US20050016193A1 - Cooling system - Google Patents

Cooling system Download PDF

Info

Publication number
US20050016193A1
US20050016193A1 US10/896,258 US89625804A US2005016193A1 US 20050016193 A1 US20050016193 A1 US 20050016193A1 US 89625804 A US89625804 A US 89625804A US 2005016193 A1 US2005016193 A1 US 2005016193A1
Authority
US
United States
Prior art keywords
cooling system
exhaust gas
engine
refrigerant
cooling
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.)
Abandoned
Application number
US10/896,258
Other languages
English (en)
Inventor
Nicolai Tarasinski
Joachim Sobotzik
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Assigned to DEERE & COMPANY reassignment DEERE & COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SOBOTZIK, JOACHIM, TARASINSKI, NICOLAI
Publication of US20050016193A1 publication Critical patent/US20050016193A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3201—Cooling devices using absorption or adsorption
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3201—Cooling devices using absorption or adsorption
    • B60H1/32011—Cooling devices using absorption or adsorption using absorption, e.g. using Li-Br and water
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3201—Cooling devices using absorption or adsorption
    • B60H1/32014—Cooling devices using absorption or adsorption using adsorption, e.g. using Zeolite and water
    • 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
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • F01P9/06—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00 by use of refrigerating apparatus, e.g. of compressor or absorber type
    • 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
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • 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
    • 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
    • F02B29/0481—Intake air cooling by means others than heat exchangers, e.g. by rotating drum regenerators, cooling by expansion or by electrical means
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • 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
    • 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
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0475—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly the intake air cooler being combined with another device, e.g. heater, valve, compressor, filter or EGR cooler, or being assembled on a special engine location
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
    • 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 an engine driven agricultural tractor cooling system with a main cooling system containing a coolant.
  • the rate of thermal output that can be rejected by a conventional cooling system is essentially determined by parameters such as the size of the surface of a cooler, heat transmission coefficients, flow velocities of the coolant, and by temperature differences of the associated media (surroundings, coolant, etc.).
  • the thermal output of conventional cooling systems is determined generally by the size of the available space of the configuration and the maximum allowable temperature difference. For a water-based cooling system, cooling this maximum temperature difference is a result of the maximum surrounding temperature and the highest allowable cooling water temperature.
  • Various cooling systems are known which achieve more efficient cooling with maximum prevailing temperature differences.
  • published German patent application DE 198 54 544 describes a cooling system for a supercharged engine with an improved cooling capacity.
  • This cooling system includes a high temperature cooling circuit and a low temperature cooling circuit.
  • the high temperature cooling circuit includes in a main branch, the engine, a high temperature re-cooler, and a branch circuit with a high temperature charge air cooler.
  • the low temperature cooling circuit includes a low temperature re-cooler in series with a low temperature charge air cooler.
  • this system also includes an engine oil/gearbox oil heat exchanger and a heat exchanger for cooling electronic components.
  • the heat rejected in the engine oil/gearbox oil heat exchanger is rejected at a relatively high temperature level, while the electronic components and the charge air is cooled simultaneously at a lower temperature.
  • this cooling system is costly, and the resulting temperature levels are not appropriate for the cooling of a supercharged engine of an agricultural tractor.
  • the system includes an adsorption refrigeration arrangement in which liquid refrigerant is evaporated, in order to extract the heat required for it from a liquid or gaseous medium for the generation of low temperatures.
  • the evaporated refrigerant is conducted to a sorbent to be adsorbed.
  • the sorbent loaded with refrigerant is heated in order to desorb the refrigerant again, and the refrigerant is subsequently liquified in order to make it available for renewed evaporation.
  • the heat rejected by the engine is used to heat the sorbent.
  • the system includes methanol as refrigerant and activated charcoal as sorbent.
  • this absorption refrigeration system is configured for the air conditioning of a vehicle, and appears to be inappropriate for the cooling of individual components of a supercharged engine, particularly that of an agricultural tractor.
  • other potential sources of heat such as the engine exhaust, cannot be utilized for the high temperatures required for the desorption in the adsorption refrigeration machine disclosed by published German patent application DE 199 27 879 A1 because extensive design-engineering changes would be required.
  • an object of this invention is to provide a cooling system which reduces the thermal load on a conventional main cooling system.
