US20050072169A1 - Cooling system with refrigerant for air conditioning and lowering temperature of engine - Google Patents
Cooling system with refrigerant for air conditioning and lowering temperature of engine Download PDFInfo
- Publication number
- US20050072169A1 US20050072169A1 US10/729,947 US72994703A US2005072169A1 US 20050072169 A1 US20050072169 A1 US 20050072169A1 US 72994703 A US72994703 A US 72994703A US 2005072169 A1 US2005072169 A1 US 2005072169A1
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- Prior art keywords
- refrigerant
- engine
- water
- fluid
- cooling system
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Classifications
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- 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0437—Liquid cooled heat exchangers
- F02B29/0443—Layout of the coolant or refrigerant circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F02B29/0462—Liquid cooled heat exchangers
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- 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
- B60H2001/3286—Constructional features
- B60H2001/3289—Additional cooling source
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/02—Intercooler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/04—Lubricant cooler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
- F02M31/20—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for cooling
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- 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
- F25B2327/00—Refrigeration system using an engine for driving a compressor
- F25B2327/001—Refrigeration system using an engine for driving a compressor of the internal combustion type
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- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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- 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
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0082—Charged air coolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0089—Oil coolers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
A cooling system with refrigerant for air conditioning and engine parts, comprising: a compressor, a high pressure circuit filled with the refrigerant; and a low pressure circuit filled with the refrigerant too. The high pressure circuit further comprises a condenser, the low pressure circuit further comprises an evaporator and a heat exchanger, the heat exchanger at an interior thereof is provided with a refrigerant passage and a fluid passage, which enters the engine, with the two passages next to each other and contacting with each other and at an exterior thereof includes a refrigerant inlet, a refrigerant outlet, a fluid entrance to the engine and a fluid exit from the engine. Once the compressor is in a state of running, the refrigerant in the low pressure circuit passes through the evaporator and enters the refrigerant passage in the engine via a connecting pipe in the low pressure circuit and the refrigerant inlet and then flows out from the heat exchanger via the refrigerant outlet; a fluid for being cooled flows into the fluid passage via the fluid entrance and flows out from the fluid exit before reaching an engine body; and temperature of the fluid during entering fluid passage is higher than the refrigerant in the refrigerant passage and heat in the fluid transmits the refrigerant between a wall of the fluid passage and a wall of the refrigerant passage.
Description
- 1. Field of the Invention
- The present invention relates to a cooling system for a car engine system/device, and particularly to a cooling system/device, in which an ordinary car room air conditioning system with refrigerant, a compressor, heat dissipating fins and pipeline for circulating the refrigerant is utilized and expanded to provide a function of engine system cooling in addition to the car room air conditioning.
- 2. Description of Related Art
- The conventional car room air conditioning system, which includes refrigerant, a compressor, heat dissipating fins and pipeline for circulating the refrigerant, usually only provides a function of cooling car room space and not for cooling the engine system. On the other hand, the engine system generally is cooled by way of water circulation of the water box system passing through the engine body (water cooling type) or part of outside air being guided to the engine blowing the dissipating fins surrounding the engine (air cooling type) with the aid of oil circulation for heat dissipation.
- These traditional cooling systems for engine are designed to meet ordinary air temperature condition and driving requirement so that it is incapable of treating abnormally high air temperature situation and/or long period of engine running fiercely. It is very likely to result in excessively high engine system temperature and lead to engine parts being out of order and/or short life span. The cooling system of the present invention allows the engine system sharing part of the air conditioning capability (usually being surplus) such that the engine system can be cooled sufficiently So as to enhance work efficiency thereof and prolong life span of the parts therein.
- The crux of the present invention is to utilize the high temperature deduction capability obtained with the refrigerant type cooling system of car room air conditioning, in which a connecting pipe between the evaporator in the low pressure stage of the refrigerant type cooling system and a dehumidifying water collector at the middle section thereof is arranged to guide the refrigerant into a heat exchanger and the refrigerant passes through a refrigerant passage in the heat exchanger before flowing back to another connecting pipe between next evaporator section and dehumidifying water collector. One of embodiments in accordance with the present invention provides that heat exchanger covers a section of the intake pipe in front of the throttle valve and the engine intake pipe has a greater area contacting with pipe wall of the refrigerant passage.
