Lock / unlocking mechanism in electric lock and electric lock

Abstract

To combine members constituting a planetary gear mechanism together with a torque limiter to thereby cause the members constituting the planetary gear mechanism and the torque limiter to rotate in unison and in a smooth manner.SOLUTION: A planetary gear component, a torque limiter, and a planet carrier constituting the planetary gear component that engages with the torque limiter are rotatably assembled between a first gear component 11 on an input side that receives a driving force of an electric motor 7 and a second gear component 15 on an output side that transmits power to a locking piece 5; when unlocking, if a load is applied to the locking piece, an internal gear 13 constituting the planetary gear component rotates in the reverse direction, causing the internal gear to abut against a stopper portion 8a provided in a lock box 2; when a holding force of the torque limiter is released or slips against the holding force of the torque limiter, the planet carrier and the second gear component on the output side that cooperates with the planet carrier to rotate in an unlocking direction.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to an unlocking mechanism for an electric lock and an electric lock, and more particularly to an unlocking mechanism for an electric lock. [Background technology]

[0002] Patent Document 1 is an invention proposed to the Office by the applicant. As shown in Figures 1, 3 and 4, the prior art invention has arm-shaped power transmission members 65, 67 and a biasing spring 119 interposed between a driving member 61 that rotates by the driving force of an electric motor 127 and a driven member 63. The driving member 61 is a member that is driven to rotate via the output shaft 129 on the electric motor 127 side and a transmission gear, and therefore corresponds to the first gear-forming member on the input side of the present invention. On the other hand, paragraph 0030 describes, along with Figure 1, that the segment gear 49 formed on the outer periphery of the dead drive gear 47 as the dead drive part meshes with a gear 125 fixedly provided in the approximate center of the driven member 63. Therefore, the dead drive gear 47 corresponds to the second gear component on the output side of the present invention.

[0003] Paragraph 0034, together with Figure 5, describes that the drive member 61 and the driven member 63 have locking arm surfaces 85 of protrusions formed on the opening and closing ends of arm-shaped power transmission members (first and second clutch arms) 65, 67, which engage with and disengage from a pair of left and right inclined surfaces 83 formed in a recess on one side of the drive member 61.

[0004] Therefore, the arm-shaped power transmission members 65, 67 can be said to correspond to a part of the drive key that constitutes the torque limiter of the present invention. The problems of the prior art invention can be understood to be reducing the frequency of switching between forward and reverse rotation of the electric motor, eliminating the need for a detection means, simplifying the structure, etc. (paragraph 0006).The basic constituent element of the solution is "the interposition of arm-shaped power transmission members 65, 67, etc. between a driving member 61 that rotates by the driving force of the electric motor 127 and a driven member 63."

[0005] However, the prior art does not disclose, as with the present invention, how to rationally combine the components of the planetary gear mechanism with a torque limiter and torque limiter canceller, and how to improve the locking / unlocking performance of the forward / backward movement of the locking piece when a load is generated on the output side where the dead drive gear is located as viewed from the input side, using the components of the planetary gear mechanism, the torque limiter, and the torque limiter drive motor as a drive source. Furthermore, the prior art does not disclose how to rationally combine the components of the planetary gear mechanism with a torque limiter and torque limiter canceller, and how to rotate the components of the planetary gear mechanism, the torque limiter, and the torque limiter canceller smoothly and integrally. Therefore, Patent Document 1 describes, but does not suggest, the provision of a configuration in which "the internal gear that constitutes the planetary gear mechanism is fixed."

[0006] Although Patent Document 2 describes the specific configuration of the power transmission mechanism in an electric lock, like Patent Document 1, it describes and does not suggest the "problem of the present invention" and the "unlocking mechanism including a torque limiter, torque limiter canceller, etc."

[0007] Patent Document 3 describes a clutch mechanism for an electric lock (claim 1). As shown in Figs. 1, 3, 4, etc., this known clutch mechanism is a clutch mechanism Y of an electric lock X having a clutch gear 11 that transmits the driving force of a drive motor 2 controlled by a control unit 1 to a daruma 5 side, in which a clutch member is constituted by an engaging pawl that engages and disengages with ratchet teeth 16 in an annular recess 15 formed in the clutch gear 11, and a latch plate 21 that fits into the annular recess and supports the engaging pawl 28, and one end of the engaging pawl 26 is connected to the clutch plate 21 via a linking means. When the clutch gear 11 receives a driving force from the drive motor 2 and rotates in a predetermined direction, the other end of the engaging pawl 26 engages with the ratchet teeth 16, causing the clutch plate 21 to rotate together with the clutch gear 11. On the other hand, when an operating force from the daruma 5 side is transmitted to the clutch plate 21 via the drive arm 4, the other end of the engaging pawl 26 does not engage with the ratchet teeth 16, causing the clutch plate 21 to rotate at least a required amount. Note that the clutch mechanism is described in, for example, Japanese Patent Application Laid-Open No. 2002-168014, as well as the above-mentioned Patent Document 3 and Japanese Patent Application Laid-Open No. 2006-138072 proposed by the patent applicant to the Office. However, neither Patent Document 2 nor Japanese Patent Application Laid-Open No. 2002-168014 discloses a rational combination of the components of the planetary gear mechanism with a torque limiter or the like. Incidentally, Patent Document 4 describes a technology that employs components constituting a planetary gear mechanism (referred to in Patent Document 4 as a planetary gear set 600) in an electric thumb turn (referred to in Patent Document 4 as a smart lock) that is attached to a fixture door. The title of the invention in Patent Document 4 is a "gear assembly," and this gear assembly comprises the planetary gear set 600 (FIG. 6) and a clutch. Therefore, when referring to the specification and drawings regarding "what" the clutch is, it can be understood that it is an "electromechanical solenoid" from the descriptions in paragraphs 0013, 0018, 0019, and FIGS. 6 and 8, for example.

