Device For Grinding A Workpiece And/Or Dressing A Tool

Abstract

Device for grinding a workpiece and/or for dressing a tool, the device including: a housing, a drive shaft which is rotatable with respect to the housing about an axis of rotation and which is designed to drive a machining means, the machining means being connectable to the drive shaft, wherein the drive shaft has a connection section for connection to the machining means, and a pressure chamber to which hydraulic pressure can be applied is arranged in the connection section and is delimited at least in sections by an elastic side wall, wherein the elastic side wall is designed to deform in order to produce a force fit between the drive shaft and the machining means when hydraulic pressure is applied to the pressure chamber.

Description

TECHNICAL FIELD

The invention relates to a device for grinding a workpiece and/or dressing a tool. The invention preferably relates to a gear grinding machine which is designed to grind a gear wheel blank. Alternatively or additionally, the invention can relate to a dressing machine which is designed to dress a tool, for example a grinding wheel. The device includes a housing and a drive shaft. The drive shaft is designed to drive a machining means, the machining means being connectable to the drive shaft in a force-fitting manner.

PRIOR ART

Devices which have a drive shaft which is rotatable about an axis of rotation are known from the prior art. The known drive shafts can set a machining means connected to the respective drive shaft into a rotational movement in such a way that a workpiece and/or a tool can be machined, in particular ground, with the rotating machining means. If the machining means is, for example, a grinding means, a gear wheel blank can be ground with the grinding means. If the machining means is designed as a dressing means, a grinding means, for example a grinding wheel, can be dressed with the dressing means.

It is known from the prior art to screw the machining means to the drive shaft. Additionally or alternatively, the known drive shafts can have a connection section, via which the machining means can be connected to the drive shaft in a force-fitting manner. The connection section can be designed as a hollow shank cone, steep taper or polygonal shank cone. Such shapes increase the force fit between the drive shaft and the machining means if the machining means is connected to the drive shaft.

The drive shafts known from the prior art are regularly equipped or loaded with a machining means manually, that is to say by a user. The same also regularly applies to the unloading or removal of the machining means from the drive shaft.

Automation of these processes is very complicated in the case of known drive shafts. As a rule, partial automation of the loading or unloading process is possible, the machining means being screwed and/or clamped to the drive shaft by a user after the machining means has been mechanically arranged on the drive shaft. The screwing and/or clamping of the machining means by a user is necessary because a high degree of precision with regard to the alignment between the machining means and the drive shaft is required for the final step of connecting the machining means to the drive shaft. If this partial step is also automated, a high level of complexity is necessary for this purpose.

In order to completely automate the loading and/or unloading process, drive shafts with a hollow shank cone, steep taper or polygonal shank cone are almost exclusively used in the prior art. In the case of this type of drive shafts, the machining means are clamped to the drive shaft regularly with the aid of a clamping system. However, the clamping systems have the disadvantage that they are very costly to procure and require a large amount of installation space on the drive shaft. Furthermore, the clamping system can cause undesired imbalances during rotation of the drive shaft. Since the clamping systems have to be arranged axially centrally within the drive shaft, it is also not possible in terms of design to carry out center balancing with an axially central balancing head. Accordingly, imbalances which adversely influence the durability of the device have to be accepted in the prior art.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a device for grinding a workpiece and/or for dressing a tool, which overcomes the aforementioned problems and disadvantages of the prior art. It is in particular an object of the present invention to provide a device which can be loaded and unloaded in a fully automated manner, i.e. without an intermediate interaction of a user with a cutting means, and which has as few imbalances as possible during operation.

This object is achieved with a device according to claim 1. Advantageous developments of the invention are the subject matter of the dependent claims and/or are explained in the following description.

The device according to the invention is suitable for grinding a workpiece. The device can be, for example, a gear grinding machine which is suitable for grinding a gear wheel blank. The device can also be designed as a grinding head of a grinding device with means for loading and unloading the grinding device. Alternatively or additionally, the device can be suitable for dressing a tool. The device can be, for example, a dressing machine which is suitable for dressing a grinding wheel.

The device includes, according to the invention, a housing and a drive shaft. The drive shaft is rotatable with respect to the housing about an axis of rotation. Furthermore, the drive shaft is designed to drive a machining means, the machining means being connectable to the drive shaft. When the machining means is driven by the drive shaft, the machining means preferably rotates about the axis of rotation. The drive shaft can be designed, in particular, as a spindle shaft.

The machining means which is connectable to the drive shaft can be designed in one piece or in multiple pieces. For example, the machining means can be a grinding wheel, in particular a grinding wheel with a steel main body, which is directly connectable to the drive shaft. Alternatively, the machining means can include a grinding wheel and a grinding wheel flange, wherein the grinding wheel flange is preferably formed by a steel main body. In such embodiments, the grinding wheel can be connectable to the drive shaft via the grinding wheel flange.

Analogously, the machining means can be a dressing means, in particular a dressing wheel, which is directly connectable to the drive shaft. Alternatively, the dressing means can include a dressing portion and a dressing means flange. In such embodiments, the dressing means can be connectable to the drive shaft via the dressing means flange. The dressing portion can be designed to dress a tool.

The drive shaft includes a connection section. The drive shaft can be connected to the machining means via the connection section. At least one pressure chamber to which hydraulic pressure can be applied is arranged in the connection section. Preferably, hydraulic pressure is applied to the pressure chamber by means of a pressurized hydraulic fluid.

The pressure chamber is at least in sections delimited by an elastic side wall. The elastic side wall is preferably provided within the connection section such that the elastic side wall is arranged between the pressure chamber and the machining means when the drive shaft is connected to the machining means.

The elastic side wall is designed to deform. The elastic side wall deforms in particular when hydraulic pressure is applied to the pressure chamber. This has the effect that a force fit between the drive shaft and the machining means, in particular between the drive shaft and a grinding wheel flange of the machining means, is produced by the deformation of the side wall.

The device according to the invention has the advantage that the pressure chamber and the elastic side wall require only very little installation space within the drive shaft in comparison with a clamping device known from the prior art. A further advantage is that the machining means can be braced reliably with the drive shaft without additional imbalances having to be expected. Not least, the loading and unloading of the device with a machining means is also considerably simplified. The machining means only has to be arranged on the connection section of the drive shaft. If the pressure chamber is then subjected to hydraulic pressure, the drive shaft and the machining means are already clamped in such a way that the machining means can be driven by the drive shaft for grinding the workpiece.

In an exemplary development of the device according to the invention, at least in sections the elastic side wall delimits the pressure chamber radially. This means that the elastic side wall is arranged with respect to the axis of rotation preferably radially between the pressure chamber and the machining means when the drive shaft is connected to the machining means. The side wall can be designed to brace the drive shaft with the machining means, in particular to brace it in the radial direction with the machining means, when hydraulic pressure is applied to the pressure chamber. For example, the side wall deforms in the radial direction when hydraulic pressure is applied to the pressure chamber. The elastic side wall is preferably designed in a sleeve-shaped manner, in particular in a hollow-cylindrical manner. Alternatively or additionally, the elastic side wall can be designed in multiple parts. For example, a plurality of elastic side walls can be arranged distributed on the drive shaft in the circumferential direction.

A development in which the elastic side wall at least in sections delimits the pressure chamber radially advantageously has the effect that a radial force fit can be produced between the drive shaft and the machining means. This has the advantage that if the pressure chamber and the elastic side wall extend over the entire circumference of the drive shaft, a very large-area and therefore a very stable force fit between the drive shaft and the machining means can be realized.