- Another embodiment of the present invention provides that the intake pipe covered by the heat exchanger is replaced with the oil pipeline and the oil pipeline in the heat exchanger has smaller pipe diameter with a roundabout way so as to extend the length thereof in the heat exchanger as long as possible for increasing contact area with the refrigerant passage. Hence, the cooling system of the present invention can cool the intake air and/or the oil of the engine in addition to the car room air conditioning. As a result, it is capable of enhancing the engine efficiency, lowering chance of malfunction for the engine and prolonging lifetime thereof.
- The present invention can be more fully understood by reference to the following description and accompanying drawings, in which:
-
FIG. 1 is a plan view of pipeline illustrating a first embodiment of the present invention applied to cooling air intake of an engine; -
FIG. 2 is a plan view of pipeline illustrating a second embodiment of the present invention applied to cooling air intake of an engine sectional view of the pivotal shaft assembly shown inFIG. 1 ; -
FIG. 3 is a plan view of pipeline illustrating a third embodiment of the present invention applied to cooling air intake of an engine perspective view of another embodiment according to the present invention; -
FIG. 4 a is a plan view illustrating an embodiment of the present invention applied to cooling engine oil; -
FIG. 4 b is a plan view illustrating a further embodiment of the present invention applied to cooling engine oil; and -
FIG. 5 is a plan view illustrating a water spray cooling apparatus. - Referring to
FIG. 1 , a cooling system with refrigerant according to the present invention includes a compressor 1, apulley 2, a condenser 4, a connectingpipe 3, which is disposed between the compressor 1 and the condenser 4, afan 5 for the condenser 4, anexpansion valve 7, anevaporator 8, a connecting pipe 6, which is disposed between the condenser and theevaporator 8, acold air fan 9, adehumidifying water collector 11, a connectingpipe 10, which is disposed between the evaporator and the dehumidifying water collector and a connectingpipe 12, which is disposed between the dehumidifying water collector and the compressor. The preceding components are basic elements required for constituting a car room of an air conditioning system. The route from the compressor 1 and the connectingpipe 3 to theexpansion valve 7 via the condenser 4 is a high pressure stage and the route after theexpansion valve 7 to the connectingpipe 12 via theevaporator 8 is a low pressure stage. - The entire circulation cycle includes the high pressure stage and the low pressure stage and is filled with the refrigerant. The refrigerant is in a state of liquid at the high pressure stage and in a state of gas at the low pressure stage. The compressor 1 compresses the refrigerant coming from the low pressure stage and sends the pressurized refrigerant to the high pressure stage. The
expansion valve 7 admits the pressurized refrigerant to flow toward the low pressure stage only if the pressure in the high pressure stage exceeds the pressure in the low pressure stage a preset pressure difference. The preset pressure difference can secure the refrigerant in the high pressure stage with a high pressure being capable of being liquefied and the refrigerant in the low pressure stage with a low pressure being gasified under a normal condition with which appropriate amount of refrigerant is filled in the cycle and the ambient temperature is in a normal range. Of course, the refrigerant in the high pressure stage may keep in a state of gas due to high temperature without cooling aids of the condenser 4 and thecondenser fan 5 in spite of being high pressure. On the other hand, the refrigerant in the low pressure stage may keep in a state of liquid due to low temperature without heat collection aids of theevaporator 8 and thecold air fan 9 in spite of being low pressure. - The gaseous refrigerant from the low pressure stage is compressed with the compressor 1 and sent to the high pressure stage as liquid refrigerant such that the temperature of the refrigerant rises under high pressure because of heat absorbing previously and the heat can be dissipated effectively to outside with aids of the condenser 4, which is provided with large cooling area, and the
condenser fan 5. Then, the refrigerant passes through theexpansion valve 7 and enters the low pressure stage with lower heat. The refrigerant entering the low pressure stage decreases the pressure thereof largely in company with lowering the temperature thereof largely. The relationship of the pressure and the temperature can be expresses with the equation of ideal gas, PV=nRT, wherein, P is designated as pressure value, V is designated as volume of a container, n is designated as number of gas molecules, R is designated as a constant and T is designated as absolute temperature. - The
