CN1265463A - Heat-exchanger - Google Patents
Heat-exchanger Download PDFInfo
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- CN1265463A CN1265463A CN 00103626 CN00103626A CN1265463A CN 1265463 A CN1265463 A CN 1265463A CN 00103626 CN00103626 CN 00103626 CN 00103626 A CN00103626 A CN 00103626A CN 1265463 A CN1265463 A CN 1265463A
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- heat
- transfer pipe
- heat exchanger
- cold
- row
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D1/047—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 the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
Abstract
Provided is a heat exchanger that can improve heat exchange efficiency. In a heat exchanger where a plurality of plate-shaped fins are stacked at specified intervals, and heat conductive pipes to pass a refrigerant in the direction of stacking are passed, and air is circulated among a group of fins, and the heat conductive pipes are arranged in plural numbers in the direction of air passage, where the key part is divided into the section abundant in the gas of a refrigerant or the gas phase and the section abundant in liquid and the liquid phase, the leeward row serves as an inlet and the windward row serves as an outlet in case that it works as a condenser, and at least some of the paths lie on top of the other between plural rows in the direction of air passage.
Description
The present invention relates to be used for the heat exchanger of aircondition.
In recent years, the necessity of earth environment protection more and more is familiar with by people.As advancing measure to have towards alternativeization of energy-conservationization of the equipment that prevents global warmingization with the cold-producing medium that ozone layer is further destroyed to this earth environment protection.Especially in the electrical household appliance group, make the high aircondition of power consumption (air regulator) high efficiency and alternativeization of cold-producing medium, the viewpoint from the environment of preserving our planet has become most important problem.
As the major technique of the high efficiency of aircondition, be that tubular shape, fin shape and the path form etc. to heat exchanger are improved, so that efficient improves.General horizontal fin finned-tubes exchanger, as shown in Figure 9, the fins set 1 that is arranged in parallel to each other by the interval that many tabular fins are left regulation and the roughly orthogonal thereto shape of relative this fins set 1, promptly the heat-transfer pipe 2 (2i, 2j, 2k) along the stacked direction break-through of fin constitutes.And the heat-transfer pipe of this heat exchanger 2 airflow directions by air (in Fig. 9 laterally) multiple row (being 2 row in Fig. 9) relatively sets.
But, in the occasion that this heat exchanger is used as condenser, the refrigerant inlet side of the heat exchanger more than gas and gas phase composition is furnished with heat-transfer pipe 2i, the 2j of 2 paths side by side, and liquid and liquid phase ingredient are become the heat-transfer pipe 2k pipe arrangement formation of pipe arrangement portion how with 1 path.Cold-producing medium in the pipe arrangement of above-mentioned each path all flows to certain direction (being direction from the top down in Fig. 9) in which heat-transfer pipe 2, is called as 2 paths just to exchange～1 positive exchange way of path.In addition, 3c is the joint member that heat-transfer pipe 2i, the 2j of 2 paths are communicated with the heat-transfer pipe 2k of 1 path.And, the flow of refrigerant direction the when arrow among Fig. 9 is represented condenser working.
Figure 10 is the air themperature of entrance and exit of the cold-producing medium that flows in heat exchanger shown in the pattern ground presentation graphs 9, temperature heat exchanger and the graph of a relation of the refrigerant condition in the heat exchanger.
These 2 paths are just being exchanged～heat exchanger of 1 positive exchange way of path is as the occasion of condenser, and the temperature of cold-producing medium becomes saturation temperature T2 by carry out heat exchange between overheated gas and air from overtemperature T1 at entrance side.And, under the state of this saturation temperature T2, carry out heat exchange in, gasiform condensation of refrigerant and become liquid.In addition, the liquid phase ingredient of cold-producing medium increases, and when the liquid that becomes 100%, is reduced to temperature T 3 from temperature T 2.
Usually, heat exchange amount Q represents with Q=Cq Δ Tm.Here, C is that air specific heat, q are that air mass flow, Δ Tm are the MTDs of the air outlet slit inlet of heat exchanger.When air specific heat C and air mass flow q are one regularly, heat exchange amount Q depends on the MTD Δ Tm of air outlet slit inlet.