In an exemplary embodiment, at least in sections the elastic side wall delimits the pressure chamber radially on the outside with respect to the axis of rotation. The elastic side wall is then advantageously designed to deform radially outwards. In particular, the elastic side wall can deform radially outwards when hydraulic pressure is applied to the pressure chamber. For example, the elastic side wall can deform radially outwards in order to produce a force fit between the drive shaft and the machining means.

The exemplary embodiment in which the elastic side wall at least in sections delimits the pressure chamber radially on the outside with respect to the axis of rotation is advantageous in particular when the machining means at least in sections encases the drive shaft.

In an alternative embodiment to the aforementioned embodiment, at least in sections the elastic side wall delimits the pressure chamber radially on the inside with respect to the axis of rotation. The elastic side wall is then advantageously designed to deform radially inwards. In particular, the elastic side wall can deform radially inwards when hydraulic pressure is applied to the pressure chamber. For example, the elastic side wall can deform radially inwards in order to produce a force fit between the drive shaft and the machining means.

The exemplary embodiment in which the elastic side wall at least in sections delimits the pressure chamber radially on the inside with respect to the axis of rotation is advantageous in particular when the drive shaft at least in sections encases the machining means.

In a further exemplary embodiment of the device, the connection section can have several pressure chambers. Preferably, each of the several pressure chambers is delimited at least in sections by the elastic side wall. In other words, at least in sections an elastic side wall can delimit several pressure chambers. Alternatively or additionally, at least in sections a side wall can in each case delimit one pressure chamber.

Several pressure chambers have the advantage that the force fit produced by the deformation of the elastic side wall can be better regulated. Moreover, several pressure chambers have the advantage that the imbalance potential is significantly reduced, especially since the hydraulic fluid can be distributed over several pressure chambers.

In a further exemplary embodiment, the device, in particular the drive shaft of the device, can have several connection sections. For example, the drive shaft can have a first connection section and a second connection section different from the first connection section. The second connection section can be arranged in an axial direction directly or indirectly next to the first connection section.

Preferably, the first connection section includes a first elastic side wall. The second connection section can include a second elastic side wall different from the first elastic side wall. Preferably, the first elastic side wall has a first radial distance from the axis of rotation. The first radial distance can be greater than or less than a second radial distance between the second elastic side wall and the axis of rotation. The drive shaft can have a first diameter in the first connection section and a second diameter in the second connection section. Preferably, the first diameter is greater than or less than the second diameter.

The different connection sections have the advantage that different machining means, in particular machining means with different internal diameters, can be braced with one and the same drive shaft. As a result, the flexibility of use of the device can be significantly increased and/or the width of the connection sections required in an axial direction can be reduced.

The device, in particular the drive shaft, can have a hydraulic fluid duct. Preferably, the hydraulic fluid duct is designed for supplying the pressure chamber with hydraulic fluid. This means that the hydraulic fluid can flow through the hydraulic fluid duct in order to reach the pressure chambers. Alternatively or additionally, a pressure increase of the hydraulic fluid already contained in the hydraulic fluid duct can be transmitted to the pressure chambers via the hydraulic fluid duct. The hydraulic fluid duct can in particular extend through the drive shaft. For example, the hydraulic fluid duct at least in sections extends parallel to the axis of rotation through the drive shaft.

A hydraulic fluid duct has the advantage that the supply of the pressure chamber with hydraulic fluid can be ensured particularly reliably and cost-effectively in terms of production.

The device can also have a pressure intensifier. The pressure intensifier can be designed, for example, to increase or raise a first fluid pressure of the hydraulic fluid to a second fluid pressure of the hydraulic fluid. A pressure intensifier can advantageously have the effect that the pressure chambers can be acted on with a higher fluid pressure than would be the case with the predefined input pressure. This has the advantage that the force-fitting connection between the drive shaft and the machining means can be improved further.

In a further exemplary embodiment, the device includes a pneumatic position detection device. The pneumatic position detection device is designed to pneumatically detect the position of the machining means connected to the drive shaft by detecting the position of the machining means connected to the drive shaft on the connection section by supplying compressed air. The pneumatic position detection device can be arranged within the drive shaft and/or be an integral part of the drive shaft.

The pneumatic position detection device can have at least two, preferably more than two and particularly preferably three, compressed air openings. The compressed air openings are designed such that compressed air can flow out of the pneumatic position detection device via the compressed air openings. If the machining means connected to the drive shaft is positioned correctly on the connection section, for example, the compressed air openings are closed by the machining means, in particular by the grinding wheel flange of the machining means. The dynamic pressure arising as a result can be detected by the pneumatic position detection device. A machining means positioned correctly on the connection section can thus be detected by the pneumatic position detection device. If the machining means connected to the drive shaft is positioned wrongly or incorrectly on the connection section, the compressed air can flow out via at least one of the compressed air openings. This outflow can likewise be detected by the pneumatic position detection device. A machining means positioned wrongly or incorrectly on the connection section can thus be detected by the pneumatic position detection device.

The pneumatic position detection device has the advantage that the correct position of the machining means on the connection section can be determined particularly reliably.

The device, in particular the drive shaft, can have a pneumatic duct. Preferably, the pneumatic duct is designed for supplying the pneumatic position detection device with compressed air. This means that the compressed air can flow through the pneumatic duct in order to reach the pneumatic position detection device. The pneumatic duct can in particular extend through the drive shaft. For example, the pneumatic duct at least in sections extends parallel to the axis of rotation through the drive shaft.

A pneumatic duct has the advantage that the supply of the pneumatic position detection device with compressed air can be ensured in the best possible manner.

In a further exemplary embodiment of the device, the device includes a blow-off device. Preferably, the blow-off device is designed to remove contaminants on the connection section. The discharge device can remove the contaminants on the connection section, for example, by blowing compressed air onto the connection section. The blow-off device can form a functional unit together with the pneumatic position detection device. Alternatively or additionally, the blow-off device can be a device of the device that is independent of the pneumatic position detection device. The blow-off device can be arranged within the drive shaft and/or be an integral part of the drive shaft.

The blow-off device can have at least one, preferably several, compressed air openings. The compressed air opening or the compressed air openings of the blow-off device can be one or more compressed air openings of the pneumatic position detection device.

Compressed air can flow out of the blow-off device in an axial direction via the compressed air openings in order then to flow over the connection section in an axial direction. As a result of this flow of compressed air over the connection section, contaminants on the connection section can be removed, in particular blown off, from the connection section.

The blow-off device can be supplyable and/or supplied with compressed air via the aforementioned pneumatic duct. Alternatively or additionally, the blow-off device can be supplied with compressed air via a pneumatic duct that is different from the aforementioned pneumatic duct. The pneumatic duct that is different from the aforementioned pneumatic duct can at least in sections extend parallel to the axis of rotation through the drive shaft.

The blow-off device advantageously has the effect that the connection section can be freed of contaminants before being equipped with the machining means and/or after removal of the machining means. If these contaminants remain between the elastic side wall and the machining means if a force fit is produced between the drive shaft and the machining means, damage to the connection section and/or the machining means is imminent. Accordingly, the service life of the connection section and the machining means is increased by the blow-off device.

In a further exemplary embodiment, the device has a connection device. The connection device can be designed to be rotationally fixed, preferably immovable, with respect to the housing. The connection device can have a hydraulic connection via which the device is supplied with hydraulic fluid, preferably with pressurized hydraulic fluid. The connection device can additionally or alternatively have a pneumatic connection. The device can be supplied with compressed air via the pneumatic connection. Preferably, the connection device is designed as a rotary inlet. This means that the connection device can have a static part, preferably an outer static part, and a part rotatable with the drive shaft, preferably an inner part rotatable with the drive shaft.

