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WO1988002471A1 - Instrument pour mesurer la hauteur - Google Patents

Instrument pour mesurer la hauteur Download PDF

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Publication number
WO1988002471A1
WO1988002471A1 PCT/CH1987/000127 CH8700127W WO8802471A1 WO 1988002471 A1 WO1988002471 A1 WO 1988002471A1 CH 8700127 W CH8700127 W CH 8700127W WO 8802471 A1 WO8802471 A1 WO 8802471A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball bearing
slide
race
axis
plane
Prior art date
Application number
PCT/CH1987/000127
Other languages
German (de)
English (en)
Inventor
Eberhard Armbruster
Antonio Soriano
Original Assignee
Wenzel Präzision GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wenzel Präzision GmbH filed Critical Wenzel Präzision GmbH
Publication of WO1988002471A1 publication Critical patent/WO1988002471A1/fr

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Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
    • G01B5/00—Measuring arrangements characterised by the use of mechanical techniques
    • G01B5/0011—Arrangements for eliminating or compensation of measuring errors due to temperature or weight
    • G01B5/0016—Arrangements for eliminating or compensation of measuring errors due to temperature or weight due to weight
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
    • G01B5/00—Measuring arrangements characterised by the use of mechanical techniques
    • G01B5/02—Measuring arrangements characterised by the use of mechanical techniques for measuring length, width or thickness
    • G01B5/06—Measuring arrangements characterised by the use of mechanical techniques for measuring length, width or thickness for measuring thickness
    • G01B5/061—Measuring arrangements characterised by the use of mechanical techniques for measuring length, width or thickness for measuring thickness height gauges

