JP2012017626A - Work range control device of work machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve both workability and stability during work with a front device, regarding a work range control device of a work machine.SOLUTION: A work range control device of a work machine includes rotary attitude detection means 11L and 11R for detecting a rotary attitude of an upper rotary body in relation to a lower traveling body. The work range control device also includes first storage means 32 for storing a side work range as a work range of the front device and second storage means 33 for storing a front work range in which a horizontal distance from a machine body center of the work machine up to an outer end is set to be larger than the side work range as the work range of the front device. Further, the work range control device includes control means 37 for limiting the work range of the front device to limit the work range to the inside of the side work range when the rotary attitude is a side attitude. When the rotary attitude is a front attitude, the work range is expanded up to the inside of the front work range.

Description

  The present invention relates to a work range control device that controls a work range of a work machine including a front device.

  2. Description of the Related Art Conventionally, a dismantling machine equipped with a long dismantling-type front device composed of a boom, a jib, an arm, and a crusher has been developed. In such a working machine, the total length of the front device is long and the posture tends to become unstable. In view of this, a technique has been proposed in which the position of the center of gravity of the aircraft is calculated at any time to improve stability against falling.

  For example, a technique for issuing an alarm according to the position of the center of gravity of the aircraft is known. In this case, an angle sensor is provided at each joint portion of the front device, and the center of gravity position of the aircraft is calculated from the posture of the front device. Further, the support force of the stable fulcrum on the ground contact surface of the lower traveling body is calculated, and an alarm is issued when the support force at the stable fulcrum on the rear side of the machine body becomes a predetermined value or less (see Patent Document 1). By using such a technique, it becomes possible to display the supporting force and the center of gravity position at the stable fulcrum on the monitor and to inform the passenger of the stability of the aircraft.

  In addition, a technique for verifying the stability of the airframe by detecting the turning state of the front device has been proposed. For example, a technique for detecting the turning angle of the upper turning body with respect to the lower traveling body and stopping the drive of the attachment device provided at the front end of the front device when the turning angle is an attachment prohibition angle range θ that is not suitable for work. Is known (see Patent Document 2). If such a technique is used, it becomes possible to prohibit the operation | work at the turning angle from which an airframe becomes unstable.

JP 7-247578 A JP 2007-113246 A

  By the way, the traveling device provided in the lower traveling body of the work machine is formed such that the longitudinal dimension as the traveling direction is larger than the width direction, and the grounding surface of the lower traveling body is the vehicle width direction of the lower traveling body. Longer in the longitudinal direction than. Therefore, it is desirable that the control for ensuring the stability of the airframe is premised on the most difficult lateral orientation (the orientation in which the front of the upper turning body faces the vehicle width direction of the lower traveling body). Even in the technique as described in Patent Document 1 described above, control is performed so that a fall does not occur even if the vehicle is at least in a horizontal posture regardless of the turning angle.

  On the other hand, the stability of the airframe against overturning depends on the turning angle of the upper turning body relative to the lower traveling body. For example, in a forward-facing posture in which the front of the upper swing body is oriented in the front-rear direction of the lower traveling body, the stability is higher than in the lateral posture, and the front device can be extended further.

  However, in the conventional technology as described above, control in consideration of such characteristics is not performed, so even if the posture is a forward posture, the operation of the front device is restricted under the same conditions as in the horizontal posture. Will be. Therefore, even if the working posture is actually highly stable, the control on the stable side is always excessively performed, and there is a problem that the work range is narrowed and the workability is lowered.

One of the purposes of this case was devised in view of such problems, and the working range of the working machine that can improve the workability while improving the stability when working with the front device. It is to provide a control device.
The present invention is not limited to this purpose, and is a function and effect derived from each configuration shown in the embodiments for carrying out the invention described later, and other effects of the present invention are to obtain a function and effect that cannot be obtained by conventional techniques. Can be positioned.

(1) The work range control device for a work machine disclosed is a work range control device for a work machine including a lower traveling body that rotatably supports an upper swing body on which a front device is pivotally supported. That is, a turning posture detecting means for detecting a turning posture of the upper turning body with respect to the lower traveling body is provided. A first storage means for storing a side work range as a work range of the front device; and a horizontal distance from a machine body center to an outer end of the work machine as the work range of the front device. And a second storage means for storing the forward work range set to be larger than that. Furthermore, when the turning posture is a side posture facing the side of the lower traveling body, the working range of the front device is limited to the inside of the side working range, and the turning posture is the lower running body. Control means for expanding the work range of the front device to the inside of the front work range when the front posture is directed forward or rearward of the body.
For example, when the posture of the upper swing body is a forward posture, the front device is controlled to reach farther than when it is in a horizontal posture.

(2) An angle detection unit that detects a node angle of the front device and a position calculation unit that calculates the position of the front end portion of the front based on the node angle detected by the angle detection unit. In this case, when the turning posture is the lateral posture, the control means prohibits the operation of the front device in which the position calculated by the position calculating means exceeds the outer end of the lateral work range. When the turning posture is the front posture, the operation of the front device is permitted until the position calculated by the position calculating means does not exceed the outer end of the front work range.
(3) The control means prohibits the turning posture from being a posture other than the forward posture when the turning posture is the forward posture.

  (4) A plate member provided on one of the lower traveling body and the upper swing body, and a plate member provided on either one of the lower traveling body and the upper swing body so as to face the plate member, A proximity switch that detects a proximity state of the member, and a forward work switch that is operated in two on / off positions by a passenger of the work machine. In this case, when the proximity means is detected by the proximity switch and the front work switch is turned on, the position calculated by the position calculation means is the outer end of the front work range. The operation of the front device is allowed until the maximum value is not exceeded. Further, when the proximity state is detected by the proximity switch and the forward work switch is turned off, the control means performs the same control as when the turning posture is the side posture.

  (5) The front device has an arm connected to the distal end side and a boom connected to the proximal end side, and the angle detection means detects a node angle of each proximal end portion of the arm and the boom. To do. Further, a vertical movement switch that is operated to two positions of on / off by a passenger of the work machine is provided. In addition, when the arm is operated with the vertical movement switch turned on, the boom is operated simultaneously with the arm based on the nodal angle of the base end of the arm and the nodal angle of the base end of the boom. And trajectory control means for moving the tip of the arm in the vertical direction.

(6) The trajectory control means calculates target boom angular speed calculation means for calculating the target value of the angular speed of the boom, and calculates the target value of the expansion / contraction speed of the boom cylinder that drives the boom based on the target value of the angular speed. And target boom cylinder speed calculation means.
(7) When the turning posture is the lateral posture, the control means limits the minimum value of the base end elevation angle of the front device to a first predetermined value or more, and the turning posture is the forward posture. In this case, the minimum value is limited to a second predetermined value that is smaller than the first predetermined value.

  (8) A base end plate fixed to one of the base end portion of the front device and the upper swing body, and a base plate fixed to either the base end portion of the front device and the upper swing body, And a boom proximity switch for detecting the proximity state of the end plate. In this case, the control means controls the elevation angle of the front device based on the proximity state detected by the boom proximity switch.

  According to the disclosed working machine work range control device, when the turning posture of the upper swing body is a lateral posture, the working range of the front device can be narrowed to improve the stability. On the other hand, when the turning posture is the forward posture, the working range of the front device can be expanded farther than in the side posture, and workability can be improved while ensuring stability.

It is a side view of a hydraulic excavator provided with a work range control device. It is a schematic diagram which shows the working area of the front apparatus on the basis of the lower traveling body of a hydraulic excavator. It is a schematic diagram which shows the working radius of a hydraulic system. It is a hydraulic circuit diagram of a hydraulic excavator. It is a block block diagram for demonstrating the controller of a hydraulic shovel. It is a side view for demonstrating the parameter regarding the attitude | position of the front apparatus of a hydraulic shovel. It is a ladder figure showing a relay circuit concerning work range control of a hydraulic excavator. It is a side view for demonstrating the work range in the side work area of a hydraulic shovel. It is a side view for demonstrating the work range in the front work area of a hydraulic shovel. It is a hydraulic circuit diagram of a hydraulic excavator. It is a block block diagram for demonstrating the controller of a hydraulic shovel. It is a block block diagram for demonstrating the jib automatic control part of a hydraulic shovel. It is a block block diagram for demonstrating the boom automatic control part of a hydraulic shovel. It is a side view for demonstrating the parameter regarding the attitude | position of the front apparatus of a hydraulic shovel. It is a partial side view which expands and shows the jib and arm of a front apparatus. It is a partial side view which expands and shows the jib cylinder of a front apparatus. It is a side view for demonstrating the parameter regarding the attitude | position of a front apparatus. It is a flowchart which illustrates the control procedure performed with a controller. It is a flowchart which illustrates the control procedure performed with a controller. It is a figure which shows the boom base end part of a hydraulic shovel, (a) is a side view, (b) is a top view. It is a schematic diagram which shows the inclination | tilt angle of the boom of a hydraulic shovel. It is a hydraulic circuit diagram of a hydraulic excavator. It is a circuit diagram which shows the relay circuit which concerns on the working range control of a hydraulic shovel.

  Hereinafter, an embodiment of a work range control device for a work machine will be described with reference to the drawings. However, the embodiment described below is merely an example, and there is no intention to exclude various modifications and technical applications that are not explicitly described in the embodiment described below. That is, the present embodiment may be variously modified and implemented without departing from the spirit of the invention.

[First embodiment]
[1. Aircraft configuration]
The work range control device disclosed as the first embodiment is applied to a hydraulic excavator 30 (work machine) shown in FIG. The hydraulic excavator 30 includes a lower traveling body 1 equipped with a crawler traveling device and an upper swing body 2 mounted on the lower traveling body 1. The upper turning body 2 is provided on the lower traveling body 1 via a turning device so as to be turnable. A drive source of the turning device is a hydraulic turning motor 25.
A front device 29 having a long dismantling specification that extends forward of the vehicle is provided on the vehicle front side of the upper-part turning body 2, and a cab on which an operator rides is provided on the left side thereof.

  The front device 29 includes a boom 3 whose base end is pivotally supported by the upper swing body 2, a jib 4 pivotally supported at the tip of the boom 3, an arm 5 pivotally supported at the tip of the jib 4, and an arm. 5 and a crusher 6 pivotally supported at the tip of 5. A pair of left and right boom cylinders 3a are interposed between the boom 3 and the upper swing body 2, and the boom 3 is driven in the vertical direction by an expansion / contraction operation. Similarly, a jib cylinder 4a is interposed between the boom 3 and the jib 4, an arm cylinder 5a is interposed between the jib 4 and the arm 5, and a bucket cylinder 6a (attachment cylinder) is interposed between the arm 5 and the crusher 6. Is installed. The jib cylinder 4a, arm cylinder 5a, and bucket cylinder 6a swing and drive the jib 4, arm 5 and crusher 6 by expansion and contraction, respectively.

  A boom angle sensor 7 that detects a boom angle α is provided at a connecting portion between the upper swing body 2 and the boom 3. The boom angle α is an elevation angle of the boom 3 with respect to the ground (the bottom surface of the upper swing body 2). Similarly, a jib angle sensor 8 is provided at a connecting portion between the boom 3 and the jib 4, and an arm angle sensor 9 is provided at a connecting portion between the jib 4 and the arm 5. The jib angle sensor 8 detects the angle of the jib 4 with respect to the boom 3 as the jib angle β, and the arm angle sensor 9 detects the angle of the arm 5 with respect to the jib 4 as the arm angle γ. These angles are transmitted to the controller 18 described later. These boom angle sensor 7, jib angle sensor 8, and arm angle sensor 9 are angle detection means for detecting the node angle of the front device 29.

As shown in FIG. 6, the signs of the boom angle α, the jib angle β, and the arm angle γ are positive when the hydraulic excavator 30 is viewed from the left side, and the clockwise turning direction with the base end of the boom 3 as the origin is positive. . A position where the base end portion of the boom 3 is pivotally supported by the upper swing body 2 is referred to as an axis o. Assuming that the ground contact surface of the lower traveling body 1 is horizontal, the vertical distance from the ground contact surface to the axis o is Z ₀ . Furthermore, the position where the boom 3 pivotally supports the jib 4 is called an axis a, the position where the jib 4 pivotally supports the arm 5 is called an axis b, and the position where the arm 5 pivotally supports the crusher 6 is the axis. Call it c. In the following description, it is assumed that the ground contact surface of the lower traveling body 1 is horizontal.

  As shown in FIGS. 1 and 2, the excavator 30 has a pair of plates 10 a and 10 b (plate members) and a pair of proximity as a device for detecting the turning angle of the upper turning body 2 with respect to the lower traveling body 1. Switches 11L and 11R (turning posture detecting means) are provided. The pair of plates 10a and 10b are fixed to the lower traveling body 1 with a space in the front-rear direction so as to face each other across the turning center. Further, the pair of proximity switches 11L and 11R are fixed to the upper swing body 2 with a space in the vehicle width direction at positions facing the pair of plates 10a and 10b. The pair of proximity switches 11L and 11R detects the presence of the pair of plates 10a and 10b within the detection range, and transmits a signal to the controller 18 and a relay circuit C6 described later.

