EP3009229A2 - Grinding machine, in particular compact tip-free grinding machine - Google Patents

Abstract

The invention relates to a grinding machine (10), with a machine bed (12), a grinding spindle (28) which is coupled to a spindle drive (36) and adapted to receive a grinding wheel (32), a control spindle (30), with a Spindle drive (38) coupled and adapted to receive a regulating wheel (34), a workpiece support (46) for receiving a workpiece to be machined (50) between the grinding spindle (28) and the control spindle (30), wherein the grinding spindle (28) and the control spindle (30) coupled to the machine bed (12) and are movable relative to each other, wherein the grinding spindle (28) and the control spindle (30) form a spindle set (22), wherein on the machine bed (12) has a longitudinal guide (68) is formed in which a base carriage (54) is received, wherein the machine bed (12) and the base carriage (54) define a first movement axis (60), the grinding spindle (28) coupled to the base carriage (54) and a second associated with the base carriage (54) and a third movement axis (64) is associated, and wherein the grinding spindle (28) and the control spindle (30) movable relative to each other and on the Workpiece support (46) are deliverable.

Description

The present invention relates to a grinding machine, in particular a compact designed centerless grinding machine, with a machine bed, a grinding spindle which is coupled with a spindle drive and adapted to receive a grinding wheel, a control spindle which is coupled with a spindle drive and adapted to receive a regulating wheel, and with a workpiece support for receiving a workpiece to be machined between the grinding spindle and the control spindle. Such grinding machines can generally be used for plunge grinding and / or through-grinding.

The present disclosure is particularly concerned with machine concepts for compact centerless centerless grinders. This should be understood in particular those grinding machines that are realized with manageable space may, for example, machines that can be realized on a base that is less than 1.5 mx 1.5 m (meters), preferably less than 1.25 mx 1.25 m. The base areas mentioned may in particular be base areas of an enclosure or of a housing of the grinding machine. It is understood that, for example by attachments and a necessary space for access openings, handling equipment, service openings and the like. Basically, a larger footprint may be required. However, it will be apparent from the dimensions given that compact grinding machines in the context of this disclosure are understood to mean those grinding machines which further reduce the footprint of conventional grinders realized in "standard sizes" by at least about 20%, preferably at least about 40% preferably below by at least 50%.

Various concepts for the design of centerless grinding machines, in particular centerless cylindrical grinding machines, are approximately from the DE 10 2011 117 819 A1 known. The document deals in particular with devices for dressing the grinding wheel and the regulating wheel of a centerless cylindrical grinding machine, wherein the dressing tools are movable in a certain way, in particular relative to the grinding wheel or the regulating wheel.

Other designs of centerless grinding machines are from about DE 60 2004 008 351 T2 , of the DE 695 10 910 T2 , as well as the DE 298 25 161 U1 known.

Grinding machines for machining are well known in the art. Furthermore, centerless grinding machines are known, in particular centerless cylindrical grinding machines. Centerless cylindrical grinding machines can be designed, for example, as external cylindrical grinding machines or internal cylindrical grinding machines. Centerless grinding machines can generally be used for machining round workpieces, preferably rotationally symmetrical workpieces. Centerless grinding machines can be used, for example, for plunge grinding or through-grinding.

Centerless grinding machines are particularly suitable for mass production and mass production. Centerless grinding machines usually have a grinding wheel and a regulating wheel, wherein both the grinding wheel and the regulating wheel are rotationally driven. The grinding wheel and the regulating wheel are usually arranged parallel to one another and designed to receive a workpiece to be machined between them. The grinding wheel usually has or is coated with an abrasive material. Regulating wheel may have as rubber materials or coated with these. Alternatively, control discs may have or be coated with ceramic materials.

Furthermore, centerless grinding machines usually have a workpiece support which acts as a support for the workpiece. During grinding in a centerless grinding machine, the workpiece can accordingly be contacted by the grinding wheel, by the regulating wheel and by the workpiece support. The grinding wheel and the regulating wheel can be arranged regularly parallel to each other. However, it is also conceivable to offset the regulating wheel by a small angle relative to the grinding wheel. This may include tilting the regulating wheel spindle about an axis, which may also be referred to as a transverse axis. The transverse axis is oriented in particular transversely to a longitudinal axis of the workpiece to be machined. In this way, a feed movement for the workpiece can be generated.

Often, the grinding wheel has a larger diameter than the regulating wheel. The grinding wheel and the regulating wheel are regularly provided with drives or can be coupled with these. Usually, the grinding wheel and the regulating wheel are driven in the same direction of rotation, but the respective drives are controlled such that a peripheral speed of the grinding wheel deviates from a peripheral speed of the regulating wheel. Since the workpiece during the grinding process is both in engagement with the grinding wheel and in engagement with the regulating wheel, which are usually driven in the same direction, this is offset by the interaction of the grinding wheel and the regulating wheel in a rotation with a sense of rotation, the direction of rotation of the grinding wheel or the regulating wheel is opposite. Due to the different peripheral speeds of the grinding wheel and the regulating wheel can between the workpiece and the grinding wheel a Obtain relative movement, which may include slippage. In this way, material can be removed from the workpiece.

Against this background, the invention has for its object to provide a grinding machine, in particular a compact designed centerless grinding machine, which can inherit the concept of a limited space and yet provides the widest possible functionality. In particular, it is preferred that non-cylindrical workpieces, such as conical workpieces, workpieces with recesses, grooves, shoulders and the like, can be machined with such a grinding machine. Furthermore, it is preferred that the grinding machine can be realized with little effort and can be operated cost-effectively. Finally, it is further preferred if the grinding machine has a high degree of robustness and possibly required service work and / or repair work can be carried out with little effort.

This object is achieved by a grinding machine, in particular a compact designed centerless grinding machine, with a machine bed, a grinding spindle which is coupled with a spindle drive and adapted to receive a grinding wheel, a control spindle which can be coupled with a spindle drive and adapted to receive a regulating wheel is a workpiece support for receiving a workpiece to be machined between the grinding spindle and the control spindle, wherein the grinding spindle and the control spindle coupled to the machine bed and are movable relative to each other, wherein the grinding spindle and the control spindle form a set of spindles, wherein on the machine bed a longitudinal guide is formed in which a base carriage is accommodated, the machine bed and the base carriage defining a first movement axis, wherein the grinding spindle is coupled to the base carriage and associated with a second movement axis, wherein the control pi bundled with the base carriage and a third axis of movement is associated, and wherein the grinding spindle and the control spindle relative to each other are movable and deliverable to the workpiece support.

The object of the invention is completely solved in this way.

In accordance with the invention, an extremely compact and space-saving design is made possible by providing the full functionality of the grinding machine, although basically only three axes of movement are provided for the essential components of the grinding machine. In the context of this elaboration, the term movement axis should be understood in its usual meaning in the field of machine tools. Accordingly, a movement axis may be a linear movement axis, which allows a linear movement between two components of the grinding machine. Furthermore, the movement axis may be a rotational movement axis or a pivoting axis which enables a relative rotational movement or pivoting movement between two components of the grinding machine. Usually, therefore, a total of six axes of motion are conceivable in three-dimensional space, as long as a Cartesian coordinate system is used. Of the six motion axes mentioned above, three axes can fundamentally relate to linear movements, for example along an X-axis, a Y-axis and a Z-axis. Furthermore, three axes of movement in the form of so-called. Swivel axes may be provided, which concern about rotational movements or pivotal movements about the X-axis, about the Y-axis and about the Z-axis. According to a common nomenclature, the axes of rotation or pivot axes may accordingly be an A-axis, a B-axis and a C-axis.

It is understood that the above configuration does not necessarily exclude, at least in some embodiments, that additional auxiliary axes are optionally provided. However, these auxiliary axes do not have to be used primarily for infeed movements within the scope of the actual workpiece machining or dressing of the grinding wheel and / or regulating wheel. For example, reference is made to a conceivable auxiliary axis for the defined inclination of the control spindle about the X axis. Such an axis can also be referred to as the A-axis and describe pivoting movements about the X-axis. By means of an A-axis movement of the control spindle, a deliberate inclination can be brought about, which can bring about a workpiece feed during through-grinding. Furthermore, even with plunge loops, an at least minimum inclination may be desired by inclining the control spindle about the X-axis in order to be able to receive the workpiece (axially) in a defined manner. This can further increase the accuracy and reproducibility.

