EP3067309B1 - Control valve for a hydraulic unit and hydraulic system with a corresponding control valve - Google Patents

Description

The present invention relates to a control valve for a hydraulic unit and a hydraulic system with a corresponding control valve. In particular, the present invention relates to a control valve for a hydraulic consumer operated by a hydraulic motor, e.g. a winch with a mooring function, a winch system with a mooring function, such as for a ship or a piste grooming vehicle, or a crane or excavator, or a linear drive, such as a boat; a hydraulic cylinder.

Winches generally have an operating mode in which a frequently hydraulically driven winch winds or unwraps a rope or rope or chain, etc., by rotating a winding drum. In another mode of operation, the rope or rope or chain, etc. is held in a stopped state by the winding drum, such as by a brake device mounted on the winding drum. Alternatively, the rope is held by an additional gripping device holding the rope.

In many applications, in addition to the above-mentioned take-up and unwind modes of operation, another mode of operation is provided to avoid overstressing the rope or slacking the rope, such as is desirable in rope winches on cargo cranes or ships or in traction winches. In the latter case, for example, winches are used as traction winches on piste maintenance vehicles in order to support the driving while working on steep ski slopes. Here, the rope is anchored by a rope winch mounted on the slope maintenance vehicle uphill to a terrain-fixed point. An uphill run of the piste grooming vehicle can then be supported by a winding operation of the winch, whereas the winch can be used when driving along a downhill slope to support the braking effect. It may happen due to unevenness in the terrain that the rope is temporarily not sufficiently stretched or is excessively tensioned, which has an impact on the safety of the driver of the piste grooming vehicle and also the life of the rope is unduly stressed. A similar problem occurs when using winches in mooring winches of ships and in load winches of cranes and in excavators.

In general, when winding and unwinding by winches, it is desirable to create a constant pulling force on the rope and, if possible, to keep the rope taut and under tension regardless of the pulling force on the rope. In this context, a mooring function is to be understood as a mode of operation of a cable winch in which a rope is kept taut and under tension. In general, a mooring function can be understood as an operating mode in which, despite the load present, a mass flow above a minimum value is provided.

In known applications, separate pressure control valves are often provided to provide the mooring function, or the consumer's supply lines are connected to the drain in a floating position.

In Scripture US 3,965,841 describes a mooring winch system for a ship, wherein two winches are controlled jointly by a control valve, so that each of the winches can perform a winding or unwinding operation or output operation. In addition to the normal winch drive can be achieved by means of two additional separate 4/3-way valves both a bias of the rope on each winch, as well as manipulations under bias of the rope.

From the Scriptures WO 2011/156829 A1 a winch for a vehicle crane is known in which a rope stress or a slack rope formation when changing the length of a crane jib can be prevented by means of an additional compensation device. Here, a low cable traction is applied by the compensation device on the load rope, so that this is stretched by the winch and the rope is wound at a necessary lower rope length between the winch and a rope fixation point, while the load rope is obtained at the required larger rope length of the winch , These are in addition to a hydraulic motor of the winch controlling main control valve, which is arranged in the form of a 5/3-way valve in front of the hydraulic motor of the winch, in the additional compensation device, an electrically operated 2/2-way valve and a pressure-limiting 2/2-way valve provided so that the compensation device can bridge a provided in a supply line of the hydraulic motor load-holding valve after the main control valve and connects the main control valve downstream supply ports of the hydraulic motor. The pressure set at the pressure limiting 2/2-way valve determines the height of the cable pull force.

A device for automatic control of the tensile force of a rope for a piste care vehicle is from the document EP 1 118 580 B1 known. An adjustment and regulation of the tensile force of a rope of an overhead winch of the snow grooming vehicle takes place here via a connected to a winch drive control unit, which is connected to pressure sensors, by means of a calculated in the control unit and setpoint based on the signals of the pressure sensors, the detect the pressure at a changeover valve of the highest value. The shuttle valve is connected between delivery lines of right-side and left-side drives in a forward direction or a reverse direction.

Further exemplary control valves for such systems are, for example, from the documents US 6,182,697 B1 and DE 42 21 757 A1 known.

Known systems with mooring function, e.g. Winches with mooring function, represent in their dimensions very large-scale devices.

In view of the above situation, it is an object to provide a compact hydraulic system with mooring function.

The foregoing object is achieved in one aspect of the invention by a control valve for a hydraulic unit. In one illustrative embodiment herein, the control valve comprises a first state for continuously dispensing a pressure medium to a hydraulic consumer, in particular a mooring winch operated by a hydraulic motor, or a hydraulic cylinder, wherein a supply port of the control valve to be connected to the hydraulic consumer a supply port is connected to a pressure port, and a second state in which the supply port is connected via a discharge passage of the control valve to a tank port of the control valve. Furthermore, the control valve comprises a third state with a corresponding stroke, along which the supply channel is connected to the discharge channel superimposed, wherein the supply channel and / or the discharge channel has a stroke-dependent cross-sectional area. Advantageously, a compact control valve is thus provided with a state for controlling a mass flow and / or pressure occurring at the supply connection of the control valve, without the need for separate saddle structures.