  • a further object of the invention is to provide such a cooling system for an engine block or a charge air cooling system.
  • a cooling system includes a known sorption cooling system.
  • the sorption cooling system includes an evaporator for evaporating a refrigerant, a sorption chamber containing an absorbent which absorbs the evaporated refrigerant, a desorption chamber for desorption of the refrigerant from the absorbent and a condenser for condensing the refrigerant.
  • a first exhaust gas stream of the engine is communicated to the desorption chamber.
  • the evaporator provides additional cooling of the coolant of the main cooling system, and/or cools a second exhaust gas stream from the engine.
  • the heat removed by the sorption cooling system or the heat removed by the evaporator can be delivered to the surroundings at a considerably higher temperature level by the condensation of the refrigerant.
  • higher temperature differences to the surroundings can be realized and hence a more compact configuration of coolers is possible.
  • the evaporator can be positioned to extract heat from other components, such as, for example, the engine itself, parts of the mechanical power transmission, components of the power electronic system, electrical machines, the vehicle cab, the charge air, a recirculated exhaust gas stream or any other components that can be cooled contained in or on the vehicle.
  • this cooling system can be used to cool fluids such as engine oil or gearbox oil.
  • the sorption cooling system extracts heat from the conventional main cooling system, at a cost in thermal output.
  • thermal output supplies the power for the sorption cooling system.
  • a “thermal compressor” is realized in contrast to the mechanically driven compressors which are widely used in refrigeration machines and in air conditioners.
  • the thermal output required to drive the sorption cooling system is extracted from the vehicle, preferably from the exhaust gas of the engine.
  • the rejected heat of the engine or the engine cooling water or any other available source of heat in the vehicle could be used.
  • the process where a material is taken up selectively by another material is known as absorption or adsorption.
  • the process is known as sorption.
  • the sorbing material is referred to as a sorbent.
  • the material that is sorbed is the sorbate. “Desorption” is the regeneration or the separation of the material that was sorbed.
  • Absorption is the process in which gases are taken up by fluids or solids, wherein the dissolved gas component is the absorbent and the fluid (solvent) is the absorbate.
  • Desorption is the reverse of the absorption, wherein gas is driven off at increased temperature and/or reduced pressure and the solvent is regenerated.
  • Adsorption is the deposition of gases and dissolved materials (adsorbate) on the surface of solids (adsorbent), for example, the binding of steam as adsorbate to an activated charcoal adsorbent. Adsorption takes place not only on the outer surface of the absorbent, but also in its pores, as long as these are accessible to the absorbate. During the adsorption process, the heat of adsorption is liberated. The heat of adsorption is approximately of the magnitude of the heat of condensation. Important adsorbents are activated charcoal, silica jell, aluminum oxide or even fullers earth.
  • desorption is the reverse of the absorption or adsorption process at higher temperatures or lower pressures where absorbed or the adsorbed material is regenerated.
  • An absorption cooling system operates with a liquid solvent as sorbent or absorbent, and an adsorption cooling system operates with a solid sorbent.
  • An absorption cooling system will include an absorbent and an absorbate, such as, for example, a solvent and a refrigerant, where the refrigerant is absorbed by the solvent and is again separated from it in the desorption process.
  • an absorbent and an absorbate such as, for example, a solvent and a refrigerant
  • lithium bromide absorbs water, and water absorbs ammonia.
  • the material absorbed functions as a refrigerant (absorbate), while the other material functions as a solvent (absorbent).
  • the refrigerant and the solvent are together characterized as an operating pair.
  • the solution of the materials is heated in order to separated them from each other again in the desorption chamber (boiler or separator).
  • the refrigerant evaporates first because of its lower evaporation temperature.
  • the evaporated refrigerant is freed from the rest of the solvent with which it had been evaporated by means of a liquid separator.
  • the refrigerant is cooled in the condenser (liquefier) and thereby liquified.
  • the pressure of the refrigerant is reduced to an evaporation pressure corresponding to a predetermined temperature by a control valve.
  • the refrigerant is evaporated by absorbing heat, and the heat absorbed provides the cooling effect.
  • the refrigerant vapor is conducted into the sorption chamber.
  • the pressure of the solvent (absorbate) is reduced by a valve to the sorption chamber pressure, cooled and conducted to the sorption chamber. Thereby, the solvent takes up the refrigerant vapor in the sorption chamber.
  • a solvent pump conducts the enriched solution back to the ejector, the circulation is thereby closed.
  • the entire solvent circulation operates as a “thermal compressor”, and functions as a compressor of a compression refrigeration machine.
  • the amount of heat required for the evaporation QO and the amount of heat required for the desorption QH can be derived from differing vehicle components, so that the amount of heat that is to be rejected by the main cooling system is reduced, and that the amount of heat required for the evaporation QO is derived from the main cooling system.
