JP2007186886A - Attachment for working machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an attachment for a working machine which can keep a braking force of an arm constant over a long period of time when the arm is turned by a touch-turn. <P>SOLUTION: A flow of oil in a hydraulic motor 10 for turning the arm 2 is stopped, the hydraulic motor 10 is used as a braking mechanism, and a drain port 14 of the hydraulic motor 10 and piping 31a for a hydraulic cylinder are connected to each other by means of branch connection piping 33. Thus, since pressure oil is automatically supplied to the hydraulic motor 10 from the side of the piping 31a, the hydraulic motor 10 is constantly filled with the pressure oil, so that the braking force can be kept constant over a long period of time. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an attachment for a construction machine that crushes a structure with an arm, for example.

  One type of work machine attachment is a crusher called a free swivel type crusher. This is a crushing mechanism in which an arm for crushing a structure and a hydraulic cylinder for opening and closing the arm are attached to a freely pivotable bracket having a sliding plate and do not have a drive source for rotating the arm. Machine. For this reason, when the arm of the free swirling crusher is rotated to change the position, it is necessary to operate a so-called turning operation in which a work machine or the like is operated to cause the arm to collide with a structure or the like and rotate. It was. When the arm is rotated by this contact, it is difficult to finely adjust the angle, and an operator who operates the work machine or the like needs high skill.

  Furthermore, in the free swirling crusher, the rotation of the arm is braked by a sliding plate attached to the bracket. This braking force is generated by pressing the frame supporting the arm against the sliding plate, and the adjustment of the braking force is adjusted by displacing the position of the frame by tightening the nut. However, in this free swirling crusher, the sliding plate is worn out in a relatively short period of time, so that the braking force is lost in a short period of time. Furthermore, since it is necessary to tighten the nut to displace the position of the frame for adjusting the braking force, the crushing operation must be stopped each time adjustment is performed, leading to a decrease in workability.

  In contrast to this free swirling crusher, there is a so-called hydraulic swirling crusher that can finely adjust the position of the arm by rotating the arm with a hydraulic motor (see Patent Document 1). . This is because an arm for crushing a structure and a hydraulic cylinder for opening and closing the arm are supported by a frame, and are attached to a bracket having a hydraulic motor and a swing bearing. It is a crusher that is driven. As a result, when the position is changed by rotating the arm, the position of the arm can be changed only by driving the hydraulic motor, and further fine adjustment can be easily performed. Therefore, the hydraulic turning crusher does not require the high skill level described above.

JP 07-127280 A

  In the hydraulic swirl crusher described above, the arm is rotated by driving a hydraulic motor. Then, after turning the arm to a predetermined position, the directional switching valve provided in the hydraulic supply source stops feeding the pressure oil so that the hydraulic motor stops driving, and flows to the hydraulic motor. Stop moving oil. As a result, after the arm is rotated to an arbitrary position, the hydraulic motor is not driven, and on the contrary, the rotation of the arm is braked, so that the arm is fixed at a predetermined position. Furthermore, some of these hydraulic swirling crushers are provided with a brake valve in the hydraulic motor, and when the pressure oil feeding is stopped, it is added to the hydraulic motor by this brake valve and the counter balance valve. The hydraulic pressure can be adjusted. By adjusting the hydraulic pressure, the braking force exerted by the hydraulic motor can be kept constant. Thereby, it becomes possible to use a hydraulic motor as a braking mechanism, and it is possible to perform contact like a free swirling crusher. Furthermore, since the hydraulic motor serves as a braking mechanism, it does not wear like a sliding plate, and adjustment work is almost unnecessary, so that workability is improved.

  However, in the above-described mode, when the hydraulic rotation is not performed for a long time and only the rotation with the contact is repeated, the load continues to be applied to the hydraulic motor, so that the oil leaks from the hydraulic motor and is discharged from the drain port. Will occur. Further, since the hydraulic turning is not performed, the pressure oil is not sent to the hydraulic motor, air is mixed into the hydraulic motor, and the braking force is lost. This phenomenon of air contamination also occurs in a hydraulic swirling crusher that uses an internal drain type motor that does not have a drain port to discharge the leaked oil. The leaked oil travels to the outside through the shaft of the internal drain type motor. It will be discharged. Therefore, even in such a crusher, the phenomenon that air is mixed and the braking force is lost occurs.

  The present invention has been made in view of the various problems as described above, and an object thereof is to keep the amount of oil inside the hydraulic motor constant when the arm is rotated without applying hydraulic pressure to the hydraulic motor. It is an object of the present invention to provide an attachment for a work machine that can maintain the braking force of an arm for a long period of time.

  In order to achieve the above object, in the work machine attachment of the present invention, an arm that opens and closes to grip an object, a hydraulic cylinder that opens and closes the arm, a hydraulic motor that rotates the arm, and a rotation of the arm A brake valve for braking the work machine, the branch pipe connecting the circuit pipe and the drain port between the circuit pipe of the hydraulic cylinder and the drain port of the hydraulic motor And a pressure reducing valve is provided between the branch pipes, and pressure oil is fed from the circuit pipe of the hydraulic cylinder to the hydraulic motor through the branch pipe. As a result, pressure oil can be fed from the hydraulic cylinder side to the hydraulic motor side, so that the hydraulic motor can always be filled with oil. Therefore, when a hydraulic motor is used as a braking mechanism, it is possible to prevent air from being mixed in due to oil leakage, and it is possible to provide an attachment for a working machine that exhibits a constant braking force for a long period of time. In addition, since a pressure reducing valve is provided between the branch pipes, pressure oil is sent from the hydraulic cylinder side to the hydraulic motor through the branch pipe even when the hydraulic pressure of the hydraulic cylinder and the pressure resistance of the drain port of the hydraulic motor are different. It is possible.

  In the work machine attachment according to the present invention, an arm that opens and closes to cut an object, a hydraulic cylinder that opens and closes the arm, a hydraulic motor that rotates the arm, and a brake that brakes the rotation of the arm. A work machine attachment comprising a valve, and a branch pipe connecting the circuit pipe and the drain port is provided between the circuit pipe of the hydraulic cylinder and the drain port of the hydraulic motor, A pressure reducing valve is provided between the branch pipes, and pressure oil is sent from the circuit pipe of the hydraulic cylinder to the hydraulic motor through the branch pipe. Thereby, even if it is a cutter which cut | disconnects a structure, it becomes possible to provide as an attachment for work machines which show | plays the characteristic effect | action of this application mentioned above.

  In the work machine attachment according to the present invention, the branch pipe is provided with an accumulator. Thereby, it is possible to absorb the surge pressure of the pressure reducing valve attached to the branch pipe and the high hydraulic pressure temporarily generated in the drain port. For this reason, it is possible to prevent the drain port having low pressure resistance from being damaged, and it is possible to always send the pressure oil from the branch pipe to the hydraulic motor through the drain port. And since it becomes possible to always fill a hydraulic motor with oil, it becomes possible to provide the attachment for work machines which shows a fixed braking force for a long period of time.

  In the work machine attachment according to the present invention, the arm and the hydraulic cylinder are supported by a frame. The hydraulic motor and the frame are supported by a bracket. As a result, a braking force can be applied to the frame to which the arm is attached by the hydraulic motor, so that the hydraulic motor can be used as a braking mechanism when the arm is rotated by turning. Therefore, in the work machine attachment according to the present invention, it is possible to maintain a state in which a constant braking force is applied for a long period of time even when the rotation by turning is performed for a long time.

  In the work machine attachment according to the present invention, a slewing bearing is provided at a sliding portion between the frame and the bracket. Thereby, when rotating a flame | frame, it becomes possible to reduce the friction which generate | occur | produces in a sliding part with a bracket. Therefore, the rotation of the frame becomes smooth, and it is possible to provide an attachment for a work machine that exhibits a constant braking force for a long time.

  The attachment for a work machine according to the present invention is characterized by being applied to a work machine that feeds pressure oil to the hydraulic cylinder. Thereby, the attachment for work machines of this invention can be applied to a free swirling crusher.

  Furthermore, the attachment for a work machine according to the present invention is applied to a work machine that feeds pressure oil to the hydraulic motor separately from the hydraulic cylinder. Thereby, the attachment for work machines of this invention can be applied to a hydraulic turning crusher.

  Further, the work machine attachment according to the present invention is applied to a work machine that feeds pressure oil to the hydraulic motor together with the hydraulic cylinder. Thereby, the attachment for work machines of this invention can be applied to the hydraulic turning crusher for work machines provided with only the hydraulic circuit on the hydraulic cylinder side.