Here, the control valve comprises a spool, which is designed such that a mass flow at the supply connection along the entire stroke of the third state is greater than zero. This provides a structurally simple solution for a control valve which, for example when applied to a cable winch, effects a constant tension of a cable that is issued or wound up by the cable winch, so that the cable is wound up and / or released during a mooring operation under tension can.

Further, the mass flow at the supply port along a portion of the stroke of the third state is lowered to a constant residual level. As a result, a predetermined pressure can be provided at the supply connection independent of the load, which allows fine adjustment of the cable tension by the cable winch during mooring.

In an illustrative embodiment of the invention, a control device is further provided, which is designed for automatic control of the control valve at least along the stroke on the basis of an external signal, the pressure and / or load on the hydraulic load, in particular in the case of a winch a winch load and or a cable pull force and / or a cable speed and / or a cable length output by the cable winch, so that a pressure output at the supply connection can be regulated to a predetermined value. In this way it is possible to operate the control valve very precisely, in particular finely adjusted, without additional control by an operator of the winch.

In an advantageous embodiment herein, a sensor device is further provided for detecting at least one actual value signal based on the external signal, wherein the control device for automatically determining a deviation of the at least one actual value signal of at least one setpoint signal and for controlling the control valve is, so that the deviation is minimized. In this way, an operation is made possible in which the actual value can be regulated efficiently to a predetermined desired value.

In a more advantageous embodiment herein, the sensor device comprises a pressure sensor and the control device is for determining a deviation of an actual pressure configured on or after the supply connection of a desired pressure. This allows a load-independent regulation of the pressure at the supply connection to a constant level.

In a further illustrative embodiment of the invention, the third state is designed for mass flow and pressure control. For example, by means of the third state, a mass flow and pressure provided to the supply port of the control valve are provided to a desired extent by having an external control signal, for example by a user via an operator interface, such as a joystick or the like, or an internal feedback in the control valve Mass flow and pressure control takes place.

In an advantageous embodiment herein, the third state comprises a first Hubwegabschnitt and a second Hubwegabschnitt having away from a neutral position a greater stroke, as a first Hubwegabschnitt corresponding stroke relative to the neutral position. In this case, the mass flow output at the supply connection can be regulated via the second stroke path section to a constant level greater than zero. This represents an advantageous embodiment of the control valve, wherein a compact structure and in particular a fast control in the third state is made possible.

In a further advantageous embodiment herein, the cross-sectional area of the discharge channel along the second Hubwegabschnitts varies depending on the stroke, in particular, the cross-sectional area of the discharge channel increases with increasing stroke. As a result, the mass flow at the supply connection can be regulated in a simple manner to a predetermined value.

In a further advantageous embodiment herein, the third state begins relative to a neutral position of the control valve after a further stroke corresponding to the second state in a range of 20% to 60% of the total stroke. This provides a very advantageous design of a control valve in which the mooring function is directly downstream of the second condition for continuous winding.

In a further illustrative embodiment of the invention, the hydraulic consumer is a winch with mooring function and the first state is for continuous unwinding or dispensing of a rope by the winch and the second state is formed to a continuous winding of the rope by the winch. As a result, winches are provided with Mooringfunktion that require no additional Aufsattelstruktur and allow a tensile force control of the rope in a simple way in 2-direction operation.

In another illustrative embodiment of the invention, the control valve is a CAN bus valve with electronics. This can be dispensed with an additional external control.

In another illustrative embodiment of the invention, a maximum cross-sectional area of the inlet nozzle is in a range of 20 mm 2 to 24 mm 2. As a result, an advantageous passage amount is provided to the supply connection.

In a further illustrative embodiment of the invention, in the third state between the pressure connection and the supply connection, a maximum mass flow from a range of 90 l / min. up to 110 l / min. up to a constant residual mass flow from a range of 5 l / min. up to 15 l / min. lift-dependent lowering. It is therefore a fast winding and fine adjustment possible, with load independent constant pressure, and thus a constant cable tension can be provided.

In a further aspect of the invention, the above object is achieved by a winch system comprising a winch with mooring function for a ship or a piste grooming vehicle or a crane or excavator, a hydraulic motor for operating the winch and a control valve according to the above-described Aspect of the invention. In these applications, a compact winch with mooring function is provided.

In some illustrative application examples, the mooring function can be used to keep the pressure of a cylinder constant. This is necessary, for example, for holding / regulating the contact pressure in a snow plow. The advantage of the mooring function proposed in various aspects of the invention lies in good flexibility in electronic parameters used to control the mooring function and in lower cost of the hydraulic components to implement the mooring function.

• Fig. 1 : schematische eine Ansicht einer Seilwinde gemäß einiger anschaulicher Ausführungsformen der vorliegenden Erfindung;
• Fig. 2 schematisch einen Schaltplan eines Steuerventils gemäß einiger anschaulicher Ausführungsformen der vorliegenden Erfindung; und
• Fig. 3 : schematisch Ventilkennlinien für ein Steuerventil gemäß einiger anschaulicher Ausführungsformen der Erfindung.

