• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to an anchor escapement for a mechanical timepiece, comprising a pivotable armature with armature pallets (2, 2 ') and an armature wheel (4) which can be acted upon by a torque and which have approximately radially outwardly directed teeth (5, 5', 5 '') over its outer circumference having. The front flanks of the pallets (2, 2 ') are designed so that they always engage with the same contact surface at each contact with the front edge of the teeth (5, 5', 5 ") of the wheel (4) ,
    公开号:CH710169A2
    申请号:CH01837/14
    申请日:2014-11-28
    公开日:2016-03-31
    发明作者:Peter Gluche；Ralph Gretzschel
    申请人:Gfd Ges Für Diamantprodukte Mbh；
    IPC主号:
    专利说明:

    The invention relates to an anchor escapement for a mechanical timepiece comprising a pivotable armature with anchor pallets and an acted upon by a torque escape wheel, which has about its outer circumference approximately radially outwardly directed teeth. The front flanks of the pallets are designed so that they are always with each contact, with the front edge of the teeth of the wheel, with the same contact surface engaged.
    The inhibition of a clock is that assembly in gear wheels, which establishes the connection between the gear train and the gear regulator. It usually consists of the escape wheel and the anchor the anchor. The gear regulator causes via the engaging in the escape wheel inhibitor the periodic stopping (inhibiting) of the gear train and thus the regular course of the clock.
    Various inhibitions have been proposed in the prior art. In the meantime, practically all mechanical watches are equipped with the same type, namely the so-called "Swiss lever escapement". In a "Swiss lever escapement", the two arms of the anchor each comprise an anchor stone (pallet), which usually consists of ruby, sapphire or garnet. These anchor stones are either used in the two arms of the anchor or made in micro-engineered anchors so made of silicon or diamond in one piece together with the anchor. The anchor stones take turns in each case one tooth of the escape wheel and hold it so tight.Anchor wheel and armature are then at rest to be accelerated again immediately at the zero crossing of the balance. Each time the balance passes the zero position in one direction or the other, it engages over the so-called lever stone in the anchor fork. As a result, the anchor releases a tooth of the escapement wheel via its respective pallet, which thus advances briefly and returns a tiny fraction of energy across the armature to the lever block and thus the balance. In the power transmission between the teeth of the escape wheel and the pallets of the armature, these two parts move under pressure against each other. At the beginning of the movement, a pallet is applied to a surface of an armature gear of the so-called resting surface. As the pallet moves against the escape wheel, a frictional force occurs. However, the friction between the pallets and the escapement wheel can affect the accuracy and life of a movement.A typical escape wheel has about 20 teeth on the circumference are distributed equidistantly. The anchor typically 2 pallets. Each turn of the escapement wheel brings each piston tooth into contact with each pallet. Thus, each pallet of the armature undergoes n times (with n = number of teeth of the wheel) wear in comparison to a piston tooth of the escape wheel. In particular, the friction between the teeth of the escape wheel and the pallets of the armature leads to a material removal, so wear on the contact surfaces of pallets and escape wheel, whereby the accuracy can be reduced and the parts in question must be replaced from time to time. This is also the reason why the pallets are made of a harder material, typically ruby.
    The inhibition is about 60% of the energy of the movement to. Especially friction losses as well as the constant acceleration and deceleration of wheel and armature are responsible for the low efficiency. In the past, therefore, attempts have been made to minimize the moment of inertia of the wheel. This was achieved on the one hand by the highest possible degree of skeletonization (removal of all superfluous volume fractions), and on the other hand by realization of a very thin wheel (about 100 microns). As a consequence, the anchor pallets must have a certain minimum thickness (e.g., 200 microns) to still ensure a safe engagement of the wheel in the pallets.
    There has been no lack of attempts to minimize this problem. Thus, it is proposed in FR 1 485 813 to bevel the teeth of escapement wheels to create a contact surface between the teeth and the anchor pallets having a smaller width. Further, in EP 1 622 826 B1 it has been proposed to use other materials, e.g. Use silicon or diamond, which should have advantages over lubricated inhibitions due to higher hardness and lower coefficients of friction. To minimize wear and friction, conventional stainless steel wheel and ruby pallet inhibitors are used for the obligatory oils.