  • the system operates more effectively with higher temperature of the cooling water of the main cooling system.
  • the tendency to raise the pressure level in the main cooling circuit in order to attain correspondingly higher allowable temperatures therefore promotes the possibilities of the absorption cooling systems.
  • the driving temperatures for the ejection lie between 90° C. and 140° C., where the medium or the components to be cooled can assume similar temperatures as with the cooling with an adsorption cooling system.
  • An adsorption cooling system includes an adsorption chamber filled with a sorbent or an adsorbent, and a desorption chamber filled with an adsorbent, a condenser and an evaporator.
  • adsorption cooling system in an adsorption cooling system various pairs of materials are possible.
  • the adsorbent may be for example, silica gel, and the refrigerant may be adsorbate water. It is also known to use activated charcoal as adsorbent and methanol as adsorbate. The process is discontinuous and closed.
  • the water (adsorbate) adhering to the silica gel (adsorbent) is driven out in the desorption chamber with the supply of an amount of heat QH by a heated water circulation associated with the desorption chamber.
  • the water is liquified in the condenser and heat is carried away by the cooling water circuit associated with the condenser.
  • the condensate is sprayed into the condenser and evaporated under strong negative pressure.
  • An amount of heat QO is extracted from the surroundings or from a component that is to be cooled.
  • the water vapor is adsorbed in the adsorption chamber and the resulting heat of adsorption is conducted to a cooling water circuit associated with the adsorption chamber.
  • the desorption of the adhering water and the generation of pressure for the condensation occurs at low temperatures of 60° C.-70° C., so that this technology can be applied at lower temperatures than with an absorption cooling system.
  • Such a sorption cooling system can be driven “at no cost” by heat sources available on the vehicle, for example, the exhaust gas, instead of mechanical power required by compressors.
  • the cooling capacities of a conventional cooling system can be reduced, and the amount of heat that must be removed in a water-to-air heat exchanger from the engine is reduced, thereby reducing the load on the main cooling system, and it is possible to remove heat at a higher temperature than in a conventional cooling system.
  • the energy required for cooling of further components can be minimized and fuel consumption can be reduced.
  • mechanical or electrical compressor drive units can be omitted or their size reduced.
  • various fluids and tractor components can be cooled to temperatures below the temperature of the surroundings.
  • a cooling system with a compressor fewer moving parts are required, and hence fewer components are subject to wear. Beyond that, the exhaust back pressure is not increased with the heat exchanger outside at the exhaust pipe of the vehicle.
  • a first exhaust gas stream of the engine is an exhaust gas stream of an exhaust gas recirculation system, so that the heat required for desorption is extracted from the vehicle exhaust gas recirculation system.
  • This advantageously cools the recirculated exhaust gas, and when the recirculated exhaust gas reaches the engine combustion chamber it results in a reduced heating of the charged air and thereby an improved charging or improved emission values can be obtained during the combustion.
  • the first exhaust gas stream is branched off from the main exhaust gas stream delivered to the environment.
  • the heat of an exhaust gas stream can be used to drive the desorption chamber, thereby improving the total energy balance of the vehicle.
  • the main cooling system is a charge air cooling system and that the evaporator of the sorption cooling system is used for additional cooling of the charge air cooling system.
  • the charge air cooling system can be configured more efficiently, or the cooling performance for the charge air can be improved so that an increased amount of charge air reaches the engine combustion chamber. This improves emission values.
  • the main cooling system is an engine block cooling system and that the evaporator of the sorption cooling system is used for additional cooling of the engine block cooling system. This reduces the load on the main engine cooling system. This can be utilized either to reduce the required cooler volume or, if necessary, to increase the entire cooling capacity.
  • the main cooling system is an air conditioner cooling system and that the evaporator of the sorption cooling system is used for additional cooling of the cab air flow.
  • This permits a reduced size of the air conditioner compressor, and less mechanical energy needs to be drained away from the vehicle. This, in turn, leads to an improved total energy balance of the vehicle and hence a lower fuel consumption.
  • the second exhaust gas stream is an exhaust gas stream of an exhaust gas recirculation system, where the evaporator of the sorption cooling system cools the exhaust gas in the exhaust gas recirculation system.
  • the heat of the exhaust gas is used to drive the desorption chamber, thus improving the total energy balance of the vehicle.
  • Another advantage is that the recirculated exhaust gas is cooled, and upon the recirculation of the exhaust gas into the engine combustion chamber, heating of the charge air is reduced, thereby improving air charge or emissions during the combustion.
  • the condenser is connected with a cooler, which carries away the heat liberated in the condenser.
  • the amount of heat generated by condensing the refrigerant (sorbent) can thereby be efficiently delivered to the surroundings, and heat is transferred at a higher temperature.
