Load control hydraulic valve device

FIELD: machine building.

SUBSTANCE: proposed device comprises first and second engine openings communication L' and N' for communication with two-way hydraulic motor D, and openings M' and O' for communication with manual-control valve H. Besides, valve device comprises normally-closed proportioning load-adjustment valve E and check valve 12 with outlet communicated with aforesaid second opening N' and inlet communicated with opening O'. Note here that check valve 12 is pre-stressed for opening solely in case its inlet exceeds preset pressure range.

EFFECT: higher reliability.

1 cl, 7 dwg

 

The invention relates to a hydraulic valve device regulation load and is described, for example, with specific reference to its application driven and controlled hydraulic cranes, in particular cranes on vehicles.

These cranes usually have a crane arm that can move up and down with hydraulic lifting cylinder double acting, which acts between the crane boom and frame construction or support of the crane. This hoist cylinder is part of a hydraulic system which includes a hydraulic pump and valve with manual control, with which the pump can be selectively connected to one chamber of the lifting cylinder when the boom must be raised, and with the second chamber of the lifting cylinder when the boom must be lowered. At the same time, in the first case, the second chamber of the lifting cylinder and in the second case, the first chamber of the lifting cylinder is connected through the valve manually operated with a tank for the hydraulic fluid.

Typically, the boom tends to move downwards under the action of its own weight and the weight of a possible load, which is suspended on the crane boom. For security reasons, the hydraulic system design so that the cargo can not is t to fall, if the hydraulic pump is not connected with the second chamber of the lifting cylinder, and by connecting the control valve to regulate the load for opening the connection from the first chamber of the lifting cylinder to the tank. If this protective measure is missing, broken line between the first chamber of the lifting cylinder and valve with manual control may cause the crane boom and possible load attached to it, freely fall. In parallel with the control valve load is a non-return valve, which is open to the first chamber of the lifting cylinder, therefore, the working fluid can pass from the pump into the chamber of the lifting cylinder. The security devices of this type are particularly common in hydraulic systems, in which the operator can directly mechanically control valve manually operated lifting cylinder, for example, by using the control knob.

Unsolved problem associated with the security scheme of the type described and other known security schemes of the same type, is that the efficiency of a hydraulic system is low and leads to the fact that the system tends to oscillate when lowering the load.

The present invention is to solve these problems and, with one of the parties is, in creating the valve control device of the load, which ensures conservation of a significant part of energy that is lost when lowering the load using a conventional hydraulic valve control devices of the load of the type indicated above, on the other hand, in the establishment of a valve control device for the load, which is able better than normal valve control device of the load, to ensure the lowering of the cargo without the formation of oscillations in the load-carrying system.

Below the invention is described in detail with reference to accompanying drawings, where:

figure 1 - view of the vehicle with hydraulically controlled boom and a hydraulic system with a hydraulic lifting cylinder double acting and conventional valve device mounted on it.

figure 2 is a hydraulic circuit diagram of the lifting cylinder of figure 1, provided with the usual valve control unit load, and attached part of the hydraulic system boom;

figure 3 is a hydraulic circuit similar to the hydraulic circuit of figure 2, but illustrating the valve control unit according to the load in accordance with the first implementation of the invention;

4 is a hydraulic circuit similar to the hydraulic circuit of figure 3, but illustrating the valve device to regulate the financing of the load, completed with a device for returning the working fluid;

5 is a hydraulic circuit similar to the hydraulic circuit of figure 4, but illustrating the valve control unit according to the load in accordance with a further implementation of the invention;

6 is a hydraulic circuit similar to the hydraulic circuit of figure 3, but illustrating the valve control unit according to the load control unit load for each chamber of the lifting cylinder; and

7 is a hydraulic circuit similar to the hydraulic circuit of the 6, but illustrating the valve device regulation load, supplemented by a device for returning the working fluid.

Hydraulically operated lifting the arrow shown in figure 1, is made with the possibility of placing on the vehicle (not shown) and has a support And with a rotary valve, which contains a rack With arrows on the top end. Hydraulic motor bilateral action in the form of a hydraulic lifting cylinder D is located between the stand With boom and base of the crane Century Lines F and G connect the two chambers of the lifting cylinder with valve H with manual control, which in the example shown is controlled by the lever and in turn is connected with a hydraulic pump and a tank T through additional lines J and K, according to the respectively.