    But the new materials, silicon and diamond have a greater hardness than steel. If these materials are used without lubrication as Hemmbauteile, resulting from this therefore also technical problems. It turns out that the components have a so-called running-in phase. The frictional contact apparently levels micro-roughness on the surface. This reduces the Gleitreibkoeffizient and consequently increases the amplitude of the balance. Usually, before the increase of the amplitude, a drop of the amplitude occurs first, which is incorporated into the surface by the accumulation of foreign bodies (eg abrasion, dust, organic particles, etc.), which are incorporated into the surface similar to the principle of a snow plow due to the existing surface roughness and the coefficient of friction increase. To avoid this effect, according to the state of the art. EP 2 107 434 proposed to design the contact surfaces of the teeth of the gear as small as possible. The same applies to the abrasion, which can also be incorporated on the surface. In the worst case, this effect can even lead to the clock stagnating. To omit this effect, such components in the prior art are usually subjected to a splash lubrication due to phenomenological observations. The remaining, thin film of oil on the surface evaporates with time and allows a nearly constant Unruhamplitude during the break-in phase. For this reason, for example, silicon components are immersed in a gasoline / oil mixture before installation in the movement.
    From studies carried out shows that the phenomenologically observed run-in phase has its cause in the leveling of a microscopic roughness. Since the new materials, in particular diamond have a significantly greater hardness than steel, consequently, a longer run-in phase is observed, since the micro-roughness remaining after processing is leveled out more slowly. In the case of diamond, the wear is even so low that even with very smooth surfaces (for example, 20 nm Rms, square roughness, root-mean-squared roughness), a more than 100-day run-in period is observed. To minimize this, for example, a less hard layer can be additionally applied to the diamond surface (see, for example, EP 2236 455), which ensures that the contacting friction surfaces become smooth more quickly. Despite the use of such layers, the break-in period is still about 40 days. The disadvantage here is that the friction properties change over a longer period of time and thus a reliable and fast control (setting the correct accuracy) of the clock is not possible.
    It is also typical for the use of new materials and microtechnical manufacturing processes that the functional surfaces of the components (the side edges) can never be aligned completely vertically-related to the top and bottom of the component. This is due to the production technology adapted from the semiconductor industry, in which the components are etched out of the plate from a plate (so-called wafer) by means of photolithography and dry etching. As a consequence, the side edges of the armature (in particular the pallets) and escape wheel (in particular the contact surfaces of the piston teeth) can be arranged either plane-parallel or opposite. In the second case arises from the typical structure of the inhibition with a thin wheel and thick anchor pallet that always the wheel has a defined contact surface, as described in EP 2 107 434 B1.
    Under a defined contact surface is understood here a contact surface, which is in contact with each contact of the components. This is due to the non-vertical arrangement in the case of diamond is very small and has the shape of a 2-4 microns wide rectangle. This area is also called geometric contact area A0. This "contact line" engages approximately centrally in the anchor pallet. Depending on the position of the movement, due to the bearing clearance of the individual components, the relative position of armature and wheel changes, so that also shifts the contact surface of the armature relative to the wheel. Usually, therefore, a 30-50 microns wide Verschleisszone on the anchor in the scanning electron microscope is visible. By contrast, the contact zone of the wheel, by definition, is "defined" independently of the relative position of wheel and armature due to the non-vertical arrangement and is always in contact with each other regardless of the relative position of the movement components. For all classic escapements, the anchor pallet has always dominated the running-in phase, so that it was made from the harder material ruby.
    Furthermore, it was found in the investigations that the break-in phase is dominated by the contact surfaces and their nature. Considering the defined, in the form of a rectangle pronounced contact surface of a piston tooth, it is found that only a fraction of the geometric contact surface A0 is actually in frictional contact with the counterpart. This is due to the microscopic nanoscale surface roughness. If one examines the so-called wing portion T of the defined contact area, i. the ratio of actually contacting area AR to the geometric contact area A0so that values of T = 10% -30% can be observed at the beginning of the break-in phase and more than 50% at the start-up phase. Since no further change (wear, erosion) of the contact surfaces could be observed after completion of the break-in period, there is much to suggest that a tribofilm can be formed on the diamond surface from this point onwards, due to the reduction of the sliding friction coefficient and thus the amplitude increase of the watch is.
    In order to obtain the shortest possible Einlaufphase, must therefore be prepared as quickly as possible, a wing portion of the defined contact area of more than 50%. This can be achieved on the one hand via the manufacturing process by reducing the surface roughness, or just by increasing the wear of the defined contact surface.
    The object of the present invention is therefore to propose an anchor escapement, which is significantly improved in relation to the friction and wear between the teeth of the gear and the pallets of the armature over the prior art, so that the accuracy and the life of a Gear train clock can be improved and at the same time can be dispensed with long run-in phases in the lubrication-free run.
    The object is solved by the characterized features of claim 1. The dependent claims show advantageous developments.
