US3861832A - Pump power governor - Google Patents

Pump power governor Download PDF

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Publication number
US3861832A
US3861832A US384789A US38478973A US3861832A US 3861832 A US3861832 A US 3861832A US 384789 A US384789 A US 384789A US 38478973 A US38478973 A US 38478973A US 3861832 A US3861832 A US 3861832A
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United States
Prior art keywords
pump
connecting rod
cylinder
piston
guide
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US384789A
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English (en)
Inventor
Claude M Pinson
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Poclain SA
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Poclain SA
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Filing date
Publication date
Priority claimed from FR7228292A external-priority patent/FR2195338A5/fr
Priority claimed from FR7314433A external-priority patent/FR2331253A5/fr
Application filed by Poclain SA filed Critical Poclain SA
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Publication of US3861832A publication Critical patent/US3861832A/en
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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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/24—Devices for determining the value of power, e.g. by measuring and simultaneously multiplying the values of torque and revolutions per unit of time, by multiplying the values of tractive or propulsive force and velocity

Definitions

  • a device for governing the power of a pump has a conventional system for varying its cylinder capacity Cl 0/450 and a control arrangement therefor including linked [51] Int.
  • the present invention relates to a device for governing the power of a pump of variable cylinder capacity.
  • the power of a hydraulic or pneumatic pump is determined from the product of the flow delivery rate from the pump and the pressure of the fluid delivered. Once this product has been determined it is necessary to keep it constant by governing the pump operation to follow a hyperbolic curve which determines the variation of one factor as a function of the variation of the other.
  • the invention proposes to cure this complexity and these disadvantages by a governor device which is simple to put into effect and precise in its results.
  • the object of the invention therefore is to provide a device for governing the power of a pump comprising particularly a system for controlling the variation of the cylinder capacity of the pump and a delivery pipe which consists of a first control member movable along a first rectilinear guide, the displacement of which varies in proportion to the value of the flow rate of the fluid conveyed by the delivery pipe, and a second control member movable along a second rectilinear guide, the displacement of which varies in direct ratio with the value of the pressure in the delivery pipe.
  • a connecting rod of variable length links the first and second members and passes through a fixed or predetermined pivot point located at the intersection between two straight lines each of which is drawn perpendicular to each of the rectilinear guides from the position of each of the first and second members signifying zero rate of flow or pressure.
  • This fixed pivot point is connected to the tip of the slide of a regulator valve in its position or rest connected with the connecting rod.
  • the regulator places the auxiliary pump in communication with the second chamber of the piston cylinder unit.
  • the auxiliary pump is connected to a fluid reservoir.
  • the second control member aforesaid consists of a piston-cylinder unit having a fixed piston which constitutes the second rectilinear guide for the cylinder mounted slidingly on this guide and defines, with the said cylinder, a chamber connected to an exhaust pipe.
  • the first control member consists of a movable cylinder mounted slidingly on a fixed piston which constitutes the first guide and defines in the cylinder two chambers connected to the delivery pipe for the pump on opposite sides of a restriction in the pipe.
  • a resilient member linked between the piston and the cylinder tends to make the volume of the chamber connected to the delivery pipe between the pump and the restriction a minimum.
  • the restriction in the last mentioned pipe is formed by a hollow conduit in the piston actuator rod of the first control member which has a gauge internal diameter and is arranged in series with the exhaust pipe.
  • the hollow actuator rod is slidably connected to the delivery pipe of the pump at the end thereof nearer to the pump.
  • the other end of the rod is anchored in a fixed position and the rod is formed from a material which has linear expansion characteristics compatible with the effects of the temperature on the viscosity of the fluid so as to compensate for temperature variatrons.
  • the first control member is formed by the tip of the system of control of the variation of the cylinder capacity of the pump retained slidingly in a slide extending parallel with the axis of the pump, onto which tip is linked one of the tips of the connecting rod aforesaid.
  • connecting rod is preferably linked to at least one of the first and second control members aforesaid by means of an arm formed integrally with the said member which arm extends perpendicular to the guide of the member and bears an adjustable member which forms the point of attachment of the corresponding tip of the connecting rod.
  • FIG. 1 is a diagrammatic representation of a first embodiment of a device in accordance with the invention
