EP3637201A1 - Vorrichtung und verfahren zum messen des drehmomentes einer spiralfeder - Google Patents

Vorrichtung und verfahren zum messen des drehmomentes einer spiralfeder Download PDF

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Publication number
EP3637201A1
EP3637201A1 EP18200169.3A EP18200169A EP3637201A1 EP 3637201 A1 EP3637201 A1 EP 3637201A1 EP 18200169 A EP18200169 A EP 18200169A EP 3637201 A1 EP3637201 A1 EP 3637201A1
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EP
European Patent Office
Prior art keywords
distal portion
shaft
ferrule
clamping ring
movable clamping
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP18200169.3A
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English (en)
French (fr)
Inventor
Marcel Gerber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Greiner Vibrograf AG
Original Assignee
Greiner Vibrograf AG
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 Greiner Vibrograf AG filed Critical Greiner Vibrograf AG
Priority to EP18200169.3A priority Critical patent/EP3637201A1/de
Publication of EP3637201A1 publication Critical patent/EP3637201A1/de
Withdrawn legal-status Critical Current

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    • G—PHYSICS
    • G04—HOROLOGY
    • G04D—APPARATUS OR TOOLS SPECIALLY DESIGNED FOR MAKING OR MAINTAINING CLOCKS OR WATCHES
    • G04D7/00—Measuring, counting, calibrating, testing or regulating apparatus
    • G04D7/10—Measuring, counting, calibrating, testing or regulating apparatus for hairsprings of balances

Definitions

  • the present invention relates generally to a device and a method for measuring the torque of a balance spring for balance-spring oscillator.
  • the geometric inaccuracies and dispersions of the process for manufacturing a balance spring although small, typically generate a dispersion of the couple of balance springs relative to a target value. This is observed for all types of hairsprings, whether they are made from metal alloy wires (for example the Invar®, Elinvar®, Nivarox® or Parachrom® alloys), from silicon by photolithographic processes, or other materials and / or processes.
  • metal alloy wires for example the Invar®, Elinvar®, Nivarox® or Parachrom® alloys
  • the operating precision required of a balance-spring oscillator is typically of the order of a few seconds per day.
  • the oscillation frequency of the balance-spring oscillators can be adjusted by various means, such as adjustable nuts or weights in order to modify the inertia of the balance.
  • the adjustment range is typically a hundred seconds per day, which is insufficient to obtain a precise walk by arbitrarily associating a balance and a hairspring.
  • a pairing, or pairing, between pendulum and balance spring is thus typically carried out, which requires being able to measure the characteristics of the balance spring and / or of the balance before associating them.
  • the natural frequency of the mechanical oscillating system of a timepiece is a function of the couple of the balance spring and the moment of inertia of the oscillating system, which can at first be considered as equal to the moment of inertia of the pendulum.
  • These torque measurements can be used either to adjust the frequency of the balance-spring assembly by modifying the inertia of the balance by selective removal of material (for example by means of a cutter or a laser) or by adjusting the length of the balance spring, that is to distribute the balance springs and balance wheels by classes according to the couple of balance springs and the inertia of the balance wheels in order to allow the aforementioned pairing.
  • European patent application No. EP 2,423,764 A1 describes a device and a method for measuring the torque of a balance spring for a balance-spring oscillator, which are particularly advantageous insofar as it is possible to measure the torque of the balance spring fitted at the center of its shell. More specifically, the device described in this patent application comprises a shaft configured to be selectively coupled to or decoupled from a ferrule secured to an internal end of the hairspring, the shaft having a distal portion configured to cooperate with the ferrule. The distal portion of the shaft is elastically deformable and configured to be insertable through an axial opening passing through the ferrule.
  • the device also comprises a support configured to support the shaft in a pivoting manner, a reference balance associated with the tree, a gripping system to keep an outer end of the hairspring fixed during the measurement, and a clamping element. configured to selectively cooperate with the distal portion of the shaft and exert a radial clamping action on the distal portion.
  • the distal portion of the shaft is provided with a coupling section having a nominal external diameter greater than the internal diameter of the axial opening of the ferrule, which coupling section provides a friction drive connection between the distal portion of the tree and the ferrule.