evaporator fan 9 blows the air coming from the car room or outdoors toward the evaporator 6 and finally to the car room as cold air via air conditioning pipeline and air outlet. As the foregoing, the refrigerant entering the low pressure stage has lowered the temperature thereof greatly and, in fact, the temperature thereof can drop below 0° C. In case of an older type of car air conditioning system (without microcomputer constant temperature control) for being used, the air outgoing pipeline may be blocked due to occurring freeze to result in outgoing air flow being less gradually till no air flow coming out if little air flow being blown out. Under this circumference, if the fan is turned up to the maximum capacity and it is switched to the mode of guiding in outside air, the temperature of the outside air is higher so as to melt the frozen pipeline and to restore the original air flow. However, the cold air becomes colder with vapor. This phenomenon proves temperature of the refrigerant in the low pressure stage can drop down below 0° C. - The highly efficient temperature reduction capability of the refrigerant type cooling system is utilized in the present invention so that a cooling block A of an engine system is introduced in the connecting
pipe 10, which is between the evaporator and dehumidified water collector in the low pressure stage. The cooling block A in the first embodiment includes aheat exchanger 20 surrounding a section of theintake pipe 21 at the front side of a throttle valve 213 (counted with intake air sequence) in the engine. Theheat exchanger 20 includes arefrigerant inlet 221, arefrigerant outlet 222 and aninternal refrigerant passage 22, which provides a greater area contacting with a section ofintake pipe 21 in theheat exchanger 20. The refrigerant passes through theevaporator 8 to enter therefrigerant passage 22 via the connectingpipe 10 and therefrigerant inlet 221 and then flows out theheat exchanger 20 via therefrigerant outlet 222. The engine intake air flows into a section of theintake pipe 21 via theair inlet 211 and then flows out theexchanger 20 via theair outlet 212 before reaching thethrottle valve 213. - Because the engine intake air has been cooled down highly efficiently during passing through the
heat exchanger 20 before entering the engine cylinder, the first embodiment of the present invention at least has the following effects: first, the gross heat of the intake air is decreased during entering the engine and it represses the engine to generate heat to a certain extent, that is, it reduces the temperature; next, due to air entering the engine having lower temperature and the engine intake pressure and the cylinder volume being unchanged, the number of gas molecules entering the engine increases according to the equation of ideal gas PV=nRT such that mixture of fuel and air in the cylinder can provide greater explosive power to enhance torque and horsepower or to save more fuel. The second effect is the same function as a light super charger mounted in a car and the air intake in the engine can increase accordingly. If an intermediate cooler do not equipped in the engine, temperature of the engine rises up during running regardless the super charger is turbine type or mechanical type. The cooling system for the engine intake air in the first embodiment of the present invention not only can increase the air intake but also can lower the engine temperature. - The embodiment shown in
FIG. 1 illustrates the path of the refrigerant flowing to thedehumidified water collector 11 from theevaporator 8 requires to pass through the cooling block A in the engine system. In fact, the entire refrigerant cycle can be designed as a cycle shown inFIG. 2 . It can be seen that there are parallel connectingpipes evaporator 8 and thedehumidifying water collector 11. The connectingpipe 10′ communicates with theevaporator 8 and thedehumidifying water collector 11 and the connectingpipe 10 at the middle section thereof is inserted with a cooling block A in the engine system such that the refrigerant, which flows to thedehumidifying water collector 11 from theevaporator 8 via the connectingpipe 10, has to passes through the cooling block A and performs cooling of the engine system. - The connecting
