Control System for Stump Cutters

Not Applicable

A portion of the disclosure of this patent document, including appendices, may contain material which is subject to copyright protection. The copyright owner has no objection to the facsimile reproduction by anyone of the patent document or the patent disclosure, as it appears in the Patent and Trademark Office patent file or records, but otherwise reserves all copyright rights whatsoever.

1. Field of the Invention

This invention pertains generally to stump cutters, and more particularly to an apparatus and method for controlling the rate of feed of a stump cutter.

2. Description of the Related Art

Stump cutting machines are well known for removing undesirable tree stumps. Such machines include a rotating cutter wheel driven by a gas or diesel engine. The cutter wheel, while rotating, is advanced toward the stump and laterally across the face of the stump. The cutter wheel is mounted at one end of a boom which is, in turn, pivotally mounted on a support frame. Hydraulic boom swing cylinders are used to pivot the boom about the pivot point to move the cutter wheel back and forth across the face of the stump to cut it away.

Stump cutters are often subjected to overload conditions which result in premature failure of certain components such as structural and shielding members, engines and drive train members. Also, with most engines, a loss of power output occurs during an overload condition as the engine speed is reduced below a rated operating speed. Less power to the cutting wheel results in reduced productivity. Further, the loss of cutter wheel speed causes a loss of cutter wheel energy which results in the wheel being less effective in smoothing out shock loads. Such loads may be several times greater than the maximum engine output torque. Also, when the cutter wheel loses speed, engine power required to accelerate the wheel back to full speed is not available for cutting the stump.

In prior art stump cutting machines, an operator has access to a needle valve to permit the operator, at his discretion, to adjust the needle valve to control the hydraulic oil to the boom cylinders in order to properly load the engine. The operator commonly adjusts the needle valve based on the sound of the engine. Such an adjustment is subject to operator error. Furthermore, an operator may not react fast enough or frequently enough to adapt to changing engine load conditions. Also, an operator might simply forget to adjust the needle valve or otherwise fail to adjust the valve during operation. As a result, at any given moment, the engine may be either overworked or underworked.

Those concerned with these and other problems recognize the need for an improved feed rate control system for stump cutters.

The present invention provides a method and an apparatus to maintain optimum engine speed and cutter wheel speed to maintain peak power output of the engine and peak flywheel effect of the stump cutter wheel. The stump cutter has a rotating cutting wheel powered by an engine, and the cutter is mounted to be moved laterally. The mounting includes a boom and at least a first hydraulic cylinder for urging the boom to move along the path of travel over the surface of a stump. The hydraulic cylinder is activated by a hydraulic circuit which includes a source of pressurized hydraulic fluid. A pressure hydraulic line connects the source of hydraulic fluid to a first port of the hydraulic cylinder and a return line is connected to a second port of the hydraulic cylinder. A valve diverts a portion of flow from the pressure line to the return line or to a sump. The valve is shiftable between at least a first and a second position. In the first position, substantially all hydraulic fluid is passed along the pressure line to the hydraulic cylinder. In the second position, at least a portion of the hydraulic fluid is diverted from the pressure line. A sensor is provided for sensing a speed of the engine or a condition of a component of the stump cutter which is a function of a speed of rotation of the engine. A circuit interconnects the sensor and the valve. The circuit selectively shifts the valve from the first position to the second position when the sensed speed of the engine is less than a predetermined minimum speed.

Therefore, an object of the present invention is the provision of an improved feed rate control system for stump cutters.

Another object of the present invention is to provide an improved feed rate control system for a stump cutter.

A further object of the invention is to provide a method and an apparatus for maintaining optimum engine speeds for stump cutters.

A still further object of the present invention is to provide an apparatus for preventing the engine speed of a stump cutter from being reduced below a predetermined amount upon advancement of the cutter wheel into a stump.

In accordance with the present invention a method for operating an engine of a stump cutter involves sensing a condition of a component of a stump cutter having an engine wherein the condition is a function of a speed of rotation of the engine and controlling movement of the stump cutter toward a stump based on the function of the speed of rotation of the engine.

For purposes of the present invention, the controlling involves reducing a speed of advancement of the stump cutter toward the stump when the speed of rotation of the engine is below a predetermined speed of rotation, increasing a speed of advancement of the stump cutter toward the stump when the speed of rotation of the engine is above a predetermined speed of rotation, and/or stopping advancement of the stump cutter toward the stump when the speed of rotation of the engine arrives at a predetermined speed of rotation.

