WO2013063864A1 - 一种空气换热器 - Google Patents

一种空气换热器 Download PDF

Info

Publication number
WO2013063864A1
WO2013063864A1 PCT/CN2012/001467 CN2012001467W WO2013063864A1 WO 2013063864 A1 WO2013063864 A1 WO 2013063864A1 CN 2012001467 W CN2012001467 W CN 2012001467W WO 2013063864 A1 WO2013063864 A1 WO 2013063864A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
heat exchanger
fan
internal combustion
combustion engine
Prior art date
Application number
PCT/CN2012/001467
Other languages
English (en)
French (fr)
Inventor
陆加孚
Original Assignee
陆晨飞
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 陆晨飞 filed Critical 陆晨飞
Priority to US14/354,584 priority Critical patent/US9200848B2/en
Publication of WO2013063864A1 publication Critical patent/WO2013063864A1/zh

Links

Classifications

    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/06—Guiding or ducting air to, or from, ducted fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • B60K11/04—Arrangement or mounting of radiators, radiator shutters, or radiator blinds
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/10—Guiding or ducting cooling-air, to, or from, liquid-to-air heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
    • 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
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • 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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • 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
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/028—Cores with empty spaces or with additional elements integrated into the cores
    • 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
    • F28D2021/004—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for engine or machine cooling systems
    • 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
    • F28D2021/0091—Radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the present invention belongs to the field of electromechanical equipment such as I: machine, mobile vehicle, refrigeration, internal combustion engine, transformer, large machine tool, etc., and relates to a heat exchanger device, and more particularly to a high efficiency gas heat exchanger. Background technique
  • a heat exchanger using a fluid such as air as a cooling medium is an indispensable device in the fields of construction machinery, moving vehicles, internal combustion engines, small refrigeration machines, transformers, and the like.
  • a fluid such as air as a cooling medium
  • Such air heat exchangers are commonly referred to as radiators, 3 ⁇ 4 - air coolers, hydraulic oil radiators, EGR coolers, etc. in industries such as automobiles, construction machinery, and internal combustion engines.
  • the fluid that is cooled is sputum, compressed air, hydraulic oil, etc., and phase change does not occur.
  • air heat exchangers also known as condensers and evaporators, will undergo a phase change in the cooled fluid refrigerant.
  • Commonly used heat exchangers include heat exchanger cores, avalanches, and air hoods.
  • the fan is coupled to the drive power source via a coupling shaft.
  • the fan drive power source may be an electric motor or a hydraulic motor, and the power of the coupling shaft of the fan on the large moving vehicle comes to the mechanical energy of the crankshaft belt of the internal combustion engine.
  • this traditional radiator has many shortcomings, such as low heat exchange efficiency, high power consumption of the fan, and large wind noise.
  • the radiator is also limited by the layout of the main unit. Too tall.
  • the existing forced convection air-cooling heat exchanger utilizes only the side of the air passage to arrange the cross-flow heat exchanger, while the other side passage space is not utilized.
  • the blow-up heat exchanger uses only the positive-pressure air flow passage, and the other intake passage space is not well arranged and is vacant.
  • the same type of suction heat exchanger utilizes only the negative pressure air passage, while the other side space is not well utilized.
  • the existing 3 ⁇ 4 gas heat exchanger such as the cooling scheme towel of the vehicle ffl cold water radiator, the speed of the wind 3 ⁇ 4 is higher, and the design of improving the heat dissipation effect is mostly to increase the speed to increase the heat exchange capacity of the heat dissipation system, and heat exchange.
  • the performance f is lower.
  • the problem of air returning to the atmosphere at a large flow rate causes waste of kinetic energy and the wind efficiency is not too high. After the air flow rate increases to a certain limit, the effect of increasing the heat exchange capacity is not significant.
  • the noise of the fan is also very high.
  • the present invention provides a heat effect heat exchanger. While improving the heat transfer efficiency of the forced convection air heat exchanger, it is possible to reduce the noise and reduce the mechanical drive power consumption of the fan. In the mobile design, the height of the vehicle radiator can be appropriately reduced. Can be widely used in a variety of heat transfer applications.
  • the high-efficiency gas heat exchanger proposed by the invention comprises a mountain front heat exchanger, a wind J3 ⁇ 4, an air guiding cylinder and a rear end heat exchanger, wherein the fan is located in the air guiding cylinder, and the fan and the air guiding cylinder are formed.
  • a fan and a duct a front end heat exchanger and a rear end heat exchanger are respectively disposed on the upper and lower sides of the air duct; the front end heat exchanger and the rear end heat exchanger are respectively - a plurality of heat exchange unit stacks Jfl is formed: the cold fluid passage of the front end heat exchanger and the rear heat exchanger is connected by the heat exchange medium-element connecting pipe ⁇ ; after the front end heat exchanger and the rear end heat exchanger ⁇ are connected, the channel is cooled The overall flow direction of the fluid is opposite to the overall flow of the cold gas.
  • the fan composed of the wind and the air guiding cylinder is any one of an axial flow type, a centrifugal type, or a mixed flow type.
  • the fan is connected to a wind driven power source, and the wind flat driving power source is disposed outside the air duct or in the air duct.
  • the fan driving power source is located outside the air duct, the fan drive shaft is changed through the front end.
  • the power-receiving hole on the heat exchanger or the rear heat exchanger is connected to the fan, and the air-tight disk is arranged in the force-receiving hole.
  • the heat exchange unit 2 102 is a front end heat exchanger, and the heat exchange medium element 101 is a rear end heat exchanger.
  • the arrangement method of the heat exchange unit according to the requirements of the design target, such as the temperature requirements for the outflow of the fluid B and the fluid C, such as Tb2 ⁇ Tc2, the condition of flowing into the fluid B and the fluid C is Tel ⁇ Tbl o is obvious because Tc2 ⁇ Te l, so Tb2 ⁇ Tc2 ⁇ Tel ⁇ Tbl.
  • the heat exchange unit is arranged in the order of heat exchange unit 01, heat exchanger element 103, heat exchange unit 104, heat exchange unit. Element: 102, and the temperature of the fluid flowing out of and out of the heat exchange unit is Tb2 ⁇ Tc2 ⁇ Tel ⁇ Tbl, opposite to the flow of fluid A.
  • the fan 8 is disposed in the heat exchanger and the air duct. In this way, the fan efficiency can be improved, and the external noise of the fan is reduced due to being shielded.
  • the fan should be properly selected to overcome the increased wind resistance.
  • the present invention adopts a scheme in which the mechanical transmission shaft passes through the heat exchanger, so that the transmission shaft passes through the heat exchange.
  • the force hole directly drives the fan 8, and the fan 8 is in the air guiding cylinder 11 between the heat exchangers, and the force-receiving hole is provided with a gas-sealing disk to block the gas flow.
  • the technical solution provided by the present invention has the beneficial effects that: compared with the prior art, in the solution of the present invention, the ff countercurrent ⁇ combination and the wind upstream and downstream air ducts are arranged at the same time, and the axial excess is fully utilized.
  • the space can effectively increase the heat exchange capacity, improve the heat exchange efficiency, and capture the compactness of the heat exchanger. If the heat exchanger has better heat transfer capacity than the design requires If it is left, the fan speed can be reduced to achieve energy saving and noise reduction.
  • the solution of the invention has the advantages of saving mechanical energy, electric energy, and reducing the strength requirement of the fan material, and has strong adaptability.
  • the mountain is mature in technology and low in material prices. After ffl is widely used, it will recover the cost in a short period of time and create energy-saving benefits. It can be widely used in fields such as vehicle machinery and refrigeration machinery that require forced air-cooled heat exchange.
