JP4943119B2 - 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.

  The method of turning the crusher main body is roughly divided into a turning type and a hydraulic turning type. In the contact-type hydraulic crusher, a plurality of conical holes are provided in the swirling wheel of the crusher body, and a steel ball mounted on a fixed bracket is urged by a spring and is seated in each conical hole. is there. By applying a force greater than the braking force acting on the steel ball from the spring, each steel ball is moved to the adjacent conical hole and applied to the crusher body. In such a contact type, the steel ball and the conical hole that contacts the steel ball are worn. Compared with the swivel type, the hydraulic swivel type is very easy to swivel, has no worn parts such as steel balls, and is easy to maintain. For this reason, there is a high need for a hydraulic swivel type. 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 connected to a hydraulic cylinder 115 that opens and closes the crushing arm. Yes. 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 116 branches off from the opening hydraulic flow path 112 and is connected to the hydraulic motor 110. The branch pipe 116 is provided with a relief valve 120, and an opening operation delay means 118 is provided between the relief valve 120 and the hydraulic motor 110. A branch pipe 117 branches from the closing hydraulic flow path 113 and is connected to the hydraulic motor 110. The branch pipe 117 is provided with a check valve 119 that prevents hydraulic fluid from flowing into the hydraulic motor 110 from the closing hydraulic flow path 113.

  In this hydraulic crusher, the opening hydraulic flow path 112 does not rise to a predetermined pressure during the opening operation of the crushing arm, the relief valve 120 is closed, and the branch pipe 116 is not in communication with the hydraulic motor 110. When the crushing arm becomes an open end and the pressure of the opening hydraulic flow path 112 rises to a predetermined pressure, the relief valve 120 opens. After the relief valve 120 is opened, the opening operation delay means 118 is opened with a delay, the branch pipe 116 communicates with the hydraulic motor 110, the hydraulic oil flows from the opening hydraulic flow path 112 to the hydraulic motor 110, and the main body of the crusher is Turn. Therefore, the crusher main body can be turned after the crushing arm has been opened and the crusher main body is prevented from turning during the crushing operation. Also, after the crushing arm opens and ends, the crusher body turns if the operation is continued for a certain period of time, so there is no need to operate a new lever or the like to turn the crusher body, making it easy to use. .

Normally, the opening hydraulic flow path 112 and the closing hydraulic flow path 113 are not equipped with pressure gauges, and the operator turns the crusher body after visually recognizing that the crushing arm is open. If necessary, turn the crusher body as necessary.
Further, when the turning of the crusher body is stopped, the opening hydraulic flow path 112 and the closing hydraulic flow path 113 are closed, and the flow of hydraulic oil to the hydraulic motor 110 is cut off. When the flow of hydraulic oil to the hydraulic motor 110 is cut off, the rotation of the hydraulic motor 110 stops and the turning of the crusher main body also stops.
JP 2001-116005 A

However, in the hydraulic crusher having the above-described hydraulic circuit, there is a possibility that the crusher body turns even when the operator does not intend to turn the crusher body.
For example, when a structure such as a building is dismantled, the hydraulic crusher often enters the structure to be crushed while performing a crushing operation with the hydraulic crusher. For this reason, the crushing operation is performed in a narrow space in the structure to be crushed.

  In order to improve work efficiency, the operator may position the next crushing operation during the opening operation of the crushing arm, and may open the crushing arm in a narrow space in the structure to be crushed. At this time, the crushing arm during the opening operation tends to come into contact with surrounding crushing objects, and resistance is easily added to the opening operation of the crushing arm. In order to ensure the strength, the diameter of the rod of the hydraulic cylinder 115 is large, and the pressure receiving area of the hydraulic cylinder 115 during the opening operation of the crushing arm is small. Therefore, when resistance is applied to the opening operation of the crushing arm, the pressure in the opening hydraulic flow path 112 immediately rises to reach a predetermined pressure, the relief valve 120 is opened, and then the opening operation delay means 118 is also opened, and the branch pipe 116 is opened. Communicates with the hydraulic motor 110. For this reason, the hydraulic motor 110 rotates and the crusher body turns. Since the opening hydraulic flow path 112 and the closing hydraulic flow path 113 are not equipped with pressure gauges, a series of circuit switching accompanying the operation of each part described above proceeds without the operator's knowledge. The turning of the crusher body that occurs during the opening operation of the crushing arm is a sudden one that is not intended by the operator, and has a considerable influence on the work efficiency. Moreover, sudden turning of the crusher body causes a fall of crushing glass and collapse of a crushing object, which is a serious safety problem.

