US3356099A

US3356099A - Cam controlled regulating device for an injection system operating on the distributor principle

Info

Publication number: US3356099A
Application number: US486743A
Authority: US
Inventors: Schmidt Friedrich Anton Franz
Original assignee: Individual
Current assignee: Individual
Priority date: 1965-09-13
Filing date: 1965-09-13
Publication date: 1967-12-05
Anticipated expiration: 1984-12-05

Description

Dec. 5, 1967 F A. F. SCHMIDT 3,356,099

CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE Filed Sept. 13, 1965 4 Sheets-Sheet l 22 I313 m 5 [4- gaf iifis nvpur FROM 40 F/GZ f9a I4 ,3

r i I8 l7 /6 Inventor.

Dec. 5, 1967 A. F. SCHMIDT 3,356,099

F. CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE Filed Sept. 15, 1965 4 Sheets-Sheet 2 10,40 l/VPl/T 50b fl /PaMACC645P4raP/ F04Z) In vemor:

Fn'edr/rh Amon Franz Sch/MHZ y ATT y j Dec. 5,' 1967 Filed Sept. 13, 1965 F. A. F. SCHMIDT CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE 4 Sheets-Sheet 5 w \\Y\ 20 W In renfor:

Dec. 5, 1967 F. A. F. SCHMIDT 3,356,099 CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE Filed Sept. 13, 1965 4 Sheets-Sheet 4 /7 22 /8 If F/555 H 54 6/ 7 /y 38 571 5 ,0 5 y l f I I 2 550 m/ ur J r ra/-z/4 (yam/ifs I I J 55 53 2 4 I 5 $6 6 2/ ,5 do )9 39 raw/v4 2/24 SUP/ L y In wen for:

ATTY- I 3,355fi99 Patented Dec. 5, 1967 ice 3,356,099 CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM @PERATING ON THE DISTRIBUTOR PRINCIPLE Friedrich Anton Franz Schmidt, Dr.-Seitz-Strasse, Murnau, Germany Filed Sept. 13, 1965, Ser. No. 486,743 18 Claims. (Cl. 137-26) ABSTRACT OF THE DISCLOSURE This invention relates to a regulating device for internal combustion engines and gas turbines, which includes a distributor injection means for feeding the fuel, by means of which an accurate dispensing of the amount of fuel is effected for each operational state according to the respective requirements of the engine. This is achieved in such a manner that the influence of speed and load take effect in the regulating system independently of one another through a cam in the regulating system, the cam controlling the rotation of an intermediate shaft for a disk mounted thereon, relative to the rotation of the drive shaft with a disk thereon. The relative movement of the disks creates a predetermined misalignment of disk passageways, thereby controlling fuel flow.

This invention relates to a regulating device for an injection system operating on the distributor principle and intended for internal combustion engines, gas turbines and jet engines, which includes two rotatable distributor disks provided with slots and/ or bores for feeding fuel, a centrifugal governor for adapting the time cross section of the openings in the distributor disks to the speed, the disks being arranged on one of two, or between two, distributor shafts and with the two rotatable distributor disks being turnable relative to one another by means of a cam member so that the quantity to be injected is fed in regulated manner in dependence both on speed and on a second, speed independent factor, e.g. the position of load or the position of the throttle valve in piston engines.

In the present invention the regulation in dependence on the position of load or the position of the throttle valve may be effected both exclusively or only partly with the aid of a cam member or may also serve only to correct the regulation by load in connection with a known base load regulating device. This base load regulating device may be either a nonrotatable distributor disk relatively turnable in dependence on load, in combination with ad ditional openings in a speed dependent relatively turnable rotating disk, or a device for regulating the fuel pressure on the upstream side of the disks.

The regulation of the quantity to be injected takes place in dependence on speed and load independently of one another through the intermediary of the cam member. Regulation of the fuel pressure permits either only additional influences such as e.g. the pressure and the temperature of ambient air and the temperature of the cooling water (cold start) to be taken into account for the quantity of fuel to be injected, independently of the regulation by speed and load, or also the influence of load and the stated additional influences to be taken into account.