  • the distal portion of the tree is also configured to allow a temporary reduction in the external diameter of the coupling section, under the radial clamping action exerted by the clamping element, and the frictionless insertion of the coupling section through the axial opening of the ferrule.
  • the clamping element consists of a clamp gripping acting radially on either side of the split part.
  • This solution has various drawbacks, in particular with regard to the precision required to ensure the radial clamping action necessary for the temporary reduction of the external diameter of the coupling section and its insertion without friction through the axial opening of the ferrule. Any inaccuracy in the tightening is likely to cause interference during the insertion of the distal portion of the shaft into the axial opening of the ferrule, or even damage the distal portion of the shaft.
  • a general aim of the present invention is therefore to propose an improved device and method for measuring the torque of a balance spring for a balance-spring oscillator.
  • an object of the present invention is to propose such a solution which is more robust and more reliable in use.
  • an object of the present invention is to propose a solution which facilitates the automation of the coupling and decoupling process from the shaft of the device to the shell of the hairspring.
  • Another object of the present invention is to propose such a solution which ensures an accurate and repeatable measurement of the balance spring torque.
  • the present invention meets these goals by proposing a device for measuring the torque of a balance spring for a balance-spring oscillator, the characteristics of which are listed in claim 1, namely such a device comprising a shaft configured to be selectively coupled to or decoupled. a ferrule secured to an internal end of the hairspring, the shaft having a distal portion configured to cooperate with the ferrule, the distal portion of the shaft being elastically deformable and configured to be insertable without friction through an axial opening crossing the ferrule.
  • the device also comprises a support configured to support the shaft in a pivoting manner, a reference balance associated with the shaft, a gripping system to keep an external end of the hairspring fixed during the measurement, and a clamping element.
  • the clamping element is configured as a movable clamping ring provided with a through hole configured to receive the distal portion of the shaft and allow the movable clamping ring to be moved axially along of the distal portion of the tree.
  • the movable clamping ring is axially movable relative to the distal portion of the shaft and to the ferrule between a first axial position in which the movable clamping ring can cooperate with the distal portion and exert the action.
  • the shaft and the movable clamping ring are both placed on the same side of the hairspring, the movable clamping ring preferably being positioned permanently on the distal portion of the tree.
  • the distal portion of the shaft may in particular have at least one additional section having a nominal external diameter less than the internal diameter of the orifice passing through the movable clamping ring, the first axial position being a position in which the movable clamping ring is positioned on the coupling section and exerts the radial clamping action of the distal portion, while the second axial position is a position in which the movable clamping ring is positioned on the section additional and frees the distal portion.
  • the above-mentioned coupling section and additional section are preferably substantially cylindrical sections of different external diameters, the additional section having an axial length greater than an axial length of the movable clamping ring.
  • a shoulder between the coupling section and the additional section can advantageously be chamfered, this in order to facilitate the insertion of the coupling section through the through hole of the movable clamping ring during the passage of the second axial position to the first axial position.
  • the coupling section can advantageously be placed in the end position at the end of the distal portion of the shaft.
  • the shaft and the movable clamping ring are placed on either side of the hairspring, and the movable clamping ring is configured to be completely disengaged from the distal portion of the tree.
  • the distal portion may in particular have at least one additional section placed in the end position at the end of the distal portion of the shaft, which additional section has a nominal external diameter greater than the internal diameter of the orifice. through the movable clamping ring, the nominal external diameter of the additional section also being less than the internal diameter of the axial opening of the ferrule, thus allowing frictionless insertion of the additional section through the opening axial of the ferrule.
  • the first axial position is in this case a position in which the movable clamping ring is positioned to cooperate with the additional section and exert the radial clamping action of the distal portion, while the second axial position is a position in which the movable clamping ring is completely disengaged from the distal portion.
  • the above-mentioned coupling section and additional section are preferably substantially cylindrical sections of different external diameters, the additional section having an axial length sufficient to be insertable through the axial opening of the ferrule and to cooperate with the movable clamping ring. , in the first axial position.
  • a distal end of the above-mentioned additional section is preferably chamfered, this in order to facilitate the insertion of the additional section through the orifice passing through the movable clamping ring.
