CN112901754B - Integrated device of bidirectional rotary power takeoff, gearbox and power takeoff - Google Patents

Integrated device of bidirectional rotary power takeoff, gearbox and power takeoff Download PDF

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Publication number
CN112901754B
CN112901754B CN202110049664.7A CN202110049664A CN112901754B CN 112901754 B CN112901754 B CN 112901754B CN 202110049664 A CN202110049664 A CN 202110049664A CN 112901754 B CN112901754 B CN 112901754B
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China
Prior art keywords
gear
output
input
shaft
output gear
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CN202110049664.7A
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Chinese (zh)
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CN112901754A (en
Inventor
魏文义
陈鹏
侯月旺
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Beijing Foton Daimler Automobile Co Ltd
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Beijing Foton Daimler Automobile Co Ltd
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Priority to CN202110049664.7A priority Critical patent/CN112901754B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F16H2057/0206—Gearboxes for particular applications for vehicle transmissions for commercial vehicles, e.g. buses or trucks

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a bidirectional rotary power takeoff, a gearbox and a power takeoff integrated device, wherein the bidirectional rotary power takeoff comprises: the device comprises a shell, an input shaft, an output shaft, a forward rotation gear set, a reverse rotation gear set and a switching mechanism. The input shaft and the output shaft are pivotally connected to the casing. The positive rotation gear set comprises a first input gear and a first output gear which is used for being meshed with the first input gear; the reverse rotation gear set comprises a second input gear and a second output gear which is meshed with the second input gear, the first input gear and the second input gear are arranged on an input shaft and have the same rotation direction, and the first output gear and the second output gear are arranged on an output shaft and have opposite rotation directions. Therefore, the switching mechanism controls the switching of the power transmission route, the forward/reverse rotation of the output shaft is realized, the refitting adaptability of the power takeoff is improved, and the rotation direction of a driving device required by an oil pump, an air pump and a water pump is not needed to be considered when the vehicle is additionally installed or refitted.

Description

Integrated device of bidirectional rotary power takeoff, gearbox and power takeoff
Technical Field
The invention relates to the field of vehicles, in particular to an integrated device of a bidirectional rotary power takeoff, a gearbox and a power takeoff.
Background
In the prior art, the power take-off used in the transmission of a freight vehicle is one-way rotation, i.e. forward rotation or reverse rotation. In the process of loading and refitting, the rotation direction of the selected oil pump, air pump, water pump or other mechanisms needs to be matched with the rotation direction of the selected oil pump, air pump, water pump or other mechanisms to work normally, if the rotation direction is not matched with the rotation direction, the power takeoff with different rotation directions needs to be replaced, or the rotation direction of the oil pump, the air pump and the water pump is matched with the power takeoff, however, in some cases, the structure of the loading is required to be adjusted, and the refitting work is troublesome.
In conclusion, the existing output shaft can only rotate in one direction, and the refitting applicability of the power takeoff is low.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, an object of the present invention is to provide a bidirectional rotary power take-off, a gearbox and a power take-off integrated device with an output shaft capable of rotating bidirectionally.
The bidirectional rotary power takeoff according to the embodiment of the first aspect of the present invention includes: the device comprises a shell, an input shaft, an output shaft, a forward rotation gear set, a reverse rotation gear set and a switching mechanism. The input shaft is pivotally connected to the housing; the output shaft is pivotally connected to the housing. The positive rotation gear set comprises a first input gear and a first output gear which is used for being meshed with the first input gear; the anti-rotation gear set comprises a second input gear and a second output gear which is meshed with the second input gear, the first input gear and the second input gear are arranged on the input shaft, the rotation directions of the first input gear and the second input gear are the same, the first output gear and the second output gear are arranged on the output shaft, and the rotation directions of the first output gear and the second output gear are opposite. The switching mechanism is used for alternatively controlling the connection of two power transmission routes, and the first power transmission route is as follows: input shaft, first input gear, first output gear, output shaft, the second power transmission route is: the input shaft, the second input gear, the second output gear and the output shaft.
Therefore, the switching mechanism controls the switching of the power transmission route, so that the rotation directions of the final output shaft are opposite when the forward rotation gear set and the reverse rotation gear set participate in torque transmission, the forward/reverse rotation of the output shaft can be realized according to the rotation directions required by the external execution mechanism, the refitting adaptability of the power takeoff is improved, the rotation directions of the gearbox or the speed reducer are not required to be considered when the gearbox or the speed reducer is matched with the power takeoff, and the rotation directions of driving devices required by an oil pump, an air pump and a water pump are not required to be considered when the vehicle is additionally arranged and refitted.
In some embodiments, the second input gear is an internal gear, and the first output gear, the second output gear, and the first input gear are external gears.
In some embodiments, the switching mechanism is configured to control the output shaft to alternatively be in dynamic coupling with the first output gear and the second output gear.
In some embodiments, the switching mechanism includes a sliding sleeve and a shifting fork, the first input gear and the second input gear are both in power coupling connection with the input shaft, the first output gear and the second output gear are sleeved outside the output shaft, the sliding sleeve is slidably sleeved outside the output shaft, the sliding sleeve is in power coupling with the output shaft, the shifting fork is suitable for driving the sliding sleeve to move, so that the first output gear is in power coupling with the output shaft when the sliding sleeve is engaged with the first output gear, and the second output gear is in power coupling with the output shaft when the sliding sleeve is engaged with the second output gear.
In some embodiments, the sliding sleeve is configured to be switchable between three positions: a first position engaged with the first output gear, a second position engaged with the second output gear, and an intermediate position between the first position and the second position.