A connection device has the advantage that the device is connectable very simply and reliably to a hydraulic circuit and/or a compressed air circuit, in particular for supplying the pressure chamber, the pneumatic position detection device and/or the blow-off device.

Advantageously, the connection device is designed to introduce the hydraulic fluid, in particular the pressurized hydraulic fluid, into the above-described hydraulic fluid duct. Alternatively or additionally, the connection device can be designed to introduce the compressed air into the above-described pneumatic duct.

The connection device can be arranged at an end of the drive shaft axially opposite the connection section. This has the advantage that the accessibility of the connection section is not impaired by the connection device. Accordingly, the connection section is very easily accessible, in particular for a changing process in which the machining means is changed. Furthermore, the risk of possible damage to the connection device during the changing process is considerably reduced.

In a further exemplary embodiment, the drive shaft can have a polygonal cross-sectional area in the connection section. The drive shaft can have, in particular, a regularly polygonal cross-sectional area, if appropriate with rounded corner regions.

The polygonal cross-sectional area in the connection section has the advantage that the machining means can be secured against rotation in addition to the force fit between the drive means and the machining means. The machining means can be secured against rotation in particular by form fit with the polygonal cross-sectional area.

In a further exemplary embodiment, the device can have a sensor device. The sensor device is preferably designed for detecting the machining means. For example, the presence of the machining means on the drive shaft can be determined via the sensor device. Alternatively or additionally, it can be determined by means of the sensor device whether the machining means is positioned correctly on the connection section and/or whether the machining means slips from the rotating drive shaft during operation of the device. The sensor device can also be designed to detect the axial position of the machining means with respect to the housing.

The sensor device can be designed to generate sensor signals. The sensor signals can be an indicator for a control and/or regulating device of the device whether the application of hydraulic pressure to the pressure chambers and/or a starting process, i. e. the driving of the drive shaft, can be started. Alternatively or additionally, an emergency shutdown of the device can be initiated on the basis of the sensor signals, for example if the sensor signals change.

The sensor device can have one or more sensors. The sensors can be, for example, a capacitive sensor, an RFID sensor and/or a magnetic field sensor.

The sensor device has the advantage that, in addition or as an alternative to the pneumatic position detection device, the position and/or the presence of a machining means can be monitored. As a result, the operational reliability of the device is significantly increased. In particularly advantageous embodiments, the device includes both a sensor device and a pneumatic position detection device. As a result, at least the presence of a machining means can be determined in two different ways, in particular redundantly.

In an advantageous development, the device can have a housing cover. The housing cover can be arranged in particular axially adjacent to the connection section of the drive shaft. Independently thereof, the housing cover can be mounted pivotably on the housing, in particular can be fastened pivotably on the housing.

In a closed state, in particular in a closed position, the housing cover can close an opening of the housing at least in sections. In an opened state, in particular in a release position, the housing cover can release the opening.

When the housing cover is in the opened state, the machining means can be introduced into the device via the opening.

In the closed state, the housing cover is designed to secure the machining means axially, in particular to secure it against an axial displacement. This is advantageous, for example, if there is no force fit between the drive shaft and the machining means, that is to say if hydraulic pressure is not applied to the pressure chamber, but the machining means is arranged on the connection section. Damage to the device, for example by a machining means slipping axially off the drive shaft, can then be prevented by the housing cover. This has the advantage that the device can be operated particularly reliably and has a high level of durability.

In an exemplary embodiment of the device with a housing cover, the device can have a monitoring unit. The monitoring unit is preferably designed to monitor the state of the housing cover. For example, the monitoring unit can determine whether the housing cover is in the opened or in the closed state.

The monitoring unit advantageously has the effect that the drive shaft is driven, for example, only when the monitoring unit has determined the closed state of the housing cover. This has the advantage that the operational reliability of the device is increased for a user.

In an exemplary development of the housing cover, a receiving and transmitting unit can be provided on the housing cover. The receiving and transmitting unit can be arranged in particular on a side of the housing cover facing the connection section of the drive shaft. The receiving and transmitting unit is advantageously designed to communicate with a balancing head in or on the drive shaft. Alternatively or additionally, the receiving and transmitting unit can be designed to determine imbalances on the rotating drive shaft, in particular to determine them in a contactless manner.

The receiving and transmitting unit has the advantage that the degree of automation of the device can be further increased. Furthermore, the machining means does not need to have a separate receiving and transmitting unit in such an embodiment. By means of the receiving and transmitting unit, control and regulation loops of the device can be implemented without the interaction by a user.

In a further exemplary embodiment, the device has a securing device. The securing device is preferably designed to secure the machining means against an axial displacement. This can be necessary in particular when the machining means is connected to the connection section of the drive shaft but hydraulic pressure has not yet been applied to the pressure chamber.

The securing device can have a securing bolt. The securing bolt is preferably displaceable in a radial direction with respect to the axis of rotation. The securing bolt is preferably arranged axially adjacent to the machining means. If the securing device secures the machining means, for example, against an axial displacement, the securing bolt can be displaced radially such that the securing bolt prevents an axial displacement of the machining means. If an axial displacement of the machining means is desired, for example during loading and/or unloading, the securing bolt can be displaced radially such that an axial displacement of the machining means is possible.

The securing device advantageously has the effect that the machining means is secured against undesired slipping off of the drive shaft. This has the advantage that the operational reliability of the device is further increased and damage, for example by a machining means slipping off the drive shaft, is effectively prevented.

In an exemplary development of the aforementioned embodiment, the securing device includes a pneumatic cylinder. The pneumatic cylinder is designed to be supplied with compressed air, in particular with compressed control air. The securing bolt is preferably arranged at least in sections displaceably in the pneumatic cylinder.

The securing device can also have a restoring element, for example a spring. The restoring element can at least in sections be arranged in the pneumatic cylinder. When the pneumatic cylinder is in the pressurized state, that is to say in particular is supplied with compressed air, the securing device can be activated as a result. For example, the pressure in the pneumatic cylinder can act on the securing bolt in such a way that a restoring force of the restoring element directed against the pressure is overcome and the securing bolt is moved against the restoring force of the restoring element. When the pneumatic cylinder is not supplied with compressed air, the securing device can be deactivated as a result. The restoring force of the restoring element then preferably has the effect that the securing bolt is moved in the direction of the restoring force.

The exemplary development of the securing device with a pneumatic cylinder and a restoring element has the advantage that the securing device can be produced very cost-effectively and simply without the reliability of the securing device being impaired.

In a further exemplary embodiment of the device, the device includes a balancing head. The balancing head is preferably arranged at an axial end of the drive shaft. The balancing head is advantageously arranged axially centrally, namely on the axis of rotation of the drive shaft. The balancing head can be provided between two pressure chambers in a radial direction.

An axially central arrangement of the balancing head has the advantage that the drive shaft can be balanced by means of center balancing. This advantageously enables extremely effective and at the same time space-saving balancing of the drive shaft.

The balancing head preferably includes one or more adjustable balancing masses. Advantageously, the balancing masses are electromagnetically adjustable. The drive shaft can be balanced by adjustment, in particular by repositioning of the balancing masses. This is advantageous in particular if, for example, after a changing process, a machining means different from the preceding machining means is connected to the drive shaft.

The balancing head preferably has a communication means. The communication means can be designed, in particular, to receive information for adjusting the balancing masses. Alternatively or additionally, the communication means can be designed to transmit information about detected imbalances during the rotational movement of the drive shaft. The communication means can be connected, for example, in an information-communicating manner to the receiving and transmitting unit of the housing cover. Preferably, the energy supply of the communication means and/or the communication with the receiving and transmitting unit of the housing cover takes place in a contactless manner, in particular wirelessly. Independently of the abovementioned, the communication means can be suitable for detecting imbalances.

