Device for controlling hydraulic cylinder
(57) Abstract:Use: electro-hydraulic automatic control systems. The inventive device includes a main shut-off and control element, accommodated in the housing, defining a proportional element 13 with the plunger resting on the host shut-off and control element made consistent with shut-off element of the plot, overlapping in the initial position of the radial channels of the main element, which is equipped with a built-in chokes in the form of holes of constant cross-section. 9 C.p. f-crystals, 4 Il. The invention relates to a device for controlling a hydraulic cylinder.A device for controlling a hydraulic cylinder containing the main shut-off and control element, accommodated in the housing with the formation of end camera control and interact with its stepped conical part with the saddle, made in the housing and separating the inlet and outlet pipes, and also specifies the proportional element with the plunger resting on spring hollow managing locking and regulating element is a stepped shape having a locking element saddle valve, placed in the Auxerre management and connected with the inlet pipe and executed in the main shut-off and control element radial channels from the outlet pipe.Object of the invention is a device for controlling a hydraulic cylinder, by means of which the flow of working fluid from this securely locking cylinder can be precisely controlled in a proportional manner with a small Executive effort.The solution to this problem is provided by the fact that the control valves and the element is made consistent with shut-off element saddle valve area of the control spool overlapping in the initial position of the radial channels of the main shut-off and control element, which is equipped with a built-in choke and performed with an intermediate chamber connected through a choke with end camera control, and through the other orifice with the inlet pipe, and an intermediate chamber with connection Manager shut-off and control element through the area of the control spool via open them channel with outlet connections.Explained in detail below and are illustrated by drawings of the three options for the implementation IIG.3 and 4 are longitudinal sections of other designs.In Fig.1 shows the housing 10A of the stop valve 10 having the shape of the Cup and adjacent the open end 10 to the housing 12 of the proportional magnet 13. Inside the valve are two closed ring groove 15, 16. The annular groove 15 is connected by a bore 18 and a pipe 19 for supplying a working medium source, and the annular groove 16 is connected by a hole 20 with a pipe 12 for supplying a medium to the consumer and removal of protection from him.In the housing 10 of the valve is inserted a cylindrical sleeve 23 fixed in the casing of the lock nut 24 with an external thread 25. The valve body contains in the region of the end face 11 a corresponding internal threads 26 extending from the cylindrical recess 27 on the end, which laid the sealing ring 28. With this ring is sealed from the outside the place of junction of the valve body with a proportional magnet. Through the sleeve 23 are two passing each other in the axial hole 30, 31, of which the opening 31 facing the end face 11 has a smaller diameter. In the wall of the bore 30, in the transition region to the hole 31 made the annular groove 32, which is connected by radial holes 33, 34 with the annular channel 36 formed by the groove 15 and the sleeve 23. The hole 31 intersects the radial hole 37, doneIn the opening 30 of the sleeve 23 is moved from the seal body 40 of the valve. It interacts with the saddle valve 41, is made at the junction of the openings 30 into the hole 31. The body 40 of the valve is in seat 41 form an obtuse cone 42, rolling in microdialysis cone 43. The junction of the blunt cone in a conical needle does not have a linear edge, and rounded.Through the body 40 of the valve are three passing each other coaxially with the axial bore 45, 46, 47. A hole 47 extending into the conical needle 43 has the smallest diameter and the hole 45 at the opposite end of the largest diameter. From the end opposite the tapered needle, the valve body is blocked by a screw 49. The threaded section 50 of the screw enters the hole 46 containing the corresponding internal threads on a portion of its length. The head 52 of the screw so close to the end of the valve body to the hole 45 and the screw 49 has been formed annular channel 54. In the threaded section 50 of the screw is made annular groove 55 in which is incorporated a sealing ring 56, the sealing annular channel 56 relative to the openings 46. In the head 52 of the screw on the side opposite to the valve body, has a blind hole 57, the bottom of which departs throttling hole 58, leaving who are looking for housing 10A and the body 40 of the valve.In the valve body 40 has two radial deaf holes 61, 62, directed towards each other from the outer surface in the region of the annular groove 32. From the base of each of them leaves one throttling opening 