CN104620069B - Parallel flow heat exchanger and the air conditioner being provided with this parallel flow heat exchanger - Google Patents

Parallel flow heat exchanger and the air conditioner being provided with this parallel flow heat exchanger Download PDF

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Publication number
CN104620069B
CN104620069B CN201380044123.9A CN201380044123A CN104620069B CN 104620069 B CN104620069 B CN 104620069B CN 201380044123 A CN201380044123 A CN 201380044123A CN 104620069 B CN104620069 B CN 104620069B
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China
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heat exchanger
flat tube
parallel flow
flow heat
refrigerant path
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CN201380044123.9A
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CN104620069A (en
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上野円
三代寿
三代一寿
吉田健司
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Sharp Corp
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Sharp Corp
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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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Abstract

The present invention provides parallel flow heat exchanger and is provided with the air conditioner of this parallel flow heat exchanger.Parallel flow heat exchanger (1) includes the flat tube (4) of many horizontal directions between the house steward (2,3) of two vertical direction and connection house steward.The flat tube of many horizontal directions is grouped further and is one group with many, and each group is constituted makes a cold-producing medium refrigerant path flowed to another root from the house steward of vertical direction.Constitute the upper limit of the radical of the flat tube of unidirectional refrigerant path, determined by the formula of regulation.

Description

Parallel flow heat exchanger and the air conditioner being provided with this parallel flow heat exchanger
Technical field
The present invention relates to the parallel flow heat exchanger of cross-flow type and this parallel flow heat exchanger is installed Air conditioner.
Background technology
Parallel flow heat exchanger is configured with multiple flat tube between multiple house stewards, makes inside flat tube Multiple coolant channels connect with the inside of house steward, and between flat tube, be configured with corrugated The fin such as fin, above-mentioned parallel flow heat exchanger is widely used in motorcar air conditioner and building The outside unit etc. of thing air conditioner.
Fig. 1 represents the structure example of parallel flow heat exchanger.It Fig. 1 is heat exchanger on the upside of paper It it is the downside of heat exchanger on the downside of upside, paper.Parallel flow heat exchanger 1 is cross-flow type, has The house steward 2,3 of two vertical direction and the flat tube 4 of configuration many horizontal directions between which. The horizontally spaced spaced and parallel configuration of house steward 2,3, flat tube 4 is between vertical direction is with regulation Away from configuration.In the actual installation stage on equipment, due to heat exchanger 1 wanting according to design Ask and place with various angles, thus " vertical direction ", " horizontal direction " in this specification and The most strictly represent above-mentioned direction.Should be understood to it is only direction substantially.
Flat tube 4 is the elongated products formed after metal carries out extrusion molding, as in figure 2 it is shown, It is being internally formed the coolant channel 5 making cold-producing medium circulate.Due to flat tube 4 so that as long limit The mode that extrusion molding direction is horizontal direction in direction configures, so the refrigeration of coolant channel 5 Agent circulating direction is also horizontal direction.Left and right directions along Fig. 2 is arranged with multiple section configuration and breaks The coolant channel 5 of face area equation.Therefore, the vertical cross section of flat tube 4 is harmonica.Each system Coolant channel 5 connects with the inside of house steward 2,3.
The flat horizontal surface of flat tube 4 is provided with fin 6.Here, use as fin 6 Corrugated fin, but can also be plate-shaped fin.In the fin 6 being arranged above and below, The fin of the superiors and the outside of undermost fin are configured with side plate 7.
House steward 2,3, flat tube 4, fin 6 and side plate 7 are by the metal of the high-termal conductivity such as aluminum Constitute, flat tube 4 relative to house steward 2,3, fin 6 is relative to flat tube 4, side plate 7 phase Fin 6 is fixed by soldering or melting welding respectively.
The inside of house steward 2 is divided into three regions S1, S2, S3 by two dividing plates P1, P2.Every Many flat tubes 4 are divided into three flat tube groups by plate P1, P2.Region S1, S2, S3 are respectively It is connected with many flat tubes 4.
The inside of house steward 3 is divided into two regions S4, S5 by a dividing plate P3.Dividing plate P3 will be many Two flat tube groups divided into by root flat tube 4.Region S4, S5 are connected with many flat tubes 4 respectively.
