WO2023051602A1 - 电子锁传动结构、电子锁及机动车辆 - Google Patents

电子锁传动结构、电子锁及机动车辆 Download PDF

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Publication number
WO2023051602A1
WO2023051602A1 PCT/CN2022/122094 CN2022122094W WO2023051602A1 WO 2023051602 A1 WO2023051602 A1 WO 2023051602A1 CN 2022122094 W CN2022122094 W CN 2022122094W WO 2023051602 A1 WO2023051602 A1 WO 2023051602A1
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WO
WIPO (PCT)
Prior art keywords
electronic lock
gear
transmission
transmission structure
worm
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2022/122094
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English (en)
French (fr)
Inventor
王超
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Changchun Jetty Automotive Parts Co Ltd
Original Assignee
Changchun Jetty Automotive Parts Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Changchun Jetty Automotive Parts Co Ltd filed Critical Changchun Jetty Automotive Parts Co Ltd
Priority to EP22874986.7A priority Critical patent/EP4411094B1/en
Priority to JP2024600048U priority patent/JP3248330U/ja
Priority to US18/695,965 priority patent/US20240401671A1/en
Publication of WO2023051602A1 publication Critical patent/WO2023051602A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/32—Details of the actuator transmission
    • E05B81/34—Details of the actuator transmission of geared transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/26—Output elements
    • E05B81/28—Linearly reciprocating elements
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/54—Electrical circuits
    • E05B81/90—Manual override in case of power failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H1/222—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes
    • F16H1/225—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes with two or more worm and worm-wheel gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
    • G—PHYSICS
    • G07—CHECKING-DEVICES
    • G07C—TIME OR ATTENDANCE REGISTERS; REGISTERING OR INDICATING THE WORKING OF MACHINES; GENERATING RANDOM NUMBERS; VOTING OR LOTTERY APPARATUS; ARRANGEMENTS, SYSTEMS OR APPARATUS FOR CHECKING NOT PROVIDED FOR ELSEWHERE
    • G07C9/00—Individual registration on entry or exit
    • G07C9/00174—Electronically operated locks; Circuits therefor; Nonmechanical keys therefor, e.g. passive or active electrical keys or other data carriers without mechanical keys
    • G07C9/00944—Details of construction or manufacture
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/02—Power-actuated vehicle locks characterised by the type of actuators used
    • E05B81/04—Electrical
    • E05B81/06—Electrical using rotary motors
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/32—Details of the actuator transmission
    • E05B81/42—Cams
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02T90/10—Technologies relating to charging of electric vehicles
    • Y02T90/14—Plug-in electric vehicles

Definitions

  • the invention relates to the technical field of electronic lock manufacturing, and more specifically, to an electronic lock transmission structure, an electronic lock and a motor vehicle.
  • the driving device in this traditional electronic lock will generate friction due to the mutual matching between the transmission mechanisms and the change of circular rotation into linear motion, which greatly consumes electric energy and motor torque, and not only leads to the short service life of the battery of the electronic lock. , It is easy to generate noise, and it is easy to cause wear of the micro-motor gear set and instability of the electronic lock drive device. Therefore, out of safety considerations, major OEMs regard the ejection force of electronic locks as an important core requirement.
  • the current electronic locks are all constructed with straight teeth, helical teeth, and bevel teeth. The reduction ratio is generally small and the ejection force is insufficient. , therefore, there is an urgent need for a new solution to solve the above problems in the prior art.
  • the object of the present invention is to provide an electronic lock structure with high ejection force.
  • the invention provides an electronic lock transmission structure, including:
  • a driving device having an output shaft
  • the transmission mechanism includes an input end and an output end, the input end is a transmission assembly connected to the output shaft, and the output end is a cam device;
  • a locking rod one end is a free end, and the other end is connected with the cam device;
  • the rotation of the output shaft is converted into the reciprocating motion of the locking rod through the transmission mechanism.
  • the reciprocating motion is one or more of stretching, translation, rotation, swing, bending, and twisting.
  • the transmission component is a first worm.
  • the output torque of the output shaft is 2.4N ⁇ mm ⁇ 10.8N ⁇ mm.
  • the output power of the driving device is 0.65W-6.2W.
  • the transmission mechanism further includes a transmission gear and an output gear
  • the transmission gear includes a first gear meshed with the first worm, and a second worm coaxially arranged with the first gear
  • the output gear includes a second gear meshed with the second worm
  • the cam device arranged on one side end face of the second gear or on the extension shaft of the second gear, the The cam device is provided with a transmission shaft, the axis of the transmission shaft is parallel to but not coincident with the axis of the second gear.
  • the transmission ratio between the driving device and the second gear is 35/1 ⁇ 155/1.
  • the rotation angle of the cam device is 18°-95°.
