WO2014112300A1

WO2014112300A1 - Waste heat utilization device

Info

Publication number: WO2014112300A1
Application number: PCT/JP2013/084573
Authority: WO
Inventors: 文彦石黒; 井口　雅夫; 英文森; 榎島　史修; 和雄片山; 尚也横町; 高三　正己
Original assignee: 株式会社豊田自動織機
Priority date: 2013-01-15
Filing date: 2013-12-25
Publication date: 2014-07-24
Also published as: JP2016040490A

Abstract

Provided is a waste heat utilization device capable of, while having a simple configuration, recovering energy and cooling a heat medium on the basis of a target physical amount by which the heat medium should be cooled. This waste heat utilization device, which is used in a drive system (1), is equipped with a Rankine cycle (3), a variable throttle valve (5), and a controller (7). In the drive system (1), pressurized air can be supplied to an engine (9). The Rankine cycle (3) has a boiler (23), a heat radiator (27), and the like, and circulates a working fluid. Furthermore, the Rankine cycle (3) is provided with the variable throttle valve (5) and the like. With this waste heat utilization device, when a large amount of cooling is requested for the pressurized air, for example, the controller (7) controls the variable throttle valve (5) so as to reduce the degree of opening. Thus, in a heat radiation unit (275) in the heat radiator (27) the temperature difference between the working fluid and the surrounding air becomes large, due to the rise in the temperature of the working fluid in conjunction with the rise in the condensation pressure of the working fluid. Therefore, the cooling capacity of the working fluid in the radiator (27) increases.

Description

Waste heat utilization equipment

The present invention relates to a waste heat utilization apparatus.

Patent Document 1 discloses a conventional waste heat utilization device. This waste heat utilization device is used in a drive system, and includes a Rankine cycle for circulating a working fluid, setting means, and control means, and is mounted on a vehicle. The drive system includes an engine that is an internal combustion engine and a coolant circuit that can circulate coolant for the engine.

The Rankine cycle has a working fluid flow path, a pump, a boiler, an expander, a radiator, a reservoir, a recovery path, a supply path, and first and second solenoid valves. The working fluid can flow through the working fluid flow path. A certain amount of working fluid is stored in the reservoir.

The pump, boiler, expander, and radiator are connected by a working fluid flow path, and the working fluid can be circulated in the order of the pump, boiler, expander, and radiator. A generator is connected to the expander.

On the other hand, each end of the collection path and the supply path is connected to the reservoir. The other end side of the recovery path is connected to the working fluid path upstream of the pump and downstream of the boiler. The other end of the supply path is connected to the working fluid path downstream of the expander and upstream of the radiator. The first solenoid valve is provided in the recovery path, and the second solenoid valve is provided in the supply path.

In this waste heat utilization apparatus, it is possible to cool the coolant and heat the working fluid by exchanging heat between the coolant and the working fluid in the boiler. And a generator is act | operated by the pressure energy at the time of a hot working fluid expanding and decompressing with an expander. Thus, in the waste heat utilization apparatus, the pressure energy of the working fluid can be recovered as electric power in the Rankine cycle.

Furthermore, in this waste heat utilization apparatus, the ECU of the vehicle sets a cooling request amount for the coolant. Here, when the required cooling amount for the coolant is large, the ECU controls the first electromagnetic valve to close and the second on-off valve to open. For this reason, the working fluid stored in the reservoir flows into the working fluid flow path via the supply path, and the flow rate of the working fluid circulating in the Rankine cycle increases. Thereby, in this waste heat utilization apparatus, in a boiler, it becomes possible for a cooling fluid to radiate heat suitably to a working fluid.

On the other hand, when the required cooling amount for the coolant is small, the ECU controls the first electromagnetic valve to open and the second on-off valve to close. Thus, in the Rankine cycle, a part of the working fluid discharged from the pump is stored in the reservoir through the recovery path. For this reason, in this waste heat utilization apparatus, the flow volume of the working fluid which circulates in a Rankine cycle reduces, and it can suppress that a cooling fluid is cooled more than necessary in a boiler.

Thus, in this waste heat utilization apparatus, it is possible to cool the coolant according to the set cooling request amount while collecting power.

JP 2008-231981

However, in the above-described conventional waste heat utilization apparatus, a reservoir, a recovery path, a supply path, and first and second electromagnetic valves are separately provided for a working fluid flow path circuit to which a pump, boiler, expander, and radiator are connected. It is necessary to provide it. For this reason, in this waste heat utilization apparatus, complication of composition is inevitable.

The present invention has been made in view of the above-described conventional situation, and solves the problem of providing a waste heat utilization apparatus capable of realizing energy recovery and suitable cooling of a heat medium while simplifying the configuration. It is an issue that should be done.

In a waste heat utilization device equipped with a Rankine cycle that circulates a working fluid used in a drive system,
The drive system includes an internal combustion engine, and a heat medium flow path that is connected to the internal combustion engine and through which a heat medium for the internal combustion engine can flow.
The Rankine cycle includes a working fluid flow path through which the working fluid can flow.
A pump for circulating the working fluid along the working fluid flow path;
A boiler that is connected downstream of the pump by the working fluid flow path and connected to the heat medium flow path, performs heat exchange between the working fluid and the heat medium, and cools the heat medium;
An expander connected by the working fluid flow path downstream of the boiler and expanding the working fluid;
A radiator that is connected by the working fluid flow path downstream of the expander and upstream of the pump, and that radiates heat of the working fluid by a cooling medium;
The radiator includes a radiator inlet that allows the working fluid to flow therein, a radiator outlet that allows the working fluid to flow out from the interior, and between the radiator inlet and the radiator outlet. A heat dissipating part located,
Between the radiator inlet and the pump, a differential pressure adjusting means capable of adjusting the pressure difference of the working fluid is provided between the upstream and the downstream of the pump,
Setting means for setting a target physical quantity for cooling the heat medium;
Control means for controlling the differential pressure adjusting means so that the pressure of the working fluid upstream of the differential pressure adjusting means increases when the heat dissipation amount of the working fluid in the heat radiating portion is insufficient based on the target physical quantity. It is characterized by having.

In the waste heat utilization apparatus of the present invention, the heat medium can be cooled and the working fluid can be heated by heat exchange between the heat medium and the working fluid in the boiler. And in a Rankine cycle, it is possible to collect | recover the pressure energy at the time of a hot working fluid being expanded and pressure-reduced with an expander. Examples of recoverable energy include power generated based on the pressure energy of the working fluid, power regenerated by the internal combustion engine, and the like.

In this waste heat utilization apparatus, the setting means sets a target physical quantity for cooling the heat medium. And based on this target physical quantity, when the heat dissipation amount of the working fluid in the heat radiating portion is insufficient, that is, when the cooling amount of the working fluid in the heat radiating portion is insufficient, the control means controls the working fluid upstream of the differential pressure adjusting means. The differential pressure adjusting means is controlled so that the pressure increases. That is, the pressure difference between the working fluid upstream of the differential pressure adjusting means and the working fluid downstream of the differential pressure adjusting means is adjusted to be large. Thereby, in a Rankine cycle, the pressure of the working fluid which distribute | circulates a working fluid flow path between the exit of an expander and a differential pressure | voltage adjustment means rises.

Further, in the heat radiating portion of the radiator, a sub-cooling region for radiating the liquid-phase working fluid can be formed in addition to the capacitor region for radiating the gas-phase working fluid. Specifically, in the condenser region, the condensing latent heat of the working fluid is radiated at a constant condensation temperature, whereby the gas phase working fluid is liquefied. Thus, the working fluid is dissipated in the capacitor region. On the other hand, the liquid-phase working fluid that has passed through the capacitor region flows into the subcool region. The working fluid radiates sensible heat while lowering the temperature in the subcool region. In this way, the working fluid is dissipated in the subcool region.

Here, as described above, when the pressure of the working fluid increases by the differential pressure adjusting means, that is, when the pressure of the working fluid flowing through the radiator increases, the temperature of the working fluid becomes high. For this reason, in the heat radiation mode in the heat radiation part as described above, the temperature difference between the condensation temperature in the capacitor region and the temperature of the cooling medium and the temperature difference between the average temperature in the subcool region and the temperature of the cooling medium become large. For this reason, when the pressure of the working fluid is high, the heat radiation amount of the working fluid in the entire heat radiating portion is increased as compared with the case where the pressure of the working fluid is low. Thereby, the temperature of the working fluid flowing out from the outlet of the subcool region, that is, the radiator outlet is lowered.

For this reason, in this waste heat utilization apparatus, when the cooling amount of the working fluid in the heat radiating part is insufficient with respect to the set target physical quantity, the difference is such that the pressure of the working fluid upstream of the differential pressure adjusting means increases. By controlling the pressure adjusting means, the working fluid can be sufficiently cooled in the heat radiating section. In this way, in this waste heat utilization apparatus, the shortage of the cooling amount of the working fluid in the heat radiating unit with respect to the target physical quantity can be solved, and the heat medium can be suitably cooled by heat exchange in the boiler. In this case, since the condensation pressure that is the pressure of the working fluid from the downstream of the expander to the upstream of the pump increases, the amount of energy that can be recovered in the Rankine cycle decreases.

