JPS5851062Y2 - Travel transmission operation device - Google Patents

Description

[Detailed description of the invention] The present invention incorporates a hydraulic transmission device such as a hydraulic continuously variable transmission (H8T) in the middle of the traveling transmission line, and operates the device to obtain variable speed output. It relates to a transmission device.

Conventionally, there was a technology that operated a latch and forward/reverse shifting with a single lever (for example, Japanese Utility Model Application Publication No. 1983-350.04), but in order to obtain the forward/reverse shifting output, a hydraulic continuously variable transmission was developed. If provided, the shift neutral position of the lever would be limited to an extremely narrow range, and an error in the connection dimensions of the lever and neutral adjustment of the transmission would result in an extremely low speed output in either forward or reverse direction. There are drawbacks such as the fact that multiple mechanisms cannot be properly interlocked due to driving at a speed lower than the specified speed, and malfunctions occur due to low speeds, making it difficult to implement.

The present invention solves the above-mentioned conventional drawbacks, and includes a running latch that continuously controls the traveling driving force outputted through a hydraulic continuously variable transmission, and the transmission is controlled by swinging in the longitudinal force direction of the aircraft. In a device equipped with an operating lever for shifting forward and backward gears, the operating lever is connected so that the latch for running the vehicle is continuously operated by swinging of the operating lever in the left-right direction of the aircraft body, and the clutch is disengaged and held. A low-speed output range for moving the operating lever in the gear shifting direction is provided, and the operating lever can be operated by cutting off the ultra-low-speed output of the transmission, and compared to conventional systems, the lever is able to move when the latch continues. It is possible to prevent malfunctions due to ultra-low speed output, to always obtain the set minimum speed shift output at the same time as the clutch is continued, and to match the relative speeds of multiple mechanisms so that they can operate properly in conjunction even when driving at low speeds. The purpose of the present invention is to provide a travel transmission operating device that can be safely handled with relatively simple maintenance and adjustment.

An embodiment of the present invention will be described below in detail with reference to the drawings.

Fig. 1 is a schematic side view of the combine harvester, and Fig. 2 is a plan view thereof, in which 1 is a track frame, 2 is a running roller,
3 is a driving sprocket, 4 is a traveling mission, 5 is a machine base, 6 is a pivot point, 7 is a lifting cylinder, 8 is a threshing section, 9
1 is a reaping section, 11 is a straw cutting section, 11 is a shell culm conveyor, 12 is a feed chain, 13 is a straw disposal chain, 1
4 is an engine, 15 is a rice holder, 16 is a driver's seat, 17 is a driving operation section, 18 is a side clutch lever, and 19 is a travel main gear shift operation lever. The shell culm is harvested and sent rearward, and the shell culm inherited to the feed chain 12 is continuously threshed in a threshing part 8.

As shown in FIG. 3, left and right drive sprockets 3, 3 which are engaged with rollers 2, 2 which run left and right are operatively connected to an engine 14 via a hydraulic continuously variable transmission 21.

The device 21 includes a hydraulic pump 22, a hydraulic motor 23, a charge pump 24, a relief valve 2.5, and a belt 26.
An input shaft 28 is operatively connected to the engine 14 through a pulley 27, and an output shaft 29 of the hydraulic motor 23 is operatively connected to a hydraulic clutch 32 through gears 30, 31.

In addition, each gear 33.34, 35.36 and the clutch 3
Hydraulic motor 23 to side clutch 37, 38 via 2
The output shaft 29 is interlocked and the clutches 37 and 38 are interlocked and connected to the left and right drive sprockets 3 through gears 39, 40 and 41, 42, respectively.

A side brake 43,44 is provided coaxially with the side clutch 37,38.

Further, the discharge side of the charge pump 24 is connected to the hydraulic cylinder 45 for engaging and operating the hydraulic clutch 32 via a 3-position 3-boat type switching valve 46, so that the hydraulic pressure of the pump 24 is applied to the cylinder 45. It forms.

4 and 5 show the connection between the swash plate 22a for varying the discharge amount of the hydraulic pump 22, the 3-position switching spool 46a of the switching valve 46, and the operating lever 19. A rectangular parallelepiped member 48 is fitted and supported, and the member 4
8 through a pin 49 so as to be rotatable only in the axial direction of the horizontal shaft 47, and a notch 52 is provided at one end of the operation plate 50 to engage with a pin 51 provided at the tip of the spool 46a. , the lever 19 is attached to the operation plate 50.
The base end is fixed, and the lever 19 is tilted in the axial direction (left and right) of the horizontal shaft 47, and the spool 4 is moved through the operation plate 50.
6a is slidably displaced, and the switching valve 46 is formed to be operated to switch between three positions.

Further, an upper link 53 is fixed to the horizontal shaft 4T, and a rod 5 is attached to a lower link 55 fixed to the support shaft 54 of the swash plate 22a.
6 to connect the link 53, and the operation plate 5
0 and the rectangular parallelepiped member 48 (back and forth), and each link 53.
55 and rod 56 to rotate the support shaft 54 to rotate the swash plate 2.
The discharge amount of the pump 22 is adjusted by changing the angle of the pump 2a.

Furthermore, the swing rings 57 and 58 that hold the operating lever 19 in the neutral position are energized to the operating plate 50, and the intermediate part of the lever 19 is inserted into the sliding locus groove 59, and the groove is closed as shown in FIG. 59 is formed into a crank shape, and is provided with a traveling neutral portion 59a1, a forward speed change portion 59b1, and a reverse speed change portion 59c,
Each transmission section 59b.

