CN105408703A - Distributor for use in a vapor compression system - Google Patents

Abstract

A distributor (142) for use in a vapor compression system (14) includes an enclosure (144) configured to be positioned in a heat exchanger (38) having a tube bundle (78) including a plurality of tubes extending substantially horizontally in the heat exchanger (38). At least one distribution device (146) formed in an end (148) of the enclosure (144) positioned to face the tube bundle (78), the at least one distribution device (146) configured to apply a fluid entering the distributor (142) onto the tube bundle (78). The enclosure (144) has an aspect ratio between about 1/2:1 and about 10:1.

Description

For the distributor in steam compression system

The cross reference of related application

This application claims priority and rights and interests that the name submitted on June 7th, 2013 is called No. 13/912634 U.S.'s non-provisional application of " steam compression system ".

Background technology

The application relates in general to the steam compression system in refrigeration, air-conditioning and frozen liq system.The application relates more specifically to distribution system in steam compression system and method.

The conventional freezing liquid system used in heating ventilation air-conditioning system comprises an evaporimeter, in order to carry out heat energy transmission between the cold-producing medium and other liquid to be cooled of system.The evaporimeter of one type comprises the housing with the many pipes forming tube bank, and liquid to be cooled circulates in pipe.Cold-producing medium is directed to and contacts with the outside of the tube bank of enclosure interior or outer surface, causes, between liquid to be cooled and cold-producing medium, heat energy transmission occurs.Such as, can by spray or cold-producing medium deposit on the outer surface of tube bank by other similar technology in so-called " falling film type " evaporimeter usually.In another example, the outer surface of described tube bank can immerse usually in the liquid refrigerant in so-called " submerged " evaporimeter whole or in part.In another example, a part for tube bank can have the cold-producing medium be deposited on outer surface, and another part of described tube bank can immerse in the liquid refrigerant be commonly called in " mixing falling film type " evaporimeter.

Due to the heat energy transmission with liquid, cold-producing medium is converted to steam state by heating, and then returns compressor and steam is compressed herein, to start another refrigerant circulation.The liquid of cooling can be circulated to the multiple heat exchangers spread in whole building.From the hot-air in building through described heat exchanger, heated at the liquid of described heat exchanger place cooling, cooled the air of building simultaneously.Turn back in evaporimeter by the liquid of the air heat of building, to repeat this process.

Summary of the invention

The present invention relates to a kind of for the distributor in steam compression system, comprise the capsule (enclosure) being configured to be positioned to have in the heat exchanger of tube bank, described tube bank has many pipes of the less horizontal extension in described heat exchanger.In the end being oriented in the face of described tube bank of described capsule, form at least one distributor, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank.Described capsule has about 1/2:1 to the length-width ratio about between 10:1.

The invention still further relates to a kind of for the distributor in steam compression system, comprise the capsule being configured to be positioned to have in the heat exchanger of tube bank, described tube bank is included in many pipes of the less horizontal extension in described heat exchanger.In the end being oriented in the face of described tube bank of described capsule, form at least one distributor, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank.Described capsule has about 1/2:1 to the length-width ratio about between 10:1.The described end of described capsule comprises an end features, and at least one distributor described comprises at least one opening be formed in described end features.With the jet angle distributing fluids between about 60 degree to about 180 degree in the substantially whole fluid pressure range that the operation that at least one opening described was configured and was set to the distributor in described system is relevant.

The present invention also relates to a kind of method of distributing fluids in steam compression system in addition.Described method comprises the capsule providing and be configured to be positioned to have in the heat exchanger of tube bank, and described tube bank is included in many pipes of the less horizontal extension in described heat exchanger.Described method is included in an end of described tube bank faced by being oriented to of described capsule and forms at least one distributor, and at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank.Described capsule has about 1/2:1 to the length-width ratio about between 10:1.Described method comprises the described steam compression system of operation.

Accompanying drawing explanation

Fig. 1 shows an exemplary for heating ventilation air-conditioning system.

Fig. 2 shows the isometric view of an example vapor compression system.

Fig. 3 and 4 schematically shows the exemplary of described steam compression system.

Fig. 5 A shows the phantom of the decomposition of exemplary evaporator.

What Fig. 5 B showed evaporimeter in Fig. 5 A overlooks isometric view.

Fig. 5 C shows the sectional view of the evaporimeter intercepted along the line 5-5 in Fig. 5 B.

What Fig. 6 A showed exemplary evaporator overlooks isometric view.

Fig. 6 B and 6C shows the sectional view of the evaporimeter intercepted along the line 6-6 in Fig. 6 A.

Fig. 7 shows the top isometric view of an exemplary of capsule.

Fig. 8 shows the plane of the capsule in Fig. 7.

Fig. 9 shows the partial front view of the capsule intercepted along the line 9-9 in Fig. 7.

Figure 10 shows the sectional view of the capsule intercepted along the line 10-10 in Fig. 9.

Figure 11 shows the sectional view of the capsule of the exemplary intercepted along the line 10-10 in Fig. 9.

Figure 12 shows the sectional view of the capsule of another exemplary intercepted along the line 10-10 in Fig. 9.

Figure 13 shows the sectional view of the capsule of another exemplary intercepted along the line 10-10 in Fig. 9.

Figure 14 shows the sectional view of the capsule of another exemplary again intercepted along the line 10-10 in Fig. 9.

Figure 15 shows an exemplary of capsule.

