CN101482349A - Condenser for use in vehicle - Google Patents
Condenser for use in vehicle Download PDFInfo
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- CN101482349A CN101482349A CNA2009100000744A CN200910000074A CN101482349A CN 101482349 A CN101482349 A CN 101482349A CN A2009100000744 A CNA2009100000744 A CN A2009100000744A CN 200910000074 A CN200910000074 A CN 200910000074A CN 101482349 A CN101482349 A CN 101482349A
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- hydroecium
- pipe
- refrigerant
- vehicle
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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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/044—Condensers with an integrated receiver
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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
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
Abstract
The invention provides a condenser for use in a vehicle, the condensation performance of which is not declined by being affected by the wind velocity, and which can improve air cooling performance or air cooling efficiency by means of cooling the coolant below a temperature of the atmosphere that is external thereto. The condenser for use in a vehicle (A1) comprises, in an integrated manner, a condensation part (4), which cools a coolant that is discharged, at a high temperature and a high pressure, to the condensation part (4) from a compressor (1) of a refrigeration cycle, by radiating heat from the coolant by way of a heat exchange between the coolant and the external atmosphere, a reservoir tank (5) that stores the coolant that has been liquefied by the condensation part (4), and a supercooling part (6), which cools the liquid coolant that is discharged to the supercooling part (6) from the reservoir tank (5) at a high pressure. The supercooling part (6) is configured to cool the liquid coolant that is discharged to the supercooling part (6) from the reservoir tank (5) at a high pressure by way of a heat exchange, which does not employ a radiator fin, between the high pressure liquid coolant and a low pressure coolant that is discharged from an evaporator (3) of the refrigeration cycle.
Description
Technical field
The present invention relates to be applicable to vehicle air conditioner, comprise the condenser for use in vehicle of condensation part, liquid storing part and supercooling portion integratedly.
Background technology
In the past, as the air-conditioning system that is applicable to vehicle, comprise the condenser for use in vehicle of condensation part, liquid storing part (fluid reservoir) and supercooling portion integratedly, known have in supercooling portion, similarly use fin with the condensation part, utilization is carried out heat exchange with extraneous air to be made from the high pressure liquid refrigerant heat radiation of liquid storing part and the device (for example, with reference to patent documentation 1) of cooling.
Patent documentation 1: TOHKEMY 2002-187424 communique
Summary of the invention
The problem that invention will solve
But in condenser for use in vehicle in the past, its supercooling portion is by the air-cooled type heat-exchanging structure that dispels the heat with the heat exchange of extraneous air, so, there is following problem.
(1) though in supercooling portion with refrigerant cools, can not be below external air temperature with refrigerant cools, being provided with under the situation that the space is restricted, can not seek to improve refrigerating capacity and refrigerating efficiency.
(2) heat exchange performance changes because of the wind speed of the travel speed of vehicle, sailing at once, and when stopping, when traffic jam is travelled etc., refrigerating capacity and refrigerating efficiency reduce.
(3) under the situation that does not change the overall thermal exchange area, if enlarge the area of supercooling portion, then the area of condensation part dwindles, and the condensation performance reduces.On the other hand, if enlarge the area of condensation part, then the area of supercooling portion dwindles, and the supercooling performance reduces.
The present invention is conceived to the problems referred to above and makes, even its objective is provide a kind of be subjected to Influences on Wind Velocity do not reduce the condensation performance yet, by refrigerant temperature being reduced to the supercooling below the external air temperature, can realize improving the condenser for use in vehicle of refrigerating capacity, refrigerating efficiency.
The scheme that is used to deal with problems
To achieve these goals, condenser for use in vehicle of the present invention, comprise integratedly by carrying out the condensation part that heat exchange makes its heat radiation cooling from high-temperature high-pressure refrigerant and the extraneous air that the compressor of freeze cycle is discharged, be stored in the liquid storing part of the cold-producing medium that this condensation part has been liquefied, the supercooling portion that high pressure liquid refrigerant from this liquid storing part is cooled off, it is characterized in that, above-mentioned supercooling portion makes between the low pressure refrigerant of discharging from the high pressure liquid refrigerant of above-mentioned liquid storing part and from the evaporimeter of above-mentioned freeze cycle by not using the heat exchange of fin, will be from the high pressure liquid refrigerant cooling of above-mentioned liquid storing part.
The effect of invention
Like this, in condenser for use in vehicle of the present invention, in supercooling portion, the low pressure refrigerant cooling of being discharged from the evaporimeter of freeze cycle from the high pressure liquid refrigerant of liquid storing part.
Therefore, when the high load capacity cooling operation, because the refrigerant temperature of evaporator outlet is lower than external air temperature, so, in supercooling portion, refrigerant temperature can be reduced to below the external air temperature.By this supercooling effect, in evaporimeter consumable cold and hot can be that enthalpy increases, can improve refrigerating capacity and refrigerating efficiency.
And, in supercooling portion, owing to do not use the heat exchange of fin, so, different with the supercooling portion that uses fin, can not be subjected to wind speed to carry out heat exchange with influencing.And, owing to do not use fin, so, compare with the supercooling portion that uses fin, can reduce the required area of supercooling portion.In other words, when guaranteeing the condensation performance, realize the miniaturization of global shape with the heat exchange area of identical condensation part.In addition, when making whole heat exchange area identical, the heat exchange area of condensation part enlarges, and the degree of its expansion is equivalent to the amount that the heat exchange area of supercooling portion reduces, and can improve the condensation performance.
As a result, do not reduce the condensation performance yet,, can realize improving refrigerating capacity and refrigerating efficiency by refrigerant temperature being reduced to the supercooling below the external air temperature even be subjected to Influences on Wind Velocity.
Description of drawings
Fig. 1 is the stereogram of freeze cycle of the vehicle of the expression condenser for use in vehicle that adopts embodiment 1.
Fig. 2 is the front view of the condenser for use in vehicle of expression embodiment 1.
Fig. 3 is the A portion amplification view of Fig. 2, the condenser for use in vehicle of expression embodiment 1.
Fig. 4 is the cutaway view of condensation part pipe in the condenser for use in vehicle of expression embodiment 1.
Fig. 5 is the pipe cutaway view of supercooling portion in the condenser for use in vehicle of expression embodiment 1.
Fig. 6 is the stereogram of supercooling portion in the condenser for use in vehicle of expression embodiment 1.
Fig. 7 is that the stereogram of existing vehicle with the freeze cycle of the vehicle of cooler adopted in expression.
Fig. 8 is that existing vehicle is used in the freeze cycle mollier diagram of the enthalpy during the high load capacity cooling operation and the relation of pressure.
Fig. 9 is that the front end air supply rate of the configuration layout of the front end air supply rate of expression benchmark vehicle, the configuration layout of being with the front end air supply rate of booster engine vehicle, motor vehicle driven by mixed power disposes the figure of the contrast of layout.
Figure 10 is in the existing condenser for use in vehicle of expression, when the supercooling zone is enlarged, and the key diagram of condensation part area decreases.
Figure 11 is that the vehicle of embodiment 1 is used in the freeze cycle, the mollier diagram of the relation of enthalpy and pressure during expression high load capacity cooling operation.
