US2752145A - Hydraulic governor for fuel injection pump - Google Patents

Description

June 26, 1956 H. o. HILL EI'AL 2,752,145

HYDRAULIC GOVERNOR FOR FUEL INJECTION PUMP Filed ma 10, 1951 4 Sheets-Sheet 1 INVENTOR5 HA'EEY o. HILL ROBERT s. JOHNSON i ffm June 26, 1956 H. O. HILL ETAL HYDRAULIC GOVERNOR FOR FUEL INJECTION PUMP Filed May 10, 195] 4 Sheets-Sheet 2 l7 la ////,'Y 1

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HYDRAULIC GOVERNOR FOR FUEL INJECTION PUMP Filed May 10 1951 4 Sheets-Sheet 3 INVENTORS HA'EEY O. HILL EOBEET 5. JOHN ON BY K ATTORNEY June 26, 1956 H. o. HILL ET AL 2,

HYDRAULIC GOVERNOR FOR FUEL INJECTION PUMP Filed May 10, 195] 4 Sheets-Sheet 4 "IIIIIIII" ,SQ/

INVENTORS HAE'EY O. HILL 1 12015521 S JOHNSON United States Patent 6 HYDRAULIC GOVERNOR FOR FUEL INJECTION PUMP Harry 0. Hill, Lansing, and Robert S. Johnson, Lake Odessa, Mich, assignors to American Bosch Anna Corporation, a corporation of New York Application May 10, 1951, Serial No. 225,532

7 Claims. (Cl. 264-3) This invention relates to new and improved hydraulic governing apparatus for rotating machinery, such as prime movers, and has particular reference to a relatively simple device which is inherently stable and in which the sensitivity of the mechanism may be adjusted.

An object of the invention is to provide a new and improved hydraulic governing apparatus.

Another object is to provide a device of the type set forth which embodies means for automatically controlling an internal combustion engine, or the like, through control of the fuel injection pump.

Another object is to provide a device of the type set forth which embodies new and improved means for providing torque control or lugging power" and declining fuel delivery with increased engine speed in a hydraulic governor apparatus. 7

Another object is to provide a hydraulic governing apparatus which embodies a hydraulic pump.

Another object is to provide a device of the type set forth in which the working pressure is variable and is controlled as a function of speed.

Another object is to provide a device of the type set forth which embodies a centrifugal pressure regulator for controlling the workin pressure thereof.

Another object is to provide a new and improved hydraulic governor apparatus which embodies centrifugal means for controlling the servo mechanism for actuating the control means.

Another object is to provide new and improved means for stabilizing a hydraulic governor apparatus.

Another object is to provide a hydraulic governor having centrifugal speed sensing mechanism.

Another object is to provide a hydraulic governor in which a speed droop is inherent in its operation and in which the amount of droop may be adjusted.

Another object is to provide an apparatus of the type set forth which is of relatively simple construction and which provides good regulation over a fairly wide speed range and which may embody an automatic torque control and which may provide an index to be used for automatic timing advance mechanism.

Other objects and advantages of the invention will be apparent from the following description taken in connection with the accompanying drawings. It will be understood that changes may be made in the details of construction and arrangement of parts without departing from the scope of the invention as set forth in the accompanying claims as the preferred form of the invention has been given by way of illustration only.

Referring to the drawings:

Fig. 1 is a side view of a hydraulic governor embodying the invention;

Fig. 2 is a sectional view of the apparatus shown in Fig. l;

Fig. 3 is a sectional view taken on line 33 of Fig. 2, looking in the direction of the arrows;

Fig. 4 is a sectional view taken on line 44 of Fig. 2, looking in the direction of the arrows;

Fig. 5 is a sectional view taken on line 5-5 of Fig. 2, looking in the direction of the arrows;

Fig. 6 is a sectional view taken on line 66 of Fig. 3, looking in the direction of the arrows;

Fig. 7 is a sectional view taken on line 7-7 of Fig. 2, looking in the direction of the arrows; and

Fi 8 is a fragmentary sectional View, on an enlarged scale, taken on line 8-8 of Fig. 2, looking in the direction of the arrows.