On the other hand, if the cooling amount of the working fluid in the heat dissipation part exceeds the target physical quantity, or if the cooling amount of the working fluid does not matter against the target physical quantity immediately after the start of the waste heat utilization device The differential pressure adjusting means is controlled so that the pressure of the working fluid upstream of the differential pressure adjusting means decreases. That is, adjustment is performed so that the pressure difference between the working fluid upstream of the differential pressure adjusting means and the working fluid downstream of the differential pressure adjusting means becomes small or the pressure difference becomes zero. Thereby, in a Rankine cycle, the pressure of the working fluid which distribute | circulates a working fluid flow path between the exit of an expander and a differential pressure | voltage adjustment means falls. In this case, contrary to the case where the cooling amount of the working fluid in the heat radiating portion is small, the temperature difference between the working fluid in the heat radiating portion and the cooling medium is small, and the heat radiating amount is small. It will not be cooled more than necessary. As a result, in this waste heat utilization apparatus, the temperature of the working fluid when flowing into the boiler does not decrease more than necessary, and cooling of the heat medium due to heat exchange in the boiler can be suppressed.

In this way, in this waste heat utilization device, the amount of cooling of the working fluid in the heat radiating section can be adjusted according to the target physical quantity simply by adjusting the pressure difference of the working fluid upstream and downstream of the differential pressure adjusting means. It is. For this reason, in this waste heat utilization apparatus, it is possible to suppress suitably the complication of a Rankine cycle.

Therefore, according to the waste heat utilization apparatus of the present invention, it is possible to realize energy recovery and suitable cooling of the heat medium while simplifying the configuration.

As the internal combustion engine, various types of engines other than gasoline engines and diesel engines can be adopted. These engines may be hybrid engines combining motors. Furthermore, these engines may be air-cooled or water-cooled.

As the heat medium, for example, an intake system fluid sucked into the internal combustion engine can be employed. The intake system fluid refers to pressurized air compressed by a supercharger, recirculated exhaust gas recirculated to an internal combustion engine, or the like. In addition to coolant such as water and LLC (Long Life Coolant), lubricating oil or the like can be used as a heat medium.

As the cooling medium, for example, water or LLC other than the heat medium other than air can be employed.

As the differential pressure adjusting means, for example, an opening adjusting means capable of adjusting the opening of the working fluid path can be employed. As such an opening adjustment means, for example, a variable throttle valve or the like can be employed.

In the waste heat utilization apparatus of the present invention, the Rankine cycle may have a gas-liquid separator that is connected by a working fluid flow path downstream of the radiator and upstream of the pump and that can separate the working fluid. And it is preferable that the differential pressure | voltage adjustment means is integrally provided with the working fluid flow path between a heat radiator and a gas-liquid separator, or a gas-liquid separator.

In this case, in the Rankine cycle, the working fluid flows into the pump in a liquid phase state. For this reason, in a Rankine cycle, it becomes possible to circulate a working fluid suitably along a working fluid flow path, and it becomes possible to perform heat exchange with a boiler suitably. For this reason, in this waste heat utilization apparatus, it becomes possible to suitably collect the pressure energy of the working fluid in the Rankine cycle.

Here, when the differential pressure adjusting means is integrated with the gas-liquid separator, the gas-liquid separator can be further integrated with the radiator.

The gas-liquid separator may have a receiver case in which a receiver inlet and a receiver outlet are formed. Further, a liquid receiving chamber for storing a working fluid in a liquid state may be formed in the receiver case. Furthermore, a working fluid flow path can be connected to each of the receiver inlet and the receiver outlet. And it is preferable that the differential pressure | voltage adjustment means is provided in the receiver case.

If it is a receiver case, it is easy to ensure a space for further providing a differential pressure adjusting means while forming a liquid receiving chamber. For this reason, by providing the differential pressure adjusting means in the receiver case, the differential pressure adjusting means and the gas-liquid separator can be easily integrated.

Also, the Rankine cycle may have a supercooler connected by a working fluid flow path downstream of the radiator and upstream of the pump, and capable of supercooling the working fluid. And it is preferable that the differential pressure | voltage adjustment means is provided between the heat radiator and the subcooler. In this case, since the working fluid cooled to the supercooled state by the supercooler flows into the pump, the occurrence of cavitation in the pump can be suppressed. Note that the radiator and the supercooler may be integrated. As described above, when the radiator and the supercooler are integrated, a portion where the working fluid reaches from the radiator to the supercooler becomes a working fluid flow path.

Here, when a gas-liquid separator is provided in the Rankine cycle, the supercooler is preferably connected by a working fluid flow path downstream of the gas-liquid separator and upstream of the pump. The differential pressure adjusting means is preferably provided in the working fluid flow path between the radiator and the gas-liquid separator. In this case, it becomes possible to supercool the liquid-phase working fluid in the supercooler. For this reason, it becomes possible to cool a working fluid suitably to a supercooled state, and it becomes possible to suppress generation | occurrence | production of the cavitation in a pump more suitably.

Thus, when the gas-liquid separator is provided in the Rankine cycle, the gas-liquid separator and the supercooler may be integrated. Further, the radiator, the supercooler, and the gas-liquid separator may be integrated. In these cases, the gas-liquid separator may be integrated with the differential pressure adjusting means.

In the waste heat utilization apparatus of the present invention, the radiator includes, for example, a gas-liquid separation unit capable of gas-liquid separation of the working fluid that has passed through the heat radiation unit, and a supercooling of the working fluid located downstream of the gas-liquid separation unit. It can have a possible supercooling part integrally. And it is also preferable that the differential pressure adjusting means is provided in the gas-liquid separator.

As described above, when the radiator has the gas-liquid separator and the supercooling unit in addition to the radiator inlet, the radiator outlet and the radiator, the gas-liquid separator or the It is possible to achieve the same effect as when a supercooler is provided.

In the waste heat utilization apparatus of the present invention, the target physical quantity may be a cooling requirement amount required by the drive system. The control means preferably controls the differential pressure adjusting means so that the pressure of the working fluid upstream of the differential pressure adjusting means increases when the required cooling amount is large.

In this case, if the required cooling amount is large and the cooling amount of the working fluid in the radiator becomes insufficient, the control means controls the differential pressure adjusting means, and controls the pressure of the working fluid upstream of the differential pressure adjusting means. increase. Thereby, since the pressure of the working fluid which distribute | circulates the inside of a radiator rises, the cooling amount of the working fluid in a thermal radiation part becomes large. For this reason, in the boiler, the heat medium can sufficiently dissipate heat to the working fluid, and the required cooling amount can be satisfied. On the other hand, when the required cooling amount is small, it is possible to increase the recoverable energy by suppressing the cooling amount of the working fluid in the heat radiating unit.

In the waste heat utilization apparatus of the present invention, the setting means can set the required cooling amount required by the drive system by various means. For example, the setting means can set the required cooling amount based on the output of the internal combustion engine. In particular, the internal combustion engine may be a vehicle engine. The setting means can set the required cooling amount based on the accelerator opening of the vehicle or the accelerator opening and the rotational speed of the vehicle engine.

Further, the setting means may include a first temperature detection means provided in the heat medium flow path or the boiler and capable of detecting the temperature of the heat medium flowing through the boiler. Then, the setting means can set the required cooling amount based on the detection value detected by the first temperature detection means. Here, when the first temperature detection means is provided in the heat medium flow path, it is possible to detect the temperature of the working fluid flowing into the boiler. On the other hand, when the first temperature detecting means is provided in the boiler, the temperature of the working fluid circulating in the boiler can be detected.

Further, the setting means may include second temperature detection means provided in the heat medium flow path and capable of detecting the temperature of the heat medium flowing out from the boiler. Then, the setting means can set the required cooling amount based on the detection value detected by the second temperature detection means.

Further, the setting means may include a first pressure detection means provided in the heat medium flow path or the boiler and capable of detecting the pressure of the heat medium flowing through the boiler. Then, the setting means can set the required cooling amount based on the detection value detected by the first pressure detection means. Similar to the first temperature detecting means, if the first pressure detecting means is provided in the heat medium flow path, the pressure of the working fluid flowing into the boiler can be detected, and if the first pressure detecting means is provided in the boiler, the boiler is detected. It is possible to detect the pressure of the working fluid that circulates.

In these cases, the setting means can accurately set the required cooling amount required by the drive system.

In the waste heat utilization apparatus of the present invention, the target physical quantity may be a coolable quantity that allows the working fluid to cool the heat medium. The control means preferably controls the differential pressure adjusting means so that the pressure of the working fluid upstream of the differential pressure adjusting means increases when the coolable amount is small.

In this case, the control means when the temperature of the working fluid is not lowered to such an extent that the heat medium can be cooled to a predetermined temperature in the heat exchange in the boiler, that is, when the cooling amount of the working fluid to the heat medium is small. Controls the differential pressure adjusting means and increases the pressure of the working fluid upstream of the differential pressure adjusting means. Thereby, the cooling amount of the working fluid in the heat radiating portion is increased, and the temperature of the working fluid when flowing into the boiler is lowered. Thus, in this waste heat utilization apparatus, it is possible to increase the amount of cooling possible for the heat medium, and it is possible to suitably cool the heat medium by heat exchange in the boiler. On the other hand, when the coolable amount of the working fluid with respect to the heat medium is large, the recoverable energy can be increased by suppressing the cooling amount of the working fluid in the heat radiating unit.