Figure 12 is illustrated under the situation about not changing with the heat exchange area of the integral body of existing vehicle condenser, in the condenser for use in vehicle of embodiment 1, and the key diagram that supercooling area decreases, zone, condensation part enlarge.
Figure 13 is the amplification view of supercooling portion of the 2nd pipe hydroecium side in the condenser for use in vehicle of expression embodiment 2.
Figure 14 is the B-B line cutaway view of Figure 13, the supercooling portion in the condenser for use in vehicle of expression embodiment 2.
Figure 15 is the pipe cutaway view of supercooling portion in the condenser for use in vehicle of expression embodiment 2.
Figure 16 is the amplification view of supercooling portion of the 2nd pipe hydroecium side in the condenser for use in vehicle of expression embodiment 3.
Figure 17 represents another routine tube section of the condensation part pipe in the condenser for use in vehicle of the present invention, and (a) expression reinforcement formula, (b) expression the 1st squash type, (c) represent the 2nd squash type.
Figure 18 is the pipe cutaway view of the supercooling portion of variation in the expression condenser for use in vehicle of the present invention, embodiment 1.
Figure 19 represents another routine tube section of the supercooling portion pipe in the condenser for use in vehicle of the present invention, (a) expression the 1st squash type, (b) combined type of sheet in expression the 2nd squash type and the 1st, (c) expression the 3rd squash type, (d) expression the 4th squash type, (e) combined type of sheet and the 2nd interior sheet in expression the 1st squash type and the 1st, (f) combined type of sheet in expression the 5th squash type and the 1st, (g) expression the 6th squash type, (h) expression the 7th squash type.
The specific embodiment
Below, with reference to illustrated embodiment 1～embodiment 3, the preferred forms that realizes condenser for use in vehicle of the present invention is described.
At first, explanation structure.
Fig. 1 is the stereogram of freeze cycle of the vehicle of the expression condenser for use in vehicle that adopts embodiment 1.Fig. 2 is the front view of the condenser for use in vehicle of expression embodiment 1.Fig. 3 is the A portion amplification view of Fig. 2, the condenser for use in vehicle of expression embodiment 1.Fig. 4 is the cutaway view of condensation part pipe in the condenser for use in vehicle of expression embodiment 1.Fig. 5 is the pipe cutaway view of supercooling portion in the condenser for use in vehicle of expression embodiment 1.Fig. 6 is the stereogram of supercooling portion in the condenser for use in vehicle of expression embodiment 1.
The freeze cycle of the vehicle of the condenser for use in vehicle A1 of employing embodiment 1 as shown in Figure 1, comprises compressor 1, condenser for use in vehicle A1, expansion valve 2, evaporimeter 3, condensation part 4, fluid reservoir 5 (liquid storing part) and supercooling portion 6.
Above-mentioned compressor 1 is by as drivings such as the engine of vehicle-mounted power source, motor, after the vaporizing system cryogen compression of the low-pressure low-temperature that will send here from evaporimeter 3, delivers to condenser for use in vehicle A1.
Above-mentioned condenser for use in vehicle A1 comprises condensation part 4, fluid reservoir 5 and supercooling portion 6 integratedly.Heat exchange will be carried out from high-temperature high-pressure refrigerant and the extraneous air that the compressor 1 of freeze cycle is discharged in above-mentioned condensation part 4, make its heat radiation, cooling.Above-mentioned fluid reservoir 5 is stored in the cold-producing medium that this condensation part 4 has been liquefied.Above-mentioned supercooling portion 6 will be from the high pressure liquid refrigerant cooling of this fluid reservoir 5.
Above-mentioned condensation part 4 is by the air blast of the wind that travels, fan, will be cooled to condensation point from the vaporizing system cryogen of the HTHP of above-mentioned compressor 1, becomes the liquefied refrigerant of temperature in the high pressure.The moisture, the dirt that contain in the liquefied refrigerant of above-mentioned fluid reservoir 5 with temperature in the high pressure are removed, and store refrigerant is so that can supply with this cold-producing medium smoothly.Above-mentioned supercooling portion 6 make from the high pressure liquid refrigerant of above-mentioned fluid reservoir 5 and between the low pressure refrigerant of above-mentioned evaporimeter 3 by not adopting the heat exchange of fin, will be from the high pressure liquid refrigerant cooling of above-mentioned fluid reservoir 5.
Above-mentioned expansion valve 2 sharply expands the liquefied refrigerant from the high pressure low temperature of above-mentioned supercooling portion 6, becomes the vaporific liquefied refrigerant of low-pressure low-temperature, delivers to evaporimeter 3.In addition, expansion valve 2 is located on the path of 3 refrigerant conveyings from supercooling portion 6 toward evaporimeter.Path from evaporimeter 3 toward supercooling portion 6 refrigerant conveyings is the simple refrigerant passage with valve function.
To import to above-mentioned evaporimeter 3 from the vaporific liquefied refrigerant of above-mentioned expansion valve 2, this evaporimeter 3 is delivered to from blower fan and is absorbed heat the indoor wind of car, makes this liquefied refrigerant evaporation, becomes the vaporizing system cryogen of low-pressure low-temperature.Then, by supercooling portion 6 the vaporizing system cryogen of low-pressure low-temperature is delivered to compressor 1.In addition, evaporimeter 3 is located in the air-conditioning unit, and this air-conditioning unit is configured in the outer instrument board of figure.
In the above-mentioned supercooling portion 6, as shown in Figure 2, will be mutually opposite direction by direction with from the cold-producing medium of the low-pressure side refrigerant passage 8 of above-mentioned evaporimeter 3 by direction setting from the cold-producing medium of the high-pressure side refrigerant passage 7 of above-mentioned fluid reservoir 5.
As shown in Figure 2, the condenser for use in vehicle A1 of embodiment 1 disposes the 1st pipe hydroecium 11 and the 2nd pipe hydroecium 12 in the both end sides of left and right directions.In above-mentioned the 1st pipe hydroecium 11, be provided with the cross septation plate 16 (the 1st demarcation strip) and the vertical demarcation strip 17 (the 1st demarcation strip) that hydroecium inside are separated into condensating refrigerant inlet hydroecium 13, high-pressure refrigerant outlet hydroecium 14 and low pressure refrigerant inlet hydroecium 15.On the other hand, in above-mentioned the 2nd pipe hydroecium 12, as shown in Figure 3, be provided with cross septation plate 21 (the 2nd demarcation strip) and the vertical demarcation strip 22 (the 2nd demarcation strip) that hydroecium inside is separated into condensating refrigerant outlet hydroecium 18, high-pressure refrigerant inlet hydroecium 19 and low pressure refrigerant outlet hydroecium 20.
That is, above-mentioned supercooling portion 6 carries out heat exchange between high-pressure side refrigerant passage 7 and low-pressure side refrigerant passage 8.Above-mentioned high-pressure side refrigerant passage 7 is communicated with the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 with the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned low-pressure side refrigerant passage 8 is communicated with the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 with the low pressure refrigerant outlet hydroecium 20 of above-mentioned the 2nd pipe hydroecium 12.