  • [0023] 1 is a schematic layout of the arrangement of the internal fan-equipped two-way cross-counter-flow heat exchanger of the present invention.
  • [0024] 2 is a schematic view of the arrangement of the '. ⁇ cross-countercurrent heat exchanger combination of the three-fluid internal airflow of the present invention.
  • [0025] 3 is a schematic structural diagram of an air cooling system of an engine of the present invention in a vehicle machine.
  • [0026] 4 is a schematic structural diagram of an air cooling system of an engine of the present invention in a vehicle machine.
  • [0027] 5 is a schematic structural view of an air cooling system of the present invention in a general-purpose machine.
  • [0029] 7 is a schematic diagram of the implementation structure of the 3 ⁇ 4 gas condenser group of the small air conditioning refrigeration system of the present invention.
  • Embodiment 1 See Figure 1, a high efficiency air heat exchanger schematic cabinet, including heat exchange unit 101, cooling fan 8, air duct 1 1, heat exchanger element connection tube 105 and heat exchange. Yuan: 102. 1.
  • the yuan: 102, the heat exchange element three 103 and the heat exchange element 104 are all in the transverse DC cross flow air heat exchanger, " ⁇ various forms, such as ⁇ Cold radiators, air-to-air coolers, air condensers, gas evaporators, etc. are all used in such heat exchange structure heat exchangers.
  • Element connection pipe 105 is connected, so that the front) ⁇ ⁇ '. yuan - 101, change unit: 102 ⁇ joint; cooling fluid ⁇ (cold air).
  • cooling fluid ⁇ cold air
  • the negative pressure difference caused by the rotation of the fan 8 enters the heat exchange ' ⁇ 101, heat exchanges with the fluid B in the heat exchange unit 101 at a temperature of tl, and heat exchange is performed by the cooling fluid A (cold air) passing through the transverse direction. After that, it enters the air duct 11 and is driven by the fan 8 in the air duct 1 1 to enter the heat exchange at a temperature of t (1).
  • the element 102 is exchanged with the cold fluid B in the heat exchange unit 102. Finally, it flows out at t2 temperature.
  • the high temperature fluid B first enters the heat exchange unit at the T1 temperature - 102 exchanges heat with the fluid A (air) at the temperature t (1) blown by the wind, and the fluid B flows out of the heat exchange unit at a temperature of T (1).
  • Fluid B enters the heat exchange unit 101 through the heat exchanger connection tube 105 at a temperature of T(1), and exchanges heat with a fluid ⁇ (air) at a temperature U of the heat exchange element, at a temperature of T2.
  • the heat exchange unit 101 flows out.
  • the flow direction of the cooling fluid A (air) is opposite to the overall flow direction of the cold fluid B, forming a two-way cross-countercurrent heat exchanger combination with a fan inside.
  • the heat exchange medium.: 102 is the front end heat exchanger, and the heat exchange unit 101 is the tantalum heat exchanger.
  • FIG. 2 is a three-fluid-fan cross-flow heat exchanger combination with a fan inside.
  • the heat exchange unit 104 and the heat exchange unit 102 are superposed into a front end heat exchanger, and the heat exchange unit 101 and the heat exchange unit 103 are superposed into a rear end heat exchanger.
  • the heat exchange unit is arranged according to the requirements of the design target, such as the temperature requirements for fluid enthalpy and fluid C, such as Tb2 ⁇ Tc2, and the condition of flowing fluid B and fluid C is Tel ⁇ Tbl. Obviously, because Tc2 ⁇ Tel, Tb2 ⁇ Tc2 ⁇ Te l ⁇ Tbl.
  • the heat exchange unit is arranged in the order of heat exchange unit 101, heat exchange unit 103, heat exchange unit 104, heat exchange unit 102, and the temperature of the fluid flowing out of and out of the heat exchange unit is Tb2 ⁇ Tc2 ⁇ Te l ⁇ Tbl , which is opposite to the flow direction of fluid A.
  • Embodiment 2 is a high-efficiency heat dissipation system for a vehicle internal combustion engine as shown in FIG. 3 and FIG.
  • a high efficiency air heat exchanger comprising an internal combustion engine exhaust muffler 1, an exhaust gas turbocharger 2, a compressor air outlet pipe 3, an air cleaner 4, an internal combustion engine cooling water outlet pipe 5, a wind pulley 6, a wind ⁇ Transmission shaft 7, wind ⁇ 8, water radiator coupling hose 9, intercooler coupling tube 10, air guiding cylinder 1 1, front end air chiller 12, front end radiator 13, rear radiator 14, rear end empty - Air cooler 15, internal combustion engine water pump inlet pipe 16, internal combustion engine intake pipe 17, internal combustion engine 18 and air sealing disk 19; wherein: internal combustion engine 18, front end radiator 13, rear radiator 14, internal combustion engine exhaust muffler 1, air filtration Unit 4 is coupled to the equipment chassis or bracket.
  • the front end - air cooler 12 and the rear end - air cooler 15 are respectively coupled to the front end heat radiator 13 and the rear end water radiator 14 by tight bolts.
  • the front end heat exchanger 13 and the end heat exchanger 14 are coupled to the air guiding cylinder 1 1 by bolts.
  • the front end air-air cooler 12 and the front end radiator 13 are connected by a tight ISI bolt to form a front end heat exchanger, and the rear end air-air cooler 15 and the rear end radiator 14 are superposed by fastening bolts. End heat exchanger.
  • the thermostat outlet pipe at the front end of the internal combustion engine 18 is coupled to the engine cooling water outlet pipe 5, and the internal combustion engine cooling water outlet pipe 5 is coupled to the rear end water radiator 14, and the end water radiator 14 and the front water radiator 13 pass through the water.
  • the radiator coupling hose 9 is connected, the front water radiator 13 ' j internal combustion engine water pump inlet pipe 16 is connected, and the internal combustion engine water inlet pipe 16 ' ⁇ internal combustion circulating cooling water pump is connected.
  • the air cleaner 4 is coupled to the compressor inlet of the exhaust gas turbocharger 2, and the compressor outlet of the exhaust turbocharger 2 is coupled to the compressor outlet pipe 3, and the compressor outlet pipe 3 1 ⁇ 2 ⁇ / ⁇ -air cooler 15 phase connection, rear end 3 ⁇ 4 - air cooler 15 and front end 3 ⁇ 4 air cooler 12 are connected by intercooler connecting pipe 10, ⁇ end space - air cooling
  • the compressor 12 is coupled to an internal combustion engine intake manifold 17 that is coupled to a cylinder intake manifold of the internal combustion engine 18.
  • the turbine interface of the exhaust gas turbocharger 2 is coupled to the cylinder exhaust of the internal combustion engine 18, and the turbine output of the exhaust turbocharger 2 is coupled to the internal combustion engine exhaust muffler 1 by bolts.
  • the side of the fan pulley 6 at the front end of the internal combustion engine 18 is coupled to the fan drive shaft 7 through a plurality of bolts, and the fan drive shaft 7 and the fan 8 are coupled by bolts.
  • the fan drive shaft 7 passes through; the end-air-air cooler 15 and the rear end heat exchanger 14 have power-removing holes, and the front and rear ends of the force-receiving holes are provided with a sealing disc 19 to ensure no air leakage.
  • the blade of the fan 8 needs to have a certain gap with the inner wall of the air guiding cylinder 11.
  • the crankshaft pulley transmits power to the fan pulley 6 through the belt, and the fan pulley 6 drives the fan 8 through the drive transmission shaft 7, and the blades of the fan 8 cut air in rotation, and the air flows from the right of the cabinet 3 Left flow.
  • the cold air enters the right end of the front-end air-air cooler 12 from the atmosphere laterally, passes through the core of the front-end air-air cooler 12, and cools the cold fluid high-temperature compressed gas therein; the cold air crosses from the front end heat exchanger The end face enters and passes through the core to cool the cold fluid internal combustion engine coolant in the front water radiator 13 and then enters the air duct 11.
  • the air After being driven by the fan 8, the air flows to the rear water radiator 14 and the rear end 3 ⁇ 4 - the air cooler 15, sequentially entering and cooling the internal combustion engine coolant and the rear air-cooler 15 in the core of the rear water radiator 14. High temperature compressed gas in the core.
  • the air flow after the completion of the cooling process flows out at a certain flow rate to the left end of the rear air-intercooler 15 to enter the atmosphere.
  • the cooling air flow and the high temperature compressed gas flow form a two-pass cross-countercurrent heat exchanger with a fan inside in the air-to-air coolers 12, 15.
