US3415441A - Method and device for the infinitely variable capacity control of pistontype compressors - Google Patents

Method and device for the infinitely variable capacity control of pistontype compressors Download PDF

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Publication number
US3415441A
US3415441A US614192A US61419267A US3415441A US 3415441 A US3415441 A US 3415441A US 614192 A US614192 A US 614192A US 61419267 A US61419267 A US 61419267A US 3415441 A US3415441 A US 3415441A
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United States
Prior art keywords
valve
compressor
chamber
suction
pipe
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Expired - Lifetime
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US614192A
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English (en)
Inventor
Kehler Theodor Karl
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Hoerbiger Ventilwerke GmbH and Co KG
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Hoerbiger Ventilwerke GmbH and Co KG
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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

Definitions

  • the invention relates to a method and a device for the infinitely variable capacity control of piston-type compressors comprising a compressor cylinder including suction valve means at the suction end and delivery valve means at the delivery end of the compressor.
  • the capacity of piston-type compressors is controlled by means of a by-pass pipe extending from the delivery end of the com-- pressor back to the suction end, wherein a manually or automatically, controled throttle valve is incorporated defining the amount of compressed medium flowing back to the suction end of the compressor.
  • a manually or automatically, controled throttle valve is incorporated defining the amount of compressed medium flowing back to the suction end of the compressor.
  • part of the compressed medium is branched off the delivery end of the compressor and delivered to a chamber, to be returned during the suction stroke of the compressor from the chamber to the cylinder space of the compressor.
  • This method is essentially a P CC combination between the conventional by-pass control system and the method of controlling by means of clearance chambers; however, substantial power losses as inherent in by-pass control are largely avoided and on the other hand, there is no need for any positively actuated valves as are necessary both for the clearance chamber control and for the backfiow or dynamic pressure control.
  • a device comprising a by-pass duct originating at the delivery end of the compressor, an adjustable throttle valve incorporated in the by-pass duct, a clearance chamber wherein the said by-pass duct terminates, and an automatic check valve used as a suction valve provided between the clearance chamber and the cylinder of the compressor and connecting the clearance chamber with the cylinder space of the compressor.
  • the device according to the invention distinguishes itself by its plain design and outstanding dependability in. operation, while permitting infinitely variable capacity control ranging from maximum delivery to idling.
  • noninterference with the working valves of the compressor precludes premature wear of the said valves and assures smooth operation of the compressor.
  • Capacity control by means of the device according to the invention is achieved by the alteration of the crosssectional flow area of the throttle valve inserted in the by-pass duct.
  • the compressor operates at full load.
  • part of the compressed medium flows into the clearance chamber, building up an intermediate pressure therein which is superior to the suction pressure, and flows during the suction stroke of the piston through the check valve of the clearance chamber back into the cylinder space, from where it is delivered back into the delivery pipe.
  • the intermediate pressure built up in the clearance chamber the quantity of the medium sucked in from the suction pipe diminishes or suction ceases completely, so that delivery is correspondingly reduced.
  • the throttle valve may be adjusted by hand or automatically controlled as a function of any operational factor, such as final pressure.
  • the most convenient size of the clearance chamber, of the cross-section of the bypass duct and the throttle valve depends on the design features of the compressor to be controlled and above all, on the desired control range. By appropriate adaptation, particularly of the size of the clearance chamber, to given operational conditions, loss in efficiency can be held to a very low level.
  • FIG. 1 is a schematic view of an embodiment of the invention showing the control of a compressor
  • FIG. 2 is an axial cross-sectional view of another embodiment of the invention.
  • the compressor comprises a cylinder 1 and a piston 2 defining a cylinder space 3.
  • valve chambers 4 and 5 are provided, of which the valve chamber 4 receives the suction valve 6 and communicates with the suction pipe 7, whereas the valve chamber 5 serves to receive the delivery valve 8 and leads to the delivery pipe 9.
  • the cylinder 1 is closed by means of a cover 10.
  • a clearance chamber 11 is provided on top of the cover 10 and communicates with the cylinder space 3 via a check valve 12 located in the cover 10, the said check valve permitting suction from the clearance chamber 11 into the cylinder space 3.
