WO2014003880A1 - Compressed gas cooling apparatus - Google Patents

Compressed gas cooling apparatus Download PDF

Info

Publication number
WO2014003880A1
WO2014003880A1 PCT/US2013/037741 US2013037741W WO2014003880A1 WO 2014003880 A1 WO2014003880 A1 WO 2014003880A1 US 2013037741 W US2013037741 W US 2013037741W WO 2014003880 A1 WO2014003880 A1 WO 2014003880A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet
outlet
gas
heat exchanger
section
Prior art date
Application number
PCT/US2013/037741
Other languages
French (fr)
Inventor
Robert L. Baker
Arun SURYANARAYANAN
Maulik R. Shelat
Jeffrey C. GOODBAND
Original Assignee
Praxair Technology, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Praxair Technology, Inc. filed Critical Praxair Technology, Inc.
Priority to CN201380033128.1A priority Critical patent/CN104364599A/en
Publication of WO2014003880A1 publication Critical patent/WO2014003880A1/en

Links

Classifications

    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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

Definitions

  • the present invention provides a compressed gas cooling apparatus that can function as an intercooler or an after-cooler and that is used to cool a gas between or after a series of compression stages. More particularly, the present invention relates to such a cooling apparatus in which both the inlet and outlet have sections of ever- increasing and ever-decreasing area, respectively, to feed gas to and from a heat exchanger positioned between the inlet and the outlet. Even more particularly, the present invention relates to such a cooling apparatus in which the ever-increasing section of the inlet is designed to further reduce pressure losses that occur due to the swirl in the gas flow imparted by the upstream compression stage introducing compressed gas into the cooling apparatus.
  • each of the compression stages is formed by a centrifugal compressor in which gas is drawn from an inlet to a vaned impeller that is driven to accelerate the gas and thereby increase the pressure and velocity of the gas.
  • the pressure loss accompanying the increase in velocity is recovered in a diffuser that surrounds the impeller and that can have vanes.
  • the gas is discharged from the impeller to a spiral-like volute having an outlet from which the pressurized gas is discharged and that surrounds the inlet.
  • the intercooler is positioned between the outlet of the upstream stage and the inlet of the downstream stage.
  • the decrease in temperature of the compressed gas through intercooling and after-cooling results in the condensation of such moisture which is discharged from the intercoolers and after-coolers so that the condensate is not carried to downstream stages or to equipment conducting processes that consume the compressed gas.
  • centrifugal compressors In air separation plants, the use of centrifugal compressors with intercoolers and after coolers is quite common.
  • the compressors can be driven by a transmission in which an electric motor drives a bull gear that drives pinion-like gears that are attached to each of the
  • the compressors are arranged about the bull gear with piping having bends to route the gas to and from intercoolers located between the compressors. As known in the art, the bends in such piping will induce a pressure drop within gas passing between the compressors. Intercoolers are
  • the centrifugal compressors are independently driven and are positioned so that the inlet of a downstream compressor is located
  • intercoolers have sections of ever-increasing transverse cross-sectional area and ever-decreasing transverse cross- sectional area, respectively, with the heat exchangers positioned between such sections.
  • These sections can be formed by sets of four plates connected together in an arrangement of a four-side polyhedron and as such have a rectangular transverse cross-sectional flow area.
  • the heat exchangers that incorporate a box-like housing are located between these sections and internally, the heat exchangers have gas passages for the flow of the gas directly from and to such inlet and outlet sections.
  • the coolant passes through coolant passages at right angles to the gas passages.
  • intercooler or after-cooler even one having a gradually increasing cross-sectional flow area, the gas tends to accumulate on the walls and at one side of the inlet. This creates a high pressure area where the flow accumulates and a low pressure area adjacent the high pressure area. This causes separation of the flow from the walls and a
  • the present invention provides a compressed gas cooling apparatus that can function as an intercooler or an after- cooler that is designed to minimize pressure drops within the inlet to the compressed gas cooling apparatus that arise from the swirl imparted into the gas flow by the compressor .
  • the present invention provides a compressed gas cooling apparatus having use as an intercooler or an after- cooler.
  • the apparatus is provided with an inlet section and an outlet section.
  • the inlet section has an inlet to receive a gas from an upstream compression stage and the outlet section has an outlet to discharge the gas, after having been cooled to a downstream compression stage.
  • a heat exchanger connects the inlet section to the outlet section and has gas passages communicating between the inlet section and the outlet section for passage of the gas and coolant passages positioned in a heat transfer
  • the inlet section portion comprises a first inlet portion and a second inlet portion.
  • the first inlet portion is located between the inlet and the second inlet portion and the second inlet portion located between the first inlet portion and the heat exchanger.
  • Each of the first inlet portion and the second inlet portion has an ever increasing transverse cross-sectional flow area.
  • the ever increasing transverse cross-sectional flow area of the second inlet portion increasing at a greater rate than the first inlet portion so that the velocity of the flow of the gas gradually decreases as the gas flows through the inlet section to a lesser extent in the first inlet portion than the second inlet portion.
  • the outlet section comprises one outlet portion of ever-decreasing transverse cross- sectional flow area for flow of the gas from the heat exchanger to the outlet such that velocity of the flow of the gas gradually increases to also reduce pressure drop.
  • the first inlet portion, the second inlet portion and the one outlet portion can be formed by sets of four sidewalls connected to one another such that the ever- increasing transverse cross-sectional flow area and the ever-decreasing transverse cross-sectional flow area are of rectangular configuration.
  • the heat exchanger has an inlet side and an outlet side located opposite to the inlet side.
  • the cooling passages extend between the inlet side and the outlet side and each of the inlet side and the outlet side is of rectangular configuration.
  • the inlet section has a third inlet portion having a first transitional transverse cross-sectional flow area that transitions from a circle, at one end, to define the inlet and at the other end, a rectangle.
  • the other end of the third portion in registry with and connected to one of the sets of four sidewalls forming the first part of inlet portion.
  • the one outlet portion is a first outlet portion and the outlet section has a second outlet portion situated such that the first outlet portion is located between the second outlet portion and the heat exchanger.
  • the second outlet portion has a second transitional transverse cross-section flow area transitioning from a circle, at one end, to define the outlet and at the other end, a rectangle.
  • the other end of the second outlet portion is in registry with and connected to a further of the sets of four sidewalls forming the first outlet portion.
  • another of the sets of four sidewalls forming the second inlet portion, at opposite ends, is in registry with and connected to the one of the sets of four sidewalls and the inlet side of the heat exchanger.
  • the further of the sets of four sidewalls forming the first outlet portion, at opposite ends, is in registry with and connected to the other end of the second outlet portion and the outlet side of the heat exchanger.
  • the first inlet portion can be subdivided into a first set of subpassages by a first set of partition elements oriented such that each of the subpassages is of rectangular configuration.
  • the second inlet portion can be subdivided into a second set of subpassages by a second set of partition elements oriented such that each of the subpassages is of
  • the second set of subpassages have more subpassages than the first set of subpassages.
  • the first outlet portion can likewise be subdivided into a third set of subpassages by a third set of partition elements.
  • the first set of partition elements, the second set of partition elements and the third set of partition elements are connected to the sidewalls and rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls.
  • the first set of subpassages has four subpassages and the second set of subpassages has twenty- four subpassages.
  • An embodiment of the present invention also provides a compressed gas cooling apparatus in which the inlet section comprises one portion having at least one sidewall forming an ever-increasing transverse cross- sectional flow area.
  • Partition elements subdivide the ever-increasing transverse cross-sectional flow area into a plurality of subpassages, each having ever-increasing transverse cross-sectional sub-flow areas so that velocity of the flow of the gas gradually decreases as the gas flows through the inlet section.
  • the sub-flow areas reduce separation of the flow of the gas from the at least one sidewall, due to swirl imparted into the flow of the gas from the upstream compression stage, thereby reducing pressure drop.
  • the outlet section comprises an outlet portion of ever-decreasing transverse cross-sectional flow area for flow of the gas from the heat exchanger to the outlet so that the velocity of the flow of the gas
  • the inlet portion and the outlet portion are formed by sets of four sidewalls connected to one another such that the ever-increasing transverse cross-sectional flow area and the ever- decreasing transverse cross-sectional flow area are of rectangular configuration.
