KR20000011894A - Lever type signal generator - Google Patents

Abstract

PURPOSE: A lever type signal generating apparatus is provided to simultaneously generate a fluid pressure signal and an electric signal according to a slope motion amount. CONSTITUTION: The lever type signal generating apparatus comprises:an operating lever(60) installed capable of performing a slope motion with regard to a body(1); a pair of operating loads(100) installed capable of moving along a central axis direction of the body(1), wherein the operating loads(100) are displaced in correlation with an inclination motion of the operating lever(60); and a fluid pressure signal generating part for generating a fluid pressure signal corresponding to a displacement amount of the operating loads(100), wherein a potential difference meter(140) is installed outside one of the operating loads(100) and generates an electric signal corresponding to a displacement amount of the operating load(100).

Description

Lever type signal generator

The present invention relates to a lever-type signal generating device that generates a signal corresponding to the amount of inclination movement of the operation lever by tilting the operation lever. More specifically, this operation is performed when a single operation lever is tilted. The present invention relates to an improvement of a lever-type signal generator for simultaneously generating an oil pressure signal and an electric signal according to an inclination momentum of a lever.

(Conventional technology)

There is provided a lever-type signal generator that generates a hydraulic signal and an electric signal at the same time by operating a tilting operation of a single operation lever and controls individual control targets by these control signals.

In this kind of prior art, for example, there is one illustrated in Japanese Patent Application Laid-Open No. 7-116729.

In this prior art, a brush is provided through an insulator on an actuating rod that reciprocates in accordance with an inclination movement of the operating lever and induces pilot oil pressure, and a resistance element is provided in the main body of the apparatus. The contact position between the brush and the resistance element is changed by the movement of the working rod, so that the electric signal is generated together with the hydraulic pressure signal in accordance with the amount of tilting movement of the operating lever.

According to this conventional technique, for example, the main pump controls the operation of the switching valve for the main work machine of a construction machine on the basis of a hydraulic signal, and controls the valve which adds or subtracts the discharge amount of the main pump based on the electric signal. The complicated control of operating the main work machine while changing the discharge amount of the gas can be made to operate the inclined movement of the single operation lever. Therefore, the operability can be remarkably improved.

In the above-mentioned prior art, in order to generate an electric signal together with a hydraulic signal, the process of attaching a brush to a working rod and the process of installing a resistance element in the apparatus main body are separately required. For this reason, manufacturing work is complicated.

Moreover, in the prior art, a brush and a resistance element are installed in the working rod and the apparatus main body that move relative to each other, and furthermore, the brush and the resistance element are always slidably contacted while they are relatively moving. You must put it. For this reason, for example, when a dimension error or an assembly error occurs, the electric signal output is directly affected. Therefore, there is a problem in terms of reliability.

In addition, it is necessary to remove the operating rod from the apparatus main body in the case of adjusting the output voltage of the electric signal in the shipment inspection or performing maintenance inspection work. Therefore, it is also very disadvantageous in terms of workability.

In addition, in the prior art, when the rate of change of the electrical signal or the reference output voltage of the electrical signal to be changed with respect to the inclination momentum of the control lever is changed, the position of the brush with respect to the operating rod with the operating rod removed from the main body of the apparatus is changed. It is necessary to change or change the arrangement position of the resistance element with respect to the apparatus main body. In addition, after changing the placement of the brush or resistor element, it is necessary to test the work rod by putting it in the body of the device each time. Therefore, a remarkably complicated work is required.

An object of the present invention is to provide a lever-type signal generator capable of outputting an electrical signal together with a hydraulic signal without preventing the manufacturing work and maintenance inspection work from being complicated, and without compromising reliability.

