DE102020002649A1 - Pressure fluid operated linear brake and tuning process - Google Patents

Abstract

Linear brake (LBR) with a brake housing (1) which at least partially encompasses a guide rail (F), in which spring assemblies (2.1) are located as energy stores, the one or more brake pistons (3) overlapping the guide rail (F) perpendicular to the direction of movement of the linear brake ( LBR) with a force applied, the brake pistons (3) interacting with simple strip-shaped wedge elements (6, 7) and linear bearings (4, 5) which, via suitably dimensioned bevels, have two opposing friction shoes (9.3) arranged on both sides of the guide rail (F) Press against friction surfaces (R) on both sides of the guide rail (F) and thus clamp the linear brake (LBR) on the guide rail (F) as well as a tuning process for this.

Description

The present invention is a linear brake actuated by the supply of pressure means for attachment to a carriage that can be moved parallel to a guide rail according to the preamble of the main claim.

It is provided that the housing of the linear brake at least partially surrounds the guide rail and that in the housing of the linear brake one or more actuator elements interacting with energy storage devices and actuated by supplying pressure media are arranged, which cause and / or cancel a clamping effect of the linear brake on the guide rail.

Linear brakes for use on guide rails are known from the prior art, such as them DE 101 27 664 C1 disclosed.

It is proposed that a fork-shaped magnet armature pretensioned by means of spring elements presses two wedge elements arranged on the side of the guide rail and opposing each other against the guide rail transversely to the direction of movement of the guide rail, thereby exerting a clamping force on the guide rail.

To release the clamping, an electromagnet arrangement is provided which attracts the magnet armature against the force of the spring elements and thus releases the clamping between the wedge elements and the guide rail.

The disadvantage of the linear brake described is its low power density, i. H. the low clamping force that can be achieved per unit volume, which is caused by the type of actuation by the electromagnet arrangement with its low forces that can be achieved with respect to the magnet armature and in the limited bending strength of the fork-shaped magnet armature.

From the DE 10 2006 019 410 A1 a linear brake for guide rails is also known, in which a piston lying transversely to the direction of movement of the linear brake is set in motion inside the brake housing by means of pressure means and spring elements.

By means of suitable bevels and rolling elements, the movement of the piston causes an elastic expansion or elastic return of the spring-elastic brake housing, whereby the linear brake is opened or closed.

The presented linear brake makes high demands on the accuracy of the production, especially in the area of the brake linings and the housing, and has no possibility of specific setting of defined clamping forces. In addition, the deformation of the housing can be transferred to the slide and thus result in positioning errors.

Linear brakes for guide rails are also known from the prior art, as shown in FIG DE 10 2006 062 295 B4 to be revealed.

The subject of this invention is also a clamping device for attachment to a slide that can be moved parallel to a guide rail, whereby the clamping on the guide rail takes place actively via a clamping element driven by means of a supply of pressure means and wherein the fork-shaped clamping element, which can be moved perpendicular to the direction of movement of the slide or the brake, is directly is in contact with the surface of the guide rail via its prism-like symmetrical internal geometry.

The disadvantage of this clamping device is the fact that the clamping effect is only maintained when the external power supply is present and the clamping effect is canceled in the event of a power failure. Furthermore, the direct contact between the fork-shaped clamping element movable in the brake and the guide rail leads to high wear on the contact surfaces and to reaction forces on the brake, which place a heavy load on the guidance of the slide connected to the brake on the guide rail.

Another linear brake for guide rails according to the prior art is off EP 2 935 929 B1 known to the applicant.

In the linear brake presented therein, a fork-shaped brake piston, lying perpendicular to the direction of movement of the brake and supported on the inner wall of the brake housing, generates or eliminates a clamping effect against the guide rail via piston bevels and transmission wedges.

The movement of the brake piston is realized by means of pressure medium and strong spring elements, which enables high power densities. Disadvantages of the linear brake are the required high manufacturing accuracy and complicated functional parts with the associated high costs.

The object of the present invention is accordingly to propose an improvement over the prior art which, for a given structural size, is higher than that of the guide rail Achievable in a large range adjustable braking force, which is designed in such a way that the clamping force is generated by an energy storage device integrated into the brake and canceled by the supply of external energy (fail-safe principle), in which the friction surfaces of the friction shoes are perpendicular without external reaction forces move to the friction surface of the guide rod or guide rail, which is also largely wear-free and maintenance-free, which can be produced inexpensively from simple components and can be easily adjusted during assembly.

According to the invention, the object is achieved with the features of the main claim.

