US20070074515A1 - Waste energy recovery method and waste energy recovery system - Google Patents
Waste energy recovery method and waste energy recovery system Download PDFInfo
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- US20070074515A1 US20070074515A1 US10/595,458 US59545805A US2007074515A1 US 20070074515 A1 US20070074515 A1 US 20070074515A1 US 59545805 A US59545805 A US 59545805A US 2007074515 A1 US2007074515 A1 US 2007074515A1
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- engine
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- boiling medium
- turbine
- cooling
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K15/00—Adaptations of plants for special use
- F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/22—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point
- F01P2003/2278—Heat pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/02—Intercooler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/04—Lubricant cooler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0437—Liquid cooled heat exchangers
- F02B29/0443—Layout of the coolant or refrigerant circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
An oil cooler for cooling hydraulic oil that has increased in temperature due to energy loss in a hydraulic circuit a radiator for cooling engine cooling water that has increased in temperature as a result of cooling an engine and an ATAAC for cooling engine intake air that has increased in temperature as a result of being compressed by a turbocharger, are provided with heat pipes for vaporizing low-boiling medium by absorbing heat from the oil cooler the radiator and the ATAAC. A power recovery turbine is rotated by energy provided by vaporized low-boiling medium is provided for the engine. A low-boiling medium circuit is provided so as to drive the turbine by feeding the low-boiling medium that has been vaporized by waste heat energy. The low-boiling medium circuit includes the heat pipes of the oil cooler the radiator, and the ATAAC, as well as the turbine.
Description
- This is a U.S. National Phase Application under 35 U.S.C. §371 of International Patent Application No. PCT/JP2005/006628, filed Apr. 5, 2005, and claims the benefit of Japanese Patent Application No. 2004-273991, filed Sep. 21, 2004, both of which are incorporated by reference herein. The International Application has not published yet at the time of filing of this application.
- 1. Field of the Invention
- The present invention relates to a waste heat energy recovery method and a waste heat energy recovery system for recovering waste heat energy generated from a hydraulic circuit or any other similar system.
- 2. Background Art
- A conventional construction machine typically has such a configuration that power is supplied from an engine, which is normally a diesel engine, to a main pump so that pressurized oil is fed from the main pump to actuator control valves.
- An actuator that has been supplied with pressurized oil fed from the corresponding actuator control valve performs a certain net amount of work on an external entity, while the remaining energy is transformed to thermal energy that is dispersed into the air, as it is lost through various relief valves, reduction of the internal area of the control valve, and piping resistance.
- An oil cooler is provided to reduce the temperature of the hydraulic oil, because a rise in the temperature of the hydraulic oil causes thermal degradation of the oil as well as a decrease in its viscosity, resulting in damage to hydraulic equipment. However, the engine has to supply additional power to drive a rotary fluid cooling machine, such as a cooling fan, for cooling the radiation fins of the oil cooler externally (e.g. see Japanese Laid-open Patent Publication No. 2000-257608 (pp 3, FIG. 2)).
- The abovementioned conventional art is explained hereunder, referring to
FIG. 2 . Amain pump 12 driven by adiesel engine 11 discharges oil, which is fed as pressurized oil through acheck valve 12 a to anactuator control valve 13. The pressurized oil is fed from theactuator control valve 13 through apipeline 14 a to anactuator 14 so that theactuator 14 performs a certain net amount of work on an external entity. Due to energy loss through heat generation by theactuator 14,various relief valves 15, internal area reduction R1 of theactuator control valve 13, and piping resistance R2 of thepipeline 14 a, etc., the remaining energy is transformed to thermal energy, most of which is dispersed as a result of increasing the temperature of the hydraulic oil. - As a rise in the temperature of the hydraulic oil causes thermal degradation of the oil as well as a decrease in its viscosity, resulting in shorter life of hydraulic equipment, the radiation fins of an
oil cooler 16 a are air-cooled by a cooling fan 18, which is driven by an externally providedhydraulic cooling motor 17 in order to reduce temperature of the hydraulic oil. In order to drive thehydraulic cooling motor 17, ahydraulic cooling pump 19 is provided, with its gears adapted to be driven by theengine 11 so that pressurized oil is fed from thehydraulic cooling pump 19 to thehydraulic cooling motor 17. Therefore, theengine 11 is required to supply power in addition to the power supplied to themain pump 12. - Similar energy loss also occurs in the cooling system of the
engine 11, in which fossil fuel, such as diesel oil, burns to generate energy to be supplied in the form of shaft power to the pump system. As much of the energy that is not consumed as the shaft power becomes thermal energy and increases the temperature of engine cooling water, the cooling fan 18, which is driven by the aforementionedhydraulic cooling motor 17, cools by means of air the radiation fins of aradiator 16 b in order to reduce the temperature of the engine cooling water. As a result, the thermal energy dissipates in the air through the radiation fins of theradiator 16 b. Theradiator 16 b is a heat exchanger provided in the engine cooling water circuit. - Furthermore, as the temperature of the engine intake air that has been pressurized by a turbocharger (not shown) provided in an engine intake system becomes high, the cooling fan 18, which is driven by the
hydraulic cooling motor 17, cools by means of air the radiation fins of an air-to-air after-cooler (hereinafter referred to as ATAAC) 16 c in order to cool the engine intake air, thereby increasing the air intake efficiency of theengine 11, as well as reducing combustion temperature so as to reduce the amount of nitrogen oxides generated. As a result, the thermal energy of the pressurized engine intake air dissipates in the air through the radiation fins of theATAAC 16 c, which is provided in an intercooler circuit. - As described above, the radiation fins of the