If the refrigerant temperature in the heat pipe of the refrigerant temperature in the heat-transfer pipe of wind upside row and its wind downside is compared, except that the short part in porch, be roughly equal temperature on the whole.Therefore, utilize these 2 paths just exchange～heat exchange of the heat exchanger of 1 positive exchange way of path in, cold-producing medium in the heat-transfer pipe of the cold-producing medium in the heat-transfer pipe of wind downside row and the temperature difference of air draught and wind upside is compared with the temperature difference of air draught and is diminished, its result, hot percent of pass reduces and the generation loss.And, in the aircondition occasion of use as the HCFC-2 in a kind of fluorine Lyons of cold-producing medium, generally, when the heat-transfer pipe radical that makes 1 passage portion increases, in fact owing to being accompanied by the increase that improves the pressure loss that causes because of the cold-producing medium flow velocity, so also especially there is the problem that may cause performance of evaporator to reduce.
The objective of the invention is to, address the above problem, the heat exchanger that can improve heat exchanger effectiveness is provided.
The invention of technical scheme 1 is a kind of heat exchanger, many flat fins are stacked with the interval of regulation, along the stacked direction break-through heat-transfer pipe by cold-producing medium is arranged, air is passed through between each fins set, set the described heat-transfer pipe of multiple row at relative air by direction, be distinguished into the many part parts many of gas phase of gas and gas-liquid two-phase flow with the liquid phase of liquid and gas-liquid two-phase flow by the refrigerant condition that in the pipe of described heat-transfer pipe, flows, on the former part, set the 1st heat-transfer pipe of 2 access structures, on latter's part, set the 2nd heat-transfer pipe of 1 access structure, by joint member the 1st and the 2nd heat-transfer pipe is interconnected, and each path of the 1st heat-transfer pipe and the 2nd heat-transfer pipe, the occasion that is working as condenser, wind downside row are inlets, wind upside row become outlet, make subtend flow pattern overlapping between multiple row at air by direction to the part of this path of major general.
Promptly, the part that the gas of cold-producing medium and the gas phase of gas-liquid two-phase flow are many, the 1st heat-transfer pipe by the subtend flow pattern that is configured to 2 access structures constitutes, and the liquid phase of liquid and gas-liquid two-phase flow part how is made of the 2nd heat-transfer pipe of the subtend flow pattern that is configured to 1 access structure.Here, so-called counter current flow is meant: in the occasion of heat exchanger as condenser, the many cold-producing medium of gas is the heat-transfer pipe by wind downside row earlier, thereafter, by with the heat-transfer pipe of these wind downside row roughly at the heat-transfer pipe of the overlapping wind upside row of airflow direction; In the occasion of heat exchanger as evaporimeter, the heat-transfer pipe that cold-producing medium is listed as by the wind upside earlier, thereafter, by the heat-transfer pipe of wind downside row.
Adopt this structure, in the occasion of heat exchanger as condenser, at the wind downside row of entrance side overheated gas refrigerant flow direction at the 1st heat-transfer pipe of 2 access structures, refrigerant temperature flows because of the wind upside row of cold-producing medium in the 1st heat-transfer pipe that descend slightly with air heat exchange and the gas phase of gas-liquid two-phase flow is many and carries out heat exchange with air, and gas refrigerant graduates into liquid.Then, the wind downside row of cold-producing medium in the 2nd heat-transfer pipe of 1 access structure that this liquid phase ingredient is many flow, with air heat exchange in the cold-producing medium that further reduces of temperature side flow and carry out heat exchange on the 2nd heat-transfer pipe apoplexy with air, cold-producing medium is further cooled.Like this, wind downside row the 1st with the 2nd heat-transfer pipe in the 1st comparing of being listed as of refrigerant temperature and corresponding respectively wind upside with the refrigerant temperature in the 2nd heat-transfer pipe, because almost temperature is higher on whole zone,, can improve heat exchanger effectiveness so the temperature difference of cold-producing medium and air becomes greatly.
In addition, in the occasion of heat exchanger as evaporimeter, the mobile of above-mentioned cold-producing medium becomes on the contrary, similarly, wind downside row the 1st with the 2nd heat-transfer pipe in the 1st comparing of being listed as of refrigerant temperature and corresponding respectively wind upside with the refrigerant temperature in the 2nd heat-transfer pipe, because temperature is higher on whole zone almost,, can improve heat exchanger effectiveness so the change of the temperature difference of cold-producing medium and air greatly.