For purposes of the present invention, the component of the engine the condition of which is sensed may be at least one member selected from the group consisting of a coil, a pump, a flowmeter, the pressure drop across an orifice in a pump line, pressure pulses in the discharge line of a gear-type pump, an electronic engine governor system, a distributor, a generator, an alternator, a flywheel, a fan blade, a pulley, a camshaft, a cutter wheel, a drive train and a drive shaft, which are operably associated with the engine.

Accordingly, in unity with the present invention, sensing involves the condition which is a function of the speed of rotation of the engine on a coil which is operatively attached to the engine; on a pump or pump component which is operatively attached to the engine; on an electronic governor which is operatively attached to the engine on a distributor which is operatively attached to the engine; on a generator which is operatively attached to the engine; on an alternator which is operatively attached to the engine; on a flywheel which is operatively attached to the engine; on a fan blade which is operatively attached to the engine; on a pulley which is operatively attached to the engine; on a camshaft which is operatively attached to the engine; on a cutter wheel which is operatively attached to the engine; on a drive train which is operatively attached to the engine; and/or on a drive shaft which is operatively attached to the engine and operatively attached to a cutter wheel.

In accordance with the present invention, a stump cutter having an engine operable at a speed of rotation including an optimum speed of rotation, and a cutter disposed to cut a tree stump is provided with a sensor for sensing a condition of a component of a stump cutter wherein condition being a function of a speed of rotation of the engine; and a control for controlling movement of the stump cutter toward a stump based on the function of the speed of rotation of the engine.

For purposes of the present invention, the control includes a speed reducer for reducing the speed of advancement of the stump cutter toward the stump when the speed of rotation of the engine is at a predetermined speed of rotation, an accelerator for increasing a speed of advancement of the stump cutter toward the stump when the speed of rotation of the engine is at a predetermined speed of rotation, and an arrestor or brake for stopping advancement of the stump cutter toward the stump when the speed of rotation of the engine arrives is at a predetermined speed of rotation.

Accordingly the component, the condition of which is a function of the engine speed being sensed, may be a coil which is operatively attached to the engine; a pump or pump component which is operatively attached to the engine; an electronic governor which is operatively attached to the engine, a distributor which is operatively attached to the engine; a generator which is operatively attached to the engine; an alternator which is operatively attached to the engine; a flywheel which is operatively attached to the engine; a fan blade which is operatively attached to the engine; a pulley which is operatively attached to the engine; a camshaft which is operatively attached to the engine; a cutter wheel which is operatively attached to the engine; a drive train which is operatively attached to the engine; and/or a drive shaft which is operatively attached to the engine and operatively attached to a cutter wheel.

In one embodiment, but not essential aspect of the invention, the signal from the component identified in the above paragraph can be transmitted to the signal processor or controller by a wire, an optical device, a radio frequency device or an audio device.

Other objects, advantages, and novel features of the present invention will become apparent from the following detailed description of the invention when considered in conjunction with the accompanying drawings, wherein:

FIG. 1 is a perspective view of a preferred embodiment of a stump cutter of the present invention attached to a towing vehicle;

FIG. 2 is a side elevational view of the stump cutter of FIG. 1 shown in readiness to cut a stump;

FIG. 3 is an enlarged partial side elevational view showing the cylinder that raises and lowers the stump cutter boom, and one of the cylinders that oscillates the boom from side-to-side;

FIG. 4 is a side elevational view similar to FIG. 2 showing the stump cutter in the lowered position engaging and cutting a stump, and showing the tongue extended from the position shown in FIG. 2;

FIG. 5 is an enlarged partial cross-sectional view taken along line 5--5 of FIG. 4, showing the boom lifting cylinder, and the cylinders used to oscillate the cutter wheel back and forth across the surface of the stump;

FIG. 6 is a top plan view of the hydraulic control levers used to actuate the hydraulic cylinders;

FIG. 7 is a schematic representation of a control system according to the present invention including a diverting valve and associated circuit elements;

FIG. 8 is a schematic of an alternate diverting valve circuit;

FIG. 9 is a schematic of a still further alternative diverting valve circuit;

FIG. 10 is a graphical representation of an operation of a control system for a stump cutter according to the present invention using an on-off solenoid valve;

FIG. 11 is the graphical representation of the operation of the control system when modified to reflect the use of a proportional controlled solenoid valve;

FIG. 12 is the graphical representation of the operation of FIG. 11 showing modification of the slope of the performance graph of FIG. 11;

FIG. 13 is the modification of the graph of FIG. 11 showing translational repositioning of the graph;

FIG. 14 is a schematic representation of an alternative embodiment of the present invention;

FIG. 15 is a schematic representation of a disabling system for the control system;

FIG. 16 is a schematic view of the engine of a stump cutter showing several alternate embodiments for providing a signal which is a function of the speed of rotation of the engine;