    According to the invention thus now the defined geometric contact surfaces A0 are reversed by a changed geometric arrangement, with the aim of fixing the contact surface of the anchor pallets (thus defined contact surface) and to keep the wheel variable. Reason for this arrangement is to accelerate the wear of the armature, contrary to all previous teachings, to reduce the duration Einlaufphase. If the anchor has the defined geometric contact surface A0, then this surface must inevitably experience the n-times wear (with n = number of piston teeth of the wheel). Surprisingly enough, this effect sets in and the break-in phase in the case of diamond disappears almost completely.
    The industrial implementation of such an inverted arrangement must also allow safe engagement of the wheel and anchor. As a consequence, the wheel, or at least the thickness of the piston tooth, must be made significantly thicker than that of the anchor pallet. This in turn results in that the wheel has a larger moment of inertia and thus reduces the efficiency of the inhibition. Advantageous here is the use of new materials (Si, diamond), on the one hand have a significantly lower density than steel and on the other hand, in the case of diamond, a very high modulus of elasticity (700 GPa-1100 GPa) at the same time high bending stress (1 GPa-10GPa). The latter parameters allow the components to skeleton even more, thereby reducing the moment of inertia and thus to increase the efficiency of the inhibition again. However, the new materials have a significantly lower density than metallic materials and the new machining processes can achieve a higher degree of skeletonization. Preferably, the density is less than 4.5 g / cm 3, more preferably 1-4 g / cm 3. Further, the wheel may be implemented in a so-called more level technique, wherein first of all a thicker plate (so-called wafer) by photolithography and reactive ion etching e.g. the outer contour of the escape wheel is etched out. It is advantageous here that the wheel is still held with small webs in the remaining wafer in order not to have to manipulate each component individually. In a further step, the inner region of the toothed wheel is thinned down via a further photolithographic step, which is precisely positioned or adjusted for the first etching step. In this case, the second step can also take place from the rear side of the wafer. Possibly. This step can also be done before exposing the outer contour of the escape wheel. Examples of this technology can i.a. from www. Sigatec.ch be removed.
    All previous approaches in watchmaking pursued in principle the approach to minimize wear and to keep the moment of inertia of the components as small as possible. Therefore, the escape wheel has always been made as thin as possible. Surprisingly, it has now been found that it is more advantageous in the case of hard materials such as diamond or silicon to specifically stimulate wear. According to the invention it is thus proposed to invert the arrangement of the inhibition such that the armature has the so-called defined geometric contact surface A0. By using materials with low density and high mechanical strength, now the escape wheel (or at least the piston teeth of the escape wheel) can be made thicker than the pallets of the anchor.
    According to the present invention, it is provided that the thickness of the pallets be 50 to 180 microns and the thickness of the teeth of the gear 100 to 500 microns, wherein it is advantageous to carry out the thickness of the pallets is smaller than the thickness of the teeth , According to the invention, the thickness is understood in each case to be the vertical distance between the upper side and the underside of the tooth or the pallet.
    According to the invention, as set forth above, the edge of the pallets is designed so that at each contact with the front edge of the teeth of the wheel always the front edge of the pallets with the same geometric contact surface A0 is engaged. According to the invention, the front flanks of the pallets and the front flanks of the teeth, which have a non-verticality, are arranged relative to one another such that a symmetrical non-verticality (clearance angle α) of at least 0.5 °, preferably 1 °, particularly preferably 2 ° arises. Typical are about 1 ° per component flank. It is also not necessary that the respective components have the same deviation from the ideals.
    In such an inventive arrangement now arise during operation of the escapement, in the direction of the relative movement, in the front flanks of the teeth, the previously mentioned defined geometric contact surfaces A0in the form of a band having a maximum width of 20 microns, preferably up to 15 microns, more preferably up to 10 microns, most preferably have up to 5 microns.
    These geometric contact surfaces A0 evidently result from the abrasion of the rough component surfaces against each other. It has now been found that, in addition to the geometric contact surface A0, when the escapement enters the escapement, a further, namely a real contact surface AR, which forms only a partial surface of the geometric contact surface A0, is formed. It has been found that the ratio of the real contact area AR to the geometric contact area A0 is between 20 and 90%.
    With respect to the geometric arrangement of the flanks of the pallets, it is preferred that the front edge of the pallet is roof-shaped with a central degree or cylindrical with an outwardly curved surface (cambered) is formed.
