JP5074739B2 - Hydraulic crusher - Google Patents

Description

  The present invention relates to a hydraulic crusher that is attached to an arm of a work carriage such as a hydraulic excavator and performs a crushing operation.

  In recent years, hydraulic crushers are often used for dismantling concrete, steel structures, and the like. The hydraulic crusher has a crushing arm supported by the crusher body, and the crushing arm crushes the object to be crushed. Many hydraulic crushers are constructed so that the crusher body can be turned. During the crushing operation, the crusher body is turned to adjust the posture of the hydraulic crusher and the opening / closing direction of the crushing arm according to the shape and state of the crushing object.

There is a great need for a hydraulic swirl type crusher because swivel operation and maintenance are easy. However, the hydraulic swivel type has a drawback in that it is necessary to provide a hydraulic piping for swiveling on a work carriage equipped with a hydraulic crusher.
In order to solve this drawback, there has been proposed a hydraulic circuit of a hydraulic crusher that enables hydraulic turning without arranging hydraulic piping for turning on a work carriage (see Patent Document 1).

  This hydraulic circuit is shown in FIG. A hydraulic motor 110 that rotates the crusher body of the hydraulic crusher is disposed in the fixed bracket 111, and a reciprocating opening hydraulic passage 112 and a closing hydraulic passage 113 are a hydraulic cylinder 115 that opens and closes the crushing arm, and a trolley pump. 116 and the hydraulic oil tank 117 are connected. When hydraulic oil is supplied from the opening hydraulic flow path 112, the hydraulic cylinder 115 contracts to open the crushing arm, and when hydraulic oil is supplied from the closing hydraulic flow path 113, the hydraulic cylinder 115 extends to expand the crushing arm. It is configured to perform a closing operation.

  A branch pipe 118 branches off from the opening hydraulic flow path 112 and is connected to the hydraulic motor 110. A relief valve 122 is installed in the branch pipe 118, and an opening operation delay means 120 and a variable throttle 123 are installed between the relief valve 122 and the hydraulic motor 110. A branch pipe 119 branches off from the closing hydraulic flow path 113 and is connected to the hydraulic motor 110. The branch pipe 119 is provided with a check valve 121 so as to prevent hydraulic fluid from flowing from the closing hydraulic flow path 113 to the hydraulic motor 110.

  In this hydraulic crusher, during the opening operation of the crushing arm, the pressure of the opening hydraulic flow path 112 does not increase to the set pressure of the relief valve 122, the relief valve 122 is closed, and the branch pipe 118 communicates with the hydraulic motor 110. Not done. When the crushing arm reaches the open end, the pressure in the opening hydraulic flow path 112 rises to the set pressure of the relief valve 122, and the relief valve 122 opens. After the relief valve 122 is opened, the opening operation delay means 120 is opened with a delay, the branch pipe 118 communicates with the hydraulic motor 110, and hydraulic oil passes from the opening hydraulic flow path 112 through the branch pipe 118 to the hydraulic motor 110. Flow, the crusher body turns.

The turning operation of the crusher body is controlled by adjusting the oil amount and pressure of the hydraulic oil to the hydraulic motor 110 by the variable throttle 123.
Therefore, the crusher body can be turned after the crushing arm has been opened and the crusher body is prevented from turning during the crushing operation. In addition, if the operation is continued for a certain period of time after the crushing arm is open, the crusher body turns, so there is no need to operate another lever to turn the crusher body, making it easy to use. .
JP 2001-116005 A

However, the hydraulic crusher having the above-described hydraulic circuit has the following problems.
According to the knowledge of the inventor, in the general hydraulic motor 110 provided in the hydraulic crusher, the differential pressure before and after necessary for the rotation of the hydraulic motor 110 is about 5 MPa, and the required flow rate of the hydraulic oil is also 30 L / It is about min. On the other hand, the bogie pump 116 of the work carriage on which the hydraulic crusher is normally mounted generally has a discharge pressure far exceeding 5 MPa and a discharge flow rate far exceeding 30 L / min. The pressure on the side hydraulic circuit far exceeds 5 MPa. Further, during the opening operation of the crushing arm, the pressure of the opening hydraulic flow path 112 generally exceeds 20 MPa. In order to open the relief valve 122 after the crushing arm is at the open end, the set pressure of the relief valve 122 must be set to a value exceeding 20 MPa. During the turning of the crusher body, the pressure of the opening hydraulic flow path 112 is maintained higher than the set pressure of the relief valve 122, and the relief valve 122 is kept open.

  Therefore, the pressure and flow rate of the hydraulic oil discharged from the bogie pump 116 far exceed the value required for the rotation of the hydraulic motor 110, and a large amount of high-pressure hydraulic oil becomes surplus oil and circulates in the hydraulic circuit. . For this reason, the energy efficiency of the hydraulic circuit is poor, and the fuel efficiency of the truck pump 116 increases. In addition, since a high pressure exceeding 20 MPa is applied to the hydraulic circuit, the durability of the equipment exposed to the high pressure is likely to decrease, and the temperature of the circulating high-pressure hydraulic oil may rise and overheat.

  Regarding the turning of the crusher main body, the crusher main body may turn even if the operator does not intend. When a hydraulic crusher enters the structure to be crushed to perform a crushing operation, positioning of the next crushing operation may be performed while the crushing arm is being opened to improve work efficiency. When the space in the structure to be crushed is narrow, the crushing arm during the opening operation comes into contact with surrounding crushing objects and the like, and resistance is easily added to the opening operation of the crushing arm. By this resistance, the pressure of the opening hydraulic flow path 112 immediately rises to the set pressure of the relief valve 122, the relief valve 122 and the opening operation delay means 120 are sequentially opened, and the branch pipe 118 communicates with the hydraulic motor 110. 110 may rotate and the crusher body may turn. This turning of the crusher body is abrupt and has a considerable influence on the work efficiency, and also causes the crushing glass to fall and the crushing object to collapse.

