CN106662380A - Branching means for a refrigerant flow of a refrigerant circuit - Google Patents
Branching means for a refrigerant flow of a refrigerant circuit Download PDFInfo
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- CN106662380A CN106662380A CN201580034621.4A CN201580034621A CN106662380A CN 106662380 A CN106662380 A CN 106662380A CN 201580034621 A CN201580034621 A CN 201580034621A CN 106662380 A CN106662380 A CN 106662380A
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- branch
- branch unit
- point
- refrigerant
- cooling
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
-
- 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
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/003—Filters
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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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
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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
- F25B2500/31—Low ambient temperatures
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off valves
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
-
- 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
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Secondary Cells (AREA)
Abstract
A branching means for a refrigerant flow of a refrigerant circuit (10), in particular of a battery cooler circuit (30), has an inlet (52) and at least two outlet lines (58) which lead to two cooling branches (34, 36), wherein at least one throttle stage is integrated into the branching means (44).
Description
Technical field
The present invention relates to be used for the branch unit of the refrigerant stream of cryogen circuit, the cryogen circuit is electric in particular
Pond chiller circuit.
Background technology
In electric vehicle or motor vehicle driven by mixed power, battery module produces heat in run duration, and the heat generally passes through
Cooling circuit dissipates.Here, in order to cool down battery module, it is advantageous to use the vehicle air conditioner being arranged in vehicle
Cooling sub-loop.
Because most of battery units are combined to form the single battery module that each other heat departs from, so as in each electricity
Without heat exchange between the module of pond, so battery chiller circuit is typically split into multiple cooling branch roads, the plurality of cooling
Road is each assigned to one or more battery modules.In this case, it is intended that cooling route refrigerant is put down
Flow through capablely.
It is known as battery chiller circuit and distributes special expansion gear, the expansion gear is arranged on going out for gas cooler
Mouthful and between the import of branch unit, the branch unit is diverted to refrigerant in each cooling branch road.Here, as swollen
Swollen device, using known thermostatic expansion valve (TXV), the state of the thermostatic expansion valve (TXV) in battery chiller circuit
It is through-flow to control refrigerant.In this example, the pressure drop in thermostatic expansion valve accounts for approximate the 60% to 95% of total pressure head, and branch
Pressure drop in device is only 3% to 10%.Its reason is, in the case where there is high environment temperature, the height of vehicle air conditioner
Pressure reduction between pressure branch road and low pressure branch road is significantly larger compared with the situation that there is low temperature.However, thermostatic expansion valve must be to
Evaporimeter provides the refrigerant of q.s, i.e., enough refrigerant flows, even if there is minimum operating temperature and therefore existing
In the case of minimum differntial pressure；And this pressure drop only in branch unit be only when less it is possible.It is thus known that branch dress
Put and be configured to little pressure drop.
In order to ensure the most long possible service life of single battery unit, it is necessary to ensure that between single battery unit only
It is no more than the very little temperature difference of 5K.However, the little pressure drop on branch unit makes it difficult to realize refrigerant to respectively
Evenly distributing for cooling branch road is planted, this always exists in the liquid-gas of branch point upstream in the case where there is relatively high temperature
In mixture.Due to the phase mixture in branch unit, it is known that branch unit must also be installed with accurately vertical direction,
Even if so as to exist it is little it is through-flow in the case of, it is also possible to realize two-phase mixture uniformly dividing as far as possible to various outlet lines
Match somebody with somebody.
Additionally, in the case where cooling down to battery module, even if in the low environment temperature for having such as little as -10 DEG C or lower
In the case of degree, cooling arrangement also must work, and this is contrary with the cooling arrangement in main cabin, and the cooling in main cabin is arranged in this
Generally it is off at a temperature of sample.
However, in the case where there is this low temperature, the liquid refrigerant in branch unit upstream is partly substantially
100%, it is known that branch unit be not configured to the part.
The content of the invention
The purpose of the present invention is on the gamut of the environment temperature of both summer and winter, it is ensured that battery cooler is returned
Uniform cooling performance in road, wherein reducing the cost and physical dimension of system simultaneously.