FIG. 17 is a perspective view showing a device for sensing the speed of the engine flywheel;

FIG. 18 is a perspective view showing devices for sensing the speed of the radiator fan and the speed of a pulley on the engine;

FIG. 19 is a perspective view showing a sensor disposed to sense the rotation of a slotted disc on the end of the engine's camshaft;

FIG. 20 is a perspective view similar to FIG. 1 showing magnetic sensors disposed to sense the speed of rotation of the cutter wheel and, alternatively, the drive train of the cutter wheel;

FIG. 21 is a schematic view showing sensors disposed to sense the rotation of a shaft through a bearing and a sensor to sense the rotation of the cutter wheel;

FIG. 22 is a schematic view of a fixed displacement pump with sensors which sense a condition of the pump system which is a function of the speed of the engine to which the pump is connected, and a signal is sent to the signal processor of the stump cutter;

FIG. 23 is a cross sectional view of a gear-type pump with a high speed pressure sensor operatively disposed in the discharge side of the pump for sensing the frequency of pressure pulses which are a function of the speed of the engine to which the pump is attached;

FIG. 24 is a schematic view of an electronic engine governor which uses the speed detection device of such electronic governor or a speed output signal from the electronic governor system to provide a speed input signal to the signal processor of the stump cutter engine speed control; and

FIG. 25 is identical to FIG. 7 except for the left-most part thereof which shows three alternatives to hard wiring the output from the component which provides an input of a signal which is a function of the speed of the engine, such alternatives being optical, radio frequency or audio devices to pass the signal to the signal processor.

Referring now to the drawings wherein like reference numerals designate identical or corresponding parts throughout the several views, FIGS. 1 and 2 show a stump cutter (10) constructed in accordance with the present invention. As best shown in FIGS. 1-5, the stump cutter (10) includes a frame (9) having a movable boom (14) pivotally attached to the frame (9) about a horizontal axis of pin (13). Referring to FIGS. 4 and 5, a connector member (7), including the pin (13), also permits the boom (14) to pivot about the vertical axis of shaft (11) as shown in FIG. 5. A hitch assembly (15) permits the stump cutter (10) to be hitched to a towing vehicle (16) and a tongue extending cylinder (121) permits the tongue (5) to telescope between the retracted position shown in FIG. 2 and the extended position shown in FIG. 4. Pneumatic wheels and tires (19) are rotatably attached to the frame (9) for permitting the stump cutter (10) to be towed from place to place, and also to facilitate the movement of the tongue (5) by the tongue extension cylinder (121) between the positions shown in FIGS. 2 and 4.

An engine (32) is mounted by resilient engine mounts (21) to the boom (14) as shown in FIGS. 1-4. Turning to FIGS. 2 and 7, the engine (32) is shown powering a hydraulic pump (35) for providing hydraulic fluid to the tongue extension cylinder (121), the boom lifting cylinder (120), and the boom swinging cylinders (18, 18'). The boom lifting cylinder (120) raises and lowers the boom (14) between the positions shown in FIGS. 2 and 4. The swing cylinders (18, 18') oscillate the boom (14) in an arc as indicated by the directional arrow A shown in FIG. 5. By connecting the source of high pressure hydraulic fluid to ports (22') and (24), while allowing hydraulic fluid to flow out of ports (22) and (24'), the boom (14) will move to the left (FIG. 1-4). Reversing the flow will cause the boom (14) to move to the right (FIGS. 1-4). The engine (32) has a rotary output shaft (not shown) which connects to a clutch (29) which can be used to selectively transmit rotary power into a gear box (31). The gear box (31) is of a conventional type, including meshing bevel gears with input and output shafts angularly disposed with respect to each other. The ratio of power transmission can be set at any desired level, for example 1:1, or any other ratio desired. Rotary power is transmitted by a shaft interconnecting the upper gear box (31) and a lower gear box (33), which, in turn, transmits rotary power to the cutter wheel (12).