(Means to solve the task)

In the invention described in claim 1, the operation lever 60 provided on the apparatus main body 1 so as to be inclined is movable, and the apparatus main body 1 is provided to be movable along the axial direction, and the operation lever ( 60 is driven by a pair of actuating rods 100 and a pair of actuating rods 120 which are correlatedly displaced in accordance with the inclined motion of the inclined motion and generates a hydraulic signal corresponding to the displacement of the actuating rod 120. In the lever-type signal generator provided with the hydraulic signal generating means, a potentiometer 140 is attached to an outer peripheral portion of any one of the pair of operating rods 100 in the apparatus main body 1. And an electric signal corresponding to the displacement of the working rod 110 is generated from the potentiometer 140.

In the invention described in claim 2, the potentiometer 140 according to claim 1 has a rotating shaft 142 and is coupled to the working rod 110 through an arm 143 provided on the rotating shaft 142. In addition, what provided the rotation angle changing means which changes the rotation angle of the said arm 143 with respect to the displacement amount of this operation rod 110 is applied.

In the invention described in claim 3, the potentiometer 140 according to claim 1 or 2, wherein the potentiometer 140 has a rotation shaft 142, and the arm 143 provided on the rotation shaft 142 is used as the potentiometer 140. It is coupled to the actuation rod 110, and the thing installed so that the movement to the said apparatus main body 1 along the axial direction of the actuation rod 110 is applied.

In the invention described in claim 4, the hydraulic signal generating means and potentiometer according to any one of claims 1 to 3, respectively, are provided with respect to the control valves RV, UV, Vl. V2 provided in a common hydraulic circuit. It applies to outputting a control signal.

1 is a cross-sectional view showing an embodiment of a lever-type signal generator according to the present invention.

2 is a cross-sectional view showing a state in which the operation lever is tilted in one direction in the lever-type signal generator shown in FIG. 1;

3 is a cross-sectional view showing a state in which the operation lever is inclined in the other direction in the lever-type signal generator shown in FIG. 1;

4 is a bottom view of the lever-type signal generator shown in FIG. 1;

FIG. 5 is a view of the arrow V in FIG. 1. FIG.

6 is a cross-sectional view taken along the line VI-VI in FIG. 5.

FIG. 7A is an exploded cross-sectional view showing a working rod and a spool member which are commonly used in the lever type signal generator shown in FIG. 1; FIG.

FIG. 7B is an assembled sectional view showing an actuating rod and a spool member commonly used in the lever type signal generator shown in FIG. 1; FIG.

8 is a control circuit diagram of a hydraulic cylinder to which the lever-type signal generator shown in FIG. 1 is applied.

FIG. 9 is a graph showing a relationship between an inclination movement amount of an operation lever and an output voltage of an electric signal output from a potentiometer in the lever type signal generator shown in FIG. 1; FIG.

* Description of the symbols for the main parts of the drawings *

One… Device body 41c... Contact

41d... . Spool base 42. Pump pressure passage,

43.. Drain passage 44... Pilot hydraulic pipe,

45... Pilot pump 60.. joystick,

80... Pilot pipeline 100... Working rod,

110... Tip member 120... Shortening Member,

130... Spool 130a.. Randbu,

130e... Circumferential groove 130f... Communication Holes,

140... Potentiometer 142. Rotation axis,

143... Driving arm 147... Seam plate,

RV… Relief Valve UV… Unload valve,

V1, V2... Directional valve

EMBODIMENT OF THE INVENTION Hereinafter, this invention demonstrates this invention in detail based on drawing which shows an example of an Example.

1 is a cross-sectional view showing an embodiment of a lever-type signal generator according to the present invention.

FIG. 2 shows a state in which the operation lever is tilted in one direction in the lever-type signal generator shown in FIG. 1. FIG. 3 shows a state in which the operation lever is tilted in the other direction in the lever-type signal generator shown in FIG. 1. FIG. 4 shows the bottom of the lever-type signal generator shown in FIG. 1.

The lever-type signal generator illustrated here is for controlling two hydraulic cylinders C1 and C2, as shown in the control circuit diagram of FIG. When applied to a hydraulic excavator, for example, the hydraulic cylinder Cl becomes the boom cylinder hydraulic cylinder C2 as the arm cylinder. The lever signal generator is installed in the driver's seat of the hydraulic excavator.