  • a by-pass pipe 13 originates at the valve chamber 5 at the delivery end of the compressor, an adjustable throttle valve 14 being inserted in the by-pass pipe which leads to the clearance chamber 11.
  • a by-pass pipe 13 with a throttle valve 14 originates at the valve chamber 5, a cooler being additionally inserted in the by-pass pipe 13.
  • the by-pass pipe 13 does not terminate in a separate clearance chamber but in the valve chamber 4, which is part of the clearance chamber 11.
  • the clearance chamber 11 is composed of the valve chamber 4 and of a cylinder 17 communicating with same via a pipe 16, the piston 18 of said cylinder being displaceably by a handwheel by means of a spindle 19, so that the volume of the clearance chamber 11 can thereby be altered.
  • the clearance chamber 11 and the valve chamber 4 are limited by means of an automatic check valve 21 opening in the same direction as the suction valve 6.
  • an automatic check valve 22 opening in the same direction as the delivery valve 8 is provided between the delivery pipe 9 and the valve chamber 5.
  • the method according to the invention and the operation of the control device according to the invention will be understood best with reference to the schematic view shown in FIG. 1.
  • the medium to be compressed is sucked from the suction pipe 7 through the valve chamber 4 and via the suction valve 6 into the cylinder space 3 where it is compressed by means of the piston 2, passing through the delivery valve 8 into the valve chamber 5 and the delivery pipe 9.
  • the throttle valve 14 When the throttle valve 14 is closed, the whole of the compressed medium is evacuated through the delivery pipe 9 so that the compressor will operate at full load. If, however, the throttle valve 14 is partly opened, part of the compressed medium flows through the by-pass pipe 13 and via the throttle valve 14 into the clearance chamber 11 from where it is sucked back via the check valve 12 into the cylinder space 3 during the suction stroke of the piston.
  • the device shown in FIG. 2 works in the same manner.
  • the medium flowing back from the delivery end of the compressor through the bypass pipe 13 is-not returned to a separate clearance chamber but to the valve cham ber 4 from where it is again sucked into the cylinder chamber 3 by means of the suction valve 6.
  • the check valve 21 prevents complete expansion of the returned medium into the suction pipe 7.
  • the cylinder 17 with piston 18 adjoining the valve chamber 4 permits infinitely variable adjustment of the volume of the clearance chamber 11 defined by the valve chamber 4, the pipe 16 and the cylinder 17. This is an advantage insofar as the size of the clearance chamber can be varied so as to suit any given regulating range of the compressor.
  • a relatively small clearance chamber is an advantage, since a comparatively high pressure build-up is then possible within a short period of time even with the throttle valve only slightly open, whereas for idling, the clearance chamber should be as large as possible so as to receive the whole of the medium compressed during the piston stroke.
  • the check valve 22 provided between the valve chamber 5 and the delivery pipe 9 as shown in FIG. 2 serves to prevent an excessive amount of compressed medium to flow from the delivery pipe 9 through the by-pass pipe 13 and the clearance chamber 11 into the cylinder space 3, filling the same completely when the throttle valve 14 is wide open. In that case, the compressor would always have to work against full feed pressure.
  • the cooler 15 incorporated in the by-pass pipe 13 serves to cool the overflowing pressure medium so as to avoid overheating of the compressor, particularly when delivery has been severely curtailed. The same result might also be achieved by incorporating the cooler in the delivery pipe of the compressor and the by-pass pipe 13 would branch 01f the said delivery pipe downstream of the cooler.
  • the clearance chamber can be defined by a suction chamber located in the cylinder-head in lieu of a valve chamber provided on the side of the cylinder of the compressor, or else part of the suction pipe might be used as a clearance chamber, in which case the said suction pipe would have to be closed by a valve corresponding to the check valve 21 shown in FIG. 2.
  • provision might be made for the gradual alteration of the size of the clearance chamber, such as for example, by the provision of one or several connectable and disconnectable clearance pockets.
  • a single clearance chamber of constant size, adapted to meet the requirements of given operational conditions, will be found to be sufficient.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
US614192A 1966-02-11 1967-02-06 Method and device for the infinitely variable capacity control of pistontype compressors Expired - Lifetime US3415441A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT126066A AT277435B (de) 1966-02-11 1966-02-11 Einrichtung zum stufenlosen Regeln der Liefermenge von Kolbenverdichtern

Publications (1)

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US3415441A true US3415441A (en) 1968-12-10

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US614192A Expired - Lifetime US3415441A (en) 1966-02-11 1967-02-06 Method and device for the infinitely variable capacity control of pistontype compressors