  The present invention solves the above-described problems, and the object of the present invention is to improve the energy efficiency of the hydraulic circuit during turning, improve the fuel efficiency of the bogie pump, and suppress the application of high pressure to the hydraulic circuit. An object of the present invention is to provide a hydraulic crusher that prevents the crusher body from turning unintentionally by an operator.

The present invention adopts the following configuration in order to solve the problem. The hydraulic crusher according to the invention of claim 1 includes a crushing arm, a crusher body that supports the crushing arm so that the crushing arm can be opened and closed, a fixed bracket that pivotally connects the crusher body to the arm of the work carriage, and a crusher body. A hydraulic crusher having a hydraulic actuator arranged to open and close the crushing arm and a hydraulic motor for turning the crusher body, and an open / close hydraulic flow path connected to the hydraulic actuator from the work carriage side, A swing hydraulic flow path branched from the open / close hydraulic flow path and connected to a hydraulic motor, and a communication between the swing hydraulic flow path opened and closed by a pilot pressure from the open / close hydraulic flow path or a hydraulic actuator. A pilot operated check valve that switches between closing, a pilot hydraulic flow path that transmits the pilot pressure to the pilot operated check valve, and a crushing arm or a hydraulic actuator Pilot hydraulic flow path opening / closing means for switching communication and closing of the pilot hydraulic flow path according to the position, and branching from the turning hydraulic flow path, bypassing the hydraulic motor, rejoining the turning hydraulic flow path, and variable a bypass passage aperture is provided, the pilot hydraulic passage is closed and a delay means for the hydraulic motor provides a delay time until the rotation from communicating, wherein the pilot operated check valve is opened When the turning hydraulic flow path communicates, the hydraulic oil supplied from the working carriage side is supplied only from the opening / closing hydraulic flow path among the hydraulic actuator, the opening / closing hydraulic flow path, and the pilot hydraulic flow path. It flows through the flow path to the hydraulic motor .

  According to the invention of claim 1, the pilot hydraulic flow path opening / closing means switches between communication and closing of the pilot hydraulic flow path according to the position of the crushing arm or the hydraulic actuator. When the pilot hydraulic flow path communicates, the pilot operation check valve is opened by the pilot pressure from the open / close hydraulic flow path or the hydraulic actuator, and the turning hydraulic flow path communicates. When the turning hydraulic flow path communicates, hydraulic fluid flows from the opening and closing hydraulic flow path through the turning hydraulic flow path to the hydraulic motor, the hydraulic motor rotates, and the crusher body turns.

  While hydraulic fluid flows to the hydraulic motor through the turning hydraulic flow path and the hydraulic motor rotates, the pressure required on the entry side of the turning hydraulic flow path is the pressure on the outlet side of the turning hydraulic flow path, A total pressure obtained by summing the differential pressure necessary for the rotation of the hydraulic motor and the resistance received from the turning hydraulic flow path is sufficient. Since the pilot check valve opens and closes by the pilot pressure from the open / close hydraulic flow path or the hydraulic actuator and switches between communication and closing of the swing hydraulic flow path, the pressure on the entry side of the swing hydraulic flow path is increased. Therefore, there is no need to switch between the communication and closing of the turning hydraulic flow path, and the pressure upstream from the hydraulic motor does not need to be higher than the total pressure. Further, surplus oil can be flowed from the turning hydraulic flow path to the bypass flow path. By adjusting the flow rate of the surplus oil flowing in the bypass flow path by the variable restriction of the bypass flow path, it is possible to suppress the high pressure from being applied to the upstream side from the hydraulic motor.

  If the crushing arm or the hydraulic actuator is not in a predetermined position, the pilot hydraulic passage and the turning hydraulic passage remain closed, the hydraulic oil does not flow to the hydraulic motor, and the crusher body does not turn. The operator can easily recognize whether or not the crusher body can be turned, and the crusher body can be prevented from turning regardless of the operator's intention. The delay time given by the delay means is the time from when the pilot hydraulic flow path is communicated to when the hydraulic motor rotates. Within this delay time, the operator can determine whether or not to rotate the crusher body.

A hydraulic crusher according to a second aspect of the present invention is the hydraulic crusher according to the first aspect, wherein the pilot hydraulic flow path opening / closing means is provided in a hydraulic actuator.
Since the pilot hydraulic flow path opening / closing means is provided in the hydraulic actuator, the number of necessary parts is reduced, the degree of freedom in arranging parts is improved, and the cost is reduced.

  Since the hydraulic crusher according to the present invention has the above-described configuration, the energy efficiency of the hydraulic circuit is good, the fuel consumption of the bogie pump can be improved, high pressure can be suppressed from being applied to the hydraulic circuit, and the operator can Unintentional rotation of the crusher body can be prevented.

A first embodiment for carrying out the present invention will be described with reference to FIGS. 1 and 2.
As shown in FIG. 1, the hydraulic crusher 1 has a crusher body 2 and a fixed bracket 3. The fixed bracket 3 is fixed to the arm of the work carriage, and the crusher main body 2 is connected to the fixed bracket 3 via the turning wheel 4. The turning wheel 4 has an inner ring and an outer ring. The inner ring is fixed to the crusher body 2 and the outer ring is fixed to the fixed bracket 3. The output gear of the hydraulic motor 5 installed on the fixed bracket 3 is in mesh with the gear of the inner ring of the turning wheel 4.

  A crushing arm 6 is supported by the crusher body 2 so as to be openable and closable, and a hydraulic cylinder 10 is installed in the crusher body 2 as a hydraulic actuator that opens and closes the crushing arm 6. When the hydraulic cylinder 10 is reduced, the crushing arm 6 is opened. When the hydraulic cylinder 10 is extended, the crushing arm 6 is closed. When the piston of the hydraulic cylinder 10 reaches the reduction side stroke end, the crushing arm 6 is opened. Thus, when the piston reaches the extension side stroke end, the crushing arm 6 is closed.