  • an installation hole is provided at one end of the locking rod connected to the cam device, and the installation hole is in a closed or open state, and the transmission shaft is arranged in the installation hole, and the transmission shaft can Driving the mounting hole and driving the locking rod to reciprocate.
  • the inner surface of the installation hole and the outer surface of the transmission shaft have a wear-resistant coating; the teeth of the first worm, the second worm, the first gear, and the second gear The surface has a wear-resistant coating.
  • the present invention also provides an electronic lock, comprising an electronic lock housing and an electronic lock transmission structure as described above, the electronic lock transmission structure is arranged in the electronic lock housing, and the electronic lock housing is A lock hole is provided, and the lock bar protrudes from the lock hole and performs reciprocating motion;
  • the electronic lock also includes a rack and a handle, the rack is provided with a rotating shaft, and the first gear is opposite to the second gear.
  • the shaft center of one side of the two worms is provided with a rotating hole, and the rotating hole is sleeved on the rotating shaft, and the third gear meshed with it is arranged on the rack, and a control rod is arranged on the axis of the third gear.
  • One end of the control rod protrudes from the housing of the electronic lock and is connected with the handle.
  • the present invention also provides a motor vehicle, comprising the above-mentioned electronic lock transmission structure and/or the above-mentioned electronic lock.
  • the transmission structure of the electronic lock disclosed in the present invention adopts the transmission of the first worm and the second worm, which can provide a larger reduction ratio, thereby outputting a larger ejection force.
  • the electronic lock disclosed by the present invention has a rack. When the transmission mechanism of the entire electronic lock is stuck, the rack can drive the first gear to disengage from the first worm, and then reset the electronic lock.
  • Fig. 1 is a structural schematic diagram of an embodiment of an electronic lock transmission structure according to the present invention.
  • Fig. 2 is a structural schematic diagram of another embodiment of an electronic lock transmission structure according to the present invention.
  • An electronic lock transmission structure as shown in Figure 1 and Figure 2, comprising:
  • a driving device 1 having an output shaft 2;
  • the transmission mechanism includes an input end and an output end connected in sequence, the input end is a transmission assembly connected to the output shaft 2, and the output end is a cam device 4;
  • Locking bar 5 one end is a free end, and the other end is connected with described cam device 4;
  • the rotation of the output shaft 2 is converted into the reciprocating motion of the locking rod 5 through the transmission mechanism.
  • the transmission component is the first worm 3 .
  • the driving device 1 is a driving motor
  • the transmission component is a first worm 3 .
  • the drive motor works, the output shaft 2 rotates, and the input end of the transmission mechanism connected to the output shaft 2 cooperates with the output end to change the rotation of the output shaft 2 into the reciprocating motion of the lock bar 5, so that the lock bar 5 can be combined with the lock
  • the hole completes the action of unblanking and unlocking.
  • the reciprocating motion is one or more of stretching, translation, rotation, swing, bending, and twisting.
  • the way of movement can be selected according to the actual use environment, as long as the reciprocating movement of the locking bar 5 can be realized.
  • the output torque of the output shaft 2 is 2.4N ⁇ mm ⁇ 10.8N ⁇ mm.
  • the output torque of the drive device 1 determines the magnitude of the force applied to the transmission mechanism. If the torque is not enough, the lock bar 5 cannot be driven to work. In order to verify the influence of the drive device 1 with different output torques on the switch of the lock bar 5, the inventor conducted a Relevant tests, the test method is to select the driving device 1 with different output torques, and the other structures are the same, and the driving device 1 that can normally drive the lock rod 5 to work is qualified, otherwise it is unqualified. If the transmission structure has abnormal noise during operation, it is also considered failed. The test results are shown in Table 1:
  • the inventor selects the minimum output torque of the driving device 1 as 2.4N mm.
  • the output torque is greater than 10.8N mm, although it can also drive the lock lever 5 to work, but because the output torque is too large, there will be abnormal noise when the transmission structure is working, so the output torque of the drive device 1 selected by the inventor is 2.4N mm -10.8N ⁇ mm.
  • it can be 3.5N ⁇ mm, 4N ⁇ mm, 6N ⁇ mm, 8N ⁇ mm, etc.
  • the output power of the driving device 1 is 0.65W-6.2W.
  • the output power of the driving device 1 determines the working speed of the transmission structure. The higher the power, the faster the transmission structure completes the work. In order to test the influence of output power on the work of the transmission structure, the inventor carried out related tests. The test method is to select drive devices 1 with different output powers.
  • the structure of the transmission structure is the same. Each drive device 1 works continuously for 1 minute, and the transmission structure is recorded. The number of times the work is completed, the number of times greater than or equal to 40 is qualified, and less than 40 is unqualified. If there is abnormal noise when the transmission structure is working, it is also considered unqualified. The results are shown in Table 2.