As shown in FIGS. 1-4, in this lever type signal generator, the upper main body block 10, the mounting plate 20 attached to the upper surface of this upper main body block 10, and the intermediate | middle plate 30 are shown. The lower body block 40 attached to the lower surface of the upper main body block 10 and the lower plate 50 attached to the lower surface of this lower main body block 40 are comprised, and the apparatus main body 1 is comprised. .

The mounting plate 20 is provided with an inclined tip member 23 through the first support shaft 22 in the cross-shaped bracket 21 provided at the upper center portion thereof. Furthermore, the operation lever 60 is attached to this inclined tip member 23 via the second support shaft 24.

The second support shaft 24 is parallel to the upper surface of the mounting plate 20 and perpendicular to the ground. The second support shaft 24 rotatably supports the operation lever 60 with respect to the inclined motion tip member 23 about its axis. That is, the operation lever 60 can be inclined in the left-right direction in FIG. 1 by rotating about the axial center of the 2nd support shaft 24. As shown in FIG.

The first support shaft 22 is parallel to the upper surface of the mounting plate 20 and is perpendicular to the second support shaft 24. The first support shaft 22 is rotatably supporting the inclined tip member 23 with respect to the bracket 21 in an intersecting shape. That is, the operation lever 60 can be inclined in the direction orthogonal to the ground in FIG. 1 by rotating around the axis of the first support shaft 22 like the inclined movement member 23.

Accordingly, the operation lever 60 can be inclined in two directions perpendicular to each other with respect to the apparatus main body 1.

This operation lever 60 is provided with the operation shaft member 61 which hold | maintains the 2nd support shaft 24 mentioned above at the base end part. The cam disk plate 62 and the knob mounting nut member 63 are attached to the threaded portion of the operation shaft member 61. The cam disk plate 62 is along the direction orthogonal to the axial center of the operation shaft member 61.

The knob mounting nut member 63 of the operation lever 60 is also equipped with a knob N (see FIG. 8) for the operator to grip the operation.

In addition, two pairs of insertion holes 11, 25, 31, 41, and 51 penetrate the apparatus main body 1 at a portion located around the cross-shaped bracket 21.

The insertion hole 25 of the mounting plate 20 and the insertion hole 11 of the upper body block 10 and the insertion hole 31 of the intermediate plate 30 and the insertion hole 51 of the lower plate 50 are respectively It is a round hole.

The insertion hole 41 of the lower main body block 40 has an oil seal mounting portion 41a, a spring accommodating portion 41b, a contact portion 41c, and a spool support portion 41d.

The insertion hole 25 of the mounting plate 20 is a diameter thinner than the insertion hole 11 of the upper main body block 10. In addition, the insertion hole 31 of the intermediate plate 30 is a diameter thinner than the insertion hole 11 of the upper main body block 10.

The oil seal mounting portion 41a is larger in diameter than the insertion hole 11 of the upper body block 10. The spring receiving portion 41b has the same inner diameter as the insertion hole 11 of the upper body block 10. The contact portion 41c is thinner than the spring accommodating portion 41b. The spool support portion 4ld has the same inner diameter as the contact portion 41c.

The insertion hole 51 of the lower plate 50 is larger in diameter than the spool support portion 41d.

These two pairs of insertion holes 11, 25, 31, 41, 51 are arranged at equal intervals on the circular arc centered on the intersection with the 1st support shaft 22 and the 2nd support shaft 24. As shown in FIG. The insertion holes 11, 25, 31, 41, and 51 are paired with each other to be positioned on the axial extension of each of the support shafts 22, 24.

As shown in FIG. 1, the support ring 71 is provided in the oil seal mounting part 41a in the insertion hole 41 of the lower main body block 40, respectively. In addition, the flag 81 of the pilot conduit 80 is connected to the insertion hole 51 of the lower plate 50, respectively.

The support ring 71 has an inner diameter smaller than that of the spring accommodating portion 41b, and holds the oil seal 70 on the inner circumferential surface.

