JP2010164003A - Exhaust heat regeneration system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an exhaust heat regeneration system having reduced cost, reduced size, and improved cycle efficiency. <P>SOLUTION: The exhaust heat regeneration system 1 includes an evaporator 2, an expander 3, a condenser 4, and a pump 5. The expander 3 expands evaporated refrigerant to generate driving force. The pump 5 forcibly feeds the condensed refrigerant. The evaporator 2 evaporates the refrigerant from the pump 5 with heating, and feeds it to the expander 3. The condenser 4 has a condenser high temperature pipe in which the refrigerant expanded by the expander 3 flows, and a condenser low temperature pipe in which the refrigerant flows to be fed from the pump 5 to the evaporator 2. The condenser 4 makes heat exchange between the refrigerant flowing in the condenser high temperature pipe and the refrigerant flowing in the condenser low temperature pipe to condense the refrigerant in the condenser high temperature pipe, and feeds only the refrigerant in a liquid condition, out of the refrigerant in the condenser high temperature pipe, to the pump 5. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an exhaust heat regeneration system that regenerates exhaust heat from, for example, an automobile engine or exhaust gas.

  2. Description of the Related Art Conventionally, there is known an exhaust heat regeneration system that regenerates exhaust heat from an engine, exhaust gas, or the like as power by using a Rankine cycle in order to improve the operation efficiency of equipment such as an automobile.

  A conventional exhaust heat regeneration system includes an evaporator that heats and evaporates the refrigerant with the exhaust heat of the engine, an expander that expands the evaporated refrigerant to generate a driving force, and condenses the expanded refrigerant to form a liquid A condenser to be in a state, and a pump for circulating the refrigerant in a liquid state by pumping it to the evaporator. The driving force generated by the expander is used, for example, for driving the engine.

  Conventionally, in order to further improve the operation efficiency, heat is exchanged between the refrigerant flowing through the refrigerant pipe connecting the expander and the condenser and the refrigerant flowing through the refrigerant pipe connecting the pump and the evaporator. An exhaust heat regeneration system provided with an exchanger has been proposed. Thereby, the heat of the refrigerant sent from the expander to the condenser is used for heating the refrigerant sent from the pump to the evaporator. In this way, the cycle efficiency is further improved (see, for example, Patent Document 1).

JP 58-12819 A

  However, the conventional exhaust heat regeneration system requires a heat exchanger in addition to an evaporator, an expander, a condenser and a pump. Therefore, the number of parts increases and the cost increases significantly. In addition, since it is necessary to secure a space for installing the heat exchanger, the system cannot be installed when the installation space is limited.

  Further, since the refrigerant from the expander is cooled by the heat exchanger before being sent to the condenser, only a part of the refrigerant may be condensed and liquefied on the upstream side of the condenser. In this case, gas and liquid coexist in the refrigerant pipe connecting the heat exchanger and the condenser, and the fluidity of the refrigerant deteriorates due to an increase in gravity and pressure loss, thereby improving cycle efficiency. Will not be able to.

  The present invention has been made in order to solve the above-described problems, and is capable of reducing the cost, reducing the size, and improving the cycle efficiency. The purpose is to obtain a system.

  The exhaust heat regeneration system according to the present invention includes an expander that expands the evaporated working fluid to generate a driving force, a pump that pumps the condensed working fluid, and evaporates the working fluid from the pump by heating to expand the expansion. A condenser high-temperature pipe and a condenser high-temperature pipe through which the working fluid expanded by the expander flows, and a condenser low-temperature pipe through which the working fluid sent from the pump to the evaporator flows. By exchanging heat between the working fluids flowing in each of the low-temperature pipes, the working fluid in the condenser high-temperature pipe is condensed, and only the working fluid in the liquid state among the working fluid in the condenser high-temperature pipe is sent to the pump. It has a condenser to send.

  In the exhaust heat regeneration system according to the present invention, heat is exchanged between the working fluid that flows through the condenser high-temperature pipe in the condenser and the working fluid that flows through the condenser low-temperature pipe, and the working fluid in the condenser high-temperature pipe Of these, only the working fluid in a liquid state is sent from the condenser to the pump, so heat exchange between the working fluid from each of the expander and the pump can be performed by the condenser. Thereby, the cycle efficiency of the exhaust heat regeneration system can be improved. Further, heat exchange can be performed between the working fluid from the expander and the working fluid from the pump without providing a heat exchanger separately from the condenser. Therefore, an increase in the number of components such as a heat exchanger can be suppressed, and the cost can be reduced and the exhaust heat regeneration system 1 as a whole can be reduced in size.

BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which shows the waste heat regeneration system by Embodiment 1 of this invention. It is a block diagram which shows the condenser of FIG. It is a Mollier diagram which shows the thermodynamic cycle of the waste heat regeneration system of FIG. It is a block diagram which shows the condenser of the waste heat regeneration system by Embodiment 2 of this invention. It is a block diagram which shows the condenser of the waste heat regeneration system by Embodiment 3 of this invention. It is a block diagram which shows the condenser of the waste heat regeneration system by Embodiment 4 of this invention. It is a front view which shows the condenser of the waste heat regeneration system by Embodiment 5 of this invention. It is a top view which shows the condenser of FIG.

Embodiment 1 FIG.
1 is a block diagram showing an exhaust heat regeneration system according to Embodiment 1 of the present invention. FIG. 1 shows an exhaust heat regeneration system that uses exhaust heat from an automobile engine. In the figure, the exhaust heat regeneration system 1 includes an evaporator 2, an expander (steam turbine) 3, a condenser 4, and a pump 5. The refrigerant that is the working fluid of the exhaust heat regeneration system is circulated between the evaporator 2, the expander 3, the condenser 4, and the pump 5. As the refrigerant, for example, refrigerant R134a or the like is used.

  Connected between the evaporator 2 and the expander 3 is a first refrigerant pipe 6 that guides the refrigerant from the evaporator 2 to the expander 3. Connected between the expander 3 and the condenser 4 is a second refrigerant pipe 7 that guides the refrigerant from the expander 3 to the condenser 4. Between the condenser 4 and the pump 5, a third refrigerant pipe 8 that leads the refrigerant from the condenser 4 to the pump 5 and a fourth refrigerant pipe 9 that leads the refrigerant from the pump 5 to the condenser 4 are connected. Yes. A fifth refrigerant pipe 10 that guides the refrigerant from the condenser 4 to the evaporator 2 is connected between the condenser 4 and the evaporator 2.

  Circulating water for cooling the engine 11 flows through the engine 11. Circulating water is circulated between the engine 11 and the evaporator 2. Connected between the engine 11 and the evaporator 2 are a high-temperature water pipe 12 that guides the circulating water from the engine 11 to the evaporator 2 and a low-temperature water pipe 13 that guides the circulating water from the evaporator 2 to the engine 11.

  The engine 11 generates a driving force for the automobile. The circulating water is heated by the heat generated by the engine 11 and sent to the evaporator 2 through the high temperature water pipe 12. The temperature of the circulating water is about 90 to 100 ° C. due to heating by the engine 11.

  The evaporator 2 has an evaporator water pipe through which circulating water flows and an evaporator refrigerant pipe through which refrigerant flows. A high temperature water pipe 12 is connected to the inlet of the evaporator water pipe, and a low temperature water pipe 13 is connected to the outlet of the evaporator water pipe. A fifth refrigerant pipe 10 is connected to the inlet of the evaporator refrigerant pipe, and a first refrigerant pipe 6 is connected to the outlet of the evaporator refrigerant pipe.

  In the evaporator 2, heat exchange is performed between the circulating water that flows through the evaporator water pipe and the refrigerant that flows through the evaporator refrigerant pipe. Thereby, circulating water is cooled and a refrigerant is heated.

  The circulating water cooled by the evaporator 2 is sent to the engine 11 through the low temperature water pipe 13. The refrigerant heated by the evaporator 2 evaporates into high-temperature and high-pressure steam. The temperature of the refrigerant | coolant at this time is about 90 degreeC. The refrigerant that has become vapor in the evaporator 2 is sent to the expander 3 through the first refrigerant pipe 6.

  The expander 3 generates a driving force by expanding the refrigerant from the evaporator 2 (that is, the refrigerant that has become vapor). The temperature of the refrigerant becomes approximately 60 ° C. due to the expansion of the refrigerant. The driving force generated by the expander 3 is used as power for driving the engine 11 or power generation by a generator, for example. The refrigerant expanded by the expander 3 is sent to the condenser 4 through the second refrigerant pipe 7.

  The condenser 4 condenses the refrigerant expanded by the expander 3 into a liquid state. The refrigerant in the liquid state is sent to the pump 5 through the third refrigerant pipe 8. The temperature of the refrigerant becomes about 30 ° C. when the refrigerant is cooled and condensed by the condenser 4.

