Patent Application
20100263361
The present invention relates to a traveling control device for a hydraulically-driven vehicle such as a wheel hydraulic excavator.
There is a hydraulically-driven vehicle known in the related art (see patent reference literature 1) that is engaged in traveling operation with pressure oil output from a hydraulic pump and supplied to a traveling hydraulic motor via a main pipeline as a control valve is driven with pilot pressure generated in response to an operation of a traveling pedal. The structure disclosed in patent reference literature 1 includes a variable relief valve via which the pressure oil from the main pipeline is relieved with the relief pressure at the variable relief valve controlled in correspondence to the pilot pressure generated as the traveling pedal is operated.
As the pilot pressure generated in the hydraulically-driven vehicle disclosed in patent reference literature 1 increases, the relief pressure also increases. This means that if the driver steps on the traveling pedal suddenly while the vehicle is ready to travel or is traveling at low speed, the vehicle will jerk ahead abruptly or accelerate too much, inducing a significant shock.
A traveling control device for a hydraulically-driven vehicle according to a first aspect of the present invention, comprises: a traveling hydraulic motor driven by oil delivered from a hydraulic pump; a speed-reducing mechanism with an adjustable speed-reduction ratio, that slows down rotation of the hydraulic motor and transmits the slowed rotation to wheels; a pressure oil control device that controls a flow of pressure oil from the hydraulic pump to the hydraulic motor in correspondence to an extent to which a traveling pedal is operated; a speed-reduction ratio detection device that detects the speed-reduction ratio at the speed-reducing mechanism; and an acceleration limiting device that restricts accelerating operation of the hydraulic motor achieved in response to an operation of the traveling pedal, when an acceleration-limiting condition, that is, the speed-reduction ratio detected by the speed-reduction ratio detection device is equal to or greater than a predetermined value, is met.
A traveling control device for a hydraulically-driven vehicle according to a second aspect of the present invention, comprises: a variable displacement traveling hydraulic motor driven by oil delivered from a hydraulic pump; a pressure oil control device that controls a flow of pressure oil from the hydraulic pump to the hydraulic motor in correspondence to an extent to which a traveling pedal is operated; a motor displacement detection device that detects a motor displacement of the hydraulic motor; and an acceleration limiting device that restricts accelerating operation of the hydraulic motor achieved in response to an operation of the traveling pedal, when an acceleration-limiting condition, that is, the motor displacement detected by the motor displacement detection device is equal to or greater than a predetermined value, is met.
A traveling control device for a hydraulically-driven vehicle according to a third aspect of the present invention, comprises: a variable displacement traveling hydraulic motor driven by oil delivered from a hydraulic pump; a speed-reducing mechanism with an adjustable speed-reduction ratio, that slows down rotation of the hydraulic motor and transmits the slowed rotation to wheels; a pressure oil control device that controls a flow of pressure oil from the hydraulic pump to the hydraulic motor in correspondence to an extent to which a traveling pedal is operated; an equivalent displacement calculating device that calculates an equivalent displacement assuming a correlation to a value obtained by multiplying a motor displacement of the hydraulic motor by the speed-reduction ratio at the speed-reducing mechanism; and an acceleration limiting device that restricts accelerating operation of the hydraulic motor achieved in response to an operation of the traveling pedal, when an acceleration-limiting condition, that is, the equivalent displacement calculated by the equivalent displacement calculating device is equal to or greater than a predetermined value, is met.
According to a fourth aspect of the present invention, in the traveling control device for a hydraulically-driven vehicle according to any one of the first to third aspects, it is preferable that the pressure oil control device is a control valve driven by pilot pressure corresponding to the extent to which the traveling pedal is operated; and the acceleration limiting device slows down response of the control valve to the pilot pressure when the acceleration-limiting condition is met, compared to response of the control valve when no acceleration-limiting condition is met.
According to a fifth aspect of the present invention, the traveling control device for a hydraulically-driven vehicle according to any one of the first to fourth aspects, may further comprise a vehicle speed detection device that detects a vehicle speed, wherein the acceleration limiting device may limit the accelerating operation when the acceleration-limiting condition is met and the vehicle speed detected by the vehicle speed detection device is equal to or less than a predetermined value.
A traveling control method adopted in a hydraulically-driven vehicle according to a sixth aspect of the present invention, comprises: detecting an acceleration-limiting condition, that is, (a) a speed-reduction ratio at a speed-reducing mechanism is equal to or greater than a predetermined value, (b) a motor displacement of a variable displacement traveling hydraulic motor is equal to or greater than a predetermined value or (c) an equivalent displacement assuming a correlation to a value obtained by multiplying the motor displacement by the speed-reduction ratio at the speed-reducing mechanism is equal to or greater than a predetermined value; and restricting accelerating operation of the hydraulic motor achieved in response to an operation of a traveling pedal, when the acceleration-limiting condition is met.