    According to the invention, a further embodiment is that the front edge of the pallets is formed in a non-vertical arrangement with respect to the top or bottom of the pallet. For this case, the front edge of the pallets may be formed as a smooth flat surface, which deviates by a maximum of + 3 °, preferably ± 1 °, more preferably by less than ± 0.5 ° from the vertical with respect to the surface of the pallets.
    However, the invention also includes all other embodiments in which the front edge of the pallets has such a design that a defined geometric contact surface A0 arises in the front flank of the teeth of the wheel.
    In the anchor escapement according to the present invention, therefore, preferably the pallets are placed obliquely against the contact surface of the armature gear, so that not the likewise lateral end face of the armature gear but only the upper edge of the tooth rests against the pallet and transverse to the direction of the edge this surface slides.
    It is also preferred, if the escape wheel is made of silicon and at least the contact areas of the teeth of the gear also analogous to the pallets a hard material coating, preferably made of diamond.
    In the preferred case, both the anchor pallets as well as the gear and the radially outwardly directed teeth are thus made of silicon and have a hard material coating.
    The hard coating of the teeth and the pallets preferably has a layer thickness of 0.5 to 100 microns, preferably 2 to 50 microns and is selected from silicon dioxide, non-stoichiometric oxides having the formula SiXOY, where x and y are integers, silicon oxynitrides or silicon carbides, silicon nitride and / or diamond. In the case of silicon devices, the contact surfaces may also simply be thermally oxidized (e.g., according to EP 1 904 901).
    It is preferred in this case if the hard coating is a coating of nanocrystalline diamond. In particular, those embodiments in which both the gear and the pallets has a nanocrystalline diamond hard coating are preferred. Preference is given to coatings which have 96 to 97% sp 3 bonded carbon at a particle size of 9 nm.
    It has further been found that it is advantageous if the nanocrystalline diamond layer has a surface roughness of 3 to 100 nm Rms, preferably 1 to 30 nm Rms, particularly preferably 1-7 nm Rms. The roughness Rms is understood to mean the square roughness corresponding to the square mean. A nanocrystalline diamond layer with such a low surface roughness requires correspondingly less run-in / start-up time, resulting in a shorter run-in phase in order to achieve a minimum and constant coefficient of friction.
    It is furthermore preferred if the crystalline domains of the nanocrystalline diamond layer have an average particle size d50 of 0.5 nm to 50 nm, preferably 1 nm to 20 nm, particularly preferably 1 nm to 10 nm. The advantage of such an embodiment is that a very homogeneous and uniform nanocrystalline diamond layer is formed with a very small particle size as described above. Smaller grains inevitably increase the grain boundary volume. If the grains are small in relation to the surface roughness, the run-in phase can also be accelerated. The relationships are shown in FIG. 7. Preference is given to a grain boundary volume of 0 to 50%, preferably from 10 to 30%. Because the separation of a single grain from the composite is easier than the smooth grinding of a large grain. Therefore, it is advantageous if the crystalline domains are smaller than 0.5 × Rt, preferably 0.2 × Rt, particularly preferably 0.1 × Rt of the remaining surface roughness. In the case of the roughness Rt, however, the absolute surface roughness Rt (roughness depth), measured as the peak-to-valley value, is to be used in this case. Rt is calculated from the difference between the maximum peak height Rp and the maximum peak depth Rv.
    Since both pure silicon and diamond are electrical insulators, it is also proposed to electrically dope both materials, so that they have at least a low electrical conductivity. As a result, electrostatic charging effects can be avoided. The doping methods of silicon are well described in the literature. In the case of diamond, it is proposed either to resort to doping with boron or with nitrogen or ammonia. (Wiora, N., et al., Synthesis and Characterization of N-type Nitrogenated, Nanocrystalline Diamond Micron Materials and Nanomaterials, 15: 96-98). It is also proposed that in the case of insulating materials, the friction partners consist of the same material, thus having the same work function. As a result, an electrostatic charge due to the mere friction contact can be largely excluded.