63, 64, a member of the hole 47. The opening 61 has an internal thread 65 in the area of the outer surface of the valve body, into which is screwed into the orifice 66. The hole 62 is closed on the outside by a tube 68. Blind hole 61 are connected by a longitudinal channel 67 with the annular channel 54; likewise, a blind hole 62 are connected by a longitudinal channel 70 with the annular channel 54. In the area of the outlet throttling holes 63, 64 through the opening 47 is held the third blind hole 69, also made radially from the outer surface of the valve body and closed in this place the tube 59 (see Fig.2).The hole 47 is moved to seal the valve 71 prior distribution. On the one hand it is extended tapered part 72 into the opening 46 and in this place interacts with the saddle 73, made in the passage holes 46 in the hole 47. On the other hand, this valve prior distribution comes to hexagonal holes 74 of the locking nut 24 and in this place interacts with the Tacana 78, guide the spring included in the hole 31 and the adjacent folded edge 79 to the end of the sleeve 23. Smart glass 78 is fixed by a locking nut 24. To do this, it made the annular groove 80, the diameter of which corresponds to the diameter of the bent edge 79. This machine 78 may be secured against radial movement by the edges of the holes 74. For this purpose, the outer diameter of the edge 79 was equal to the inner diameter of a circle inscribed in the hexagon hole 74. On the inner side of the guide Cup 78 rests one end of a compression spring 82, the other end of which is adjacent to the washer 83 is mounted on the spool 71 prior distribution. This washer is held together by a retaining ring 85 which is inserted in an annular groove 84 on the end of the spool prior distribution.In the area between the guide Cup 78 and microdialysis cone 43 in the spool 71 preliminary distribution of a radial hole 87. It connects with an elongated blind hole 88 extending from the extended conical portion 72 of the spool. On the surface of the spool 71 is formed of two annular groove 90, 91, between which there is a narrow belt 92. When the cone 72 of the spool predvaritelnogo ahadith from the belt 92 to the cone 72, the expansion starts from the bottom of the groove. Together with the wall of the bore 47 of the annular grooves 90, 91 form two annular channel 94, 95, are related to each other blind hole 69 in any operating position of the spool prior distribution. The diameter of the blind hole 69 is selected so that these channels remained United and with the movements of the spool.Shut-off valve 10 is in the closed position when nevidimom the plunger is proportional to the magnet 13. The force of the spring 82 cone 72 of the spool 71 prior distribution is pressed to its seat 73 and the body 40 of the valve seat 41. At the same time the belt 92 overlaps the throttling holes 63, 64. From the supply pipe 19 is connected to the orifice 66 through holes 18, the annular channel 36, the holes 33, 34 and the annular groove 32. Further, the working environment in the annular channel 67 enters the annular chamber 54 and thence through a throttling orifice 58 and the hole 57 in the pressure chamber 60. At the same time the longitudinal channel 70 connects the annular channel 54 with a hole 62. On the side of the outlet closed on one side by the valve body hole 31 are connected through holes 37, the annular channel 38 and openings 20 with the pipe 21. Because the butt is the larger annular surface ARthe difference of the squares of the holes 30 and 31 causes additional clamping the valve body to the valve seat 41. Leakage in the closed position of the valve is very small thanks to the integrated saddle valve and a long guide sliding of the spool 71 prior distribution in the hole 47.When enabled, the proportional magnet 13, the spool 71 is moved to the left by the plunger 75, the cone spool 72 moves away from the seat 73 and closed with one hand belt 92 throttling holes 63, 64 is opened.When the pressure in the pipe 19, the working medium flows from this pipe, as previously described, the holes 61, 62 and thence through the throttling openings 63, 64 in the annular channel 95. Closed blind hole 69 communicates with the annular channel 94. Hence, the working environment into an open seat 73 is closed at one side hole 46. The longitudinal bore 88 and the transverse hole 87 in the valve hole 71 46 is connected with the hole 31, which, as described above, is connected with the pipe 21 on the output side.When opening the throttling holes 63, 64, belt 92 with respect to the input inductor 66, the pressure in the hole 61 and the pressure in chamber 60 will fall so, ctana moves to the left. The working medium flows from the annular groove 32 at the open seat 41 in the hole 31 and thence falls into the discharge pipe 21. When the spool 71 under the action of the spring 82 moves to the right when the retraction of the plunger 75, the body 40 of the valve moves with it (servo control). This movement of the valve body caused by the change in the