  Here, as shown in FIG. 2, two types of work areas, a front work area and a side work area, are assumed on the basis of the lower traveling body 1 of the excavator 30. The front work area is a work area of the front device 29 in a forward-facing posture in which the front surface of the upper swing body 2 (the side where the front device 29 is located when viewed from the center of rotation) is directed in the front-rear direction of the lower traveling body 1. On the other hand, the side work area is a work area of the front device 29 in a lateral posture in which the front surface of the upper swing body 2 faces the vehicle width direction of the lower traveling body 1. The hydraulic excavator 30 determines whether the work area of the front device 29 is a front work area or a side work area, and performs control according to the type of these work areas.

  For example, in the state shown in FIG. 2, the pair of proximity switches 11L and 11R both detect the plate 10a, and the work area of the front device 29 is the front work area. When the upper turning body 2 turns clockwise, the pair of proximity switches 11L and 11R also rotate around the turning center in the clockwise direction. Immediately before the work area of the front device 29 moves from the front work area to the side work area, the one proximity switch 11R does not detect the plate 10a. Further, when the upper swing body 2 turns until the work area of the front device 29 becomes the side work area, both the proximity switches 11L and 11R do not detect the plate 10a.

The detection state of the pair of proximity switches 11L and 11R corresponds to the turning angle of the upper turning body 2 with respect to the lower traveling body 1. Moreover, the turning direction with respect to the lower traveling body 1 of the upper turning body 2 is grasped by referring to the detection states of the two proximity switches 11L and 11R.
The fixed positions of the plates 10a and 10b and the proximity switches 11L and 11R can be changed as appropriate. For example, these may be provided inside the swing bearing, or the plates 10a and 10b may be fixed to the upper swing body 2 side and the proximity switches 11L and 11R may be fixed to the lower travel body 1 side.

In the hydraulic excavator 30, two types of work radii corresponding to the above work areas are set in advance. As shown in FIG. 3, the work radius R ₁ in the front work area is set larger than the work radius R ₂ in the side work area. The work radius R ₂ is a work radius during normal work, and the work radius R ₁ is an extended work radius that is allowed only in the front work area.

A front work switch 12 is provided in the cab of the hydraulic excavator 30 to increase the work radius, and the work range of the front device 29 in the front work area is limited only when the front work switch 12 is turned on. Enlarged. When the front work switch 12 is off, even if the front device 29 is located in the front work area, the work range is limited to the inside of the work radius R ₂ indicated by a broken line in FIG.

[2. Hydraulic circuit]
[2-1. Main circuit]
FIG. 4 shows a hydraulic circuit of the hydraulic excavator 30. The hydraulic circuit is provided with a main circuit C1 through which hydraulic oil supplied to a hydraulic actuator (various hydraulic drive devices) flows and a plurality of pilot circuits.
The main circuit C1 is provided with a hydraulic pump 41 driven by the engine. Here, the boom cylinder 3a, the jib cylinder 4a, the arm cylinder 5a, and the swing motor 25 are displayed as hydraulic actuators on the main circuit C1, and other hydraulic actuators are omitted.

  The hydraulic pump 41 is a variable displacement hydraulic oil pump driven by an engine (not shown), and sucks the hydraulic oil from the hydraulic oil tank 24 and supplies the hydraulic oil to each hydraulic actuator. The hydraulic pump 41 is provided with a regulator that controls the discharge flow rate and the discharge pressure by adjusting the inclination angle of the tilting swash plate.

  A control valve unit 40 including a plurality of control valves is interposed between the hydraulic pump 41 and each hydraulic actuator. The control valve unit 40 includes a turning control valve 22, a boom control valve 26, a jib control valve 27, and an arm control valve 28. These control valves 22 and 26 to 28 switch the position of the flow rate control spool to a plurality of positions according to the input to the operation lever, and variably control the flow direction and flow rate of the hydraulic oil. The spool positions of these control valves 22, 26 to 28 are controlled in accordance with the pilot pressure introduced at both ends of the spool.

  Each control valve 22, 26-28 is provided corresponding to each above-mentioned hydraulic actuator. For example, the flow direction and flow rate of the hydraulic oil supplied to the turning motor 25 are controlled by the turning control valve 22. Similarly, the boom control valve 26, the jib control valve 27, and the arm control valve 28 control the flow direction and flow rate of the hydraulic oil supplied to the boom cylinder 3a, the jib cylinder 4a, and the arm cylinder 5a, respectively.

  The pilot circuit is a circuit connected to both ends of the spools of the control valves 22, 26 to 28, and here, a swing pilot circuit C2, a boom pilot circuit C3, a jib pilot circuit C4, and an arm pilot circuit C5 are exemplified. The turning pilot circuit C2 is a pilot circuit for the turning control valve 22, and the boom pilot circuit C3 is a pilot circuit for the boom control valve 26. Similarly, jib pilot circuit C4 and arm pilot circuit C5 are pilot circuits of jib control valve 27 and arm control valve 28, respectively.

[2-2. Swivel pilot circuit]
The turning pilot circuit C2 is provided with turning remote control valves 21L and 21R fixed to the lower end of the turning operation lever 21. The turning remote control valves 21L and 21R are control valves that generate pilot pressures having a magnitude corresponding to the operation amount and the operation direction input to the turning operation lever 21, respectively. A pilot pump 20 and a hydraulic oil tank 24 are connected to these swing remote control valves 21L and 21R. Note that one turning remote control valve 21L generates a pilot pressure related to the turning operation of the upper turning body 2 in the left rotation direction (counterclockwise), and the other turning remote control valve 21R moves in the right rotation direction (clockwise). A pilot pressure related to the turning operation is generated.

  On the pilot passage between the turning remote control valve 21L and the turning control valve 22, a turning restriction electromagnetic valve 23L is interposed. Similarly, on the pilot passage between the turning remote control valve 21R and the turning control valve 22, a turning restriction electromagnetic valve 23R is interposed. These turning restriction solenoid valves 23L and 23R are solenoid valves whose spool position is switched to two positions by a relay circuit C6 described later. The spool position is changed to the a position when not energized, and the spool position is changed to the b position when energized. .

  As shown in FIG. 4, the turning restriction electromagnetic valves 23L and 23R block the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 when the spool position is the position a, and the pilot of the turning control valve 22 The pressure is released (communication) to the hydraulic oil tank 24 side. Further, when the spool position is at the position b, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 is connected. That is, the turning restriction electromagnetic valves 23L and 23R function to permit or prohibit the turning operation by the turning operation lever 21.

[2-3. Boom pilot circuit]
The boom pilot circuit C3 is provided with boom remote control valves 42L and 42R fixed to the lower end of the boom operation lever 42.
Each of the boom remote control valves 42L and 42R is a control valve that generates a pilot pressure having a magnitude corresponding to the operation amount and the operation direction input to the boom operation lever 42. The pilot pump 20 and the hydraulic oil tank 24 are connected to these boom remote control valves 42L and 42R. One boom remote control valve 42L generates a pilot pressure related to the boom raising operation, and the other boom remote control valve 42R generates a pilot pressure related to the boom lowering operation. One of the boom remote control valves 42L and 42R corresponding to the tilting direction of the boom operating lever 42 is opened according to the tilting angle to generate a pilot pressure according to the opening.

  On the pilot passage between the boom remote control valve 42R and the boom control valve 26, the boom limiting electromagnetic valve 15 is interposed. The boom limiting electromagnetic valve 15 is an electromagnetic valve whose spool position is switched between two positions by the controller 18.

  The boom limiting solenoid valve 15 blocks the pilot passage between the boom remote control valve 42R and the boom control valve 26 when the spool position is the position a, and opens the pilot pressure of the boom control valve 26 to the hydraulic oil tank 24 side (communication). ) Further, the pilot passage between the boom remote control valve 42R and the boom control valve 26 is connected when the spool position is at the position b. That is, the boom limiting solenoid valve 15 functions to permit or prohibit the boom 3 lowering operation (the boom cylinder 3a reducing operation) by the boom operation lever 42.

[2-4. Jib pilot circuit]
The jib pilot circuit C4 is provided with jib remote control valves 43L and 43R fixed to the lower end portion of the jib operation lever 43.
Each of the jib remote control valves 43L and 43R is a control valve that generates a pilot pressure having a magnitude corresponding to the operation amount and the operation direction input to the jib operation lever 43. The pilot pump 20 and the hydraulic oil tank 24 are connected to these jib remote control valves 43L and 43R. Of these jib remote control valves 43L and 43R, one corresponding to the tilt direction of the jib operation lever 43 is opened according to the tilt angle, and a pilot pressure corresponding to the opening degree is generated. One jib remote control valve 43L generates a pilot pressure related to the jib raising operation, and the other jib remote control valve 43R generates a pilot pressure related to the jib lowering operation.

  On the pilot passage between the jib remote control valve 43L and the jib control valve 27, a jib limiting electromagnetic valve 16L is interposed. Similarly, on the pilot passage between the jib remote control valve 43R and the jib control valve 27, a jib limiting electromagnetic valve 16R is interposed. The jib limiting solenoid valves 16L and 16R are solenoid valves whose spool position is switched between two positions by the controller 18.

  The jib limiting solenoid valves 16L and 16R block the pilot passage between the jib remote control valves 43L and 43R and the jib control valve 27 when the spool position is the a position, and the pilot pressure of the jib control valve 27 is changed to the hydraulic oil tank 24 side. Open (communication). Further, when the spool position is at the position b, the pilot passage between the jib remote control valves 43L and 43R and the jib control valve 27 is connected. That is, the jib limiting solenoid valves 16L and 16R function to permit or prohibit the operation of the jib cylinder 4a by the jib operation lever 43.

[2-5. Arm pilot circuit]
The circuit configuration of the arm pilot circuit C5 is the same as that of the jib pilot circuit C4. The arm pilot circuit C5 is provided with arm remote control valves 44L and 44R fixed to the lower end portion of the arm operation lever 44.
Each of the arm remote control valves 44L and 44R is a control valve that generates a pilot pressure having a magnitude corresponding to the operation amount and the operation direction input to the arm operation lever 44. A pilot pump 20 and a hydraulic oil tank 24 are connected to these arm remote control valves 44L and 44R. One of the arm remote control valves 44L and 44R corresponding to the tilt direction of the arm operation lever 44 is opened according to the tilt angle, and a pilot pressure corresponding to the opening degree is generated. One arm remote control valve 44L generates a pilot pressure related to the arm-in operation, and the other arm remote control valve 44R generates a pilot pressure related to the arm-out operation.

  On the pilot passage between the arm remote control valve 44L and the arm control valve 28, an arm limiting electromagnetic valve 17L is interposed. Similarly, an arm limiting electromagnetic valve 17R is interposed on the pilot passage between the arm remote control valve 44R and the arm control valve 28. These arm limiting electromagnetic valves 17L and 17R are electromagnetic valves whose spool position is switched between two positions by the controller 18.

  The arm limiting solenoid valves 17L and 17R block the pilot passage between the arm remote control valves 44L and 44R and the arm control valve 28 when the spool position is at the position a, and the pilot pressure of the arm control valve 28 is reduced to the hydraulic oil tank 24 side. Open (communication). Further, the pilot passage between the arm remote control valves 44L and 44R and the arm control valve 28 is connected when the spool position is at the position b. That is, the arm limiting electromagnetic valves 17L and 17R function to permit or prohibit the operation of the arm cylinder 5a by the arm operation lever 44.

[3. controller]
The controller 18 (control means) shown in FIG. 5 is an electronic control device provided as an LSI device in which a known microprocessor, CPU, ROM, RAM and the like are integrated. On the input side of the controller 18, a boom angle sensor 7, a jib angle sensor 8, an arm angle sensor 9, a pair of proximity switches 11L and 11R, and a front work switch 12 are connected. The controller 18 controls the operation of the front device 29 based on information transmitted from these.

  Functions programmed as software or hardware circuits inside the controller 18 are schematically shown in FIG. The controller 18 includes a position calculation unit 31, a side work range data storage unit 32, a front work range data storage unit 33, a turning angle determination unit 34, a front member data storage unit 35, a data switch 36 and a work range restriction determination unit 37. Is provided.

The front member data storage unit 35 stores information related to the dimensions of each member of the front device 29. For example, as shown in FIG. 6, the distance L ₁ (boom length) from the axis o to the axis a, the distance L ₂ (jib length) from the axis a to the axis b, the axis b to the axis c Distance L ₃ (arm length), vertical distance Z ₀ from the ground contact surface of the lower traveling body 1 to the shaft center o, etc. are stored in the front member data storage unit 35 and used at any time for calculation in the position calculation unit 31. The

The position calculation unit 31 (position calculation means) calculates the coordinates of the tip of the arm 5 based on the boom angle α, the jib angle β, and the arm angle γ detected by the boom angle sensor 7, the jib angle sensor 8, and the arm angle sensor 9. Calculate. The position calculation unit 31 calculates the position of the axis c in a coordinate system with the origin of the perpendicular line drawn from the axis o to the ground plane. The coordinates (X _C , Y _C ) of the axis c are given by the following formulas 1 and 2, respectively. The coordinates of the axis c as the arm tip position calculated here are transmitted to the work range restriction determination unit 37.

The side work range data storage unit 32 (first storage unit) stores the work range of the front device 29 allowed in the side work area, and the front work range data storage unit 33 (second storage unit) The work range of the front device 29 allowed in the work area is stored. For example, the work radius R ₂ of the side work area is stored in the side work range data storage unit 32, and the work radius R ₁ of the front work area is stored in the front work range data storage unit 33.
The turning angle determination unit 34 determines a work area and a work state of the front device 29 based on information detected by the pair of proximity switches 11L and 11R and the front work switch 12, and includes an OR calculator 34a and an AND calculation. A device 34b is provided.