oil cooler 16 a, the radiation fins of theradiator 16 b, and the radiation fins of the ATAAC 16 c are air-cooled by the cooling fan 18, which is driven by the externally providedhydraulic cooling motor 17, in order to reduce the temperatures of the hydraulic oil and other fluids, i.e. the engine cooling water and the engine intake air. In order to drive thehydraulic cooling motor 17, the aforementionedhydraulic cooling pump 19 is provided, separately from themain pump 12, in a pump assembly attached to an output shaft of theengine 11, so as to feed pressurized oil from thehydraulic cooling pump 19 to thehydraulic cooling motor 17. - Therefore, the
engine 11 is required to supply power in addition to the power supplied to themain pump 12. Moreover, thermal energy dissipates in the air through the radiation fins of theoil cooler 16 a, which is a heat exchanger, as well as the radiation fins of theradiator 16 b and ATAAC 16 c. - This presents the problem of substantial power loss of the
engine 11, resulting in very poor energy use efficiency. - In
FIG. 2 , which provides an example using concrete values to explain the above problem, 95% of the shaft output power of theengine 11 is the effective shaft input power to themain pump 12, while the remaining 5% is the effective shaft input power to thehydraulic cooling pump 19. - In order to solve the above problem, an object of the present invention is to improve the energy use efficiency of the engine.
- The present invention provides a waste heat energy recovery method for recovering waste heat energy by using a low-boiling medium to absorb waste heat energy from hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine, as well as waste heat energy from another fluid that has increased in temperature as a result of operation of the engine, and rotating a power recovery turbine by utilizing the low-boiling medium that has vaporized as a result of absorbing the heat so as to boost the power of the engine by means of the turbine. By transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well the other fluid that has increased in temperature as a result of operation of the engine, the hydraulic oil and the other fluid are cooled while the low-boiling medium is vaporized, so that the vaporized low-boiling medium rotates the turbine, which then provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy of the hydraulic oil and the other fluid, is effectively recirculated to the engine through the turbine, the energy use efficiency of the engine is improved.
- The present invention also provides a waste heat energy recovery system having an oil cooler, another cooling means, a power recovery turbine, and a low-boiling medium circuit. The oil cooler serves to cool hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine. The other cooling means serves to cool another fluid that has increased in temperature as a result of operation of the engine. The aforementioned turbine is provided for the engine and adapted to be rotated by energy provided by a vaporized low-boiling medium. The low-boiling medium circuit serves to drive the turbine by providing the turbine with the low-boiling medium that has been vaporized by waste heat energy from the oil cooler and the other cooling means. With the configuration as above, by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well as the other fluid that has increased in temperature as a result of operation of the engine, the hydraulic oil and the other fluid are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the other cooling means, is effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine is improved.
- According to another feature of the present invention, the aforementioned other cooling means of a waste heat energy recovery system is a radiator for cooling engine cooling water that has increased in temperature as a result of cooling the engine. With the configuration as above, by transferring waste heat energy from the hydraulic oil and engine cooling water to the low-boiling medium, the hydraulic oil and the engine cooling water are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the radiator, is effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine is improved.
- According to yet another feature of the present invention, the aforementioned other cooling means of a waste heat energy recovery system as claimed in claim 2 is an intake air cooler for cooling engine intake air that has increased in temperature as a result of being compressed by a turbocharger. With the configuration as above, by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well as the engine intake air that has increased in temperature as a result of being compressed by the turbocharger, the hydraulic oil and the engine intake air are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the intake air cooler, is effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine is improved.
- According to yet another feature thereof, the present invention provides a waste heat energy recovery system having an oil cooler, a radiator, an intake air cooler, a power recovery turbine, and a low-boiling medium circuit. The oil cooler serves to cool hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine. The radiator serves to cool engine cooling water that has increased in temperature as a result of cooling the engine. The intake air cooler serves to cool engine intake air that has increased in temperature as a result of being compressed by a turbocharger. The aforementioned turbine is provided for the engine and adapted to be rotated by energy provided by a vaporized low-boiling medium. The low-boiling medium circuit serves to drive the turbine by providing the turbine with the low-boiling medium that has been vaporized by waste heat energy from the oil cooler, the radiator, and the intake air cooler. With the configuration as above, by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit, the engine cooling water that has increased in temperature as a result of cooling the engine, and also from the engine intake air that has increased in temperature as a result of being compressed by the turbocharger, the hydraulic oil, the engine cooling water, and the engine intake air are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler, the radiator, and the intake air cooler, is effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine is improved.