  • Table 2 Effects of different output powers on the working speed and abnormal noise of the transmission structure
  • the output power of the drive device 1 when the output power of the drive device 1 is less than 0.65W, the number of switches completed by the transmission structure within 1 minute is less than 40 times, and the speed is too slow to be unqualified, so the inventor selected the minimum power of the drive device 1 as 0.65W. W, when the output power of the driving device 1 is greater than 6.2W, the speed of the transmission structure will enter the bottleneck period due to the influence of the overall design, there will be no obvious improvement, and abnormal noise will appear at the same time, so the output power of the driving device 1 selected by the inventor is 0.65 W, 6.2W. Specifically, it can be 0.9W, 0.96W, 1W, 1.08W, 2W, 3W, etc.
  • the transmission mechanism further includes a transmission gear and an output gear
  • the transmission gear includes a first gear 61 meshing with the first worm 3 , and a second gear coaxially arranged with the first gear 61 Two worms 62
  • the output gear includes a second gear 7 meshing with the second worm 62, and a second gear 7 that is arranged on the end face of one side of the second gear 7 or on the extension shaft of the second gear 7
  • the cam device 4 is provided with a transmission shaft 41 , the axis of the transmission shaft 41 is parallel to but not coincident with the axis of the second gear 7 .
  • the driving device 1 drives the output shaft 2 to rotate, the first worm 3 rotates with the output shaft 2 , and the first gear 61 meshing with the first worm 3 also rotates.
  • the second worm 62 is arranged coaxially with the first gear 61 , so driven by the first gear 61 , the second worm 62 also rotates, and drives the second gear 7 to rotate, thereby driving the cam device 4 to rotate.
  • the cam device 4 has a transmission shaft 41, which is parallel to the axis of the second gear 7, so that when the second gear 7 rotates, the cam device 4 can drive the lock lever 5 to work normally.
  • the first gear 61 and the second gear 7 are helical gears.
  • the transmission ratio between the driving device 1 and the second gear 7 is 35/1 ⁇ 155/1.
  • the inventor selected different transmission ratios of the driving device 1 and the second gear 7 for testing, and observed the number of times the locking or opening actions of the locking lever 5 were completed within 1 minute. If it was less than 40 times, it was unqualified. Abnormal noise is also unqualified, and the results are shown in Table 3.
  • the rotation angle of the cam device 4 is 18°-95°.
  • the rotation angle of the cam device 4 can also determine the stroke of the locking bar 5 .
  • the stroke of the locking lever 5 is not enough to complete the locking work.
  • the rotation angle of the cam device 4 was too large, after the lock bar 5 stretched to the working position, the cam device 4 was still outputting the power of rotation, which easily caused the damage of the transmission mechanism.
  • the test method is to prepare the driving device 1 with different rotation angles of the cam device 4.
  • the other structures of the transmission structure are the same, and the stroke of the locking bar 5 can be completed.
  • the locking action is qualified, otherwise it is unqualified.
  • a larger rotation angle means a larger stroke of the locking rod 5, and correspondingly, the size of each connecting part needs to be increased, which easily causes contact with other parts in the transmission hook and thus affects the use of the transmission structure.
  • the angle of rotation of the cam device 4 in this case is also considered unqualified, and the test results are as shown in Table 4:
  • Table 4 The influence of the rotation angle range of different cam devices on the function of the transmission structure and whether it touches other devices
  • the inventor selects the output end rotation angle of the cam device 4 as 18°. °, 95°. Specifically, it can be 50°, 60°, 70° or 80°, etc.
  • One end of the lock bar 5 connected to the cam device 4 is provided with a mounting hole 51, the mounting hole 51 is in a closed or open state, the transmission shaft 41 is arranged in the mounting hole 51, and the transmission shaft 41 can The mounting hole 51 is driven to drive the locking rod 5 to reciprocate.
  • the transmission shaft 41 as a part of the cam device 4, also rotates when the cam device 4 rotates.
  • the transmission shaft 41 rotates to the top of the mounting hole 51, Sliding contact with the upper part in the mounting hole 51 will drive the lock lever 5 to move upwards to complete the unlocking action; The lever 5 moves downward to complete the locking action.
  • the inner surface of the mounting hole 51 and the outer surface of the transmission shaft 41 have a wear-resistant coating; the first worm 3, the second worm 62, the first gear 61 and the second gear 7 There is a wear-resistant coating on the tooth surface.
  • the material of the wear-resistant coating includes ceramics, alloys, oxides or fluoroplastics.
  • the wear-resistant coating comprises one of gold, silver, nickel, tin, tin-lead alloy, zinc, silver-antimony alloy, palladium, palladium-nickel alloy, graphite silver, hard silver, graphene silver and silver-gold-zirconium alloy one or more species.
