FIELD: machine building.
SUBSTANCE: invention refers to hydraulic control units for agricultural or building machines. A valve cluster to control at least one consumer is proposed, the consumer comprises two connections (A, B) to the consumer sides, connection (P) to a pump and connection (T) to a tank as well as four slide control valves (C1-C4) which are hydraulically controlled by relevant control connection (c1-c4). The first slide control valve (C1) couples the connection (P) to the pump and the first connection (A) to the consumer side, the second slide control valve (C2) couples the connection (P) to the pump and the second connection (B) to the consumer side, the third slide control valve (C3) couples the first connection (A) to the consumer side and the connection (T) to the tank and the fourth slide control valve (C4) couples the second connection (B) to the consumer side and the connection (T) to the tank. Additionally two servovalves (Y1, Y2) are provided to control the control connections (c1-c4) respectively of each pair of slide control valves (C1-C4).
EFFECT: reduced inner pressure losses and higher efficiency of consumer operation.
15 cl, 4 dwg
The technical field to which the invention relates.
The present invention relates to a valve block to control - in particular independently of the load - at least one consumer, such as a hydraulic cylinder, hydraulic motor or the like, the consumer. Application of the invention is particularly in the area of agricultural machinery, fitted units with hydraulic or hydraulic control, or the area of construction machinery.
The level of technology
From patent document EP 0473030 A1 is known a valve block of the specified type, in which between the two connections (connections) to the sides of the user, connecting to the pump and connecting to Baku, there are four Bolotnikova control valve with hydraulic control, which connect the connection to the pump and connecting to Baku with each of the connections to the sides of the consumer. Spool control valve between the connection to the pump and connections to the sides of the user can be managed in a deliberate way. When one of them opens, high pressure is supplied through the check valve in the first of the connections to the consumer side. Spool control valve between the second connection to the consumer side and connecting to the tank has a control input, which include what with the release of the first spool of the control valve so when the opening of the first spool of the control valve high pressure at its output also causes the opening of the second spool of the control valve. This provides the possibility that when the first spool control valve and the first connection to the consumer side of the hydraulic oil is supplied to the first cavity of the double-acting consumer, from the second cavity consumers hydraulic oil is drained to the tank via the second connection to the consumer side and the second spool control valve.
So even at idle the pump can maintain high pressure on the output side of the consumer and to fix it in the prescribed position between the first and second Bolotnikova control valves and two connections to the sides of the consumer, there are two non-return valve. Since the entire flow of the supply of hydraulic oil to the consumer must pass through one of the two check valves, a differential pressure on the back of the valves has a negative impact on the efficiency of the hydraulic machine, which is known to the valve block.
Known to the valve block can be used to supply to the consumer regardless of the pressure load through what is coming on the need to change the customer for the pressure load is given to the input of one of the check valves and fed through the signal line pressure load compensator for connecting to the pump block valve and optionally a regulator of the pump. So that in the neutral position compensator was securely locked or the pump was switched off, the pressure in the signal line pressure load must be guaranteed equal to the pressure in the tank in spite of the high pressures in other components of the valve block. To ensure this, the first and second spool control valves controlling the flow of the medium under pressure between the connection to the pump and connections to the sides of the consumer, as the main Bolotnikova control valves combined each respectively in the pilot valve with auxiliary Bolotnikova control valves, and auxiliary spool control valve each way valve in the locked position of the main spool of the control valve connects the signal line pressure load to the tank via the return line and drain leaks. The main spool control valves way valves must be of large dimensions, in order to let all the oil flow between the pump and the consumer with a small pressure drop. When combined with the auxiliary Bolotnikova control valve in the pilot valve required for them constructive space becomes even greater.
Disclosure of inventions
The objective of the invention is the creation of a block clap is new for controlling at least one consumer, which is minimized internal pressure losses and, accordingly, provide consumers with high efficiency.
The problem is solved due to the fact that in the valve block containing two nodes are connected (called connections) to the sides of the user, the node connection (referred to as connection to the pump and the node connection (hereinafter referred to as connecting to Baku, as well as four hydraulically controlled with appropriate management connection Bolotnikova control valve, of which the first spool control valve connects the connection to the pump and the first connection to the consumer side, the second spool control valve connects the connection to the pump and a second connection to the consumer side, the third spool control valve connects the first connection to the side consumer and connecting to Baku and the fourth spool control valve connects the second connection to the consumer side and connecting to Baku, provided by the first servo valve and the second servo valve to control the control connections respectively of each pair Bolotnikova control valves.