According to the above embodiment, it is proposed to provide the grinding machine with only three axes of movement for its essential components. By way of example, the three axes of motion can be selected from the "pool" of axes of movement illustrated above. If, for example, the grinding spindle and the control spindle of the grinding machine are concerned, which may in principle be coupled to one another but movably mounted relative to one another, it would even be conceivable to carry out two of the abovementioned three axes of motion as fundamentally parallel or coincident axes of movement. This can bring about the further advantage that guide elements or the like of the two parallel or coincident movement axes can be used. This can further reduce the effort for the realization of the grinding machine.

If, in the context of this elaboration, it is said that a first component can be coupled or coupled with a second component, this can include both the case where the two components are directly coupled or coupled with one another, or the case where both components are indirect coupled or coupled together. An indirect coupling can take place, for example, if further components of the first component and the second component are interposed. If, however, in the context of these statements, it is explicitly mentioned that a first component is coupled directly to or incorporated in a second component, it can be assumed that no further component of the first component and the second component is interposed or interposed.

According to the nomenclature customary in machine tools, in particular grinding machines, the longitudinal guide may in particular be a so-called Z-guide, which allows movement in the longitudinal direction Z-direction. Usually, the longitudinal direction or Z-direction is oriented parallel to a longitudinal axis of the workpiece to be machined or of a tool holder or support designed to receive the workpiece.

Further, a transverse direction or X-direction is usually defined which is perpendicular to the longitudinal direction and can span a plane together with the longitudinal direction, which may be oriented, for example, essentially parallel to a supporting surface of the machine bed. Furthermore, a so-called. Vertical direction or Y-direction can be provided, which can basically describe a vertical extent.

If, in the context of this elaboration, a delivery movement is mentioned, this generally refers to a movement of the grinding spindle or the regulating spindle, which can take place substantially in the transverse direction, that is to say essentially perpendicular to the longitudinal direction. It is understood that, in principle, movements are also conceivable which are not ideally executed parallel to the transverse direction or perpendicular to the longitudinal direction. This may be the case, in particular, when a deliberate inclination of the grinding wheel and / or the regulating wheel in relation to the longitudinal axis of the workpiece to be machined is brought about, for example, to effect a workpiece feed. Within the scope of this elaboration, a feed movement is basically a movement essentially parallel to the longitudinal direction and essentially perpendicular to the transverse direction. The feed movement can take place, for example, during through-grinding through the workpiece itself relative to the spindle set. For this purpose, it is conceivable to tilt the control spindle in a defined manner about a transverse axis in order to generate a force component acting in the feed direction when it is being attacked on the workpiece. The corresponding movement axis can also be referred to as the A-axis, which describes pivoting movements about those transverse axes.

Preferably, both the grinding spindle and the control spindle are coupled indirectly via the base carriage to the machine bed of the grinding machine. Thus, both the grinding spindle and the regulating spindle can be moved together by a corresponding amount in the longitudinal direction when the base carriage is moved in the longitudinal direction. The spindle set formed by the grinding spindle and the control spindle can be considered as a logical unit. In other words, the term spindle set can primarily serve as the name of the group formed by the grinding spindle and the regulating spindle. It is not necessary here that the grinding spindle and the control spindle must form a structural unit.

The above design of the grinding machine has the significant design advantage that about no separate B-axis (movement axis for pivoting movements around the Y-axis) is required to bring about a certain inclination between the grinding spindle and the workpiece support or the control spindle and the workpiece support. By means of such B-axes, of which one is usually provided for each of the grinding spindle and the control spindle, such inclinations can on the one hand be generated easily and flexibly and adapted during operation of the grinding machine. This can increase the flexibility and productivity of a conventional grinding machine. At the same time, however, the structural complexity for such an arrangement, which makes correspondingly necessary further movement axes, significantly larger.

The present invention therefore makes use of the fact that workpieces whose shape differs significantly from a pure cylindrical shape can also be processed if the grinding wheel and / or the regulating wheel are correspondingly "mirror-symmetrical" to the workpiece. According to the basic concept described above, it is at least possible that the grinding spindle and the control spindle can be moved "freely" in such a way that the grinding wheel received on the grinding spindle and / or the regulating wheel accommodated on the control spindle can be brought into engagement with corresponding dressing tools Adjust the contour of the desired shape of the workpiece to be machined. In other words, at least one dressing unit may be provided with a dressing tool, which is preferably fixedly coupled to the machine bed, so that using only three axes of movement adjustment of the grinding wheel or the regulating wheel can be made to allow the machining of non-cylindrical workpieces , Ideally, each of the grinding wheel and the regulating wheel can be delivered by itself, using only two axes of the three axes, in the desired manner to the dressing tool associated with the respective disk and to obtain its desired contour by a cutting engagement.

The above-illustrated basic principle of a compact designed centerless grinder with only three axes of motion for the major components of the grinder allows for a plurality of variations which may be the subject of preferred embodiments.

According to a preferred embodiment, the first spindle of the spindle set is coupled via a primary guide unit to the base carriage, which defines the second movement axis, wherein a second spindle of the spindle set is coupled via a secondary guide unit to the base carriage, which defines the second movement axis, wherein at least one the primary guide unit and the secondary guide unit is designed as a pivoting guide or linear guide.

Preferably, the primary guide unit and the secondary guide unit use at least sections of the same guide elements. It is further preferred if the primary guide unit and the secondary guide unit define parallel movement axes or even at least partially coincident motion axes.

According to a further embodiment, the primary guide unit is coupled to the base carriage. According to a further variant, the secondary guide unit is also coupled directly to the base carriage. In this way, both the primary guide unit and the secondary guide unit can use the same guide elements that are provided in the base carriage. According to an alternative embodiment, the primary guide unit is coupled directly to the base carriage, wherein the secondary guide unit is coupled directly to the primary guide unit. According to this embodiment, the primary guide unit may be interposed between the base carriage and the secondary guide unit.

According to a further embodiment, a movement of the primary guide unit relative to the base carriage effects a corresponding movement of the secondary guide unit relative to the base carriage. This is particularly the case when the primary guide unit is coupled directly to the secondary guide unit and disposed between the secondary guide unit and the base carriage.

According to an alternative embodiment, the primary guide unit and the secondary guide unit are independently movable relative to the base carriage. In other words, the primary guide unit and the secondary guide unit can, on the one hand, use the same guide elements, at least in sections, on the one hand, which are provided in the base carriage. However, separate drive means may further be provided which allow movement of both guide units independently of each other.

According to a further embodiment of the grinding machine, a transverse guide is formed on the base carriage on which a primary carriage and a secondary carriage are accommodated, wherein a first spindle of the spindle set is associated with the primary carriage, and wherein a second spindle of the spindle set is associated with the secondary carriage. In other words, the primary guide unit can be designed as a primary slide. Accordingly, the secondary guide unit may be formed as a secondary carriage. The transverse guide can also be referred to as X-guide. In particular, the transverse guide is designed as a linear guide. The transverse guide can in particular be oriented substantially perpendicular to the longitudinal guide. The primary carriage and the secondary carriage may be associated with a common transverse guide, which is formed on the base carriage. Thus, it is not necessary to provide a separate transverse guide for each carriage.

The spindle set comprises the grinding spindle and the control spindle. Accordingly, the first spindle may be one of the two spindles and the second spindle may be the other of the two spindles.

In an alternative embodiment of the grinding machine, at least one spindle of the spindle set is received in a pivotable manner on the base carriage and can be delivered to the workpiece support by a pivoting movement about a pivot axis. Also, a pivoting movement about the longitudinal axis (Z-axis) can cause a feed movement in the transverse direction (X-direction) when the disc associated with the at least one spindle is accommodated eccentrically to the pivot axis. The pivot axis can also be referred to as C-axis. According to this embodiment, at least one of the primary guide unit and the secondary guide unit is formed as a pivot guide.

