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US3511582A - Method and apparatus for the continuous regulation of the output of piston pumps and piston compressors - Google Patents

Method and apparatus for the continuous regulation of the output of piston pumps and piston compressors Download PDF

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Publication number
US3511582A
US3511582A US698475A US3511582DA US3511582A US 3511582 A US3511582 A US 3511582A US 698475 A US698475 A US 698475A US 3511582D A US3511582D A US 3511582DA US 3511582 A US3511582 A US 3511582A
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United States
Prior art keywords
piston
valve
point
pressure
cut
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Expired - Lifetime
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US698475A
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English (en)
Inventor
Helmut Bauer
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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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston

Definitions

  • the invention relates to a method and apparatus for the continuous regulation of the output of piston pumps and piston compressors, especially pumps and compressors working at very high pressures, having hydraulic transmission of the driving power from a mechanically driven driving iston, e.g. driven by a crank or the like, to a working piston rigidly connected with the pumps or compressor piston, without changing the speed of the mechanical drive.
  • a mechanically driven driving iston e.g. driven by a crank or the like
  • a limit is set to the rational use of these modes of regulation because along with the difficulty in coping with the adjusting force necessary at high pressures, the constructional design presents extremely ditficult problems.
  • the two end chambers separated from one another by the driving and working pistons are connected together for an adjustable time interval forming a predetermined fraction (which may be zero) of one stroke period, whereby the working piston and thus the high pressure piston are brought to rest during the said time interval during each stroke.
  • Apparatus serving for carrying out this method comprises a first cut-off valve controlled in dependence on 3,511,582 Patented May 12, 1970 the movement of the driving piston and arranged in a first transfer duct between said end chambers, a first nonreturn valve arranged in said first transfer duct, a second cut-off valve also controlled in dependence on the movement of the driving piston, and arranged in a second transfer d not between said end chambers.
  • FIG. 1 shows the arrangement of the pistons for the hydraulic power transmission
  • FIG. 2 is a diagram showing pressure of the fluid medium being pumped or compressed, ploted against the movement of the two high pressure pistons, at full load;
  • FIG. 3 is a diagram showing the pressure in the hydraulic driving medium plotted against the movement of the driving piston, at full load;
  • FIG. 4 is a valve diagram at full load, that is with the cut-off valves closed;
  • FIG. 5 is a similar diagram to FIG. 2 but at less than full load
  • FIG. 6 is a similar diagram to FIG. 3 but at the same fraction of full load as in FIG. 5;
  • FIG. 7 is a corresponding cut-off valve diagram
  • FIG. 8 shows the complete mechanism with cut-01f valves, synchronising lever and non-return valves, and
  • FIG. 9 is a diagram illustrating the mode of operation of the synchronsing lever.
  • two high pressure pistons 1 are in known manner carried and moved by a working piston 2 which is actuated through oil or other hydraulic medium acted upon by a driving piston 3.
  • the pistons 1 are of smaller diameter than the piston 2 so that the pressure in the hydraulic medium is reduced compared with that in the fluid being pumped or compressed.
  • the high pressure cylinders 11' of the compressor or pump in which the pistons or plungers 1 work lie on opposite sides of the machine.
  • the effective surface of the working piston 2 is made greater than that of the driving piston 3 (as more clearly indicated in FIGURE 8) to reduce still further the pressure developed in the hydraulic medium the pressure in which is in the inverse ratio of the effective surface of the working piston 2, to that of the driving piston 3 which is mechanically driven in known manner, the piston strokes occurring in phase but in opposite direction, and their lengths also being in the same inverse ratio.
  • hydraulic medium oil will usually be referred to as the hydraulic medium.
  • FIG. 2 the course of the pressure of the fluid being compressed acting on the right hand high pressure piston 1 at full load during one complete stroke cycle is represented by the solid line 67896.
  • the dash line 12-1310-11-12 shows the course of the pressure of the fluid medium occurring at the same time and acting on the left hand high pressure piston 1.
  • the diagram in FIG. 3 shows the course of the hydraulic medium pressure in the cylinder end chambers 4 and 5 during power transmission at full load, neglecting the effects produced by compressibility of the oil, and inertia of the moving piston in order to simplify the drawing.
  • the line 6-7-8-9-6 indicates the pressure at full load for the right hand high pressure piston 1 and the line 10-11-12-13-10 the pressure for the left hand high pressure piston 1.
  • the compression lines and expansion lines cross at the points 14 and 15. At these two points therefore the pressures acting on the left hand and right hand high pressure pistons I are the same and in consequence again ignoring compressibility of the oil and inertia effects at the cylinder end chambers 4 and 5, the oil pressure must be equal at the points 14 and '15 of the diagram of FIG. 3.
  • the non-return valve opens at point at which the oil pressures on the two sides of the working piston 2 are again equal so that the oil can flow from one side of the piston to the o h when the working piston 2 and therewith the two high pressure pistons 1, again come to rest.
  • FIG. 5 The diagram of the reduced output according to FIG. 5 is characterised by the hatched area 6-14-20-21-8-15-22-23-6, and according to FIG. 6 by the hatched area -26-18-15-20. If the transfer is free of loss these areas of the diagram in FIG. 5 and FIG. 6 are equal and represent the power requirements.