The OR calculator 34a outputs a logical sum of signals transmitted from the pair of proximity switches 11L and 11R. When the front device 29 is located in the front work area, the output signal from the OR calculator 34a is turned on, and when it is located in the side work area, the output signal from the OR calculator 34a is turned off.
The AND operation unit 34b outputs a logical product of the signal output from the OR operation unit 34a and the signal transmitted from the front work switch 12. Here, the ON signal is output only when the front work switch 12 is turned ON and the front device 29 is located in the front work area.

Based on the signal transmitted from the turning angle determination unit 34, the data switch 36 receives one of the work range information stored in the side work range data storage unit 32 and the front work range data storage unit 33. This is selected and transmitted to the work range restriction determination unit 37. Here, the former is selected when the output signal of the AND calculator 34b is an off signal, and the latter is selected when the output signal is an on signal.
That is, the work radius R ₁ of the front work area is transmitted to the work range restriction determination unit 37 only when the front work switch 12 is turned on and the front device 29 is located in the front work area. When the front work switch 12 is turned off or the front device 29 is positioned in the side work area, the work radius R ₂ of the side work area is transmitted to the work range restriction determination unit 37.

The work range restriction determination unit 37 determines whether the coordinates (X _C , Y _C ) of the axis c calculated by the position calculation unit 31 are within the work range selected by the data switch 36. The front device 29 is controlled. For example, when the input from the data switch 36 is the working radius R ₁ , it is determined whether or not the x coordinate X _C of the axis c is less than the working radius R ₁ . Here, when X _C ≧ R ₁ , the boom limit solenoid valve 15, the jib limit solenoid valves 16L and 16R, and the arm limit solenoid valves 17L and 17R are controlled to control the respective spool positions to the a position. . In this case, only the raising operation of the boom 3 is allowed, and the operation of the jib 4 and the arm 5 is prohibited.

Further, at this time, the work range restriction determination unit 37 displays on the monitor console 13 in the cab that the front end of the front device 29 exceeds the preset work range, and outputs a warning sound from the speaker 14. When X _C <R ₁ by the raising operation of the boom 3, the work range restriction determination unit 37 sets the boom positions of the boom restriction solenoid valve 15, the jib restriction solenoid valves 16L and 16R, and the arm restriction solenoid valves 17L and 17R to the b position. To control. Thereby, it will be in the normal operation state in which all operation of boom 3, jib 4, and arm 5 was permitted.

[4. Relay circuit]
The relay circuit C6 in FIG. 7 is an electric circuit for controlling the turning restriction electromagnetic valves 23L and 23R. The symbol + B shown in FIG. 7 indicates a DC power supply line, and the symbol GND indicates a ground line. The relay circuit C6 is roughly divided into three circuits: a first circuit C6 _A , a second circuit C6 _B, and a third circuit C6 _C.

The first circuit C6 _A is a circuit for switching the excitation / de-excitation state of the relay in accordance with the on / off state of the front work switch 12. _A first relay coil 38 and a second relay coil 39 are interposed in parallel on the first circuit C6A. Both the first relay coil 38 and the second relay coil 39 are excited only when the front work switch 12 is turned on.

The second circuit C6 _B is a circuit for controlling the turning restriction electromagnetic valve 23R related to the right turning operation by the first relay coil 38. A circuit is branched in parallel on the power supply line side from the rotation limiting electromagnetic valve 23R, and contacts 38a and 38b of the first relay coil 38 are interposed on the respective circuits. One contact 38a is a contact that is turned on when the first relay coil 38 is excited, and the other contact 38b is a contact that is turned off when the first relay coil is excited. A proximity switch 11R is interposed on the circuit on the side where the contact 38a is provided.
In the second circuit C6 _B, the other contact 38b side is turned on, the turning limit electromagnetic valve 23R is energized when de-energized the first relay coil 38. Further, at the time of exciting the first relay coil 38, the turning restriction electromagnetic valve 23R is energized only when the proximity switch 11R is on (the plates 10a and 10b are detected).

The third circuit C6 _C is a circuit for controlling the turning restriction electromagnetic valve 23L related to the left turning operation by the second relay coil 39. A circuit branches in parallel on the power supply line side from the turning restriction electromagnetic valve 23L, and contacts 39a and 39b of the second relay coil 39 are interposed on the respective circuits. One contact 39a is a contact that is turned on when the second relay coil 39 is excited, and the other contact 39b is a contact that is turned off when the second relay coil 39 is excited. A proximity switch 11L is interposed on the circuit on the side where the contact 39a is provided.
In the third circuit C6 _C, the other contact 39b is turned on, the turning limit electromagnetic valve 23L is energized when de-energized second relay coil 39. Further, at the time of exciting the second relay coil 39, the turning restriction electromagnetic valve 23L is energized only when the proximity switch 11L is on (the plates 10a and 10b are detected).

[5. Action]
[5-1. When front operation / front work switch is off]
When the front work switch 12 is turned off, an off signal is output from the AND calculator 34b of the controller 18 in FIG. 5 regardless of the detection state of the proximity switches 11L and 11R. Therefore, the data switch 36 selects the work range information stored in the side work range data storage unit 32. Thereby, the work radius R ₂ of the side work area is transmitted to the work range restriction determination unit 37. Further, the position calculation unit 31 of the controller 10 calculates the coordinates (X _C , Y _C ) of the axis c that is the tip position of the arm 5 based on the boom angle α, the jib angle β, and the arm angle γ. It is input to the restriction determination unit 37.

The work range restriction determination unit 37 determines whether or not the x-coordinate X _C of the axis c is less than the work radius R ₂ . Here, when the x coordinate X _C is less than the working radius R ₂ , the spool positions of the boom limiting solenoid valve 15, the jib limiting solenoid valves 16L and 16R and the arm limiting solenoid valves 17L and 17R are controlled to the b position, and the boom 3, all operations of jib 4 and arm 5 are allowed.

On the other hand, as shown in FIG. 8, when the posture of the front device 29 extends forward and the x-coordinate X _C of the axis c reaches a work radius R ₂ or more, the boom limiting solenoid valve 15, the jib limiting solenoid valve 16L, The spool positions of 16R and arm limiting solenoid valves 17L, 17R are controlled to the a position. That is, the operation of the jib 4 and the arm 5 is prohibited, and the lowering operation of the boom 3 is prohibited, and the working range of the front device 29 is limited.
Further, the monitor console 13 displays that the front end of the front device 29 has exceeded a preset work range, and a warning sound is output from the speaker 14. Thereby, the boom raising operation for making the x coordinate X _C of the axis c less than the working radius R ₂ is prompted.

In the posture in which the front end of the front device 29 is located in the warning area in FIG. For example, in consideration of the distance and the weight of the axis c to the tip of the crusher 6, by setting the operating radius R ₂ in front of the danger zone as viewed from the fuselage of the hydraulic excavator 30, than the working radius R ₂ The area up to the outer danger area is the warning area.

[5-2. When the swivel operation / forward operation switch is off]
When the forward work switch 12 is turned off, in the relay circuit C6 shown in FIG. 7, the first relay coil 38 and the second relay coil 39 are in a non-excited state. Thus, one contact 38a of the second circuit C6 _B is turned off, the other contact 38b is turned on. Similarly, one contact 39a also in the third circuit C6 _C is turned off, the other contact 39b is turned on. As a result, regardless of the detection state of the proximity switches 11L and 11R (regardless of the turning angle), the turning restriction electromagnetic valves 23L and 23R are energized, and the spool position is switched to the b position.
Therefore, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 communicates, and a normal operation state in which the left and right turning operation by the turning operation lever 21 is allowed is obtained.

[5-3. When front operation / front work switch is on]
When the front work switch 12 is turned on while the front device 29 of the excavator 30 is located in the front work area, at least one of the pair of proximity switches 11L and 11R detects the plates 10a and 10b. The ON signal is output from the OR calculator 34a of the controller 18 in FIG. At this time, since the forward work switch 12 is on, an ON signal is also output from the AND calculator 34b, and the data switch 36 selects the work range information stored in the forward work range data storage unit 33. Thereby, the work radius R ₁ of the front work area is transmitted to the work range restriction determination unit 37. Further, the position calculation unit 31 of the controller 10 calculates the coordinates (X _C , Y _C ) of the axis c that is the tip position of the arm 5 based on the boom angle α, the jib angle β, and the arm angle γ. It is input to the restriction determination unit 37.

The work range restriction determination unit 37 determines whether or not the x coordinate X _C of the axis c is less than the work radius R ₁ . When the x-coordinate X _C is less than the working radius R ₁ , the spool positions of the boom limiting solenoid valve 15, the jib limiting solenoid valves 16L and 16R, and the arm limiting solenoid valves 17L and 17R are controlled to the b position. All manipulations of jib 4 and arm 5 are allowed. Since the work radius R ₁ in the front work area is larger than the work radius R ₂ in the side work area, the range in which the front device 29 can be moved is greatly expanded as shown in FIG.

On the other hand, when the posture of the front device 29 extends forward and the x-coordinate X _C of the axis c becomes the working radius R ₁ or more, the boom limiting solenoid valve 15, the jib limiting solenoid valves 16L and 16R, and the arm limiting solenoid valves 17L and 17R. The spool position is controlled to the a position. That is, the operation of the jib 4 and the arm 5 is prohibited, and the lowering operation of the boom 3 is prohibited, and the working range of the front device 29 is limited.
Further, the monitor console 13 displays that the front end of the front device 29 has exceeded a preset work range, and a warning sound is output from the speaker 14. Thereby, the boom raising operation for making the x coordinate X _C of the axis c less than the working radius R ₁ is urged.

[5-4. When the swivel operation / forward operation switch is on]
In the relay circuit C6 shown in FIG. 7, when the forward work switch 12 is turned on, the first relay coil 38 and the second relay coil 39 are excited. Thus, one contact 38a of the second circuit C6 _B is turned on, the other contact 38b is turned off. Further, one contact 39a also in the third circuit C6 _C is turned on, the other contact 39b is turned off.

  At this time, if both the proximity switches 11L and 11R detect either of the plates 10a and 10b, the turning restriction electromagnetic valves 23L and 23R are energized, and the spool position is switched to the b position. Therefore, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 communicates, and a normal operation state in which the left and right turning operation by the turning operation lever 21 is allowed is obtained.

Further, for example, when the front device 29 by the operation of the right-turn direction is about to enter the lateral work area, one of the proximity switch 11R is plate 10a, longer detects 10b, proximity switch 11R on the second circuit C6 _B is Turn off. As a result, the turning restriction electromagnetic valve 23R related to the right turning operation is de-energized, and the spool position of the turning restriction electromagnetic valve 23R is switched to the position a. Therefore, the spool position of the turning control valve 22 returns to neutral, the right turning of the upper turning body 2 is stopped, and further turning is prohibited.

At this time, the other proximity switch 11L still plates 10a, if detects 10b, proximity switch 11L on the third circuit C6 _C is on. Therefore, the energized state of the turning restriction electromagnetic valve 23L related to the left turning operation is maintained, and the left turning operation of the upper turning body 2 (that is, the operation for returning the turning angle to the front work area side) is allowed.
The same applies to the case where the front device 29 tries to enter the side work area by an operation in the left turn direction, for example. The left turn of the upper swing body 2 is stopped, and further turning is prohibited and the right turn is prohibited. A turning operation is allowed.

[6. effect]
Thus, according to the work range control device of the disclosed work machine, different work areas are set for each of the front work area and the side work area, and particularly in the front work area that is advantageous from the standpoint of aircraft stability. The scope of work is greatly expanded. That is, when the turning posture is the forward posture, the working range of the front device 29 can be expanded farther than in the side posture, and workability can be improved while ensuring stability. Moreover, when the turning posture of the upper turning body 2 is a side posture, the working range of the front device 29 can be narrowed to improve the stability.

  Also, according to the disclosed work range control device, the controller 18 can calculate the position of the front end portion of the front device 29, so that the work machine can be prevented from overturning and the body stability can be improved. it can. Furthermore, when the turning posture is the forward posture, the front end portion of the front device 29 can be extended farther than in the side posture, and the efficiency of the dismantling work using the crusher 6 can be increased.

  Further, in the disclosed work range control device, when the front work switch 12 is operated, the work area of the front device 29 is limited only to the front work area, and the turning operation to the side work area (from the front work area to the outside). The operation that tries to exit) is prohibited. Therefore, it is possible to reliably prevent the front end portion of the front device 29 from jumping out of the lateral work area, and to ensure work stability.

Moreover, in the disclosed work range control device, an operation input to the front work switch 12 is included as one of the control conditions for expanding the work range. That is, the passenger can select whether or not to expand the work range, and convenience can be improved.
Furthermore, in the disclosed work range control apparatus, the conditions for expanding the work range are AND conditions of the proximity state detection by the proximity switches 11L and 11R and the on operation of the front work switch 12. Therefore, in the unlikely event that any sensor or switch fails or a disconnection occurs, the side work range is always selected.