  • the sorption chamber is connected with a cooler which carries away the heat liberated in the sorption chamber.
  • FIG. 1 is a schematic block diagram of a cooling system according to the invention with a sorption cooling system to reduce the load on a charge air cooling circuit;
  • FIG. 2 is a schematic block diagram of a sorption cooling system which reduces the load on the charge air cooling system
  • FIG. 3 is a schematic block diagram of a cooling system according to the invention with a sorption cooling system which reduces the load on the cooling circuit for an internal combustion engine;
  • FIG. 4 is a schematic block diagram of a cooling system according to the invention with a sorption cooling system which cools an exhaust gas recirculation system;
  • FIG. 5 is a schematic block diagram of a cooling system according to the invention with a sorption cooling system which reduces the load on a cab air cooling system.
  • FIG. 1 shows a cooling system 10 for an internal combustion engine 12 with a charge air system 14 , a charge air cooling system 16 , an engine cooling system 18 , an exhaust gas recirculation system 20 , and a sorption cooling system 22 .
  • the sorption cooling system 22 is applied in order to reduce the load on the charge air cooling system 16 .
  • the engine 12 includes an intake system 24 which is supplied with super charged and cooled air 26 and recirculated exhaust gas 28 .
  • the recirculated exhaust gas 28 is withdrawn from the exhaust gas stream 30 flowing out of the engine 12 and conducted to the intake system 24 of the engine 12 .
  • the exhaust gas recirculation system 20 By means of the exhaust gas recirculation system 20 , the amount of the exhaust gas delivered to the surroundings can be reduced and the emissions reduced.
  • the engine cooling system 18 is connected to the engine 12 over coolant lines 32 .
  • the coolant lines 32 are connected with an engine cooler 34 , so that a coolant (not shown) in the coolant lines 32 circulates between the engine cooler 34 and the engine 12 and carries away heat generated in the engine 12 to the engine cooler 34 .
  • the charge air system 14 is used, among other uses, to compress the intake air taken in from the surroundings so that an increased amount of air flows into the intake system 24 of the engine 12 , resulting in improved combustion of the fuel and thereby reducing emissions in the exhaust gas.
  • the charge air system 14 includes an air filter 36 that filters intake air taken in from the surroundings and from which the filtered intake air is conducted into a turbo-supercharger 38 .
  • the turbo-supercharger 38 includes a drive side (not shown) and a compressor side (not shown). The drive side of the turbo-supercharger 38 is driven by a drive exhaust gas stream 40 , where the drive exhaust gas stream 40 is also branched off from the exhaust gas stream 30 .
  • the intake air from the air filter 36 is compressed in the compressor side of the turbo-supercharger 38 .
  • This compression increases the density of the intake air and increases the heat of the intake air.
  • This heat has a negative effect on the combustion of the fuel, for which reason the charge air system 14 as a rule is also connected to a charge air cooling system 16 .
  • the charge air cooling system 16 includes a charge air cooler 42 which is connected over charge air coolant lines 44 with a heat exchanger 46 .
  • the heat exchanger 46 is positioned between the turbo-supercharger 38 and the intake system 24 so that a coolant (not shown) in the charge air coolant lines 44 circulates between the heat exchanger 46 and the charge air cooler 42 and cools a flow of heat coming from the compressed charge air on the charge air cooler 42 .
  • the sorption cooling system 22 includes a desorption chamber 48 arranged in the recirculated exhaust gas stream 28 , a condenser 50 associated with the desorption chamber 48 , a condenser cooler 54 connected by condenser coolant lines 52 for removing the heat liberated in the condenser, an evaporator 56 arranged at the charge air coolant lines 44 , and a sorption chamber 58 with a sorption chamber cooler 62 connected by sorption chamber coolant lines 60 for removing the heat liberated in the sorption chamber 58 .
  • FIGS. 2-5 At least some components similar to those shown in FIG. 1 and with the same reference numbers are also included in FIGS. 2-5 .
  • FIG. 2 illustrates the principle of operation of a cooling system wherein the sorption cooling system 22 reduces the load on the charge air cooling system 16 .
  • FIGS. 1 and 3 - 5 are omitted from FIG. 2 to better illustrate the operation of the cooling system 10 .
  • the sorption cooling system 22 of FIG. 2 includes a solvent circulation circuit 64 and a refrigerant circuit 66 .
  • the solvent circuit 64 includes the desorption chamber 48 driven by the recirculated exhaust gas stream 28 , a first control valve 68 , the sorption chamber 58 and a solvent pump 70 .
  • the refrigerant circuit 66 includes the desorption chamber 48 driven by the recirculated exhaust gas stream 28 , the condenser 50 , a second control valve 72 , the evaporator 56 and the sorption chamber 58 .
  • the condenser 50 and the sorption chamber 48 are each connected with a cooler 54 , 62 which delivers the thermal output to be carried away from the condenser 50 or the sorption chamber 58 to the surroundings.
  • the evaporator 56 of the sorption cooling system 22 is integrated into the charge air cooling circuit 74 of the charge air cooling system 16 .
  • the cooling system 10 includes a two-material mixture (not shown) in the solvent circuit 64 , which is located in the supply line 76 directed at the desorption chamber 48 .