  • the distal portion of the shaft has a split part, which split part is configured to be insertable through the axial opening passing through the ferrule, the split part being preferably provided with at least a longitudinal slot extending substantially axially along the distal portion of the shaft.
  • the distal portion of the shaft may in particular comprise a tip, preferably removable, made integral with the tree.
  • the pivot axis of the shaft is substantially vertical and the support comprises at least a first bearing supporting a lower end of the shaft, the support preferably comprising a second bearing supporting a part median of the shaft, and the gripping system comprises a fixed part and a spiral gripping support movable horizontally relative to the fixed part and configured to engage with the external end of the spiral.
  • the device further comprises a first drive for ensuring a relative axial movement between the gripping system and the distal portion of the shaft and / or a second drive for ensuring the axial movement of the movable clamping ring.
  • the Figure 1 shows a cross-sectional view of a torque measuring device - device generally designated by the reference numeral 10 - of a hairspring 20 according to a first alternative embodiment of the present invention.
  • This device 10 comprises a shaft 1 configured to be selectively coupled to or decoupled from a ferrule 25 secured to an internal end of the hairspring 20.
  • a distal portion 1a of the shaft 1 is configured to cooperate with the ferrule 25, the distal portion 1a of the shaft 1 being elastically deformable and configured to be insertable without friction through an axial opening 25a passing through the ferrule 25.
  • the distal portion 1a of the shaft 1 has a slotted part 4, which slotted part 4 is configured to be insertable through the axial opening 25a passing through the ferrule 25.
  • This slotted part 4 can in particular be provided at least one longitudinal slot 4a extending substantially axially along the distal portion 1a of the shaft 1, as illustrated schematically in the Figure 1 .
  • the distal portion 1a of the shaft 1 may advantageously include an end piece, here forming the slotted part 4, which end piece is made integral with the shaft 1.
  • This end piece is ideally designed to be removable and, if necessary, to adapt the distal portion 1a of the shaft 1 with the specific geometry and dimensions of the shell 25.
  • the device 10 also comprises a support 2 configured to support the shaft 1 in a pivoting manner, a reference balance 3 associated with the shaft 1 (for example a flywheel or any other reference element whose moment of inertia is known), a gripping system 7, 8 for holding an outer end of the hairspring 20 fixed during the measurement, as well as a clamping element 5 configured to cooperate selectively with the distal portion 1a of the shaft 1 and exert a radial clamping action on the distal portion 1a, as will be described more fully below.
  • a support 2 configured to support the shaft 1 in a pivoting manner
  • a reference balance 3 associated with the shaft 1 for example a flywheel or any other reference element whose moment of inertia is known
  • a gripping system 7, 8 for holding an outer end of the hairspring 20 fixed during the measurement
  • a clamping element 5 configured to cooperate selectively with the distal portion 1a of the shaft 1 and exert a radial clamping action on the distal portion 1a, as will be described more fully below.
  • the support 2 is designed to support the shaft 1 in a vertical position so that the pivot axis of the shaft 1 is substantially vertical.
  • the support 2 preferably comprises a first bearing 2a supporting a lower end of the shaft 1 and a second bearing 2b supporting a middle part of the shaft 1.
  • the reference balance 3 is here disposed on the shaft 1 so as to be positioned between the two support points formed by the bearings 2a and 2b.
  • the gripping system 7, 8 preferably comprises a fixed part 8 and a gripping support for hairspring 7 movable horizontally relative to the fixed part 8 and configured to engage with the external end of hairspring 20. It will be understood therefore, during a measurement of the torque of the hairspring 20, the external end of the hairspring 20 is retained fixed by the gripping system 7, 8.
  • the distal portion 1a of the shaft 1 is in turn designed to come into taken with the ferrule 25 which is integral with the internal end of the hairspring 20.
  • the distal portion 1a of the shaft 1 is more particularly provided with a coupling section 4.1, which has a nominal external diameter, designated D1, which is greater than the internal diameter, designated D25, of the axial opening 25a of the ferrule 25.
  • This coupling section 4.1 is intended to provide a friction drive connection between the distal portion 1a of the shaft 1 and the ferrule 25.
