• 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:
    AXIAL MACHINING DEVICE AND METHOD OF PERFORMING AXIAL MACHINING ON A WORKING PIECE.The present invention provides an axial machining device (1) comprising a tool carrier spindle (3) rotatable in a housing (2), the housing housing a transmission system (5) causing the spindle to advance automatically in relation to the housing (2) under the effect of the tool carrier spindle being driven in rotation, the transmission system (5) including a screwed forward gear (15) in the spindle (3), the device being characterized by the fact that it includes an elastic return member (40) propelling the forward sprocket (15) in a first axial direction opposite to the forward direction (A) of the spindle (3 ), and the fact that it includes a first rolling bearing (50) having rolling members (51) rolling on a waving track having an axial component, thus periodically driving the forward sprocket (15) to move in a second from the direction opposite to the first, such that the rotation of the spindle (3) is accompanied by axial vibratory movement.
    公开号:BR112012011516B1
    申请号:R112012011516-2
    申请日:2010-11-16
    公开日:2020-10-27
    发明作者:Grégoire Peigne
    申请人:Mitis；
    IPC主号:
    专利说明:

    The present invention relates to devices for axial machining, such as drilling, drilling, and grinding, and more particularly it relates to the 5 compact devices that incorporate means for transmitting feed and movement to the tool, eg a drill bit. drilling.
    Patent application FR 2 881 366 in the name of SETI TEC describes a drilling device including a drive sprocket 10 for driving a rotating drill conveyor spindle and a lead sprocket connected to the drill conveyor spindle via a connection threaded.
    A similar device is shown in Figure 1. In this figure, the numerical references are the same as those used below for reference to components that are identical or similar.
    Vibratory drilling devices are also known from the following publications: WO 2008/000935 A1, DE 10 2005 002 462 B4, US 7 510 024 B2, FR 2 907 695, and US 2007/209813.
    The vibratory assistance serves to break up filings and increase the quality of the drilled holes, eliminating the risk of clogging, to increase tool life and to make the method more reliable.
    In publications FR 2 907 695, US 7 510 024, and US 2007/209813, oscillations are generated by meat without rolling members. That gives rise to friction in the meats, generating heat and noise. In addition, the ideal vibratory frequency for good chip fragmentation is not always obtained because the frequency is an integer multiple of the differential rotation speed between the feed sprocket and the spindle or casing, this differential is directly related to the number 30 oscillations of the meat.
    In patent DE 10 2005/002462, a spring exerts a return force on a roller bearing that includes a raceway that is waved in the direction of advance of the drill bit for the purpose of producing axial vibration. In the case of high axial pressure on the drill bit, 35 the bearing members can stop rolling on the waving track and the bit can stop oscillating. To avoid this inconvenience, the spring must be very hard, which can cause the bearing to be oversized. That gives rise to the increase in size and costs.
    In addition, the device is mounted on the end of the spindle, under the feed system, thus adding to the overall size and leading to greater complexity.
    There is a need to further improve drilling devices, namely those for machining large aviation workpieces, such as fuselage or wing parts.
    The invention further provides an axial machining device comprising a rotating tool carrier spindle in a housing, the housing housing a transmission system to cause the spindle to advance automatically in relation to the housing under the effect of the tool carrier spindle being driven in rotation, the transmission system including an advance gear screwed into the spindle.
    The device comprises an elastic return member propelling the advancing sprocket in a first axial direction preferably opposite the advancing direction of the spindle (i.e. its direction of movement during machining). The device includes a first bearing bearing having rolling members rolling on a waving track having an axial waving component, thus periodically driving a forward sprocket to move in a second direction opposite to the first, such that the spindle rotation is accompanied by axial vibratory movement.
    The device of the invention is compact because the means for creating the vibratory movement are integrated within the housing. Friction is also greatly reduced because of the bearing members.
    In addition, the invention makes it possible to generate axial vibration at a frequency that is associated with the speed of rotation of the rotating sprocket, thus allowing the number of oscillations per revolution to remain constant regardless of the advance settings. A variant of the invention, in which the first bearing supports directly against the feed wheel and in which the frequency of axial vibration is then directly associated with the speed of rotation of the rotating gear wheel and not with the speed of rotation of the feed spindle. tool, this advantage is lost, but other advantages remain.
    It is advantageous for the return member to propel the forward gear in a direction opposite to the forward direction of the spindle. This makes it possible to use the first roller bearing to exert an axial force in the forward direction of the spindle. Thus, even if the drill bit is axially overloaded, it continues to be subjected to vibratory movement. In addition, neither the return member nor the first bearing housing needs to be oversized. The device thus remains easy to integrate into a housing containing the spindle transmission and feed system.
    The first bearing housing advantageously has rollers, since the rollers are capable of withstanding greater forces than the balls.
    The waving track co-operates with the rolling members as the epicyclic gear acting as a reduction gear and decreasing the number of oscillations per revolution. The first bearing, therefore, serves to reduce friction and reduce the vibratory movement by the epicyclic gear.
    The waving track can be configured to produce a number of vibrating periods per revolution of the tool carrier spindle that is not an integer, or that is still an irrational number. The number of vibrating periods per revolution of the tool carrier spindle can, for example, be between 1 and 3 (excluding final values) and can in particular be equal to about 1.5 or 2.5. The waveform may have an odd number of waves, eg, winding waves per revolution. For example, three ripples on the waving track can generate about 1% oscillations per revolution of the spindle, given the rotation of the bearing members. A non-integer number makes it possible to avoid cutting edges after parallel paths during drilling, and thus increases the efficiency with which the filings are fragmented.
    The waving track preferably produces an irrational, non-integer number of vibrating periods per revolution of the tool carrier spindle.
    The first bearing housing may have a flat ring and a wave ring with the bearing members rotating between them, these rings being stationary or mobile within the device. The wave ring defines the wave path.
    The number of bearing members between the flat ring and the wave ring is equal to the number of waves in the wave ring.
    Because one of the rings is wavy, the path followed by the rolling members of the ring is not a two-dimensional (2D) circle, but a three-dimensional (3D) sine wave. Thus, the lengths of the paths over a ring plane and a wave ring are different, even if the diameters of the rings are the same.
    Willis' formula can be applied to the invention. Thus, it can be written as the path of the current point on the wave ring: where R1 is the radius of the path in the ring, □ is the angle formed by the current point, N is the number of waves, and A is its amplitude.
    In differentiating this equation, the following equation is obtained:
    The absolute value or norm of this equation is used to obtain the derivative of the curvilinear abscissa axis, that is, the length of the path s1 of the wave ring:
    The integration of the above equation serves to calculate the curvilinear abscissa s1: where the integral above is the incomplete elliptic integral of the second type.
    In the flat ring, the path length s2 can be written merely as the perimeter of a circle: where R2 is the radius of the ring.
    The reduction rates r1 and r2 of epicyclic gear in relation to the movable ring or the stationary ring respectively can be written as follows:
    This calculation involves numerous parameters and by its nature gives rise to a number of oscillations per revolution that is irrational, as explained in the following examples.
    Taking the same radii for the flat and undulation rings, ie R1 = R2 = 20 mm (mm), N = 3 for the number of undulations, and A = 0.5 mm for their amplitudes, the reduction rates of the epicyclic gear are approximately equal to r1 = 0.500351 and r2 = 0.499649, thus giving 1.50105 vibrating periods per revolution of the spindle if the wave ring is stationary and 1.499895 vibrating periods per revolution of the spindle if the flat ring is stationary.
    Using radii of different values, ie R1 = 22 mm and R2 = 20 mm, and A = 0.1 mm with the same number of ripples, the reduction rates of the epicyclic gear are approximately equal to r1 = 0.523821 and r2 = 0.4776179, giving 1.57146 vibrating periods per spindle revolution for a stationary wave ring and 1.42854 vibrating periods per spindle revolution for a flat stationary ring.
    An irrational number of oscillations per revolution of the spindle makes it possible to avoid any risk of self-sustaining vibration or chatter.