  As shown in FIG. 2, open / close hydraulic flow paths 61 and 62 are connected to the hydraulic cylinder 10 from the work carriage through the swivel 54A. When the hydraulic cylinder 10 is reduced, the open / close hydraulic flow path 61 is on the hydraulic oil supply side, and the open / close hydraulic flow path 62 is on the hydraulic oil discharge side, and when the hydraulic cylinder 10 is extended, the open / close hydraulic flow path 62 operates. The oil supply side serves as an oil supply side, and the open / close hydraulic flow path 61 serves as a hydraulic oil discharge side.

A turning hydraulic flow path 74 is branched from the opening / closing hydraulic flow path 61 on the fixed bracket 3 side and connected to the hydraulic motor 5, and a check valve 49 </ b> A is installed in the turning hydraulic flow path 74. The check valve 49A is a pilot operated check valve, and a pilot hydraulic flow path 67 described later is connected to the pilot port of the check valve 49A.
The hydraulic motor 5 has a general brake valve 53 in case of overload or turning.

The turning hydraulic flow path 75 is connected from the hydraulic motor 5 to the opening / closing hydraulic flow path 62 on the fixed bracket 3 side, and the check valve 49D is installed in the turning hydraulic flow path 75. The check valve 49D is configured to flow hydraulic oil from the hydraulic motor 5 side to the open / close hydraulic flow path 62 side.
A bypass hydraulic flow path 78 branches from the turning hydraulic flow path 74 and is connected to the turning hydraulic flow path 75. A variable throttle 50 </ b> A is installed in the bypass hydraulic flow path 78.

The pilot hydraulic passage 67 connects between the pilot port of the check valve 49 </ b> A and the opening / closing hydraulic passage 61 on the fixed bracket 3 side, and the check valve 49 </ b> E is installed in the pilot hydraulic passage 67. The check valve 49E is configured to flow hydraulic oil from the check valve 49A side to the open / close hydraulic flow path 61 side.
The configuration of the hydraulic crusher 1 described so far is hereinafter referred to as a basic configuration.

A rod guard 12 is attached to the piston rod of the hydraulic cylinder 10. When the piston of the hydraulic cylinder 10 reaches the reduction side stroke end, the rod guard 12 pushes the spool 31 of the switching valve 30 described later, and when the piston of the hydraulic cylinder 10 moves away from the reduction side stroke end, the rod guard 12 is removed from the spool 31. It is the structure which leaves.
On the crusher body 2 side, the pilot hydraulic flow path 65 is branched from the opening / closing hydraulic flow path 61 and connected to the primary side of the switching valve 30. The switching valve 30 is a mechanical cam operated valve and serves as a pilot hydraulic flow path opening / closing means. The installation position of the switching valve 30 in the crusher body 2 is a position where the switching valve 30 is not exposed to the outside from the crusher body 2. The switching valve 30 has a spool 31 biased by a spring. When the rod guard 12 pushes the spool 31, the switching valve 30 is in the open position, and when the rod guard 12 is separated from the spool 31, the switching valve 30 is in the closed position. It becomes the composition which becomes.

  The pilot hydraulic passage 66 is connected from the secondary side of the switching valve 30 to the port 44A of the delay valve 40 described later through the swivel 54B, and the check valve 49F is connected to the pilot hydraulic passage 66 on the crusher body 2 side. is set up. The check valve 49F is configured to flow hydraulic oil from the delay valve 40 side to the switching valve 30 side. When the switching valve 30 is in the open position, the pilot hydraulic passage 66 communicates by bypassing the check valve 49F, and when the switching valve 30 is in the closed position, the pilot hydraulic passage 66 is closed by the check valve 49F. It has a configuration.

  The delay valve 40 is a cavity-type delay valve that constitutes a delay means and includes a piston 41, a primary side oil chamber 42, a secondary side oil chamber 43, and ports 44A, 44B, 44C, and 44D. The primary side oil chamber 42 and the secondary side oil chamber 43 are on both sides of the piston 41, the port 44A is formed at the end of the primary side oil chamber 42, and the ports 44C and 44D are formed at the end of the secondary side oil chamber 43. The port 44B is formed at a position slightly closer to the primary side oil chamber 42 than the center. The port 44B is connected to a pilot hydraulic flow path 67 between the check valve 49A and the check valve 49E. When the piston 41 moves to the end of the secondary oil chamber 43, the port 44B opens and the delay valve 40 opens, and when the piston 41 moves toward the primary oil chamber 42, the port 44B closes and the delay valve 40 opens. It becomes the structure which will be in a closed state. In FIG. 2, the delay valve 40 is closed.

  The delay valve flow path 88 branches off from the open / close hydraulic flow path 62 on the fixed bracket 3 side. The delay valve flow path 88 is divided into branch delay valve flow paths 89 and 90, and the branch delay valve flow paths 89 and 90 are connected to the ports 44 </ b> C and 44 </ b> D of the delay valve 40. The variable throttle 50B is installed in the branch delay valve channel 89, and the check valve 49G is installed in the branch delay valve channel 90. The check valve 49G is configured to flow hydraulic oil from the delay valve flow path 88 side to the delay valve 40 side.

Next, the operation will be described.
First, the case where the hydraulic cylinder 10 is reduced and the crushing arm 6 is opened will be described. First, it is assumed that the delay valve 40 is in a closed state.
The open / close hydraulic flow path 61 becomes high pressure on the hydraulic oil supply side, the open / close hydraulic flow path 62 becomes low pressure on the hydraulic oil discharge side, and the hydraulic cylinder 10 is reduced. Until the piston of the hydraulic cylinder 10 reaches the reduction stroke end, the rod guard 12 is separated from the spool 31 of the switching valve 30, the switching valve 30 is in the closed position, and the pilot hydraulic flow path 66 is closed. Therefore, the hydraulic oil does not flow from the open / close hydraulic flow channel 61 through the pilot hydraulic flow channel 65 to the pilot hydraulic flow channel 66.