In addition, the disclosed work range control apparatus includes a control configuration for switching work areas with simple logic in the controller 18. Therefore, for example, the function can be improved by simply modifying the work range control system of a conventional hydraulic excavator, and there is an advantage that it is cost-effective.
Moreover, in the disclosed work range control device, the turning position is detected using the pair of proximity switches 11L and 11R, so that the swivel joint mounted on the conventional hydraulic excavator, for example, can be applied without modification. There is also an advantage of being able to.

[Second Embodiment]
[1. Aircraft configuration]
The work range control device disclosed as the second embodiment is obtained by adding automatic posture control of the front device 29 to the work range control device of the first embodiment, and is applied to the hydraulic excavator 30 shown in FIG. Components corresponding to those described above are denoted by the same reference numerals and description thereof is omitted. An automatic control switch 50 (vertical movement switch) for switching on / off of automatic attitude control of the front device 29 is provided in the cab of the hydraulic excavator 30. The automatic attitude control is performed at least when the automatic control switch 50 is turned on.

  Automatic posture control refers to, for example, the front device 29 so that the front end portion does not enter the warning area when a single-action operation of the arm 5 that brings the front end portion of the front device 29 closer to the warning area in FIG. 9 is input. It is control which moves the front-end | tip part of automatically in the perpendicular direction. For example, when an arm-out operation is input to the arm operation lever 44 from the state shown in FIG. 9, the crusher 6 and the arm 5 rotate about the axis “b” of the base end and move forward and upward of the machine body. To do. Under such circumstances, when the tip of the arm 5 tries to enter the warning zone, the boom 3 and the jib 4 are automatically driven in the upward direction so as to be linked with the movement of the arm 5, and the crusher 6 Avoid entering the warning area. Note that the direction in which the boom 3 and the jib 4 are driven by the automatic posture control depends on the posture and movement direction of the arm 5.

[2. Hydraulic circuit]
FIG. 10 shows a hydraulic circuit of the excavator 30. This hydraulic circuit differs from the hydraulic circuit of the first embodiment in the specific structures of the boom pilot circuit C3, the jib pilot circuit C4, and the arm pilot circuit C5. The boom pilot circuit C3, the jib pilot circuit C4, and the arm pilot circuit C5 have a function of cutting off the pilot pressure generated by the remote control valve. In particular, the boom pilot circuit C3 and the jib pilot circuit C4 have a function of switching between manual pilot pressure supply by lever operation and automatic pilot pressure supply not by lever operation.

[2-1. Boom pilot circuit]
The boom pilot circuit C3 is provided with boom remote control valves 42L and 42R that generate pilot pressure having a magnitude corresponding to the operation amount and operation direction input to the boom operation lever 42. One of the boom remote control valves 42L and 42R corresponding to the tilting direction of the boom operating lever 42 is opened according to the tilting angle to generate a pilot pressure according to the opening. One boom remote control valve 42L generates a pilot pressure related to the boom raising operation, and the other boom remote control valve 42R generates a pilot pressure related to the boom lowering operation.

  A shuttle valve 53 and a boom remote control pressure sensor 54 are interposed on a passage connecting the downstream side of one boom remote control valve 42L and the downstream side of the other boom remote control valve 42R. The shuttle valve 53 is a high pressure selection valve that selects one of the high pressures of the downstream pressures of the boom remote control valves 42L and 42R. The boom remote control pressure sensor 54 is a sensor that detects the magnitude of the pressure selected by the shuttle valve 53. The pressure (boom remote control pressure) detected here is transmitted to the controller 18.

  On the pilot circuit between one boom remote control valve 42L and the boom control valve 26, a boom electromagnetic switching valve 51L and a boom electromagnetic proportional pressure reducing valve 52L are provided. Similarly, a boom electromagnetic switching valve 51R and a boom electromagnetic proportional pressure reducing valve 52R are interposed on the pilot passage between the other boom remote control valve 42R and the boom control valve 26.

  The boom electromagnetic switching valves 51L and 51R are switching valves whose spool position is switched to two positions by the controller 18, and switch between supplying the pilot pressure manually or automatically controlling the pilot pressure. These boom electromagnetic switching valves 51L and 51R connect the pilot passages between the boom remote control valves 42L and 42R and the boom control valve 26 when the spool position is the a position, and are generated by the boom remote control valves 42L and 42R. Transmits remote control pressure downstream.

  Further, when the spool position is at the position b, the pilot passage between the boom remote control valves 42L and 42R and the boom control valve 26 is shut off, and the remote control pressure generated by the pilot pump 20 is transmitted to the downstream side. That is, the a position is a spool position during manual pilot pressure control, and the b position is a spool position during automatic attitude control.

  The boom electromagnetic proportional pressure reducing valves 52L and 52R are electromagnetic proportional valves that variably control the magnitude of pilot pressure introduced from the boom electromagnetic switching valves 51L and 51R side and transmit it to the boom control valve 26. The magnitude of the pilot pressure transmitted to the boom control valve 26 via the boom electromagnetic proportional pressure reducing valves 52L and 52R is adjusted by the controller 18.

  At the time of automatic attitude control, a pilot pressure of a magnitude necessary for appropriately moving the boom 3 is calculated by the controller 18 as needed, and the opening degree of the boom electromagnetic proportional pressure reducing valves 52L and 52R is controlled. When the pilot pressure is manually supplied, the pilot pressure from the boom remote control valves 42L and 42R is directly transmitted to the boom control valve 26 without being changed. Alternatively, the transmission of the pilot pressure is blocked by reducing the opening, and the operation of the boom 3 is stopped. Thus, the boom electromagnetic proportional pressure reducing valves 52L and 52R have a function of controlling (including not changing or completely shutting off) the magnitude of the pilot pressure transmitted to the boom control valve 26.

[2-2. Jib pilot circuit]
The circuit configuration of the jib pilot circuit C4 is the same as that of the boom pilot circuit C3. The jib pilot circuit C4 is provided with jib remote control valves 43L and 43R that generate pilot pressure having a magnitude corresponding to the operation amount and operation direction input to the jib operation lever 43. The pilot pump 20 and the hydraulic oil tank 24 are connected to these jib remote control valves 43L and 43R. Of these jib remote control valves 43L and 43R, one corresponding to the tilt direction of the jib operation lever 43 is opened according to the tilt angle, and a pilot pressure corresponding to the opening degree is generated. One jib remote control valve 43L generates a pilot pressure related to the jib raising operation, and the other jib remote control valve 43R generates a pilot pressure related to the jib lowering operation.

  A shuttle valve 57 and a jib remote control pressure sensor 58 are interposed on a passage connecting the downstream side of one jib remote control valve 43L and the downstream side of the other jib remote control valve 43R. The shuttle valve 57 is a high pressure selection valve that selects one of the high pressures of the downstream pressures of the jib remote control valves 43L and 43R. The jib remote control pressure sensor 58 is a sensor that detects the magnitude of the pressure selected by the shuttle valve 57. The pressure (jib remote control pressure) detected here is transmitted to the controller 18.

  On the pilot circuit between one jib remote control valve 43L and the jib control valve 27, a jib electromagnetic switching valve 55L and a jib electromagnetic proportional pressure reducing valve 56L are provided. Similarly, a jib electromagnetic switching valve 55R and a jib electromagnetic proportional pressure reducing valve 56R are interposed on the pilot passage between the other jib remote control valve 43R and the jib control valve 27.

  The jib electromagnetic switching valves 55L and 55R are switching valves whose spool position is switched between two positions by the controller 18, and switch between supplying the pilot pressure manually or automatically controlling the pilot pressure. These jib electromagnetic switching valves 55L and 55R connect the pilot passages between the jib remote control valves 43L and 43R and the jib control valve 27 when the spool position is the a position, and are generated by the jib remote control valves 43L and 43R. Transmits remote control pressure downstream.

  Further, when the spool position is at the position b, the pilot passage between the jib remote control valves 43L and 43R and the jib control valve 27 is blocked, and the remote control pressure generated by the pilot pump 20 is transmitted downstream. That is, the a position is a spool position during manual pilot pressure control, and the b position is a spool position during automatic attitude control.

  The jib electromagnetic proportional pressure reducing valves 56L and 56R are electromagnetic proportional valves that variably control the magnitude of pilot pressure introduced from the jib electromagnetic switching valves 55L and 55R side and transmit it to the jib control valve 27. The magnitude of the pilot pressure transmitted to the jib control valve 27 via the jib electromagnetic proportional pressure reducing valves 57L and 57R is adjusted by the controller 18.

  At the time of automatic attitude control, a pilot pressure of a magnitude necessary for appropriately moving the jib 4 is calculated by the controller 18 as needed, and the opening degree of the jib electromagnetic proportional pressure reducing valves 56L and 56R is controlled. When the pilot pressure is manually supplied, the pilot pressure from the jib remote control valves 43L and 43R is directly transmitted to the jib control valve 27 without being changed. Alternatively, the operation of the jib 4 is stopped by reducing the opening degree to interrupt the transmission of the pilot pressure. Thus, the jib electromagnetic proportional pressure reducing valves 56L and 56R have a function of controlling (including not changing or completely shutting off) the pilot pressure transmitted to the boom control valve 27.

[2-3. Arm pilot circuit]
The arm pilot circuit C5 is provided with arm remote control valves 44L and 44R that generate a pilot pressure having a magnitude corresponding to the operation amount and the operation direction input to the arm operation lever 44. A pilot pump 20 and a hydraulic oil tank 24 are connected to these arm remote control valves 44L and 44R. One of the arm remote control valves 44L and 44R corresponding to the tilt direction of the arm operation lever 44 is opened according to the tilt angle, and a pilot pressure corresponding to the opening degree is generated. One arm remote control valve 44L generates a pilot pressure related to the arm-in operation, and the other arm remote control valve 44R generates a pilot pressure related to the arm-out operation.

  On the pilot passage between the arm remote control valve 44L and the arm control valve 28, an arm electromagnetic proportional pressure reducing valve 59L is interposed. Similarly, an arm electromagnetic proportional pressure reducing valve 59R is interposed on the pilot passage between the arm remote control valve 44R and the arm control valve 28. These arm electromagnetic proportional pressure reducing valves 59L and 59R are electromagnetic proportional valves that variably control the magnitude of pilot pressure introduced from the arm remote control valves 44L and 44R side and transmit them to the arm control valve 28. The magnitude of the pilot pressure transmitted to the arm control valve 28 via the arm electromagnetic proportional pressure reducing valves 59L and 59R is adjusted by the controller 18.

  The arm electromagnetic proportional pressure reducing valves 59L and 59R have a function of controlling the magnitude of the pilot pressure transmitted to the arm control valve 28 (including not changing or completely shutting off). It also has a function of stopping the operation of the arm 5 by blocking the transmission of the pilot pressure.

[3. controller]
[3-1. Overview]
As shown in FIG. 11, on the input side of the controller 18, the boom angle sensor 7, the jib angle sensor 8, the arm angle sensor 9, the pair of proximity switches 11L and 11R, and the front work switch 12 are provided as in the first embodiment. Is connected. Furthermore, an automatic control switch 50, a boom remote controller pressure sensor 54, and a jib remote controller pressure sensor 58 are connected to the controller 18 of the second embodiment. The controller 18 controls the operation of the front device 29 based on information transmitted from these. The boom remote control pressure and the jib remote control pressure are respectively used for grasping whether or not the boom 3 and jib 4 are operated by the operator.

The controller 18 performs the same control as in the first embodiment in a state where the automatic control switch 50 is turned off. That is, the work range of the front device 29 is set according to the operating state of the front work switch 12, and the front end portion of the front device 29 is prevented from jumping out of the work area.
Here, the movement of the boom 3 is prevented by controlling the boom electromagnetic proportional pressure reducing valves 52L and 52R instead of the boom limiting solenoid valve 15 of the first embodiment. Similarly, the jib electromagnetic proportional pressure reducing valves 56L and 56R are controlled instead of the jib limiting electromagnetic valves 16L and 16R, and the arm electromagnetic proportional pressure reducing valves 59L and 59R are controlled instead of the arm limiting electromagnetic valves 17L and 17R.

  On the other hand, when the automatic control switch 50 is turned on, automatic attitude control is performed according to the lever operation state. Functions related to automatic attitude control programmed as software or hardware circuits inside the controller 18 are schematically shown in FIG.

[3-2. Automatic control unit]
The controller 18 is provided with an automatic control unit 45 (trajectory control means). The automatic control unit 45 includes a jib automatic control unit 46 and a boom automatic control unit 47. The automatic control unit 45 determines the start condition of the automatic attitude control (for example, that the tip of the arm 5 is about to exceed the working range), and controls the jib electromagnetic switching valves 55L and 55R and the boom electromagnetic switching valves 51L and 51R. To do. Further, the automatic control unit 45 controls the boom electromagnetic proportional pressure reducing valves 52L and 52R and the jib electromagnetic proportional pressure reducing valves 56L and 56R to perform automatic posture control.

  The jib automatic control unit 46 calculates the operation of the jib 4 during automatic posture control, and controls the jib electromagnetic proportional pressure reducing valves 56L and 56R. Here, the control amount for driving the jib 4 is calculated so that the tip of the front device 29 moves in the vertical direction when the arm 5 is operated.