  • the distal portion 1a of the shaft 1 is configured to allow a temporary reduction in the external diameter of the coupling section 4.1, under the radial clamping action exerted by the clamping element 5, and the insertion without friction of the coupling section 4.1 through the axial opening 25a of the ferrule 25.
  • the clamping element is configured as a movable clamping ring 5 provided with a through orifice 5a configured to receive the distal portion 1a of the shaft 1 and allow the movable clamping ring 5 to be moved axially along the distal portion 1a of the shaft 1, as will be discussed more precisely with reference to Figures 2 to 4 .
  • the through hole 5a of the movable clamping ring 5 therefore has an internal diameter, designated D5, which is less than the internal diameter D25 of the axial opening 25a of the ferrule 25.
  • the mobile clamping ring 5 is axially displaceable relative to the distal portion 1a of the shaft 1 and to the ferrule 25 between a first axial position, designated P1, in which the movable clamping ring 5 can cooperate with the distal portion 1a (see in particular the Figure 2 ) and exert the radial clamping action of the distal portion 1a, allowing the frictionless insertion of the coupling section 4.1 through the axial opening 25a of the ferrule 25 (see the Figure 3 ), and at least a second axial position, designated P2, in which the movable clamping ring 5 releases the distal portion 1a, allowing the establishment of the friction drive connection between the coupling section 4.1 and the ferrule 25 (see it Figure 4 ).
  • the device 10 is illustrated in the Figure 1 in a first configuration where the distal portion 1a of the shaft 1 of the device 10 is decoupled from the shell 25 of the hairspring 20, and where the movable clamping ring 5 occupies the second position P2 mentioned above. This is a position at rest where the movable clamping ring 5 exerts no stress on the distal portion 1a of the shaft 1.
  • the shaft 1 and the movable clamping ring 5 are both placed on the same side of the hairspring 20.
  • the movable clamping ring 5 is preferably permanently positioned on the distal portion 1a of the shaft 1. A total disengagement of the movable clamping ring 5 from the distal portion 1a of the shaft 1 is not necessary here, except for the needs of a possible change of the end piece 4.
  • the distal portion 1a of the shaft 1 has at least one additional section 4.2 having a nominal external diameter, designated D2, which is less than the internal diameter D5 of the through orifice 5a of the movable clamping ring 5.
  • the first axial position P1 is, as illustrated in the Figure 2 , a position in which the movable clamping ring 5 is positioned on the coupling section 4.1 in order to exert the radial clamping action of the distal portion 1a and allow the frictionless insertion of the coupling section 4.1 through of the axial opening 25a of the ferrule 25, as illustrated in the Figure 3 .
  • the second axial position P2 is, as illustrated in the Figure 4 , a position in which the movable clamping ring 5 is positioned on the additional section 4.2 in order to release the distal portion 1a and thus establish the friction drive connection between the coupling section 4.1 and the ferrule 25.
  • the coupling section 4.1 and the additional section 4.2 are advantageously substantially cylindrical sections of different external diameters D1, D2, the additional section 4.2 having an axial length L2 greater than an axial length, designated L5, of the movable clamping ring 5 More precisely, the axial length L2 of the additional section 4.2 is chosen so as to be able to receive the mobile clamping ring 5 entirely, as illustrated in the Figures 1 and 4 .
  • the axial length L1 of the coupling section 4.1 is itself selected to allow the engagement of the distal section 1a of the shaft 1 through the axial opening 25a of the ferrule 25 while ensuring that the ring of movable clamping 5 remains in engagement with the coupling section 4.1, in the first axial position P1, as illustrated in Figure 3 .
  • the axial length L1 will therefore depend on the axial length L5 of the movable clamping ring 5 and the distance separating it, in the first axial position P1, from the ferrule 25. It is only after the coupling section 4.1 is inserted in the desired position that the movable clamping ring 5 can be repositioned in the second axial position P2, as illustrated in Figure 4 , in order to free the distal portion 1a from the shaft 1 and thus allow the establishment of a friction drive connection between the coupling section 4.1 and the ferrule 25.
  • the coupling section 4.1 is advantageously placed in the end position at the end of the distal portion 1a of the shaft 1.
