JPS6078141A - Automatic load controller in transmission - Google Patents

Abstract

PURPOSE:To automatically perform shift-up and -down of speed change steps by installing automatic control valves between a selectively operating valve and a clutch apparatus and switching the automatic control valves according to the variation of load, keeping the position of the selectively operating valve as it is. CONSTITUTION:A check valve V1, hydraulic valve V2 for main speed-change, hydraulic valve V3 for sub-speed-change, automatic control valves V4 and V5, and solenoid valves SV1 and SV2 for operating the automatic control valves V4 and V5 are provided as the hydraulic valves for controlling the pressure of a hydraulic pump P. When an automatic control switch is turned ON, a signal is input into the solenoid valve from a controller by the aid of an engine revolution-number sensor, and the spool of the automatic control valve is shifted to perform automatic shift-up and -down of speed change steps.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic clutch type transmission used in construction machinery, agricultural machinery, etc.

The characteristics of a hydraulic clutch type transmission are that it is possible to change speeds without disengaging the main clutch, and because the speed change is performed by the sliding of a hydraulic valve spool rather than the sliding of a series of gears, the operating force is small. There are advantages such as being able to live comfortably.

In addition to this, the present invention is provided with an electromagnetically operated automatic control valve, which senses the load on the transmission based on signals such as engine speed load, and automatically controls the transmission without manual operation by the operator. This is intended to increase or decrease the number of gears.

This is intended to eliminate damage to various parts or insufficient work due to overload work, and to ensure that work is always performed with the engine in its maximum output state.

The purpose of the present invention is as described above, and the detailed structure of the present invention will be explained based on the drawings of the embodiments shown in the attached drawings.

FIG. 1 is a side sectional view of a planetary gear type hydraulic clutch transmission. FIG. 2 is a hydraulic circuit diagram in which the automatic load control device of the present invention is attached to the hydraulic clutch transmission device of FIG. 1.

The structure of the hydraulic clutch device shown in FIG. 1 will be explained.

Attach the transmission case (5) to the front wall OD and the rear wall (I
3) is closed to form an oil bath type transmission chamber.

Engine power is input into this transmission chamber via an input shaft (1) via a main clutch device. A spline-engaged fixed gear 0Φ09σω is fixed on the input shaft (1). The rear end of the input shaft (1) is loosely fitted into the front inner hole of the output shaft (2) via a bearing metal. The input shaft (1) and the output shaft (2) are connected together on the same axis.

However, since both shafts are connected by a metal bearing, different rotations can be performed.

The bearing plate (6) on the input shaft (1) is supported in an idling state by the bearing [29], and similarly, the bearing plate (7) on the output shaft (2) is also supported in an idling state by the bearing (3ω). It is supported in a rotating state.

Between these two bearing plates (6) (7), six planetary gear support shafts (3) (3) (31 (41 (4) (4)) are fixedly installed. Planetary gear support shafts ( Since the reverse planetary gear Q21t181 is always engaged between 3) and (4), the spacing between the shafts is constant.

As for the basic configuration, the planetary gear support shafts (3) and (4) are:
Two pieces per set is enough, but 18 pieces that perform the same role are used.
Three sets are arranged at every 0°, and the configuration is such that the load is balanced.

FIG. 1 shows only one planetary gear support shaft (31(4)) and one set of planetary gears on the planetary gear support shaft (31(4)).

Further, as shown in FIG. 1, the distances of the planetary gear support shafts (31 (4) from the axes of the input shaft (1) and output shaft (2) are different from each other).

The distance of the planetary gear support shaft (3) into which the planetary gears (18), (19) (221) are loosely fitted is the same as that of the planetary gear O'7) (2)
The distance between the planetary gear support shaft (4) and the loosely fitted planetary gear support shaft (4) is set to 1. A set of two loosely fitted gears Q21t181 is used for reverse movement.

That is, the planetary gear 011) is loosely fitted onto the planetary gear support shaft (3), the planetary gear (121) is loosely fitted onto the planetary gear support shaft (4),
The two are constantly intertwined.