Accordingly, there is a problem in work safety and efficiency in switching the closing and communication of the branch pipe 116 by opening and closing the opening operation delay means 118 using the pressure of the opening hydraulic flow path 112.
Further, when the pressure of the opening hydraulic flow path 112 rises because the relief valve 120 is opened, the addition of the hydraulic pump of the work carriage increases and the hydraulic equipment that is configured is consumed.
The operator can swivel the crusher body only when the crushing arm opens and ends, except when the crushing arm contacts the obstacle during the opening operation and turns suddenly. As a result, work efficiency may be reduced. For example, even if the object to be crushed becomes smaller due to changes in the work site and it is not necessary to open the crushing arm to the end, when turning the crusher body, open the crushing arm each time it turns. Must be opened, resulting in wasted time and reduced work efficiency.

  The present invention solves the above-mentioned problems, and the purpose of the present invention is to prevent the crusher body from turning only when the operator intends, and to prevent the crusher body from turning unintentionally by the operator. It is to provide a hydraulic crusher with improved reliability, work efficiency and hydraulic oil circulation efficiency.

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 to turn the crusher body,
A hydraulic flow path for opening and closing connected to the hydraulic actuator from the work carriage side;
A turning hydraulic flow path connected to the hydraulic motor from the hydraulic actuator;
A turning hydraulic flow path opening / closing means for switching between communication and closing of the turning hydraulic flow path according to the position of the crushing arm or the hydraulic actuator;
Delay means for giving a delay time from when the turning hydraulic flow path communicates until the hydraulic motor rotates;
A bypass flow path that branches off from the turning hydraulic flow path and bypasses the hydraulic motor and the delay means to join the turning hydraulic flow path;
A throttle provided in the bypass flow path, and the turning hydraulic flow path opening / closing means is provided in the hydraulic actuator.

  According to the first aspect of the present invention, communication and closing of the turning hydraulic flow path are switched according to the position of the crushing arm or the opening / closing hydraulic actuator, and only when the crushing arm or the opening / closing hydraulic actuator is in a predetermined position. The crusher body turns. If the crushing arm or the opening / closing hydraulic actuator is not in a predetermined position, the crusher body does not turn. Therefore, the operator can easily recognize whether or not the crusher body can be turned, and the crusher body can be prevented from turning suddenly. Further, the operator can determine whether or not to rotate the crusher body within the delay time given by the delay means.

Since the hydraulic actuator has the turning hydraulic flow path opening / closing means, the number of necessary parts is reduced, the degree of freedom in arranging parts is improved, and the cost is reduced.
The hydraulic oil flowing to the hydraulic motor is adjusted to the optimum flow rate and pressure for the hydraulic motor operation by the bypass flow path, and the pressure of the entire hydraulic circuit is kept low.
When stopping the turning of the crusher body, the operator closes the open / close hydraulic flow path. When the open / close hydraulic flow path is closed, the hydraulic oil in the turning hydraulic flow path upstream of the hydraulic motor flows through the bypass flow path to the low-pressure turning hydraulic flow path and does not flow into the hydraulic motor. Therefore, when the operator closes the open / close hydraulic flow path, the rotation of the hydraulic motor is immediately stopped, and the turning of the crusher body is also immediately stopped, so that excellent operation reactivity can be obtained.

A hydraulic crusher according to a second aspect of the present invention is the hydraulic crusher according to the first aspect, wherein the turning hydraulic flow path between the junction where the bypass flow path joins the turning hydraulic flow path and the hydraulic motor Has a relief valve.
According to the invention of claim 2, if the relief valve is opened while the crusher body is turning, the hydraulic oil flows to the hydraulic motor and the hydraulic motor continues to rotate. When stopping the turning of the crusher body, if the relief valve is closed, the hydraulic oil does not flow to the hydraulic motor, the rotation of the hydraulic motor is stopped, and the turning of the crusher body is also stopped.

