JP2005313878A - Rankine cycle system and control method for the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a Rankine cycle system which is capable of efficient energy recovery by suppressing losses resulting upon changeover between the stoppage and operation of a Rankine cycle, and a control method for the system. <P>SOLUTION: The Rankine cycle system comprises the Rankine cycle 30A which includes a pump 32 that pressure transfers a medium flowing out of a first heat dissipator 11, a heater 30 that heats the medium transferred from the pump 32, and an expander 100 that expands the vapor medium from the heater 30 to convert the pressure energy of the medium into mechanical kinetic energy. The system also has a controller 40 which changes the operational state of the Rankine cycle 30A from stoppage to operation and vice versa. The controller 40 retards a change in an operating state of the expander 100 relative to a change in the same of the pump 32 when changing the operational state of the Rankine cycle 30A. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention is applied to a power recovery technology that uses waste heat of an internal combustion engine such as an automobile, and is particularly suitable for use in a waste heat utilization device of an internal combustion engine having a Rankine cycle in an air-conditioning refrigeration cycle, and It relates to the control method.

  As a conventional waste heat utilization device for an internal combustion engine, for example, one disclosed in Patent Document 1 is known. That is, this waste heat utilization device is a heater that uses a pressurizing pump and cooling water of an internal combustion engine as a heating source so as to be in parallel with an evaporator in a refrigeration cycle for air conditioning (high temperature in Patent Document 1). The pressure pump and the heater are selectively connected to the refrigeration cycle by a three-way valve. In addition, a compressor using an internal combustion engine as a drive source is also used as an expander.

As a result, when the refrigerant flows to the pressurizing pump and heater side by switching the three-way valve, a Rankine cycle that uses the compressor as an expander can be formed, and the thermal energy obtained from the cooling water can be mechanical energy So that it can be recovered. By returning this mechanical energy to the internal combustion engine, the internal combustion engine can be economically operated.
Japanese Patent No. 2540738

  However, in the above prior art, although the control conditions of each device (three-way valve, pressure pump, compressor, etc.) at the time of refrigeration cycle or Rankine cycle operation are described, switching between both the refrigeration cycle and Rankine cycle There is no description of an optimal control method related to the start and stop of Rankine cycle operation.

  That is, the present inventor considered that the refrigeration cycle and the Rankine cycle are operated alternately, such as when the Rankine cycle is operated and energy recovery is measured when the cooling temperature by the refrigeration cycle is sufficiently low. I tried to confirm.

  First, when switching from the refrigeration cycle to the Rankine cycle, in order to start the Rankine cycle, when the pressure pump is operated and the expander is in an operable state, the refrigerant flow (expansion operation) in the expander is changed. Therefore, it takes time to pressurize the refrigerant with the pressurizing pump, and efficient energy recovery cannot be performed. If energy cannot be recovered in a short time, the cooling temperature will rise and the cooling feeling will deteriorate.

  Further, when switching from the Rankine cycle to the refrigeration cycle, when the pressurization pump is stopped and the expander is stopped in order to stop the Rankine cycle, the refrigerant pressurized by the pressurization pump is transferred to the heater. Since the remaining power cannot be recovered as effective power in the expander, the work of refrigerant pressurization in the pressurization pump is discarded, resulting in power loss in the pressurization pump.

  As described above, it was found that various losses occur in the start and stop of Rankine cycle operation, and the energy efficiency aimed by this waste heat utilization device cannot be sufficiently obtained.

  In view of the above problems, an object of the present invention is to provide a Rankine cycle device and a control method thereof that enable efficient energy recovery by suppressing loss when switching between the stopped state and the operating state of the Rankine cycle. There is to do.

  In order to achieve the above object, the present invention employs the following technical means.

  In invention of Claim 1, the pump (32) which pumps the medium which flows out out of a 1st heat radiator (11), the heater (30) which heats the medium sent from the pump (32), a heater ( The Rankine cycle (30A) having an expander (100) that converts the pressure energy of the medium into mechanical kinetic energy by expanding the vapor medium from 30), and the Rankine cycle (30A) in a stopped state and an operating state. In the Rankine cycle device comprising the control device (40) for switching between the two, the control device (40) expands with respect to the change in the operating state of the pump (32) when switching the Rankine cycle (30A) state. It is characterized by delaying the change in the operating state of the machine (100).

  Thereby, at the time of switching to the operation state of the Rankine cycle (30A), the pressurization time of the medium by the pump (32) can be shortened, and at the time of switching to the stop state of the Rankine cycle (30A), the pump The pressurized work of (32) is not wasted, and efficient energy recovery by the Rankine cycle (30A) is generally possible.

  In the invention according to claim 2, the control device (40) starts the operation of the expander (100) after starting the operation of the pump (32) when the Rankine cycle (30A) is switched from the stopped state to the operating state. It is characterized by letting.

  Thereby, when the pump (32) is operated, there is no outflow (expansion) of the refrigerant from the expander (100), the refrigerant is pressurized by the pump (32) in a short time, and the expander ( The mechanical kinetic energy from 100) can be sufficiently extracted.

  Specifically, as in the invention described in claim 3, it is preferable to start the operation of the pump (32) and start the operation of the expander (100) after the first predetermined time (t1) has elapsed.

  Further, as in the invention described in claim 4, after the pressure of the medium pressurized by the pump (32) rises to the first predetermined pressure (P1) or more, the expander (100) is started to operate. May be.

  In the invention according to claim 5, the expander (100) is connected to the rotating electrical machine (200) having both functions of a generator and an electric motor, and the control device (40) is connected to the expander (100). ), The rotating electric machine (200) is operated as an electric motor.

  Thereby, since the expander (100) can be started in advance using the rotating electrical machine (200) as an external force, the expander (100) can be operated smoothly.

  In the invention described in claim 6, when the Rankine cycle (30A) is switched from the operation state to the stop state, the control device (40) stops the operation of the expander (100) after stopping the pump (32). It is characterized by letting.

  Thus, even after the pump (32) is stopped, the superheated steam medium from the heater (30) that remains in the pressurized state is used to expand the expander (100), and the thermal energy of the medium is reduced. It can be regenerated to mechanical kinetic energy without waste.

  Specifically, as in the seventh aspect of the invention, the pump (32) is deactivated and the expander (100) is deactivated after the second predetermined time (t2) has elapsed.

  Further, as in the invention described in claim 8, after the pressure of the medium pressurized by the pump (32) has dropped below the second predetermined pressure (P2), the expander (100) is stopped. Or, as in the ninth aspect of the invention, after the pressure difference between the high pressure side and the low pressure side of the pump (32) has dropped below a predetermined pressure difference (ΔP), the expander (100) is deactivated. Anyway. Furthermore, as in the invention described in claim 10, the generator (200) is connected to the expander (100), and the power generation amount of the generator (200) by the expander (100) is a predetermined power generation amount (W). The expander (100) may be deactivated after being lowered below.

  In addition, as in the invention described in claim 11, it is effective to connect the rotating electrical machine (200) as a generator that regenerates mechanical kinetic energy to electrical energy to the expander (100). Energy can be recovered.

  As in the invention described in claim 12, the Rankine cycle device uses a medium as a refrigerant, a compressor (100) that compresses the refrigerant, and a second radiator (11) that cools the refrigerant from the compressor (100). It is good also as a thing provided with the refrigerating cycle (10A) which has).

  And like invention of Claim 13, when switching a control apparatus (40) from the driving | running state as a refrigerating cycle (10A) to the driving | running state to a Rankine cycle (30A), a Rankine cycle (30A) The state may be switched from the stopped state to the operating state.

