US2280845A - Air compressor system - Google Patents

Air compressor system Download PDF

Info

Publication number
US2280845A
US2280845A US187704A US18770438A US2280845A US 2280845 A US2280845 A US 2280845A US 187704 A US187704 A US 187704A US 18770438 A US18770438 A US 18770438A US 2280845 A US2280845 A US 2280845A
Authority
US
United States
Prior art keywords
compressor
air
cooling medium
water
compression
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
US187704A
Inventor
Humphrey F Parker
Original Assignee
Humphrey F Parker
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 Humphrey F Parker filed Critical Humphrey F Parker
Priority to US187704A priority Critical patent/US2280845A/en
Application granted granted Critical
Publication of US2280845A publication Critical patent/US2280845A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/58Cooling; Heating; Diminishing heat transfer
    • F04D29/582Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06Cooling; Heating; Prevention of freezing
    • F04B39/062Cooling by injecting a liquid in the gas to be compressed

Description

April 28,1942. H. F. PARKER A 2,280,845
AIR COMPRESSOR SYSTEM f Filed Jan. 29. 1938 2 Sheets-Sheet l T T ORNE I6.
- April 28, 1942. H. F. Pimm-:R
AIR oMPREssoR SYSTEM 2 Sheets-Sheef 2 Filed Jam. 29, 1888 l VENTOR ATTOR/ VEK Patented Apr. 28, 1942 UNITED N STATES PATENT oF'FlcE g Amcommissoa SYSTEM, Humphrey F. Parker, Detroit, Mich. Application January 29, 193s, serial No. 181,704
1-1 claim. (ci. 23o-zot)` The present invention relates to methods of and apparatus for compressing air and other gases. A principal object of the invention is to reduce the temperature rise that accompanies adiabatic compression, thereby approaching the isothermal cycle more closely than has heretofore been practicable and reducing the power consumption necessary for a given output.
Further principal objects `of the invention are,
Y to increase the speed of operation of compressors,
thereby reducing their weight, bulk, initial cost and cost of installation; to increase the output of existing compressors by safely increasing the operating speeds thereof; to reduce the number of stages of compression, incompressing to very high pressures, without sacrifice in eiilciency; to eliminate deposits of carbon and gum upon valves and other parts of the system; to reduce templates injecting the cooling medium into the system in a thoroughly atomized state, and, before proceeding to a .descriptionf ofthe iherein disclosed embodiments ofthe invention', the following data is of interesty as bearing upon the magnitude of the change brought about 'by effective atomization in place of the spray injection previously used. v
Attention is erst invited to the identities involved in compressing one thousand cubic feet of air initially 50% saturated with moisture at 60Y F. to eight atmospheres absolute (103 lbs. per square inch gauge). Withk adiabatic compression, the temperature rise in vtliisicaseis 4305. F. giving, a iinal temperature` ofg490.". Itmay be supposed that a' quantity of water equal in weight to the air be intimately mixed with theair in a the quantity of cooling water necessary for a f given final temperature ofy the compressed gas;
to simplify the casting of compressor cylinders tained, in a broad sense, by introducing into the gas to be compressed a non-compressible heat absorbing and heat carrying medium, and then, afterA compression, in separating and removing this medium, and with it the greater part of the heat-of compression, from the compressed gas. 'The preferred medium is cold water, although in certain cases other liquids such as oil may be used. The liquid is passed through atominng means whereby it is' broken up intoa finelyv divided mist-like form, and is thereafter intimately mixed with the air or other gas to be compressed. By breaking up the liquid into globules suiiiciently small to remain suspended in the air, the ratio of surface to volume is made very large, and the time required for a given heat exchange between air and water very short, i. e. measurable in thousandths of a second.
The resulting system will be recognized as being of the wet type. and, in one sense, the present invention may be characterized as rendering the wet-compression principle, with its recognized thermodynamic advantages, applicable to modern high speed compressor requirements.
As mentioned above, the present invention conformfine enough to maintain substantial temperature equilibrium during compression. This quantity is arbitrarily assumed, andmoreor less water may be used. depending upon whether lower iinal temperatures are desired or a smaller consumption of cooling water. The weight of 1,000 cubic feet of air under the above conditions is 75.70 pounds. 'I'he same weight of water occupies 1.22 cubic feet, which represents one part in 820 of the uncompressed mixture or less than one per cent of the nal volume. The rst eiect of the injection of water is to saturate the air. 'I'his requires the conversion of .4 pound of waterl into vapor, leaving approximately 75 pounds which remain in the liquid state throughout compression. Assuming thev value of .25 for the speciiic heat of the air and vapor, thevcompression is accompanied by the generation of 48060 B. t. u.s of heat. This heat is now imparted to the` mixture of air and water, and resuits in a risein temperature of 86 F. 'Ihe final texiperatureof theair is thus 146 F. in place of 49 Y The above may be expressed in another way by statingthat, while the horsepower loss which accompanies adiabatic compressionis 27.4%, this loss is reduced by this invention, in the above case, to 5.5%. In actual practice the above theoretical loss for dry compressors is reduced by water jacketing the cylinder, but there neverl use of the same quantity of water in an aftercooler of the type described hereinafter will bringl the final temperature of the compressed air down to about 17 F. above the initial temperature of air and water. In conventional practice with after-coolers used in conjunction with dry" comv .10 inch.
An effective atomizing nozzle is capable of reducing a liquid to 'particles having a diameter of less than .001 inch. In the matter of heat absorptionmoreover, the advantage of the small particles varies inversely as the square of the diameter, so that anatomized particle possesses an advantage over the spray particle discussed above of the order of ten thousand to one.
Heat transfer is a function of temperature difference; ottime; of surface area; and of depth of penetration. Comparing now 'a body of a given volume with the same quantity of material divided into bodies of half the diameter, eight such bodies are required. The surface area in the first case is fr, while that in the second case is 81r(r/2) 2, or 2n, showing that, for a given volume, surface area increases directly as decrease in diameter. It is obvious, in a globule or sphere, that the necessary distance of penetration decreases directly as the radius, so that, for
a given temperature difference, the time required for heat exchange from the air to the vwater particles is reduced as a function of the square of an injector timed for the compression stroke only.
The invention is illustrated'in the following drawings, in which:
Figure 1 is a view in side elevation of a single stage compressor system embodying the invention;
Fig. 2 is a view in section of an atomizing nozzle which 'is preferably utilized in thesystem of Fig. 1;
Fig. 3 is a view in side elevation of a modied form of the invention, in which the cooling medium is recirculated;
Fig. 4 is a View in section of an unloader'valve preferably utilized in the system of Fig. 3;
Fig. 5 is a View in side elevation of a two stage compressor system embodying the invention;
Fig. 6 is a fragmentary view of a modification of the invention;
Fig. '7 is a view in section of an atomizing nozzle preferably used -in the system of Fig. 6; and,
Fig. 8 is a view in vertical section of a further modification of the invention.
the particle diameter, or, in the case discussed i above, to one ten-thousandth of the former time. With an improvement ofthis order possible, an
ample margin is available to increase speeds, if
desired, ten or twenty times. over the previous practice in fwet compression and still eiect a close approximation to complete heat transfer.
In previous attempts to practice wet compression, dilculty has been experienced with lubrication. This has been due to the actual presence of bodiesof watery within the cylinder, which washed off the lubricant from the walls., rInl the present invention, the lubrication requirements are comparable with those of a vsteam cylinder. As is well knownvthis calls for the use of more lubricant than an air compressor cylinder, but a quantity which is still entirely reasonable. This necessary extra oil could not be added in a cylinder operating on dry compression as it would result in carbonization or gumming of the valves. In the present invention, however, the nnal temperature is so low that nosuch trouble is encountered.
