Electric hydraulic flow control with integral flow regulation

FIELD: engines and pumps.

SUBSTANCE: flow control and control method of the control is intended for hydraulic system of working machine. Control includes housing with inlet hole and outlet hole, main bypass valve located inside the housing between inlet and outlet holes and including the forward end and hollow end. Valve has the possibility of being moved between open position in which the liquid flows from inlet hole to outlet hole, and closed position in which the liquid flow between inlet and outlet holes is locked. In addition, control has auxiliary valve having the possibility of being moved so that they can selectively attach hollow end of the main bypass valve to the drain, thus influencing the movement of the main bypass valve between open and closed positions. Besides, flow control includes solenoid mechanism intended to move auxiliary valve. Position of auxiliary valve depends on liquid pressure in inlet hole.

EFFECT: higher reliability of hydraulic system.

10 cl, 3 dwg

 

The technical field to which the invention relates.

The present invention relates to electro-hydraulic flow control valve, in particular for electro-hydraulic flow control valve with adjustable flow.

The level of technology

In such working machines, such as excavators, loaders, bulldozers, graders, and other types of heavy vehicles, use one or more hydraulic actuators to perform a variety of tasks. These actuators are hydraulically connected with the pump mounted on the working machine, which delivers the fluid under pressure in the cavity of the actuator. Typically, the pump and the actuator are connected via an electro-hydraulic valve system for controlling flow of fluid under pressure entering the cavity of the drives in and out of them. The flow entering the cavity drives and leaving them fluid is directly related to the performance of the drives.

In hydraulic systems working machines, which hydraulically connect multiple actuators with a common pump, during operation of the actuator can cause undesirable pressure fluctuations. In particular, the pressure of the fluid supplied to one drive, it may desirable to vary with the consumption of other drive fluid from the same hydraulic system or displacement by another drive fluid in the same Hydra is a symbolic value system. If the electrohydraulic valve system is controlled by the area of a carrying section, the pressure fluctuations can cause unstable and/or unexpected movement of the actuator. In particular, in order to move the actuator at a given speed, the element electro-hydraulic valve system can be moved so as to open a channel for fluid on the value of a given area of a carrying section. Given the area of a carrying section is determined by the settlement of supplied pressure, which corresponds to the desired flow rate and the resulting performance of the drive. When the pressure of the fluid supplied to the electrohydraulic valve system deviates from the calculated flow rate and the speed of the drive also deviate from the desired values.

One way to improve the management of flow of the fluid supplied to the actuator described in US 5878647, where the hydraulic system contains two filling valve, pump with volume regulation and hydraulic drive. Filling valves connecting the said pump or piston cavity, either with the rod cavity of the hydraulic actuator, which causes the movement of a hydraulic actuator. Each of these nutrients contains valves to compensate for the pressure, which determines the pressure at the outlet of nutrient valves and Pade is the largest of these pressures on the control input of the pump with a volume control, to affect the operation of the pump so as to make the pressure drop for each nutrient valves approximately constant, thereby bringing the pressure, and the resulting fluid flow through each of the solenoid valves to the calculated pressure and desired flow rate.

Although the mechanisms of pressure compensation, described in US 5878647 can reduce fluctuations in pressure within the hydraulic system, they can work with delay, to be expensive, and reduce the reliability of the hydraulic system. In particular, the mechanisms of pressure compensation according to US 5878647 to act so as to affect the fluid pressure directed through the filling valves, only after determining undesirable pressure drop on them. In addition, even after the compensation mechanisms of pressure change characteristic of the pump, the impact from this change may not be realized immediately. By the time when an undesirable pressure drop was adjusted to match the calculated pressure drop, the flow rate of the fluid supplied to the actuator may already deviated from the required flow rate for a considerable period of time. Additional components of compensation mechanisms pressure can increase the cost and reduce the unreliability of Hydra is velicescu schema.

The flow regulator according to the present invention is designed to solve the above problems.

Disclosure of inventions

One object of the present invention is a nutrient flow control valve that includes a housing with an inlet and outlet. The flow regulator also contains the main gate valve, located inside the housing between the inlet and outlet ports. The main gate valve has a nasal and hollow ends and configured to move between an open position in which fluid flows from the inlet to the outlet, and a closed position in which fluid flow is blocked between the inlet and outlet ports. The flow regulator also includes an auxiliary valve arranged to move so as to selectively connect the hollow end of the main flow valve with drain, thereby affecting movement of the main flow valve between the open and closed positions. In addition, the flow control valve includes a solenoid mechanism for moving the auxiliary valve, the position of which depends on the fluid pressure in the inlet port.

Preferably solenoid mechanism configured to move the pilot valve to the preset value, thereby vyzyvaemsya main by-pass valve by a specified amount, determined by the calculation fluid pressure in the inlet port.

Preferably the auxiliary valve is arranged to move when the pressure of the fluid in the inlet so as to maintain essentially constant the flow rate of the liquid flowing from the inlet to the outlet.

Preferably in the auxiliary valve is made the Central hole.

Preferably the solenoid mechanism includes an electromagnetic coil, the armature and connected with it the stud, anchor and stilettos made the Central hole communicated with the Central hole of the auxiliary valve.

Preferably largely bypass valve is made the Central hole communicated with the Central hole of the auxiliary valve, while in the Central hole of the main by-pass valve is a check valve.

Another object of the present invention is a method of controlling nutrient flow regulator. The method includes a stage on which direct the flow of fluid under pressure to the main flow valve on the flow regulator, and the stage at which electronically move the auxiliary valve to hydraulically move the main gate valve to a predetermined position and to allow fluid p is d pressure to flow through the flow regulator to the desired speed. The method also includes the step, which automatically adjust the position of the auxiliary valve when the pressure of the fluid so as to maintain the desired flow through the flow regulator.

Preferably specified position determined on the basis of the estimated fluid pressure.

Preferably the method further includes steps that allow fluid to pass through the auxiliary valve during its movement; allows fluids to pass through the main bypass valve; and restrict the flow of fluid through the main valve in one direction.