Definitions

  • the invention relates to a height gauge according to the preamble of claim 1.
  • a height gauge of the type mentioned is used to determine the height of a measuring point above a reference plane, which is usually the surface of a measuring table, with the highest possible accuracy on a measurement object.
  • the measurement is carried out with the aid of a slide that moves along a guide track.
  • the measuring distance is the same as the path covered by the sled on the guideway, it is a 1: 1 image of the height to be measured, i.e. the length of the perpendicular drawn from the measuring point to the reference plane.
  • the height of the measuring point can be determined, the height difference between two measuring points can also be determined.
  • the accuracy required by a height gauge is around 3 / um.
  • the main problem is to provide a straight vertical guideway for the slide and to arrange it normal to the horizontal reference plane.
  • the main problem mentioned can be broken down into various sub-problems, but the accuracy achieved depends on the solution of all these sub-problems, i.e. the solutions to the sub-problems are not separate and independent of one another, but interact with one another.
  • a partial problem consists in the exact mounting of the height measuring gauge on the measuring table in the static case and in the dynamic case.
  • a conventional solution is storage based on the tripod principle.
  • the base of the height gauge is attached to the supported at three points.
  • these three points can be arranged in such a way that they define a rather large support triangle, the contact area of the three legs that can be reached with them is very small, which leads to a high load on the material of the base and also on the measuring table.
  • With the three-leg principle it is still possible to immerse the base in the unevenness in the measuring table, despite the large area spanned by the support triangle, since the immersion of just one leg tilts the base as a whole.
  • the height gauge is open Canting susceptible.
  • the base of the height gauge has to be periodically lapped due to the uneven wear, which still occurs due to the so-called slipping despite air cushions, which is extremely expensive.
  • the height measuring gauge usually includes integrated evaluation electronics, the supply transformer of which develops heat due to the power loss, This evaluation electronics together with the transformer must not be attached to the base.
  • Another sub-problem is the exact mounting of the guideway for the slide on the base in the static case and in the dynamic case.
  • a conventional solution consists in the design of the guide track for the slide as a guide profile or guide plate and in the attachment of this guide track to the stand with the aid of a larger number of screws. These screws must not be tightened tightly, otherwise there will be tensions that deform the guideway. Tightened screws also lead to deformations due to the thermal dimensional changes of the guideway and the stand. Only slightly tightened screws can loosen completely. In the end, the conventional fastening of the guideway to the stand with the aid of a larger number of screws leads to a very poorly defined state of tension.
  • the stand As a carrier of the guideway, the stand must therefore be designed as much as possible so that it has a high degree of rigidity and its geometry remains as unaffected as possible by the various forces that arise in the static and dynamic cases.
  • a conventional solution consists in forming the stand with three plates welded together, one of which carries the guideway. But this creates an asymmetrical construction that is also asymmetrical is stressed, so that tensions arise that are reduced over time via deformations.
  • Another sub-problem is to reduce to a minimum the inaccuracies which are caused directly by the guideway and by the slide. Such inaccuracies produce pitch, roll and roll movements of the slide during its movement along the guideway in a certain direction and when the direction of movement is reversed (so-called tipping over). A hysteresis is also noticeable when the direction is reversed.
  • roller bearings are excluded because they have a rolling resistance that is too high for this application.
  • Ball bearings are used, but they have various shortcomings. Examples of these defects include: the eccentricity, taper and lack of roundness of the races of the ball bearings; the asymmetry of the raceways in the ball bearing rings with respect to the plane of symmetry normal to the roll axis; the inclined position of the roll axis in relation to the direction of movement, which means that certain forces are not in the plane of symmetry and therefore the connecting line between the point of contact of a ball with an outer race and the point of contact of a ball with an inner race is not in the plane of symmetry .
  • this straight line tilts into the position symmetrical with respect to the plane of symmetry, because the balls change into their other equilibrium position.
  • Inaccuracies can also be attributed to the guideway. Apart from the deformations of the stator that are passed on by the guideway, the surface of the guideway has other causes of inaccuracies in that local variations in its surface condition can change the behavior of the ball bearings.
  • a conventional partial solution to the guiding problem is that the ball bearings are specifically selected and individually adjusted on the height measuring gauge by means of the deformations which are brought about, which is associated with a very high outlay.
  • the special base of the height gauge has a large area and has a flat contact surface with the reference plane of the measuring table.
  • This contact surface is relieved by the air pressure, ie the air pressure transfers the weight of the height measuring gauge to the entire surface of the measuring table, which is encompassed by the extent of the depression in the base.
  • the base does not float on an air cushion, so that the support remains free of canting, and nevertheless, thanks to the relief, the sliding properties of the base on the measuring table are almost as good as with an air cushion.
