KR101868504B1 - Device for transmitting control force of HST for work vehicle - Google Patents
Device for transmitting control force of HST for work vehicle Download PDFInfo
- Publication number
- KR101868504B1 KR101868504B1 KR1020170002762A KR20170002762A KR101868504B1 KR 101868504 B1 KR101868504 B1 KR 101868504B1 KR 1020170002762 A KR1020170002762 A KR 1020170002762A KR 20170002762 A KR20170002762 A KR 20170002762A KR 101868504 B1 KR101868504 B1 KR 101868504B1
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- KR
- South Korea
- Prior art keywords
- pressure
- turning
- hst
- arm
- driving
- Prior art date
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Classifications
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
- A01B33/00—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs
- A01B33/08—Tools; Details, e.g. adaptations of transmissions or gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
- B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
- F16H2059/0256—Levers for forward-reverse selection only, e.g. for working machines having a separate lever for switching between forward and reverse mode
Abstract
[0001] The present invention relates to a HST driving force transmitting device for a work vehicle, and more particularly, to a trunnion arm for inputting an operating force according to the operation of a turning operation mechanism to a turning HST, And a swing servo mechanism for transferring the swing arm to the inside; Wherein the servo mechanism for pivoting is configured such that either one of the differential pressure between the neutral position of the trunnion arm and the differential pressure for the left (?) Swing operation and the right (?) Swing operation is greater than the other differential pressure By setting it higher, it is possible to improve the straightness of the vehicle.
Description
BACKGROUND OF THE
Generally, the working vehicle for agricultural machinery includes tractor, combine, and rice milling machine. Among them, the combine is a working car for agricultural machinery that breaks, selects and harvests rice, barley, wheat, etc., and adopts a crawler type driving system because of its working characteristics.
The combine has a power transmission structure for shifting the power generated by the engine as a driving source in the transmission and transmitting the shifted power to a driving wheel for traveling.
Particularly, the transmission is equipped with a hydraulic type continuously variable transmission (HST) (hereinafter, also referred to as 'HST') which allows a continuously variable transmission. In the case of a crawler type combine, a traveling HST and a turning HST .
The forward and reverse continuously-variable shifting through the driving HST is enabled by operating the levers in the vicinity of the driver's seat. When the levers in the periphery are operated, they are transmitted to the traveling HST via the traveling operation transmitting device composed of a link mechanism to transmit the operating force of the levers in the vicinity, and the power input from the engine is shifted from the traveling HST to the desired speed range And then transmitted to the drive shaft through the transmission mechanism, the planetary gear mechanism, the transmission gear mechanism, and the like, thereby driving the crawler on the right and left sides of the traveling body.
The continuously-variable shifting through the HST for turning can be performed by operating the turning lever provided on the driver's seat while the vehicle is advancing or retracting. When the revolving lever is operated, the revolving operation is transmitted to the revolving HST through a swing operation transmitting device including a rod and a link for transmitting the operating force of the revolving lever, and the output power is transmitted to the turn gear through the idle gear of the transmission The input is reversed. When the turn gear is reversed, the output of one side is decelerated more than that of the straight ahead, and the output of the opposite side is increased more than that of the straight ahead, so that a difference in rotation is generated between the left and right crawlers, and as a result, the vehicle can be turned.
As a result, the running HST is operated by the forward, neutral, and reverse operations of the peripheral speed lever, and the turning HST is operated by the left turn, neutral, and priority operation of the turning lever. At this time, the peripheral speed lever transmits the operating force to the traveling HST through the traveling operation transmitting device connected to the traveling HST, and the turning lever transmits the operating force to the turning HST through the swing operation transmitting device connected to the traveling HST.
However, since the driving force transmitting device for transmitting the operating force to the respective HSTs from the peripheral speed lever or the revolving lever is composed of the integral link structure, the peripheral speed lever or the turning lever may move finely regardless of the driver's will, There is a problem that the operation force transmission device operates sensitively and malfunction occurs.
That is, since the operation force transmitting device is connected by a link mechanism such as an arm and a rod, and each connecting portion is integrally coupled with the hole and the pin and is configured to simultaneously transmit the operating force while being integrally moved by lever operation or the like, Even when the lever is moved finely regardless of the driver's will in the neutral state of the lever, the operating force transmitting device is interlocked and the operating force is transmitted to the HST. When the misfeeded operating force is transmitted to the HST, Problems such as the vehicle turning back and forth or turning are generated. As a result, the reliability of the operation force transmitting device is deteriorated and a safety accident may occur.
SUMMARY OF THE INVENTION The present invention has been conceived to solve the problems described above, and it is an object of the present invention to provide an HST driving operation force of a work vehicle which can improve the straightness of a vehicle and increase the reliability of driving operation, And to provide a delivery device.