  The pump 5 pumps the refrigerant that has become a liquid state in the condenser 4. The refrigerant is sent to the evaporator 2 through the fourth refrigerant pipe 9, the condenser 4 and the fifth refrigerant pipe 10 in this order. The refrigerant is circulated among the evaporator 2, the expander 3, the condenser 4 and the pump 5 by the power of the pump 5.

  The condenser 4 gives heat held by the refrigerant from the expander 3 to the refrigerant from the pump 5. That is, the condenser 4 forcibly exchanges heat between the refrigerant from the expander 3 and the refrigerant from the pump 5. The temperature of the refrigerant sent from the pump 5 to the evaporator 2 becomes about 50 ° C. as the refrigerant flows through the condenser 4.

  FIG. 2 is a block diagram showing the condenser 4 of FIG. In the figure, the condenser 4 includes a condenser high-temperature pipe 14 through which the refrigerant expanded by the expander 3 flows, a condenser low-temperature pipe 15 through which the refrigerant sent from the pump 5 to the evaporator 2 flows, a condenser high-temperature pipe 14 and A common fin (thermal conductor) 16 that contacts each of the condenser low-temperature pipes 15, and a fan (fluid device) 17 that generates an air flow (flow of heat transfer fluid) toward the condenser high-temperature pipe 14. have.

  A second refrigerant pipe 7 is connected to the inlet of the condenser high-temperature pipe 14, and a third refrigerant pipe 8 is connected to the outlet of the condenser high-temperature pipe 14 via a liquid receiver (not shown). A fourth refrigerant pipe 9 is connected to the inlet of the condenser low-temperature pipe 15, and a fifth refrigerant pipe 10 is connected to the outlet of the condenser low-temperature pipe 15.

  The condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 are arranged at intervals in the direction of air flow by the fan 17. The condenser low-temperature pipe 15 is arranged at a position farther from the fan 17 than the condenser high-temperature pipe 14. That is, the condenser low-temperature pipe 15 is arranged downstream of the air flow by the fan 17 with respect to the condenser high-temperature pipe 14.

  The heat of the refrigerant in the condenser high-temperature pipe 14 is transmitted to the refrigerant in the condenser low-temperature pipe 15 through the air sent by the fan 17 and the fins 16. Thereby, the refrigerant in the condenser high-temperature pipe 14 is cooled, and the refrigerant in the condenser low-temperature pipe 15 is heated. The refrigerant cooled in the condenser high-temperature pipe 14 is condensed to be in a liquid state.

  The condenser high-temperature pipe 14 is connected to the top of the receiver, and the third refrigerant pipe 8 is connected to the bottom of the receiver. Accordingly, the refrigerant that has become liquid in the condenser high-temperature pipe 14 is stored in the liquid receiver. Thereby, only the refrigerant in a liquid state among the refrigerant in the condenser high-temperature pipe 14 is sent to the third refrigerant pipe 8.

  The condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 are in contact with a plurality of fins 16 arranged at intervals. Each fin 16 is a metal plate-like member. The thickness of each fin 16 is smaller than the diameter of each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Each fin 16 is arranged along the direction of air flow by the fan 17. Further, each fin 16 is integrated with the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15.

  FIG. 3 is a Mollier diagram showing the thermodynamic cycle of the exhaust heat regeneration system of FIG. 1. As shown in the figure, the thermodynamic cycle of the exhaust heat regeneration system 1 is a Rankine cycle. 3, point a is the state of the refrigerant at the inlet of the pump 5, point b is the outlet of the pump 5, point c is the outlet of the evaporator 2, and point d is the outlet of the expander 3.

  That is, the refrigerant is sent from the condenser 4 to the pump 5 in a liquid state at point a. Thereafter, the refrigerant is boosted by receiving power from the pump 5 and enters a liquid state at point b. Thereafter, the refrigerant is heated at a constant pressure while being sent in the order of the condenser 4 and the evaporator 2, and becomes vapor at point c (gas state) at the outlet of the evaporator 2. Thereafter, the refrigerant is adiabatically expanded by the expander 3 to become steam at point d, and is sent to the condenser 4. Thereafter, the refrigerant is cooled at a constant pressure by the condenser 4 and returns to the liquid state at point a.

  Next, the cycle efficiency η of the Rankine cycle is expressed by Expression (1), where Ha, Hb, Hc, and Hd are refrigerant enthalpies at points a, b, c, and d, respectively.

