JP5359857B2 - Construction machinery - Google Patents

Description

  The present invention relates to a construction machine provided with an exhaust gas purification device.

  Conventionally, there is a construction machine in which an exhaust gas purification device is attached to an exhaust pipe of an engine. As this exhaust gas purification device, there is a DPF (Diesel Particulate Filter, a filter for capturing particulate matter contained in exhaust gas of a diesel engine). If the DPF is used as it is, it will be clogged with captured matter (particulate matter). Therefore, a technique for regenerating the DPF by increasing the engine and pump loads is known.

Patent Document 1 discloses a technique for incinerating captured DPF by increasing the engine load by increasing the engine rotation speed and limiting (squeezing) the pump discharge amount to increase the engine exhaust temperature. Has been.
Patent Document 2 discloses a technique of increasing the engine load by simultaneously increasing the pump discharge amount and the pump discharge pressure and increasing the exhaust temperature to a temperature at which the oxidation catalyst provided in the exhaust gas purification device is activated. Yes.

FIG. 10 shows a hydraulic circuit diagram of a conventional construction machine. The construction machine 800 includes an engine 1, an exhaust gas purification device 2 attached to an exhaust pipe 1a of the engine 1, a pump 3 driven by the engine 1, an actuator 8 to which hydraulic oil is supplied from the pump 3, a pump 3, a hydraulic oil tank 5 that supplies hydraulic oil to the hydraulic fluid 3 and returns hydraulic oil discharged from the actuator 8, and an actuator control valve 7 that is provided between the pump 3 and the actuator 8 and controls the operation of the actuator 8. . Furthermore, a flow path 31 that connects the pump 3 and the actuator control valve 7, a flow path 33 that connects the flow path 31 and the hydraulic oil tank 5, and a pressure control valve 9 that is provided on the flow path 33. Prepare.
In the construction machine 800, as described above, the engine 1 and the pump 3 are loaded in order to regenerate the exhaust gas purification device 2 (hereinafter simply referred to as “loading” or the like). When this load is applied, the hydraulic oil discharged from the pump 3 returns to the hydraulic oil tank 5 through the flow path 31, the flow path 33, and the pressure control valve 9. Further, the hydraulic oil discharged from the pump 3 also flows through the flow path 31 to the actuator control valve 7 side.

  When this load is applied, there is a risk that the actuator 8 may cause an unintended movement of the operator (the person who operates the construction machine 800). Therefore, Patent Document 2 describes a technique for applying a load only when the actuator control valve 7 is in a neutral position (switching position 7Ab). Patent Document 1 does not describe specific means for avoiding such danger.

JP-A 63-297722 Japanese Patent No. 3073380

  However, the above technique has the following problems.

  First, there is a problem that the actuator 8 moves due to leakage of hydraulic oil from the actuator control valve 7. That is, most of the actuator control valves 7 of the construction machine are usually constituted by spool valves, but there is a considerable amount of hydraulic fluid leakage in these spool valves. In particular, when a load is applied (when the discharge pressure of the pump 3 is increased), the amount of hydraulic oil leakage increases more than usual. Due to this leakage, a considerable pressure is applied to the actuator 8 even when the actuator control valve 7 is in the neutral position (switching position 7Ab). And there exists a possibility that the motion of the actuator 8 which an operator does not intend may generate | occur | produce.

  As another problem, there is a problem that the above movement occurs when a sensor (neutral detection switch) for detecting the neutral position (switching position 7Ab) of the actuator control valve 7 is abnormal. That is, when the attachment position of the neutral detection switch is deviated or when the voltage is dropped, the actuator control valve 7 detects that it is neutral even though it is not in the neutral position (switching position 7Ab). Then, the movement of the actuator 8 unintended by the operator occurs.

  When the actuator 8 moves as described above, the main body of the construction machine 800 or the work machine attached to the main body may come into contact with the surrounding objects and damage the surrounding objects. Moreover, even if the movement of the actuator 8 is small, the movement of the actuator 8 unintended by the operator may occur, which may cause distrust to the product (construction machine).

  An object of the present invention is to provide a construction machine that suppresses movement of an actuator when a load is applied.

