Linear guide

Abstract

The invention relates to a linear guide having a profile body extending along a movement axis and a slide which is mounted on the profile body so as to be linearly movable along the movement axis and which has a rolling bearing unit which bears against a guide track by means of at least one rolling body, the guide track has two guide rails which are arranged in a row along the movement axis and which are accommodated in a form-fitting manner on the profile body in a spatial direction which is oriented transversely to the movement axis, the end faces of the two guide rails which lie opposite each other delimit a docking region, and wherein the end faces of the two guide rails which lie opposite each other delimit the docking region. A material-fitting region is formed between the respective guide rail and the profiled body adjacent to each abutment region, said material-fitting region extending along the movement axis at most over 10% of the total length of the respective guide rail, and a material-fitting connection is formed between the guide rail and the profiled body in said material-fitting region.

Description

Technical Field

[0001] The invention relates to a linear guide having a slide which is linearly movable guided on a profile body and is used for converting a rotary movement of a drive motor into a linear movement of the slide. Background Art

[0002] For example, linear guides are used by the applicant in linear transmissions sold under the name ELGD and used in the field of automation technology in order to convert a rotary motion of a rotary drive, such as a pneumatic motor or an electric motor, into a linear motion of a slide. For example, the slide can be equipped with a workpiece carrier in order to displace the workpiece from a receiving position to a delivery position during the linear motion. Summary of the invention

[0003] The object of the present invention is to provide a linear guide with which large slide movement paths can be achieved.

[0004] This object is achieved in that a linear guide comprises a profile body extending along a movement axis and a slide, wherein the slide is supported on the profile body in a linearly movably manner along the movement axis and comprises a rolling bearing unit, which rests on a guide path (Führungsbahn) with at least one rolling body, wherein the guide path comprises two guide rails (Führungsschiene) arranged in parallel with each other along the movement axis, wherein the guide rails are respectively received in the profile body in a form-fitting manner in a spatial direction oriented transversely to the movement axis, wherein the end faces of the two guide rails lying opposite each other limit a docking area, and wherein a material-fitting area is respectively constructed between the respective guide rail and the profile body adjacent to the docking area, the material-fitting area extending along the movement axis over a maximum of 10% of the total length of the respective guide rail, and in this material-fitting area a material-fitting connection is constructed between the guide rail and the profile body.

[0005] The profile body forms the basic structure for the linear guide and is a component of the linear guide which can be fastened, for example, to the machine frame in order to provide a linear movement of the slide there, for example for the transfer of workpieces between a receiving position for the workpieces and a delivery position for the workpieces. The task of the profile body is to guide the slide linearly and as far as possible without play along the axis of movement, so that the slide has preferably exactly one degree of freedom of movement oriented along the axis of movement relative to the profile body. In addition, the task of the profile body is to conduct the forces acting on the slide, which are conducted via at least one rolling bearing unit to a guide rail associated with the profile body, to the machine frame. For example, the rolling bearing unit can be at least one linear reciprocating ball bearing guide (Kugelumlaufführung), which is also called a rolling bearing shoe. In such a linear reciprocating ball bearing guide, a plurality of bearing balls are accommodated in a housing and are held there on an elliptical track by suitable guide means, wherein the bearing balls protrude beyond the housing at the surface of the linear reciprocating ball bearing guide and abut against the guide rail.

[0006] Furthermore, the task of the profile body is to provide an interface for the installation of a rotary drive, such as a pneumatic motor or an electric motor, wherein the rotary motion of the drive can be converted into the desired linear motion, for example, by means of a toothed belt movably mounted on the profile body or by means of a threaded spindle movably mounted on the profile body. Accordingly, another task of the profile body is to establish a force flow between the drive and the slide and thereby to dissipate the reaction forces resulting from the interaction between the drive and the slide.

[0007] Depending on the length of the profile body, which can be in particular between 10 cm and 600 cm, it may be necessary to arrange several guide rails one after the other along the axis of movement, since the guide rails are available only in limited lengths due to their manufacturing method. For example, it is provided that, in the case of a purely exemplary length of 400 cm of the profile body, two guide rails are arranged in a row on the profile body. The problem that arises here is that the guide rails, although connected to the profile body in a form-fitting manner in all spatial directions transverse to the axis of movement due to their contour and the corresponding contour of the profile body, must have a certain degree of freedom of movement in the direction of the axis of movement. This degree of freedom of movement in the direction of the longest extension of the guide rail is required in order to be able to achieve compensation between the generally different extensions of the profile body and the guide rails in the event of temperature changes acting on the linear guide, wherein the difference in extension in the direction of the axis of movement is greatest, since this is also an extension of the profile body and the guide rails that is several times greater than their extension in the spatial direction transverse to the axis of movement.