Due to the fact that this eliminates the need for conventional control of the third and fourth Bolotnikova control valves is the exploits of the outlet pressure of the first and second Bolotnikova control valves, no longer require check valves to maintain the required pressure difference between connecting to the consumer side and managing connection of the third or fourth spool of the control valve. With the exception of check valves also eliminates the associated pressure, which improves the efficiency of the consumer. Due to the fact that each servo valve controls not one, but two Bolotnikova control valves may also be maintained low flow rate of hydraulic fluid required to operate the servo-valves, and hence associated with the operation of the servo-valves power loss.
There are various possibilities for the submission Bolotnikova control valve to the servo-valves. According to the first simple example of executing the control connection of the first and fourth Bolotnikova control valves connected in parallel to the output of the first servo valve and the control connection of the second and third Bolotnikova control valves connected in parallel to the output of the second servo valve. This provides the ability to simultaneously open the first and fourth spool control valves and to lead the user double-acting in the first direction or a second and third spool control valves and lead POTREBITEL in the opposite direction.
According to the second exemplary embodiment further development of the invention can be implemented in a floating position of the consumer, where he can move under the action of external forces. This feature is due to the fact that for the first and second Bolotnikova control valves are respectively the first and the second switching valve, and the first switching valve selectively connects the control connection of the first spool of the control valve with the first servo valve or connecting to Baku, and the second switching valve selectively connects the control connection of the second spool of the control valve with the second servo valve or connecting to Baku. Through the first spool control valve depending on the position intended for him switching valve can control the flow of hydraulic fluid to the consumer or diversion from the consumer via the first connection to the consumer side. Through the coordinated activation of both servo-valves, the consumer can operate in two opposite directions.
The diverter valve can serve or valves as such, or way valves. When these are way valves, the first moves the second valve can selectively connect the first servo valve with one of the control connections of the two related Bolotnikova control valves, especially the first and third Bolotnikova control valve and the second valve may be selectively connect the second servo valve with one of the control connections of the two related Bolotnikova control valves, particularly the second and fourth Bolotnikova control valves. For example, the output pressure from the first servo valve can be transmitted through the first valve, on the one hand, on the third spool control valve to provide exhaust hydraulic fluid from the first connection to the consumer side, and simultaneously translate the second one way valve in the position in which the outlet pressure of the second servo valve is transmitted to the control connection of the second spool of the control valve to supply hydraulic fluid to the consumer via the second connection to the consumer side.
Preferably required for switching the first and second switching valves outlet pressure servo-valves below the output pressure required to open Bolotnikova control valves. Thus, coordinated by increasing the pressure at the output of the two servo-valves you switch both of the switching valve. This prevents the switching of the change-over valves p and open Bolotnikova control valves.
Preferably, the two changeover valves contain each of the second control input to which the return stroke leads him out, so the available output pressure counteracts the pressure applied to the first control input. This pressure is fed backward to the second control output, ensures the retention of the switching valve in the position it occupies in the absence of pressure, although the pressure at the first control input. So that while applying pressure on both the switching valve they do not change their position.
Preferably, the servo-valves made in the form of proportional pressure reducing valves.
To enable control of the connected consumer, regardless of the load preferably between connection to the pump and the first and second Bolotnikova control valves built individual pressure control valve controlled by the pressure in one of the connections to the side of the consumer.
Using tperemoga check valve between the control input of the individual differential valve and each of the connections to the consumer side at the individual differential valve may be transferred to the highest pressure in the connections to the sides of the user without changing the pressure in the other under the notes to the side of the consumer. When the pump is switched off check valves prevent flow under pressure from a single connection to the consumer side to the other through the signal line load pressure, so that the user cannot inadvertently succumb to the influence of the external load. Unlocking one of the check valves also allows you to properly convey to the individual differential valve pressure discharged from one of the connections to the sides of the consumer.
To control the unlocking of check valves in the best case scenario can be used an output signal of one of the servo-valves.
As mentioned above, in a stationary position should be prevented uncontrolled increase in pressure at the control connection of the individual differential valve in order to avoid false regulating the pump or servo-valves. To ensure this, preferably otpiranii check valves are designed so that in its shut-off position connects the control connection of the individual differential valve connecting to Baku. Because otpiranii check valves shall be designed to permit only a small part of the flow through the first-fourth spool control valves, they can be made small in size and, accordingly, small design, the structural space is also running message Manager connect individual differential valve connected to the tank through aceramic check valves.