  • FIG. 2 is a diagrammatic representation of a second embodiment of a device in accordance with the invention.
  • FIGS. 3 and 4 are two respective variants upon the embodiments of FIGS. 1 and 2;
  • FIG. 5 is a diagrammatic representation of a third embodiment of the invention.
  • a device for governing the power of a pump 7 comprising a device for controlling the variation in its cylinder capacity 8 and a delivery pipe 9.
  • This device comprises a first control member sensitive to the variations of flow from the pump 7, consisting of a movable cylinder 10 containing and slidably receiving piston 11 having a rod 12 which constitutes a straight line guide for the cylinder.
  • the piston 11 divides cylinder 10 into two chambers 13 and 14, respectively connected to pipe 9 by two pipes or conduits 15 and 16 respectively formed on opposite sides of piston 11 in piston rod 12.
  • the latter also includes a restriction 9a in communication with pipe 9 as seen in FIG. 1 and which is gauged in diameter and length such that the flow of fluid in restriction 9a is always laminar whatever its rate of flow.
  • a spring 17 is positioned between piston l1 and the end of cylinder 10 in such a way that its effect tends to make the volume of the opposite chamber 13 a minimum.
  • a second cylinder 21 contains a piston 22 that divides the cylinder into two chambers with the chamber 24 thereof communicating with pipe 9 through a port 25 formed in the fixed piston rod 23, which acts as a guide for this cylinder.
  • Cylinder 21 is provided with a stud 27, having a position indicated at 27' which signifies zero pressure in pipe 9.
  • This stud is located in one of the slots 28 in a connecting rod 29, while a second slot 31 is arranged in connecting rod 29 so as to enable a pin 32 carried by the cylinder to slide along the connecting rod 29.
  • the pin 32 adopts at the very least, theoretically when the flow from the pump 7 is zero, the position as indicated at 32'.
  • the connecting rod 29 passes through the point 34 when the device is in equilibrium as shown. At the equilibrium position the tip or free end of the rod 35 which is pivotally connected to rod 29 is located at point 34.
  • the rod 35 controls the position of the slide of a regulator or valve 36 in the neutral position.
  • the end of rod 35 is connected with connecting rod 29 by means of a hingepin or the like in any convenient manner.
  • Regulator 36 is capable of putting an auxiliary pump 37 selectively in communication with: (1) a pipe 38 connecting it to a first chamber 39 of a doubleacting piston-cylinder unit 40; (2) with a pipe 42 connecting it to a second chamber 42 of the said unit 40; or (3) with a fluid reservoir 43 by means of pipeline 44.
  • the rod 40a of the piston of the unit 40 is linked to the member 8 for controlling the variation of the cylinder capacity of the pump 7.
  • the cylinders 10 and 21 have divergent movements when the device records an increase of pressure and an increase of flow simultaneously. Recording of the variation in flow is effected by means of a pressure take-off at each end of the restriction or gauge pipe 9a.
  • any variation in the rate of flow brings about a variation in load loss proportional to the variation in the rate of flow.
  • This load loss in the pipe 9a creates a drop in pressure in fluid downstream of the pipe 911 with respect to the fluid located upstream.
  • the pressure in the fluid upstream of the pipe 9a is the pressure in chamber 10 since the latter is connected to the portion of the pipe 9 upstream of the pipe 9a through the pipe or port 15.
  • recording of the pressure in pipe 9 is achieved by means of cylinder 21.
  • the pressure in chamber 24 of that cylinder is the same as that in the pipe 9 to which the chamber is connected through the pipe or conduit 25.
  • the spring 26 balances the effect of the pressure in the chamber 24 and the position of equilibrium attained by the cylinder 21 with respect to the fixed piston 22 results from greater or less compression of the spring 26, proportional to the value of the pressure recorded.
  • the device described is indeed a governor of the power of a pump. It is known in fact that the power of a pump is equal to the product of its rate of flow and the pressure of the fluid discharged. If the distance 32' 34 is called a, the distance 34 27' b, the distance 27 27 p (because it is significant of the pressure reigning in the pipe), and finally the distance 32' 32 q, one can write from the fact that the device is in equilibrium and hence that the connecting rod 29 passes through the point 34:
  • the governing principle therefore rests in the fact that the variation in the cylinder capacity of the pump must be subjected to the variation in the position of the connecting rod with respect to the predetermined point 34 and that this variation in cylinder capacity brings about in return, by the action of the member 10, the location of the connecting rod 29 straight through the point 34. The subjection is then in a closed loop. Any variation of one or both of the values of the pressure and the rate of flow of the fluid delivered by the pump 7 will modify the position of the pin carried by or received in the connecting rod.
  • This variation will be communicated to the slide of the regulator 36 which will establish a communication between the auxiliary pump 37 and one of the chambers 39 or 42 so as to displace the rod 40a of the unit 40 and thereby actuate the member 8 for controlling variation of the cylinder capacity of the pump 7 in the direction of a compensation of the variation of the pressures or rate of flow.