A balancing head having a communication means has the advantage that the degree of automation of the device is further increased.

In a further exemplary embodiment, the device includes a drive equipment. Preferably, the drive equipment is designed to drive the drive shaft, that is to say to set the drive shaft in a rotational movement about the axis of rotation. The drive equipment can have a stator and a rotor. The rotor is advantageously connected rotationally fixed to the drive shaft and can be driven by the stator. The stator can be designed to generate an alternating magnetic field, wherein the rotor is driven by the alternating magnetic field. Preferably, the stator is designed fixed to the housing.

In a further exemplary embodiment, the device can have a carrier. The carrier is preferably designed to transport one or more machining means. A machining means can be arranged on the drive shaft, in particular on the connection section, by means of the carrier. Alternatively or additionally, a machining means can be removed from the drive shaft, in particular from the connection section, by means of the carrier. Preferably, the carrier is designed to transport a machining means axially towards the drive shaft and/or to transport it axially away from the drive shaft.

A device with a carrier has the advantage that the drive shaft can be loaded and unloaded with a machining means in a fully automated manner.

In an exemplary development of the device with a carrier, the carrier is connected to an automatically operable handling unit, in particular is arranged on an automatically operable handling unit. The handling unit can be designed to move a plurality of carriers in an automated manner and/or independently of one another, in particular to move a plurality of carriers at the same time.

The handling unit advantageously enables an automated changing process. This has the advantage that the degree of automation of the device is further increased.

The carrier can have one or more grippers. The gripper is preferably designed to grip a machining means. If the gripper has gripped a machining means, for example, the carrier can transport the machining means. The gripper is preferably designed in such a manner that the gripper can be brought into engagement with an annular groove of the machining means, in particular an annular groove on the grinding wheel flange of the machining means. If the carrier has a plurality of grippers, the grippers can be distributed on the carrier in the circumferential direction, in particular be distributed regularly on the carrier.

A carrier having one or more grippers has the advantage that the machining means can be transported particularly reliably through the carrier and/or can be positioned particularly precisely by the carrier on the connection section.

In an alternative development, the carrier can be of shovel-shaped or fork-shaped design. Additionally or alternatively, the carrier can be designed to pass under the machining means, for example if the machining means is positioned on the connection section. In such a development, the carrier can be produced very cost-effectively.

In a further alternative development, the carrier can be designed as a sliding cylinder. A machining means can then slide back and forth in an axial direction on the sliding cylinder. In such a development, the carrier is relatively cost-effective in terms of production and can be operated very simply in terms of use.

The object mentioned at the outset is also achieved, according to the invention, with a method according to claim 21. Advantageous developments of the method according to the invention are the subject matter of dependent claim 22 and/or are explained in the following description.

The method according to the invention is a method for equipping or loading a device with a machining means. The device is a device according to the aforementioned embodiments.

In the method, a machining means is provided within the scope of a first method step. The provision can take place by means of a carrier. In the provision, the machining means is transported at least next to the housing of the device. The machining means can be provided in particular by means of the carrier.

In a further method step, the machining means is positioned on the drive shaft, in particular on the connection section of the drive shaft. The positioning can take place by the carrier, for example.

Subsequently, hydraulic pressure is applied to the pressure chamber of the device. By applying hydraulic pressure to the pressure chamber, the drive shaft is connected to the machining means in a force-fitting manner.

The method according to the invention has the advantage that the device can be loaded with a machining means in a particularly simple manner, and in particular without any intermediate interaction with a user, that is to say in a fully automated manner.

In an advantageous development of the method, a housing cover is opened before the positioning of the machining means on the drive shaft, in particular on the connection section. By opening the housing cover, in particular an opening of the housing is released, via which opening the machining means is introducible into the device. Preferably, the position of the housing cover is monitored by a monitoring unit.

By means of the monitoring unit, the loading method can advantageously be carried out in a fully automated manner.

In a further exemplary development, the housing cover is closed after the positioning of the machining means on the drive shaft, in particular on the connection section. Alternatively or additionally, the housing cover can be closed before hydraulic pressure is applied to the pressure chamber.

On the one hand, this has the advantage that the housing cover forms a safety device against slipping off of the machining means from the drive shaft. Such a safety device is advantageous in particular when hydraulic pressure is not applied to the pressure chamber or has not yet been applied to it sufficiently. When hydraulic pressure is applied to the pressure chamber and the drive shaft rotates, for example, the closed housing cover has the advantage that the rotation of the drive shaft can be monitored by a receiving and transmitting unit on the housing cover.

Before the application of hydraulic pressure to the pressure chamber, in a further exemplary embodiment of the method, the presence of the machining means on the connection section can be determined and/or checked. Alternatively or additionally, the position of the machining means on the connection section can be determined and/or checked. Preferably, the presence and/or the position of the machining means is determined and/or checked with a pneumatic position detection device. Notwithstanding the above, the presence and/or the position of the machining means can be determined and/or checked with a sensor device. Particularly preferably, the presence and/or the position of the machining means is determined and/or checked redundantly with a pneumatic position detection device and a sensor device.

This has the advantage that hydraulic pressure is not applied to the pressure chamber until it has been determined that the machining means is positioned correctly in relation to the connection section. As a result, unnecessary defects can be avoided and the durability of the device, in particular of the pressure chambers, can be increased. Furthermore, this increases worker protection, especially since possible bursting of the pressure chamber can be particularly effectively prevented.

The object mentioned at the outset is also achieved, according to the invention, with a method according to claim 23. Advantageous developments of the method according to the invention are the subject matter of dependent claim 24 and/or are explained in the following description.

The method according to the invention is a method for removing a machining means from a device. The device is a device according to the aforementioned embodiments.

In the method, the pressure chamber is relieved within the scope of a first method step in order to release the force-fitting connection between the machining means and the drive shaft.

The machining means is then removed from the connection section. The removal of the machining means can take place by means of a carrier, for example.

The method according to the invention has the advantage that the machining means can be removed from the device in a particularly simple manner, without any intermediate interaction with a user, that is to say in a fully automated manner, or at least in a partially automated manner.

In an exemplary development of the aforementioned method, a housing cover is opened before the removal of the machining means from the connection section of the drive shaft. By opening the housing cover, an opening of the housing is released. By way of example, the carrier is introducible into the housing via the opening. The carrier can be introducible axially into the housing, in particular with respect to the axis of rotation.

Preferably, the carrier is designed to remove the machining means from the drive shaft, in particular from the connection section, and/or to remove it axially from the housing of the device via the opening. That is to say that the machining means can be removed from the device via the opening.

The housing cover can be opened before the pressure chamber is relieved. Preferably, the carrier is then introduced into the housing of the device before the pressure chamber is relieved. In this case, the machining means is advantageously secured by the carrier against slipping off, in particular against axial slipping off, of the drive shaft when the pressure chamber is relieved.

Alternatively, the housing cover can be opened after the pressure chamber is relieved. This has the advantage that the machining means is secured by the housing cover against slipping off, in particular against axial slipping off, of the drive shaft when the pressure chamber is relieved.

In a further exemplary embodiment of the method for removing the machining means, the machining means can be secured by a securing device before the pressure chamber is relieved. The securing device can in particular prevent axial slipping off of the drive shaft when the pressure chamber is relieved. Alternatively or additionally, the securing device can prevent axial slipping off of the machining means before the machining means is removed from the connection section of the drive shaft by the carrier.

