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Publication numberUS2592940 A
Publication typeGrant
Publication dateApr 15, 1952
Filing dateApr 8, 1947
Priority dateApr 16, 1946
Publication numberUS 2592940 A, US 2592940A, US-A-2592940, US2592940 A, US2592940A
InventorsMaurice Monoyer
Original AssigneeMaurice Monoyer
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Pressure transformer
US 2592940 A
Abstract  available in
Images(3)
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Claims  available in
Description  (OCR text may contain errors)

April 15, 1952 MQNQYER 2,592,940

PRESSURE TRANSFORMER Filed April 8, 1947 3 Sheets-Sheet l A ril 15, 1952 M. MONOYER PRESSURE TRANSFORMER 3 Sheets-Sheet 2 Filed April 8, 1947 J21 6 MMM April 15, 1952 M. MONOYER PRESSURE TRANSFORMER 3 Sheets-Sheet 5 Filed April 8 1947 Patented Apr. 15, 1952 UNITED STATES PATENT OFFICE PRESSURE TRANSFORMER Maurice 'Monoyer, Brussels, Belgium Application April 8, 1947, Serial No. 740,189 In Belgium April 16, 1946 Claims. (01. 10351) The invention relates to the combination of an hydraulic pressure transformer with a low pressure pump and in particular with a centrifugal pump for the purpose of continuously delivering a liquid at high pressure.

An object of the invention is to provide a new combination of elements which is adapted to supply a continuous delivery of liquid at high pressure when supplied with driving liquid at a low pressure from a centrifugal pump.

Another object of the invention is to provide a combination of elements in which a centrifugal pump is supplying liquid at low pressure to a pressure transformer through a rotating distributor for driving differential double-acting pistons moving in low pressure cylinders having equal'diameter while the high pressure cylinders located at each end of each low pressure cylinder have diameters different from one another.

Still another object of the invention is to'provide a combination of a centrifugal pump with a pressure transformer in which the high pressure cylinders are alternately located around the rotating distributor so that the high pressure cylinders of a certain diameter are located between high pressure cylinders of different diameters.

Still another object of the invention consists in providing on the discharging pipe an automatic device for controlling the pressure of the exhausted liquid which comprises a chamber having two valves, one of which moves under the joint action of the pressures of the driving fluid and of the discharged fluid While the other is actuated under the action of the driving fluid only.

With these objects and other purposes as shown below, the invention will be described and more particularly pointed out in the following specification, drawings and claims.

In the drawings:

Figure 1 is a diagrammatic sectional view showing the principle of operation of the combination according to the invention.

Figure 2 is a diagrammatic sectional view particularly illustrating an automatic device on the discharging pipe.

Figure 3 is a diagrammatic sectional view showing a combination in which the high pressure cylinders have difierent diameters.

Figure 4 is a 'transversal sectional view through a combination with six differential pistons, wherein the high pressure cylinders of different diameter are alternately located around th distributor.

Figures 5, 6 and 7 are sectional views through the automatic device, the latter being respectively 'at rest, at the time of being actuated by the liquid at low pressure and at the time of being actuated at high pressure.

Figure 8 is a view partly in section and partly in perspective for illustrating the-speed reducing device.

In the figures like reference characters relate to like parts.

According-to Figure 1, a pump 1 draws liquid from a tank 2 and delivers it at low pressure through a pipe 3, which divides into two branches 6 and l, a rotary distributor 4, which is actuated by a pulley 5 and which puts these branches into communication with one or the other of the faces of a piston l0, freely sliding in a cylinder 12. Two other pistons H and Ila. connected to the piston I!) slide in two other cylinders l3 and [3a. l4 and I 5 are passages through the distributor 4, communicating with the pipes l and 6 respectively.