On above-mentioned the 1st pipe hydroecium 11, be provided with the inlet opening 23 of acceptance from the cold-producing medium of above-mentioned compressor 1 in the position that is communicated with condensating refrigerant inlet hydroecium 13.In addition, on above-mentioned the 1st pipe hydroecium 11, be provided with refrigerant inlet opening 24 in the position that is communicated with condensating refrigerant inlet hydroecium 13 and high-pressure refrigerant outlet hydroecium 14, this refrigerant inlet opening 24 is to accept from the inlet peristome of the cold-producing medium of above-mentioned evaporimeter 3 with towards the exit opening portion of the cold-producing medium of above-mentioned expansion valve 2.
In above-mentioned the 2nd pipe hydroecium 12, be provided with condensating refrigerant is exported the liquid storage inlet tube 25 that hydroecium 18 is communicated with fluid reservoir 5, be provided with the high-pressure refrigerant liquid storage outlet 26 that hydroecium 19 is communicated with fluid reservoir 5 that enters the mouth.In addition, on above-mentioned the 2nd pipe hydroecium 12, be provided with low pressure refrigerant is exported the low pressure refrigerant pipe 27 that hydroecium 20 is communicated with compressor 1.
As shown in Figures 2 and 3, above-mentioned condensation part 4 has many condensation part pipes 28 and is located at the fin 29 between adjacent tubes in these many condensation part pipes 28.Above-mentioned many condensation parts pipe 28 will above-mentioned the 1st pipe hydroecium 11 condensating refrigerants inlet hydroeciums 13, export hydroecium 18 with the condensating refrigerant of above-mentioned the 2nd pipe hydroecium 12 and link up.As shown in Figure 4, above-mentioned condensation part pipe 28 carries out heat exchange effectively in order to make by its inner cold-producing medium and extraneous air, forms flat oval cross sectional shape, makes the structure of interior sheet or porous (separation).Fin 29 is located at the position of the flat upper and lower surface of condensation part pipe 28.
As depicted in figs. 1 and 2, above-mentioned fluid reservoir 5 is configured in the position that is adjacent along above-mentioned the 2nd pipe hydroecium 12, import cold-producing medium from the condensating refrigerant outlet hydroecium 18 of above-mentioned the 2nd pipe hydroecium 12, cold-producing medium is supplied to the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12.
As shown in Figure 5 and Figure 6, above-mentioned supercooling portion 6 is made of many high pressure side pipes 30 and supercooling portion tube shell 31.Above-mentioned many high pressure side pipes 30 link up the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 and the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned supercooling portion tube shell 31 links up the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 low pressure refrigerant outlet hydroecium 20 with above-mentioned the 2nd pipe hydroecium 12.Above-mentioned high pressure side pipe 30 and condensation part pipe 28 similarly carry out heat exchange effectively in order to make by its inner high-pressure refrigerant and low pressure refrigerant by the outside, form flat oval cross sectional shape.As shown in Figure 5 and Figure 6, above-mentioned supercooling portion tube shell 31 across uniformly-spaced space configuration, positions 6 high pressure side pipes 30 around whole 6 high pressure side pipes 30 time in order to keep this state to 6 high pressure side pipes 30.
The path that will be formed by the inner surface of above-mentioned high pressure side pipe 30 is as high-pressure side refrigerant passage 7, and the path that will be formed by the outer surface of the inner surface of above-mentioned supercooling portion tube shell 31 and above-mentioned high pressure side pipe 30 is as low-pressure side refrigerant passage 8.
Below, its effect is described.
" technology of existing condenser for use in vehicle " at first, is described.Then, be divided into " effect that improves the refrigerating capacity refrigerating efficiency ", " improving the effect of condensation performance ", " making the effect of condenser for use in vehicle miniaturization ", " not adopting the supercooling effect of fin " several sections, the effect of the condenser for use in vehicle A1 of embodiment 1 is described.
" technology of existing condenser for use in vehicle "
As shown in Figure 7, the freeze cycle of vehicle air conditioner comprises compressor (Compressor), condenser for use in vehicle, expansion valve (TXV) and evaporimeter (Evaporator).Existing condenser for use in vehicle comprises condensation part (Condenser), fluid reservoir (Liquid Tank) and supercooling portion (Sub CoolCondenser) integratedly.Be known in this supercooling portion, similarly adopt fin, make from compressor and carry out heat exchange, make its heat radiation and cool off, pass through expansion valve again and supply to evaporimeter through high pressure liquid refrigerant and the extraneous air that condensation part and fluid reservoir import with the condensation part.In addition, come the cold-producing medium of flash-pot directly to supply to compressor.
The mollier diagram of Fig. 8 is represented existing freeze cycle.Among the figure, transverse axis is represented enthalpy, and the longitudinal axis is represented pressure.The low-pressure low-temperature vaporizing system cryogen that A is ordered is increased pressure while improving enthalpy in compressor, become the vaporizing system cryogen of HTHP at the B of compressor outlet point.Then, the cold-producing medium of compressor outlet carries out heat exchange with extraneous air in the condensation part of condenser for use in vehicle and supercooling portion, is dispelled the heat and is cooled, and becomes liquefied refrigerant warm in the high pressure at the C point of supercooling portion outlet.Then, sharply expand, become the vaporific liquefied refrigerant of low-pressure low-temperature at the D point of expansion valve outlet by the liquefied refrigerant that in expansion valve, makes temperature in the high pressure.Then, the vaporific liquefied refrigerant of low-pressure low-temperature absorbs heat in evaporimeter, becomes the vaporizing system cryogen of low-pressure low-temperature at the E of evaporator outlet point.This flow process is carried out repeatedly.
From mollier diagram shown in Figure 8 as can be known, the refrigeration performance (performance of evaporator) of evaporimeter performance be by the refrigerant condition of the refrigerant condition of evaporator inlet and evaporator outlet poor, be that the enthalpy extent determines.That is, though the refrigerant flow of expansion valve control evaporator inlet,, the refrigerant condition of evaporator inlet (enthalpy, humidity) is by the condensation ability decision of condenser for use in vehicle.
To this, in the existing condenser for use in vehicle, because supercooling portion is the air-cooled type heat-exchanging structure by dispelling the heat with the heat exchange of extraneous air, so, the outlet refrigerant condition (enthalpy) of condenser for use in vehicle, even rate of heat exchange is 100%, refrigerant temperature can not be cooled to below the external air temperature.Therefore, when for example externally air themperature is 35 ℃ of such high load capacity cooling operations, owing to refrigerant temperature can not be cooled to external air temperature below 35 ℃, so, can not guarantee has bigger enthalpy difference between evaporator inlet and the evaporator outlet, refrigerating capacity and refrigerating efficiency are low.
On the other hand, in recent years, for environmental protection, vehicle trends towards with the float toleranceization of booster engine or with engine and the motor hybrid powerization as power source.Therefore, as shown in Figure 9, the float tolerance engine vehicle of band booster, because the reason that the space is set of CAC (Charge Air Cooler, charger-air cooler), the space that is provided with of compressor and radiator is restricted.In addition, the vehicle of mixed motivity type, the cooling for the high-voltage system of drive motor etc. is arranged on condenser side with secondary radiator, and like this, the space that is provided with of condenser is restricted.And, because collision restriction (crashworthiness) has also produced the so-called limitation in height with the gap enlargement on engine room top.Because there is the recoil to air supply rate in said circumstances, the height of condenser reduces, the tendency that the condensation ability reduces.At this moment, compare when obtaining guaranteeing with benchmark condenser height, refrigerating capacity and refrigerating efficiency reduce.
