Patent Description:
Patent Literature <NUM> discloses a work vehicle (tractor) including a hydrostatic, continuously variable transmission device (continuously variable transmission section), a planetary transmission device (compound planetary power transmission section, speed change and output section), a forward/backward travel switching device, a speed change operation tool (shift lever), and a forward/backward travel switching tool (forward-reverse lever). The continuously variable transmission device receives and varies motive power from the engine and outputs the varied motive power. The planetary transmission device composites motive power from the engine and motive power from the continuously variable transmission device and outputs the composite motive power. The planetary transmission device also varies the composite motive power in response to the continuously variable transmission device being varied. The forward/backward travel switching device is switchable between a forward-travel power transmission state and a backward-travel power transmission state. In the forward-travel power transmission state, the forward/backward travel switching device switches the composite motive power from the planetary transmission device into forward-travel motive power and outputs the forward-travel motive power to travel devices (front wheels, rear wheels). In the backward-travel power transmission state, the forward/backward travel switching device switches the composite motive power from the planetary transmission device into backward-travel motive power and outputs the backward-travel motive power to the travel devices. The speed change operation tool is for use to vary the continuously variable transmission device to change the vehicle speed. The forward/backward travel switching tool is for use to switch the forward/backward travel switching device.

The work vehicle (tractor) configured as above has a vehicle speed determined on the basis of the rotation speed (number of revolutions) of the composite motive power. The rotation speed determined the ratio (gear ratio) between the number of revolutions of the engine and the number of revolutions of the output shaft. The rotation speed of the composite motive power is determined on the basis of the speed range of the planetary transmission device and motive power (swash plate angle) outputted from the continuously variable transmission device. The speed range is determined through an operation of clutches of the planetary transmission device. The continuously variable transmission device has a swash plate that is tilted across a neutral position to and from a state (-MAX) in which the swash plate is maximally tilted to one side and a state (+MAX) in which the swash plate is maximally tilted to the other side. The continuously variable transmission device, in other words, alternates between normal rotation and reverse rotation. Each change in the speed range switches the direction in which the swash plate is tilted and thereby switches between normal rotation and reverse rotation. This gradually changes the rotation speed of the composite motive power.

The continuously variable transmission device has a swash plate angle controlled with use of operating oil supplied from a hydraulic cylinder controlled with use of two electromagnetic valves, which are in turn controlled on the basis of the electric current value of a control signal The work vehicle may be configured such that one of the electromagnetic valves controls the swash plate angle on the normal rotation side of the neutral position through the hydraulic cylinder, whereas the other electromagnetic valve controls the swash plate angle on the reverse rotation side of the neutral position through the hydraulic cylinder. The electromagnetic valves are, in this case, switched at the neutral position of the swash plate.

Patent Literature <NUM> discloses an apparatus for controlling a continuously variable transmission device for work machines.

While the electromagnetic valves receive electric current when the swash plate of the continuously variable transmission device starts to tilt at the switch of the electromagnetic valves, the electric current has a value (that is, a rising electric current value) that may vary according to each electromagnetic valve due to, for example, a load on an axle (that is, the input and output shafts of the continuously variable transmission device), the temperature of operating oil, or the number of revolutions of the engine. This may lead to the gear ratio being controlled inappropriately near the neutral position of the swash plate.

For instance, the gear ratio may not reach its target value even in response to the electromagnetic valves being switched and the electric current value for controlling the electromagnetic valves being brought to a predetermined rising electric current value. The gear ratio may reach its target value before the electric current value reaches the rising electric current value. Further, controlling the electromagnetic valves may be followed by the start of the tilt of the swash plate with a problematic delay in-between due to the configuration of the hydraulic circuit.

The present invention has an object of switching electromagnetic valves in a timely manner.

In order to attain the above object, an electromagnetic valve control device according to an embodiment of the present invention includes: an electromagnetic valve control device for a transmission configured to vary motive power from a drive section with use of a gear transmission and a hydrostatic, continuously variable transmission device and output the varied motive power, the electromagnetic valve control device being configured to control, based on a target gear ratio and with use of a value of electric current for the continuously variable transmission device, a first electromagnetic valve configured to control a pump swash plate on a normal rotation side of a neutral position and a second electromagnetic valve configured to control the pump swash plate on a reverse rotation side of the neutral position, a current gear ratio obtainer configured to obtain a current gear ratio as a ratio of the number of output revolutions of the drive section and the number of output revolutions of the transmission; a current electric current value obtainer configured to obtain a current electric current value as the value of the electric current to be inputted to the first electromagnetic valve or the second electromagnetic valve; and a switching controller configured to, based on the current electric current value and a gear ratio difference as a difference between the target gear ratio and the current gear ratio, perform electromagnetic valve switching control of switching between use of the first electromagnetic valve to control the pump swash plate and use of the second electromagnetic valve to control the pump swash plate.

A work vehicle according to an embodiment of the present invention includes: a drive section; a hydrostatic, continuously variable transmission device configured to vary motive power from the drive section and output the varied motive power; a gear transmission configured to composite motive power from the drive section and motive power from the hydrostatic, continuously variable transmission device, vary the composite motive power, and output the varied composite motive power; a first electromagnetic valve configured to control a pump swash plate of the continuously variable transmission device on a normal rotation side of a neutral position; a second electromagnetic valve configured to control the pump swash plate on a reverse rotation side of the neutral position; and an electromagnetic valve control device of the embodiment of the invention described above.

Each embodiment above is capable of performing electromagnetic valve switching control in accordance with how the pump swash plate is controlled with use of the first and second electromagnetic valves, as detected on the basis of the gear ratio difference. This allows the electromagnetic valves to be switched in a timely manner.

The electromagnetic valve control device may be further configured such that the switching controller performs the electromagnetic valve switching control in response to (i) the current electric current value being not larger than a predetermined electric current threshold value and simultaneously (ii) the gear ratio difference being not smaller than a predetermined gear ratio difference threshold value.

The above configuration allows the switching controller to switch the electromagnetic valves more accurately and in a timelier manner, on the basis of the current electric current value and the gear ratio difference.

The electromagnetic valve control device may further include: a storage configured to store information on a rising electric current value as a value of the electric current at which value the pump swash plate starts to tilt from the neutral position, wherein the switching controller subtracts the rising electric current value from the current electric current value to give a first difference and performs the electromagnetic valve switching control in response to (i) the first difference being not larger than a predetermined first electric current threshold value as the electric current threshold value and simultaneously (ii) the gear ratio difference being not smaller than a predetermined first switching target deviation as the gear ratio difference threshold value.

The above configuration allows the switching controller to, on the basis of a rising electric current value that varies due to, for example, a load on an axle, the temperature of operating oil, and the number of revolutions of the engine, switch the electromagnetic valves early in response to the gear ratio difference being large even if the current electric current value has not reached the rising electric current value. This allows the electromagnetic valves to be switched in a timely manner.