    The invention will now be described by way of example only with reference to several figures.<Tb> FIG. 1 <SEP> schematically shows the top view of a Swiss lever escapement in the two rest positions.<Tb> FIG. 2 <SEP> shows the dynamic implication process of a Swiss lever escapement as shown in FIG.<Tb> FIG. 3 <SEP> now shows an enlarged view of the behavior of the contact surfaces of a Swiss lever escapement of the prior art during the Impulsionsvorgangs.<Tb> FIG. 4 <SEP> shows a corresponding schematic representation when the position of the clock changes.<Tb> FIG. 5 <SEP> now shows an inventive configuration of the contact surfaces as they are during the Impulsionsvorgangs in the invention.<Tb> FIG. 6 shows the embodiment according to the invention in an enlarged view when the bearing is changed.<Tb> FIG. 7 <SEP> shows a graphic representation of how the grain size relates to the grain boundary volume.<Tb> FIG. 8 <SEP> shows scanning electron micrographs of a piston tooth after 9 days of uninterrupted run of inhibition.<Tb> FIG. 9 <SEP> shows the geometric contact area A0 in an enlarged view as well as the real contact area AR.<Tb> FIG. 10 <SEP> shows experimentally determined amplitudes and gear values of an ETA caliber type 2 892 A2 equipped with a conventional diamond-coated inhibition.<Tb> FIG. 11 <SEP> now also shows for comparison the experimentally determined amplitudes and gait values of an ETA caliber type 2 892 A2 equipped with a diamond-coated inhibition according to the invention.<Tb> FIG. 12 to 14 <SEP> show further embodiments according to the invention in a schematic representation, as they are during the Implusionsvorganges in the invention.
    Fig. 1 shows a plan view of a Swiss lever escapement. Fig. 1a shows the state of the armature 1 and the wheel 4 at start and Fig. 1b after the zero crossing of the restlessness.
    As can be seen from Fig. 1a, the escape wheel 4 in the case shown here 20 piston teeth 5 on. The armature 1 has an input pallet 2 and an output pallet 2, which are alternately engaged with the piston teeth 5 of the wheel 4 in engagement. FIGS. 1a and 1b respectively show the rest conditions. In Fig. 1b, the new position of the piston tooth 5 is set. The stopper 20 serves the armature 4 as a stop. Alternatively, it is also possible to dispense with such a stop by inserting a shoulder in the anchor pallets. Such an embodiment is described, for example, in Swiss Patent Specification CH 567 293, in particular FIGS. 5 and 6. It is essential that in a Swiss lever escapement of the prior art with each revolution of the wheel 4 all 20 piston teeth 5 of the wheel 4 each once interact with both the input pallet 2 and the output pallet 2. In Fig. 1, the direction of rotation is indicated by the arrow.
    FIG. 2 now shows the Swiss lever escapement described in more detail in FIG. 1, in this case during the dynamic implusion process (interaction between piston tooth 5 and anchor pallet 2 or 2). In the enlarged illustration (detail A) the main areas are shown enlarged. The piston tooth 5 of the wheel 4 has already left the resting surface 22 and is located on the lifting surface 23 of the input pallet 2. By the applied torque of the gear train now slides the piston tooth 5 on the lifting surface 23 of the input pallet 2 and pushes the anchor pallet 2 back. For a better understanding of the process, reference is made to FIG. 3. With 21, the position is shown, with which the pallet 2 is engaged with the armature 5.
    Fig. 3 shows an enlarged view of how the contact surfaces behave to each other. To ensure that the piston teeth 5 of the escape wheel 4 securely engage in the pallets 2, 2 of the armature 1, the pallets 2, T of the armature 1 are made thicker than the piston teeth 5 of the wheel. This can be seen in particular from the section A-A. For a better understanding of the course of the Impulsionsvorganges in a Swiss lever escapement of the prior art is shown in detail B in more detail, with 25 again the point is shown, in which the pallet 2 is in engagement with the tooth 5. Due to the manufacturing process, the flanks 12 of the tooth 5 and the flanks 8 of the pallets 2 of the components never at an angle of 90 ° to the surface (so-called non-verticality). As a consequence, the components can thus be installed so that the functional surfaces are plane-parallel to each other. Usually, the components are now mounted so that the flanks are aligned with each other, so that a clearance angle α results. In the case presented here, a symmetrical non-verticality of 2 ° each was assumed. Typical are about 1 ° per component flank. In this case, it is not necessary for the functional surfaces of wheel 4 and armature 1 to have the same deviation from the ideals.
    Fig. 4 shows now the behavior of the components to each other in a change in position of the clock. In Fig. 4, the initial position is shown in the left part at section A-A and detail C, as previously described in Fig. 3 has been described in more detail. Now, if a change in position of the clock occurs, so does the bearing clearance, i. the relative position of the components to each other. This results in a shift Δh between the piston tooth 5 and the input pallet 2, as shown in detail B in the right half of Fig. 4. It is important that the piston tooth 5 of the wheel 4 due to the clearance angle α now at the point 25 is engaged, but still working on the same contact surface A0. The contact point 25 of the lever surface 23 of the input side 2, however, is now shifted by the amount .DELTA.h.
    5 now shows an embodiment according to the invention. Analogous to the embodiment of the prior art described above, in turn, due to the manufacturing process, the flanks 12 of the piston tooth 5 as well as the edge 8 of the pallet 2 have a non-verticality. Also in the inventive solution, the components are mounted so that the flanks 8,12 are aligned against each other, so that, analogous to Figs. 3 and 4, a clearance angle β results. This is again shown in detail in FIG. In the embodiment according to FIG. 5 again a symmetrical non-verticality of 2 ° was assumed. Also in the invention about 1 ° per component edge 8 and 12 are preferred. It is also not necessary here for the functional surfaces of wheel 4 and armature 1 to have the same deviation from the ideals. Deviating from the prior art but now that the piston tooth 5 of the wheel was made thicker than the thickness of the pallets 2 of the armature 4. Thus, a secure engagement of the piston teeth 5 is ensured in the anchor pallet 2 again. With 30 again the contact point is designated. The improved function resulting from the arrangement according to the invention is evident from FIG. 6.
    Fig. 6 shows the sectional view of Fig. 5 now upon entry of a bearing change of the clock. This occurs again when the clock is turned, for example. By the bearing clearance, the relative position of the components to each other changes. This also results in a shift Δh of the contact points 30 between the piston tooth 5 and input pallet 2. It is essential to the invention that the lever surface of the pallet 2 now still works on the same geometric contact surface A0 (defined contact surfaces) due to the clearance angle α. The contact point 30 of the piston tooth 5 of the escape wheel 4, however, is shifted by the amount .DELTA.h.
    It is crucial that in comparison to the prior art, the defined contact surface of the anchor pallet undergoes n-times wear by this arrangement, so that they can shrink more quickly. As a result of the inverse arrangement according to the invention, a significantly improved running-in behavior of the components is thus achieved, so that the clock is already ready for operation at an earlier point in time.
    Fig. 7 now shows how the grain boundary volume behaves to the grain size. As is apparent from Fig. 7, an increased grain boundary volume is inevitably achieved by smaller grains. A grain boundary volume of from 0 to 50%, preferably from 10 to 30%, is preferred.
    8 shows an enlarged representation (FIG. 8 a) of a piston tooth 5 and in FIG. 8 b the section enlarged in FIG. 8 a.
    The illustration in FIG. 8b shows a piston tooth 5 according to the invention after 9 days of uninterrupted running of the inhibition. The geometric contact area A0, which is represented by the dark part, may have a width of 0.5 to 20 μm, preferably of 1 to 10 μm, very particularly preferably of 1 to 5 μm. The real contact area AR (light stripe) is limited to the outermost upper part of the component due to the non-verticality of the component. Under 25,000 times magnification, it can be seen that the geometric contact area A0 is only about 1.5 to 2 μm wide in the example case. The dark color which surrounds the geometric contact surface A0 results from the abrasion of the originally microscopically rough component surface. The bright area was polished by the function of the component and is actually in contact with the pallets (2, 2). According to the invention, this is called a real contact surface AR. Due to the brightness difference, it is possible to determine the geometric and real contact surface and form the quotient.
    This is also illustrated, inter alia, in FIG. 9, in which again the geometric contact area A0 is shown again in FIG. 9a and the real contact area AR is shown in FIG. 9b. If we now form the ratio AR to A0, this results in 74.6% in the present case. During the break-in phase, the real contact surface increases until typically a wing portion T of more than 50% is reached. Similar evaluations were also with another caliber type ETA 2 824 A2 (also Pointage 20.3, so same Hemmbauteile) which works, however, with a much higher torque. This also results in a significantly higher surface pressure. Again, it was found that a minimum of 50% wing area is required to complete the run-in period.
    10 shows experimentally determined amplitudes and gait values of an ETA caliber type 2 892 A2 equipped with a conventional diamond-coated inhibition with a sp <2> -containing final layer according to European Patent EP 2 236 455 B2. This escapement is lubrication-free.
    The amplitude values (FIG. 10a) are measured (acoustically) by means of a time scale type Witschi Ml and optically controlled. The displayed values are arithmetic mean values of 6 layers each (top, bottom, top, right, bottom, left) The measurement interval was 30 seconds, the stabilization time also 30s. The mean gear deviation (FIG. 10b) is also an arithmetic average of 6 plies (see amplitude measurement).
    Good to see is the typical amplitude drop within the first 7 days. Afterwards, the amplitude slowly rises again and reaches its starting value after approx. 40 days. This behavior is also explained by the shrinkage of the components. The defined contact surface of the wheel is polished by frictional contact with the anchor pallets. If the wing portion of more than 50% is reached, no further removal takes place, and it can form a tribofilm on the contact surfaces. The dashed line shows when the break-in phase is completed.