In addition, during the space is set is restricted to certain altitude of condenser, the performance of supercooling portion (refrigerant condition) is influential to performance of evaporator (cold power), so, in order to improve the performance of supercooling portion, enlarge the heat exchange area of supercooling portion.But at this moment, as shown in figure 10, when the heat exchange area of supercooling portion was enlarged, the area of expansion was equivalent to the amount that the heat exchange area of condensation part dwindles, so the condensation performance reduces.
And fin is similarly adopted in existing supercooling portion and condensation part, cools off by dispelling the heat with the heat exchange of extraneous air.That is, when high vehicle speeds, can obtain high heat exchange performance by the wind speed of the wind that travels.But, when stopping or traffic jam travel when waiting because do not travel wind or the wind that travels are very little, so, refrigerating capacity and refrigerating efficiency reduction.
The requirement of the inventor in order to realize improving the heat exchange performance of supercooling portion corresponding to the miniaturization ground of condenser for use in vehicle, the low-pressure side refrigerant temperature of freeze cycle is lower than external air temperature when being conceived to make high load capacity.According to this starting point, the structure of supercooling portion is, make from the high pressure liquid refrigerant of liquid storing part and between the low pressure refrigerant of the evaporimeter of freeze cycle by not using the heat exchange of fin, will be from the high pressure liquid refrigerant cooling of liquid storing part.As a result,, do not reduce the condensation performance yet,, realized the raising of refrigerating capacity and refrigerating efficiency by refrigerant temperature being reduced to the supercooling below the external air temperature even be subjected to Influences on Wind Velocity.
" improve the effect of refrigerating capacity refrigerating efficiency "
In the following description, the whole size of the whole size of the condenser for use in vehicle A1 of embodiment 1 and existing condenser for use in vehicle is identical, and the ratio in the zone of the zone of the condensation part 4 of embodiment 1 and the ratio in the zone of supercooling portion 6 and existing condensation part and the zone of supercooling portion is identical.
The mollier diagram of Figure 11, the freeze cycle of the condenser for use in vehicle A1 of embodiment 1 is adopted in expression.Among the figure, transverse axis is represented enthalpy, and the longitudinal axis is represented pressure.The low-pressure low-temperature vaporizing system cryogen that A is ordered is increased pressure while improving enthalpy in compressor 1, become the vaporizing system cryogen of HTHP at the B of compressor outlet point.Then, the cold-producing medium of compressor outlet carries out heat exchange with extraneous air in the condensation part 4 of condenser for use in vehicle A1, is dispelled the heat and is cooled, C ' of 4 outlets liquefied refrigerants that become temperature in the high pressure in the condensation part.And then in the supercooling portion 6 of condenser for use in vehicle A1, from the low pressure refrigerant cooling that the high pressure liquid refrigerant of fluid reservoir 5 is come flash-pot 3, " point becomes the liquefied refrigerant of high pressure low temperature at the C of supercooling portion 6 outlets.Then, in expansion valve 2, sharply expand, " put the vaporific liquefied refrigerant that becomes low-pressure low-temperature at the D of expansion valve outlet by the liquefied refrigerant that makes high pressure low temperature.Then, the vaporific liquefied refrigerant of low-pressure low-temperature absorbs heat in evaporimeter 3, becomes the vaporizing system cryogen of low-pressure low-temperature at the E point of evaporimeter 3 outlets.This flow process is carried out repeatedly.
From mollier diagram shown in Figure 11 as can be known, the refrigeration performance (performance of evaporator) of evaporimeter 3 performance be by the refrigerant condition of the refrigerant condition of evaporator inlet and evaporator outlet poor, be that the enthalpy extent determines.That is, though the refrigerant flow of expansion valve 2 control evaporator inlets,, the refrigerant condition of evaporator inlet (enthalpy, humidity) is by the condensation ability decision of condenser for use in vehicle A1.
To this, among the condenser for use in vehicle A1 of embodiment 1, in supercooling portion 6 from the high pressure liquid refrigerant of fluid reservoir 5 when the high load capacity cooling operation, by than external air temperature low pressure refrigerant cooling low, that come flash-pot 3.Therefore, be that enthalpy is reduced to the C point from C ' in the supercooling portion of existing condenser for use in vehicle, and in the supercooling portion 6 of embodiment 1, " the point that enthalpy can be reduced to C from C '.Utilize this supercooling effect, in evaporimeter 3 consumable cold and hot can be enthalpy, be from the D degree of ", compare with existing condenser for use in vehicle, having enlarged from a D " to a D to a some E, refrigeration performance is improved.
Like this, the size of the condenser for use in vehicle A1 of embodiment 1 is big or small identical with existing condenser for use in vehicle, when the ratio in the zone of the zone of the condensation part 4 of embodiment 1 and the ratio in the zone of supercooling portion 6 and existing condensation part and the zone of supercooling portion is identical, can improve refrigerating capacity and refrigerating efficiency.
" improve the effect of condensation performance "
In the following description, the whole size of the whole size of the condenser for use in vehicle A1 of embodiment 1 and existing condenser for use in vehicle is identical, and the radical of the refrigerant pipe of the supercooling portion 6 of embodiment 1 is identical with the radical of the refrigerant pipe of existing supercooling portion.
Therefore, during the whole size of the condenser for use in vehicle A1 of embodiment 1 and existing condenser for use in vehicle whole big or small identical, as shown in figure 12, the heat exchange area that can make condensation part 4 is than existing enlarged areas, and the degree of its expansion is equivalent to the amount of the heat exchange area of supercooling portion 6 than existing area minimizing.
Like this, the whole size of the condenser for use in vehicle A1 of embodiment 1 is identical with the whole size of existing condenser for use in vehicle, when the radical of the radical of the refrigerant pipe of supercooling portion 6 and the refrigerant pipe of existing supercooling portion is identical, the supercooling performance that can make supercooling portion 6 is than existing improve, and, can make the condensation performance than existing raising because the heat exchange area of condensation part 4 enlarges.
" make the effect of condenser for use in vehicle miniaturization "
In the following description, the heat exchange area of the condensation part 4 of the condenser for use in vehicle A1 of embodiment 1 is identical with the heat exchange area of the condensation part of existing condenser for use in vehicle.
The condenser for use in vehicle A1 of embodiment 1, owing to do not use fin, so even the refrigerant pipe radical of supercooling portion 6 is identical with the refrigerant pipe radical of existing supercooling portion, the required area that also can make supercooling portion 6 is littler than the required area of the existing supercooling portion that uses fin.And, when if the supercooling performance level of the supercooling performance of supercooling portion 6 and existing supercooling portion is identical, the radical of the refrigerant pipe of supercooling portion 6 is lacked than existing, compare when identical, can further reduce the required area of supercooling portion with the refrigerant pipe radical of the refrigerant pipe radical of supercooling portion 6 and existing supercooling portion.