The heat exchanger of the present invention of technical scheme 2 is in technical scheme 1 described heat exchanger, makes the outlet of the wind upside row in the path of the 2nd heat-transfer pipe be positioned at these wind upside row bottom.
Adopt this structure, in the occasion that heat exchanger is used as condenser, because the export department of the 2nd heat transmitter that can the liquid refrigerant temperature is minimum is configured in the lower end of heat exchanger, so can with on the wind and wind under the 2nd heat-transfer pipe make counter current flow completely, the condensation performance is further improved, and can prevent the fluid-tight in the aircondition of converter type.
Adopt this structure, with heat exchanger as the occasion of evaporimeter, for each row of the 1st heat-transfer pipe assignment system cryogen equably, can improve performance of evaporator, the Y branching type current divider of versatility is arranged by use simultaneously, can reduce cost significantly.
Technical scheme 4 described heat exchangers are in technical scheme 1-3 in arbitrary described heat exchanger, make the part of the 1st heat-transfer pipe be positioned at the below of the 2nd heat-transfer pipe.
Technical scheme 5 described heat exchangers are in technical scheme 4 described heat exchangers, and the inlet of 1 path of the 1st heat-transfer pipe is positioned near the lower end of wind downside row.
Structure according to this technical scheme 4 and technical scheme 5 described heat exchangers, in the occasion that heat exchanger is used as the heat source side heat exchanger of heat-pump type air-conditioner, because 1st heat-transfer pipe higher than the 2nd heat-transfer pipe temperature is positioned at the bottom of heat exchanger, if this heat exchanger is positioned near the orientation substrate of off-premises station, can improves the defrost performance when heating the defrosting running and prevent that the off-premises station substrate from freezing (freezing).
Adopt this structure, compare with the HCFC-22 of general employed a kind of freon, because a kind of HFC-32 in replacement fluorine Lyons of the low approximately 20-30% of using system internal pressure loss or contain mix refrigerant or the hydrocarbon cold-producing medium of HFC-32 is so can improve condenser performance and the loss of the device performance that avoids evaporating.
The simple declaration of accompanying drawing:
Fig. 1 is the stereogram of the heat exchanger major part of the present invention the 1st embodiment.
Fig. 2 is the side view of this embodiment heat exchanger.
Fig. 3 be expression with the heat exchanger of this embodiment the refrigerant temperature during as condenser change, the ideograph of the state of the air themperature of heat exchange and the cold-producing medium in the heat exchanger.
Fig. 4 is the side view of the heat exchanger of the present invention the 2nd embodiment.
Fig. 5 is the side view of the heat exchanger of the present invention the 3rd embodiment.
Fig. 6 is the side view of the heat exchanger of the present invention the 4th embodiment.
Fig. 7 is the refrigeration cyclic graph in the aircondition of the summary heat exchanger of representing to have the foregoing description.
Fig. 8 is the side view of the heat exchanger of expression the present invention the 5th embodiment.
Fig. 9 is the side view of heat exchanger in the past.
Figure 10 is that heat exchanger that expression will be the in the past refrigerant temperature during as condenser changes, the ideograph of the state of the cold-producing medium of the air themperature of heat exchange and heat exchanger.
The explanation of embodiment:
Below, with reference to the accompanying drawings example of the present invention is described.In addition, put on identical label and omit its explanation with the member that in the past heat exchanger has a said function.
Fig. 1 is a major part stereogram of representing heat exchanger of the present invention is applicable to the 1st embodiment of condenser, and Fig. 2 is the side view (when the arrow of expression flow of refrigerant direction is represented condenser working) of this heat exchanger.
As shown in Figure 1 and Figure 2, in this heat exchanger, also be laminated with many flat fin 1a, and this fins set 1 is quadrature shape ground roughly, promptly the heat-transfer pipe 2 of cold-producing medium is arranged along the stacked direction break-through of fin relatively, and air is passed through between each fins set 1 with predetermined distance.And, heat-transfer pipe 2 is divided into the many part parts many of gas phase of the gas and the gas-liquid two-phase flow of the cold-producing medium that in pipe, flows with the liquid phase of liquid and gas-liquid two-phase flow, and partly set the 1st heat-transfer pipe 2a, the 2b of 2 access structures at the former, partly set the 2nd of 1 access structure this 2c that conducts heat the latter, the 1st heat- transfer pipe 2a, 2b are communicated with the 2nd heat-transfer pipe 2c by joint member 3.