Brief description of drawings

Figure 1 schematically shows a side view of the working machine according cited as an example of a variant embodiment of the invention;

figure 2 schematically shows an exemplary embodiment of the hydraulic system of the working machine shown in figure 1;

figure 3 shows a section of the regulator of the hydraulic system shown in figure 2.

The implementation of the invention

Figure 1 shows an example of the working machine 10, which may be a self-propelled machine designed to perform some type of work related to this industry, such as mining, construction, agriculture, transport or any other branch of industry is nasty. For example, work machine 10 may be a machine designed to move soil, such as excavator, bulldozer, loader, excavator-type backhoe, grader, dump truck, or any other machine that moves soil. Work machine 10 may also be a stationary machine such as a generator set, a pump, or any other suitable manufacturing production machine. Work machine 10 may include a frame 12, at least one work tool 14, and the hydraulic cylinder 16 connecting a work tool 14 to the frame 12. Alternatively, instead of the hydraulic cylinder 16, the machine may include a hydraulic motor.

Frame 12 may include a structural element that supports the movement of the working machine 10. The frame 12 may represent, for example, a stationary base frame connecting the energy source (not shown) with a traction device 18, the movable frame element lever system, or any other known frame.

Work tool 14 may be a device used when performing tasks. For example, the tool 14 may be a knife, a bucket, a shovel, a Ripper, platform truck, drive unit, or any other known device for performing tasks. Work and is strument 14 may be connected to the frame 12 by a hinge 20, a lever system with a hydraulic cylinder 16 forming element lever system, or any other suitable method. The working tool 14 is made to rotate, rotation, sliding, rolling or moving relative to the frame 12 by any known method.

As shown in figure 2, the hydraulic cylinder 16 may be one of the components of the hydraulic system 22, which act together to move a work tool 14. The hydraulic system 22 may include a reservoir 24, a source 26 of fluid under pressure, a relief valve 28, the piston cavity, the make-up valve 30, the piston cavity, a relief valve 32 rod end, charging valve 34 rod end, a drain valve 36, the piston cavity, a drain valve 38 rod end, nutrient controller 40 flow piston cavity and nutritious controller 42 thread the rod end. The hydraulic system 22 may include additional components, such as, for example, pressure sensor, temperature sensor, position sensor, control unit, battery, and other known components of the hydraulic system.

The hydraulic cylinder 16 may include a pipe 46 and located inside the node 48 of the piston. One of these elements may be hinged to the frame 12, and others who Goy - with the working tool 14. It is assumed that the tube 46 and/or the node 48 of the piston alternatively, may be rigidly connected to either the frame 12 or the working tool 14. The hydraulic cylinder 16 may include a first cavity 50 and the second cavity 52, separated by a node 48 of the piston. The first and second cavities 50, 52 can be selectively supplied with fluid under pressure supplied by the source 26, and hydraulically connected to the tank 24 by the node 48 of the piston inside the tube 46, thereby changing the effective length of hydraulic cylinder 16. The extension and retraction of the hydraulic cylinder 16 facilitates the movement of the working tool 14.

Node 48 of the piston may include a piston 54 mounted coaxially with the pipe 46 and located within it, and the stem 56 of the piston attached to the frame 12 or the working tool 14 (Fig 1). The piston 54 may include a first hydraulic surface 58 and a second hydraulic surface 59, opposite to the first hydraulic surface 58. The unbalance force caused by fluid pressure on the first and second hydraulic surface 58, 59, can lead to the displacement of node 48 of the piston inside the tube 46. For example, when the force on first hydraulic surface 58 more force on second hydraulic surface 59 node 48 of the piston can be displaced, increasing the effect of the main length of the hydraulic cylinder 16. Similarly, when a force on second hydraulic surface 59 more force on first hydraulic surface 58, the node 48 of the piston may be drawn into the pipe 46, reducing the effective length of hydraulic cylinder 16. With the piston 54 can be connected to the sealing element (not shown), such as o-ring seal for restricting fluid flow between the inner wall of the pipe 46 and the outer cylindrical surface of the piston 54.

The tank 24 is designed to maintain the supply of liquid. The liquid may include, for example, special oil for hydraulic systems, engine lubricating oil, gear lubricating oil, or any other known liquid. Pick up liquid from the reservoir 24 and return it back can be one or more hydraulic systems within the working machine 10. It is also assumed that the hydraulic system 22 may be connected to multiple separate fluid reservoirs.

The source 26 may be made so as to collect the liquid from the reservoir 24 and to direct fluid under pressure into the hydraulic system 22. The source 26 may be a pump, such as, for example, a pump with a volume control, a pump with a constant flow or any other known source of fluid supply under pressure. The source 26 may be referred to in de is constituted by an energy source (not shown) of the working machine 10, for example, with an intermediate shaft (not shown), a belt (not shown), an electrical circuit (not shown), or driven in any other suitable way. The source 26 may be designed to supply fluid under pressure only in the hydraulic system 22 or, alternatively, he may apply fluid under pressure in the additional hydraulic system 55 within the working machine 10.

A relief valve 28, the piston cavity may hydraulically connect the first cavity 50 with the reservoir 24 through a channel 60 for fluid, relieving pressure in the hydraulic system 22. In particular, the relief valve 28, the piston cavity may include a valve element that is spring-loaded towards the closed or blocking fluid position and configured to move in the direction to open or transmissive liquid position in excess of a predetermined value of pressure within the channel 60 for the liquid. Thus, the valve piston 28 of the cavity can be made with the possibility of reducing surge pressure within hydraulic system 22 caused by external forces acting on the working tool 14 and the piston 54. It is assumed that the relief valve 28, the piston cavity may be missing.

In addition to the internal valve piston 30 of the cavity can be designed to allow fluid from the tank 24 to flow into the first cavity 50 when the pressure of the liquid. In particular, the make-up valve 30, the piston cavity may include a valve element configured to move from a closed or blocking fluid position toward the open or transmissive liquid position to pass fluid from the reservoir 24 into the first cavity 50 when the pressure of the fluid within the channel 60 below the pressure of the fluid within the tank 24. Thus, charging valve 30, the piston cavity may reduce the incidence of pressure within hydraulic system 22 caused by external forces acting on the working tool 14 and the piston 54. It is assumed that make-up valve piston 30 of the cavity may be missing.