  • the subpassages are each of rectangular configuration.
  • the heat exchanger has an inlet side, an outlet side located opposite to the inlet side, the cooling passages that extend between the inlet side and the outlet side.
  • Each of the inlet side and the outlet side is of rectangular configuration.
  • the at least one sidewall of the inlet portion is one of the sets of four sidewalls. A further of the sets of four sidewalls form the outlet portion.
  • the inlet portion is a first inlet portion and the outlet portion is a first outlet portion.
  • the inlet section has a second inlet portion and the outlet section has a second outlet portion.
  • the second inlet portion has a first transitional transverse cross-sectional flow area transitioning from a circle, at one end, to define the inlet and at the other end, a rectangle. The other end of the second inlet portion in registry with the one of the sets of four sidewalls forming the first inlet portion.
  • the second outlet portion has a second transitional transverse cross-section flow area
  • the one of the sets of four sidewalls forming the first inlet portion is connected to and in registry with the inlet side of the heat exchanger at a location of the inlet section opposite to the second inlet portion.
  • the further of the sets of four sidewalls forming the first outlet portion is connected to and in registry with the outlet side of the heat exchanger at a location of the outlet section opposite to the second outlet portion.
  • the partition elements of the first inlet portion can be a first set of partition elements and the subpassages are a first set of subpassages and the first outlet portion has a second set of partition elements that form a third set of subpassages of rectangular configuration.
  • the first set of partition elements and the second set of partition elements are connected to the sidewalls. Rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls.
  • the heat exchanger can be of cross-counter flow arrangement.
  • the cooling passages are formed between a plurality of parallel fins oriented at right angles with respect to the inlet side and the outlet side of the heat exchanger.
  • the coolant passages are formed by coolant tubes that penetrate the parallel fins for circulation of the coolant and are in an orthogonal orientation with respect to the parallel fins.
  • the coolant tubes comprise a set of inlet coolant tubes, a first set of intermediate coolant tubes, a second set of intermediate coolant tubes and a set of outlet coolant tubes.
  • These inlet, intermediate and outlet coolant tubes are arranged to provide four passes within the heat exchanger.
  • the heat exchanger has two end portions located opposite to one another and two spaced, transversely extending top and bottom panels connecting the end portions and forming the inlet side and the outlet side of the heat exchanger.
  • plenum are situated, side by side, at one of the two end portions and are in flow communication with the inlet
  • coolant tubes and the outlet coolant tubes respectively, to introduce the coolant into the inlet coolant tubes and to discharge the coolant from the outlet coolant tubes.
  • Reversal plenums are located at the end portions of the heat exchanger and are configured such that coolant from the inlet tubes flows into the first set of intermediate coolant tubes at the other of the end portions, after
  • coolant from the first set of intermediate coolant tubes flows into the second set of intermediate coolant tubes at the one of the end portions, after having traversed the heat exchanger. Subsequently, coolant from the second set of intermediate coolant tubes flows into the set of outlet coolant tubes, after having traversed the heat exchanger and thereafter, flows from the set of outlet coolant tubes into the outlet plenum.
  • the heat exchanger can have a condensate disengagement chamber located between the outlet side and the coolant tubes and the parallel fins to allow condensed water to separate from the compressed gas passing through the heat exchanger.
  • An elongated, tube-like drain is located at the bottom of the condensate disengagement chamber to collect the condensed water separated from the gas and to discharge the condensed water from the heat exchanger .
  • the coolant tubes can be connected to and supported at their ends by two opposed tube sheets .
  • FIG. 1 is a perspective view of a compressed gas cooling apparatus of the present invention
  • FIG. 2 is an exploded, perspective view of an inlet section used in the apparatus illustrated in Fig. 1;
  • FIG. 3 is a sectional, perspective view of the inlet section used in the apparatus illustrated in Fig. 1 taken along line 3-3 of Fig. 1 ;
  • FIG. 4 is a perspective view of an alternative embodiment of a compressed gas cooling apparatus of the present invention
  • Fig. 5 is an exploded, perspective view of an inlet section used in the apparatus illustrated in Fig.4.
  • FIG. 6 is a sectional perspective view of the inlet section used in the apparatus illustrated in Fig. 1 taken along line 6-6 of Fig 4 ;
  • FIG. 7 is an exploded, perspective view of an outlet section used in the apparatus illustrated in Figs. 1 and 4 ;
  • FIG. 8 is a top plan view of a heat exchanger in accordance with the present invention that is used in the apparatus illustrated in Figs. 1 and 4;
  • Fig. 9 is a fragmentary, sectional perspective view of the heat exchanger illustrated in Fig. 8 taken along line 9-9 thereof, showing fins, cooling passages and coolant tubes used within the heat exchanger;
  • Fig. 10 is a sectional, perspective view of the heat exchanger used in the apparatus illustrated in Figs. 1 and 4 with the fins removed to illustrate the coolant tubes, inlet, outlet and reversal plenums and a condensate
  • apparatus can function as an intercooler between
  • Apparatus 1 has an inlet section 2, an outlet section 3 and a heat exchanger 4 connecting the inlet section 2 to the outlet section 3.
  • the inlet section 2 has an inlet 10 to receive a gas flow "A" from an upstream compression stage, not illustrated.
  • the upstream compression stage could be a centrifugal compressor or an axial compressor.
  • the gas flow indicated by arrowhead "A” entering the inlet 10 has a swirl or a rotational component to the flow designated by curved arrowhead "B".
  • Such swirl is imparted to the flow by the rotational components of the compressor, for instance, the impeller of a centrifugal compressor.
  • inlet section 2 is provided with a first inlet portion 14, a second inlet portion 16 and optionally, a third inlet portion 18.
  • all of these portions have an ever increasing transverse cross-sectional flow area that will act to gradually reduce the velocity of the gas flow before entering the heat exchanger 4. This will reduce pressure drop or loss in the flow due to turbulence that would otherwise be induced in the gas flow due to a sudden enlargement in cross-sectional flow area from the inlet opening 10.
  • the pressure drop or loss in the gas flow also arises from the swirl "B" introduced into the flow by the upstream compressor. This "swirl" or rotation in the flow tends to cause the gas to accumulate on one side of the inlet section 2.
  • This accumulation in turn creates a high pressure area and an adjacent low pressure area.
  • a separation of the gas flow appears at wall regions of the inlet portion towards the adjacent low pressure region which in turn results in a backward circulation of the gas flow leading to an increase in pressure drop in the gas flow.
  • the first inlet portion 14 is formed by a set of four sidewalls 20, 22, 24 and 26 that are connected to one another such that the ever-increasing transverse cross- section flow area is of rectangular configuration.
  • the second inlet portion 16 is formed by another set of four sidewalls 28, 30, 32 and 34 that are connected to one another to again form an ever-increasing transverse cross- sectional flow are of rectangular configuration.
  • the swirl “B” will tend to cause the gas flow "A” to accumulate along sidewalls 26 and 34 of the first and second sections 14 and 16 and portions of adjacent sidewalls 20, 24 and 28,32 located close to the sidewalls 26 and 34. This will create a high pressure field within the gas flow "A” at such sidewall regions. In more central regions of the first and second sections 14 and 16, located at a distance from the sidewalls 26 and 34, the flow is not subject to such accumulation and therefore, has a lower pressure. As mentioned above, this pressure difference will potentially cause recirculation of the gas flow "A” from the higher to the lower pressure regions resulting in a pressure drop.
  • the ever-increasing transverse cross sectional flow area of the second inlet portion 16 increases at a greater rate than that of the first inlet portion 14.
  • the effect of this is that the velocity of the gas flow through the first inlet portion 14 will decrease to a lesser extent than the gas flow within the second inlet portion 16.
  • the resulting higher velocity of the gas flow within the first inlet portion 14 will tend to reduce the separation of the gas flow from the walls of the inlet section 2 and allow the swirl "B" to dissipate somewhat before the gas flow reaches the second inlet portion 16.
  • First section 14 would originate from the apex of such bell shape and second section 16 would terminate at the mount of such bell shape.
  • first section 14 has an aspect ratio of between 0.4 and 0.5. This aspect ratio is measured by dividing the maximum width of first section 14, as seen at the juncture of the first section 14 with the second section 16, by its length.
  • the second section 16 preferably has an aspect ratio of between 0.2 and 0.4. This aspect ratio is
  • the rectangular cross-sectional flow areas of the first inlet portion 14 is divided into a first set of subpassages, for example subpassage 36 and the second inlet portion 16 is subdivided into a second set of subpassages, for example subpassage 38.
  • These rectangular subdivisions serve to reduce pressure drop further by preventing gas flow from accumulating on one side of the inlet portion 2 as a result of the swirl "B".
  • the first set of subpassages 36 are formed by a first set of partition elements 40 and 42, positioned at right angles to one another and the second set of subpassages 38 are formed from sets of partition elements 40 and 42 and 44 and 46.