Yet, in this heat exchanger, each path of the 1st heat- transfer pipe 2a, 2b and the 2nd heat-transfer pipe 2c is under situation about working as condenser, and wind downside row are inlets, wind upside row become outlet, make the part of this path make subtend flow pattern overlapping between multiple row at air by direction at least.
Then, the action to this heat exchanger describes.Fig. 3 is the ideograph of the state of expression air themperature during as condenser, the variations in temperature from the inlet of cold-producing medium to outlet, heat exchange and the cold-producing medium in the heat exchanger with this heat exchanger.
In the occasion that this heat exchanger is used as condenser, the overheated gas cold-producing medium is listed as at the wind downside that entrance side flows through in the 1st heat- transfer pipe 2a, 2b, and refrigerant temperature is because of dropping to T2 with air heat exchange from T1.Cold-producing medium is that the row of the wind upside in the 1st heat- transfer pipe 2a, 2b flow and carry out heat exchange with air under the state of T2 in temperature, and gas refrigerant graduates into liquid.Then, the cold-producing medium that this liquid phase ingredient is many cuts up with a hay cutter row down by the wind of joint member 3 in the 2nd heat-transfer pipe 2c of 1 access structure and flows, and carries out heat exchange and makes temperature drop to T3 from T2 with air.Also having, is under the state of T3 in temperature, and then the row of the wind upside in the 2nd heat-transfer pipe 2c flow, and carry out heat exchange and make temperature drop to T4 from T3 with air.
Like this, owing to be configured to make cold-producing medium at first to flow to wind downside row, flow to wind upside row then, so as shown in Figure 3, heat-transfer pipe 2a, the 2b of wind downside row, the refrigerant temperature in the 2c are compared with the refrigerant temperature of wind upside row, almost the temperature on whole zone uprises, and it is big that the temperature difference of cold-producing medium and air becomes.Therefore, it is big that the average air temperature difference Δ Tm before and after the heat exchange becomes, and can increase substantially the efficient of heat exchange, and according to experiment, its heat exchange amount Q has improved 5% than access structure in the past.
Though the foregoing description is with the situation of heat exchanger as condenser, is being used as under the situation of evaporimeter, although direction of refrigerant flow is opposite, its effect can be suitable fully equally.Promptly, under the situation of evaporimeter, because of the liquid and the many cold-producing medium elder generations of liquid phase of throttling arrangement adiabatic expansion flow to the 2nd heat-transfer pipe 2c of 1 access structure, because by joint member 3, with heat exchange in the many cold-producing medium of gas and gas phase composition flow into the 1st heat-transfer pipe 2a, the 2b of 2 access structures, so on the wind with wind under temperature difference (about 5～50K) situation is compared, and evaporimeter is lower by (about 1～2K) with condenser.But, each path of the 1st heat- transfer pipe 2a, 2b and the 2nd heat-transfer pipe 2c is being done the time spent as evaporimeter, wind upside row are inlets, wind downside row become outlet, because the part of this path makes subtend flow pattern overlapping between multiple row at air by direction at least, so it is big that the temperature difference of cold-producing medium and air becomes, and can improve effectiveness of heat exchanger.
Then, in conjunction with Fig. 4 the 2nd embodiment of the present invention is described.Fig. 4 is the side view (situation the when arrow of expression flow of refrigerant direction is represented condenser working) that expression is applicable to heat exchanger of the present invention the 2nd embodiment of condenser.Be that with the difference of the 1st embodiment the export mixes that the wind upside in the path of the 2nd heat-transfer pipe 2c is listed as is positioned at these wind upside row bottom.
The effect of the heat exchanger of the 2nd embodiment now is described.In general, the wind speed bottom of heat exchanger part is lower.The 2f of export department as the wind upside heat-transfer pipe among the 2nd heat-transfer pipe 2c of the heat exchanger characteristics of the 2nd embodiment, doing the time spent as condenser, because temperature becomes minimum, so the heat exchanger ability that makes the 2nd heat-transfer pipe 2c of counter current flow structure with 1 path is compared with the heat exchanger ability of the 1st embodiment become big, as seen can improve heat exchanger performance by the described 2f of export department is placed.Also have, if adopt the heat exchanger of the 2nd embodiment, the 2f of export department does not take the such matrix access structure of the heat exchanger of the 1st embodiment, near the 2f of export department path is not to rise from bottom to top, so especially the low speed in the frequency conversion type air conditioning device, be the slow occasion of cold-producing medium flow velocity, also can prevent the fluid-tight that is produced.
