JPS6236250B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a two-system operating mechanism capable of operating two systems of operated sources by unidirectional movement of one operating lever.

BACKGROUND ART Conventionally, there has been a mechanism that operates using a single lever as a two-system operating means. At this time, the operating direction of the operating lever is 360 degrees around the axis, that is, there are operating means in all directions and straight operating means in the vertical or horizontal direction. Further, the operation is transmitted to each system that is to operate based on the operation via a dedicated rod. However, these operating means are subject to limitations such as the large operating range of the operating lever and the need for a dedicated rod for each system to be operated, making it impossible to use them in places where the operating points are small. Furthermore, in locations where the system to be operated is remote, the specialized rods exhibit complicated movements, and the rods interfere with each other, making remote control impossible. However, since a large number of transmission means such as dedicated rods or wires are involved, there are problems such as difficulty in operating smoothly. For these reasons, it is effective to use an operating means in which one lever can be operated in only one direction, straight forward or straight backward, and can operate two operated systems.

FIG. 1 shows a schematic diagram of an already proposed rotation operation mechanism for a rotating drum in a concrete mixer vehicle. In the figure, concrete mixer truck 6
The rotation operation mechanism of the rotary drum 61 at 0 consists of control of the engine E, which is the operating source, and control of the oil pump OP, which operates by obtaining the driving force of the engine E. Because it is a special type of concrete mixer vehicle, especially when discharging fresh concrete, the operating location may vary depending on the discharge situation.
It is required to be able to operate at appropriate locations such as the front or rear of the vehicle, the front and rear sides of the vehicle, and the upper part of the chute near the discharge port. Therefore, the rear control lever 1 is provided at the minimum number of operating points, and the control lever 1A is provided in the driver's cab (cab) 64. These operating levers 1 and 1A operate in one direction: straight forward or straight backward.In particular, the rear control lever 1 has an operating range (A operating range) θ of the oil pump OP in the center as shown in Fig. 2. The two operating ranges of engine E (B operating range) θ _{1 and} θ ₁ adjacent to the operating limits C ₁ and D ₁ of A operating range θ are both limits A and A of the B operating range. The operating range of the rear control lever 1 is between. Therefore, the rotary drum 61 (first
Even though the rotation operation shown in the figure) is performed, if further rotation is required, the engine E is operated in the B operation range θ ₁ , θ ₁ . Further, as shown in FIG. 3, the in-cab control lever 1A has only the operating range of the oil pump OP (A operating range), and the operating range is between the two limits C ₂ and D ₂ of the A operating range. Inside the cab 64 (Fig. 1) is the engine E.
Since the operating mechanism is naturally provided as an accelerator lever, the control lever 1A having only the A operating range is sufficient. FIG. 4 shows a schematic configuration diagram of the operating mechanism in FIG. 1. In the figure 3
is a T-shaped counter lever, one end of which is connected to the rear control lever 1 via a connecting member, for example, a control cable 2, and the other end of which is provided with a rotating roller 4, which is connected to the escapement lever 5. It rolls in contact with the elongated hole 7 and the arcuate cam 8. In addition, escapement lever 5
is fixed to one end of the shaft body 19, and the pump lever 2
0 is fixed to the other end of the shaft body 19. The in-cab control lever 1A is connected to the tip of a limiter lever 12 via a control cable 21, and this lever 12 has a shaft support 22 that pivotally supports a shaft body 19. When the limiter lever 12 is tilted by the shaft body 19 and the shaft support 22, the rotating roller 15 at the tip of the elastaste lever 13 comes into contact with the elongated hole 17 of the limiter lever 12 due to the elasticity of the spring 16, as shown in FIG. Keep rolling. Furthermore, the other end 9 of the counter lever 3 is connected to the accelerator lever 11 of the engine E through an A release means consisting of a link part 23 having a pin 22 and a yoke part 25 having a long groove 24 that engages with the pin 22A. be done.