The HST driving force transmitting device for a work vehicle according to the present invention for realizing the above object includes a trunnion arm for inputting operation force according to the operation of the turning operation mechanism to the HST for turning, To the inside of the HST using a hydraulic pressure; Wherein the servo mechanism for pivoting is configured such that either one of the differential pressure between the neutral position of the trunnion arm and the differential pressure for the left (?) Swing operation and the right (?) Swing operation is greater than the other differential pressure Is set higher.
Here, the?,? Direction differential pressure of the servo servomotor for swing is lower than the? Differential pressure of the? Servo pressure of the swing servomotor at the time of swinging in the left (?) Direction, At the time of swing, the pressure difference at the β side can be set to the unilateral pressure higher than the differential pressure.
On the other hand, the?,? Direction differential pressure of the servo mechanism for swiveling is lower than the differential pressure of? On the? -Position of the swivel servo mechanism when the swiveling servo mechanism is rotated in the right (?) Direction, , The pressure on the? Side may be set to a unilateral pressure higher than the primary pressure.
The differential pressure difference between the α and β directions of the servo mechanism for pivoting is set to be lower by about 3 to 7 bar than the β differential pressure when the swinging motion is in the left direction α direction, The pressure on the β side of the servo mechanism can be set 5 to 7 bar higher than the differential pressure.
On the other hand, a traveling trainer arm for inputting operation force according to the operation of the peripheral speed lever to the traveling HST, and a traveling servo for transmitting the operating force inputted through the traveling traynion arm to the inside of the traveling HST A mechanism is provided; It is preferable that the driving servomechanism is set so that the difference between the advance (a) and reverse (?) Difference pressures is set to be the same around the neutral position of the throne arm.
At this time, the differential pressure of? And? Of the traveling servomechanism can be set to? 5 bar at the basic pressure of charge.
The above and other objects and advantages of the present invention will become more apparent by describing in detail exemplary embodiments thereof with reference to the attached drawings in which: In addition to the principal task solutions as described above, various task solutions according to the present invention will be further illustrated and described.
The HST driving force transmitting device for a work vehicle according to the present invention can improve the straightness of the vehicle because the chock pressure of the swing servomechanism is set to be the unilateral pressure and the chock pressure of the traveling servomechanism is set to be the same When the vehicle is stopped, the neutral maintenance performance can be improved.
FIG. 1 is a perspective view showing a traveling and turning operation force transmitting device and a speed changing device according to an embodiment of the present invention.
Fig. 2 is a perspective view of a main portion of the driving force transmitting device for driving and turning driving shown in Fig. 1. Fig.
FIG. 3 is a configuration diagram showing a traveling driving force transmitting device according to an embodiment of the present invention.
4 is a configuration diagram illustrating a turning driving force transmitting device according to an embodiment of the present invention.
5 is a view for explaining a buffer hole of the driving force transmitting device for traveling and turning driving according to an embodiment of the present invention.
6 to 9 are graphs showing vehicle movement according to an extended length of a buffer hole of a running driving force transmitting device according to an embodiment of the present invention.
10 to 13 are graphs showing vehicle movement according to an extended length of a buffer hole of a turning driving force transmitting device according to an embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
1 is a perspective view showing a driving force transmitting device and a shift device of a working vehicle according to an embodiment of the present invention.
In Fig. 1,
The
The
A traveling
The traveling
First, the configuration of the traveling
1, a running
The driving
The traveling
The traveling
The traveling
Here, each of the arms, rods, and the like that constitute the traveling
Particularly, in the traveling
The driving
2 and 3, a traveling
For reference, the sizes of the holes are overrepresented so that the driving
In FIG. 2, since the
The length of the running
On the other hand, since the traveling
It is also possible to provide a buffer member for holding the position of the
However, since the buffer member has a low elastic force such that the elastic force does not affect the force transmitted when the elastic force is transmitted, and the buffer pin for traveling 285 moves in the middle of the buffer hole for
When the buffer member is formed in the traveling
On the other hand, the
The traveling
However, when the traveling
It is preferable that the erroneous operation preventing structure of the
In this embodiment, the traveling operation motor 230 is operated by a signal that senses the operating state of the
Now, a method of setting an appropriate extension length of the driving
Referring to FIG. 3 and FIG. 5, the design formula of the running
Referring to FIG. 5, since the buffer hole is elongated like an oval shape in the operation force transmitting direction, the extended length C d of the buffer hole and the relational expression of the short axis a and the long axis b are expressed by
[Equation 1]
C d = b - a
3, the length of the
&Quot; (2) "
C d = k · L d 1 /
Here, k represents a constant for setting the driving
The actuating angles? And? Of the
The extended length C d of the
The reason why the extension length C d is designed to be large as the length L d1 of the input arm increases is because the length of the input arm is set to be longer than the length of the input arm The angle gradually becomes smaller, and accordingly, the transmission of the operation force of the lever in the vicinity is sensitized at a small angle. Therefore, it is desirable to increase the extension length C d of the
Table 1 below shows the extension length (C d ) which is set according to the change of the length (L d1 ) of the input arm.
