CN210034309U - Planetary wheel type unpowered interruption two-gear transmission - Google Patents
Planetary wheel type unpowered interruption two-gear transmission Download PDFInfo
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- CN210034309U CN210034309U CN201920552949.0U CN201920552949U CN210034309U CN 210034309 U CN210034309 U CN 210034309U CN 201920552949 U CN201920552949 U CN 201920552949U CN 210034309 U CN210034309 U CN 210034309U
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Abstract
The utility model discloses a two gearboxes that keep off of planetary wheel type unpowered interruption, in the gearbox, the sun gear is coaxial to be linked firmly on the input shaft, the planet wheel is rotatory to be installed on the planet carrier, the planet wheel meshes with sun gear and ring gear mutually simultaneously, diaphragm spring clutch and input shaft are connected, the friction disc links firmly on the input shaft, clutch flywheel dish links firmly with the one end of planet carrier, the planet carrier other end links firmly with the output shaft, controllable formula freewheel clutch's inner circle is fixed in the circumference outside of ring gear, the outer lane is fixed on the inside wall of casing. The gearbox can realize first-gear forward, second-gear forward, first-gear reverse, unpowered interrupted gear shifting and brake energy recovery control. The utility model provides a keep off the gear and reverse a car the speed too fast and freewheel clutch the safety problem of jamming phenomenon appears, reduced the space size of gearbox, reduced the quality of gearbox to can keep off operating condition at the vehicle and carry out effectual braking energy recovery down.
Description
Technical Field
The utility model belongs to the technical field of electric vehicle transmission system, concretely relates to planet wheel type is unpowered to be interrupted two and is kept off gearbox.
Background
The reduction of dependence on petroleum is an important direction in the development of the modern automotive industry. In recent two years, the development of pure electric vehicles in China is rapid, and various types of pure electric vehicles are released in the market by various enterprises and enter industrialization.
The pure electric automobile has a plurality of driving mechanisms, for example, a gearless motor direct-drive scheme is adopted, namely, a motor directly drives wheels through a speed reducing device with a fixed speed ratio, the transmission mode has good smoothness, but the requirements on the performance of a motor battery are high, and the vehicle dynamic performance is poor. The transmission scheme of the motor and the gearbox greatly reduces the requirement of the vehicle on a motor battery, improves the low-speed climbing capacity and the high-speed running capacity of the vehicle, and improves the running efficiency of the motor.
Unlike internal combustion engines, electric motors do not place much demand on the number of transmission gears, but place high demands on transmission efficiency and shifting comfort of the transmission. At present, the variable-speed transmission schemes without gear shifting power interruption comprise a Continuously Variable Transmission (CVT), a dual-clutch automatic transmission (DCT) and the like, and wet clutches or transmission belts are adopted in the schemes, so that the cost is high, and the transmission efficiency is low. The AMT has the advantage of high transmission efficiency, but the traditional gear shifting process of the automatic electric-control mechanical transmission has power interruption, so that the running smoothness of a vehicle is influenced. In addition, the operating mechanism of the conventional mechanical automatic transmission includes a shift fork and a shift fork shaft, which increases the size of the transmission and increases the cost. It is very necessary to develop a special simple and efficient power-interruption-free gear shifting gearbox specially applied to an electric vehicle.
Patent CN105864372A proposes a planetary gear type two-gear transmission, which can only reverse gear at the second gear, and because the ratio of the second gear is larger, the defects of too fast driving speed of reverse gear of vehicle and insufficient power exist; in addition, when the reverse gear is carried out through the two-gear, the jamming phenomenon easily occurs to the first-gear overrunning clutch.
Patent CN107489741A proposes a parallel shaft type two-gear transmission, which has large axial and radial dimensions, a non-compact structure, large mass and large occupied space; in addition, the overrunning clutch designed by the patent adopts a structure with a single roller and a double wedge-shaped space, the roller has a large movement stroke in the process of switching from a forward gear to a reverse gear, and the problems of roller clamping stagnation, impact, poor adhesion between the roller and the wedge-shaped space inclined plane and the like exist; meanwhile, the roller has large movement stroke and slow response speed in the process of switching from the forward gear to the reverse gear, so that the effective braking energy recovery can not be carried out when the vehicle is braked under the working state of the first gear of the gearbox; furthermore, the freewheel clutch roller according to this patent is preloaded against the locking surface of the wedge space by means of the roller cage only with the flap spring, with the risk that the freewheel clutch roller will disengage from the locking surface of the wedge space.
Disclosure of Invention
To the defect that exists among the above-mentioned prior art, the utility model provides a planetary gear type is unpowered to be interrupted two and keeps off gearbox has solved the safety problem that adopts two to keep off the gear speed of backing a car too fast and freewheel clutch appearance jamming phenomenon among the prior art, has reduced the space size of gearbox, has reduced the quality of gearbox to can keep off operating condition at the vehicle and can carry out effectual braking energy recovery down. With the attached drawings, the technical scheme of the utility model is as follows:
a planetary gear type unpowered interrupt two-gear transmission is composed of an input shaft 2, a diaphragm spring clutch 3, a planetary gear type transmission mechanism, a controllable overrunning clutch 6, an output shaft 10 and a shell 4;
the planetary gear type transmission mechanism consists of a sun gear 9, a planetary gear 8, a planet carrier 5 and a gear ring 7, wherein the sun gear 9 is coaxially and fixedly connected to the input shaft 2, the planetary gear 8 is rotatably arranged on the planet carrier 5, and the planetary gear 8 is simultaneously meshed with the sun gear 9 and the gear ring 7;
the diaphragm spring clutch 3 is coaxially connected with the input shaft, a friction plate 36 of the diaphragm spring clutch 3 is coaxially and fixedly connected to the input shaft 2, a clutch flywheel disc 38 of the diaphragm spring clutch 3 is coaxially and fixedly connected with one end of the planet carrier 5, and the other end of the planet carrier 5 is coaxially and fixedly connected with the output shaft 10;
the inner ring of the controllable overrunning clutch 6 is fixed on the outer side of the circumference of the gear ring 7, and the outer ring 61 of the controllable overrunning clutch 6 is fixed on the inner side wall of the shell 4.
