KR100684819B1 - Device for controlling timely changeable connection of two connecting members which can be operated by pressure medium with a pressure medium source - Google Patents

Abstract

A control device for controlling a variable changeable connection of two connecting members operated by a compression medium having a pressure medium source,

The main control valve 21 which connects between the compressed medium source and the actuating connecting member has a simple structure, thereby obtaining a high degree of accuracy, and the main control valve 21 has an inlet 22 connected to the compressed medium source. , Having two outlets 23, 24 configured on the operative connecting member, which outlets are controlled by the main control slider 26 moving through two servomechanisms 60, 61 operating opposite to each other, At least one of the two servomechanisms is bounded by a compression chamber 62 disposed in the housing 25, which is guided through at least one pilot control valve 43 actuated in accordance with the supplied control signal. It is operated by the compression medium adjacent to the inlet 22 through the flow path 67 formed in the housing 25, and the load is reduced, and the compression chamber 62 is bounded and held by the main control slider 26.把持), The effective piston surface area of the moving piston is less than a given total surface area of the main control slider 26.

Compression media, connecting members, control valves, servomechanisms, valve sliders, compression chambers.

Description

DEVICE FOR CONTROLLING TIMELY CHANGEABLE CONNECTION OF TWO CONNECTING MEMBERS WHICH CAN BE OPERATED BY PRESSURE MEDIUM WITH A PRESSURE MEDIUM SOURCE}

1 is a schematic diagram of a two-stroke large diesel engine with a control device according to the invention for controlling the actuators of an injection pump and a discharge valve.

FIG. 2 is an enlarged view of the control device according to FIG. 1.

FIG. 3 is an illustration of a variant of FIG. 1 with a fuel injection device operated through a common rail without a pump. FIG.

The present invention relates to a control device for controlling the changeable connection between two connecting members operated by a compression medium having a compression medium source, in particular a hydraulically operated injector and a hydraulic discharge valve of a cylinder of a two-stroke large diesel engine. A changeable connection control device.

In a practical two-stroke large diesel engine, two control valves are attached to the injector and the discharge valve. However, the installation of such a valve with two separate control valves has been found to be costly.

Unpublished German Patent Application No. 103 11 493.9 discloses a device having a main control valve composed of the above-mentioned slider valve, through which the actuating device of the injection valve and the actuating device of the discharge valve are provided. ) Can be connected.

The housing of the main control valve has an inlet connected to a central compression medium source and an outlet formed in so-called actuators which are both circumferentially connected to the inlet via movement of the main control slider arranged to be moved into the housing. do. The entrance is blocked at the central position of the main control slider. An actuator attached to the main control slider blocks the piston supported in the valve housing at both end regions of the main control slider and through the flow path disposed on the main control slider to the compressed medium at the inlet of the housing of the main control valve. It is provided with the pressure chamber accommodated in the end area | region of the main control slider actuated by it. At the same time the supply of the compressed medium added to the at least one pressure chamber is controlled by a servovalve slider arranged to be moved to the main control slider, the servovalve slider being mechanically connected and in accordance with the supplied motor signal, the pilot ( pilot) Actuates a mobile device operated by a control valve. Servo valve sliders with actuators prepared here require a relatively large installation cost and footprint. In addition, a relatively large integrated inertia formed by the inertia of the servovalve slider and the main control slider occurs. Similarly, in unpublished German patent application 103 25 067.0 a similar arrangement is proposed in which the servovalve slider accommodated in the main control slider is hydraulically actuated. However, this cannot overcome the above drawbacks.

In addition, in US Patent US-A 5 237 968, three hydraulic coupling members in the form of injection valves, and inlet and outlet valve actuators are similarly controlled over time by a slider valve having one movable control slider. A four-stroke engine has been disclosed. Here, since the arrangement of this method requires a relatively large flow cross section, the control slider has one relatively large diameter. By this known arrangement the end control slider is operated together with the pressure spring. The other end of the control slider closes the pressure chamber operated by the compressed medium in the atmosphere at the inlet of the compressed medium of the slider valve, the operation of which is controlled by a pilot control valve including a piezoelectric element. The pressure chamber bordering the control slider has a relatively large cross section identical to the control slider. Therefore, a relatively large liquid volume is required to realize the length variation of the control slider. On this, a relatively large amount of time is required depending on the experiment, which leads to poor dynamic characteristics of known control valves. The use of high pressure can cause errors in the position of the control slider, and thus the arrangements known to date have been inefficient and insufficient.

