US3526213A - Hydraulic governor having acceleration sensing means - Google Patents

Hydraulic governor having acceleration sensing means Download PDF

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Publication number
US3526213A
US3526213A US747346A US3526213DA US3526213A US 3526213 A US3526213 A US 3526213A US 747346 A US747346 A US 747346A US 3526213D A US3526213D A US 3526213DA US 3526213 A US3526213 A US 3526213A
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United States
Prior art keywords
pressure
fuel
engine
passage
speed
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Expired - Lifetime
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US747346A
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English (en)
Inventor
Samuel E Arnett
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Bendix Corp
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Bendix Corp
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Publication date
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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D13/00—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/0971—Speed responsive valve control
    • Y10T137/0989—Acceleration responsive valve control

Definitions

  • H6. 1 is a schematic representation of a combustion engine and fuel control embodying the present invention therefor;
  • H6. 2 is a sectional schematic view taken on line 2-2 of F [G 1;
  • FIG. 3 is a sectional schematic view taken on line 3-3 of FIG. 1.
  • numeral 20 designates a conventional combustion engine having a rotatable output shaft 22 the speed of which represents engine revolutions or speed.
  • Engine speed is controlled in accordance with a control lever 24, the position of which is transmitted via linkage mechanism 26 to a fuel meter generally indicated by 28.
  • a rotary input signal, N representative of engine rotational speed is supplied to fuel meter 28 via suitable linkage mechanism generally indicated by 30 and connected to output shaft 22.
  • the fuel meter 28 is connected in flow controlling relationship with a fuel supply conduit 32 which transmits pressurized fuel from an engine driven fuel pump 34 to the engine 20.
  • the inlet of pump 34 is supplied fuel at pressure P from a fuel tank 36.
  • the fuel meter 28 includes a casing 38 having an inlet 40 connected to receive fuel at pump discharge pressure P, from conduit 32 and an outlet 42 connected to discharge metered fuel flow at pressure P to conduit 32.
  • a variable area fuel pressure responsive metering valve 44 slidably carried in a passage 46 connecting inlet and outlet 40 and 42, respectively, is positioned to vary the effective flow area of passage 46 and thus metered fuel flow at pressure P to the engine 20.
  • the valve 44 is positioned by a differential area piston 48 fixedly secured thereto and slidably carried in a chamber 50. The entire area of one side of piston 48 is exposed to chamber 50 at a controlled servo pressure P,..
  • valve 44 is of the well-known integrating type wherein the valve 44 becomes stabilized when a predetermined ratio of fuel pressures P P and P is established corresponding to the ratio of fixed areas against which the pressure P,, P, and P respectively, act.
  • a variation in one or more of the fuel pressures P P and P will upset the predetermined fuel pressure ratio causing the valve 44 to move in one direction or the other depending upon the relative pressure error and continue to move until the predetermined fuel pressure ratio is established.
  • the servo pressure P is derived downstream from a restriction 56 in a passage 58 connecting chamber 50 with passage 46 at fuel pressure l upstream from valve 44.
  • a branch passage 60 connects passage 58 downstream from restriction 56 with the interior of casing 38 at pump inlet pressure P and is provided with a valve orifice 62 at the discharge end thereof.
  • a flapper valve 64 at one end of a lever 66 is adapted to cooperate with orifice 62 to vary the effective flow area thereof and thus the fuel pressure P, intermediate restriction 56 and orifice 62 depending upon the position of lever 66.
  • the lever 66 is pivotally mounted on a fixed support 67 and is loaded by a reference force derived from a compression spring 68 interposed between lever 66 and a spring retainer 70.
  • the spring retainer 70 is positioned by a follower 72 pivotally mounted on a fixed support 74 and bearing against a rotatable cam 76 which, in turn, is carried by a shaft 78 suitably mounted for rotation in casing 38 and actuated by linkage mechanism 26 in response to movement of control lever 24.
  • the reference force derived from spring 68 is opposed by a force generated as a function of engine speed, N, by a bellows 80 which has a fixed end secured to a fixed support 82 by any suitable fastening means providing a fluid seal and an opposite movable end 84 bearing against lever 66.
  • the bellows 80 is aligned with spring 68 and vented interiorly via a passage 86 to a source of controlled fuel pressure P which varies with engine speed as will be described.
  • the bellows 80 is exposed exteriorly to fuel pump inlet pressure P, thereby causing the bellows 80 to expand or contract in response to the fuel pressure differential P, -P generated thereacross.
