EP2425101A2 - Dispositif d'exploitation de chaleur et procédé de fonctionnement - Google Patents

Dispositif d'exploitation de chaleur et procédé de fonctionnement

Info

Publication number
EP2425101A2
EP2425101A2 EP10710225A EP10710225A EP2425101A2 EP 2425101 A2 EP2425101 A2 EP 2425101A2 EP 10710225 A EP10710225 A EP 10710225A EP 10710225 A EP10710225 A EP 10710225A EP 2425101 A2 EP2425101 A2 EP 2425101A2
Authority
EP
European Patent Office
Prior art keywords
working fluid
condenser
utilization device
heat utilization
adjusted
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.)
Withdrawn
Application number
EP10710225A
Other languages
German (de)
English (en)
Inventor
Jan GÄRTNER
Thomas Koch
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
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 Daimler AG filed Critical Daimler AG
Publication of EP2425101A2 publication Critical patent/EP2425101A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • 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
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • 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
    • 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
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • 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

Definitions

  • the present invention relates to a method for operating a heat utilization device, in particular a motor vehicle, with the features of the preamble of claim 1. Furthermore, the invention relates to a heat utilization device for use as a waste heat utilization device of an internal combustion engine, in particular of a motor vehicle.
  • US Pat. No. 5,327,987 discloses a hybrid vehicle having an internal combustion engine driving a first vehicle axle, an electric motor driving a second vehicle axle, and a waste heat utilization device using an exhaust heat and an engine heat, wherein a pressure control device for regulating a high pressure in the region of a heat-carrying heat exchanger Waste heat recovery device is provided.
  • DE 10 2004 024 402 A1 describes a heat engine with an expansion machine and with an electric rotary device which can be used as a current generator or electric motor.
  • a power transmission device disposed between the expansion machine and the rotary electric device is formed as a planetary gear, wherein the expansion machine, the rotary electric device and the power transmission device are integrally housed in a housing.
  • a described in DE 10 2007 024 894 A1, designed as Clausius-Rankine cycle heat utilization device is connected via a condenser of the heat utilization device with a cooling circuit, both circuits share both the working fluid and the condenser.
  • a working fluid mass flow of the Rankine cycle is reduced when a predicted total working fluid mass flow of both circuits exceeds a preset threshold.
  • US Pat. No. 7,174,732 B2 describes a heat utilization device with an expansion machine, a condenser, a feed pump and an evaporator, wherein a rotation of a fan of the condenser is regulated on the basis of a signal of a pressure sensor arranged after the expansion machine and in front of the condenser. By controlling the fan, the pressure prevailing after the expansion machine pressure is controlled.
  • the present invention is concerned with the problem of providing, for a method of operating a heat utilization device and a heat utilization device for use as a waste heat utilization device of an internal combustion engine, an improved or at least another embodiment, which is particularly characterized in that even during a high load operation of a heat of vaporization of the heat utilization device the heat-using device can not be damaged by overheating, without costly over-dimensioning the heat-using device due to its cost.
  • the invention is based on the general idea of increasing the condensation temperature in a condenser of the heat utilization device by raising a low pressure prevailing in the region of the condenser so that a gaseous working fluid coming from an expansion machine of the heat utilization device can be completely liquefied in the condenser. If the working fluid is not completely liquefied in the condenser, a feed pump of the heat utilization device following in a working fluid path has to perform the liquefaction of the partially gaseous or vaporous working fluid. Either in this case, the feed pump with high cost of such performance designed or it is permanently destroyed by the temporary occurrence of gaseous or vaporous working fluid. This can be avoided by increasing a condensation temperature in the condenser, thereby enabling a cost-effective design of the heat utilization device.
  • the expansion ratio is defined as the ratio of the pressure before expansion to the pressure after expansion.
  • the pressure ratio or expansion ratio is directly related to the volume ratio, ie the ratio of the volume before expansion to the volume after expansion, the expansion machine.
  • This volumetric ratio can be reduced by adjusting the valve timing in reciprocating engines or in slot-controlled engines by adjusting the slot timing or variable turbine geometry. Alternatively or additionally, a throttle may also be used.
  • a reduction in the expansion ratio can be achieved by increasing the low pressure in the circuit, lowering the high pressure, or a combination of both.
  • the expansion ratio is reduced by increasing an inflow cross section of an inflow path of the working fluid to the expansion machine.
