CN104364599A - Compressed gas cooling apparatus - Google Patents
Compressed gas cooling apparatus Download PDFInfo
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- CN104364599A CN104364599A CN201380033128.1A CN201380033128A CN104364599A CN 104364599 A CN104364599 A CN 104364599A CN 201380033128 A CN201380033128 A CN 201380033128A CN 104364599 A CN104364599 A CN 104364599A
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1615—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
- F28D7/1623—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium with particular pattern of flow of the heat exchange media, e.g. change of flow direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0292—Other particular headers or end plates with fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2225/00—Reinforcing means
- F28F2225/08—Reinforcing means for header boxes
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A compressed gas cooling apparatus in which gas from an upstream compression stage enters an inlet section from an inlet opening and flows to a heat exchanger that cools the gas. The cooled gas then flows from the heat exchanger to the outlet section where the gas is discharged from an outlet opening. Pressure drop within the apparatus is decreased by providing the inlet and outlet sections with ever increasing and decreasing cross-sectional flow areas. In order to further decrease pressure drop due to a swirl within the gas flow imparted from the upstream compression stage, the inlet section is provided with first and second subsections wherein the cross-sectional flow area of the first subsection increases at lesser rate than the second subjection. Alternatively, or in addition, the inlet section can be provided with partitions to divide the gas flow into subflows in order to lessen pressure drop from swirl.
Description
Technical field
The invention provides a kind of Compressed Gas cooling device, it can play the effect of intercooler or aftercooler, and it makes between a series of compression stage or afterwards refrigerating gas.More specifically, the present invention relates to this type of cooling device: both entrance and exits have continuous increase (ever-increasing) respectively and constantly reduce the section of area of (ever-decreasing) wherein, so that gas is positioned at heat exchanger between entrance and outlet and from the heat exchanger feed gas of locating between inlet and outlet to delivering to.Even more specifically, the present invention relates to this type of cooling device: the section design of the continuous increase of entrance wherein becomes the pressure loss reduced further owing to occurring at the vortex (swirl) in the gas flow given by the upstream compression stage introduced in cooling device by Compressed Gas.
Background technology
The gas of large volume compresses in multiple commercial Application in compressibility, and compressibility has a series of level, and these grades carry out refrigerating gas with the cooling during rolling between level.In each compression stage, give the energy (being also known as the heat of compression) that gas carrys out heated air removed by intercooler.After aftercooler can be positioned on last of compression stage.
Typically, each in compression stage is formed by centrifugal compressor, and in centrifugal compressor, gas is drawn into the impeller (vaned impeller) of band leaf from entrance, impeller with leaf is driven accelerates gas, and improves pressure and the speed of gas thus.The pressure loss with the increase in speed is recovered surround impeller and can have in the diffuser of leaf (vane).Gas is from impeller drainage to helical form (spiral-like) helix tube (volute) with outlet, and gas-pressurized is from outlet drain, and gas-pressurized holds entrance.Intercooler is positioned between the outlet of upstream stage and the entrance of downstream stage.When gas (such as air) is containing moisture, the condensation of this type of moisture from intercooler and aftercooler discharge is caused, so that condensate can not be carried into downstream stage or the equipment to the technique of carrying out compressed gas consuming via the reduction in the temperature of the Compressed Gas of cooling during rolling and rear cooling.
In air separation equipment, the use with the centrifugal compressor of intercooler and aftercooler is quite common.Compressor can be driven by transmission mechanism, and in this transmission mechanism, electrical motor driven gear wheel, gear wheel driving pinion shape (pinion-like) gear, pinion shape gear is attached in each in compressor, to transfer drives impeller.Therefore, compressor is arranged in around the gear wheel with pipeline, and pipeline has elbow (bends), gas is transported (route) and transports to the intercooler between compressor or from the intercooler between compressor.As known in the art, the elbow in this type of pipeline is by the pressure drop within the gas causing through compressor.Intercooler typically is pipe and shell structure, and pipe is used to transmit (pass) cooling agent (it can be water) wherein, comes and carries out indirect heat exchange with the gas that pipe at right angles passes through.The layout of the fin penetrated by pipe for the path of gas is formed.Gas enters the shell of this type of heat exchanger by entrance bin (plenum), and at the opposite end place of shell from the discharge of outlet bin.Gas introduces from this type of bin at a right angle with shell and discharge by the entrance and exit of shell.As will be appreciated, there is the further pressure loss of arranging since then due to the change on flow direction, and similarly, there is quick increase in the cross-sectional flow area of bin from the inlet to the outlet and subsequently from outlet bin to the quick increase the cross-sectional flow area of outlet.Air separation equipment in, these pressure losses must by increase compression and the power consumption therefore increased compensate.Identical consideration is applied to other commercial Application of multi-stage compression system.
The considerable more of the placement of compressor and intercooler are freely possible, and wherein compressor independently and directly driven by high-speed permanent magnetic motor.Reducing with the cooling during rolling of gas in multi-stage compression system and the pressure drop of rear cooling from origin in the placement of compressor can be used.Such as, in U.S. Patent Publication No. 2010/0329895, centrifugal compressor is separately driven, and determines that position becomes so that the entrance of downstream compressor is orientated as relative with the outlet of upstream compressor.In addition, each entrance and exit to intercooler has the cross-sectional area and ever-reduced cross-sectional area that constantly increase respectively, with the heat exchanger be positioned between this type of section.These sections can be formed by the group of the four blocks of plates linked together with the four polyhedral layouts in side, and therefore have rectangle lateral cross flow area.The heat exchanger combining box-like housing is between these sections and in inside, heat exchanger has gas passage, and gas passage is used for the stream directly from this type of entrance zone, threshold zone and the gas to this type of exit zone.Cooling agent and gas passage at right angles pass through coolant channel.As will be appreciated, this type of layout reduces otherwise the prior art from the elbow of pipeline had between level is arranged the pressure loss caused, and due to the Rapid Variable Design of area and to heat exchanger with carry out automatic heat-exchanger and the Rapid Variable Design in the direction of stream in heat exchanger self and the pressure loss that causes.