  • the thermostat valve When the internal combustion engine 18 is in operation, if the internal circulation cooling temperature reaches the set value, the thermostat valve will be opened, and the high-temperature internal combustion engine coolant flows into the heat exchanger core of the rear end radiator through the internal combustion engine cooling water outlet pipe 5, and the air side. The flowing cold air undergoes the first heat exchange; the high-temperature internal combustion engine coolant flows out of the rear end radiator 14, and enters the core of the front end radiator 13 through the radiator coupling hose 9, and performs secondary heat exchange with the cold air flowing through the gas side.
  • the temperature of the coolant of the internal combustion engine is reduced to a certain value, and after passing through the water pump inlet pipe 16 of the internal combustion engine, the mountain circulating water pump draws water back into the internal circulation cooling system of the internal combustion engine 18.
  • the cooling air flow and the internal combustion engine cooling liquid flow are formed in the front end radiator 13 and the rear end radiator 14 to form a two-way cross-flow countercurrent heat exchanger having a fan inside.
  • the crankshaft pulley drives the fan pulley 6, the fan pulley 6 and the fan drive shaft 7 and the fan 8 are all tightly coupled, and the fan drive shaft 7 passes through the air-to-air cooler 15 and the rear end heat exchange.
  • the square-shaped force-receiving hole of the device 14; the fan 8 is rotatably driven to drive air flow.
  • a sealing disc 19 is installed at both ends of the square-shaped force-receiving hole of the air-to-air cooler 15 and the rear end heat exchanger 14 to prevent the flow of air, and the rounding hole allows the fan shaft 7 to pass through.
  • the air sealing disk 19 has a through hole, and the through hole diameter is slightly larger than the shaft diameter of the fan drive shaft 7. There is a certain gap between the blades of the fan 8 and the inner wall of the air duct 1 1 , which is related to the efficiency of the fan.
  • the front end 3 ⁇ 4 - the air cooler 12 and the front end radiator 13 are coupled by a tight W bolt, the S addition front end heat exchanger, and the rear end air-air cooler 15 and the rear end radiator 14 are coupled by fastening bolts , S plus back end heat exchanger.
  • cooling air (a fluid heat exchange device with a fluid of a high temperature compressed gas of a cold fluid and a coolant fluid of an internal combustion engine, forming an internal wind/3 Three-fluid two-way cross-countercurrent combined heat exchanger.
  • the front end radiator 13 and the rear end radiator 14 described herein are various cross-flow air-coolant heat exchange devices commonly used in the industry, and the
  • An integrated series counterflow air-cooling heat exchanger is arranged between the upstream and downstream air passages of the fan. This type of heat exchanger combination has the following characteristics:
  • the design of the multi-pass cross-counterflow combination is adopted to increase the heat exchange efficiency ⁇ of the system, which is similar to the existing radiator arrangement method.
  • the heat exchange capacity will increase.
  • the wind / * i double side 3 ⁇ 4 between the S radiator the total heat dissipation area is greatly increased, will increase the heat exchange capacity.
  • the above two measures work together to greatly increase the heat exchange capacity. If there is a surplus of heat exchange capacity, the flow of cooling air can be reduced: thus, the design speed F of the fan can be lowered. According to the mountain textbook, the air flow of the fan is proportional to the speed of the fan.
  • the fan drive power and fan noise pressure level are proportional to the cube of the fan speed.
  • the driving power of the fan 8 will be greatly reduced in proportion to the speed of the cube.
  • the crankshaft of the internal combustion engine increases the net power output and reduces the fuel consumption rate.
  • the fan speed is reduced, and the fan noise level is also reduced by the third power of the speed ratio.
  • nj adjusts a plurality of variables related to the heat sink, such as adjusting the windward area of the heat exchanger, adapting to a lower engine compartment, and bringing diversity and flexibility to the whole vehicle design.
  • the diameter of the fan can be appropriately reduced, and the material strength required for the wind can be reduced to reduce the cost.
  • Fan noise can be reduced. Due to the wind in the air duct 1 1 and the front radiator, the end radiator, the fan 8 cutting airflow noise can be shielded.
  • each heat exchange unit brings about the diversity of the heat exchanger layout design, and the front and rear passages of the wind 8 can be arranged to combine one or more radiators; the same-cooled fluid
  • the heat exchange unit can be connected to the electronically controlled switching valve through a plurality of heat exchange unit connecting pipes, and the electronically controlled switching valve performs a series combination, a parallel combination or a proportional switch part of the radiator channel under the control of the control program.
  • the function of intelligently adjusting the switching control of the heat exchanger cooling capacity is realized.
  • the fan 8 may be in the form of an axial flow suction fan or a blower, and the direction of the cooling pipe is also reversed when the wind direction changes.
  • the fan 8 in the cabinet 3 is a suction type.
  • Example 3 a general mechanical high efficiency air heat exchanger set as shown in Table 5.
  • the motor 20 is coupled to the fan drive shaft 7 through the bolts via the coupling 21, and the torque is transmitted to the fan 8, and the blades of the fan 8 rotate in the wind guide 1 1 respectively.
  • ⁇ 8 front and rear end faces generate positive and negative pressure
  • the cooling air enters the air duct 11 through the rear end heat sink 14 due to the negative pressure
  • the air is driven from the left to the side of the cabinet by the fan 8 to enter the front end radiator 13, which is respectively and/or the end
  • the heat fluid enthalpy in the radiator 14 and the front end radiator 13 is heat exchanged/twisted, and the hot air enters the atmosphere from the right end surface.
  • Pavilion 5 Stroke 8 is a hair dryer fan.
  • the hot fluid enthalpy enters from the main circulation system ⁇ into the front end radiator 13 and traverses the cold air espresso heat exchange, and then enters the rear end radiator 14 to exchange heat with the traversed cold air, the hot fluid A is Cool iil lHl to the host's circulatory system.
  • the electric motor 20 is a power source of the fan 8.
  • the power source may also be a mechanical power source such as a ffl hydraulic pump, a motor or a drive pulley.
  • Wind 3 ⁇ 4 form "J is an axial-flow suction fan or a blower fan. When the wind is changed, the wind direction is reversed.
  • This two-fluid countercurrent heat exchanger group can be widely used in the fields of automobiles, diesel locomotives, boring machines, transformers, and large machine tools. It is a cold fluid, such as coolant, cutting fluid, hydraulic oil, etc.
  • the refrigerant (superheated steam) is exchanged from the main circulation system pipe into the front condenser 23 to exchange heat with the traversing cold air, and the enthalpy is passed through the connecting copper pipe 22 into the rear condenser 24 and the cold air passing through After heat exchange, the refrigerant is condensed and returned to the main system's circulation system in a liquid state.
  • the front condenser 23 and the rear condenser 24 are commonly used equipment in the industry, and have a copper tube fin type, a tube belt type, etc., and are also in the category of heat exchangers. Again, this principle is used in the evaporation heat exchange of refrigerants.
  • the condenser and evaporator of the two-way counterflow heat exchanger combination can be widely applied to small and medium-sized refrigeration and air-conditioning machinery and other fields.
  • the wind type can be an axial flow suction fan or a blower.) When the wind direction changes, the direction of the cooling pipe also reverses accordingly.
  • Embodiment 2 The mainframes of Embodiment 2, Example 3, and Example 4 are all energy-consuming machines used for a long time, and the social quantity is ⁇ : (large, so energy saving and noise reduction are significant. Compared with modern human society I: large The increase in energy consumption and the skyrocketing energy prices in recent years, the use of commodities for energy-saving measures, the cost of equipment for manufacturing new heat exchangers is very low and affordable. ffl households will obviously benefit from energy conservation and will recover quickly. The cost of energy-saving equipment. The reduction of fan noise can improve the quality of the machine and bring environmental benefits.
  • the coolant radiator or the like can improve the heat exchange performance.
  • the power consumption of the fan will probably decrease.
  • the sound pressure level of the fan noise can also be reduced.