  In the invention described in claim 14, the expander (100) is connected to a rotating electric machine (200) having both functions of a generator and an electric motor, and the refrigerant is supplied to the compressor (100) side or the expander ( 100) having a valve mechanism (107) for switching in and flowing in, and when the control device (40) operates the expander (100), after operating the rotating electrical machine (200) as an electric motor, The valve mechanism (107) switches the refrigerant inflow from the compressor (100) side to the expander (100) side.

  Accordingly, when the operation is switched from the refrigeration cycle (10A) to the Rankine cycle (30A) and the Rankine cycle (30A) is started to operate, the refrigerant heated immediately after the switching of the valve mechanism (107) is transferred to the expander (100). Can be converted into power effectively.

  And like invention of Claim 15, when switching a control apparatus (40) from the driving | running state as Rankine cycle (30A) to the driving | running state to a refrigerating cycle (10A), Rankine cycle (30A) The state may be switched from the operating state to the stopped state.

  In the invention described in claim 16, the generator (200) is connected to the expander (100), and the refrigerant is switched to either the compressor (100) side or the expander (100) side. The control device (40) has a valve mechanism (107) for inflow, and when the expansion device (100) is stopped, the control device (40) causes the valve mechanism (107) to inject the refrigerant from the expander (100) side to the compressor (100). After switching to the side, the rotation of the generator (200) is stopped.

  Accordingly, when the operation is switched from the Rankine cycle (30A) to the refrigeration cycle (10A) and the Rankine cycle (30A) is stopped, the refrigerant is not introduced into the expander (100) and the expander (100) rotates. Since the rotation of the generator (200) is stopped after the power is lost, the generator (200) does not act as a brake that counteracts the rotational force of the expander (100), and wasteful power can be consumed. Absent.

  The invention according to claim 17 includes an electric motor (200) for driving the compressor (100), and the control device (40) serves as a drive source of the compressor (100) for the internal combustion engine (20) or the electric motor (200). Of the internal combustion engine (20) after using the driving force of the electric motor (200) when operating the refrigeration cycle (10A) with the expander (100) stopped. The compressor (100) is operated by a driving force.

  Thereby, the torque for starting the compressor (100) can be prevented from being applied to the internal combustion engine (20), so that the internal combustion engine (20) is not shocked and the passenger is uncomfortable. There is nothing.

  The necessity of operation of the compressor (100) by the electric motor (200) may be determined according to the low-pressure side pressure of the compressor (100) as in the invention described in claim 18. Thereby, it can prevent operating an electric motor (200) wastefully.

  Specifically, the compressor (100) may be operated by the electric motor (200) until the low-pressure side pressure becomes equal to or lower than the third predetermined pressure (P3) as in the invention described in claim 19.

  In addition, as in the twentieth aspect, the compressor (100) may be operated by the electric motor (200) for a third predetermined time (t3).

  In the inventions according to the twelfth to twentieth aspects, as in the invention according to the twenty-first aspect, the first radiator (11) and the second radiator (11) include the Rankine cycle (30A) and the refrigeration. It is good to use in common with a cycle (10A), and it can be set as a compact Rankine cycle apparatus.

  In the invention described in claim 22, the expander (100) also serves as the compressor (100) in the refrigeration cycle (10A), and the power of the internal combustion engine (20) is transmitted to the compressor (100). 100) is provided with a power transmission mechanism (300).

  Thereby, while being able to set it as a compact Rankine cycle apparatus, a compressor (100) can be driven with the motive power of an internal combustion engine (20).

  In the invention according to claim 23, the expander (100) also serves as the compressor (100) in the refrigeration cycle (10A), and has an electric motor (200) that drives the compressor (100). It is a feature.

  Thereby, while being able to set it as a compact Rankine cycle apparatus, a compressor (100) can be driven with the motive power of an electric motor (200).

  In the invention described in claim 23, in the invention described in claim 24, the electric motor (200) also drives the pump (32).

  Thereby, since the drive source of the pump (32) can be shared with the drive source of the compressor (100), a drive source dedicated to the pump (32) can be dispensed with.

  The invention according to claim 25 is characterized in that the pump (32) is connected to the expander (100).

  Thereby, since the pump (32) can be operated by the driving force of the expander (100), a driving source dedicated to the pump (32) can be dispensed with.

  In a twenty-sixth aspect of the present invention, the heat source for heating the medium in the heater (30) is waste heat energy of the internal combustion engine (20).

  Thereby, the waste heat of an internal combustion engine (20) can be utilized effectively.

  According to a twenty-seventh aspect of the present invention, an electric motor (200) for driving the compressor (100) is provided, and the internal combustion engine (20) or the electric motor is provided as a drive source for the compressor (100) by the control device (40). You may apply to what selects at least one of (200).

  In the invention of claim 28, the pump (32) for pumping the medium, the heater (30) for heating the medium sent from the pump (32), and the vapor medium from the heater (30) are expanded. In a method for controlling a Rankine cycle having an expander (100) that converts pressure energy of a medium into mechanical kinetic energy, the medium is pumped by a pump (32) to a heater (30) and the medium is expanded by the expander (100). Of the expansion machine (100) with respect to the change of the operation process of expanding the pump (32), the stop process of stopping the expander (100), and the operation process of stopping the pump (32) And a switching step for switching the state of the Rankine cycle between the operation step and the stop step.

  Thereby, it can be set as the control method of the Rankine-cycle apparatus of Claim 1.

  As in the invention described in claim 29, the switching step is to start the operation of the expander (100) after starting the operation of the pump (32) and switch the Rankine cycle from the stop step to the operation step. can do.

  Further, as in the invention described in claim 30, the switching step is to switch the Rankine cycle from the operation step to the stop step by stopping the operation of the expander (100) after stopping the operation of the pump (32). It is also good.

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
In the present embodiment, the Rankine cycle device according to the present invention is applied to an idle stop vehicle, a hybrid vehicle, or the like in which an engine (corresponding to the internal combustion engine in the present invention) 20 is stopped according to traveling conditions. The Rankine cycle device includes a Rankine cycle 30A that recovers energy from waste heat generated by the engine 20 and a control device 40. The Rankine cycle 30A includes a refrigeration cycle 10A. The operation of the Rankine cycle 30A and the refrigeration cycle 10A is controlled by the control device 40, and the waste heat utilization device (hereinafter, waste heat utilization device) 1 of the internal combustion engine is formed as a whole. Hereinafter, the whole structure of the waste heat utilization apparatus 1 is demonstrated using FIG.

  The expander-integrated compressor 10 outputs a mechanical energy by converting a fluid pressure at the time of expansion of the superheated steam refrigerant (medium) into kinetic energy, and a pump mode in which the gas-phase refrigerant (medium) is pressurized and discharged. It is a fluid machine that also has a motor mode. A radiator (corresponding to the first radiator and the second radiator in the present invention) 11 is connected to a discharge side (a high-pressure port 110 described later) of the expander-integrated compressor 10, and is a discharge that cools the refrigerant while radiating heat. It is a refrigerator. The details of the expander-integrated compressor 10 will be described later.

  The gas-liquid separator 12 is a receiver that separates the refrigerant that has flowed out of the radiator 11 into a gas-phase refrigerant and a liquid-phase refrigerant, and the decompressor 13 expands the liquid-phase refrigerant separated by the gas-liquid separator 12 under reduced pressure. In this embodiment, the refrigerant is decompressed in an enthalpy manner, and the degree of superheat of the refrigerant sucked into the expander-integrated compressor 10 when the expander-integrated compressor 10 is operating in the pump mode is predetermined. A temperature-type expansion valve that controls the throttle opening so as to be a value is adopted.

