US3004410A

US3004410A - Adjustable timing device

Info

Publication number: US3004410A
Application number: US647578A
Authority: US
Inventors: Earl R Pierce
Original assignee: Motors Liquidation Co
Current assignee: Motors Liquidation Co
Priority date: 1957-03-21
Filing date: 1957-03-21
Publication date: 1961-10-17
Anticipated expiration: 1978-10-17

Description

2 Sheets-Sheet 1 E. R. PIERCE ADJUSTABLE TIMING DEVICE Oct. 17, 1961 Filed Maron 21, 1957 Oct. 17, 1961 E. R. PIERCE 3,004,410

ADJUSTABLE TIMING DEVICE Filed March 2l, 1957 2 Sheets-Sheet 2 I IH 72a .zLl i H- Y T -A INVENTOR.

- the engine. shaft 4 adjacent its end opposite the camshaft and 1s liaise Ware Filed Mar. 21, 1957, ser. No. 647,578 12 claims. (ci. s4-.25)

This invention relates generally to means for varying the angular relationship between a driving shaft and a driven shaft and, more specifically, to a device for varying the timing of the injection or admission of fuel in an internal combustion engine and for analogous purposes.

Fuel injection type engines, such zas diesel engines, are quite sensitive to the timing of the injection of fuel. Hence, it is desirable lfor most efficient operation of such engines, particularly of engines operating over a wide speed range, to advance and retard the injection timing in accordance with the fuel used and variations in engine speed. Injection timing devices for such engines are well known and generally include a speed sensitive device operable to mechanically or hydraulically shift the timing relationship 'between two shafts. In general, however, the known devices are rather complicated, expensive in construction, lack sensitiveness in operation, and are extremely susceptible to wear and operational failures due to the severe intermittent torque loads imposed thereon duiing each engine operating cycle.

Among the principal objects of the invention are to provide a new and improved device for varying the angular relationship between a driving shaft and a driven shaft; to provide a new and improved device for hydraulically and automatically adjusting the timing of fuel injection apparatus in accordance with engine speed; to provide a timing device with means for automatically and hydraulically altering the time of beginning of fuel injection according to the engine speed requirements and with means for selectively altering the time of beginning of fuel injection according to the type of engine fuel to give improved fuel economy andk engine performance; to providesuch a device which is highly responsive to speed changes and positive in action; to provide a timing device of the type set forth which is relatively simple, rugged and economical in construction and adjustment; and to provide such a device eliminating the necessity of highly precisioned, expensive elements as required in prior timing devices.

The foregoing and other objects, advantages and features of the present invention will be apparent from the following description of a preferred illustrative embodiment of a timing device constructed in accordance with the invention, having reference to the accompanying drawings, in which:

FIGURE l is taken substantially in longitudinal section but with portions thereof in elevation to show the details of construction;

FIGURE 2 Vis a sectional view taken substantially on the line 2 2 of FIGURE l;

FIGURE 3 is a fragmentary sectional view taken substantially on the line 3 3 of FlGURE 2; and

FIGURE 4 is a fragmentary sectional view taken substantially on the line 4-4 of FIGURE l.

Referring more particularly to FIGURE l of the drawings, an engine housing or frame is partially shown at 2 and rotatably mounts a driving shaft 4 and a camshaft 6 in axially aligned and spaced relation. The camshaft is adapted to actuate associated fuel injection mechanism, not shown, to sequentially inject controlled quantities of fuel -into the several combustion chambers of A timing gear 8 is secured to the driving Patent FCS driven by a gear 10. The gear 10 is journaled in the frame 2 and is adapted to be rotatably driven by the engine crankshaft, not shown. An accessory drive shaft 12 is also splined to the gear itl as indicated at i2' and extends longitudinally of the engine to its opposite end.

