WO2012105383A1 - 車両用動力伝達装置 - Google Patents
車両用動力伝達装置 Download PDFInfo
- Publication number
- WO2012105383A1 WO2012105383A1 PCT/JP2012/051535 JP2012051535W WO2012105383A1 WO 2012105383 A1 WO2012105383 A1 WO 2012105383A1 JP 2012051535 W JP2012051535 W JP 2012051535W WO 2012105383 A1 WO2012105383 A1 WO 2012105383A1
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- WO
- WIPO (PCT)
- Prior art keywords
- brake
- shaft
- casing
- vehicle
- 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
- 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
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
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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
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
- F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
- F16D55/36—Brakes with a plurality of rotating discs all lying side by side
- F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
-
- 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
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0936—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only two idle gears and one gear fixed to the countershaft
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19233—Plurality of counter shafts
Definitions
- the present invention relates to a vehicle power transmission device that is mounted on a work vehicle such as a wheel loader or a wheeled excavator and transmits the rotation of a prime mover to an output shaft for traveling.
- a wheel-type work vehicle such as a wheel loader or a wheel-type excavator typically travels on a general road toward a work site by rotationally driving wheels.
- the wheel-type work vehicle drives a hydraulic motor by an engine and transmits the rotation of the hydraulic motor to the wheel, and transmits the rotation of the engine to the wheel via a torque converter and a power transmission mechanism.
- a work vehicle that transmits the rotation of the engine to the wheels via the torque converter is usually provided with a vehicle power transmission device including a speed change mechanism between the torque converter and the axle, and the vehicle power transmission device.
- a vehicle power transmission device including a speed change mechanism between the torque converter and the axle, and the vehicle power transmission device.
- a vehicle power transmission device includes a casing mounted on a vehicle, a rotation shaft that is rotatably supported in the casing and rotated by a prime mover, and a rotation shaft that is rotatably supported in parallel in the casing.
- a plurality of transmission shafts that change the rotational speed to different rotational speeds, and the rotation shaft and any one of the transmission shafts provided between the rotation shaft and each of the transmission shafts.
- a clutch mechanism to be connected and an output shaft that is always connected to the respective transmission shafts via gears and outputs the rotation of one transmission shaft selected by the clutch mechanism to the wheels of the vehicle body.
- the vehicle power transmission device includes a negative brake device (parking brake) for applying a braking force in a state where the work vehicle is parked.
- This brake device is usually provided between any one of the plurality of transmission shafts always connected to the output shaft via a gear and the casing (see Patent Document 1). .
- the brake device of the vehicle power transmission device is normally configured by alternately overlapping a plurality of fixed brake plates and a plurality of rotation brake plates in the axial direction.
- Each fixed brake plate can be moved in the axial direction by being splined to the casing side and fixed in the rotational direction, and each rotary side brake plate can be splined to the transmission shaft side to It can move in the direction and rotates integrally with the transmission shaft.
- the brake device uses a spring force to bring the fixed side brake plate and the rotary side brake plate into contact with each other so that the friction between the two can be reduced.
- a braking force is applied to the transmission shaft by force.
- the braking force acting on the transmission shaft is released by separating the stationary brake plate and the rotating brake plate against the spring force by the brake release pressure. .
- the brake device of the vehicle power transmission device functions not only as a parking brake at the time of parking, but also as an emergency brake that applies a braking force to a working vehicle that is traveling in an emergency, for example.
- one brake device is provided between one transmission shaft and the casing among the plurality of transmission shafts always connected to the output shaft. For this reason, there is a problem that it is difficult to generate a sufficient braking force in an emergency by one brake device.
- the present invention has been made in view of the above-described problems of the prior art, and can provide a large braking force to the output shaft, and can suppress generation of heat during traveling of the vehicle.
- the purpose is to provide a power transmission device.
- the present invention provides a casing mounted on a vehicle, a rotating shaft that is rotatably supported in the casing and rotated by a motor mounted on the vehicle, and is arranged in parallel in the casing. And a plurality of transmission shafts that are rotatably supported by the rotation shaft to change the rotation of the rotation shafts to different rotational speeds, and any one of the transmission shafts provided between the rotation shafts and the transmission shafts.
- a clutch mechanism that selectively connects the transmission shaft and the rotation shaft, and a rotation of one transmission shaft that is always connected to each transmission shaft via a gear and selected by the clutch mechanism is output to the wheels of the vehicle.
- the present invention is applied to a vehicle power transmission device including an output shaft.
- a feature of the present invention is that the casing is provided with a plurality of brake devices for applying braking force to the respective transmission shafts.
- the braking force applied to the output shaft can be increased by providing a brake device for each of the plurality of transmission shafts. Therefore, it is not necessary to increase the number of fixed brake plates and rotating brake plates constituting each brake device, and a sufficient gap can be secured between each fixed brake plate and each rotating brake plate. .
- the rotation-side brake plate can be prevented from contacting the fixed-side brake plate when the vehicle is running, the heat generated by the brake device can be suppressed, and each rotation-side brake plate can be smoothly rotated. it can. Therefore, energy loss transmitted to the output shaft can be suppressed, and the rotational output of the prime mover can be efficiently transmitted to the wheels.
- each transmission shaft by suppressing the number of rotation-side brake plates attached to each transmission shaft, the axial dimension of each transmission shaft is shortened compared to, for example, a case where a large number of rotation-side brake plates are attached to one transmission shaft. Therefore, the entire power transmission device can be configured compactly.
- the plurality of brake devices are arranged so as to be shifted to one side in the axial direction with respect to the plurality of transmission shafts.
- the brake devices can be collectively arranged on the same side in the axial direction of each transmission shaft. Therefore, when connecting a hydraulic hose for supplying pressure oil for operation to each brake device, these hydraulic hoses can be set to substantially the same length. As a result, the pressure oil for operation can be supplied to each brake device almost simultaneously, and the operation timing of each brake device can be matched.
- the casing is configured such that any one of the transmission shafts and the other transmission shaft are disposed on both sides of the output shaft. According to this configuration, the braking force can be simultaneously applied to one transmission shaft and the other transmission shaft arranged with the output shaft interposed therebetween using the brake device.
- the casing is formed by a front casing, an intermediate casing located on the rear side of the front casing, and a rear casing located on the rear side of the intermediate casing, and the rotating shaft is formed on the intermediate casing.
- the transmission shaft is supported by the rear casing, and the transmission shafts are positioned below the rotary shaft and are supported by the intermediate casing and the rear casing so as to be opposed to each other in the left and right directions.