  • the self-lapping remains low; in the course of using the height measuring gauge, there is no noticeable deterioration in the perpendicularity of the measuring path to the reference plane.
  • the amount of air required for this is small since it is not intended to form an air cushion, and therefore only a small amount of air escapes between the non-ideal contact surfaces of the base and the measuring table.
  • the support is not based on the tripod principle, the heating of the base due to the power loss on a transformer does not have a significant effect on the accuracy, so that the evaluation electronics together with its supply transformer can be easily integrated in the vicinity of the base of the height gauge , For example, by arranging them in the handle, which can be thermally decoupled from the base as a precaution.
  • the special double mounting of the column in the stand ensures that the forces acting on the column are always symmetrical to the longitudinal axis of the column, regardless of an adjustment of the column in relation to the base of the height gauge. Apart from the forces exerted by the sled, essentially only gravity acts on the column. In particular, the sliding fit in the upper bearing allows the column to expand freely. Thus, there are no tensions on the column which could impair the necessary quality of the column geometry achieved during manufacture, since these tensions would tend to be reduced by deformations over time.
  • the perpendicularity of the column to the reference plane can also be adjusted independently of the base of the height gauge thanks to the upper sliding seat which can be adjusted parallel to the reference plane.
  • the special upper bearing of the column exerts only insignificant forces on the stand, which arise in maintaining the unstable balance of the column and lie in a plane normal to the longitudinal axis of the stand. This bearing therefore does not generate any torque on the stand. Otherwise, the stand is constructed symmetrically. Apart from the fastening screws which are screwed in from the base and from above, but which are arranged axially symmetrically, there are no elements which generate stresses during assembly which occur in the would be degraded over time by deformation. The tension of the steel strip, which creates the connection with the counterweights, is also transmitted in exactly one of the planes of symmetry via the deflection rollers and their roller bearings on the top and bottom of the stand, so that this stress is also symmetrical.
  • each ball bearing axis allows the respective axis to be set relative to the running surface in such a way that the taper of the outer surface of the outer race is compensated for.
  • This adjustment option also allows the respective axis to be aligned such that all the forces come to lie in the plane of symmetry, which also means that the points of contact between the balls and the running surfaces touching them also come to lie in this plane of symmetry. Thanks to the excellent adjustment of the slide's ball bearings, the tension of the steel band and the mass of the counterweights attached to them can be lower than with conventional height gauges, which in turn helps to keep the stand's load low.
  • FIG. 2 is a partially broken perspective drawing of part of the inventive height gauge in the vicinity of the slide, partly with parts shown transparently,
  • FIG. 3 shows a perspective drawing of a part of the height measuring gauge according to the invention in the vicinity of the counterweight of the slide, partly with parts shown in a transparent manner
  • FIG. 4 shows a perspective drawing of a part of the height measuring gauge according to the invention in the vicinity of the upper part of the height measuring gauge, partly with parts shown in a transparent manner
  • FIG. 5 shows a side view of the base of the height measuring gauge according to the invention, in a vertical axial section
  • 6a is a side view of a lockable ball bearing support of the height measuring gauge according to the invention, partly in a vertical axial section,
  • FIG. 6b is a plan view of the same ball bearing carrier as in Fig. 6a,
  • 7a is a side view of an elastically pressed
  • Ball bearing carrier of the height measuring gauge according to the invention partly in a vertical axial section
  • FIG. 7b is a plan view of the same ball bearing carrier as in Fig. 7a
  • 8 is a side view of a fastening system or a pressing system for the ball bearing supports of the height measuring gauge according to the invention, partly in a vertical axial section.
  • FIGS. 1 to 8 parts of the height measuring gauge, which occur several times with the same design, are identified by the same reference numerals. In the following, these reference numerals are retained every time, even if a designated part cannot be seen in the figure just described, for example because it is covered because of the perspective view.
  • a base 1 of the height measuring gauge is shown, which is intended to lie on the horizontal surface of a measuring table and to be easily displaceable thereon in the horizontal direction.
  • This horizontal surface of the measuring table therefore coincides with the lower surface of the "base 1, which forms a flat support surface 2 for supporting the height measuring gauge on the measuring table and at the same time a reference plane of the height measuring gauge to the measuring table.
  • On the base 1 there is a vertical guideway 3 is supported for a slide 4 (FIG. 2) on which a button 5 can be fastened, and a vertical guide track 6 for a counterweight 7 (FIG. 3) is also supported on the base 1.
  • the counterweight 7 is at a fastening point 8 is connected to the carriage 4 by a band 9 and 10 for train and counter-train 10.