Figure 2 shows a portion of the hydraulic mechanism, which is used to control the lifting cylinder D. First, the lower chamber of the lifting cylinder (Cam lift) has a first hole of the engine, hereafter referred to as the bottom hole L of the lifting cylinder, because of the lifting cylinder D forms engine. The F line connects the bore of the lifting cylinder with the first working hole M in the valve H with manual control, which in the example shown is a valve with an open center. Second, the upper chamber of the lifting cylinder (camera lowering) respectively has a second hole of the engine, called the upper hole N the lifting cylinder, which is connected with the second working hole Of the valve H with manual control via line G. line F posted by normally closed proportional control valve for the load.

The valve E regulation load has one inlet opening which is in communication with the bottom hole L of the lifting cylinder, and one outlet, which is in communication with the first working hole M in the valve H with manual control, one of the first intake control, which is also using the line P is in communication with the first working hole M, and the second intake control that is away is in communication with the upper hole N the lifting cylinder through line Q control. In cooperation with the valve E regulation load is a non-return valve R, which is connected with the bottom hole L of the lifting cylinder and the first working hole M in the valve H with manual control and is open toward the opening L of the lifting cylinder. The valve E regulation load constantly drawn in to the closed position by a spring S.

When the arrow on the valve of figures 1 and 2 is maintained stationary when the valve H with manual control is shown in the neutral position, the pump I pump the working fluid under very low pressure back on line J and through the valve H with manual control directly into the tank So

When lifting With (increasing positive load) valve H with manual control skips the working fluid under high pressure from the pump I through the first operating hole M and the non-return valve R in the lower chamber of the lifting cylinder D. At the same time, the working fluid flows under low pressure line G and through the valve H with manual control in the tank So

When lowering the boom With the decline in the positive load) the working fluid is bypassed from the pump I through the second operating hole Of the valve H with manual control in the upper chamber of the lifting cylinder D. At the same time, the working fluid through the line Q control affects Verhny the side of the valve E regulation load and press it to open position in opposition to the action of the spring S. Since the outlet pressure of the pump works against the spring force S, contributing to the opening of the valve E regulation load at the output of the pump is set to a relatively high pressure part of the pump is returned, filling the upper chamber of the lifting cylinder D. the entire pump flow will also have high pressure at great loss of power.

Another disadvantage of the known system of Fig 1 and 2 is that when lowering the load it has a tendency to oscillations that depend on strong changes of pressure in the upper chamber of the cylinder, depending on the speed at which the plunger is moved in the lifting cylinder D.

The valve control unit according to the load in accordance with the invention represents a significant improvement in respect to power losses and the trend towards the emergence of oscillations in comparison with the prior art, is evident from figures 1 and 2. Five examples of implementation of the invention shown in Fig.3-7. These figures schematically differ from figure 2 only in the construction of the valve control device of the load, and so on the remaining parts of figure 3-7 for the same or corresponding elements are the same positions and designations. With a few exceptions the same sa the th applicable for elements in the valve control unit load figure 3-7, which correspond to the elements in the valve E regulation load figures 1 and 2.

In General, the valve control unit according to the load indicated on the figures in position 10. It is partly corresponds to the valve E regulation load of 1, 2 and similarly he has, for example, proportional-holding valve load, but it is supplemented with some additional non-return valves. In addition to the non-return valve 11 and the spring S, which correspond to the non-return valve T and the spring S in figure 2, respectively, it has two other check valve 12 and 15.

Together with these non-return valves 12 and 15, the valve E regulation load, which includes a check valve 11, forms a valve device 10 of regulation load. This valve device 10 of regulation load figure 3, 4 and 5, dashed, and may form the valve site, which can be installed on the lifting cylinder d To the valve device 10 of regulation load can be attached tube or pipe for passing the working fluid in the lift cylinder D and out through the valve H with manual control. Place on the valve device 10 of regulation at the load, where they can be connected to a lifting cylinder D, that is attached to the lifting cylinder D, i.e. upper and n is gnee holes L and N of the lifting cylinder, denoted by L' and N', respectively, and they form the first and second connecting holes of the engine, respectively. Where the valve device 10 of regulation load can be connected with working holes M and the valve H with manual control, in this case called the first connecting valve hole and the second connecting hole of the valve, respectively, and denoted by M' and O', respectively.

The check valve 12, which is located in the G line and connects the upper connection hole N' the cylinder with the second connecting hole Of' the valve and then through the second operating hole Of the valve H with manual control, is open to the connecting hole N' the cylinder is loaded, pre preloaded to a closed position by a spring 16 to open only when the selected high pressure inlet, which is relatively low, for example, comprising 10-15% higher pressure at the pump outlet. In the present example case, the opening pressure of the check valve 12 is about 30 bar (3 MPa).

