WO2012052226A2 - Dispositif de récupération de chaleur dissipée - Google Patents

Dispositif de récupération de chaleur dissipée Download PDF

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Publication number
WO2012052226A2
WO2012052226A2 PCT/EP2011/065659 EP2011065659W WO2012052226A2 WO 2012052226 A2 WO2012052226 A2 WO 2012052226A2 EP 2011065659 W EP2011065659 W EP 2011065659W WO 2012052226 A2 WO2012052226 A2 WO 2012052226A2
Authority
WO
WIPO (PCT)
Prior art keywords
gas
condenser
working fluid
pump
air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2011/065659
Other languages
German (de)
English (en)
Other versions
WO2012052226A3 (fr
Inventor
Manfred Schmitt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2012052226A2 publication Critical patent/WO2012052226A2/fr
Anticipated expiration legal-status Critical
Publication of WO2012052226A3 publication Critical patent/WO2012052226A3/fr
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—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 combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D19/00—Degasification of liquids
    • B01D19/0036—Flash degasification
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat

Definitions

  • the invention relates to a device for waste heat recovery. Specifically, the invention relates to a device for waste heat recovery, in an air-compressing, self-igniting internal combustion engine or a mixture-compressing, spark-ignited
  • Vacuum pump required, which pumps off the air before commissioning and also during operation. It is also conceivable that the air is displaced from the steam circuit by the steam circuit is completely filled with working fluid at a standstill. When heating the system, the liquid is partially displaced by the steam forming in a designated tank.
  • this has the disadvantage that large amounts of fluid in the steam circuit are required, which slow down the warm-up and operating point change significantly, and that an additional volume of construction for the fluid tank is required and there is a corresponding additional weight.
  • this concept also has the disadvantage that, when the system is turned off, there are no sufficient air cushions in the lines and components, so that damage is possible during freezing. Disclosure of the invention
  • Claim 1 has the advantage that an improved structure and improved functionality are possible. Specifically, leakage of working fluid from the steam circuit may be reduced and additional may be added
  • Components can be saved.
  • damage can be avoided by freezing and it can also be a quick thawing when restarting the device for
  • Waste heat utilization will be enabled.
  • gas storage can be stored in an advantageous manner air or another gas.
  • vacuum pumps for pumping out the air from the system can be saved, so that there is a cost savings.
  • part of the working fluid is lost when pumping out the air from the system, which is avoided by the absence of the vacuum pump from the outset. A leakage of the
  • Working fluids can be minimized.
  • water or a mixture of water and an additive can be used as the working fluid. This can be done at low ambient temperatures, an expansion of the freezing water.
  • a gas cushion can be realized in a suitable manner by the gas stored in the gas storage in the components of the gas circuit, so that this expansion is possible without damaging the components of the steam circuit.
  • a fast thawing can be made possible when restarting.
  • the steam circuit is not completely filled with the working fluid to displace all of the air therefrom, but only as much working fluid is charged as is required to operate the steam process and to compensate for leakage.
  • the remaining volume of the steam circuit remains filled with air. Thus prevails at standstill almost ambient pressure in the steam circuit, whereby the leakage and the
  • the air in the condenser is at startup in an advantageous manner by a pump, in particular a fluid pump in the
  • Connecting line is much smaller than a length of the connecting line. This can be achieved that in operation as little air in the reservoir
  • the surface (interface) between the air and the liquid is as small as possible.
  • a further advantageous measure to keep the surface between the air and the liquid as small as possible, is that the gas storage has a mean diameter which is much smaller than a length of the gas reservoir.
  • At least one valve is arranged in the connection between the gas reservoir and the high-pressure region.
  • a complete media separation can be achieved by a shut-off valve in the connection between the gas storage and the high pressure area.
  • the shut-off valve is then opened only for intentional storage or discharge of the air in or out of the gas storage. For example, the shut-off valve during commissioning during the
  • Venting phase open and closed in operation after complete venting. If, after a long period of operation, air collects again in front of the shut-off valve, this air can be stored in the gas storage tank by opening it briefly in an operating phase in which the operating pressure is higher than the injection pressure in the gas storage tank.
  • the valve in the connection between the gas storage and the high-pressure region is designed as a media-separating valve.
  • the media-separating valve can be designed as a float valve corresponding to an automatic ventilation valve for heating systems.
  • at least one separating device is provided and that the gas reservoir is connected to the high-pressure region via the separating device.
  • the separating device can be configured advantageously as a settling chamber. The deposition of air can be done by gravity, the Settling chamber is configured for example by an upward funnel in an extended fluid line.
  • the separating device is designed as a separating device. In this case, for example, a cyclone principle, a gas-permeable, but liquid-blocking membrane, a climate membrane or the like can be used. Thus, the separation of the air through the
  • the steam circuit has an expansion device and that a displacement volume of the expansion device can be limited so that a predetermined injection pressure for the high-pressure region can be set. This can be generated without additional components required for storing the air in the gas storage Ein umandruck. It is also advantageous for this purpose that the steam circuit has an evaporator and a valve which is arranged in the high-pressure region, in particular in front of the evaporator, and via which a injection pressure for the high-pressure region can be set.
  • a particular advantage of the valve disposed in front of the evaporator is that the evaporator has a relatively low pressure and can therefore outgas air enriched in the water.
  • this can be used to limit a swallowing volume.
  • the arrangement of the valve in front of the evaporator has the advantage that a relatively small valve can be used.
  • the steam circuit has a condenser, that a pump is provided, that a suction side of the pump is connected to the condenser, that a delivery side of the pump is connected to the gas accumulator and that the suction side of the pump is thus connected to the condenser is that gas from a forming in a condensation of a working gas cushion is sucked into the gas storage.
  • gas forming in the condenser in particular air, can be led directly into the gas reservoir.
  • the condensing capacity available for the condensation is optimized at the same time, since the gas cushion is reduced.
  • the steam circuit is largely filled with air, with little collected water is provided. However, it is unfavorable when starting operation, if air in the
  • Capacitor is because then there is air on the walls of the condenser. Therefore, it is also advantageous that air is sucked out of the condenser during startup.
  • the air can also be advantageously conveyed into the gas storage during commissioning of the device and also during operation by the fluid pump, which can also convey gases, or by an additional vacuum pump.
  • the steam circuit has a condenser and a suction device downstream of the condenser, that a suction line of the suction device in opens the condenser and that an opening point of the suction line is arranged on the condenser, that gas from a forming in a condensation of a working gas cushion in the steam circuit is sucked.
  • This can be done in a simple manner an extraction of the collecting air in the condenser. In this case, for example, a suction jet principle can be exploited.
  • the condensation performance of the capacitor is optimized.
  • the device is at least substantially filled with a working fluid and a gas as a filling.
  • the gas may comprise air and / or nitrogen.
  • the device then contains, in addition to the working fluid, a gas containing the
  • Negative pressure limited during a system shutdown is preferably based on the ambient pressure.
  • the working fluid can be collected in an exhaust gas heat exchanger and / or in a heatable reservoir.
  • the working fluid then collects in the plant standstill in the exhaust gas heat exchanger or in the heatable reservoir.
  • the working fluid for example water
  • the exhaust gas heat exchanger which is made frost-proof, or the heatable reservoir.
  • the working fluid in particular the water, by a suitable arrangement of the components of the device in the evaporator, in particular in a
  • Exhaust heat exchanger run, be pumped by a pump, in particular the fluid pump, or be blown by the gas, in particular the air in the gas storage in the evaporator, which is possible by opening the associated valve. It is therefore advantageous that the working fluid in a mounting position by gravity in a
  • Exhaust heat exchanger flows and / or that the working fluid is at least partially conveyed by means of a fluid pump in the exhaust gas heat exchanger and / or the gas from the
  • Gas storage is available to the working fluid from at least one component,
  • Blowout flows due to the pressure difference gas from the gas storage in the steam circuit.
  • the gas can flow in the two possible directions through the steam circuit.
  • particularly remaining fluid residues which collect, for example, in the form of small puddles in the steam circuit, can be transported away.
  • sensitive components that are disturbed or damaged in function by freezing water or the like may be blown out.
  • FIG. 1 shows a device for utilizing waste heat in a schematic illustration according to a first exemplary embodiment of the invention
  • Fig. 2 shows a device for waste heat utilization in a schematic representation according to a second embodiment of the invention
  • Fig. 3 shows a gas storage and a connection line of a device for
  • Fig. 1 shows a device 1 for waste heat recovery in a schematic representation according to a first embodiment of the invention.
  • the device 1 for waste heat utilization can be used in particular for an internal combustion engine.
  • the exhaust gases emitted by the internal combustion engine can be deprived of energy.
  • the device 1 is suitable for waste heat utilization for applications in motor vehicles.
  • the internal combustion engine can in this case be configured in particular as an air-compressing, self-igniting or mixture-compressing, spark-ignited internal combustion engine.
  • the apparatus 1 for waste heat utilization of the invention is also suitable for other applications.
  • the device 1 has a steam circuit 2 with an evaporator 3, a
  • Expansion device 4 and a capacitor 5 The evaporator 3 can
  • a liquid working fluid is evaporated.
  • the expansion device 4 is arranged downstream of the evaporator 3. Via a line 6, the evaporated working fluid to the expansion device 4th guided. As a result, the expansion device 4 is driven.
  • the expansion device 4 may comprise a turbine which drives an electric generator for generating electrical energy.
  • the capacitor 5 is the
  • the steam circuit 2 may have one or more leakage points.
  • An example of such a leakage point is a shaft seal of the expansion device 4.
  • Such leakage points are usually air in the steam circuit 2.
  • the forming at a standstill of the device 1 vacuum is limited.
  • the same pressure arises within the steam circuit 2 as outside.
  • fluid leakage to the outside is minimized.
  • the Ein heading horrin in the high pressure region 1 1 can be set in different ways.
  • One possibility is that a swallow volume of
  • Expansion device 4 is limited. Another possibility is that in the line 10, a valve 12 is disposed in front of the evaporator 3. Via the valve 12, the desired Einariadruck can then be generated and adjusted.
  • An advantage of the valve 12 in front of the evaporator 3 is that in the evaporator 3, a lower pressure prevails and thus can outgas enriched air in the working fluid.
  • the device 1 has a gas storage 15, which serves for storing a gas, in particular air.
  • the gas storage 15 is dimensioned so large that all the air in the device 1, for example, the given at a pressure of about 100 kPa (1 bar) air capacity, can be added at the selected injection pressure.
  • the pressure level for storage should be chosen to be slightly lower than the operating pressure at the frequently approached operating points, so that even during operation still residual air can be stored.
  • the design of the device 1 is such that it can be achieved during operation that as little air as possible accumulates in the working fluid flowing past the gas reservoir 15. Namely, if air accumulates in the working fluid flowing through the line 10, then this air passes back into the condenser, from where it would have to be pumped out again. In order to avoid the accumulation of the working fluid, the interface between the air and the working fluid is kept as small as possible.
  • the gas storage 15 is connected via a line 16 to the high-pressure region 1 1. It is the
  • Inner diameter of the line 16 is much smaller than the length of the line 16 to choose.
  • the gas storage 15 via the line 16 directly to the line 10th is much smaller than the length of the line 16 to choose.
  • shut-off valve 17 is arranged in the conduit 16.
  • shut-off valve 17 is then opened only for the intentional storage or discharge of air into or out of the gas storage 15. In operation, the shut-off valve 17 remains closed after complete venting in the rule. However, collects after a longer period of operation again air in front of the shut-off valve 17, then this air can by briefly opening in an operating phase in which the operating pressure higher than the
  • the gas reservoir 15 is additionally or alternatively connected via a media-separating valve 18 to the high-pressure region 1 1.
  • a media-separating valve 18 for example, serve a float valve.
  • the steam circuit 2 may also have a separator 19.
  • Separating device 19 can in this case exploit the gravity for separating the media.
  • the separation device 19 may comprise an upwardly directed funnel 20 which is arranged behind the pump 8 in the flow direction of the working fluid. Through the funnel 20 an expanded fluid line is formed, which acts as a calming chamber. The entrained air can then go up from the working fluid to the line 16.
  • the separation device 19 can also exploit another principle, in particular a cyclone principle.
  • a gas-permeable, but liquid-blocking membrane or the like may be integrated into the separation device 19.
  • the device 1 also has a suction device 21.
  • the suction device 21 is arranged in the steam circuit 2. This leads a
  • the suction line 22 opens at a suitable mouth point 23 into the condenser 5. Furthermore, an end 24 of the suction line 22 is arranged in front of the pump 8 in the suction line 9. About the
  • Suction lines 9, 22, a suction pump is realized.
  • the suction device 21 operates according to the suction jet principle. Via the suction line 9, liquid working fluid is sucked out of the condenser 5 by the pump 8.
  • the discharge point 23 of the suction line 22 is arranged at a location of the condenser 5, at which preferably air accumulates. This may be, for example, the area above the liquid level of the working fluid.
  • a negative pressure in the suction line 22 is generated.
  • the pump 8 thus enables, in addition to the working fluid, the air is sucked with.
  • the suction line 9 serves at least substantially as a suction line 9 for liquid working fluid, while the suction line 22 at least in
  • the pump 8 Essentially serves as air suction 22.
  • the pump 8 is suitable both for conveying liquid working fluid and for gas delivery.
  • the working fluid of the steam circuit 2 is preferably collected at a point where it can be reheated or thawed as quickly as possible when restarting.
  • the evaporator 3 is particularly suitable. Therefore, the evaporator 3 is structurally preferably designed so that it is not damaged by the freezing working fluid. This can be achieved by releasing air from the gas reservoir 15 when the device 1 is shut off, which air at least partially reaches the evaporator 3. Accordingly, in other components in which it can be damaged by freezing working fluid, a gas cushion can be created, which allows expansion of the freezing working fluid.
  • the device 1 can be structurally designed so that the evaporator 3 is arranged at the lowest point and the working fluid expires in a corresponding wiring by gravity into the evaporator 3. If this is structurally not possible, then the working fluid can be pumped into the evaporator 3 by the pump 8 serving as the fluid pump 8. Remaining fluid residues in the lines or components of the steam circuit 2 can be blown out by opening the shut-off valve 17 after the vapor pressure in the steam circuit 2 has dropped. To complete a shutdown as quickly as possible, the condenser cooling can be maintained by the capacitor 5 until the residual heat from the device 1 is largely dissipated and no working fluid condenses more, which would have to be pumped from the pump 8.
  • Fig. 2 shows a device 1 for waste heat recovery in a schematic representation according to a second embodiment.
  • a pump 30 is provided, via the air from the condenser 5 can be pumped.
  • a suction side 31 of the pump 30 is connected to the condenser 5 via the suction line 22 at the point of discharge 23.
  • a delivery side 32 of the pump 30 is connected to the conduit 16 via a gas conduit 33, which in particular serves for the passage of air.
  • the gas line 33 is in this case preferably between the shut-off valve 17 and the
  • the gas line 33 can also be connected to the line 16 between the high-pressure region 11 and the shut-off valve 17. In an embodiment in which no shut-off valve 17 is provided, the gas line 33 is connected to the line 16 in a suitable manner.
  • the pump 30 may in this case be configured as a vacuum pump 30.
  • High pressure range 1 1 is connected and that a mean diameter of the
  • Connecting line 16 is much smaller than a length of the connecting line 16. Additionally or alternatively, it is advantageous if the gas storage 15 has an average diameter which is much smaller than a length of the gas reservoir 15th
  • the gas accumulator 15 is designed such that for a volume of the gas accumulator 15 and a length of the gas accumulator 15, the following relation (1) is fulfilled:
  • both the volume and the length can be determined relatively easily, so that a suitable embodiment can be selected and checked in a simple manner.
  • the condition (1) with the auxiliary control (2) can serve both for a suitable selection of the volume of the gas reservoir 15 and the length of the gas reservoir 15 and for a suitable selection of the volume of the connecting line 16 and the length of the connecting line 16.
  • Connecting line 16 may be advantageously designed, if each of the operation (1) with the auxiliary control (2) meet.
  • the diameter is then smaller than x times the length, where x furthermore satisfies the condition (2):
  • Fig. 3 shows a gas storage 15 and a connecting line 16 of a device 1 for waste heat recovery in an excerpt, schematic, not to scale
  • the gas storage 15 is designed as a cylindrical gas storage 15.
  • the connecting line 16 is designed as a cylindrical connecting line 16.
  • the gas storage 15 has a mean diameter 40, which is equal to the diameter (inner diameter) 40 of the gas reservoir 15 due to the cylindrical configuration. Accordingly, a mean diameter 41 is the
  • Connecting line 16 equal to the diameter (inner diameter) 41 of the
  • the gas storage 15 also has a length 42. Furthermore, the connection line 16 shown in sections has a length 43. Due to gravity is in an upper part 44 of the gas storage 15 air, while in a lower part 45 of the gas reservoir 15 is a liquid. Also, the connection line 16 is with the liquid filled. Preferably, the gas storage 15 is filled to 2/3 with air.
  • An interface 46 results between the air and the liquid.
  • the air can dissolve in the liquid at the interface 15. However, gravity counteracts diffusion of the dissolved air to and through the connecting line 16.
  • the size of the interface 46 is constant regardless of the size of the liquid-filled portion 45.
  • the gas storage 15 is dimensioned for this purpose that it is never completely full of air during operation. At standstill, however, the liquid is pressed out of the gas reservoir 15.
  • the geometry of the gas reservoir 15 is selected so that the condition (3) is satisfied with the constraint (2) and thus the interface 46 is small. As a result, the solution of air in the liquid is reduced as much as possible.
  • the embodiments of the device 1 described with reference to FIGS. 1 and 2 can also be modified by an omission, an exchange, a supplement or a combination of components. As a result, an adaptation to the particular application is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Waste-Gas Treatment And Other Accessory Devices For Furnaces (AREA)

Abstract

Dispositif (1) de récupération de chaleur dissipée comportant un circuit de vapeur (2) et un accumulateur de gaz (15). Selon l'invention, l'accumulateur de gaz (15) est relié par un conduit de liaison (16) à vanne d'arrêt (17) à une zone de haute pression (11) du circuit de vapeur (2). L'ouverture de la vanne d'arrêt (17) permet, en fonctionnement, la pénétration de l'air sortant de la zone de haute pression (11) du circuit de vapeur (2) dans l'accumulateur de gaz (15).
PCT/EP2011/065659 2010-10-18 2011-09-09 Dispositif de récupération de chaleur dissipée Ceased WO2012052226A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010042558 DE102010042558A1 (de) 2010-10-18 2010-10-18 Vorrichtung zur Abwärmenutzung
DE102010042558.3 2010-10-18

Publications (2)

Publication Number Publication Date
WO2012052226A2 true WO2012052226A2 (fr) 2012-04-26
WO2012052226A3 WO2012052226A3 (fr) 2013-05-16

Family

ID=44645113

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/065659 Ceased WO2012052226A2 (fr) 2010-10-18 2011-09-09 Dispositif de récupération de chaleur dissipée

Country Status (2)

Country Link
DE (1) DE102010042558A1 (fr)
WO (1) WO2012052226A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3365617A4 (fr) * 2015-10-22 2018-08-29 QTF Sweden AB Procédé de dégazage de mélanges liquides à faibles points d'ébullition dans des systèmes fermés
CN116696531A (zh) * 2023-04-27 2023-09-05 浙江三可热交换系统有限公司 一种列车用微通道热交换系统

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3004216B1 (fr) * 2013-04-09 2017-11-17 Exoes Systeme et methode de gestion du gel dans un circuit de conversion d'energie thermique
DE102014206038A1 (de) * 2014-03-31 2015-10-01 Mtu Friedrichshafen Gmbh System für einen thermodynamischen Kreisprozess, Steuereinrichtung für ein System für einen thermodynamischen Kreisprozess, Verfahren zum Betreiben eines Systems, und Anordnung mit einer Brennkraftmaschine und einem System
FR3038349B1 (fr) * 2015-06-30 2020-05-08 C3Tech Dispositif de stockage d'energie electrique utilisant de l'air comprime
DE102016007494A1 (de) * 2016-06-18 2017-12-21 Daimler Ag Vorrichtung und Verfahren zum Betrieb eines Abwärmenutzungssystems
CN113587208A (zh) * 2021-08-03 2021-11-02 中国华能集团清洁能源技术研究院有限公司 一种蒸汽管网储能在线定量计算方法和系统

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB750071A (en) * 1953-09-16 1956-06-06 Sulzer Ag Expelling water from the tube systems of steam generators
US3597621A (en) * 1967-12-01 1971-08-03 Kiichi Yamada Special thermal electric power generating unit using pressurized hot air together with superheated steam
DE19953612A1 (de) * 1999-11-08 2001-05-10 Abb Alstom Power Ch Ag Wärmetauscher
DE10048439C2 (de) * 2000-09-29 2002-09-19 Siemens Ag Dampfturbinenanlage und Verfahren zum Betreiben einer Dampfturbinenanlage
DE102007034025A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Hydraulischer Hybridantrieb für ein Fahrzeug
FR2956153B1 (fr) * 2010-02-11 2015-07-17 Inst Francais Du Petrole Dispositif de controle d'un fluide de travail a bas point de congelation circulant dans un circuit ferme fonctionnant selon un cycle de rankine et procede utilisant un tel dispositif
DE102010028013A1 (de) * 2010-04-21 2011-10-27 Robert Bosch Gmbh Vorrichtung zur Abwärmenutzung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3365617A4 (fr) * 2015-10-22 2018-08-29 QTF Sweden AB Procédé de dégazage de mélanges liquides à faibles points d'ébullition dans des systèmes fermés
CN116696531A (zh) * 2023-04-27 2023-09-05 浙江三可热交换系统有限公司 一种列车用微通道热交换系统
CN116696531B (zh) * 2023-04-27 2024-03-22 浙江三可热交换系统有限公司 一种列车用微通道热交换系统

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WO2012052226A3 (fr) 2013-05-16
DE102010042558A1 (de) 2012-04-19

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