The setting means can be set by various means also about the coolable amount that the working fluid can cool the heat medium. For example, the setting means may set the coolable amount based on the temperature of the working fluid from the radiator outlet to the working fluid inlet in the boiler. Particularly in this case, the setting means may include third temperature detection means provided in the Rankine cycle and capable of detecting the temperature of the working fluid flowing into the boiler. And it is preferable that a setting means sets the cooling possible amount with respect to a thermal medium based on the detected value which the 3rd temperature detection means detected.

Further, the setting means may include second pressure detection means provided in the Rankine cycle and capable of detecting the pressure of the working fluid from the downstream of the differential pressure adjusting means to the upstream of the pump. Then, the setting means can set the coolable amount based on the detection value detected by the second pressure detection means.

In these cases, the setting means can accurately set the coolable amount by which the working fluid can cool the heat medium.

According to the waste heat utilization apparatus of the present invention, it is possible to realize energy recovery and suitable cooling of the heat medium while simplifying the configuration.

1 is a schematic structural diagram showing a waste heat utilization apparatus of Example 1. FIG. It is sectional drawing which concerns on the waste heat utilization apparatus of Example 1, and shows the state in which the capacitor | condenser area | region increased and the subcool area | region decreased in the thermal radiation part. It is a Mollier diagram which shows the driving | running state in the state which concerns on the waste heat utilization apparatus of Example 1, and the capacitor | condenser area | region increased and the subcool area | region decreased in the thermal radiation part. It is sectional drawing which shows the state which concerns on the waste heat utilization apparatus of Example 1, and the subcool area | region increased and the capacitor | condenser area | region decreased in the thermal radiation part. It is a Mollier diagram which shows the driving | running state in the state which concerns on the waste heat utilization apparatus of Example 1, and the subcool area | region increased and the capacitor | condenser area | region decreased in the thermal radiation part. FIG. 3 is a schematic structural diagram showing a waste heat utilization apparatus of Example 2. It is a Mollier diagram which shows the driving | running state in the state which concerns on the waste heat utilization apparatus of Example 2, and the capacitor | condenser area | region increased and the subcooling area | region decreased in the thermal radiation part. It is a Mollier diagram which shows the driving | running state in the state which concerns on the waste heat utilization apparatus of Example 2, and the subcool area | region increased and the capacitor | condenser area | region decreased in the thermal radiation part. It is sectional drawing which concerns on the waste-heat utilization apparatus of Example 3, and shows a radiator, a gas-liquid separator, a variable throttle valve, etc. It is sectional drawing which concerns on the waste heat utilization apparatus of Example 4, and shows a radiator, a gas-liquid separator, a variable throttle valve, etc. It is sectional drawing which concerns on the waste-heat utilization apparatus of Example 5, and shows a radiator, a gas-liquid separator, a variable throttle valve, a subcooler, etc. It is sectional drawing which concerns on the waste-heat utilization apparatus of Example 6, and shows a radiator, a gas-liquid separator, a variable throttle valve, a subcooler, etc. It is sectional drawing which concerns on the waste-heat utilization apparatus of Example 7, and shows a radiator, a gas-liquid separator, a variable throttle valve, a subcooler, etc. It is a schematic structure figure which shows the waste heat utilization apparatus of Example 8. FIG. 10 is a cross-sectional view illustrating a radiator unit according to an eighth embodiment.

Embodiments 1 to 8 embodying the present invention will be described below with reference to the drawings. The waste heat heat utilization devices of Examples 1 to 8 are all mounted on a vehicle.

(Example 1)
As shown in FIG. 1, the waste heat utilization apparatus of the first embodiment is used in a drive system 1 and includes a Rankine cycle 3, a variable throttle valve 5, and a controller 7. In this waste heat utilization apparatus, the variable throttle valve 5 corresponds to the differential pressure adjusting means in the present invention, and the controller 7 corresponds to the setting means and the control means.

The drive system 1 has an engine 9 as an internal combustion engine, a turbocharger 11, and pipes 13 to 17. The engine 9 is a diesel engine. The engine 9 is formed with an exhaust port 9a for exhausting exhaust and an intake port 9b for sucking in pressurized air described later. This pressurized air is an intake system fluid and corresponds to a heat medium in the present invention. A gasoline engine may be used as the engine 9 instead of the diesel engine.

The turbocharger 11 is operated by the exhaust gas discharged from the engine 9 and supplies the engine 9 with pressurized air obtained by pressurizing air outside the vehicle.

The pipe 13 has one end connected to the exhaust port 9a of the engine 9 and the other end connected to the turbocharger 11. By circulating this pipe 13, it is possible to guide the exhaust discharged from the engine 9 to the turbocharger 11.

The pipe 14 has one end connected to the turbocharger 11 and the other end connected to a pressurized air inlet 23a of a boiler 23 described later. One end of the pipe 15 is connected to the pressurized air outlet 23 b of the boiler 23, and the other end is connected to the intake port 9 b of the engine 9. By circulating these

pipes

14 and 15, the compressed air compressed by the turbocharger 11 can be guided to the boiler 23 and further to the engine 9. That is, these

pipes

14 and 15 correspond to the heat medium flow path in the present invention.

The turbocharger 11 is connected to one end sides of the

pipes

16 and 17. The other end side of the pipe 16 is connected to a muffler (not shown). The other end side of the pipe 17 opens to an outside air introduction portion of the vehicle (not shown). The pipe 16 communicates with the pipe 13 via the turbocharger 11. Similarly, the pipe 17 communicates with the pipe 14 via the turbocharger 11.

The piping 14 is provided with a first temperature sensor 19 and a first pressure sensor 21. Each of the first temperature sensor 19 and the first pressure sensor 21 is electrically connected to the controller 7.

The first temperature sensor 19 detects the temperature of the pressurized air flowing through the pipe 14, that is, the temperature of the pressurized air flowing into the boiler 23, and transmits the detected value to the controller 7. The first temperature sensor 19 corresponds to the first temperature detecting means in the present invention.

The first pressure sensor 21 detects the pressure of the pressurized air flowing into the boiler 23 based on the pressure of the pressurized air flowing through the pipe 14, and transmits the detected value to the controller 7. The first pressure sensor 21 corresponds to the first pressure detection means in the present invention.

The piping 15 is provided with a second temperature sensor 22. The second temperature sensor 22 is also electrically connected to the controller 7. The second temperature sensor 22 detects the temperature of the pressurized air flowing through the pipe 15, that is, the temperature of the pressurized air that has flowed out of the boiler 23, and transmits the detected value to the controller 7. The second temperature sensor 22 corresponds to the second temperature detection means in the present invention.

Rankine cycle 3 includes an electric pump P1, a boiler 23, an expander 25, a radiator 27, a gas-liquid separator 29, and pipes 31 to 35 as working fluid paths. An HFC 134a as a working fluid can flow through the pipes 31 to 35.

The electric pump P1 is electrically connected to the controller 7. A discharge port 101 and a suction port 102 are formed in the electric pump P1.

The boiler 23 has a pressurized air inlet 23a through which pressurized air flows in, a pressurized air outlet 23b through which pressurized air flows out, a working fluid inlet 23c through which the working fluid flows in, and a working fluid out. A working fluid outlet 23d is formed. A heat radiating plate 23e is provided inside the boiler 23. The interior of the boiler 23 is partitioned into a first passage 23f and a second passage 23g by the heat radiating plate 23e.

The first passage 23f communicates with the pressurized air inlet 23a and the pressurized air outlet 23b at both ends, respectively, so that the pressurized air can flow therethrough. Further, the second passage 23g communicates with the working fluid inlet 23c and the working fluid outlet 23d at both ends, respectively, so that the working fluid can flow therethrough. In the boiler 23, the pressurized air in the first passage 23f and the working fluid in the second passage 23g exchange heat through the heat radiating plate 23e, thereby cooling the pressurized air and heating the working fluid. It is possible to do. That is, the boiler 23 also functions as a cooler for the pressurized air.

The expander 25 is formed with an inlet 25a through which a working fluid flows and an outlet 25b through which the working fluid flows out. The expander 25 generates a rotational driving force by expanding the working fluid heated through the boiler 23. A known generator (not shown) is connected to the expander 25. The generator generates power by the rotational driving force of the expander 25 and charges the battery (not shown) with electric power.

As shown in FIG. 2, the radiator 27 includes first and

second heads

271 and 273 extending vertically in the vertical direction and a heat radiating portion 275 extending horizontally with respect to the first and

second heads

271 and 273. Yes. The heat radiating portion 275 is constituted by a plurality of tubes communicating with the first head 271 and the second head 273. Although not shown in the figure, in the heat dissipating part 275, heat dissipating fins are provided between the tubes. In this heat radiator 27, when flowing through the heat radiating portion 275, the working fluid is radiated to the air passing through the heat radiator 27. The air passing through the radiator 27 corresponds to the cooling medium in the present invention. Thereby, the radiator 27 cools the working fluid.