In some embodiments, one end of the sliding sleeve has a first engagement tooth; the end face of the first output gear is provided with a second engaging tooth for engaging with the first engaging tooth of the sliding sleeve.
In some embodiments, the other end of the sliding sleeve has a third engagement tooth; the second output gear includes first and second teeth coaxially connected and disposed at intervals in an axial direction, the first teeth meshing with the second input gear, an end face of the second teeth having fourth engaging teeth for engaging with third engaging teeth.
In some embodiments, the second output gear further comprises a sleeve connecting the first tooth portion and the second tooth portion, and the sleeve is hollow around the output shaft, and an outer wall of the sleeve is connected with the casing through a first rolling support member, so that the second tooth portion and the sliding sleeve are fixed relative to each other and the output shaft is pivoted relative to the casing.
In some embodiments, the reverse rotation gear set is disposed proximate to an input end of the input shaft, the forward rotation gear set is disposed proximate to an output end of the output shaft, and the output end of the output shaft is further pivotally connected to the housing via a second rolling support.
In some embodiments, the second input gear, the first input gear, and the input shaft are integrally formed as a gear shaft.
In some embodiments, the second input gear includes an end plate vertically connected to the input shaft and a ring gear connected to one side of the end plate and having internal teeth formed inside the ring gear, the input shaft being pivotally connected to the housing through a third rolling support between the end plate and the first input gear; at least one of the two ends of the input shaft is pivotally connected to the housing by a fourth rolling support.
In some embodiments, the switching mechanism includes a sliding sleeve slidably sleeved outside the input shaft and the sliding sleeve is in power coupling with the input shaft, the first input gear and the second input gear are sleeved on the input shaft, and the shifting fork is suitable for driving the sliding sleeve to be engaged with one of the first input gear and the second input gear so as to alternatively couple the input shaft with the first input gear and the second input gear in power.
In some embodiments, the switching mechanism is configured to alternatively control engagement of the first input gear with the first output gear, engagement of the second input gear with the second output gear.
In some embodiments, the first output gear and the second output gear are both in power coupling with the output shaft, the switching mechanism is adapted to drive the output shaft to move axially, and the second output gear is staggered from the second input gear when the first output gear is meshed with the first input gear; when the second output gear is meshed with the second input gear, the first output gear is staggered from the first input gear.
In some embodiments, the switching mechanism includes a sliding sleeve and a shifting fork, the first output gear, the sliding sleeve and the second output gear are sequentially and coaxially fixed, and are in power coupling with the output shaft and slidably sleeved outside the output shaft, and the interval between the first output gear and the second output gear is smaller than the interval between the first input gear and the second input gear.
In some embodiments, the switching mechanism is a pneumatic switching mechanism, and the switching mechanism further comprises a driving member, wherein the driving member comprises a cylinder, an air storage cylinder and a rotation direction control switch which are connected in series, the cylinder is connected with the shifting fork, and the rotation direction control switch is used for controlling the action direction of the cylinder so as to control the moving position of the shifting fork.
An integrated transmission and power take-off device according to an embodiment of the second aspect of the present invention includes: the transmission, bi-directional rotating power take-off of any of the above embodiments, one of the input shaft, first input gear, second input gear of the bi-directional rotating power take-off being mated with the transmission to receive a torque output of the transmission.
In some embodiments, the bidirectional rotary power take-off is connected to the gearbox at a rear position, and an input shaft of the bidirectional rotary power take-off is fixedly connected with an output transmission shaft of the gearbox.
In some embodiments, the bidirectional rotary power take-off is laterally connected to the gearbox, and an input external gear is arranged on an input shaft of the bidirectional rotary power take-off, and the input external gear is meshed with one gear of the gearbox.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:
FIG. 1 is a schematic diagram of a rear-mounted bi-directional rotating power take-off in accordance with one embodiment of the present invention.
Fig. 2 is a schematic diagram of a rear-mounted bi-directional rotary power take-off in accordance with another embodiment of the present invention.
Fig. 3 is a schematic view of a side-mounted bi-directional rotary power take-off in accordance with yet another embodiment of the present invention.
Fig. 4 is a schematic diagram of an integrated device (power take-off rear) according to one embodiment of the invention.
Fig. 5 is a schematic diagram of an integrated device (power take-off side) according to another embodiment of the invention.
Fig. 6 is a schematic diagram of an integrated device according to yet another embodiment of the invention.
Reference numerals:
bidirectional rotary power take-off 100;
a housing 10;
an input shaft 20; an input external gear 21;
an output shaft 30;
a forward rotation gear set 40; a first input gear 41; a first output gear 42; second engagement teeth 421;
a counter-rotating gear set 50; a second input gear 51; an end plate 511; a ring gear 512; a second output gear 52; a first tooth 521; a second tooth 522; fourth engagement teeth 5221; a sleeve 523;
a switching mechanism 60; a sliding sleeve 61; a first engagement tooth 611; a third engagement tooth 612; a fork 62; a driving member 63; a cylinder 631; a gas cylinder 632; a rotation direction control switch 633;
a first rolling support a; a second rolling support b; a third rolling support c; a fourth rolling support d;
a transmission 200; an output drive shaft 201; a housing 202.
Detailed Description
Embodiments of the present invention will be described in detail below, by way of example with reference to the accompanying drawings.
The integrated device of the bidirectional rotary power take-off 100, the transmission 200 and the power take-off according to the embodiment of the present invention is described below with reference to fig. 1 to 6.
According to the bidirectional rotary power take-off 100 of the embodiment of the first aspect of the present invention, the bidirectional rotary power take-off 100 includes: the gear box comprises a casing 10, an input shaft 20, an output shaft 30, a positive rotation gear set 40, a negative rotation gear set 50 and a switching mechanism 60.