As shown in FIG. 8, the pilot pipe line 80 is for supplying pilot pressure to the direction control valves Vl and V2 provided in the hydraulic cylinders C1 and C2, respectively.

The pilot conduits 80 are paired each time corresponding to the pair of insertion holes 11, 25, 31, 41, and 51. The pair of pilot conduits 80 located on the axial extension line of the first support shaft 22 are connected to pilot holes of one of the directional control valves V1, respectively. The pair of pilot pipe lines 80 located on the axial extension line of the second support shaft 24 are connected to pilot holes of the other direction control valve V2, respectively.

Moreover, the said operation | movement main body 100 is provided in the said apparatus main body 1 in the site | part from the insertion hole 11 of the upper main body block 10 to the accommodating part 41b of the lower main body block 40, respectively. Furthermore, the spool 130 is provided in the part which reaches from the spring accommodating part 41b to the insertion hole 51 of the lower plate 50, respectively.

As shown in FIGS. 1, 7A, and 7B, the actuating rod 100 includes a tip shaft member 110 and a base shaft member 120 each formed separately from each other. These tip members 110 and base shaft members 120 are bonded to each other.

The tip shaft member 110 is formed by integrally forming the contact rod portion 110a and the coupling rod portion 110b. The contact rod part 110a is a diameter slightly smaller than the insertion hole 25 of the mounting plate 20. The tip end of the contact rod part 110a is spherical. The engaging rod portion has the same circumferential shape as the insertion hole 11 of the upper body block. The engaging rod portion 110b is provided with an annular engaging groove 110C on the outer peripheral surface of the intermediate portion.

In addition, a center hole 110d is opened in the tip end member 110 in the base end surface 11e of the coupling rod part 110b.

As is also clear from Fig. 1, the tip shaft member 110 has a shorter overall length than the insertion hole 11 of the upper body block 10 in the engaging rod portion 110b. The tip shaft member 110 can move in the axial center direction in the insertion hole 11 of the upper body block 10.

The base shaft member 120 is formed by integrally forming the guide rod portion 120a, the first piston cap portion 120b, and the second piston cap portion 120c. The guide rod portion 120a is slightly smaller in diameter than the center hole 110d of the tip shaft member 110. The first piston cap portion 120b is cylindrical in pressure contact with the oil seal 70. The second piston cap portion 120c has the same cylindrical shape as the spring receiving portion 41b of the lower body block 40.

In addition, a spring accommodation hole 120e is opened in the base end member 120 in the base end surface of the second piston cap 120c. Furthermore, the spool movable hole 120f opens in 120 g of internal upper walls of the spring accommodation hole 120e.

As is also clear from FIG. 1, the length of the second piston cap portion 120c is shorter in the axial direction than the spring receiving portion 41b of the lower body block 40. The second piston cap portion 120c can be moved in the axial direction in the spring receiving portion 41b of the lower body block 40.

All lengths of the 1st piston cap part 120b are longer than the oil seal mounting part 41a of the lower main body block 40. FIG. When the front end surface of the 2nd piston cap part 120c abuts on the base end surface of the support ring 71, this 1st piston cap part 120b protrudes into the insertion hole 11 of the upper main body block 10. As shown in FIG.

The spool 130 is formed by integrally forming the land portion 130a, the vertical shaft portion 130b, the holding shaft portion 130c, and the head shaft portion 130d. The land portion 130a is almost the same outer diameter as the spool support portion 41d of the lower body block 40. The speech shaft portion 130b is thinner than the land portion 130a. The holding shaft portion 130c is smaller in diameter than the speech shaft portion 130b.

The head shaft portion 130d has the same outer diameter as the speech shaft portion 130b. This spool 130 is provided to be movable to the spool support part 41d via the land part 130a.

As is clear from the figure, the spool 130 is formed with a circumferential groove 130e on the outer circumferential surface of the land portion 130a. Moreover, the communication hole 130f is formed in the part from the base end surface to the said circumferential groove 130e.

