Electrohydraulic control device for a user double action

 

(57) Abstract:

The device is intended for hydraulic systems. In the device using two proportional working 4-way 2-position solenoid valve truck valve element and through two shut-off valves truck designs possible continuous control of flow to the consumer and from him, and as the fourth operating position is achieved freeplay. Solenoid valves have the same design and installed on each path volumetric flow of current to the consumer and arising out of it, and each accession for the consumer hermetically blocked saddle valve element of the solenoid valve and shut-off valve. Solenoid valves contain the main governing and pre-control links, interacting with each other in the type of servo control and without costing a separate supply of hydraulic oil. The technical result - can be continuously and with a short response time to manage high hydraulic capacity. 19 C.p. f-crystals, 10 ill.

Art

The invention proceeds from electrohydraulic shown in restrictive part p. 1 of the claims.

From European application N 0110126 A1 already know this electrohydraulic control device, which has to manage the user double action moving in the longitudinal direction of the spool 4-linear 3-point definition is driven by two opposite located on the body magnets. To reduce leaks each joining user is locked hydraulically operated shut-off coupling with valve and the function of preliminary control these shut-off valves take those rods that pass including the movement of the magnets on the spool. In addition to the functions of lifting, holding and lowering, due to the simultaneous excitation of both magnets can be achieved additionally fourth position for free running. In addition, the control device can also be used to control the user a single action. The disadvantage of this control device is that it works with pure comprising magnets and therefore accurate proportional control of the volumetric flow is impossible. In addition, the performance of stocks as a pre-control links leading to relate is combined with 4-way 3-way plunger valve and with employees prior to control rod leads to a significant increase constructive length along the axis of the spool, what makes the control device is unsuitable for mobile applications.

Next, application Germany N 4140604 A1 it is known electrohydraulic control device, working with a proportional magnet and is suitable for precise control of the volumetric flow. While located in the main valve element pre-control valve element driven by the proportional magnet interacts type servo control main valve element than is achieved in the short time of operation and, thereby, good regulating characteristics. Valve units for the speed of the main and preliminary control is designed in the form of a saddle valve, allowing leakage is minimal. The control device is so designed that a separate supply of hydraulic oil is not necessary. The disadvantage of this control device is that it can only perform the function of the 2-linear 2-point distribution, and therefore unsuitable in that state for controlling double-acting consumer.

Advantages of the invention

Electrohydraulic control device according to the invention with a distinctive prozacbuy it can manage user double action with minimal leakage. Thanks to the choice of the drive spool solenoid valves provide a short response time, which leads to a good adjustment to the characteristic control device, which can achieve, in General, four operating positions with only two magnets, so, besides the usual functions of lifting, holding and lowering, due to the excitation of both magnets may fourth position as a free wheel; the sequence of inclusion in this arbitrary. The control device operates without a separate supply of hydraulic oil and can be also used for a user a single action. The controller is compact and therefore suitable for mobile applications.

Thanks are given in the dependent claims measures possible preferred modification and improvement of a control device according to p. 1. Particularly preferably, if used to regulate the volumetric flow solenoid valves are made pursuant to sub. 2-9, which is especially optimally achieved these goals. Especially useful if shutoff valves are made pursuant to sub. 10-12, which provides nadineeee device can be used on one side of the housing, due to which cost perhaps additional mechanical connection; this achieves a compact design. Further preferably, if the body is made under item 15 or 17, so that the necessary seat for the main valve parts in body cheap to manufacture. Appropriate next run on PP 16, 18 and 19, and the position of the isolation valves in the casing provides a compact design and short channels have a positive impact on the control characteristic. Other preferred embodiments of the shows in the rest of the items in the description and in the drawing.

Drawing

The exemplary embodiment of the invention shown in the drawing and explained in more detail in the following description. In the drawing depict: Fig. 1 is a simplified diagram of an electrohydraulic control device for a user double action; Fig. 2 is a longitudinal section in proportion to the running of the electromagnetic valve in a simplified design implementation, as is shown in Fig. 1 in the form of a diagram; Fig. 3 - part of the control device of Fig. 1 with shut-off valves in the simplified control circuit; Fig. 4 is a longitudinal section of a separate shut-off valve in a simplified design, the determinant of the device of Fig. 1 in a simplified design execution, and this longitudinal section is depicted by the line VI-VI of Fig. 7; Fig. 7 is a cross-section on the line VII-VII of Fig. 6; Fig. 8 is a cross-section on the line VIII-VIII of Fig. 6; Fig. 9 is a section along the line IX-IX of Fig. 7; Fig. 10 is a longitudinal section of a second form of execution in proportion to the running of the electromagnetic valve for use in the control device of Fig. 1.

