WO2006003840A1 - 車両の変速装置 - Google Patents
車両の変速装置 Download PDFInfo
- Publication number
- WO2006003840A1 WO2006003840A1 PCT/JP2005/011581 JP2005011581W WO2006003840A1 WO 2006003840 A1 WO2006003840 A1 WO 2006003840A1 JP 2005011581 W JP2005011581 W JP 2005011581W WO 2006003840 A1 WO2006003840 A1 WO 2006003840A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- transmission shaft
- transmission
- shaft
- rotation
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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- 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
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
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- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- 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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion
Definitions
- the present invention relates to a transmission of a vehicle such as a tractor or a construction vehicle.
- a transmission using a hydraulic clutch has conventionally been used for a powered vehicle such as a tractor!
- a hydraulic clutch is often used for a reverser mechanism that performs forward and reverse operation of the airframe, and a hydraulic clutch is often used for a main transmission.
- large-sized tractors often use hydraulic clutches not only for the main transmission but also for the auxiliary transmission for the purpose of improving operability and reducing shock at the time of clutch connection.
- Patent Document 1 describes that a hydraulic reverser mechanism is provided at the rear of the engine, and a hydraulic main transmission and an auxiliary transmission are provided at the rear of the transmission, capable of four-speed shifting. .
- Patent Document 1 Japanese Patent Application Laid-Open No. 8-338525 (FIG. 1)
- the hydraulic clutch can only be provided with two sets of clutches back to back at the front and rear of the rotating cylindrical drum.
- a separate counter shaft must be provided in addition to the transmission shaft supporting the shaft, and at least two shafts are required.
- forward and reverse clutches should be provided on the front and back of the cylindrical drum, and an idle shaft for reverse rotation must be provided, increasing the number of axial holes in the case and increasing the internal structure. It has the disadvantage that it becomes complicated in itself and the front and back length of the aircraft also becomes long.
- the problem to be solved by the present invention is to provide a transmission that can configure the inside of the transmission case in a compact manner without increasing the overall length of the airframe.
- the present invention takes the following technical measures.
- the invention according to claim 1 is characterized in that the drive shaft (27) and the output side transmission shaft (48) arranged on the same axial center to which the engine power is transmitted, the drive shaft (27) and the transmission shaft (48) And the cylindrical fixed drum (50) fixed to the case (6) and the cylindrical fixed drum (50).
- the planetary gear mechanism (28) comprises a carrier (30) and a planetary gear.
- a transmission in a motor vehicle is configured such that the carrier (30) is fixed by rotation of the outer clutch (B) and the transmission shaft (48) is reversely rotated.
- the rotation of the drive shaft (27) interlocks the planetary gear mechanism (28), and by the connection of the clutch (A) of the two clutches (A, B) arranged inside and outside
- the carrier (30) of the planetary gear mechanism (28) is integrated with the sun gear (34) of the output side transmission shaft (48) to rotate positively relative to the drive shaft (27), and the carrier (30) is engaged by connecting the clutch (B). Reverse rotation by fixing).
- the two clutches (A, B) are disposed radially inward and outward, overlapping axially in the axial direction, so they are not bulky in the axial direction.
- the invention according to claim 2 comprises a transmission shaft (48) and an output shaft (80), which are disposed on the same axial center, to which engine power is transmitted, the transmission shaft (48), and the output shaft ( 80), the cylindrical fixed drum (50) fixed to the case (6), and the transmission shaft in the space inside the cylindrical fixed drum (50).
- the planetary gear mechanism (28a) comprises a carrier (77), a planetary gear (79 ⁇ ) and a sun gear (80a), the carrier (77) and the sun gear (80a) are integrally rotated by connecting the inner clutch (C), and the outer
- the transmission (70) is fixed by connecting the D (D), and the output shaft (80) is shifted at high and low speeds.
- the rotation of the transmission shaft (48) interlocks the planetary gear mechanism (28a), and among the two clutches (C, D) disposed on the inside and outside, the planetary gear is obtained by connecting the clutch (C).
- the carrier (77) of the mechanism (28a) is integrated with the sun gear (80a) of the output shaft (80) to transmit the rotation of the transmission shaft (48) and fix the carrier (77) by connection of the clutch (D). In some cases, shift to high and low.
- the two clutches (C, D) are disposed radially inward and outward, overlapping axially in the axial direction, so they are not bulky in the axial direction.
