US20140033710A1 - Rankine cycle system - Google Patents
Rankine cycle system Download PDFInfo
- 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
- Authority
- 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
Links
Images
Classifications
-
- 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.
Landscapes
- 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)
Abstract
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, a Rankine cycle system which is capable of continuing the circulation of working fluid by an expansion machine even when the pump mechanism is locked is provided. This Rankine cycle system of the invention employs a pump and an expansion machine coupled in a tandem manner. A first shaft of the pump and a second shaft of the expansion machine are concentric and the first shaft is capable of transmitting power to the second shaft. A pump torque limiter is provided between the first shaft and a main gear. A one-way clutch is provided between a sensing shaft and the second shaft.
Description
- The present invention relates to a Rankine cycle system.
- A Rankine cycle system of the background art is disclosed in
patent publication 1. 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. In other words, 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. In the housing, a power generating mechanism is also provided between the pump mechanism and the expansion mechanism.
- In this fluid machine, 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.
- In this Rankine cycle system, 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.
- In this Rankine cycle system, 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. During the time, 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.
- Therefore, if the first shaft portion and the second shaft portion rotate in the same direction and the rotational speed of the second shaft portion is smaller than the rotational speed of the first shaft portion, 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.
- Then, when the rotational speed of the second shaft portion reaches to exceed the rotational speed of the first shaft portion, 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.
-
- {Patent Publication 1} JP-A-2008-274834
- However, in the Rankine cycle system of the background art described above, when the pump mechanism is locked by seizure or the like, the first shaft portion stops together with the pump mechanism, and hence engine torque cannot be transmitted to the expansion mechanism via the second shaft portion, and the expansion mechanism is stopped. In this case, the expansion mechanism cannot be operated as a blower by driving the expansion mechanism by the engine, and hence the circulation of the working fluid cannot be continued.
- In view of such circumstance of the background art described above, it is an object of the invention to provide 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.
- In order to solve the above-described problem, a Rankine cycle system of the invention comprises:
- a pump; a boiler; an expansion machine; a condenser; and pipes,
- 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.
- Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
-
FIG. 1 is a schematic structure drawing illustrating a Rankine cycle system ofEmbodiment 1 to Embodiment 4. -
FIG. 2 illustrates the Rankine cycle system ofEmbodiment 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 ofEmbodiment 3 and is an enlarged partial plan view of a one-way clutch. -
FIG. 9 illustrates the Rankine cycle system ofEmbodiment 3 and is an enlarged partial cross-sectional view of the one-way clutch. -
FIG. 10 illustrates the Rankine cycle system ofEmbodiment 3 and is an enlarged partial cross-sectional view of the one-way clutch. -
FIG. 11 illustrates the Rankine cycle system ofEmbodiment 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. - Referring now to the drawings,
Embodiments 1 to 4 in which the invention is embodied have been described. - A Rankine cycle system of
Embodiment 1 includes apump 1, aboiler 3, anexpansion machine 5, acondenser 7, andpipes 9 a to 9 d as illustrated inFIG. 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 thepump 1 and theexpansion machine 5 coupled in a tandem manner. In other words, thefluid machine 11 includes ahousing 23 having afront housing 13, a firstfixed block 15, a secondfixed block 17, afixed scroll 19, and arear housing 21 as illustrated inFIG. 2 . - The