  • Partition elements 40 and 42 extend the length of the first inlet portion 14 and the second inlet portion 16. Partition elements 44 and 46 are confined to the second inlet portion 16 and are positioned at right angles to one another. As illustrated each of the subpassages 36 and 38 are of rectangular configuration and are each of ever
  • the partition element 40 is connected along its edges to sidewalls 20, 24 and 28, 32; and the partition element 42 is connected along its edges to sidewalls 22, 26; and 30, 34. Further, the partition elements 44 are connected to sidewalls 28 and 32 and the partition elements 46 are connected to sidewalls 30 and 34. These connections are preferred in order to help maintain structural
  • first inlet portion 14 and the second inlet portion 16 are normally in tension during use of the apparatus 1. Further structural integrity is provided by frame-like stiffing members 48 connected to the set of sidewalls 20, 22, 24 and 26 forming the first inlet portion 14 and to sidewalls 28, 30, 32 and 34 forming the second inlet portion 16. As can be appreciated, such connections of the partition elements and the use of the frame-like stiffing members to reduce the thickness and weight of the sidewalls 20 through 34 that are necessary to contain compressed gases at high pressure.
  • the second inlet portion 16 has more subpassages 38 than the subpassages 36 of the first inlet portion 14. Preferably there are 24 of such
  • first inlet portion 14 has a smaller cross-section than the second inlet portion 16, there is less stress and therefore, fewer partition elements are required in the first inlet portion for structural integrity.
  • first inlet section 14 could simply be provided with a circular opening to form the inlet 10
  • the third inlet portion 18 is provided having a transitional transverse, cross-sectional flow area that transitions from the circular inlet opening 10, at one end and a rectangle at the other end.
  • the sidewalls 50 thereof are therefore, curved at the inlet opening 10 and are planar at the other end thereof to form the rectangle.
  • the sidewalls 50 are connected to and in registry with the sidewalls 20, 22, 24 and 26 of the first inlet portion 14.
  • the sidewalls 20, 22, 24 and 26 are also preferably connected to an in registry with the sidewalls 28, 30, 32 and 34 of the second inlet portion 16.
  • the sidewalls 28, 30, 32 and 34 are connected to and in registry with the inlet side 106 of the heat exchanger 4. It is possible, however to provide a spacer section having a uniform, rectangular cross-sectional flow area between the second inlet section 16 and the heat exchanger 4.
  • Apparatus 1' differs from apparatus 1 in that it is provided with an inlet section 2' having a first inlet portion 52 of ever increasing cross-sectional flow area and a second inlet portion 54 of similar configuration to the third inlet portion 18 of apparatus 1.
  • First inlet portion 52 is formed by a set of four sidewalls 56, 58, 60 and 62 that are connected to one another such that the ever-increasing transverse cross- section flow area is of rectangular configuration.
  • the second inlet portion 54 provided further pressure drop by provision of its transitional transverse cross-section flow area that transitions from the circular inlet opening 10', at one end and a rectangle at the other end.
  • the sidewalls 64 thereof are therefore, curved at the inlet opening 10' and are planar at the other end thereof to form the rectangle.
  • the sidewalls 64, at the other end of second inlet portion 54 are connected to an in registry with sidewalls 56, 58, 60 and 62 of the first inlet portion 56.
  • pressure drop within the inlet section 2' is reduced by provision of the ever-increasing transverse cross-section flow area provided by the first inlet portion 52.
  • the pressure drop due to swirl is reduced by means of a set of partitions 66 and 68, positioned at right angles with respect to one another and that subdivide the transverse cross-sectional flow area into subpassages, for instance subpassage 70, each of ever increasing transverse cross sectional flow area.
  • the partition elements 66 and 68 prevent the formation of a high pressure wall region, resulting from the swirl in the flow, from influencing the subflows in adjacent subpassages 70.
  • the partitions 66 and 68 are also connected to the sidewalls 56, 60 and 58, 62, respectively, to add to the structural integrity of the first portion 52 of the inlet section 2'. Additionally, optional frame-like stiffening members 72 connected to the outer surfaces of the sidewalls 56, 58, 60 and 62 add to the structural integrity and strength of the first portion 52.
  • outlet section 3 again has an ever decreasing transverse cross- section flow area to allow the velocity of the flow to gradually increase.
  • the design of the outlet section 3 is less critical in decreasing pressure drop than the inlet sections 2 and 2' of the apparatus 1 and 1', respectively.
  • the illustrated outlet section 3 is of the same design in both apparatus 1 and 1' .
  • the outlet section 3 could have the same design as either of the inlet sections 2 and 2' .
  • the illustrated outlet section 3 is preferably provided with a first outlet portion 74 and a second outlet portion 76.
  • the first outlet portion 74 is formed by a set of four sidewalls 78, 80, 82 and 84 connected together to provide a rectangular, transverse cross-section flow area.
  • the first outlet portion 74 could terminate in an outlet opening, preferably, to reduce pressure drop, the second outlet portion 76 has a second transitional
  • transverse cross-section flow area formed by a set of four sidewalls 86, 88, 90 and 92 that transitions from a circle, at one end, to define an outlet 94 from which the outlet stream "C" is discharged and at the other end, a rectangle.
  • Sidewalls 86, 88, 90 and 92 are connected to and in
  • rectangular frame-like members 100 can be connected to the sidewalls 78, 80, 82 and 84 to provide additional strength.
  • heat exchanger 4 is of common design with respect to apparatus 1 and apparatus 1' and functions to remove the heat of compression from the incoming gas stream "A" by providing indirect heat exchange between a cooling fluid and the gas stream.
  • the cooling fluid which can be water, enters through an inlet 102 and is discharged from an outlet 104.
  • heat exchanger 4 connects the inlet section 2 to the outlet section 3 with respect to apparatus 1.
  • heat exchanger 4 also connects inlet section 2' to outlet section 3 in apparatus 1' .
  • Heat exchanger 4 is provided with an inlet side 106 connected to inlet sections 2 and 2' and an outlet side 108 connected to outlet section 3.
  • the connections need not be direct and rectangular spacer-like elements could be provided within such sections.
  • the gas to be cooled enters the heat exchanger 4 from the inlet sections 2 and 2' at the inlet side 106 and the cooled gas is discharge from the heat exchanger 4 from the outlet side 108 to the outlet section 3.
  • the indirect heat exchange within heat exchanger 4 is accomplished by means gas passages 110 that are formed between a series of parallel, fin-like plate elements 112.
  • the fin-like plate elements 112 are penetrated by a set of outlet coolant tubes 122 which provide the coolant passages for the coolant.
  • the fin-like plate elements 112 are also penetrated by other sets of coolant tubes designated by reference numbers 116, 118 and 120 and to be discussed hereinafter.
  • inlet side 106 is an open rectangular area that is framed to receive the gas flow "A" and pass into the gas passages 110.
  • outlet side 108 is an open rectangular area that is framed to discharge the gas flow "A", after having been cooled, to the outlet section 3.
  • the rectangular areas are equal to those provided by inlet section 2 and 2' and outlet section 3.
  • the coolant tubes comprise a set of inlet coolant tubes 116, first and second sets of intermediate coolant tubes 118 and 120 and a set of outlet coolant tubes 122.
  • the heat exchanger 4 has two end portions 130 and 132 located opposite to one another that are connected the two spaced, transversely extending top and bottom panels 134 and 136 thereby forming the inlet side 106 and the outlet side 108 of the heat exchanger which are rectangular openings to the heat
  • a base 138 is connected to the bottom panel 136 to elevate the bottom panel 132 above ground level.
  • inlet plenum 140 and outlet plenum 142 Contained within end portion 130 is an inlet plenum 140 and an outlet plenum 142 that are located side- by-side, are situated within end portion 130.
  • Inlet plenum 140 and outlet plenum 142 are in flow communication with the inlet coolant tubes 116 and the outlet coolant tubes 122, respectively.
  • the coolant is introduced into the inlet coolant tubes 116 from the inlet 102 in direction of the arrowhead "D" and is discharged from the outlet coolant tubes through the outlet plenum 142 and to the outlet 104 in direction of arrowhead "E".
  • a reversal plenum 144 is located between the inlet plenum 140 and the outlet plenum 142 and two reversal plenums 146 and 148 are formed within the other end portion 132 by provision of a dividing plate 150.
  • the coolant enters the inlet tubes 116 from the inlet plenum 140. After traversal of the heat exchanger, the coolant reverses flow direction within reversal plenum 146 in the direction of arrowhead "G" and then flows through the first set of intermediate coolant tubes 118 until the coolant reaches the reversal plenum 144. Within reversal plenum 144, the coolant again reverses direction and flows through the second set of intermediate coolant tubes 120 until reaching reversal plenum 148.
  • the coolant again reverses direction in the direction of arrowhead "H" and flows through the outlet coolant tubes 122 to the outlet plenum 142 from which the coolant is discharged from heat exchanger 4 from the outlet 104.
  • a disengagement chamber 152 is provided adjacent to the outlet side 108 of the heat exchanger 4.
  • the disengaged water collects in the bottom panel 136 and is discharged from openings 154 and 156 to an elongated, tube-like drain 158 located beneath the bottom panel 136 and adjacent the base 138 for discharge of the collected water.