The guide rod 120a is inserted into the center hole 110d of the tip shaft member 110 through the following spring 121.

The following spring 121 has a length longer than that of the central hole 11d of the tip shaft member 110. The following spring 121 always pushes the tip shaft member 110 toward the tip with respect to the base shaft member 120.

The spool 130 holds the spring sheet 131 to the holding shaft portion 130c so as to be movable. The spring sheet 131 is fitted into the spring hole 120e. A peeling spring 132 is interposed between the bottom wall of the spring accommodating portion 41b and the spring sheet 131.

The peeling spring 132 has length longer than the said spring accommodating part 41b. The peeling spring 132 has a spring force sufficiently larger than the following spring 121 mentioned above. The peeling spring 132 pushes the spring seat 131 on the inner upper wall of the second piston cap 120c. Moreover, the 2nd piston cap part 120c of the base end shaft member 120 is always pressed against the base end surface of the support ring 71 via the spring seat 131. As shown in FIG.

The spool 130 has a pressure setting spring 133 interposed between the front end face of the land portion 130a and the spring sheet 131.

The pressure setting spring 133 has a spring force sufficiently smaller than the peeling spring 132. The pressure setting spring 133 always pushes the spool 130 toward the proximal end with respect to the spring seat 131.

As for the circumferential groove 130e, the spring seat 131 pushes against the inner upper wall of the second piston cap part 120c and the second piston cap part 120c of the base end shaft member 120 abuts against the base end surface of the support ring 71. In the closed state, it is located in the engagement portion between the spring receiving portion 41b and the contact portion 41c of the lower body block 40. Further, these spring receiving portions 41b and the contact portions 41c communicate with each other. At this time, the spring receiving portion 41b and the insertion hole 51 of the lower plate 50 communicate with each other through the communication hole 130.

On the other hand, in the lever-type signal generator, pump pressure passages 42 and drain passages 43 are formed inside the lower body block 40, as shown in Figs. In addition, the upper body block 10 is provided with a potentiometer 140, one for each of the pair of operating rods 100.

The base end of the pump pressure passage 42 is connected to the pilot pump 45 through the pilot hydraulic pipe 44 after opening to the side surface of the lower main body block 40.

The front end of the pilot passage 44 branches into four inside the lower main body block 40, and each of them opens to the circumferential surface of the spool support portion 41d.

The base end of the drain passage 43 is opened to the side surface of the lower main body block 40 and is connected to the working oil tank 47 through the drain pipe passage 46.

The front end of the drain passage 43 branches into four inside the lower main body block 40, and each of them opens to the circumferential surface of the spring accommodating portion 41b.

FIG. 5 is a V view at the arrow in FIG. 1. FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG. 5.

As shown in FIG. 1 and FIGS. 4-6, the potentiometer 140 is equipped with the rotating shaft 142 provided in the center part of the main body 141, and the drive arm 143 provided in this rotating shaft 142, respectively. do. The potentiometer 140 outputs a control signal corresponding to the swing position of the drive arm 143 relative to the main body 141 to the valve control unit VC (see FIG. 8), respectively.

As is also clear from FIG. 1, each of the potentiometers 140 has each main body 141 held on a separate adjustment bracket 144.

The adjustment bracket 144 has a length hole 144a in each flange. The adjustment bracket 144 is provided with a shim plate (rotation angle changing means) 147 between the flange and the flange 144. Furthermore, each potentiometer 140 is holdably adjustable by fastening the screws 146 to the common unit plate 145 through the length hole 144a.

These potentiometers 140 are attached to the upper body block 10 so that the unit plate 145 faces the insertion holes 11 which are provided adjacent to each other of the upper body block 10. Furthermore, the distal end portions of the driving arms 143 are engaged with the engaging grooves 110c of the corresponding working rods 100 through the engaging openings 145a formed in the unit plate 145, respectively. Reference numeral 148 in the figure denotes a unit cover covering each potentiometer 140.

Hereinafter, the operation of the lever-type signal generator will be described.

