DE202016105352U1 - Spoilerjustage - Google Patents

Abstract

Spoiler adjustment with at least two linear cylinders or differential cylinders with hydraulic chambers (12, 13, 22, 23),
each of which has a piston (21) hydraulically clamped on both sides with a spoiler connector,
characterized in that
a common 4/4 valve (50, 50 ') for driving (72, 74) of the parallel-connected linear or differential cylinder upstream of this
wherein the differential cylinder or linear cylinder via at least two, in particular a first and a second, for the differential cylinder or linear cylinder jointly guided hydraulic lines (30, 40) are connected.

Description

The present invention relates to a spoiler adjustment with the aid of at least two linear cylinders, each of the linear cylinders having at least two hydraulic chambers, which can be filled with hydraulic fluid such as a gear oil. In such a system, the hydraulic fluids in the two hydraulic chambers may be under different pressures.

In other words, the present invention relates to a spoiler adjustment according to the preamble of claim 1.

Technical area

One way to apply the energies for the adjustment of spoilers on motor vehicles, is given by the formation of hydraulic circuits with corresponding transmission chains. Here, as an adjusting element, which is also sometimes referred to as an actuator, for the spoiler gladly resorted to a single or a set of several linearly operating hydraulic cylinders.

State of the art

In the field of application of hydraulic brakes, a wide variety of safety-related controls are already presented in intellectual property literature, some of them also rely on linearly operating hydraulic cylinders. So starts the US 5 509 383 A (Applicant: ITT Automotive Europe GmbH, priority days: 20.02.1991, 22.06.1991, 19.08.1991) based on their first figures with the idea of a brake system and transmits the findings on braking to other hydraulic controls, such. In 5 to a hydraulic circuit for controlling two camshaft adjusters via a valve, which forms a similar throttle to both adjusters.

The EP 1 138 582 A2 (Applicant: Dr. Ing. Hc F. Porsche Aktiengesellschaft, priority date: 31.03.2000) describes a classic donor-receiver system, which also strongly reminds of the origin in the brake area, but with a drive unit and two telescopic displays for the control of a Spoilers (also referred to in the document as the rear wing and spoiler) is equipped. Each telescopic display consists of an inner tube connected to a rear wing and an outer tube held in position. A return movement takes place due to integrally arranged springs. The EP 1 138 582 A1 Already recognizes that such an arrangement involves the risk of uneven movement of the telescope exhibitor. For this reason, to promote a harmonious overall movement of the rear spoiler (spoiler) is provided that at the outputs of the hydraulic cylinder of the drive unit, a nozzle is installed through which at a different strong movement of the telescope exhibitor, a balance of the hydraulic fluid and thereby a more uniform movement can be effected should.

The WO 2008/110 620 A1 (Applicants: CONTINENTAL TEVES AG & Co. OHG, CONTI TEMIC MICROELECTRONIC GMBH, priority days: 15.03.2007, 02.11.2007), which in contrast to EP 1 138 582 A2 explicitly even reported (see page 3) that their starting point is the electro-hydraulic vehicle brake, so also a donor-receiver system, developed the proposal to realize additional movement tasks with additional piston-cylinder units. Two pumps as pressure sources are connected to a common pressure path. Hydraulic valves are arranged in parallel to the pressure sources in a connection between the pressure path and a suction path. Piston-cylinder units are supplied with pressure medium, so that they are extended substantially as simultaneously as possible. Already by these words in that introductory passage of the description of the WO 2008/110 620 A1 a person skilled in the art understands that a simultaneous extension is only to be determined in the case of a distanced, restricted view, that is, only on the merits.

A similar hydraulic circuit, as in the WO 2008/110 620 A1 , For controlling a hydraulic cylinder with two control pressure chambers is the only figure of DE 10 2005 010 638 A1 (Applicant: Bosch Rexroth Aktiengesellschaft, filing date: 08.03.2005). From a hydraulic pump, a pressure medium is conveyed into the working pressure line. The working pressure line has a first and a second working pressure line branch. In addition, signal pressure lines are available. Via a first line branch of the first control pressure chamber is connected to a first valve. Via a second line branch of the first control pressure chamber is connected to a second valve. The second control pressure chamber is connected via a third line branch with a third valve and a fourth line branch with a fourth valve. The in the DE 10 2005 010 638 A1 The circuit shown in the principle is shown in the DE 10 2006 021 939 A1 (Applicant: Robert Bosch GmbH, filing date: 11.05.2006) decorated with other valves such as check valves to lock in case of the drop in the delivery pressure of the pressure medium source to be adjusted motor vehicle parts immediately in their current position. In addition, a manual emergency operation is provided. That is, so that only a single hydraulic cylinder can take any position, The control of four valves and associated auxiliary valves must be carried out. In contrast, the shows WO 2008/110 620 A1 how to achieve a similar effect with two valves.

The German utility model DE 88 06 109 U1 (Applicant: Robert Bosch GmbH, filing date: 07.05.1988) presents a charge-pressure-system in which two cylinders can be controlled in parallel via a 3/3-valve, which can move a spoiler against two springs. Neither a synchronization of the cylinders, nor a securing or locking a once occupied spoiler position seems to have been a noteworthy topic at this early date in 1988.

Different gear ratios are shown in the 43 figures of DE 103 47 203 A1 (Applicant: ZF Sachs AG; priority date: 18.11.2002), many of which are drawn with a pump arrangement consisting of a pump drivable by a drive unit and a pump comprising at least one electric motor driven pump. Pressure control valves are intended to provide a required clutch actuation pressure, wherein the clutch actuators are designed as each equipped with a spring slave cylinder.

task

Automotive spoilers perform various tasks and functions, for some, a spoiler has a decorative character, especially in high-performance vehicles, the overall driving behavior, not least in extreme situations such as cornering at the border of road adhesion, designed for the interaction of all driving behavior influencing components of the vehicle.

Drivers of such vehicles rely on the fact that all components work reliably, including, of course, the spoiler belongs. However, should a technical defect or technical malfunction occur, then at least one state should be aimed for, which does not have a negative effect on the driving dynamics of the vehicle, so that ideally a tracking exit from a movement of the vehicle is ensured as comprehensively as possible from a curve ,

If the spoiler is designed as a hydraulically adjustable component, then the safety function described above can also be implemented in parts in the hydraulics. For this purpose, a hydraulic circuit and it is appropriate to design circuit components for this purpose.

invention description

The object of the invention is achieved by a spoiler adjustment according to claim 1. Advantageous developments can be found in the dependent claims.

Spoilers, especially on powerful vehicles, belonging to the category of powerful vehicles, vehicles with 500 hp and more on the output side of the drive train are advantageously as permanently in their position and / or position changeable vehicle components shapable, ideally from an end position (retracted position) to the other end position (maximum extended end position) within less than a second, preferably less than 0.75 seconds, more preferably even less than 0.5 seconds are changeable. In other words, the controlled spoiler is constantly adjustable. A corresponding device or the adaptation of the spoiler can also be referred to as spoiler adjustment.

A hydraulic spoiler adjustment is characterized by numerous advantages, to name a few. As a fast controllability of actuators that can still cover a considerable stroke, z. B. in an embodiment 10 cm, z. B. even 20 cm in a further embodiment. In one embodiment, the path or the stroke to be handled can be settled in a range of 150 mm. The main direction of movement of a spoiler can be realized by a linear movement by means of linear cylinders or differential cylinders.

The use of linear cylinders basically helps to map a desired height adjustment of a spoiler directly through the path, whereby, of course, pivotal movements can also be attributed to linear movements. The use of a differential cylinder is z. In cases where the one direction of movement (eg the direction of retraction) should be able to pass at a higher speed than the other movement (eg the direction of extension). As a result, depending on the wishes of the spoiler control, it depends on whether linear cylinders, differential cylinders, synchronizing cylinders or other types of cylinders with double-acting pistons are used.