    11, the experimentally determined amplitudes and gait values of an ETA caliber type 2892A2 are equipped with the diamond-coated inhibition according to the invention without soft sp <2> -containing end layer according to FIG. EP 2 236 455. The inhibition runs without lubrication.The amplitude values (FIG. 11a) are in turn measured (acoustically) by means of a time scale type Witschi Ml and optically controlled. The displayed values are in turn arithmetic mean values of 6 layers each (top, bottom, top, right, bottom, left) The measurement interval was 30 seconds, the stabilization time also 30s. The mean gear deviation (FIG. 11b) is also an arithmetic average of 6 plies (see amplitude measurement).It can be clearly seen that the typical amplitude drop now takes place within the first 2 days (conventionally about 7). Afterwards the amplitude will increase again very fast and will exceed your starting value after approx. 10 days. This behavior is also explained by the shrinkage of the components. The defined contact surface of the armature is polished by the frictional contact with the anchor pallets. If the wing portion of more than 50% is reached, no further removal takes place, and it can form a tribofilm on the contact surfaces. The fact that the defined contact surface experiences 20 times the wear of a piston tooth, the inlet chamfer is shortened accordingly. Furthermore, a significantly higher stability in the accuracy of accuracy.
    FIGS. 12 to 14 now show further embodiments according to the invention, how and in what manner the piston tooth 5 and the pallet 2 can be formed in order to enable the geometric contact surface A0 according to the invention.
    In Fig. 12a, such an embodiment is shown in plan view and in Fig. 12b of the marked in Fig. 12a section.
    In contrast to the embodiment according to FIG. 5, the pallet 2 is now beveled twice with respect to its flank in the embodiment according to FIG. 12, so that in turn a defined contact point 30 is formed on engagement with the tooth 5.
    In Fig. 13 a further embodiment is shown and that here is an embodiment in which the pallet 2 has a rounded edge. FIG. 13b again shows a detail of the plan view of such a configuration and in FIGS. 13a and 13b shows the contact point 30 in an enlarged view. FIG. 14 shows yet another embodiment, in which case the pallet 2 has a design , as has already been described in FIG. 12, but now the piston tooth 5 is formed angled here. In FIG. 14, a plan view of the configuration is again shown in detail in FIG. 14b and in FIGS. 14b and 14c respectively enlarged representations, the contact point 30 again being visible, so that a geometric contact surface A0 can again form here as well ,
    权利要求:
    Claims (13)
    [1]
    1. Anchor escapement for a mechanical timepiece comprising a pivotable armature (1) with anchor pallets (2, 2) and an armature wheel (4) which can be acted upon by a torque, which have teeth (5, 5, 5 ) during operation of the escapement a sliding relative movement is produced in which the front flanks (8) of the pallets (2, 2) are in succession and alternately in contact with the front flanks of the teeth (5, 5, 5), characterized,in that the front flank (8) of the pallets (2, 2) are designed such that, on each contact with the front flank (12) of the teeth (5, 5, 5) of the wheel (4), the front one Flank (8) of the pallets (2, 2) is always in engagement with the same contact surface, wherein at least the flanks (8) of the pallets (2, 2) and the front edge (12) of the teeth (5, 5 , 5) have a hard material coating.
    [2]
    2. anchor escapement according to claim 1, characterized in that the front flanks (8) of the pallets (2, 2) and the front flanks (12) of the teeth (5, 5, 5) have a non-verticality and are arranged to each other so that a clearance angle α of at least 0.1 ° -5 °, preferably 0.1 ° -3 ° and particularly preferably from 0.1 ° -1 °.
    [3]
    3. anchor escapement according to claim 1 or 2, characterized in that form during operation of the escapement, in the direction of the relative movement, in the front flanks (12) of the teeth (5, 5, 5) geometric contact surfaces A0 in the form of a band which preferably have a width of 0.5 to 20 μm, 0.5 μm to 10 μm, particularly preferably 0.5 to 5 μm.
    [4]
    4. anchor escapement according to claim 3, characterized in that in the geometric contact surface A0a (on) polished real contact surface AR is formed, wherein the ratio AR / A0 is between 20 and 90%.
    [5]
    5. anchor escapement according to one of claims 1 to 4, characterized in thatthe front flanks (8) of the pallets (2, 2) are roof-shaped with a central degree or cylindrical with an outwardly curved surface, wherein the geometric contact surface A0 is formed by the central degree or by the outwardly curved surface.