A check valve built into the individual pressure control valve, allows for the failure of the pump to avoid a sudden pressure drop at the connection sides of the consumer and therefore unmanaged moving consumer under load.
The subject of the invention is also a tractor equipped with a valve block of the type described, which can be connected to the unit with hydraulic adjustment or hydraulic actuator, such as a plow or cutter bar working body.
A short list of drawings
Other features and advantages of the invention will be clear from the following description of embodiments of the invention with reference to the drawings. In the drawings:
figure 1 depicts a hydraulic circuit of a valve system according to the first exemplary embodiment of the invention,
figure 2 schematically depicts in the context of one of the valves of the system of figure 1,
figure 3 depicts a hydraulic circuit of a valve system according to the second exemplary embodiment of the invention,
figure 4 depicts a hydraulic circuit of a valve system according to the third exemplary embodiment of the invention.
The implementation of the invention
Figure 1 shows the hydraulic circuit diagram of the valve block according to the first exemplary embodiment of the invention. The valve block can be mounted on the tractor front or be the and for connection to him as a consumer of the Executive cylinder or motor replacement front or rear of the working unit, such as cleaning brush, blade ploughs, plough, sectional cutting or reaping machine or similar units.
Shown in the drawings, the valve block is connected to four lines, which are shown as parallel lines in the lower part of the drawings, namely going from a not shown pump line P high pressure, leading to the tank line T zero pressure to the line control pressure Px and to the signal line LS pressure load. To these four lines P, T, RH, LS can be connected in parallel several blocks valves to serve multiple consumers attached unit or control unit with multiple degrees of freedom.
The exhaust from the line P high-pressure branch P1 passes through the individual pressure control valve C5, controlled by the pressure in the signal line LS pressure load to the two way valves C1 and C2 with hydraulic control, equipped with return springs. Two connections And, to the sides of the consumer connected to the outputs of the two way valves C1, C2. Way valves are made with a locking seat and are arranged so that when excessive pressure in the connection to the consumer side of the body of each valve is pressed against the saddle. Thus, way valves C1, C2 absolutely tightly holding high pressure in one of the under the of Lucene to the sides of the consumer, which may occur when an external load acts on the connected consumer. An example is the load on the hydraulic cylinder, which in traffic or when maneuvering holds hung on the tractor plow in the raised position above the ground or when the plow pushes it down to keep it at the desired depth.
The other two valves NW, C4 interconnect connections to the sides of the consumer with the T line of zero pressure.
In figure 1 all standard valves C1-C4 shown in the locked position. When opening a way valves C1 and C4 in one cavity of the double-acting consumer, connected to the connections a, b, may be supplied hydraulic fluid through the connection a and the second cavity of the consumer through a connection In may derive a corresponding amount of hydraulic fluid. If open way valves S2, Sz, hydraulic fluid is delivered to consumers through the connection and is discharged into the tank through the connection A. Throughput cross-section way valves C1-C4 continuously changes in the function of the control pressure received at the control connection C1-C4 of the respective valves.
Two proportional pressure reducing valve Y1, Y2 serve as servo-valves to create this control pressure. Proportional the e pressure reducing valves Y1, Y2 is connected to the line control pressure Px and T line of zero pressure and have each managed connection U1, U2, in which pressure is continuously adjusted using electrical means between the pressures in the lines Px, and So Proportional pressure reducing valve Y1 controls the line pressure 1 servo, which connects the control connections C1, C4 valves C1 and C4. Similarly proportional pressure reducing valve Y2 controls the pressure in line 2 of the servo, which connects the control connection C2, C3 valves C2 and C3.
Otpiranii check valves R1, R2 are each a corresponding control connection G1 or G2, which is connected with the line 1 or 2 servo, and the input connected to the connection or to the consumer side, and two outputs, which are connected with a line of T-zero pressure or through branches LS1 or LS2 and switching valve W1 with the signal line LS pressure load.
The second switching valve W2, built-in signal line LS pressure load, selectively either to apply pressure on the control connection C5 individual differential valve C5, or to submit it to another not shown in the drawing, the valve block, connected parallel to the lines P, T, RC, LS, to regulate the external pump, Pete the existing line R high pressure.
Figure 1 check valves R1, R2 shown in neutral position in which both the output of each valve are connected. Due to this pressure is absent in the signal line LS pressure load. Accordingly, the individual pressure control valve C5 locked, and the external pump is turned off. Accidental leakage, due to which hydraulic fluid can get into the signal line LS pressure load may not lead to high blood pressure.