Further, the controllable overrunning clutch 6 is composed of an inner ring, an outer ring 61, a retainer 62, a first roller 63A, a second roller 63B, a first tab spring 64A, a second tab spring 64B and an electromagnet 65, wherein the inner ring and the outer edge of the hub of the gear ring 7 are integrally designed;
a plurality of corresponding shuttle-shaped spaces are formed between the inner wall of the outer ring 61 and the outer wall of the gear ring 7 along the circumferential direction, the retainer 62 is formed by fixedly connecting an end plate and a shifting frame, the shifting frame is sleeved between the inner wall of the outer ring 61 and the outer wall of the gear ring 7, the baffle plate arranged on the inner wall of the outer ring 61 in each shuttle-shaped space is divided into two symmetrical sides, in one side of each shuttle-shaped space, the first roller 63A is arranged between the corresponding pair of roller shifting plates, two ends of the first tab spring 64A are respectively connected between the baffle plate and the shifting plate, in the other side of each shuttle-shaped space, the second roller 63B is arranged between the corresponding pair of roller shifting plates, and two ends of the second tab spring 64B are respectively connected between the baffle plate and;
an electromagnetic control block 66 is arranged on the circumference of an end plate of the retainer 62, the electromagnet 65 is correspondingly matched with the electromagnetic control block 66, the electromagnet 65 is electrified or powered off, so that the electromagnetic control block 66 is attracted or repelled, the electromagnetic control block 66 is further controlled to drive the retainer 62 to rotate along the axial direction, and the first roller 63A and the second roller 63B move along the circumferential direction in the corresponding shuttle-shaped space under the combined action of a pulling frame of the retainer 62, the first folding spring 64A and the second folding spring 64B.
Further, one end of the input shaft 2 is connected with the output end of the motor 1 through a spline, the input shaft 2 is rotatably mounted on the front side wall of the housing 4 through a deep groove ball bearing, the output shaft 10 is coaxially arranged with the input shaft 2, and the output shaft 10 is rotatably mounted on the rear side wall of the housing 4 through a deep groove ball bearing.
Furthermore, in the planetary gear type transmission mechanism, the planet carrier 5 consists of a planet carrier left support plate 51, a planet shaft 52 and a planet carrier right support plate 53;
the planet carrier left support plate 51 and the planet carrier right support plate 53 are coaxially and symmetrically arranged, two ends of the planet carrier 52 are vertically fixed on the planet carrier left support plate 51 and the planet carrier right support plate 53, the planet wheel 8 is rotatably installed on the planet carrier 52 through a needle bearing, a hollow shaft is coaxially arranged at the front end of the planet carrier left support plate 51, the hollow shaft of the planet carrier left support plate 51 is coaxially sleeved outside the input shaft 2, the outer wall of the hollow shaft of the planet carrier left support plate 51 is connected with the clutch flywheel disc 38 of the diaphragm spring clutch 3 through a second spline 54, and the planet carrier right support plate 53 is connected with the output shaft 10 through a spline.
Further, the diaphragm spring clutch 3 is composed of a release bearing 31, a diaphragm spring 32, a diaphragm spring support ring 33, a clutch cover 34, a clutch pressure plate 35, a friction plate 36 and a clutch flywheel plate 38 which are arranged in sequence from front to back;
the clutch flywheel disc 38 is coaxially connected with the planet carrier left support plate 51 through the first spline 39, the friction plate 36 is coaxially and fixedly connected on the input shaft 2, the clutch pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 covers the clutch pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly installed on the front end surface of the clutch flywheel disc 38 through the connecting bolt 37, the diaphragm spring bearing ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and installed on the clutch cover 34 through the diaphragm spring bearing 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 clutch pressure plate 35.
Further, the diaphragm spring clutch 3 is a dry clutch or a wet clutch.
Further, the diaphragm spring clutch 3 is a single plate clutch or a multiple plate clutch.
Compared with the prior art, the beneficial effects of the utility model reside in that:
1. the planetary wheel type unpowered interrupt two-gear gearbox solves the problem of power interruption of traditional AMT gear shifting, can realize unpowered interrupt gear shifting, has power output in the process of gear rising or gear falling all the time, improves the smoothness of the gear shifting process, and can realize a smooth speed ratio switching process;
2. the planetary wheel type unpowered interrupt two-gear gearbox of the utility model cancels the traditional gearbox synchronizer structure, does not need an independent synchronizer actuating mechanism, and only needs the clutch actuating mechanism and the retainer control mechanism to realize the gear shifting action, thereby having low production cost and simple control;
3. the planetary gear type unpowered interrupt two-gear gearbox of the utility model can adopt a dry diaphragm spring clutch and a wet clutch; in addition, the diaphragm spring clutch can be a single diaphragm spring clutch or a plate clutch, can be a normally open clutch or a normally closed clutch, and has wide application and strong applicability;
4. the overrunning clutch of the planetary gear type unpowered interrupt two-gear gearbox of the utility model adopts the bidirectional overrunning clutch, so that the forward and backward of the first gear can be realized, the problem of high speed when the planetary gear type two-gear gearbox is reversed through the two-gear in the prior art is solved, and the safety problem of jamming of the overrunning clutch is effectively eliminated;
5. planetary gear type is unpowered to be interrupted two and keeps off planetary gear train compact structure that the gearbox adopted, and planetary gear gearbox's diameter is little, more is applicable to the electric motor car that requires the compactness to the transmission system structure.
6. Planetary gear type is unpowered to be interrupted two freewheel clutch control mechanism that keep off gearbox adopted can guarantee that the roller laminates at wedge space internal surface all the time when the folded piece spring breaks down, avoids appearing the roller and breaks away from one and keeps off, reverse gear operation locking face, the phenomenon of power disappearance appears.
Drawings
Fig. 1 is a schematic view of the planetary gear type unpowered interrupt two-gear transmission of the present invention in a first-gear state; fig. 2 is a schematic view of the structure and power transmission of the planetary gear type unpowered interrupt two-gear transmission in the second gear state of the present invention;
fig. 3 is a schematic structural diagram of the diaphragm spring clutch in the first gear operating state in the transmission of the present invention;
fig. 4 is a schematic structural diagram of the diaphragm spring clutch in the second gear state in the transmission of the present invention;
FIG. 5 is a schematic structural view of a controllable overrunning clutch in the transmission of the present invention;
FIG. 6 is a schematic view of an exploded structure of a controllable overrunning clutch in the transmission according to the present invention;
FIG. 7 is a schematic view of the operation state of the controllable overrunning clutch in the transmission according to the present invention when the controllable overrunning clutch is engaged counterclockwise;
FIG. 8 is a schematic view of the operating state of the controllable overrunning clutch in the transmission according to the present invention when the controllable overrunning clutch is engaged clockwise;
FIG. 9 is a schematic view of the operating state of the controllable overrunning clutch when the controllable overrunning clutch is not engaged in the transmission according to the present invention;
fig. 10 is a schematic structural diagram of a planetary gear transmission mechanism in the transmission of the present invention.
In the figure:
1 motor, 2 input shafts, 3 diaphragm spring clutches, 4 shells,
5 a planet carrier, 6 a controllable overrunning clutch, 7 a gear ring, 8 planet gears,
9 sun gear, 10 output shaft;
31 release bearing, 32 diaphragm spring, 33 diaphragm spring spider, 34 clutch cover,
35 clutch pressure plate, 36 friction plate, 37 connecting bolt, 38 clutch flywheel plate,
39 a first spline;
51 planet carrier left support plate, 52 planet shaft, 53 planet carrier right support plate, 54 second spline;
61 outer race, 62 cage, 63A first rollers, 63B second rollers,
64A first folding spring, 64B second folding spring, 65 electromagnet and 66 electromagnetic control block.
Detailed Description
For further explanation the technical solution and the specific working process of the present invention, in combination with the drawings of the specification, the specific embodiment of the present invention is as follows:
as shown in fig. 1, the utility model provides a planetary gear type unpowered interruption two-gear gearbox, which comprises an input shaft 2, a diaphragm spring clutch 3, a planetary gear type transmission mechanism, a controllable overrunning clutch 6, an output shaft 10 and a shell 4. One end of an input shaft 2 is connected with the output end of a motor 1, the other end of the input shaft 2 is connected with a sun gear 9 of a planetary gear transmission mechanism, a diaphragm spring clutch 3 is installed on the input shaft 2, a clutch flywheel disc 38 of the diaphragm spring clutch 3 is connected with a planet carrier 5 of the sun gear 9 of the planetary gear transmission mechanism, the input shaft 2 and an output shaft 10 are installed on a shell 4 in a supporting mode, and a controllable overrunning clutch 6 is installed between the outer wall of a gear ring 7 of the sun gear 9 of the planetary gear transmission mechanism and the inner wall of the shell 4. The specific composition and connection relationship of the gearbox are as follows:
as shown in fig. 1, an output end of a motor 1 is connected with one end of an input shaft 2 through a spline to realize power transmission, the input shaft 2 is rotatably mounted on a front side wall of a housing 4 through a deep groove ball bearing, an output shaft 10 is linearly arranged with the input shaft 2, and the output shaft 10 is rotatably mounted on a rear side wall of the housing 4 through the deep groove ball bearing.
As shown in fig. 1 and 10, the planetary gear type transmission mechanism is composed of a sun gear 9, planet gears 8, a planet carrier 5 and a gear ring 7, wherein the planet carrier 5 is composed of a planet carrier left support plate 51, a planet shaft 52 and a planet carrier right support plate 53, the planet carrier left support plate 51 and the planet carrier right support plate 53 are coaxially and symmetrically arranged, two ends of the planet shaft 52 are respectively and vertically fixed on the planet carrier left support plate 51 and the planet carrier right support plate 53, the sun gear 9 is coaxially and fixedly connected with the input shaft 2, the planet gears 8 are rotatably mounted on the planet shaft 52 through needle bearings, the gear ring 7 is coaxially arranged with the sun gear 9, the inner side of the planet gears 8 is engaged with the sun gear 9, the outer side of the planet gears 8 is engaged with the gear ring 7, the front end of the planet carrier left support plate 51 is coaxially provided with a hollow shaft, the hollow shaft of the planet carrier left support plate 51 is coaxially sleeved on the outer side of the input shaft 2 The clutch flywheel disc 38 is connected, and the planet carrier right support plate 53 is coaxially connected with the output shaft 10 through a spline to realize power transmission.
As shown in fig. 1 and 3, the diaphragm spring clutch 3 is composed of a release bearing 31, a diaphragm spring 32, a diaphragm spring support ring 33, a clutch cover 34, a clutch pressure plate 35, a friction plate 36 and a clutch flywheel plate 38, which are arranged in this order from front to back. The clutch flywheel disc 38 is coaxially connected with the planet carrier left support plate 51 through the first spline 39, the friction plate 36 is coaxially and fixedly connected on the input shaft 2, the clutch pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 covers the clutch pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly installed on the front end surface of the clutch flywheel disc 38 through the connecting bolt 37, the diaphragm spring bearing ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and installed on the clutch cover 34 through the diaphragm spring bearing 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 clutch pressure plate 35.
The diaphragm spring clutch can adopt a dry clutch or a wet clutch, and can adopt a single-plate clutch or a multi-plate clutch.
The diaphragm spring clutch 3 has two working states:
1. as shown in fig. 3, the release bearing 31 moves backward in the axial direction of the input shaft 2 under the action of an external force, and under the pushing action of the release bearing 31, the release finger end of the diaphragm spring 32 moves backward in the axial direction of the input shaft 2, so that the diaphragm spring 32 is gradually compressed, and under the supporting action of the diaphragm spring support ring 33, the pressure plate end of the diaphragm spring 32 drives the clutch pressure plate 35 away from the surface of the friction plate 36, so that the clutch pressure plate 35 is separated from the friction plate 36, the clutch flywheel 38 is also separated from the friction plate 36, no torque is transmitted between the friction plate 36 and the clutch flywheel 38, and the diaphragm spring clutch 3 is in a release state.
2. As shown in fig. 4, 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, and under the supporting action of the diaphragm spring supporting ring 33, the pressure plate end of the diaphragm spring 32 drives the clutch pressure plate 35 to press the friction plate 36 against the clutch flywheel plate 38, so that torque is transmitted between the friction plate 36 and the clutch flywheel plate 38, and the diaphragm spring clutch 3 is in a combined state.
As shown in fig. 1, 5 and 6, the controllable overrunning clutch 6 is composed of an inner ring (gear ring 7), an outer ring 61, a holder 62, a first roller 63A, a second roller 63B, a first flap spring 64A, a second flap spring 64B and an electromagnet 65. Wherein, the inner ring of the controllable overrunning clutch 6 is the outer edge of the hub of the gear ring 7 of the planetary gear transmission mechanism, the outer ring 61 is pressed into the shell 4, and is fixed on the inner wall of the shell 4, the outer ring 61 is sleeved outside the gear ring 7, a plurality of arc-shaped grooves are uniformly arranged on the inner wall of the outer ring 61 along the circumferential direction, so that a plurality of corresponding shuttle-shaped spaces with narrow ends and wide middle parts are formed between the inner wall of the outer ring 61 and the outer wall of the gear ring 7 along the circumferential direction, the expression "narrow at both ends and wide in the middle" means that the radial distance between the inner wall of the outer ring 61 corresponding to both ends of the shuttle-shaped space and the outer wall of the gear ring 7 is small, the radial distance between the inner wall of the outer ring 61 corresponding to the middle of the shuttle-shaped space and the outer wall of the gear ring 7 is large, a baffle is arranged at the radial middle part of each arc-shaped groove on the inner wall of the outer ring 61 to divide the corresponding shuttle-shaped space into two parts which are symmetrical in the circumferential direction; the retainer 62 is fixedly connected with a poking frame by an end plate, an electromagnetic control block 66 is arranged on the circumference of the end plate, the poking frame is composed of poking plates which are arranged in pairs along a plurality of groups, the poking plates are vertically arranged along the circumferential direction of the end surface of the end plate, the poking frame is sleeved between the inner wall of the outer ring 61 and the outer wall of the gear ring 7, wherein, in a plurality of shuttle-shaped spaces between the outer ring 61 and the gear ring 7, two pairs of poking plates are correspondingly arranged in each shuttle-shaped space, a pair of poking plates are correspondingly arranged on two sides of the shuttle-shaped space which is divided by the baffle, wherein, in one side of the shuttle-shaped space, a first roller 63A is arranged between a pair of corresponding roller poking plates, two ends of a first folding spring 64A are respectively connected between the baffle and the poking plates, in the other side of the shuttle-shaped space, a second roller 63B is arranged between a pair of corresponding, the installation modes of the rollers and the folding springs in the shuttle-shaped spaces are the same; under the combined action of the shifting frame and the corresponding folding spring, the roller moves in the corresponding shuttle-shaped space along the circumferential direction, when the roller moves to the end part of the shuttle-shaped space, the roller is wedged between the inner wall of the outer ring 22 of the overrunning clutch and the outer wall of the inner ring of the overrunning clutch, when the gear ring 7 rotates along a certain direction, the controllable overrunning clutch is locked to realize power transmission, and when the roller moves to the middle of the shuttle-shaped space, the roller freely moves between the inner wall of the outer ring 22 of the overrunning clutch and the outer wall of the inner ring of the overrunning clutch to separate the outer ring 22 of the overrunning clutch from the inner ring of the overrunning clutch and realize unpowered transmission.
The position of the electromagnet 65 is matched with the position of the electromagnetic control block 66 of the retainer 62, and the electromagnet 65 is switched on or off, so that the electromagnetic control block 66 is attracted or repelled, and the electromagnetic control block 66 is controlled to drive the retainer 62 to rotate for a certain angle along the circumferential direction.
As described above, a plurality of shuttle-shaped spaces are provided between the outer ring 61 of the controllable overrunning clutch 6 and the gear ring 7, one of the two narrow ends of the shuttle-shaped space is a reverse operation locking end, the corresponding arc-shaped groove surface of the outer ring 61 is a reverse operation locking surface, the other end is a reverse operation locking end, and the corresponding arc-shaped groove surface of the outer ring 61 is a reverse operation locking surface;
the controllable overrunning clutch 6 has three working states:
1. when the controllable overrunning clutch 6 is in an initial state, the electromagnet 65 is in a power-off state, the retainer 62 does not rotate, as shown in fig. 7, at this time, under the action of the pretightening force of the first folding spring 64A, the poking plate of the retainer 62 pokes the first roller 63A to the corresponding narrow end on one side of the shuttle-shaped space, so that the first roller 63A is wedged in the narrow end, the narrow end is a blocking operation locking end, and the corresponding arc-shaped groove surface of the outer ring 61 is a blocking operation locking surface; at this time, in the other side of the shuttle-shaped space, under the limitation of the corresponding poking plate of the retainer 62, the second flap spring 64B is in a compressed state, so that the second roller 63B is poked to the middle part of the shuttle-shaped space, and a gap is left between the second roller 63B and the inner wall of the outer ring 61; at this time, when the gear ring 7 rotates in the reverse direction (counterclockwise), the outer ring 61 and the gear ring 7 are locked, that is, the controllable overrunning clutch 6 is locked, so that power transmission is realized, and when the gear ring 7 rotates in the forward direction (clockwise), the gear ring 7 freely rotates relative to the outer ring 61, so that the controllable overrunning clutch 6 has no power transmission.
2. When the electromagnet 65 is in the energized state in the controllable overrunning clutch 6, under the action of the attraction force generated by the electromagnet 65, the electromagnetic control block 66 on the retainer 62 drives the retainer 62 to rotate forward (clockwise) by a certain angle, as shown in fig. 8, in one side of the shuttle-shaped space, the poking plate of the retainer 62 pokes the first roller 63A to the middle of the shuttle-shaped space by overcoming the elastic force of the first folding spring 64A, so that a gap is left between the first roller 63A and the inner wall of the outer ring 61; at this time, in the other side of the shuttle-shaped space, under the combined action of the second flap spring 64B and the retainer 62, the shifting plate of the retainer 62 shifts the second roller 63B to the narrow end corresponding to the shuttle-shaped space, so that the second roller 63B is wedged tightly in the narrow end, the narrow end is the reverse gear operation locking end, and the corresponding arc-shaped groove surface of the outer ring 61 is the reverse gear operation locking surface; at this time, when the gear ring 7 rotates in the forward direction (clockwise), the outer ring 61 and the gear ring 7 are locked, that is, the controllable overrunning clutch 6 is locked, so that power transmission is realized, and when the gear ring 7 rotates in the reverse direction (counterclockwise), the gear ring 7 freely rotates relative to the outer ring 61, so that the controllable overrunning clutch 6 has no power transmission.
3. When the electromagnet 65 is in the energized state in the controllable overrunning clutch 6, the current flowing through the electromagnet 65 is controlled to further control the electromagnetic acting force generated by the electromagnet 65 on the electromagnetic control block 66 on the retainer 62, so as to drive the retainer 62 to rotate forward (clockwise) by a certain angle, as shown in fig. 9, at this time, the electromagnet 65 balances the electromagnetic force acting on the holder 62 and the elastic force of the first and second flap springs 64A and 64B, so that in one side of the shuttle space, under the action of the retainer 62 and the first folding spring 64A, the first roller 63A is shifted to the middle of the shuttle-shaped space, so that a gap is left between the first roller 63A and the inner wall of the outer ring 61, so that in one side of the shuttle-shaped space, under the use of the retainer 62 and the two-fold spring 64B, the second roller 63B is also shifted to the middle part of the shuttle-shaped space, so that a gap is reserved between the second roller 63B and the inner wall of the outer ring 61; at this time, no matter the ring gear 7 rotates in the forward direction (clockwise) or in the reverse direction (counterclockwise), the ring gear 7 rotates freely relative to the outer ring 61, and the controllable overrunning clutch 6 has no power transmission.
The controllable overrunning clutch 6 may also adopt other structural forms, and is not limited to the structure described in this embodiment, the flap spring may also adopt other forms of springs or elastic bodies, or may not adopt a spring, but two electromagnets may be installed on both sides to control the cage, or a permanent magnet may be installed on the cage control portion, and the current direction of the electromagnets may be changed to generate an attractive force or a repulsive force, thereby controlling the rotational motion of the cage.
The working process of the planetary gear type unpowered interrupt two-gear transmission comprises the following steps: the method comprises the following steps of:
the specific process of the first gear advancing is as follows:
when the vehicle moves forward in the first gear, as shown in fig. 3, the clutch actuator controls the release bearing 31 to move backward, 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, and under the supporting action of the diaphragm spring support ring 33, the pressure plate end of the diaphragm spring 32 drives the clutch pressure plate 35 to separate from the surface of the friction plate 36, the friction plate 36 also separates from the clutch flywheel disc 38, the diaphragm spring clutch 3 is in a release state, the diaphragm spring clutch 3 does not have power transmission, and the clutch flywheel disc 38 and the planet carrier 5 move synchronously because the planet carrier left end plate 51 is in splined connection with the clutch flywheel disc 38; when the vehicle is moving forward in the first gear, as shown in fig. 1, looking toward the front end of the input shaft 2, the input shaft 2 is driven by the motor 1 to rotate forward (clockwise), the sun gear 9 coaxially connected to the input shaft 2 rotates forward synchronously and drives the planet gear 8 to rotate in reverse, at this time, according to the transmission characteristics of the planetary gear transmission mechanism, the planet gear 8 rotates in reverse to make the ring gear 7 tend to rotate in reverse along the axis, at this time, as shown in fig. 7, the controllable overrunning clutch 6 is in the initial state, i.e., the electromagnet 65 is powered off, in the controllable overrunning clutch 6, the retainer 62 wedges the first roller 63A at a blocking end of the shuttle space under the elastic force of the first tab spring 64A and the second tab spring 64B respectively, so as to separate the second roller 63B from the outer ring 61, at this time, when the ring gear 7 rotates in reverse, the controllable overrunning clutch 6 is blocked, because the gear ring 7 tends to rotate reversely, the gear ring 7 and the outer ring 61 are locked, and the outer ring 61 is fixed on the inner wall of the shell 4, so that the gear ring 7 is relatively fixed and static; the vehicle keeps off and advances, 1 forward rotation of motor is with power through input shaft 2 input to the gearbox, 2 forward rotations of input shaft drive sun gear 9 synchronous forward rotations, sun gear 9 drives planet wheel 8 reverse rotations, because ring gear 7 relatively fixed, planet wheel 8 revolves along 2 axis forward of input shaft under the reaction force of ring gear 7, promote planet carrier 5 to follow 2 axis forward rotations of input shaft promptly, because the moment increase of planet carrier 5, so the rotational speed of planet carrier 5 reduces, planet carrier 5 drives the output shaft 10 synchronous forward rotations rather than the splined connection, final power is exported through output shaft 10 and is realized keeping off and advance one.
As described above, as shown by the thick solid line in fig. 1, the power transmission route for the forward first gear is: motor 1, input shaft 2, sun gear 9, planet wheel 8, planet carrier 5, output shaft 10.
The first gear forward is mainly used for vehicle starting and working conditions requiring high torque operation, such as climbing and the like.
The second-gear advancing process comprises the following specific steps:
when the vehicle advances in two grades, as shown in fig. 4, the clutch actuator controls the release bearing 31 to move forward, the diaphragm spring 32 moves forward and extends along the axial direction of the input shaft 2 under the action of restoring force, and under the supporting action of the diaphragm spring supporting ring 33, the pressure plate end of the diaphragm spring 32 drives the clutch pressure plate 35 to press the friction plate 36 on the clutch flywheel disc 38, the diaphragm spring clutch 3 is in a combined state, in the diaphragm spring clutch 3, the friction plate 36 transmits power to the clutch flywheel disc 38, and the clutch flywheel disc 38 drives the planet carrier 5 connected with the spline of the clutch to rotate synchronously, and the diaphragm spring clutch 3 realizes power transmission; when the vehicle advances in two gears, as shown in fig. 2, when viewed facing the front end of the input shaft 2, the input shaft 2 rotates forward (clockwise) under the driving of the motor 1, the sun gear 9 coaxially and fixedly connected to the input shaft 2 rotates forward synchronously, and at the same time, the input shaft 2 drives the planet carrier 5 to rotate forward synchronously through the diaphragm spring clutch 3, so that the sun gear 9 rotates synchronously with the planet carrier 5, and at the same time, the controllable overrunning clutch 6 is in an initial state, i.e., the electromagnet 65 is powered off, as shown in fig. 7, the gear ring 7 in the controllable overrunning clutch 6 rotates freely forward relative to the outer ring 61, so that the gear ring 7 rotates freely forward along the axis of the input shaft 2, and according to the transmission characteristic of the planetary gear transmission mechanism, the whole planetary gear transmission mechanism revolves along the forward direction of the input shaft 2 at the same revolution speed as the input shaft 2; the first gear of the vehicle advances, the motor 1 rotates forwards to input power to the gearbox through the input shaft 2, the input shaft 2 rotates forwards to drive the whole planetary gear type transmission mechanism to rotate forwards along the input shaft 2, the planet carrier 5 drives the output shaft 10 to rotate forwards, the rotating speed of the output shaft 10 is the same as that of the input shaft 2, and finally the power is output outwards through the output shaft 10 to realize the second gear advancing.
As described above, as shown by the thick solid line in fig. 2, the power transmission route for the forward movement in the second gear is: the device comprises a motor 1, an input shaft 2, a diaphragm spring clutch 3, a planet carrier 5 and an output shaft 10.
The second-gear forward motion is mainly used for the high-speed running working condition of the vehicle.
The third step is that the specific process of the first gear reverse is as follows:
when the vehicle is in reverse gear, as shown in fig. 3, the clutch actuator controls the release bearing 31 to move backwards, under the pushing action of the release bearing 31, the release finger end of the diaphragm spring 32 moves backwards along the axial direction of the input shaft 2, so that the diaphragm spring 32 is gradually compressed, and under the supporting action of the diaphragm spring bearing ring 33, the pressure plate end of the diaphragm spring 32 drives the clutch pressure plate 35 to separate from the surface of the friction plate 36, the friction plate 36 also separates from the clutch flywheel disc 38, the diaphragm spring clutch 3 is in a release state, the diaphragm spring clutch 3 does not have power transmission, and the clutch flywheel disc 38 and the planet carrier 5 move synchronously because the planet carrier left end plate 51 is in splined connection with the clutch flywheel disc 38; when the vehicle is in first gear and reverse, as shown in fig. 1, looking toward the front end of the input shaft 2, the input shaft 2 rotates in reverse (counterclockwise) direction under the driving of the motor 1, the sun gear 9 coaxially connected to the input shaft 2 rotates in reverse synchronously and drives the planet gear 8 to rotate in forward direction, at this time, according to the transmission characteristics of the planetary gear transmission mechanism, the planet gear 8 rotates in forward direction to make the ring gear 7 tend to rotate in forward direction along the axis, at this time, as shown in fig. 8, the electromagnet 65 in the controllable clutch 6 is energized, under the action of the electromagnetic force, the electromagnetic control block 66 drives the retainer 62 to rotate in forward direction (clockwise) for a certain angle, under the combined action of the retainer 62, the first tab spring 64A and the second tab spring 64B, the first roller 63A is separated from the outer ring 61, and the second roller 63B is wedged at the first gear operation locking end of the shuttle space, at the moment, when the gear ring 7 rotates forwards, the controllable overrunning clutch 6 is locked, because the gear ring 7 has a trend of rotating forwards, the gear ring 7 and the outer ring 61 are locked, and the outer ring 61 is fixed on the inner wall of the shell 4, so that the gear ring 7 is relatively fixed and static; the vehicle is in first gear and reverses, the motor 1 rotates reversely to input power to the gearbox through the input shaft 2, the input shaft 2 rotates reversely to drive the sun gear 9 to rotate synchronously and reversely, the sun gear 9 drives the planet gear 8 to rotate forwardly, the gear ring 7 is relatively fixed, the planet gear 8 revolves reversely along the axis of the input shaft 2 under the reaction force of the gear ring 7, namely, the planet carrier 5 is pushed to rotate reversely along the axis of the input shaft 2, the torque of the planet carrier 5 is increased, the rotation speed of the planet carrier 5 is reduced, the planet carrier 5 drives the output shaft 10 connected with the spline of the planet carrier 5 to rotate synchronously and reversely, and finally, the power is output outwards through the output shaft 10 to.
As described above, the power transmission route for the first gear reverse is: motor 1, input shaft 2, sun gear 9, planet wheel 8, planet carrier 5, output shaft 10. Therefore, the power transmission route of the reverse gear is the same as the transmission route of the forward gear, but the rotating directions of the running components are opposite.
The first gear reverse is mainly used for the vehicle reverse working condition.
Fourthly, the specific process of the power-interruption-free gear shifting is as follows:
the unpowered interrupted gear shifting comprises a first gear up-shifting process and a second gear down-shifting process, and the reverse gear shifting generally occurs during parking without power.
1. The first gear-up and second gear-down process is as follows:
when the motor 1 of vehicle outwards outputs the rotational speed and reaches the speed of settlement, through discernment throttle aperture signal, acquires the intention of driving, and then judges that the vehicle needs high-speed when moving, then the vehicle sends the control command signal that a fender rose two to the gearbox, and the vehicle begins to carry out the process that a fender rose two: when the first gear is shifted up to the second gear, the electromagnet 65 in the controllable overrunning clutch 6 is powered off, the first roller 63A is wedged tightly at the first gear operation locking end of the shuttle-shaped space, the gear ring 7 rotates freely in the forward direction and rotates in the reverse direction to be locked, at the moment, the clutch actuator controls the diaphragm spring clutch 3 to be gradually combined, the clutch pressure plate 35, the friction plate 36 and the clutch flywheel plate 38 generate sliding friction and transmit torque, namely, the power transmitted to the planet carrier 5 by the input shaft 2 through the diaphragm spring clutch 3 is gradually increased, as the rotating speed of the planet carrier 5 is gradually increased, the power input through the input shaft 2 is transmitted downwards from the sun gear 9 when the first gear advances, and is transmitted downwards from the planet carrier 5 when the second gear advances, namely, the power is gradually transmitted to the planet carrier 5 from the sun gear 9, as the rotating speed of the planet carrier 5 gradually increases, in the planet gear type transmission mechanism, the rotating speed of the planet carrier 5 driving the down-star gear 8 is gradually the same as the rotating, the meshing force between the planet wheel 8 and the sun wheel 9 is reduced, namely the power transmitted from the sun wheel 9 to the planet wheel 8 is reduced, the autorotation speed of the planet wheel 8 along the axis of the planet wheel is gradually reduced to zero, at the moment, the whole planetary wheel type transmission mechanism is driven by the input shaft 2 to rotate in the forward direction, the gear ring 7 can also rotate in the forward direction, the power is transmitted through the diaphragm spring clutch 3 after being input through the input shaft 2, and then is directly transmitted to the output shaft 10 through the planet carrier 5, and finally the power is output outwards through the output shaft 10 to realize the forward movement of the second gear, namely, the process of one gear lifting and the second gear lifting is realized, and the whole gear lifting process.
2. The second gear descending process is as follows:
when the vehicle runs at a high speed and meets an uphill road condition, the vehicle speed is reduced under the condition of no brake pedal signal, at the moment, the speed is reduced and the torque is increased to pass through an uphill road section, namely, the vehicle needs to send a control instruction signal for reducing the first gear by the second gear to the gearbox, and the vehicle starts to execute the process of reducing the first gear by the second gear: when the second gear is shifted down to the first gear, the electromagnet 65 in the controllable overrunning clutch 6 is powered off, the first roller 63A is wedged at the first gear operation locking end of the shuttle-shaped space, the gear ring 7 rotates freely in the forward direction and rotates in the reverse direction to be locked, at the moment, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be gradually separated, the clutch pressure plate 35, the friction plate 36 and the clutch flywheel plate 38 are in sliding friction, the transmission torque is gradually reduced, namely, the power transmitted by the input shaft 2 to the planet carrier 5 through the diaphragm spring clutch 3 is gradually reduced, so that the power of the planet carrier 5 is gradually smaller than the resistance borne by the power, 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, and is transmitted downwards from the sun gear 9 when the first gear advances, namely, the power is gradually transmitted to the sun gear 9 from the planet carrier 5, and is gradually reduced along, in the planetary gear type transmission mechanism, the planetary gear 8 starts to restore the reverse rotation along the axis of the planetary gear 8, the meshing force between the sun gear 9 and the planetary gear 8 is gradually increased, the power starts to be transmitted downwards from the planetary gear 8, meanwhile, the rotating speed of the gear ring 7 is gradually reduced until the reverse rotation is locked, the power is transmitted to the output shaft 10 through the sun gear 9, the planetary gear 8 and the planetary carrier 5 in sequence after being input through the input shaft 2, finally the power is output outwards through the output shaft 10 to realize the forward movement of the first gear, namely, the process of the first gear descending of the second gear is realized, and the whole gear ascending process is free of power.
Fifthly, the specific process of braking and braking energy recovery is as follows:
the braking and braking energy recovery control comprises the following steps: the control system comprises brake control, first-gear brake energy recovery control and second-gear brake energy recovery control.
1. The brake control process is as follows:
when the vehicle is in the first-gear advancing or second-gear advancing process, the vehicle recognizes a brake pedal signal, and the brake pedal signal is smaller than a preset value, the vehicle is judged to start conventional brake control at the moment, and at the moment, the vehicle stops supplying current to the motor 1 and still excites the motor 2, so that the rotor of the motor 1 rotates forwards, and generates reverse electromotive force to charge the battery; when the vehicle recognizes that the brake pedal signal is greater than the preset value, namely the brake pedal reaches a larger opening, emergency brake control is needed at the moment, reverse current voltage is provided for the motor 1, the motor 1 is rapidly stopped to realize emergency brake, at the moment, the sun gear 9 and the output shaft 10 in the gearbox generate larger reverse resistance simultaneously, the gearbox is stopped to operate, when the speed of the motor is recognized to be reduced to the preset value, the reverse current is provided for the motor 1, and forward voltage is provided to prevent the vehicle from running backwards.
2. The first-gear braking energy recovery control process specifically comprises the following steps:
when the vehicle moves forward in the first gear, if the throttle opening signal is not identified or the brake pedal signal smaller than the preset value is identified, and the speed of the vehicle is increased, the vehicle is judged to be in a downhill working condition at the moment, and the vehicle starts a first-gear braking energy recovery process: when the vehicle moves forward in the first gear, the input shaft 1 of the gearbox rotates in the forward direction, when braking is carried out, the vehicle still continues to move forward in the braking process due to inertia of the vehicle, the residual power of the gearbox and the vehicle transmission components behind the power transmission route of the gearbox is reversely transmitted to the planet carrier 5 through the output shaft 10, at the moment, the planet carrier 5 serves as a power source, in the first gear state, the controllable overrunning clutch 6 can freely rotate in the forward direction and is not transmitted in a power-free mode, so the power cannot be transmitted to the motor 1 downwards, the electromagnet 65 in the controllable overrunning clutch 6 needs to be electrified, after the retainer 62 rotates for a certain angle under the action of electromagnetic force, the first roller 63A is separated from the outer ring 61 under the combined action of the retainer 62, the first tab spring 64A and the second tab spring 64B, the second roller 63B is wedged at the first gear operation locking end of the shuttle-shaped space, at the moment, the gear ring 7 rotates forwards and is locked, power is transmitted to the motor 1 through the planet wheel 8, the sun wheel 9 and the input shaft 2 in sequence after being transmitted through the planet carrier 5, and finally the motor 1 rotates forwards to generate reverse electromotive force to charge the battery; when the vehicle speed is detected to start to drop, the gearbox is switched back to the first gear forward state.
3. The second-level braking energy recovery control process is specifically as follows:
when the vehicle advances at the second gear, the input shaft 1 of the gearbox rotates forwards, when the vehicle brakes, the vehicle still continues to move forwards in the braking process due to inertia of the vehicle, residual power of the gearbox and a vehicle transmission component behind a power transmission line of the gearbox is reversely transmitted to the planet carrier 5 through the output shaft 10, and the whole planetary gear type transmission mechanism rotates integrally under the second gear state, so that the power is transmitted through the planet carrier 5 and then directly transmitted to the motor 1 through the diaphragm spring clutch 3 and the input shaft 2 in sequence, at the moment, if the vehicle does not detect an accelerator opening degree signal, current does not need to be supplied to the motor 1, and at the moment, the motor 1 rotates forwards to generate reverse electromotive force to charge a battery.
Claims (7)
1. A planet wheel type unpowered interruption two-gear transmission is characterized in that:
the planetary transmission mechanism is composed of an input shaft (2), a diaphragm spring clutch (3), a planetary gear type transmission mechanism, a controllable overrunning clutch (6), an output shaft (10) and a shell (4);
the planetary gear type transmission mechanism consists of a sun gear (9), a planetary gear (8), a planet carrier (5) and a gear ring (7), wherein the sun gear (9) is coaxially and fixedly connected to the input shaft (2), the planetary gear (8) is rotatably arranged on the planet carrier (5), and the planetary gear (8) is simultaneously meshed with the sun gear (9) and the gear ring (7);
the clutch is characterized in that the diaphragm spring clutch (3) is coaxially connected with the input shaft, a friction plate (36) of the diaphragm spring clutch (3) is coaxially and fixedly connected to the input shaft (2), a clutch flywheel disc (38) of the diaphragm spring clutch (3) is coaxially and fixedly connected with one end of the planet carrier (5), and the other end of the planet carrier (5) is coaxially and fixedly connected with the output shaft (10);
the inner ring of the controllable overrunning clutch (6) is fixed on the outer side of the circumference of the gear ring (7), and the outer ring (61) of the controllable overrunning clutch (6) is fixed on the inner side wall of the shell (4).