An object of the present invention is to provide an apparatus of the above-described method, which is implemented without a servo device and at the same time guarantees dynamic characteristics and a high level of accuracy. The object of the invention is achieved through the combination of the features according to claim 1.

Accordingly, the present invention provides a time-varying change of a control device for controlling a variable changeable connection of two connecting members operated by a compression medium having a compression medium source, in particular a hydraulically operated injector and a hydraulic stroke of a two-stroke large engine cylinder. And a main control valve configured as a slider valve for connecting between the compressed medium source and the actuating connecting member, the housing containing the movable main control slider in a housing connected to the compressed medium source. It has an inlet and two outlets which are connectable to the inlet by means of a main control slider moving through the attached actuator, which are also selectively separated and constituted in a load reducing actuation connecting member. Here, the actuator attached to the main control slider has two servo mechanisms which are configured at opposite ends of the main control slider to oppose each other, at least one of which depends on at least one supplied control signal. Mains delimited by a pressure chamber and a compression chamber arranged in a housing which is guided by a pilot control valve constructed in the housing and guided by an inlet at the inlet through a flow path installed in the housing and under load. It has a moving piston grasping the control slider, the effective piston surface area of which is smaller than the total adjacent surface area of the main control slider. Since the pressure chambers of the servo mechanisms facing each other are configured on the housing side, inflow and outflow of the compression medium are preferably controlled by a pilot control valve. The servo control slider disposed on the main control slider is not necessary in this case. Therefore, the effective piston surface area of the moving pistons of both servo mechanisms becomes relatively small, and a relatively small hydraulic fluid is required to obtain the state change of the main control slider preferably. Therefore, a very short reaction time is preferably generated. In this way, in the main control valve according to the present invention, not only the closing operation is performed but also a given progression of the closing process is obtained. That is, a predetermined injection embodiment is obtained.

Developments consistent with the preferred embodiments and objects of the means according to the invention are described in the dependent claims.

The sensor device is preferably configured at an axial position of the main control slider, and the pilot control valve is actuated via the exit signal of the device. This preferably enables the construction of a closed automatic control system. Thus, in the attainable state of the main control slider, high accuracy is possible, and more precisely, it has particularly good dynamic characteristics when a relatively high pressure of the liquid of the hydraulic device is supplied. Here, with the help of the proposed feedback, the servo mechanisms facing each other can average the moving force applied to the main control slider at each position of the movement path of the main control slider. Therefore, a preferred injection embodiment is thereby realized.

The sensor device is equipped with a measuring device for scanning the position of the main control slider without contact to suit the purpose. For this reason, the source of error, such as a frictional force which reacts with the movement of a main control slider, can be prevented preferably.

Preferred means according to the present invention comprise a servomechanism actuated by a pilot control valve, equally arranged in the housing, bounded by a moving piston configured on the main control slider, with a pressure chamber operated at a constant pressure. Accordingly, the configuration of the arrangement according to the present invention can be simplified. At the same time, the moving piston bounded by the pressure chamber operated at the moving pressure can be operated directly with the main control slider, preferably via an additional pressure spring, to shorten the operating time and prevent resonance.

Further preferred embodiments and the effective development of said means are described in the other dependent claims, which in the following examples illustrate the invention in detail.

The main use area of the present invention is, for example, a two-stroke diesel engine, particularly a two-stroke large diesel engine, used as a ship drive device. Therefore, a relatively smoothly running engine with good piston motion, high injection volume, long injection time and outlet opening time for this motion is important. Great force is required to operate the injector and discharge valve.

Two-stroke large diesel engines of this type generally comprise a plurality of cylinders arranged in series and in series, and only one cylinder 1 is shown for the purpose of illustrating the illustration of FIG. 1. In the cylinder 1, the piston 2 connected to the crosshead 4 which is operated together with the crankshaft 6 via the connecting rod 5 is arranged to be movable. The piston 2 is at least one embodiment bounded by a combustion chamber 7 in which two injection nozzles 8 arranged in the region of the cylinder head are operated by fuel. In the lower region of the cylinder liner there is an air inlet 9 connected to an air supply, which is controlled by a piston 2, through which the combustion chamber 7 is operated by air.

The exhaust gas generated by the combustion reaches the discharge pipe 11 discharged through the central discharge port 10 configured in the region of the cylinder head. The discharge valve 12 is vertically operated by the actuator 13 which opens and closes the discharge port 10 which is configured and installed as a hydraulic device connecting member at the central discharge port 10. In the present embodiment, the injection nozzle 8 is provided with an injection pump 14, and the pump chamber 15 of the injection pump is operated by the fuel prepared through the supply device as indicated by the arrow 16. Fuel is injected from the pump chamber 15 by an actuator 17 with a so-called plunger, which likewise is configured as a hydraulic coupling member, the piston of which is connected with the plunger.