In addition, the check valve 15, which is not pre-preloaded included counter towards the non-return valve 12 to permit release of the upper chamber of the lifting cylinder lifting Zilin the re D in the second working chamber Of the valve H with manual control via the upper connection hole N' the cylinder.

One control line 18, which corresponds to the line Q control in figure 2, connects the inlet of the control valve E regulation load line G on the inlet side of the check valve 12.

The valve E regulation load made with the possibility of opening at the lower limit of the specified range of the pressure is proportional from fully closed to its fully open position when the control pressure in the control line 18 increases from the lower limit to the upper limit of the pressure range. The upper limit of the pressure range, at least slightly below the pressure at which offer pre-preloaded non-return valve 12. In the example, the pressure range is from 10 to 25 bar (1-2,5 MPa), respectively, slightly less than the pressure required to open the pre-bogatogo check valve 12. Therefore, the pump flow to the lift cylinder D, which is located in the system of figures 1 and 2, together with the known control valve load, due to the fact that the pressure in line G is changed depending on the speed of the piston in the lifting cylinder D, resulting eliminates the undesirable tendency of oscillation in the cylinder.

Figs.4 and 5 show two further preferred embodiment of the invention, which according the invention represents a further development of the implementation of figure 3. There are two additional check valves, which are made with the possibility of returning the working fluid from the lower holes of the lifting L of the cylinder in the top hole N the lifting cylinder during lowering of the load. The advantage of this return is primarily in the fact that the pump does not work when lowering the load, and that the lowering of the cargo can be executed without hesitation.

The check valve 13 in line F is connected between the release valve E regulation load and the first connecting hole M' valve. He previously drawn in to the closed position by a spring 17, first and foremost, to open at a high, but low pressure compared to the opening pressure of the check valve 12, which in the selected example case is 3 bar (0.3 MPa).

The check valve 14, which is not pre-preloaded, is located between the release valve E regulation load and the upper connection hole N' the cylinder. Because it is not pre preloaded to the closed position, it is more easily opened than the check valve 13. However, it is not absolutely necessary in order to obtain the desired result, the check valve 13 was previously so low. The line from the valve E regulation load che the ez valve H with manual control themselves include some resistance, which has the same effect as previously preloaded valve, whereupon the working fluid will choose the path of minimum resistance, which when lowering the load passes through the check valve 14 to the upper hole N the lifting cylinder, in this case, where the pressure is close to zero.

The valve H with manual control is located so that the operator, by setting the working valve in position lowering, that is, by performing a manual connection line G with the pump I and the connection line F to the tank T can change the pressure in lines G and thereby the pressure at the inlet of the control valve E regulation load within the selected pressure range. As in this case, the check valve 12, the opening pressure is not achieved, and since the check valve 15 remains closed, the flow of the working fluid will not leak from the pump I to the G line in the top hole N the lifting cylinder, and the pressure at the pump outlet will serve only as a control signal for the valve E regulation load.

Therefore, when lowering the load capacity of the pump is not spent: spent the pump power is limited to relatively low power required to maintain a control signal to the valve E regulation load that he supported open.

When about is ushkanii cargo plunger lifting cylinder D is extruded, under the action of the load, the flow of working fluid out of the lower openings L of the lifting cylinder and the lower fixing holes L' of the cylinder and passes through the valve E regulation load. This stream passes first of all through practically not under pressure to open the check valve 14 to the upper chamber of the lifting cylinder, so that it is continuously filled in the same extent that it increases its volume. Because the flow coming from the lower chamber of the lifting cylinder is greater than the flow, which can take the upper chamber of the lifting cylinder, some of the flow passes through the check valve 13 and the valve H with manual control in the tank So

When lifting the valve H with manual control set in the position in which it connects the first working hole M in the valve H with manual control and the pump I, line F and through the check valve 11 and the lower connecting hole L' of the valve with the lower hole L of the lifting cylinder, so that the lower chamber of the lifting cylinder can be filled with the working fluid at a pressure that is needed to lift the load. The working fluid, which in this case is displaced from the upper chamber of the lifting cylinder through the top hole N the lifting cylinder and the upper connection hole N' the valve, passes completely through the open check valve 15 and line G to the second connection opening Of the' valve and the working hole and then into the tank T. Therefore, the lift is essentially in the same manner as in the case of the known valve E regulation load of figures 1 and 2.