front housing 13 is formed with ablock chamber 13 a and amain shaft hole 13 b. Themain shaft hole 13 b communicates the outside and theblock chamber 13 a. In the interior of theblock chamber 13 a, the first fixedblock 15 and the second fixedblock 17 are fixed. Theblock chamber 13 a is partitioned into agear pump chamber 13 c, astorage chamber 13 d, and ahollow chamber 13 e. Thegear pump chamber 13 c is defined by thefront housing 13 and the first fixedblock 15. Thestorage chamber 13 d is formed in the interior of the second fixedblock 17. Thehollow chamber 13 e is defined by thefront housing 13 and the second fixedblock 17 for reducing the weight. - A bearing
apparatus 25 and ashaft seal apparatus 27 are provided in the interior of themain shaft hole 13 b. Arotary shaft 29 is axially rotatably supported by the bearingapparatus 25 and theshaft seal apparatus 27. Therotary shaft 29 corresponds to a first shaft portion and a second shaft portion. Therotary shaft 29 extends orthogonally to thegear pump chamber 13 c and extends into thestorage chamber 13 d. Apulley 33 is fixed to therotary shaft 29 projecting from thefront housing 13. Thefront housing 13 is provided with abearing apparatus 35. Thepulley 33 is configured to be rotatable about themain shaft hole 13 b by the bearingapparatus 35. Thepulley 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 fixedblock 15 are formed with asecondary shaft hole 13 f parallel to themain shaft hole 13 b. Two bearingapparatuses 37 are provided in the interior of thesecondary shaft hole 13 f. Asecondary shaft 39 is axially rotatably supported by the bearingapparatuses 37. Thesecondary shaft 39 extends orthogonally to thegear pump chamber 13 c. - In the interior of the
gear pump chamber 13 c, amain gear 41 is provided on therotary shaft 29 by apump torque limiter 43. Themain gear 41 is configured to be rotatable by therotary shaft 29. Themain gear 41 corresponds to a pump mechanism. Thepump torque limiter 43 is configured not to transmit power between therotary shaft 29 and themain gear 41 when therotary shaft 29 generates torque equal to or higher than a predetermined value with respect to themain gear 41. In the interior of thegear pump chamber 13 c, asecondary gear 45 is provided on thesecondary shaft 39. Thesecondary gear 45 is press-fitted onto thesecondary shaft 39. Themain gear 41 and thesecondary gear 45 engage with each other. Thepump 1 is composed of therotary shaft 29, thesecondary shaft 39, themain gear 41, thesecondary gear 45, thefront housing 13, and the first fixedblock 15. - The
front housing 13 is formed with afirst inlet port 13 g and afirst outlet port 13 h both communicating with thegear pump chamber 13 c. - The
rotary shaft 29 integrally includes alarge diameter portion 29 a formed into a column shape having a large diameter at a portion behind thegear pump chamber 13 c. Two bearingapparatuses 47 are provided in the interior of the second fixedblock 17. Thelarge diameter portion 29 a is axially rotatably supported by the bearingapparatuses 47. Aneccentric pin 29 b deviated with respect to therotary shaft 29 is formed behind thelarge diameter portion 29 a. Thelarge diameter portion 29 a and theeccentric pin 29 b both function as the second shaft portion together with therotary shaft 29. - The fixed
scroll 19 has a fixedbase plate 19 a, a fixedperipheral wall 19 b, and a fixedspiral wall 19 c. The fixedbase plate 19 a is orthogonal to therotary shaft 29. The fixedperipheral wall 19 b extends cylindrically in the axial direction around a peripheral edge of the fixedbase plate 19 a. The fixedperipheral wall 19 b is fixed to thefront housing 13. The fixedspiral wall 19 c extends spirally in the axial direction toward theeccentric pin 29 b on the inside of the fixedbase plate 19 a. - A
movable scroll 49 is stored between the fixedscroll 19 and the second fixedblock 17. Themovable scroll 49 has amovable base plate 49 a, aboss portion 49 b, and amovable spiral wall 49 c. Themovable base plate 49 a is orthogonal to therotary shaft 29. Theboss portion 49 b extends cylindrically at a center of themovable base plate 49 a in the axial direction toward theeccentric pin 29 b. The fixedspiral wall 49 c extends spirally and protrudes in the axial direction toward the fixedscroll 19 on the inside of themovable base plate 49 a. The fixedscroll 19 and themovable scroll 49 engage each other whereby anexpansion chamber 51 is defined. Themovable scroll 49 corresponds to an expansion mechanism. - A