    [6]
    6. anchor escapement according to one of claims 1 to 5, characterized in thatthe front flanks (8) of the pallets (2, 2) are formed as smooth flat surfaces, which by a maximum of ± 2 °, preferably 1 °, more preferably less than 0.5 ° from the vertical, with respect to the top of the pallets , wherein the geometric contact surface A0 is formed by the outward edge.
    [7]
    7. anchor escapement according to one of claims 1 to 6, characterized in thatthe thickness of the pallets (2, 2) is 50 to 180 μm and the thickness of the teeth (5, 5, 5) of the gear (4) is 100 to 250 μm, the thickness of the pallets (2, 2) being smaller than the thickness of the teeth (5, 5, 5) of the gear (4), each with respect to the vertical with respect to the top.
    [8]
    8. anchor escapement according to one of claims 1 to 7, characterized in thatat least the contact surface of the front flank (12) of the teeth (5, 5, 5) which is in engagement with the front edge (8) of the pallets (2, 2), have a hard material coating.
    [9]
    9. anchor escapement according to at least one of claims 1 to 8, characterized in thatthe hard coating of the teeth (5, 5, 5) and the pallets (2, 2) has a layer thickness of 1 to 100 microns, preferably 5 to 50 microns and is selected from silicon oxide such as SiO 2, non-stoichiometric oxides having the formula SiXOY where x and y are integers, or silicon carbide, silicon nitride and / or diamond, diamond-like carbon (DLC), ruby, sapphire, silicon carbide.
    [10]
    10. anchor escapement according to claim 9, characterized in thatthe hard coating is a coating of nanocrystalline diamond.
    [11]
    11. anchor escapement according to claim 10, characterized in thatthe nanocrystalline diamond layer has at least one of the following properties:a) a surface roughness rms of 1 to 100 nm rms, preferably 1 to 30 nm rms, particularly preferably 1 to 7 nm Rms,b) that the crystalline domains have an average particle size d50 of 1 nm to a maximum of 50 nm, preferably from 1 nm to 10 nm, andc) that the nanocrystalline diamond layer has a bending stress of 1 to 10 GPa, preferably of at least 2 GPa, preferably of at least 5 GPa and more preferably at least 7 GPa.d) that the nanocrystalline diamond layer has a layer thickness in the contact region of 0.5 .mu.m to 100 .mu.m, preferably 2-50 microns and more preferably 2-10 microns.e) that the nanocrystalline diamond layer has an E modulus of 700 GPA to 1143 GPA, preferably from 400 GPA to 900 GPA.
    [12]
    12. anchor escapement according to at least one of claims 1 to 1 that at least the escape wheel was made of a material that has a density of 0.5 g / cm <3> to than 4.5 g / cm <3>, more preferably from 1 to 4 g / cm 3.
    [13]
    13. anchor escapement according to at least one of claims 1 to 12, characterized in thatthe pallets (2, 2) and / or the armature (1) and / or the wheel (4) are made of silicon and provided with the hard material layer.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    SU47937A1|1935-10-31|1936-07-31|В.П. Козлов|Anchoring for balance watches|
    CH357021A|1959-09-03|1961-09-15|John Perret Fils De|Timepiece lever escapement|
    FR1485813A|1966-06-17|1967-06-23|Pforzheimer Uhren Rohwerke|Watch movement for wristwatches|
    CH1082672A4|1972-07-19|1975-03-14|
    CH612308A|1975-09-10|1979-07-31|Lever escapement|
    FR2731715B1|1995-03-17|1997-05-16|Suisse Electronique Microtech|MICRO-MECHANICAL PART AND METHOD FOR PRODUCING THE SAME|
    EP1233314A1|2001-02-15|2002-08-21|DAMASKO, Konrad|Clockwork|
    DE10317889B4|2003-04-17|2008-10-30|GFD-Gesellschaft für Diamantprodukte mbH|Micromechanical component and method for its production|
    AT416401T|2005-06-28|2008-12-15|Eta Sa Mft Horlogere Suisse|REINFORCED MICROMECHANICAL PART|
    DE102008029429A1|2007-10-18|2009-04-23|Konrad Damasko|Method for producing mechanical functional elements for movements as well as functional element produced by this method|
    EP2107434B1|2008-04-02|2013-09-18|Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA|Mechanical timer|
    EP2236455B1|2009-04-02|2015-10-21|GFD Gesellschaft für Diamantprodukte mbH|Micromechanical component with reduced wear|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    EP14185997.5A|EP3001256B1|2014-09-23|2014-09-23|Anchor escapement|
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