Figure 5 shows another implementation in which omitted the valve H with manual operation, the pump I, the tank T and lines J and K, which connect the valve with manual control with pump and tank, but as figure 4, which applies in cases where it is often desirable to push down the plunger lifting cylinder D, for example, for pressing the rack boom or fixtures to the ground or other support. In such cases, the creation of differential pressure, for example 30 bar (3 MPa), as in the above example, pre-pojetom reverse valve 12 can be difficult for reasons of power consumption. To eliminate this inconvenience check valve 12 does not have pre-clamped springs, shown in figure 3. Instead, it provided a hydraulic pre-clamped device 19, which automatically becomes inactive when the pressure disappears, for example, when the aperture L of the lifting cylinder is blocked.

Pre-clamped device 19 consists of a single-action cylinder, the plunger rod 20 which acts on the check valve 12 in the closing direction. Cylindrical chamber adjusting the ameres connected with the lower connecting hole L' of the cylinder and the bottom hole L of the cylinder through line 21 to the control. In the cylindrical chamber of the cylinder, respectively, there is no pressure or almost no pressure when the upper chamber of the lifting cylinder is under pressure, and for this reason the valve E regulation load opens. Thus the flow from the pump can flow through the check valve 12 to the upper chamber of the lifting cylinder without any significant pressure drop.

An implementation option, shown in Fig.6, different from the version of the implementation shown in figure 3, the two valves E, E1 regulation load, each of which belongs to each one of the cylindrical chambers of the lifting cylinder D. the Valve E regulation load performs the same function as the valve E regulation load figure 3, 4 and 5, that is, it provides protection against uncontrolled movement of the plunger lifting cylinder to the lower end of the cylinder (bottom). Valve E1 regulation load performs a corresponding function with respect to the movement of the plunger toward the cavity of the plunger rod of the lifting cylinder (up). The function of the valve E1 regulation at the load is required in situations where the load tends to reject the plunger lifting cylinder in the direction of the stem cavity of the plunger, for example, when the load is changed from the load during the raising of the e cargo (positive load) to the load when lowering the load (negative load).

Valve E1 regulation load on the circuit of Fig.6 replaces the check valve 15 of Fig 3, 4 and 5. In addition, the check valve 11 from the same figures replaced by a pre-preloaded check valve 12A, which has a capability of functioning similarly to the non-return valve 12. Thus, in the diagram shown in Fig.6, it eliminates the undesirable tendency of the cylinder to make the oscillation, when the cylinder is switched to the mode of ascent.

Same as figure 5 differs from figure 3, the diagram of figure 7 differs from the circuit of figure 6. That is, in the figure, the two flaps hold the load with the addition of two devices for returning the working fluid.

Check valves 12, 13 and 14 are essentially the same manner as in figure 5. Check valve 11A is located and has an inlet connected to the tank So Pre-preloaded check valve 12A, which serves the upper cylindrical chamber of the lifting cylinder D, of course, has an inlet connected to the first connecting hole M' valve. The check valve 14A has a issue connected with the lower connecting hole L' of the cylinder and thus also with the release valve 11A.

The device E1 regulation load is in the same manner as the valve E regulation load, except that it caters to the upper chamber under the lot of the cylinder. Inlet valve E1 regulation load is in the message respectively with the upper connection hole N' the valve and the top of the hole N the lifting cylinder, and the outlet is in communication with the intake on a lightly pre-pojetom reverse valve 13A and the inlet fully open the check valve 14A. The release on the back of the valve 13A, of course, connected to the line G and About'. The release valve 14A is connected with the lower connecting hole L' of the cylinder and thus also with line 21 control for pre-clamped device 19.

Valve E1 regulation load also has a check valve 12A with hydraulic pre-clamped device 19A, which has similarities with the previously clamped by the device 19 includes a cylinder 20A unilateral action, the plunger rod which acts on the check valve in the closing direction via line 21A of the control, which is connected to the upper connection hole N' the cylinder and the top of the hole N the lifting cylinder.

If the load on the piston of the lifting cylinder is positive and therefore tends to move the plunger lifting cylinder toward the lower end of the lifting cylinder, the check valve 12 is tightened in the direction of closures protect the resulting pressure in the lower chamber of the lifting cylinder. If the valve H with manual control is in the neutral position, the check valve 12 is securely closed due to the pressure load. In addition, the closed valve E regulation load.