According to a further embodiment, a first spindle of the spindle set is pivotally received on the base carriage and deliverable by a pivoting movement about a pivot axis on the workpiece support, wherein a second spindle of the spindle set is slidably received along a transverse guide and deliverable to the workpiece support. In other words, a guide unit can be configured as a linear guide unit and another guide unit can be designed as a pivot guide unit.

According to a further embodiment, at least the base carriage, the primary guide unit or the secondary guide unit have an integrated travel drive. The integrated travel drive is preferably designed as a structurally integrated travel drive. This may involve, for example, a travel motor being assigned directly to the base carriage, the primary guide unit or the secondary guide unit. In other words, no complex means for power transmission are required, such as belt drives, chain drives, hydraulic drives or the like. This can lead to further simplifications in the design of the grinding machine and further reduce the required space.

An integrated travel drive can for example also be referred to as a so-called "flying" drive. On the one hand, this may mean that sufficiently flexible lines must be provided in order to supply the drives, which in principle are themselves movable relative to the machine bed, with energy. By way of example, at least one so-called cable drag may be required. Conversely, however, no complicated mechanical power transmission via gear or the like. Between stationary drives, which are fixed about the machine bed, and an object to be moved, such as the base carriage, the primary guide unit or the secondary guide unit required.

According to a development of this embodiment, at least one integrated travel drive is coupled to a threaded spindle, in particular with a rotatably received threaded spindle. Accordingly, the at least one integrated travel drive can comprise, for example, a spindle nut or a similar component which can be rotated by means of a suitable motor in order to bring about a relative movement. Accordingly, about an output rotation of a motor via the spindle nut in a longitudinal movement can be transferred.

If the corresponding positioning drive is configured as a pivoting drive, the integrated drive can be, for example, a so-called high-torque drive (High Torque Motor).

According to a further alternative embodiment, at least one integrated travel drive is designed as a direct drive. Direct drives are conceivable for both quarter-turn actuators and linear drives. If a linear drive is assumed, the direct drive can in particular comprise a linear motor. For example, it is conceivable to provide both for the primary carriage and for the secondary carriage in each case a linear motor, which can be coupled to the same stator, which may be formed approximately on the base carriage.

It will be appreciated that in a linear motor, a stator is typically a linearly extending element which cooperates with a "rotor". In simple terms, a linear motor can be regarded as the "development" of a motor with a rotary output.

According to a further embodiment of the grinding machine, the workpiece support is fixed to the machine bed. This has the significant advantage that the workpiece support can be realized with little structural effort. It is not necessary to provide the workpiece support with suitable feed drives and / or feed drives. Required feed movements and / or feed movements can be brought about by a suitable interaction of the base carriage with the primary guide unit and the secondary guide unit.

According to a further embodiment of the grinding machine, at least one dressing unit is provided for receiving a dressing tool, wherein the at least one dressing unit is designed for machining at least the grinding wheel or the regulating wheel, and wherein the at least one dressing unit is fixed to the machine bed.

Preferably, the grinding machine is provided with a machine control capable of at least engaging the grinding wheel or the regulating wheel in a controlled manner with the respectively associated dressing tool in order to machine an outer contour, in particular a peripheral contour, of the respective pane. In this way, non-cylindrical rotationally symmetrical workpieces can be machined without requiring separate pivoting drives (B-axis drives) for pivoting the grinding spindle and / or the control spindle about the Y-axis. Furthermore, the required control technology and / or control technology for such a B-axis can be saved.

According to a development of this embodiment, the at least one dressing unit of the workpiece support is arranged adjacent. This has the significant advantage that the dressing tool provided on the at least one dressing unit is easily accessible. In this way, even if only a limited process space is provided, which is usually associated with compact outer dimensions of the grinding machine, a comprehensive functionality can be provided. The process space of the grinding machine can be defined, for example, by maximum dimensions of workpieces to be machined and / or of recordable grinding wheels or regulating wheels.

According to a preferred embodiment, a grinding machine, in particular a compact designed centerless grinding machine, exactly one base slide, which is received on the machine bed and designed to realize a common feed movement of the grinding wheel and the regulating wheel, exactly one primary guide unit and exactly one secondary guide unit, the base carriage The primary guide unit is coupled to realize a feed movement with a first spindle of the spindle set and the secondary guide unit for realizing a feed movement with a second spindle of the spindle set, wherein the base carriage, the primary guide unit and the Secondary guide unit are configured to move the first spindle and the second spindle with respect to the workpiece support and at least one dressing unit, wherein exactly three axes of movement are provided, wherein the machine bed and the base carriage along the longitudinal guide define the first axis of movement, wherein the primary Guide unit defines the second movement axis, and wherein the secondary guide unit defines the third axis of movement.

The named embodiment may in particular be the subject of an independent invention.

If, in the context of this disclosure, it is said that "exactly" a number of elements are provided, it should be understood in particular that no more than the stated number of elements is installed. When referring to "just one element", it is to be understood that "a single" such element is intended.

A grinding machine designed according to at least some basic principles of this disclosure may be modified in various ways to form suitable variants.

With regard to conceivable axis concepts for the axes of motion used, it is essential that three axes of motion are used. The movement axis formed between the machine bed and the base carriage is designed in particular as a so-called Z-axis. A relative movement between the grinding spindle and the base slide or between the control spindle and the base slide can be accomplished via the primary guide unit and via the secondary guide unit. According to a variant, the primary guide unit is designed as an X-axis, wherein the secondary guide unit is designed as a so-called. X-axis. Starting from this variant, it is conceivable, on the one hand, that the primary guide unit and the secondary guide unit use at least sections of the same guide elements. However, it is also conceivable that the X-axes defined by the primary guide unit and the secondary guide unit are spaced apart from each other and oriented parallel to one another.

According to a further embodiment, at least one of the primary guide unit and the secondary guide unit instead of a linear guide or linear axis as Pivoting guide or pivot axis be configured, in particular as a so-called. C-axis, which allows a pivoting movement or rotational movement about the Z-axis.

If both the primary guide unit and the secondary guide unit each define an X-axis, it is conceivable on the one hand that the X-axes are symmetrical. However, it is also conceivable asymmetric design of the X-axis.

The at least one dressing unit is preferably fixedly coupled to the machine bed, that is not movable relative to the machine bed. The at least one dressing unit can be arranged in spatial proximity to the workpiece support. However, it is also conceivable that the at least one dressing unit is arranged at a distance from the workpiece support on the machine bed.

The at least one dressing unit can be arranged on the one hand directly on the machine bed. However, it is also conceivable to provide the at least one dresser on a bridge (portal) or a support arm, which is fixedly coupled to the machine bed. In the same way, the arrangement of the workpiece support can be varied.

Also with regard to the at least one traversing drive different variants are conceivable. Preferably, at least one of the travel drives of the base carriage, the primary guide unit and the secondary guide unit is designed as a linear drive which comprises at least one threaded spindle and a nut which can be coupled thereto. Either the threaded spindle or the nut can be added rotatably. The respective other element of the threaded spindle and the nut can be rotatably driven to effect a linear movement.

In particular, when the primary guide unit is designed as a primary slide and the secondary guide unit as a secondary slide, two slides can be assigned to both slides that use a common threaded spindle. Each of the travel drives of the primary carriage and the secondary carriage can accordingly a rotatable nut to move the primary carriage or the secondary carriage along the threaded spindle.

Designs are also conceivable in which motors of the respective travel drives are not received directly on the element to be moved, that is to say on the base carriage, on the primary carriage and / or on the secondary carriage. Accordingly, the motor may be "fixed" from the point of view of the element to be traversed and, for example, rotatably drive a threaded spindle which cooperates with a nut which is fixedly coupled to the respective carriage in order to bring about the movement of movement. As already described above, at least one linear motor can be provided instead of at least one threaded spindle drive.

