Coupling device for creating a non-permanent hydraulic connection - Patents.com

Abstract

To provide a fluid coupling device having a very simple structure and requiring almost no installation space, which can also be used in fixed or driven tool holders and other limited installation situations.

Description

[Technical Field]

[0001] In the field of manufacturing technology, fluid-actuated clamping systems are frequently used in driven or fixed tool holders. The tool holder comprises a (centering) receptacle. An adapter or tool is inserted into the receptacle. The clamping system is then activated to clamp the adapter or tool. [Background technology]

[0002] Adapters are frequently used to allow a variety of different tools, such as lathe tools, drill bits, or milling cutters, to be clamped in the same receptacle. These adapters form the interface for the receptacle and the clamping system of, for example, a tool holder. For reasons of linguistic simplicity, the component that is clamped with the fluid-actuated clamping device of the tool holder is called the "adapter," which can be the tool, the tool holder (e.g., a drill chuck), or something else.

[0003] Hereinafter, the term "fluid" includes both liquids (e.g., hydraulic fluids) and compressed gases. "Fluid actuation" accordingly includes both actuation by liquids (e.g., hydraulic mechanisms) and actuation by gases.

[0004] The advantage of fluid clamps is their high clamping force while at the same time having relatively small dimensions. In addition, fluid-operated actuators are very robust and can withstand the harsh conditions of use in manufacturing over long operating times.

[0005] There are clamping systems in which the clamping force is continuously maintained by a compression spring. To release the clamping system, the spring force must be overcome and the tension bolt can be moved from the clamped position to the open position. In this case, the single-acting hydraulic cylinder is also referred to as a "cylinder structure" or simply referred to as a "cylinder". Such a single-acting cylinder has only one hydraulic connection. In clamping systems with an automatic locking function and no spring that applies a clamping force continuously, a double-acting cylinder (structure) is required to be able to move the tension bolt of the clamping system from the open position to the clamped position and back again.

[0006] Additionally, there are clamping systems that are permanently held in a clamped position by pressurized fluid and / or where pressurized fluid serves to fix the clamped position.

[0007] Between machining steps, when the tool holder is not in operation, the adapter can be changed, e.g., to replace a worn cutting tool with a new cutting tool, or to replace a cutting tool used for rotary machining with a cutting tool for drilling.

[0008] Therefore, when a tool holder is not operating in the machining position, another tool holder having its cutting tool in the machining position can simultaneously perform a machining process outside the machining position and replace the adapter of the tool holder that is not operating.

[0009] To be able to perform the desired operation (clamping or unclamping), pressurized fluid must be transferred to the cylinder. Clamping or unclamping of the clamping system occurs when the tool holder is not in operation.

[0010] In either case, the tool holder is located in the workspace at the center of rotation or in another machine tool.

[0011] Supplying fluid from the pump to the cylinder is particularly complicated because the supply line must pass through all of the machine tool shafting, including the tool holder and, in the case of a driven tool, the spindle, which rotates during operation.

[0012] In summary, what is needed is a detachable fluid connection between the fluid supply of the tool holder and the fluid cylinder, which detachable connection will also be referred to below as a coupling device.

[0013] A coupling system is known from European patent EP 1 058 044 B1, by means of which two lines containing pressurized fluids can be detachably connected to one another and then detached again. This coupling system has proven successful in practice. However, it is very complex and requires a large amount of axial installation space.

[0014] The reason is that the first connection (female) has two valves (auxiliary and main control valves) arranged one behind the other. In addition, the second connection (male) has two valves arranged one behind the other. This sequential arrangement of four valves (two main valves and two auxiliary valves) requires a large amount of installation space, is complex to manufacture, and is therefore not practical or usable in conjunction with a tool holder.

[0015] Furthermore, similar coupling systems are known from JP 2017-26131 A and US 2010 0 096 032 A1.

[0016] In these systems, it is assumed for perfect function that the two links are positioned perpendicular to each other and centrally one above the other, which means that there are no angular or positional deviations. Summary of the Invention

[0017] The object of the present invention is to provide a connection device for pressurized fluid, by means of which a tool holder having a fluid-actuated clamping system can be temporarily supplied with pressurized fluid in a simple, reliable and space-saving manner.

[0018] Furthermore, the detachable coupling device is easy to operate between the fluid supply device and the tool holder and / or spindle, operates in a space-saving manner, and functions reliably. Furthermore, it tolerates small angular and positional deviations, for example, to allow for radial transmission in rotationally symmetric components such as spindles. Furthermore, the coupling device reliably seals the interface in the uncoupled state, keeping leakage as low as possible.

[0019] Automatic tool changes in the tool holder (e.g., with the assistance of a handling robot or robotic arm) must also be supported or enabled.

[0020] According to the invention, a fluid coupling device is provided, comprising a first coupling and a second coupling cooperating with the first coupling, the first coupling being designed as a spring-loaded double check valve, the second coupling comprising an actuator piston displaceably guided in a housing, on which an outwardly opening directional valve is arranged, the actuator piston dividing a cylinder bore into a first cylinder chamber and a second cylinder chamber, the actuator piston having a (spherical / barrel-shaped) conical section or an inner dome section at its end facing the first coupling, and the first coupling having a shoulder at its end facing the second coupling.

[0021] The coupling device according to the invention is designed, as usual, in two parts: a first coupling part, most commonly integrated in the part to be supplied with fluid, and a second coupling part, provided on the supply side.

[0022] In the embodiment as is, the first connection can be arranged on the tool holder or on the spindle, while the second connection can be integrated into a feeding bracket that is part of the handling device or robot hand.

[0023] When it's time to change the tool in the tool holder, the robot arm moves the supply bracket very close to the tool holder, so that the second connection of the power supply bracket and the first connection of the tool holder are opposite each other, with a gap of a few millimeters between them. Naturally, additional positioning stops or pins can be integrated into the supply bracket to allow for more accurate pre-positioning.

[0024] If fluid must be supplied to the spindle (e.g., the driven tool holder), the second connection can instead be installed in a housing surrounding the spindle, with the fluid then being supplied from the machine tool to the housing of the driven tool holder and from there through the second connection to the first connection of the spindle.

[0025] However, it is also advantageous to supply the housing of the driven tool holder with fluid via the described supply bracket and at least one first coupling device, from where the fluid can pass to the spindle to the clamping system via a fluid connection present inside the housing and at least one second pairing (coupling device) of second and first connections.

[0026] The coupling device according to the present invention allows both the first and second couplings to have a very simple structure and compact size. The first coupling is ultimately a double check valve, the valve member of which is externally accessible. In the method according to the present invention, the outward-opening valve tappet of the second coupling opens "automatically" as soon as the actuator piston of the second coupling contacts the first coupling.

[0027] The second connection according to the invention provides a displaceable actuator piston, which can be moved (hydraulically, mechanically or electrically) a few millimeters in the direction of the first connection. The actuator piston is an independent moving shaft of the second connection, which allows the coupling to be closed and reopened.

[0028] The actuator piston contains a directional valve with an outward-opening valve tappet. The valve tappet of the directional valve is connected or coupled to the actuator piston. The valve seat of the directional valve is displaceable relative to the actuator piston. In this way, the directional valve is said to have an "inward-opening valve seat," and the combination of the actuator piston and the inward-opening valve seat allows movement of the actuator piston to open the directional valve in the second connection by a few millimeters and open the check valve in the first connection in the same movement.

[0029] As soon as the actuator piston returns (hydraulic or via a spring), the directional valve and check valve close. The two parts of the coupling are hydraulically closed to each other and to the surroundings. No fluid can escape to the surroundings or be exchanged between the couplings.

[0030] Thus, for example, if the above-described feed bracket is brought by the robot hand into a position where the second coupling (of the feed bracket) is directly in front of the first coupling of the tool holder, and the two couplings are aligned with each other but not yet touching, the actuator piston can move in the direction of the first coupling.

[0031] As soon as the actuator piston contacts the valve housing of the first connection, a hydraulic connection exists between the first connection and the second connection. Further, movement of the actuator piston opens the check valve in the first connection and the directional valve in the second connection.

[0032] Check valves are opened by lifting the valve member of the first connection inward from its seat, while directional valves are opened by lifting the valve seat off the fixed valve tappet.

[0033] The second connection requires only one valve, a directional valve that opens outwards. Due to this very simple design, the manufacturing costs are relatively low and, above all, the installation space requirements are low.

[0034] Considering that the second linkage is part of a handling system, e.g. a robot hand, only one supply bracket with one (number) second linkage (e.g. for actuating a single-acting cylinder) or two (number) second linkages (e.g. for actuating a double-acting cylinder) is / are required for each machine tool.

[0035] The supply bracket may also have more than one secondary connection if additional fluid is supplied to the tool holder or spindle via the supply bracket. For example, additional secondary connections may provide compressed gas to ensure flat contact with the adapter receptacle, monitor or confirm completion of the clamping process, or allow cleaning of the contact surfaces.

[0036] All tool holders present in the workspace of the handling device or robot hand can be reached as needed. The coupling device according to the invention can be closed, and the clamping system of the tool holder can be released or clamped as needed. When the clamping system is removed, the adapter with the tool to be replaced can be removed from the receptacle of the tool holder and an adapter with a new tool can be inserted into the receptacle, for example to replace a blunt tool or to replace an adapter with a drill with an adapter with a milling cutter. The clamping system is then moved into the clamping position, and the tool holder is again ready for use. As already explained, this can also be done while adjacent tool holders are performing machining operations.

[0037] The coupling device according to the invention has a simple design and requires little installation space. It should also be mentioned that this coupling device does not require any modifications or interventions in the machine tool for clamping and unclamping the clamping system of the tool holder. Therefore, automatic tool changes are possible on standard machines / machine tools. Retrofitting of existing machines with automatic tool changes is also possible.