  A construction machine according to a first invention includes an engine, an exhaust gas purification device attached to an exhaust pipe of the engine, a pump driven by the engine, an actuator supplied with hydraulic oil from the pump, and the pump A hydraulic oil tank that supplies hydraulic oil to the hydraulic oil and returns hydraulic oil discharged from the actuator; an actuator control valve that is provided between the pump and the actuator and controls the operation of the actuator; and the pump Switching means provided between the actuator control valve and the actuator control valve, wherein the switching means is capable of supplying the hydraulic oil discharged from the pump to the actuator control valve, the pump and the actuator. The control valve is shut off and the hydraulic oil discharged from the pump is pressurized. When the engine and the pump are loaded in order to regenerate the exhaust gas purification device, it is possible to switch to a second state in which it is possible to return to the hydraulic oil tank via a control valve or a flow control valve. The switching means is in the second state.

  In this construction machine, the switching means is in the second state when a load is applied to the engine and the pump in order to regenerate the exhaust gas purification device (when the load is applied). When the switching means is in the second state, the pump and the actuator control valve are disconnected, and the hydraulic oil discharged from the pump can return to the hydraulic oil tank via the pressure control valve or the flow rate control valve. is there. Therefore, the hydraulic oil discharged from the pump is not supplied to the actuator control valve when a load is applied. Further, the hydraulic oil is not supplied to the actuator that controls the operation of the actuator control valve. Therefore, it is possible to suppress the actuator from moving when a load is applied.

  A second invention is a construction machine according to the first invention, and when the switching means is in the second state, the hydraulic oil between the switching means and the actuator control valve passes through the switching means. It is possible to return to the hydraulic oil tank.

  In this construction machine, the pressure of the hydraulic oil between the switching means and the actuator control valve becomes the pressure of the hydraulic oil tank. Therefore, the pressure of the hydraulic oil applied to the actuator control valve is smaller than the case where a pressure higher than the pressure of the hydraulic oil tank is applied to the actuator control valve. Therefore, hydraulic fluid is not supplied to the actuator that controls the operation of the actuator control valve. Therefore, it is possible to more reliably suppress the actuator from moving when a load is applied.

  In particular, the present invention has a configuration in which the pump and the actuator control valve are shut off when a load is applied. Therefore, the hydraulic oil discharged from the pump when a load is applied is not supplied to the actuator control valve. Therefore, it is possible to suppress the actuator from moving when a load is applied.

It is a hydraulic circuit diagram of a construction machine. It is a figure which shows the control flow at the time of load application. FIG. 3 is a diagram corresponding to FIG. 1 of a second embodiment. It is the FIG. 1 equivalent view of 3rd Embodiment. FIG. 6 is a diagram corresponding to FIG. 1 of a fourth embodiment. FIG. 10 is a view corresponding to FIG. 1 of a fifth embodiment. It is FIG. 1 equivalent view of 6th Embodiment. FIG. 6 is a hydraulic circuit diagram showing the periphery of a switching valve according to a first modification. FIG. 9 is a diagram corresponding to FIG. It is a hydraulic circuit diagram of the conventional construction machine.

  Embodiments of a construction machine according to the present invention will be described below with reference to the drawings. The first to fourth embodiments are open center circuits, and the fifth and sixth embodiments are closed center circuits (details of each circuit will be described later).

(First embodiment)
FIG. 1 is a hydraulic circuit diagram of a construction machine. FIG. 2 is a diagram showing a control flow when a load is applied. Hereinafter, the configuration of the construction machine 100 will be described in detail with reference to FIGS. 1 and 2. In addition, the same code | symbol is attached | subjected about the part same as the conventional construction machine 800 shown in FIG. 10, and description is abbreviate | omitted.

  Specifically, the construction machine 100 is, for example, a mobile crane. Explaining the outline of the construction machine 100, as shown in FIG. 1, the exhaust temperature of the engine 1 is raised by increasing the load of the engine 1 and the pump 3 (loading), and the exhaust gas purification device 2 is regenerated. It has a function. A switching valve 21 is provided in the flow path 31 connecting the pump 3 and the actuator control valve 7. When the load is not applied, the switching valve 21 is switched to the first switching position 21 a and the hydraulic oil discharged from the pump 3 is supplied to the actuator control valve 7. When the load is applied, the switching valve 21 is switched to the second switching position 21b, the pump 3 and the actuator control valve 7 are shut off, and the hydraulic oil discharged from the pump 3 is operated via the pressure control valve 9. Returned to the oil tank 5.