The purpose is by for cryogen circuit, the particularly refrigerant stream of battery chiller circuit branch unit
Realize, the branch unit has import and with least two outlet lines for leading to two cooling branch roads, wherein at least
One throttling level is integrated in the branch unit.Because refrigerant distribution and the function of decompression are combined in a part,
Therefore physical dimension and manufacturing cost are reduced.Relative to known arrangement, expansion gear (i.e. pressure reducer) can be obviously reduced
The distance between branch unit in branch road is cooled down with each, this causes the liquid portion of particularly refrigerant to each cooling
The evenly distribution on road.Therefore, also ensure that liquid refrigerant to each cooling branch road uniform of battery chiller circuit and
Enough supplies.
In a preferred embodiment, the level that throttles is arranged in the upstream of the branch point of each outlet line, wherein, throttling level is special
Not located immediately at the upstream of branch point.Because the space at shunting of the throttle point with refrigerant stream to each outlet line connects
Closely, the liquid and gas in refrigerant stream keep being thoroughly mixed in the downstream of throttle point, thereby, it is ensured that refrigerant is (including refrigerant
Liquid portion) evenly distributing to each outlet line.Due to cooling performance it is mainly relevant with the evaporation of the liquid phase of refrigerant,
Therefore the cooling performance of high uniformity can be obtained in two cooling branch roads.
By using throttling level in the upstream of branch point, it has proved that advantageously, directly use in the downstream of throttling level
Filter, to keep liquid phase and gas phase and refrigerant well to mix, and realizes two-phase during each outlet line is diverted to
Optimal possible homogenization.In another preferred embodiment, the level that throttles is arranged under the branch point of two outlet lines
Trip.Therefore, the import pressure of branch unit can continue the on high-tension side pressure being approximately corresponding in cryogen circuit, and refrigeration
The thermodynamic state of agent at least remains overcritical in the case where there is high environment temperature.Originally it is in branch point, refrigerant
With single phase presence, and therefore, it is possible to be easy to be evenly distributed to each outlet line, without running into regard to two-phase mixtures
The known problem of the distribution of thing.
Throttling the level preferably throttle point with each outlet line, the i.e. contraction flow region of flow cross section, the throttle point is special
There is no identical form, make the same terms in all outlet ports pipeline and in all coolings supplied from the outlet line
It is dominant in branch road.
The throttle point of throttling level can be formed by the duct calibrated.The duct of calibration is preferably formed directly into branch unit
In main body, and it is formed in the Trunk Line of branch point upstream or each overall group in the outlet line in branch point downstream
Into part.The length and internal diameter in the duct of calibration can highly precisely be limited and reproducibly manufactured so that can be accurate
The pressure drop of ground setting throttle point both sides.Furthermore, it is not necessary that using extra part.
If throttling level is arranged in outlet line, the duct calibrated can be formed as directly engaging the branch of Trunk Line
Point, to keep the structure length of branch unit less.
In another preferred embodiment, the level that throttles has the throttle point formed by the insertion tube of the internal diameter with calibration.
In this example, according to known decompression principle, single pipe is inserted in import, Trunk Line and/or outlet line, to realize
The accurate reduction of the actual internal area at throttle point.This pipe can be in simple and cheap mode and prefabricated with high accuracy,
And the appropriate location for being inserted into and being fastened in branch unit.In order to pipe is fastened in the main body of branch unit, Guan Ke
To be for example inserted in the screw shell in the main body for being screwed into branch unit.This is in the region of the import of branch unit
Or the throttle point in the region of Trunk Line and the throttle point in the region of outlet line are contemplated that.Accordingly it is also possible to hold
Change places and change and simply safeguard throttle point.
Stop is advantageously set on screw shell, and the stop guarantees main body of the pipe in branch unit
Interior is accurately positioned.
Duct and the pipe for the internal diameter with calibration for calibration, the suitable inner diameter of throttle point is for example in 0.2 He
Between 1.0mm, and appropriate length is between 10mm and 40mm.With the increase of the length of throttle point, flowing becomes more stable,
And reduce the sensitiveness produced to the vibration in flowing.
In order to prevent polluteing throttle point, preferably filter is set in the upstream of throttle point.
In a possible embodiment, by two throttling levels provide two-stage decompressions, the two throttling levels just flow and
Speech is series connection, and each throttling level has throttle point.Here, first throttle level can be arranged on Trunk Line in the upstream of branch point
In or be arranged in the region of the import of branch unit, and second throttling level can the arranged downstream of branch point outlet
In pipeline.
The respective internal diameter of throttle point is regularly predetermined, and is filled branch is not changed in structure for insertion tube
Can not change in the case of putting.
Pressure drop is set expecting on branch unit by the design of throttle point, especially by the arrangement of throttle point, horizontal stroke
Section and length are setting.