  The evaporator 14 is a heat absorber that evaporates the refrigerant decompressed by the decompressor 13 and exerts an endothermic action. The check valve 14 a is connected to the compressor-integrated compressor 10 from the refrigerant outlet side of the evaporator 14. The refrigerant is allowed to flow only to the refrigerant suction side (low pressure port 111 described later) when operating in the pump mode.

  These expander-integrated compressor 10, radiator 11, gas-liquid separator 12, decompressor 13, evaporator 14 and the like constitute a refrigeration cycle 10A that moves the heat on the low temperature side to the high temperature side.

  The heater 30 is provided in a refrigerant circuit that connects the expander-integrated compressor 10 and the radiator 11 and heat-exchanges the refrigerant flowing through the refrigerant circuit and the engine coolant to heat the refrigerant. The three-way valve 21 switches between the case where the engine cooling water flowing out from the engine 20 is circulated to the heater 30 and the case where it is not circulated. The three-way valve 21 is controlled by a control device 40 described later.

  The first bypass circuit 31 is a refrigerant passage that guides the liquid-phase refrigerant (medium) separated by the gas-liquid separator 12 to the refrigerant inlet side of the radiator 11 in the heater 30, and the first bypass circuit 31 includes In addition, a liquid pump (corresponding to the pump in the present invention) 32 for circulating the liquid-phase refrigerant and a check valve 31a that allows the refrigerant to flow only from the gas-liquid separator 12 side to the heater 30 side are provided. . In this embodiment, the liquid pump 32 employs an electric pump and is controlled by a control device 40 described later.

  The second bypass circuit 33 is a refrigerant passage that connects the refrigerant outlet side (low-pressure port 111 described later) and the refrigerant inlet side of the radiator 11 when the expander-integrated compressor 10 operates in the motor mode. The second bypass circuit 33 is provided with a check valve 33 a that allows the refrigerant to flow only from the expander-integrated compressor 10 side to the refrigerant inlet side of the radiator 11.

  The on-off valve 34 is an electromagnetic valve that is provided between the radiator 11 and the heater 30 and opens and closes the refrigerant passage, and is controlled by a control device 40 described later. Further, on the refrigerant discharge side (the high pressure chamber 104 side described later) when the expander-integrated compressor 10 operates in the pump mode, the operation of the expander-integrated compressor 10 is set to either the pump mode or the motor mode. A valve mechanism 107 for switching is provided. This will be described later together with the expander-integrated compressor 10.

  Then, by using the radiator 11 of the refrigeration cycle 10A in common, the energy from the waste heat generated in the engine 20 by the gas-liquid separator 12, the liquid pump 32, the heater 30, the expander-integrated compressor 10 and the like is used. A Rankine cycle 30A to be collected is configured.

  The water pump 22 circulates engine cooling water, and the radiator 23 is a heat exchanger that cools the engine cooling water by exchanging heat between the engine cooling water and outside air. The water pump 22 is a mechanical pump that operates by obtaining power from the engine 20, but an electric pump driven by an electric motor may be used.

  Further, a water temperature sensor 24 for detecting the temperature of the engine cooling water is provided on the outlet side of the engine 20, and a temperature signal detected (output) by the water temperature sensor 24 is input to a control device 40 described later. .

  The control device 40 receives an A / C request signal determined based on a set temperature set by the occupant, environmental conditions, and the like, a signal from the water temperature sensor 24, and the like, and based on these signals, the three-way valve 21, the liquid pump 32, the on-off valve 34, the expander-integrated compressor 10 (valve mechanism 107, rotating electric machine 200 (detailed later), electromagnetic clutch 300 (detailed later)) are controlled.

  The rotating electric machine 200 is provided with an inverter 26 for adjusting the electric power from the battery 25 and supplying the electric power to the rotating electric machine 200 or charging the battery 25 with electric power generated (regenerated) by the rotating electric machine 200. ing. The electric power of the battery 25 is supplied to various electric loads (headlights, engine accessories, etc.) 27 of the vehicle.

  Next, details of the expander-integrated compressor 10 will be described with reference to FIG. FIG. 2 is a cross-sectional view of the expander-integrated compressor 10. The expander-integrated compressor 10 is connected by a pump motor mechanism 100 that compresses or expands a gas-phase refrigerant and a shaft 108 of the pump motor mechanism 100. The rotary electric machine 200 and the pump motor mechanism 100, that is, an electromagnetic clutch 300 constituting a power transmission mechanism for transmitting the power from the engine 20 to the shaft 108 so as to be able to be intermittently connected.

  The rotating electrical machine 200 includes a stator 210 and a rotor 220 that rotates within the stator 210, and is disposed in the stator housing 230. In the present embodiment, when electric power is supplied from the battery 25 to the stator 210 via the inverter 26, the rotating electrical machine 200 operates as an electric motor that rotates the rotor 220 to drive the pump motor mechanism 100, Further, when a torque for rotating the rotor 220 is input, electric power is generated, and this electric power is operated as a generator that charges the battery 25 via the inverter 26. The operation of the rotating electrical machine 200 is controlled by the control device 40.

  The electromagnetic clutch 300 includes a pulley section 310 that receives power from the engine 20 via a V-belt, an excitation coil 320 that generates a magnetic field, a friction plate 330 that is displaced by an electromagnetic force by a magnetic field induced by the excitation coil 320, and the like. Therefore, when connecting the engine 20 side and the expander-integrated compressor 10 (shaft 108) side, energizing the excitation coil 320, and disconnecting the engine 20 side and the expander-integrated compressor 10 side, The energization to the exciting coil 320 is cut off. The operation of the electromagnetic clutch 300 is controlled by the control device 40.

  The pump motor mechanism 100 has the same structure as a known scroll-type compression mechanism. Specifically, the pump motor mechanism 100 has a fixed scroll (shell) 102 fixed to the stator housing 230 via the middle housing 101, a middle It comprises a turning scroll 103 that turns and displaces in a space between the housing 101 and the fixed scroll 102, a valve mechanism 107 that opens and closes communication passages 105 and 106 that connect the working chamber V and the high-pressure chamber 104, and the like.

  Here, the fixed scroll 102 is configured to have a plate-like substrate portion 102a and a spiral tooth portion 102b protruding from the substrate portion 102a toward the middle housing 101, while the orbiting scroll 103 is formed on the tooth portion 102b. It is configured to have a spiral tooth portion 103b that contacts and meshes, and a base plate portion 103a on which the tooth portion 103b is formed. The volume of the working chamber V formed by the scrolls 102 and 103 is reduced (in the pump mode) and expanded (in the motor mode).

  The shaft 108 serves as a rotation axis of the rotor 220 and is a crankshaft having an eccentric portion 108a that is eccentric with respect to the rotation center axis at the longitudinal end portion thereof. It is connected to be rotatable.

  Further, the rotation prevention mechanism 109 makes the orbiting scroll 103 rotate once around the eccentric portion 108a while the shaft 108 rotates once. For this reason, when the shaft 108 rotates, the orbiting scroll 103 revolves around the rotation center axis of the shaft 108 without rotating, and the working chamber V is displaced from the outer diameter side to the center side of the orbiting scroll 103. The volume changes so as to decrease, and conversely, as the displacement from the center side of the orbiting scroll 103 to the outer diameter side, the volume changes so as to increase.