Description of examples of implementation

In Fig. 1 simplified schema depicted electrohydraulic control device 10 to control the consumer 11 double action, used for load-break switches. The control device 10 contains two electromagnetic valves 12, 13 are of the same design. Both performed as a proportion of operating valves with 4-linear 2-point distribution, driven by corresponding proportional magnet 14, 15. Each solenoid valve is arranged to move its respective magnet 14 or 15 against the force of the spring 16 from the initial position 17 in the working position 18, and in proportion to the electrical input of the control value flow continuously produced electromagnetic valve 12 and 13 is odvod 19, attached to the adjustable pump 21, which supplies the working fluid. Next, each of the electromagnetic valve 12, 13 contains marked with the letter R drain 22 is discharged into the tank 23. In addition, each solenoid valve 12, 13 contains the letters A and B corresponding accession 24 and 25 for engines. In the depicted initial position 17 supply 19 is hydraulically blocked connection 24 for the engine is connected to the drain 22, and connection 25 for the engine blocked saddle valve element 26 of the electromagnetic valve 12, 13. When the deviation in the working position 18 supply 19 is connected with connection 24 for the engine, and the accession of 25 for the engine is discharged into the drain 22, and these connections are made with the possibility of permanent control.

In the control unit 10 from the connection 24 for the engine on the solenoid valve 12 to the connection 28 to the consumer leads the working channel 27, which is equipped with a shut-off valve 29 with hydraulic control. Shut-off valve 29 is made in the form of controlled non-return valve, with the inlet 31 is connected with connection 24 for the engine, release 32 - 28 accession to the consumer, and the control connection 33 in ctromagnetic valve 12 to the connection 36 to the consumer leads the bypass shut-off valves drain channel 35.

Accordingly the solenoid valve 13 from the connection 24 for the engine to attach to the consumer leads the working channel 37, which is equipped with a shut-off valve 38 is identical with shut-off valve 29 design. From the connection 25 to the engine, the solenoid valve 13 to the connection 28 to the consumer leads the bypass shut-off valves 29, 38 drain channel 41.

The control device 10 includes a further changeover valve 42, valve 43 which is spring centered to the middle position. Rocker valve 42 attached to its end connections 44, 45 for supplying pressure respectively to the channels 27 and 37 before shut-off valves, respectively, 29 and 38, while its average connection 46 informs the regulated pump 21 corresponding to the maximum pressure load or when there is no pressure or equal pressures unloads this average connection 36 in connection 47 to the tank.

In Fig. 2 shows a longitudinal section of the electromagnetic valve 12 in a simplified design execution, schematically depicted in Fig. 1. This assumes that the proposal from Germany N 4140604 A1 famous design of the control device of nekovee with Fig. 1 elements are denoted by the same reference position.

In Fig. 2 in the housing 50 of the electromagnetic valve 12 is made through the spool bore 51 with a few concessions, in which close through the annular extensions formed the inlet chamber 52, the first chamber 53 for the engine, drain camera 54, the intermediate chamber 55 and the second chamber 56 to the engine. These cameras are connected properly with the inlet 19 (P), the first 24 accession (A) for the engine, drain 22 (R) and the second joining 25 (B) for the engine. In the bore 51 is a main control link 57 within which is located a pre-control link 58, which is driven by the anchor 70 is proportional magnet 14 against the force of the spring 16. Both link 57, 58 operate on the type of servo control, and for reliable sealing the second chamber 56 for the engine they perform the functions of saddle valves. The main control element 57 includes for this purpose at its pointing away from the magnet 14 the end of the main valve cone 59, which communicates with still located in the body seat 60 between the second chamber 56 to the motor and an intermediate chamber 55. Master control link 57 limits with the butt of his superior is 2, loading master control link 57 in the direction of its initial position 17. Next, the main valve cone 59 is made so that it forms loaded by pressure in the second chamber 56 engine first differential surface 63, the loading master control link 57 in the direction of opening. The connection from the second chamber 56 to the engine through the intermediate chamber 55 to the drain chamber 54 downstream from the main valve cone 59 controls the first segment 64 of the plunger with chamfers 65 for precision control. On the main control link 57 at a distance from the first segment 64 of the plunger in the zone of the first chamber 53 for the engine is made of the second section 66 of the plunger, through which the second control edge 67 and the respective grooves 68 for precision control connection from the inlet chamber 52 to the first chamber 53 for the engine. Facing the magnet 14, the end of the main control link 57 is made so that it forms loaded by pressure in supply 19 second differential surface 69 which, when the loading pressure with a first pressure surface 63 loads the main control element 57 in the direction of opening. On the main control link 57 second tretau 53 for the engine with the drain chamber 54.

Pre-control link 58 is to control the flow of hydraulic oil from the pressure chamber 61 to the drain chamber 54 performs the function precision control edge 72 of the valve and perform the function of the secure sealing of the pre-control cone 73, consistently located in the flow of hydraulic oil. Pre-control link 58 is made with pressure compensation and loaded resting motionless on the spring case 16 in the direction of the initial position 17, and it is backed its previously managing cone 73 on the corresponding seat in the main control link 57. Pressure chamber 61 can be alternately loaded with the operating fluid pressure in the inlet chamber 52 can flow through the longitudinal bore 74 and is located stationary on the housing of the check valve 75 to the inlet orifice 79 in the pressure chamber 61. At high pressure load in the chamber 56 to the engine working fluid flows through located in the main valve cone 59 check valve 76 to the inlet orifice 79 in the pressure chamber 61. For draining the working fluid from the pressure chamber 61 through the pre-control link 58 in the main control link 57 steps you electrohydraulic control device 10 will be explained below with reference to Fig. 1 and 2.