- the invention according to claim 3 comprises a drive shaft (27) disposed on the same axial center to which engine power is transmitted, a transmission shaft (48) and an output shaft (80), and the drive shaft ( 27) and planetary gear mechanisms (28, 28 a) respectively provided between the transmission shaft (48) and the transmission shaft (48) and the output shaft (80), and fixed to the case (6) and
- a cylindrical fixed drum (50) provided with a partition wall (55) for partitioning the internal space in the front and back, and one of the front and rear spaces of the partition wall (55) in the cylindrical fixed drum (50)
- a part of the first clutch (A) for shifting the rotation of the drive shaft (27) and transmitting it to the transmission shaft (48), and a part of the first clutch (A) in the axial direction of the transmission shaft (48)
- a second clutch (B) is provided on the radially outer side in an overlapping and radial direction to shift the rotation of the drive shaft (27) and transmit it to the transmission shaft (48), and a partition wall (in the cylindrical drum
- the loose gear mechanism is disposed between the drive side shaft and the driven side shaft, and two clutches (A, B) or (C, D) are provided.
- (A) in which the clutch is disposed radially inward.
- the combination of the planetary gear mechanism (28, 28a) with the carrier (30, 77) of the planetary gear mechanism (28, 28a) rotates or fixes the driven side shaft positively or negatively. Since the clutch (B, D) on the side that requires a large braking force when fixing the carrier (30, 77) is selected from reverse rotation to high and low, the power transmission efficiency is good as well. You can not lose engine horsepower.
- the four clutches (A, B, C, D) sandwiching the central partition wall (55) are structured so as to form a cylindrical fixed drum (50) in two pairs in front and rear, Since one set of clutches are stored in radial direction, they are not bulky in the axial direction.
- FIG. 1 is a side view of the tractor 1.
- the tractor 1 includes left and right front wheels 2 and 2 and left and right rear wheels 3 and 3 as traveling devices, and the rotational power of the engine 5 mounted in the bonnet 4 is appropriately decelerated by the transmission in the transmission case 6
- the rotary power is configured to be transmitted to the front wheels 2 and 2 and the rear wheels 3 and 3.
- a forward / reverse switching device 8 for switching the traveling direction of the vehicle, and a main transmission 9 and an auxiliary transmission 86 for changing the vehicle speed.
- the vehicle moves forward or backward by moving the forward / backward switching lever 10 provided below the steering wheel 11 in the forward / backward direction.
- a hydraulic cylinder case 14 is provided at the rear upper portion of the transmission case 6, and lift arms 15, 15 are pivotally mounted on the left and right sides of the hydraulic cylinder case 14 so as to be vertically pivotable.
- Lower lower links 16, 16 are provided at the lower part so that they can rotate up and down.
- Lift rods 17 and 17 are interposed between lift arms 15 and 15 and lower links 16 and 16 and a rotary tiller 18 which is a working machine is connected to the rear of lower links 16 and 16. ing.
- the rotary cultivating device 18 has a rotary cover 22 covering the tilling portion 21 and the upper side of the tilling portion 21 and a rear cover 23 pivotally attached to the rear of the rotary cover 22.
- a flywheel case 26 having a flywheel 25 at the front and a bearing mounting hole at the rear is connected, and at the rear of the case 26 a drive integral with the flywheel 15
- a sun gear 27a provided at the end of the shaft 27, and a transmission case 6 for incorporating a planetary gear mechanism 28 driven by the same gear 27a are connected.
- the planetary gear mechanism 28 has the sun gear 27a, the carrier 30 and a plurality of planetary gears 32 ⁇ and a sun gear 34 on the output side and the like, and the planetary gears 32 ⁇ are fixed to the carrier 30. Each is rotatably supported by a pin 35 ⁇ ⁇ ⁇ .
- One planetary gear 32 includes large and small two-step gears 32a and 32b, and a sun gear 27a of a drive shaft 27 formed at an end of the drive shaft 27 is engaged with a large diameter gear 32a of the planetary gear 32.
- the small diameter gear 32b is in mesh with the gear 39 supported by the pin 37 in the carrier 30, and this gear 39 is in direct mesh with the output side sun gear 34.
- the rotating body 40 is a bowl-shaped rotating body having a boss 40a along the axial longitudinal direction and a cross-sectional shape having a bowl-like shape in the central portion, and the forward side in the traveling direction is open. It is integrally fixed by a bolt not shown. Therefore, when the carrier 30 rotates, the rotating body 40 also rotates together.
