EP0060244B1 - Rotationsempfindlicher druckregler - Google Patents

Rotationsempfindlicher druckregler Download PDF

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Publication number
EP0060244B1
EP0060244B1 EP81901007A EP81901007A EP0060244B1 EP 0060244 B1 EP0060244 B1 EP 0060244B1 EP 81901007 A EP81901007 A EP 81901007A EP 81901007 A EP81901007 A EP 81901007A EP 0060244 B1 EP0060244 B1 EP 0060244B1
Authority
EP
European Patent Office
Prior art keywords
spool valve
engine
outlet
pressure
regulator
Prior art date
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
Application number
EP81901007A
Other languages
English (en)
French (fr)
Other versions
EP0060244A4 (de
EP0060244A1 (de
Inventor
Dennis H. Gibson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Publication of EP0060244A1 publication Critical patent/EP0060244A1/de
Publication of EP0060244A4 publication Critical patent/EP0060244A4/de
Application granted granted Critical
Publication of EP0060244B1 publication Critical patent/EP0060244B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/12—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic
    • F02D1/122—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic control impulse depending only on engine speed
    • F02D1/125—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic control impulse depending only on engine speed using a centrifugal governor

Definitions

  • This invention relates generally to fuel delivery systems for combustion ignition engines and more particularly to a rotation sensitive pressure regulator for limiting exhaust smoke and/or the rise in engine torque.
  • FR-A-2016482 describes a rotation sensitive pressure regulator comprising an inlet (30,31); an outlet (39, 40); a vent conduit (35); valve means having a reciprocable spool valve (5) movable between a first (31­-39), a second (37 blocking 39) and a third (39-35) position; fly weight means (9) for moving the spool valve (5) in a first direction and towards its first position in response to increased rotation of speed of the flyweight means, and means (spring 15) for urging the spool valve in a second direction opposite to the first direction and towards its third position in response to the decreased rotational speed of the flyweight means.
  • Fluid stabilising means (chamber 19) are provided which are responsive to the fluid pressure in the outlet (39, 40) (via elements 42, 101, 91, 24) and which are acting against each movement of the spool valve.
  • US-A-3049867 describes stabilizing spool valve movement by use of fluid pressure in its outlet.
  • a rotation sensitive pressure regulator comprising an inlet and outlet; a vent conduit; valve means having a reciprocable spool valve for modulating fluid pressure in the outlet in response to the position of the spool valve, the reciprocable spool valve being sequentially movable between a first position communicating fluid pressure from the inlet to the outlet, a second position blocking the outlet from the inlet and a third position communicating the outlet with the vent conduit; flyweight means for moving the spool valve in a first direction and towards its first position in response to increased rotational speed of the flyweight means is characterized by means for urging the spool valve in a second direction opposite to the first direction and towards its third position in response to fluid pressure in the outlet and decreased rotational speed of the flyweight means.
  • Reliable and repeatable performance is attained by utilizing a nondeformable actuator member which eliminates the necessity for a diaphragm and an actuating spring.
  • the stability of the regulator is provided through the use of a spring that can adjust the static force on the spool valve.
  • Fig. 1 illustrates a rotation sensitive pressure regulator 7 that is used on a compression ignition engine (not shown).
  • the regulator includes a speed input shaft 8 that is driven by the engine at a speed proportional to the crankshaft speed.
  • the input shaft is mounted for rotation within two duplex bearings 9 that are rigidly mounted in a base 10.
  • the base attaches the regulator 7 to the engine (not shown) and seals the bottom of the regulator 7 from contamination by dirt and oil.
  • the regulator 7 further includes a body or housing 11 which houses the apparatus.
  • the base 10 and the body 11 are sealed by an 0-ring 12.
  • the speed input shaft 8 rotates a fly-weight assembly 13 that includes a disc shaped carrier 14 on which is mounted a plurality of clevices 15. On each clevice is a pin 16 that acts as a pivot for a fly-weight 17. The fly-weights are located between the clevices and pivot about the pins 16. When the shaft 8 rotates, the carrier 14 rotates at the same speed and the fly-weights pivot outwardly away from the axis of rotation due to centrifugal force.
  • Each fly-weight 17 has a toe 18 that engages the outer race or ring of a bearing 20.
