US3295748A - Arrangement for the continuous adjustment of the output of a piston compressor - Google Patents

Arrangement for the continuous adjustment of the output of a piston compressor Download PDF

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Publication number
US3295748A
US3295748A US472455A US47245565A US3295748A US 3295748 A US3295748 A US 3295748A US 472455 A US472455 A US 472455A US 47245565 A US47245565 A US 47245565A US 3295748 A US3295748 A US 3295748A
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United States
Prior art keywords
cylinder
auxiliary chamber
piston
compressor
fluid
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Expired - Lifetime
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US472455A
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English (en)
Inventor
Leitgeb Anton
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Burckhardt Compression AG
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Maschinenfabrik Burckhardt AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers

Definitions

  • the auxiliary chamber is constituted by a cylinder inside which a piston is adapted to move so as to modify the volume of said chamber.
  • the starting of the piston is however a diflicult matter, chiefly for high pressures, by reason of the high energy required for the movement of such a piston.
  • auxiliary chamber which ensures a continuous operation and wherein the auxiliary chamber is of an unvarying size, so as to allow a cutting out of the movable piston, said auxiliary chamber communicating with the cylinder during an adjustable duration.
  • Said connection of a variable duration is ensured by a valve which may, under the action of a spring, be shifted during the compression stroke of the piston under the action of suitable means, so as to maintain the connection between the auxiliary chamber and the cylinder as long as the energy developed by the thrust of the gas acting on the closing member forming part of the valve is larger than the energy developed by the pressure of the spring.
  • said valve is open as long as the pressure inside the cylinder is lower than the pressure of the spring so that consequently the gas enclosed in the auxiliary chamber returns into the cylinder, whereby the amount of gas sucked in is reduced correspondingly.
  • the present invention has for its object to cut out the above drawbacks by resorting to an arrangement for the continuous adjustment of the output, which arrangement includes an auxiliary chamber having a constant volume and which is filled with a fluid under a variable pressure.
  • this object is reached through the fact that the auxiliary chamber is connected with the compressor cylinder through a throttling member adapted to be locked and providing an adjustable crosssection for the flow of fluid, said throttling member being associated with a check and suction valve equipping the compressor cylinder; the arrangement thus devised is such that during the compression stroke of the piston, a fraction of the fluid to be compressed is delivered under pressure into the auxiliary chamber, which fraction returns during the suction stroke of the piston into the cylinder through the check valve and the throttling valve, whereby the volume of fluid sucked into the cylinder is reduced.
  • a predetermined pressure is established the value of which depends on the cross-section of the passageway provided by the throttling member into the auxiliary chamber and the value of said pressure may vary between Zero and the maximum value of the compression produced by the compressor.
  • the check valve remains closed.
  • said valve opens when the pressure in the cylinder drops underneath that prevailing in the auxiliary chamber; the gas enclosed then escapes without being subjected to any throttling effect into the cylinder and this escape modifies correspondingly the volume of fluid sucked in in accordance with the amount of gas which has expanded.
  • the arrangement according to the invention as disclosed operates without any loss under full load conditions when the throttling member is closed and the case is the same for the minimum output conditions to be considered when the throttling member is completely open, since no throttling is then performed. For adjustments ranging between these two extreme conditions, a slight loss through throttling appears. Such a loss is however very small since only a reduced fraction of the volume delivered is subjected to this throttling and furthermore the throttling is not performed between the output pressure and the suc tion pressure, but only down to the pressure prevailing at such a moment inside the auxiliary chamber. Such reduced losses are allowable since, on the other hand, the reliability in operation of the adjusting system is particularly high.
  • the throttling member or valve includes a movable member, preferably a needle valve, which does not resonate with the machine so that it may operate freely and is not subjected to the action of disturbing members.
  • FIG. 1 is a transverse cross-section showing the auxiliary chamber equipping the head of the cylinder of a compressor.
  • the whole system, the adjustable throttling member and the suction valve are fitted in the wall of said cylinder head, between the auxiliary chamber and the cylinder bore.
  • FIG. 2 is a transverse cross-section of a modified embodiment of the auxiliary chamber carrying a unit including the suction valve associated with the throttling member.
  • FIG. 3 is a cross-section of a further modification wherein the suction valve fitted in a central position forms a check valve or flap valve which opens towards the auxiliary chamber while its stroke is adjustable.
  • FIG. 4 is a transverse cross-section showing an arrangement according to which a fraction of the suction pipe serves as an auxiliary chamber as provided by the fitting of a second suction valve therein, said auxiliary chamber being connected with the cylinder bore through the agency of a throttling member lying outside the cylinder.
  • FIG. 5 is a cross-section of an arrangement similar to that illustrated in FIG. 4, wherein the throttling member connecting the cylinder bore with the auxiliary chamber is arranged centrally and inside the suction valve.
  • 1 designates the auxiliary chamber which may be given any desired shape, while its volume corresponds to the maximum range required for adjustment; 2 designates the throttling member and 3 the check valve.
  • the cross-sectional passage provided through the seat 4 of the throttling valve 2, which seat is fitted in the upper wall 17 of the cylinder 15, may be adjusted, as required by the pressure to be obtained in the auxiliary chamber 1, by the needle valve 5 controlled in an axial direction by a rod 6.
