US3407992A - Aerodynamic pressure wave machine - Google Patents

Aerodynamic pressure wave machine Download PDF

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Publication number
US3407992A
US3407992A US610117A US61011767A US3407992A US 3407992 A US3407992 A US 3407992A US 610117 A US610117 A US 610117A US 61011767 A US61011767 A US 61011767A US 3407992 A US3407992 A US 3407992A
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United States
Prior art keywords
gas
pressure
high pressure
cold
low pressure
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Expired - Lifetime
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US610117A
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English (en)
Inventor
Jenny Ernst
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BBC Brown Boveri AG Switzerland
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Bbc Brown Boveri & Cie
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21C—PRODUCTION OF CELLULOSE BY REMOVING NON-CELLULOSE SUBSTANCES FROM CELLULOSE-CONTAINING MATERIALS; REGENERATION OF PULPING LIQUORS; APPARATUS THEREFOR
    • D21C3/00—Pulping cellulose-containing materials
    • D21C3/02—Pulping cellulose-containing materials with inorganic bases or alkaline reacting compounds, e.g. sulfate processes
    • D21C3/022—Pulping cellulose-containing materials with inorganic bases or alkaline reacting compounds, e.g. sulfate processes in presence of S-containing compounds

Definitions

  • This invention relates to an aerodynamic pressure wave machine and more particularly is directed to a novel arrangement whereby the magnitude of the pressure at the high pressure cold outlet is equal to or greater than the pressure at the high pressure hot inlet even though the pressure of the low pressure cold inlet gas is substantially lower than the pressure of the low pressure hot outlet gas.
  • My novel arrangement provides for a portion of the gas in the high pressure zone of the cycle of operation to be diverted to the low pressure zone of the cycle of operation.
  • Aerodynamic pressure wave machines of the general nature covered by this application are well known in the art and are illustrated and described in US. Patent 2,- 957,304 issued Oct. 25, 1960 to M. Berchtold, entitled Aerodynamic Wave Machine Used as a Supercharger for Reciprocating Engines; 2,970,745 issued Feb. 7, 1961 to M. Berchtold, entitled Wave Engine; 3,012,708 issued Dec. 12, 1961 to M. Berchtold, entitled Aerodynamic Wave Machine Port Lead Edge Modification for Extended Speed Range; 3,145,909 issued Aug. 25, 1964 to F. J. Gardiner, entitled Pressure Transformer; all of the aforementioned being assigned to the I-T-E Circuit Breaker Company.
  • the present invention utilizes substantially the same general arrangement disclosed in the aforementioned US. patents but provides for a novel re-arrangement of the ports and a novel reinsertion of a portion of the hot gas to achieve the desired results.
  • applicants structure can be comprised of a rotor having a plurality of cells on the perimeter thereof and a stator plate with ports on each side of the rotor in order to control the inlet and outlet of the various gases which are to be or have been compressed or expanded.
  • the flow of the compressed cold gas is greater than the How of the expanded hot gas. This is greater than the flow of the expanded hot gas.
  • This surplus flow of the gas passing through the turbine produces shaft power.
  • any desired temperature can be obtained by mixing the heated and unheated gases. This temperature will depend on th permissible turbine inlet temperature. However, this mixing is undesirable since it lowers the efiiciency of the combination of the units.
  • one such unit is identified as a pressure transformer as illustrated in German Patent 1,000,- 132.
  • the device does not equally exchange pressure between the cold and the hot gases.
  • there must be in the pressure transformer a substantial difference between the low pressure hot outlet gas and the low pressure cold inlet gas in order to produce a significant large difference between the high pressure cold outlet gas and the high pressure hot inlet gas.
  • the compression pressure ratio of the cold gas after and before compression can be larger than the expansion pressure ratio of the hot gas before and after expansion. Such condition can be obtained even though there is equal mass flow of the hot and the cold gas.
  • thermodynamic processes such as a power producing cycle
  • the cold gas is compressed in the wave machine after being discharged from the turbine compressor and the hot gas leaving the combustion chamber expands first in the pressure exchanger and then in the turbine. Since the pressure drop in the combustion chamber is relatively small, the pressure of the high pressure cold outlet gas is slightly below the pressure of the high pressure hot inlet gas.
  • My present invention is specifically directed to a novel port arrangepressure gas'in order to achieve this result.
  • My invention has a substantial modification of the prior art design which can attain the desired operating conditions aforementioned by dividing at least one of the high pressure gas flows. That is, the main high pressure flow of either hot gas to be expanded or cold gas which has been compressed, has a portion of the flow diverted to assist in the'scavenging of the cells in a low pressure zone or stage of the cycle.
  • my pressure wave machine is designed to have at least one additional inlet port in the low pressure zone or portion of the cycle for the purpose of providing full scavenging.