Branch unit can for example affect the 10 to 50% of overall presure drop.
In the case where there is about 20 DEG C to 40 DEG C of environment temperature, i.e., under the conditions of summer, refrigerant is preferably in branch unit
Entrance still only lies substantially in overcritical or liquid with single-phase.
In the case where there is about -10 DEG C to 0 DEG C of low ambient temperature, i.e., in the winter time during use, refrigerant is preferably filled in branch
The entrance put is completely in its liquid phase.In this case, can also not ask to two evenly distributing for outlet line
Topic.
Preferably, refrigerant stream does not have the phase being clearly separated under any mode of operation in branch point downstream so that
All the time refrigerant stream evenly distributing to two outlet lines is realized.Therefore, always it is to ensure that battery module in two cooling branch roads
In uniform cooling.Additionally, with regard to substantially reducing with the sensitivity of the deviation of vertically-mounted position.
In a preferred embodiment, branch unit has two outlet lines.It is self-evident, can provide in branch unit
Three or more outlet lines, rather than two outlet lines.Equally, the cooling of another battery with same or like structure
Device loop can be connected in parallel with regard to the battery chiller circuit with the branch unit
Description of the drawings
Based on multiple exemplary embodiments and the present invention will be described in greater detail with reference to the attached drawings below.In the accompanying drawings：
Fig. 1 is the schematic diagram of vehicle air conditioner, and its battery chiller system has branch unit of the invention；
Fig. 2 shows the schematic sectional view of the branch unit of the invention in first embodiment；
Fig. 3 shows the schematic sectional view of the branch unit of the invention in second embodiment；
Fig. 4 shows the schematic cross-sectional of the pressure reducer with branch unit of the invention in 3rd embodiment
Figure；
Fig. 5 is the schematic diagram of the switch periods of the stop valve of the pressure reducer of battery chiller system；
Fig. 6 is schematic diagram of the maximum differential pressure at the pressure reducer of battery chiller system as the function of environment temperature；
Fig. 7 is the schematic diagram of the enthalpy difference as the function of environment temperature of the evaporation of R744；With
Fig. 8 shows the Mollier diagram (Mollier diagram) of refrigerant R744, shows there is low and high environment
The working range of battery chiller system during temperature
Specific embodiment
Fig. 1 shows the cryogen circuit 10 of vehicle air conditioner (not illustrating in greater detail).Refrigerant is (in such case
It is down R744) flow through multiple cooling sub-loops.The refrigerant is compressed in compressor 12, then in gas cooler 14
Cooling, for example, cooled down by surrounding air., subsequently by inner heat exchanger 16, wherein it is by one for gaseous high-pressure refrigerant
A little heat energy are discharged into the refrigerant of the expansion on stream is returned.
In the first cooling sub-loop 18, the evaporimeter 20 that refrigerant stream passes through vehicle air conditioner, for example, by the steaming
Send out the cooling vehicle interior of device 20 cabin.
The upstream of evaporimeter 20 is provided with stop valve 22, when cooling down, can close by the stop valve 22
Cooling sub-loop 18.In this example, stop valve 22 includes the pressure reduction stage of the opening form with the cross section for reducing, the decompression
Level is used as throttle point and realizes the demi-inflation of refrigerant by decompression.
Decompression here from high-pressure side to low-pressure side shrinks to realize by regularly predetermined cross section, for example for
Known to R744 cryogen circuits.The diameter of the throttle point is selected especially in the way of the desired properties depending on evaporimeter
Select.Stop valve 22 is bridged by the bypass line 24 with safety valve 26.Safety valve 26 is configured to work as and reaches at safety valve 26
During critical pressure threshold value, it is allowed to which refrigerant circulation supercooling sub-loop 18, the critical pressure threshold value may, for example, be approximate 120-
150 bars (12-15MPa).
In general, when using R744 as refrigerant, it is necessary to protect cryogen circuit from overvoltage impact.This
In the case of, this realizes that safety valve 26 opens the height from cryogen circuit in the case where pressure increases suddenly by safety valve 26
Pressure side to the flowing of low-pressure side connects.In this case, the bypass functionality can use under the conditions of all operations.This pressure
Rising can occur for example in the case of strong vehicle acceleration, and in this case, compressor handling capacity can not be sufficiently fast
Ground is adjusted downwards so that substantial amounts of gas is directed in gas cooler 14.