The above-described co-operation between a centrifugal governor of the above-defined construction and a cam member for the application of a further speed independent control quantity is known in principle. This principle of regulation is used in a form of construction in which for the purpose of turning two rotatable distributor disks relative to one another, centrifugal weights are arranged to turn a distributor shaft with a relatively turnable distributor disk through the intermediary of a sleeve, an axially shiftable bushing mounted therein and finally through a high-pitch thread. In this known construction a cam member is arranged on an end face of the said bushing and the influence of load is taken into account on the cam member in axial direction.

In the known constructions of injection systems the given spring characteristic of the centrifugal governor for the entire range of regulation is not so designed that the differences of height of the cam member can be made sutliciently favorable for prescribed requirements as to regulation. In general, in a number of methods, difficulties with respect to accuracy of regulation result from the fact that owing to the steep regions of the cam member necessary in view of the requirements as to regulation made on the machines coming into question, great operating and frictional forces become necessary which result in inaccuracies of regulation.

The present invention proposes a regulating system which involves considerable improvements in the mode of operation and reliability over known regulating systems of similar type. Contrary to conventional constructions with one or more springs, a decisive improvement is achieved by the fact that a division of the required regulating movements is carried out in such a manner that part of the speed dependent regulating operations is taken into account by the spring movement by corresponding modulation of the spring characteristic. Thereby the remaining regulating movements to be actuated by the cam member become 50 small that excessive inclinations which are disadvantageous for accuracy will be unnecessary. With the described regulation a specific variation of the regulating characteristic, which is adapted to the special requirements as to regulation, is carried out in dependence on speed, that is to say that not, as usual, a speed dependent progressive characteristic given by the normal spring characteristic is produced but the regulating characteristic such as spring deflection is specially adapted to the re quirements prescribed by the shape of the cam member. As means to achieve this, combinations known per se of several springs are proposed, however, provision is preferably made of individual springs the characteristic of which is realized in the specially required manner by a variation of the thickness and the cross section as well as of the diameter of the windings. Thus, the shape of the cam member and the spring characteristic are systematically balanced for the individual speed ranges. That is to say, the cam member is not adapted to the action of a projected spring or group of springs, but a mutual adaptation is effected for the purpose of obtaining an accurate adjustment of the characteristic curves and avoiding inaccuracies due to increased frictional forces.

In particular, with this combined regulating system, in the range of low numbers of revolution and in idle motion the spring characteristic can be so designed by appropriately shaping the spring and the cam member that smooth idling and uniform transitions to small positions of load are ensured.

In order to obtain the required special regulator characteristic, use may be made of individual springs as well as of spring assemblies. The individual springs may be made by various manufacturing processes which are concerned with conventional methods for the manufacture in one piece, e.g., preliminary forging in different thicknesses, mechanical working, cutting working, stepwise drawing etc. In the case of individual springs, also a rigid or non-positive assemblage of component parts may be taken into consideration.

It is the object or" the present invention to make the known regulating device of simpler construction and fur- .3 ther to considerably increase the accuracy of regulation by the omission of transmission elements, particularly of the high-pitch thread. This object is achieved by moving the cam member on a centrifugal weight in radial direction along a tracer which is arranged on an intermediate shaft, is in turn movable axially along the cam member by load rods and capable of converting the differences of height of the cam member into turning movement of the rotatable distributor disks relative to one another.

For improving the accuracy of regulation, the stream of fuel is conducted in the same direction by incorporating a fuel feed pump of swash plate type construction in a casing of the regulator, whereby the fuel feed is more favorable than in the previous arrangements in which the fuel feed pump is located outside the regulator casing, because no fuel columns tending to vibrations in the pressure pipes from the fuel feed pump to the regulator are present in this case and, when incorporating the fuel feed pump in the regulator casing, the fuel can flow through the regular in one direction only and need not be reversed once or several times, as was hitherto usual. Due to this construction disturbance to a satisfactory flow of fuel in the pressure pipes to the injection nozzles is largely re duced, with the result that the high precision of the regulating device can really be fully utilized for the internal combustion engine.

An important advantage consists in the arrangement of the rotatable relatively turnable distributor disks relative to one another. Contrary to the hitherto known arrangements in which the two rotatable relatively turnable disks are arranged directly side by side, these disks are separated from one another by a fixed disk. This has the advantage that on both sides of the two rotatable disks only relatively small frictional forces of the fluid are still prevailing which in the event of a regulating turning movement can be overcome more easily by the regulating forces of the regulator than the relatively great static friction as occurs between the two rotatable relatively turnable disks in hitherto known arrangements. The elimination of the static friction means a greater utilization of even smaller regulating forces for the relative turning movement of the disks and thus increased accuracy of the regulator. Furthermore, this also substantially improves the reproducibility of the dosed quantities of fuel since the hysteresis of the regulator is decreased.