  • the shifting of the rod 6 is obtained by means of a hand-wheel 7 or the like control mechanism.
  • the adjustment of the cross-sectional area of the passageway opening towards the auxiliary chamber may as well be ensured by a cylindrical slide valve, instead of a needle valve. As illustrated in FIG. 1 for instance, the
  • bottom of the auxiliary chamber may be provided in the usual manner, in the vicinity of the throttling member 2 with a check valve 3 forming also a suction valve opening into the bore of the compressor cylinder.
  • the compressed gas entering the chamber 1 during the compression stroke of the piston 16 through the throttling member 2 expands inside the compressor cylinder during the subsequent suction stroke, the gas passing then without any loss due to throttling, through the passageway provided by the check valve 3 and the cross-sectional area uncovered by the throttling member. This ensures a variation in the amount of fluid sucked in in direct relationship with the adjusted pressure prevailing inside the auxiliary chamber 1
  • the embodiment illustrated in FIG. 2 differs from that illustrated in FIG.
  • the seat 8 for the throttling member is formed centrally of the suction valve 3 which is given a generally annular shape.
  • the cross-sectional area of the passageway open through the seat 8 is adjusted by the needle valve 5 forming the throttling member.
  • Said coaxial arrangement of the unit including the suction valve and the throttling member is of advantage by reason of its reduced bulk, chiefly in the case of small diameter cylinders.
  • FIG. 3 illustrates an application of the invention according to which the suction valve 3 carried by the auxiliary chamber is associated with a throttling member forming also a check valve and located centrally of the suction valve 3.
  • Said flap valve 9 opens towards the inside of the auxiliary chamber 1 and its stroke is limited by a stop 10 which may be shifted axially by suitable control means 11 so as to allow obtaining the desired adjusted throttling.
  • FIGS. 4 and 5 illustrate a modification of the arrangements according to FIGS. 1, 2 and 3, in which modification a fraction of the suction pipe 12 plays the part of an auxiliary chamber.
  • the auxiliary chamber is closed by a second suction valve 13 inserted ahead of the suction valve 3, the space lying between the two valves 3 and 13 acting as the output adjusting means.
  • the throttling member 2 which may be controlled by hand or through any other suitable means is shown as connected on the one hand with the bore in the cylinder 15 and on the other hand with the auxiliary chamber extending between the valves 3 and 13. The operation is the same as that described with reference to the arrangements illustrated in FIGS. 1, 2 and 3.
  • a fluid compressor including at least one cylinder, a piston reciprocable therein, and at least one auxiliary pressure-adjusting chamber
  • a fluid compressor including at least one cylinder, a piston reciprocable therein and at least one auxiliary pressure-adjusting chamber
  • a fluid compressor including at least one cylinder, a piston reciprocable therein, and at least one auxiliary pressure-adjusting chamber, separated by a partition from the cooperating cylinder, the combination of two passages extending through said partition and connecting said cylinder with the associated auxiliary chamber, an adjustable throttling member in one of said passages through which a fraction of the fluid compressed by the piston in the compressor or cylinder is diverted into the auxiliary chamber, means adjusting the area of the passageway provided by the throttling member and a suction valve in the other passage allowing the passage of fluid from the auxiliary chamber into the compressor cylinder during the suction stroke of the piston in the compressor cylinder.
  • a fluid compressor including at least one cylinder, a piston reciprocable therein and at least one auxiliary pressure-adjusting chamber
  • a first central passage and a second annular passage surrounding the first passage and connecting said cylinder with the associated auxiliary chamber
  • an adjustable throttling member in the first passage through which a fraction of the fluid compressed by the piston in the compressor or cylinder is diverted into the auxiliary chamber
  • means adjusting the area of the passageway provided by the throttling member and an annular suction valve in the second passage allowing the passage of fluid from the auxiliary chamber into the compressor cylinder during the suction stroke of the piston in the compressor cylinder.
  • a fluid compressor including at least one cylinder, a piston reciprocable therein and at least one auxiliary pressure-adjusting chamber
  • a suction pipe opening into the auxiliary chamber a first suction valve between the suction pipe and the auxiliary chamber, two passages connecting said cylinder with the associated auxiliary chamber, an adjustalble throttling member in one of said passages through which a fraction of the fluid compressed by the piston in the compressor cylinder is diverted into the auxiliary chamber, means adjusting the area of the passageway provided by the throttling member and a second suction valve in the other passage allowing the passage of fluid from the auxiliary chamber back into the compressor cylinder during the suction stroke of the piston in the compressor cylinder.
  • a fluid compressor including at least one cylinder, a piston reciprocable therein and at least one auxiliary pressure-adjusting chamber, the combination of two passages connecting said cylinder with the associated auxiliary chamber, an adjustable throttling check valve in one of said passages through which a fraction of the fluid compressed by the piston in the compressor cylinder is diverted into the auxiliary chamber, an adjustable stop defining the outermost position to be assumed by the throttling check valve, means adjusting the location of said stop, and a suction valve in the other pas sage allowing the passage of fluid from the auxiliary chamher into the compressor cylinder during the suction stroke of the piston in the compressor cylinder.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Cosmetics (AREA)
  • Compressor (AREA)
US472455A 1964-07-17 1965-07-16 Arrangement for the continuous adjustment of the output of a piston compressor Expired - Lifetime US3295748A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH940664A CH417835A (de) 1964-07-17 1964-07-17 Einrichtung zur stufenlosen Regulierung der Förderleistung an Kolbenkompressoren