A relief valve 32 rod end may hydraulically connect the second cavity 52 from the reservoir 24 through a channel 62 for fluid, relieving pressure in the hydraulic system 22. In particular, the safety valve 32 rod end may include a valve element that is spring-loaded towards the closed or blocking fluid position, and is arranged to move in the direction to open or transmissive liquid position in excess of a predetermined value of pressure inside the channel 62 for the liquid. Thus, the relief valve 32 rod end can be made with the possibility of reducing surge pressure within hydraulic system 22 caused by external forces acting on the working tool 14 and the piston 54. It is assumed that the relief valve 28, the piston cavity may be missing.

Make-up valve 34 and the rod end can be made so as to allow fluid from the tank 24 to flow into the second cavity 52 when the pressure of the liquid. In particular, charging valve 34 and the rod end may include a valve element configured to move from a closed or blocking fluid position toward the open or transmissive liquid position to pass fluid from the reservoir 24 into the second cavity 52 when the pressure of the fluid within the channel 62 below the pressure of the fluid within the tank 24. Thus, charging valve 34 and the rod end can reduce the pressure drop within hydraulic system 22 caused by external forces acting on the working tool 14 and the piston 54. It is assumed that the feed valve 34 and the rod end may be missing.

Drain valves 36, 38 and nutrient regulators 40, 42, the piston and the rod ends can be hydraulically interconnected. Often the spine, drain valves 36, 38 of the piston cavity and the rod end can be connected in parallel to the common drain channel 64. Nutritional regulators 40, 42 flow piston cavity and the rod end can be connected in parallel to the input common channel 66 for fluid. Nutritional controller 40 of the flow and a drain valve 36, the piston cavity can be connected in parallel with the channel 60 for the liquid. Nutritional controller 42 of the flow and a drain valve 38 and the rod end can be connected in parallel with the channel 62 for the liquid.

A drain valve 36, the piston cavity may be located between the first cavity 50 and the reservoir 24 and are made so as to regulate the flow of fluid under pressure directed from the first cavity 50 into the reservoir 24. In particular, a drain valve 36, the piston cavity may include a proportional spring-loaded valve mechanism, which is actuated by the solenoid to move between a first position in which fluid is able to flow from the first cavity 50, and a second position in which fluid flow from the first cavity 50 is blocked. It is also assumed that a drain valve 36, the piston cavity may, alternatively, be a hydraulic actuator, a mechanical actuator, a pneumatic drive or operate any other approach is the common method.

A drain valve 38 and the rod end can be located between the second cavity 52 and the reservoir 24 and are made so as to regulate the flow of fluid under pressure directed from the second cavity 52 into the reservoir 24. In particular, a drain valve 38 and the rod end may include a proportional spring-loaded valve mechanism, which is actuated by the solenoid to move between a first position in which fluid is able to flow from the second cavity 52, and a second position in which fluid flow from the second cavity 52 is blocked. It is also assumed that a drain valve 38 and the rod end may, alternatively, be a hydraulic actuator, a mechanical actuator, a pneumatic drive or operate any other suitable method.

Nutritional controller 40 flow piston cavity may be located between the source 26 and the first cavity 50 and include components that act together to regulate the flow of fluid under pressure directed from the source 26 in the first cavity 50. In particular, as shown in figure 3, nutritious controller 40 flow piston cavity may include a housing 68, the adapter 70, the solenoid mechanism 72, the auxiliary valve 74, the main bypass valve 76 and a lot smedium the x springs 78, 80 and 82. It is assumed that the offset of one of the springs 78 and 80 may be reduced or absent entirely.

The housing 68 may include a Central hole 84, the inlet 86 and outlet 88. Annular channel 90 may connect the Central hole 84, the inlet 86 and outlet 88. It is assumed that the housing 68 may be designed to accommodate nutrient controller 40 flow piston cavity or may optionally include one or more components, such as a drain valve 36, the piston cavity, a drain valve 38 rod end and nutritious controller 42 thread rod end.

The adapter 70 may be located inside the Central hole 84 and include solenoid mechanism 72 and the auxiliary valve 74. In particular, the adapter 70 may include a Central hole 91 for accommodating the solenoid mechanism 72 and a blind hole 92 for accommodating the auxiliary valve 74. The adapter 70 may contain a filler bracket 94 mounted therein by threaded connection, in order to close the end of the adapter 70, which protrudes from the housing 68. It is assumed that within the grooves 97 and groove 99 of the adapter 70 may be located one or more sealing means (not shown), such as, for example, conceviable or other sealing means to minimize leakage between the housing 68 and the adapter 70 and between the adapter 70 and the main bypass valve 76, respectively,

Solenoid mechanism 72 may be located inside the adapter 70 and is made so that, when applying an electric current proportional to move the auxiliary valve 74 against the action of springs 78 and 80. In particular, the solenoid mechanism 72 may include an electromagnetic coil 98 and the anchor 100 that contains the pin 110, is connected by a thread with the auxiliary valve 74. When applying to the electromagnetic coil 98 of the electric current anchor 100 can be attracted against the action of springs 78 and 80 to the electromagnetic coil 98. The magnitude of the electric current filed on the electromagnetic coil 98 may determine the compression springs 78 and 80 and in turn how close the anchor 100 is attracted to the electromagnetic coil 98. The pin 110 may include a Central hole 112 to reduce resistance and create undesirable pressure fluctuations inside the feed regulator 40 flow piston cavity when moving the anchor 100 and the pins 110 on the inside of the adapter 70.

