US2745384A - Centrifugal governor with hydraulic booster - Google Patents

Description

DRAULIC BOOSTER 4 Sheets-Sheet 1 Filed April 23 1951 FIG.6.

INVENTOR.

HERMA ADLER BY I ATTORNEYS y 15, 1956 H. G. ADLER 2,745,384

CENTRIFUGAL GOVERNOR WITH HYDRAULIC BOOSTER Filed April 23, 1951 4 Sheets$heet 2 I II2 I H8 72 9 E ||6 62 f; lo 76 g 1 K 60' Gn 74 I I4 5 8 I 78 IO May 15, 1956 H6. ADLER CENTRIFUGAL GOVERNOR WITH HYDRAULIC BOOSTER Filed April 23 1951 4 Sheets-Sheet 3 n2 J 26 i n4 I 94 I00 I I28 2 $2 I26 H6 .4 IO I h lg 40 INVENTOR. 42 E HERMAN G.ADLER ATTORNEYS May 15, 1956 H. G. ADLER 2,745,384

CENTRIFUGAL GOVERNOR WITH HYDRAULIC BOOSTER Filed April 25, 1951 4 Sheets-Sheet 4 IOO I no H4 94 6:. b 72 LE; I28 I S. L K ||6 l0 40 42 INVENTOR.

DLER

United States Patent CENTRIFUGAL GOVERNOR WITH HYDRAULIC BOOSTER Herman G. Adler, Detroit, Mich, assignor to Novi Ecuipment Company, Novi, Mich, a corporation of Michigan Application April 23, 1951, Serial No. 222,336

10 Claims. (Cl. 121-43) The present invention relates to an engine governor, and more particularly to a governor including centrifugal means responsive to speed of an engine in combination with a hydraulic motor such as a piston and cylinder for effecting control of the engine.

It is an object of the present invention to provide a simplified hydraulic governor in which the centrifugal unit, the actuating motor, and a valve for controlling the actuating motor in accordance with engine speed is compactly arranged in a simple casting so as to occupy a minimum of space and to permit fabrication of the units at a low cost.

It is a further object of the present invention to provide a hydraulic governor characterized by its ability to prevent substantially overshooting of speed under severe operating conditions.

It is a further object of the present invention to provide a novel arrangement of centrifugal governor, hydraulic valve actuated thereby, and hydraulic motor controlled by said valve.

, Other objects and features of the invention will become apparent as the description proceeds, especially when taken in conjunction with the accompanying drawings, wherein:

Figure l is a plan view of a governor assembly constructed in accordance with the present invention.

Figure 2 is a section on the line 2-2, Figure 1.

Figure 3 is a sectional view similar to Figure 2 showing the unit under different operating conditions.

Figure 4 is a view similar to Figure 2 showing the unit under yet another different operating condition.

' Figure 5 is a section on the line 5-5, Figure 2.

Figure 6 is asection on the line 66, Figure l. Figure 7 is a side elevation of the metering sleeve.

Described in general terms, the hydraulic governor comprises a main casting having an enlarged, chamber at one side thereof communicating with a bore which .extends from the chamber through to the opposite side of the casting. The casting is provided with an elongated power cylinder formed integrally therewith, which is closed at the same side of the casting as the chamber. The cylinder is open at the opposite end and is provided with a removable head; The head is apertured to pro vide for passageof a piston rod connected to mechanism for controlling 'the speed of the engine. The casting is provided with a passage connecting the closed end of the cylinder with the chamber and a spring is located between the closed end of the cylinder and the piston constantly biasing the piston toward the open end of the cylinder. A fluid passage is provided in the casting which intersects the bore and extends to the interior of the cylinderbetweenthe head of the cylinder and the piston. A centrifugal unit connected to be driven by the engine is located in the chamber and includes a shiftable part engaging a valve slidably mounted in the bore to control the passage of hydraulic fluid to the cylinder.

Referring now to the drawings, the governor comprises a main; casting 10 provided with an enlarged chamber 12 at one side thereof. As shown in Figure 2,. the cham I 2,745,384 Patented May 15, 1956 her is generally cylindrical at its outer portion and includes a conical inner portion 14. Communicating with the inner end of the conical portion 14 is a bore 16 extend-j ing to the opposite side of the casting 10. Closely adjacent and parallel to the chamber 12 and the bore 16 is a cylinder 18 which is closed at one end by a transverse wall 20 which is part of the casting. The upper end of the cylinder'18 is closed by a removable head 22 having a bore 24 therethrough slidably receiving a piston rod 26 connected at its inner end to a piston 28. Intermediate the transverse wall 20 of the cylinder and the piston 28 is a compression spring 30 constantly urging the piston upwardly, as seen in Figure 1.