In the first position "neutral" both proportional magnet 14, 15 is de-energized, and the solenoid valves 12, 13 are in their respective initial position 17. Thus, their supply 19 is blocked, as shown in Fig. 2 the second control edge 67 of the second segment 66 of the plunger. Further, in the initial position 17 each solenoid valve 12, 13 connection 24 for the engine unloaded to a drain 22, and in Fig. 2 the third control edge 71 on the second leg 66 of the plunger controls the connection from the first chamber 53 for the engine to drain the chamber 54. Later in this original position 17 of the second joining 25 for motor truck blocked the valve element 26 of the respective electromagnetic valves 12, 13 to reduce oil leaks. The main valve cone 59 is pressed by the pressure in the pressure chamber 61 to the corresponding saddle 60, because the higher of the pressures existing in the second chamber 56 to the engine or in the inlet chamber 52 can flow through the check valves 76, 75 in the pressure chamber 61 and there's loads more pressure surface 62. Thus the closing force acting on the main control element 57, in any case, more effort opening, katorevenge in the inlet chamber 52 on the differential surface 69. Pressure chamber 61 is securely managing pre cone 73 on the pre-control link 58. The very pre-control link 58 is pressed by a spring 16 is fixedly supported on the housing, to the corresponding seat in the main control link 57.

In this neutral position, the solenoid valves 12, 13 unload adjacent segments of the respective operating channels 27, 37, so that the inlet 31 of the respective shut-off valve 29, 38 there is no pressure. After crossing the control line 34, 39, pressure balanced control accession 33 both shut-off valves 29, 38, the valves are pressed by their springs into the corresponding locking position, so that the release 32 is hydraulically blocked. Thus, the first connection 28 for the consumer also hydraulically blocked the first shut-off valve 29 and saddle valve element 26 in the second electromagnetic valve 13, while the second connection 36 for the consumer blocked the second shut-off valve 38 and saddle valve element 26 in the first electromagnetic valve 12. In the consumer 11 double-acting hydraulically blocked, thereby, the piston rod 78.

1, the proportional magnet 14 of the first electromagnetic valve 12 is current, what is the proportional flow rate control to the user 11. The magnet 15 of the second solenoid valve 13 is de-energized. After you move the first electromagnetic valve 12 to its operating position 13 he connects the inlet 19 with the first accession 24 for the engine, so that the working fluid flows from the regulated pump 21 through the electromagnetic valve 12 and the first working channel 27, and through the opening shut-off valve 29 to the first connection 23 for the consumer and, thus, into the cylinder chamber of the consumer 11. The first shut-off valve 29 acts as a purely non-return valve as its control connection 33 unloaded into the tank through the first control line 34, the length of the second working channel 37 and the second solenoid valve 13. At the same time, the second solenoid valve 13 blocks the second drain channel 41 his saddle valve element 26. The working fluid flows from the annular cavity of the user 11 via the second connection 36 for the consumer and the first drain channel 35 to the second connection 25 for the engine on the ground electromagne shut-off valve 29 in the first working channel 27 occurs through the second control line 39 also in the control accession 33 of the second shut-off valve 38, due to which it operates as a shut check valve and blocks their output 32 from the inlet 31. The pressure in the first working channel 27 is supplied via the connection 44 to the supply pressure changeover valve 42, the other connection 45 for supplying a pressure which is discharged into the tank. The spool 43 changeover valve 42 is moved to its right end position, the pressure comes from the first joining 44 for supplying pressure through the secondary connection 46 in the load pressure line to a regulated pump 21, while the connection 47 to the reservoir is blocked. The control device 10 can, therefore, operate in a known manner as a load break switch.

When the deviation of the electromagnetic valve 12 in the position "up", i.e., in the working position 18, the efforts of the proportional magnet 14 would not be able to directly control considered here hydraulic power. For this reason, the chief Executive of the link 57 is required auxiliary drive, which is designed according to the type of servo control. Located in the main control link 57 pre-control link 58 is made for this purpose with pressure compensation and what about against the force of the spring 16. However, his pre-control cone 73 opens a connection from the pressure chamber 61 through the pre-control link 58 and the transverse bore 77 to the drain chamber 54. While previously the managing cone 73 provides a sealed block, the edge 72 of the spool preliminary control link 58 provides precision control of the flow of hydraulic oil in order to continuously control the pressure in the pressure chamber 61. When opening the connection edge 72 of the spool and advanced managing cone 73 decreases the pressure in the pressure chamber 61, and decreases, thus, the closing force acting on the main control link 57. Current to the first differential surface 63 of the pressure load in the second chamber 56 to the motor and acting on the second differential surface 69 of the input pressure in the inlet chamber 52 is driven by the main control element 57 of Fig. 2 to the left, and the main control element 57 in a known manner follows the previously managing link 58 on the type of servo control. Thus the opening movement of the main valve cone 59 is lifted from the located stationary in the body of the saddle 60 and Sol precision control to the drain chamber 54. Regulation of the magnitude of the volumetric flow from the second accession of 25 for the engine to drain 22 is constant, and thus, proportional to the value of the current to the magnet 14. During this opening movement of the main control link 57 his third control edge 71 on the second leg 66 of the plunger blocks the connection from the first chamber 53 for the engine to drain the chamber 54, while simultaneously, the second control edge 67 opens the connection from the inlet chamber 52 to the first chamber 53 for the engine. The volume flow control with grooves 68 for precision control. During this process of managing both small check valve 75, 76 series with the respective inlet choke 79, choose a higher pressure to drive the main control link 57. It is either the inflation pressure in the inlet chamber 52, or the pressure load in the second chamber 56 to the engine, first of all, if dominated by pulling a load. This higher pressure is always acting on the larger pressure surface 62 and causes the closing force on it. Using the first electromagnetic valve 14 is, therefore, in position "up" the volume control on the face of the control element 57, so the control flow is proportional to the value of the current to the magnet 14.