Refrigerant from the backflow of evaporimeter 20 is present in storage again by inner heat exchanger 16 and by holder 28
Any liquid refrigerant of storage 28 is separated, and then refrigerant flow back into compressor 12.
With the first cooling sub-loop 18 concurrently, refrigerant flows through battery cooling circuit 30, and battery cooling circuit 30 is electricity
A part for pond chiller system 32.Battery chiller circuit can have the cooling power of about 0.5 to 2kW.Hybrid power
Or the battery unit of electric vehicle (here is not shown specifically) is arranged in this case in multiple modules, these modules are by simultaneously
Two cooling branch roads 34,36 of connection connection are cooled down.Therefore, in this case, battery chiller circuit 30 be divided into two it is cold
But branch road 34,36, two cooling branch roads open into common backflow suction line 38 after by battery module.Cooling
Road 34,36 is used as evaporimeter, and the liquid refrigerant in the evaporimeter absorbs the heat from battery unit, therefore is changed into gas
State.
In the downstream of the outlet of evaporimeter 20, the first cooling sub-loop 18 is passed through in backflow suction line 38.
Pressure reducer 40 is arranged in the upstream of two cooling branch roads 34,36.In modification shown here, pressure reducer 40 has
It is arranged in the stop valve 42 of the upstream of branch unit 44.
In the possibility embodiment being further described below (see Fig. 4), stop valve 42 and branch unit 44 are combined in list
In individual part.However, they can also be formed as single part.Stop valve 42 is may be omitted with, and is filled by branch completely
Put 44 realizations decompression.Stop valve 42 is connected to controller 46, and controller 46 can limit the open mode of stop valve 42.In the example
In, stop valve 42 can only be in two state of a control open and closes.In this example, in the direct downstream of stop valve 42
Temperature sensor i is disposed with, the temperature sensor is connected similarly to controller 46.Here, it is connected similarly to the of controller 46
Two temperature sensor T2 are set directly at the tie point 48 of two cooling branch roads 34,36.Fig. 2 to Fig. 4 shows branch unit
44 various embodiments.In order to clear, reference 44 has been used to all three embodiment.Branch unit shown in Fig. 2
44 have main body 50, and the recessed import 52 in main body 50, import 52 is transitioned in Trunk Line 54.In the end of Trunk Line 54
Branch point 56 is disposed with, Trunk Line 54 continues to be divided into two outlet lines 58 from the branch point 56, in these examples, the two
Outlet line each has identical form.Each outlet line 58 is transitioned in outlet 60, and corresponding outlet line 58 passes through
The outlet 60 is connected in two cooling branch roads 34,36 of battery chiller circuit 30.
Throttling level is integrated in branch unit 44, and the throttling level has the contraction flow region as throttle point, and the contraction
Therefore the decompression in restriction downstream is realized in portion.
In the illustrated example shown in fig. 2, by the duct of each one with regularly predetermined diameter and length calibration
62, realize throttling level in each outlet line 58.In this case, the duct 62 of calibration directly engages branch point 56,
And therefore as previously mentioned located immediately at the downstream of Trunk Line 54.Replace the branch road in two outlet lines 58, it is also possible to carry
The branch being supplied in more than two outlet line 58.Likewise it is possible to be connected in parallel relative to battery chiller circuit 30
Other battery chiller circuit (not shown) in multiple distributors 44 are provided.
In this example, the level that throttles is arranged on the downstream of branch point 56.This has the effect that, complete in Trunk Line 54
Ground is substantially completely in single-phase (it is overcritical or liquid to depend on environment temperature, as will be described in more detail)
Refrigerant is equably diverted to two outlet lines 58.Due to uniform coherent condition, the non-vertical of branch unit 44 is installed
Position does not result in any problem yet.Here, filter 64 is set in import 52, to prevent the pollution of branch unit 44.
In these examples, import 52 is formed in connector 66, and by the connector 66, branch unit 44 can connect
To battery chiller circuit 30 pipeline or be connected to stop valve 42 (referring to Fig. 4).
The duct 62 of calibration has the diameter of such as 0.2mm-1.0mm and the length of 10mm-40mm, wherein with throttle point
Length increase, flowing becomes more stable, and produces the trend of vibration in flowing and also reduce.Fig. 3 shows branch unit 44
An embodiment, wherein throttling level be arranged in the region of Trunk Line 54.In this case, decompression is in branch point 56
Upstream occurs.There is filter 68 in the arranged downstream of throttle point, the filter 68 is complete by the gentle body portion of liquid portion
Mixing and refrigerant is homogenized in throttle point downstream, so as to realize evenly distributing to two outlet lines 58.