proportion of pressure on the ends of the valve body and the mechanical movement with the valve. The displacement force of the spool is determined by the spring 82 and the friction in the hole 47. Since the pressure in the annular channel 94, 95 are aligned through hole 69, the valve does not operate hydraulic forces. Therefore, the resultant forces acting on the spool, small. When the pressure in the intake pipe 19 is so small that it does not cause movement of the body 40 of the valve spool supports such a move. When opening (moving left) spool abuts the end face of the conical portion 72 of the screw 52 after full opening of the throttling holes 63 and 64 and thereby support moving to the left. When locking the valve body 40 is captured by a tapered part 72 of the spool.In Fig. 3 shows a modified construction as compared with Fig. 1, where the valve body is done is gcit manufacturing, since the closure of the cone and the cone of micromanagement can be processed separately. Tight sliding in the sleeve 23, the rod 40A of the valve is composed of an inner cylindrical sleeve 100 and the outer cylindrical sleeve 101. The outer diameter of the sleeve 101 corresponds to the diameter of the hole 30 in the sleeve 23. This outer sleeve 101 includes two through-passing each other in the axial holes 102, 103, and the diameter of the hole 103 less. This diameter is smaller and the diameter of the hole 31 in the sleeve 23. Facing the seat 41 and the end face of the outer sleeve 101 is made in the form of an obtuse cone 105, converging in the area of the diameter of the hole 31, i.e. in the area of the seat valve 41 having a rounded transition 107, so that at the end of the sleeve valve body remains the annular shoulder 108, the outer diameter is slightly less than the diameter of the hole 31. In the cartridge case 101 is made from the outer surface of the radial blind hole 109, from the base which leaves a throttling hole 110 included in the axial hole 102. Holes 109, 110 connecting hole 102 with the annular groove 32.The inner sleeve 100 comprises microdialysis cone 111 included in the hole 31, and a cylindrical section 112 through a hole 103 in automatr microdialysis housing 111 the outside diameter of the annular shoulder 108. Microdialysis cone is attached directly to the ring to shoulder, forming a smooth transition from cone 105 through section 107 to the cone 111.Through the inner sleeve 100 are two passing each other in the axial hole 114, 115, and the hole 115 has a smaller diameter. From the outer surface 112 depart two radial holes 116, 117 towards each other, from which, respectively, leave throttling holes 118, 119, ending in the hole 115. In the area of the inlet throttling holes 118, 119 through the hole 115 passes another hole 120, also starting on the outer surface 112 and closed there stopper, not shown in the drawing.The body 40A of the valve with one hand (the opposite cone micromanagement) is blocked by a screw 49A. The threaded portion 50 of the screw enters the hole 114 in the inner sleeve, the appropriate length of which is made of the internal thread 122. The head 52A of the screw so close to the end of the outer sleeve 101 so that the inner sleeve firmly attracted to the outer sleeve. Between the sleeves in holes 102 and section 112 is formed an annular chamber 123, limited by the screw. In the threaded part 50A of the screw is made of a ring is ke 52A on the side the opposite cone micromanagement made blind hole 57A, from the base which leaves a throttling hole 58A, ending in the annular chamber 123.In the hole 115 is moved to seal the spool 71A prior distribution, similar to that described in the previous example. He enters his cone 72A into the hole 114 and there communicates with the saddle 125, made in the place of passage holes 114, 115. Belt 92A on the outer surface of the spool when the seal cone 72A to the saddle 125 locks the throttling holes 118, 119. Annular grooves 90A, A form together with the wall of the hole 115 two annular channel 126, 127, communicating with each other through a blind hole 120 in any operating position of the spool prior distribution.The principle of operation of this check valve is similar to the effect of the above example of constructive perform.In Fig. 4 shows another example implementation that is different from other previous execution of the body of the valve and valve prior distribution. The same parts are denoted by the same numerals. The cone-shaped body 40B of the valve differs from the structures of the body 40, 40A of the valve reduced sidodadi each other sections 130, 131, 132. Plot 130 protruding from the holes W corresponds to the hole 47. In the area between the throttling holes V, W and end microdialysis cone V completed section 131 of larger diameter, rolling in section 132, opened in microdialysis cone. The diameter of the section 132 is smaller than the area 130. The transition between the sections 131, 132 are made in the form of a saddle W.The spool V prior distribution consists of two cylindrical sections 134, 