[0008] In order to ensure a secure fixation of the two guide rails on the profile body despite this, it is provided that the guide rails are respectively partially connected to the profile body by material bonding adjacent to the abutment region defined by the mutually opposite end faces of the two guide rails. By means of this material bonding connection between the respective guide rail and the profile body, which is only partially constructed along the axis of movement, it is ensured that the respective guide rail can move substantially freely relative to the profile body along the axis of movement outside the material bonding region formed by the material bonding connection, so that no internal stresses occur between the profile body and the guide rails in the event of temperature changes for the profile body and the respective guide rail and the elongation changes that accompany this. In addition, by means of the material bonding region, it is ensured that the guide path formed by the two guide rails and provided for the rolling body to abut against each other has no deflection in the abutment region that could impair the rolling movement of the rolling bearing unit. Instead, the material bonding region is constructed in such a way that there is a gap between the two guide rails in the abutment region, which gap is negligible at room temperature and at deviating ambient temperatures within the intended application range of the linear guide.

[0009] In order to ensure the free mobility of the corresponding guide rail along the axis of movement over the greatest possible extension, it is provided that the extension of the material-fitting area along the axis of movement is no more than 10% of the total length of the corresponding guide rail. It is preferably provided that the material-fitting area extends from the abutment area over a maximum length of 8 cm, preferably 6 cm, in particular 4 cm.

[0010] Advantageous developments of the invention are the subject matter of the dependent claims.

[0011] The material-fitting area between the profile body and the respective guide rail is expediently designed as a bonding point. This allows for a free choice of the positioning of the abutment area, since, for such a design of the material-fitting area, no additional mechanical prerequisites need to be provided on the profile body and / or on the guide rail, as would be required, for example, when fixing mutually opposite end areas of the guide rail by means of fastening means, such as screws. Furthermore, by suitable selection of the adhesive for producing the bonding point, an advantageous expansion compensation between the profile body and the guide rail for the material-fitting area can be ensured, so that stresses between the profile body and the guide rail that may occur during temperature changes can be limited to a minimum, since these stresses are compensated by the adhesive, which preferably has residual elasticity.

[0012] Preferably, the guide rail is configured with a constant rail profile along the axis of motion and has a guide area for the rolling body to abut against and an abutment area for abutting against the abutment surface of the profile body, wherein the abutment area has a support area facing away from the guide area and a clamping area adjacent to the support area on both sides, and the clamping area respectively encloses an acute angle with the support area. For example, the guide rail has a rail profile in a cross-sectional plane oriented transversely to the axis of motion, the rail profile is configured at least substantially mirror-symmetrically, and in the rail profile, the guide area has a recess with a circular segment profile on the edge side, which can be used for the rolling of the bearing ball. An abutment area is configured at the rear side of the guide rail facing away from the guide area, and the abutment area is designed for a form-fitting connection between the guide rail and the profile body. For this purpose, the abutment area includes a support area, which can also be referred to as the rear side of the guide area and is configured to abut against the corresponding abutment surface of the profile body. Preferably, the support area is configured flatly or at least has a flatly configured section. The clamping regions are each designed in such a way that they adjoin the support region on both sides and each of them encloses an acute angle with the support region. The orientation of the clamping regions ensures a favorable introduction of forces between the slide and the rolling bearing unit, the guide rail and the profile body mounted thereon. For example, in a cross-sectional plane, the contour of the guide rail is enveloped by an envelope curve that is designed as a rhombus or diamond.

[0013] In a further development of the invention, it is provided that the profile body is constructed with a constant body contour along the axis of movement and has a receiving recess for accommodating the guide rail, wherein the receiving recess has two contact surfaces arranged at a distance from each other, preferably oriented parallel to each other, in particular arranged in a common plane, and two clamping surfaces oriented at an acute angle to the contact surfaces. As a result, the receiving area of ​​the profile body is prepared for positively accommodating the guide rail and has a body contour that at least approximately corresponds to the contour of the guide rail in a cross-sectional plane oriented transversely to the axis of movement. It is particularly preferably provided that the body contour is designed in the receiving area so that the guide rail can be first pushed into the receiving area along the axis of movement with low friction starting from the axial end face of the profile body and then a local deformation of the receiving area is carried out in order to thereby ensure a positive fixing of the guide rail on the profile body in all spatial directions outside the axis of movement.

