WO2013077679A1 - Transmission - Google Patents

Transmission Download PDF

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Publication number
WO2013077679A1
WO2013077679A1 PCT/KR2012/009996 KR2012009996W WO2013077679A1 WO 2013077679 A1 WO2013077679 A1 WO 2013077679A1 KR 2012009996 W KR2012009996 W KR 2012009996W WO 2013077679 A1 WO2013077679 A1 WO 2013077679A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
shift control
transmission
gears
Prior art date
Application number
PCT/KR2012/009996
Other languages
English (en)
Korean (ko)
Inventor
전정호
Original Assignee
Jeon Jeong Ho
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 Jeon Jeong Ho filed Critical Jeon Jeong Ho
Publication of WO2013077679A1 publication Critical patent/WO2013077679A1/fr

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Classifications

    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
    • F16H3/30—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial
    • F16H3/32—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial and an additional shaft
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/06—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with spur gear wheels
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/42—Clutches or brakes
    • B60Y2400/421—Dog type clutches or brakes

Definitions

  • the present invention relates to a transmission that can be universally applied to a device that requires a shift, such as a bicycle, a vehicle, an industrial machine, and more particularly, a smooth shift is possible by alleviating a shift shock when shifting, and a power transmission method of a simple gear gear. It is possible to reduce the manufacturing cost by enabling the structure to be simplified and miniaturized, and to realize high transmission ratio by simple structure, and to improve the accuracy and efficiency of power transmission even when transmitting large power. It is about.
  • the gearbox is provided with a plurality of gears on the main shaft and the sub-shaft, and is a device for changing the driving torque and rotational speed by changing the bite of each gear, and the transmission applied to the vehicle is installed between the clutch and the propulsion shaft, To increase or decrease the rotational force of the engine to suit the driving state of the car to deliver to the drive wheels, the transmission is applied to a device that requires a shift, such as bicycles and other industrial machinery.
  • Such a transmission includes a manual transmission in which shifting is performed by a driver's operation, and an automatic transmission in which shifting is automatically performed.
  • the automatic transmission there is a problem that the cost is high due to the complicated structure and the efficiency is low, and in the case of the conventional continuously variable transmission, there is a problem in that slipping occurs and there is a limit in transmitting large power.
  • Figures 1 and 2 show a planetary gearbox transmission disclosed in the Patent Publication No. 10-2005-0098730 and multiple transmissions connected in series.
  • a conventional planetary gear type transmission includes an input shaft 10, an planetary gear assembly 30 fixed on an input shaft 10, an auxiliary 35, and an output shaft installed on opposite sides of the input shaft 10. (20), the slider (40) which can move left and right on the output shaft (20), the connection means (60) provided in a part of the planet carrier (33) of the planetary gear assembly (30), and the connection provided in a part of the support (35).
  • the means 61, the connection means 70 installed in a part of the slider 40, etc. are comprised.
  • the main part of the planetary gear assembly 30 is composed of a sun gear 31, a planetary gear 32, a planetary carrier 33 including a pinion shaft 33a and a fixing portion 33b, a ring gear 34 and the like. do.
  • the ring gear 34 is here fixed by the fastening means 80 as a fastening element.
  • the auxiliary body 35 is fixed to the planetary gear assembly 30 at a predetermined distance on the input shaft 10.
  • An output shaft 20 is installed on the opposite side of the input shaft 10, and a bearing 90 is provided at the contact portion between the input shaft 10 and the output shaft 20 to mitigate frictional force.
  • a slider 40 capable of moving forward and backward is provided on the output shaft 20, a slider 40 capable of moving forward and backward is provided.
  • Sliding means 50 is provided at the contact portion between the slider 40 and the output shaft 20 to enable forward and backward movement and power connection of the slider 40.
  • the connecting means 60 is installed in a part of the planetary carrier 33 of the planetary gear assembly 30, the connecting means 61 is installed in a part of the auxiliary body 35, and the connecting means (a part of the slider 40). 70) are installed.
  • the connecting means 70 of the slider 40 and the connecting means 60 of the planet carrier 33 are connected when the slider 40 is advanced, and the connecting means of the slider 40 when the slider 40 is backward.
  • the 70 is connected with the connecting means 61 of the auxiliary 35.
  • the planetary gear assembly 30 is rotated together with the rotation of the input shaft 10.
  • the sun gear 31 and the planetary gear 32 rotate, and the planet carrier 33 rotates at the same time.
  • the slider 40 connected to the connecting means 60 of the planetary carrier 33 and the connecting means 70 of the slider 40 rotates, and with the rotation of the slider 40,
  • the output shaft 20 rotates.
  • the speed ratio becomes deceleration (stage 1).
  • I denotes a first transmission
  • II denotes a second transmission.
  • the output shaft 20 of the first transmission I becomes the input shaft 10 'of the second transmission II connected in series. In this way, it is possible to increase the shift stage by connecting a plurality of planetary gear transmissions.