In the third position "lower", corresponding to the lowering of the piston rod 78 of the consumer 11, is driven only by the second solenoid valve 13, while the first electromagnetic valve 12 is not excited. Volumetric flow is moving in respectively opposite direction to the consumer 11 double-action from him. When the working fluid flows from the regulated pump 21 through which in the working position 18 and the second solenoid valve 13, the second working channel 37, operating as a check valve, the second check valve 38 to the connection 36 to the consumer and further into the annular cavity of the consumer 11. Simultaneously, the working fluid drained from the cylinder bore of the user 11 via the first connection 28 for the consumer, the second drain valve 41 and the second solenoid valve 13 into the tank 23. The first shut-off valve 29 operates as locked-return valve, while the changeover valve 42 is another its final position and connects the connection 45 for supplying a pressure medium accession 46 and, thereby, with adjustable pump 21. These the first valve 12, the type of servo control.

For the fourth position of the control device 10, namely a free motion, magnets 14, 15 both of the electromagnetic valves 12, 13 simultaneously served the maximum current, rejecting them, thus, in their working position 18. Thus, the pressure in both working channels 27, 37 in their segments for the respective shut-off valves 29, 38 upstream of the same. This pressure is fed through the respective intersecting control lines 34, 39 to the control connections 33 both of the respective shut-off valves 29, 38, through which they work as locked-in check valves. Due to the equal pressure valve 43 changeover valve 42 remains is depicted in the middle position, so that the average of the accession 46 offloaded to the connection 47 to the tank, and attach 44, 45 for the supply pressure is blocked. This means no signal load switch for supplying pressure through an adjustable pump 21 and, thus, no increase in pressure. Both sides of the channel 35, 41 unloaded respective solenoid valves 12, 13 in the tank 23, so that the user 11 double action makes freeplay.

With the aid of which the user 11 double-acting consumer single action only connected to the first connection 28 to the consumer, and the second connection 36 for the consumer is not used. In this case the neutral position is achieved, as before, if the two magnets 14, 15 are not excited. The position "up" is achieved when the supply current only to the first electromagnetic valve 12, and the position of "lowering" - when applying current to both solenoid valves 12, 13, and the valve 13 is rejected only in accordance with the desired current sinking.

With this control device 10 can be implemented, thus, along with the function double-acting as a single action, and using two magnets, it is possible, in General, four operating positions. The control device 10 operates without a separate supply managing pressure, and due to my truck valve elements with small leaks. With the free course or when lowering in the implementation of the functions of the single steps are not necessary pressure release and thereby increase the pressure of the pump. Due to the selected actuator spools solenoid valves 12, 13 can achieve a short response time, so that the control device 10 has a good control characteristic.

In Fig. 3 diagrams the ROM 81 of the control lines. Avoid crossing control lines 34, 39 in Fig. 1, which is undesirable in the valve body, the circuit 81 in Fig. 3 contains the main control line 82 which connects both governors joining 33 both shut-off valves 29, 38. Later in the gates 83 both shut-off valves 29, 38 there is one little check valve 84 and parallel to the orifice 85. A small check valve 84 in the shutter 83 is used to activate the solenoid valve 12 or 13 is appropriate shut-off valve 29 or 38 could work as a simple check valve and relatively fast to open. In parallel to the choke 85 shut-off pressure can be directed through gate 83 on its rear side, so that the need for intersecting lines disappears. When triggered, only the electromagnetic valve 12, the pressure p1 in the inlet 31 more pressure p3 in the control accession 33, the check valve 29 operates as a check valve and gate 83 is lifted from the seat. Simultaneous activation of both the solenoid valves 12, 13 pressure p1 and p3 are equal in size, so that the spring 86 holds the shutter 83 is pressed against the saddle position. The circuit 81 for schev 29, 38 is retained if the orifice 85 is only one of the two gates 83.

In Fig. 4 shows a longitudinal section of a shut-off valve 90, which is feasible functions is schematically depicted in Fig. 3 shut-off valve 29. Schematically depicted in Fig. 1 and 3 shutters are made so that they have the ratio of the diameter of the seat diameter of the neck is 1. This embodiment assumes hardened saddles that adversely when performing the control valve 10 in a die-cast housing. In order to therefore facilitate the implementation of the shut-off valve 29 in Fig. 3 die-cast, locking the valve in Fig. 4 is executed as a valve with a differential surfaces, which does not require precise diameter of the saddle, but on the contrary, works with a relatively wide geometry saddle and costs due to the small specific pressure die-cast. To perform as a valve with a differential surfaces shutoff valve 90 includes hiltebrand gate 91, which controls the connection from the inlet 31 to the outlet 32 and is installed with the possibility of hermetic sliding on the finger-continued 92 of the locking plunger 93. The shutter 91 is backed through the spring 94 for locking the plunger 93, 92 continuation is 96 housing and limits the camera 97, hosts the spring 94 and through which the throttle groove 98 is associated with the release of 32. In the locking plunger 93 is made coming from the inlet 31 to the control connection 33, the groove 99, which is known in itself, throttle return valve. When this function return valve 84 in Fig. 3 performs a triangular washer 101, in which the orifice 85 is made in the center of the small hole. In cross section in Fig. 5 visible form of this triangular washer 101.

Using shut-off valve 90 in Fig. 4 can constructively to implement the function of the stop valve 29 in Fig. 3, and from managing accession 33 leaves only one main control line 82. If this shut-off valve 90 controls the accession 33 unloaded, and the pressure p3 is equal to zero, when the volumetric flow at the inlet 31 of the shutter 91 is opened and when the increased pressure p1 will send volumetric flow in issue 32, a pressure p2 which is less than the pressure p1. On the contrary, if the control connection 33 is loaded, and the pressure p3 is equal to the pressure in the inlet 31, the check valve 90 is blocking the connection to release 32. The locking plunger 93 is displaced when the pressure in the control accession 33 against the force of the spring 94 and underlying digno located in the housing of the saddle.

In Fig. 6 in the form of a longitudinal section shows the design of the control device 10 in Fig. 1, with the same elements as in Fig. 1-5, are denoted by the same reference position. In comparison with the control device, schematically shown in Fig. 1, the control device of Fig. 6 additionally includes a housing 50 individual valve 105 a constant pressure difference associated with both the solenoid valves 12, 13. To explain the control device of Fig. 6 reference should be made to Fig. 7 - 9, depicting respectively sections on the lines VII-VII, VIII-VIII of Fig. 6 and the section along the line IX-IX of Fig. 7. In addition, specify the exact nature of the longitudinal section in Fig. 6 along the line VI-VI in Fig. 7.

The control device 10 in Fig. 6, the housing 50 has basically the shape of a rectangular parallelepiped, because the device is designed for sabovoy the design of the LS system. In case both solenoid valves 12, 13 are installed with their longitudinal axes parallel to each other so that one end surface 106 placed both proportional magnet 14, 15. By placing both of the magnets on one side of the control device 10 is particularly suitable for mechanical actuation. On cescolini ledges spool bore 51 of both the electromagnetic valves 12, 13. Mounting surface 107 is closed by the cover 108, which made the first connection 28 for the consumer, while the second connection 36 for the consumer lies in the heart of the case 50. Both join 28, 36 are open to the surface 109. In higher bore 51, is made in the case 50 is closer to the surface 109, the first electromagnetic valve 12 and the second solenoid valve 13 is installed in the underlying higher bore 51. As further depicted in Fig. 6, the inlet chamber 52 of both the solenoid valves 12, 13 are connected and directed to the inside of the valve 105 a constant pressure difference, which can be supplied with working fluid through connection 111 adjustable pump 21.

As further depicted in Fig. 7 and 8, the solenoid valves 12, 13 are located in different longitudinal planes parallel to the flange surfaces 112 of the housing 50. Due to the passing at a distance from each other in longitudinal planes through the solenoid valves 12, 13 can be located closer to each other when viewed in the direction of height that provides a compact design and short channels. As further depicted in Fig. 7 in conjunction is their electromagnetic valves 12, 13. Thus in Fig. 7 shows that the distance between passing through the shut-off valves 29, 38 longitudinal planes substantially greater than the distance between the longitudinal planes passing through the solenoid valves 12, 13. In addition, shut-off valves 29, 38 are offset in height relative to each other to provide a particularly compact design. It is evident from Fig. 7 shows that the second connection 36 to the consumer associated with the second camera 56 engine first electromagnetic valve 12 and, additionally, with the release of 32 of the second shut-off valve 38. Later in the same plane section of the second chamber 56 to the second engine valve 13 associated with the release of 32 of the first shut-off valve 29 and simultaneously connected with the first 28 accession to the consumer through the bottom of the recess 113, and a transverse channel 114 and the vertical channel 115.