Even in open text discussed above, also do not understand: the pressure loss is also caused by the vortex introduced in stream, flow to into intercooler or the entrance zone, threshold zone of other Compressed Gas cooling device used in conjunction with compressor and exit zone.When centrifugal compressor Compressed Gas, this type of vortex in stream is caused by impeller and diffuser arrangement.When this type of stream enters to the entrance of intercooler or aftercooler, even when entering an entrance with the area of section increased gradually, gas is tending towards being accumulated on wall and at the side place of entrance.This generates the area of low pressure of high-pressure area and this high-pressure area contiguous of wherein flowing accumulation.This causes stream to be separated from wall, and the recirculation within the entrance to intercooler or aftercooler, and this transfers the another component producing gross pressure decline.
As will be discussed, among other things, the invention provides a kind of Compressed Gas cooling device, it can play the effect of intercooler or aftercooler, and intercooler or aftercooler design reduce the pressure drop within the entrance to Compressed Gas cooling device caused from the vortex given air-flow by compressor.
Summary of the invention
The invention provides a kind of Compressed Gas cooling device had as intercooler or aftercooler.This device is provided with entrance zone, threshold zone and exit zone.Entrance zone, threshold zone has entrance, and with from upstream compression stage receiver gases, and exit zone has outlet, with after cooling at gas by gas discharging to downstream compression stage.Entrance zone, threshold zone is connected on exit zone by heat exchanger, and have and be communicated with for the gas passage by gas between entrance zone, threshold zone with exit zone, and become with gas passage heat transfer relation to locate for making cooling agent by the coolant channel to be cooled the gas through gas passage by the indirect heat exchange with cooling agent.Entrance zone, threshold zone part comprises the first intake section and the second intake section.First intake section is between entrance and the second intake section, and the second intake section is between the first intake section and heat exchanger.Each in first intake section and the second intake section all has the lateral cross flow area constantly increased.The lateral cross flow area of the continuous increase of the second intake section increases with the speed larger than the first intake section, so that the speed of the stream of gas flows through the first intake section up to the degree little by little reduced in the first intake section than less in the second intake section at gas.Which suppress being separated, to reduce pressure drop of stream owing to being administered to the gas that the vortex in the stream of gas causes from upstream compression stage and the first intake section and each the sidewall in the second intake section.Exit zone comprises an exit portion of the ever-reduced lateral cross flow area flowing to outlet for gas from heat exchanger, the speed of the stream of gas is little by little increased, also reduces pressure drop.
First intake section, the second intake section and this exit portion can be formed by the group being connected to four sidewalls gone up each other, make the lateral cross flow area that constantly increases and ever-reduced lateral cross flow area be rectangular configuration.Heat exchanger has entrance side and orientates the outlet side relative with this entrance side as.Cooling channel extends between entrance side and outlet side, and each in entrance side and outlet side is rectangular configuration.Entrance zone, threshold zone has the 3rd intake section, the 3rd intake section have from one end with the First Transition lateral cross flow area of the rectangular transition of the circle and other end place that limit entrance.The other end of Part III with define intake section four sidewalls of first group in one aim at (in registry with) and be connected.This exit portion is the first exit portion, and exit zone has the second exit portion, and this second exit portion is located so that the first exit portion is between the second exit portion and heat exchanger.Second exit portion has the second transition lateral cross flow area of the rectangular transition to limit circle and the other end place exported from one end.The other end of the second exit portion with define the first exit portion four sidewalls group in another aim at and be connected.
In a particular embodiment, another defining in the group of four sidewalls of the second intake section at two ends place is aimed at the entrance side of in the group of four sidewalls and heat exchanger and is connected on them.Another defining in the group of four sidewalls of the first exit portion at opposite end place is aimed at the other end of the second exit portion and the outlet side of heat exchanger and is connected.
In order to reduce the pressure drop caused by the vortex in air-flow further, first intake section can divide (subdivide) to become first group of sub-channel by the first set isolation element again, the first set isolation element be oriented so that in sub-channel each be rectangular configuration.Second intake section can be divided into second group of sub-channel by second component every element again, second component every element be oriented so that in sub-channel each be rectangular configuration.Second group of sub-channel has sub-channel more more than first group of sub-channel.First exit portion similarly can be divided into the 3rd group of sub-channel by three components every element again.First set isolation element, second component are connected on sidewall every element and three components every element, and rectangle frame rack-like stiffened members is connected on the outer surface of each in the group of four sidewalls.In a particular embodiment, first group of sub-channel has four sub-channels, and second group of sub-channel has 24 sub-channels.
Embodiments of the invention additionally provide a kind of pressure-air cooling device, and entrance zone, threshold zone comprises a part wherein, and this part has at least one sidewall defining the lateral cross flow area constantly increased.The lateral cross flow area constantly increased is divided into multiple sub-channel by separating element again, and each all has the sub-flow area of lateral cross constantly increased, so that the speed of the stream of gas little by little reduces when gas flows through entrance zone, threshold zone.Sub-flow area reduces being separated of air-flow caused by the vortex owing to being administered to from upstream compression stage in the stream of gas and at least one sidewall, thus reduces pressure drop.Exit zone comprises for from heat exchanger to the exit portion of the ever-reduced lateral cross flow area of the stream of the gas of outlet, so that the speed of the stream of gas little by little increases when gas flows in exit zone, also reduces pressure drop.
In this type of embodiment, intake section and exit portion are formed by the group being connected to four sidewalls gone up each other, make the lateral cross flow area that constantly increases and ever-reduced lateral cross flow area be rectangular configuration.Sub-channel each be rectangular configuration.The outlet side that heat exchanger has entrance side and entrance side relative positioning, the cooling channel extended between entrance side and outlet side.Each in entrance side and outlet side is rectangular configuration.At least one sidewall of intake section is one in the group of four sidewalls.Another in the group of four sidewalls forms exit portion.Intake section is the first intake section, and exit portion is the first exit portion.Entrance zone, threshold zone has the second intake section, and exit zone has the second exit portion.Second intake section have from one end with the First Transition lateral cross flow area of the rectangular transition of the circle and other end place that limit entrance.The other end of the second intake section with define the first intake section four sidewalls group in one aim at.Similarly, the second exit portion has the second transition lateral cross flow area of the rectangular transition to limit circle and the other end place exported from one end.The other end of the second exit portion is aimed at another in the group of four sidewalls.