  • the corrosion resistance time test in Table 5 below is to put the relevant test sample into the salt spray test chamber, spray salt spray on each position of the test sample, take it out and clean it every 20 hours to observe the surface corrosion In other words, it is one cycle, until the corrosion area on the surface of the test piece is greater than 10% of the total area, stop the test and record the number of cycles at that time. In this embodiment, the number of cycles less than 80 is considered unqualified.
  • the number of frictions in Table 5 is to fix the test sample on the test bench, and every time after 100 contact friction tests, stop to observe the damage of the wear-resistant coating of the test sample, scratches appear, and the test sample is exposed. If the material of the piece itself is not used, the experiment is stopped, and the number of frictions at that time is recorded. In this embodiment, the number of frictions less than 8000 times is unqualified.
  • the coating material is gold, silver, silver-antimony alloy, palladium, palladium-nickel alloy, graphite silver, hard silver, graphene silver and silver-gold-zirconium alloy
  • the experimental results exceed the standard value more , the performance is relatively stable.
  • the coating material is gold, silver, nickel, tin, tin-lead alloy, zinc
  • the inventor selects the coating material as gold, silver, nickel, tin, tin-lead alloy, zinc, hard silver silver antimony
  • alloy palladium, palladium-nickel alloy, graphite silver, graphene silver and silver-gold-zirconium alloy.
  • the present invention also provides an electronic lock, comprising an electronic lock housing and an electronic lock transmission structure as described above, the electronic lock transmission structure is arranged in the electronic lock housing, and the electronic lock housing is A lock hole is provided, and the lock bar 5 protrudes from the lock hole and reciprocates;
  • the electronic lock also includes a rack 8 and a handle 92. As shown in FIG. Rotating hole, the rotating hole is sleeved on the rotating shaft 81, the third gear 9 meshing with it is arranged on the rack 8, a control rod 91 is arranged on the axis of the third gear 9, and the control rod One end of 91 protrudes from the housing of the electronic lock and is connected with the handle 92 .