Four embodiments of the invention will now be described by way of example and with reference to the accompanying drawings, in which:

FIG. 1 is a longitudinal section through a regulating device according to the invention;

FIG. 2 is a section taken on the line IIII of FIG. 1;

FIG. 3 is a longitudinal section through a second embodiment of the invention;

FIG. 4 is a diagrammatic sketch illustrating the principle of cooperation of the regulating elements;

FIG. 5 is a longitudinal section through a third embodiment of the invention, and

FIG. 6 is a similar view of a fourth embodiment of the invention.

FIG. 1 shows an embodiment in which a distributor driving shaft 1 constructed as a hollow shaft has a distributor disk 2 arranged thereon. The rotatable distributor disk 2 and a further rotatable distributor disk 4 arranged on a regulating shaft 3 are provided with

passage openings

6 and 7, respectively, for the purpose of feeding fuel in a quantitatively regulated manner. Located between the two shafts 1 and 3 is a centrifugal governor 5 for turning in dependence on speed the distributor disk 4 relative to the fuel passage openings 6 in the distributor disk 2. Fuel under pressure can pass through a bore 8 into an inner space 9 of the distributor and thence through a bore 10 in a fixed disk 11 and the

passage openings

7 and 6 in the

rotatable distributor disks

4 and 2, respectively, into outlet passages 12 and further through injection pipes not shown into the respective injection nozzles.

The centrifugal governor 5 contained in the embodiment of FIG. 1 includes two

centrifugal weights

14 and 15 which are guided in radial direction by rods 19. The centrifugal force is compensated by springs 20 which have a speed dependent elasticity constant for the purpose of realizing the speed characteristic of the internal combustion engine. The centrifugal weight 14 has a cam member 13 fixed thereon and the centrifugal weight 15 carries a counterweight 21. A curved boundary surface 40 (FIG. 2) of the cam member 13 can be traced by a feeler roller 18 provided wit-h a restoring spring, not shown, of a tracer 17 which is mounted on an intermediate shaft 16, and this tracing movement will be converted into turning movement of the intermediate shaft 16 relative to the driving shaft 1. As the tracer 17 is guided in a longitudinal slot 22 in the regulating shaft 3, turning of the intermediate shaft 16 relative to the driving shaft 1 is at the same time transmitted to the regulating shaft 3. The intermediate shaft 16 is mounted within the regulating shaft 3 so as to be axially shiftable in dependence on load. The feeler roller 18 can trace the cam member 13 in radial direction in dependence on speed and in axial direction in dependence on load. The centrifugal weights are guided symmetrically to the regulating shaft 3 by cranks 38 through the intermediary of a coupling member 39.

The rods 19 are intended to guide the movement of the centrifugal weights in parallel. The cranks 38 together with the disks 39 are intended to ensure an identical deflection by coupling the two centrifugal weights. The mode of operation is easily understood when FIGS. 1 and 2 are compared taking into consideration the following explanation. Each of the

centrifugal weights

14 and 15 is provided with two bores, the centrifugal weight 14 having the bores 19a and the centrifugal weight 15 the bores 19b. These bores 19a and 1% are arranged in such a manner that the

centrifugal weights

14 and 15 are movable on the rods 19 along the bores, which rods are mounted in the shaft 1, and the centrifugal weights are guided by the rods 19.

On one end face of the centrifugal weights 14 and 15 (the right-hand side of FIG. 1) each centrifugal weight is provided with a rotatable crank 38.

These cranks are connected through the intermediary of a coupling member 39 designed as a disk. In this manner the

centrifugal weights

14 and 15 are kinematically connected through the intermediary of the cranks 38 and the coupling member 39 in such a manner that the deflection of the centrifugal weights is always identical. Due to this construction the respective characteristic curves can be realized with utmost accuracy in the entire working range of the machine by the combined design of the spring characteristic on the one hand and of the cam member on the other hand. In particular, with this combined regulating system, in the range of small numbers of revolution and in idle motion the spring characteristic will be so designed by correspondingly shaping the spring and the cam member that great paths of the regulating members will result at small regulating forces so that smooth idling and uniform transitions to small load points are ensured.