- the brake devices are provided on the front surface of the front casing and positioned on the front end side of the transmission shafts. .
- the vehicle power transmission device including each brake device is efficiently cooled. be able to.
- each of the brake devices is configured as a negative brake that releases the brake when pressure oil is supplied to the oil chamber, and the hydraulic pump and each of the brake devices are connected via an oil passage.
- a brake release position where pressure oil is supplied from the hydraulic pump to the oil chamber of each brake device to release the braking force, and the oil chamber of each brake device is connected to the tank and the braking force is connected.
- a brake control valve having a braking position for applying a braking force, and each brake device simultaneously applies a braking force to each of the transmission shafts by the brake control valve or simultaneously applies a braking force to each of the transmission shafts. It is set as the structure which cancels
- a braking force can be simultaneously applied to each transmission shaft from each brake device, and a large braking force obtained by adding the braking forces of these brake devices can be obtained. Can be given to the output shaft.
- the brake control valve is switched to the brake release position, the braking force acting on each transmission shaft from each brake device can be released at the same time, and the output shaft can be smoothly rotated.
- the vehicle includes a front vehicle body provided with a front wheel, a rear vehicle body provided with a rear wheel, and the front vehicle body and the rear vehicle body provided between the front vehicle body and the rear vehicle body.
- a connecting mechanism that is connected to bendable in the left and right directions, the prime mover is mounted on one of the front vehicle body and the rear vehicle body, and the casing includes the connection mechanism and the prime mover.
- the brake device is provided in the one vehicle body so as to face the coupling mechanism and disposed on one side in the axial direction of each transmission shaft.
- FIG. 4 is a right side view of the vehicle power transmission device as seen from the direction of arrows IV-IV in FIG. 3.
- FIG. 5 is a longitudinal sectional view of the vehicle power transmission device as seen from the direction of arrows VV indicated by a one-dot chain line in FIG. 4.
- FIG. 4 is a right side view of the vehicle power transmission device as seen from the direction of arrows VV indicated by a one-dot chain line in FIG. 4.
- FIG. 5 is an enlarged cross-sectional view of the main part of the first and second transmission shafts, the output shaft, the first and second brake devices, etc., as viewed from the direction of arrows VI-VI indicated by the two-dot chain line in FIG. 4.
- FIG. 2 is a hydraulic circuit diagram including first and second brake devices.
- reference numeral 1 denotes a wheel loader as a typical example of a wheel type work vehicle.
- a front vehicle body 3 provided with left and right front wheels 2 and a rear vehicle body 5 provided with left and right rear wheels 4 are connected in a left and right direction via a coupling mechanism 6. It is connected so that it can be bent.
- the wheel loader 1 is configured as an articulated work vehicle that performs steering by bending the front vehicle body 3 and the rear vehicle body 5 in the left and right directions.
- the connecting mechanism 6 includes rear and upper front brackets 6A that protrude rearward from the rear end side of the front vehicle body 3, upper and lower rear brackets 6B that protrude forward from the front end side of the rear vehicle body 5, and the vertical direction. And a connecting pin 6C that rotatably connects the front bracket 6A and the rear bracket 6B.
- a steering cylinder 7 is provided between the front vehicle body 3 and the rear vehicle body 5. The wheel loader 1 expands and contracts the steering cylinder 7 so that the front vehicle body 3 and the rear vehicle body 5 bend in the left and right directions around the connection pin 6C of the connection mechanism 6 to perform steering during traveling. (See FIG. 2).
- the front body 3 of the wheel loader 1 is provided with a working device 8 provided with a loader bucket 8A so as to be able to move up and down.
- the rear body 5 of the wheel loader 1 is provided with a cab 9 that defines a cab, an engine 10 as a prime mover, a vehicle power transmission device 21 described later, and the like.
- a front axle (front axle) 11 extending in the left and right directions is provided below the front body 3, and left and right front wheels 2 are attached to both ends of the front axle 11.
- a rear axle (rear axle) 12 extending in the left and right directions is provided below the rear vehicle body 5, and left and right rear wheels 4 are attached to both ends of the rear axle 12.
- the front axle 11 is connected to the output shaft 54 of the vehicle power transmission device 21 via the propeller shaft 13
- the rear axle 12 is connected to the output shaft 54 of the vehicle power transmission device 21 via the propeller shaft 14.
- the vehicle power transmission device 21 indicates a vehicle power transmission device mounted on the wheel loader 1. As shown in FIGS. 1 and 2, the vehicle power transmission device 21 is connected to the engine 10 and decelerates the rotational output of the engine 10 to transmit it to the front axle 11 and the rear axle 12.
- the vehicle power transmission device 21 includes a casing 22, a torque converter 23, a forward shaft 27, a reverse shaft 34, a rotational shaft 35, first and second transmission shafts 40 and 41, and a first-speed clutch mechanism 50, which will be described later.
- the second-speed clutch mechanism 51, the output shaft 54, the first and second brake devices 61 and 71, and the like are configured.
- Reference numeral 22 denotes a casing that forms an outer shell of the vehicle power transmission device 21, and the casing 22 includes a torque converter 23, a forward shaft 27, a reverse shaft 34, a rotary shaft 35, first and second transmission shafts 40, 41, a first-speed clutch mechanism 50, a second-speed clutch mechanism 51, and an output shaft 54 are accommodated.
- the casing 22 is formed in a hollow box shape including a front casing 22A positioned on the front side in the front and rear directions, an intermediate casing 22B positioned on the intermediate portion, and a rear casing 22C positioned on the rear side.
- the casing 22 is disposed so that the rear casing 22C faces the engine 10.
- the torque converter 23 is disposed on the upper end side of the casing 22, and the torque converter 23 is connected to a crankshaft (not shown) of the engine 10 and transmits the rotational output of the engine 10 to the drive shaft 23A via oil.
- the drive shaft 23 ⁇ / b> A of the torque converter 23 is supported by the rear casing 22 ⁇ / b> C via the bearing 24 and is supported by the intermediate casing 22 ⁇ / b> B via the bearing 25.
- a drive gear 26 is attached to one end side (front side) of the drive shaft 23A located in the intermediate casing 22B in the vicinity of the bearing 25.
- the forward shaft 27 is disposed below the torque converter 23, and the forward shaft 27 is connected to a drive shaft 23A of the torque converter 23 via a forward clutch mechanism 33 described later when the wheel loader 1 travels forward. Is.
- one end side (front side) in the axial direction of the forward shaft 27 is supported by the intermediate casing 22B via the bearing 28, and the other end side (rear side) in the axial direction is supported by the rear casing 22C via the bearing 29.