  • the two-part mixture in the supply line 76 consists of a solvent (not shown) which is mixed with a refrigerant (not shown) for cooling and circulating in the refrigerant circuit 66 or which has sorbed this in the sorption chamber 58 .
  • the two-part mixture is conveyed by the solvent pump 70 into the desorption chamber 48 .
  • the two-part mixture is heated by the heat from the recirculated exhaust gas stream 28 .
  • the refrigerant taken up by the solvent has a lower evaporation temperature than the solvent, so that the refrigerant evaporates before the solvent evaporates. This causes the desorption of the refrigerant out of the solvent.
  • the refrigerant vapor desorbed in the desorption chamber 48 or driven out flows through a first connecting line 78 into the condenser 50 .
  • the refrigerant vapor is liquified in the condenser 50 where the thermal flow is carried away at a higher temperature level compared to a conventional cooling system and with a higher temperature difference between the condenser cooler 54 and condenser 50 .
  • the condensed or cooled refrigerant flows into the evaporator 56 over a supply line 80 controlled by the second control valve 72 .
  • the refrigerant is evaporated in the evaporator while taking up heat from the charge air cooling system 16 . Heat is thereby effectively withdrawn from the charge air cooling system 16 by the evaporator 56 or by the heat taken up by the refrigerant.
  • the cooling system 10 reduces the load on the charge air cooling system 16 , thereby either improves the cooling capacity of the charge air cooling system 16 or reduces the dimensions of the charge air cooling system 16 .
  • the refrigerant vapor flowing out of the evaporator 56 flows into the sorption chamber 58 .
  • the solvent circulating in the solvent circuit flows over the first control valve 68 into the sorption chamber 58 and is available to take up the refrigerant vapor or for the sorption of the refrigerant vapor.
  • the refrigerant vapor is taken up by the solvent or it is sorbed, thereby generating heat of solution that is carried away over the sorption cooler 62 .
  • the refrigerant flowing out of the evaporator that has not been evaporated or is still liquid is conducted over a further supply line 82 over the desorption chamber 48 and driven into the condenser 50 . Thereby, both circuits are closed, that is, the refrigerant circuit 66 and the solvent circuit 64 are closed.
  • the improved cooling performance relative to the charge air on the basis of lower combustion temperatures in the intake system 24 of the engine 12 improves emissions.
  • the cooling system 10 and the sorption cooling system 22 of FIG. 2 can also reduce the load on other main cooling systems or even for the cooling of the recirculated exhaust gas 48 . This is shown in FIGS. 3-5 .
  • the evaporator 56 is integrated into the engine cooling system 18 .
  • the heat removal of the engine cooling system 18 or the reduction of the load on the engine cooling system 18 is performed in the same way by the evaporator 56 , as is the case with the reduction of the load on the charge air cooling system 16 of FIG. 1 or 2 .
  • a separate exhaust gas stream 84 is branched off from the main exhaust gas stream 30 in order to drive the desorption chamber.
  • FIGS. 1 and 2 is also conceivable, in which the desorption chamber 48 is driven by the recirculated exhaust gas stream 28 as is shown in FIG. 3 with a desorption chamber 48 ′ driven by a recirculated exhaust gas stream.
  • FIG. 3 embodiment reduces the load on the engine cooling system 18 , either by increasing the cooling capacity of the engine cooling system 18 or by reducing the size of the engine cooling system 18 .
  • the sorption cooling system 10 can be used to cool the recirculated exhaust gas stream 28 , to improve combustion performance of the engine 12 and thereby reduce the load on the engine cooling system 18 and the charge air cooling system 16 , or improve the entire energy balance of the engine 12 . If the recirculated exhaust gas stream 28 is conducted without any cooling into the intake system 24 of the engine 12 , the charge air that was previously cooled by the charge air cooling system 16 is heated. This worsens emission performance of the engine 12 .
  • the evaporator 56 of FIG. 4 is integrated into the exhaust gas recirculation system 20 and heat is withdrawn from the recirculated exhaust gas stream 28 during the evaporation of the refrigerant in the evaporator 56 .
  • the separated exhaust gas stream 84 is also used to drive the desorption chamber 48 .
  • the evaporator 56 is integrated into an air conditioning cooling system (not shown).
  • an air conditioning cooling system (not shown).
  • a cab air stream 86 pre-cooled by a conventional, mechanically driven compressor (not shown), can be post-cooled or, in a reverse arrangement, also pre-cooled by the evaporator 56 and post-cooled by the compressor.
  • the other components of the cooling system of FIG. 5 can be arranged similarly to the embodiments of FIGS. 1-4 .
  • the reduced load on the air conditioning system by the desorption cooling system leads to smaller mechanically driven compressor and thereby reduces energy requirements for the air conditioning system.
  • the sorption cooling systems of FIGS. 1-5 can also be combined with each other.
  • several evaporators can be arranged in a parallel or a series circuit and used to cool the charge air, the recirculated exhaust gas, 58 , the engine cooling water and/or the cab air stream 86 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Optical Couplings Of Light Guides (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
US10/896,258 2003-07-22 2004-07-21 Cooling system Abandoned US20050016193A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10333219.7 2003-07-22
DE10333219A DE10333219A1 (de) 2003-07-22 2003-07-22 Kühlanordnung