Referring more particularly to the drawings, wherein similar reference characters designate corresponding parts throughout, the device shown embodying the invention comprises a housing or casing 11 having the bearing 12 in which is journalled the end 13 of the drive shaft or cam shaft of the fuel injection pump (not shown).

Also extending into housing 11 is theend of the fuel pump control rack or rod 14 which has an extension 15 connected to power piston 16 which is arranged to move the rack or rod 14 toward increasing fuel by hydraulic pressure and to move it into the direction of decreasing fuel by action of spring 17.

Piston 15 is mounted for movement in cylinder 18.

Extension 15 has a reduced portion 19 mounted in an opening in piston member 16 and at the free end of'said reduced portion 19 is spring seat 20 and spring 21 is provided between seat 28 and piston 16.

This reduced portion 19 and spring 21 are actuated by means of lever 22 on shaft 23 and which is adapted to be rotated by means of handle 24. This is for the purpose of returning the control rod to no fuel position regardless of the position of power piston 16. This arrangement is provided for shutting off the engine.

Cam shaft 13 has gear 25 splined on hub 26 carried by shaft 13 and this gear forms one member of a gear pump. The other gear 27 of said gear pump is keyed to shaft 28 and centrifugal pressure regulator 29 is also keyed to said shaft 28.

Shaft 28 is journalled in bearing 36 in the main housing and shaft 28 is provided with a central opening or bore 31.

The output of the gear pump is directed through passage 32 to annular groove 33 around shaft 28 and then through a multiplicity of ports 34 to bore 31 from which it passes through a pair of ports 35 back to the reservoir when centrifugally actuated pistons 36 and 36a are moved sufficiently to uncover ports 35.

The pressure in bore 31 urging piston 36a to uncover ports 35 acts against the force of spring 37 and centrifugal action of the pistons 36 and 36a to thereby regulate the fluid pressure within bore 31 which is therefore regulated or controlled as a function of the speed of rotation of shaft 28.

It will be noted that piston 36a is of larger diameter than piston 36 and because of this difference in diameter any increase in pressure moves the valve so as to open port 35 and provide an escape for the excess fluid, thereby regulating the pressure of fluid in chamber 31 which is, therefore, regulated or controlled as a function of the speed of rotation of shaft 28, as stated above.

Fluid from bore 31 then passes through duct 38 to ducts 39 and 40. Duct 39 communicates through port 41 to annulus 42 around valve 43 and valve 43 has land 44 cooperating a number of ports 45 which control the flow of fluid to and from power piston bore 18 through duct 46.

Piston 43 is provided with a central bore 47 and a pair of radial ports 48 through which fluid returning from bore 18 through duct 46 and ports 45 can be returned to the reservoir.

The position of valve 43 is controlled by the centrifugal action of balls 49 which rotate between cup 50 and plate 51 and which is resisted by the action of spring 52.

These balls 49 are driven by extensions of shaft 28, as will be seen in 'Fig. 8. The extensions of shaft "28 are provided for driving the balls upon rotation of the shaft and to allow them freemovement ina radial direction.

The end of spring 52 is held in a cup retainer 53 which isfulcrumed on lever .54andat-its opposite end carries seat '55 for power piston spring 17. The position of lever 54 is controlled by means of control fork 56 on control shaft 57 which is controlled by lever 58.

The force of power spring 17 is transmitted through lever 54 to regulating spring 59 which is carried in slot 60 in 'plate 61 and keeper 62 is slidably mounted on plate .61 and arranged to vary the effective length of spring 59-and is adapted to be locked inadjusted position by screw 63.

Fork 56 has the limits of its motion controlled or restricted by screws 64 and 65 of which screw 64 controls the idle speed adjustment and screw 65 controls the maximum speed adjustment.

Plate 61 has its end 61a secured to the adjacent wall of the housing.