The first head 271 of the radiator 27 is formed with a radiator inlet 27a through which a working fluid flows. The second head 273 is formed with a radiator outlet 27b through which the working fluid flows out from the inside. Further, as shown in FIG. 1, an electric fan 27 c is provided in the vicinity of the radiator 27. The electric fan 27 c is electrically connected to the controller 7.

The gas-liquid separator 29 has a cylindrical receiver case 290 as shown in FIG. The receiver case 290 is formed with a receiver inlet 29a at a position upstream of the working fluid in the circulation direction of the working fluid, which will be described later. Outflow port 29b is formed. A liquid receiving chamber 29c is formed in the receiver case 290. The gas-liquid separator 29 separates the working fluid flowing in from the receiver inlet 29a into gas and liquid. The gas-liquid separator 29 stores the working fluid in a liquid state in the liquid receiving chamber 29c, and causes the stored working fluid in a liquid state to flow out from the receiver outlet 29b in order.

As shown in FIG. 1, the electric pump P1, the boiler 23, the expander 25, the radiator 27, and the gas-liquid separator 29 are connected by pipes 31 to 35. Specifically, the discharge port 101 of the electric pump P1 and the working fluid inlet 23c of the boiler 23 are connected by a pipe 31. The working fluid outlet 23 d of the boiler 23 and the inlet 25 a of the expander 25 are connected by a pipe 32. An outlet 25 b of the expander 25 and a radiator inlet 27 a of the radiator 27 are connected by a pipe 33. A radiator outlet 27 b of the radiator 27 and a receiver inlet 29 a of the gas-liquid separator 29 are connected by a pipe 34. The receiver outlet 29b of the gas-liquid separator 29 and the suction port 102 of the electric pump P1 are connected by a pipe 35.

In the Rankine cycle 3, the working fluid circulates in the pipes 31 to 35 by operating the electric pump P1. Specifically, the working fluid circulates in the order from the discharge port 101 of the electric pump P1 through the boiler 23, the expander 25, the radiator 27, and the gas-liquid separator 29 to the suction port 102 of the electric pump P1.

The variable throttle valve 5 is provided in the pipe 34. The variable throttle valve 5 is electrically connected to the controller 7. The variable throttle valve 5 can adjust the pressure of the working fluid flowing between the outlet 25b of the expander 25 and the variable throttle valve 5 by adjusting the opening of the variable throttle valve 5 itself. Thereby, the variable throttle valve 5 can adjust the pressure difference of the working fluid between its upstream and downstream.

The piping 31 is provided with a third temperature sensor 37. The third temperature sensor 37 is electrically connected to the controller 7. The third temperature sensor 37 detects the temperature of the working fluid flowing through the pipe 31, that is, the temperature of the working fluid flowing into the boiler 23, and transmits the detected value to the controller 7. The third temperature sensor 37 corresponds to the third temperature detecting means in the present invention. Note that the third temperature sensor 37 may be provided in the pipe 34 or the pipe 35.

Further, a second pressure sensor 39 is provided at a position downstream of the variable throttle valve 5 in the pipe 34. The second pressure sensor 39 is also electrically connected to the controller 7. The second pressure sensor 39 detects the pressure of the working fluid from the downstream of the variable throttle valve 5 to the upstream of the electric pump P1, based on the pressure of the working fluid flowing downstream from the variable throttle valve 5 in the pipe 34. The detected value is transmitted to the controller 7. The second pressure sensor 39 corresponds to the second pressure detecting means in the present invention. The second pressure sensor 39 can also be provided in the pipe 35.

The controller 7 controls each operation of the electric pump P1 and the electric fan 27c. Further, the controller 7 is configured to be able to detect the accelerator opening of the vehicle based on a signal received from the ECU or the like (not shown) of the vehicle, and can detect the output of the engine 9 based on the accelerator opening. It has become. The controller 7 may detect the output of the engine 9 based on the accelerator opening and the rotational speed of the engine 9.

Furthermore, the controller 7 stores a control map for adjusting the opening degree of the variable throttle valve 5. The controller 7 stores a threshold for the temperature of the pressurized air and the working fluid, and a threshold for the pressure of the pressurized air and the working fluid, in addition to the threshold for the output of the engine 9. Then, the controller 7 detects the detected output of the engine 9, the detection values by the first to

third temperature sensors

19, 22, and 37, the detection values by the first and

second pressure sensors

21, 39, and each threshold value stored in advance. Thus, it is possible to set a target physical quantity for cooling the pressurized air. More specifically, based on the output of the engine 9, the detection values by the first and

second temperature sensors

19 and 22, and the detection value by the first pressure sensor 21, the controller 7 requests the cooling request amount requested by the drive system 1. In other words, it is possible to set the required cooling amount for the pressurized air. On the other hand, based on the detection value by the third temperature sensor 37 and the detection value by the second pressure sensor 39, the controller 7 can set the coolable amount of the working fluid with respect to the pressurized air.

The controller 7 controls the variable throttle valve 5 based on the set target physical quantity so that the opening degree is decreased when the heat dissipation amount of the working fluid in the heat dissipation portion 275 of the radiator 27 is insufficient. Specifically, in addition to the output of the engine 9, each threshold value stored in advance by the controller 7 for each detected value by the first to

third temperature sensors

19, 22, 37 and the first and

second pressure sensors

21, 39 is set. If it exceeds, the controller 7 will judge that the thermal radiation amount of the working fluid in the thermal radiation part 275 is insufficient. Thereby, the controller 7 controls so that the opening degree of the variable throttle valve 5 decreases.

The waste heat heat utilization device configured in this way operates as follows by driving the vehicle.

When the vehicle is driven, the engine 9 is operated in the drive system 1, and the exhaust discharged from the exhaust port 9 a flows through the pipe 13 and reaches the turbocharger 11. As a result, the turbocharger 11 is operated, and the air outside the vehicle flowing in from the pipe 17 is sucked into the turbocharger 11 and compressed. At this time, the exhaust gas that has reached the turbocharger 11 is discharged from the pipe 16 through the muffler to the outside of the vehicle. The air compressed by the turbocharger 11 flows through the pipe 14 as pressurized air. The pressurized air flows into the boiler 23 from the pressurized air inlet 23a and flows through the first passage 23f. At this time, the first temperature sensor 19 detects the temperature of the working fluid flowing through the pipe 14 and transmits the detected value to the controller 7. Similarly, the first pressure sensor 21 detects the pressure of the working fluid flowing through the pipe 14 and transmits the detected value to the controller 7.

Also, with the start of driving of the vehicle, the controller 7 operates the electric pump P1 and the electric fan 27c. Here, immediately after the vehicle is driven, the temperature of the working fluid does not become a big problem with respect to the required cooling amount for the pressurized air and the coolable amount of the working fluid for the pressurized air in the waste heat heat utilization device. For this reason, the controller 7 has a pressure difference between the working fluid upstream of the variable throttle valve 5 and the working fluid downstream of the variable throttle valve 5 so that the flow rate of the working fluid flowing through the pipe 34 is maximized. The opening degree of the variable throttle valve 5 is controlled so as to decrease. For this reason, the condensing pressure of the working fluid passing through the radiator 27 is minimized.

Thus, in the Rankine cycle 3, the working fluid is discharged from the discharge port 101 of the electric pump P1, and flows through the second passage 23g from the working fluid inflow passage 23c of the boiler 23 via the pipe 31. The third temperature sensor 37 detects the temperature of the working fluid flowing through the pipe 31 and transmits the detected value to the controller 7.

The working fluid flowing through the second passage 23g exchanges heat with the pressurized air flowing through the first passage 23f. Thus, the pressurized air is cooled and the working fluid is heated. Since the pressurized air becomes high temperature by being compressed, the working fluid is suitably heated.

The pressurized air cooled in the boiler 23 flows out from the pressurized air outlet 23b in a state where the density is increased, and flows through the pipe 15. At this time, the second temperature sensor 22 detects the temperature of the working fluid flowing through the pipe 15 and transmits the detected value to the controller 7. The pressurized air flowing through the pipe 15 is supplied to the engine 9 from the intake port 9 b of the engine 9. Thus, in this waste heat utilization apparatus, since pressurized air can be supplied to the engine 9 in a high density state, the output of the engine 9 can be increased.

On the other hand, the working fluid heated in the boiler 23 flows out from the working fluid outflow passage 23d in a high-temperature and high-pressure state, and reaches the inside of the expander 25 from the inlet 25a of the expander 25 through the pipe 32. In the expander 25, the high-temperature and high-pressure working fluid is expanded and depressurized. The generator connected to the expander 25 generates electric power by the pressure energy at this time. Thus, in the Rankine cycle 3 in this heat utilization apparatus, the pressure energy of the working fluid can be recovered as electric power.