  The communication passage 105 is a discharge port that discharges the compressed refrigerant by communicating the working chamber V and the high-pressure chamber 104, which have a minimum volume in the pump mode, and the communication passage 106 has an operation that has the minimum volume in the motor mode. This is an inflow port that leads the high-temperature and high-pressure refrigerant introduced into the high-pressure chamber 104 through communication between the chamber V and the high-pressure chamber 104, that is, superheated vapor refrigerant to the working chamber V.

  The high-pressure chamber 104 has a function of a discharge chamber that smoothes the pulsation of the refrigerant discharged from the communication passage 105 (hereinafter referred to as the discharge port 105). The high-pressure chamber 104 includes a heater 30 and A high-pressure port 110 connected to the radiator 11 side is provided.

  The low-pressure port 111 connected to the evaporator 14 and the second bypass circuit 33 side is provided in the stator housing 230, and passes through the stator housing 230 and the middle housing 101 to both the housings 101, 230 and the fixed scroll 102. Communicated with the space between.

  The discharge valve 107 a is a reed valve-like check valve that is disposed on the high-pressure chamber 104 side of the discharge port 105 and prevents the refrigerant discharged from the discharge port 105 from flowing back from the high-pressure chamber 104 to the working chamber V. The stopper 107b is a valve stop plate that restricts the maximum opening of the discharge valve 107a, and the discharge valve 107a and the valve stop plate 107b are fixed to the substrate portion 102a by bolts 107c.

  The spool 107d is a valve body that opens and closes the communication passage 106 (hereinafter referred to as the inflow port 106), and the electromagnetic valve 107e controls the communication state between the low pressure port 111 side and the back pressure chamber 107f, thereby controlling the back pressure chamber 107f. The spring 107g is an elastic means that acts on the spool 107d with an elastic force in a direction to close the inflow port 106, and the throttle 107h has a predetermined passage resistance and the back pressure chamber 107f. This is resistance means for communicating with the high-pressure chamber 104.

  When the electromagnetic valve 107e is opened, the pressure in the back pressure chamber 107f is lower than that in the high pressure chamber 104, and the spool 107d is displaced to the right in FIG. 2 while pushing and contracting the spring 107g, so that the inflow port 106 is opened. Since the pressure loss at the throttle 107h is very large, the amount of refrigerant flowing from the high pressure chamber 104 into the back pressure chamber 107f is negligibly small.

  On the other hand, when the electromagnetic valve 107e is closed, the pressure in the back pressure chamber 107f and the pressure in the high pressure chamber 104 become equal, so the spool 107d is displaced to the left in FIG. 2 by the force of the spring 107g. close up. That is, a pilot type electric on-off valve that opens and closes the inflow port 106 is configured by the spool 107d, the electromagnetic valve 107e, the back pressure chamber 107f, the spring 107g, the throttle 107h, and the like. The electric on-off valve and the discharge valve 107a constitute a valve mechanism 107 for switching the pump motor mechanism 100 to a pump mode or a motor mode. The operation of the valve mechanism 107 (specifically, the electromagnetic valve 107e) is controlled by the control device 40.

  Next, the operation (control by the control device 40) of the waste heat utilization apparatus 1 according to the present embodiment will be described using the main flowchart shown in FIG. 3 and the sub-flowcharts (subroutines) shown in FIGS. In each flow, the case where the pump motor mechanism 100 is operated in the pump mode is expressed as “compressor”, the case where the pump motor mechanism 100 is operated in the motor mode is expressed as “expander”, and the case where the rotating electric machine 200 is used for power generation. A “generator” and a case where it is used as an electric drive source are described as “motor”.

  First, when there is an A / C request from the occupant, the control device 40 executes an air conditioning (cooling) operation in step S100. That is, by applying a rotational force to the shaft 108 of the expander-integrated compressor 10, the orbiting scroll 103 of the pump motor mechanism 100 is rotated to suck and compress the refrigerant (pump mode), thereby operating the refrigeration cycle 10A.

  Specifically, the on / off valve 34 is opened with the liquid pump 32 stopped, and the engine cooling water is not circulated to the heater 30 side by switching the three-way valve 21. Further, the shaft 108 is rotated with the solenoid valve 107e closed and the inflow port 106 closed by the spool 107d.

  At this time, when the rotational force is applied to the shaft 108, the rotational force is mainly applied by the power of the engine 20 by connecting the engine 20 side and the expander-integrated compressor 10 side with the electromagnetic clutch 300 (engine 20 operation). And the electromagnetic clutch 300 separates the engine 20 side and the expander-integrated compressor 10 side and applies a rotational force by the rotating electrical machine 200 (when the engine 20 is stopped).

  Incidentally, in this embodiment, since the shaft 108 is shared with the rotor shaft of the rotor 220, when the shaft 108 is rotated by the power of the engine 20, the rotating electrical machine 200 operates as a generator. It is desirable to store the generated power in the battery 25 or to energize the stator 210 so that the rotating electrical machine 200 does not become a power load when viewed from the engine 20.

  As a result, the expander-integrated compressor 10 sucks the refrigerant from the low pressure port 111 and compresses it in the working chamber V, and then discharges the compressed refrigerant to the discharge port 105, the high pressure, as in the known scroll compressor. Discharge from the high-pressure port 110 through the chamber 104.

  The refrigerant discharged from the high-pressure port 110 is the heater 30 → the open / close valve 34 → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the evaporator 14 → the check valve 14a → the expander-integrated compressor 10. The low-pressure port 111 is circulated in the order (circulates the refrigeration cycle 10A). The conditioned air is absorbed by the refrigerant evaporated in the evaporator 14 and cooled. At this time, since the engine coolant does not circulate through the heater 30, the refrigerant is not heated by the heater 30, and the heater 30 functions as a simple refrigerant passage.

  In step S110, it is determined whether air-conditioning air cooling is necessary. This is determined by whether or not the cooled conditioned air temperature is higher than the set temperature of the occupant in the A / C request signal. If it is determined in step S110 that cooling is necessary, the process proceeds to step S120, and the refrigeration cycle 10A is continuously operated (steady operation).

  On the other hand, if NO in step S110, that is, if it is determined that the conditioned air temperature is sufficiently cooled and lower than the set temperature, the process proceeds to step S130, and cooling of the conditioned air is interrupted. This is performed by disconnecting the electromagnetic clutch 300 or stopping the rotary electric machine 200 and stopping the pump motor mechanism 100.

  In step S140, it is determined whether a condition for operating Rankine cycle 30A is satisfied. This is determined from the detection signal of the water temperature sensor 24 that detects the engine coolant temperature. When the temperature is higher than a predetermined coolant temperature, the waste heat recovery of the engine 20 (recovers the heat energy of the coolant). If the engine cooling water temperature is lower than the predetermined cooling water temperature, it is determined NO in step S130.

  If it is determined in step S140 that the condition is satisfied, a Rankine cycle start operation is executed in step S200. If NO is determined, the process returns to step S110.

  Step S200 is a step that is a first characteristic part in the present invention, and the operation timing of the liquid pump 32 and the pump motor mechanism 100 (motor mode) is finely controlled. The details will be described below using the sub-flowchart shown in FIG.

  First, in step S210, the operation of the refrigeration cycle 10A is switched to the operation of the Rankine cycle 30A. That is, the on-off valve 34 is closed and the engine cooling water is circulated to the heater 30 side by switching the three-way valve 21.