Securing by means of the securing device has the advantage that possible damage by a machining means slipping off the drive shaft is effectively prevented. This can be advantageous in particular during the relieving of the pressure chamber. The securing device increases the operational safety and the durability of the device.

The object mentioned at the outset is also achieved, according to the invention, with a changing method for changing the machining means according to claim 25.

The changing method according to the invention relates to a changing process on a device in which process a machining means is changed. The device is a device according to the aforementioned embodiments. The changing method includes at least the above-described method for equipping the device with a machining means and the method for removing the machining means from the device. These two methods are carried out, according to the invention, with a first machining means.

Thereafter, at least the method for equipping the device with a second machining means different from the first machining means is carried out.

In this method according to the invention, the changing process can advantageously be carried out in a fully automated manner, that is to say without any user interaction, or at least in a partially automated manner.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-described, different and exemplary features can be combined with one another according to the invention, insofar as this is technically meaningful and suitable. Further features, advantages and embodiments of the invention emerge from the following description of exemplary embodiments and with reference to the figures. In the figures:

FIG. 1 shows a perspective illustration of a first exemplary embodiment of a device for grinding a workpiece and/or for dressing a tool,

FIG. 2 shows a sectional illustration of the first exemplary embodiment,

FIG. 3 shows a partial detail of the sectional illustration according to FIG. 2,

FIG. 4 shows a perspective illustration of a second exemplary embodiment of a device for grinding a workpiece and/or for dressing a tool,

FIG. 5 shows a sectional illustration of the second exemplary embodiment,

FIG. 6 shows a perspective illustration of a third exemplary embodiment of a device for grinding a workpiece and/or for dressing a tool,

FIG. 7 shows a perspective illustration of a fourth exemplary embodiment of a device for grinding a workpiece and/or for dressing a tool,

FIG. 8 shows a sectional illustration of the fourth exemplary embodiment, and

FIG. 9 shows a sectional illustration of a fifth exemplary embodiment of a device for grinding a workpiece and/or for dressing a tool.

WAYS OF CARRYING OUT THE INVENTION

FIG. 1 shows a first exemplary embodiment of a device 1 in a perspective illustration.

The device 1 includes a housing 2 with a housing cover 3. The housing cover 3 is pivotable with respect to the rest of the housing 2 between a closed position and a release position. In FIG. 1, the housing cover 3 is shown in the closed position. In the closed position, the housing cover 3 closes an opening 4 of the housing 2. When the housing cover 3 is pivoted and/or pivoted from the closed position into the release position, the housing cover 3 releases the opening 4.

A machining means 30 can be introduced into the device 1 and/or removed from the device 1 via the opening 4. In the illustration shown in FIG. 1, the machining means 30 is introduced into the device 1. The machining means 30 includes a grinding wheel and a grinding wheel flange 31 with an annular groove 32, the functions of which are described in more detail further below.

The machining means 30 is connected to the device 1 via a drive shaft 5 of the device 1. The drive shaft 5 is rotatable with respect to the housing 2 about an axis of rotation D (cf. FIG. 2). The drive shaft 5 is designed to drive the machining means 30.

A balancing head 19 is arranged at the axial end of the drive shaft 5 visible in FIG. 1. The balancing head 19 includes a communication means 27 which is designed to transmit and/or receive information. The information can be used, in particular, for adjusting balancing masses arranged in the balancing head 19.

The housing cover 3 includes a receiving and transmitting unit 26 which is arranged axially opposite the communication means 27 of the balancing head 19 when the housing cover 3 is in the closed position. The receiving and transmitting unit 26 is designed to exchange information with the communication means 27 and/or to determine imbalances during rotation of the drive shaft 5.

In FIG. 1, a connection device 13 of the device 1 can also be seen. The connection device 13 is rotationally fixed with respect to the housing 2. In other words, the connection device 13 does not rotate with the drive shaft 5 when the drive shaft 5 drives the cutting means 30. The connection device 13 is designed to supply the device 1 with a pressurized hydraulic fluid. For this purpose, the connection device 13 has a hydraulic connection 14. Pressurized hydraulic fluid can flow into the connection device 13 via the hydraulic connection 14. Independently thereof, the connection device 13 is designed to supply the device 1 with compressed air. For this purpose, the connection device 13 has a pneumatic connection 15. Compressed air can flow into the connection device 13 via the pneumatic connection 15.

FIG. 2 shows the first exemplary embodiment of the device 1 illustrated in FIG. 1 in a sectional view. The section selected for the illustration runs along the axis of rotation D.

The housing cover 3 is pivotable about a pivot axis, not shown in FIG. 2, in order to be pivoted or swivelled from the closed position into the release position and/or from the release position into the closed position. The pivot axis is arranged orthogonally to the axis of rotation D and orthogonally to the image plane of FIG. 2. For a better understanding of the pivot axis of the housing cover 3, reference is also made to the illustrations in FIGS. 4 to 8.

The connection device 13 arranged on the right in FIG. 2 is designed at its axial end facing the drive shaft 5 in such a way that the pressurized hydraulic fluid can flow into a hydraulic fluid duct 11 of the drive shaft 5. The hydraulic fluid duct 11 at least in sections extends parallel to the axis of rotation D through the drive shaft 5.

The device 1 also includes a pressure intensifier 33 in the exemplary embodiment illustrated in FIG. 1 and in FIG. 2. The pressure intensifier 33 is designed to increase and/or reduce the pressure of the hydraulic fluid in the hydraulic fluid duct 11.

Independently thereof, the connection device 13 is designed at its axial end facing the drive shaft 5 in such a way that the compressed air can flow into at least one pneumatic duct 12 of the drive shaft 5. The pneumatic duct 12 at least in sections extends parallel to the axis of rotation D through the drive shaft 5.

The drive shaft 5 is driven by a drive equipment 20. The drive equipment 20 includes a stator 21 immovable with respect to the housing 2. The stator 21 is designed to drive a rotor 22 connected at least rotationally fixed to the drive shaft 5. The stator 21 preferably generates an alternating magnetic field which brings about a rotational movement of the rotor 22 about the axis of rotation D. Due to the connection between the rotor 22 and the drive shaft 5, the drive shaft 5 is also necessarily driven by the rotor 22.

In the first exemplary embodiment of the device 1, the drive shaft 5 includes a first connection section 6 and a second connection section 7. In alternative exemplary embodiments, however, the drive shaft 5 can also have only one connection section. The drive shaft 5 is connected to the machining means 30, in particular the grinding wheel flange 31 of the machining means 30, via the connection sections 6, 7. With regard to the structural and geometrical details of the connection sections 6, 7, reference is made to the explanations below with regard to FIG. 3.

In each of the connection sections 6, 7, the drive shaft 5 has two pressure chambers 8. The pressure chambers 8 are designed to be supplied with hydraulic pressure. For this purpose, the pressure chambers 8 are connected fluidically to the hydraulic fluid duct 11. In other words, the pressure chambers 8 are supplied with hydraulic fluid via the hydraulic fluid duct 11. Advantageously, hydraulic pressure is always applied to the pressure chambers 8 at the same time and with the same intensity.

The pressure chambers 8 of the first connection section 6 are delimited at least in sections by a first elastic side wall 9. The pressure chambers 8 of the second connection section 7 are delimited at least in sections by a second elastic side wall 10.