  • the coupling section 4.1 is exclusively used for the coupling with the ferrule 25, and provide an additional section, below the additional section 4.2, intended exclusively for the clamping operation by means of the movable clamping ring 5.
  • the diameter D5 of the through opening 5a formed through the movable clamping ring 5 is strictly less than the diameter D25 of the axial opening 25a of the ferrule 25.
  • the diameter D5 of the through opening 5a and the diameter of the additional section are chosen to allow a radial clamping action to be exerted on the distal portion 1a of the shaft 1, and therefore on the coupling section 4.1.
  • the coupling section 4.1 would possibly be preceded by a section of smaller diameter than the internal diameter D25 of the axial opening 25a of the ferrule 25.
  • the shoulder 4.1a between the coupling section 4.1 and the additional section 4.2 is chamfered in order to facilitate the insertion of the coupling section 4.1 through the through hole 5a of the movable clamping ring 5 during the passage from the second axial position P2 to the first axial position P1.
  • the transition surface between the coupling section 4.1 and the additional section 4.2 can be essentially conical.
  • the distal end of the coupling section 4.1 can likewise be chamfered to facilitate the insertion of the coupling section 4.1 through the through hole 5a of the movable clamping ring 5 during the assembly or reassembly of the device 10.
  • the movable clamping ring 5 is preferably mounted so as to be permanently positioned on the distal portion 1a of the shaft 1.
  • the Figure 5 shows a cross-sectional view of a torque measuring device - device generally designated by the reference numeral 10 * - of a hairspring 20 according to a second variant embodiment of the present invention.
  • This device 10 * likewise comprises a shaft 1 * configured to be selectively coupled to or decoupled from a ferrule 25 integral with an internal end of the hairspring 20, a support 2 configured to support the shaft 1 * in a pivoting manner, a reference balance 3 associated with the shaft 1 *, a gripping system 7, 8 for holding an outer end of the hairspring 20 fixed during the measurement, as well as a movable clamping ring 5 * forming a clamping element configured for selectively cooperate with the distal portion 1a * of the shaft 1 * and exert a radial clamping action on the distal portion 1a *.
  • the distal portion 1a * of the shaft 1 * likewise advantageously comprises a tip 4 *, preferably removable, forming a split part, which tip 4 * is made integral with the shaft 1 * in the image of what
  • the distal portion 1a * of the shaft 1 * is provided, like the first alternative embodiment, with a coupling section 4.1 *, which has a nominal external diameter, designated D1 *, which is greater than the diameter internal D25 of the axial opening 25a of the ferrule 25.
  • This coupling section 4.1 * is similarly intended to provide a friction drive connection between the distal portion 1a * of the shaft 1 * and the ferrule 25.
  • the distal portion 1a * of the shaft 1 * is also configured to allow a temporary reduction of the external diameter of the coupling section 4.1 *, under the radial clamping action exerted by the movable clamping ring 5 *, and l insertion without friction of the coupling section 4.1 * through the axial opening 25a of the ferrule 25.
  • the mobile clamping ring 5 * is provided with a through hole 5a configured to receive the distal portion 1a * of the shaft 1 * and allow the movable clamping ring 5 * to be moved axially along the distal portion 1a * of the shaft 1 *, as will be discussed more specifically with reference to Figures 6 to 8 .
  • the internal diameter D5 of the through orifice 5a of the movable clamping ring 5 * is therefore less than the internal diameter D25 of the axial opening 25a of the ferrule 25.
  • the mobile clamping ring 5 * is similarly axially displaceable relative to the distal portion 1a * of the shaft 1 * and to the ferrule 25 between a first axial position, designated P1 *, in which the mobile clamping ring 5 * can cooperate with the distal portion 1a * (see in particular the Figure 6 ) and exert the radial tightening action of the distal portion 1a *, allowing the frictionless insertion of the coupling section 4.1 * through the axial opening 25a of the ferrule 25 (see the Figure 7 ), and at least a second axial position, designated P2 *, in which the movable clamping ring 5 * releases the distal portion 1a *, allowing the establishment of the friction drive connection between the coupling section 4.1 * and shell 25 (see the Figure 8 ).
