat may be used effectively while cooling the compressed air.
  • the pump torque limiter 43 blocks power transmission between the rotary shaft 29 and the main gear 41 . Therefore, even when the pump 1 is stopped, the rotary shaft 29 allows continuation of the rotation. Therefore, the power is transmitted to the eccentric pin 29 b , and the expansion machine 5 is driven by the engine continuously. Therefore, the expansion machine 5 may be used as a blower to continue circulation of the refrigerant.
  • the compressed air may be cooled preferably by continuing the circulation of the refrigerant by the expansion machine 5 .
  • the Rankine cycle system of Embodiment 2 employs a fluid machine 12 illustrated in FIG. 3 .
  • the fluid machine 12 includes a first shaft 30 axially rotatably supported in the main shaft hole 13 b of the front housing 13 .
  • the first shaft 30 corresponds to the first shaft portion.
  • a sensing shaft 61 formed into a cylindrical shape and concentric with the first shaft 30 is provided between the pump torque limiter 43 and the main gear 41 .
  • the two bearing apparatuses 47 provided in the second fixed block 17 axially rotatably support a bottomed cylindrical second shaft 32 .
  • the second shaft 32 corresponds to the second shaft portion.
  • the first shaft 30 and the second shaft 32 are concentric.
  • the second shaft 32 is formed with an eccentric pin 32 b deviated with respect to the first shaft 30 and the second shaft 32 .
  • a one-way clutch 65 and a bearing apparatus 67 are provided between the first shaft 30 and the second shaft 32 in the radial direction.
  • a rear end of the sensing shaft 61 is bent radially outward in a flange shape.
  • a disc spring 63 is provided between the rear end of the sensing shaft 61 and the one-way clutch 65 in the axial direction. The disc spring 63 corresponds to a sensing spring.
  • the one-way clutch 65 includes an outer race 71 , an inner race 72 , a plurality of column-shaped rollers 73 and a holder 74 .
  • the outer race 71 rotates integrally with the second shaft 32 .
  • the inner race 72 rotates integrally with the first shaft 30 .
  • the respective rollers 73 are provided between the outer race 71 and the inner race 72 .
  • the holder 74 holds the respective rollers 73 .
  • the inner peripheral surface of the outer race 71 forms a cylindrical inner peripheral rolling surface 71 a .
  • the outer peripheral surface of the inner race 72 is formed into a polygonal shape being concentric with the first shaft 30 .
  • the outer peripheral surface of the inner race 72 has a plurality of plane portions 720 and a plurality of corner portions 721 and 722 .
  • the corner portions 721 are on the front side in a direction of rotation R of the first shaft 30 .
  • the corner portions 722 are on the rear side in a direction of rotation R of the first Shaft 30 . All the entire plane portions 720 and the corner portions 721 and 722 correspond to an outer peripheral rolling surface 72 a .
  • the respective rollers 73 are stored between the inner peripheral rolling surface 71 a and the outer peripheral rolling surfaces 72 a .
  • the same number of stators 75 as the rollers 73 are fixed to the inner race 72 .
  • a forward urging spring 77 is provided between each of the stators 75 and each of the rollers 73 .
  • the respective forward urging springs 77 have a forward urging force which causes the respective rollers 73 to be positioned on the front side in the direction of rotation R of the first shaft 30 .
  • Boss portions 74 a and 74 b extending in the axial direction are formed in the holder 74 between the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a .
  • the both boss portions 74 a and 74 b sandwich front ends and rear ends of the respective rollers 73 . Accordingly, the both boss portions 74 a and 74 b rotatably hold the front ends and the rear ends of the respective rollers 73 .
  • the disc spring 63 illustrated in FIG. 3 is provided between the sensing shaft 61 and the holder 74 .
  • Other configurations are the same as Embodiment 1.
  • the first shaft 30 is rotated. If the pump 1 is not subjected to seizure or the like, and the pump torque limiter 43 transmits the power from the first shaft 30 to the sensing shaft 61 and the main gear 41 , the pump 1 is driven.
  • the pump 1 sucks refrigerant from the first inlet port 13 g and discharges the refrigerant from the first outlet port 13 h . Therefore, the refrigerant is supplied from the pump 1 to the boiler 3 . In the boiler 3 , the refrigerant is heated by compressed air.
  • the refrigerant expandable by being heated flows from the second inlet port 21 a of the expansion machine 5 , and the refrigerant after the expansion flows out from the second outlet port 19 e . Therefore, the second shaft 32 is rotated in the same direction as the first shaft 30 .
  • the respective rollers 73 held in the holder 74 compress the respective forward urging springs 77 and, at the same time, move relatively in the direction opposite to the direction of rotation R (move counterclockwise in the drawing) due to the difference in rotating speed between the first shaft 30 and the holder 74 .
  • the respective rollers 73 are positioned respectively on the respective plane portions 720 of the inner race 72 , engagement between the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a by the respective rollers 73 is released. Therefore, the one-way clutch 65 blocks power transmission between the second shaft 32 and the first shaft 30 .
  • the respective rollers 73 rotate relatively in the same direction as the direction of rotation R (move clockwise in the drawing) in the one-way clutch 65 . Accordingly, in the one-way clutch 65 , the respective rollers 73 are positioned respectively on the sides of the respective corner portions 721 of the inner race 72 , and are engaged between the outer race 71 and the inner race 72 . Therefore, the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a engage by the respective rollers 73 . Accordingly, the one-way clutch 65 allows power transmission between the second shaft 32 and the first shaft 30 .
  • the second shaft 32 and the first shaft 30 rotate integrally by being directly connected.