The elastic side walls 9, 10 are designed to deform in a radial direction. This has the effect that when hydraulic pressure is applied to the pressure chambers 8, the elastic side walls 9, 10 deform radially outwards. This deformation of the elastic side walls 9, 10 in the radial direction has the consequence that when a machining means 30 is arranged on the connection sections 6, 7 of the drive shaft 5 and hydraulic pressure is applied to the pressure chambers 8, the elastic side walls 9, 10 are pressed against the inner lateral surface of the grinding wheel flange 31 of the machining means 30. As a result, the drive shaft 5 is braced with the machining means 30. The elastic side walls 9, 10 are connected to the grinding wheel flange 32 of the machining means 30 in a force-fitting manner by the hydraulic pressure in the pressure chambers 8.

For the sake of durability, it is advantageous that hydraulic pressure is not applied to the pressure chambers 8 until a machining means 30 is positioned correctly on the connection sections 6, 7. Otherwise, there is the risk that the elastic side walls 9, 10 deform in an uncontrolled manner and the drive shaft 5 can be damaged as a result. In order to ensure that a machining means 30 is positioned on the connection sections 6, 7 and in order to ensure that the machining means 30 is also positioned correctly on the connection sections 6, 7, the device 1 includes a pneumatic position detection device 28 and a sensor device 16. In principle, it is sufficient if the device has either a pneumatic position detection device 28 or a sensor device 16. However, the probability of an incorrect detection is significantly reduced by the redundancy.

The sensor device 16 includes a sensor element 17. In the illustrated exemplary embodiment, the sensor element 17 is a capacitive sensor element 17 which is designed as a proximity sensor. The proximity of the machining means 30, in particular the proximity of the grinding wheel flange 31 of the machining means 30, can be detected by means of the capacitive sensor element 17. In this case, the capacitive sensor element 17 is set such that the proximity is detected only when the machining means 30 is positioned correctly on the connection sections 6, 7 of the drive shaft 5.

The pneumatic position detection device 28 is designed to detect the position of the machining means 30 connected to the drive shaft 5, in particular by supplying compressed air. For this purpose, the pneumatic position detection device 28 has three compressed air openings 29. The compressed air openings 29 are distributed regularly at a distance of 120° in each case over the circumference of the drive shaft 5 and are designed such that compressed air can flow out of the compressed air openings 29 in an axial direction. In FIG. 2, one of the three compressed air openings 29 is shown.

The compressed air supply of the pneumatic position detection device 28 takes place via the pneumatic duct 12. The compressed air openings 29 are arranged on the drive shaft 5 in such a manner that if a machining means 30, in particular the grinding wheel flange 31 of the machining means 30, is positioned correctly on the connection sections 6, 7, the compressed air openings 29 are closed by the machining means 30, in particular by the grinding wheel flange 31. The closure of the compressed air openings 29 causes the compressed air to build up within the pneumatic position detection device 28.

If the machining means 30, in particular the grinding wheel flange 31, is not positioned correctly on the connection sections 6, 7, the compressed air will flow out via at least one of the compressed air openings 29. This leads to a pressure loss within the pneumatic position detection device 28. This pressure loss can be measured in such a manner that, on one hand, it can be detected whether a machining means 30 is positioned at all on the connection sections 6, 7 and, on the other hand, it can be detected if the machining means 30 has an oblique position with respect to the axis of rotation D.

In addition to the sensor device 16 and the pneumatic position detection device 28, a monitoring unit (not illustrated) for monitoring the closed state of the housing cover 3 is provided in the first exemplary embodiment. As an additional safety measure, hydraulic pressure is not applied to the pressure chambers 8 until it is determined by the monitoring unit that the housing cover 3 is in the closed position, as shown in FIGS. 1 and 2.

Only when the closed position of the housing cover has been determined by the monitoring unit, the sensor device 16 has detected an approach of the machining means 30 and a uniform dynamic pressure has built up within the pneumatic position detection device 28 is hydraulic pressure applied to the pressure chambers 8 in the first exemplary embodiment. In a next step, it is measured by means of pressure sensors (not illustrated) whether a sufficiently high hydraulic pressure has built up in the pressure chambers 8. Only when all these prerequisites are met is the drive shaft 5 driven by the drive equipment 20 and the machining means 30 rotated by the drive shaft 5.

FIG. 3 shows a detail of the drive shaft 5 from FIG. 2. In the detail shown in FIG. 3, in particular the connection sections 6, 7 are illustrated on an enlarged scale. The illustration of the machining means 30 has been omitted in the illustration of FIG. 3 for the sake of clarity.

As can be seen in FIG. 3, the first connection section 6 and the second connection section 7 are arranged at an axial end of the drive shaft 5 (in the illustrations of FIG. 2 and FIG. 3, the connection sections 6, 7 are arranged at the left axial end of the drive shaft 5). The first connection section 6 and the second connection section 7 form at least in sections the outer lateral surface of the drive shaft 5.

The first connection section 6 differs substantially from the second connection section 7 in that the first elastic side wall 9 of the first connection section 6 has a smaller radial distance from the axis of rotation D than the second elastic side wall 10 of the second connection section 7. In other words, the drive shaft 5 has a greater diameter in the second connection section 7 than in the first connection section 6. The different radial distances of the connection sections 6, 7 have the effect that machining means 30 with different internal diameters can be braced with one and the same drive shaft.

In order to enable a machining means 30 to be pushed onto the drive shaft 5 (in the illustration selected in FIG. 3, the machining means is pushed onto the drive shaft 5 from left to right), the second connection section 7, i.e. the connection section 7 with the greater diameter, is arranged in the pushing-on direction behind the first connection section 6, i.e. the connection section 6 with the smaller diameter.

The device 1 can also have a blow-off device not illustrated in FIGS. 1 to 3. The blow-off device is designed to blow contaminants from the connection sections 6, 7 if no machining means 30 is positioned on the connection sections 6, 7. This is important in particular because the contaminants would otherwise be clamped between the elastic side walls 9, 10 and the grinding wheel flange 31 of the machining means 30 during the next bracing of the drive shaft 5 with the machining means 30. This can lead to damage to the connection sections 6, 7 and/or the machining means 30 or disturb the frictionless operation.

In order to free the connection sections 6, 7 from contaminants, it is possible to integrate the blow-off device into the pneumatic position detection device 28. For example, compressed air can be blown out via the compressed air openings 29 of the pneumatic position detection device 28 if no machining means 30 is positioned on the connection sections 6, 7. On account of the axial outflow direction, the compressed air then flows directly over the connection sections 6, 7, so that any contaminants on the connection sections 6, 7 are blown off in an axial direction (from right to left in FIG. 3).

In an alternative exemplary embodiment (not illustrated), the discharge device can also be a device of the device 1 that is separate from the pneumatic position detection device 28. For this purpose, a separate pneumatic duct can be provided which, analogously to the pneumatic duct 12, at least in sections extends parallel to the axis of rotation D through the drive shaft 5.

In the first exemplary embodiment according to FIGS. 1-3, the drive shaft 5 has a circular cross-sectional area in the region of the connection sections 6, 7. In alternative exemplary embodiments, however, it is also conceivable for the drive shaft 5 to have a polygonal cross-sectional area, in particular a regularly polygonal cross-sectional area, in the region of the connection sections 6, 7.

FIG. 4 shows a perspective illustration of a second exemplary embodiment of the device 1. In contrast to the first exemplary embodiment, the device 1 of the second exemplary embodiment additionally includes a changing device 50 for changing the machining means 30. Otherwise, the structural design of the device 1 according to the second exemplary embodiment corresponds to the structural design of the device 1 according to the first exemplary embodiment.

The changing device 50 is designed to load and/or unload the drive shaft 5 with a machining means 30. A changing process can also be carried out by the changing device 50. This means that a first machining means 30 on the drive shaft 5 can be replaced by a second machining means 30 different from the first machining means 30 by means of the changing device 50. For handling the different machining means 30, in particular for the automated handling of the different machining means 30, the changing device 50 is connected to a handling unit, not illustrated.