pipe 10 provides avalve 101 at least at an end thereof. Once the refrigerant cooling system is started by the user, the car room air conditioning can be performed regardless the cooling function of the engine system is effected or not. The cooling function of the engine system depends on if thevalve 101 being opened or closed. In case of thevalve 101 being opened, the refrigerant can pass through the connectingpipe 10 and the cooling block A to result in cooling function of the engine system. In case of thevalve 101 being closed, the refrigerant stops passing through the connectingpipe 10 and the cooling block A such that it is not possible to provide the cooling function of the engine system. Even if thevalve 101 has been opened and the engine system has performed the function of cooling the engine system in the embodiment, part of the refrigerant flows to thedehumidifying water collector 11 directly from theevaporator 8 via the connectingpipe 10. In order to allow the cooling function of the engine system being performed more effectively, a three-waysingle choice valve 102 can be mounted at a junction of the connectingpipe 10′ and the connectingpipe 10 as shown inFIG. 3 instead of thevalve 101, which only can be operated with the opening and the closing states. This design allows the user to select a way that the refrigerant only flows along the cooling block A of the engine system and provides a better cooling function for the engine system than the previous design or select another way that the refrigerant only passes through the connectingpipe 10′ directly for stopping the cooling function of the engine system. - The cooling block A of the cooling system with refrigerant according to the present invention can be used for cooling turbine super charging engine or mechanical charging engine in addition to using for natural air intake engine. The cooling block A can be joined to the intermediate cooler frequently utilized by the super charging system and is positioned closer the
throttle valve 213 than the intermediate cooler. The cooling system with refrigerant according to the present invention can lower air temperature in theintake pipe 21 below the ambient temperature. The conventional intermediate cooler is only possible to lower air temperature in theintake pipe 21 closer to the ambient temperature. Alternatively, the cooling block A of the cooling system with refrigerant according to the present invention can be used instead of the intermediate cooler frequently utilized by the super charging engine, which is responsible for lowering the temperature of the intake air. The intake air is often pressurized to occur temperature rise, and the effect is much better than the intermediate cooler. - Further, the cooling block A of the cooling system with refrigerant according to the present invention can be used for cooling engine oil in addition to being used for cooling natural air intake engine or intake air of the super charging engine. Referring to
FIGS. 4 a and 4 b, the cooling block A of the engine system for cooling engine oil is processed by that the refrigerant enters the connectingpipe 10 between the evaporator at the low pressure stage and the dehumidifying water collector and flows and finally flows out of theheat exchanger 20 to therefrigerant passage 22 in theheat exchanger 20 via therefrigerant inlet 221 to flow back to next section of the connectingpipe 10 between the evaporator and the dehumidifying water collector. The embodiment being different from the cooling system shown in FIGS. 1 to 3 is in that theengine intake pipe 21 included in theheat exchanger 20 contacting withrefrigerant passage 22 as shown in FIGS. 1 to 3 and anoil passage 21 included in theheat exchanger 20 contacting with therefrigerant passage 22 as shown inFIG. 4 . The engine oil enters theengine oil passage 21 in theheat exchanger 20 via theoil inlet 211 and flows out of the heat exchanger via theoil outlet 212 toward the next section of the oil circulation cycle. - Because temperature of the oil is pretty high during the engine running and the temperature much higher than that of the engine intake air, the
oil passage 21 in theheat exchanger 20 is provided with a smaller cross section or a smaller passage diameter and with a circuitous way so as to extend the length of the oil in theheat exchanger 20 as longer as possible and increase contact area of theoil passage 21 with therefrigerant passage 22 as shown inFIG. 4 a. Another way for increasing the contact area is to provide a plurality of parallel oil passages with smaller cross sections or smaller passage diameters connecting with theoil inlet 211 and theoil outlet 212 as shown inFIG. 4 a. The cooling system with refrigerant according to the present invention is capable of effectively lowering the temperature of the oil in the engine quickly such that it is possible to avoid malfunction and/or to prolong parts in the cooling system. - When the cooling system with refrigerant according to the present invention is applied to cool the engine oil, the refrigerant circuit outside the
heat exchanger 20 can be arranged as that illustrated in FIGS. 1 to 3 in which the through connectingpipe 10′, thevalve 101 and theswitch valve 102 can be included or excluded. - The cooling system with refrigerant according to the present invention can be attached with a water spray cooling device to cool each high temperature component in the engine chamber including the engine itself during the car running. Referring to