[0014] In a further embodiment of the invention, it is provided that a first cavity is formed between the contact surface of the profile body and the guide rail, and a second cavity is formed between the corresponding contact surface and the adjacently arranged clamping surface together with the guide rail, wherein the first cavity and / or the second cavity is filled with a connecting material, in particular an adhesive, in the material-fitting region. By using at least one of the cavities to accommodate the connecting material, in particular an adhesive, it is ensured that the material thickness of the connecting material is sufficient to ensure expansion compensation between the profile body and the guide rail. Preferably, a plurality of the cavities are provided with connecting material in order to ensure a secure fixation between the guide rail and the profile body, wherein the extension of the material-fitting region along the axis of movement is selected to be as short as possible.

[0015] The profile body is advantageously associated with two guide paths, which are spaced apart from one another in a spatial direction transverse to the axis of motion, in particular arranged mirror-symmetrically with respect to a mirror plane containing the axis of motion. This allows the slider to be supported on both sides when using at least two rolling bearing units and associated guide rails. It is particularly advantageous to provide that a first docking region for a first guide path comprising at least two guide rails is configured at a different position along the axis of motion than a second docking region for a second guide path arranged opposite the first guide path. This prevents the slider from passing through two docking regions simultaneously when moving along the axis of motion.

[0016] It is preferably provided that the profile body is made of aluminum and the guide rail is made of steel. This allows the profile body to be produced using an aluminum extrusion process, which is a cost-effective option for producing a body with complex profiles. With regard to the fatigue strength requirements to be met, the use of steel for the guide rail is advantageous, primarily because the bearing balls of the rolling bearing unit are also made of steel and thus ensure a particularly favorable rolling pair between the bearing balls and the guide rail.

[0017] In an advantageous improvement of the invention, it is provided that the slide has a spindle nut, which is penetrated by a threaded spindle that is rotationally movably supported on the profile body and extends along the axis of movement. In this embodiment, the linear guide forms a linear transmission device for converting a rotary motion into a linear motion. For this purpose, the drive axis of the drive device is oriented parallel to the axis of movement. As a result, the rotary motion of the drive axis can be introduced into the threaded spindle that extends along the axis of movement and is rotatably supported on the profile body via a coupling arranged on the end side on the profile body. The rotary motion of the threaded spindle is converted into a translational motion via a spindle nut associated with the slide, which spindle nut engages with an internal thread in the external thread of the threaded spindle.

[0018] Alternatively, it can be provided that the slide is coupled to an upper run or a lower run of a toothed belt extending along the axis of movement, wherein a belt pulley mounted rotatably on the profile body is arranged at mutually opposite end regions of the profile body. In this case, the linear guide forms a linear transmission for converting a rotary motion into a linear motion. Here, the drive axis of the drive device is oriented transversely to the axis of movement and is connected to a first belt pulley mounted rotatably on the profile body, which is at least partially wound by a toothed belt and can be designed in particular as a toothed belt pulley with an external toothing. In addition, a second belt pulley, which can be designed, for example, as a deflection wheel or a toothed belt pulley, is rotatably supported on the profile body, which second belt pulley is arranged at a distance relative to the first belt pulley along the axis of movement and is also partially wound by a toothed belt.

[0019] The two guide rails are expediently connected to the profile body only in a form-fitting manner outside the respective material-fitting regions. This allows the guide rails to have a single, almost point-like connection to the profile body in terms of their fixation in the direction of the axis of movement and to be freely movable in their remaining extension along the axis of movement, if friction effects between the guide rails and the profile body, which could result from the form-fitting fixation of the guide rails on the profile body in all spatial directions outside the axis of movement, are neglected. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] An advantageous embodiment of the present invention is shown in the drawings.

[0021] Figure 1 A linear guide having a profile body and a slide which is linearly movably supported on the profile body is shown.