The present invention further contemplates a continuous injection, as distinguished from an Referring now to Fig. 1, an air compressor of the reciprocating type is shown at III. This comprises a cylinder I2 of the double acting type having an .air intake at I4 and an air outlet at I6. Automatic intake valves, which may be of any of the wellvknown types, are indicated at I8, and exhaust valves at 20. The piston (not shown) in the cylinder I2 is operated by the electric motor 22 which drives the flywheel 24 through belt 26. The compressor, as thus far described, may be identical with or comparable to compressors now in use.
Before being inducted into intake I4, in accordance with the present invention, the entering air is passed through the mixing chamber 28, which is provided with a plurality of atomizing nozzles 30. During the passage of the air or other fluid through the chamber 28, it is subjected to the atomized liquid, and a thorough mixing of the air and cooling liquid results. 'I'he term atomizing is used vin the present specification and claims to mean the breaking up of a liquid into very fine mist-like particles. Also the terms mixture," mixing and the like are used in the present specification and claims in example, a suitable nozzle is shown in Fig. 2 as' intermittent injection. By using continuous injection, the rate of injection of water is`comparable with that of the oil injection'in a Diesel engine, in which injection takes place only during about thirty degrees of crankshaft angle.`
The weight of oil injected in the case of thefDiesel is about one fifteenth of the air used, which is injected during about one-twelfth of a revocomprising a shell 3l havinga small 4orifice 33,
and a core 35, pressed into the shell. The core i hasa helical passage 31 cut in its cylindrical outer surface. vWater entering by the inlet pipe 39 is given a rotary motion by the helix, so that when forced through the orice 33 it spreads out into a cone and breaks up into minute particles. Water is supplied to these nozzles by the pipe 32, under pressure developed by the pump 34. As
shown, pump 34 is of the multi-cylinder type, ca`
pable o'fdeveloping a continuous, uniform pressure, and is driven by the motor 22 which drives the compressor. Accordingly, when the motor 22 and the compressor are stopped, the supply of water to the atomizing nozzles is stopped also.
'Ihe pump 34 draws cold water from any suitable source, and is provided with a iilter 36 and a pressure limiting relief valve 38. When water at a temperature below atmospheric is available,
By way of the mixing chamber 28 becomes in addition a precooler, and provides all the advantages of that device without a separateunit.
The air and Water mixture is drawn into cylinder I2 through intake valves I8, is compressed, and then discharged through exhaust valves 20 Y and outlet pipe I6 to the separator unit 40. Pref..
erably the air enters this at the top, tangentially. The body of the separator. surrounding the outlet pipe 42, which extends into the lower chamber 44, is filled with very fine copper Wool, i. e., very fine turnings 46, or other material adapted to provide a labyrinthine passage for the mixture. The mist-like particles of water strike the surfaces of the Wool, adherey to them, coalesce into drops, and fal-l into the collecting sump 48 at the bottom of chamber 44. The air, however, being less dense, moves on through the labyrlnthine passages into chamber 44 and out by way of outlet pipe 42. Sump 48 is provided with a water outlet 50 controlled by needle valve 52. The upper end of valve 52 is attached to an arm 63, one end of which is pivoted to the separator casing and the other end of which carries the float 55. Water collects in sump 48 until it begins to lift float 55 whereupon valve 52 is lifted and further water is discharged through outlet 50, without permitting the escape of any air or the loss of pressure.
The compressed air, freed from entrained moisture in the liquid phase, may now be delivered to a receiver and to the ldevices to be operated by it. It may be expected, however, to be saturated with water vapor at a temperature probably about 140 F. Since this air will cool considerably before reaching the devices to be operated by it, it may deposit water in the pipes and other parts of the system with undesirable results. This condition is usually alleviated by an after-cooler, ofthe surface condenser type. In the present case an after-,cooler of this type may be used, especially when applying the invention to an existing compressor where a sur-v face cooler is already in use. Preferably, however, in place of the conventional after-cooler, a mixing chamber is used similar to that previously described. This is shown at 54, and is equipped with sprays 56, which are supplied through pipe 32. Sprays 56 may be and preferably are duplicates of the previously described sprays 80. With this new after-cooler, the temperature of the air may readily be brought down to within ten degrees of that of the water, with the use of materially less Water than is necessary with aconventional after-cooler. l
`The cooled mixture of air and water globules now passes by pipe 58 to separator 60, which as shown, is similar to separator 40. The nal air, free from entrained moisture in either vapor or liquid phase, is discharged through pipe 18 for delivery, and the cooling water is released by needle valve I2 through outlet 10. Mixing chamber 54 is also provided with a sump shown at 80, and a drain 82, controlled by needle valve 84 and float 86 to dispose of liquid which may strikethe sides of the chamber and collect in the sump.
In the modification shown in Fig. 3, oilv is used preferably are constructed as ldescribed with ref-A erence to nozzles 30. The air and oil mixture is inducted into cylinder I2 as before by intake pipe I4, and is discharged by outlet pipe I6 into separator 206. This is essentially like separator 40 except that the needle valve 52 and its 'float control are omitted.- The separated oil, carrying most of the heat of compression, is then passed by way of the pipe 208 into the heat exchanger 2III. 'I'his is provided with a nest of tubes 2I2 through which cold water is circulated. The heat added to the oil in the compressor is thereby transferred to the water, and the oil, under in the case illustrated being steam supplied to the cylinder 2I6 from steam pressure line 2I8, under control of hand throttle 220.
Valve 2I4 is normally shut by spring 222 acting againstv the upper side of piston 224 to force valve element 226 onto its seat. Pipe 228 connects the chamber 230 beneath piston 224 to steam line 232, between throttle 220 and cylinder 2I6. When the throttle is opened, pressure is admitted not only to the cylinder 2I6 but also to the chamber 230 beneath piston 224, forcing the piston upwardly against springv 222 and opening valve element 226. When throttle 220 is closed, pressure is shut off from line 232 and from chamber 230, and spring 222 re-seats valve 226 and shuts off the line from separator 206.
It is common practice to equip an air compressor with an unloader valve which is designed to permit the driving engine and the compressor piston to remain in motion under frictional load only, the air load being removed by the operation of the valve. In compressors so equipped and embodying the present invention, it is necessary, or at least desirable, to shut oil the supply of liquid to the atomizers in the mixing chamber when the unloader is in operaiton. With this in view, valve 234 is incorporated in delivery line -236 to atomizers 204. This valve is normally held ber 250 is connected by pipe 252 with compressordelivery pipe 254 and lis subject to the pressure on the high side of the system. A spring 256 acts on diaphragm 258 and is adjusted so that it just balances the pressure on the diaphragm at the maximum pressure desired in the system.
,When the delivery pressure exceeds this gure,
the diaphragm is lifted, opening needle valve 260 and admitting pressure to chamber 262, thereby forcing valve 246 onto its seat 263 and shutting off the supply of intake air to the compressor. Chamber 262 is connected by pipe 264 with the upper side of piston 240, so that when valve 246 is closed, pressure acts on 'piston 240 and closes valve 234 also, shutting off the supply of liquid to nozzles 204.