The embodiment shown in FIG. 3 includes a centrifugal governor 45 having two

centrifugal weights

43 and 44 which are pivotable about

pins

23 and 24, respectively, and guided in radial direction in guideways 42. The centrifugal force is compensated by a restoring spring 46- arranged on a driving shaft 41, which spring may also have a speed dependent elasticity constant. The centrifugal weight 43 has a cam member 47 fixed thereon and the centrifugal weight 44 carries a counterweight 48 corresponding to the cam member 47. Also in this embodiment a curved boundary surface of the cam member 47 can be traced by a feeler roller 50 provided with a restoring torsion spring 25, of a tracer 51 which is fixed on an intermediate shaft 52, and this tracing movement will be converted into turning movement of the intermediate.

shaft 52 relative to the driving shaft 41. An actuating rod 26 is fixed on the intermediate shaft 52 for the purpose of applying load from outside onto the intermediate shaft 52 and transmitting turning movement of the intermediate shaft 52 relative to the driving shaft 41 from the intermediate shaft to a regulating shaft 53. This actuating rod 26 is axially guided in an axial slot 49 of the regulating shaft 53 and movable by means of actuating rods 27 and 23, a ring 29 and a bearing 30 from load rods arranged to turn the ring 29. The actuating rods 27 and 28 are slidable in slanting

grooves

31 and 32 of the ring 29 longitudinally of the axis of the regulating shaft 53.

That portion of the device containing the

elements

26 and 29 serves for transforming the rotating movement initiated by an accelerator pedal through the toothed rim 29a into a longitudinal movement of the shaft 52 for the purpose of moving the tracer 51. In this connection the following detailed explanations are made:

The ring 29 is rotated from the accelerator pedal rods. This is carried out through a toothed rack (not illustrated) actuated by the accelerator pedal rods, the rack engaging the toothed rim 29a of the ring 29. A slanting groove 32 is arranged within the ring 29, the rods 27 and 28 sliding in this groove and axially moving in the

longitudinal grooves

31 and 32 when the ring 29 is rotated. The rods 27 and 2.8 engage the bores 30a and 30b in the outer ring of a needle bearing 30 which is also axially movable. When rotating the ring 29 the rod 26 is thus axially displaced and also axially displaces the shaft 52 and the tracer 51. A biasing means for measuring the load is neither provided nor necessary because the movement of the load lever is positively transmitted through the intermediary of the described mechanism to the tracer. The spring 25 is merely intended for pressing the tracer 51 against the cam member 47 in order to maintain the positive connection between the tracer 51 and the cam member 47. A rigid coupling between the intermediate shaft 52 or the regulating shaft 53 and the driving shaft 41 by the actuating rod 26 is avoided by

appropriate openings

33 and 34 in the driving shaft 41.

The quantity of fuel to be injected can be regulated in dependence on speed and load by the relative turning movement of the

rotatable distributor disks

2 and 4 according to the above-described principle and additionally in dependence on other factors (e.g. pressure and temperature of ambiency, temperature of cooling water) in conjunction with a variation of the injection pressure. Generation of pressure is effected e.g. by means of a pressure regulator 37 which can be influenced by the third factor.

FIG. 4 shows a diagrammatic sketch illustrating the co-operation of the regulating elements. The

centrifugal weights

14 and 15 exert a centrifugal force on the springs 20. The centrifugal weights are moved apart according to the specially designed spring characteristic in dependence on speed. This movement is transmitted to the cam member 13 in the direction of arrow 35. In accordance with the differences of height of the construction of the cam member in this direction of movement, this movement is transferred to the tracer 17 which is connected to the output of the regulator. The speed independent control quantity in the direction of arrow 36 is transmitted from the tracer 17 to the cam member 13, with the tracer 17 moving over the cam member 13 perpendicularly to the speed dependent direction of movement indicated by arrow 67, and an additional movement of the regulating elements at the output of the regulator is achieved by corresponding differences of height of the construction of the cam member 13 in this direction. It is of no consequence to the principle of regulation whether the speed dependent movement is transmitted from the centrifugal weights primarily to the cam member 13 and from this secondarily to the tracer 17 or vice versa. The

same applies analogously to the application of the speed independent control quantity.