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)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种空气换热器，包括前端换热器（101）、风扇（8）、导风筒（11）、后端换热器（102）、风扇动力源（20）和风扇传动轴（7），前端换热器（101）与后端换热器（102）由换热器联接管（105）串联联接，前端换热器（101）和后端换热器（102）可各由一个或多个换热单元叠加而组成，分别布置在风机通道的上游和下游，风扇（8）设置在换热器的导风筒（11）内，采用二程交叉逆流换热。该空气换热器结构简单、工艺成熟、换热效能高、结构紧凑、风扇消耗功率低、噪声低、成本低。

Description

一种空气换热器 技术领域
E0001] 本发明属于 I：程机械、移动车辆、制冷、内燃机、变压器、大型机床等机电设备领 域，涉及一种换热器设备，尤其涉及一种高效 气换热器。 背景技术
[0002] 利用空气等流体作为冷却介质的换热器是工程机械、移动车辆、内燃机、小型制冷 机械、变压器等领域中不可缺少的设备。如水冷内燃机驱动的移动车辆的冷却液散热器、中 冷器、液压油散热器、 EGR冷却器，小型制冷机械的强制通风空气冷却式制冷剂冷凝器,大型 变压器的风冷油散热器等，都需要利用风 ^强迫驱动空气，横向穿过交叉流散热器的芯部 进行热交换，使散热器或冷凝器内的被冷流体的热量传出来。这类空气换热器在汽车、工程 机械和内燃机等行业大多称为散热器、¾ -空中冷器、液压油散热器、 EGR冷却器等。 被冷 却的流体有泠却液、压缩空气、液压油等， 般不发生相变。 在制冷行业空气换热器也称为 冷凝器和蒸发器等，被冷却的流体制冷剂将发生相变。 这些工作过程均和热量传递有着密 切联系，因而均可以通过以上各类换热器来 ¾成。
[0003] 常用的换热器包括换热器芯、风崩和导风罩。 风扇通过联接轴与驱动动力源联 接。 风扇驱动动力源可以是电动机或液压马达,而在大型移动车辆上风扇的联接轴的动力 來 i内燃机的曲轴皮带盘的机械能。 这种传统的散热器与新型散热器相比存在诸多不足， 如换热效能偏低、风扇消耗功率偏高、风 噪卢较大等性能缺点，散热器还受到主机布置的 限制，不能做得过于高大。
[0004] 通过分析，现有的强迫对流空气冷却换热器，只利用了空气通道的 侧布置交义 流换热器，而另一侧通道空间没有得到利用。 如吹风式换热器只利用了正压力空气气流通 道，而另一侧进气通道空间没有很好地布置利用，被空置。同样吸风式换热器只利用了负压 力空气通道，而另 ·侧空间没有很好地利用。
[0005] 现有的 ¾气换热器,如车辆 ffl 冷水散热器的冷却方案巾，风 ¾的转速较 ，改进 散热效果的设计中大都以提高转速来增加散热系统的换热能力，换热效能 f 较低。这种方 案中，空气以较大的流速回到大气中的问题，造成动能浪费，且风 ^效 也不 ¾。 空气流量 增加到一定极限后，换热能力增加的效果不大。 风机的噪声也非常高。
[0006] 因此提供性能优良的大功率的、低机械驱动消耗功率的换热器丄作 ¾得非常重 要。在现在石油资源价格不断高涨的情况下，各种节能、降耗工作是非常重要的。 降低噪声 也是环保 I：作中非常重要的内容。车辆、小型制冷空调机等产品的社会需求数 tt非常庞大, 因此，在提供高效大功率风冷换热器的同时，节能降耗、降噪工作非常重要而迫切需要。 发明内容
[0007] 本发明的 的在于提供一种 ^效空气换热器。 在提高强迫对流空气换热器换热 效能的同时，又有可能降低噪声，降低风扇的机械驱动消耗功率。 在移动 ^辆设计中，可以 适当降低车辆散热器的高度。 能够广泛地 Wffl于多种换热的场合。
确认本 [0008] 本发明提出的高效^气换热器，山前端换热器、风 J¾、导风筒和; Ϊ端换热器组成， 风扇位于导风筒内，所述风扇和导风筒组成风机及风道；所述风道的上、下游分别设置前端 换热器和后端换热器；所述前端换热器和后端换热器分别山- ·个或多个换热单元叠 Jfl而 成：前端换热器和后端换热器的被冷流体通道由换热中-元联接管 Φ联；前端换热器和后端 换热器 Φ联联接后，通道内的被冷流体的整体流向与冷 ^气整体流向相逆。
[0009] 本发明中，所述风 与导风筒组成的风机为轴流式、离心式或混流式中任一种。
[0010] 本发明中，所述风扇连接风 驱动动力源，所述风扁驱动动力源^以布置于风道 外或风道内，当风扇驱动动力源位于风道外时，风扇传动轴通过位于前端换热器或后端换 热器上的取力孔连接风扇，取力孔中设置封气盘。
[001 1 ] 本发明的原理如下 -
( 1 )在风机的上下游两端面同时安装交叉流空气换热 'ϊ，元，并用管路 Φ联连通换热单 元。 冷却风的流向与换热器间被冷流体的整体流向相反。 山教科书可知，同样的外界条件 和同样的换热器换热面积下，：-.程交叉流逆流换热器的换热效能 ε 比单程交叉流换热器 的高。见阁 1，内部有风扇的二程交叉逆流换热器组合的布置方式示意图。同样并列增加一 组换热器后，见阁 2，三流体内部有风扇的二程交叉逆流换热器组合的布置方式示意图。
[0012] 图 1中，换热^元二 102为前端换热器，换热中元一 101为后端换热器。
[0013] 2巾，换热单元四 104、换热 元二 102 'S加成前端换热器，换热单元一 101、换 热单元三 103叠加成后端换热器。
[0014] 换热单元的排列方法，按设计目标的要求，如对流体 B、流体 C流出的温度要求如 Tb2 < Tc2,流进流体 B、流体 C的条件为 Tel < Tbl o 很明显，因为 Tc2 < Te l，所以 Tb2 < Tc2 < Tel < Tbl。 换热单元排立顺序为换热单元一 ] 01、换热 元三 103、换热单元四 104、换热羊.元 ： 102，其流出和流出换热单元流体的温度排序为 Tb2 < Tc2 < Tel < Tbl， 与流体 A的流向相逆。
[0015] ( 2 )在（1 )的基础上，利用风扇 8 端的进出风道 方便地增加空气侧的总换热面 积，由教科 ίί中的换热器的效能-传热 元数计算法，即 ε - NTU法中的 ：程交叉逆流换热 器的计算曲线査得：传热 ^元数 NTU同比增大，在同样的水当 Μ比 R曲线上，曲线正斜率较 大，换热效能 ε 可大幅提高。
[0016] ( 3 )降低风扇 8的设计转速。 山于以上（1 ) ( 2 )的措施，换热器的能力大幅提升。 换热器换热能力将有可能在满足设备需求后,换热能力有剩余。因此，针对某一确定的散热 设计需求，在满足设备需求后，适当减少冷却空气流 Μ，采 ^用降低风 8转速的措施。 此措 施可以大幅降低风扇 8的驱动功率，减小风扇 8的噪声声压级。
[0017] ( 4 )风扇 8布置在换热器及风道中。 这样设计方案，可以提高风扇效率，同时风机 对外噪声因被屏蔽而降低。 风扇要适当选型，以克服增加的风阻。
[0018] ( 5 )具体实施中，为了能使风扇的动力从换热器外传入，本发明采 ffl了机械传动轴 穿越换热器的方案，使传动轴穿过换热 .元中的取力孔并直接驱动风扇 8,而风扇 8在换热 器之间的导风筒 11内，取力孔设有封气盘以阻挡气体流动。
C0019] 本发明提供的技术方案带来的有益效果是：相比现有技术，本发明的方案中，采 ffl 逆流 Φ联组合和风 上下游风道巾同时布置换热单元，充分利用轴向多余空间，能很有效 地增大换热能力，提¾换热效能，捉高换热器紧凑程度。若换热器比设计要求的换热能力有 剩余，则可以降低风扇转速，达到节能、降噪的效果。
C0020] 有案例计算中，在汽车发动机水散热器改进设计案例中，采用本发明方案，提 高换热器换热效能约 50%,风 ^驱动功率约降低 46%左 ，发动机燃油消耗率降低 0. 9〜 3. 1%,风扇噪声的声压级也可下降 40〜 50%。 节能投资 iHl报周期小于三个 Jj。
[0021 ] 在设计过程中，具体的换热器规格、结构等设计方案，需考虑多个因素后，在试验 后确定。