  The pump 3 is driven by the engine 1. Then, the hydraulic oil is sucked from the hydraulic oil tank 5 through the filter 4 and supplied to the actuator 8 and the like. The pump 3 is a variable capacity pump whose capacity is changed by changing the tilt angle.

  The actuator 8 operates by supplying hydraulic oil from the pump 3. The construction machine 100 includes a motor 8A and a cylinder 8B as the actuator 8. The motor 8A is used, for example, for rotation and turning of a wheel, a crawler, an upper turning body, and a winch (each not shown) of the construction machine 100. The cylinder 8B is used for raising and lowering a boom (not shown) of the construction machine 100, for example.

  The actuator control valve 7 is provided between the pump 3 and the actuator 8 and controls the operation of the actuator 8. More specifically, it is a spool type three-position switching valve having six ports. The construction machine 100 includes, as the actuator control valve 7, an actuator control valve 7A that controls the operation of the motor 8A and an actuator control valve 7B that controls the cylinder 8B. Since the actuator control valves 7A and 7B have the same function, only the actuator control valve 7A will be described next, and the description of the actuator control valve 7B will be omitted.

The actuator control valve 7A is switched to switching positions 7Aa, 7Ab, and 7Ac by a pilot pressure supplied from a hydraulic pilot valve (not shown).
In the switching positions 7Aa and 7Ac, the hydraulic oil from the pump 3 and the flow path 31 is supplied to the motor 8A, and the motor 8A operates. Further, the hydraulic oil provided for the operation of the motor 8A returns to the hydraulic oil tank 5 via the actuator control valve 7A and the flow path 32.
The switching position 7Ab is a neutral position, and hydraulic oil from the pump 3 and the flow path 31 is not supplied to the motor 8A. Further, the hydraulic oil returns to the hydraulic oil tank 5 through the flow path 32 (bleed flow path). In other words, it is an open center. Strictly speaking, hydraulic fluid from the flow path 31 leaks to the motor 8A side.

  The pressure control valve 9 is a relief valve that opens when a predetermined pressure is exceeded. The pressure control valve 9 protects the circuit and limits the amount of load applied. More specifically, the pressure control valve 9 is provided on the flow path 33 that connects the flow path 31 (the branch point 33a thereof) and the hydraulic oil tank 5. Further, by adjusting the strength of the spring of the pressure control valve 9, the work (product of the pressure and the flow rate) of the pump 3 when the load is applied can be changed. Of the flow path 31, the flow path 31 a is between the pump 3 and the branch point 33 a, the flow path 31 b is between the branch point 33 a and the switching valve 21 (described later), and the switching valve 21 and the actuator control valve 7. A channel 31c is defined between the two.

  The switching valve 21 (switching means) is a two-port two-position switching valve and can be switched between a first switching position 21a and a second switching position 21b. The switching valve 21 is provided between the pump 3 and the actuator control valve 7. More specifically, it is installed closer to the actuator control valve 7 (downstream) than the branch point 33a on the flow path 31. The flow path 31b is connected to the input port, and the flow path 31c is connected to the output port.

  In the first switching position 21 a (first state), the switching valve 21 can supply the hydraulic oil discharged from the pump 3 to the actuator control valve 7. That is, the flow path 31b and the flow path 31c communicate. By supplying the hydraulic oil to the actuator control valve 7, the actuator 8 can be operated.

  In the second switching position 21 b (second state), the switching valve 21 blocks between the pump 3 and the actuator control valve 7. That is, the channel 31b and the channel 31c are blocked. At this time, the hydraulic oil discharged from the pump 3 can return to the hydraulic oil tank 5 through the flow path 31a, the flow path 33, and the pressure control valve 9.

  Next, the operation when loading is described. When the DPF provided in the exhaust gas purification device 2 is clogged by the captured material, the back pressure of the exhaust gas purification device 2 increases. When this is detected by a pressure sensor (not shown), an alarm (not shown) is sounded to notify the operator, and the operator neutralizes the operation lever (not shown). At this time, the actuator control valve 7A is switched to the neutral position (switching position 7Ab). Then, when the operator presses a regeneration control start switch (not shown), the above-described loading on the engine 1 and the pump 3 is started.

