KR100283001B1 - Speed increase valve for crusher - Google Patents

Abstract

The present invention provides an increaser valve for a shredder that prevents unexpected operation of the cylinder due to leakage and pressure generation in the main control valve of the excavator as well as reducing pressure loss in the valve.

The speed increasing valve includes a first port P1 and a second port P2 connected to the supply or discharge side of the hydraulic oil, and a first cylinder port CP1 and a second cylinder port CP2 connected to the cylinder shaft. A sleeve 14 and a sleeve reciprocated in the sleeve, the first port (P1) is opposed to the first cylinder port (CP1) and the second port (P2) is the second cylinder port (CP2) And an initial mode flow path section in which at least one of the opposing ports is closed, and the first and second cylinder ports CP1 and CP2 communicate with each other and the first and second ports P1. And a spool 16 forming a speed increase mode flow path section communicating with at least one of the ports P2, and a normal mode flow path section in which each of the opposing ports P1-CP1 and P2-CP2 communicate with each other; Pilot pipes PV1 and PV2 installed on one side of the spool and communicating with the first and second ports P1 and P2, respectively. Spool switching means for switching the spool 16 in accordance with the pressure applied by the force) and pressurizing means for providing a reaction force to the movement of the spool on the opposite side of the spool switching means.

Description

Speed increase valve for crusher

The present invention relates to a speed increase valve, and more particularly, to a speed increase valve for a shredder that prevents unexpected operation of a cylinder due to leakage and pressure generation at the main control valve of an excavator, as well as reducing pressure loss in the valve. .

In general, a variety of heavy equipment is used in the construction site or civil engineering site, and among these heavy equipment is a heavy equipment called an excavator for crushing obstacles, such as rock on the construction site or existing concrete structures, or to work in the pit . Such an excavator is provided with a crusher for supplying a power source such as hydraulic pressure from the excavator and operated by the hydraulic pressure to actually crush the obstacles. Jaw crushers, which have the advantage of being easy to exchange and having a high grinding ratio, are widely used. The jaw crusher is equipped with two tooth plates facing each other at a constant angle, one of which is fixed and the other one is configured to reciprocate by the eccentric motion of the main shaft with the upper or lower support point as the support point. In the mode in which the crushed material is interposed between the tooth plates, when one tooth plate is advanced with respect to the other tooth plate, it is compressed and crushed, and when it is retracted, the crushed material is discharged.

In order to advance and retract the tooth plate, the crusher is provided with an acceleration valve or a speed increase valve AV as schematically shown in FIG. 1. The speed increasing valve AV is disposed between the main control valve M of the excavator (not shown) and the cylinder C for actually operating the jaw or the tooth plate of the crusher by receiving hydraulic pressure from the main control valve M of the excavator. have. Referring to the operation of the crusher having such a speed increase valve, the main control valve M in the initial mode shown in Figure 1 through the first port (P1) to one side of the speed increase valve (AV), that is, the cylinder When the hydraulic oil is supplied to the large diameter chamber through the first cylinder port CP1, the driving rod R installed in the cylinder so as to be reciprocated moves in the forward direction as indicated by the arrow A1, and at the same time the small diameter of the cylinder C Since the residual pressure oil of the seal is discharged through the second cylinder port CP2 and flows through the speed increase valve AV to the large diameter chamber, the pressure oil discharged from the small diameter chamber is added in addition to the existing hydraulic pressure flowing to the large diameter chamber, thereby driving the driving rod R. It is to be accelerated.

At this time or afterwards, when a load is applied to the driving rod R, the pilot pressure at the first port P1 of the main control valve M increases, and when the pilot pressure continues to rise and becomes higher than the set pressure, the speed increasing valve The operation of the driving rod R also returns to the normal mode from the speed increase mode as the AV is converted to the normal mode. In this mode, the hydraulic oil flows to the speed increasing valve AV through the second port P2 by the operation of the main control valve M, but since the speed increasing valve maintains the closed mode, the second port P2 The pilot pressure is increased, and when the pilot pressure at the second port P2 continues to rise and becomes higher than the set pressure, the speed increase valve AV is switched. Accordingly, the second cylinder port CP2 is changed. The oil will flow into the small diameter chamber. At this time, the flow pressure of the hydraulic oil is maintained at a value very lower than the set pilot pressure of the first port P1 of the main control valve M, so that in the case of reversing in the direction of the arrow A2 of the drive rod R, the speed increases It does not go into mode. As a result, the speed increase valve AV enters the speed increase mode only in the forward operation of the driving rod R. FIG.

