• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A gearing unit with planetary gearing employs a load sensor in the form of a stationary pin provided with a strain gauge transducer easily accessible via a bore in its casing. A brake with respective plate carriers is associated with the planetary gearing. One of these carriers is held stationary with the aid of the load sensor while the other of the carriers meshes via teeth with a rotatable component of the gearing. During operation the carriers lock together to hold the component of the planetary gearing stationary to permit drive to be transmitted. The load sensor is then subjected to force proportional to the dynamic loading on the gearing and brake. In the event of overloading the carriers are disengaged by hydraulic force in response to a signal from the sensor to permit the planetary gearing component to rotate and thus interrupts the drive.
    公开号:SU1443811A3
    申请号:SU843754758
    申请日:1984-06-27
    公开日:1988-12-07
    发明作者:Боле Вернер
    申请人:Геверкшафт Эйзенхютте Вестфалия (Фирма)；
    IPC主号:
    专利说明:

    in the form of a hollow wheel 17 with teeth 18 for engagement with planetary carriers 14 and external teeth 19. A safety coupling (PM) 20 is located in the transmission housing at the side of PS 4. It includes a rotating part 21 and a mating interface located therein part 22. The rotating part is made as a brake drum and has external teeth 24. The mating part 22 is fixed against rotation OF 32. The latter includes a pressure axis and an axis segment with strain gauges. During operation, the wheel 17 of the IC 4 transmission with the closed PM 20 is kept from rotation due to reliance on IZ 32. Through the holding force acting on IZ 32, the load and, correspondingly, the torque are measured continuously. When the preset torque is exceeded, the PM 20 is hydraulically opened. In this case, the hollow wheel 17 of the MS 4 freely rotates together with the rotating portion 21 PM 20. Thus, the transmission output is separated from the drive. 7 hp ff, 3 ill.
    The invention relates to a transmission, in particular for driving coal plows, chain scraper conveyors, etc., with overload protection, having a measuring element loaded due to the power flow in the transmission, which, depending on the load on the transmission output, controls the separation output transmission from the drive safety clutch.
    The purpose of the invention is to increase the durability of the transfer work and reduce the labor and material costs of its operation,
    FIG. shows the proposed transmission with safety clutch, horizontal section; in Fig. 2, the planetary gear stage with a brake drum attached to it and you; a measuring element filled in the form of a measuring axis; on fig.Z - measuring element with strain gauge strips located on it, top view.
    Transmission J (Fig. 1) is mainly intended for chain drives, in particular, for driving coal plow conveyed by means of chain drafts or for chain scraper conveyors, used primarily in underground mining. Transmission: 1 has in the general housing 2 transmissions a cylindrical part of the 3rd transmission and the planetary gear A of the transmission following it. The input shaft of the gear unit is designated with the position 5, and its output shaft is marked with the position 6. With the output shaft 6 in the case of the plow drive, the plow sprocket is connected. 5 The kinematic chain of the 3-cylinder cylindrical part includes cylindrical gears 7-10. The cylindrical wheel 7 is located on the input shaft 5 installed in the transmission housing 2, while the cylindrical wheel 10 is located on the shaft 11 which is coaxial with the output shaft 6 of the transmission 11. With the shaft 11 it is connected to a rotational shaft 12 by rotation wheel 13 planetary gears 4th gear. Three planetary carriers 14 are engaged with the sun wheel 13, mounted with the possibility of rotation on axes 15 on a common planetary carrier 16. Planetary drivers 14 are in gear with a hollow coaxially engaging sun wheel 13.
    5 wheel 17, equipped with internal
    teeth 18 for engagement with the planetary carrier 14 and the outer teeth 19. The planet carrier 14 carries the output shaft 6 of the transmission 1.