Furthermore, among these planetary gears, only the reverse planetary gear a does not mesh with the internal gear, but the other planetary gears are
Internal gear 24] (2!i) (26)H (support)) are meshed with each other. Internal gear (241 (25) (2
G+ (271 (28) is 2 pieces each) (7) It is constructed in the shape of a clutch facing, and the outer periphery is a cylindrical inner diameter metal 00
) and is rotatable.

In addition, the cylindrical inner diameter metal is the transmission case (5)
The friction plate device (5) for the hydraulic clutch is fixed to the inner wall of the hydraulic clutch and slides back and forth.

In this way, due to the structure of the cylindrical inner diameter metal shaft, the friction plate device m (521 (521m) is non-rotatable but can be moved back and forth, and the internal gear (to) 125) 126) @ is rotatable on the outer periphery. The cylindrical inner diameter metal ring is supported by a bearing. or,
Further inside the cylindrical inner diameter metal (10), there is a hydraulic cylinder l-ring (8a) (ab )(
sc) (sdXse) is installed.

The friction plate, internal gear, and hydraulic cylinder ring constitute a hydraulic clutch device, so there is a retaining ring (roller) l (561 [571 (581)
Intermediate between them prevents interference between them and maintains their independence.

When assembling, the cylindrical inner diameter metal 00) is engaged and fitted into the transmission case (5) and fixed so as not to rotate, and the protrusion is fitted into the retaining groove of the cylindrical inner diameter metal to prevent friction. Board 621 (5211521152(5
21 is inserted, and the internal gear (241
(To) Noso (To) is inserted, and then a hydraulic cylinder ring is fitted into the clutch to form a set of hydraulic clutch devices, and each set is fixed with an O-ring. The hydraulic cylinder is configured as a bellows type or the like.

Let me explain the shifting action.

Within this transmission case (5), two transmission systems, a main transmission and a sub transmission, are performed.

The main transmission shifts to 3 gears: 1 forward gear, 2 forward gears, and reverse, and the auxiliary gearbox shifts to 2 gears: high speed and low speed.
In total, there are 6 gears, 4 forward gears and 2 reverse gears.

First, let me explain the main transmission.

The first forward stage of the main transmission is connected to the fixed gear 0 (
The planetary gear (17+) is rotated through the hydraulic cylinder (A) to tighten the friction plate mark on the hydraulic cylinder (A), and the internal gear (
When the rotation of 2) is stopped, the planetary gear 0η starts to revolve, causing the planetary gear support shaft (4) to rotate.

Next, the second forward stage of the main transmission is the fixed gear (1) on the input shaft (1).
The planetary gear U% is rotated from 1e, and the hydraulic cylinder (B
), when the rotation of the internal gear (26) is stopped, the planetary gear 119) starts to revolve, causing the planetary gear support shaft (3) to revolve.

Next, let me explain the main shift in reverse.

Fixed gear a9 of input shaft (1), planetary gear support shaft (4)
Rotate the upper idler planet gear a and the idler planet gears a are always meshed with the planet gear u51, so the planet gear 5) is rotated in the opposite direction to the rotation direction of the other planet gears. be. p1 by hydraulic cylinder (R)
When the internal gear (25) is made unrotatable, the planetary gear support shaft (
3) begins to revolve in the opposite direction. In this way, the integrated planetary gear support shaft (31 (4)) revolves at a speed corresponding to the main gear shift. Planetary gear (2
2) If the gear 131 is loosely fitted and the internal gear meshed with it is made unable to rotate, a sub-shift is performed.

The low speed of the sub-shift is obtained by disabling the free rotation of the internal gear frame by the hydraulic cylinder (X). As a result, the planetary gear rotates the fixed gear [20] on the output shaft (2), and low-speed rotation is transmitted to the output shaft.

Further, the high speed of the sub-shift can be obtained by making the internal gear (Inc.) unrotatable by the hydraulic cylinder (Y).