Then, in conjunction with Fig. 5 the heat exchanger of the 3rd embodiment is described.Fig. 5 is the side view (when the arrow of expression flow of refrigerant direction is represented evaporator operation) that expression is applicable to heat exchanger of the present invention the 3rd embodiment of evaporimeter.Be with the difference of the heat exchanger of above-mentioned the 2nd embodiment, the joint member 3 that connects the 1st and the 2nd heat- transfer pipe 2a, 2b, 2c is made Y branching type current divider 3a.
With the occasion of this heat exchanger as evaporator operation, when making from the cold-producing medium 5c of the air-flow two-phase flow of the 2nd heat-transfer pipe 2c and the 1st heat- transfer pipe 2a, 2b shunting, by adopting Y branching type current divider 3a to be arranged to level or vertical as joint member 3, cold-producing medium 5a, the 5b that flows into the 1st heat- transfer pipe 2a, 2b roughly can be distributed equably, can increase substantially performance of evaporator.Also have, owing to use the Y branching type current divider 3a that versatility is arranged, not having the situation of versatility part to compare with use can reduce cost.
Then, in conjunction with Fig. 6 the 4th embodiment is described.Fig. 6 is the side view (when the arrow of expression flow of refrigerant direction is represented condenser working) that expression is applicable to heat exchanger of the present invention the 4th embodiment of condenser.Be with the difference of above-mentioned the 3rd embodiment, the heat-transfer pipe 2b of a side among the 1st heat-transfer pipe 2a, the 2b of 2 access structures is configured in the opposing party's the 1st heat-transfer pipe 2a and the below of the 2nd heat-transfer pipe 2c.
Come the effect of the heat exchanger of the 4th embodiment is described with Fig. 6 and Fig. 7.Fig. 7 is the figure of general kind of refrigeration cycle of expression heat-pump type air-conditioner, this kind of refrigeration cycle be with compressor 11, cross valve 12, utilize side heat exchanger 13, heat source side heat exchanger (off-premises station) 14, throttling arrangement 15 respectively annularly pipe arrangement connect and constitute.Heat exchanger 14 in the occasion of the heat exchanger that uses the 4th embodiment, when cooling operation as condenser working, when warming operation as evaporator operation.Here, when under the state of low temperature (for example 2 ℃/wet-bulb temperature of outside air temperature is 1 ℃), heating, because heat source side heat exchanger 14 works as evaporimeter, so the fin frosting when continuing running continuously, just needs to defrost in order to recover heating capacity.In defrosting, turn round with kind of refrigeration cycle, heat source side heat exchanger 14 carries out work as condenser, and frost dissolves and wanders to the bottom from the top of heat exchanger.
Therefore, occasion at the heat exchanger of the 3rd embodiment shown in Figure 5, because the bottom of heat exchanger has the suitable heat-transfer pipe of exit portion with the minimum condenser of temperature, so the water that accumulates on the substrate that is located on the off-premises station build-ups ice, tend to reduce heating capacity and have on substrate, produce the big situation of change of freezing along with continuous running.
In contrast, occasion at the heat exchanger of the 4th embodiment, as shown in Figure 6, be configured in the opposing party's the 1st heat-transfer pipe 2a and the below of the 2nd heat-transfer pipe 2c by the 1st heat-transfer pipe 2b with the side in 2 access structures, when the defrosting running, the cold-producing medium that flows to the higher temperatures of the 1st heat-transfer pipe 2b can be configured in the position of the substrate 6 of the most close heat source side heat exchanger (off-premises station) 14.Therefore, the temperature that can make substrate 6 rises highly than the heat exchanger of the 3rd embodiment, and can prevent freezes on substrate 5 and this is frozen in defrosting running back becomes big situation.Also have, because the 1st heat- transfer pipe 2a, 2b and the 2nd heat-transfer pipe 2c keep the form of 2 path counter current flow～1 path counter current flow respectively, so can obtain the performance that is equal to mutually up to effectiveness of heat exchanger with the 3rd embodiment.