- According to yet another feature of the present invention the low-boiling medium circuit includes heat pipes, a feed line, and a return line, the aforementioned heat pipes serving to permit a part of the low-boiling medium fed from a low-boiling medium pump to an evaporator of an air conditioning device circuit to branch off from the air conditioning device circuit and pass through the oil cooler and the other cooling means so that the low-boiling medium vaporizes by absorbing heat from the oil cooler and the other cooling means, the aforementioned air conditioning device circuit including a compressor, a condenser, a receiver, the aforementioned low-boiling medium pump, an expansion valve, and the aforementioned evaporator, all of which are installed in a construction machine and connected to one another in an endless circuit, the aforementioned feed line serving to provide the turbine with low-boiling medium that has been vaporized inside the heat pipes, and the aforementioned return line serving to recirculate the low-boiling medium from the turbine to the intake end of the compressor of the air conditioning device circuit. With the configuration as above, when a part of the low-boiling medium fed to the evaporator of the air conditioning device circuit installed in the construction machine branches off and passes through the heat pipes, the waste heat energy of the hydraulic oil that has increased in temperature as a result of loss of energy as well as the other fluid that has increased in temperature as a result of operation of the engine is transferred to the aforementioned part of the low-boiling medium. As a result, the hydraulic oil and the other fluid are cooled while the low-boiling medium in the heat pipes is vaporized, the vaporized low-boiling medium is fed through the feed line to the turbine and thereby drives the turbine, and the low-boiling medium from the turbine is recirculated through the return line to the intake end of the compressor. As the configuration described above enables an air conditioning device circuit to be provided at lower cost by effectively using a part of the air conditioning device circuit already incorporated in the construction machine, eliminates the necessity of conventional expensive components, such as a cooling motor and a cooling pump for driving a cooling fan, and also eliminates the power loss resulting from driving the cooling pump, the configuration described above is cost effective.
- According to yet another feature of the present invention the aforementioned turbine is connected to a power transmission system, which branches off from a power transmission unit that enables the engine to drive the pump. By using the power transmission system, which branches off from the power transmission unit that enables the engine to drive the pump, the configuration described above facilitates installation of the turbine. Furthermore, by driving the turbine by means of the low-boiling medium vapor that has been vaporized by the waste heat energy from the oil cooler and the waste heat energy from the other cooling means, and feeding driving torque generated in the turbine to the engine through the power transmission system, the configuration described above reduces the driving power of the engine to drive the pump, thereby enabling reduction of fuel consumption by the engine, as well as effective recovery of thermal energy lost in the hydraulic circuit.
- According to the present invention by transferring waste heat energy to a low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well as the other fluid that has increased in temperature as a result of operation of the engine, the hydraulic oil and the other fluid are cooled while the low-boiling medium is vaporized, so that the vaporized low-boiling medium rotates the turbine, which then provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate from the hydraulic oil and the other fluid into the air as waste heat energy, can be effectively recirculated to the engine through the turbine, the energy use efficiency of the engine can be improved.
- According to another feature of the present invention by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well as the other fluid that has increased in temperature as a result of operation of the engine, the hydraulic oil and the other fluid are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the other cooling means, can be effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine can be improved.
- According to yet another feature of the present invention by transferring waste heat energy from the hydraulic oil and engine cooling water to the low-boiling medium, the hydraulic oil and the engine cooling water are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the radiator, can be effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine can be improved.
- According to yet another feature of the present invention by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit as well as the engine intake air that has increased in temperature as a result of being compressed by the turbocharger, the hydraulic oil and the engine intake air are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler and the intake air cooler, can be effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine can be improved.
- According to yet another feature of the present invention by transferring waste heat energy to the low-boiling medium from the hydraulic oil that has increased in temperature as a result of loss of energy in the hydraulic circuit, the engine cooling water that has increased in temperature as a result of cooling the engine, and also from the engine intake air that has increased in temperature as a result of being compressed by the turbocharger, the hydraulic oil, the engine cooling water, and the engine intake air are cooled while the low-boiling medium is vaporized. And by providing the turbine with the vaporized low-boiling medium through the low-boiling medium circuit in order to drive the turbine so that the turbine provides a boost to the engine and thereby recovers the waste heat energy. As a part of the lost engine power, which would, in case of a conventional art, wastefully dissipate into the air as waste heat energy from the oil cooler, the radiator, and the intake air cooler, can be effectively recirculated to the engine by means of the low-boiling medium circuit and the turbine, the energy use efficiency of the engine can be improved.