Assuming that the passage 15 of the distributor i is open, the passage M being closed, then the liquid arriving from the pump I through the pipe '6 traverses the distributor 4 and goes into a chamber 12a in the cylinder 12, so as to act upon the face 9 of the piston Ill, thus urging the differential piston Ill-l li la towards the left and producing a partial vacuum in the compression chamber Hi. The chamber l2a is filled with liquid coming from the pipe 6. The same applies to the chamber it, which is filled with liquid by a pipe ll, by which the two chambers |2a and I6 communicate with one another if a valve [8 located on this pipe is open. When the chamber 16 is full, the distributor 4 continuing its course opens the passage l4, thus enabling the liquid coming from the pipe 1 to.

enter the chamber I212.

The differential piston Hlll returns towards the right, compressing in the chamber It the liquid contained therein, which closes the valve I8 and opens a valve l9, which admits the liquid to a channel 29, leading to the service pipe 2|. The liquid contained in the chamber I20; returns to the tank 2 by a pipe 22 through a separate passage, not shown, provided in the distributor 4, which communicates with a pipe-line, not shown, and the cycle recommences with the opening of the port l5, the closing of the port Hi, and the opening of the ports, not shown, that enable the fluid contained in the chamber 121) to return to the tank 2.

Figure 2 represents an application of the in vention. In this figure, two differential pistons 2i and 22 are represented, moving in cylinders 29 and 3%! respectively. A distributor 25 turning in a casing 26 is actuated through the medium of a pulley 24 by a motor 23. In the casing 25, an annular crown-member 2'l2la is constructed in such a manner that the fluid can pass into the cylinders 29 and 38 on to one or the other face of the pistons 21 and 22 according to the position of ports 3| and 32 pro vided in the distributor 25.

The centrifugal pump l drawing water from the tank 2 feeds through the pipe 3 an annular cavity 27-2la. provided in the casing 26. Figure 2 represents the apparatus at the time when the distributor is so placed that the annular crown-member 21--2Ta enables the fluid to pass from the port 32 on to the face 34 of the piston 2| and from the port 3| on to the face 33 of the piston 22 in the direction of the arrows. The fluid is also directed into compression chambers 31 and 38 through pipes 35 and 36 by opening valves 39 and 4B.

The piston 2i is therefore urged upwards and the piston 22 downwards. This movement first has the effect of delivering the fluid contained in the portions 45 and 46 of the cylinders 29 and 30 through pipes 43 and 44 and through a central pipe-system 41 to the tank 2, and then of compressing the fluid that had been admitted into the compression chambers 48 and 49 during the preceding stroke, thus compelling the valves 50 and to open and to allow the fluid to pass into a pipe-system 52-5354-55, the end 55 of which leads to an automatic device 56, which feeds the service pipe 51.

Since the distributor 25 continues to turn, the same cycle recommences for the other faces of the piston, thus enabling the pipe system 5! to be continuously fed with compressed fluid through the automatic device 56.

It need hardly be said that the principle of the apparatus hereinbefore described can also be applied to pressure-reducing apparatus especially intended for liquids, which apparatus, receiving a high-pressure liquid, uses the driv ing power of the said liquid in order to deliver a greater volume of another liquid at low pressure.

If the system be used as a press pump, the various phases involved may be automatically effected, namely:

(1) Approach stroke of the piston of the pump (low pressure).

(2) Pressure stroke (at high pressure).

Automatic working is eifected by interposing an automatic device 56 (Figure 2), as hereinbefore stated. A pipe system 58 branched on the supply pipe 3 of the centrifugal pump is connected to the device 56, and the delivery of this pump constitutes the approach delivery at low pressure.

At the beginning of a pressing operation, the pressure in the pipe system 51 which leads towards the press is zero, and the device 56 is in the stoppage position (see also Figure 5), the

valves 59 and 60 pressing on their respective seats.

In order to lower the piston of the press, an operation which is effected at low pressure, the centrifugal pump l delivers into the pipe system 58, and raises the valve 59, and the fluid travels towards the service pipe 5'! (see also Figure 6). The valve 60 is kept on its seat by the action of a strong adjustable spring pressing upon this valve through the medium of a piston 6|. The pipe system 55 is therefore shut off by the valve 60, and hence there is established in the pipe system 525354-55 a pressure equal to the maximum pressure which is capable of being produced by the small pistons Condelivery of the pump l.

and hence the pressure-transformer is for the moment out of service and does not use the This delivery therefore passes entirely through the pipe system 58 the service pipe 51 by raising the valve 59, and effects the low-pressure approach stroke of the press connected to this service pipe.