As can be seen further from Fig. 8, the first chamber 53 for the first engine of the electromagnetic valve 12 is directed obliquely downward u-shaped recess, so that it is connected with the inlet 31 of the first shut-off valve 29, as shown in more detail in Fig. 9. Accordingly, the first chamber 53 for the engine of the second solenoid valve 13 alapana 38, as shown in more detail in Fig. 9. The discharge chamber 54 of both the solenoid valves 12, 13 are connected through the drain channels 116 and connecting or end plate (not shown). Accordingly, as in the drain channels 116, through the housing 50 passes pumping channel 111.

As can be seen from Fig. 6 in conjunction with Fig. 9, due to such arrangement of solenoid 12, 13 and gate 29, 38 of the valve is achieved that all arranged stationary in the housing seat in two Bolotnikova the bores 51 of the electromagnetic valves 12, 13 and bores 96 of the housing for shut-off valves 29, 38 are open to the mounting surface 107 and can be well treated there. Due to the constructive execution of the control device 10 in Fig. 6 achieved all of the features and advantages described in connection with the control device of Fig. 1. In addition, the spatial location of both electromagnetic 12, 13, both the shut-29, 38 and rocker valves 42 in the housing 50 leads to an extremely compact design, especially suitable for mobile use. As can be seen from Fig. 9, the shut-off valves 29, 38 can also completely abandon function composed of washer-like valve 101 and to provide only the military between main control line 82 should be in this case only half more load.

The principle of operation of the control device 10 in Fig. 6, in General, similar to the principle of the control device of Fig. 1, and reference should be made to the principle of operation of the electromagnetic valve 12 of Fig. 2 and shut-off valve 90 in Fig. 4. Below you only want to comment briefly on the nature of the flow in the housing 50, resulting in the "lifting" and "lowering". If set to "rise" has only worked electromagnetic valve 12, the volumetric flow flowing from the pump channel 111 through the valve 105 a constant differential pressure in the inlet chamber 52, passes through a second control edge 67 in the first chamber 53 for the engine. As can be seen from Fig. 8, the volumetric flow flowing down there in the u-shaped notch and goes from there to the inlet 31 of the second shut-off valve 29, as shown in Fig. 9. Shut-off valve 29 opens a connection to your issue 32, where the ow rate, as is evident from Fig. 7, flows through the second chamber 56 to the engine at the second solenoid valve 13 further down in the pocket-type hollows. provinces in the recess 113, where it is through the cross channel 114 and the working channel 115 in the cover 108 goes to the first connection 28 for the consumer. At the same time, the current back from the consumer volumetric flow is directed into utmaning valve 12 and open the main valve cone 59 through the intermediate chamber 55 and chamfers 65 for precision control in the discharge chamber 54. As further shown in Fig. 7, this current back volumetric flow gets to release 32 of the second shut-off valve 38, which, however, due to the pressure loading through the main control line 82 operates as a shut check valve and blocks the connection to its inlet 31.

If set to "lowering" is triggered only the second solenoid valve 13, and then supplied through the valve 105 a constant differential pressure volume flow flows from the common inlet chamber 52 into the first chamber 53 for the engine of the second valve 13. As further shown in Fig. 8, the volumetric flow goes from there through directed obliquely upward in the recess of the first chamber 53 for the engine in the inlet 31 of the second shut-off valve 38. The latter operates as a check valve and opens a connection to his edition 32, where the ow rate, as shown in more detail in Fig. 7, flows past the second chamber 56 of the first electromagnetic valve 12 to the second connection 36 for the consumer and on to the consumer 11. Stemming from the consumer 11 volume flow passes through a connection 28 for the consumer, the working channels 115, 114 pocket-type hollows. provinces in the recess 113 and further into the second chamber 56 to the engine of the second Elet through the intermediate chamber 55 to the drain chamber 54. The rest of the function changeover valve 42 and three-dimensional flows in the "free running" can be seen from Fig. 1.

In Fig. 10 shows a longitudinal section of another constructive form of execution of the electromagnetic valve 120 that is used in the control device 10 for a schematic of the electromagnetic valves 12, 13. The solenoid valve 120 is comparable in its basic construction to the electromagnetic valve 12 of Fig. 2 in that it contains a main control link 121 and located it pre-control link 122, interacting with each other in the type of servo control, and pre-control link 122 is actuated by the armature 59 is proportional magnet 14. In the housing 50 of the electromagnetic valve 120 is performed end-to-end, with several ledges spool bore 123 through the annular extensions formed the inlet chamber 124, the first and second chambers 125 and 126 respectively to the engine, the intermediate chamber 127 and the drain chamber 128. The inlet chamber 124 is connected with the inlet 19 (P), the first chamber 125 for the engine - with the first accession 24 (A) for the engine, the second chamber 126 to the engine is appropriately vtool 128 cameras made, located stationary in the housing, saddle 129 communicating with the main valve cone 131, which is located remote from the magnet 14 the end of the main control link 121. At a distance from him master control link 121 has a first segment 132 of the plunger with grooves 133 for precision control, control the connection between the intermediate chamber 127 and the second chamber 126 to the engine, which is sealed in the main control link 121 ring 134 of circular cross section. On the second segment 135 of the plunger in the zone of the first chamber 125 engine is a second control edge 136 with the bordering grooves 137 for precision control, the control connection from the inlet chamber 124 to the first chamber 125 for the engine. The third control edge 138 on the second segment 135 of the plunger serves to discharge the first chamber 125 for the engine, and the discharge occurs through the notch 139 in the drain chamber 128. Pre-control link 122 that is part of a blind hole 141 of the main control link 121, managed by edges 142 of the valve connection from the inlet chamber 124 to the mechanical pressure chamber 143, which includes facing the magnet 14, the end of the main control link 121. Deaf is rsen 145. Located in the discharge chamber 128 main spring 146 presses the main control link 121 to its original position 17, and the main valve cone 131 based on still located in the housing seat 129. On the side of the magnet 14 in the extended interval Zolotnik bore 123 still set the ring box 147, which supports the spring 148, pre-clamping control link 122 to the armature 59 of the magnet 14.