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

COMPRESSED GAS COOLING APPARATUS
Field of the Invention:
[0001] The present invention provides a compressed gas cooling apparatus that can function as an intercooler or an after-cooler and that is used to cool a gas between or after a series of compression stages. More particularly, the present invention relates to such a cooling apparatus in which both the inlet and outlet have sections of ever- increasing and ever-decreasing area, respectively, to feed gas to and from a heat exchanger positioned between the inlet and the outlet. Even more particularly, the present invention relates to such a cooling apparatus in which the ever-increasing section of the inlet is designed to further reduce pressure losses that occur due to the swirl in the gas flow imparted by the upstream compression stage introducing compressed gas into the cooling apparatus.
Background of the Invention:
[0002] Large volumes of gas are compressed in a variety of industrial applications within compression systems having a series of stages with intercooling between stages to cool the gas. The energy imparted to the gas in each of the compression stages heats the gas, also known as the heat of compression, is removed by the intercoolers . An after-cooler can be positioned after the last of the compression stages.
[0003] Typically, each of the compression stages is formed by a centrifugal compressor in which gas is drawn from an inlet to a vaned impeller that is driven to accelerate the gas and thereby increase the pressure and velocity of the gas. The pressure loss accompanying the increase in velocity is recovered in a diffuser that surrounds the impeller and that can have vanes. The gas is discharged from the impeller to a spiral-like volute having an outlet from which the pressurized gas is discharged and that surrounds the inlet. The intercooler is positioned between the outlet of the upstream stage and the inlet of the downstream stage. Where the gas, such as air, contains moisture, the decrease in temperature of the compressed gas through intercooling and after-cooling results in the condensation of such moisture which is discharged from the intercoolers and after-coolers so that the condensate is not carried to downstream stages or to equipment conducting processes that consume the compressed gas.
[0004] In air separation plants, the use of centrifugal compressors with intercoolers and after coolers is quite common. The compressors can be driven by a transmission in which an electric motor drives a bull gear that drives pinion-like gears that are attached to each of the
compressors to in turn drive the impellers. Thus, the compressors are arranged about the bull gear with piping having bends to route the gas to and from intercoolers located between the compressors. As known in the art, the bends in such piping will induce a pressure drop within gas passing between the compressors. Intercoolers are
typically of shell and tube construction in which the tubes are used to pass a coolant, that can be water, into indirect heat exchange with the gas passing at right angles to the tubes. Passages for the gas are formed by an arrangement of fins through which the tubes penetrate. The gas enters the shell of such a heat exchanger through an inlet plenum and is discharged, at the opposite end of the shell from an outlet plenum. Gas is introduced and
discharged from such plenums at right angles to the shell through and inlet and outlet thereof. As can be
appreciated there exists a further pressure loss from such arrangement due to the change in direction of flow and also, the rapid increase in cross-sectional flow area from the inlet to the inlet plenum and then from the outlet plenum to the outlet. In air separation plants, these pressure losses must be compensated for by increased compression and therefore, increased power consumption. The same
considerations apply to other industrial application of multi-stage compression systems.
[0005] Considerably more freedom in the placement of compressors and intercoolers is possible where the
compressors are independently and directly driven by high speed permanent magnet motors. The freedom in the
placement of the compressors can be used to reduce pressure drops that accompany the intercooling and after-cooling of gases within multi-stage compression systems. For instance, in US Patent Publication No. 2010/0329895, the centrifugal compressors are independently driven and are positioned so that the inlet of a downstream compressor is located
opposite to the outlet of an upstream compressor.
Additionally, each of the inlets and outlets to the
intercoolers have sections of ever-increasing transverse cross-sectional area and ever-decreasing transverse cross- sectional area, respectively, with the heat exchangers positioned between such sections. These sections can be formed by sets of four plates connected together in an arrangement of a four-side polyhedron and as such have a rectangular transverse cross-sectional flow area. The heat exchangers that incorporate a box-like housing are located between these sections and internally, the heat exchangers have gas passages for the flow of the gas directly from and to such inlet and outlet sections. The coolant passes through coolant passages at right angles to the gas passages. As can be appreciated, such an arrangement reduces pressure losses that would otherwise arise from prior art arrangements having piping bends between stages and pressure losses due to rapid changes of area and direction of flow to and from the heat exchanger and within the heat exchanger itself.
[0006] What has not been appreciated, even in the publication discussed above, is that pressure losses also arise from the swirl induced into the flow entering inlet and outlet sections of the intercooler or other compressed gas cooling apparatus used in connection with a compressor. When the centrifugal compressor compresses the gas such a swirl in the flow is induced by the impeller and diffuser arrangement. When such flow enters an inlet to the
intercooler or after-cooler, even one having a gradually increasing cross-sectional flow area, the gas tends to accumulate on the walls and at one side of the inlet. This creates a high pressure area where the flow accumulates and a low pressure area adjacent the high pressure area. This causes separation of the flow from the walls and a
recirculation within the inlet to the intercooler or after- cooler that in turn produces a yet further component of the overall pressure drop.
[0007] As will be discussed, the present invention, among other aspects, provides a compressed gas cooling apparatus that can function as an intercooler or an after- cooler that is designed to minimize pressure drops within the inlet to the compressed gas cooling apparatus that arise from the swirl imparted into the gas flow by the compressor .
Summary of the Invention
[0008] The present invention provides a compressed gas cooling apparatus having use as an intercooler or an after- cooler. The apparatus is provided with an inlet section and an outlet section. The inlet section has an inlet to receive a gas from an upstream compression stage and the outlet section has an outlet to discharge the gas, after having been cooled to a downstream compression stage. A heat exchanger connects the inlet section to the outlet section and has gas passages communicating between the inlet section and the outlet section for passage of the gas and coolant passages positioned in a heat transfer
relationship with the gas passages for passage of a coolant to cool the gas passing through the gas passages through indirect heat exchange with a coolant. The inlet section portion comprises a first inlet portion and a second inlet portion. The first inlet portion is located between the inlet and the second inlet portion and the second inlet portion located between the first inlet portion and the heat exchanger. Each of the first inlet portion and the second inlet portion has an ever increasing transverse cross-sectional flow area. The ever increasing transverse cross-sectional flow area of the second inlet portion increasing at a greater rate than the first inlet portion so that the velocity of the flow of the gas gradually decreases as the gas flows through the inlet section to a lesser extent in the first inlet portion than the second inlet portion. This inhibits separation of the flow of the gas from sidewalls of each of the first inlet portion and the second inlet portion, due to swirl imparted into the flow of the gas from the upstream compression stage to reduce pressure drop. The outlet section comprises one outlet portion of ever-decreasing transverse cross- sectional flow area for flow of the gas from the heat exchanger to the outlet such that velocity of the flow of the gas gradually increases to also reduce pressure drop.
[0009] The first inlet portion, the second inlet portion and the one outlet portion can be formed by sets of four sidewalls connected to one another such that the ever- increasing transverse cross-sectional flow area and the ever-decreasing transverse cross-sectional flow area are of rectangular configuration. The heat exchanger has an inlet side and an outlet side located opposite to the inlet side. The cooling passages extend between the inlet side and the outlet side and each of the inlet side and the outlet side is of rectangular configuration. The inlet section has a third inlet portion having a first transitional transverse cross-sectional flow area that transitions from a circle, at one end, to define the inlet and at the other end, a rectangle. The other end of the third portion in registry with and connected to one of the sets of four sidewalls forming the first part of inlet portion. The one outlet portion is a first outlet portion and the outlet section has a second outlet portion situated such that the first outlet portion is located between the second outlet portion and the heat exchanger. The second outlet portion has a second transitional transverse cross-section flow area transitioning from a circle, at one end, to define the outlet and at the other end, a rectangle. The other end of the second outlet portion is in registry with and connected to a further of the sets of four sidewalls forming the first outlet portion.
[0010] In a specific embodiment, another of the sets of four sidewalls forming the second inlet portion, at opposite ends, is in registry with and connected to the one of the sets of four sidewalls and the inlet side of the heat exchanger. The further of the sets of four sidewalls forming the first outlet portion, at opposite ends, is in registry with and connected to the other end of the second outlet portion and the outlet side of the heat exchanger.
[0011] In order to further reduce the pressure drop resulting from swirl within the gas flow, the first inlet portion can be subdivided into a first set of subpassages by a first set of partition elements oriented such that each of the subpassages is of rectangular configuration. The second inlet portion can be subdivided into a second set of subpassages by a second set of partition elements oriented such that each of the subpassages is of
rectangular configuration. The second set of subpassages have more subpassages than the first set of subpassages. The first outlet portion can likewise be subdivided into a third set of subpassages by a third set of partition elements. The first set of partition elements, the second set of partition elements and the third set of partition elements are connected to the sidewalls and rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls. In a specific embodiment, the first set of subpassages has four subpassages and the second set of subpassages has twenty- four subpassages.
[0012] An embodiment of the present invention also provides a compressed gas cooling apparatus in which the inlet section comprises one portion having at least one sidewall forming an ever-increasing transverse cross- sectional flow area. Partition elements subdivide the ever-increasing transverse cross-sectional flow area into a plurality of subpassages, each having ever-increasing transverse cross-sectional sub-flow areas so that velocity of the flow of the gas gradually decreases as the gas flows through the inlet section. The sub-flow areas reduce separation of the flow of the gas from the at least one sidewall, due to swirl imparted into the flow of the gas from the upstream compression stage, thereby reducing pressure drop. The outlet section comprises an outlet portion of ever-decreasing transverse cross-sectional flow area for flow of the gas from the heat exchanger to the outlet so that the velocity of the flow of the gas
gradually increases as the gas flows in the outlet section to also reduce pressure drop.