Detailed description of the invention

Fig. 1 illustrates an exemplary environments of HVAC (HVAC) system 10, and described system 10 is included in the frozen liq system used in the building 12 of typical commercial facility.System 10 can comprise steam compression system 14, and steam compression system 14 can be supplied can in order to cool the frozen liq of building 12.System 10 can comprise: boiler 16, can in order to the heated liquid heated building 12 in order to supply; And make air cycle through the air distribution system of building 12.Described air distribution system also can comprise return air duct 18, air supply line 20 and air disposer 22.Air disposer 22 can comprise heat exchanger, and described heat exchanger is connected to boiler 16 and steam compression system 14 by conduit 24.Heat exchanger in air disposer 22 can according to the operator scheme of system 10, receives the heated liquid from boiler 16 or the frozen liq that receives from steam compression system 14.Shown system 10 all has independently air disposer on every one deck of building 12, but should be appreciated that, can share some assemblies between two layers or more layer.

An example vapor compression system 14 during Fig. 2 and Fig. 3 illustrates and can be used on HVAC system---such as HVAC system 10---.Compressor reducer 32, condenser 34, expansion gear 36 and liquid chiller that steam compression system 14 can make refrigerant circulation process be driven by motor 50 or evaporimeter 38.Steam compression system 14 also can comprise control panel 40, and this control panel 40 can comprise mould/number (A/D) converter 42, microprocessor 44, nonvolatile memory 46 and interface board 48.Some embodiments that can be used as the fluid of the cold-producing medium in steam compression system 14 are the cold-producing mediums based on hydrogen fluorohydrocarbon (HFC), the cold-producing medium of " natural " cold-producing medium of such as R-410A, R-407, R-134a, HF hydrocarbon (HFO), such as ammonia (NH3), R-717, carbon dioxide (CO2), R-744 or alkyl cold-producing medium, water vapour or other suitable type arbitrary.In an exemplary embodiment, what steam compression system 14 can use in following every type device is one or more: in VSD52, motor 50, compressor reducer 32, condenser 34 and/or evaporimeter 38.

The motor 50 used together with compressor reducer 32 can provide power by speed-changing transmission device (VSD) 52, also directly can power from interchange (AC) or direct current (DC) power supply.If use VSD52, so VSD52 receives the AC electric power with specific fixed line voltage and fixed line frequency from AC power supplies, and the electric power with variable voltage and frequency is provided to motor 50.Motor 50 can comprise the motor of arbitrary type that can provide power by VSD or directly power from AC or DC power supply.For example, motor 50 can be switching magneti-resistance motor, induction conductivity, electronic commutation permanent magnet motor or other suitable motor type arbitrary.In Alternative exemplary embodiment, other driving mechanism such as such as steam or combustion gas turbine or engine etc. and associated component can in order to drive compressor reducer 32.

Compressor reducer 32 pairs of refrigerant vapours compress and by discharge pipe line by steam delivery to condenser 34.Compressor reducer 32 can be centrifugal compressed device, helical compression device, reciprocating compressor reducer, rotary compressor, fork compressor reducer, scroll compressor device, turbocompressor, or other suitable compressor reducer arbitrary.The refrigerant vapour being delivered to condenser 34 by compressor reducer 32 transfers heat to fluid, such as water or air.Due to fluid generation heat trnasfer, therefore refrigerant vapour is condensed into refrigerant liquid in condenser 34.The liquid refrigerant carrying out condenser 34 flows through expansion gear 36 and arrives evaporimeter 38.In the exemplary shown in Fig. 3, condenser 34 is Water cooling types, and comprises the tube bank 54 being connected to cooling tower 56.

Be delivered to the liquid refrigerant of evaporimeter 38 from another fluid absorbent thermal, and there occurs phase transformation and become refrigerant vapour, another fluid described and condenser 34 fluid type used can be the same or different.In the exemplary shown in Fig. 3, evaporimeter 38 comprises the tube bank with supply line 60S and return line 60R, and wherein supply line 60S and return line 60R is connected in cooling load 62.Process fluid, such as water, ethylene glycol, calcium chloride brine, sodium chloride brine or other suitable liquid arbitrary, enter evaporimeter 38 via return line 60R and exit evaporimeter 38 via supply line 60S.Evaporimeter 38 makes the temperature of the process fluid in pipe reduce.Tube bank in evaporimeter 38 can comprise many pipes and multiple tube bank.Vapor refrigerant exits evaporimeter 38 and turns back to compressor reducer 32 by suction line, to complete circulation.

Fig. 4 is similar to Fig. 3, is depicted as the refrigerant loop with intermediate loop 64, and intermediate loop 64 to can be placed between condenser 34 and expansion gear 36 thus increases cooling capacity, raises the efficiency and performance.Intermediate loop 64 has suction line 68, and suction line 68 can be directly connected to condenser 34 or fluidly can be communicated with condenser 34.As diagram, suction line 68 comprises the expansion gear 66 being positioned at intermediate receptacle 70 upstream.In an exemplary embodiment, intermediate receptacle 70 can be flash tank, also referred to as flash distillation intercooler.In Alternative exemplary embodiment, intermediate receptacle 70 can be configured to heat exchanger or " surperficial economizer ".In flash distillation intercooler is arranged, the first expansion gear 66 is in order to reduce the pressure of the liquid received from condenser 34.During expansion process in flash distillation intercooler, a part of liquid evaporation.Intermediate receptacle 70 can in order to make the steam of evaporation and the fluid separation applications received from condenser.The liquid of evaporation can be drawn into a port by compressor reducer 32 by pipeline 74, and this carries out or carries out in the interstage of compression under the pressure between suction side and waste side.Unevaporated liquid is cooled by expansion process, and is collected in the bottom of intermediate receptacle 70, by comprising the pipeline 72 of the second expansion gear 36, being recovered flowing to evaporimeter 38 again at the described liquid of bottom.

As known in the art, in " surperficial intercooler " is arranged, implementation process is slightly different.Intermediate loop 64 can operate in a manner similar to that described above, only receive a part for cold-producing medium and all the other cold-producing mediums directly advance to expansion gear 36 from condenser 34 unlike intermediate loop 64, instead of receive the cold-producing medium of whole amount from condenser 34 as shown in Figure 4.