  • the connecting rod will change position and drive the slide of the regulator 36 into its position of putting the pump 37 in communication with the pipe 38 and the chamber 39, bringing about by filling of this chamber, a displacement of the rod 40a, and hence of the control member 8, in the direction of increasing the cylinder capacity.
  • any feeding of a chamber by the pump 37 opens the other chamber to the exhaust in the convention manner.
  • FIG. 2 another embodiment of the invention is illustrated in which certain members described in relation to FIG. 1 are identified with the same references.
  • the pump 7 is represented in the form of a barrel pump capable of being driven in rotation by a shaft 52.
  • the pump includes rotary pistons having piston rods 53 maintained constantly in contact with a tiltable disc or plate 54 which is part of the system of controlling the variation of the pumps cylinder capacity, as by feeding fluid under pressure into pipe 9.
  • the plate 54 is titltable (i.e., pivotable) on the axis or pivot 54a and is extended by a connecting rod 54b of variable length. This is achieved by use of a telescopic rod, without departing from the scope of the invention.
  • Pipe 9 is in communication with the pipe 25 of cylinder 21 in order to convey fluid at the discharge pressure from the pump into the chamber 24 of the second member in the manner described above with respect to H0. 1.
  • Connecting rod 29 is of variable length, and is linked between cylinder 21 and connecting rod 54b by means of an idler stud 55 slidably mounted in the slot 54c of the connecting rod 54b and the slot 31 of the connecting rod 29 at their point of intersection.
  • the stud is also slidably retained in a fixed slide or slot 56 which extends parallel to the axis of the pump 7.
  • the movable member indicating rate of flow is the stud 55 actuated by the plate 54 controlling the variation of the cylinder capacity of the pump 7.
  • the distance 55 S5 likewise called q signifies the theoretical rate of flow from the pump since this rate of flow in contrast to FIG. 1 is not measured but proceeds from the geometrical data of the pump.
  • the principle and the method of subjection of the pump is identical with that of the device described in relation to FIG. 1. It is seen particularly here that the plate 54 or the system of control 8 is actuated by a lug 57 carried by the rod 40a of the jack 40 and engaged in the slot 54c in the connecting rod 54b.
  • the device as shown in FIG. 1 governs the output power of the pump since the values that it takes into account are the pressure and rate of flow of the fluid really delivered.
  • the device as shown in FIG. 2 governs the input power of a pump because it takes into account a theoretical rate of flow and hence neglects leakages of fluid at the level of the pump.
  • FIGS. 1 and 2 enable governing of the power of a pump at its value W a X b.
  • FIGS. 3 and 4 show how one can in a simple manner act upon dimension a. It is quite obvious that these are only embodiments and that numerous variants can be applied to them.
  • FIG. 3 takes up again in an arrangement similar to that of FIG. 1 certain members from the latter with the same references.
  • the cylinder includes an arm I8 having a slot 19 in which is mounted slidingly the pin 32.
  • the latter through a clamping device 33 or the like is capable of being clamped or fixed in any position along arm 13.
  • the distance a to be taken into account is hence that which separates the point 34 from this guide 12'.
  • FIG. 4 shows a governor device similar to that of FIG. 3 with the same reference numerals applied to like ports, and has the possibility of selecting the power of the pump.
  • the slide 56 is arranged in a guide 59.
  • a screw-andmut system for example the position of the slide 56 with respect to the guide 57 is acted upon.
  • the dimension a is chosen and hence the power of the pump can be adjusted as described above.
  • the dimension q is only representative of the theoretical rate of flow from the pump if it is taken at a fixed distance from the axis of tilt 54a of the plate 54. It is therefore necessary to arrange, between the slide 56 and the connecting rod 54b linked to the plate 54, and auxiliary connecting rod 58 furnished with a slot 580. The length q is then measured at the level of the rod 40a of the jack 40 fixed with respect to the pump and the connecting rod 58 capable of being displaced parallel to itself under the action of the jack 40 recalls this length q to the level of the movable slide 54.
  • the device in accordance with the invention due to this possible subjection, enables governing of the power of a group of pumps comprising for example a constant flow pump and a variable flow pump such as 7.
  • the power of the constant flow pump being only a function of the pressure of the fluid delivered, it is sufficient to subject the slide 55 or the pin 32 to the pressure in the load circuit by means of a guide member of piston-cylinder type 21-22, the displacement of which would be made compatible with those of the members described in the device in accordance with the invention.
  • FIG. 5 is a variant upon the device described with respect to FIG. 1 with like parts bearing the same reference numerals.
  • the two movable members or cylinders 10 and 21 are arranged along parallel guides or piston rods 12 and 23.
  • the relationship W a X b p X q requires that in order to define similar triangles 32, 32', 34 and 27, 27', 34, described above.
  • the connecting rod 29 at its point coinciding with the point 34 must form a right angle. More generally, if the two guides aforesaid define any angle between them the connecting rod 29 which connects the two movable members must form an angle the complement of the angle between these two guides for the relationship a X b X p X q to hold.