- According to yet another feature of the present invention when a part of the low-boiling medium fed to the evaporator of the air conditioning device circuit installed in the construction machine branches off and passes through the heat pipes, the waste heat energy of the hydraulic oil that has increased in temperature as a result of loss of energy as well as the other fluid that has increased in temperature as a result of operation of the engine is transferred to the aforementioned part of the low-boiling medium. As a result, the hydraulic oil and the other fluid are cooled while the low-boiling medium in the heat pipes is vaporized, the vaporized low-boiling medium is fed through the feed line to the turbine and thereby drives the turbine, and the low-boiling medium from the turbine is recirculated through the return line to the intake end of the compressor. As the configuration described above enables an air conditioning device circuit to be provided at lower cost by effectively using a part of the air conditioning device circuit already incorporated in the construction machine, eliminates the necessity of conventional expensive components, such as a cooling motor and a cooling pump for driving a cooling fan, and also eliminates the power loss resulting from driving the cooling pump, the configuration described above is cost effective.
- According to yet another feature of the present invention by using the power transmission system, which branches off from the power transmission unit that enables the engine to drive the pump, the configuration described above facilitates installation of the turbine. Furthermore, by driving the turbine by means of the low-boiling medium vapor that has been vaporized by the waste heat energy from the oil cooler and the waste heat energy from the other cooling means, and feeding driving torque generated in the turbine to the engine through the power transmission system, the configuration described above reduces the driving power of the engine to drive the pump, thereby enabling reduction of fuel consumption by the engine, as well as effective recovery of thermal energy lost in the hydraulic circuit.
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FIG. 1 is a fluid circuit diagram of a waste heat energy recovery system according to an embodiment of the present invention. -
FIG. 2 is a circuit diagram of a conventional hydraulic circuit. - The present invention is explained hereunder, referring to
FIG. 1 . The elements similar to those of the conventional art shown inFIG. 2 are identified with the same reference codes, and their explanation is omitted hereunder. - As shown in
FIG. 1 , a diesel engine (hereinafter simply referred to as engine) 11 is mounted on a construction machine, such as a hydraulic excavator. Theengine 11 is adapted to drive a pump, i.e.main pump 12, through a drivingshaft unit 21 and anengine gear unit 22 that branches off from the drivingshaft unit 21. The drivingshaft unit 21 serves as a power transmission unit, and theengine gear unit 22 serves as a power transmission system. In place of a conventionalhydraulic cooling pump 19, a steam turbine (hereinafter simply referred to as turbine) 24 is provided for theengine 11. Theturbine 24 is a small power recovery turbine adapted to be rotated by means of energy provided by vaporized low-boiling medium (what is widely known as refrigerant) and is connected to ashaft 23 of theengine gear unit 22. - The temperature of hydraulic oil increases and generates thermal energy as a result of loss of hydraulic energy from hydraulic output from a
hydraulic circuit 25, which includes themain pump 12, the aforementioned energy loss being the remaining energy after subtracting the energy consumed in thehydraulic circuit 25 for effective work. As most of this thermal energy passes through an oil cooler 16 a, which is a heat exchanger provided in a hydraulicoil return circuit 26, the oil cooler 16 a is adapted to cool the hydraulic oil that has increased in temperature. - As was the case with the oil cooler 16 a, other cooling means are provided to cool other fluids whose temperature increases with operation of the
engine 11. In the case of the present embodiment, the other cooling means are aradiator 16 b for cooling engine cooling water and anintake air cooler 16 c, such as an air-to-air after-cooler (hereinafter referred to as ATAAC), for cooling engine intake air. - To be more specific, similar energy loss also occurs in the cooling system of the
engine 11, in which fossil fuel, such as diesel oil, burns to generate energy to be supplied in the form of shaft power to the pump system. Much of the energy that is not consumed as the shaft power becomes thermal energy and passes through theradiator 16 b, which is provided in an engine cooling water circuit. Therefore, theradiator 16 b is adapted to cool the engine cooling water that has increased in temperature due to cooling theengine 11, in other words, due to waste of combustion energy in theengine 11. - Furthermore, when the engine intake air is compressed by a turbocharger (not shown) that is provided in an engine intake system, the temperature of the engine intake air increases. Therefore, the
ATAAC 16 c, which is provided in an intercooler circuit, is adapted to cool the engine intake air that has increased in temperature, thereby increasing the air intake efficiency of theengine 11, as well as reducing its combustion temperature so as to reduce the amount of nitrogen oxides generated. - A normal air conditioning device (hereinafter simply referred to as air-con) that is mounted on a construction machine, such as a hydraulic excavator, has an air-