Fig. 5 A to Fig. 5 C illustrates the exemplary of the evaporimeter being configured to " mixing falling film type " evaporimeter.As shown in Figure 5 A to 5 C shown in FIG., evaporimeter 138 comprises the generic cylindrical housing 76 of many pipes having and form tube bank 78, tube bank 78 along the length direction of housing 76 less horizontal extend.At least one support member 116 can be positioned in housing 76 to support the described many pipes in tube bank 78.Suitable fluid, such as water, ethene, ethylene glycol or calcium chloride brine flow through each pipe of tube bank 78.Be positioned distributor 80 above tube bank 78 cold-producing medium 110 to be distributed, deposit or be applied to from multiple position on each pipe tube bank 78.In an exemplary embodiment, the cold-producing medium deposited by distributor 80 can be liquid refrigerant completely, but in another exemplary, the cold-producing medium deposited by distributor 80 can comprise liquid refrigerant and vapor refrigerant.

At each pipe ambient dynamic of tube bank 78 and the liquid refrigerant not changing state be collected in the low portion of housing 76.Collected liquid refrigerant can form the Chi Huozhuji district 82 of liquid refrigerant.Any combination of lengthwise position relative to tube bank 78 or lateral attitude can be comprised from the deposition position of distributor 80.In another exemplary, be not limited to the deposition position of each pipe in top depositing to tube bank 78 from the deposition position of distributor 80.Distributor 80 can comprise the multiple nozzles being carried out feed by the spread source of cold-producing medium.In an exemplary embodiment, spread source is a pipe being connected to cryogen source (such as condenser 34).Nozzle comprises injection nozzle, but also comprises and cold-producing medium can be guided or be directed to the opening of the machining on the surface of pipe.Nozzle can apply cold-producing medium according to preassigned pattern (such as injection stream pattern), and the pipe of the upper row of tube bank 78 is capped.Restrain 78 each pipes can be arranged to promote that cold-producing medium is with following fluxus formae, the form of described cold-producing medium can be the film, coalescent and form the liquid refrigerant of drop around tube-surface, or in some instances, be positioned at curtain or the curtain of the liquid refrigerant bottom tube-surface.The curtain that formed promotes the wetting of tube-surface, the heat transference efficiency between the cold-producing medium which enhancing the surperficial ambient dynamic of the fluid at each Bottomhole pressure of tube bank 78 and each pipe in tube bank 78.

In the pond 82 of liquid refrigerant, tube bank 140 can be immersed or be immersed at least partly, to provide the transmission of the additional thermal energy between cold-producing medium and process fluid, thus the pond 82 of evaporating liquid cold-producing medium.In an exemplary embodiment, restrain 78 and can be positioned (that is, overlapping at least in part) above tube bank 140 at least in part.In an exemplary embodiment, evaporimeter 138 comprises a bilateral system, process fluid wherein to be cooled is first at the Bottomhole pressure of tube bank 140, and directed with each Bottomhole pressure in tube bank 78 on the direction contrary with the flowing in tube bank 140 subsequently.In the alternate path of described bilateral system, in tube bank 78, the temperature of the fluid of flowing reduces, and therefore needs the heat trnasfer that small amount occurs between the cold-producing medium flowed on the surface of tube bank 78, to obtain the process fluid with desired temperature.

Should be appreciated that, although disclosed a bilateral system, wherein the first path to be associated and alternate path is associated with tube bank 78 with tube bank 140, also contemplates the layout that other is possible.For example, evaporimeter 138 can comprise a single-pass sytem, and wherein process fluid flows through tube bank 140 and tube bank 78 with same direction.Or evaporimeter 138 can comprise a three pass system, wherein two paths are associated with tube bank 140 and all the other paths are associated with tube bank 78, or one of them path with restrain 140 be associated and all the other two paths with restrain 78 and be associated.In addition, evaporimeter 138 can comprise the bilateral system of an alternative expression, and one of them path is associated with restraining both 140 with tube bank 78, and alternate path is also associated with restraining both 140 with tube bank 78.In an exemplary embodiment, tube bank 78 is positioned above tube bank 140 at least in part, makes to there is the gap be separated between tube bank 78 with tube bank 140.In another exemplary, cover 86 is overlying in tube bank 78, and wherein cover 86 extends towards described gap and ends at described near gaps.In a word, present invention contemplates and there is any number of vias object system, wherein each path can with pipe 78 and restrain one of 140 or both be associated.

Capsule or cover 86 are positioned to stop that cross flow one occurs substantially above tube bank 78, cross flow one and vapor refrigerant or liquid and the lateral flow of vapor refrigerant 106 between each pipe of tube bank 78.Each pipe of tube bank 78 is laterally defined above the pipe that cover 86 is positioned tube bank 78.Cover 86 comprises the upper end 88 near the upper part being positioned housing 76.Distributor 80 can be positioned between cover 86 and tube bank 78.In another exemplary, it is neighbouring but outside at cover 86 that distributor 80 can be positioned cover 86, makes distributor 80 not between cover 86 and tube bank 78.But even if distributor 80 is not between cover 86 and tube bank 78, the nozzle of distributor 80 is also still configured to be guided by cold-producing medium or be applied on the surface of pipe.The upper end 88 of cover 86 is configured to prevent the stream of the cold-producing medium (namely liquid and/or vapor refrigerant 106) of applied cold-producing medium 110 and part evaporation from directly flowing to outlet 104 substantially.But the cold-producing medium 110 applied and cold-producing medium 106 are subject to the restriction of cover 86, and more particularly, are forced between wall 92 and advance downwards, and cold-producing medium just can exit via the open end 94 in cover 86 afterwards.The flowing of vapor refrigerant 96 around cover 86 also relates to evaporated cold-producing medium and flows out from the pond 82 of liquid refrigerant.