135 and section 135 passes through microdialysis cone to the plunger 75 and interacts with him and guiding device for the spring, as described earlier. Section 135 of the valve has a smaller diameter than section 132 of the hole, resulting in between the valve and the hole in the seat formed by the annular chamber 133. In the area of the plot holes 131 segment 135 of the valve contains a narrow band 137, interacting with the saddle W. The diameter of the belt is equal to the diameter of plot holes 130 Section 135 of the spool in the field of throttling holes V, V enters the segment 134, tightly sliding in the hole 130, and into the holes W. Between segment 135 of the spool and plot holes 130 remains extended Koltsevaya 137 adjacent to the saddle W.In the spool V, as in the previously described embodiments, there is a limit hole B protruding from the holes B and communicates with the transverse hole W.When nevidimom the pusher proportional magnet 13 belt 137 under the action of the spring adjacent to the saddle W.At the same time the segment 134 of the valve overlaps the throttling holes V, W. In this position, the working medium passes from the pipe 19 to the inlet side through hole 18, the annular channel 36 and the annular groove 32 in the orifice 66. From here through the blind hole 61 and the longitudinal channel 67 has access to the annular chamber 54, connected, in turn, longitudinal channel 70 with a blind hole 62.The annular chamber 54, as described above, according throttling hole 58 with the pressure chamber 60. The impact of hydraulic fluid and mechanical forces in the case newadvent pusher proportional magnet as described in the example according to Fig. 1.When moving the spool W pusher 75 to the left belt 137 is moving away from the saddle V and previously buried on the one hand segment 134 of the valve throttling holes V, W offer. In this working environment comes from blind holes 61, 62 through D. the annular chamber 138 leading to the hole 31. The latter, as described earlier, communicates with the pipe 21 on the output side.The opening and closing of the seat valve 41 is the same as that described in the example according to Fig.1. 1. Device for controlling a hydraulic cylinder containing the main shut-off and control element, accommodated in the housing with the formation of end camera control and interact with its stepped conical part with the saddle, made in the housing and separating the inlet and outlet pipes, and also specifies the proportional element with the plunger resting on spring hollow managing locking and regulating element is a stepped shape having a locking element saddle valve, placed in the axial bore of the main shut-off and control element and separating the control end of the control chamber and connected with the inlet pipe, made mostly shut-off and control element, radial channels from the outlet of the nozzle, characterized in that the control valves and the element is made of c consecutive shut-off element saddle valve area of the control spool overlapping in the initial position of the radial channels cos the measure, connected through a choke with end camera control, and through the other orifice with the inlet pipe, and an intermediate chamber with connection Manager shut-off and control element through the area of the control spool via open them channel with outlet connections.2. The device under item 1, characterized in that the built-in chokes are made in the form of holes of constant cross-section.3. The device according to PP. 1 and 2, characterized in that the intermediate chamber is connected to radial canals by means of longitudinal channels made around the axial bore of the main shut-off and control element.4. The device according to PP. 1 to 3, characterized in that the radial channels made with Windows that communicate with the belt control valves element with the formation of the throttling slots of variable cross-section.5. The device according to PP. 1 to 4, characterized in that the control valves and the element is spring-loaded by spring tension, situated on the side of the pusher master element made in the form of a proportional electromagnet.6. The device according to PP. 1 to 5, characterized in that step nonmicrosomal cone and a truncated cone with an obtuse angle at the vertex.7. The device according to PP. 1 to 6, characterized in that the control valves and the element has an annular groove, providing hydrostatic pressure compensation.8. The device according to p. 7, characterized in that, in the main shut-off and control element made blind hole intersecting the axial bore with the ability to connect the annular grooves of the control valves of the element.9. The device according to PP. 1 to 8, characterized in that the main shut-off and control element made of composite of inner and outer sleeves.10. The device according to PP. 1 to 6, characterized in that the annular working edge of the control valves of the element is made in the form of a cylindrical band, interacting with a saddle on its flat end surface.