  Further, in the work machine attachment of the present invention, a drain pipe is connected to the drain port of the hydraulic motor or the branch pipe, and a switching machine that switches connection between the drain pipe and the branch pipe is provided. It is characterized by. Thereby, it becomes possible to connect to the drain port and the oil tank provided in the work machine. Therefore, the work machine attachment according to the present invention can be switched between a form when using hydraulic turning and a form when using free turning by simply switching the switching machine.

  The fluid circuit of the present invention is a fluid circuit that opens and closes and rotates an arm by fluid pressure, the first actuator that opens and closes the arm, the second actuator that rotates the arm, and the first And a brake valve that adjusts the amount of fluid that flows when the external force is applied to the second actuator when an external force is applied to the second actuator. A branch pipe that connects the circuit pipe of the actuator and the drain port of the second actuator is provided, and a pressure reducing valve is provided between the branch pipes. Thereby, the first actuator and the second actuator can be connected, and the fluid can be sent from the first actuator to the second actuator. Therefore, it is possible to always fill the second actuator with fluid, and when the second actuator is used as a braking mechanism, it is possible to prevent air from being mixed due to liquid leakage. In addition, it is possible to provide a fluid circuit that exhibits a constant braking force for a long period of time. Further, since the pressure reducing valve is provided between the branch pipes, even when the flowing water pressures used by the first actuator and the second actuator are different, the liquid is sent from the drain port to the second actuator through the branch pipe. It is possible.

  Embodiments of the present invention will be described below with reference to the drawings. The embodiments described below do not limit the invention according to the scope of claims, and all combinations of features described in the embodiments are not necessarily essential to the establishment of the present invention. Absent.

  FIG. 1 is a plan view of a hydraulic swirl crusher 1 (work machine attachment) according to a first embodiment of the present invention. As shown in FIG. 1, a hydraulic swirl crusher 1 according to this embodiment includes a pair of arms 2, two hydraulic cylinders 3 corresponding to the respective arms 2, a pair of arms 2, and two hydraulic cylinders 3. A support frame 4 and a bracket 5 that rotatably supports the frame 4 are provided. The frame 4 and the bracket 5 are connected via a swivel bearing 12. The pair of arms 2 are arranged in line symmetry, and are supported by the frame 4 by two corresponding frame mounting pins 7 so as to be swingable, and are paired by hydraulic cylinder connection pins 8 respectively. 3 is swingably connected.

  The arm 2 is a substantially triangular member, and a tip crushing claw 2a for crushing concrete is provided at the tip. And the shearing blade 2b is attached with a volt | bolt etc. in the vicinity supported by the frame attachment pin 7 so that rocking | fluctuation is possible, and the intermediate crushing claw 2c is provided in the intermediate part of the front-end crushing claw 2a and the shearing blade 2b. Yes.

  The hydraulic cylinder 3 includes a substantially cylindrical piston rod 3a and a substantially cylindrical cylinder outer cylinder 3b. The piston rod 3a is swingably supported on the bracket 5 side of the frame 4. The opposite side of the cylinder outer cylinder 3 b where the piston rod 3 a is inserted is connected to the arm 2 by a hydraulic cylinder connection pin 8. The hydraulic cylinder connection pin 8 is attached outside the place where the frame attachment pin 7 of the arm 2 is attached.

  The frame 4 includes a support portion 4a having a substantially rectangular plane, and an annular flange 4b that is rotatably attached to the bracket 5. The support portion 4a supports the pair of arms 2 so as to be swingable by frame mounting pins 7 corresponding to the respective arms 2, and supports the piston rods 3a of the two hydraulic cylinders 3 so as to be swingable. . And the support part 4a becomes a mode rotated together with rotation of the annular flange 4b.

  The bracket 5 includes a main body 5a for fixing the hydraulic swirling crusher 1 and an annular flange 5b connected to the frame 4. The main body 5a includes a swing pin 34 (see FIG. 3 described later) and the like. A mounting hole 5c is provided for mounting the. Further, the main body 5a is provided with a cylinder pressure oil supply port 52, a motor pressure oil supply port 53, and a drain pipe connection port 54. Next, the relationship between the bracket 5 and the frame 4 will be described in detail with reference to FIG.

  FIG. 2 is a cross-sectional view of a mounting portion between the bracket 5 and the frame 4 of the present embodiment. As shown in the figure, a bearing outer ring 12a of the slewing bearing 12 is attached to the annular flange 5b, and a bearing inner ring 12b of the slewing bearing 12 is attached to the annular flange 4b by mounting bolts 13, and the bearing outer ring 12a and the bearing inner ring 12b are The ball 12c is rotatably joined. A hydraulic motor 10 is attached to the annular flange 5b, and a pinion 11 is provided on the rotating shaft of the hydraulic motor 10. Further, gear teeth are formed on the inner peripheral surface of the bearing inner ring 12b and mesh with the pinion 11 to form an internal gear.

  When pressure oil is fed into the hydraulic motor 10 via the motor pressure oil supply port 53, the hydraulic motor 10 starts to drive and the pinion 11 rotates. Then, since the driving force is transmitted from the pinion 11 to the gear formed on the bearing inner ring 12b, the annular flange 4b rotates. Thereby, since the frame 4 rotates, the position of the arm 2 can be moved.

  Further, a center swivel joint 9 is provided at the center of the mounting portion between the annular flange 4b and the annular flange 5b, and the pressure oil is fed into the hydraulic cylinder 3 via the center swivel joint 9. Therefore, even if the frame 4 is rotated in the same direction several tens of times, the pressure oil can be fed into the hydraulic cylinder 3. As a result, the hydraulic cylinder 3 expands and contracts, and as a result of this expansion and contraction, the arm 2 can be opened and closed with the frame mounting pin 7 as a swing center as shown in FIG.

  The bracket 5 includes a branch connection pipe 33 (see FIG. 4 described later), a pressure reducing valve 63 (see FIG. 4 described later), and an accumulator 64 (see FIG. 4 described later), which are characteristic parts of the present embodiment. ), A drain connection pipe 65a (see FIG. 4 to be described later), and a stop valve 66 (see FIG. 4 to be described later). A counter balance valve 61 (see FIG. 4 to be described later) is provided in the hydraulic motor 10. And a brake valve 62 (see FIG. 4 described later). Details of these members will be described in detail with reference to FIG. Next, the aspect in which the hydraulic turning crusher 1 of this embodiment crushes the structure will be described with reference to FIG.

  FIG. 3 is a diagram illustrating a state in which the hydraulic swirl crusher 1 according to the present embodiment is attached to a hydraulic excavator 20 (work machine) that is one of the work machines. As shown in FIG. 3, the hydraulic swivel crusher 1 is a crusher that is attached to the hydraulic excavator 20 and crushes the structure 40.

  The hydraulic swirling crusher 1 is attached to the distal end portion of the work arm 30 of the hydraulic excavator 20 via the bracket 5. The hydraulic cylinder side pipes 31a and 31b, the hydraulic motor side pipes 32a and 32b, and the drain pipe 65 of the excavator 20 are provided with two cylinder pressure oil supply ports 52 provided in the bracket 5 and two motor pressure oils. Connected to the supply port 53 and the drain pipe connection port 54, respectively. The cylinder pressure oil supply port 52 and the motor pressure oil supply port 53 are also provided on the opposite side of the work arm 30, but are not shown in the present embodiment.

  In this aspect, the hydraulic swirl crusher 1 performs crushing work by feeding pressure oil from the hydraulic excavator 20. That is, the hydraulic swirling crusher 1 is configured to expand and contract the hydraulic cylinder 3 by opening and closing the hydraulic cylinder 3 by feeding the hydraulic oil from the hydraulic cylinder side pipes 31 a and 31 b to the hydraulic cylinder 3, thereby opening and closing the hydraulic motor pipe 32 a. , 32b is sent to the hydraulic motor 10 to drive the hydraulic motor 10 and rotate the frame 4. The hydraulic swirling crusher 1 swings in the X1 and Y1 directions shown in FIG. 3 with the swing pin 34 as the swing center when the arm cylinder 30a of the work arm 30 expands and contracts.

  By performing the above operations in combination, the hydraulic swirl crusher 1 of the present embodiment crushes the structure 40. For example, when crushing the reinforced concrete flat plate 40a of the structure 40, the arm 2 is sandwiched from the end of the reinforced concrete flat plate 40a, and the arm 2 is closed. Then, the crushing claw 2a comes into contact with the reinforced concrete flat plate 40a, and the stress is applied to the contacted position as it is. Therefore, a crack is generated around this position, and a part of the reinforced concrete flat plate 40a can be crushed.