Itwill be understood, of course, that this combination of an unloader valve such as 242, and a cooperating valve 234 may be used with the form of the invention shown in Fig. 1. In such case, the valve 234 will be placed in line 32, and valve 242 will be placed in line |4. Water will then be shut oi from sprays 30 and 56, being discharged instead through relief valve 38.
Fig. 5 illustrates a method of applying the invention to a two stage compressor. All parts relating to the first stage of compression may be the same as those shown in Fig. 1, and are indicated by corresponding numerals. The after-cooler 54, however, in this case becomes an inter-cooler and the cool moisture free air in pipe 18, instead of being delivered into the equipment to b e operated, is passed into a third mixing chamber |00. This is equipped with atomizing nozzles, similar to nozzles 30. As a result, a mixture of air and minute water globules is inducted into the high pressure cylinder |04 whence it is discharged at a higher pressure by way of outlet |06 into a third separator |08. In separator |08 the water, carrying most of the heat of compression, is removed from the air, which is then passed into a fourth and final mixing chamber I l0 corresponding in structure and in function to chamber 54 of Fig. 1-. The air then proceeds through a nal separator ||2 and is delivered in a cool, moisture free state by outlet I |4 for storage or use as may be desired.
From the foregoing description, it will be appreciated that the embodiments shown in Figs. l, 3 and 5 can be characterized as utilizing an antechamber, provided with one orfmore atomizing nozzles, in which the air or other gas to be compressed is mixed with a cooling medium, preferably oil or water, which is injected into the air or other gas in a very finely divided or atomized state. Due to the enlarged size of the antechamber, the movement of the air or other gas particles therethrough is relatively slow, so that ample time is afforded for the atomized cooling medium to be thoroughly and uniformly mixed therewith.
As previously mentioned, although a part of the atomized cooling medium passes into the vapor state, either before or during its passage through the compressor I2, by far the major portion of the atomized cooling medium remains in the liquid phase during its passage through the system.
The retention of the cooling medium in the liquid phase is of substantial importance, since it will be appreciated that the heat generated in the compressor may be much more efficiently transferred to the cooling medium in the liquid phase than would be the case if it were in the vapor phase.
As a. consequence of the complete mixture, in the ante-chamber, of the air or gas to be compressed, with a suitable quantity of atomized cooling medium preponderantly in the liquid phase, the heat of compression generated in the ,compressor very rapidly transfers to the cooling medium, so that the temperature of the mixture -asitleaves the compressor is very substantially lower than would otherwise be the case.
The above described embodiments are further characterized in that means are provided to abments, it is lfound desirable to eliminate the separate ante-chambers such as 28 of Fig. 1, and in such event the arrangement of Fig. 6 may be used, which is characterized by the provision of a continuous injection of atomized particles, preferably water particles, directly into the cylinder itself.
Referring particularly to Fig. 6, a compressor of generally conventional construction comprises the cylinder casing 210, within which the piston 212 is reciprocable. The head 214 is formed to provide an inlet chamber 216, and an outlet chamber 218. Conventional valves 280 and 282 control communication, respectively, between the inlet 216 and the chamber space 284, and between the outlet 218 and the chamber space l284.'
In accordance with the present invention,4
286 may be and preferably are continuously sup- 4 plied with the selected cooling medium in the manner described with reference to either Fig, l or Fig. 3. l
In practicing the embodiment shown in Fig. 6, it is preferred to construct the atomizing nozzles 286 in accordance with the showing of Fig. '7. In Fig. 7 a nozzle 286 is illustrated as being' provided with a tip 288 having a thin walled spherical head 280 through which a number of very fine holes 282, of the order of ,010" in diameter, are drilled. Each nozzle is adapted for operation at pressures of the order 'of about 1000 pounds per square inch, Whereas pressures of the` order of about pounds per square inch usually sullice for the nozzle structure shown in detail in Fig. 2. It is preferred that all of the holes 292 be drilled in the same plane, and in fitting injector 286 into the cylinder 210,this plane is arranged parallel with the cylinder head. The atomized particles are thus injected into a relatively shallow zone parallel to and adjacent the cylinder head. A minimum percentage of the particles thus strike the cylinder walls or piston head, while a maximum mixing eiect is secured dueto the fact that, in entering and in leaving, the air is required to pass through the zone of the particles.
It Will be appreciated that the operation of the arrangement shown in Fig. 6, as applied to either a single stage system such as shown in Figs. 1 and 3, or to a multistage system such as shown in Fig. 5, may duplicate the operation of the previously described embodiments, with the exceptions noted above, namely, that the antechambers of the earlier embodiments are eliminated and instead the cooling medium is injected directly in the cylinder. The embodiment of Fig. 6 thus retains all of the advantages incident to the continuous injection of an atomized cooling medium and, while the advantages incident to the use of an ante-chamber for mixing. purposes are sacrificed, this sacrifice is offset in part by a saving in the space requirements of the system as a'whole.
The arrangement shown in Fig. 8, illustrates the adaptation of 'the invention to a centrifugal compressor. In Fig. 8, a centrifugal compressor 300 is provided with a series of similar impellers.
means are provided to successively' introduce suitable quantities of cooling medium into the compressor, for mixing with the air or other gas, and for successively abstracting the cooling medium from the air or other gas. Preferably,l the arrangement is such that the air or other gas is supplied with a quantity of cooling medium once for each stage of the compressor, and such that It will be understood that in the broader aspects of the invention, the nozzle 3| I may be dispensed with and the nozzle 3I3 relied upon to inject all of the cooling medium for the second stage, and alternatively that the nozzle 3I3 may' l bedispdhsed with and the nozzle 3| I relied upon the just mentioned quantity of cooling medium Y is abstracted from the air or` other gas before the latter enters the next successive stage of the compressor. Each stage of the compressor is thus preferably provided with injecting mechanism and separating mechanism.
In the relation particularly shown in the drawing, the-rst stage 300dpi the compressor is provided with an injecting nozzle 3I0, of suitable construction to thoroughly and effectively atomize a cooling medium. The nozzle 3I0 is disposed to open into the compressor casing relatively near the axis "thereof, and the cooling medium introduced therethrough thus mixes with the incoming air or other gas just prior to the time that the latter enters the corresponding impeller 302.
'I'he air or other gas being compressed is conventionally acted upon bythe impeller 302 associated with the first stage, whereas the cooling medium, being substantially heavier, is thrown outwardly by centrifugal force and strikes the outer peripheral surface 3I2 of the compressor casing, at which point it coalesces into a nlm of water. 'I'his film of water is swept around to the lower side of the compressor casing and drains therefrom through a pssage 3I5 into a sump 3H. Sump 3M is provided with a iloat controlled valve 3I6 through which the collected cooling medium is removed from the compresser, either for disposal, or for recirculation, as in the case of the system of Fig. 3.
In accordance with the present invention, as stated generally above, the cooling medium associated with the second stage of the compressor may be introduced therein at any time after the abstraction of the cooling medium associated with the ilrst stage, and preferably before the air or other gas enters the impeller associated with the second stage. Accordingly, the second stage of the compressor is provided with a pair of nozzles 3II and 3I3, which may duplicate in vconstruction the previously described nozzle 3I`0. Where both nozzles 3II and 3I3 are utilized, it is preferred that they be of slightly smaller capacity than the single nozzle 3I0. The nozzle 3II opens into the compressor casing relatively near the outer peripheral surface 3l! of the latter and the nozzle 3 I3 opens into the compressor casing at a point corresponding to the position of the nozzle 3I0.