Then, in conjunction with Fig. 8 the heat exchanger of the 5th embodiment is described.Fig. 8 is that expression is with the side view (situation when the arrow of expression flow of refrigerant direction represent condenser working) of heat exchanger application of the present invention in the 5th embodiment of condenser.Be with the difference of above-mentioned the 4th embodiment, will place at the inlet heat-transfer pipe 2h of portion of described the 1st heat-transfer pipe 2b of the 2nd heat-transfer pipe 2c bottom between heat exchanger lower floor to 2 heat-transfer pipe and be placed on the off-premises station that is setting heat source side heat exchanger 14 substrate 6 near.
In the occasion that this heat exchanger is used for the same kind of refrigeration cycle of the 4th embodiment, owing to the inlet heat-transfer pipe 2h of portion that leads to the highest condenser of temperature can be configured in the position of the substrate 6 of close off-premises station in when running defrosting, so can make the heat exchanger rising De Genggao of the temperature of substrate 6 than the 4th example, the turn round icing change of metacoxal plate 6 of just can preventing to defrost is big.This structure is especially effective to the heat-pump type air-conditioner of the compressor that uses the constant speed a little less than the defrost performance.Also have, because the 1st heat- transfer pipe 2a, 2b and the 2nd heat-transfer pipe 2c keep the form of 2 path counter current flow～1 path counter current flow respectively, so can obtain to reach and the equal performance of the effectiveness of heat exchanger of the 4th embodiment.
As the cold-producing medium of the heat exchanger that is used in above each embodiment, can use a kind of HCFC-22 in fluorine Lyons, as replacing mix up cold-producing medium or the hydrocarbon cold-producing medium that product also can use a kind of HFC-32 in replacement fluorine Lyons or contain HFC-32.
Occasion at the heat-pump-type room conditioning of the HCFC-22 that uses a kind of fluorine Lyons, as previously mentioned, appending of the minimizing of number of vias and valve class, to increase the generally influence for the performance reduction bigger because of the pressure loss that increases along with flow velocity and the valve class is appended in practicality, here, the ratio that the pressure loss of each cold-producing medium of the cooling cycle system of HCFC-22 alleviates is used in following " table 1 " expression relatively.
[table 1]
| The kind of cold-producing medium | System's internal pressure loss ratio (relatively with HCFC-22 as 100% situation) |
| ????HCFC-22 | ????100％ |
| ????HFC-407C | ????100～103％ |
| ????HFC-407A | ????70～80％ |
| ????HC-290 | ????70～80％ |
HFC-407C in [table 1], HFC-410A are the mix refrigerants that contains a kind of HFC-32 in replacement fluorine Lyons respectively, and HC-290 is the hydrocarbon cold-producing medium.We know HFC-32 or contain the part of the mix refrigerant of HFC-32 (HFC-410A) or a kind of relatively chlorofluoromethane refrigerant HCFC-22 of hydrocarbon cold-producing medium (HC-290) that the pressure loss alleviates about 20-30%.Therefore, in the heat exchanger of the various embodiments described above, by using described HFC-32 or containing mix refrigerant or the hydrocarbon cold-producing medium of HFC-32, can alleviate the pressure loss of evaporimeter significantly, compare during with the HCFC-22 that uses in the past, also can improve effectiveness of heat exchanger the evaporator-condenser both sides.
In addition, though in above-mentioned example, described the situation that by direction heat- transfer pipe 2a, 2b, 2c is adapted to the heat exchangers of 2 row with respect to air arbitrarily, but be not limited thereto, certainly, even also can be suitable for for by direction heat-transfer pipe 2 being adapted to the above heat exchanger of 3 row with respect to air.
Claims (6)
1. heat exchanger, a plurality of tabular fins are stacked with the interval of regulation, along the stacked direction break-through heat-transfer pipe by cold-producing medium is arranged, air is passed through between each fins set, set the described heat-transfer pipe of multiple row at relative air by direction, it is characterized in that, be distinguished into the many part parts many of gas phase of gas and air-flow two-phase flow with the liquid phase of liquid and gas-liquid two-phase flow by the refrigerant condition that in the pipe of described heat-transfer pipe, flows, on the former part, set the 1st heat-transfer pipe of 2 access structures, on latter's part, set the 2nd heat-transfer pipe of 1 access structure, by joint member the described the 1st and the 2nd heat-transfer pipe is interconnected, and the occasion that each path of the described the 1st and the 2nd heat-transfer pipe is working as condenser, wind downside row are inlets, wind upside row become outlet, and make subtend flow pattern overlapping between multiple row at air by direction to the part of the described path of major general.