[ 0013 ] In such embodiment, the inlet portion and the outlet portion are formed by sets of four sidewalls connected to one another such that the ever-increasing transverse cross-sectional flow area and the ever- decreasing transverse cross-sectional flow area are of rectangular configuration. The subpassages are each of rectangular configuration. The heat exchanger has an inlet side, an outlet side located opposite to the inlet side, the cooling passages that extend between the inlet side and the outlet side. Each of the inlet side and the outlet side is of rectangular configuration. The at least one sidewall of the inlet portion is one of the sets of four sidewalls. A further of the sets of four sidewalls form the outlet portion. The inlet portion is a first inlet portion and the outlet portion is a first outlet portion. The inlet section has a second inlet portion and the outlet section has a second outlet portion. The second inlet portion has a first transitional transverse cross-sectional flow area transitioning from a circle, at one end, to define the inlet and at the other end, a rectangle. The other end of the second inlet portion in registry with the one of the sets of four sidewalls forming the first inlet portion. Similarly, the second outlet portion has a second transitional transverse cross-section flow area
transitioning from a circle, at one end, to define the outlet and at the other end, a rectangle. The other end of the second outlet portion is in registry with the further of the sets of four sidewalls.
[0014] The one of the sets of four sidewalls forming the first inlet portion is connected to and in registry with the inlet side of the heat exchanger at a location of the inlet section opposite to the second inlet portion. The further of the sets of four sidewalls forming the first outlet portion is connected to and in registry with the outlet side of the heat exchanger at a location of the outlet section opposite to the second outlet portion. The partition elements of the first inlet portion can be a first set of partition elements and the subpassages are a first set of subpassages and the first outlet portion has a second set of partition elements that form a third set of subpassages of rectangular configuration. The first set of partition elements and the second set of partition elements are connected to the sidewalls. Rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls.
[0015] In any embodiment of the present invention, the heat exchanger can be of cross-counter flow arrangement. The cooling passages are formed between a plurality of parallel fins oriented at right angles with respect to the inlet side and the outlet side of the heat exchanger. The coolant passages are formed by coolant tubes that penetrate the parallel fins for circulation of the coolant and are in an orthogonal orientation with respect to the parallel fins.
[ 0016 ] Preferably, the coolant tubes comprise a set of inlet coolant tubes, a first set of intermediate coolant tubes, a second set of intermediate coolant tubes and a set of outlet coolant tubes. These inlet, intermediate and outlet coolant tubes are arranged to provide four passes within the heat exchanger. The heat exchanger has two end portions located opposite to one another and two spaced, transversely extending top and bottom panels connecting the end portions and forming the inlet side and the outlet side of the heat exchanger. An inlet plenum and an outlet
plenum are situated, side by side, at one of the two end portions and are in flow communication with the inlet
coolant tubes and the outlet coolant tubes, respectively, to introduce the coolant into the inlet coolant tubes and to discharge the coolant from the outlet coolant tubes.
Reversal plenums are located at the end portions of the heat exchanger and are configured such that coolant from the inlet tubes flows into the first set of intermediate coolant tubes at the other of the end portions, after
having traversed the heat exchanger. The coolant then flows from the first set of intermediate coolant tubes flows into the second set of intermediate coolant tubes at the one of the end portions, after having traversed the heat exchanger. Subsequently, coolant from the second set of intermediate coolant tubes flows into the set of outlet coolant tubes, after having traversed the heat exchanger and thereafter, flows from the set of outlet coolant tubes into the outlet plenum.
[0017] The heat exchanger can have a condensate disengagement chamber located between the outlet side and the coolant tubes and the parallel fins to allow condensed water to separate from the compressed gas passing through the heat exchanger. An elongated, tube-like drain is located at the bottom of the condensate disengagement chamber to collect the condensed water separated from the gas and to discharge the condensed water from the heat exchanger .
[0018] Further, within the heat exchanger, the coolant tubes can be connected to and supported at their ends by two opposed tube sheets .
Brief Description of the Drawings
[0019] While the specification concludes with claims distinctly pointing out the subject matter that Applicants regard as their invention, it is believed that the invention will be better understood when taken in
connection with the accompanying drawings in which:
[0020] Fig. 1 is a perspective view of a compressed gas cooling apparatus of the present invention;
[0021] Fig. 2 is an exploded, perspective view of an inlet section used in the apparatus illustrated in Fig. 1;
[0022] Fig. 3 is a sectional, perspective view of the inlet section used in the apparatus illustrated in Fig. 1 taken along line 3-3 of Fig. 1 ;
[0023] Fig. 4 is a perspective view of an alternative embodiment of a compressed gas cooling apparatus of the present invention; [0024] Fig. 5 is an exploded, perspective view of an inlet section used in the apparatus illustrated in Fig.4.
[0025] Fig. 6 is a sectional perspective view of the inlet section used in the apparatus illustrated in Fig. 1 taken along line 6-6 of Fig 4 ;
[0026] Fig. 7 is an exploded, perspective view of an outlet section used in the apparatus illustrated in Figs. 1 and 4 ;
[0027] Fig. 8 is a top plan view of a heat exchanger in accordance with the present invention that is used in the apparatus illustrated in Figs. 1 and 4;
[0028] Fig. 9 is a fragmentary, sectional perspective view of the heat exchanger illustrated in Fig. 8 taken along line 9-9 thereof, showing fins, cooling passages and coolant tubes used within the heat exchanger; and
[0029] Fig. 10 is a sectional, perspective view of the heat exchanger used in the apparatus illustrated in Figs. 1 and 4 with the fins removed to illustrate the coolant tubes, inlet, outlet and reversal plenums and a condensate
disengagement chamber and drain thereof.
Detailed Description
[0030] With reference to Figure 1, a compressed gas cooling apparatus 1 in accordance with the present
invention is illustrated. As mentioned above, such
apparatus can function as an intercooler between
compression stages or an after-cooler to cool the gas discharged from a compression stage to be used in
downstream processing. Apparatus 1 has an inlet section 2, an outlet section 3 and a heat exchanger 4 connecting the inlet section 2 to the outlet section 3. The inlet section 2 has an inlet 10 to receive a gas flow "A" from an upstream compression stage, not illustrated. The upstream compression stage could be a centrifugal compressor or an axial compressor. In either case, the gas flow indicated by arrowhead "A" entering the inlet 10 has a swirl or a rotational component to the flow designated by curved arrowhead "B". Such swirl is imparted to the flow by the rotational components of the compressor, for instance, the impeller of a centrifugal compressor.
[0031] The gas flow "A", after having been cooled in the heat exchanger 4 is discharged from an outlet 12 of the outlet section 3 as a cooled gas flow shown as arrowhead "C" .
[0032] With additional reference to Figures 2 and 3, inlet section 2 is provided with a first inlet portion 14, a second inlet portion 16 and optionally, a third inlet portion 18. As is apparent, all of these portions have an ever increasing transverse cross-sectional flow area that will act to gradually reduce the velocity of the gas flow before entering the heat exchanger 4. This will reduce pressure drop or loss in the flow due to turbulence that would otherwise be induced in the gas flow due to a sudden enlargement in cross-sectional flow area from the inlet opening 10. However, the pressure drop or loss in the gas flow also arises from the swirl "B" introduced into the flow by the upstream compressor. This "swirl" or rotation in the flow tends to cause the gas to accumulate on one side of the inlet section 2. This accumulation in turn creates a high pressure area and an adjacent low pressure area. As a result, a separation of the gas flow appears at wall regions of the inlet portion towards the adjacent low pressure region which in turn results in a backward circulation of the gas flow leading to an increase in pressure drop in the gas flow.
[0033] The first inlet portion 14 is formed by a set of four sidewalls 20, 22, 24 and 26 that are connected to one another such that the ever-increasing transverse cross- section flow area is of rectangular configuration. The second inlet portion 16 is formed by another set of four sidewalls 28, 30, 32 and 34 that are connected to one another to again form an ever-increasing transverse cross- sectional flow are of rectangular configuration.
Specifically, the swirl "B" will tend to cause the gas flow "A" to accumulate along sidewalls 26 and 34 of the first and second sections 14 and 16 and portions of adjacent sidewalls 20, 24 and 28,32 located close to the sidewalls 26 and 34. This will create a high pressure field within the gas flow "A" at such sidewall regions. In more central regions of the first and second sections 14 and 16, located at a distance from the sidewalls 26 and 34, the flow is not subject to such accumulation and therefore, has a lower pressure. As mentioned above, this pressure difference will potentially cause recirculation of the gas flow "A" from the higher to the lower pressure regions resulting in a pressure drop.
[0034] However, as can best be seen in Figure 3, the ever-increasing transverse cross sectional flow area of the second inlet portion 16 increases at a greater rate than that of the first inlet portion 14. The effect of this is that the velocity of the gas flow through the first inlet portion 14 will decrease to a lesser extent than the gas flow within the second inlet portion 16. The resulting higher velocity of the gas flow within the first inlet portion 14 will tend to reduce the separation of the gas flow from the walls of the inlet section 2 and allow the swirl "B" to dissipate somewhat before the gas flow reaches the second inlet portion 16. Since flow velocity is also decreasing along the length of the second inlet portion 16, pressure drop in the gas flow that otherwise would have been produced by the swirl "B" and a sudden increase in area will be reduced. The second inlet portion abuts the heat exchanger 4 and thereby also serves to distribute the gas flow across the heat exchanger 4.
[0035] In order to best reduce the pressure drop
resulting from the swirl "B", the first and second sections 14 and 16 are preferably designed to lie tangent to a bell- shaped curve given by the formula for an ellipse (bell- shape) ( (x-i) 2/a2) + ( (y-j ) 2/b2) = 1 where (i,j) is the centre of the ellipse, a and b are the half distances on x and y axes respectively. First section 14 would originate from the apex of such bell shape and second section 16 would terminate at the mount of such bell shape. Even more preferably, first section 14 has an aspect ratio of between 0.4 and 0.5. This aspect ratio is measured by dividing the maximum width of first section 14, as seen at the juncture of the first section 14 with the second section 16, by its length. The second section 16 preferably has an aspect ratio of between 0.2 and 0.4. This aspect ratio is
measured by dividing the maximum width of second section 16, as seen at the juncture of the second section 16 with the heat exchanger 4, by its length.