[0008] Additionally, as shown in FIG. 8B, when the engagement rod (movable armature 802) of the electromechanical solenoid using the planetary gear set 600 in Patent Document 4 expands due to the spring force of the biasing spring, it engages with the engagement portion 612 formed on the disk-shaped upper surface of the carrier 604 constituting the planetary gear set 600 in the radial direction (engagement step 0019 in automatic mode). On the other hand, FIG. 8A shows the opposite: when the engagement rod contracts, it disengages from the engagement portion 612 of the carrier 604. Patent Document 4 uses the solenoid's engagement rod (movable armature 802) as a clutch, as described above, but does not describe or suggest any specific configuration other than the clutch that controls the extension and retraction of the engagement rod. Furthermore, unlike the present invention, there is no mention of how to deal with the situation in which lateral pressure is applied to the side of the locking piece through the door due to an external factor when unlocking begins. Therefore, it is necessary to address the problems of Patent Document 4. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] Japanese Patent Application Laid-Open No. 2013-204367 [Patent Document 2] Patent No. 5139836 [Patent Document 3] Patent No. 4878964 [Patent Document 4] Japanese Patent Application Publication No. 2018-28259 Summary of the Invention [Problem to be solved by the invention]

[0010] The primary objective of this invention is to rationally (easily) combine the components of the planetary gear mechanism with the torque limiter, thereby ensuring smooth operation of the planetary gear mechanism components, torque limiter, etc. The secondary objective is to improve the locking / unlocking performance of the locking lever when a load is applied to the output side, where the dead drive gear is located as viewed from the input side of the drive motor as the drive source. In particular, when an external factor applies lateral pressure through the door to the side of the locking lever (e.g., the side of a protruding deadbolt) at the start of unlocking, preventing the locking lever from retracting into the lock box, the planetary gear mechanism principle is used to return the locking lever to the unlocked position. Examples of such external factors include negative pressure inside the room, pressure on the door caused by a human hand pressing against a locked door during an evacuation, or a voltage drop due to long wiring distances between the control panel and the electric lock. [Means for solving the problem]

[0011] The unlocking mechanism in the electric lock of the present invention is characterized in that a planetary gear component (U), a torque limiter (31), and a planet carrier (16) constituting the planetary gear component that engages with the torque limiter are rotatably assembled between a first gear component (11) on the input side that receives the driving force of the electric motor (7) and a second gear component (15) on the output side that transmits power to the locking piece (5), and when unlocking, when a load is applied to the locking piece, the internal gear (13) constituting the planetary gear component rotates in the reverse direction, causing the internal gear to abut against a stopper portion (8a) provided in the lock box (2), and the holding force of the torque limiter is released or slips against the holding force of the torque limiter, causing the planet carrier and the second gear component on the output side that cooperates with the planet carrier to rotate in the unlocking direction.

[0012] The above configuration further includes an internal gear (13) constituting the planetary gear component, which has continuous circumferential convex portions and concave portions that engage and disengage with the drive key (32) that constitutes the torque limiter, and a torque limiter canceller (12) provided at a position on one side of the internal gear, and when the torque limiter canceller abuts against a stopper portion (8a) provided in the lock box (2), the engagement state of the first engagement protrusion (32a) of the drive key is released and the planetary gear (26) slides on the upper surface wall of the circumferential convex portion of the torque limiter canceller and the upper surface wall of the circumferential convex portion of the internal gear that is arranged in a staggered pattern relative to the upper surface wall, causing the planetary carrier to rotate. The planetary gear further includes an internal gear (13) constituting the planetary gear component, and a torque limiter canceller (12) provided at one side of the internal gear, and when the torque limiter canceller (12) and the internal gear (13) are combined in the axial direction, a gap (S) for fine adjustment of the internal gear is formed between the end face of the approximately C-shaped engaging protrusion formed in the circumferential direction of the canceller and the approximately arc-shaped engaging protrusion formed in the circumferential direction of the internal gear. The planetary gear further includes an internal gear (13) constituting the planetary gear component, and a torque limiter canceller (12) provided at one side of the internal gear, and when the torque limiter canceller (12) and the internal gear (13) are combined together in the axial direction, a gap (S) is generated between both end faces of a thick, approximately arc-shaped engagement protrusion (13a) provided on the outer periphery of the internal gear and both end faces of a C-shaped thick portion (21b) of the canceller, allowing the position of the internal gear to be finely adjusted in the circumferential direction, and a pair of compression springs (19) are incorporated into the gap.