The actuator 13 of the discharge valve 12 and the actuator 17 of the injection pump 14 are actuated by hydraulic pressure with the compressed medium supplied by the compressed medium source 18 through operation. This operation takes place in accordance with the angular position and rotational speed of the crankshaft 6, the load, the pressure and the like as well as the engine signal. The compression medium source 18 in this embodiment consists of a pressure chamber which is operated by a hydraulic system and supported by a predetermined pressure via a pump 19 which drives directly or indirectly on the crankshaft 6.

In the present embodiment, the pressure chamber constituting the compression medium source 18 is formed of a common rail and branches to conduits 20 which supply a plurality of installed consumers, and the conduits 20 are each provided by valves installed. It is controlled on and off. In deployments with multiple cylinders, one common rail is installed that passes through all or at least one cylinder group.

A common main control valve 21 is installed in the actuator to control the pressure operation of the actuator of the hydraulic system connecting member constituting the discharge valve 12 and the actuator of the hydraulic system connecting member constituting the injection pump 14. do. The common main control valve 21 is configured as a moving valve, in which one hole formed in the main control slider 26 is formed in the housing 25 of the moving valve, by means of a compressed medium source having the shape of a common rail. The inlet 22 formed, the outlets 23 and 24 formed in the actuators 13 and 17, and at least one further outlet 40, here a pressureless backflow tube back to the compression medium tank not shown in detail. It constitutes two further outlets 40 which can be connected. So-called inlets and outlets are formed in the main control slider 26. It is in communication with an elongated groove moving up and down through the adjustment edge of the main control slider 26 supplied to the area of the housing hole. In order to obtain a large flow cross section in which a large amount of supply can be obtained, the main control slider 26 has a relatively large diameter.

The main control slider 26 has one zero position in the center and is moved from side to side in the axial direction starting from here. According to the figure, the inlet 22 is separated into outlets 23 and 24 at the central zero position of the main control slider 26, which are each connected to one outlet 40. On the other hand, the main control slider 26 is constituted with a root face which covers the inlet 22 or a circular groove communicating with the inlet as shown in FIG. The main control slider 26 is deflected from side to side in the illustrated intermediate position of the main control slider 26 so as to be connected to the inlet 22 or a circular groove communicating with the inlet, respectively. At the same time, the connection of the pressureless outlet 40 is dropped. On the other hand, the main control slider 26 is formed with a circular groove 42 which surrounds both sides of the root surface 41 wide in the axial direction, and the main control slider has a root surface ( It is possible to achieve a predetermined connection between the inlet 22 and one of the outlets 23 or 24 upon axial movement of the main control slider 26 which is larger than the lateral protrusion of 41. Therefore, the open horn cross section depends on the position of the main control slider 26, and this flow cross section greatly expands in the right or left end position. Suitable grooves are configured to prevent accidental operation of the so-called flow paths.

The main control slider 26 is moved axially by an attached actuator, ie an actuator. As can be seen in Fig. 2, the movement separates the servo mechanisms 60, 61 attached to the end portions opposed to each other in the axial direction of the main control slider 26, and the servo mechanisms 60, 61 are respectively main. A pressure chamber 62 actuated by a compression medium adjacent to the inlet 22, starting from the opening of the valve housing 25 containing the control slider 26 and forming a sack hole on the housing side; The pressure chamber 62 borders the main control slider 26 via a moving piston 63 or 64 which is directly or indirectly attached side by side to the adjacent front of the main control slider 26.

In an embodiment of the invention, the lower pressure chamber 62 of both pressure chambers 62 is operated at a constant pressure, where the pressure chamber 62 is via an opening system 65 configured in the valve housing 25. It is connected to the inlet (22). No backflow connection is necessary here. The moving piston 64 is supported by the main control slider 26 via a pressure spring which is generally dish-shaped. However, like the moving piston 63 positioned oppositely, the moving piston 64 is effectively gripped directly by the main control slider 26. The moving pistons 63 and 64 are preferably fixedly connected to the main control slider 26. This ensures that the body contact is always supported on the surface of the device of the associated parts facing each other.

Here, the pressure chamber 62 located at the top in Fig. 2, that is, the pressure chambers 62 facing each other, is operated at a control pressure. On the other hand, preferably, a pilot control valve 43 attached to the valve housing 25 and operated by a control signal is configured, and the pilot control valve 43 opens a flow path 65 formed in the valve housing 25. It is connected to the pressure chamber 62, the inlet 22, and the outlet 40 through which pressure does not work.