One of defining in the group of four sidewalls of the first intake section connects and is registered on the entrance side of the heat exchanger of the position at the entrance zone, threshold zone relative with the second intake section.Another defining in the group of four sidewalls of the first exit portion connects and is registered on the outlet side of the heat exchanger of the position at the exit zone relative with the second exit portion.The separating element of the first intake section can be the first set isolation element, and sub-channel is first group of sub-channel, and the first exit portion has the second component of the 3rd group of sub-channel forming rectangular configuration every element.First set isolation element and second component are connected on sidewall every element.Rectangle, the stiffened members of frame-like is connected on the outer surface of each in the group of four sidewalls.
In any embodiment of the invention, heat exchanger all can be intersect reverse (cross-counter) spread and put.Cooling channel is being formed relative between the entrance side of heat exchanger and multiple parallel fins of outlet side orientation with right angle.Coolant channel is formed by coolant hose, and these coolant hoses penetrate parallel fins, for the circulation of cooling agent, and is on orthogonal directed relative to parallel fins.
Preferably, coolant hose comprises the group of entrance coolant hose, the group of first group of intercoolant pipe, second group of intercoolant pipe and outlet coolant pipe.These entrance coolant hoses, intercoolant pipe and outlet coolant pipe are arranged to provide and pass in heat exchanger four times.Heat exchanger has to be orientated as and two end portion respect to one another, and link part and form that the entrance side of heat exchanger and outlet side two are isolated, the top panel that laterally extends and bottom panel.Entrance bin and outlet bin are positioned at a place in two end portion abreast, and become to flow with outlet coolant pipe with entrance coolant hose respectively and be communicated with, to be introduced in entrance coolant hose by cooling agent, and by cooling agent from outlet coolant tube drainage.Reverse bin is positioned at the end portion of heat exchanger, and is configured so that in cooling agent from inlet tube another place's inflow first group of intercoolant pipe after crossing heat exchanger in end portion.After crossing heat exchanger, cooling agent flows out from first group of intercoolant pipe subsequently, in another place's inflow second group of intercoolant pipe in end portion.Then, after crossing heat exchanger, the cooling agent from second group of intercoolant pipe flows in the group of outlet coolant pipe, and after this, flows into outlet bin from the group of outlet coolant pipe.
Heat exchanger can have the condensate be positioned between outlet side and coolant hose and parallel fins and depart from room, is separated from the Compressed Gas through heat exchanger to allow condensed water.Elongate tubular discharge portion (drain) is positioned at condensate and departs from the bottom place of room, to collect condensed water from gas separaion and by condensed water from heat exchangers.
In addition, in heat exchanger, coolant hose can be connected on two relative tube sheets, and is supported by two relative tube sheets at their end place.
Accompanying drawing explanation
Although description is clearly to indicate that applicant regards that claims of their subject matter of an invention terminate as, it is believed that the present invention will understand better when being associated with accompanying drawing, in the accompanying drawings:
Fig. 1 is the perspective view of Compressed Gas cooling device of the present invention;
Fig. 2 is the decomposition diagram of the entrance zone, threshold zone used in illustrated device in FIG;
The cross-sectional perspective view of entrance zone, threshold zone of Fig. 3 for using in the illustrated in FIG device got along the line 3-3 of Fig. 1;
Fig. 4 is the perspective view of the alternative of Compressed Gas cooling device of the present invention;
Fig. 5 is the decomposition diagram of the entrance zone, threshold zone used in illustrated device in the diagram;
The cross-sectional perspective view of entrance zone, threshold zone of Fig. 6 for using in the illustrated in FIG device got along the line 6-6 of Fig. 4;
Fig. 7 is the decomposition diagram of the exit zone used in illustrated device in figures 1 and 4;
Fig. 8 is the top plan view according to heat exchanger of the present invention used in illustrated device in figures 1 and 4;
Fig. 9 is the perspective partial section view of illustrated in fig. 8 heat exchanger got along the line 9-9 of Fig. 8, shows the fin, cooling channel and the coolant hose that use in heat exchanger; And
Figure 10 is the cross-sectional perspective view of the heat exchanger used in illustrated device in figures 1 and 4, and eliminates fin, to illustrate coolant hose, entrance bin, outlet bin and oppositely bin and condensate depart from room and discharge portion thereof.
Detailed description of the invention
With reference to figure 1, illustrate according to Compressed Gas cooling device 1 of the present invention.As described above, such device can play the effect of intercooler between compression stage or aftercooler, to cool the gas of discharging from compression stage that will use in downstream process.The heat exchanger 4 that device 1 has entrance zone, threshold zone 2, exit zone 3 and is connected to by entrance zone, threshold zone 2 on exit zone 3.Entrance zone, threshold zone 2 has entrance 10, to receive the air-flow " A " from not shown upstream compression stage.Upstream compression stage can be centrifugal compressor or axial compressor.In either case, the air-flow identified by the arrow " A " entering entrance 10 has the vortex to stream or rotational component indicated by curved arrow " B ".This type of vortex is flowed by the rotary part (such as, the impeller of centrifugal compressor) of compressor.
In heat exchanger 4 after cooling, air-flow " A " discharges from the outlet 12 of exit zone 3 as the such as cooling blast shown in arrow " C ".