- the input gear 30 is provided at an intermediate portion in the axial direction of the forward shaft 27, and the input gear 30 is always meshed with the drive gear 26.
- a needle bearing 31 is provided between the input gear 30 and the forward shaft 27, and the input gear 30 is rotatable with respect to the forward shaft 27.
- a forward clutch mechanism 33 which will be described later, is provided between the forward shaft 27 and the input gear 30, and the forward clutch mechanism 33 switches the forward shaft 27 and the input gear 30 to a connected state or an open state (disengaged state). be able to.
- an output gear 32 is splined to the other end side of the forward shaft 27 in the axial direction, and the output gear 32 always rotates integrally with the forward shaft 27.
- the hydraulic forward clutch mechanism 33 is provided between the forward shaft 27 and the input gear 30, and the forward clutch mechanism 33 is operated when the wheel loader 1 travels forward. That is, when the wheel loader 1 travels forward, the forward clutch mechanism 33 is brought into a connected state, whereby the forward shaft 27 and the input gear 30 are brought into a connected state and integrated. Thereby, the rotation of the drive gear 26 is transmitted to the rotation shaft 35 described later via the input gear 30, the forward shaft 27, and the output gear 32. On the other hand, when the wheel loader 1 travels backward, the forward clutch mechanism 33 is opened, whereby the forward shaft 27 and the input gear 30 are separated from each other, and the power transmission to the forward shaft 27 is cut off.
- a reverse shaft 34 is disposed on the opposite side of the forward shaft 27 across the drive shaft 23A of the torque converter 23.
- the reverse shaft 34 is connected to the drive shaft 23A when the wheel loader 1 travels backward.
- the reverse shaft 34 is also provided with the same input gear, output gear, and reverse clutch mechanism (not shown) as the forward shaft 27. Accordingly, by connecting the reverse clutch mechanism with the forward clutch mechanism 33 disconnected, the rotation of the drive gear 26 is transmitted to the rotation shaft 35 described later via the reverse shaft 34 and the like.
- the rotary shaft 35 indicates a rotating shaft disposed below the forward shaft 27 and the reverse shaft 34.
- the rotary shaft 35 is used to transmit the rotational output of the engine 10 via the torque converter 23, the forward shaft 27, the reverse shaft 34, and the like.
- one end side of the rotating shaft 35 in the axial direction is supported by the intermediate casing 22B via the bearing 36, and the other end side of the rotating shaft 35 in the axial direction is supported by the rear casing 22C via the bearing 37. Yes.
- An output gear 38 is formed integrally with one end side in the axial direction of the rotary shaft 35 so as to be located in the vicinity of the bearing 36.
- the output gear 38 is always meshed with a first-speed input gear 44 of the first transmission shaft 40 described later.
- An input / output gear 39 is splined to the other end side in the axial direction of the rotary shaft 35 in the vicinity of the bearing 37, and the input / output gear 39 is a gear having a diameter larger than that of the output gear 38. .
- the input / output gear 39 always meshes with an output gear 32 provided on the forward shaft 27 and an output gear (not shown) provided on the reverse shaft 34, and for the second speed of the first transmission shaft 40 described later. It is always meshed with the input gear 46.
- 40 indicates a first transmission shaft disposed below the rotation shaft 35
- 41 indicates a second transmission shaft similarly disposed below the rotation shaft 35.
- These transmission shafts 40 and 41 are arranged side by side on both the left and right sides with the rotation shaft 35 and an output shaft 54 described later interposed therebetween.
- the first speed change shaft 40 changes the rotation of the rotary shaft 35 to either the first speed rotation having the smallest rotation speed range or the second speed rotation having a larger rotation speed range than the first speed rotation. Is transmitted to the output shaft 54.
- the second transmission shaft 41 rotates the rotation shaft 35 in either the third speed rotation having a larger rotation speed range than the above-described second speed rotation or the fourth speed rotation having a larger rotation speed range than the third speed rotation. And is transmitted to the output shaft 54.
- first transmission shaft 40 and the second transmission shaft 41 are configured in substantially the same manner, the configuration of the first transmission shaft 40 will be described in detail below. The description of the configuration is omitted.
- the first transmission shaft 40 is supported at one end side in the axial direction by the intermediate casing 22B via the bearing 42, and supported at the other end side in the axial direction by the rear casing 22C via the bearing 43.
- One end portion (front end portion) of the first transmission shaft 40 in the axial direction protrudes through the bearing 42 into the front casing 22A.
- the first speed input gear 44 is provided on one side in the axial direction of the first transmission shaft 40 adjacent to the bearing 42, and the first speed input gear 44 is always meshed with the output gear 38 of the rotary shaft 35. Yes.
- a needle bearing 45 is provided between the first speed input gear 44 and the first transmission shaft 40, and the first speed input gear 44 is rotatable with respect to the first transmission shaft 40.
- a first-speed clutch mechanism 50 which will be described later, is provided between the first transmission shaft 40 and the first-speed input gear 44. The first-speed clutch mechanism 50 allows the first transmission shaft 40 and the first-speed input gear 44 to be used. The connection state with the input gear 44 and the open state (disengaged state) can be switched.
- the second-speed input gear 46 is provided on the other side in the axial direction of the first transmission shaft 40 adjacent to the bearing 43, and the second-speed input gear 46 is a gear having a smaller diameter than the first-speed input gear 44. Therefore, it is always meshed with an input / output gear 39 attached to the rotary shaft 35.
- a needle bearing 47 is provided between the second-speed input gear 46 and the first transmission shaft 40, and the second-speed input gear 46 is rotatable with respect to the first transmission shaft 40.
- a second-speed clutch mechanism 51 which will be described later, is provided between the first transmission shaft 40 and the second-speed input gear 46, and the first-speed transmission shaft 40 and the second-speed clutch mechanism 51 are provided by the second-speed clutch mechanism 51. The connection state with the input gear 46 and the open state (disengaged state) can be switched.
- the output gear 48 is spline-coupled to one end portion (front end portion) of the first transmission shaft 40 in the axial direction.
- the output gear 48 is disposed in the front casing 22A, and a low-speed side input gear 57 of the output shaft 54 described later.
- the output gear 48 is provided with a cylindrical portion 48 ⁇ / b> A that protrudes on the opposite side to the first transmission shaft 40.
- the cylindrical portion 48A is concentric with the first transmission shaft 40 and is supported by the front casing 22A via a bearing 49.