The configuration of the speed increase valve AV and its operation mode will be described in more detail with reference to FIG. 2. This speed increase valve AV is each of the 1st port P1 and the 2nd port P2 of the main control valve M of the excavator shown in FIG. 1, and each 1st cylinder port CP1 of the cylinder, and The second cylinder port CP2 includes a valve block B which communicates with each other. Inside the valve block B, a sleeve 1 communicates with the respective ports is provided, and the sleeve 1 The spool 2, which is reciprocated by the respective ports, is built in the inner side. In addition, the bush 3 is provided in contact with one side of the sleeve 1, and the piston 4 is provided in the inside of the bush 3 so as to reciprocate. The piston 4 is connected to one side of the spool 2 by the roller 5. A spacer 6 is formed on the other side of the sleeve 1, and inside the spacer 6, a spring seat 7 is connected to the other side of the spool 2 and the spring 8 is elastically supported. Is installed. Of course, each component installed inside the valve block B is protected and closed by a plug 9 which is releasably fastened to both sides thereof.

Referring to the operation of the speed increase valve configured as described above, when the hydraulic oil is supplied through the first port P1 by the main control valve as described above, the spool 2 is moved so that the left side of the bush 3 is moved. By contacting the right side, the first port P1, the first cylinder port CP1, and the second cylinder port CP2 communicate with each other to form a speed increasing mode. Thereafter, the first pilot pipe line PV1 communicates with the first cylinder port CP1, and when the pressure of the first cylinder port CP1 rises, the roller 5 moves to the right. When the spool 2 is moved to the right and is switched, the speed increase valve is in a release mode. In addition, the second pilot pipe (PV2) is connected to the second port (P2) when the pressure of the second port (P2) is above the set pressure to push the piston (4) to the right to operate the valve in normal mode. Will be done. At this time, since the diameter of the piston 4 is larger than the diameter of the roller 5, the spool 2 can be switched even at a pressure lower than the pressure of the first pilot valve PV1. Of course, the spring seat 7 serves to cause cracking when the preload is set by the spring 8 provided thereon so that a pressure greater than a certain pressure is applied to the spring seat, and the spool 2 The pipe line formed inside of) serves to drain the pressure oil between the spool 2 and the bush 3 to prevent the generation of resistance when the spool is switched.

However, in the conventional speed increase valve configured as described above, one problem inevitably occurs. That is, since the speed increase mode of the speed increase valve maintains the mode in which the first port, the first cylinder port, and the second cylinder port communicate with each other, leakage of oil from the main control valve of the excavator, which is a phenomenon that is inevitable in the excavator, is observed. Due to the generation and pressure generation, there is a problem in that unwanted driving of the driving rod is caused by the pressure difference area between the large diameter chamber and the small diameter chamber of the cylinder.

Accordingly, the present invention has been made to solve the above problems, an object of the present invention is to provide a speed increase valve for a shredder that can prevent the cylinder rod is operated even if leakage and pressure build-up occurs in the main control valve of the excavator It is.

1 is a hydraulic circuit diagram of a speed increase valve for a general crusher.

2 is a cross-sectional view showing the configuration of the speed increase valve of FIG.

3 is a hydraulic circuit diagram of a speed increase valve for a crusher according to the present invention.

4 is a cross-sectional view showing the configuration of the speed increase valve of FIG.

♣ Explanation of symbols for the main parts of the drawing ♣

10: speed increasing valve 12: valve block

14: sleeve 16: spool

18: bush 20: piston

22: roller 23: spacer

24: spring seat 26: first spring

28: second spring C: cylinder

CP1, CP2: Cylinder port M: Main control valve

P1, P2: port

The purpose of the present invention is to provide a speed increase valve for increasing a drive rod installed reciprocally in a cylinder, the first port and the second port being built into the valve block and connected to the supply or discharge side of the hydraulic oil, and connected to the cylinder side. A sleeve having a first cylinder port and a second cylinder port, and reciprocally mounted in the sleeve, the first port facing the first cylinder port and the second port facing the second cylinder port An initial mode flow path section in which at least one of the opposing ports is closed, and an acceleration in which the first and second cylinder ports communicate with each other and with at least one of the first and second ports A spool forming a mode flow path section and a normal mode flow path section in which each of the opposing ports communicate with each other; Spool switching means for switching the spool according to the pressure applied by the pilot pipe communicating with the first and second ports, respectively, and pressurizing means for providing a reaction force to the movement of the spool opposite the spool switching means. It can be achieved by the speed increase valve for the crusher.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

3 is a hydraulic circuit diagram illustrating an installation state and a connection structure of a speed increaser valve for a crusher according to the present invention, and FIG. 4 is a cross-sectional view showing the configuration of the speed increase valve according to the present invention in detail. It is to be understood that directional terms such as left, right, etc., as set forth herein are set in fragments in the figures, and such directional terms may be different in practical application.