[0022] Figure 2 A method for introducing linear motion into a Figure 1 A strict schematic diagram of a first embodiment of a drive mechanism on a slide, also referred to as a spindle drive,

[0023] Figure 3 A method for introducing linear motion into a Figure 1 Strict schematic diagram of a second embodiment of the drive mechanism on the slide, also known as a toothed belt drive,

[0024] Figure 4 Shown according to Figure 1 An enlarged view of the main contour of the profile body and a detailed view of the guide rail accommodated therein, and

[0025] Figure 5 Shown according to Figure 1A perspective view of a profile body having two guide rails arranged in a row and a docking area formed between the guide rails, and a detailed view of a docking area. DETAILED DESCRIPTION

[0026] exist Figure 1 The linear guide 1 shown in FIG. 1 comprises a profile body 2 which is designed purely by way of example as an aluminum extrusion part and which extends with a constant contour along a movement axis 4 and on which a slide 3 is mounted linearly movably along the movement axis 4. In order to ensure a linearly movable mounting of the slide 3 with little play, in particular without play, relative to the profile body 2, guide paths 5 arranged opposite one another are designed purely by way of example on the profile body 2, which guide paths are provided for schematically Figure 2 and Figure 3 The rolling movement of the rolling body 76 of the rolling bearing unit 74 is shown in FIG.

[0027] In order to support the slide 3 in a linearly movable manner, it is provided that the slide 3 partially extends into the recess 6 of the U-shaped profile body 2, wherein the guide path 5 is arranged in a manner adjacent to the bottom surface 7 of the recess 6 purely by way of example. It is also provided that the slide 3 is in mechanical contact with the profile body 2 only via the rolling body 76, while all other areas of the slide 3 are arranged with a movement gap (not shown in detail) relative to the profile body 2. In order to prevent dirt from penetrating into the recess 6, a cover strip 8 is provided, which closes the recess 6 and can be lifted by the slide 3 in a manner (not shown in detail) so as not to hinder the linear movement of the slide 3 along the movement axis 4. Purely by way of example, the cover strip 8 is drawn in the rear area of ​​the profile body 2, while the cover strip 8 is not shown in the front area of ​​the profile body 2, in order to make the positioning of the guide path 5 visible in particular.

[0028] exist Figure 1 The linear guide 1 shown in FIG. 2 can optionally be equipped with a spindle drive or a toothed belt drive in order to bring about the desired linear movement of the slide 3 relative to the profile body 2 .

[0029] exist Figure 2 In the embodiment of the drive mechanism as a spindle drive, purely by way of example and purely schematically, this embodiment is merely intended to explain how such a spindle drive can be designed in principle. Figure 2As can be seen in the figure, a drive motor 51, which can be designed as a pneumatic motor or an electric motor, for example, has a drive shaft 52. The drive shaft 52 can be subjected to energy loading from the drive motor 51 to perform a rotational movement. It is provided here that the axis of rotation of the drive shaft 52 is identical to the axis of movement 4. The drive shaft 52 is connected to a threaded spindle 54 in a rotationally fixed manner via a coupling 53, so that the rotational movement of the drive shaft 52 causes the same rotational movement of the threaded spindle 54. The threaded spindle 54 has an external thread 55 and is respectively rotatably supported in spindle bearings 56 at opposite end regions. Each of the spindle bearings 56 can be fastened in a manner not shown in detail. Figure 2 The threaded spindle 54 is received on or in the profile body 2 (not shown) so that the threaded spindle 54 is received on the profile body 2 only so that it can be moved in rotation.

[0030] Partially cut away and relative to Figure 1 and Figure 2 The slide 3, which is shown only strictly schematically in the figure, is equipped in the lower region with two rolling bearing units 74 arranged at a distance from each other along the movement axis 4, each of which comprises a bearing housing 75 and a rolling body 76 accommodated therein and is each designed as a linear reciprocating ball bearing guide. The task of the rolling bearing unit 74 is to ensure a linearly movable support of the slide 3 on the profile body 2 without play or at least with as little play as possible and to support the torque acting on the slide 3 about the movement axis 4. For this purpose, two rows of rolling bodies 76 of the respective rolling bearing unit 74 are in contact with the guide path 5 in the profile body 2, such as in the case of the roller bearing unit 74. Figure 1 and Figure 3 As shown in more detail in .

[0031] The slide 3 has a recess 77 in which a spindle nut 57 is accommodated, which is connected to the slide 3 in a manner not shown in detail and engages with an internal thread 58 in an external thread 55. Due to the linear mobility of the slide 3 relative to the profile body 2 and the torque support for the slide 3 relative to the profile body 2 ensured by the rolling bearing unit 74, a linear movement of the slide 3 along the movement axis 4 is generated from the rotational movement of the threaded spindle 54 about the movement axis 4.