Reference diagram 2 and 3 in addition, entrance zone, threshold zone 2 is provided with the first intake section 14, second intake section 16, and is provided with the 3rd intake section 18 alternatively.As apparent, all these parts all have the lateral cross flow area constantly increased, and this will be used for little by little reducing the speed of air-flow before air-flow enters heat exchanger 4.This will reduce due to the pressure drop in the stream of turbulent flow or loss, turbulent flow otherwise cause due to the unexpected amplification in the cross-sectional flow area from inlet opens 10 in the gas flow.But the pressure drop in air-flow or loss are also caused by the vortex " B " introduced in stream by upstream compressor." vortex " in this stream or rotation are tending towards causing gas buildup on the side of entrance zone, threshold zone 2.This accumulation then create higher-pressure region and adjacent low-pressure area.As a result, being separated in of air-flow occurs towards the place of wall district of the intake section of adjacent low-pressure area, this then cause air-flow towards Posterior circle, cause the increase on the pressure drop in air-flow.
First intake section 14 is formed by the group of four sidewalls 20,22,24,26, and they are connected to goes up each other, makes the lateral cross flow area that constantly increases be rectangular configuration.Second intake section 16 is formed by the group of another four sidewalls 28,30,32 and 34, and they are connected to goes up each other, forms again the transversal surface current of the continuous increase of rectangular configuration.Specifically, vortex " B " will be tending towards causing air-flow " A " along the sidewall 34 of the sidewall 26 of the first section 14 and the second section 16 and be positioned at the part of the adjacent wall 20,24 close to sidewall 26 place and the adjacent wall 28,32 close to sidewall 34 place and accumulate.This will be in this type of sidewall region in air-flow " A " and produce the high pressure field of force.Be arranged in the district apart from first section 14 of sidewall 26 and 34 a distance and the more center of the second section 16, stream is accumulated by this can not, and therefore has lower pressure.As described above, this pressure differential will cause air-flow " A " to be recycled to lower pressure district from elevated pressures district potentially, result in pressure drop.
But as can finding best in figure 3, the lateral cross flow area of the continuous increase of the second intake section 16 increases with the speed larger than the first intake section 14.Such effect is, is reduced with the degree less than the air-flow in the second intake section 16 by the speed of the air-flow of the first intake section 14.The fair speed of the gained of the air-flow in the first intake section 14 reduces the separation of air-flow from the wall of entrance zone, threshold zone 2 by being tending towards, and allows vortex " B " to dissipate a little before air-flow arrives the second intake section 16.Because flowing velocity also reduces along the length of the second intake section 16, therefore otherwise the pressure drop in the air-flow produced by vortex " B " and the unexpected increase on area will be reduced.Second intake section abut heat exchanger 4, and thus also serve dispensing air-flow cross heat exchanger 4.
In order to reduce the pressure drop caused by vortex " B " best, the first section 14 and the second section 16 be preferably designed so that be set to by the formula ((x-i) for oval (bell)
2/ a
2)+((y-j)
2/ b
2bell curve given by)=1 is tangent, and wherein (i, j) is oval center, a and b is respectively the half-distance on x and y-axis line.First section 14 will be derived from this bell summit, and the second section 16 terminates at this bell bottom (mount) place.Even more preferably, the first section 14 has the length-width ratio between 0.4 to 0.5.This length-width ratio by with such as seen by the joint of the first section 14 and the second section 16 Breadth Maximum of the first section 14 record divided by its length.Second section 16 preferably has the length-width ratio between 0.2 to 0.4.This length-width ratio by with such as seen by the joint of the second section 16 and heat exchanger 4 Breadth Maximum of the second section 16 record divided by its length.
Although the first intake section 14 and the second intake section 16 reduce the pressure drop in air-flow by being tending towards alone for the above reasons, but preferably, the rectangular cross section flow area of the first intake section 14 is divided into first group of sub-channel, such as, sub-channel 36, and the second intake section 16 is divided into second group of sub-channel again, such as, sub-channel 38.These rectangles again portions are used for reducing pressure drop further by the side that prevents air-flow to be accumulated in intake section 2 due to vortex " B ".First group of sub-channel 36 is formed by the first set isolation element 40 and 42 of locating each other in right angle, and second group of sub-channel 38 is formed by the group of separating element 40 and 42 and 44 and 46.The length of separating element 40 and 42 extend through first intake section 14 and the second intake section 16.Separating element 44 and 46 is limited to the second intake section 16, and locates each other in right angle.As illustrated, each in sub-channel 36 and 38 is rectangular configuration, and each is, and area constantly increases.
Separating element 40 is along its edge conjunction on sidewall 20,24 and 28,32; And separating element 42 is along its edge conjunction to sidewall 22,26; On 30,34.In addition, separating element 44 is connected on sidewall 28 and 32, and separating element 46 is connected on sidewall 30 and 34.These connections are preferred, to assist the structural intergrity of maintenance first intake section 14 and the second intake section 16, and usually tension between the operating period of device 1.Further structural intergrity is provided by frame-like stiffened members 48, frame-like stiffened members 48 is connected in the group of the sidewall 20,22,24 and 26 defining the first intake section 14, and is connected to and defines on the sidewall 28,30,32 and 34 of the second intake section 16.As will be appreciated, this type of separating element connection and use frame-like stiffened members to reduce sidewall 20 until 34 thickness and weight for being required with high pressure containment compressed air.
As illustrated, the second intake section 16 has sub-channel 38 more more than the sub-channel 36 of the first intake section 14.Preferably, compared with four sub-channels 36, there are 24 these type of sub-channels 38.Such main cause is, because the first intake section 14 has the cross section less than the second intake section 16, therefore there is less stress, and therefore, needs less separating element to come for structural intergrity in the first intake section.
Although the first entrance zone, threshold zone 14 can be provided with circular open simply to form entrance 10, preferably, the 3rd intake section 18 is set to the transition lateral cross flow area of the rectangular transition had from the round entrance opening 10 of one end and other end place.Therefore its sidewall 50 bends at inlet opens 10 place, and is flat to form rectangle at its other end place.This contributes to reducing pressure drop by the sharply transition between the rectangular cross section flow area of being avoided round entrance opening 10 and provided by the first intake section 14 and the second intake section 16 again.