As shown in fig. 1 and 4, the input shaft 20 is pivotably connected to the housing 10; the output shaft 30 is pivotally connected to the housing 10. The positive rotation gear set 40 includes a first input gear 41, a first output gear 42 for meshing with the first input gear 41; the counter-rotating gear set 50 includes a second input gear 51, a second output gear 52 for meshing with the second input gear 51, the first input gear 41 and the second input gear 51 are disposed on the input shaft 20, the first input gear 41 and the second input gear 51 have the same rotation direction, the first output gear 42 and the second output gear 52 are disposed on the output shaft 30, and the rotation directions of the first output gear 42 and the second output gear 52 are opposite.
The switching mechanism 60 is used for alternatively controlling the connection of two power transmission routes, wherein the first power transmission route is as follows: the input shaft 20, the first input gear 41, the first output gear 42, the output shaft 30, and the second power transmission path is: an input shaft 20, a second input gear 51, a second output gear 52, and an output shaft 30.
Specifically, the input shaft 20 and the output shaft 30 of the bi-directional rotation power take-off 100 are located in the casing 10, rotatable about their own central axes, and the input shaft 20 and the output shaft 30 are disposed parallel to each other.
It will be appreciated that the power transmission path refers to a torque transmission path, and torque is transmitted according to the first power transmission path to the first input gear 41 via the input shaft 20 to drive the first input gear to rotate in the same direction as the input shaft 20, and then is transmitted via each of the gears in the positive rotation gear set 40 that mesh with each other, and finally is transmitted from the first output gear 42, so as to transmit power to the output shaft 30 associated with the output gear. The distance of torque transmitted according to the second power transmission route is similar to that described above, and will not be described here.
The input shaft 20 is typically connected to a transmission mechanism such as a speed reducer or a gearbox 200 to divide a portion of the torque from the transmission mechanism, but does not affect the normal operation of the transmission mechanism; the output shaft 30 is adapted to be coupled to an actuator, such as a hydraulic pump, an air pump, a water pump, etc., for providing mechanical energy to the actuator.
In the forward rotation gear set 40 and the reverse rotation gear set 50, one gear set makes the rotation direction of the input shaft 20 the same as that of the output shaft 30, and the other gear set makes the rotation direction of the input shaft 20 opposite to that of the output shaft 30. The positive rotation means that the output shaft 30 is eventually driven to rotate in the positive direction (clockwise rotation), and the negative rotation means that the output shaft 30 is eventually driven to rotate in the negative direction (counterclockwise rotation). The rotational direction of the output shaft 30 is determined by the rotational direction of the input shaft 20 and the gear set.
For example, the rotation directions of the first input gear 41 and the first output gear 42 of the forward rotation gear set 40 may be set to be opposite such that when the input shaft 20 rotates counterclockwise and torque is transmitted in the first power transmission path, the output shaft 30 rotates clockwise, thereby achieving forward rotation. The rotation directions of the first input gear 41 and the first output gear 42 of the forward rotation gear set 40 may also be set to be the same, and when the input shaft 20 rotates clockwise and torque is transmitted in the first power transmission path, the output shaft 30 rotates clockwise, whereby forward rotation can also be achieved. The design concept of the reverse rotation of the output shaft 30 is similar to that described above, and is not repeated here.
In summary, as long as the rotation directions of the input gear and the output gear of one gear set are the same and the rotation directions of the input gear and the output gear of the other gear set are opposite in the forward rotation gear set 40 and the reverse rotation gear set 50, two selectable rotation directions of the output shaft 30 can be realized no matter the input shaft 20 is clockwise or anticlockwise.
Therefore, the switching mechanism 60 controls the switching of the power transmission route, so that the rotation directions of the positive rotation gear set 40 and the negative rotation gear set 50 are opposite when the positive rotation gear set and the negative rotation gear set 50 participate in torque transmission, and the positive rotation/negative rotation of the output shaft 30 can be realized by switching to the corresponding power transmission route according to the rotation directions required by the external execution mechanism, so that the refitting adaptability of the bidirectional rotary power takeoff 100 is improved, the rotation directions of the gearbox 200 or the speed reducer are not required to be considered when the bidirectional rotary power takeoff 100 is matched, and the rotation directions of driving devices required by an oil pump, an air pump and a water pump are not required to be considered when the vehicle is additionally installed or refitted. Input shaft 20 output shaft 30
Alternatively, the second input gear 51 is an internal gear, and the first output gear 42, the second output gear 52, and the first input gear 41 are external gears. In this way, the first input gear 41 and the first output gear 42 can realize external engagement, the second input gear 51 and the second output gear 52 can realize internal engagement, both external engagement and internal engagement can realize torque transmission, the rotation directions of the two gears of the internal engagement are the same, and the rotation directions of the two gears of the external engagement are opposite.
Thus, the first input gear 41 and the first output gear 42 can transmit the torque in the same direction as the torque of the input shaft 20, and the rotation direction of the output shaft 30 is not changed, so that the output shaft 30 and the input shaft 20 can rotate in the same direction; the torque output by the externally meshed second input gear 51 and second output gear 52 is opposite to the rotation direction of the input shaft 20, so that the output shaft 30 and the input shaft 20 rotate in different directions, and thus different gears are meshed, the output shaft 30 can rotate in different directions, and the adaptation degree of the bidirectional rotary power takeoff 100 to external connection is improved.