  When the piston of the hydraulic cylinder 10 reaches the reduction side stroke end, the crushing arm 6 becomes an open end, and the rod guard 12 pushes the spool 31 of the switching valve 30, and the switching valve 30 is switched to the open position. When the switching valve 30 is in the open position, the pilot hydraulic flow path 66 bypasses the check valve 49F and communicates, and hydraulic oil passes from the opening / closing hydraulic flow path 61 through the pilot hydraulic flow paths 65 and 66 to the delay valve 40. It flows into the primary side oil chamber 42. The hydraulic oil in the primary side oil chamber 42 pushes the piston 41 of the delay valve 40 to the end on the secondary side oil chamber 43 side, and the hydraulic oil in the secondary side oil chamber 43 passes through the branch delay valve channel 89 and the delay valve channel 88. It passes through and is discharged to the open / close hydraulic flow path 62. The hydraulic oil discharged from the secondary oil chamber 43 is throttled by the variable throttle 50B, the speed of the piston 41 is reduced, and the delay valve 40 is gradually opened.

  When the delay valve 40 is opened, the hydraulic oil flows from the primary oil chamber 42 of the delay valve 40 through the pilot hydraulic passage 67 to the pilot port of the check valve 49A, and the pressure in the pilot hydraulic passage 67 is changed to the pilot pressure. As a result, the check valve 49A is opened. When the check valve 49 </ b> A is opened, the hydraulic oil flows from the high-pressure opening / closing hydraulic passage 61 to the turning hydraulic passage 74, and further flows from the turning hydraulic passage 74 to the hydraulic motor 5 and the bypass hydraulic passage 78.

When hydraulic fluid flows from the turning hydraulic flow path 74 to the hydraulic motor 5, the hydraulic motor 5 rotates and the crusher body 2 turns. The hydraulic oil that has flowed to the hydraulic motor 5 flows to the turning hydraulic flow path 75.
The hydraulic fluid that has flowed into the bypass hydraulic flow path 78 flows into the turning hydraulic flow path 75 as surplus oil. The flow rate of the surplus oil can be adjusted by the variable throttle 50A of the bypass hydraulic flow path 78, and at the same time, the pressure and flow rate of the hydraulic oil flowing to the hydraulic motor 5 can be adjusted. The turning speed of the crusher body 2 can be adjusted by adjusting the flow rate of the hydraulic oil flowing to the hydraulic motor 5.

The hydraulic oil that has rotated the hydraulic motor 5 and the surplus oil that has flowed into the bypass hydraulic flow path 78 are both discharged from the turning hydraulic flow path 75 to the open / close hydraulic flow path 62.
When the crusher body 2 turns, the open / close hydraulic flow paths 61 and 62 are closed, the supply of hydraulic oil to the hydraulic motor 5 is stopped, the rotation of the hydraulic motor 5 is stopped, and the crusher body 2 stops turning. . When the turning of the crusher body 2 is stopped, the crusher body 2 is positioned by the arm of the work carriage. When the crusher body 2 is positioned, the hydraulic cylinder 10 is extended to close the crushing arm 6, and the crushing arm 6 crushes and crushes the object to be crushed to perform crushing work.

When the hydraulic cylinder 10 is extended, the open / close hydraulic flow path 62 becomes high pressure on the hydraulic oil supply side, and the open / close hydraulic flow path 61 becomes low pressure on the hydraulic oil discharge side. When the hydraulic cylinder 10 is extended, the rod guard 12 is separated from the spool 31 of the switching valve 30, the switching valve 30 is switched to the closed position, and the pilot hydraulic flow path 66 is closed by the check valve 49F.
Since the open / close hydraulic flow path 62 is at a high pressure, hydraulic oil passes from the open / close hydraulic flow path 62 through the delay valve flow path 88 and the branch delay valve flow paths 89 and 90 to the secondary side oil chamber 43 of the delay valve 40. Flowing. The piston 41 of the delay valve 40 moves to the primary side oil chamber 42 side end, the hydraulic oil in the primary side oil chamber 42 passes through the pilot hydraulic flow paths 66 and 65, and is discharged to the open / close hydraulic flow path 61. Return to the closed state.

When the piston 41 of the delay valve 40 starts to move toward the primary side oil chamber 42, the port 44B of the delay valve 40 is immediately closed. When the port 44B is closed, the hydraulic oil remains in the pilot hydraulic passage 67, but the remaining hydraulic oil passes through the check valve 49E and is discharged to the open / close hydraulic passage 61, and the pressure in the pilot hydraulic passage 67 is reduced. The check valve 49A is closed, and the turning hydraulic flow path 74 is closed.
When the object to be crushed is crushed by the crushing arm 6, the hydraulic cylinder 10 is reduced and the crushing arm 6 is opened. When the crushing arm 6 is opened, the crusher body 2 is turned as necessary, and the crusher body 2 is positioned for the next crushing operation.

  Since the hydraulic crusher 1 is as described above, when the hydraulic motor 5 rotates and the crusher body 2 turns, the pressure required on the entry side of the turning hydraulic flow path 74 is applied to the check valves 49A and 49D. The total pressure is the sum of each resistance, the differential pressure before and after the hydraulic motor 5, and the back pressure from the opening and closing hydraulic flow path 62. If the resistances of the check valves 49A and 49D are reduced, the pressure required on the entry side of the turning hydraulic flow path 74 can be further reduced, and the pressure applied to the equipment of the hydraulic circuit can be suppressed to a low level. Can be prevented from decreasing.

In addition, since the total pressure is sufficient for the pressure required on the entry side of the turning hydraulic flow path 74, the cart pump does not need to discharge a large amount of high-pressure hydraulic oil. Since the discharge pressure of the cart pump at this time is below the inflection point of the PQ curve, the energy efficiency of the hydraulic circuit is good, and the fuel consumption of the cart pump is suppressed low.
Note that the crusher main body 2 is swung only when the hydraulic cylinder 10 is reduced to the reduction side stroke end and the crushing arm 6 becomes an open end. There is no turning.