With the juststated arrangement, itwill be appreciated that as the air or other gas passes the outer peripheral surface 3I2 of the compressor, at which time the first charge of cooling medium is abstracted therefrom, and starts moving radially inwardly. toward the impeller 302 associated with the second stage, it is subjected to the successive actions of the nozzles 3II and 3I3, and is thereby supplied with a new charge of cooling medium. 'Ihe cooling medium thus supplied, in advance of the passage of the air or other gas Athrough the second stage, is abstracted therefrom in thev previously described manner, and it will be understood that the successive stages of the compressor are also preferably supplied with nozzle arrangements corresponding to the nozzles 3II and 3| 3.
entirely. It will further be appreciated'that, if desired, groups of nozzles, such as 3I0, 3| I, and 3I3, maybe provided for' the respective stages,V and be distributed circumferentially around the compressor. v
All of the nozzles 3I0, 3H, and 3I3 are illustrated as being supplied with cooling medium through a supply line 308 having branches corresponding tothe successive stages. The line 300 may be supplied with cooling medium in either the manner described above with reference to Fig. 1 or the manner described in con, nection with Fig. 3.
It will be appreciated that if desired, a plurality of passages 3I5 may be provided for each stage of the compressor, instead of the single passage 3I6 shown in Fig. 8, the preferred arrangement being one in which the several passages 3I5 drain into a common sump 3H, but open into the compressor casing at a plurality of points spaced circumferentially therearound. l
From the foregoing, it will be appreciated that the general operation of the system of Fig. 8 may duplicate the general operation described with reference to the embodiment of Figs. 1, 3, and 5 for single or multi-stage systems, respectively, except that the injection of the liquid occurs within the compressor rather than in an ante-chamber.
Although vonly several specific embodiments of the invention have been described in detail, it will be appreciated that various changes in the method of practicing the invention, and that various modications in the form, number, and arrangement of the parts may be made without departing from the scope of the invention.
What is claimed is:
l. A multistage compressor system comprising means for effecting iirstand second stages of compression, means for mixing an atomized liquid with the gas to be compressed prior to the completion of the first stage of the compression of said gas, means for eliminating said atomized liquid after the completion of said first stage, a second means for mixing an atomized liquid with said gas after said first elimination, a second elimination means effective after said second mixing operation and prior to the commencement of the second stage of compression, means for effecting a third mixing operation prior to the completion of said second stage of compression, and a third elimination means effective subsequent to the completion of said second stage of compression.
2. In combination, a compressor and operating means therefor, means for supplying a fluid to the compressor for compression thereby, continuously acting means for forming a mixture of the fluid and a cooling medium in atomized form prior to its discharge from the compressor, start and stop control means for said compressor, and means controlled by said start and stop control means for controlling said mixing means.
I tinuously acting means for forming a mixture of the fluid and a cooling Amedium in atomized form prior to its discharge from the compressor, an
unloader valve mechanism associated with said compressor, and valve means controlled by said unloader valve mechanism for controlling said mixing means.
4. In, combination, a compressor of the centrifugal type formed to provide a plurality of stages and having an impeller associated with each of said stages, and means including at least one atomizing nozzle associated with each stage of compression and effective to continuously injecta cooling medium in atomized form into said compressor; said nozzles being arranged to inject said cooling medium into the gas being compressed prior to the time that said gas reaches the corresponding impeller.
5. In a process for compressing a fluid, the steps of subjecting the fluid to the action oiv a 'compresson continuously mixing with the fluid prior to'its discharge from the compressor a cooling medium in atomized form capable of suspension in the fluid and in such quantity that a substantial part thereof remains in said compressed iluid in a` liquid state, separating said cooling medium from said fluid after compression thereof, extracting heat from said cooling medium after said separation, and remixing said cooling medium with further supplies of said fluid.
6. In combination, a compressor and operating means therefor, means for supplying a fluid to the compressor for compression thereby, continuously acting means for injecting into the fluid prior to its discharge from the compressor a cooling medium in atomized form capable of suspensionin the fluid and in such quantity that a substantial part thereof remains in said compressed fluid in a liquid state, means for separating the cooling medium from the fluid after the compression thereof, and an after-cooler'associated with the system forreducing the temperature of the separated duid.
7. In combination, a compressor and operating means therefor, means for supplying a fluid to the compressor for compression thereby,l continuously acting means for injecting into the fluid prior to its discharge from the compressor a cooling medium in atomized form capable of suspension in the fluid and in such quantity that a substantial part thereofV remains in saidl compressed uid in a liquid state, means for separating the cooling medium from the fluid after the compression thereof, means for extracting heat' from said separated cooling medium, and means for returning said cooling medium to said injecting means.
- 8. In combination, a compressor for a iluid formed to provide a cylinder and having a piston movable therein, means including at least one atomizing nozzle for continuously injecting into said cylinder during the operation of said piston a cooling medium in atomized form capable of suspension in said uid and in such quantity that a substantial part oi' said medium remains in the compressed fluid in a liquid state, and separating means associated with said compressor for separating said cooling medium from the compressed gas after the discharge thereof from the compressor.
9. In combination, a compressor for a fluid formed to provide a compressor space and compressor element movable therein, means including at least one atomizing nozzle for continuously in Jecting into said space during the operation of said element, a coolingI medium in atomized form capable ofv suspension in said fluid and in such quantity that a substantial part of said medium remains in the compressed uid in a liquid state, and separating means associated with said compressor for separating said cooling medium from the compressed gas after the discharge thereof from the compressor.
10. In combination, a compressor and operating means therefor, means for supplying fluid to the compressor for compression thereby, and means including an antechamber and a plurality of atomizing nozzles associated therewith for injecting into the uid, before the admission of the fluid to the compressor, a cooling medium in atomized form capable of suspension in the fluid. 1l. In combination, a compressor and operating means therefor, said compressor having a compression space and means for supplying fluid to the compressor for compression thereby comprising an anterchamber separate from but communicating with said space through which fluid to be compressed is introduced into said space, and means including atomizing means associated with said antechamber for introducing into the iluid, while in said antechamber and prior to its admission into said space, a cooling medium in atomized form capable of suspension in the uid.
HUMPHREY F. PARKER.
US187704A 1938-01-29 1938-01-29 Air compressor system Expired - Lifetime US2280845A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US187704A US2280845A (en) 1938-01-29 1938-01-29 Air compressor system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US187704A US2280845A (en) 1938-01-29 1938-01-29 Air compressor system