Alternatively, the switching mechanism 60 is used to control the output shaft 30 to be alternatively coupled with the first output gear 42 and the second output gear 52. It will be appreciated that by modulation of the switching mechanism 60, it is possible to choose to have the first output gear 42 move in synchronism with the output shaft 30 or the second output gear 52 rotate in synchronism with the output shaft 30. That is, the switching mechanism 60 controls whether or not power is transmitted between the output shaft 30 and the first output gear 42 and the second output gear 52.
In the following, by taking the power coupling of the output shaft 30 and the first output gear 42 as an example, the "power coupling" is explained, and the power coupling herein refers to that the output shaft 30 and the first output gear 42 do not rotate relatively in the radial direction, and when power is transmitted to the first output gear 42, the first output gear 42 can drive the output shaft 30 to rotate together, that is, torque can be transmitted therebetween. Specifically, the means for achieving the power coupling may be to fix the output shaft 30 and the first output gear 42, or to slide the output shaft 30 and the first output gear 42 in the axial direction, but the two may be a tight fit, a transition fit, or a spline fit, so that when the output shaft 30 and the first output gear 42 rotate, the two may not be dislocated in the axial direction and may not be displaced relative to each other in the rotational direction.
Similarly, the power coupling between the output shaft 30 and the second output gear 52, or the power coupling between other parts, may be substituted into the above description, and will not be repeated here.
Therefore, torque transmission between the output shaft 30 and any one of the forward rotation gear set 40 and the reverse rotation gear set 50 is realized by arranging the switching mechanism 60, so that the switching of the rotation direction is controlled at the terminal of power transmission, only the output shaft 30 drives one gear for power coupling at a time, the load on the output shaft 30 is reduced, and the torque transmission loss is reduced.
Further, the switching mechanism 60 includes a sliding sleeve 61 and a shifting fork 62, the first input gear 41 and the second input gear 51 are both in power coupling connection with the input shaft 20, the first output gear 42 and the second output gear 52 are sleeved outside the output shaft 30, the sliding sleeve 61 is slidably sleeved outside the output shaft 30, the sliding sleeve 61 is in power coupling with the output shaft 30, and the shifting fork 62 is suitable for driving the sliding sleeve 61 to move, so that the first output gear 42 is in power coupling with the output shaft 30 when the sliding sleeve 61 is engaged with the first output gear 42, and the second output gear 52 is in power coupling with the output shaft 30 when the sliding sleeve 61 is engaged with the second output gear 52.
The "empty sleeve" means that the gear is sleeved outside the shaft, the gear and the shaft do not slide relatively in the axial direction, and the rotation of the gear and the shaft do not interfere with each other in the circumferential direction.
As shown in fig. 1 and 3, the first output gear 42 and the second output gear 52 are sleeved on the output shaft 30, so that the first output gear 42 and the second output gear 52 can move on the output shaft 30 along the axial direction. The inner hole of the sliding sleeve 61 is provided with an inner spline, the area of the output shaft 30 used for being matched with the sliding sleeve 61 is provided with an outer spline matched with the inner spline, the shifting fork 62 is used for shifting the sliding sleeve 61 to adjust the position of the sliding sleeve 61 on the output shaft 30 outside the output shaft 30 and axially between the first output gear 42 and the second output gear 52, so that the sliding sleeve 61 can be engaged with one of the output gears, and the output shaft 30 can rotate along the corresponding rotation direction.
Therefore, the output shaft 30 is provided with the sliding sleeve 61 capable of sliding along the axial direction of the output shaft 30, so that the sliding sleeve 61 is engaged with one output gear when sliding leftwards and engaged with the other output gear when sliding rightwards, the output gears which are not engaged with the sliding sleeve 61 cannot move along with the output shaft 30 because of being sleeved on the output shaft 30, interference and influence on rotation of the output shaft 30 cannot be caused, and the first output gear 42 and the second output gear 52 cannot generate axial displacement during switching, so that transmission engagement of the forward rotation gear set 40 and the reverse rotation gear set 50 always keeps good contact, and fit gaps among engagement teeth cannot change along with the switching rotation direction, and power transmission is stable and reliable.
In detail, the sliding sleeve 61 is configured to be switchable between three positions: a first position engaged with the first output gear 42, a second position engaged with the second output gear 52, and an intermediate position between the first and second positions.
Thus, when the sliding sleeve 61 is positioned at the first position, the first output gear 42 is matched with the first input gear 41, so that the rotation of the output shaft 30 along one direction is realized; when the sliding sleeve 61 is positioned at the second position, the second output gear 52 is matched with the second input gear 51, so that the rotation of the output shaft 30 along the other direction is realized; when the slide 61 is in the neutral position, the output shaft 30 does not rotate, and the bidirectional rotary power take-off 100 does not operate.
Therefore, the output shaft 30 is respectively in the first position, the second position and the middle position by operating the shifting fork 62, so that three states of forward rotation/reverse rotation and stop of the output shaft 30 are correspondingly realized, and due to the arrangement of the middle position, transition is provided for switching between forward rotation and reverse rotation, so that the sliding sleeve 61 can be in the middle position in the initial state, a user can correspondingly adjust the rotation direction according to the application occasion, and even if the condition of forgetting to adjust the rotation direction is forgotten, the output shaft 30 does not transmit torque, and the self-propelled mechanism is not damaged.
Further, one end of the sliding sleeve 61 has a first engagement tooth 611; the end face of the first output gear 42 has second engagement teeth 421 for engagement with the first engagement teeth 611 of the sliding sleeve 61. As shown in fig. 5, when the sliding sleeve 61 slides toward the first output gear 42, the engaging external teeth of the sliding sleeve 61 engage with the second engaging teeth 421 of the first output gear 42, specifically, the second engaging teeth 421 and the first engaging teeth 611 may be spline-engaged, and at this time, the sliding sleeve 61 temporarily locks the first output gear 42 and the output shaft 30, and the three are formed as a whole that moves together without relative displacement therebetween.