Should be appreciated that, the relative terms indicated at least is above nonrestrictive about other exemplary in the disclosure.For example, cover 86 can rotate relative to other evaporator assemblies previously discussed, and that is, the cover 86 comprising wall 92 is not limited to vertical orientation.After cover 86 has carried out abundant rotation around the axis of each pipe being substantially parallel to tube bank 78, cover 86 can have been thought to be no longer each pipe " top " of " being positioned " tube bank 78 be also no longer each pipe of " laterally defining " tube bank 78.Similarly, " top " end 88 of cover 86 can no longer be positioned near " upper part " of housing 76, and this kind that other exemplary is not limited between cover and housing is arranged.In an exemplary embodiment, cover 86 is constipation bundle after covering tube bank 78, but in another exemplary, cover 86 still extends further after covering tube bank 78.

Force after cold-producing medium 106 travels across open end 94 between wall 92 downwards at cover 86, the flow direction flip-flop of vapor refrigerant, advances to the upper part of housing 76 from the low portion of housing 76 in the space afterwards between housing 76 and wall 92.In conjunction with gravitational effect, the flip-flop of flow direction causes the part in all cold-producing medium drops carried under one's arms and liquid refrigerant 82 or housing 76 to be collided, and then these drops are removed from the stream of vapor refrigerant 96.And, the mist of refrigerant of advancing between wall 92 along the length direction of cover 86 gathers into larger drop, these larger drops are separated more easily by gravity, or maintain fully near restraining the place of 78 or contacting with tube bank 78, to allow by making mist of refrigerant evaporate with the heat trnasfer of tube bank.Because the size of drop increases, carried out the improved efficiency of fluid separation applications by gravity, thus allow the vapor refrigerant 96 of the upwards speed with increase to flow through the evaporimeter in the space between wall 92 and housing 76.No matter vapor refrigerant 96 is flow from open end 94 or flow from the pond 82 of liquid refrigerant, all flows through a pair extension 98, and described extension 98 is given prominence to and admission passage 100 from wall 92 near upper end 88.Vapor refrigerant 96 is by slit 102 admission passage 100, and slit 102 is the spaces between the end of extension 98 and housing 76, and vapor refrigerant 96 exits evaporimeter 138 at outlet 104 place afterwards.In another exemplary, vapor refrigerant 96 is by being formed at opening in extension 98 or hole instead of slit 102 admission passage 100.In another exemplary, slit 102 can be formed by the space between cover 86 and housing 76, and that is, cover 86 does not comprise extension 98.

In other words, once cold-producing medium 106 exits from cover 86, vapor refrigerant 96 just flow to the upper part of housing 76 along the path of regulation from the low portion of housing 76.In an exemplary embodiment, described path can be symmetrical substantially between cover 86 and the surface of housing 76 before arrival outlet 104.In an exemplary embodiment, near evaporator outlet, be provided with multiple baffle plate (such as extension 98), in order to stop the directapath of vapor refrigerant 96 to compressor inlet.

In an exemplary embodiment, cover 86 and comprise substantial parallel relative wall 92.In another exemplary, each wall 92 can extend generallyperpendicularly and end at open end 94, and the position of open end 94 is relative with upper end 88 substantially.Upper end 88 and wall 92 are closely positioned near each pipe of tube bank 78, and its mesospore 92 extends towards the low portion of housing 76, laterally to define each pipe of tube bank 78 substantially.In an exemplary embodiment, wall 92 can and tube bank 78 in each pipe spaced apart about 0.02 inch (0.5mm) between about 0.8 inch (20mm).In another exemplary, wall 92 can and tube bank 78 in each pipe spaced apart about 0.1 inch (3mm) between about 0.2 inch (5mm).But the spacing between the pipe of upper end 88 and tube bank 78 can significantly be greater than 0.2 inch (5mm), to provide enough spacing to be positioned by distributor 80 to manage between the upper end of cover.In an exemplary embodiment, wherein cover 86 each wall 92 substantial parallel and housing 76 is cylindrical, wall 92 also can be arranged symmetrically with around the central vertical symmetrical plane of housing, and spatially discrete wall 92 is halved by described plane.In other exemplary, wall 92 is without the need to vertically extending past the lower tube of tube bank 78, and wall 92 is also without the need to for plane, because wall 92 can be bending or has other molded non-planar.Regardless of concrete structure, cover 86 is all configured in the boundary of wall 92, make cold-producing medium 106 flow through the open end 94 of cover 86.

Fig. 6 A to Fig. 6 C is depicted as the exemplary of the evaporimeter being configured to " falling film type " evaporimeter 128.As shown in Fig. 6 A to Fig. 6 C, evaporimeter 128 is similar to the evaporimeter 138 shown in Fig. 5 A to 5C, does not comprise tube bank 140 unlike in the cold-producing medium pond 82 of evaporimeter 128 in the low portion being collected in housing.In an exemplary embodiment, cover 86 is constipation bundle after covering tube bank 78, but in another exemplary, cover 86 still extends towards cold-producing medium pond 82 further after covering tube bank 78.In another exemplary, cover 86 terminates when described cover not exclusively covers tube bank, terminates when namely covering tube bank substantially.

As shown in Fig. 6 B and Fig. 6 C, can use pump 84 that liquid refrigerant pond 82 is recycled to distributor 80 from the low portion of housing 76 via pipeline 114.As further shown in figure 6b, pipeline 114 can comprise adjusting device 112, and adjusting device 112 fluidly can be communicated with a condenser (not shown).In another exemplary, injector (not shown) can be adopted to use the low portion draw liquid cold-producing medium 82 of pressurize refrigerant from housing 76 of condenser 34, and described condenser 34 operates by means of Bernoulli effect.Described injector is combined with the function of adjusting device 112 and pump 84.