Like this, when the heat exchange area of the condensation part 4 of the condenser for use in vehicle A1 of embodiment 1 is identical with the heat exchange area of the condensation part of existing condenser for use in vehicle, can keep original condensation performance with the heat exchange area of identical condensation part 4, and realize the miniaturization of global shape.Like this, for environmental protection, can promote the float toleranceization of band booster engine, be the hybrid powerization of power source, even the height of condenser reduces with engine and motor, also can suppress the reduction of condensation performance, can guarantee original refrigerating capacity and refrigerating efficiency at least.
" do not use the supercooling effect of fin "
In the supercooling portion 6 of the condenser for use in vehicle A1 of embodiment 1, high-pressure refrigerant from fluid reservoir 5, high-pressure refrigerant at high-pressure refrigerant inlet hydroecium 19 that links the 2nd pipe hydroecium 12 and the 1st pipe hydroecium 11 exports in the many high pressure side pipes 30 of hydroecium 14, for example flows from right to left in Fig. 2.Simultaneously, come the low pressure refrigerant of flash-pot 3,, for example in Fig. 2, flow from left to right in the inside of the supercooling portion tube shell 31 of the low pressure refrigerant outlet hydroecium 20 of low pressure refrigerant inlet hydroecium 15 that links the 1st pipe hydroecium 11 and the 2nd pipe hydroecium 12.Then, between high-pressure refrigerant by high pressure side pipe 30 inside and low pressure refrigerant, carry out heat exchange effectively by the outside that centered on by supercooling portion tube shell 21.
Like this, in supercooling portion 6, owing to do not use the heat exchange of fin, so, different with the supercooling portion that uses fin, can not be subjected to Influences on Wind Velocity, stably carry out heat exchange.That is, when stopping and traffic jam when travelling, though do not travel wind or the wind that travels are very little,, do not had or not the influence of the wind that travels, can bring into play refrigerating capacity and refrigerating efficiency.
Below, description effect
The condenser for use in vehicle A1 of embodiment 1 can obtain the following effect of enumerating.
(1) condenser for use in vehicle A1 comprises condensation part 4, liquid storing part (fluid reservoir 5) and supercooling portion 6 integratedly.Heat exchange will be carried out from high-temperature high-pressure refrigerant and the extraneous air that the compressor 1 of freeze cycle is discharged in this condensation part 4, make its heat radiation and cool off.This liquid storing part is stored in the cold-producing medium that this condensation part 4 has been liquefied.This supercooling portion 6 will be from the high pressure liquid refrigerant cooling of this liquid storing part (fluid reservoir 5).Above-mentioned supercooling portion 6 make from the high pressure liquid refrigerant of above-mentioned liquid storing part (fluid reservoir 5) and between the low pressure refrigerant of the evaporimeter 3 of above-mentioned freeze cycle by not using the heat exchange of fin, will be from the high pressure liquid refrigerant cooling of above-mentioned liquid storing part (fluid reservoir 5).Therefore, even be subjected to Influences on Wind Velocity, the condensation performance does not reduce yet, and by refrigerant temperature being reduced to the supercooling below the external air temperature, can realize the raising of refrigerating capacity and refrigerating efficiency.
(2) above-mentioned supercooling portion 6 will be mutually opposite direction by direction with from the cold-producing medium of the low-pressure side refrigerant passage 8 of above-mentioned evaporimeter 3 by direction setting from the cold-producing medium of the high-pressure side refrigerant passage 7 of above-mentioned liquid storing part (fluid reservoir 5).Therefore, carry out the situation of heat exchange when high-pressure side cold-producing medium and low-pressure side cold-producing medium are flowed in the same direction and compare, can be by carrying out heat exchange effectively with the high-pressure side refrigerant cools.In addition, when high-pressure side cold-producing medium and low-pressure side cold-producing medium are flowed in the same direction, begin the zone in heat exchange, though the refrigerant temperature difference is big, in the heat exchange end region, the refrigerant temperature difference reduces.To this, when high-pressure side cold-producing medium and low-pressure side cold-producing medium are flowed in the opposite direction, begin the zone from heat exchange and can guarantee that to the heat exchange end region big refrigerant temperature is poor.
(3) both end sides at left and right directions disposes the 1st pipe hydroecium 11 and the 2nd pipe hydroecium 12, in above-mentioned the 1st pipe hydroecium 11, be provided with the cross septation plate 16 and the vertical demarcation strip 17 that hydroecium inside are separated into condensating refrigerant inlet hydroecium 13, high-pressure refrigerant outlet hydroecium 14 and low pressure refrigerant inlet hydroecium 15, in above-mentioned the 2nd pipe hydroecium 12, be provided with the cross septation plate 21 and the vertical demarcation strip 22 that hydroecium inside are separated into condensating refrigerant outlet hydroecium 18, high-pressure refrigerant inlet hydroecium 19 and low pressure refrigerant outlet hydroecium 20.Above-mentioned supercooling portion 6 carries out heat exchange between high-pressure side refrigerant passage 7 and low-pressure side refrigerant passage 8.Above-mentioned high-pressure side refrigerant passage 7 is communicated with the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 with the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned low-pressure side refrigerant passage 8 is communicated with the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 with the low pressure refrigerant outlet hydroecium 20 of above-mentioned the 2nd pipe hydroecium 12.Therefore, directly utilize existing the 1st pipe hydroecium 11 and the 2nd pipe hydroecium 12 that is configured in the left and right directions two side ends, each hydroecium 11,12 is divided into Room 3, can easily be provided as the high-pressure side refrigerant passage 7 and the low-pressure side refrigerant passage 8 of passing through the mutually opposite supercooling of direction portion 6 of cold-producing medium.
(4) above-mentioned condensation part 4 has many condensation part pipes 28 and is located at the fin 29 between adjacent tubes in these many condensation part pipes 28.Above-mentioned many condensation parts pipe 28 links up the condensating refrigerant inlet hydroecium 13 of above-mentioned the 1st pipe hydroecium 11 and the condensating refrigerant outlet hydroecium 18 of above-mentioned the 2nd pipe hydroecium 12.Above-mentioned liquid storing part is made of fluid reservoir 5, this fluid reservoir 5 is configured in the position that is adjacent along above-mentioned the 2nd pipe hydroecium 12, import cold-producing medium from the condensating refrigerant outlet hydroecium 18 of above-mentioned the 2nd pipe hydroecium 12, cold-producing medium is supplied to the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12.Therefore, needn't carry out significantly design alteration, with regard to the condensation performance that can obtain with the condenser for use in vehicle A1 of the compactedness when setting up fluid reservoir 5 as guaranteeing to carry out heat exchange with extraneous air to existing condenser for use in vehicle.
(5) above-mentioned supercooling portion 6 is made of many high pressure side pipes 30 and supercooling portion tube shell 31.Above-mentioned many high pressure side pipes 30 link up the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 and the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned supercooling portion tube shell 31 links up the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 low pressure refrigerant outlet hydroecium 20 with above-mentioned the 2nd pipe hydroecium 12.The path that will be formed by the inner surface of above-mentioned high pressure side pipe 30 is as high-pressure side refrigerant passage 7, and the path that will be formed by the outer surface of the inner surface of above-mentioned supercooling portion tube shell 31 and above-mentioned high pressure side pipe 30 is as low-pressure side refrigerant passage 8.Therefore, form the supercooling portion 6 of the miniaturization that has suppressed requisite space, can bring into play the supercooling performance with big heat exchange area.