According to a seventh aspect of the present invention, a hydraulically-driven vehicle equipped with a traveling control device according to any of the first to fifth aspects.
According to the present invention, an abrupt start and abrupt acceleration of the vehicle can be prevented by restricting operation of the traveling pedal.
The following is a description of an embodiment of a traveling control device for a hydraulically-driven vehicle according to the present invention given in reference to
The displacement angle (displacement volume) of the hydraulic pump 11, which is a variable displacement pump, is controlled by a pump regulator 11A. The pump regulator 11A includes a torque-limiting unit to which the pump outlet pressure is fed back, and horse power control is executed so as to ensure that the load determined in correspondence to the pump outlet pressure and the pump displacement volume does not exceed the engine output. The regulator 11A further includes a maximum displacement limiting unit that determines the maximum flow rate for the hydraulic pump 11.
The hydraulic motor 5 is a variable displacement motor equipped with a self-pressure displacement control mechanism and the motor drive pressure is applied from a shuttle valve 14 to a control piston 15 and a servo piston 16 of the hydraulic motor 5. As a result, a small motor displacement qm1 is assumed over a low motor drive pressure range and a large motor displacement qm2 is assumed over a high motor drive pressure range, as shown in
The switching direction along which the switchover occurs at the control valve 12 and the stroke length at the control valve 12 are controlled based upon the traveling pilot pressure originating from a pilot circuit. The pilot circuit includes a pilot pump 21, a pair of traveling pilot valves 23A and 23B that generate a pilot pressure corresponding to the extent to which an accelerator pedal 22 is pressed down and a pair of slow-return valves 24A and 24B respectively disposed between the pilot valve 23A and a pilot port of the control valve 12 and between the pilot valve 23B and a pilot port of the control valve 12.
While the slow-return valve 24A includes a restrictor 26A and a hydraulic switching valve 25A disposed in parallel to each other, the slow-return valve 24B includes a restrictor 26B and a hydraulic switching valve 25B disposed in parallel to each other. The hydraulic switching valves 25A and 25B are each switched to a position A or to a position B via an electromagnetic switching valve 27. Namely, as the electromagnetic switching valve 27 is switched to position B, the pilot pressure from the pilot pump 21 is applied to the hydraulic switching valves 25A and 25B. As a result, the hydraulic switching valves 25A and 25B are switched to position A, thereby disallowing the pilot pressure supply to the control valve 12 via the hydraulic switching valve 25A or 25B, and the pilot pressure from the pilot pump 21 is instead supplied to the control valve 12 via the restrictor 26A or 26B. As the electromagnetic switching valve 27 is switched to position A, the application of pilot pressure to the hydraulic switching valves 25A and 25B stops. Consequently, the hydraulic switching valves 25A and 25B are switched to position B, allowing the pilot pressure to be supplied to the control valve 12 via the hydraulic switching valve 25A or 25B instead of via the restrictor 26A or 26B.
The accelerator pedal 22 is allowed to rotate along the forward direction or the rearward direction as its front side is pressed down (front stepping operation) or its rear side is pressed down (rear stepping operation). As the front side of the accelerator pedal 22 is pressed down, the pilot valve 23A is driven, whereas as the rear side of the accelerator pedal 22 is pressed down, the pilot valve 23B is driven.
In step S3, a decision is made based upon the signal provided from the pressure sensor 32 as to whether or not the small motor displacement qm1 is currently assumed, i.e., whether or not the pump outlet pressure is equal to or greater than a predetermined value. If it is decided in step S3 that the large motor displacement qm2 is currently assumed, the operation proceeds to step S4 to switch the electromagnetic switching valve 27 to position B. As a result, the hydraulic switching valves 25A and 25B are switched to position A, thereby disallowing pilot pressure supply via the hydraulic switching valve 25A or 25B. If, on the other hand, it is decided in step S1 that the vehicle is currently traveling at high speed, or it is decided in step S2 that the speed-reduction ratio is high and it is also decided in step S3 that the small motor displacement qm1 is currently assumed, the operation proceeds to step S5. In step S5, the electromagnetic switching valve 27 is switched to position A. As a result, the hydraulic switching valves 25A and 25B are switched to position B, thereby allowing the pilot pressure to be supplied via the hydraulic switching valve 25A or 25B.
The primary operation of the traveling control device achieved in the embodiment is now explained. It is assumed in the description that the vehicle is engaged in forward traveling operation.
As the driver steps down on the front side of the accelerator pedal 22 while the hydraulic excavator is in a stationary state, the pilot valve 23A is driven in correspondence to the extent of the front stepping operation and the pilot pressure from the pilot valve 23A is applied to the control valve 12 via the slow-return valve 25A. As a result, the control valve 12 is switched to a position F, allowing the pressure oil from the hydraulic pump 11 to be guided to the hydraulic motor 5 via the control valve 12 and allowing the pressure oil to act as pilot pressure on the counterbalance valve 13 to switch the counterbalance valve 13 from the neutral position to the position F. The hydraulic motor 5 is thus driven and the hydraulic excavator is caused to travel forward.