FIELD: automotive industry.
SUBSTANCE: distributor comprises housing provided with the central cylindrical bore and control passages oriented radially, cylindrical slide with collars sealed over the outer surface, at least one electropneumatic control valve, and system of passages and air-lines that connect the distributor with the actuator (air-operated cylinder). The cylindrical slide is mounted directly in the bore of the housing for permitting axial movement.
EFFECT: enhance reliability.
4 cl, 5 dwg
SUBSTANCE: hydraulic control valve is designed to control hydraulically operated assembly units of mobile machines. The two-stage hydraulic control valve with controlled time of the second stage slide valve switching over consists of the first stage hydraulic control valve with electromagnets and the second stage hydraulic control valve comprising a body with cast channels to connect the working hydraulic lines and control lines, a slide valve with return springs arranged on its ends, end face covers. In compliance with this invention, threaded throttle control elements interacting with spring-loaded check valves are arranged in the said end face covers, one in each cover.
EFFECT: simplification of design, higher reliability.
FIELD: machine building.
SUBSTANCE: invention relates to machine building and can be used in control over whatever assemblies with actuators controlled by remote means. The electrohydraulic on\off four-line slide control valve with actuator and hydraulic valve is proposed. Note that the actuator front flange accommodates a hydraulic valve. Working fluid is fed from the electrohydraulic valve into the slide control valve chambers via the hydraulic valve.
EFFECT: higher reliability.
FIELD: instrument engineering.
SUBSTANCE: said unit is designed for valve control of operating fluid to various hydraulic consumers. The unit comprises a square metal case with internal channels, four external branch lines and independent tank ports, pilot-operated valves consisting of a gate, a pilot, a flange with supply, branch and tank ports with in-built end cap in one of two control pressure supply (branch) channels to the gate, the return valves in-built in branch channels of external branch and supply lines of operating fluid. The initial position of the unit involves combined number and arrangement of plugs in the flanges, the return valves supplying control pressure from external supply and branch lines to the gates of the controlled valves thereby changing between normally opened on normally closed positions thereof and on the contrary. There are twelve such positions, and further changing of the unit positions is carried out by combination and number of the pilots actuated by electric means. The return valves ensure supply (branch) of operating fluid to any of four external lines.
EFFECT: high leak tightness, handling ease and ease of fabrication; high reliability and maintainability.
FIELD: engines and pumps.
SUBSTANCE: proposed valve serves to vary direction of the flow and/or to start (stop) compressed airflow in air lines of pneumatic drives depending upon mechanical, pneumatic or electric control effect. It consists of plunger casing at least one electropneumatic valve and mechanical back-up drive. Plunger built-up casing consists of metal perforated tube supporting parts fitted thereon and made from polymer thermoplastic material, said parts being tightened together by flanges with the help of nuts and studs. Casing tightness is provided for by a system of sealing elements. Electropneumatic valve of control valve incorporates reinforced locking elements of the armature.
EFFECT: reduced weight and costs, higher reliability and expanded performances.
10 cl, 16 dwg
FIELD: machine building.