  • the inner race of the bearing is rigidly attached to a nondeformable actuator member 19 that is an integral part of valve means 21 for regulating the outlet fluid pressure of the regulator 7. More precisely, the member 19 is a stem located on the lower end of a spool valve 21 a and serves as a rigid coupling directly engaged by both the fly-weight assembly 13 and the spool valve for moving the spool valve in an upward direction in response to rotation of the fly-weight assembly.
  • the bearing 20 permits the fly-weights to rotate relative to the spool valve during operation.
  • the spool valve has upper and lower relieved portions 22, 23, respectively, that form a control land 24.
  • the upper relieved portion 22 communicates with a vent conduit 28 in the body 11 and the lower relieved portion 23 communicates with a supply conduit or inlet 26.
  • the supply conduit is connected to a source of fluid pressure (not shown).
  • the supply conduit 26 is connected to the intake manifold so that the regulator is supplied with pressurized air corresponding to the manifold pressure.
  • the control land 24 covers a controlled air conduit or outlet 29.
  • regulated air at a predetermined pressure is provided through this conduit 29 to a fuel air ratio controller 31 as described below.
  • the spool valve 21 a slides up and down within a bushing 33 that is rigidly mounted within the body 11 of the regulator 7.
  • the conduits 26, 28 and 29 communicate with the spool valve through the bushing.
  • the clearance between the spool valve and the bushing is approximately 3.30 x 10- s m (130 millionths of an inch) so that air may be controlled by this spool valve.
  • the spool valve 21 a and the bushing 33 can be fabricated from either stainless steel or porcelain. Porcelain is preferred if high temperature moisture laden air is to be encountered from the intake manifold.
  • the regulator 7 is provided with means 32 for urging the spool valve 21 a in a downward direction in opposition to the fly-weight assembly 13 in response to fluid pressure in the outlet 29.
  • the urging means includes a cavity or chamber 34 formed around the top of the bushing 33 by a cover 35 and a gasket 36 secured to the regulator housing 11 by a plurality of bolts 37 and which seal the fluid pressure within the regulator.
  • the cavity is connected to the controlled air conduit 29 by a passage 38.
  • the urging means 32 further includes a compression spring 40 and which urges the spool valve 21 a in a downward direction and places a static force on the spool valve that opposes the upward force generated by the rotation of the fly-weights 17.
  • An adjusting screw 39 is threadably received in the cover 35 to adjust the compression of the spring which provides a way to vary the effect of the fly-weights and to move the operating curve of the regulator as described below in connection with Fig. 2.
  • the adjustment screw 39 is properly positioned, the screw is locked in place with a jam nut 42 that engages the adjustment screw 39 and the cover 35.
  • a rubber seal washer 43 is used to prevent the escape of fluid pressure from around the screw.
  • the regulator 7 controls the pressure in the controlled air conduit 29 by moving the control land 24 on the spool valve 21 a with respect to the conduit 29.
  • the position of the control land is controlled by a plurality of forces.
  • the downward force on the spool valve includes a force due to the fluid pressure in the cavity 34 under the cover 35.
  • the pressure in this cavity 34 is equal to the pressure in the controlled air conduit 29 and is communicated to the cavity via the passage 38.
  • the upward force on the spool valve includes the force due to the rotation of the fly-weights 17. This force is equal to a constant K times the square of the speed of the shaft 8 so that the upward force is proportional to the square of the engine speed.
  • the constant K includes the number and mass of the fly-weights, the distance between the center of mass of the fly-weights and the pin 16 and the distance between the toe 18 and the pin 16.
  • the cavity around the fly-weights is vented to the atmosphere so that no fluid pressure acts on the bottom of the spool valve.
  • the pressure in the controlled air conduit 29 is directed to the fuel air ratio controller 31.
  • the controller includes an upper chamber 45 and a lower chamber 46 separated by a diaphragm 47.
  • the diaphragm is spring loaded with a spring 48 that eliminates preloading the diaphragm.
  • the pressure from the regulator 7 is directed into the upper chamber 45 and the lower chamber 46 is constantly at atmospheric pressure.
  • the bottom of the diaphragm 47 is connected to a bolt 49 that engages a fuel rack collar 50 that positions the fuel rack 51.
  • the purpose of the fuel air ratio controller 31 is to resist the movement of the fuel rack 51 during acceleration and to coordinate movement of the fuel rack 51 with the amount of air available in the intake manifold (not shown).
  • the regulator 7 controls the fluid pressure in the controlled air conduit 29 as a function of the rotation of the speed input shaft 8.