In the example of fig. 3, throttle point is formed by the single insertion tube 70 of the internal diameter with calibration.Internal diameter and length can
With selecting with the situation identical mode in the duct 62 of the calibration of foregoing example embodiment.
In in order to pipe 70 to be fastened on the main body 50 of branch unit 44, screw shell 72 is provided with, the screw shell 72 revolves
In being screwed to the connector 66 of import 52.Replace screw shell 72, being also using the plug-in type sleeve being inserted in connector 66 can
Can.
Screw shell 72 has end stop 74, and it is used for being accurately positioned in Trunk Line 54 of pipe 70.
In inlet side, pipe 70 is covered by filter 64, and filter 64 prevents the pollution to branch unit 44.
The insert type 70 of the internal diameter of calibration can accurately be produced as duct.
Replace insertion tube 70, it is also possible to form duct in main body 50 in Trunk Line, is such as example directed to regard to Fig. 2
Described by outlet line 58.Similarly, in the embodiment shown in Figure 2, replace, in the duct 62 of calibration, each having school
It is also possible that one pipe 70 of accurate internal diameter is inserted in outlet line 58.
Furthermore, it is possible to not only one throttle point is provided in branch unit 44, but two sections connected for flowing
Flow point, wherein first segment flow point are arranged in Trunk Line 54, and the second throttle point in each outlet line 58 by each one
Contraction flow region is formed.
Fig. 4 shows pressure reducer 40, and it has the two throttling levels connected for flowing.
In this case, pressure reducer 40 is made up of branch unit 44 and stop valve 42, and these are by branch unit 44
Connector 66 is screwed together.In this example, branch unit 44 is corresponding to the branch unit 44 shown in Fig. 2.However, it is also possible to
Using the branch unit or some other suitable branch units 44 of the embodiment according to Fig. 3.
In this example, stop valve 42 is switched by electromagnet 76, and electromagnet 76 is connected to battery chiller system 32
Controller 46.By means of electromagnet 76, stop valve 42 switches between two switching state open and close, wherein leading to
Crossing the refrigerant stream of the import 78 of stop valve 42 is allowed completely or is stopped completely.
In the direct downstream of the valve seat 80 of stop valve 42, first throttle level is realized, in this example the hole by calibrating
Realize that the first throttle level constitutes for the refrigerant, contraction flow region with through flow cross section in road 82.The horizontal stroke in the duct 82 of calibration
Section narrows relative to the cross section of import 78, and also the cross section relative to the adjacent import 52 of branch unit 44 narrows.
By this way, first expansion and the first decompression of refrigerant are realized in the duct 82 of calibration.In branch unit 44, formed
Second throttling level, in this example, the contraction flow region formed by the duct 62 calibrated in outlet line 58 is formed, the second section
Stream level realizes second decompression and further expansion of refrigerant.
Replace the duct 82 of the calibration in the main body of stop valve 42, can be with the setting in the import 52 of branch unit 44
The duct of the calibration of the internal diameter with calibration or pipe 70.In this way it is possible to further simplify the construction of stop valve 42.
In two cooling branch roads 34,36 that refrigerant flows into battery chiller circuit 30 from outlet line 58.
In the embodiment shown in fig. 1, battery chiller system 32 be configured such that " winter condition " exist it is low
In the case of environment temperature, i.e., in the case where there is the temperature between about -10 DEG C and 0 DEG C, about 10 are obtained on pressure reducer
The enthalpy difference of the pressure reduction of bar and about 240kJ/kg.Can also be with regard between the high-pressure side of whole cryogen circuit 10 and low-pressure side
Pressure reduction is constructing pressure reduction.The particular design of the throttling level that these parameters pass through pressure reducer 40 is realizing.
Importantly, the refrigerant flow realized by the cross section contraction flow region throttled in level is sufficiently large, though so as to
Also in battery chiller circuit 30 enough cooling performances are provided in the case of low ambient temperature for battery module.In these rings
Under the conditions of border, the phase boundray to supercriticality exceeds only about 1 to 5 Kelvin (also seeing Fig. 8).