In an exemplary embodiment, a layout of pipe or tube bank can be defined by the vertical and multiple evenly spaced pipe of horizontal aligument, thus forms the profile that can be substantially rectangle.But, also can use the tube bank of stacked arrangement, wherein respectively manage neither perpendicular alignmnet also out-of-level aligning, and also can take and the tube bank of the unevenly spaced layout opened.

In another exemplary, also contemplate different beam configuration.For example, finned tube (not shown) can be used in tube bank, such as, along uppermost level row or the uppermost part of tube bank.Except using the possibility of finned tube, also can adopt and apply for pool boiling---such as in " submerged " evaporimeter---more valid function and the pipe developed.Combine in addition or with finned tube, also porous coating can be coated to the outer surface of each pipe of tube bank.

In another exemplary, the cross-sectional profiles of evaporator shell can be non-circular.

In an exemplary embodiment, a part for cover can partly extend in housing outlets.

In addition, the expansion function of the expansion gear of system 14 can be brought in distributor 80.In an exemplary embodiment, two expansion gears can be adopted.An expansion gear is illustrated as the injection nozzle being arranged in distributor 80.Before the expansion that another expansion gear (such as, expansion gear 36) can provide at the injection nozzle be positioned in evaporimeter, provide preliminary demi-inflation to cold-producing medium.In an exemplary embodiment, the liquid level by the liquid refrigerant 82 in evaporimeter controls another expansion gear, i.e. non-spray nozzles expansion gear, to consider such as to evaporate the change with operating conditions such as condensing pressure and part cooling loads.In Alternative exemplary embodiment, the liquid level by liquid refrigerant within the condenser controls expansion gear, or in another exemplary, controls expansion gear by the liquid level of the liquid refrigerant in " flash distillation economizer " container.In an exemplary embodiment, major part expands and can occur in nozzle, thus provides larger pressure differential, allows nozzle to have the size of reduction, because this reducing size and the cost of nozzle simultaneously.

The application is with reference to other open text, comprise that to be such as contained in applicant in the denomination of invention that on September 3rd, 2010 submits to be the distributor in " VAPORCOMPRESSIONSYSTEM ", No. 12/875748 U.S.'s non-provisional application for a patent for invention, this application is included in herein by entirety by reference.

Fig. 7 shows the exemplary of distributor 142, and this distributor 142 is configured to be similar to the previously such as mode shown in Fig. 6 B and the fluid entering described distributor 142 is applied to tube bank.Distributor 142 comprises a capsule 144, and this capsule has an end 148 being positioned to face tube bank (such as Fig. 6 B) and towards an opposed end 150 away from described tube bank.Distributor 142 also comprises and being formed in end 150 and the entrance 156 extended between end (terminus) 152 and opposing end portions 154.End 148 comprises at least one distributor 146 or multiple distributor 146 end features 158 associated therewith operably.In one embodiment, distributor 146 comprises the opening 160 (Fig. 9) be formed in the end features 158 of end 148.Because this arranges, the fluid 206 (it can comprise the two-phase mixture of steam and liquid) entered in the entrance 156 of capsule 144 is distributed by the length direction along described capsule 144, and leaves capsule 144 by distributor 146 as distributing fluids 208.Due to the capsule 144 of this novelty structure, improve the flowing of the distributing fluids 208 along the length of capsule 144, that is, the length be directed to along described capsule more uniformly flows.

It should be understood that and can use one, two or more distributors 142 in single tube bank.In one embodiment, two or more distributors can have the jet angle 166 (Figure 11) for the overlap of distributing fluids 208.In one embodiment, tube bank can be divided into multiple regions with independent distributor, such as vertical region of separating.Such as, for the large tube bank being divided into vertical region of separating, one or more distributor can be set between each region, with provide the improvement of the pipe to described tube bank, multilayer soaks.

Although capsule 144 is illustrated as the structure of the multi-disc assembling such as consisted of welding in Fig. 7-10, it can be extruded, has entirety or monolithic construction.

Figure 10 shows the cross section by the opening 160 of formation in the end features 158 of end 148 intercepted along the line 10-10 in Fig. 9.End 148 extends to relative envelope portion 168,170.As shown in Figure 10, envelope portion 168,170 parallel to each other, and there is the plane of symmetry 180 relative to each other.As further shown in Figure 10, capsule has height 176 and width 178.Term " length-width ratio of capsule " refers to that height 176 is divided by its width 178.The length-width ratio of capsule can at about 1/2:1 with about between 10:1, about 1/2:1 and about between 8:1, about 2:1 and about between 6:1, about 2:1 and about between 4:1, about 2:1 and about between 3:1, about 3:1 and about between 8:1, about 4:1 and about between 6:1, about 2:1, about 3:1, about 4:1 or the combination of its anyon.By the length-width ratio of suitable dimension, in conjunction with size and the interval of opening 160, fluid stream through the opening 160 of described capsule can be optimised, that is, make in the length of described capsule more even in the substantially whole fluid pressure range be associated with the operation of the distributor in the disclosure.