The working fluid depressurized in the expander 25 flows out from the outlet 25b and reaches the first head 271 from the radiator inlet 27a of the radiator 27 via the pipe 33 as shown in FIG. Then, the working fluid in the first head 271 circulates in each tube as the heat radiating unit 275 toward the second head 273. The working fluid that has flowed into the first head 271 is in the gas phase.

The working fluid that circulates in the heat radiating unit 275 is cooled by dissipating heat to the air around the radiator 27, that is, the ambient air blown by the electric fan 27c. As a result, as indicated by dot hatching in FIG. 2, a part of the working fluid flowing through the heat radiating portion 275 changes from the gas phase to the liquid phase, and the liquid phase working fluid is cooled. That is, the heat radiating portion 275 can be formed with a capacitor region 275a that radiates heat of a gas-phase working fluid and a subcool region 275b that radiates heat of a liquid-phase working fluid. In the subcool region 275b, the working fluid is supercooled. In a state where the condensation pressure of the working fluid passing through the radiator 27 is minimized, the capacitor region 275a that radiates the gas-phase working fluid is increased in the heat radiating portion 275, and the liquid-phase working fluid is radiated. The subcool region 275b is reduced. The working fluid that has finished radiating heat in the heat radiating portion 275 flows out of the radiator outlet 27b and circulates in the pipe 34. The second pressure sensor 39 detects the pressure of the working fluid flowing through the pipe 34 and transmits the detected value to the controller 7.

The working fluid flowing through the pipe 34 reaches the receiver chamber 29c from the receiver inlet 29a of the gas-liquid separator 29. The working fluid is gas-liquid separated in the liquid receiving chamber 29c. The liquid-phase working fluid flows out from the receiver outlet 29b, and is sucked into the electric pump P1 from the suction port 102 via the pipe 35. Then, the working fluid is discharged from the discharge port 101 to the pipe 31 again.

As described above, the working fluid in the Rankine cycle 3 in a state where the opening degree control of the variable throttle valve 5 is performed so that the flow rate of the working fluid flowing through the pipe 34 becomes maximum is approximately the Mollier shown in FIG. It changes like a diagram. That is, the working fluid discharged by the electric pump P1 changes its pressure and enthalpy in the order of A → B → C → D → D ′ → A. Here, a region between the point D and the point D ′ is the condensation region X1 in the heat dissipation portion 275. A portion between the point D ′ and the point A is a supercooling region Y1 in the heat dissipation portion 275. In the Rankine cycle 3 in this state, the pressure change from the point C to the point D in the working fluid, that is, the pressure energy of the working fluid during decompression and expansion in the expander 25 is large. For this reason, in Rankine cycle 3, it is possible to efficiently recover power.

In this waste heat utilization apparatus, it is possible to adjust the heat radiation amount of the working fluid in the heat radiating section 275, that is, the cooling amount of the working fluid in the heat radiating section 275, based on the target physical quantity for cooling the pressurized air. Specifically, the target physical quantity for cooling the pressurized air refers to the required cooling amount for the pressurized air and the coolable amount of the working fluid for the pressurized air. Hereinafter, the case where the amount of cooling of the working fluid is adjusted based on the required cooling amount and the case where the amount of cooling of the working fluid is adjusted according to the coolable amount will be described separately.

<When adjusting the cooling amount of the working fluid based on the required cooling amount>
When the output request to the engine 9 is large and the accelerator opening of the vehicle increases, the output of the engine 9 detected by the controller 7 increases. Further, as the output demand for the engine 9 increases, the air is compressed to a higher pressure in the turbocharger 11. For this reason, the temperature and pressure of the pressurized air flowing through the pipe 14 rise. Moreover, since the temperature of the pressurized air when flowing into the boiler 23 is high, the temperature of the pressurized air when flowing out from the boiler 23 also rises. As a result, the temperature of the pressurized air flowing through the pipe 15 also increases. For these reasons, in addition to the output of the engine 9, the detection values by the first,

second temperature sensors

19, 22 and the first pressure sensor 21 exceed the threshold values stored in the controller 7. As a result, the controller 7 sets the required cooling amount for the pressurized air to a predetermined value. Here, if the required cooling amount for the pressurized air is large and the cooling amount of the working fluid in the heat radiating unit 275 is insufficient, the controller 7 can satisfy the set required cooling amount. Then, the opening degree of the variable throttle valve 5 is adjusted. As a result, the controller 7 increases the pressure of the working fluid upstream of the variable throttle valve 5 and increases the pressure difference between the working fluid upstream of the variable throttle valve 5 and the working fluid downstream of the variable throttle valve 5.

Specifically, the controller 7 performs control so that the opening degree of the variable throttle valve 5 decreases based on the control map, and the working fluid that circulates from the outlet 25b of the expander 25 to the variable throttle valve 5. Increase the condensation pressure. Here, the controller 7 adjusts the opening degree of the variable throttle valve 5 in accordance with the set required cooling amount for the pressurized air. For this reason, the amount of increase in the condensing pressure of the working fluid is appropriately adjusted in accordance with the set required cooling amount.

Thus, as the pressure of the working fluid rises, as shown in FIG. 4, in the radiator 27, the subcool region 275b occupies about half of the heat radiating portion 275. That is, the subcool region 275b is increased and the capacitor region 275a is decreased in the heat dissipating part 275, compared to the case where the opening degree of the variable throttle valve 5 is maximum.

Thus, when the controller 7 performs control so that the opening degree of the variable throttle valve 5 is decreased, the working fluid in the Rankine cycle 3 changes approximately as shown in the Mollier diagram shown in FIG. That is, the working fluid discharged by the electric pump P1 changes its pressure and enthalpy in the order of A → B → C → E → E ′ → F → A. Here, between the point E and the point E ′ is a condensation region X2 in the heat radiating unit 275 when the opening degree of the variable throttle valve 5 is reduced. And between E 'point and F point becomes the supercooling area | region Y2 in the thermal radiation part 275 when the opening degree of the variable throttle valve 5 reduces.

The condensation pressure in the condensation region X2 and the supercooling region Y2 is higher than the condensation pressure in the condensation region X1 and the supercooling region Y1 shown in FIG. For this reason, in the state where the opening degree of the variable throttle valve 5 is decreased, the cooling amount in the heat radiating unit 275 can be increased as compared with the case where the opening degree of the variable throttle valve 5 is the maximum. Thereby, in the state where the opening degree of the variable throttle valve 5 is decreased, the temperature of the working fluid flowing into the boiler 23 is lowered, and in the boiler 23, the pressurized air can radiate heat to the low-temperature working fluid. It becomes. That is, it becomes possible to satisfy the set cooling request amount. In this way, in this waste heat utilization apparatus, even when the required cooling amount for the pressurized air is large, the working fluid can be cooled so as to satisfy it, and the output of the engine 9 can be improved. Become.

Here, when the opening of the variable throttle valve 5 is reduced, the pressure at the point E is higher than the point D shown in FIG. That is, in the state in which the pressure of the working fluid in the Rankine cycle 3 is increased, as shown in FIG. 5, the pressure change from the point C to the point E in the working fluid becomes small. For this reason, compared with the case where the opening degree of the variable throttle valve 5 is the maximum, the amount of electric power that can be recovered in the Rankine cycle 3 is reduced. In addition, as the condensing pressure of the working fluid is increased in this way, the pressure of the working fluid flowing out from the radiator 27 (pressure at the point F in FIG. 5) is also larger than when the opening of the variable throttle valve 5 is maximum. Become high. However, even in such a case, the pressure of the working fluid decreases from the F point to the A point through the gas-liquid separator 29. For this reason, the pressure of the working fluid when sucked into the suction port 102 of the electric pump P1 is almost the same as that when the opening of the variable throttle valve 5 is maximum. As described above, since the working fluid when sucked into the suction port 102 of the electric pump P1 is unlikely to change depending on the opening of the variable throttle valve 5, in this waste heat utilization device, the casing of the electric pump P1 is made thinner. It is possible to keep the sealing pressure low.

<When adjusting the cooling amount of the working fluid based on the cooling possible amount>
A state in which the temperature of the working fluid is not lowered to such an extent that the pressurized air can be cooled to a predetermined temperature in the heat exchange in the boiler 23, that is, the working fluid has a high temperature and can be cooled with respect to the pressurized air. Is small, each detected value by the third temperature sensor 37 and the second pressure sensor 39 exceeds each threshold value stored in the controller 7. Thereby, the controller 7 sets the cooling possible amount with respect to the pressurized air of a working fluid to a predetermined value. Here, if the cooling amount of the working fluid in the heat radiating unit 275 is insufficient, and the cooling amount for the pressurized air of the working fluid is insufficient, the controller 7 can perform the cooling that is insufficient. It is determined that the amount should be increased to a predetermined size. That is, when the coolable amount of the working fluid with respect to the pressurized air is small, the controller 7 performs control so that the opening degree of the variable throttle valve 5 decreases.

By controlling the controller 7 so that the opening degree of the variable throttle valve 5 is decreased, the condensation pressure in the heat radiating unit 275 increases as in the case where the required cooling amount for the pressurized air is large, and the working fluid is cooled. The amount increases. Thereby, the temperature of the working fluid is lowered to such an extent that the pressurized air can be cooled to a predetermined temperature by heat exchange in the boiler 23. For this reason, it becomes possible to increase the coolable amount of the working fluid with respect to the pressurized air. Thus, in this waste heat utilization apparatus, the pressurized air can be suitably cooled by heat exchange in the boiler 23.