Publications (1)

Publication Number Publication Date
US3295748A true US3295748A (en) 1967-01-03

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US472455A Expired - Lifetime US3295748A (en) 1964-07-17 1965-07-16 Arrangement for the continuous adjustment of the output of a piston compressor

Country Status (5)

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US (1) US3295748A (de)
CH (1) CH417835A (de)
DE (1) DE1428005A1 (de)
GB (1) GB1092700A (de)
NL (1) NL6509166A (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415441A (en) * 1966-02-11 1968-12-10 Hoerbiger Ventilwerke Ag Method and device for the infinitely variable capacity control of pistontype compressors
US3878770A (en) * 1973-07-16 1975-04-22 Ingersoll Rand Co Clearance pocket assembly
US4043710A (en) * 1976-08-09 1977-08-23 Bunn Stuart E Compressor unloader assembly
US4234290A (en) * 1978-11-30 1980-11-18 Binks Manufacturing Company Turbine pump
EP0044606A1 (de) * 1980-07-17 1982-01-27 General Motors Corporation Leerlaufschaltung für einen Axialkolbenkompressor
US4445824A (en) * 1981-11-02 1984-05-01 Ball Value Co., Inc. Valve for compressor clearance or by-pass control
US4447193A (en) * 1981-07-20 1984-05-08 Ball Valve Co., Inc. Compressor unloader apparatus
US5580225A (en) * 1995-07-27 1996-12-03 Pettibone Corporation Pulsation causing check valve assembly for a plural piston pump system
US5611200A (en) * 1993-07-28 1997-03-18 Honeywell Inc. Linear hydraulic actuator with adjustable output speed
US20030106301A1 (en) * 1998-07-31 2003-06-12 Holtzapple Mark T. Quasi-isothermal brayton cycle engine
US20040154328A1 (en) * 1998-07-31 2004-08-12 Holtzapple Mark T. Vapor-compression evaporative air conditioning systems and components
EP1270900B1 (de) * 1998-07-31 2006-03-22 The Texas A & M University System Brennkraftmaschine
US20060239849A1 (en) * 2002-02-05 2006-10-26 Heltzapple Mark T Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20060279155A1 (en) * 2003-02-05 2006-12-14 The Texas A&M University System High-Torque Switched Reluctance Motor
US20070237665A1 (en) * 1998-07-31 2007-10-11 The Texas A&M Univertsity System Gerotor Apparatus for a Quasi-Isothermal Brayton Cycle Engine
US20080063551A1 (en) * 2006-09-13 2008-03-13 R. Conrader Company Head Discharging Compressor System
US20090324432A1 (en) * 2004-10-22 2009-12-31 Holtzapple Mark T Gerotor apparatus for a quasi-isothermal brayton cycle engine
US20100003152A1 (en) * 2004-01-23 2010-01-07 The Texas A&M University System Gerotor apparatus for a quasi-isothermal brayton cycle engine
US20100266435A1 (en) * 1998-07-31 2010-10-21 The Texas A&M University System Gerotor Apparatus for a Quasi-Isothermal Brayton Cycle Engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016015880B3 (de) * 2016-01-27 2025-12-31 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kolbenkompressor mit Entlüftungseinrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1867681A (en) * 1931-07-31 1932-07-19 Vitler Mfg Company Compressor
US2214922A (en) * 1938-02-10 1940-09-17 Carter Carburetor Corp Pulsating pressure device
US2241195A (en) * 1939-01-10 1941-05-06 Cooper Bessemer Corp Compressor unloading mechanism