First, in FIG. 3, the speed increase valve 10 according to the present invention basically receives hydraulic pressure from the main control valve M and the main control valve M of the excavator to operate the driving rod R therein. Are arranged between the cylinders C, and the speed increase valve 10 is connected to the first port P1 and the second port P2 of the main control valve M, It is connected to the first cylinder port CP1 and the second cylinder port CP2.

The configuration of the speed increase valve according to the present invention will be described in detail with reference to FIG. 4. The speed increase valve 10 according to the present invention basically includes a valve block 12, and the valve block 12 is supplied with pressure oil. Alternatively, the sleeve 14 includes a first port P1 and a second port P2 connected to the discharge side, and a first cylinder port CP1 and a second cylinder port CP2 connected to the cylinder C side. It is installed.

In particular, the sleeve 14 is formed with two flow paths 14a and 14b communicating with the second cylinder port CP2, and the spool 16 is built in the inside thereof. The first port P1 faces the first cylinder port CP1, and the second port P2 faces the second cylinder port CP2, but at least one of the opposing ports is closed. An acceleration mode flow path section in which the initial mode flow path section and the first and second cylinder ports CP1 and CP2 communicate with each other and in communication with at least one of the first and second ports P1 and P2; Each of the ports P1-CP1 and P2-CP2 is configured to form a normal mode flow path in communication with each other. In the spool 16, of course, a conduit line 16a shown in dotted line is formed, and one side of the sleeve 14 is provided with a bush 18 in contact.

In addition, the two flow paths 14a and 14b communicating with the second cylinder port CP2 of the sleeve 14 are formed in the first port P1 and the first cylinder port when the spool 16 is in the increased flow path section. When CP1 and the first channel 14a communicate with each other, the second channel 14b is closed, and when the spool 16 is in the normal channel section, the second port P2 and the second channel 14b mutually In communication with the first passage 14a is preferably formed to be closed.

In addition, the inner side of the bush 18 is installed on one side of the spool 16 and in accordance with the pressure applied by the pilot pipe lines PV1 and PV2 communicating with the first and second ports P1 and P2, respectively. Spool switching means for switching the spool 16 is provided. In more detail, the spool switching means is a piston for pressing the spool 16 to one side according to the application of the pressure of the second pilot pipe (PV2) in communication with either one of the first and second ports (P1, P2). And the pressure of the second pilot pipe line PV1 interposed between the piston 20 and the spool 16 and communicating with either one of the first and second ports P1 and P2. It includes a roller 22 for pressing the spool 16 to one side.

Here, the piston 20 receives pressure from the pilot pipe line PV2 communicating with the second port P2, and the roller 22 communicates with the first pilot pipe line PV1 communicating with the first port P1. It is preferable that it is formed to receive a pressure from the roller, and also the roller 22 which receives the pressure from the area of the hydraulic part of the piston 20 to receive the pressure from the second pilot pipe (PV2) from the first pilot pipe (PV1). It is preferable to be comprised so that it may become larger than the area of the hydraulic pressure part of (). On the other hand, the spacer 23 is provided on the other side of the sleeve 14, the spring seat 24, which is a pressing means associated with it on the other side of the spool 16 is installed inside the spacer 23 is provided with the direction switching means Is installed.

In particular, the inside of the spool 16 and the spring seat 24 have a double spring for controlling the movement of the spool, that is, a first spring 26 built into the spool 16 and extrapolated to the spring seat. A second spring 28 is provided. Here, it is preferable that the first spring 26 and the second spring 28 have different spring constants, and the first spring 26 is connected to the first and second pilot pipes PV1 and PV2 in the initial mode. The spool 16 is formed to have a spring pressure to be switched to the speed increase mode when a predetermined pressure or more is applied, and the first spring 28 has a pressure greater than that of the first split in each of the pilot pipes PV1 and PV2. When a large pressure is applied, the spool 16 is formed to have a spring pressure that is switched from the speed increasing mode to the normal mode. In addition, the spool 16 has two flow paths 30 and 32 formed in the valve block 12 to form two closed spaces together with the sleeve 14.