2. heat exchanger as claimed in claim 1 is characterized in that, makes the outlet of the wind upside row on the path of described 2 heat-transfer pipes be positioned at described wind upside row bottom.
3. heat exchanger as claimed in claim 1 or 2 is characterized in that, described joint member is made Y branching type current divider.
4. as each described heat exchanger in the claim 1～3, it is characterized in that, make the part of described the 1st heat-transfer pipe be positioned at the below of described 2 heat-transfer pipes.
5. heat exchanger as claimed in claim 4 is characterized in that, the inlet of 1 path of described the 1st heat-transfer pipe is positioned near the lower end of described wind downside row.
6. as each described heat exchanger in the claim 1～5, it is characterized in that,, use HFC-32 or contain mix refrigerant or the hydrocarbon cold-producing medium of HFC-32 as cold-producing medium.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP49233/99 | 1999-02-26 | ||
| JP4923399A JP2000249479A (en) | 1999-02-26 | 1999-02-26 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1265463A true CN1265463A (en) | 2000-09-06 |
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ID=12825194
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 00103626 Pending CN1265463A (en) | 1999-02-26 | 2000-02-25 | Heat-exchanger |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP1031801A3 (en) |
| JP (1) | JP2000249479A (en) |
| CN (1) | CN1265463A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2952736A1 (en) * | 1979-12-29 | 1981-07-02 | Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart | HEAT EXCHANGER, ESPECIALLY TWO OR MULTIPLE FLOW CAPACITOR FOR AIR CONDITIONING IN MOTOR VEHICLES |
| US4831844A (en) * | 1988-05-26 | 1989-05-23 | General Motors Corporation | Condenser with improved flow path |
| JP2907864B2 (en) * | 1989-04-28 | 1999-06-21 | 株式会社東芝 | Heat pump type air conditioner indoor unit heat exchanger |
| US5219023A (en) * | 1992-03-09 | 1993-06-15 | General Motors Corporation | Three row condenser with high efficiency flow path |
| JP2979926B2 (en) * | 1993-10-18 | 1999-11-22 | 株式会社日立製作所 | Air conditioner |
| JPH07208821A (en) * | 1994-01-17 | 1995-08-11 | Toshiba Corp | Air conditioner |
| JP3275559B2 (en) * | 1994-09-20 | 2002-04-15 | 株式会社日立製作所 | Refrigeration equipment |
| US5810074A (en) * | 1996-09-13 | 1998-09-22 | American Standard Inc. | Serial heat exchanger and cascade circuitry |
-
1999
- 1999-02-26 JP JP4923399A patent/JP2000249479A/en active Pending
-
2000
- 2000-02-25 CN CN 00103626 patent/CN1265463A/en active Pending
- 2000-02-25 EP EP00103971A patent/EP1031801A3/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101592411B (en) * | 2008-05-29 | 2012-07-11 | 日立空调·家用电器株式会社 | Refrigeration cycle device |
| CN103069245A (en) * | 2010-08-05 | 2013-04-24 | 三菱电机株式会社 | Heat exchanger and refrigeration and air conditioning device |
| CN102635931A (en) * | 2012-02-17 | 2012-08-15 | 海尔集团公司 | Air-conditioner heat exchanger and air-conditioner by using mixing refrigerant |
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| CN105283718B (en) * | 2013-06-13 | 2017-10-24 | 三菱电机株式会社 | Air-conditioning device |
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| US10605502B2 (en) | 2014-10-07 | 2020-03-31 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
| CN106440863A (en) * | 2016-05-11 | 2017-02-22 | 南京工业大学 | Stacked type finned tube heat exchanger |
| CN111928685A (en) * | 2020-08-19 | 2020-11-13 | 三一重机有限公司 | Radiator heat dissipation performance optimization method, radiator and engineering machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1031801A3 (en) | 2001-12-05 |
| EP1031801A2 (en) | 2000-08-30 |
| JP2000249479A (en) | 2000-09-14 |
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