  • the rotation of the first shaft 30 may be regenerated for the engine or the like or may be provided for power generation for the power generator or the power generating mechanism.
  • Heat of the refrigerant passing through the expansion machine 5 is discharged by the condenser 7 . In this manner, in this Rankine cycle system, waste heat may be used effectively while cooling the compressed air.
  • the pump torque limiter 43 does not transmit the power from the first shaft 30 to the sensing shaft 61 and the main gear 41 . Therefore, the sensing shaft 61 stops rotation and hence, the first shaft 30 continues to rotate even when the pump 1 is stopped. In this case, the sensing shaft 61 pulls the holder 74 of the one-way clutch 65 toward the rear side in the direction of rotation R by the disc spring 63 . Therefore, in the one-way clutch 65 , as illustrated in FIG.
  • the respective rollers 73 are positioned respectively at the respective corner portions 722 on the rear side of the inner race 72 and are engaged between the outer race 71 and the inner race 72 . Therefore, the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a engage by the respective rollers 73 . Accordingly, the one-way clutch 65 allows power transmission between the second shaft 32 and the first shaft 30 . Then, the second shaft 32 and the first shaft 30 rotate integrally by being directly connected. Therefore, power is transmitted from the engine to the second shaft 32 by the first shaft 30 , so that the expansion machine 5 may be used as a blower to continue circulation of the working fluid.
  • the Rankine cycle system may achieve the same effects and advantages as Embodiment 1.
  • this Rankine cycle system when the high-low pressure difference is small, there arises a merit that a drag loss of the expansion machine 5 does not occur.
  • the configuration is simple and costs are lower in comparison with the configuration in which the expansion machine 5 is driven by an external signal by sensing the lock of the pump 1 .
  • the Rankine cycle system of Embodiment 3 employs a one-way clutch 66 illustrated in FIGS. 8 to 11 .
  • the one-way clutch 66 includes a holder 78 and a plurality of rearward urging springs 79 .
  • the same number of pairs of stators 75 and 76 as the rollers 73 are fixed to the inner race 72 .
  • the respective rollers 73 are stored between the respective pairs of stators 75 and 76 .
  • the forward urging spring 77 is provided between each of the stators 75 and each of the rollers 73 .
  • the rearward urging spring 79 is provided between each of the rollers 73 and each of the stators 76 .
  • the respective rearward urging springs 79 have a rearward urging force which causes the respective rollers 73 to be positioned on the rear side in the direction of rotation R of the first shaft 30 .
  • the rearward urging force is set to be weaker than the forward urging force of the forward urging springs 77 .
  • this one-way clutch 66 if the rotational speed of the second shaft 32 is smaller than the rotational speed of the first shaft 30 , the respective partitioning walls 78 a move relatively in the direction opposite from the direction of rotation R as illustrated in FIG. 10 (move counterclockwise in the drawing) due to the difference in rotating speed between the first shaft 30 and the holder 78 , and compress the respective forward urging springs 77 respectively.
  • the respective rollers 73 move in the opposite direction from the direction of rotation R and are positioned on the respective plane portions 720 of the inner race 72 respectively. Therefore, engagement between the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a by the respective rollers 73 is released. Accordingly, the one-way clutch 66 blocks power transmission between the second shaft 32 and the first shaft 30 .
  • the respective rollers 73 move in the same direction as the direction of rotation R and are positioned at the respective corner portions 721 on the front side of the inner race 72 , thereby becoming engaged between the outer race 71 and the inner race 72 . Therefore, the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a engage by the respective rollers 73 .
  • the one-way clutch 66 allows power transmission between the second shaft 32 and the first shaft 30 .
  • the pump torque limiter 43 does not transmit the power from the first shaft 30 to the sensing shaft 61 and the main gear 41 . Therefore, the sensing shaft 61 stops rotation and hence the first shaft 30 continues to rotate even when the pump 1 is stopped. In this case, the sensing shaft 61 pulls the holder 78 of the one-way clutch 66 toward the rear side in the direction of rotation R by the disc spring 63 . Therefore, in the one-way clutch 66 , as illustrated in FIG.
  • the respective rollers 73 are positioned respectively at the respective corner portions 722 on the rear side of the inner race 72 and are engaged between the outer race 71 and the inner race 72 . Therefore, the inner peripheral rolling surface 71 a and the outer peripheral rolling surface 72 a engage by the respective rollers 73 .
  • the one-way clutch 66 allows power transmission between the second shaft 32 and the first shaft 30 . Then, the second shaft 32 and the first shaft 30 rotate integrally by being directly connected. Therefore, power is transmitted from the engine to the second shaft 32 by the first shaft 30 , so that the expansion machine 5 may be used as a blower to continue circulation of the working fluid.
  • Embodiment 4 As illustrated in FIG. 12 , an expansion machine torque limiter 69 is provided between the second shaft 32 and the first shaft 30 . In contrast, the sensing shaft 61 and the disc spring 63 are not provided. Other configurations are the same as Embodiment 2.
  • the expansion machine 5 may be used as a blower to continue circulation of the refrigerant.
  • the expansion machine torque limiter 69 blocks the power transmission between the second shaft 32 and the first shaft 30 .
  • the power generating mechanism may be provided between the pump 1 and the expansion machine 5 .
  • the invention is applicable to the Rankine cycle system for a vehicle, a waste heat utilizing apparatus or the like.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US13/948,461 2012-07-31 2013-07-23 Rankine cycle system Abandoned US20140033710A1 (en)