Publications (1)

Publication Number Publication Date
US20050016193A1 true US20050016193A1 (en) 2005-01-27

Family

ID=33483005

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/896,258 Abandoned US20050016193A1 (en) 2003-07-22 2004-07-21 Cooling system

Country Status (4)

Country Link
US (1) US20050016193A1 (de)
EP (1) EP1500802B1 (de)
AT (1) ATE384194T1 (de)
DE (2) DE10333219A1 (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060144232A1 (en) * 2005-01-04 2006-07-06 Carrier Corporation Method for detecting a fault in an HVAC system
WO2007120581A1 (en) * 2006-04-12 2007-10-25 Questair Technologies Inc. Adsorptive intercooler
US20080092539A1 (en) * 2006-10-23 2008-04-24 Southwest Research Institute System And Method For Cooling A Combustion Gas Charge
US20090188734A1 (en) * 2008-01-30 2009-07-30 Kevin Gordon Braun Flow-Inducing Baffle For Engine Compartment Ventilation
US20120042665A1 (en) * 2010-08-18 2012-02-23 Remy Technologies, L.L.C. Reject heat driven absorption cooling cycle
CN103395353A (zh) * 2013-08-09 2013-11-20 天津大学 一种车载复合太阳能及尾气余热回收吸收式制冷系统
US9487075B2 (en) 2014-03-03 2016-11-08 Cnh Industrial America Llc Work vehicle with traction gearbox cooling
WO2016196198A1 (en) * 2015-05-29 2016-12-08 Thermo King Corporation Sorption system in a transport refrigeration system
CN106837520A (zh) * 2017-01-19 2017-06-13 成都叮当自动化设备有限公司 一种可预热的低温发动机
US9796240B2 (en) 2015-08-12 2017-10-24 Caterpillar Inc. Engine off vapor compression adsorption cycle
EP3214296A3 (de) * 2011-01-20 2017-11-22 Cummins Intellectual Properties, Inc. Rankine-kreislauf-wärmerückgewinnungssystem und -verfahren mit verbesserter agr-temperaturregelung
CN107867144A (zh) * 2016-09-27 2018-04-03 福特环球技术公司 用于冷却剂系统的方法和系统
US20180194196A1 (en) * 2017-01-06 2018-07-12 GM Global Technology Operations LLC Systems and methods utilizing heat pumps to recover thermal energy from exhaust gas
US10093147B2 (en) * 2016-09-27 2018-10-09 Ford Global Technologies, Llc Methods and systems for coolant system
US10281179B1 (en) * 2017-04-07 2019-05-07 David John Prezioso Replacement compressor assembly for an air conditioning system and method
WO2020020998A1 (de) * 2018-07-27 2020-01-30 Fahrenheit Gmbh Brennkraftmaschine mit ladelufttemperierung mittels einer sorptionsvorrichtung
US10634398B2 (en) * 2015-12-18 2020-04-28 Carrier Corporation Heating, ventilation, air conditioning and refrigeration system
US10648710B2 (en) * 2016-03-30 2020-05-12 Kabushiki Kaisha Toyota Chuo Kenkyusho Heat pump system and cooling generation method
US11725667B2 (en) 2019-12-30 2023-08-15 Cnh Industrial America Llc Air source system of an agricultural system