  And the reinforcing bar 40b remaining after crushing the reinforced concrete flat plate 40a is cut by the shearing blade 2b of the arm 2. However, the reinforcing bar 40b arranged in the direction parallel to the arm 2 becomes the same as the direction of the shearing blade 2b and cannot be cut as it is. Disconnect. By repeating the above-described crushing of the reinforced concrete flat plate 40a and cutting of the reinforcing bar 40b, it is possible to crush the reinforced concrete flat plate 40a. Further, when a structure disposed substantially perpendicular to the ground surface, such as a reinforced concrete column 40c, is crushed, the frame 4 is rotated to bring the arm 2 into a substantially horizontal aspect with respect to the ground surface. All can be crushed like the flat plate 40a.

  In the hydraulic turning crusher 1, when the frame 4 is rotated, the arm 4 is brought into contact with the structure 40 and pressed to rotate the frame 4 in addition to the rotation by driving the hydraulic motor 10. It is also possible to perform so-called contact. In this case, braking is performed by the hydraulic motor 10 when the frame 4 rotates. This braking will be described later in detail with reference to FIG.

  Next, a hydraulic swivel hydraulic circuit 60 of the hydraulic swirl crusher 1 of the present embodiment will be described with reference to FIG.

  FIG. 4 is a schematic diagram of a hydraulic swirl hydraulic circuit 60 between the hydraulic swirl crusher 1 and the excavator 20 according to the present embodiment. As shown in FIG. 4, an oil tank 21 for storing oil, a cylinder side pump 22, a motor side pump 23, and a cylinder side direction switching valve are provided on the hydraulic excavator 20 side of the hydraulic swing type hydraulic circuit 60. 24 and a motor side direction switching valve 25. Further, the cylinder side pump 22 is provided with a cylinder side relief valve 26, and the motor side pump 23 is provided with a motor side relief valve 27.

  The cylinder-side pump 22 is a pump that feeds oil stored in the oil tank 21 to the hydraulic cylinder 3. The cylinder-side pump 22 is provided with a cylinder-side relief valve 26, which protects the circuit piping and the like on the hydraulic cylinder 3 side from a suddenly generated hydraulic pressure.

  The motor-side pump 23 is a pump that feeds oil stored in the oil tank 21 to the hydraulic motor 10. The motor-side pump 23 is provided with a motor-side relief valve 27, which protects the circuit piping and the like on the hydraulic motor 10 side from a hydraulic pressure that is abruptly generated.

  The cylinder side direction switching valve 24 is a valve for switching the supply of pressure oil from the cylinder side pump 22 to the hydraulic cylinder 3. The cylinder side direction switching valve 24 includes three flow paths, ie, a parallel flow path 24a, a neutral flow path 24b, and a cross flow path 24c. By switching the flow paths, the feeding of pressure oil is switched. Yes.

  The motor side direction switching valve 25 is a valve for switching the feeding of pressure oil from the motor side pump 23 to the hydraulic motor 10. The cylinder side direction switching valve 25 includes three flow paths, a parallel flow path 25a, a neutral flow path 25b, and a cross flow path 25c, and switching the flow of pressure oil is performed by switching the flow paths. ing.

  As described above, the hydraulic cylinder 3, the center swivel joint 9, and the hydraulic motor 10 are provided on the hydraulic rotary crusher 1 side of the hydraulic rotary hydraulic circuit 60. The hydraulic motor 10 is provided with a drain port 14, and the circuit piping on the hydraulic motor 10 side is provided with a counter balance valve 61 and a brake valve 62. And the branch connection piping 33 (branch piping) which is the characteristic part of this embodiment is provided in the hydraulic rotation type crusher 1 side of the hydraulic rotation type hydraulic circuit 60.

  The counter balance valve 61 is a valve for preventing the hydraulic motor 10 from rotating by closing the circuit on the hydraulic motor 10 side to stop the flow of oil when the arm 2 is not rotated. The counter balance valve 61 includes three flow paths, a forward flow path 61a, a closed flow path 61b, and a reverse flow path 61c. The flow path is in accordance with the rotation direction of the hydraulic motor 10 and the stop mode. It is designed to switch.

  The brake valve 62 is formed by two relief valves 62 a, and the two relief valves 62 a are provided in both forward and reverse directions in parallel to the hydraulic motor 10. The brake valve 62 can provide resistance to the oil in the circuit of the hydraulic motor 10, and can apply a braking force to the rotation of the frame 4 via the hydraulic motor 10.

  The drain port 14 is a hole provided in the hydraulic motor 10 and allows oil leaked from the hydraulic motor 10 to escape to the outside.

  The branch connection pipe 33, which is a characteristic part of the present embodiment, is a pipe for connecting the hydraulic cylinder side pipe 31 a and the drain port 14 of the hydraulic motor 10. The branch connection pipe 33 is provided with a pressure reducing valve 63, an accumulator 64, a stop valve 66, and a drain connection pipe 65a. In the hydraulic swivel crusher 1, the hydraulic oil can be automatically fed from the hydraulic cylinder side pipe 31 a side to the hydraulic motor 10 during the crushing operation by the branch connection pipe 33. .

  The pressure reducing valve 63 is a valve provided between the branch connection pipes 33 for reducing the pressure oil sent from the hydraulic cylinder side pipe 31 a side to the drain port 14 side of the hydraulic motor 10. Even if the pressure oil fed from the cylinder-side pump 22 is higher than the pressure resistance of the drain port 14 by the pressure reducing valve 63, the pressure oil can be reduced, so that the hydraulic motor 10 is connected via the drain port 14 with low pressure resistance. It is possible to feed pressure oil into

  The accumulator 64 is a member for absorbing the surge pressure of the pressure reducing valve 63 provided between the pressure reducing valve 63 on the branch connection pipe 33 and the drain port 14 and the high pressure temporarily generated in the drain port 14. . In the pressure reducing valve 63, a surge pressure may be generated, and this surge pressure may reach the drain port 14 through the branch connection pipe 33 as indicated by an arrow a in FIG. In that case, since the drain port 14 has low pressure resistance, it may be damaged. Conversely, when an impact load is generated in the hydraulic motor 10 while the hydraulic motor 10 is filled with oil, a high pressure may be temporarily generated in the drain port 14. In this case, as shown by the arrow b in FIG. 4, the generated pressure may reach the pressure reducing valve 63 through the branch connection pipe 33. In addition to the drain port 14 having low pressure resistance, the pressure reducing valve 63 Otherwise, the branch connection pipe 33 and the hydraulic motor 10 itself may be damaged.

  The accumulator 64 is provided to absorb the above-described surge pressure or a temporarily generated high pressure. Since these accumulators 64 absorb these pressures, it is possible to reduce the damage rate of the hydraulic motor 10, the drain port 14 provided in the hydraulic motor 10, the pressure reducing valve 63, the branch connection pipe 33, and the like. Become. This makes it possible to extend the life of each member described above.

  The drain connection pipe 65a is a circuit pipe branched from a pipe between the pressure reducing valve 63 and the accumulator 64 on the branch connection pipe 33, and is connected to the drain connection pipe 65 on the excavator 20 side. Then, the oil leaked from the hydraulic motor 10 can be returned to the oil tank 21 by the drain connection pipe 65a.

  The stop valve 66 is a valve for stopping the pressure oil provided in the vicinity of the pressure reducing valve on the branch connection pipe 33. The stop valve 66 is switched in accordance with the usage mode of the hydraulic motor 10. By switching the stop valve 66, it is possible to switch between a hydraulic swing type usage mode and a free swing type usage mode. It has become.

  Next, the operation of the hydraulic turning hydraulic circuit 60 of this embodiment will be described. When crushing the structure 40 with the arm 2, the user switches the cylinder side direction switching valve 24 to the parallel flow path 24a. As a result, the pressure oil is sent from the cylinder-side pump 22 to the hydraulic cylinder-side pipe 31b through the parallel flow path 24a, and is sent to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the X2 direction by the pressure oil sent, the piston rod 3a moves in the X2 direction, and the hydraulic cylinder 3 extends. Therefore, as shown in FIG. 1, the pair of arms 2 swings in the closing direction, and the structure 40 is sandwiched and crushed.

  Next, when the arm 2 is opened, the user switches the cylinder side direction switching valve 24 to the cross flow path 24c. As a result, the pressure oil is sent from the cylinder side pump 22 to the hydraulic cylinder side pipe 31 a via the cross passage 24 c and then to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the Y2 direction by the pressure oil sent in, the piston rod 3a moves in the Y2 direction, and the hydraulic cylinder 3 contracts. Therefore, as shown in FIG. 1, the pair of arms 2 swings in the opening direction.