  • the speed input shaft is operatively connected to the crankshaft of an engine (not shown) so that the shaft 8 turns at an integral multiple of the speed of the engine.
  • the regulator is connected to a source of fluid pressure such as the intake manifold of a turbocharged engine via the supply conduit 26.
  • the regulator is also vented to the atmosphere through the vent conduit 28.
  • the engine turns the speed input shaft 8 at a multiple of the crankshaft speed. If the input shaft 8 increases in speed, the fly-weights 17 tend to move outward away from the axis of rotation and thus the toes 18 tend to move the spool valve 21 a in an upward direction via the actuator member 19. This upward motion tends to connect the fluid pressure in conduit 26 to the controlled air conduit 29 via the lower relieved portion 23 of the spool valve.
  • the pressure in conduit 29 increases, the pressure in the cavity 34 under the cover 35 increases via passage 38 and tends to force the top of the spool valve in a downward direction against the upward force of the fly-weights.
  • the pressure in conduit 29 is increased until the control land 24 again covers the controlled air conduit 29.
  • a balanced condition results with a predetermined pressure in conduit 29 and with the fly-weight force exactly opposing the spring and output pressure forces.
  • the fly-weights 17 tend to move toward the axis of rotation which causes the spool valve 21 a to move in a downward direction.
  • the elevated pressure in conduit 29 also acts through passage 38 to force the spool valve in a downward direction.
  • the control land 24 vents conduit 29 to the atmosphere via the upper relieved portion 22 of the spool valve and the vent conduit 28. This venting lowers the force on the top of the spool valve and tends to permit the spool valve to move upward.
  • the pressure in conduit 29 is thereby decreased until the control land 24 again covers the controlled air conduit and the opposing forces are balanced.
  • Th regulator 7 through the predetermined pressure in conduit 29 controls the pressure in the upper chamber 45 of the fuel air ratio controller 31.
  • This controller controls the position of the fuel rack 51 which regulates the amount of fuel delivery per pump stroke to the cylinders of the engine (not shown).
  • the bolt 49 permits a larger amount of fuel delivery to the cylinders. The opposite occurs when the pressure in the upper chamber is decreased.
  • the fuel pump (not shown) automatically increases the delivery of fuel to the cylinder.
  • This increase in fuel delivery is a function of the change of efficiency of the fuel pump as the engine speed decreases.
  • the speed input shaft 8 turns at a slower speed. This slower speed decreases the fly-weight force and along with the pressure in the passage 38 causes the spool valve to move downward. This vents a portion of the air pressure in the upper chamber 45 out to the atmosphere through the vent conduit 28.
  • the diaphragm 47 in turn moves the rack 51 to reduce the amount of fuel delivery.
  • Fig. 2 illustrates the performance curves of an engine that utilizes a rotation sensitive pressure regulator 7 according to the present invention.
  • Graph 56 is the curve of torque (brake mean effective pressure in kPa or psi) vs. engine speed (rpm).
  • Graph 57 illustrates the production of smoke vs. engine speed, and
  • graph 58 illustrates the position of the fuel rack with respect to engine speed. In graph 58 zero indicates the center of the travel of the rack and the graph has an abscissa of plus or minus (.254 cm) (0.10 inches) either side of center.
  • Point A indicates the high idle position where at 2200 rpm there is no load on the engine.
  • Point B is the balance point where maximum horsepower is developed at the rated speed of the engine.
  • the effect of the pressure regulator 7 is indicated by the upward sloping linear curve 65.
  • the slope of this curve is fixed by the number, mass, and geometry of the fly-weights and the area of the top of the spool valve 21 a.
  • the position of this curve 65 crosses along the horizontal axis is controlled by the spring 40. That is to say, the spring controls the speed at which Point C occurs which is the point at which the regulated fuel rack curve 65 crosses the fixed rack lug curve. For example, if the compression on the spring is increased, starred curves 56', 57' and 65' are produced.
  • the maximum elevation in torque and the net production of smoke can be controlled by the apparatus described herein.
  • the present invention controls the generation of smoke and limits the rise in engine torque by pulling the fuel rack back when the engine lugs. Stability of the system and reliable performance are obtained by utilizing the spool valve 21 a, the actuator member (19) and the spring 40.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Safety Valves (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (6)