59c and the longitudinal direction of the fuselage, the operating lever 19 located approximately in the center of the traveling neutral section 59a is moved to both ends of the neutral section 59a, that is, to the left and right, and the switching valve 46 is switched to operate the cylinder 45. At the same time, each transmission section 59
b, 59c, that is, by moving the lever 19 back and forth, the swash plate 22a of the hydraulic pump 22 is tilted in the forward and reverse directions.

The present invention is constructed as described above, and the operating lever 19 is always held by the spring 57.5 as shown in FIGS. 3 to 6.
8, the latch 3 is positioned approximately at the center of the neutral portion 59a formed in the groove 58, and runs while keeping the switching valve 46 neutral.
2 is turned off, and the swash plate 22a of the hydraulic pump 22 is kept neutral to maintain the output rotation of the hydraulic motor 23 at approximately zero.

Then, tilt the lever 19 to the left or right, and press the lever 1.
9 to one end side of the neutral portion 59a, the switching valve 46 is switched via the operation plate 50, the cylinder 45 is operated by the hydraulic pressure of the charge pump 24, and the running latch 32 is turned on. An output shaft 29 is coupled to left and right sprockets 3.3.

Further, when the lever 19 is tilted forward and the lever 19 is moved within the forward transmission section 59b, the swash plate 22a is tilted via the links 53, 55 and the rod 56, and the hydraulic pump 23
is rotated in the forward direction, and the number of revolutions of the output shaft 290 increases or decreases depending on the inclination angle of the swash plate 22a.
3, the left and right crawlers 2
, 2 to move the combine forward.

On the other hand, when the lever 19 is tilted rearward and the lever 19 is moved within the reverse transmission section 59c, the swash plate 2 moves in the opposite direction to that described above.
2a tilts, causing the hydraulic pump 23 to rotate in the reverse direction, which is transmitted to the left and right sprockets 3 through the latch 32 running, and the left and right crawlers 2.2 are driven in the reverse direction, causing the combine to move backward.

When the lever 19 is returned to the neutral portion 59a, each spring 57, 58 moves the lever 19 back to the approximate center of the neutral portion 59a, returning the switching valve 46 to the neutral position and keeping the running latch 32 in the OFF state. , whereby the transmission 2
1 and each sprocket 3°3.

8 shows a modification of the sliding locus groove 59 of the lever 19, and the spool 46a of the switching valve 46 is shown in FIG.
The sliding trajectory groove 60. is provided with a low speed output range a so that the lever 19 can be slightly swung back and forth when the lever 19 is stopped (neutral).
61, and is configured so that the extremely low speed output from the transmission 21 is disconnected by the latch 32 that runs.

For example, when the cutting blade 20 is driven in conjunction, operating within the low-speed output range a and cutting the culm at a very low speed with the cutting blade 20 may cause accidents such as pulling out the culm due to poor cutting of the culm. When the section 9 is driven independently, the traveling speed of the combine harvester and the speed at which the shell culms are conveyed by the conveyor 11 do not match, and the amount of shell culms conveyed becomes irregular, resulting in accidents such as the shell culms becoming clogged on the way. However, these inconveniences caused by ultra-low speed work can be resolved by disconnecting the latch 32, which operates at a speed below a certain speed, as described above.First, the lever 19 is tilted back and forth within the low speed output range a. Running latch 3
2 is off, the transmission 21 is operated, and the pump 23 is turned off.
The output shaft 29 of is idled at a constant speed or less.

Next, the lever 19 is tilted to the left and right, the groove pressure cylinder 45 is activated as described above, and the latch 32 for running is turned on, and the left and right crawlers 2, 2 are moved at a certain speed or higher as shown in FIG.
It drives the combine harvester.

As is clear from the above embodiments, the present invention includes a running latch 32 that intermittently controls the traveling driving force outputted through the hydraulic continuously variable transmission 21, and a driving latch 32 that controls the transmission 21 by swinging the aircraft in the longitudinal direction. Operation lever 1 for shifting forward and backward
9, in which these are connected so that the moving latch 32 is continuously operated by the swinging of the operating lever 19 in the left-right direction of the aircraft body, and the operating lever 19 is operated while the clutch 32 is disengaged and held. The control lever 19 is provided with a low-speed output range a that moves the control lever 19 in the shifting direction, and cuts off the very low-speed output of the transmission 21 to move the operating lever 19.
The lever 19 can be operated more easily than in the past.
It is possible to prevent malfunctions due to extremely low speed output when the latch 32 continues to run at 0, and it is possible to always obtain the set minimum speed shift output at the same time as the clutch 32 is continued, and to match the relative speeds of multiple mechanisms to achieve low speed running. However, it can be operated in a proper interlocking manner, and it can be handled safely with simpler maintenance and adjustment than before, and has remarkable effects such as being extremely practical.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention: Fig. 1 is a schematic side view of the combine harvester, Fig. 2 is a plan view of the same, Fig. 3 is a traveling transmission system diagram, and Figs. 4 and 5 are enlarged views of main parts. 6 is a partial explanatory diagram thereof, FIGS. 7 and 8 are explanatory diagrams showing the previous modification, and FIG. 9 is an explanatory diagram of its operation. 19...Operating lever, 21...Hydraulic transmission, 32...Hydraulic clutch (latch for running).

Claims (1)

[Scope of utility model registration request] It is equipped with a running latch 32 that intermittently controls the traveling driving force outputted through the hydraulic continuously variable transmission 21, and an operating lever 19 that controls the transmission 21 by swinging the aircraft in the longitudinal direction to perform forward and backward shifting. In this device, the moving latch 32 is connected so as to be continuously operated by the swinging of the operating lever 19 in the left-right direction of the aircraft body, and the operating lever 19 is moved in the gear shifting direction with the clutch 32 being disengaged and held. A travel transmission operating device characterized by providing a low-speed output range a for movement.