  Further, when the user switches the cylinder side direction switching valve 24 to the neutral flow path 24b, the pressure oil is not sent to the hydraulic cylinder pipes 31a and 31b. Therefore, the expansion / contraction of the hydraulic cylinder 3 is stopped, and the opening / closing of the arm 2 is stopped. And since the oil inside the hydraulic cylinder 3 does not move, the stop mode of the arm 2 is maintained.

  Next, when rotating the frame 4, first, the motor side direction switching valve 25 is switched to the parallel flow path 25a. Then, pressure oil is sent from the motor side pump 23 to the hydraulic motor side pipe 32b via the parallel flow path 25a, and the pilot of the counter balance valve 61 detects the pressure of the hydraulic motor side pipe 32b. Then, the counter balance valve 61 is switched to the normal flow path 61a, pressure oil is sent to the hydraulic motor 10 through the positive flow path 61a, the hydraulic motor 10 rotates in one direction, and the frame 4 rotates. Let

  When rotating the frame 4 in the reverse direction, first, the motor side direction switching valve 25 is switched to the cross flow path 25c. Then, pressure oil is sent from the motor-side pump 23 to the hydraulic motor-side pipe 32a through the cross passage 25c, and the pilot of the counter balance valve 61 detects the pressure of the hydraulic motor-side pipe 32a. Then, the counter balance valve 61 switches to the reverse flow path 61c, pressure oil is fed into the hydraulic motor 10 through the reverse flow path 61c, the hydraulic motor 10 rotates in the reverse direction, and the frame 4 rotates in the reverse direction. Move.

  When the hydraulic motor 10 is driven and the frame 4 is rotated as described above, in the branch connection pipe 33 which is a characteristic part of the present embodiment, the stop valve 66 is closed and the drain connection pipe 65a and the drain pipe are closed. 65 is connected. As a result, the drain port 14 and the oil tank 21 are connected via the branch connection pipe 33, the drain connection pipe 65a, and the drain pipe 65, and play the same role as the drain pipe of a normal hydraulic swirl crusher. It is possible.

  As described above, in the hydraulic turning crusher 1, the arm 2 can be opened / closed and rotated by the two pumps of the cylinder side pump 22 and the motor side pump 23. Next, the contact operation in the hydraulic turning crusher 1 of the present embodiment will be described in detail with reference to FIG.

  FIG. 5 is a first diagram for illustrating braking by hydraulic pressure of the hydraulic swirling crusher 1 of the present embodiment. As shown in FIG. 5, in the hydraulic swirl crusher 1 of this embodiment, when the frame 4 is applied, it is necessary to apply a braking force by the hydraulic motor 10 as described above. Therefore, the motor side direction switching valve 25 is switched to the neutral flow path 25b. Then, since pressure oil is not sent to the hydraulic motor side pipes 32a and 32b, the pilot of the counter balance valve 61 does not detect the pressure of the hydraulic motor side pipes 32a and 32b. Therefore, the counter balance valve 61 is switched to the closed flow path 61b. Thereby, the movement of the oil in the circuit piping on the hydraulic motor 10 side is stopped.

  Therefore, the rotation of the hydraulic motor 10 is stopped, and the rotation of the frame 4 at that time is stopped. However, if the rotation of the hydraulic motor 10 is completely stopped, the hydraulic motor 10 or the pinion 11 and the bearing inner ring 12b may be damaged when a load is applied to the frame 4 via the arm 2 or the like. There is. For this reason, the hydraulic motor 10 is provided with a brake valve 62. By adjusting the pilot pressure on the hydraulic motor 10 by the two relief valves 62a of the brake valve 62, a load exceeding a certain level is applied to the hydraulic motor 10. Only in this case, the oil in the hydraulic motor 10 moves. And since the fixed braking force with respect to rotation is given to the flame | frame 4 with the oil inside the hydraulic motor 10, the hydraulic motor 10, the pinion 11, and the bearing inner ring | wheel 12b are prevented from being damaged.

  However, the counter balance valve 61 is switched to the closing circuit 61b, the drain port 14 and the oil tank 21 are connected, and the braking force is applied to the frame 4 by the hydraulic motor 10, so that the arm 2 is turned for a long time. When the rotation is performed, a load is continuously applied to the hydraulic motor 10. Therefore, the oil leaks from the hydraulic motor 10 and is sent to the oil tank 21, or the oil leaks from the shaft of the hydraulic motor 10 and air is mixed into the hydraulic motor 10, resulting in a loss of braking force. It was.

  In order to eliminate the state where the braking force is lost, it is necessary to send the pressure oil from the motor-side pump 23 to the hydraulic motor 10 each time. For this reason, the frame 4 cannot be continuously rotated by turning, and it is difficult to improve workability.

  Therefore, in the hydraulic swirl crusher 1 of the present embodiment, the branch connection pipe 33 is provided to automatically feed the pressure oil during the crushing operation, and the oil leakage of the hydraulic motor 10 and the air It is possible to prevent mixing. Next, the mode at the time of using this branch connection piping 33 is demonstrated.

  First, the stop valve 66 of the branch connection pipe 33 is opened, the drain pipe connection port 54 is sealed with a plug attached, and the hydraulic cylinder side pipe 31 a and the drain port 14 are connected. Thereby, since oil does not flow to the drain pipe 65, the connection between the drain port 14 and the oil tank 21 is disconnected, and oil leaking from the hydraulic motor 10 is not sent to the oil tank 21.

  In this embodiment, the drain pipe connection port 54 is sealed by attaching a plug. However, when the drain pipe 65 is provided with a stop valve, the drain pipe can be simply switched by switching the stop valve. The same effect as sealing the connection port 54 can be achieved.

  When the piston rod 3a of the hydraulic cylinder 3 is moved in the Y2 direction in the hydraulic swing hydraulic circuit 60 having such an aspect, as shown in FIG. 5, the pressure oil is passed from the cylinder side pump 22 via the cross flow path 24c. Then, it is fed into the hydraulic cylinder side piping 31a, and is then fed into the hydraulic cylinder 3 to move the piston rod 3a in the Y2 direction. The oil filled in the hydraulic cylinder 3 until then is pushed by the pressure oil sent from the hydraulic cylinder side pipe 31a and returned to the oil tank 21 through the hydraulic cylinder side pipe 31b and the cross passage 24c. Come.

  At the same time, the pressure oil decompressed so as not to damage the hydraulic motor 10 and the drain port 14 provided in the hydraulic motor 10 by the pressure reducing valve 63 from the branch connection pipe 33 provided in the hydraulic cylinder side pipe 31a is drain port. 14 to the hydraulic motor 10. That is, when oil leaks from the hydraulic motor 10, the pressure oil is automatically supplied from the branch connection pipe 33. As a result, even when oil leaks from the shaft of the hydraulic motor 10 or the like, it is possible to quickly supply pressure oil again, and the hydraulic motor 10 can always be filled with oil. Therefore, the braking force of the hydraulic motor 10 is not lost when air is mixed in, and the crushing operation by continuous contact can be performed.

  In the hydraulic swirl crusher 1 of the present embodiment described above, it is possible to automatically feed pressure oil to the hydraulic motor 10. As a result, even if the operation of rotating the arm 2 by rotating the arm 2 to repeat the position movement is repeated, the hydraulic motor 10 can be always filled with oil. Power is not lost. Furthermore, it is possible to extend the life of each member by the accumulator 64, and the number of member replacements is also reduced. Thereby, in the hydraulic turning crusher 1, the braking force of the arm 2 can be kept constant for a long period of time. Note that the branch connection pipe 33 of this embodiment can also be used when the frame 4 is rotated by sending pressure oil from the motor-side pump 23 to the hydraulic motor 10.

  Next, a second embodiment of the present invention will be described. In addition, in 2nd Embodiment, about the structure which overlaps with 1st Embodiment mentioned above, the same number is attached | subjected and description is abbreviate | omitted and it differs from 1st Embodiment of the attachment for work machines of this embodiment. Only the part relating to the free swirling crusher 101 which is a characteristic part will be described.

  FIG. 6 is a view showing a state in which a free swirl crusher 101 (work machine attachment) according to a second embodiment of the present invention is attached to a hydraulic excavator 120 which is one of the work machines. As shown in FIG. 6, the free swivel crusher 101 is a crusher that is attached to a working machine such as a hydraulic excavator 120 to crush the structure 40. Since the free swirl crusher 101 is the same as the hydraulic swirl crusher 1 of the first embodiment, reference is also made to FIGS.