To operate the preferred embodiment shown in FIGS. 1-5, the towing vehicle (16) is used to tow the stump cutter (10) to the location of the stump (30), and position it as shown in FIG. 2, by backing it up to the stump (30). The operator then moves the panel (20) out to the operating position. The top of the panel (20) includes a transparent viewing window and a flexible rubber curtain (49a) which hangs down from the panel (20) to protect the legs of the operator. The curtain assembly (49) actually extends completely around the rear and sides of the frame (9) of the stump cutter (10) to catch and collect the chips from the cutting wheel (12). Once the engine (32) is started, the operator engages the clutch (29) to cause the drive train to rotate the cutter wheel (12). By operating the control levers (25) on the panel (20), the operator extends the cylinder (120) so that the cutter (12) engages the stump (30). The tongue (5) is also extended from the position shown in FIG. 2 to the position shown in FIG. 4. This can be done in any order desired. The lift cylinder (120), of course, causes the cutter wheel (12) to move up and down and the tongue cylinder (121) causes the cutter wheel (12) to move fore and aft, towards and away from the stump (30). The operator simultaneously uses the controls (25) to cause the hydraulic swing cylinders (18, 18') to move the boom (14) in an oscillating arc over the surface of the stump (30), thereby causing the stump to be cut away. The chips are collected in the area enclosed by the curtain (49) as shown in FIG. 4. In the FIG. 4 position, when the cutter wheel shield (55) abuts the top of the stump (30), it pivots upwardly about a pivot point (58) and against the resistance cylinder (57), which biases it to its lowered position shown in FIGS. 1 and 2. Having the oscillating feature of the boom (14) is extremely important because if it were not present on the frame (9), it would require that the towing vehicle (16) be used to re-position the cutter wheel (12) from time to time to move it to one side or the other of the stump (30).

FIG. 7 shows a stump cutter (10) having a cutter wheel (12) mounted on a boom structure (14) for rotation about the axis X--X of wheel (12). The boom structure (14) is pivotally mounted to a support platform or frame (9), by connector member (7), to pivot about a generally vertical axis of shaft (11).

In the preferred embodiment, an actuator in the form of two hydraulic cylinders (18, 18') are provided for urging the boom structure and cutter wheel (12) to move back and forth along the direction of travel indicated by arrow A. Other advancing structures, such as electric actuators, could be used instead. The hydraulic cylinders include a head end (18a, 18a') and a rod end (18b, 18b'). The head ends (18a, 18a') are pivotally mounted to a connector member (7) as shown in FIGS. 3 and 5. The rod ends (18b, 18b') are pivotally mounted to the boom structure (14) as shown in FIGS. 3, 5 and 7.

The hydraulic cylinders include first ports (22, 22') and second ports (24, 24'). The first ports (22, 22') pass hydraulic fluid into or out of the head ends (18a, 18a') of the cylinders (18, 18'). The second ports (24, 24') pass hydraulic fluid into or out of the rod end (18b, 18b') of the hydraulic cylinder (18, 18') as is conventional.

With the structure thus described, when hydraulic fluid is admitted to ports (22, 24'), the boom structure and cutter wheel move downwardly in the view of FIGS. 5 and 7. When hydraulic fluid is admitted to the ports (24, 22'), the boom structure and cutter wheel move upwardly as viewed in FIGS. 5 and 7. By reason of moving the cutter wheel (12) in the direction of arrow A, the cutter wheel (12) can be advanced across the face of a stump (30) to thereby remove the stump (30).

Power to the cutter wheel (12) is provided by an engine (32) which may be powered by gasoline or diesel fuel. A pump drive arrangement (34) from the engine (32) drives a hydraulic pump (35), which is a source of hydraulic fluid for the cylinders (18, 18').

From time to time, the operator will advance the cutter wheel into the stump at a rate faster than a rate that the engine (32) can handle. The result is a reduction in the speed of the engine (32) below its rated output speed. The present invention, in its preferred embodiment, is directed to an electronic and hydraulic circuit for reasonable avoidance of engine overload, i.e., engine operation below the rated operating speed. Also, it is desirable to maintain a feed rate that will fully load the engine rather than having the engine underloaded.

The hydraulic circuit (FIG. 7) includes a main control valve (36) having a first hydraulic line (38) connected to ports (22, 24'). In one embodiment, FIG. 7, line 38 has segments (38a) and (38b) joined by a valve (50) as will be described. A second hydraulic line (40) connects the control valve (36) to ports (22', 24). A line (42) connects the control valve (36) to a sump (44). A source line (46) connects the control valve (36) to the hydraulic pump (35).

The control valve (36) may be shifted from a first position shown to a second position reversing the flow from the first position thereof. The valve (36) also has a third position shown by the center portion of valve (36) in FIG. 7 which allows no flow to the boom swing cylinders (18, 18'). In the first position, pressurized hydraulic fluid from line (46) is admitted to line (38). Also, in the first position, hydraulic fluid in line (40) is passed through line (42) to sump (44). When the control valve (36) is shifted to its second position, pressurized hydraulic fluid from line (46) is passed to line (40) and hydraulic fluid in line (38) is vented through line (42) to sump (44). The control valve (36) is shiftable by an operator to selectively permit the operator to change the direction of travel of the cutter wheel between the direction of arrow A in FIG. 7, and the opposite direction.