Therefore, the corresponding tooth shapes for engagement are machined on the sliding sleeve 61 and the first output gear 42, so that the connection and locking of the output shaft 30 and the corresponding output gear can be realized while the sliding sleeve 61 moves in place, no additional locking piece is needed, and the operation is simple and quick.
Optionally, the other end of the sliding sleeve 61 has a third engagement tooth 612; the second output gear 52 includes a first tooth 521 and a second tooth 522 coaxially connected and disposed at a spacing in the axial direction, the first tooth 521 meshing with the second input gear 51, and an end surface of the second tooth 522 having a fourth engagement tooth 5221 for engagement with the third engagement tooth 612.
As shown in fig. 3, the third engaging teeth 612 may be located on an end surface of the sliding sleeve 61, may be located on an outer wall of the sliding sleeve 61, may extend through the entire sliding sleeve 61 in an axial direction of the sliding sleeve 61, or may be distributed on an outer wall of the sliding sleeve 61, near both ends of the sliding sleeve 61. Thus, the first engagement tooth 611 can be engaged with the first output gear 42 located at the right end of the sliding sleeve 61, and the third engagement tooth 612 can be engaged with the second output gear 52 located at the left end of the sliding sleeve 61.
The first tooth 521 and the second tooth 522 are coaxially arranged, the external teeth of the first tooth 521 mesh with the internal teeth of the second input gear 51, the diameter of the first tooth 521 is smaller than one half of the diameter of the first input gear 41, a fourth engaging tooth 5221 is provided at an end of the second tooth 522 facing away from the first tooth 521, and the fourth engaging tooth 5221 can mesh with the third engaging tooth 612 at the end face of the sliding sleeve 61. When the third engagement tooth 612 is meshed with the second tooth portion 522, the second output gear 52 of the output shaft 30 transmits torque to the sliding sleeve 61, and the sliding sleeve 61 drives the output shaft 30 to rotate together.
Thus, the first tooth 521 and the second tooth 522 provided at intervals reduce the sliding stroke of the sliding sleeve 61, so that the sliding sleeve 61 can be quickly engaged with the second output gear 52 when working, and the working efficiency of the output shaft 30 is improved. Meanwhile, the fourth engaging teeth 5221 are arranged on the end face of the second tooth part 522, so that the fourth engaging teeth can be conveniently engaged with the sliding sleeve 61, and the engaged structure is more compact.
Specifically, the second output gear 52 further includes a sleeve 523, the sleeve 523 connects the first tooth 521 and the second tooth 522, and the sleeve 523 is hollow around the output shaft 30, and the outer wall of the sleeve 523 is connected to the casing 10 through the first rolling support a, so that the sleeve 523 and the output shaft 30 are fixed relative to each other and pivot relative to the casing 10 when the second tooth 522 is engaged with the sliding sleeve 61.
As shown in fig. 1 and 3, the first tooth 521 and the second tooth 522 are connected by a sleeve 523, the sleeve 523 is sleeved on the output shaft 30, a first rolling support a is further provided on the outer wall of the sleeve 523, and the first rolling support a is fixed on the casing 10. The sleeve 523 is fixedly connected to the first tooth 521 and the second tooth 522 and rotates simultaneously, and the second output gear 52 and the output shaft 30 rotate in the same direction and are fixed relatively. The rolling support may in particular be a rolling bearing.
Thus, the first rolling support member a of the output shaft 30 axially positions the second output gear 52 outside the sleeve 523 of the second output gear 52 to support the output shaft 30, so that the output shaft 30 can be supported at multiple points when torque is transmitted, and power transmission is smoother.
Optionally, the counter-rotating gear set 50 is arranged close to the input end of the input shaft 20, the positive-rotating gear set 40 is arranged close to the output end of the output shaft 30, and the output end of the output shaft 30 is further pivotally connected to the housing 10 by means of a second rolling support b.
As shown in fig. 1, 2 and 3, one end of the input shaft 20, which is close to the gearbox 200, is an input end, and the counter-rotating gear set 50 of the input end can realize the rotation of the input shaft 20 and the output shaft 30 in the same direction, and the frequency of the rotation of the output shaft 30 of the bidirectional rotary power takeoff 100 is controlled by controlling the transmission ratio of the second output gear 52 and the second input gear 51. The reverse rotation gear set 50 and the forward rotation gear set 40 are replaceable in position, and the reverse rotation gear set 50 may be located near the output. The output end is pivotally engaged with and passes through a second rolling support b fixed to the casing 10.
Thus, the second rolling support b is pivotally connected to the housing 10, defining the axial position of the second rolling support b and the output shaft 30, so that the second rolling support b better supports the output shaft 30 without affecting the rotation of the output shaft 30.
Alternatively, as shown in fig. 2, the second input gear 51, the first input gear 41, and the input shaft 20 are integrally formed as gear shafts.
Therefore, the integrally formed design simplifies the assembly process and improves the assembly efficiency of the power takeoff.
Further, the second input gear 51 includes an end plate 511 and a gear ring 512, the end plate 511 is vertically connected with the input shaft 20, the gear ring 512 is connected to one side of the end plate 511 and an inner tooth is formed inside the gear ring 512, and the input shaft 20 is pivotally connected to the casing 10 through a third rolling support c located between the end plate 511 and the first input gear 41; at least one of both ends of the input shaft 20 is pivotally connected to the casing 10 through a fourth rolling support d.