Both the at least one traversing drive for the X-axis or the X-axes and the traversing drive for the Z-axis can basically be realized as a threaded spindle drive, linear motor or in a similar manner. If a threaded spindle drive is provided, it is on the one hand conceivable to drive the threaded spindle itself. On the other hand, it is conceivable to drive a mother, which is coupled to the threaded spindle, in which case the threaded spindle is then received rotatably.

All of the aforementioned variants can in principle be combined with one another. If a grinding machine according to the aspects and variants of this embodiment is realized, can be realized with limited space and manageable effort a machine that has a wide range of applications and despite the compact simple design allows many applications.

Such a compact designed grinding machine is suitable for example for small series production and / or medium batch production. It is understood that, for example, in mass production usually single-purpose machines or specially adapted multi-purpose machines are used, which usually require significantly larger installation spaces and footprints.

It is understood that the features of the invention mentioned above and those yet to be explained below can be used not only in the particular combination indicated, but also in other combinations or in isolation, without departing from the scope of the present invention.

Fig. 1

eine schematische frontale Ansicht einer Schleifmaschine, die als spitzenlose Schleifmaschine ausgestaltet ist;

Fig. 2

eine stark vereinfachte schematische Teilansicht einer spitzenlosen Schleifmaschine in Draufsicht;

Fig. 3

eine stark vereinfachte schematische Draufsicht einer Ausgestaltung einer spitzenlosen Schleifmaschine mit drei Bewegungsachsen in einer ersten Konfiguration;

Fig. 4

einen stark vereinfachten schematischen Schnitt durch eine Schleifmaschine, die der Gestaltung gemäß Fig. 3 zumindest ähnlich gestaltet, ist entlang der Linie IV-IV in Fig. 3;

Fig. 5

eine weitere stark vereinfachte schematische Draufsicht der Schleifmaschine gemäß Fig. 3 in einem von der Ansicht gemäß Fig. 3 abweichenden Zustand;

Fig. 6

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine in einem ersten Zustand;

Fig. 7

eine weitere stark vereinfachte schematische Ansicht der Schleifmaschine gemäß Fig. 6 in einem weiteren Zustand;

Fig. 8

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 9

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 10

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 11

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 12

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 13

eine stark vereinfachte schematische Draufsicht einer weiteren Ausgestaltung einer spitzenlosen Schleifmaschine;

Fig. 14

einen stark vereinfachten seitlichen Schnitt durch eine weitere Ausgestaltung einer spitzenlosen Schleifmaschine; und

Fig. 15

einen stark vereinfachten seitlichen Schnitt durch noch eine weitere Ausgestaltung einer spitzenlosen Schleifmaschine.

Further features and advantages of the invention will become apparent from the following description of several preferred embodiments with reference to the drawings. Show it:

Fig. 1

a schematic frontal view of a grinding machine, which is designed as a centerless grinding machine;

Fig. 2

a highly simplified schematic partial view of a centerless grinding machine in plan view;

Fig. 3

a highly simplified schematic plan view of an embodiment of a centerless grinding machine with three axes of movement in a first configuration;

Fig. 4

a highly simplified schematic section through a grinding machine, the design according to Fig. 3 at least similar, is along the line IV-IV in Fig. 3 ;

Fig. 5

a further simplified schematic plan view of the grinding machine according to Fig. 3 in one of view Fig. 3 deviant state;

Fig. 6

a highly simplified schematic plan view of another embodiment of a centerless grinding machine in a first state;

Fig. 7

a further simplified schematic view of the grinding machine according to Fig. 6 in another condition;

Fig. 8

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 9

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 10

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 11

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 12

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 13

a highly simplified schematic plan view of another embodiment of a centerless grinding machine;

Fig. 14

a greatly simplified lateral section through a further embodiment of a centerless grinding machine; and

Fig. 15

a greatly simplified lateral section through yet another embodiment of a centerless grinding machine.

Fig. 1 FIG. 10 illustrates a frontal view of a grinding machine, designated 10. Regarding Fig. 1 as well as with additional reference to Fig. 2 , which shows a schematic highly simplified partial view of a grinding machine 10 in plan view, the basic structure and essential components of the grinding machine 10 are described below.

The grinding machine 10 may in particular be designed as a so-called centerless grinding machine 10. Exemplary are the basis of the Fig. 1 and 2 Formed grinding machines designed as centerless external cylindrical grinding machines. The grinding machine 10 has a machine bed 12, which can also be referred to as a frame. On the machine bed 12 slide guides 14, 16 may be added, which allow traversing movements of components of the grinding machine 10.

In the Fig. 1 and 2 is in synopsis, a coordinate system XYZ removable, which is used to denote main directions or main axes of the grinding machine 10. Z is regularly referred to as an axis which coincides approximately with a longitudinal axis of a workpiece received on the machine tool 10 or is oriented at least parallel thereto. The axis Z is further oriented parallel to at least one spindle axis of the grinding machine 10. With X, an axis is regularly referred to, which can also serve as a delivery axis. Usually, the axis X is oriented perpendicular to the axis Z. The axis X is generally referred to as working axis. An axis Y generally indicates a vertical extent. The axis Y is usually oriented perpendicular to the axis X and perpendicular to the axis Z.

The slide guides 14, 16 may be designed as translational guides and in particular allow feed movements along the X axis. However, the carriage guides 14, 16 may also be designed as cross slide guides. Accordingly, the slide guides 14, 16 may also allow movement along the Z axis in addition to movement along the X axis. The Z-axis can also be called a feed axis. Conceivable directions of movement, which are made possible by the slide guide 14, 16 are in Fig. 2 indicated by 18, 20 indicated arrows.

The grinding machine 10 may further include a wheelhead 24 and a control wheel spindle 26. On grinding wheel head 24, a grinding spindle 28 may be rotatably received. At the regulating wheel spindle 26, a control spindle 30 may be rotatably received. The grinding spindle 28 may be designed to receive at least one grinding wheel 32. The control spindle 30 may be designed to receive at least one regulating wheel 34. The grinding headstock 24 may be further provided with a grinding wheel drive 36, but at least be coupled to a corresponding grinding wheel drive 36. The regulating wheel spindle 26 may be provided with a regulating wheel drive 38, but at least be coupled to a regulating wheel drive 38. The carriage guide 14 is assigned to the wheel spindle 24. The carriage guide 16 is assigned to the regulating wheel spindle 26. The slide guides 14, 16 may be coupled to suitable drives to enable translational movements of the wheelhead 24 and the regulating wheel spindle 26 in an XZ plane, for example, compare arrows 18, 20 in FIG Fig. 2 ,

The grinding wheel drive 36 may comprise at least one motor, in particular an electric motor. The regulating wheel drive 38 may comprise at least one motor, in particular an electric motor. The grinding wheel drive 36 may be coupled directly or indirectly with the grinding spindle 28. Indirect coupling can take place via a gear, a clutch or the like. The regulating wheel drive 38 may be coupled directly or indirectly to the control spindle 30. An indirect coupling can be done via a gearbox, a clutch or similar zwischenschaltbare elements.

The grinding spindle 28 may have at least one bearing 40, preferably two bearing points 40-1, 40-2, between which the grinding wheel 32 is arranged, cf. Fig. 2 , The control spindle 30 may have at least one bearing 42, preferably a first bearing 42-1 and a second bearing 42-2. Between the bearings 42-1, 42-2, the at least one regulating wheel 34 may be arranged, in particular also compare Fig. 2 ,

Between the grinding spindle 28 and the control spindle 30, a workpiece support 46 is arranged, which is received on a workpiece support holder 48. The workpiece support 46 is designed to receive or support a workpiece 50 which can be received between the grinding spindle 28 and the control spindle 30 for grinding. The workpiece support 46 may also be referred to as a support ruler.