An adjustable timing device or coupling 2d constructed in accordance with the invention interconnects the adjacent ends of the shaft Vl and camshaft 6. The timing device or coupling Ztl comprises a manually adjustable mechanism indicated at A which provides for adjustment of the angular phase relationship between the injector pump camshaft and the engine crankshaft in accordance 'with the type of fuel being utilized, and a hydraulically actuated mechanism indicated at B which, automatically adjusts the timing phase relationship ber tween the camshaft and the crankshaft in accordance with the speed of the engine. The two adjusting mechanisms A and B are drivingly interconnected by a flexible coupling C which is adapted to accommodate limited axial misalignment and deflection as well as expansion and contraction of the two shafts.

The manually adjustab-le mechanism A includes a male cone member 22 which is drivingly secured to the end of the camshaft 6 by tapered splines as shown at 24. The member Z2 has an external cone surface 2.6 which is adapted lto be frictionally engaged by a mating female cone surface Z8 formed internally of an embracing collet 30. A Spanner nut 34 is threadable on self-locking Acme-type lthreads formed on the collet, as indicated at 32, and is adapted to draw the mating conical surfaces of the member Z2 and the collet into driving frictional engagement.

'For the purpose of tightening and loosening the nut 34 relative to the collet, the collet is provided with a flange 36 having suitable Spanner lugs 38 formed thereon. Thus the nut and collet may be rotatably loosened or tightened relative to each other by the use of suitable Spanner wrenches. Loosening of the nut 34 on the collet permits rotation of the collet relative to the camshaft for adjustment of the timing phase angle therebetween. Ti-ghtening the nut serves to rcs-establish a driving connection between the cone surfaces of the member 22 and the collet 30 in their adjusted position.

A plurality of indexing pins 40 radiate from the male cone member and extend through slots or openings ft2 formed in the collet intermediate its flanged and cone sur-face portions. The slots 42 are elongated circumferentially of the collet and are of an arcuate length limiting the rotation of collet relative to the male member 22 to the range of angular adjustment required by the various fuels for which the engine is intended. A spring biased detent 44 carried 4by the male cone member is adapted to engage a plurality of longitudinally extending grooves 46 formed circumferentially of the cone surface of the collet. The circumferential spacing of the grooves 46 corresponds to the angular timing relationships required 4for different types of fuel. Hence, the detent and the grooves coact to provide both feel and audible reference in effecting the precise angular timing adjustments required for the different fuels.

As indicated above, Vthe exible coupling CV drivingly interconnects the two adjusting mechanisms A and B. This coupling includes a plurality of radially spaced pins 48 which are riveted tothe collet flange 36. These pins extend axially through openings provided therefor in a resilient gasket 50l and sldably project into a plurality of holes 52 formed in a driving spider or disk 54. The pins 48 and their respective holes have normal bearing clearances therebetween which cooperate with the resilient gasket 50 to permit the coupling C toI accommodate limited misalignment between the disk 54- and the collet ange 36. The spider 54 is axially spaced from and drivingly connected to a member 56 forming one end of a cylinder assembly 58 of the mechanism B. This driving connection is provided by a plurality of lugs orprongs 60 which project axially from the end member into a plurality of holes 61. provided therefor in the spider 54.

The cylinder assembly S is mounted for limited rotation with respect to the gear-driven shaft 4 and denes a chamber 58V of stepped diameter adjacent the end of the shaft opposite the timing gear 8. The end member 56 is centrally perforated, as indicated at 62, to embrace the adjacent end of the gear driven shaft 4 and a closure plug 63 is threadably sealed therein. As best seen in FIGURE 4, the shaft 4 is circumferentially relieved at 64 to receive two diamet-rically opposed tangs 65 extending radially inwardly from the end member 56 to limit the rotation permitted between the shaft 4 and the cylinder assembly 58. The tangs 65 also coact with a retaining washer 66 and a nut 67 threaded on the reduced diameter end of the shaft 4 to locate the cylinder assembly 58 axially of the shaft 4.

