Auxiliary drive system for combines

Claim 2

In a combine having a pair of main drive wheels, a pair of steerable wheels, a hydraulic motor, a variable ratio transmission interconnecting the hydraulic motor and the main drive wheels, and a variable displacement pump for driving the hydraulic motor, a variable torque auxiliary drive system for the sterrable wheels comprising: a pair of auxiliary hydraulic motors operably connected to and for driving the steerable wheels; fluid line means connecting the auxiliary hydraulic motors with the pump in parallel relation with the first-mentioned hydraulic motor and in parallel relation with each other; and pressurecompensated flow control means limiting the maximum flow to each of the auxiliary motors whereby the torque applied to the steerable wheels will be proportional to the torque applied to the main drive wheels and lo otractiff one steerable wheel will not result in loss of power to the main drive wheels.

Claim 3

In a combine for harvesting grain crops having means for gathering and threshing grain, a grain tank for temporay storage of the grain, a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, transmission means interconnecting the main hydraulic motor and the main drive wheels, a variable displacement, reversible delivery, pump, and a first pair of fluid lines interconnecting the two sides of the pump with the two sides of the main motor, an auxiliary drive system for the steerable wheels comprising: a pair of auxiliary reversible hydraulic motors individually connected to the pair of steerable wheels through individual transmission means; second and third pairs of fluid lines interconnecting the two sides of the pair of auxiliary hydraulic motors with the first pair of fluid lines to connect the pair of auxiliary hydraulic motors with the hydraulic pump in parallel with the main hydraulic motor and in parallel with each other; and pressure-compensated flow control valve means interposed in each fluid line of the second and third pairs of fluid lines limiting the maximum fluid flow to each of the auxiliary hydraulic motors whereby the torque applied to the steerable wheels will be proportional to the torque applied to them main drive wheels and ss of traction of either ne or both of the steerble whels will not result in loss4 of power tothe main drive wheels.

Claim 4

In a combine for harvesting grain crops having means for gathering and threshing grain, a grain tank for temporay storage of the grain, a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, transmission means interconnecting the main hydraulic motor and the main drive wheels, a variable displacement, reversible delivery, pump, and a first pair of fluid lines interconnecting the two sides of the pump with the two sides of the main motor, an auxiliary drive system for the steerable wheels comprising: a pair of auxiliary reversible hydraulic motors individually connected to the pair of steerable wheels through individual transmission means; second and third pairs of fluid lines interconnecting the two sides of the pair of auxiliary hydraulic motors with the first pair of fluid lines to connect the pair of auxiliary hydraulic motors with the hydraulic pump in parallel with the main hydraulic motor and in parallel with each other; and pressure-compensated flow control valve means interposed in each fluid line of the second and third pairs of fluid lines limiting the maximum fluid flow to each of the auxiliary hydraulic motors whereby the torque applied to the steerable wheels will be proportional to the torque applied to them main drive wheels and ss of traction of either ne or both of the steerble whels will not result in loss4 of power tothe main drive wheels.

Claim 5

The invention set forth in claim 2 wherein thE flow control valve means limit the maximum fluid flow to the auxiliary hydraulic motors in a direction to drive the auxiliary hydraulic motors forwardly to a value greater than the maximum fluid flow to the auxiliary hydraulic motors in a direction to drive the auxiliary hydraulic motors rearwardly.