At first, structure is described.
Figure 13 is the amplification view of supercooling portion of the 2nd pipe hydroecium side in the condenser for use in vehicle of expression embodiment 2.Figure 14 is the B-B cutaway view of Figure 13, the supercooling portion in the condenser for use in vehicle of expression embodiment 2.Figure 15 is the pipe cutaway view of supercooling portion in the condenser for use in vehicle of expression embodiment 2.
As shown in figure 13, the condenser for use in vehicle A2 of embodiment 2 comprises condensation part 4, supercooling portion the 6, the 2nd pipe hydroecium 12, condensating refrigerant outlet hydroecium 18, high-pressure refrigerant inlet hydroecium 19, low pressure refrigerant outlet hydroecium 20, cross septation plate 21, vertical demarcation strip 22, liquid storage inlet tube 25, liquid storage outlet 26, low pressure refrigerant pipe 27, condensation part pipe 28, fin 29, inside tube 32 and outboard tube 33.
Above-mentioned supercooling portion 6 is the bimetallic tube structures that are made of many inside tube 32 and Duo Gen outboard tube 33.Above-mentioned many inside tube 32 link up the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 and the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned many outboard tube 33 link up the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 and the low pressure refrigerant outlet hydroecium 20 of above-mentioned the 2nd pipe hydroecium 12.
As shown in figure 15, the path that will be formed by the inner surface of above-mentioned inside tube 32 is as high-pressure side refrigerant passage 7, and the path that will be formed by the outer surface of the inner surface of above-mentioned outboard tube 33 and above-mentioned inside tube 32 is as low-pressure side refrigerant passage 8.In addition, other structure is identical with embodiment 1, therefore the structure of correspondence is annotated with same reference numerals, and its explanation is omitted.
Then, its effect is described.
In the supercooling portion 6 of the condenser for use in vehicle A2 of embodiment 2, high-pressure refrigerant from fluid reservoir 5 exports in the many inside tube 30 of hydroecium 14 at the high-pressure refrigerant of high-pressure refrigerant inlet hydroecium 19 that links the 2nd pipe hydroecium 12 and the 1st pipe hydroecium 11, for example flows from right to left in Figure 13.Simultaneously, the low pressure refrigerant that comes flash-pot 3 for example flows in Figure 13 from left to right in outboard tube 33 inside of the low pressure refrigerant outlet hydroecium 20 of low pressure refrigerant inlet hydroecium 15 that links the 1st pipe hydroecium 11 and the 2nd pipe hydroecium 12.And, in the inside tube 32 that constitutes by bimetallic tube and each compound tube of outboard tube 33, between high-pressure refrigerant by inside tube 32 inside and low pressure refrigerant, carry out heat exchange effectively by the outside that centers on by outboard tube 33.Other effect is identical with embodiment 1, so its explanation is omitted.
Then, description effect.
In the condenser for use in vehicle of embodiment 2, except (1)～(4) effect, also has following effect with embodiment 1.
(6) above-mentioned supercooling portion 6 is the bimetallic tube structures that are made of many inside tube 32 and Duo Gen outboard tube 33.Above-mentioned many inside tube 32 link up the high-pressure refrigerant inlet hydroecium 19 of above-mentioned the 2nd pipe hydroecium 12 and the high-pressure refrigerant outlet hydroecium 14 of above-mentioned the 1st pipe hydroecium 11.Above-mentioned many outboard tube 33 link up the low pressure refrigerant inlet hydroecium 15 of above-mentioned the 1st pipe hydroecium 11 and the low pressure refrigerant outlet hydroecium 20 of above-mentioned the 2nd pipe hydroecium 12.The path that will be formed by the inner surface of above-mentioned inside tube 32 is as high-pressure side refrigerant passage 7, and the path that will be formed by the outer surface of the inner surface of above-mentioned outboard tube 33 and above-mentioned inside tube 32 is as low-pressure side refrigerant passage 8.Therefore, for example, the condensation part can be managed 28 sharedly, help the cost of supercooling portion 6 as outboard tube 33, and, by the independently heat exchange action of each bimetallic tube structure, can bring into play the supercooling performance.
Embodiment 3
Embodiment 3 is examples of having cancelled the fin that is located at the interface between condensation part and the supercooling portion.
At first, structure is described.
Figure 16 is the amplification view of supercooling portion of the 2nd pipe hydroecium side in the condenser for use in vehicle of expression embodiment 3.
As shown in figure 16, the condenser for use in vehicle A3 of embodiment 3 comprises condensation part 4, supercooling portion the 6, the 2nd pipe hydroecium 12, condensating refrigerant outlet hydroecium 18, high-pressure refrigerant inlet hydroecium 19, low pressure refrigerant outlet hydroecium 20, cross septation plate 21, vertical demarcation strip 22, liquid storage inlet tube 25, liquid storage outlet 26, low pressure refrigerant pipe 27, condensation part pipe 28, fin 29, inside tube 32 and outboard tube 33.
This embodiment 3, its essential structure is identical with the condenser for use in vehicle A2 of embodiment 2, but cancelled the fin that is located at the interface between condensation part 4 and the supercooling portion 6, the condensation part of the lowest positions of condensation part 4 pipe 28 ' and the outboard tube 33 of the position, the top of supercooling portion 6 between be provided with space S.In addition, other structure is identical with embodiment 1,2, and therefore the structure to correspondence marks with same reference numerals, and its explanation is omitted.
Then, its effect is described.In the condenser for use in vehicle A3 of this embodiment 3, owing to cancelled the fin that is located at the interface between condensation part 4 and the supercooling portion 6, so, can avoid the heat transmission between supercooling portion 6 and the extraneous air, and can avoid the heat transmission between supercooling portion 6 and the condensation part 4.Can guarantee that supercooling portion 6 has and condensation part 4 heat exchange environment independently, the influence of the wind of avoiding travelling improves the supercooling performance.In addition, other effect is identical with embodiment 1,2, and its explanation is omitted.
Then, description effect.
In the condenser for use in vehicle of embodiment 3, except the effect of (1)～(5) with embodiment 1 and embodiment 2 (6), also has following effect.
(7) owing to cancelled the fin that is located at the interface between above-mentioned condensation part 4 and the above-mentioned supercooling portion 6, so, guarantee that supercooling portion 6 has with respect to condensation part 4 heat exchange environment independently, the influence of the wind of avoiding travelling, and raising supercooling performance.
More than, with reference to embodiment 1～embodiment 3 condenser for use in vehicle of the present invention has been described, still, concrete structure is not limited to these embodiment.Only otherwise break away from the invention main idea of each technical scheme of claims, just can allow and carry out design alteration, append etc.