  • the control of the pump is the same as in the cases of preceding figures, that is, in a closed loop between the slope of the control system 8 and the position of the connecting rod 29 with respect to the point 34.
  • FIGS. 1, 3 and 5 it is seen that the connection of the portion of pipe contained between the pump 7 and the guide 12 for the movable member 10 to the portion 9a of this pipe inside the guide 12 is slidable and enables the two portions to be movable with respect to one another in the direction of their greater dimension. This arrangement therefore enables movement of the guide 12 and in particular allows its expansion in the direction of its length.
  • the difference between the pressures in chambers 13 and 14 of the member 10 are representative of the load loss in the fluid in the pipe 9a and therefore of its rate of flow and its viscosity, the latter in general becoming lower with temperature.
  • a given position of equilibrium of the member 10 will signify a greater and greater rate of flow in proportion as the temperature of the fluid flowing in the pipe 9a rises.
  • the device in accordance with the invention has the further advantage of offering a simple kinematic device in which the movable members vary linearly with the physical magnitudes which they represent. The result is great ease of execution and easy initial adjustment.
  • a device for governing the power of a pump having exhaust and delivery pipes said device including control means for varying the pumps cylinder capacity, said device comprising a first rectilinear guide, a first control member movably mounted on said guide, means operatively connecting said control member to said pump for displacing said control member with respect to said guide distances proportional to the value of the rate of flow of the'fluid delivered by the pump; a second rectilinear guide, a second control member movably mounted on said second guide, means operatively connecting said second control member to said pump for displacing said second control member with respect to said second rectilinear guide distances which vary in direct ratio with the value of the pump delivery pressure; a connecting rod of variable length operatively connecting said first and second control members; said connecting rod being located to pass, when the device is in equilibrium, through a predetermined point defined by the intersection between two straight lines respectively drawn perpendicular to each of said guides from the relative position from each of the first and second control members, representative of zero rate of
  • a second chamber of said piston-cylinder unit having a piston rod operatively connected to the control means for varying pump displacement capacity when the connecting rod is displaced with respect to said predetermined point due to a drop in power of the pump;
  • said second control member consists of a piston-cylinder unit having a fixed piston which defines said second rectilinear guide for the cylinder mounted slidingly thereon.
  • said piston defining in said cylinder a chamber connected to said exhaust pipe; and resilient means in said cylinder connected between the piston and the cylinder for making the volume of the chamber a minimum.
  • said first control member consists of a movable cylinder mounted slidably on a fixed piston defining said first guide and forming in said last mentioned cylinder two chambers connected by a conduit having a restriction therein; and resilient means connected between the piston and cylinder for making the volume of the chamber connected to said delivery pipe between the pump and the restriction a minimum.
  • a device as defined in claim 3 wherein the restriction in said pipe is formed by a conduit formed in the actuator rod of the piston of the first control member, said conduit having a guaged internal diameter and arranged in series with an exhaust pipe.
  • a device as defined in claim 4 wherein said conduit is slidably connected to the delivery pipe of the pump, and said conduit is secured in a fixed position at its other end and is formed from a material which has linear expansion characteristics compatible with the effects of temperature on the viscosity of the fluid so as to compensate for temperature.
  • connecting rod is linked to at least one of the first and second control members by means of an arm formed integrally with its associated control member, which arm extends perpendicularly to the associated guide of the latter and includes means for adjustably securing one end of the connecting rod along the arm.
  • a device as defined in claim 6 wherein said slide is slidably mounted in a guide part arranged perpendicularly to its greater dimension and provided with means for fixing the slide in any of its positions; and an intermediate connecting rod of variable length arranged perpendicularly to said slide and capable of being displaced parallel to itself defining the linking of the connecting rod with the control system; and means for connecting the connecting rod and the intermediate connecting rod in the slide, the connection between the intermediate connecting rod and the control system being maintained in a fixed guide extending parallel with the direction of the slide.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US384789A 1972-08-04 1973-08-02 Pump power governor Expired - Lifetime US3861832A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7228292A FR2195338A5 (enExample) 1972-08-04 1972-08-04
FR7314433A FR2331253A5 (fr) 1973-04-19 1973-04-19 Dispositif de regulation de la puissance d'entree d'au moins une pompe a cylindree variable