The boom automatic control unit 47 calculates the operation of the boom 3 during automatic posture control, and controls the boom electromagnetic proportional pressure reducing valves 52L and 52R. Also here, the control amount for driving the boom 3 is calculated so that the front end portion of the front device 29 moves in the vertical direction when the arm 5 is operated. However, in the actual control, the driving of the jib 4 is prioritized over the driving of the boom 3.
The boom automatic control unit 47 drives the boom 3 when the target jib angle β _dm calculated by the jib automatic control unit 46 does not fall within the movable angle range of the jib 4. That is, the boom 3 is driven when the expansion / contraction length of the jib cylinder 4a reaches the minimum value or the maximum value (when the jib cylinder 4a contracts to the minimum or extends to the maximum).

[3-3. Jib automatic control unit]
A control block diagram of the jib automatic control unit 46 is illustrated in FIG. The jib automatic control unit 46 is provided with a target jib angle calculator 60, an arm angular speed calculator 62, a target jib angular speed calculator 63, a target jib cylinder speed calculator 64, and a jib angular speed calculator 66. The jib automatic control unit 46 includes control arithmetic units 61 and 67, a feed forward gain setting unit 65, subtracters 68a and 68b, an adder 68c, and valve signal converters 69a and 69b.

The target jib angle calculator 60 calculates the target value of the angle of the jib 4 that must be moved in order to move the tip of the arm 5 in the vertical direction while the posture of the boom 3 is fixed, as the target jib angle β _dm . Is. The target jib angle calculator 60 receives information on the work range selected by the data switch 36, the boom angle α, the jib angle β, and the arm angle γ. Here, as shown in FIG. 14, the horizontal distance from the axis a to the axis c is set to X _dm1 . The target jib angle calculator 60 calculates a target jib angle β _dm for moving the jib 4 so that the horizontal distance X _dm1 becomes constant as the arm 5 moves. The horizontal distance X _dm1 is given by Equation 3 below.

Further, as shown in FIG. 15, the distance L _ac from the axis a to the axis c is given by the following expression 4.

In FIG. 15, an auxiliary line Z ₁ passing through the axis a and parallel to the Z axis is shown. If the angle between the line segment ac and the auxiliary line Z ₁ is β _Z , the following equation 5 may be satisfied in order for the horizontal distance X _{dm1 to} be constant. Therefore, the angle β _Z can be expressed as the following expressions 6 and 7. Equation 6 shows a case where the axis c is located above the axis a, and Equation 7 shows a case where the axis c is located below the axis a.

Further, as shown in FIG. 15, when the angle formed by the line segment ac and the line segment ab is β ₃ , the angle β ₃ can be obtained by the following Expression 8.

Therefore, the target jib angle β _dm is given by Equation 9 below. The target jib angle β _dm calculated by the target jib angle calculator 60 in this way is transmitted to the subtractor 68a.

The subtractor 68 a subtracts the actual jib angle β from the target jib angle β _dm calculated by the target jib angle calculator 60 to obtain a difference, and transmits the difference to the control calculator 61.
The control calculator 61 performs a PI control calculation based on the difference obtained by the subtractor 68a, and calculates a position feedback control signal for setting the angle β of the jib 4 to the target jib angle β _dm . The position feedback control signal calculated here is transmitted to the adder 68c.

  The arm angular velocity calculator 62 calculates the arm angular velocity γ ′ by differentiating the detected value of the arm angle γ detected by the arm angle sensor 9 with respect to time. The arm angular velocity γ ′ calculated here is transmitted to the target jib angular velocity calculator 63. In the following formulas, dot notation is used as a differential symbol, and in the text, a prime symbol is used instead of dot notation for convenience.

The target jib angular velocity calculator 63 (target boom angular velocity calculating means) calculates the target value of the angular velocity of the jib 4 necessary for moving the tip of the arm 5 in the vertical direction as the target jib angular velocity β _dm ′. Differentiating both sides of Equation 3 above yields Equation 10 below.

Therefore, the target jib angular velocity β _dm ′ with respect to the arm angular velocity γ ′ is given by the following equation 11. The target jib angular velocity β _dm ′ calculated here is transmitted to the target jib cylinder velocity calculator 64 and the subtracter 68b.

The jib angular velocity calculator 66 calculates the jib angular velocity β ′ by differentiating the detected value of the jib angle β detected by the jib angle sensor 8 with respect to time. The jib angular velocity β ′ calculated here is transmitted to the subtractor 68b.
The subtractor 68 b subtracts the actual jib angular velocity β ′ from the target jib angular velocity β _dm ′ calculated by the target jib angular velocity calculator 63 to obtain a difference and transmits the difference to the control calculator 67.
The control calculator 67 performs a PI control calculation based on the difference obtained by the subtractor 68b, and calculates an angular velocity feedback control signal for setting the angular velocity β ′ of the jib 4 to the target jib angular velocity β _dm ′. The angular velocity feedback control signal calculated here is transmitted to the adder 68c.

The target jib cylinder speed calculator 64 (target boom cylinder speed calculator) converts the target jib angular speed β _dm ′ calculated by the target jib angular speed calculator 63 into the target jib cylinder speed V _cy2 . Placing the length of Jibushirinda 4a and X _cy2, rate of expansion and contraction of Jibushirinda 4a is given as the time differential value X _cy2 '. Here, as shown in FIG. 16, the rotation center point of the base end portion on the boom 3 side of the jib cylinder 4a is set as a support shaft d, and the rotation center point of the tip portion on the jib 4 side is set as a support shaft e. Further, the angle between the line segment ae and a line segment ab beta ₁ Distant, an angle between the line segment ao and line segment ad beta ₂ Distant, the distance between the points ad L _4, the distance between the points ae Is L ₅ , the length of the jib cylinder 4a is given by the following equations 12 and 13.

Further, when the above expression 12 is differentiated with respect to time, the following expression 14 is obtained. If the relational expression between the angular velocity β ′ of the jib 4 and the cylinder speed X _cy2 ′ is derived by arranging this, the following equation 15 is obtained.

The target jib cylinder speed V _cy2 calculated here is transmitted to the feed forward gain setting unit 65.
The feedforward gain setting device 65 calculates a speed feedforward control signal in consideration of the flow rate of hydraulic oil flowing into the jib cylinder 4a based on the input target jib cylinder speed _Vcy2 . The speed feedforward control signal calculated here is transmitted to the adder 68c.

  The adder 68c receives the position feedback control signal calculated by the control calculator 61, the angular velocity feedback control signal calculated by the control calculator 67, and the velocity feedforward control signal calculated by the feedforward gain setting unit 65. The added control signal is calculated. The control signal calculated here is transmitted to the valve signal converters 69a and 69b. When the control signal is positive, the signal of the jib electromagnetic proportional pressure reducing valve 56L is output from one signal converter 69a according to the magnitude of the control signal. When the control signal is negative, a signal is output from the other signal converter 69b, and the jib electromagnetic proportional pressure reducing valve 56R is controlled.

[3-4. Boom automatic control unit]
A control block diagram of the boom automatic control unit 47 is illustrated in FIG. The boom automatic control unit 47 has the same configuration as the jib automatic control unit 46, and includes a target boom angle calculator 70, an arm angular velocity calculator 72, a target boom angular velocity calculator 73, a target boom cylinder velocity calculator 74, and a boom. An angular velocity calculator 76 is provided. Further, the boom automatic control unit 47 is provided with control arithmetic units 71 and 77, a feed forward gain setting unit 75, subtracters 78a and 78b, an adder 78c, and valve signal converters 79a and 79b.

The target boom angle calculator 70 calculates, as the target boom angle α _dm , the target value of the angle of the boom 3 that must be moved in order to move the tip of the arm 5 in the vertical direction while the posture of the jib 4 is fixed. Is. The target boom angle calculator 70 receives information on the work range selected by the data switch 36, the boom angle α, the jib angle β, and the arm angle γ.

Here, as shown in FIG. 17, the distance from the axis o to the axis c is denoted as L _oc , and the angle between the line segment ao and the line segment ac is denoted as β ₄ . The angle β ₄ is given by Equation 16 below, and the distance L _oc is given by Equation 17 below. Note that the distance L _ac is given by the above-described equation 4, and the angle β ₃ is given by the above-described equation 8.

Here, as shown in FIG. 17, the horizontal distance from the axial center o to the axial center c is _Xdm0 . The target boom angle calculator 70 calculates a target boom angle α _dm for moving the boom 3 so that the horizontal distance X _dm0 becomes constant as the arm 5 moves. The target boom angle α _dm is given by Equation 18 below. The target boom angle α _dm calculated here is transmitted to the subtractor 78a.

The subtractor 78 a subtracts the actual boom angle α from the target jib angle α _dm calculated by the target jib angle calculator 60 to obtain a difference, and transmits the difference to the control calculator 71.
The control calculator 71 performs PI control calculation based on the difference obtained by the subtractor 78a, and calculates a position feedback control signal for setting the angle α of the boom 3 to the target boom angle _αdm . The position feedback control signal calculated here is transmitted to the adder 78c.

  The arm angular velocity calculator 72 calculates the arm angular velocity γ ′ by time-differentiating the detected value of the arm angle γ detected by the arm angle sensor 9 in the same manner as the arm angular velocity calculator 62 described above. The arm angular velocity γ ′ calculated here is transmitted to the target boom angular velocity calculator 73.

The target boom angular velocity calculator 73 (target boom angular velocity calculating means) calculates the target value of the angular velocity of the boom 3 necessary for moving the tip of the arm 5 in the vertical direction as the target boom angular velocity α _dm ′. First, _assuming that the horizontal distance _Xdm0 shown in FIG. 17 is constant, the following Expression 19 is established.

Here, when the jib angle β is regarded as a constant and differentiated with respect to time, the following Expression 20 is obtained.

Therefore, the target boom angular velocity α _dm ′ with respect to the arm angular velocity γ ′ is given by the following equation (21). The target boom angular speed α _dm ′ calculated here is transmitted to the target boom cylinder speed calculator 74 and the subtractor 78b.

The boom angular velocity calculator 76 calculates the boom angular velocity α ′ by differentiating the detected value of the boom angle α detected by the boom angle sensor 7 with respect to time. The boom angular velocity α ′ calculated here is transmitted to the subtractor 78b.
The subtractor 78 b subtracts the actual boom angular velocity α ′ from the target boom angular velocity α _dm ′ calculated by the target boom angular velocity calculator 73 to obtain a difference, and transmits the difference to the control calculator 77.

The control calculator 77 performs a PI control calculation based on the difference obtained by the subtractor 78b, and calculates an angular velocity feedback control signal for setting the angular velocity α ′ of the boom 3 to the target boom angular velocity α _dm ′. The angular velocity feedback control signal calculated here is transmitted to the adder 78c.

The target boom cylinder speed calculator 74 (target boom cylinder speed calculator) converts the target boom angular speed α _dm ′ calculated by the target boom angular speed calculator 73 into the target boom cylinder speed V _cy1 . If the length of the boom cylinder 3a is set to _Xcy1 , the expansion / contraction speed of the boom cylinder 3a is given as its time differential value _Xcy1 '. Here, based on the relational expression between the angular speed α ′ of the boom 3 and the cylinder speed X _cy1 ′ of the boom cylinder 3a obtained by the same calculation method as the calculation by the target jib cylinder speed calculator 64, the target boom cylinder speed V _cy1 is _calculated . Calculate. The target boom cylinder speed _Vcy1 obtained here is transmitted to the feed forward gain setting device 75.

The feedforward gain setting device 75 calculates a speed feedforward control signal in consideration of the flow rate of hydraulic oil flowing into the boom cylinder 3a based on the input target boom cylinder speed _Vcy1 . The speed feedforward control signal calculated here is transmitted to the adder 78c.

  The adder 78c receives the position feedback control signal calculated by the control calculator 71, the angular velocity feedback control signal calculated by the control calculator 77, and the velocity feedforward control signal calculated by the feedforward gain setting unit 75. The added control signal is calculated. The control signal calculated here is transmitted to the valve signal converters 79a and 79b. When the control signal is positive, the signal of the boom electromagnetic proportional pressure reducing valve 52L is output from one signal converter 79a according to the magnitude of the control signal. When the control signal is negative, a signal is output from the other signal converter 79b, and the boom electromagnetic proportional pressure reducing valve 52R is controlled.

[4. flowchart]
A flowchart of automatic attitude control performed by the controller 18 is illustrated in FIG. This flow is repeatedly performed when the controller 18 is energized.
In step A 10, information such as the dimensions of each member constituting the front device 29 is read from the front member data storage unit 35 and transmitted to the automatic control unit 45.

  In subsequent step A20, the boom angle α, jib angle β, and arm angle γ detected by the boom angle sensor 7, the jib angle sensor 8, and the arm angle sensor 9 are input to the automatic control unit 45. Further, the operation state of the automatic control switch 50, the boom remote control pressure detected by the boom remote control pressure sensor 54 and the jib remote control pressure detected by the jib remote control pressure sensor 58 are also input to the automatic control unit 45.

  In Step A30, the attitude of the front device 29 is calculated based on the boom angle α, the jib angle β, and the arm angle γ. Thereafter, in step A40, it is determined whether or not the automatic control switch 50 is turned on. If the automatic control switch 50 is on, the process proceeds to step A50 related to automatic attitude control. On the other hand, if it is off, the process proceeds to step A200, and automatic attitude control is not performed.