Such as, shown in as common in Fig. 8-10, entrance 156 has the length 194 between about 1/6 to 1/3 of length 200.Entrance 156 is positioned in the middle of relative end sections 196,198 substantially.In one embodiment, the adjacent apertures 160 be formed in the end features 158 of end 148 is spaced from each other interval 164 identical substantially along length 200.In another embodiment, interval 164 between the adjacent apertures at least partially 160 that entrance 156 is connected can be greater than the interval 202 between the adjacent apertures at least partially 160 that end sections 196 is connected, and/or the interval 204 that can be greater than between the adjacent apertures at least partially 160 that end sections 198 is connected, for promoting that fluid more uniformly flows through collective's opening 160 along the length 200 of capsule 144.In one embodiment, the interval 202 and between the adjacent apertures at least partially 160 that is connected of end sections 196 can relative to and the adjacent apertures at least partially 160 that is connected of end sections 198 between interval 204 spaced apart fifty-fifty substantially.In one embodiment, opening 160 comprises substantial uniform width 162.In one embodiment, the cut end of opening 160 can be " right angle is square " or general rectangular, although in further embodiment, described cut end can be the combination of curve or curve and straight line, have with Figure 11-14 in respectively shown by end features 158,258,358,458 similar modes, as discussed in detail further below.In further embodiment, opening 160 can the vicissitudinous width of tool.Therefore, should be appreciated that, the size of opening 160 corresponds to the distance 186 (also referred to as height) from the cut end of opening 160 to the point of contact far away 184 (Figure 11) of the end features 158 of capsule, and the combination of width 162 (Figure 10).That is, if the width 162 of opening 160 is equal to each other substantially, and if the height of opening or distance 186 also substantially equal, then the size of opening 160 will be considered to substantially equal.In one embodiment, the width 162 of its split shed 160 is mutually different, height or the distance 186 of opening can be mutually unequal, but the size of opening 160 can be substantially mutually equal, as long as consequently have substantial uniform fluid stream along in the length 200 (Fig. 8) of described capsule.In one embodiment, at least two in described opening 160 are equal to each other or size is impartial substantially substantially.

Although envelope portion 168,170 is illustrated as general parallel orientation in Fig. 10, envelope portion 168 can comprise an angular variation 172, and/or envelope portion 170 can comprise an angular variation 174.Therefore, envelope portion 168,170 can eachly offset between 0 to about 45 degree from being parallel to each other or the combination of its anyon, forms " V " shape.In one embodiment, if desired, angular variation 172 and/or angular variation 174 can along the length variations of described capsule.

Figure 11 is the enlarged drawing in the region 11 in Figure 10, shows the further details of the exemplary end features 158 of capsule 144.As further shown in Figure 11, feature 158 defines a curve or domed profiles, and it has radius or effective radius or radial distance 189 and extends to relative envelope portion 168,170.In one embodiment, radius or effective radius or radial distance 189 can comprise one or more curve with different curvature radius.Effective radius or radius or radial distance 189 stretch out from central point or with the coincide point 181 that the reference line 182 being essentially perpendicular to described relative envelope portion 168,170 overlaps.As shown in Figure 10, envelope portion 168,170 parallel to each other, and there is the symmetrical plane of symmetry 180, and in one embodiment, the plane of symmetry 180 overlaps with reference line 182.In one embodiment, coincide point 181 is not positioned at the center of capsule 144.In one embodiment, capsule does not have the plane of symmetry.Opening 160 comprises the edge 161,163 be associated with the cut end of opening 160, and edge 161 associates and near envelope portion 168, and edge 163 associates and near envelope portion 170.As further shown in Figure 11, reference line 183 is essentially perpendicular to relative envelope portion 168,170, and extends past edge 161,163.Reference line 182 is parallel to reference line 183.The end features 158 of end 148 comprise relative to the distal part 187 of envelope portion 168,170 point of contact far away 184 overlapped with reference line 185, this reference line 185 and reference line 182,183 parallel to each other.The edge 161,163 of opening 160 to the distal part 187 of end features 158 point of contact 184 between spacing or effective spacing, measured by along reference line 185, create distance 186.Extend past the spacing between the reference line 182 of coincide point 181 and point of contact 184 far away, as along as described in reference line 185 measure, create distance 188.Distance 188 is greater than distance 186.That is, the radius relevant to tangent portion, distally (point of contact 184 (distance 188) of such as end features 158) or effective radius or radial distance 189, be greater than the effective spacing between relevant edge 161,163, portion tangent to distally (such as point of contact 184 (apart from 186) far away) or spacing.Therefore, the jet angle 166 flowing through the distributing fluids of opening 160 is limited between about 60 degree to about 180 degree, between about 90 degree to about 180 degree, between about 120 degree to about 180 degree, between about 150 degree to about 180 degree, between about 160 degree to about 180 degree, between about 160 degree to about 170 degree, between about 160 degree to about 165 degree, about 160 degree, about 165 degree and about 170 degree, described jet angle 166 keeps relative constancy in the substantially whole fluid pressure range that the operation of the distributor to described steam compression system is relevant.

Figure 12 is the enlarged drawing in a region in the region 11 being similar to Figure 10, it illustrates the more details of an exemplary end features 258 of capsule 144.As shown further in figure 12, feature 258 defines the square or rectangular profile in right angle be made up of the linear segments of capsule, and it has effective radius or effective radial distance 289, and extends to relative envelope portion 168,170.Effective radius or effectively radial distance 289 stretch out from central point or with the coincide point 281 that the reference line 282 being essentially perpendicular to described relative envelope portion 168,170 overlaps.In one embodiment, coincide point 281 is not positioned at the center of capsule 144.In one embodiment, capsule does not have the plane of symmetry.Opening 260 comprises the edge 261,263 be associated with the cut end of opening 260, and edge 261 associates and near envelope portion 168, and edge 263 associates and near envelope portion 170.As further shown in Figure 12, reference line 283 is essentially perpendicular to relative envelope portion 168,170, and extends past edge 261,263.Reference line 282 is parallel to reference line 283.The end features 258 of end 148 comprise relative to the distal part 287 of envelope portion 168,170 point of contact far away 284 overlapped with reference line 285, this reference line 285 and reference line 282,283 parallel to each other.The edge 261,263 of opening 260 to the distal part 287 of end features 258 point of contact 284 between spacing or effective spacing, as measured along reference line 285, create distance 286.Extend past the spacing between the reference line 282 of coincide point 281 and point of contact 284 far away, as along as described in reference line 285 measure, create distance 288.Distance 288 is greater than distance 286.That is, the effective radius relevant to tangent portion, distally (point of contact 284 (distance 288) of such as end features 258) or effectively radial distance 289, be greater than the effective spacing between relevant edge 161,163, portion tangent to distally (such as point of contact 284 (distance 286)) or spacing.Therefore, the jet angle 166 (Figure 11) flowing through the distributing fluids of opening 260 is limited between about 60 degree to about 180 degree, between about 90 degree to about 180 degree, between about 120 degree to about 180 degree, between about 150 degree to about 180 degree, between about 160 degree to about 180 degree, between about 160 degree to about 170 degree, between about 160 degree to about 165 degree, about 160 degree, about 165 degree and about 170 degree, described jet angle 166 keeps relative constancy in the substantially whole fluid pressure range that the operation of the distributor to described steam compression system is relevant.