Located within the casting 10 is a fluid passage comprising straight sections 32, 34, and 36. The passages 34 and 36 connect at opposite sides of the cylindrical bore 16. Another passage 38 is provided which connects the lower side of the cylinder 18 to the chamber 12.

Located principally within the chamber 12 is a centrifugal device comprising a rotary shaft 40 having a sleeve 42 pressed thereon, the sleeve 42 having a radially outwardly extending flange 44. Rotatably received on the shaft 40 and in abutment with the flange 44 is a ball race 46 herein shown as having a flat radially extending ball engaging surface 48. Rigidly secured to the shaft 40 is a driver 50 carrying a plurality of centrifugal balls 52.' Rotatably and slidably mounted on the shaft 40 is a second ball' race 54 having a conically disposed ball engaging surface 56. It will be apparent that as'the bals move outwardly under the influence of centrifugal force, the upper ball race 54 is moved axially of shaft 40 and upwardly thereon as illustrated in Figure l.

Located within the cylindrical bore 16 of the casting 10 is a metering sleeve 60. The meteringsleeve 60 has a port 62 in one side thereof in communication with the fluid'passage 34. At its opposite side it is provided with a narrow notch or metering slot 64. Located axially beyond the metering sleeve 60 is a second valve sleeve 66 which is spaced from the metering sleeve 60 to provide an annular space therebetween. Preferably, the bore 16 of the casting is cylindrically recessed as indicated at 68 to provide an annular enlarged fluid passage. The metering slot 64 and the annular passage 68 are in communication through the fluid passage 36 to the upper end of the cylinder 18.

Slidahly mounted in the metering sleeve 60 is a spool or shuttle valve70 having an upper land 72, a lower land 74, and an elongated annular groove 76 intermediate said lands. The valve 70 intermediate its ends is provided with a transverse wall 78 having an opening 80 therethrough. Below the transverse wall 78 the valve 70 has one or more outlet ports 82 adapted to communicate with the interior of the chamber 12.

"The upper end of the bore 16 is closed by a removable plate 84 carrying an adjusting screw 86, the lower end of which is provided with a spring seat 88 engaging one end of acompression spring 90. The lower end of the compression spring 90 is seated against the upper surface of the transverse wall 78. Obviously, compression of the spring 90 may be varied by adjustment of the screw 86, and the screw is retained in adjusted position by a lock nut 92. The upper end of the screw and lock nut are covered and concealed'by a removable threaded closure element 94.

Obviously, compression of the spring 90 acts to resist upward movement of the race 54 and accordingly the spring acts as a governor spring to determine the speed at which the governor controls the operation of the engine. The shaft 40'is connected to a rotating part of the engine in the usual manner.

The piston rod 26 at its upper end carries a head to which a rocker arm or lever 102 is pivoted interof the operator.

control-waive of the'enginea mediate the ends thereof linkage is connected such thatupward movement of the link 106, as seen in Figure 2,.res'u lts in opening .movement of the .valve or resultsin an increase in. speed of th e enginep i an abutment' pin 112 which limits movement ofthe rocker lever 102 in one direction as seen in Flgure 3;

. Intermediate-the head I of the piston rod 26 and the a removable head 22 of the cylinder is ashort 'relatively strong. compression type buffer spring 114. This spring is engaged by the head 100 ata'predetermined point, in its downward movement, as seenin- Figure 2,: and operates toprovide stability at or near no load. v

The piston 28 isprovided with an upwardly extending To one free end of the'rocker arm 102 there is rovided a link 104 extends to a food pedal or other instrumentality under the control The otherend of the rocker lever102 is connected by a link '6 to a speed control device on the engine such for example, as ac'arburetorvalve. The

, the engine. At this time the ball race 54' is in its Iower- 1 The removable head 22' is provided with a laterally 7 and upwardlyextending projection 110 recessed to receive pin- 116 received within: a guide recess I18 provided with-:

in'the cylinder. 7 V w 7 V I A bypass passage 120 isprovided which connects the fluid passage 36 with the interior of the chamber 12. The passage 1 20 is'provided with-means for-variably restn'cting flow of fluid through the passage and this means the casting 10 is provided witha boss 122 which has a transverse opening 124 therein,- the outer portion of which is internally threaded. Inwardly of its threaded portion- 'the' opening 124 is reduced in cross-section and intersects the passagef120, Located in the reduced portion of a the opening '124 is a part 126 having a flat, surface 128 providing for a flow of fluid from the upper portion of the passage 1% into. the opening 124 beyond the open end or the ,part 126; The part 126 is provided with an axially extending opening. 130 and a; transverse opening 132 which communicates with the passage 120. Located within the threaded portion OffthE opening 120 is a meteringvalve 134having a'threaded head and provided with a metering point 136 ;which enters intothe axial opening the part, 1 26. Accordingly, adjustment'of the metering valve 134 adjusts the flow of fluid through the passage 120 by restricting the space between the is illustrated in detail in Figure .5. As seen in this figure V i the removal ofload, engine speed increases rapidly-and the balls 52 move outwardly, thus moving'ball race54 upp point 136 and the end opening intopthe part 126'. A" compression spring 138 is interposed between the meter,

ing valve 134 and the part 126, and a closure nut-V140- provided for the opening 120.

' The present device is intended to control the speed of V an'engine in such a way as to prevent excessivespeed's =4 The bypass passage 120 permits adjustment of the operation of the valve and tends to smooth out the action ofthe unit.

Three different operating conditions areillu strated in Figures 2, 3 and 4. In Figure 2 an operating condition,

is illustrated in which the engine is running dead idle. As illustrated in this figure the link 104 is in upper position and the governor is inefiective to control speedof most position and the valve 7'0 is'held in its lowermost position by the governor spring 90. At this time'it be observedthat the upper land 72 of the valve isbelow the bottom of the metering notch 64 and accordingly how of fluid from thereduced portion ofthe valve'76 to the cylinder 18 is'prevented- At the same time, there is a passage for fluid out of the cylinder which includes the passage 36, the interior, of the hollow valve 70,;the port 80 through the transverse wall. of the valve, and the transverse ports 82 in the lower portion ofthe valve thus permitting fluid to flow from the cylinder to the interior V of the chamber 12.

In Figure 3 the parts are illustrated in operativelor speed controllingposition. At this time the foot pedal has been depressed tobring one arm of the rocker lever 102' into abutment with thepin 112. This has the effect of first opening the throttle as a result of corresponding. movementof the link 106. As the engine speed increases the balls52 move outwardly and move the upper-race 54" upwardly,,thus displacing valve 70 upwardly to a position where the'upper land 72 opens a passage through the metering not'ch64 permitting fluid under pressure to flow into the upper end of the cylinder and moving thepiston 28 downwardly. At this time the foot pedal willbe held depressed andthe control action of the governor results in rocking movement of the'1ever-102 about the axis illustratedin Figure 3. In practice, the positionillustrated'in Figure 3 is that'assumed when the engine is 7 about 2800.R. P. M. under full load.' 7

igure 4 there is illustrated acondition which is reached when load is removed from the engine. Due to wardly. At somepredetermin ed speed, as for example 2950 R-. P. M., the-lower edge of the land 72'reaches the upper end of. the metering notch 64; If the governed:

speed of 2 950 P'. M. (forexample) is exceededint- I that upward movement of the valve-70 opens'the annular port definedbetween the adjacent ends of the metering sleeve and the upper sleeve 66. This provides, with a. minimum of upward movement ot. the valve 70,-a very large massive flow ofhydraulic fluid, thepassages and when the throttle is fully opened'iuider no load or under lightloadt .One of the'par'ticiilar uses forywhich the unit was designed is a tank engine characteriied by high power and an.extremely light. fly 'wheel; Accordingly,

under no load the motor tends to accelerate-to dangerous speeds extremely. rapidly.- It is a requirement thatthe governoroperate to" move theacarburetor' throttle from wide opento fully closed in a small fradtionof a second.- I At'the same'time substantial-power is required to effect movementtof the throttle valve or 'carburetor valve which is 'thereas'on 'the hydraulic motor" ini the formof apiston and cylinder device is employed. The desired resultsare accomplished by providing for actuation or the piston 28* inone direction by hydraulic fluid and effeeting move men-tof thepiston'iirthe opposife'direction by thetcomaa through the passage 381to the chamber 12. Moreover,

the ,valveis particularly designed so' that as the upper limit of governed speed isexceeded, a massive snbstan tiallyinstaritaneous flow of-hydrauliefluid 'isri-nt'rbduced into the cylinder, so that thepistori will be-moved' downwardly with. extreme rapidity',-'thus closing: the-,throttl'e 'or pression' spring 30. Theside of the piston engaged by V the compression spring 30 'is subjected to atmosphericports. being. designed so that a substantially unrestricted; flowiof fluid may take place in the-valve through the cylinder. This results in almost instant downward movemerit; of the piston 28 to its lowermost position where it abuts anembossment 142- provid'edat the bottom ofthe.

cylinder 18f The final downward movementof the pis' ten 28 to the positionshown inFigure 4 is o'pposed by the relatively strong compression spring 114.-

' In'order to adjust the governorjto operateat desired. conditions, the firstiadjustment isfmade with'thefoot pedal fully depressed and the engineoperating under'firll loadas illustrated in Figures. At this timescrew" 863's adjusted to giveia desired speedtothe engine as for ex these circumstances the metering-valve 1344s adjustedinwar-diyuntil the engine speed-is equal to 2950 R l.- M1.