1 shows a state where the operation lever 60 is in neutral. In this neutral state, the 2nd piston cap part 120c of each operation rod 100 is pressed against the base end surface of the support ring 71 by the peeling spring 132. As shown in FIG. Further, the tip shaft member 110 of each working rod 100 is pushed against the cam disc plate 62 through each contact rod portion 110a by the following spring 121. By the action of these peeling springs 132 and the following spring 121, the axial center of the operation shaft part 61 follows a perpendicular direction.

In this state, the circumferential groove 130e of the spool 130 provided in each of the operation dogs 100 is located at the engagement portion between the spring receiving portion 41b and the connecting portion 41c of the lower main body block 40. Therefore, the spring receiving portion 41b and the insertion hole 51 of the lower plate 50 communicate with each other.

As a result, all pilot pipe lines 80 and 80 'become drain pressure. Each of the directional control valves V1 and V2 of the hydraulic cylinders C1 and C2 is held in neutral, and the hydraulic cylinders C1 and C2 do not operate.

Next, the operation in the case where the operation lever 60 is tilted around the axis of the second support shaft 24 in the above-described state will be described.

As shown in FIG. 2, when the operation lever 60 is tilted toward the right around the axis of the second support shaft 24, the operation rod 100 on the right side is lowered through the cam disc plate 62. Move.

At this time, the operation force for moving the operation rod 100 downward is to resist the pushing force of the peeling spring 132 installed on the operation rod 100 on the right. In addition, the downward movement amount of the actuating rod 100 depends on the amount of inclination movement of the operation lever 60.

When the operation rod 100 on the right side moves downward, the spool 130 on the right side moves downward according to the amount of inclination movement of the operation lever 60 by the pushing force of the pressure setting spring 133. Since the circumferential groove 130e is located in the pump pressure passage 42, the pump pressure passage 42 and the insertion hole 51 of the lower plate 50 communicate with each other through the communication hole 130f.

As a result, the pilot pressure is supplied to one pilot hole of the direction control valve VI through the pilot pipe line 80. The other pilot hole of this direction control valve V1 becomes a drain pressure, as mentioned later. For this reason, the direction control valve VI moves left and the hydraulic cylinder C1 extends | stretches.

The pilot pressure supplied through the pilot conduit 80 is determined by the balance between the force that tries to move the spool 130 upward by the hydraulic pressure of the pilot conduit 80 and the pushing force of the pressure setting spring 133. do. In other words, the pilot pressure is in accordance with the amount of inclination of the operation lever 60.

At this time, in the operation rod 100 on the left side, the proximal end member 120 is proximal end face of the support ring 71 through the stepped portion 120h between the second piston cap 120c and the first piston cap 120b. Maintain a position in contact with

Therefore, the other pilot hole of the direction control valve VI becomes drain pressure like the neutral state mentioned above.

In addition, the tip shaft member 110 is moved upward by the pushing force of the following spring 121 interposed between the base shaft member 120 and is always in contact with the cam disk plate 62. .

Next, the operation | movement in the case of removing the operation force which tilted the operation lever 60 from the state shown in FIG. 2 is demonstrated.

When the operation force of the operation lever 60 is removed, the base end shaft member 120 moves upward by the pushing force of the peeling spring 132. Moreover, the cam disk plate 62 is pushed upward through the tip shaft member 110. Therefore, the process returns to the neutral state shown in FIG.

As a result, the pilot holes of the direction control valve V1 become drain pressure, respectively. Therefore, when the direction control valve VI returns to the neutral position, the hydraulic cylinder C1 stops in the extended state.

Next, the operation in the case where the operation lever 60 is tilted toward the left around the axis of the second support shaft 24 will be described.

When the operation lever 60 is inclined to the left side, as shown in FIG. 3, the operation rod 100 on the left side moves downward through the cam disc plate 62. When the working rod 100 moves downward, the spool 130 on the left side moves downward by the pushing force of the pressure setting spring 133. Therefore, the space between the pump pressure passage 42 and the insertion hole 51 of the lower plate 50 communicates with each other through the circumferential groove 130e and the communication hole 130f.