The electromagnetic valve control device may be further configured such that the switching controller performs the electromagnetic valve switching control in response to (i) the current electric current value being not larger than the rising electric current value and simultaneously (ii) the gear ratio difference being not smaller than a predetermined second switching target deviation as the gear ratio difference threshold value, the second switching target deviation being smaller than the first switching target deviation.

The above configuration allows the switching controller to switch the electromagnetic valves in response to the current gear ratio being apart from the target gear ratio by not smaller than a predetermined value even if the current electric current value has not reached the rising electric current value. This allows the electromagnetic valves to be switched appropriately.

The electromagnetic valve control device may be further configured such that the switching controller subtracts the current electric current value from the rising electric current value to give a second difference and performs the electromagnetic valve switching control in response to (i) the second difference being not larger than a predetermined second electric current threshold value and simultaneously (ii) the gear ratio difference being not smaller than a predetermined third switching target deviation as the gear ratio difference threshold value, the third switching target deviation being smaller than the second switching target deviation.

The above configuration allows the switching controller to perform electromagnetic valve switching control before the current electric current value reaches the rising electric current value, and thereby allows the switching controller to switch the electromagnetic valves in a timely manner and bring the gear ratio to an appropriate value early.

The electromagnetic valve control device may be further configured such that the switching controller retains said value of electric current for controlling the first electromagnetic valve and the second electromagnetic valve in response to (i) the second difference being not larger than the second electric current threshold value and simultaneously (ii) the gear ratio difference being smaller than the third switching target deviation.

The above configuration allows the switching controller to retain the current electric current value and then resume electromagnetic valve switching control in response to the gear ratio difference increasing by not smaller than a predetermined value. This allows the electromagnetic valves to be switched in a timely manner.

The electromagnetic valve control device may be further configured such that the switching controller avoids performing the electromagnetic valve switching control over a predetermined time period after once performing the electromagnetic valve switching control.

The switch of the electromagnetic valves may be followed by input of a control signal (or electric current value) into the electromagnetic valves with a time lag in-between or by the start of the tilt of the swash plate with a time lag in-between. Further, switching the electromagnetic valves repeatedly at short intervals may lead to unstable operation of the continuously variable transmission device. The above configuration prevents the electromagnetic valves from being switched at short intervals. This ensures appropriate input of a control signal (or electric current value), appropriate tilt of the swash plate, and stable operation of the continuously variable transmission device.

The description below deals with a tractor as an example of the work vehicle of the present invention with reference to drawings. The embodiment described below is of a tractor including a body. <FIG> shows arrow F to indicate the forward side of the body, arrow B to indicate the backward side of the body, arrow U to indicate the upward side of the body, and arrow D to indicate the downward side of the body. The front side of <FIG> corresponds to the left side of the body, whereas the back side of <FIG> corresponds to the right side of the body.

As illustrated in <FIG>, the tractor includes a pair of left and right turnable and drivable front wheels <NUM> ("travel device"), a pair of left and right drivable rear wheels <NUM> ("travel device"), and a body <NUM> supported by the front and rear wheels <NUM> and <NUM>. The tractor includes a motive section <NUM> including an engine <NUM> ("drive section") at a front portion of the body <NUM>. The tractor includes a driver section <NUM> and a link mechanism <NUM> at a back portion of the body <NUM>. The driver section <NUM> is configured to accommodate an operator for driving the tractor. The link mechanism <NUM> is configured to couple an implement such as a rotary tiller device to the tractor in such a manner that the implement is capable of being lifted and lowered. The driver section <NUM> includes a driver's seat <NUM>, a steering wheel <NUM> for use to turn the front wheels <NUM>, and a cabin <NUM> defining a driver space. The body <NUM> includes a body frame <NUM> including an engine <NUM>, a transmission case <NUM>, and front-wheel support frame members <NUM>. The transmission case <NUM> has a front portion coupled to a back portion of the engine <NUM>. The front-wheel support frame members <NUM> are coupled to a lower portion of the engine <NUM>. The tractor includes a power takeoff shaft <NUM> at a back portion of the transmission case <NUM>. The power takeoff shaft <NUM> is configured to take off motive power from the engine <NUM> and transmits the motive power to the implement coupled with use of the link mechanism <NUM>.

As illustrated in <FIG>, the tractor includes a power transmission device <NUM> for travel, a rear-wheel differential mechanism <NUM>, and a front-wheel differential mechanism <NUM>. The power transmission device <NUM> is configured to transmit motive power from the engine <NUM> to the front and rear wheels <NUM> and <NUM>. The power transmission device <NUM> includes a transmission <NUM> contained in the transmission case <NUM> and configured to vary motive power from the engine <NUM> and transmit the varied motive power to the rear-wheel differential mechanism <NUM> and the front-wheel differential mechanism <NUM>.

As illustrated in <FIG>, the transmission <NUM> includes an input shaft <NUM>, a main transmission section <NUM>, a forward/backward travel switching device <NUM>, a gear mechanism <NUM>, and a front-wheel power transmission section <NUM>. The input shaft <NUM> is disposed at a front portion of the transmission case <NUM> and configured to receive motive power from the output shaft 4a of the engine <NUM>. The main transmission section <NUM> is configured to receive motive power from the input shaft <NUM>, vary the motive power, and output the varied motive power. The forward/backward travel switching device <NUM> is configured to receive the motive power outputted from the main transmission section <NUM> and switch the rotation direction of the motive power between a forward-travel direction and a backward-travel direction. The gear mechanism <NUM> is configured to transmit the output from the forward/backward travel switching device <NUM> to the input shaft 16a of the rear-wheel differential mechanism <NUM>. The front-wheel power transmission section <NUM> is configured to receive motive power outputted from the forward/backward travel switching device <NUM>, vary the motive power, and output the varied motive power to the front-wheel differential mechanism <NUM>.

As illustrated in <FIG>, the main transmission section <NUM> includes a continuously variable transmission device <NUM> and a planetary transmission device <NUM> ("gear transmission"). The continuously variable transmission device <NUM> is configured to receive motive power from the input shaft <NUM>. The planetary transmission device <NUM> is configured to receive motive power from the input shaft <NUM> and the output from the continuously variable transmission device <NUM>.

The continuously variable transmission device <NUM> is of a hydraulic type (that is, a hydrostatic transmission or HST), and includes a hydraulic pump P with a variable capacity and a hydraulic motor M. The continuously variable transmission device <NUM> is configured to vary motive power from the input shaft <NUM> into normal-direction motive power or reverse-direction motive power in accordance with the swash plate angle of the hydraulic pump P. The continuously variable transmission device <NUM> is also configured to continuously vary the rotation speed (that is, the number of revolutions) of the normal-direction motive power or reverse-direction motive power in accordance with the swash plate angle and output the resulting motive power from its motor shaft 28b. As illustrated in <FIG>, the continuously variable transmission device <NUM> includes a pump shaft 28a coupled. to the hydraulic pump P as well as to the input shaft <NUM> with a rotary shaft <NUM> and a first gear mechanism <NUM> in-between. The input shaft <NUM> is coupled to a front end portion of the rotary shaft <NUM>, which has a back end portion coupled to the first gear mechanism <NUM>, which is then coupled to the pump shaft 28a. The hydraulic motor M is configured to output to the motor shaft 28b motive power corresponding to pressure oil supplied from the hydraulic pump P.