The changing device 50 includes a carrier 51, which is designed to transport the machining means 30. As shown in FIG. 4, the machining means 30 is introduced into the housing 2 or removed from the housing 2 of the device 1 via the opening 4 through the carrier 51. The machining means 30 is moved in an axial direction by the carrier 51 with respect to the axis of rotation D. As a result, the carrier 51 can push the machining means 30 onto the drive shaft 5, in particular onto the connection sections 6, 7, and/or remove it from the drive shaft 5, in particular from the connection sections 6, 7.

According to the second exemplary embodiment, a plurality of grippers 52, namely a total of three grippers 51 of identical design, are arranged on the carrier 51. As can be seen in FIG. 4, the grippers 52 are distributed on the carrier 51 at regular distances (all) 120° over the circumference of the carrier 51. The grippers 51 are designed to engage in the annular groove 32 of the grinding wheel flange 31 in order to transport the machining means 30.

As can be seen very well in the sectional illustration of the second exemplary embodiment shown in FIG. 5, the grinding wheel flange 31 is engaged behind at least in sections by the grippers 51 when the grippers 51 engage radially in the annular groove 32. As a result of this form fit between the grippers 51 and the annular groove 31, the machining means 30 can be gripped particularly reliably and stably by the carrier 51.

In an exemplary method for loading or equipping the device 1 with a machining means 30, the machining means 30 is firstly provided axially to the left next to the device by the changing device 50. In this case, the carrier 51 grips the machining means 30 by means of the grippers 51.

Subsequently, the housing cover 3 is opened, so that the housing cover 3 assumes the position shown in FIGS. 4 and 5 and the opening 4 is released. As a result of an axial displacement of the carrier 51, the machining means 30 is then introduced into the housing 2 of the device 1 via the opening 4. The axial displacement with respect to the axis of rotation D takes place until the machining means 30 is pushed onto the connection sections 6, 7 of the drive shaft 5 and is positioned correctly. The correct positioning of the machining means 30 can be determined, as already described above, by the sensor device 16 and/or by the pneumatic position detection device 28. Subsequently, hydraulic pressure is applied to the pressure chambers 8 in order to connect the drive shaft 5 to the machining means 30 in a force-fitting manner.

Before the drive shaft 5 is then driven by the drive equipment 20, the carrier 52 has to be pulled out of the housing 2 and the housing cover 3 closed again. For this purpose, the grippers 52 are moved radially outward. As a result, the engagement of the grippers 52 with the annular groove 32 is released. Subsequently, the carrier 52 is moved axially out of the housing 2.

In an exemplary method for unloading the device 1 or for removing a machining means 30 from the device 1, the drive shaft 5 is fully braked in a first step. Subsequently, the housing cover 3 is opened, so that the carrier 52 can be introduced into the housing 2 axially via the opening 4. When the carrier 52 is positioned exactly with respect to the machining means 30, the grippers 52 are moved radially inwards in order to be brought into engagement with the annular groove 32. As a result, the machining means 30 is fixed by means of the changing device 50. Subsequently, the pressure chambers 8 are fully relieved. The force-fitting connection between the machining means 30 and the drive shaft 5 is thus released. The machining means 30 can then be pulled off the drive shaft 5. This can be realized by the carrier 52, which is fixedly connected to the machining means 30 via the grippers 52, being pulled axially out of the housing 2 via the opening 4.

By means of a serial sequence of the methods for loading and unloading the device 1 with in each case different machining means 30, a fully automated changing process can be carried out.

FIG. 6 shows a perspective illustration of a third exemplary embodiment of the device 1. The third exemplary embodiment differs from the second exemplary embodiment only in the changing device 60.

In the changing device 60 of the third exemplary embodiment, the carrier 61 is of shovel-shaped design. In alternative exemplary embodiments, however, the carrier 61 can also be of fork-shaped design. It is important that the carrier 61 has such a width that the carrier 61 can engage with its side elements 62 in the annular groove 32 of the machining means 30.

The method for loading the device 1 with the changing device 60 according to the third exemplary embodiment takes place analogously to the loading method with the changing device 50 according to the second exemplary embodiment. The two loading methods differ only in that, instead of releasing the grippers 52 from engagement with the annular groove 31, the carrier 61 is lowered in order to release the side elements 62 from engagement with the respectively corresponding annular groove 31.

In order to unload the device 1, the carrier 61 can be moved up to the drive shaft 5. For this purpose, the carrier 61 can be moved parallel to the axis of rotation D of the drive shaft 5. Subsequently, the machining means 30 can be pulled off the drive shaft 5 and mounted on the carrier 61. In this case, each side element 62 of the carrier 61 engages in a corresponding annular groove 32 of the machining means 30. The machining means 30 can then be moved out of the housing 2 analogously to the method according to the second exemplary embodiment. In this case, the engagement of the side elements 62 in the corresponding annular grooves 32 has the effect that the machining means 30 rests securely on the carrier 61.

FIG. 7 shows a perspective illustration of a fourth exemplary embodiment of a device 1. The fourth exemplary embodiment differs from the second and the third exemplary embodiment of the device 1 in the changing device 70.

In the fourth exemplary embodiment, the carrier 71 of the changing device 70 is a sliding cylinder 71. The sliding cylinder 71 is designed in such a manner that a machining means 30, in particular the grinding wheel flange 31 of the machining means 30, can slide back and forth in an axial direction on the outer lateral surface of the sliding cylinder 71.

For loading purposes, the sliding cylinder 71, together with a machining means 30 positioned on the sliding cylinder 71, can be introduced axially into the housing 2 via the opening 4. If the sliding cylinder 71 bears with an axial end face against the drive shaft 5 (cf. FIG. 8), the machining means 30 can be pushed onto the drive shaft 5 by the sliding cylinder 71.

For unloading purposes, the machining means 30 arranged on the drive shaft 5 can be pushed onto the sliding cylinder 71 by the connection sections 6, 7 and can then be pulled axially out of the housing 2 together with the sliding cylinder 71 via the opening 4.

FIG. 8 shows the fourth exemplary embodiment in a sectional illustration. It can be seen here that the outer diameter of the sliding cylinder 71 corresponds to the outer diameter of the first connection section 6 of the drive shaft 5.

FIG. 9 shows a sectional illustration of a fifth exemplary embodiment of the device 1. The device 1 of the fifth exemplary embodiment corresponds structurally substantially to the device 1 according to the first exemplary embodiment. In this respect, reference is made to the description of the first exemplary embodiment with regard to identical reference numerals. The section which was selected for the illustration in FIG. 9 runs orthogonally to the axis of rotation D and intersects the balancing head 19 in its communication means 27.

The device 1 according to the fifth exemplary embodiment differs from the device 1 according to the first exemplary embodiment in that the device 1 of the fifth exemplary embodiment has an additional securing device 18. The securing device 18 is designed to secure the machining means 30 against an axial displacement. For this purpose, the securing device 18 has a securing bolt 23, a pneumatic cylinder 24 and a restoring element 25.

The securing bolt 23 can be moved back and forth with respect to the housing 2 and/or with respect to the pneumatic cylinder 24 between a first position and a second position which differs from the first position. FIG. 9 shows the securing bolt 23 in the second position. In the second position, the securing bolt 23 is at least in sections pressed out of the pneumatic cylinder 24. The part of the securing bolt 23 which is at least in sections pressed out of the pneumatic cylinder 24 is in this case pushed radially inwards such that an axial displacement of the machining means 30 out of the image plane is prevented by the securing bolt 23.