If the valve H with manual control result in a situation of increasing positive load pressure in line 18A of the control opens the valve E1 regulation load, so that the control valve load opens the way of release from the upper chamber of the lifting cylinder in a slightly pre-preloaded check valve 13A, the valve H with manual control via valve with manual control in the tank So the check valve 14A is held securely closed by the high pressure in the lower chamber of the lifting cylinder. To the upper chamber of the lifting cylinder pressure is not applied, and this means that the check valve 12A is deprived of preload and can be opened without any significant loss of pressure fluid from the pump I to the lower chamber of the lifting cylinder.

If the option is positive, the load should be reduced, the valve H with manual control set in the position in which it connects the pump I from line G. In this case, the valve E regulation load is opened by pressure in the control line 18, so that the working fluid when a large pressure differential may be Yudina in a controlled manner from the lower chamber of the lifting cylinder partially through the fully open valve 14 in the upper chamber of the cylinder, so the camera is replenished and cavitation therein is prevented, and partly through a slightly pre-preloaded check valve 13 into the tank So

On the other hand, if the load is negative or is changed from positive to negative, so she tends to push the piston in the lifting cylinder D in the direction of the stem cavity of the plunger and thereby to maintain the upper chamber of the lifting cylinder under high pressure, while the lower chamber of the cylinder pressure is not supplied, the high pressure in the upper chamber of the lifting cylinder through its impact on pre-clamped device 19A prevents opening of the valve. If then the piston in the lifting cylinder is shifted in the direction of action of the load, i.e. in the direction of the stem cavity of the plunger (up), the valve H with manual control set in the position in which it connects the pump I from line F. the pump Pressure acts through line 18A of the control valve E regulation load so that it opens and releases the working fluid from the upper chamber of the lifting cylinder with a large pressure drop.

Produced by the working fluid first flows through the fully open valve 14A in the lower chamber of the lifting cylinder, filling it with DOP is niceley working fluid, taken from the tank T through the check valve 11A, so that it is in the lower chamber of the lifting cylinder, cavitation is prevented. Therefore, the removal of the load is controlled with a valve E regulation load and without having to add any worthwhile power from the pump I. To perform this operation, the valve is manually operated, as shown in the figure, must be open center, since the distribution of fluid that passes through the check valve 11A, it is assumed through the Central hole.

Similarly, the control unit load from figure 4 and from the same reasons that have been stated in accordance with its description, the valve device 10 of regulation load of 5 and 7 also work very economically and without, or almost without, trends towards the emergence of oscillations.

It should be noted that despite the implementation of a control unit according to the load of Fig.7. the double function of regulation load compared to the valve control devices of the load from figure 4 and 5, the number of check valves is not doubled. In comparison with the known valve E regulation load of figures 1 and 2 the valve device 10 of regulation load of 4 and 5 have four valve more. Despite the double is a function of regulation load, valve device regulation load of 7 has only two non-return valve is greater than the valve control unit according to the load of figure 4 and 5.

1. Hydraulic valve device regulation load containing the first connection opening (L') of the engine and a second connection opening (N') of the motor is made with the possibility of connection with the first hole (L) of the engine and a second hole (N) of the engine, respectively, in the hydraulic motor is bidirectional (D), in particular a hydraulic cylinder, double acting, the first connecting hole (M') of the valve and a second connection opening (O') of the valve, made with the possibility of connection with individual workers holes M and O, respectively, in the valve H with manual control normally closed proportional valve (E) of regulation load, with the inlet connected to the first connecting hole (L') of the engine, and the output connected to the first connecting hole (M') of the valve, and the intake control, hydraulically connected with the second connecting hole (O') of the valve and is arranged to change the position of the opening between a closed position and a fully open position when the pressure at the inlet of the control is changed within a given the first pressure range, the first check valve (12), which has a discharge side connected with the second connecting hole (N') of the engine, and the intake side connected with the second connecting hole (O') of the valve, and which pre-preloaded or can be pre-drawn in to open only when the pressure at its inlet side is higher than the specified pressure range.

2. The valve control unit according to the load according to claim 1, in which the opening pressure of the first check valve (12) is adjustable by the pressure in the first connecting hole (L') of the engine.

3. The valve control unit according to the load according to claim 1 or 2, containing the second, mostly without pressure outdoor check valve (14)having an inlet connected to the release valve (E) of regulation load, and the output of which is connected with the second connecting hole (N') of the engine.