The position at which lever or fork 56 engages lever 54 is below the center line of spring cup 53 thus as piston 16 is moved toward increased fuel, increasing the load on spring 17, spring and the upper end of lever 54 are deflected to the left which results in a decrease in the load on spring 52 and moves cup 53 to the left and reduces the load on spring 52 which will cause the valve land 44 to cover ports 45 at a slightly lower speed than would otherwise be required. Conversely as power piston 16 moves in a direction toward decreased fuel the load on spring 17 is decreased causing spring 59 and upper end of lever 54 to deflect to the right and then cup 53 moves to the right and that increases the load on spring 52 and causes the governor to run at a slightly higher speed when land 44 covers ports 45 (equilibrium position).

By varying the position of keeper 62 the stiffness of spring 59 can be changed causing a greater or lesser deflection of spring 59 and the upper end of lever 54.

Thus it will be seen that the speed difference between equilibrium-positions of valve 43 can be varied by changing the position of keeper 62. V i

This ability to change the speed differential by means of a simple adjustment provides a construction having a fuel quantity sensing mechanism that tends to provide stability of operation.

This arrangement provides a construction which is inherently stable and provides a means for adjusting the sensitivity of the mechanism.

Because of spring 59 a speed droop is inherent inthe operation'of this governor. The amount of speed droop can be changed by changing the effective length and therefore the stiffness of spring 59 by means of slidable keeper 62 as described.

As power piston 16 moves to increase fuel it will strike maximum fuel adjusting screw 66 which is mounted in lever'67. Lever 67 is arranged to engage thrust bearing 68 opposite to spring 52 and lower end of lever 67 is provided with pin 69 having a ball shaped end 70 adapted to engage a torque control piston if desired or a fixed stop in the governor housing. As piston 16 moves maximum fuel adjusting screw'66 and lever 67 to the left, lever 67 engages thrust bearing'68 and moves control valve 43 to the left and causes land 44 to close ports 45 and prevent further delivery of'fluid through duct 46 to'bore 18.

If a torque control arrangement isdesired'a piston 71 is provided in cylinder 72 and said piston is adapted to be moved downward by pressure of fluid from duct 4% and moves against the force of spring 73. V

This piston 71 is provided with a cam surface 74 which may be contoured to desired shape and ballend 7610f pin 69 which projects through a hole in the wall of cylinder 72 is adapted toengage said cam surface. As piston 16 engages screw 66 and moves the'upper end of lever 67 to the left lever .67 pivots abouta point near the centerof 4 valve 43 until ball engages cam surface 74. Further motion of piston 16 will cause lever 67 to engage thrust bearing 68 and stop the delivery of fluid to piston 16 as previously described.

It will be seen that as piston 71 moves in accordance with the pressure existing in duct 46 that the amount of pivoting motion of lever 67 will change accordingly and thereforethelever 67 will engage thrustbearing 68 at a diflerent point in the motion of piston 16 thus providing a variable maximum fuel position with respect to speed and therefore providing the torque control feature-regardless of maximum speed setting.

Pin and spring 76 are provided to position lever 67 away from thrust bearing '68 and plateSl. during normal operation of thegovernor so it will not impose a friction load on the valve action by touching the valve.

Hub 26 is provided with a number of ports 26a through which fluid can pass from chamber A through chamberB to chamber C. As shaft 13 revolves ports 26a tend to act as a centrifugal pump and tend to raise the level of fluid in chamber C above the level existing in chambers A and B. This tends to provide the gear pump with an ample supply of fluid even though the fluid may be at a low level.

In operation, the pump camshaft 1?: drives the gear pump which pumps fuel under pressure, which pressure corresponds to pump speed, into bore 31 and any excess pressure passes piston 36a to outlet 35 and, therefore, the pressure of fluid within bore 31 is controlled.

The rotation of member 28 effects movement of centrifugal ball members 49 which move outwardly and actuate spring 52, the tension on which is controlled by lever 57. As the ball weights 49 go out, they move valve 43 to a position which allows fluid to go through duct 46 into chamber 18 which moves the fuel pump control 14 to the position of more fuel against the force of spring As member 16 hits adjustable stop 66 which controls the maximum fuel quantity, valve 43 is moved to a position calling for less fuel and then overcomes the action of the centrifugal ball members. i

In this manner, the position of the fuel pump control rack is controlled.