con circuit 37, which may otherwise be referred to as an air conditioning device circuit comprises acompressor 32, acondenser 33, areceiver 35, a low-boilingmedium pump 36, an expansion valve (not shown), and an evaporator (not shown), all of which are serially connected to one another in an endless circuit. Thecompressor 32 is adapted to be driven by amotor 31. Thecondenser 33 serves to condense a low-boilingmedium 34, such as a CFC substitute, by releasing heat from the low-boiling medium to the outside. Thereceiver 35 serves to retain the condensed low-boilingmedium 34. The low-boilingmedium pump 36 is adapted to be driven by theaforementioned motor 31 so as to feed the low-boilingmedium 34 by applying pressure. The expansion valve serves to reduce pressure of the low-boilingmedium 34. The evaporator serves to cause the low-boilingmedium 34 that is vaporizing after passing through the expansion valve to absorb heat from the outside. As a conventional system has a circuit of this type, the air-con circuit 37 is also shown inFIG. 2 , which illustrates the conventional art. - Using the air-
con circuit 37, a low-boilingmedium circuit 38 that includes at least the oil cooler 16 a, theradiator 16 b, theATAAC 16 c, and theturbine 24 is provided to drive theturbine 24 by feeding the low-boiling medium that has been vaporized by waste heat energy recovered from the oil cooler 16 a, theradiator 16 b, and theATAAC 16 c. - The low-boiling
medium circuit 38 includesheat pipes feed line 42, and areturn line 43. A part of the low-boiling medium fed from the low-boilingmedium pump 36 to the expansion valve and the evaporator of the air-con circuit 37, which is installed in the cab of the construction machine, is branched off from the air-con circuit 37 and directed into the oil cooler 16 a, theradiator 16 b, and theATAAC 16 c through theheat pipes feed line 42 serves to feed the low-boiling medium that has vaporized in theheat pipes turbine 24. Thereturn line 43 serves to return the low-boiling medium from theturbine 24 to the intake end of thecompressor 32 of the air-con circuit 37. - Next, the function and effects of the embodiment shown in
FIG. 1 is explained hereunder. - In the
hydraulic circuit 25 including themain pump 12, nearly all of the thermal energy generated as a result of loss of hydraulic energy at anactuator control valve 13, arelief valve 15, piping, and anactuator 14 causes a rise in the temperature of hydraulic oil. The hot hydraulic oil passes the oil cooler 16 a, which is provided in the hydraulicoil return circuit 26. As described above, theheat pipe 41 a is provided inside the oil cooler 16 a so that the low-boilingmedium 34, such as A CFC substitute, to be fed to the evaporator of the air-con circuit 37, which is installed in the construction machine, branches off the air-con circuit 37 and passes through theheat pipe 41 a. Therefore, instead of conventional air cooling by a cooling fan 18 driven by ahydraulic cooling motor 17, the low-boiling medium reduces the temperature of the hydraulic oil and recovers thermal energy by removing heat from the hot hydraulic oil in the course of vaporization by the thermal energy of the hydraulic oil in the oil cooler 16 a. - The
aforementioned turbine 24 is connected to theengine gear unit 22, which is a power transmission system for enabling theengine 11 to drive the main pump. By feeding the vaporized low-boiling medium to theturbine 24, theturbine 24 is driven by the low-boiling medium, and the driving power of theengine 11 to drive themain pump 12 is reduced by the driving torque generated in theturbine 24, thereby enabling reduction of fuel consumption by the engine, as well as effective recovery of thermal energy loss, the thermal energy loss being the energy remaining after subtracting the energy consumed in thehydraulic circuit 25 for effective work. - As described above, thermal energy is generated from the rise in the hydraulic oil temperature resulting from energy loss in the
hydraulic circuit 25, in which themain pump 12 is provided. The resulting thermal energy is absorbed by the low-boiling medium, which vaporizes as a result of absorption of the thermal energy. The vaporized low-boiling medium rotates theturbine 24, and the rotatedturbine 24 boosts engine power. Thus, the energy is recovered. - In order to increase the energy use efficiency of the
engine 11, it is desirable to perform energy recovery with the oil cooler 16 a,radiator 16 b, andATAAC 16 c simultaneously, rather than with the oil cooler 16 a alone. - This can be done by causing a part of the condensed low-boiling
medium 34 fed from the low-boilingmedium pump 36 to the evaporator of the air-con circuit 37 to branch off from the air-con circuit 37 and pass through theheat pipes radiator 16 b, and theATAAC 16 c, and, when the low-boilingmedium 34 passes through theheat pipes FIG. 2 ). - At that time, the hydraulic oil that has increased in temperature in the
hydraulic circuit 25 radiates its heat into the low-boiling medium in theheat pipe 41 a of the oil cooler 16 a so that the low-boiling medium vaporizes by absorbing the thermal energy of the hydraulic oil and thereby cools the hydraulic oil. At the same time, the radiator water that has become hot as a result of cooling theengine 11 radiates its heat into the low-boiling medium in theheat pipe 41 b of theradiator 16 b so that the low-boiling medium vaporizes by absorbing the thermal energy of the hot radiator water, thereby cooling the radiator water so that it can serve again as the cooling water. Simultaneously, the engine intake air that has increased in temperature as a result of being compressed by the turbocharger radiates its heat into the low-boiling medium in theheat pipe 41 c of theATAAC 16 c so that the low-boiling medium vaporizes by absorbing thermal energy of the engine intake air and thereby cools the engine intake air. - By feeding the low-boiling medium that has vaporized in the
heat pipes turbine 24, which is connected to theshaft 23 of theengine gear unit 22 and serves to retrieve driving force from theengine 11 to drive not only themain pump 12 but also other elements, the driving power of theengine 11 to drive themain pump 12 is reduced by the driving torque generated in theturbine 24. - For cooling the