In addition to the end member 56, the cylinder assembly includes a housing member 68 having an outer cylinnot shown. The passage 76 in turn opens on an annular receiving chamber 77 formed between a connterbore 78 in the engine frame and two axially spaced seal rings 79 carried by the housing hub 64b. The receiving chamber 77 is -in turn connected by suitable passages in the housing hub, as indicated at 8011,17 and c, to a port 3l in the valve body 70C which opens on the valve bore 70d. When the valve member 71 is in its position shown drical portion 63a which is sealed at one end to the outer i periphery of the end member S6 and defines the larger diameter cylindrical surface of the chamber 58. Intermediate its ends, the housing member extends radially inwardly to a hub portion 6311 which is journaled on the shaft l4 by a bearing 69. An inner cylindrical portion 68C extends axially of the hub portion in concentrically spaced relation to the outer housing portion 68a and defines the smaller diameter cylindrical surface of the chamber 58'. The end of the chamber 58 opposite the end member 56 is dened in part by a radially extending web portion 70a of an annular member 70 which is telescopically mounted within and serves as a partition separating the chamber 58 from the annular recess 58" defined between the cylindrical housing portions 68a and 68C. A hub 7Gb of the member 70 embraces the inner cylindrical housing portion 68C and locates the web portion 70a axially with respect to the housing member. A valve body 70C is also formed integrally of the member 70 within the recess 58 and has a radially extending bore 70d therein reciprocably mounting a spool type valve member 71. The valve member 71 is operable in accordance with the speed of the shaft 4 to control the ow of actuating fluid to and from the opposite ends of the chamber '58'.

The several elements of the cylinder assembly 5S are secured together by a plurality of radially spaced, axially extending studs 72a, b and c. Each of these studs are of stepped diameter having a large diameter portion intermediate its ends ywhich serves to locate the end member 56 axially with respect to the member 68. The large diameter portions of these studs also project through and lprovide a dowel-type driving connection with a piston member 74 which -is reciprocably mounted within the chamber 58'. The piston member 74 comprises a radially extending web Which sealingly engages the outer cylin- 4drical housing portion 68a adjacent its outer periphery and an axially extending hub portion, one end of which, as shown, sealingly engages the adjacent inner cylindrical housing portion 68a The piston member 74 is also drivingly connected to the shaft 4 through mating helical splines which `are indicated at 75 and are formed internally of the piston hub and externally of the end of shaft 4. Consequently, axial shifting of the piston relative to the shaft 4 effects a change in the angular phase relationship between the camshaft-driving cylinder assembly 58 and the gear-driven shaft '4.

As indicated above, the axialrshiftngzof the piston 74 Y is controlled by the speed responsive movement of valve member 71 which controls the application and drainage of pressurized lubricating oil to and from the ends of the chamber 58' on opposite sides of the piston. pressurized lubricating oil is supplied to a passagef76 in the engine frame 2 from the engine oil press-ure pump,

The

Vend of the stud 72a within the reces 53".

in FIGURE l and in full lines in FIGURE 2, the reduced diameter central portion of the valve member is operable to connect the pressure inlet port 81 to the end of the chamber 58 to the right of the piston 74 through a second port 82 opening on the bore 70d. In this position, the reduced `diameter. outer portion of the valve member also uncovers a third port 83 opening on the bore '70a'. As Ibest seen in FIGURE 3, the outlet port 83 is connected through passages 84 and 34' in the stud 72a and the valve body 70e, respectively, to the end of the chamber 58' to the left of the piston. Consequentiy, this uncovering of the port 83 permits the oil in the left end of the chamber 58 to drain into the recess 58" from which it drains to the engine sump, not shown. Hence, the pressurized oil delivered to the right end of chamber 58 is operable to maintain or shift the piston into abutment with the end member '56 thereby accomplishing one timing phase relationship between the camshaft driving housing and the gear driven shaft.

In the illustrative embodiment, the annular recess SS is drained to the engine sump through one or more radial ports 86 which are open inwardly on an annular passage 88 formed between a counterbore in the hub portion of member 70 and the housing member 68. The annular passage 8-8 is connected by a plurality of passages 90 in the hub portion of the housing Imember 68 to a second annular passage 92. formed between the bearing 69 and a recess of undercut in the housing hub. The passage 92 is connected through an axially extending passage 94 to the annular space intermediate the end of the housing hub and the bottom of the counterbore 78. rhis space is in turn connected by passage 96 in the engine frame to the interior of the timing gear housing 98 from which the oil is returned to the engine sump.