  • the slider 40 is moved forward and backward during shifting so that the connecting means 70 of the slider 40 is connected to the connecting means 60 of the planet carrier 33 or the connecting means of the auxiliary 35 ( 61) in the process of being engaged in the power breakage phenomenon occurs and the gears during gear shifting shock, the shift is unstable, there is a problem that the efficiency of power transmission falls.
  • the prior art includes a configuration that can connect the torque converter (not shown) to the transmission to mitigate the shock during the shift of the gear type transmission by the shift force by the fluid of the torque converter.
  • the torque converter is additionally installed in order to alleviate the shock during the shift, the manufacturing cost of the transmission increases, and the volume increases, which makes it difficult to apply to a device requiring a compact transmission such as a bicycle.
  • the conventional bicycle transmission it is generally configured to shift using a multi-stage sprocket gear, but even in this case, a shift shock occurs during shifting, and shifting is not smoothly performed during shifting. have.
  • the present invention has been made to solve the above problems, and an object thereof is to provide a transmission that can obtain a high transmission ratio while simplifying the connection structure between the gears for the multi-shift.
  • Another object of the present invention is to provide a transmission that enables stable and high efficiency power transmission by relieving shift shocks during shifting, enabling smooth shifting, and preventing breakage of power during shifting.
  • the present invention is to provide a transmission that can be universally applied to a device that requires a shift, such as bicycles, vehicles, industrial machinery by enabling the transmission of large power by configuring the connection structure between the gears in a simple gear gear method. .
  • the front fixing plate 110 and the rear fixing plate 120 is disposed on both sides to form the appearance of the transmission, the fixing plate 100 is installed in the gear for the multi-stage shifting );
  • a main gear 200 which is rotatably installed to penetrate the rear fixing plate 120 and coupled to the shaft 210 to transmit a driving force;
  • a first gear 300 which is rotatably connected to the main gear 200 in a state where the main gear 200 penetrates the front fixing plate 110 and is installed in a forward and backward direction, and has a first clutch means formed on one surface thereof; It is supported on the rear fixing plate 120, is rotatably connected to a shaft provided on the same axis as the shaft of the first gear 300, the surface facing the one surface of the first gear 300
  • a second gear 400 having a second clutch means connected to or spaced from the first clutch means in conjunction with the forward and backward movement of the first gear 300 to function as a clutch;
  • An output gear 500 connected through the second gear 400 and a power transmission means 600;
  • shift control means which controls the first
  • the shaft of the first gear 300 and the shaft of the second gear 400 may be configured separately or integrally.
  • first clutch means and the second clutch means are formed along the circumferential direction, respectively, on opposite surfaces of the first gear 300 and the second gear 400, and simply the first clutch means and the second clutch means.
  • first clutch means and the second clutch means respectively formed along the circumferential direction on the opposite surface of the first gear 300 and the second gear 400, consists of inclined surfaces of different directions only one-way rotation
  • first catching jaw 311,321,331,341
  • second catching jaw 411,421,431,441
  • first clutch means and the second clutch means are respectively provided in the first gear 300 and the second gear 400, the rotational force is transmitted in one direction and the slip in the opposite direction is cut off the power It may be composed of a first clutch bearing 329 and a second clutch bearing 429.
  • the first gear 300 is always arranged on the outer circumferential surface of the main gear 200 at regular intervals and is composed of a plurality of first gear (310, 320, 330, 340) having different diameters for multi-stage shifting
  • the second gear 400 is made of the same number as the first gear 300, and is composed of a plurality of second gears (410, 420, 430, 440) having different diameters according to the gear ratio, and the first of the first gear (310, 320, 330, 340)
  • One clutch means may be configured by the shift control means (700,700 ') to be controlled individually back and forth movement.
  • the shift control means 700 is rotated about the rotating shaft 710 connected to the front fixed plate 110 and spaced up and down and made of a shift control panel 720 coupled to the rotating shaft 710
  • the shift Control panel 720 is composed of a plurality of plates 721,722 spaced apart in the axial direction of the rotary shaft 710
  • the plate 721,722 is a pressing portion of a curved shape in a predetermined angle section with respect to the rotary shaft 710 721b and 722b are formed so that, when the shift control panel 720 is rotated, the press plates 315 formed at the end of the first gear rotation shaft protruding outwardly of the front fixing plate 110 are the press portions 721b and 722b. It may be configured to be moved back and forth along the shape of).
  • the first gear 300 is always arranged on the outer circumferential surface of the main gear 200 at regular intervals and is composed of a plurality of first gear (310, 320, 330, 340) having different diameters for multi-stage shifting
  • the second gear 400 is made of the same number as the first gear 300, and is composed of a plurality of second gears (410, 420, 430, 440) having different diameters according to the transmission ratio, one side of the first gear (310, 320, 330, 340)
  • Couplings 325 and 345 having protrusions 325a and 345a are integrally coupled to each other, and the forks 325a and 345a penetrate the front fixing plate 110 to be moved forward and backward by the shift control means 700.
  • the locking grooves 326a and 346a of the 326 and 346 may be coupled to each other.
