WO2019020806A1

WO2019020806A1 - Hydraulic device, in particular hydraulic valve or hydraulic controller

Info

Publication number: WO2019020806A1
Application number: PCT/EP2018/070465
Authority: WO
Inventors: Patrick Wohlhauser; Van No Lanevongsa; Lennard GEISSLER
Original assignee: Liebherr Machines Bulle Sa
Priority date: 2017-07-27
Filing date: 2018-07-27
Publication date: 2019-01-31
Also published as: CH714022A1

Abstract

The present invention relates to a hydraulic device, in particular a hydraulic valve or hydraulic controller, comprising a housing (14), at least one plunger (17) which is axially movably mounted in a housing bore, and at least one compression spring (18) acting upon the plunger. The invention is characterized in that a plug (20) is inserted directly into the housing bore, the position of which influences the bias of at least one compression spring (18), and at the same time said plug forms a closure system for sealing the spring chamber which contains at least one compression spring.

Description

Hydraulic device, in particular hydraulic valve or hydraulic regulator

The invention relates to a hydraulic device, in particular a hydraulic valve or a hydraulic controller, with a housing, a piston axially displaceably mounted in a housing bore and at least one pressure spring acting on it.

In the following explanation, in the text passages in which the disclosure of the invention relates to the application of the invention features to hydraulic regulators, the term control piston commonly used in this environment is used instead of the generalized term piston. In the text passages in which the disclosure of the invention relates to the application of the invention features to hydraulic valves, the term spool common in this field is used instead of the generalized term piston. In the general text parts, the term piston is continued.

The invention features can be applied to all different types of hydraulic controllers z. As pressure regulator, power regulator, volumetric flow controller, etc. and on all different types of hydraulic valves z. B. Pressure relief valves, proportional valves, etc. To clarify the general applicability of the invention features should be emphasized the content already contained in the previous sentence that the invention features applicable to hydraulic regulators and hydraulic valves, regardless of whether the hydraulic device has additional control inputs or not. The term control input is to be understood here as an additional possibility of intervention, to impart a further force to the piston, which is axially displaceably mounted in a housing bore. This could be z. Example, be an additional oil connection to another control surface of the piston, an actuator (eg., A proportional solenoid) with the same force can be exerted on the piston, etc.

A pressure regulator may be used to operate a hydraulic displacement unit, for example a hydraulic pump. If the pressure regulator has an additional control input, the oil pressure present at the high-pressure outlet of the hydraulic pump can be regulated to a certain level as a function of the control signal supplied thereto; of course, provided that sufficient hydraulic power can be supplied to the hydraulic pump. The pressure level must exceed a minimum value in order to maintain an oil leak required for self-lubrication of the hydraulic pump or hydraulic system. At the same time, the pressure level at the high-pressure outlet of the hydraulic pump must be limited to an upper value in order to avoid its overload or that of the components of the hydraulic system. This compliance with a two-sided limitation of the pressure range - often referred to as two-sided pressure cut-off - is also required for a hydraulic motor operating in pump mode. In practice, this mode is, for example, in the braking operation of a hydraulic traction drive or when discharging a load from a operated by a hydraulic motor winch.

By changing the bias of the compression spring via an externally accessible screw can be set in relation to the example pressure-controlled hydraulic pump, the lower and upper limit pressure. A pressure control is then possible within the bandwidth between these limit pressures. Provided that enough mechanical power can be supplied to the hydraulic pump, the pressure level at the high pressure outlet of the hydraulic pump does not drop below the lower limit pressure. Exceeding the upper limit pressure is not possible.

FIG. 1 shows a longitudinal section of a regulator axis equipped with the components using the example of a regulator main stage. The left part of this figure, starting at the arranged between the control piston 1 and coil spring 2 spring plate 3a, shows a known from the prior art mechanism for adjusting the spring preload. The design is based on a multipart, introduced into the controller housing 4 adjustment system consisting of the Einstellschraubenführungshülse 5 and the actual screw 6 to change the bias of the coil spring 2. In the embodiment shown, the screwed into the regulator housing 4 Einstellschraubenführungshülse 5 is a lining of the spring chamber 9 The right-side collar of the adjusting screw guide sleeve 5 forms the end stop of the spring plate 3a and thus also acts as an end stop of the control piston 1. Since the position of this covenant is independent of the screwing depth of the adjusting screw 6, this results in a final fixed minimum value of the lower pressure cut-off. The left portion of the screw 6 is guided via a threaded connection to the adjusting screw guide sleeve 5 to the outside. This allows the setting of different biases of the coil spring 2 and thus the specification of a certain, but within a certain range freely adjustable pressure cut.

In order to prevent the automatic adjustment, the set position of the adjusting screw 6 is fixed by means of a lock nut 8. However, the fixing by means of the lock nut 8 always leads to an unavoidable slight change in position of the adjusting screw 6 and thereby to an influence on the bias and thus the actual pressure cut. This error can be compensated only by a deliberately deviating to the desired position adjustment of the adjusting screw 6, which then in the ideal case by the subsequent fixation of Kontermut- ter 8 caused adjustment has been compensated. With this approach, with a little bit of patience and practice, you can achieve a sufficiently accurate pressure cutoff setting on a main controller. In contrast, accurately setting a load sensing pressure value on a load-sensing controller using the design presented is quite tedious and yet imprecise.

The object of the present invention is to provide a simplified and particularly cost-effective solution for the adjustment system.

This object is achieved by a hydraulic device according to the features of claim 1. Advantageous embodiments of the device are the subject of the dependent claims.

The device may be a hydraulic valve or a hydraulic regulator. In this case, a plurality of valve elements or regulator axes can be accommodated in a common housing. As a valve element is understood here the arrangement of a control slide with compression spring, a regulator axis comprises a control piston and at least one compression spring. In such hydraulic devices in the housing a plurality of valve elements / controller axes are installed, the sealing plugs of the valve elements / controller axes do not necessarily have to be identical, but may instead differ from each other in one or more features, be it a combination of different inventive embodiments or be it one Combination of inventive embodiments with designs already in accordance with the prior art, for. B. a twin housing, which houses a novel load-sensing controller and a state of the art stage for pressure cut.

For such provided with a pressure port spring chambers of the inventive approach allows a much simpler and cheaper construction the hydraulic device, with the addition of the above-discussed problems is bypassed.

The inventive hydraulic device according to claim 1 provides for a stopper instead of a one-piece adjusting screw plug. The sealing plug performs a sealing function to prevent such hydraulic oil passing in the spring chamber of the hydraulic component from coming out of the housing of the hydraulic device. Accordingly, the stopper must be equipped with a sealing system.

This can preferably be done by a corresponding annular recess on the lateral surface of the sealing plug and the local installation of an O-ring or a resting on a support ring O-ring. In contrast to a structure of the hydraulic device, which includes a one-piece adjusting screw, there is no threaded connection for a construction using a sealing plug between this and the housing bore.