When one of the two pressure reducing valves, such as valve Y1 is opened, the pressure in line 1 of the servo increases and way valves C1, C4 are opened proportionally to the pressure. The output pressure differential valve C5 is supplied to the connection And, at the same time via connection To a fluid medium under pressure can flow to the tank. High pressure in line 1 of the servo leads to the switching valves R1 in a position in which it connects the connection And branch LS1 and simultaneously interrupts the connection of the branch LS1 with a line of T-zero pressure. When this signal line LS pressure load passes the pressure that is present on the connection A. Differential valve C5 in a known manner regulates the flow of fluid from the pump to the connection a, so that a constant pressure difference is th between the output of the differential valve C5 and managing input, associated with the signal line LS pressure load. This pressure difference is essentially equal to the pressure drop across the spool valves S1, while there is a direct linear relationship between the reduced cross section of the spool valves S1 and volumetric flow supplied to the consumer via the connection A.
If due to any failure of the pump decreases the line pressure P high pressure or acting on consumer external load causes the pressure in the connection And to the side of the consumer exceeds the line pressure P, built-in check valve 3 causes the locking differential valve C5. Consequently, in such cases the opposite happens, consumer movements, and it is locked in the position reached.
Figure 2 schematically shows a sectional otheremail check valve R1 or R2 according to a preferred exemplary embodiment. In the housing 10 is formed a groove with multiple speed zones of different diameters. In the wide part of the groove on the right side of figure 2 has a movable piston 11. On the rear side 12 of the piston 11 applies the line pressure control pressure Px. Front side 13 of the piston limits the cavity 14 that is associated with the T line of zero pressure. Screwed into the groove of the housing 10 liner 15 includes a protrusion 17, when the in the notch 16 on the front side 13 of the piston. The protrusion 17 centers coil spring 18 which presses the piston 11 to the right against the action of the control pressure acting on the back side 12.
The insert 15 has an axial groove 19 and at least three radial grooves 20, 21, 22, intersecting the axial groove 19. The groove 20 extends into the cavity 14, the groove 21 communicates with the branch LS1 or LS2 signal line LS pressure load, and a groove 22 communicates with the connection or to the side of the consumer. In the axial groove 19 is installed with the possibility of axial movement of the rod 23. Shown in figure 2 the position of the narrow tip 24 of the rod is located within the area of the axial grooves 19, which connects the grooves 20, 21, so that the signal line LS load pressure communicates with the cavity 14 and the pressure therein is maintained equal to the pressure in the tank, i.e. zero. The spring 25 and, in that case, the excess pressure in the connection or to the consumer side keep the ball 26 is pressed against the seat 27 of the valve between the grooves 21, 22. Thus, the ball 26 and seat 27 of the valve form a check valve, which is capable of maintaining a high pressure connection And or to the side of the consumer, even in the absence of pressure in the signal line LS load pressure and communicating with the groove 21.
Under the positive action of the control pressure on the rear sides of the 12 of the piston 11 is moved to the left and catches with a rod 23. While the section 28 of the base of the rod 23, the diameter of which corresponds exactly to the diameter of the groove 19, is pushed into the connecting grooves 20, 21 plot of the axial grooves 19 and locks it. In the interrupted communication between the signal line LS pressure load and the cavity 14. In conclusion, the tip 24 abuts against the ball 26 and removes it from the seat 27 of the valve. When this check valve opens and the signal line LS load pressure enters the pressure that is present in the connection or to the side of the consumer. Due to the fact that the rod 23 is initially locks the message with the cavity 14 to unlock the valve, eliminates uncontrollable outflow of fluid under pressure from the connection or to the side of the consumer to the tank through valve R1 or R2.
In the drawing it is seen that the cross-section of the piston 11 is many times larger than the diameter of the ball 26 so that a relatively low control pressure to the rear side 12 of the piston sufficient to move the ball 26 from its seat 27, even when it is pressed against the seat 27 of the high pressure connection to the consumer side.
Figure 3 the valve block shown in the second exemplary embodiment of the invention. Line P, T, RC, LS, valves C1-C4, Y1, Y2 and R1, R2, and individual pressure control valve C5 are the same as in figure 1 and not described again. Significant ex is the difference between an example run in figure 3 from the example of figure 1 is an additional way valves V1, V2. In the shown figure 3 neutral way valve V1 connects the managed connection U1 pressure reducing valve Y1 and control connections C3, v2 way valves C3 and V2, and control connections C1, G1 way valves S1, R1 T line of zero pressure.