Publications (1)

Publication Number Publication Date
US2280845A true US2280845A (en) 1942-04-28

Family

ID=22690114

Family Applications (1)

Application Number Title Priority Date Filing Date
US187704A Expired - Lifetime US2280845A (en) 1938-01-29 1938-01-29 Air compressor system

Country Status (1)

Country Link
US (1) US2280845A (en)

Cited By (56)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549819A (en) * 1948-12-22 1951-04-24 Kane Saul Allan Axial flow compressor cooling system
US2786626A (en) * 1952-08-07 1957-03-26 Gulf Oil Corp Process for the compression of gases
US2924292A (en) * 1956-02-16 1960-02-09 Cons Electrodynamics Corp Apparatus for pumping
US3216648A (en) * 1962-04-02 1965-11-09 Stephen H Ford Automatic blowdown system for compressors
US3369533A (en) * 1965-01-04 1968-02-20 Bbc Brown Boveri & Cie Method of and apparatus for prevention of deposits of contaminants in the flow path of turbo-compressors
FR2519383A1 (en) * 1982-01-04 1983-07-08 Gen Electric Multiple stage radial compressor with water injection - has jet openings through walls of stages, arranged symmetrically about axis
GR890100213A (en) * 1989-04-04 1991-09-27 Athanasios Nasikas Method and mechanism of approaching isothermal air compression by means of little diameter doplets evaporation
WO1993024754A2 (en) * 1992-05-29 1993-12-09 National Power Plc A gas compressor
US5282726A (en) * 1991-06-21 1994-02-01 Praxair Technology, Inc. Compressor supercharger with evaporative cooler
GB2283543A (en) * 1992-05-29 1995-05-10 Nat Power Plc A gas compressor
US5454426A (en) * 1993-09-20 1995-10-03 Moseley; Thomas S. Thermal sweep insulation system for minimizing entropy increase of an associated adiabatic enthalpizer
WO1998016741A1 (en) 1996-10-14 1998-04-23 National Power Plc Apparatus for controlling gas temperature in compressors
USRE37603E1 (en) 1992-05-29 2002-03-26 National Power Plc Gas compressor
WO2003021107A1 (en) * 2001-08-31 2003-03-13 Innogy Plc Piston compressor
US20070140889A1 (en) * 2005-12-15 2007-06-21 Jiing Fu Chen Flow passage structure for refrigerant compressor
JP2010127245A (en) * 2008-11-28 2010-06-10 Mitsubishi Heavy Ind Ltd Centrifugal compressor
US20100205960A1 (en) * 2009-01-20 2010-08-19 Sustainx, Inc. Systems and Methods for Combined Thermal and Compressed Gas Energy Conversion Systems
US20100229544A1 (en) * 2009-03-12 2010-09-16 Sustainx, Inc. Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage
US20100329909A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100326075A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US7900444B1 (en) 2008-04-09 2011-03-08 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
JP2011074888A (en) * 2009-10-01 2011-04-14 Mitsubishi Heavy Ind Ltd Centrifugal compressor
US20110115223A1 (en) * 2009-06-29 2011-05-19 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20110233934A1 (en) * 2010-03-24 2011-09-29 Lightsail Energy Inc. Storage of compressed air in wind turbine support structure
US8037678B2 (en) 2009-09-11 2011-10-18 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US8046990B2 (en) 2009-06-04 2011-11-01 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage and recovery systems
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8117842B2 (en) 2009-11-03 2012-02-21 Sustainx, Inc. Systems and methods for compressed-gas energy storage using coupled cylinder assemblies
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8191362B2 (en) 2010-04-08 2012-06-05 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8234863B2 (en) 2010-05-14 2012-08-07 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8240146B1 (en) 2008-06-09 2012-08-14 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8272212B2 (en) 2011-11-11 2012-09-25 General Compression, Inc. Systems and methods for optimizing thermal efficiencey of a compressed air energy storage system
US8359856B2 (en) 2008-04-09 2013-01-29 Sustainx Inc. Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US8522538B2 (en) 2011-11-11 2013-09-03 General Compression, Inc. Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator
US8539763B2 (en) 2011-05-17 2013-09-24 Sustainx, Inc. Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems
US8567303B2 (en) 2010-12-07 2013-10-29 General Compression, Inc. Compressor and/or expander device with rolling piston seal
US8572959B2 (en) 2011-01-13 2013-11-05 General Compression, Inc. Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system
US8578708B2 (en) 2010-11-30 2013-11-12 Sustainx, Inc. Fluid-flow control in energy storage and recovery systems
US8667792B2 (en) 2011-10-14 2014-03-11 Sustainx, Inc. Dead-volume management in compressed-gas energy storage and recovery systems
US8677744B2 (en) 2008-04-09 2014-03-25 SustaioX, Inc. Fluid circulation in energy storage and recovery systems
CN104179531A (en) * 2014-07-25 2014-12-03 北京航空航天大学 Heat-work conversion mechanism based on open-close coupling thermodynamic cycle
US8997475B2 (en) 2011-01-10 2015-04-07 General Compression, Inc. Compressor and expander device with pressure vessel divider baffle and piston
US9109512B2 (en) 2011-01-14 2015-08-18 General Compression, Inc. Compensated compressed gas storage systems
US9109511B2 (en) 2009-12-24 2015-08-18 General Compression, Inc. System and methods for optimizing efficiency of a hydraulically actuated system
WO2016153627A1 (en) * 2015-03-26 2016-09-29 Exxonmobil Upstream Research Company Wet gas compression
US10215184B2 (en) 2015-03-26 2019-02-26 Exxonmobil Upstream Research Company Controlling a wet gas compression system
US10975869B2 (en) 2017-12-13 2021-04-13 Exponential Technologies, Inc. Rotary fluid flow device
US10989110B2 (en) 2018-01-18 2021-04-27 Mark J. Maynard Gaseous fluid compression with alternating refrigeration and mechanical compression using a first and second bank of compression coupled with first and second cascading heat pump intercoolers having a higher and a lower temperature section