  • the low pressure can be increased by opening the Zuströmqueriteses of the working fluid to the expansion machine.
  • an increase in the low pressure in a low pressure path of the working fluid occurs almost simultaneously with the increase of the condensation temperature in the low pressure path.
  • the reduction of the expansion ratio is performed by adjusting the low pressure by changing a speed of the expander.
  • the reduction of the expansion ratio is carried out by adjusting the low pressure to the expansion machine by slit control of the inflow cross section of the working fluid.
  • a heat transfer stream from Working fluid can be increased to a condenser environment.
  • this is only sufficiently effective in cooperation with the increase of the condensation temperature, since in the case of a very small temperature difference between the condensation temperature and an ambient temperature of the condenser environment, the heat transfer current is almost negligible. Accordingly, a reduction in the working fluid mass flow causes a reduction in the heat transfer flow from the working fluid to a condenser environment.
  • the ambient temperature may be at least partially formed by the temperature of a cooling medium of the capacitor.
  • Fig. 1 is a pressure-enthalpy diagram of a Clausius-Rankine cycle process in
  • a heat utilization device 1 a heat of evaporation 2, such.
  • an expansion machine 3 As an internal combustion engine, as a high-temperature heat source, an expansion machine 3 with a power converter 4, a capacitor 5 as a low-temperature heat source and a feed pump 6 on.
  • the evaporation heat source 2 As a high-temperature heat source, heat is added to the Capacitor 5 is transferred as a low temperature source, thereby converting a part of the transferred heat by the heat utilization device 1 into usable mechanical work, while simultaneously cooling the evaporation heat source 2 by the transfer and heating a condenser environment of the condenser 5.
  • a pressure-enthalpy curve 7 of a working fluid of the heat utilization device 1 which together with an x-axis 8, on which the enthalpy h is removed, encloses a region 9, which indicates a simultaneous presence of a gaseous and a liquid state of aggregation of the working fluid.
  • the vaporization curves 13, 14, 15, 16 in region 9, which characterize the presence of the liquid and gaseous states of the working fluid, are parallel to the x-axis 8.
  • the vaporization curves 13, 14, 15, 16 strike in the area 9 a second time with the pressure-enthalpy curve 7 in several points 17 ', 18', 19 ', 20' together.
  • the curve points 17 ', 18', 19 ', 20' all the working fluid has changed from the liquid state of matter into the gaseous state of matter.
  • the curve of the evaporation curves 13, 14, 15, 16 in the region 12 of the gaseous state of matter of the working fluid thus shows the behavior of the working fluid in the gaseous state of matter with further pressure reduction. According to the course of evaporation curves 13, 14, 15, 16 in region 12, this process is not isenthalpic.
  • FIG. 1 shows a cyclic process 21 which illustrates the different states A, B, C 1 D of the working fluid in the cyclic process 21.
  • the working fluid is present as superheated steam or superheated gas.
  • the gas flows through the expansion machine 3, wherein the working fluid undergoes a pressure drop and a temperature drop. In this case, an enthalpy difference ⁇ h is converted by the expansion machine 3 into useful work.
  • the working fluid is liquefied by the condenser 5.
  • the working fluid flows through the feed pump 6 on the way from C to D and experiences an almost isenthalpic pressure increase, since the enthalpy increase, in the case of an isentropic process, a product of volume and pressure difference, with compression of liquids compared to other enthalpy differences of the cycle 21 very is low.
  • the liquefied working fluid is first heated to the evaporation temperature, then evaporated and a resulting vapor of the working fluid is overheated up to the point A by the waste heat of the evaporation heat source 2.
  • the above-described cycle with the states A, B, C, D of the working fluid essentially represents an ideal cycle.
  • the state point B does not lie exactly on the pressure-enthalpy curve 7. Namely, if the working fluid is partially already liquefied during flow through the expansion machine 3, the state point B is within the range 9. In this case, the enthalpy difference ⁇ h and thus the energy yield of useful mechanical work is increased. If the vaporous working fluid has to be cooled down before flowing through the condenser 5 before it can be liquefied, the state point B is arranged in the region 12. It is also possible that the state point C is also not on the pressure-enthalpy curve 7.
  • the state point C is in the range 10. If the condenser 5 does not completely liquefy the working fluid, the state point C lies within the range 9.
  • a temperature difference ⁇ T between the ambient temperature of the condenser environment and the condensation temperature Tu of the working fluid is largely responsible for the magnitude of the heat transfer flow dQ between the working fluid and the condenser environment.
  • the heat transfer between the condenser environment and the working fluid takes place according to the following formula:
  • A is the area of heat transfer
  • ⁇ T is the temperature difference between the ambient temperature of the
  • Working fluid mass flow of the working fluid is.
  • the height of the heat transfer flow dQ can also be increased by a working fluid mass flow because the heat transfer coefficient a is dependent on the working fluid mass flow and becomes larger the larger the working fluid mass flow.
  • FIG. 2 shows the result of such an increase of the low pressure from pu to Pu * with respect to the cyclic process 21.
  • the working fluid during z. B. the flow through the evaporation heat source 2 thus a reduced high pressure p 0 * and a reduced evaporation temperature T 0 * on.
  • the low pressure pu * and the condensation temperature T y * of the working fluid z. B. increases when flowing through the capacitor 5.
  • the change of the low pressure from pu to pu * is possible by reducing the expansion ratio, for example, by changing an inflow cross section of an inflow path of the working fluid to the expansion machine 3 of the heat utilization device 1.
  • the inflow cross section is in an expedient embodiment by a throttle device 24 in the form z.
  • a throttle valve As a throttle valve, a variable turbine geometry or the like on demand reduced or increased. This raises automatically and at the same time by increasing the inflow cross section an increase of the low pressure pu and the condensation temperature Tu of the working fluid in the region of the condenser 5 with a likewise simultaneously occurring increase in the high pressure p 0 and the evaporation temperature To in the range of the evaporation heat source 2 a.
  • the working fluid mass flow through z. B. the feed pump 6 can be increased.
  • Increasing the working fluid mass flow leads, via the increase in the heat transfer coefficient ⁇ , to an increased heat transfer flow dQ from the working fluid to the condenser environment.
  • Disadvantageous of an increase in the working fluid mass flow is the fact that, despite an increase in the heat transfer coefficient and the transferred heat, the amount of heat to be dissipated for complete condensation of the working fluid increases.
  • a preferred embodiment takes into account that, especially in a high-load operation of the evaporation heat source 2 of the heat utilization device 1, the capacitor 5 may no longer be able to dissipate the amount of heat completely and because of this complete condensation of the working fluid is no longer ensured. Particularly in this case, by raising the condensation temperature Tu of the working fluid, it is possible to increase the heat transfer current dQ. Since more heat can be transferred from the working fluid to the condenser environment, complete liquefaction of the working fluid is ensured again.
  • the ambient temperature of the condenser environment is taken into account and, if appropriate, the condensation temperature Tu of the working fluid is also adapted in a normal-load operation. This can be used at very high ambient temperatures z. B. be necessary in the summer to ensure complete liquefaction of the working fluid.
  • an advantageous embodiment can be equipped with a sensor device which determines the pressure and / or the temperature at at least one point of the cycle 21. Due to the at least one determined measured value, the low pressure pu is then adjusted. For this reason, it may be advantageous to determine the pressure and / or the temperature in the condenser 5, shortly after the expansion machine 3 and in the evaporation heat source. Also advantageous is the determination of the working fluid mass flow.
  • the cycle 21 is designed as a Clausius-Rankine cycle. Also conceivable, however, is the design as a Carnot cycle, as a Stirling cycle or the like.
  • a heat utilization device 1 which is used in the manner described above as a waste heat utilization device of an internal combustion engine, has the advantage that the entire heat utilization device 1 can be dimensioned smaller, without suffering damage in certain situations due to overheating.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un procédé visant à faire fonctionner un dispositif d'exploitation de chaleur (1), notamment d'un véhicule à moteur, ce dispositif d'exploitation de chaleur (1) comportant un fluide de travail qui, après expansion dans une machine à expansion (3) du dispositif d'exploitation de chaleur (1), est liquéfié par un condenseur (5) du dispositif d'exploitation de chaleur (1). L'ouverture d'une section transversale d'alimentation d'un fluide de travail du dispositif d'exploitation de chaleur (1) sur une machine à expansion (3) du dispositif d'exploitation de chaleur (1) permet, par une augmentation immédiate d'une basse pression (pU, pU*) du fluide de travail dans la zone du condenseur (5) et par une augmentation immédiate subséquente de la température de condensation (TU, TU*) du fluide de travail dans la zone du condenseur (5), d'accroître le flux de transfert de chaleur (dQ) du fluide de travail à la zone du condenseur et d'assurer ainsi une liquéfaction totale du fluide de travail dans le condenseur (5).
EP10710225A 2009-04-29 2010-03-18 Dispositif d'exploitation de chaleur et procédé de fonctionnement Withdrawn EP2425101A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009019385 2009-04-29
DE102009041550A DE102009041550A1 (de) 2009-04-29 2009-09-15 Wärmenutzungsvorrichtung und Betriebsverfahren
PCT/EP2010/001720 WO2010124765A2 (fr) 2009-04-29 2010-03-18 Dispositif d'exploitation de chaleur et procédé de fonctionnement

Publications (1)

Publication Number Publication Date
EP2425101A2 true EP2425101A2 (fr) 2012-03-07

Family

ID=42813796

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10710225A Withdrawn EP2425101A2 (fr) 2009-04-29 2010-03-18 Dispositif d'exploitation de chaleur et procédé de fonctionnement

Country Status (6)

Country Link
US (1) US20120096857A1 (fr)
EP (1) EP2425101A2 (fr)
JP (1) JP2012525528A (fr)
CN (1) CN102414400A (fr)
DE (1) DE102009041550A1 (fr)
WO (1) WO2010124765A2 (fr)

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DE102010063701B4 (de) * 2010-12-21 2019-02-07 Robert Bosch Gmbh Verfahren und Vorrichtung zur Nutzung von Abwärme einer Wärmekraftmaschine
DE102011003607A1 (de) * 2011-02-03 2012-08-09 Bayerische Motoren Werke Aktiengesellschaft Verfahren und System zum Betreiben einer Expansionsmaschine mittels dem Abgas eines Verbrennungsmotors entzogener Wärmeleistung
DE102011109384A1 (de) 2011-08-04 2012-02-09 Daimler Ag Brennkraftmaschine mit einer Wärmerückgewinnungsvorrichtung und Verfahren zum Betrieb einer Brennkraftmaschine
JP6097115B2 (ja) * 2012-05-09 2017-03-15 サンデンホールディングス株式会社 排熱回収装置
DE102013001569B4 (de) * 2013-01-30 2025-04-24 Mercedes-Benz Group AG Verfahren zum Betreiben einer Abwärmenutzungsvorrichtung

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Also Published As

Publication number Publication date
CN102414400A (zh) 2012-04-11
US20120096857A1 (en) 2012-04-26
JP2012525528A (ja) 2012-10-22
WO2010124765A3 (fr) 2011-10-13
WO2010124765A2 (fr) 2010-11-04
DE102009041550A1 (de) 2010-11-04

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