Region S1 is connected with cold-producing medium discrepancy pipe 8.Region S3 is connected with cold-producing medium discrepancy pipe 9.
The function of heat exchanger 1 is as described below.When heat exchanger 1 is used as coagulator, cold-producing medium leads to Cross cold-producing medium and come in and go out pipe 8 to region S1 supply.The cold-producing medium entering region S1 passes through join domain The many flat tubes 4 of S1 and region S4 flow to region S4.Above-mentioned many flat tubes 4 are constituted Flat tube group constitutes refrigerant path A.Refrigerant path A is represented by hollow arrow.In addition Refrigerant path also represented by hollow arrow.
The cold-producing medium entering region S4 is turned back at this, and by join domain S4 and region S2 Many flat tubes 4 to region S2 flow.The flat tube group that above-mentioned many flat tubes 4 are constituted is constituted Refrigerant path B.
The cold-producing medium entering region S2 is turned back at this, and by join domain S2 and region S5 Many flat tubes 4 to region S5 flow.The flat tube group that above-mentioned many flat tubes 4 are constituted is constituted Refrigerant path C.
The cold-producing medium entering region S5 is turned back at this, and by join domain S5 and region S3 Many flat tubes 4 to region S3 flow.The flat tube group that above-mentioned many flat tubes 4 are constituted is constituted Refrigerant path D.The cold-producing medium entering region S3 flows out from cold-producing medium discrepancy pipe 9.
In this manual, pipe 9 will be come in and gone out to initial folding from come in and go out pipe 8 or cold-producing medium of cold-producing medium Return or turn back and next turn back between interval be referred to as " unidirectional ".Refrigerant path A, B, C, D is referred to as unidirectional refrigerant path.
When heat exchanger 1 is used as vaporizer, cold-producing medium comes in and goes out pipe 9 to region S3 confession by cold-producing medium Give.The flowing of cold-producing medium hereafter is contrary as refrigerant path during coagulator with heat exchanger 1. That is, cold-producing medium is with refrigerant path D → refrigerant path C → refrigerant path B → cold-producing medium road Entrance region, the path S1 of footpath A, and flow out from cold-producing medium discrepancy pipe 8.
In parallel flow heat exchanger, in order to improve performance, carry out various improvement in design. Above-mentioned example can be inquired in patent documentation 1～3.
In the parallel flow heat exchanger that patent documentation 1 is recorded, flat connect two house stewards many Multiple parallel fluid diameter that is internally formed of flat pipe is that 0.015 inch (about 0.38 millimeter) arrives The coolant channel of 0.07 inch of (about 1.78 millimeters) scope.The section of above-mentioned coolant channel Profile has the part of the plural relatively straight wire converged and is formed at the position that they converge At least one depressed part.Further, according to said structure, flat tube before the air side closed Face area is little, so the decline of air side pressure will not be made to increase such that it is able to make air side heat pass Pass surface to increase.
In the parallel flow heat exchanger described in patent documentation 2, by flat tube inner refrigerant passage Height be set as 0.35 millimeter to 0.8 millimeter.Thus, the thermal diffusivity produced by flowing resistance is made Can sloping portion and by the raw heat dispersion sloping portion of pipe crushing loss of production and diminish, thus improve Heat dispersion.
In the parallel flow heat exchanger described in patent documentation 3, make shunting parameter γ 0.5 with On, described shunting parameter γ is the drag parameter β entrance side house steward relative to cold-producing medium of flat tube The ratio of drag parameter α.Thus, prevent cold-producing medium with the pressure of the refrigerant inlet of house steward Flowing concentrated by the flat tube that high part connects, it is possible to make the pressure applied to each flat tube uniform, Thus obtain good SHUNT state, therefore, it is possible to play good heat exchange performance.