  • the shift control means 700 is rotated about the rotating shaft 710 connected to the front fixed plate 110 and spaced up and down and made of a shift control panel 720 coupled to the rotating shaft 710
  • the shift Control panel 720 is composed of a plurality of plates 721,722 spaced apart in the axial direction of the rotary shaft 710
  • the plate 721,722 is a pressing portion of a curved shape in a predetermined angle section with respect to the rotary shaft 710 721b and 722b are formed such that, when the shift control panel 720 rotates, the shaft portions 326b and 346b of the forks 326 and 346 are moved back and forth along the shapes of the pressing parts 721b and 722b.
  • the first gear 300 is always arranged on the outer circumferential surface of the main gear 200 at regular intervals and is composed of a plurality of first gear (310, 320, 330, 340) having different diameters for multi-stage shifting
  • the second gear 400 is made of the same number as the first gear 300, and is composed of a plurality of second gears (410, 420, 430, 440) having different diameters according to the transmission ratio, one side of the first gear (310, 320, 330, 340)
  • the connecting members 327 and 347 are integrally coupled to each other, and the outside of the connecting members 327 and 347 slides forward and backward along the connecting members 327 and 347 and the dog clutches 328 and 348 having the first clutch means are coupled to one surface thereof.
  • the fork parts 328a and 348a of the dog clutches 328 and 348 are formed with locking parts 328b and 348b and penetrate the front fixing plate 110 to be moved back and forth by the shift control means 700.
  • Engagement grooves (326a, 346a) of 326,346 may be configured to be engaged.
  • the shift control means 700 is made of a shift control panel 720 rotated about the rotary shaft 710 connected to the front fixed plate 110 and spaced apart from the rotary shaft 710, the shift control panel ( 720 consists of a plurality of plates 721 and 722 spaced apart in the axial direction of the rotating shaft 710, the plate 721, 722 is a pressing portion 721b of a curved shape in a predetermined angle section with respect to the rotating shaft 710. , 722b is formed so that, when the shift control panel 720 rotates, the shaft portions 326b and 346b of the forks 326 and 346 are moved back and forth along the shapes of the pressing portions 721b and 722b. .
  • main gear 200 and the first gear 300 may be composed of a helical gear.
  • the pressing parts 721b and 722b are formed in an angle range larger than the angle range based on the rotation shaft 710 between the first gears 300 disposed adjacent to each other, and thus the rotation control panel 720 is rotated.
  • two pairs of gears corresponding to each other of the first gear 300 and the second gear 400 may be configured to be in a power transmission state overlapping each other in a predetermined section to mitigate a shift shock.
  • the power transmission means 600 may be composed of a plurality of gears (410, 420, 430, 440) constituting the second gear 400 and a chain (610) connecting the output gear (500).
  • the power transmission unit 600 connects the plurality of gears 410, 420, 430, and 440 constituting the second gear 400 to the output gear 500. It may be configured as a worm wheel 620.
  • the power transmission unit 600 includes a worm wheel 620 connecting the plurality of gears 410, 420, 430, and 440 constituting the second gear 400. It may be composed of a chain 610 connected to the worm wheel 620.
  • a reverse rotation second gear 450 may be connected to the worm wheel 620, and a reverse rotation gear 460 may be connected to the reverse rotation second gear 450.
  • the shaft of the first gear 300 and the shaft of the second gear 400 is composed of an integral shaft 380
  • the first gear 300 is a predetermined interval on the outer peripheral surface of the main gear 200
  • Is made of the same number as the first gear 300 is composed of a plurality of second gears (410, 420, 430, 440, 450, 460, 470) having different diameters in accordance with the transmission ratio is connected to the corresponding integral shaft 380, respectively, the integral shaft ( 380 is disposed to penetrate the front fixing plate 110 and the rear fixing plate 120, and the shift control means 700 'selectively shifts one of the integrated shafts 380 forward and backward. That can be configured.
  • first gear 300 is fixed to the integrated shaft 380 is rotated integrally
  • second gear 400 is connected to the integrated shaft 380 via a bearing
  • the guide member 800 Is supported by the first gear 300 to prevent movement toward the first gear 300
  • the integrated shaft 380 is supported by the bearings on the front fixing plate 110 and the rear fixing plate 120 so as to move forward and backward and rotate. It can be configured to be connected.
  • first gear 300 and the second gear 400 is connected to the integrated shaft 380 via a bearing, and both ends of the first gear 300 are fastened to the integrated shaft 380. It is supported by the snap ring 900, the second gear 400 is supported by the guide member 800 to prevent the movement to the first gear 300 side, the integral shaft 380 is the front fixing plate 110 and the rear fixing plate 120 may be configured to be supported forward and backward.
  • the guide member 800 is composed of a circular plate 810 provided on one side of the second gear 400 facing the first gear 300, the circular plate 810 through the main gear
  • the number of connection holes 830 corresponding to the first gear 300 and the second gear 400 may be formed so that the holes 820 and the first clutch means and the second clutch means can be connected to each other. have.
  • the shift control means 700 ′ is provided on the outer surface of the front fixing plate 110 and the outer surface of the rear fixing plate 120 to be interlocked with the first shift control member 730 and the second shift control member 740. And an inner side surface of the first shift control member 730 and the second shift control member 740, wherein any one of the integrated shaft 380 is rotated when the shift control means 700 'is rotated.