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1867681A (en) * 1931-07-31 1932-07-19 Vitler Mfg Company Compressor
US2214922A (en) * 1938-02-10 1940-09-17 Carter Carburetor Corp Pulsating pressure device
US2241195A (en) * 1939-01-10 1941-05-06 Cooper Bessemer Corp Compressor unloading mechanism

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415441A (en) * 1966-02-11 1968-12-10 Hoerbiger Ventilwerke Ag Method and device for the infinitely variable capacity control of pistontype compressors
US3878770A (en) * 1973-07-16 1975-04-22 Ingersoll Rand Co Clearance pocket assembly
US4043710A (en) * 1976-08-09 1977-08-23 Bunn Stuart E Compressor unloader assembly
US4234290A (en) * 1978-11-30 1980-11-18 Binks Manufacturing Company Turbine pump
EP0044606A1 (de) * 1980-07-17 1982-01-27 General Motors Corporation Leerlaufschaltung für einen Axialkolbenkompressor
US4373870A (en) * 1980-07-17 1983-02-15 General Motors Corporation Variable capacity positive displacement type compressor
US4447193A (en) * 1981-07-20 1984-05-08 Ball Valve Co., Inc. Compressor unloader apparatus
US4445824A (en) * 1981-11-02 1984-05-01 Ball Value Co., Inc. Valve for compressor clearance or by-pass control
US5611200A (en) * 1993-07-28 1997-03-18 Honeywell Inc. Linear hydraulic actuator with adjustable output speed
US5580225A (en) * 1995-07-27 1996-12-03 Pettibone Corporation Pulsation causing check valve assembly for a plural piston pump system
US7093455B2 (en) 1998-07-31 2006-08-22 The Texas A&M University System Vapor-compression evaporative air conditioning systems and components
US20040154328A1 (en) * 1998-07-31 2004-08-12 Holtzapple Mark T. Vapor-compression evaporative air conditioning systems and components
US6886326B2 (en) 1998-07-31 2005-05-03 The Texas A & M University System Quasi-isothermal brayton cycle engine
EP1270900B1 (de) * 1998-07-31 2006-03-22 The Texas A & M University System Brennkraftmaschine
US20030106301A1 (en) * 1998-07-31 2003-06-12 Holtzapple Mark T. Quasi-isothermal brayton cycle engine
US9382872B2 (en) 1998-07-31 2016-07-05 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20070237665A1 (en) * 1998-07-31 2007-10-11 The Texas A&M Univertsity System Gerotor Apparatus for a Quasi-Isothermal Brayton Cycle Engine
US8821138B2 (en) 1998-07-31 2014-09-02 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20100266435A1 (en) * 1998-07-31 2010-10-21 The Texas A&M University System Gerotor Apparatus for a Quasi-Isothermal Brayton Cycle Engine
US7726959B2 (en) 1998-07-31 2010-06-01 The Texas A&M University Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20060239849A1 (en) * 2002-02-05 2006-10-26 Heltzapple Mark T Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US7663283B2 (en) 2003-02-05 2010-02-16 The Texas A & M University System Electric machine having a high-torque switched reluctance motor
US20060279155A1 (en) * 2003-02-05 2006-12-14 The Texas A&M University System High-Torque Switched Reluctance Motor
US20100003152A1 (en) * 2004-01-23 2010-01-07 The Texas A&M University System Gerotor apparatus for a quasi-isothermal brayton cycle engine
US20110200476A1 (en) * 2004-01-23 2011-08-18 Holtzapple Mark T Gerotor apparatus for a quasi-isothermal brayton cycle engine
US8753099B2 (en) 2004-01-23 2014-06-17 The Texas A&M University System Sealing system for gerotor apparatus
US7695260B2 (en) 2004-10-22 2010-04-13 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20100247360A1 (en) * 2004-10-22 2010-09-30 The Texas A&M University System Gerotor Apparatus for a Quasi-Isothermal Brayton Cycle Engine
US20090324432A1 (en) * 2004-10-22 2009-12-31 Holtzapple Mark T Gerotor apparatus for a quasi-isothermal brayton cycle engine
US8905735B2 (en) 2004-10-22 2014-12-09 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US20080063551A1 (en) * 2006-09-13 2008-03-13 R. Conrader Company Head Discharging Compressor System

Also Published As

Publication number Publication date
CH417835A (de) 1966-07-31
GB1092700A (en) 1967-11-29
NL6509166A (de) 1966-01-18
DE1428005A1 (de) 1969-01-30

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