  η = (Hc−Hd) / (Hc−Hb) (1)

  Here, in the condenser 4, a part of the heat (Hd−Hd ′) of the refrigerant expanded by the expander 3 is given to the refrigerant discharged from the pump 5 as recovered heat (Hb′−Hb). That is, part of the heat of the refrigerant expanded by the expander 3 is recovered and used for heating the liquid refrigerant from the pump 5. Therefore, the cycle efficiency η ′ of the exhaust heat regeneration system 1 is expressed by Expression (2).

η ′ = (Hc−Hd) / {(Hc−Hb) − (Hb−Hb ′)}
= (Hc−Hd) / (Hc−Hb ′)> η (2)

  It can be seen from the equation (2) that the cycle efficiency η ′ of the exhaust heat regeneration system 1 is improved.

  In such an exhaust heat regeneration system 1, heat exchange is performed between the refrigerant flowing through the condenser high-temperature pipe 14 in the condenser 4 and the refrigerant flowing through the condenser low-temperature pipe 15. Of the refrigerants, only the refrigerant in a liquid state is sent from the condenser 4 to the pump 5, so heat exchange between the refrigerants from the expander 3 and the pump 5 can be performed by the condenser 4. Thereby, the improvement of the cycle efficiency of the exhaust heat regeneration system 1 can be aimed at. Further, heat exchange can be performed between the refrigerant from the expander 3 and the refrigerant from the pump 5 without providing a heat exchanger separately from the condenser. Therefore, an increase in the number of components such as a heat exchanger can be suppressed, and the cost can be reduced and the exhaust heat regeneration system 1 as a whole can be reduced in size.

  Further, since the fin 16 is in contact with each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15, the heat conduction of each fin 16 causes a refrigerant between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Heat exchange can be performed. Therefore, the amount of heat exchange in the condenser 4 can be increased, and the cycle efficiency of the exhaust heat regeneration system 1 can be further improved.

  Further, since the condenser low-temperature pipe 15 is arranged on the downstream side of the air flow from the condenser high-temperature pipe 14, the heat of the refrigerant in the condenser high-temperature pipe 14 is transferred to the refrigerant in the condenser low-temperature pipe 15. Can be given efficiently. Therefore, the amount of heat exchange in the condenser 4 can be further increased, and the cycle efficiency of the exhaust heat regeneration system 1 can be further improved.

Embodiment 2. FIG.
In the first embodiment, only the plate-like fins 16 are in contact with the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 as heat conductors, but the block-like member is brought into contact with the fins 16 as a heat conductor. May be.

  That is, FIG. 4 is a configuration diagram showing the condenser 4 of the exhaust heat regeneration system according to the second embodiment of the present invention. In the figure, a plurality of fins 16 and a block-shaped member 21 are in contact with each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 as heat conductors. The material which comprises each fin 16 and the block-shaped member 21 is made into the metal (for example, copper, aluminum alloy, etc.) with high heat conductivity.

  The dimensions of the block-like member 21 (the thickness of the block-like member 21) in the length direction of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 are the pipe diameters of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 respectively. Is bigger than. Therefore, the thickness of the block-shaped member 21 is larger than the thickness of the fin 16. Each fin 16 and the block-shaped member 21 are integrated with the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Other configurations are the same as those in the first embodiment.

  In such an exhaust heat regeneration system, the block-like member 21 having a thickness larger than the pipe diameters of the pipes 14 and 15 contacts the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 together with the fins 16 as a heat conductor. Therefore, the amount of heat transferred from the condenser high temperature pipe 14 to the condenser low temperature pipe 15 can be increased. Therefore, the amount of heat exchange in the condenser 4 can be further increased, and the cycle efficiency of the exhaust heat regeneration system 1 can be further improved.

  In the above example, each of the fins 16 and the block-shaped member 21 is in contact with the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15, but the block-shaped member is connected to the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Only 21 may be contacted.

Embodiment 3 FIG.
In the first embodiment, the common fin 16 is in contact with each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15, but separate fins are in contact with each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. You may let them.

  That is, FIG. 5 is a block diagram showing the condenser 4 of the exhaust heat regeneration system according to Embodiment 3 of the present invention. In the figure, a plurality of high temperature side fins 31 are in contact with the condenser high temperature pipe 14, and a plurality of low temperature side fins 32 are in contact with the condenser low temperature pipe 15. The high temperature side fin 31 and the low temperature side fin 32 are arranged apart from each other. The high temperature side fins 31 and the low temperature side fins 32 are metal plate-like members, and are arranged along the direction of air flow by the fan 17. In addition, the high temperature side fins 31 are arranged at intervals, and the low temperature side fins 32 are arranged at intervals. Other configurations are the same as those in the first embodiment.