The hydraulic crusher according to the invention of claim 3 includes a crushing arm, a crusher body that supports the crushing arm so as to be openable and closable, 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 to turn the crusher body,
A hydraulic flow path for opening and closing connected to the hydraulic actuator from the work carriage side;
A turning hydraulic flow path connected to the hydraulic motor from the hydraulic actuator;
A turning hydraulic flow path opening / closing means for switching between communication and closing of the turning hydraulic flow path according to the position of the crushing arm or the hydraulic actuator;
Delay means for giving a delay time from when the turning hydraulic flow path communicates until the hydraulic motor rotates;
A bypass passage that branches off from the turning hydraulic passage, bypasses the hydraulic motor, and joins the turning hydraulic passage;
A pilot operated check valve that is provided in the bypass flow path and opens and closes with the pressure of the hydraulic flow path for turning downstream of the hydraulic motor as a pilot pressure;
And a variable throttle provided in a turning hydraulic passage on the upstream side of the hydraulic motor.

  According to the invention of claim 3, when stopping the turning of the crusher body, the operator closes the open / close hydraulic flow path. When the open / close hydraulic flow path is closed, the hydraulic oil in the turning hydraulic flow path on the downstream side of the hydraulic motor loses its place, and the pressure in the turning hydraulic flow path on the downstream side of the hydraulic motor instantaneously increases. This increase in pressure opens the pilot check valve in the bypass flow path. The high-pressure hydraulic oil left in the turning hydraulic passage upstream of the hydraulic motor flows from the bypass passage to the low-pressure turning hydraulic passage and does not flow to the hydraulic motor. Therefore, when the operator closes the open / close hydraulic flow path, the rotation of the hydraulic motor is immediately stopped, and the turning of the crusher body is also immediately stopped, so that excellent operation reactivity can be obtained.

  Since the present invention is a hydraulic crusher as described above, the crusher body turns only when the operator intends to prevent the crusher body from turning unintended by the operator. It has excellent reactivity, improving work efficiency and hydraulic oil circulation efficiency.

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 80 and 81 are connected to the hydraulic cylinder 10 from the work carriage through the swivel 77. When the hydraulic cylinder 10 is contracted, the open / close hydraulic flow path 80 becomes the hydraulic oil supply side, and the open / close hydraulic flow path 81 becomes the hydraulic oil discharge side, and when the hydraulic cylinder 10 extends, the open / close hydraulic flow path 81 operates. The oil supply side serves as an oil supply side, and the open / close hydraulic flow path 80 serves as a hydraulic oil discharge side.

The configuration of the hydraulic crusher 1 described so far is hereinafter referred to as a basic configuration.
A cylinder port 15 is formed in the cylinder tube 14 of the hydraulic cylinder 10, and the cylinder port 15 serves as a turning 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. A plurality of piston seals are attached to the piston 11. FIG. 2 shows a state where the cylinder port 15 communicates with the reduction-side oil chamber 18.

The open / close hydraulic flow path 80 is connected to the reduction-side oil chamber 18 of the hydraulic cylinder 10, and the open / close hydraulic flow path 81 is connected to the expansion-side oil chamber 19 of the hydraulic cylinder 10.
A turning hydraulic flow path 90 is connected from the cylinder port 15 to the pilot operated check valve 67, and a turning hydraulic flow path 91 is connected from the pilot operated check valve 67 to the port 44 of the delay valve 40 described later. The direction of the pilot operated check valve 67 is a direction in which the hydraulic oil flows from the cylinder port 15 to the delay valve 40. The pilot ratio of the pilot operation check valve 67 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 pilot operation check valve 67 passes through the pilot operation check valve 67. Appropriate values have been selected to allow passage.

The branch hydraulic flow path 84 branches from the turning hydraulic flow path 91 and is connected to the open / close hydraulic flow path 80, and the check valve 64 is installed in the branch hydraulic flow path 84. The direction of the check valve 64 is a direction in which hydraulic fluid flows from the turning hydraulic passage 91 to the opening / closing hydraulic passage 80.
The delay valve 40 is a cavity-type delay valve that constitutes a delay means and includes a piston 41, a primary oil chamber 42, a secondary oil chamber 43, and ports 44, 45, 46, and 47. The primary oil chamber 42 and the secondary oil chamber 43 are on both sides of the piston 41, the port 44 is formed at the primary oil chamber 42 side end, and the ports 46 and 47 are formed at the secondary oil chamber 43 side end. The port 45 is formed at a position slightly closer to the primary oil chamber 42 than the center. When the piston 41 moves to the end of the secondary oil chamber 43, the port 45 opens and the delay valve 40 opens, and when the piston 41 moves toward the primary oil chamber 42, the port 45 closes and the delay valve 40 opens. It becomes the structure which will be in a closed state.