    0 In the gear housing 2, to the side of the planetary gear stage 4, there is a safety clutch 20 operating as a brake, which consists of a switchable electro-hydraulic 5 KIM by means of a disc friction clutch, and includes
    3
    the rotating gear unit 2 with the possibility of free rotation and located in this part coaxially with it, the mating part 22 of the mufti. Between the rotating part 2J and the mating part 22 of the coupling there is a package of 23 friction disks made in the usual way, part of the friction disks of which is connected to the rotating part 21, and the part with the coupling mating part 22, however, with the possibility of axial displacement. The rotating part 21 is designed as a brake drum and has external teeth 24, with which a transfer part, namely a hollow wheel 17, is kinematically connected to a fixed part during operation. As shown in Fig. 2, the kinematic connection is made through a small intermediate wheel 25 with external teeth On the one hand, it engages with the outer teeth 19 of the hollow wheel 17 and, on the other hand, with the outer teeth 24 of the rotating part 21 of the safety clutch. The rotating part 21 is mounted in bearings in the transmission housing. Confronted with



    The coupling part 22 is located on the axle of the 30 mating coupling part 22 of the coupling 26 installed in bearings 27 there is a pressure cavity 37 of annular shape, when loaded with pressure which the pressure ring 36 moves 28 bearing flange 29 .. The flange 29 has an outer circumference groove with a radial thrust surface 30.
    The housing 2 of the transmission 1 is fitted on the spring 35 of the locking device to the outer circumference of the flange 29 state - (not shown), and by this the most secure axial protection against the restoring force
    from the opening, a receiving chamber 31 for the measuring element 32, which is made (FIG. 2) in the form of a measuring axis, carrying at least one tensometric strip 34 on a section of the axis 33 that narrows down in diameter (four shown diagonally with respect to axes strain gauges 34). A larger diameter part of the axis is threaded and screwed outside into the internal thread of the receiving chamber 31. Thus, the measuring element 32 is installed in the receiving chamber 31 and the latter is locked out. In accordance with this, the measuring element at the same time forms a closure part for the receiving chamber.
    The receiving chamber continues axially inward into the hole, which takes as an intermediate element a pressure axis 35, resting one end on the abutment surface 30 of the flange 29 and the other end on the measuring element 32. The measuring element and the pressure axis are approximately tangential to the flange 29. With the closed safety clutch 20, the matching part 22 of the coupling rests through the pressure axis 35 on the measuring element 32, Thus with the closed safety clutch the hollow wheel J 7 y erzhivaets from rotating.
    With the drive reversible in the direction of rotation, the flange 29 can also be attached with two diametrically opposed measuring elements 32 in the structure shown, so that the mating part 22 of the coupling and the hollow wheel 17 are held by both measuring elements in B1 than the axes from rotating in both directions of rotation.
    The mating part of the clutch 22 bears on itself an axial displaceable pressure ring 36, which is adjacent to the package 23 of the friction discs. Between the lining ring 36 and the annular ring, the axis flies against the restoring force
    Coupler sleeve 20 opens. The discharge cavity 37 through channels 38 and 39 is connected to an external source of hydraulic pressure medium. The channels 38 and 39 are made in the form of axial and radial holes in the axle shaft 26 and the part located on it in the form of the hub of the mating part 22 of the coupling.
    During operation, the hollow wheel 17 of the planetary gear 4 gear with the closed safety clutch 20 is held by rotating the measuring element 32 against rotation. Through
    The holding force acting on the measuring element 32 continuously changes the load, respectively the torque, on the output shaft 6 of the transmission. Electrical measurements
    rhythmic values through the wires 40 (FIG. 3), brought out of the receiving chamber 31, are supplied to an electronic control device (not shown) that controls the safety
    the clutch 20 according to the torque acting at the transmission output in such a way that when the pre-assigned torque is exceeded (The moment, for example, when the plow is blocked), the safety clutch 20 by hydraulically locking the magnetic valve attached to the safety clutch opens so that the hollow wheel 17 of the planetary stage 4 the transmission can freely rotate together with the rotating part 21 of the safety clutch 20 and thus the transmission output is separated from the actuator. short switching times, the known magnetic valve is predominantly known servoventil, the switching time of which is at most about 20 ms, mostly less than 10 ms. Through channels 38 and 39 with a closed safety clutch 20, there is a constant circulation pressure in the hydraulic system, which includes the pressure chamber 37, so that the hydraulic system is kept at a pre-assigned pre-stress, In addition, the response time of the safety clutch decreases,
    权利要求:
    Claims (7)
    [1]
    1. Transmission with overload protection, in particular to drive coal plots, including a gear housing, a flow-loaded measuring control element depending on the load at the gear output by a safety clutch separating the gear output from the gear drive, characterized in that in order to increase the durability of the transfer and to reduce the labor and material costs of its operation, the measuring element is designed as a pressure axis with strain gages located on it and installed inserted in the housing slot with the possibility of its replacement, the safety coupling is made with rotating and mating parts, the last of which is fixed from the rotating element by the measuring element, and the gear is equipped with a planetary stunt
    5 0 5 0
    five
    0
    five
    0
    The foam is fixed during operation, the part of which is made in the form of a hollow wheel, with external teeth, mounted in the housing with the possibility of kinematic interaction with the rotating part of the safety clutch and rotation when the position is open with the last.