  • the band for train 9 runs up from the counterweight 7, via a horizontal deflection roller 11 (FIG. 4), which is in the vicinity of the upper part of the height gauge is arranged, and from there down to the carriage 4, to which it is connected at an attachment point that is not visible in the perspective view m counterweight 7 down, over a horizontal-axis deflection roller 12 (Fig. 1), which is arranged in the vicinity of the base 1 of the height measuring gauge, and from there up to the slide 4, with which it is attached to the same in the Spective view not visible attachment point is connected as the band for train 9.
  • the base 1 is essentially symmetrical about a vertical axis of symmetry 13 (FIG. 5).
  • the outer circumference of the contact surface 2 is designated 16.
  • the support surface 2 i is essentially symmetrical about the vertical axis of symmetry 13, and it lies between the circumference 15 of the depression 14 and the outer circumference 16 of the support surface 2.
  • the circumference 15 of the depression 14 is circular and the circumference 16 of the support surface 2 is essentially quadrangular (possibly with rounded or beveled corners), the dimensions being selected such that the projection of the depression 14 onto the support surface 2 covers an area which is 30 to "50% of the inside the circumference 16 of the total base area of the base 1.
  • an air inlet duct 17 from a connection for compressed air (not shown) to the depression 14 and on the other hand an air outlet duct 18 from the depression 14 to a pressure regulating device which is designed as a nozzle 19 and causes an overpressure in the depression 14, when compressed air is supplied via the air inlet duct 17.
  • a vertical stand 20 is supported, which is designed as a vertically aligned double-T profile.
  • the flanges of the double-T profile are supported and fastened to the base, for example by screws (not shown) which are screwed into the flanges from below and through base 1.
  • This stand 20 is near its upper end (Fig. 4) with a support member 21 provided, which is advantageously formed substantially as a plate and is supported and fastened to the flanges of the double-T profile, for example by screws (not shown) which are screwed into the flanges from above and through the carrier part 21 become.
  • Two columns 22 and 23 lead from the base 1 to the carrier part 21, both of which are designed in the form of a square profile and are arranged such that the web of the double-T profile lies between the two columns 22 and 23.
  • a holder 24 for the upper end of the column 22 and a holder 25 for the upper end of the column 23 are arranged in the carrier part 21.
  • the brackets 24 and 25 are releasably attached to the carrier part 21, the holder 24 by means of screws, not shown, which are guided through the holes 26 in the holder 24 and the holes 27 in the carrier part 21, the holder 25 by means of screws 28, which are horizontal are guided through the carrier part 21.
  • the brackets 24 and 25 are on the carrier part by displacement in a horizontal plane
  • the holder 24 is translationally displaceable, while the holder 25 is set according to the principle of the rotatable eccentric. With the screws mentioned, the brackets 24 and 25 and thus the columns 22 and 23 can be locked in the set position.
  • the brackets 24 and 25 are as plain bearings for the columns
  • a bolt 29 is axially screwed into the bore 30 of the column 22 for this purpose.
  • This bolt 29 is axially sliding through the bore 31 of the bracket 24 but without play.
  • the bolt 29 is inserted into the bore of a sleeve 32 without play slidably guided, and this sleeve 32 is fixed in the bracket 24.
  • the column 23 is fastened, for example, in a similar manner, not shown, in the holder 25 without play.
  • the column 22 is supported on the base 1 via a joint 33 of the ball-socket type.
  • a recess 35 in the form of a hollow cone is arranged at the lower end of the column 22.
  • a recess 36 (FIG. 5) in the form of a vertical-axis hollow cone is arranged on the base coaxially to the longitudinal axis of the column 22.
  • a ball 37 is arranged which touches the outer surface of one and the other hollow cone 35 and 36 along a circle.
  • the ball 37 is provided with an axial bore.
  • a bolt 34 is axially screwed into the lower end of the column 22 and is passed through the axial bore of the ball 37 essentially without contact.
  • an elastic element 38 for example a " spiral spring”
  • a screw nut 39 are arranged such that the column 22 is pulled against the base 1 with moderate force and thus the joint 33 is always under moderate pressure remains.
  • the column 22 serves as a vertical guideway 3 for the slide 4, while the column 23 serves as a vertical guideway 6 for the counterweight 7.
  • the slide 4 runs along the column 22, while the counterweight 7 runs along the column 23.
  • the two other side surfaces, which are also adjacent to one another, can be designed as merely flat counter pressure surfaces if the measures specified below are taken in order to maintain the accuracy.
  • the web of the double-T profile has a recess in the vicinity of the base 1 and in the vicinity of the support part 21, which enables the deflection roller 11 to be arranged on the support part 21 and the deflection roller 12 on the base 1.
  • the axes of the deflection rollers 11 and 12 lie essentially in the extension of the web of the double-T profile, so that the web lies between the two vertical parts of the band for train 9 and the band for counter train 10.
  • Races 40 are arranged in the vicinity of the upper and lower ends of the slide 4 and roll on the respective corresponding side surface of the column 22.
  • the running rings 40 are over one.
  • respective ball bearings 41 are supported on respective ball bearing supports 42 and 43, which in turn are supported on the slide 4.
  • At least the ball bearing supports 42 for those races 40 which roll on one of the guide surfaces can be adjusted relative to the slide 4 in the rolling, pitching and rolling directions and can be locked in the set position.