For this purpose, the linear brake is equipped with a housing that at least partially encompasses the guide rail, in which there are spring assemblies as energy storage devices, which apply a force to one or more piston elements that overlap the guide rail with a force perpendicular to the direction of movement of the linear brake, the piston elements on both sides of the guide rail with simple strip-shaped wedge elements cooperate, which press two opposing friction jaws arranged on both sides of the guide rail against friction surfaces of the guide rail on both sides via appropriately dimensioned bevels and thus clamp the linear brake on the guide rail.

For an optimal function of the linear brake, a simple tuning method is proposed in which the actual dimensions of the receiving areas of the brake housing for the strip-shaped wedge elements are determined on the linear brake and predetermined target dimensions of the receiving areas for the strip-shaped wedge elements are produced by inserting matching tuning strips.

In the case of the presented linear brake, one or more spring assemblies are provided as energy accumulators for closing, and the linear brake is opened by one or more pressure medium-actuated piston / cylinder arrangements, the force of which acts against that of the spring assemblies.

In order to achieve a high power density of the linear brake, strong spring assemblies preferably formed from disc springs are used as energy stores. To open the linear brake against the spring assemblies, piston / cylinder arrangements are proposed in which the greatest possible effective piston area is achieved by means of support rings that are inserted into the brake housing.

Instead of disc springs, any other type of mechanical spring elements, pressurized piston / cylinder arrangements or pressurized diaphragm accumulators are conceivable as energy accumulators and the linear brake can alternatively also be opened by electrical, electromechanical or piezoelectric actuators.

To increase the efficiency of the power transmission as well as to further increase the clamping forces, the strip-shaped wedge elements actuated by the fork-shaped pistons are mounted against each other and opposite the existing actuation and support surfaces by rolling elements, but the use of plain bearings made of suitable sliding materials is also conceivable at this point. Alternatively, it is also conceivable to manufacture the wedge elements themselves from sliding materials and to dispense with separate bearing elements.

For a further increase in the achievable clamping force, several of the described clamping arrangements can be arranged one behind the other in the brake housing in the direction of movement of the guide rail and actuated jointly or individually.

Furthermore, in addition to being used for linear guides, the brake according to the invention is also suitable for clamping rotating components, provided a suitable braking surface is available.

Further advantageous details on the mode of operation of the linear brake according to the invention emerge from the subclaims of the invention and from the description of the drawings mentioned below.

• 1 die räumliche Darstellung einer Außenansicht der Linearbremse mit einem Schnittverlauf A-A und einem Schnittverlauf B-B;
• 2 eine Explosionsdarstellung der Linearbremse mit zugeordneter Führungsschiene;
• 3 einen Schnitt A-A durch die erfindungsgemäße Linearbremse im ungebremsten Zustand und eine Detailansicht A;
• 4 einen Schnitt A-A durch die erfindungsgemäße Linearbremse im gebremsten Zustand und eine Detailansicht B;
• 5 einen Schnitt A-A durch eine weitere erfindungsgemäße Linearbremse im gebremsten Zustand und eine Detailansicht C.
• 6 einen Schnitt B-B durch eine teilmontierte erfindungsgemäße Linearbremse während eines Abstimmvorgangs.

Show:

• 1 the three-dimensional representation of an external view of the linear brake with a section AA and a section BB;
• 2 an exploded view of the linear brake with an associated guide rail;
• 3 a section AA through the linear brake according to the invention in the unbraked state and a detailed view A. ;
• 4th a section AA through the linear brake according to the invention in the braked state and a detailed view B;
• 5 a section AA through a further linear brake according to the invention in the braked state and a detailed view C.
• 6th a section BB through a partially assembled linear brake according to the invention during a tuning process.

1 shows a three-dimensional external view of the linear brake according to the invention actuated by means of external energy ( LBR ) consisting of the brake housing ( 1 ), which the guide rail also shown ( F. ) partially encompassed. For the The illustrated linear brake ( LBR ) on the brake housing ( 1 ) via connection bores ( A. ) for connection to an external pressure medium supply.

The brake housing ( 1 ) is constructed in several parts and consists of a housing body ( 1.1 ), a case back made of two parts ( 1.3 ) and a housing cover ( 1.2 ), which via cover screws ( 12.1 ) on the housing body ( 1.1 ) is fixed.

The linear brake shown here ( LBR ) has two in the direction of carriage travel ( M1 , M2 ) one behind the other, schematically shown brake pistons ( 3 ). Equipping the linear brake ( LBR ) with one or more than two brake pistons ( 3 ) conceivable.

The transmission of the desired braking forces of the linear brake ( LBR ) onto the guide rail ( F. ) takes place via a with the housing body ( 1.1 ) connected resilient transmission plate ( 9 ), which with friction jaws not shown here ( 9.3 ) is equipped.

For the connection between the linear brake ( LBR ) and the slide, not shown, are used by several in the housing body ( 1.1 ) inserted screw thread ( 1.9 ).

To clarify the geometrical shape and the geometrical assignment of the linear brake ( LBR ) The exploded view in 2 .