2. The planetary two-speed gearbox without power interruption of claim 1, wherein:
the controllable overrunning clutch (6) consists of an inner ring, an outer ring (61), a retainer (62), a first roller (63A), a second roller (63B), a first folding spring (64A), a second folding spring (64B) and an electromagnet (65), wherein the inner ring and the outer edge of the hub of the gear ring (7) are integrally designed;
a plurality of corresponding shuttle-shaped spaces are formed between the inner wall of the outer ring (61) and the outer wall of the gear ring (7) along the circumferential direction, the retainer (62) is formed by fixedly connecting an end plate and a shifting frame, the shifting frame is sleeved between the inner wall of the outer ring (61) and the outer wall of the gear ring (7), each shuttle-shaped space is divided into two symmetrical sides by a baffle arranged on the inner wall of the outer ring (61), in one side of the shuttle-shaped space, a first roller (63A) is arranged between a pair of corresponding roller shifting plates, two ends of a first folding spring (64A) are respectively connected between the baffle and the shifting plates, in the other side of the shuttle-shaped space, a second roller (63B) is arranged between a pair of corresponding roller shifting plates, and two ends of a second folding spring (64B) are respectively connected between the baffle and the roller shifting plates;
an electromagnetic control block (66) is arranged on the circumference of an end plate of the retainer (62), the electromagnet (65) and the electromagnetic control block (66) are correspondingly matched, the electromagnet (65) is electrified or powered off, so that the electromagnetic control block (66) is attracted or repelled, the electromagnetic control block (66) is further controlled to drive the retainer (62) to rotate along the axial direction, and under the combined action of a pulling frame of the retainer (62), a first folding spring (64A) and a second folding spring (64B), the first roller (63A) and the second roller (63B) move along the circumferential direction in the corresponding shuttle-shaped space.
3. The planetary two-speed gearbox without power interruption of claim 1, wherein:
one end of the input shaft (2) is connected with the output end of the motor (1) through a spline, the input shaft (2) is rotatably installed on the front side wall of the shell (4) through a deep groove ball bearing, the output shaft (10) and the input shaft (2) are coaxially arranged, and the output shaft (10) is rotatably installed on the rear side wall of the shell (4) through the deep groove ball bearing.
4. The planetary two-speed gearbox without power interruption of claim 1, wherein:
in the planetary gear type transmission mechanism, a planet carrier (5) consists of a planet carrier left support plate (51), a planet shaft (52) and a planet carrier right support plate (53);
the planet carrier left support plate (51) and the planet carrier right support plate (53) are coaxially and symmetrically arranged, two ends of a planet shaft (52) are perpendicularly fixed on the planet carrier left support plate (51) and the planet carrier right support plate (53), a planet wheel (8) is rotatably installed on the planet shaft (52) through a needle bearing, a hollow shaft is coaxially arranged at the front end of the planet carrier left support plate (51), the hollow shaft of the planet carrier left support plate (51) is coaxially sleeved on the outer side of the input shaft (2), the outer wall of the hollow shaft of the planet carrier left support plate (51) is connected with a clutch flywheel disc (38) of the diaphragm spring clutch (3) through a second spline (54), and the planet carrier right support plate (53) is connected with the output shaft (10) through a spline.
5. The planetary two-speed gearbox without power interruption of claim 1, wherein:
the diaphragm spring clutch (3) consists of a release bearing (31), a diaphragm spring (32), a diaphragm spring supporting ring (33), a clutch cover (34), a clutch pressure plate (35), a friction plate (36) and a clutch flywheel plate (38) which are sequentially arranged from front to back;
the clutch flywheel disc (38) is coaxially connected with a planet carrier left support plate (51) through a first spline (39), a friction plate (36) is coaxially and fixedly connected to an input shaft (2), a clutch pressure plate (35) is coaxially arranged at the front end of the friction plate (36), a clutch cover (34) covers the outer sides of the clutch pressure plate (35) and the friction plate (36), the clutch cover (34) is coaxially and fixedly installed on the front end face of the clutch flywheel disc (38) through a connecting bolt (37), a diaphragm spring supporting ring (33) is fixed on the clutch cover (34), a diaphragm spring (32) is supported and installed on the clutch cover (34) through a diaphragm spring supporting ring (33), the front end of the diaphragm spring (32) is in contact connection with a release bearing (31), and the rear end of the diaphragm spring (32) is in contact connection with the clutch pressure plate (35).
6. A planetary gear type no-power-interruption two-gear transmission as claimed in claim 1 or 5, wherein:
the diaphragm spring clutch (3) is a dry clutch or a wet clutch.
7. A planetary gear type no-power-interruption two-gear transmission as claimed in claim 1 or 5, wherein:
the diaphragm spring clutch (3) is a single-plate clutch or a multi-plate clutch.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201920552949.0U CN210034309U (en) | 2019-04-23 | 2019-04-23 | Planetary wheel type unpowered interruption two-gear transmission |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201920552949.0U CN210034309U (en) | 2019-04-23 | 2019-04-23 | Planetary wheel type unpowered interruption two-gear transmission |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109899469A (en) * | 2019-04-23 | 2019-06-18 | 吉林博承传动系统科技有限公司 | A kind of planet gear type power failure-free two keeps off gearbox and its shift control method |
| CN113028005A (en) * | 2021-04-06 | 2021-06-25 | 长沙理工大学 | Gear box |
| CN113500910A (en) * | 2021-08-16 | 2021-10-15 | 北京理工大学 | Forward and backward mechanism for vehicle |
| CN109899469B (en) * | 2019-04-23 | 2024-04-30 | 吉林博承传动系统科技有限公司 | Planetary wheel type unpowered interruption two-gear gearbox and gear shifting control method thereof |
-
2019
- 2019-04-23 CN CN201920552949.0U patent/CN210034309U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109899469A (en) * | 2019-04-23 | 2019-06-18 | 吉林博承传动系统科技有限公司 | A kind of planet gear type power failure-free two keeps off gearbox and its shift control method |
| CN109899469B (en) * | 2019-04-23 | 2024-04-30 | 吉林博承传动系统科技有限公司 | Planetary wheel type unpowered interruption two-gear gearbox and gear shifting control method thereof |
| CN113028005A (en) * | 2021-04-06 | 2021-06-25 | 长沙理工大学 | Gear box |
| CN113500910A (en) * | 2021-08-16 | 2021-10-15 | 北京理工大学 | Forward and backward mechanism for vehicle |
| CN113500910B (en) * | 2021-08-16 | 2023-11-17 | 北京理工大学 | Forward and backward mechanism for vehicle |
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