FIG. 5 , thewater spray device 50 includes awater trough 51, a water deliverpipeline 52, awater pump 53 and aspray nozzle 54. Thespray nozzle 54 is provided with small outgoing apertures for keeping water pressure so as to spray very fine water columns or mist columns with a shape of approximate straight lines. Thespray nozzle 54 can be mounted in front of a heat dissipating water box of the water cooling type engine or a heat dissipating fins of the air cooling type engine to face the water box or the fins. Once the car is moving, the air at the front side entering the engine is helpful for the water columns reaching the engine and other high temperature parts in the engine. Thewater spray nozzle 54 can mounted in front of the heat dissipating fins for oil and face the heat dissipating fins for oil to cool the oil. Alternatively, the water spray device includes twowater nozzles 54 to face the heat dissipating water box and the heat dissipating fins for oil respectively. - The
water trough 51 can be set up independently or the heat dissipating water box in the water cooling type engine can be used as thewater trough 51. Thewater pump 53 connects with alogic control unit 55 so that thewater pump 53 can run or stop running depend on instructions of thelogic control unit 55. Thelogic control unit 55 continuously receives a serious of signals from atemperature sensor 56 and the signals represent temperature values. The temperature values are compared constantly with preset temperature values under specific actuation conditions by thelogic control unit 55 and then thewater pump 53 is ordered to actuate an action of pressing water such that the pressed water can sprinkle via thenozzle 54. Thetemperature sensor 56 can be mounted to contact with the water box, the engine or the heat dissipating fins for oil to pick the data of temperatures there. The preset temperature values under specific actuation conditions in thelogic control unit 55 can be assigned in the factory or can be obtained by way of anactuation temperature adjuster 57 such as a turning knob or a plurality of buttons being connected to thelogic control unit 55. Thetemperature adjuster 57 also can include a device of temperature scale, digital display or analog display of temperature. - The user can adjust the preset actuation temperature to a little higher an average temperature of the water box, the oil or the engine under normal driving condition such that the
logic control unit 55 can order thewater pump 53 to press water out via thenozzle 54 once the detected temperature is higher than the preset actuation temperature and most mechanical parts in the engine room can reduce the temperature quickly. The nozzle can stop spraying the water once the detected temperature drops below the preset actuation temperature. Hence, the engine system of a car can keep a constant temperature during running. - While the invention has been described with reference to the preferred embodiments thereof, it is to be understood that modifications or variations may be easily made without departing from the spirit of this invention, which is defined by the appended claims.
Claims (11)
1. A cooling system with refrigerant for air conditioning and engine parts, comprising:
a compressor,
a high pressure circuit filled with the refrigerant; and
a low pressure circuit filled with the refrigerant too;
wherein, the high pressure circuit further comprises a condenser, the low pressure circuit further comprises an evaporator and a heat exchanger, the heat exchanger at an interior thereof is provided with a refrigerant passage and a fluid passage, which enters the engine, with the two passages next to each other and contacting with each other and at an exterior thereof includes a refrigerant inlet, a refrigerant outlet, a fluid entrance to the engine and a fluid exit from the engine;
whereby, once the compressor is in a state of running, the refrigerant in the low pressure circuit passes through the evaporator and enters the refrigerant passage in the engine via a connecting pipe in the low pressure circuit and the refrigerant inlet and then flows out from the heat exchanger via the refrigerant outlet; a fluid for being cooled flows into the fluid passage via the fluid entrance and flows out from the fluid exit before reaching an engine body; and temperature of the fluid during entering fluid passage is higher than the refrigerant in the refrigerant passage and heat in the fluid transmits the refrigerant between a wall of the fluid passage and a wall of the refrigerant passage.
2. The cooling system with refrigerant as defined in claim 1 , wherein the low pressure circuit further comprises a through pipe parallel to the heat exchanger to allow at least part of the refrigerant not passing through the heat exchanger during circulating in the cooling system.
3. The cooling system with refrigerant as defined in claim 2 , wherein the connecting pipe is provided with a valve adjacent to the refrigerant inlet of the heat exchanger to control the refrigerant passing through the heat exchanger.