  • the protrusion 731 pushing one end of both ends of the selected shaft to one side and the engaging groove 741 for receiving the other end may be formed in a position corresponding to each other.
  • the built-in bicycle transmission was used only in a special layer because of high cost and structural complexity.
  • the connection structure between the gears for shifting is simple, making it easy to manufacture and miniaturization, as well as a wide transmission ratio. It can be easily adjusted to contribute to the popularization of the built-in bicycle transmission.
  • the configuration of the 10-speed is very easy and the shifting operation is easy, and thus it can be applied to a vehicle transmission.
  • the present invention is made of a gear-type power transmission structure can reduce the unit cost, not only easy to design a wide transmission ratio and a large number of stages, but also high power transmission efficiency, accurate output value can be obtained, low unit price It can be widely applied to various industrial fields that need a transmission with a wide transmission ratio and a large number of stages.
  • FIG. 1 is a cross-sectional view showing an example of a conventional planetary gear type transmission
  • FIG. 2 is a diagram illustrating a multiple transmission in which the transmission shown in FIG. 1 is connected in series;
  • FIG. 3 is a partial cutaway perspective view of a transmission according to a first embodiment of the present invention.
  • FIG. 4 is a longitudinal sectional view showing an internal structure of a transmission according to a first embodiment of the present invention
  • FIG. 5 is a longitudinal sectional view showing an internal structure of a transmission according to a second embodiment of the present invention.
  • FIG. 6 is a longitudinal sectional view showing an internal structure of a transmission according to a third embodiment of the present invention.
  • FIG. 7 is a view showing a first embodiment of the clutch means of the first gear and the second gear
  • FIG. 9 is a view showing an embodiment of a connection structure between a main gear and a first gear
  • FIG. 11 shows a first embodiment of a power transmission means
  • FIG. 13 shows a third embodiment of a power transmission means
  • 15 is a (a) plan view and (b) side view showing a first embodiment of a shift control means for power transmission control between a first clutch means and a second clutch means;
  • 16 is a longitudinal sectional view showing an internal structure of a transmission according to a fourth embodiment of the present invention.
  • FIG. 17 is a side view of the guide member shown in FIG. 16;
  • FIG. 18 is a (a) side view, (b) a perspective view, a second shift control member of a first shift control member constituting a second embodiment of a shift control means for power transmission control between a first clutch means and a second clutch means; (C) side view, (d) perspective view,
  • FIG. 19 is an exploded view for explaining the principle of operation of the shift control means shown in FIG.
  • 20 is a longitudinal sectional view showing an internal structure of a transmission according to a fifth embodiment of the present invention.
  • fixing plate 110 front fixing plate
  • Second bearing 450 Second gear for reverse rotation
  • shift control plate 730 first shift control member
  • FIG 3 is a partial cutaway perspective view of a transmission according to an embodiment of the present invention
  • Figure 4 is a longitudinal sectional view showing the internal structure of the transmission according to an embodiment of the present invention.
  • the front fixing plate 110 and the rear fixing plate 120 are coupled to each other by maintaining a predetermined distance by the fastening member 130 to form an external shape of the transmission and the multi-stage transmission therein.
  • Fixing plate 100 is provided for the gears are installed.
  • the rear fixing plate 120 has a shaft 210 through which a driving force is input and is rotatably installed through the bearing 220, and a main gear 200 is coupled to one end of the shaft 210.
  • the front fixing plate 110 is prevented from rotational movement, the shaft (313, 323, 333, 343) is penetrated to enable forward or backward movement, one end of the shaft (313, 323, 333, 343) through the first bearing (312, 322, 332, 342) via the first gear (300) 310, 320, 330, 340 are rotatably coupled.
  • the first gear 300 is disposed so as to remain engaged with the main gear 200 irrespective of the forward and backward movement, and for this purpose, the length of the axial width of the first gear 300 is greater than that of the main gear 200. The length of the axial width is made larger. Due to the configuration in which the first gear 300 is in constant mesh with the main gear 200, a separate operation for engaging the main gear 200 and the first gear 300 at the time of shifting may be omitted. It is possible to fundamentally prevent shift shock that may occur during engagement.
  • the first gears 310, 320, 330, and 340 are disposed at 90 ° intervals on the outer circumferential surface of the main gear 200.
  • the first gears 310, 320, 330, and 340 are composed of diameters of different sizes for the multi-stage shifting.
  • the forward and backward movements of the first gears 310, 320, 330, and 340 are configured to be independently performed by shift control means 700 (see FIG. 15), which will be described later.
  • the number of the first gear 300 can be configured freely two or more.
  • the second gear 400 (400; 410, 420, 430, 440) is rotatably connected via the. As the shafts 413, 423, 433 and 443 are fixed to the rear fixing plate 120, the second gear 400 rotates in place without forward and backward movement during rotation.
  • the second gear 400 is configured in the same number as the first gear 300, it may be configured to have a different diameter according to the transmission ratio of the desired output.