The movement of the limiter lever 12 operated by the in-cab control lever 1A configured as described above and transmitted to the elastane lever 13 is transmitted to the shaft body 14.
is transmitted to the counter lever 3 via. The counter lever 3 operates the escapement lever 5, transmits rotation to the pump lever 20 via the shaft body 19, and controls the control lever 10 to operate the oil pump OP (A operation) via the control cable 21A. transmitted to. At this time, as shown in FIG. 5, the limiter lever 12 is prevented from exceeding the A operation range by the stoppers 26, 26A.

The operation that the rear control lever 1 transmits to the oil pump OP within the operating range θ of A in FIG.
0. At the same time, the in-cab control lever 1A is interlocked from the counter lever 3 via the shaft body 14, elastane lever 13, and limiter lever 12. However, beyond the operation (A operation) range θ of the pump OP and in the accelerator operation (B operation) range θ ₁ of the engine E, the connection between the pin 22 of the link part 23, which is the A relief means, and the long groove 24 of the yoke part 25 is Due to the engagement, the A release B operation is performed. At this time, as shown in FIG. 6, by operating B of the rear control lever 1, the limiter lever 1
2 is a stopper 26 and an elastane lever 1
The rotating roller 15 of No. 3 comes into contact with the arc-shaped cam 18 of the limiter lever 12, and the limiter lever 12
There is no change in the operating angle, and the pump OP operation (A operation) remains at its maximum state even during accelerator operation (B operation). FIG. 7 shows an explanatory diagram of the operation of the A-operation B return mechanism, where A shows the normal operation and B shows the abnormal operation. In the figure, when the control lever 1A inside the cab operates normally in the forward and reverse directions, only the oil pump OP is operated (A operation), the engine E is in an idling state, and B
No operation is performed. Now, when the in-cab control lever 1A is rapidly operated, the four rear control levers 1 in FIG. 1 that are interlocked with this lever 1A are also rapidly interlocked. For this,
A large inertial force is generated in these levers 1. Due to the inertial force in the direction of the arrow P, the counter lever 3 moves to B
There was a drawback that the accelerator operating angle shifted to the accelerator operating angle shown in , and the accelerator lever 11 was operated and the engine E was revved up. In addition, in order to return the B operation state to the A operation state, the limiter lever 12 in FIG.
It was difficult to return the elastaste lever 13 in the direction of the arrow T unless a large rotational force S was applied to the elastaste lever 13.

In view of the above-mentioned points, it is an object of the present invention to provide a one-lever, one-way, two-system operating mechanism in which the control lever is easy to handle, its operation is reliable, and safe.

According to the present invention, this object is achieved by a U-shaped lever having an opening groove and rotating together with a counter lever, which slides along a slide guide connected to the second operating lever via a connecting member, and has one end. a slide yoke having a long groove that engages with the opening groove of the U-shaped lever and allows the shaft to rotate and slide freely; and an elastic member provided between the slide yoke and the slide guide. member, and by rapid operation of the second operating lever,
An overshoot operation is provided between the A and B operation ranges, which is applied to the B system operated source by an inertial force generated in the first operation lever transmitted through the slide boss, the U-shaped lever, and the counter lever. This is achieved by keeping it within the inoperable range and suppressing it with the elastic member.

Next, embodiments according to the present invention will be described in detail based on the drawings.