  In step A50, based on the boom remote control pressure and the jib remote control pressure, it is determined whether or not at least one of the boom 3 or the jib 4 is not operated. Here, if the boom 3 or the jib 4 is operated, it will progress to step A200 and automatic posture control will not be implemented. On the other hand, when neither the boom 3 nor the jib 4 is operated, the process proceeds to step A60.

In Step A60, it is determined whether or not the front end portion of the front device 29 (for example, the position of the axis c of the front end portion of the arm 5) is located in the work area. The work area here is either a front work area or a side work area in the first embodiment, and is a work area set according to the posture of the upper swing body 2 with respect to the lower traveling body 1. . Here, if it is within the work area, the flow ends.
As a result, even if the automatic control switch 50 is turned on, it can be freely moved while the front device 20 is located in the work area. On the other hand, if the front end portion of the front device 29 is about (or exceeds) the work area, the control proceeds to step A70.

In Step A70, the jib automatic control unit 46 and the position of the axis c at that time (that is, the position where the front device 29 is extended to the maximum and close to the working range limit) are used as a reference. In each of the boom automatic control units 47, target arm tip horizontal distances _Xdm1 and _Xdm0 are set. The target arm distal horizontal distance X _dm0 set by the boom automatic control unit 47, coincides with one of the working radius R ₂ of the working radius R ₁ or forward working area of the side work area. On the other hand, the target arm tip horizontal distance X _dm1 set by the jib automatic control unit 46 changes each time according to the posture of the front device 29.

  In step A80, the work range restriction determination unit 37 displays on the monitor console 13 in the cab that the front end of the front device 29 exceeds the preset work range, and a warning sound is output from the speaker 14. Further, the automatic posture control notifies that the front device 29 is controlled differently from the operation of the operator.

In subsequent step A90, the target jib angle β _dm is calculated in the target jib angle calculator 60 of the jib automatic controller 46. In step A100, the automatic control unit 45 controls the spool positions of the boom electromagnetic switching valves 51L and 51R and the jib electromagnetic switching valves 55L and 55R to the b position. Thereby, the operation input from the boom operation lever 42 and the jib operation lever 43 becomes invalid, and the operation pilot pressure can be freely changed.

In Step A110, it is determined whether or not the target jib angle β _dm calculated in Step A90 is within the movable angle range (within a predetermined range) of the jib 4. Here, when the target jib angle β _dm is within the movable angle range of the jib 4, the process proceeds to step A 120, and the automatic attitude control of the jib 4 is performed by the jib automatic control unit 46. Thereby, for example, the jib 4 moves up and down in conjunction with the operation of the arm 5, and the locus of the tip is controlled so that the tip of the front device 29 moves in the vertical direction. At this time, the boom 3 is in a fixed position.

On the other hand, when the target jib angle β _dm is outside the movable angle range of the jib 4, the process proceeds to step A 130, and the automatic posture control of the boom 3 is performed by the boom automatic control unit 47. Thereby, for example, the boom 3 moves up and down in conjunction with the operation of the arm 5 and the locus of the tip is controlled so that the tip of the front device 29 moves in the vertical direction. At this time, the jib 4 is in a fixed position.

  When the automatic attitude control is not performed, in step A200, the automatic control unit 45 controls the spool positions of the boom electromagnetic switching valves 51L and 51R and the jib electromagnetic switching valves 55L and 55R to the a position. Thereby, the operation input from the boom operation lever 42 and the jib operation lever 43 becomes effective, and the normal boom operation and jib operation are possible.

In subsequent Step _A210 , the target arm tip horizontal distances _Xdm1 and _Xdm0 are set in the jib automatic control unit 46 and the boom automatic control unit 47, respectively, with the position of the axis c at that time as a reference. In Step A220, it is determined whether or not the front device 20 is located in the work area. Here, when the front device 29 is in the work area, the flow is finished as it is, and when the front device 29 is outside the work area (or is about to go out of the work area), the process proceeds to Step A230.

  In step A <b> 230, the work group is controlled so that the restriction determination unit 37 stops the operation of the front device 29. For example, the boom electromagnetic proportional pressure reducing valves 52L and 52R, the jib electromagnetic proportional pressure reducing valves 56L and 56R, and the arm electromagnetic proportional pressure reducing valves 59L and 59R are completely closed to cut off the transmission of the pilot pressure, and the operation of the front device 29 is forced. To stop. This prevents the front device 29 from jumping out of the work area.

[5. Action, effect]
According to the disclosed working range control device for a work machine, when the front end of the front device 29 enters the warning area by operating the arm 5, the jib 4 is automatically tilted without the operator operating the jib 4. The x coordinate X _C of the axis c which is the tip of the arm 5 is controlled so as not to exceed the working radius in the working area. If the target jib angle β _dm does not fall within the movable angle range, the boom 3 is automatically tilted even if the operator does not operate the boom 3, and the x-coordinate X _C of the axis c is the work. It is controlled not to exceed the working radius in the area. Therefore, the locus of the tip of the front device 29 can be controlled in the vertical direction so that the tip of the front device 29 does not move outside the working range, and the stability of the work can be further improved.

In the disclosed work range control device, the jib automatic control unit 46 not only calculates the target jib angle β _dm , but also calculates the target jib angular velocity β _dm ′, and further, based on the target jib angular velocity β _dm ′ Jib cylinder speed _Vcy2 is calculated. As a result, it is possible to drive the arm tip vertically with high accuracy, and accurate trajectory control is possible.

Furthermore, in the disclosed work range control apparatus, similar trajectory control is performed not only on the jib 4 but also on the boom 3. That is, the boom automatic control unit 47 not only calculates the target boom angle α _dm , but also calculates the target boom angular velocity α _dm ′, and further calculates the target boom cylinder velocity V _cy2 based on the target boom angular velocity α _dm ′. ing. Thereby, accurate trajectory control becomes possible. Further, even if the jib 4 alone is in a posture in which the arm tip cannot be driven vertically, driving the boom 3 enables more flexible control, and the range of automatic posture control can be expanded. it can.

[6. Modified example]
Each structure and each process of 2nd embodiment can be selected as needed, or may be combined suitably. In the second embodiment described above, the work range control device according to the first embodiment is exemplified by adding the automatic posture control of the front device 29, but the basic configuration is not limited to that of the first embodiment. This work range control device can be applied to any work machine having an upper swing body on which a front device having an arm connected to the front end side and a boom connected to the base end side is pivotally supported. It is.

  Further, in the second embodiment described above, the automatic posture control that automatically drives the jib 4 or the boom 3 is performed when the tip of the arm 5 is about to exceed the working range. The starting condition of the attitude control is not limited to this. For example, regardless of the position of the tip of the arm 5, automatic posture control may always be performed when the arm 5 is operated alone with the automatic control switch 50 being turned on.

  A control flowchart in this case is illustrated in FIG. This flowchart is different from the flowchart shown in FIG. 18 in step A60, and the step is performed when the front end portion of the front device 29 (for example, the position of the axis c of the front end portion of the arm 5) is located in the work area. Proceed to A90. Thus, if the front device 20 is positioned in the work area with the automatic control switch 50 being turned on, automatic posture control is always performed, and the automatic posture control of the jib 4 (step A120) or the boom 3 Automatic attitude control (step A130) is performed.

  By such control, it becomes possible to move the tip of the arm vertically in the vertical direction at an arbitrary position, and operability can be improved. For example, the crusher 6 can be easily moved along the wall surface of a high structure, and the dismantling work can be performed efficiently.

[7. Addendum]
Regarding the second embodiment, the following additional notes are disclosed.

(Appendix 1)
A working range control device for a working machine comprising an upper revolving body on which a front device having an arm connected to a distal end side and a boom connected to a proximal end side is pivotally supported,
Arm angle detection means for detecting a nodal angle of the base end of the arm as an arm angle;
Boom angle detection means for detecting the nodal angle of the base end of the boom as a boom angle;
A computing means for computing the target boom angle that causes the boom to move horizontally in the opposite direction and the same distance as the horizontal movement distance of the arm caused by the fluctuation of the arm angle;
A working range control device for a working machine, comprising: interlocking means for interlocking the boom so that the boom angle becomes the target boom angle when the arm is moved.

(Supplement 1)
2. Description of the Related Art Conventionally, a technique for controlling the attitude of a front device has been known for the purpose of preventing the body from overturning. For example, in the case of a dismantling work machine equipped with a front device with a long dismantling specification consisting of four parts, a boom, a jib, an arm, and a crusher, a work range in which a crusher located at the front end of the front work machine is set in advance In some cases, the angle of the joint of each part is limited so as not to exceed the value, and the operation of the hydraulic cylinder for driving each part is automatically stopped. On the other hand, posture control of the front device for improving work efficiency is not performed.

  One of the attitude controls for improving the work efficiency here is a vertical movement operation of the front end of the front device. For example, when crushing an object with a large vertical dimension such as a mid-to-high-rise building, retaining wall, or chimney, you want to move it directly above or below without changing the horizontal position of the crusher There is. However, since the front device of the long dismantling specification is composed of four parts, it is difficult to move the tip linearly in the vertical direction, and the skill of the operator is required.

If the front device can be driven linearly with a simpler operation, workability during dismantling work will be improved, and it will be possible to prevent erroneous operations such as moving the front device tip along an incorrect path. Stability is also improved.
Therefore, the horizontal movement distance generated at the tip of the arm due to the fluctuation of the arm angle when the arm is operated is calculated. In addition, a target boom angle that causes horizontal movement in the opposite direction at the same distance as this movement distance to the tip of the boom is calculated. That is, the boom is driven so that at least the tip of the arm does not move in the horizontal direction when the arm is operated. By such control, it becomes possible to move the tip of the arm in the vertical vertical direction, and operability can be improved.

  Here, the arms and booms are defined only by the positional relationship of at least the front end side and the base end side in the front device. For example, when the front device is composed of four parts, that is, a boom, a jib, an arm, and a crusher, the interlocking unit may link the jib when the arm is moved, or may move the arm when the crusher is moved. Good. That is, any configuration may be used as long as the horizontal movement of the distal end is canceled by the rocking of the proximal end member.

(Appendix 2)
And further comprising storage means for storing the work range of the front device,
The work range control device for a work machine according to claim 1, wherein the interlocking means interlocks the boom when the front device tries to exceed the work range.

(Supplement 2)
When it is necessary to move the front end of the front device near the boundary of the working range, it becomes possible to control the front end position of the front device so as not to cross the boundary, improving workability and stability. be able to.

(Appendix 3)
The work machine according to appendix 1 or 2, wherein the control means includes target boom cylinder speed calculating means for calculating a target value of a telescopic speed of a boom cylinder that drives the boom based on the target boom angle. Work range control device.

(Supplement 3)
By calculating not only the target value of the boom angle but also the target value of the boom speed, and further calculating the target value of the expansion and contraction speed of the boom cylinder, it is possible to drive the arm tip vertically with high accuracy and an accurate trajectory. Control becomes possible.

[Third embodiment]
[1. Aircraft configuration]
Components corresponding to the above-described elements will be described using the same reference numerals. The work range control device disclosed as the third embodiment is different from the work range control device of the first embodiment in the method for limiting the operation of the boom 3, and the boom angle sensor 7 in the excavator 30 shown in FIG. Instead of this, a device for detecting the boom angle α shown in FIGS. 20 (a) and 20 (b) is provided.

  That is, a pair of boom proximity switches 81a and 81b and a boom plate 82 (base end plate) are provided at the base end portion of the boom 3 of the excavator 30. The pair of boom proximity switches 81a and 81b are fixed to the upper swing body 2 side via the mounting bracket 81c, and the boom plate 82 is fixed to the boom 3 at a position facing the boom proximity switches 81a and 81b. The pair of boom proximity switches 81a and 81b detects the presence of the boom plate 82 within the detection range, and transmits a signal to a relay circuit C7 described later.

As shown in FIG. 20 (a), the mounting bracket 81c, for example a boom angle alpha is arranged along a line segment oa directed from the axis o the axis a when the orientation is a predetermined value alpha _0, the upper revolving It is fixed to the swing frame 83 of the body 2. The boom proximity switches 81a and 81b are both fixed on the mounting bracket 81c so as to be positioned on the line segment oa.

  On the other hand, as shown by a broken line in FIG. 20A, the boom plate 82 has a first plate portion 82a having an end coincident with an imaginary line F passing through the axis o in a side view, and the same axis o. And a second plate portion 82b having an end that coincides with the imaginary line S passing therethrough. The first plate portion 82a is formed in a surface shape corresponding to a locus generated when the end side coinciding with the virtual line F is moved in an arc shape with the axis o as the center. Similarly, the 2nd plate part 82b is formed in the surface shape corresponding to the locus | trajectory produced when the edge side which corresponds to the virtual line S centering on the axial center o is moved in circular arc shape.

In FIG. 20A, the angle between the line segment oa and the virtual line F is α ₁ , and the angle between the line segment oa and the virtual line S is α ₂ (where α ₁ > α ₂ ). Further, the first plate portion 82a is fixed at a position facing one boom proximity switch 81a on the side surface of the boom 3, and the second plate portion 82b is fixed at a position facing the other boom proximity switch 81b.

Thus, one boom proximity switch 81a detects the presence of the first plate portion 82a within the detection range and transmits a signal to the controller 18 when the boom angle α is equal to or greater than (α ₀ −α ₁ ). . When the boom angle α is less than (α ₀ −α ₁ ), the first plate portion 82a is not detected. That is, one boom proximity switch 81a functions as a means for determining whether or not the boom angle α is equal to or greater than (α ₀ −α ₁ ).