As soon as this stroke is terminated, which happens when the force on the piston of the press increases, the delivery of the pump I stops and the pressure in the pipe-system 5851 therefore increases up to the maximum value which the centrifugal pump can attain.

This feature has two results:

(1) The valve 59 is closed by the action of its return spring, since the delivery is zero; and

(2) The pressure attained in the pipe 51 is also transmitted to the inside of the apparatus 56, that is to say, to a chamber 62, which communicates with the pipe 51.

This pressure is just the pressure which, acting upon the piston Si. is capable of overcoming the tension of the adjustable spring 63. Hence, the piston 6| moves, compressing the spring 63 and liberating the valve 60, which opens. We then have the position of Figure 7, that is to say, the valve 59 is closed and the valve 68 is open. Owing to the opening of the latter valve, the pipe system 54 (which was subjected to high pressure as indicated at the beginning of this description) is put into communication with the chamber 62 and with the pipe system 51, which are both at low pressure. Consequently, the pressure in the pipe system 54 falls so as to equal that of the pipe 51 and the chamber 62.

At this junction the pressure-transformer begins to function. Indeed, the pressure in the pipe system 525354-55 having fallen, the small pistons 62, 63, 64 and 65 are no longer subjected to a force capable of counteracting the force acting upon the pistons 2| and 22, and the movement of the said pistons is produced while eifecting the discharge of the delivery occasioned by the pistons 62, 63, 64 and through the manifold 5253--5455 towards the pipe system 51 and passing through the valve 60, which is raised. I

The second stage of the press operation now begins, that is to say, the stage of the highpressure stroke. This stroke will continue until the maximum pressure has been reached in the pipe system 51, which pressure will be that causing the pistons 62, 63, 64 and to be immobilised as hereinbefore explained.

When the press operation is completed, the pipe system 51 is isolated from the press by a cock placed on the said press. This pipe system 51 therefore remains at maximum pressure, thus keeping the pistons 62, 63, 64 and 65 immobilised.

At the time of a fresh press operation, the pipe system 51 is again put into communication with the press (the pressure of which has been previously reduced to zero) which has the effect of returning the valve 60, to its seat through the action of a spring 63, which is no longer balanced by the force on the piston 6|, and the same cycle recommences.

It is possible further to increase the effectiveness of such a hydraulic-pump press by providing two series of pistons of different cross sections, thus enabling an intermediate pressure to be created, which may be called moderate pressure.

(3) Small delivery at high pressure by the second seriesof pistons.

This automatic apparatus is, in this case, the apparatus represented at -I0 in Figure 3.

Itwill first of all be noticed that the pipes 35 and, 38 inFigure .2 are replaced in Figure 3 by tubes or ducts 84a, 85a, 86 a, 8117,, which are inside pistons 84, 85, 88 and 81, provided with valves-8412,1351), 88b and 81b respectively at their ends, :and communicating with the chambers of the :[IliSiJQHS 82 and :83 throughv lateral openings, these tubes thusenabling the part of the fluid to be compressed to enter the compression chambers 88, 8.9,, 90 and 9| .so as to be com- Pressed therein.

In Figure 3, TI is a retaining, or non-return valve located .at the low pressure, 12: isa valve loaded with an adjustable spring for the meanpressure delivery, and "I3 is .a valve loaded with an adjustable springfor 'the high-pressure delivery.

(2) Moderate delivery, at moderate pressure, through the manifold 92 corresponding to the pistons 84 and 85 which function alone-the two pistons 88 and 8'! (see Figures'3 and 4) remaining stationary;

(3) Small delivery at high pressure through the manifold .93 corresponding to the two pistons 86 and 81 (Figures 3 and 4) which function alone,

the'pistons 84 and 85 being automatically immobilised because they cannot overcome the pressure established in the manifold 92, which is greater than the pressure that canbe produced by the pistons 84 and 85.