4. The cooling system with refrigerant as defined in claim 2 , wherein the connecting pipe is provided with a valve adjacent to the refrigerant outlet of the heat exchanger to control the refrigerant passing through the heat exchanger.
5. The cooling system with refrigerant as defined in claim 2 , wherein a conjunction of at least a connecting pipe and the through pipe is provided with a one to two single switch valve to control the refrigerant passing through the heat exchanger or the through pipe only.
6. The cooling system with refrigerant as defined in claim 1 , wherein the fluid in the engine is intake air.
7. The cooling system with refrigerant as defined in claim 1 , wherein the fluid in the engine is engine oil.
8. The cooling system with refrigerant as defined in claim 1 , further comprises a water spray cooling device, which includes a water trough, a water delivering pipeline, a water pump and a nozzle, and the water nozzle is disposed in front of a heat dissipating water box of a water cooling type engine and face the heat dissipating water box.
9. The cooling system with refrigerant as defined in claim 1 , further comprises a water spray cooling device, which includes a water trough, a water delivering pipeline, a water pump, a nozzle, a logic control unit and a temperature sensor, with the water pump receiving an instruction of the logic control unit to pump or not pump water to the nozzle and the instruction of pumping water being based on if temperature data transmitted by the temperature sensor being greater than a preset value, wherein the nozzle is disposed in front of a heat dissipating water box of a water cooling type engine and face the heat dissipating water box.
10. The cooling system with refrigerant as defined in claim 1 , further comprises a water spray cooling device, which includes a water trough, a water delivering pipeline, a water pump and a nozzle, wherein the nozzle is disposed in front of and faces the heat dissipating fins for oil.
11. The cooling system with refrigerant as defined in claim 1 , further comprises a water spray cooling device, which includes a water trough, a water delivering pipeline, a water pump, a nozzle, a logic control unit and a temperature sensor, with the water pump receiving an instruction of the logic control unit to pump or not pump water to the nozzle and the instruction of pumping water being based on if temperature data transmitted by the temperature sensor being greater than a preset value, wherein the nozzle is disposed in front of and faces heat dissipating fins for oil.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW092217640 | 2003-10-01 | ||
TW092217640U TWM245304U (en) | 2003-10-01 | 2003-10-01 | Refrigerant cooling system featuring with dual functions of air conditioning and engine cooling |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050072169A1 true US20050072169A1 (en) | 2005-04-07 |
Family
ID=34390176
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/729,947 Abandoned US20050072169A1 (en) | 2003-10-01 | 2003-12-09 | Cooling system with refrigerant for air conditioning and lowering temperature of engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US20050072169A1 (en) |
JP (1) | JP3102322U (en) |
KR (1) | KR200344422Y1 (en) |
AU (1) | AU2003266788A1 (en) |
TW (1) | TWM245304U (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2020316A1 (en) * | 2007-07-31 | 2009-02-04 | Behr GmbH & Co. KG | Reservoir for cooling a mainly gaseous fluid designed for motor charging |
DE102011113242A1 (en) | 2011-09-13 | 2012-03-29 | Daimler Ag | Circuit arrangement for cooling motor car, has vehicle component cooling circuit branched in flow direction of coolant to expansion valve, where coolant circulates in entire arrangement until phase transition undergoes in exchangers |
CN102410113A (en) * | 2011-11-25 | 2012-04-11 | 无锡市豫达换热器有限公司 | Fuel oil cooler assembly |
WO2014058293A1 (en) * | 2012-10-10 | 2014-04-17 | Kineflux Sdn Bhd | Intercooler for vehicular engine |