  • the present invention also provides a motor vehicle, comprising the above-mentioned electronic lock transmission structure and/or the above-mentioned electronic lock.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Lock And Its Accessories (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)

Abstract

一种电子锁传动结构、电子锁及机动车辆，包括：驱动装置（1），具有输出轴（2）；传动机构，包括输入端和输出端，输入端为与输出轴（2）连接的传动组件，输出端为凸轮装置（4）；锁杆（5），一端为自由端，另一端与凸轮装置（4）连接；输出轴（2）的转动通过传动机构转化为锁杆（5）的往复运动。该电子锁传动结构采用第一蜗杆（3）和第二蜗杆（62）传动，能够提供较大的减速比，从而输出较大的顶出力。且电子锁具有齿条（8），齿条（8）能够在整个电子锁的传动机构卡死时，带动第一齿轮（61）与第一蜗杆（3）脱离，进而对电子锁重新设置。

Description

电子锁传动结构、电子锁及机动车辆
本申请要求2021年9月30日递交的申请号为202122387018.X、主题名称为“电子锁传动结构、电子锁及机动车辆”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及电子锁制造技术领域，更具体地，涉及一种电子锁传动结构、电子锁及机动车辆。
背景技术
随着汽车产业的蓬勃发展，新能源电动汽车具有能源清洁、行驶安静、行驶无污染排放等特点越来越受到大众的喜爱，而与新能源电动汽车相关的充电枪又对电动汽车起着至关重要的作用，从而越来越受到生产方的重视。同时，充电枪的广泛使用使得充电枪的电子锁越来越受到人们的重视，电子锁的种类也多种多样，在这个竞争激烈的市场中，电子锁的稳定性、灵敏度和节能耐用就成为各生产厂家研究的重点。众所周知，电子锁一般采用电流比较小的微小电机，为了实现微电机的较大转动力矩，微电机一般都会是高速旋转。这种传统电子锁中的驱动装置就会由于传动机构之间的相互吻合以及圆周转动改变为直线运动而产生摩擦力，极大地损耗了电能和电机力矩，不仅导致电子锁的电池使用寿命过短，易产生噪音，而且容易造成微电机齿轮组磨损和电子锁驱动装置不稳定。因此出于安全考虑，各大主机厂均对电子锁顶出力作为一个重要的核心要求，但目前的电子锁均为直齿、斜齿、伞齿等构造，减速比普遍较小，顶出力不足，因此，现有技术中亟需一种新的方案来解决上述问题。
发明内容
本发明的目的是提供一种具有高顶出力的电子锁结构。
本发明提供了一种电子锁传动结构，包括：
驱动装置，具有输出轴；
传动机构，包括输入端和输出端，所述输入端为与所述输出轴连接的传动组件，所述输出端为凸轮装置；
锁杆，一端为自由端，另一端与所述凸轮装置连接；
所述输出轴的转动通过所述传动机构转化为所述锁杆的往复运动。
在优选的实施方式中，所述往复运动方式为伸缩、平移、转动、摇摆、弯曲、扭曲中的一种或多种。
在优选的实施方式中，所述传动组件为第一蜗杆。
在优选的实施方式中，输出轴的输出扭矩为2.4N·mm～10.8N·mm。
在优选的实施方式中，所述驱动装置的输出功率为0.65W～6.2W。
在优选的实施方式中，所述传动机构还包括传动齿轮和输出齿轮，所述传动齿轮包括与所述第一蜗杆啮合的第一齿轮，以及与所述第一齿轮同轴设置的第二蜗杆；所述输出齿轮包括与所述第二蜗杆啮合的第二齿轮，以及设置在所述第二齿轮一侧端面上或者设置在所述第二齿轮的延伸轴上的所述凸轮装置，所述凸轮装置设置传动轴，所述传动轴的轴线与所述第二齿轮的轴线平行但不重合。
在优选的实施方式中，所述驱动装置与所述第二齿轮的传动比为35/1～155/1。
在优选的实施方式中，所述凸轮装置的转动角度为18°～95°。
在优选的实施方式中，所述锁杆与所述凸轮装置连接的一端设置安装孔，所述安装孔为封闭或开口状态，所述传动轴设置在所述安装孔中，所述传动轴能够驱动所述安装孔并带动所述锁杆往复运动。
在优选的实施方式中，所述安装孔内表面、所述传动轴外表面具有耐磨镀层；所述第一蜗杆、所述第二蜗杆、所述第一齿轮和所述第二齿轮的齿面上具有耐磨镀层。
本发明还提供了一种电子锁，包括电子锁壳体和如上所述的一种电子锁传动结构，所述电子锁传动结构设置在所述电子锁壳体中，所述电子锁壳体上设置锁孔，所述锁杆从所述锁孔中伸出并做往复运动；所述电子锁还包括齿条和把手，所述齿条上设置有转轴，所述第一齿轮相对所述第二蜗杆的一侧的轴心设置转孔，所述转孔套接在所述转轴上，所述齿条上设置有与其啮合的第三齿轮，所述第三齿轮的轴线上设置控制杆，所述控制杆一端伸出所述电子锁壳体，与所述把手连接。