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US (1) US3415441A (da)
AT (1) AT277435B (da)
BE (1) BE693360A (da)
DE (1) DE1628163A1 (da)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3523745A (en) * 1968-05-20 1970-08-11 Air Reduction Vent valve
US4065237A (en) * 1976-05-17 1977-12-27 The Scott & Fetzer Company Valve apparatus for expansible chamber
US4413951A (en) * 1980-10-06 1983-11-08 Lexair, Inc. Capacity control arrangement for fixed speed compressor
US5141415A (en) * 1988-05-06 1992-08-25 Alfred Teves Gmbh Piston pump
US5219455A (en) * 1991-02-26 1993-06-15 Giant S.R.L. Pump for ice-cream machines
US20140286799A1 (en) * 2013-03-20 2014-09-25 Wen San Chou Air compressor having buffering compartment
US9046096B2 (en) 2007-08-21 2015-06-02 Wabco Gmbh Piston air compressor
TWI548812B (zh) * 2013-02-23 2016-09-11 周文三 空氣壓縮機裝置
US11592014B2 (en) * 2018-03-01 2023-02-28 Ai Alpine Us Bidco Inc. Method and system for gas compressor control

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3908610A1 (de) * 1989-03-16 1990-09-20 Wabco Westinghouse Fahrzeug Einrichtung zur erzeugung von druckluft

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1154798A (en) * 1912-07-29 1915-09-28 Charles Otis Palmer Governor for air-compressors.
US1740967A (en) * 1928-03-28 1929-12-24 Frick Co Variable-capacity-control compressor
US1759617A (en) * 1927-08-27 1930-05-20 Firm Hoerbiger & Co Gas compressor
US2036846A (en) * 1934-03-14 1936-04-07 York Ice Machinery Corp Compressor
US2047167A (en) * 1932-04-13 1936-07-07 Baldwin Southwark Corp Adjustable clearance mechanism
US3255955A (en) * 1962-10-04 1966-06-14 Hoerbiger Ventilwerke Ag Infinitely variable capacity control system for compressors and device for stepless regulating according to this system
US3295748A (en) * 1964-07-17 1967-01-03 Burckhardt Ag Maschf Arrangement for the continuous adjustment of the output of a piston compressor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1154798A (en) * 1912-07-29 1915-09-28 Charles Otis Palmer Governor for air-compressors.
US1759617A (en) * 1927-08-27 1930-05-20 Firm Hoerbiger & Co Gas compressor
US1740967A (en) * 1928-03-28 1929-12-24 Frick Co Variable-capacity-control compressor
US2047167A (en) * 1932-04-13 1936-07-07 Baldwin Southwark Corp Adjustable clearance mechanism
US2036846A (en) * 1934-03-14 1936-04-07 York Ice Machinery Corp Compressor
US3255955A (en) * 1962-10-04 1966-06-14 Hoerbiger Ventilwerke Ag Infinitely variable capacity control system for compressors and device for stepless regulating according to this system
US3295748A (en) * 1964-07-17 1967-01-03 Burckhardt Ag Maschf Arrangement for the continuous adjustment of the output of a piston compressor

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3523745A (en) * 1968-05-20 1970-08-11 Air Reduction Vent valve
US4065237A (en) * 1976-05-17 1977-12-27 The Scott & Fetzer Company Valve apparatus for expansible chamber
US4413951A (en) * 1980-10-06 1983-11-08 Lexair, Inc. Capacity control arrangement for fixed speed compressor
US5141415A (en) * 1988-05-06 1992-08-25 Alfred Teves Gmbh Piston pump
US5219455A (en) * 1991-02-26 1993-06-15 Giant S.R.L. Pump for ice-cream machines
US9046096B2 (en) 2007-08-21 2015-06-02 Wabco Gmbh Piston air compressor
TWI548812B (zh) * 2013-02-23 2016-09-11 周文三 空氣壓縮機裝置
US20140286799A1 (en) * 2013-03-20 2014-09-25 Wen San Chou Air compressor having buffering compartment
US9328725B2 (en) * 2013-03-20 2016-05-03 Wen San Chou Air compressor having buffering compartment
US11592014B2 (en) * 2018-03-01 2023-02-28 Ai Alpine Us Bidco Inc. Method and system for gas compressor control

Also Published As

Publication number Publication date
BE693360A (da) 1967-07-03
DE1628163A1 (de) 1971-08-05
AT277435B (de) 1969-12-29

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