In summer under main environment temperature, i.e., in the case where+40 DEG C of temperature is up to about, in cryogen circuit 10
And battery cooler circuit 30 high-pressure side and low-pressure side between there is sizable pressure reduction.In order to prevent under these conditions
By the mistake big flow of the liquid coolant of branch unit 44, stop valve 42 is operated in a pulsed fashion, wherein crossing the liquid of big flow
Body cooling agent can not in cooling branch road 34,36 evaporating completely, and therefore reduce the evaporimeter 20 of air-conditioning for crew module
Cooling performance.
This schematically shows in Figure 5.Block curve is represented, in the case of high environment temperature, stop valve 42 passes through
Controller 46 is with pulse-width modulation operation so that cooling performance is optimised.The opening duration of stop valve 42 by controller 46 from
By temperature sensor T1And T2The value of the signal for sending, i.e., the refrigerant temperature from the import 52 of branch unit 44 and described
Refrigerant is calculated by the refrigerant temperature after the cooling branch road 34,36 of battery chiller circuit 30.
The time period remained turned-off between 42 two open modes of stop valve can be 30 seconds or more；This is also applied for
The time period that stop valve 42 is opened between dwell period.This is possible, because the battery cooler with battery module is returned
Road 30 has the higher thermal activities quality of the evaporimeter 20 of ratio such as vehicle air conditioner.
In winter, that is to say, that in the case where there is low environment temperature and little pressure reduction, on the contrary, situation is off
Valve 42 is constantly opened (referring to the dotted line in Fig. 5).
Fig. 6 and Fig. 7 show as environment temperature it is function, on the high-pressure side of cryogen circuit 10 and in its low pressure
Pressure present on side.On high-tension side pressure distribution is represented by rhombus, and the pressure distribution in low-pressure side is by square expression.From
As can be seen that in the case where there are the winter conditions between -10 DEG C to 0 DEG C in Fig. 6, it is contemplated that 7bar's to 9bar (0.7 to 0.9MPa)
Pressure reduction, and under the conditions of the summer of 25 to 40 DEG C of environment temperature, there is considerably higher pressure reduction, such as 35bar to 65bar
(3.5 to 6.5MPa), wherein even there may be the pressure reduction of 90bar.According to this measurement, for cryogen circuit 10 in show
There is battery chiller system 32, the optimum configuration of pressure reducer 40 can be calculated.For this purpose, refrigerant must also be considered (in this example
In, R744) evaporation during enthalpy difference, the enthalpy difference in the figure 7 as environment temperature function draw.
Pressure reduction between high-pressure side and low-pressure side is greatly increased with the rising of environment temperature.Due to produced quality
Flow approximately changes with the square root of pressure reduction, therefore when for environment temperature being such as -10 DEG C, battery cooler is returned
The possibility cooling performance on road 30 reduces about 40% relative to+40 DEG C of environment temperature.If battery chiller system 32 and
Particularly pressure reducer 40 is optimised for operation at low ambient temperatures, then this has the effect that：There is high environment temperature
During the operation of degree, stop valve 42 should be closed on the time of about 30%-90%.
The remainder of cryogen circuit 10, particularly for vehicle air conditioner evaporimeter 20 cooling sub-loop 18
The construction of remainder do not affected by these considerations because the pressure reducer 40 only in battery chiller circuit 30 must be by phase
Should ground construction.Fig. 8 shown under summer condition (high environment temperature) and winter conditions (low ambient temperature) based on mollier diagram,
The circulation that the operation of cryogen circuit 10 is passed through.
Top circulation (point A to G) in curve map describes the operation in the presence of high environment temperature.High-pressure side, at this
In the case of kind preferably between 80 and 120 bars, operate in subcritical range.From point A to point B, cause in compressor 12
The compression of cryogen.From point B to point C, postcritical refrigerant is cooled in gas cooler 14.From point C to point D, by interior
Portion's heat exchanger 16 realizes the further cooling on the high-pressure side of cryogen circuit 10.From point D to point E, in pressure reducer 40
Reduce pressure in first throttle level, wherein decompression at most occurs until liquid boundary so that refrigerant is into branch unit 44
When only keep single-phase form or in a supercritical state.From point E to point F, in the second throttling level of pressure reducer 40 one is entered
Step decompression, under this example, occurs in the outlet line 58 of branch unit 44.From point F to point G, occur in battery cooler
The cooling of the battery module in the cooling branch road 34,36 in loop 30, wherein refrigerant is evaporated, and is absorbed from battery module
Heat.Finally, from point G to point A, refrigerant flows through inner heat exchanger 16 via backflow suction line 38, returns to compressor 12, its
Described in Refrigerant absorption from high pressure branch road heat.In the winter time in operation (the bottom circulation in Fig. 8, point a-f), in critical point
Same loop performed below.From point a to point b, refrigerant is compressed, and from point b to point d, the refrigerant is cooled.Causing
(point d to point e), refrigerant are completely in liquid phase after expansion of the cryogen in the first throttle level of pressure reducer 40.Only when it
By the second throttling level, (during point e to point f), refrigerant just has gaseous parts.