Preferably, sidewall 50 connects and is registered on the sidewall 20,22,24 and 26 of the first intake section 14.Sidewall 20,22,24 is also preferably connected with 26 and is registered on the sidewall 28,30,32 and 34 of the second intake section 16.Sidewall 28,30,32 is connected with 34 and is registered on the entrance side 106 of heat exchanger 4.But be possiblely to provide isolation section, this isolation section has in the cross-sectional flow area of the second entrance zone, threshold zone 16 with the consistent rectangle between heat exchanger 4.Similarly, furthermore it is possible that this type of isolation section is located in the first entrance zone, threshold zone 14 and the second entrance zone, threshold zone 16 any one or between the two, or between the 3rd entrance zone, threshold zone 18 and the first entrance zone, threshold zone 14.
With reference to Figure 4 and 5, illustrate Compressed Gas cooling device 1', it is the alternative of device 1.The difference of device 1' and device 1 is that it is provided with entrance zone, threshold zone 2', and entrance zone, threshold zone 2' has the second intake section 54 that the first intake section 52 that cross-sectional flow area constantly increases and structure are similar to the 3rd intake section 18 of device 1.
First intake section 52 is formed by the group of four sidewalls 56,58,60 and 62, and they are connected to each other, and makes the lateral cross flow area that constantly increases be rectangular configuration.In addition, although can be provided with simple inlet opens, the second intake section 54 provides further pressure drop by providing its transition lateral cross flow area of the rectangular transition from the round entrance opening 10' of one end and other end place.Its sidewall 64 therefore at inlet opens 10' place for bending, and be flat to form rectangle at its other end place.Sidewall 64 is connected at the other end place of the second intake section 54 on the sidewall 56,58,60 and 62 of the first intake section 56 of aligning.
Reference diagram 6 in addition, the pressure drop in entrance zone, threshold zone 2' reduces by providing the lateral cross flow area of the continuous increase provided by the first intake section 52.Because the pressure drop of vortex reduces by means of the group of separator 66 and 68, the group of separator 66 and 68 relative to each other location at a right angle and lateral cross flow area is divided into sub-channel (such as again, sub-channel 70), each sub-channel is that cross-sectional flow area constantly increases.The subflow that separating element 66 and 68 prevents from being caused forming high pressure wall district by the vortex in stream and affects in adjacent sub-channel 70.
Separator 66 and 68 is also connected respectively on sidewall 56,60 and 58,62, to increase the structural intergrity of the Part I 52 of entrance zone, threshold zone 2'.In addition, the optional frame-like stiffened members 72 be connected on the outer surface of sidewall 56,58,60 and 62 adds structural intergrity and the intensity of Part I 52.
Reference diagram 7 in addition, exit zone 3 has again ever-reduced cross-sectional flow area, little by little increases to allow the speed flowed.The design of exit zone 3 is reducing point other entrance 2 and the 2' key that are not so good as device 1 and 1' in pressure drop.In fact, illustrated exit zone 3 to be and to design in the same manner in two devices 1 and 1'.Alternatively, exit zone 3 can have the design identical with any one in 2' with entrance zone, threshold zone 2.
Illustrated exit zone 3 is provided preferably with the first exit portion 74 and the second exit portion 76.First exit portion 74 provides the group of four sidewalls 78,80,82 and 84 of rectangle lateral cross flow area to be formed by linking together.Although the first exit portion 74 can preferably in exit opening termination reduce pressure drop, the second exit portion 76 have from one end with the second transition lateral cross flow area formed by the group of four sidewalls 86,88,90 and 92 of the rectangular transition of the circle and the other end that limit outlet 94 (outlet flow " C " is discharged from this outlet 94).Sidewall 86,88,90 is connected with 92 and is registered to and defines on four sidewalls 78,80,82 and 84 of the first exit portion 74.
Preferably, for the object of structural intergrity, provide the group of separator 96 and 98, they are connected respectively on sidewall 80,84 and sidewall 78,82.In addition, rectangle frame rack-like component 100 can be connected on sidewall 78,80,82 and 84, to provide extra intensity.
Reference diagram 8 in addition, heat exchanger 4 is the common design about device 1 and device 1', and by providing the indirect heat exchange between cooling fluid and air-flow to play the effect removing the heat of compression from the air-flow entered " A ".The cooling fluid that can be water enters via entrance 102, and discharges from outlet 104.As illustrated in fig. 1, about device 1, entrance zone, threshold zone 2 is connected on exit zone 3 by heat exchanger 4.Similarly, in device 1', entrance zone, threshold zone 2' is also connected on exit zone 3 by heat exchanger 4.Heat exchanger 4 is provided with the entrance side 106 be connected on entrance zone, threshold zone 2 and 2' and the outlet side 108 be connected on exit zone 3.As described above, connect and do not need for directly, and rectangle barrier-like element can be located in this type of section.Gas to be cooled enters heat exchanger 4 from the entrance zone, threshold zone 2 of entrance side 106 and 2', and refrigerating gas discharges from heat exchanger 4, from outlet side 108 to exit zone 3.
As can finding best in fig .9, the indirect heat exchange in heat exchanger 4 have been come by means of gas passage 110, and gas passage 110 is formed between series of parallel fin panel element 112.Fin panel element 112 is penetrated by the group of the outlet coolant pipe 122 of the coolant channel provided for cooling agent.Although not shown, fin panel element 112 is also by indicating by reference to label 116,118 and 120 and the group of other coolant hose discussed hereinafter being penetrated.In this regard, entrance side 106 is the rectangular area of opening, and it is constructed as receiving air-flow " A " and passing in gas passage 110.Similarly, outlet side 108 is open rectangle region, and it is constructed, after air-flow " A " has cooled, air-flow " A " is disposed to exit zone 3.In illustrated device 1 and 1', rectangular area equal to be provided by entrance zone, threshold zone 2 and 2' and exit zone 3 those.