4. The valve control unit according to the load according to claim 1, containing the third, slightly pre-preloaded non-return valve (13)having an inlet connected to the release valve (E) of regulation load, and the output connected to the first connecting hole (M') of the valve.

5. The valve control unit according to the load according to claim 4, containing the fourth check valve (15), connected in opposite relative to the lane the WMD non-return valve (12) and having an inlet side, connected with the second connecting hole (N') of the engine, and the exhaust side connected with the second connecting hole (O') of the valve.

6. The valve control unit according to the load according to claim 5, containing the fifth check valve (11), connected in opposite with respect to the valve (E) of regulation load and having an output, connected to the first connecting hole (L') of the engine, and an inlet connected to the first connecting hole (M') of the valve.

7. The valve control unit according to the load according to claim 1, containing additional, normally closed proportional valve (E1) of regulation load performed similar to the first valve (E) of regulation load and having an inlet connected with the second connecting hole (N') of the engine, and the output of which is connected with the second connecting hole (O') of the valve, and the intake control, hydraulically connected with the first connecting hole (M') of the valve and is arranged to change the position of the opening between a closed position and a fully open position when the pressure at the inlet of the control is changed within a specified range of the pressure, and additional non-return valve (12A)having a discharge side connected with the first connecting hole (L') of the engine and having an inlet from the horon, connected with the first connecting hole (M') of the valve, and which pre-preloaded or can be pre-drawn in to open only when the pressure at its inlet side is higher than the specified pressure range.

8. The valve control unit according to the load according to claim 7, in which additional opening pressure check valve (12A) is regulated by the pressure in the second connecting hole (N') of the engine.

9. The valve control unit according to the load according to claim 7, containing the sixth, mainly without the pressure open valve (14A)having an inlet connected with an additional release valve (E1) of regulation load, and the output connected to the first connecting hole (L') of the engine.

10. The valve control unit according to the load according to claim 7, containing the sixth check valve (13A), performed similarly to the third non-return valve (13) and having an inlet side connected to the issue of additional valve (E1) of regulation load, and which connects this issue with the second connecting hole (O') of the valve and pre-drawn in to open only at a somewhat increased pressure on the release.

11. The valve control unit according to the load according to claim 7, containing the seventh check valve (11) - Rev.), which has an inlet side connected to the tank (T), and the discharge side connected with the second connecting hole (N') of the engine.



 

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3 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: power efficient working equipment consists of turning platform, of gantry, of boom, of stick, of bucket, of hydro-cylinders of boom lift. of hydro-cylinders of stick turn and of hydro-cylinder of bucket turn. In vertical plane of symmetry of the boom between hydro-cylinders of stick turn there is installed a pneumatic hydro-cylinder pivotally secured on the turning platform and the boom, a piston cavity of which is connected at least with two gas tanks charged with compressed air at pressure over 10 MPa. Total volume of gas tanks amounts to at least four working volumes of the pneumatic hydro-cylinder. At least one hydraulic damper of working fluid pressure charged with compressed air over 15 MPa is connected to piston cavities of the boom hydro-cylinders.

EFFECT: improved design of working equipment of hydraulic excavator, reduced fluctuations of pressure in hydro-system of working equipment.

2 dwg

FIELD: mining.

SUBSTANCE: energy-saving operating equipment includes digging arm base, digging arm head, handle, bucket, the main hydraulic cylinders for lifting the digging arm, control hydraulic cylinder of the digging arm length, additional balancing pneumatic cylinder connected to portal and to the digging arm base. Piston cavity of balancing pneumatic hydraulic cylinder is connected to gas bottle charged with pressure of more than 10 MPa and having the volume equal at least to five operating volumes of balancing pneumatic hydraulic cylinder. At that, to piston cavity at least of one main hydraulic cylinder for lifting the digging arm there connected is hydropneumatic accumulator the gas cavity of which is charged with initial pressure of more than 10 MPa and divided at least into two gas chambers separated with a partition in which an adjustable orifice is installed.

EFFECT: higher operating efficiency of machine, lower energy losses and higher efficiency of operating equipment.

2 dwg

FIELD: earth-moving facilities; hydraulic drives of scraper working members.