  • the device 10 * is illustrated in the Figure 5 in a first configuration where the distal portion 1a * of the shaft 1 * of the device 10 * is decoupled from the ferrule 25 of the hairspring 20, and where the movable clamping ring 5 * occupies a position where it is completely disengaged from the distal portion 1a * of the shaft 1 *.
  • the shaft 1 * and the movable clamping ring 5 * are placed on either side of the hairspring 20.
  • the movable clamping ring 5 * is therefore necessarily configured, in this case, to be completely disengaged from the distal portion 1a * of the shaft 1 *.
  • the distal portion 1a * of the shaft 1 * has at least one additional section 4.2 * placed in the end position at the end of the distal portion 1a * of the shaft 1 *, which additional section 4.2 * has a diameter nominal external, designated D2 *, which is greater than the internal diameter D5 of the through orifice 5a of the movable clamping ring 5 *.
  • This nominal external diameter D2 * is moreover less than the internal diameter D25 of the axial opening 25a of the shell 25, thus allowing the frictionless insertion of the additional section 4.2 * through the axial opening 25a of the shell 25 , and this independently of the clamping action exerted by the movable clamping ring 5 *.
  • the first axial position P1 * is, as illustrated in the Figures 5 to 7 , a position in which the movable clamping ring 5 * is positioned to cooperate with the additional section 4.2 * and exert the radial clamping action of the distal portion 1a *, allowing the insertion without friction of the coupling section 4.1 * through the axial opening 25a of the shell 25, as illustrated more specifically in the Figure 7 .
  • the second axial position P2 * is itself, as illustrated in the Figure 8 , a position in which the movable clamping ring 5 * is completely disengaged from the distal portion 1a * in order to release the distal portion 1a * and establish the friction drive connection between the coupling section 4.1 * and the ferrule 25 .
  • the coupling section 4.1 * and the additional section 4.2 * are advantageously substantially cylindrical sections with different external diameters D1 *, D2 *.
  • the axial length L1 * of the coupling section 4.1 * must be sufficient to ensure the friction drive connection with the ferrule 25.
  • the axial length L2 * of the additional section 4.2 * is itself selected to allow frictionless insertion of the additional section 4.2 * through the axial opening 25a of the ferrule 25 and to cooperate with the movable clamping ring 5 *, positioned in its first axial position P1 *, before the coupling section 4.1 * ends at the ferrule 25, as illustrated in the Figure 6 .
  • the distal end 4.2a * of the additional section 4.2 * is chamfered in order to facilitate the insertion of the additional section 4.2 * through the through orifice 5a of the movable clamping ring 5 *.
  • a relative axial displacement is operated between the gripping system 7, 8 and the distal portion 1a, resp. 1a * of tree 1, resp. 1 *.
  • this relative displacement can be operated by hand, it may be advantageous to provide a first drive to ensure this relative displacement. It may likewise be advantageous to provide a second drive to ensure the axial displacement of the movable clamping ring 5, resp. 5 *.
  • the presence of such drives will in particular allow great automation of the process, and therefore greater robustness in use and better repeatability of the measurements.
  • the method of measuring the torque of a balance spring to be qualified can be implemented using the aforementioned device 10 or 10 *, and this in the following manner.
  • the hairspring to be measured 20 is positioned on the gripping system 7, 8 of the device 10, resp. 10 *, then the outer end of the hairspring 20 is fixed using the gripping system 7, 8.
  • the movable clamping ring 5, resp. 5 * is then positioned relative to the distal portion 1a, resp. 1a *, from tree 1, resp. 1 *, and to the shell 25 so as to occupy the first axial position P1, resp. P1 * (see again Figure 2 or Figure 5 ) and allow the radial clamping action of the distal portion 1a, resp. 1a *.
  • this is achieved as soon as the movable clamping ring 5 is placed in its first axial position P1.
  • the coupling section 4.1, resp. 4.1 * can be inserted through the axial opening 25a of the ferrule 25.
  • the movable clamping ring 5, resp. 5 * is repositioned towards the second axial position P2, resp. P2 *, so as to release the distal portion 1a, resp. 1a *, and thus establish the friction drive link between the coupling section 4.1, resp. 4.1 *, and the shell 25.