The grinding spindle 28 with the grinding wheel 42 received thereon is rotatable or rotationally drivable about a longitudinal axis. The control spindle 30 with the regulating wheel 34 received thereon is rotatable or rotationally drivable about a longitudinal axis. The grinding spindle 28 and the control spindle 30 can cooperate in such a way that the workpiece 50 received between them can be displaced by the grinding wheel 32 and the regulating wheel 34 in rotation about its longitudinal axis. In other words, the workpiece 50 can be driven indirectly via the grinding wheel 32 and the regulating wheel 34. Like a synopsis of Fig. 1 and 2 can be removed, the longitudinal axes can be arranged in a common XZ plane. In particular, the longitudinal axes can be aligned parallel to one another. However, as already mentioned above, it is also conceivable that at least the control spindle 30 or its longitudinal axis is slightly inclined relative to the longitudinal axis of the grinding spindle 28 or pivoted about the transverse axis. Such an inclination can cause a feed of the workpiece 50. This may be particularly advantageous for so-called Durchgangsschleifvorgänge. It can namely be effected in this way a workpiece feed. It is understood that a feed of the workpiece 50 can be accomplished in other ways. In general, the grinding machine 10 can also be designed to carry out recess grinding processes.

Based on the representation according to Fig. 1 Furthermore, it can be seen that the grinding wheel 32 and the regulating wheel 34 are basically rotatably drivable with a same direction of rotation. Usually, a rotary drive of the grinding wheel 32 and the regulating wheel 34 takes place in such a way that different peripheral speeds result therefrom. A resulting circumferential speed difference may cause slippage of the workpiece 50 by the grinding wheel 32 and the regulating wheel 34. In principle, the workpiece 50 is rotated by the grinding wheel 32 and the regulating wheel 34, the direction of rotation of which is opposite to the direction of rotation of the grinding wheel 32 and the regulating wheel 34. Due to the different peripheral speeds of the grinding wheel 32 and the regulating wheel 34, however, there is no "ideal" slip-free entrainment. Rather, between the workpieces 50 and the grinding wheel 32, a relative movement, in particular a sliding relative movement, can result. This relative movement ensures the material removal on the workpiece 50.

By suitable control of slide drives (in the Fig. 1 and 2 not separately shown) of at least the grinding headstock 24 or the regulating wheel spindle 26, further, a feed force in the X direction on the workpiece 50 can be defined and generated. In other words, the workpiece 50 is clamped between the grinding wheel 32 and the regulating wheel 34, in particular clamped with a bias voltage.

By way of example, the grinding machine 10 may further comprise a supply 44 for a cooling lubricant (KSS supply). Furthermore, a dressing device 66 for dressing the grinding wheel 32 can in particular be assigned to the wheelhead 24. The grinding machine 10 may be provided with a controller 52 through which an operator can operate and operate the grinding machine 10. It is understood that the control device 52 can also be designed for automated control of the grinding machine 10.

The following are based on the Fig. 3 to 15 Various embodiments of grinding machines 10 configured in accordance with at least some principles of the present disclosure are illustrated. Preferably, it is the grinding machines 10 each centerless grinding machines. The grinding machines 10 are also characterized by their extremely compact design, which is favored by the respective machine concept.

Insofar as elements, components and / or assemblies are provided with the same reference numerals in the context of this disclosure, it should be assumed that these - in any case with regard to the concepts illustrated here - are of the same nature. It is understood, however, that constructive modifications of the elements, components and / or assemblies are conceivable. However, this is usually explained separately.

According to the basis of the Fig. 3 to 15 illustrated embodiments, both the grinding wheel 32 and the regulating wheel 34 may be cantilevered. It is understood that in principle, a design according to Fig. 2 is conceivable, wherein at least the grinding wheel 32 or the regulating wheel 34 is received between two bearing points 40, 42.

With particular reference to the Fig. 3 to 5 a first embodiment of a grinding machine 10 is illustrated and described in more detail. The Fig. 3 and 5 each show schematically greatly simplified plan views of the grinding machine 10, wherein movable components of the grinding machine 10 in the Fig. 3 and 5 occupy different relative positions. Fig. 4 shows a side section through the grinding machine 10 along the line IV-IV. Also the representation according to Fig. 4 is very simplified and schematic in nature. This requires in particular that Fig. 4 no completely correct cut playback of the according to the Fig. 3 and 5 illustrated embodiment of the grinding machine 10 must be. Nevertheless illustrated Fig. 4 a conceivable section through the grinding machine 10th

In Fig. 5 Furthermore, for reasons of illustration, a coordinate system is shown, wherein in the plane of view of the Fig. 5 an x-axis and a z-axis are visible. A corresponding Y-axis (vertical axis) extends substantially perpendicular to the plane of view of Fig. 5 , see. Fig. 4 , In particular, the X-axis can also be referred to as a transverse axis and describe a transverse direction. In particular, the Z-axis can Also referred to as a longitudinal axis and describe a longitudinal direction. Furthermore, in Fig. 5 indicated by a designated C arrow, a so-called. Pivot axis, which can also be referred to as C-axis. The C-axis indicates rotational movements and / or pivoting movements about the Z-axis. Similarly, rotational or pivotal movements about the X-axis may be referred to as A-axis and rotational or pivotal movements about the Y-axis as B-axis, cf. this also in Fig. 1 shown coordinate system. That in the Fig. 4 and 5 Coordinate system shown can be applied to all of the designs according to the Fig. 3 as well as 6 to 15 are transmitted.

Referring again to the Fig. 3, 4 and 5 the basic structure of the design of the grinding machine 10 is explained in more detail. In basically already described manner, the grinding machine 10 is provided with a wheelhead 24 and a control headstock 26. The wheelhead 24 carries a grinding spindle 28, on which a grinding wheel 32 can be received. The control headstock 26 carries a control spindle 30 to which a regulating wheel 34 can be received. Together, the grinding wheel 32 and the regulating wheel 34 can act on a workpiece 50 to be machined, which is received on a workpiece support 46.

To act on the workpiece 50, it is necessary, the grinding spindle 28 and the control spindle 30 controlled and defined deliver to the workpiece 50 and to move in a feed movement relative to the workpiece support 46.

For this purpose, the grinding machine 10 has a carriage arrangement, in particular a cross slide arrangement, which comprises a plurality of carriages 54, 56, 58. On the machine bed 12 of the grinding machine 10, a base carriage 54 is received, which in turn carries a primary carriage 56 and a secondary carriage 58. The base carriage 54 cooperates with the machine bed 12 to define a first movement axis 60 in this manner. The first movement axis 60 may, in particular, be a so-called longitudinal axis (Z movement axis). Further, the base carriage 54 may cooperate with the primary carriage 56 to define another axis of motion. By way of example, this may be the third movement axis 64. The third movement axis 64 can also be referred to as a so-called. Transverse axis (X-axis motion). Finally, the base carriage 54 may be approximately with the secondary carriage 58 cooperate to define a second axis of motion 62. The second movement axis 62 may also be referred to as a transverse axis (X-movement axis). For further distinguishability, it is conceivable to designate the second movement axis 62 as the X1 axis and the third movement axis 64 as the X2 movement axis.

According to the basis of the Fig. 3 and the Fig. 5 illustrated embodiment, for example, the control spindle 30 is added to the primary carriage 56. Furthermore, by way of example, the grinding spindle 28 is received on the secondary carriage 58. It is understood that the assignment can in principle be made in the reverse manner. If in the context of this embodiment of primary elements, secondary elements and first, second, third elements and the like. Is mentioned, this should primarily serve only the distinctness and in particular no qualitative emphasis characterize. The movement axes 60, 62, 64 are in Fig. 5 illustrated by appropriate block arrows. It is understood that in at least some embodiments, the second movement axis 62 and the third movement axis 64 may be oriented parallel to each other. Furthermore, the first movement axis 60 is oriented at least in some embodiments perpendicular to the second movement axis 62 and / or to the third movement axis 64.

Between the machine bed 12 and the base carriage 54, a longitudinal guide or longitudinal guide unit 68 is formed, which comprises at least one longitudinal guide element 70. The at least one longitudinal guide element 70 may be, for example, a guide rail or the like. In particular, the longitudinal guide element 70 may be fixed to the machine bed 12. In a corresponding manner, a counter contour can be provided in the primary carriage 56, for example a rider or the like, in order to be able to move the primary carriage 56 along the guide element 70 in the Z direction.