It should be mentioned again that in one embodiment of a linear cylinder or a differential cylinder, a piston runs or moves. The piston can take various positions along a path, in particular a straight, elongated path. The position of the piston is determined by a ratio between two hydraulic chambers in the linear cylinder or in the differential cylinder. As control and control variables both volume controls and pressure controls can be used. The piston of a linear cylinder or a differential cylinder is located, in particular if it assumes a center position along its path of movement, between two hydraulic chambers which can be filled with hydraulic fluid. The piston is thus hydraulically clamped. Both sides of the piston, the top and the bottom are limits of hydraulic chambers. The hydraulic chambers can be differently filled with hydraulic fluid, which adjusts the position of the piston within its path of movement.

The movement of the piston should be passed on to the spoiler. For this purpose, spoiler connectors are attached to the piston, for. B. lifting rods or extension lever. The linear movement of the pistons can be converted or translated by means of the spoiler connectors into the movement of the spoiler extensions.

In the context of experiments, it has been found to be particularly advantageous if at least two pistons for the movement with the interposition of spoiler connectors are available. In the end areas of a spoiler, mechanical supports and connections for the spoiler can be placed particularly favorably. This includes the spoiler connector. In a favorable embodiment, linear cylinders are positioned in the vicinity of extremities of the flat, elongated and narrow spoiler, in other words on the left and right at the end of the spoiler.

To change or exact adjustment of the respective piston positions in the linear or differential cylinders, a 4/4-valve is provided. The 4/4 valve can be called a common valve. The 4/4 valve similarly supplies a first cylinder and a second cylinder, e.g. B. a first linear cylinder, in particular synchronizing cylinder, and a second linear cylinder, in particular synchronizing cylinder, or a first differential cylinder and a second differential cylinder. In a further embodiment, also a third and fourth linear cylinder, alternatively a third and fourth differential cylinder. It is especially economical if, for all these cylinders, which result in particular from a set of linear and / or differential cylinders, the 4/4 valve is the jointly controlling valve, ie a main control valve for all linear cylinders or differential cylinders of the spoiler adjustment.

The valve sits away from the cylinders, which are mechanically coupled as close as possible to the spoiler via their spoiler connectors. From the 4/4 valve, two hydraulic lines lead to the cylinders. One of the hydraulic lines, in particular a first hydraulic line, leads to all similar first chambers of the cylinder. A second hydraulic line leads to all second chambers of the cylinder. Each cylinder has at least two ports. The first hydraulic line leads to one port. The second hydraulic line leads to the second connection. At least in sections, there is only a single hydraulic line per downstream chamber connection of the cylinder. Feeding to the hydraulic chambers, this uniform, common hydraulic line can be fanned out or split up in the end into the number of hydraulic chambers to be controlled.

If it is a proportional control valve in particular in the 4/4-valve, the pressure and / or volume ratios in the hydraulic chambers of the cylinder can be adjusted continuously. All similar hydraulic chambers, z. For example, the hydraulic chambers pushing out the spoiler connectors may be designated as A-chambers, leading to a same port on the grouping 4/4 valve.

The spoiler, which should be able to occupy several different layers, includes in its control cylinder. The cylinders have pistons. The pistons are located between a first hydraulic chamber and a second hydraulic chamber, it being understood that a hydraulic chamber can also be reduced in volume to almost 0 or actually 0 in individual positions. When the piston of a cylinder, such as a linear cylinder or a differential cylinder, moves in one direction, the volumes of the two hydraulic chambers that clamp the piston change. The piston is hydraulically clamped on two sides and can change its position.

In addition to the 4/4 control valve, there is at least one further component which operates like a valve, namely a blocking regulator, between the 4/4 valve and the consumers, the linear and / or differential cylinders. The blocking regulator responds to pressure conditions. The blocking regulator blocks the return flow of the hydraulic fluid from one of the hydraulic chambers in a first situation. If a pressure difference between a primary side of the blocking regulator and a secondary side of the blocking regulator exceeds a minimum pressure difference, the blocking regulator opens, so that outflow of the hydraulic agent from the chamber is possible. If the pressure differences are insufficient, the blocking regulator remains in its locked position. The piston, which has found its position due to the pressure in the hydraulic chamber, changes its position only minimally when other power conditions should act on the spoiler.

In addition, the overpressure in one of the hydraulic lines is taken into account. It is considered an overpressure in a hydraulic line, which is not the hydraulic line, in which the lock controller can perform its function for the hydraulic fluid. In other words, if the blocking regulator is located in the first hydraulic line and selectively leaves or blocks hydraulic means, an overpressure in a second hydraulic line is monitored by means of a control line on the blocking regulator.

Non-return valves which can be precontrolled are suitable as blocking regulators, with a pressure being taken up in a further hydraulic line as pilot control means.

The blocking regulator prevents outflow or outflow of the hydraulic fluid from its associated chamber of the cylinder, in particular the linear cylinder or differential cylinder, or the chambers of the cylinder, which are the same in type. Only when a minimum pressure threshold is exceeded does the blocking regulator allow further hydraulic fluid either into the hydraulic chambers or it allows hydraulic fluid to escape from the hydraulic chambers. The outflow, the leakage of the hydraulic fluid from the same-direction chambers of the cylinder is in one embodiment only possible if a pressure in another hydraulic line is exceeded so far that in the other hydraulic line, a higher pressure prevails than in the influenced by the lock controller hydraulic line ( possibly even after a delay .DELTA.t).

Thanks to the hydraulic equal control of the hydraulic chambers of the same type in the cylinders, all linear cylinders and differential cylinders behave almost identically to each other. Occur undesirable situations, such. B. a collapse of the hydraulic fluid supply, z. B. due to a pump error, which usually occur rarely, thanks to the at least one locking regulator, the previously controlled position or position of the spoiler is held.

An uncontrolled receding spoiler in its initial position, especially in its retracted position is thus prevented in many cases of error, which can be understood as a contribution to increasing safety when driving the vehicle.

In the following, advantageous embodiments and developments are set forth, which in themselves, both individually and in combination, can also disclose inventive aspects.

If, with the aid of blocking regulators, as discussed above, the hydraulic circuit is realized, it is in principle possible, in only one hydraulic line of several, leading to a cylinder hydraulic lines, eg. B. in the respective first hydraulic line, only such a lock controller, z. B. in the form of a check valve as a blocking regulator to provide. Per cylinder should be arranged in such a configuration, at least in a line leading to the cylinder, a blocking regulator. For a cylinder clamped on two sides, there are therefore a first and a second hydraulic line. Of these two hydraulic lines in one embodiment, only the respective first hydraulic line has a blocking regulator. In an alternative embodiment, only the respective second hydraulic line has a blocking regulator. Where a check valve is used, z. B. advantageously be used in one embodiment spring-biased check valves. If the number of valves is reduced, this increases the integrated safety in the hydraulic circuit.

In one to the idea, realized only in one of two hydraulic lines arranged blocking controller circuit concept, in particular alternative control concept, it is also conceivable that in each of the hydraulic lines, all of which lead to cylinder spoiler adjustment, a check valve is arranged. That is, there is a blocking regulator per line leading to one of the chambers of a cylinder. The number of check valves corresponds to the number of, possibly merged, (central) hydraulic lines. In such a count of the number of hydraulic lines z. B. only the grouping hydraulic lines or their grouping sections are counted. The number of grouping hydraulic lines corresponds in such a case, the number of existing lock regulator, in particular the number of check valves. Each hydraulic line, which leads either to a (hydraulic) chamber of the cylinder or away from a chamber of the cylinder, is guided via a blocking regulator. The working side of the 4/4 valve can also be referred to as the downstream side. The pressure supply side of the 4/4 valve or the tank outlet side can also be referred to as the inflow side of the 4/4 valve. Thus, with respect to the consumer (s), the downstream side is "cylinder" after the 4/4 valve. On the inflow side is thus in relation to the consumer or "cylinder" in front of the 4/4 valve. As a result, each line can be locked separately. It increases the hydraulic safety.