The operator can determine whether or not to turn the crusher body 2 within a delay time from when the crushing arm 6 is in the open end to when the delay valve 40 is in the open state. The delay time is adjusted by the variable aperture 50B.
Since the switching valve 30 is installed at a position where the switching valve 30 is not exposed to the outside from the crusher main body 2, the spool 31 of the switching valve 30 is prevented from coming into contact with an object to be crushed, crushed glass, or the like. The switching valve 30 does not accidentally enter the open position due to contact with an object or the like, the delay valve 40 and the check valve 49A do not enter the open position, and the crusher body 2 may turn suddenly. Absent. Accordingly, the crusher main body 2 turns only when the operator intends, and the safety and reliability of the hydraulic crusher 1 are excellent.

A second embodiment for carrying out the present invention will be described with reference to FIG. The same components as those in the first embodiment are denoted by the same reference numerals.
The hydraulic crusher 1 has the same basic configuration as that shown in FIG. 1 in the first embodiment.
A cylinder port 15 is formed in the cylinder tube 14 of the hydraulic cylinder 10, and the cylinder port 15 serves as a pilot hydraulic flow path opening / closing means. The opening position of the cylinder port 15 in the cylinder tube 14 is a position where the piston 11 communicates with the reduction-side oil chamber 18 when the piston 11 reaches the reduction-side stroke end. When the piston 11 reaches the reduction side stroke end, the cylinder port 15 communicates with the reduction side oil chamber 18, and when the piston 11 moves from the reduction side stroke end toward the extension side stroke end, first, the cylinder port 15 is moved to the piston 11. Then, the cylinder port 15 communicates with the extension-side oil chamber 19. FIG. 3 shows a state in which the cylinder port 15 communicates with the reduction-side oil chamber 18.

The open / close hydraulic flow path 61 is connected to the reduction-side oil chamber 18 of the hydraulic cylinder 10, and the open / close hydraulic flow path 62 is connected to the expansion-side oil chamber 19 of the hydraulic cylinder 10.
The pilot hydraulic flow path 65 is connected from the cylinder port 15 to the check valve 49H, and the pilot hydraulic flow path 66 is connected from the check valve 49H to the port 44A of the delay valve 40. The check valve 49H is a pilot operated check valve, and the pilot hydraulic flow path 71 is connected from the open / close hydraulic flow path 62 to the pilot port of the check valve 49H. The pilot ratio of the check valve 49H is such that when the cylinder port 15 communicates with the reduction side oil chamber 18, the hydraulic oil flowing from the reduction side oil chamber 18 to the check valve 49H can pass through the check valve 49H. Appropriate values are selected.

On the fixed bracket 3 side, the branch hydraulic passage 84 is branched from the pilot hydraulic passage 66 and connected to the opening / closing hydraulic passage 61, and the check valve 49 </ b> J is installed in the branch hydraulic passage 84. The check valve 49J is configured to flow hydraulic oil from the pilot hydraulic flow path 66 side to the open / close hydraulic flow path 61 side.
The fixed bracket 3 is provided with a delay valve 40, a delay valve flow path 88, branch delay valve flow paths 89 and 90, a variable throttle 50B, and a check valve 49G having the same configuration as in the first embodiment.

Next, the operation will be described.
First, a case where the hydraulic cylinder 10 extends and the crushing arm 6 performs a closing operation will be described.
The open / close hydraulic flow path 61 becomes low pressure on the hydraulic oil discharge side, the open / close hydraulic flow path 62 becomes high pressure on the hydraulic oil supply side, the hydraulic cylinder 10 extends, and the crushing arm 6 is closed. Do.

  When the piston 11 reaches the reduction side stroke end, the cylinder port 15 communicates with the reduction side oil chamber 18, and when the piston 11 moves toward the extension side stroke end, the cylinder port 15 is once blocked by the piston 11. Thereafter, the cylinder port 15 communicates with the extension side oil chamber 19. While the cylinder port 15 communicates with the reduction-side oil chamber 18, the check valve 49H closes with the hydraulic pressure of the open / close hydraulic flow path 62 as the pilot pressure. While the cylinder port 15 is in communication with the extension-side oil chamber 19, the check valve 49H is closed using the self pressure as the pilot pressure. Therefore, while the hydraulic cylinder 10 is extended, the check valve 49H is closed, and hydraulic oil does not flow from the pilot hydraulic flow path 65 to the pilot hydraulic flow path 66.

The hydraulic fluid flows from the high-pressure switching hydraulic passage 62 through the delay valve passage 88 and the branch delay valve passages 89 and 90 to the secondary side oil chamber 43 of the delay valve 40, and the piston 41 of the delay valve 40 moves. The hydraulic oil in the primary side oil chamber 42 is discharged to the low-pressure opening / closing hydraulic flow path 61 through the pilot hydraulic flow path 66 and the branch hydraulic flow path 84, and the delay valve 40 is closed.
When the crushing arm 6 is closed, the open / close hydraulic flow path 61 becomes the hydraulic oil supply side and becomes high pressure, the open / close hydraulic flow path 62 becomes the hydraulic oil discharge side and becomes low pressure, and the hydraulic cylinder 10 Shrinking and the crushing arm 6 opens.

  If the cylinder port 15 communicates with the extension side oil chamber 19 and the piston 11 moves toward the reduction side stroke end while the piston 11 is on the extension side stroke end side, the cylinder port 15 is once blocked by the piston 11. When the piston 11 reaches the reduction side stroke end, the cylinder port 15 communicates with the reduction side oil chamber 18. While the cylinder port 15 is in communication with the extension-side oil chamber 19, the check valve 49H closes with the self-pressure, that is, the back pressure of the hydraulic oil discharged to the open / close hydraulic flow path 62 as the pilot pressure. When the cylinder port 15 communicates with the reduction side oil chamber 18, the hydraulic oil flows from the reduction side oil chamber 18 to the pilot hydraulic flow path 65. The pressure of the hydraulic fluid flowing from the reduction side oil chamber 18 through the pilot hydraulic flow path 65 to the check valve 49H is higher than the pilot pressure that has closed the check valve 49H until then. Therefore, when the piston 11 reaches the reduction side stroke end and the cylinder port 15 communicates with the reduction side oil chamber 18, the check valve 49H opens, and the pilot hydraulic flow path 65 and the pilot hydraulic flow path 66 communicate with each other. The hydraulic oil flows from the pilot hydraulic flow path 65 to the pilot hydraulic flow path 66.