Figure 13 is the enlarged drawing in a region in the region 11 being similar to Figure 10, it illustrates the more details of an exemplary end features 358 of capsule 144.As further shown in fig. 13, end features 358 defines " V " shape profile be made up of the linear segments of capsule, and it has effective radius or effective radial distance 389, and extends to relative envelope portion 168,170.Effective radius or effectively radial distance 389 stretch out from central point or with the coincide point 381 that the reference line 382 being essentially perpendicular to described relative envelope portion 168,170 overlaps.In one embodiment, coincide point 381 is not positioned at the center of capsule 144.In one embodiment, capsule does not have the plane of symmetry.Opening 360 comprises the edge 361,363 be associated with the cut end of opening 360, and edge 361 associates and near envelope portion 168, and edge 363 associates and near envelope portion 170.As further shown in Figure 13, reference line 383 is essentially perpendicular to relative envelope portion 168,170, and extends past edge 361,363.Reference line 382 is parallel to reference line 383.The end features 358 of end 148 comprise relative to the distal part 387 of envelope portion 168,170 point of contact far away 384 overlapped with reference line 385, this reference line 385 and reference line 382,383 parallel to each other.The edge 361,363 of opening 360 to the distal part 387 of end features 358 point of contact 384 between spacing or effective spacing, as measured along reference line 385, create distance 386.Extend past the spacing between the reference line 382 of coincide point 381 and point of contact 384 far away, as along as described in reference line 385 measure, create distance 388.Distance 388 is greater than distance 386.That is, the effective radius relevant to tangent portion, distally (point of contact 384 (distance 388) of such as end features 358) or effectively radial distance 389, be greater than the effective spacing between relevant edge 361,363, portion tangent to distally (such as point of contact 384 (distance 386) far away) or spacing.Therefore, the jet angle 166 (Figure 11) flowing through the distributing fluids of opening 360 is limited between about 60 degree to about 180 degree, between about 90 degree to about 180 degree, between about 120 degree to about 180 degree, between about 150 degree to about 180 degree, between about 160 degree to about 180 degree, between about 160 degree to about 170 degree, between about 160 degree to about 165 degree, about 160 degree, about 165 degree and about 170 degree, described jet angle 166 keeps relative constancy in the substantially whole fluid pressure range that the operation of the distributor to described steam compression system is relevant.

Figure 14 is the enlarged drawing in a region in the region 11 being similar to Figure 10, it illustrates the more details of the exemplary end features 458 of capsule 144.As further illustrated in fig. 14, end features 458 defines the profile that a bottom be made up of the linear segments of capsule and the combination of curved section is " D " shape, it has effective radius or effective radial distance 489, and extends to relative envelope portion 168,170.In one embodiment, curve section and the linear segments of different layout or profile can be used.Effective radius or effectively radial distance 489 stretch out from central point or with the coincide point 481 that the reference line 482 being essentially perpendicular to described relative envelope portion 168,170 overlaps.In one embodiment, coincide point 481 is not positioned at the central point of capsule 144.In one embodiment, capsule does not have the plane of symmetry.Opening 460 comprises the edge 461,463 be associated with the cut end of opening 460, and edge 461 associates and near envelope portion 168, and edge 463 associates and near envelope portion 170.As further shown in Figure 13, reference line 483 is essentially perpendicular to relative envelope portion 168,170, and extends past edge 461,463.Reference line 482 is parallel to reference line 483.The end features 458 of end 148 comprises point of contact 484 far away relative to the distal part 487 of envelope portion 168,170, and this point of contact 484 far away overlaps with reference line 485, and this reference line 485 is parallel to each other with reference line 482,483.The edge 461,463 of opening 460 to the distal part 487 of end features 458 point of contact 484 between spacing or effective spacing, as measured along reference line 485, create distance 486.Extend past the spacing between the reference line 482 of coincide point 481 and point of contact 484 far away, as along as described in reference line 485 measure, create distance 488.Distance 488 is greater than distance 486.That is, the effective radius relevant to tangent portion, distally (point of contact 484 (distance 488) of such as end features 458) or effectively radial distance 489, be greater than the effective spacing between relevant edge 461,463, portion tangent to distally (such as point of contact 484 (distance 486) far away) or spacing.Therefore, the jet angle 166 (Figure 11) flowing through the distributing fluids of opening 460 is limited between about 60 degree to about 180 degree, between about 90 degree to about 180 degree, between about 120 degree to about 180 degree, between about 150 degree to about 180 degree, between about 160 degree to about 180 degree, between about 160 degree to about 170 degree, between about 160 degree to about 165 degree, about 160 degree, about 165 degree and about 170 degree, described jet angle 166 keeps relative constancy in the substantially whole fluid pressure range that the operation of the distributor to steam compression system is relevant.