The brake housing ( 1 ) consists of a housing body ( 1.1 ) with a cover screw ( 12.1 ) screw-connected housing cover ( 1.2 ) as well as a two-part over ground screws ( 12.2 ) screw-connected case back ( 1.3 ).

To stiffen the brake housing ( 3 ) and for centering the spring assembly ( 2.1 ) a concentric inside the spring assembly ( 2.1 ) horizontal connecting pin ( 1.10 ), which is connected to the housing body ( 1.1 ) and the housing cover ( 1.2 ) is screwed.

As an interface for connecting the linear brake ( LBR ) screw-on threads ( 1.9 ), which are inserted into the housing body ( 1.1 ) are introduced.

The actuator inside the brake housing ( 1 ) a piston mechanism is arranged, which consists of a brake piston ( 3 ) with a screw-connected piston ring ( 10 ) and the one to open the linear brake ( LBR ) via one of the connection bores ( A. ) is supplied with a pressure medium.

To close the linear brake ( LBR ) a spring package consisting of disc springs is used ( 2.1 ), which is in a mounting hole ( 3.3 ) of the brake piston ( 3 ) and that is on the housing cover ( 1.2 ) is supported.

The force of the spring assembly ( 2.1 ) is used to achieve the desired braking effect via piston ends ( 3.6 ) of the brake piston ( 3 ) through the housing body ( 1.1 ) through on gear wedges ( 6th ) transferred via linear support bearings ( 4th ) and tuning bars ( 8th ) on the housing support surface ( 1.15 ) of the housing body ( 1.1 ) and supported by linear thrust bearings ( 5 ) and pressure wedges ( 7th ) an infeed movement to the guide rail ( F. ) to generate.

The infeed movement is transferred to resilient transmission plates ( 9.1 ) of the transfer plate ( 9 ) transmitted and generated via jaw carrier ( 9.2 ) and friction shoes ( 9.3 ) the desired clamping effect against the guide rail ( F. ). The transfer tabs ( 9.1 ) opposite the jaw carriers ( 9.2 ) as well as the jaw carriers ( 9.2 ) opposite the friction shoes ( 9.3 ) can be materially connected by gluing, soldering or welding or by a rivet or screw connection. It is also conceivable that the friction jaws ( 9.3 ) directly on the transfer tabs ( 9.1 ) to be attached.

The friction shoes ( 9.3 ) be made from an organic friction material, from a plastic material, from a ceramic material, from a metal alloy, preferably steel or bronze or a mixture of the materials mentioned.

In 3 becomes a first section AA and a detail A. the linear brake according to the invention ( LBR ), with the corresponding cutting line from 1 can be seen.

The illustrated linear brake ( LBR ) is open, i.e. not on the guide rail ( F. ) clamped, which is at the air gap ( G ) between the guide rail ( F. ) and the friction shoe ( 9.3 ) shows.

• - Einem Kolbenabsatz (3.4), der von einem Kolbenschaft (3.1) und einem Kolbenflansch (3.5) gebildet wird.
• - Einem Kolbengewinde (3.2) auf dem Ende des Kolbenschafts (3.1), das dem Gehäusedeckel (1.2) zugewandt ist.
• - Einer Aufnahmebohrung (3.3) für das Federpaket (2.1), die konzentrisch innerhalb des Kolbenschafts (3.1) liegt.
• - Kolbenenden (3.6), die sich in Richtung zum Gehäuseboden (1.3) hin an den Kolbenflansch (3.5) anschließen.

In the three-part housing body made up of the parts ( 1.1 ), Housing cover ( 1.2 ) and two-part case back ( 1.3 ) existing symmetrical brake housing ( 1 ) there is initially a brake piston ( 3 ), which consists of the following geometric areas:

• - A butt heel ( 3.4 ), which is supported by a piston skirt ( 3.1 ) and a piston flange ( 3.5 ) is formed.
• - a piston thread ( 3.2 ) on the end of the piston skirt ( 3.1 ), which is attached to the housing cover ( 1.2 ) is facing.
• - A mounting hole ( 3.3 ) for the spring package ( 2.1 ), which are concentric within the piston skirt ( 3.1 ) lies.
• - piston ends ( 3.6 ) facing towards the bottom of the case ( 1.3 ) towards the piston flange ( 3.5 ) connect.

The piston ( 3 ) is via the corresponding piston thread ( 3.2 ) and piston ring thread ( 10.1 ) with the piston ring ( 10 ) screw-connected, with the piston ring ( 10 ) via a piston ring inner seal ( 10.2 ) opposite the piston skirt ( 3.1 ) and with an outer piston ring seal ( 10.3 ) compared to the housing extension ( 1.5 ) is sealed.