The hydraulic oil flows from the pilot hydraulic flow path 66 to the primary oil chamber 42 of the delay valve 40, and the hydraulic oil in the secondary oil chamber 43 of the delay valve 40 passes through the branch delay valve flow path 89 and the delay valve flow path 88. The delay valve 40 is gradually opened in the open / close hydraulic flow path 62.
After the delay valve 40 is gradually opened, as in the first embodiment, the check valve 49A is opened, the hydraulic oil flows to the hydraulic motor 5, the hydraulic motor 5 rotates, and the crusher body 2 is Turn. Further, part of the hydraulic oil flows as surplus oil through the bypass hydraulic flow path 78, and the hydraulic oil is discharged from the hydraulic motor 5 and the bypass hydraulic flow path 78 to the open / close hydraulic flow path 62. When the crusher body 2 turns, the open / close hydraulic flow paths 61 and 62 are closed, the supply of hydraulic oil to the hydraulic motor 5 is stopped, the rotation of the hydraulic motor 5 is stopped, and the crusher body 2 stops turning. . And if turning of the crusher main body 2 is stopped, the crusher main body 2 is positioned by the arm of the work carriage, and the crushing arm 6 is closed.

In the hydraulic crusher 1 as described above, since the hydraulic cylinder 10 has the cylinder port 15 as the pilot hydraulic flow path opening / closing means, the number of necessary parts can be reduced, the degree of freedom in arranging parts can be improved, and the cost can be reduced. It becomes possible.
Other operations are the same as those in the first embodiment.
A third embodiment for carrying out the present invention will be described with reference to FIG. The same components as those in the first embodiment are denoted by the same reference numerals.

The hydraulic crusher 1 has the same basic configuration as that shown in FIG. 1 in the first embodiment.
The hydraulic cylinder 10 has a cylinder tube 14 and a piston 11, and a cylinder port 15 is formed in the cylinder tube 14, and the cylinder port 15 has the same configuration as that of the second embodiment.
A projecting portion 21 projecting into the cylinder tube 14 is formed on the end plate 20 of the cylinder tube 14, and a cushion chamber 22 is formed at the tip of the piston 11 so as to be able to fit with the projecting portion 21. An end plate port 23 is formed in the end plate 20, and the extension side oil chamber 19 communicates with a branch hydraulic passage 85 to be described later through the end plate port 23. The protrusion 21, the cushion chamber 22 and the end plate port 23, and a check valve 49K and a variable throttle 50C installed in a branch hydraulic flow path 85 to be described later constitute delay means.

Similarly to the first embodiment, open / close hydraulic flow paths 61 and 62 are connected to the hydraulic cylinder 10, the open / close hydraulic flow path 61 communicates with the reduction-side oil chamber 18, and the open / close hydraulic flow path 62 is It communicates with the extension side oil chamber 19.
On the crusher body 2 side, a branch hydraulic flow path 85 is branched from the open / close hydraulic flow path 62 and connected to the end plate port 23. A check valve 49K and a variable throttle 50C are installed in parallel in the branch hydraulic flow path 85, and the check valve 49K is configured to flow hydraulic oil from the open / close hydraulic flow path 62 side to the end plate port 23 side.

  A pilot hydraulic flow path 65 is connected from the cylinder port 15 to the check valve 49H. The check valve 49H has a configuration similar to that of the second embodiment. The pilot hydraulic passage 66 is connected from the check valve 49H to the pilot hydraulic passage 67, and the pilot hydraulic passage 71 is connected from the branch hydraulic passage 85 to the pilot port of the check valve 49H.

Next, the operation will be described.
First, a case where the hydraulic cylinder 10 extends and the crushing arm 6 performs a closing operation will be described.
When the open / close hydraulic flow path 61 becomes a low pressure on the hydraulic oil discharge side and the open / close hydraulic flow path 62 becomes a high pressure on the hydraulic oil supply side, the hydraulic cylinder 10 extends and the crushing arm 6 is closed. I do.
When the hydraulic cylinder 10 is extended, the hydraulic oil flows directly from the opening / closing hydraulic passage 62 to the extension-side oil chamber 19 and from the opening / closing hydraulic passage 62 to the extension-side oil chamber 19 through the branch hydraulic passage 85. .

As in the second embodiment, while the hydraulic cylinder 10 extends, the check valve 49H is closed, and hydraulic oil does not flow from the pilot hydraulic flow path 65 to the pilot hydraulic flow path 66.
When the crushing arm 6 finishes the closing operation, the opening / closing hydraulic passage 61 becomes the hydraulic oil supply side and becomes high pressure, the opening / closing hydraulic passage 62 becomes the hydraulic oil discharge side and becomes low pressure, and the hydraulic cylinder 10 becomes Shrinking and the crushing arm 6 opens. The hydraulic oil is discharged directly from the extension-side oil chamber 19 to the open / close hydraulic flow path 62, and is discharged to the open / close hydraulic flow path 62 through the variable throttle 50 </ b> C of the branch hydraulic flow path 85.

When the piston 11 approaches the reduction side stroke end and the protruding portion 21 of the end plate 20 is fitted into the cushion chamber 22 of the piston 11, the hydraulic oil discharged from the extension side oil chamber 19 to the open / close hydraulic flow path 62 is variable. The speed of the piston 11 is reduced and the opening speed of the crushing arm 6 is also reduced.
Similarly to the second embodiment, the piston 11 reaches the reduction side stroke end, the cylinder port 15 communicates with the reduction side oil chamber 18, and the check valve 49H opens. When the check valve 49H is opened, the hydraulic oil flows from the pilot hydraulic passage 65 through the pilot hydraulic passages 66 and 67 to the pilot port of the check valve 49A, and the check valve 49A is opened.