    [2]
    2. Transmission according to claim, characterized in that the rotating part of the safety clutch is made in the form of an externally threaded brake drum, which is installed with the possibility of interaction through an intermediate wheel with a fixed part of the transmission of the planetary stage.
    [3]
    3. Transmission according to claims 1-2, characterized in that the mating part of the safety coupling is provided with a flange, the outer cylindrical surface of which is made with a recess of the measuring element.
    [4]
    4J The transmission according to claims 1–3, which is based on the fact that the axis of the measuring element is designed as a locking housing for the closure part with a thread,
    [5]
    5. Transmission according to claims 1–4, which means that the safety clutch is made in the form of an electro-hydraulically openable disk friction clutch, and the matching part is connected with a linear connection leading to the pressure cavity of the safety clutch.
    [6]
    6, the transmission according to claims 1-5, which is flashing with the fact that the safety coupling is located in the transmission housing or in the additional housing attached thereto, which is provided with a socket for the measuring element.
    [7]
    7. Transmission of pop. 1 differs in that it is equipped with an additional diametrically opposite main measuring element.
    8, Transfer according to claims 1-7. characterized in that the mating part of the safety coupling is fixed by measuring elements against rotation in both directions of rotation.
    FIG. 2
    "Ff
    -L J "L
    Fig.z
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1443811A3|1988-12-07|Transmission protected against overload, particularly, for coal plough drive
    US4614134A|1986-09-30|Overload protection system for planetary gear drive
    US4215594A|1980-08-05|Torque responsive speed shift mechanism for power tool
    US4279330A|1981-07-21|Double-acting disc brake
    US6142274A|2000-11-07|Power take-off unit with selectively engaged brake
    US4976667A|1990-12-11|Differential clutch and lever actuation system therefor
    US4516444A|1985-05-14|High-low braked gear drive
    WO1996041089A1|1996-12-19|Hydraulically-operable locking differential with in-line piston means
    US4179016A|1979-12-18|Final drive gearing with brake
    US4762215A|1988-08-09|Brake torque limiting coupling
    US4186826A|1980-02-05|Torque limiting clutch brake
    US3685371A|1972-08-22|Reversing transmission
    US4682678A|1987-07-28|Gearing units for use with mining equipment
    GB2141199A|1984-12-12|Overload protection in gearing units for use with mining apparatus
    RU1811557C|1993-04-23|Device for drive of chain ploughing unit
    US4049103A|1977-09-20|Automatic transmission
    US4919008A|1990-04-24|Differential smart clutch with gear reaction
    US3833099A|1974-09-03|Sealed oil filled clutch with brake means to inhibit rotation upon disengagement
    US4238967A|1980-12-16|Driving arrangement
    US4195537A|1980-04-01|Automatic transmission
    US2825234A|1958-03-04|Multiple arrangement for frictional power transmission
    US5819895A|1998-10-13|Bridging device for a hydrodynamic hydraulic coupling
    SU1038651A1|1983-08-30|Internal safety clutch
    CA1227188A|1987-09-22|Winch drive means
    JP2770240B2|1998-06-25|Lifting device brake device
    同族专利:
    公开号 | 公开日
    FR2548263B1|1988-03-11|
    BE900008A|1984-10-15|
    US4601218A|1986-07-22|
    FR2548263A1|1985-01-04|
    ZA844856B|1985-02-27|