As shown in fig. 3, a ring gear 512 is provided on an end surface of the end plate 511 on the side close to the second output gear 52, and internal teeth of the ring gear 512 mesh with the second output gear 52 above the input shaft 20. A third rolling support c is further provided on the input shaft 20 below the second output gear 52, the third rolling support c being engaged with the input shaft 20, the input shaft 20 being rotatable relative to the third rolling support c.
Therefore, at least one fourth rolling support d is arranged at two ends of the input shaft 20, so that the input shaft 20 is pivotally connected with the casing 10, and meanwhile, the support of the input shaft 20 and the radial limitation of the input shaft are increased together with the third rolling support c, so that the input shaft 20 rotates more stably, and radial runout in the rotating process due to overlong axial length is avoided.
In some embodiments, the switching mechanism 60 includes a sliding sleeve 61 and a shifting fork 62, the sliding sleeve 61 is slidably sleeved outside the input shaft 20, the sliding sleeve 61 is in power coupling with the input shaft 20, the first input gear 41 and the second input gear 51 are sleeved on the input shaft 20, and the shifting fork 62 is adapted to drive the sliding sleeve 61 to engage with one of the first input gear 41 and the second input gear 51 so as to selectively couple the input shaft 20 with the first input gear 41 and the second input gear 51.
Thus, the switching mechanism 60 is disposed on the input shaft 20, and the input gear is sleeved on the input shaft 20, so that the input gear is moved, only one input gear is engaged with the sliding sleeve 61, and the torque of the input shaft 20 is transmitted through the input gear engaged with the sliding sleeve 61, thereby driving the output shaft 30 to rotate in the corresponding rotational direction.
In other embodiments, the switching mechanism 60 is used to alternatively control the engagement of the first input gear 41 with the first output gear 42 and the engagement of the second input gear 51 with the second output gear 52.
By providing the switching mechanism 60, it is possible to facilitate adjustment of the engagement of the input gear and the output gear, for example, in the case where the input shaft 20 rotates counterclockwise, when the output shaft 30 is required to rotate in the forward direction, the slide sleeve 61 can be adjusted to engage the first input gear 41 with the second output gear 52; when reverse rotation of the output shaft 30 is desired, the sliding sleeve 61 can be adjusted to mate the second input gear 51 and the second output gear 52.
Therefore, only one gear set is in a meshed state, so that the interference of the gear set which does not transmit torque to the output shaft 30 to the other working gear set when the two gear sets work simultaneously is avoided, and the transmission efficiency is improved.
In a specific example, the first output gear 42 and the second output gear 52 are both in power coupling with the output shaft 30, the switching mechanism 60 is adapted to drive the output shaft 30 to move axially, and the second output gear 52 is staggered from the second input gear 51 when the first output gear 42 is meshed with the first input gear 41; when the second output gear 52 meshes with the second input gear 51, the first output gear 42 is offset from the first input gear 41.
That is, the first output gear 42 and the second output gear 52 may be fixed to the output shaft 30 in the axial direction, and the switching mechanism 60 causes one of the output gears located on the output shaft 30 of the bidirectional rotary power take-off 100 to mesh with the corresponding input gear and the other output gear to be offset from the other input gear by adjusting the axial position of the output shaft 30 of the bidirectional rotary power take-off 100.
Thus, by adjusting the axial position of the output shaft 30, the engagement of the output gear and the input/output gear is controlled, and torque transmission is achieved.
In another specific example, the switching mechanism 60 includes a sliding sleeve 61 and a shifting fork 62, where the first output gear 42, the sliding sleeve 61 and the second output gear 52 are coaxially fixed in sequence, and the three are in power coupling with the output shaft 30 and slidably sleeved outside the output shaft 30, and a space between the first output gear 42 and the second output gear 52 is smaller than a space between the first input gear 41 and the second input gear 51. As shown in fig. 2 and 3, the sliding sleeve 61 is provided between the first output gear 42 and the second output gear 52, and all three are movable in the axial direction of the output shaft 30, but are defined in the radial direction.
Thus, the first output gear 42, the second output gear 52 and the sliding sleeve 61 are sleeved on the output shaft 30, and different rotation directions of the output shaft 30 can be realized by changing the relative positions of the sliding sleeve 61 and the output gears. The distance between the first output gear 42 and the first input gear 41 is smaller, mainly because after the distance between the output shaft 30 and the input shaft 20 is determined, the first output gear 42 is externally meshed with the first input gear 41, and the second output gear 52 is internally meshed with the second input gear 51, so that on one hand, the output gear and the input gear can be accurately meshed; on the other hand, the coaxiality of the first input gear 41 and the second input gear 51, and the second output gear 52 and the second input gear 51 is ensured.
Alternatively, the switching mechanism 60 is a pneumatic switching mechanism 60, the switching mechanism 60 further includes a driving member 63, the driving member 63 includes a cylinder 631, an air cylinder 632, and a rotation direction control switch 633 connected in series with each other, the cylinder 631 is connected to the fork 62, and the rotation direction control switch 633 is used for controlling the movement direction of the cylinder 631 so as to control the movement position of the fork 62.
As shown in fig. 4, 5 and 6, the air cylinder 632 supplies air to the air cylinder 631, the rotation direction control switch 633 is connected with the air cylinder 631 to control the movement of the air cylinder 631, so that the air cylinder 631 drives the shifting fork 62 to move, and thus the shifting fork 62 is shifted to the sliding sleeve 61, when the telescopic rod of the air cylinder 631 extends or retracts, the shifting fork 62 correspondingly slides leftwards or rightwards, the sliding sleeve 61 is pushed to move to a preset position, and one of two power transmission paths is controlled to be connected, so that the output shaft 30 rotates along the corresponding rotation direction.