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Application Number Priority Date Filing Date Title
JP2012169091A JP2014029120A (ja) 2012-07-31 2012-07-31 ランキンサイクル
JP2012-169091 2012-07-31

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US20140033710A1 true US20140033710A1 (en) 2014-02-06

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US13/948,461 Abandoned US20140033710A1 (en) 2012-07-31 2013-07-23 Rankine cycle system

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US (1) US20140033710A1 (ja)
EP (1) EP2703608A2 (ja)
JP (1) JP2014029120A (ja)
CN (1) CN103573310A (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170089295A1 (en) * 2015-09-29 2017-03-30 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Heat energy recovery system

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5145042A (en) * 1989-05-26 1992-09-08 Roger Macpherson Roller clutch
JPH05126029A (ja) * 1991-10-31 1993-05-21 Toyota Autom Loom Works Ltd 可変容量ピストンポンプ
US6474457B2 (en) * 2000-10-19 2002-11-05 Aichi Kikai Kogyo Kabushiki Kaisha Bi-directional clutch
US7249459B2 (en) * 2003-06-20 2007-07-31 Denso Corporation Fluid machine for converting heat energy into mechanical rotational force
EP1939479B1 (en) * 2006-09-28 2012-07-11 JTEKT Corporation Torque limiter-incorporating one-way clutch
JP2008164030A (ja) * 2006-12-27 2008-07-17 Jtekt Corp 一方向クラッチ
JP5084342B2 (ja) 2007-04-27 2012-11-28 サンデン株式会社 流体機械、該流体機械を用いたランキン回路及び車両の廃熱利用システム
JP2010249130A (ja) * 2009-03-27 2010-11-04 Sanden Corp 流体機械

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170089295A1 (en) * 2015-09-29 2017-03-30 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Heat energy recovery system
US9995244B2 (en) * 2015-09-29 2018-06-12 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Heat energy recovery system

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JP2014029120A (ja) 2014-02-13
EP2703608A2 (en) 2014-03-05

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