    DE3323250A1|1985-01-10|
    GB2142405A|1985-01-16|
    AU559876B2|1987-03-19|
    GB2142405B|1986-07-16|
    GB8416149D0|1984-08-01|
    AU2992584A|1985-01-03|
    PL248398A1|1985-03-12|
    DE3323250C2|1992-12-10|
    PL141431B1|1987-07-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB488154A|1936-12-02|1938-07-01|Siemens App Und Maschinen Gmbh|Improvements in or relating to torque measuring devices|
    US2436947A|1943-11-23|1948-03-02|Elox Soc|Overload release clutch|
    US2791920A|1952-08-16|1957-05-14|Gen Controls Co|Load operating device with automatic disconnecting mechanism|
    US2790340A|1954-09-07|1957-04-30|Mach Tool Control Corp|Work-load indicator|
    FR1169955A|1956-03-26|1959-01-08|Maschf Augsburg Nuernberg Ag|Safety device in the event of an overload for winches, in particular dam valve winches|
    US3078750A|1959-07-06|1963-02-26|Harris Intertype Corp|Cutting machine|
    US3613721A|1969-12-17|1971-10-19|Allis Chalmers Mfg Co|Wicket gate overload sensor and protector|
    DE2460098C3|1974-12-19|1982-06-16|Gewerkschaft Eisenhütte Westfalia, 4670 Lünen|Electric chain drive for planing systems, chain conveyor and the like.|
    GB1587294A|1977-06-02|1981-04-01|Dresser Europe Sa|Mining machine haulage transmission|
    DE3043237C2|1980-11-15|1989-04-27|Gewerkschaft Eisenhuette Westfalia Gmbh, 4670 Luenen, De|
    JPS6250692B2|1981-09-08|1987-10-26|Kubota Ltd|DE3425638C2|1984-07-12|1993-09-30|Westfalia Becorit Ind Tech|Gearbox with overload protection, in particular for driving coal planes and the like.|
    DE3510455C1|1985-03-22|1993-07-29|Klöckner-Becorit GmbH, 4620 Castrop-Rauxel|Drive for heavy starting machines in underground mine operation|
    DE3545314C2|1985-12-20|1991-04-18|Jahnel-Kestermann Getriebewerke Bochum Gmbh, 4630 Bochum, De|
    AT385086B|1986-04-16|1988-02-10|Voest Alpine Ag|DRIVE ARRANGEMENT FOR THE SCRAPER HEADS OF A SCRAPER|
    DE4002303A1|1990-01-26|1991-08-01|Gewerk Eisenhuette Westfalia|Electric motor and associated gears|
    DE4021302A1|1990-07-04|1992-01-16|Atlas Copco Eickhoff Road|Cutting and loading machine - has load sensing on conveyor with control of cutting speed to prevent overloading|
    US5071397A|1990-10-01|1991-12-10|Sundstrand Corporation|Jam tolerant geared rotary actuator with automatic disconnect|
    US5304102A|1991-02-21|1994-04-19|Nissan Motor Co., Ltd.|Control for shift in automatic transmission|
    DE9312367U1|1993-08-25|1994-01-27|Wangermann Jochen R Dr Ing|Planetary gear|
    LT4160B|1995-06-16|1997-05-26|Bendra Lietuvos Ir Jav Imone A|Archimed and gravity motor|
    US5779587A|1996-08-30|1998-07-14|Curtiss Wright Flight Systems, Inc.|Jam tolerant rotary actuator with shear pins and disengagement coupling|
    DE19752242A1|1997-11-26|1999-06-17|Tueschen & Zimmermann|Drive train for chain conveyors|
    DE19835334C2|1998-08-05|2003-04-10|Tueschen & Zimmermann|Drive train for equipment used underground with circulating chain train|
    US6260668B1|1999-04-29|2001-07-17|Highland Machinery Corporation|Brake system for electrically powered vehicles|
    CN106068200B|2014-01-16|2020-02-28|传输Cvt股份有限公司|Slip control method and arrangement for a powertrain system comprising a continuously variable transmission|
    CN106795964A|2014-07-30|2017-05-31|传输Cvt股份有限公司|For the hydraulic pressure control method by sliding and device of the power train including buncher|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE3323250A|DE3323250C2|1983-06-28|1983-06-28|
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