The effective piston surface area of the moving piston 62 is actually smaller than the respective total formed surface area of the main control slider 26, equal to the effective piston surface area of the moving piston 64. On the other hand, the effective piston surface operated at the control pressure is preferably twice as large as the moving piston 64 operated at the opposite constant pressure. Therefore, in the case of operating the large moving piston 63 at a pressure adjacent to the inlet 22, the force generated here, that is, the force generated by the small moving piston 64 operated at the same pressure, can be overcome. In the example, the main control slider 26 is moved downward while facing this less force. In the case of reducing the load on the upper pressure chamber 62, ie the moving piston 63, the main control slider 26 is moved upwards through the opposite moving piston 64 which is operated at a constant pressure.

The main control slider 26, which is operated through the opposite directions of the two servo mechanisms 60, 61, is moved when the moving force acting on the slider is not the same, and is supported at the corresponding position. Therefore, the main control sliders 26 are supported at predetermined positions, respectively, in accordance with the corresponding balance of the moving force applied thereto. In this way, it is possible to carry out each predetermined process of operating the actuators 13 and 17 arranged later. For example, a small amount may be initially sprayed to start the spraying process, the amount may be increased in the course of the dispersion process, and may be terminated at one time. Similarly, since the reciprocating piston configured in the discharge valve 12 can be stopped with respect to the opening movement end, braking of the end position is unnecessary.

The pilot control valve 43 is effectively configured as a proportional valve that opens and closes the formed flow path in accordance with a control signal input from the inlet 22 to the pressure chamber 62 or from the pressure chamber 62 to the outlet 40. The pilot control valve 43 is configured with a signal generator 29 for receiving a control signal and converting it into a signal suitable for operation of the pilot control valve 43. The signal supplied to the signal generator 29 is generated according to the engine signal supplied from the signal generator. The electronic calculator 68 is configured as a signal generator, which is processed by the signal generator 29 according to the engine signal supplied through the input arrow 69 by a program, and the main control slider 26. Calculates a signal corresponding to a predetermined moment of time. The outlet of the electronic calculator 68 is connected to the inlet of the signal generator 29 by the signal line 70.

In this embodiment, feedback is provided with the actual situation of the main control slider 26 to increase accuracy. In contrast, the main control slider 26 is configured with a sensor device 71 for capturing the axial position. The outlet of the sensor device 71 is located in correspondence with the actual value at the inlet of the electronic calculator 68. The signal that forms the standard value calculated from the difference between the actual value and the electronic calculator 68 is supplied to a signal generator that generates an adjustment signal of the pilot control valve 43. In this way, a high degree of accuracy is achieved by actually closing the automatic adjustment system. This allows the use of high pressures in which the effective surface area of the moving pistons 63, 64 can be particularly small.

A sensor device 71 having a measuring device acting as a contactless device is configured to prevent the movement resistance applied from the sensor device 71 to the main control slider 26. This is constituted as an inductive measuring device in the present embodiment, which has a fixed pin 73 and a main control slider erected as anchors firmly fixed by the axial radial operation of the main control slider 26. And a coil disposed at 26 to surround the opening 72. The opening 72 is open at the end opposite the fixing pin 73 for the purpose.

In the present embodiment, the opening 72 is arranged to be coaxial with the axis of the main control slider 26, and the servo mechanism 61 on the side of the sensor device corresponds to the device of the main control slider 26. It is arranged eccentrically with respect to the axis. The opposing servo mechanism 60 is disposed coaxially with the axis of the main control slider 26 with respect to it, and correspondingly with the axis of the opening 72. Therefore, since the servo mechanism is formed as a bag-shaped opening and branches in the inclined conduit, collision with the moving piston 63 is prevented. It is also preferably firmly connected to the main control slider 26. Likewise, the opposing moving piston 64 is fixed to the main control slider 26, so that continuous contact can be ensured. However, an elastic support of the moving piston 64 can also be considered. The moving pistons 63 and 64 may be composed of one part, or preferably of several parts as in this embodiment.

In the embodiment according to FIG. 1, an injection pump 14 is attached to the injection valve 8, and the actuator 17 of the injection pump next to the actuator 13 of the discharge valve 12 is connected to the control device of the present invention. Can be controlled. However, the control device according to the present invention can be used without the injection pump according to the arrangement, this embodiment is as shown in FIG.