Auxiliary valve 74 may be a type of valve with zero leakage, which is slidable inside the adapter 70 for opening and closing of the channel 114. In particular, the auxiliary valve 74 may include a rod 116 is connected by a thread with a locking element 118 and pin 110. The pin 110 in the connection is to the anchor 100 and the rod 116 of the auxiliary valve can function as in order to adjust the relative position of the locking element 118 of the adapter 70. As in the rod 116 of the auxiliary valve and stop element 118 can be made of the Central hole 120 for hydraulic communication with Central bore 112. The rod 116 of the auxiliary valve may include an external groove 121, are made so as to hold the sealing element such as o-ring seal to reduce leakage of fluid between the auxiliary valve 74 and the counter bore 92. The locking element 118 may include surface 122, is made to engage with the seat 124 of the adapter 70 and the passage 127, which restricts the fluid flow from the inlet 86 to the channel 114 for fluid. The passage 127 may be a diametrical gap, a groove or a drilled hole. When the surface 122 and the seat 124 is introduced into the mesh, it is possible to prevent the fluid flow from the inlet 86 to the channel 114 for fluid through the passage 127. When the solenoid mechanism 72 is enabled, pulling the anchor 100 and the pin 110 to each other, thereby the inlet 86 and the channel 114 for fluid hydraulically connected through a passage 127. The channel 114 to the hydraulic fluid may be in communication with the outlet channel 88. Alternatively, it is assumed that the rod 116 is vspomogateljno valve and the locking element 118, if desired, can be made in one piece.

Hydraulic forces that occur on the surfaces 125 a,b of the locking element 118 may provide the movement of the pilot valve 74. The force of action on the surface 125 may be determined by the difference of the squares formed by a circle with a diameter drawn through the passage 127 or about him, and the surface 122 of the auxiliary contact of the valve seat 124. The force of action on the surface 125b may be determined by the difference of the squares formed by a circle with a diameter drawn through the passage 127 or around it, and a circle with a diameter of the opposite end of the stud 110. These two forces acting on the surface 125 a and 125b may be almost equal. When the liquid from the inlet 86 flows through the passage 127 to the channel 114, the fluid pressure acting on the surface 125 a,b, can be combined with the impact force of the solenoid mechanism 72 to the auxiliary valve 74 to move the locking element 118, or to counteract this force. For example, when the pressure of the fluid from the inlet 86 acting on the surface 125b increases, the surface 122 and the seat 124 may be displaced toward each other, thereby restricting the fluid flow through the channel 114. On the contrary, when the fluid pressure acting on surface 125b is reduced, the fluid acting on the surface 125 may move the surface 122 article is pornoho element 118 from seat 124, thereby reducing the restriction of the fluid flowing through the channel 114 to the liquid.

The main bypass valve 76 may be a valve of a type with zero leakage, which is made so as to selectively allow fluid to flow from the inlet 86 to the outlet 88. In particular, the surface 128 of the main relief valve 76 may be so located as to come into contact with the seat 130 of the housing 68 of the regulator. When the surface 128 and the saddle 130 are in contact, the fluid flow is directed from the inlet 86 to the outlet 88 may be blocked. On the contrary, when the surface 128 and the saddle 130 are separated from each other, fluid can flow from the inlet 86 to the outlet 88. The area between the surface 128 and seat 130, together with pressure on the forward end 76A of the main Poppet valve 76 may determine the fluid flow coming from the inlet 86 to the outlet 88.

When moving the pilot valve 74 surface 128 may be selectively come into contact and out of contact with the saddle (130). In particular, the main bypass valve 76, together with the housing 68, the adapter 70 and the auxiliary valve 74 may form a control cavity 126. Power from the action of the fluid on the forward end 76A of the main relief valve 76 may protivodeistvovat force caused by the pressure of the fluid inside the control cavity 126 and acting on the hollow end 76b of the main relief valve 76, and the force caused by the compression bias of the springs 80 and 82. In order to open the main valve 76, the surface 122 may be offset from the seat 124 to drain the fluid from the control cavity 126. When the liquid is drained from the control cavity 126, the fluid acting on the forward end 76A of the main relief valve 76 may overcome the force from bias spring 80 and 82 to move the main valve 76 toward the auxiliary valve 74 to close the main valve 76, the solenoid mechanism 72 can be disabled, which allows the bias of the springs 80 and 82 to return auxiliary valve 74 to the closed position (for example, in which the surface 122 is in contact with the saddle 124). When the auxiliary valve 74 is in the closed position, the inside of the control cavity 126 may increase the pressure, leading to the closure of the main relief valve 76 (for example, to move the surface 128 to contact with the saddle 130).

Fluctuations in the supply pressure in the inlet port 86 can affect the movement of the main relief valve 76. In particular, as described above, the increase in fluid pressure in the inlet port 86 which may cause movement of the pilot valve 74, which limits the flow of liquid through the channel 114, while a decrease in pressure can cause movement of the pilot valve 74, to help reduce the restriction of fluid flow through the channel 114. Increase limit the flow through the channel 114 can lead to increased pressure inside the control cavity 126, which will allow the main bypass valve 76 to move because of the bias of the spring 82 and trailing hydrodynamic forces in the closed position (for example, moving surface 128 toward the saddle 130), thus remains essentially the same fluid flow is directed from the inlet 86 to the outlet 88, with increasing feed pressure. The decrease limit the flow through the channel 114 can lead to a reduction in pressure inside the control cavity 126, which will allow the main bypass valve 76 to move because of the bias of the spring 82 and trailing hydrodynamic forces in the direction to the open position (for example, moving surface 128 on the saddle 130), thus remains essentially the same fluid flow is directed from the inlet 86 to the outlet 88, when reducing the supply pressure.

The main bypass valve 76 may be connected to the adapter 70 for installation in the housing 68 as the valve patronag the type. In one example, the main bypass valve 76 may include a pin 132, which is in engagement with the shoulder 134 of the adapter 70 after Assembly of the main relief valve 76 with the adapter 70. Thus, you can create a subassembly consisting of the adapter 70, the pilot valve 74, the main by-pass valve 76 and springs 78-82. After Assembly with the housing 68 can be saved, the gap between the pin 132 and the adapter 70.