  As described above, even if the high temperature side fins 31 in contact with the condenser high temperature pipe 14 and the low temperature side fins 32 in contact with the condenser low temperature pipe 15 are arranged apart from each other, The heat of the refrigerant in the condenser high-temperature pipe 14 can be transferred to the refrigerant in the condenser low-temperature pipe 15, and heat exchange can be performed in the condenser 4 without providing a separate heat exchanger. Thereby, the cycle efficiency of the exhaust heat regeneration system 1 can be improved, and the cost can be reduced and the size can be reduced.

Embodiment 4 FIG.
In the third embodiment, the plurality of high temperature side fins 31 are in contact with the condenser high temperature pipe 14 and the plurality of low temperature side fins 32 are in contact with the condenser low temperature pipe 15, but the low temperature side fins 32 may be omitted. .

  That is, FIG. 6 is a block diagram showing the condenser 4 of the exhaust heat regeneration system according to Embodiment 4 of the present invention. In the figure, the low temperature side fin 32 is not provided in the condenser low temperature pipe 15, and the outer peripheral surface of the condenser low temperature pipe 15 is exposed to the outside air as it is. The condenser low-temperature pipe 15 is arranged away from each high-temperature side fin 31. Other configurations are the same as those of the third embodiment.

  Thus, even if there is no low temperature side fin 32 in contact with the condenser low temperature pipe 15, the heat of the refrigerant in the condenser high temperature pipe 14 is transferred to the refrigerant in the condenser low temperature pipe 15 by the air flow by the fan 17. The heat exchange can be performed in the condenser 4 without providing a separate heat exchanger. Thereby, the cycle efficiency of the exhaust heat regeneration system 1 can be improved, and the cost can be reduced and the size can be reduced.

  In the above example, the fin (high temperature side fin 31) is in contact with only the condenser high temperature pipe 14 out of the condenser high temperature pipe 14 and the condenser low temperature pipe 15, but the condenser high temperature pipe 14 and the condenser. Of the low-temperature pipe 15, the fin (low-temperature side fin 32) may be brought into contact only with the condenser low-temperature pipe 15. Further, neither the condenser high-temperature pipe 14 nor the condenser low-temperature pipe 15 may have fins. Even in this case, the heat of the refrigerant in the condenser high-temperature pipe 14 can be transferred to the refrigerant in the condenser low-temperature pipe 15 by the air flow by the fan 17.

Embodiment 5 FIG.
In the first embodiment, the interval between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is equal at any position of each pipe 14, 15. May be made different according to the positions of the pipes 14 and 15.

  That is, FIG. 7 is a front view showing the condenser 4 of the exhaust heat regeneration system according to the fifth embodiment of the present invention. FIG. 8 is a top view showing the condenser 4 of FIG. In the figure, an inlet portion 14 a of the condenser high-temperature pipe 14 and an outlet portion 15 b of the condenser low-temperature pipe 15 are arranged in the upper part of the condenser 4. In the lower part of the condenser 4, an outlet portion 14 b of the condenser high-temperature pipe 14 is arranged. In the middle part of the condenser 4, an inlet portion 15 a of the condenser low-temperature pipe 15 is arranged.

  The refrigerant from the expander 3 flows into the condenser high-temperature pipe 14 from the inlet portion 14 a of the condenser high-temperature pipe 14. The refrigerant that has passed through the condenser high-temperature pipe 14 flows out from the outlet portion 14 b of the condenser high-temperature pipe 14. The refrigerant from the pump 5 flows into the condenser low-temperature pipe 15 from the inlet portion 15 a of the condenser low-temperature pipe 15. The refrigerant that has passed through the condenser low-temperature pipe 15 flows out from the outlet portion 15 b of the condenser low-temperature pipe 15.

  The interval between the condenser hot pipe 14 and the condenser cold pipe 15 is narrower at the position of the inlet 14 a of the condenser hot pipe 14 than at the outlet 14 b of the condenser hot pipe 14. That is, the space between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is narrower in the upper part of the condenser 4 than in the lower part of the condenser 4 and is narrowest in the upper part of the condenser 4. In this example, the interval between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is equal within a predetermined length range from the inlet portion 14 a to the condenser high-temperature pipe 14.