bush balancer 53 is provided between thelarge diameter portion 29 a of therotary shaft 29 and themovable scroll 49. Thebush balancer 53 is formed with apin hole 53 a extending in the axial direction. Theeccentric pin 29 b is inserted through thepin hole 53 a. A bearingapparatus 55 is provided in the interior of theboss portion 49 b of themovable scroll 49. Thebush balancer 53 is axially rotatably supported by the bearingapparatus 55. - A plurality of
rotation preventing pins 57 a are fixed to a back surface of the second fixedblock 17. The respectiverotation preventing pins 57 a extend toward themovable base plate 49 a of themovable scroll 49. A plurality ofrotation preventing holes 57 b are formed so as to be depressed on a front surface of themovable base plate 49 a. Distal end portions of therotation preventing pins 57 a are loosely fitted into the respectiverotation preventing holes 57 b. Cylindrical rings 57 c are loosely fitted into the respectiverotation preventing holes 57 b. When therotary shaft 29 rotates, the respectiverotation preventing pins 57 a slide and roll in the inner peripheral surfaces of therings 57 c. Accordingly themovable scroll 49 is restricted from rotation and is only capable of revolving about therotary shaft 29. - The fixed
base plate 19 a of the fixedscroll 19 is formed with anintake port 19 d communicating with theexpansion chamber 51 at a center thereof. The fixedscroll 19 and therear housing 21 define anintake chamber 59 which communicates with theintake port 19 d. Therear housing 21 is formed with asecond inlet port 21 a communicating with theintake chamber 59. The fixedscroll 19 is formed with asecond outlet port 19 e communicating with theexpansion chamber 51 on the outer peripheral side. Theexpansion machine 5 includes the fixedscroll 19, therear housing 21, themovable scroll 49, the second fixedblock 17, thebush balancer 53, thelarge diameter portion 29 a, theeccentric pin 29 b, the respectiverotation preventing pins 57 a, and therespective rings 57 c, or the like. - In this Rankine cycle system, as illustrated in
FIG. 1 , thefirst outlet port 13 h of thepump 1 of thefluid machine 11 is connected to theboiler 3 by thepipe 9 a and theboiler 3 is connected to thesecond inlet port 21 a of theexpansion machine 5 by thepipe 9 b. Thesecond outlet port 19 e of theexpansion mechanism 5 is connected to thecondenser 7 by thepipe 9 c, and thecondenser 7 is connected to thefirst inlet port 13 g of thepump 1 by thepipe 9 d. - In this Rankine cycle system, by the rotation of the
pulley 33 of thefluid machine 11 illustrated inFIG. 2 by the engine, therotary shaft 29 is rotated. If themain gear 41 is not subjected to seizure or the like, and thepump torque limiter 43 transmits the power from therotary shaft 29 to themain gear 41, thepump 1 is driven. Thepump 1 sucks refrigerant from thefirst inlet port 13 g and discharges the refrigerant from thefirst outlet port 13 h. Accordingly, the refrigerant is supplied from thepump 1 to theboiler 3. In theboiler 3, the refrigerant is heated by heat of compressed air supplied to the engine. In theboiler 3, for example, 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 theexpansion machine 5, and the refrigerant after the expansion flows out from thesecond outlet port 19 e. Accordingly, therotary shaft 29 is rotated. The rotation of therotary 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 theexpansion machine 5 is radiated by thecondenser 7. In this manner, in this Rankine cycle system, waste heat may be used effectively while cooling the compressed air. - When the
pump 1 is locked by seizure or the like, the torque of therotary shaft 29 with respect to thepump 1 exceeds a predetermined value, and thepump torque limiter 43 blocks power transmission between therotary shaft 29 and themain gear 41. Therefore, even when thepump 1 is stopped, therotary shaft 29 allows continuation of the rotation. Therefore, the power is transmitted to theeccentric pin 29 b, and theexpansion machine 5 is driven by the engine continuously. Therefore, theexpansion machine 5 may be used as a blower to continue circulation of the refrigerant. - Therefore, in this Rankine cycle system, even when the
pump 1 is locked, the compressed air may be cooled preferably by continuing the circulation of the refrigerant by theexpansion machine 5. - The Rankine cycle system of Embodiment 2 employs a
fluid machine 12 illustrated inFIG. 3 . Thefluid machine 12 includes afirst shaft 30 axially rotatably supported in themain shaft hole 13 b of thefront housing 13. Thefirst shaft 30 corresponds to the first shaft portion. Asensing shaft 61 formed into a cylindrical shape and concentric with thefirst shaft 30 is provided between thepump torque limiter 43 and themain gear 41. - The two bearing