  • All relevant ball bearing supports 42 ie the ball bearing supports 42 for all race rings 40 which roll on the column 22 on one of the guide surfaces, can be mounted in this way. If, however, these guide surfaces are arranged such that one of them, namely the guide surface 44 in FIG. 2, faces the button 5, it is possible and inexpensive to place those races 40 which roll on this guide surface 44 facing the button 5 on one to mount on the slide 4 firmly supported ball bearing carrier, which simplifies the ball bearing carrier in question except for one axis of the ball bearing in question.
  • the ball bearing supports 43 for those races 40 which roll on a counter pressure surface are arranged on the slide 4 such that they can move in the rolling, pitching and rolling directions and are elastically loaded towards the relevant counter pressure surface.
  • a ball bearing carrier 42 is shown for a race 40 rolling on a guide surface.
  • This ball bearing carrier 42 is intended and designed to be set on the carriage 4 in the rolling and pitching directions according to the tripod principle.
  • an adjusting screw (not shown) can be screwed into one of the threaded bores 45, 46, 47 of the ball bearing carrier 42 (also visible in FIG. 2).
  • the tips of these adjusting screws rest on the slide 4.
  • the ball bearing carrier 42 is also designed and designed to be adjusted on the carriage 4 in the direction of the roll.
  • an adjusting screw (not shown) can be screwed into a threaded bore 48 (also visible in FIG. 2) of the ball bearing carrier 42.
  • the tip of this adjusting screw also lies on the slide 4.
  • this adjusting screw To adjust this adjusting screw, its head is accessible through a bore 58 (FIG. 2) in the carriage 4 for a screwdriver.
  • a fastening screw 49 (FIG. 8) is through a bore 50 for fastening the ball bearing carrier 42 to the carriage 4 of the ball bearing carrier 42 and inserted into the slide 4 screwed, the diameter of the bore 50 is larger than the diameter of the fastening screw 49.
  • this fastening screw 49 can serve as an axis for rotation of the ball bearing carrier 42 on the carriage 4 and thanks to the play provided between the bore 50 and the fastening screw 49 also adjustment of the ball bearing carrier 42 on the slide 4 in the rolling and pitching direction is permitted.
  • the seat of the head 51 of the fastening screw 49 is formed as a conically shaped bore 52. Between this seat or the conically shaped bore 52 and the head 51 of the fastening screw 49, a washer 53 designed as a hemisphere is arranged, which is placed on the fastening screw 49 such that the hemisphere faces and is adjacent to the conical bore 52.
  • the head 51 of the fastening screw 49 could be designed as a hemisphere facing the conical bore 52.
  • the fastening screw 49 can be used in an inverted position, the head of the fastening screw 49 lies in the carriage 4, while a screw nut is screwed onto the body of the fastening screw 49 after the washer 53.
  • the screw nut could be formed directly as a hemisphere facing the conical bore 52. It can also facilitate the construction and assembly of this fastening means for the ball bearing carrier 42 if a washer 54 is inserted between the flat side of the washer 53 designed as a hemisphere and the head 51 or the nut of the fastening screw 49, which serves only as a spacer and is designed as a cylinder with mutually parallel end faces.
  • this bore 55 for receiving and holding the (not shown) axis of the ball bearing 41 provided for the race 40. So that the race 40 rolls on the guide surface, this bore 55 and its axis are arranged parallel to the guide surface.
  • the axes of the three threaded bores 45, 46, 47 of the ball bearing carrier 42 are parallel to one another, to the axis of the bore 55 (and thus also to the axis of the race 40 and to the relevant one Guide surface on which the race 40 rolls) is arranged orthogonally and symmetrically to the plane of symmetry 66 of the race 40.
  • the axes of the threaded bores 45, 46 intersect the axis of the bore 55 (and thus also the axis of the race 40) at right angles, and they are symmetrical to the plane of symmetry 56 of the race 40 arranged.
  • the axis of the threaded bore 47 (and thus also the axis of the adjusting screw inserted therein) is arranged in the plane of symmetry 56 of the race. These axes of the three adjusting screws are thus arranged in the projection plane of FIG. 6b at the corner points of an isosceles triangle.
  • the axis of the fastening screw 49 lies parallel to the axes of the threaded bores 45, 46-, 47 and therefore also to the axes of the three adjusting screws.
  • This axis of the fastening screw 49 intersects the projection plane of FIG. 6b essentially in the center 57 of the (not shown) circumference of the isosceles triangle corresponding to the axes of the threaded bores 45, 46, 47, i.e. it lies at the same distance from each of the three other axes in the plane of symmetry 56 of the race 40.
  • the axis of the threaded bore 48 (and thus also the axis of the adjusting screw used therein) is arranged parallel to the guide surface and normal to the plane of symmetry 56, that is to say it lies parallel to the projection plane of FIG. 6b and Axis of the bore 55 (and thus also to the axis of the race 40).
  • This axis of the threaded bore 48 is closer to the center 57 than the axis of the threaded bore 47, ie this axis of the threaded bore 48 intersects the plane of symmetry 56 between the center 57 and the corner point of the isosceles triangle lying on the plane of symmetry 56, where the axis of the threaded bore 47 lies.
  • a threaded bore 59 which is essentially parallel to the threaded bore 48, is arranged on the slide, into which a counter screw (not shown) is screwed, the tip of which bears against the ball bearing carrier 42. Tightening this counter screw acts counter to tightening the screw in the thread. hole 48 inserted adjusting screw.
  • the fastening screw 49 is now loosened, thanks to the ball-socket-gel.enk formed by the washer 53 in the conical bore 52, the tilting of the ball bearing carrier 42 by adjusting the adjusting screws in the threaded holes 45, 46, 47 and the rotation of the Ball bearing support 42 by adjusting the adjusting screw and the counter screw in the threaded bores 48 and 59.