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2886222B1 (fr) * 2005-05-30 2008-12-05 Giat Ind Sa Dispositif de gestion de l'energie thermique pour un vehicule
DE102010049918A1 (de) 2010-10-28 2011-06-30 Daimler AG, 70327 Aufgeladene Brennkraftmaschine eines Kraftfahrzeuges
KR101271762B1 (ko) 2010-12-16 2013-06-05 삼성중공업 주식회사 과급기가 설치된 선박의 흡입공기 냉각시스템
DE102011115018A1 (de) 2011-06-21 2013-01-10 Günter Kreitz Sonnenkollektoren, Heizkörper, Kühlkörper
DE102012221569A1 (de) * 2012-11-26 2014-05-28 Robert Bosch Gmbh Kühlvorrichtung für einen Verbrennungsmotor
DE102013215608A1 (de) * 2013-08-07 2015-02-12 Behr Gmbh & Co. Kg Kühlsystem und zugehöriges Betriebsverfahren
DE102015224593A1 (de) * 2015-12-08 2017-06-08 Mahle International Gmbh Ladeluftkühlvorrichtung für eine Frischluftanlage einer Brennkraftmaschine eines Kraftfahrzeugs
CN107172865A (zh) * 2017-06-29 2017-09-15 南京工业大学 一种使用喷雾冷却和吸附式制冷的机载高热流密度设备热管理系统
DE102020205168B3 (de) * 2020-04-23 2021-05-06 Bayerisches Zentrum für Angewandte Energieforschung e.V. Vorrichtung mit Verbrennungsmotor zur Erzeugung von elektrischer Energie und Sorptionswärmepumpe
DE102021105089B3 (de) 2021-03-03 2022-02-10 CM Fluids AG Kalorisches Fahrzeugmanagementsystem

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1806712A (en) * 1931-05-26 Cooling system foe
US2725044A (en) * 1952-09-19 1955-11-29 Andrew W Doyle Cooling system for internal combustion engines
US5383341A (en) * 1991-07-23 1995-01-24 Uri Rapoport Refrigeration, heating and air conditioning system for vehicles
US5896747A (en) * 1995-08-01 1999-04-27 Antohi; Valentin Vehicular absorption air conditioning process and system utilizing engine coolant waste heat
US6543411B2 (en) * 2000-02-26 2003-04-08 Daimlerchrysler Ag Method for generating a homogeneous mixture for auto-ignition internal combustion engines and for controlling the combustion process
US20030150434A1 (en) * 2000-07-28 2003-08-14 Leedham Stewart William Exhaust gas cooler with bypass tube and exhaust gas recirculation valve

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH248927A (de) * 1945-06-18 1947-05-31 Schweizerische Lokomotiv Verbrennungsmotor mit Vorkühlung.
DE19900965A1 (de) * 1999-01-13 2000-07-20 Volkswagen Ag Absorptionsklimaanlage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1806712A (en) * 1931-05-26 Cooling system foe
US2725044A (en) * 1952-09-19 1955-11-29 Andrew W Doyle Cooling system for internal combustion engines
US5383341A (en) * 1991-07-23 1995-01-24 Uri Rapoport Refrigeration, heating and air conditioning system for vehicles
US5896747A (en) * 1995-08-01 1999-04-27 Antohi; Valentin Vehicular absorption air conditioning process and system utilizing engine coolant waste heat
US6543411B2 (en) * 2000-02-26 2003-04-08 Daimlerchrysler Ag Method for generating a homogeneous mixture for auto-ignition internal combustion engines and for controlling the combustion process
US20030150434A1 (en) * 2000-07-28 2003-08-14 Leedham Stewart William Exhaust gas cooler with bypass tube and exhaust gas recirculation valve