The sealing plug is preferably fixed with a component axially in the housing bore. One possible embodiment of this fixation, referred to below as Variant 1, can be achieved by providing an inner radial groove in the housing bore. This inner radial groove is preferably located on the side facing away from the spring chamber side of the housing bore and precisely at that position, which connects directly to the region of the housing bore, which is filled by the sealing plug. At least one shaft securing ring can be inserted into this inner radial groove. When installing the sealing plug into the housing bore, the plug can be pushed further than in its intended end position in the direction of the spring chamber by a corresponding tool. Then, the shaft securing ring can be inserted into the said radial inner groove. If the said tool is discontinued, the end of the sealing plug is replaced by the restoring force of the pressure spring. pressed against the shaft retaining ring. This is a clear axial position of the assembled sealing plug.

The sealing plug may include the spring plate.

The use of the sealing plug allows a change in the bias of the compression spring only by component changes (e.g., replacement or addition or removal of components). For example. different, adapted to the respective required bias of the compression spring plugs are used, of which each desired bias of the appropriate plug is used. The adjustment can be made via the Bauteilabmass between the bearing surface to the shaft locking ring and the bearing surface of the compression spring. Advantageously, this is done by the production of identical blanking blanks with a corresponding excess. The required for individual adjustment Bauteilabmass is created in a post.

In all alternatives described below, the finished closure plug can be made as a common part, because the individually required bias of the compression spring is achieved by other measures. It can be used, for example, by their different length adapted compression springs, the spring constant (spring rate) must have the same value in all cases. Alternatively, it is conceivable to use spring plates with different, adapted plate thickness. This may be a spring plate, which is arranged between the piston and compression spring. Alternatively, a separate spring plate could be applied to the stopper, the plate thickness is measured depending on the required bias. Particularly preferred is the arrangement of a releasably attached to the stopper spring plate, so that, depending on the needs of a suitable spring plate with the appropriate strength for the desired bias is selected. Alternatively, an adapted piston could also be used. In this case, the section of the piston lying to the spring chamber could be beyond the functional range of a control chamber of the device (for example, beyond an annular recess of the piston to provide the required oil connections between different stages within the hydraulic device (eg between a pre-and main stage of a piston) two-stage hydraulic controller) as well as to provide the required oil connections to the outer terminals of the device serve) have different lengths, which are significant for the bias of the compression spring.

In a preferred embodiment, one or more washers may be placed between the compression spring and one of its bearing surfaces or on both bearing surfaces to achieve the required preload of the compression spring. It may be the bearing surface of that spring plate, which is located at the end facing the piston or the spring plate on the side of the sealing plug, which may be formed as mentioned as a separate component or by an extension of the sealing plug. To achieve a specific preload, a single washer that fits exactly in its thickness can be used, or several washers that fit the full thickness can be used. Alternatively or additionally, washers fitted in their thickness can be installed between the shaft securing ring and the end of the sealing plug.

In an advantageous embodiment, both bearing surfaces for the compression spring made of a cured material by curing the entire component or a hardening of the relevant surface areas or a suitable coating of the entire component or a suitable coating of the relevant surface areas.

In a particularly advantageous embodiment, one or both of these hardened contact surfaces of the compression spring is replaced by the use of hardened substrates. shown washers. This has the advantage that for the more complex components materials with a much lower hardness can be used.

In the preferred embodiment, two hardened washers of a standard size are used as contact surfaces of the pressure spring and the adjustment of the concretely required preload of the pressure spring is achieved by the use of additional matched in their thickness disc washers. Advantageously, these matched washers are inserted between the shaft securing ring and the sealing plug. In this construction, the dimension over which the bias of the compression spring can be varied in the intended adjustment can be measured directly from the outside without having to remove the hydraulic device. Similarly, for a change in the bias of the compression spring, the hydraulic device must not be removed.

Instead of using an inner radial groove for the shaft securing ring can according to an alternative embodiment of the invention, hereinafter referred to as variant 2, the closure plug within its outer surface have an outer radial groove into which a shaft retaining ring is inserted. During installation, the shaft retaining ring is first inserted into the outer radial groove before the sealing plug is inserted into the housing bore.

The dimensions of the outer radial groove and the shaft retaining ring are designed so that the sealing plug can be inserted with attached shaft locking ring in the housing bore. This concerns, inter alia, the coordinated dimensions of the groove and those of the relaxed shaft securing ring and the width to which the corrugated locking ring can be compressed as intended. In a coordinated position, the housing bore has a dedicated annular recess, the dimensions of which are again designed such that as soon as the mounted on the outer radial groove of the sealing plug shaft securing ring reaches the annular recess engages in the same and remains in this position. With the exception of the use of washers in the housing bore outside the area closed by the sealing plug, all of the aforementioned possibilities can also be used for the variant 2 for preparation, so that when inserting the sealing plug into the locking position there is the required bias of the compression spring. Accordingly, in an advantageous embodiment, the bearing surfaces of the compression spring can be performed by hardened washers of a standard size and the adjustment of the bias of the compression spring within the adjustment can be achieved by the use of washers in matching thickness, so that the complex components regardless of the required bias of the compression spring Common parts can be performed.

In variant 2, the plug can obviously not be removed after its installation in the hydraulic device. This has the advantage that an unauthorized opening of the hydraulic device or the improper adjustment of the bias of the compression spring can be avoided per se. But it is clear that a proper subsequent adjustment of the bias of the compression spring resp. a subsequent adjustment of the hydraulic device impossible.

In a further advantageous embodiment of the hydraulic device, hereinafter referred to as variant 3, the closure stop near the end facing the spring chamber within its lateral surface on an outer radial groove into which a shaft securing ring is placed prior to assembly. The dimensions of this outer radial groove and the shaft retaining ring are designed so that the sealing plug can be inserted into the housing bore in the attached and thereby intentionally compressed shaft locking ring.

When appropriately dimensioned dimensioned the shaft securing ring when passing through a narrowing portion of the housing bore, the preferably designed conical, further compressed and can finally dip into the spring chamber. In the interior of the spring chamber or at least in a first section, the housing bore has a larger inner diameter, so that the shaft securing ring can widen again. Preferably, this inner diameter is correspondingly large, that the shaft securing ring widens to the diameter at which there is no longer any mechanical stress, ie assumes the diameter that has the shaft securing ring as a loose unobstructed component. There is a sudden change in the inner diameter between the end region of the narrowing section of the housing bore and the spring chamber which is in focus at the instantaneous examination. By this measure it is achieved that the sealing plug can not be removed as soon as the shaft securing ring is completely immersed in the spring chamber.