[0013] Furthermore, the electric lock includes an unlocking mechanism in the electric lock of claim 1, and the second gear component on the output side that constitutes the unlocking mechanism is engaged with a dead drive gear (21), and when unlocking, when the second gear component rotates, the dead drive gear rotates in the opposite direction to the second gear component, causing the locking piece to move backward into the lock box. [Effects of the Invention]

[0014] The planetary gear mechanism components and torque limiter are rationally (easily) combined between the first gear component on the input side and the second gear component on the output side that transmits power to the locking lever, allowing the planetary gear mechanism components and torque limiter to rotate smoothly and integrally around the central axis. Furthermore, when a load is applied to the output side, where the dead drive gear is located as viewed from the input side using a drive motor as the drive source, the locking / unlocking performance of the locking lever's forward / backward movement can be improved. In particular, if an external factor applies lateral pressure through the door to the side of the locking lever (for example, the side of a protruding deadbolt) when unlocking begins, preventing the locking lever from retracting into the lock box, the principle of the planetary gear mechanism can be used to return the locking lever to the unlocked position. [Brief explanation of the drawings]

[0015] 1 to 17 are explanatory views showing a first embodiment of the present invention. [Figure 1] 1 is a schematic front view of a locking / unlocking device for an electric lock according to a first embodiment (locked state). [Figure 2] FIG. [Figure 3] FIG. 2 is a schematic explanatory diagram of the members that make up the planetary gear mechanism (a sun gear provided on a first gear component 11, three planetary gears, an internal gear, and a planetary carrier). [Figure 4] FIG. 1 is an exploded perspective view of the components that make up the main part of the unlocking mechanism (the same applies to the locking mechanism) (the first gear component 11 is depicted in the foreground on the left). [Figure 5] 5 is an exploded perspective view showing the components of the main part shown in FIG. 4 from the opposite side (the first gear component 11 is drawn on the right). FIG. [Figure 6] In Figure 4, this is a perspective view of the torque limiter (in an assembled state), the torque limiter canceller 12 and the internal gear 13 (in an assembled state), and the planet carrier 16 that supports the planet gear 26, which are incorporated between the first gear component 11 and the second gear component 15 (not shown). [Figure 7] FIG. 7 is a perspective view of the state of FIG. 6 as seen from the opposite side. [Figure 8] FIG. 10 is an explanatory diagram of the second gear component 15 on the output side in the locked position (the planetary carrier is in the neutral position). [Figure 9] FIG. 9 is an explanatory diagram from a front view based on FIG. 8. [Figure 10] FIG. 9 is an explanatory diagram taken along line AA in FIG. 8. [Figure 11] FIG. 9 is an explanatory diagram taken along line BB in FIG. 8. [Figure 12] FIG. 9 is an explanatory diagram taken along line CC in FIG. 8. [Figure 13] Flowchart-like schematic diagram 1 of normal operation. [Figure 14] 2 is a flow chart-like schematic explanatory diagram following Figure 13. [Figure 15] Flowchart-like schematic diagram 1 for when under high load. [Figure 16] 2 is a flow chart-like schematic explanatory diagram following Figure 15. [Figure 17] 1 is a schematic front view of a locking / unlocking device for an electric lock according to a first embodiment (unlocked state). DETAILED DESCRIPTION OF THE INVENTION

[0016] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a front view of a locking / unlocking device for an electric lock. Note that an electric lock generally has a control unit for rotating the drive motor forward and backward inside the lock box, but this is omitted in Fig. 1. A power source (secondary battery) is also provided appropriately inside or outside the lock box, but is also omitted.

[0017] Electric locks generally have both the functions of "manual locking and unlocking" and "automatic locking and unlocking" using the driving force of an electric motor. The same is true for the electric lock X of this embodiment. Here, the various components required for manual locking and unlocking operations, such as the daruma holder, daruma, stopper that restricts the rotation range of the daruma (locking and unlocking range), and transmission gears on the daruma side that rotate by the operating force of the cylinder lock or thumb turn, are not shown and will only be briefly described.

[0018] Meanwhile, in relation to the problem to be solved by the invention, the "unlocking mechanism Y in the electric lock" will be specifically explained with reference to the drawings. Note that the locking mechanism using the electric motor 7 operates in the opposite manner to the unlocking mechanism.

[0019] Now, the components required for the power transmission mechanism (especially the unlocking mechanism Y) that transmits the driving force of the electric motor 7 are as shown in Figure 1. In the electric lock X in Figure 1, first, 1 is the door of the fixture, 2 is the lock box, 3 is the front back plate, and 4 is the front plate. These are well known, so a detailed explanation will be omitted.