[0036] While the first and second inlet portions 14 and 16 alone will tend to reduce pressure drop in the gas flow for reasons mentioned above, preferably, the rectangular cross-sectional flow areas of the first inlet portion 14 is divided into a first set of subpassages, for example subpassage 36 and the second inlet portion 16 is subdivided into a second set of subpassages, for example subpassage 38. These rectangular subdivisions serve to reduce pressure drop further by preventing gas flow from accumulating on one side of the inlet portion 2 as a result of the swirl "B". The first set of subpassages 36 are formed by a first set of partition elements 40 and 42, positioned at right angles to one another and the second set of subpassages 38 are formed from sets of partition elements 40 and 42 and 44 and 46. Partition elements 40 and 42 extend the length of the first inlet portion 14 and the second inlet portion 16. Partition elements 44 and 46 are confined to the second inlet portion 16 and are positioned at right angles to one another. As illustrated each of the subpassages 36 and 38 are of rectangular configuration and are each of ever
increasing area.
[ 0037 ] The partition element 40 is connected along its edges to sidewalls 20, 24 and 28, 32; and the partition element 42 is connected along its edges to sidewalls 22, 26; and 30, 34. Further, the partition elements 44 are connected to sidewalls 28 and 32 and the partition elements 46 are connected to sidewalls 30 and 34. These connections are preferred in order to help maintain structural
integrity of the first inlet portion 14 and the second inlet portion 16 and are normally in tension during use of the apparatus 1. Further structural integrity is provided by frame-like stiffing members 48 connected to the set of sidewalls 20, 22, 24 and 26 forming the first inlet portion 14 and to sidewalls 28, 30, 32 and 34 forming the second inlet portion 16. As can be appreciated, such connections of the partition elements and the use of the frame-like stiffing members to reduce the thickness and weight of the sidewalls 20 through 34 that are necessary to contain compressed gases at high pressure.
[0038] As illustrated, the second inlet portion 16 has more subpassages 38 than the subpassages 36 of the first inlet portion 14. Preferably there are 24 of such
subpassages 38 as compared with the four subpassages 36. A major reason for this is that since the first inlet portion 14 has a smaller cross-section than the second inlet portion 16, there is less stress and therefore, fewer partition elements are required in the first inlet portion for structural integrity.
[0039] Although first inlet section 14 could simply be provided with a circular opening to form the inlet 10, preferably, the third inlet portion 18 is provided having a transitional transverse, cross-sectional flow area that transitions from the circular inlet opening 10, at one end and a rectangle at the other end. The sidewalls 50 thereof are therefore, curved at the inlet opening 10 and are planar at the other end thereof to form the rectangle.
This again helps to lower pressure drop by avoiding an abrupt transition between the circular inlet opening 10 and the rectangular cross-sectional flow areas provided by the first inlet portion 14 and the second inlet portion 16.
[0040] Preferably, the sidewalls 50 are connected to and in registry with the sidewalls 20, 22, 24 and 26 of the first inlet portion 14. The sidewalls 20, 22, 24 and 26 are also preferably connected to an in registry with the sidewalls 28, 30, 32 and 34 of the second inlet portion 16. The sidewalls 28, 30, 32 and 34 are connected to and in registry with the inlet side 106 of the heat exchanger 4. It is possible, however to provide a spacer section having a uniform, rectangular cross-sectional flow area between the second inlet section 16 and the heat exchanger 4.
Likewise it is also possible to provide such a spacer section between either or both of the first inlet section 14 and the second inlet section 16 or between the third inlet portion 18 and the first inlet portion 14.
[0041] With reference to Figures 4 and 5, a compressed gas cooling apparatus 1' is illustrated that is an
alternative embodiment of the apparatus 1. Apparatus 1' differs from apparatus 1 in that it is provided with an inlet section 2' having a first inlet portion 52 of ever increasing cross-sectional flow area and a second inlet portion 54 of similar configuration to the third inlet portion 18 of apparatus 1.
[0042] First inlet portion 52 is formed by a set of four sidewalls 56, 58, 60 and 62 that are connected to one another such that the ever-increasing transverse cross- section flow area is of rectangular configuration. Again, although a simple inlet opening could be provided, the second inlet portion 54 provided further pressure drop by provision of its transitional transverse cross-section flow area that transitions from the circular inlet opening 10', at one end and a rectangle at the other end. The sidewalls 64 thereof are therefore, curved at the inlet opening 10' and are planar at the other end thereof to form the rectangle. The sidewalls 64, at the other end of second inlet portion 54 are connected to an in registry with sidewalls 56, 58, 60 and 62 of the first inlet portion 56.
[0043] With additional reference to Figure 6, pressure drop within the inlet section 2' is reduced by provision of the ever-increasing transverse cross-section flow area provided by the first inlet portion 52. The pressure drop due to swirl is reduced by means of a set of partitions 66 and 68, positioned at right angles with respect to one another and that subdivide the transverse cross-sectional flow area into subpassages, for instance subpassage 70, each of ever increasing transverse cross sectional flow area. The partition elements 66 and 68 prevent the formation of a high pressure wall region, resulting from the swirl in the flow, from influencing the subflows in adjacent subpassages 70.
[0044] The partitions 66 and 68 are also connected to the sidewalls 56, 60 and 58, 62, respectively, to add to the structural integrity of the first portion 52 of the inlet section 2'. Additionally, optional frame-like stiffening members 72 connected to the outer surfaces of the sidewalls 56, 58, 60 and 62 add to the structural integrity and strength of the first portion 52.
[0045] With additional reference to Figure 7, outlet section 3 again has an ever decreasing transverse cross- section flow area to allow the velocity of the flow to gradually increase. The design of the outlet section 3 is less critical in decreasing pressure drop than the inlet sections 2 and 2' of the apparatus 1 and 1', respectively. In fact, the illustrated outlet section 3 is of the same design in both apparatus 1 and 1' . Alternatively, the outlet section 3 could have the same design as either of the inlet sections 2 and 2' .
[0046] The illustrated outlet section 3 is preferably provided with a first outlet portion 74 and a second outlet portion 76. The first outlet portion 74 is formed by a set of four sidewalls 78, 80, 82 and 84 connected together to provide a rectangular, transverse cross-section flow area. Although the first outlet portion 74 could terminate in an outlet opening, preferably, to reduce pressure drop, the second outlet portion 76 has a second transitional
transverse cross-section flow area formed by a set of four sidewalls 86, 88, 90 and 92 that transitions from a circle, at one end, to define an outlet 94 from which the outlet stream "C" is discharged and at the other end, a rectangle. Sidewalls 86, 88, 90 and 92 are connected to and in
registry with the four sidewalls 78, 80, 82 and 84 forming the first outlet portions 74.
[0047] Preferably, for purposes of structural integrity, sets of partitions 96 and 98 are provided that are
connected to sidewalls 80, 84 and sidewalls 78, 82, respectively. Additionally, rectangular frame-like members 100 can be connected to the sidewalls 78, 80, 82 and 84 to provide additional strength.
[0048] With additional reference to Figure 8, heat exchanger 4 is of common design with respect to apparatus 1 and apparatus 1' and functions to remove the heat of compression from the incoming gas stream "A" by providing indirect heat exchange between a cooling fluid and the gas stream. The cooling fluid, which can be water, enters through an inlet 102 and is discharged from an outlet 104. As illustrated in Figure 1, heat exchanger 4 connects the inlet section 2 to the outlet section 3 with respect to apparatus 1. Similarly, heat exchanger 4 also connects inlet section 2' to outlet section 3 in apparatus 1' . Heat exchanger 4 is provided with an inlet side 106 connected to inlet sections 2 and 2' and an outlet side 108 connected to outlet section 3. As mentioned above, the connections need not be direct and rectangular spacer-like elements could be provided within such sections. The gas to be cooled enters the heat exchanger 4 from the inlet sections 2 and 2' at the inlet side 106 and the cooled gas is discharge from the heat exchanger 4 from the outlet side 108 to the outlet section 3.
[0049] As can best be seen in Figure 9, the indirect heat exchange within heat exchanger 4 is accomplished by means gas passages 110 that are formed between a series of parallel, fin-like plate elements 112. The fin-like plate elements 112 are penetrated by a set of outlet coolant tubes 122 which provide the coolant passages for the coolant. Although not illustrated, the fin-like plate elements 112 are also penetrated by other sets of coolant tubes designated by reference numbers 116, 118 and 120 and to be discussed hereinafter. In this regard, inlet side 106 is an open rectangular area that is framed to receive the gas flow "A" and pass into the gas passages 110.
Similarly, the outlet side 108 is an open rectangular area that is framed to discharge the gas flow "A", after having been cooled, to the outlet section 3. In the illustrated apparatus 1 and 1', the rectangular areas are equal to those provided by inlet section 2 and 2' and outlet section 3.
[0050] With additional reference to Figure 10, the coolant tubes comprise a set of inlet coolant tubes 116, first and second sets of intermediate coolant tubes 118 and 120 and a set of outlet coolant tubes 122. The
aforementioned coolant tubes are supported at opposite ends by perforated tube sheets 124 and 126 and at intermediate locations by the fin-like plate elements 112. Optional support plates 128 are connected at opposite ends to transversely extending top and bottom panels 134 and 136 to assist in maintaining structural integrity against internal pressures. It is to be noted that the heat exchanger 4 has two end portions 130 and 132 located opposite to one another that are connected the two spaced, transversely extending top and bottom panels 134 and 136 thereby forming the inlet side 106 and the outlet side 108 of the heat exchanger which are rectangular openings to the heat
exchanger by virtue of such construction. A base 138 is connected to the bottom panel 136 to elevate the bottom panel 132 above ground level.
[ 0051 ] Contained within end portion 130 is an inlet plenum 140 and an outlet plenum 142 that are located side- by-side, are situated within end portion 130. Inlet plenum 140 and outlet plenum 142 are in flow communication with the inlet coolant tubes 116 and the outlet coolant tubes 122, respectively. The coolant is introduced into the inlet coolant tubes 116 from the inlet 102 in direction of the arrowhead "D" and is discharged from the outlet coolant tubes through the outlet plenum 142 and to the outlet 104 in direction of arrowhead "E". A reversal plenum 144 is located between the inlet plenum 140 and the outlet plenum 142 and two reversal plenums 146 and 148 are formed within the other end portion 132 by provision of a dividing plate 150. The coolant enters the inlet tubes 116 from the inlet plenum 140. After traversal of the heat exchanger, the coolant reverses flow direction within reversal plenum 146 in the direction of arrowhead "G" and then flows through the first set of intermediate coolant tubes 118 until the coolant reaches the reversal plenum 144. Within reversal plenum 144, the coolant again reverses direction and flows through the second set of intermediate coolant tubes 120 until reaching reversal plenum 148. At reversal plenum 148, the coolant again reverses direction in the direction of arrowhead "H" and flows through the outlet coolant tubes 122 to the outlet plenum 142 from which the coolant is discharged from heat exchanger 4 from the outlet 104.
[0052] In case of such gases as air, the incoming air will contain water vapor that will be condensed by the coolant. In order to disengage the water, a disengagement chamber 152 is provided adjacent to the outlet side 108 of the heat exchanger 4. The disengaged water, collects in the bottom panel 136 and is discharged from openings 154 and 156 to an elongated, tube-like drain 158 located beneath the bottom panel 136 and adjacent the base 138 for discharge of the collected water.
[0053] While the present invention has been described with reference to preferred embodiments, as will occur to those skilled in the art, numerous changes, additions and omissions can be made without departing from the spirit and scope of the present invention as set forth in the appended claims .