  • the fastening screw 49 is tightened slightly, the adjusting screws seated in the threaded bores 45, 46, 47 are pressed against the slide 4, so that the position tion of the ball bearing carrier 42 is firmly defined and locked according to the tripod principle.
  • the washer may be advantageous to design the washer as an elastic element, for example in the form of a rubber cylinder or a package of spring washers, in order to use an elastic force or a spring force instead of a metered tightening torque of the fastening screw 49 (both cases are analogous, in that way or so an elastic load is generated and converted into force).
  • a ball bearing carrier 43 is on a counter pressure surface rolling race 40 shown.
  • This ball bearing carrier 43 is intended and designed to be set on the carriage 4 in the rolling and pitching directions according to the tripod principle.
  • an adjusting screw (not shown) can be screwed into one of the threaded bores 60, 61 of the ball bearing carrier 43. The tips of these adjusting screws rest on the slide 4.
  • the race acts here as the third leg, as will be explained in the following.
  • a pressure screw 49 FIG.
  • the ball bearing carrier 43 is also designed and designed to be set on the slide 4 in the direction of the roll.
  • an adjusting screw (not shown) can be screwed into a threaded bore 63 of the ball bearing carrier 43.
  • the tip of this adjusting screw also lies on the slide 4. To adjust this adjusting screw, its head is accessible to a screwdriver through a bore 58 in the slide 4.
  • the seat of the head 51 of the pressure screw 49 is designed as a conically shaped bore 64. Between this seat or the conically shaped bore 64 and the head 51 of the fastening screw 49 there is a washer 53 designed as a hemisphere, which is placed on the pressure screw 49 such that the hemisphere faces the conical bore 64 and is adjacent. Between the head 51 of the pressure screw 49 and the plane On the side of the washer 53, which is designed as a hemisphere, an element 54 is inserted, which is elastic at least in the axial direction and is designed as a cylinder with mutually parallel end faces. For example, this element 54 can be designed in the form of a rubber cylinder or a package of spring washers.
  • the axially directed elastic force of the elastic member 54 acts between the head 51 of the Anpressschraube 49 and the ball bearing support 43 in such a direction that the ball bearing support 43 and thus also of the race 40 is pressed to 'counter-pressure surface.
  • the pressure screw 49 can be used in an inverted position, the head of the pressure screw 49 lies in the slide 4, while a screw nut is screwed onto the body of the pressure screw 49 after the washer 53 and the elastic element 54.
  • this bore 65 for receiving and holding the (not shown) axis of the ball bearing 41 for the race 40. So that the race 40 rolls on the counter pressure surface, this bore 65 and its axis are arranged parallel to the counter pressure surface.
  • the axes of the threaded bores 60, 61 of the ball bearing carrier 43 are parallel to one another, to the axis of the bore 65 (and thus also to the axis of the race 40, as well as to the relevant counter pressure surface on which the Race 40 rolls) orthogonally, and arranged symmetrically to the plane of symmetry 66 of the race 40.
  • These axes of the two adjusting screws are thus arranged in the projection plane of FIG. 7b at the corner points of the base of an isosceles triangle, the third corner point of which is the orthogonal projection 67 of the center of the race 40 on the same projection plane of FIG. 7b is.
  • the axis of the pressure screw 49 lies parallel to the axes of the threaded bores 60, 61 and therefore also to the axes of the two adjusting screws.
  • This 7b essentially intersects the axis of the pressure screw 49 in FIG. 7b in the center 68 of the (not shown) circumference of the isosceles triangle corresponding to the axes of the threaded bores 60, 61 and the orthogonal projection 67 of the center of the race 40, ie it lies in the plane of symmetry 66 of the race 40 at the same distance from the two other axes and to the center of the contact point of the race 40 with the counter pressure surface (whose projection onto the projection plane of FIG. 7 b yes coincides with the projection 67 of the center of the race 40).
  • the axis of the threaded bore 63 (and thus also the axis of the adjusting screw used therein) is arranged parallel to the counter pressure surface and normal to the plane of symmetry 66, i.e. it lies parallel to the projection plane of FIG. 6b and to the axis of the bore 65 (and thus also to the axis of the Race 40).
  • This axis of the threaded hole 63 is closer to the center 68 than the axes of the threaded holes 60 and 61, i. H.
  • this axis of the threaded bore 63 intersects the plane of symmetry 66 between the center 68 and the corner points of the base of the isosceles triangle lying on the plane of symmetry 66, the third corner point of which projects the projection 67 of the center of the race 40 on the same projection plane of FIG 7b is.
  • a threaded bore 59 which is essentially parallel to the threaded bore 63 and into which a counter screw (not shown) is screwed, the tip of which bears against the ball bearing carrier 43, is arranged on the slide. Tightening this counter screw acts counter to tightening the adjusting screw inserted in the threaded bore 63.
  • the pressure screw 49 allows the ball bearing carrier 43 to be tilted by adjusting the adjusting screws in the threaded bores 60, 61 and the rotation of the ball bearing carrier 43 by adjusting the adjusting screw and the counter screw in the threaded bores 63 and 59.
  • the system behaves as if the contact screw 49 were always a slightly tightened fastening screw .
  • the adjusting screws seated in the threaded bores 60, 61 are pressed against the slide 4 and the race 40 against the counter pressure surface, so that the position of the ball bearing carrier 42 according to the tripod principle is fixed and also the opposite race arranged on the ball bearing carrier 42 40 is constantly tightened or pressed against its corresponding guide surface.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)