Patent documentation 1: flat No. 5-87752 of Japanese Laid-Open Patent Publication
Patent documentation 2: Japanese Laid-Open Patent Publication 2001-165532
Patent documentation 3: Japanese Laid-Open Patent Publication 2000-111274
Summary of the invention
When parallel flow heat exchanger is used as vaporizer, when considering the system of flowing in refrigerant path During cryogen, it is desirable to do not produce " bias current " state, " bias current " state should refer to substantial amounts of liquid system Cryogen is at a certain flat Bottomhole pressure, and substantial amounts of gas refrigerant is at other flat Bottomhole pressure. It is an object of the invention to provide the parallel flow heat exchanger of a kind of cross-flow type, never produce bias current Viewpoint is set out, and the radical of the flat tube constituting refrigerant path is carried out optimal design.Particularly originally The purpose of invention is to make the flat tube radical of the refrigerant path that the ratio of gas refrigerant is big optimal Change.
The present invention provides a kind of parallel flow heat exchanger, and it is cross-flow type, described parallel type heat exchange Device includes: the house steward of two vertical direction；And connect many horizontal directions between described house steward Flat tube, the flat tube of described many horizontal directions is by further packet and be one group with many, Each group is constituted makes from the house steward of described two vertical direction of cold-producing medium flow to another root Unidirectional refrigerant path, described parallel flow heat exchanger, for the off-premises station of air conditioner, is constituted The upper limit of the radical of the described flat tube of described unidirectional refrigerant path, by being obtained by following formula A To numerical value ± 2 determine, under the radical of the described flat tube constituting described unidirectional refrigerant path Limit is determined by following formula B, n ＜ 3.0 × 10-4× Q+8.0 (A), n ＞ (α Q+ β) × {(1.4×10-16)×L/(d×A’2)}0.5(B), wherein, n is to constitute unilateral system cryogen The radical of the flat tube in path, Q be rated capacity and using W as unit, α=0.0161, β=8.86, L be length of pipe and using m as unit, d be hydraulic diameter and using m as unit, A ' is one The cross-sectional area of the coolant channel of root flat tube by m2As unit.
Additionally, the present invention also provides for a kind of parallel flow heat exchanger, it is cross-flow type, described and flow Formula heat exchanger includes: the house steward of two vertical direction；And connect many between described house steward The flat tube of horizontal direction, the flat tube of described many horizontal directions is by packet further and with many Root is one group, and each group is constituted makes from the house steward of described two vertical direction of cold-producing medium to separately The unidirectional refrigerant path of a piece flowing, described parallel flow heat exchanger is for the room of air conditioner Interior machine, constitutes the upper limit of the radical of the described flat tube of described unidirectional refrigerant path, by by with Numerical value ± 2 that lower formula A obtains determine, constitute the described flat of described unidirectional refrigerant path The lower limit of the radical of pipe is determined by following formula B, n ＜ 4.2 × 10-4× Q+7.9 (A), n ＞ (α Q+ β) × { (1.4 × 10-16)×L/(d×A’2)}0.5(B), wherein, n is structure Become the radical of the flat tube of unidirectional refrigerant path, Q be rated capacity and using W as unit, α=0.0228, β=6.62, L be length of pipe and using m as unit, d is hydraulic diameter by m As unit, A ' is the cross-sectional area of the coolant channel of a flat tube by m2As unit.
Additionally, the present invention also provides for a kind of air conditioner, this air conditioner is by said structure Parallel flow heat exchanger is arranged in off-premises station or indoor set.
According to the present invention, the parallel flow heat exchanger of a kind of cross-flow type can be obtained, will not be because of refrigeration The circulating load of agent and produce bias current.
Accompanying drawing explanation
Fig. 1 is the brief configuration figure of the parallel flow heat exchanger of cross-flow type.
Fig. 2 is the sectional drawing of the II-II line along Fig. 1.
Fig. 3 is the table of the specification of the experiment product of flat tube.
Fig. 4 is to represent circulating mass of refrigerant and do not produce the table of relation of flat tube radical of bias current.
Fig. 5 is the curve chart of the relation representing circulating mass of refrigerant and flat tube radical.
Fig. 6 is the curve chart of the relation representing heating capacity and circulating mass of refrigerant.
Fig. 7 is the curve chart of the relation representing refrigerating capacity and circulating mass of refrigerant.
Fig. 8 is the curve chart of the flat tube radical optimum range of air conditioner off-premises station.
Fig. 9 is the curve chart of the flat tube radical optimum range of air conditioner indoor unit.