  As shown in FIGS. 1 to 3 and 6, the free swirling crusher 101 is attached to the distal end portion of the working arm 30 of the excavator 120 via the bracket 5. Then, hydraulic cylinder side pipes 131 a and 131 b (see FIG. 7 described later) of the hydraulic excavator 120 are connected to two cylinder pressure oil supply ports 52 provided in the bracket 5. Further, since the excavator 120 does not include the hydraulic motor side piping and the drain piping, the two motor pressure oil supply ports 53 and the drain piping connection port 54 of the free swirling crusher 101 are attached with plugs. Is sealed. The cylinder pressure oil supply port 52 and the motor pressure oil supply port 53 are also provided on the opposite side of the work arm 30, but are not shown in the present embodiment.

  In this aspect, the free swirling crusher 101 performs crushing work by sending pressure oil from the excavator 120. In other words, the free swirl crusher 101 opens and closes the arm 2 by expanding and contracting the hydraulic cylinder 3 by sending the pressure oil from the hydraulic cylinder side pipes 131a and 131b to the hydraulic cylinder 3. As in the hydraulic swirl crusher 1, the free swirl crusher 101 has the rocking pin 34 as the rocking center as the arm cylinder 30a of the work arm 30 expands and contracts, and X3 and Y3 shown in FIG. Swing in the direction.

  Further, in the free swirling crusher 101, since there is no hydraulic motor side piping, no hydraulic oil is supplied to the hydraulic motor 10, and the hydraulic motor 10 is not driven, so the frame 4 cannot be rotated by hydraulic pressure. Therefore, in the free swivel crusher 101, the arm 4 is brought into contact with the structure 40 and pressed to rotate the frame 4, so that the frame 4 is rotated. In this case, the hydraulic motor 10 is filled with oil in a state in which the oil does not flow, and the hydraulic motor 10 brakes the rotation of the frame 4. This braking will be described in detail later with reference to FIG.

  By performing the above operations in combination, the free swirling crusher 101 of the present embodiment can crush the structure 40. Note that the movement of the free swirl crusher 101 when crushing is substantially the same as that of the hydraulic swirl crusher 1, and a description thereof will be omitted here. Next, the free swivel hydraulic circuit 160 of the free swirl crusher 101 of this embodiment will be described with reference to FIG.

  FIG. 7 is a schematic diagram of a free swivel hydraulic circuit 160 between the free swirl crusher 101 and the excavator 120 according to the present embodiment. As shown in FIG. 7, in the free swivel hydraulic circuit 160, the motor-side pump 23 and the motor-side directional switching valve provided in the hydraulic swivel hydraulic circuit 60 of the first embodiment are disposed on the hydraulic excavator 120 side. 25 and the motor side relief valve 27 are not provided. Regarding the other members, the same members as those of the hydraulic swing hydraulic circuit 60 of the first embodiment are provided in the free swing hydraulic circuit 160, and therefore description of each member is omitted.

  Next, the operation of the hydraulic turning hydraulic circuit 160 of this embodiment will be described. When crushing the structure 40 with the arm 2, the user switches the cylinder side direction switching valve 24 to the parallel flow path 24a. As a result, the pressure oil is sent from the cylinder-side pump 22 to the hydraulic cylinder-side pipe 131 b through the parallel flow path 24 a and then to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the X4 direction by the pressure oil sent, the piston rod 3a moves in the X4 direction, and the hydraulic cylinder 3 extends. Therefore, as shown in FIG. 6, the pair of arms 2 swings in the closing direction, and the structure 40 is sandwiched and crushed.

  Next, when the arm 2 is opened, the user switches the cylinder side direction switching valve 24 to the cross flow path 24c. As a result, the pressure oil is sent from the cylinder side pump 22 to the hydraulic cylinder side pipe 131 a via the cross passage 24 c and then to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the Y4 direction by the pressure oil sent in, the piston rod 3a moves in the Y4 direction, and the hydraulic cylinder 3 contracts. Therefore, as shown in FIG. 6, the pair of arms 2 swings in the opening direction.

  Further, when the cylinder side direction switching valve 24 is switched to the neutral flow path 24b, the pressure oil is not sent to the hydraulic cylinder side pipes 131a and 131b. Therefore, the expansion and contraction of the hydraulic cylinder 3 is stopped, and the opening and closing of the arm 2 at that time is stopped. And since the oil inside the hydraulic cylinder 3 does not move, the stop mode of the arm 2 is maintained.

  As described above, in the free swirl crusher 101, only the opening and closing of the arm 2 is performed by the cylinder-side pump 22. Next, with reference to FIG. 8, a detailed description will be given of braking when performing contact with the free swirling crusher 101 of the present embodiment.

  FIG. 8 is a view for explaining braking by hydraulic pressure of the free swirling crusher 101 of the present embodiment. As shown in FIG. 8, in the free swirling crusher 101 of this embodiment, when the frame 4 is turned around, it is necessary to apply a braking force by the hydraulic motor 10 as in the first embodiment. Therefore, a plug is attached to the two pressure oil supply ports 53 for the motor, the circuit piping on the hydraulic motor 10 side is closed, and the oil is filled inside the hydraulic motor 10, so that the circuit piping on the hydraulic motor 10 side is filled with oil. Stop oil movement.

  As a result, the rotation of the hydraulic motor 10 is stopped, and the rotation of the frame 4 at that time is stopped. However, if the rotation of the hydraulic motor 10 is completely stopped, the hydraulic motor 10 or the pinion 11 and the bearing inner ring 12b may be damaged when a load is applied to the frame 4 via the arm 2 or the like. There is. For this reason, the hydraulic motor 10 is provided with a brake valve 62. By adjusting the pilot pressure on the hydraulic motor 10 by the two relief valves 62a of the brake valve 62, a load exceeding a certain level is applied to the hydraulic motor 10. Only in this case, the oil in the hydraulic motor 10 moves. And since the fixed braking force with respect to rotation is given to the flame | frame 4 with the oil inside the hydraulic motor 10, the hydraulic motor 10, the pinion 11, and the bearing inner ring | wheel 12b are prevented from being damaged.

  However, if the arm 2 is turned by applying the braking force to the frame 4 by the hydraulic motor 10 for a long time, a load is continuously applied to the hydraulic motor 10. Therefore, the oil leaks from the hydraulic motor 10 and the oil leaks from the shaft of the hydraulic motor 10, causing air to enter the hydraulic motor 10, resulting in a loss of braking force. In order to eliminate the state in which the braking force is lost, it is necessary to add oil to the hydraulic motor 10 each time, and the frame 4 cannot be rotated by continuously applying the oil. . For this reason, workability cannot be improved only by using the hydraulic motor 10 as a braking device.

  Therefore, in the free swirl crusher 101 of the present embodiment, the branch connection pipe 133 is provided, and oil is automatically fed during the crushing operation, so that the oil leaks out from the hydraulic motor 10 and air is mixed. Can be prevented. Next, the mode at the time of using this branch connection piping 133 is demonstrated.

  First, in the free swing hydraulic circuit 160, the hydraulic cylinder side pipe 131 a and the drain port 14 are connected by the branch connection pipe 133. At this time, the stop valve 66 of the branch connection pipe 133 is opened, and the drain pipe connection port 54 is sealed by attaching a plug.

  In this manner, when the piston rod 3a of the hydraulic cylinder 3 is moved in the Y4 direction, the pressure oil is transferred from the cylinder-side pump 22 to the hydraulic cylinder-side pipe 131a via the cross passage 24c as described above. Then, it is fed into the hydraulic cylinder 3 to move the piston rod 3a in the Y4 direction. The oil that has been filled in the hydraulic cylinder 3 until then is pushed by the pressure oil sent from the hydraulic cylinder side pipe 131a and returned to the oil tank 21 via the hydraulic cylinder side pipe 131b and the cross passage 24c. Come.

  At the same time, the pressure oil decompressed so as not to damage the hydraulic motor 10 and the drain port 14 provided in the hydraulic motor 10 by the pressure reducing valve 63 from the branch connection pipe 133 provided in the hydraulic cylinder side pipe 131a is drain port. 14 to the hydraulic motor 10. That is, when oil leaks from the hydraulic motor 10, the pressure oil is automatically supplied from the branch connection pipe 133. As a result, even when oil leaks from the shaft of the hydraulic motor 10 or the like, it is possible to quickly supply pressure oil again, and the hydraulic motor 10 can always be filled with oil. Therefore, the braking force of the hydraulic motor 10 is not lost when air is mixed in, and the crushing operation by continuous contact can be performed.

  In the above-described free swirling crusher 101 of the present embodiment, it is possible to automatically feed pressure oil to the hydraulic motor 10. As a result, even if the operation of rotating the arm 2 by rotating the arm 2 to repeat the position movement is repeated, the hydraulic motor 10 can be always filled with oil. Power is not lost. Furthermore, it is possible to extend the life of each member by the accumulator 64, and the number of member replacements is also reduced. Thereby, in the free swivel type crusher 101, the braking force of the arm 2 can be kept constant for a long period of time.