CN105222385A (en) * | 2015-10-20 | 2016-01-06 | 西安交通大学 | A kind of Trans-critical cycle CO 2combined heat-pump system |
US20160231043A1 (en) * | 2013-10-17 | 2016-08-11 | Carrier Corporation | Air intake for refrigerated container assembly |
DE102015215164A1 (en) | 2015-08-07 | 2017-02-09 | Continental Automotive Gmbh | Thermal management system for a motor vehicle and method for operating a thermal management system for a motor vehicle |
CN106855015A (en) * | 2015-12-08 | 2017-06-16 | 福特环球技术公司 | Engine air path cooling system |
US10830122B2 (en) | 2018-10-29 | 2020-11-10 | Fca Us Llc | Intake and charge air cooling system |
CN112963239A (en) * | 2020-03-11 | 2021-06-15 | 宜康新方有限公司 | Air cooling chamber assembly and internal combustion engine with air cooling chamber assembly |
US11680515B1 (en) | 2022-03-31 | 2023-06-20 | Fca Us Llc | Intake and charge air cooling system with passive variable charge enabler |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108005781A (en) * | 2018-01-09 | 2018-05-08 | 重庆智仁发电设备有限责任公司 | Constant-temperature low-noise sound generating set |
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- 2003-10-01 TW TW092217640U patent/TWM245304U/en not_active IP Right Cessation
- 2003-12-09 US US10/729,947 patent/US20050072169A1/en not_active Abandoned
- 2003-12-09 AU AU2003266788A patent/AU2003266788A1/en not_active Abandoned
- 2003-12-17 JP JP2003273181U patent/JP3102322U/en not_active Expired - Fee Related
- 2003-12-23 KR KR20-2003-0039942U patent/KR200344422Y1/en not_active IP Right Cessation
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US3441011A (en) * | 1967-09-05 | 1969-04-29 | Thomas M Karl | Apparatus for controlling intake air temperature |
US4480439A (en) * | 1981-01-16 | 1984-11-06 | Nissan Motor Company, Limited | Supply-air cooling system for an engine including a turbocharger |
US6394076B1 (en) * | 1998-09-23 | 2002-05-28 | Duane L. Hudelson | Engine charge air cooler |
US6796134B1 (en) * | 2003-08-05 | 2004-09-28 | Daimlerchrysler Corporation | Charge air intercooler having a fluid loop integrated with the vehicle air conditioning system |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2020316A1 (en) * | 2007-07-31 | 2009-02-04 | Behr GmbH & Co. KG | Reservoir for cooling a mainly gaseous fluid designed for motor charging |
DE102011113242A1 (en) | 2011-09-13 | 2012-03-29 | Daimler Ag | Circuit arrangement for cooling motor car, has vehicle component cooling circuit branched in flow direction of coolant to expansion valve, where coolant circulates in entire arrangement until phase transition undergoes in exchangers |
CN102410113A (en) * | 2011-11-25 | 2012-04-11 | 无锡市豫达换热器有限公司 | Fuel oil cooler assembly |
WO2014058293A1 (en) * | 2012-10-10 | 2014-04-17 | Kineflux Sdn Bhd | Intercooler for vehicular engine |
US20160231043A1 (en) * | 2013-10-17 | 2016-08-11 | Carrier Corporation | Air intake for refrigerated container assembly |
EP3058292B1 (en) * | 2013-10-17 | 2021-01-27 | Carrier Corporation | Air intake for refrigerated container assembly |
DE102015215164A1 (en) | 2015-08-07 | 2017-02-09 | Continental Automotive Gmbh | Thermal management system for a motor vehicle and method for operating a thermal management system for a motor vehicle |
CN105222385A (en) * | 2015-10-20 | 2016-01-06 | 西安交通大学 | A kind of Trans-critical cycle CO 2combined heat-pump system |
CN106855015A (en) * | 2015-12-08 | 2017-06-16 | 福特环球技术公司 | Engine air path cooling system |
US10830122B2 (en) | 2018-10-29 | 2020-11-10 | Fca Us Llc | Intake and charge air cooling system |
CN112963239A (en) * | 2020-03-11 | 2021-06-15 | 宜康新方有限公司 | Air cooling chamber assembly and internal combustion engine with air cooling chamber assembly |
US11680515B1 (en) | 2022-03-31 | 2023-06-20 | Fca Us Llc | Intake and charge air cooling system with passive variable charge enabler |
Also Published As
Publication number | Publication date |
---|---|
AU2003266788A1 (en) | 2005-04-21 |
TWM245304U (en) | 2004-10-01 |
JP3102322U (en) | 2004-07-02 |
KR200344422Y1 (en) | 2004-03-09 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |