CN212318686U

CN212318686U - Planetary wheel type two-gear gearbox based on pawl type overrunning clutch

Info

Publication number: CN212318686U
Application number: CN202020241581.9U
Authority: CN
Inventors: 韩毓东; 岳汉奇; 蔡文奇; 高炳钊
Original assignee: Jilin Bocheng Transmission System Technology Co ltd
Current assignee: Jilin Bocheng Transmission System Technology Co ltd
Priority date: 2020-03-03
Filing date: 2020-03-03
Publication date: 2021-01-08
Anticipated expiration: 2030-03-03

Abstract

The utility model discloses a planet wheel type two-gear gearbox based on pawl type overrunning clutch, the gearbox comprises an input shaft, a diaphragm spring clutch, a planet wheel type transmission mechanism, a pawl type overrunning clutch assembly and an output shaft, the pawl type overrunning clutch assembly realizes locking or overrunning through pawls which are arranged between an outer ring and an inner ring in pairs, the pawls are connected with a control ring at the axial outer side through pawl control pins, the control ring controls the pawl control pins to drive the pawls to swing up and down through control windows arranged on the control ring, and then bidirectional locking, unidirectional locking or bidirectional overrunning of the clutch is realized; the gearbox can realize the processes of first-gear advancing, second-gear advancing, first-gear backing and unpowered interrupted gear shifting. The utility model discloses realizing that one keeps off to advance and fall back and can carry out on the basis that unpowered interruption shifted, can also undertake great load, further promoted the effect of shifting.

Description

Planetary wheel type two-gear gearbox based on pawl type overrunning clutch

Technical Field

The utility model belongs to the technical field of electric vehicle transmission system, concretely relates to planetary wheel type two keep off gearbox based on pawl formula freewheel clutch.

Background

The patent application number is 2019103261167, the name is that the problem of traditional AMT power interruption of shifting has been solved to the technical scheme that provides in "planet wheel formula is unpowered to break off two-gear gearbox and shift control method" and can realize unpowered to break off and shift, the process gearbox of stepping up or stepping down has power output all the time, the ride comfort of the process of shifting is improved, can realize smooth speed ratio switching process can, and planet wheel formula is unpowered to break off two-gear gearbox can realize that one keeps off and go forward and one keeps off and go back, effectively solved and adopted two gears to reverse speed among the prior art and too fast and the safety problem that overrun clutch appears the jamming phenomenon.

However, the controllable overrunning clutch adopted in the technical scheme of the patent is a roller type overrunning clutch, the power transmitted by the roller type overrunning clutch is limited, and serious abrasion easily occurs when the load is too large, so that the phenomenon of slip failure occurs; in addition, the controllability of the roller in the roller-type overrunning clutch is low, and the control effect of the clutch is poor. Therefore, the transmission performance of the gearbox in the technical scheme of the patent is affected accordingly.

Disclosure of Invention

To the defect that exists among the above-mentioned prior art, the utility model discloses a planetary wheel type two keeps off gearbox based on pawl formula freewheel clutch realizes that one keeps off to go forward and reverse and can carry out the basis that unpowered interruption shifted, can also undertake great load, further promotes the effect of shifting. With the attached drawings, the technical scheme of the utility model is as follows:

planetary wheel type two-gear gearbox based on pawl type overrunning clutch comprises: the planetary gear type transmission mechanism comprises a planet carrier 5, a gear ring 7, a planet gear 8 and a sun gear 9, the diaphragm spring clutch 3 is mounted on the input shaft 2 coaxially and fixedly connected with the sun gear 9, a flywheel disc 38 of the diaphragm spring clutch 3 is coaxially connected with the gear ring 7, and the output shaft 10 is coaxially connected with the planet carrier 5;

the overrunning clutch assembly is a pawl type overrunning clutch assembly 6 and consists of a pawl type overrunning clutch and a clutch control mechanism;

the pawl type overrunning clutch consists of an outer ring 61, a control ring 62, a forward pawl 63, a reverse pawl 64 and an inner ring, wherein the outer ring 61 is fixed on the gearbox shell 4, the inner ring is positioned outside the gear ring 7 and is integrally arranged with the gear ring 7, the forward pawl 63 and the reverse pawl 64 are uniformly arranged in pairs in an annular space between the outer ring 61 and the inner ring, the pawl roots of the forward pawl 63 and the reverse pawl 64 are rotatably arranged on the outer ring 61, the pawl heads of the forward pawl 63 and the reverse pawl 64 are oppositely arranged and are clamped with pawl clamping grooves on the outer circular surface of the inner ring, folding pieces are respectively arranged between the forward pawl 63 and the reverse pawl 64 and the outer ring 61, the forward pawl 63 and the reverse pawl 64 are respectively connected with a forward control window 622 and a reverse control window 623 on the control ring 62 in a sliding manner through pawl control pin arranged on the axial side surface of the forward pawl 63 and the reverse pawl 64, and under the rotation, the forward pawl 63 and the reverse pawl 64 swing up and down to be clamped or separated with a pawl clamping groove on the outer circular surface of the inner ring, and then bidirectional locking, unidirectional locking or bidirectional overrunning between the gear ring 7 and the outer ring 61 is achieved.

The clutch control mechanism is composed of a control motor 65, a transmission shaft 66, a worm 57, a sensor 68 and a worm wheel 69, wherein the control motor 65 is coaxially and fixedly connected with one end of the transmission shaft 66, the sensor 68 is installed at the other end of the transmission shaft 66, the worm 57 is coaxially installed on the transmission shaft 66 and meshed with the worm wheel 69 coaxially fixed on the outer circumference of the control ring 62, and then the control ring 62 is controlled to rotate.

Further, on the control ring 62, the control surface at the bottom of the forward control window 622 is a forward control window inclined surface 624 and a forward control window plane 625 which are sequentially and continuously arranged along the rotation direction of the control ring 62, the control surface at the bottom of the reverse control window 623 is a reverse control window inclined surface 626 and a reverse control window inclined surface 627 which are sequentially and continuously arranged along the rotation direction of the control ring 62, wherein the forward control window inclined surface 624 and the reverse control window inclined surface 627 are both curved surfaces which gradually approach the circle center position of the control ring 62 along the rotation direction of the control ring 62, and the forward control window plane 625 and the reverse control window plane 626 are both curved surfaces which are concentrically arranged with the control ring 62.

Further, evenly open a plurality of pawl draw-in groove pairs along the circumferencial direction on the outer disc of inner circle, every group draw-in groove pair comprises two pawl draw-in grooves, two pawl draw-in grooves respectively with the pawl head phase-match of forward pawl 63 and reverse pawl 64, when the draw-in groove of inner circle to arbitrary a set of pawl pair department, forward pawl 63 and reverse pawl 64 all can be including the pawl draw-in groove that the outer disc of inner circle corresponds to find the pawl draw-in groove of phase-match joint with it inwards.

Further, the inner side wall of the outer ring 61 is provided with a plurality of sets of pawl installation grooves corresponding to the forward pawls 63 and the reverse pawls 64 one to one, and each pawl installation groove in the pawl installation groove pair is provided with a folding spring installation groove.

Further, the diaphragm spring clutch 3 release bearing 31, the diaphragm spring 32, the spring support ring 33, the clutch cover 34, the pressure plate 35, the friction plate 36 and the flywheel disc 38 are sequentially arranged from front to back;

the flywheel disc 38 is coaxially connected with the connecting end of the gear ring 7 through a spline 39, the friction plate 36 is coaxially and fixedly connected on the input shaft 2, the pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 covers the pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly installed on the front end surface of the flywheel disc 38 through a bolt 37, the spring support ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and installed on the clutch cover 34 through the spring support ring 33, the front end of the diaphragm spring 32 is in contact connection with the release bearing 31, and the rear end of the diaphragm spring 32 is in contact connection with the pressure plate 35.

Furthermore, one end of the planet carrier 5 is coaxially sleeved on the input shaft 2 in a hollow manner, and the other end of the planet carrier 5 is coaxially and fixedly connected with the output shaft 10; the planet wheel 8 is arranged on the planet carrier 5 in an empty sleeve mode, one side of the planet wheel 8 is meshed with the outer side of the sun wheel 9, and the other side of the planet wheel 8 is meshed with the inner side of the gear ring 7.

Compared with the prior art, the beneficial effects of the utility model reside in that:

1. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the pawl type overrunning clutch is adopted, so that larger load can be borne, and larger power transmission is realized;

2. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, a planetary wheel type transmission structure is adopted and matched with the pawl type overrunning clutch, the unpowered interruption transmission process is smoother, and the gear shifting effect is further improved;

3. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the adopted pawl type overrunning clutch can effectively reduce abrasion, and the working process is more accurate and reliable;

4. in the planetary wheel type two-gear gearbox based on pawl type overrunning clutch, the pawl type overrunning clutch of the adoption drives the pawl to lift through the control window on the control ring, so that the pawl lifting process is more stable and the position is more accurate, and the clutch is placed to generate noise.

4. In the planet wheel type two-gear gearbox based on the pawl type overrunning clutch, the control ring of the worm and gear type control mechanism control clutch is adopted to rotate, the transmission ratio is increased, the control is more accurate, the self-locking effect is also achieved, and the control ring is prevented from shifting.

Drawings

Fig. 1 is a schematic structural diagram of the planetary gear type two-gear transmission of the present invention in a first gear state;

fig. 2 is a schematic structural diagram of the planetary gear type two-gear transmission of the present invention in a two-gear state;

fig. 3 is a schematic structural diagram of a diaphragm spring clutch in the planetary gear type two-gear transmission of the present invention;

fig. 4 is a front view of a pawl type overrunning clutch assembly in the planetary gear type two-speed transmission according to the present invention;

fig. 5 is a top view of a pawl type overrunning clutch assembly in the planetary gear type two-speed transmission according to the present invention;

fig. 6 is an exploded view of a pawl type overrunning clutch in the planetary gear type two-gear transmission according to the present invention;

fig. 7 is a schematic diagram of a control ring structure of a pawl type overrunning clutch in the planetary gear type two-gear transmission according to the present invention;

fig. 8 is a schematic diagram of a bidirectional locking state of a pawl type overrunning clutch in the planetary gear type two-gear transmission according to the present invention;

fig. 9 is a schematic diagram of a one-way overrunning state of a pawl type overrunning clutch in the planetary gear type two-gear transmission according to the present invention;

fig. 10 is a schematic diagram of a bidirectional overrunning state of a pawl type overrunning clutch in the planetary gear type two-gear transmission according to the present invention;

in the figure:

1 driving motor, 2 input shafts, 3 diaphragm spring clutches, 4 gearbox shells,

5 planet carriers, 6 pawl type overrunning clutch assemblies, 7 gear rings, 8 planet wheels,

9 sun gear, 10 output shaft;

31 release bearing, 32 diaphragm spring, 33 spring support ring, 34 clutch housing

35 pressure plates, 36 friction plates, 37 bolts, 38 flywheel plates,

39 splines;

61 outer race, 62 control ring, 63 forward pawl, 64 reverse pawl,

65 control motor, 66 drive shaft, 67 worm, 68 sensor,

69 a worm gear;

621 control ring body, 622 forward control window, 623 reverse control window, 624 forward control window ramp,

625 positive control window plane, 626 negative control window plane, 627 negative control window slope, 628 worm link plate.

Detailed Description

For clear and complete description of the technical solution and the specific working process of the present invention, the following embodiments are provided in conjunction with the accompanying drawings of the specification:

as shown in fig. 1, the utility model discloses a planetary gear type two keep off gearbox based on pawl formula freewheel clutch, the gearbox comprises input shaft 2, diaphragm spring clutch 3, gearbox casing 4, planet carrier 5, pawl formula freewheel clutch assembly 6, ring gear 7, planet wheel 8, sun gear 9 and output wheel 10. One end of the input shaft 2 is coaxially and fixedly connected with the output end of the driving motor 1, and the other end of the input shaft 2 penetrates through the gearbox shell 4 to be coaxially and fixedly connected with a sun wheel 9 in the gearbox shell 4; the diaphragm spring clutch 3 is coaxially arranged on the input shaft 2, wherein a friction plate 36 in the diaphragm spring clutch 3 is coaxially and fixedly connected with the input shaft 2, and a connecting end of a flywheel disc 37 in the diaphragm spring clutch 3 is sleeved on the input shaft 2 in a hollow manner and is coaxially and fixedly connected with a gear ring 7 in the gearbox shell 4; one end of the planet carrier 5 is coaxially sleeved on the input shaft 2 in a hollow manner, and the other end of the planet carrier 5 is coaxially and fixedly connected with the output shaft 10; the planet wheel 8 is arranged on the planet carrier 5 in an empty sleeve mode, one side of the planet wheel 8 is meshed with the outer side of the sun wheel 9, and the other side of the planet wheel 8 is meshed with the inner side of the gear ring 7; the planet carrier 5, the gear ring 7, the planet wheel 8 and the sun wheel 9 form a planet wheel type transmission mechanism; in the pawl type overrunning clutch assembly 6, the outer ring of the pawl type overrunning clutch is fixed on the inner side wall of the gearbox shell 4, the inner ring of the pawl type overrunning clutch is coaxially arranged on the outer side wall of the gear ring 7 and is fixedly connected with the outer side wall to form an integrated structure, and therefore the inner ring of the pawl type overrunning clutch is the gear ring 7.

As shown in fig. 1 and 3, the diaphragm spring clutch 3 release bearing 31, the diaphragm spring 32, the spring support ring 33, the clutch cover 34, the pressure plate 35, the friction plate 36 and the flywheel disc 38 are sequentially arranged from front to back. The flywheel disc 38 is coaxially connected with the connecting end of the gear ring 7 through a spline 39, the friction plate 36 is coaxially and fixedly connected on the input shaft 2, the pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 covers the pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly installed on the front end surface of the flywheel disc 38 through a bolt 37, the spring support ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and installed on the clutch cover 34 through the spring support ring 33, the front end of the diaphragm spring 32 is in contact connection with the release bearing 31, and the rear end of the diaphragm spring 32 is in contact connection with the pressure plate 35.

The diaphragm spring clutch 3 has two working states:

1. when the release bearing 31 moves backward along the axial direction of the input shaft 2 under the action of an external force, under the pushing action of the release bearing 31, the release finger end of the diaphragm spring 32 moves backward along the axial direction of the input shaft 2, so that the diaphragm spring 32 is gradually compressed, under the supporting action of the spring support ring 33, the pressure plate end of the diaphragm spring 32 drives the pressure plate 35 to be away from the surface of the friction plate 36, so that the pressure plate 35 is separated from the friction plate 36, the flywheel disc 38 is also separated from the friction plate 36, no torque is transmitted between the friction plate 36 and the clutch flywheel disc 38, and the diaphragm spring clutch 3 is in a release state at this time.

2. When the release bearing 31 moves forward along the axial direction of the input shaft 2 under the action of external force, the diaphragm spring 32 moves forward along the axial direction of the input shaft 2 under the action of restoring force, so that the diaphragm spring 32 gradually extends, under the supporting action of the spring supporting ring 33, the pressure plate 35 is driven by the pressure plate end of the diaphragm spring 32 to press the friction plate 36 on the flywheel disc 38, so that torque is transmitted between the friction plate 36 and the flywheel disc 38, and at the moment, the diaphragm spring clutch 3 is in a combined state.

The pawl type overrunning clutch assembly 6 consists of a pawl type overrunning clutch and a clutch control mechanism.

As shown in fig. 4 and 6, the pawl type overrunning clutch includes: an outer ring 61, a control ring 62, a forward pawl 63, a reverse pawl 64, and a ring gear 7 (inner ring); the gear ring 7 is coaxially arranged on the inner side of the outer ring 61, the forward pawl 63 and the reverse pawl 64 are arranged in an annular gap between the outer ring 61 and the gear ring 7, the control ring 62 is arranged on the axial outer side of the gear ring 7 and is in matched connection with the forward pawl 63 and the reverse pawl 64 so as to control the forward pawl 63 and the reverse pawl 64 to swing up and down, and the snap springs are respectively arranged at two axial ends of the outer ring 61 so as to realize axial limiting of components in the outer ring 61.

As shown in fig. 6 and 8, the forward pawls 63 and the reverse pawls 64 are arranged in pairs between the outer ring 61 and the ring gear 7, in the present embodiment, there are six sets of pairs of the forward pawls 63 and the reverse pawls 64 uniformly distributed in the annular space between the outer ring 61 and the ring gear 7, and the structures of the forward pawls 63 and the reverse pawls 64 are identical.

As shown in fig. 8, the forward pawls 63 and the reverse pawls 64 are symmetrically mounted with respect to the radial direction of the outer ring 61 and the ring gear 7 such that the forward pawls 63 and the reverse pawls 64 are arranged in reverse; the pawl roots of the forward pawl 63 and the reverse pawl 64 are both arranged in pawl mounting grooves in the inner side wall of the outer ring 61, and the pawl heads of the forward pawl 63 and the reverse pawl 64 are matched and clamped with a pawl clamping groove closed on the outer circumference of the gear ring 7; folding springs are arranged between the forward pawl 63 and the reverse pawl 64 and the inner side wall of the outer ring 61; and pawl control pins are arranged on the axial outer sides of the forward pawls 63 and the reverse pawls 64 and are connected in a control window of the control ring 62 in a sliding manner, and the control ring 62 controls the swinging of the forward pawls 63 and the reverse pawls 64 through the matching of the control window and the pawl control pins.

As shown in fig. 7 and 8, the control ring main body 621 of the control ring 62 is an annular plate structure, six groups of control window pairs are opened on the control ring main body 621, the six groups of control window pairs respectively correspond to six groups of pawl pairs composed of forward pawls 63 and reverse pawls 64 one by one, each group of control window pairs is composed of a forward control window 622 and a reverse control window 623, the forward control window 622 is connected with a pawl control pin of the forward pawl 63 in a matching manner, and the reverse control window 623 is connected with a pawl control pin of the reverse pawl 64 in a matching manner; the matching connection of the control window and the pawl control pin means that: the pawl control pin is inserted into the control window, is connected with the control surface at the bottom of the control window, and controls the pawl control pin to move through the control surface at the bottom of the control window in the process of abutting against the control surface at the bottom of the control window, so that the pawl control pin is lifted, and the corresponding pawl is controlled by the pawl control pin to swing up and down, therefore, the swing mode of the pawl depends on the design of the control surface at the bottom of the control window, and the shape of the corresponding control surface can be designed to realize different working modes according to the actual working condition; in this embodiment, as shown in fig. 8, 9 and 10, the control ring 62 rotates clockwise relative to the forward pawls 63 and the reverse pawls 64 distributed in a ring shape, and further controls the corresponding pawls to swing through the pawl control pins, and accordingly, the swinging manner of the forward pawls 63 and the reverse pawls 64 is designed as follows: firstly: the forward pawl 5 and the reverse pawl 6 are both at the initial positions of the corresponding control windows, namely the lowest positions; then: the forward pawl 5 is kept at the lowest position and the reverse pawl 6 is gradually lifted to the highest position, and at the moment, the forward pawl 5 and the reverse pawl 6 are located at the middle positions of the corresponding control windows; and finally: the forward pawl 63 is gradually raised to the uppermost position and the reverse pawl 64 is held at the uppermost position, at which time the forward pawl 63 and the reverse pawl 64 are both at the end positions of the corresponding control windows. In match, the control window pair on the control ring has the following structure:

as shown in fig. 7, the control ring main body 621 of the control ring 62 is provided with six groups of control window pairs, the six groups of control window pairs are respectively in one-to-one correspondence with the six groups of pawl pairs formed by the forward pawls 63 and the reverse pawls 64, each group of control window pairs is formed by a forward control window 622 and a reverse control window 623, the forward control window 622 is in fit connection with the pawl control pin of the forward pawl 63, and the reverse control window 623 is in fit connection with the pawl control pin of the reverse pawl 64; the control surface at the bottom of the forward control window 622 comprises a forward control window inclined plane 624 and a forward control window plane 625 which are sequentially arranged clockwise (namely, the same rotation direction as the control ring 62), the forward control window inclined plane 624 and the reverse control window plane 625 are continuous without blocking, wherein the forward control window inclined plane 624 is an arc surface which is gradually far away from the circle center position of the control ring 62 anticlockwise (namely, opposite to the rotation direction of the control ring 62), and the forward control window plane 625 is an arc surface which is concentrically arranged with the control ring 62; the control surface at the bottom of the reverse control window 623 comprises a reverse control window plane 626 and a reverse control window inclined plane 627 which are sequentially arranged clockwise (i.e. the same rotation direction as the control ring 62), and the reverse control window plane 626 and the reverse control window inclined plane 627 are continuous without blocking, wherein the reverse control window plane 626 is an arc surface which is concentrically arranged with the control ring 62, and the reverse control window inclined plane 627 is an arc surface which is gradually away from the center position of the control ring 62 counterclockwise (i.e. the opposite rotation direction of the control ring 62). The forward control window ramp 624 and the reverse control window ramp 626 are the same length, and the forward control window ramp 625 and the reverse control window ramp 627 are the same length.

Similarly, when the pawl control pin of the reverse pawl 64 is inserted into the reverse control window 623, the pawl control pin of the reverse pawl 64 is always pressed against the control surface of the reverse control window 623 under the elastic force of the correspondingly installed flap spring, and when the pawl control pin of the forward pawl 63 is inserted into the reverse control window 623, the pawl control pin of the reverse pawl 64 is always pressed against the control surface of the forward control window 623 under the elastic force of the correspondingly installed flap spring.

Furthermore, a worm wheel attachment plate 628 is provided radially outside the control ring 62 for fixedly mounting a worm wheel 69 of the clutch control mechanism.

The pawl type overrunning clutch has three working states:

1. as shown in fig. 7 and 8, when the forward pawl 63 is located at the initial position of the forward control window 622 and the pawl control pin of the reverse pawl 64 is located at the initial position of the reverse control window 623, the pawl heads of the forward pawl 63 and the reverse pawl 64 are located at the lowest positions and respectively engaged with the pawl grooves on the outer circumferential surface of the ring gear 7; because the forward pawl 63 and the reverse pawl 64 are arranged in the opposite direction, under the clamping action of the forward pawl 63 and the reverse pawl 64, the outer ring 61 and the gear ring 7 are locked in both clockwise and counterclockwise directions, namely, in a bidirectional locking manner, and power transmission can be realized in both clockwise and counterclockwise directions of the outer ring 61 and the gear ring 7.

2. As the control ring 62 rotates clockwise, as shown in fig. 7 and 9, the pawl control pin of the forward pawl 63 moves under the action of the forward control window plane 625 of the control ring 62, since the forward control window plane 625 is coaxially disposed with the control ring 62, the pawl control pin of the forward pawl 63 does not move in the radial direction of the control ring 62, so that the forward pawl 63 is always held at the lowest position (i.e., the position closest to the center of the control ring 62), at the same time, the pawl control pin of the reverse pawl 64 is moved by the reverse control window ramp 627 of the control ring 62, since the reverse control window inclined plane 627 is gradually away from the center of the control ring 62 in the counterclockwise direction, as the control ring 62 rotates clockwise, the pawl control pin of the reverse pawl 64 is gradually away from the center of the control ring 62 in the radial direction of the control ring 62, and the reverse pawl 64 is gradually lifted under the driving of the pawl control pin of the reverse pawl 64; when the pawl control pin of the forward pawl 63 is located at the boundary between the forward control window plane 206 and the forward control window inclined plane, i.e., at the middle position of the forward control window 622, the forward pawl 63 is still at the lowest position, i.e., the forward pawl 63 still remains in clamping connection with the pawl slot on the outer circumferential surface of the gear ring 7, and at this time, the pawl control pin of the reverse pawl 64 is located at the boundary between the reverse control window inclined plane 627 and the reverse control window plane 626, i.e., at the middle position of the reverse control window 623, at this time, the reverse pawl 64 rises to the highest position (i.e., at the position farthest from the center of the control ring), i.e., the reverse pawl 64 disengages from the pawl slot on the outer; at this time, the gear ring 7 is locked in the clockwise direction relative to the outer ring 61 and can rotate freely in the counterclockwise direction, and at this time, the clockwise rotation of the gear ring 7 relative to the outer ring 61 can transmit power, and the counterclockwise rotation can not transmit power, i.e. one-way overrunning.

3. As shown in fig. 7 and 10, as the control ring 62 rotates clockwise, the pawl control pin of the forward pawl 63 starts to move under the action of the forward control window inclined plane 624 of the control ring 62, because the forward control window inclined plane 624 gradually moves away from the center of the control ring 62 counterclockwise, as the control ring 62 continues to rotate clockwise, the pawl control pin of the forward pawl 63 gradually moves away from the center of the control ring 62 along the radial direction of the control ring 62, and the forward pawl 63 is gradually lifted up under the driving of the pawl control pin of the forward pawl 63 until the leftmost end of the forward control window inclined plane 624, i.e. the end position of the forward control window 622, at which time the forward pawl 63 is lifted to the highest position (i.e. the position farthest from the center of the control ring), at which time the forward pawl 63 is disengaged from the pawl catching groove on the outer circumferential surface of the control ring 7; meanwhile, the pawl control pin of the reverse pawl 64 moves to the end position of the forward control window 622 under the action of the reverse control window plane 626 of the control ring 62, and because the reverse control window plane 626 is coaxially arranged with the control ring 62, the pawl control pin of the reverse pawl 64 does not move along the radial direction of the control ring 62, and the reverse pawl 64 is kept at the highest position, namely, the forward pawl 63 and the reverse pawl 64 are separated from the pawl clamping groove on the outer circumferential surface of the gear ring 7; at this time, the forward pawls 63 and the reverse pawls 64 are disengaged from the pawl slots on the outer circumferential surface of the gear ring 7, so that the gear ring 7 can freely rotate in both the clockwise direction and the counterclockwise direction relative to the outer ring 61, and no power transmission, that is, bidirectional overrunning, is performed between the gear ring 7 and the outer ring 61 in both the clockwise direction and the counterclockwise direction.

As shown in fig. 4 and 5, the clutch control mechanism is composed of a control motor 65, a transmission shaft 66, a worm 67, a sensor 68, and a worm wheel 69; the output end of the control motor 65 is coaxially and fixedly connected with one end of the transmission shaft 66, the worm 67 is coaxially fixed on the shaft diameter of the transmission shaft 66, the sensor 68 is arranged at the other end of the transmission shaft 66, and the rotation angle of the transmission shaft 66 is detected through the sensor 68 so as to obtain the rotation angle of the worm 67; the worm wheel 69 is coaxially arranged on the radial outer side of the control ring 62 through the worm connecting plate 28, and the worm wheel 69 is meshed with the worm 67 to form a worm-gear transmission pair.

Under the drive of the control motor 65, the worm 67 rotates synchronously with the transmission shaft 66 and drives the worm wheel 69 fixedly connected with the control ring 62 to rotate, the control ring 62 controls the corresponding forward pawl 63 and the reverse pawl 64 to swing up and down, and then the control of the pawl type overrunning clutch is realized, in the process, the sensor 68 detects the rotation angle of the worm 67, and then judges the angle of the worm wheel 69 driving the control ring 62 to rotate, and further judges the movement positions of pawl control pins of the forward pawl 63 and the reverse pawl 64 on the corresponding control surface, and finally the accurate control of the locking or overrunning of the clutch is realized.

The specific working process of the planetary gear type two-gear transmission based on the pawl type overrunning clutch comprises the following steps: first gear forward, second gear forward, first gear reverse and no power interruption gear shifting.

The specific process of the first gear advancing is as follows:

when the vehicle moves forward in the first gear, the diaphragm spring clutch 3 is controlled by the clutch actuator to be in a separated state, and at the same time, the clutch control mechanism in the pawl type overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl type overrunning clutch to rotate, so that a forward pawl 63 moves along a forward control window 622 and keeps clamped with a clamping groove on the outer circumferential surface of a gear ring 7, a reverse pawl 64 moves along a reverse control window 623 and is separated from the clamping groove on the outer circumferential surface of the gear ring 7, at the moment, the clutch control mechanism stops operating, as shown in fig. 9, at the moment, the gear ring 7 rotates and is locked in a reverse direction (namely clockwise direction in fig. 8) relative to an outer ring 61, an input shaft 2 rotates in the forward direction under the driving of a motor 1, a sun gear 9 coaxially connected to the input shaft 2 rotates synchronously in the forward direction, and the sun gear 9 drives a planet gear, the gear ring 7 is caused to generate a trend of rotating reversely along the axis, because the gear ring 7 and the outer ring 61 are locked relatively at the moment, and the outer ring 61 is fixed on the gearbox shell 4, the gear ring 7 is fixed at the moment, according to the transmission characteristic of the planetary gear type transmission mechanism, the planetary gear 8 revolves along the sun gear 9 in the positive direction at the moment, the planetary gear carrier 5 is further driven to rotate in the positive direction synchronously, and finally, power is output outwards through the output shaft 10 to realize forward movement in a first gear;

secondly, the specific process of the second gear advancing is as follows:

when the vehicle advances in the second gear, the clutch actuator controls the diaphragm spring clutch 3 to be in the engaged state, and at the same time, the clutch control mechanism in the pawl type overrunning clutch assembly is started, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl type overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and is disengaged from the clamping groove on the outer circumferential surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and is disengaged from the clamping groove on the outer circumferential surface of the gear ring 7, at this time, the clutch control mechanism stops operating, as shown in fig. 10, at this time, the gear ring 7 can freely rotate in both directions relative to the outer ring 61, and the input shaft 2 rotates in the forward direction under the driving of the motor 1, on the one hand: the sun gear 9 coaxially connected with the input shaft 2 rotates in the positive direction, and on the other hand: under the combined driving of the diaphragm spring clutch 3, the gear ring 7 and the input shaft 2 synchronously rotate in the positive direction, so that at the moment, the whole planetary gear type transmission mechanism consisting of the planet carrier 5, the gear ring 7, the planet gear 8 and the sun gear 9 rotates in the positive direction, the planet carrier 5 drives the output shaft 10 to synchronously rotate in the positive direction, and finally, power is output outwards through the output shaft 10 to realize secondary forward movement;

thirdly, the specific process of the first gear reversing is as follows:

when the vehicle is in first gear and backs up, the diaphragm spring clutch 3 is controlled by the clutch actuator to be in a separated state, and at the same time, the clutch control mechanism in the pawl type overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl type overrunning clutch to rotate, so that a forward pawl 63 moves along a forward control window 622 and keeps clamped with a clamping groove on the outer circumferential surface of the gear ring 7, a reverse pawl 64 moves along a reverse control window 623 and keeps clamped with a clamping groove on the outer circumferential surface of the gear ring 7, at the moment, the clutch control mechanism stops operating, as shown in fig. 8, at the moment, the gear ring 7 is locked relative to the outer ring 61 in bidirectional rotation, the input shaft 2 is driven by the motor 1 to rotate in reverse direction, a sun gear 9 coaxially connected to the input shaft 2 in synchronous and reverse rotation, the sun gear 9 drives the planet gear 8 to rotate in forward direction, the gear ring 7 is enabled to generate a trend of rotating in the positive direction along the axis, because the gear ring 7 and the outer ring 61 are locked relatively at the moment, and the outer ring 61 is fixed on the gearbox shell 4, the gear ring 7 is fixed at the moment, according to the transmission characteristic of the planetary gear type transmission mechanism, the planetary gear 8 revolves along the sun gear 9 in the reverse direction at the moment, the planetary carrier 5 is further driven to rotate in the reverse direction synchronously, and finally, power is output outwards through the output shaft 10 to realize one-gear reversing;

the unpowered interrupted gear shifting comprises a first gear ascending process and a second gear descending process;

1. the first gear and the second gear are specifically lifted as follows:

when the first gear is shifted up to the second gear, the clutch actuator controls the diaphragm spring clutch 3 to be gradually combined, meanwhile, the clutch control mechanism in the pawl type overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl type overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622, the forward pawl 63 gradually moves from being clamped with the clamping groove on the outer circumferential surface of the gear ring 7 to being separated from the clamping groove on the outer circumferential surface of the gear ring 7, and the reverse pawl 64 moves along the reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7; in the process, the power transmitted by the input shaft 2 to the gear ring 7 through the diaphragm spring clutch 3 is gradually increased, along with the combination, the power input through the input shaft 2 is transmitted by the sun gear 9 when the input shaft advances from the first gear, and is gradually transmitted to the gear ring 7 and the sun gear 9 when the input shaft advances from the second gear, along with the gradual increase of the rotation speed of the planet carrier 5, the revolution speed of the planet carrier 5 driving the downstream planet gear 8 is gradually the same as the rotation speed of the sun gear 9, so that the meshing force between the planet gear 8 and the sun gear 9 is reduced, the power transmitted by the sun gear 9 to the planet gear 8 is reduced, the rotation speed of the planet gear 8 along the axis is gradually reduced to zero, at the moment, the forward pawl 63 and the reverse pawl 64 in the pawl overrunning clutch are separated from the clamping grooves on the outer circumferential surface of the gear 7, the gear ring 7 can freely rotate relative to the outer ring 61, and at the moment, the whole planetary gear transmission mechanism, therefore, the gear ring 7 also rotates forwards, power is transmitted through the diaphragm spring clutch 3 after being input through the input shaft 2, then is transmitted to the planet carrier 5 through the gear ring 7 and then is transmitted to the output shaft 10, finally, the power is output outwards through the output shaft 10 to realize first gear and second gear shifting, and the whole shifting process is free of power interruption;

2. the process of the first gear reduction of the second gear is as follows:

when the second gear is shifted down to the first gear, the clutch actuator controls the diaphragm spring clutch 3 to gradually separate, and meanwhile, the clutch control mechanism in the pawl type overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl type overrunning clutch to rotate reversely, so that the forward pawl 63 moves along the forward control window 622, the forward pawl 63 gradually moves from being separated from a clamping groove on the outer circumferential surface of the gear ring 7 to being clamped with a clamping groove on the outer circumferential surface of the gear ring 7, and the reverse pawl 64 moves along the reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7 until the gear ring 7 freely rotates in the forward direction (anticlockwise direction in the figure) relative to the outer ring 61 and is reversely locked; in the process, the power transmitted by the input shaft 2 to the gear ring 7 through the diaphragm spring clutch 3 is gradually reduced, the power of the planet carrier 5 is gradually smaller than the resistance force applied by the planet carrier 5, the rotating speed of the planet carrier 5 is gradually reduced, the power input through the input shaft 2 is transmitted downwards from the planet carrier 5 when the second gear advances, the power is gradually transmitted downwards from the sun gear 9 when the first gear advances, namely, the power is gradually transferred to the sun gear 9 from the planet carrier 5, in the planetary gear type transmission mechanism, the planet gear 8 starts to restore the reverse rotation along the self axis along the rotating speed of the planet gear 8, the meshing force between the sun gear 9 and the planet gear 8 is gradually increased, the power is transmitted downwards from the planet gear 8, meanwhile, the rotating speed of the gear ring 7 is gradually reduced until the reverse rotation is locked, and the power is transmitted to the output shaft 10 through the sun gear 9, the planet gear 8 and the planet carrier 5 in sequence after being input through, finally, the power is output outwards through the output shaft 10 to realize the forward movement of the first gear, namely the process of descending the second gear and the first gear is realized, and the whole gear ascending process is free from power interruption.

Claims

1. Planetary wheel type two-gear gearbox based on pawl type overrunning clutch comprises: input shaft (2), diaphragm spring clutch (3), planet wheel formula drive mechanism, freewheel clutch assembly and output shaft (10), wherein, planet wheel formula drive mechanism comprises planet carrier (5), ring gear (7), planet wheel (8) and sun gear (9), its characterized in that:

the diaphragm spring clutch (3) is arranged on the input shaft (2) coaxially and fixedly connected with the sun gear (9), a flywheel disc (38) of the diaphragm spring clutch (3) is coaxially connected with the gear ring (7), and the output shaft (10) is coaxially connected with the planet carrier (5);

the overrunning clutch assembly is a pawl type overrunning clutch assembly (6) and consists of a pawl type overrunning clutch and a clutch control mechanism;

the pawl type overrunning clutch is composed of an outer ring (61), a control ring (62), a forward pawl (63), a reverse pawl (64) and an inner ring, wherein the outer ring (61) is fixed on a gearbox shell (4), the inner ring is positioned on the outer side of a gear ring (7) and is integrally arranged with the gear ring (7), the forward pawl (63) and the reverse pawl (64) are uniformly arranged in an annular space between the outer ring (61) and the inner ring in pairs, pawl roots of the forward pawl (63) and the reverse pawl (64) are rotatably arranged on the outer ring (61), pawl heads of the forward pawl (63) and the reverse pawl (64) are oppositely arranged and are clamped with pawl clamping grooves on the outer circular surface of the inner ring, folding springs are respectively arranged between the forward pawl (63) and the reverse pawl (64) and the outer ring (61), and the forward pawl (63) and the reverse pawl (64) are respectively connected with a forward control window (622) and a reverse control window (64) on the control ring (62) through pawl control pins arranged on the axial side surfaces of the The window making (623) is in sliding connection, and under the rotation control of the control ring (62), the forward pawl (63) and the reverse pawl (64) swing up and down to realize clamping connection or separation with a pawl clamping groove on the outer circular surface of the inner ring, so that bidirectional locking, unidirectional locking or bidirectional overrunning between the gear ring (7) and the outer ring (61) is realized;

the clutch control mechanism is composed of a control motor (65), a transmission shaft (66), a worm (57), a sensor (68) and a worm wheel (69), wherein the control motor (65) is coaxially and fixedly connected with one end of the transmission shaft (66), the sensor (68) is installed at the other end of the transmission shaft (66), the worm (57) is coaxially installed on the transmission shaft (66) and meshed with the worm wheel (69) coaxially fixed on the outer circumference of the control ring (62), and then the control ring (62) is controlled to rotate.

2. A planetary gear type two-gear gearbox based on a pawl type overrunning clutch according to claim 1, characterized in that:

on control ring (62), the control surface of forward control window (622) bottom is forward control window inclined plane (624) and forward control window plane (625) that set up in proper order in succession along control ring (62) direction of rotation, and the control surface of reverse control window (623) bottom is reverse control window plane (626) and reverse control window inclined plane (627) that set up in succession in proper order along control ring (62) direction of rotation, and wherein, forward control window inclined plane (624) and reverse control window inclined plane (627) are the curved surface that is close to control ring (62) centre of a circle position gradually along control ring (62) direction of rotation, and forward control window plane (625) and reverse control window plane (626) are the curved surface that sets up with control ring (62) concentric.

3. A planetary gear type two-gear gearbox based on a pawl type overrunning clutch according to claim 1, characterized in that:

the outer disc of inner circle is evenly opened along the circumferencial direction has a plurality of pawl draw-in groove pairs, and every group draw-in groove pair comprises two pawl draw-in grooves, two pawl draw-in grooves respectively with the pawl head phase-match of forward pawl (63) and reverse pawl (64), when the draw-in groove of inner circle pair department to arbitrary a set of pawl, forward pawl (63) and reverse pawl (64) homoenergetic can be at the pawl draw-in groove that the outer disc of inner circle corresponds to find the pawl draw-in groove of phase-match joint with it inwards.

4. A planetary gear type two-gear gearbox based on a pawl type overrunning clutch according to claim 1, characterized in that:

the inner side wall of the outer ring (61) is provided with a plurality of groups of pawl mounting grooves which correspond to the forward pawls (63) and the reverse pawls (64) one to one, and each pawl mounting groove in the pawl mounting groove pair is provided with a folding spring mounting groove.

5. A planetary gear type two-gear gearbox based on a pawl type overrunning clutch according to claim 1, characterized in that:

the diaphragm spring clutch (3) is characterized in that a release bearing (31), a diaphragm spring (32), a spring support ring (33), a clutch cover (34), a pressure plate (35), a friction plate (36) and a flywheel disc (38) are sequentially arranged from front to back;

flywheel dish (38) pass through spline (39) and the link coaxial coupling of ring gear (7), friction disc (36) coaxial fixed connection is on input shaft (2), pressure disk (35) coaxial setting is in the front end of friction disc (36), clutch cover (34) cover is put in pressure disk (35) and friction disc (36) outside, and clutch cover (34) pass through bolt (37) coaxial fixed mounting on the preceding terminal surface of flywheel dish (38), spring support circle (33) are fixed on clutch cover (34), diaphragm spring (32) pass through spring support circle (33) support mounting on clutch cover (34), diaphragm spring (32) front end and release bearing (31) contact link to each other, diaphragm spring (32) rear end and pressure disk (35) contact link to each other.

6. A planetary gear type two-gear gearbox based on a pawl type overrunning clutch according to claim 1, characterized in that:

one end of the planet carrier (5) is coaxially sleeved on the input shaft (2) in a hollow manner, and the other end of the planet carrier (5) is coaxially and fixedly connected with the output shaft (10); the planet wheel (8) is mounted on the planet carrier (5) in an empty sleeve mode, one side of the planet wheel (8) is meshed with the outer side of the sun wheel (9), and the other side of the planet wheel (8) is meshed with the inner side of the gear ring (7).