Should be appreciated that, to corresponding distance 186,286,386,486 relevant lines 183,283,383,483 are not limited to each respective edges 161 and 163,261 and 263,361 and 363,461 and 463 extending past respective openings 160,260,360,460.Such as, in one embodiment, the edge 161 and 163 of opening 160 can offset relative to line 183, represents average distance 186 between corresponding edge 161,163 to make line 183.But, line 183,283,383,483 and be less than the respective distance 188,288,388,488 of the correspondence between online 182,282,382,482 and the respective distance 188,288,388,488 of correspondence to corresponding point of contact 184,284,384,484 to the respective distance 186,286,386,486 of the correspondence at corresponding point of contact 184,284,384,484, to guarantee the consistent controlled jet angle 166 (Figure 11) of distributing fluids stream, in order to object described above.

Figure 15 shows an exemplary of distributor 142, different from linear axis 190, this distributor 142 has an axis of bending 192, compared with the distributor (such as with have different structure opening 160 (Fig. 8) combine) with straight line or linear axis, this distributor 142 arranges the Liquid distribution that can provide improvement for some tube banks.

Although only illustrate and describe characteristic sum embodiments more of the present invention, but those skilled in the art can expect many modifications and variations (such as, change in the size of various element, size, structure, shape and ratio and in parameter value (such as temperature, pressure etc.), mounting arrangements, materials'use, color, orientation etc.), and do not depart from novel teachings and the advantage of the theme described in claim in itself.The order of any process or method step or sequence can change according to alternate embodiment or reset.Therefore, it should be understood that appended claims is intended to cover and allly thisly drop on amendment in true spirit of the present invention and change.In addition; in order to provide the brief description of exemplary; perhaps, all features of actual embodiment are not described (namely; those features irrelevant with implementing at present desired optimal mode of the present invention, or those features had nothing to do with fully openly the present invention for required protection).Should be appreciated that, in the development process of any actual embodiment, as in any engineering or design object, a large amount of concrete implementation decisions can be made.Development so may be complicated and time-consuming, but for benefiting from the those of ordinary skill of present disclosure, the normal work to do remaining design, processing and produce, and without the need to excessive experiment.

Claims (20)

1., for the distributor in steam compression system, comprising:

Capsule, is configured to be positioned to have in the heat exchanger of tube bank, and described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor, be formed at the end be oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank;

Wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1.

2. distributor as claimed in claim 1, the described end of wherein said capsule comprises an end features, and at least one distributor described comprises at least one opening be formed in described end features,

With the jet angle distributing fluids between about 60 degree to about 180 degree in the substantially whole fluid pressure range that the operation that at least one opening wherein said was configured and was set to the distributor in described system is relevant.

3. distributor as claimed in claim 2, wherein said end features comprises at least one in curved profile, linear profile or its combination.

4. distributor as claimed in claim 2, comprises the substantial parallel opposite segments extended away from the described end of described capsule.

5. distributor as claimed in claim 4, wherein said opposite segments can from the skew 0 degree that is parallel to each other to about 45 degree.

6. distributor as claimed in claim 4, wherein relevant to described end features and the reference line being essentially perpendicular to the opposite segments of described end features is oriented to the distally tangent portion of first distance from described end features, to the effective spacing relevant existence second distance between the edge be formed at least one opening described and the tangent portion, distally of end features, described first distance is greater than described second distance.

7. distributor as claimed in claim 6, the central point of the effective radius of wherein said reference line and described end features coincides.

8. distributor as claimed in claim 7, the plane of symmetry and the described central point of wherein said capsule coincide.

9. distributor as claimed in claim 1, wherein said length-width ratio at about 2:1 to about between 4:1.

10. distributor as claimed in claim 1, wherein said length-width ratio is about 2:1.

11. distributors as claimed in claim 1, wherein said length-width ratio is about 4:1.

12. distributors as claimed in claim 2, wherein said jet angle is between about 160 degree to about 170 degree.

13. distributors as claimed in claim 2, wherein said jet angle is about 165 degree.

14. distributors as claimed in claim 2, one of them entrance is formed in the end being oriented to away from described tube bank of described capsule, described entrance is configured to receive fluid and enters in described capsule, described entrance is located substantially between two parties relative to the length of described capsule, and described entrance is about 1/6 of the length of described capsule to about 1/3.

15. distributors as claimed in claim 14, at least one distributor wherein said length comprised along described capsule is formed at the multiple openings in described end features.

16. distributors as claimed in claim 15, are wherein formed at the described multiple opening size equalization substantially in described end features.

17. distributors as claimed in claim 14, are wherein formed at the described multiple opening uniform intervals substantially in described end features.

18. distributors as claimed in claim 14, at least one distributor wherein said comprises the multiple openings be formed in described end features, first spacing at least partially with the centre portion of the length corresponding to described capsule of described multiple opening, and second spacing had at least partially corresponding at least one end section in paired end section of the residue opening of described multiple opening, described first spacing is less than described second spacing.

19. 1 kinds, for the distributor in steam compression system, comprising:

Capsule, is configured to be positioned to have in the heat exchanger of tube bank, and described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor, be formed in the end being oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank;

Wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1;

The described end of wherein said capsule comprises an end features, and at least one distributor described comprises at least one opening be formed in described end features;

With the jet angle distributing fluids between about 60 degree to about 180 degree in the substantially whole fluid pressure range that the operation that at least one opening wherein said was configured and was set to the distributor in described system is relevant.

The method of 20. 1 kinds of distributing fluids in steam compression system, comprising:

There is provided the capsule being configured to be positioned to have in the heat exchanger of tube bank, described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor is formed in the end being oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank, and wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1; And

Operate described steam compression system.