Claims

We Claim:
1. A compressed gas cooling apparatus comprising:
an inlet section having an inlet to receive a gas from an upstream compression stage;
an outlet section having an outlet to discharge the gas, after having been cooled to a downstream compression stage;
a heat exchanger connecting the inlet section to the outlet section and having gas passages communicating between the inlet section and the outlet section for passage of the gas and coolant passages positioned in a heat transfer relationship with the gas passages for passage of a coolant to cool the gas passing through the gas passages through indirect heat exchange with a coolant; the inlet section comprising a first inlet portion and a second inlet portion, the first inlet portion located between the inlet and the second inlet portion and the second inlet portion located between the first inlet portion and the heat exchanger; and
each of the first inlet portion and the second inlet portion having an ever increasing transverse cross- sectional flow area, the ever increasing transverse cross- sectional flow area of the second inlet portion increasing at a greater rate than the first inlet portion so that the velocity of the flow of the gas gradually decreases as the gas flows through the inlet section to a lesser extent in the first inlet portion than the second inlet portion and separation of the flow of the gas from sidewalls of each of the first inlet portion and the second inlet portion, due to swirl imparted into the flow of the gas from the upstream compression stage, is inhibited to reduce pressure drop; and
the outlet section comprising one outlet portion of ever-decreasing transverse cross-sectional flow area for flow of the gas from the heat exchanger to the outlet such that velocity of the flow of the gas gradually increases to also reduce pressure drop.
2. The apparatus of claim 1, wherein:
the first inlet portion, the second inlet portion and the one outlet portion are formed by sets of four sidewalls connected to one another such that the ever-increasing transverse cross-sectional flow area and the ever- decreasing transverse cross-sectional flow area are of rectangular configuration;
the heat exchanger has an inlet side, an outlet side located opposite to the inlet side, the cooling passages extend between the inlet side and the outlet side and each of the inlet side and the outlet side is of rectangular configuration;
the inlet section has a third inlet portion having a first transitional transverse cross-sectional flow area transitioning from a circle, at one end, to define the inlet and at the other end, a rectangle, the other end of the third portion in registry with and connected to one of the sets of four sidewalls forming the first inlet portion; the one outlet portion is a first outlet portion;
the outlet section has a second outlet portion situated such that the first outlet portion is located between the second outlet portion and the heat exchanger, the second outlet portion having a second transitional transverse cross-section flow area transitioning from a circle, at one end, to define the outlet and at the other end, a rectangle; and
the other end of the second outlet portion is in registry with and connected to a further of the sets of four sidewalls forming the first outlet portion.
3. The apparatus of claim 2, wherein
another of the sets of four sidewalls forming the second inlet portion, at opposite ends, is in registry with and connected to the one of the sets of four sidewalls and the inlet side of the heat exchanger; and
the further of the sets of four sidewalls forming the first outlet portion , at opposite ends, is in registry with and connected to the other end of the second outlet portion and the outlet side of the heat exchanger.
4. The apparatus of claim 2, wherein:
the first inlet portion is subdivided into a first set of subpassages by a first set of partition elements oriented such that each of the subpassages is of
rectangular configuration;
the second inlet portion is subdivided into a second set of subpassages by a second set of partition elements oriented such that each of the subpassages is of
rectangular configuration;
the second set of subpassages having more subpassages than the first set of subpassages.
5. The apparatus of claim 4, wherein:
the first outlet portion is subdivided into a third set of subpassages by a third set of partition elements; the first set of partition elements, the second set of partition elements and the third set of partition elements are connected to the sidewalls; and
rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls .
6. The apparatus of claim 4, wherein the first set of subpassages has four subpassages and the second set of subpassages has twenty-four subpassages.
7. A compressed gas cooling apparatus comprising:
an inlet section having an inlet to receive a gas from an upstream compression stage;
an outlet section having an outlet to discharge the gas, after having been cooled to a downstream compression stage;
a heat exchanger connecting the inlet section to the outlet section and having gas passages communicating between the inlet section and the outlet section for passage of the gas and coolant passages positioned in a heat transfer relationship with the gas passages for passage of a coolant to cool the gas passing through the gas passages through indirect heat exchange with a coolant; the inlet section comprising one portion having at least one sidewall forming an ever-increasing transverse cross-sectional flow area and partition elements
subdividing the ever-increasing transverse cross-sectional flow area into a plurality of subpassages, each having ever-increasing transverse cross-sectional sub-flow areas so that velocity of the flow of the gas gradually
decreases as the gas flows through the inlet section and the sub-flow areas reduce separation of the flow of the gas from at least one sidewall, due to swirl imparted into the flow of the gas from the upstream compression stage, thereby reducing pressure drop; and
the outlet section comprising an outlet portion of ever-decreasing transverse cross-sectional flow area for flow of the gas from the heat exchanger to the outlet so that the velocity of the flow of the gas gradually
increases as the gas flows in the outlet section to also reduce pressure drop.
8. The apparatus of claim 7, wherein:
the inlet portion and the outlet portion are formed by sets of four sidewalls connected to one another such that the ever-increasing transverse cross-sectional flow area and the ever-decreasing transverse cross-sectional flow area are of rectangular configuration;
the subpassages are each of rectangular configuration; the heat exchanger has an inlet side, an outlet side located opposite to the inlet side, the cooling passages extend between the inlet side and the outlet side and each of the inlet side and the outlet side is of rectangular configuration;
the at least one sidewall of the inlet portion is one of the sets of four sidewalls;
a further of the sets of four sidewalls form the outlet portion;
the inlet portion is a first inlet portion, the outlet portion is a first outlet portion, the inlet section has a second inlet portion and the outlet section has a second outlet portion; the second inlet portion has a first transitional transverse cross-sectional flow area transitioning from a circle, at one end, to define the inlet and at the other end, a rectangle, the other end of the first inlet portion in registry with the one of the sets of four sidewalls forming the first inlet portion;
the second outlet portion has a second transitional transverse cross-section flow area transitioning from a circle, at one end, to define the outlet and at the other end, a rectangle; and
the other end of the second outlet portion is in registry with the further of the sets of four sidewalls.
9. The apparatus of claim 8, wherein:
the one of the sets of four sidewalls forming the first inlet portion is connected to and in registry with the inlet side of the heat exchanger at a location of the inlet section opposite to the second inlet portion; and the further of the sets of four sidewalls forming the first outlet portion is connected to and in registry with the outlet side of the heat exchanger at a location of the outlet section opposite to the second outlet portion.
10. The apparatus of claim 8 wherein:
the partition elements of the first inlet portion are a first set of partition elements and the subpassages are a first set of subpassages;
the first outlet portion has a second set of partition elements that form a third set of subpassages of
rectangular configuration;
the first set of partition elements and the second set of partition element are connected to the sidewalls; and rectangular, frame-like stiffening members are connected to outer surfaces of each of the sets of the four sidewalls .
11. The apparatus of claim 2 or claim 4 or claim 5 or claim 8 or claim 10, wherein:
the heat exchanger is of cross-counter flow
arrangement;
the cooling passages are formed between a plurality of parallel fins oriented at right angles with respect to the inlet side and the outlet side of the heat exchanger; and the cooling passages are formed by coolant tubes that penetrate the parallel fins for circulation of the coolant and are in an orthogonal orientation with respect to the parallel fins .
12. The apparatus of claim 11, wherein:
the coolant tubes comprise a set of inlet coolant tubes a first set of intermediate coolant tubes, a second set of intermediate coolant tubes and a set of outlet coolant tubes arranged to provide four passes within the heat exchanger;
the heat exchanger has two end portions located opposite to one another and two spaced, transversely extending top and bottom panels connecting the end portions and forming the inlet side and the outlet side of the heat exchanger;
an inlet plenum and an outlet plenum are located side- by-side, are situated at one of the two end portions and are in flow communication with the inlet coolant tubes and the outlet coolant tubes, respectively, to introduce to the coolant into the inlet coolant tubes and to discharge the coolant from the outlet coolant tubes; and
reversal plenums are located at the end portions of the heat exchanger and are configured such that coolant from the inlet tubes flows into the first set of
intermediate coolant tubes at the other of the end portions, after having traversed the heat exchanger, coolant from the first set of intermediate coolant tubes flows into the second set of intermediate coolant tubes at the one of the end portions, after having traversed the heat exchanger, coolant from the second set of intermediate coolant tubes flows into the set of outlet coolant tubes, after having traversed the heat exchanger and thereafter, flows from the set of outlet coolant tubes into the outlet plenum.
13. The apparatus of claim 11, wherein the heat exchanger has a condensate disengagement chamber located between the outlet side and the coolant tubes and the parallel fins to allow condensed water to separate from the compressed gas passing through the heat exchanger and an elongated, tubelike drain located at the bottom of the condensate
disengagement chamber to collect the condensed water
separated from the gas and to discharge the condensed water from the heat exchanger.
14. The apparatus of claim 12, wherein the heat exchanger has a condensate disengagement chamber located between the outlet side and the coolant tubes and the parallel fins to allow condensed water to separate from the compressed gas passing through the heat exchanger and an elongated, tubelike drain located at the bottom of the condensate
disengagement chamber to collect the condensed water separated from the gas and to discharge the condensed water from the heat exchanger.
15. The apparatus of claim 13, wherein the coolant tubes are connected to and supported at their ends by two opposed tube sheets .
PCT/US2013/037741 2012-06-29 2013-04-23 Compressed gas cooling apparatus WO2014003880A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201380033128.1A CN104364599A (en) 2012-06-29 2013-04-23 Compressed gas cooling apparatus