[0038] An advantage is therefore that the supply of the fluid clamping system of the tool holder is carried out "outside" the machine tool, for example by a handling robot equipped with a supply bracket according to the invention and having a moving shaft that is integrated in the supply bracket and can be controlled independently. No intervention or modification of the machine tool using the tool holder is necessary. However, the coupling device according to the invention can also be used as a supplement to a fluid line through the machine, for example from the housing to the spindle of the driven tool.

[0039] Due to the (spherical / barrel-shaped) inner cone or inner dome, the actuator piston centers itself and also centers the second connection on the shoulder of the first connection. This measure significantly increases the reliability of the connection device and allows it to be used even under "harsh" industrial conditions.

[0040] According to an advantageous development of the invention, the clearance between the cylinder bore and the actuator piston at the end of the actuator piston facing away from the first connection is smaller than the clearance between the cylinder bore and the actuator piston at the end facing the first connection, so that the actuator piston can tilt slightly when centered on the conical shoulder of the first connection.

[0041] In a preferred embodiment, the fluid chamber of the second connection opens into a guide bore in which a sleeve-shaped valve seat of the directional valve is displaceably accommodated, and a valve tappet of the directional valve is connected to the actuator piston and protrudes through the sleeve-shaped valve seat.

[0042] In a preferred embodiment, the valve tappet is designed with a valve plate that limits the outward movement of a movable valve seat (e.g. in the form of a press fit or a movable seat ring) in the guide bore of the actuator piston.

[0043] Optionally, the valve seat can still be opened via a stop on the actuator piston, which is particularly important if hydraulic pressure is present in the second connection but the first connection is not provided as a mating part, for example if the supply bracket is incorrectly positioned.

[0044] This means that pressurized fluid in the actuator piston's fluid chamber forces the seat ring of the valve seat to seal against the valve plate of the valve tappet, thus closing the directional valve. Both valves (directional valve and check valve) open only when the second connection is seated on the first connection.

[0045] To ensure that the valve seat is pressed against the valve plate of the valve tappet under all circumstances, even when the fluid chamber is not pressurized, in an advantageous development a second compression spring is arranged in the fluid chamber, which compression spring presses the valve plate of the valve seat against the valve plate of the valve tappet.

[0046] The above object is also achieved by a fluid connection device consisting of a first connection part and a second connection part cooperating with the first connection part, the first connection part being designed as a spring-loaded double check valve, the second connection part having an actuator piston displaceably guided in a housing, the actuator piston being designed as a stepped piston, a first part of the actuator piston defining the first cylinder chamber and a second part of the actuator piston defining a third cylinder chamber, the diameter D23.1 of the first part being smaller than the diameter D23.2 of the second part of the actuator piston, so that an annular surface is generated in the third cylinder chamber.

[0047] In a further advantageous development, a first seal is provided at the end of the actuator piston facing away from the first connection and a second seal is provided at the end of the actuator piston facing towards the first connection, the second seal being radially flexible so as to seal the second cylinder chamber even if the actuator piston is tilted or offset relative to the cylinder bore, thereby ensuring good sealing of the second connection even under unfavourable conditions (when the actuator piston is tilted).

[0048] In an advantageous embodiment of the invention, a fluid chamber is formed in the actuator piston, the fluid chamber being closed at one end and fluidly connected to a fluid supply via a circumferential groove and at least one radial bore present on the exterior of the actuator, for example via a supply line in the housing of the supply bracket, through which fluid (e.g., hydraulic oil) can be provided by the fluid assembly at a desired pressure.

[0049] To enable the actuator piston to move back and forth in a desired manner within the cylinder bore of the housing, the actuator piston can divide the cylinder into a first cylinder chamber and a second cylinder chamber, the first cylinder chamber being capable of being supplied with fluid via a controllable first control line and the second cylinder chamber being capable of being supplied with fluid via a controllable second control line.

[0050] The actuator piston moves back and forth through the cylinder bore depending on which control line carries the pressurized fluid. As a result, for example, by activating one of the control lines, it is possible to move the actuator piston, and with it the directional valve, toward the first connection. In this way, the actuator piston is moved in the desired direction without moving the robot hand. As a result, the distance between the first and second connections that exists before the connection process can be eliminated, and a fluid connection between the first and second connections can be created.

[0051] The actuator piston, which houses the fluid chamber, the second compression spring and the outwardly opening directional valve according to the invention, allows for a very compact and in particular very short design to be achieved. Furthermore, the actuator piston and directional valve according to the invention are easy to manage in terms of the production process, so that they can be made available at a relatively low cost and with a long service life.

[0052] A sleeve-shaped valve seat is guided by the actuator piston. A valve tappet of a directional valve, connected to the actuator piston, projects through this valve seat. A valve plate of the valve tappet defines the passage of the valve seat in the guide bore.

[0053] It is particularly advantageous if the valve seat includes a sleeve and a seat ring accommodated and guided in the sleeve, along with a spring element. One end of the spring element is supported against the sleeve, and the other end is supported against the seat ring. As a result, the angular offset between the first and second coupling parts can be compensated for without impairing the function of the coupling device. This angular compensation according to the present invention expands the scope of use to applications in which the first coupling element is mounted on a rotatably mounted spindle. This allows compensation for errors that frequently occur when positioning the spindle.

[0054] In the case of a coupling device, a second compression spring can be arranged in the fluid chamber, in which case the spring force exerted by the second compression spring on the valve seat acts against a defined stop or, if the spring element has a higher spring force than the second compression spring, acts against the valve plate of the valve tappet.

[0055] In an advantageous embodiment of the coupling device according to the invention, the check valve of the first coupling part comprises a valve housing, an opening for the fluid is connected to the check valve, the opening is formed in the valve housing, the opening opens onto a shoulder of the valve housing, and when the coupling device is closed, the shoulder enters the guide bore of the second coupling part.

[0056] As a result of this very simple and robust solution, the shoulder of the first connection brings about the opening of the directional valve in the second connection as soon as the actuator piston of the second connection moves in the contact direction of the first connection or its shoulder, with the directional valve opening outwards.

[0057] At the same time, the valve tappet in the second connection presses against the valve member and the first compression spring in the first connection, causing the seal ring to lift off the valve housing and expose the check valve opening.

[0058] Alternatively, the end faces of the valve housing and actuator piston can be designed as a pair of centering cones (male / female, female / male).

[0059] Of course, other centering pairings are possible, such as dome-shaped pairings, or combinations of conical and dome-shaped or sphero-conical profiles.

[0060] In an advantageous development, the fluid chamber is fluidly connected to and supplied with fluid via a circumferential groove present on the outside of the actuator piston and at least one radial bore to a supply pipe of the housing, at least in the open position of the directional valve, where the valve plate is not resting on the valve seat.

[0061] Optionally, the first cylinder chamber can be supplied with fluid via a first control line, and (also optionally) the second cylinder chamber can be supplied with fluid via a second control line.

[0062] In a particularly advantageous embodiment of the second connection, a third compression spring is arranged outside the second cylinder chamber or housing, the spring force of which acts on the actuator piston and counteracts the force of the fluid in the first cylinder chamber.

[0063] The fluid chamber can be supplied with fluid via a supply line or a combined control and supply line. Preferably, the third cylinder chamber and the fluid chamber are simultaneously supplied with fluid via a control and supply line. This allows for a very compact design and reduces manufacturing effort. In an advantageous development, the coupling device according to the invention has a throttle or diaphragm between the fluid chamber and the directional valve. As a result, when the directional valve is open, the outflow of pressurized fluid from the fluid chamber is restricted, thereby maintaining a minimum overpressure in the fluid chamber and the third cylinder chamber. As a result, the actuator piston remains in the open position. The throttle can be designed as an annular gap between the valve tappet and the valve seat or its sleeve.

[0064] The machining space of a machining operation is always limited. However, the second connection requires a certain amount of space to provide the required actuation force at a specified fluid pressure. The development according to the present invention, in which at least a second portion of the actuator piston has an oval or elliptical cross section and at least a second portion of the cylinder bore also has an oval or elliptical cross section, provides a way around this dilemma. For the same area of ​​the second portion of the actuator piston, the total length of the second connection in one direction is reduced. This reduction makes it possible to use the coupling device according to the present invention in some applications, even under limited conditions.

[0065] An advantageous design of the first connection part relates to the check valve. It comprises a valve housing with a fluid opening formed therein, which is hydraulically connected to a check valve. The opening is formed in a shoulder of the valve housing, so that when the connection device is closed, the shoulder dips into the guide bore of the second connection part, lifting the valve seat of the directional valve off the valve plate of the valve tappet, and opening or closing the line or spindle of the housing by the check valve. If the shoulder of the valve housing is designed to be frustoconical or dome-shaped, the centering between the first connection part and the second connection part is further improved.

[0066] The coupling device according to the invention can be used in various arrangements. It is preferred if the second coupling is arranged on the supply bracket. The supply bracket, in turn, comprises a housing with a cylinder bore for receiving the actuator piston.

[0067] When the tool holder clamping system provides a double-acting fluid cylinder, two first connections are integrated into the tool holder. The supply bracket also has two second connections. The second connections are then positioned so that the second and first connections are positioned opposite each other without changing the position of the supply bracket. Depending on whether the clamping system is open or closed, one of the connections functions as a fluid supply and the other as a fluid discharge, or vice versa.

[0068] If the tool holder clamping system provides a single-acting hydraulic cylinder, only one first connection is integrated into the tool holder, and the supply bracket only requires one second connection.

[0069] However, it is also possible for a feed bracket according to the invention with two or more second connections to work with only one first connection. The second connection of the feed bracket is then positioned a short distance in front of the first connection of the tool holder. The connection is closed by the targeted actuation of the actuator piston belonging to this second connection.

[0070] The present invention can be used in a fixed tool holder that includes a housing, at least one centering receptacle disposed in the housing for receiving an adapter, and a fluid-actuated clamping system for clamping and releasing the adapter from the centering receptacle, wherein a first coupling is present in the housing and interacts with a second coupling of a feed bracket.