[0032] exist Figure 3 , purely by way of example and purely schematically, an embodiment of the drive mechanism as a toothed belt drive is shown, which is intended to explain how such a toothed belt drive can be constructed in principle. It is provided that a first belt pulley 63 is fastened to a drive shaft 62 of a drive motor 61, wherein the drive shaft 62 is oriented transversely to the axis of movement 4. The first belt pulley 63 is rotatably fixed to the drive shaft 62 of the drive motor 61, like the second belt pulley 64, in a manner not shown in detail. Figure 363 and 64 respectively, wherein the toothed belt 65 is wound around the first belt pulley 63 and the second belt pulley 64 by approximately 180°, wherein the toothing of the toothed belt, which is not shown in detail, engages in the toothing of the two belt pulleys 63 and 64, which is also not shown in detail. The upper run 66 of the toothed belt 65 is guided through the recess 77 of the slide 3 and is fastened at the upper side of the recess 77. For this purpose, a fastening plate 68 is provided, which engages in the toothing of the toothed belt 65 in a manner not shown in detail and is connected to the slide 3, for example, by means of screws, which are not shown. The lower run 67 of the toothed belt 65 is guided below the slide 3.

[0033] You can use the basis Figure 2 The driving mechanism can also be used according to Figure 3 The drive mechanism displaces the slide 3 linearly along the movement axis 4 relative to the profile body 2. In order to ensure the above-described support of the slide 3 with no clearance or at least a small clearance relative to the profile body 2, the guide paths 5 arranged opposite to each other are respectively configured as guide rails 31, such as Figure 4 Preferably, the guide rail 31 is made of steel and has a cross-sectional plane oriented transversely to the axis of motion 4 (which corresponds to Figure 4 In the illustration plane ) there is a rail profile 32 which can be functionally divided into a guide area 33 and a contact area 34.

[0034] The guide area 33 is manufactured with high precision, in particular as a ground surface, and is used locally for the abutment of the rolling body 76 of the corresponding rolling bearing unit 74. The abutment area 34 extends adjacent to the guide area 33, which is provided for positively locking in a correspondingly designed receiving recess 23 of the profile body 2 and can, if necessary, also be manufactured at least locally with high precision, in particular by grinding.

[0035] As from Figure 4 As can be seen in the FIGURE, the guide region 33 has a rolling surface 41 which is designed in the form of a circle segment and is oriented mirror-symmetrically with respect to the mirror plane 40 and is provided for a rolling movement of the rolling body 76 .

[0036] The contact area 34 includes a support area 35 and two clamping areas 36 and 37 respectively arranged between the guide area 33 and the support area 35. For example, it is provided that the support area 35 has two support surfaces 42, 43 arranged at a distance from each other and located in a common plane, and the support surfaces are configured to contact the corresponding contact surfaces 24, 25 of the profile body 2. The clamping areas 36, 37 extend adjacent to the support surfaces 42, 43, and the clamping areas respectively have prismatic surfaces 44, 45 oriented at an acute angle to each other, wherein the prismatic surfaces 44, 45 are oriented at an acute angle 38, 39 to the support surfaces 42, 43, respectively. Corresponding to Figure 4 , the prismatic surfaces 44, 45 can be enclosed purely by way of example by a rhombus-shaped enveloping geometry shown in dashed lines. The prismatic surfaces arranged adjacent to the guide area 33 are designed to be in flat contact with the clamping surfaces 26, 27 of the profile body 2. It is preferably provided that, for the purpose of mounting the guide rail 31, there is initially still a distance (not shown) between the clamping area 36 and the clamping surface 26 arranged opposite, so that the guide rail 31 can be pushed into the receiving recess 23 of the profile body 2 with low friction. In order to ensure a positive fixing of the guide rail 31 in all spatial directions outside the axis of movement 4, a plastic deformation of the projection 28, on the underside of which the clamping surface 26 is formed, is carried out at a later point in time, whereby the distance between the clamping surface 26 and the clamping area 36 is reduced to zero.

[0037] exist Figure 5 2 shows a profile body 2 with a guide rail 31 accommodated therein, wherein the guide path 5 which is completely visible due to the perspective view is formed by two guide rails 31 arranged one behind the other in a row along the movement axis 4. Figure 5 As can be seen in the detailed view of FIG. 4 , the two guide rails 31 adjoin each other with mutually opposite end faces 46, 47 in a butt joint region 48. Starting from the butt joint region 48, material-bonding regions 49, 50, which are only schematically drawn, extend in both directions along the axis of movement 4, in which material-bonding regions a material-bonding connection is formed between the respective profile rail 31 and the profile body 2.