[0020] Next, reference numeral 5 denotes a locking piece, which may be, for example, a deadbolt 5a and a kama-dead 5b interlocked with it. The locking piece 5 moves forward and backward relative to the front panel 4 as a result of the rotational drive of the deadbolt drive gear 21. When viewed from the first gear member 11 on the output member side of the electric motor 7, the locking piece 5 corresponds to the final operating member on the output side. In this embodiment, the locking piece 5 is a "deadbolt 5a" and a "kama-dead 5b" interlocked with it, but it may be either the deadbolt 5a or the kama-dead 5b. The deadbolt 5a is guided by a horizontal guide (horizontal elongated hole, horizontal guide rod, etc.) provided or formed on the opposing inner wall surface of the lock box 2. The kama-dead 5b is supported rotatably around the kama-dead shaft 6.

[0021] Here, we will explain the "manual locking / unlocking operation." The manual locking / unlocking operation mainly consists of a daruma receiver, a daruma as the manual driving member, and a daruma-side transmission gear that rotates when the cylinder lock or thumb turn is operated. The daruma is rotatably supported in a daruma bearing hole. The daruma has fan-shaped engaging teeth (daruma gear) on its outer periphery. A tailpiece, which is the output member of the cylinder lock, engages with the daruma hole. A thumbturn is provided on the door 1 on the opposite side of the cylinder lock. The output member of the thumbturn also engages with the daruma hole, just like the tailpiece. As will be described later, the locking piece 5 moves forward and backward by the driving rotation of a deadbolt drive gear that has a drive arm as the driving member on the electric motor side.

[0022] In Figure 1, a dead drive gear 21 is rotatably supported on a shaft 22 in the approximate center of the lock box 2. The dead drive gear 21 can rotate clockwise and counterclockwise around the shaft. The dead drive gear 21 is rotated by the driving force of the electric motor 7. 1 shows the locked state in which the locking piece 5 is fully extended. In the locked state, the drive arm 21a extending radially outward of the deadbolt drive gear 21 presses against the inclined front seat of the deadbolt 5a. The fan-shaped engagement teeth 21b on the opposite side of the drive arm mesh with the second gear component 15 on the output side, which will be described later.

[0023] Next, the "unlocking mechanism Y in an electric motor" will be described. The unlocking mechanism Y has an electric motor 7 fixed inside the lock box 2. In FIG. 1, the electric motor 7 is installed at an angle at a position above and to the right of the fan-shaped engaging teeth 21b of the dead drive gear 21 via the motor case 8. In this embodiment, a stopper portion 8a is provided at an appropriate position on the motor case 8 to receive the protrusion of a torque limiter canceller 12 (described later) when it rotates (see FIG. 15). This stopper portion 8a may be provided near the torque limiter canceller (hereinafter also referred to as "canceller 12") on the inner wall surface of the lock box 2. For example, a small diameter transmission gear (worm gear) 10 is interposed between the protruding output shaft (worm) 9 of the electric motor 7 arranged at an angle and a large diameter first gear component 11 on the input side having a gear around its entire circumference.

[0024] In Fig. 1, a canceller 12 is rotatably combined in a recess formed in one side surface (the side surface on the near side) of the first gear component 11. Furthermore, an internal gear 13, which is a component of a planetary gear mechanism, is combined with the canceller 12 so as to be able to rotate relatively thereto. In the embodiment, when the canceller 12 and the internal gear 13 are combined in the axial direction, a gap S for fine adjustment of the internal gear is created between the end face of a substantially C-shaped engagement protrusion formed in the circumferential direction of the canceller 12 and a substantially arc-shaped engagement protrusion formed in the circumferential direction of the internal gear 13 (see Fig. 7).

[0025] The gap S for fine adjustment of the internal gear is intended to ensure that the upper wall surface of the convex portion of the canceller 12 and the upper wall surface of the circumferential convex portion of the internal gear 13 are continuously aligned in a zigzag pattern, as will be described later. Furthermore, in Figure 1, the output-side second gear component 15 can be seen on the near side, rotatably supported on a horizontal central axis 14 perpendicular to the wide side of the lock box 2.

[0026] A planet carrier (hereinafter referred to as "carrier"), a component of the planetary gear mechanism, is rotatably supported on the back side of the second gear component 15. A magnetic sensor 41 for detecting a locking signal is attached to a protrusion that protrudes radially outward from the outer periphery of the second gear component 15, while a magnetic sensor 42 for detecting a clutch neutral position is attached to a protrusion that protrudes radially outward from the outer periphery of the carrier 16. Detection signals from the detection means 41 and 42 are sent to a control unit (not shown), which controls the drive of the drive motor 7 as appropriate. In Figure 1, the total of three planetary gears and torque limiters (e.g., three drive keys and three drive springs) rotatably supported on the carrier 16 are not shown, so they are shown in an exploded perspective view (see, for example, Figures 4 and 5).