Therefore, through the arrangement of the switching mechanism 60, the moving direction of the piston rod in the air cylinder 631 can be controlled, so that the shifting fork 62 is driven to move to a designated position, the bidirectional movement of the shifting fork 62 is realized, the rotation direction of the output shaft 30 is conveniently controlled according to the rotation direction required by the external actuating mechanism, and the device has good applicability.
Of course, the present invention is not limited thereto, and the fork 62 may be provided to be manually controlled.
The integrated device of the transmission 200 and the power take-off according to the embodiment of the second aspect of the present invention includes: the gearbox 200, the bi-directional rotating power take-off 100 of any of the above embodiments, one of the input shaft 20, the first input gear 41, the second input gear 51 of the bi-directional rotating power take-off 100 is matched to the gearbox 200 to receive the torque output of the gearbox 200.
It will be appreciated that at the junction of gearbox 200 and bi-directional rotating power take-off 100, gearbox 200 may be mated with input shaft 20 of bi-directional rotating power take-off 100, or the gears of gearbox 200 may be meshed with the input gears of bi-directional rotating power take-off 100, thereby effecting transfer of torque in gearbox 200 to bi-directional rotating power take-off 100 for output via input shaft 20 and output shaft 30 of bi-directional rotating power take-off 100 to a hydraulic pump, pneumatic pump, or the like coupled thereto.
Therefore, the integrated device can facilitate the transmission of torque, increase the universality of the transmission and the bidirectional rotary power takeoff 100 through the diversity of the rotation direction of the output shaft 30, reduce the problem of mismatch with the upper assembly possibly existing in the installation process, and avoid the increase of time and labor cost caused by reworking.
Alternatively, as shown in fig. 4, the bidirectional rotary power take-off 100 is connected to the transmission case 200 at a rear position, and the input shaft 20 of the bidirectional rotary power take-off 100 is fixedly connected to the output transmission shaft 201 of the transmission case 200.
Therefore, the bidirectional rotary power take-off 100 is connected with the gearbox 200 in a rear mode, and can be directly connected with the input shaft 20 of the bidirectional rotary power take-off 100 through the output transmission shaft 201 of the gearbox 200, the transmission path is more direct, the structure of the integrated device is more compact, and the tightness of the bidirectional rotary power take-off 100 is better.
In addition, for the rear-mounted bidirectional rotary power take-off 100, a fourth rolling support d is provided at the joint between the bidirectional rotary power take-off 100 and the transmission case 200, the fourth rolling support d is fixedly connected with the casing 10, the input shaft 20 of the bidirectional rotary power take-off 100 is engaged with the fourth rolling support d, and the periphery of the fourth rolling support d is subjected to sealing treatment.
Alternatively, as shown in fig. 5, the bidirectional rotary power take-off 100 is laterally connected to the transmission 200, and an input external gear 21 is provided on the input shaft 20 of the bidirectional rotary power take-off 100, and the input external gear 21 is meshed with one gear of the transmission 200. It will be appreciated that one gear of the transmission 200 meshes with the input external gear 21 provided circumferentially of the second input gear 51, driving rotation of the second input gear 51, thereby transmitting torque in the transmission 200 to the bidirectional rotary power take-off 100.
Therefore, the input shaft 20 of the side bidirectional rotary power take-off device 100 is parallel to the output shaft 30 of the gearbox 200, and torque can be transmitted out of the gearbox 200 in a gear meshing mode, so that the axial length of the integrated device is shortened, and the integrated device is more convenient to arrange on the whole vehicle.
For the side bidirectional rotary power take-off 100, the connection part with the gearbox 200 is open, or the casing 10 of the bidirectional rotary power take-off 100 is communicated with the casing 202 of the gearbox 200, the side bidirectional rotary power take-off 100 can be manufactured integrally or connected through fasteners, the space occupied by gear engagement is large, and the casing 10 of the power take-off is communicated with the casing 202 of the gearbox 200, so that the convenience in installation can be improved.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention.
In the description of the invention, a "first feature" or "second feature" may include one or more of such features. In the description of the present invention, "plurality" means two or more. In the description of the invention, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, and may also include the first and second features not being in direct contact but being in contact with each other by another feature therebetween. In the description of the invention, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature.
In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.

Claims (17)

1. A bi-directional rotating power take-off comprising:
a housing;
an input shaft pivotally connected to the housing;
an output shaft pivotally connected to the housing;
a positive-going gear set including a first input gear, a first output gear for meshing with the first input gear;
the anti-rotation gear set comprises a second input gear and a second output gear which is used for being meshed with the second input gear, the first input gear and the second input gear are arranged on the input shaft, the rotation directions of the first input gear and the second input gear are the same, the first output gear and the second output gear are arranged on the output shaft, and the rotation directions of the first output gear and the second output gear are opposite;
The switching mechanism is used for alternatively controlling the connection of two power transmission routes, and the first power transmission route is as follows: input shaft, first input gear, first output gear, output shaft, the second power transmission route is: the input shaft, the second input gear, the second output gear and the output shaft are integrally formed into a gear shaft;
the switching mechanism is a pneumatic switching mechanism, the switching mechanism further comprises a driving piece, the driving piece comprises a cylinder, an air storage cylinder and a rotation direction control switch which are connected in series, the cylinder is connected with a shifting fork, and the rotation direction control switch is used for controlling the action direction of the cylinder so as to control the moving position of the shifting fork.