本发明同时提供了一种机动车辆，包括如上所述的一种电子锁传动结构和/或如上所述的电子锁。
根据本公开的一个实施例，本发明公开的电子锁传动结构采用第一蜗杆和第二蜗杆传动，能够提供较大的减速比，从而输出较大的顶出力。本发明公开的电子锁具有齿条，齿条能够在整个电子锁的传动机构卡死时，带动第一齿轮与第一蜗杆脱离，进而对电子锁重新设置。
通过以下参照附图对本发明的示例性实施例的详细描述，本发明的其它特征及其优点将会变得清楚。
附图说明
结合在说明书中并构成说明书的一部分的附图示出了本发明的实施例，并且连同其说明一起用于解释本发明的原理。
图1为本发明一种电子锁传动结构一种实施例的结构示意图。
图2为本发明一种电子锁传动结构另一种实施例的结构示意图。
【附图标记说明】
1、驱动装置；
2、输出轴；
3、第一蜗杆；
4、凸轮装置；
41、传动轴；
5、锁杆；
51、安装孔；
61、第一齿轮；
62、第二蜗杆；
7、第二齿轮；
8、齿条；
81、转轴；
9、第三齿轮；
91、控制杆；
92、把手。
具体实施方式
现在将参照附图来详细描述本发明的各种示例性实施例。应注意到：除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本发明的范围。
以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本发明及 其应用或使用的任何限制。
对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为说明书的一部分。
在这里示出和讨论的所有例子中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它例子可以具有不同的值。
一种电子锁传动结构，如图1和图2所示，包括：
驱动装置1，具有输出轴2；
传动机构，包括依次连接的输入端和输出端，所述输入端为与所述输出轴2连接的传动组件，所述输出端为凸轮装置4；
锁杆5，一端为自由端，另一端与所述凸轮装置4连接；
所述输出轴2的转动通过所述传动机构转化为所述锁杆5的往复运动。
进一步的，所述传动组件为第一蜗杆3。
在本实施例中，驱动装置1为驱动电机，传动组件为第一蜗杆3。当驱动电机工作时输出轴2进行转动，与输出轴2连接的传动机构的输入端与输出端配合，将输出轴2的转动变为锁杆5的往复运动，从而使锁杆5能够结合锁孔完成开锁和解锁的动作。
具体的，所述往复运动方式为伸缩、平移、转动、摇摆、弯曲、扭曲中的一种或多种。运动的方式可以根据实际的使用环境进行选择，只要能够实现锁杆5的往复运动均可以。
在一实施例中，所述输出轴2的输出扭矩为2.4N·mm～10.8N·mm。
驱动装置1的输出扭矩决定了施加在传动机构上力的大小，若扭矩不够，则无法带动锁杆5工作，为了验证不同输出扭矩的驱动装置1对锁杆5开关的影响，发明人进行了相关测试，测试方法为选用不同输出扭矩的驱动装置1，其他结构相同，能够正常带动锁杆5工作的驱动装置1为合格，否则为不合格，若传动结构在工作中出现异响也视为不合格。测试结果如表1所示：
表1：不同输出扭矩的驱动装置1能否正常带动锁杆5工作
扭矩(N·mm) 2.3 2.4 3.0 3.6 3.9 4.5 5.5 6.5 7.6 8.8 9.9 10.8 11
能否工作 否 能 能 能 能 能 能 能 能 能 能 能 能
是否异响 否 否 否 否 否 否 否 否 否 否 否 否 是
如表1所示，驱动装置1的输出扭矩小于2.4N·mm后，无法带动锁杆5工作，因此 发明人选用驱动装置1的输出扭矩最小为2.4N·mm。当输出扭矩大于10.8N·mm后，虽然也能带动锁杆5工作，但是因为输出扭矩太大会使传动结构工作时出现异响，因此发明人选用的驱动装置1的输出扭矩为2.4N·mm－10.8N·mm。
具体可以为3.5N·mm、4N·mm、6N·mm、8N·mm等。
在一些实施例中，所述驱动装置1的输出功率为0.65W～6.2W。
驱动装置1的输出功率，决定了传动结构的工作速度，功率越高，传动结构完成工作的速度越快，功率越小，传动结构完成工作的速度越慢以致无法完成锁杆5的运动。为了测试输出功率对传动结构工作的影响，发明人进行了相关测试，测试的方法为选用不同输出功率的驱动装置1，传动结构的结构相同，每个驱动装置1连续工作1分钟，记录传动结构完成工作的次数，次数大于等于40为合格，小于40为不合格。若在传动结构工作时出现异响也视为不合格。结果如表2所示。
表2：不同输出功率对传动结构工作速度和异响的影响
功率(W) 0.6 0.65 0.7 0.8 1.5 2.2 2.9 3.5 4.3 4.8 5.5 6.2 6.4
完成次数 38 40 47 52 55 58 61 63 65 66 70 71 71
是否异响 否 否 否 否 否 否 否 否 否 否 否 否 是