- the carrier 30 and the rotating body 40 are integrally supported by two bearings 41 and 42 at the front and back.
- the output side sun gear 34 has a cylindrical portion 34b having a crank-like cross-sectional shape at its rear portion and having a large diameter extending radially outward, and the cylindrical portion 34b has a front and rear direction.
- a slit 34c is provided along this, and this slit 34c has a donut shaped clutch disc 44 ⁇ ⁇ ⁇
- This slit 34c has a donut shaped clutch disc 44 ⁇ ⁇ ⁇
- the piston 46 and the clutch disc 44 constitute a forward clutch of the forward / backward switching device 8 as a first clutch, and the clutch for forward movement is hereinafter referred to as a forward clutch A.
- a reverse clutch B as a second clutch described later is provided on the radially outer side of the forward clutch A.
- the fixed drum 50 accommodating the forward clutch A and the reverse clutch B has a cylindrical shape, and a partition wall 55 is provided at the central portion for partitioning the front and rear space portions.
- the fixed drum 50 has a structure in which a protrusion 50b is provided on an outer peripheral portion thereof, and the protrusion 50b is fixed to an inner wall provided at an appropriate position in the transmission case 6 to support the fixed drum 50. There is.
- the reverse clutch B is composed of a piston 53 and a clutch disc 52.
- an oil passage 57 is formed in the partition wall 55 of the fixed drum 50, and the oil passage 57, a cylinder chamber 47 for forward movement, and a cylinder chamber 58 for reverse movement are respectively connected, and hydraulic oil is It is configured to flow into each cylinder room.
- a counter panel (biasing means) 60 is provided in the radial inner chamber.
- the outer chamber is provided with a cylinder chamber 62 and a piston 63 (actuator).
- the rotating body 65 is a second rotating body corresponding to the rotating body 40 disposed in the front space portion, and a bearing provided on the fixed drum 50 It is rotatably supported by 66. Further, slits 68 along the longitudinal direction are provided on the outer periphery of the rotating body 65, and between the slits 68 and the large diameter portion 48a of the transmission shaft 48 can be moved in the axial longitudinal direction.
- a force of one separator plate 75 is provided between the two clutch disks 70 and 74 so as to separate the two, and the separator plate 75 is configured to be always pressed forward by the counter panel 60. I see! The counter plate 60 causes the separator plate 75 to push the piston 63 back to the inactive side.
- the separator plate 75 is provided between the clutch disc 70 and the clutch disc 74 so as to be movable in the front-rear direction. Under normal conditions, the radially inner clutch discs 70 are crimped together to form the outer side. There is a gap between the clutch disc 74 and the clutch disc 74. On the other hand, when hydraulic fluid is introduced into the cylinder chamber 62 and the piston 63 is moved rearward, the radially outer clutch disks 74 are crimped, but there is a gap between the radially inner clutch disks 70. It is composed of
- the radially inner disc panel 60 and the clutch disc 70 are referred to as a low speed clutch C as a third clutch, and the piston 63 and the clutch disc 74 of the inner clutch C are It is called a high-speed clutch D as a clutch, and the whole is called a first high-low switching clutch (C, D).
- the carrier 77 is fixed in a manner similar to that of the planetary gear mechanism 28a, and more specifically, in the same manner as the front carrier 30.
- the planetary gear 79 is rotatably supported.
- the planetary gear 79 comprises a large diameter gear 79a and a small diameter gear 79b, and the large diameter gear 79a meshes with the sun gear 82 on the transmission shaft 48 side, and the small diameter gear 79b is a sun gear 80a on the output shaft 80 side. I am in love with you.
- forward clutch A first clutch
- reverse clutch B second clutch
- a low speed clutch C third clutch
- a high speed clutch D fourth clutch
- the forward clutch A first clutch
- the reverse clutch B second clutch
- the low speed clutch C third clutch
- the high speed clutch D fourth clutch
- the forward clutch A (first clutch) and the reverse clutch B (second clutch) overlap in the front-rear direction, and the low-speed clutch C (third clutch) and the high-speed clutch D (fourth clutch) also partially in the front-rear direction Since they are configured to overlap, it is possible to greatly shorten the longitudinal length of the transmission while having four clutches A, B, C, and D.