In embodiment 1～3,, as shown in Figure 4, represented in the pipe of flat oval cross sectional shape, to have disposed the example of interior sheet as condensation part pipe 28.But the cross sectional shape of condensation part pipe, structure are not limited to shown in Figure 4.For example, also can become the condensation part pipe 28a that in the pipe of flat oval cross sectional shape, is incorporated with reinforcement shown in Figure 17 (a) like that.Also can by forming the extrusion molding of many square refrigerant passage, form condensation part pipe 28b shown in Figure 17 (b) like that.Also can by forming the extrusion molding of many circular refrigerant passage, make condensation part pipe 28c shown in Figure 17 (c) like that.
In embodiment 1, as shown in Figure 5, expression supercooling portion 6 is by many high pressure side pipes 30 and the example that constitutes around its supercooling portion tube shell 31.But, for example also can be as shown in Figure 18, supercooling portion 6 be by the high pressure side pipe 30 that forms by the extrusion molding that forms many circular refrigerant passage ' and around many high pressure side pipes 30 ' supercooling portion tube shell 31 constitute.
In embodiment 2,3, as the pipe of supercooling portion 6 structure, as shown in figure 15, expression is the example of the bimetallic tube that is made of inside tube 32 and outboard tube 33.But the pipe structure of supercooling portion is not limited to shown in Figure 15.For example, also can form the pipe 34a of supercooling portion by the extrusion molding that forms 2 flat high-pressure side refrigerant passage 7 and low-pressure side refrigerant passage 8 shown in Figure 19 (a) like that.Also can be shown in Figure 19 (b) like that, the extrusion molding pipe of the low-pressure side refrigerant passage 8 by forming flat high-pressure side refrigerant passage 7 and periphery and the combination of interior sheet form the pipe 34b of supercooling portion.Also can be shown in Figure 19 (c) like that, the extrusion molding of the low-pressure side refrigerant passage 8 by forming square high-pressure side refrigerant passage 7 and periphery forms the pipe 34c of supercooling portion.Also can be shown in Figure 19 (d) like that, the extrusion molding of the low-pressure side refrigerant passage 8 by forming circular high-pressure side refrigerant passage 7 and periphery forms the pipe 34d of supercooling portion.Also can be shown in Figure 19 (e) like that, the extrusion molding pipe by forming 2 flat high-pressure side refrigerant passage 7 and low-pressure side refrigerant passage 8 and the combination of interior sheet form the pipe 34e of supercooling portion.Also can be shown in Figure 19 (f) like that, the extrusion molding pipe by forming flat high-pressure side refrigerant passage 7 and interrupted low-pressure side refrigerant passage 8 and the combination of interior sheet form the pipe 34f of supercooling portion.Also can be shown in Figure 19 (g) like that, the high-pressure side refrigerant passage 7 by forming many circles and the extrusion molding of low-pressure side refrigerant passage 8 form the pipe 34g of supercooling portion.Also can be shown in Figure 19 (h) like that, the high-pressure side refrigerant passage 7 by forming many circles and the extrusion molding of many oblong low-pressure side refrigerant passage 8 form the pipe 34h of supercooling portion.
Claims (7)
1. condenser for use in vehicle, it comprises that integratedly the high-temperature high-pressure refrigerant that will discharge from the compressor of freeze cycle and extraneous air carry out heat exchange and make the condensation part of its heat radiation and cooling, be stored in the liquid storing part of the cold-producing medium that this condensation part has been liquefied, the supercooling portion that high-pressure refrigerant from this liquid storing part is cooled off, it is characterized in that, above-mentioned supercooling portion make from the high pressure liquid refrigerant of above-mentioned liquid storing part and between the low pressure refrigerant of the evaporimeter of above-mentioned freeze cycle by not using the heat exchange of fin, will be from the high pressure liquid refrigerant cooling of above-mentioned liquid storing part.
2. condenser for use in vehicle according to claim 1, it is characterized in that above-mentioned supercooling portion will be mutually opposite direction by direction with from the cold-producing medium of the low-pressure side refrigerant passage of above-mentioned evaporimeter by direction setting from the cold-producing medium of the high-pressure side refrigerant passage of above-mentioned liquid storing part.
3. condenser for use in vehicle according to claim 2 is characterized in that,
Both end sides at left and right directions disposes the 1st pipe hydroecium and the 2nd pipe hydroecium;
In above-mentioned the 1st pipe hydroecium, be provided with the 1st demarcation strip that hydroecium inside is separated into condensating refrigerant inlet hydroecium, high-pressure refrigerant outlet hydroecium and low pressure refrigerant inlet hydroecium;
In above-mentioned the 2nd pipe hydroecium, be provided with the 2nd demarcation strip that hydroecium inside is separated into condensating refrigerant outlet hydroecium, high-pressure refrigerant inlet hydroecium and low pressure refrigerant outlet hydroecium;
Above-mentioned supercooling portion carries out heat exchange between high-pressure side refrigerant passage and low-pressure side refrigerant passage, above-mentioned high-pressure side refrigerant passage is communicated with the high-pressure refrigerant inlet hydroecium of above-mentioned the 2nd pipe hydroecium with the high-pressure refrigerant outlet hydroecium of above-mentioned the 1st pipe hydroecium, above-mentioned low-pressure side refrigerant passage is communicated with the low pressure refrigerant inlet hydroecium of above-mentioned the 1st pipe hydroecium with the low pressure refrigerant outlet hydroecium of above-mentioned the 2nd pipe hydroecium.
4. condenser for use in vehicle according to claim 3 is characterized in that,
Above-mentioned condensation part has the fin between the adjacent tubes of managing and being located at these many condensation part pipes in many condensation parts; Above-mentioned many condensation parts pipe links up the condensating refrigerant inlet hydroecium of above-mentioned the 1st pipe hydroecium and the condensating refrigerant outlet hydroecium of above-mentioned the 2nd pipe hydroecium;
Above-mentioned liquid storing part is made of fluid reservoir, this fluid reservoir is configured in and the 2nd pipe hydroecium position adjacent along above-mentioned the 2nd pipe hydroecium, import cold-producing medium from the condensating refrigerant outlet hydroecium of above-mentioned the 2nd pipe hydroecium, cold-producing medium is supplied to the high-pressure refrigerant inlet hydroecium of above-mentioned the 2nd pipe hydroecium.
5. according to claim 3 or 4 described condenser for use in vehicle, it is characterized in that,
Above-mentioned supercooling portion is made of many high pressure side pipes and supercooling portion tube shell, above-mentioned many high pressure side pipes link up the high-pressure refrigerant outlet hydroecium of the high-pressure refrigerant of above-mentioned the 2nd pipe hydroecium inlet hydroecium with above-mentioned the 1st pipe hydroecium, and the enter the mouth low pressure refrigerant of hydroecium and above-mentioned the 2nd pipe hydroecium of the low pressure refrigerant that above-mentioned supercooling portion tube shell will above-mentioned the 1st pipe hydroecium exports hydroecium and links up;
The path that will be formed by the inner surface of above-mentioned high pressure side pipe is as the high-pressure side refrigerant passage, and the path that will be formed by the outer surface of the inner surface of above-mentioned supercooling portion tube shell and above-mentioned high pressure side pipe is as the low-pressure side refrigerant passage.