The lock regulator has a preferential forward direction and a reverse direction. If hydraulic fluid is at a higher pressure on an inlet side, ie on the side of the blocking regulator that is farther away from the cylinders, the blocking regulator opens into its passage position. If hydraulic fluid is present at a higher pressure on the working side, that is, on the side closer to the cylinders of the blocking regulator, then the blocking regulator locks in a first operating state. The blocking controller opens at a Pressure gradient in the inflow direction. The blocking controller locks in a state at a pressure gradient in the outflow direction. In response to an overpressure in one of those hydraulic lines, which is assigned directly as a line of a hydraulic chamber, the lock regulator, the check valve in the locked position. Thus, the check valves become not only by the pressure ratios in the hydraulic line having the check valve, that is, by the check valve alternately in a locked state and in an open state influencing hydraulic line, but also by the pressure conditions in the hydraulic line in which the check valve is not arranged , controlled. Advantageously, the non-return valves are in an open position in response to the overpressure in the other hydraulic line, which is therefore different from the hydraulic line controlling it. Conversely, a flow of hydraulic fluid from a chamber of the differential cylinder or the linear cylinder is prevented as long as there is no pressure in a not leading to this chamber hydraulic line. It may also be said, in an advantageous development, the non-return valves may, depending on a pressure in another hydraulic line, meaning a hydraulic line in which the non-return valve does not function as a blocking element, effect the switching-on and the blocking. The check valve operates in a first hydraulic line. The check valve changes its state in response to a pressure in a second hydraulic line. The check valve or the blocking regulator are provided as controlling elements for a first hydraulic line. A pressure in a second hydraulic line is detected by the check valve or the blocking regulator. The check valve or the blocking regulator operates in dependence on a pressure in the second hydraulic line. In two hydraulic lines, each with a check valve results in a cross over the check valves, the pressure of a hydraulic line is taken into account for controlling the check valve in the other hydraulic line. Should the circuit of the hydraulics for the spoiler adjustment comprise more than two hydraulic lines to the cylinders, the check valve, which is integrated in a hydraulic line, can be controlled depending on the pilot pressure and / or the overpressure in one or more of the other hydraulic lines. By thus designed check valves as a lock regulator for the supply of hydraulic chambers with hydraulic means of the synchronization of the cylinder used for spoiler adjustment can be further improved and a fast control of the cylinder can be realized.

In a favorable development, the pressure in a second hydraulic line (in comparison with the first hydraulic line as the one in which the blocking regulator operates) is available as a pilot pressure for the blocking regulator in the first hydraulic line. In a favorable hydraulic circuit, which can be operated according to an advantageous control process of the hydraulics, the check valve for the spoiler adjustment, which is provided in a hydraulic line, in particular the first hydraulic line, controlled in response to a pilot pressure in another hydraulic line. With a missing pilot pressure in another hydraulic line, in particular the second hydraulic line, the check valve is in a blocking position as long as a pressure before the check valve, in particular in a line section between 4/4-valve and check valve, is lower than a pressure downstream of the check valve , So in particular in a line section to the hydraulic chamber, a subsequent to the check valve line section leading to the associated hydraulic chamber. Further, the check valves may be advantageously controlled in response to an overpressure in the other hydraulic line when there are two hydraulic lines for each cylinder. The pressure in the counteracting chamber of the cylinder is taken into account in the switching behavior of the blocking regulator, i. h., it takes place in the end a hydraulic feedback, which increases the safety.

Preferably ball seat valves are used as check valves, which open only as a result of exceeding a minimum pressure in the hydraulic line. Advantageously, all hydraulic lines are equipped with a non-return valve, wherein the non-return valves block the outflow of hydraulic fluid from a respective non-return valve associated hydraulic chamber of the linear cylinder or the differential cylinder in a control position. The non-return valves are preferably provided downstream, ie after the 4/4 valve. But it is also conceivable to use a check valve in front of the 4/4 valve, ie on the inflow side. Ball seat valves are extremely safe hydraulic components.

In an advantageous development, the blocking controller does not react directly to each pressure or pressure difference in durchschaltender manner, but it is a minimum pressure required. Only at a minimum pressure, the check valve reacts in an opening manner. Only at a minimum pressure difference does the blocking regulator open the hydraulic line.

The inherent behavior of the spoiler can also be taken into account when designing the hydraulic circuit. If the spoiler is designed so that aerodynamic influences move the spoiler either in the extended or in the retracted position, the lock regulators can be designed so that these existing forces and thus pressures are compensated. In a special Advantageous development of the spoiler can be designed so that it - tends to a home and / or rest position - in particular due to aerodynamic effects. This can also contribute to the weight of the spoiler. Due to its own weight, the device with the spoiler can be designed so that the spoiler strives in the retracted position. The aerodynamic effects can be such that the spoiler is either pulled out or even struts into the retracted position. The hydraulic circuit may now have at least one of the effects, weight effect and / or aerodynamic effect, in the control behavior, e.g. Due to hysteresis (s).

In a preferred embodiment of the spoiler adjustment according to the present invention, the hydraulics of Spoilerjustage is supplied via a pressure line of a hydraulic transmission control of the motor vehicle. A favorable hydraulic transmission control is designed so that it - escaping especially without charge-pressure system - has a central pressure line. At this central pressure line, which is the highest pressure reference point in the hydraulic circuit, all control loops can be connected. The pressure line is easy to continue only up to the control valve of Spoilerjustage. Each functional group, such as the spoiler adjustment, is stich-like from the central pressure line. The transmission control conventionally already has a number of consumers, z. As for the control of actuators, a transmission differential, clutches, hybrid clutches, etc. Another consumer in the form of a hydraulic unit for controlling the Spoilerjustage can be designed with respect to its temporal switching behavior so that it does not affect the rest of the transmission control (noticeable). It is thus not a complete, separate hydraulic circuit, provided that the pressure supply is to count, for the spoiler adjustment required because, for example, pumps and components for the preparation of a hydraulic fluid are already available for the transmission control. Advantageously, this hydraulic unit spoiler adjustment can be supplied offset in time to the other consumers. Overall, this can be reduced energy requirements for the control of the transmission and the spoiler adjustment.

Another contribution to the safety and functionality of the spoiler adjustment is the deliberate routing to the cylinders. After the 4/4 valve, firstly group or group lines or centrally guided hydraulic line, which can also be referred to as a combined (central) hydraulic line, can be guided. These group lines, because they supply or dispose of several hydraulic chambers, ie group-like cylinders, are to be fanned out in front of the cylinders. If the fanning out positions are chosen so that the line lengths between the line sections before and after fanning out are almost identical, d. H. are the same length (eg deviate only by 10 cm to 20 cm with each other), in particular with a similar cross-section of each of the lines and line sections an equal hydraulic behavior is present. The spoiler reacts equally to each of its cylinders. Uncontrolled effects affecting the safety in the spoiler adjustment are reduced.

As already mentioned, in a preferred embodiment of the spoiler adjustment according to the invention, the 4/4 valve is designed as a proportional directional valve. About a slide, the z. B. between a spring and a plunger z. B. is movable by an electromagnet, is displaceably clamped, different working positions of the 4/4-valve can be adjusted. It is advantageous that in a rest position of the 4/4-valve z. B. is determined by the fact that the valve is not switched against the force of the spring, a pressure-less switching of the hydraulic circuits is ensured. Instead of a depressurized switching position, a position for decoupling may also represent the first switching position of the valve. When depressurised, the pressure in the lines is reduced until a pressure threshold underrun has taken place. A decoupling separates the supply line and the discharge, that is, the line to and from the valve. The pressure in the working lines thus remains unchanged, except for a natural leakage, when changing over from a working position to the decoupling position. A valve with a decoupling position in the first switching position, the powerless control position of the valve, ensures that the currently prevailing status quo in the hydraulic unit is maintained. Next is a first working position for pressurizing similar hydraulic chambers, z. B. the B-chambers, the differential cylinder or the linear cylinder defines can be promoted in the hydraulic fluid in this chamber. A second working position of the 4/4 valve is for pressurizing similar hydraulic chambers, z. As the A-chambers, the differential cylinder or linear cylinder provided, wherein the pressurizable in the second working position hydraulic chambers, mirror image arranged hydraulic chambers to the pressurized hydraulic chambers, d. H. the B-chambers, are in the first working position. Between the first working position and the second working position, a complete blocking position is advantageously to be found, in which the slide or piston in the 4/4 valve interrupts all ports of the 4/4 valve.