  After the check valve 49A is opened, as in the first embodiment, the check valve 49A is opened, the hydraulic oil flows to the hydraulic motor 5, the hydraulic motor 5 rotates, and the crusher body 2 turns. Further, part of the hydraulic oil flows through the bypass hydraulic flow path 78 as surplus oil, and the hydraulic oil is discharged from the hydraulic motor 5 and the bypass hydraulic flow path 78 to the open / close hydraulic flow path 62. When the crusher body 2 turns, the open / close hydraulic flow paths 61 and 62 are closed, the supply of hydraulic oil to the hydraulic motor 5 is stopped, the rotation of the hydraulic motor 5 is stopped, and the crusher body 2 stops turning. . And if turning of the crusher main body 2 is stopped, the crusher main body 2 is positioned by the arm of the work carriage, and the crushing arm 6 is closed.

  Since the hydraulic crusher 1 is as described above, the time from when the operator visually recognizes the reduction of the opening speed of the crushing arm 6 until the crushing arm 6 reaches the open end is a delay time. The operator can determine whether or not to turn the crusher body 2. By adjusting the variable throttle 50C, it is possible to adjust the time from when the opening speed of the crushing arm 6 is decelerated until the opening end is reached.

Since the hydraulic cylinder 10 has the pilot hydraulic flow path opening / closing means and the delay means, the number of necessary parts can be reduced, the degree of freedom of arrangement of each part in the fixed bracket 3 with a small space margin is improved, and the cost can be reduced. It becomes.
Other operations are the same as those in the first embodiment.
A fourth embodiment for carrying out the present invention will be described with reference to FIG. The same components as those in the first embodiment are denoted by the same reference numerals.

The hydraulic crusher 1 has the same configuration as that shown in FIG. 1 in the first embodiment except for the following points.
The turning hydraulic flow path 74 is branched from the opening / closing hydraulic flow path 61 on the fixed bracket 3 side and connected to the port 44A of the delay valve 40, and the check valve 49A which is a pilot operated check valve is connected to the turning hydraulic flow path. It is installed in the road 74. A pilot hydraulic passage 66 is connected from the secondary side of the switching valve 30 to the pilot port of the check valve 49A. A turning hydraulic passage 77 is connected to the hydraulic motor 5 from the port 44 </ b> B of the delay valve 40.

Next, the operation will be described.
First, the case where the hydraulic cylinder 10 is reduced and the crushing arm 6 is opened will be described. First, it is assumed that the delay valve 40 is in a closed state.
Similar to the first embodiment, the switching valve 30 is in the closed position until the hydraulic cylinder 10 is reduced and the piston of the hydraulic cylinder 10 reaches the reduction side stroke end. The pilot hydraulic passage 66 is closed by the check valve 49F, and the hydraulic oil does not flow from the opening / closing hydraulic passage 61 through the pilot hydraulic passage 65 to the pilot hydraulic passage 66.

  When the piston of the hydraulic cylinder 10 reaches the reduction side stroke end, the switching valve 30 is in the open position, and the pilot hydraulic flow path 66 communicates bypassing the check valve 49F. The hydraulic fluid flows from the open / close hydraulic passage 61 through the pilot hydraulic passages 65 and 66 to the pilot port of the check valve 49A, the check valve 49A is opened, and the turning hydraulic passage 74 is communicated. When the turning hydraulic flow path 74 communicates, hydraulic oil flows from the opening / closing hydraulic flow path 61 through the turning hydraulic flow path 74 to the primary side oil chamber 42 and the bypass flow path 78 of the delay valve 40. When the hydraulic oil flows into the primary oil chamber 42 of the delay valve 40, the hydraulic oil in the secondary oil chamber 43 is discharged to the open / close hydraulic flow path 62, and the delay valve 40 is gradually opened.

When the delay valve 40 is in the open state, hydraulic oil flows from the primary oil chamber 42 of the delay valve 40 through the port 44B to the turning hydraulic passage 77, and from the turning hydraulic passage 77 to the hydraulic motor 5, The hydraulic motor 5 rotates and the crusher main body 2 turns. The hydraulic fluid flows from the hydraulic motor 5 to the turning hydraulic passage 75.
The hydraulic oil flowing from the turning hydraulic flow path 74 to the bypass hydraulic flow path 78 becomes surplus oil, and the flow rate of the surplus oil is adjusted by the variable throttle 50A of the bypass hydraulic flow path 78, and at the same time, the delay valve from the turning hydraulic flow path 74 The flow rate of the hydraulic fluid that flows to the hydraulic motor 5 through the hydraulic passage 40 and the turning hydraulic passage 77 is also adjusted, and the turning speed of the crusher body 2 is adjusted.

The hydraulic oil flowing to the hydraulic motor 5 and the surplus oil flowing to the bypass hydraulic flow path 78 are discharged from the turning hydraulic flow path 75 to the open / close hydraulic flow path 62, respectively.
When the crusher body 2 turns, the open / close hydraulic flow paths 61 and 62 are closed, the supply of hydraulic oil to the hydraulic motor 5 is stopped, the rotation of the hydraulic motor 5 is stopped, and the crusher body 2 stops turning. . When the crusher body 2 stops turning, the crusher body 2 is positioned with the arm of the work carriage, the hydraulic cylinder 10 is extended to close the crush arm 6, and the crushing arm 6 crushes the object to be crushed. Perform crushing work.