Similarly, the other boom proximity switch 81b detects the presence of the second plate portion 82b within the detection range and transmits a signal to the controller 18 when the boom angle α is equal to or greater than (α ₀ −α ₂ ). . When the boom angle α is less than (α ₀ −α ₂ ), the second plate portion 82b is not detected. That is, the other boom proximity switch 81b functions as a means for determining whether or not the boom angle α is equal to or greater than (α ₀ −α ₂ ).

  The fixing positions of the boom plate 82 and the boom proximity switches 81a and 81b can be changed as appropriate. For example, these may be built in the boom 3, or the boom plate 82 may be fixed to the swing frame 83 side, and the boom proximity switches 81a and 81b may be fixed to the boom 3 side.

  In addition, the hydraulic excavator 30 includes a pair of plates 10a and 10b and a pair of proximity switches 11L and 11R similar to those of the first embodiment as a device for detecting the turning angle of the upper swing body 2 with respect to the lower traveling body 1. Is provided. The pair of proximity switches 11L and 11R detects the presence of the pair of plates 10a and 10b within the detection range, and transmits a signal to the controller 18 and a relay circuit C7 described later.

The two types of boom angles detected by the boom proximity switches 81 a and 81 b are used as threshold values for the movable range of the boom 3 corresponding to the work area of the excavator 30. For example, as shown in FIG. 21, the minimum boom angle in the side work area is set to (α ₀ −α ₂ ), and the minimum boom angle in the front work area is smaller than (α ₀ −α ₂ ) ( α ₀ −α ₁ ).

Note that the maximum boom tip distance in the side work area (horizontal distance from the axis o to the axis a) is L ₁ cos (α ₀ -α ₂ ), and the maximum boom tip distance in the front work area is L ₁ cos (α ₀ -α ₁ ). That is, in the front work area, the tip of the boom 3 can be positioned farther from the body than the side work area, and the work range in the front work area is expanded.

Such control for expanding the work range is performed only when the front work switch 12 is turned on. When the front work switch 12 is off, the minimum boom angle is set to the set value (α ₀ −α ₂ ) in the side work area even if the front device 29 is located in the front work area.

[2. Pilot circuit]
FIG. 22 shows a hydraulic circuit of the excavator 30. The hydraulic circuit is provided with a main circuit C1 through which hydraulic oil supplied to a hydraulic actuator (various hydraulic drive devices) flows and a plurality of pilot circuits. The main circuit C1 is the same as that of the first embodiment. In the first embodiment, the boom limiting electromagnetic valve 15 of the boom pilot circuit C3 is exemplified by being controlled by the controller 18, but in the third embodiment, the boom limiting electromagnetic valve 15 is controlled by a relay circuit C7 described later. The

  The turning restriction solenoid valves 23L and 23R interposed in the turning pilot circuit C2 block the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 when the spool position is the b position, and the turning control valve 22 Is released (communication) to the hydraulic oil tank 24 side. Further, when the spool position is at the position a, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 is connected. The turning restriction solenoid valves 23L and 23R have a characteristic that the spool position is set to the b position when energized and the spool position is set to the a position when not energized.

  The boom limiting solenoid valve 15 interposed in the boom pilot circuit C3 shuts off the pilot passage between the boom remote control valve 42R and the boom control valve 26 when the spool position is at the position b, and the pilot pressure of the boom control valve 26 is increased. Open (communication) to the hydraulic oil tank 24 side. Further, the pilot passage between the boom remote control valve 42R and the boom control valve 26 is connected when the spool position is the position a. The boom limiting solenoid valve 15 has a characteristic that the spool position is in the b position when energized and the spool position is in the a position when de-energized.

[3. Relay circuit]
As shown in FIG. 23, the relay circuit C7 is roughly divided into four circuits, a first circuit C7 _A , a second circuit C7 _B , a third circuit C7 _C, and a fourth circuit C7 _D. Note that the symbol + B shown in FIG. 23 indicates a DC power supply line, and the symbol GND indicates a ground line.

The first circuit C7 _A, a circuit for switching the state of the excitation / non-excitation of the relay according to a pair of proximity switches 11L, 11R and a pair of boom proximity switches 81a, 81b on / off state. Here, a first relay coil 84, a second relay coil 85, a third relay coil 86, and a fourth relay coil 87 are provided corresponding to the proximity switches 11L and 11R and the boom proximity switches 81a and 81b. Each relay coil is energized when the switch is on.

Second circuit C7 _B is a circuit for switching the state of the excitation / non-excitation of the fifth relay coil 88 according to the state of the on / off the front working switch 12. The second circuit C7 on _B, fifth relay coil 88 and the front work switch 12 is interposed in series from the ground line side. The circuit branches into two on the power supply line side from the front work switch 12, and each circuit is connected to the power supply line. A contact 84a of the first relay coil 84 and a contact 85a of the second relay coil 85 are interposed in series in one of these two parallel circuits. Further, a contact 88a for self-holding the energization state of the fifth relay coil 88 is interposed on the other circuit.

The contact 84 a is a contact that is turned on when the first relay coil 84 is excited, and the contact 85 a is a contact that is turned on when the second relay coil 85 is excited. For example, when the front device 29 is located in the front work area, both the contacts 84a and 85a are turned on.
The contact 88a is a contact that is turned on when the fifth relay coil 88 is excited, and has a function of self-holding the energized state of the fifth relay coil 88. Accordingly, when the front work switch 12 is turned on when the front device 29 is located in the front work area, the fifth relay coil 88 is excited, and thereafter, the fifth relay is operated unless the front work switch 12 is turned off. The coil 88 continues to be excited.

The third circuit C7 _C is a circuit for controlling the turning restriction electromagnetic valves 23R and 23L related to the turning operation in accordance with the detection state of the proximity switches 11L and 11R. The third circuit power supply line side of the C7 _C, contact 88b which is turned on when the excitation of the fifth relay coil 88 is interposed. Further, the circuit branches into two on the ground line side from the contact 88b, and each circuit is connected to the ground line.

  In one of these two parallel circuits, a turning restriction electromagnetic valve 23R related to a right turning operation and a contact 84b of the first relay coil 84 are interposed in series. The contact 84 b is a contact that is turned off when the first relay coil 84 is excited. On the other circuit, a turning control electromagnetic valve 23L related to the left turning operation and a contact 85b of the second relay coil 85 are interposed in series. The contact 85 b is a contact that is turned off when the second relay coil 85 is excited. Accordingly, when the proximity switch 11R is turned off (the plates 10a and 10b are not detected) when the fifth relay coil 88 is excited, the turning restriction electromagnetic valve 23R is energized. Further, when the proximity switch 11L is turned off (the plates 10a and 10b are not detected) when the fifth relay coil 88 is excited, the turning restriction electromagnetic valve 23L is energized.

Fourth circuit C7 _D is a circuit for controlling according boom limit electromagnetic valve 15 according to the boom operating boom proximity switch 81a, the detection state at 81b. Fourth circuit C7 _D includes a line buzzer 90 is interposed, the line boom limit electromagnetic valve 15 is interposed, and a connecting passage 89 which connects between these two lines. The buzzer 90 and the boom limiting electromagnetic valve 15 are provided on the ground line side of each line, and the connection path 89 connects the power line side with respect to the buzzer 90 and the boom limiting electromagnetic valve 15.

A contact 88 c of the fifth relay coil 88 and a contact 86 a of the third relay coil 86 are interposed in one of the two circuits closer to the power supply line than the connection path 8. On the other side, a contact 88d of the fifth relay coil 88 and a contact 87a of the fourth relay coil 87 are interposed.
The contact 88 c is a contact that is turned on when the fifth relay coil 88 is excited, and conversely, the contact 88 d is a contact that is turned off when the fifth relay coil 88 is excited. The contact 86 a is a contact that is turned off when the third relay coil 86 is excited, and the contact 87 a is a contact that is turned off when the fourth relay coil 87 is excited.

In the fourth circuit C7 _D, at the time of energization of the fifth relay coil 88, the buzzer 90 and the boom restriction solenoid valve 15 is energized in response to the state of the excitation / non-excitation of the third relay coil 86. On the other hand, when the fifth relay coil 88 is excited, the buzzer 90 and the boom limiting solenoid valve 15 are energized in accordance with the excitation / non-excitation state of the fourth relay coil 87 instead of the third relay coil 86.

[4. Action]
[4-1. When the swivel operation / forward operation switch is off]
In a state where the front work switch 12 is turned off, the second circuit C7 _B in relay circuit C7 is not energized. Fifth relay coil 88 becomes de-energized state, the contact 88b of the third circuit C7 _C is turned off. As a result, the turning restriction solenoid valves 23L and 23R are de-energized regardless of the detection states of the proximity switches 11L and 11R, and the spool position is set to the a position. Therefore, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 communicates, and a normal operation state in which the left and right turning operation by the turning operation lever 21 is allowed is obtained.

[4-2. When the boom operation / forward operation switch is off]
In the fourth circuit C7 _D in the relay circuit C7, contact 88d is turned on with the contact 88c is turned off. The buzzer 90 and the boom limiting solenoid valve 15 are energized when the fourth relay coil 87 is closed, that is, when the boom side switch 81b does not detect the presence of the second plate portion 82b. Limited to.

That is, when the boom angle α is equal to or greater than (α ₀ −α ₂ ), the buzzer 90 and the boom limit solenoid valve 15 are not energized, and the spool position of the boom limit solenoid valve 15 is the a position. Accordingly, the pilot passage between the boom remote control valve 42R and the boom control valve 26 communicates, and a normal operation state in which the operation of the boom 3 by the boom operation lever 42 is allowed is obtained.

On the other hand, when the boom lowering operation is continued and the boom angle α becomes less than (α ₀ −α ₂ ), the boom proximity switch 81b is disconnected and the fourth relay coil 87 is de-energized. Also, the contacts 88d of the fourth circuit C7 _D is turned on, the buzzer 90 and the boom restriction solenoid valve 15 is energized. As a result, a warning sound is emitted from the buzzer 90, the spool position of the boom restriction solenoid valve 15 is switched to the b position, and further boom lowering operations are restricted.

[4-3. When the swivel operation / forward operation switch is on]
In a state where the front device 29 of the hydraulic excavator 30 is located in front work area, the first relay coil 84 and a second relay coil 85 are both energized with the first circuit C7 _A in relay circuit C7. When the front working switch 12 in a state where the front device 29 is located in front work area is operated on, the second circuit C7 fifth relay coil 88 is excited by the contact 88a of the _B closes (turns on) The excitation state is self-maintained. Further, the contact 88b of the third circuit C7 _C is turned on.

In this case, the proximity switch 11L, 11R are both plates 10a, if the detected one of the 10b, the contact 84b of the third circuit C7 _C, 85b are both turning limit solenoid valve because it is off 23L, 23R is not Energization is performed, and these spool positions become the b position. Therefore, the pilot passage between the turning remote control valves 21L and 21R and the turning control valve 22 communicates, and a normal operation state in which the left and right turning operation by the turning operation lever 21 is allowed is obtained.

Further, for example, when the front device 29 tries to enter the lateral work area by an operation in the right turn direction, the one proximity switch 11R does not detect the plates 10a and 10b, and the first relay coil 84 is de-energized. Thus, contact 84b of the third circuit C7 _C is turned on, the turning limit electromagnetic valve 23R according to the right turn operation is energized. Therefore, the spool position of the turning restriction electromagnetic valve 23R is switched to the b position, and the spool position of the turning control valve 22 returns to neutral. The right turn of the upper swing body 2 is stopped, and further turning is prohibited.

At this time, the other proximity switch 11L still plates 10a, if detects 10b, the second relay coil 85 remains energized, the contacts 85b of the third circuit C7 _C is off. Therefore, the spool position of the turning restriction electromagnetic valve 23L related to the left turning operation related to the left turning operation is maintained at the position a, and the left turning operation of the upper swing body 2 (that is, for returning the turning angle to the front work area side). Operation) is allowed.
The same applies to the case where the front device 29 tries to enter the side work area by an operation in the left turn direction, for example. The left turn of the upper swing body 2 is stopped, and further turning is prohibited and the right turn is prohibited. A turning operation is allowed.

[4-4. When the boom operation / forward operation switch is on]
In the fourth circuit C7 _D in the relay circuit C7, along with contact 88c is turned on, the contacts 88d are turned off. The buzzer 90 and the boom limiting solenoid valve 15 are energized when the third relay coil 86 closes the contact 86a, that is, when the boom side switch 81a does not detect the presence of the first plate portion 82a. Limited to.
That is, when the boom angle α is equal to or greater than (α ₀ −α ₁ ), the buzzer 90 and the boom limiting solenoid valve 15 are not energized, and the spool position of the boom limiting solenoid valve 15 is the a position. Accordingly, the pilot passage between the boom remote control valve 42R and the boom control valve 26 communicates, and a normal operation state in which the operation of the boom 3 by the boom operation lever 42 is allowed is obtained.

The angle (α ₀ −α ₁ ) here is an angle smaller than the angle (α ₀ −α ₂ ) described above. That is, when the front work switch 12 is turned on, a boom lowering operation that allows the boom angle α to be smaller than that during the off operation is permitted. Therefore, as shown in FIG. 21, the boom 3 can be inclined deeper in the front work area than in the side work area. As the boom angle α is smaller, the horizontal distance L _BM from the axis o at the base end of the boom 3 to the axis a at the tip increases.