- forward clutch A is provided radially inward on the front side of the partition wall of fixed drum 50
- reverse clutch B is provided on the outer side thereof
- carrier 30 and sun gear 34 are integrated and directly transmitted. Since the transmission side is the gear transmission through the planetary gear 32, the power transmission efficiency on the forward side, which is frequently used, is good and the loss of horsepower and the like is reduced.
- a second main transmission 9b and a third main transmission 9c are provided behind the first main transmission 9a to shift the rotational force extracted from the output shaft 80 into four more stages. It is More specifically, a rear shift unit 84 capable of four-speed shifting is provided to the front shift unit 83 accommodating the forward / reverse switching device 8 and the first main transmission 9a, and this shift unit The second main transmission 9b and the third main transmission 9c are constructed by taking out only the portion of the first main transmission 9a out of the transmission unit 83 on the front side and providing them symmetrically in the front-rear direction. ing.
- the second high-low switching clutch (E, F) corresponding to the first high-low switching clutch (C, D) in the front shift unit 83 performs two-speed shifting, and the second shift unit 84 on the rear side Three more gear shifts are performed by the three high / low switching clutches (G, H), and the total number of travel gear stages can be eight.
- a partition wall 255 is provided at the front and rear center of the fixed drum 250 and the front side with the partition wall 255 in between.
- the high speed clutch E and the low speed clutch F of the second main transmission 9b are accommodated in the space of the second main transmission 9b, and the high speed clutch G and the low speed clutch H of the third main transmission 9c are accommodated in the rear space.
- the high speed clutch E of the second main transmission 9b is composed of a flat panel 260 and a clutch disc 270
- the low speed clutch F is composed of a piston 263 and a clutch disc 274.
- This low speed clutch F has a radius relative to the high speed clutch E
- the clutches E and F are provided on the outer side in the direction, and are provided so as to partially overlap in the front and rear directions.
- the high speed clutch G and the low speed clutch H of the third main transmission 9c are accommodated behind the partition wall 255, and the third clutch G is composed of a counter panel 261 and a clutch disc 271.
- the low speed clutch H Is composed of a piston 264 and a clutch disc 262.
- the low speed clutch H is provided radially outward with respect to the high speed clutch G, and is disposed such that a part of the clutches overlap in the front-rear direction.
- the front rotary member 300 is rotatably supported on the fixed drum 250 by the bearing 302.
- the front rotary member 300 is engaged with the two sets of clutch disks 270, 274 of the second main transmission 9b so as to be movable in the front-rear direction.
- the front end of the rotating body 300 is integrally formed with the carrier 306 supporting the planetary gear 304.
- the planetary gear 306 is formed of a two-step gear, and the large diameter gear 304a is engaged with the sun gear 310 at the rear end of the output shaft 80, and the small diameter gear 304b is engaged with the sun gear 316 splined to the second transmission shaft 320.
- the counter plate 260 always presses the separator plate 275 to the rear side, so that the high-speed clutch E is engaged. keep. That is, the sun gear 316 and the carrier 306 rotate together at high speed.
- the gear ratio is set such that the rotational speed at which the reduction ratio is larger is slightly slower than when the high speed clutch E is connected.
- the radially outer clutch disks 262 are pressure-bonded to each other, and the low speed clutch H is engaged.
- the rotational speed of the third output shaft 350 changes depending on whether the high speed clutch G is in the engaged state or the low speed clutch H is in the engaged state. That is, when the high speed clutch G is engaged, the sun gear 330 and the carrier 32 8 at the rear end of the second transmission shaft 320 rotate together, and when the low speed clutch H is engaged, the rotating body 324 and the carrier 32 8 are stopped.
- the rotation of the second transmission shaft 320 is transmitted to the third output shaft 350 through the sun gear 330 and the planetary gear 332 sequentially at relatively low speed.
- the reduction ratio of the power by the first high-low switching clutch (C, D) set most on the power side (rotation of the output shaft relative to the input shaft)
- the speed reduction ratio of the second high / low switching clutch (E, F) and the third high / low switching clutch (G, H) is set to 1 or less, ie, deceleration. (See Figure 7)
- the first speed which is the lowest speed position in the main shift, is that the piston 63 of the first high / low switching clutch is not operating, ie, the controller (control means) 7 is “off”.
- the piston 263 of the second high-low switching clutch (E, F) is activated, that is, the energization by the controller 7 is "ON (ON)”
- the piston 264 of the third high-low switching clutch (G, H) is activated, that is, the controller 7 It becomes a combination of "on (ON)".
- the piston 63 of the first high / low switching clutch (C, D) operates, that is, power on by controller 7 ⁇ (ON)
- the piston 263 of the switching clutch, F) is not operated, ie, the energization by the controller 7 is “OFF”, and the piston 263 is not operated of the third height switching clutch (G, H), ie, the electricity of the controller 7 is switched. It is a combination of "off" yarns.
- the third high-low switching clutch (G, H) is the low-speed clutch (H) is "on (ON)” Therefore, the first high-low switching clutch (C, D) selects the high-speed clutch (C) that is “on”, and the second high-low switching clutch (E, F) is "on (ON)” Because the low speed clutch (F) is selected, it is not possible to select any speed other than the 2nd speed.
- the third high-low switching clutch (G, H) is set to “OFF (off)” of the high speed clutch (G). Therefore, the first high-low switching clutch (C, D) selects the low-speed clutch (C) that is “OFF” and the second high-low switching clutch (E, F) is "OFF".
- the high speed clutch (E) which is “” is selected and can not be selected except the 7th speed.
- the main transmission 9 of the tractor 1 As a result, in the main transmission 9 of the tractor 1, a problem occurs in the hydraulic system or the electric system, and even if all the pistons of the three high / low switching clutches are not hydraulically operated, the main transmission 9 is set to the medium speed position, specifically to the 2nd speed, and on the contrary, even if the hydraulic pressure continues to be applied to the pistons of the three high and low switching clutches, it is set to the 7th speed.
- the vehicle can be moved quickly and safely to a repair place or the like.
- the auxiliary transmission 86 is a transmission that transmits the rotation appropriately shifted by the main transmission 9 from the third output shaft 350 to the auxiliary transmission shaft 87 coaxially via each reduction gear or clutch. is there.
- the power for driving the front wheel branched from the drive gear-on shaft 91 is transmitted to the front wheel speed increasing device 97 consisting of a constant speed four wheel clutch 95 and a speed increasing clutch 96, and the constant speed four wheel clutch 95 is engaged.
- the front and rear wheels 2 and 3 are driven with the circumferential speeds of the rear wheel 3 and the front wheel 2 substantially equal, and when the acceleration clutch 96 is connected, the front wheel drive shaft 98 is accelerated and rotated. It is configured to rotate by doubling its circumferential speed than the rear wheel 3.
- reference numeral 99 is a front wheel differential gear
- 100 is a reduction gear mechanism of the front wheel final case portion
- 101 is a front wheel final reduction gear mechanism.
- the rotational power of the engine 5 is transmitted to the PTO clutch 106 through the gear mechanism 104, and the rotational power switched on / off by the clutch 106 is appropriately selected by the PTO transmission device 109 capable of switching between high and low levels. It is configured to be shifted and transmitted to the forward / reverse switching device 108 provided further rearward via the PTO transmission shaft 105. The rotation switched by the forward / reverse switching device 108 is taken out from the PTO shaft 110. Therefore, in this embodiment, two-step rotation can be set for both forward rotation and reverse rotation.
- the hydraulic oil delivered from the hydraulic pump 115 enters the proportional pressure reducing valve 120 and is maintained at a constant pressure, and the forward clutch A and the pistons 46 and 53 of the reverse clutch B and the first main shift are sequentially arranged from the top of the circuit.
- the piston 63 for operating the high-speed clutch D of the device 9a, the piston 263 for operating the low-speed clutch F of the second main transmission device 9b, and the low-speed clutch of the third main transmission 9c Are sent to proportional control valves 121, 122, 123, 124, 125 which respectively control the pistons 264 which operate. In these proportional control valves, the opening amount of the valve is controlled by the energization command from the controller 7.
- the forward clutch A and the reverse clutch B are proportionally controlled in response to a signal from a potentiometer 128 provided on the pivot base of the clutch pedal 129. Therefore, in a conventional tractor or automobile having a mechanical clutch, a half clutch state can be created according to the amount of depression of the clutch pedal 129 and according to the load state of the engine, and the vehicle speed can be obtained steplessly. is there.
- the controller 7 issues commands according to the shift timing, vehicle speed, load condition, etc., and the clutch connection timing is appropriate. It is controlled.