apparatuses 47 provided in the second fixedblock 17 axially rotatably support a bottomed cylindricalsecond shaft 32. Thesecond shaft 32 corresponds to the second shaft portion. Thefirst shaft 30 and thesecond shaft 32 are concentric. Thesecond shaft 32 is formed with aneccentric pin 32 b deviated with respect to thefirst shaft 30 and thesecond shaft 32. - A one-way clutch 65 and a
bearing apparatus 67 are provided between thefirst shaft 30 and thesecond shaft 32 in the radial direction. A rear end of thesensing shaft 61 is bent radially outward in a flange shape. Adisc spring 63 is provided between the rear end of thesensing shaft 61 and the one-way clutch 65 in the axial direction. Thedisc spring 63 corresponds to a sensing spring. - As illustrated in
FIGS. 4 to 7 , the one-way clutch 65 includes anouter race 71, aninner race 72, a plurality of column-shapedrollers 73 and aholder 74. Theouter race 71 rotates integrally with thesecond shaft 32. Theinner race 72 rotates integrally with thefirst shaft 30. Therespective rollers 73 are provided between theouter race 71 and theinner race 72. Theholder 74 holds therespective rollers 73. - The inner peripheral surface of the
outer race 71 forms a cylindrical inner peripheral rollingsurface 71 a. The outer peripheral surface of theinner race 72 is formed into a polygonal shape being concentric with thefirst shaft 30. The outer peripheral surface of theinner race 72 has a plurality ofplane portions 720 and a plurality ofcorner portions corner portions 721 are on the front side in a direction of rotation R of thefirst shaft 30. Thecorner portions 722 are on the rear side in a direction of rotation R of thefirst Shaft 30. All theentire plane portions 720 and thecorner portions surface 72 a. Therespective rollers 73 are stored between the inner peripheral rollingsurface 71 a and the outer peripheral rolling surfaces 72 a. The same number ofstators 75 as therollers 73 are fixed to theinner race 72. A forward urgingspring 77 is provided between each of thestators 75 and each of therollers 73. The respective forward urging springs 77 have a forward urging force which causes therespective rollers 73 to be positioned on the front side in the direction of rotation R of thefirst shaft 30.Boss portions holder 74 between the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a. The bothboss portions respective rollers 73. Accordingly, the bothboss portions respective rollers 73. Thedisc spring 63 illustrated inFIG. 3 is provided between the sensingshaft 61 and theholder 74. Other configurations are the same asEmbodiment 1. - In this Rankine cycle system, by the rotation of the
pulley 33 of thefluid machine 12 illustrated inFIG. 3 by the engine, thefirst shaft 30 is rotated. If thepump 1 is not subjected to seizure or the like, and thepump torque limiter 43 transmits the power from thefirst shaft 30 to thesensing shaft 61 and themain gear 41, thepump 1 is driven. Thepump 1 sucks refrigerant from thefirst inlet port 13 g and discharges the refrigerant from thefirst outlet port 13 h. Therefore, the refrigerant is supplied from thepump 1 to theboiler 3. In theboiler 3, the refrigerant is heated by compressed air. - The refrigerant expandable by being heated flows from the
second inlet port 21 a of theexpansion machine 5, and the refrigerant after the expansion flows out from thesecond outlet port 19 e. Therefore, thesecond shaft 32 is rotated in the same direction as thefirst shaft 30. - Here, if the rotational speed of the
second shaft 32 is smaller than the rotational speed of thefirst shaft 30, as illustrated inFIG. 6 , therespective rollers 73 held in theholder 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 thefirst shaft 30 and theholder 74. Accordingly, in the one-way clutch 65, therespective rollers 73 are positioned respectively on therespective plane portions 720 of theinner race 72, engagement between the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a by therespective rollers 73 is released. Therefore, the one-way clutch 65 blocks power transmission between thesecond shaft 32 and thefirst shaft 30. - As illustrated in