- One end side of the cylindrical portion 48A in the axial direction protrudes outside the front casing 22A through the bearing 49 and extends into a first brake device 61 described later.
- 50 indicates a hydraulic first-speed clutch mechanism provided between the first transmission shaft 40 and the first-speed input gear 44.
- the first speed clutch mechanism 50 is operated when an output shaft 54 described later is rotated at the first speed. That is, when the first speed clutch mechanism 50 is connected, the first transmission shaft 40 and the first speed input gear 44 are connected and integrated, and when the first speed clutch mechanism 50 is released, The connection between the transmission shaft 40 and the first-speed input gear 44 is disconnected (becomes a disconnected state).
- Reference numeral 51 denotes a hydraulic two-speed clutch mechanism provided between the first transmission shaft 40 and the second-speed input gear 46.
- the second speed clutch mechanism 51 is operated when an output shaft 54 described later is rotated at a second speed. That is, when the second speed clutch mechanism 51 is connected, the first transmission shaft 40 and the second speed input gear 46 are connected and integrated, and when the second speed clutch mechanism 51 is released, The transmission shaft 40 and the second-speed input gear 46 are disconnected (become disconnected).
- the first speed change shaft 40 and the first speed input gear 44 are connected by connecting the first speed clutch mechanism 50.
- the rotation of the rotation shaft 35 is transmitted to the output shaft 54 described later via the output gear 38, the first-speed input gear 44, the first transmission shaft 40, and the output gear 48.
- the first speed change shaft 40 and the second speed input gear 46 are connected by connecting the second speed clutch mechanism 51.
- the rotation of the rotation shaft 35 is transmitted to the output shaft 54 described later via the input / output gear 39, the second speed input gear 46, the first transmission shaft 40, and the output gear 48.
- FIG. 1 When viewing the second transmission shaft 41 disposed on the opposite side of the first transmission shaft 40 across the output shaft 54, one end of the second transmission shaft 41 in the axial direction is shown in FIG. The side protrudes into the front casing 22A.
- An output gear 52 is splined to one end of the second transmission shaft 41.
- the output gear 52 is a gear having a diameter larger than that of the output gear 48 attached to the first transmission shaft 40, and always meshes with a high-speed side input gear 58 of the output shaft 54 described later.
- the output gear 52 is provided with a cylindrical portion 52 ⁇ / b> A that protrudes on the side opposite to the second transmission shaft 41.
- the cylindrical portion 52A is concentric with the second transmission shaft 41 and is supported by the front casing 22A via a bearing 53.
- One end side of the cylindrical portion 52A in the axial direction protrudes outside the front casing 22A through the bearing 53 and extends into a second brake device 71 described later.
- the second speed change shaft 41 and the third speed input gear (not shown) are connected by connecting the third speed clutch mechanism (not shown). State. Thereby, the rotation of the rotary shaft 35 is transmitted to the output shaft 54 described later via the output gear 38, the third speed input gear (not shown), the second transmission shaft 41, and the output gear 52.
- the second speed change shaft 41 and the fourth speed input gear (not shown) are connected by connecting a fourth speed clutch mechanism (not shown). State. Thereby, the rotation of the rotary shaft 35 is transmitted to the output shaft 54 described later via the input / output gear 39, the fourth speed input gear (not shown), the second transmission shaft 41, and the output gear 52.
- the output shaft 54 indicates an output shaft disposed below the first transmission shaft 40 and the second transmission shaft 41.
- the output shaft 54 includes rotation of the first transmission shaft 40 selected by the first speed clutch mechanism 50 or the second speed clutch mechanism 51 (first speed rotation or second speed rotation), third speed clutch mechanism or fourth speed.
- One of the rotations (third speed rotation or fourth speed rotation) of the second transmission shaft 41 selected by the clutch mechanism (not shown) is output.
- one axial end side of the output shaft 54 is supported by the front casing 22A via a bearing 55, and the other axial end side of the output shaft 54 is supported by the intermediate casing 22B via a bearing 56. Yes.
- one end side of the output shaft 54 protrudes to the outside of the front casing 22A through the bearing 55, and a front flange 54A is attached to the protruding end portion of the output shaft 54.
- the propeller shaft 13 is connected to the front flange 54 ⁇ / b> A of the output shaft 54, and the rotational output of the output shaft 54 is transmitted to the front axle 11 of the wheel loader 1 through the propeller shaft 13.
- the other end of the output shaft 54 protrudes to the outside of the intermediate casing 22B through the bearing 56, and a rear flange 54B is attached to the protruding end of the output shaft 54.
- the propeller shaft 14 is connected to the rear flange 54B of the output shaft 54, and the rotational output of the output shaft 54 is transmitted to the rear axle 12 of the wheel loader 1 through the propeller shaft 14.
- the low speed side input gear 57 is splined to an intermediate portion in the axial direction of the output shaft 54, and the low speed side input gear 57 is located in the vicinity of the bearing 55 and disposed in the front casing 22 ⁇ / b> A. Is always meshed with an output gear 48 attached to the. Therefore, when the rotation of the rotation shaft 35 is transmitted to the first transmission shaft 40 via the first-speed clutch mechanism 50 or the second-speed clutch mechanism 51, the rotation of the first transmission shaft 40 (first-speed rotation). Or 2nd speed rotation) is transmitted to the output shaft 54 via the output gear 48 and the low speed side input gear 57. The rotation of the output shaft 54 is transmitted to the front axle 11 of the wheel loader 1 via the front propeller shaft 13 and is transmitted to the rear axle 12 via the rear propeller shaft 14.
- the high speed side input gear 58 is spline coupled to the intermediate portion of the output shaft 54 in the axial direction adjacent to the low speed side input gear 57. As shown in FIG. 6, the high speed side input gear 58 is a gear having a smaller diameter than the low speed side input gear 57, and is always meshed with the output gear 52 attached to the second transmission shaft 41. Accordingly, when the rotation of the rotation shaft 35 is transmitted to the second transmission shaft 41 via the third-speed clutch mechanism or the fourth-speed clutch mechanism (both not shown), the second transmission shaft 41 The rotation (third speed rotation or fourth speed rotation) is transmitted to the output shaft 54 via the output gear 52 and the high speed side input gear 58. The rotation of the output shaft 54 is transmitted to the front axle 11 of the wheel loader 1 via the front propeller shaft 13 and is transmitted to the rear axle 12 via the rear propeller shaft 14.
- the output shaft 54 is always connected to the first transmission shaft 40 via the low speed side input gear 57 and the output gear 48, and is connected to the second speed via the high speed side input gear 58 and the output gear 52.