[0071] In a corresponding manner, the coupling according to the present invention may also be used in a driven tool holder comprising a housing, a spindle mounted to the housing, at least one centering receptacle arranged on the spindle for an adapter, and a fluid-actuated clamping system for clamping and releasing the adapter from the centering receptacle.

[0072] In a preferred embodiment, at least one first connection is provided on the spindle, preferably on the collar of the spindle.

[0073] In a further preferred embodiment, it is provided that at least one of the second connections is installed in a housing surrounding the spindle and is supplied with fluid via the housing and adjacent components (e.g. components of a machine tool or handling system).

[0074] To minimize the mechanical load on the spindle due to the actuator piston approaching the valve housing or the valve tappet approaching the valve member, it is advantageous, especially in double-acting hydraulic clamping systems, to position the two first couplings opposite each other on the spindle, thus offset by 180°. Then, when the second couplings simultaneously approach the two first couplings on the spindle, the radial forces acting on the spindle cancel each other out, and the spindle bearings are subjected to only a very small load. Furthermore, deflection of the spindle due to radial forces is prevented. When more than two coupling systems are used, the spindle's position and orientation relative to the actuator forces acting on it are selected so that the resulting forces largely cancel each other out.

[0075] In a particularly advantageous embodiment of the supply bracket with two second connections, these second connections (hereinafter designated number 1 and number 2) are connected in opposite directions to the fluid lines of the supply bracket. In the case of a second connection in which a control line and a combined control supply line are connected, for example, the control line of second connection number 1 and the control line of second connection number 2 are connected to the same fluid line, and vice versa. The extension of the actuator piston can be achieved via two hydraulically separated pistons of the actuator piston, one of which is connected to a fluid chamber. The return of the actuator piston to its uncoupled position is achieved via a spring.

[0076] Using this "backward" coupling configuration, two fluid lines can actuate the cylinder structure of the tool holder in the following manner. The piston and the piston rod move in both directions. The movement of the piston expels the fluid displaced by the cylinder structure, The volume change of the first cylinder chamber or the third cylinder chamber is compensated for by one of the two second connections.

[0077] Further advantages and advantageous embodiments of the invention can be found in the following drawings, the description and claims. All features disclosed in the drawings, the description and the claims may be essential to the invention both individually and in any combination. [Brief explanation of the drawings]

[0078] [Figure 1] FIG. 1 shows a cross section through an embodiment of a coupling device according to the invention in an open state. [Figure 2] FIG. 2 shows the same coupling device in a closed position. [Figure 3] FIG. 3 shows a tool holder and a robot hand, in particular equipped with a feeding bracket according to the invention. [Figure 4a] FIG. 4a shows a view from the front of the centering receptacle of the tool holder according to FIG. [Figure 4b] FIG. 4b shows a view from the front of the centering receptacle of the tool holder according to FIG. [Figure 5] FIG. 5 shows a section through a driven tool holder with two coupling devices and an installed spindle. [Figure 6] FIG. 6 shows a section through a second embodiment of a coupling device according to the invention in the closed state. [Figure 7] FIG. 7 shows a section through a third embodiment of a coupling device according to the invention. [Figure 8] Figure 8 shows a section through the third embodiment in a closed state. [Figure 9] FIG. 9 shows a cross section of the third embodiment in an open state, with offset and angular error. [Figure 10] FIG. 10 shows a section through the third embodiment in a closed state to illustrate the present invention's compensation of offset and angular errors. [Figure 11] FIG. 11 shows two sections through a fourth embodiment having an elliptical actuator piston. [Figure 12-1] FIG. 12-1 shows the integration of the second embodiment in the tool holder and its coupling configuration in two views. [Figure 12-2] FIG. 12-2 shows the integration of the second embodiment in the tool holder and its coupling configuration in two views. [Figure 13-1] FIG. 13-1 shows the integration of the second embodiment in the supply bracket and its coupling configuration in two views. [Figure 13-2] FIG. 13-2 shows the integration of the second embodiment in the supply bracket and its coupling configuration in two views. [Figure 14-1] FIG. 14-1 illustrates the transfer of fluid to the cylinder structure of the tool holder according to the present invention. [Figure 14-2] FIG. 14-2 illustrates the transfer of fluid to the cylinder structure of the tool holder according to the present invention. [Figure 14-3] FIG. 14-3 illustrates the transfer of fluid to the cylinder structure of the tool holder according to the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0079] Figure 1 shows a coupling device according to the invention in an open state. The coupling device comprises a first coupling part 1 and a second coupling part 3. The first coupling part 1 is shown in the lower part of Figure 1, and the second coupling part 3 in the upper part of Figure 1. As has already been mentioned several times in the description, the coupling device according to the invention can be used in many different configurations.

[0080] In Figure 1, the first connection 1 is integrated into the toolholder spindle 5, as shown in more detail in Figure 5. Figure 1 shows only a small cross section of the spindle 5 so that the structural features of the first connection 1 and the second connection 3 can be clearly seen.

[0081] The first connection 1 comprises a check valve 7, the valve member 9 of which is held and guided in a valve housing 11. The valve housing 11 is screwed onto the spindle 5 by means of a screw thread. Alternatively, the check valve 7 can be connected by a press fit or a snap fit.

[0082] A shoulder 13 with an opening 15 that is closed in this position is formed at the upper end of the valve housing 11 in Figure 1. In this embodiment, a sealing ring 16 is disposed on the valve member 9 and acts together with a conical valve seat (not numbered) in the valve housing 11. The valve member 9 is pressed against the valve seat by a first compression spring 17, designed as a Belleville spring assembly, so that the check valve 7 is closed in the position shown in Figure 1.

[0083] The top part of Figure 1 shows the second coupling part 3, which is for example integrated into the housing 113 of the tool holder 111. A cylinder bore 21 is present in the housing 113. The actuator piston 23 is guided in a way that provides both movement and sealing for the cylinder bore 21.

[0084] The actuator piston 23 divides the cylinder bore 21 into a first cylinder chamber 25 and a second cylinder chamber 27. A first control line 29 opens into the first cylinder chamber 25. If pressurized fluid is present in this first control line 29, the volume of the first cylinder chamber 25 increases, and the first actuator piston 23 moves downwards in FIG. 1 until it comes to rest on the plane (not numbered) of the first connection 1, or on a shoulder (not numbered) of the cylinder bore 21 if this first connection 1 is not present as a connection partner (for example, because the spindle 5 is in an incorrect rotational position). The lowering end position is then reached. In this case, fluid is expelled from the second cylinder chamber 27 via a second control line 31.

[0085] To return the actuator piston 23 from its lower end position to its upper end position shown in Figure 1, pressurized fluid is directed in a corresponding manner to the second cylinder chamber 27 via the second control line 31. At the same time, fluid is expelled from the first cylinder chamber 25 via the first control line 29.

[0086] A fluid chamber 33 is formed inside the actuator piston 23. This fluid chamber 33 is self-closed. Fluid can only be supplied to the fluid chamber 33 via a radial bore 37 and a circumferential groove 39 located on the outside of the actuator piston 23. In this embodiment, the circumferential groove 39 is arranged and dimensioned such that there is always a fluid connection between the supply line 41 of the housing 19 and the circumferential groove 39, regardless of the position of the actuator piston 23 in the cylinder bore 21. However, this fluid connection, if it exists, is sufficient and particularly advantageous only when the actuator piston 23 is in its lower end position (FIG. 2). In particular, the coupling device is closed.

[0087] A second compression spring 43 is clamped in the fluid chamber 33 and presses a sleeve-shaped valve seat 45 towards the first connection 1 or towards the valve plate 51 of the valve tappet 49 (downwards in FIG. 1).

[0088] The sleeve-shaped valve seat 45 is guided in a manner that allows it to move and provides a seal in the guide bore 47 of the actuator piston 23. Like the valve seat of the check valve 7, it has a seat ring 45.2, preferably made of plastic or rubber. The valve tappet 49 of the directional valve is fixedly connected to the actuator piston 23. The valve tappet 49 has at its lower end a relatively long, thin cylindrical shaft on which the already mentioned valve plate 51 is formed.

[0089] 1, the valve seat 45 is in its closed position. That is, the second compression spring 43 presses the valve seat 45 together with the seat ring 45.2 against the valve plate 51 of the valve tappet 49. In this position of the valve seat 45, fluid cannot flow from the supply line 41 through the fluid chamber 33 in the direction of the first connection 1. The directional valve of the actuator piston 23 is closed.

[0090] At this point, when pressurized fluid is supplied to the first cylinder chamber 25 via the first control line 29, the actuator piston 23 moves downward in Figure 1, as shown in Figure 2. For clarity, only a few reference numbers are shown in Figure 2.

[0091] It can be seen that the valve tappet 49 is connected to the actuator piston 23 and therefore synchronizes with the movement of the actuator piston 23. As soon as the actuator piston 23 moves slightly downwards, the valve seat 45 comes into contact with the shoulder 13 of the first connection part 1.

[0092] The valve seat 45 cannot follow the movement of the actuator piston 23 due to the shoulder 13. The second compression spring 43 is compressed and lifts the valve seat 45 from the valve plate 51 of the valve tappet 49. As a result, the directional valve of the second connection 3 opens.

[0093] At the same time, however, the valve tappet 49 of the directional valve also ensures that the check valve 7 of the first connection 1 is also opened. This is achieved by the valve tappet 49 of the second connection 3, which is connected to the actuator piston 23, pressing the movable valve member 9 of the check valve 7 in the first connection 1 downwards against the force of the first compression spring 17 (in FIG. 2) and opening it.

[0094] In this way, a fluid connection is formed between the first connection 1 and the second connection 3 .

[0095] As is clear from Figure 2, there is only a small leakage volume between the shoulder 13 of the first connection part 1 and the guide bore 47 of the actuator piston 23. The resulting potential leakage rate is very low.

[0096] When the coupling is to be reopened, pressurized fluid is applied to the second control line 31, causing the actuator piston 23 to move upward in the cylinder bore 21. This in turn causes the valve tappet 49 of the second coupling 3 to move upward, causing the valve member 9 of the check valve 7 to move upward against the valve seat by the first compression spring 17, closing it.