Cited By (121)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549819A (en) * 1948-12-22 1951-04-24 Kane Saul Allan Axial flow compressor cooling system
US2786626A (en) * 1952-08-07 1957-03-26 Gulf Oil Corp Process for the compression of gases
US2924292A (en) * 1956-02-16 1960-02-09 Cons Electrodynamics Corp Apparatus for pumping
US3216648A (en) * 1962-04-02 1965-11-09 Stephen H Ford Automatic blowdown system for compressors
US3369533A (en) * 1965-01-04 1968-02-20 Bbc Brown Boveri & Cie Method of and apparatus for prevention of deposits of contaminants in the flow path of turbo-compressors
FR2519383A1 (en) * 1982-01-04 1983-07-08 Gen Electric Multiple stage radial compressor with water injection - has jet openings through walls of stages, arranged symmetrically about axis
GR890100213A (en) * 1989-04-04 1991-09-27 Athanasios Nasikas Method and mechanism of approaching isothermal air compression by means of little diameter doplets evaporation
US5282726A (en) * 1991-06-21 1994-02-01 Praxair Technology, Inc. Compressor supercharger with evaporative cooler
WO1993024754A2 (en) * 1992-05-29 1993-12-09 National Power Plc A gas compressor
WO1993024754A3 (en) * 1992-05-29 1994-03-17 Nat Power Plc A gas compressor
GB2283543A (en) * 1992-05-29 1995-05-10 Nat Power Plc A gas compressor
JP3504946B2 (en) 1992-05-29 2004-03-08 イノジーパブリックリミテッドカンパニー Heat recovery device
US5771693A (en) * 1992-05-29 1998-06-30 National Power Plc Gas compressor
USRE37603E1 (en) 1992-05-29 2002-03-26 National Power Plc Gas compressor
US5454426A (en) * 1993-09-20 1995-10-03 Moseley; Thomas S. Thermal sweep insulation system for minimizing entropy increase of an associated adiabatic enthalpizer
US5641273A (en) * 1993-09-20 1997-06-24 Moseley; Thomas S. Method and apparatus for efficiently compressing a gas
GB2333135A (en) * 1996-10-14 1999-07-14 Nat Power Plc Apparatus for controlling gas temperature in compressors
AU725179B2 (en) * 1996-10-14 2000-10-05 National Power Plc Apparatus for controlling gas temperature in compressors
US6206660B1 (en) * 1996-10-14 2001-03-27 National Power Plc Apparatus for controlling gas temperature in compressors
GB2333135B (en) * 1996-10-14 2000-05-24 Nat Power Plc Apparatus for controlling gas temperature
CN1082623C (en) * 1996-10-14 2002-04-10 国家电力有限公司 Apparatus for controlling gas temperature in compressors
WO1998016741A1 (en) 1996-10-14 1998-04-23 National Power Plc Apparatus for controlling gas temperature in compressors
WO2003021107A1 (en) * 2001-08-31 2003-03-13 Innogy Plc Piston compressor
US20040244580A1 (en) * 2001-08-31 2004-12-09 Coney Michael Willoughby Essex Piston compressor
US20070140889A1 (en) * 2005-12-15 2007-06-21 Jiing Fu Chen Flow passage structure for refrigerant compressor
US7641439B2 (en) * 2005-12-15 2010-01-05 Industrial Technology Research Institute Flow passage structure for refrigerant compressor
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8627658B2 (en) 2008-04-09 2014-01-14 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8677744B2 (en) 2008-04-09 2014-03-25 SustaioX, Inc. Fluid circulation in energy storage and recovery systems
US8713929B2 (en) 2008-04-09 2014-05-06 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US8733094B2 (en) 2008-04-09 2014-05-27 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8209974B2 (en) 2008-04-09 2012-07-03 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
US7900444B1 (en) 2008-04-09 2011-03-08 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
US8733095B2 (en) 2008-04-09 2014-05-27 Sustainx, Inc. Systems and methods for efficient pumping of high-pressure fluids for energy
US8359856B2 (en) 2008-04-09 2013-01-29 Sustainx Inc. Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8763390B2 (en) 2008-04-09 2014-07-01 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8240146B1 (en) 2008-06-09 2012-08-14 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
JP2010127245A (en) * 2008-11-28 2010-06-10 Mitsubishi Heavy Ind Ltd Centrifugal compressor
US7958731B2 (en) 2009-01-20 2011-06-14 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US8122718B2 (en) 2009-01-20 2012-02-28 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US20100205960A1 (en) * 2009-01-20 2010-08-19 Sustainx, Inc. Systems and Methods for Combined Thermal and Compressed Gas Energy Conversion Systems
US8234862B2 (en) 2009-01-20 2012-08-07 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US8234868B2 (en) 2009-03-12 2012-08-07 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage
US7963110B2 (en) 2009-03-12 2011-06-21 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage
US20100229544A1 (en) * 2009-03-12 2010-09-16 Sustainx, Inc. Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage
US8046990B2 (en) 2009-06-04 2011-11-01 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage and recovery systems
US8479502B2 (en) 2009-06-04 2013-07-09 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8201403B2 (en) 2009-06-29 2012-06-19 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8191361B2 (en) 2009-06-29 2012-06-05 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8196395B2 (en) 2009-06-29 2012-06-12 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8196398B2 (en) 2009-06-29 2012-06-12 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8191360B2 (en) 2009-06-29 2012-06-05 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8201402B2 (en) 2009-06-29 2012-06-19 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20110023488A1 (en) * 2009-06-29 2011-02-03 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20110023977A1 (en) * 2009-06-29 2011-02-03 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8215106B2 (en) 2009-06-29 2012-07-10 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8893487B2 (en) 2009-06-29 2014-11-25 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100329903A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8182240B2 (en) 2009-06-29 2012-05-22 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8181456B2 (en) 2009-06-29 2012-05-22 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8240142B2 (en) 2009-06-29 2012-08-14 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8468814B2 (en) 2009-06-29 2013-06-25 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100326075A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100326069A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100329891A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20100329909A1 (en) * 2009-06-29 2010-12-30 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8793989B2 (en) 2009-06-29 2014-08-05 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8353156B2 (en) 2009-06-29 2013-01-15 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8356478B2 (en) 2009-06-29 2013-01-22 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8756929B2 (en) 2009-06-29 2014-06-24 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8387374B2 (en) 2009-06-29 2013-03-05 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8146354B2 (en) * 2009-06-29 2012-04-03 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8393148B2 (en) 2009-06-29 2013-03-12 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8436489B2 (en) 2009-06-29 2013-05-07 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20110115223A1 (en) * 2009-06-29 2011-05-19 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8450884B2 (en) 2009-06-29 2013-05-28 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8756928B2 (en) 2009-06-29 2014-06-24 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8215105B2 (en) 2009-06-29 2012-07-10 Lightsail Energy Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8561399B2 (en) 2009-06-29 2013-10-22 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8037678B2 (en) 2009-09-11 2011-10-18 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US8109085B2 (en) 2009-09-11 2012-02-07 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US8468815B2 (en) 2009-09-11 2013-06-25 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
JP2011074888A (en) * 2009-10-01 2011-04-14 Mitsubishi Heavy Ind Ltd Centrifugal compressor
US8117842B2 (en) 2009-11-03 2012-02-21 Sustainx, Inc. Systems and methods for compressed-gas energy storage using coupled cylinder assemblies
US9109511B2 (en) 2009-12-24 2015-08-18 General Compression, Inc. System and methods for optimizing efficiency of a hydraulically actuated system
US9024458B2 (en) 2010-03-24 2015-05-05 Lightsail Energy, Inc. Energy storage system utilizing compressed gas
US9581140B2 (en) 2010-03-24 2017-02-28 Lightsail Energy, Inc. Storage of compressed air in wind turbine support structure
US20110233934A1 (en) * 2010-03-24 2011-09-29 Lightsail Energy Inc. Storage of compressed air in wind turbine support structure
US8723347B2 (en) 2010-03-24 2014-05-13 Lightsail Energy, Inc. Energy storage system utilizing compressed gas
US8247915B2 (en) 2010-03-24 2012-08-21 Lightsail Energy, Inc. Energy storage system utilizing compressed gas
US8661808B2 (en) 2010-04-08 2014-03-04 Sustainx, Inc. High-efficiency heat exchange in compressed-gas energy storage systems
US8191362B2 (en) 2010-04-08 2012-06-05 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8245508B2 (en) 2010-04-08 2012-08-21 Sustainx, Inc. Improving efficiency of liquid heat exchange in compressed-gas energy storage systems
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8234863B2 (en) 2010-05-14 2012-08-07 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US8578708B2 (en) 2010-11-30 2013-11-12 Sustainx, Inc. Fluid-flow control in energy storage and recovery systems
US8567303B2 (en) 2010-12-07 2013-10-29 General Compression, Inc. Compressor and/or expander device with rolling piston seal
US8997475B2 (en) 2011-01-10 2015-04-07 General Compression, Inc. Compressor and expander device with pressure vessel divider baffle and piston
US8572959B2 (en) 2011-01-13 2013-11-05 General Compression, Inc. Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system
US9260966B2 (en) 2011-01-13 2016-02-16 General Compression, Inc. Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system
US9109512B2 (en) 2011-01-14 2015-08-18 General Compression, Inc. Compensated compressed gas storage systems
US8806866B2 (en) 2011-05-17 2014-08-19 Sustainx, Inc. Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems
US8539763B2 (en) 2011-05-17 2013-09-24 Sustainx, Inc. Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems
US8667792B2 (en) 2011-10-14 2014-03-11 Sustainx, Inc. Dead-volume management in compressed-gas energy storage and recovery systems
US8272212B2 (en) 2011-11-11 2012-09-25 General Compression, Inc. Systems and methods for optimizing thermal efficiencey of a compressed air energy storage system
US8387375B2 (en) 2011-11-11 2013-03-05 General Compression, Inc. Systems and methods for optimizing thermal efficiency of a compressed air energy storage system
US8522538B2 (en) 2011-11-11 2013-09-03 General Compression, Inc. Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator
CN104179531A (en) * 2014-07-25 2014-12-03 北京航空航天大学 Heat-work conversion mechanism based on open-close coupling thermodynamic cycle
US10989212B2 (en) 2015-03-26 2021-04-27 Exxonmobile Upstream Research Company Controlling a wet gas compression system
US10215184B2 (en) 2015-03-26 2019-02-26 Exxonmobil Upstream Research Company Controlling a wet gas compression system
US10253781B2 (en) 2015-03-26 2019-04-09 Exxonmobil Upstream Research Company Wet gas compression
WO2016153627A1 (en) * 2015-03-26 2016-09-29 Exxonmobil Upstream Research Company Wet gas compression
US10975869B2 (en) 2017-12-13 2021-04-13 Exponential Technologies, Inc. Rotary fluid flow device
US10989110B2 (en) 2018-01-18 2021-04-27 Mark J. Maynard Gaseous fluid compression with alternating refrigeration and mechanical compression using a first and second bank of compression coupled with first and second cascading heat pump intercoolers having a higher and a lower temperature section