Further advantages will become apparent from the description of some specific illustrative embodiments of the present invention as illustrated in the accompanying figures. Showing:

• Fig. 1 1 is a schematic view of a winch according to some illustrative embodiments of the present invention;
• Fig. 2 schematically a circuit diagram of a control valve according to some illustrative embodiments of the present invention; and
• Fig. 3 FIG. 2 schematically shows valve characteristics for a control valve according to some illustrative embodiments of the invention. FIG.

Regarding Fig. 1 Various illustrative embodiments will be described below. Here, by way of example, a hydraulically operated winch system 1 is shown. The winch system 1 may be provided on a ship or a piste grooming vehicle or a crane or an excavator. The winch system 1 comprises a winch 5 with a drum 46 on which a rope 3 is wound. The drum 46 is operated by a hydraulic motor 47, which is supplied with hydraulic fluid via supply lines 48 by a hydraulic pump (not shown). The cable winch system 1 further comprises a control valve 49, which is arranged in the hydraulic circuit of the hydraulic drive in front of the hydraulic motor 47.

Furthermore, a sensor arrangement is provided in the cable winch system 1, which may comprise at least one of different sensor units 50, 51, 54. For example, a rotation and / or a direction of rotation of the drum 46 may be detected by the sensor unit 50, wherein in one illustrative example, the rotational speed of the drum 46 may be detected by the sensor unit 50. By means of the sensor unit 51, a voltage of the cable 3 can be detected. Furthermore, a speed of the rope, for example during winding or unwinding, can be detected by the detection device 51. Further, power and / or load of the hydraulic motor 47 may be monitored by a sensor unit 54 on the hydraulic motor 47. Here, for example, the hydraulic pressure in the hydraulic motor 47 and / or a speed and / or torque, etc. of the hydraulic motor 47 are detected.

This in Fig. 1 shown winch system 1 may further include a control device having, for example, a logic unit 44. The logic unit 44 is connected to the sensor arrangement, so that the sensor signals output by the sensor units 50, 51 and 54 are supplied to the logic unit 44. For example, the logic unit 44 may include a processor, such as a CPU of a computer system. Thus, the logic unit 44 from the sensor array detected actual value signals from at least one of the sensor units 50, 51, 54, respectively.

In some illustrative embodiments, the logic unit 44 is configured to determine control signals based on the sensed actual value signals supplied to the logic unit 44. The control signals are output from the logic unit 44 to the control valve 49, so that the control valve 49 is controlled by the logic unit 44, wherein an operating mode of the hydraulic motor 47 is adjusted by the control valve 49. In some illustrative examples, a first state of the control valve 49 may cause a winding operation of the winch 5, in particular, the first state may correspond to a winding mode of the winch system 1. A second state of the control valve 49 may cause a discharge or unwinding of the cable 3 from the winch 5, in particular, the second state may correspond to a unwinding mode of the cable winch system 1. For example, in some illustrative embodiments, in the first state of the control valve 49, the hydraulic motor 47 may output high torque at low drum rotation speed, thereby allowing the cable 3 to be wound under load. In addition, in the first state of the control valve 49, the hydraulic motor 47 can provide a low torque at high rotational speed of the drum 46, which corresponds to a high-speed, no-load winding. A more detailed description of the control valve 49 is given below with respect to Fig. 2 ,

Regarding the representation in Fig. 1 It is noted that the connecting lines between the logic unit 44 and the individual sensor units or the control valve 49 are shown very schematically. This is not a limitation of the present invention, as the connections between the logic unit 44 and the individual sensor units 50, 51 and 54, as well as between the logic unit 44 and the

Control valve 49 may be provided, for example, by electrical lines and / or wireless connections.

Optionally, as in Fig. 1 2, a safety switch 53 configured to turn off the hydraulic motor 47 by switching the control valve 49 to a neutral state may be provided. For example, the safety switch 53 can be triggered manually or automatically when the cable tension is exceeded above a predetermined maximum value. The predetermined maximum value may be, for example, a setpoint input via an input device 55 directly in the safety switch or indirectly via the logic unit 44. Additionally or alternatively, set values for the rotational speed of the drum 46 and / or a hydraulic pressure on the hydraulic motor 47 and / or a torque output by the hydraulic motor and / or a speed output from the hydraulic motor 47 may be provided via the input device 55. The safety switch 53 may be a mechanical or electromechanical or electrical or electronic switch. Thereby, for example, exceeding of predetermined maximum values input by a user via the input device 55 can be effectively prevented by the safety switch 53.