Claim 6

An auxiliary drive system for a vehicle having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, variable ratio transmission means interconnecting the main hydraulic motor with the main drive wheels, a variable displacement, reversible delivery, pump, and a pair of fluid lines intercnnecting the two sides of the main motor with the pump, the auxiliary drive system comprising: a pair of reversible auxiliary hydraulic motors individually connected to the pair of steerable wheels, a directional control valve having alternate on and off positions; second and third pairs of fluid lines connecting the two sides of the auxiliary hydraulic motors to one side of the directional control valve in parallel relationship to each other; a fourth pair of fluid lines interconnecting the second side of the directional control valve with the first pair of fluid lines so that the auxiliary hydraulic motors are connected in parallel with the main hydraulic motor when the directional control valve is in the on position; and a pressure-compensated flow control valve means interposed in each of the fluid lines of the second and thirf pairs of fluid lines limiting the maximum flow of uid to each of the axuiliary hydraulic motors; whereby, by manipulation of the directional onrol valve, the auxiliary drive system can be cut in and out at will, the torqye applied to the eerable wheels will be proportional to the torque applied to the main drive wheels when ehe directional control valve is in the on position, loss of traction of eithr one or both of the steerable wheels will not result in loss of power to themai rive wheels, atio of main drive wheel torque to steerable wheel torque can be varied.

Claim 7

An auxiliary drive system for a vehicle having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, variable ratio transmission means interconnecting the main hydraulic motor with the main drive wheels, a variable displacement, reversible delivery, pump, and a pair of fluid lines intercnnecting the two sides of the main motor with the pump, the auxiliary drive system comprising: a pair of reversible auxiliary hydraulic motors individually connected to the pair of steerable wheels, a directional control valve having alternate on and off positions; second and third pairs of fluid lines connecting the two sides of the auxiliary hydraulic motors to one side of the directional control valve in parallel relationship to each other; a fourth pair of fluid lines interconnecting the second side of the directional control valve with the first pair of fluid lines so that the auxiliary hydraulic motors are connected in parallel with the main hydraulic motor when the directional control valve is in the on position; and a pressure-compensated flow control valve means interposed in each of the fluid lines of the second and thirf pairs of fluid lines limiting the maximum flow of uid to each of the axuiliary hydraulic motors; whereby, by manipulation of the directional onrol valve, the auxiliary drive system can be cut in and out at will, the torqye applied to the eerable wheels will be proportional to the torque applied to the main drive wheels when ehe directional control valve is in the on position, loss of traction of eithr one or both of the steerable wheels will not result in loss of power to themai rive wheels, atio of main drive wheel torque to steerable wheel torque can be varied.

Claim 8

The auxiliary drive system set forth in claim 4 wherein the flow control valve means limit the maximum fluid flow to the auxiliary hydraulic motors in a direction to drive the auxiliary hydraulic motors forwardly to a. ue greater than the maximum fluid flow to he axuiliary hydraulic motors in a direction to drive the auxiliary hydraulic motors rearwardly.

Claim 9

The auxiliary drive system set forth in claim 4 wherein the directional control valve interconnects the second and third pair of fluid lines with a fluid reservoir when in the off position to thereby prevent the auxiliary hydraulic motors from braking the vehicle.

Claim 10

In a crop harvester having a pair of forward main drive wheels, a pair of rear steerable wheels, a hydraulic otor, a variable radio transmission interconnecting the hydraulicmo r and the main drive wheels, and a vairable displacement pump or driving the hydraulic motor, a variable torque auxiliary drive system for the rear sterrable wheels comprising: a pair of auxiliary hydraulic motors operatively connected to and for driving the sterrable wheels; fluid line means connecting the auxiliary hydraulic motors with the pump in parallel relation with the first-mentioned hydraulic motor and in parallel relation with each other, and pressure compensated flow control m-ans limiting the maximum flow to each ofthe auxiliary motors whereby the torque applied to the main drive wheels and loss of traction to one of the steerable wheels will not result in loss of power tothemai drive wheels.

Claim 11

In a crop harvester having a pair of forward main drive wheels, a pair of rear steerable wheels, a hydraulic otor, a variable radio transmission interconnecting the hydraulicmo r and the main drive wheels, and a vairable displacement pump or driving the hydraulic motor, a variable torque auxiliary drive system for the rear sterrable wheels comprising: a pair of auxiliary hydraulic motors operatively connected to and for driving the sterrable wheels; fluid line means connecting the auxiliary hydraulic motors with the pump in parallel relation with the first-mentioned hydraulic motor and in parallel relation with each other, and pressure compensated flow control m-ans limiting the maximum flow to each ofthe auxiliary motors whereby the torque applied to the main drive wheels and loss of traction to one of the steerable wheels will not result in loss of power tothemai drive wheels.

Claim 12

In a crop harvester having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, transmission means interconnecting the main hydraulic motor and the main drive wheels, a variable displacement, reversible delivery, pump, and a first pair of fluid lines interconnecting the two sides of the pump with the two sides of the main motor, an auxiliary drive system for the steerable wheels comprising: a pair of auxiliary reversibLe hydraulic motors individually connected to the pair of steerable wheels through individual transmission means; second and third pairs of fluid lines interconnecting the two sides of the pair of auxiliary hydraulic motors with the first pair of fluid lines to connect the pair of auxiliary hydraulic motors with the hydraulic pump in parallel with the main hydraulic motor and in parallel with each other; and pressure compensated flow control valve means interposed in each fluid line of the second and third pairs of fluid lines limiting the maximum fluid flow to each of the auxiliary hydraulic motors whereby the torque applied to the steerable wheels will be proportional to the torque applied to the main drive wheels and loss of traction to either one or both of the steerable wheels will not result in loss of power to the main drive wheels.

Claim 13

In a crop harvester having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, transmission means interconnecting the main hydraulic motor and the main drive wheels, a variable displacement, reversible delivery, pump, and a first pair of fluid lines interconnecting the two sides of the pump with the two sides of the main motor, an auxiliary drive system for the steerable wheels comprising: a pair of auxiliary reversibLe hydraulic motors individually connected to the pair of steerable wheels through individual transmission means; second and third pairs of fluid lines interconnecting the two sides of the pair of auxiliary hydraulic motors with the first pair of fluid lines to connect the pair of auxiliary hydraulic motors with the hydraulic pump in parallel with the main hydraulic motor and in parallel with each other; and pressure compensated flow control valve means interposed in each fluid line of the second and third pairs of fluid lines limiting the maximum fluid flow to each of the auxiliary hydraulic motors whereby the torque applied to the steerable wheels will be proportional to the torque applied to the main drive wheels and loss of traction to either one or both of the steerable wheels will not result in loss of power to the main drive wheels.

Claim 14

In a crop harvester having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, a variable ratio transmission interconnecting the main hydraulic motor and the main drive wheels, and a variable displacement, reversible delivery, pump for driving the hydraulic motor, a variable torque auxiliary drive system for the rear steerable wheels comprising: a pair of auxiliary reversible hydraulic motors operatively connected to and for driving the steerable wheels; directional flow control valve means having alternate on and off positions; and fluid line means interconnecting one side of the valve means with the auxiliary hydraulic motors and a second side of the valve means with the pump in parallel relation with the main hydraulic motor so that when the valve means is in the on position the torque applied to the steerable wheels will be proportional to the torque applied to the main drive wheels, and, by changing the ratio of the variable ratio transmission, the ratio of main drive wheel torque to steerable wheel torque can be varied. in In the manufacture of sheets of corrugated paperboard material, it is necessary to sever sheets of a desired length from a continuous web of corrugated material manufactured by a corrugating machine. The sheets are most commonly cut by counter-rotating knives mounted on cylinders which shear the sheets at the desired length. In order to achieve a clean cut, it is necessary that the peripheral speed of the knives be equivalent to the lineal speed of the corrugated material at the time the cut is made. Thus, if the lineal speed of the corrugated web is kept constant, which is normally the situation, the rotational speed of the knife cylinders must be adjusted if a sheet of a different length is desired. The present state of the art is illustrated by rotary cutoff mechanisms such as the Model (JR) manufactured by the Langston Corp., 6th and Jefferson Sts., Camden, N.J. 08104. This is an involved mechanical linkage system which will allow the cylinders to rotate at a slower rate during noncutting periods than during the cutting period, and will allow adjustment of the overall speed of rotation of the knife cylinders to compensate for different the switch 56 being on the lobe of the cam 58 in which position, the logic and control unit 54 is off. This insures that the knife cylinder 10 is traveling at the proper speed at the time the cut is made. After this period of cutting, the roller switch 56 is turned off by virtue of dropping off of the lobe of the cam 58, thereby energizing the logic and control unit 54, which in turn energizes the electric motor 46 and begins counting pulses from the pulse transmitter

Claim 15

In a crop harvester having a pair of main drive wheels, a pair of steerable wheels, a main reversible hydraulic motor, a variable ratio transmission interconnecting the main hydraulic motor and the main drive wheels, and a variable displacement, reversible delivery, pump for driving the hydraulic motor, a variable torque auxiliary drive system for the rear steerable wheels comprising: a pair of auxiliary reversible hydraulic motors operatively connected to and for driving the steerable wheels; directional flow control valve means having alternate on and off positions; and fluid line means interconnecting one side of the valve means with the auxiliary hydraulic motors and a second side of the valve means with the pump in parallel relation with the main hydraulic motor so that when the valve means is in the on position the torque applied to the steerable wheels will be proportional to the torque applied to the main drive wheels, and, by changing the ratio of the variable ratio transmission, the ratio of main drive wheel torque to steerable wheel torque can be varied. in In the manufacture of sheets of corrugated paperboard material, it is necessary to sever sheets of a desired length from a continuous web of corrugated material manufactured by a corrugating machine. The sheets are most commonly cut by counter-rotating knives mounted on cylinders which shear the sheets at the desired length. In order to achieve a clean cut, it is necessary that the peripheral speed of the knives be equivalent to the lineal speed of the corrugated material at the time the cut is made. Thus, if the lineal speed of the corrugated web is kept constant, which is normally the situation, the rotational speed of the knife cylinders must be adjusted if a sheet of a different length is desired. The present state of the art is illustrated by rotary cutoff mechanisms such as the Model (JR) manufactured by the Langston Corp., 6th and Jefferson Sts., Camden, N.J. 08104. This is an involved mechanical linkage system which will allow the cylinders to rotate at a slower rate during noncutting periods than during the cutting period, and will allow adjustment of the overall speed of rotation of the knife cylinders to compensate for different the switch 56 being on the lobe of the cam 58 in which position, the logic and control unit 54 is off. This insures that the knife cylinder 10 is traveling at the proper speed at the time the cut is made. After this period of cutting, the roller switch 56 is turned off by virtue of dropping off of the lobe of the cam 58, thereby energizing the logic and control unit 54, which in turn energizes the electric motor 46 and begins counting pulses from the pulse transmitter

Claim 16

It is important to realize that the cessation of pulse counting and consequently the cessation of the rotation of the electric motor 46 will not necessarily correspond to any particular position on the profile of the cam 58. When the switch 56 once again rides up the lobe of the cam 58, it will turn off and reset the logic and control unit 54. The point of cessation of counting will occur when the input from the motor 46 has retarded tha angular displacement of the knife cylinder 10 by the amount of web 65 length desired in excess of 36 inches. At the time of a pulse transmitter for sensing and transmitting the pulses generated by said pulse generator; means connected to said pulse transmitter and said drive means for limiting the rotation of said drive means to a pre-selected number of pulse counts; and

Claim 17

It is important to realize that the cessation of pulse counting and consequently the cessation of the rotation of the electric motor 46 will not necessarily correspond to any particular position on the profile of the cam 58. When the switch 56 once again rides up the lobe of the cam 58, it will turn off and reset the logic and control unit 54. The point of cessation of counting will occur when the input from the motor 46 has retarded tha angular displacement of the knife cylinder 10 by the amount of web 65 length desired in excess of 36 inches. At the time of a pulse transmitter for sensing and transmitting the pulses generated by said pulse generator; means connected to said pulse transmitter and said drive means for limiting the rotation of said drive means to a pre-selected number of pulse counts; and