[0097] In a corresponding manner, the valve seat 45 of the second connection 3 also moves relative to the actuator piston 23 (downwards in FIGS. 1 and 2), closing the directional valve of the second connection 3 .

[0098] 1 and 2 illustrate the function of the actuator piston 23 as an independent moving shaft for closing and opening the coupling device according to the invention, and the actuator piston 23 can be actuated electrically, magnetically or electromechanically.

[0099] In order to explain various aspects in which the coupling device according to the present invention can be used, various configurations are shown below with reference to FIGS.

[0100] 3 shows a robot hand 101 that can be mounted on an industrial robot (not shown), which comprises several assemblies, of which the feeding bracket 53 according to the invention is of particular interest.

[0101] A movable gripper 103 is attached to the robotic hand 101, and Figure 3 holds an adapter 105 with a cutting tool 107 (shown here as a drill) and a hollow shaft 109. This adapter 105 is shown for illustrative purposes only; the invention is not limited to this type of adapter 105.

[0102] Gripper 103 serves to insert adapter 105 into centering receptacle 63 of tool holder 111 (shown in partial view) or to remove it when required. The fluid connection between supply bracket 53 and tool holder 111 does not need to be removed for this purpose.

[0103] In the case of a driven tool holder 111, the centering receptacle 63 is located on the rotatably mounted spindle 5 (see Figures 4 and 5). In the case of a fixed tool holder, the centering receptacle 63 is located in the housing 113 of the tool holder 111.

[0104] A fluid-actuated clamping system must be actuated on the spindle 5 of the tool holder 111 so that the gripper 103 can insert the adapter 105 into the centering receptacle 63 or, if necessary, remove it. The clamping system shown in FIG. 3 comprises multiple clamping segments arranged around a tension bolt. Axial movement of the tension bolt relative to the spindle 5 opens and clamps the clamping system. The movement of the tension bolt and the actuation force required for clamping the clamping system are also provided by the fluid-actuated, single-acting or double-acting cylinder arrangement described above.

[0105] The supply of the clamping system or the supply of the cylinder structure with pressurized fluid (and possibly the removal of fluid from the pressure chamber of the cylinder structure) is carried out by a supply bracket 53 according to the invention.

[0106] In FIG. 3, the supply bracket 53 and the docking part 115 of the spindle 5 are partially shown so that the two second coupling parts 3 and the two first coupling parts 1 are visible.

[0107] Without going into the structural details of the spindle 5, it should only be pointed out that the spindle 5 according to this embodiment has at its front end a collar 65. The two first coupling parts 1 are arranged opposite each other at the collar 65.

[0108] 4a and 4b show in side view two variants of the feeding bracket 53. The feeding bracket 53 according to FIG. 4a comprises an approximately semicircular or C-shaped docking part 115 with two second connecting parts 3.

[0109] The feeding bracket 53 according to FIG. 4b comprises a substantially semicircular or C-shaped docking portion 115 with three second connecting portions 3.

[0110] Thus, two or three first connections 1 are provided in the spindle 5 and / or housing 113 of the stationary tool holder 111 .

[0111] 4a and 4b show the same situation as in FIG. 3, but from a different viewing direction towards the spindle 5, with its centering receptacle 63 and the docking part 115 of the supply bracket 53.

[0112] 4a and 4b, it can be clearly seen that the docking portion 115 surrounds the collar 65, with the second coupling portions 3 of the docking portion 115 positioned opposite each of the first coupling portions 1 of the collar 65.

[0113] When two couplings (FIG. 4a) or three couplings (FIG. 4b) are open, the actuator piston 23 of the second coupling 3 is in the position shown in FIG.

[0114] When two connections (FIG. 4a) or three connections (FIG. 4b) are closed, the actuator piston 23 of the second connection 3 is in the position shown in FIG.

[0115] By actuating one or more actuator pistons 23 in a targeted manner, one or more coupling devices can be closed or opened independently of the others. This is done by targeted and individual actuation of the actuator pistons 23 of the second coupling 3. The feeding bracket 53 and / or the docking part 115 do not change their position. Meanwhile, the gripper 103 of the robot hand 101 can insert or remove the adapter 105 from the centering receptacle 63.

[0116] This allows for automatic changing of the adapter 105, which simultaneously releases and clamps the fluid-actuated clamping system of the spindle 5.

[0117] Thus, two second coupling parts 3 are arranged opposite each other in the C-shaped docking part 115 of the supply bracket 53. If the robot hand 101 is positioned relative to the spindle 5 and the supply bracket 53 such that the first coupling part 1 of the spindle 5 and the second coupling part 3 of the supply bracket 53 are opposite each other, the actuator pistons 23 of the second coupling parts 3 can move radially inward towards the first coupling parts 1, thereby closing the coupling device in the manner described with reference to FIG.

[0118] Two mutually facing second couplings 3 according to Figures 1 and 2 are shown in Figure 4a. As a result, the radial forces exerted on the spindle 5 by the second couplings 3 and / or their actuator pistons 23 cancel each other out when the coupling is closed. The mount of the spindle 5 is unloaded.

[0119] Three opposing second couplings 3 according to Figures 1 and 2 are shown in Figure 4b. In this embodiment, the three coupling devices are arranged in such a way that the forces arising from the actuator piston allow complete or virtually complete compensation for the radial forces acting on the spindle 5.

[0120] 5 shows a further embodiment of the application of the coupling device according to the invention, and the cross section shows a spindle 5 having a centering receptacle 63. The first coupling part 1 is not located on the collar 65, but rather on the spindle between the bearings of the spindle 5.

[0121] In this embodiment, each of the two second connections 3 is located in the housing 113 between the bearings and can independently actuate the actuator pistons 23. Again, the actuator pistons 23 are positioned such that when the actuator piston 23 opens the directional valve of the second connection 3, it opens the associated check valve 7 of the first connection 1 of the spindle 5.

[0122] Of course, the example shown on the basis of Figures 3 to 5 is not exhaustive but is intended merely to illustrate by way of example how the first connecting part 1 and the second connecting part 3 must be positioned relative to one another in order to be able to open and close the connecting device according to the invention when the actuator piston 23 is actuated.

[0123] A combination of Figures 4a, 4b and 5 is also possible and convenient, in which case the fluid is led to the tool holder 111 via the embodiment according to Figure 4a or 4b, and then from the housing 113 to the spindle via the embodiment according to Figure 5.

[0124] 6 shows a second embodiment of the second connecting portion 3 according to the present invention. In various embodiments, the same components are given the same reference numerals. In the following description of the second connecting portion 3, the terms "upper" and "lower" are used. In this case, "lower" refers to the location where the first connecting portion 1 is located.

[0125] The second embodiment requires only one control line 29 and an associated control supply line 32, and unlike the first embodiment, no separate supply line (41 in Figure 1) is required.

[0126] The following describes the differences from the first embodiment, and for other points, refer to the description of the first embodiment.

[0127] The actuator piston 23 is designed as a stepped piston. Accordingly, the cylinder bore 21 is also designed as a stepped bore. An upper part 23.1 of the actuator piston 23, having a diameter D23.1, is sealingly guided in a portion 21.1 of the cylinder bore 21. This portion 21.1 is formed as a blind bore in a cover 24 that is screwed onto the housing 19. A lower part 23.2 of the actuator piston 23, having a diameter D23.2, is sealingly guided in a portion 21.2 of the cylinder bore 21. This portion 21.2 is formed in the housing 19.

[0128] The diameter D23.2 of the "lower" portion is larger than the diameter D23.1 of the "upper" portion (D23.2>D23.1).

[0129] This means that the lower part 23.2 located under the cover 24 has an annular surface 69 whose projected hydraulically effective annular surface A69 is equal to the difference between the circular surface A23.2 of the lower part 23.2 of the actuator piston 23 and A23.1 of the upper part 23.1 of the actuator piston 23.

[0130] The space bounded by the second part 23.2 of the actuator piston 23 and the annular surface 69 is also referred to as the third cylinder chamber 39.

[0131] It is structurally possible for the surface A 23 . 1 of the upper part 23 . 1 of the actuator piston 23 to be equal to the annular surface 69 .

[0132] As a result, the circumferential groove 39 according to this embodiment functions as a third cylinder chamber 39, and may also be referred to as such.

[0133] The stepped design of the actuator piston 23 has the following advantages:

[0134] 1) When pressure is applied to the first control line 29, the fluid under pressure in the first cylinder chamber 25 exerts a hydraulic force on the actuator piston 23, which moves downwards against the force of the disc spring 67 (position shown in Figure 6), thus establishing a fluid connection between the first connection 1 and the second connection 3. Then, the fluid can flow out of the first connection 1 in an unpressurized state, via the combined control supply line 32, through the fluid chamber 33, the radial bore 37 and the third cylinder chamber 39.

[0135] 2) When pressure is applied to the control supply line 32, the fluid under pressure in the third cylinder chamber 39 exerts a hydraulic force on the actuator piston 23, which in turn moves downwards against the force of the disc spring 67 (to the position shown in Figure 6), establishing a fluid connection between the first connection 1 and the second connection 3. The fluid can then reach the fluid chamber 33, for example via the radial bore 37, and from there be conducted to the first connection. 3) When pressure is applied to the first control line 29 and the control supply line 32, the forces from the two cylinder chambers are applied and the pressurized fluid exerts a hydraulic force on the actuator piston 23, which moves it downwards (to the position shown in Figure 6) against the force of the disc spring 67 and a fluid connection is established between the first connection 1 and the second connection 3.

[0136] In other words, pressure only needs to be present in one of the cylinder chambers 25, 39 to cause the actuator piston 23 to extend.

[0137] If the surface A23.1 of the upper part 23.1 of the actuator piston 23 is equal to the annular surface 69, then, assuming the same pressure conditions, the fluid forces acting on the actuator piston 23 in both cases will be equal in magnitude and directed in the same direction.