Figure 10 is the curve chart of the relation representing circulating mass of refrigerant and suction pressure.
Figure 11 is the curve chart of the relation representing circulating mass of refrigerant and flat tube radical.
Figure 12 is the radical of the flat tube representing off-premises station heat exchanger and heats rated capacity The curve chart of relation.
Figure 13 is radical and the refrigeration rated capacity of the flat tube representing heat exchanger used for indoor machine The curve chart of relation.
Figure 14 is the air conditioner being provided with parallel flow heat exchanger brief representing the present invention Structure chart, is the figure representing state when heating operating.
Figure 15 is the air conditioner being provided with parallel flow heat exchanger brief representing the present invention Structure chart, the figure of state when being to represent cooling operation.
Description of reference numerals
1 heat exchanger
2,3 house steward
4 flat tubes
5 coolant channels
6 fin
7 side plates
A, B, C, D refrigerant path
Detailed description of the invention
The parallel flow heat exchanger of the present invention is the parallel flow heat exchanger 1 of the cross-flow type shown in Fig. 1, And the radical of the flat tube 4 constituting refrigerant path is set by the method for following description.But, The quantity of refrigerant path is not limited to four.Can ratio more than four, it is also possible to fewer than four.
First, the upper limit of the radical of the flat tube 4 constituting unidirectional refrigerant path is drawn.According to Lower formula A obtains higher limit.
When this parallel flow heat exchanger being used for the off-premises station of air conditioner,
N ＜ 3.0 × 10-4×Q+8.0…(A)
When this parallel flow heat exchanger being used for the indoor set of air conditioner,
N ＜ 4.2 × 10-4×Q+7.9…(A)
Wherein, n is the radical of the flat tube constituting unidirectional refrigerant path, Q be rated capacity also Using W as unit.
Formula A is derived by experiment.The table of Fig. 3 represents the specification of the flat tube used in an experiment. Experiment product a is width 16.2mm, thickness 1.9mm, coolant channel cross-sectional area 13mm2.Real The product b of testing is width 13.9mm, thickness 1.9mm, coolant channel cross-sectional area 11mm2.Experiment Product c is width 16.2mm, thickness 1.6mm, coolant channel cross-sectional area 11mm2.Experiment product D is width 19.2mm, thickness 1.9mm, coolant channel cross-sectional area 14mm2。
Experiment is carried out as follows.Cold-producing medium is made to circulate in the flat tube of various radicals, and By being confirmed whether to create bias current with perusal thermography.Use four shown in Fig. 3 kind experiment Product, for each experiment product, change circulating load and make refrigerant cycle.The table of Fig. 4 summarizes upper State in circulating mass of refrigerant unconfirmed to bias current (the most sometimes by this state be referred to as " nothing Bias current ") the maximum radical of flat tube.
In the table of Fig. 4, experiment 1 uses experiment product a.Circulating mass of refrigerant is 27.3kg/h Time be 8 without bias current maximum root number.Without bias current maximum root number when circulating mass of refrigerant is 42.5kg/h It it is 9.It it is 10 without bias current maximum root number when circulating mass of refrigerant is 64.3kg/h.Cold-producing medium follows It it is 10 without bias current maximum root number when circular rector is 63.2kg/h.
Experiment 2 uses experiment product b.Without bias current maximum root when circulating mass of refrigerant is 20.9kg/h Number is 9.It it is 8 without bias current maximum root number when circulating mass of refrigerant is 22.1kg/h.
Experiment 3 uses experiment product c.Without bias current maximum root when circulating mass of refrigerant is 59.2kg/h Number is 10.It it is 9 without bias current maximum root number when circulating mass of refrigerant is 48.8kg/h.Cold-producing medium It it is 8 without bias current maximum root number when circulating load is 26.4kg/h.
Experiment 4 uses experiment product b.Without bias current maximum root when circulating mass of refrigerant is 54.8kg/h Number is 8.It it is 8 without bias current maximum root number when circulating mass of refrigerant is 89.2kg/h.
Experiment 5 uses experiment product d.Without bias current maximum root when circulating mass of refrigerant is 26.6kg/h Number is 6.It it is 9 without bias current maximum root number when circulating mass of refrigerant is 44.3kg/h.Cold-producing medium It it is 9 without bias current maximum root number when circulating load is 67.3kg/h.