As best seen in FIGURES 2 and 3, a centrifugal iiyweight No is pivotally mounted on the reduced diameter It will be noted that this centrifugal Weight is of a conguration mating outwardly with the cylindrical inner surface of the housing 68 and inwardly with the `member '70. This weight includes an arm portion 100e which thrustably engages the end of the valve member 71 and an outer weight portion 100i?. A tensive spring 102 extends between theweight portion 1001 and a pin 104 carried by the memlber 70 andy normally biases the weight member and consequently the valve member toward their positions shown in full lines in FIGURE 2 when the engine `is below a certain predetermined speed.

The geometry of the weight with respectto its pivot and the spring 102 is such that as it swings radially outwardly the centrifugal forces acting thereon increase at a greater rate than do the deflection forces acting on the spring. Hence, as the engine reaches or exceeds the above-mentioned predetermined speed, the centrifugal forces acting on the valve member and the centrifugal weight result in the rapid outward movement of the weight member to its position shownin broken lines thus permitting the valve member to move to its position shown in broken lines in FIGURE 2. -In this position the reduced diameter central portion of the valve member 71 interconnects the ports 81 and 83 thereby delivering actuating pressure to the left end of chamber 58 while the reduced diameter lower portion of the valve member connects the port SZ to the annular drain recess 8S. The consequent axial'shifting of the piston member to the right results in the rotation of the camshaft driving cylinder housing to its second of two timing positions relative members.

to the gear driven shaft 4. It will be noted that the liuid pressure delivered to the left end of the chamber "speed also provides a built-in hysteresis effect insuring timing stability in either one of the two timing positions. This is true since the speed of the engine must necessarily Vdrop a certain amount below the aforementioned speed before the spring will return the weight and valve member inwardly to positions wherein the valve member 'again delivers actuating uid to the right end and vents the left end of chamber S' thereby returning the piston to its rst timing position. The more or less hydraulic locking of the piston member 74 in either one of its two adjusted positions as provided by this relatively snap action of the centrifugal valve-controlling mechanism also represents a compromise from the progressive speed timing characteristics which are desirable for such engines. However, inthe prior art devices wherein such progressive timing adjustments are provided, the sudden torque Iloadings imposed on the camshaft by the actuation of the associated fuel injection mechanisms have general- `ly resulted in the destructive impacting of the driving surfaces on the several elements of the drive train.

The slidable and exible connection provided by the coupling C drivingly accommodates limited variations in the axial spacingv and alignment between the manually adjustable mechanism A and the hydraulically operated, speed responsive timing mechanism B and thus isolates axial misalignments and deflections between the two shafts which would otherwise result in distortions and seizures of the two timing mechanisms.

From the foregoing description, it will be apparent that the invention provides a relatively simple, compact and rugged device for adjusting the timing or angular phase relationship between any two driving and driven shaft By way of example, the driven shaft may be an exhaust or intake valve actuating member for an engine. Consequently, various modifications may be made from the illustrative embodiment without departing from the spirit and scope of the invention, as defined in the following claims.

I claim:

l. In a device of the character described, a drive shaft, a shaft adapted to be driven by said drive shaft, and means for drivingly interconnecting said shafts and for adjusting the angular phase relationship therebetween, said means including a housing embracing one of said shafts and mounted for limited rotation with respect thereto, said housing dening a cylinder, a piston reciprocably mounted in said cylinder, said piston being non-rotatably dowelled with respect to said housing and helically splined to said one shaft for limited axial movement and rotation with respect thereto, fluid pressure supply means includng a valve member operable between two positions to alternatively control the admission and discharge of pressurized fluid to and from the opposite ends of said cylinder as separated by said piston, centrifugal means including a weight member pivotally mounted to swing radially outwardly with respect to said housing and adapted to control the operative position of said control valve in accordance with the rotative speed of said one shaft, means biasing said weight member radially inwardly and tending to maintain said valve member -in one of its operative positions, said centrifugal means and said biasing Ameans being cooperatively associated to maintain said valve member in its said one position when the rotative speed of said shafts is below a predetermined speed and to permit said valve member to be rapidly actuated to its second position when the rotative speed of said shafts is above said predetermined speed, and flexible coupling means drivingly connecting said housing to the other of said shafts and accommodating limited variations in the axial spacing and alignment between said housing and said other shaft thereby isolating axial misaligmnents and deflections between said shafts from said housing and piston.