As described above, in this waste heat utilization apparatus, the controller 7 adjusts the opening degree of the pipe 34 by the variable throttle valve 5 and only adjusts the pressure difference of the working fluid upstream and downstream of the variable throttle valve 5. It is possible to adjust the cooling amount of the working fluid in the radiator 27 according to the required cooling amount and the cooling possible amount. For this reason, in this waste heat utilization apparatus, complication of Rankine cycle 3 can be suppressed suitably.
It becomes.

Therefore, according to the waste heat utilization apparatus of the first embodiment, it is possible to achieve power recovery and suitable pressurized air cooling while simplifying the configuration.

Further, in this waste heat utilization apparatus, the working fluid can be caused to flow into the electric pump P1 in the liquid phase state by the gas-liquid separator 29. For this reason, in this waste heat utilization apparatus, in Rankine cycle 5, it becomes possible to circulate a working fluid suitably along piping 31-35, and it becomes possible to perform heat exchange in boiler 23 suitably. Yes.

Furthermore, in this waste heat utilization apparatus, the controller 7 is based on the detection values of the first to

third temperature sensors

19, 22, 37 and the first and

second pressure sensors

21, 39 in addition to the output of the engine 9. It is possible to accurately set the cooling requirement amount and the cooling possible amount.

(Example 2)
The waste heat utilization apparatus of the second embodiment includes a Rankine cycle 3a as shown in FIG. 6 instead of the Rankine cycle 3 in the waste heat utilization apparatus of the first embodiment.

Rankine cycle 3 a further includes a supercooler 43 and a pipe 36 as a working fluid path in addition to the components of Rankine cycle 3. As shown in FIG. 11 described later, the supercooler 43 includes first and

second heads

431 and 433 extending vertically in the vertical direction, and a supercooling unit 435 extending horizontally with respect to the first and

second heads

431 and 433. have. The supercooling unit 435 is also configured by a plurality of tubes communicating with the first head 431 and the second head 433. Further, similarly to the radiator 27, in the supercooling section 435, heat radiation fins are provided between the tubes.

The first head 431 of the supercooler 43 is formed with a supercooler inlet 43a through which a working fluid flows. The second head 433 is formed with a subcooler outlet 43b through which the working fluid flows out from the inside. Further, as shown in FIG. 6, an electric fan 43 c is provided in the vicinity of the supercooler 43. The electric fan 43 c is electrically connected to the controller 7.

In this Rankine cycle 3a, the receiver outlet 29b of the gas-liquid separator 29 and the supercooler inlet 43a of the supercooler 43 are connected by a pipe 35. Further, the subcooler outlet 43b of the supercooler 43 and the suction port 102 of the electric pump P1 are connected by a pipe 36. That is, in the Rankine cycle 3a, the supercooler 43 is provided at a position downstream of the gas-liquid separator 29 and upstream of the electric pump P1 in the direction of circulation of the working fluid.

The controller 7 controls the operation of the electric fan 43c in addition to each control in the waste heat utilization apparatus of the first embodiment. Other configurations of the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the first embodiment, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

In this waste heat utilization device, the working fluid cooled by the radiator 27 can be supercooled by the supercooling part 435 of the supercooler 43. Here, in the Rankine cycle 3a, since the supercooler 43 is located downstream of the gas-liquid separator 29, the working fluid flowing into the supercooling unit 435 becomes a liquid phase. For this reason, the working fluid can be suitably cooled to the supercooled state in the supercooler 43.

Specifically, as shown in FIG. 7, point D ′ and A in a state in which the opening control of the variable throttle valve 5 is performed so that the flow rate of the working fluid flowing through the pipe 34 is maximized. Is larger than the Rankine cycle 3 in the waste heat utilization apparatus of the first embodiment. In other words, in the Rankine cycle 3a, it is possible to secure a larger amount of the supercooling region Y3 than the supercooling region Y1 in the Rankine cycle 3 shown in FIG. In addition, the Rankine cycle 3 and the Rankine cycle 3a are the same about the condensation region X1 of the working fluid.

Further, in this Rankine cycle 3a, the controller 7 performs control so that the opening degree of the variable throttle valve 5 is decreased, so that the working fluid changes approximately as shown in the Mollier diagram shown in FIG. That is, by performing supercooling by the supercooler 43, the working fluid in the Rankine cycle 3a changes its pressure and enthalpy in the order of A → B → C → E → E ′ → F → G → A. . Here, when the working fluid is supercooled by the supercooler 43, a change in the enthalpy of the working fluid occurs between the point G and the point A.

As described above, in the Rankine cycle 3a in this waste heat utilization apparatus, the temperature of the working fluid can be suitably reduced. Thereby, in this waste heat utilization apparatus, generation | occurrence | production of the cavitation in the electric pump P1 can be suppressed suitably. Other operations in the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the first embodiment.

(Example 3)
In the Rankine cycle 3, the waste heat utilization apparatus of the third embodiment is configured by integrating the variable throttle valve 5 and the gas-liquid separator 29 as shown in FIG. Specifically, the variable throttle valve 5 and the gas-liquid separator 29 are integrated by arranging the variable throttle valve 5 in the receiver case 290. The variable throttle valve 5 can adjust the pressure difference of the working fluid between its upstream and downstream by adjusting the opening degree downstream of the receiver inlet 29a.

The second pressure sensor 39 is provided in the receiver case 290. As a result, the second pressure sensor 39 is downstream of the variable throttle valve 5 based on the pressure of the working fluid flowing downstream of the variable throttle valve 5 in the pipe 34, that is, downstream of the receiver inlet 29 a in the pipe 34. To the upstream of the electric pump P <b> 1 is detected, and the detected value is transmitted to the controller 7. Also in this embodiment, the second pressure sensor 39 can be provided in the pipe 35. Other configurations in this embodiment are the same as those of the waste heat utilization apparatus of the first embodiment.

Since the receiver case 290 is formed to have a certain volume, it is possible to secure a space for further providing the variable throttle valve 5 while forming the liquid receiving chamber 29c therein. For this reason, by providing the variable throttle valve 5 in the receiver case 290, the variable throttle valve 5 and the gas-liquid separator 29 can be easily integrated. For this reason, in this waste heat utilization apparatus, the mounting property to a vehicle is improving. Other operations in the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the first embodiment.

Example 4
As shown in FIG. 10, the waste heat utilization apparatus of the fourth embodiment integrates the radiator 27 and the gas-liquid separator 29 in the Rankine cycle 3, and further, the gas-liquid separator 29 and the variable throttle valve 5. Are integrated.

Specifically, the second head 273 and the receiver case 290 of the radiator 27 are disposed adjacent to each other, and the radiator 27 and the receiver case 290 are connected and integrated by a connection path 45. One end side of the connecting path 45 is connected to the radiator outlet 27 b of the second head 273, and the other end side is connected to the receiver inlet 29 a of the receiver case 290 and extends into the receiver case 290. Yes. The connection path 45 constitutes a part of the working fluid path. In addition, since the 2nd head 273 and the receiver case 290 are connected by the connection path 45, the piping 34 is not provided in the Rankine cycle 3 in this waste heat utilization apparatus.

Further, similarly to the waste heat utilization apparatus of the third embodiment, the variable throttle valve 5 and the gas-liquid separator 29 are integrated by arranging the variable throttle valve 5 in the receiver case 290. Thus, in the waste heat utilization apparatus, the radiator 27, the variable throttle valve 5, and the gas-liquid separator 29 are integrated.

The variable throttle valve 5 adjusts the pressure difference of the working fluid between its upstream and downstream by adjusting the opening degree downstream of the receiver inlet 29a. The second pressure sensor 39 is provided in the pipe 35. As a result, the second pressure sensor 39 detects the pressure of the working fluid from the downstream of the variable throttle valve 5 to the upstream of the electric pump P1 based on the pressure of the working fluid flowing downstream from the receiver outlet 29b. The detected value is transmitted to the controller 7. In addition, by providing the second pressure sensor 39 in the receiver case 290, the downstream of the variable throttle valve 5 and the upstream of the electric pump P1 based on the pressure of the working fluid that circulates downstream of the receiver inlet 29a in the connection path 45. The pressure of the working fluid up to may be detected. Other configurations in this embodiment are the same as those of the waste heat utilization apparatus of the first embodiment.

In this waste heat utilization device, the radiator 27, the variable throttle valve 5, and the gas-liquid separator 29 are integrated, so that the mountability to the vehicle is further improved as compared with the waste heat utilization device of the third embodiment. Is possible. Other operations in the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the first embodiment.

(Example 5)
In the Rankine cycle 3a, the waste heat utilization apparatus of the fifth embodiment is configured by integrating the variable throttle valve 5 and the gas-liquid separator 29 as shown in FIG. The integration of the variable throttle valve 5 and the gas-liquid separator 29 is the same as the waste heat utilization apparatus of the third embodiment, and is realized by arranging the variable throttle valve 5 in the receiver case 290. In the waste heat utilization apparatus, the second pressure sensor 39 is provided in the receiver case 290. Note that the second pressure sensor 39 may be provided in the pipe 35 or the pipe 36. Other configurations of the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the second embodiment.