It is noted that in FIG. 7, valve (36) is shown in a simplified form. In actuality, the valve (36) represents one spool of what is typically a multi-spool valve block as illustrated in FIG. 6. The oil, therefore, does not usually come directly from the pump (35), pass through the spool valve (36) and go back to the sump (42) without being used for other functions such as for the lift cylinder (120) and the tongue extension cylinder (121).

A solenoid-operated valve (50) is disposed along line (38) and has a vent line (52) connected from the solenoid-operated valve to line (40). The solenoid-operated valve (50) is shiftable between at least two positions. In its first position, line (38a) is uninterrupted. In the second position, line (38a) is connected to line (40). The solenoid valve (50) is shifted between the first and second positions by use of a signal-processing circuit (54).

As is conventional, engine (32) is provided with an alternator (56). The alternator (56) generates a signal that is proportional to engine (32) speed. Engine speed could be sensed by other devices, for example, off a crankshaft pulley. The signal sensed by sensor (60) is passed along electrical circuit line (62) to the signal processor (54). Signal processor (54) is connected by electrical line (64) to the solenoid valve (50).

Upon the sensor (60) generating a signal indicating an engine speed at or preferably below a predetermined minimum (for example, below 2600 rpm), the signal-processing circuit (54) activates the solenoid valve (50) to shift the solenoid valve (50) to the second position to divert fluid flow between lines (38a) and (40). When the speed of the engine (32) is sensed to be at or preferably above the predetermined minimum, the signal-processing circuit returns the solenoid valve (50) to its first position wherein no diverting of flow occurs between lines (38a) and (40).

An optional needle valve (70) is also provided connecting lines (38a) and (40). Needle valve (70) may be adjusted by an operator to control the amount of flow, if any, between lines (38a) and (40).

FIG. 8 shows an alternative placement of valve (50). Unlike FIG. 7, the valve (50) is not located in line (38). The valve (50) is positioned much like valve (70), between the pressure and return lines (38) and (40). The valve (50) allows oil flow from whichever is the pressure line (38 or 40) to line (52). Check valves (51) direct the flow of oil. FIG. 9 shows a still alternative placement of valve (50) similar to FIG. 8. In each of FIGS. 7, 8 and 9, needle valve (70) is optional and valve (50) is preferably a proportional valve.

With the invention thus described as shown in FIG. 7, the present invention retards the advance of the cutter wheel (12) in response to reduced engine speed. The system responds before an overload condition occurs. In response to reduced engine speed, the advance of the cutter (12) into the stump (30) is retarded by reason of flow being diverted to the return line (42) and sump (44).

In the present invention, oil or hydraulic fluid is directed away from the swing cylinder system by proportional valve (50) in greater quantities as the engine speed decreases. As a result, under certain conditions, the boom (14) will not swing at all. Accordingly, such a system can provide for disabling the electrical circuit automatically when the cutter wheel drive is disengaged by placing switch (230) in the position shown in FIG. 15. As a result, the operator or maintenance personnel may swing the boom (14) at any engine speed when necessary or desirable.

FIG. 15 illustrates an electrical circuit for disabling the control system for the swing cylinders (18, 18'). The circuit includes a double-pole, double-throw switch (230) connected across an ignition switch (210) to a battery (200). The ignition switch can be positioned in one of three positions. In the position shown, the battery (200) terminates at an open circuit.

The ignition switch (210) can be thrown to two active positions. In the first active position, contact is made only with contact A. In the second position, the switch element (210b) makes contact simultaneously with both contact points A and S.

The contact position A (FIG. 15) refers to a contact position for both the accessories and a normal run position. Contact position S is a position for starting the engine (32) of the stump cutter (10). The switch (230) is connected to a starter circuit (231), a clutch controller circuit (220) (as is conventional) and the circuit (54) of FIG. 7. The switch (230) may be thrown to an up position in which case power is provided to the starter circuit (231), assuming ignition switch element (210b) of switch (210) is in contact with contact S. Simultaneously, the switch (230) is in a clutch disengage position such that circuit (220) provides power to a clutch actuator (240) to disengage the clutch. When switch (230) is thrown in the down position, the power is diverted from the starter circuit (231) to an open circuit (232) and power is provided to an engage side of the clutch control circuit (220) to operate the clutch actuator (240). Simultaneously, power is also provided to circuit (54) to permit the control of valve (50) of FIG. 7. It will be appreciated that the clutch control circuit (220) and the clutch actuator (240) are commercially available items.