FIG. 8 is a schematic configuration diagram of an embodiment according to the present invention;
FIG. 9 is a schematic configuration diagram of the main part of FIG. 8, and FIG. 10 is a parts diagram of the main part. Figures 8 to 10
In the figure, parts having the same functions as in FIG. 4 are given the same reference numerals. A U-shaped lever 27 is fixed to one end of the shaft 14 that rotates the counter lever 3, and rotates together with the counter lever 3. The rotation roller 29 is provided at the lower end of the slide yoke 30, and
It rolls within the character-shaped opening groove 28. slide yoke 3
0 is a connecting fitting 4 that slides along the slide guide 31 and is provided at one end of the slide guide 31.
It is connected to the in-cab control lever 1A via a control cable 21 connected to 1. Additionally, an elastic member, such as a spring 33, is provided between the slide yoke 30 and the slide guide 31.
is provided, and its elasticity is adjusted by an adjustment screw 34. The shaft body 19, which rotatably slides in the long groove 35 provided in the slide yoke 30, transmits the rotation of the escapement lever 5 to the pump lever 20. Therefore, the slide yoke 30 slides along the slide guide 31 and is rotatable about the shaft body 19. This long groove 35 allows the slide yoke 30 to move when the slide yoke 30 moves in the arrow direction X shown in FIG.
The upper and lower limits of the stopper are formed. In particular, the lower limit of the long groove 35 determines the operating radius of the slide yoke 30. Further, the restoring force during this movement in the arrow direction X is provided by the spring 33.

Next, FIG. 11 shows an explanatory view of the operation of the main part in FIG. 8, where A indicates an operation within the A operation range, and B indicates an operation beyond the A operation range. In the figure, parts having the same functions as in FIG. 8 are given the same reference numerals. Cab control lever 1
When the slide guide 31 rotates in the arrow direction P1 due to A, the slide yoke 30 tilts until the slide guide 31 contacts the stopper 26 and is restrained from rotating. At this time, due to the engagement between the rotating roller 29 and the long groove 28 of the U-lever 27, the U-lever 27 also tilts about the shaft body 14.
This tilting of the U-lever 27 is transmitted to the counter lever 3, and operation A for operating the oil pump OP is performed. At the same time, the rear control lever 1 is interlocked with the in-cab control lever 1A. Note that the inclination angle of the slide yoke 30, at which the slide guide 31 is prevented from rotating by the stopper 26, is A ₀ , and the inclination angle of the U-lever 27 _{is A1} .
shall be. The positions of these inclination angles A ₀ and A ₁ are the maximum positions of the A operation.

However, when the in-cab control lever 1A is rapidly operated, a large inertial force Q is generated in the interlocking rear control lever 1, and the U-lever 27 is rotated about the shaft body 14 by this inertial force Q. Ru. Due to this rotation, the slide yoke 30 moves in the direction of the arrow U against the spring 33. Therefore, the U-lever 27 is within the A operation range.
A exceeds ₁ . However, if this U-lever 27 goes too far, it will cause the engine E to operate within the B operation range B ₁
In order to prevent the non-operating range D ₁ from reaching the A operating range
It is provided between A ₁ and B operation range B ₁ . Therefore, the width of the inoperative range D 1 is selected so that the U-lever 27 always remains within the inoperative range D ₁ and does not go too far into _the B operation range B ₁ . In addition, the inertia force against the inertia force Q of the spring 33 is adjusted by the adjustment screw 34, so that
It is pulled back from D ₁ to A operation range A ₁ , and A operation range A ₁
suppressed inward.

Next, FIG. 12 shows a force balance diagram of the slide yoke when the in-cab control lever is operated, where A indicates an increase in the A operating range and B indicates a decrease.
C is a state diagram of the slide yoke. In the figure
R ₁ and R ₂ are the operating direction of the slide yoke 30, L ₁ is the operating force of the slide yoke 30 in the arrow direction R ₁ ,
_K1 is the lower limit of the long groove 35 of the slide yoke 30,
This is a reaction force in the direction of the slide yoke 30 that is generated between the slide yoke 19 and the shaft body 19 located at the lower limit. M ₁ is a reaction force generated on the U-lever 27. Further, K ₂ is the reaction force against the spring 33 of the shaft body 19 located at the lower limit of the long groove 35 of the slide yoke 30, 1 and 2 are the operating forces of the slide yoke 30 in the direction of the arrow R ₂ , and M ₂ is the reaction generated on the U-lever 27. It is power. Now, at A, the spring 33 is pressed against the slide yoke 3 because the shaft body 19 is pressed to the lower limit of the long groove 35.
0 does not require elasticity to be able to hold the A operating radius. In order for the shaft body 19 to be located at the lower limit of the long groove 35 at point B and for the slide yoke 30 to maintain the operating radius A, the spring 33 requires a reaction force greater than the reaction force _K2 .