  Next, a third embodiment of the present invention will be described. In addition, in 3rd Embodiment, the same number is attached | subjected about the structure which overlaps with 1st, 2nd embodiment mentioned above, description is abbreviate | omitted, and it differs from 1st, 2nd embodiment of the attachment for work machines. Only the part related to the hydraulic swirl crusher 201 which is a characteristic part of the present embodiment will be described.

  FIG. 9 is a diagram showing a state in which a hydraulic swirl crusher 201 (work machine attachment) according to the third embodiment of the present invention is attached to a hydraulic excavator 220 which is one of the work machines. As shown in FIG. 9, the hydraulic turning crusher 201 is a crusher that is attached to a working machine such as a hydraulic excavator 220 and crushes the structure 40. The hydraulic swirl crusher 201 includes a sequence valve 29 (see FIG. 10 described later) and a throttle valve 15 (described later) in the circuit piping on the hydraulic motor 10 side of the hydraulic swirl crusher 1 of the first embodiment. 10) and a check valve 17 (see FIG. 10 described later) are added, and the motor pressure oil supply port 53 and the drain piping connection port 54 are not provided. Since the other members are substantially the same as those of the hydraulic swirl crusher 1 of the first embodiment, reference is also made to FIGS. 1 to 3 below. The operation of the sequence valve 29, the throttle valve 15, and the check valve 17 will be described in detail later with reference to FIG.

  As shown in FIGS. 1 to 3 and 9, the hydraulic swirl crusher 201 is attached to the distal end portion of the working arm 30 of the hydraulic excavator 220 via the bracket 5. Then, hydraulic cylinder side pipes 231 a and 231 b (see FIG. 10 described later) of the hydraulic excavator 220 are connected to two cylinder pressure oil supply ports 52 provided in the bracket 5. And hydraulic motor side branch supply pipes 232a and 232b (see FIG. 10 described later) are connected to the hydraulic cylinder side pipes 231a and 231b, respectively. The cylinder-side pressure oil supply port 52 is also provided on the opposite side of the work arm 30, but is not shown in the present embodiment.

  In this manner, the hydraulic swirl crusher 201 performs crushing work by sending pressure oil from the excavator 220. That is, like the hydraulic swirl crusher 1, the hydraulic swirl crusher 201 extends and contracts the hydraulic cylinder 3 when the hydraulic oil is fed from the hydraulic cylinder side pipes 231a and 231b to the hydraulic cylinder 3, and the arm 2 Is opened and closed, and pressure oil is sent from the hydraulic motor side branch supply pipe 232a to the hydraulic motor 10, thereby driving the hydraulic motor 10 to rotate the frame 4. Then, the hydraulic turning crusher 201 swings around X5 and Y5 shown in FIG. 9 with the swing pin 34 as the swing center, as the arm cylinder 30a of the work arm 30 expands and contracts.

  By performing the operations described above in combination, the hydraulic swirl crusher 201 of the present embodiment can crush the structure 40. The movement of the hydraulic swirl crusher 201 when crushing is substantially the same as that of the hydraulic swirl crusher 1 of the first embodiment, and thus the description thereof is omitted here.

  Further, in the hydraulic turning crusher 201, when the frame 4 is rotated, the arm 2 is brought into contact with the structure 40 and pressed to rotate the frame 4 in addition to the rotation by driving the hydraulic motor 10. It is also possible to perform so-called contact. In this case, braking of the frame 4 is performed by the hydraulic motor 10. This braking will be described later in detail with reference to FIG. Next, a hydraulic swivel hydraulic circuit 260 of the hydraulic swirl crusher 201 of this embodiment will be described with reference to FIG.

  FIG. 10 is a schematic diagram of a hydraulic swivel hydraulic circuit 260 between the hydraulic swirl crusher 201 and the excavator 220 according to the present embodiment. As shown in FIG. 10, in the hydraulic swing hydraulic circuit 260, the hydraulic excavator 220 is provided with the motor side pump 23, the motor side direction switching valve 25, and the free swing hydraulic circuit 160 of the second embodiment. The motor side relief valve 27 is not provided. In addition to the members provided in the hydraulic swing hydraulic circuit 60 of the first embodiment, a sequence valve 29, a throttle valve 15 and a check valve 17 are provided on the hydraulic swing crusher 201 side. The stop valve 66 is not provided in the branch connection pipe 233.

  The sequence valve 29 is a valve that controls the flow of pressure oil in the hydraulic swing hydraulic circuit 260. When the oil pressure applied to the sequence valve 29 exceeds a certain value, the pressure oil flows through the sequence valve 29. ing. The sequence valve 29 is provided on the hydraulic motor side branch supply pipe 232a. In the hydraulic swing hydraulic circuit 260, the hydraulic motor 10 starts driving after the piston rod 3a of the hydraulic cylinder 3 moves in the Y6 direction. It is an aspect.

  The throttle valve 15 is a valve for adjusting the flow rate of the pressure oil provided on the hydraulic motor side branch supply pipe 232a. As a result, the amount of pressure oil flowing through the hydraulic motor 10 is adjusted to adjust the driving speed of the hydraulic motor 10.

  The check valve 17 is a valve provided on the hydraulic motor side branch supply pipe 232b for preventing the flow of pressure oil from the hydraulic cylinder side pipe 231b to the hydraulic motor side branch supply pipe 232b. As a result, when the piston rod 3a of the hydraulic cylinder 3 moves in the X6 direction, the pressure oil does not flow into the hydraulic motor side branch supply pipe 232b and the hydraulic motor 10 is not reversed.

  Next, the operation of the hydraulic turning hydraulic circuit 260 of this embodiment will be described. When crushing the structure 40 with the arm 2, the user switches the cylinder side direction switching valve 24 to the parallel flow path 24a. As a result, the pressure oil is sent from the cylinder side pump 22 to the hydraulic cylinder side pipe 231b through the parallel flow path 24a, and is sent to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the X6 direction by the pressure oil sent, the piston rod 3a moves in the X6 direction, and the hydraulic cylinder 3 extends. Therefore, as shown in FIG. 9, the pair of arms 2 swings in the closing direction, and the structure 40 is sandwiched and crushed.

  Next, when the arm 2 is opened, the user switches the cylinder side direction switching valve 24 to the cross flow path 24c. As a result, the pressure oil is sent from the cylinder side pump 22 to the hydraulic cylinder side pipe 231 a via the cross flow path 24 c and then to the hydraulic cylinder 3. Then, since the piston rod 3a is pushed in the Y6 direction by the pressure oil sent, the piston rod 3a moves in the Y6 direction, and the hydraulic cylinder 3 contracts. Therefore, as shown in FIG. 9, the pair of arms 2 swings in the opening direction.

  Further, when the user switches the cylinder side direction switching valve 24 to the neutral flow path 24b, the pressure oil is not sent to the hydraulic cylinder pipes 231a and 231b. Therefore, the expansion / contraction of the hydraulic cylinder 3 is stopped, and the opening / closing of the arm 2 is stopped. And since the oil inside the hydraulic cylinder 3 does not move, the stop mode of the arm 2 is maintained.

  Next, when the frame 4 is rotated, first, the cylinder side direction switching valve 24 is switched to the cross flow path 24c. Then, as described above, the pressure oil is fed into the hydraulic cylinder 3, the piston rod 3a moves in the Y6 direction, and the hydraulic cylinder 3 contracts. Thereafter, when the movement of the piston rod 3a is completed and the hydraulic cylinder 3 is contracted to the limit, the hydraulic pressure is applied to the sequence valve 29, and the pressure oil is sent to the hydraulic motor 10 side through the sequence valve 29. When the pilot of the counter balance valve 61 detects the pressure in the hydraulic motor side branch supply pipe 232a, the counter balance valve 61 is switched to the positive flow path 61a, and the pressure is supplied to the hydraulic motor 10 through the positive flow path 61a. Oil is sent in. As a result, the hydraulic motor 10 rotates in one direction to rotate the frame 4.

  Further, when the pilot of the counter balance valve 61 stops detecting the pressure of the hydraulic motor side branch supply pipe 232a, the counter balance valve 61 is switched to the closed flow path 61b, and the supply of the pressure oil to the hydraulic motor 10 is stopped. Therefore, the hydraulic motor 10 stops rotating.

  In the hydraulic swirl crusher 201 of the present embodiment, the check valve 17 is provided in the hydraulic motor side branch supply pipe 232b so that the hydraulic motor 10 does not reverse. The check valve 17 allows the flow of pressure oil. Therefore, the hydraulic motor 10 is driven only in one direction.