When the extended length (C d) of the input arm length (L d1) can be appropriately set the extension length (C d) in accordance with the change, but the running
The length L d1 of the
This will be described with reference to Figs. 6 to 9. Fig.
Figs. 6 to 9 are graphs showing vehicle movement along the length of the driving
As shown in FIG. 6, when the extended length C d of the running
However, as shown in FIG. 7, when the running
8 and 9 are graphs showing vehicle movement when the extension length of the driving
As shown in FIG. 8, even when the extension length of the running
However, as shown in Fig. 9, when the extended length of the running
Therefore, the extension length C of the running
Next, the configuration of the
1, a turn potentiometer 320 is provided on a lower portion of a
The turning potentiometer 320 is capable of transmitting a signal to the swing control unit (not shown) for controlling the
On the other hand, the turning control unit may be provided together with the turning potentiometer 320 or the turning
The turning
The swing
The swing
Each of the arms, rods, and the like that constitute the swing
In particular, at least one of the parts where the pin and the hole are coupled in the swing
The other holes except for the turning
2 and 4, the hole formed at the end of the swinging
In FIG. 4, too, the hole size is excessively expressed so that the turning
2, since the
The length of the elongated hole of the swinging
On the other hand, since the pivoting
It is also possible to provide a buffer member for holding the position of the swinging
On the other hand, the
The
It is preferable that the erroneous operation preventing structure of the turning
In the above description, the structure for generating the turning operation force by using the turning
The structure using the handle is generally constituted by a rim of a circular structure operated by a driver and a spoke for supporting the rim, and a handle shaft for transmitting the rotational force of the rim at the center of the rim. It is preferable that the turning operation motor is driven by detecting the degree of rotation of the handle shaft by using the turning potentiometer 320 or the like as described above also in the structure using the turning handle. Such a handle using turning operation structure is disclosed in Japanese Patent Laid-Open Nos. 10-1370993 and 10-2011-0068733, so that detailed drawing examples and explanations thereof will be omitted.
Now, a method of setting an appropriate length of the swinging
Referring to FIGS. 4 and 5, the design equation of the swinging
Referring to FIG. 5, the extended length (C t ) of the buffer hole and the relational expression (a) and (b) of the short axis (a)
&Quot; (3) "
C t = b - a
4, the length of the
&Quot; (4) "
C t = k · L t 1 / α
Here, k represents a setting constant of the swing buffer hole. The constant k can be appropriately changed according to the design conditions, and is set to 1.2 in the present embodiment.
And, L t2 is because the operation angle α and β have the same value of the trunnion arms (370) for, turning to 60mm fixed value, the operating angle of the trunnion arms of the turning HST for the setting to the normal 18 ° is set to 18 do.
When this setting as, [Equation 4] C t = 1.2L t1 / 18 is therefore, in a state where the L value t2 is fixed, the length of the arm swing motor (335) for, depending on the size of the hole extended length L t1 buffer (C t ) is also different. That is, when the length L t1 of the motor arm becomes large, the extended length C t of the buffer hole becomes large. When the length L t1 of the motor arm becomes small, the extended length C t of the buffer hole It will be that much smaller.
The reason for designing the extended length C t of the buffer hole as the length L t1 of the motor arm becomes larger is that the turning trunnion arm 20 is set at 18 degrees as the length L t1 of the motor arm becomes longer, The angle for actuating the
Table 2 shows the extension length (C t ) of the buffer holes set in accordance with the change in the length (L t1 ) of the motor arm.
If the extended length C t of the turning
The length L t1 of the swinging
This will be described with reference to FIGS. 10 to 13. FIG.
Figs. 10 to 11 are graphs showing the vehicle movement along the length of the swing buffer hole. Fig.
10, when the extended length C t of the swinging
However, as shown in FIG. 11, when the swinging
12 and 13 are graphs showing vehicle movement when the extension length of the swinging buffer hole is 3 mm or more.
As shown in FIG. 12, even when the extension length C t of the
However, as shown in FIG. 13, when the extension length C t of the swinging
Therefore, the extension length C t of the swinging
On the other hand, in the traveling
1 and 2, each of the
Here, each of the
Therefore, the
4, the
Therefore, in consideration of this point, it is necessary for the
The charging pressure setting of the
That is, when the
For example, when turning in the left (alpha) direction, the pressure on the a side of the
On the contrary, the?,? Direction differential pressure of the
It is preferable that the parking pressure setting of the
That is, the method of correcting the parking pressure of the
3, the pressure difference between the left side? And the right side? Of the
For example, it is preferable that the differential pressure of? And? Centered on the neutral position of the
By setting the differential pressure of the
As described above, the technical ideas described in the embodiments of the present invention can be implemented independently of each other, and can be implemented in combination with each other. While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art. It is possible. Accordingly, the technical scope of the present invention should be determined by the appended claims.