Next, Fig. 13 shows a force balance diagram of the slide yoke when operating the rear control lever, and A is B.
When increasing in the operating range, B is also decreasing, C
is a state diagram at the maximum position of B operation. In the figure
S ₁ and S ₂ are the operating directions of the U-lever 27, K ₃ is the reaction force against the spring 33 of the shaft body 19 located at the lower limit of the long groove 35 of the slide yoke 30, M ₃ is the operating force of the U-lever 27, and L ₃ is the spring reaction. This is a reaction force generated on the slide yoke 30 due to the component force of the force K ₃ and the U-lever operating force M ₃ . K ₄ is a reaction force in the direction of the slide yoke 30 that is generated between the lower limit of the long groove 35 of the slide yoke 30 and the shaft body 19 located at this lower limit. The spring 33 requires a reaction force greater than the reaction force K3 so that the shaft body 19 is positioned at the lower limit of the long groove 35 at A, and the slide yoke 30 maintains the A half-axis. In this case, in the mechanism shown in FIG. 8, the operating force received by the slide yoke 30 is only due to the weight of the control lever 1A in the cab and the frictional resistance of the control cable 21, and the reaction force L3 is extremely small. The drag force is small. In addition, in the mechanism shown in FIG. 15, the reaction force L3 of the slide yoke 30 is larger than that in the mechanism shown in FIG. 8 because the operating force of the pump is applied to the mechanism shown in FIG. Therefore, it is necessary to increase the resistance of the spring 33. At B, the spring 33 does not require elasticity for the slide yoke 30 to maintain the operating radius A because the shaft body 19 is pressed against the lower limit of the long groove 35. At C, the slide yoke 30 is held in the A operation range by the stopper 26, and the shaft body 19 is extended to the upper limit position of the long groove 35 by the B operation of the U-lever 27. Therefore, the U-lever 27 was previously operated B due to the resistance of the spring 33.

Next, FIG. 14 shows a configuration diagram of the embodiment shown in FIG. 8, in which A is a front view thereof, B is a side view thereof, C is a back view thereof, and D is a plan view thereof. In the figure, parts having the same functions as in FIG. 8 are given the same reference numerals. The unit frame 40 is provided with a shaft support that pivotally supports the shaft bodies 14 and 19.
A counter lever 3 is fixed to one end of 4. Further, the U-lever 27 is fixed to the other end via the unit frame 40. An escapement lever 5 that engages with the counter lever 3 is fixed to one end of the shaft body 19. The long groove 35 of the slide yoke 30 slidably slides on the shaft body 19 via the unit frame 40. Furthermore, a pump lever 20 shown in FIG. 8 is fixed to the other end of the shaft body 19.
Note that 41 is a connecting fitting provided on the slide guide 31 to which the control cable 21 is connected. This connecting fitting 41 allows the slide yoke 30 to tilt in an A operation range _A1 , as shown by the chain line. 42 is a connection hole for connecting the control cable 2 to the counter lever 3. The end portion 9 of the counter lever 3 and the B operation link portion 23 are connected by a universal joint 43 and a threaded rod 44. 45 is a link lever of the link portion 23. Reference numeral 46 denotes a hole position restraining plate in which a plurality of holes 47 are provided. A spherical body 48 is provided at the tip of the link lever 45 and is pressed by a spring (not shown).
7 for positioning. The width of the inactive range D1 between the A operating range _A1 and the B operating range _B1 is selected by adjusting the length l of the threaded rod 44.
By adjusting the length l, the pin 22 provided on the link lever 45 engages with the long groove 24 of the yoke portion 25 in FIG.
Perform operation B. Therefore, in the B operation range B1, the accelerator lever 11 of the engine E operates,
In the A operation range _A1 and the non-operation range D1,
Engine E continues to be in an idling state.