2. In a device of the character described, a drive shaft, a shaft adapted to be rotatably driven by said drive shaft, and means for drivingly interconnecting said shafts and `for automatically adjusting the angular phase relationship therebetween in accordance with the rotative speed of `said shafts, said means including a cylinder drivingly conand from the opposite ends of said cylinder as separated by said piston, and centrifugal means including a weight member pivotally mounted with respect to said cylinder about an axis parallel to said other shaft to swing radially outwardly in accordance-with the rotative speed imparted thereto, said weight member having an operative connection with said control valve and being adapted to control the operative position thereof, and means biasing said weight member and said valve member in opposition to the centrifugal forces acting thereon and tending to maintain said valve member in one of its operative positions, said centrifugal means and said biasing means being cooperatively associated to maintain said valve member in its said one position when the rotative speed of said shafts is below a predetermined speed and to permit said valve member to be rapidly actuated to its second position when the rotative speed of said shafts is above said predetermined speed.y

' drive shaft, means for drivingly interconnecting said shafts including a cylinder embracing one of said shafts and mounted for limited rotation with respect thereto, means drivingly connecting said cylinder to the other of said shafts and manually adjustable to vary the angular phase relationship therebetween, a piston reciprocably mounted within said cylinder in non-rotatable relation thereto, said piston being helically splined to said one shaft for limited axial movement and rotation varying the angular phase relationship of said cylinder and piston with respect to said one shaft, fluid pressure supply means including a valve member centrifugally shiftable between two positions to control the alternative admission and discharge of pressurized fluid to and from the opposite ends of said cylinder Yto Vactuate said piston axially of said cylinder,

a centrifugal weight member pivotally mounted to swing radially outwardly with respect to said housing in accordance with the rotative speed imparted thereto, said weight member being adapted to control the operative position of said control valve, means for biasing said weight member and said valve member radially inwardly in opposition to the centrifugal forces acting thereon and tending to maintain said valve member in one of its operative positions, and said centrifugal Weight member and said biasing means coacting to maintain said valve member in its said one position when the rotative speed of said shafts is below a predetermined speed and to permit said valve member to be centrifugally actuated to its second position when the rotative speed of'said shafts is above said predetermined speed.

4. In a device of the character described including a drive shaft and a shaft adapted to be rotatably driven by said drive shaft, means for drivingly interconnecting said shafts including a cylinder drivingly connected to one of said shafts and embracing the other of said shafts for limited rotation with respect thereto, a piston reciprocably and non-rotatably mounted within said cylinder and helically splined to said other shaft for limited axial movement and rotation varying the angular phase relationship of said' cylinder and piston with respect to said other shaft, fluid pressure supply means including a valve member centrifugally shiftable radially of said cylinder between two positions to control the alternative admission and discharge of pressurized uid to and from the opposite ends of said cylinder to actuate said piston axially of the said cylinder and other shaft, and governor means Yoperable in accordance with the rotative speed of said shafts to control the operative position of said valve member, said governor means including means for biasing and maintaining said valve member radially inwardly in one of its operative positions when the rotative speed of said shafts is below a predetermined speed in opposition to the centrifugal forces acting thereon and permitting said valve member to be centrifugally'actuated and maintained in its second position when the rotative speed of said shafts is above said predetermined speed.