[0138] In the first embodiment, a fluid connection is provided for the second cylinder chamber 27. In the second and third embodiments, a disk spring 67 is present in the second cylinder chamber 27, which, when the first control line 29 or the control supply line 32 is depressurized, moves the actuator piston 23 to a defined position, i.e., upwards, so that the directional valve is closed. In addition to the disk spring 67, the second cylinder chamber 27 may also be supplied with pressurized fluid at least once via another control line (not shown).

[0139] Between the inner diameter of the sleeve-shaped valve seat 45 and the outer diameter of the shaft of the valve tappet 49 there is a cylindrical gap 75, the plane of which is designated A1. When the directional valve is open, fluid flows through this gap from the fluid chamber 33 to the first connection 1 or from the first connection 1 to the fluid chamber 33.

[0140] Plane A1 is less than cross-sectional plane A2 of control supply line 32, which supplies or drains fluid to or from fluid chamber 33. As a result, the gap between the inner diameter of valve seat 45 and the outer diameter of the shaft of valve tappet 49 functions as a diaphragm or throttle 75. It restricts the outflow of fluid from fluid chamber 33 through the open directional valve, keeping the pressure in fluid chamber 33 at a sufficiently high level so that the coupling device remains closed, and therefore actuator piston 23 remains in the "open position."

[0141] FIG. 7 shows a second embodiment of a second coupling part 3 according to the invention.

[0142] Similarly, the third embodiment requires only one control line 29 and the control and supply connection line 32 does not require a separate supply line 41 .

[0143] Also, the structural and hydraulic properties of the third embodiment correspond to those of the second embodiment, and therefore, to avoid repetition, the differences with respect to the second embodiment shown in Figure 6 will be described in more detail below.

[0144] In the third embodiment, a conical section 77 is provided at the end of the actuator piston 23 facing the first connecting part 1. This conical section 77 can be designed as a spherical cone or a dome. The first connecting part 1 has a dome-shaped or frusto-conical shoulder 13.

[0145] When the actuator piston 23 extends towards the first link 1, the cone 77 centres the actuator piston 23 on the shoulder 13. In this way, it is possible to compensate for an offset between the first link 1 and the second link 3. Such an offset, which may be, for example, 0.5 mm or 1 millimetre (1 mm), may result from positioning inaccuracies of the robot hand guiding the second link 3.

[0146] In order to enable the actuator pistons 23 to be tilted or pivoted by a small angle (for example, up to 3°), it is optionally possible to make the gap between the actuator pistons 23 in the region of the first part 21.1 of the cylinder bore 21 smaller than the gap between the actuator pistons 23 in the region of the second part 21.2 of the cylinder bore 21.

[0147] A seal 79 is arranged in a groove in the cover 24 in the region of the first portion 21.1 of the cylinder bore 21. A seal 81 is arranged in a groove in the actuator piston 23 in the region of the second portion 21.2 of the cylinder bore 21. The seal 81 is designed to seal the third cylinder chamber 39 against the second cylinder chamber 27 even in the case of an inclined position of the actuator piston 23 and / or an axial offset of the actuator piston 23 relative to the cylinder bore 21.

[0148] In this way, angular or positional errors between the first connecting part 1 and the second connecting part 3 can be compensated for, for example, up to 3° or 1 mm.

[0149] To ensure optimal sealing of the two connections 1 and 3 in the event of an angular or positional offset, the valve seat 45 can be designed in several sections. In the embodiment shown in FIG. 7, it comprises a seat ring 45.2 that is displaceably or rotatably mounted on the sleeve 45.1. A spring element 45.3 arranged on the sleeve 45.1 presses the seat ring 45.2 against the valve plate 51. The seat ring 45.2 can be tilted in its guide in the sleeve 45.1 if the longitudinal axes of the first connection 1 and the second connection 3 do not run parallel to each other but rather have an angular error of several degrees.

[0150] As a result of the sum of these individual measurement values, which can be added together, it is possible to compensate for possible positional and / or angular errors between the first connecting part 1 and the second connecting part 3 without any functional and adhesion limitations.

[0151] Figure 8 shows a third embodiment of the coupling device in the closed state. To improve clarity, only a few reference numerals have been included in this figure.

[0152] It can be clearly seen that the (inner) cone 77 of the actuator piston 23 is centered on the dome-shaped shoulder 13 of the first connecting part 1. Of course, as mentioned above, it is also possible to design the cone 77 convex and the shoulder 13 conical.

[0153] The terms "offset" and "angular error" are illustrated with reference to Figure 9. "Offset" is denoted as "ΔX" in Figure 9. It specifies the distance between the longitudinal axis of the first link 1 and the second link 3 at the point of contact of the links that is parallel to the longitudinal axis of the second link 3.

[0154] The term "angular error" is shown as "ΔX°" in Figure 9. It specifies the angle between the contact surfaces of the first connecting portion 1 and the second connecting portion 3. The longitudinal axes of the first connecting portion 1 and the second connecting portion 3 are also not parallel or concentric, but move at an angle of "ΔX°" relative to each other.

[0155] Conventional coupling devices cannot compensate for significant "offset" or significant "angular error", in which case they can no longer close and unacceptable leakage rates occur.

[0156] 10 shows a detail of the third embodiment in the closed state. It can be clearly seen that the actuator piston 23, and thus also the sleeve-shaped valve seat 45, is angled as a result of the centering of the cone 77 relative to the shoulder 13, increasing the angular error of the contact surfaces relative to each other. The angular error "ΔX°" is thus made up of the angular deflection "Δ_xD835_xDC4B_1°" of the spindle 5 and the angular deflection "Δ_xD835_xDC4B_2°" of the actuator piston 23. In this illustration, the angular error "ΔX°" is approximately 4°.

[0157] It can be clearly seen that the dome-shaped shoulder 13, which can also be designed in the shape of a truncated cone, and the inner cone 77, which can be designed in the shape of a truncated cone or a sphere, ensure that a hydraulic connection is established between the first connecting part 1 and the second connecting part 3 despite angular errors.

[0158] Since the seat ring 45.2 is spring-loaded against the valve plate 51, if the step 13 (due to the angular error "ΔX°") were to abut the seat ring 45.2, no undesirable consequences would result.

[0159] The ability of the coupling device according to the present invention to compensate for angular errors and offsets significantly expands its field of application. As shown in Figure 9, the first coupling 1 can be placed on a rotatably mounted spindle 5. The rotational position of this spindle can only be controlled within a certain range, e.g., 3°. This means that during a tool change, when the coupling device needs to be closed, an angular error of several degrees "ΔX°" regularly occurs during production operation. If the spindle 5 is also held (unsigned), e.g., by a drive, angular deviations of the spindle can result in an angular error "ΔX°" and a position error "ΔX", which are not compensated for by the closing of the coupling device itself. In this case, the coupling device must be able to compensate for this. With the help of the coupling device according to the present invention, this angular error "ΔX°" and position error "ΔX" can be compensated for without malfunction or leakage.

[0160] 11 shows a fourth embodiment of the connecting device according to the present invention. The difference from the other embodiments relates to the second connecting portion 3.

[0161] In a fourth embodiment, at least the second portion 23.2 of the actuator piston 23 is not round but has an oval shape. The second portion 21.2 of the cylinder bore 21 is therefore also oval in cross section. The oval second portion 23.2 of the actuator piston 23 and the second portion 21.2 of the cylinder bore 21 can both be produced, for example, by non-circular turning or grinding.

[0162] If we assume that the second portion 23.2 of the actuator piston 23 and the second portion 21.2 of the cylinder bore 21 are elliptical, it is sufficient if the minor axis of the ellipse is approximately equal to the diameter D23.1 of the first portion 23.1 of the actuator piston 23.

[0163] The major axis of the ellipse is significantly larger than the diameter D 23.1 of the first part 23.1 of the actuator piston 23. As a result, the overall length of the second connecting part 3 in one direction can be significantly reduced without reducing the piston surface of the second part 23.2 of the actuator piston 23.

[0164] In the fourth embodiment, the third compression spring 67 is not located in the second cylinder chamber 27, but is located above the cover 24 (if present) rather than outside the housing 113,19.

[0165] The spacer sleeve 22 and the valve tappet 49 are guided in a sealing manner through the housing 113, 19 or the cover 24, so that the spring force of the third compression spring 67 can act on the actuator piston 23 via the valve tappet 49.

[0166] The structural and hydraulic characteristics (not shown) of the fourth embodiment correspond to those of the second and third embodiments.

[0167] The operating modes of the second and third embodiments of the coupling device according to the invention in the housing 113 of the driven tool holder 111 will now be explained with reference to Figures 12-1 and 12-2. Two coupling devices according to the invention, each having a first coupling part 1 and a second coupling part 3, are provided in the housing 113 of the tool holder 111.

[0168] The coupling device connects the cylinder structure 117 of the spindle to the fluid lines of the housing 113 of the tool holder 111 .

[0169] 13-1 and 13-2, the operating modes of the second and third embodiments are illustrated and explained using a feed bracket 53 with two second connecting parts 3 and a tool holder 111 with a double-acting cylinder structure 117.

[0170] 12-1 and 12-2 to illustrate the hydraulic coupling arrangement to the tool holder 111, a double-acting cylinder structure 117 is shown in simplified form on the tool holder or its spindle 5. Each coupling 123, 125 of the cylinder structure 117 is coupled to one coupling of two first couplings 123, 125 of the tool holder or its spindle 5.

[0171] The pressure applied to the line is symbolized by the number of arrows (two arrows = high pressure, one arrow = low pressure).

[0172] A first fluid line 119 and a second fluid line 121 are present in the housing 113. The first fluid line 119 is connected to a first control line 29 of the second connection 3.1 (top of FIG. 12-1) and a control supply line 32 of the other second connection 3.2 (bottom of FIG. 12-1).

[0173] The second fluid line 121 is connected to the control supply line 32 at the second connection 3.1 (top in FIG. 12-1) and to the first control line 29 at the other second connection 3.2 (bottom in FIG. 12-1).