  • First clutch means 311, 321, 331, 341 and second clutch means 411, 421, 431, 441 are provided on opposing surfaces of the first gear 300; 310, 320, 330, 340 and the second gear 400; 410, 420, 430, and 440, respectively, by the shift control means 700.
  • the first clutch means 311, 321, 331, 341 and the second clutch means 411, 421, 431, 441 are connected to or spaced apart from each other to power the first gear 300 from the first gear 300 to the second gear 400. Clutch function to transmit or block the.
  • the first gear 300 is moved forward and the first clutch means (311, 321, 331, 341) formed on one surface of the first gear 300 and the second clutch means (411, 421, 431, 441) formed on one surface of the second gear 400 facing the first gear 300 is In the state of being connected to each other, in the state of being connected by the clutch means of any one of the plurality of first gear (310, 320, 330, 340) constituting the first gear 300 and the clutch means of the second gear 400 corresponding to the shifting It is configured to rotate.
  • the second gear 400 is connected to each other by the power transmission means 600, when the power of the first gear 300 is transmitted to any one of the second gear 400, all the second gear 400 is Will rotate together.
  • the output gear 500 is connected to the power transmission means 600 together to rotate the output gear 500 in proportion to the rotational speed of the second gear 400, the rear fixing plate 120 It is passed through the bearing 520 through the output gear 500 is coupled to the output is shifted to the desired rotational speed through the shaft 510 coupled.
  • the shafts 313, 323, 333, 343 to which the first gear 300 is connected and the shafts 413, 423, 433 and 443 to which the second gear 400 is connected are separated from each other on the same axis, and the first clutch
  • the configuration for the connection and disconnection between the means (311,321,331,341) and the second clutch means (411,421,431,441) when the first gear 300 is configured to move forward or backward by the shift control means (700)
  • the configuration for the connection and separation between the first clutch means (311, 321, 331, 341) and the second clutch means (411, 421, 431, 441) can be variously modified, other embodiments will be described in order below.
  • FIG. 5 is a longitudinal sectional view showing an internal structure of a transmission according to a second embodiment of the present invention.
  • the above-described embodiment and the other components are configured in the same, the first gear 300 and the second gear 400, the shaft (350, 360) is axially coupled to form an integrated structure Both ends of the shafts 350 and 360 are different in that they are fixedly mounted to the front fixing plate 110 and the rear fixing plate 120, respectively.
  • couplings 325 and 345 are integrally coupled to one side of the first gear 300, and flanges protruding portions 325a and 345a are coupled to the couplings 325 and 345. Is formed, the front fixing plate 110 is passed through the shaft portion (326b, 346b) of the forks (326, 346) moved forward and backward by the shift control means 700, the end of the shaft portion (326b, 346b) the projection. Engaging grooves 326a and 346a engaged with the 325a and 345a are integrally formed.
  • the couplings 325 and 345 to which the protruding portions 325a and 345a are coupled to the engaging grooves 326a and 346a of the forks 326 and 346 and the agents coupled thereto are moved forward along the main gear 200 so that the first clutch means 321 and 341 are connected to the second clutch means 421 and 441 so as to drive power between the first gear 300 and the second gear 400. It becomes a delivery state.
  • the transmission according to the present embodiment is a configuration for connection and separation between the first clutch means (311, 321, 331, 341) and the second clutch means (411, 421, 431, 441), the connecting members 327, 347 are integrally coupled to one side of the first gear (320, 340).
  • the outside of the connecting members 327 and 347 slides back and forth along the connecting members 327 and 347, and the dog clutches 328 and 348 having the first clutch means 328c and 348c are coupled to one surface thereof, and the dog clutches 328 and 348.
  • the engaging portions 328b and 348b are formed in the body portions 328a and 348a, and the front fixed plate 110 penetrates the shaft portions 326b and 346b of the forks 326 and 346 which are moved back and forth by the shift control means 700.
  • the end portions of the shaft portions 326b and 346b are integrally formed with locking grooves 326a and 346a engaged with the locking portions 328b and 348b.
  • first clutch means 328c and 348c and the second clutch means 421 and 441 are connected to or separated from each other by the forward and backward movement of the forks 326 and 346 by the shift control means 700 so that the first gear ( Power is transmitted or interrupted between 300 and the second gear 400.
  • the first gear 300 rotates in place without moving forward and backward, and the dog clutches 328 and 348 are moved forward and backward so that the first gear 300 and the second gear ( Since the power transmission between the 400 is made, since the position of the contact surface of the first gear 300 and the main gear 200 is always constant, the first gear 300 and the main gear 200 are helical gears in addition to the spur gears. Can be configured. As such, when the first gear 300 and the main gear 200 are configured as helical gears, axial slippage at the contact surface can be prevented to further improve the power transmission capability.
  • the dog clutches 328 and 348 slide forward and backward on the connecting members 327 and 347 so that power is transmitted or interrupted between the first gear 300 and the second gear 400, but the dog clutch ( 328 and 348 may be configured to allow a smoother shift when shifting using a synchronizer (always bite synchronization type).
  • first clutch means 311, 321, 331, 341 of the first gear 300 and the second clutch means 411, 421, 431, 441 of the second gear 400 will be described.