Preferably, at least two hydraulic pumps are provided for supplying the hydraulic circuit for the spoiler adjustment. there Advantageously, two hydraulic pumps of the transmission control can be used. A pressure for the hydraulic means of Spoilerjustage is related by at least one of the at least two existing. So a sufficient pressure can be ensured, even if one of the pumps is not operated, z. B. because it fails or z. B. for energy conservation reasons. To cover required high pressures or in sufficiently short times, both pumps can be used to supply the Spoilerjustage or operated. Also, a mutual operation of the two pumps is possible. In one embodiment, one pump may be a mechanically driven pump while the other pump is a pump equipped and driven by an electric motor.

A particularly advantageous control of the 4/4-valve is to determine the respective slide or piston position of the 4/4-valve over a duty cycle. Depending on the quantity to be controlled and the desired maximum pressure in the spoiler adjustment, directly controlled and pilot-valve-controlled spool valves can be used as a 4/4 valve.

Another advantage is that the spoiler adjustment in this embodiment can be easily controlled depending on an output speed from the transmission, since the hydraulic transmission control already includes the hydraulic unit for Spoilerjustage. In addition, it is also possible to make the hydraulic unit for spoiler adjustment to a hydraulic control for driving dynamics components and vehicle brake components. A transmission control unit determines the switching states of the transmission components. As part of the transmission control, the spoiler adjustment can also be integrated into the control program. The spoiler adjustment becomes a mathematical or programmatic or logical part of the transmission hydraulics.

Alternative design, current controller in each line, adjustable to test stand

A check valve can also perform the function of a flow regulator, whereby the check valve regulates the flow. Friction effects in the cylinders and different behavior of the pistons in the cylinders can be compensated. Advantageously, the check valves can be used as throttle points in the supply line into the hydraulic chambers.

In the context of the efficient production of a transmission hydraulic according to the invention, the non-return valves can be designed as adjustable current regulator. When the spoiler adjustment is assembled, the flow cross-section of the check valves, in particular the inlet and / or outlet of the ball seat valves, can be adjusted by means of actuators such as adjusting screws. If, during a first test of functional safety and serviceability, it emerges that a different movement behavior of the cylinders is to be observed, in particular despite the numerous measures of the uniform control of the cylinders, it can be determined by means of the actuators, e.g. B. of adjustable aperture, a check valve can be set as a throttle in the hydraulic line.

Thanks to the additional control lines, the blocking regulators can be regarded as multi-functional links. At a sufficient pressure difference between inflow and outflow side of the blocking regulator opens this. At a counter pressure or a back pressure of the lock regulator remains in the closed position. Except in the situation that sufficient pressure is present in another hydraulic line, the blocking controller does not switch between the two states independently, but only pressure-dependent. The controller has bistable positions or circuit states with the help of the additional control line to the blocking regulator. This will u. a. a functional safety integrated into the hydraulic circuit. Thanks to the bistable positions of each blocking regulator, which is equipped with a control line, the inflow and outflow can be controlled.

In particular, it can be ensured that the spoiler remains in a desired position, in particular in an extended position, even in the event of defects in the hydraulic fluid supply, even if aerodynamic effects act on it or if its own weight would cause it to lower.

The previously described combinations and exemplary embodiments can also be considered in numerous other connections and combinations.

Brief Description

The present invention may be better understood by reference to the accompanying figures, which set forth by way of example particularly advantageous design possibilities without restricting the present invention thereto

1 1 is a hydraulic circuit diagram of an embodiment of a motor vehicle transmission with a first variant of a hydraulic circuit for a spoiler adjustment according to the invention;

2 the first variant of a hydraulic (circuit) for a spoiler adjustment according to the invention as in 1 .

3 a second variant of a hydraulic (circuit) for a spoiler adjustment according to the invention,

4 3 a hydraulic circuit diagram of a further embodiment of a motor vehicle transmission with a third variant of a hydraulic system for a spoiler adjustment according to the invention,

5 the third variant of a hydraulic (circuit) for a Spoilerjustage invention as in 4 and

6 a hydraulic circuit diagram of a third embodiment of a motor vehicle transmission with a further variant of a hydraulic (circuit) for a Spoilerjustage invention.

figure description

The design options shown in the individual figures can also be interconnected in any form.

Based on 1 intended to general aspects of a hydraulic control 100 be described for a motor vehicle transmission, which is a variant of a hydraulic for a spoiler adjustment 1 according to the invention comprises (similarly a spoiler adjustment 1' to 3 ). It is in 1 a hydraulic control for an exemplary transmission (not shown graphically) having a dual clutch unit, a differential unit and a hybrid clutch unit; however, it is clear to one skilled in the art that a hydraulics for a spoiler adjustment 1 . 1' respectively. 400 is useful according to the invention in other types of motor vehicle transmissions, z. B. in automatic transmissions.

The hydraulic control 100 has individual strands 110 . 120 . 130 . 140 and 150 on, which each take on a specific task to control the motor vehicle transmission. In the exemplary transmission, the strands are 110 and 120 each provided for an actuator by the z. B. synchronizations of a Räderumlaufgetriebes can be moved. Each of the strands 110 and 120 has two double-chamber cylinders 111 . 111 ' and 121 . 121 ' on. Each of the double-chamber cylinders 111 . 111 ' and 121 . 121 ' are control or switching valves 112 . 112 ' . 122 . 122 ' as assigned to 3/4-proportional control valves, which serve in a conventional manner for controlling the actuators. The cylinders 111 . 111 ' can have a branching supply line 113 and the cylinders 121 . 121 ' over a branching supply line 123 be supplied with hydraulic fluid according to a position of the valves 112 . 112 ' . 122 . 122 ' , To form a cut-off level is in the supply lines 113 and 123 one control valve each 115 . 125 intended.

The strand 130 is for the hydraulic actuation of a hybrid clutch and the train 140 is intended for the actuation of the two clutches of a double clutch.

The strand 130 for the hybrid clutch is used to control a clutch cylinder 131 and includes in its supply line 133 a control valve 132 , Using the through the clutch cylinder 131 actuated separating clutch, such as. As a jaw clutch, the one drive motor from the other drive motor (each not shown graphically) can be separated. For friction clutches as disconnect couplings or hybrid clutches, the illustrated proportional control valve is particularly advantageous 132 ,

The strand 140 branches to a first sub-string for controlling a first clutch cylinder 141 and a second sub-string for controlling a second clutch cylinder 141 ' , Each of the sub-strands includes a control valve 142 . 142 ' with pressure control, a buffer 144 . 144 ' and a pressure sensor 145 . 145 ' , With the help of the pressure sensor 145 . 145 ' can also be (indirectly) the position of the clutch cylinder 141 . 1411 determine. The control valve 142 . 142 ' is also like the other control valves 112 . 112 ' , a proportional control valve. The buffers 144 . 144 ' can be used to suppress vibrations, if one of the clutch cylinder is in use or performs a synchronization process. To the control valves 142 . 142 ' is ever a diversion 146 . 146 ' each provided with a check valve, which is a return of hydraulic fluid to a supply line 143 to the strand 140 enable. The supply line 143 includes a switching valve 147 together for both partial strands.

The strand 150 is provided for the hydraulic actuation of the differential unit and in turn comprises a clutch cylinder 151 , a control valve 152 with pressure control, a buffer 154 and a pressure sensor 155 , The clutch cylinder 151 depends on the position of the control valve 152 via a supply line 153 provided.