[0027] Referring to other drawings together with Figure 1, the "unlocking mechanism Y for an electric motor" of the embodiment rotatably incorporates a planetary gear component U (a sun gear 25 fixedly provided at the center of the first gear component 11, a carrier 16 that supports the planetary gears 26 that mesh with the sun gear, and an internal gear 13 that meshes with the planetary gear), a torque limiter 31, a canceller 12 that has convex portions and concave portions continuously formed on its inner surface so as to engage and disengage with a plurality of drive keys 32 that constitute the torque limiter, and the carrier 16 that constitutes the planetary gear component U that is always engaged with the second engagement protrusion 32b of the drive key 32 of the torque limiter and is capable of engaging and disengaging with the first engagement portion 32a of the drive key 32, between a large-diameter first gear component 11 on the input side that receives the driving force of the electric motor 7 and a second gear component 15 on the output side that transmits power to the deadbolt 5a that serves as the locking piece 5.

[0028] The electric lock X has the unlocking mechanism Y built into the lock box 2, and the second gear component 15 on the output side is engaged with the dead drive gear 21, which can also be used to lock and unlock the locking piece 5 by manual locking and unlocking operations.

[0029] In an embodiment, as will be described later, when the locking piece 5 protrudes from the front panel 4 of the lock box 2 during locking and a load is applied to the locking piece 5 through the door 1, the planetary carrier 16 and the canceller 12 rotate in the opposite direction with the canceller 12 colliding with the stopper portion 8a provided on the lock box side, thereby disengaging the multiple first engaging protrusions 32a of the drive key 32 of the torque limiter 31 at the required position, and in this state the multiple planetary gears 26 slide alternately on the upper wall surface of the circumferential convex portion of the canceller 12 and the upper wall surface of the circumferential convex portion of the internal gear 13 arranged in a zigzag pattern against the upper wall surface, and as a result the carrier 16 and the second gear component 15 on the output side that cooperates with the carrier rotate together in the unlocking direction (see Figure 16).

[0030] <Planetary gear component U> A planetary gear mechanism, as a generally known technology, typically includes a sun gear, a plurality of planetary gears (e.g., three) that mesh with the sun gear, a planet carrier that rotatably supports the planetary gears, and an internal gear that meshes with the planetary gears. It is also known that if either the sun gear or the internal gear is not fixed, the three planetary gears revolve around the sun gear as the sun gear rotates, while if the internal gear is fixed, the three planetary gears are forced to rotate in reverse. The embodiments utilize the principle of such a planetary gear mechanism.

[0031] Therefore, first, the members that make up the planetary gear mechanism will be described with reference to Figures 3, 13, etc. In this embodiment, first, the sun gear 25 is fixedly attached to the shaft cylinder portion 11a of the first gear component member 11.

[0032] Therefore, the sun gear 25 rotates in the same direction as the first gear component 11 around the central axis 14 provided in the lock box 2. Next, the three planetary gears 26 are rotatably supported on three support shafts 16a of the planetary carrier 16. Therefore, the three planetary gears 26 can revolve. Furthermore, the internal gear 13 can rotate in cooperation with the three planetary gears 26, but can also be stopped (fixed) by an external factor. In the latter case, due to the principle of the planetary gear mechanism, the planetary gears 26 rotate in the opposite direction (change direction).

[0033] <First gear component 11 and second gear component 15> The first gear component 11 on the input side corresponds to the driving member when viewed from the electric motor 7 side. The first gear component 11 as the driving member has a shaft hole formed in the center of its disk shape, and engagement teeth 11b formed all around its outer periphery. A recess is also formed on one side of the disk shape. Referring to the perspective view of FIG. 5, a stepped shaft cylinder portion 11a having a through hole communicating with the shaft hole is formed in the center and protrudes in the axial direction. A sun gear 25 that constitutes the planetary gear mechanism U is fixed to the stepped shaft cylinder portion 11a. Therefore, because the first gear component 11 and the sun gear 25 are integral, the first gear component 11 and the sun gear 25 are driven to rotate in the same direction around the central axis 14 on the lock box 2 side. For example, when the first gear component 11 rotates clockwise by the driving force of the electric motor 7, the sun gear 25 also rotates clockwise.

[0034] On the other hand, the second gear component 15 on the output side corresponds to a driven member when viewed from the perspective of the first gear component 11 on the input side. Note that, when viewed from the perspective of a manually operated member such as a thumb turn, the second gear component 15 on the output side corresponds to a driving member.

[0035] The second gear component 15 is located on the opposite side of the input side of the first gear component 11. The second gear component 15 is formed in a disk shape with a smaller radius than the first gear component 11, and has a shaft hole in its center that is supported by the central shaft 14 on the lock box side.

[0036] Although detailed explanations will be omitted, the disk-shaped first gear component 11 has a segment gear 15a formed on part of its outer periphery, and the segment gear 15a engages with the fan-shaped engaging teeth (segment gear) 21a of the dead drive gear 21 as shown in Figure 1.