As a result, the pilot pressure is supplied to the other pilot hole of the direction control valve V1 through the pilot pipe line 80 '. One pilot hole of this directional control valve V1 is a drain pressure, the directional control valve V1 is bypassed, and the hydraulic cylinder Cl degenerates below.

During these operations, the potentiometer 140 is operated in accordance with the displacement amount of the tip shaft member 110 in the working rod 100. From the operated potentiometer 140, an electric signal corresponding to the amount of tilt movement of the operation lever 60 is output. This electric signal is output to the valve control unit VC. That is, when the operation lever 60 is tilted toward the right around the axis of the second support shaft 24, the driving arm 143 rotates counterclockwise by the downward movement of the tip shaft member 110. When the operation lever 60 is tilted toward the left around the axis of the second support shaft 24, the driving arm 143 rotates clockwise by the upward movement of the tip shaft member 110. Therefore, the control signals corresponding to the swing positions of the drive arm 143 relative to the main body 141 are respectively output to the valve control unit VC.

The valve control unit VC given an electric signal has an unload valve UV for controlling the supply pressure from the main pump 150 and a relief valve RV for setting the highest supply pressure from the main pump 150, respectively. Individual control is performed based on the output signal from the potentiometer 140. The operating characteristics of the hydraulic circuit are changed by changing the set pressure of these valves UV and RV.

As a result, the valve control unit VC makes it possible to change the set pressures of the unload valve UV and the relief valve RV in accordance with the inclination movement amount of the operation lever 60.

Therefore, for example, when the set pressure of the unload valve UV is changed in proportion to the inclination movement amount of the operation lever 60, it is possible to reduce energy waste when the inclination movement amount of the operation lever 60 is small. The operability when the inclination movement amount of the operation lever 60 is large can be improved. It is also possible to change the operating characteristics in the same hydraulic circuit.

In this case, even if a failure occurs in the electric signal system, for example, it does not affect the basic operation of the operation of the hydraulic cylinder C1. Therefore, even when applied to a hydraulic excavator, there is no risk of compromising reliability.

In addition, according to the lever-type signal generator, a unitized potentiometer 140 is provided in the apparatus main body 1. Therefore, manufacturing work and maintenance inspection work are not complicated. In addition, the reliability of the electrical signal output from the potentiometer 140 is improved.

Furthermore, since only one potentiometer 140 is provided for the pair of operating rods 100 that are correlated and displaced, it is possible to reduce the size of the device and reduce the number of parts.

By the way, as shown by the broken line in FIG. 9, the ratio of the change of the electrical signal output from the potentiometer 140 with respect to the inclination momentum of the operation lever 60 is changed, or operation is shown by the dashed-two dotted line in the figure. It is necessary to change the reference output voltage of the electrical signal output from the potentiometer 140 with respect to the tilt movement amount of the lever 60.

In this case, first, by changing the thickness of the shim plate 147 interposed between the unit plate 45 and the adjustment bracket 144, the shaft center of the rotating shaft 142 and the operating rod (in the potentiometer 140) ( The distance between the shaft center of 100) is changed. Furthermore, the drive arm 143 is changed to one of a different length.

As a result, the rotation angle of the drive arm 143 with respect to the displacement amount of the tip shaft member 110 in the actuating rod 100 can be easily changed. Therefore, it becomes possible to easily adjust the ratio of the displacement amount of the electric signal output with respect to the tilt movement amount of the operation lever 60. In addition, application of an extension and contraction as the drive arm 143 of the potentiometer 140 makes it unnecessary to replace the drive arm 143 when changing the ratio of the displacement amount of the electrical signal to the tilt movement amount of the operation lever 60. . Therefore, the work can be further facilitated.

On the other hand, by changing the fastening position of the screw 146 with respect to the length hole 144a provided in the adjustment bracket 144, the swinging position of the drive arm 143 with respect to the main body 141 can be changed. Therefore, it becomes possible to change the reference output voltage of the electric signal with respect to the tilt momentum of the operation lever 60.