  • a primary object of my invention is to provide a novel aerodynamic wave machine in which the pressure of the cold gas at the high pressure outlet port is equal to or greater than the pressure of the hot gas at the high pressure inlet port even though the pressure of the cold gas at a low pressure inlet port is considerably lower than the pressure of the hot gas being discharged at the low pressure outlet port.
  • Another object of my invention is to provide a novel aerodynamic wave machine which is particularly adaptable for use in combination with a gas turbine and provides for maximum efficiency.
  • Still another object of my invention is to provide a high efficiency aerodynamic wave machine which may be used in combination with a gas turbine and provides an arrangement in which one of the high pressure gas is subdivided so that a portion of the high pressure gas is reinserted in the low pressure zone or cycle of the machine to aid in scavenging.
  • Another object of my invention is to provide a novel aerodynamic wave machine in which there is an additional inlet port or opening in the low pressure portion of the cycle for introducing a portion of either the hot or cold high pressure gas obtained from the high pressure cycle of the device.
  • FIGURE 1 is a schematic developed view of the rotor and ports showing the condition of the gas in each section of the rotor with respect to temperature and pressure for a reverse cycle of operation.
  • a first embodiment of the invention is illustrated in which a portion of the high pressure hot available gas is diverted for insertion into an additional port located in the low pressure cycle.
  • FIGURE 2 is a state diagram for the wave machine of FIGURE 1 and is a plot of the pressure ratio with respect to the speed of sound for the vertical axis and the flow of velocity for the horizontal axis.
  • FIGURE 3 is a schematic developed view of the rotor and ports showing the condition of the gas in each section of the rotor with respect to temperature and pressure for a reverse cycle of operation.
  • FIGURE 3 illustrates a second embodiment in which a portion of the high pressure cold outlet gas is diverted to be reinserted in an additional inlet port located in the low pressure cycle of the wave machine.
  • FIGURE 4 is a state diagram for the wave machine of FIGURE 3 and is a plot of the pressure ratio with respect to the speed of sound for the vertical axis and the flow of velocity for the horizontal axis.
  • FIGURES l and 3 both illustrate the concept of my invention wherein a portion of one of the high pressure gases can be diverted to be subsequently reinserted into an additional inlet port in the low pressure cycle of the machine but each of these figures illustrate a ditferent embodiment for carrying out the common concept.
  • the high pressure zone or portion of the cycle for the two embodiments are substantially identical in operation.
  • the high pressure hot gas enters the rotor cells through the high pressure inlet port 2v and this hot gas leaves the rotor cell through the low pressure ports brand In.
  • the cold gas flows'into the cells of the rotor at the low pressure ports 1v and 1v and is discharged, after compression, through the high pressure outlet port 211.
  • the cell'of the rotor is completely filled with cold gas at a low pressure and is stationary as illustrated in the state diagrams of FIGURES 2 and 4.
  • the left hand of the cell of the rotor initially reaches the leading edge of the high pressure hot inlet p0rt 2v and thereafter the right-hand end of the cell is opened by the leading edgeof the high pressure cold outlet port 2 n. Thereafter, the right-hand end of the cell is first closed by the leading edge of the low pressure outlet port 2;: and, subsequently, the left-hand edge is closed by the trailing edge of the high pressure hot inlet port 2v.
  • the conditions 1, 3 and 5 represent the flow of the hot gas entering the cell at a cold pressure of P and compresses the cold gas to a total pressure of P shown at conditions 2 and 4.
  • the hot gas which enters through the high pressure hot inlet port 2v displaces the cold compressed gas which is then discharged through the high pressure cold outlet port 2n.
  • the pressures P and P are substantially equal with the pressure P being slightly greater than the pressure P .
  • This condition is indicated by the proximity of the two ellipses illustrated in the state diagram of the numeralsZv and 2m 7
  • the high pressure cold outlet port 211 closes the cell before the high pressure hot inlet port 2v so that the high pressure of the gas in field 6 is maintained in the rotor following the extraction of the compressed cold gas from the high pressure cold outlet port 2):.
  • the hot gasat high pressure retained in the rotor can be discharged through the low pressure port 1n located at field 7 and, since the right-hand end of the cell of the rotor is thereafter opened by the low pressure inlet port 1v, cold gas will be drawn into the rotor through the low pressure port 1v at field 8 as a result of the discharge of the hot" gas through the port In. Since the pressure in field'8 is lower than the pressure in field 7, reflected waves could reverse the'fiow direction of the fresh cold gas and--thus-upset the cycle. In order to prevent this from happening, the cell is immediatelyclosed at its left end by the trailing .edge of the outlet port 121 and thereafter immediately closed at itsright end by the trailing edge of the-cold: inlet port 1v. Thus, the pressure in the. field; 9 is betweentheextremes of the high andlow pressure of the machine as .clearly indicated in the state diagramsof FIGURES 2 and 4. v
  • FIGURES 1 and Z-there is illustrated an arrangement whereby a portion of the available high pressure hot gas entering the hot inlet port 2v is divided to enter the machine at an additional inlet port 2v.
  • the additional inlet port 2v in fact is a significant contribution of the present invention,