FIG. 5 , when the rotational speed of thesecond shaft 32 reaches to exceed the of thefirst shaft 30, therespective 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, therespective rollers 73 are positioned respectively on the sides of therespective corner portions 721 of theinner race 72, and are engaged between theouter race 71 and theinner race 72. Therefore, the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a engage by therespective rollers 73. Accordingly, the one-way clutch 65 allows power transmission between thesecond shaft 32 and thefirst shaft 30. Then, thesecond shaft 32 and thefirst shaft 30 rotate integrally by being directly connected. The rotation of thefirst 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 theexpansion machine 5 is discharged by thecondenser 7. In this manner, in this Rankine cycle system, waste heat may be used effectively while cooling the compressed air. - When the
pump 1 is locked by seizure or the like, thepump torque limiter 43 does not transmit the power from thefirst shaft 30 to thesensing shaft 61 and themain gear 41. Therefore, thesensing shaft 61 stops rotation and hence, thefirst shaft 30 continues to rotate even when thepump 1 is stopped. In this case, thesensing shaft 61 pulls theholder 74 of the one-way clutch 65 toward the rear side in the direction of rotation R by thedisc spring 63. Therefore, in the one-way clutch 65, as illustrated inFIG. 7 , even when the rotational speed of thesecond shaft 32 is smaller than the rotational speed of thefirst shaft 30, therespective rollers 73 are positioned respectively at therespective corner portions 722 on the rear side of theinner race 72 and are engaged between theouter race 71 and theinner race 72. Therefore, the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a engage by therespective rollers 73. Accordingly, the one-way clutch 65 allows power transmission between thesecond shaft 32 and thefirst shaft 30. Then, thesecond shaft 32 and thefirst shaft 30 rotate integrally by being directly connected. Therefore, power is transmitted from the engine to thesecond shaft 32 by thefirst shaft 30, so that theexpansion machine 5 may be used as a blower to continue circulation of the working fluid. - Therefore, the Rankine cycle system may achieve the same effects and advantages as
Embodiment 1. In addition, in this Rankine cycle system, when the high-low pressure difference is small, there arises a merit that a drag loss of theexpansion machine 5 does not occur. In this Rankine cycle system, the configuration is simple and costs are lower in comparison with the configuration in which theexpansion machine 5 is driven by an external signal by sensing the lock of thepump 1. - The Rankine cycle system of
Embodiment 3 employs a one-way clutch 66 illustrated inFIGS. 8 to 11 . The one-way clutch 66 includes aholder 78 and a plurality of rearward urging springs 79. - The same number of pairs of
stators rollers 73 are fixed to theinner race 72. Therespective rollers 73 are stored between the respective pairs ofstators forward urging spring 77 is provided between each of thestators 75 and each of therollers 73. The rearward urgingspring 79 is provided between each of therollers 73 and each of thestators 76. The respective rearward urgingsprings 79 have a rearward urging force which causes therespective rollers 73 to be positioned on the rear side in the direction of rotation R of thefirst shaft 30. The rearward urging force is set to be weaker than the forward urging force of the forward urging springs 77. - The same number of
partitioning walls 78 a as therollers 73 extending in the axial direction are formed in theholder 78. Therollers 73 are stored between the both partitioningwalls 78 a. Other configurations are the same as Embodiment 2. - In this one-way clutch 66, if the rotational speed of the
second shaft 32 is smaller than the rotational speed of thefirst shaft 30, therespective partitioning walls 78 a move relatively in the direction opposite from the direction of rotation R as illustrated inFIG. 10 (move counterclockwise in the drawing) due to the difference in rotating speed between thefirst shaft 30 and theholder 78, and compress the respective forward urging springs 77 respectively. Therespective rollers 73 move in the opposite direction from the direction of rotation R and are positioned on therespective plane portions 720 of theinner race 72 respectively. Therefore, engagement between the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a by therespective rollers 73 is released. Accordingly, the one-way clutch 66 blocks power transmission between thesecond shaft 32 and thefirst shaft 30. - On the other hand, as illustrated in