  • the reference force derived from spring 68 is opposed by a second force generated as a function of the rate of change of engine speed or engine acceleration, N, by a diaphragm 88 pivotally attached to one end of lever 66 via backing plate 89 and pin 90 and exposed on one side to fuel pump inlet pressure P
  • the opposite side of diaphragm 88 is exposed to controlled fuel pressure P ⁇ in a chamber 92 partially defined by a cap member 94 which clamps the radially outermost portion of diaphragm 88 to casing 38 via suitable fastening means such as bolts 96.
  • the casing 38 is provided with a recess 98 and bore 100 adapted to receive a bearing member 102 fixedly secured therein by any suitable means such as a press fit.
  • a rotatable circular table 104 slidably carried by bearing member 102 is provided with a shaft portion 106 which is connected to and driven by linkage mechanism 30 in response to rotary motion of output shaft 22.
  • the table 104 is generally cup-shaped with the base portion thereof bored to provide a diametrically extending cylinder 108 having a fuel inlet port 110 at one end thereof.
  • An annular channel 114 surrounding cylinder 108 Supplies pressurized fuel to inlet port 110 and receives pressurized fuel from passage 46 at pump discharge pressure P via ports 116 and 118 in table 104, an annular recess 120 and passage 122 in bearing member 102 and passage 124 in casing 38.
  • a fixed restriction 126 in passage I24 controls fuel flow therethrough to provide a pressure drop P P,., for control purposes depending upon the effective flow area of inlet port U0.
  • inlet port 110 The downstream side of inlet port 110 is beveled to provide a valve seat 128 against which one end of a centrifugal weight member 130 slidably carried in cylinder 108 is adapted to seat thereby controlling the effective flow area of inlet port 110 from which fuel passes to the interior of casing 38 at pressure P via annulus 132 and a plurality of circumferentially spaced apart passages 134 in the wall of cylinder 108 (see FIG. 2), a passage 136 and an annulus 138 in shaft portion 106, a passage 140 in bearing member 102 and passage 142 in casing 38.
  • a plug 144 suitably recessed to accommodate an O ring seal 146 is fixedly secured in one end of cylinder 108 by any suitable means such as a press fit.
  • a stop 148 integral with plug 144 is adapted to be engaged by weight member 130 to limit the axial travel thereof in response to the fuel pressure P acting against the end of weight member 130.
  • the annular channel 114 communicates with the interior of bellows 80 via a passage 150 in table 104, an annulus 152 in bearing member 102, a passage 154 in casing 38 and passage 86.
  • a double row helically wound tube 156 encircling the wall of cup-shaped table 104 is provided with an open end 158 aligned with the rotational axis of table 104 and supported by an extension 160 of a tubular fitting 162 which, in turn, is axially aligned with table 104 and rotatably carried in a fixed bracket 164 extending from casing 38.
  • the opposite end 165 of tube 156 is secured in an opening 167 in tubularfitting 162 and communicates via passage 166 therein with a passage 168 in bracket 164 which, in turn, communicates through a passage 170 in cap member 94 with chamber 92.
  • a vent passage 172 containing a restriction 174 is provided in bracket 164 to vent passage 168 to the interior of casing 38 at fuel pump inlet pressure P,,.
  • the fuel pressure P transmitted to bellows 80 is generated by the weight member 130 which is urged toward valve seat 128 under the influence of the rotating table 104 to the extent of controlling flow through orifice 110 such that the centrifugal force generated by the rotating weight member 130 as a function of the speed of rotation of table 104 is opposed by an equal and opposite force generated by the fuel pressure P acting against the end area of weight member 130 exposed to annular channel 114.
  • control lever 24 is actuated to request an engine acceleration to a higher engine speed
  • the cam 76 is rotated accordingly causing compression of spring 68 and closing movement of flapper valve 64.
  • the resulting increase in servo pressure P upsets piston 48 and thus metering valve 44 in an opening direction which, in turn, results in an increase in metered fuel flow through outlet 42 and conduit 32 to the engine thereby initiating an increase in speed thereof.
  • the fuel pressure P increases by virtue of the progressive increase in rotational speed of table 104 which tends to urge weight member 130 toward valve seat 128 which, in turn, reduces the effective flow area of orifice 110 causing an increase in pressure P in chamber 114.
  • the pressure P acting against the end of weight member 130 increases as the effective area of orifice 110 decreases with the resulting force progressively balancing the opposing centrifugal force of weight member 130.
  • the bellows 80 being vented interiorly to the pressure P and exteriorly to pressure Pi generates a corresponding force as a result of the P ---P pressure differential acting thereon which force is imposed against lever 66.
  • tube 156 tends to accelerate the fuel in rotating tube 156 which, due to the tendency of the fuel to resist a change in velocity thereof generates a fuel pressure differential Pi P across tube 156 which varies as a function of the rate of change of rotational speed thereof.