5. A governor mechanism for automatically adjusting the angular phase relationship between two shafts in accordance with the rotative speed of said shafts, said shafts comprising a drive shaft and a shaft adapted to be rotatably driven by and axially spaced from said drive shaft, said mechanism including a cylinder drivingly connected to one of said shafts and rotatably embracing the other of said shafts, a piston reciprocably and non-rotatably mounted within said cylinder and helically splined Vto said other shaft, fluid pressure supply means including a valve member carried by said cylinder and centrifugally shiftable radially thereof between two positions to alternatively control the admission and discharge of pressurized uid to and from the opposite ends of said cylinder to'actuate said piston axially of said cylinder and said other shaft thereby varying the angular phase relationship of said cylinder and piston with respect to `said` other shaft, and speed responsive means operableto maintain said valve memberin 'its inner operative position in opposition to the centrifugal forces acting thereon when the rotative speed of said shafts is below a predetermined speed and said speed responsive'means being operable topermit said valve member to be-centrifugally actuated and maintained in its outer operative position when the rotative speed of said shafts' is above said predetermined speed.

6. A coupling device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and' a shaft adapted to be driven thereby,said coupling device comprising arst phase-adjusting mechanism associated with one of said shafts and including a cylinder rotatably embracing said one shaft, a piston recip- Y rocably and non-rotatably Vmounted withinV said cylint der and helically splined to said one shaft,-fluid pressure supply means including atvalve member carried by said cylinder and shiftable radially thereof between two positions alternatively controlling the admissionk and. discharge of pressurized fluid to and from the opposite ends Vof said cylinder thereby actuating said piston axially of said cylinder and said one shaft to rotate said piston and cylinder relative to said one shaft, speed responsive means operable to maintain said valve member in its inner operative position in opposition to the centrifugal forces acting A thereon when the' rotative speed of said shafts is below a predetermined speed and operable to permit said valve member to be centrifugally actuated to its Vouter position when the rotative speed of said shafts is above said predetermined speed; a, second phase-adjusting mechanism associatedwith the other of said shafts and including an annular flange member carried by said other shaft and havingv an external cone surface thereon, a second annular member having an internal cone surface thereon adapted to drivingly engage the cone surface on said iiange member, means for alternatively tightening and loosening said annular members relative to each other to drivingly engage and disengage said cone surfaces, stop means associated with said annular members for limiting the angular rotation permitted therebetween when said cone surfaces are disengaged, and detent indexing means associated with said annular members for adjusting said annular members intermediate the rotational 'limits permitted by said stop means; and a flexible coupling means for drivingly interconnecting and accommodating limited variations in axial spacing and alignment between said cylinderand said second annular member thereby isolating axial misaligninents and deflections between said shafts from said rst and second phase adjusting mechanisms. Y

7. A device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft Vand a shaft adapted to be driven thereby, said device comprising a `first phase-adjusting mechanism associated with one of said shafts and including a cylinder rotatably embracing said one shaft, means including a piston reciprocably mounted within said cylinder and operable upon reciprocation of said piston to adjust the angular phase relationship between said one shaft and said cylinder, and speed responsive pressure supply means including a Y, Valve member shiftable between two positions alternative- `said other shaft, a` second annular member having a surface thereon adapted to drivingly engage said rst annular member, means for alternatively tightening and loosening said annular members relative to each other to drivingly engage and disengage said annular members, stop means associated with said annular members for limiting the angular rotation permitted therebetween and detent indexingv means associated with said annular members for referencing the angular adjustment of said annular members when said cone surfaces are disengaged; and a flexible coupling means drivingly interconnecting said cylinder and said second annular member and adapted to accommodate and isolate axial misalignments anddeflections between said'shaft from'said first and second phase adjusting mechanisms.V

8. A device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and a shaft adapted to be driven thereby, said device comprising an annular flange member carried by one of said shafts and having an external lcone surface thereon, a second annular member having an internal cone surface thereon adapted to drivingly engage the cone surface on'said flange member, means for alternatively tightening and loosening saidannular members relative to each other to drivingly engage and disengage said cone surfaces, stopV means associated Ywith said annular members for limiting the angular-rotation permitted therebetween when Y said cone surfaces are disengaged, and detent indexing means associated with said annular members for refer- 'encing the adjustment of said annular members intermediate vthe rotational limits4 permitted by said stop means, and a`exible`coupling means drivingly lnterconnecting said second' annular member to the other of sa1d v'shafts andadapted accommodate axial rnisalignments and dellections'between said'shafts-V thereby preventing deec- VG'dSiQfiiQll Of .Said annular members.