[0037] Furthermore, an arc-shaped engaging protrusion 15b is formed on one side surface of the disk-shaped first gear component 11, as shown in Figures 1 and 14, for example, and both circumferential end surfaces of the arc-shaped engaging protrusion 15b can abut against an arc-shaped engaging protrusion 16b formed on the other side surface of the carrier 16.

[0038] <Relationship between the canceller 12 and the internal gear 13> For example, as shown in Figures 4 and 5, the canceller 12 is an annular body having a ring-shaped thin portion 12a and a C-shaped thick portion 12b, with an engaging protrusion 12c formed on a portion of the outer periphery of the ring-shaped thin portion 12a. Also, referring to Figure 4, an annular portion 12d, which is the same size as or slightly smaller than the ring-shaped thin portion 12a, is integrally formed on one side of the front side of the ring-shaped thin portion 12a (the peripheral surface opposite the approximately C-shaped thick portion 12b), and recesses and protrusions are formed continuously on the inner peripheral surface of the annular portion or the ring-shaped thin portion 12a. Here, the upper surface of the protrusion of the canceller 12 is referred to as "upper wall surface a" for convenience. Meanwhile, the upper surface of the protrusion on the inner peripheral surface of the internal gear 13 is referred to as "upper wall surface b" for convenience.

[0039] To explain further, in this embodiment, for example, as shown in Figures 6 and 7, a ring-shaped internal gear 13 is slidably fitted on the inner peripheral surface of the C-shaped thick portion 12b. When the annular canceller 12 and the ring-shaped internal gear 13 are axially integrated as shown in Figure 2, a gap S is generated between both end faces of the thick arc-shaped engagement protrusions 13a provided on the outer periphery of the internal gear 13 and both end faces of the C-shaped thick portion 12b of the canceller 12, allowing for fine adjustment of the position of the internal gear 13. A pair of compression springs 19 are incorporated into the gap S (see Figure 12). As mentioned above, a magnetic sensor 41 for a locking signal is attached to a protrusion protruding radially outward from the outer periphery of the second gear component 15 (see Figure 1).

[0040] <Composition of Career 16> 4 and 6, the carrier 16 is also formed in a disk shape with a shaft hole in its center, and support shafts 16a for the planetary gears 26 are integrally provided concentrically with the shaft hole at predetermined intervals. Referring to FIG. 4, one side of the disk-shaped carrier 16 is provided with a total of three support shafts 16a spaced at predetermined intervals in the circumferential direction, and symmetrical support protrusions 16b each having a bent fingertip are provided between each of the support shafts 16a. Radial long grooves 17 are formed on the opposing surfaces of the symmetrical support protrusions 16c. As shown in FIG. 13, radial finger-shaped second engagement protrusions 32b provided on each of the three driver keys 32 constituting the torque limiter 31 are constantly engaged with the radial long grooves 17.

[0041] As described above, the other side of the disk-shaped carrier 16 is provided with an outer arc-shaped engagement protrusion 16b that can engage with the inner arc-shaped engagement protrusion 15b of the output-side second gear component 15. As described above, the carrier 16 has a magnetic sensor 42 for detecting the clutch neutral position attached to a small, angle-shaped protrusion on the radially outward side (see FIG. 1).

[0042] <Torque Limiter 31> In this embodiment, a torque limiter 31 is provided between the first gear component 11 and the carrier 16, engaging with the canceller 12 and the internal gear 13. The torque limiter 31 is made up of a total of three drive key springs 33. The first axial engaging protrusion 32a functions to transmit power to the canceller 12 and the internal gear 13.

[0043] Therefore, each of these drive keys 31 has a first axial engagement protrusion 32a that simultaneously engages and disengages with a recess formed continuously in the circumferential direction of the canceller 12 and a recess formed continuously in the circumferential direction of the internal gear 13, and a second engagement protrusion 32b that always engages with a radial long groove 17 formed between each of a plurality of symmetrical engagement protrusions that form pairs in the circumferential direction of the carrier 16.

[0044] In a preferred embodiment, the torque limiter 31 exerts a holding force on the canceller 12 and the internal gear 13 when the first engagement protrusion 32a of the drive key 31 is simultaneously engaged with the recess of the canceller 12 and the recess of the internal gear 13. Depending on the embodiment, the canceller 12 may not be present. In such a case, the torque limiter 31 exerts a holding force when the first engagement protrusion 32a of the drive key 32 is engaged with the recess of the internal gear 13.

[0045] <Flowchart-like overview> The operating modes during normal operation and high load will be described in detail with reference to Figures 13 to 16. Figures 13 and 14 are schematic explanatory diagrams of the operating modes during normal operation. Figure 14 is an explanatory diagram following Figure 13.

[0046] First, in Figure 13, S1 indicates a state where there is no load on the deadbolt. Now, let's assume that the driving force of the drive motor causes the first gear component 11 on the input side to rotate in the clockwise direction indicated by the arrow. Since the internal gear 11 is not fixed, according to the principle of the planetary gear mechanism U, the three planetary gears 26 revolve in the same direction (clockwise) around the sun gear 25 of the first gear component 11.

[0047] Therefore, the canceller 12 also rotates in the same direction (clockwise). At this time, as shown in S2, the first axial engagement protrusion 32a of the drive key 32 of the torque limiter 31 simultaneously engages with the recesses of the canceller 12 and the internal gear 13 in the axial direction (exerting a holding force), regardless of the presence of a pair of compression springs for fine adjustment of the internal gear 13, which will be described later.

[0048] In S2, for ease of understanding, the recess in the canceller 12 and the recess in the internal gear 13 are drawn side by side, but the two recesses overlap in the axial direction (front-to-back direction). Also, the little finger-shaped first engagement protrusion 32b in the radial direction of the drive key 32 engages with the long groove 17 in the radial direction between the pair of support protrusions 16c. S3 indicates that the torque limiter 31, canceller 12, and internal gear 13 can rotate clockwise integrally.

[0049] 14, when the trick limiter 31, canceller 12, and internal gear 13 rotate clockwise, as described above, the second engagement projection 32b of the drive key 31 engages with the long groove 17 of the carrier 16, so the carrier 16 also rotates clockwise in the same manner as the components 31, 12, and 13. At this time, the canceller 12 is designed so that it does not collide with the stopper portion 8a on the lock box 2 side.

[0050] Furthermore, while the carrier 16 is rotating clockwise, its outer arc-shaped engagement protrusion 16b abuts against the inner arc-shaped engagement protrusion 15b of the second gear component 15 on the output side, causing the second gear component 15 to rotate clockwise as indicated by the arrow (S4).

[0051] In S5, the segment gear 15a of the second gear component 15 is engaged with the fan-shaped engaging teeth (segment gear) 21b of the deadbolt drive gear 21 as shown in Figure 1, causing the deadbolt drive gear 21 to rotate counterclockwise as indicated by the arrow. As a result, in S5 and S6, the deadbolt 5a is pressed by the drive arm 21a of the deadbolt drive gear 21 and retracts into the lock box 2.

[0052] Next, Figures 15 and 16 show the operation mode under high load. Figure 16 is a schematic explanatory diagram following Figure 15.

[0053] First, in Figure 15, S7 is the state where the deadbolt is under load. In addition, S7 is the state where, when unlocking begins, lateral pressure is applied to the side of the locking tab (for example, the side of the protruding deadbolt) through the door due to an external factor, and as a result, the locking tab 5 does not retract into the lock box 2.

[0054] In S8, the first gear component 11 on the input side starts to rotate clockwise as in S1, but when the drive arm 21 of the dead drive gear 21 hits the inclined rear seat of the deadbolt 5a, the deadbolt 5a does not move, so a load is applied to the second gear component 15 on the output side, and the second gear component 15 does not move.

[0055] In S9, the clear 16 rotates slightly clockwise during the unlocking drive, but stops when its outer arc-shaped engagement protrusion 16b hits the inner arc-shaped engagement protrusion 15b of the second gear component 15. In addition, the clear 16 rotates until it hits the second gear component 15, but the second gear component 15 does not move, so it is fixed in a predetermined position. At S10, the curia 16 is in a stopped state, so the three planetary gears 26 are supported by the support shaft of the curia 16 at that position according to the principle of the planetary gear mechanism U, and rotate in the reverse direction of the arrow at that position (they are in a forced rotation state).

[0056] As a result, the internal gear 3 and canceller 12 rotate counterclockwise (S11), despite the presence of the torque limiter 31. In S12, the canceller 12, which has rotated in the reverse direction by the required amount via the three planetary gears 26, comes to a halt when its engagement protrusion 12c hits a stopper portion 8a provided at an appropriate location (for example, the motor case 8) inside the lock box 2. At that moment, in S12, the canceller 12 has come to a halt, and the internal gear 11 begins to move, attempting to shift by half a pitch in its circumferential direction, due to the return action of the spring forces of the pair of left and right compression springs 19, resulting in a disengagement phenomenon between the planetary gears 26 and the convex and concave portions of the internal gear.

[0057] As a result, the first engagement protrusions 32a of the three drive keys 32 completely retract radially inward from the recesses of the internal gear against the biasing force of their driver springs 33. In addition, the axial first engagement protrusions 32a simultaneously disengage from the recesses of the canceller 12 and the internal gear 13. At this time, the radial second engagement protrusions 32b remain engaged with (do not disengage from) the radial long grooves of the carrier 16.

[0058] In S14, the convex portion of the internal gear 11 is shifted by half a pitch in the circumferential direction relative to the convex portion of the canceller 12, so that the concave portion of the torque limiter 31 disappears (as if only the convex portion remained), and the "upper wall surface a" of the convex portion of the canceller 12 and the "upper wall surface b" of the convex portion of the internal gear 13 are staggered in the circumferential direction. Therefore, the inner peripheral wall of the torque limiter 31 becomes smooth. To explain technically, when the internal gear 11 is fixed, the curia 16 increases its torque and starts to rotate clockwise. At this time, the curia 16 no longer has the recess of the torque limiter 31, so the rotational resistance is reduced and torque loss is also reduced (torque switching, so to speak).