  • the gas entering the additional inlet port 2v is at the same pressure as the hot gas entering the main hot inlet port 2v. Since the gas entering the additional inlet port 2v is at the high pressure of P the pressure of the gas in the cell is raised so that the gas at field 11 is higher than the pressure of the gas in field 9.
  • This elevated pressure, created in the low pressure zone of the cycle of operation is now sufiiciently high to permit a desirable level of scavenging in the low pressure zone so that all of the hot gas which has been expanded can be exhausted from the rotor.
  • all of the remaining expanded hot gas will be exhausted through the low pressure hot outlet port In.
  • the right-hand end of the rotor is opened to the 'low pressure cold inlet port 1v.
  • the cold gas enters the cell so that it can be subsequently compressed in the high pressure zone of the cycle of operation.
  • a second high pressure port 2v (not shown) could be incorporated into the machine.
  • the second high pressure port 2v is not required since all of the expanded hot gas has been discharged through the low pressure hot outlet port In as indicated by the interface dotted line representation.
  • the cycle can start all over again in that the field is in fact the same as the field 0 in which the description of the cycle of operation started. That is, the entire cell is filled with fresh cold gas at low pressure ready to be compressed as it enters the high pressure zone of the cycle.
  • the mode and cycle of operation of embodiments 1 and 3 are identical for fields 0-9.
  • I have illustrated the manner in which the high pressure cold gas can be utilized, instead of the high pressure hot gas, to be reinserted into the low pressure zone or cycle. That is, the high pressure compressed cold gas at the outlet port 2n is bypassed from the main flow and reinserted into the cycle at the additional inlet port 2n located in the low pressure zone.
  • cold gas which had previously been compressed in the high pressure zone, enters the cells at field 10 at pressure P and furnishes the necessary energy required for scavenging the expanded hot gas out of the rotor. It is apparent, of course, that the main portion of the compressed cold gas can be utilized in any desirable arrangement required for the wave machine.
  • the introduction of.the compressed cold gas at the additional inlet port 2n raises the pressure of the gas at field 9 to an elevated pressure at field-11 so that the hot gas can be easily and readily scavenged or exhausted through, the low pressure hot outlet 1n.
  • the cell is thoroughly scavenged, as illustrated by the interfaced dotted line, so that the cold fresh gas completely fills the rotor. Since some of the cold fresh gas may also be discharged through the outlet port In the efficiency of the cycle shown in FIGURES 3 and 4 is lower than the efliciency of the cycle illustrated in FIGURES 1 and 2.
  • FIGURES 1 and 2 illustrates a bypass of the high pressure hot gas for subsequent reinsertion into cycle
  • the embodiment of FIGURES 3 and 4 illustrates a bypass of the high pressure cold gas for subsequent reinsertion into the low pressure zone of the cycle of operation.
  • FIGURES 1 and 3 it will be apparent to those skilled in the art that in some installations it may be desirable to combine the embodiments of FIGURES 1 and 3 into a single cycle of operation so that there is a bypass and an additional inlet port for both the high pressure hot and cold gas.
  • the invention is illustrated in connection with a preferred structural arrangement in which the cells are rotated and the ports are stationary in the two stator plates on each side of the rotor.
  • the concept of the present invention could be achieved by an arrangement in which the cells are stationary and the ports are located in rotating casings on either side of the cells.
  • the pressure or aerodynamic wave machine with the improvements of my present invention could be used in a thermo-cycle with considerable advantages.
  • My invention results in a substantially improved scavenging arrangement with a higher purity of the compressed cold 'gas.
  • the pressure wave machine of the present invention is combined with a gas turbine, the rotational speed of the rotor can easily be modified to obtain optimum operating conditions.
  • gas pockets can be provided in the stator plates of the general type described and illustrated in US. Patents 3,120,920 issued Feb.
  • An aerodynamic wave machine having a rotor and a stator on each side of said rotor; said machine having a high pressure zone and a low pressure zone;
  • said high pressure zone having a first high pressure outlet port for gas which has been compressed and a first high pressure inlet port for gas to be expanded;
  • said low pressure zone having a first and second low pressure inlet port for gas to be compressed, -a first and second low pressure outlet port for gas which has been expanded, and a second high pressure inlet port for a portion of the gases divided from at least one of said first high pressure ports in said high pressure zone;
  • said second high pressure inlet port at said low pressure zone being operative to aid the scavenging of the low pressure gas in said rotor through said first low pressure outlet port; said second high pressure inlet port of said low pressure zone being located between one of the sets of said first and second low pressure ports.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Inorganic Chemistry (AREA)
  • Supercharger (AREA)
US610117A 1966-01-28 1967-01-18 Aerodynamic pressure wave machine Expired - Lifetime US3407992A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH122166A CH441868A (de) 1966-01-28 1966-01-28 Verfahren zum Betrieb einer aerodynamischen Druckwellenmaschine