According to some illustrative embodiments, the tensile force of the rope 3 in the in Fig. 1 shown winch unit 1 are automatically controlled. For this purpose, at least one actual value signal from at least one of the sensor units 50, 51, 54 is detected and output to the logic unit 44. By comparing the at least one actual value signal with at least one setpoint signal, a deviation of the actual value signal from the setpoint signal is determined by the logic unit 44 and a control signal is output from the logic unit 44 to the control valve 49 to the hydraulic motor 47th fully automatic control. As a result, a minimization of the deviation of the at least one detected actual value from a desired value can be achieved, so that the at least one actual value is kept as constant as possible during operation of the cable winch system 1, in particular in one of the states of the control valve 29. For example, a deviation of the actual value from the nominal value by as much as 10% of the nominal value, for example by less than 5% or by less than 1%, may be as constant as possible. Furthermore, it is possible for a user to specify not only a definition of at least one nominal value but also a tolerance within which deviations of the actual values from corresponding nominal values are tolerable, for example by the input of absolute limit values or relative limit values with regard to specified nominal values. Possible target values may be a pressure on the control valve, a pressure in the engine, a winch load, a cable pull, a rope speed, a length of the discharged or unwound rope, a length of the wound rope, a change in length of the issued and / or wound rope per unit time ( eg per second, per 5 seconds, per 10 seconds, etc.) and the like. Additionally or alternatively, setpoints may also relate to external parameters, such as a vehicle speed (excavator or piste grooming vehicle), swell (ship), weight of a load (crane), and the like.

It is noted that according to the in Fig. 1 an automatic control of operation of the winch 5 can be provided, so that according to the foregoing explanations deviations, for example in the cable force and / or hydraulic pressure in the hydraulic motor 47 and / or in the rotational speed of the drum 46 and / or in a tensile force of the rope 3 are minimized. It is therefore an automatic control of the operation of the winch 5 in the winch system 1 is provided, which takes into account the dynamics of the application, for example as a mooring winch on a ship or on a snow grooming vehicle or on an excavator or on a crane without by a Operator additional manual control inputs, for example via a joystick, are required. Since the automatic control of the operation of the winch 5 within the winch system 1 minimizes deviations from actual value signals with respect to setpoint signals relevant parameters or parameters for the operation of the winch 5, a life of the winch 5, and in particular of the rope 3, compared to known winches is extended. Alternatively, a control of the control valve 49 may be effected by external control signals input by, for example, a user of the illustrated winch system 1 by means of a user interface (not shown). The user interface may be, for example, a joystick, a keyboard, a button, a touch screen, or other suitable device that allows an operator to input control commands to control the control valve 49. In this case, the user interface (not shown) may be directly connected to the control valve or be provided on / in the control valve. Alternatively, the user interface may be directly or indirectly connected to the logic unit 44.

If, during operation of the winch 5 slipping of rope 3 or a slip on a by the winch 5 to be conveyed load (not shown) occurs, so For example, at least one of the sensor units 50, 51 detects a deviation in the cable speed with which the cable 3 is rolled up or output by the drum 46, and / or a change in the speed of the drum 46, which is dependent on a set value for the cable speed of the cable 3 and / or for a rotational speed of the drum 46 deviates. Due to the determined deviation, the logic unit 44 outputs a control signal to the control valve 49 in order to minimize the deviation or readjust the different size. This is advantageous, for example, in the case of very long rope lengths, in which the tensile stress in the rope is subject to very great fluctuations due to the existing rope elasticity of the rope 3. The winch system 1, in this case, as explained above, provide a control of the winch 5, which is independent of the cable pulling force applied to the cable 3.

According to an example of an illustrative application in which the winch wind system 1 is provided, for example, on a piste grooming vehicle as a traction winch unit to assist driving movements of the snow grooming vehicle on a ski slope, a rope speed of the rope 3 can be detected by the sensor unit 51 and as an actual value signal to the logic unit 44 are issued. In the logic unit 44, a comparison of the actual value signal of the rope speed with a setpoint signal, for example given by the instantaneous speed of the vehicle on a slope or a setpoint input via the input device 55, can be compared.

For example, in a downhill direction of the slope grooming vehicle and a pulling direction against the direction of travel, a supporting braking action by the cable wind system 1 can be achieved by setting the speed of the drum 46, and consequently the rope speed of the cable 3, by means of the hydraulic motor 47 in that the cable speed 3 detected by the sensor unit 51 is smaller than the instantaneous speed of the piste grooming vehicle on a slope. For example, an allowable maximum speed given on the slope for the piste care vehicle can be predetermined here. By controlling the cable winch 5 in such a way that a certain cable speed 3 is present, which is smaller than the speed of the snow grooming vehicle, an assisting braking effect is achieved. It is noted that the amount of braking action may be further adjusted via a predetermined deviation of the cable speed from the instantaneous speed; for example, in some illustrative examples, it may be desirable herein a predetermined deviation of the rope speed from the instantaneous speed of the piste grooming vehicle is maintained.

In another example, in which the piste grooming vehicle travels up the slope and the pulling direction of the rope 3 in the direction of travel of the piste grooming vehicle, by means of the cable winch unit 1 a cable speed can be set which is greater than or equal to the speed of the piste grooming vehicle. As a result, a tensile force can be maintained in the rope, which supports the travel drive more or less depending on the size.