In addition with reference to Figure 10, coolant hose comprises the group of the group of entrance coolant hose 116, first group of intercoolant pipe 118 and second group of intercoolant pipe 120 and outlet coolant pipe 122.Aforementioned coolant hose is supported by perforated tube sheets 124 and 126 at opposite end place, and is supported by fin panel element 112 in middle position.Optional support plate 128 is connected on the top panel 134 and bottom panel 136 that laterally extend at opposite end place, overcome internal pressure with auxiliary and maintain structural intergrity.Will it is to be noted that, heat exchanger 4 has two end portion 130 and 132 of relative to each other locating, end portion 130 is connected two isolated top panels 134 of laterally extending and bottom panel 136 with 132, thus forming entrance side 106 and the outlet side 108 of heat exchanger, entrance side 106 and outlet side 108 are benefited from this class formation and are the rectangular aperture to heat exchanger.Base 138 is connected on bottom panel 136, so that bottom panel 132 is risen to more than ground level.
Be included in end portion 130 be and the entrance bin 140 being positioned at end portion 130 of registration and outlet from bin 142.Entrance bin 140 flows with outlet coolant pipe 122 one-tenth with entrance coolant hose 116 respectively with outlet bin 142 and is communicated with.Cooling agent is introduced entrance coolant hose 116 from entrance 102 in the direction of arrow & quot, and via outlet bin 142 from outlet coolant tube drainage, and outlet 104 is disposed on the direction of arrow " E ".Reverse bin 144 is between entrance bin 140 and outlet bin 142, and two reverse bins 146 and 148 are formed in another end portion 132 by providing division plate 150.Cooling agent enters inlet tube 116 from entrance bin 140.After crossing heat exchanger, cooling agent in reverse bin 146 on arrow " G " direction reversed flow move direction, and then flow through first group of intercoolant pipe 118, until cooling agent arrives reverse bin 144.In reverse bin 144, cooling agent is reverse direction again, and flows through second group of intercoolant pipe 120, until arrive reverse bin 148.At reverse bin 148 place, cooling agent is reverse direction on the direction of arrow " H " again, and flow to outlet bin 142 via outlet coolant pipe 122, and cooling agent is discharged from heat exchanger 4 from outlet bin 142 from outlet 104.
When the gas of such as air, the air entered will comprise steam, and steam will by cooling agent condensation.In order to Separation of Water, depart from the outlet side 108 that room 152 is set to proximity thermal interchanger 4.The water be separated is collected in bottom panel 136, and is disposed to from opening 154 and 156 and is positioned at below bottom panel 136 and the elongate tubular discharge portion 158 of the water for discharging collection of proximate base 138.
Although the present invention describes with reference to preferred embodiment, as the skilled person would expect, numerous amendment, interpolation and omission can be made when not departing from the spirit and scope of the present invention as set forth in the dependent claims.
Claims (15)
1. a Compressed Gas cooling device, it comprises:
Entrance zone, threshold zone, it has entrance, with from upstream compression stage receiver gases;
Exit zone, it has outlet, with after having cooled at described gas by described gas discharging to downstream compression stage;
Heat exchanger, described entrance zone, threshold zone is connected on described exit zone by it, and has: gas passage, and it is communicated with between described entrance zone, threshold zone with described exit zone, for passing through described gas; And coolant channel, it becomes heat transfer relation to locate with described gas passage, for by cooling agent, with by cooling described gas through described gas passage with the indirect heat exchange of cooling agent;
Described entrance zone, threshold zone comprises the first intake section and the second intake section, and described first intake section is between described entrance and described second intake section, and described second intake section is between described first intake section and described heat exchanger; And
Each in described first intake section and described second intake section all has the lateral cross flow area constantly increased, the lateral cross flow area of the described continuous increase of described second intake section increases with the speed larger than described first intake section, so that the degree that the speed of the stream of described gas little by little reduces in described first intake section when described gas flows through described entrance zone, threshold zone is than less in described second intake section, and because from described upstream compression stage, the vortex given in the stream of described gas causes the stream of described gas suppressed with being separated of the sidewall of each in described second intake section with described first intake section, to reduce pressure drop, and
Described exit zone comprises the ever-reduced exit portion of lateral cross flow area flowing to described outlet for described gas from described heat exchanger, the speed of the stream of described gas is little by little increased, also reduces pressure drop.
2. device according to claim 1, wherein:
Described first intake section, described second intake section and a described exit portion are formed by the group being connected to four sidewalls gone up each other, make the lateral cross flow area of described continuous increase and described ever-reduced lateral cross flow area be rectangular configuration;
Described heat exchanger has entrance side, orientates the outlet side relative with described entrance side as, and described cooling channel extends between described entrance side and described outlet side, and each in described entrance side and described outlet side is rectangular configuration;
Described entrance zone, threshold zone has the 3rd intake section, described 3rd intake section have from one end with the First Transition lateral cross flow area of the rectangular transition of the circle and other end place that limit described entrance, the other end of described Part III with define described first intake section described four sidewalls group in one aim at and be connected;
A described exit portion is the first exit portion;
Described exit zone has the second exit portion, described second exit portion is located so that described first exit portion is between described second exit portion and described heat exchanger, and described second exit portion has the second transition lateral cross flow area sentenced from one end and limit the circle of described outlet and the rectangular transition of the other end; And
The other end of described second exit portion with define described first exit portion described four sidewalls group in another aim at and be connected.
3. device according to claim 2, wherein,
Define at opposite end place another in the group of described four sidewalls of described second intake section aim at the described entrance side of in the group of described four sidewalls and described heat exchanger and be connected; And
Another defining in the group of described four sidewalls of described first exit portion at opposite end place is aimed at the other end of described second exit portion and the described outlet side of described heat exchanger and is connected.
4. device according to claim 2, wherein:
Described first intake section is divided into first group of sub-channel again by the first set isolation element, described first set isolation element be oriented so that in described sub-channel each be rectangular configuration;
Described second intake section is divided into second group of sub-channel by second component again every element, described second component every element be oriented so that in described sub-channel each be rectangular configuration;
Described second group of sub-channel has sub-channel more more than described first group of sub-channel.