Abstract

Le socle présente un axe de symétrie vertical et au centre de sa face inférieure un affaissement dans lequel débouchent un canal d'admission d'air comprimé et un canal d'évacuation d'air conduisant à une buse de régulation de pression. Le socle porte un montant (20) vertical à profil en forme de T double portant une colonne de profilé carré pour un chariot (4) muni d'un palpeur (5). Des bandes (9, 10) de traction passant sur des renvois sont reliées au chariot (4) et à un contrepoids. Le montant (20) porte un support sur lequel se trouve un organe de fixation réglable et blocable qui constitue un palier à glissement pour l'extrémité supérieure de la colonne. Au moins la colonne (22) pour le chariot (4) repose sur le socle par l'intermédiaire d'une articulation à rotule. Les galets de roulement (40) du chariot sont retenus dans des paliers à roulements à billes, les uns étant réglables et pouvant être bloqués en direction de roulement, de roulis et de tangage, les autres étant mobiles en direction de roulement, de roulis et de tangage et rappelés élastiquement vers la colonne (22). Ainsi, seules deux faces voisines de la colonne doivent être d'une grande précision.
PCT/CH1987/000127 1986-10-03 1987-09-30 Instrument pour mesurer la hauteur WO1988002471A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH395686 1986-10-03
CH3956/86-4 1986-10-03