  • the suction stroke which in the full load diagram is equal to the distance (FIG. 5) is shortened by the regulating operation to the distance 24. It will be seen that the distances 24 and 25 are proportional to the areas of the corresponding diagrams, i.e. the reduction in power requirement is as great as the reduction in the suction load and the regulation is theoretically free of loss.
  • connection between the cylinder ends 4 and 5 is established by the cut-off valve shortly after the dead point and is closed again by the valve after a period which is adjustable.
  • FIG. 8 The mechanism for regulating the double acting driving cylinder is shown in FIG. 8 which among other things shows a slide cut-off valve and a non-return valve for eachend of the cylinders disposed in a corresponding transfer duct connecting the end chambers 4 and 5.
  • the cut-off valves are driven from the driving piston 3 and run synchronously therewith.
  • the mode of operation of the valves is shown in FIG.-7.
  • a slide valve 27 which at the predetermined setting assumed, opens at the point 20' (FIG. 7) and remains open over the whole period 20-16-'11-20.
  • the valve opening is, however, ineffective up to the point 14 because a non-return valve 29 is provided which is so directed that it is held closed when the pressure in chamber 5 is higher than in chamber 4 and it only. permits flow of the oil through the slide valve when the relative values of the oil pressures in the chambers 4 and 5 on opposite sides of the piston 2 change over at point 14.
  • FIG. 8 shows diagrammatically a driving and adjusting mechanism for the slide valves 27 and 28.
  • the first slide valve 28 is driven from the driving piston 3 through a rocking lever 53.
  • One end point of the lever 53 is connected to the piston rod 31 of the driving piston 3.
  • the other end point 37 of the lever 53 will for the moment be assumed fixed.
  • the valve 28 is driven from the point 32 on the lever 53 and thus makes a movement which is synchronous with that of the driving piston 3 but on a smaller scale. If now the driving piston 3 moves to the right that is to say when pressure acts in the chamber 4, the valve 28 will also move to the right and at a certain instant will open a connection between the chamber 5 and the non-return valve 30.
  • the nonreturn valve 30 only opens during the movement of the driving piston 3 to the left when the pressure in the chamber 5 rises above the pressure in the chamber 4, i.e. at the point 15 in the diagram according to FIG. 7.
  • the instant of opening of the valve 28 can be adjusted at will by lengthening or shortening the corresponding valve rod 33. This is indicated diagrammatically in FIG. 8, e.g. by a screw sleeve 38 adjustable during operation.
  • the other chamber 5 is controlled by the slide valve 27 the movement of which must be opposite to that of the valve 28. Accordingly the valve 27 is driven through a reversing lever 35 with fulcrum at 36.
  • the upper end point 37 of the lever 53 is not in fact fixed as was above assumed but is connected through a link 38 with the working piston 2.
  • the mode of operation of the link 38 is diagrammatically shown in FIG. 9.
  • valve 28 reaches point 46.
  • connection from the cylinder end chamber 5 to the cylinder end chamber 4 is closed and the working piston 2 is set in movement. It reaches the end of the stroke 41 as soon as the driving piston 3 has reached the point 49.
  • the valve 28 is now at 44.
  • the stroke of the valve 28 is accordingly increased at part load. While at full load it is given by the length 45-47, at part load this length increases to the length 4448, when 48-46 corresponds to the opening of the valves and 4644 the closing.
  • the stroke of the valve 28 increases as the stroke of the working piston 2 is set smaller. This condition is desirable because at small outputs larger transfer flow cross sections are necessary.
  • the diagram of 'FIG. 9 also shows diagrammatically how by the operation of the synchronising lever 53 the mid-position of the working piston 2 is automatically set with reduction in stroke.
  • means for continuous regulation of the output of the pump or compressor without changing the speed of the mechanical drive comprising a first cut-off valve controlled in dependence on the movement of the driving piston and arranged in a first transfer duct between said end chambers, a first non-return valve arranged in said first transfer duct, a second cut-off valve also controlled in dependence on the movement of the driving piston and arranged in a second transfer duct between said end chambers, the movements of the cut-off valves being in opposite phase, and a second non-return valve arranged in said second transfer duct, the non-return valves being so disposed and the cut-off valves so timed that each transfer duct is opened by the non-return valve when the pressure in said end chambers equalise if the cut-off valve is open and
  • a piston pump or compressor as set forth in claim 1 in which the first cut-off valve is connected to the driving piston through a rocking lever which transmits the movements of the driving piston to the first cut-off valve synchronously but on a smaller scale.
  • a piston pump or compressor as set forth in claim 3 in which the drive of the second cut-off valve is effected from one end of a reversing lever the other end of which 18 connected to the first cut-off valve and which is fulcrummed between its ends.
  • a piston pump or compressor as set forth in claim 2 in which the drive to the first cut-off valve is through a valve rod the effective length of which can be adjusted, thereby to regulate the time of closing of the cut-otf valves.
  • a piston pump or compressor as set forth in claim 4 in which the length of the rod is adjustable by a screw sleeve into which the rod is screwed.
  • a piston pump or compressor as set forth in claim 2 in which the rocking lever is connected by one end to the piston rod of the driving piston and connected by its other end through a link with the working piston in such a Way that even at part-load operation with shortened stroke, the mid-point of the stroke always coincides with the midpoint of the length of the Working cylinder.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Reciprocating Pumps (AREA)
US698475A 1967-01-23 1968-01-17 Method and apparatus for the continuous regulation of the output of piston pumps and piston compressors Expired - Lifetime US3511582A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH90967A CH470582A (de) 1967-01-23 1967-01-23 Verfahren und Einrichtung zur stufenlosen Regulierung der Förderleistung an Kolbenpumpen und -kompressoren mit hydraulischer Übertragung für höchste Drücke bei konstanter Hubzahl