  • FIG. 7 shows a first embodiment of the clutch means of the first gear and the second gear
  • FIG. 8 shows a second embodiment of the clutch means of the first gear and the second gear.
  • first clutch means and the second clutch means each include a first catching jaw 311, 321, 331, 341 and a second catching jaw 411, 421, 431, 441, respectively.
  • the second locking jaws 411, 421, 431, 441 are formed in plural along the circumferential direction on opposite surfaces of the first gear 300 and the second gear 400, respectively.
  • Figure 7 (a) shows that the first clutch means and the second clutch means are formed along the circumferential direction on opposite surfaces of the first gear 300 and the second gear 400, respectively;
  • Figure 7 (b) is composed of one side at a right angle and the other side is inclined,
  • the first catching jaws 311, 321, 331, 341 and the second catching jaws 411, 421, 431, 441 are inclined in opposite directions to each other so that power is transmitted when rotating to one side and power transmission is blocked by slip when rotating to the other side.
  • the function is configured to be performed.
  • the first clutch bearing 329 and the second clutch bearing 429 are provided at a bearing portion supporting the first gear 300 and the second gear 400 in one direction when shifting. The power is transmitted but the slip is generated in the opposite direction, so the power transmission is blocked.
  • the first locking jaw (311, 321, 331, 341) and the second locking jaw (411, 421, 431, 441) can implement the same effect even if the triangular structure.
  • the clutch bearings are provided in the first gear 300 and the second gear 400, respectively, but may be provided only in one of them.
  • FIG. 9 is a view showing an embodiment of a connection structure between a main gear and a first gear
  • FIG. 10 is a view showing a length relationship from the center of the main gear to the outer end of the second gear.
  • the diameter and the number of the first gear (310, 320, 330, 340) can be arbitrarily adjusted.
  • the diameter of the main gear 200 is 200 mm
  • the diameters of the first gears 310, 320, 330, 340 are 50 mm, 40 mm, 30 mm, and 20 mm.
  • the distance between the center of the shaft 210 of the main gear 200 and the center of the shafts 313, 323, 334, and 343 of the first gears 310, 320, 330, and 340 is 125 mm, 120 mm, 115 mm, and 110 mm, respectively.
  • the second gears 410, 420, 430, and 440 illustrates the configuration of the second gears 410, 420, 430, and 440, wherein the shafts 313, 323, 333, 343 of the first gears 310, 320, 330, 340 and the shafts 413, 423, 433, 443 of the second gears 410, 420, 430, 440 are positioned on the same axis.
  • the diameter of the second gear (410, 420, 430, 440) is composed of 20mm, 30mm, 40mm, 50mm, respectively.
  • the distances from the center of the shaft 210 of the main gear 200 to the outer ends of the second gears 410, 420, 430, and 440 are all equal to 135 mm, forming a perfect circle, and the worm wheel is outside the second gears 410, 420, 430, 440. 620 can be connected.
  • 1570 / 251.2 6.25 shift ratio.
  • the speed ratio can be freely set, and the number of gear stages can be freely set. It can be set.
  • the case in which the diameter of the main gear 200 is configured to 70 mm and the first gear 300 and the second gear 400 are configured in seven stages is shown in Table 1 below.
  • the rotation distance difference between the 1st and 2nd stage is 86.78mm
  • the difference between the 2nd and 3rd stage is 71.73mm
  • the difference between the 3rd and 4th stage is 83.25mm
  • the difference between the 4th and 5th stage is 65.94mm
  • the 5th and 6th stages is 83.92mm
  • the difference between 6 and 7 is 69.93mm.
  • FIG. 11 is a view showing a first embodiment of the power transmission means.
  • a plurality of gears 410, 420, 430, and 440 constituting the second gear 400 and the output gear 500 are connected together by a chain 610. Even if the distance from the center of the shaft 210 of the main gear 200 to the outer end of the second gear 400 is not constant, power transmission to the shifted output gear 500 is possible, so that the speed ratio can be easily adjusted. have.
  • the power transmission means 600 has a constant length from the center of the axis of the shaft 210 of the main gear 200 to the outer surface of each of the plurality of gears 410, 420, 430, and 440 constituting the second gear 400.
  • the output gear 500 may be configured to be fitted to the worm wheel 620 as shown, or may be configured to be fitted to the worm wheel 620 although not shown.
  • Fig. 13 shows a third embodiment of the power transmission means.
  • the power transmission means 600 according to the present embodiment is connected so that a plurality of gears 410, 420, 430, and 440 constituting the second gear 400 are joined to the worm wheel 620, and the chain 610 is disposed outside the bending wheel 620. It is made up of a connected structure.
  • Power transmission means 600 includes all of the configuration of the embodiment shown in Figure 12, the worm wheel 620 is connected to the reverse gear second gear 450, the reverse gear second gear 450 ), The reverse rotation gear 460 is connected, the power transmission means 600 according to the present embodiment can be applied to a device such as a vehicle capable of moving forward and backward.