When applying high pressure at the control connection v1-way valve V1 is switched to a position in which it connects the control connection C1, G1 reducing valve Y1 and management connections C3, v2 T line of zero pressure. Similarly way valve V2 in the absence of pressure on it connects the managed connection N2 pressure reducing valve Y2 and control connections C4, v1 way valves C4 and V1, and control connections C2, G2 way valves C2, R2 T line of zero pressure. In contrast to this position when applying high pressure at the control connection v2 connects the pressure reducing valve Y2 and control connections C2, G2, and line T is zero pressure and control connections C4, v1.
When both the pressure reducing valve Y1, Y2 are closed, locked also way valves C1-C4. When you open pressure reducing valve Y1 and pressure on its managed connection N1 increases, it leads first to the opening of the valve C3, so that fluid under pressure can be discharged from the consumer is Italia through the connection And to the side of the consumer, and to the switching valve V2 into its state of high pressure. Now, when also offer pressure reducing valve Y2, this leads to the opening of the valve C2, so that the connection to the consumer side there is high pressure. At the same time switches the valve R2, so that high pressure is distributed to the signal line LS pressure load and controls the operation of the individual differential valve C5. Thus, the adjustable independently of the load flow of fluid under pressure is delivered to consumers through the connection and the corresponding flow is diverted from the consumer to the tank through the connection A.
If pressure reducing valves Y1, Y2 are opened in reverse order, high pressure is supplied to the connection a and connection communicates with the T line of zero pressure, and the consumer is in the opposite direction.
Figure 3 shows two control input at each pilot valve V1, V2. As mentioned above, one input, v1 or v2 is connected with the output of another way valve V2 or V1. On the other entrance vT or v2' receives the output pressure of its own way valve V1, V2. When you open both the pressure reducing valve Y1, Y2, influence of pressure on both managers connect v1 and v2 or v1 and v2' are mutually compensated, and way valves V1, V2 remain in shown in F. the D.3 neutral position. As a consequence, the valve C3, C4 are opened and the valves S1, S2 remain closed. When this is associated with the connection And the consumer is in a floating state, that is, he may succumb to the influence of external loads such as the weight of the raised plow, and in this case through one of the connections And, In the hydraulic fluid can be sucked from the tank and through another, it can be discharged into the tank. Floating position provides the opportunity for units, such as sweeping brush or blade ploughs, when processing passively follow the contour of the surface.
Above we have considered the possibility of using the valve block in figure 3 to operate the double-acting consumer, associated with the two connections a And C. Alternative possibility is the independent control of two consumers simple steps, when the control pressure required for switching valves V1 or V2 is lower than that required to open way valves C1-C4. So, for example, required to switch way valves V1, V2, control pressure is about 3 bar, and way valves C1-C4 begin to open only when the control pressure of 5 bar or higher and fully opened when the control pressure of 20 bar.
For retracting the consumer easy on istia over the connection And you must open way valve C3, while running the valves C1, C2, C4 remain closed. When the pressure reducing valve Y1 is opened, a Y2 remains closed, valve V2 is switched, as soon as pressure on the managed connection way valve Y1 is greater than 3 bar. Since the valve Y2 is closed, it does not affect way valves C2 and C4. Valve C3 is opened as soon as the pressure on the managed connection valve Y1 exceed 5 bar. During this time the control connection way valve S1 is retained by the valve without pressure, so that the valve S1 is closed.
To advance through consumer connection a, it should be possible to open the valve C1, while the valves C2-C4 remain closed. This is achieved by beginning on a managed connection U2 valve Y2 is configured pressure, for example, 4 bars. This entails switching valves V1, but not enough to open the valve C4. Now valve V1 connects the managed connection U1 connection C1, so that by opening the servo valve Y1 can be opened way valve C1.
In exactly the same way the consumer can be controlled by connection Century. This is understandable self-explanatory due to the symmetry of the valve block.
Figure 4 block to apanov shown in the third exemplary embodiment. It differs from the valve unit of figure 1 that the addition of two switching valves F1, F2 with hydraulic control. Switching valves F1, F2 are built to flow respectively in front of and control connections C1, C2 way valves C1, C2 in order to connect a controlled reducing valve Y2 connection C1 or managed connection U1 valve Y1 or T line of zero pressure, and to connect a controlled reducing valve Y1 connection C2 or managed connection U2, or T line of zero pressure. Switching valves F1, F2, and way valves V1, V2 in figure 3 serve to provide the possibility of opening two way valves C3, C4, control the exhaust flow from the consumer, while running the valves C1, C2, controlling the pressure supply to the consumer, remain closed, which provides a floating state of the consumer.