如表2所示，当驱动装置1的输出功率小于0.65W后，1分钟内传动结构完成的开关次数小于40次，速度太慢为不合格，所以发明人选择驱动装置1的最小功率为0.65W，当驱动装置1的输出功率大于6.2W后，传动结构受整体设计的影响速度进入瓶颈期，无明显提升，同时还会出现异响，因此发明人选用的驱动装置1的输出功率为0.65W、6.2W。具体可以为0.9W、0.96W、1W、1.08W、2W、3W等。
在一些实施方式中，所述传动机构还包括传动齿轮和输出齿轮，所述传动齿轮包括与所述第一蜗杆3啮合的第一齿轮61，以及与所述第一齿轮61同轴设置的第二蜗杆62；所述输出齿轮包括与所述第二蜗杆62啮合的第二齿轮7，以及设置在所述第二齿轮7一侧端面上或者设置在所述第二齿轮7的延伸轴上的所述凸轮装置4，所述凸轮装置4设置传动轴41，所述传动轴41的轴线与所述第二齿轮7的轴线平行但不重合。
驱动装置1带动输出轴2进行转动，第一蜗杆3随输出轴2转动，与第一蜗杆3啮合的第一齿轮61也转动。第二蜗杆62与第一齿轮61同轴设置，所以在第一齿轮61的带动下，第二蜗杆62也转动，并带动第二齿轮7转动，从而带动凸轮装置4转动。凸轮装置4具有传动轴41，传动轴41与第二齿轮7的轴线平行，这样在第二齿轮7转动时， 凸轮装置4能够带动锁杆5正常的工作。所述第一齿轮61和第二齿轮7为斜齿轮。
进一步的，所述驱动装置1与所述第二齿轮7的传动比为35/1～155/1。
驱动装置1与第二齿轮7的传动比太大需要更多的响应时间，如果传动比太小则会由于控制不精确容易发生异响。因此，发明人选择了不同的驱动装置1与第二齿轮7的传动比进行测试，观察1分钟内锁杆5锁止或开启动作完成的次数，小于40次为不合格，在测试过程中如果出现异响也为不合格，结果如表3所示。
表3：不同的驱动装置1与第二齿轮7的传动比对完成次数的影响
传动比 30/1 35/1 50/1 65/1 70/1 88/1 115/1 140/1 155/1 160/1
完成次数 38 40 47 52 55 58 61 63 65 66
是否异响 否 否 否 否 否 否 否 否 否 是
从表3可知，驱动装置1与第二齿轮7的传动比过小时，锁杆5在1分钟内完成的锁止或开启动作不足40次，所以不合格，同时，当驱动装置1与第二齿轮7的传动比大于155/1后，传动结构出现异响也为不合格，所以发明人选用驱动装置1与第二齿轮7的传动比为35/1～155/1。
在优选的实施例中，所述凸轮装置4的转动角度为18°～95°。
凸轮装置4的转动角度也能决定锁杆5的行程。当凸轮装置4的转动角度过小时，锁杆5的行程不够，无法完成锁止工作。而当凸轮装置4的转动角度过大时，锁杆5伸到工作位置后，凸轮装置4依然在输出转动的力，容易导致传动机构的损坏。为了验证凸轮装置4的转动角度对传动结构的影响，发明人进行了测试，测试方法为准备凸轮装置4的转动角度不同的驱动装置1，传动结构其他结构相同，能够使锁杆5的行程完成锁止动作为合格，否则为不合格。更大的旋转角度意味着更大的锁杆5的行程，相应的就需要增加各个连接部件的尺寸，这就容易导致与传动结钩中的其他部件发生碰触从而影响传动结构的使用。这种情况的凸轮装置4的转动角度也视为不合格，测试结果如表4所示：
表4：不同凸轮装置的转动角度范围对传动结构功能的影响及与其他器件是否碰触
转动角度 16 18 28 36 47 55 61 70 78 83 89 95 96
能否锁止 否 是 是 是 是 是 是 是 是 是 是 是 是
是否碰触 否 否 否 否 否 否 否 否 否 否 否 否 是
从表4中可知，当凸轮装置4的转动角度小于18°之后，锁杆的行程不够，无法完成 锁止工作。当凸轮装置4的转动角度大于95°之后，传动结构的器件之间会有不必要的接触，会产生异响，也为不合格，因此，发明人选用凸轮装置4的输出端转动角度为18°、95°。具体可以为50°、60°、70°或80°等。
所述锁杆5与所述凸轮装置4连接的一端设置安装孔51，所述安装孔51为封闭或开口状态，所述传动轴41设置在所述安装孔51中，所述传动轴41能够驱动所述安装孔51并带动所述锁杆5往复运动。
传动轴41作为凸轮装置4的一部分在凸轮装置4转动时，也随之转动，以锁杆5进行垂直于水平方向的往复运动为例，当传动轴41旋转至安装孔51内的上方时，与安装孔51内的上部滑动接触，会驱使锁杆5朝上方移动，完成开锁动作；当传动轴41旋转至安装孔51内的下方时，与安装孔51内的下部滑动接触，会驱使锁杆5朝下方移动，完成锁止动作。
进一步的，所述安装孔51内表面、所述传动轴41外表面具有耐磨镀层；所述第一蜗杆3、所述第二蜗杆62、所述第一齿轮61和所述第二齿轮7的齿面上具有耐磨镀层。
更进一步的，所述耐磨镀层的材质含有陶瓷、合金、氧化物或氟塑料。
优选地，所述耐磨镀层包括金、银、镍、锡、锡铅合金、锌、银锑合金、钯、钯镍合金、石墨银、硬银、石墨烯银和银金锆合金中的一种或多种。
下表5中的耐腐蚀性时间测试，是将相关的测试样件放入到盐雾喷淋试验箱内，对测试样件的各个位置喷淋盐雾，每隔20小时取出清洗观察表面腐蚀情况，即为一个周期，直到测试样件表面腐蚀面积大于总面积的10％的时候，停止测试，并记录当时的周期数。在本实施例中，周期数小于80次认为不合格。表5中的摩擦次数是将测试样件固定在实验台上，并且每经过100次的接触摩擦测试，就要停下来观察测试样件耐磨镀层破坏的情况，出现划伤，并露出测试样件本身材质，则实验停止，记录当时的摩擦次数。在本实施例中，摩擦次数小于8000次为不合格。