In the described advantageous variant 4 of the hydraulic device, the housing bore between the region in which there is the constriction of its inner diameter, which causes the desired compression of the mounted shaft securing ring during assembly of the sealing plug, and the spring chamber on an inner radial groove. Once the shaft lock ring is completely immersed in said inner radial groove, the plug can not be removed.

In addition, it may be provided that the housing of the hydraulic device is provided with at least one protective cap, which is releasably fixable to the housing for covering the at least one sealing plug. The attachment of the cap can be done by means of one or more pronounced on the cap claws. These claws hold in complementary recesses of the housing, so that there is a positive connection between the cap and housing. It is particularly advantageous if the claws or other components of the protective cap are provided with corresponding predetermined breaking points, so that the protective cap can not be detached from the housing in a non-destructive manner. This ensures that a change in the bias of or the spring elements immediately by the absence or the defective cap is visible. It is also possible to equip the system with different protective caps, for example differently colored protective caps. About the optical design of the cap can then be signaled when or by whom a corresponding change in the bias of the piston spring was made. In hydraulic devices with multiple valve elements or multiple controller axes within a common housing, the cap can cover a plurality of plugs.

The invention also relates to the inventive use of the hydraulic device according to the invention in the embodiment with sealing plug for pressure cut in a hydraulic system, in particular for Druckabschnei- tion during operation of an axial piston pump or an axial piston motor.

Also conceivable is the use of the hydraulic device in the embodiment with sealing plug as a pressure limiting valve for limiting the maximum pressure level within a hydraulic system.

Furthermore, the present invention relates to a hydraulic system comprising at least one axial piston motor or at least one axial piston pump and at least one hydraulic device designed in the embodiment with sealing plug as a hydraulic controller according to the present invention, which is connected to an axial piston pump or an axial piston motor for pressure cut. Accordingly, the advantages and properties of the hydraulic device according to the invention also apply without restriction to the hydraulic system or the inventive use of the device, which is why a repeated description is omitted here.

Furthermore, the present invention relates to a hydraulic system comprising at least one hydraulic device in the embodiment with sealing plug in the form of a hydraulic valve according to the present invention. For example. will that Hydraulic valve used to limit the pressure of the system pressure within the hydraulic system.

Further advantages and features of the invention will be explained in more detail below with reference to an embodiment shown in the figures. Show it:

FIG. 1 shows a conventional main stage of a multistage hydraulic regulator,

Figure 2 is a sectional view of a hydraulic device in the form of a two-stage hydraulic controller, each stage is equipped with a set screw plug

FIG. 3 shows a detailed view of the hydraulic regulator of FIG. 2,

FIG. 4 is a perspective sectional view of the hydraulic regulator according to FIG. 2,

FIG. 5 shows a further detailed view of the hydraulic regulator according to FIG. 2,

6 shows a detail view in section of a hydraulic device according to a second variant,

FIG. 7: representations of the adjusting screw plug according to FIG. 6 during different phases during assembly into the hydraulic device;

FIG. 8 shows a detail view in section of a hydraulic device according to a third variant,

9 shows a detail view in section of a hydraulic device according to a fourth variant, FIG. 10 shows a perspective view of a hydraulic regulator according to FIG. 2 with mounted protective cap,

Figure 1 1: detailed views of the cap and

Figure 12: a sectional view of the protective cap and the hydraulic controller with mounted protective cap.

A possible variant of a hydraulic device will be presented below with reference to FIGS 2 to 5, which is a hydraulic controller with a load-sensing controller I and a pressure cut II, which are located in a common housing 14. The explanation of this variant is based on the assumption that the hydraulic controller is used to actuate the actuator of a hydraulic pump. The hydraulic regulator has four external connections 10, 1 1, 12, 13 to provide oil connections, namely the connection 10 to the high-pressure outlet of the hydraulic pump to be controlled, the connection 1 1 to the tank return, a connection 12 to the adjusting device of the hydraulic pump and a connection 13 for the Supply of external control pressure. The load-sensing controller I and the pressure cut-off II are connected to each other via a common bore 15, which is sealed to the outside.

Both controller axes, ie those of the load-sensing controller I and the pressure cut-off II, are equipped with the following components from right to left in relation to the arrangements selected in FIG. A closure system 16, which is oil-tight even at the maximum possible pressure level in the high-pressure bore 10a. A control piston 17, with two corresponding sections existing annular recesses along its lateral surface (not shown in Figure 2), so that depending on the longitudinal position of the control piston 17, the required oil connections both within the controller and to the outer connections 10-13 are present. A compression spring 18 with a support system 19 of the Piston end. (The support system 19 may, for example, as a spring plate and the compression spring 18 may, for example, be designed as a helical spring.) Alternatively, a compression spring-pad system can be constructed by a juxtaposition of disc springs.)

An adjusting screw 20 for biasing the compression spring 18 with serving as a spring plate extension. A closure system which must be sealing up to the maximum possible oil pressure level in the spring chamber 18a. According to this variant, the closure is formed by the adjusting screw 20, i. the adjusting and locking screw 20 is in one piece.

It is an advantageous limitation of the possible adjustment range of the minimum and maximum bias of the compression spring 18 and thus provides an advantageous limitation of the possible adjustment of the pressure cut for the connected hydraulic pump. In most applications of a hydraulic controller, the highest pressure levels can occur at the maximum possible bias of the compression spring 18 at the high pressure outlet of the hydraulic pump. The maximum possible value of this pressure level is lower at a weaker bias of the compression spring 18. A use of the regulator, in which a reverse relationship between the bias of the compression spring 18 and the pressure level, which is present at the high pressure outlet 10 of the hydraulic pump, is possible, but will not be considered in the following text.

Stop for limiting the minimum bias of the compression spring 18th

In the spring chamber 18a of the load-sensing regulator I, the screw connection between the regulator housing 14 and the adjusting screw 20 must be sealing against the maximum possible via the terminal 13 supplied pressure level of the control pressure, which may be in practice at some 10 bar , In the serving as a sealing element O-ring 22 groove 21 in the adjusting screw 20 is a support ring 23 is placed (see. Detail view of Figure 4). At a correspondingly high control pressure, the O-ring 22 is pressed against the support ring 23, whereby the load-sensing controller I remains pressure-tight. In the pressure cut II, the O-ring 22 can also be combined with a support ring 23 to maintain a common part strategy. Here is sufficient for sealing the sole use of an O-ring 22 on the adjusting screw 20, because there is always low pressure in the thus sealed volume. Either consists of this volume 18b a sole oil connection to the tank return via the port 12 or in this volume 18b is only a slight overpressure of about 1 to 2 bar before, and then if, due to the position of the control piston 17, a reflux of hydraulic oil from the port 12 of the adjusting device (ie from the actuating cylinder) coming into the tank return.