- the transmission shaft 41 is always connected. For this reason, when the output shaft 54 rotates and the wheel loader 1 is traveling, the first transmission shaft 40 and the second transmission shaft 41 always rotate integrally with the output shaft 54.
- the 61 denotes a first brake device provided in the casing 22, and the first brake device 61 applies a braking force to the first transmission shaft 40.
- the first brake device 61 is arranged to be shifted to one end side (front end side) in the axial direction of the first transmission shaft 40, and the coupling mechanism 6 shown in FIG. 1 among the front casing 22 ⁇ / b> A constituting the casing 22. Is detachably attached to the front surface 22A1 facing the surface.
- the first brake device 61 is composed of, for example, a wet multi-plate type negative brake. When the wheel loader 1 is parked or when the traveling wheel loader 1 is to be stopped in an emergency, the first brake device 61 is connected to the first transmission shaft 40. Apply braking force.
- the first brake device 61 releases the braking force applied to the first transmission shaft 40 when the wheel loader 1 travels.
- the first brake device 61 includes a brake case 62, an adapter 63, each fixed brake plate 64, each rotation side brake plate 65, a brake piston 66, which will be described later, A spring member 68 and an oil chamber 69 are included.
- the brake case 62 is an outer shell of the first brake device 61, and the brake case 62 is detachably attached to the front surface 22A1 of the front casing 22A.
- the brake case 62 includes a cylindrical main body portion 62A that surrounds the cylindrical portion 48A of the output gear 48 from the outer peripheral side, a lid portion 62B that covers the opening side of the main body portion 62A, a main body portion 62A and a lid. It is comprised by the intermediate
- the intermediate cylinder portion 62C is provided with an inward flange portion 62D projecting radially inward in the radial direction and a brake release pressure inlet 62E.
- the fixed brake plates 64 and the rotary brake plates 65 are accommodated on the inner peripheral side of the main body 62A, and the brake piston 66 is slidably inserted on the inner peripheral side of the intermediate cylinder 62C. It is fitted.
- the brake case 22 is attached to the front surface 22A1 of the front casing 22A by a plurality of bolts 62F.
- the cylindrical adapter 63 is attached to the outer peripheral side of the cylindrical portion 48A of the output gear 48.
- the adapter 63 is spline-coupled to the outer peripheral side of the cylindrical portion 48 ⁇ / b> A and rotates integrally with the first transmission shaft 40.
- Each rotation-side brake plate 65 to be described later is splined to the outer peripheral side of the adapter 63.
- the plurality of fixed-side brake plates 64 are disposed on the inner peripheral side of the brake case 62, and each fixed-side brake plate 64 is formed as an annular plate using, for example, a metal material.
- Each fixed-side brake plate 64 is spline-coupled to the inner peripheral surface of the main body portion 62A constituting the brake case 62 in a state where the fixed-side brake plate 64 and the rotation-side brake plate 65, which will be described later, alternately overlap in the axial direction. Accordingly, each fixed-side brake plate 64 is movable in the axial direction with respect to the brake case 62 and is not rotated in the circumferential direction with respect to the brake case 62.
- the plurality of rotation-side brake plates 65 are arranged on the inner peripheral side of the brake case 62 together with each fixed-side brake plate 64, and the rotation-side brake plates 65 are formed as an annular plate using, for example, a metal material. Yes.
- Each rotation-side brake plate 65 is splined to the outer peripheral side of the adapter 63 so as to overlap with each fixed-side brake plate 64 alternately in the axial direction. Accordingly, each rotation-side brake plate 65 is movable in the axial direction with respect to the adapter 63 and is not rotated in the circumferential direction with respect to the adapter 63.
- the brake piston 66 is inserted into the inner peripheral side of the intermediate cylinder portion 62 ⁇ / b> C constituting the brake case 62, and the brake piston 66 frictionally engages by pressing the fixed brake plates 64 and the rotary brake plates 65. As a result, a braking force is applied to the first transmission shaft 40 via the adapter 63 and the output gear 48.
- the brake piston 66 has a large-diameter portion 66A that is in sliding contact with the inner peripheral surface of the intermediate cylindrical portion 62C, and a small-diameter portion 66B that is in sliding contact with the inner peripheral surface of the inward flange portion 62D provided in the intermediate cylindrical portion 62C. It is formed in a stepped cylindrical shape.
- the backup ring 67 is formed as a hollow disk-like body, and the backup ring 67 is provided between the front surface 22A1 of the front casing 22A and the brake piston 66 in the brake case 62.
- the backup ring 67 regulates the axial movement of the stationary brake plate 64 and the rotating brake plate 65 pressed by a spring member 68 described later.
- the plurality of spring members 68 are provided between the brake case 62 and the brake piston 66.
- Each spring member 68 is formed of a compression coil spring, and the lid portion 62B of the brake case 62 and the large-diameter portion 66A of the brake piston 66. It is disguised between.
- Each spring member 68 constantly urges the brake piston 66 in a direction in which the fixed brake plate 64 and the rotation brake plate 65 are pressed. As a result, the brake plates 64 and 65 are sandwiched between the brake piston 66 and the backup ring 67 and apply braking force to the first transmission shaft 40.
- the oil chamber 69 for releasing the brake is provided between the intermediate cylinder portion 62C of the brake case 62 and the brake piston 66.
- the oil chamber 69 has a large diameter between the inward flange portion 62D of the intermediate cylinder portion 62C and the brake piston 66.
- An annular shape is formed around the entire circumference between the portion 66A.
- the oil chamber 69 communicates with a brake release pressure inlet 62E provided in the intermediate cylinder portion 62C.
- the second brake device 71 indicates a second brake device provided between the casing 22 and the second transmission shaft 41, and the second brake device 71 applies a braking force to the second transmission shaft 41.
- the second brake device 71 is arranged so as to be shifted to one end side (front end side) in the axial direction of the second transmission shaft 41 and is detachably attached to the front surface 22A1 of the front casing 22A constituting the casing 22.
- the second brake device 71 is composed of, for example, a wet multi-plate type negative brake.
- the second brake device 71 When the wheel loader 1 is parked or when the traveling wheel loader 1 is to be stopped in an emergency, the second brake device 71 is connected to the second transmission shaft 41. Apply braking force. On the other hand, the second brake device 71 releases the braking force applied to the second transmission shaft 41 when the wheel loader 1 travels.
- the brake case 72 of the second brake device 71 is detachably attached to the front surface 22A1 of the front casing 22A while surrounding the cylindrical portion 52A of the output gear 52 from the outer peripheral side.
- the brake case 72 includes a main body portion 72A, a lid portion 72B, an intermediate cylinder portion 72C, an inward flange portion 72D, and a brake release pressure inlet 72E. Yes.
- the brake case 72 is attached to the front surface 22A1 of the front casing 22A by a plurality of bolts 72F.
- an adapter 73 splined to the outer peripheral side of the cylindrical portion 52A of the output gear 52, a plurality of stationary brake plates 74 splined to the inner peripheral side of the main body 72A, A plurality of rotation-side brake plates 75 that are spline-coupled to the outer peripheral side of the adapter 73 so as to alternately overlap with the fixed-side brake plates 74 are provided.
- a brake piston 76 having a large diameter portion 76A and a small diameter portion 76B and slidably inserted on the inner peripheral side of the intermediate cylinder portion 72C, and each fixed brake plate 74, A backup ring 77 that restricts the movement of each rotation-side brake plate 75 in the axial direction is provided. Further, in the brake case 72, a spring member 78 that constantly urges the brake piston 76 in a direction of pressing the stationary brake plate 74 and the rotating brake plate 75, and between the intermediate cylinder portion 72 ⁇ / b> C and the brake piston 76. And an oil chamber 79 into which pressure oil for releasing the brake is introduced.
- the brake piston 76 of the second brake device 71 is a spring member 78.
- the fixed brake plates 74 and the rotary brake plates 75 are frictionally engaged with each other by the urging force. Accordingly, the second brake device 71 applies a braking force to the second transmission shaft 41.
- the brake piston 76 is separated from the rotation-side brake plate 75 against the urging force of the spring member 78. . Thereby, the second brake device 71 releases the braking force applied to the second transmission shaft 41.
- the output shaft 54 is always connected to the first transmission shaft 40 and the second transmission shaft 41. For this reason, a braking force can be applied to the first transmission shaft 40 by the first braking device 61 and a braking force can be applied to the second transmission shaft 41 by the second braking device 71. As a result, a large braking force added by the first and second brake devices 61 and 71 can be applied to the output shaft 54. Therefore, when the traveling wheel loader 1 is stopped in an emergency, the wheel loader 1 can be stopped quickly and reliably by the large braking force by the first and second brake devices 61 and 71.
- the hydraulic pump 81 is driven to rotate by the engine 10 to discharge the hydraulic oil stored in the hydraulic oil tank 82 to the oil passage 83 as pressure oil.
- the oil passage 83 is connected to the oil chamber 69 of the first brake device 61 via the first branch oil passage 83A, and the second brake device 71 via the second branch oil passage 83B.
- An oil chamber 79 is connected.
- the hydraulic pump 81 and the hydraulic oil tank 82 constitute a hydraulic source.
- the brake control valve 84 is located between the oil chambers 69 and 79 and the hydraulic pump 81 and is provided in the middle of the oil passage 83.
- the brake control valve 84 is, for example, a manually operable electromagnetic valve having a 3 port 2 position. It consists of a valve.
- the brake control valve 84 is provided with an electromagnetic pilot portion 84A and a manual operation lever 84B, and is provided with a return spring 84C.
- the electromagnetic pilot portion 84A is connected to a power source 86 via a brake release switch 85.
- the brake release switch 85 is opened when the wheel loader 1 is parked or when the traveling wheel loader 1 is emergency stopped, and closed when the wheel loader 1 is traveling.
- the brake control valve 84 holds the braking position (A) by the return spring 84C when no signal (current from the power source 86) is supplied to the electromagnetic pilot portion 84A. To do.
- the brake control valve 84 is switched to the brake release position (B) when a signal is supplied to the electromagnetic pilot portion 84A by closing the brake release switch 85.
- the brake control valve 84 holds the braking position (A). At this time, the supply of pressure oil to the oil chamber 69 of the first brake device 61 and the oil chamber 79 of the second brake device 71 is stopped. Therefore, the brake piston 66 of the first brake device 61 frictionally engages each stationary brake plate 64 and each rotation brake plate 65 by the urging force of the spring member 68, thereby causing the first transmission shaft 40 to move. On the other hand, a braking force is applied.
- the brake piston 76 of the second brake device 71 frictionally engages each stationary brake plate 74 and each rotation side brake plate 75 by the biasing force of the spring member 78, thereby A braking force is applied to the transmission shaft 41.
- the brake control valve 84 is switched to the brake release position (B).
- pressure oil brake release pressure
- the brake piston 66 of the first brake device 61 is separated from the rotation-side brake plate 65 against the biasing force of the spring member 68, so that the braking force on the first transmission shaft 40 is released.
- the brake piston 76 of the second brake device 71 is separated from the rotation-side brake plate 75 against the biasing force of the spring member 78, so that the braking force on the second transmission shaft 41 is released. Is done.
- a pressure sensor 87 is provided between the oil chambers 69 and 79 and the brake control valve 84.
- the pressure sensor 87 detects the pressure of the brake release pressure supplied to the oil chambers 69 and 79 of the first and second brake devices 61 and 71.
- the pressure sensor 87 notifies the driver by turning on a warning light (not shown) in the cab 9, for example.
- an accumulator 88 is connected between the hydraulic pump 81 and the brake control valve 84. The accumulator 88 supplies brake release pressure to the oil chambers 69 and 79 in place of the hydraulic pump 81 when the discharge pressure from the hydraulic pump 81 decreases for some reason.
- the vehicle power transmission device 21 has the above-described configuration, and the operation of the vehicle power transmission device 21 will be described below.
- the brake release switch 85 in FIG. 7 is opened, and the brake control valve 84 holds the braking position (A). Accordingly, the brake release pressure from the hydraulic pump 81 is not supplied to the oil chamber 69 of the first brake device 61 and the oil chamber 79 of the second brake device 71. In this state, the first brake device 61 applies a braking force to the first transmission shaft 40 and the second brake device 71 applies a braking force to the second transmission shaft 41.
- the brake control valve 84 is switched to the brake release position (B), and the pressure oil (brake release pressure) from the hydraulic pump 81 passes through the oil passage 83 to the oil chamber 69 of the first brake device 61 and the second. Are simultaneously supplied to the oil chamber 79 of the brake device 71. As a result, the braking force from the first brake device 61 on the first transmission shaft 40 and the braking force from the second brake device 71 on the second transmission shaft 41 are simultaneously released.
- the rotational output of the engine 10 is transmitted to the rotary shaft 35 via the torque converter 23, the forward shaft 27, etc. of the vehicle power transmission device 21.