  Next, the liquid pump 32 is started in step S220, and the pressure of the refrigerant sent from the gas-liquid separator 12 to the heater 30 is increased. At this time, since the inflow port 106 of the pump motor mechanism 100 is still closed by the spool 107d, the refrigerant does not flow into the working chamber V from the high pressure chamber 104 side (the refrigerant does not expand). The liquid pump 32 quickly raises the refrigerant.

  In step S230, after a predetermined time (corresponding to the first predetermined time in the present invention) t1, the pump motor mechanism 100 is activated (as an expander) in the motor mode in step S240. The predetermined time t1 is a time required for the refrigerant pump 32 to sufficiently increase the refrigerant pressure to a pressure corresponding to the temperature of the engine coolant in the heater 30. In addition, since the motor mode needs to be activated by external force, the rotating electric machine 200 is operated as an electric motor and the orbiting scroll 103 is activated. And it raises to predetermined rotation speed. Incidentally, the turning direction of the turning scroll 103 is opposite to that in the pump mode.

  Further, in step S250, the solenoid valve 107e is opened, the spool 107d is slid to the right in FIG. 2, and the inflow port 106 is opened, so that the pump motor mechanism 100 is switched so that the motor mode can be operated. This completes the startup operation subroutine (step S210 to step S250) of Rankine cycle 30A corresponding to step S200, and proceeds to step S300 of the main flow.

  In step S300, steady operation control of Rankine cycle 30A is performed. Here, the high-pressure superheated vapor refrigerant heated by the heater 30 is introduced into the high-pressure chamber 104 into the pump motor mechanism 100 to be expanded, thereby turning the orbiting scroll 103 and rotating the shaft 108 to obtain a mechanical output. Get. Then, the rotor 220 is rotated by the obtained mechanical output to generate electric power by the rotating electric machine 200, and the generated electric power is stored in the battery 25.

  Specifically, the high-pressure superheated vapor refrigerant heated by the heater 30 is introduced into the working chamber V via the inflow port 106 and expanded in the high-pressure chamber 104. As a result, the orbiting scroll 103 that has started turning by the rotary electric machine 200 in step S240 is turned by the expansion of the superheated steam. At this time, the operation of the rotating electric machine 200 as an electric motor is stopped. Then, the refrigerant whose pressure has been reduced after finishing the expansion flows out from the low pressure port 111, and the rotational energy given to the orbiting scroll 103 is transmitted to the rotor 220 of the rotating electrical machine 200.

  And the refrigerant | coolant which flows out out of the low voltage | pressure port 111 is 2nd bypass circuit 33-> check valve 33a-> radiator 11-> gas-liquid separator 12-> 1st bypass circuit 31-> check valve 31a-> liquid pump 32-> heater 30 → The expansion unit-integrated compressor 10 (high pressure port 110) is circulated in this order (circulating through the Rankine cycle 30A).

  During the operation of the Rankine cycle 30 </ b> A, the rotational speed of the rotating electrical machine 200 is adjusted according to the engine coolant temperature so that the maximum generated power can be obtained by the rotating electrical machine 200. That is, when the pressure of the refrigerant flowing through the heater 30 is too high with respect to the engine coolant temperature, the rotational speed of the rotating electrical machine 200 is increased to accelerate expansion and decrease the pressure. On the other hand, when the pressure of the refrigerant is too low, the number of rotations is decreased to increase the pressure by decreasing the expansion speed. In this way, the operation balance of the Rankine cycle 30A is maintained, and high power generation is obtained.

  After performing the steady operation of the Rankine cycle 30A, it is determined in step S310 whether air-conditioning air cooling is necessary as in step S110. This is to confirm whether the conditioned air is higher than the set temperature because the refrigeration cycle 10A is stopped while the Rankine cycle 30A is being operated.

  If it is determined NO in step S310, step S300 is repeated. If it is determined that it is necessary, the Rankine cycle 30A is interrupted in step S320. Here, the engine cooling water is prevented from flowing through the heater 30 by switching the three-way valve 21.

  In step S400, the return operation of the refrigeration cycle 10A is executed. This step S400 is a step that is a second characteristic part in the present invention, and details a stop timing of the liquid pump 32 and the pump motor mechanism 100 (motor mode) and a starting method of the pump motor mechanism 100 (pump mode). It is supposed to be controlled. The details will be described below with reference to the sub-flow charts shown in FIGS.

  First, in step S405, the liquid pump 32 is stopped, and in step S410, power generation regeneration by the rotating electrical machine 200 is continued. Then, it is determined whether or not a predetermined time (corresponding to the second predetermined time in the present invention) t2 has elapsed since the liquid pump 32 was stopped in step S415A. The predetermined time t2 is a time required until the pressure of the superheated steam refrigerant from the heater 30 decreases as the liquid pump 32 stops, and expansion in the pump motor mechanism 100 cannot be obtained.

  If it is determined NO in step S415A, step S410 is repeated. If it is determined that the time has elapsed, the pump motor mechanism 100 is stopped in step S420 so that the pump mode can be operated. Specifically, the electromagnetic valve 107e is closed, and the inflow port 106 is closed by the spool 107d. In step S425, the rotating electrical machine 200 is stopped (power generation is stopped). Furthermore, switching from Rankine cycle 30A to refrigeration cycle 10A is performed by opening on-off valve 34 in step S430.

  Next, when operating the refrigeration cycle 10A (air-conditioning mode start), it is determined in step S435 whether or not the operation of the Rankine cycle 30A has been executed immediately before, and if it is determined that it has been executed, the pump motor mechanism 100 is determined in step S440. It is determined whether or not the low pressure side pressure is equal to or higher than a predetermined pressure (corresponding to the third predetermined pressure in the present invention) P3, and if it is determined to be equal to or higher than the predetermined pressure P3, the process proceeds to step S445. The predetermined pressure P3 is a pressure that does not require excessive starting torque as the low-pressure side pressure when the pump motor mechanism 100 is started in the pump mode.

  In step S445, the rotary electric machine 200 is operated as an electric motor, and the pump motor mechanism 100 is activated in the pump mode. When the low-pressure side pressure drops below the predetermined pressure P3, the drive of the pump motor mechanism 100 is switched from the rotating electrical machine 200 to the engine 20 in step S450. This is done by stopping the rotating electrical machine 200 and connecting the electromagnetic clutch 300.

  If it is determined NO in step S435, the determination of the low-pressure side pressure is unnecessary, and the process proceeds to step S445. If NO is determined in step S440, it is determined that the low-pressure side pressure is sufficiently reduced, and the rotation is performed. The pump motor mechanism 100 is not required to be activated by the electric machine 200, and is directly driven by the engine 20 in step S450. And it transfers to the steady operation of refrigeration cycle 10A of step S120 demonstrated initially.

  From the above configuration description and operation description, the following operational effects are obtained in the present embodiment.

  First, in order to switch from the operation of the refrigeration cycle 10A to the operation of the Rankine cycle 30A, when the Rankine cycle 30A is switched to the operating state, the pump motor mechanism 100 is operated after a predetermined time t1 has elapsed after the liquid pump 32 is operated. Since the operation is performed in the mode (steps S220 to S240), there is no outflow (expansion) of the refrigerant from the pump motor mechanism 100 when the liquid pump 32 is operated, and the liquid pump 32 pressurizes the refrigerant in a short time. The mechanical energy from the pump motor mechanism 100 that is formed and subsequently operated can be sufficiently extracted.

  When the pump motor mechanism 100 is operated in the motor mode, the rotary electric machine 200 is activated in advance as an external force (step S240), so that the pump motor mechanism 100 can be operated smoothly.