  As shown in FIGS. 1 and 2, when the regeneration control is started, the electromagnetic switching valve 22 is excited, and the electromagnetic switching valve 22 is switched from the switching position 22a to 22b. Thereby, the pilot pressure from the pilot pressure source 40 is applied to the switching valve 21, and the switching valve 21 is switched from the first switching position 21a to the second switching position 21b. Thereby, the pump 3 and the actuator control valve 7 are shut off. Further, the hydraulic oil discharged from the pump 3 returns to the hydraulic oil tank 5 via the pressure control valve 9.

(Characteristics of construction machine of this embodiment)
The construction machine 100 of this embodiment has the following features.

  As shown in FIG. 1, in the construction machine 100 of this embodiment, when a load is applied to the engine 1 and the pump 3 in order to regenerate the exhaust gas purification device 2 (when the load is applied), the switching valve 21 is in the second switching position 21b. It is. When the switching valve 21 is in the second switching position 21b, the pump 3 and the actuator control valve 7 are disconnected, and the hydraulic oil discharged from the pump 3 returns to the hydraulic oil tank 5 via the pressure control valve 9. It is possible. Therefore, the hydraulic oil discharged from the pump 3 is not supplied to the actuator control valve 7 when a load is applied. Further, the hydraulic oil is not supplied to the actuator 8 (8A) that controls the operation of the actuator control valve 7 (7A). Therefore, it is possible to suppress the actuator 8 from moving when a load is applied.

Further, consider a case where a sensor (neutral detection switch, not shown) for detecting neutrality (switching position 7Ab) is attached to the actuator control valve 7, and this sensor has an abnormality. At this time, the load is applied in a state where the actuator control valve 7 is deviated from the neutral position (in the switching position 7Aa or 7Ac). Even in this case, since hydraulic fluid is not supplied to the actuator control valve 7 when a load is applied, the movement of the actuator 8 is suppressed.
Furthermore, even if the actuator control valve 7 is not neutral, the actuator is restrained from moving when a load is applied. Therefore, it is not necessary to add a neutral detection switch to the actuator control valve 7. Therefore, the number of parts can be reduced as compared with the case where a neutral detection switch is provided.

(Second Embodiment)
FIG. 3 shows a hydraulic circuit of the construction machine 200 according to the second embodiment. This construction machine 200 is different from the first embodiment in that a pressure control valve 9 is added to the flow path 233. Since other configurations are the same as those of the first embodiment, the same reference numerals are given and description thereof is omitted.

  The main relief valve 10 is disposed at the same position as the pressure control valve 9 (see FIG. 1) of the first embodiment and has the same function as the pressure control valve 9. The set pressure of the main relief valve 10 is higher than the set pressure of the pressure control valve 9 (see FIG. 3) described below.

  As shown in FIG. 3, the pressure control valve 9 is provided on a flow path 233 that connects the output port of the switching valve 221 and the hydraulic oil tank 5. The pressure control valve 9 is set to open at a pressure lower than that of the main relief valve 10.

  The switching valve 221 (switching means) is a three-port two-position switching valve and includes a first switching position 221a and a second switching position 221b. A channel 31b is connected to the input port, and a channel 31c and a channel 233 are connected to the output port. The switching valve 221 operates as follows.

  In the first switching position 221a (first state), the hydraulic oil discharged from the pump 3 is supplied to the actuator control valve 7 and does not flow to the pressure control valve 9 side. That is, the flow paths 31b and 31c communicate with each other, and the flow paths 31b and 233 are blocked.

  In the second switching position 221b (second state), the hydraulic oil discharged from the pump 3 is not supplied to the actuator control valve 7 and returns to the hydraulic oil tank 5 via the pressure control valve 9. That is, the flow path 31b and the flow path 31c are blocked, and the flow path 31b and the flow path 233 communicate with each other. When the load is applied, the hydraulic oil discharged from the pump 3 passes through the pressure control valve 9 having a lower set pressure than the main relief valve 10. Thereby, compared with the case where the main relief valve 10 is provided and the pressure control valve 9 is not provided, it is possible to prevent the pump 3 and the flow path 31 from being overloaded.