A turning hydraulic flow path 92 is connected to the hydraulic motor 5 from the port 45 of the delay valve 40.
The hydraulic motor 5 has a general brake valve 75 in case of overload or turning.
The turning hydraulic flow path 93 is connected from the hydraulic motor 5 to the opening / closing hydraulic flow path 81 on the fixed bracket 3 side, and the check valve 61 is installed in the turning hydraulic flow path 93. The direction of the check valve 61 is a direction in which hydraulic fluid flows from the hydraulic motor 5 to the turning hydraulic flow path 81.

The delay valve channel 95 branches off from the opening / closing hydraulic channel 81 on the fixed bracket 3 side. The delay valve channel 95 is divided into branch delay valve channels 97 and 98, and the branch delay valve channels 97 and 98 are connected to the ports 46 and 47 of the delay valve 40. The variable throttle 51 is installed in the branch delay valve channel 97, and the check valve 62 is installed in the branch delay valve channel 98. The direction of the check valve 62 is a direction in which hydraulic fluid flows from the delay valve flow path 95 to the delay valve 40.
In addition to the branch hydraulic flow path 84, a bypass flow path 87 branches from the turning hydraulic flow path 91. The bypass passage 87 is connected to the turning hydraulic passage 93. A junction 88 where the bypass passage 87 joins the turning hydraulic passage 93 is between the hydraulic motor 5 and the check valve 61. A restriction 53 is installed in the bypass flow path 87.

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 80 becomes low pressure on the hydraulic oil discharge side, the open / close hydraulic flow path 81 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 is in communication with the reduction-side oil chamber 18, the pilot operation check valve 67 is closed with the extension side hydraulic pressure of the open / close hydraulic flow path 81 as the pilot pressure. While the cylinder port 15 is in communication with the extension side oil chamber 19, the pilot operated check valve 67 is closed with the self pressure as the pilot pressure. Therefore, while the hydraulic cylinder 10 is extended, the pilot operation check valve 67 is closed, and hydraulic oil does not flow from the turning hydraulic flow path 90 to the turning hydraulic flow path 91.

The hydraulic oil flows from the opening / closing hydraulic flow path 81 through the delay valve flow path 95 and the branch delay valve flow paths 97 and 98 to the secondary side oil chamber 43 of the delay valve 40, and the piston 41 of the delay valve 40 moves to be primary. The hydraulic oil in the side oil chamber 42 is discharged to the low-pressure turning hydraulic passage 91 through the turning hydraulic passage 91 and the branch hydraulic passage 84, and the delay valve 40 is closed.
When the crushing arm 6 is closed, the open / close hydraulic flow path 80 becomes the hydraulic oil supply side and becomes high pressure, the open / close hydraulic flow path 81 becomes the hydraulic oil discharge side and becomes low pressure, and the hydraulic cylinder 10 becomes 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 pilot operation check valve 67 closes with the self pressure, that is, the back pressure of the hydraulic oil discharged to the open / close hydraulic flow path 81 as the pilot pressure. Yes. 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 turning hydraulic passage 90. The pressure of the hydraulic fluid that flows from the reduction side oil chamber 18 through the turning hydraulic passage 90 to the pilot operated check valve 67 is much larger than the pilot pressure that has closed the pilot operated check valve 67 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 pilot check valve 67 opens, and the turning hydraulic flow path 90, the turning hydraulic flow path 91, And hydraulic oil flows from the turning hydraulic passage 90 to the turning hydraulic passage 91.

The hydraulic oil flows from the turning hydraulic flow path 91 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 97 and the delay valve flow path 95. As a result, the delay valve 40 is gradually opened.
A part of the hydraulic oil flowing through the turning hydraulic passage 91 also flows into the bypass passage 87. The restrictor 53 restricts the hydraulic oil flowing through the bypass flow path 87 to control the flow rate and pressure, and controls the flow rate and pressure of the hydraulic oil flowing to the hydraulic motor 5 through the turning hydraulic flow paths 90, 91, 92. . Therefore, the hydraulic oil flowing to the hydraulic motor 5 by the bypass flow path 87 is adjusted to a flow rate and pressure optimal for the operation of the hydraulic motor 5, and the pressure of the entire hydraulic circuit is kept low.