As a result, the planetary gear 131 rotates the output shaft (2) according to the rotation difference.
) of the fixed gear above ), and a high speed sub-shift can be obtained.

Select the main gear with the hydraulic cylinder (A)) (B),
By selecting the auxiliary gear stage with the hydraulic cylinders ((A) and (Y), four forward gears and two reverse gears are shifted. In order to select the hydraulic cylinder, two sets of hydraulic valves (V
l) (B3) is provided.

When the hydraulic pulp (B2) for the main transmission and the hydraulic valve (B3) for the auxiliary transmission are operated by sliding the spool (4η) of the hydraulic pulp (B2) for the main transmission with one transmission lever, By sliding the cam (C) fixed to this,
The sub-shift hydraulic valve (B3) is also configured to be operated at the same time.

This will be explained with reference to FIG.

The hydraulic pressure/cruise that controls the pressure of the hydraulic pump (P) includes a check pulp (Vl), a hydraulic knob for main transmission (Vl), a hydraulic knob for auxiliary transmission (B3), and an automatic control pulp (V4XV5). , and automatic control (B4)
(B5) Fully operated solenoid valve (SVI) (S
V2) is provided.

The cam (C) is provided with a groove and a protrusion, so that the gear position (B4) ( fz)
At the position (B2), the cam (C) is configured as a protrusion, and conversely, at the position (B3) (fz) (rt), it is a groove. Then, by pushing the spool of the ball (4g) and check valve (Vl), the pressure oil of the pump (P) is sent to the port (P3') of the hydraulic valve (B3) for the auxiliary transmission. We are switching between oiling and not oiling.

The ball (49) of the check valve (B1) is (B4) (
When pushed into the protrusion of fz) (B2), Che.7
The spool haze of Kunokurupu (B1) resists the spring (6]) and opens the bottom (Pi), and connects the hydraulic pressure for the sub-transmission to the boat (P3'') of Pulp (B3). Sends pressure oil,
The spool of (B3) (4 camphors slide to the left against the spring (60) and the port shown in Figure 2), (B3) and the boat (X8
) are connected, the hydraulic cylinder (X) is connected, and the second
From the low speed of the auxiliary gear shown in the figure, Pau) (B3) and Pau)
(B3) communicates through the through hole in the spool (48), thereby switching to the high position of the sub-shift.

With this structure, when the cam (C) is operated together with the hydraulic pulp (Vl), the auxiliary gear changes instantaneously between high and low levels due to the grooves and protrusions of the cam (C).

Hydraulic pulp for main transmission (■ in Fig. 2)
2) Boat, (A2) Boat, (B2) Boat, (R2
) All boats are connected to the drain boat and are neutral (N)
maintains the state of

When the spool (47) is slid to the left from this state,
The (B2) boat and the (RZ) boat communicate through the through hole of the spool (471), and the speed becomes astern (rIXr2).

When the spool (47) is moved a little to the right from the state shown in FIG. 2, the (B2) boat communicates with the (A2) boat and becomes the (f 1 ) (f x ) stage with a low forward speed. Furthermore, if you slide the spool (4η further to the right), (B2)
The port and (B2) port communicate, and the forward wave speed (f 3
) (f 4 ).

The cam (C
), it is necessary to provide a groove and a protrusion on the spool (4).
The spacing between the lands and paths of η is twice the spacing of the conventional one.

In such a configuration, the present invention further includes this main transmission hydraulic pulp (■2) and a hydraulic cylinder (A) (
An automatic control valve (Vs) is interposed between R) and (B), and a hydraulic pulp (Vs) for auxiliary transmission and a hydraulic cylinder (X
) (Y) is interposed with an automatic control valve (■4).

The automatic control valve (V4) is operated using the solenoid valve (S
The automatic control valve (5) is configured to perform switching by a solenoid valve (SV2).

The solenoid valve (SVz) has a gear position (fz).
(f3) (f4), the engine speed is constant (
M) Constructed to allow pressure oil to pass through when lowered. (19V1) is configured to be excited when the engine speed drops by (M) when the gear position is (fl).