In addition, only the case where the operation lever 60 is inclined about the axis of the second support shaft 24 with respect to the operation of the lever-type signal generator is described. The same goes for the case of tilting in the direction of the side.

In addition, in the above-described embodiment, the operation lever 60 is exemplified by tilting around the axis of the first support shaft 22 and the second support shaft 24. However, in the present invention, it is of course possible to apply also to tilt the operation lever 60 around the unique support shaft.

Moreover, although the above-mentioned embodiment illustrates the lever-type signal generator which outputs a control signal to the various control valves installed in the hydraulic circuit of the hydraulic excavator, it can of course also be applied to controlling other equipment. In this case, it is not always necessary to change the operating characteristics of the hydraulic circuit according to the amount of inclination of the operation lever 60. For example, when controlling two or more actuators simultaneously, the operation amount of each operation lever for each actuator is controlled simultaneously. By the combination of the actuator, it is also possible to control the operating characteristics of the hydraulic circuit.

According to the invention described in claim 1 of the present invention, an electric signal is output together with a hydraulic signal by providing a potentiometer in the apparatus main body.

Therefore, the manufacturing operation is not complicated. In addition, since the potentiometer is unitized, there is no fear that the reliability of the output electrical signal is lowered.

In addition, during maintenance work of the potentiometer, work such as removing the operating rod from the main body of the device is unnecessary, which is advantageous in terms of workability.

Furthermore, since one potentiometer is provided for a pair of correlated displacement working rods, it is possible to reduce the size of the device and reduce the number of parts.

According to the invention described in claim 2 of the present invention, the rotation angle of the arm with respect to the displacement amount of the working rod can be easily changed. Therefore, it becomes possible to easily adjust the ratio of the displacement amount of the electric signal output with respect to the tilt movement amount of the operation lever.

According to the invention described in claim 3 of the present invention, by moving the potentiometer relative to the apparatus main body, it becomes possible to easily adjust the reference output voltage of the electric signal output with respect to the tilting movement amount of the operation lever.

According to the invention described in claim 4 of the present invention, pressure control is performed, for example, to control the operation of the main direction control valve for the main work machine based on a hydraulic signal, and to add or subtract the discharge amount of the main pump based on an electric signal. By controlling the valve, it becomes possible to make a complicated control of operating the main work machine while changing the discharge amount from the main pump as the inclined motion operation of a single operation lever. Therefore, the operability can be remarkably improved.

Claims (4)

An operation lever 60 installed on the apparatus main body l so as to allow an inclined movement; A pair of actuating rods 100 mounted to the apparatus main body 1 so as to be movable along the axial direction, and correlatedly displaced according to the inclined motion of the operating lever 60; In the lever-type signal generating device which is driven by the pair of actuating rods 120 and has a hydraulic signal generating means for generating a hydraulic signal corresponding to the displacement amount of the actuating rod 120, An electric potentiometer 140 is provided in the outer peripheral part of the pair of the actuating rods 100 in the apparatus main body 1, and the electricity corresponding to the displacement amount of the actuating rod 110 from the potentiometer 140 is provided. A lever-type signal generator, characterized in that for generating a signal. The method of claim 1, wherein the potentiometer 140 has a rotating shaft 142, coupled to the operating rod 110 through the arm 143 installed on the rotating shaft 142, the working rod 110 And a rotation angle changing means for changing the rotation angle of the arm (143) with respect to the displacement amount of the lever. The method according to claim 1 or 2, wherein the potentiometer 140 has a rotating shaft 142, and is coupled to the operating rod 110 through an arm 143 installed on the rotating shaft 142, the operation A lever-type signal generating device, characterized in that the device is installed so as to move in the axial direction of the rod (110). The hydraulic pressure generating means and the potentiometer 140 respectively output control signals to control valves RV, UV, V1, and VZ provided in a common hydraulic circuit. Lever type signal generator, characterized in that.