2. The bi-directional rotating power take-off of claim 1, wherein the second input gear is an internal gear and the first output gear, the second output gear, and the first input gear are external gears.
3. The bi-directional rotating power take-off of claim 2, wherein the switching mechanism is configured to control the output shaft to be alternatively power coupled with the first output gear and the second output gear.
4. A bi-directional rotary power take-off as claimed in claim 3 wherein the switching mechanism comprises a slide sleeve and a shift fork, the first input gear and the second input gear are both in power coupling connection with an input shaft, the first output gear and the second output gear are hollow and sleeved outside the output shaft, the slide sleeve is slidably sleeved outside the output shaft, the slide sleeve is in power coupling with the output shaft, the shift fork is suitable for driving the slide sleeve to move so that the first output gear is in power coupling with the output shaft when the slide sleeve is engaged with the first output gear, and the second output gear is in power coupling with the output shaft when the slide sleeve is engaged with the second output gear.
5. The bi-directional rotating power take-off of claim 4, wherein the sliding sleeve is configured to be switchable between three positions: a first position engaged with the first output gear, a second position engaged with the second output gear, and an intermediate position between the first position and the second position.
6. The bi-directional rotating power take-off of claim 4 wherein one end of the sliding sleeve has a first engagement tooth; the end face of the first output gear is provided with a second engaging tooth for engaging with the first engaging tooth of the sliding sleeve.
7. The bi-directional rotating power take-off of claim 4 wherein the other end of the sliding sleeve has a third engagement tooth; the second output gear includes first and second teeth coaxially connected and disposed at intervals in an axial direction, the first teeth meshing with the second input gear, an end face of the second teeth having fourth engaging teeth for engaging with third engaging teeth.
8. The bi-directional rotating power take-off of claim 7, wherein the second output gear further comprises a sleeve connecting the first and second teeth, the sleeve being hollow about the output shaft, an outer wall of the sleeve being connected to the housing by a first rolling support such that the second teeth are in sliding engagement with the sleeve, the output shaft being fixed relative to each other and pivoting relative to the housing.
9. The bi-directional rotating power take-off of claim 8, wherein the counter-rotating gear set is disposed proximate an input end of the input shaft and the positive rotating gear set is disposed proximate an output end of the output shaft, the output end of the output shaft further being pivotally connected to the housing via a second rolling support.
10. The bi-directional rotating power take-off according to claim 1, wherein the second input gear includes an end plate and a ring gear, the end plate is vertically connected with the input shaft, the ring gear is connected at one side of the end plate and an inner tooth is formed inside the ring gear, and the input shaft is pivotally connected to the housing through a third rolling support member located between the end plate and the first input gear;
at least one of the two ends of the input shaft is pivotally connected to the housing by a fourth rolling support.
11. The bi-directional rotating power take-off of any one of claims 1-2, wherein the switching mechanism comprises a sliding sleeve slidably disposed over the input shaft and in dynamic coupling with the input shaft, the first and second input gears being free of the input shaft, and a shift fork adapted to drive the sliding sleeve into engagement with one of the first and second input gears to selectively couple the input shaft with the first and second input gears.
12. The bi-directional rotating power take-off of any one of claims 1-2, wherein the switching mechanism is configured to alternatively control engagement of the first input gear with the first output gear and engagement of the second input gear with the second output gear.
13. The bi-directional rotating power take-off of claim 12, wherein the first output gear and the second output gear are both in power coupling with the output shaft, the switching mechanism is adapted to drive the output shaft to move axially, and the second output gear is offset from the second input gear when the first output gear is meshed with the first input gear; when the second output gear is meshed with the second input gear, the first output gear is staggered from the first input gear.
14. The bi-directional rotating power takeoff of claim 12, wherein the switching mechanism comprises a sliding sleeve and a shifting fork, the first output gear, the sliding sleeve and the second output gear are sequentially and coaxially fixed, are in power coupling with an output shaft and are slidably sleeved outside the output shaft, and the distance between the first output gear and the second output gear is smaller than the distance between the first input gear and the second input gear.
15. An integrated transmission and power take-off device, comprising:
a gearbox;
a bi-directional rotating power take-off as claimed in any one of claims 1 to 14, wherein one of the input shaft, first input gear, second input gear of the bi-directional rotating power take-off is matched to the gearbox to receive torque output of the gearbox.
16. The integrated device of claim 15, wherein the bi-directional rotating power take-off is post-connected to the gearbox, and an input shaft of the bi-directional rotating power take-off is fixedly connected to an output drive shaft of the gearbox.
17. The integrated device of claim 15, wherein the bi-directional rotating power take-off is laterally coupled to the gearbox, an external input gear is provided on an input shaft of the bi-directional rotating power take-off, the external input gear being meshed with a gear of the gearbox.
CN202110049664.7A 2021-01-14 2021-01-14 Integrated device of bidirectional rotary power takeoff, gearbox and power takeoff Active CN112901754B (en)

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CN113417975A (en) * 2021-06-23 2021-09-21 北京福田戴姆勒汽车有限公司 Power takeoff and vehicle with same

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CN110345209A (en) * 2019-06-28 2019-10-18 江苏美械变速箱有限公司 Speed change gear and automobile
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Publication number Priority date Publication date Assignee Title
JPH10127102A (en) * 1996-10-30 1998-05-19 Matsuyama Plow Mfg Co Ltd Mission device for farm work machine and farm work machine
CN1781754A (en) * 2004-12-04 2006-06-07 周海仙 Two speed two-way power takeoff for vehicle
CN101135365A (en) * 2007-10-22 2008-03-05 江南大学 Large angle pendulum motion and non-impacting start-up intermittent mechanism
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