Torque control piston 71 is adapted to be actuated and cam surface 74 on piston 71 engages ball end 70 of pin 69 and moves maximum fuel stop 66 to a position of larger fuel quantity. Piston 71 is only actuated when the fluid pressure is suflicient to overcome the force of spring 73.

As previously pointed out, as the piston 71 is moved in accordance with the pressure in duct 40, the amount of pivoting motion of lever 67 will change accordingly and, therefore, lever 67 will engage thrust bearing 68 at adifferent point in the motion of piston 16, thus providing a variable maximum fuel position with respect to speed and providing the torque control feature regardless of maximum speed setting of stop 66.

It is believed that the operation of the device will be clearly understood from the foregoing from which it will be seen that relatively simple, efficient and economical means have been provided forobtaining all of the objects and advantages of the invention.

We claim:

1. In a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being longitudinally adjustable to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuelinjection pump, said piston being actuated by fluid controlled by said control valve member, a second cylinder and a' piston member in said second cylinder and adapted to be actuated by fluid pressure, said second piston member having a contoured surface, and a lever operatively connected to said valve member and having portions adapted to engage said piston and said contoured surface on said second piston.

2. In a device of the ck tracter described, a shaft adapted to be rotated, a valve member operatively associated with said shaft, said valve member being longitudinally adjustable to control the supply of fluid, and piston adapted to be connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member, a spring opposing the action of said piston and an adjustable leaf spring for varying the spring forces on said piston.

3. In a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being longitudinally adjustable in said bore to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member, a second cylinder and a piston member in said second cylinder and adapted to be actuated by fluid pressure, said second piston member having a contoured surface, and a lever operatively connected to said valve member and having portions adapted to engage said piston and said contoured surface on said second piston, a spring opposing the action of said piston and resilient means for varying the spring forces on said piston.

4. In a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being longitudinally adjustable in said bore to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member and a lever operatively connected to said valve member and having a portion adapted to engage said piston and be actuated thereby for actuating said valve member, a spring opposing the action of said piston and resilient means for varying the spring forces on said piston.

5. In a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being longitudinally adjustable to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member and centrifugal means operatively connected to said shaft for operating said valve member, a second cylinder and a piston mernber in said second cylinder and actuated by fluid pressure, said second piston member having a contoured surface,

and a lever operatively connected to said valve member and having portions adapted to engage said piston and said contoured surface on said second piston.

6. In a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being longitudinally adjustable to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member and centrifugal means operatively connected to said shaft for operating said valve member, a spring opposing the action of said piston and resilient means for varying the spring forces on said piston.

7. in a device of the character described, a shaft adapted to be rotated and having a bore, a valve member in said bore and operatively associated with said shaft, said valve member being adjustable to control the supply of fluid, a cylinder, and a piston in said cylinder and connected to the control rack of a fuel injection pump, said piston being actuated by fluid controlled by said control valve member, centrifugal means operatively connected to said shaft for effecting movement of said valve member in one direction, spring means opposing said movement and spring means opposing the movement of said piston and adjustable means cooperating with said spring opposing the movement of said piston for changing the speed diflerential between equilibrium positions of said valve member, and a lever operatively connected to said valve member and having a portion adapted to engage said piston and be actuated thereby for actuating said valve member.

References Cited in the file of this patent UNITED STATES PATENTS 1,189,697 Kasley et al. July 4, 1916 1,372,502 Grun Mar. 22, 1921 2,020,847 Mitereff Nov. 12, 1935 2,233,319 Lozivit et al. Feb, 25, 1941 2,252,838 Drake et al Aug. 19, 1941 2,324,514 Kalin July 20, 1943 2,341,384 Kalin Feb. 8, 1944 2,364,116 Whitehead Dec. 5, 1944 2,371,157 Drake Mar. 13, 1945 2,373,684 Holloway Apr. 17, 1945 2,452,088 Whitehead Oct. 26, 1948 2,478,752 Drake Aug. 9, 1949 2,494,630 Richmond Jan. 17, 1950 2,524,630 MacNeil et al. Oct. 3, 1950 2,533,231 Drake et al. Dec. 12, 1950 2,565,041 Parker Aug. 21, 1951 2,623,504 Rodeck et al. Dec. 30, 1952

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