Inside the Central hole 138 of the main relief valve 76 may be located a check valve 136 to facilitate unidirectional flow from the inlet 86 through the main bypass valve 76. It is assumed that the check valve 136 may be missing. It is also assumed that when a check valve 136, the sealing element, usually located inside the outer groove 121 may be omitted, which reduces the delay of the auxiliary valve. In addition, it is assumed that the check valve 136 may be replaced by a tapering passage (not shown). When the nutrient controller 42 thread the rod end includes a narrowing passage, the magnitude of the contraction can be adjusted so that the nutritional regulator 42 thread the rod end could be managed by area or flow.

Nutritional regulator 42 thread rod end (figure 2 may be located between the source 26 and the second cavity 52, and may include components, which act synergistically to regulate the flow of fluid under pressure directed from the source 26 to the second cavity 52. Since the components and operation of nutrient regulator 42 thread the rod end is essentially the same nutritional components of the controller 40 flow piston cavity, a description of the nutrient regulator 42 thread the rod end is omitted.

The described hydraulic system can be applied to any work machine that includes a hydraulic actuator, which requires precise control of pressure and/or expenses of the fluid supplied to the actuator. The described hydraulic system can provide bystrorastvorimae pressure control, which leads to a constant predictable performance of the drive at a low cost, simple design. Next will be described the principle of operation of the hydraulic system 22.

The hydraulic cylinder 16 can be moved by fluid pressure in response to the input action of the operator. Fluid may be supplied under pressure from a source 26 and directed to the fuel regulators 40, 42 flow piston and rod ends. In response to the input action of the operator to pull or drag the node 48 of the piston relative to the tube 46 is activated solenoid mechanism 72 nutrient controller 40 or 42, Prov is Giva anchor 100 to the electromagnetic coil 98. When the anchor 100 is attracted to the electromagnetic coil 98 connected therewith auxiliary valve 74 is moved, deriving from the contact surface 122 of the seat 124 to the corresponding value ensuring the discharge of fluid from the control cavity 126 at an appropriate speed. When the control cavity 126 merges the fluid in the main bypass valve 76 creates a differential pressure which overcomes the force of springs 80 and 82 and causes the surface 128 of the main relief valve 76 out of contact with the seat 130 of the housing 68 of the regulator to the appropriate value, thereby hydraulically connecting the inlet 86 to the output 88 and after that filling one of the cavities 50 and 52 of fluid under pressure to the desired speed.

The value of electric current supplied to the solenoid mechanism 72 may be based on the rated pressure of the fluid inside the control cavity 126 and the required flow rate from the control cavity 126. In particular, the value of electric current supplied to the electromagnetic coil 98 may correspond to the compression springs 78 and 80, which leads to the formation of a given cross-sectional area of flow between surface 122 and seat 124. Given the cross-sectional area of flow between surface 122 and seat 124 provides a specified fluid flow from the control cavity 126 and posleduushie pressure in the main bypass valve 76, which defines a predetermined cross-sectional area of flow between surface 128 and seat 130. Similarly, a given cross-sectional area of flow between surface 128 and seat 130 provides a specified fluid flow directed from the inlet 86 to the outlet 88, which leads to the desired speed of the actuation of the hydraulic cylinder 16. The relationship between the supplied electric current, and compression springs 78-82, square hydraulic surfaces 125 a,b, the area of the orifice in the passage 127 and the main hydrodynamic forces regulation, which results in the required areas orifice can be determined by analytical procedures, laboratory tests, test conditions and/or by other known methods.

Nutritional regulators 40, 42 flow piston and the rod ends can be adapted to situations in which the fluid pressure supplied to the nasal end 76A, deviates from the design pressure. In particular, since the source 26 may be hydraulically connected with many actuators, one actuator may affect the pressure and subsequent fluid flow directed to the hydraulic cylinder 16. These pressure fluctuations, if left unregulated, could lead to bore abellinum and/or unexpected movement of the hydraulic cylinder 16 and the working tool 14. These effects can be accounted for by the fact that hydraulic surface 125a,b operate so that proportionally move the auxiliary valve 74 in response to fluid pressure within hydraulic system 22 and the resulting hydrodynamic forces acting on the surface 128, thereby providing an essentially constant flow of fluid directed from the inlet 86 to the outlet 88. For example, when the pressure of the fluid supplied into the inlet 86 increases, the force acting on the surface 125b, similarly, is increased by moving the surface 122 against the attraction of the solenoid mechanism 72 in the direction of the seat 124, thereby reducing the effective area of the orifice between the surface 122 and seat 124. This increased restriction to fluid leaving the control cavity 126 may increase the pressure of the fluid inside the control cavity 126 acting on the hollow end 76b, resulting in the displacement of the surface 128 toward the saddle 130. Moving surface 128 toward the saddle 130 may reduce the effective area of the orifice between the inlet 86 and outlet 88, thereby providing essentially the same flow that was when most of the cross-section area to increase pressure. On the contrary, when the pressure of the fluid, p is given by the inlet 86, decreases, the force acting on the surface 125b and the opposite pull of the solenoid mechanism 72 may similarly be reduced so that the force acting on the surface 125b, moves the surface 122 of the seat 124. This reduced restriction to fluid leaving the control cavity 126, reduces the pressure of the fluid inside the control cavity 126 acting on the hollow end 76b, resulting in the displacement of the surface 128 on the saddle 130. Moving surface 128 from the seat 130 can increase the effective area of the orifice between the inlet 86 and outlet 88, thereby providing essentially the same flow that was with a smaller cross-sectional area of flow to reduce pressure.

Specialists in the art will understand that the described flow regulator and the hydraulic system can be manufactured in various modifications and changes. Other embodiments of the invention will be obvious to a person skilled in the art upon consideration of the description and the practical implementation of the described flow regulator and hydraulic systems. For example, it is assumed that the drain valves 36, 38 of the piston and the rod ends (2) can be substantially similar in design and function, nutrient regulators 40, 42 of the thread of the piston rod and the floor of the building. Understood that the description and ways of implementation will be considered only as an example, the volume of the inventions defined by the claims.