  • an additional first gear (not shown) connected to the second gear 450 for reverse rotation is additionally installed in the first gear 300, and all the The first gear 310, 320, 330, 340 and the second gear 410, 420, 430, 440 may be configured to be connected to the reverse gear first gear and the second gear in a state in which the first gear 310, 320, 330, 340 is disconnected.
  • Fig. 15 is a (a) plan view and (b) side view showing a first embodiment of a shift control means for power transmission control between the first clutch means and the second clutch means.
  • the shift control means 700 transfers the shafts 313, 323, 333, and 343 of the first gear 300. ), And the shaft portions 326b and 346b of the forks 326 and 346 are moved forward and backward by the shift control means 700 in FIGS. 5 and 6.
  • the shift control means 700 is rotated about a rotation shaft 710 connected to the front fixed plate 110 and is composed of a shift control panel 720 coupled to the rotation shaft 710, and the shift control panel 720 is the It consists of a plurality of plates (721,722) coupled to the rotation axis 710 spaced apart in the axial direction.
  • the plates 721 and 722 are formed with flat portions 721a and 722a and pressing portions 721b and 722b having a curved shape in a predetermined angular section based on the rotation shaft 710. Therefore, when the shift control panel 720 is rotated, in the case of the embodiment shown in FIG. 4, the pressing plate 315 formed at the end of the first gear rotating shaft protruding outwardly of the front fixing plate 110 is the pressing part 721b, 5 and 6, the shafts 326b and 346b of the forks 326 and 346 are moved back and forth along the shapes of the pressing parts 721b and 722b.
  • any one gear 310, 320, 330, 340 of the plurality of first gears 300 selectively transmits power to the corresponding gears 410, 420, 430, 440 of the second gear 400.
  • the pressing portions (721b, 722b) are disposed adjacent to each other as shown by hatching in Figure 15 (a)
  • the first gear 300 and the second gear 400 is formed in an angle range larger than the angle range based on the rotation shaft 710 between the first gear 300 when shifting by one direction rotation of the shift control panel 720.
  • 2 pairs of gears corresponding to each other are configured to be in a power transmission state overlapping each other in a predetermined section.
  • the first clutch means and the second clutch means should be a structure capable of transmitting power in one direction and slip in the other direction to cut off the power.
  • the first gear 310 is described as having 1 stage, the first gear 320 as 2 stages, the first gear 330 as 3 stages, and the first gear 340 as 4 stages.
  • the first gear 310 When the first gear 310 is moved forward and connected to the second gear 410, the first gear 310 is in the first stage. In this case, the first gear 310 of the first stage is advanced to the second gear 420 while the first gear 320 of the second stage is advanced while the state of being advanced toward the second gear 410 is maintained. In this case, the second gear 410 slips with the first gear 310 due to the fast rotational force of the second gear 420 to over rotate. At this time, the power is shifted from the first gear to the second gear without any interruption. Thereafter, when the first gear 310 of the first stage is reversed while the second stage is engaged, the speed of the second stage is maintained.
  • Shifting on this principle enables smooth and accurate shifting while preventing power loss due to shifting during shifting.
  • the shift control means 700 is configured as a plate type shift control panel 720 as an example, but the shift control means 700 is not limited to such a configuration, and the hydraulic or air pressure or other individual adjustment mechanism It can be configured as a structure that can be adjusted individually.
  • the input shaft and the output shaft may be reversed to operate.
  • an inverse transmission ratio may be obtained in comparison with the above-described embodiment.
  • FIG. 16 is a longitudinal sectional view showing an internal structure of a transmission according to a fourth embodiment of the present invention
  • FIG. 17 is a side view of the guide member shown in FIG. 16
  • FIG. 18 is a power transmission control between the first clutch means and the second clutch means.
  • the shaft in which the first gear 300 and the second gear 400 are axially coupled is an integrated shaft 380.
  • the integrated shaft 380 is configured to penetrate the front fixing plate 110 and the rear fixing plate 120 so that both ends thereof protrude outward from the front fixing plate 110 and the rear fixing plate 120.
  • the first gear 300 and the second gear 400 are configured in seven stages, and the first gear 300 is always engaged at regular intervals on the outer circumferential surface of the main gear 200.
  • a plurality of second gears 410, 420, 430, 440, 450, 460 and 470 are provided in the same number as the first gear 300 and have different diameters, and the bearings 422 and 442 are connected to the integral shafts 380; 381, 382, 383, 384, 385, 386 and 387 respectively. It is.
  • the integrated shaft 380 is connected to the front fixing plate 110 and the rear fixing plate 120 via bearings 382a, 382b, 384a, and 384b so as to be supported forward and backward and rotatable.
  • a guide member 800 is provided to prevent the second gear 400 from moving toward the first gear 300 when the integrated shaft 380 moves backward (left side in the drawing).
  • the guide member 800 includes a circular plate 810 provided at one side of the second gear 400 facing the first gear 300.
  • a main gear through hole 820 through which the main gear 200 penetrates is formed, and a connection hole 830 through which the second clutch means 421 and 441 penetrates is formed.
  • the first clutch means 321, 341 and the second clutch means 421, 441 are connected to each other through the connection hole 830 while preventing the movement of the second gear 400 during the backward movement of the integrated shaft 380. have.