In the first position, the securing bolt 23 is displaced radially outwards to such an extent that the securing bolt 23 is arranged completely or at least substantially within the pneumatic cylinder 24. This has the consequence that the securing bolt 23 does not prevent resp. releases an axial displacement of the machining means 30 out of the image plane in the first position.

In other words, an axial displacement of the machining means 30 is released by the securing device 18 when the securing bolt 23 is in the first position. When the securing bolt 23 is in the second position (cf. FIG. 9), the securing device 18 secures the machining means 30 against an axial displacement. This is preferably the case if a machining means 30 is arranged on the drive shaft 5, but hydraulic pressure is not or not sufficiently applied to the pressure chambers 8 of the connection sections 6, 7.

The restoring element 25 is designed as a spring 25 in the exemplary embodiment illustrated in FIG. 9. The restoring element 25 exerts a compressive force on the securing bolt 23 in the second position of the securing bolt 23. The compressive force of the restoring element 25 is designed in such a way that the compressive force promotes a displacement of the securing bolt 23 from the first position into the second position. In other words, the securing bolt 23 is pressed radially inwards by the restoring element 25.

The displacement of the securing bolt 23 from the second position into the first position is brought about by pneumatic pressure being applied to the pneumatic cylinder 24. The pneumatic pressure is so great that the restoring force of the restoring element 25 is overcome. Under the influence of the pneumatic pressure, the securing bolt 23 moves radially inwards, i.e. the second position, radially outwards, i.e. into the first position.

In the method for loading the device, the securing device 18 can secure the machining means 30 after the positioning of the machining means 30 on the drive shaft 5. This ensures that the machining means 30 cannot slip axially, for example during the pressure build-up within the pressure chambers 8.

Analogously, the securing device 18 can secure the machining means 30 in the method for unloading the device, for example while the pressure chambers 8 are relieved. The securing device 18 can be designed such that a certain slipping of the machining means 30 on the drive shaft 5 is permitted, although slipping of the machining means 30 off from the drive shaft 5 is prevented by the securing device 18.

Claims

1. A device for grinding a workpiece and/or for dressing a tool, the device including:

(a) a housing,

(b) a drive shaft rotatable with respect to the housing about an axis of rotation and configured to drive a machining means, the machining means being connectable to the drive shaft, wherein

(c) the drive shaft has a connection section for connection to the machining means, and

(d) a pressure chamber to which hydraulic pressure can be applied is arranged in the connection section and is delimited at least in sections by an elastic side wall, wherein

(e) the elastic side wall is configured to deform when hydraulic pressure is applied to the pressure chamber in order to produce a force fit between the drive shaft and the machining means,

wherein the device has a connection device rotationally fixed with respect to the housing, and wherein the connection device includes a hydraulic connection for supplying the device with hydraulic fluid and/or a pneumatic connection for supplying the device with compressed air.

2. The device according to claim 1, wherein the side wall at least in sections delimits the pressure chamber radially with respect to the axis of rotation, and the side wall is configured to brace the drive shaft in the radial direction with the machining means when hydraulic pressure is applied to the pressure chamber.

3. The device according to claim 1, wherein the side wall at least in sections delimits the pressure chamber radially on the outside with respect to the axis of rotation, and the side wall is configured to deform radially on the outside when hydraulic pressure is applied to the pressure chamber in order to produce a force fit between the drive shaft and the machining means.

4. The device according to claim 1, wherein the connection section has several pressure chambers, wherein each of the several pressure chambers is delimited at least in sections by the elastic side wall.

5. The device according to claim 1, wherein the drive shaft has a first connection section and a second connection section, wherein the first connection section includes a first elastic side wall at a first radial distance from the axis of rotation, and the second connection section includes a second elastic side wall at a second radial distance from the axis of rotation, wherein the first radial distance is greater than or less than the second radial distance.

6. The device according to claim 1, wherein the drive shaft has a hydraulic fluid duct for supplying the pressure chamber with the hydraulic fluid.

7. The device according to claim 1, wherein the device has a pneumatic position detection device, wherein the position detection device is configured to detect the position of the machining means connected to the drive shaft by supplying compressed air.

8. The device according to claim 1, wherein the device has a blow-off device, wherein the blow-off device includes a pneumatic duct, which at least in sections extends parallel to the axis of rotation through the drive shaft, and the blow-off device is configured to remove contaminants on the connection section by blowing compressed air, which can be supplied via the pneumatic duct, onto the connection section.

9. (canceled)

10. The device according to claim 1, wherein the device has a sensor device, wherein the sensor device is configured to detect a correct fit of the machining means with respect to the drive shaft.

11. The device according to claim 1, wherein the device has a housing cover and the housing cover is arranged axially in front of the connection section of the drive shaft, and the housing cover in the closed state at least in sections closes an opening of the housing, wherein a machining means is introducible into the device via the opening in the open state of the housing cover, and wherein in the closed state of the housing cover the machining means is preferably axially secured even in the absence of a force fit between the drive shaft and the machining means.

12. The device according to claim 11, wherein further comprising a receiving and transmitting unit arranged on a side of the housing cover facing the connection section of the drive shaft.

13. The device according to claim 1, wherein the device has a securing device wherein the securing device is configured to secure the machining means against an axial displacement when the machining means is connected to the connection section of the drive shaft.

14. The device according to claim 13, wherein the securing device has a pneumatic cylinder configured to be transferred between a first position, in which the securing device releases an axial displacement of the machining means, and a second position, in which the securing device secures the machining means against an axial displacement.

15. The device according to claim 1, characterized in that further comprising a balancing head is arranged centrally at an axial end of the drive shaft, preferably in the connection section.

16. The device according to claim 1, wherein the device has a carrier, wherein the carrier is configured to transport the machining means.

17. The device according to claim 16, wherein the carrier is arranged on an automatically operable handling unit.

18. The device according to claim 16, wherein the carrier has a gripper, wherein the gripper is configured to engage in an annular groove on the machining means in order to transport the machining means.

19. The device according to claim 16, wherein the carrier is shovel-shaped.

20. The device according to claim 16, wherein the carrier is a sliding cylinder, and the sliding cylinder is configured such that the machining means can slide back and forth in an axial direction on the sliding cylinder.

21. The device according to claim 1, wherein the sensor device includes at least one sensor element configured to detect the axial position of the machining means with respect to the housing.

22. The device according to claim 1, wherein the grinding machine has a pressure intensifier in the drive shaft.

23. A method for equipping a device according to claim 1 with a machining means, the method including the following method steps:

(a) providing the machining means,

(b) positioning the machining means on the connection section of the drive shaft, and

(c) applying hydraulic pressure to the pressure chamber in order to connect the drive shaft to the machining means in a force-fitting manner.

24. The method according to claim 23, wherein, before the application of hydraulic pressure to the pressure chamber, a presence and a position of the machining means on the connection section is determined with a position detection device and/or a sensor device.

25. A method for removing a machining means from a device according to claim 1, the method including the following method steps:

(a) relieving the pressure chamber in order to release the force-fitting connection between the machining means and the drive shaft, and

(b) removing the machining means from the connection section of the drive shaft.

26. The method according to claim 25, wherein, before the pressure chamber is relieved or before the machining means is removed from the connection section of the drive shaft, an axial slippage of the machining means off the drive shaft is prevented by a securing device.

27. A changing method for changing a machining means on a device according to claim 1, wherein the method according to claim 23 and the method according to one claim 25 are carried out with a first machining means and subsequently at least the method according to claim 23 is carried out with a second machining means different from the first machining means.