The principle of operation of the electromagnetic valve 120, in General, similar to the operating principle of the electromagnetic valve 12 of Fig. 2. When unexcited the magnet 14 is achieved is shown in Fig. 1, the electromagnetic valve 12 of the connection switching, and the second connection 25 for the engine tightly locked the main valve cone 131, which is the saddle valve function 26. For sealing the second joining 25 for the engine in the direction of the first chamber 125 engine is ring 134 of circular cross section, which may be made in the form of sliding rings or piston rings. Here as seals are also possible long narrow slit. When applying current to the magnet 14 of the electromagnetic valve 120 is deflected into the working position 18, and pre-control link 122 is made with pressure compensation, so the anchor 59 has to overcome only the force of the spring 147. Through edge 142 of the spool pre-control link 122 may increase the pressure in the pressure chamber 143, so that prevails acting on the main control link 121 opening force, resulting in that link 121 against the force of the main spring 146 is pressed to the left in its operating position. The main valve cone 131 is lifted from its seat 129, and opening grooves 133 for precision control to regulate the volume flow flowing from the second chamber 126 to the engine through the intermediate chamber 127 to a drain 22. Of course, this control flow is proportional to the magnitude of the signal current is proportional to the magnet 14. Simultaneously with the opening movement of the third control edge 138 locks the connection from the first chamber 125 to the engine through the notch 139 to a drain 22, whereas the second control edge 136 at the same time opens a connection to the inlet 19. Using grooves 137 for precision control you can adjust the volume of the stream flowing from the inlet chamber 124 to the first chamber 125 for the engine. The pressure in the pressure chamber 143, the value of which vyzyvaemye flowing through the orifice 144 to a drain 22. The damping piston 145 provides a uniform and damped movement of the main control link 121.

Solenoid valve 120 in Fig. 10 may be similar to that of the electromagnetic valve 12 of Fig. 2 are accommodated in the housing 50 together with other functional elements, so achieved the same effect and the same advantages as the control device of Fig. 6

Needless to say, is depicted in the form of possible changes, not distracting from the basic idea of the invention.

1. Electrohydraulic control device for a user double-acting, in which two joining for the consumer blocked each shut-off valve with hydraulic control, of which each shutoff valve installed in the working channel passing between accession to the consumer and electromagnetic control means, and in which at least one connection for the customer with the ability to block or connection control means alternately with the inlet or discharge and connection to the supply occurs through the spool valve element control means, which in the initial position unload veddah same proportionally operating solenoid valves (12, 13, 120) 4-linear 2-point distribution from which each solenoid valve (12, 13, 120) contains the first connection (24) for the engine associated with leading to shut-off valve (29, 38) working channel (27) and controlled by a spool valve element (67, 71), with each solenoid valve (12, 13, 120) includes a second connection (25) for motor-driven truck valve element (26) and connected through the drain channel (35, 41) with the corresponding electromagnetic valve (13, 12) attach (36, 28) for the consumer, and the drain channel (35, 41) bypasses the isolation valves (29, 38).

2. The device under item 1, characterized in that in the initial position (17) of each solenoid valve (12, 13; 120) a second connection (25) for the engine blocked saddle valve (26), while the element (67, 71) spool valve blocks the inlet (19), while in the working position (18) supply (19) is connected with the first connection (24) for the engine, and the second connection (25) for the engine with the sink (22).

3. The device under item 1 or 2, characterized in that the solenoid valve (12, 13; 120) is made in the form of pre-u is driven by the proportional magnet (14, 15) pre-control element (58) communicating with the master control link (57) type of servo control, main control element (57) is blocking a second connection (25) for the engine, the corresponding saddle valve element of the main valve cone (59), which is in connection to a drain (22) sequentially enabled with edge (65) for precision control on the main control element (57), provided spatially separated from her control edges (67, 71) for controlling the first connection (24) for the engine.

4. The device according to p. 3, characterized in that the main control element (57) thickened end, a main valve cone (59), limits on the adjacent end face to the main control element (57) pressure chamber (61), the pressure in which loads the main control element (57) in the closing direction and which is arranged to discharge from the pre-control link (58) to a drain (22), pre-control element (58) has a flange (72) spool and located in series with it pre-control cone (73) and loaded by a spring (16) against the variance of the proportional magnet (14) the account of the differential surface (63), loaded by pressure in the second accession (25) for the engine in the direction of opening.