  At this time, after the rotary electric machine 200 is operated as an electric motor, the inflow port 106 is opened by the spool 107d and the pump mode is switched to the motor mode (step S240 to step S250), so that the heated refrigerant is effectively powered immediately after the switching. Can be converted to

  Further, in order to switch from the operating state of the Rankine cycle 30A to the operating state of the refrigeration cycle 10A, when the Rankine cycle 30A is switched to the stopped state, the liquid pump 32 is stopped (after the predetermined time t2 has elapsed), and then the motor mode Since the pump motor mechanism 100 in operation is stopped (steps S405 to S420), the pump motor is used for a predetermined time t2 by using the superheated vapor refrigerant from the heater 30 that remains pressurized. It is expanded by the mechanism 100, and the heat energy of the refrigerant can be regenerated to mechanical energy without waste.

  At this time, the pressure of the refrigerant is reduced by the operation of the pump motor mechanism 100, and when starting the refrigeration cycle 10A, the starting torque of the pump motor mechanism 100 operated in the pump mode is prevented from increasing, and the power to the engine 20 is increased. The load can be reduced.

  Furthermore, when the pump motor mechanism 100 is stopped, the rotation of the rotating electrical machine 200 is stopped after the inflow port 106 is closed by the spool 107d and the motor mode is switched to the pump mode (steps S420 to S425). The rotation of the rotary electric machine 200 is stopped after the rotational force due to the motor mode (expansion) of the pump motor mechanism 100 is lost, and the rotary electric machine 200 does not act as a brake that counteracts the rotational force at the time of expansion. Power consumption.

  Further, when the pump motor mechanism 100 is operated in the pump mode, the pump motor mechanism 100 is activated by the rotary electric machine 200 and then the engine 20 (step S445 to step S450). Can be prevented from being applied to the engine 20, so that the engine 20 is not shocked and the passenger is not uncomfortable.

  At this time, since the necessity of activation by the rotating electrical machine 200 is determined according to the low-pressure side pressure of the pump motor mechanism 100 (steps S440 to S445), it is possible to prevent the rotating electrical machine 200 from operating wastefully.

  Furthermore, since the pump motor mechanism 100 can be used as both a compressor and an expander, a compact waste heat utilization apparatus 1 can be obtained.

  In the sub-flowchart in FIG. 4, the determination value in step S230 may be the pressure of the refrigerant pressurized by the liquid pump 32 instead of the time from the start of the liquid pump 32 (predetermined time t1). The pump motor mechanism 100 may be operated in the motor mode at a pressure (corresponding to the first predetermined pressure in the present invention) P1 or higher.

  In the sub-flowchart in FIG. 6, the pump motor mechanism 100 is operated by the rotating electrical machine 200 based on the low-pressure side pressure as in steps S440 to S445. The engine 20 may be operated after being operated by the rotating electrical machine 200 for a time (corresponding to the third predetermined time in the present invention) t3.

(Second Embodiment)
A second embodiment of the present invention is shown in FIGS. This is a modification of step S415A during the flow when the return operation of the refrigeration cycle 10A described in FIG. 5 is executed.

  That is, after stopping the liquid pump 32 in step S405, as a determination for stopping the motor mode of the pump motor mechanism 100 in step S420 and switching to the pump mode, as shown in step S415B of FIG. It may be determined whether or not the pressure of the pressurized refrigerant (high-pressure side pressure of Rankine cycle 30A) has decreased to a predetermined pressure (corresponding to the second predetermined pressure in the present invention) P2 or less. The predetermined pressure P2 is a pressure at which expansion in the pump motor mechanism 100 cannot be obtained.

  Further, as shown in step S415C of FIG. 8, it may be determined whether or not the pressure difference between the high pressure side and the low pressure side of the liquid pump 32 has dropped below a predetermined pressure difference ΔP.

  According to this, when the predetermined pressure P2 is used (step S415B), if the high pressure side pressure of the Rankine cycle 30A is operating at a low level, the predetermined pressure P2 becomes a sweet judgment value. By using the difference ΔP, the determination that the motor mode of the pump motor mechanism 100 is stopped can be made more reliable.

  Furthermore, as shown in step S415D of FIG. 9, it may be determined whether or not the power generation amount of the rotating electrical machine 200 has decreased to a predetermined power generation amount W or less.

(Third embodiment)
A third embodiment of the present invention is shown in FIG. 3rd Embodiment changes the expander integrated compressor 10 with respect to the said 1st Embodiment.

  Here, a power transmission path is switched among the pump motor mechanism 100, the rotary electric machine 200, and the electromagnetic clutch 300, and a speed change mechanism 400 including a planetary gear mechanism that transmits the rotational power of the rotational power by reducing or increasing the speed is added. doing.

  The speed change mechanism 400 includes a sun gear 401 provided in the center, a planetary carrier 402 connected to a pinion gear 402a that revolves around the outer periphery of the sun gear 401, and a ring-shaped ring gear provided further on the outer periphery of the pinion gear 402a. 403.

  The sun gear 401 is integrated with the rotor 220 of the rotating electrical machine 200, the planetary carrier 402 is integrated with the shaft 331 that rotates integrally with the friction plate 330 of the electromagnetic clutch 300, and the ring gear 403 is further integrated with the shaft 331. 108 is integrated.

  A one-way clutch 500 is interposed between the shaft 331 and the stator housing 230. The one-way clutch 500 allows the shaft 331 to rotate only in one direction (the rotation direction of the pulley unit 310). The bearing 404 supports the sun gear 401, that is, the rotor 220 so as to be rotatable with respect to the shaft 331, and the bearing 405 supports the shaft 331 (planetary carrier 402) so as to be rotatable with respect to the shaft 108. is there.

  When the electromagnetic clutch 300 connects the engine 20 side and the expander-integrated compressor 10 side to give a rotational force by the power of the engine 20, torque sufficient to prevent the sun gear 401, ie, the rotor 220, from rotating. By energizing the rotary electric machine 200 so as to be generated at 220, the pump motor mechanism 100 is accelerated and operates in the pump mode. Further, by changing the rotation speed of the rotating electrical machine 200, the pump motor mechanism 100 can be shifted (increased or decelerated).

  When the electromagnetic clutch 300 separates the engine 20 side and the expander-integrated compressor 10 side to apply a rotational force by the rotating electrical machine 200, the rotating electrical machine 200 is energized to determine the rotation direction of the pulley unit 310. By operating in the reverse direction, the pump motor mechanism 100 operates in the pump mode. At this time, since the shaft 331 (planetary carrier 402) is locked by the one-way clutch 500 and does not rotate, the rotational force of the rotating electrical machine 200 is decelerated by the transmission mechanism 400 and transmitted to the pump motor mechanism 100.

  The pump motor mechanism 100 operates in the motor mode by allowing the superheated vapor refrigerant from the heater 30 to flow into the pump motor mechanism 100 with the electromagnetic clutch 300 disconnected. At this time, the shaft 331 (planetary carrier 402) is locked by the one-way clutch 500 and does not rotate. Therefore, the rotational force of the pump motor mechanism 100 is increased by the speed change mechanism 400 and transmitted to the rotating electrical machine 200. Power generation at 200 is possible.

  When such an expander-integrated compressor 10 is used, during operation of the refrigeration cycle 10A, the rotating electric machine 200 is operated as a generator by setting the rotor 220 in a rotation-permitted state. In the return operation execution (step S400 in FIG. 3), the generator stop control in step S425 described in FIG. 5 is preferably abolished, and the loss associated with the deceleration and acceleration of the rotating electrical machine 200 due to the stop is good. Eliminating power saving control can be achieved.