In this waste heat utilization apparatus, the variable throttle valve 5 and the gas-liquid separator 29 are integrated, so that even when the supercooler 43 is provided, the Rankine cycle 3a is preferably prevented from becoming complicated. It becomes possible to do. For this reason, also in this waste heat utilization apparatus, the mounting property to a vehicle is improving. Other operations in the waste heat utilization apparatus are the same as those in the waste heat utilization apparatus of the second embodiment.

(Example 6)
As shown in FIG. 12, in the Rankine cycle 3a, the waste heat utilization apparatus of the sixth embodiment is formed by integrating the radiator 27 and the supercooler 43, and the variable throttle valve 5 and the gas-liquid separator 29. Are formed integrally. Specifically, the radiator 27 and the supercooler 43 are integrated with each other by integrating the first head 271 of the radiator 27 and the second head 433 of the supercooler 43 and the second of the radiator 27. This is realized by integrating the head 273 and the first head 431 of the subcooler 43. The radiator 27 and the supercooler 43 and the gas-liquid separator 29 are connected by the pipe 34 and the pipe 35 as in the waste heat utilization apparatus of the second embodiment.

The integration of the variable throttle valve 5 and the gas-liquid separator 29 in this waste heat utilization device and the arrangement of the second pressure sensor 39 are the same as in the waste heat utilization device of the fifth embodiment. Other configurations of the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the second embodiment.

In this waste heat utilization apparatus, in addition to the integration of the variable throttle valve 5 and the gas-liquid separator 29, the radiator 27 and the supercooler 43 are also integrated. For this reason, in this waste heat utilization apparatus, the mounting property to a vehicle is higher. Other operations in the waste heat utilization apparatus are the same as those in the waste heat utilization apparatus of the second embodiment.

(Example 7)
As shown in FIG. 13, in the Rankine cycle 3a, the waste heat utilization apparatus of Example 7 integrates the supercooler 43 and the gas-liquid separator 29, and further, the gas-liquid separator 29 and the variable throttle valve 5 are integrated. And integrated.

Specifically, the first head 431 and the receiver case 290 of the supercooler 43 are disposed adjacent to each other, and the supercooler 43 and the receiver case 290 are connected and integrated by the connection path 47. . One end side of the connection path 47 is connected to the subcooler inlet 43 a of the first head 431, and the other end is connected to the receiver outlet 29 b of the receiver case 290 and extends into the receiver case 290. ing. The connecting path 47 also constitutes a part of the working fluid path. In addition, since the 1st head 431 and the receiver case 290 are connected by the connection path 47, in this waste heat utilization apparatus, the piping 35 is not provided in the Rankine cycle 3a.

The integration of the variable throttle valve 5 and the gas-liquid separator 29 and the arrangement of the second pressure sensor 39 are the same as in the waste heat utilization apparatus of the fifth embodiment. Thereby, in this waste heat utilization apparatus, the supercooler 43, the variable throttle valve 5, and the gas-liquid separator 29 are integrated. Other configurations of the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the second embodiment.

In this waste heat utilization device, the supercooler 43, the variable throttle valve 5, and the gas-liquid separator 29 are integrated, so that the mountability on the vehicle is high. Other operations in the waste heat utilization apparatus are the same as those in the waste heat utilization apparatus of the second embodiment.

(Example 8)
The waste heat utilization apparatus according to the eighth embodiment includes a Rankine cycle 3b as shown in FIG. 14 instead of the Rankine cycle 3 in the waste heat utilization apparatus according to the first embodiment.

Rankine cycle 3 b has a radiator unit 49 instead of radiator 27 in Rankine cycle 3. In addition, this Rankine cycle 3 b has a pipe 55 instead of the

pipes

34 and 35 in the Rankine cycle 3. The radiator unit 49 corresponds to the radiator in the present invention. The pipe 55 also corresponds to a working fluid path.

As shown in FIG. 15, the radiator unit 49 includes first and

second heads

491 and 493 that extend vertically in the vertical direction, a heat radiating unit 495 and a supercooling unit 497 that extend horizontally in the left and right direction, and a gas-liquid separation unit 499. And an upstream connection path 501 and a downstream connection path 503. The heat radiating part 495 and the supercooling part 497 are configured by a plurality of tubes communicating with the first head 491 and the second head 493, respectively. Although not shown in the figure, fins for heat radiation are provided between the tubes constituting the heat radiation part 495 and between the tubes constituting the supercooling part 497.

The first head 491 is formed with a radiator inlet 49a through which the working fluid flows in and a radiator outlet 49b through which the working fluid flows out from the inside. A first partition wall 49c is formed to be separated from the side. Further, the second head 493 is formed with an upstream side connection port 49d, a downstream side connection port 49e, and a second partition wall 49f that divides the inside into an upstream side and a downstream side of the working fluid.

The gas-liquid separator 499 is provided adjacent to the second head 493. The gas-liquid separator 499 is formed in a cylindrical shape, and a liquid receiving chamber 51 is formed therein. The gas-liquid separation unit 499 is formed with a receiver inflow port 53a through which the working fluid flows in and a receiver outflow port 53b through which the liquid working fluid flows out from the inside.

The gas-liquid separator 499 and the second head 493 are integrally connected by the upstream connection path 501 and the downstream connection path 503. One end of the upstream connection path 501 is connected to the upstream connection port 49 d of the second head 493, and the other end is connected to the receiver inlet 53 a of the gas-liquid separator 499 and extends into the liquid receiving chamber 51. ing. One end side of the downstream side connection path 503 is connected to the receiver outlet 53 b of the gas-liquid separation unit 499, and the other end side is connected to the downstream side connection port 49 e of the second head 493.

Further, a variable throttle valve 5 is provided in the gas-liquid separator 499. Thereby, in this waste heat utilization apparatus, the gas-liquid separation part 499, by extension, the radiator unit 49 and the variable throttle valve 5 are integrated. The variable throttle valve 5 adjusts the pressure difference of the working fluid between its upstream and downstream by adjusting the opening degree downstream of the receiver inlet 53a.

As shown in FIG. 14, an electric fan 49g is provided in the vicinity of the radiator unit 49. The electric fan 49g is electrically connected to the controller 7. Further, in this Rankine cycle 3 b, the outlet 25 b of the expander 25 and the radiator inlet 49 a of the radiator unit 49 are connected by a pipe 33. The radiator outlet 49b of the radiator unit 49 and the suction port 102 of the electric pump P1 are connected by a pipe 55.

The second pressure sensor 39 is provided in the pipe 55. The second pressure sensor 39 detects the pressure of the working fluid from the downstream of the variable throttle valve 5 to the upstream of the electric pump P <b> 1 based on the pressure of the working fluid flowing through the pipe 55, and sends the detected value to the controller 7. To send. The second pressure sensor 39 may be provided in the gas / liquid separator 499. Other configurations of the waste heat utilization apparatus are the same as those of the waste heat utilization apparatus of the first embodiment.

In the Rankine cycle 3b in this waste heat utilization apparatus, as shown in FIG. 15, the working fluid that has passed through the expander 25 flows into the first head 491 of the radiator unit 49 from the radiator inlet 49a. Then, the working fluid flows through the heat radiating unit 495 and reaches the second head 493. At this time, the working fluid flowing through the heat radiating unit 495 is cooled by heat exchange with the surrounding air blown by the electric fan 49g. Here, similarly to the waste heat utilization apparatus of the first embodiment or the like, a capacitor region 495a and a subcool region 495b can be formed in the heat dissipation portion 495. The ratio of the condenser region 495a and the subcool region 495b in the heat radiating unit 495 can be adjusted by adjusting the opening of the variable throttle valve 5 by the controller 7 in accordance with the required cooling amount and the cooling possible amount. It is.

The working fluid that has reached the second head 493 flows into the gas-liquid separator 499 via the upstream connection path 501 and is gas-liquid separated. Then, the liquid working fluid is stored in the liquid receiving chamber 51. In addition, the working fluid in the liquid receiving chamber 51 flows through the downstream connection path 503 and flows into the second head 493 again from the downstream connection port 49e. The working fluid flows through the supercooling unit 497 and reaches the first head 491 while being supercooled by the surrounding air blown by the electric fan 49g. Then, the working fluid flows out from the radiator outlet 49b, flows through the pipe 55, and is sucked into the electric pump P1 through the suction port 102.

Here, in this radiator unit 49, the first partition 49c is formed in the first head 491, and the second partition 49f is formed in the second head 493. For this reason, in the radiator unit 49, the working fluid flowing in from the radiator inlet 49a does not flow out of the radiator outlet 49b without passing through the radiator 495, the gas-liquid separator 499, and the supercooling part 497. Further, the working fluid that has flowed into the second head 493 through the gas-liquid separation unit 499 does not flow through the heat dissipation unit 495 again.