In the examples described above, the cable winch system 1 basically provides a cable 3 held taut and under tension in all driving situations. However, this is not a limitation on piste grooming vehicle, but can also be done for ships, excavators and cranes in respective operating modes. It is noted that a control as described with reference to the preceding examples is independent of the cable pull force present on the cable 3.

It is noted that a rope speed of the rope 3 in some illustrative embodiments may e.g. can be done by detecting the rotational speed of a pulley (not shown) with a constant diameter or by detecting the speed of the cable drum based on the sensor unit 50, in the latter case, if necessary, the changing drum diameter is taken into account by wound cable layers.

In some illustrative examples, a method for winch control of the winch 5 within the winch system 1 in the illustrative application of a ship or an excavator or a crane or a piste grooming vehicle, detecting a value as an actual value, the speed of a load to be conveyed by the winch 5 (not illustrated), such as the ship or the piste grooming vehicle or a load to be conveyed by the crane or excavator, detecting a rope speed or a magnitude proportional to the rope speed as an actual value, comparing the detected actual value and determining a control signal for the control valve 49 Basis of a deviation of the actual value of a predetermined desired value, eg a speed of the vehicle or the like, include, wherein minimizing the deviation in the further operation of Winch 5 or a constant holding a deviation at a desired level in the further operation of the winch 5 is achieved.

Although in terms of Fig. 1 illustrative applications with a winch described above, it is noted that alternatively instead of the winch 5 in Fig. 1 another hydraulic consumer may be provided, such as a linear actuator, wherein a supply of a hydraulic cylinder is controlled by a hydraulic pump by means of the control valve 49. Furthermore, the pressure in the hydraulic consumer and / or the load on the hydraulic consumer can be detected by a suitable sensor arrangement and used to control the control valve 49 analogously to the preceding description.

Fig. 2 schematically shows a section 100 of a circuit diagram in a supply system in front of a hydraulic motor, for example, the hydraulic motor 47 in Fig. 1 , with a control valve 110, which the control valve 47 in Fig. 1 and is controlled by a controller 114. The control valve 110 may, in some illustrative embodiments of the invention, be configured as a spool valve with a spool 112, the control device 114 being implemented as a spool control. The control device 114 controls a stroke of the control valve 110, in particular of the spool 112 in the control valve 110, if the control valve 110 is designed as a slide valve.

According to illustrative embodiments of the invention, the control device 114 may be supplied with a control signal which controls a stroke of the control valve 110. Alternatively, the control signal in the control device may be controlled based on external signals. For this purpose, the control device 114 may, for example, be connected to a user input, such as a joystick or the like, so that the control valve 110 can be controlled by an operator. Additionally or alternatively, the controller 114 may be configured to automatically control the control valve 110. It is noted that the control device comprises a logic unit corresponding to the logic unit 44 Fig. 1 or may be associated with it, with reference to the preceding description.

The control valve 110 has a first supply port A, a second supply port B, a pressure port P, a first tank port R1 and a second tank port R2, the second tank port R2 being optional is provided. In some alternative embodiments, only one of the tank ports R1, R2 may be provided, eg the tank port R1.

Valve spool portions corresponding to a first state I of the control valve 110, a second state II of the control valve 110, a third state III of the control valve 110, and a neutral position N of the control valve 110 are formed along the spool 112. In other words, the states I, II, III and N can correspond, for example, to different stroke path sections of a stroke path of the spool 112 in the control valve 110 along the spool. Here, the first state I corresponds, for example, a first Hubwegabschnitt, the second state II a second Hubwegabschnitt, the third state III a third Hubwegabschnitt and the neutral position N corresponds to a fourth Hubwegabschnitt.

In some example embodiments, the neutral position N may correspond to a zero position of the spool 112 in the control valve 110. The first Hubwegabschnitt according to the first state I may, for example, a right-hand relative to the neutral position N along the first Hubwegabschnitts correspond. The second state II may, for example, correspond to a left-hand stroke about the second stroke path section. The third state III may, for example, correspond to a left-hand stroke around the third stroke-path section, wherein the left-hand stroke according to the third travel-path section is greater than the left-hand stroke according to the second travel path section. However, this is not a limitation of the present invention, as any combination of states I, II, III, and N may be formed along the spool 112.

Hereinafter, a function of the individual states of the control valve 110 will be explained in accordance with FIG Fig. 2 described in more detail with reference to some illustrative embodiments of the invention.