1. Rotationsempfindlicher Druckregler (7) mit einem Einlaß (26), einem Auslaß (29), einer Ablaßleitung (28), Ventilmitteln (21) mit einem hin- und herbewegbaren Kolbenventil (21 a) zur Modulation des Strömungsmitteldrucks im Auslaß (29) infolge der Position des Kolbenventils, wobei das hin- und herbewegbare Kolbenventil (21 a) sequentiell zwischen einer ersten, zweiten und dritten Position bewegbar ist, wobei in der ersten Position Strömungsmitteldruck vom Einlaß (26) zum Auslaß (29) geleitet wird, während in der zweiten Position der Auslaß (29) gegenüber dem Einlaß (26) gesperrt ist, wobei schließlich in der dritten Position der Auslaß (29) mit der Ablaßleitung (28) in Verbindung steht, und schließlich mit Fliehkraftmitteln (13) zur Bewegung des Kolbenventils (21 a) in einer ersten Richtung und zu seiner ersten Position hin infolge einer erhöhten Drehzahl der Fliehkraftmittel (13), gekennzeichnet durch Mittel (32), um das Kolbenventil (21 a) in eine zweite Richtung entgegengesetzt zur ersten Richtung und in seine dritte Position hin zu drükken, und zwar infolge von Strömungsmitteldruck im Auslaß (29) und verminderter Drehzahl der Fliehkraftmittel (13).
2. Rotationsempfindlicher Druckregler (7) nach Anspruch 1, wobei die Drückmittel (32) eine Druckkammer (34) aufweisen, um Strömungsmitteldruck an ein Ende des Kolbenventils (21 a) anzulegen und Durchlaßmittel (38) zur Verbindung von Strömungsmitteldruck vom Auslaß (29) zur Druckkammer (34).
3. Rotationsempfindlicher Druckregler (7) nach Anspruch 2, wobei die Drückmittel (32) ferner eine Druckfeder (40) aufweisen, um das Kolbenventil (21 a) in der zweiten Richtung vorzuspannen, und wobei die an das Kolbenventil (21 a) durch die Fliehkraftmittel (13) angelegte Kraft den kombinierten Kräften von Feder (40) und dem vorbestimmten Druck in der Druckkammer (34) entgegenwirken.
4. Rotationsempfindlicher Druckregler (7) nach Anspruch 3 mit Mitteln (39), um selektiv die Kompression der Feder (40) einzustellen und eine Gleichgewichtsposition des Ventilkolbens (21 a) vorzusehen.
5. Rotationsempfindlicher Druckregler (7) nach Anspruch 1, wobei das Kolbenventil (21 a) einen Steuersteg (24) aufweist zur Modulation des Strömungsmitteldrucks im Auslaß (29) infolge der Position des Kolbenventils (21 a).
6. Rotationsempfindlicher Druckregler (7) nach einem der Ansprüche 1 bis 5, wobei das Kolbenventil (21 a) durch die Fliehkraftanordnung (13) betätigt wird, und zwar über einen nicht deformierbaren Schaft (19) am Kolbenventil (21).
EP81901007A 1980-09-11 1980-09-11 Rotationsempfindlicher druckregler Expired EP0060244B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1980/001168 WO1982001036A1 (en) 1980-09-11 1980-09-11 Rotation sensitive pressure regulator