SUBSTANCE: hydraulic valve consists of case with channels of hydraulic feed supply and working cavity channels, of electro-hydraulic valve, of hydraulic compensator with isolating valve, of two-stage-electro-fluid amplifier of "nozzle-gate" type, of damping throttle, and of two replenishing and two safety valves. The hydraulic valve is equipped with six-port two-position annular flow valve with a slide of small length with internal channels and a throttle orifice in a collar of the slide. The valve shuts off a drain channel of the electro-hydraulic amplifier from a draining hydraulic line running to the hydraulic compensator and simultaneously it communicates it with a drain through the throttle orifice in the collar of the slide when the working cavity channels operate under the mode of annular flow. Also, the valve totally communicates the drain channel of the electro-hydraulic amplifier with the drain hydraulic line to the hydraulic compensator and cuts off the throttle orifice in the collar of the slide from the drain channel of the electro-hydraulic amplifier under the control mode.
EFFECT: raised reliability, simplified design, and reduced dimensions and weight of hydraulic valve.
FIELD: engines and pumps.
SUBSTANCE: device is meant for control of position of actuator in aircraft engine using electrically controlled servo-valve. Actuator (50) includes a slide (52) with at least two steps (54, 56) meant for sliding in cylinder, and two chambers (62, 64) of control connected with corresponding workholes (85, 86) of electrically controlled hydraulic distributor (20) of servo-valve. Chambers (62, 64) of control are located each on one side of corresponding step, and intermediate chamber connected to high or low pressure is located between other sides of steps. In case of failure of electrical control a slider of distributor (20) is set to protection position in which in chambers (62, 64) of control of actuator the same low or high pressure is settled opposite to pressure generated in intermediate chamber (66), so that each step (54, 56) of actuator slider is influenced by high pressure on one side and low pressure on the other side. Tightness between each step (54, 56) of actuator slider and actuator cylinder (60) is provided by dynamic sealing (70) producing friction force between step and cylinder depending on pressure difference influencing two sides of step, so that in case of failure of electrical control actuator slide valve stops in its position at the moment of failure ("failure freezing"). Actuator (50) may be a unit for aircraft engine fuel measurement.
EFFECT: higher reliability.
4 cl, 10 dwg
FIELD: machine building.
SUBSTANCE: proposed mechanism comprises pilot stage made up of electrohydraulic proportioning valve electrically connected to control unit, main stage made up of three-line restricting slide multiposition hydraulic control valve and element indicating filling of throw-in friction-clutch hydraulic cylinder. Main stage and pilot stage attached to main valve body joint surface are integrated in single unit. Said indicator is structurally separated from main stage. Main stage body hydraulic chambers are arranged on the side of its joint to controlled structure and geometrically defined by combination of planes and cylindrical surfaces. Said chambers are produced by machining to feature box shape. Aforesaid indicator is made up of one or several elements, i.e. pressure gage, working fluid flow valve, or flow rate meter, friction-clutch drive and drive part rpm transducers.
EFFECT: higher reliability.
7 cl, 9 dwg
FIELD: machine building.
SUBSTANCE: distributor has valve four-line three position symmetrical hydraulic circuit with discharge, drainage lines, and with two output lines with separating cavities of the hydraulic engine. It contains three amplification cascades and hydraulic lock. All shutoff-control elements are made in form of balls.
EFFECT: significant improvement of design of the hydraulic distributor for operation with electrolytic aggressive and low viscous sea water as work liquid of the hydraulic distributor in drives of the underwater robot.
3 cl, 2 dwg
FIELD: hydro automatics.
SUBSTANCE: invention relates to hydro automatics, particularly to electro-hydraulic amplifiers, and can be used in high-precision control systems of working mechanisms of movable vehicles and aircrafts. Electromechanical converter is made in the form of a stepper motor with discrete nature of movement and digital control, mechanism for returning a four-clamp cylindrical slide valve in neutral position comprises a preliminarily compressed centering springs located in the end cavities of the four-clamp cylindrical slide valve.
EFFECT: obtaining a digital control and reduced impact effect of reverse jets in the hydraulic amplifier due to a stepper motor with finite number of stable positions.
1 cl, 1 dwg