If the experimental result of Fig. 4 is mapped, then become the curve chart of Fig. 5.Describe approximation Straight line, according to the approximate expression of straight line approximation,
N=1.9 × 10-2m+7.8…(a)
Draw ± 2.
Circulating mass of refrigerant m (kg/h) is set as the value that the rated capacity to mill run is directly proportional. Fig. 6 and Fig. 7 represents the relation of circulating mass of refrigerant and ability.
Heat rated capacity Q (unit is W) if used and represented by formula, then it represents that for:
M=0.0161Q+8.86 ... (b)
If using refrigeration rated capacity Q (unit is W) and being represented by formula, then it represents that for:
M=0.0228Q+6.621 ... (c)
How much deviation is there is because product is different in rated capacity with the relation of circulating mass of refrigerant.It addition, Circulating mass of refrigerant is calculated simply by following formula.
Circulating mass of refrigerant m=compressor rotary speed × suction pressure density × compressor volume
When parallel flow heat exchanger is used as the off-premises station heat exchanger of air conditioner, heating fortune Becoming vaporizer when turning, parallel flow heat exchanger is used as the heat exchanger used for indoor machine of air conditioner Time, become vaporizer when cooling operation.
Therefore, as shown in Figure 8, when parallel flow heat exchanger is used as off-premises station heat exchanger, According to above-mentioned formula (a), (b), constitute radical upper of the flat tube of unidirectional refrigerant path It is limited to:
N=3.0 × 10-4Q+8.0
± 2.
As it is shown in figure 9, when parallel flow heat exchanger is used as heat exchanger used for indoor machine, according to Above-mentioned formula (a), (c), the upper limit of the radical constituting the flat tube of unidirectional refrigerant path is:
N=4.2 × 10-4Q+7.9
± 2, it is possible to suppress bias current.
Then, the lower limit of the radical of the flat tube 4 constituting each refrigerant path is drawn.If heat is handed over The outlet temperature of parallel operation is:
Tout＜ 0 DEG C
The most as shown in Figure 10, suction pressure significantly declines.That is, relative to circulating mass of refrigerant, suck Pressure drastically reduces.This is to cause owing to outlet temperature reaches less than 0 DEG C frosting.
If the temperature caused by pressure loss Δ P is declined as TDp, then
TRin-TDp＜ 0 degree
TRinIt it is the entrance evaporating temperature of cold-producing medium.The unit of pressure loss Δ P is Pa.
That is,
PRin-Δ P ＞ Plim
PRinIt is entrance evaporating pressure, PlimThe saturation pressure of cold-producing medium when being 0 DEG C.
Here,
Δ P=λ × L/d × ρ × u2/2
λ is the coefficient of friction between inwall and the cold-producing medium of flat tube 4.L is length of pipe and is made by m For unit.D be hydraulic diameter and using m as unit.ρ is refrigerant density by kg/m3As Unit.U be the flow velocity of cold-producing medium and using m/s as unit.
Flow velocity u is drawn by following formula.
U=M/ ρ A
M be circulating mass of refrigerant and using kg/s as unit.A is to constitute unidirectional refrigerant path The summation of the coolant channel cross-sectional area of many flat tubes 4 by m2As unit.
Therefore,
Δ P=λ/2 ρ × L/dA2×M2
If here, using the coolant channel cross-sectional area of a flat tube 4 as A ', then
A=nA '
N is the radical of the flat tube 4 constituting unidirectional refrigerant path.
Here,
Δ P ＜ PRin-Plim
Therefore,
λ/2ρ×L/(dn2×A’2)×M2＜ PRin-Plim
Here,
n2＞ M2×λ/2ρ×L/dA’2×1/(PRin-Plim)
According to above formula,
N ＞ M{ λ/2 ρ × L/dA '2×1/(PRin-Plim)}0.5…(d)
As the circulating mass of refrigerant m (kg/h) that unit is different from M, it is set as and commonly produces The value that the rated capacity of product is directly proportional.Therefore, it is expressed as:
M=α Q+ β
Fig. 6 and Fig. 7 represents the relation of circulating mass of refrigerant and ability.If, with heating specified energy Power Q (unit is W) represents formula, then it represents that for:
M=0.0161Q+8.86
That is, α=0.0161, β=8.86.