When, for example, on a managed connection N2 pressure is controlled through this connection switching valve F1 connects the control connection C1 connecting U1. When the pressure reducing valve Y1 is open, while the valve Y2 is closed, as in the exemplary embodiment of figure 1, increases pressure on the control connections C1 and C4 and is associated with the connection and the user double-acting bring the SJ in the first direction. When the valve Y2 is open and the valve Y2 remains closed, open way valves C2, C3 and the consumer is in the opposite direction. However, if simultaneously open both the pressure reducing valve Y1, Y2, both the switching valve F1, F2 are switched before the pressure at the control connection way valves C1, C2 becomes high enough to open them. Due to this, the control connections are connected with a line of T-zero pressure and the valves S1, S2 remain closed, while the valves C3 and C4 are opened as soon as the pressure on their managers connections, C3, C4 will be sufficient.
1. The valve block for controlling at least one consumer, containing two connections (a, b) to the sides of consumer connection (P) to the pump and connection (T) to Baku, as well as four hydraulically controlled with appropriate management connection Bolotnikova control valve (C1-C4), of which the first spool control valve (C1) connects the connection (P) to the pump and the first connection (A) to the consumer side, the second spool control valve (C2) connects the connection (P) to the pump and a second connection (In to the consumer side, the third spool control valve (C3) connects the first connection (A) to the consumer side and the connection (T) to Baku and che the fourth spool control valve (C4) connects the second connection (In) to the side of the consumer and the connection (T) to Baku, differentthat contains the first servo valve (Y1) and the second servo valve (Y2) to manage and control connections (C1-C4), respectively, each pair Bolotnikova control valves.
2. The valve block according to claim 1, characterized in that the control connection (C1, C4) one pair Bolotnikova control valves, particularly the first and fourth Bolotnikova control valves (C1; C4)connected in parallel to the output (N1) of the first servo valve (Y1), and the control connection (C2, C3) another pair Bolotnikova control valves, particularly the second and third Bolotnikova control valves (C2; C3)connected in parallel to the output (V2) of the second servo valve (Y2).
3. The valve block according to claim 1, characterized in that the first and second Bolotnikova control valves (C1, C2) are respectively the first and second switching valves (F1, F2, V1, V2), and the first switching valve (F1, V1) selectively connects the control connection (C1) of the first spool control valve (C1) with the first servo valve (Y1) or connection (T) to the tank, and the second switching valve (F2, V2) selectively connects the control connection (C2) of the second spool control valve (C2) with the second servo valve (Y2) or connection (T) to the tank.
4. The valve block according to claim 3, characterized in that p is pout switching valve is the first directional control valve (V1), which selectively connects the first servo valve (Y1) with one of the control connections (C1, C3) two related Bolotnikova control valves, in particular the first and third Bolotnikova control valves (C1, C3), and the second switching valve is the second directional control valve (V2), which selectively connects the second servo valve (Y2) to one of the control connections (C2, C4) two related Bolotnikova control valves, particularly the second and fourth Bolotnikova control valves (C2, C4).
5. The valve block according to claim 3 or 4, characterized in that the first switching valve (F1, V1) contains the first control input (v1)associated with the second servo valve (Y2), and the second switching valve (F2, V2) contains the second control input (v2)associated with the first servo valve (Y1).
6. The valve block according to claim 5, characterized in that required for switching the first and second switching valves (V1, V2; F1, F2) output pressure servo-valves (Y1, Y2) output below the pressure required to open Bolotnikova control valves (C1-C4).
7. The valve block according to claim 6, characterized in that both the servo valve (Y1, Y2) can be controlled simultaneously.
8. The valve block according to claim 6, characterized in that the first and second switching valves (V1, V2) output is made with the return stroke of the second control is usamu input (v1', v2'), so the available output pressure counteracts the pressure applied to the first control input (v1, v2).
9. The valve block according to any one of claims 1 to 4, 6-8, characterized in that the servo-valves (Y1, Y2) are proportional pressure reducing valves.
10. The valve block according to any one of claims 1 to 4, 6-8, characterized in that the connection (P) to the pump and the first and second Bolotnikova control valves (C1, C2) built individual differential valve (C5), controlled by the pressure in one of the connections to the side of the consumer.
11. The valve block of claim 10, characterized in that between the control input of the individual differential valve (C5) and each of the connections (a, b) to the consumer side there otheremail check valve (R1, R2).