9. A device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and a shaft adapted to be driven thereby, said device comprising a first annular member carried by one of said shafts, a second annular member embracing said rst member and having a surface thereon adapted to driving- 4ly engage a mating surface on said first member, means including a third annular member threadable on one of said first and second members to alternatively tighten and loosen said first and second annular members relative to each other to drivingly engage and disengage said surfaces, stop means associated with said annular members for limiting the angular rotation permitted therebetween When said surfaces are disengaged, and detent indexing means associated with said annular members for referencing the adjustment of said annular members intermediate the rotational limits permitted by said stop means; and coupling means drivingly interconnecting said second annular member to the other of said shafts and adapted to accommodate axial misalignments and deflections between said shafts thereby preventing deective distortion of said annular members.

10. A device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and a shaft adapted to be driven thereby, said device comprising a rst phase-adjusting mechanism including a first member drivingly connected to one of said shafts and mounted for limited rotation with respect thereto and means for automatically adjusting the angular phase relationship between said one shaft and said member in accordance with the rotational speed of said shafts, a second phase-adjusting mechanism including a second member drivingly connectable to the other of said shafts and mounted for limited rotation with respect thereto and means for manually establishing the angular phase relationship and driving connection between said other shaft and said second member, and a exible coupling means drivingly interconnecting said first and second members and adapted to accommodate axial misalignments and deflections between said shafts thereby preventing deflective distortion of said first and second phase adjusting mechanisms.

11. A coupling device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and a shaft adapted to be driven thereby, said coupling device including a cylinder rotatably embracing one of said shafts and drivingly connected to the other of said shafts, a piston reciprocably and non-rotatably mounted Within said cylinder and helically splined to said one shaft, fluid pressure supply means including a valve member carried by said cylinder and shiftable radially thereof between two positions alternatively controlling the admission and discharge of pressurized fluid to and from the opposite ends of said cylinder thereby actuating said piston axially of said cylinder and said one shaft to rotate said piston and cylinder and thereby said other shaft relative to said one shaft, and speed responsive means operable to maintain said valve member in its inner phase controlling position in opposition to the centrifugal forces acting thereon when the rotative speed of said shafts is below a predetermined speed and operable to permit said valve member to be centrifugally actuated to its outer phase controlling position when the rotative speed of said shafts is above said predetermined speed.

12. A device for drivingly interconnecting and adjusting the angular phase relationship between a driving shaft and a shaft adapted to be driven thereby, said device including a cylinder rotatably embracing said one shaft, means including a piston reciprocably mounted within said cylinder and operable upon reciprocation of said piston to adjust the angular phase relationship between said one shaft and said cylinder, speed responsive pressure supply means including a valve member shiftable between two positions alternatively controlling the admission and discharge of pressurized uid to and from the opposite ends of said cylinder in accordance with the rotational speed of said shafts thereby actuating said piston axially of said cylinder to adjust the angular phase relationship therebetween, a first annular member carried by said other shaft, a second annular member drivingly connected to said cylinder and drivingly engageable with said first annular member, and means for alternatively tightening and loosening said annular members relative to each other to drivingly engage and disengage said annular members to thereby adjust the angular phase relationship between said housing and said other shaft.

References Cited in the file of this patent UNITED STATES PATENTS 680,170 Oldfield et al. Aug. 6, 1901 1,400,079 Kolling Dec. 13, 1921 1,682,270 Eriksen Aug. 28, 1928 1,942,512 Lee Ian. 9, 1934 2,107,070 Fleury Feb. 1, 1938 2,527,517 Baker et al. Oct. 31, 1950 2,708,354 Brady et al. May 17, 1955 2,899,810 Pierce Aug. 18, 1959