Additionally, represent formula if, with refrigeration rated capacity Q (unit is W), then it represents that for:
M=0.0228Q+6.62
That is, α=0.0228, β=6.62.
As long as using when as off-premises station heat exchanger and heating rated capacity, when as indoor set With using refrigeration rated capacity during heat exchanger.
How much deviation is there is because product is different in rated capacity with the relation of circulating mass of refrigerant.It addition, Circulating mass of refrigerant utilizes following formula simply to calculate.
Circulating mass of refrigerant m=compressor rotary speed × suction pressure density × compressor volume
Additionally, generally the pressure loss is suppressed at below 200kPa.Therefore,
PRin-Plim＜ 200 × 103
Coefficient of friction λ changes according to circulating mass of refrigerant, refrigerant pressure, the shape etc. of flat tube. Normal domestic use air conditioner is 0.5～about 0.05.Although additionally, density p is according to refrigeration Pressure and the aridity of agent and change, but be generally 20～70kg/m when using gas refrigerant3。
If according to foregoing, being m by M identity transformation, then
N ＞ (α Q+ β) × Π × L/ (d × A '2)}0.5
Π is:
1.4×10-16＜ Π ＜ 4.8 × 10-15
When lower limit radical exceedes the result of calculation of the upper limit radical calculated by formula A, preferably exist The midway branch of entrance or heat exchanger.
Here, owing to preferably making the pressure loss low, thus Π be preferably used minimum, i.e. 1.4 × 10-16。
Therefore,
N ＞ (α Q+ β) × { (1.4 × 10-16)×L/(d×A’2)}0.5…(B)
As it has been described above, according to formula B, it can be deduced that constitute the flat tube 4 of unidirectional refrigerant path The lower limit of radical.
The example pictorialization of result of calculation that will be calculated by formula B in Figure 12, Figure 13.
Figure 12 represents the radical of the flat tube of off-premises station heat exchanger and heats the pass of rated capacity System.Figure 13 represents radical and the relation of refrigeration rated capacity of the flat tube of heat exchanger used for indoor machine. These curves represent according to rated capacity make the unidirectional refrigerant path of composition flat tube 4 radical Goodization, the value that wherein becomes lower limit.
Parallel flow heat exchanger 1 may be mounted in separate air regulation machine.Separate air is adjusted Joint machine is made up of off-premises station and indoor set.Off-premises station includes compressor, cross valve, expansion valve, room Outside heat exchangers and outside pressure fan etc..Indoor set includes indoor side heat exchanger and indoor Pressure fan etc..Outdoor heat exchanger becomes vaporizer when heating operating, becomes when cooling operation For coagulator.Indoor side heat exchanger becomes coagulator when heating operating, becomes when cooling operation For vaporizer.
Figure 14 is denoted as cooling cycle system and uses the separate air regulation of heat pump circulating system The basic structure of machine.Heat pump circulating system 101 is by compressor 102, cross valve 103, outside The heat exchanger 106 of heat exchanger 104, puffing device 105 and indoor connects into ring-type. Compressor 102, cross valve 103, heat exchanger 104 and puffing device 105 are housed in outdoor In the casing of machine.Heat exchanger 106 is housed in the casing of indoor set.Heat exchanger 104 and room The pressure fan 107 in outside combines.Heat exchanger 106 combines with the pressure fan 108 of indoor.Send Blower fan 107 includes propeller type fan.Pressure fan 108 includes cross flow fan.
The parallel flow heat exchanger 1 of the present invention can serve as the structure of the heat exchanger 106 of indoor set Key element.Three heat exchangers 106A, 106B, 106C are combined into covering and send by heat exchanger 106 The top of blower fan 108.Any one in heat exchanger 106A, 106B, 106C can be made For parallel flow heat exchanger 1.
The parallel flow heat exchanger 1 of the present invention is also used as the heat exchanger 104 of off-premises station.