1. Nutritional regulator (40) stream, comprising a housing (68) with the input (86) and weekends (88) holes located in the housing between the inlet and outlet ports of the main relief valve (76), which includes a nose end (76A) and the hollow end (76b) and configured to move between an open position in which fluid can pass from the inlet to the outlet, and a closed position in which the passage of fluid between the inlet and outlet ports closed, the auxiliary valve (74), with the possibility of moving to selective connection of the hollow end of the main by-pass valve with drain (34), thereby affecting movement of the main by-pass valve between the open and closed positions, and a solenoid mechanism (72) to move the pilot valve, the position of which depends on the fluid pressure in the inlet port.

2. Nutrient flow regulator according to claim 1, in which the solenoid mechanism configured to move the pilot valve to the preset value, thereby causing displacement of the main by-pass valve to the preset value determined is AAMWU design pressure of fluid in the inlet.

3. Nutrient flow regulator according to claim 2, in which the auxiliary valve is arranged to move when the pressure of the fluid in the inlet so as to maintain essentially constant the flow rate of the liquid flowing from the inlet to the outlet.

4. Nutrient flow regulator of claim 1, wherein in the auxiliary valve is made the Central hole (120).

5. Nutrient flow regulator according to claim 4, in which the solenoid mechanism includes an electromagnetic coil (98), the anchor (100) and connected with it the pin (110), with the anchor and the hairpin is made the Central hole (112)provided with a Central hole of the auxiliary valve.

6. Nutrient flow regulator according to claim 5, in which largely bypass valve is made the Central hole (138), communicated with the Central hole of the auxiliary valve, while in the Central hole of the main by-pass valve is a check valve (136).

7. Method of nutrient management controller (40) thread according to any one of claims 1 to 6, including the steps that direct the flow of fluid under pressure to the main bypass valve (76) flow control valve, move the auxiliary valve (74) using electronics to hydraulically move the main valve in the ass the TES position and allow fluid under pressure to flow through the flow regulator to the desired speed, and automatically adjust the position of the auxiliary valve when the pressure of the fluid so as to maintain the desired flow through the flow regulator.

8. The method according to claim 7, in which the preset position determined on the basis of the estimated fluid pressure.

9. The method according to claim 7, further comprising the steps, which allow fluid to pass through the auxiliary valve during its movement; allows fluids to pass through the main relief valve and restrict the flow of fluid through the main valve in one direction.

10. Working machine (10)containing a working tool (14); the associated hydraulic cylinder (16) to move a work tool, comprising at least one cavity (50); source (24) of fluid under pressure communicated with the specified at least one cavity; and nutritional regulator (40) thread according to any one of claims 1 to 6, is configured to regulate the flow of the liquid delivered under pressure in said at least one cavity.



 

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2 dwg

FIELD: machine building.

SUBSTANCE: in amplifier there is implemented jet amplifier stage with two pressure nozzles and correspondingly with two receiving channels connected by means of their hydraulic lines with sub-end cavities of slide. The jet amplifier stage consists of two cylinder elements coaxially and with a gap installed in a case. A deflector gate of an electro-mechanic converter is arranged in slots in the cylinder elements from the side of ends facing each other. The pressure nozzle and the receiving channel are coaxially arranged in the slot of each element from the side of cylinder surface. Threaded sleeves are screwed on threaded ends of the cylinder elements from the side opposite to the slot. With their external thread the sleeves are screwed into the case. Also thread in the case, on the cylinder elements and correspondingly in the threaded sleeves has different pitch.

EFFECT: improved processability of fabrication, simplification of jet amplifier design and facilitation of its adjustment with high accuracy.

1 dwg

FIELD: machine building.

SUBSTANCE: distributor is designed for supply and withdrawal of fluid into cavity of hydraulic engine and for protecting it from overloads, for locking cavity and for maintaining suspended load, for replacing load from cavity of hydraulic engine and damping to facilitate uniform motion at any specified speed. The distributor consists of a rectangular metal case of platen mounting with bypass, supply and drain lines, of a safety valve with a pilot, of a controlled valve with a pilot and two back valves each including a bush-seat, a ball and a spring. Also a safety valve is installed into the end of the case along its lengthwise axis; the valve is equipped with two control valves and the pilot. The control valve with the pilot is installed perpendicular to lengthwise axis of the case. Notably, under-valve cavity of the safety valve is connected with a side surface of the gate of the control valve and the drain line via a channel; the supply line is connected to the under valve cavity of the control valve; the drain line is connected with the side surface of the safety valve, while the back valves are installed in withdrawal channels of drain and supply lines; the back valves shut off the channels pressure tight from overflows of fluid from one line to another.

EFFECT: facilitating multi-functionality of device, simplicity of fabrication, high maintainability, easy control and high reliability.

5 dwg

Valve // 2347127

FIELD: machine building.

SUBSTANCE: invention relates to hydro pneumatic automatic control devices and can be used in aircraft hydraulic control systems. The proposed valve incorporates a body with the pressure, control and drain channels separated by two cups arranged in the valve body and provided with aligned grooves and holes. A push rod is arranged in the said grooves to move therein. The aforesaid holes in the cups are made on both sides of the push rod to contact, by their outer edges, with the ball-like shut-off members. One of the said balls, on the drain side, interacts with a spring-loaded rod moving inside the electromagnetic drive stator. Note that in one position of the aforesaid rod, the control channel communicates with the drain line while, in the other position, it communicates with the pressure channel. There is a spring-loaded plunger fitted in the valve body of the pressure side, its end face interacting with the shut-off member on the aforesaid side. Cylindrical collars are made on the outer surface of every cup on the side of holes and aligned with them. One of the said collar accommodates on the drain side a sleeve locked in a blind groove aligned with the sleeve through hole receiving a ball. The collar of other cup, but on the pressure side, accommodates a similar sleeve with the ball.

EFFECT: higher valve tightness.

1 dwg

FIELD: engines and pumps.