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US3861832A true US3861832A (en) 1975-01-21

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US384789A Expired - Lifetime US3861832A (en) 1972-08-04 1973-08-02 Pump power governor

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US (1) US3861832A (enExample)
JP (1) JPS4985601A (enExample)
DE (1) DE2339598A1 (enExample)
ES (1) ES417600A1 (enExample)
GB (1) GB1437413A (enExample)
IT (1) IT994555B (enExample)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4013380A (en) * 1974-11-18 1977-03-22 Massey-Ferguson Services N.V. Control systems for variable capacity hydraulic machines
US4077744A (en) * 1974-11-18 1978-03-07 Massey-Ferguson Services N.V. Control systems for variable capacity hydraulic machines
US4913180A (en) * 1988-11-03 1990-04-03 Bahm, Inc. Control system and method for chemical injectors
US20230105578A1 (en) * 2021-10-04 2023-04-06 Hamilton Sundstrand Corporation Variable positive displacement pump actuator systems

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932984A (en) * 1956-07-05 1960-04-19 Napier & Son Ltd Torsional vibration dampers
US2971498A (en) * 1956-02-21 1961-02-14 Von Roll Ag Hydraulic control device for a hydrostatic drive
US3163115A (en) * 1960-03-08 1964-12-29 American Brake Shoe Co Horsepower limiting devices
US3554671A (en) * 1967-08-25 1971-01-12 Bellows Valvair Kamper Gmbh Device for adjusting the stroke of a variable displacement pump to maintain the product of pressure and volume per stroke constant
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
US3732036A (en) * 1971-03-24 1973-05-08 Caterpillar Tractor Co Summing valve arrangement
US3758235A (en) * 1971-09-22 1973-09-11 Sperry Rand Corp Power transmission
US3788731A (en) * 1971-07-19 1974-01-29 Canon Kk Two point focus variable magnification lens system

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2971498A (en) * 1956-02-21 1961-02-14 Von Roll Ag Hydraulic control device for a hydrostatic drive
US2932984A (en) * 1956-07-05 1960-04-19 Napier & Son Ltd Torsional vibration dampers
US3163115A (en) * 1960-03-08 1964-12-29 American Brake Shoe Co Horsepower limiting devices
US3554671A (en) * 1967-08-25 1971-01-12 Bellows Valvair Kamper Gmbh Device for adjusting the stroke of a variable displacement pump to maintain the product of pressure and volume per stroke constant
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
US3732036A (en) * 1971-03-24 1973-05-08 Caterpillar Tractor Co Summing valve arrangement
US3788731A (en) * 1971-07-19 1974-01-29 Canon Kk Two point focus variable magnification lens system
US3758235A (en) * 1971-09-22 1973-09-11 Sperry Rand Corp Power transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4013380A (en) * 1974-11-18 1977-03-22 Massey-Ferguson Services N.V. Control systems for variable capacity hydraulic machines
US4077744A (en) * 1974-11-18 1978-03-07 Massey-Ferguson Services N.V. Control systems for variable capacity hydraulic machines
US4913180A (en) * 1988-11-03 1990-04-03 Bahm, Inc. Control system and method for chemical injectors
US20230105578A1 (en) * 2021-10-04 2023-04-06 Hamilton Sundstrand Corporation Variable positive displacement pump actuator systems
US11994117B2 (en) * 2021-10-04 2024-05-28 Hamilton Sundstrand Corporation Variable positive displacement pump actuator systems

Also Published As

Publication number Publication date
ES417600A1 (es) 1976-06-01
DE2339598A1 (de) 1974-02-21
GB1437413A (en) 1976-05-26
JPS4985601A (enExample) 1974-08-16
IT994555B (it) 1975-10-20

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