When the delay valve 40 is in the open state, hydraulic oil flows from the primary side oil chamber 42 through the turning hydraulic passage 92 to the hydraulic motor 5, and the hydraulic motor 5 rotates to turn the crusher body 2. Then, the hydraulic oil flows from the hydraulic motor 5 through the turning hydraulic passage 93 to the opening / closing hydraulic passage 80.
When the crusher main body 2 is turned by a required amount, the opening and closing hydraulic flow paths 80 and 81 are closed, the supply of hydraulic oil to the hydraulic motor 5 is stopped, and the crusher main body 2 stops turning. High-pressure hydraulic oil is left in the turning hydraulic passages 90 and 91, the primary side oil chamber 42 of the delay valve 40, and the turning hydraulic passage 92. The remaining high-pressure hydraulic fluid flows from the bypass passage 87 through the turning hydraulic passage 93 to the low-pressure opening / closing hydraulic passage 81 and does not flow to the hydraulic motor 5. Therefore, when the operator closes the opening and closing hydraulic flow paths 80 and 81, the rotation of the hydraulic motor 5 is immediately stopped, and the turning of the crusher body 2 is also immediately stopped, so that excellent operation reactivity is obtained.

When the turning of the crusher body 2 is stopped, the crusher body 2 is positioned with the arm of the work carriage, and then the crushing arm 6 is closed.
Since the hydraulic crusher 1 is as described above, the crusher main body 2 turns only when the crushing arm 6 is in the open end.
Due to the positional relationship between the piston 11 and the cylinder port 15, the turning hydraulic flow path 91 is closed or communicated, so that the crusher main body 2 is prevented from turning suddenly, and the crusher main body 2 turns only when the operator intends. In addition, the safety and certainty of the hydraulic crusher 1 are excellent.

A delay time is generated by the delay valve 40, and the operator can determine whether or not the crusher body 2 is turned within this delay time.
Since the hydraulic cylinder 10 has the cylinder port 15 as the turning 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.
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 configuration as that of the first embodiment except for the following points.
In the turning hydraulic passage 93, a relief valve 76 is installed between the hydraulic motor 5 and the junction 88. The relief valve 76 is configured to be opened by the pressure of the turning hydraulic passage 93 between the hydraulic motor 5 and the relief valve 76.

Next, the operation will be described.
The hydraulic crusher 1 has the following actions in addition to the actions of the first embodiment.
When the pilot operation check valve 67 is opened, the delay valve 40 is gradually opened, and the hydraulic oil flows from the delay valve 40 to the turning hydraulic passage 92, the hydraulic oil flows from the turning hydraulic passage 92 to the hydraulic motor 5. And flows into the turning hydraulic passage 93. The hydraulic oil flows into the turning hydraulic passage 93, the pressure of the turning hydraulic passage 93 between the hydraulic motor 5 and the relief valve 76 rises, and the relief valve 76 opens. The relief valve 76 is opened, and the hydraulic oil exiting the hydraulic motor 5 flows from the turning hydraulic flow path 93 to the opening / closing hydraulic flow path 81. The hydraulic motor 5 is rotated by hydraulic oil passing through the hydraulic motor 5, and the crusher body 2 is turned.

  When the crusher body 2 turns by a necessary amount, the opening and closing hydraulic flow paths 80 and 81 are closed, and the supply of hydraulic oil to the hydraulic motor 5 is cut off. The amount of hydraulic fluid flowing from the hydraulic motor 5 to the turning hydraulic passage 93 decreases, the pressure of the turning hydraulic passage 93 between the hydraulic motor 5 and the relief valve 76 decreases, and the relief valve 76 closes. When the relief valve 76 is closed, the flow of hydraulic oil through the hydraulic motor 5 is completely stopped. Therefore, after closing the opening and closing hydraulic flow paths 80 and 81, it is completely prevented that the hydraulic motor 5 rotates and the crusher main body 2 continues to turn, and the operation reactivity is improved.

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 configuration as that of the first embodiment except for the following points.
A variable throttle 50 is installed in the turning hydraulic flow path 92 between the port 45 of the delay valve 40 and the hydraulic motor 5. A throttle is not installed in the bypass channel 87, and a pilot operation check valve 69 is installed. A pilot line 72 branches off from a junction 88 between the bypass flow path 87 and the turning hydraulic flow path 93 and is connected to a pilot port of a pilot operation check valve 69. When the pilot operation check valve 69 is opened by the pilot pressure in the pilot line 72, the hydraulic fluid flows from the turning hydraulic passage 91 to the turning hydraulic passage 93 through the bypass passage 87.
The pilot ratio of the pilot operated check valve 69 is a value at which the pilot operated check valve 69 is not opened by the pressure of the turning hydraulic flow path 93 at the junction 88 while the operator performs the turning operation of the crusher body 2. Is set to

Next, the operation will be described.
The hydraulic crusher 1 has the following actions in addition to the actions of the first embodiment.
While the operator performs the turning operation of the crusher body 2, the pilot check valve 69 is closed, and the hydraulic oil does not flow from the turning hydraulic flow path 91 to the bypass flow path 87. The turning speed of the crusher body 2 is adjusted by adjusting the flow rate of the hydraulic fluid flowing from the turning hydraulic flow paths 91 and 92 to the hydraulic motor 5 by the variable throttle 50. Then, the hydraulic oil flows from the hydraulic motor 5 through the turning hydraulic passage 93 to the opening / closing hydraulic passage 81.