FIG. 9 , when the rotational speed of thesecond shaft 32 reaches to exceed the rotational speed of thefirst shaft 30, therespective partitioning walls 78 a move relatively in the same direction as the direction of rotation R (move clockwise in the drawing) in the one-way clutch 66, and press therespective rollers 73. In this case, the rearward urging force of the rearward urging springs 79 is set to be weaker than the forward urging force of the forward urging springs 77 as described above, the respective rearward urging springs 79 are compressed by therespective rollers 73. Accordingly, therespective rollers 73 move in the same direction as the direction of rotation R and are positioned at therespective corner portions 721 on the front side of theinner race 72, thereby becoming engaged between theouter race 71 and theinner race 72. Therefore, the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a engage by therespective rollers 73. The one-way clutch 66 allows power transmission between thesecond shaft 32 and thefirst shaft 30. - When the
pump 1 is locked by seizure or the like, thepump torque limiter 43 does not transmit the power from thefirst shaft 30 to thesensing shaft 61 and themain gear 41. Therefore, thesensing shaft 61 stops rotation and hence thefirst shaft 30 continues to rotate even when thepump 1 is stopped. In this case, thesensing shaft 61 pulls theholder 78 of the one-way clutch 66 toward the rear side in the direction of rotation R by thedisc spring 63. Therefore, in the one-way clutch 66, as illustrated inFIG. 11 , even when the rotational speed of thesecond shaft 32 is smaller than the rotational speed of thefirst shaft 30, therespective rollers 73 are positioned respectively at therespective corner portions 722 on the rear side of theinner race 72 and are engaged between theouter race 71 and theinner race 72. Therefore, the inner peripheral rollingsurface 71 a and the outer peripheral rollingsurface 72 a engage by therespective rollers 73. The one-way clutch 66 allows power transmission between thesecond shaft 32 and thefirst shaft 30. Then, thesecond shaft 32 and thefirst shaft 30 rotate integrally by being directly connected. Therefore, power is transmitted from the engine to thesecond shaft 32 by thefirst shaft 30, so that theexpansion machine 5 may be used as a blower to continue circulation of the working fluid. - In this Rankine cycle system, since the
respective rollers 73 are stabilized between theinner race 72 and theouter race 71 by the forward urging springs 77, thepartitioning walls 78 a, and the rearward urging springs 79 respectively in the one-way clutch 66, whereby the preferable operability is exercised. Other effects and advantages are the same as Embodiment 2. - The Rankine cycle system of Embodiment 4, as illustrated in
FIG. 12 , an expansionmachine torque limiter 69 is provided between thesecond shaft 32 and thefirst shaft 30. In contrast, thesensing shaft 61 and thedisc spring 63 are not provided. Other configurations are the same as Embodiment 2. - In this Rankine cycle system, when the
pump 1 is locked by seizure or the like, thefirst shaft 30 continues the rotation by thepump torque limiter 43. In this case, thesecond shaft 32 continues to rotate even when thepump 1 is stopped as long as the torque of thesecond shaft 32 with respect to thefirst shaft 30 does not exceed a predetermined value. Therefore, theexpansion machine 5 may be used as a blower to continue circulation of the refrigerant. When the torque of thesecond shaft 32 with respect to thefirst shaft 30 exceeds the predetermined value, the expansionmachine torque limiter 69 blocks the power transmission between thesecond shaft 32 and thefirst shaft 30. - In this Rankine cycle system, even when the
expansion machine 5 is locked by seizure or the like, when thepump 1 is operated normally, thefirst shaft 30 continues to rotate by the expansionmachine torque limiter 69, and thesecond shaft 32 stops rotation. In this case, since thepump 1 moves normally, circulation of the refrigerant can be continued by thepump 1. Other effects and advantages are the same as Embodiment 2. - Although the invention has been described with reference to
Embodiments 1 to 4, the invention is not limited toEmbodiments 1 to 4 described above, and may be applied by changing as needed within the range not departing the scope thereof. - For example, within the
housing 23 of thefluid machines pump 1 and theexpansion machine 5. - The invention is applicable to the Rankine cycle system for a vehicle, a waste heat utilizing apparatus or the like.