100: transmission device 150: drive output shaft
200: traveling operation transmitting device 201: peripheral speed lever
210: HST for traveling 220: Potentiometer for driving
230: a traveling operation motor 235: a traveling motor arm
240: first transmission rod 250: arm unit
260: second transmission rod 270: trunnion arm for traveling
280: traveling buffer connection part 281: traveling buffer hole
285: Driving buffer pin 290: Driving servo mechanism
300: turning operation transmitting device 301: turning lever
310: HST 320 for turning: Potentiometer for turning
330: Operation motor for turning 335: Motor arm for turning
360: Turning transfer rod 370: Trunnion arm for turning
380: Buffer connection part for swinging 381: Buffer hole for swinging
385: Buffer for rotation 390: Servo mechanism for turning
Claims (6)
Wherein the servo mechanism for pivoting is configured such that either one of the differential pressure between the neutral position of the trunnion arm and the differential pressure for the left (?) Swing operation and the right (?) Swing operation is greater than the other differential pressure And the HST driving force transmitting device of the working vehicle.
When the rotary servo mechanism is rotated in the left (alpha) direction, the difference between the a and b values is smaller than the difference between the a and b values, Wherein the pressure difference between the first and second pressure chambers is set to be a one-side pressure higher than the primary pressure.
The?,? Direction differential pressure of the servo mechanism for pivoting is lower than the? Difference pressure of? On the? -Position servo mechanism of the pivoting servo mechanism when turning in the right (?) Direction, Wherein the pressure in the a side is set to a unilateral pressure higher than the basic pressure of the charge.
The differential pressure difference between the α and β directions of the servo mechanism for pivoting is set to be lower by about 3 to 7 bar than the β differential pressure when the swinging motion is in the left direction α direction, And the β side pressure of the servo mechanism is set to be 5 to 7 bar higher than the primary pressure.
A driving trainer arm for inputting operation force according to the operation of the levers in the vicinity to the driving HST and a driving servomechanism for transmitting operation force inputted through the driving trainer arm to the inside of the driving HST by using the hydraulic pressure ;
Wherein the driving servomechanism is set such that the difference between the differential pressure of forward (?) And reverse (?) Differential pressure is set to be the same around the neutral position of the trunnion arm.
Characterized in that the differential pressure between the α and β of the servomotor for running is set to ± 5 bar at the basic pressure of the charge.
Priority Applications (1)
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KR1020170002762A KR101868504B1 (en) | 2017-01-09 | 2017-01-09 | Device for transmitting control force of HST for work vehicle |
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KR1020170002762A KR101868504B1 (en) | 2017-01-09 | 2017-01-09 | Device for transmitting control force of HST for work vehicle |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20220068892A (en) | 2020-11-19 | 2022-05-26 | 국제종합기계 주식회사 | Device for transmitting force of work vehicle |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000069838A (en) * | 1998-09-02 | 2000-03-07 | Yanmar Agricult Equip Co Ltd | Vehicle speed control system for farm working machine |
JP2001336634A (en) * | 2000-05-25 | 2001-12-07 | Yanmar Diesel Engine Co Ltd | Swash plate operating mechanism of hydraulic continuously variable transmission device |
KR100584785B1 (en) | 1998-12-16 | 2006-05-30 | 얀마-노키 가부시키가이샤 | Work vehicle |
KR20110068733A (en) * | 2008-09-16 | 2011-06-22 | 얀마 가부시키가이샤 | Combine |
KR101301859B1 (en) | 2012-08-21 | 2013-08-29 | 국제종합기계 주식회사 | Transmission for combine |
-
2017
- 2017-01-09 KR KR1020170002762A patent/KR101868504B1/en active IP Right Grant
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000069838A (en) * | 1998-09-02 | 2000-03-07 | Yanmar Agricult Equip Co Ltd | Vehicle speed control system for farm working machine |
KR100584785B1 (en) | 1998-12-16 | 2006-05-30 | 얀마-노키 가부시키가이샤 | Work vehicle |
JP2001336634A (en) * | 2000-05-25 | 2001-12-07 | Yanmar Diesel Engine Co Ltd | Swash plate operating mechanism of hydraulic continuously variable transmission device |
KR20110068733A (en) * | 2008-09-16 | 2011-06-22 | 얀마 가부시키가이샤 | Combine |
KR101301859B1 (en) | 2012-08-21 | 2013-08-29 | 국제종합기계 주식회사 | Transmission for combine |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20220068892A (en) | 2020-11-19 | 2022-05-26 | 국제종합기계 주식회사 | Device for transmitting force of work vehicle |
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