In the foregoing discussion, the valve (50) may be a simple "on-off" valve. However, it is believed that such a valve (50) could lead to choppy cutting performance and that a proportional valve (50) is preferred. With reference to FIG. 10, a graph is shown indicating operation of the system of the present invention where valve (50) is an on-off solenoid valve. FIG. 10 illustrates the amount of oil or hydraulic fluid being diverted from the swing cylinders (18, 18') as a function of an engine rpm for engine (32). In FIG. 10, a specific engine is presented which has representative performance of a no-load high idle speed at 2,860 rpm and a rated load speed of 2,600 rpm. The valve (50) is controlled by circuitry (54) to divert one hundred percent of the oil or hydraulic fluid from the cylinders (18, 18') upon obtaining a sensed engine speed of 2,575 rpm. As the load increases, the engine speed will decrease from high idle (no load) speed. When the load becomes such that the engine speed drops one percent (i.e., about 25 rpm) below the rated load speed, one hundred percent of the hydraulic fluid is diverted away from the pressure line and routed to the return line. As the engine speed recovers, one hundred percent of the flow is again directed to the swing cylinders (18, 18').

As previously mentioned, it is believed that an on-off solenoid valve in place of valve (50) may result in a jerky cutting operation for a stump cutter. FIG. 11 represents the operation of the stump cutter where valve (50) is a proportional solenoid valve. The solid line of FIG. 11, indicated by points a-b-d, represents a proportional solenoid valve (50) where the amount of hydraulic fluid being diverted from the swing cylinders (18, 18') increases approximately as a straight line function to a responsive decrease in engine rpm. In this example, the amount of hydraulic fluid diverted from the swing cylinder pressure line varies in proportion to the engine speed. Optional line a-b-c permits a faster swing operation under low load conditions where an operator may be interested in rapidly positioning the cutter wheel (12) to a different location. Line a-b-d provides smoother engagement of the swinging boom structure (14) and cutter wheel (12) with the stump (30) when an unloaded cutter wheel (12) first contacts the stump (30). Through selection of the circuitry of circuit (54), either of the graph profiles shown in FIG. 11 is attainable. Also, line a-b-d or line a-b-c should be established to ensure that the engine (32) runs as close as possible to the rated load speed during the working cycle of the engine (32) and the stump cutter (10). It is undesirable to either overwork or underwork the engine.

Further, it may desirable to disengage the electrical circuit (54) when the cutter wheel drive is disengaged with a system such as that shown in FIG. 15 by use of switch (230). This will permit the boom structure (14) to swing at reduced engine speeds such as when performing maintenance. Also, it may be desirable to provide a lock (8) (FIG. 3) which may mechanically lock the boom structure (14) in place during transportation.

A still further alternative embodiment of the present invention is to provide circuitry (54) to modify the positioning and geometry of lines a-b-c and a-b-d in FIG. 11. This is illustrated in FIGS. 12 and 13. In FIG. 12, the slope of lines a-b-d and a-b-c are modified, as illustrated by lines a'-b'-d', a'-b'-c', a"-b"-d" and a"-b"-c", to change the slope of the graphs. In FIG. 13, the positioning of the lines is translated to the left or the right of the original lines a-b-c-d. Either option can be selected through modification of circuitry (54).

A still further embodiment of the present invention is shown in FIG. 14. In FIG. 14, the proportional control valve (50) is not utilized. Instead, a variable displacement pump (35') is utilized. The sensed speed of the engine (32) is utilized by circuitry (54) to control the output of the variable displacement pump (35') which then controls the control valve (36) operating the swing cylinders (18, 18'). A standard pump (35") controls the raising and lowering cylinder (120) and a tongue extending cylinder (121) typically found with stump cutters which are controlled by separate respective control valves (36') and (36") (FIGS. 6 and 14). With the embodiment of FIG. 14, the variable output being provided to the swing cylinders (18, 18') is provided by a variable output pump (35') rather than by a proportional solenoid valve (50) of the previously discussed embodiments. A further alternative to FIG. 14 is to eliminate pump (35") and have pump (35') provide flow to valves (36') and (36") as well as to valve (36).

FIGS. 16-21 essentially show the equivalence of using a sensor (60) to sense the speed of the engine (32) with other devices which either directly sense a condition of a component of the stump cutter, which is a function of the engine speed or sense a condition of another component of the stump cutter which can produce a signal which is a function of speed of the engine (32).

Components of the stump cutter, a condition which may be sensed for purposes of the present invention, include components selected from the group consisting of a coil, a pump, a distributor, a generator, an alternator, a flywheel, a fan blade, a pulley, a camshaft, a cutter wheel, a drive train and a drive shaft.

The condition of such components, which is a function of the engine speed that is sensed by sensors in accordance with the present invention, is described in more detail below.