[0022] 本发明方案有节约 H]'观的机械能、电能、降低风扇材料的强度要求等优势，有很强 的适应能力。 山于工艺成熟，材料价格低， ffl广使用后会在很短的周期内收回成本，创造节 能效益。 可广泛用于车辆机械、制冷机械等需要进行强迫风冷热交换的领域。 附图说明
[0023] 1是本发明的内部有风扇的二程交叉逆流换热器组合的布置方式示意阁。
[0024] 2是本发明的三流体内部有风 ^的 '.稃交叉逆流换热器组合的布置方式示意 图。
[0025] 3是本发明在车辆机械中发动机的空气散热系统的实施结构示意阁。
[0026] 4是本发明在车辆机械中发动机的空气散热系统的实施结构示意阁 A向视阁。
[0027] 5是本发明在通用机械中的空气散热系统的实施结构示意图。
[0028] m 6 ¾本发明在小型空调制冷系统空气冷凝器组的实施结构示意阁。
[0029] 7是本发明在小型空调制冷系统¾气冷凝器组的实施结构示意阁 A向视阁。
[0030] ^中标号：1为内燃机排气消声器，2为废气涡轮增 j玉器, 3为压气机出气管， 4为空 气滤清器， 5为内燃机冷却水出水管， 6为风扇皮带轮， 7为风扇传动轴， 8为风扇， 9为水散热 器联接胶管， 10为中冷器联接管， 11为导风筒， 12为前端空 -空中冷器， 13为前端散热器， 14为后端散热器， 15为后端空 -空巾冷器， 16为内燃机水汆进水管， 17为内燃机进气接管， 18为内燃机， 19为封气盘， 20为电动机， 21为联轴器, 22为联接铜管， 23为前冷凝器， 24为 后冷凝器， 101为换热中.元 - , 102为换热单元 103为换热单元三， 104为换热中.元四， 105 为换热单元联接管。 具体实施方式
[0031 ] 为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对实施例或现 有技术描述中所需要使用的附图作简 介绍，显而易见地，下面描述中的附阁仅仅是本发 明的实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据附 图获得其他的附阁。
[0032] 下而结 V附阁
Figure imgf000005_0001
5、阁 6、阁 7对本发明的实施方案例作进行详 细说明，本实施方案在以本发明技术方案为前提下进行实施，给出了详细的实施方式和具 体的操作过程，但本发明的保护范围不限于下述的¾施例。
[0033] ¾施例 1：见图 1，一种高效空气换热器示意阁，包括换热单元一 101、冷却风扇 8、 导风筒 1 1、换热 元联接管 105和换热中.元 ： 102。 1、阁 2中的换热单元一 101、换热中. 元 ： 102、换热 元三 103及换热 元 104均 于横向直流交叉流空气换热器，" Γ冇多种 形式，如^冷散热器、空空中冷器、空气冷凝器、^气蒸发器等均 ¾于此类换热结构换热器。 换热单元一 101、换热 ¥.元 ：102,山换热中.元联接管 105联接，使前 ) ί换Υ'.元 - 101、换单元 ： 102 Φ联；冷却流体 Α (冷空气）因风扇 8转动产生的负压差进入换热' ϊ元 · 101，以 t l 温度与换热单元一 101 内的流体 B发生热交换，横向穿过的冷却流体 A (冷空气）进行热交 换后又进入导风筒 11，在导风筒 1 1 内被风扇 8驱动以 t ( 1 )温度进入换热中.元二 102，与 换热单元二 102内的被冷流体 B发牛热交换，最后以 t2温度流出。 高温流体 B首先以 T1 温度进入换热单元 -. 102与风^ 8吹来的 t ( 1 )温度的流体 A (空气）进行热交换，流体 B 以 T ( 1 )的温度流出换热单兀 '. 102：流体 B以 T ( 1 )温度通过换热 儿联接管 105进入 换热单元一 101与交叉流过换热^元的温度为 U的流体 Α (空气）进行热交换，以 T2温度 流出换热单元一 101。
[0034] 冷却流体 A (空气）的流向与被冷流体 B的整体流向相反，形成内部有风扇的 二程交叉逆流换热器组合。
[0035] 阁 1中，换热中.元:： 102为前端换热器，换热单元一 101为 )ΰ端换热器。
[0036] 同样可以在风^ 8的前后端同时增加多种不同的流体 Φ联换热器组，图 2就是 - 种内部有风扇的三流体— :程交叉逆流换热器组合。
[0037] 图 2中，换热单元四 104、换热单元二 102叠加成前端换热器，换热单元一 101、换 热单元三 103叠加成后端换热器。
[0038] 换热单元的排列方法，按设计目标的要求，如对流体 Β、流体 C流出的温度要求如 Tb2 < Tc2，流进流体 B、流体 C的条件为 Tel < Tbl。 很明显，因为 Tc2 < Tel，所以 Tb2 < Tc2 < Te l < Tbl。 换热单元排立顺序为换热单元一 101、换热单元三 103、换热单元四 104、换热单元二 102,其流出和流出换热单元流体的温度排序为 Tb2 < Tc2 < Te l < Tbl , 与流体 A的流向相逆。
[0039] 实施例 2，如图 3、阁 4所示的车用内燃机高效^气散热系统。
[0040] 一种高效空气换热器，包括内燃机排气消声器 1、废气涡轮增压器 2、压气机出气 管 3、空气滤清器 4、内燃机冷却水出水管 5、风 皮带轮 6、风^传动轴 7、风^ 8、水散热器 联接胶管 9、中冷器联接管 10、导风筒 1 1、前端空 空屮冷器 12、前端散热器 13、后端散热 器 14、后端空 -空中冷器 15、内燃机水泵进水管 16、内燃机进气接管 17、内燃机 18和封气 盘 19；其中：内燃机 18、前端散热器 13、后端散热器 14、内燃机排气消声器 1、空气滤清器 4 均与设备底盘或支架相联接。前端 -空中冷器 12、后端 -空中冷器 15均分别与前端散 热器 13、后端水散热器 14通过紧阆螺栓相联接。 前端换热器 13、 端换热器 14之间通过 螺栓与导风筒 1 1相联接。
C0041 ] 前端空一空中冷器 12与前端散热器 13通过紧 ISI螺栓相联接叠加成前端换热器， 后端空 -空中冷器 15与后端散热器 14通过紧固螺栓相联接叠加成后端换热器。
[0042] 内燃机 18前端的恒温器出水管与内燃机冷却水出水管 5联接，内燃机冷却水出水 管 5与后端水散热器 14相联接， 端水散热器 14与前端水散热器 13通过水水散热器联接 胶管 9相联接，前端水散热器 13 ' j内燃机水泵进水管 16相联接，内燃机水汆进水管 16 'ν 内燃循环冷却水泵相联接。
[0043] 空气滤清器 4与废气涡轮增压器 2的压气机进气口相联接，废气涡轮增压器 2的 压气机出口与压气机出气管 3相联接，压气机出气管 3 ½· /Γί端空 -空中冷器 15相联接，后 端¾ -空中冷器 15与前端 ¾ 空中冷器 12通过中冷器联接管 10相联接， ^端空 -空中冷 器 12与内燃机进气接管 17相联接，内燃机进气接管 17与内燃机 18的气缸进气管相联接。 废气涡轮增压器 2的涡轮机接口与内燃机 18的气缸排气 相联接，废气涡轮增压器 2的涡 轮机出 Π与内燃机排气消声器 1通过螺栓相联接。
[0044] 内燃机 18前端的风扇皮带轮 6的侧面与风扇传动轴 7通过多个螺栓相联接，风扇 传动轴 7与风扇 8通过螺栓相联接。 风扇传动轴 7穿过; 端空 -空中冷器 15和后端换热 器 14的取力孔,取力孔的前后两端均安装有封气盘 19，确保无大 M空气泄漏。 风扇 8的叶 片需与导风筒 11的内壁之间留有一定的间隙。