表5：不同镀层材质测试样件受摩擦次数和耐腐蚀性的影响
Figure PCTCN2022122094-appb-000001
从上表5可以看出，当选用镀层材质为金、银、银锑合金、钯、钯镍合金、石墨银、硬银、石墨烯银和银金锆合金时，实验结果超过标准值较多，性能比较稳定。当选用镀层材质为镍、锡、锡铅合金、锌时，实验结果也是能够符合要求的，因此，发明人选择镀层材质为金、银、镍、锡、锡铅合金、锌、硬银银锑合金、钯、钯镍合金、石墨银、石墨烯银和银金锆合金中的一种或多种。
本发明还提供了一种电子锁，包括电子锁壳体和如上所述的一种电子锁传动结构，所述电子锁传动结构设置在所述电子锁壳体中，所述电子锁壳体上设置锁孔，所述锁杆5从所述锁孔中伸出并做往复运动；
所述电子锁还包括齿条8和把手92，如图2所示，所述齿条8上设置有转轴81，所述第一齿轮61相对所述第二蜗杆62的一侧的轴心设置转孔，所述转孔套接在所述转轴81上，所述齿条8上设置有与其啮合的第三齿轮9，所述第三齿轮9的轴线上设置控制杆91，所述控制杆91一端伸出所述电子锁壳体，与所述把手92连接。
当电子锁因故卡死时，可以在电子锁壳体外面转动把手92，带动控制杆91转动，进而带动第三齿轮9转动，这样与第三齿轮9啮合的齿条8就会进行直线运动，转轴81通过转孔带动第一齿轮61平移，从而使第一齿轮61与第一蜗杆3脱离，以此来解决电子锁内部结构的卡死。当电子锁正常工作时，第一齿轮61旋转，转孔围绕转轴81旋转，所以齿条8不会影响第一齿轮61的正常工作。
本发明还提供了一种机动车辆，包括如上所述的一种电子锁传动结构和/或如上所述的电子锁。
虽然已经通过例子对本发明的一些特定实施例进行了详细说明，但是本领域的技术人员应该理解，以上例子仅是为了进行说明，而不是为了限制本发明的范围。本领域的技术人员应该理解，可在不脱离本发明的范围和精神的情况下，对以上实施例进行修改。本发明的范围由所附权利要求来限定。

Claims (12)

  1. 一种电子锁传动结构，其特征在于，包括：
    驱动装置，具有输出轴；
    传动机构，包括输入端和输出端，所述输入端为与所述输出轴连接的传动组件，所述输出端为凸轮装置；
    锁杆，一端为自由端，另一端与所述凸轮装置连接；
    所述输出轴的转动通过所述传动机构转化为所述锁杆的往复运动。
  2. 根据权利要求1所述的一种电子锁传动结构，其特征在于，所述往复运动方式为伸缩、平移、转动、摇摆、弯曲、扭曲中的一种或多种。
  3. 根据权利要求1所述的一种电子锁传动结构，其特征在于，所述传动组件为第一蜗杆。
  4. 根据权利要求1所述的一种电子锁传动结构，其特征在于，所述输出轴的输出扭矩为2.4N·mm～10.8N·mm。
  5. 根据权利要求1所述的一种电子锁传动结构，其特征在于，所述驱动装置的输出功率为0.65W～6.2W。
  6. 根据权利要求3所述的一种电子锁传动结构，其特征在于，所述传动机构还包括传动齿轮和输出齿轮，所述传动齿轮包括与所述第一蜗杆啮合的第一齿轮，以及与所述第一齿轮同轴设置的第二蜗杆；所述输出齿轮包括与所述第二蜗杆啮合的第二齿轮，以及设置在所述第二齿轮一侧端面上或者设置在所述第二齿轮的延伸轴上的所述凸轮装置，所述凸轮装置设置传动轴，所述传动轴的轴线与所述第二齿轮的轴线平行但不重合。
  7. 根据权利要求6所述的一种电子锁传动结构，其特征在于，所述驱动装置与所述第二齿轮的传动比为35/1～155/1。
  8. 根据权利要求6所述的一种电子锁传动结构，其特征在于，所述凸轮装置的转动角度为18°～95°。
  9. 根据权利要求6所述的一种电子锁传动结构，其特征在于，所述锁杆与所述凸轮装置连接的一端设置安装孔，所述安装孔为封闭或开口状态，所述传动轴设置在所述安装孔中，所述传动轴能够驱动所述安装孔并带动所述锁杆往复运动。
  10. 根据权利要求9所述的一种电子锁传动结构，其特征在于，所述安装孔内表面、所述传动轴外表面具有耐磨镀层；所述第一蜗杆、所述第二蜗杆、所述第一齿轮和所述 第二齿轮的齿面上具有耐磨镀层。
  11. 一种电子锁，其特征在于，包括电子锁壳体和如权利要求6-10任一项所述的一种电子锁传动结构，所述电子锁传动结构设置在所述电子锁壳体中，所述电子锁壳体上设置锁孔，所述锁杆从所述锁孔中伸出并做往复运动；所述电子锁还包括齿条和把手，所述齿条上设置有转轴，所述第一齿轮相对所述第二蜗杆的一侧的轴心设置转孔，所述转孔套接在所述转轴上，所述齿条上设置有与其啮合的第三齿轮，所述第三齿轮的轴线上设置控制杆，所述控制杆一端伸出所述电子锁壳体，与所述把手连接。
  12. 一种机动车辆，其特征在于，包括如权利要求1至10任一项所述的一种电子锁传动结构和/或如权利要求11所述的电子锁。
PCT/CN2022/122094 2021-09-30 2022-09-28 电子锁传动结构、电子锁及机动车辆 Ceased WO2023051602A1 (zh)

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