Through the use of a load-sensing controller I, a so-called demand flow control of the hydraulic pump is achieved. By such a regulation is avoided under the objective of saving energy that the hydraulic pump in those operating phases builds up an unnecessarily high pressure level in the hydraulic oil circuit in which the hydraulic consumers require only small volume flows of hydraulic oil. In terms of energy efficiency, setting the lowest possible load-sensing pressure is beneficial. However, operation in the low pressure range where the control does not operate reliably (below about 10 bar) must be avoided. Therefore, a load-sensing controller has an end stop position beyond which no further lowering of the load-sensing pressure is possible, the so-called pmin stop. In certain applications, such as winch drives, there must be some pressure reserve, which is why the load-sensing pressure is set to a few tens of bars (up to 60 bar). So that in this case the setting is avoided to an unnecessarily high value, you can also equip the load-sensing controller I with a pmax stop. It makes sense to adjust the load sensing pressure setting to suit the needs of the hydraulic system and the application.

By using a pressure cut-off II for controlling a hydraulic pump, the setting range for the maximum possible at its high-pressure outlet Pressure level limited, which serves to avoid overloading of the hydraulic system including the hydraulic pump itself. In contrast to a pressure limiting valve, which dissipates the excess power via a bypass and thus ultimately converts a part of the provided by the hydraulic pump hydraulic power in the heating of hydraulic oil acts a pressure cut on the actuator of the hydraulic pump such that the so-called cut-off not can be exceeded. The need for a pmax stop for a press cut is certainly self-explanatory. If the pressure levels are too low, stable control is not possible. In addition, cut-off pressure set at a very low pressure level would prevent the leakage required for lubrication. For the reasons mentioned, a pm in impact is also useful for a pressure cut.

In the variant of the mounted regulator shown in FIG. 2, the narrow end of the adjusting screw 20 projects axially into the helical spring 18. In its continuation, the adjusting screw 20 has a larger diameter. At a certain length of the adjusting screw 20 is a particularly significant increase in their outer diameter before. There is a surface which is aligned perpendicular to the imaginary axis of the adjusting screw 20, on which this is supported on the coil spring designed as a compression spring 18 (see Figure 2). This support surface may also be conical or curved (convex or concave). Instead of a coil spring 18 and the use of another spring element, such as a juxtaposition of individual disc springs is possible.

In an optional variant, the adjusting screw 20 is not supported directly on the compression spring 18, but via a washer joined therebetween. In this case, a hardened washer is particularly preferably used. Generally, a coil spring 18 will scrape at its bearing surface during use and could lead to material wear over its useful life. In any case, chip formation must be avoided as abrasive material would enter the oil circuit and cause consequential damage. Therefore, the support surface must be hardened. The design of a fully or partially hardened setscrew 20 is of course much more expensive than the use of a hardened washer.

The lengths along which the adjusting screw 20 is close to the inner surface of their receiving bore in the controller housing 14, designed as follows: Adjacent to the existing for accommodating said sealing element groove 21 is in each case a longitudinal section of the adjusting screw 20, in which the outer diameter has almost the same dimension of the opposite inner diameter of the housing bore in the regulator housing 14. In the end region of the adjusting screw 20, where the largest diameter is present, there is an external thread 24. The opposite region of the housing bore in the controller housing 14 has a matching internal thread, from the later described radial groove 25 in the axial direction to a section ranges from which the diameter of the housing bore tapers steadily. In the variant according to FIGS. 2 to 5, the number of threads within the housing bore is greater than that of the adjusting screw 20, but this is not absolutely necessary. With respect to this threaded connection, such a coordination between the adjusting screw 20 and its housing bore in the regulator housing 14 is required, which allows the setting of different spring preloads, which include the adjustment range of the low bias of the compression spring.

In a further variant, the adjusting screw plug 20 is completely within the controller housing 14 over its entire operating range and, after insertion of the adjusting screw 20 into its installed position during assembly of the controller, a designated securing mechanism is mounted, which prevents the actuator -Verschlussschraube 20 can be removed by turning it alone. In the variant shown, this can be done by a radial groove 25, which along the portion of the housing bore, which is located outside the installation space of the adjusting screw 20, in the Wall of the housing bore of the controller housing 14 is incorporated. A shaft securing ring 26 (see FIG. 4) can be introduced into this radial groove 25. Clearly, the complete unscrewing the adjusting screw 20 is only possible by previous removal of the shaft securing ring 26. Without removal of the shaft lock ring 26 this forms when unscrewing the adjusting screw 20 a stop or an end position.

Ideally, the radial groove 25 and thus the shaft securing ring 26 is located exactly at that position, so that in the presence of the end position, at which the head of the adjusting screw 20 abuts against the shaft securing ring 26, the minimum allowable bias of the compression spring 18 results , With this setting, the set cut-off pressure is at the still permissible minimum value. By configuring the position of the shaft securing ring 26 or its bearing surface facing the interior of the regulator housing 14, the distance along the adjusting screw 20 between the support surface to the shaft lock ring 26 to the support surface of the compression spring 18, the spring length of the relaxed compression spring 18, her Spring hardness, the thickness of the spring plate 19 and the piston end position of the spring plate 19 results in a minimum value of the bias of the compression spring 18th

In a further variant, the two bearing surfaces on which the compression spring 18 is supported particularly wear-resistant z. B. by curing or coating the one-piece locking screw 20 or the spring plate 19 or both parts. In an alternative variant, instead of an extension on the one-piece adjusting screw 20, a separate spring plate is present. In one possible variant, only the bearing surfaces on which the compression spring 18 is supported are hardened or coated. In one variant, the said more complex components are not hardened or coated, but the bearing surfaces on which the compression spring 18 is supported, are represented by put on hardened washers. In another variant are hardened washers in standard dimensions. If, starting from a specific controller configuration, a change is to be made in such a way that the lowest possible setting value of the minimum spring preload is to be raised and the setting value of the maximum possible preload remains unchanged, then bsw. a locking screw 20 are used with a longer screw head or a locking screw at the head end is an extension. Alternatively, the provided for receiving the shaft locking ring in the housing bore radial inner groove at a greater depth, that is introduced closer to the spring chamber. Under this objective, a washer or a stack of several washers with an adjusted total thickness is preferably inserted between the adjusting screw plug 20 and the shaft securing ring 26. At the place of installation no hardened washers are required; Rather, this is also a plastic version possible.

If a change is to be made on the basis of a specific controller configuration in such a way that the lowest possible setting value of the minimum spring preload is to be lowered and the setting value of the maximum possible preload remains unchanged, the opposite steps can be taken; a shortening of the screw head of the adjusting screw 20, if enough threads are available or a reduction in the length of existing on the screw head extension. Alternatively, the provided for receiving the shaft securing ring in the housing bore radial inner groove can be introduced at a smaller depth. If a stack of at least one washer is present between the adjusting screw 20 and the shaft securing ring 26, its overall thickness can be reduced.