As explained above, according to the present invention, the excessive movement to the B system operated source due to the inertia force that may be generated in the interlocked rear control lever due to rapid operation of the control lever in the cab is prevented from occurring within the inoperable range. It stays at D1 and is pulled back to the A operating range by the spring's anti-inertia force, making it easy to handle the control lever inside the cab and making the operation safe and reliable.

[Brief explanation of the drawing]

Figure 1 is a schematic configuration diagram of the rotary operation mechanism that has already been proposed for a rotating drum in a concrete mixer vehicle, Figure 2 is an explanatory diagram of the operating range of the rear control lever, and Figure 3 is an explanatory diagram of the operation of the control lever in the cab. , FIG. 4 is a schematic configuration diagram of the operating mechanism in FIG. 1, FIGS. 5 and 6 are explanatory diagrams of the operation of the limiter lever and the elastane lever,
FIG. 7 shows an explanatory diagram of the operation of the A operation B return mechanism,
A is during normal operation, B is during abnormal operation, 8th
The figure is a schematic configuration diagram of an embodiment according to the present invention, FIG. 9 is a schematic configuration diagram of the main part of FIG. 8, FIG. 10 is a parts diagram of the main part, and FIG. 11 is the main part of FIG. An operation explanatory diagram is shown, A indicates operation within the A operation range,
B shows the movement beyond the A operating range, and Figure 12 shows the force balance diagram of the slide yoke when operating the control lever inside the cab.
is the same when decreasing, C is the state diagram of the slide yoke,
Fig. 13 shows a force balance diagram of the slide yoke when the rear control lever is operated, A is an increase in the B operation range, B is a decrease in the same range, C is a state diagram at the maximum position of B operation, and Fig. 14 is a state diagram of the 8 The configuration diagram of the embodiment shown in the figure is shown, in which A is a front view thereof, B is a side view thereof, C is a back view thereof, and D is a plan view thereof. 1: Rear control lever, 1A: Cab control lever, 3: Counter lever, 5:
Escapement lever, 10: Control lever, 11: Accelerator lever, 14, 14A, 1
9, 19A: Shaft body, 27: U lever, 30: Slide yoke, 33: Spring.

Claims (1)

[Claims] 1 A first operating lever 1 that moves straight forward or backward in one direction between an A operating range provided in the center and two B operating ranges adjacent to both operating limits of this A operating range.
and a second operating lever that moves straight forward or backward in one direction only in the A operating range, one end of which is connected to the first operating lever via the connecting member 2, and the other end of which is connected to the B via the A release means. a T-shaped counter lever 3 that connects only the operating range to the B-system operated source E;
An escapement lever 5 is provided with an elongated hole 7 and an arcuate cam 8 with which the other end of the counter lever engages, and one end is fixed to the escapement lever and the other end is connected to the A via a connecting member 21A. An operating mechanism consisting of a shaft body 19 that connects only the operating range to the A system operated source OP, a U-shaped lever 27 having an opening groove 28 and rotating together with the counter lever, and connecting with the second operating lever. Slide guide 3 connected via member 21
a slide yoke 30 having a long groove 35 that slides along the axis 1, one end of which engages with the opening groove of the U-shaped lever, and allows the shaft body 19 to rotate and slide; and an elastic member 33 provided between the slide yoke and the slide guide, and when the second operation lever is rapidly operated, the first A device characterized in that an excessive motion exerted on the B-system operated source by an inertial force generated in the operating lever is kept within an inoperable range provided between the A and B operating ranges, and is suppressed by the elastic member. One-way lever operation and two-system operation mechanism.