  Each fin 16 is in contact with each of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Further, each fin 16 is disposed over the entire length of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. Therefore, the length of the fin 16 located between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is shorter in the upper part of the condenser 4 than in the lower part of the condenser 4. That is, the length of the fin 16 located between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is closer to the inlet 14a of the condenser high-temperature pipe 14 than the position closer to the outlet 14b of the condenser high-temperature pipe 14. The closer position is shorter. Other configurations are the same as those in the first embodiment.

  In such an exhaust heat regeneration system 1, the interval between the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15 is narrower at the position of the inlet 14a than the position of the outlet 14b of the condenser high-temperature pipe 14, Since the fin 16 is disposed at least at the inlet 14a of the condenser hot pipe 14, the heat from the condenser hot pipe 14 to the condenser cold pipe 15 is transferred to the fin 16 at the position of the inlet 14a of the condenser hot pipe 14. It can be easier to communicate through. Since the temperature of the refrigerant is higher at the inlet 14a of the condenser hot pipe 14 than at the outlet 14b of the condenser hot pipe 14, such a configuration allows the condenser hot pipe 14 and the condenser to be condensed. It is possible to improve the efficiency of heat exchange between the refrigerants flowing through the low temperature pipes 15. Accordingly, the length of the condenser low-temperature pipe 15 can be shortened, and the overall size of the condenser 4 can be reduced.

  In the above example, the fins 16 are disposed over the entire lengths of the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15, but a predetermined portion (condensation) of the condenser high-temperature pipe 14 including the inlet portion 14a. The fin 16 may be brought into contact with the condenser low-temperature pipe 15 only in a part of the condenser high-temperature pipe 14. Further, the fin 16 may be used as the block-shaped member 21.

  Further, in each of the above embodiments, air flowing by the fan 17 is used as a heat transfer fluid for exchanging heat between the refrigerant in the condenser high-temperature pipe 14 and the condenser low-temperature pipe 15. However, for example, a liquid such as water flowing by a flowing water pump (fluid device) may be used as the heat transfer fluid. For example, when the exhaust heat regeneration system is mounted on a vehicle such as an automobile, heat can be exchanged in the condenser 4 by the air flow caused by the traveling of the vehicle, so the fan 17 is not necessary. .

  Moreover, in each said embodiment, although the exhaust heat of the engine 11 is collect | recovered, you may make it collect | recover the exhaust heat of the exhaust gas of a motor vehicle.

  1 Exhaust heat regeneration system, 2 evaporator, 3 expander (steam turbine), 4 condenser, 5 pump, 14 condenser high temperature piping, 15 condenser low temperature piping, 16 fin (thermal conductor), 17 fan, 21 block Member (thermal conductor).

Claims (6)

An expander that expands the evaporated working fluid to generate a driving force;
A pump that pumps the condensed working fluid,
An evaporator that evaporates the working fluid from the pump by heating and sends it to the expander, a condenser high-temperature pipe through which the working fluid expanded by the expander flows, and a working fluid that is sent from the pump to the evaporator A condenser low-temperature pipe flowing through the condenser, and the working fluid in the condenser high-temperature pipe is condensed by exchanging heat between the working fluid flowing through the condenser high-temperature pipe and the condenser low-temperature pipe. A waste heat regenerative system comprising a condenser for sending only the working fluid in a liquid state to the pump among the working fluid in the high-temperature pipe.   The exhaust heat regeneration system according to claim 1, wherein the condenser further includes a common heat conductor that is in contact with the condenser high-temperature pipe and the condenser low-temperature pipe.   The exhaust heat regeneration system according to claim 2, wherein the heat conductor is a plate-like fin. The heat conductor is a block-shaped member,
The exhaust heat regeneration system according to claim 2, wherein a thickness of the block-shaped member is larger than a pipe diameter of the condenser high-temperature pipe and the condenser low-temperature pipe.   The exhaust heat regeneration system according to any one of claims 2 to 4, wherein the heat conductor is in contact with an inlet portion of the condenser high-temperature pipe and the condenser low-temperature pipe. The condenser further includes a fluid device that generates a flow of heat transfer fluid,
The exhaust according to any one of claims 1 to 5, wherein the low-temperature pipe in the condenser is arranged downstream of the flow of the heat transfer fluid with respect to the high-temperature pipe in the condenser. Thermal regeneration system.

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