-
- 1 . . . pump
- 3 . . . boiler
- 5 . . . expansion machine
- 7 . . . condenser
- 9 a-9 d . . . pipe
- 13 . . . front housing
- 13 g . . . first inlet port
- 13 h . . . first outlet port
- 15 . . . first fixed block
- 17 . . . second fixed block
- 19 . . . fixed scroll
- 19 e . . . second outlet port
- 21 . . . rear housing
- 21 a . . . second inlet port
- 23 . . . housing
- 29 . . . rotary shaft (first shaft portion, second shaft portion)
- 30 . . . first shaft (first shaft portion)
- 32 . . . second shaft (second shaft portion)
- 41 . . . main gear (pump mechanism)
- 43 . . . pump torque limiter
- 49 . . . movable scroll (expansion mechanism)
- 61 . . . sensing shaft
- 63 . . . disc spring (sensing spring)
- 65, 66 . . . one-way clutch
- 69 . . . expansion machine torque limiter
- 71 . . . outer race
- 71 a . . . inner peripheral rolling surface
- 72 . . . inner race
- 72 a . . . outer peripheral rolling surface
- 73 . . . roller
- 74, 78 . . . holder
- 75 . . . stator
- 77 . . . forward urging spring
- 79 . . . rearward urging spring
Claims (5)
1. A Rankine cycle system comprising: a pump; a boiler; an expansion machine; a condenser; and pipes;
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.
2. The Rankine cycle system according to claim 1 wherein
the first shaft portion and the second shaft portion are concentric,
a one-way clutch is provided between the first shaft portion and the second shaft portion so as to block power transmission between the second shaft portion and the first shaft portion if the rotational speed of the second shaft portion is smaller than the rotational speed of the first shaft portion, and allow the power transmission between the second shaft portion and the first shaft portion if the rotational speed of the second shaft portion reaches to exceed the rotational speed of the first shaft portion,
the pump is provided with a sensing shaft configured to rotate when the pump mechanism is in operation, and
the one-way clutch allows the power transmission between the second shaft portion and the first shaft portion even when the rotational speed of the second shaft portion is smaller than the rotational speed of the first shaft portion when the rotation of the sensing shaft is stopped.
3. The Rankine cycle system according to claim 2 , wherein
the sensing shaft is a cylindrical shape concentric with the first shaft portion,
the one way clutch includes:
an outer race configured to rotate integrally with the second shaft portion and formed with a cylindrical inner peripheral rolling surface;
an inner race configured to rotate integrally with the first shaft portion and formed with a polygonal outer peripheral rolling surface;
rollers configured to be stored between the inner peripheral rolling surface and the outer peripheral rolling surface;
stators provided as many as the rollers and fixed to the inner race;
forward urging springs provided between the stators and the rollers respectively, and having a forward urging force which causes the respective rollers to be positioned on the front side in the direction of rotation of the first shaft portion;
a holder configured to hold the respective rollers between the inner peripheral rolling surface and the outer peripheral rolling surface; and
a sensing spring provided between the sensing shaft and the holder.
4. The Rankine cycle system according to claim 3 , wherein
the one-way clutch includes rearward urging springs provided between the respective stators and the respective rollers and having a rearward urging force which causes the respective rollers to be positioned on the rear side of the first shaft portion in the direction of rotation, and
the rearward urging force is weaker than the forward urging force.