  • the shifting control means 700 for controlling the shaft of any one of the integral shafts (380; 381, 382, 383, 384, 385, 386, 387) to move forward and backward on the outer surface of the front fixing plate 110 and the outer surface of the rear fixing plate (120). ') Is provided.
  • the shift control means 700 ′ is provided on the first shift control member 730 provided on the outer surface of the front fixing plate 110 and the outer shift surface of the rear fixation plate 120, and the first shift control member 730.
  • the second shift control member 740 is rotated in conjunction with. Referring to FIG. 18, one end of both ends of the integrated shaft 380 selected to correspond to the gear shift stage may be pushed toward the front side of the inner side of the first shift control member 730 and the second shift control member 740.
  • Protrusions 731; 731a to 731g and locking grooves 741; 741a to 741g for locking the other end of the integrated shaft 380 are formed at positions corresponding to each other.
  • the transmission according to the present embodiment is a modification of some of the above-described configurations of the fourth embodiment, and includes bearings 322 and 342 at the connection portion between the integrated shaft 380 and the first gear 300 and the first gear. Both ends of the 300 are supported by the snap ring 900 fastened to the integrated shaft 380 such that the first gear 300 moves forward and backward together with the integrated shaft 380 when the integrated shaft 380 moves forward and backward. Consists of.
  • the integrated shaft 380 is configured to be connected between the front fixing plate 110 and the rear fixing plate 120 without a bearing as a medium through which the rotation is limited and is configured to only move forward and backward.
  • both ends of the first gear 300 are supported by the snap ring 900, and the second gear 400 is guided by the guide member 800 as in the fourth embodiment described above. It is configured to prevent movement to the side.
  • both ends of the second gear 400 are supported by the snap ring 900, and the first gear 300 is prevented from moving toward the second gear 400 by the guide member 800. It may also be configured to.
  • the first gear 300 is rotated in place, the second gear 400 is moved forward and backward by the worm wheel 620 or the ring gear described above is connected to the first clutch means and the second clutch means.
  • the transmission in accordance with the present invention while using a simple gear connection structure can be continuously transmitted power without shifting, while the main gear 200 and the first gear 300 is always maintained in a state of being engaged Since the shift is made, the shock generated during shifting can be alleviated, and the simplified structure makes it easy to manufacture and miniaturizes the device, and can be applied to a device that requires shifting such as a bicycle, a vehicle, or an industrial machine. .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Une transmission de la présente invention comprend: une plaque de fixation présentant une plaque de fixation avant et une plaque de fixation arrière disposées sur ses deux faces ; une transmission principale accouplée à un arbre qui pénètre dans la plaque de fixation arrière et qui est agencé de façon à pouvoir tourner et transmettre une force d'entraînement ; un premier pignon raccordé à un arbre qui pénètre dans la plaque de fixation avant et qui est agencé de façon à pouvoir se déplacer dans les sens avant et arrière de sorte que le premier pignon soit toujours en rotation et enclenché dans la transmission, le premier pignon présentant une surface pourvue de premières dentures; un second pignon soutenu au niveau de la plaque de fixation arrière et raccordé à un arbre de manière colinéaire avec l'arbre raccordé au premier pignon, le second pignon présentant une surface dotée de secondes dentures et opposée à ladite surface du premier pignon de sorte que les secondes dentures fonctionnent comme un engrenage en étant raccordées ou séparées des premières dentures par enclenchement avec le mouvement avant et arrière du premier pignon ; un pignon de sortie raccordé au second pignon par un moyen de transmission d'énergie; et un moyen de commande de transmission permettant de commander la fonction embrayage entre les premières dentures du premier pignon et les secondes dentures du second pignon.
PCT/KR2012/009996 2011-11-23 2012-11-23 Transmission WO2013077679A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2011-0123006 2011-11-23
KR1020110123006A KR20130057202A (ko) 2011-11-23 2011-11-23 변속기

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WO2013077679A1 true WO2013077679A1 (fr) 2013-05-30

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102044298B1 (ko) * 2018-06-28 2019-12-02 한국철도기술연구원 동력 차단이 가능한 철도차량용 전자기계 제동시스템

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6455450A (en) * 1987-08-24 1989-03-02 K Seven Kk Transmission
JPH0676959U (ja) * 1993-03-31 1994-10-28 ミノルタ株式会社 画像形成装置
JP2000291796A (ja) * 1999-04-05 2000-10-20 Daihatsu Motor Co Ltd 車両用変速機の自動シフト装置
JP2000310298A (ja) * 1999-04-27 2000-11-07 Asahi Optical Co Ltd モータ連動切換装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6455450A (en) * 1987-08-24 1989-03-02 K Seven Kk Transmission
JPH0676959U (ja) * 1993-03-31 1994-10-28 ミノルタ株式会社 画像形成装置
JP2000291796A (ja) * 1999-04-05 2000-10-20 Daihatsu Motor Co Ltd 車両用変速機の自動シフト装置
JP2000310298A (ja) * 1999-04-27 2000-11-07 Asahi Optical Co Ltd モータ連動切換装置

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