5. device according to claim 4, wherein:
Described first exit portion is divided into the 3rd group of sub-channel by three components again every element;
Described first set isolation element, described second component are connected on described sidewall every element and described three components every element; And
Rectangle frame rack-like stiffened members is connected on the outer surface of each in described group of described four sidewalls.
6. device according to claim 4, wherein, described first group of sub-channel has four sub-channels, and described second group of sub-channel has 24 sub-channels.
7. a Compressed Gas cooling device, it comprises:
Entrance zone, threshold zone, it has entrance, with from upstream compression stage receiver gases;
Exit zone, it has outlet, with after having cooled at described gas by described gas discharging to downstream compression stage;
Heat exchanger, described entrance zone, threshold zone is connected on described exit zone by it, and has: gas passage, and it is communicated with between described entrance zone, threshold zone with described exit zone, for passing through described gas; And coolant channel, it becomes heat transfer relation to locate with described gas passage, for by cooling agent, with by cooling described gas through described gas passage with the indirect heat exchange of cooling agent;
Described entrance zone, threshold zone comprises a part, and a described part has: at least one sidewall, which form the lateral cross flow area constantly increased; And separating element, the lateral cross flow area of described continuous increase is divided into multiple sub-channel by described separating element again, each in described multiple sub-channel all has the sub-flow area of lateral cross constantly increased, so that the speed of the stream of described gas little by little reduces when described gas flows through described entrance zone, threshold zone, and what described sub-flow area made the stream of the described gas caused due to the vortex be administered in the stream of described gas from described upstream compression stage and at least one sidewall is separated reduction, thus reduces pressure drop; And
Described exit zone comprises the ever-reduced exit portion of lateral cross flow area flowing to described outlet for described gas from described heat exchanger, so that the speed of the stream of described gas little by little increases when described gas flows in described exit zone, also reduce pressure drop.
8. device according to claim 7, wherein:
Described intake section and described exit portion are formed by the group being connected to four sidewalls gone up each other, make the lateral cross flow area of described continuous increase and described ever-reduced lateral cross flow area be rectangular configuration;
Described sub-channel each be rectangular configuration;
Described heat exchanger has entrance side, orientates the outlet side relative with described entrance side as, and described cooling channel extends between described entrance side and described outlet side, and each in described entrance side and described outlet side is rectangular configuration;
At least one sidewall described of described intake section is one in the group of described four sidewalls;
Another in the group of described four sidewalls forms described exit portion;
Described intake section is the first intake section, and described exit portion is the first exit portion, and described entrance zone, threshold zone has the second intake section, and described exit zone has the second exit zone;
Described second intake section have from one end with the First Transition lateral cross flow area of the rectangular transition of the circle and other end place that limit described entrance, the other end of described first intake section with define described first intake section described four sidewalls group in one aim at;
Described second exit portion have from one end with the second transition lateral cross flow area of the rectangular transition of the circle and other end place that limit described outlet; And
The other end of described second exit portion is aimed at another in the group of described four sidewalls.
9. device according to claim 8, wherein:
One of defining in the group of described four sidewalls of described first intake section connects and is registered on the described entrance side of the described heat exchanger of the position at the described entrance zone, threshold zone relative with described second intake section; And
Another defining in the group of described four sidewalls of described first exit portion connects and is registered on the described outlet side of the described heat exchanger of the position at the described exit zone relative with described second exit portion.
10. device according to claim 8, wherein:
The described separating element of described first intake section is the first component isolated component, and described sub-channel is first group of sub-channel;
Described first exit portion has second component every element, and described second component forms the 3rd group of sub-channel of rectangular configuration every element;
Described first set isolation element and described second component are connected on described sidewall every element; And
Rectangle frame rack-like stiffened members is connected on the outer surface of each in described group of described four sidewalls.
11. according to claim 2 or claim 4 or claim 5 or claim 8 or device according to claim 10, wherein:
Described heat exchanger is that intersection reverse flow is arranged;
Described cooling channel is being formed relative between the described entrance side of described heat exchanger and multiple parallel fins of described outlet side orientation at a right angle; And
Described cooling channel is formed by coolant hose, and described coolant hose penetrates the described parallel fins of the circulation for described cooling agent, and is on orthogonal directed relative to described parallel fins.
12. devices according to claim 11, wherein:
Described coolant hose comprises the group being arranged to provide the group first group of intercoolant pipe of the entrance coolant hose passed in described heat exchanger four times, second group of intercoolant pipe and outlet coolant pipe;
Described heat exchanger has orientates two end portion respect to one another as, and connects described end portion and form the isolated top panel that laterally extends of the described entrance side of described heat exchanger and described outlet side two and bottom panel;
Entrance bin and outlet bin are located abreast, be arranged in a place of described two end portion, and become to flow with described outlet coolant pipe with described entrance coolant hose respectively and be communicated with, enter in described entrance coolant hose to guide to described cooling agent, and from cooling agent described in described outlet coolant tube drainage; And
Reverse bin is positioned at the described end portion of described heat exchanger, and be configured to flow in described first group of intercoolant pipe at another place in described end portion after crossing described heat exchanger from the cooling agent of described inlet tube, the place of cooling agent after crossing described heat exchanger in described end portion from described first group of intercoolant pipe flows in described second group of intercoolant pipe, cooling agent from described second group of intercoolant pipe flows in the group of described outlet coolant pipe after crossing described heat exchanger, and after this, flow into described outlet bin from the group of described outlet coolant pipe.
13. devices according to claim 11, wherein, the condensate that described heat exchanger has between described outlet side and described coolant hose and described parallel fins departs from room, be separated from the described Compressed Gas through described heat exchanger to allow condensed water, and be positioned at the elongate tubular discharge portion at bottom place that described condensate departs from room, to collect described condensed water from described gas separaion and by described condensed water from described heat exchangers.
14. devices according to claim 12, wherein, the condensate that described heat exchanger has between described outlet side and described coolant hose and described parallel fins departs from room, be separated from the described Compressed Gas through described heat exchanger to allow condensed water, and be positioned at the elongate tubular discharge portion at bottom place that described condensate departs from room, to collect described condensed water from described gas separaion and by described condensed water from described heat exchangers.