Figure 14 represents state when heating operating.Now, from the High Temperature High Pressure of compressor 102 ejection Cold-producing medium enter indoor heat exchanger 106 and at this dispel the heat, condense.From heat exchanger 106 The cold-producing medium sent enters the heat exchanger 104 of outside swollen at this from puffing device 105 Swollen, and after outdoor air absorbs heat, return compressor 102.By the pressure fan of indoor 108 air-flows generated promote that heat exchanger 106 dispels the heat, the pressure fan 107 of outside the gas generated Stream promotes that heat exchanger 104 absorbs heat.
State when Figure 15 represents cooling operation or when defrosting operates.Now, switching cross valve 103 It is contrary with when heating operating to make the flow direction of cold-producing medium.That is, from the high temperature of compressor 102 ejection The cold-producing medium of high pressure enters the heat exchanger 104 of outside and dispels the heat at this, condenses.From heat exchange The cold-producing medium that device 104 is sent enters the heat exchanger 106 of indoor also from puffing device 105 Expand at this, and after room air absorbs heat, return compressor 102.By outside The air-flow that pressure fan 107 generates promotes that heat exchanger 104 dispels the heat, by the pressure fan 108 of indoor The air-flow generated promotes that heat exchanger 106 absorbs heat.
Above, embodiments of the present invention are illustrated, but the scope of the present invention does not limit In this, various change can be carried out without departing from the spirit and scope of the present invention.
Industrial applicibility
The present invention can be widely used in the parallel flow heat exchanger of cross-flow type.

Claims (4)

1. a parallel flow heat exchanger, for cross-flow type, described parallel flow heat exchanger includes:
The house steward of two vertical direction；And
Connect the flat tube of many horizontal directions between described house steward,
The flat tube of described many horizontal directions is grouped further and is one group with many, each group Constitute make cold-producing medium from the house steward of described two vertical direction to another root flow unidirectional Refrigerant path,
Described parallel flow heat exchanger is characterised by,
Described parallel flow heat exchanger is used for the off-premises station of air conditioner,
Constitute the upper limit of the radical of the described flat tube of described unidirectional refrigerant path, by by following Numerical value ± 2 that formula A obtains determine, constitute the described flat tube of described unidirectional refrigerant path The lower limit of radical determined by following formula B,
N ＜ 3.0 × 10-4×Q+8.0(A)
N ＞ (α Q+ β) × { (1.4 × 10-16)×L/(d×A’2)}0.5(B)
Wherein, n is the radical of the flat tube constituting unidirectional refrigerant path, Q be rated capacity also Using W as unit, α=0.0161, β=8.86, L be length of pipe and using m as unit, d Be hydraulic diameter and using m as unit, A ' is the cross-sectional area of the coolant channel of a flat tube And by m2As unit.
2. an air conditioner, it is characterised in that pacify in the off-premises station of described air conditioner Equipped with the parallel flow heat exchanger described in claim 1.
3. a parallel flow heat exchanger, for cross-flow type, described parallel flow heat exchanger includes:
The house steward of two vertical direction；And
Connect the flat tube of many horizontal directions between described house steward,
The flat tube of described many horizontal directions is grouped further and is one group with many, each group Constitute make cold-producing medium from the house steward of described two vertical direction to another root flow unidirectional Refrigerant path,
Described parallel flow heat exchanger is characterised by,
Described parallel flow heat exchanger is used for the indoor set of air conditioner,
Constitute the upper limit of the radical of the described flat tube of described unidirectional refrigerant path, by by following Numerical value ± 2 that formula A obtains determine, constitute the described flat tube of described unidirectional refrigerant path The lower limit of radical determined by following formula B,
N ＜ 4.2 × 10-4×Q+7.9(A)
N ＞ (α Q+ β) × { (1.4 × 10-16)×L/(d×A’2)}0.5 (B)
Wherein, n is the radical of the flat tube constituting unidirectional refrigerant path, Q be rated capacity also Using W as unit, α=0.0228, β=6.62, L be length of pipe and using m as unit, d Be hydraulic diameter and using m as unit, A ' is the cross-sectional area of the coolant channel of a flat tube And by m2As unit.
4. an air conditioner, it is characterised in that pacify in the indoor set of described air conditioner Equipped with the parallel flow heat exchanger described in claim 3.
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