6. according to claim 3 or 4 described condenser for use in vehicle, it is characterized in that,
Above-mentioned supercooling portion is the bimetallic tube structure that is made of many inside tube and Duo Gen outboard tube, above-mentioned many inside tube link up the high-pressure refrigerant inlet hydroecium of above-mentioned the 2nd pipe hydroecium and the high-pressure refrigerant outlet hydroecium of above-mentioned the 1st pipe hydroecium, and above-mentioned many outboard tube link up the low pressure refrigerant inlet hydroecium of above-mentioned the 1st pipe hydroecium and the low pressure refrigerant outlet hydroecium of above-mentioned the 2nd pipe hydroecium;
The path that will be formed by the inner surface of above-mentioned inside tube is as the high-pressure side refrigerant passage, and the path that will be formed by the outer surface of the inner surface of above-mentioned outboard tube and above-mentioned inside tube is as the low-pressure side refrigerant passage.
7. according to each described condenser for use in vehicle in the claim 4～6, it is characterized in that,
The fin that is arranged on the interface between above-mentioned condensation part and the above-mentioned supercooling portion has been cancelled in above-mentioned condensation part.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008003873 | 2008-01-11 | ||
| JP2008003873A JP2009166529A (en) | 2008-01-11 | 2008-01-11 | Vehicular condenser |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101482349A true CN101482349A (en) | 2009-07-15 |
Family
ID=40585598
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009100000744A Pending CN101482349A (en) | 2008-01-11 | 2009-01-05 | Condenser for use in vehicle |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20090178435A1 (en) |
| EP (1) | EP2078906A2 (en) |
| JP (1) | JP2009166529A (en) |
| CN (1) | CN101482349A (en) |
| TW (1) | TW200930586A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102759282A (en) * | 2011-04-29 | 2012-10-31 | 比亚迪股份有限公司 | Vehicle air-conditioning system |
| CN103868286A (en) * | 2012-12-13 | 2014-06-18 | 现代自动车株式会社 | Cooling system for vehicle |
| CN111114243A (en) * | 2018-10-30 | 2020-05-08 | 现代自动车株式会社 | Cooling module for a vehicle |
| CN113294942A (en) * | 2020-02-24 | 2021-08-24 | 马勒国际公司 | Heat exchanger and refrigerant circulation loop |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9410709B2 (en) * | 2007-04-05 | 2016-08-09 | Johnson Controls Technology Company | Multichannel condenser coil with refrigerant storage receiver |
| KR101238688B1 (en) | 2009-10-16 | 2013-03-04 | 한라공조주식회사 | Cold reserving heat exchanger and manufacturing method thereof |
| FR2960950B1 (en) * | 2010-06-07 | 2013-12-06 | Valeo Systemes Thermiques | UNITARY SYSTEM COMPRISING A CONDENSER, A BOTTLE AND AN INTERNAL HEAT EXCHANGER |
| DE102011007784A1 (en) * | 2011-04-20 | 2012-10-25 | Behr Gmbh & Co. Kg | capacitor |
| US20120291478A1 (en) * | 2011-05-20 | 2012-11-22 | Kia Motors Corporation | Condenser for vehicle and air conditioning system for vehicle |
| KR101734281B1 (en) * | 2011-05-20 | 2017-05-12 | 현대자동차 주식회사 | Condenser for vehicle |
| JP5668610B2 (en) * | 2011-06-10 | 2015-02-12 | カルソニックカンセイ株式会社 | Water-cooled condenser |
| JP5786497B2 (en) * | 2011-06-30 | 2015-09-30 | ダイキン工業株式会社 | Heat exchanger |
| TWM419065U (en) * | 2011-07-15 | 2011-12-21 | Hon Hai Prec Ind Co Ltd | Module data center energy saving system |
| KR101318643B1 (en) | 2011-07-27 | 2013-10-17 | 한라비스테온공조 주식회사 | Cooling module and control method thereof |
| JP5903795B2 (en) * | 2011-08-09 | 2016-04-13 | ダイキン工業株式会社 | Refrigeration unit |
| DE102013211221A1 (en) * | 2013-06-14 | 2014-12-18 | Behr Gmbh & Co. Kg | Heat exchanger |
| WO2017054087A1 (en) | 2015-10-02 | 2017-04-06 | Dana Canada Corporation | Refrigeration system with integrated core structure |
| DE102019211341A1 (en) * | 2019-07-30 | 2021-02-04 | Mahle International Gmbh | Heat exchanger |
| WO2022064554A1 (en) * | 2020-09-23 | 2022-03-31 | 三菱電機株式会社 | Heat exchanger, and air conditioner provided with heat exchanger |
| WO2022215242A1 (en) * | 2021-04-09 | 2022-10-13 | 三菱電機株式会社 | Outdoor unit and air-conditioning device |
| JP7150215B1 (en) * | 2021-06-29 | 2022-10-07 | 三菱電機株式会社 | refrigeration cycle equipment |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5275233A (en) * | 1993-01-25 | 1994-01-04 | Ingersoll-Rand Company | Apparatus for removing moisture from a hot compressed gas |
| DE19918617C2 (en) * | 1999-04-23 | 2002-01-17 | Valeo Klimatechnik Gmbh | Gas cooler for a supercritical CO¶2¶ high pressure refrigerant circuit of an automotive air conditioning system |
| JP2002187424A (en) | 2000-12-19 | 2002-07-02 | Denso Corp | Condenser for vehicle |
| US7337832B2 (en) * | 2003-04-30 | 2008-03-04 | Valeo, Inc. | Heat exchanger |
| JP4222137B2 (en) * | 2003-07-22 | 2009-02-12 | 株式会社デンソー | Radiator |
| US7621150B2 (en) * | 2007-01-05 | 2009-11-24 | Delphi Technologies, Inc. | Internal heat exchanger integrated with gas cooler |
-
2008
- 2008-01-11 JP JP2008003873A patent/JP2009166529A/en active Pending
-
2009
- 2009-01-05 CN CNA2009100000744A patent/CN101482349A/en active Pending
- 2009-01-07 US US12/318,734 patent/US20090178435A1/en not_active Abandoned
- 2009-01-09 EP EP09000199A patent/EP2078906A2/en not_active Withdrawn
- 2009-01-10 TW TW098100831A patent/TW200930586A/en unknown
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102759282A (en) * | 2011-04-29 | 2012-10-31 | 比亚迪股份有限公司 | Vehicle air-conditioning system |
| CN103868286A (en) * | 2012-12-13 | 2014-06-18 | 现代自动车株式会社 | Cooling system for vehicle |
| CN111114243A (en) * | 2018-10-30 | 2020-05-08 | 现代自动车株式会社 | Cooling module for a vehicle |
| CN111114243B (en) * | 2018-10-30 | 2024-03-15 | 现代自动车株式会社 | Cooling module for a vehicle |
| CN113294942A (en) * | 2020-02-24 | 2021-08-24 | 马勒国际公司 | Heat exchanger and refrigerant circulation loop |
Also Published As
| Publication number | Publication date |
|---|---|
| TW200930586A (en) | 2009-07-16 |
| JP2009166529A (en) | 2009-07-30 |
| US20090178435A1 (en) | 2009-07-16 |
| EP2078906A2 (en) | 2009-07-15 |
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