  • the actual torque measurement operation can then begin, which involves the release of the shaft 1, resp. 1 *, so as to be able to pivot about its pivot axis, the oscillation of the assembly formed by the shaft 1, resp. 1 *, reference pendulum 3 and hairspring 20, and the measurement of the resulting oscillation of said assembly.
  • This measurement can in particular consist of a measurement of the oscillation frequency which, taking into account the fact that the moment of inertia of the reference balance 3 is known, makes it possible to deduce a measurement of the torque of the balance spring 20. It is obviously it is understood that a measurement of the oscillation period will likewise make it possible to derive the oscillation frequency, and consequently to deduce a measurement of the torque of the hairspring 20.
  • the process ends with the repositioning of the movable clamping ring 5, resp. 5 *, relative to the distal portion 1a, resp. 1a *, and at the ferrule 25 towards the first axial position P1, resp. P1 *, so as to exert again the radial clamping action of the distal portion 1a, resp. 1a *, and remove the friction drive link between the coupling section 4.1, resp. 4.1 *, and the ferrule 25.
  • the process can then be repeated with another hairspring to be measured and qualified.
  • the support for the shaft of the device in any suitable manner making it possible to ensure that the shaft is pivotally supported.
  • the hairspring gripping system can likewise be configured in any suitable manner making it possible to fix an external end of the hairspring during the measurement.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Pivots And Pivotal Connections (AREA)
EP18200169.3A 2018-10-12 2018-10-12 Vorrichtung und verfahren zum messen des drehmomentes einer spiralfeder Withdrawn EP3637201A1 (de)

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EP18200169.3A EP3637201A1 (de) 2018-10-12 2018-10-12 Vorrichtung und verfahren zum messen des drehmomentes einer spiralfeder

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2384520A (en) 1944-04-17 1945-09-11 Sheffield Corp Spring gauging device
CH483050A (de) 1966-09-15 1969-08-29 Straumann Inst Ag Einrichtung zur elektrischen Messung des Kraftmomentes von abgelängten Spiralfedern und des Trägheitsmomentes von Unruhen
JPS58146980U (ja) * 1982-03-30 1983-10-03 稲毛　邦善 分針歯車のスリツプ装置
CH690874A5 (de) 1996-05-10 2001-02-15 Witschi Electronic Ag Verfahren zum dynamischen Auswuchten und Abgleichen eines mechanischen Schwingsystem.
EP2128723A1 (de) 2008-05-27 2009-12-02 Sigatec SA Verfahren zur Herstellung oder Zusammensetzung eines Oszillators und nach diesem Verfahren hergestellter Oszillator
EP2423764A1 (de) 2010-08-31 2012-02-29 Rolex S.A. Vorrichtung zum Messen des Drehmomentes einer Spirale
CN106568658A (zh) * 2016-11-01 2017-04-19 西安交通大学 一种微纳尺度下材料扭转拉伸不同性能的测试装置及方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2384520A (en) 1944-04-17 1945-09-11 Sheffield Corp Spring gauging device
CH483050A (de) 1966-09-15 1969-08-29 Straumann Inst Ag Einrichtung zur elektrischen Messung des Kraftmomentes von abgelängten Spiralfedern und des Trägheitsmomentes von Unruhen
JPS58146980U (ja) * 1982-03-30 1983-10-03 稲毛　邦善 分針歯車のスリツプ装置
CH690874A5 (de) 1996-05-10 2001-02-15 Witschi Electronic Ag Verfahren zum dynamischen Auswuchten und Abgleichen eines mechanischen Schwingsystem.
EP2128723A1 (de) 2008-05-27 2009-12-02 Sigatec SA Verfahren zur Herstellung oder Zusammensetzung eines Oszillators und nach diesem Verfahren hergestellter Oszillator
EP2423764A1 (de) 2010-08-31 2012-02-29 Rolex S.A. Vorrichtung zum Messen des Drehmomentes einer Spirale
CN106568658A (zh) * 2016-11-01 2017-04-19 西安交通大学 一种微纳尺度下材料扭转拉伸不同性能的测试装置及方法

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