SUBSTANCE: valve has a body with the feed pressure supply channel, an outlet channel, a controlled pressure outlet channel and an inner boring accommodating a control valve with an inner channel with throttle communicating the inlet channel with the left-hand space formed by the body boring and the left-hand end face of the said control valve and communicating with the outlet channel via the control valve, and a channel communicating the outlet channel with the right-hand space formed by the body boring and the control valve right-hand end face and containing a return spring acting on the slide valve. The slide valve incorporates an additional spring-loaded channel communicating the right-hand space with the outlet channel, while the channel communicating the outlet channel with the right-hand space accommodates an additional throttle. In compliance with the other valve version, the right-hand space can communicate via the spring-loaded valve with the outlet channel. Here the additional spring-loaded valve is arranged inside the slide valve or in the main valve body.

EFFECT: smooth engagement of gearbox friction gear wheels.

4 cl, 5 dwg

FIELD: engines and pumps.

SUBSTANCE: method and device are intended for control system operated by gaseous working medium. The method consists in the following. With the switched off electromagnetic drive windings, the armature is set at its travel centre, and, during drive operation, electromagnetic forces are induced on the armature each side in turn. Here, air being distributed is forced to blast the electromagnetic drive stator and windings to create equal in size and opposite-sign forces acting on the armature along its travel. The distributor is made up of two concentrically located cylinders jointed by a connector in their central zone. Coils with windings are arranged between cylinders on both sides of the connector with a gap for air to pass through. The smaller diameter cylinder accommodates a cylinder rod making a dual-action armature with blind holes on its every end to accommodate the springs resting against the covers, thus retaining the rods with an equal clearance relative to covers. The cylinders walls have two rows of inclined holes symmetric relative to the connector jointing the cylinders.

EFFECT: lower electric power consumption.

2 cl, 1 dwg

FIELD: hydraulics.

SUBSTANCE: device comprises sleeve with step outer side and axial passage that receives two cylindrical collars of the step slide valve whose third collar is provided with face stop. The outer side of the smaller diameter of the sleeve is provided with the first and second grooves interconnected through the axial passage. The outer surface of greater diameter of the sleeve has two chamferings whose surfaces are connected with the axial passage through openings. The first collar is arranged near the face of the slide valve opposite to the stop to define a control chamber, is provided with two flat chamferings, and is made for permitting cooperation with the ports of the first groove in the sleeve. The second collar is separated from the third collar by a groove and is made for permitting cooperation with radial openings of the sleeve. The first groove is open from its face, and the ports of the second groove are connected with the space defined in the axial passage between the collars of the slide valve.

EFFECT: enhanced efficiency.

6 cl, 10 dwg

FIELD: fluid-pressure actuators.

SUBSTANCE: system of hydraulic valves comprises first actuating connection and the second actuating connection which are connected with the hydraulic consumer, system of supplying connections that has the connection with the pressure source and connection with the vessel, first valve system that disconnect the system from the pressure source or controllably connect it with the first actuating connection or the second actuating connection, second system of valves that disconnects the system from the vessel or connects it controllably with the first actuating connection or the second actuating connection, and control unit that controls the first valve system and second valve system. At least one valve system is provided with the pickup of the extent of opening connected with the control unit that controls the valve system depending on the signal from the pickup of the extent of opening and reference signal.

EFFECT: enhanced precision of control.

15 cl, 3 dwg

FIELD: production of hydraulic distributor for electro-hydraulic amplifiers.

SUBSTANCE: the hydraulic distributor is intended for use in electro-hydraulic amplifiers and is supplied with the drive of a sliding valve made in the form of a turning electrical motor, on the shaft of which there is a cantilever eccentric with a ball bearing. On the sliding valve there is a groove for interaction with the bearing and the shaft sealed with a reinforced sealing ring.

EFFECT: the invention ensures increased efficiency of the hydraulic distributor operation.

2 cl, 4 dwg

FIELD: production of hydraulic distributor for electro-hydraulic amplifiers.

SUBSTANCE: the hydraulic distributor is intended for use in electro-hydraulic amplifiers and is supplied with the drive of a sliding valve made in the form of a turning electrical motor, on the shaft of which there is a cantilever eccentric with a ball bearing. On the sliding valve there is a groove for interaction with the bearing and the shaft sealed with a reinforced sealing ring.

EFFECT: the invention ensures increased efficiency of the hydraulic distributor operation.

2 cl, 4 dwg

FIELD: fluid-pressure actuators.

SUBSTANCE: system of hydraulic valves comprises first actuating connection and the second actuating connection which are connected with the hydraulic consumer, system of supplying connections that has the connection with the pressure source and connection with the vessel, first valve system that disconnect the system from the pressure source or controllably connect it with the first actuating connection or the second actuating connection, second system of valves that disconnects the system from the vessel or connects it controllably with the first actuating connection or the second actuating connection, and control unit that controls the first valve system and second valve system. At least one valve system is provided with the pickup of the extent of opening connected with the control unit that controls the valve system depending on the signal from the pickup of the extent of opening and reference signal.

EFFECT: enhanced precision of control.

15 cl, 3 dwg

FIELD: hydraulics.

SUBSTANCE: device comprises sleeve with step outer side and axial passage that receives two cylindrical collars of the step slide valve whose third collar is provided with face stop. The outer side of the smaller diameter of the sleeve is provided with the first and second grooves interconnected through the axial passage. The outer surface of greater diameter of the sleeve has two chamferings whose surfaces are connected with the axial passage through openings. The first collar is arranged near the face of the slide valve opposite to the stop to define a control chamber, is provided with two flat chamferings, and is made for permitting cooperation with the ports of the first groove in the sleeve. The second collar is separated from the third collar by a groove and is made for permitting cooperation with radial openings of the sleeve. The first groove is open from its face, and the ports of the second groove are connected with the space defined in the axial passage between the collars of the slide valve.

EFFECT: enhanced efficiency.

6 cl, 10 dwg

FIELD: engines and pumps.