For realizing the second movement axis 62 or the third movement axis 64, a primary guide unit 72 and / or a secondary guide unit 74 can also be formed. In particular, the guide units 72, 74 may be a transverse guide unit 76. The transverse guide unit 76 can comprise at least one guide element 78, which is designed, for example, as a guide rail fixed to the base slide 54. The primary guide unit 72 may be the base carriage 54 and be interposed between the primary carriage 56. The secondary guide unit 74 may be interposed between the base carriage 54 and the secondary carriage 58. Accordingly, sliding contours and / or riders may be formed on both the primary carriage 56 and the secondary carriage 58 to ensure movement of the primary carriage 56 and the secondary carriage 58 in the X direction relative to the base carriage 54.

Accordingly, both the base carriage 54, the primary carriage 56 and the secondary carriage 58 may be designed to be movable. For this purpose, the grinding machine 10 may have a first travel drive 82, a second travel drive 84 and a third travel drive 86. The travel drives 82, 84, 86 are preferably integrated travel drives. This may include in particular that corresponding motors 88, 90, 92 of the travel drives 82, 84, 86 are fixedly assigned to a carriage 54, 56, 58 to be moved. In other words, according to at least some embodiments, it may be preferable if one or all of the motors 88, 90, 92 are not received on the machine bed 12 in a frame-fixed manner. In this way, complex equipment for power transmission can be avoided.

The first traversing drive 82 is associated with the base carriage 54 and provided with the first motor 88. The second traversing drive 84 is associated with the primary carriage 56 and provided with the second motor. The third travel drive 86 is associated with the secondary carriage 58 and provided with the third motor 92. According to a preferred embodiment, at least one of the travel drives 82, 84, 86 has a screw spindle or a screw spindle gear 94, 96, 98. By way of example, the first travel drive 82 can be coupled to a first screw spindle 94. This may be about a screw spindle 94, which is fixed to the machine bed 12. Accordingly, the first motor 88 of the first travel drive 82 may act on, for example, a spindle nut to rotate it to move the base carriage 54 in a controlled manner in the Z direction.

According to at least some embodiments, it is preferred if the second travel drive 84 and the third travel drive 86 are coupled to a common screw spindle 96. The screw spindle 96 can in particular on the base carriage 54th be set. Accordingly, the second motor 90 may act on a nut to move the primary carriage 56 in the X direction. Likewise, the third motor 92 may act on a nut to move the secondary carriage 58 in the X direction. Even if the second travel drive 84 and the third travel drive 86 use the same second screw spindle 96, the primary carriage 56 and the secondary carriage 58 can be moved relative to each other. Since the primary carriage 56 and the secondary carriage 58 at least partially share the same transverse guide unit 76 and at least partially the same threaded spindle or screw spindle 96, significant structural simplifications may result.

Overall, both the grinding spindle 28 and the control spindle 30 can be moved in a plane defined by the Z-axis and the X-axis. A movement in the Z-direction is carried out for the grinding spindle 28 and the control spindle 30 as a rule synchronously, since both are received on the base carriage 54.

In various embodiments of the present disclosure, it is just preferred that the grinding machine 10 have no B-axis for the grinding spindle 28 and / or the control spindle 30. As a rule, a B-axis is a pivot axis, the pivoting movements about the Y-axis (cf. Fig. 4 ) allowed. Such axes can be realized only with relatively high construction costs. This increases on the one hand the space requirement and on the other hand the costs.

According to the present disclosure, it is proposed to make the grinding machine 10 otherwise capable of processing non-cylindrical rotationally symmetric workpieces. This can be done in particular if at least the grinding wheel 32 or the regulating wheel 34 are adapted to the contour of the workpiece 50 to be machined. This can preferably take place via at least one dressing unit 102, 104. The dressing unit 102 may be associated with the grinding spindle 28. The dressing unit 104 may be associated with the control spindle 30. In the dressing unit 102, a dressing tool 106 is provided which is adapted to cooperate with the grinding wheel 32. In the dressing unit 104, a dressing tool 108 is provided, which is designed to cooperate with the regulating wheel 34.

By way of example, the dressing unit 102 may comprise an integrated tool spindle and a corresponding drive for driving an approximately disk-like dressing tool 106 in order to machine the grinding wheel 32. By way of example, the dressing unit 104 may comprise a fixed dressing tool 108 which is approximately similar to a turning tool. It is understood that, in principle, modified embodiments of the dressing units 102, 104 are also conceivable. The dressing units 102, 104 are preferably coupled to the machine bed 12 in a frame-fixed manner. This can be done, for example, via a carrier 112, cf. especially Fig. 4 ,

The carrier 112 may be rigidly coupled to the machine bed 12. The carrier 112 may in particular be designed to carry the workpiece support 46 for receiving the workpiece 50 and at least the first dressing unit 102 or the second dressing unit 104. In particular, at least one of the dressing units 102, 104 may be arranged adjacent to the workpiece support 46. It is understood that embodiments are also conceivable in which at least one of the dressing units 102, 104 is received at a significant distance from the workpiece support 46 on the machine bed 12. In Fig. 4 Furthermore, schematically indicated is a cover which may comprise frame-fixed parts 114 and movable parts 116. The cover 114, 116 may be by way of example telescopic plates, bellows and similar covers.

A relative movement between the grinding wheel 32 and the first dressing unit 102 and between the regulating wheel 34 and the second dressing unit 104 can be effected by the travel drives 82, 84, 86 of the grinding machine 10. Thus, it is preferred if the dressing units 102, 104 do not comprise separate travel drives. This can lead to further structural simplifications. In other words, the ability of the grinding spindle 28 and the control spindle 30 to be traversed in a plane spanned by the axes Z and X can also be used to define the grinding wheel 32 and the regulating wheel 34, respectively, in cooperation with the dressing units 102, 104 to edit to allow the machining of non-rotationally symmetrical workpieces 50. This may be at least partially conical, stepped and / or spherical workpieces 50. Furthermore, the processing of punctures, paragraphs and / or similar design elements provided with workpieces 50 is conceivable.

Fig. 4 illustrates in a greatly simplified form based on a sectional view of a "layer structure" of the grinding machine 10. In principle, already described above, the base carriage 54 can be taken longitudinally movable on the machine bed 12 (see., By a double arrow in Fig. 4 indicated first movement axis 60). The primary carriage 56 and the secondary carriage 58 can be accommodated on the base carriage 54 in the manner already described above. The sectional view according to Fig. 4 further shows that, for example, the wheelhead 24 may be received on the secondary carriage 58. The grinding headstock 24 carries the grinding spindle 28 with the grinding wheel 32. The grinding spindle 32 can be brought into engagement with the workpiece 50, which is receivable on the workpiece support 46. The workpiece support 46 can be received in a stationary manner together with at least one dressing unit 102 on a support 112 fixed to the frame.

Fig. 5 shows a grinding machine 10, which basically with the grinding machine 10 according to Fig. 3 corresponds. In Fig. 5 However, the base carriage 54, the primary carriage 56 and the secondary carriage 58 are moved such that the grinding wheel 32 and the regulating wheel 34 can come into engagement with these associated dressing units 102, 104. It is understood that such dressing operations do not necessarily have to be made simultaneously for the grinding wheel 32 and the regulating wheel 34. In Fig. 5 Furthermore, a conceivable stepped contour of the grinding wheel 32 is indicated by dashed lines. Accordingly, stepped portions, conical portions and / or curved portions may be formed on the grinding wheel 32 to image a desired geometry of the workpiece 50 to be machined. Also, the regulating wheel 34 can be dressed in a similar manner, although it is not absolutely necessary for the regulating wheel 34 to exactly replicate the desired geometry of the workpiece 50. Such non-cylindrical or stepped rotationally symmetrical contours can be generated with the dressing units 102, 104.

Fig. 5 further illustrates a conceivable access direction 118 from which the grinding machine 10 may be accessible to an operator. Usually, the grinding machine 10 at its access direction 118 side facing at least one door, a gate, flaps, hoods or similar elements that allow a defined access.