As described above, the radiator unit 49 includes the gas-liquid separator 499 and the supercooling unit 497 in addition to the heat radiator 495, so that the gas-liquid separator 29 and the supercooler 43 are separately provided. Without providing, it is possible to achieve the same effect as the waste heat utilization apparatus of the second embodiment.

Further, in the radiator unit 49, the variable throttle valve 5 is provided in the gas-liquid separation unit 499 in addition to the heat radiation unit 495, the gas-liquid separation unit 499, and the supercooling unit 497 being integrated. For this reason, as compared with the case where the radiator 27, the variable throttle valve 5, the gas-liquid separator 29, and the supercooler 43 are individually provided as in the waste heat utilization apparatus of the second embodiment, the Rankine cycle. It is possible to suppress complication of the configuration of 3b. For this reason, this waste heat utilization apparatus is also highly mounted on a vehicle. Other operations in the waste heat utilization apparatus are the same as those in the waste heat utilization apparatus of the second embodiment.

In the above, the present invention has been described with reference to the first to eighth embodiments. However, the present invention is not limited to the first to eighth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

For example, the controller 7 adjusts the cooling amount of the working fluid based on the required cooling amount or the coolable amount, but instead, the working fluid is based only on either the required cooling amount or the coolable amount. The amount of cooling may be adjusted.

Further, the first temperature sensor 19 and the first pressure sensor 21 may be provided for the first passage 23 f of the boiler 23. In this case, the first temperature sensor 19 can detect the temperature of the pressurized air flowing through the first passage 23f. Further, the first pressure sensor 21 can detect the pressure of the pressurized air flowing through the first passage 23f.

Further, the controller 7 is configured to set the required cooling amount based on any one of the output of the engine 9, the detected value by the first and

second temperature sensors

19 and 22, and the detected value by the first pressure sensor 21. You may do it. Furthermore, the controller 7 may be configured to set the required cooling amount based on a detection value arbitrarily selected from these.

Similarly, the controller 7 may be configured to set the coolable amount based on either the detection value by the third temperature sensor 37 or the detection value by the second pressure sensor 39.

Further, the drive system 1 may be configured such that a part of the exhaust discharged from the engine 9 is recirculated to the engine 9 as recirculated exhaust, and heat may be exchanged between the recirculated exhaust and the working fluid in the boiler 23.

Further, in the radiator unit 49 in the eighth embodiment, the heat radiating part 495 and the supercooling part 497 are formed with the same size, but not limited to this, the heat radiating part 495 and the supercooling part 497 are different in size. It may be formed.

The present invention can be used not only for waste heat utilization devices mounted on transport vehicles such as trucks and buses and vehicles such as passenger cars, but also for stationary waste heat utilization devices.

DESCRIPTION OF SYMBOLS 1 ...

Drive system

3, 3a, 3b ... Rankine cycle 5 ... Variable throttle valve (differential pressure adjustment means)
7: Controller (setting means, control means)
14, 15 ... Piping (heat medium flow path)
19 ... 1st temperature sensor (1st temperature detection means)
21 ... 1st pressure sensor (1st pressure detection means)
22 ... 2nd temperature sensor (2nd temperature detection means)
DESCRIPTION OF SYMBOLS 23 ... Boiler 25 ... Expander 27 ... Radiator 27a ... Radiator inlet 27b ... Radiator outlet 29 ... Gas-liquid separator 29a ... Receiver inlet 29b ... Receiver outlet 29c ... Reservoir 31-36 ... Piping (operation) Fluid flow path)
37 ... Third temperature sensor (third temperature detecting means)
39: Second pressure sensor (second pressure detecting means)
43 ... Supercooler 49 ... Heatsink unit (heatsink)
49a ... Radiator inlet 49b ... Radiator outlet 55 ... Piping (working fluid flow path)
290 ... Receiver case 275 ... Heat radiation part 495 ... Heat radiation part 497 ... Supercooling part 499 ... Gas-liquid separation part P1 ... Electric pump (pump)

Claims

In a waste heat utilization device equipped with a Rankine cycle that circulates a working fluid used in a drive system,
The drive system includes an internal combustion engine, and a heat medium flow path that is connected to the internal combustion engine and through which a heat medium for the internal combustion engine can flow.
The Rankine cycle includes a working fluid flow path through which the working fluid can flow.
A pump for circulating the working fluid along the working fluid flow path;
A boiler that is connected downstream of the pump by the working fluid flow path and connected to the heat medium flow path, exchanges heat between the working fluid and the heat medium, and cools the heat medium;
An expander connected by the working fluid flow path downstream of the boiler and expanding the working fluid;
A radiator that is connected by the working fluid flow path downstream of the expander and upstream of the pump and that radiates heat of the working fluid by a cooling medium;
The radiator includes a radiator inlet that allows the working fluid to flow therein, a radiator outlet that allows the working fluid to flow out from the interior, and between the radiator inlet and the radiator outlet. A heat dissipating part located,
Between the radiator inlet and the pump, there is provided a differential pressure adjusting means capable of adjusting the pressure difference of the working fluid between its upstream and downstream,
Setting means for setting a target physical quantity for cooling the heat medium;
Control means for controlling the differential pressure adjusting means so that the pressure of the working fluid upstream of the differential pressure adjusting means increases when the heat dissipation amount of the working fluid in the heat radiating portion is insufficient based on the target physical quantity. And a waste heat utilization device.
The Rankine cycle has a gas-liquid separator that is connected by the working fluid flow path downstream of the radiator and upstream of the pump, and capable of gas-liquid separation of the working fluid,
The waste heat utilization apparatus according to claim 1, wherein the differential pressure adjusting means is provided integrally with the working fluid flow path between the radiator and the gas-liquid separator or with the gas-liquid separator.
The gas-liquid separator has a receiver case in which a receiver inlet and a receiver outlet are formed,
A liquid receiving chamber for storing the working fluid in a liquid state is formed in the receiver case,
The working fluid flow path is connected to the receiver inlet and the receiver outlet, respectively.
The waste heat utilization apparatus according to claim 2, wherein the differential pressure adjusting means is provided in the receiver case.
The Rankine cycle has a supercooler connected by the working fluid flow path downstream of the radiator and upstream of the pump, and capable of supercooling the working fluid,
The waste heat utilization apparatus according to claim 1 or 2, wherein the differential pressure adjusting means is provided in the working fluid flow path between the radiator and the supercooler.
The Rankine cycle has a supercooler connected by the working fluid flow path downstream of the gas-liquid separator and upstream of the pump, and capable of supercooling the working fluid,
The waste heat utilization apparatus according to claim 2 or 3, wherein the differential pressure adjusting means is provided in the working fluid flow path between the radiator and the gas-liquid separator.
The target physical quantity is a cooling request quantity required by the drive system,
The said control means controls the said differential pressure | voltage adjustment means so that the pressure of the said working fluid upstream of the said differential pressure | voltage adjustment means may increase, when the said cooling required amount is large. Waste heat utilization equipment.
The waste heat utilization apparatus according to claim 6, wherein the setting means sets the required cooling amount based on an output of the internal combustion engine.
The internal combustion engine is a vehicle engine;
The waste heat utilization apparatus according to claim 7, wherein the setting means sets the required cooling amount based on an accelerator opening degree of the vehicle or the accelerator opening degree and a rotational speed of the vehicle engine.
The setting means includes first temperature detection means provided in the heat medium flow path or the boiler and capable of detecting the temperature of the heat medium flowing through the boiler,
The waste heat utilization apparatus according to claim 6, wherein the setting unit sets the required cooling amount based on a detection value detected by the first temperature detection unit.
The setting means includes second temperature detection means provided in the heat medium flow path and capable of detecting the temperature of the heat medium flowing out of the boiler,
The waste heat utilization apparatus according to claim 6, wherein the setting unit sets the cooling request amount based on a detection value detected by the second temperature detection unit.
The setting means includes first pressure detection means provided in the heat medium flow path or the boiler and capable of detecting the pressure of the heat medium flowing through the boiler,
The waste heat utilization apparatus according to claim 6, wherein the setting unit sets the required cooling amount based on a detection value detected by the first pressure detection unit.
The target physical quantity is a chillable amount by which the working fluid can cool the heat medium,
The said control means controls the said differential pressure | voltage adjustment means so that the pressure of the said working fluid upstream of the said differential pressure | voltage adjustment means may increase, when the said cooling possible amount is small. Waste heat utilization equipment.
The waste heat utilization apparatus according to claim 12, wherein the setting means sets the coolable amount based on a temperature of the working fluid from the radiator outlet to the inlet of the working fluid in the boiler.
The setting means includes third temperature detection means provided in the Rankine cycle and capable of detecting the temperature of the working fluid flowing into the boiler.
The waste heat utilization apparatus according to claim 13, wherein the setting means sets the coolable amount based on a detection value detected by the third temperature detection means.
The setting means includes second pressure detection means provided in the Rankine cycle and capable of detecting the pressure of the working fluid from the downstream of the differential pressure adjusting means to the upstream of the pump.
The waste heat utilization apparatus according to claim 12, wherein the setting means sets the coolable amount based on a detection value detected by the second pressure detection means.