The hydraulic control 100 has a pressure supply line 160 on top of that by a processing unit 200 is supplied for the treatment of hydraulic fluid. From the pressure supply line 160 branch the supply lines 113 . 123 . 133 . 143 and 153 from. The strands 110 . 120 . 130 . 140 . 150 However, with the help of the valves 115 . 125 . 132 . 147 and 152 from the pressure supply line 160 be shut off. The pressure supply line 160 is the central pressure supply line, from the pressure level all consumers, possibly reduced in pressure, are supplied.

The processing unit 200 promotes a hydraulic fluid from a hydraulic fluid sump 201 and serves to provide the hydraulic means for the hydraulic control 100 , The processing unit 200 is as a double pump system with a first pump 210 and a second pump 212 educated. About pumping lines 220 and 222 the hydraulic fluid is removed from the sump 201 pumped. On the output side of the pumps 210 . 212 is the pressure supply line 160 connected, taking after the pumps 210 . 212 one control valve each 230 and 232 for controlling the hydraulic fluid supply in the pressure supply line 160 is provided. The processing unit 200 is to provide cooled hydraulic fluid and at the same time sufficient pressure in the pressure supply line 160 sure.

From the pressure supply line 160 branches a supply line 240 in the sense of a stub line coming off the valve 230 directly from the pump 210 and / or via a connection section 224 that is attached to the valve 232 connects, from the pump 212 can be fed. The pressure supply line 160 the hydraulic control 100 feeds via the supply line 240 a hydraulic control unit 1 , as it is based on a first variant of a hydraulic system for a spoiler adjustment according to the invention. The control unit 1 for the spoiler adjustment is thus part of the hydraulic control 100 of the motor vehicle transmission. Advantageously, therefore, the spoiler adjustment can be regulated in dependence on an output speed of the transmission.

The control unit 1 the first variant of Spoilerjustage is using 2 explained in more detail. The spoiler adjustment comprises two cylinders, a first cylinder 10 and a second cylinder 20 , each with a piston 11 . 21 by means of the control unit 1 be driven hydraulically. The cylinders 10 and 20 act as a linear cylinder or differential cylinder. To the pistons 11 . 21 are each mounted spoiler connector (not shown), which in turn are attached to a spoiler (not shown), so that the spoiler by means of hydraulically driven pistons 11 . 21 can be adjusted. The spoiler additionally represents a mechanical coupling of the cylinders. The pistons 11 . 21 divide the cylinders 10 . 20 by stamping in each case in a first hydraulic chamber 12 . 22 and a second hydraulic chamber 13 . 23 , The first hydraulic chambers 12 . 22 and the second hydraulic chambers 13 . 23 are in their cylinders 10 . 20 thus mirror image of the punches on the piston 11 and 21 arranged. The pistons 11 . 21 are between the hydraulic chambers 12 . 22 and 13 . 23 Hydraulically clamped on both sides and acting in both directions, so that the spoiler can be lifted and lowered via spoiler connector. In this case, the first hydraulic chambers 12 . 22 are referred to as A-chambers, which extend the spoiler, and the second hydraulic chambers 13 . 23 can be referred to as B-chambers, which retract the spoiler.

The hydraulic chambers 12 . 13 and 22 . 23 be via a first hydraulic line 30 and a second hydraulic line 40 with hydraulic fluid from the treatment unit 200 provided. The cylinders 10 and 20 are through the hydraulic lines 30 and 40 connected in parallel. Here is the first hydraulic line 30 for the first hydraulic chamber 12 of the first cylinder 10 and the first hydraulic chamber 22 of the cylinder 20 run jointly and can the first hydraulic chambers 12 . 22 provide together. Likewise, the second hydraulic line 40 for the second hydraulic chamber 13 of the first cylinder 10 and the second hydraulic chamber 23 of the second cylinder 20 run jointly and can the second hydraulic chambers 13 . 23 provide together. For this purpose, the jointly managed hydraulic lines fan out 30 and 40 preferably in line sections 31 and 32 , respectively. 41 and 42 , on, each to one of the first hydraulic chambers 12 . 22 , or to one of the second hydraulic chambers 13 . 23 , to lead. In the variant shown, the line section leads 31 to the first hydraulic chamber 12 of the first cylinder 10 , the line section 32 to the first hydraulic chamber 22 of the second cylinder 20 , the line section 41 to the second hydraulic chamber 13 of the first cylinder 10 and the line section 42 to the first hydraulic chamber 23 of the second cylinder 20 , Advantageously, the line sections 31 and 32 for the first hydraulic chambers 12 . 22 and the line sections 41 and 42 for the second hydraulic chambers 13 . 23 show the same hydraulic behavior. This can be z. B. be achieved by equal lengths of the line sections and the same cross section of the lines, whereby hydraulic effects, such as hydraulic friction, due to a same friction distance are at least approximately equal in both sections. It can also be a diaphragm in the cylinders 10 . 20 or at a check valve 70 . 75 be used so that the friction in the cylinders 10 . 20 is subordinate in their importance to the aperture.

The first hydraulic line 30 and the second hydraulic line 40 are to an output side of a 4/4 valve 50 connected, which is formed in this example as a proportional valve with four ports. On the input side is the 4/4 valve 50 to the supply line 240 the hydraulic control 100 or the pressure supply line 160 (please refer 1 ) connected. The 4/4 valve 50 supplies both the first cylinder 10 as well as the second cylinder 20 and thus forms a common main control valve for both cylinder 10 . 20 , The variant of the spoiler adjustment shown comprises two cylinders 10 . 20 , However, it is basically conceivable that even more cylinders are used for adjusting the spoiler, which then also from the main control valve in the form of the 4/4-valve 50 can be supplied. The first hydraulic chambers 12 . 22 and the second hydraulic chambers 13 . 23 can be filled differently with hydraulic fluid, bringing the position of the piston 11 . 21 in the cylinders 10 . 20 changed and the spoiler is adjusted between a home or rest position and different extension positions.

To adjust the spoiler, the 4/4-valve 50 occupy four different working positions. In a pressure release position 51 are both hydraulic lines 30 and 40 from the supply line 240 closed off and to a marsh 60 connected, so that the hydraulic control unit 1 at least in the first hydraulic line 30 and the second hydraulic line 40 to the check valves 70 . 75 is depressurized. The first and second hydraulic lines merge 30 and 40 inside the valve and open into the port to the swamp 60 , In a first job 52 is the second hydraulic line 40 for the common filling of the second hydraulic chambers 13 . 23 to the supply line 240 connected and the first hydraulic line 30 is for the discharge of hydraulic fluid from the first hydraulic chambers 12 . 22 to the swamp 60 connected. In a locked position 53 are both hydraulic lines 30 and 40 from the supply line 240 and also from the swamp 60 separated. All four ports of the 4/4 valve 50 are closed. In a second job 54 is the first hydraulic line 30 for the common filling of the first hydraulic chambers 12 . 22 to the supply line 240 connected and the second hydraulic line 40 is for discharge from the second hydraulic chambers 13 . 23 to the swamp 60 connected. As described above, those are in the second working position 54 pressurizable first hydraulic chambers 12 . 22 arranged in mirror image with respect to the second hydraulic chambers 13 . 23 who are in first job 52 are pressurizable. Furthermore, the blocking position 53 between the first job 52 and the second job 54 provided, like 2 can be seen.

The 4/4 valve 50 is preferably cartridge- or sleeve-like formed with a slide and can be switched along its longitudinal direction between the different working positions by moving the slider or the piston. Next is the 4/4 valve 50 advantageous over a spring 55 spring biased and is by means of an electromagnet 56 a pilot valve 80 between the working positions 51 . 52 . 53 . 54 against the force of the spring 55 moved or switched. In the in 2 variant shown is the spring 55 in the first working position as far as possible relaxed and the 4/4-valve 50 is in a quiet location. Therefore, the hydraulic control unit 1 in the rest position of the 4/4 valve 50 depressurized.