SUBSTANCE: proposed hydraulic drive contains pressure spool installed in parallel with like spaces of two hydraulic cylinders, pressure main line connected between two check valves, free outlet of check valve being connected with inlet of pressure spool and one hydraulic cylinder. Free inlet is connected with outlet of pressure spool and other hydraulic cylinder, drum main line connects opposite spaces of hydraulic cylinders. Hydraulic drive is furnished with two series-connected pressure spools. Inlet of first pressure spool and outlet of second pressure spool are connected with outlet of first hydraulically controlled reversible spool. Their common line is connected with controllable space of second hydraulic cylinder and is separated by check valve from pressure main line. Inlets of first hydraulically controlled reversible spool are connected to outputs of second hydraulically controlled reversible spool and are connected with controllable spaces of first and second hydraulic cylinders. One inlet of second hydraulically controlled reversible spool is connected with inlet of pressure spool and is connected to pressure line through check valve, and second inlet is separated from pressure line by other check valve. Control spaces of two hydraulically controlled reversible spools are united and are connected to pressure main line through two-position spool.

EFFECT: improved efficiency of control of scraper blade system.

4 dwg

FIELD: handling machinery, particularly soil-shifting, mining, agricultural and loading cyclic machines.

SUBSTANCE: device includes implement, main hydraulic cylinders and balancing hydraulic cylinder, at least one gas cylinder and hydropneumatic accumulator, main and additional hydrodistributors, as well as safety valve. Gas cylinder communicates with gas chamber of hydropneumatic accumulator. Device made in the first embodiment has the second additional hydrodistributor connecting working chambers of the main hydraulic cylinders with each other and with pump. Rod end of balancing hydraulic cylinder communicates with rod ends of the main ones. In the second embodiment additional hydraulic cylinder is arranged in main hydrodistributor case and connected to hydrolines of the main hydraulic cylinders through hydrolines. Additional hydrodistributor is installed so that additional hydrodistributor may connect working chambers of the main hydraulic cylinders with each other and with the pump when additional hydrodistributor is installed in the first position. Additional hydrodistributor being installed in the second position may connect working chambers of main hydraulic cylinders with each other and with drain. Rod end of balancing hydraulic cylinder is connected with rod ends of main hydraulic cylinders.

EFFECT: increased machine productivity due to increased implement hoisting speed.

3 cl, 4 dwg

FIELD: mechanical engineering, particularly hydraulically driven dredgers.

SUBSTANCE: drive comprises power plant with controlled power pumps having servo control taps, gear-box, hydraulic motors and hydraulic equipment. Hydraulic equipment has hydraulic distributor with address travel spool and its servo control taps, power hydraulic lines and servo control loop with hydraulic lines. The controlled power pumps may supply predetermined volume of working liquid at zero pressure in servo control lines thereof. Hydraulic lines for servo control of address travel spool have additional circuit including control unit, servo control lines and logical hydraulic OR valve with two inlet and one outlet taps. Hydraulic lines of servo control circuit included in additional loop are connected with inlet taps of hydraulic OR valve having outlet tap communicated with servo control taps of address travel spool.

EFFECT: provision of no-failure gear actuation in standing still dredger.

2 dwg

FIELD: mechanical engineering, particularly hydraulic systems for mobile machines.

SUBSTANCE: hydraulic system comprises hydraulic reservoir, controllable hydraulic pump with load-sensitive control slide, power hydraulic line protected with safety valve, main hydraulic distributor with three-position slide having one pressure supply means, two discharge lines, two working outlet means and line, which provides connection of each working outlet means with LS line, attached to control slide. The hydraulic system is provided with pressure control valve and with controllable reducing valve installed in LS line. Input and output of reducing valve are connected to hydraulic distributor and control slide correspondingly. Control line of reducing valve is linked to pressure control valve outlet. Inlet and discharge line of the pressure control valve are connected with power hydraulic line and with hydraulic reservoir correspondingly.

EFFECT: increased operational efficiency and reliability.

7 cl, 1 dwg

FIELD: earth-moving, mining, building machines and other wheeled and caterpillar handling periodically acting machines.

SUBSTANCE: device comprises working implement, main and balancing hydraulic cylinders, gas cylinder, main and additional working liquid distribution means. The piston cavity of balancing hydraulic cylinder is connected with gas cylinder. Additional distribution means may connect working cavities of main hydraulic cylinders one with another and with hydraulic pump during implement lifting.

EFFECT: increased working implement lifting speed without pump and system parameter change.

4 dwg

FIELD: mining industry, mechanical engineering, possible use in system for controlling caterpillar drive of mining machine.

SUBSTANCE: hydro-system contains pumps for caterpillar drive and pump, feeding system of working functions of machine, hydro-distributors for controlling caterpillar drive, driving hydro-motors and working mains, two controllable check valves and hydro-distributor for controlling system of machine working functions. Outlet channels of hydro-distributor for controlling system of machine working functions are connected to inlet channels of controllable check valves, which are connected between each other. Outlet channels of these valves are connected to working mains of driving hydro-motors and hydro-distributors for controlling caterpillar drive.