The primary carriage 56 and the secondary carriage 58 can mesh at least in sections, in order to enable a further reduction of the required installation space. Exemplary shows Fig. 5 in that the primary carriage 56 has a plurality of guide sections 122, for example a total of four guide sections 120, of which two are each assigned to a guide element 78 and formed on opposite ends of the primary carriage 56. Accordingly, a recess 120 can be formed between two guide sections 122 spaced apart, which exposes at least a portion of the transverse guide unit 76 or of a corresponding guide element 78. Accordingly, the secondary carriage 58 may have corresponding guide sections 124, which cooperate in the region of the recess 120 with the at least one guide element 78. In other words, the primary carriage 56 and the secondary carriage 58 may be "entangled".

Based on 6 and 7 A modified embodiment of a grinding machine 10 is illustrated. The 6 and 7 can in principle relate to the same embodiment, wherein essential components of the grinding machine 10, in particular a base carriage 54, a primary carriage 56 and / or a secondary carriage 58 in the 6 and 7 be shown in different travel positions.

The design according to the 6 and 7 essentially differs from the design according to the Fig. 3 and 5 in that, on the one hand, the workpiece support 46 is accommodated centrally on the machine bed 12 together with the first dressing unit 102 and the second dressing unit 104. This further includes that at least the base carriage 54, a cutout or recess 126 must be provided to make the workpiece support 46 and the dressing units 102, 104 accessible. In particular, the recess 126 may also extend through the primary carriage 56. Furthermore, the design differs according to the 6 and 7 from the design according to the Fig. 3 and 5 in that the recesses 120 in the region of the primary carriage 56 are designed as "closed" recesses 120, ie form a closed profile on the primary carriage 56. This can in particular further increase the rigidity and guidance accuracy.

Fig. 8 illustrates another exemplary embodiment of a grinding machine 10, which at least in principle the designs according to the Fig. 3 to 7 is largely similar. The workpiece support 46 and the dressing units 102, 104 are received or fixed in an edge region of the machine bed 12. In basically known manner, the base carriage 54, the primary carriage 56 and the secondary carriage 58 are received on the machine bed 12, wherein the secondary spindle 58, the grinding spindle 28 and the primary carriage 56, the control spindle 30 is added. The primary carriage 56 is provided with a travel drive 84. The secondary carriage 58 is provided with a travel drive 86. The travel drives 84, 86 share a common screw spindle or threaded spindle 96. At least some of the guide sections 124 of the secondary carriage 58 are arranged in recesses 120 which are formed in the primary carriage 56.

Fig. 9 FIG. 2 illustrates another exemplary embodiment of a grinding machine 10, which basically has the design according to FIG Fig. 8 is similar. The grinding machine 10 off Fig. 9 However, this essentially differs from the design according to Fig. 8 in that the primary carriage 56 and the secondary carriage are not "entangled" with each other or do not engage with each other and / or engage over one another in order to cooperate with the transverse guide unit 76. In other words, the primary carriage 56 and the secondary carriage 58 are received at a distance from each other at the transverse guide unit 76. However, the travel drives 84, 86 of the primary carriage 56 and the secondary carriage 58 may share a common lead screw or lead screw 76 to independently move the primary carriage 56 and the secondary carriage 58 in the transverse direction (X direction).

Fig. 10 illustrates a further alternative embodiment of a grinding machine 10. In a known manner, the grinding machine 10, a machine bed 12 on which a base carriage 54, a primary carriage 56 and a secondary carriage 58 are added. Furthermore, a longitudinal guide unit 68 and a transverse guide unit 76 are provided in a known manner. The design according to the Fig. 10 differs approximately from the designs according to the Fig. 3 to 9 essentially in that the motors 88, 90, 92 of the travel drives 82, 84, 86, which are coupled to the base carriage 54, the primary carriage 56 and the secondary carriage 58, each not in the zu moving component are integrated. In other words, about the motor 88 of the first traversing drive 82 is fixed to the machine bed 12. The motor 90 of the second travel drive 84 is fixed to the base carriage 54. Likewise, the motor 92 of the third travel drive 86 is fixed to the base carriage 54. By way of example, the motors 88, 90, 92 may each be coupled with screw spindles or threaded spindles 94, 96, 98 in order to move the base slide 54, the primary slide 56 and the secondary slide 58 in the desired manner. The basis of the Fig. 10 illustrated embodiment accordingly shows a variant of the grinding machine 10, in which the second traversing drive 84, which cooperates with the primary carriage 56, and the third traversing drive 86, which cooperates with the secondary carriage 58, each with its own screw spindle 96, 98 are coupled.

Another exemplary embodiment of a grinding machine 10 is based on Fig. 11 illustrated. The design of the grinding machine 10 according to Fig. 11 is fundamentally at least similar to the embodiments already described above. However, a modification results with regard to the detailed design of the travel drives 82, 84 and 86. At least one of the travel drives 82, 84, 86 can in fact be configured as a so-called linear motor 130, 132, 134 or such a linear motor 130, 132, 134 exhibit. A linear motor is usually a gearless motor designed to directly generate linear motion. In other words, a linear motor can be understood as a "development" of a (rotationally effective) electric motor. By way of example, the travel drive 82 assigned to the base carriage 54 may comprise a first linear motor 130, which cooperates with a first stator 136. The stator 136 may basically extend parallel to the longitudinal guide unit 68. It would also be conceivable, according to a further alternative embodiment, to combine the stator 136 and the longitudinal guide unit 68 with one another.

The second carriage drive 84 assigned to the primary carriage 56 can, for example, have a second linear motor 132, which is coupled to a stator 138. The third carriage drive 86 assigned to the secondary carriage 58 may have a third linear motor 134, which is coupled to the second stator 138. In principle already described above, accordingly, the second linear motor and the third linear motor 134 may share the same stator 138. The second stator 138 can basically extend parallel to the transverse guide unit 76. According to further alternative embodiments, the transverse guide unit 76 and the second stator 138 may be coupled together or integrated with each other.

In the case of the Fig. 3 to 11 illustrated embodiments of the grinding machine, the three required axes of movement 60, 62, 64 are all realized as a linear axis. However, it is also conceivable in principle to carry out at least one or two of the axes of movement 60, 62, 64 as a pivot axis, in particular as a so-called C-axis, which allows a rotational movement or pivotal movement about the longitudinal axis or Z-axis. Such embodiments are described below with reference to Fig. 12 and the Fig. 13 illustrated.

Fig. 12 1 illustrates an embodiment of a grinding machine 10, in which a base carriage 54 is provided, which is movable in the longitudinal direction by means of a longitudinal guide unit 68 in basically the manner described above. Further, a secondary carriage 58 is provided for the grinding spindle 28, which is coupled to a transverse guide unit 76 to allow a (linear) movement in the transverse direction (X direction). For this purpose, a travel drive 86 is provided which comprises a motor 92 and is coupled to a threaded spindle or screw spindle 96.

However, in order to enable a corresponding feed movement in the transverse direction or X-direction in the control spindle 30, the grinding machine 10 according to the Fig. 12 a positioning drive 84, which is designed as a pivot drive. The traversing drive 84 has a pivoting motor 152, which allows a pivoting movement about a pivot axis 148, which may be basically oriented parallel to the Z-axis, cf. approximately Fig. 5 , The control spindle 30 is accommodated eccentrically on the pivot axis 148. Accordingly, a pivoting movement about the pivot axis 148 can cause a resultant advancing movement, which in Fig. 12 is illustrated by a double arrow labeled 158. It is understood that the pivoting movement, which is caused by the pivot drive, on the one hand comprises a linear component in the transverse direction or X-direction effective. However, the pivoting movement is to be understood as a combined movement, which also differently oriented movement components includes. However, a desired feed motion can readily be realized via a corresponding machine control.

Another alternative embodiment of a grinding machine 10, based on the Fig. 13 is distinguished from the embodiments already described above primarily by the fact that neither a (linearly movable) primary carriage 56 nor a (linearly movable) secondary carriage 58 is provided. The corresponding travel drives 84, 86 are in accordance with the grinding machine 10 Fig. 13 both realized as part-turn actuators. The traversing drive 84 is basically according to the already with reference to the Fig. 12 illustrated designed as a pivot drive Verfahrantrieb 84 designed. Accordingly, the travel drive 84 has a pivot axis 148, which is coupled to a pivot motor 152. Thus, the control spindle 30 can be pivoted about the pivot axis 148 to produce a resultant feed motion 158.