(Fourth embodiment)
A fourth embodiment of the present invention is shown in FIG. The expander-integrated compressor 10 in the first to third embodiments includes an electromagnetic clutch 300 as a power transmission mechanism, and when the pump motor mechanism 100 is operated in the pump mode, the driving force or rotation of the engine 20 Although the driving force of the electric machine (electric motor) 200 is used, the present invention is not limited to this, and the electromagnetic clutch 300 is abolished so that the pump mode can be operated only by the driving force of the rotating electric machine (electric motor) 200. Also good.

(Fifth embodiment)
A fifth embodiment of the present invention is shown in FIGS. The fifth embodiment is different from the fourth embodiment in that the liquid pump 32 is changed to the heat medium pump 600 and the heat medium pump 600 is integrally connected to the expander-integrated compressor 10.

  The heat medium pump 600 is disposed on the anti-pump motor mechanism side of the rotating electrical machine 200 and is accommodated in a pump housing 601 fixed to the stator housing 230. Similar to the pump motor mechanism 100, the heat medium pump 600 includes a fixed scroll 602 including a substrate portion 602a and a tooth portion 602b, and a turning scroll 603 including a substrate portion 603a and a tooth portion 603b. The fixed scroll 602 is fixed to the pump housing 601, and the orbiting scroll 603 is disposed in a space formed by the pump housing 601 and the fixed scroll 602. Note that the orbiting scroll 603 can be revolved while being prevented from rotating by the rotation prevention mechanism 605.

  The pump housing 601 is provided with an inflow port 601a that is connected from the gas-liquid separator 12 side and communicates with the inside of the pump housing 601 and the orbiting scroll 603 side. Further, the fixed scroll 602 is provided with a discharge port 602c connected from the working chamber P formed by both scrolls 602 and 603 to the heater 30 side.

  The pump shaft 604 is rotatably supported by a bearing 604c fixed to the pump housing 601. The pump shaft 604 has an eccentric portion 604a that is eccentric with respect to the rotation center axis at one longitudinal end portion, and a bushing 604b and a bearing 603c are provided. Via the orbiting scroll 603. The other longitudinal end of the pump shaft 604 is connected to the other end of the shaft 108. Here, a hole 604d is provided on the other side of the pump shaft 604, and the other end side of the shaft 108 having a small diameter is inserted. A one-way clutch 700 is provided between the shaft 108 and the pump shaft 604. The one-way clutch 700 rotates the pump shaft 604 by meshing with the pump shaft 604 when the shaft 108 rotates in the reverse direction, and disengages from the pump shaft 604 when the shaft 108 rotates in the forward direction. The shaft 108 and the pump shaft 604 are disconnected (the pump shaft 604 is not rotated).

  A shaft seal 800 is provided between the stator housing 230 and the pump shaft 604 as a shaft seal device that seals between the rotating electrical machine 200 and the heat medium pump 600.

  In the waste heat utilization apparatus 1 using the expander-integrated compressor 10, the control device 40 operates the rotating electrical machine 200 as an electric motor when operating the refrigeration cycle 10A, and causes the shaft 108 to rotate (forward rotation). To turn the orbiting scroll 103 of the pump motor mechanism 100 to suck and compress the refrigerant (pump mode).

  In the pump mode, since the pump shaft 604 of the heat medium pump 600 is disengaged from the shaft 108 by the one-way clutch 700, the heat medium pump 600 is stopped and does not become an operating resistance in the rotating electrical machine 200.

  Moreover, the control apparatus 40 operates the rotary electric machine 200 as an electric motor (reverse direction rotation) when starting Rankine cycle 30A. At this time, the pump shaft 604 of the heat medium pump 600 is engaged with the shaft 108 by the one-way clutch 700, and the heat medium pump 600 is driven. Then, the high-pressure superheated vapor refrigerant heated by the heater 30 is introduced into the working chamber V of the pump motor mechanism 100 and expands (motor mode). Due to the expansion of the superheated steam refrigerant, the orbiting scroll 103 orbits in the opposite direction to that in the pump mode, and the driving force applied to the shaft 108 is transmitted to the rotor 220 of the rotating electrical machine 200. When the driving force transmitted to the shaft 108 exceeds the driving force for driving the heat medium pump 600, the heat medium pump 600 is operated by the pump motor mechanism 100, and the rotating electric machine 200 is a generator. Will be operated as. The electric power obtained by the rotating electric machine 200 is charged to the battery 25 by the inverter 26.

  Thus, the drive source of the heat medium pump 600 can be shared with the drive source of the pump motor mechanism 100 (rotary electric machine 200), and the heat medium pump 600 can be operated by the drive force of the pump motor mechanism 100 (motor mode). The drive source dedicated to the heat medium pump 600 can be eliminated.

(Other embodiments)
In each of the above-described embodiments, the Rankine cycle 30A is provided with the refrigeration cycle 10A. Control may be performed by the control device 40 with a focus on switching.

  Further, in each of the above-described embodiments, the pump motor mechanism 100 is used both as a compressor and an expander. However, each is set independently, and is arranged in parallel between the evaporator 14 and the heater 30. You may be made to do.

  In each of the above-described embodiments, the scroll type pump motor mechanism 100 and the heat medium pump 600 are employed. However, the present invention is not limited to this, and other types such as a rotary type, a piston type, and a vane type are used. It can also be applied to a type of pump motor mechanism and heat medium pump.

  In each of the above-described embodiments, the energy (electric energy) recovered by the expander-integrated compressor 10 is stored in the battery 25. However, the energy is stored as mechanical energy such as kinetic energy by a flywheel or elastic energy by a spring. May be.

  Further, in each of the above-described embodiments, the vehicle engine (internal combustion engine) 20 is used as the heat source for heating the refrigerant in the heater 30. Any battery stack, various motors, inverters, and the like that generate heat during operation and discard some of the heat for temperature control (waste heat is generated) can be widely applied.

It is a mimetic diagram showing the whole waste heat utilization device of an internal-combustion engine concerning an embodiment of the present invention. It is sectional drawing which shows the expander integrated compressor in 1st Embodiment. It is a main flowchart used for control at the time of operating a refrigerating cycle and a Rankine cycle alternately. It is a subflowchart used for control of Rankine cycle starting operation execution. 3 is a sub-flowchart 1 used for controlling execution of a refrigeration cycle return operation in the first embodiment. It is a sub-flowchart used for control of air-conditioning mode start execution. It is a sub-flowchart 2 used for control of refrigerating cycle return operation execution in a 2nd embodiment. It is a sub flow chart 3 used for control of refrigerating cycle return operation execution in a 2nd embodiment. It is a sub flowchart 4 used for control of refrigerating cycle return operation execution in a 2nd embodiment. It is sectional drawing which shows the expander integrated compressor in 3rd Embodiment. It is sectional drawing which shows the expander integrated compressor in 4th Embodiment. It is a schematic diagram which shows the whole structure of the waste-heat utilization apparatus of the internal combustion engine in 5th Embodiment. It is sectional drawing which shows the expander integrated compressor in 5th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Waste heat utilization apparatus of internal combustion engine 10A Refrigeration cycle 10 Expander-integrated compressor 11 Radiator (first radiator, second radiator)
20 engine (internal combustion engine)
30A Rankine cycle 30 Heater 32 Liquid pump (pump)
40 Control device 100 Pump motor mechanism (expander, compressor)
107 Valve mechanism 200 Rotating electric machine (electric motor, generator)
300 Electromagnetic clutch (power transmission mechanism)