[0038] It is preferably provided that such a material-fitting connection in the corresponding material-fitting areas 49, 50 is established in that the first cavity 91 and / or the second cavity 92 and / or the third cavity 93 are filled in sections with a hardenable amorphous substance, preferably an adhesive, in particular a two-component epoxy resin adhesive, so as to thereby achieve the desired material fit between the guide rail 31 and the profile body 2.

[0039] As from Figure 5As can be seen from the illustration of , the two integrally bonded regions 49 , 50 are designed so as to directly adjoin the abutment region 48 , whereas outside of the integrally bonded regions 49 , 50 , no integrally bonded connection is provided between the guide rail 31 and the profile body 2 .

[0040] In a variant of the linear guide (not shown), a section is formed between two integrally bonded areas, in particular at the level of the abutment area 48 , in which no integrally bonded connection is provided between the guide rail and the profile body.

Claims

1. A linear guide (1) having a profile body (2) extending along a movement axis (4) and a slide (3), wherein: The slide is supported on the profile body (2) in a linearly movable manner along the movement axis (4) and has a rolling bearing unit (74), which is in contact with a guide path (5) by means of at least one rolling body (76), wherein the guide path (5) has two guide rails (31) arranged in parallel with each other along the movement axis (4), and the guide rails are respectively received on the profile body (2) in a form-fitting manner in a spatial direction oriented transversely to the movement axis (4), wherein the end faces (46, 47) of the two guide rails (31) facing each other limit a docking area (48), and wherein a material-fitting area (49, 50) is formed between the respective guide rail (31) and the profile body (2) adjacent to the docking area (48), the material-fitting area extending along the movement axis (4) over a maximum of 10% of the total length of the respective guide rail (31), and in the material-fitting area a material-fitting connection is formed between the guide rail (31) and the profile body (2).

2. The linear guide (1) according to claim 1, characterized in that The material-bonding areas (49, 50) between the profile body (2) and the respective guide rail (31) are designed as bonding locations.

3. The linear guide (1) according to claim 1 or 2, characterized in that The guide rail (31) is constructed with a constant rail profile (32) along the movement axis (4) and has a guide area (33) for a rolling body (76) to abut against and an abutment area (34) for abutting against abutment surfaces (24, 25) of the profile body (2), wherein the abutment area (34) has a support area (35) facing away from the guide area (33) and clamping areas (36, 37) adjacent to the support area (35) on both sides, the clamping areas each enclosing an acute angle (38, 39) with the support area (35).

4. The linear guide (1) according to claim 3, characterized in that The profile body (2) is constructed with a constant body contour along the movement axis (4) and has a receiving recess (23) for accommodating the guide rail (31), wherein the receiving recess (23) has two contact surfaces (24, 25) arranged at a distance from each other, preferably oriented parallel to each other, and in particular arranged in a common plane, and two clamping surfaces (36, 37) oriented at an acute angle to the contact surfaces (24, 25), respectively.

5. The linear guide (1) according to claim 4, characterized in that A first cavity (91) is constructed between the abutment surface of the profile body (2) and the guide rail (31), and a second and / or third cavity (92, 93) is constructed together with the guide rail between the corresponding abutment surface (24, 25) and the adjacently arranged clamping surface (36, 37), wherein the first cavity (91) and / or the second and / or third cavity (92, 93) are filled with a connecting material, in particular an adhesive, in the material matching area (49, 50).

6. Linear guide (1) according to any one of the preceding claims, characterized in that The profile body (2) is associated with two guide paths (5), which are spaced apart from one another in a spatial direction transverse to the movement axis (4), in particular arranged mirror-symmetrically with respect to a mirror plane containing the movement axis (4).

7. Linear guide (1) according to any one of the preceding claims, characterized in that The profile body (2) is made of aluminum and the guide rail (31) is made of steel.

8. Linear guide (1) according to any one of the preceding claims, characterized in that The slide (3) has a spindle nut (57) through which a threaded spindle (54) is penetrated, which is supported rotatably on the profile body (2) and extends along the movement axis (4).

9. The linear guide (1) according to any one of claims 1 to 7, characterized in that The slide (3) is coupled to an upper run (55) or a lower run (67) of a toothed belt (65) extending along the movement axis (4), wherein belt pulleys (63, 64) rotatably supported on the profile body (2) are respectively arranged at opposite end regions of the profile body (2).

10. Linear guide (1) according to any one of the preceding claims, characterized in that The two guide rails (31) are connected to the profile body (2) only in a form-fitting manner outside of the corresponding material-fitting regions (49, 50).

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