  When the hydraulic cylinder 10 is extended, as in the first embodiment, the open / close hydraulic flow path 62 becomes the hydraulic oil supply side and becomes high pressure, and the open / close hydraulic flow path 61 becomes the hydraulic oil discharge side. And low pressure. The hydraulic cylinder 10 is extended, the switching valve 30 is switched to the closed position, and the pilot hydraulic flow path 66 is closed by the check valve 49F. The hydraulic oil flows from the high-pressure opening / closing hydraulic flow path 62 to the secondary oil chamber 43 of the delay valve 40, and the piston 41 of the delay valve 40 moves to the primary side oil chamber 42 side end. The hydraulic oil in the primary side oil chamber 42 is discharged to the turning hydraulic passage 74, and the delay valve 40 returns to the closed state. The hydraulic oil discharged from the primary side oil chamber 42 to the turning hydraulic passage 74 flows through the check valve 49A to the low pressure opening / closing hydraulic passage 61.

When the piston 41 of the delay valve 40 starts to move toward the primary oil chamber 42, the port 44B of the delay valve 40 is immediately closed, and the turning hydraulic flow path 77 is closed.
After crushing and crushing the object to be crushed with the crushing arm 6, the hydraulic cylinder 10 is reduced and the crushing arm 6 is opened, and the crusher body 2 is turned as necessary. Perform positioning.

In the hydraulic crusher 1 as described above, the delay valve 40 is actuated after the check valve 49A is switched and the pressure in the hydraulic circuit is reduced, so compared with the first to third embodiments, The pressure acting on the delay valve 40 becomes low, and the device itself can be downsized.
Other operations are the same as those in the first embodiment.
In the first and fourth embodiments, the pilot hydraulic flow path 65 is branched from the open / close hydraulic flow path 62 and connected to the primary side of the switching valve 30, and the crushing arm 6 is closed. If the rod guard 12 sometimes pushes the spool 31 of the switching valve 30 so that the switching valve 30 is in the open position, after crushing the structure to be crushed, the exposed rebar is pinched by the crushing arm 6. It is also possible to turn.

  Further, in the first and fourth embodiments, the rod guard 12 of the hydraulic cylinder 10 pushes the spool 31 of the switching valve 30, but instead, other positions whose positions change according to the state of the crushing arm 6 are used. A configuration may be adopted in which a thing pushes the spool 31. For example, the piston rod of the hydraulic cylinder 10 may be configured to push the spool 31, the crushing arm 6 may be configured to push the spool 31, and the hydraulic cylinder 10 itself that swings according to the operation of the crushing arm 6 may pull the spool 31. It is good also as a structure to push.

  In the second embodiment, the pilot hydraulic flow path 71 is branched from the opening / closing hydraulic flow path 61 and connected to the check valve 49H, and the opening position of the cylinder port 15 in the cylinder tube 14 is defined as the piston 11. If the position reaches the extension side oil chamber 19 when the extension side stroke end is reached, the crusher body 2 can be turned only when the crushing arm 6 is in the closed end.

It is sectional drawing of the hydraulic crusher which concerns on 1st Embodiment. It is a block diagram of the hydraulic circuit of the hydraulic crusher which concerns on 1st Embodiment. It is a block diagram of the hydraulic circuit of the hydraulic crusher which concerns on 2nd Embodiment. It is a block diagram of the hydraulic circuit of the hydraulic crusher which concerns on 3rd Embodiment. It is a block diagram of the hydraulic circuit of the hydraulic crusher which concerns on 4th Embodiment. It is a block diagram of the hydraulic circuit of the conventional hydraulic crusher.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic crusher 2 Crusher body 3 Fixed bracket 4 Swivel wheel 5 Hydraulic motor 6 Crushing arm 10 Hydraulic cylinder 11 Piston of hydraulic cylinder 12 Rod guard 14 Cylinder tube 15 Cylinder port 18 Reduction side oil chamber 19 Extension side oil chamber 20 End plate DESCRIPTION OF SYMBOLS 21 Protrusion part 22 Cushion chamber 23 End plate port 30 Switching valve 31 Switching valve spool 40 Delay valve 41 Delay valve piston 42 Primary side oil chamber 43 Secondary side oil chamber 44A, 44B, 44C, 44D Delay valve port 49A, 49D, 49E, 49F, 49G, 49H, 49J, 49K Check valve 50A, 50B, 50C Variable throttle 53 Brake valve 54A, 54B Swivel 61, 62 Open / close hydraulic flow path 65, 66, 67, 71 Pilot hydraulic flow path 74 , 75, 77 Hydraulic flow path for swiveling 8 bypass hydraulic passage 84 and 85 branch hydraulic passage 88 delay valve channel 89 and 90 branch delay valve channel

Claims (2)

A crushing arm, a crusher body that supports the crushing arm so that the crushing arm can be opened and closed, a fixed bracket that is connected to the arm of the work carriage so that the crushing machine body can pivot, and a hydraulic actuator that is disposed on the crushing machine body and opens and closes the crushing arm And a hydraulic crusher having a hydraulic motor for turning the crusher body,
A hydraulic flow path for opening and closing connected to the hydraulic actuator from the work carriage side;
A turning hydraulic passage branched from the opening and closing hydraulic passage and connected to a hydraulic motor;
A pilot operated check valve that opens and closes by a pilot pressure from the opening and closing hydraulic flow path or a hydraulic actuator and switches communication and closing of the turning hydraulic flow path;
A pilot hydraulic flow path for transmitting the pilot pressure to the pilot operated check valve;
A pilot hydraulic flow path opening / closing means for switching between communication and closing of the pilot hydraulic flow path according to the position of the crushing arm or the hydraulic actuator;
A bypass flow path that branches off from the turning hydraulic flow path, bypasses the hydraulic motor, rejoins the turning hydraulic flow path, and is provided with a variable throttle;
Have a, a delay means for the pilot hydraulic passage gives a delay time from the communication until the hydraulic motor is rotated,
When the pilot operation check valve is opened and the turning hydraulic flow path communicates, the hydraulic oil supplied from the work carriage side opens and closes among the hydraulic actuator, the open / close hydraulic flow path, and the pilot hydraulic flow path. A hydraulic crusher that flows from only the hydraulic flow path to the hydraulic motor through the turning hydraulic flow path .   2. The hydraulic crusher according to claim 1, wherein the pilot hydraulic flow path opening / closing means is provided in a hydraulic actuator.

Images