T n ng t c ea at d c i mo decrease t eflo or and its metering valve 134 7 operating at; 1

fluid through the bypass passage 120 has the effect of decreasing engine speed.

With the governor adjusted as above described, it will operate at full load at 2800 R. P. M. for example, and will govern the speed up to 2950 R. P. M. under no load conditions. Moreover, due to the design of the governor, and particularly to the arrangement for quick response upon exceeding the predetermined top limit of governed speed, substantial over-shooting is prevented even though the engine has inherently a very rapid acceleration. Moreover, the governor operates smoothly and without substantial surges to control the speed of the engine at intermediate speeds under intermediate loads.

Referring now to Figure 6, means are provided for looking the valve 70 in position during shipment of the governor. This means comprises a threaded opening 150 carrying a locking screw 152, the metering sleeve 60 being provided with an opening for the passage of a pin portion 154 carried by the screw 152. The pin portion 154 engages the valve 70 intermediate its lands 72 and 74 and prevents its separation from the assembly.

The metering sleeve 60 in the particular embodiment illustrated, comprises a cylindrical sleeve having a port 62 for communication with the passage 34. The metering notch 64 is herein shown as of rectangular cross-section and in the particular valve illustrated, has a width of about .026" and a depth of about .1175".

The entire unit is housed within a unitary casting, which forms a housing for the rotary elements, the control valve, and the power cylinder. The power cylinder is located parallel to and at the side of the chamber and communicating bore. The fluid passages are arranged such that they may be drilled in the casting. Thus passage 34 is in alignment with the open end of the bore 16 and is drilled therethrough. Fluid passage 36 is in alignment with the open end of cylinder 18 and is drilled therethrough. Fluid passages 38 and 120 are in alignment with the open end of chamber 12 and are drilled therethrough. Fluid passage 32 and opening 124 are drilled directly from exterior surfaces of the casting. By the defined arrangement, the unit is cheap and easy to make and in completed form represents a most eflicient use of space.

The drawings and the foregoing specification constitute a description of, the improved engine governor in such full, clear, concise and exact terms as to enable any person skilled in the art to practice the invention, the scope of which is indicated by the appended claims.

What I claim as my invention is:

1. Structure of the character described comprising a casting having an enlarged chamber open at one side thereof, a bore extending from said chamber to the other side of said body, a cylinder in said body at the side of said chamber and bore, said cylinder being open at the side of said body opposite said chamber and its opposite end being closed, a removable head for the open end of said cylinder including an abutment thereon, a piston in said cylinder, a piston rod extending from said piston through said head, a lever pivoted to the outer end of said rod and movable into engagement with said abutment, an operator control link connected to said lever, a governing link also connected to said lever for connection with a speed control element, centrifugal governing means in said chamber, a valvein said bore operably'connected to said means, and a fluid passage in said body controlled by said valve for carrying fluid under pressure to said cylinder.

2. Structure as defined in claim 1 in which a passage is provided in said body connecting the closed end of said cylinder to said chamber.

3. Structure as defined in claim 2 comprising a compression spring between the closed end of said cylinder and said piston.

4. Structure as defined in claim 3 comprising a short compression spring operable during only a part of the stroke of said piston to oppose movement of said piston toward the closed end of said cylinder.

5. In a governor of the character described, a casting having a large chamber open at one sidethereof including an inner conical portion; a bore extending from-the inner end of said conical portion and open at the other side of said casting; a power cylinder formed in said casting having a closed end at the said one side thereof and open at the said other side thereof; a first straight fluid passage extending into said casting adjacent a side of said chamber; a second straight fluid passage extending along the side of the conical portion of said chamber, communicating with said first passage, intersecting a side of said bore, and aligned with the open end of said bore; a third straight fluid passage extending into said bore at one end thereof, extending into said power cylinder at the other end thereof and in alignment with the open end of said power cylinder; a fourth straight fluid passage connecting the closed end of said powercylinder to said chamber, and in alignment with the open end of said chamber; and a fifth straight fluid passage connecting said third fluid passage to the interior of said chamber and in alignment with the open end of said casting.