[0045] 内燃机 18丄作时，曲轴皮带轮通过皮带将动力传递给风扇皮带轮 6，风扇皮 带轮 6通过驱动传动轴 7驱动风扇 8，风扇 8的叶片在旋转中切割空气，空气从阁 3的右向 左流动。 首先，冷空气横向从大气进入前端空 -空中冷器 12的右端面，通过前端空 -空中 冷器 12的芯部，冷却其中的被冷流体高温压缩气体；冷空气横向交叉从前端换热器 13 端 面进入并通过芯部，冷却前端水散热器 13中的被冷流体内燃机冷却液，然后进入导风筒 11 内。 经过风扇 8的驱动，空气流向后端水散热器 14和后端 ¾ -空中冷器 15，依次进入并 冷却后端水散热器 14芯部内的内燃机冷却液和后端空 - 屮冷器 15的芯部内的高温压缩 气体。完成冷却过程后的空气流以一定的流速流出后端空 - 中冷器 15的左端面，进入大 气。这样冷却空气流与高温压缩气体流在空-空中冷器 12、15组中形成内部有风扇的二程 交叉逆流换热器。
[0046] 内燃机 18工作时，若内循环冷却温度达到设定值，恒温器阀将打开，高温内燃机 冷却液经内燃机冷却水出水管 5流入后端散热器 的换热器芯部，与空气侧流过的冷空气 发生首次热交换；高温内燃机冷却液流出后端散热器 14，通过散热器联接胶管 9进入前端 散热器 13的芯部，与 ¾气侧流过的冷空气发生二次热交换：经过.：次冷却后内燃机冷却液 温度被降低到一定值，经过内燃机水泵进水管 16后山循环水泵将水抽回到内燃机 18的内 循环冷却系统中。这样冷却空气流与内燃机冷却液体流在前端散热器 13、后端散热器 14中 形成内部有风扇的二程交义逆流换热器。
[0047] 内燃机 18丄作时，曲轴皮带轮带动风扇皮带轮 6，风扇皮带轮 6与风扇传动轴 7 和风扇 8都已紧固联接，而风扇传动轴 7穿越空―空中冷器 15和后端换热器 14的方型取 力孔；风扇 8得以转动驱动空气流动。 在空 -空中冷器 15和后端换热器 14的方型取力孔 的两端安装有的封气盘 19，功能是阻止空气的流动，加丄冇圆孔充许风扇传动轴 7穿越,封 气盘 19有穿轴孔，其穿轴孔径略大于风扇传动轴 7的轴径。 风扇 8的叶片需与导风筒 1 1 的内壁之间留有一定的间隙,其与风扇的效率有关。
[0048] 前端 ¾ -空中冷器 12与前端散热器 13通过紧 W螺栓相联接， S加成前端换热器， 后端空 -空中冷器 15与后端散热器 14通过紧固螺栓相联接，S加成后端换热器。
[0049] 如图 3所示，两组 Φ联换热器叠加形成冷却空 :(流体与被冷流体高温压缩气体和 内燃机冷却液流体三种流体的换热装置，形成内部有风 /3的三流体二程交叉逆流组合换热 器。
[0050] 本文叙述的前端散热器 13、后端散热器 14，是行业内常用的各种交叉流空气 -冷 却液热交换设备， ||]'以是管带式、管片式等，行业中常称为水散热器， 于换热器的范畴； 空 -空中冷器也是行业内常用的各种交叉流空气 -空气热交换设备，有管片式、板翅式等， 也^于换热器的范畴。 风竊为行业中常用的轴流风 a。 [0051 ] 山于风扇的上下游风道^间布置了整体串联逆流式风冷换热器，这种形式的换热 器组合有如下特点：
( 1 )用于车辆内燃机的散热系统制造设计中时，山于采用了多程交叉逆流组合的设计 方案，使得系统的换热效能 ε 增加，相对现有的散热器布置法，在同样的冷空气流量情况 下，将增加热交换能力。 又因为风 /*i双侧 ¾间同时配 S散热器，散热总面积较易大幅度增 加，将增加热交换能力。 以上的两个措施共同作用，可大幅增加热交换能力。 若换热能力 有富余，可减少冷却空气的流 Μ:，因此可使风扇的设计转速 F降。 山教科书知，风机的空气 流量与风扇的转速成正比，风扇的驱动功率和风扇噪声声压级均与风扇转速的三次方成正 比。 降低风扇的转速，风扇 8的驱动功率将按转速比三次方的比例大幅下降。 内燃机的曲 轴可增加净功率输出，降低燃油消耗率。降低风扇的转速 ,风扇噪声声压级也按转速比的三 次方的幅度下降。
[0052] ( 2 ) nj以调节多个与散热器有关的变量，如调节换热器的迎风面积， 适应较低的 发动机机舱，给整车设计带来多样性、灵活性。 风扇的直径可以适当减小，对风^的材料强 度要求的降低，可降低成本。
[0053] ( 3 )可以降低风扇噪声。 因风 在导风筒 1 1和前端散热器、 端散热器内，风扇 8 切割气流噪声可被屏蔽。
[0054] ( 4 )各换热单元顺序的排列组合可变性带来换热器布置设计方案的多样性，风 8 的前后通道均可布置组合 -个或多个散热器；同 -被冷流体的换热单元可以通过多个换热 单元联接管与电控切换阀门连接，在^关控制程序的控制作用下，电控切换阀门执行串联 组合、并联组合或比例开关部份散热器通道等命令，实现换热器冷却能力智能调整切换控 制的功能。
[0055] ( 5 )风扇 8形式可以是轴流式吸风扇或吹风 ，风 风向变换时冷却管道走向也 相应反转。 阁 3中风扇 8为吸风式。
[0056] ( 6 )风 8要做适当选型，以克服增加的风阻。
[0057] ； i:施例 3，如阁 5所示的通用机械高效空气换热器组。
[0058] 实施结构阁见阁 5中，电动机 20通过联轴器 21与风扇传动轴 7通过螺栓相联接， 将扭矩传递给风扇 8 ,风扇 8叶片在导风简 1 1内旋转，分别在风^ 8前后端面产生正负压 力，冷却空气因负压穿过后端散热器 14进入导风筒 11内，空气从阁左向厶被风扇 8驱动 ，进入前端散热器 13，依次分别与/ ή端散热器 14、前端散热器 13中的热流体 Α发生热交 换/ Π，热 气从右端面进入大气中。 阁 5中风 8为吹风式风扇。
[0059] 热流体 Λ从主机循环系统屮进入前端散热器 13与橫穿过去的冷空气发牛热交换， 然后进入后端散热器 14与横穿过去的冷空气发生热交换，热流体 A被冷却 iil lHl到主机的循 环系统中。
[0060] 电动机 20为风扇 8的动力源，在 I：程设计中此动力源也可选 ffl液压 ¾达、电动机 或传动皮带轮等机械动力源。 风 ¾形式 "J以是轴流式吸风扇或吹风扇，风^风向变换时冷 却 ΐ?道走向也相应反转。
[0061 ] 这种二流体逆流换热器组^形式可以广泛应用于汽车、内燃机车、 Ί :程机械、变压 器、大型机床 领域。 被冷流体 以是 ^种冷却液、切削液和液压油等。
C0062] ¾施例 4，如阁 6、阁 7所示的小型¾调制冷系统高效空气冷凝聚器组。 [0063] ¾施结构阁见阁 6中，电动机 20通过联接轴 7，将扭矩传递给风扇 8,风扇 8叶片 在导风筒内旋转，分别在风 *i前； Γί产生正负压， 1*1 6中为吹风式风 ，冷却空气因负压从大 气中进入并穿过/ Γί冷凝器 24进入导风筒 1 1内，空气从阁从左向 依次穿过后冷凝器 24、导 风筒 11及前冷凝器 23，分别与后冷凝器 24、前冷凝器 23中的制冷剂发生热交换后，空气进 入大气中。
[0064] 制冷剂（过热蒸汽）从主机循环系统管道进入前冷凝器 23与横穿过去的冷空气发 生热交换，乂通过联接铜管 22进入后冷凝器 24乂与横穿过去的冷空气发生热交换,制冷剂 被冷凝后，以液态回到主机的循环系统中。
[0065] 前冷凝器 23、后冷凝器 24均为行业内常用的设备，有铜管翅片式、管带式等，也 属于换热器的范畴。 同样，此原理 "用于制冷剂的蒸发热交换中。
[0066] 这种二程逆流换热器组合形式的冷凝器、蒸发器可以广泛应用于中小型制冷空调 机械及其他领域。
[0067] 风^形式可以是轴流式吸风扇或吹风) 风 风向变换时冷却管道走向也相应反 转。
[0068] 实施例 2、例 3、例 4的主机，均为长期使用的耗能机械，社会保有量 Γ: (大，故节能、 降噪的意义重大。 相比现代人类社会 I，：大的能源消费增幅和近年的能源价格的暴涨,商品 用于节能措施的，制造新型换热器的设备成本是非常较低的，可以承受的。 ffl户将从节能中 明显受益，会很快收回节能设备成本的。风扇噪声的降低可以提高产器的品质，并带来环保 效益。
[0069] 如一般内燃机的风 ίί3附件消耗功率约占其总功率的 2〜 7%，若能应用本发明的技 术方案，冷却液散热器等可以提高换热效能。 风扇消耗功率将可能降低。 风扇噪声的声压 级也可下降。
[0070] 工程机械、乘用车辆、机车车辆和变压器的换热器的风 节能也是如此。
[0071 ] 小型 凋制冷行业的风^节能及降噪，可以应用木发明技术，并将取得明显的节 能、环保优势。