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7494536B2 (en) * 2005-01-04 2009-02-24 Carrier Corporation Method for detecting a fault in an HVAC system
US20060144232A1 (en) * 2005-01-04 2006-07-06 Carrier Corporation Method for detecting a fault in an HVAC system
WO2007120581A1 (en) * 2006-04-12 2007-10-25 Questair Technologies Inc. Adsorptive intercooler
US20080092539A1 (en) * 2006-10-23 2008-04-24 Southwest Research Institute System And Method For Cooling A Combustion Gas Charge
US7721543B2 (en) * 2006-10-23 2010-05-25 Southwest Research Institute System and method for cooling a combustion gas charge
US20090188734A1 (en) * 2008-01-30 2009-07-30 Kevin Gordon Braun Flow-Inducing Baffle For Engine Compartment Ventilation
US8230957B2 (en) 2008-01-30 2012-07-31 Deere & Company Flow-inducing baffle for engine compartment ventilation
US8978395B2 (en) * 2010-08-18 2015-03-17 Remy Technologies, L.L.C. Reject heat driven absorption cooling cycle
US20120042665A1 (en) * 2010-08-18 2012-02-23 Remy Technologies, L.L.C. Reject heat driven absorption cooling cycle
EP3214296A3 (de) * 2011-01-20 2017-11-22 Cummins Intellectual Properties, Inc. Rankine-kreislauf-wärmerückgewinnungssystem und -verfahren mit verbesserter agr-temperaturregelung
US11092069B2 (en) 2011-01-20 2021-08-17 Cummins Inc. Rankine cycle waste heat recovery system and method with improved EGR temperature control
CN103395353A (zh) * 2013-08-09 2013-11-20 天津大学 一种车载复合太阳能及尾气余热回收吸收式制冷系统
US9487075B2 (en) 2014-03-03 2016-11-08 Cnh Industrial America Llc Work vehicle with traction gearbox cooling
US10571165B2 (en) 2015-05-29 2020-02-25 Thermo King Corporation Sorption system in a transport refrigeration system
US20180149393A1 (en) * 2015-05-29 2018-05-31 Thermo King Corporation Sorption system in a transport refrigeration system
WO2016196198A1 (en) * 2015-05-29 2016-12-08 Thermo King Corporation Sorption system in a transport refrigeration system
US9796240B2 (en) 2015-08-12 2017-10-24 Caterpillar Inc. Engine off vapor compression adsorption cycle
US10634398B2 (en) * 2015-12-18 2020-04-28 Carrier Corporation Heating, ventilation, air conditioning and refrigeration system
US10648710B2 (en) * 2016-03-30 2020-05-12 Kabushiki Kaisha Toyota Chuo Kenkyusho Heat pump system and cooling generation method
CN107867144A (zh) * 2016-09-27 2018-04-03 福特环球技术公司 用于冷却剂系统的方法和系统
US10093147B2 (en) * 2016-09-27 2018-10-09 Ford Global Technologies, Llc Methods and systems for coolant system
US10124647B2 (en) * 2016-09-27 2018-11-13 Ford Global Technologies, Llc Methods and systems for coolant system
US10807436B2 (en) 2016-09-27 2020-10-20 Ford Global Technologies, Llc Methods and systems for coolant system
US20180194196A1 (en) * 2017-01-06 2018-07-12 GM Global Technology Operations LLC Systems and methods utilizing heat pumps to recover thermal energy from exhaust gas
CN106837520A (zh) * 2017-01-19 2017-06-13 成都叮当自动化设备有限公司 一种可预热的低温发动机
US10281179B1 (en) * 2017-04-07 2019-05-07 David John Prezioso Replacement compressor assembly for an air conditioning system and method
WO2020020998A1 (de) * 2018-07-27 2020-01-30 Fahrenheit Gmbh Brennkraftmaschine mit ladelufttemperierung mittels einer sorptionsvorrichtung
US11725667B2 (en) 2019-12-30 2023-08-15 Cnh Industrial America Llc Air source system of an agricultural system

Also Published As

Publication number Publication date
ATE384194T1 (de) 2008-02-15
DE10333219A1 (de) 2005-02-24
EP1500802B1 (de) 2008-01-16
EP1500802A1 (de) 2005-01-26
DE502004005945D1 (de) 2008-03-06

Similar Documents

Publication Publication Date Title
US20050016193A1 (en) Cooling system
US7721543B2 (en) System and method for cooling a combustion gas charge
KR101759027B1 (ko) 자동차의 공기 조화 시스템 및 상기 공기 조화 시스템의 작동 방법
AU618509B2 (en) Absorption refrigeration method and apparatus
US5896747A (en) Vehicular absorption air conditioning process and system utilizing engine coolant waste heat
CA2742321A1 (en) Improved adsorption cooling system and adsorption cooling method for an aircraft
KR20110096179A (ko) 흡수 냉동기를 구비한 차량, 특히 자동차
KR102266401B1 (ko) 자동차 공조 시스템용 장치 및 이 장치를 작동시키기 위한 방법
CN202757337U (zh) 经济器螺杆式制冷压缩机组
CN103394267A (zh) 一种结合冷凝和吸附的油气回收装置
CN105143788B (zh) 组合蒸气吸收和机械压缩循环设计
EP2653691B1 (de) Einlassluftkühlsystem für ein schiff mit turbolader
CN102322706A (zh) 利用发动机余热驱动的车载制冷设备
JP2004340520A (ja) 冷凍サイクル装置
JP2014001876A (ja) 吸着式冷凍装置及びエンジン駆動式空調装置
KR100520100B1 (ko) 냉동시스템
US20190003749A1 (en) Heating, ventilation, air conditioning and refrigeration system
JP6724621B2 (ja) 車両用熱利用システム
KR200267157Y1 (ko) 냉동시스템
CN1292332A (zh) 汽车用溴化锂吸收式制冷装置
CN218501653U (zh) 一种矿井下用降温除水除油装置
CN214984730U (zh) 固体吸附制冷增强型汽车空调系统
CN215216753U (zh) 一种复叠式制冷机组
CN214164683U (zh) 电动客车及其空调系统
JPH03204569A (ja) 油噴射式スクリュー圧縮機を用いた冷凍方法ならびにヒートポンプ方法

Legal Events

Date Code Title Description
AS Assignment

Owner name: DEERE & COMPANY, ILLINOIS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARASINSKI, NICOLAI;SOBOTZIK, JOACHIM;REEL/FRAME:015626/0528

Effective date: 20040713

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION