WO2017150952A1 - Réducteur de vitesse pour camion mélangeur de béton - Google Patents

Réducteur de vitesse pour camion mélangeur de béton Download PDF

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Publication number
WO2017150952A1
WO2017150952A1 PCT/KR2017/002384 KR2017002384W WO2017150952A1 WO 2017150952 A1 WO2017150952 A1 WO 2017150952A1 KR 2017002384 W KR2017002384 W KR 2017002384W WO 2017150952 A1 WO2017150952 A1 WO 2017150952A1
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WO
WIPO (PCT)
Prior art keywords
gear
reducer
planetary gear
output shaft
flange
Prior art date
Application number
PCT/KR2017/002384
Other languages
English (en)
Korean (ko)
Inventor
손호연
김당주
배명호
이종문
김지윤
김봉근
김동한
Original Assignee
(주)대호하이드로릭
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
Priority claimed from KR1020160026597A external-priority patent/KR20170103547A/ko
Priority claimed from KR1020160165334A external-priority patent/KR101756459B1/ko
Application filed by (주)대호하이드로릭 filed Critical (주)대호하이드로릭
Priority to CN201780000144.9A priority Critical patent/CN107407375A/zh
Priority to PH12017501320A priority patent/PH12017501320A1/en
Publication of WO2017150952A1 publication Critical patent/WO2017150952A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28C—PREPARING CLAY; PRODUCING MIXTURES CONTAINING CLAY OR CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28C5/00—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions
    • B28C5/42—Apparatus specially adapted for being mounted on vehicles with provision for mixing during transport
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
    • B60P3/00—Vehicles adapted to transport, to carry or to comprise special loads or objects
    • B60P3/16—Vehicles adapted to transport, to carry or to comprise special loads or objects for carrying mixed concrete, e.g. having rotatable drums
    • 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
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • 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
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings

Definitions

  • the present invention relates to a speed reducer of a mixer truck for concrete placing, and in particular, the warp center of the speed reducer including the mixer drum and a cover flange supporting the mixer drum is formed to be located at the rear of the speed reducer, so as to provide vibration, load, impact, output, and the like. It is an invention for a reducer that has a strong performance against a load.
  • a concrete mixer truck carries a ready-mixed concrete mixed with cement, sand, gravel and water in a production plant of ready-mixed concrete (bottle dough or plaster or fresh concrete) to a construction site.
  • 1 is a view showing a conventional concrete mixer truck.
  • a general concrete mixer truck operates a motor and a reducer 1 connected to the motor in order to prevent solidification of the ready-mixed concrete in the mixer drum during transportation of the ready-mixed concrete.
  • the ready-mixed concrete inside the mixer drum is stirred while rotating at a speed (for example, 5 to 10 rpm).
  • the reducer 1 of the concrete mixer truck is driven by a hydrostatic motor, which is an essential device for rotating the mixer drum, to change the power to the required rotational force according to the speed.
  • the gear of the reducer 1 of the concrete mixer truck as described above utilizes various types of planetary gear systems to smoothly rotate the initial mixer drum.
  • Planetary gear systems are a very important part of mixer reducers with regard to the strength problems of concrete mixer trucks.
  • studies on bending and compression loads and analysis of specifications of the planetary gear system of the mixer reducer (1) are essential. Is done.
  • 2 is a cross-sectional view showing a speed reducer 1 according to the prior art. 2 is a view shown in US Patent Publication 2008-0318722.
  • the reducer 1 is firmly installed on the fixed base 2.
  • the fixed base 2 connects and fixes the reducer 1 to the chassis.
  • the reducer 1 in the related art transmits the driving force of the motor to the planetary gear mechanism through the shaft 10 to rotate the mixer drum.
  • the plunger 20 moves from the shaft 10 toward the mixer drum. 10, which is supported from the bearing 21, the plunger 20 is connected to the planetary gear mechanism (30 ⁇ 33) and is configured to transmit the driving force of the motor to the drum.
  • the reducer according to the prior art as shown in FIG. 2 causes the center of light (ac) to be directed toward the front (motor side) of the reducer 1 by the weight of the mixer drum and the ready-mixed concrete and the planetary gear mechanism supporting the mixer drum. do.
  • the plunger 20 and the bearing 21 which act as a kind of jig absorb the fluctuations of the center of the light (a.c.).
  • the plunger 20 and the bearing 21 only have to endure all the swing angle loads, and thus the durability of the high load, the shock due to vibration, the wear phenomenon, etc. is weak, and due to the structural limitations, the plunger 20 and the bearing There is a problem that the service life of (21) is shortened.
  • Japanese Patent No. 3,369,72 relates to the self-weighting of a concrete mixer truck drum loading weight, and a problem is to accurately detect a load sharing state of concrete in a drum based on a detection value of a load sensor.
  • US Patent No. 7832919 discloses a design related to a gear train for driving a mixer drum mounted on a vehicle, which discloses a design for absorbing the weight of the drum and the inner concrete.
  • An object of the present invention devised to solve the problems of the prior art is to provide a speed reducer of a mixer truck that is improved in durability and has a longer service life.
  • the present specification is to provide an invention in which the internal structure of the reducer is improved to effectively distribute the load load acting on the mixer drum.
  • a reducer of a concrete mixer truck the reducer housing;
  • a planetary gear train accommodated in the reducer housing and configured to transmit power;
  • a gear flange having a first tooth shape formed on an outer circumference thereof to be engaged with the planetary gear train;
  • An output shaft having an end connected to the gear flange and a plurality of keys cut in an axial direction;
  • An internal gear having a spline formed at an inner circumference of the output shaft to allow slip motion, and an outer circumference having a second tooth shape;
  • a cover flange formed with a frame having a predetermined thickness to support the mixer drum in a circumferential direction, and having a third tooth shape formed in the hollow inner circumference of the hollow gear so as to engage with the internal gear.
  • the gear flange, the planetary gear train is connected to one side, the output shaft may be connected to the other side.
  • the output shaft a bearing is mounted in the vicinity of the gear flange along the longitudinal direction of the shaft may be accommodated in the housing.
  • bearing may be a roller bearing for supporting the load of the mixer drum
  • a plurality of roller bearings are located on the side of the output shaft along the longitudinal direction of the output shaft, and the size of the roller bearing closer to the gear coupling side is larger than the roller bearing close to the gear flange side of the plurality of roller bearings. It may be characterized in that it is formed to be large.
  • the output shaft may be coupled to the cover flange in a state in which an internal gear is mounted at a position spaced apart from the gear flange along the longitudinal direction of the shaft and protrudes out of the housing.
  • the gear flange and the output shaft may be integrally formed.
  • the planetary gear train is a differential planetary gear train, which includes a sun gear, a planet gear meshed with an outer circumference of the sun gear, a carrier for receiving the planet gear, and a ring gear engaged with the outer circumference of the planet gear.
  • the planetary gear includes a non-rotating ring gear and a first planetary gear meshing with the non-rotating ring gear among the rotating ring gears, and a second planetary gear meshing with the sun gear, wherein the planetary gear and the carrier are cluster gear type,
  • the carrier may accommodate the first planetary gear and the second planetary gear together, and the rotary ring gear may transmit the decelerated output from the planetary gear to a gear flange engaged with an inner circumference of the rotary ring gear.
  • the planetary gear may be connected to the carrier through a pin penetrating the planetary gear, and may include a gear bearing between the pin and the planetary gear.
  • the reducer of the mixer truck may further include an elastic member for supporting the axial load of the output shaft,
  • the center bush may further include.
  • the rocking portion of the light center is formed on the rear side (drum side) of the reducer, not on the front side of the reducer, and as a result, there is an effect of improving durability of the reducer by dispersing disturbance acting on the reducer. .
  • the service life of the speed reducer can be considerably extended compared to the prior art, and the product reliability can be improved.
  • 1 is a view showing a conventional concrete mixer truck.
  • FIG. 2 is a cross-sectional view showing a speed reducer according to the prior art.
  • FIG 3 is a perspective view showing a reducer according to an embodiment of the present invention.
  • Figure 4 is an exploded perspective view showing a reducer according to an embodiment of the present invention.
  • FIG. 5 is a view showing a side view of the drawing of FIG. 4.
  • FIG. 6 is a cross-sectional view showing a speed reducer according to an embodiment of the present invention.
  • FIG. 7 is a diagram illustrating a drum load acting on a reducer and a state in which loads are distributed within the reducer.
  • FIG. 8 is a view showing a gear flange, an elastic member and an output shaft according to an embodiment of the present invention.
  • FIG. 9 is a view showing the input and output gear ratio of the planetary gear train according to an embodiment of the present invention.
  • connection herein includes direct connection and indirect connection between one member and another member, and may mean all physical or electrical connections such as adhesion, attachment, fastening, bonding, and coupling.
  • the concrete mixer truck reducer 100 of the present invention comprises a reducer housing 110; A planetary gear train 120 accommodated in the reducer housing 110 and provided to transmit power; A gear flange 130 having a first tooth shape g1 formed on an outer circumference thereof to be engaged with the planetary gear train 120; An output shaft 140 whose end is connected to the gear flange 130 and a plurality of keys are cut in the axial direction; An internal gear 150 having a spline formed on a key of the output shaft to allow slip movement, and a second tooth shape g2 formed on an outer circumference; And a cover flange 160 having a third thickness g3 formed at a hollow inner circumferential edge of the hollow inner circumference to be engaged with the internal gear 150, and a frame having a predetermined thickness to support the mixer drum in the circumferential direction.
  • the reducer housing 110 may be divided into a front housing 110a on the motor side and a rear housing 110b on the mixer drum side, and the planetary gear train 120 and the gear flange 130 inside the reducer housing 110. Etc. can be accommodated.
  • the front housing 110a and the rear housing 110b should be able to be firmly bound to each other by a fastening mechanism such as a bolt, and sealed as various sealing members to protect the electrical equipment contained therein from the inflow of external foreign substances such as rainwater. It may be a structure.
  • the base 101 of the present invention is integrally connected to the rear housing 110b
  • the present invention is not necessarily limited thereto, and other embodiments or details within an equivalent range may be fixed if the base 101 of the present invention is stably fixed from the undercarriage of the vehicle.
  • An exemplary configuration will also be included within the scope of the present invention.
  • the base 101 may be integrally connected with the front housing 110a of the reducer.
  • the mixer drum should be inclined and rotated in order to prevent solidification of the concrete mixer. Therefore, the reducer housing 110 of the present invention may be inclined at a predetermined angle. When installed in, it is arranged to be inclined at a certain angle.
  • the planetary gear train 120 of the present invention is a planetary gear 122 and the planetary gear that are accommodated in the sun gear 121 and the sun gear 121 are accommodated in the reduction gear housing 110 and receives a driving force from a driving motor.
  • Carrier 124 for receiving 122 and the planetary gear 122 may include a ring gear 123 is engaged.
  • the configuration of the planetary gear train 120 including the planetary gear 122 and the carrier 124 adopts a cluster gear type to improve the durability of the entire planetary gear train 120.
  • the target output and the rotational speed can be set variously according to the embodiment, and a very large reduction ratio can be obtained depending on the number of teeth and the teeth of the gear.
  • a detailed tooth of the planetary gear train 120 and a detailed description thereof will be omitted, but technical features of the planetary gear train 120 of the present invention will be described in detail later with reference to FIG. 9.
  • Gear flange 130 of the present invention is connected to the planetary gear train 120, the gear (g1) may be formed on the outer circumference as a component that receives the driving force. Specifically, the gear flange 130 in which the gear teeth are formed on the outer circumference of the gear flange 130 is engaged with the gear formed on the inner circumference of the ring gear 123 to transmit the driving force to the mixer drum side.
  • the output shaft 140 of the present invention has a predetermined length and is configured to transfer the driving force transmitted through the gear flange 130 to the mixer drum side.
  • the output shaft 140 is connected to the gear flange 130 and a plurality of keys are cut in the axial direction.
  • the gear flange 130 and the output shaft 140 may be integrally formed.
  • Internal gear 150 is configured to surround a portion of the output shaft 140, the spline (sp) is formed on the inner periphery so as to allow a slip movement is fitted to the key (key) of the output shaft, the second periphery As a gear member having a tooth shape g2, it may serve to transmit power transmitted from the output shaft 140 to the mixer drum side.
  • the cover flange 160 is located on the outer side of the internal gear 150, the cover flange 160 is formed in the hollow inner circumference so as to be engaged with the internal gear 150, and a third tooth shape g3 is formed and is circumferential.
  • Direction may be made of a frame formed to have a predetermined thickness to support the mixer drum.
  • the planetary gear train 110 is located on the opposite side of the gear coupling with respect to the gear flange 130.
  • Gear coupling refers to a configuration including the internal gear 150 and the cover flange 160, the gear coupling is the output shaft 140 outside the reduction gear housing 110 It is connected to one end of.
  • the internal gear 150 acts as a hub and the cover flange 160 acts as a sleeve to operate as a gear coupling as a whole.
  • the cover flange 160 may be an element that directly contacts the mixer drum.
  • the internal gear 150 may be an internal gear 150 that is engaged with the inner circumference of the cover flange 160 and is also engaged with the output shaft 140.
  • the gear flange 130 may have a planetary gear train 120 connected to one side thereof, and an output shaft 140 connected to the other side thereof. That is, the planetary gear train 120 is connected to one side of the gear flange 130 and the output shaft 140 is connected to the other side.
  • the planetary gear train 120 is located at the motor side with respect to the gear flange 130, and the output shaft 140 is located at the mixer drum side. That is, the planetary gear train 120 is located on the opposite side of the gear coupling with respect to the gear flange 130.
  • the overall center of gravity is relatively high, while in the present invention, the overall center of gravity of the components including the reducer and the mixer drum is lowered compared to the prior art. There is. Thus, the stability of the mixer truck itself is improved.
  • the output shaft 140 is mounted with the internal gear 150 at a position spaced apart from the gear flange 130 along a longitudinal direction of the shaft by a predetermined distance. At this time, the output shaft 140 is mounted with the internal gear 150 in a state protruding outside the housing 110, and is also connected to the cover flange 160 via the internal gear 150.
  • the center of gravity is lower than the prior art, but on the contrary, the center of light (ac) ) Moves a considerable distance from the motor side to the mixer drum side.
  • the outer periphery of the output shaft 140 is formed with a stepped portion 142 can be distinguished from the outer side and the inner side of the reducer housing 110 from this.
  • the stepped portion 142 may serve as a kind of bush to serve as a boundary between the reduction gear 110 housing and the internal gear 150. In addition, it may serve to seal the inside so that oil supplied to prevent wear of the gear mechanism does not leak from the reducer 100.
  • the stepped portion 142 may be an annular body made of a rigid material.
  • the gear flange 130 and the output shaft 140 may be integrally formed.
  • the gear flange 130 is connected to one end of the output shaft 140 in the longitudinal direction, and a key may be formed along the outer periphery of the output shaft 140 along the axial direction.
  • a fixing key 140 ′ is formed at the outer circumference of the output shaft 140 to secure one end of the output shaft 140 to the internal gear 150 or the mixer drum side. It may be.
  • the internal gear 150 may be formed on a spline at an inner circumference of the internal gear 150 to be inserted into a key of the output shaft 140 to allow slip motion.
  • the spline sp is an involute spline, and a plurality of teeth corresponding to a key may be arranged at equal intervals to transmit a large torque. Accordingly, by adjusting the clearance between the key (key) of the output shaft 140 and the spline (sp) of the internal gear 150, it is possible to give the role of appropriately adjusting the allowable swing angle according to the mixer drum rotation.
  • the allowable swing angle here can be set around -6 ° to + 6 °.
  • a second tooth shape g2 may be formed at the outer circumference of the internal gear 150, and the second tooth shape g2 is engaged with the third tooth shape g3 formed at the inner circumference of the cover flange 160, thereby preventing the internal gear. 150 may transfer the driving force received from the output shaft 140 to the cover flange 160 again.
  • the cover flange 160 is formed to surround the internal gear 150, and the hollow inner circumference of the internal contact gear 150 may be formed to correspond to the shape of the internal gear 150.
  • the internal gear 150 may correspond to a ball gear.
  • the periphery of the second tooth g2 is formed to have a gentle slope curve in cross section.
  • the internal gear 150 may be formed as a spherical body having a constant radius of curvature r. Further, as shown in the figure, when viewed from the whole by processing the one end and the other end, the inside may be a ring-shaped internal gear 150 in which a spline is formed and the outer circumference is formed with a gear g2.
  • a third tooth shape g3 is formed at an inner circumference thereof, and a frame having a predetermined thickness in the circumferential direction is formed.
  • the cover flange 160 of the present invention may be divided into a first cover flange 160a (or front cover flange) in the motor direction and a second cover flange 160b (or rear cover flange) in the mixer drum direction.
  • the first cover flange 160a contacts the second cover flange 160b and simultaneously binds the internal gear 150. You can.
  • the outer circumference of the internal gear 150 of the present invention may be formed such that the surface adjacent to the second tooth shape g2 has a spherical surface having a predetermined radius of curvature r as viewed in cross section.
  • a curved paper surface c may be formed on the inner circumference of the cover flange 160 to surround the internal gear 150.
  • the durability of the load acting on the center of the transcritical center (a.c.) can be further increased.
  • the gear coupling formed of the internal gear 150 and the cover flange 160 can be mounted close to the reducer output, that is, the mixer drum side, the gear coupling in the related art is used. It can be installed inside the reducer and prevents the risk of damage to the gear coupling due to the rocking of the mixer drum.
  • the gear coupling of the present invention has an advantage of excellent serviceability by being located on the output side.
  • roller bearing and the elastic member as a shock absorber for the working load of the reducer of the present invention will be described in detail.
  • roller bearing 141 for supporting the load of the mixer drum.
  • the roller bearing 141 may support the output shaft 140 more firmly by applying a taper roller bearing.
  • a plurality of roller bearings 141 are positioned along the longitudinal direction of the output shaft 140 in the side of the output shaft 140, according to an embodiment of the present invention.
  • the roller bearing close to the gear coupling side may be larger in size than the roller bearing close to the gear flange 130.
  • the roller bearing closer to the gear flange 130 side may be referred to as the front bearing 141a
  • the roller bearing closer to the gear coupling side may be referred to as the rear bearing 141b, that is, the rear bearing 141b than the front bearing 141a. It is to be molded by mounting the size of the larger.
  • the drum load Wd applied through the output shaft 140 causes a load on the planetary gear train 120 in the longitudinal direction of the output shaft 140.
  • a very large load acts on the output shaft 140 and the gear flange 130 connected thereto, which causes a major failure of the speed reducer.
  • a plurality of roller bearings 141 are provided to reduce the load acting on the gear flange 130.
  • the roller bearing 141 shown in FIG. 6 is located in the up and down directions with respect to the axial direction of the output shaft 140, the roller bearing 141 is shown based on the axial direction of the output shaft 140 according to an embodiment. It may be arranged radially.
  • the rear bearing 141b located at the rear side (mixer drum side) of the plurality of roller bearings 141 is relatively compared to the front bearing 141a located at the front side (motor side). It is characterized by a large size.
  • a very large load acts on the reducer. If the load is not properly controlled, a very large stress is generated at the bent portion of the output shaft 140 to the gear flange 130. In some cases, cracks or breakages occur, which is a fatal problem.
  • the load formed on the inlet side (mixer drum side) of the reducer housing 110 of the output shaft 140 has a rear bearing 141b having a relatively larger size than the front bearing 141a.
  • the size of the front bearing 141a is larger than the rear bearing 141b, since the load acting on the bearing is transmitted toward the inner planetary gear train 120 mostly without facing the surface direction of the reducer housing 110. High risk of breakage is undesirable. Therefore, according to the present embodiment, there is an effect to withstand larger loads compared to the embodiment in which the size of the bearing is uniformly common in the front and the rear or the front bearing 141a is larger than the rear bearing 141b.
  • the reducer may arrange the elastic member S therein to support the load of the mixer drum transferred in the axial direction of the output shaft 140.
  • the elastic member S may correspond to a general spring, but a plate spring having excellent space utilization rather than a tension spring is preferable.
  • the elastic member S may serve as a shock absorber against a load acting in the axial direction of the output shaft 140 by its elastic force.
  • a center bushing CB may be provided between the sun gear 121 and the elastic member S to further improve the buffering capacity against the load in the axial direction.
  • an eastern bush formed of a special alloy may be used as the center bush CB. By forming a valley (not shown) on the surface of the center bush CB, the effect of increasing lubricity by oil flowing inside the planetary gear train may be exerted. The lubrication effect of the eastern sheath at high speed rotation between the shaft and the carrier has the effect of increasing the service life of the gear train.
  • roller bearing 141 serves to primarily buffer by distributing the load acting on the reducer to the housing surface, the elastic member s secondly buffers the load acting on the reducer by using elastic force. Play a role. And when the center bush (CB) is provided with a buffer function over three stages, it is possible to significantly improve the durability of the reducer against the axial load.
  • CB center bush
  • the differential planetary gear train of the present invention includes a sun gear 121, a planetary gear 122 engaged with the outer circumference of the sun gear 121, and a carrier 124 for receiving the planetary gear 122 and the planetary gear. And a ring gear 123 engaged to an outer circumference thereof, wherein the planetary gear includes a first planetary gear 122a engaged with the non-rotating ring gear 123a of the non-rotating ring gear 123a and the rotating ring gear 123b.
  • the second planetary gear 122b meshes with the sun gear 121.
  • the planetary gear 122 carrier 124 is a cluster gear type, and may accommodate the first planetary gear 122a and the second planetary gear 122b together in the carrier 124. 123 may transmit the decelerated output from the planetary gear 122 to the gear flange 130.
  • the planetary gear train structure of the present invention is specialized in the speed reducer of the mixer drum, and since the drum rotates only in one direction, when the ring gear is bolted to the housing and not rotated, the planetary gear train of the present invention is different from the general differential planetary gear train commonly used in a vehicle. It is not necessary to have a configuration such as a clutch, but rather a simpler and more compact design can be borrowed, but there is an advantage that a large reduction ratio can be obtained depending on the number of gear teeth and the design of the teeth.
  • the planetary gear train of the present invention is connected to the carrier 124 through the pin 122c penetrating the planetary gear 122 as the planetary gear 122 of the cluster gear type, the pin 122c and the planetary gear 122. ) Is provided with a gear bearing 122d.
  • a gear bearing 122d As the gear bearing 122d of the present invention, similarly to the roller bearing 141 described above, tapered bearings can be used to disperse the load in the axial direction, thereby improving the durability of the planetary gear train. This allows the roller bearing 141 to absorb and distribute the axial load primarily, and the gear bearing 122d to absorb and distribute the axial load secondarily.
  • the planetary gear train 120 is designed to fit a differential planetary gear used in a conventional vehicle to a reducer of a mixer truck, and to have a simple structure and a compact structure while obtaining a high reduction ratio.
  • a complex planetary gear train structure composed of a combination of a plurality of sun gears, a plurality of planetary gears, and a plurality of carriers commonly used in a conventional mixer reducer, one sun gear 121, a cluster gear type planetary gear (122) and ring gears (123).
  • the power is output to the ring gear 123, it is formed to face toward the mixer drum through the gear flange 130 in the ring gear 123.
  • the ring gear 123 and the gear flange 130 is rotated in a state of having a slight gap between the rotation and the gear flange 130 and the ring gear 123 by bringing the advantages in manufacturing and at the same time, the ring gear 123
  • the dynamic load in the radial direction (the direction perpendicular to the axial direction) acting on) is distributed and absorbed in the ring gear 123 and the gear flange 130, respectively.
  • the length of the gear flange 130 occupies a substantial portion over the front and rear of the reducer, which is disadvantageous in terms of assembling, and has a large load in the radial direction of the planetary gear train. There is a risk of breakage easily.
  • Equation 1 the reduction ratio of the planetary gear train illustrated in FIG. 9 may be derived as shown in Equation 1 below.
  • the planetary gear train 120 is configured differentially to maintain or increase the efficiency of the reducer, but also reduce the overall reducer volume. Therefore, the mountability and space efficiency of the reducer are also increased.
  • the service life of the speed reducer can be considerably extended compared to the prior art, and the industrial drum can be used because the performance requirement of the mixer drum can be satisfied.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Health & Medical Sciences (AREA)
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  • Transportation (AREA)
  • Structural Engineering (AREA)
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Abstract