In the first state I, a first supply channel between the pressure port P and the second supply port B and a first discharge channel between the first supply port A and the second tank port R2 can be provided along the first Hubwegabschnitts. The first supply channel between the pressure port P and the second supply port B may, for example, have a stroke-dependent cross-section which increases with increasing stroke from the neutral position N to the first state I, so that a mass flow at the second supply port

B supplied by a pressure means, for example, a hydraulic fluid (such as a hydraulic oil, air or other suitable fluid, which is conventionally used in hydraulic systems), which flows through the first supply passage from the pressure port P to the second supply port B, increases. According to some illustrative embodiments, the stroke-dependent cross section of the first supply channel represents a cross section along the flow path of the pressure medium along the first supply channel between the second supply port B and the pressure port P with stroke-varying cross-sectional area. For example, the cross section between a gate edge and an edge of one the supply port B connected hole stroke dependent on the position of the slide can be adjusted. For example, the cross-section along the stroke can have a monotonically increasing or decreasing cross-sectional area, with the cross-sectional area increasing or decreasing from zero to a maximum cross-section.

It is noted that the term "channel" represents a connection between two locations in the flow path of the pressure medium, which flows through the control valve between an input terminal and an output terminal. For example, a channel may represent a connection between P and A or between P and B or between A and R1 or between A and R2 or between B and R1 or between B and R2 or a portion of the aforementioned connection paths.

In the second state II, a second supply channel between the pressure port P and the first supply port A and a second discharge port between the second supply port B and the first tank port R1 can be provided along the second Hubwegabschnitts. The second supply channel between the pressure port P and the first supply port A may, for example, have a stroke-dependent cross-section which increases with increasing stroke from the neutral position to the second state II, so that a mass flow through the second supply nozzle from the pressure port P to the first supply port A. increases, as previously explained with respect to the first supply channel.

In state III, the second discharge channel can furthermore be provided along the third stroke path section between the second supply connection B and the first tank connection R1, wherein furthermore a fourth connection can be formed between the first supply connection A and the pressure connection P, wherein according to the fourth connection, the second supply channel is connected overlying the Hubwegabschnitts with the first discharge channel overlapping. According to some illustrative embodiments herein, the first and / or second bleed passage may have a stroke-dependent cross-section. Alternatively or additionally, the first supply channel and / or the second supply channel has a stroke-dependent cross section.

The various states I to III of a control valve according to some illustrative embodiments of the invention will be described below with reference to FIG Fig. 3 described in which valve characteristics of a control valve according to some illustrative embodiments of the invention are shown. The control valve has a first supply connection, a second supply connection, a pressure connection and a tank connection. In some examples, the control valve may correspond to the control valve 110 in FIG Fig. 2 be educated.

Along the abscissa of in Fig. 3 A stroke position H of a control valve is shown, such as the spool 112 in the control valve 110. In a region around the origin of the diagram along the stroke axis, a neutral position N is arranged in which substantially no mass flow from a pressure port, eg P in Fig. 2 , to supply lines, eg the supply lines A and B in Fig. 2 , is available. This may correspond to a winch winch operation in some illustrative embodiments of the invention.

Towards the left, the region N is followed by a first stroke path section corresponding to a first state I (for example, the state I which, with regard to FIG Fig. 2 described above), wherein the first Hubwegabschnitt in Fig. 3 designated H1. To the right of the region N follows a second Hubwegabschnitt corresponding to a second state II (eg, the state II, in terms of Fig. 2 described above), wherein the second Hubwegabschnitt in Fig. 3 labeled H2. The second Hubwegabschnitt H2 further includes a third Hubwegabschnitt corresponding to a third state III (eg, the state III, with respect Fig. 2 described above), wherein the third Hubwegabschnitt in Fig. 3 designated H3. As shown, this results in the sequence of states I, N, II, III along the stroke H from left to right. It should be noted that this is not a limitation of the present invention, since alternatively, another arrangement of the states I, II, III and N along the stroke H III, II, N, I or another arrangement obtained by a suitable permutation of I, II, III, N.

Along the ordinate are in the diagram in Fig. 3 Mass flows Q (exactly Q _A and Q _B , eg in l / min) and cross-sections A (more precisely A _A and A _B ) shown by nozzles between the pressure port and the supply lines out, under a cross section in this context, a cross-sectional area, eg in mm ² , is to be understood.

In the presentation of Fig. 3 in particular, the mass flow Q _B denotes the mass flow from the pressure connection, eg P in Fig. 2 , to the second supply connection, eg B in Fig. 2 , while the mass flow Q _A, the mass flow from the pressure port, eg P in Fig. 2 , to the first supply connection, eg A in Fig. 2 , designated.

In the presentation of Fig. 3 the cross section A of a nozzle along the negative direction of the ordinate is positively plotted. In this case, the cross section A _{B designates} in particular the cross section of a discharge channel from the second supply connection B to the tank connection R1, while the cross section A _{A designates} the cross section of a discharge channel from the first supply connection A to the tank connection R 2.

As can be seen from the characteristic diagram in Fig. 3 results, the mass flow Q _B along the first stroke H1 increases with increasing stroke in the first state I. This means that with increasing stroke in the first state I (in Fig. 3 to the left along the abscissa) the cross section of a supply nozzle between the pressure connection, eg P in Fig. 2 , and the second supply connection, eg B in Fig. 2 , gets bigger. Furthermore, in the first state I, a discharge channel between the first supply connection, for example A in Fig. 2 , and a tank connection, eg R1 or R2 in Fig. 2 formed, whose cross-section increases with increasing stroke along the Hubwegabschnitts H1.