At the same time, a common rail 18 'actuated by the fuel compressed in advance is provided, and the flow path 20' branched from the common rail to the cylinder 1 is selectively sprayed by the control device of the present invention, respectively. It is connected with the actuator 13 of the valve 8 or the discharge valve 12. The configuration of the pilot control valve of the main control valve 21 and the control apparatus of the present invention added thereto is consistent with the above-described embodiment, and the difference from the above-described embodiment is previously described by the compression medium according to the embodiment of FIG. Compressed fuel is used. Therefore, the common rail 18 'installed in the compressed medium source is operated by fuel through the installed pump 19'. The hydraulic device connecting member which constitutes the actuator 13 of the discharge valve 12 is operated by fuel as a source of compression medium.

 The control device according to the present invention can be implemented without a servo device, and the dynamic characteristics and high level of precision can be guaranteed. In addition, by simplifying the arrangement arranged according to the present invention, the moving piston bounded by the pressure chamber actuated by the moving pressure can be operated together with the main control slider by an additional pressure spring to simplify the operating time and prevent resonance. In addition, the control device of the present invention can be applied to a two-stroke large diesel engine.

Claims (12)

Two connecting members actuated by a pressurized medium having a pressure medium source, the hydraulically actuated injector 8 of the cylinder 1 of a two-stroke large diesel engine and a hydraulically actuated outlet valve ( 12) A control device for controlling a changeable connection over time, A main control valve 21 connected between the compression medium source and the connecting member and configured as a moving valve; One housing for receiving a movable main control slider 26; One inlet 22 connected to the compressed medium source, Two outlets 23 and 24 formed in the connecting member; Equipped with The two outlets are separated from the inlet 22 by the main control slider 26 moving through the attached actuator to reduce the load, and are also optionally connected to the inlet 22, The actuating device attached to the main control slider 26 has servo mechanisms 60 and 61 configured at both ends of the main control slider 26 and operated in reverse with each other. At least one of the servo mechanisms includes a moving piston 63 gripping a main control slider 26 bounded by a pressure chamber 62 disposed in the housing 25, The pressure chamber 62 is guided by at least one pilot pilot valve 43 actuated in accordance with a control signal supplied to a compression medium adjacent to the mouth 22 via a flow path 67 configured in the housing 25. Are operated, and the load is reduced, The effective piston surface area of the moving piston 63 is less than the given total surface area of the main control slider 26. Control device, characterized in that. The method of claim 1, Sensor device (71) is installed in the axial position of the main control slider, the control device characterized in that the pilot control valve (43) is operated by the exit signal of the sensor device. The method of claim 2 The control device, characterized in that the pilot control valve (43) is actuated when there is a deviation between the predetermined standard value and the actual value of the exit signal of the sensor device (71). The method of claim 2, The sensor device (71) is characterized in that it comprises an inductive measuring device for scanning the position of the main control slider (26) without contact. The method of claim 1, The servo mechanism 61 facing the servo mechanism 60 operated by the pilot control valve 43 is disposed in the housing 25, And a pressure chamber (62) operating at a constant pressure, bounded by a moving piston (64) held by the main control slider (26). The method of claim 5, Control chamber, characterized in that the pressure chamber (62) operated at a constant pressure is connected to the inlet (22) through a flow path (65) configured in the housing (25). The method of claim 5, And the moving piston (63, 64) is fixed to the main control slider (26). The method of claim 1, The moving piston 63 of the servo mechanism 60 operated by the pilot control valve 43 has the same effective piston surface area as the moving piston 64 facing the servo mechanism 61 operated at a constant pressure. Control device, characterized in that. The method of claim 1, The pilot control valve 43 is a control device, characterized in that consisting of a proportional valve for opening and closing the flow path in accordance with the supplied control signal. The method of claim 1, The moving force applied to the main control slider 26 by the servo mechanisms 60 and 61 facing each other is adjusted at each position of the main control slider 26 between the two ends by the pilot control valve 43. Control device, characterized in that. The method according to any one of claims 1 to 10, A two-stroke diesel engine having the discharge valve 12 and at least one main control valve 21 configured in the actuators 13, 17 of the injection pump 14, the main control valve in a two-stroke large diesel engine. Control medium, characterized in that the compressed medium source (18) connected with the inlet (22) of the (21) is configured identically to a common rail operated by hydraulic oil. The method according to any one of claims 1 to 10, In a two-stroke diesel engine without an injection pump, the compressed medium source 18 connected to the inlet 22 of the main control valve 21 in a two-stroke large diesel engine is configured identically to a common rail operated by fuel, Arrangement of the injection valve by the main control valve (21) and the control device characterized in that it is possible to control the time-varying operation of the actuator (13) operated by the fuel supplied to the discharge valve (12).

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