La présente invention concerne un réducteur de vitesse pour un camion mélangeur pour déposer du béton et, plus particulièrement, un réducteur de vitesse dont le centre aérodynamique, comprenant un tambour mélangeur et une bride de capot supportant le tambour mélangeur, est positionné à l'arrière du réducteur de vitesse, de façon à avoir ainsi une résistance élevée vis-à-vis des vibrations, du poids, de l'impact, de la sortie et d'autres charges.
PCT/KR2017/002384 2016-03-04 2017-03-06 Réducteur de vitesse pour camion mélangeur de béton WO2017150952A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201780000144.9A CN107407375A (zh) 2016-03-04 2017-03-06 混凝土搅拌车的减速器
PH12017501320A PH12017501320A1 (en) 2016-03-04 2017-07-20 Reducer for concrete mixer truck

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR1020160026597A KR20170103547A (ko) 2016-03-04 2016-03-04 콘크리트 믹서 트럭의 감속기
KR10-2016-0026597 2016-03-04
KR1020160165334A KR101756459B1 (ko) 2016-12-06 2016-12-06 콘크리트 믹서 트럭의 감속기
KR10-2016-0165334 2016-12-06

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WO2017150952A1 true WO2017150952A1 (fr) 2017-09-08

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PCT/KR2017/002384 WO2017150952A1 (fr) 2016-03-04 2017-03-06 Réducteur de vitesse pour camion mélangeur de béton

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CN (1) CN107407375A (fr)
PH (1) PH12017501320A1 (fr)
WO (1) WO2017150952A1 (fr)

Cited By (1)

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