- the maximum depression operation of the clutch pedal 129 gives priority to the detection of the switch 130, it is always detected also by the potentiometer type clutch pedal depression position sensor 128. Then, when only one of them does not detect the maximum depression position, it is determined that the sensor or the switch is broken, and a warning is displayed on the meter panel 131.
- the shift switch provided on the shift lever 13 is first pressed to designate the shift stage, and in this state the forward / backward movement lever 10 is moved forward to gradually move from the clutch pedal 129 that was stepping on. Release your feet.
- it sends from hydraulic pump 115
- the discharged hydraulic pressure oil passes through the proportional pressure reducing valve 120 to reach the proportional control valve 121, and the pressure controlled hydraulic oil flows into the cylinder chamber 47 on the forward side.
- the piston 46 of the forward clutch A moves forward to crimp the clutch disc 44, integrally carry the carrier 30 of the planetary gear mechanism 28 and the sun gear 34, and transmit the rotation in the same direction as the output shaft 27.
- axis 48 is the shift switch provided on the shift lever 13 pressed to designate the shift stage, and in this state the forward / backward movement lever 10 is moved forward to gradually move from the clutch pedal 129 that was stepping on. Release your feet.
- it sends from hydraulic pump 115
- the discharged hydraulic pressure oil passes through the proportional pressure reducing valve 120 to
- the selected clutch in the front gear shift unit 83 or the rear gear shift unit 84 is connected to obtain the desired main gear shift.
- the auxiliary transmission 86 is selected from one of three speeds among "High Speed H”, “Medium Speed M”, and “Low Speed L", and one speed can be selected to drive the machine at the gear speed specified by the operator. .
- the hydraulic oil in the cylinder chamber 47 on the forward clutch side is returned to the tank 6 side, and the hydraulic oil flows into the reverse clutch cylinder chamber 58 provided on the radially outer side thereof.
- the piston 53 moves to the front side, and the clutch discs 52 are crimped to fix the carrier 30 to the fixed drum 50 side.
- the rotation of the output shaft 27 gives a reverse rotation to the transmission shaft 48 through the output gear 27a, the planetary gears 32a and 32b of the planetary gear mechanism 28, the gear 39 and the sun gear 34 sequentially.
- the aircraft starts moving backward at almost the same speed as the forward speed, and makes the aircraft move backward.
- the stepping operation of the clutch pedal 129 is detected by the potentiometer type clutch pedal stepping position sensor 128 and the clutch pedal maximum stepping position detection switch 130.
- the forward clutch A or the reverse clutch B is configured to be in a half clutch state according to the stepping-on position or to be turned off to stop the machine body.
- both the forward clutch A and the reverse clutch B are controlled by the proportional control valves 121 and 122, it is possible to reduce the shock of clutch connection.
- selection of the forward side and the reverse side is performed depending on whether the carrier 30 of the planetary gear mechanism 28 is rotated or fixed. In order to fix the carrier 30, a large force is required.
- the forward clutch A is radially inward, and a large braking force is applied when the carrier 30 is fixed. Since the necessary clutch on the reverse side is provided radially outward, there is no loss of engine horsepower which is higher than the power transmission efficiency at the time of reverse travel during forward travel.
- the clutch B on the reverse side is slightly connected with the clutch A on the forward side connected.
- the rotation of the transmission shaft can be finely controlled, and pressure control of the clutches A and B can be easily performed according to the work load.
- a first main transmission 9a having a high speed clutch C and a low speed clutch D is provided at the rear of the transmission of the forward / reverse switching device 8, and the planetary gear mechanism 28a is linked to this.
- Second and third main transmissions 9b and 9c combining two high and low clutches and planetary gear mechanisms 28b and 28c are also provided at the rear of the transmission, and one gear is selected from the combinations shown in FIG. Although it is configured to select, if configured in this way, power transmission will not be interrupted during shifting.
- the speed at which a person walks corresponds to about 3 to 5 km Zh
- the traveling speed on the road with the tractor or the like corresponds to about 10 to 35 km Zh
- the tractor 1 the main transmission Even if the pistons of all the clutches D, F, and H that force 9 are inactivated, it is set to cover the two-speed shift of the 15th and 23rd speeds.
- the power transmission of one of the three transmissions 9a, 9b, 9c is transmitted to the low speed clutch C by energization when decelerating.
- the others may be configured as non-energized control valves of all the clutches and as medium-speed positions excluding the lowest speed position and the highest speed position when fully energized as accelerations when high speed clutches E and G are activated by energization. .