FIG. 5 shows an embodiment of the regulating system in which the cam member 13 is fixed on the centrifugal weight 14 of the centrifugal governor and movable by the centrifugal weight 14 in radial direction indicated by arrow 69 along the tracer 17 which is arranged on the intermediate shaft 16 and movable axially along the cam member 13 by the speed independent control quantity 68, the differences of height of the construction of the cam member 12 being transmittable as turning movement to the output shaft 3 of the regulator.

The embodiment shown in FIG. 6 corresponds practically to the embodiment of FIG. 1 having a fuel feed pump incorporated therein. Fuel can pass under small inlet pressure through a bore 55 into an inner space 56 of a fuel feed pump 54 known per se. The distributor driving shaft 1 has a swash plate 57 fixed thereon which is driven with the speed of the regulator. A piston 58 is constantly urged by a pressure spring 59 against an oblique surface 60 of the swash plate 57 so that it can erform reciprocating movements within a bore 61 during the rotation of the swash plate 57. In the moved-out position of the piston 58 a suction valve 63 is opened by a bore 62 of the piston and fuel sucked into the bore 61. When the piston 58 is moved into the bore 61, the suction valve 63 will be closed and the fuel fed into an inner space 65 of the distributor on opening of a pressure valve 64. From the inner space 65 the fuel passes through the passage opening 6 inthe-rotating distributor disk 2, through the bore 10 in the fixed disk 11 and through the passage opening 7 in the second rotating distributor disk 4- into outlet passages 66 and further through the injection pipe to the respective injection n02.- Zles.

If this effective control cross section or open passage cross section of the two rotating disks would remain constant at increasing speed of the disks the amount of fuel passing through the set of disks per revolution would continuously decrease with increasing speed because the period of time in which the effective (open) control cross section of the rotating disks passes over the input and output bores in the fixed disks would become smaller and smaller.

The-time cross section means the integration of these passage cross sections over the time differentials.

In order that the penetrating amount of fuel does not decrease, or decreases more or less according to the requirements when the speed increases according to the operational requirements of the respective engine (e.g. an Otto engine), a centrifugal governor causes a relative rotation of the two rotating disks whereby the effective control cross section can be enlarged in order to be capable of adjusting the time cross section to the requirements by changing the flow cross section of the fuel passage.

In the case of decrease of speed the same applies analogously.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be conidered in all respects as illustrative and not restrictive, the-scope of the invention being indicated by the appended claims rather than by the foregoing description and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

I claim:

1. A fuel regulating device comprising a distributor injection means having fuel passage means t'herethrough, a centrifugal governor associated with an input shaft, a cam member movable radially of said input shaft by said centrifugal governor, a cam tracer carried by an intermediate shaft, and first and second means for varying the cross section of said passage means in speed dependent and speed independent relation respectively, relative to said input shaft, said first means comprising at least one spring having a pre-selected deflection characteristic and cooperating with said governor for relative movement of said cam member and cam tracer; said second means including means responsive to an external load being associated with said intermediate shaft for movement of said cam tracer relative to said cam member.

2. A regulating device as claimed in claim 1, wherein the spring characteristic is designed to correspond to the path of movement of governor weights such that in ranges of regulation in which relative-1y great paths of a contact element of the tracer on the cam member must be achieved, thus normally steep regions of the cam member would be necessary, the movement of centrifugal weights forming the centrifugal governor will be large, but in ranges where only small regulating movements are required, the movements of the centrifugal weights will be small.

3. A regulating device as claimed in claim 1, wherein the cam member is directly carried by a centrifugal weight of the centrifugal governor.

4. A regulating device as claimed in claim 1, wherein the centrifugal governor has two centrifugal weights, a casing portion of the input shaft carries the centrifugal governor, means are provided for guiding the two centrifugal weights of the centrifugal governor radially to the axis of the regulator in the casing thereof, two cranks serve to guide the two centrifugal weights of the centrifugal governor symmetrically to the axis of the regulator in the casing thereof, each spring having a speed dependent elastically constant and wherein said springs are radially acting.

5. A regulating device as claimed in claim 4, wherein the means for guiding the centrifugal weights radially to the axis of the regulator comprise rods.

6. A regulating device as claimed in claim 4, wherein the means for guiding the centrifugal weights symmetric to the axis of the regulator comprise connecting links.