However, in example as herein described, refrigerant still only exists in single-phase form in branch unit 44.With this
Mode, compared with the presence of phase mixture, it is easier to realize evenly distributing to two cooling branch roads 34,36.
Claims (10)
1. one kind is used for the branch unit of the refrigerant stream of cryogen circuit (10), and the cryogen circuit is particularly battery cooler
Loop, the branch unit has import (52) and with least two outlets for leading to two cooling branch roads (34,36)
Line (58), wherein at least one throttling level is integrated in the branch unit (44).
2. branch unit according to claim 1, it is characterised in that the throttling level is arranged into two outlet lines (58)
Branch point (56) upstream.
3. branch unit according to claim 2, it is characterised in that filter (68) is arranged under the throttling level
Trip.
4. branch unit according to claim 1, it is characterised in that the throttling level is arranged in two outlet lines (58)
Branch point (56) downstream.
5. branch unit according to claim 4, it is characterised in that throttling level tool in each outlet line (58)
There is contraction flow region.
6. the branch unit described in aforementioned claim, it is characterised in that the throttling level has by calibrating
Duct (62) formed throttle point.
7. branch unit according to claim 6, it is characterised in that the duct (62) of the calibration is formed as directly engagement
The branch point (56) of Trunk Line (54).
8. the branch unit according in claim 1 to 6, it is characterised in that the throttling level has by with school
The throttle point that the insertion tube (70) of accurate internal diameter is formed.
9. branch unit according to claim 8, it is characterised in that the pipe (70) be inserted into screw shell (72) or
In plug-in type sleeve, the sleeve is screwed into or is inserted in the main body of the branch unit (44) (50).
10. the branch unit described in aforementioned claim, it is characterised in that first throttle level is arranged in described
The upstream of branch point (56), and the second throttling level is arranged in the downstream of the branch point (56).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014108989.8A DE102014108989A1 (en) | 2014-06-26 | 2014-06-26 | Branch for a refrigerant flow of a refrigerant circuit |
| DE102014108989.8 | 2014-06-26 | ||
| PCT/EP2015/064105 WO2015197612A1 (en) | 2014-06-26 | 2015-06-23 | Branching means for a refrigerant flow of a refrigerant circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106662380A true CN106662380A (en) | 2017-05-10 |
Family
ID=53476896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580034621.4A Pending CN106662380A (en) | 2014-06-26 | 2015-06-23 | Branching means for a refrigerant flow of a refrigerant circuit |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20170138651A1 (en) |
| EP (1) | EP3161393A1 (en) |
| JP (1) | JP2017523371A (en) |
| CN (1) | CN106662380A (en) |
| DE (1) | DE102014108989A1 (en) |
| WO (1) | WO2015197612A1 (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20160223239A1 (en) * | 2015-01-31 | 2016-08-04 | Trane International Inc. | Indoor Liquid/Suction Heat Exchanger |
| CN107403975B (en) * | 2017-07-21 | 2019-09-27 | 精进电动科技股份有限公司 | A kind of energy-storage battery liquid cooling system current equalizer and method |
| US10738667B2 (en) * | 2017-11-03 | 2020-08-11 | Dana Heavy Vehicle Systems Group, Llc | Heat transfer system |
| FR3077376A1 (en) * | 2018-01-31 | 2019-08-02 | Valeo Systemes Thermiques | REFRIGERANT FLUID CIRCUIT FOR IMPROVED PERFORMANCE VEHICLE |
| DE102019208976A1 (en) | 2019-06-19 | 2020-12-24 | Volkswagen Aktiengesellschaft | Branch piece for a fluid line |
| FR3116598A1 (en) * | 2020-11-24 | 2022-05-27 | Valeo Systemes Thermiques | Refrigerant circuit comprising a particulate filter |