If a change in the bandwidth between the lowest possible and the highest adjustable spring preload is required on the basis of a specific controller configuration without post-processing of the controller housing, different conversions also exist here. Since the shift of this bandwidth to lower spring preloads in each case contrary measures As for increasing this bandwidth, the explanations are limited to the latter. A stronger preload and higher restoring force is achieved by using a longer spring with the same spring rate. Alternatively, such a change would be possible by means of such a conversion, which leads to a located at a small distance from the adjusting screw 20 end position of the spring plate 19 (a piston 17, with respect to its hydraulic control function at the same setting position further into the spring chamber 18a inside is sufficient or the use of a spring plate 19 with a correspondingly thicker edge thickness, etc.).

As a further alternative, a locking screw could be used, whose longitudinal section between the groove 21 for receiving the sealing system 22, 23 and the bearing surface of the compression spring 18 has a greater mass.

In contrast to these four possibilities, a shift in the bandwidth between the lowest possible and the highest possible adjustable spring preload can be achieved, preferably washers are used. The use of washers is, for example, possible between the control piston 17 and the spring plate 19, between the spring plate 19 and the compression spring 18, between the compression spring 18 and the adjusting screw 20th

Particularly advantageous is the use of at least one washer between the compression spring 18 and its bearing surface on the adjusting screw 20 or on the spring plate 19 or on the bearing surface of these two components. Using washers in different slightly different thicknesses or several very thin washers, the desired adjustment of the bandwidth of the bias of the compression spring 18 can be achieved. Since the surface of a washer on which the compression spring 18 rests, should advantageously be made of a particularly hard material, it may be advantageous to harden a designated washer on one side. In order to achieve the actual required distance, a corresponding layer thickness can be removed from the uncured side of the prepared washer or this washer may be used in a stack with at least one other washer, depending on whether the prepared washer is too thick or too thin. Very particular preference is given to using each of a hardened washer of a standard size on each support surface of the compression spring 18 and, if necessary, to use further required washers of uncured standard material.

In a described as in the previous text, built hydraulic regulator, the adjusting screw 20 can be moved with the intended mounting tool within the adjustment range, whereas - by unknowingly turning the adjusting screw 20 in the direction of application unduly low spring preloads is avoided; as well as a careless dismantling of the adjusting screw 20.

Thus, the mounting of the adjusting screw 20 is feasible, the associated mounting thread in the controller housing 14 may extend to the outer end of the housing bore. A spaced on both sides of the installation location of the shaft retaining ring 26 longitudinal portion of the housing bore is advantageously made as a cylindrically designed lowering, whose diameter is slightly larger than the outer diameter of the thread 24. The latter facilitates the assembly of the shaft securing ring 26 and avoids deformation of the thread 24 through the shaft securing ring 26. Alternatively, to a reaching to the surface of the housing 14 thread to achieve the same advantages of the entire length portion within the housing bore, starting from the housing surface into the slightly above the installation of the shaft lock ring 26 outstanding length portion of the inner diameter have a width that is slightly larger than the outer diameter of the existing for installation of the adjusting screw 20 thread 24.

For attaching a mounting tool for actuating the locking screw 20 (for installation or removal and adjustment of the Cut-off pressure or the load-sensing pressure) is located starting from its front side a recess suitable for the tool (see, for example, Figure 4). The construction of the adjusting screw 20 allows a variety of possible embodiments of such recesses. This can be either deliberately compatible with a standard tool (here: a hexagon socket) executed in a standard size or executed in order to better protection against tampering such that actuation only by a special, no standard corresponding tool is possible.

Stop for limiting the maximum preload of the coil spring

The example shown in FIGS. 2 to 5 has two adjustment ranges. Referring to the application example load-sensing control can be set within a certain range, the lower adjustment range, the load-sensing pressure level from the absolute minimum value to a pressure level, which is still typical for applications in which the achievement of the lowest possible power loss is an absolute priority whereas, in an overlying adjustment range, a load-sensing pressure level can be set for respective applications for which the provision of some pressure reserve is necessary or advantageous.

With reference to the application example of pressure cutoff, which is maintained in the following text, within a certain range, the lower adjustment range, the cutoff pressure can be set from a minimum value preset by the pmin stop up to the upper limit of the pressure level at which the hydraulic system is operated permanently can. Within a bandwidth immediately adjacent thereto, the cut-off pressure can be set within a temporarily permissible overpressure range up to an upper limit that can no longer be exceeded. When the adjusting screw 20 is moved, the installer perceives whether its position would cause a pressure cut below or within the regular working range. To explain this novel regulator-securing mechanism, the length portion of the adjusting screw 20 mounted in the controller housing 14 is considered, which is located in the vicinity of the O-ring 22. Essential features of this length section are shown in FIG. 5, which shows a detailed view of the regulator of FIGS. 2 to 4.

Starting from a positioning of the adjusting screw 20 in the controller housing 14, in which the compression spring 18 has the minimum allowable or slightly higher bias, is the right side of the O-ring 23 lying longitudinal section x of the lateral surface of the adjusting screw 20 at the opposite Wall section 11 of the housing bore of the regulator housing 14, where an inner diameter of size D1 is present. Due to the local, relatively large distance is initially at a continued screwing in the adjusting screw 20 into the controller housing 14 within this length section x virtually no friction. A friction between the adjusting screw 20 and the controller housing 14 occurs at the threaded connection 24 and in the areas of the O-ring 22, the optionally existing support ring 23 and the possibly existing washers. A certain amount of friction is necessary because otherwise the adjusting screw 20 could automatically adjust before fixing the setting. To prevent the automatic adjustment - such as vibrations occurring during the application - the adjusting screw 20 is fixed by a clamping screw 52, which is provided for example via a at the corresponding point of the regulator housing 14 with a continuous threaded bore and a cylindrical portion of Adjustment screw 20 hits. When loosening the clamping screw 52, the adjusting screw 20 can be adjusted within a certain range. Depending on the setting, the pressure level is set, which can be present at the high pressure output 10 of the hydraulic pump with a correspondingly sufficient mechanical input power. As mentioned above, this limit, which can be set on a hydraulic controller, is referred to as a pressure cutoff. dung. The so-called cut-off pressure can be adjusted within a certain range.

In order to avoid damage, the bandwidth of the cut-off pressure should only be adjusted in the range in which the hydraulic pump or a hydraulic motor or a hydraulic system can be operated permanently. In order to prevent damage and prevent danger, the cut-off pressure must not be above a critical value.