  As described above, in the hydraulic swirl crusher 201 of this embodiment, the opening and closing of the arm 2 and the rotation of the frame 4 can be performed only by the cylinder-side pump 22. Next, with reference to FIG. 11, a detailed description will be given of braking at the time of performing turning in the hydraulic swirl crusher 201 of the present embodiment.

  FIG. 11 is a diagram for explaining braking by hydraulic pressure of the hydraulic turning crusher 201 of the present embodiment. As shown in FIG. 11, in the hydraulic turning crusher 201 of the present embodiment, it is necessary to apply a braking force by the hydraulic motor 10 when the frame 4 is applied. Therefore, the movement of oil in the hydraulic motor 10 is stopped.

  As a result, the rotation of the hydraulic motor 10 is stopped, and the rotation of the frame 4 at that time is stopped. However, if the rotation of the hydraulic motor 10 is completely stopped, the hydraulic motor 10 or the pinion 11 and the bearing inner ring 12b may be damaged when a load is applied to the frame 4 via the arm 2 or the like. There is. For this reason, the hydraulic motor 10 is provided with a brake valve 62. By adjusting the pilot pressure on the hydraulic motor 10 by the two relief valves 62a of the brake valve 62, a load exceeding a certain level is applied to the hydraulic motor 10. Only in this case, the oil in the hydraulic motor 10 moves. And since the fixed braking force with respect to rotation is given to the flame | frame 4 with the oil inside the hydraulic motor 10, the hydraulic motor 10, the pinion 11, and the bearing inner ring | wheel 12b are prevented from being damaged.

  However, if the arm 2 is turned by applying the braking force to the frame 4 by the hydraulic motor 10 for a long time, a load is continuously applied to the hydraulic motor 10. Therefore, the oil leaks from the hydraulic motor 10 and the oil leaks from the shaft of the hydraulic motor 10, causing air to enter the hydraulic motor 10, resulting in a loss of braking force. In order to eliminate the state in which the braking force is lost, it is necessary to add oil to the hydraulic motor 10 each time, and the frame 4 cannot be rotated by continuously applying the oil. . For this reason, there is a case in which the braking performance is remarkably deteriorated when continuously applied.

  Therefore, in the hydraulic swirl crusher 201 of the present embodiment, the branch connection pipe 233 is provided to automatically feed the pressure oil during the crushing operation, and the oil leakage of the hydraulic motor 10 and the air It is possible to prevent mixing. Next, the mode at the time of using this branch connection piping 233 is demonstrated.

  In the hydraulic swing type hydraulic circuit 260, when the piston rod 3a of the hydraulic cylinder 3 is moved in the Y6 direction, as shown in FIG. 11, the pressure oil is supplied from the cylinder side pump 22 via the cross passage 24c to the hydraulic cylinder side. It is fed into the pipe 231a and then into the hydraulic cylinder 3 to move the piston rod 3a in the Y6 direction. The oil that has been filled in the hydraulic cylinder 3 until then is pushed by the pressure oil sent from the hydraulic cylinder side pipe 231a and returned to the oil tank 21 via the hydraulic cylinder side pipe 231b and the cross passage 24c. Come.

  At the same time, from the branch connection pipe 233 provided in the hydraulic cylinder side pipe 231a, the pressure oil reduced in pressure so as not to damage the hydraulic motor 10 and the drain port 14 provided in the hydraulic motor 10 by the pressure reducing valve 63 is supplied to the drain port. 14 to the hydraulic motor 10. That is, when oil leaks from the hydraulic motor 10, the pressure oil is automatically supplied from the branch connection pipe 233. As a result, even when oil leaks from the shaft of the hydraulic motor 10 or the like, it is possible to quickly supply pressure oil again, and the hydraulic motor 10 can always be filled with oil. Therefore, the braking force of the hydraulic motor 10 is not lost when air is mixed in, and the crushing operation by continuous contact can be performed.

  In the hydraulic swirl crusher 201 of the present embodiment described above, the hydraulic oil can be automatically fed to the hydraulic motor 10. As a result, even if the operation of rotating the arm 2 by rotating the arm 2 to repeat the position movement is repeated, the hydraulic motor 10 can be always filled with oil. Power is not lost. Furthermore, it is possible to extend the life of each member by the accumulator 64, and the number of member replacements is also reduced. Thereby, in the hydraulic turning crusher 201, the braking force of the arm 2 can be kept constant for a long period of time.

  In addition, although branch connection piping 33, 133, 233 of this embodiment is connected with hydraulic cylinder side piping 31a, 131a, 231a, this is not an essential structure of this invention. For example, the branch connection pipes 33, 133, 233 may be connected to the hydraulic cylinder side pipes 31b, 131b, 231b. Moreover, although the accumulator 64 is provided in the branch connection piping 33, 133, 233 of this embodiment, this accumulator 64 is not an essential structure of this invention. However, from the viewpoint of protection in the hydraulic circuit, it is preferable to implement the present invention that the accumulator 64 is provided.

  Moreover, in the hydraulic swirl crushers 1 and 201 and the free swivel crusher 101 of the present embodiment, the number of the hydraulic cylinders 3 for opening and closing the arm 2 is two, but it may be one or three or more. It doesn't matter.

  Moreover, although the attachment for work machines of this embodiment was made into the hydraulic swirl crusher 1,201 and the free swivel crusher 101 which open and close the arm 2 and crush the structure 40, this invention is limited to a crusher. Is not to be done. For example, a cutting machine equipped with a cutter for cutting steel frames and timber may be used.

  Furthermore, in the hydraulic swirl crusher 1 and the free swirl crusher 101 of this embodiment, as can be seen from the fact that many common members are used, a working machine that feeds pressure oil only to the hydraulic cylinder 3, hydraulic pressure By applying the same attachment to both the working machine that sends pressure oil separately to the cylinder 3 and the hydraulic motor 10, it is possible to achieve the characteristic operation of the present embodiment.

  Although the present embodiment has been described above, the hydraulic swirl crusher 1, 201 and the free swirl crusher 101 according to the present embodiment are connected to the hydraulic cylinder side pipe of the hydraulic cylinder 3 through the branch connection pipes 33, 133, 233. It is characterized in that the pressure oil is fed into the hydraulic motor 10 from 31a, 131a, 231a. As a result, pressure oil can be fed from the hydraulic cylinder 3 side to the hydraulic motor 10 side, so that the hydraulic motor 10 can be always filled with oil. Therefore, when the hydraulic motor 10 is used as a braking mechanism, it is possible to prevent air from being mixed in due to oil leakage, and the hydraulic swirl crushers 1, 201 and free swirl crushing that have a constant braking force for a long period of time. The machine 101 can be provided. Further, even when the working hydraulic pressure of the hydraulic cylinder 3 and the pressure resistance of the drain port 14 of the hydraulic motor 10 are different, the pressure oil can be sent from the hydraulic cylinder 3 side to the hydraulic motor 10 through the branch connection pipes 33, 133 and 233. It is possible.

  Further, the cutting machine according to the present embodiment is characterized in that the pressure oil is fed from the hydraulic cylinder side pipes 31a, 131a, 231a of the hydraulic cylinder 3 to the hydraulic motor 10 through the branch connection pipes 33, 133, 233. Thereby, even if it is a cutting machine provided with the cutter which cut | disconnects a steel frame and wood, it becomes possible to provide as a cutting machine which show | plays the characteristic effect | action of this application mentioned above.

  Moreover, in the hydraulic swirl crushers 1, 201 and the free swirl crusher 101 of the present embodiment, the branch connection pipes 33, 133, 233 are provided with an accumulator 64. As a result, it is possible to absorb the surge pressure of the pressure reducing valve 63 attached to the branch connection pipes 33, 133, and 233 and the high hydraulic pressure temporarily generated in the drain port 14. Therefore, it is possible to prevent the drain port 14 having a low pressure resistance from being damaged, and it is possible to always send the pressure oil from the branch connection pipes 33, 133, and 233 to the hydraulic motor 10 through the drain port 14. And since it becomes possible to always fill the hydraulic motor 10 with oil, it becomes possible to provide the hydraulic swirl crushers 1 and 201 and the free swirl crusher 101 that provide a constant braking force for a long time. .