According to some illustrative embodiments, in the second state II of the control valve is between the pressure port, eg P in Fig. 2 , and the first supply connection, eg A in Fig. 2 , A supply channel formed whose cross-section is stroke-dependent. In particular, the cross section of the supply channel increases with increasing stroke along the stroke path section H2 (in FIG Fig. 3 to the right) until the maximum cross-section is reached, ie a maximum

Mass flow between the pressure connection, eg P in Fig. 2 , and the first supply connection, eg A in Fig. 2 , is trained. At the same time, between the second supply connection, eg B in Fig. 2 , and a tank connection, eg R1 or R2 in Fig. 2 , a discharge channel is formed whose cross-section depending on the stroke along the Hubwegabschnitts H2 (in Fig. 3 to the right) increases.

With increasing stroke along the Hubwegabschnitts H2, in particular with entry into the Hubwegabschnitt H3, the control valve is in the third state III on. Here the supply channel between the pressure connection, eg P in Fig. 2 , and the first supply connection, eg A in Fig. 2 , regulated by a control of the control valve, for example by means of a measuring throttle and a pressure compensator connected to a spool, so that with increasing stroke in Hubwegabschnitt H3 results in a reduction of the cross section of the supply channel. In this case, the control valve is configured such that a lowering of the mass flow through the nozzle is lowered to a constant level at which the cross section of the nozzle in the control valve remains constant and adjusts a load-independent mass flow control. It is possible that for reasons of stability or for reasons of minimizing the power loss, a falling or rising curve instead of the constant course of the characteristic curve can be defined by a corresponding design of the control valve.

In the third state III, the supply channel between the pressure connection and the first supply connection is connected in a superimposing manner to a discharge channel which is connected between the first supply connection A and a tank connection, for example R1 or R2 in FIG Fig. 2 , is formed. This the mass flow between the pressure port, eg P in Fig. 2 , and the first supply connection, eg A in Fig. 2 , superimposed drainage channel may have a stroke-dependent cross section, so that effectively the mass flow from the pressure port, eg P in Fig. 2 , to the first supply connection, eg A in Fig. 2 , can be lowered with increasing cross-section. Here, the mass flow Q _A between the pressure port, eg P in Fig. 2 , and the first supply connection, eg A in Fig. 2 , are lowered along the stroke H3 within a Hubwegabschnitts a to a constant minimum level in state III, which is substantially constant along a subsequent to the Hubwegabschnitt a further Hubwegabschnitt b of the stroke H3 and the leakage of the engine can correspond. In some illustrative embodiments, the characteristic curve of Q _A in FIG Fig. 3 eg be greater than zero along the stroke H3 or Further along the Hubwegabschnitts b in state III can be gradually lowered to a predetermined value greater than zero or increased along the Hubwegabschnitts b to a predetermined value. In a Hubwegabschnitt c, which adjoins the Hubwegabschnitt b, a stroke-dependent cross-section of a discharge channel is opened to one of the tank ports R1 or R2 out, as shown by the line A _A in Fig. 3 along the Hubwegabschnitts c is shown. Here, the cross-sectional area of the discharge channel along the Hubwegabschnitts c varies depending on the stroke, in particular, the cross-sectional area of the discharge channel with increasing stroke in Hubwegabschnitt c is greater.

In illustrative embodiments of a winch, a winch may be operated in the hoistway section a of state III for winding a rope. In Hubwegabschnitt b the rope (with a certain winch tension or a certain hydraulic pressure for the hydraulic motor of the winch) is kept taut. In Hubwegabschnitt c unwinding of the rope can be done when a pulling load from the outside acts on the winch.

In exemplary applications in which, for example, a walking excavator is partially fastened by means of a rope on a slope and moves downhill with a walking movement, the stroke path section c can be used for the mooring function, wherein, for example, the entire supply inflow of the mooring valve (compare Q _A in Fig. 3 ) and a considerably larger proportion of the hydraulic consumer, for example 100 l / min, via the discharge channel (see A _A in FIG Fig. 3 ) can drain.

According to some illustrative embodiments, the control valve may, as it regards the Fig. 1 . Fig. 2 and Fig. 3 described may be a CAN bus valve with electronics. This allows increased system security with less wiring costs and a very high ease of use, the software of the electronics can be easily and optimally adapted to configurations of hydraulic consumers, such as a winch or a hydraulic cylinder.

In some illustrative embodiments, in principle, a control valve may be provided for a hydraulic actuator powered by a hydraulic motor, wherein the control valve includes a first tank port, a pressure port, a first supply port for a first supply line of the hydraulic motor, a second supply port for a second supply line of the hydraulic motor hydraulic motor and a spool whose stroke in the control valve has three different Hubwegbereiche, wherein along a first Hubwegbereichs a first supply channel between the pressure port and the first supply port and a first connection between the second supply port and the first tank port can be provided, wherein along a second Hubwegbereichs a second supply channel between the pressure port and the second supply port and a second connection between the first pressure port and the first tank port can be provided, and the Mooring function along a third Hubwegbereichs is provided, the third connection between the first supply terminal and the the first tank port and a fourth connection between the second supply port and the pressure port is formed, wherein the fourth connection along the third Hubwegbereichs by a first Ablasskanal superimposed with stroke-dependent cross-section, which connects the second supply port to the first tank connection or a second tank connection.

In some illustrative examples, the first connection and / or the second connection may form a separate discharge channel with a stroke-dependent cross-section.

In some illustrative examples, the third connection and / or the fourth connection may form its own supply channel with stroke-dependent cross-section.

Claims (12)

1. Control valve (49; 110) for a hydraulic device, wherein the control valve (49; 110) comprises a first state (I) for continuously delivering a pressure medium to a hydraulic consumer, in particular a cable winch (5) with mooring function operated by a hydraulic motor (47) or a hydraulic cylinder, a supply port (B) of the control valve to be connected to the hydraulic consumer being connected to a pressure port (P) via a supply duct, and a second state (II), in which the supply port (B) is connected to a tank connection (R1; R2) of the control valve (49; 110) via a discharge duct of the control valve (49; 110), wherein the control valve (49; 110) comprises a third state (III) with a corresponding stroke path (H3) along which the supply duct is connected to the discharge duct in a superimposed manner, wherein the supply duct and/or the discharge duct have a stroke-dependent cross-sectional area, wherein the control valve (49; 110) comprises a slide piston (112),
   the slide piston (112) being designed such that a mass flow at the supply port (B) is greater than zero along the entire stroke path (H3) of the third state (III), and
   characterized in that
   the mass flow at the supply port (A) can be reduced to a constant residual level along a section of the stroke path (H3) of the third state (III).
2. Control valve (49; 110) according to claim 1, wherein the third state (III) is formed for mass flow and pressure control.
3. Control valve (49; 110) according to claim 2, wherein the third state has a first stroke path section (a) and a second stroke path section (b) which has a greater stroke away from a neutral position (N) than a stroke relative to the neutral position (N) corresponding to the first stroke path section (a), and wherein the mass flow output at the supply port (B) is controllable to a constant level greater than zero via the second stroke path section (b).
4. Control valve (49; 110) according to Claim 3, wherein the cross-sectional area of the discharge duct changes stroke-dependently along a third stroke path section (c) adjoining the second stroke path section (b) and, in particular, the cross-sectional area of the discharge duct increases along the third stroke path section (c) with increasing stroke.
5. Control valve (49; 110) according to one of claims 2 to 4, wherein the third state (III) starts from a neutral position (N) of the control valve (49; 110) away after a further stroke (H2) corresponding to the second state (II) in a range of 20% to 60% of the total stroke (H).
6. Control valve (49; 110) according to one of claims 1 to 5, wherein the hydraulic consumer is a rope winch (5) having a mooring function and the first state (I) is adapted for continuously unwinding or discharging a rope (3) through the rope winch (5) and the second state (II) is adapted for continuously winding the rope (3) through the rope winch (5).
7. A control valve (49; 110) according to any one of claims 1 to 6, wherein the control valve (49; 110) is a CAN bus valve having electronics.
8. Control valve (49; 110) according to one of claims 1 to 7, wherein in the third state (III) between the pressure port (P) and the supply port (B) a maximum mass flow can be reduced from a range from 90 l/min to 110 l/min to a constant residual mass flow from a range from 5 l/min to 15 l/min depending on the stroke.
9. System having a control valve (49; 110) according to any one of claims 1 to 8, further comprising a control device (44, 114) adapted to automatically control the control valve (49; 110) at least along the stroke path (H3) of the third state (III) on the basis of an external signal which designates a pressure and/or a load at the hydraulic consumer, in particular in the case of a cable winch (5) a winch load and/or a cable pulling force and/or a cable speed and/or a cable length output or unwound from the cable winch (5), so that a pressure output at the supply port (B) can be adjusted to a predeterminable pressure.
10. System according to claim 9, further comprising a sensor arrangement (50, 51, 54) for detecting at least one actual value signal based on the external signal, wherein the control device (44, 114) is adapted for automatically determining a deviation of the at least one actual value signal from at least one set value signal and for controlling the control valve (49; 110) so that the deviation is minimized.
11. System according to claim 10, wherein the sensor assembly (50, 51, 54) comprises a pressure sensor, and the control device (44, 114) is configured to determine a deviation of an actual pressure at or downstream of the supply port (B) from a set pressure.
12. Cable winch system (1) comprising a cable winch (5) having a mooring function for a ship or snow groomer or crane or excavator, in particular a walking excavator, a hydraulic motor (47) for operating the cable winch (5) and a control valve (49; 110) according to any one of claims 1 to 8 and/or a system according to any one of claims 9 to 11.

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