An electric motor 95 with a vertical shaft is the sole source of motive power for the unit, and

the distributor 8| is-set-inmotion by means of a speed-reducing device with gear wheels 08, it-

" self driven by the vertical spindle of the centrifugal pump.

The mode ,of operation is identical with that ofthe apparatus illustrated in Figure 2, with the modification that when the low-pressure deliveryrterminates. the valve 12 opens under the action of the. :pressure on thepiston, and,

when this medium-pressure delivery terminates.

the valve.".'|;3 opens :under the action of the .new

pressure acting upon the piston 1-5,. and does each of them a different .series of valves, pistons and springs.

Figures .3 and 4 show a form of construction of .a .pressqpump so arranged as to operate the centrifugal pump and the distributor by the same source of. power.

.The functioning .is as. follows: A centrifugal pump 16 sucks the liquid from a tank 11 forming a.s.tand.forrthe group, through-1a filter l8, and discharges the said liquid at a .low pressure through channels I9 into an annular chamber. A distributor 8| effects the successive dis tribution of the liquid between groups of pistons 82 and 83, which are thereby actuated with a reciprocating motion, as are also the mediumpressure pistons 84- and 85, and the high-presesure pistons 88 and 81, which discharge into chambers 88, 89, 90 and 9| leading to manifolds 92 and93.

The medium-pressure pistons 84 and '85, the

cross sections 1 area of which is greater than.

that of the pistons 86 and-81, produce a final pressure which is lower than that of the latter pistons, but thequanti-ty delivered by the former pistons is larger. Home, with the automatic adjusting device 10, the following stages occur forione press operation:

('1) Approach-stroke, during which the centrifugal pump delivers directly through the manifold, the pistons 84, 85, 88 and 81 being immobilised;

device and the distributor.

Figure 8 gives details of the speed-reducing The speed-reducing device is constructed as follows: .A main shaft 91, connecting the motor to the centrifugal pump, carries a pinion 98, which engages with two toothed wheels 99 and I00. These two toothed wheels are mounted upon spindles I0'I and '|02 whichare fixed to a plate 103 which is rigid with a distributor -8I. Moreover, these spindles |0| and I02 carry two small pinions I05 and I06 driven by the wheels 99 and -I00 and engaging with an "internally toothed .crown wheel I0], which remains fixed.

The rotation of the pinion 98 rotates the plate I03- and consequently the distributor 8|, in the same direction but at a very much reduced speed, since the latterspeed is a function of the ratio between the! numbers of teeth on the pinion 98 and on the toothed wheels 99 and I00 on the one hand, and of the ratio between the numbers of teeth of the satellite pinions I05 and I05 and the ring of internal teeth I01 on the other hand.

The distributor 8|. comprises a series of passages. I08 and I09 which traverse the vwall, and of cells III! and III, which have no communication with the inside of the distributor sheath 8|,. When this distributor turns; one cell IIO puts an annular channel II 2II2a, which is under pressure, into communication with the lower face .of the piston 83 through a channel IYI4,

while the upper face of the piston 83. is put into pens over the whole of the series of pistons, so

that the delivery occasioned by the pistons is. continuous. This is due to a careful arrangemerit of the channels and ports over the dis- (1) To use an air or gas driving-fluid and to compress a liquid;

The low-pressure feed pump may be omitted if use be made of a driving fluid at low pressure drawn from an existing supply pipe (water from a hydraulic main or the like).

In this case the rotation of the rotary distributor is effected by means of a separate small motor, or by any other device, turbine for example, using the driving fluid.

What I claim is: I

1. In a combination with a centrifugal pump of a pressure transformer comprising a plurality of low pressure cylinders, a high pressure cylinder at each end of each low pressure cylinder, a difierential piston moving in each of said cylinders, a rotating distributor located between said cylinders for alternatively supplying fluid from said centrifugal pump to the opposite sections of the low pressure cylinders and to the high pressure cylinders, an external means for driving said rotating distributor, a discharging pipe, an automatic device located on said discharging pipe for controlling the pressure of the exhausted fluid, said automatic device comprising a chamber provided with two valves, one of which moving under the joint action of the pres sures of the driving fluid and of the discharged fluid, the other moving under the action of the driving fluid only.