12. The valve block according to claim 11, characterized in that otpiranii check valves (R1, R2) can be unlocked by one of the servo-valves (Y1, Y2).
13. The valve block according to claim 11 or 12, characterized in that otpiranii check valves (R1, R2) is designed so that in its shut-off position connects the control connection of the individual differential valve (C5) with connection (T) to the tank.
14. The valve block according to any one of claims 1 to 4, 6-8, 11, 12 characterized in that the individual differential valve (C5) integrated non-return valve (3).
15. The path is R, provided with a block valve, as claimed in any of the preceding paragraphs, differentthe fact that he made with the possibility of connection to the valve block Assembly with hydraulic adjustment or hydraulic drive, in particular a plow or cutter bar.
FIELD: physics; control.
SUBSTANCE: disclosed group of inventions relates to a hydraulic control system for working machines. The hydraulic control system has a pump, a tool actuator, a tool control valve configured to control the flow of pressurised fluid fed to the tool actuator, and a controller. The controller includes a feed-forward control map which responds to the intended change in the required flow rate with the possibility of relating the tool movement request to the change in discharge flow rate of the pump, and operably connected to the tool control valve and the pump. The controller can further be configured to receive a tool movement request. The controller can further be configured to estimate changes in the required flow rate of the tool control valve associated with the tool movement request. The controller can also be configured to generate instructions for adjusting the discharge flow rate of the pump based on the intended change in the required flow rate to execute the tool movement request. Also disclosed are a method of controlling tool movement and a machine having said hydraulic system.
EFFECT: providing feed-forward control to change supply of a liquid before the need thereof arises.
19 cl, 3 dwg
FIELD: machine building.
SUBSTANCE: invention relates to operation of working machine hydraulic system. Proposed method comprises the steps that follow. Equipment configuration is retained at definite orientation to measure first pressure in hydraulic drive chamber (56, 58) connected with equipment at preset position. First signal is compared with first pressure magnitude. First functional relationship (71) is selected from multiple memorised functional relationship if said first signal is higher than first pressure magnitude. Second functional relationship is selected from multiple memorised functional relationships if said first signal is lower than first pressure magnitude. Hydraulic drive is controlled on the basis of selected functional relationship. Note here that each of multiple memorised functional relationships is associated with different category of equipment configuration.
EFFECT: possibility to modify relationship between hydraulic drive speed.
9 cl, 3 dwg
FIELD: machine building.
SUBSTANCE: invention refers to machine-building hydraulics, and namely to hydraulic actuators of mobile machines and hydraulic plants of cyclic action with several actuating mechanisms. The invention proposes a channel of multiflow hydraulic actuator, which is intended for supply of a working liquid flow to pressure cavities and consists of several in-series connected double flow cavities having the possibility of disconnecting their inlets and outlets. Besides, on the flow inlet side, each double flow cavity is connected to the corresponding pressure cavity. Besides, in ties between pressure and overflow cavities there additionally installed are check valves directed with their outlets to pressure cavities. And outlets of double flow cavities are connected through inlets of check valves to the corresponding pressure cavities. Besides, the outlet of the last double flow cavity serves as an inlet for the other flow.
EFFECT: proposed invention allows supplying two independent flows via one hydraulic channel with several pressure cavities, as well as simplifying a hydraulic actuator and reducing dimensions of hydraulic equipment.
2 cl, 8 dwg
SUBSTANCE: ripper contains bidirectional liquid energy accumulator, underlying machine, framed suspension with hinged ripper tip mounted on it and elastic system. At that elastic system contains the main cylinder with piston at the rod mounted on the frame and power-operated rod passing through articulated rod and ripper tip. At that the main cylinder is divided by partition into two independent cylinders equipped with main and auxiliary cavity. In auxiliary cavities of cylinders there are installed pistons connected to hollow rods which interact with power-operated rods passing through the main cavities and fixed at inners walls of travelling barrel covering the main cylinder which is connected to ripping rack through a hinge. Auxiliary cavities of each cylinder are equipped with openings from rod side and free piston side, which interact with reversive hydro pump through bidirectional hydraulic locks and pipelines. Besides elastic system is equipped with auxiliary reversive hydro pump which outlet is connected though bidirectional hydraulic locks to openings in walls of the main cylinder cavities while its inlet is connected to pipeline with a tank for liquid storage.
EFFECT: increasing efficiency of soil ripping due to reduction of pulling force and dynamic loads acting on underlying machine and their transfer to the area of soil destruction within the wide range for forced oscillation frequencies of actuating device.