In FIG. 16, the alternator/generator (56) generates a signal which is transmitted to the computer/controller (71). The signal from the alternator/generator (56) will then be processed in the computer/controller (71) to indicate that it is a function of the speed of the engine (32) and this information is then used to maintain the optimum rpm of the engine (32).

Similarly, the coil (73), a sensor (74) on the pump (75) and the distributor (77) can be utilized to send a signal to the computer/controller (71). Since these signals indicate conditions which are all a function of the engine speed, they can be used to control the optimum speed of the engine (32) as described above by regulating the rate of advancement of the cutter wheel toward the stump as may be required to reduce or increase the load on the engine (32) through the cutter wheel's contact with the stump.

Turning to FIG. 17, a flywheel (78) of the engine (32) is shown with a starter (79). The teeth (80) of the engine flywheel can individually be sensed as they pass by the sensor (81.) The signal produced by sensing the speed of the teeth (80) of the flywheel (78), a condition which is a function of the speed of the rotation of the engine (32) is fed to the computer/controller (71) to control the movement of the stump cutter (10).

In FIG. 18, the speed of the blades of engine radiator fan (82) is sensed by use of a light transmitter (83) which sends a signal of light to a light detecting device (84). The blades of the engine radiator fan (82) interrupt the light as they pass by. As the light is applied and then taken away from the photo detecting device (84), the device (84) will emit a signal. A counter (not shown) will count these signals and then transfer this information to the controller/microprocessor (71). This signal is transmitted to the computer/controller (71) for indicating the speed of the engine (32). These optical type sensors can, of course, be used on other moving devices such as on the teeth of a gear.

Similarly, a pulley (85) driven by a belt (86) off drive pulley (87) has openings (88) therethrough. An optical sensor which includes a light transmitter (89) and a light receiver (90), senses the passage of light through the openings in the pulley (85). The speed of the rotation of the pulley (85) is a sensed condition of the pulley (85), which is a function of the speed of rotation of the engine (32). This information is transmitted to the computer/controller (71) and is used to control the rate of advancement of the cutter wheel (12) towards the stump in a manner discussed in detail above.

FIG. 19 shows the engine (32) with a four-leaf-clover shaped disc (91) attached to the end of the camshaft (92). A magnetic sensor (93) is positioned to sense the passage of each of the lobes of the disc (91) as a condition of the camshaft (92) which condition is a function of engine speed. This provides information to the computer/controller (71) for controlling the advancement of the cutter wheel (12) above. Disc (91) is not part of the camshaft gear but is a special disc added to the camshaft for this sensing purpose. Disc (91) can have more or less lobes or depressions than the number shown in FIG. 19.

Referring now to FIG. 20, a magnetic sensor (94) is shown disposed on the shield (95) and a target (96) is disposed on the drive shaft (97). The sensor (94) detects the passage of the target (96) in its rotation on the shaft (97). Shaft rotation is a condition which is a function of engine speed. A signal from the sensor (94) is transmitted to the computer/controller (71) for processing to control the advancing of the cutter wheel (12) toward the stump as discussed above.

A magnetic sensor (98) also is shown in FIG. 20 for sensing the speed of the cutter wheel (12) by sensing when the target (99) passes by the magnetic sensor (98). Similarly, this information from the magnetic sensor (98) is fed to the computer/controller (71) for controlling the advancement of the cutter wheel (12) towards the stump.

Referring now to FIG. 21, the engine (32) drives a drive belt (100) around pulleys which, in turn, drives a shaft (101). The drive shaft (101) is supported by bearings (102 &103). The bearing (103) has a sensor (104) thereon for sensing the speed of rotation of the shaft (101).

Bearings which will sense the speed of shaft rotation can be purchased as a unit, for example, Dodge brand bearing monitors are available from Rockwell Automation Corporation.

Similarly, a belt (105) is driven by pulley (106) and drives pulley (107) to turn the shaft (108) of cutter wheel (12). This cutter wheel (12) has a target (109) thereon which is sensed by magnetic sensor (110). The rotation of the cutter wheel (12) is a function of the speed of the engine (32). The signal from sensor (110) is fed to the computer/controller (71), and this signal is used to control the speed of the engine (32) as discussed above.

FIGS. 16-21, therefore, show various ways that a condition of a component which is a function of the speed of the engine (32) can be sensed either directly or indirectly. Of course, those skilled in this art can conceive of many other ways to sense the speed of the engine (32) or of things or components that could be a function of the speed of the engine (32). For example, even a strain gauge (not shown) on the engine mounts could sense torque and provide information which would be a function of the speed of the engine (32).

In FIGS. 16-21 numerous ways are shown to sense a condition which is a function of the engine speed or the actual engine speed. Thus, although a plurality of ways are illustrated, it is only necessary to use one of these in any one situation. For example, in FIG. 16 if the speed of the alternator/generator (56) is being used to send a signal to the computer/controller (71), then it is not necessary to sense any other speed or condition of another component of the stump cutter which is a function of engine speed.

Referring now to FIG. 22, a fixed displacement pump (75) similar to that shown in FIG. 16 is operatively attached to the engine (32) of FIG. 16. A number of alternative ways to sense a condition of the pump (75) in order to provide a signal to the signal processor (71) which is a function of the speed of the engine (32) is shown by sensors (74a), (74b), (74c) and (74d). The sensor (74a) is a magnetic sensor which counts the rotations or cycles of the pulley (175), this pulley (175) is rotating as a function of the engine speed of engine (32).

Pressure sensor (74b) detects the pressure in the discharge port of pump (75) and relays this pressure to the signal processor (71), such pressure being a function of the speed of the engine (32).

Referring again to FIG. 22, a flowmeter (74c) in the discharge line of pump (75) measures the flow through the discharge line and sends a signal to signal processor (71), such signal being a function of the speed of the engine (32).

Still referring to FIG. 22, a pressure differential device (74d) is disposed in the discharge line and has an orifice/venturi therein which is a calibrated restriction. The pressure drop P1-P2 across this restriction may be used to compute flow, which is a function of engine speed. This pressure drop is transmitted to signal processor (71).

Referring now to FIG. 23, a gear pump (275) is shown and has a high speed pressure sensor (74e) attached on the discharge side thereof. This high speed pressure sensor (74e) senses pulses from the gear pump (275). The gear pump (275) draws fluid into the gear set. As the gears move in and out of mesh, pressure pulses occur in the high pressure fluid. The pulse frequency is proportional to the number of gear teeth. The high speed pressure sensor (74e) detects the pulses and relays this information to the signal processor (71). The signal processor (71) counts the pulses, correlates the count to engine speed, and performs its other functions accordingly to provide a signal which is a function of the engine speed.

FIG. 24 shows an alternate way to use a signal which is a function of the engine speed. An electronic governor system (200) is controlled initially by an input from a speed detection device (201) which could be a magnetic shaft rotation detection device as discussed elsewhere in this patent application or other ways to sense the speed of the engine. This signal is not only used for the electronic governor system, but it can be also used for the signal processor, either (54) as shown in FIGS. 7 and 25 or the signal processor (71) as shown in FIGS. 16, 22, 23 and 24.

Alternatively, the electronic governor systems will compute an actual speed and therefore can have a speed output signal (202) which can be fed into the signal processor (54) or (71) and will be the actual speed of the engine. The signal processor then controls the valve (50) as is shown in the FIG. 25 embodiment, for example.

Referring again to FIG. 24, it is noted that the electronic governor system could be one of any one of a number of electronic governor systems, for example as shown in U.S. Pat. Nos. 3,900,013, 3,563,219 and 4,676,218, which patents are incorporated herein by reference. The electronic governor system typically just controls the speed of the engine by controlling the fuel and/or air mixture through a speed detection device and sending a signal to a fuel input device such as a valve that would control either fuel or air or perhaps two valves; one which would control the fuel and one which would control the air to the engine.

Referring now to FIG. 25, it is noted that everything in this drawing is exactly like that of FIG. 7 except that instead of having a hard wire (62) from the alternator (56) to the signal processor (54), wireless devices such as optical device (160), radio frequency device (170) or audio device (180) can be alternatively utilized, instead of the hard wire (62). In this arrangement, an optical transmitter (161) would transmit the signal from the sensor (60) and this optical transmitter would send a signal to an optical receiver (162) whereby this optical receiver (162) would provide the information into the signal processor (54). Similarly, a radio frequency device (170) uses a radio frequency transmitter (171) which receives a signal from sensor (60). Transmitter (171) transmits a wireless signal to radio frequency receiver (172), this radio frequency signal being passed on to the signal processor (54), without wires, just like the optical transmitter is transmitted without wires.

Referring again to FIG. 25, alternatively, a wireless connection could be an audio-type such as (180) wherein the sensor (60) feeds a signal into a speaker-type transmitter (181). This speaker-type transmitter (181) sends its signal to a microphone-type receiver (182) on the signal processor (54) to thereby communicate a wireless signal to the signal processor (54). These wireless transmitters (160), (170) or (180) could be used in combination with any of the other components which will give a signal proportional to the speed of the engine.

Although only exemplary embodiments of the invention have been described in detail above, those skilled in the art will readily appreciate that many modifications are possible without materially departing from the novel teachings and advantages of this invention. Accordingly, all such modifications are intended to be included within the scope of this invention as defined in the following claims.