[0174] The two second connections 3.1, 3.2 are therefore connected "backwards" to the fluid lines 119, 121. Figure 12-1 shows a situation in which the first fluid line 119 is supplied with pressurized fluid (see the two arrows). The second fluid line 121 then serves to discharge the (unpressurized) fluid that is discharged from the cylinder structure 117. However, it is also possible for the second fluid line 121 to operate at a lower pressure than the first fluid line 119.

[0175] In Figure 12-1, both coupling devices are closed, i.e., there is a fluid connection between the first fluid line 119 and the first coupling 123 of the cylinder structure 117. Additionally, there is a fluid connection between the second fluid line 121 and the second coupling 125 of the cylinder structure 117.

[0176] Fluid in the first fluid line 119, under high pressure, passes through the first control line 29 to the first cylinder chamber 25 (top of Figure 12-1) of the second connection 3.1, causing the volume of the first cylinder chamber 25 to increase, causing the actuator piston 23 (together with the associated check valve in the first connection 1) to move the directional valve open.

[0177] In this case, no high pressure fluid (from the first fluid line 119) passes through the closed coupling device 3.1 to the cylinder structure 117 of the tool holder 111.

[0178] Rather, fluid discharged from the cylinder structure 117 at the second connection 125 can pass through the first connection 1 and the open second connection 3.1 and through this connection device (including the first connection 1 and the second connection 3.1) to the second fluid line 121.

[0179] The situation is different in the second coupling device 3.2 (bottom in FIG. 12-1), which is also closed. Here, pressurized fluid from the first fluid line 119 passes via the control supply line 32 to the third cylinder chamber 39 and the fluid chamber 33 of the second connection 3.2 (bottom in FIG. 12-1). As a result, the volume of the third cylinder chamber 39 increases, and the actuator piston 23 (together with the associated check valve 7 of the first connection 1) moves the directional valve open. This coupling device (including the first connection 1 and the second connection 3.2) also closes as a result. The resulting increase in the size of the first cylinder chamber 25 causes (unpressurized) fluid to be sucked out of the second fluid line 121 via the first control line 29 of the second connection 3.2.

[0180] When this coupling device 1, 3.2 is closed, fluid under high pressure (from the first fluid line 119) passes through the third cylinder chamber and the radial bore(s) 37, through the fluid chamber 33 and the gap (restriction 75) with surface A1 (described above in connection with Figures 6 and 7) to the first coupling 1. From there it passes via the first coupling 123 to the cylinder structure 117, displacing the piston located therein (Figure 12-1 above).

[0181] As a result of the movement of the piston of the cylinder structure, 117 (non-pressurized) fluid is discharged through the second connection 125 and passes to the second fluid line 121 via the closed connection device 1, 3.1 as described above.

[0182] 12-2 shows a situation where the first fluid line 119 is not pressurized and high pressure exists in the second fluid line 121. As a result, the direction of movement of the cylinder structure 117 is reversed.

[0183] The second connection 3.1 (top in FIG. 12-2) supplies the fluid chamber 33 with pressurized fluid, which then reaches the second connection 125 of the cylinder structure 117.

[0184] In the second connection 3.2 (bottom in FIG. 12-2) pressurized fluid is supplied to the first cylinder chamber 25. Unpressurized fluid is exhausted from the first connection 123 via this connection device 1, 3.2.

[0185] 13-1 and 13-2 show a front view of the tool holder 111 and supply bracket 53 with the second coupling 3 according to FIG. 6 and with two fluid lines 119 and 121. The operating mode has already been explained in detail with reference to FIGS. 12-1 and 12-2. Of the cylinder structure 117 located in the tool holder or its spindle, the first coupling 123, the second coupling 125 and the cylinder 117 are shown in simplified form.

[0186] In short, with the help of the second connection 3 shown in Figures 6 and 7 and the connection configuration shown in Figures 12-1 and 12.2, only two fluid lines 119, 121 are possible.

[0187] The cylinder structure 117 is actuated to actuate the piston, which in turn causes the piston rod to move in both directions, expelling fluid displaced by the movement of the piston in the cylinder structure 117, compensating for the change in volume of the first cylinder chamber 25 in one of the two second connecting portions 3 by extending the second connecting portion 3, and compensating for the change in volume of the other second connecting portion 3 and the third cylinder chamber when the second connecting portion 3 is extended.

[0188] 14-1 to 14-3, there is illustrated the transfer of hydraulic fluid from the housing 19 to the spindle 5, which has a double-acting cylinder structure 117. With reference to these figures, it is clear what is meant by the term "reversely."

[0189] Since the cylinder arrangement 117 is double acting, there are two connections 123, 125 and two (numbered) first connections 1.1 and 1.2 on the spindle 5. The housing 19 is provided with two (numbered) second connections 3.1, 3.2.

[0190] The first link 1.1 is connected to link 123 of the cylinder structure 117. The first link 1.2 is connected to link 125 of the cylinder structure 117.

[0191] In Fig. 14-1, the spindle 5 is positioned so that the first connection 1 and the second connection 3 face each other. They are not (yet) in contact with each other. The fluid in the first control lines 29.1, 29.2 and the control supply lines 32.1, 32.2 is not yet pressurized.

[0192] In Figure 14-2, the fluid in the control supply line 32.1 is under pressure. This is indicated by two arrows. The direction of the arrows indicates the direction of flow. As a result, the third cylinder chamber 39 is also pressurized. As a result, the actuator piston 23.11 moves in the direction of the first connection 1.1.

[0193] Since the second connections 3.1 and 3.2 are "backward connected," this pressure is also present in the control line 29.2 of the second connection 3.2 (bottom of Figures 14-1 to 14-3). From here, the pressurized fluid enters the first cylinder chamber 25.2 of the second connection 3.2. As a result, the actuator piston 23.12 also moves in the direction of the first connection 1.2.

[0194] It is important that in this connection both actuator pistons 23 move in the direction of the first connection 1, but in one case pressure is present in the control supply line 32.1 and in the other case pressure is present in the first control line 29.1. Nevertheless, both actuator pistons 23.11 and 23.12 move in the direction of the first connection 1 assigned to them.

[0195] In the position of the actuator piston 23 shown in FIG. 14-2, the sleeve-shaped valve seat 45 rests against the end face of the shoulder 13 of the first connection 1 and is already pre-centered, if necessary, by the conical section 77 of the actuator piston 23 in the event of a strong angular or positional deviation. The seal maintains its contact and prevents fluid from reaching the outside. The check valve 7 of the first connection 1 is still closed, since the valve tappet 49 of the second connection 3 has not yet been pressed in the direction of the first connection 1.1 or 1.2. Likewise, the shoulder 13 does not yet press the sleeve-shaped valve seat 45 in the direction of the second connection 3, where the seat ring 45.2 would lift off the valve plate 51.

[0196] In the position shown in Fig. 14-3 (compared to the position shown in Fig. 14-2), the actuator pistons 23.11, 23.12 move towards the first connection 1 so that the valve tappets 49 of the first connection 3 lift the valve members 9 of the check valves 7 from their seats against the force of the first compression springs 17. At the same time, the sleeve-shaped valve seats are pressed by the shoulder 13 towards the second connection so that the seat ring 45.2 lifts off the valve plate 51. This means that the connection is open (open position).

[0197] In the open position, pressurized fluid flows from the control supply line 29.1 through the open coupling device 3.1, 1.1, through the coupling 123 and into the first working chamber 127 of the cylinder structure 117, displacing its piston 129 (to the left in Figures 14-2 and 14-3).

[0198] The piston 129 displaces unpressurized fluid from the other cylinder chamber 131. This displaced fluid passes through the connection 125, the open connections 1.2 and 3.2 and into the control supply line 29.2. When the piston 129 of the cylinder structure 117 is moved in the opposite direction, the control supply line 32.12 of the second connection 3.2 (bottom in Figures 14-1 to 14-3) and the control line 29.1 of the second connection 3.1 (top in Figures 14-1 to 14-3) are exposed to pressurized fluid. [Explanation of symbols]

[0199] 1 First connecting part 3 Second connection 5 shaft 7 Check valve 9 Valve members 11 Valve housing 13 Shoulder 15 Opening 16 Seal ring 17 First compression spring 19 Housing 21 Cylinder bore 23 Actuator piston 24 Cover 25 First Cylinder Chamber 27 Second Cylinder Chamber 29 First Control Line 31 Second Control Line 32 Control supply line 33 Fluid Chamber 37 Radial Bore 39 Circumferential groove, third cylinder chamber 41 Supply Line 43 Second compression spring 45 Sleeve-shaped valve seat 45.1 Sleeve 45.2 seat ring 45.3 Spring Elements 47 guide bore 49 Valve tappet 51 Valve plate 53 Supply bracket 63 Centering Receptacle 65 Color 67 Third compression spring, disc spring 69 Annular Surface 73 Protrusion 75 throttle 77 Cone 79 First (actuator piston) seal 81 Second (actuator piston) seal 101 Robot Hand 103 Gripper 105 Adapter 107 Cutting tools, drills 109 Hollow Shaft 111 Tool holder 113 Tool holder housing 115 Docking section 117 Cylinder structure 119 First Fluid Line 121 Second Fluid Line 123 first connecting portion of cylinder structure 117 125 second connecting portion of cylinder structure 117 127 First Cylinder Chamber 129 Piston 131 second cylinder chamber

Claims

1. a housing (19, 113), a spindle (5), a centering receptacle (63) arranged on the spindle (5) for receiving an adapter (105), and a fluid-actuated clamping system for clamping or detaching the adapter (105) from the centering receptacle (63), wherein at least one first connection (1) is present on the spindle (5) and at least one second connection (3) is present on the housing (19, 113), and wherein the first connection (1) and the second connection (3) are suitable to cooperate to form a fluid connection; The first connection (1) is formed as a spring-loaded check valve (7), the second connection (3) comprises an actuator piston (23) displaceably guided in the housing (19, 113), An outwardly opening directional valve is disposed on the actuator piston (23), The tool holder (111) is characterized in that the actuator piston (23) divides the cylinder bore (21) into a first cylinder chamber (25) and a second cylinder chamber (27).