2. In a combination with a centrifugal pump of a pressure transformer comprising a plurality of low pressure cylinders having the same diameters, a high pressure cylinder at each end of each low pressure cylinder, some high pressure cylinders having equal diameters, a differential piston moving in each of said cylinders, a rotating distributor located between said cylinders for alternatively supplying fluid from said centrifugal pump to the opposite sections of the low pressure cylinders and to the high pressure cylinders, an external means for driving said rotating distributor, a discharging pipe, an au tomatic device located on said discharging pipe, said automatic device comprising a chamber provided with two valves, one of which moving under the joint action of the driving fluid and of the discharged fluid, the other moving under the action of the driving fluid only.

3. In a combination with a centrifugal pump of a pressure transformer comprising a plurality of low pressure cylinders having the same diameters, a high pressure cylinder at each end of each low pressure cylinder, half the number of the high pressure cylinders having diameters different from those of the other half, a differential piston moving in each of said cylinders, a rotating distributor located between said cylinders for alternatively supplying fluid from said centrifugal pump to the opposite sections of the low pressure cylinders and to the high pressure cylinders, an external means for driving simultaneously said rotating distributor and said pump, a discharging pipe, an automatic device located on said discharging pipe, said automatic device comprising a chamber provided with two valves, one of which moves under the joint action of the pressures of the driving fluid and of the discharged fluid and the other under the action of the driving fluid only.

4. In a combination with a centrifugal pump of a pressure transformer comprising a plurality of low pressure cylinders, a high pressure cylinder at each end of each low pressure cylinder, a differential piston moving in each of said cylinders, a rotating distributor located between said cylinders for alternatively supplying fluid from said centrifugal pump to the opposite sections of the low pressure cylinders and to the high pressure cylinders, an external means-for driving said rotating distributor, a discharging pipe, an automatic device located on said discharging pipe for controlling the pressure of the exhausted fluid, said automatic device comprising a chamber provided with two valves, one of which moving under the joint action of the pressures of the driving fluid and of the discharged fluid, the other moving under the action of the driving fluid only, said low pressure cylinders havingequal diameter and said high pressure cylinders having different diameters.

5. In a combination with a centrifugal pump of the pressure transformer comprising a plurality of low pressure cylinders, a high pressure cylinder at each end of each low pressure cylinder, a diflerential piston moving in each of said cylinders, a rotating distributor located between said cylinders for alternatively supplying fluid from said centrifugal pump to the opposite sections of the low pressure cylinders and to the high pressure cylinders, an external means for driving said rotating distributor, a discharging pipe, an automatic device located on said discharging pipe for controlling the pressure of the exhausted fluid, said automatic device comprising a chamber provided with two valves, one of which moving under the joint action of the pres-'- sure of the driving fluid and of the discharged fluid, the other moving under the action of the driving fluid only, said low pressure cylinders having equal diameter and said'high pressure cylinders having different diameters, said high pressure cylinders being arranged around the rotating distributor so that the high pressure cylinders having a certain diameter are located between the high pressure cylinders of a difiercut-diameter.