Publications (3)

Publication Number Publication Date
EP0060244A1 EP0060244A1 (de) 1982-09-22
EP0060244A4 EP0060244A4 (de) 1983-01-14
EP0060244B1 true EP0060244B1 (de) 1985-01-09

Family

ID=22154530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81901007A Expired EP0060244B1 (de) 1980-09-11 1980-09-11 Rotationsempfindlicher druckregler

Country Status (7)

Country Link
EP (1) EP0060244B1 (de)
JP (1) JPH0321731B2 (de)
BE (1) BE889962A (de)
BR (1) BR8009105A (de)
CA (1) CA1153648A (de)
DE (1) DE3069956D1 (de)
WO (1) WO1982001036A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9549928B2 (en) 2011-04-29 2017-01-24 The University Of Toledo Muscarinic agonists as enhancers of cognitive flexibility
US10835532B2 (en) 2008-05-15 2020-11-17 The University Of Toledo Muscarinic agonists as cognitive enhancers

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108266276A (zh) * 2018-02-08 2018-07-10 常州市美特精密电机有限公司 摩托车怠速马达

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1117008A (fr) * 1955-01-04 1956-05-15 Régulateur automatique de vitesse à servo-moteur hydraulique
FR2016482A1 (de) * 1968-08-28 1970-05-08 Bosch

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2566188A (en) * 1944-09-01 1951-08-28 Marquette Metal Products Co Engine regulating system
US2868184A (en) * 1957-04-22 1959-01-13 Curtiss Wright Corp Engine load limiting controls
US3049867A (en) * 1959-09-21 1962-08-21 Woodward Governor Co Governor for turbo-supercharged prime movers
US3077873A (en) * 1961-08-04 1963-02-19 Caterpillar Tractor Co Pressure actuated fuel control for supercharged engines
US3777730A (en) * 1972-03-20 1973-12-11 Caterpillar Tractor Co Fuel limiting device
US3795233A (en) * 1972-05-19 1974-03-05 Caterpillar Tractor Co Fuel-air ratio control for supercharged engines
US4068642A (en) * 1975-11-14 1978-01-17 Caterpillar Tractor Co. Fuel ratio control with manually operated air override
US4136656A (en) * 1977-07-26 1979-01-30 Tsentralny Nauchno-Issledovatelsky Dizelny Institut Load control device for turbo-suspercharged diesel engines
US4149507A (en) * 1977-10-27 1979-04-17 Caterpillar Tractor Co. Fuel-air ratio control with torque-limiting spring for supercharged engines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1117008A (fr) * 1955-01-04 1956-05-15 Régulateur automatique de vitesse à servo-moteur hydraulique
FR2016482A1 (de) * 1968-08-28 1970-05-08 Bosch

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10835532B2 (en) 2008-05-15 2020-11-17 The University Of Toledo Muscarinic agonists as cognitive enhancers
US9549928B2 (en) 2011-04-29 2017-01-24 The University Of Toledo Muscarinic agonists as enhancers of cognitive flexibility

Also Published As

Publication number Publication date
DE3069956D1 (en) 1985-02-21
EP0060244A4 (de) 1983-01-14
JPH0321731B2 (de) 1991-03-25
BR8009105A (pt) 1982-07-13
CA1153648A (en) 1983-09-13
BE889962A (fr) 1981-12-01
WO1982001036A1 (en) 1982-04-01
EP0060244A1 (de) 1982-09-22
JPS57501389A (de) 1982-08-05

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