- the first speed change shaft 40 and the first speed input gear 44 are connected by connecting the first speed clutch mechanism 50.
- the rotation of the rotating shaft 35 is transmitted to the first transmission shaft 40 via the output gear 38 and the first-speed input gear 44.
- the rotation of the first transmission shaft 40 is transmitted from the output gear 48 to the low-speed input gear 57 of the output shaft 54, and the output shaft 54 rotates at the first speed.
- the high speed side input gear 58 attached to the output shaft 54 together with the low speed side input gear 57 is always meshed with the output gear 52 of the second speed change shaft 41, the second speed change shaft 41 is the output shaft. Rotate together with 54.
- the rotation of the output shaft 54 is transmitted to the front axle 11 via the propeller shaft 13 and also to the rear axle 12 via the propeller shaft 14.
- the left and right front wheels 2 attached to the front axle 11 and the left and right rear wheels 4 attached to the rear axle 12 rotate, thereby causing the wheel loader 1 to run at a first speed. Can do.
- the driver opens the brake release switch 85 and switches the brake control valve 84 to the braking position (A).
- the supply of pressure oil to the oil chamber 69 of the first brake device 61 and the oil chamber 79 of the second brake device 71 is cut off.
- the first brake device 61 applies braking force to the first transmission shaft 40
- the second brake device 71 applies braking force to the second transmission shaft 41.
- the first transmission shaft 40 connected to the output shaft 54 via the output gear 48 and the low speed side input gear 57, and the output gear 52 and the high speed side input gear 58 connected to the output shaft 54.
- a braking force can be simultaneously applied to the second transmission shaft 41. Therefore, the output shaft 54 can receive a large braking force obtained by adding the braking force of the first brake device 61 and the braking force of the second brake device 71. As a result, the traveling wheel loader 1 can be stopped quickly and reliably.
- the first brake device 61 is provided on the casing 22, and is controlled by the first transmission shaft 40 that is always connected to the output shaft 54 via the output gear 48 and the low-speed side input gear 57.
- the second brake device 71 is provided on the casing 22 and applies braking force to the second transmission shaft 41 that is always connected to the output shaft 54 via the output gear 52 and the high-speed side input gear 58. It is configured.
- the first transmission shaft 40 when the rotary shaft 35 and the first transmission shaft 40 are connected by the first-speed clutch mechanism 50 or the second-speed clutch mechanism 51, the first transmission shaft connected to the rotary shaft 35.
- a braking force can be applied to 40 by the first brake device 61.
- a braking force can be applied to the second speed change shaft 41 that is not connected to the rotary shaft 35 using the second brake device 71.
- the traveling wheel loader 1 when the traveling wheel loader 1 is brought to an emergency stop, a large braking force obtained by adding the braking forces of the first and second brake devices 61 and 71 can be applied to the output shaft 54. For this reason, compared with the case where one brake device is provided between any one of the plurality of transmission shafts and the casing, the traveling wheel loader 1 can be stopped quickly and reliably. it can.
- the braking force applied to the output shaft 54 can be increased. .
- the braking force applied to the output shaft 54 can be increased.
- the vehicle power transmission device 21 as a whole can be configured more compactly than when a large number of rotation-side brake plates are attached to a single transmission shaft.
- the first brake device 61 is disposed so as to be shifted to one end side in the axial direction of the first transmission shaft 40
- the second brake device 71 is disposed on one end side in the axial direction of the second transmission shaft 41.
- the first and second brake devices 61 and 71 can be collectively arranged on the same side (front end side) in the axial direction of the first and second transmission shafts 40 and 41.
- a hydraulic hose (not shown) that supplies pressure oil from the hydraulic pump 81 to the oil chamber 69 of the first brake device 61, and pressure oil from the hydraulic pump 81 to the oil chamber 79 of the second brake device 71.
- the hydraulic hose (not shown) for supplying the pressure can be set to approximately the same length.
- pressure oil can be supplied and discharged simultaneously to the first and second brake devices 61 and 71, and the operation timings of the first and second brake devices 61 and 71 can be matched.
- a casing 22 constituting the vehicle power transmission device 21 is mounted on the rear vehicle body 5 of the wheel loader 1, and the first brake device 61 and the second brake device 71 are faced to the coupling mechanism 6 in the front casing 22 ⁇ / b> A. Is detachably attached to the front surface 22A1. For this reason, it is possible to supply a large amount of cooling air to the first and second brake devices 61 and 71 using the traveling wind pressure when the wheel loader 1 travels. As a result, the vehicle power transmission device 21 including the first and second brake devices 61 and 71 can be efficiently cooled.
- the front and rear vehicle bodies 3 and 5 of the wheel loader 1 are bent around the coupling mechanism 6 to connect the first and second brake devices 61 and 71 to the coupling mechanism. 6 can be easily attached to and removed from the front face 22A1 of the front casing 22A facing the front face 6. Thereby, workability
- the vehicle power transmission device 21 is provided with two transmission shafts of the first transmission shaft 40 and the second transmission shaft 41, and the first and second transmission shafts 40,
- the case where the two brake devices of the 1st brake device 61 and the 2nd brake device 71 are provided between 41 and the casing 22 is illustrated.
- the present invention is not limited to this.
- three or more transmission shafts may be provided, and three or more brake devices corresponding to the number of the transmission shafts may be provided.
- the vehicle power transmission device 21 is mounted on the rear body 5 of the wheel loader 1 and the first and second brake devices 61 and 71 are arranged facing the coupling mechanism 6 is illustrated. ing.
- the present invention is not limited to this.
- the vehicle power transmission device 21 is mounted on the front body 3, and the first and second brake devices 61 and 71 are arranged to face the coupling mechanism 6. Good.
- the wheel loader 1 is illustrated as a work vehicle on which the vehicle power transmission device 21 is mounted.
- the present invention is not limited to this, and can be widely applied to other work vehicles such as construction vehicles such as wheel excavators, transport vehicles such as lift trucks, and agricultural vehicles such as tractors.