    It is particularly advantageous to have a non-integer and irrational number of oscillations per revolution, in particular when using the device to perform countersinking and machining operations with an internal diameter. An irrational number of oscillations per revolution makes it possible to avoid a shape defect at the end of the operation, in particular when there is an end of stroke interval after a few seconds, during which there is no advance. If the advance is stopped at the end of the stroke for a defined number of revolutions, then, when using an irrational and non-integer number of oscillations per revolution, the resulting surface, which may be conical or flat, for example, is not subject to any oscillation permanently located anywhere, so a form of defect, if any, is acceptable. The peak of each angular oscillation is compensated somewhat in relation to the oscillation of the previous one.
    The transmission system may include a rotating sprocket used to drive the rotating tool carrier spindle and arranged in the housing with the possibility of moving axially in relation to the housing. The first bearing housing can support directly against the rotating sprocket.
    The swivel gear can be located between the forward gear and the first bearing bearing, however, in a variant, the forward gear can be located between the swivel gear and the first bearing bearing.
    The device may have a second roller bearing interposed between the advancing sprocket and the rotating sprocket.
    The lead gear can rotate within a third bearing housing, in particular a needle roller. A needle bearing makes it easier to accommodate the axial movement of the feed wheel than the ball bearing.
    The elastic return member may comprise a pressure washer with the tool carrier spindle passing through it. The thrust washer can rest against an inner ring radially of a fourth bearing housing through which the tool carrier spindle passes, e.g. a roller bearing having two rows of balls, thus allowing the accuracy of the orientation to be increased.
    The invention also provides an axial machining method in which use is made of a device as defined above.
    The invention can be better understood by reading the following detailed non-limiting description of the modalities of the invention and analyzing the accompanying drawings, where:
    Figure 1 is a longitudinal section view of an example of a prior art device;
    Figure 2 is a view similar to Figure 1 showing an example of a drilling device made in accordance with the invention;
    Figure 3 is a view similar to Figure 2 showing a variant embodiment;
    Figure 4 is a perspective view showing an example of a waveform;
    Figure 5 is a kinematic or skeleton diagram of an example device made in accordance with the invention; and
    Figures 6 and 7 are kinematic diagrams for various embodiments of the devices of the invention.
    The machining device according to the invention shown in Figure 2, in particular, a drilling device, comprises a housing 2 that houses part of a tool carrier spindle 3, and a system 5 for automatically driving and advancing the spindle 3. System 5 is coupled to a drive motor 112 shown in Figures 5 to 7, such a motor can be a pneumatic motor, for example. Spindle 3 drives a drill bit or cutter (not shown) in order to perform axial machining, for example, drilling.
    As an example, system 5 is similar to that described in patent application FR 2 881 366 and it has a rotating gear wheel 10 that rotates with hole 3 at the same time, allowing relative axial movement, the connection between the wheel rotating gear 10 and spindle 3, a sliding connection being, for example, spindle 3 possibly having grooves in which corresponding grooves of the rotating gear 10 are coupled.
    The rotating sprocket 10 is driven in rotation about the X axis by a drive wheel 11 coupled to the motor.
    The system 5 also has a feed sprocket 15 which is axially movable within the housing 2 along the X axis and which includes a thread 16 threaded onto a threaded portion of the spindle 3, such that the rotation of the feed sprocket 15 in the spindle 3 causes the spindle to move axially. For example, the spindle can travel approximately 0.1 mm approximately by one revolution of the spindle. The spindle rotation speed can, for example, be in the range of 300 revolutions per minute (rpm) at 5000 rpm.
    The lead sprocket 15 can rotate with respect to the rotation sprocket 10, a rolling bearing 17 having bearing members like balls being axially interposed between them, as shown.
    The lead sprocket 15 can rotate within a bottom guide roller bearing 18 which serves to guide you in rotation while allowing the lead sprocket 15 to have a certain upward axial stroke in relation to housing 2.
    An elastic return member 40, such as a thrust washer, is interposed between the forward sprocket 15 and the bearing 18. The thrust washer 40 is axially supported against the inner ring of the bearing 18.
    The rotating sprocket 10 is movable within the housing 2 along the X axis, and is driven to move upwardly by the pressure washer 40 through the forward sprocket 15 and the bearing 17.
    A bearing housing 50 is axially interposed between the casing 2 and the rotating sprocket 10, remotely from the advancing sprocket 15. Thus, the rotating sprocket 10 is propelled to hold against the bearing 50 by the thrust washer 40 .
    Bearing 50 has bearing members 51 which, in the example shown, are rollers inserted in a housing 54 and which rotate between a smooth top bearing ring 52 resting against a top bearing bearing 55 to guide the rotating sprocket 10, and a ripple bottom ring 53 defining a ripple track, resting on a shoulder 88 of the rotating sprocket 10. An example of a ripple track 100 with an axial component is shown in Figure 4. This Figure shows the radius R1 of the ring and angle □ used to calculate the number of vibrating periods per spindle revolution, as described above.
    The axis of rotation of each bearing member 51 can be perpendicular to the X axis, as shown.
    For example, the top bearing 55 is a ball bearing, but it could be some other type of bearing.
    The waving track causes the rollers 51 to move axially during their rotation. The extreme amplitude of this axial movement can, for example, be in the range of 0.2 mm to 0.4 mm. Such axial movement is transmitted through the rotating gear wheel 10 to the feed gear 15, and thus to the tool carrier spindle 3.
    The ripple track preferably has an odd number of ripples per revolution, in order to obtain a vibratory frequency that is an non-integer multiple, in particular an irrational multiple, of the rotation frequency.
    The system 5 includes a drive wheel 60 to drive the forward sprocket 15, such a drive wheel is coupled to the wheel 11 by a clutch clutch and can be automatically decoupled from the drive wheel 11 at the end of the downward stroke of the spindle 3 so as to allow the spindle to be raised.
    The wheel 60 drives the forward sprocket 15 at a rotation speed that is slightly different from the rotation speed of the rotary sprocket 10, so as to generate the desired forward movement for the spindle 3 in the forward direction A, in a manner known.
    At the end of the forward movement of the spindle 3, a backrest 90 carried by the spindle 3 comes to support against the end edge surface of the rotating sprocket 10 and causes the drive wheel 60 to move away from the drive wheel 11.
    The drive wheel 60 downwardly carries a piston 70 which carries a seal ring 92. When the drive wheel 60 is coupled to the drive wheel 11, the seal ring isolates chamber 72 located above the piston from a compressed air inlet 94. When the piston 70 is moved downwards, the sealing ring 92 stops sealing and the pressure that exists above the chamber 72 drives the piston 70 downwards. The drive wheels 11 and 60 are then completely decoupled and the spindle can move upwards. A valve 96 is actuated by hole 3 at the end of its upward movement, thus bringing chamber 72 to atmospheric pressure and allowing piston 70 to rise under the effect of a return spring 73. The drive wheels 11 and 60 can be couple together again.
    The transmission system may be similar to that described in patent application FR 2 881 366.
    The variant modality shown in Figure 3 differs from that in Figure 2 in particular in that the bottom bearing 18 is replaced by a needle bearing 98 that accommodates axial movement between the raceways more easily. The spindle 3 is guided at its bottom end by a bearing 99 having two rows of balls.
    A needle bearing 100 is also used to replace the top bearing 55 for the guide rotation of the rotating sprocket 10.
    The top of spindle 3 is guided in rotation by a ball bearing 101. The thrust washer 40 rests against the bottom ring of bearing 99 having two rows of balls.
    Figure 5 is a kinematic diagram of an example of a device made in accordance with the invention.
    This diagram shows the connections between the main elements of the device described above. The motor 112 to which the transmission system 5 is coupled by the drive wheel 11 can also be seen.
    In the variants of Figures 6 and 7, the system 5 is integrated in a 5 configuration in which the forward and transmission sprockets are interchangeable. The location of the return means 40 differs between the modalities of Figures 6 and 7.
    Naturally, the invention is not limited to the examples shown. In particular, it is possible to make the transmission and advance system 5 out of 10 other ways.
    The term "comprising one" should be understood as being synonymous with "comprising at least one".
    权利要求:
    Claims (15)
    [0001]
    1. Axial machining device (1), comprising a tool carrier spindle (3) rotatable in a housing (2), the housing (2) housing a transmission system (5) causing the spindle (3) to automatically advance in relation to the housing (2) under the effect of the tool carrier spindle (3) being driven in rotation, the transmission system (5) including an advance gear (15) screwed to the spindle (3), the device including a elastic return member (40) driving the forward sprocket (15) in a first axial direction opposite to the forward direction (A) of the spindle (3), the device being characterized by the fact that it includes a first bearing bearing ( 50) having rolling members (51) rolling on a waving track having an axial component, thereby periodically propelling the forward sprocket (15) to move in a second direction opposite to the first, such that the rotation of the spindle (3) is accompanied by the axi vibratory movement al.
    [0002]
    2. Device according to claim 1, characterized by the fact that the first bearing housing (50) has rollers (51).
    [0003]
    Device according to claim 1 or 2, characterized by the fact that the waving track has a non-integer number of vibrating periods per revolution of the tool carrier spindle (3).
    [0004]
    4. Device according to claim 3, characterized by the fact that the waving track produces an irrational number of vibratory periods per revolution of the conveyor spindle (3).
    [0005]
    Device according to any one of claims 1 to 4, characterized in that the transmission system (5) includes a rotating gear wheel (10) serving to drive the rotating and arranged tool carrier spindle (3) in the housing (2) with the possibility of moving axially in relation to it.
    [0006]
    6. Device according to claim 5, characterized by the fact that the rotating gear wheel (10) is located between the forward gear wheel (15) and the first rolling bearing (50).
    [0007]
    Device according to claim 5 or 6, characterized by the fact that the device includes a second roller bearing (17) interposed between the forward sprocket (15) and the rotating sprocket (10).
    [0008]
    Device according to any one of claims 1 to 7, characterized in that the forward sprocket (15) rotates within a third bearing housing, in particular a needle roller (98).
    [0009]
    Device according to any one of claims 1 to 8, characterized in that the elastic return member (40) comprises a pressure washer with the tool carrier spindle (3) passing through it.
    [0010]
    10. Device according to claim 9, characterized in that the pressure washer rests against a radially inner ring of a fourth bearing housing through which the tool carrier spindle (3) passes, in particular a bearing (99 ) having two rows of spheres.
    [0011]
    11. Device according to any one of claims 1 to 10, characterized in that the waving track has an odd number of wavings.
    [0012]
    12. Device according to claim 1, characterized by the fact that the first bearing housing (50) has a flat ring (52) and a wave ring (53) with the bearing members (51) rotating between them , the waving ring (53) defining the waving track, the flat ring (52) or the waving ring (53) being stationary within the device.
    [0013]
    13. Device according to claim 3 or 4, characterized by the fact that the number of vibrating periods per revolution of the tool carrier spindle (3) is between 1 and 3.
    [0014]
    14. Method of performing axial machining on a workpiece, characterized by the fact that it makes use of a device (1), as defined in any of claims 1 to 13.
    [0015]
    15. Method, according to claim 14, characterized by the fact that the method is applied to countersinking or machining operations of internal diameter.
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    同族专利:
    公开号 | 公开日
    US9156116B2|2015-10-13|
    FR2952563B1|2012-02-03|
    CA2780783A1|2011-05-26|
    WO2011061678A3|2012-01-05|
    ES2439819T3|2014-01-24|
    EP2501518B1|2013-10-23|
    CN102639293B|2015-12-02|
    JP2013510732A|2013-03-28|
    CN102639293A|2012-08-15|
    CA2780783C|2017-08-15|
    US20130051946A1|2013-02-28|
    JP2016028844A|2016-03-03|
    WO2011061678A2|2011-05-26|
    EP2501518A2|2012-09-26|
    BR112012011516A2|2016-06-07|
    FR2952563A1|2011-05-20|
    JP5901531B2|2016-04-13|
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    法律状态:
    2019-01-08| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-08-27| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-04-07| B09A| Decision: intention to grant|
    2020-10-27| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 16/11/2010, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    FR0958081A|FR2952563B1|2009-11-17|2009-11-17|AXIAL MACHINING DEVICE|
    FR0958081|2009-11-17|
    PCT/IB2010/055191|WO2011061678A2|2009-11-17|2010-11-16|Axial machining device|
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