FIELD: engines and pumps.
SUBSTANCE: proposed device comprises control means and detection means. Control means serve to control engine output power for driving the machine. Detection means allow identification of reverse conditions, motion speed and preset gear ratio. In reverse, control means vary output power by control over engine shaft rpm.
EFFECT: fuel savings.
3 cl, 7 dwg
SUBSTANCE: loader boom hydraulic cylinder is proposed, comprising a body, lower and upper covers of the hydraulic cylinder, a braking device and a check valve. At the same time the check valve is made in the form of a cylindrical cap with a spring inside and an inlet nozzle installed in a separate body fixed on the hydraulic cylinder body. Besides, the specified valve communicates with the piston cavity of the hydraulic cylinder by means of an additional hole made in the hydraulic cylinder body.
EFFECT: elimination of piston strikes against a hydraulic cylinder cover as a loader boom is installed in a position of excavating start at the level of the support surface.
SUBSTANCE: collector of bulldozer equipment of an earth mover is proposed, which comprises a body with radial holes for supply and discharge of working fluid, connected as capable of rotation and axial displacement with a blade frame. Inside the body there is a part of a fixed core, installed with a gap into eyes of the blade frame and stopped by the other part against rotation in a lever of a blade lifting mechanism. Besides, the body is equipped with a leash element with a through slot. The fixed core is made with circular grooves for installation of seals and circular bores, communicated with radial holes of the body and channels of supply and discharge of working fluid in the lever of the blade lifting mechanism and axial channels for transfer of working fluid from the lever of the blade lifting mechanism to the blade frame. At the same time the specified axial channels are closed with plugs with seals at the end side of the core and are pressed with a flange on bolts. Connection of the body with the blade frame is carried out by means of a threaded element screwed into the blade frame and stretching via the central axial hole installed into a cut slot of the leash element, a stop made in the form of a four-face rod with a base in the form of a square, with a support site perpendicular to its faces. Between the leash element and the stop in the radial direction there is a gap, the value of which is more than the total value of gaps between the outer surface of the core and inner surfaces of the blade frame eyes. Height from the surface joined with the blade frame to the support site of the stop is more than the thickness of the leash element, and the width of the stop is less than the width of the slot of the leash element.
EFFECT: increased operational resource of a collector due to elimination of direct transfer of loads from a movable part of a machine towards a fixed one.
SUBSTANCE: working mechanism comprises basic mechanism, cab and cab manipulator articulated with basic mechanism designed to change the cab position relative to said basic mechanism. Note here that cab manipulator is equipped with at least one hydraulic actuator to turn the cab about horizontal axis relative to basic mechanism. Note here that said cab id coupled with said manipulator to allow the turns actuated by tilt control hydraulic drive. Besides, said working mechanism includes the cab emergent exit system incorporating one emergent tilt valve for cab tilt adjustment device designed to orient the cab in normal position in emergent exit.
EFFECT: reliable escape of engineman cab.
9 cl, 3 dwg
SUBSTANCE: device to control lifting-digging mechanisms comprises a compressor, an oil and moisture separator and a receiver, pneumatically serially connected to each other. At the same time the outlet of the receiver is pneumatically connected to inlets of adsorbers with evenly distributed heaters, and outlets of adsorbers are pneumatically connected to a load. The compressor is equipped with a suction filter, comprising a casing with a conical bottom, a nozzle of cleaned air exhaust, a condensate extractor, installed in the bottom hole, a reflecting partition and a nozzle of cleaned air supply. The filter casing is made in the form of a double-layer jacket with an air cavity connected by the nozzle of heating regenerated air supply by means of a pipeline and a control valve with adsorbers by a nozzle of heating regenerated air discharge into atmosphere. Evenly distributed heaters in adsorbers are separated by partitions from adsorbent grains. At the same time each of the partitions is made of a bimetal. Besides, the material of the bimetal at the side of the heater has a conductivity ratio that is 2.0-2.5 times higher than the material at the side of adsorbent grains.
EFFECT: maintenance of efficient operation during long-term operation of a control device of lifting-digging mechanisms, by provision of specified quality of compressed air drying due to elimination of thermal damage of adsorbent grains.
SUBSTANCE: fluid-controlled slide valve is arranged between load mechanism hydraulic cylinder rod end and pressure valve inlet line. Control chamber of said valve is communicated with front shutter drive hydraulic cylinder chamber for it to be closed.
EFFECT: independent operation of hydraulic cylinders.
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.
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.
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.
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.
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.
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.
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.