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US3407992A true US3407992A (en) 1968-10-29

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US610117A Expired - Lifetime US3407992A (en) 1966-01-28 1967-01-18 Aerodynamic pressure wave machine

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US (1) US3407992A (de)
CH (1) CH441868A (de)
DE (1) DE1503490B2 (de)
FR (1) FR1508893A (de)
GB (1) GB1160146A (de)
NL (1) NL145023B (de)
SE (1) SE344223B (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE790403A (fr) * 1971-10-21 1973-04-20 Gen Power Corp Turbo-compresseur integral a onde
US5916125A (en) * 1997-05-16 1999-06-29 Allison Engine Company, Inc. Forced purge wave rotor
US6449939B1 (en) 2000-05-26 2002-09-17 Rolls-Royce Corporation Pulsed detonation engine wave rotor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1138394A (fr) * 1954-10-20 1957-06-13 Perfectionnements apportés aux échangeurs de pression
GB996266A (en) * 1962-05-17 1965-06-23 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchangers

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1138394A (fr) * 1954-10-20 1957-06-13 Perfectionnements apportés aux échangeurs de pression
GB996266A (en) * 1962-05-17 1965-06-23 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchangers

Also Published As

Publication number Publication date
FR1508893A (fr) 1968-01-05
GB1160146A (en) 1969-07-30
NL145023C (de) 1975-07-15
DE1503490B2 (de) 1971-08-15
SE344223B (de) 1972-04-04
DE1503490A1 (de) 1970-04-09
NL145023B (nl) 1975-02-17
CH441868A (de) 1967-08-15
NL6701281A (de) 1967-07-31

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