7. A regulating device as claimed in claim 2, wherein the spring characteristic is designed by variable thickness of the windings in dependence on speed in such a manner that the required variation in length of the spring is realized in such a way that the associated angles of inclination on the cam member are reduced to mean values on an average.

8. A regulating device as claimed in claim 2, wherein the spring characteristic is designed by variation of the diameter of the windings in dependence on speed in such a manner that the required variation in length of the spring is realized in such a way that the associated angles of inclination on the cam member are reduced to mean values on an average.

9. A regulating device as claimed in claim 2, wherein the spring characterstic is designed by variation of the pitch in dependence on speed in such a manner that the required variation in length of the spring is realized in such a way that the associated angles of inclination on the cam member are reduced to mean values on an average.

10. A regulating device as claimed in claim 2, wherein by combining at least two of the following three measures: variable thickness of the windings, variation of the diameter of the windings and variation of the pitch the spring characteristic is designed in dependence on speed in such a manner that the required variation in length of the spring is realized in such a way that the associated angles of 8 inclination on the cam member are reduced to mean values on an average.

11. A regulating device as claimed in claim 1, wherein when the device is used for internal combustion engines and gas turbines, spring characteristic and cam member are designed to co-operate in such a manner that in the range of small outputs and in idle motion very small angles of inclination of the cam member are associated with large paths of centrifugal weights forming the centrifugal governor, thereby to achieve particularly smooth idling and good transitions in the range of small positions of load.

12. A regulating device as claimed in claim 2, wherein relatively rotatable distributor disks comprise said passage means, said input shaft carrying one said disk, and a distributor shaft carrying another disk, said distributor shaft being non-positively connected to the intermediate shaft tracer and the tracer itself is capable of converting, by its non-positive connection with the distributor shaft, the differences of height of the cam member directly into turning movement of the rotatable distributor disks relative to one another.

13. A regulating device as claimed in claim 1, wherein the centrifugal governor has two centrifugal weights, a casing portion of the input shaft rotatably mounts the centrifugal governor, connecting links are provided for radially guiding the two centrifugal weights of the centrifugal governor, and axially acting regulator spring means having a speed dependent elasticity constant are provided for restoring the two centrifugal weights.

14. A regulating device as claimed in claim 1, wherein a fuel feed pump is provided associated with said distributor injection means.

15. A regulating device as claimed in claim 14, wherein the fuel feed pump is of swash plate type construction with axial passage of fuel to the distributor disks.

16. A regulating device as claimed in claim 1, wherein a pressure regulating element is provided for additionally regulating the fuel pressure and relative turning of the rotatable distributor disks is effected by speed and load in combination with a known regulation of the quantity of fuel in dependence on an additional factor by the additional regulation of the fuel pressure by means of the pressure regulating element.

17. A regulating device as claimed in claim 1, wherein the combined speed dependent and speed independent variation of said passage means of the distributor injection means serving to supply the fuel is effected by relative rotation of two rotating distributor disks provided with slots.

18. The regulating device of claim 17 wherein said passage means defines a time cross-section of fuel flow during operation of the device.

References Cited UNITED STATES PATENTS 1,096,386 5/1914 Norton 73-537 2,081,466 5/1937 Tarisien 137-56 2,352,736 7/1944 Richmond 137--29 2,805,549 9/1957 Hensleigh et al. 6054 2,867,084 l/l959 Criswell 6039.28 3,016,911 1/1962 Strand l37----33 3,200,886 8/1965 Magri et a1. 60-39.28 X

JULIUS E. WEST, Primary Examiner.

Claims

1. A FUEL REGULATING DEVICE COMPRISING A DISTRIBUTOR INJECTION MEANS HAVING FUEL PASSAGE MEANS THERETHROUGH, A CENTRIFUGAL GOVERNOR ASSOCIATED WITH AN INPUT SHAFT, A CAM MEMBER MOVABLE RADIALLY OF SAID INPUT SHAFT BY SAID CENTRIFUGAL GOVERNOR, A CAM TRACER CARRIED BY AN INTERMEDIATE SHAFT, AND FIRST AND SECOND MEANS FOR VARYING THE CROSS SECTION OF SAID PASSAGE MEANS IN SPEED DEPENDENT AND SPEED INDEPENDENT RELATION RESPECTIVELY, RELATIVE TO SAID INPUT SHAFT, SAID FIRST MEANS COMPRISING AT LEAST ONE