The hydraulic variant for a spoiler adjustment according to the invention, as in 2 shown points in the first hydraulic line 30 a check valve 70 and in the second hydraulic line 40 a check valve 75 on. The check valves 70 and 75 are advantageously designed as spring-biased check valves and biased against the direction to pressurize the hydraulic chambers, so that an outflow of hydraulic fluid from the hydraulic chambers 12 . 13 . 22 . 23 in a control position of the check valves 70 . 75 Is blocked. The check valves 70 . 75 thus act as a blocking regulator. The first check valve 70 is due to a pressure difference in the first hydraulic line 30 controlled so that the hydraulic line 30 can be referred to as a controlling hydraulic line. The same applies to the second check valve 75 and the second hydraulic line 40 , The check valves 70 and 75 are each downstream from the 4/4 valve 50 in the hydraulic line 30 and 40 arranged.

In another hydraulic variant with a control unit 1' for a spoiler adjustment according to the invention, as in 3 shown, only the first hydraulic line 30 a first check valve 70 on and in the second hydraulic line 40 no check valve is provided.

An advantageous process for controlling the inventive spoiler adjustment with the inclusion of a check valve as the first check valve 70 as a blocking regulator, for the sake of simplicity, it is first based on the hydraulic variant 3 explained. In the variant of 3 serves the second hydraulic line 40 for pressurizing the cylinder 10 and 20 , in particular the hydraulic chambers 13 and 23 , When increasing the pressure in the second hydraulic chambers 13 and 23 become the pistons 11 and 21 inside the cylinder 10 and 20 shifted, so even in the first hydraulic chambers 12 and 22 and consequently in the section of the first hydraulic line 30 that between the cylinders 10 . 20 and the check valve 70 is located, an increase in pressure takes place. At first, the check valve remains 70 in the control position and blocks outflow of hydraulic fluid. The check valve is advantageous 70 the first hydraulic line 30 pre-controlled and has a drive for this purpose 72 on which the check valve 70 depending on the pressure conditions in the second hydraulic line 40 controls. In addition, in the second hydraulic line 40 a pressure sensor may be provided which emits a signal. Like from the 3 is seen, the check valve 70 hydraulically via the control 72 driven. The means the check valve 70 is indeed by the controlling hydraulic line 30 in which it is arranged, controlled, in addition, the check valve 70 through the control 72 also in dependence on a pressure in the second hydraulic line 40 , which has no direct controlling effect on the check valve, to be controlled. In an alternative embodiment, the control can be realized via a signal of the pressure sensor. In the advantageous control process, the check valve 70 in response to an overpressure in the second hydraulic line 40 by means of the control 72 brought into an open position. This allows the first hydraulic chambers 12 . 22 be relieved and influence the position of the piston 11 . 21 in the cylinders 10 . 20 be taken. Due to the jointly guided hydraulic lines while the piston 11 . 21 and thus also the spoiler connector symmetrically and evenly actuated. But if in the second hydraulic line 40 , without the check valve 70 , a pilot pressure to pressurize the cylinders 10 . 20 over the hydraulic chambers 13 . 23 is missing, the check valve remains 70 as long as in a blocking position, such as a pressure in the first hydraulic line 30 between 4/4 valve 50 and check valve 70 is lower than a pressure between the check valve 70 and the cylinders 10 . 20 , or a pressure in the first hydraulic chambers 12 . 22 , The control 72 is not necessary for this.

Off at the hydraulic variant 2 with the control unit 1 and two check valves 70 . 75 the control process can be analogous to the variant 3 expire. In addition, however, is another control 74 provided, which is complementary to the control 72 between the first hydraulic line 30 and the check valve 75 acts. For the check valve 75 is the second hydraulic line 40 the controlling line. To supplement this control, the control switches 74 the check valve 75 in response to an overpressure in the first hydraulic line 30 , Next remains the check valve 75 in a locked position, as long as a pressure in the second hydraulic line 40 between 4/4 valve 50 and check valve 75 is lower than a pressure between the check valve 75 and the cylinders 10 . 20 or a pressure in the second hydraulic chambers 13 . 23 , At least one of the check valves 70 and 75 This is preferably designed as a ball seat valve, which opens only as a result of exceeding a minimum pressure.

The hydraulic unit 1 according to the variant of 2 and the hydraulic unit 1' according to the variant of 3 further comprise a pilot valve 80 for hydraulic control of the piston. The pilot valve 80 is over the electromagnet 56 driven. The pilot valve 80 serves as reinforcement in the control of the 4/4 valve 50 , The pilot valve 80 is over a line 81 with a filter to the supply line 240 and parallel to the 4/4 valve 50 connected. The electromagnet 56 can via the pilot valve 80 the working position of the slide, ie the 4/4 valve 50 to adjust. The slide position is determined by a duty cycle between a working voltage and a reverse voltage, ie in proportional behavior is the 4/4-valve 50 adjusted via the duty cycle of the voltage. The pilot valve 80 is about a spring 82 spring biased and includes a locking position 83 with return into a swamp 84 and a passage position 85 ,

Incidentally, the description may 2 also on the 3 z. B. with respect to the four hydraulic line sections 31 . 32 . 41 . 42 be transmitted. Works the pilot valve 80 not or is it in a locked position 83 so pushes the spring 55 of the valve 50 the piston in its locked position 51 ,

4 illustrates another hydraulic control 300 for a motor vehicle transmission, which comprises a further variant of a hydraulic system for a spoiler adjustment according to the invention. The hydraulic control 300 is for an exemplary transmission with a 3-way clutch unit (or a unit through which three different clutches can be controlled) and designed with an actuator unit with four actuators. The hydraulic control 300 further comprises a conditioning unit 200 ' for hydraulic fluid. The processing unit 200 ' delivers via a pump (not shown) connected to a hydraulic connector 203 connected hydraulic fluid from a sump 201 ' can suck. The pump supplies a pressure supply line 360 , To the pressure supply line 360 is a first strand 310 connected, divided into four equal sub-strands 320 . 320 ' . 320 '' . 320 ''' divides. Each sub-string 320 . 320 ' . 320 '' . 320 ''' includes a double chamber cylinder 321 to which a control valve 322 upstream. The strand 310 points in a supply line 312 before dividing into the partial strands 320 . 320 ' . 320 '' . 320 ''' a control valve 315 on. Next is a second strand 330 to the pressure supply line 360 connected, divided into three equal sub-strands 340 . 340 ' . 340 '' separates. Each sub-string 340 is analogous to the coupling strands 140 out 1 constructed and includes a clutch cylinder 341 , a control valve 342 with pressure control, a buffer 344 and a pressure sensor 345 , In a supply line 332 is a control valve 335 (in the sense of a cut-off valve) before separation into the strands 340 intended.

To the pressure supply line 360 is a supply line 240 ' connected to a hydraulic control unit 400 supplied, as it is based on a further variant of a hydraulic system for a spoiler adjustment according to the invention. The control unit 400 is in 5 illustrated in detail. Same or functionally similar components and components such as valves of the control unit 400 and the control unit 1 as previously described, are identified with the same reference numerals. This concerns in particular the 4/4 valve 50 ' , the hydraulic lines 30 and 40 with the check valve 70 and 75 as well as the cylinders 10 and 20 , Instead of controlling the 4/4 valve 50 by means of a pilot valve 80 is in the hydraulic variant of the control unit 400 a directly controlled electric 4/4 valve 50 ' intended. The 4/4 valve 50 ' has a directly electrically adjustable magnet 90 that is against the power of the spring 55 works and the working positions 51 . 52 . 53 and 54 of the 4/4 valve 50 ' established.

6 shows a further embodiment of a hydraulic control unit 500 , The control unit 500 is part of a transmission hydraulic circuit 100 ^I. The transmission hydraulic circuit 100 ^I is similar to the transmission hydraulic circuit 100 in numerous hydraulic sections or areas. The transmission hydraulic circuits 100 . 100 ^I can realize identical functions. Explanations of the transmission hydraulic circuit 100 thus can also be used as an explanation of the transmission hydraulic circuit 100 ^I understood and seen, unless differences are apparent from the schematic.

The transmission hydraulic circuit 100 ^I can be implemented particularly advantageous as a control housing with integrated oil or hydraulic channels. The transmission hydraulics 100 ^I have two pumps 510 . 512 , The pump 510 is a combustion engine driven pump. The pump 512 is an electric motor driven pump. It is particularly advantageous to provide two pumps, so depending on the hybrid operating mode of the vehicle in which the transmission hydraulics 100 ^I installed a pump 510 or the other pump 512 can be operated. If necessary, if particularly large amounts of oil are needed, both pumps 510 . 512 operated to z. B. to be able to replenish the oil distribution line within times such as 10 ms. The pumps 510 . 512 Obtain the hydraulic fluid oil from an oil sump 501 , Other oil tanks 510 ^I , 501 ^II are available as drains to individual valves with T-connection. The oil of the oil collecting tank 501 is through the filter 650 First filtered before it enters the single or respective pump 510 respectively. 512 entry. 6 shows a central filter 650 , In 1 is shown that in place of the central filter 650 also single filter before each pressure supply element, the pumps 210 . 212 can be connected upstream. An execution after 6 is more compact. An execution after 1 ensures an oil supply even in cases where one of the filters, eg. B. due to particles in the oil, should be clogged.

The transmission hydraulics 100 ^I after 6 is as a control plate 78 realized. Only the consumers like the hydraulic cylinders 640 . 640 ^I am with their leads outside the control panel 78 arranged. The transmission hydraulics 100 ^I thus represents the housing for the hydraulics. The consumers like the hydraulic cylinders 640 . 640 ^I are to the housing of the transmission hydraulics 100 ^I connected (eg via plug connector 76 ^IV or other transfer points such as tubes). The connectors 76 ^IV are realized as socket-plug systems. The socket is in the control plate 78 installed. About the cross section of the connector of the connector 76 ^IV can be the connector 76 ^{IV be designed} as throttles.

The control plate 78 or the transmission hydraulics 100 ^I has single strands 610 . 620 . 630 . 640 . 640 ^I on, each in consumer like the hydraulic cylinder 640 . 640 ^I end up. A first assembly 610 in a separate hydraulic train is used for the control of the switching elements of a sub-transmission. A second module, also in its own strand, is used to control the claw switching elements of a second sub-transmission. A third assembly 630 is an assembly for clutch control as a disconnect clutch of an optional aufschaltbaren electric motor. A fourth assembly 640 serves as a control route for coupling and uncoupling a clutch of a double clutch. One to the fourth module 640 identically constructed further fourth module 640 ^I serves as an actuator for the uncoupling or coupling of a partial transmission of a dual-clutch transmission via a clutch.

The control plate 78 has to the outside numerous first transfer points, in particular connectors 76 . 76 ^I , 76 ^II , 76 ^III , 76 ^IV and second transfer points, in particular connectors 77 . 77 ^I , 77 ^II , 77 ^III , 77 ^IV up. Some transfer points (connectors 76 . 76 ^IV , 77 . 77 ^IV ) are for the connection of actuators such as the cylinders 10 . 20 or the hydraulic cylinders 640 . 640 ^I determined. Some transfer points (connectors 76 ^II , 76 ^III , 77 ^II , 77 ^III ) serve as connection points between the pressure generators, the pumps 510 . 512 and the subsequent control unit located in the control panel 78 is installed. Other transfer points (connectors 76 ^I , 77 ^I ) are deliberately designed outlets to the outside to z. B. about to be cooled assemblies of the vehicle to flush with hydraulic fluid.

From the central oil supply line 540 getting their supply from the pumps 510 . 512 gets a strand, which is a hydraulic unit 500 for the control of the cylinders 10 . 20 a spoiler is. The cylinders 10 . 20 are at the control panel 78 via the transfer points (connector 76 . 77 ) connectable. About the hydraulic lines 30 . 40 passing through the transfer points 76 . 77 are guided, the hydraulic fluid in the chambers of the cylinder, depending on the position of the 4/4-valve 50 be in and out. The 4/4 valve 50 is a spring-loaded valve thanks to the spring 55 , The 4/4 valve 50 is a pilot operated valve due to the pilot valve 80 , The 4/4 valve 50 has four switch positions 52 . 53 . 53 ^I , 54 , The 4/4 valve 50 includes two working positions 52 . 54 , The working positions 52 . 54 supply the cylinders 10 . 20 in a reciprocal or mirror-image manner, ie, when changing from the first working position 52 in the second working position 54 are the previously pressurized chambers of the cylinder 10 . 20 to the tank open chambers. The relieved chambers of cylinders 10 . 20 be after a change from a working position 54 to the other working position 52 to (with pressure) acted upon working chambers. The 4/4 valve 50 has two blocking positions 53 . 53 ^I. The pilot valve 80 is a via an electromagnet 56 actuated hydraulic valve. The pilot valve 80 is through the integrated spring 82 equipped with a preferred position. The preferred position of the pilot valve 80 is the first position 83 which is a deflation position. In the bleed position, the hydraulic fluid from the control line to the 4/4 valve in the sump 84 reach. In addition, there is a second position 85 in which the pilot valve 80 the hydraulic fluid from the supply line 81 switches on the control side of the 4/4 valve. The hydraulic medium of the supply line 81 comes from the central supply line 540 ,

The connectors 76 . 77 are throttling points in the hydraulic lines 30 . 40 , The connectors 76 . 77 are the closest places in the hydraulic lines 30 . 40 designed. Through these throttles in the hydraulic lines 30 . 40 can the hydraulic pressure gradient to the cylinders 10 . 20 be set. Using the throttles of the connectors 76 . 77 is the response of the cylinders 10 . 20 certainly. Different mobilities in the cylinders 10 . 20 can use the connectors 76 . 77 be unified. A return flow through the connectors 76 . 77 can be delayed by the throttling effect.

Will the 1 with the 6 As one skilled in the art will appreciate, instead of performing separate check valves such as check valves 70 . 75 (please refer 2 ) an integration of the controlling hydraulic elements in the connector 76 . 77 is also possible. Depending on the requirements of the hydraulic behavior of the cylinders 10 . 20 due to the pressure in the central pressure supply line 540 can the connectors 76 . 77 as throttles and / or as non-return valves such as check valves 70 . 75 be designed.

In a particularly simple variant, the respective swamps, such as the swamp 201 for the entire hydraulic system or the oil collecting tanks 501 . 501 ^I and the swamps 60 . 84 for the individual valve outlets, combined into a single overall sump.

Such as the control process described above is particularly helpful in a spoiler, which shows by its attachment and / or position an aerodynamic force effect in the direction of a home or rest position of the spoiler on the vehicle. The aerodynamic force effect on the spoiler depends on the speed of the vehicle and thus on the output speed of the vehicle driving gearbox. On the effects of the aerodynamic force on the pressure in the hydraulic chambers of the cylinder the spoiler adjustment can be done via the check valve 70 and possibly also the check valve 75 be specifically influenced to keep the spoiler in any driving situation in a desired location. Further, such a control process is advantageous in a spoiler having a permanent dead weight inclination in each of its extended positions. In any case, the use of a check valve or the check valves, the controlled position or position of the spoiler can be held, even if the hydraulic fluid supply from the transmission hydraulics fails or becomes faulty.

LIST OF REFERENCE NUMBERS

1, 1 ', 400

Hydraulic control unit

10

cylinder

11

piston

12

first hydraulic chamber

13

second hydraulic chamber

20

cylinder

21

piston

22

first hydraulic chamber

23

second hydraulic chamber

30

first hydraulic line

31

first line section

32

second line section

40

second hydraulic line

41

third line section

42

fourth line section

50, 50 '

4/4-valve

51

depressurisation

52

first job

53, 53 ^I

blocking position

54

second job

55

feather

56

electromagnet

60

swamp

70

check valve

72

control

74

control

75

check valve

76, 76 ^I , 76 ^II , 76 ^III , 76 ^IV

first transfer points, in particular connectors, z. B. with integrated throttle

77, 77 ^I , 77 ^II , 77 ^III , 77 ^IV

second transfer points, in particular connectors, z. B. with integrated throttle

78

Control plate, in particular limit of the control plate

80

pilot valve

81

supply

82

feather

83

first position

84

swamp

85

second position

90

magnet

100, 100 ^I

Transmission hydraulic control, abbreviated hydraulic control, z. B. in the form of a hydraulic control housing

110

first strand, in particular a first actuator, preferably a socket selection valve

111, 111 '

Dual-chamber cylinder

112, 112 '

control valve

113

supply

115

control valve

120

second strand, in particular a second actuator, in particular a socket selection valve

121, 121 '

Dual-chamber cylinder

122, 122 '

control valve

123

supply

125

control valve

130

third strand, in particular for controlling the hybrid clutch

131

clutch cylinder

132

control valve

133

supply

140

fourth strand, in particular for controlling the double clutch

141, 141 '

clutch cylinder

142, 142 '

control valve

143

supply

144, 144 '

cache

145, 145 '

pressure sensor

146, 146 '

detour

147

switching valve

150

fifth strand, in particular for controlling the differential unit or the differential gear

151

clutch cylinder

152

control valve

153

supply

154

cache

155

pressure sensor

160

Pressure supply line

200, 200 '

conditioning unit

201, 201 '

Hydraulic sump

203

Plug connection, hydraulic plug connection

210

pump

212

pump

220

pumping line

222

pumping line

224

connecting portion

230

Valve

232

Valve

240, 240 '

supply

300

hydraulic control

310

first strand, in particular the actuator unit

312

supply

315

control valve

320, 320 ', 320' ', 320' ''

Sub-string, in particular first, second, third and fourth sub-string

321

Dual-chamber cylinder

322

control valve

330

second strand, in particular the triple clutch or the triple clutch group

332

supply

335

control valve

340, 340 ', 340' '

Substrand, in particular first, second and third sub-strand

341

clutch cylinder

342

control valve

344

Storage

345

pressure sensor

360

Pressure supply line

500

hydraulic unit, in particular for control

501, 501 ^I , 501 ^II

Oil reservoir

510

first pump, in particular internal combustion engine driven pump

512

second pump, in particular an electric motor driven pump

540

Oil distribution line, in particular central oil supply line

610

first assembly, especially in its own strand

620

second assembly, especially in its own strand

630

third assembly, especially in its own strand

640, 640 ^I

fourth assembly, in particular hydraulically severable

641, 641 ^I

hydraulic consumer, in particular hydraulic cylinder

650

Central filter or main filter

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 5509383 A [0004]
• EP 1138582 A2 [0005, 0006]
• EP 1138582 A1 [0005]
• WO 2008/110620 A1 [0006, 0006, 0007, 0007]
• DE 102005010638 A1 [0007, 0007]
• DE 102006021939 A1 [0007]
• DE 8806109 U1 [0008]
• DE 10347203 A1 [0009]

Claims (14)

Spoiler adjustment with at least two linear cylinders or differential cylinders with hydraulic chambers ( 12 . 13 . 22 . 23 ), each of which has a hydraulically clamped piston ( 21 ) with a spoiler connector, characterized in that a common 4/4 valve ( 50 . 50 ' ) for activation ( 72 . 74 ) of the parallel interconnected linear or differential cylinder is connected upstream of these, wherein the differential cylinder or linear cylinder via at least two, in particular a first and a second, for the differential cylinder or linear cylinder jointly guided hydraulic lines ( 30 . 40 ) are connected. Spoiler adjustment according to claim 1, characterized in that in at least the first hydraulic line ( 30 ) to the differential cylinders or to the linear cylinders a check valve ( 70 . 75 ), in particular a spring-biased check valve, is present. Spoiler adjustment according to claim 2, characterized in that both hydraulic lines ( 30 . 40 ) downstream of the 4/4 valve ( 50 . 50 ' ) with a check valve ( 70 . 75 ), which is an outflow of a hydraulic fluid from an associated hydraulic chamber ( 12 . 13 . 22 . 23 ) locks the linear cylinder or the differential cylinder in a control position. Spoiler adjustment according to one of claims 2 to 3, characterized in that the check valves ( 70 . 75 ) in response to an overpressure in one of the hydraulic lines ( 30 . 40 ), which has a hydraulic line other than that ( 30 . 40 ) is in an open position. Spoiler adjustment according to one of claims 2 to 4, characterized in that the at least one check valve ( 70 . 75 ) at a missing pilot pressure from one of the further hydraulic lines ( 30 . 40 ), in particular the second hydraulic line ( 40 ), as long as in a locked position ( 53 . 53 ^I ), as long as a pressure in front of the check valve ( 70 . 75 ), in particular in a line section ( 31 . 32 . 41 . 42 ) between 4/4 valve ( 50 . 50 ' ) and check valve ( 70 . 75 ), is lower than a pressure downstream of the check valve ( 70 . 75 ), in particular in comparison with a line section ( 31 . 32 . 41 . 42 ) to its associated hydraulic chamber ( 12 . 13 . 22 . 23 ). Spoiler adjustment according to one of the preceding claims 2 to 5, characterized in that at least one of the check valves ( 70 . 75 ) is a ball seat valve, which opens only as a result of exceeding a minimum pressure. Spoiler adjustment according to one of the preceding claims, characterized in that a spoiler, which is connected to the spoiler connector, a spoiler, by its attachment and / or position an aerodynamic force action in the direction of a home or rest position of the spoiler and / or a has permanent own weight loss inclination in each of its extended positions. Spoiler adjustment according to one of the preceding claims, characterized in that the spoiler adjustment has as supply source a pressure line of a hydraulic transmission control. Spoiler adjustment according to one of the preceding claims, characterized in that the jointly guided hydraulic lines are fanned out at the points at which to the hydraulic chambers ( 12 . 13 . 22 . 23 ) Line sections ( 31 . 32 . 41 . 42 ) are brought together with the same hydraulic behavior. Spoiler adjustment according to one of the preceding claims, characterized in that the 4/4-valve ( 50 . 50 ' ) in a rest position, preferably by a spring tension on the piston ( 21 ), ensures depressurization or decoupling of the hydraulic circuits. Spoiler adjustment according to one of the preceding claims, characterized in that one of the positions of the 4/4 valve, which is preferably a proportional directional valve, a first working position ( 52 ) for pressurizing similar hydraulic chambers ( 12 . 13 . 22 . 23 ) is the differential cylinder or the linear cylinder, another position of the 4/4 valve ( 50 . 50 ' ) a second job ( 54 ) for pressurizing similar hydraulic chambers of the differential cylinder or linear cylinder, wherein in the second working position ( 54 ) pressurizable hydraulic chambers ( 12 . 13 . 22 . 23 ) mirror-inverted hydraulic chambers ( 12 . 13 . 22 . 23 ) to the pressurized hydraulic chambers ( 12 . 13 . 22 . 23 ) in the first employment position ( 52 ), and between the first job ( 52 ) and the second job ( 54 ) a complete blocking position ( 53 . 53 ^I ), in which a slide in the, preferably cartridge-type, 4/4-valve ( 50 . 50 ' ) all ports of the 4/4 valve ( 50 . 50 ' ) interrupts. Spoiler adjustment according to one of the preceding claims, characterized in that a pressure for the spoiler adjustment from at least one of two existing hydraulic pumps is available. Spoiler adjustment according to one of the preceding claims, characterized in that a Electromagnet ( 56 ), either directly or indirectly via a pilot valve ( 80 ) by a Tastungsverhältnis a slide position of the 4/4-valve ( 50 . 50 ' ). Spoiler adjustment according to one of the preceding claims, characterized in that the spoiler adjustment in response to an output speed from a transmission whose hydraulic control comprises as part of the spoiler adjustment, is adjustable.

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