• 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 a transmission module (100) for a force comprising: - two toothed wheels (200) connected to a main shaft (210); a first ratchet carrier (300a) and a second ratchet carrier (300b) provided with a first pawl (310a) and a second pawl (310b), and arranged, when activated, to drive the wheels teeth rotated by pressing the ratchet against a tooth of the toothed wheel; a first cam (400a) and a second cam (400b) arranged to actuate, respectively, in a first angular stroke around an axis YY 'of the first cam (400a), the first pawl (310a), and, according to a second angular stroke around the axis YY 'of the second cam (400b) different from the first angular stroke, the second pawl (310b).
    公开号:FR3080663A1
    申请号:FR1853683
    申请日:2018-04-26
    公开日:2019-11-01
    发明作者:Denis Perrin
    申请人:Schneider Electric Industries SAS；
    IPC主号:
    专利说明:

    TITLE
    EFFORT TRANSMISSION MODULE
    DESCRIPTION
    TECHNICAL AREA
    The present invention relates to a force transmission module, and in particular a double pawl transmission module. More particularly, the present invention relates to a force transmission module intended to transmit a force to a mechanical energy accumulation system, in particular to a closing spring of an electric breaking device, such as a circuit breaker, a switch or disconnector.
    PRIOR STATE OF THE ART
    A force transmission module known from the prior art comprises:
    - at least one toothed wheel fixedly linked to a main shaft, adapted to transmit a force to an energy storage system via the main shaft,
    - A system for driving the toothed wheel in rotation in a direction of rotation, known as a direct direction, around the main axis.
    In general, the energy storage system is a mechanical energy storage system, and in particular a spring for closing a current cut-off device such as a circuit breaker.
    The drive system may in particular include ratchet systems.
    In particular, documents [1] and [2] cited at the end of the description each propose a drive system provided with several pawls. However, their arrangement and their drive mode do not open the way to a smooth rotation of the toothed wheel, and de facto limit the mechanical durability of the transmission module.
    In this regard, the emergence of renewable energies, and the multiplication of the number of decentralized sources of energy production, requires much more frequent maneuvers of electrical cut-off devices, and consequently of the force transmission module. It is thus necessary to be able to have a force transmission module capable of performing for example 30,000 cycles against 10,000 today.
    A planetary gear, instead of ratchet systems, could be implemented to overcome the above problems.
    However, such a training system is not satisfactory. Indeed, a planetary gear train comprises a large number of parts, and is therefore complicated to implement on the technical level. It is also relatively expensive.
    In particular, the parts making up the planetary gear train include in particular gears, the manufacture of which requires a particularly high degree of precision, thereby penalizing their manufacturing cost.
    An object of the present invention is therefore to propose a force transmission module which is simpler to implement than the transmission module known from the state of the art.
    Another object of the present invention is also to propose a force transmission module having appreciable mechanical durability, and in particular capable of being able to endure at least 30,000 cycles.
    Another object of the present invention is also to propose a force transmission module in which the drive force by a plurality of pawls of the toothed wheel can be smoothed so as to limit the wear of the transmission module and of its motorization.
    Another object of the present invention is also to propose a force transmission module allowing manual actuation.
    Finally, another object of the present invention is to propose a force transmission module whose manufacturing and implementation costs are optimized.
    STATEMENT OF THE INVENTION
    The aims of the present invention are, at least in part, achieved by a force transmission module comprising:
    - At least one toothed wheel fixedly connected to a main shaft extending along a main axis XX ';
    - at least a first pawl holder and a second pawl holder provided, respectively, with a first pawl and a second pawl, each of the first pawl and second pawl being arranged to, when activated, drive the wheel toothed in rotation in one direction, said direct direction, about the main axis by pressing the pawl considered against a tooth of the toothed wheel;
    - At least two cams, fixedly connected to each other, say, respectively, first cam and second cam arranged to actuate, respectively, the first pawl according to a first angular stroke around an axis YY 'of the first cam, and the second pawl according to a second angular travel around the axis YY 'of the second cam different from the first angular travel.
    According to one embodiment, the first angular travel and the second angular travel have zero overlap, and their sum is 360 °.
    According to an embodiment, the first angular stroke and the second angular stroke are each equal to 180 °.
    According to one embodiment, the at least two cams are arranged so that the activation of one and / or the other of the first and second pawls by the cam intended to activate it is directly preceded by a phase of engagement of said pawl by this same cam, the engagement phase comprising putting the pawl considered in abutment against a tooth of the at least one toothed wheel according to an angular stroke of engagement of said cam.
    According to one embodiment, the at least two cams are arranged so that the activation of one and / or the other of the first and second pawls by the cam intended to activate it is directly followed by a phase of disengagement of said pawl by this same cam, the disengagement phase comprising a reduction in the support of the pawl against the tooth according to a law of continuous decrease of said support according to an angular travel of disengagement of said cam.
    According to one embodiment, the first pawl holder and the second pawl holder are each in pivot connection with the main shaft.
    According to one embodiment, the at least two cams are integral with a camshaft extending along the axis YY 'essentially parallel to the main axis XX'.
    According to one embodiment, the first pawl holder and the second pawl holder are each provided with a roller, called respectively, first roller and second roller, against which come into abutment according to their contour, respectively, the first cam and the second cam, the first cam and the second cam exerting the activation of the first pawl and the second pawl, respectively, via the first roller and the second roller, and their respective pawl carriers.
    According to one embodiment, the at least one toothed wheel comprises a first toothed wheel and a second toothed wheel, advantageously identical, arranged to be driven in rotation, respectively, by the first pawl and the second pawl.
    According to one mode of implementation, a complete revolution around the axis YY 'of the assembly formed by the first and second cams induces the rotation of the at least one toothed wheel according to an angular stroke corresponding to a tooth of l '' at least one gear.
    According to one embodiment, the transmission module comprises means for driving in rotation about the axis YY 'of the at least two cams, the drive means advantageously comprise a motor and a reduction gear (gearmotor) or a crank.
    According to one embodiment, the first pawl holder and / or the second pawl holder are also adapted to be operated manually.
    According to one embodiment, the main shaft has two ends, at least one of which is intended to transfer mechanical force to a mechanical accumulation system.
    According to one embodiment, the mechanical accumulation system comprises a compression spring.
    The invention also relates to an electrical device comprising a force transmission module according to the present invention.
    BRIEF DESCRIPTION OF THE DRAWINGS
    Other characteristics and advantages will appear in the following description of a force transmission module according to the invention, given by way of nonlimiting examples, with reference to the appended drawings in which:
    - Figure 1 is a schematic representation of the transmission module according to the present invention, in a perspective view;
    - Figure 2 is a schematic perspective representation of the transmission module, according to the present invention, integrated in a control mechanism of an electrical switching device;
    - Figure 3 is a schematic representation of the transmission module according to the present invention, in a perspective view;
    - Figures 4a to 4g are schematic representations of the different operating sequences of the transmission module in its entirety, according to a profile view, and in particular according to a profile view allowing the observation of the first wheel, the first pawl and the first cam;
    FIGS. 5a to 5g are schematic representations according to operating sequences of the transmission module identical, respectively, to FIGS. 4a to 4g, and also according to an identical profile view, the mechanism associated with the first wheel, with the first pawl and the first cam being however removed so as to allow the observation of the second wheel, the second pawl and the second cam;
    - Figure 6 is a temporal representation (horizontal axes) of the different operating phases of the transmission module according to the present invention, the angular travel of the first cam being shown in the upper part and that of the second cam in the lower part.
    DETAILED PRESENTATION OF PARTICULAR EMBODIMENTS
    The present invention provides a force transmission module which comprises a toothed wheel provided with a main axis intended to transmit the force to a mechanical energy accumulation system.
    According to the present invention, the toothed wheel is rotated by two pawls, called first pawl and second pawl, activated independently and alternately by two cams, said first and second cam, integral with the same camshaft.
    In particular, the cam profiles are arranged so that a continuous and smooth force is exerted on the toothed wheel.
    The present invention will now be described in detail and in connection with Figures 1 to 3.
    The transmission module 100 comprises at least one toothed wheel 200 secured to a main shaft 210 which extends along a main axis XX '(Figure 1).
    By “toothed wheel” is meant a wheel provided with teeth on at least part of its periphery, for example on half of its periphery.
    It is also understood that a toothed wheel secured to a main shaft implies, within the meaning of the present invention, a fixed connection between said wheel and said shaft. However, the fixed link does not prevent the disassembly of the at least one toothed wheel which can slide along the main shaft.
    The at least one gear 200 can also include a first gear 200a and a second gear 200b. The first and second toothed wheels 200a and 200b are advantageously identical, mutually parallel, and in the same orientation.
    The main shaft 210 includes a first end 210a and a second end 210b.
    Either of the first and second ends 210a and 210b, for example the second end 210b, has grooves or teeth which are intended to transmit the force to a mechanical energy accumulation system.
    The transmission module 100 comprises at least a first pawl holder 300a and a second pawl holder 300b provided, respectively, with a first pawl 310a and a second pawl 310b (FIGS. 1 and 3).
    A pawl holder comprises for example a plate, preferably metallic on which the pawl is fixed.
    The first pawl 310a and the second pawl 310b are arranged to, when activated, drive the at least one toothed wheel 200 in rotation in a first direction around the main axis XX '.
    In particular, the rotational drive of the at least one toothed wheel 200 is caused by pressing the pawl considered against a tooth of the at least one toothed wheel.
    It is therefore understood that the driving in rotation of the at least one toothed wheel by one or the other of the first and second pawls 310a and 310b, is executed by application of a mechanical force by the pawl concerned against a tooth of said wheel.
    It is understood, within the meaning of the present invention, that the first pawl and the second pawl can both act on the same wheel or each act on a different wheel. For example, the first pawl 310a and the second pawl 310b can be arranged to drive in rotation, respectively, the first wheel 200a and the second wheel 200b.
    Unlike the planetary gear train known from the state of the art, the pawls and pawls are technically simple to implement and do not require any particular precaution, such as the implementation of a reduction stage intended to protect them.
    Furthermore, the first pawl holder 300a and the second pawl holder 300b may be identical so that their integration into the transmission module 100 is facilitated and that their pairing with the cams is not necessary.
    In addition, the implementation of pawl holders requires fewer parts and is relatively economical compared to a planetary gear.
    It is also understood, without it being necessary to specify it, that the first and the second pawls are each provided with a return system, in particular a spring, arranged to force the contact between each pawl and the at least one gear wheel.
    The return system also makes it possible to bring the roller into abutment against the cam as soon as the latter no longer acts on said roller.
    The transmission module 100 also includes a first cam 400a and a second cam 400b linked by a fixed link (FIGS. 1 to 3).
    The invention is described with two cams, however a person skilled in the art can extend the principles set out to a larger number of cams.
    It is understood, within the meaning of the present invention, that the two cams are also arranged to rotate about an axis YY '(FIG. 1).
    Advantageously, the axis YY 'is essentially parallel to the main axis XX'.
    Still advantageously, the first and second cams 400a and 400b are integral with a camshaft 410 which extends along the axis YY '(Figures 1 to 3).
    The transmission module 100 can advantageously comprise means for driving in rotation about the axis YY 'of the at least two cams. In particular, the drive means may include an electrical control which acts on a geared motor or a crank.
    The first cam 400a and the second cam 400b are arranged to activate alternately, respectively, the first pawl 310a and the second pawl 310b via the pawl holders.
    By "activate alternately", it should be understood that the two pawls act according to two different time phases, which may however have an overlap. In other words, there may exist a period of time which is generally less than each of the two time phases during which the two pawls 310a and 310b are activated and both drive the at least one toothed wheel 200.
    It is understood that the activation of one or the other of the first and second pawls, respectively, by the first cam and the second cam is a function of the cam profile and more particularly of the contour of said first and second cams.
    The first cam 400a is in particular arranged to actuate the first pawl 310a according to an angular course, called first angular course, around the axis YY '.
    Equivalently, the second cam 400b is arranged to actuate the second pawl 310b according to an angular travel, called the second angular travel, around the axis YY '.
    By “angular stroke” is meant a continuous range of angles of rotation of the assembly formed by the first cam and the second cam. It is understood that an angular travel can take any value between 0 ° and 360 °.
    The profile of the first cam 400a according to the first angular stroke can advantageously be adapted so that the first pawl imposes a constant torque, throughout the duration of said first stroke, on at least one toothed wheel, and in particular the first toothed wheel .
    Equivalently, the profile of the second cam 400b along the second angular stroke can advantageously be adapted so that the second pawl imposes a constant torque, throughout the duration of said second stroke, on at least one toothed wheel, and in particular the second gear.
    Particularly advantageously, the first angular travel and the second angular travel have zero overlap, and their sum is equal to 360 °.
    Thus, during a complete revolution of the assembly formed by the first cam and the second cam around the axis YY ′, the at least one toothed wheel and the camshaft essentially rotate continuously with little or no d 'jerks.
    Still advantageously, the first angular travel and the second angular travel are each equal to 180 °.
    The combination of these two characteristics advantageously makes it possible to smooth, at least in part, the force exerted on the teeth of each of the first and second toothed wheels, and consequently, limit the stresses liable to damage and / or affect the reliability of the first and second gears. This arrangement also makes it possible to preserve as well as the camshaft as well as its drive system (geared motor).
    By way of example, a complete revolution around the axis YY ′ of the assembly formed by the first and second cams 400a and 400b induces the rotation of the first and second toothed wheels according to an angular stroke corresponding to a tooth of each of these two wheels.
    According to an advantageous embodiment, the first cam and the second cam can be arranged so that the activation of one and / or the other of the first and second pawls by the cam intended to activate it is directly preceded by a phase of engagement of said pawl by this same cam. An engagement phase includes pressing one or the other of the first and second pawl against a tooth, respectively, of the first gear or of the second gear according to an angular travel of engagement of the cam considered.
    Still according to an advantageous embodiment, the first cam and the second cam can be arranged so that the activation of one and / or the other of the first and second pawls by the cam intended to activate it is directly followed by 'a phase of disengagement of said pawl by this same cam, the disengagement phase comprising a reduction in the support of the pawl against the tooth according to a law of continuous decrease of said support according to an angular travel of disengagement of said cam.
    It is understood that the engagement and disengagement phases relate to a particular profile of one and the other of the first and second cams over a predetermined angular travel. These profile adjustments are within the reach of those skilled in the art and can in particular correspond to an increase and a decrease in the force exerted on the pawl.
    According to an advantageous embodiment, the first pawl holder 300a and the second pawl holder 300b are each in pivot connection with the main shaft 210 (FIG. 1).
    In particular, each pawl holder 300a and 300b comprises a slot in which the main shaft 210 is inserted. Such an arrangement makes it possible to give the transmission module the compactness necessary for its use in a reduced space.
    The first pawl holder 300a and the second pawl holder 300b may each be provided with a roller, called respectively, first roller 320a and second roller 320b (FIG. 1).
    The first and second rollers 320a and 320b allow in particular the respective activations of the first and second pawls 310a and 310b. In particular, the first cam 400a and the second cam 400b act, respectively, on the first roller 320a and on the second roller 320.
    In operation, the first cam 400a abuts against the first roller 320a at its contour, called the first contour. Thus, during its rotation according to the first angular stroke, the first cam 400a pushes the first roller 320a and consequently activates the first pawl 310a (because the first roller and the first pawl are integral with the same pawl holder).
    The second cam 400b abuts against the second roller 320b at its contour, called the second contour. Thus, during its rotation according to the second angular stroke, the second cam 400a pushes the second roller 320b and consequently activates the second pawl 310b (because the second roller and the second pawl are integral with the same pawl holder).
    FIGS. 4a to 4g are schematic representations of the different operating sequences of the transmission module in its entirety, according to a profile view, and in particular according to a profile view allowing the observation of the first wheel, the first pawl and the first cam.
    FIGS. 5a to 5g are schematic representations according to operating sequences of the transmission module identical, respectively, to FIGS. 4a to 4g, and also according to an identical profile view, the mechanism associated with the first wheel, with the first pawl and with the first cam being however removed so as to allow the observation of the second wheel, the second pawl and the second cam.
    FIGS. 4a to 4b correspond to a phase of engagement of the first pawl 310a against a tooth of the first toothed wheel 200a. In this regard, the profile of the first cam 400a associated with an engagement phase comprises a section, essentially, planar over a predetermined angular travel of said cam, for example 38 ° (Zone “A” in FIG. 6).
    During this phase, the first pawl 310a rises rapidly in contact with a tooth of the first toothed wheel 200a, so as to make up for any play between the tooth and the first pawl 310a. In parallel with this phase of engagement of the first pawl, the second cam 400b ends its second angular stroke during which the second pawl 310b is activated (FIGS. 5a and 5b).
    FIGS. 4b to 4e correspond to a phase in which the first pawl 310a is activated by the first cam 400a during the first angular stroke. The cam profile associated with this phase can for example correspond to a divergent spiral profile, for example over a first angular travel of the order of 180 ° (Zone "B" in FIG. 6).
    This first angular travel also begins with a phase of disengagement of the second pawl 310b (FIGS. 5b and 5c) according to an angular travel for example of 55 °.
    During this disengagement phase, the support of the second pawl 310b on the tooth of the second gear 200b decreases until it is canceled.
    The disengagement phase of the second pawl 310b can be directly followed by a rest phase (Figures 5c and 5d) of said pawl during which the latter no longer drives the second wheel and jumps onto the next tooth.
    Finally, this rest phase is in turn followed by an engagement phase of the second pawl 310b (Zone “C” in FIG. 6, and FIGS. 5d and 5e). The terms of the engagement phase of the second pawl 310b and of the activation phase of the first pawl 310a are, advantageously, concomitant.
    The engagement phase of the second pawl 310b is directly followed by the disengagement phases of the first pawl 310a (area "D" in Figure 6, and Figures 4e and 4f), and activation of the second pawl 310b (area "E" in Figure 6, Figures 5e to 5g). The disengagement phase of the first pawl 310a corresponds to a reduction in the torque exerted by said pawl on the first wheel 200a so that the second pawl fully takes over the drive relay of the second wheel 200b (integral with the first wheel).
    Following the disengagement phase of the first pawl 310a, there follows, successively, for the first pawl 310a, a rest phase (zone “F” in FIG. 6, and FIGS. 4f and 4g) and, after a jump to the next tooth, again an engagement phase (zone “G” in FIG. 6, and FIG. 4f) which ends, simultaneously with the activation phase of the first pawl.
    The operating sequence proposed above makes it possible to ensure the continuity of training of the first and second toothed wheels while minimizing, or even canceling, any jerks likely to occur, in particular on said first and second toothed wheels. The absence of jerks makes it possible to preserve the mechanical integrity of the entire force transmission module, and in particular the camshaft.
    This operating mode therefore makes it possible to ensure the mechanical durability of the module, and thus to increase its reliability.
    The transmission module described in the present invention is then advantageously implemented in a control mechanism of an electrical appliance (for example of power cut), of the circuit breaker or disconnector switch type (FIG. 2). More particularly, the transmission module can be used to compress / reset the closing / opening spring of the electrical device.
    REFERENCES [1] EP 2,269,772 [2] US 4,423,649
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    1. Transmission module (100) of an effort comprising:
    - at least one toothed wheel (200) fixedly connected to a main shaft (210) extending along a main axis XX ';
    - at least a first pawl holder (300a) and a second pawl holder (300b) provided, respectively, with a first pawl (310a) and a second pawl (310b), each of the first pawl (310a) and second pawl (310b) being arranged to, when activated, drive the toothed wheel in rotation in a direction, called direct direction, around the main axis by pressing the pawl considered against a tooth of the toothed wheel;
    - At least two cams, fixedly connected to each other, called, respectively, first cam (400a) and second cam (400b) arranged to actuate, respectively, the first pawl (310a) according to a first angular stroke around an axis YY ' of the first cam (400a), and the second pawl (310b) according to a second angular travel around the axis YY 'of the second cam (400b), different from the first angular travel.
    [2" id="c-fr-0002]
    2. Module according to claim 1, wherein the first angular travel and the second angular travel have zero overlap, and their sum is 360 °.
    [3" id="c-fr-0003]
    3. Module according to claim 1 or 2, wherein the first angular travel and the second angular travel are each equal to 180 °.
    [4" id="c-fr-0004]
    4. Module according to one of claims 1 to 3, wherein the at least two cams are arranged so that the activation of one and / or the other of the first and second pawls (310b) by the cam intended to activating it is directly preceded by an engagement phase of said pawl by this same cam, the engagement phase comprising pressing the pawl considered against a tooth of the at least one toothed wheel (200) along a stroke angular engagement of said cam.
    [5" id="c-fr-0005]
    5. Module according to one of claims 1 to 4, wherein the at least two cams are arranged so that the activation of one and / or the other of the first and second pawls by the cam intended to activate it either directly followed by a phase of disengagement of said pawl by this same cam, the disengagement phase comprising a reduction in the support of the pawl against the tooth according to a law of continuous decrease of said support according to an angular travel of disengagement of said cam.
    [6" id="c-fr-0006]
    6. Module according to one of claims 1 to 5, wherein the first pawl holder (300a) and the second pawl holder (300b) are each in pivot connection with the main shaft (210).
    [7" id="c-fr-0007]
    7. Module according to one of claims 1 to 6, wherein the at least two cams are integral with a camshaft (410) extending along the axis YY 'essentially parallel to the main axis XX'.
    [8" id="c-fr-0008]
    8. Module according to one of claims 1 to 7, wherein the first pawl holder (300a) and the second pawl holder (300b) are each provided with a roller, called respectively, first roller (320a) and second roller (320b), against which abut along their contour, respectively, the first cam (400a) and the second cam (400b), the first cam (400a) and the second cam (400b) exerting the activation, respectively, of the first pawl (310a) and the second pawl (310b), respectively via the first roller (320a) and the second roller (320b), and their respective pawl holders.
    [9" id="c-fr-0009]
    9. Module according to one of claims 1 to 8, wherein the at least one toothed wheel (200) comprises a first toothed wheel and a second toothed wheel, advantageously identical, arranged to be driven in rotation, respectively, by the first pawl (310a) and the second pawl (310b).
    [10" id="c-fr-0010]
    10. Module according to one of claims 1 to 9, wherein a complete revolution around the axis YY 'of the assembly formed by the first and second cams induces the rotation of the at least one toothed wheel (200) according to an angular stroke corresponding to a tooth of the at least one toothed wheel (200).
    [11" id="c-fr-0011]
    11. Module according to one of claims 1 to 10, wherein the transmission module (100) comprises drive means in rotation about the axis YY 'of the at least two cams, the drive means advantageously comprise a motor or a crank.
    [12" id="c-fr-0012]
    12. Module according to one of claims 1 to 11, wherein the first pawl holder (300a) and / or the second pawl holder (300b) are also adapted to be operated manually.
    [13" id="c-fr-0013]
    13. Module according to one of claims 1 to 12, wherein the main shaft (210) comprises two ends of which at least one is intended to transfer a mechanical force to a mechanical accumulation system.
    [14" id="c-fr-0014]
    14. Module according to claim 13, wherein the mechanical accumulation system comprises a compression spring.
    [15" id="c-fr-0015]
    15. An electrical appliance comprising a force transmission module according to one of claims 1 to 14.
    类似技术:
    公开号 | 公开日 | 专利标题
    EP3561832B1|2020-08-19|Module for transmitting a force
    EP1437260B1|2006-03-22|Rear-view vehicle mirror pivotable on two axes
    EP2073228B1|2010-12-22|Compact control for medium- and high-voltage electric devices
    FR2923099A1|2009-05-01|ELECTROMECHANICAL ACTUATOR WITH SPRING SPIRE SPRING-TYPE MECHANICAL BRAKE
    WO2010040678A1|2010-04-15|Emergency stop device
    FR2835093A1|2003-07-25|ELECTRICAL SWITCHING APPARATUS PROVIDED WITH A MOTORIZED CONTROL AND METHOD FOR CONTROLLING SUCH AN APPARATUS
    CA2059133C|2001-10-02|Control device for the timed release of a mechanism
    EP2605256A1|2013-06-19|Operating device of the motor-drive of the contact closing device reset device in an electric protection apparatus and apparatus comprising same
    EP2189995B1|2012-02-08|Control of high- or medium-voltage electrical switchgear with improved double latching and associated arming method
    FR2611549A3|1988-09-09|Self-powered motorised shears
    EP2575150A1|2013-04-03|Motorization disengagement device of the reset device of the contact closing device in an electric protection apparatus and apparatus comprising same
    EP1993115B1|2012-12-12|Device for controlling the connection and disconnection of two parts and electrical appliance comprising such a device
    FR2778789A1|1999-11-19|Circuit breaker for low voltage AC electrical installations
    FR2571783A1|1986-04-18|Meshing control device of the starter gear for an internal combustion engine starter motor
    EP2073227B1|2010-11-24|Compact and robust control for medium- and high-voltage electric devices
    EP0801409B1|1999-03-17|Remote control interrupter
    CH716985A2|2021-06-30|Display change mechanism.
    WO2014083064A1|2014-06-05|Control device of the spring type particularly for a high-voltage or medium-voltage circuit breaker or switch
    EP0518768B1|1995-08-30|Switching device for electric household appliance programmer
    EP1394651A1|2004-03-03|Indexing device with repeatable and precise operation
    EP1670009A2|2006-06-14|Operation mechanism for a multipole switch
    FR2756320A1|1998-05-29|Drive mechanism and end-of-course detector for motor driven roller blinds
    EP2488921A1|2012-08-22|Energy source for a striking mechanism, and timepiece provided with such an energy source
    FR2706674A1|1994-12-23|Device for cutting off an electrical line with improved control means
    BE676837A|
    同族专利:
    公开号 | 公开日
    US10850957B2|2020-12-01|
    ES2823448T3|2021-05-07|
    EP3561832A1|2019-10-30|
    EP3561832B1|2020-08-19|
    US20190330032A1|2019-10-31|
    FR3080663B1|2020-05-22|
    CN110410478A|2019-11-05|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP2269772A2|2009-07-03|2011-01-05|Josef Bättig|Ratchet wrench with reinforced torque|
    US20130062175A1|2011-09-08|2013-03-14|Timothy Gordon Robirds|Electrical switching apparatus, and stored energy assembly and energy storage and release control mechanism therefor|
    US20160343520A1|2015-05-22|2016-11-24|Eaton Corporation|Electrical switching apparatus and stored energy assembly therefor|
    US2946563A|1955-10-14|1960-07-26|Eaton Lawrence Edward|Tension retaining binder|
    GB830545A|1956-01-09|1960-03-16|Legrand Pierre|Improvements in or relating to chain locking devices|
    GB1418013A|1972-06-16|1975-12-17|Kohler G|Drum winch|
    JPS643300B2|1983-04-12|1989-01-20|Fuji Electric Co Ltd|
    US4591029A|1984-08-17|1986-05-27|Da Foe John P|Load actuating braking apparatus|
    US4723757A|1986-04-11|1988-02-09|Durbin-Durco, Inc.|Ratchet-wheel-pawl assembly and release means for portable winch|
    US5020648A|1988-11-14|1991-06-04|Reliable Plastics Engineering Company|Ratchet assembly|
    US5458318A|1993-10-15|1995-10-17|Kci Konecranes International Corporation|Drum brake|
    SE503792C2|1995-03-22|1996-09-09|Henry Norrby|Implements for applying traction in straps|
    US6087610A|1997-05-28|2000-07-11|General Electric Company|Closing springs release mechanism for industrial-rated circuit breaker|
    US6494435B1|2000-03-21|2002-12-17|Denis G. Cauchon|Spring-loaded safety winch for load restraint system|
    US6726182B2|2001-01-17|2004-04-27|W. W. Patterson Company|Manual winch with dual locking dogs|
    KR100402110B1|2001-09-12|2003-10-17|주식회사 고려호이스트|safety device for air balancing hoist|
    US7686282B2|2008-05-30|2010-03-30|Amoss Trading Services, Inc.|Handle-operated brake/release mechanism for a cable drum winch|
    FR2983293B1|2011-11-28|2014-08-01|Schneider Electric Ind Sas|METHOD FOR EVALUATING THE MECHANICAL PERFORMANCE OF A CUTTING APPARATUS AND CUTTING APPARATUS FOR CARRYING OUT SAID METHOD|
    US9388026B2|2014-01-10|2016-07-12|Daniel Doig|Winch and method of use thereof|
    US10266377B2|2016-04-22|2019-04-23|Arcosa, Inc.|Winch tightening mechanism|
    US10737916B2|2016-06-20|2020-08-11|W. W. Patterson Company|Manual marine winch with safety loading handle and integrated locking dog release|CN110919581B|2019-12-11|2021-03-09|大连交通大学|Automatic bidirectional ratchet wheel tightening mechanism|
    CN111550502B|2020-05-12|2021-08-06|联想万像科技有限公司|Clutch and printer|
    法律状态:
    2019-04-29| PLFP| Fee payment|Year of fee payment: 2 |
    2019-11-01| PLSC| Search report ready|Effective date: 20191101 |
    2020-04-30| PLFP| Fee payment|Year of fee payment: 3 |
    2021-04-27| PLFP| Fee payment|Year of fee payment: 4 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1853683|2018-04-26|
    FR1853683A|FR3080663B1|2018-04-26|2018-04-26|STRESS TRANSMISSION MODULE|FR1853683A| FR3080663B1|2018-04-26|2018-04-26|STRESS TRANSMISSION MODULE|
    ES19167033T| ES2823448T3|2018-04-26|2019-04-03|Effort transmission module|
    EP19167033.0A| EP3561832B1|2018-04-26|2019-04-03|Module for transmitting a force|
    US16/374,092| US10850957B2|2018-04-26|2019-04-03|Effort transmission module|
    CN201910332548.9A| CN110410478A|2018-04-26|2019-04-24|Power transfer module|
    [返回顶部]