  When the crusher body 2 turns by a necessary amount, the opening and closing hydraulic flow paths 80 and 81 are closed, and the supply of hydraulic oil flowing to the hydraulic motor 5 is cut off. When the opening / closing hydraulic flow path 80 is closed, high-pressure hydraulic oil is left in the turning hydraulic flow paths 92, 91, 90 on the upstream side of the hydraulic motor 5. When the opening / closing hydraulic flow path 81 is closed, the hydraulic oil in the turning hydraulic flow path 93 on the downstream side of the hydraulic motor 5 loses its place, and the pressure in the turning hydraulic flow path 93 increases instantaneously. Due to this pressure increase, the pilot pressure in the pilot line 72 increases, the pilot operation check valve 69 opens, and the bypass flow path 87 communicates. When the bypass passage 87 communicates, the high-pressure hydraulic fluid in the turning hydraulic passages 92, 91, 90 flows from the bypass passage 87 through the turning hydraulic passage 93 to the low-pressure opening / closing hydraulic passage 81, It does not flow to the hydraulic motor 5. Therefore, when the opening and closing hydraulic flow paths 80 and 81 are closed, the rotation of the hydraulic motor 5 is immediately stopped, and the turning of the crusher body 2 is also immediately stopped, so that excellent operation reactivity can be obtained.

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 conventional hydraulic crusher.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic crusher 2 Crusher main body 3 Fixed bracket 4 Swivel wheel 5 Hydraulic motor 6 Crushing arm 10 Hydraulic cylinder 11 Piston of hydraulic cylinder 14 Cylinder tube 15 Cylinder port 18 Reduction side oil chamber 19 Extension side oil chamber 40 Delay valve 41 Delay valve Piston 42 Primary side oil chamber 43 Secondary side oil chamber 44, 45, 46, 47 Delay valve port 50, 51 Variable throttle 53 Throttle 61, 62, 64 Check valve 67, 69 Pilot operated check valve 70, 72 Pilot line 75 Brake valve 76 Relief valve 77, 78 Swivel 80, 81 Opening / closing hydraulic flow path 84 Branching hydraulic flow path 87 Bypass flow path 88 Confluence 90, 91, 92, 93 Turning hydraulic flow path 95 Delay valve flow path 97 , 98 Branch delay valve flow path

Claims (3)

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 flow path connected to the hydraulic motor from the hydraulic actuator;
A turning hydraulic flow path opening / closing means for switching between communication and closing of the turning hydraulic flow path according to the position of the crushing arm or the hydraulic actuator;
Delay means for giving a delay time from when the turning hydraulic flow path communicates until the hydraulic motor rotates;
A bypass flow path that branches off from the turning hydraulic flow path and bypasses the hydraulic motor and the delay means to join the turning hydraulic flow path;
A throttle provided in the bypass flow path,
A hydraulic crusher, wherein the turning hydraulic flow path opening / closing means is provided in a hydraulic actuator.   2. The hydraulic crusher according to claim 1, further comprising a relief valve provided in a turning hydraulic flow path between a joining point where the bypass flow path joins the turning hydraulic flow path and the hydraulic motor. 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 flow path connected to the hydraulic motor from the hydraulic actuator;
A turning hydraulic flow path opening / closing means for switching between communication and closing of the turning hydraulic flow path according to the position of the crushing arm or the hydraulic actuator;
Delay means for giving a delay time from when the turning hydraulic flow path communicates until the hydraulic motor rotates;
A bypass passage that branches off from the turning hydraulic passage, bypasses the hydraulic motor, and joins the turning hydraulic passage;
A pilot operated check valve that is provided in the bypass flow path and opens and closes with the pressure of the hydraulic flow path for turning downstream of the hydraulic motor as a pilot pressure;
A hydraulic crusher comprising: a variable throttle provided in a turning hydraulic flow path upstream of the hydraulic motor.

Images