Claims

1. 一种高效空气换热器，其特征在于山前端换热器、风扇、导风筒和后端换热器组成， 风扇位于导风筒内，所述风扇和导风筒组成风机及风道；所述风道的上、下游分别设置前端 换热器和后端换热器；所述前端换热器和后端换热器分别山一个或多个换热 ^元叠加而 成；前端换热器和后端换热器的被冷流体通道山换热1 Ϊ1.元联接管 Φ联；前端换热器和后端 换热器 Φ联联接后，通道内的被冷流体的整体流向与冷空气整体流向相逆。
2. 根据权利要求 1所述的高效空气换热器，其特征在于所述风廟与导风简组成的风 机为轴流式、离心式或混流式中任一种。
3. 根据权利要求 1所述的高效空气换热器，其特征在于所述风扇连接风扇驱动动 力源，所述风扇驱动动力源可以布置于风道外或风道内，当风扇驱动动力源位于风道外时， 风扇传动轴通过位于前端换热器或后端换热器上的取力孔连接风扇，取力孔两端设置封气 盘。
4.一种如权利要求 1所述的高效空气换热器在车川内燃机散热系统中的应用，其特征 在于所述散热器上设置内燃机排气消声器（1)、废气涡轮增压器（2)、压气机出气管（3)、空 气滤淸器（4)、内燃机冷却水出水管（5)、风 皮带轮（6)、风扇传动轴（7)、风扇（8)、水散 热器联接胶管（9)、中冷器联接管（10)、导风筒（11)、前端空 -空中冷器（12)、前端散热器
(13)、后端散热器（14)、后端空 -空中冷器（15)、内燃机水泵进水管（16)、内燃机进气接管 (17)、内燃机 (18)和封气盘 (19)；内燃机（18)、前端散热器 (13)、后端散热器 (14)、内燃机 排气消声器（1)、空气滤清器（4)均与设备底盘或支架相联接；前端空-空中冷器（12)、后 端空-空中冷器（15)均分别与前端散热器（13)、后端散热器（14)通过紧固螺栓相联接； 前端散热器（13)、后端散热器 (14)之间通过螺栓与导风筒 (11)相联接：内燃机 (18)前端 的恒温器出水管与内燃机冷却水出水管（5)联接，内燃机冷却水出水管（5)与后端散热器
(14)相联接，后端散热器（14)与前端散热器（13)通过水换热器联接胶管（9)相联接，前 端散热器（13)与内燃机水泵进水管（16)相联接，内燃机水泵进水管（16)与内燃循环冷却 水泵相联接；空气滤清器（4)与废气涡轮增压器（2)的压气机进气口相联接,废气涡轮增压 器（2)的压气机出口与压气机出气管（3)相联接，压气机出气管（3)与后端空-空巾冷器
(15)相联接，后端空-空中冷器（15)与前端 ¾中冷器（12)通过中冷器联接管（10)相 联接，前端空 -空中冷器（12)与内燃机进气接管（17)相联接，内燃机进气接管（17)与内 燃机（18)的气缸进气管相联接；废气涡轮增压器（2)的涡轮机接口与内燃机（18)的气缸 排气管相联接，废气涡轮增压器（2)的涡轮机出口与内燃机排气消声器（1)通过螺栓相联 接；内燃机（18)前端的风扇皮带轮（6)的侧面与风扇传动轴（7)通过多个螺栓相联接，风 扇传动轴（7)与风扇（8)通过螺栓相联接；风扇传动轴（7)穿过后端空-空中冷器（15)和 后端散热器（14)的取力孔，取力孔的前后两端均安装有封气盘（19)；风扇（8)的叶片与导 风筒（11)的内壁之间留有一定的间隙：前端空-空中冷器（12)与前端散热器（13)通过紧 1 1螺栓相联接叠加成前端换热器，后端空-空中冷器（15)与后端散热器（14)通过紧固螺 栓相联接 S加成后端换热器。
5. -种如权利要求 1所述的高效^气换热器在通用机械中的应用。
6. -种如权利要求 1所述的高效 气换热器在小型空调制冷系统中的应用。
PCT/CN2012/001467 2011-10-31 2012-10-30 一种空气换热器 WO2013063864A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/354,584 US9200848B2 (en) 2011-10-31 2012-10-30 Air heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2011103130501A CN102384676B (zh) 2011-10-31 2011-10-31 一种高效空气换热器
CN201110313050.1 2011-10-31

Publications (1)

Publication Number Publication Date
WO2013063864A1 true WO2013063864A1 (zh) 2013-05-10

Family

ID=45824325

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2012/001467 WO2013063864A1 (zh) 2011-10-31 2012-10-30 一种空气换热器

Country Status (3)

Country Link
US (1) US9200848B2 (zh)
CN (1) CN102384676B (zh)
WO (1) WO2013063864A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108547777A (zh) * 2018-05-23 2018-09-18 熙诚环保科技（苏州）有限公司 一种具有防腐功能的斜流风机

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102384676B (zh) 2011-10-31 2013-05-29 陆加孚 一种高效空气换热器
DE202012013027U1 (de) * 2012-06-04 2014-09-03 Förderverein dream4life e.V. Vorrichtung zur Umwandlung thermischer Energie in mechanische Energie und umgekehrt
US9603282B2 (en) * 2014-01-03 2017-03-21 Microsoft Technology Licensing, Llc Datacenter and cooling control fault-tolerance using compute resources
CN106323065A (zh) * 2015-07-09 2017-01-11 内蒙古亿利新中农沙地农业投资股份有限公司 一种沙地井水增温装置
CN106224077A (zh) * 2016-08-29 2016-12-14 江苏嘉和热系统股份有限公司 一种汽车散热器芯体
CN106948918A (zh) * 2017-03-07 2017-07-14 安徽全柴锦天机械有限公司 一种环保型柴油机缸体的冷却系统
CN108561221A (zh) * 2018-04-03 2018-09-21 广州电力机车有限公司 自卸车水冷却系统设计方法
US11486647B1 (en) * 2018-05-01 2022-11-01 Hudson Products Corporation Internal drive system for air-cooled heat exchangers
CN109057938A (zh) * 2018-08-13 2018-12-21 广西柳工机械股份有限公司 装载机吸风式散热系统
US11124047B2 (en) * 2018-11-03 2021-09-21 Hyundai Motor Company Vehicular HVAC system with liquid-cooled charge air cooler integration
US11639684B2 (en) 2018-12-07 2023-05-02 Polaris Industries Inc. Exhaust gas bypass valve control for a turbocharger for a two-stroke engine
US20200182164A1 (en) 2018-12-07 2020-06-11 Polaris Industries Inc. Method And System For Predicting Trapped Air Mass In A Two-Stroke Engine
US11828239B2 (en) 2018-12-07 2023-11-28 Polaris Industries Inc. Method and system for controlling a turbocharged two stroke engine based on boost error
US11352935B2 (en) * 2018-12-07 2022-06-07 Polaris Industries Inc. Exhaust system for a vehicle
US11236668B2 (en) 2018-12-07 2022-02-01 Polaris Industries Inc. Method and system for controlling pressure in a tuned pipe of a two stroke engine
US11280258B2 (en) 2018-12-07 2022-03-22 Polaris Industries Inc. Exhaust gas bypass valve system for a turbocharged engine
US11174779B2 (en) 2018-12-07 2021-11-16 Polaris Industries Inc. Turbocharger system for a two-stroke engine
US11725573B2 (en) 2018-12-07 2023-08-15 Polaris Industries Inc. Two-passage exhaust system for an engine
FI129146B (fi) * 2019-02-08 2021-08-13 Hoegforsgst Oy Primäärilämmitystä käyttävä hybridilämmitysjärjestelmä
CN111609631A (zh) * 2019-02-26 2020-09-01 青岛海尔电冰箱有限公司 风机位于蒸发器中间的冰箱
CN111609630A (zh) * 2019-02-26 2020-09-01 青岛海尔电冰箱有限公司 风机位于蒸发器中间的冰箱
US11014440B2 (en) * 2019-07-29 2021-05-25 Ford Global Technologies, Llc Structural cooling pack
US11434834B2 (en) 2020-01-13 2022-09-06 Polaris Industries Inc. Turbocharger system for a two-stroke engine having selectable boost modes
US11788432B2 (en) 2020-01-13 2023-10-17 Polaris Industries Inc. Turbocharger lubrication system for a two-stroke engine
CA3105239C (en) 2020-01-13 2023-08-01 Polaris Industries Inc. Turbocharger system for a two-stroke engine having selectable boost modes
CA3217527A1 (en) 2020-01-13 2021-07-13 Polaris Industries Inc. Turbocharger lubrication system for a two-stroke engine
US11150162B1 (en) 2020-05-28 2021-10-19 Lennox Industries Inc. Determination of pulley ratio of a belt-drive blower
CN112650315B (zh) * 2020-09-09 2021-11-05 江苏振宁半导体研究院有限公司 一种温控器的温控方法
CN113983584A (zh) * 2021-11-16 2022-01-28 曾昭达 冷暖型绿色环动空调
CN114060980A (zh) * 2021-11-16 2022-02-18 曾昭达 单冷型绿色环动空调
CN114889089B (zh) * 2022-05-21 2023-05-16 江西科惠达实业有限公司 一种具有冷却效果的电缆生产用螺杆橡胶挤出机
CN114922724B (zh) * 2022-06-17 2023-10-31 奇瑞汽车股份有限公司 车辆控制方法及系统
CN115060097B (zh) * 2022-08-18 2022-11-15 南通好通科技有限公司 一种具有水循环系统的石墨换热器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08159582A (ja) * 1994-12-06 1996-06-21 Yoriyuki Oguri 新代替冷媒ガスｈｆｃを使用したヒートポンプの空冷 コンデンサー。
JP2000241046A (ja) * 1999-02-24 2000-09-08 Usui Internatl Ind Co Ltd 低温装置
JP2006017369A (ja) * 2004-06-30 2006-01-19 Mitsubishi Electric Building Techno Service Co Ltd 空気調和機の室内機
JP2008051369A (ja) * 2006-08-23 2008-03-06 Matsushita Electric Ind Co Ltd 冷凍システムおよびこれを備えた保冷庫
CN102384676A (zh) * 2011-10-31 2012-03-21 陆加孚 一种高效空气换热器

