JP2009185772A - Fluid machine and rankine cycle using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine and a Rankine cycle using the same, capable of optionally adjusting capacity of a pump mechanism regardless of the rotating speed of an expansion mechanism. <P>SOLUTION: This fluid machine has integrally the expansion mechanism 30 rotating by the expansion of a working fluid, a generator 40 driven by torque of the expansion mechanism 30, and a pump mechanism 50 driven by the torque of the expansion mechanism 30. Since the pump mechanism 50 is constituted so that capacity can be varied to the rotating speed of the expansion mechanism 30, the capacity of the pump mechanism 50 can be optionally adjusted regardless of the rotating speed of the expansion mechanism 30, and a flow rate of fluid forcibly fed by the pump mechanism 50 can be always properly set. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a fluid machine used in, for example, a waste heat utilization device that generates power using waste heat of a vehicle engine, and a Rankine cycle using the fluid machine.

  Conventionally, Rankine cycles used in vehicles and the like condense an evaporator that evaporates the working fluid by the waste heat of the engine, an expander that drives the generator by expansion of the evaporated working fluid, and the working fluid that has flowed out of the expander. And a pump that pumps the working fluid from the condenser to the evaporator. Further, as a fluid machine used in such a Rankine cycle, an apparatus in which an expander, a generator, and a pump are integrally provided is known (for example, see Patent Document 1).

The fluid machine includes an expansion mechanism that generates a rotational force by expansion of the working fluid, a generator that is driven by the rotational force of the expansion mechanism, and a pump mechanism that is driven by the rotational force of the expansion mechanism together with the generator. The working fluid is pumped from the condenser to the evaporator by a pump mechanism. In this fluid machine, the pump mechanism is driven by the expansion mechanism, so that there is an advantage that it is not necessary to separately use a pump driving motor.
JP 2005-30386 A

  By the way, in the Rankine cycle, the amount of heat absorbed and the amount of heat released vary depending on the vehicle speed and the outside air temperature, so the flow rate of the working fluid needs to be adjusted accordingly. However, in the fluid machine, when the pump mechanism is driven by the expansion mechanism, since the expansion mechanism and the pump mechanism are directly connected to each other, the capacity of the pump mechanism cannot be changed with respect to the rotation speed of the expansion mechanism. There was a problem that the pump flow rate in the Rankine cycle could not be adjusted properly.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a fluid machine capable of arbitrarily adjusting the capacity of the pump mechanism regardless of the rotation speed of the expansion mechanism, and a Rankine using the same. To provide a cycle.

  In order to achieve the above object, the present invention provides an expansion mechanism that generates a rotational force by expansion of a working fluid, a generator that is driven by the rotational force of the expansion mechanism, and a pump mechanism that is driven by the rotational force of the expansion mechanism. In the fluid machine including the above, the pump mechanism has a variable capacity.

  As a result, the expansion mechanism is rotated by the expansion of the working fluid, and the generator and the pump mechanism are driven by the expansion mechanism. At that time, by changing the capacity of the pump mechanism, the capacity of the pump mechanism can be arbitrarily adjusted regardless of the rotation speed of the expansion mechanism.

  In order to achieve the above object, the present invention expands the working fluid evaporated by the evaporator with the expansion mechanism of the fluid machine, and condenses the working fluid flowing out from the expansion mechanism. The working fluid condensed by the condenser and discharged from the condenser is pumped to the evaporator by the pump mechanism of the fluid machine.

  As a result, the working fluid evaporated by the evaporator is expanded by the expansion mechanism, and the working fluid condensed by the condenser is pumped to the evaporator by the pump mechanism. Therefore, the power obtained by the expansion of the working fluid is not only generated. It can also be used to circulate the working fluid.

  According to the fluid machine of the present invention, since the capacity of the pump mechanism can be arbitrarily adjusted regardless of the rotation speed of the expansion mechanism, the flow rate of the fluid pumped by the pump mechanism can always be made appropriate. This is extremely advantageous when used in a vehicle waste heat utilization device that uses waste heat of an engine.

  Further, according to the Rankine cycle of the present invention, the power obtained by the expansion of the working fluid can be used not only for power generation but also for the circulation of the working fluid, which is extremely advantageous for improving the efficiency of the Rankine cycle.

  1 and 2 are schematic configuration diagrams showing an embodiment of a vehicle waste heat utilization apparatus using the Rankine cycle of the present invention, and FIG. 2 is a side sectional view of a fluid machine used in the Rankine cycle of the present invention. This waste heat utilization device is used for an automobile using an engine as a drive source, and generates power using waste heat of the engine.

  The waste heat utilization apparatus of this embodiment includes a cooling water circuit 2 that circulates cooling water of the engine 1, a heat medium circuit 3 that circulates a heat medium heated by the exhaust gas of the engine 1, and waste heat of the engine 1. And a Rankine cycle 4 that generates electricity as a heat source.

  The coolant circuit 2 includes an engine 1, a radiator 5 that cools the coolant, a coolant heater 6 that heats the coolant by exchanging heat with the heat medium of the heat medium circuit 3, and a working fluid of the Rankine cycle 4. Is connected to an evaporator 7 that evaporates by exchanging heat with the cooling water, and the first pump 8 circulates the cooling water. The cooling water circuit 2 is provided with a bypass flow path 9 that connects the inflow side and the outflow side of the radiator 5, and either the flow path on the radiator 5 side or the bypass flow path 9 is flown on the engine 1 side by the thermostat 10. It is designed to communicate with the road. The thermostat 10 is a known device that adjusts the opening of the three-way valve in accordance with the temperature so that the temperature on the outflow side (engine 1 side) becomes a predetermined temperature. The cooling water heater 6 and the evaporator 7 are connected in parallel to the cooling water outflow side of the engine 1, and the first and second electromagnetic valves 11, 11 are provided on the cooling water inflow side of the cooling water heater 6 and the evaporator 7. 12 are provided.

  The heat medium circuit 3 stores a heat medium heater 13 that heats the heat medium by exchanging heat with the exhaust gas in the exhaust gas flow path 1 a of the engine 1, and the heat medium heated by the heat medium heater 13. A heat storage tank 14 having a heat insulating structure, a superheater 15 that superheats the working fluid of the Rankine cycle 4, and a cooling water heater 6 of the cooling water circuit 2 are connected, and the heat medium is circulated by the second pump 16. It is like that. In this case, a heat medium that has a boiling point higher than that of the cooling water and can be stored in the heat storage tank 14 as a liquid is used as the heat medium. The cooling water heater 6 and the superheater 15 are connected in parallel to the cooling water outflow side of the heat storage tank 14, and the third and fourth electromagnetic valves 17 are connected to the heat medium inflow side of the cooling water heater 6 and the superheater 15. , 18 are provided.

  The Rankine cycle 4 is formed by connecting the evaporator 7, the superheater 15, an expansion mechanism 30 of the fluid machine 20 described later, and a condenser 19 that condenses the working fluid flowing out from the expansion mechanism 30. The working fluid is circulated by the pump mechanism 50. In this case, for example, a fluorocarbon refrigerant (R245ca, R245fa, R152a, etc.) is used as the working fluid.

  In addition, the cooling water circuit 2 is provided with a temperature switch 2 a that operates the solenoid valves 11, 12, 17, and 18 in accordance with the temperature of the cooling water flowing out from the radiator 5.

  Next, the fluid machine 20 used for the Rankine cycle 4 will be described. The fluid machine 20 includes an expansion mechanism 30 that is rotated by expansion of a working fluid, a generator 40 that is driven by the rotational force of the expansion mechanism 30, a pump mechanism 50 that is driven by the rotational force of the expansion mechanism 30, and an expansion mechanism. The shaft 60 is configured to transmit the rotational force of 30 to the generator 40 and the pump mechanism 50, and the generator 40 can be driven by the electric power supplied from the outside to drive the pump mechanism 50.

  The expansion mechanism 30 includes a cylindrical first housing 31 closed at one end, a second housing 32 closed at the other end of the first housing 31, and the first housing 31 facing each other in the axial direction. The fixed scroll member 33 and the movable scroll member 34 arranged in this manner are provided, and the shaft 60 is rotated by the eccentric rocking motion of the movable scroll member 34.

  The first housing 31 has a working fluid outlet 31 a on a side surface, and a working fluid inlet 31 b is provided on one end face of the first housing 31. A bearing portion 32a extending in a cylindrical shape in the axial direction is provided on one end side of the second housing 32, and a long hole 32b extending in the radial direction is provided on one end side in the radial direction of the other end surface.

  One end of the fixed scroll member 33 is fixed to the first housing 31, and a spiral body 33 a facing the movable scroll member 34 is provided on the other end surface. A flow hole 33 b that communicates with the inlet 31 b of the first housing 31 is provided on one end surface of the fixed scroll member 33. The movable scroll member 34 has a spiral body 34a opposite to the fixed scroll member 33 on one end surface, and the spiral body 34a of the movable scroll member 34 meshes with the spiral body 33a of the fixed scroll member 33 so as to be able to swing eccentrically. An engagement pin 34b is provided on one end side in the radial direction of the other end surface of the movable scroll member 34 to engage with the long hole 32b of the second housing 32 so as to be movable in the radial direction. The engagement pin 34b and the long hole 32b Thus, the rotation of the movable scroll member 34 is restricted. A boss portion 34c is provided at the center of the other end surface of the movable scroll member 34, and an eccentric bush 35 is rotatably supported in the boss portion 34c via a bearing 35a. A support shaft 35b that is coaxial with the shaft 60 protrudes from one end side of the eccentric bush 35, and a balance weight 36 for correcting the static balance is attached to the support shaft 35b. A rotating body 37 that rotates by an eccentric bush 35 is rotatably supported in the bearing portion 32a of the first housing 32 via a bearing 37a, and a support shaft 35b of the eccentric bush 35 is provided at the radial center of the rotating body 37. Is inserted in a rotatable manner, and an eccentric pin 37b is provided on the rotating body 37 so as to be rotatably engaged with one end of the eccentric bush 35 in the radial direction. The rotating body 37 is connected to one end side of the shaft 60 via a one-way clutch 38 as a one-way transmission mechanism, and transmits only one-way rotational force to the shaft 60.

  The generator 40 includes a cylindrical housing 41 having both ends opened, a stator 42 fixed to the inner peripheral surface of the housing 41, a winding 43 held by the stator 42, and a rotor disposed inside the stator 42. 44, and the rotor 44 is fixed to the shaft 60.

  The pump mechanism 50 includes a cylindrical housing 51 whose one end is closed, a cylinder block 52 having one end connected to the other end of the housing 51, a plurality of pistons 53 provided in the cylinder block 52, and a cylinder block 52. A cylinder head 54 disposed on the other end side, a valve plate 55 provided between the cylinder block 52 and the cylinder head 54, a swash plate 56 slidably engaged with one end side of each piston 53, A variable mechanism 57 for changing the inclination angle of the swash plate 56 is provided, and the swash plate 56 is rotated by a shaft 60.

  A bearing portion 51a extending in the axial direction is provided at one end of the housing 51, and a shaft 60 is rotatably supported by the bearing portion 51a via a bearing 51b.

  The cylinder block 52 has a cylinder 52a, and both ends of each cylinder 52a are opened to the housing 51 side and the valve plate 55 side, respectively. Further, the other end side of the shaft 60 is rotatably supported by the cylinder block 52 via a bearing 52b.

  Each piston 53 is slidably provided in each cylinder 52a, and an engaging portion 53a that engages with the swash plate 56 is provided at one end thereof. The engaging portion 53a has a pair of hemispherical surfaces facing each other, and a hemispherical shoe 53b is slidably provided between the hemispherical surfaces.

  The cylinder head 54 has a discharge chamber 54a and a suction chamber 54b for working fluid, and the discharge chamber 54a and the suction chamber 54b are open to the cylinder block 52 side. The discharge chamber 54a is provided at the center of the cylinder head 54, and the cylinder head 54 is provided with a discharge port (not shown) communicating with the discharge chamber 54a. The suction chamber 54b is provided around the discharge chamber 54a, and the cylinder head 54 is provided with a suction port (not shown) communicating with the suction chamber 54b.

  The valve plate 55 has a plurality of discharge holes 55a and suction holes 55b communicating with each cylinder 52a, and the discharge holes 55a and the suction holes 55b communicate with the discharge chamber 54a and the suction chamber 54b of the cylinder head 54, respectively. A discharge side plate 55c is disposed on one surface side (cylinder head 54 side) of the valve plate 55, and a discharge valve (not shown) for opening and closing each discharge hole 55a is provided on the discharge side plate 55c. Further, a suction side plate 55d is disposed on the other surface side (cylinder block 52 side) of the valve plate 55, and suction valves (not shown) for opening and closing each suction hole 55b are provided on the suction side plate 55d. Yes.

  The swash plate 56 is provided so as to be tiltable with respect to the axial direction of the shaft 60, and an engaging portion 53a of each piston 53 is slidably engaged with a peripheral portion thereof via a shoe 53b. The swash plate 56 is tiltably connected to a rotating plate 56a that rotates integrally with the shaft 60. The swash plate 56 is rotated about the shaft 60 by the rotating plate 56a, and reciprocally moves each piston 53 with a stroke amount corresponding to the inclination angle. It has become. A shaft 60 passes through the central portion of the swash plate 56, and the shaft 60 is provided with a long hole 60a extending in the axial direction. That is, the central portion of the swash plate 56 is engaged with the long hole 60a via the pin 56b, and the pin 56b moves in the long hole 60a of the shaft 60 as the swash plate 56 tilts. .

  The variable mechanism 57 includes a rod 57 a having one end coupled to the pin 56 b of the swash plate 56 and a drive unit 57 b that moves the rod 57 a in the axial direction of the shaft 60. The rod 57 a is slidable in the shaft 60. Is provided. The drive unit 57b is a known mechanism that can move the rod 57a by an arbitrary amount in the axial direction, such as a gear unit provided with a motor, for example, and the inclination of the swash plate 56 based on a signal from an external control unit (not shown). Change the angle.

  In the fluid machine 20 configured as described above, the inflow side of the expansion mechanism 30 is connected to the outflow side of the superheater 15 of the Rankine cycle 4, and the outflow side of the expansion mechanism 30 is connected to the inflow side of the condenser 19. In the fluid machine 20, the suction side of the pump mechanism 50 is connected to the outflow side of the condenser 19, and the discharge side of the pump mechanism 50 is connected to the inflow side of the evaporator 7.

  In the expansion mechanism 30, when the working fluid flows between the scroll members 33 and 34 via the inflow port 31b, the working fluid expands between the spiral bodies 33a and 34a, and the movable scroll member 33 moves to the spiral bodies 33a and 34a. Eccentric rocking motion is performed around the engaging pin 34b so as to increase the volume between them. As a result, the eccentric bush 35 in the boss portion 34 c of the movable scroll member 34 rotates around the support shaft 35 b, and the eccentric pin 37 b that engages with the eccentric bush 35 rotates by the eccentric bush 35. When the eccentric pin 37 b rotates, the rotating body 37 rotates, and the rotational force of the rotating body 37 is transmitted to the shaft 60 via the one-way clutch 38.

  In the generator 40, when the shaft 60 is rotated by the expansion mechanism 30, the rotor 44 is rotated to generate an electromotive force, and the generated electric power is supplied to the outside.

  In the pump mechanism 50, when the shaft 60 rotates, the swash plate 56 rotates while engaging with each piston 53, and each piston 53 reciprocates within the cylinder 52 a with a stroke amount corresponding to the inclination angle of the swash plate 56. As a result, the working fluid is sucked into the cylinder 52a via the suction chamber 54b of the cylinder head 54, and discharged from the cylinder 52a to the outside via the discharge chamber 54a.

  Next, the operation of the waste heat utilization apparatus using the fluid machine 20 will be described. First, when the cooling water of the engine 1 is higher than a predetermined temperature (for example, 80 ° C.), the flow path on the radiator 5 side of the thermostat 10 communicates with the flow path on the engine 1 side, and a cooling water circuit is formed by the temperature switch 2a. The second first solenoid valve 11 is closed and the second solenoid valve 12 is opened. As a result, the cooling water flowing out from the engine 1 flows through the evaporator 7 and the radiator 5 and flows into the engine 1 as indicated by solid line arrows in the figure. At that time, the working fluid of the Rankine cycle 4 is evaporated by the high-temperature cooling water flowing through the evaporator 7. Further, the third electromagnetic valve 17 of the heat medium circuit 3 is closed and the fourth electromagnetic valve 18 is opened by the temperature switch 2a. As a result, the heat medium heated to a temperature higher than the boiling point of the cooling water by the heat medium heater 13 is stored in the heat storage tank 14 kept warm by the heat insulating material, and the heat storage tank 14 is stored. In addition, the heat medium flowing out of the heat storage tank 14 flows through the superheater 15 and flows into the heat medium heater 13. At that time, the working fluid of Rankine cycle 4 is superheated by a high-temperature (for example, 200 ° C.) heat medium flowing through superheater 15.

  In addition, the working fluid of the Rankine cycle 4 flows to the evaporator 7, the superheater 15, the expansion mechanism 30 of the fluid machine 20, the condenser 19, and the pump mechanism 50 of the fluid machine 20, as indicated by a dashed line arrow in the drawing. And flows into the evaporator 7. That is, the working fluid that has been saturated and evaporated in the evaporator 7 is heated by the superheater 15, becomes superheated steam, flows into the expansion mechanism 30, and expands in the expansion mechanism 30, so that the generator 40 is caused to expand by the expansion mechanism 30. Driven. At that time, when the rotation speed of the expansion mechanism 30 is low, such as when the Rankine cycle 4 is started, a voltage is applied to the generator 40 by an external power source, and the generator 40 is driven as a motor at a higher rotation than the expansion mechanism 30. As a result, the pump mechanism 50 is driven by the generator 40 (motor). At this time, the rotational force of the generator 40 (motor) is not transmitted to the expansion mechanism 30 by the one-way clutch 38, and the load of the expansion mechanism 30 is not applied to the generator 40 (motor). And if the rotation speed of the expansion mechanism 30 exceeds the rotation speed of the generator 40 (motor), the application of the voltage to the generator 40 will be stopped and it will switch to the electric power generation by the generator 40.

  The working fluid that has flowed out of the expansion mechanism 30 is condensed by the condenser 19, then pumped by the pump mechanism 50, and flows into the evaporator 7. At that time, in the pump mechanism 50, when the tilt angle of the swash plate 56 is increased by the variable mechanism 57, the stroke amount of each piston 53 increases, and when the tilt angle is decreased, the stroke amount decreases. It is possible to adjust the pump mechanism 50 so as to have an appropriate capacity according to operating conditions such as the vehicle speed and the outside air temperature.

  Next, immediately after the engine 1 is stopped and immediately after the engine 1 is started after a long time has passed, if the cooling water of the engine 1 is below a predetermined temperature (for example, 80 ° C.), the bypass flow path 9 of the thermostat 10 is used. The side communicates with the flow path on the engine 1 side, and the first electromagnetic valve 11 of the cooling water circuit 2 is opened and the second electromagnetic valve 12 is closed by the temperature switch 2a. As a result, the cooling water flowing out from the engine 1 flows through the cooling water heater 6 and the bypass flow path 9 and flows into the engine 1 as indicated by broken line arrows in the figure. Further, the third electromagnetic valve 17 of the heat medium circuit 3 is opened and the fourth electromagnetic valve 18 is closed by the temperature switch 2a. As a result, as indicated by broken line arrows in the figure, the high-temperature (for example, 200 ° C.) heat medium stored in the heat storage tank 14 flows through the cooling water heater 6 and flows into the heat medium heater 13. In that case, the cooling water of the cooling water circuit 2 is heated by the heat medium which distribute | circulates the cooling water heater 6, and the temperature of a cooling water rises rapidly.

  Thus, according to the fluid machine 20 of the present embodiment, the expansion mechanism 30 that rotates by the expansion of the working fluid, the generator 40 that is driven by the rotational force of the expansion mechanism 30, and the rotational force of the expansion mechanism 30 are driven. The pump mechanism 50 is integrally provided and the capacity of the pump mechanism 50 is variable with respect to the rotation speed of the expansion mechanism 30. Therefore, the capacity of the pump mechanism 50 is arbitrarily adjusted regardless of the rotation speed of the expansion mechanism 30. The flow rate of the fluid pumped by the pump mechanism 50 can always be made appropriate.

  In this case, the working fluid evaporated in the evaporator 7 of the Rankine cycle 4 is expanded by the expansion mechanism 30, and the condensed working fluid is pumped to the evaporator 7 side by the pump mechanism 50. The power obtained by the expansion of can be used not only for power generation but also for circulation of the working fluid, which is extremely advantageous for improving the efficiency of the Rankine cycle 4.

  The pump mechanism 50 reciprocates in the cylinder 52a to suck and discharge the fluid, the swash plate 56 slidably engaged with the piston 53, and the swash plate 56 to rotate the swash plate 56. Since the shaft 60 for reciprocating the piston according to the inclination angle of the plate 56 and the variable mechanism 57 for changing the inclination angle of the swash plate 56, the capacity can be increased without changing the rotation speed of the shaft 60 by the expansion mechanism 30. Can be changed. As a result, the structure can be simplified as compared with, for example, a case in which the capacity is changed using a reduction gear, which is extremely advantageous for downsizing and cost reduction.

  Further, the rotational force of the expansion mechanism 30 is transmitted to the generator 40 only in a predetermined rotational direction by the one-way clutch 38, and the generator 40 is configured to be rotatable in the predetermined rotational direction as a motor. When the rotational speed of the expansion mechanism 30 is low, such as during startup, the pump mechanism 50 is driven by applying a voltage to the generator 40 from an external power source and driving the generator 40 as a motor at a higher speed than the expansion mechanism 30. It can be driven by the generator 40 (motor), and the rotational force necessary for the pump mechanism 50 can always be obtained.

  In addition, the expansion mechanism 30 includes the fixed scroll member 33 and the movable scroll member 34 that rotates the shaft 60 by swinging eccentrically due to the expansion of the working fluid flowing between the fixed scroll member 33. And an efficient scroll expander can be constructed, which is extremely advantageous for practical use.

  FIG. 3 is a side sectional view of a fluid machine showing another embodiment of the present invention, and the same reference numerals are given to the same components as those in the above embodiment.

  The fluid machine 20 of the present embodiment is provided with a plurality of diaphragms 58 instead of the pistons 53 of the pump mechanism 50. The diaphragm 58 is made of a flexible film-like member provided on one end side of the cylinder 52a, and is formed of a known material such as resin, metal, or rubber. The diaphragm 58 is provided so that a space between one surface side and the valve plate 55 side is sealed, and an engaging member 59 that engages the swash plate 56 is attached to the other surface. The engaging member 59 is provided with an engaging portion 59a on one end side like the piston 53 of the above-described embodiment, and the engaging portion 59a is slidably engaged with the peripheral portion of the swash plate 56 via the shoe 59b. ing.

  In the pump mechanism 50 of this embodiment, when the shaft 60 rotates, the swash plate 56 rotates while engaging with the engaging member 59 of each diaphragm 58, and each engaging member 59 corresponds to the inclination angle of the swash plate 56. Each diaphragm 58 expands and contracts by reciprocating in the cylinder 52a by the stroke amount. At this time, when the engaging member 59 moves toward the other end side of the cylinder 52 a, the diaphragm 58 extends to increase the volume between the valve plate 55 and the diaphragm 58, and the working fluid is sucked into the suction chamber 54 b of the cylinder head 54. And is sucked into the diaphragm 58 side. Further, when the engaging member 59 moves toward one end of the cylinder 52a, the diaphragm 58 contracts, the volume between the valve plate 55 and the diaphragm 58 is reduced, and the working fluid passes through the discharge chamber 54a from the diaphragm 58 side. And discharged to the outside. At this time, if the inclination angle of the swash plate 56 is increased by the variable mechanism 57, the expansion / contraction amount of each diaphragm 58 increases, and if the inclination angle is decreased, the expansion / contraction amount decreases, so that the operating conditions of the Rankine cycle 4 are the same as in the above embodiment. Accordingly, the capacity of the pump mechanism 50 can be adjusted to be appropriate.

  As described above, according to the present embodiment, the pump mechanism 50 of the fluid machine 20 is expanded and contracted in a predetermined direction to suck and discharge the working fluid, and the swash plate slidably engaged with the diaphragm 58. 56, the shaft 60 that expands and contracts the diaphragm 58 according to the inclination angle of the swash plate 56 by rotating the swash plate 56, and the variable mechanism 57 that changes the inclination angle of the swash plate 56. Similarly, the capacity can be changed without changing the rotational speed of the shaft 60 by the expansion mechanism 30, which is extremely advantageous for downsizing and cost reduction. In this case, since the diaphragm 58 is used for the suction and discharge of the working fluid, the working fluid does not enter the drive mechanism section such as the swash plate 56 and the shaft 60 in the housing 51, and is brought into contact with the working fluid. It is possible to prevent the durability of the drive mechanism portion from being lowered. Moreover, since it is not necessary to mix the lubricating oil for lubricating the drive mechanism part with the working fluid, the heat exchange characteristics of the working fluid are not deteriorated due to the mixing of the lubricating oil, and the efficiency of the Rankine cycle 4 is improved. Very advantageous.

The schematic block diagram which shows one Embodiment of the waste heat utilization apparatus for vehicles using the Rankine cycle of this invention. Side sectional view of a fluid machine used in the Rankine cycle of the present invention Side surface sectional drawing of the fluid machine which shows other embodiment of this invention.

Explanation of symbols

  4 ... Rankine cycle, 7 ... Evaporator, 19 ... Condenser, 20 ... Fluid machinery, 30 ... Expansion mechanism, 33 ... Fixed scroll member, 34 ... Fixed scroll member, 40 ... Generator, 50 ... Pump mechanism, 52a ... Cylinder 53 ... Piston, 56 ... Swash plate, 57 ... Variable mechanism, 58 ... Diaphragm, 60 ... Shaft.

Claims (6)

In a fluid machine including an expansion mechanism that generates a rotational force by expansion of a working fluid, a generator that is driven by the rotational force of the expansion mechanism, and a pump mechanism that is driven by the rotational force of the expansion mechanism.
A fluid machine characterized in that the pump mechanism has a variable capacity. According to the tilt angle of the swash plate by rotating the swash plate, the piston that sucks and discharges the fluid by reciprocating in the cylinder, the swash plate that is slidably engaged with the piston, and the swash plate. The fluid machine according to claim 1, wherein the fluid machine includes a rotating shaft for reciprocating the piston and a variable mechanism for changing an inclination angle of the swash plate. A diaphragm that sucks and discharges fluid by extending and contracting the pump mechanism in a predetermined direction, a swash plate that is slidably engaged with the diaphragm, and a diaphragm that rotates according to the inclination angle of the swash plate The fluid machine according to claim 1, comprising: a rotating shaft that expands and contracts the shaft, and a variable mechanism that changes an inclination angle of the swash plate. The expansion mechanism includes a fixed scroll member and a movable scroll member that generates a rotational force by eccentrically oscillating due to expansion of the working fluid flowing between the fixed scroll member and the fixed scroll member. 2. The fluid machine according to 2 or 3. A unidirectional transmission mechanism that transmits the rotational force of the expansion mechanism to the generator only in a predetermined rotational direction;
The fluid machine according to claim 1, 2, 3 or 4, wherein the generator is configured to rotate in the rotation direction as a motor by electric power supplied from outside. A Rankine cycle comprising the fluid machine according to claim 1, 2, 3, or 5.
The working fluid evaporated by the evaporator is expanded by the expansion mechanism of the fluid machine, the working fluid flowing out from the expansion mechanism is condensed by the condenser, and the working fluid flowing out from the condenser is pumped to the evaporator by the pump mechanism of the fluid machine. A Rankine cycle that is configured to

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