EFFECT: possible movement of mining machine in case of breakdown of driving pumps at the expense of influx of working liquid from pump driving system normally used for working functions of machine.

1 dwg

FIELD: earth moving machinery.

SUBSTANCE: invention relates to hydraulic drives of draw-booster gears of tractor-drawn scrapers. Proposed hydraulic drive contains pump, hydraulic tank, hydraulic cylinder, pressure valve connected in parallel with hydraulic cylinder, and hydraulic distributor. Hydraulic drive contains additionally hydraulic accumulator, time relay, check valve, pressure valve is provided with control line, and hydraulic cylinder has control arm engaging with two-position spool whose input is connected with pump and output, through time relay, with hydraulic accumulator and control line of pressure valve and with input of check valve whose output is connected to input of pressure valve.

EFFECT: provision of automatic continuous increase of adhesion weight of tractor of scraper when digging.

3 dwg

FIELD: earth-moving and transport machines, particularly blade assemblies having changeable width of cut.

SUBSTANCE: blade assembly comprises side sections and central section. The sections are provided with undercutting blades and are directly connected to bucket bottom. The central section is hinged to bucket bottom and is operated by rotation hydraulic cylinders through operation levers. Undercutting blades made as gussets are connected to inner edges of side sections from below. The gussets have supports to cooperate with central section in lower position thereof. Undercutting blades of central section are connected to outer side edges of central section. Undercutting gussets are provided with orifices to arrange fixers installed in lower parts of side sections so that they may cooperate with end switches. Position switches adapted to cooperate with operation levers of central section in central or extreme positions are mounted on bucket side walls. Hydraulic cylinders for central section rotation are linked in pairs to hydraulic cylinders for bucket operation. Lifting and lowering cavities of hydraulic cylinders are correspondingly communicated with raising and deepening cavities of hydraulic cylinders for central section rotation. Hydraulic drive for blade assembly includes hydraulically operated on-off three-way slide. The first outlet of the slide is united with the third one and is linked to raising cavity of hydraulic cylinder for central section rotation. Operational chamber and the first inlet of the slide are connected to outlet of pressure slide having output connected to lowering cavities of hydraulic cylinders for bucket operation. The second and the third inlets of on-off three-way slide are correspondingly connected to lifting cavities of hydraulic cylinders, which operate front bucket gate and lowering cavity of hydraulic cylinders for bucket operation.

EFFECT: decreased load to be applied to blade system during earth cutting as central section is in central and extreme positions, provision of automatic installation of above section in side blade plane and in extreme positions.

9 dwg

FIELD: mechanical engineering.

SUBSTANCE: group of invention relates to boom earth-moving, mine, construction and loading lifting-and-transporting machines of cyclic action. Proposed balancing system contains working equipment, boom hydraulic cylinders and balancing cylinder including hydraulic rod space and gas piston space connected with gas bottle, and distributors. According to first design version, hydraulic rod space of balancing cylinder is connected by hydraulic line with drain into hydraulic tank, and distributor of hydraulic liquid is installed for connecting in one position of spool, of boom hydraulic cylinders working spaces to each other with hydraulic pump. According to second design version, distributor is installed in system for connecting working spaces of boom hydraulic cylinders to each other and with hydraulic pump. According to third design version, rod space of balancing cylinder is connected with distributor installed for connecting, in one position of spool, of rod space of balancing cylinder with into hydraulic tank, and in other position, with hydraulic pump. Distributor is installed in hydraulic line of boom hydraulic cylinders for connecting, in one position of spool, of spaces of boom hydraulic cylinders to each other and with hydraulic pump.

EFFECT: increased capacity of machine owing to higher speed of lifting and lowering of working equipment.

5 cl, 6 dwg

FIELD: mechanical engineering, particularly earth-moving and construction equipment to be operated at low temperatures.

SUBSTANCE: device for hydraulic drive heating comprises heat engine and hydraulic pump kinematically connected with each other. Device also has liquid heat carrier circulation loop including heat accumulator. Heat pipe is connected to heat engine exhaust pipe through two-way valve. Heating member is arranged in tank and linked to heat engine generator.

EFFECT: increased simplicity and efficiency of hydraulic drive heating at negative ambient temperatures.

1 dwg

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