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Abstract
Description
2 前車輪
3 前部車体(車体)
4 後車輪
5 後部車体(車体)
6 連結機構
10 エンジン(原動機)
21 車両用動力伝達装置
22 ケーシング
35 回転軸
40 第1の変速軸(変速軸)
41 第2の変速軸(変速軸)
48 出力歯車(歯車)
50 1速用クラッチ機構(クラッチ機構)
51 2速用クラッチ機構(クラッチ機構)
52 出力歯車(歯車)
54 出力軸
57 低速側入力歯車(歯車)
58 高速側入力歯車(歯車)
61 第1のブレーキ装置
71 第2のブレーキ装置
Claims (6)
- 車両(1)に搭載されたケーシング(22)と、該ケーシング(22)内に回転可能に支持され前記車両(1)に搭載された原動機(10)によって回転される回転軸(35)と、前記ケーシング(22)内に並列に並んで回転可能に支持され前記回転軸(35)の回転を互いに異なる回転数に変速する複数本の変速軸(40,41)と、前記回転軸(35)と前記各変速軸(40,41)との間に設けられ前記各変速軸(40,41)のうちいずれか一の変速軸と前記回転軸(35)とを選択的に接続するクラッチ機構(50,51)と、前記各変速軸(40,41)に歯車(48,52,57,58)を介して常時連結され前記クラッチ機構(50,51)によって選択された一の変速軸の回転を前記車両(1)の車輪(2,4)に出力する出力軸(54)とを備えてなる車両用動力伝達装置において、
前記ケーシング(22)には、前記各変速軸(40,41)に対してそれぞれ制動力を付与する複数個のブレーキ装置(61,71)を設ける構成としたことを特徴とする車両用動力伝達装置。 - 前記複数個のブレーキ装置(61,71)は、前記複数本の変速軸(40,41)に対して軸方向の一側に片寄せてそれぞれ配置する構成としてなる請求項1に記載の車両用動力伝達装置。
- 前記ケーシング(22)には、前記出力軸(54)を挟んで両側に前記各変速軸(40,41)のうちいずれか一の変速軸と他の変速軸とをそれぞれ配置する構成としてなる請求項1に記載の車両用動力伝達装置。
- 前記ケーシング(22)は、フロントケーシング(22A)と、該フロントケーシング(22A)の後側に位置する中間ケーシング(22B)と、該中間ケーシング(22B)の後側に位置するリヤケーシング(22C)とにより形成され、
前記回転軸(35)は前記中間ケーシング(22B)と前記リヤケーシング(22C)とによって支持され、
前記各変速軸(40,41)は前記回転軸(35)の下側に位置して前記中間ケーシング(22B)と前記リヤケーシング(22C)とによって左,右方向で対向するようにそれぞれ支持され、
前記出力軸(54)は、前記各変速軸(40,41)の下側に位置して前記中間ケーシング(22B)と前記フロントケーシング(22A)とによって支持され、
前記各ブレーキ装置(61,71)は、前記各変速軸(40,41)の前端側に位置して前記フロントケーシング(22A)の前面(22A1)に設ける構成としてなる請求項1に記載の車両用動力伝達装置。 - 前記各ブレーキ装置(61,71)は、油室(69,79)に圧油が供給されることにより制動を解除するネガティブ型ブレーキとして構成し、
油圧ポンプ(81)と前記各ブレーキ装置(61,71)との間を油路(83)を介して接続し、該油路(83)の途中には、油圧ポンプ(81)から前記各ブレーキ装置(61,71)の油室(69,79)に圧油を供給し制動力を解除する制動解除位置と、前記各ブレーキ装置(61,71)の油室(69,79)をタンク(82)に接続し制動力を付与する制動位置とを有するブレーキ制御弁(84)を設け、
前記各ブレーキ装置(61,71)は、前記ブレーキ制御弁(84)によって前記各変速軸(40,41)に対して同時に制動力を付与し、または前記各変速軸(40,41)に対して同時に制動力を解除する構成としてなる請求項1に記載の車両用動力伝達装置。 - 前記車両(1)は、前車輪(2)が設けられた前部車体(3)と、後車輪(4)が設けられた後部車体(5)と、前記前部車体(3)と後部車体(5)との間に設けられ前記前部車体(3)と後部車体(5)とを左,右方向に屈曲可能に連結する連結機構(6)とにより構成し、
前記前部車体(3)および後部車体(5)のうち一方の車体に前記原動機(10)を搭載し、前記ケーシング(22)は、前記連結機構(6)と前記原動機(10)との間に位置して前記一方の車体に設け、前記ブレーキ装置(61,71)は、前記連結機構(6)と対面して前記各変速軸(40,41)の軸方向の一側に配置する構成としてなる請求項1に記載の車両用動力伝達装置。
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KR1020137012411A KR101874656B1 (ko) | 2011-02-02 | 2012-01-25 | 차량용 동력 전달 장치 |
CN201280004334.5A CN103282691B (zh) | 2011-02-02 | 2012-01-25 | 车辆用动力传递装置 |
US13/877,376 US20130298708A1 (en) | 2011-02-02 | 2012-01-25 | Power transmission device for vehicle |
DE112012000651.8T DE112012000651B4 (de) | 2011-02-02 | 2012-01-25 | Leistungsübertragungsvorrichtung für ein Fahrzeug |
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JP2011020622A JP5638976B2 (ja) | 2011-02-02 | 2011-02-02 | 車両用動力伝達装置 |
JP2011-020622 | 2011-02-02 |
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PCT/JP2012/051535 WO2012105383A1 (ja) | 2011-02-02 | 2012-01-25 | 車両用動力伝達装置 |
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US (1) | US20130298708A1 (ja) |
JP (1) | JP5638976B2 (ja) |
KR (1) | KR101874656B1 (ja) |
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JP5837471B2 (ja) * | 2012-10-02 | 2015-12-24 | 日立建機株式会社 | 車両用動力伝達装置 |
CN104132083B (zh) * | 2014-07-21 | 2016-06-29 | 龙岩文伍车桥制造有限公司 | 带湿式制动器的汽车变速箱 |
WO2016180898A1 (en) * | 2015-05-11 | 2016-11-17 | Dana Belgium N.V. | Transmission for a vehicle and driveline comprising the transmission |
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- 2012-01-25 CN CN201280004334.5A patent/CN103282691B/zh active Active
- 2012-01-25 KR KR1020137012411A patent/KR101874656B1/ko active IP Right Grant
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Also Published As
Publication number | Publication date |
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JP2012159166A (ja) | 2012-08-23 |
KR101874656B1 (ko) | 2018-07-04 |
US20130298708A1 (en) | 2013-11-14 |
DE112012000651B4 (de) | 2020-07-09 |
JP5638976B2 (ja) | 2014-12-10 |
DE112012000651T5 (de) | 2013-11-14 |
KR20130135253A (ko) | 2013-12-10 |
CN103282691B (zh) | 2016-03-02 |
CN103282691A (zh) | 2013-09-04 |
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