When starting the vehicle at a work site on rough ground or on an uphill slope, a large traveling torque is required and, accordingly, the speed-reduction ratio is set to low by operating the gearshift lever. In addition, when the vehicle starts moving, the motor drive pressure increases. Thus, the large motor displacement qm2 is assumed and the hydraulic excavator starts traveling at low speed with high torque. In this situation, the electromagnetic switching valve 27 is switched to position B through the processing (step S4) described earlier. Consequently, the hydraulic switching valves 25A and 25B are switched to position A and the pilot pressure from the pilot valve 23A is applied to the control valve 12 via the restrictor 26A at the slow-return valve 24A. Thus, even if the driver steps hard on the accelerator pedal 22, the pilot pressure applied to the control valve 12 increases gradually. As a result, the control valve 12 makes a slow transition from the neutral position to the position F, which prevents the hydraulic excavator from jerking forward abruptly and helps reduce shock at the start of movement.
After the hydraulic excavator has started traveling, the hydraulic switching valve 25A remains at the position A (step S4) as long as the traveling speed is equal to or less than the predetermined value V0, the speed-reduction ratio is low and the large motor displacement qm2 is sustained. In this state, the pilot pressure does not increase rapidly even if the driver steps on the accelerator pedal 22 abruptly for rapid acceleration and instead, the control valve 12 makes a slow transition toward the position F. This means that, when the traveling torque is significant, the hydraulic excavator does not accelerate suddenly, assuring better driver comfort.
Once the vehicle starts traveling at a constant speed and the traveling torque decreases in a light-load condition, e.g., on a flat surface, the driver in the operator's cab operates the gearshift lever to switch the speed-reduction ratio to high and the small motor displacement qm1 is assumed in correspondence to the light load. Consequently, the electromagnetic switching valve 27 is switched to position A and the hydraulic switching valve 25A is switched to position B (step S5). As the driver steps on the accelerator pedal 22 in this state, pilot pressure from the pilot valve 23A is applied to the control valve 12 via the hydraulic switching valve 25A (check valve) without passing through the restrictor 26A. In response, the control valve 12 is immediately switched toward the position F and the hydraulic excavator accelerates with quick response to the operation of the accelerator pedal 22, assuring desirable acceleration performance. In this situation, the shock attributable to acceleration is minimized due to the small traveling torque.
When the vehicle is traveling at high speed exceeding the predetermined value V0, the electromagnetic switching valve 27 is switched to position A and the hydraulic switching valve 25A is switched to position B (step S5) even if the speed-reduction ratio is low or even if the large motor displacement qm2 is assumed. As a result, the pilot pressure generated in response to an operation of the accelerator pedal 22 immediately acts on the control valve 12, allowing the hydraulic excavator to accelerate with quick response to the operation of the accelerator pedal 22, thereby assuring desirable acceleration performance. In this situation, the driver is subjected to only a small shock and is assured of a comfortable ride since the vehicle speed is high.
If the driver in the vehicle traveling in response to a front stepping operation on the accelerator pedal 22 stops the operation of the accelerator pedal 22, the pilot valve 23A is set in communication with the reservoir. In this situation, the pilot pressure, having been applied to the control valve 12, is caused to return to the reservoir via the slow-return valve 24A and the pilot valve 23A. During this process, the flow of returning oil becomes constricted at the restrictor 26A of the slow-return valve 24A and thus, the control valve 12 makes a gradual transition to the neutral position. Abrupt deceleration of the vehicle is thus prevented and any deceleration shock is minimized.
The following operational effects can be achieved through the embodiment described above.
(1) If the speed-reduction ratio is set to low or the large motor displacement qm2 is assumed in the vehicle traveling at low speed with the vehicle speed V equal to or less than V0, the hydraulic switching valves 25A and 25B are switched to position A so as to guide the pilot pressure from the pilot valve 23A to the control valve 12 via the restrictor 26A. Thus, even if the driver steps on the accelerator pedal 22 abruptly, the control valve 12 makes a gradual changeover, which reduces the shock occurred as the vehicle starts moving or accelerates.
(2) If the speed-reduction ratio is set to high and the small motor displacement qm1 is assumed in the vehicle traveling at low speed, the hydraulic switching valves 25A and 25B are switched to position B so as to guide the pilot pressure from the pilot valve 23A to the control valve 12 via the check valve at the hydraulic switching valve 25A. Thus, as long as the traveling torque is small and the shock occurred during acceleration is not an issue, the vehicle is allowed to accelerate with quick response to the operation of the accelerator pedal 22.
(3) While the vehicle is traveling at high speed with the vehicle speed V greater than V0, the hydraulic switching valve 25A is switched to position B, regardless of the speed-reduction ratio or the motor displacement, so as to guide the pilot pressure from the pilot valve 23A to the control valve 12 via the check valve at the hydraulic switching valve 25A. As a result, the control valve 12 is switched with quick response in the vehicle traveling at high speed to assure desirable acceleration performance.
In the embodiment of the present invention described above, the accelerating operation via the travel pedal is restricted so as to prevent an abrupt start or an abrupt acceleration of the vehicle.
The electromagnetic switching valve 27 is switched to position B in the vehicle traveling at low speed (V≦V0) if the speed-reduction ratio is set to low, i.e., if the speed-reduction ratio value is equal to or greater than the predetermined value, or if the motor displacement is equal to or greater than the predetermined value (if the large motor displacement qm2 is assumed). In other words, in the embodiment described above, the electromagnetic switching valve 27 is switched to position B if an acceleration-limiting condition is met. The acceleration-limiting conditions under which the electromagnetic switching valve 27 is switched to position B are not limited to those described above. For instance, a value obtained as the product of the speed-reduction ratio, the motor displacement and a predetermined constant may be set as an equivalent capacity, and the electromagnetic switching valve 27 may be switched to position B by judging that an acceleration-limiting condition is met if the equivalent capacity during low-speed traveling operation is equal to or greater than a predetermined value. In this case, the controller 30 should calculate the equivalent capacity and make a decision as to whether or not the acceleration-limiting condition is satisfied. A means other than the selector switch 31 may be utilized as a speed-reduction ratio detection means and a means other than the pressure sensor 32 may be used as a motor displacement detection means. As an alternative, a separate equivalent capacity calculation means may be employed. In addition, the electromagnetic switching valve 27 may be switched to position B by assuming that an acceleration-limiting condition is met if the speed ratio is low, i.e., if the speed ratio is equal to or greater than a predetermined value, if the motor displacement is equal to or greater than a predetermined value or if the equivalent capacity is equal to or greater than a predetermined value, regardless of the vehicle speed.
If the decision as to whether or not an acceleration-limiting condition is met is made simply by deciding whether or not the motor displacement is equal to or greater than a predetermined value (whether or not the large motor displacement qm2 is assumed), the speed-reduction ratio does not need to be detected. If the decision as to whether or not an acceleration-limiting condition is met is made simply by deciding whether or not the speed-reduction ratio is set to low, i.e., whether or not the speed-reduction ratio is equal to or greater than a predetermined value, the motor displacement does not need to be detected. Under such circumstances, the hydraulic motor 5 may be constituted as a fixed displacement traveling hydraulic motor.
In the embodiment described above, the hydraulic switching valves 25A and 25B are switched on/off to position A or to position B. However, the present invention is not limited to this example and instead, the hydraulic switching valves 25A and 25B may each be constituted with a variable throttle valve or metering valve. In conjunction with such hydraulic switching valves, the extent of switchover may be controlled in correspondence to the equivalent capacity so that the passage area of the hydraulic switching valves 25A and 25B decreases as the equivalent capacity increases, as indicated by the characteristics f1 in
In addition, while the electromagnetic switching valve 27 is switched in response to the control signal provided from the controller 30 so as to slow down the response of the control valve 12 to the pilot pressure when an acceleration-limiting condition is satisfied, e.g., when the large motor displacement is assumed, when the speed-reduction ratio is large or when the equivalent capacity is large, compared to the response of the control valve 12 when no such condition is met, an acceleration limiting means other than this may be adopted. For instance, the pump capacity of the hydraulic pump 11 may be reduced when an acceleration-limiting condition is met, compared to the pump capacity assumed when no such condition is satisfied.
While the flow of pressure oil to the hydraulic motor 5 is controlled via the control valve 12 in the embodiment described above, a pressure oil control means other than this may be adopted. The rotation of the hydraulic motor 5 may be communicated to the tires 8 via a speed-reducing mechanism other than the transmission 6. In addition, while the present invention is adopted in a hydraulic excavator in the embodiment described above, the present invention may be equally effectively adopted in another type of hydraulically-driven vehicle. Namely, as long as the features characterizing the present invention and the functions of the present invention are not compromised, the present invention is not limited to the traveling control device achieved in the embodiment. It is to be noted that the embodiment described above simply represents an example and no limitations or restrictions are imposed by the correspondence between the description of the embodiment and the description in the scope of patent claims.
The disclosure of the following priority application is herein incorporated by reference:
Japanese Patent Application No. 2006-217077 filed Aug. 9, 2006
| Number | Date | Country | Kind |
|---|---|---|---|
| 2006-217077 | Aug 2006 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2007/065656 | 8/9/2007 | WO | 00 | 5/20/2010 |