(Third embodiment)
FIG. 4 shows a hydraulic circuit of the construction machine 300 according to the third embodiment. The construction machine 300 is different from the second embodiment in that the same operation as that of the switching valve 221 according to the second embodiment is performed by the switching valve 21 and the switching valve 321. Since other configurations are the same as those in the first and second embodiments, the same reference numerals are given and description thereof is omitted.

  As shown in FIG. 4, the pressure control valve 9 is provided on the upstream side of the switching valve 21. More specifically, it is provided on the flow path 333 that connects the branch point 333a on the flow path 31b (or 31a) and the hydraulic oil tank 5.

  The switching valve 321 (switching means) is a 2-port 2-position switching valve, and includes a first switching position 321a and a second switching position 321b. Further, it is provided on the flow path 333 and is provided between the branch point 333 a and the pressure control valve 9. The switching valve 321 operates as follows.

  In the first state, the switching valve 21 switches to the first switching position 21a. At the same time, the switching valve 321 switches to the first switching position 321a. As a result, the flow path 333 is blocked, and the hydraulic oil discharged from the pump 3 does not flow to the pressure control valve 9 on the downstream side of the switching valve 321.

  In the second state, the switching valve 21 switches to the second switching position 21b. At the same time, the switching valve 321 switches to the second switching position 321b. More specifically, as in the first embodiment, when the electromagnetic switching valve 22 is switched from the switching position 22a to 22b, the pilot hydraulic pressure from the pilot pressure source 40 is supplied to the switching valve 21. At this time, the pilot hydraulic pressure is also supplied to the switching valve 321. Then, the switching valve 321 is switched to the second switching position 321b. As a result, the hydraulic oil discharged from the pump 3 returns to the hydraulic oil tank 5 via the flow paths 31 a, 31 b, 333, the switching valve 321, and the pressure control valve 9.

(Fourth embodiment)
FIG. 5 shows a hydraulic circuit of the construction machine 400 according to the fourth embodiment. The construction machine 400 is different from the second embodiment in that the construction machine 400 includes a flow path 434 that returns the hydraulic oil from the flow path 31c upstream of the actuator control valve 7 to the hydraulic oil tank 5 via the switching valve 421. It is. Since other configurations are the same as those of the second embodiment, the same reference numerals are given and description thereof is omitted.

  As shown in FIG. 5, the flow path 434 is a flow path that returns the hydraulic oil in the flow path 31 c on the upstream side of the actuator control valve 7 to the hydraulic oil tank 5 via the switching valve 421. More specifically, the flow path connects the switching valve 421 and the hydraulic oil tank 5.

  The switching valve 421 (switching means) is a 4-port 2-position switching valve, and includes a first switching position 421a and a second switching position 421b, and operates as follows.

  In the first switching position 421a (first state), the flow paths 31b and 31c communicate with each other. At the same time, the flow paths 233 and 434 communicate with each other. At this time, since the flow paths 233 and 434 are not connected to the pump 3, no hydraulic oil flows through these flow paths.

  In the second switching position 421b (second state), the hydraulic oil between the switching valve 421 and the actuator control valve 7 can return to the hydraulic oil tank 5 via the switching valve 421. More specifically, at the second switching position 421b, the flow paths 31b and 233 communicate with each other as in the second embodiment. At the same time, the flow paths 31c and 434 communicate with each other. As a result, the pressure in the flow path 31 c, that is, the pressure applied to the actuator control valve 7 is reduced to the pressure in the hydraulic oil tank 5.

(Characteristics of construction machine of this embodiment)
The construction machine 400 of this embodiment has the following features.

  In this construction machine 400, the hydraulic oil pressure between the switching valve 421 and the actuator control valve 7 (flow path 31 c) is the hydraulic oil tank 5 pressure. Therefore, compared with the case where the pressure larger than the pressure of the hydraulic oil tank 5 is applied to the actuator control valve 7, the pressure of the hydraulic oil applied to the actuator control valve 7 is smaller. Therefore, the hydraulic oil is not supplied more to the actuator 8 (8A) that controls the operation of the actuator control valve 7 (7A). Therefore, it is possible to more reliably suppress the movement of the actuator 8 when a load is applied.