Claims (30)

A pump (32) for pumping the medium flowing out from the first radiator (11), a heater (30) for heating the medium sent from the pump (32), and a vapor medium from the heater (30) A Rankine cycle (30A) having an expander (100) that converts the pressure energy of the medium into mechanical kinetic energy by expanding
In the Rankine cycle device comprising the control device (40) for switching the state of the Rankine cycle (30A) between the stopped state and the operating state,
When the state of the Rankine cycle (30A) is switched, the control device (40) delays the change in the operation state of the expander (100) with respect to the change in the operation state of the pump (32). Characteristic Rankine cycle device.   The control device (40) starts operating the expander (100) after starting the pump (32) when switching the Rankine cycle (30A) from a stopped state to an operating state. The Rankine cycle apparatus according to claim 1.   The Rankine according to claim 2, wherein the control device (40) starts operating the pump (32) and starts operating the expander (100) after a first predetermined time (t1) has elapsed. Cycle equipment.   The controller (40) starts the operation of the expander (100) after the pressure of the medium pressurized by the pump (32) rises to a first predetermined pressure (P1) or more. The Rankine cycle device according to claim 2. The expander (100) is connected to a rotating electric machine (200) having both functions of a generator and an electric motor,
The control device (40) operates the rotating electric machine (200) as an electric motor before starting the operation of the expander (100), according to any one of claims 2 to 4. The described Rankine cycle apparatus.   The control device (40) stops the operation of the expander (100) after stopping the operation of the pump (32) when switching the Rankine cycle (30A) from an operation state to a stop state. The Rankine cycle apparatus according to any one of claims 1 to 5.   The Rankine according to claim 6, wherein the control device (40) stops the operation of the pump (32) and stops the operation of the expander (100) after a second predetermined time (t2) has elapsed. Cycle equipment.   The control device (40) stops the operation of the expander (100) after the pressure of the medium pressurized by the pump (32) drops below a second predetermined pressure (P2). The Rankine cycle apparatus according to claim 6.   The control device (40) stops the operation of the expander (100) after the pressure difference between the high pressure side and the low pressure side of the pump (32) falls below a predetermined pressure difference (ΔP). The Rankine cycle apparatus according to claim 6. A generator (200) is connected to the expander (100),
The control device (40) stops the operation of the expander (100) after the power generation amount of the generator (200) by the expander (100) is reduced to a predetermined power generation amount (W) or less. The Rankine cycle apparatus according to claim 6.   The expander (100) is connected to a rotating electrical machine (200) as a generator that regenerates the mechanical kinetic energy into electrical energy. The Rankine cycle apparatus according to claim 9.   A refrigeration cycle (10A) having a compressor (100) that compresses the refrigerant using the medium as a refrigerant and a second radiator (11) that cools the refrigerant from the compressor (100) is provided. The Rankine cycle apparatus according to any one of claims 1 to 11.   The control device (40) switches the state of the Rankine cycle (30A) from the stopped state to the operating state when switching from the operating state as the refrigeration cycle (10A) to the operating state to the Rankine cycle (30A). The Rankine cycle apparatus according to claim 12. The expander (100) is connected to a rotating electric machine (200) having both functions of a generator and an electric motor,
A valve mechanism (107) for switching the refrigerant to either the compressor (100) side or the expander (100) side to flow in;
When operating the expander (100), the control device (40) operates the rotating electric machine (200) as an electric motor, and then causes the valve mechanism (107) to inject the refrigerant into the compressor (100). The Rankine cycle apparatus according to claim 12 or 13, wherein the expander (100) side is switched from the) side.   The control device (40) switches the state of the Rankine cycle (30A) from the operation state to the stop state when switching from the operation state as the Rankine cycle (30A) to the operation state to the refrigeration cycle (10A). The Rankine cycle apparatus according to claim 12. A generator (200) is connected to the expander (100),
A valve mechanism (107) for switching the refrigerant to either the compressor (100) side or the expander (100) side to flow in;
When the controller (40) stops the expander (100), the valve mechanism (107) switches the refrigerant inflow from the expander (100) side to the compressor (100) side. The Rankine cycle device according to claim 15, characterized in that the rotation of the generator (200) is stopped. An electric motor (200) for driving the compressor (100) is included, and the control device (40) selects at least one of the internal combustion engine (20) and the electric motor (200) as a driving source of the compressor (100). And
The controller (40) stops the expander (100) and operates the refrigeration cycle (10A), after using the driving force of the electric motor (200), the internal combustion engine (20) The Rankine cycle apparatus according to claim 15 or 16, wherein the compressor (100) is operated by a driving force.   The said control apparatus (40) determines the necessity of operation | movement of the said compressor (100) by the said electric motor (200) according to the low voltage | pressure side pressure of the said compressor (100), The Claim 17 characterized by the above-mentioned. The described Rankine cycle apparatus.   The said control apparatus (40) operates the said compressor (100) with the said electric motor (200) until the said low voltage | pressure side pressure becomes below 3rd predetermined pressure (P3), The said control device (40) is characterized by the above-mentioned. Rankine cycle equipment.   18. The Rankine cycle device according to claim 17, wherein the control device (40) operates the compressor (100) for a third predetermined time (t3) by the electric motor (200).   The first radiator (11) and the second radiator (11) are commonly used in the Rankine cycle (30A) and the refrigeration cycle (10A). The Rankine cycle apparatus according to any one of the above. The expander (100) also serves as the compressor (100) in the refrigeration cycle (10A),
The rankine according to any one of claims 12 to 21, further comprising a power transmission mechanism (300) for driving power of the internal combustion engine (20) to drive the compressor (100). Cycle equipment. The expander (100) also serves as the compressor (100) in the refrigeration cycle (10A),
The Rankine cycle device according to any one of claims 12 to 22, further comprising an electric motor (200) that drives the compressor (100).   24. The Rankine cycle device according to claim 23, wherein the electric motor (200) also drives the pump (32).   The Rankine cycle device according to any one of claims 1 to 24, wherein the pump (32) is connected to the expander (100).   The Rankine cycle apparatus according to any one of claims 1 to 25, wherein a heat source for heating the medium in the heater (30) is waste heat energy of the internal combustion engine (20).   An electric motor (200) for driving the compressor (100) is provided, and at least one of the internal combustion engine (20) and the electric motor (200) is used as a drive source of the compressor (100) by the control device (40). The Rankine cycle apparatus according to any one of claims 1 to 16, and 21 to 26, wherein the Rankine cycle apparatus is selected. A pump (32) for pumping the medium, a heater (30) for heating the medium sent from the pump (32), and expanding the vapor medium from the heater (30) to increase the pressure energy of the medium. In a method for controlling a Rankine cycle having an expander (100) that converts mechanical kinetic energy,
An operation step of pumping the medium to the heater (30) by the pump (32) and expanding the medium by the expander (100);
Stopping the pump (32) and stopping the expander (100);
A switching step of delaying a change in the operating state of the expander (100) with respect to a change in the operating state of the pump (32) and switching the Rankine cycle state between the operating step and the stopping step; A Rankine cycle control method comprising:   29. The switching step is characterized in that after the pump (32) is started to operate, the expander (100) is started to switch the Rankine cycle from the stop step to the operation step. The Rankine cycle control method described in 1.   29. The switching step is characterized in that after the pump (32) is deactivated, the expander (100) is deactivated to switch the Rankine cycle from the operation step to the stop step. Alternatively, the Rankine cycle control method according to claim 29.

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