As illustrated in <FIG>, the planetary transmission device <NUM> includes a planetary transmission unit 31A and an output section 31B. The planetary transmission unit 31A is configured to receive motive power from the input shaft <NUM> and the output from the continuously variable transmission device <NUM>. The output section 31B is configured to receive motive power from the planetary transmission unit 31A and output the motive power in one of four speed ranges. As illustrated in <FIG> and <FIG>, the planetary transmission unit 31A includes a first planetary transmission section <NUM> and a second planetary transmission section <NUM> backward of the first planetary transmission section <NUM>. The first planetary transmission section <NUM> includes (i) a first sun gear 32a, (ii) a first planetary gear 32b meshing with the first sun gear 32a, and (iii) a first ring gear 32c including inner teeth meshing with the first planetary gear 32b. The second planetary transmission section <NUM> includes (i) a second sun gear 33a, (ii) a second planetary gear 33b meshing with the second sun gear 33a, (iii) a second ring gear 33c including inner teeth meshing with the second planetary gear 33b, and (iv) a second carrier 33d holding the second planetary gear 33b.

As illustrated in <FIG>, the main transmission section <NUM> includes a second gear mechanism <NUM> extending from the first sun gear 32a to the motor shaft 28b of the continuously variable transmission device <NUM> and configured to transmit the output from the continuously variable transmission device <NUM> to the first sun gear 32a. The main transmission section <NUM> includes a third gear mechanism <NUM> extending from the first ring gear 32c to the input shaft <NUM> and configured to transmit motive power from the input shaft <NUM> to the first ring gear 32c. As illustrated in <FIG> and <FIG>, the first planetary transmission section <NUM> includes an interlocking gear 32d meshing with the first planetary gear 32b and coupled in an interlocked manner to the second planetary gear 33b with use of a coupler 33e. The first and second planetary transmission sections <NUM> and <NUM> constitute a so-called compound planetary transmission section.

As illustrated in <FIG> and <FIG>, the output section 31B includes a first input shaft 34a, a second input shaft 34b, and a third input shaft 34c in a triple-shaft structure as well as an output shaft <NUM> parallel to, for example, the first input shaft 34a. The first input shaft 34a is coupled to the second ring gear 33c. The second input shaft 34b is coupled to the second carrier 33d. The third input shaft 34c is coupled to the second sun gear 33a. The first input shaft 34a is coupled to a first range gear mechanism 36a. The main transmission section <NUM> includes a first clutch CL1 extending from the first range gear mechanism 36a to the output shaft <NUM>. The third input shaft 34c is coupled to a second range gear mechanism 36b. The main transmission section <NUM> includes a second clutch CL2 extending from the second range gear mechanism 36b to the output shaft <NUM>. The second input shaft 34b is coupled to a third range gear mechanism 36c. The main transmission section <NUM> includes a third clutch CL3 extending from the third range gear mechanism 36c to the output shaft <NUM>. The third input shaft 34c is coupled to a fourth range gear mechanism 36d. The main transmission section <NUM> includes a fourth clutch CL4 extending from the fourth range gear mechanism 36d to the output shaft <NUM>.

The main transmission section <NUM> is configured as follows: The motive power output from the engine <NUM> transmits through the input shaft <NUM>, the rotary shaft <NUM>, and the first gear mechanism <NUM> to the hydraulic pump P of the continuously variable transmission device <NUM>. The continuously variable transmission device <NUM> outputs the motive power from its motor shaft 28b as normal-direction motive power or reverse-direction motive power. The continuously variable transmission device <NUM> continuously varies the rotation speed (that is, the number of revolutions) of the normal-direction motive power or reverse-direction motive power. The continuously variable transmission device <NUM> transmits the motive power through the second gear mechanism <NUM> to the first sun gear 32a of the first planetary transmission section <NUM>. The engine <NUM> transmits motive power through the input shaft <NUM> and the third gear mechanism <NUM> to the first ring gear 32c of the first planetary transmission section <NUM>. The first and second planetary transmission sections <NUM> and <NUM> composite (i) the motive power outputted from the continuously variable transmission device <NUM> to the first ring gear 32c and (ii) the motive power outputted from the engine <NUM> to the first ring gear 32c. The second planetary transmission section <NUM> transmits the composite motive power to the output section 31B, which then outputs the composite motive power from its output shaft <NUM>.

The main transmission section <NUM> is configured as follows: With the first clutch CL1 engaged, the composite motive power as composited by the planetary transmission unit 31A is varied by the first range gear mechanism 36a and first clutch CL1 of the output section 31B into motive power in the first-gear range. The motive power in the first-gear range is transmitted from the second ring gear 33c to the first input shaft 34a of the output section 31B. In this state, the motive power in the first-gear range is continuously varied through the operation of the continuously variable transmission device <NUM>, and is outputted from the output shaft <NUM>.

With the second clutch CL2 engaged, the composite motive power as composited by the planetary transmission unit 31A is varied by the second range gear mechanism 36b and second of the output section 31B into motive power in the second-gear range. The motive power in the second-gear range is transmitted from the second sun gear 33a to the third input shaft 34c of the output section 31B. During this operation, the motive power in the second-gear range is continuously varied through the variation of the continuously variable transmission device <NUM>, and is outputted from the output shaft <NUM>.

With the third clutch CL3 engaged, the composite motive power as composited by the planetary transmission unit 31A is varied by the third range gear mechanism 36c and third clutch CL3 of the output section 31B into motive power in the third-gear range. The motive power in the third-gear range is transmitted from the second carrier 33d to the second input shaft 34b of the output section 31B. During this operation, the motive power in the third-gear range is continuously varied through the variation of the continuously variable transmission device <NUM>, and is outputted from the output shaft <NUM>.

With the fourth clutch CL4 engaged, the composite motive power as composited by the planetary transmission unit 31A is varied by the fourth range gear mechanism 36d and fourth clutch CL4 of the output section 31B into motive power in the fourth-gear range. The motive power in the fourth-gear range is transmitted from the second sun gear 33a to the third input shaft 34c of the output section 31B. During this operation, the motive power in the fourth-gear range is continuously varied through the variation of the continuously variable transmission device <NUM>, and is outputted from the output shaft <NUM>.

As illustrated in <FIG>, the forward/backward travel switching device <NUM> includes an input shaft 23a, an output shaft 23b, a forward-travel gear interlocking mechanism 23c, and a backward-travel gear interlocking mechanism 23d. The input shaft 23a is coupled to the output shaft <NUM> of the planetary transmission device <NUM>. The output shaft 23b is parallel to the input shaft 23a. The input shaft 23a is provided with a forward clutch CLF and a reverse clutch CLR. The forward-travel gear interlocking mechanism 23c extends from the forward clutch CLF to the output shaft 23b. The backward-travel gear interlocking mechanism 23d extends from the reverse clutch CLR to the output shaft 23b.