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13/538,387 2012-06-29
US13/538,387 US20140000841A1 (en) 2012-06-29 2012-06-29 Compressed gas cooling apparatus

Publications (1)

Publication Number Publication Date
WO2014003880A1 true WO2014003880A1 (en) 2014-01-03

Family

ID=48326438

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2013/037741 WO2014003880A1 (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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9528427B2 (en) 2013-12-26 2016-12-27 Mazda Motor Corporation Intake system for engine

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9857109B2 (en) * 2008-01-02 2018-01-02 Johnson Controls Technology Company Heat exchanger
EP3265727A1 (en) * 2015-03-06 2018-01-10 Ariston Thermo S.p.A. Air conveyor for heat pump
US20170089643A1 (en) * 2015-09-25 2017-03-30 Westinghouse Electric Company, Llc. Heat Exchanger
US10914319B2 (en) * 2016-02-26 2021-02-09 Mitsubishi Heavy Industries Compressor Corporation Cooling device and compressor system
DE102016112453A1 (en) * 2016-07-07 2018-01-11 Man Diesel & Turbo Se Geared turbine machine
EP3339792B1 (en) * 2016-12-20 2020-03-18 Alfa Laval Corporate AB Header for a heat exchanger and a heat exchanger
EP3348947B1 (en) 2017-01-13 2020-11-04 HS Marston Aerospace Limited 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
IT201700087168A1 (en) * 2017-07-28 2019-01-28 Eurochiller S R L Air condenser
US11255615B2 (en) 2018-01-23 2022-02-22 Hamilton Sundstrand Corporation Heat exchanger flexible manifold
US10443959B2 (en) * 2018-03-16 2019-10-15 Hamilton Sundstrand Corporation Integral heat exchanger manifold guide vanes and supports
US11686530B2 (en) 2018-03-16 2023-06-27 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold
WO2019183312A1 (en) 2018-03-23 2019-09-26 Modine Manufacturing Company High pressure capable liquid to refrigerant heat exchanger
JP7013316B2 (en) * 2018-04-26 2022-01-31 三菱重工コンプレッサ株式会社 Centrifugal compressor
US10995997B2 (en) * 2018-06-26 2021-05-04 Hamilton Sunstrand Corporation Heat exchanger with integral features
US11371780B2 (en) * 2018-06-26 2022-06-28 Hamilton Sundstrand Corporation Heat exchanger with integral features
US11333438B2 (en) * 2018-06-26 2022-05-17 Hamilton Sundstrand Corporation Heat exchanger with water extraction
US11098966B2 (en) 2018-08-08 2021-08-24 Denso International America, Inc. Header tank for heat exchanger
US10926364B2 (en) 2018-10-03 2021-02-23 Hamilton Sundstrand Corporation Plate-fin heat exchanger core design for improved manufacturing
FR3089001B1 (en) * 2018-11-23 2021-07-30 Commissariat A L Energie Atomique Et Aux Energies Alternatives Method for producing a heat exchanger collector with hot isostatic compression (CIC), application to the production of absorbers for a concentrated solar thermal power plant
US11226158B2 (en) 2019-04-01 2022-01-18 Hamilton Sundstrand Corporation Heat exchanger fractal splitter
CN112032078B (en) * 2020-07-29 2021-09-03 武汉大学 Active high-efficient accuse temperature's efflux spray tube cooling system
US20220106046A1 (en) * 2020-10-06 2022-04-07 Honeywell International Inc. Pressure containment component for aircraft systems

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3392211A (en) * 1964-03-07 1968-07-09 Basf Ag Production of ethylene by thermal cracking of hydrocarbons
GB1190958A (en) * 1966-06-24 1970-05-06 Lummus Co Connector Duct
GB2090631A (en) * 1981-01-02 1982-07-14 Ingersoll Rand Co Intercoolers for gas compressor units
US4452216A (en) * 1982-09-27 1984-06-05 Allis-Chalmers Corporation Even temperature intercooler
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
EP0864839A2 (en) * 1997-03-11 1998-09-16 Behr GmbH & Co. Heat exchanger, more particularly supercharge air cooler, for automotive vehicle
US20030111209A1 (en) * 1999-01-20 2003-06-19 Hino Motors, Ltd. EGR cooler
US20100329895A1 (en) 2009-06-24 2010-12-30 Robert Leroy Baker Multistage compressor installation

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2106458A (en) * 1935-12-23 1938-01-25 Anemostat Corp Air distributing device
US2768814A (en) * 1950-10-27 1956-10-30 Frey Plate warmer exchanger
US4279297A (en) * 1978-10-16 1981-07-21 Gte Products Corporation Housing for ceramic heat recuperators and assembly
US4415024A (en) * 1980-11-05 1983-11-15 Joy Manufacturing Company Heat exchanger assembly
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
DE102009049483A1 (en) * 2009-10-15 2011-04-21 Modine Manufacturing Co., Racine Heat exchanger and seal arrangement for it

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3392211A (en) * 1964-03-07 1968-07-09 Basf Ag Production of ethylene by thermal cracking of hydrocarbons
GB1190958A (en) * 1966-06-24 1970-05-06 Lummus Co Connector Duct
GB2090631A (en) * 1981-01-02 1982-07-14 Ingersoll Rand Co Intercoolers for gas compressor units
US4452216A (en) * 1982-09-27 1984-06-05 Allis-Chalmers Corporation Even temperature intercooler
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
EP0864839A2 (en) * 1997-03-11 1998-09-16 Behr GmbH & Co. Heat exchanger, more particularly supercharge air cooler, for automotive vehicle
US20030111209A1 (en) * 1999-01-20 2003-06-19 Hino Motors, Ltd. EGR cooler
US20100329895A1 (en) 2009-06-24 2010-12-30 Robert Leroy Baker Multistage compressor installation

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9528427B2 (en) 2013-12-26 2016-12-27 Mazda Motor Corporation Intake system for engine
DE102014018765B4 (en) 2013-12-26 2019-09-19 Mazda Motor Corp. Inlet system for engine and method for controlling the flow rate of intake air

Also Published As

Publication number Publication date
US20140000841A1 (en) 2014-01-02
CN104364599A (en) 2015-02-18

Similar Documents

Publication Publication Date Title
US20140000841A1 (en) Compressed gas cooling apparatus
US8647076B2 (en) Multistage compressor installation
US5727623A (en) Dehumidifier having two heat exchangers
US9377226B2 (en) Evaporator and turbo chiller including the same
KR100487591B1 (en) Turbo compressor
US10514046B2 (en) Air management system for the outdoor unit of a residential air conditioner or heat pump
US6725912B1 (en) Wind tunnel and heat exchanger therefor
JP2009139078A (en) Indoor unit for air conditioner
CA2178221C (en) Cold air supply unit
JP4876868B2 (en) Turbo compressor
US6910349B2 (en) Suction connection for dual centrifugal compressor refrigeration systems
KR20080027174A (en) Composite heat-releasing device, cooling unit, and cooling apparatus and its assembly
JP4191477B2 (en) An arrangement for a multistage heat pump assembly.
JP6621187B2 (en) Refrigerator, compressor system
WO2019196959A1 (en) Fan and roof machine
US9470244B2 (en) Compressor with cooling function
US20110033306A1 (en) Cross-flow fan and air conditioner equipped with same
JP2014137219A (en) Cooler
JP6545424B1 (en) Air conditioner
US11959492B2 (en) Hybrid after cooling system and method of operation
CN219103781U (en) Plate heat exchanger, cooling liquid circulation system and electric automobile
US20230047198A1 (en) Induced draft heat rejection equipment with top mounted backward-curved centrifugal fans
JPS5928212Y2 (en) Heat exchanger for multi-stage turbo compressor
US20190111359A1 (en) Modular heat exchanger, moisture separator and pulsation dampener for a multi-stage fluid compressor
KR20070113910A (en) Indoor machine of slim type in air conditioner

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13721480

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13721480

Country of ref document: EP

Kind code of ref document: A1