  Note that the hydraulic circuit of the present embodiment is an open center circuit. That is, when the actuator control valve 7 is in the neutral position (switching position 7Ab), the hydraulic oil in the flow path 31c returns from the flow path 32 (bleed flow path) to the hydraulic oil tank 5. Therefore, in principle, the actuator 8 is not moved by the hydraulic oil in the flow path 31c. However, when the actuator control valve 7 is in a position other than the neutral position (switching position 7Aa or 7Ac) due to an erroneous operation or the like, the hydraulic oil in the flow path 31c may flow to the actuator 8 and the actuator 8 may move. Therefore, by reducing the pressure of the hydraulic oil in the flow path 31c to the pressure of the hydraulic oil tank 5 as described above, it is possible to more reliably suppress the actuator from moving when a load is applied.

(Fifth embodiment)
FIG. 6 shows a hydraulic circuit of a construction machine 500 according to the fifth embodiment. The construction machine 400 (see FIG. 5) according to the fourth embodiment constitutes an open center circuit, whereas the construction machine 500 constitutes a closed center circuit. The construction machine 500 is different from the fourth embodiment in that an unload valve 509 is provided as a pressure control valve. Since other configurations are the same as those in the fourth embodiment, the same reference numerals are given and description thereof is omitted.

  The actuator control valve 507 is a switching valve that controls the actuator 8 as shown in FIG. When the actuator 8 is operated (at the switching positions 507Aa and 507Ac), the hydraulic oil used for operating the actuator 8 returns to the hydraulic oil tank 5 through the flow path 532, as in the fourth embodiment. On the other hand, when the actuator 8 is not operated (at the neutral position, that is, at the switching position 507Ab), the flow path 31c and the flow path 532 are blocked. As a result, the hydraulic oil in the flow path 31 c does not return to the hydraulic oil tank 5 from the flow path 532. That is, it is a closed center.

  The pressure compensation valve 523 is provided on the upstream side of the actuator control valve 507, and keeps the flow rate of the hydraulic oil supplied to the actuator control valve 507 constant. The pressure compensation valve 523 does not have a function of shutting off the pump 3 and the actuator control valve 7 when a load is applied.

  The unload valve 509 (pressure control valve) is a switching valve provided in the flow path 233, and includes a switching position 509a and a switching position 509b. These switching positions will be described later.

  The switching valve 521 (switching means) is a 4-port 2-position switching valve, and includes a first switching position 521a and a second switching position 521b.

In the first switching position 521a (first state), the flow paths 31a and 31c communicate with each other. At the same time, the hydraulic oil discharged from the pump 3 can flow to the unload valve 509 side. That is, the flow paths 31a and 233 communicate with each other.
Here, when the actuator control valve 507 is in the switching position 507Ab (neutral state), the unload valve 509 is in the switching position 509a. The hydraulic oil discharged from the pump 3 returns to the hydraulic oil tank 5 via the flow path 31a, the switching valve 521, the flow path 233, and the unload valve 509.
When the actuator control valve 507 is at the switching position 507Aa or 507Ac (when the operator operates the lever), the unloading valve 509 is at the switching position 509b. More specifically, the hydraulic oil in the flow path 31c is supplied to the unload valve 509 via the pressure compensation valve 523, the actuator control valve 507, and the flow path 535, and the unload valve 509 is switched to the switching position 509b. Thereby, the flow path 233 is blocked. The hydraulic oil discharged from the pump 3 is supplied to the actuator 8A.

In the second switching position 521b (second state), the flow path 31c and the flow path 434 communicate with each other, and the hydraulic oil in the flow path 31c returns to the hydraulic oil tank 5.
Here, this circuit is a closed center. That is, when the actuator control valve 507 is in the switching position 507 Ab (neutral state), the hydraulic oil in the flow path 31 c does not return to the hydraulic oil tank 5 from the flow path 532. Therefore, if it is as it is, hydraulic oil may remain in the flow path 31c and the actuator 8 may operate. However, since the hydraulic oil in the flow path 31c returns to the hydraulic oil tank 5 through the flow path 434 as described above, the actuator 8 does not move.

(Sixth embodiment)
FIG. 7 shows a hydraulic circuit of a construction machine 600 according to the sixth embodiment. This construction machine 600 is different from the fifth embodiment in that an unload valve 509 is provided in the flow path 633. The pressure control valve 9, the main relief valve 10, and the switching valve 421 are the same as those in the fourth embodiment (see FIG. 5), although they are different from those in the fifth embodiment. Since other configurations are the same as those of the fifth embodiment, the same reference numerals are given and description thereof is omitted.