15. devices according to claim 13, wherein, described coolant hose is connected on two relative tube sheets, and is supported by two relative tube sheets at the end place of described coolant hose.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/538,387 US20140000841A1 (en) | 2012-06-29 | 2012-06-29 | Compressed gas cooling apparatus |
| US13/538387 | 2012-06-29 | ||
| PCT/US2013/037741 WO2014003880A1 (en) | 2012-06-29 | 2013-04-23 | Compressed gas cooling apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104364599A true CN104364599A (en) | 2015-02-18 |
Family
ID=48326438
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380033128.1A Pending CN104364599A (en) | 2012-06-29 | 2013-04-23 | Compressed gas cooling apparatus |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20140000841A1 (en) |
| CN (1) | CN104364599A (en) |
| WO (1) | WO2014003880A1 (en) |
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| CN111263871A (en) * | 2017-07-28 | 2020-06-09 | 欧洲冷水机组有限公司 | Air condenser |
| CN111989495A (en) * | 2018-04-26 | 2020-11-24 | 三菱重工压缩机有限公司 | Centrifugal compressor |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2768814A (en) * | 1950-10-27 | 1956-10-30 | Frey | Plate warmer exchanger |
| DE3131720A1 (en) * | 1981-01-02 | 1982-08-05 | Ingersoll-Rand Co., 07675 Woodcliff Lake, N.J. | GAS COMPRESSOR UNIT |
| JPS57192798A (en) * | 1981-05-21 | 1982-11-26 | Unyusho Senpaku Gijutsu Kenkyusho | Flow path of heat transmitting surface formed with expanded flow path and diffuser type heat exchanger utilizing the same |
| US4415024A (en) * | 1980-11-05 | 1983-11-15 | Joy Manufacturing Company | Heat exchanger assembly |
| US4452216A (en) * | 1982-09-27 | 1984-06-05 | Allis-Chalmers Corporation | Even temperature intercooler |
| EP0864839A2 (en) * | 1997-03-11 | 1998-09-16 | Behr GmbH & Co. | Heat exchanger, more particularly supercharge air cooler, for automotive vehicle |
| CN101929470A (en) * | 2009-06-24 | 2010-12-29 | 普莱克斯技术有限公司 | Multistage compressor installation |
| US20110088886A1 (en) * | 2009-10-15 | 2011-04-21 | Klaus Kalbacher | Heat exchanger and seal arrangement for the same |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2106458A (en) * | 1935-12-23 | 1938-01-25 | Anemostat Corp | Air distributing device |
| NL128466C (en) * | 1964-03-07 | |||
| GB1190958A (en) * | 1966-06-24 | 1970-05-06 | Lummus Co | Connector Duct |
| US4279297A (en) * | 1978-10-16 | 1981-07-21 | Gte Products Corporation | Housing for ceramic heat recuperators and assembly |
| US4778003A (en) * | 1983-01-03 | 1988-10-18 | The Dow Chemical Company | Heat exchanger with novel seal for tube sheet |
| US5110560A (en) * | 1987-11-23 | 1992-05-05 | United Technologies Corporation | Convoluted diffuser |
| US20030111209A1 (en) * | 1999-01-20 | 2003-06-19 | Hino Motors, Ltd. | EGR cooler |
-
2012
- 2012-06-29 US US13/538,387 patent/US20140000841A1/en not_active Abandoned
-
2013
- 2013-04-23 WO PCT/US2013/037741 patent/WO2014003880A1/en active Application Filing
- 2013-04-23 CN CN201380033128.1A patent/CN104364599A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2768814A (en) * | 1950-10-27 | 1956-10-30 | Frey | Plate warmer exchanger |
| US4415024A (en) * | 1980-11-05 | 1983-11-15 | Joy Manufacturing Company | Heat exchanger assembly |
| DE3131720A1 (en) * | 1981-01-02 | 1982-08-05 | Ingersoll-Rand Co., 07675 Woodcliff Lake, N.J. | GAS COMPRESSOR UNIT |
| JPS57192798A (en) * | 1981-05-21 | 1982-11-26 | Unyusho Senpaku Gijutsu Kenkyusho | Flow path of heat transmitting surface formed with expanded flow path and diffuser type heat exchanger utilizing the same |
| US4452216A (en) * | 1982-09-27 | 1984-06-05 | Allis-Chalmers Corporation | Even temperature intercooler |
| EP0864839A2 (en) * | 1997-03-11 | 1998-09-16 | Behr GmbH & Co. | Heat exchanger, more particularly supercharge air cooler, for automotive vehicle |
| CN101929470A (en) * | 2009-06-24 | 2010-12-29 | 普莱克斯技术有限公司 | Multistage compressor installation |
| US20110088886A1 (en) * | 2009-10-15 | 2011-04-21 | Klaus Kalbacher | Heat exchanger and seal arrangement for the same |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108027222A (en) * | 2015-09-25 | 2018-05-11 | 西屋电气有限责任公司 | Heat exchanger |
| CN107091578A (en) * | 2017-04-28 | 2017-08-25 | 哈尔滨汽轮机厂辅机工程有限公司 | A kind of large-scale rectangular condenser of aixal admission |
| CN111263871A (en) * | 2017-07-28 | 2020-06-09 | 欧洲冷水机组有限公司 | Air condenser |
| CN111989495A (en) * | 2018-04-26 | 2020-11-24 | 三菱重工压缩机有限公司 | Centrifugal compressor |
| CN112032078A (en) * | 2020-07-29 | 2020-12-04 | 武汉大学 | Active high-efficient accuse temperature's efflux spray tube cooling system |
| CN112032078B (en) * | 2020-07-29 | 2021-09-03 | 武汉大学 | Active high-efficient accuse temperature's efflux spray tube cooling system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014003880A1 (en) | 2014-01-03 |
| US20140000841A1 (en) | 2014-01-02 |
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