MAURICE MONOYER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US38531 *May 12, 1863Themselves And HImprovement in water-engines
US305972 *May 9, 1883Sep 30, 1884 Axel sjogeen
US1377585 *Jul 18, 1919May 10, 1921Reiert JohansonHydraulic transformer
US2053543 *Jan 18, 1932Sep 8, 1936Continental Motors CorpFuel pumping system for engines
US2484884 *Jun 10, 1946Oct 18, 1949Hanna Engineering WorksHydraulic transformer
IT285985B * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2689527 *Feb 11, 1949Sep 21, 1954Borg WarnerFuel injector pump
US2698580 *Jan 23, 1951Jan 4, 1955Cav LtdPump
US2708412 *Dec 2, 1950May 17, 1955Otto MuellerBooster for increasing delivered hydraulic pressure
US2819835 *Nov 26, 1954Jan 14, 1958Harwood Engineering CoSystem for delivering a continuous and steady flow of a compressible fluid at high pressure
US2829501 *Aug 21, 1953Apr 8, 1958D W BurkettThermal power plant utilizing compressed gas as working medium in a closed circuit including a booster compressor
US2867893 *Sep 1, 1955Jan 13, 1959Arne O AndresenDescaling apparatus for forging ingots
US2935952 *Jun 12, 1957May 10, 1960Howard E RosePressure booster or de-booster
US2961741 *May 9, 1956Nov 29, 1960American Steel FoundriesHydraulic descaler
US2970546 *Apr 23, 1958Feb 7, 1961White Howard TFluid pressure systems
US3022738 *Apr 20, 1959Feb 27, 1962Archie Krute EverettPump systems
US3033218 *Sep 21, 1959May 8, 1962Fairchild Stratos CorpFluid proportioner
US3181286 *Nov 5, 1958May 4, 1965Nat Tank CoApparatus for recovering hydrocarbons and liquids from gas streams
US3266422 *Dec 5, 1961Aug 16, 1966Matheisel Rudolph ARechargeable accumulator system for auxiliary power supply
US3314367 *Sep 20, 1965Apr 18, 1967Crane CoHydraulic transformer
US3344714 *Oct 5, 1964Oct 3, 1967Wilkins & AssFluid pressure transmission system
US3450055 *Jun 21, 1967Jun 17, 1969Lucas Industries LtdFluid proportioning devices
US3487892 *May 31, 1968Jan 6, 1970Kiefer William JPositive displacement lubrication system
US3604213 *Jan 10, 1969Sep 14, 1971Herbert Leland ParsonsChemical grouting proportioning pumping method and apparatus
US4235154 *Mar 29, 1979Nov 25, 1980Neumann Engineering & Manufacturing CompanyVibration motor
US4373874 *Jul 6, 1981Feb 15, 1983Albert PhillipsFluid actuated pump system
US4378784 *Feb 8, 1982Apr 5, 1983Grumman Aerospace CorporationSolar heating system
US4714411 *Jun 16, 1986Dec 22, 1987Normalair-Garrett (Holdings) LimitedFluid pressure intensifier device
US4752192 *Jun 12, 1987Jun 21, 1988Ab Asea-AtomRotating drum pump having a plurality of fluid driven pistons
US4780064 *Feb 10, 1986Oct 25, 1988Flow Industries, Inc.Pump assembly and its method of operation
US4919039 *Jul 25, 1988Apr 24, 1990General Electric CompanyHydraulic turning gear
US5205722 *Jun 4, 1991Apr 27, 1993Hammond John MMetering pump
US5387090 *Apr 11, 1994Feb 7, 1995Knf Neuberger GmbhTwo-stage positive displacement pump
US5584669 *Jan 24, 1995Dec 17, 1996Knf Neuberger GmbhTwo-stage positive displacement pump
US7740455Jul 9, 2007Jun 22, 2010Brian NissenPumping system with hydraulic pump
US20070240595 *Apr 18, 2007Oct 18, 2007Heidelberger Druckmaschinen AgMethod and apparatus for metering printing fluid, printing press and system having the apparatus and method for driving a pump
EP2971800A4 *Mar 14, 2014Nov 23, 2016Atomic Energy Of Canada Ltd Énergie Atomique Du Canada LimitéeRegulator apparatus having a charging valve assembly and a flow multiplier assembly
WO2014138998A1Mar 14, 2014Sep 18, 2014Atomic Energy Of Canada Limited / Énergie Atomique Du Canada LimitéeRegulator apparatus having a charging valve assembly and a flow multiplier assembly
Classifications
U.S. Classification417/203, 417/225, 91/327, 417/252, 417/347, 91/39, 417/397, 91/36
International ClassificationF04B9/117, F04B9/113, F15B3/00, F04B9/00
Cooperative ClassificationF04B9/113, F04B9/1172, F15B3/00
European ClassificationF15B3/00, F04B9/113, F04B9/117A