  The unload valve 509 is provided in the flow path 633 as shown in FIG. The flow path 633 connects the flow path 31 c and the hydraulic oil tank 5. More specifically, the flow path 633 connects the hydraulic oil tank 5 with a branch point 633 a between the switching valve 421 and the pressure compensation valve 523.

  In the first to sixth embodiments, the load pressure is set by the pressure control valve. However, the load pressure can also be set by the flow control valve.

(Modification 1)
FIG. 8 shows a hydraulic circuit showing the periphery of the switching valve 221 according to the first modification. The pressure control valve 9 (see FIG. 3) of the second embodiment can be replaced with a throttle 709 (flow rate control valve). In this case, the load pressure (pressure in the flow path 31) is controlled by adjusting the opening area of the throttle 709.

(Modification 2)
FIG. 9 shows a hydraulic circuit around the switching valve 421 according to the second modification. The pressure control valve 9 (see FIG. 5) of the fourth embodiment can be replaced with a throttle 709.

  As mentioned above, although embodiment of this invention was described based on drawing, a specific structure is not restricted to these embodiment, It can change in the range which does not deviate from the summary of invention.

  For example, as shown in FIGS. 1 and 3 to 9, in the above embodiment, the first state and the second state are switched by using one or two switching valves as switching means. However, the present invention can be applied even if the number and positions of the valves are changed, for example, the operation performed with one valve in the above embodiment is performed with two or more valves. More specifically, for example, the same operation as that of the switching valve 221 shown in FIG. 3 was performed by the two switching valves 21 and 321 shown in FIG. Similarly, for example, the function of the switching valve 421 shown in FIG. 5 may be divided into two, with one switching valve connected to the flow path 233 and the other switching valve connected to the flow path 434. .

Further, for example, as shown in FIGS. 1 and 3 to 7, in the above embodiment, the motor 8 </ b> A and the cylinder 8 </ b> B are shown as the actuator 8, but the number of the actuators 8 may be 1 or 3 or more.
Further, when there are a plurality of actuators 8, the invention can be applied if there is a switching means (such as the switching valve 21 shown in FIG. 1) upstream of at least one actuator control valve 7.
More specifically, for example, when a neutral ABT actuator often used in a traveling system is used, the pressure applied to the actuator is forcibly reduced to the pressure of the hydraulic oil tank 5 when the actuator control valve is in a neutral state. As described above, among the plurality of actuators provided in the construction machine, there are some which do not cause much problem that the actuator moves when a load is applied. The switching valve 21 may not be provided on the upstream side of such an actuator, and the switching valve 21 may be provided only on the upstream side of the other actuators 8 (actuators that are problematic when applied).

DESCRIPTION OF SYMBOLS 1 Engine 1a Exhaust pipe 2 Exhaust gas purification device 3 Pump 8 Actuator 5 Hydraulic oil tank 7 Actuator control valve 21,221,321,421,521 Switching valve (switching means)
9 Pressure control valve 10 Main relief valve (pressure control valve)
509 Unload valve (pressure control valve)
709 Restriction (flow control valve)

Claims (1)

Engine,
An exhaust gas purification device attached to the exhaust pipe of the engine;
A pump driven by the engine;
An actuator to which hydraulic oil is supplied from the pump;
A hydraulic oil tank that supplies hydraulic oil to the pump and returns hydraulic oil discharged from the actuator;
An actuator control valve that is provided between the pump and the actuator and controls the operation of the actuator;
Switching means provided between the pump and the actuator control valve,
The switching means is
A first state capable of supplying hydraulic oil discharged from the pump to the actuator control valve;
A second state in which the pump and the actuator control valve are shut off, and the hydraulic oil discharged from the pump can return to the hydraulic oil tank via the pressure control valve or the flow rate control valve; , Can be switched to,
When imposing a load on the engine and the pump in order to reproduce the exhaust gas purifying device, said switching means Ri said second state that is
When the switching means is in the second state, the hydraulic oil between the switching means and the actuator control valve can return to the hydraulic oil tank via the switching means.
Construction machinery.

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