The housing bore for accommodating the adjusting screw 20 in the regulator housing 14 has a longitudinal section 12 adjoining the longitudinal section 11. At the transition region of these two longitudinal sections 11, 12 there is a change in the inner diameter from D1 to D2, wherein the inner diameter D2 present in the longitudinal section 12 is slightly smaller than the diameter D1. In this case, the inner diameter D1 is matched to the outer diameter Dx of the adjusting screw 20, which has this in the longitudinal section x, that with a correspondingly far screwed adjusting screw plug 20, the overlap of the longitudinal section x of the adjusting screw 20 and of the longitudinal section 12 of the housing bore in the controller housing 14 leads, in this overlap region an interference fit is present.

If there is such an overlap and thus the said interference fit, a higher torque must be applied for screwing in and out of the adjusting screw plug 20. By a corresponding dimensioning of the diameters D1 and Dx as well as a corresponding quality of the affected surfaces, it is achieved that the adjusting screw 20 can be moved within this overlapping area with an effort that is still easy to handle, but already appreciably higher, to be applied to the assembly tool. At the end facing the compression spring 18 end of the longitudinal portion 12 is a significant taper of the inner diameter of the housing bore of the regulator housing 14 before. The tapering region forms a stop on which the adjusting screw 20 finally abuts when it is screwed further into the regulator housing 14 starting from the overlapping region. By a, as shown in Figure 5 to be recognized according to each other adapted bevel on reaching this second and simultaneously final / hard stop when the adjusting screw 20 and the housing bore in the controller housing 20 is an enlarged butt surface 28, whereby a higher stability of the attack is achieved. Significantly counteracted is the danger that the striking the stop edge of the adjusting screw 20 gradually hinereürter into the attack and the associated risks of material entering the oil circuit abrasion and an unintended displacement of the final stop position are much less likely.

In a variant, without counteracting the preceding features by the one advantageous in terms of manufacturing and function construction to achieve protection against negligent removal of the adjusting screw and a limitation of the minimum pressure levels, the affected controller components are dimensioned such that the Stell- Closure screw 20 is then in the overlapping area, if the specified by their local position to a pressure cut to an already particularly high pressure level, the presence of such a pressure level at the high pressure outlet 10 of the hydraulic pump is less than a pressure, when reached the risk of instantaneous damage or even an immediate destruction of the hydraulic pump is present. Nevertheless, a longer-lasting operation of the hydraulic pump with the particularly high pressure life would be shortening. From the features described above it follows that in this variant, while retaining the previous, the tapered abutment surfaces 28 of the adjusting screw 20 and the housing bore of the regulator housing 14 should meet at which such a bias of the compression spring 18 is present, which is a Druck- In any case, this is below a critical value above which critical damage to the hydraulic pump would occur.

In the following, in addition to the variant presented above with one-piece locking screw 20, three extensions based thereon (one variant 2, one variant 3 and one variant 4) will be presented.

The housing 14 of a hydraulic controller (see Figures 1 to 5) equipped with a locking screw 20 according to the first variant (in relation to the drawing orientation) on the left side to accommodate the shaft securing ring 26 must have a certain additional length. This fundamental disadvantage can be avoided by the use of a locking screw 20 of the variant 2, 3 or 4. The modes of operation of these variants are explained one after the other based on their respective installation process in the controller housing 14, from which beyond the design features of the variants are shown.

Installation of a locking screw 20 'of variant 2:

In the phase of installation shown in FIG. 6, a few threads 24 'located at the head of the adjusting screw 20' engage in the internal thread 24a 'of the regulator housing 14'. (Right of the head, the lateral surface of the adjusting screw 20 'in the axial direction many different each rotationally symmetric sections.) Near the right end of the adjusting screw 20' is a radial groove 25 'with an attached shaft securing ring 26'.

In the installation situation shown in Figure 7a, the adjusting screw 20 'is screwed a little further into the regulator housing 14' and is located exactly at the position at which the not yet compressed shaft securing ring 26 'on the narrowing wall portion 29' of the housing bore Recording the adjusting screw 20 'is applied. By continuing the screwing the shaft securing ring 26 'along the contour of the guided narrowing wall portion 29 'along and thereby always further compressed accordingly until the region of this radial groove 25' of the adjusting screw 20 'penetrates into the spring chamber 18a'. The local inner diameter is correspondingly large, so that relaxed at a certain penetration depth of the shaft securing ring 26 '.

Based on the installation situation shown in FIG. 7b, it can be seen that the locking screw 20 'can no longer be dismantled, but the relaxed shaft lock ring 26', which is still locked in its radial groove 25 ', impinges on a flat wall area in the interior of the spring chamber 18a', whereby an end stop is present. Consequently, there is a defined minimum value of the bias of the compression spring 18 'using such a set screw plug. As a result of the shaft retaining ring 26 'located in the spring chamber 18a', there is no clearly defined upper limit of the prestress of the compression spring 18 'in the variant illustrated here, and thus no upper limit of the pressure cut. With respect to the entire hydraulic device, such a limitation can be achieved by exactly those principles for a locking screw 20 'of the variant 2 as well as on this in the controller housing 14' running housing bore analogous to the configuration for using a set screw 20 of variant 1 be taken over.

By a small modification of the housing bore in the regulator housing 14 "for receiving the adjusting screw 20 'of variant 2, the stop for achieving the maximum predeterminable upper pressure cut off can be implemented differently.This implementation, referred to as variant 3 according to FIG Housing bore of the regulator housing 14 "between the spring chamber 18a" and the narrowing, preferably conically narrowing portion 31 "an appropriately designated as an annular chamber 30" range.The annular chamber 30 "has an expanded cross-section. When mounting the associated adjusting screw 20 "of variant 3 of the radial groove 25" patch shaft securing ring 26 "on reaching the corresponding screwing over the cone-shaped portion 31" of the housing shell upset until it dips into the annular chamber 30 "and expands there to its original dimensions, but still remains locked in the radial groove 25". From the perspective of the shaft securing ring 26 ", there is an abrupt constriction and thus an insurmountable position in the transition region between the annular chamber 30" and the spring chamber 18a ", just as at the transition region between the annular chamber 30" and the conical section 31 "of the housing bore the adjusting screw 20 "only within the axial extent of the annular chamber 30" corresponding bandwidth can be moved.

9, the section provided at its head with the external thread 24 '' is interrupted by a radial groove 25 '', and the housing bore of the regulator housing 14 '' is equipped with the internal thread Section over a certain length interrupted by a radial groove 32 '' introduced there, which has at least a greater up to a much greater Längenabmass than their depth ,

To mount such a set screw 20 "'of variant 3, the regulator housing 14"' must be positioned such that the adjusting screw 20 "'can be inserted vertically from above There, the shaft securing ring 26 "'is positioned so that it is in the spring chamber 18a'" facing end portion of the radial groove 32 "', where the cross section is again correspondingly narrowed, plan for Lying comes. Subsequently, the adjusting screw 20 "'is inserted into the housing bore and screwed into the regulator housing 14"'. The intended design provides that the wire diameter of the shaft securing ring 26 "'has a maximum of the width of the flank width of the thread 24"', so that the already in the controller housing 14 "'used and of the spring chamber 18a'" facing end portion of the radial groove 32 "' As soon as the adjusting screw plug 20 "'is screwed in so far that its radial groove 25"' reaches the shaft securing ring 26 "', it locks in place there. From this assembly description it is clear that the diameter of the cross-sectional area Ax must be slightly larger than the resulting during the assembly step diameter of the shaft lock ring 26 '' when sliding over the thread 24 '' of the set screw 20 '' to take its final position, namely in the radial groove 25 "'of the adjusting screw 20"'.

FIG. 9 shows such an adjusting screw 20 "'with attached shaft securing ring 26"' in the described end position. As can be clearly seen, results in each adjustment a fixed end stop and thus a defined on both sides limited bandwidth of the adjustable bias of the compression spring. In this case, the design of the contour at the two ends of the groove 32 "'of its longitudinal extent is of considerable importance: if the locking screw 20"' reaches the near zone of one of its end positions or one of its end positions, then the shaft locking ring 26 " A force acting on the shaft securing ring 26 '' makes sense for the following consideration: a radial force component related to the regulator axis presses the shaft securing ring 26 '' into two components. 'exactly in the center of the head of the adjusting screw 20' 'existing radial groove 25' 'inside. The other axial force component related to the governor axis exerts a force on the shaft retainer ring 26 "'which tends to push the shaft retainer ring 26"' out of the radial groove 25 "'present in the head of the retainer screw 20"'. H. at least the tendency to destroy the end stop.

Particularly unfavorable would be an angular shape of the said contour, because then only a force is present when reaching the end position, which tends to cause the shaft securing ring 26 "'from the locking screw 20''present in the locking screw 20''. A radial groove 25 "'threatens to push out and the other direction of force by which depression of the shaft securing ring 26" into this radial groove 25 "does not exist at all However, a convex or conical contour with respect to the governor axis is unfavorable since it tends to tilt the shaft lock ring 26 '' when the lock screw 20 '' is screwed into one of its end positions, thus a concave contour is usefully used. In a preferred embodiment, the contour concludes positively with that of the surface of the shaft securing ring 26 '' from which this assumes when it is pressed into the radial groove 25 "'of the adjusting screw 20"'. In a particularly preferred embodiment, this contour is slightly larger than such a form-fitting contour, so that when reaching an end stop on the one hand said desired directional component of the force is relatively large and on the other hand tilting is avoided.

In order for the adjusting screw 20 "'to be able to rotate over the entire intended setting range and thus the thread 24"' of the adjusting screw 20 "'and the regulator housing 14"' over the entire toothing area, the groove area 32 must be provided Clearly, there are the same continuations of the threads that would exist if these radial grooves 32 '', 25 '' were absent.

The latter relationships are obviously also valid for the end stop position of the shaft securing ring 26 'in the spring chamber 18a "in variant 2 and also for the two end stop positions of the shaft securing ring 26" in the annular chamber 30 "in the variant 3.

Application on hydraulic valves

The hydraulic device can also be applied to hydraulic valves. As one of many application examples, an adjustable pressure relief valve can be used. The possible adjustment range can be the same Conversions as in the illustrated embodiments with the pmin and the pmax-stop are limited. Likewise, the creation of two different adjustment ranges, which is also advantageous in certain applications for a pressure relief valve and other hydraulic valves implement,

Protective cap / double protection cap

In an expansion stage, a protective cap can be used both for a hydraulic controller that corresponds to the state of the art and for a hydraulic regulator according to the invention; equally for a prior art or a hydraulic valve according to the invention. Especially for the hydraulic regulator designed in the preferred variant, the use of a component designated as a protective cap and in the case of a two-stage regulator as a double protective cap 50 and explained in more detail below is proposed. An embodiment of the double protection cap 50 is shown in Figs. 10-12. FIG. 1 shows the lower and upper side of the double protection cap 50 in two figures. FIG. 12 shows a sectional view of the protective cap 50 or of the regulator housing 14 with mounted double protective cap 50.

In production, the double cap 50 can be placed as soon as the shaft retaining rings 26 have been mounted. Even without equipment with a double cap 50, the controller remains fully functional. By means of double protective cap 50, the region of the housing bore located outside the adjusting screw 20 in the regulator housing 14 can be covered with the existing threads 24, the built-in shaft securing rings 26 and the head-side depressions of the adjusting screw 20 to which the assembly tool must be attached to protect it from damage and dust and other contamination.

The double protective cap 50 is equipped with corresponding jaws 51, which in positionally correct placement by a slight pressing in complementary Snap recesses on the regulator housing 14. In addition, recesses 53 may be provided on the cap 50 and the claws 51, respectively, to increase the flexibility of the cap 50 and to facilitate assembly. As materials for the production of double protection caps 50 offers a suitable for the conditions of use plastic z. B. PVC. In an advantageous embodiment, the removal of a double protective cap inevitably leads to their intended destruction. Particularly advantageous is an availability of such double protection caps 50 in different colors. Then it is possible to equip the controller in a factory assembly each with a double cap 50 of the color a. When working on the controller by employees or specially certified service technicians of other companies, double protection caps 50 in one color b can be used. In order not to discourage potential customers by service bonding, double protection caps 50 in a color c could be freely salable so that corresponding hydraulic regulators can be provided with such after third party work on the regulator. (The latter and the extended thoughts merely describe the example of a possible constellation.)

In the case of particularly high safety requirements, the double protective caps 50 of the colors a and b can be marked with a unique number. By the relevant employee of the service network could then be created before each application of a then clearly identifiable new double protection cap 50 on the known by its own ident number controller a note about the previously performed work. Centrally managed can then - as long as only within a factory assembly and carried out by certified service technicians - a gapless service proof be deposited. In order to prevent again an unidentified forgery of the double protective caps 50, they can be clearly marked with a so-called tracer.

According to the present invention, the hydraulic device is equipped with a sealing plug instead of a locking screw. This embodiment is not shown in any of the illustrations, but the only gen constructive differences to the embodiments of Figures 2 to 9 or 10-12 briefly summarized.

If a hydraulic device according to the described exemplary embodiment according to variant 1 with the sealing plug is inserted into the hydraulic regulator, the longitudinal section of which is shown in FIG. 2 using the one-piece locking screw 20, a very similar-looking arrangement results. The differences amount to three details. The end of the sealing plug would abut, as mentioned, on the shaft securing ring 25. In addition, the representation of said threaded connection 24 according to the convention of technical drawings would be omitted. Furthermore, the cut-away recess for attaching a screwing tool would not be present or such a recess would be unnecessary.

In the previously described variant 2 of the hydraulic device, the sealing plug may have, within its lateral surface, an external radial groove into which a shaft securing ring is placed prior to assembly. Variant 2 of the hydraulic device using a sealing plug has some analogy to the construction of the hydraulic device shown in Figures 6 and 7, or may have such analogy, although in the latter construction a setting plug 20 is used. It can be seen from FIG. 8 how the contour of the housing bore for a hydraulic device of variant 3 can be designed.

According to the previously described variant 3 of the hydraulic device with sealing plug, near the end facing the spring chamber, an outer radial groove may be present within the lateral surface of the sealing plug, into which a shaft securing ring is placed prior to assembly. The dimensions of the outer radial groove and that of the shaft retaining ring are designed so that the sealing plug can be pushed into the housing bore when the shaft locking ring is placed on and pressed against it as intended. Variant 3 of the hydraulic device using a The sealing plug has a certain analogy to the variant of the hydraulic device shown in FIG. 9 or may have such an analogy. It can be seen from FIG. 9 how the contour of the housing bore for a hydraulic device of variant 3 can be designed.

The advantages of the invention as well as the advantageous embodiments can be summarized as follows. While the adjusting screw 20, 20 ', 20 ", 20"' is in one piece - various embodiments are shown in Figures 2 to 9 -, the same applies to the inventive low-cost variant of the hydraulic system according to the invention, in which a closure plug is used, there is the corresponding functions according to the prior art subsystem from a built-in the device housing adjusting screw guide sleeve 5 and the actual screw 8 (see Figure 1). The production cost of each of these two components 5, 6 is approximately comparable to that of the one-piece adjusting screw 20, 20 ', 20 ", 20"'. In addition, both the adjusting screw guide sleeve 5 and the adjusting screw 6 each require an oil seal. Nevertheless, the execution of the hydraulic device prevents the negligent unconscious complete unscrewing the adjusting screw 20, 20 ', 20 ", 20"'.

Accidental, unintentional setting of an inventive hydraulic controller or hydraulic valve, whereby the hydraulic machine or the hydraulic system operates in an outside of the allowable pressure range, which in turn to secondary damage - such as damage to the hydraulic machine, other hydraulic components or the destruction of components and also a shooting out the closure device in the event of a thread breakage - is prevented. The latter clearly represents a measure for accident prevention.

Also, in a device according to Figures 2 to 9 defined according to the requirement setting the bias of the compression spring can be made much faster and more precise, because there is the distortion and fixing the Setting screw plug in the radial direction and therefore exerts no influence on the previously set axial position of the adjusting screw. On the other hand, the countering of a setting screw 6 corresponding to the prior art causes a falsification of the setting value, which in the case of corresponding applications already leads to comparatively large deviations in the operation of the hydraulic system. Such a sensitive application is, for example, the demand flow control in which a small distortion in the specification of the load-sensing pressure already draws a significant undesirable feedback.

Instead of a simple stop with which a single absolute maximum value of the adjustable preload of a compression spring is fixed, there is a temporally permissible overload range based on the application example pressure cut-off, which is limited by a final maximum value. While a fitter / service technician sets the pressure cutoff on the controller, it is immediately noticeable whether this adjustment is made within the specified operating range or already within the temporarily permissible overload range.

Protection against damage and against the ingress of dust and other contamination is made possible by the double protection cap 50. The different colors of double protection caps opens up a better traceability, whether the pressure cut has been set differently on a hydraulic controller after its delivery, resp. the bias of a compression spring of the hydraulic arrangement. This, depending on the accepted effort in varying degrees to a clear gap-free proof of service.

Claims

claims

1 . Hydraulic device, in particular hydraulic valve or hydraulic regulator, with a housing, at least one piston axially displaceably mounted in a housing bore, and in each case at least one pressure spring acting on the piston,

characterized,

in that at least one sealing plug inserted directly into the housing bore is provided, the position of which influences the prestress of at least one pressure spring and at the same time forms a closure system for sealing the spring chamber containing at least one compression spring to the outside.

2. Hydraulic device according to claim 1, characterized in that the sealing plug comprises at least one radial groove into which a sealing element, in particular an O-ring, is introduced.

3. A hydraulic device according to claim 2, characterized in that in addition to the sealing element in the radial groove, a support ring is introduced, against which the sealing element can be pressed at a corresponding pressure level within the spring chamber.

4. Hydraulic device according to one of the preceding claims, characterized in that at least one screw is provided by the closure plug after adjustment to the desired position against the housing of the hydraulic device clamped and thereby can be fixed.

5. Hydraulic device according to one of the preceding claims, characterized in that the closure stopper comprises a spring plate as a stop for the compression spring, wherein the spring plate is ideally designed as a separate and detachable from the closure member.

6. Hydraulic device according to one of the preceding claims, characterized in that the position of the sealing plug by means of at least one securing element, preferably a shaft securing ring, is limited, preferably to prevent complete removal of the sealing plug and / or to ensure a sufficient sealing effect of the sealing plug.

7. A hydraulic device according to claim 6, characterized in that the shaft securing ring is introduced into an inner radial groove of the housing bore, wherein the inner radial groove is preferably located on the side facing away from the spring chamber side of the housing bore, ideally at the position which is immediately adjacent connects the area of the housing bore that is filled by the sealing plug.

8. A hydraulic device according to claim 6, characterized in that the shaft securing ring is introduced into an outer radial groove of the lateral surface of the sealing plug.

9. A hydraulic device according to claim 8, characterized in that the introduced into the outer radial groove shaft securing ring is located within a dedicated for the shaft retaining ring receiving annular recess of the housing bore or the spring chamber.

10. Hydraulic device according to one of the preceding claims 6 to 9, characterized in that in the housing bore, one or more washers are introduced or introduced between the shaft securing ring and the sealing plug in order to influence the bias of the compression spring. 1 . Hydraulic device according to one of claims 5 to 10, characterized in that at least one of the stop surfaces of the compression spring and the compression spring each have one or more washers are introduced or can be introduced to prevent wear of the stop surfaces by the overlying compression spring and by the Closing plug adjustable preload to influence the compression spring.

12. Hydraulic device according to one of the preceding claims, characterized in that at least one protective cap is provided, which is fixable to the housing for covering the at least one sealing plug, in particular by means of one or more pronounced on the protective cap claws, which engage in complementary recesses of the housing , wherein the protective cap is not non-destructively detachable from the housing.

13. Hydraulic device according to one of the preceding claims, characterized in that the device is a hydraulic valve with one or more valve elements, wherein at least one of these valve elements comprises the sealing plug according to the invention.

14. Hydraulic device according to one of the preceding claims 1 to 12, characterized in that the device is a hydraulic controller with one or more controller axes, wherein at least one regulator axis comprises the sealing plug according to the invention.