  Further, in the hydraulic swirl crusher 1, 201 and the free swirl crusher 101 of the present embodiment, the arm 2 and the hydraulic cylinder 3 are supported by a frame 4. The hydraulic motor 10 and the frame 4 are supported by a bracket 5. As a result, the hydraulic motor 3 can apply a braking force to the frame 4 to which the arm 2 is attached. Therefore, when the arm 2 is rotated by turning, the hydraulic motor 10 is used as a braking mechanism. Is possible. Therefore, in the hydraulic swirl crusher 1,201 and the free swirl crusher 101 of the present embodiment, even when the turning by turning is performed for a long time, a state where a constant braking force is applied for a long time is maintained. Is possible.

  Further, the hydraulic swirl crusher 1, 201 and the free swirl crusher 101 of the present embodiment are characterized in that a swivel bearing 12 is provided at a sliding portion between the frame 4 and the bracket 5. Thereby, when the frame 4 is rotated, it is possible to reduce the friction generated at the sliding portion with the bracket 5. Therefore, the rotation of the frame 4 is smooth, and it is possible to provide the hydraulic swirl crushers 1, 201 and the free swivel crusher 101 that have a constant braking force for a long time.

  Further, the free swirling crusher 101 of the present embodiment is characterized in that it is applied to a working machine that feeds pressurized oil to the hydraulic cylinder 3. Thereby, the free swirling crusher 101 of this embodiment can be applied to the hydraulic excavator 120.

  Furthermore, the hydraulic swirl crusher 1 of the present embodiment is characterized in that it is applied to a working machine that sends pressure oil to the hydraulic motor 10 separately from the hydraulic cylinder 3. Thereby, the hydraulic turning crusher 1 of the present embodiment can be applied to the hydraulic excavator 20.

  The hydraulic swirl crusher 201 of the present embodiment is characterized in that it is applied to a working machine that feeds hydraulic oil to the hydraulic motor 10 together with the hydraulic cylinder 3. Thereby, the hydraulic swirl crusher 201 of this embodiment can be applied to the hydraulic swivel crusher of the hydraulic excavator 220 having only the hydraulic cylinder pipes 231a and 231b on the hydraulic cylinder 3 side. Become.

  In the hydraulic swirl crusher 1 and free swivel crusher 101 of the present embodiment, a drain connection pipe 65a is connected to the drain port 14 of the hydraulic motor 10 or the branch connection pipes 33 and 133. A stop valve 66 for switching the connection between the connection pipe 65a and the branch connection pipes 33 and 133 is provided. Accordingly, the work machine attachment according to the present embodiment can be switched between the form of using the hydraulic turning and the form of using the free turning by simply switching the stop valve 66. 1. It can be used for both the free swirl crusher 101.

  As long as it is an attachment for a working machine provided with a fluid circuit, not only a crusher but also various attachments such as a grapple, a steel cutter, and a wood cutter are applicable.

1 is a plan view of a hydraulic swirl crusher 1 according to a first embodiment of the present invention. It is sectional drawing of the mounting part of the bracket 5 and the flame | frame 4 of this embodiment. 1 is a view showing a state in which a hydraulic swirl crusher 1 is attached to a hydraulic excavator 20. 1 is a schematic diagram of a hydraulic swing hydraulic circuit 60. FIG. It is the 1st figure for explaining braking by oil pressure of hydraulic swirl crusher 1. FIG. It is a figure which shows the state which attached the free swirling crusher 101 to the hydraulic shovel car 120. 1 is a schematic diagram of a free swivel hydraulic circuit 160. FIG. It is a figure for demonstrating the braking by the hydraulic pressure of the free swivel crusher 101. FIG. It is a figure which shows the state which attached the hydraulic rotation type crusher 201 to the hydraulic shovel car 220. FIG. 2 is a schematic diagram of a hydraulic swing hydraulic circuit 260. FIG. It is a figure for demonstrating the braking by the hydraulic pressure of the hydraulic turning crusher 201. FIG.

Explanation of symbols

1 Hydraulic swirling crusher (work machine attachment),
2 arms,
2a Tip crushing claw,
2b shearing blade,
2c Intermediate crushing nails,
3 Hydraulic cylinder,
3a piston rod,
3b cylinder outer cylinder,
4 frames,
4a support part,
4b annular flange,
5 Bracket,
5a body part,
5b annular flange,
5c mounting hole,
7 Frame mounting pin,
8 Hydraulic cylinder connection pin,
10 Hydraulic motor,
11 pinion,
12 slewing bearing,
12a bearing outer ring 12b bearing inner ring 12c ball 13 mounting bolt,
14 Drain port,
15 Throttle valve 17 Check valve 20 Hydraulic excavator (work machine),
21 Oil tank,
22 Cylinder side pump,
23 Motor side pump,
24 cylinder side direction switching valve,
24a parallel flow path,
24b neutral flow path,
24c cross flow path,
25 motor side direction switching valve,
25a parallel flow path,
25b neutral flow path,
25c crossing channel,
26 Cylinder side relief valve,
27 motor side relief valve,
29 Sequence valve 30 Working arm,
30a Arm cylinder 31a, 31b Hydraulic cylinder side piping,
32a, 32b Hydraulic motor side piping,
33 Branch connection piping (branch piping),
34 Swing pin,
40 structure,
40a reinforced concrete flat plate,
40b rebar,
40c reinforced concrete columns,
52 Cylinder pressure oil supply port,
53 Pressure oil supply port for motor,
54 Drain piping connection port,
60 hydraulic swivel hydraulic circuit,
61 Counter balance valve,
61a forward flow path,
61b closed flow path,
61c reverse flow path,
62 Brake valve,
62a relief valve,
63 Pressure reducing valve,
64 Accumulator,
65 drain piping,
65a Drain connection pipe 66 Stop valve (switching machine),
101 Free swivel crusher (work machine attachment),
120 hydraulic excavator (work machine),
131a, 131b hydraulic cylinder side piping,
133 Branch connection piping (branch piping),
160 free swivel hydraulic circuit,
201 hydraulic swirl crusher (work machine attachment),
220 hydraulic excavator (work machine),
231a, 231b Hydraulic cylinder side piping,
232a, 232b Hydraulic motor side branch supply pipe 233 Branch connection pipe (branch pipe),
260 hydraulic swivel hydraulic circuit,

Claims (11)

An arm that opens and closes to grip an object;
A hydraulic cylinder for opening and closing the arm;
A hydraulic motor for rotating the arm;
A brake valve for braking the rotation of the arm;
An attachment for a working machine comprising:
Between the circuit pipe of the hydraulic cylinder and the drain port of the hydraulic motor, a branch pipe that connects the circuit pipe and the drain port is provided,
A pressure reducing valve is provided between the branch pipes,
An attachment for a working machine, wherein pressure oil is fed from a circuit pipe of the hydraulic cylinder to the hydraulic motor through the branch pipe. An arm that opens and closes to cut an object;
A hydraulic cylinder for opening and closing the arm;
A hydraulic motor for rotating the arm;
A brake valve for braking the rotation of the arm;
An attachment for a working machine comprising:
Between the circuit pipe of the hydraulic cylinder and the drain port of the hydraulic motor, a branch pipe that connects the circuit pipe and the drain port is provided,
A pressure reducing valve is provided between the branch pipes,
An attachment for a working machine, wherein pressure oil is fed from a circuit pipe of the hydraulic cylinder to the hydraulic motor through the branch pipe. The work machine attachment according to claim 1, wherein the branch pipe is provided with an accumulator. The work machine attachment according to any one of claims 1 to 3, wherein the arm and the hydraulic cylinder are supported by a frame. The work machine attachment according to claim 4, wherein the hydraulic motor and the frame are supported by a bracket. 6. The work machine attachment according to claim 5, wherein a slewing bearing is provided at a sliding portion between the frame and the bracket. The work machine attachment according to any one of claims 1 to 6, wherein the work machine attachment is applied to a work machine that feeds pressure oil to the hydraulic cylinder. The work machine attachment according to claim 7, wherein the work machine attachment is applied to a work machine that sends pressure oil to the hydraulic motor separately from the hydraulic cylinder. The work machine attachment according to claim 7, wherein the work machine attachment is applied to a work machine that feeds pressure oil to the hydraulic motor together with the hydraulic cylinder. The drain port of the hydraulic motor or the branch pipe is connected to a drain pipe, and is provided with a switching machine that switches the connection between the drain pipe and the branch pipe. The work machine attachment according to any one of 9. A fluid circuit for opening and closing and rotating an arm by fluid pressure,
A first actuator for opening and closing the arm;
A second actuator for rotating the arm;
A brake valve that adjusts the amount of fluid flowing by the external force when an external force is applied to the second actuator when the flow of the fluid is stopped with respect to the second actuator;
A fluid circuit, wherein a branch pipe connecting the circuit pipe of the first actuator and the drain port of the second actuator is provided, and a pressure reducing valve is provided between the branch pipes.

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