6. In a governor of the character described, means for controlling supply and exhaust of pressure fluid to a fluid motor, comprising a body having a hollow cylindrical part opening at one end into a completely annular enlargement, the end of said part at said enlargement having a surface perpendicular to the axis of said part provided with a relatively narrow notch extending axially of said part from said surface, an inlet passage having an inlet port opening into said part intermediate the ends thereof, a supply passage opening into said enlargement, a valve having spaced annular lands spanning said inlet port and an intermediate reduced portion, the one of said lands adjacent said enlargement having at the end thereof adjacent said reduced portion an end surface perpendicular to the axis of said cylindrical part whereby movement of the said end surface of said one land over said notch provides for a restricted flow past said valve, and movement of the said end surface of said one land past the end surface of said cylindrical part provides for a greatly increased flow past said valve.

7. Structure as defined in claim 6 comprising a passage connecting said supply passage to exhaust, and an adjustable metering valve in said last recited passage to provide for a constant but restricted flow of fluid from said sup ply passage to exhaust when said valve is in position'to connect said inlet and supply passages.

8. In a governor of the character described, a casting having a large chamber open at one side thereof including an inner conical portion; a bore extending from the inner end of said conical portion and open at the other side of said casting; a power cylinder formed in said casting having a closed end at the said one side thereof and open at the said other side thereof; a straight fluid inlet passage extending along the side of said conical portion of said chamber, intersecting a side of said bore, and aligned with the open end of said bore; a straight fluid supply passage connecting said bore and one end of said cylinder and aligned with the open end of said cylinder; a straight drain passage connecting the closed end of said cylinder and said chamber and aligned with the open side of said chamber; and another straight passage connecting said supply passage and said chamber and aligned with the open side of said chamber.

9. A governor comprising a unitary casting having a chamber extending upwardly from its bottom surface, said chamber having a lower cylindrical portion and an upper inwardly tapered conical portion, a bore extending from the upper end of said chamber to the upper surface of said casting, said casting having a vertical power cylinder formed therein parallel to and spaced laterally from said chamber, said cylinder being closed at its bottom and open at its top, a removable top closure for said cylinder, a power piston in said cylinder having'a piston rod extending through said closure, centrifugalvmeans centrifugal means; a removable closure for the upper end of' said bore, resilient means below said'closure and efiective to oppose vertical movement of said valve means in response to increase intspeed of said centrifugal means, atfluid'passage leading from the lower surface of said casting to said valve means" andfrom said valve means to the upper end of said cylinder, a drain passage leading 7,

- from the lower end of said cylinder. to said chamber, and

a bypass passage connecting said chamber to the portion of said first passage intermediate said valve means and said cylinder. 7

,10; Structure of the character described comprising a casting ha'vingan enlarged chamber 'openat one'side thereof, a bore'extending from said chamber to the other V oted to the outer end of said rod, said structure'including a rigidabutment extending beyond said head, said lever 'beingmovable intd'engagement with said abutment by movement of said rod or by rocking movement on said rod, or by a combination of both, an operator control 7 connected to said lever, a governing link also connecfed to saidlever for connection with a speed control element, centrifugal governing means; in said chamber, a valve in said bore ,operably connected'to said means, and a fluid pass-age in said bodycontroll'edby said valve for carrying fluid underpressnre to;said cylinder."

References Cited in the file of this patent UNITED STATES'PATENTS 451,719 Lactation; .May S, 799,236 'Iohnson Y V Sept. 12 1905 1,080,900 Demo Dec. 9, 19 137 1,231,257 Herr' -June 26, 1917 11,947,009 Jimerson,; Feb. 13,, 1934 1,987,505" Edler T 1Jan. 8f, 2,157,472 Bellis, May 9,1939 2,209,418 Overbeke July 30, 1940 2,237,799 Nest 'Apr'. 8,'l9'4-t 2,256,970 Bryant V Sept. 23, 194l 2,292,805 Tippen '..'Aug'.;l1, 1942 2,352,736 Richmond July 4, 1944 2,397,213 Smith M'ar'. 26, 1946 2 ,402,972 Mitchell 'July 2, 1946 2,479,813 Chamberlin Au:g; 23', 1949 2,516,723 Rodeck 7111 125, 1950 2,567,753 Ana-ro- Sept. ,11, 1951 t FOREIGN PATENTS l 7 252,760 7 Germany V Oct. 2 ,1912;-

762,114 France 1934 883,951 France p 1943 S'WitZerland 'D'ec.'1, 1950

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