In principle, the travel drive 86 for the grinding spindle 28 can likewise comprise a pivot axis 150, which is coupled to a pivoting motor 154. The swing motor 154 may be configured to pivot the grinding spindle 28 about the pivot axis 150. The grinding spindle 28 is in this case preferably arranged eccentrically to the pivot axis 150. Accordingly, a pivoting of the grinding spindle about the pivot axis 150 causes a resultant feed movement of the grinding spindle, which in Fig. 13 is illustrated by a double arrow labeled 160. In Fig. 13 Furthermore, it is shown by way of example that at least one of the dressing units 102, 104 can be accommodated on the machine bed 12 at a distance from the workpiece support. It is understood that this embodiment with regard to the arrangement of the dressing units 102, 104 can also be applied to all of the aforementioned embodiments.

The FIGS. 14 and 15 show in highly simplified schematic form of lateral cuts through various embodiments of grinding machines 10. Comparative is in this context to the Fig. 4 directed. The basis of the Fig. 14 and the Fig. 15 illustrated sections may basically be similarly positioned. Even if the basis of the Fig. 14 and the Fig. 15 illustrated sections not on the embodiment of the according to the Fig. 3 and the Fig. 5 based grinder, so is at least for orientation on the section line IV-IV in Fig. 3 to illustrate an imaginary arrangement of the respective section.

Fig. 4 1 illustrates an embodiment of the grinding machine 10 in which the workpiece support 46 and the at least one dressing unit 102, 104 are accommodated on a support arm, which is received on the side of the machine bed. Accordingly, a C-type support structure for the workpiece support 46 and the at least one dressing unit 102, 104 may result.

According to Fig. 14 a modification of the grinding machine 10 may consist in that the workpiece support 46 and / or the at least one dressing unit 102, 104 are fixed centrally on the machine bed 12 and comprise a carrier 112 which projects through a recess 126, which at least in the base carriage 54 and possibly also in the primary carriage 56, possibly even in the secondary carriage 58 is formed. Accordingly, the embodiment according to the Fig. 14 about with the basis of the 6 and 7 illustrated plan views correspond.

Fig. 15 shows a further modified embodiment of a grinding machine 10, in which the carrier is formed like a portal and fixed to the machine bed 12. At least the workpiece support 46 and / or at least one dressing unit 102, 104 can be accommodated on the gantry support 112.

It should be understood that the above-described embodiments and embodiments are to be understood as exemplifying embodiments of the basic concept of the present disclosure. Accordingly, it goes without saying that detailed aspects of an embodiment can readily be combined with detailed aspects of a further embodiment.

Claims (15)

Grinding machine (10), in particular compact designed centerless grinding machine, with a machine bed (12), a grinding spindle (28) which is coupled with a spindle drive (36) and adapted to receive a grinding wheel (32), a control spindle (30) a workpiece support (46) for receiving a workpiece to be machined (50) between the grinding spindle (28) and the control spindle (30), wherein the grinding spindle (28 ) and the control spindle (30) coupled to the machine bed (12) and are movable relative to each other, wherein the grinding spindle (28) and the control spindle (30) form a spindle set (22), wherein on the machine bed (12) has a longitudinal guide (68) is formed, on which a base carriage (54) is received, wherein the machine bed (12) and the base carriage (54) define a first movement axis (60), wherein the grinding spindle (28) with the Basisschlit coupled (54) and a second movement axis (62) is associated, wherein the control spindle (30) coupled to the base carriage (54) and a third movement axis (64) is assigned, and wherein the grinding spindle (28) and the control spindle (30 ) are movable relative to each other and on the workpiece support (46) are deliverable. A grinding machine according to claim 1, wherein a first spindle (28; 30) of the spindle set (22) is coupled to the base carriage (54) via a primary guide unit (72) defining the second movement axis (62) and a second spindle (32). 28; 30) of the spindle set (22) is coupled to the base carriage (54) via a secondary guide unit (74) defining the third movement axis (64), at least one of the primary guide unit (72) and the secondary guide unit (74). is designed as a pivoting guide or linear guide. The grinding machine of claim 2, wherein the primary guide unit (72) is coupled directly to the base carriage (54), and wherein the secondary guide unit (74) is coupled directly to the base carriage (54) or directly to the primary guide unit (72). A grinding machine according to claim 2 or 3, wherein movement of the primary guide unit (72) relative to the base carriage (54) causes corresponding movement of the secondary guide unit (74) relative to the base carriage (54). A grinding machine according to claim 2 or 3, wherein the primary guide unit (72) and the secondary guide unit (74) are independently movable relative to the base carriage (54). A grinding machine according to any one of the preceding claims, wherein a transverse guide (76) is formed on the base carriage (54) and receives a primary carriage (56) and a secondary carriage (58), a first spindle (28; 30) of the spindle set (22 ) is associated with the primary carriage (56), and wherein a second spindle (28; 30) of the spindle set (22) is associated with the secondary carriage (58). Grinding machine according to one of claims 1 to 5, wherein at least one spindle (28; 30) of the spindle set (22) is pivotally received on the base carriage (54) and by a pivoting movement about a pivot axis (148; 150) on the workpiece support (46) deliverable is. Grinding machine according to one of claims 1 to 5, wherein a first spindle (28; 30) of the spindle set (22) is pivotally received on the base carriage (54) and by a pivoting movement about a pivot axis (148; 150) on the workpiece support (46) can be fed , and wherein a second spindle (28; 30) of the spindle set (22) is slidably received along a transverse guide (76) and can be fed to the workpiece support (46). Grinding machine according to one of claims 1 to 8, wherein at least the base carriage (54), the primary guide unit (72) or the secondary guide unit (74) has an integrated travel drive (82, 84, 86), in particular a structurally integrated travel drive. Grinding machine according to claim 9, wherein at least one integrated travel drive (82, 84, 86) with a threaded spindle (94, 96, 98) is coupled, in particular a rotatably received threaded spindle. Grinding machine according to claim 9, wherein at least one integrated travel drive (82, 84, 86) is designed as a direct drive (130, 132, 134), in particular as a linear motor, wherein preferably a plurality of linear motors are provided, which are coupled to the same stator (138) , Grinding machine according to one of claims 1 to 11, wherein the workpiece support (46) on the machine bed (12) is fixed. Grinding machine according to one of claims 1 to 12, wherein at least one dressing unit (102, 104) for receiving a dressing tool (106, 108) is provided, wherein the at least one dressing unit (102, 104) for processing at least the grinding wheel (32) or the Regulating wheel (34) is formed, and wherein the at least one dressing unit (102, 104) on the machine bed (12) is fixed. The grinding machine of claim 13, wherein the at least one dressing unit (102, 104) is disposed adjacent the workpiece support (46). Grinding machine (10) according to one of claims 1 to 14, comprising exactly one base slide (54) which is received on the machine bed (12) and designed to realize a common feed movement of the grinding wheel (32) and the regulating wheel (34), exactly one primary guide unit (72) and exactly one secondary guide unit (74), which are received on the base carriage (54) and preferably at least partially equal guide elements (78), wherein the primary guide unit (72) for realizing a feed movement with a first spindle (28 30) of the spindle set (22) and the secondary guide unit (74) for realizing a feed movement with a second spindle (28; 30) of the spindle set (22) is coupled, wherein the base carriage (54), the primary guide unit (72) and the secondary guide unit (74) are configured to support the first spindle (28; 30) and the second spindle (28; 30) with respect to the workpiece support (46) and at least one dressing unit (102, 104), wherein exactly three movement axes (60, 62, 64) are provided, wherein the machine bed (12) and the base carriage (54) along the longitudinal guide (68) define the first movement axis (60), wherein the primary guide unit (72) defines the second movement axis (62), and wherein the secondary guide unit (74) defines the third movement axis (64).

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