  • the fluid pressure Pf is transmitted via passage 168 to chamber 92 which responds to the Pi -P fuel pressure differential thereacross and loads lever 66 in a clockwise direction in opposition to compression spring 68 thereby augmenting the force applied by bellows 80.
  • the lead signal represented by pressure differential P P for any given rate of change of speed of output shaft 22 will depend upon the effective diameter of the coil of tube 156 as well as the diameter and length of tube 156 which may be selected in accordance with the control characteristic desired. Furthermore, the length of tube 156 may be minimized by virtue of gain from pressure to torque through the effective lever arm of lever 66 through which diaphragm 88 acts.
  • the cross sectional area of tube 156 should be made sufficiently large to provide the necessary fuel flow into chamber 92 as the volume thereof increases thereby minimizing any tendency for delay of the generated pressure P due to fuel movement in tube 156.
  • the tube 156 is positioned with its one end 158 located at a lower level than the opposite end 165 thereof to generate sufficient pressure head to ensure that the tube 156 is maintained full of fuel
  • Engine governor means for use with a combustion engine fuel control device having engine fuel control valve means responsive to a force error input signal derived from a reference force and an opposing force generated as a function of engine rotational speed, said governor means comprising:
  • rotatable means operatively connected to the engine for generating said opposing force as a function of engine rotational speed
  • said other end of said fluid filled passage is vented to said source of pressurized fluid via a restricted passage and said fluid pressure responsive means is responsive to the fluid pressure generated between the restricted portion of said passage and said other end of said fluid filled passage in response to the rate of change of rotational speed of said fluid filled passage.
  • Engine governor means as claimed in claim 2 wherein:
  • said fluid pressure responsive means is provided with opposite sides operatively connected to said restricted passage and responsive to a fluid pressure differential generated thereacross as a result of the rate of change of rotational speed of said fluid filled passage.
  • said rotatable means includes a rotatable casing operatively connected to and rotated by said engine;
  • a fluid chamber defined by said casing and provided with an inlet and an outlet;
  • a restricted supply conduit operatively connecting said inlet with a second source of pressurized fluid pressure
  • centrifugal weight means slidably carried in said casing for radial movement relative to the axis of rotation of said casing and adapted to control the effective flow area of said outlet and thus the fluid pressure level in said chamber in accordance with he centrifugal force generated by said centrifugal weight means as a function of the rotational speed of said casing;
  • weight means being stabilized in response to the fluid pressure in said chamber acting thereagainst in opposition to said centrifugal force
  • fluid pressure responsive means operatively connected to said fuel control valve means and said fluid chamber for generating said opposing force as a function of engine rotational speed.
  • said fluid pressure responsive means communicating with said fluid chamber is a bellows member vented interiorly to said fluid chamber and exteriorly to said first named source of pressurized fluid at relatively lower pressure compared to said second source and responsive to the fluid pressure differential therebetween.
  • said rotatable means includes a rotatably mounted support member
  • said means defining a fluid filled passage is a tube secured to said support member and rotatable therewith about a common axis of rotation.
  • Engine governor means as claimed in claim 4 and further including:
  • stop means secured to said casing and adapted to be engaged by said centrifugal weight means to limit the radially inward movement thereof in response to the fluid pressure in said chambers.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US747346A 1968-07-24 1968-07-24 Hydraulic governor having acceleration sensing means Expired - Lifetime US3526213A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US74734668A 1968-07-24 1968-07-24

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US3526213A true US3526213A (en) 1970-09-01

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Application Number Title Priority Date Filing Date
US747346A Expired - Lifetime US3526213A (en) 1968-07-24 1968-07-24 Hydraulic governor having acceleration sensing means

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US (1) US3526213A (enrdf_load_stackoverflow)
FR (1) FR2013587A1 (enrdf_load_stackoverflow)
GB (1) GB1224285A (enrdf_load_stackoverflow)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7731602U1 (de) * 1977-10-13 1978-01-26 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Waelzlager fuer bandtragrollen

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FR2013587A1 (enrdf_load_stackoverflow) 1970-04-03
GB1224285A (en) 1971-03-10

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