- clutch discs of a pair of hydraulic clutches inside and outside are selectively turned on / off to cope with each of them.
- the power transmission device of a vehicle comprising: control means (7) for switching the changing position of the vehicle by press-fitting operation of each clutch disc according to an energization command, the speed changing device (9a , 9b, 9c) at two places of the clutch disc, biasing means (60, 260, 261) for always biasing one disc to the on state, and the energization command by the control means (7)
- the first clutch disc is disengaged against the biasing force of the biasing means (60, 260, 261).
- an actuator (63, 263, 264) for receiving the other clutch disc, and the power transmission ratio of the plurality of planetary gear mechanisms (28a, 28b, 28c) can be determined by the actuator (63, 263, 264). When all of them are in the non-operation state and when they are all in the middle position except the lowest position and the highest position obtained by the plurality of transmissions (9a, 9b, 9c) Thus, the transmission of one transmission (9a) of the plurality of transmissions (9a, 9b, 9c) is set to increase or decrease the power transmission ratio of the transmission (9a).
- an oil passage 57 is provided in the central partition wall 55 of the fixed drum 50, and one pair of clutches are provided on the front and rear sides of the partition wall 55 to constitute a transmission unit. Therefore, the structure can be simplified, the oil passage can be easily formed, and the handling becomes easy.
- one transmission shaft 48 is incorporated with one front and rear force of the fixed drum 50, and the planetary gear mechanism 28, 28a is assembled from the front and rear to this transmission shaft 48.
- the planetary gear mechanism 28, 28a is assembled from the front and rear to this transmission shaft 48.
- the present invention is applicable to a vehicle such as a tractor or a construction vehicle provided with a transmission that can compactly construct the inside of a transmission case without increasing the overall length of the airframe.
- FIG. 1 An overall side view of the tractor.
- FIG. 2 Sectional view (1) of the main part of the transmission.
- FIG. 3 A sectional view (2) of the main part of the transmission.
- FIG. 6 A block diagram showing the connection state of the controller.
- FIG. 7 A diagram for explaining the relationship between the number of shift speeds and the operation of the clutch.
- FIG. 8 A diagram for explaining the relationship between the number of shift speeds of another form and the operation of a clutch.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
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- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2004-192623 | 2004-06-30 | ||
JP2004192623A JP2006017142A (ja) | 2004-06-30 | 2004-06-30 | 動力車両の変速装置 |
JP2005-129958 | 2005-04-27 | ||
JP2005129958A JP2006307940A (ja) | 2005-04-27 | 2005-04-27 | 車両の変速装置 |
Publications (1)
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WO2006003840A1 true WO2006003840A1 (ja) | 2006-01-12 |
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PCT/JP2005/011581 WO2006003840A1 (ja) | 2004-06-30 | 2005-06-24 | 車両の変速装置 |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006307999A (ja) * | 2005-04-28 | 2006-11-09 | Iseki & Co Ltd | 車両の変速制御装置 |
CN108204451A (zh) * | 2018-01-17 | 2018-06-26 | 济南大学 | 一种软轴式三档变速箱和离合器的液压控制***和控制方法及操作方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH02102044U (ja) * | 1989-01-31 | 1990-08-14 | ||
JPH0796894A (ja) * | 1993-09-28 | 1995-04-11 | Kanzaki Kokyukoki Mfg Co Ltd | 舶用機関の可逆転油圧式クラッチ機構 |
JPH07224864A (ja) * | 1994-02-10 | 1995-08-22 | Kubota Corp | 油圧クラッチの作動方法及びその装置 |
-
2005
- 2005-06-24 WO PCT/JP2005/011581 patent/WO2006003840A1/ja active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH02102044U (ja) * | 1989-01-31 | 1990-08-14 | ||
JPH0796894A (ja) * | 1993-09-28 | 1995-04-11 | Kanzaki Kokyukoki Mfg Co Ltd | 舶用機関の可逆転油圧式クラッチ機構 |
JPH07224864A (ja) * | 1994-02-10 | 1995-08-22 | Kubota Corp | 油圧クラッチの作動方法及びその装置 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006307999A (ja) * | 2005-04-28 | 2006-11-09 | Iseki & Co Ltd | 車両の変速制御装置 |
CN108204451A (zh) * | 2018-01-17 | 2018-06-26 | 济南大学 | 一种软轴式三档变速箱和离合器的液压控制***和控制方法及操作方法 |
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