Optionally, in order to minimize the resistance when the hydraulic oil passes through the speed increase valve, it is preferable to incline at an inclination angle θ inward from both ends of each of the flow paths 30 and 32, and the inclination angle θ is 45 ° to It is preferable that it is 70 degrees.

Of course, each component installed in the valve block 12 is shielded by a plug 29 which releasably closes both ends of the valve block.

The speed increase valve 10 configured as described above is installed in connection with the main control valve M and the cylinder C of the excavator as shown in FIG. 3, and the speed increase valve 10 is supplied from the main control valve M. Operation of the spool by the pressurized oil is switched to the initial mode, the speed increasing mode and the normal mode as described above. Here, the initial mode is a mode in which the flow rate does not flow because the second port P1 and the second cylinder port CP1 are closed, and in the case of switching from the initial mode to the increase mode, the main control valve M is in a neutral state. When present, the switching of the speed increase valve is controlled by the first spring 26 having a relatively low spring constant so as to overcome the leakage and generation pressure generated in the valve. In addition, in the case of switching from the speed increase mode to the normal mode, relatively high hydraulic pressure is required as compared with the above-described switching from the initial mode to the speed increase mode. In this case, the second spring 28 having a relatively high spring constant It has an operating structure in which the switching is controlled.

The switching to each mode will be described in more detail with reference to FIG. 4. In the initial mode of the speed increase valve, the first port P1 is opposed to the first cylinder port CP1 and the second port. An initial mode flow path section in which at least one of the ports P2 is opposed to the second cylinder port CP2 is closed is formed, so that the left end of the spool 16 is in contact with the right end of the bush 18. At this time, the first port P1 and the first cylinder port CP1 are interconnected by the sleeve 14, but the second port P2 and the second cylinder port CP2 are in a closed mode so that the hydraulic oil cannot flow. . Switching of the spool 16 in this state is only affected by the first spring 26 while no load is applied to the second spring 28, which is fitted with the first spring 28. This is because the spring seat 24 is in contact with the right end of the sleeve 14 but not in contact with the spool 16.

In this state, the speed increase mode flow path section in which the first and second cylinder ports CP1 and CP2 communicate with each other and at least one of the first and second ports P1 and P2 communicates with each other by a driver's operation. Once formed, the pressure of the first port P1 rises and the hydraulic pressure is supplied through the first pilot pipe line PV1 and applied to the roller 22 so that the roller 22 is pushed to the right, and at the same time, the spool 16 ) Is moved to the right to come into contact with the spring seat 24. As such, when the spool 16 is moved to the right side, the first port P1, the first cylinder port CP1, and the second cylinder port CP2 communicate with each other by the spool 16 and the second port P2. ) Only the closed mode, and thus the speed increase valve 10 achieves the speed increase mode, so that the driving rod R is driven in the forward direction in FIG. 3.

Subsequently, when each of the ports P1-CP1 and P2-CP2 opposing each other in the speed increasing mode as described above is formed in the normal mode flow path section communicating with each other, the hydraulic pressure is supplied through the pilot valve PV1 to supply the roller 22. Is pushed further to the right to return to the normal mode as shown in FIG. In this normal mode, the spring 16 is affected by the pressure set by both the first spring 26 and the second spring 28, but the spring constant of the second spring 28 is actually the second spring 26. It is understood that the spool 16 is actually affected by the value set by its outer spring 28 since it is greater than the spring constant of.

On the other hand, each end of the two flow paths (30, 32) formed in the spool (16) is formed to have an inclination angle (θ) toward the center portion thereof, so that the pressure loss during the flow of the pressurized oil inside the speed increase valve (10) It can be seen that it is minimized. In addition, since the diameter of the piston 20 is larger than the diameter of the roller 22, when the hydraulic oil is supplied through the second port P2 of the main control M, the pressure of the second port P2 is increased. When the hydraulic pressure supplied by the second pilot valve PV2 is applied to the piston 20 and the roller 22, they are moved to switch the spool 16. Accordingly, in the normal mode, even after the switching pressure of the spool 16 supplied from the second pilot pipe PV2 is smaller than the pressure by the first pilot valve PV1, the driving rod R shown in FIG. At the time of the forward operation, the driving speed R is reversed without the formation of the instantaneous or temporary speed increase mode, that is, the driving rod R is not advanced.