5. The device according to p. 4, characterized in that the main control element (57) has a second, loading it in the direction of opening the differential surface (69), loaded by the pressure in supply (19), with mechanical pressure chamber (61) is made with the possibility of loading through check valves (75, 76) and the supply choke (79) selectively higher pressure in the second accession (25) for the engine or in supply (19).

6. The device according to PP. 3 to 5, characterized in that the main control element (57) solenoid valve (12) is located in the higher bore (51), which made the appropriate connections (19, 22, 24, 25) cameras, of which the drain chamber (54) is located between the first and second chambers (53, 56) for the engine, and the inlet chamber (52) between the first chamber (53) for the engine and the magnet (14), while the second chamber (56) for the engine is turned on from the magnet (14) side, with, in particular, between the second chamber (56) for the engine and drain the chamber (54) is located intermediate chamber (55).

7. The device according to p. 3, characterized in that the main governing star, adode (124), and located at one end of the main valve cone (131) manages the connection to located in higher bore (123) on the outside and facing away from the magnet (14) drain chamber (128), in which the spring (146) load master control link (121) in the direction of the original position and presses the main valve cone (131) it is located stationary on the housing seat (129), while the opposite and lying near the magnet (14) end of the main control link (121) limits the pressure chamber (143), the pressure at which the load master control link (121) against the force of the spring (146) in the direction of the operating position (18) and pressure chamber (143) is configured to link previously managing link (122) with an inlet (19) and is connected through a throttle hole (144) with the first drain (22), and pre-control element (122) is kept pressed against the anchor (59) is proportional magnet (14) spring (147), resting motionless on the body.

8. The device according to p. 7, characterized in that the orifice (144) executed in the main control link (121), which is included in the drain chamber (128) damping piston (145) with the drain orifice is mounted for sliding.

) installed in higher bore (123), which made the appropriate connections camera: of which the first and second cameras (125, 126) for the engine are located near and between the first chamber (125) for the engine and the magnet (14) is the inlet chamber (124), while the drain chamber (128) is pointing away from the magnet (14) side of the outside of the second camera (126) for the engine, in this case, in particular, between the second camera (126) for the engine and drain the camera (128) is located intermediate chamber (127).

10. The device according to PP.1 to 9, characterized in that both shut-off valve (29, 38) are located in the circuit (34, 39, 82) control lines, in which the pressure in the inlet of one shut-off valve (29, 38) from the supply, which serves for locking the other shut-off valve (38, 29) is sent over the control connection (33) on the other shut-off valve (38, 29) at its spring-loaded rear side.

11. The device according to p. 10, characterized in that serving to lock the pressure is directed through the shut-off valves (29, 38), for which the shut-off valve (83) contains at least one orifice (85), in particular a throttle check valve (84, 85), and the control connection (33) both shut-off valve (82) are connected.

12. The device according to claim what opportunity slip by finger-continued (92) of the locking plunger (93) and by means of a spring (94) based on the last moreover, the outer diameter of the locking plunger (93) and shutter (91) basically the same, between the inlet (31) from the supply and control connection (33) through check valve (90) is a groove (99), in which there is at least one orifice (85), in particular a throttle check valve (84, 85).

13. The device according to PP.1 - 12, characterized in that between the first connection (24) for the engine of both magnets (12, 13) includes a changeover valve (42), which in spring centered middle position relieves the average accession, the corresponding line pressure load, and when the loading pressure of one of the accessions (44, 45) for supplying a pressure directs the pressure in the line pressure loads.

14. The device according to PP.1 - 13, characterized in that both solenoid valves (12, 13) mounted in the housing (50) having essentially the shape of a rectangular parallelepiped, so that their longitudinal axes parallel to each other, and their proportional magnets (14, 15) located on one end surface (106).

15. The device according to p. 14, characterized in that opposite their respective magnets (14, 15) end surface (106) of the housing (50) has montanio (36, 28) for the consumer, lying, in particular, both on the same upper side (109).

16. The device under item 14 or 15, characterized in that the housing (50) in the area between the two solenoid valves (12, 13) have both shut-off valve (29, 38) and a changeover valve (42).

17. The device according to PP. 14 to 16, characterized in that the respective main control links (57) both solenoid valves (12, 13) positioned stationary in the housing seat (60) and the corresponding shut-off valves (29, 38) saddles are useparallelgc the bores (51, 96), open to the mounting surface (107).

18. The device according to PP.14 to 17, characterized in that the longitudinal axis of the solenoid valves (12, 13) lie in the housing (50) in two parallel longitudinal axes, passing at a distance from each other.

19. The device under item 18, characterized in that the installed useparallelgc each other shut-off valves (29, 38) lie in different transverse planes passing at a distance from each other, thus, in particular, the distance between the corresponding longitudinal planes larger than the distance between the solenoid valves (12, 13).

20. The device according to PP.15 to 19, characterized in that the housing is it pumping channel (111).

 

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