| EP4068471A1 (en) * | 2021-03-29 | 2022-10-05 | Castrol Limited | Heat transfer system with heat transfer fluid including liquid and gas components |
| EP4068472A1 (en) * | 2021-03-29 | 2022-10-05 | Castrol Limited | Heat transfer system with heat transfer fluid including liquid and gas components |
| EP4068470A1 (en) * | 2021-03-29 | 2022-10-05 | Castrol Limited | Heat transfer system with heat transfer fluid including liquid and gas components |
| DE102021204489A1 (en) * | 2021-05-04 | 2022-11-10 | BSH Hausgeräte GmbH | Dryerless refrigeration circuit, method of assembling a refrigeration circuit and refrigeration device |
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|---|---|---|---|---|
| DE1904245A1 (en) * | 1969-01-29 | 1970-08-06 | Ver Deutsche Metallwerke Ag | Attachment method for capillary tube - in refrigerator elements |
| US20040035134A1 (en) * | 2002-08-22 | 2004-02-26 | Oberley Brian J. | Remote distributor with integrated check valve |
| JP2008157305A (en) * | 2006-12-21 | 2008-07-10 | Denso Corp | Pressure control valve and supercritical refrigeration cycle |
| US20100313585A1 (en) * | 2006-04-21 | 2010-12-16 | Parker Christian D | Fluid expansion-distribution assembly |
| US20130087204A1 (en) * | 2011-10-07 | 2013-04-11 | Trane International Inc. | Pressure Correcting Distributor For Heating and Cooling Systems |
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| JPS56161458U (en) * | 1980-04-30 | 1981-12-01 | ||
| JPH0338598Y2 (en) * | 1985-05-17 | 1991-08-14 | ||
| JPS6433479A (en) * | 1987-07-28 | 1989-02-03 | Fuji Heavy Ind Ltd | Flow diverter for refrigerator |
| US6023940A (en) * | 1998-07-06 | 2000-02-15 | Carrier Corporation | Flow distributor for air conditioning unit |
| JP2000356438A (en) * | 1999-06-15 | 2000-12-26 | Kobo Koki:Kk | Fluid circuit pipe |
| JP4560939B2 (en) * | 2000-10-20 | 2010-10-13 | ダイキン工業株式会社 | Refrigerant shunt and air conditioner using the same |
| JP2011094946A (en) * | 2009-09-30 | 2011-05-12 | Daikin Industries Ltd | Gas refrigerant separator, gas refrigerant separator-cum-refrigerant flow divider, expansion valve, and refrigeration device |
| JP5083390B2 (en) * | 2010-08-02 | 2012-11-28 | ダイキン工業株式会社 | Refrigerant flow divider, refrigerant flow divider integrated expansion device and refrigeration device |
| JP6098121B2 (en) * | 2012-11-07 | 2017-03-22 | 株式会社デンソー | Cooling system |
-
2014
- 2014-06-26 DE DE102014108989.8A patent/DE102014108989A1/en active Pending
-
2015
- 2015-06-23 CN CN201580034621.4A patent/CN106662380A/en active Pending
- 2015-06-23 JP JP2016575114A patent/JP2017523371A/en active Pending
- 2015-06-23 US US15/317,528 patent/US20170138651A1/en not_active Abandoned
- 2015-06-23 EP EP15730794.3A patent/EP3161393A1/en not_active Withdrawn
- 2015-06-23 WO PCT/EP2015/064105 patent/WO2015197612A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1904245A1 (en) * | 1969-01-29 | 1970-08-06 | Ver Deutsche Metallwerke Ag | Attachment method for capillary tube - in refrigerator elements |
| US20040035134A1 (en) * | 2002-08-22 | 2004-02-26 | Oberley Brian J. | Remote distributor with integrated check valve |
| US20100313585A1 (en) * | 2006-04-21 | 2010-12-16 | Parker Christian D | Fluid expansion-distribution assembly |
| JP2008157305A (en) * | 2006-12-21 | 2008-07-10 | Denso Corp | Pressure control valve and supercritical refrigeration cycle |
| US20130087204A1 (en) * | 2011-10-07 | 2013-04-11 | Trane International Inc. | Pressure Correcting Distributor For Heating and Cooling Systems |
Also Published As
| Publication number | Publication date |
|---|---|
| US20170138651A1 (en) | 2017-05-18 |
| DE102014108989A1 (en) | 2015-12-31 |
| JP2017523371A (en) | 2017-08-17 |
| EP3161393A1 (en) | 2017-05-03 |
| WO2015197612A1 (en) | 2015-12-30 |
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Application publication date: 20170510 |