As a result, two flow paths communicating with the second cylinder port CP2 are formed in the spool 16, and two flow paths 30 and 32 are formed in the spool 16, thereby forming the sleeve 14 and the spool 16. In the initial mode of the speed increasing valve, the closed flow space formed by) is maintained in the closed mode, so that the main control valve M is maintained when the main control valve M is kept in a neutral state. It is to block the generated pressure and leakage. In addition, the spring seat 24 is provided with a two-stage spring, whereby the speed increase valve 10 is switched from the initial mode to the speed increase mode by the inner spring 26 at a low pressure and also from the speed increase mode to the normal mode. Is performed at high pressure by the outer spring 28. In addition, by the inclination angle θ formed at each end of the flow path (30, 32) formed in the spool 16, the pressure loss and resistance generated while the hydraulic oil passes through the speed increase valve can be minimized.

According to the speed increasing valve for the crusher according to the present invention as described above, when the main control valve is in a neutral state, the flow path of the speed increasing valve is closed, so that even if pressure is formed or leakage occurs in the main control valve, The supply of pressure oil to the furnace is cut off and the driving rod is completely blocked from being operated in an undesired direction, thereby improving the operating performance of the cylinder and the driving rod.

While a preferred embodiment according to the present invention has been described above, it will be understood by those skilled in the art that various modifications and changes can be made without departing from the scope of the appended claims.

Claims (7)

In the speed increase valve for increasing the drive rod installed reciprocally in the cylinder, A first port P1 and a second port P2 built in the valve block and connected to the supply or discharge side of the pressurized oil; and a first cylinder port CP1 and a second cylinder port CP2 connected to the cylinder shaft side. With the sleeve 14 to say, It is reciprocally installed in the sleeve, the first port (P1) is opposed to the first cylinder port (CP1) and the second port (P2) is arranged to be opposite to the second cylinder port (CP2) And an initial mode flow path section in which at least one of the opposing ports is closed, and the first and second cylinder ports CP1 and CP2 communicate with each other, and at least one of the first and second ports P1 and P2. A spool 16 forming a speed increase mode flow path section communicating with one port, and a normal mode flow path section in which each of the opposing ports P1-CP1 and P2-CP2 communicate with each other; Spool switching means for switching the spool 16 in accordance with the pressure applied by the pilot pipe (PV1, PV2) installed on one side of the spool and communicated with the first and second ports (P1, P2), respectively; And a pressurizing means for providing a reaction force to the movement of the spool opposite the spool switching means. The spool switching means according to claim 1, wherein the spool switching means moves the spool (16) to one side according to the application of the pressure of the second pilot pipe (PV2) in communication with either one of the first and second ports (P1, P2). A piston 20 to pressurize, Interposed between the piston 20 and the spool 16 and the spool to one side according to the application of the pressure of the first pilot pipe (PV1) in communication with either one of the first and second ports (P1, P2) A crusher speed increasing valve, characterized in that consisting of a roller 22 for pressurizing. The piston (20) according to claim 2, wherein the piston (20) receives pressure from the second pilot pipe (PV2) in communication with the second port (P2), and the roller (22) communicates with the first port (P1). Pressure is applied from the first pilot pipeline (PV1), and the area of the hydraulic part of the piston (20) receiving the pressure from the second pilot pipeline (PV2) is applied to the pressure from the first pilot pipeline (PV1). A speed increasing valve for a crusher, characterized in that it is larger than the area of the hydraulic part of the roller 22. The crusher speed increasing valve according to claim 1, wherein the pressurizing means is composed of double springs having different spring constants. The method of claim 1, wherein the double spring has a first spring having a spring pressure that the spool 16 is switched to the increase mode when a predetermined pressure or more is applied to the first and second pilot pipes (PV1, PV2) in the initial mode. A second spring having a spring 26 and a spring pressure for switching the spool 16 from a speed increasing mode to a normal mode when a pressure greater than the pressure of the first split is applied to the respective pilot pipes PV1 and PV2; The speed increase valve for the crusher, characterized in that consisting of a spring (28). The second cylinder port (CP2) of the sleeve 14 is composed of two flow paths, the first port (P1), the first cylinder port (CP1) when the spool is the speed increase passage section And the first flow passage 14a communicate with each other and the second flow passage 14b is closed, and when the spool is in the normal flow passage section, the second port P2 and the second flow passage 14b communicate with each other and the first flow passage 14b. The flow passage 14a is a speed increasing valve for the crusher, characterized in that formed to be closed. 2. The speed increasing valve for the crusher according to claim 1, wherein an outer end of each flow path of the spool is formed to be inclined to form an inclination angle θ toward the center to minimize resistance when the oil flows inside the spool. .