[0059] S15 is the same as S13 during normal operation, and thereafter, the members 31, 12, and 13 rotate together in the unlocking direction, and then the second gear component member 15 on the output side also rotates in the unlocking direction, resulting in the state of step 6 during normal operation. [Industrial Applicability]

[0060] The present invention can be used in the field of electric locks that are attached to the opening and closing bodies of building fixtures, etc. [Explanation of symbols]

[0061] X...electric lock, Y... Electric motor unlocking mechanism, 1...door of building material, 2...lock box, 3...front back panel, 4...front panel, 5...locking piece, 5a...deadbolt, 7...electric motor, 8...motor case, 8a...stopper portion, 9...protruding output shaft (worm), 10...Transmission gear (worm gear), 11...first gear component on input side, 11a...shaft cylinder portion, 11b...engaging teeth, 12... Torque limiter canceller (Canceller 12), a...upper wall surface of the convex part of the canceller 12, 12a... ring-shaped thin-walled part, 12b...C-shaped thick portion, 12c...engagement protrusion, 12d...annular portion, S...Gap, U...planetary gear component, 13... internal gear, 13a... arc-shaped engagement protrusion, 25...sun gear, 26...planet gear, 14...center shaft, b...upper wall surface of the convex portion of the internal gear 13, 15... second gear component on the output side, 15a...segment gear, 15b...inner arc-shaped engagement protrusion, 16...Planetary carrier (carrier 16), 16a...support shaft, 16b...arc-shaped engagement protrusion, 16c...outer support protrusion, 17...radial grooves, 18..., 19...Compression spring, 21...dead drive gear, 21a...drive arm, 21b...fan-shaped engaging teeth, 22…, 23…, 24…, 27…, 28…, 29…, 31...torque limiter, 32...Drive key, 32a...first engagement protrusion, 32b...second engagement protrusion, 33...Drive spring.

Claims

1. An electric lock unlocking mechanism characterized in that a planetary gear component (U), a torque limiter (31), and a planet carrier (16) constituting the planetary gear component that engages with the torque limiter are rotatably assembled between a first gear component (11) on the input side that receives the driving force of an electric motor (7) and a second gear component (15) on the output side that transmits power to the locking piece (5), and when a load is applied to the locking piece during unlocking, the internal gear (13) constituting the planetary gear component rotates in the reverse direction, causing the internal gear to abut against a stopper portion (8a) provided in the lock box (2), and the holding force of the torque limiter is released or slips against the holding force of the torque limiter, causing the planet carrier (16) and the second gear component (15) on the output side that cooperates with the planet carrier to rotate in the unlocking direction.

2. The unlocking mechanism for an electric lock of claim 1 further includes an internal gear constituting the planetary gear component having circumferentially continuous convex portions and concave portions that engage and disengage with the drive key (32) that constitutes the torque limiter, and a torque limiter canceller (12) provided at a position on one side of the internal gear, wherein when the torque limiter canceller abuts against a stopper portion (8a) provided in the lock box (2), the engagement state of the first engagement protrusion (32a) of the drive key is released and the planetary gear (26) slides over the upper surface wall of the circumferential convex portion of the torque limiter canceller and the upper surface wall of the circumferential convex portion of the internal gear that is arranged in a staggered pattern relative to the upper surface wall, causing the planet carrier to rotate.

3. The unlocking mechanism for an electric lock of claim 1 further includes an internal gear (13) constituting the planetary gear component and a torque limiter canceller (12) provided at one side of the internal gear, and when the torque limiter canceller (12) and the internal gear (13) are combined in the axial direction, a gap (S) for fine adjustment of the internal gear is created between the end face of the approximately C-shaped engaging protrusion formed in the circumferential direction of the canceller and the approximately arc-shaped engaging protrusion formed in the circumferential direction of the internal gear.

4. The unlocking mechanism for an electric lock of claim 1 further includes an internal gear (13) constituting the planetary gear component and a torque limiter canceller (12) provided on one side of the internal gear, and when the torque limiter canceller (12) and the internal gear (13) are combined together in the axial direction, a gap (S) is created between both end faces of a thick, approximately arc-shaped engaging protrusion (13a) provided on the outer periphery of the internal gear and both end faces of a C-shaped thick portion (21b) of the canceller, allowing the position of the internal gear to be fine-tuned in the circumferential direction, and a pair of compression springs (19) are incorporated into the gap.

5. An electric lock including an unlocking mechanism in the electric lock of claim 1, wherein the second gear component on the output side constituting the unlocking mechanism is engaged with a dead drive gear (21), and when unlocking, when the second gear component rotates, the dead drive gear rotates in the opposite direction to the second gear component, causing the locking piece to move backward into the lock box.

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