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3058317A (en) * 1958-03-31 1962-10-16 Superior Air Products Co Vaporization of liquefied gases
US3203499A (en) * 1962-06-08 1965-08-31 Caterpillar Tractor Co Cooling arrangement for supercharged engines
GB1111562A (en) * 1964-05-01 1968-05-01 Aero Hydraulics Ltd Heat exchanger arrangements
US3377023A (en) * 1966-02-01 1968-04-09 Caterpillar Tractor Co Discriminating variable speed control for multiple heat exchanger fan motors
US3779341A (en) * 1972-10-16 1973-12-18 Modine Mfg Co Noise suppressive fan shroud
DE2655017C2 (de) * 1976-12-04 1986-09-18 Klöckner-Humboldt-Deutz AG, 5000 Köln Brennkraftmaschine mit Hochaufladung
JPS58210487A (ja) * 1982-05-31 1983-12-07 Mitsubishi Electric Corp 熱交換装置
JPH0247228Y2 (zh) * 1985-09-14 1990-12-12
US5226285A (en) * 1989-12-18 1993-07-13 Danhard, Inc. Self-cleaning heat exchanger fan assembly and controls
US5172753A (en) * 1991-10-15 1992-12-22 General Motors Corporation Automobile heating system
US5259206A (en) * 1991-12-05 1993-11-09 Danhard, Inc. Compact condenser
US5269143A (en) * 1992-12-07 1993-12-14 Ford Motor Company Diesel engine turbo-expander
CN2171080Y (zh) * 1993-08-31 1994-07-06 杨国平 多功能空调机
GB2302135A (en) * 1995-06-09 1997-01-08 Perkins Ltd Cooling and oil separation for engine blow-by gases
DE19540591C2 (de) * 1995-10-31 1999-05-20 Behr Gmbh & Co Verfahren zur Regelung der Volumenstromverteilung in einem Kühlmittelkreislauf für Kraftfahrzeuge mit Motor und Vorrichtung zur Durchführung des Verfahrens
US5901786A (en) * 1998-09-21 1999-05-11 Ford Motor Company Axial fan sandwich cooling module incorporating airflow by-pass features
US6155335A (en) * 1999-04-26 2000-12-05 Delphi Technologies, Inc. Vehicle fan shroud and component cooling module
JP2004092921A (ja) * 2002-08-29 2004-03-25 Denso Corp 熱交換器
DE10316108B4 (de) * 2003-04-09 2007-03-22 Daimlerchrysler Ag Dichtungselement für eine Kühlmodulanordnung eines Kraftfahrzeuges und Kühlmodulanordnung mit einem solchen Dichtungselement
US7178579B2 (en) * 2003-11-26 2007-02-20 Proliance International Inc. Heat exchanger package with split charge air cooler
JP2008232548A (ja) * 2007-03-22 2008-10-02 Daikin Ind Ltd 熱交換器
DE102008034122B4 (de) * 2008-07-18 2010-06-02 Herbst, Donald, Dipl.-Ing. Wärmetauscher, Verfahren zum Betreiben des Wärmetauschers und Verwendung des Wärmetauschers in einer Klimaanlage
CN101666528A (zh) * 2008-09-05 2010-03-10 张桂伟 一种节能空调
CN201273700Y (zh) * 2008-09-17 2009-07-15 朱江勇 带有空调的安全快速空气源热水器
CN102095230A (zh) * 2009-12-11 2011-06-15 严继光 具有双级表冷器的空气处理机
US20130192795A1 (en) * 2012-01-31 2013-08-01 Suryanarayana R. GADHIRAJU Cooling system having anti-recirculation feature

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08159582A (ja) * 1994-12-06 1996-06-21 Yoriyuki Oguri 新代替冷媒ガスｈｆｃを使用したヒートポンプの空冷 コンデンサー。
JP2000241046A (ja) * 1999-02-24 2000-09-08 Usui Internatl Ind Co Ltd 低温装置
JP2006017369A (ja) * 2004-06-30 2006-01-19 Mitsubishi Electric Building Techno Service Co Ltd 空気調和機の室内機
JP2008051369A (ja) * 2006-08-23 2008-03-06 Matsushita Electric Ind Co Ltd 冷凍システムおよびこれを備えた保冷庫
CN102384676A (zh) * 2011-10-31 2012-03-21 陆加孚 一种高效空气换热器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108547777A (zh) * 2018-05-23 2018-09-18 熙诚环保科技（苏州）有限公司 一种具有防腐功能的斜流风机
CN108547777B (zh) * 2018-05-23 2023-08-15 熙诚环保科技（苏州）有限公司 一种具有防腐功能的斜流风机

Also Published As

Publication number Publication date
US9200848B2 (en) 2015-12-01
US20140366815A1 (en) 2014-12-18
CN102384676A (zh) 2012-03-21
CN102384676B (zh) 2013-05-29

Similar Documents

Publication Publication Date Title
WO2013063864A1 (zh) 一种空气换热器
US7669417B2 (en) Engine after-cooling system
CN103129348B (zh) 一种电动汽车热泵系统
CN106032919A (zh) 一种冷冻水冷却系统
CN102331046B (zh) 一种组合式气-水双热源热泵型电动汽车空调系统
CN205900740U (zh) 一种电动汽车用电池热管理系统
JP4089428B2 (ja) 空冷式熱交換装置
WO2020238193A1 (zh) 一种新组合的车辆双循环冷却系统
CN104315739B (zh) 具有双冷凝双散热的冷液机
CN102331048A (zh) 一种复合式气-水双热源热泵型电动汽车空调系统
CN201133280Y (zh) 一种发动机中冷系统
CN106556083A (zh) 一种具备喷射器的多联机空调系统及其控制方法
CN203626949U (zh) 一种发动机进气管路冷却系统
CN109186116B (zh) 一种采用涡轮增压器的空气循环热泵系统
CN207496426U (zh) 一种纯电动客车热泵空调系统
CN202350214U (zh) 一种组合式气-水双热源热泵型电动汽车空调系统
CN202338974U (zh) 一种复合式气-水双热源热泵型电动汽车空调系统
CN206572659U (zh) 串联式双温冷水机组
CN210821747U (zh) 一种汽车热泵空调的散热回路及其空调系统
CN208630308U (zh) 一种新能源汽车用串联空调冷凝器结构
CN206834299U (zh) 一种冷媒循环式动力电池热管理系统
CN106247832A (zh) 一种汽车用组合式热管换热器
US11208944B2 (en) Cooling system for internal combustion engine
CN208012143U (zh) 中间补气的一次节流中间不完全冷却热泵系统
CN111923693A (zh) 电动汽车热泵空调系统及电动汽车

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12845959

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 14354584

Country of ref document: US

122 Ep: pct application non-entry in european phase

Ref document number: 12845959

Country of ref document: EP

Kind code of ref document: A1