Then, the gear stage is (fl) (N) (rl) (
In the case of r2), a prohibition circuit is provided in the controller (
SVz ), (SVr is configured so that it does not operate. In that case, the automatic control valve (V4) (Vs)
It is pushed to the normal position by the spring 162) [63), and no downshift is performed.

Also, if the transmission system is equipped with a manual/automatic changeover switch, if you set it to manual (SVI) (SV2)
is not energized under any circumstances. Automatic control valve (V
s) (V4) has a spring in the normal position +63+ +62
It is pushed to 1 and does not move.

When the automatic control switch is turned on and the gear is set to (fl), the load is applied to such an extent that the engine speed drops. The spring is energized and high pressure oil enters the (P4') port of the automatic control valve (V4).
621, the spool moves to the left, and the spool (6
5) becomes the inverted position. Then, the state in which the pressure oil in the (Pz) port was in the hydraulic cylinder (Y) is switched b, and the pressure oil in the (Pt) port is in the hydraulic cylinder (X).
), and the sub-shift becomes low speed. (fl) is automatically shifted down to (fl).

Also, when the gear position is (f3), the engine speed is (
M) When the solenoid valve (SVl) (SV
4) are both energized, the automatic control valve (■5) is reversed, and the high forward gear of the main transmission is switched to the low forward gear.
The automatic control valve (■) is also reversed, the high speed of the sub-shift becomes low speed, and ('') is shifted up to (fl).

Similarly, if the gear is set to (f4) and set to automatic, the engine speed will drop below (c), causing (EIVI).
is energized, the automatic control valve (■4) is reversed, and the auxiliary gear is switched from high speed to low speed, and the gear changes from (f4) to (f
This falls to 3).

When the load is reduced from the downshifted state and the engine speed exceeds (M), the solenoid pulp (SVI)
(SV'z) (7) When the excitation is cut off, the automatic control valves (v4) (■5) are automatically restored (by the spring connection), and the gear is shifted up and returned to the predetermined gear position.

As described above, the present invention includes an automatic control valve interposed between a hydraulic pulp for selection operation and a hydraulic clutch device in a transmission that selects a gear train and changes speed by a selection operation of a hydraulic clutch device. , the hydraulic pulp for selection operation remains in the same position, and the automatic control pulp is changed according to load fluctuations to select the gear connection, so the engine rotation can be sensed by the rotation speed sensor during work, By operating the automatic control valve, it is possible to automatically shift down from the gear set on the front gear shift lever to one gear lower depending on the increase or decrease in load, and when the overload subsides, the shift lever will shift back to the set gear. can be automatically reverted to
This eliminates the need for the operator to perform sophisticated operations such as checking the engine status and quickly downshifting.

In addition, automatic control valves and solenoid pulps for performing these operations are attached to hydraulic pulps for selective operations.
Since it can be removed, it can be installed later as an option, and by removing the automatic control pulp and solenoid pulp, it can be returned to a normal hydraulic clutch type transmission.

[Brief explanation of drawings]

FIG. 1 is a side sectional view of a planetary gear type hydraulic clutch type transmission. FIG. 2 is a hydraulic circuit diagram in which the automatic load control device of the present invention is attached to the transmission device of FIG. 1. (■1)...Check pulp (■2)...Hydraulic pulp for main shift (V3)...Hydraulic pulp for sub-shift (V4) (V5)...Automatic control pulp (SVz
) (SVI)...Solenoid pulp applicant Yanmar Diesel Co., Ltd. agent Patent attorney Toshikazu Yano

Claims (1)

[Claims] In a transmission that selects a gear train and changes speed by selecting a hydraulic clutch device, an automatic control valve is interposed between the hydraulic valve for selection operation and the hydraulic clutch device. An automatic load control device for a transmission, characterized in that the automatic load control device for a transmission is configured to select gear connections by switching automatic control valves according to changes in load while maintaining the same position.