Similar Documents

Publication Publication Date Title
US2280845A (en) Air compressor system
US2628015A (en) Engine-driven air compressor
US2372846A (en) Water distillation
JPS58155287A (en) Refrigerating unit
GB1346514A (en) Gas liquid separator for use in a refrigeration system
US3074243A (en) Vortex water cooler
US2353966A (en) Liquid cooling system for internal-combustion engines
US3141293A (en) Method and apparatus for refrigerating combustion air for internal combustion engines
US2252914A (en) Diesel engine
US4437813A (en) Gas receiving and transmitting system
US3208667A (en) Compressor
US2487176A (en) System for recovering water from exhaust gas
GB764951A (en) Method and apparatus for liquefying natural gas for shipment and storage
US3090208A (en) Cooling method by means of negative pressure given on the vortex tube
US2252187A (en) Arrangement in combustion motor, compressor, or the like
US2033166A (en) Means for supercharging internal combustion engines
US1967251A (en) Lubricating system
US2935978A (en) Moisture control for engines
CN106801667B (en) Air compressor energy-saving device of air and its application method
CN207048936U (en) The recovery system of natural gas compressor
CN102134503B (en) Clean oil device for recycling natural gas and oil gas
US3051148A (en) Two cycle-radial, high-supercharge engines
US2336480A (en) Lubricating system for aircraft superchargers
US2215266A (en) Apparatus for compressing and cooling air
US1725881A (en) Apparatus for operating liquid turbines by means of combustion machines