Engaging the forward clutch CLF couples the input shaft 23a to the forward-travel gear interlocking mechanism 23c. This achieves a forward-travel power transmission state, in which motive power from the input shaft 23a is transmitted through the forward-travel gear interlocking mechanism 23c to the output shaft 23b. Engaging the reverse clutch CLR couples the input shaft 23a to the backward-travel gear interlocking mechanism 23d. This achieves a backward-travel power transmission state, in which motive power from the input shaft 23a is transmitted through the backward-travel gear interlocking mechanism 23d to the output shaft 23b.

The forward/backward travel switching device <NUM> receives the output from the planetary transmission device <NUM> at the input shaft 23a. Engaging the forward clutch CLF causes motive power from the input shaft 23a to be converted by the forward clutch CLF and the forward-travel gear interlocking mechanism 23c into forward-travel motive power to be transmitted to the output shaft 23b. Engaging the reverse clutch CLR causes motive power from the input shaft 23a to be converted by the reverse clutch CLR and the backward-travel gear interlocking mechanism 23d into backward-travel motive power to be transmitted to the output shaft 23b. The output shaft 23b transmits the forward-travel motive power and backward-travel motive power through the gear mechanism <NUM> to the rear-wheel differential mechanism <NUM> and the front-wheel power transmission section <NUM>.

The rear-wheel differential mechanism <NUM> receives the forward-travel motive power or backward-travel motive power from the forward/backward travel switching device <NUM>, and transmits the motive power from a pair of left and right output shafts 16b to the respective rear wheels <NUM>. The left output shaft 16b transmits its motive power through a planetary deceleration mechanism <NUM> to the left rear wheel <NUM>. The left output shaft 16b is provided with a steering brake <NUM>. The right output shaft 16b transmits its motive power to the right rear wheel <NUM> in a system including a planetary deceleration mechanism <NUM> and a steering brake <NUM> (not illustrated in the drawing) similarly to the power transmission system for the left rear wheel <NUM>. The body <NUM> (see <FIG>) is easily turnable in accordance with how each steering brake <NUM> is operated.

As illustrated in <FIG>, the front-wheel power transmission section <NUM> includes an input shaft 25a and an output shaft 25b. The input shaft 25a is coupled to the output shaft 24a of the gear mechanism <NUM>. The output shaft 25b is parallel to the input shaft 25a. The input shaft 25a is provided with a constant-rate clutch CLT and a rate-increasing clutch CLH backward of the constant-rate clutch CLT. The front-wheel power transmission section <NUM> includes a constant-rate gear mechanism <NUM> extending from the constant-rate clutch CLT to the output shaft 25b and a rate-increasing gear mechanism <NUM> extending from the rate-increasing clutch CLH to the output shaft 25b. The output shaft 24a of the gear mechanism <NUM> is provided with a parking brake <NUM>.

The front-wheel power transmission section <NUM> is configured as follows: Engaging the constant-rate clutch CLT causes motive power from the input shaft 25a to be transmitted through the constant-rate clutch CLT and the constant-rate gear mechanism <NUM> to the output shaft 25b. The constant-rate gear mechanism <NUM> achieves a constant-rate power transmission state, in which the output shaft 25b outputs motive power for driving the front wheels <NUM> such that the front wheels <NUM> have a circumferential speed equal to that of the rear wheels <NUM>. Engaging the rate-increasing clutch CLH causes motive power from the input shaft 25a to be transmitted through the rate-increasing clutch CLH and the rate-increasing gear mechanism <NUM> to the output shaft 25b. The rate-increasing gear mechanism <NUM> achieves a front-wheel rate-increasing power transmission state, in which the output shaft 25b outputs motive power for driving the front wheels <NUM> such that the front wheels <NUM> have a circumferential speed higher than that of the rear wheels <NUM>. The output from the output shaft 25b is received by the front-wheel differential mechanism <NUM> through a rotary shaft <NUM> coupling the output shaft 25b to the input shaft 17a of the front-wheel differential mechanism <NUM>.

The body <NUM> (see <FIG>) is configured as follows: Engaging the constant-rate clutch CLT leads to a four-wheel drive mode in which the front and rear wheels <NUM> and <NUM> are driven such that the front wheels <NUM> have an average circumferential speed equal to that of the rear wheels <NUM>. Engaging the rate-increasing clutch CLH leads to a four-wheel drive mode in which the front and rear wheels <NUM> and <NUM> are driven such that the front wheels <NUM> have an average circumferential speed higher than that of the rear wheels <NUM>. Engaging the rate-increasing clutch CLH allows the body <NUM> to turn with a radius smaller than when the constant-rate clutch CLT is engaged.

The continuously variable transmission device <NUM> is controlled by the hydraulic circuit illustrated in <FIG> as an example. The hydraulic circuit includes a hydraulic cylinder <NUM>, a speed change valve unit <NUM> including electromagnetically operated valves, and a hydraulic pump <NUM>. The continuously variable transmission device <NUM> is controlled on the basis of a change ("tilt") in the angle ("swash plate angle") of a swash plate <NUM> ("pump swash plate") of the hydraulic pump P, and outputs from the hydraulic motor M motive power corresponding to the swash plate angle of the hydraulic pump P. The swash plate <NUM> is controlled on the basis of the amount of operating oil supplied from the hydraulic pump <NUM> through the hydraulic cylinder <NUM> and the pressure of the operating oil ("operating oil pressure"). The operating oil supplied (or discharged) from the hydraulic cylinder <NUM> is controlled by the speed change valve unit <NUM>.

As illustrated in <FIG>, the hydraulic cylinder <NUM> is coupled to the swash plate <NUM>. The hydraulic cylinder <NUM> includes two oil chambers 50A and 50B. The speed change valve unit <NUM> is connected to the hydraulic cylinder <NUM> through an operating oil path <NUM>, and controls the hydraulic cylinder <NUM> to cause the hydraulic cylinder <NUM> to discharge operating oil to the hydraulic pump P. The hydraulic pump <NUM> is connected to the speed change valve unit <NUM> through a supply oil path <NUM>. The hydraulic pump P is connected to the hydraulic motor M through a drive oil path <NUM> connected to an emergency relief valve <NUM>.

The hydraulic circuit is configured such that the speed change valve unit <NUM> is switchable to cause operating oil from the hydraulic pump <NUM> to be supplied from either of the two oil chambers of the hydraulic cylinder <NUM>. The speed change valve unit <NUM> includes a first electromagnetic valve 52A and a second electromagnetic valve 52B. The first electromagnetic valve 52A is configured to cause operating oil to be discharged from the oil chamber 50A to the normal rotation side of the neutral position. The second electromagnetic valve 52B is configured to cause operating oil to be discharged from the oil chamber <NUM> B to the reverse rotation side of the neutral position. As described above, the first and second electromagnetic valves 52A and 52B are each switched across the neutral position of the swash plate <NUM> (that is, the neutral state of the continuously variable transmission device <NUM>) so that the swash plate <NUM> is tilted to an inclination angle corresponding to the respective positions of the first and second electromagnetic valves 52A and 52B as operated, thereby operating the continuously variable transmission device <NUM>.

With reference to <FIG> and <FIG>, the description below deals with how the main transmission section <NUM> is configured to change the vehicle speed. <FIG> shows a vertical axis indicative of the calculated gear ratio G ("current gear ratio") and the rotation speed V of the input shaft 16a (which corresponds to the vehicle speed). The calculated gear ratio G refers to the ratio of the number of revolutions of the input shaft 16a to the number of revolutions of the input shaft <NUM>. <FIG> shows a horizontal axis indicative of how the continuously variable transmission device <NUM> is varied. The symbol "N" indicates the neutral state. The symbol "-MAX" indicates that the continuously variable transmission device <NUM> has been varied to output reverse-direction motive power for the maximum speed (that is, the largest swash plate angle for the reverse rotation). The symbol "+MAX" indicates that the continuously variable transmission device <NUM> has been varied to output normal-direction motive power for the maximum speed (that is, the largest swash plate angle for the normal rotation). The symbols "G1", "G2", "G3", and "G4" refer to preset gear ratios.

Varying the continuously variable transmission device <NUM> from -MAX toward +MAX with the first clutch CL1 engaged increases the rotation speed V in the first-gear range continuously from zero speed. Within the first-gear range, the calculated gear ratio G is C1N with the continuously variable transmission device <NUM> in the neutral state. In response to the calculated gear ratio G reaching G1, speed change control means <NUM> disengages the first clutch CL1 and engages the second clutch CL2. Varying the continuously variable transmission device <NUM> from +MAX toward -MAX with the second clutch CL2 engaged increases the rotation speed V in the second-gear range continuously. Within the second-gear range, the calculated gear ratio G is C2N with the continuously variable transmission device <NUM> in the neutral state. In response to the calculated gear ratio G reaching G2, the speed change control means <NUM> disengages the second clutch CL2 and engages the third clutch CL3. Varying the continuously variable transmission device <NUM> from -MAX toward +MAX with the third clutch CL3 engaged increases the rotation speed V in the third-gear range continuously. Within the third-gear range, the calculated gear ratio G is C3N with the continuously variable transmission device <NUM> in the neutral state. In response to the calculated gear ratio G reaching G3, the speed change control means <NUM> disengages the third clutch CL3 and engages the fourth clutch CL4. Varying the continuously variable transmission device <NUM> from +MAX toward -MAX with the fourth clutch CL4 engaged increases the rotation speed V in the fourth-gear range continuously. Within the fourth-gear range, the calculated gear ratio G is C4N with the continuously variable transmission device <NUM> in the neutral state.

With reference to <FIG>, <FIG>, and <FIG>, the description below deals with how speed change is controlled.

The driver section <NUM> includes, for example, a shift pedal <NUM> as a speed change operation tool for varying the continuously variable transmission device <NUM>. The driver section <NUM> includes a potentiometer <NUM> configured to detect the position of the shift pedal <NUM> as operated. The present embodiment, which includes a potentiometer <NUM>, may alternatively include any of various position detecting mechanisms such as a mechanism including a detection switch.

The tractor includes a controller <NUM> configured to control the speed change operation on the basis of the shift pedal <NUM> as operated. The controller <NUM> includes a processor such as a central processing unit (CPU) or electronic control unit (ECU). The controller <NUM> is linked to the continuously variable transmission device <NUM> with the first electromagnetic valve 52A or second electromagnetic valve 52B in-between. The controller <NUM> is also linked to the first to fourth clutches CL1 to CL4 of the planetary transmission device <NUM> ("gear transmission"). The controller <NUM> is configured to detect on the basis of information detected by the potentiometer <NUM> that the shift pedal <NUM> has been operated and vary the continuously variable transmission device <NUM>. During this operation, the controller <NUM> switches the speed change valve unit <NUM> for controlling the swash plate angle between the first and second electromagnetic valve 52A and 52B each time the swash plate <NUM> of the hydraulic pump P is tilted across the neutral position ("electromagnetic valve switching control"). The controller <NUM> is also configured to control how the first to fourth clutches CL1 to CL4 are switched.

The controller <NUM> is linked to a number-of-revolutions detector 4A, a number-of-revolutions detector 31C, a gear position detector 31D, an electric current detector 52C, and an electric current detector 52D.

The number-of-revolutions detector 4A is configured to detect the number of revolutions of the engine <NUM> (that is, an engine output revolutions number <NUM>) and transmit information on the number of revolutions of the engine <NUM> to the controller <NUM>. The number-of-revolutions detector 31C is configured to detect the number of output revolutions of the transmission <NUM> (that is, a gear output revolutions number <NUM>) and transmit information on the number of revolutions of the transmission <NUM> to the controller <NUM>. The number-of-revolutions detector 31C may be configured to, for instance, detect the number of revolutions of the input shaft 16a of the rear-wheel differential mechanism <NUM> or the number of revolutions of the output shaft <NUM> of the planetary transmission device <NUM> ("gear transmission"). The number-of-revolutions detector 31C may, if configured to detect the number of revolutions of the input shaft 16a, detect the number of revolutions of a power transmission gear <NUM> provided for the input shaft 16a.

The gear position detector 31D is configured to detect the current speed range, that is, which of the first to fourth clutches CL1 to CL4 is engaged, and transmit information on the result of the detection to the controller <NUM>.

The electric current detector 52C is configured to measure the value of electric current ("control signal") inputted to the first electromagnetic valve 52A and transmit information on the electric current value to the controller <NUM>. The electric current detector 52D is configured to measure the value of electric current ("control signal") inputted to the second electromagnetic valve 52B and transmit information on the electric current value to the controller <NUM>.

The controller <NUM> functions as an electromagnetic valve control device configured to, as part of the operation of varying the continuously variable transmission device <NUM>, perform electromagnetic valve switching control, that is, switch the first and second electromagnetic valves 52A and 52B on and off, on the basis of information that the controller <NUM> has obtained from components such as the number-of-revolutions detector 4A and a switching table <NUM>. The controller <NUM> is also configured to select an electric current value to be transmitted to the first electromagnetic valve 52A or second electromagnetic valve 52B having been switched on and output information on the electric current value to the first electromagnetic valve 52A or second electromagnetic valve 52B.

With reference to <FIG>, <FIG>, and <FIG>, the description below deals with a configuration for performing electromagnetic valve switching control.

The controller <NUM> includes a data communicator <NUM>, a target gear ratio obtainer <NUM>, a current gear ratio obtainer <NUM>, an current electric current value obtainer <NUM>, a switching controller <NUM>, and a storage <NUM>. The controller <NUM> also includes a speed change controller <NUM> configured to control the speed change together with the switching controller <NUM>.

The data communicator <NUM> is connected to elements such as the potentiometer <NUM>, the number-of-revolutions detectors 4A and 31C, the gear position detector 31D, and the electric current detectors 52C and 52D in such a manner as to be capable of data communication. The data communicator <NUM> is also configured to transmit a control signal to elements such as the first and second electromagnetic valves 52A and 52B and the planetary transmission device <NUM> ("gear transmission").

The storage <NUM> stores in advance information on a rising electric current value <NUM> (hereinafter also indicated as "(b)") of each of the first and second electromagnetic valves 52A and 52B and the switching table <NUM>. The rising electric current value <NUM> refers to the electric current value for a control signal at which value the gear ratio starts to change for each of the first and second electromagnetic valves 52A and 52B, and hence to the electric current value at which the swash plate <NUM> starts to become inclined (or tilted) from the neutral position. The rising electric current value <NUM>, in other words, refers to the value of electric current at a time point at which a gradual increase in electric current starts to change the gear ratio and thereby move the swash plate <NUM> within each speed range.

The target gear ratio obtainer <NUM> is configured to obtain from the potentiometer <NUM> through the data communicator <NUM> information on the position of the shift pedal <NUM> as operated and calculate (or obtain) a target gear ratio <NUM> (hereinafter also indicated as "(c)") corresponding to the position. The target gear ratio obtainer <NUM> stores information on the target gear ratio <NUM> in the storage <NUM>.

The current gear ratio obtainer <NUM> is configured to obtain through the data communicator <NUM> information on an engine output revolutions number <NUM> that the number-of-revolutions detector 4A has obtained and information on a gear output revolutions number <NUM> that the number-of-revolutions detector 31C has obtained and calculate the current gear ratio <NUM> (hereinafter also indicated as "(d)"). The current gear ratio obtainer <NUM> stores information on the current gear ratio <NUM> in the storage <NUM>.

The current electric current value obtainer <NUM> is configured to obtain through the data communicator <NUM> information on the electric current value that the electric current detector 52C has detected and information on the electric current value that the electric current detector 52D has measured. The current electric current value obtainer <NUM> stores in the storage <NUM> information on the larger one of the two electric current values as a current electric current value <NUM> (hereinafter also indicated as "(a)"), which is the electric current value for a control signal with which the hydraulic pump P is being controlled. The current electric current value obtainer <NUM> stores the current electric current value <NUM> in association with information on whether the electric current value is as measured by the electric current detector 52C or the electric current detector 52D, that is, whether the electric current value is for a control signal on the normal rotation side or for a control signal on the reverse rotation side.

The switching controller <NUM> is configured to calculate the difference between the target gear ratio <NUM> and the current gear ratio <NUM> as a gear ratio difference <NUM> (hereinafter also indicated as "(f)") and store information on the gear ratio difference <NUM> in the storage <NUM>. The switching controller <NUM> is also configured to perform electromagnetic valve switching control, that is, switch the first and second electromagnetic valves 52A and 52B on and off, on the basis of the current electric current value <NUM> and the switching table <NUM>. The switching controller <NUM> performs electromagnetic valve switching control on the basis of, for example, the rising electric current value <NUM>, the current electric current value <NUM>, the gear ratio difference <NUM>, and the switching table <NUM> as discussed later.

The storage <NUM> stores information on the current gear position <NUM> obtained from the gear position detector 31D through the data communicator <NUM>. The gear position <NUM> corresponds to that clutch of the output section 31B which has been engaged and thus to the current speed range. Specifically, the gear position <NUM> of <NUM> corresponds to the first-gear range, in which the first clutch CL1 is engaged; the gear position <NUM> of <NUM> corresponds to the second-gear range, in which the second clutch CL2 is engaged; the gear position <NUM> of <NUM> corresponds to the third-gear range, in which the third clutch CL3 is engaged; and the gear position <NUM> of <NUM> corresponds to the fourth-gear range, in which the fourth clutch CL4 is engaged.

The rising electric current value <NUM> of each of the first and second electromagnetic valves 52A and 52B is determined in advance for each gear position <NUM> as below with the engine <NUM> having been warmed up and the transmission oil at <NUM>, and is stored in the storage <NUM>.

First, with the gear position <NUM> at <NUM>, the target electric current value is, as illustrated in <FIG>, gradually swept for the first electromagnetic valve 52A from the state in which the current gear ratio <NUM> is C1N with the continuously variable transmission device <NUM> in the neutral state. This increases the current electric current value <NUM>, and starts to change the current gear ratio <NUM> from the value indicative of the neutral position (C1N) at an electric current value. This value is used as the rising electric current value <NUM> of the first electromagnetic valve 52A, at which the swash plate <NUM> starts to tilt. A similar operation is then performed to determine the rising electric current value <NUM> of the second electromagnetic valve 52B. Further, the rising electric current value <NUM> of each of the first and second electromagnetic valves 52A and 52B is determined for each gear position <NUM> as the gear position <NUM> is switched. <FIG> shows a solid line to indicate how the current gear ratio changes in response to the target electric current value supplied to the first electromagnetic valve 52A and a broken line to indicate how the current gear ratio changes in response to the target electric current value supplied to the second electromagnetic valve 52B.

The switching table <NUM> stored in the storage <NUM> stores switching conditions for the electromagnetic valve switching control. The switching table <NUM> stores a first switching target deviation 70b (hereinafter also indicated as "(F1)"), a second switching target deviation 70c (hereinafter also indicated as "(F2)"), and a third switching target deviation 70a (hereinafter also indicated as "(F3)"), each of which is, among different switching threshold values for each engaged clutch (or gear position <NUM>), a gear ratio difference threshold value and is determined in advance. The first to third switching target deviations 70b, 70c, and 70a are determined in advance for each gear position <NUM> on the basis of, for example, the gear ratio with the continuously variable transmission device <NUM> in the neutral state and the range of variation of the gear ratio. The third switching target deviation 70a is smaller than the second switching target deviation 70c, which is then smaller than the first switching target deviation 70b. As illustrated in <FIG>, the switching table <NUM> also stores a first electric current threshold value 70f (hereinafter also indicated as "(A1)") and a second electric current threshold value <NUM> (hereinafter also indicated as "(A2)"), each of which is an electric current threshold value among the switching threshold values and is determined in advance. The switching table <NUM> may also store information on, for example, an expected gear ratio corresponding to the neutral position (or neutral point) of the continuously variable transmission device <NUM>, the range of variation in this gear ratio, and the width of this gear ratio as the width of the range of variation in the gear ratio.

With reference to <FIG>, <FIG>, and <FIG>, the description below deals with how the switching controller <NUM> operates for the electromagnetic valve switching control.

As described above, the storage <NUM> stores information on the switching table <NUM> and the rising electric current value <NUM> determined in advance (step #<NUM> in <FIG>).

Then, the target gear ratio obtainer <NUM> continuously obtains information on the position of the shift pedal <NUM> as operated from the potentiometer <NUM> for the shift pedal <NUM> through the data communicator <NUM> for speed change control including the electromagnetic valve switching control while the tractor is traveling. The target gear ratio obtainer <NUM> calculates a target gear ratio <NUM> corresponding to the position and stores the target gear ratio <NUM> in the storage <NUM> (step #<NUM> in <FIG>).

The current gear ratio obtainer <NUM> continuously obtains information on an engine output revolutions number <NUM> from the number-of-revolutions detector 4A of the engine <NUM> through the data communicator <NUM>. Similarly, the current gear ratio obtainer <NUM> continuously obtains information on a gear output revolutions number <NUM>, which is the number of output revolutions of the planetary transmission device <NUM>, from the number-of-revolutions detector 31C of the planetary transmission device <NUM> through the data communicator <NUM>. The current gear ratio obtainer <NUM> divides the gear output revolutions number <NUM> by the engine output revolutions number <NUM> and multiplies the quotient by <NUM>,<NUM> to determine the current gear ratio <NUM>. The current gear ratio obtainer <NUM> stores information on the current gear ratio <NUM> in the storage <NUM> (step #<NUM> in <FIG>). The current gear ratio obtainer <NUM> also obtains information on the current gear position <NUM> from the gear position detector 31D of the planetary transmission device <NUM> through the data communicator <NUM> and stores the information in the storage <NUM>.

The current electric current value obtainer <NUM> continuously obtains from the electric current detectors 52C and 52D through the data communicator <NUM> information on the electric current value for a control signal to be transmitted to the first and second electromagnetic valves 52A and 52B. The controller <NUM> determines which electromagnetic valve is being used to control the swash plate <NUM> of the continuously variable transmission device <NUM> and stores in the storage <NUM> as the current electric current value <NUM> information on the value of electric current being inputted to that electromagnetic valve (step #<NUM> in <FIG>).

Steps #<NUM> to #<NUM> in <FIG> are carried out while the tractor is traveling or the engine <NUM> is running, and are not necessarily carried out in this order.

Next, the switching controller <NUM> determines the difference between the target gear ratio <NUM> and the current gear ratio <NUM> as a gear ratio difference <NUM> and stores information on the gear ratio difference <NUM> in the storage <NUM> (step #<NUM> in <FIG>). The gear ratio difference <NUM> is the absolute value of the difference.

Then, the switching controller <NUM> performs electromagnetic valve switching control on the basis of the switching table <NUM>, the rising electric current value <NUM>, the current electric current value <NUM>, and the gear ratio difference <NUM> (step #<NUM> in <FIG>). Specifically, the switching controller <NUM> performs electromagnetic valve switching control, that is, switches the first and second electromagnetic valves 52A and 52B on and off, as a result of determining on the basis of the current gear position <NUM> how close to the rising electric current value <NUM> the current electric current value <NUM> has decreased and how apart from the target gear ratio <NUM> the current gear ratio <NUM> has become.

Performing the above control makes it possible to detect how the swash plate <NUM> is tilted, on the basis of the axle load with use of the difference between the current electric current value <NUM> and the rising electric current value <NUM>. Further, the relationship between the target gear ratio <NUM> and the current gear ratio <NUM> makes it possible to determine whether the continuously variable transmission device <NUM> is being controlled such that the swash plate <NUM> is moved to the neutral position or such that the swash plate <NUM> is moved beyond the neutral position and tilted in an accelerated manner. Performing the electromagnetic valve switching control on the basis of how the swash plate <NUM> has been tilted on the basis of the axle load prevents the first and second electromagnetic valves 52A and 52B from being switched in a delayed manner and allows the first and second electromagnetic valves 52A and 52B to be switched smoothly. If the continuously variable transmission device <NUM> is being controlled such that the swash plate <NUM> is moved beyond the neutral position and tilted in an accelerated manner, the above configuration makes it possible to switch the first and second electromagnetic valves 52A and 52B early. The above control thereby allows the electromagnetic valves to be switched in a timely manner.

The description below deals with the electromagnetic valve switching control in detail.

First, the switching controller <NUM> subtracts the rising electric current value <NUM> from the current electric current value <NUM> to give a difference and determines whether (a) - (b) ≤ (A1), that is, whether the difference is not larger than a predetermined first electric current threshold value 70f stored in the switching table <NUM> (step #<NUM> in <FIG>). The first electric current threshold value 70f is, for example, <NUM> mA.

If the switching controller <NUM> has determined that the difference is not larger than the first electric current threshold value 70f (yes in step #<NUM> in <FIG>), the switching controller <NUM> determines that the current electric current value <NUM> is close to the rising electric current value <NUM> to some extent. The switching controller <NUM> then stores information on the gear ratio difference <NUM> in the switching table <NUM> on the basis of the current gear position <NUM>, and determines whether (f) ≥ (F1), that is, whether the gear ratio difference <NUM> is not smaller than a predetermined first switching target deviation 70b corresponding to the gear position <NUM> (step #<NUM> in <FIG>).

If the switching controller <NUM> has determined that the gear ratio difference <NUM> is not smaller than the first switching target deviation 70b (yes in step #<NUM> in <FIG>), the switching controller <NUM> performs electromagnetic valve switching control, that is, switches off the engaged one of the first and second electromagnetic valves 52A and 52B and switches on the disengaged one thereof (step #<NUM> in <FIG>).

With the current electric current value <NUM> close to the rising electric current value <NUM> and the gear ratio difference <NUM> large over some extent, performing electromagnetic valve switching control after the current electric current value <NUM> has reached the rising electric current value <NUM> would not easily bring the gear ratio to an appropriate value. The above configuration allows the switching controller <NUM> to perform electromagnetic valve switching control before the current electric current value <NUM> reaches the rising electric current value <NUM>, and thereby allows the switching controller <NUM> to switch the electromagnetic valves in a timely manner and bring the gear ratio to an appropriate value early.

If the switching controller <NUM> has determined in step #<NUM> that the gear ratio difference <NUM> is smaller than the first switching target deviation 70b (no in step #<NUM> in <FIG>), the switching controller <NUM> determines whether (a) ≤ (b), that is, whether the current electric current value <NUM> is not larger than the rising electric current value <NUM> (step #<NUM> in <FIG>).

If the switching controller <NUM> has determined that the current electric current value <NUM> is not larger than the rising electric current value <NUM> (yes in step #<NUM> in <FIG>), the switching controller <NUM> subtracts the current electric current value <NUM> from the rising electric current value <NUM> to give a difference and determines whether (b) - (a) ≤ (A2), that is, whether the difference is not larger than a predetermined second electric current threshold value <NUM> stored in the switching table <NUM> (step #<NUM> in <FIG>). The second electric current threshold value <NUM> is, for example, <NUM> mA.

If the switching controller <NUM> has determined that the difference is not larger than the second electric current threshold value <NUM> (yes in step #<NUM> in <FIG>), the switching controller <NUM> determines on the basis of the current gear position <NUM> whether the gear ratio difference <NUM> is not smaller than a third switching target deviation 70a, which is smaller than the first switching target deviation 70b (step #<NUM> in <FIG>).

If the switching controller <NUM> has determined that the gear ratio difference <NUM> is not smaller than the third switching target deviation 70a (yes in step #<NUM> in <FIG>), the switching controller <NUM> performs electromagnetic valve switching control (step #<NUM> in <FIG>).

As described above, with the current electric current value <NUM> close to the rising electric current value <NUM> to some extent and the gear ratio difference <NUM> relatively small, the switching controller <NUM> performs electromagnetic valve switching control even if the current electric current value <NUM> has not reached the rising electric current value <NUM>. The switching controller <NUM>, in other words, needs to switch the electromagnetic valves if the current electric current value <NUM> is close to the rising electric current value <NUM> to some extent and the gear ratio difference <NUM> is large to some extent, as well as if the current electric current value <NUM> is below the rising electric current value <NUM>. As discussed later, if the switching controller <NUM> were configured to switch the electromagnetic valves in response to the gear ratio difference <NUM> being very small (that is, not larger than the third switching target deviation 70a), the switching controller <NUM> would be switching the electromagnetic valves frequently due to load variation and the continuously variable transmission device <NUM> being incapable of moving so subtly near the neutral position. The switching controller <NUM> is thus configured to avoid switching the electromagnetic valves in response to the gear ratio difference <NUM> being very small (that is, not larger than the third switching target deviation 70a). This allows the switching controller <NUM> to switch the electromagnetic valves in a timely manner and bring the gear ratio to an appropriate value early.

If the switching controller <NUM> has determined in step #<NUM> that the gear ratio difference <NUM> is smaller than the third switching target deviation 70a (no in step #<NUM> in <FIG>), the switching controller <NUM> avoids performing electromagnetic valve switching control, and operates to retain the current electric current value <NUM> (step #<NUM> in <FIG>).

With the current electric current value <NUM> decreased to close to the rising electric current value <NUM> and the gear ratio difference <NUM> relatively small, the swash plate <NUM> may not become much tilted due to the small current electric current value <NUM>. Thus, the switching controller <NUM>, in the above state, retains the current electric current value <NUM> and then resumes electromagnetic valve switching control in response to the gear ratio difference <NUM> increasing by not smaller than a predetermined value. This allows the electromagnetic valves to be switched in a timely manner.

If the switching controller <NUM> has determined in step #<NUM> that the difference is larger than the second electric current threshold value <NUM> (no in step #<NUM> in <FIG>), the switching controller <NUM> determines on the basis of the current gear position <NUM> whether the gear ratio difference <NUM> is not smaller than a second switching target deviation 70c, which is larger than the third switching target deviation 70a and smaller than the first switching target deviation 70b (step #<NUM> in <FIG>).

If the switching controller <NUM> has determined that the gear ratio difference <NUM> is not smaller than the second switching target deviation 70c (yes in step #<NUM> in <FIG>), the switching controller <NUM> performs electromagnetic valve switching control (step #<NUM> in <FIG>).

As described above, the switching controller <NUM> performs electromagnetic valve switching control if (i) the current electric current value <NUM> is not larger than the rising electric current value <NUM> and simultaneously (ii) the gear ratio difference <NUM> is not smaller than the second switching target deviation 70c. This allows the switching controller <NUM> to switch the electromagnetic valves in response to the current gear ratio <NUM> being apart from the target gear ratio <NUM> by not smaller than a predetermined value even if the current electric current value <NUM> has not reached the rising electric current value <NUM>. This in turn allows the electromagnetic valves to be switched appropriately.

If no in steps #<NUM>, #<NUM>, and #<NUM>, the switching controller <NUM> restarts the process from step #<NUM>.

The switch of the electromagnetic valves is followed by input of a control signal (or electric current value) into the electromagnetic valves with a time lag in-between. Further, the switch of the electromagnetic valves is followed by the start of the tilt of the swash plate <NUM> with a time lag in-between. If the switching conditions are satisfied again immediately after the switching controller <NUM> has switched the electromagnetic valves, the switching controller <NUM> will switch the electromagnetic valves again accordingly. This may lead to a control signal (or electric current value) being inputted inappropriately or to the swash plate <NUM> being tilted inappropriately. Further, switching the electromagnetic valves repeatedly at short intervals may lead to unstable operation of the continuously variable transmission device <NUM>.

With the above configuration, the switching controller <NUM> avoids performing electromagnetic valve switching control over a predetermined time period after once switching the electromagnetic valves. This ensures appropriate input of a control signal (or electric current value), appropriate tilt of the swash plate <NUM>, and stable operation of the continuously variable transmission device <NUM>.

(<NUM>) For each of the embodiments described above, the switching table <NUM> does not necessarily store the three switching threshold values of the first to third switching target deviations 70b, 70c, and 70a as switching threshold values (that is, gear ratio difference threshold values), and may store one, two, or four or more switching threshold values. The switching controller <NUM>, in this case as well, performs electromagnetic valve switching control for each gear position <NUM> in correspondence with how the current electric current value <NUM> and the rising electric current value <NUM> are related to their respective switching threshold values.

The switching controller <NUM> is thereby capable of performing electromagnetic valve switching control appropriately according to, for example, the surroundings of the transmission <NUM> or the current state of the environment.

(<NUM>) For each of the embodiments described above, the switching threshold values are not necessarily stored in the switching table <NUM>, and may be in the form of a function involving the current electric current value <NUM> and the rising electric current value <NUM> for each gear position <NUM>. The function may be set by, for example, linearly interpolating a predetermined value.

The above configuration allows the switching controller <NUM> to perform electromagnetic valve switching control more easily.

Claim 1:
An electromagnetic valve control device for a transmission configured to vary motive power from a drive section with use of a gear transmission (<NUM>) and a hydrostatic, continuously variable transmission device (<NUM>) and output the varied motive power, the electromagnetic valve control device being configured to control, based on a target gear ratio and with use of a value of electric current for the continuously variable transmission device, a first electromagnetic valve (52A) configured to control a pump swash plate on a normal rotation side of a neutral position and a second electromagnetic valve (52B) configured to control the pump swash plate on a reverse rotation side of the neutral position,
the electromagnetic valve control device (<NUM>) comprising:
a current gear ratio obtainer (<NUM>) configured to obtain a current gear ratio as a ratio of the number of output revolutions of the drive section and the number of output revolutions of the transmission;
the electromagnetic valve control device being characterized in that it comprises:
a current electric current value obtainer (<NUM>) configured to obtain a current electric current value as the value of the electric current to be inputted to the first electromagnetic valve or the second electromagnetic valve; and
a switching controller (<NUM>) configured to, based on the current electric current value and a gear ratio difference as a difference between the target gear ratio and the current gear ratio, perform electromagnetic valve switching control of switching between use of the first electromagnetic valve to control the pump swash plate and use of the second electromagnetic valve to control the pump swash plate.