Publications (1)

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US3511582A true US3511582A (en) 1970-05-12

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US698475A Expired - Lifetime US3511582A (en) 1967-01-23 1968-01-17 Method and apparatus for the continuous regulation of the output of piston pumps and piston compressors

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US (1) US3511582A (xx)
BE (1) BE709650A (xx)
CH (1) CH470582A (xx)
DE (1) DE1653571A1 (xx)
FR (1) FR1551633A (xx)
GB (1) GB1209111A (xx)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3653211A (en) * 1969-06-12 1972-04-04 Burckhardt Ag Maschf Hydraulic power transmission
US3699676A (en) * 1971-09-08 1972-10-24 Eugene F Beck Hydraulic system

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1966608A (en) * 1932-08-11 1934-07-17 Cuthbert H Cardwell Engine for operating vehicle or other doors by compressed air
US2172240A (en) * 1937-01-27 1939-09-05 Sullivan Machinery Co Safety means for motors
US2450751A (en) * 1946-03-07 1948-10-05 Eastman Kodak Co Constant flow pump
US2766590A (en) * 1951-10-18 1956-10-16 Ford Motor Co Fluid pressure system for motivating a reciprocating load
US2882685A (en) * 1956-07-02 1959-04-21 Gleason Works Hydraulic motion transmitting system
US3040533A (en) * 1960-02-25 1962-06-26 Celotex Corp Hydraulic pressure equalizing system
US3108436A (en) * 1960-07-19 1963-10-29 Panhard & Levassor Ets Machines of the piston-pump type
US3115676A (en) * 1960-11-23 1963-12-31 American Beryllium Company Inc High speed forging apparatus
US3314366A (en) * 1964-12-22 1967-04-18 Burckhardt Ag Maschf Compressors or pumps with hydraulic transmission

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1966608A (en) * 1932-08-11 1934-07-17 Cuthbert H Cardwell Engine for operating vehicle or other doors by compressed air
US2172240A (en) * 1937-01-27 1939-09-05 Sullivan Machinery Co Safety means for motors
US2450751A (en) * 1946-03-07 1948-10-05 Eastman Kodak Co Constant flow pump
US2766590A (en) * 1951-10-18 1956-10-16 Ford Motor Co Fluid pressure system for motivating a reciprocating load
US2882685A (en) * 1956-07-02 1959-04-21 Gleason Works Hydraulic motion transmitting system
US3040533A (en) * 1960-02-25 1962-06-26 Celotex Corp Hydraulic pressure equalizing system
US3108436A (en) * 1960-07-19 1963-10-29 Panhard & Levassor Ets Machines of the piston-pump type
US3115676A (en) * 1960-11-23 1963-12-31 American Beryllium Company Inc High speed forging apparatus
US3314366A (en) * 1964-12-22 1967-04-18 Burckhardt Ag Maschf Compressors or pumps with hydraulic transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3653211A (en) * 1969-06-12 1972-04-04 Burckhardt Ag Maschf Hydraulic power transmission
US3699676A (en) * 1971-09-08 1972-10-24 Eugene F Beck Hydraulic system

Also Published As

Publication number Publication date
FR1551633A (xx) 1968-12-27
CH470582A (de) 1969-03-31
BE709650A (xx) 1968-05-30
GB1209111A (en) 1970-10-21
DE1653571A1 (de) 1971-07-08

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