SUBSTANCE: method and device are intended for control system operated by gaseous working medium. The method consists in the following. With the switched off electromagnetic drive windings, the armature is set at its travel centre, and, during drive operation, electromagnetic forces are induced on the armature each side in turn. Here, air being distributed is forced to blast the electromagnetic drive stator and windings to create equal in size and opposite-sign forces acting on the armature along its travel. The distributor is made up of two concentrically located cylinders jointed by a connector in their central zone. Coils with windings are arranged between cylinders on both sides of the connector with a gap for air to pass through. The smaller diameter cylinder accommodates a cylinder rod making a dual-action armature with blind holes on its every end to accommodate the springs resting against the covers, thus retaining the rods with an equal clearance relative to covers. The cylinders walls have two rows of inclined holes symmetric relative to the connector jointing the cylinders.

EFFECT: lower electric power consumption.

2 cl, 1 dwg

FIELD: engines and pumps.

SUBSTANCE: valve has a body with the feed pressure supply channel, an outlet channel, a controlled pressure outlet channel and an inner boring accommodating a control valve with an inner channel with throttle communicating the inlet channel with the left-hand space formed by the body boring and the left-hand end face of the said control valve and communicating with the outlet channel via the control valve, and a channel communicating the outlet channel with the right-hand space formed by the body boring and the control valve right-hand end face and containing a return spring acting on the slide valve. The slide valve incorporates an additional spring-loaded channel communicating the right-hand space with the outlet channel, while the channel communicating the outlet channel with the right-hand space accommodates an additional throttle. In compliance with the other valve version, the right-hand space can communicate via the spring-loaded valve with the outlet channel. Here the additional spring-loaded valve is arranged inside the slide valve or in the main valve body.

EFFECT: smooth engagement of gearbox friction gear wheels.

4 cl, 5 dwg

Valve // 2347127

FIELD: machine building.

SUBSTANCE: invention relates to hydro pneumatic automatic control devices and can be used in aircraft hydraulic control systems. The proposed valve incorporates a body with the pressure, control and drain channels separated by two cups arranged in the valve body and provided with aligned grooves and holes. A push rod is arranged in the said grooves to move therein. The aforesaid holes in the cups are made on both sides of the push rod to contact, by their outer edges, with the ball-like shut-off members. One of the said balls, on the drain side, interacts with a spring-loaded rod moving inside the electromagnetic drive stator. Note that in one position of the aforesaid rod, the control channel communicates with the drain line while, in the other position, it communicates with the pressure channel. There is a spring-loaded plunger fitted in the valve body of the pressure side, its end face interacting with the shut-off member on the aforesaid side. Cylindrical collars are made on the outer surface of every cup on the side of holes and aligned with them. One of the said collar accommodates on the drain side a sleeve locked in a blind groove aligned with the sleeve through hole receiving a ball. The collar of other cup, but on the pressure side, accommodates a similar sleeve with the ball.

EFFECT: higher valve tightness.

1 dwg

FIELD: machine building.

SUBSTANCE: distributor is designed for supply and withdrawal of fluid into cavity of hydraulic engine and for protecting it from overloads, for locking cavity and for maintaining suspended load, for replacing load from cavity of hydraulic engine and damping to facilitate uniform motion at any specified speed. The distributor consists of a rectangular metal case of platen mounting with bypass, supply and drain lines, of a safety valve with a pilot, of a controlled valve with a pilot and two back valves each including a bush-seat, a ball and a spring. Also a safety valve is installed into the end of the case along its lengthwise axis; the valve is equipped with two control valves and the pilot. The control valve with the pilot is installed perpendicular to lengthwise axis of the case. Notably, under-valve cavity of the safety valve is connected with a side surface of the gate of the control valve and the drain line via a channel; the supply line is connected to the under valve cavity of the control valve; the drain line is connected with the side surface of the safety valve, while the back valves are installed in withdrawal channels of drain and supply lines; the back valves shut off the channels pressure tight from overflows of fluid from one line to another.

EFFECT: facilitating multi-functionality of device, simplicity of fabrication, high maintainability, easy control and high reliability.

5 dwg

FIELD: machine building.

SUBSTANCE: in amplifier there is implemented jet amplifier stage with two pressure nozzles and correspondingly with two receiving channels connected by means of their hydraulic lines with sub-end cavities of slide. The jet amplifier stage consists of two cylinder elements coaxially and with a gap installed in a case. A deflector gate of an electro-mechanic converter is arranged in slots in the cylinder elements from the side of ends facing each other. The pressure nozzle and the receiving channel are coaxially arranged in the slot of each element from the side of cylinder surface. Threaded sleeves are screwed on threaded ends of the cylinder elements from the side opposite to the slot. With their external thread the sleeves are screwed into the case. Also thread in the case, on the cylinder elements and correspondingly in the threaded sleeves has different pitch.

EFFECT: improved processability of fabrication, simplification of jet amplifier design and facilitation of its adjustment with high accuracy.

1 dwg

FIELD: machine building.

SUBSTANCE: two-position hydraulic distributor with pulse control refers to hydraulics and can be used as hydraulic equipment of mobile machines. A valve of the hydro-distributor slides along a guide block and is fixed in two points, when control pulse electric signal is transmitted to electro-magnetic valve.

EFFECT: reduced dimensions and weight of electric magnet, reduced power consumption, increased reliability of hydraulic distributor operation.

2 dwg

FIELD: engines and pumps.

SUBSTANCE: flow control and control method of the control is intended for hydraulic system of working machine. Control includes housing with inlet hole and outlet hole, main bypass valve located inside the housing between inlet and outlet holes and including the forward end and hollow end. Valve has the possibility of being moved between open position in which the liquid flows from inlet hole to outlet hole, and closed position in which the liquid flow between inlet and outlet holes is locked. In addition, control has auxiliary valve having the possibility of being moved so that they can selectively attach hollow end of the main bypass valve to the drain, thus influencing the movement of the main bypass valve between open and closed positions. Besides, flow control includes solenoid mechanism intended to move auxiliary valve. Position of auxiliary valve depends on liquid pressure in inlet hole.

EFFECT: higher reliability of hydraulic system.

10 cl, 3 dwg

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