Publications (1)

Publication Number Publication Date
WO1988002471A1 true WO1988002471A1 (fr) 1988-04-07

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PCT/CH1987/000127 WO1988002471A1 (fr) 1986-10-03 1987-09-30 Instrument pour mesurer la hauteur

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989009921A1 (fr) * 1988-04-08 1989-10-19 L.K. Tool Company Limited Appareil de commande d'elements dans des machines de mesure
EP0346272A1 (fr) * 1988-06-07 1989-12-13 Hans Meyer Dispositif pour mesurer une longueur
EP0579961A1 (fr) * 1992-07-16 1994-01-26 Tesa Brown & Sharpe S.A. Appareil de mesure de grandeurs linéaires
CN110926304A (zh) * 2020-01-03 2020-03-27 洛阳Lyc轴承有限公司 一种特大型阶梯轴环/中小型调心滚子轴承检测装置
US11035658B2 (en) 2017-04-19 2021-06-15 Renishaw Plc Positioning apparatus
US11060836B2 (en) 2017-04-19 2021-07-13 Renishaw Plc Bearing arrangement
US11236987B2 (en) 2017-04-19 2022-02-01 Renishaw Plc Load bearing structure

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3460263A (en) * 1968-02-28 1969-08-12 Pipe Machinery Co The Gauge and sliding supports therefor
US3639993A (en) * 1970-02-09 1972-02-08 Dea Spa Improvements relating to machines and apparatus having a support for guiding a movable member
GB1290855A (fr) * 1969-04-26 1972-09-27
FR2201756A5 (fr) * 1972-09-29 1974-04-26 Balea Georges
FR2207845A1 (fr) * 1972-11-30 1974-06-21 Auriol Et Cie Hte Garonn
GB1452280A (en) * 1973-03-02 1976-10-13 British United Shoe Machinery Measuring machines

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3460263A (en) * 1968-02-28 1969-08-12 Pipe Machinery Co The Gauge and sliding supports therefor
GB1290855A (fr) * 1969-04-26 1972-09-27
US3639993A (en) * 1970-02-09 1972-02-08 Dea Spa Improvements relating to machines and apparatus having a support for guiding a movable member
FR2201756A5 (fr) * 1972-09-29 1974-04-26 Balea Georges
FR2207845A1 (fr) * 1972-11-30 1974-06-21 Auriol Et Cie Hte Garonn
GB1452280A (en) * 1973-03-02 1976-10-13 British United Shoe Machinery Measuring machines

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989009921A1 (fr) * 1988-04-08 1989-10-19 L.K. Tool Company Limited Appareil de commande d'elements dans des machines de mesure
EP0346272A1 (fr) * 1988-06-07 1989-12-13 Hans Meyer Dispositif pour mesurer une longueur
US4972603A (en) * 1988-06-07 1990-11-27 Hans Meyer Linear measuring device
EP0579961A1 (fr) * 1992-07-16 1994-01-26 Tesa Brown & Sharpe S.A. Appareil de mesure de grandeurs linéaires
US11035658B2 (en) 2017-04-19 2021-06-15 Renishaw Plc Positioning apparatus
US11060836B2 (en) 2017-04-19 2021-07-13 Renishaw Plc Bearing arrangement
US11236987B2 (en) 2017-04-19 2022-02-01 Renishaw Plc Load bearing structure
CN110926304A (zh) * 2020-01-03 2020-03-27 洛阳Lyc轴承有限公司 一种特大型阶梯轴环/中小型调心滚子轴承检测装置

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