2. 1. A tool holder (111) comprising a housing (19, 113), a spindle (5), a centering receptacle (63) arranged on the spindle (5) for receiving an adapter (105), and a fluid-actuated clamping system for clamping or disengaging the adapter (105) from the centering receptacle (63), At least one first connection (1) is present on said spindle (5), At least one second connection (3) is present on said housing (19, 113); the first connection (1) and the second connection (3) are suitable to cooperate to form a fluid connection; The first connection (1) is formed as a spring-loaded check valve (7), the second coupling (3) comprises an actuator piston (23) displaceably guided in the housing (19, 113); An outwardly opening directional valve is disposed on the actuator piston (23), The actuator piston (23) is designed as a stepped piston, a first portion (23.1) of the actuator piston (23) defining a first cylinder chamber (25); a second portion (23.2) of the actuator piston (23) defining a second cylinder chamber (27); 1. A tool holder (111) characterized in that the diameter (D23.1) of the first part (23.1) of the actuator piston (23) is smaller than the diameter (D23.2) of the second part (23.2) of the actuator piston (23), such that a third cylinder chamber (39) having an annular surface (69) is present at the transition between the first part (23.1) and the second part (23.2) of the actuator piston (23).

3. 1. A tool holder (111) comprising: a housing (113), a spindle (5), a centering receptacle (63) arranged on said spindle (5) for receiving an adapter (105), and a fluid-actuated clamping system for clamping or disengaging the adapter (105) from said centering receptacle (63), At least one first connection (1) is present on said spindle (5), At least one second connection (3) is present on said housing (113), the first connection (1) and the second connection (3) are suitable for forming a fluid connection device, The first connection (1) is designed as a spring-loaded check valve (7), the second coupling (3) comprises an actuator piston (23) displaceably guided in the housing (113); An outwardly opening directional valve is disposed on the actuator piston (23), a sleeve-shaped valve seat (45) of the directional valve is displaceably received in a guide bore (47) of the second connecting part (3); the first connecting part (1) has a shoulder at its end facing the second connecting part (3), and when the connecting device is closed, the shoulder dips into the guide bore (47) of the second connecting part (3), the fluid chamber (33) of the second connecting part (3) opens into the guide bore (47), and when the valve seat (45) comes into contact with the shoulder and is lifted, a valve tappet of the directional valve is connected to the actuator piston (23) and protrudes through the sleeve-shaped valve seat (45).

4. A sleeve-shaped valve seat (45) of the directional valve is displaceably accommodated in a guide bore (47) of the second connecting portion (3), 3. The tool holder (111) according to claim 1 or 2, characterized in that the or each first connecting part (1) has a shoulder (13) at its end facing the second connecting part (3), which, when the connecting device is closed, dips into the guide bore (47) of the second connecting part (3), so that the fluid chamber (33) of the second connecting part (3) opens into the guide bore (47), and when the valve seat (45) comes into contact with the shoulder and is lifted, a valve tappet of the directional valve is connected to the actuator piston (23) and protrudes through the sleeve-shaped valve seat (45).

5. 5. The tool holder (111) according to any one of claims 1 to 4, characterized in that the check valve (7) of the first connection part (1) is arranged radially with respect to the axis of the centering receptacle (63).

6. The system comprises two second connections (3.1, 3.2), a first fluid line (119) and a second fluid line (121), each of said second connections (3.1, 3.2) being connected to a first restriction 6. The tool holder (111) according to claim 1, further comprising a first control line (29) and a second control line (31), wherein the first control line (29) of one second connection (3.1) and the second control line (31) of the other second connection (3.2) are connected to the first fluid line (119), and the second control line (31) of the one second connection (3.1) and the first control line (29) of the other second connection (3.2) are connected to the second fluid line (121).

7. 7. The tool holder (111) according to any one of claims 1 to 6, characterized in that the fluid-operated actuator of the clamping system comprises a single-acting cylinder arrangement (117), a first connection (1) for the supply of the cylinder arrangement (117) being provided for clamping and releasing the clamping system.

8. 7. The tool holder (111) according to any one of claims 1 to 6, characterized in that the fluid-operated actuator of the clamping system comprises a double-acting cylinder structure (117), and two first connections (1) for supplying connections (123, 125) of the cylinder structure (117) are provided for clamping and releasing the clamping system.

9. a supply bracket (53) comprising at least one second connection (3) suitable for cooperating with the first connection (1) to form, together with the first connection (1), a fluid connection; The first connection (1) is formed as a spring-loaded check valve (7), the second connection (3) comprises an actuator piston (23) displaceably guided in a housing (19, 113), An outwardly opening directional valve is disposed on the actuator piston (23), The actuator piston (23) divides the cylinder bore (21) into a first cylinder chamber (25) and a second cylinder chamber (27); The supply bracket (53) has a C-shaped docking portion (115), A supply bracket (53) in which at least two of said second connecting portions (3) are arranged in said docking portion (115).

10. a supply bracket (53) comprising at least one second connection (3) suitable for cooperating with the first connection (1) to form, together with the first connection (3), a fluid connection; The first connection (1) is formed as a spring-loaded check valve (7), the second connection (3) comprises an actuator piston (23) displaceably guided in a housing (19, 113), An outwardly opening directional valve is disposed on the actuator piston (23), The actuator piston (23) is designed as a stepped piston, a first portion (23.1) of the actuator piston (23) defining a first cylinder chamber (25); a second portion (23.2) of the actuator piston (23) defining a second cylinder chamber (27); the diameter (D23.1) of the first portion (23.1) of the actuator piston (23) is smaller than the diameter (D23.2) of the second portion (23.2) of the actuator piston (23), such that a third cylinder chamber (39) having an annular surface (69) exists at the transition between the first portion (23.1) and the second portion (23.2) of the actuator piston (23); The supply bracket (53) has a C-shaped docking portion (115), A supply bracket (53) in which at least two of said second connecting portions (3) are arranged in a docking portion (115).

11. 11. A supply bracket (53) according to claim 9 or 10, characterized in that each of the second coupling parts (3) is compatible with a first coupling part (1) of a tool holder (111) according to any one of claims 1 to 8.

12. 12. The supply bracket (53) according to any one of claims 9 to 11, characterized in that the supply bracket (53) comprises two second connections (3.1, 3.2), a first fluid line (119) and a second fluid line (121), each of the second connections (3.1, 3.2) comprising a first control line (29) and a second control line (31), the first control line (29) of one second connection (3.2) and the second control line (31) of the other second connection (3.2) being connected to the first fluid line (119), and the second control line (31) of the one second connection (3.1) and the first control line (29) of the other second connection (3.2) being connected to the second fluid line (121).

13. 9. The tool holder (111) according to any one of claims 1 to 8, characterized in that it comprises at least two second connecting portions (3), each of which is adapted to one of the first connecting portions (1) of the tool holder (111).

14. 14. Tool holder (111) according to claim 13, characterized in that the at least two second connections (3) are arranged such that forces exerted on the first connection (1) by valve tappets (49) of the second connections (3) are completely or at least largely cancelled out.

15. 15. The tool holder (111) according to any one of claims 1 to 8, 13 and 14, characterized in that a gap between the cylinder bore (21) and the actuator piston (23) at an end of the actuator piston (23) facing away from the first connection part (1) is smaller than a gap between the cylinder bore (21) and the actuator piston (23) at an end of the actuator piston (23) facing towards the first connection part (1).

16. 16. The tool holder (111) according to any one of claims 1 to 8 and 13 to 15, characterized in that a first seal (79) is provided at an end of the actuator piston (23) remote from the first connection (1) and a second seal (81) is provided at an end of the actuator piston (23) facing the first connection (1), the second seal (81) being radially flexible so as to seal the second cylinder chamber (27) even when the actuator piston (23) is tilted or offset relative to the cylinder bore (21).

17. Tool holder (111) according to claim 16, when dependent on claim 2, characterized in that the second seal (81) seals the third cylinder chamber (39) against the second cylinder chamber (27).

18. A fluid chamber (33) is formed in the actuator piston (23) so as to be closed at one end, the fluid chamber (33) opens into a guide bore (47), a sleeve-shaped valve seat (45) of the directional valve is displaceably accommodated in the guide bore (47), a valve tappet (49) of the directional valve is connected to the actuator piston (23) and protrudes through the sleeve-shaped valve seat (45), and the valve 18. The tool holder (111) according to any one of claims 1 to 8 and claims 13 to 17, characterized in that a valve plate (51) of a valve pet (49) limits the path of the valve seat (45) in the guide bore (47).

19. 19. Tool holder (111) according to claim 18, characterized in that the valve seat (45) comprises a sleeve (45.1), a seat ring (45.2) accommodated and guided in the sleeve (45.1), and a spring element (45.3), the spring element (45.3) being supported by one end of the sleeve (45.1) and the other end of the seat ring (45.2).

20. 20. The tool holder (111) according to claim 18 or 19, characterized in that a second compression spring (43) is arranged in the fluid chamber (33), and a spring force acting on the valve seat (45) by the second compression spring (43) presses the valve seat (45) against the valve plate (51) of the valve tappet (49).

21. 21. The tool holder (111) according to any one of claims 17 to 20, characterized in that the fluid chamber (33) is fluidly connected to a supply line (41, 121) of a housing (19, 113) or a supply bracket (53) via a circumferential groove (39) present on the outside of the actuator piston (23) and is supplied with fluid via at least one radial bore (37), at least in the open position of a directional valve.

22. The tool holder (111) according to any one of claims 1 to 8 and 13 to 21, characterized in that the first cylinder chamber (25) can be supplied with a fluid via a first control line (29, 119).

23. The tool holder (111) according to any one of claims 1 to 8 and 13 to 22, wherein the second cylinder chamber (27) can be supplied with fluid via a second control line (31).