engine 11, in the place of a conventional hydraulic cooling pump 19 (FIG. 2 ), theturbine 24, which is a small power recovery turbine adapted to be rotated by the vaporized low-boiling medium, is connected to theengine gear unit 22, which is a power transmission system for enabling theengine 11 to drive the main pump. Therefore, the power loss by theengine 11 resulting from driving ahydraulic cooling pump 19 is mitigated. - As described above, in the place of a conventional
hydraulic cooling pump 19, theturbine 24, which is a small power recovery turbine adapted to be rotated by the vaporized low-boiling medium, is connected to theengine gear unit 22, which is a power transmission system for enabling theengine 11 for a construction machine to drive the main pump, and theheat pipes radiator 16 b, and theATAAC 16 c so that a part of the low-boilingmedium 34 to be fed to the evaporator of the air-con circuit 37, which is normally installed in a construction machine, branches off from the air-con circuit 37 and passes through theheat pipes medium 34 by means of thermal energy of the high temperature fluid in the oil cooler 16 a, theradiator 16 b, and theATAAC 16 c so as to remove heat from the high temperature fluid, thereby cooling the fluid and also recovering the thermal energy. By thus eliminating the necessity of conventional expensive components, such as ahydraulic cooling motor 17 and apump 19 for driving a cooling fan, the system according to the invention enables reduction of production costs. - Furthermore, by causing a part of the low-boiling medium fed to the evaporator of the air-
con circuit 37, which is installed in the construction machine, to branch off from the air-con circuit 37 and pass through theheat pipes radiator 16 b, and theATAAC 16 c, the configuration of the embodiment enables the low-boiling medium to vaporize through absorption of waste heat energy from the oil cooler 16 a, theradiator 16 b, and theATAAC 16 c. The low-boiling medium that has vaporized in theheat pipes feed line 42 to theturbine 24, from which the low-boiling medium is recirculated to the intake end of thecompressor 32 of the air-con circuit 37 through thereturn line 43. Therefore, the configuration described above enables a low-boilingmedium circuit 38 to be provided at low cost by effectively using a part of the air-con circuit 37 already incorporated in the construction machine and adding theheat pipes feed line 42, and thereturn line 43. - Furthermore, according to the invention, by using the
engine gear unit 22 serving as a power transmission system that branches off from the drivingshaft unit 21, by means of which theengine 11 drives themain pump 12, aturbine 24 can be easily installed so that the low-boiling medium that has vaporized in theheat pipes radiator 16 b, and theATAAC 16 c can be fed to theturbine 24, which is connected to theengine gear unit 22, by means of which theengine 11 drives the main pump. The low-boiling medium vapor fed to theturbine 24 generates driving torque in theturbine 24, and the resulting driving torque reduces the driving power of theengine 11 to drive the main pump, thereby enabling reduction of fuel consumption by the engine, as well as effective recovery of thermal energy loss in thehydraulic circuit 25. - The features of the invention described above offer the following benefits.
- It is possible to improve the energy use efficiency of the
engine 11. To be more specific, it is possible to reduce the engine output to as low as approximately 92% so that an engine one class lower can be used, enabling downsizing of theengine 11 and cost reduction. - Furthermore, by lowering the working temperature of hydraulic oil, it is possible to extend the life of hydraulic oil and also to prevent the decrease in viscosity of hydraulic oil, thereby extending the life of sliding portions of hydraulic components.
- Furthermore, the invention eliminates the necessity of such expensive components as a motor and a pump for driving a cooling fan. The elimination of such components not only enables downsizing and cost reduction of the cooling unit but also eliminates such noise as wind noises of the cooling fan and prevents clogging of the heat exchanger that would otherwise occur due to dust contained in the cooling air. Yet another benefit of the invention lies in that the system of the invention does not cause thermal pollution of the environment, because it does not radiate heat to the outside. Therefore, the invention realizes an environmentally-friendly cooling system.
- According to the embodiment shown in the drawing, by means of the
heat pipes radiator 16 b and theATAAC 16 c, the low-boiling medium is vaporized by absorption of heat from the oil cooler 16 a, theradiator 16 b, and theATAAC 16 c so that energy is recirculated to theturbine 24. However, energy may be recirculated to theturbine 24 by using other configuration to which the invention is applicable; for example, the low-boiling medium may be vaporized by absorption of heat from the oil cooler 16 a by using theheat pipe 41 a passing through the oil cooler 16 a, as well as absorption of heat by using either one of theheat pipes radiator 16 b and theATAAC 16 c. - The present invention is applicable to not only a construction machine, such as a hydraulic excavator, a bulldozer, or a loader, but also any other machine provided with a hydraulic circuit that includes a pump driven by an engine.
Claims (7)
1. A waste heat energy recovery method comprising steps of:
using a low-boiling medium to absorb waste heat energy from hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine, as well as waste heat energy from another that has increased in temperature as a result of operation of said engine,
rotating a power recovery turbine by utilizing the low-boiling medium that has vaporized as a result of absorbing the heat; and
boosting power of said engine by means of said turbine.
2. A waste heat energy recovery system comprising:
an oil cooler for cooling hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine;
another cooling means for cooling another fluid that has increased in temperature as a result of operation of said engine;
a turbine for recovering driving power, said turbine provided for said engine and adapted to be rotated by energy provided by a vaporized low-boiling medium; and
a low-boiling medium circuit serves to drive said turbine by providing said turbine with the low-boiling medium that has been vaporized by waste heat energy from the oil cooler and the aforementioned other cooling means.
3. A waste heat energy recovery system as claimed in claim 2 , wherein:
said other cooling means is a radiator for cooling engine cooling water that has increased in temperature as a result of cooling said engine.
4. A waste heat energy recovery system as claimed in claim 2 , wherein:
said other cooling means is an intake air cooler for cooling engine intake air that has increased in temperature as a result of being compressed by a turbocharger.
5. A waste heat energy recovery system comprising:
an oil cooler for cooling hydraulic oil that has increased in temperature as a result of loss of energy in a hydraulic circuit that includes a pump adapted to be driven by an engine;
a radiator for cooling engine cooling water that has increased in temperature as a result of cooling said engine;
an intake air cooler for cooling engine intake air that has increased in temperature as a result of being compressed by a turbocharger;
a turbine for recovering driving power, said turbine provided for said engine and adapted to be rotated by energy provided by a vaporized low-boiling medium.
6. A waste heat energy recovery system as claimed in any one of the claims from claim 2 to claim 5 , wherein said a low-boiling medium circuit comprises:
heat pipes that permit a part of the low-boiling medium that is fed from a low-boiling medium pump to an evaporator of an air conditioning device circuit to branch off from said air conditioning device circuit and pass through said oil cooler and said other cooling means so that said low-boiling medium vaporizes by absorbing heat from said oil cooler and said other cooling means, said air conditioning device circuit comprising a compressor, a condenser, a receiver, said low-boiling medium pump, an expansion valve, and said evaporator, all of which are installed in a construction machine and connected to one another in an endless circuit;
a feed line serving to provide said turbine with the low-boiling medium that has been vaporized inside said heat pipes; and
return line serving to recirculate the low-boiling medium from said turbine to the intake end of said compressor of said air conditioning device circuit.
7. A waste heat energy recovery system as claimed in any one of the claims from claim 2 to claim 6 , wherein:
said turbine is connected to a power transmission system that branches off from a power transmission unit that enables the engine to drive the pump.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-273991 | 2004-09-21 | ||
JP2004273991A JP2006090156A (en) | 2004-09-21 | 2004-09-21 | Method for regenerating waste heat energy and waste heat energy regenerating device |
PCT/JP2005/006628 WO2006033182A1 (en) | 2004-09-21 | 2005-04-05 | Waste heat energy regenerating method and waste heat energy regenerating apparatus |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070074515A1 true US20070074515A1 (en) | 2007-04-05 |
Family
ID=36089948
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/595,458 Abandoned US20070074515A1 (en) | 2004-09-21 | 2005-04-05 | Waste energy recovery method and waste energy recovery system |
Country Status (5)
Country | Link |
---|---|
US (1) | US20070074515A1 (en) |
EP (1) | EP1793111A1 (en) |
JP (1) | JP2006090156A (en) |
CN (1) | CN1842649A (en) |
WO (1) | WO2006033182A1 (en) |
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US20070214789A1 (en) * | 2006-03-15 | 2007-09-20 | Erwin Stiermann | Vehicle or stationary power plant having a turbocharged internal combustion engine as a drive source |
US20100011738A1 (en) * | 2008-07-18 | 2010-01-21 | General Electric Company | Heat pipe for removing thermal energy from exhaust gas |
US20100018180A1 (en) * | 2008-07-23 | 2010-01-28 | General Electric Company | Apparatus and method for cooling turbomachine exhaust gas |
US20100024382A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Heat recovery steam generator for a combined cycle power plant |
US20100028140A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Heat pipe intercooler for a turbomachine |
US20100024429A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Apparatus, system and method for heating fuel gas using gas turbine exhaust |
US20100064655A1 (en) * | 2008-09-16 | 2010-03-18 | General Electric Company | System and method for managing turbine exhaust gas temperature |
US20100243215A1 (en) * | 2009-03-25 | 2010-09-30 | Ferrari S. P. A. | Cooling system for a vehicle with hybrid propulsion |
US20130067951A1 (en) * | 2011-09-16 | 2013-03-21 | Anest Iwata Corporation | Waste heat utilizing device for air compressor |
ITTO20111184A1 (en) * | 2011-12-21 | 2013-06-22 | Soilmec Spa | MACHINE FOR CONSTRUCTION EQUIPPED WITH AN ENERGY RECOVERY SYSTEM. |
EP2889492A1 (en) * | 2013-12-13 | 2015-07-01 | CNH Industrial Italia S.p.A. | Fluid cooler bypass system for an agricultural work vehicle |
US10436529B1 (en) | 2018-08-23 | 2019-10-08 | William T. Holley, Jr. | Hydraulic fluid coolers |
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US20080127665A1 (en) * | 2006-11-30 | 2008-06-05 | Husky Injection Molding Systems Ltd. | Compressor |
CN101070866B (en) * | 2007-07-06 | 2010-09-15 | 纪玉龙 | Hydraulic system heat-energy recovering and utilizing method and apparatus |
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JP6012810B1 (en) * | 2015-04-30 | 2016-10-25 | 三井造船株式会社 | Supercharger surplus power recovery device for internal combustion engine |
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KR101779560B1 (en) * | 2016-04-28 | 2017-09-18 | 재단법인 건설기계부품연구원 | Fuel efficiency improvement system by recovering waste heat of construction machinery |
KR101911139B1 (en) * | 2016-04-28 | 2018-10-23 | 재단법인 건설기계부품연구원 | Fuel efficiency improvement system by recovering waste heat of construction machinery |
KR101799577B1 (en) * | 2016-04-28 | 2017-11-20 | 재단법인 건설기계부품연구원 | Fuel efficiency improvement system by recovering waste heat of construction machinery |
CN110088485A (en) * | 2016-10-28 | 2019-08-02 | A&A国际有限公司 | Thermal hydraulic propulsion system |
KR101827460B1 (en) * | 2016-12-14 | 2018-02-08 | 재단법인 건설기계부품연구원 | Warm-up system by recovering waste heat of construction machinery |
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US20100146969A1 (en) * | 2006-03-15 | 2010-06-17 | Man Nutzfahrzeuge Ag | Vehicle or Stationary Power Plant Having a Turbocharged Internal Combustion Engine as a Drive Source |
US8365526B2 (en) * | 2006-03-15 | 2013-02-05 | Man Truck & Bus Ag | Vehicle or stationary power plant having a turbocharged internal combustion engine as a drive source |
US20070214789A1 (en) * | 2006-03-15 | 2007-09-20 | Erwin Stiermann | Vehicle or stationary power plant having a turbocharged internal combustion engine as a drive source |
US20100011738A1 (en) * | 2008-07-18 | 2010-01-21 | General Electric Company | Heat pipe for removing thermal energy from exhaust gas |
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US20100018180A1 (en) * | 2008-07-23 | 2010-01-28 | General Electric Company | Apparatus and method for cooling turbomachine exhaust gas |
US8186152B2 (en) | 2008-07-23 | 2012-05-29 | General Electric Company | Apparatus and method for cooling turbomachine exhaust gas |
US20100024429A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Apparatus, system and method for heating fuel gas using gas turbine exhaust |
US20100024382A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Heat recovery steam generator for a combined cycle power plant |
US8157512B2 (en) * | 2008-07-29 | 2012-04-17 | General Electric Company | Heat pipe intercooler for a turbomachine |
US8359824B2 (en) | 2008-07-29 | 2013-01-29 | General Electric Company | Heat recovery steam generator for a combined cycle power plant |
US20100028140A1 (en) * | 2008-07-29 | 2010-02-04 | General Electric Company | Heat pipe intercooler for a turbomachine |
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US20100064655A1 (en) * | 2008-09-16 | 2010-03-18 | General Electric Company | System and method for managing turbine exhaust gas temperature |
US8281884B2 (en) * | 2009-03-25 | 2012-10-09 | Ferrari S.P.A. | Cooling system for a vehicle with hybrid propulsion |
US20100243215A1 (en) * | 2009-03-25 | 2010-09-30 | Ferrari S. P. A. | Cooling system for a vehicle with hybrid propulsion |
US20130067951A1 (en) * | 2011-09-16 | 2013-03-21 | Anest Iwata Corporation | Waste heat utilizing device for air compressor |
US8943853B2 (en) * | 2011-09-16 | 2015-02-03 | Anest Iwata Corporation | Waste heat utilizing device for air compressor |
EP2615288A1 (en) * | 2011-12-21 | 2013-07-17 | Soilmec S.p.A. | Construction equipment equipped with an energy recovery apparatus |
ITTO20111184A1 (en) * | 2011-12-21 | 2013-06-22 | Soilmec Spa | MACHINE FOR CONSTRUCTION EQUIPPED WITH AN ENERGY RECOVERY SYSTEM. |
EP2889492A1 (en) * | 2013-12-13 | 2015-07-01 | CNH Industrial Italia S.p.A. | Fluid cooler bypass system for an agricultural work vehicle |
US10260824B2 (en) | 2013-12-13 | 2019-04-16 | Cnh Industrial America Llc | Fluid cooler bypass system for an agricultural work vehicle |
US10436529B1 (en) | 2018-08-23 | 2019-10-08 | William T. Holley, Jr. | Hydraulic fluid coolers |
Also Published As
Publication number | Publication date |
---|---|
WO2006033182A1 (en) | 2006-03-30 |
CN1842649A (en) | 2006-10-04 |
JP2006090156A (en) | 2006-04-06 |
EP1793111A1 (en) | 2007-06-06 |
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