On the other hand, when the boom lowering operation is continued and the boom angle α becomes less than (α ₀ −α ₁ ), the boom proximity switch 81b is disconnected and the fourth relay coil 87 is de-energized. Also, the contacts 88d of the fourth circuit C7 _D is turned on, the buzzer 90 and the boom restriction solenoid valve 15 is energized. As a result, a warning sound is emitted from the buzzer 90, the spool position of the boom restriction solenoid valve 15 is switched to the b position, and further boom lowering operations are restricted.

[5. effect]
As described above, according to the work range control device of the disclosed work machine, different minimum boom angles are set for each of the front work area and the side work area, and the front work area particularly advantageous in terms of airframe stability. The scope of work at will be greatly expanded. That is, when the turning posture is the forward posture, the inclination of the boom 3 can be made larger (the minimum boom angle is made smaller) than in the side posture, and the work range can be easily determined while ensuring stability. And workability can be improved. Moreover, when the turning posture of the upper turning body 2 is a side posture, the inclination of the boom 3 can be reduced (the minimum boom angle can be increased), and the stability can be improved.

  Further, by limiting the elevation angle of the base end portion of the front device 29, the working range of the front device 29 can be easily determined, and a simple control configuration can be achieved. For example, although the controller 18 of the first embodiment calculates the coordinates of the tip of the arm 5, such a calculation can be omitted and the work range can be controlled only by the boom angle α.

  Further, according to the disclosed work range control apparatus, not only the controller 18 but also the boom angle sensor 7 can be dispensed with regarding the posture control of the boom 3. In particular, in the work range control device of the third embodiment, the minimum boom angle can be reliably ensured without increasing the cost with a simple configuration in which the boom proximity switches 81a and 81b and the boom plate 82 are provided at the base end portion of the boom 3. Can be grasped. Further, since the boom limiting solenoid valve 15 and the swing limiting solenoid valves 23L and 23R are controlled using the relay circuit C7 that operates based on the detection state of the boom proximity switches 81a and 81b, the application to the conventional system is possible. It is easy and the cost can be reduced as compared with the conventional system.

Further, in the disclosed work range control apparatus, the conditions for expanding the work range (conditions for bringing the fifth relay coil 88 into the excited state) are the proximity state detection and the forward work switch in the proximity switches 11L and 11R. This is an AND condition with 12 ON operations. Therefore, in the unlikely event that any sensor or switch fails or a disconnection occurs, the minimum boom angle is always set to (α ₀ −α ₂ ) on the stable side. Therefore, the stability of control can be improved.

[6. Modified example]
Each structure and each process of 3rd embodiment can be selected as needed, or may be combined suitably. In the above-described third embodiment, the modification of the method for limiting the operation of the boom 3 in the work range control device of the first embodiment is illustrated, but the basic configuration is not limited to that of the first embodiment. . This work range control device can be applied to any work machine having an upper swing body on which a front device having an arm connected to the front end side and a boom connected to the base end side is pivotally supported. It is.

In the third embodiment described above, the minimum boom angle that is different between the front work area and the side work area is set, but the size of the minimum boom angle is not a preset fixed value, but the type of the front device 29. Alternatively, the variable may be corrected according to the weight of the crusher 6, the inclined state of the lower traveling body 1 (the stability of the road surface), or the like. Alternatively, instead of setting the two-stage minimum boom angle, a multi-stage minimum boom angle may be set. In this case, the minimum boom angle is set to be smaller as the front direction of the upper swing body 2 is closer to the longitudinal direction of the lower traveling body 1, and the minimum boom is set as the front direction of the upper swing body 2 is closer to the vehicle width direction of the lower traveling body 1. It is conceivable to set a large angle.
With such a configuration, it is possible to further expand the work range while ensuring the airframe stability, and to improve workability.

[7. Addendum]
Regarding the third embodiment, the following additional notes are disclosed.

(Appendix 1)
A work range control device for a work machine including a lower traveling body that rotatably supports an upper swing body on which a front device is pivotally supported,
An elevation angle detecting means for detecting a proximal end elevation angle of the front device;
A work range control device for a work machine, comprising: control means for restricting an operation in a direction in which a base end elevation angle of the front device decreases.

(Supplement 1)
The posture of the front device changes according to the size and angle of each part constituting the front device. For example, in the case of a dismantling work machine equipped with a front device of a long dismantling specification consisting of four parts of a boom, jib, arm and crusher, by providing a plurality of angle sensors for detecting the angle of the joint of each part, It is possible to calculate the correct posture of the front device. However, an electronic control device is required to perform the calculation based on the detection signal of the angle sensor, and the system becomes expensive.

  One of the factors that greatly affects the horizontal extension distance of the front device from the airframe is the base end elevation angle. That is, it is possible to grasp the general state of the posture of the front device by referring to the elevation angle of the base end portion of the front device. Further, by restricting the operation in the direction in which the base end elevation angle decreases, the front device is restrained from moving forward, so that the working range of the front device is limited. Therefore, it is possible to manage the working range of the front device only by the elevation angle of the base end portion without calculating the position of the front end portion of the front device accurately using, for example, an electronic control device, etc. The operability and workability can be improved.

(Appendix 2)
A turning posture detecting means for detecting a turning posture of the upper turning body with respect to the lower traveling body;
The control means restricts the minimum value of the elevation angle of the base end of the front device to a first predetermined value or more when the turning posture is a side posture facing the side of the lower traveling body, and The supplementary note 1, wherein the minimum value is limited to a second predetermined value that is smaller than the first predetermined value when the turning posture is a front posture facing the front or the rear of the lower traveling body. Work range control device for work machines.

(Supplement 2)
By limiting the minimum value of the base end elevation angle according to the turning posture, it is possible to improve workability while ensuring stability. For example, when the turning posture of the upper turning body is a side posture, the working range of the front device can be narrowed to improve the stability. On the other hand, when the turning posture is the forward posture, the working range of the front device can be extended farther than when the side posture is set.

(Appendix 3)
The elevation angle detecting means is fixed to one of the base end of the front device and the upper swing body, and is fixed to the other of the base end of the front device and the upper swing body, A boom proximity switch for detecting the proximity state of the plate,
The work range control device for a work machine according to appendix 1 or 2, wherein the control means controls the elevation angle of the base end portion based on the proximity state detected by the boom proximity switch.

(Supplement 3)
With a simple configuration, the elevation angle of the base end can be ascertained without increasing the cost.

(Appendix 4)
The control means includes a switching valve interposed on a pilot operation circuit of the front device, and a relay circuit that switches a spool position of the switching valve based on the proximity state detected by the boom proximity switch. The working range control device for a working machine according to supplementary note 3, characterized in that it is a feature.

(Supplement 4)
Control of the switching valve using a relay circuit makes it easier to simplify the configuration. In addition, it can be easily applied to a conventional system, and the cost can be reduced as compared with the conventional system.

  The present invention can be applied to all work range control devices for work machines (for example, hydraulic excavators, hydraulic cranes, etc.) equipped with a front work machine.

DESCRIPTION OF SYMBOLS 1 Lower traveling body 2 Upper turning body 3 Boom 3a Boom cylinder 4 Jib 4a Jib cylinder 5 Arm 5a Arm cylinder 6 Crusher 6a Bucket cylinder 7 Boom angle sensor (angle detection means)
8 Jib angle sensor (angle detection means)
9 Arm angle sensor (angle detection means)
10a, 10b Plate (plate member)
11L, 11R proximity switch (turning posture detection means)
12 Front work switch 13 Monitor console 14 Speaker 15 Boom limiting solenoid valve 16L, 16R Jib limiting solenoid valve 17L, 17R Arm limiting solenoid valve 18 Controller (control means)
21 turning operation levers 21L, 21R turning remote control valve 22 turning control valves 23L, 23R turning restricting solenoid valve 29 front device 30 hydraulic excavator 31 position calculating section (position calculating means)
32 Side work range data storage unit (first storage means)
33 Front work range data storage unit (second storage means)
34 Turning angle determination unit 35 Front member data storage unit 37 Work range restriction determination unit 42 Boom operation levers 42L and 42R Boom remote control valve 43 Jib operation levers 43L and 43R Jib remote control valve 44 Arm operation levers 44L and 44R Arm remote control valve 45 Automatic control (Trajectory control means)
46 Jib automatic control unit 47 Boom automatic control unit 50 Automatic control switch (vertical movement switch)
51L, 51R Boom electromagnetic switching valve 52L, 52R Boom electromagnetic proportional pressure reducing valve 53 Shuttle valve 54 Boom remote pressure sensor 55L, 55R Jib electromagnetic switching valve 56L, 56R Jib electromagnetic proportional pressure reducing valve 57 Shuttle valve 58 Jib remote pressure sensor 59L, 59R Arm Electromagnetic proportional pressure reducing valve 60 Target jib angle calculator 61 Control calculator 62 Arm angular velocity calculator 63 Target jib angular velocity calculator (target boom angular velocity calculator)
64 Target jib cylinder speed calculator (target boom cylinder speed calculator)
65 Feed forward gain setter 66 Jib angular velocity calculator 67 Control calculator 69a, 69b Valve signal converter 70 Target boom angle calculator 71 Control calculator 72 Arm angular velocity calculator 73 Target boom angular velocity calculator (target boom angular velocity calculator)
74 Target boom cylinder speed calculator (target boom cylinder speed calculator)
75 Feed forward gain setter 76 Boom angular velocity calculator 77 Control calculator 79a, 79b Valve signal converter 81a, 81b Boom proximity switch 81c Mounting bracket 82 Boom plate (base plate)
82a First plate portion 82b Second plate portion 83 Swing frame 90 Buzzer C1 Main circuit C2 Rotating pilot circuit C3 Boom pilot circuit C4 Jib pilot circuit C5 Arm pilot circuit C6 Relay circuit C7 Relay circuit

Claims (8)

A work range control device for a work machine including a lower traveling body that rotatably supports an upper swing body on which a front device is pivotally supported,
A turning posture detecting means for detecting a turning posture of the upper turning body with respect to the lower traveling body;
First storage means for storing a side work range as a work range of the front device;
Second storage means for storing a front work range in which a horizontal distance from the machine body center to the outer end of the work machine is set larger than the side work range as the work range of the front device;
When the turning posture is a side posture facing the side of the lower traveling body, the working range of the front device is limited to the inner side of the side working range, and the turning posture of the lower traveling body is A work range control device for a work machine, comprising: a control unit that expands the work range of the front device to the inside of the front work range when the front posture is directed forward or rearward. Angle detecting means for detecting a node angle of the front device;
Position calculating means for calculating the position of the front end portion of the front based on the node angle detected by the angle detecting means;
The control means
When the turning posture is the side posture, the operation of the front device in which the position calculated by the position calculating means exceeds the outer end of the side work range is prohibited,
When the turning posture is the front posture, the operation of the front device is permitted until the position calculated by the position calculating means does not exceed the outer end of the front work range. Item 2. A work range control device for a work machine according to Item 1. The work range control of the work machine according to claim 2, wherein when the turning posture is the forward posture, the control means prohibits the turning posture from being a posture other than the forward posture. apparatus. A plate member provided on one of the lower traveling body and the upper swing body;
A proximity switch that is provided on either one of the lower traveling body and the upper swing body so as to face the plate member, and detects a proximity state of the plate member;
A forward work switch operated in two positions on / off by a passenger of the work machine,
The control means
The front device until the position calculated by the position calculation means does not exceed the outer end of the front work range when the proximity state is detected by the proximity switch and the front work switch is turned on. Allow operation,
The same control as that when the turning posture is the side posture is performed when the proximity state is detected by the proximity switch and the forward work switch is turned off. 2. A work range control device for a work machine according to 2 or 3. The front device has an arm coupled to the distal end side and a boom coupled to the proximal end side,
The angle detection means detects the node angles of the base ends of the arms and the boom,
A vertical movement switch that is operated in two positions on / off by a passenger of the work machine;
When operating the arm with the vertical movement switch turned on, the boom is operated simultaneously with the arm based on the nodal angle of the base end of the arm and the nodal angle of the base end of the boom. The work range control device for a work machine according to any one of claims 2 to 4, further comprising trajectory control means for moving the tip of the arm in a vertical direction. The trajectory control means is
Target boom angular velocity calculating means for calculating a target value of the angular velocity of the boom;
6. A working range of a working machine according to claim 5, further comprising target boom cylinder speed calculating means for calculating a target value of a telescopic speed of a boom cylinder that drives the boom based on the target value of the angular speed. Control device. The control means
When the turning posture is the side posture, the minimum value of the base end elevation angle of the front device is limited to a first predetermined value or more, and when the turning posture is the front posture, the minimum value The work range control device for a work machine according to any one of claims 1 to 6, characterized in that is limited to a second predetermined value that is smaller than the first predetermined value. A base plate fixed to either the base end of the front device or the upper swing body;
A boom proximity switch that is fixed to either the base end portion of the front device or the upper swing body and detects the proximity state of the base end plate;
The work range control device for a work machine according to claim 7, wherein the control means controls an elevation angle of the front device based on the proximity state detected by the boom proximity switch.

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