The piston chamber ( 3.7 ) is via the connection hole ( A. ) is supplied with a pressure medium, the pressure of which on the piston ring effective surface ( 10.4 ) acts and the piston ( 3 ) in relation to the brake housing ( 1 ) in its against the force of the spring assembly ( 2.1 ) facing end position in piston release direction ( P2 ) holds.

The pressure medium used can be gaseous substances, preferably compressed air or pressure fluids, preferably hydraulic oil or water-based emulsions.

On the side of the brake housing ( 1 ) are the piston ring effective area ( 10.4 ) an annular housing effective area ( 1.12 ) and a support ring effective area ( 11.3 ) opposite, whose surfaces add up in an advantageous manner, whereby the annular surface of the piston shoulder can be used as an effective piston surface.

The support ring ( 11 ) is via a support ring inner seal ( 11.1 ) opposite the piston skirt ( 3.1 ) and via an outer support ring seal ( 11.2 ) opposite the housing body ( 1.1 ) sealed.

The piston ends ( 3.6 ) reach through housing window ( 1.8 ) of the brake housing ( 1 ) and are in pressing contact with gearbox wedge flanks ( 6.3 ) of gear wedges ( 6th ), with the piston ends ( 3.6 ) not with the gear wedge flanks ( 6.3 ) are connected but only touch them. The gear wedges ( 6th ) are advantageously provided by return springs ( 2.2 , not shown) in the direction of the piston release direction ( P2 ) applied.

In the wedge reception rooms ( 1.4 ) of the brake housing are on the of the guide rail ( F. ) facing away from the gear wedges ( 6th ) linear support bearings ( 4th ) and tuning bars ( 8th ), whereby the support bearings ( 4th ) are designed as roller bearings to achieve a high degree of efficiency and each consist of a support bearing cage ( 4.1 ) and several support bearing rollers ( 4.2 ) are formed and the support bearings ( 4th ) by return springs ( 8.2 ) in their end position in the piston release direction ( P2 ) are located.

In the housing groove ( 1.11 ) is a carrier plate ( 9 ) with transmission screws ( 12.3 ) attached, which is attached via resilient transmission lugs ( 9.1 ) that supports the guide rail ( F. ) and those with jaw carriers ( 9.2 ) and friction shoes ( 9.3 ) are equipped.

Between the gear wedges ( 6th ) and the back of the flap ( 9.5 ) the transfer tabs ( 9.1 ) there are pressure wedges ( 7th ) and linear thrust bearings ( 5 ), which are also designed as roller bearings and each consist of a thrust bearing cage ( 5.1 ) and several thrust bearing rollers ( 5.2 ) exist, whereby the pressure wedges ( 7th ) by return springs ( 2.2 , not shown) in the direction of the piston closing direction ( P1 ) are acted upon and the linear thrust bearings ( 5 ) by actuation by means of return springs ( 2.2 ) in the direction of the piston loosening direction ( P2 ) are in their end position.

With the linear support bearings ( 4th ) and linear thrust bearings ( 5 ) preferably roles ( 4.2 , 5.2 ) in the form of cylindrical rollers; alternatively, rolling elements with other geometries can also be used, such as balls, barrels or other types of rotationally symmetrical bodies.

Alternatively, the linear support bearings ( 4th ) and / or linear thrust bearings ( 5 ) can also be designed as a plain bearing or it can be used when manufacturing the gear wedges ( 6th ) and / or pressure wedges ( 7th ) made of a plain bearing material or, in the case of a coating with a plain material, entirely on linear support bearings ( 4th ) and / or linear thrust bearings ( 5 ) can be waived.

When closing, the linear brake ( LBR ) is transformed into a state like that in 4th is shown with detail B, where the linear brake ( LBR ) in 4th with regard to the functional parts and their functional arrangement of the linear brake ( LBR ) the end 3 is equivalent to.

Via the connection bores ( A. ) occurs when the linear brake is closed ( LBR ) a removal of the piston chamber ( 3.7 ) on the piston ring effective area ( 10.4 ) effective pressure, whereby the brake piston ( 3 ) by the force of the spring assembly ( 2.1 ) in piston closing direction ( P1 ) is moved.

The brake piston ( 3 ) over the piston ends ( 3.6 ) in pressing contact with the Gear wedges ( 6th ), which are thus in the piston closing direction ( P1 ) are moved and the case back ( 1.3 ) approach.

The gear wedges ( 6th ) support themselves during this movement with the gear wedge back ( 6.2 ) via linear support bearings ( 4th ) on the printing areas ( 8.2 ) the tuning bars ( 8th ), which in turn with the support surfaces ( 8.1 ) in contact with the housing support surfaces ( 1.15 ) of the housing body ( 1.1 ) stand.

Printing area ( 8.2 ) and support surface ( 8.1 ) the tuning bar ( 8th ) are in 4th executed in parallel, but can also form a small wedge angle of less than 5 degrees with each other.

When moving the gear wedges ( 6th ) in piston closing direction ( P1 ) takes place due to the angle of incidence of preferably less than 10 degrees between the back of the gear wedge ( 6.2 ) and the gear wedge slope ( 6.1 ) a movement of the linear thrust bearings ( 5 ), the pressure wedges ( 7th ) and the transfer tabs ( 9.1 ) in jaw closing direction ( C1 ) instead, whereby the angle of attack between the pressure wedge bevel ( 7.1 ) and pressure wedge angle ( 7.2 ) preferably the angle of attack of the gear wedges ( 6th ) correspond.

The resilient transmission lugs ( 9.1 ) of the transfer plate ( 9 ) with the jaw supports ( 9.2 ) and the friction shoes ( 9.3 ) are thus against the guide rail ( F. ) and create a clamping effect there.

During the described movement of the gear wedges ( 6th ) in piston closing direction ( P1 ) are located on the bottom of the case ( 1.3 ) supporting return springs ( 2.2 ) the gear wedges ( 6th ), the linear support bearing ( 4th ) and the linear thrust bearing ( 5 ) compressed, whereby the linear support bearings ( 4th ) and the linear thrust bearings ( 5 ) compared to the gear wedges ( 6th ) only cover about half the way.

The tuning bars ( 8th ) and pressure wedges ( 7th ) place in piston closing direction ( P1 ) no way back, the former between the housing body ( 1.1 ) and case back ( 1.3 ) are fixed and the latter are fixed by return springs ( 2.2 ) with the case back ( 1.3 ) are kept in contact.

To open the linear brake ( LBR ) or to remove the clamping between the friction jaws ( 9.3 ) and the guide rail ( F. ) the piston chamber is connected via the connection bores ( A. ) is supplied with a pressure medium and the brake piston or pistons ( 3 ) move together with the piston rings ( 10 ) against the force of the spring assemblies ( 2.1 ) in the piston release direction ( P2 ).

The return springs ( 2.2 ) and with the piston ends ( 3.6 ) gear wedges in pressing contact ( 6th ) follow the movement of the brake pistons ( 3 ) and enable a return movement of the transmission tabs ( 9 ), the pressure wedges ( 7th ) and the linear thrust bearing ( 5 ) in the jaw release direction ( C2 ).

The linear thrust bearings ( 5 ) and linear support bearings ( 4th ) are reset by the return springs ( 2.2 ) back to their end position in the piston release direction ( P2 ) returned.

The clamping of the linear brake ( LBR ) on the guide rail ( F. ) is thus canceled, the friction shoes ( 9.3 ) are due to the spring action of the transmission lugs ( 9.1 ) from the friction surface ( R. ) of the guide rail ( F. ) lifted off and the linear brake ( LBR ) can be moved with the slide along the guide rail ( F. ) can be moved freely.

The one in the explanations to 4th The process sequence shown basically describes the mode of operation of a so-called closed-circuit brake, which means that the linear brake ( LBR ) is closed without the supply of external energy and is only opened by supplying external energy, in the present case by supplying pressure media.

This takes into account the so-called fail-safe principle, which means that if the external energy supplied fails, here in the form of pressure media, the linear brake ( LBR ) remains closed and that there are then no uncontrolled movements between the linear brake ( LBR ) and guide rail ( F. ) comes.

In 5 with the detail C is a further embodiment of the linear brake according to the invention ( LBR ), which with regard to the function and operating state of the linear brake ( LBR ) in 4th corresponds, so is closed. There is therefore no air gap ( G ) between the friction shoes ( 9.3 ) and the friction surfaces ( R. ) of the guide rail ( F. ).

At the in 5 shown linear brake ( LBR ) the resilient transfer plate ( 9 ) with the transfer tabs ( 9.1 ) through both sides of the guide rail ( F. ) arranged transfer plates ( 9 ) replaced with guide pins ( 9.4 ) are connected. The guide pins ( 9.4 ) are in guide bushes ( 1.14 ), which in turn are guided in guide bores ( 1.13 ) of the housing body ( 1.1 ) are used.

This causes a movement of the transfer plates ( 9 ) in jaw closing direction ( C1 ) and in the jaw release direction ( C2 ) allows.

Alternatively, it is conceivable to use the guide pins ( 9.4 ) directly in the guide bores ( 1.13 ) of the housing body ( 1.1 ) or the guide bushes designed as plain bearings ( 1.14 ) to be replaced by linear roller bearings such as ball bushings.

The return movement of the friction jaws ( 9.3 ) opposite the friction surfaces ( R. ) the guide rail is secured by bolt return springs ( 2.3 ) achieved.

With the illustrated linear brake ( LBR ) are the friction shoes ( 2.3 ) directly with the transfer plates ( 9 ) connected, but it is also conceivable to use the friction jaws ( 9.3 ) over brake pads ( 9.2 ) on the transfer plates ( 9 ) to be connected.

In 6th a second section BB of the linear brake according to the invention ( LBR ), with the cutting line from 1 emerges.

A tuning process for the linear brake according to the invention ( LBR ) presented, in particular for the embodiments according to 1 until 4th , where the linear brake ( LBR ) with a transfer plate ( 9 ) with elastic transmission lugs ( 9.1 ) is equipped.

The aim of the coordination process is to establish production-related tolerances in the area of the transfer plate ( 9 ) and the wedge receiving area ( 1.4 ) of the housing body ( 1.1 ) so that for both sides of the guide rail ( F. ) arranged wedge gear a uniform movement behavior is achieved, which leads to the fact that the brake pistons ( 3 ) evenly in piston closing direction ( P1 ) and in piston release direction ( P2 ) without moving in the housing body ( 1.1 ) to tilt.

For this purpose, it is suggested to first use the linear brake ( LBR ) without mounted housing base ( 1.3 ) and without a wedge mechanism with the housing cover ( 1.2 ) down in a device.

Then the complete transfer plate ( 9 ) into the housing groove ( 1.11 ) inserted and secured with the transmission screws ( 2.3 ) on the housing body ( 1.1 ) attached.

This is followed by an operation to ensure that the linear brake ( LBR ) on both sides of the guide rail ( F. ) or the guide rail dummy ( FD ) an installation space of the same width with a nominal dimension ( S. ) is available for the wedge gear.

To do this, first between the opposite and with the transmission tabs ( 9.1 ) connected friction shoes ( 9.3 ) a guide rail dummy ( FD ) and then the friction jaws ( 9.3 ) moved against the dummy from both sides at the same speed and with the same force until they rest against it.

In this state, a first actual dimension ( T1 ) between the housing support surface ( 1.15 ) and the back of the flap ( 9.5 ) and then a second actual dimension ( T2 ) between the housing support surface ( 1.15 ) and the back of the flap ( 9.5 ).

Then a first step between the first actual dimension ( T1 ) and the nominal size ( S. ) a difference is formed which corresponds to a first strip thickness ( U1 ) a first tuning bar ( 8th ) is equivalent to. Then between the second actual dimension ( T2 ) and a nominal size ( S. ) a difference is formed which corresponds to a second strip thickness ( U2 ) a second tuning bar ( 8th ) is equivalent to.

From a range of prefabricated tuning strips ( 8th ) different thickness between their supporting surface ( 8.1 ) and printing area ( 8.2 ) then the support strips ( 8th ) with the appropriate strip thicknesses ( U1 , U2 ) removed and placed in the linear brake ( LBR ) built-in.

The range of tuning bars ( 8th ) can advantageously be designed in such a way that the tuning strips ( 8th ) are available in a gradation with increments of 0.02mm, whereby smaller or larger increments are also conceivable.

Then the linear brake can be installed ( LBR ) with the installation of the linear support bearings ( 4th ), the gear wedges ( 6th ), the linear thrust bearing ( 5 ), the pressure wedges ( 7th ) and the other components.

A linear brake ( LBR ) with a guide rail ( F. ) at least partially encompassing brake housing ( 1 ), in which spring assemblies ( 2.1 ) are located as an energy store, which one or more of the guide rail ( F. ) overlapping brake piston ( 3 ) perpendicular to the direction of movement of the linear brake ( LBR ) apply a force, whereby the brake pistons ( 3 ) with simple strip-shaped wedge elements ( 6th , 7th ) interact, the two on both sides of the guide rail ( F. ) arranged opposing friction shoes ( 9.3 ) against mutual friction surfaces ( R. ) of the guide rail ( F. ) press and thus the linear brake ( LBR ) on the guide rail ( F. ) clamp.

To optimize the function of the linear brake ( LBR ) a simple tuning process is proposed in which the linear brake ( LBR ) Actual dimensions ( T1 , T2 ) of receiving spaces for the strip-shaped wedge elements ( 6th , 7th ) determined and carried out Insertion of tuning bars ( 8th ) matching strip thickness ( U1 , U2 ) specified nominal dimensions ( S. ) the receiving areas for the strip-shaped wedge elements ( 6th , 7th ) getting produced.

With the presented linear brake ( LBR ) are one or more spring assemblies ( 2.1 ) and the opening of the linear brake ( LBR ) is carried out by one or more pressure medium-actuated piston / cylinder arrangements, the force of which counteracts that of the spring assemblies ( 2.1 ) works.

To achieve a high power density of the linear brake ( LBR ), strong spring assemblies ( 2.1 ) used. To open the linear brake against the spring assemblies ( 2.1 ), piston / cylinder arrangements are proposed in which support rings ( 11 ) that go into the brake housing ( 1.1 ) are inserted, the largest possible effective piston area is achieved.

To increase the efficiency of the power transmission and to further increase the clamping forces, the strip-shaped wedge elements ( 6th , 7th ) against each other and against the existing actuation and support surfaces by linear bearings ( 4th , 5 ) with rollers ( 4.2 , 5.2 ) be stored.

Further features of the invention emerge from the patent claims, possible combinations of features not being restricted to the examples in the description or the patent claims.

List of reference symbols

A.

Connection hole

C1

Jaw closing direction

C2

Jaw release direction

F.

Guide rail

FD

Guide rail dummy

G

Air gap

LBR

Linear brake

M1

First direction of sled travel

M2

Second direction of carriage travel

P1

Piston closing direction

P2

Piston release direction

R.

Friction surface

S.

Nominal size

T1

first actual size

T2

second actual size

U1

first thickness of the last

U2

second strip thickness

1

Brake housing

1.1

Housing body

1.2

Housing cover

1.3

Case back

1.4

Wedge receiving space

1.5

Housing extension

1.6

Housing heel

1.7

Housing center bar

1.8

Housing window

1.9

Screw-on thread

1.10

Connecting pin

1.11

Housing groove

1.12

Housing effective area

1.13

Pilot hole

1.14

Guide bush

1.15

Housing support surface

2.1

Spring package / energy storage

2.2

Return spring

2.3

Bolt return spring

3

Brake piston

3.1

Piston skirt

3.2

Piston thread

3.3

Location hole (for TF)

3.4

Butt heel

3.5

Piston flange

3.6

Piston end

3.7

Piston chamber

4th

Linear support bearing

4.1

Support bearing cage

4.2

Support bearing roller

5

Linear thrust bearing

5.1

Thrust bearing cage

5.2

Thrust bearing roller

6th

Gear wedge

6.1

Gear wedge incline

6.2

Gear wedge back

6.3

Gear wedge flank

7th

Pressure wedge

7.1

Pressure wedge slope

7.2

Pressure wedge back

7.3

Pressure wedge flank

8th

Tuning bar

8.1

Support surface

8.2

Printing area

8.3

Groin flank

9

Transfer plate

9.1

Transfer tab

9.2

Jaw carrier

9.3

Friction jaw

9.4

Guide pin

9.5

Flap back

10

Piston ring

10.1

Piston ring thread

10.2

Piston ring inner seal

10.3

Piston ring outer seal

10.4

Piston ring effective area

11

Support ring

11.1

Support ring inner seal

11.2

Support ring outer seal

11.3

Support ring effective area

12.1

Cover screw

12.2

Ground screw

12.3

Transmission screw

QUOTES INCLUDED IN THE DESCRIPTION

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Patent literature cited

• DE 10127664 C1 [0003]
• DE 102006019410 A1 [0007]
• DE 102006062295 B4 [0010]
• EP 2935929 B1 [0013]

Claims (17)

Linear brake (LBR) for attachment to a slide that can be moved along a guide rail (F) with a brake housing (1) at least partially encompassing the guide rail (F), with an energy store (2.1) arranged on or in the brake housing (1), with a through the Energy storage device (2.1) acted upon by the brake piston (3), the piston ends (3.6) of which overlap the guide rail (F), the brake piston (3) being moved by the energy storage device (2.1) in the piston closing direction (P1) against the guide rail (F) and wherein the brake piston (3) is moved in the piston release direction (P2) against the energy accumulator (2.1) by a force generating system acted upon by pressure means, characterized in that when the brake piston (3) moves in the piston closing direction (P1), the piston ends (3.6 ) exert a force on both sides of the guide rail (F) lying gear wedges (6), which are supported by adjusting strips (8) in the brake housing (1) and which are de The guide rail (F) causes an infeed movement against a transfer plate (9) connected to the brake housing (1) and the brake shoes (9.3) connected to it, thereby clamping the linear brake against the guide rail. Linear brake after Claim 1 , characterized in that the force generation system, which causes the linear brake (LBR) to be opened by the application of pressure media, is a system consisting of a piston and cylinder. Linear brake according to the Claims 1 and 2 , characterized in that the piston consists of the brake piston (3) and a piston ring (10) connected to it and that the cylinder is formed by a housing extension (1.5) of the brake housing (1), by an effective housing surface (1.12) and a support ring (11) is formed. Linear brake according to the Claims 1 until 3 , characterized in that in the brake housing (1) circular ring surfaces in the form of a supporting ring effective surface (11.3) and a housing effective surface (1.12) are added to a common effective surface which can be acted upon by the pressure medium and which corresponds in size to a piston ring effective surface (10.4). Linear brake after Claim 1 , characterized in that the force generation system, which causes the linear brake (LBR) to be opened by the application of pressure media, is a system consisting of pressure membranes. Linear brake after at least one of the Claims 1 until 5 , characterized in that the energy storage devices provided for closing the linear brake (LBR) are mechanical spring assemblies (2.1), preferably disc springs. Linear brake after at least one of the Claims 1 until 6th , characterized in that the spring assemblies (2.1) serving as energy stores lie concentrically within the piston and cylinder system provided for opening the linear brake (LBR) by the application of pressure means. Linear brake after at least one of the Claims 1 until 7th , characterized in that linear bearings (4, 5) in the form of roller bearings are arranged between the gear wedges (6) and tuning strips (8) and / or between the gear wedges (6) and pressure wedges (7). Linear brake after at least one of the Claims 1 until 7th , characterized in that linear bearings (4, 5) in the form of slide bearings are arranged between the gear wedges (6) and tuning strips (8) and / or between the gear wedges (6) and pressure wedges (7). Linear brake after at least one of the Claims 1 until 7th , characterized in that the gear wedges (6) and / or the pressure wedges (7) and / or the tuning strips (8) consist of a sliding material or are coated with a sliding material and that thus the gear wedges (6) and pressure wedges (7) and / or the gear wedges (6) and tuning strips (8) are in direct contact with one another without linear bearings (4, 5). Linear brake after at least one of the Claims 1 until 10 , characterized in that the transfer plate (9) on the side of the guide rail (F) has resilient transfer lugs (9.1) which are connected via jaw carriers (9.2) or directly to friction shoes (9.3) and that the transfer plate (9) is connected to the brake housing , preferably screw-connected by means of transmission screws (12.3). Linear brake after at least one of the Claims 1 until 11 , characterized in that the transmission plate (9) with the resilient transmission lugs (9.1) is designed and designed so that when the linear brake (LBR) is open, the friction shoes (9.3) resiliently at a distance from the friction surfaces (R) of the guide rail (F ) holds. Linear brake after at least one of the Claims 1 until 10 , characterized in that the transfer plate (9) with the friction jaws (9.3) is arranged to the side of the guide rail (F) and is connected to guide pins (9.4) which are inserted via guide bushes (1.14) or directly into Guide bores (1.13) of the brake housing (1) are stored and which have bolt return springs (2.3) in order to cause the friction shoes (9.3) to be rejected by the guide rail (F) when the linear brake (LBR) is open. Linear brake after at least one of the Claims 1 until 13th , characterized in that several brake systems consisting of spring assemblies (2.1) and piston / cylinder arrangements are arranged one behind the other (in a row) in the direction of movement of the linear brake (LBR) on the guide rail (F). Method for coordinating a linear brake (LBR) for attachment to a slide that can be moved along a guide rail (F), with a brake housing (1) at least partially encompassing the guide rail (F), with an energy store (2.1) arranged on or in the brake housing (1) ), with a brake piston (3) acted upon by the energy store (2.1), the piston ends (3.6) of which overlap the guide rail (F), with gear wedges (6) on both sides of the guide rail (F) in contact with the piston ends (3.6), which, when the brake pistons (3) move in the piston closing direction (P1), are supported by adjusting strips (8) in the brake housing (1) and by pressure wedges (7) on both sides of the guide rail (F), an infeed movement against a brake housing (1) effect connected transfer plate (9) and associated brake shoes (9.3) and thereby clamp the linear brake (LBR) with respect to the guide rail (F), characterized in that during the Installation of the linear brake (LBR) first a guide rail dummy (FD) is inserted between the friction shoes (9.3), that then the friction shoes (9.3) are brought into contact with the guide rail dummy (FD) by a device, that then a first Actual dimension (T1) and a second actual dimension (T2) between the transmission tabs (9.1) of the transmission plate (9) and the housing support surfaces (1.15) are determined that then each of the first actual dimension (T1) and the second actual dimension (T2) a nominal dimension (S) is subtracted for the width of the installation space of the wedge gear, resulting in a first strip thickness (U1) and a second strip thickness (U2) for the tuning strips (8), which are then installed in the linear brake (LBR). Procedure for tuning a linear brake according to Claims 15 , characterized in that an assortment of prefabricated tuning strips with graduated strip thicknesses (U1, U2) is available during assembly, preferably with increments of 0.02mm, from which the tuning strips with the appropriate strip thicknesses (U1, U2) are removed and installed . Procedure for tuning a linear brake according to Claims 15 , characterized in that during assembly there is an assortment of tuning strips with the same strip thickness and provided with a machining allowance, from which two tuning strips are taken, which are processed in a separate processing step to the strip thicknesses (U1, U2) and are then stored in the Brake can be mounted.

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