24. 2. A tool holder (111) according to claim 2, or any one of claims 4 to 8 which rely on claim 2, or claims 13 to 23 which rely on claim 2, characterized in that a third compression spring (67) is arranged outside the second cylinder chamber (27) or the housing (19, 113) or the supply bracket (53), such that a spring force acting on the actuator piston (23) counteracts a (pressure) force of a fluid located in the first cylinder chamber (25) and / or the third cylinder chamber (39).

25. 25. The tool holder (111) according to any one of claims 19 to 24, characterized in that the fluid chamber (33) can be supplied with fluid via a supply line (41) or a combination of a control supply line (32) and a supply line (41), at least in the open position of the directional valve.

26. The tool holder (111) according to claim 2, any one of claims 4 to 8 which rely on claim 2, and any one of claims 10 to 25 which rely on claim 2, wherein the third cylinder chamber (39) and the fluid chamber (33) are simultaneously supplied with fluid via a controlled supply line (32).

27. Claim 1, dependent on claim 2, characterized in that a throttle (75) or orifice is present between the fluid chamber (33) and the directional valve, restricting the outflow of pressurized fluid from the fluid chamber (33) when the directional valve is open, thereby maintaining a minimum overpressure in the fluid chamber (33) and the third cylinder chamber (39).

27. A tool holder (111) according to any one of claims 8 to 26.

28. 28. Tool holder (111) according to claim 27, characterized in that the throttle (75) is designed as an annular gap between a valve tappet (49) and a valve seat (45) or a sleeve (45.1).

29. 10. The tool holder (111) according to claim 1, any one of claims 4 to 8 which rely on claim 1, and any one of claims 13 to 28 which rely on claim 1, wherein at least the second portion (23.2) of the actuator piston (23) has an oval or elliptical cross section, and at least the second portion (21.2) of the cylinder bore (21) has an oval or elliptical cross section.

30. 30. The tool holder (111) according to any one of claims 1 to 8 and 13 to 29, characterized in that the check valve (7) of the first connection (1) comprises a valve housing (11), an opening (15) for the fluid connected to the check valve (7) is formed in the valve housing (11), the opening (15) is formed in a shoulder (13) of the valve housing (11), and when the connection device is closed, the shoulder (13) enters a guide bore (47) of the second connection (3), a valve seat (45) of the directional valve is lifted from a valve plate (51) of a valve tappet (49), and a line (18) of the valve housing (11) or a spindle (5) is opened or closed by the check valve (7).

31. 31. Tool holder (111) according to claim 30, characterized in that the shoulder (13) of the valve housing (11) is designed in a frustoconical or dome-shaped manner.

32. 32. The tool holder (111) according to any one of claims 1 to 8 and 13 to 31, characterized in that the actuator piston (23) has at its end a conical portion (77) or an inner dome portion facing the first connecting portion (1), and the first connecting portion (1) has at its end a shoulder (13) facing the second connecting portion (3).

33. A supply bracket (53) according to any one of claims 9 to 12, characterized in that it comprises at least two second connecting portions (3), each of which is adapted to fit with one of the first connecting portions (1) of the supply bracket (53).

34. 34. A supply bracket (53) according to claim 33, characterized in that the at least two second couplings (3) are arranged so that the forces exerted on the first couplings (1) by the valve tappets (49) of the second couplings (3) are completely or at least largely cancelled out.

35. A supply bracket (53) according to any one of claims 9 to 12, 33 and 34, characterized in that a gap between the cylinder bore (21) and the actuator piston (23) at an end of the actuator piston (23) facing away from the first connection part (1) is smaller than a gap between the cylinder bore (21) and the actuator piston (23) at an end of the actuator piston (23) facing towards the first connection part (1).

36. A first seal (79) is provided at an end of the actuator piston (23) remote from the first connection (1), and a second seal (81) is provided at an end of the actuator piston (23) facing the first connection (1), the second seal (81) being adapted to seal the actuator piston (23) when the actuator piston (23) is tilted relative to the cylinder bore (21) or when the actuator piston (23) is tilted relative to the cylinder bore (21). The supply bracket (53) according to any one of claims 9 to 12 and claims 33 to 35, characterized in that it is radially flexible so as to seal the second cylinder chamber (27) even when the second cylinder chamber (27) is offset.

37. 37. Supply bracket (53) according to claim 36, when dependent on claim 10, characterized in that the second seal (81) seals the third cylinder chamber (39) against the second cylinder chamber (27).

38. 38. A supply bracket (53) according to any one of claims 9 to 12 and claims 33 to 37, characterized in that a fluid chamber (33) is formed in the actuator piston (23) so as to be closed at one end, the fluid chamber (33) opens into a guide bore (47), a sleeve-shaped valve seat (45) of the directional valve is displaceably received in the guide bore (47), a valve tappet (49) of the directional valve is connected to the actuator piston (23) and protrudes through the sleeve-shaped valve seat (45), and a valve plate (51) of the valve tappet (49) limits the path of the valve seat (45) in the guide bore (47).

39. 39. The supply bracket (53) according to claim 38, characterized in that the valve seat (45) comprises a sleeve (45.1), a seat ring (45.2) accommodated and guided in the sleeve (45.1), and a spring element (45.3), the spring element (45.3) being supported by one end of the sleeve (45.1) and the other end of the seat ring (45.2).

40. 40. The supply bracket (53) according to claim 38 or 39, characterized in that a second compression spring (43) is arranged in the fluid chamber (33), and a spring force acting on the valve seat (45) by the second compression spring (43) presses the valve seat (45) against the valve plate (51) of the valve tappet (49).

41. A supply bracket (53) according to any one of claims 37 to 40, characterized in that the fluid chamber (33) is fluidly connected to a supply line (41, 121) of the housing (19, 113) or of the supply bracket (53) via a circumferential groove (39) present on the outside of the actuator piston (23) and is supplied with fluid via at least one radial bore (37) at least in the open position of the directional valve.

42. A supply bracket (53) according to any one of claims 9 to 12 and 33 to 41, characterized in that the first cylinder chamber (25) can be supplied with fluid via a first control line (29, 119).

43. A supply bracket (53) according to any one of claims 9 to 12 and 33 to 42, characterized in that the second cylinder chamber (27) can be supplied with fluid via a second control line (31).

44. A supply bracket (53) according to any one of claims 10, 11 and 12 which rely on claim 10, and claims 33 to 43 which rely on claim 10, characterized in that a third compression spring (67) is arranged outside the second cylinder chamber (27) or the housing (19, 113) or the supply bracket (53), and the spring force acting on the actuator piston (23) counteracts the (pressure) force of the fluid located in the first cylinder chamber (25) and / or the third cylinder chamber (39).

45. The fluid chamber (33) is connected to the supply line at least in the open position of the directional valve. A supply bracket (53) according to any one of claims 39 to 44, characterized in that the fluid can be supplied via a line (41) or a line that combines a control supply line (32) and a supply line (41).

46. The supply bracket (53) according to any one of claims 10, 11 and 12 which rely on claim 10, and claims 30 to 45 which rely on claim 10, wherein the third cylinder chamber (39) and the fluid chamber (33) are simultaneously supplied with fluid via a controlled supply line (32).

47. A supply bracket (53) according to any one of claims 38 to 46, with reference to claim 10, characterized in that a throttle (75) or orifice is present between the fluid chamber (33) and the directional valve, thereby restricting the outflow of pressurized fluid from the fluid chamber (33) when the directional valve is open, and maintaining a minimum overpressure in the fluid chamber (33) and the third cylinder chamber (39).

48. 48. The supply bracket (53) according to claim 47, characterized in that the throttle (75) is designed as an annular gap between the valve tappet (49) and the valve seat (45) or sleeve (45.1).

49. 9, claim 11 or 12 which rely on claim 9, and any one of claims 33 to 48 which rely on claim 9, wherein at least the second portion (23.2) of the actuator piston (23) has an oval or elliptical cross section, and at least the second portion (21.2) of the cylinder bore (21) has an oval or elliptical cross section.

50. 50. The supply bracket (53) according to any one of claims 9 to 12 and 33 to 49, wherein the check valve (7) of the first connection (1) comprises a valve housing (11), an opening (15) for the fluid connected to the check valve (7) is formed in the valve housing (11), the opening (15) is formed in a shoulder (13) of the valve housing (11), and when the connection device is closed, the shoulder (13) enters a guide bore (47) of the second connection (3), a valve seat (45) of the directional valve is lifted from a valve plate (51) of a valve tappet (49), and a line (18) of the valve housing (11) or spindle (5) is opened or closed by the check valve (7).

51. 51. A supply bracket (53) according to claim 50, characterized in that the shoulder (13) of the valve housing (11) is designed in a frustoconical or dome-shaped manner.

52. A supply bracket (53) according to any one of claims 9 to 12 and claims 33 to 51, characterized in that the actuator piston (23) has at its end a conical portion (77) or an inner dome portion facing the first connecting portion (1), and the first connecting portion (1) has at its end a shoulder (13) facing the second connecting portion (3).

53. 33. A rotary machine comprising at least one tool holder (111) according to any one of claims 1 to 8 and 13 to 32, characterized in that the fluid-operated actuator of the clamping system comprises a cylinder structure (117), and at least one first connection (1) for the supply of the cylinder structure (117) is provided for clamping and releasing the clamping system.

54. A supply bracket (53) according to any one of claims 9 to 12 and claims 33 to 52 54. The rotary machine of claim 53, comprising:

55. 32. A machining center comprising at least one tool holder (111) according to any one of claims 1 to 8 and 13 to 32, characterized in that the fluid-operated actuator of the clamping system comprises a cylinder structure (117), and at least one first connection (1) for the supply of the cylinder structure (117) is provided for clamping and releasing the clamping system.

56. 56. A machining center according to claim 55, characterized in that it comprises a feed bracket (53) according to any one of claims 9 to 12 and claims 33 to 52.

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