5. The Rankine cycle system according to claim 1 , wherein
the first shaft portion and the second shaft portion are concentric, and
an expansion machine torque limiter is provided between the second shaft portion and the first shaft portion.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012169091A JP2014029120A (en) | 2012-07-31 | 2012-07-31 | Rankine cycle |
JP2012-169091 | 2012-07-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140033710A1 true US20140033710A1 (en) | 2014-02-06 |
Family
ID=48915857
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/948,461 Abandoned US20140033710A1 (en) | 2012-07-31 | 2013-07-23 | Rankine cycle system |
Country Status (4)
Country | Link |
---|---|
US (1) | US20140033710A1 (en) |
EP (1) | EP2703608A2 (en) |
JP (1) | JP2014029120A (en) |
CN (1) | CN103573310A (en) |
Cited By (1)
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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5145042A (en) * | 1989-05-26 | 1992-09-08 | Roger Macpherson | Roller clutch |
JPH05126029A (en) * | 1991-10-31 | 1993-05-21 | Toyota Autom Loom Works Ltd | Variable capacity piston pump |
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 (en) * | 2006-12-27 | 2008-07-17 | Jtekt Corp | One-way clutch |
JP5084342B2 (en) * | 2007-04-27 | 2012-11-28 | サンデン株式会社 | Fluid machine, Rankine circuit using the fluid machine, and vehicle waste heat utilization system |
JP2010249130A (en) * | 2009-03-27 | 2010-11-04 | Sanden Corp | Fluid machine |
-
2012
- 2012-07-31 JP JP2012169091A patent/JP2014029120A/en active Pending
-
2013
- 2013-07-23 US US13/948,461 patent/US20140033710A1/en not_active Abandoned
- 2013-07-29 EP EP13178388.8A patent/EP2703608A2/en not_active Withdrawn
- 2013-07-31 CN CN201310328564.3A patent/CN103573310A/en active Pending
Cited By (2)
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 |
Also Published As
Publication number | Publication date |
---|---|
JP2014029120A (en) | 2014-02-13 |
CN103573310A (en) | 2014-02-12 |
EP2703608A2 (en) | 2014-03-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1582693B1 (en) | Scroll fluid machine | |
KR101783131B1 (en) | Compressor | |
WO2010109875A1 (en) | Fluid machine | |
US9481234B2 (en) | Vehicle driving system, and method of assembling vehicle driving system | |
US6994531B2 (en) | High-speed fluidic device | |
US4183425A (en) | Clutch-brake with speed differential coolant pump | |
US20130012349A1 (en) | Gear train unit and arrangement for a stamping press | |
JP2009156088A (en) | Vane type compressor unit | |
US10260604B2 (en) | Speed increaser | |
WO2018025878A1 (en) | Double rotating scroll-type compressor and method for designing same | |
US20140033710A1 (en) | Rankine cycle system | |
JP5482706B2 (en) | Compressor with transmission | |
US10683926B2 (en) | Oil pump driving device | |
JP5106334B2 (en) | Fluid machinery | |
US11204033B2 (en) | Oil pump driving device | |
JP7061976B2 (en) | Friction engagement device | |
JP4537846B2 (en) | Double wrap scroll fluid machine | |
JP2012219820A (en) | In-wheel motor drive device | |
US11111850B2 (en) | Rotational drive unit for a fan | |
JP4578252B2 (en) | Wet clutch brake device for mechanical press | |
JP2019157729A (en) | Both rotating scroll compressor | |
JP2000257558A (en) | Compressor with reverse rotation prevention mechanism | |
EP2551449A1 (en) | Fluid machine | |
JP2004019808A (en) | Friction roller type transmission | |
JP2004156743A (en) | Driving device and high-speed fluid device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MORI, HIDEFUMI;IGUCHI, MASAO;ENOKIJIMA, FUMINOBU;AND OTHERS;SIGNING DATES FROM 20130716 TO 20130718;REEL/FRAME:030856/0969 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |