WO2019033420A1 - Dual-power planetary speed changing device of type other than ravigneaux type - Google Patents
Dual-power planetary speed changing device of type other than ravigneaux type Download PDFInfo
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- WO2019033420A1 WO2019033420A1 PCT/CN2017/098133 CN2017098133W WO2019033420A1 WO 2019033420 A1 WO2019033420 A1 WO 2019033420A1 CN 2017098133 W CN2017098133 W CN 2017098133W WO 2019033420 A1 WO2019033420 A1 WO 2019033420A1
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- gear
- power
- planetary
- shaft
- sun gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
Definitions
- the utility model relates to the technical field of power control, in particular to a non-Raphaelno type dual-power planetary gear shifting device.
- the electric vehicle is driven by the vehicle power battery as the electric vehicle. Because the electric vehicle has the characteristics of energy saving, environmental protection, light weight and low cost, it is more and more valued. However, since the power and output torque of the motor are poor compared to the engine, in order to solve the problem of insufficient power of the electric vehicle, many small cars adopt a hybrid structure, which is large in size and low in energy utilization rate; the existing electric power In practical applications, the vehicle transmission needs to be used in conjunction with the clutch.
- a non-Raphaelno type dual-power planetary gear shifting device comprising a planetary gear mechanism, a first power motor, a second power motor and a power output gear;
- the planetary gear mechanism includes a planet carrier and a first sun gear and a second sun gear which are sequentially disposed in the planetary carrier from front to back and are coaxially and in parallel with each other, and the planetary carrier is axially axially
- the direction is provided with a plurality of planetary coaxial shafts evenly distributed around the first sun gear and the second sun gear, and each of the planetary coaxial shafts is provided with a first mesh for meshing with the first sun gear a planetary gear and a second planetary gear for meshing with the second sun gear;
- the first power motor is disposed on a front side of the planet carrier and coaxially distributed with the planet carrier, and a power output shaft of the first power motor is coupled to the first sun gear;
- the second power motor is disposed on the planet carrier The rear side is coaxially distributed with the planet carrier, and the power output shaft of the second power motor is meshed with the second sun gear, and the power output gear is mounted on the planet carrier.
- the planet carrier comprises two bracket plates which are arranged in front and rear relative to each other, and the first sun gear and the second sun gear are sequentially clamped between the two bracket plates from front to back, the planetary coaxial
- the front and rear ends of the shaft are respectively rotatably coupled to the corresponding bracket plates, and the power output gears are integrally assembled with one of the bracket plates.
- a coupling rod is disposed between each adjacent two of the planetary coaxial shafts, and the front and rear ends of the coupling rod are respectively fixedly connected with the corresponding bracket plates.
- the front end surface central region of the first sun gear extends forward in the axial direction to form a first power that is distributed through the bracket plate on the front side for connection with the power output shaft of the first power motor.
- Connecting a shaft, and the first power connecting shaft is provided with a first bearing for rotatingly contacting the first power connecting shaft with the bracket plate on the front side;
- a central portion of the rear end surface of the second sun gear extends rearward in the axial direction to form a second power connection shaft extending through the bracket plate on the rear side for connection with the power output shaft of the second power motor
- the second power connecting shaft is provided with a second bearing for rotatingly contacting the second power connecting shaft with the bracket plate at the rear side;
- the first sun gear and the second sun gear are in rotational contact by a third bearing.
- the power output gear is sleeved on the first power connection shaft and fixed to the front end surface of the planet carrier.
- it further includes a differential gear that meshes with the power output gear, the differential gear being sleeved on a power output shaft.
- the utility model selects two power motors with different (or the same) rotational speed and power parameters as the power source of the device, and according to different situations, the logic control or the brakes of the two power motors can be adopted.
- the device can obtain different speed ratio or power output mode to realize the functions of shifting and shifting of the device; the structure is simple and compact, and the application range is wide.
- the power output effect of the multi-speed shift can be realized by the cooperation between the two power motors.
- the power output mode is variable and adjustable, no need to configure the clutch, etc., and has strong practical value and market promotion value.
- FIG. 1 is a schematic view showing the driving relationship between the mechanisms of the embodiment of the present invention.
- FIG. 2 is a schematic structural view of the main body of the embodiment of the present invention (1);
- Figure 3 is a schematic view of the structural assembly of the main body portion of the embodiment of the present invention (2);
- FIG. 4 is a schematic cross-sectional structural view of a main body portion of an embodiment of the present invention.
- FIG. 5 is a schematic exploded view showing the structure of a planetary gear mechanism according to an embodiment of the present invention.
- a planetary gear mechanism
- b first power motor
- c second power motor
- d power output gear
- e differential
- Planetary support 111, support plate; 112, coupling shaft; 12, first sun gear; 121, first power connection shaft; 13, second sun gear; 131, second power connection shaft; a planetary coaxial shaft; 15, a first planetary gear; 16, a second planetary gear;
- A the first bearing
- B the second bearing
- D the third bearing
- the non-Raphaelno type dual-power planetary gear shifting device includes a planetary gear mechanism a, a first power motor b, a second power motor c, and a power output gear e; wherein the planetary gear mechanism includes a planet carrier 11 and a first sun gear 12 and a second sun gear that are sequentially disposed in the planetary carrier 11 from front to back and are coaxially and in parallel with each other 13.
- a plurality of planetary coaxial shafts 14 uniformly distributed around the first sun gear 12 and the second sun gear 13 are mounted in the planetary support 11 in the axial direction, and each of the planetary coaxial shafts 14 is provided with one a first planetary gear 15 for meshing with the first sun gear 12 and a second planetary gear 16 for meshing with the second sun gear 13; meanwhile, the first power motor b is placed on the front side of the planetary carrier 11 And being coaxially distributed with the planet carrier 11, and the power output shaft of the first power motor b is connected to the first sun gear 12; the second power motor c is placed on the rear side of the planet carrier 11 and coaxially distributed with the planet carrier 11, and Power of the second power motor c The output shaft is meshed with the second sun gear 13, and the power output gear d is mounted on the planet carrier 11.
- the first sun gear 12 can form a gear transmission effect by utilizing the power input from the first power motor b through its structural engagement relationship with the first planetary gear 15, since the first planetary gear 15 is mounted through the planetary coaxial shaft 14
- the planetary carrier 11 can finally drive the power output gear d to rotate through the planetary carrier 11.
- the second sun gear 13 can use the power input by the second power motor c to pass through the second planetary gear 16
- the structural engagement relationship between the two forms a gear transmission effect, so that the power output gear d can be finally rotated by the planetary carrier 11;
- the planetary gear mechanism a has two power source inputs (ie: the first power motor b and a second power motor c) forming a dual power shifting device; the entire shifting device can be finally achieved by logical control of the two power motors or by configuring a brake for each motor and an intermeshing constraint between the sun gear and the corresponding planet gear
- the following technical effects are formed: 1.
- the device By separately configuring a power motor having different (or the same) rotational speed or power parameters, starting separately When the motors are used, the device can obtain different gear ratios, thereby achieving the effect of shifting and shifting.
- the transmission effect of the planetary gear mechanism a can be used to form a power output multiplication effect, etc., to enhance the The speed of the drive mechanism; the shifting gear can be quickly and efficiently completed without the need to configure the clutch device throughout the process, effectively reducing the cost of the device in a specific application and the complexity of using the system. 2.
- the motor When running at low speed, the motor itself will slow down, but the output power of the two will be superimposed, which makes the device have high output torque, which is very suitable for starting, uphill or high load of the vehicle.
- Road conditions when the mid-speed gear is running, the brakes can be configured for the motor to achieve a moderate output speed and a relatively uniform torque. It is suitable for vehicles running at a uniform speed on a smooth municipal road; Since the rotational speeds of the two motor outputs can be superimposed by the gear mechanism, the output speed can be rapidly increased to provide conditions for the vehicle to travel at a high speed or at a high speed. 3.
- the two motors use the coaxial mechanism of the coaxial gear assembly to effectively enhance the structural integration of the device, achieve the effect of reducing the volume and weight, and facilitate the assembly and use of the device. 4, the entire device is suitable for applications such as electric cars, electric motorcycles, electric agricultural vehicles, electric trucks, wheel power shifts, energy-saving elevators, hydropower or wind power multi-stage coupling devices.
- the planetary carrier 11 of the present embodiment includes two bracket plates 111 which are vertically distributed forward and backward, and the first sun gear 12 and the second sun gear 13 are sequentially clamped from front to back. Between the two bracket plates 111, the front and rear ends of the planetary coaxial shaft 14 are respectively pivotally connected with the corresponding bracket plates 111, and the power output gear d is integrally assembled with one of the bracket plates 111.
- the structure of the planet carrier 11 it can be rendered similar to a frame-like open structure to facilitate disassembly or assembly of the various gears and associated components.
- a coupling bar is disposed between each adjacent two planetary coaxial shafts 14 112.
- the front and rear ends of the coupling rod 112 are respectively fixedly connected to the corresponding bracket plate 111.
- a central portion of the front end surface of the first sun gear 12 extends forward in the axial direction to form a through-through.
- the bracket plate 111 on the front side is distributed for the first power connection shaft 121 connected to the power output shaft of the first power motor b, and the first power connection shaft 121 is fitted with a first power connection shaft
- the rod 121 is in rotational contact with the bracket plate 111 on the front side of the first bearing A; at the same time, in the central portion of the rear end surface of the second sun gear 13, extending rearward in the axial direction, a bracket plate is formed through the rear side.
- the plate 111 serves as a second bearing B in rotational contact; and the first sun gear 12 and the second sun gear 13 are in rotational contact by a third bearing D.
- the power output gear d of the present embodiment is set on the first power connection shaft 121 and fixed on the front end surface of the planetary carrier 11 (specifically, on the bracket plate 111 on the front side), thereby reducing The volume of the entire device provides structural conditions.
- a differential e is further disposed between the power output gear d and the driven mechanism, and the differential e includes a power output gear.
- the d-phase meshing differential gear 21, the differential gear 21 is sleeved on a power output shaft 22, so that the power output shaft 22 can be structurally connected with the driven mechanism to drive the driven mechanism to operate.
- the utility model relates to the technical field of power control, in particular to a multi-speed multi-power planetary gear shifting device.
- a planetary gear transmission is a gearbox mainly composed of a planetary ring gear, a sun gear, a planetary gear (also called a satellite gear) and a gear shaft, which can be based on a planetary ring gear, a sun gear and a planetary gear.
- the output control is widely used in many industries such as fuel vehicles, electric vehicles, hydraulic and wind power equipment, construction machinery, civil appliances, military equipment and so on.
- the existing planetary gear transmission needs to be used in combination with a clutch in a practical application, that is, the output shaft of the clutch is used as an input shaft of the transmission to cut off or transmit the power input from the engine to the transmission through the clutch, thereby realizing the shifting shift. Therefore, the transmission also has the following problems in the actual use process: 1. Frequent starting of the clutch may cause serious heat generation phenomenon of the transmission due to friction between components, which affects the power performance and service life of the transmission; In the process of shifting and shifting, there will be frequent power interruption and rigid impact between structural parts, which seriously affects the use and experience of the transmission. 3. The transmission cannot achieve efficient switching effect of speed and torque. Moreover, the power output mode is single, the power input energy cannot be reasonably utilized, and the energy saving and environmental protection effects are poor. 4. The complex oil circuit and the circuit control mechanism need to be configured, which not only reduces the reliability of the transmission, but also increases the production and use cost of the transmission.
- a multi-speed multi-power planetary gear shifting device comprising a rear planetary gear mechanism, a front planetary gear mechanism and a power output gear;
- the pre-stage planetary gear mechanism includes an inner ring gear housing, a front stage planetary bracket mounted in the inner ring gear housing and coaxially distributed with the inner ring gear housing, and a front planetary bracket mounted in the front stage a front stage sun gear coaxially distributed with the front stage planet carrier;
- the front stage planet carrier is provided with a plurality of front stages that are evenly distributed around the front stage sun gear and simultaneously mesh with the ring gear case and the front stage sun gear a planetary gear, a central portion of the rear end surface of the ring gear case is provided with a power connection bushing, and a central portion of the rear end surface of the front stage sun gear is provided with a first power connection shaft extending through the power connection bushing.
- a central portion of the front end surface of the front stage planetary carrier is disposed with a front end surface extending through the inner ring gear case and is inserted into the rear stage planetary gear mechanism by the rear end side of the rear stage planetary gear mechanism to drive the rear stage planetary a second power connecting shaft for power output of the gear mechanism, wherein the first power connecting shaft is connected with a front stage planetary bracket by utilizing an meshing relationship between the front stage sun gear and the front stage planetary gear
- the first power motor and/or the power connection bushing connected to the second power connecting shaft rotates with a meshing relationship between the ring gear case and the front stage planetary gear to drive the second power connection through the front stage planet carrier a second power motor that rotates the shaft;
- a front end side of the rear stage planetary gear mechanism is provided with a third power motor for driving the rear stage planetary gear mechanism for power output, and the power output gear is mounted on the power output end of the planetary gear mechanism of the rear stage. on.
- the front stage planet carrier comprises a hollow body portion and a transition sleeve portion formed by a central portion of the rear end surface of the disk portion extending rearward in the axial direction, the body portion of the disk portion a plurality of planetary gear shaft mounting holes are circumferentially opened on the circumference wall, and each of the planetary gear shaft mounting holes is provided with a front stage planetary gear;
- the second power connecting shaft is formed by a front end surface of the disk body portion
- the central region is formed by extending forward in the axial direction, the front stage sun gear is disposed in the disk body portion, and the first power connection shaft is inserted through the transition sleeve portion.
- the front end portion of the front stage sun gear is provided with a first bearing for rotatingly contacting the front stage sun gear with the disk body portion
- the first power connection shaft is provided with two separate sleeves for respectively a second bearing for rotatingly contacting the first power connecting shaft with the disk portion and rotating the first power connecting shaft with the transition sleeve portion, wherein the front and rear ends of the disk portion are respectively provided with a a third bearing in which the disk portion is in rotational contact with the ring gear housing.
- the ring gear case includes an inner ring gear for meshing with the front stage planetary gear, a first ring gear flange located on the front side of the inner ring gear and integrated with the inner ring gear, and a second ring gear flange integrated with the inner ring gear and integrated with the inner ring gear, the third bearing being clamped between the first ring gear flange and the front end surface of the disc body portion and the second Between the ring gear flange and the rear end surface of the disk body portion, the power connection bushing is formed by extending a central portion of the rear end surface of the second ring gear flange in the axial direction, the second power The connecting shaft is distributed through the first ring gear flange.
- the rear stage planetary gear mechanism comprises a rear stage planetary carrier and a first rear stage sun gear and a second device which are sequentially arranged in the rear stage planetary carrier and are coaxially and parallelly distributed from each other in front to rear.
- a rear stage sun gear wherein the rear stage planetary carrier is provided with a plurality of rear stage planetary coaxial shafts uniformly distributed around the first rear stage sun gear and the second rear stage sun gear in the axial direction, each of which is a rear stage planetary coaxial shaft is provided with a first rear stage planetary gear for meshing with the first rear stage sun gear and a second rear stage planetary gear for meshing with the second rear stage sun gear;
- the third power motor is disposed on a front side of the rear stage planetary carrier and coaxially distributed with the rear stage planetary carrier, and the power output shaft of the third power motor is connected to the first rear stage sun gear; the second power The connecting shaft is coupled to the second rear stage sun gear, and the power output gear is fitted to the rear stage planet carrier.
- the rear stage planet carrier comprises two bracket plates which are arranged in front and rear relative to each other, and the first rear stage sun gear and the second rear stage sun gear are sequentially clamped between the two bracket plates from front to back.
- the front and rear ends of the rear planetary coaxial shaft are respectively rotatably connected to the corresponding bracket plates, and the power output gear is integrally assembled with one of the bracket plates, and the second power connecting shaft is located through The bracket plate on the rear side is connected to the second rear stage sun gear.
- a coupling rod is disposed between each adjacent two of the rear stage planetary coaxial shafts, and the front and rear ends of the coupling rod are respectively fixedly connected with the corresponding bracket plates.
- the front end surface central region of the first rear stage sun gear extends forward in the axial direction to form a distribution of the bracket plate extending through the front side for connection with the power output shaft of the third power motor.
- the stage power is connected to the shaft, and the rear stage power connection shaft is provided with a fourth bearing for rotatingly contacting the rear stage power connection shaft with the bracket plate on the front side, the first rear stage sun gear a second bearing is in rotational contact with the second rear stage sun gear, and the second power connecting shaft is provided with a sixth for rotationally contacting the second power connecting shaft with the bracket plate on the rear side. Bearing.
- a shift gear mechanism including a shifting shaft and a first shifting gear and a second shifting gear sequentially disposed on the shifting shaft in an axial direction of the shifting shaft, the first The shifting gear meshes with the power output gear, and the first shifting gear drives the second shifting gear to rotate synchronously through the shifting shaft.
- it further includes a differential gear that meshes with the second shifting gear, the differential gear being sleeved on a power take-off shaft.
- the utility model can achieve the following beneficial effects by selecting a plurality of power motors having different (or the same) power and speed parameters and utilizing the cooperation between the structural components:
- the entire device can obtain different gear ratios, thereby achieving shifting, stepless or more Level without shifting and other functions, and due to the shifting and changing of the entire device
- the gear is realized by the control of the power motor, and it is not necessary to configure the clutch for the device, so that the structural impact problem between the components during the shifting process can be avoided;
- Multiple power motors can switch different powers in time according to different usage conditions, and can be quickly switched under different conditions, so that the motor always works in the high efficiency range;
- the whole device can be formed into a structure with a circumferential multi-tooth distribution, which ensures uniform force of the device, thereby improving the power output efficiency and reducing the wear rate between components. , the amount of noise and the reduction of calorific value provide favorable structural conditions;
- the structure is simple and compact, and the power output effect of multi-speed shifting can be realized by the cooperation between a plurality of power motors, and the power output mode is variously variable and adjustable, and has strong practical value and market promotion value.
- FIG. 1 is a schematic view showing the driving principle between the mechanisms of the embodiment of the present invention.
- FIG. 2 is a schematic structural view of the main body of the embodiment of the present invention (1);
- Figure 3 is a schematic view of the structural assembly of the main body portion of the embodiment of the present invention (2);
- FIG. 4 is a schematic cross-sectional structural view of a main body portion of an embodiment of the present invention.
- FIG. 5 is a schematic structural view of a planetary gear mechanism of a front and a rear stage according to an embodiment of the present invention
- FIG. 6 is a schematic exploded view showing the structure of a front stage planetary gear mechanism according to an embodiment of the present invention.
- FIG. 7 is a schematic exploded view showing the structure of a planetary gear mechanism of a rear stage according to an embodiment of the present invention.
- rear stage planetary support 211, bracket plate; 212, coupling rod; 22, first rear stage sun gear; 221, rear stage power connection shaft; 23, second rear stage sun gear; 24, rear stage planet Coaxial shaft; 25, first rear stage planetary gear; 26, second rear stage planetary gear;
- A the first bearing
- B the second bearing
- D the fourth bearing
- E the fifth bearing
- F the sixth bearing
- G the third bearing.
- the present embodiment provides a multi-speed multi-power planetary gear shifting device comprising a rear planetary gear mechanism a, a front planetary gear mechanism b and a power output gear c;
- the front stage planetary gear mechanism b includes an inner ring gear housing 11, a front stage planetary bracket 12 mounted in the inner ring gear housing 11 and coaxially distributed with the inner ring gear housing 11, and a front mounting bracket
- the front stage sun gear 13 is disposed coaxially with the front stage planet carrier 12 in the stage planet carrier 12;
- the front stage planet carrier 12 is provided with a plurality of circumferentially arranged front sun gears 13 evenly distributed and simultaneously with the ring gear case 11
- the front stage planetary gear 14 meshing with the front stage sun gear 13 is provided with a power connection bushing 15 at a central portion of the rear end surface of the inner ring gear case 11, and a through hole is provided in a central portion of the rear end face of the front stage sun gear 13
- the first power connecting shaft 16 distributed by the power connecting s
- the first power connecting shaft 16 is connected with a second power connecting shaft through the front stage planetary carrier 12 by the meshing relationship between the front stage sun gear 13 and the front stage planetary gear 14
- the first power motor d and/or the power connection bushing 15 for rotating the rod 17 are connected by a meshing relationship between the ring gear housing 11 and the front stage planetary gear 14 to drive the second power connecting shaft through the front stage planetary carrier 12.
- a second power motor e that rotates; at the same time, a third power motor f for driving the rear stage planetary gear mechanism a for power output is mounted on the front end side of the rear stage planetary gear mechanism a, and the power output gear c It is mounted on the power output end of the planetary gear mechanism a of the rear stage.
- At least one front stage power motor ie, the first power motor d and/or the second power motor e may be used, and the two may be separately set or may be simultaneously set.
- the two front stage power motors may be The coaxial central motor is used to realize the effect of the dual-power coaxial output.
- the power input source of the pre-stage planetary gear mechanism b the power output end of the pre-stage planetary gear mechanism b and the third power motor f are utilized.
- a multi-speed gear shifting device of the multi-power motor can be formed by combining with the transmission performance of the planetary gear mechanism itself, that is,
- the first power motor d inputs power through the first power connection shaft 16 to the front stage sun gear 13, and drives each of the front stage planetary gears 14 by the structural meshing relationship between the front stage sun gear 13 and the front stage planetary gear 14. Since the front stage planetary gear 14 is mounted on the front stage planetary carrier 12, the front stage planetary carrier 12 is further driven to revolve around the axis, thereby using the second power to connect the shaft 17 to the rear stage planet.
- the gear mechanism a inputs power;
- the second power motor e can drive the ring gear case 11 to rotate by the power connection bushing 15, and drive each of the front stage planetary gears 14 by the structural meshing relationship between the ring gear case 11 and the front stage planetary gear 14. Rotation, based on the same driving principle as the first power motor d, to finally input power to the rear stage planetary gear mechanism a through the second power connecting shaft 17;
- the power output from the third power motor f and the front planetary gear mechanism b can be simultaneously used to form two power transmissions.
- the power output gear c mounted on the power output end of the planetary gear mechanism a of the rear stage is finally utilized as a component of the power output of the entire apparatus.
- the shifting device of the embodiment can achieve the following beneficial effects: 1. Based on the structural features of the plurality of power motors of the entire device, by selecting a power motor having different (or the same) power and speed parameters, the entire The device obtains different gear ratios to achieve functions such as shifting, stepless shifting or multi-step shifting, and since the shifting and shifting of the entire device is achieved by controlling the power motor, there is no need to configure the clutch for the device. It can avoid the structural impact problem between components during the shifting process; 2. Multiple power motors can switch different powers according to different usage conditions, and can switch jobs quickly under different conditions, so that the motor is always efficient. Working in the segment area; 3.
- the front stage planetary carrier 12 of the present embodiment includes a hollow body portion 121 and a disk portion 121.
- a transition sleeve portion 122 formed by extending a central portion of the rear end surface rearward in the axial direction, a plurality of planetary gear shaft mounting holes 123 are circumferentially opened on the peripheral wall of the disk portion 122, and each of the planetary gear shaft mounting holes 123 is provided with a front stage planetary gear 14; and the second power connecting shaft 17 is formed by extending a central portion of the front end surface of the disk portion 121 in the axial direction, and the front stage sun gear 13 is placed on the disk.
- the first power connection shaft 16 is distributed through the transition sleeve portion 122.
- the ring gear housing, the planetary gears and the sun gear can be in a relatively concentric distribution state, and the solar gear and the planetary gears can be relatively sealed. Structure space.
- a front end portion of the front stage sun gear 13 is provided with a front sun gear 13 and a disk portion 121.
- the first bearing A for rotational contact is provided with two on the first power connection shaft 16 for respectively rotating the first power connection shaft 16 with the disk portion 121 and connecting the first power connection shaft 16
- the second bearing B in rotational contact with the transition sleeve portion 122 is provided with a third bearing G for rotationally contacting the disk portion 121 and the ring gear housing 11 at the front and rear ends of the disk portion 121, respectively.
- the ring gear housing 11 of the present embodiment includes an inner ring gear 111 for meshing with the front stage planetary gear 14, and is located at the inner tooth.
- the third bearing G is sandwiched between the first ring gear flange 112 and the front end surface of the disk portion 121 and between the second ring gear flange 113 and the rear end surface of the disk portion 121, and the power connection bushing is 15 is formed by extending a central portion of the rear end surface of the second ring gear flange 113 rearward in the axial direction, and the second power connecting shaft 17 is distributed through the first ring gear flange 112.
- the rear stage planetary gear mechanism a of the present embodiment includes a rear stage planetary carrier 21 and first rear stage sun gears 22 which are sequentially disposed in the rear stage planetary carrier 21 from front to rear and are coaxially and in parallel with each other.
- the rod 24 is provided with a first rear stage planetary gear 25 for meshing with the first rear stage sun gear 22 and a second rear stage sun gear 23 on each of the rear stage planetary coaxial shafts 24.
- the second rear stage planetary gear 26 is engaged; at the same time, the third power motor f is placed on the front side of the rear stage planetary carrier 21 and coaxially distributed with the rear stage planetary carrier 21, and the power output shaft of the third power motor f is First rear stage sun gear 22 Company; and a second drive coupling shaft 17 connected to the second-stage sun gear 23, the power output gear set to the rear stage c planet carrier 21.
- the second rear stage sun gear 23 can form a gear transmission effect by the structural engagement relationship between the power input from the front stage planetary gear mechanism b and the second rear stage planetary gear 26,
- the second stage planetary gear 26 is mounted on the rear stage planet carrier 21 through the rear stage planetary coaxial shaft 24, so that the power output gear c can be finally rotated by the rear stage planetary carrier 21, based on the same reason, first
- the rear stage sun gear 22 can use the power input by the third power motor f to form a gear transmission effect through its structural meshing relationship with the first rear stage planetary gear 25, since the first rear stage planetary gear 25 is also passed through the rear stage planetary
- the coaxial shaft 24 is mounted on the rear stage planet carrier 21, so that the power output gear c can be finally rotated by the rear stage planetary carrier 21; the third power motor f and the front stage planetary gear can be controlled by logic control.
- the mechanism b separately performs power input to finally form different power output effects, and the two can simultaneously perform power input through the cooperation of the brakes, and utilize the function of gear meshing to form power superposition (acceleration), deceleration, braking, and the like. A variety of output effects.
- the rear stage planetary carrier 21 of the present embodiment includes two bracket plates 211 which are vertically distributed back and forth, the first rear stage sun gear 22 and the second rear stage sun gear. 23 is sequentially clamped between the two bracket plates 211 from front to back, and the front and rear ends of the rear planetary coaxial shaft 24 are respectively pivotally connected with the corresponding bracket plates 211, and the power output gear c and one of the brackets are respectively
- the plate 211 is assembled as one body, and the second power connection shaft 17 is connected to the second rear stage sun gear 23 through the bracket plate 211 on the rear side.
- the rear stage planet carrier 21 is a component that provides an assembly position for the power output gear c and needs to be operated by itself, in order to ensure its structural stability, it is also disposed between each adjacent two rear stage planetary coaxial shafts 24 There is a coupling rod 212, and the front and rear ends of the coupling rod 212 are respectively fixedly connected with the corresponding bracket plate 211.
- a central portion of the front end surface of the first rear stage sun gear 22 extends forward in the axial direction to form a bracket plate 211 penetrating the front side.
- the rear stage power connection shaft 221 is distributed for the power output shaft of the third power motor f, and the rear stage power connection shaft 221 is provided with a rear power connection shaft 221 and a front side.
- the fourth bearing D of the bracket plate 211 is in rotational contact, the first rear stage sun The gear 22 and the second rear stage sun gear 23 are in rotational contact with a fifth bearing E.
- the second power connecting shaft 17 is provided with a bracket plate 211 for connecting the second power connecting shaft 17 with the rear side.
- the sixth bearing F is in rotational contact.
- a shift gear mechanism g is further disposed between the power output gear c and the driven member, and the shift gear mechanism g mainly includes a shift shaft 31 and The first shifting gear 32 and the second shifting gear 33 are sequentially fitted on the shifting shaft 31 in the axial direction of the shifting shaft 31, and the first shifting gear 32 meshes with the power output gear c, whereby the first shifting gear can be utilized 32, the second shifting gear 33 is driven to rotate synchronously by the shifting shaft 31, and the driven member is connected by the second shifting gear 33, and the number of teeth of the first shifting gear 32 is not equal to the number of teeth of the second shifting gear 33, thereby realizing the transmission. Ratio change output.
- a differential h is further disposed between the transmission gear mechanism g and the driven member, and the differential h includes a differential gear 41 that meshes with the second shifting gear 33, and the differential gear 41 is sleeved. On a power output shaft 42. Thereby, the output rotational speed of the device can be further adjusted by the differential gear 41 to drive the driven member to operate by the power output shaft 42.
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Abstract
Disclosed is a dual-power planetary speed changing device of a type other than a Ravigneaux type, the device comprising a first power motor (b), a second power motor (c), a power output gear (d), and a planetary gear mechanism (a) composed of a planetary carrier (11), a first sun gear (12), a second sun gear (13), a first planetary gear (15) and a second planetary gear (16), wherein the first power motor (b) is arranged at a front side of the planetary carrier (11), and a power output shaft of the first power motor is connected to the first sun gear (12); and the second power motor (c) is arranged at a rear side of the planetary carrier (11), a power output shaft of the second power motor is meshed with the second sun gear (13), and the power output gear (d) is assembled on the planetary carrier (11). By selectively providing two power motors with different or identical rotational speed(s) and power parameters as power sources of the device, according to different circumstances, the logical control over the two power motors or the provision of a brake can enable the device to obtain different rotational speed ratios or power output modes, thereby achieving functions such as speed changing and gear shifting of the device.
Description
本实用新型涉及动力控制技术领域,尤其是一种非拉威挪式双动力行星齿轮变速装置。The utility model relates to the technical field of power control, in particular to a non-Raphaelno type dual-power planetary gear shifting device.
电动车是以车载动力蓄电池为动力驱动电动车辆行驶,由于电动车具有节能、环保、轻便、费用较低等特点,越来越受重视。但是,由于电动机的功率以及输出扭矩等相比发动机较差,为解决电动车的动力不足的问题,较多的小型车采用混合动力结构,体积较大且能量利用率不高;现有的电动车变速器在实际应用中需要与离合器进行配合使用,离合器频繁的启动会造成变速器因部件之间的摩擦而出现严重的发热现象,影响了变速器的动力性能和使用寿命;在换挡变速过程中经常会出现动力中断现象及结构件之间刚性冲击现象,严重影响了变速器的使用和体验效果;变速器无法实现速度与扭力的高效切换效果,且动力输出模式单一,无法高效利用动力输入能源,达到高效的节能环保目的;配置的油路及电路控制机构复杂,降低了变速器的可靠性,且增加了变速器的生产及使用成本。
The electric vehicle is driven by the vehicle power battery as the electric vehicle. Because the electric vehicle has the characteristics of energy saving, environmental protection, light weight and low cost, it is more and more valued. However, since the power and output torque of the motor are poor compared to the engine, in order to solve the problem of insufficient power of the electric vehicle, many small cars adopt a hybrid structure, which is large in size and low in energy utilization rate; the existing electric power In practical applications, the vehicle transmission needs to be used in conjunction with the clutch. Frequent starting of the clutch will cause serious heat generation in the transmission due to friction between the components, affecting the power performance and service life of the transmission; There will be a power interruption phenomenon and a rigid impact between structural parts, which seriously affects the use and experience of the transmission; the transmission cannot achieve efficient switching of speed and torque, and the power output mode is single, and the power input energy cannot be utilized efficiently, achieving high efficiency. The purpose of energy saving and environmental protection; the complicated oil circuit and circuit control mechanism are configured, which reduces the reliability of the transmission and increases the production and use cost of the transmission.
针对上述现有技术存在的不足,本实用新型的目的在于提供一种非拉威挪式双动力行星齿轮变速装置。In view of the deficiencies of the prior art described above, it is an object of the present invention to provide a non-Raphaelno type dual power planetary gear shifting device.
为了实现上述目的,本实用新型采用如下技术方案:In order to achieve the above object, the utility model adopts the following technical solutions:
一种非拉威挪式双动力行星齿轮变速装置,它包括一行星系齿轮机构、一第一动力马达、一第二动力马达和一动力输出齿轮;A non-Raphaelno type dual-power planetary gear shifting device comprising a planetary gear mechanism, a first power motor, a second power motor and a power output gear;
所述行星系齿轮机构包括一行星支架以及由前至后顺序地装设于行星支架内且相互间呈同轴并行分布的第一太阳齿轮和第二太阳齿轮,所述行星支架内沿轴向方向装设有若干根环绕第一太阳齿轮和第二太阳齿轮均匀分布的行星同轴轴杆,每根所述行星同轴轴杆上均套装有一用于与第一太阳齿轮相啮合的第一行星齿轮和一用于与第二太阳齿轮相啮合的第二行星齿轮;The planetary gear mechanism includes a planet carrier and a first sun gear and a second sun gear which are sequentially disposed in the planetary carrier from front to back and are coaxially and in parallel with each other, and the planetary carrier is axially axially The direction is provided with a plurality of planetary coaxial shafts evenly distributed around the first sun gear and the second sun gear, and each of the planetary coaxial shafts is provided with a first mesh for meshing with the first sun gear a planetary gear and a second planetary gear for meshing with the second sun gear;
所述第一动力马达置于行星支架的前方侧并与行星支架同轴分布,且所述第一动力马达的动力输出轴与第一太阳齿轮相连;所述第二动力马达置于行星支架的后方侧并与行星支架同轴分布,且所述第二动力马达的动力输出轴与第二太阳齿轮相啮合,所述动力输出齿轮装配于行星支架上。The first power motor is disposed on a front side of the planet carrier and coaxially distributed with the planet carrier, and a power output shaft of the first power motor is coupled to the first sun gear; the second power motor is disposed on the planet carrier The rear side is coaxially distributed with the planet carrier, and the power output shaft of the second power motor is meshed with the second sun gear, and the power output gear is mounted on the planet carrier.
优选地,所述行星支架包括两块呈前后相对分布的支架板,所述第一太阳齿轮和第二太阳齿轮由前至后顺序地夹持于两块支架板之间,所述行星同轴轴杆的前后两端分别与相对应的支架板轴转连接,所述动力输出齿轮与其中一块支架板装配为一体。Preferably, the planet carrier comprises two bracket plates which are arranged in front and rear relative to each other, and the first sun gear and the second sun gear are sequentially clamped between the two bracket plates from front to back, the planetary coaxial The front and rear ends of the shaft are respectively rotatably coupled to the corresponding bracket plates, and the power output gears are integrally assembled with one of the bracket plates.
优选地,每相邻的两根所述行星同轴轴杆之间还设置有一根联轴杆,所述联轴杆的前后两端分别与对应的支架板作固定连接。Preferably, a coupling rod is disposed between each adjacent two of the planetary coaxial shafts, and the front and rear ends of the coupling rod are respectively fixedly connected with the corresponding bracket plates.
优选地,所述第一太阳齿轮的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板分布以用于与第一动力马达的动力输出轴相连的第一动力连接轴杆,且所述第一动力连接轴杆上套装有一将第一动力连接轴杆与位于前方侧的支架板作转动接触的第一轴承;Preferably, the front end surface central region of the first sun gear extends forward in the axial direction to form a first power that is distributed through the bracket plate on the front side for connection with the power output shaft of the first power motor. Connecting a shaft, and the first power connecting shaft is provided with a first bearing for rotatingly contacting the first power connecting shaft with the bracket plate on the front side;
所述第二太阳齿轮的后端面中心区域沿轴向方向向后延伸后形成有一贯穿于位于后方侧的支架板分布以用于与第二动力马达的动力输出轴相连的第二动力连接轴杆,且所述第二动力连接轴杆上套装有一将第二动力连接轴杆与位于后方侧的支架板作转动接触的第二轴承;a central portion of the rear end surface of the second sun gear extends rearward in the axial direction to form a second power connection shaft extending through the bracket plate on the rear side for connection with the power output shaft of the second power motor And the second power connecting shaft is provided with a second bearing for rotatingly contacting the second power connecting shaft with the bracket plate at the rear side;
所述第一太阳齿轮与第二太阳齿轮之间通过一第三轴承作转动接触。 The first sun gear and the second sun gear are in rotational contact by a third bearing.
优选地,所述动力输出齿轮套装于第一动力连接轴杆上并固定于行星支架的前端面上。Preferably, the power output gear is sleeved on the first power connection shaft and fixed to the front end surface of the planet carrier.
优选地,它还包括一与动力输出齿轮相啮合的差速齿轮,所述差速齿轮套接于一动力输出轴上。Preferably, it further includes a differential gear that meshes with the power output gear, the differential gear being sleeved on a power output shaft.
由于采用了上述方案,本实用新型通过选配两个具有不同(或相同)转速和功率参数的动力马达作为装置的动力源,根据不同的情况通过对两个动力马达的逻辑控制或者配置制动器可使装置得到不同的转速比或动力输出模式,实现装置的变速、换挡等功能;其结构简单紧凑、适用范围广,通过两个动力马达之间的配合可实现多档变速的动力输出效果,且动力输出模式多样可变可调,无需配置离合器等,具有很强的实用价值和市场推广价值。Due to the adoption of the above scheme, the utility model selects two power motors with different (or the same) rotational speed and power parameters as the power source of the device, and according to different situations, the logic control or the brakes of the two power motors can be adopted. The device can obtain different speed ratio or power output mode to realize the functions of shifting and shifting of the device; the structure is simple and compact, and the application range is wide. The power output effect of the multi-speed shift can be realized by the cooperation between the two power motors. And the power output mode is variable and adjustable, no need to configure the clutch, etc., and has strong practical value and market promotion value.
图1是本实用新型实施例的各机构间的驱动关系示意图;1 is a schematic view showing the driving relationship between the mechanisms of the embodiment of the present invention;
图2是本实用新型实施例的主体部分的结构装配示意图(一);2 is a schematic structural view of the main body of the embodiment of the present invention (1);
图3是本实用新型实施例的主体部分的结构装配示意图(二);Figure 3 is a schematic view of the structural assembly of the main body portion of the embodiment of the present invention (2);
图4是本实用新型实施例的主体部分的截面结构示意图;4 is a schematic cross-sectional structural view of a main body portion of an embodiment of the present invention;
图5是本实用新型实施例的行星系齿轮机构的结构分解示意图;5 is a schematic exploded view showing the structure of a planetary gear mechanism according to an embodiment of the present invention;
图中:In the picture:
a、行星系齿轮机构;b、第一动力马达;c、第二动力马达;d、动力输出齿轮;e、差速器;a, planetary gear mechanism; b, first power motor; c, second power motor; d, power output gear; e, differential;
11、行星支架;111、支架板;112、联轴杆;12、第一太阳齿轮;121、第一动力连接轴杆;13、第二太阳齿轮;131、第二动力连接轴杆;14、行星同轴轴杆;15、第一行星齿轮;16、第二行星齿轮;11. Planetary support; 111, support plate; 112, coupling shaft; 12, first sun gear; 121, first power connection shaft; 13, second sun gear; 131, second power connection shaft; a planetary coaxial shaft; 15, a first planetary gear; 16, a second planetary gear;
21、差速齿轮;22、动力输出轴;21, differential gear; 22, power output shaft;
A、第一轴承;B、第二轴承;D、第三轴承。A, the first bearing; B, the second bearing; D, the third bearing.
以下结合附图对本实用新型的实施例进行详细说明,但是本实用新型可以由权利要求限定和覆盖的多种不同方式实施。The embodiments of the present invention are described in detail below with reference to the accompanying drawings, but the present invention can be implemented in various different ways as defined and covered by the claims.
如图1至图5所示,本实施例提供的一种非拉威挪式双动力行星齿轮变速装置,它包括一行星系齿轮机构a、一第一动力马达b、一第二动力马达c和一动力输出齿轮e;其中,行星系齿轮机构包括一行星支架11以及由前至后顺序地装设于行星支架11内且相互间呈同轴并行分布的第一太阳齿轮12和第二太阳齿轮13,在行星支架11内沿轴向方向装设有若干根环绕第一太阳齿轮12和第二太阳齿轮13均匀分布的行星同轴轴杆14,每根行星同轴轴杆14上均套装有一用于与第一太阳齿轮12相啮合的第一行星齿轮15和一用于与第二太阳齿轮13相啮合的第二行星齿轮16;同时,第一动力马达b置于行星支架11的前方侧并与行星支架11同轴分布,且第一动力马达b的动力输出轴与第一太阳齿轮12相连;第二动力马达c置于行星支架11的后方侧并与行星支架11同轴分布,且第二动力马达c的动力输出轴与第二太阳齿轮13相啮合,而动力输出齿轮d则装配于行星支架11上。As shown in FIG. 1 to FIG. 5, the non-Raphaelno type dual-power planetary gear shifting device provided by the embodiment includes a planetary gear mechanism a, a first power motor b, a second power motor c, and a power output gear e; wherein the planetary gear mechanism includes a planet carrier 11 and a first sun gear 12 and a second sun gear that are sequentially disposed in the planetary carrier 11 from front to back and are coaxially and in parallel with each other 13. A plurality of planetary coaxial shafts 14 uniformly distributed around the first sun gear 12 and the second sun gear 13 are mounted in the planetary support 11 in the axial direction, and each of the planetary coaxial shafts 14 is provided with one a first planetary gear 15 for meshing with the first sun gear 12 and a second planetary gear 16 for meshing with the second sun gear 13; meanwhile, the first power motor b is placed on the front side of the planetary carrier 11 And being coaxially distributed with the planet carrier 11, and the power output shaft of the first power motor b is connected to the first sun gear 12; the second power motor c is placed on the rear side of the planet carrier 11 and coaxially distributed with the planet carrier 11, and Power of the second power motor c The output shaft is meshed with the second sun gear 13, and the power output gear d is mounted on the planet carrier 11.
第一太阳齿轮12可利用第一动力马达b输入的动力通过其与第一行星齿轮15之间的结构啮合关系形成齿轮传动效应,由于第一行星齿轮15是通过行星同轴轴杆14装设于行星支架11上的,故可最终通过行星支架11带动动力输出齿轮d进行转动,基于同理,第二太阳齿轮13可利用第二动力马达c输入的动力通过其与第二行星齿轮16之间的结构啮合关系形成齿轮传动效应,故也可最终通过行星支架11带动动力输出齿轮d进行转动;基于此,行星系齿轮机构a具备两个动力源输入端(即:第一动力马达b和第二动力马达c),形成双动力变速装置;通过对两个动力马达的逻辑控制或者为每个马达配置制动器以及太阳齿轮与对应的行星齿轮之间的相互啮合约束,可最终使整个变速装置形成以下技术效果:1、通过配置具有不同(或相同)转速或功率参数的动力马达,在单独启动其中一个马达时,可使装置得到不同的变速比,进而实现换挡变速的效果,在同时启动两个马达时,通过行星系齿轮 机构a的传动效应,可形成动力输出倍增等效果,以提升被驱动机构的速度;在整个过程中无需配置离合装置,即可快速有效地完成换挡变速的目的,有效地降低了装置在具体应用时的使用成本以及使用其系统的复杂性。2、在进行低速档运行时,由于马达本身会降速运转,但两者的输出动力会被最终叠加,从而使得装置具备较高的输出扭力,极其适合车辆的起步、上坡或者高载的路况;当进行中速档运行时,则可通过为马达配置制动器等,来实现装置输出速度适中、扭力相对平均的效果,适合车辆在平缓的市政道路上匀速行驶;而在进行高速档运行时,由于两个马达输出的转速可通过齿轮机构进行叠加,故输出速度可得到迅速提升,从而为车辆的快速或高速行驶提供条件。3、两个马达利用齿轮机构采用同轴双边装配的行驶,可有效增强装置的结构集成度,达到减小体积及重量的效果,便于装置的装配使用。4、整个装置适合应用于诸如电动小车、电动摩托车、电动农用车、电动货车、轮毂动力变速、节能电梯、水电或风电多级耦合装置等诸多领域。The first sun gear 12 can form a gear transmission effect by utilizing the power input from the first power motor b through its structural engagement relationship with the first planetary gear 15, since the first planetary gear 15 is mounted through the planetary coaxial shaft 14 The planetary carrier 11 can finally drive the power output gear d to rotate through the planetary carrier 11. For the same reason, the second sun gear 13 can use the power input by the second power motor c to pass through the second planetary gear 16 The structural engagement relationship between the two forms a gear transmission effect, so that the power output gear d can be finally rotated by the planetary carrier 11; based on this, the planetary gear mechanism a has two power source inputs (ie: the first power motor b and a second power motor c) forming a dual power shifting device; the entire shifting device can be finally achieved by logical control of the two power motors or by configuring a brake for each motor and an intermeshing constraint between the sun gear and the corresponding planet gear The following technical effects are formed: 1. By separately configuring a power motor having different (or the same) rotational speed or power parameters, starting separately When the motors are used, the device can obtain different gear ratios, thereby achieving the effect of shifting and shifting. When the two motors are started at the same time, the transmission effect of the planetary gear mechanism a can be used to form a power output multiplication effect, etc., to enhance the The speed of the drive mechanism; the shifting gear can be quickly and efficiently completed without the need to configure the clutch device throughout the process, effectively reducing the cost of the device in a specific application and the complexity of using the system. 2. When running at low speed, the motor itself will slow down, but the output power of the two will be superimposed, which makes the device have high output torque, which is very suitable for starting, uphill or high load of the vehicle. Road conditions; when the mid-speed gear is running, the brakes can be configured for the motor to achieve a moderate output speed and a relatively uniform torque. It is suitable for vehicles running at a uniform speed on a smooth municipal road; Since the rotational speeds of the two motor outputs can be superimposed by the gear mechanism, the output speed can be rapidly increased to provide conditions for the vehicle to travel at a high speed or at a high speed. 3. The two motors use the coaxial mechanism of the coaxial gear assembly to effectively enhance the structural integration of the device, achieve the effect of reducing the volume and weight, and facilitate the assembly and use of the device. 4, the entire device is suitable for applications such as electric cars, electric motorcycles, electric agricultural vehicles, electric trucks, wheel power shifts, energy-saving elevators, hydropower or wind power multi-stage coupling devices.
为便于对行星齿轮机构a进行拆装维护,本实施例的行星支架11包括两块呈前后相对分布的支架板111,第一太阳齿轮12和第二太阳齿轮13由前至后顺序地夹持于两块支架板111之间,行星同轴轴杆14的前后两端分别与相对应的支架板111轴转连接,而动力输出齿轮d则与其中一块支架板111装配为一体。由此,通过对行星支架11的结构优化,可使其呈现出类似于框架式的开放结构,以便于对各个齿轮及相关部件进行拆卸或装配。In order to facilitate the disassembly and maintenance of the planetary gear mechanism a, the planetary carrier 11 of the present embodiment includes two bracket plates 111 which are vertically distributed forward and backward, and the first sun gear 12 and the second sun gear 13 are sequentially clamped from front to back. Between the two bracket plates 111, the front and rear ends of the planetary coaxial shaft 14 are respectively pivotally connected with the corresponding bracket plates 111, and the power output gear d is integrally assembled with one of the bracket plates 111. Thus, by optimizing the structure of the planet carrier 11, it can be rendered similar to a frame-like open structure to facilitate disassembly or assembly of the various gears and associated components.
由于行星支架11是为动力输出齿轮d提供装配位置的部件且其本身需要进行动作,为保证其结构稳固性,每相邻的两根行星同轴轴杆14之间还设置有一根联轴杆112,联轴杆112的前后两端分别与对应的支架板111作固定连接。Since the planetary carrier 11 is a component that provides an assembly position for the power output gear d and needs to be operated by itself, in order to ensure structural stability, a coupling bar is disposed between each adjacent two planetary coaxial shafts 14 112. The front and rear ends of the coupling rod 112 are respectively fixedly connected to the corresponding bracket plate 111.
为保证行星系齿轮机构a的顺畅运转,同时优化其结构并为其与动力马达的快速装配提供便利条件,在第一太阳齿轮12的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板111分布以用于与第一动 力马达b的动力输出轴相连的第一动力连接轴杆121,且在第一动力连接轴杆121上套装有一将第一动力连接轴杆121与位于前方侧的支架板111作转动接触的第一轴承A;同时,在第二太阳齿轮13的后端面中心区域沿轴向方向向后延伸后形成有一贯穿于位于后方侧的支架板111分布以用于与第二动力马达c的动力输出轴相连的第二动力连接轴杆131,且第二动力连接轴杆131上套装有一将第二动力连接轴杆131与位于后方侧的支架板111作转动接触的第二轴承B;而第一太阳齿轮12与第二太阳齿轮13之间则通过一第三轴承D作转动接触。In order to ensure the smooth operation of the planetary gear mechanism a, while optimizing its structure and providing a convenient condition for its rapid assembly with the power motor, a central portion of the front end surface of the first sun gear 12 extends forward in the axial direction to form a through-through. The bracket plate 111 on the front side is distributed for the first power connection shaft 121 connected to the power output shaft of the first power motor b, and the first power connection shaft 121 is fitted with a first power connection shaft The rod 121 is in rotational contact with the bracket plate 111 on the front side of the first bearing A; at the same time, in the central portion of the rear end surface of the second sun gear 13, extending rearward in the axial direction, a bracket plate is formed through the rear side. 111 is distributed for the second power connection shaft 131 connected to the power output shaft of the second power motor c, and the second power connection shaft 131 is provided with a bracket for the second power connection shaft 131 and the rear side. The plate 111 serves as a second bearing B in rotational contact; and the first sun gear 12 and the second sun gear 13 are in rotational contact by a third bearing D.
作为一个优选方案,本实施例的动力输出齿轮d套装于第一动力连接轴杆121上并固定于行星支架11的前端面上(具体为位于前方侧的支架板111上),从而为减小整个装置的体积提供结构条件。As a preferred embodiment, the power output gear d of the present embodiment is set on the first power connection shaft 121 and fixed on the front end surface of the planetary carrier 11 (specifically, on the bracket plate 111 on the front side), thereby reducing The volume of the entire device provides structural conditions.
为能够对装置输出的动力作进一步变换处理,以实现最终的动力输出效果,在动力输出齿轮d与被驱动机构之间还装设一差速器e,差速器e包括一与动力输出齿轮d相啮合的差速齿轮21,差速齿轮21套接于一动力输出轴22上,以利用动力输出轴22可与被驱动机构进行结构连接,以带动被驱动机构进行动作。In order to further transform the power outputted by the device to achieve the final power output effect, a differential e is further disposed between the power output gear d and the driven mechanism, and the differential e includes a power output gear. The d-phase meshing differential gear 21, the differential gear 21 is sleeved on a power output shaft 22, so that the power output shaft 22 can be structurally connected with the driven mechanism to drive the driven mechanism to operate.
以上所述仅为本实用新型的优选实施例,并非因此限制本实用新型的专利范围,凡是利用本实用新型说明书及附图内容所作的等效结构或等效流程变换,或直接或间接运用在其他相关的技术领域,均同理包括在本实用新型的专利保护范围内。The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the patent of the present invention. Any equivalent structure or equivalent process transformation using the specification and the drawings of the present invention may be directly or indirectly applied to Other related technical fields are equally included in the scope of patent protection of the present invention.
一种多档多动力行星齿轮变速装置Multi-speed multi-power planetary gear shifting device
本实用新型涉及动力控制技术领域,尤其是一种多档多动力行星齿轮变速装置。The utility model relates to the technical field of power control, in particular to a multi-speed multi-power planetary gear shifting device.
众所周知,行星齿轮变速器是一种主要由行星齿圈、太阳齿轮、行星齿轮(又称卫星齿轮)和齿轮轴等部件组成的齿轮箱,其可根据行星齿圈、太阳齿轮和行星齿轮之间的运动关系来实现诸如输入轴与输出轴之间脱离刚性传动关系、输入轴与输出轴之间的同向或反向传动关系以及输入轴与输出轴之间传动比关系的改变,来达到对动力输出的控制,被广泛应用于诸如燃油汽车、电动汽车、水力及风力发电设备、工程机械、民用电器、军用装备等诸多行业领域内。As we all know, a planetary gear transmission is a gearbox mainly composed of a planetary ring gear, a sun gear, a planetary gear (also called a satellite gear) and a gear shaft, which can be based on a planetary ring gear, a sun gear and a planetary gear. The relationship of motion to achieve a dynamic transmission relationship between the input shaft and the output shaft, a co-rotation or reverse transmission relationship between the input shaft and the output shaft, and a change in the transmission ratio between the input shaft and the output shaft to achieve power The output control is widely used in many industries such as fuel vehicles, electric vehicles, hydraulic and wind power equipment, construction machinery, civil appliances, military equipment and so on.
现有的行星齿轮变速器在实际应用中需要与离合器进行配合使用,即利用离合器的输出轴作为变速器的输入轴,以通过离合器切断或传递发动机向变速器输入的动力,从而实现换挡变速。由此,也导致变速器在实际使用的过程中普遍存在如下问题:1、离合器频繁的启动会造成变速器因部件之间的摩擦而出现严重的发热现象,影响了变速器的动力性能和使用寿命;2、在换挡变速的过程中会出现经常性的动力中断的现象以及结构件之间刚性冲击的现象,严重影响了变速器的使用和体验效果;3、变速器无法实现速度与扭力的高效切换效果,且动力输出模式单一,无法合理地利用动力输入能源,节能环保效果差;4、需要配置复杂的油路及电路控制机构,不但降低了变速器的可靠性,而且增加了变速器的生产及使用成本。The existing planetary gear transmission needs to be used in combination with a clutch in a practical application, that is, the output shaft of the clutch is used as an input shaft of the transmission to cut off or transmit the power input from the engine to the transmission through the clutch, thereby realizing the shifting shift. Therefore, the transmission also has the following problems in the actual use process: 1. Frequent starting of the clutch may cause serious heat generation phenomenon of the transmission due to friction between components, which affects the power performance and service life of the transmission; In the process of shifting and shifting, there will be frequent power interruption and rigid impact between structural parts, which seriously affects the use and experience of the transmission. 3. The transmission cannot achieve efficient switching effect of speed and torque. Moreover, the power output mode is single, the power input energy cannot be reasonably utilized, and the energy saving and environmental protection effects are poor. 4. The complex oil circuit and the circuit control mechanism need to be configured, which not only reduces the reliability of the transmission, but also increases the production and use cost of the transmission.
因此,有必要对现有的行星齿轮变速器提出改进方案,以最大限度地提升变速器的性能并满足实际应用过程中的实际需求。
Therefore, it is necessary to propose an improvement to the existing planetary gear transmission to maximize the performance of the transmission and meet the actual needs in the actual application process.
针对上述现有技术存在的不足,本实用新型的目的在于提供一种多档多动力行星齿轮变速装置。In view of the deficiencies of the prior art described above, it is an object of the present invention to provide a multi-speed multi-power planetary gear shifting device.
为了实现上述目的,本实用新型采用如下技术方案:In order to achieve the above object, the utility model adopts the following technical solutions:
一种多档多动力行星齿轮变速装置,它包括一后级行星系齿轮机构、前级行星系齿轮机构和一动力输出齿轮;A multi-speed multi-power planetary gear shifting device comprising a rear planetary gear mechanism, a front planetary gear mechanism and a power output gear;
所述前级行星系齿轮机构包括一内齿圈壳、一装设于内齿圈壳内并与内齿圈壳呈同轴分布的前级行星支架以及一装设于前级行星支架内并与前级行星支架呈同轴分布的前级太阳齿轮;所述前级行星支架上装设有若干个环绕前级太阳齿轮均匀分布并同时与内齿圈壳和前级太阳齿轮相啮合的前级行星齿轮,所述内齿圈壳的后端面的中心区域设置有一动力连接轴套,所述前级太阳齿轮的后端面的中心区域设置有一贯穿动力连接轴套分布的第一动力连接轴杆,所述前级行星支架的前端面的中心区域设置有一贯穿内齿圈壳的前端面分布并由后级行星系齿轮机构的后端侧插装于后级行星系齿轮机构内以驱动后级行星系齿轮机构进行动力输出的第二动力连接轴杆,所述第一动力连接轴杆连接有一利用前级太阳齿轮与前级行星齿轮之间的啮合关系通过前级行星支架带动第二动力连接轴杆进行转动的第一动力马达和/或所述动力连接轴套连接有一利用内齿圈壳与前级行星齿轮之间的啮合关系通过前级行星支架带动第二动力连接轴杆进行转动的第二动力马达;The pre-stage planetary gear mechanism includes an inner ring gear housing, a front stage planetary bracket mounted in the inner ring gear housing and coaxially distributed with the inner ring gear housing, and a front planetary bracket mounted in the front stage a front stage sun gear coaxially distributed with the front stage planet carrier; the front stage planet carrier is provided with a plurality of front stages that are evenly distributed around the front stage sun gear and simultaneously mesh with the ring gear case and the front stage sun gear a planetary gear, a central portion of the rear end surface of the ring gear case is provided with a power connection bushing, and a central portion of the rear end surface of the front stage sun gear is provided with a first power connection shaft extending through the power connection bushing. A central portion of the front end surface of the front stage planetary carrier is disposed with a front end surface extending through the inner ring gear case and is inserted into the rear stage planetary gear mechanism by the rear end side of the rear stage planetary gear mechanism to drive the rear stage planetary a second power connecting shaft for power output of the gear mechanism, wherein the first power connecting shaft is connected with a front stage planetary bracket by utilizing an meshing relationship between the front stage sun gear and the front stage planetary gear The first power motor and/or the power connection bushing connected to the second power connecting shaft rotates with a meshing relationship between the ring gear case and the front stage planetary gear to drive the second power connection through the front stage planet carrier a second power motor that rotates the shaft;
所述后级行星系齿轮机构的前端侧装设有一用于驱动后级行星系齿轮机构进行动力输出的第三动力马达,所述动力输出齿轮装设于后级行星系齿轮机构的动力输出端上。a front end side of the rear stage planetary gear mechanism is provided with a third power motor for driving the rear stage planetary gear mechanism for power output, and the power output gear is mounted on the power output end of the planetary gear mechanism of the rear stage. on.
优选地,所述前级行星支架包括一中空结构的盘体部以及一由盘体部的后端面的中心区域沿轴向方向向后延伸后形成的过渡套管部,所述盘体部的
周壁上环周地开设有若干个行星齿轮轴安装孔,每个所述行星齿轮轴安装孔内均装设有一前级行星齿轮;所述第二动力连接轴杆由盘体部的前端面的中心区域沿轴向方向向前延伸后成型,所述前级太阳齿轮置于盘体部内,所述第一动力连接轴杆贯穿于过渡套管部分布。Preferably, the front stage planet carrier comprises a hollow body portion and a transition sleeve portion formed by a central portion of the rear end surface of the disk portion extending rearward in the axial direction, the body portion of the disk portion
a plurality of planetary gear shaft mounting holes are circumferentially opened on the circumference wall, and each of the planetary gear shaft mounting holes is provided with a front stage planetary gear; the second power connecting shaft is formed by a front end surface of the disk body portion The central region is formed by extending forward in the axial direction, the front stage sun gear is disposed in the disk body portion, and the first power connection shaft is inserted through the transition sleeve portion.
优选地,所述前级太阳齿轮的前端部上套装有一用于将前级太阳齿轮与盘体部作转动接触的第一轴承,所述第一动力连接轴杆上套装有两个分别用于将第一动力连接轴杆与盘体部作转动接触及将第一动力连接轴杆与过渡套管部作转动接触的第二轴承,所述盘体部的前后两端分别套装有一用于将盘体部与内齿圈壳作转动接触的第三轴承。Preferably, the front end portion of the front stage sun gear is provided with a first bearing for rotatingly contacting the front stage sun gear with the disk body portion, and the first power connection shaft is provided with two separate sleeves for respectively a second bearing for rotatingly contacting the first power connecting shaft with the disk portion and rotating the first power connecting shaft with the transition sleeve portion, wherein the front and rear ends of the disk portion are respectively provided with a a third bearing in which the disk portion is in rotational contact with the ring gear housing.
优选地,所述内齿圈壳包括一用于与前级行星齿轮相啮合的内齿圈、位于内齿圈的前方侧并与内齿圈装配为一体的第一齿圈法兰盘和位于内齿圈的后方侧并与内齿圈装配为一体的第二齿圈法兰盘,所述第三轴承夹持于第一齿圈法兰盘与盘体部的前端面之间以及第二齿圈法兰盘与盘体部的后端面之间,所述动力连接轴套由第二齿圈法兰盘的后端面的中心区域沿轴向方向向后延伸后成型,所述第二动力连接轴杆贯穿于第一齿圈法兰盘分布。Preferably, the ring gear case includes an inner ring gear for meshing with the front stage planetary gear, a first ring gear flange located on the front side of the inner ring gear and integrated with the inner ring gear, and a second ring gear flange integrated with the inner ring gear and integrated with the inner ring gear, the third bearing being clamped between the first ring gear flange and the front end surface of the disc body portion and the second Between the ring gear flange and the rear end surface of the disk body portion, the power connection bushing is formed by extending a central portion of the rear end surface of the second ring gear flange in the axial direction, the second power The connecting shaft is distributed through the first ring gear flange.
优选地,所述后级行星系齿轮机构包括一后级行星支架以及由前至后顺序地装设于后级行星支架内且相互间呈同轴并行分布的第一后级太阳齿轮和第二后级太阳齿轮,所述后级行星支架内沿轴向方向装设有若干根环绕第一后级太阳齿轮和第二后级太阳齿轮均匀分布的后级行星同轴轴杆,每根所述后级行星同轴轴杆上均套装有一用于与第一后级太阳齿轮相啮合的第一后级行星齿轮和一用于与第二后级太阳齿轮相啮合的第二后级行星齿轮;Preferably, the rear stage planetary gear mechanism comprises a rear stage planetary carrier and a first rear stage sun gear and a second device which are sequentially arranged in the rear stage planetary carrier and are coaxially and parallelly distributed from each other in front to rear. a rear stage sun gear, wherein the rear stage planetary carrier is provided with a plurality of rear stage planetary coaxial shafts uniformly distributed around the first rear stage sun gear and the second rear stage sun gear in the axial direction, each of which is a rear stage planetary coaxial shaft is provided with a first rear stage planetary gear for meshing with the first rear stage sun gear and a second rear stage planetary gear for meshing with the second rear stage sun gear;
所述第三动力马达置于后级行星支架的前方侧并与后级行星支架同轴分布,且所述第三动力马达的动力输出轴与第一后级太阳齿轮相连;所述第二动力连接轴杆与第二后级太阳齿轮相连,所述动力输出齿轮套装于后级行星支架上。
The third power motor is disposed on a front side of the rear stage planetary carrier and coaxially distributed with the rear stage planetary carrier, and the power output shaft of the third power motor is connected to the first rear stage sun gear; the second power The connecting shaft is coupled to the second rear stage sun gear, and the power output gear is fitted to the rear stage planet carrier.
优选地,所述后级行星支架包括两块呈前后相对分布的支架板,所述第一后级太阳齿轮和第二后级太阳齿轮由前至后顺序地夹持于两块支架板之间,所述后级行星同轴轴杆的前后两端分别与相对应的支架板轴转连接,所述动力输出齿轮与其中一块支架板装配为一体,所述第二动力连接轴杆穿过位于后方侧的支架板后与第二后级太阳齿轮相连。Preferably, the rear stage planet carrier comprises two bracket plates which are arranged in front and rear relative to each other, and the first rear stage sun gear and the second rear stage sun gear are sequentially clamped between the two bracket plates from front to back. The front and rear ends of the rear planetary coaxial shaft are respectively rotatably connected to the corresponding bracket plates, and the power output gear is integrally assembled with one of the bracket plates, and the second power connecting shaft is located through The bracket plate on the rear side is connected to the second rear stage sun gear.
优选地,每相邻的两根所述后级行星同轴轴杆之间还设置有一根联轴杆,所述联轴杆的前后两端分别与对应的支架板作固定连接。Preferably, a coupling rod is disposed between each adjacent two of the rear stage planetary coaxial shafts, and the front and rear ends of the coupling rod are respectively fixedly connected with the corresponding bracket plates.
优选地,所述第一后级太阳齿轮的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板分布以用于与第三动力马达的动力输出轴相连的后级动力连接轴杆,且所述后级动力连接轴杆上套装有一用于将后级动力连接轴杆与位于前方侧的支架板作转动接触的第四轴承,所述第一后级太阳齿轮与第二后级太阳齿轮之间通过一第五轴承转动接触,所述第二动力连接轴杆上套装有一用于将第二动力连接轴杆与位于后方侧的支架板作转动接触的第六轴承。Preferably, the front end surface central region of the first rear stage sun gear extends forward in the axial direction to form a distribution of the bracket plate extending through the front side for connection with the power output shaft of the third power motor. The stage power is connected to the shaft, and the rear stage power connection shaft is provided with a fourth bearing for rotatingly contacting the rear stage power connection shaft with the bracket plate on the front side, the first rear stage sun gear a second bearing is in rotational contact with the second rear stage sun gear, and the second power connecting shaft is provided with a sixth for rotationally contacting the second power connecting shaft with the bracket plate on the rear side. Bearing.
优选地,它还包括一变速齿轮机构,所述变速齿轮机构包括一变速轴以及沿变速轴的轴向方向顺序地套装于变速轴上的第一变速齿轮和第二变速齿轮,所述第一变速齿轮与动力输出齿轮相啮合,所述第一变速齿轮通过变速轴带动第二变速齿轮作同步转动。Preferably, it further includes a shift gear mechanism including a shifting shaft and a first shifting gear and a second shifting gear sequentially disposed on the shifting shaft in an axial direction of the shifting shaft, the first The shifting gear meshes with the power output gear, and the first shifting gear drives the second shifting gear to rotate synchronously through the shifting shaft.
优选地,它还包括一与第二变速齿轮相啮合的差速齿轮,所述差速齿轮套接于一动力输出轴上。Preferably, it further includes a differential gear that meshes with the second shifting gear, the differential gear being sleeved on a power take-off shaft.
由于采用了上述方案,本实用新型通过选配具有不同(或相同)功率和转速参数的多个动力马达并利用结构部件之间的配合,可实现以下有益效果:Due to the adoption of the above scheme, the utility model can achieve the following beneficial effects by selecting a plurality of power motors having different (or the same) power and speed parameters and utilizing the cooperation between the structural components:
1、基于整个装置存在多个动力马达的结构特点,通过选配具有不同(或相同)功率和转速参数的动力马达,即可使整个装置得到不同的变速比,从而实现变速、无级或多级无离合换挡等功能,并且由于整个装置的变速及换
挡是通过对动力马达的控制来实现的,无需为装置配置离合器,从而可避免在换挡过程中出现部件之间的结构冲击问题;1. Based on the structural characteristics of multiple power motors in the whole device, by selecting a power motor with different (or the same) power and speed parameters, the entire device can obtain different gear ratios, thereby achieving shifting, stepless or more Level without shifting and other functions, and due to the shifting and changing of the entire device
The gear is realized by the control of the power motor, and it is not necessary to configure the clutch for the device, so that the structural impact problem between the components during the shifting process can be avoided;
2、多个动力马达根据不同的使用情况可及时切换不同动力,在不同情况下均可快速地切换,让马达始终在高效区范围内工作;2. Multiple power motors can switch different powers in time according to different usage conditions, and can be quickly switched under different conditions, so that the motor always works in the high efficiency range;
3、通过改变动力马达的电控逻辑或者为每个动力马达配置制动器,可分配出多种动作模式,实现多种不同动力输出的效果;3. By changing the electronic control logic of the power motor or configuring the brake for each power motor, multiple action modes can be assigned to achieve a variety of different power output effects;
4、通过太阳齿轮与行星齿轮之间的对位啮合关系,可使整个装置形成圆周多齿分布的结构,保证装置受力均匀,进而为动力输出效率的提高、部件之间磨损率的减小、噪音量及发热量的降低提供了有利的结构条件;4. Through the alignment relationship between the sun gear and the planetary gear, the whole device can be formed into a structure with a circumferential multi-tooth distribution, which ensures uniform force of the device, thereby improving the power output efficiency and reducing the wear rate between components. , the amount of noise and the reduction of calorific value provide favorable structural conditions;
基于此,其结构简单紧凑、通过多个动力马达之间的配合可实现多档变速的动力输出效果,且动力输出模式多样可变可调,具有很强的实用价值和市场推广价值。Based on this, the structure is simple and compact, and the power output effect of multi-speed shifting can be realized by the cooperation between a plurality of power motors, and the power output mode is variously variable and adjustable, and has strong practical value and market promotion value.
图1是本实用新型实施例的各机构间的驱动原理示意图;1 is a schematic view showing the driving principle between the mechanisms of the embodiment of the present invention;
图2是本实用新型实施例的主体部分的结构装配示意图(一);2 is a schematic structural view of the main body of the embodiment of the present invention (1);
图3是本实用新型实施例的主体部分的结构装配示意图(二);Figure 3 is a schematic view of the structural assembly of the main body portion of the embodiment of the present invention (2);
图4是本实用新型实施例的主体部分的截面结构示意图;4 is a schematic cross-sectional structural view of a main body portion of an embodiment of the present invention;
图5是本实用新型实施例的前、后级行星系齿轮机构的结构示意图;5 is a schematic structural view of a planetary gear mechanism of a front and a rear stage according to an embodiment of the present invention;
图6是本实用新型实施例的前级行星系齿轮机构的结构分解示意图;6 is a schematic exploded view showing the structure of a front stage planetary gear mechanism according to an embodiment of the present invention;
图7是本实用新型实施例的后级行星系齿轮机构的结构分解示意图;7 is a schematic exploded view showing the structure of a planetary gear mechanism of a rear stage according to an embodiment of the present invention;
图中:In the picture:
a、后级行星系齿轮机构;b、前级行星系齿轮机构;c、动力输出齿轮;d、第一动力马达;e、第二动力马达;f、第三动力马达;g、变速齿轮机构;h、差速器;
a, the rear planetary gear mechanism; b, the front planetary gear mechanism; c, the power output gear; d, the first power motor; e, the second power motor; f, the third power motor; g, the gear mechanism ;h, differential;
11、内齿圈壳;111、内齿圈;112、第一齿圈法兰盘;113、第二齿圈法兰盘;12、前级行星支架;121、盘体部;122、过渡套管部;123、行星齿轮轴安装孔;13、前级太阳齿轮;14、前级行星齿轮;15、动力连接轴套;16、第一动力连接轴杆;17、第二动力连接轴杆11, inner ring gear; 111, inner ring gear; 112, first ring gear flange; 113, second ring gear flange; 12, front stage planetary support; 121, disk body; 122, transition sleeve Pipe; 123, planetary gear shaft mounting hole; 13, front stage sun gear; 14, front stage planetary gear; 15, power connection bushing; 16, first power connecting shaft; 17, second power connecting shaft
21、后级行星支架;211、支架板;212、联轴杆;22、第一后级太阳齿轮;221、后级动力连接轴杆;23、第二后级太阳齿轮;24、后级行星同轴轴杆;25、第一后级行星齿轮;26、第二后级行星齿轮;21, rear stage planetary support; 211, bracket plate; 212, coupling rod; 22, first rear stage sun gear; 221, rear stage power connection shaft; 23, second rear stage sun gear; 24, rear stage planet Coaxial shaft; 25, first rear stage planetary gear; 26, second rear stage planetary gear;
31、变速轴;32、第一变速齿轮;33、第二变速齿轮;31, a shifting shaft; 32, a first shifting gear; 33, a second shifting gear;
41、差速齿轮;42、动力输出轴;41, differential gear; 42, power output shaft;
A、第一轴承;B、第二轴承;D、第四轴承;E、第五轴承;F、第六轴承;G、第三轴承。A, the first bearing; B, the second bearing; D, the fourth bearing; E, the fifth bearing; F, the sixth bearing; G, the third bearing.
以下结合附图对本实用新型的实施例进行详细说明,但是本实用新型可以由权利要求限定和覆盖的多种不同方式实施。The embodiments of the present invention are described in detail below with reference to the accompanying drawings, but the present invention can be implemented in various different ways as defined and covered by the claims.
如图1至图7所示,本实施例提供的一种多档多动力行星齿轮变速装置,它包括一后级行星系齿轮机构a、前级行星系齿轮机构b和一动力输出齿轮c;其中,前级行星系齿轮机构b包括一内齿圈壳11、一装设于内齿圈壳11内并与内齿圈壳11呈同轴分布的前级行星支架12以及一装设于前级行星支架12内并与前级行星支架12呈同轴分布的前级太阳齿轮13;在前级行星支架12上装设有若干个环绕前级太阳齿轮13均匀分布并同时与内齿圈壳11和前级太阳齿轮13相啮合的前级行星齿轮14,在内齿圈壳11的后端面的中心区域设置有一动力连接轴套15,在前级太阳齿轮13的后端面的中心区域设置有一贯穿动力连接轴套15分布的第一动力连接轴杆16,在前级行星支架12的前端面的中心区域设置有一贯穿内齿圈壳11的前端面分布并由后级行星系齿轮机构a的后端侧插装于后级行星系齿轮机构a内以驱动后级行星系齿轮机构a
进行动力输出的第二动力连接轴杆17,第一动力连接轴杆16连接有一利用前级太阳齿轮13与前级行星齿轮14之间的啮合关系通过前级行星支架12带动第二动力连接轴杆17进行转动的第一动力马达d和/或动力连接轴套15连接有一利用内齿圈壳11与前级行星齿轮14之间的啮合关系通过前级行星支架12带动第二动力连接轴杆17进行转动的第二动力马达e;同时,在后级行星系齿轮机构a的前端侧装设有一用于驱动后级行星系齿轮机构a进行动力输出的第三动力马达f,动力输出齿轮c装设于后级行星系齿轮机构a的动力输出端上。As shown in FIG. 1 to FIG. 7 , the present embodiment provides a multi-speed multi-power planetary gear shifting device comprising a rear planetary gear mechanism a, a front planetary gear mechanism b and a power output gear c; The front stage planetary gear mechanism b includes an inner ring gear housing 11, a front stage planetary bracket 12 mounted in the inner ring gear housing 11 and coaxially distributed with the inner ring gear housing 11, and a front mounting bracket The front stage sun gear 13 is disposed coaxially with the front stage planet carrier 12 in the stage planet carrier 12; the front stage planet carrier 12 is provided with a plurality of circumferentially arranged front sun gears 13 evenly distributed and simultaneously with the ring gear case 11 The front stage planetary gear 14 meshing with the front stage sun gear 13 is provided with a power connection bushing 15 at a central portion of the rear end surface of the inner ring gear case 11, and a through hole is provided in a central portion of the rear end face of the front stage sun gear 13 The first power connecting shaft 16 distributed by the power connecting sleeve 15 is disposed at a central portion of the front end surface of the front stage planetary bracket 12 with a front end surface extending through the inner ring gear housing 11 and rearward of the planetary gear mechanism a of the rear stage. End side inserted into the rear planetary gear machine the rear stage to drive a planetary gear mechanism a
a second power connecting shaft 17 for performing power output, the first power connecting shaft 16 is connected with a second power connecting shaft through the front stage planetary carrier 12 by the meshing relationship between the front stage sun gear 13 and the front stage planetary gear 14 The first power motor d and/or the power connection bushing 15 for rotating the rod 17 are connected by a meshing relationship between the ring gear housing 11 and the front stage planetary gear 14 to drive the second power connecting shaft through the front stage planetary carrier 12. a second power motor e that rotates; at the same time, a third power motor f for driving the rear stage planetary gear mechanism a for power output is mounted on the front end side of the rear stage planetary gear mechanism a, and the power output gear c It is mounted on the power output end of the planetary gear mechanism a of the rear stage.
由此,利用至少一个前级动力马达(即:第一动力马达d和/或第二动力马达e,两者可分别设置,也可同时设置,在同时设置时,两个前级动力马达可采用同轴中置电机的形式,以实现双动力同轴输出的效果)作为前级行星系齿轮机构b的动力输入源,利用前级行星系齿轮机构b的动力输出端和第三动力马达f作为后级行星系齿轮机构a的两个动力输入源,通过与行星系齿轮机构本身的传动性能的融合可形成多动力马达多档位的齿轮变速装置,即:Thus, at least one front stage power motor (ie, the first power motor d and/or the second power motor e may be used, and the two may be separately set or may be simultaneously set. When simultaneously set, the two front stage power motors may be The coaxial central motor is used to realize the effect of the dual-power coaxial output. As the power input source of the pre-stage planetary gear mechanism b, the power output end of the pre-stage planetary gear mechanism b and the third power motor f are utilized. As the two power input sources of the planetary gear mechanism a of the latter stage, a multi-speed gear shifting device of the multi-power motor can be formed by combining with the transmission performance of the planetary gear mechanism itself, that is,
1、第一动力马达d通过第一动力连接轴杆16向前级太阳齿轮13输入动力,利用前级太阳齿轮13与前级行星齿轮14之间的结构啮合关系驱动各个前级行星齿轮14进行自转,由于前级行星齿轮14是装配于前级行星支架12上的,故进而带动前级行星支架12以前级太阳齿轮13为轴进行公转,从而利用第二动力连接轴杆17向后级行星系齿轮机构a输入动力;1. The first power motor d inputs power through the first power connection shaft 16 to the front stage sun gear 13, and drives each of the front stage planetary gears 14 by the structural meshing relationship between the front stage sun gear 13 and the front stage planetary gear 14. Since the front stage planetary gear 14 is mounted on the front stage planetary carrier 12, the front stage planetary carrier 12 is further driven to revolve around the axis, thereby using the second power to connect the shaft 17 to the rear stage planet. The gear mechanism a inputs power;
2、第二动力马达e则可通过动力连接轴套15驱动内齿圈壳11进行转动,利用内齿圈壳11与前级行星齿轮14之间的结构啮合关系驱动各个前级行星齿轮14进行自转,基于与第一动力马达d相同的驱动原理,以最终通过第二动力连接轴杆17向后级行星系齿轮机构a输入动力;2. The second power motor e can drive the ring gear case 11 to rotate by the power connection bushing 15, and drive each of the front stage planetary gears 14 by the structural meshing relationship between the ring gear case 11 and the front stage planetary gear 14. Rotation, based on the same driving principle as the first power motor d, to finally input power to the rear stage planetary gear mechanism a through the second power connecting shaft 17;
3、与此同时,通过选用具有双动力输入的后级行星系齿轮机构a,可同时利用第三动力马达f和前级行星系齿轮机构b输出的动力形成两个动力输
入,以最终利用装配于后级行星系齿轮机构a的动力输出端上的动力输出齿轮c作为整个装置的动力输出的部件。3. At the same time, by selecting the rear planetary gear mechanism a with dual power input, the power output from the third power motor f and the front planetary gear mechanism b can be simultaneously used to form two power transmissions.
Into, the power output gear c mounted on the power output end of the planetary gear mechanism a of the rear stage is finally utilized as a component of the power output of the entire apparatus.
基于此,本实施例的变速装置可实现以下有益效果:1、基于整个装置存在多个动力马达的结构特点,通过选配具有不同(或相同)功率和转速参数的动力马达,即可使整个装置得到不同的变速比,从而实现变速、无级换挡或多级换挡等功能,并且由于整个装置的变速及换挡是通过对动力马达的控制来实现的,无需为装置配置离合器,从而可避免在换挡过程中出现部件之间的结构冲击问题;2、多个动力马达根据不同的使用情况可及时切换不同动力,在不同情况下均可快速地切换工作,让马达始终在到高效段区范围内工作;3、通过改变动力马达的电控逻辑或者配合制动器等元件可分配出多种档位切换或制动模式,实现不同动力输出的效果;4、通过太阳齿轮与行星齿轮之间的对位啮合关系,可使整个装置形成圆周多齿分布的结构,保证装置受力均匀,进而为动力输出效率的提高、部件之间磨损率的减小、噪音量及发热量的降低提供了有利的结构条件。Based on this, the shifting device of the embodiment can achieve the following beneficial effects: 1. Based on the structural features of the plurality of power motors of the entire device, by selecting a power motor having different (or the same) power and speed parameters, the entire The device obtains different gear ratios to achieve functions such as shifting, stepless shifting or multi-step shifting, and since the shifting and shifting of the entire device is achieved by controlling the power motor, there is no need to configure the clutch for the device. It can avoid the structural impact problem between components during the shifting process; 2. Multiple power motors can switch different powers according to different usage conditions, and can switch jobs quickly under different conditions, so that the motor is always efficient. Working in the segment area; 3. By changing the electronic control logic of the power motor or by matching the brakes and other components, a variety of gear shifting or braking modes can be assigned to achieve different power output effects; 4. Through the sun gear and the planetary gear The inter-parallel meshing relationship enables the entire device to form a structure with a circumferential multi-tooth distribution, ensuring uniform force on the device. To improve the efficiency of the power output, between the members is reduced, the amount of noise and wear rates reduce the heat provided favorable structural conditions.
为优化整个前级行星系齿轮机构b的结构,保证各个组成部件之间的结构紧凑性,本实施例的前级行星支架12包括一中空结构的盘体部121以及一由盘体部121的后端面的中心区域沿轴向方向向后延伸后形成的过渡套管部122,在盘体部122的周壁上环周地开设有若干个行星齿轮轴安装孔123,每个行星齿轮轴安装孔123内均装设有一前级行星齿轮14;而第二动力连接轴杆17则由盘体部121的前端面的中心区域沿轴向方向向前延伸后成型,前级太阳齿轮13置于盘体部121内,第一动力连接轴杆16贯穿于过渡套管部122分布。由此,通过采用壳体状的行星支架并配合内齿圈壳,可使内齿圈壳、行星齿轮和太阳齿轮呈相对的同心分布状态,并为太阳齿轮以及行星齿轮的装配提供相对密闭的结构空间。In order to optimize the structure of the entire pre-stage planetary gear mechanism b and ensure the compactness between the various components, the front stage planetary carrier 12 of the present embodiment includes a hollow body portion 121 and a disk portion 121. A transition sleeve portion 122 formed by extending a central portion of the rear end surface rearward in the axial direction, a plurality of planetary gear shaft mounting holes 123 are circumferentially opened on the peripheral wall of the disk portion 122, and each of the planetary gear shaft mounting holes 123 is provided with a front stage planetary gear 14; and the second power connecting shaft 17 is formed by extending a central portion of the front end surface of the disk portion 121 in the axial direction, and the front stage sun gear 13 is placed on the disk. In the body 121, the first power connection shaft 16 is distributed through the transition sleeve portion 122. Thus, by adopting a shell-shaped planet carrier and fitting the ring gear case, the ring gear housing, the planetary gears and the sun gear can be in a relatively concentric distribution state, and the solar gear and the planetary gears can be relatively sealed. Structure space.
为保证各个运动部件能够进行顺畅地运动,从而实现齿轮传动效应,在前级太阳齿轮13的前端部上套装有一用于将前级太阳齿轮13与盘体部121
作转动接触的第一轴承A,在第一动力连接轴杆16上套装有两个分别用于将第一动力连接轴杆16与盘体部121作转动接触及将第一动力连接轴杆16与过渡套管部122作转动接触的第二轴承B,在盘体部121的前后两端分别套装有一用于将盘体部121与内齿圈壳11作转动接触的第三轴承G。In order to ensure that the respective moving parts can smoothly move to achieve the gear transmission effect, a front end portion of the front stage sun gear 13 is provided with a front sun gear 13 and a disk portion 121.
The first bearing A for rotational contact is provided with two on the first power connection shaft 16 for respectively rotating the first power connection shaft 16 with the disk portion 121 and connecting the first power connection shaft 16 The second bearing B in rotational contact with the transition sleeve portion 122 is provided with a third bearing G for rotationally contacting the disk portion 121 and the ring gear housing 11 at the front and rear ends of the disk portion 121, respectively.
作为一个优选方案,为便于对前级行星系齿轮机构b进行拆装维护,本实施例的内齿圈壳11包括一用于与前级行星齿轮14相啮合的内齿圈111、位于内齿圈111的前方侧并与内齿圈111装配为一体的第一齿圈法兰盘112和位于内齿圈111的后方侧并与内齿圈111装配为一体的第二齿圈法兰盘113,第三轴承G夹持于第一齿圈法兰盘112与盘体部121的前端面之间以及第二齿圈法兰盘113与盘体部121的后端面之间,动力连接轴套15由第二齿圈法兰盘113的后端面的中心区域沿轴向方向向后延伸后成型,第二动力连接轴杆17贯穿于第一齿圈法兰盘112分布。As a preferred solution, in order to facilitate the disassembly and maintenance of the front stage planetary gear mechanism b, the ring gear housing 11 of the present embodiment includes an inner ring gear 111 for meshing with the front stage planetary gear 14, and is located at the inner tooth. A first ring gear flange 112 integrally fitted with the inner ring gear 111 on the front side of the ring 111 and a second ring gear flange 113 integrally formed on the rear side of the inner ring gear 111 and integrated with the ring gear 111 The third bearing G is sandwiched between the first ring gear flange 112 and the front end surface of the disk portion 121 and between the second ring gear flange 113 and the rear end surface of the disk portion 121, and the power connection bushing is 15 is formed by extending a central portion of the rear end surface of the second ring gear flange 113 rearward in the axial direction, and the second power connecting shaft 17 is distributed through the first ring gear flange 112.
为使后级行星系齿轮机构a能够将由第三动力马达f以及由前级行星系齿轮机构b输入的动力进行转换后通过动力输出齿轮c进行输出,同时最大限度地降低整个装置的复杂性,本实施例的后级行星系齿轮机构a包括一后级行星支架21以及由前至后顺序地装设于后级行星支架21内且相互间呈同轴并行分布的第一后级太阳齿轮22和第二后级太阳齿轮23,在后级行星支架21内沿轴向方向装设有若干根环绕第一后级太阳齿轮22和第二后级太阳齿轮23均匀分布的后级行星同轴轴杆24,在每根后级行星同轴轴杆24上均套装有一用于与第一后级太阳齿轮22相啮合的第一后级行星齿轮25和一用于与第二后级太阳齿轮23相啮合的第二后级行星齿轮26;同时,第三动力马达f置于后级行星支架21的前方侧并与后级行星支架21同轴分布,且第三动力马达f的动力输出轴与第一后级太阳齿轮22相连;而第二动力连接轴杆17则与第二后级太阳齿轮23相连,动力输出齿轮c套装于后级行星支架21上。In order to enable the rear stage planetary gear mechanism a to convert the power input by the third power motor f and the front stage planetary gear mechanism b and output it through the power output gear c while minimizing the complexity of the entire apparatus, The rear stage planetary gear mechanism a of the present embodiment includes a rear stage planetary carrier 21 and first rear stage sun gears 22 which are sequentially disposed in the rear stage planetary carrier 21 from front to rear and are coaxially and in parallel with each other. And the second rear stage sun gear 23, in the rear stage planetary carrier 21, a plurality of rear stage planetary coaxial shafts uniformly distributed around the first rear stage sun gear 22 and the second rear stage sun gear 23 are mounted in the axial direction The rod 24 is provided with a first rear stage planetary gear 25 for meshing with the first rear stage sun gear 22 and a second rear stage sun gear 23 on each of the rear stage planetary coaxial shafts 24. The second rear stage planetary gear 26 is engaged; at the same time, the third power motor f is placed on the front side of the rear stage planetary carrier 21 and coaxially distributed with the rear stage planetary carrier 21, and the power output shaft of the third power motor f is First rear stage sun gear 22 Company; and a second drive coupling shaft 17 connected to the second-stage sun gear 23, the power output gear set to the rear stage c planet carrier 21.
由此,第二后级太阳齿轮23可利用前级行星系齿轮机构b输入的动力通过其与第二后级行星齿轮26之间的结构啮合关系形成齿轮传动效应,由于第
二后级行星齿轮26是通过后级行星同轴轴杆24装设于后级行星支架21上的,故可最终通过后级行星支架21带动动力输出齿轮c进行转动,基于同理,第一后级太阳齿轮22可利用第三动力马达f输入的动力通过其与第一后级行星齿轮25之间的结构啮合关系形成齿轮传动效应,由于第一后级行星齿轮25同样是通过后级行星同轴轴杆24装设于后级行星支架21上的,故也可最终通过后级行星支架21带动动力输出齿轮c进行转动;通过逻辑控制可使第三动力马达f和前级行星系齿轮机构b分别进行动力输入,以最终形成不同的动力输出效果,也可通过制动器的配合使两者能够同时进行动力输入,利用齿轮啮合的作用,以便形成动力叠加(加速)、减速、制动等多种输出效果。Thereby, the second rear stage sun gear 23 can form a gear transmission effect by the structural engagement relationship between the power input from the front stage planetary gear mechanism b and the second rear stage planetary gear 26,
The second stage planetary gear 26 is mounted on the rear stage planet carrier 21 through the rear stage planetary coaxial shaft 24, so that the power output gear c can be finally rotated by the rear stage planetary carrier 21, based on the same reason, first The rear stage sun gear 22 can use the power input by the third power motor f to form a gear transmission effect through its structural meshing relationship with the first rear stage planetary gear 25, since the first rear stage planetary gear 25 is also passed through the rear stage planetary The coaxial shaft 24 is mounted on the rear stage planet carrier 21, so that the power output gear c can be finally rotated by the rear stage planetary carrier 21; the third power motor f and the front stage planetary gear can be controlled by logic control. The mechanism b separately performs power input to finally form different power output effects, and the two can simultaneously perform power input through the cooperation of the brakes, and utilize the function of gear meshing to form power superposition (acceleration), deceleration, braking, and the like. A variety of output effects.
为便于对后级行星系齿轮机构b进行拆装维护,本实施例的后级行星支架21包括两块呈前后相对分布的支架板211,第一后级太阳齿轮22和第二后级太阳齿轮23由前至后顺序地夹持于两块支架板211之间,后级行星同轴轴杆24的前后两端分别与相对应的支架板211轴转连接,动力输出齿轮c与其中一块支架板211装配为一体,第二动力连接轴杆17穿过位于后方侧的支架板211后与第二后级太阳齿轮23相连。由此,通过对后级行星支架21的结构优选,可使其呈现出类似于框架式开放结构,以便于对各个齿轮及相关部件进行装配。In order to facilitate the disassembly and maintenance of the planetary gear mechanism b of the rear stage, the rear stage planetary carrier 21 of the present embodiment includes two bracket plates 211 which are vertically distributed back and forth, the first rear stage sun gear 22 and the second rear stage sun gear. 23 is sequentially clamped between the two bracket plates 211 from front to back, and the front and rear ends of the rear planetary coaxial shaft 24 are respectively pivotally connected with the corresponding bracket plates 211, and the power output gear c and one of the brackets are respectively The plate 211 is assembled as one body, and the second power connection shaft 17 is connected to the second rear stage sun gear 23 through the bracket plate 211 on the rear side. Thus, by optimizing the structure of the rear stage planet carrier 21, it can be rendered similar to a frame type open structure to facilitate assembly of the various gears and related components.
由于后级行星支架21是为动力输出齿轮c提供装配位置的部件且其本身需要进行动作,为保证其结构稳固性,在每相邻的两根后级行星同轴轴杆24之间还设置有一根联轴杆212,联轴杆212的前后两端分别与对应的支架板211作固定连接。Since the rear stage planet carrier 21 is a component that provides an assembly position for the power output gear c and needs to be operated by itself, in order to ensure its structural stability, it is also disposed between each adjacent two rear stage planetary coaxial shafts 24 There is a coupling rod 212, and the front and rear ends of the coupling rod 212 are respectively fixedly connected with the corresponding bracket plate 211.
为保证后级行星系齿轮机构a的顺畅运转,同时优化其结构,在第一后级太阳齿轮22的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板211分布以用于与第三动力马达f的动力输出轴相连的后级动力连接轴杆221,且后级动力连接轴杆221上套装有一用于将后级动力连接轴杆221与位于前方侧的支架板211作转动接触的第四轴承D,第一后级太阳
齿轮22与第二后级太阳齿轮23之间通过一第五轴承E转动接触,在第二动力连接轴杆17上套装有一用于将第二动力连接轴杆17与位于后方侧的支架板211作转动接触的第六轴承F。In order to ensure the smooth operation of the planetary gear mechanism a of the rear stage and optimize its structure, a central portion of the front end surface of the first rear stage sun gear 22 extends forward in the axial direction to form a bracket plate 211 penetrating the front side. The rear stage power connection shaft 221 is distributed for the power output shaft of the third power motor f, and the rear stage power connection shaft 221 is provided with a rear power connection shaft 221 and a front side. The fourth bearing D of the bracket plate 211 is in rotational contact, the first rear stage sun
The gear 22 and the second rear stage sun gear 23 are in rotational contact with a fifth bearing E. The second power connecting shaft 17 is provided with a bracket plate 211 for connecting the second power connecting shaft 17 with the rear side. The sixth bearing F is in rotational contact.
为能够对装置的输出转速作进一步变速处理,以实现最终的动力输出效果,在动力输出齿轮c与被驱动部件之间还增设有一变速齿轮机构g,变速齿轮机构g主要包括一变速轴31以及沿变速轴31的轴向方向顺序地套装于变速轴31上的第一变速齿轮32和第二变速齿轮33,第一变速齿轮32与动力输出齿轮c相啮合,以此可利用第一变速齿轮32通过变速轴31带动第二变速齿轮33作同步转动,进而利用第二变速齿轮33来连接被驱动部件,并且第一变速齿轮32的齿数与第二变速齿轮33的齿数不相等,从而实现传动比变化输出。In order to further shift the output speed of the device to achieve the final power output effect, a shift gear mechanism g is further disposed between the power output gear c and the driven member, and the shift gear mechanism g mainly includes a shift shaft 31 and The first shifting gear 32 and the second shifting gear 33 are sequentially fitted on the shifting shaft 31 in the axial direction of the shifting shaft 31, and the first shifting gear 32 meshes with the power output gear c, whereby the first shifting gear can be utilized 32, the second shifting gear 33 is driven to rotate synchronously by the shifting shaft 31, and the driven member is connected by the second shifting gear 33, and the number of teeth of the first shifting gear 32 is not equal to the number of teeth of the second shifting gear 33, thereby realizing the transmission. Ratio change output.
作为一个优选方案,在变速齿轮机构g与被驱动部件之间还增设一差速器h,差速器h包括一与第二变速齿轮33相啮合的差速齿轮41,差速齿轮41套接于一动力输出轴42上。以此,可通过差速齿轮41对装置输出转速作进一步调整,以通过动力输出轴42带动被驱动部件进行动作。As a preferred solution, a differential h is further disposed between the transmission gear mechanism g and the driven member, and the differential h includes a differential gear 41 that meshes with the second shifting gear 33, and the differential gear 41 is sleeved. On a power output shaft 42. Thereby, the output rotational speed of the device can be further adjusted by the differential gear 41 to drive the driven member to operate by the power output shaft 42.
以上所述仅为本实用新型的优选实施例,并非因此限制本实用新型的专利范围,凡是利用本实用新型说明书及附图内容所作的等效结构或等效流程变换,或直接或间接运用在其他相关的技术领域,均同理包括在本实用新型的专利保护范围内。
The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the patent of the present invention. Any equivalent structure or equivalent process transformation using the specification and the drawings of the present invention may be directly or indirectly applied to Other related technical fields are equally included in the scope of patent protection of the present invention.
Claims (16)
- 一种非拉威挪式双动力行星齿轮变速装置,其特征在于:它包括一行星系齿轮机构、一第一动力马达、一第二动力马达和一动力输出齿轮; 所述行星系齿轮机构包括一行星支架以及由前至后顺序地装设于行星支架内且相互间呈同轴并行分布的第一太阳齿轮和第二太阳齿轮,所述行星支架内沿轴向方向装设有若干根环绕第一太阳齿轮和第二太阳齿轮均匀分布的行星同轴轴杆,每根所述行星同轴轴杆上均套装有一用于与第一太阳齿轮相啮合的第一行星齿轮和一用于与第二太阳齿轮相啮合的第二行星齿轮; 所述第一动力马达置于行星支架的前方侧并与行星支架同轴分布,且所述第一动力马达的动力输出轴与第一太阳齿轮相连;所述第二动力马达置于行星支架的后方侧并与行星支架同轴分布,且所述第二动力马达的动力输出轴与第二太阳齿轮相啮合,所述动力输出齿轮装配于行星支架上。A non-Raphaelno type dual-power planetary gear shifting device, comprising: a planetary gear mechanism, a first power motor, a second power motor and a power output gear; the planetary gear mechanism comprises a a planetary carrier and a first sun gear and a second sun gear which are sequentially disposed in the planetary carrier and are coaxially and parallelly distributed from each other in front and rear, and the planetary carrier is provided with a plurality of surrounding portions in the axial direction a planetary coaxial shaft in which a sun gear and a second sun gear are evenly distributed, and each of the planetary coaxial shafts is provided with a first planetary gear for meshing with the first sun gear and a a second planetary gear that meshes with the sun gear; the first power motor is disposed on a front side of the planetary carrier and coaxially distributed with the planetary carrier, and the power output shaft of the first power motor is coupled to the first sun gear; The second power motor is disposed on a rear side of the planet carrier and coaxially distributed with the planet carrier, and the power output shaft of the second power motor is meshed with the second sun gear. The power output gear mounted on the planetary carrier.
- 如权利要求1所述的一种非拉威挪式双动力行星齿轮变速装置,其特征在于:所述行星支架包括两块呈前后相对分布的支架板,所述第一太阳齿轮和第二太阳齿轮由前至后顺序地夹持于两块支架板之间,所述行星同轴轴杆的前后两端分别与相对应的支架板轴转连接,所述动力输出齿轮与其中一块支架板装配为一体。A non-Raphaelno type dual-power planetary gear shifting device according to claim 1, wherein said planetary carrier comprises two bracket plates arranged in a front-rear relationship, said first sun gear and said second sun The gears are sequentially clamped between the two bracket plates from front to back. The front and rear ends of the planetary coaxial shaft are respectively rotatably connected with the corresponding bracket plates, and the power output gear is assembled with one of the bracket plates. As one.
- 如权利要求2所述的一种非拉威挪式双动力行星齿轮变速装置,其特征在于:每相邻的两根所述行星同轴轴杆之间还设置有一根联轴杆,所述联轴杆的前后两端分别与对应的支架板作固定连接。A non-Raphaelno type dual-power planetary gear shifting device according to claim 2, wherein a coupling rod is disposed between each of the two adjacent planetary coaxial shafts, The front and rear ends of the coupling rod are respectively fixedly connected with the corresponding bracket plates.
- 如权利要求2所述的一种非拉威挪式双动力行星齿轮变速装置,其特征在于:所述第一太阳齿轮的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板分布以用于与第一动力马达的动力输出轴相连的第一动力连接轴杆,且所述第一动力连接轴杆上套装有一将第一动力连接轴杆与位于前方侧的支架板作转动接触的第一轴承; 所述第二太阳齿轮的后端面中心区域沿轴向方向向后延伸后形成有一贯穿于位于后方侧的支架板分布以用于与第二动力马达的动力输出轴相连的第二动力连接轴杆,且所述第二动力连接轴杆上套装有一将第二动力连接轴杆与位于后方侧的支架板作转动接触的第二轴承; 所述第一太阳齿轮与第二太阳齿轮之间通过一第三轴承作转动接触。A non-Raphaelno type dual-power planetary gear shifting device according to claim 2, wherein a central portion of the front end face of the first sun gear extends forward in the axial direction to form a through-front The side bracket plates are distributed with a first power connection shaft for connecting with the power output shaft of the first power motor, and the first power connection shaft is provided with a first power connection shaft and a front side a first bearing of the bracket plate for rotational contact; a central portion of the rear end surface of the second sun gear extends rearward in the axial direction to form a distribution of the bracket plate extending through the rear side for powering the second power motor a second power connecting shaft connected to the output shaft, and the second power connecting shaft is provided with a second bearing for rotatingly contacting the second power connecting shaft with the bracket plate at the rear side; the first sun The gear and the second sun gear are in rotational contact by a third bearing.
- 如权利要求1所述的一种非拉威挪式双动力行星齿轮变速装置,其特征在于:所述动力输出齿轮套装于第一动力连接轴杆上并固定于行星支架的前端面上。A non-Raphaelno type dual-power planetary gear shifting device according to claim 1, wherein said power output gear is sleeved on the first power connecting shaft and fixed to the front end surface of the planetary carrier.
- 如权利要求1所述的一种非拉威挪式双动力行星齿轮变速装置,其特征在于:它还包括一与动力输出齿轮相啮合的差速齿轮,所述差速齿轮套接于一动力输出轴上。A non-Raphaelno type dual-power planetary gear shifting device according to claim 1, further comprising: a differential gear meshing with the power output gear, said differential gear being sleeved to a power On the output shaft.
- 一种多档多动力行星齿轮变速装置,其特征在于:它包括一后级行星系齿轮机构、前级行星系齿轮机构和一动力输出齿轮;A multi-speed multi-power planetary gear shifting device, characterized in that it comprises a rear planetary gear mechanism, a front planetary gear mechanism and a power output gear;所述前级行星系齿轮机构包括一内齿圈壳、一装设于内齿圈壳内并与内齿圈壳呈同轴分布的前级行星支架以及一装设于前级行星支架内并与前级行星支架呈同轴分布的前级太阳齿轮;所述前级行星支架上装设有若干个环绕前级太阳齿轮均匀分布并同时与内齿圈壳和前级太阳齿轮相啮合的前级行星齿轮,所述内齿圈壳的后端面的中心区域设置有一动力连接轴套,所述前级太阳齿轮的后端面的中心区域设置有一贯穿动力连接轴套分布的第一动力连接轴杆,所述前级行星支架的前端面的中心区域设置有一贯穿内齿圈壳的前端面分布并由后级行星系齿轮机构的后端侧插装于后级行星系齿轮机构内以驱动后级行星系齿轮机构进行动力输出的第二动力连接轴杆,所述第一动力连接轴杆连接有一利用前级太阳齿轮与前级行星齿轮之间的啮合关系通过前级行星支架带动第二动力连接轴杆进行转动的第一动力马达和/或所述动力连接轴套连接有一利用内齿圈壳与前级行星齿轮之间的啮合关系通过前级行星支架带动第二动力连接轴杆进行转动的第二动力马达;The pre-stage planetary gear mechanism includes an inner ring gear housing, a front stage planetary bracket mounted in the inner ring gear housing and coaxially distributed with the inner ring gear housing, and a front planetary bracket mounted in the front stage a front stage sun gear coaxially distributed with the front stage planet carrier; the front stage planet carrier is provided with a plurality of front stages that are evenly distributed around the front stage sun gear and simultaneously mesh with the ring gear case and the front stage sun gear a planetary gear, a central portion of the rear end surface of the ring gear case is provided with a power connection bushing, and a central portion of the rear end surface of the front stage sun gear is provided with a first power connection shaft extending through the power connection bushing. A central portion of the front end surface of the front stage planetary carrier is disposed with a front end surface extending through the inner ring gear case and is inserted into the rear stage planetary gear mechanism by the rear end side of the rear stage planetary gear mechanism to drive the rear stage planetary a second power connecting shaft for power output of the gear mechanism, wherein the first power connecting shaft is connected with a front stage planetary bracket by utilizing an meshing relationship between the front stage sun gear and the front stage planetary gear The first power motor and/or the power connection bushing connected to the second power connecting shaft rotates with a meshing relationship between the ring gear case and the front stage planetary gear to drive the second power connection through the front stage planet carrier a second power motor that rotates the shaft;所述后级行星系齿轮机构的前端侧装设有一用于驱动后级行星系齿轮机构进行动力输出的第三动力马达,所述动力输出齿轮装设于后级行星系齿轮机构的动力输出端上。a front end side of the rear stage planetary gear mechanism is provided with a third power motor for driving the rear stage planetary gear mechanism for power output, and the power output gear is mounted on the power output end of the planetary gear mechanism of the rear stage. on.
- 如权利要求1所述的一种多档多动力行星齿轮变速装置,其特征在于:所述前级行星支架包括一中空结构的盘体部以及一由盘体部的后端面的中心区域沿轴向方向向后延伸后形成的过渡套管部,所述盘体部的周壁上环周地开设有若干个行星齿轮轴安装孔,每个所述行星齿轮轴安装孔内均装设有一前级行星齿轮;所述第二动力连接轴杆由盘体部的前端面的中心区域沿轴向方向向前延伸后成型,所述前级太阳齿轮置于盘体部内,所述第一动力连接轴杆贯穿于过渡套管部分布。 A multi-speed multi-power planetary gear shifting device according to claim 1, wherein said front stage planetary carrier comprises a hollow body portion and a central portion of the rear end surface of the disk portion along the axis a transition sleeve portion formed to extend rearwardly, a plurality of planetary gear shaft mounting holes are circumferentially opened on a peripheral wall of the disk body portion, and each of the planetary gear shaft mounting holes is provided with a front stage a planetary gear; the second power connecting shaft is formed by extending a central portion of a front end surface of the disk portion in an axial direction, the front stage sun gear is disposed in the disk portion, and the first power connecting shaft The rod runs through the transition sleeve portion of the cloth.
- 如权利要求2所述的一种多档多动力行星齿轮变速装置,其特征在于:所述前级太阳齿轮的前端部上套装有一用于将前级太阳齿轮与盘体部作转动接触的第一轴承,所述第一动力连接轴杆上套装有两个分别用于将第一动力连接轴杆与盘体部作转动接触及将第一动力连接轴杆与过渡套管部作转动接触的第二轴承,所述盘体部的前后两端分别套装有一用于将盘体部与内齿圈壳作转动接触的第三轴承。A multi-speed multi-power planetary gear shifting device according to claim 2, wherein the front end portion of the front stage sun gear is provided with a first portion for rotationally contacting the front stage sun gear with the disc body portion. a bearing, the first power connecting shaft is provided with two for respectively rotating the first power connecting shaft with the disk portion and rotating the first power connecting shaft with the transition sleeve portion. In the second bearing, the front and rear ends of the disc body are respectively provided with a third bearing for rotatingly contacting the disc body portion with the ring gear housing.
- 如权利要求3所述的一种多档多动力行星齿轮变速装置,其特征在于:所述内齿圈壳包括一用于与前级行星齿轮相啮合的内齿圈、位于内齿圈的前方侧并与内齿圈装配为一体的第一齿圈法兰盘和位于内齿圈的后方侧并与内齿圈装配为一体的第二齿圈法兰盘,所述第三轴承夹持于第一齿圈法兰盘与盘体部的前端面之间以及第二齿圈法兰盘与盘体部的后端面之间,所述动力连接轴套由第二齿圈法兰盘的后端面的中心区域沿轴向方向向后延伸后成型,所述第二动力连接轴杆贯穿于第一齿圈法兰盘分布。A multi-speed multi-power planetary gear shifting device according to claim 3, wherein said inner ring gear housing includes an inner ring gear for meshing with the front stage planetary gears, and is located in front of the inner ring gear a first ring gear flange integrally assembled with the inner ring gear and a second ring gear flange at the rear side of the inner ring gear and integrated with the inner ring gear, the third bearing being clamped to Between the first ring gear flange and the front end face of the disk body portion and between the second ring gear flange and the rear end face of the disk body portion, the power connection bushing is behind the second ring gear flange The central portion of the end face is formed to extend rearward in the axial direction, and the second power connecting shaft is distributed through the first ring gear flange.
- 如权利要求1-4中任一项所述的一种多档多动力行星齿轮变速装置,其特征在于:所述后级行星系齿轮机构包括一后级行星支架以及由前至后顺序地装设于后级行星支架内且相互间呈同轴并行分布的第一后级太阳齿轮和第二后级太阳齿轮,所述后级行星支架内沿轴向方向装设有若干根环绕第一后级太阳齿轮和第二后级太阳齿轮均匀分布的后级行星同轴轴杆,每根所述后级行星同轴轴杆上均套装有一用于与第一后级太阳齿轮相啮合的第一后级行星齿轮和一用于与第二后级太阳齿轮相啮合的第二后级行星齿轮;A multi-speed multi-power planetary gear shifting device according to any one of claims 1 to 4, wherein said rear stage planetary gear mechanism comprises a rear stage planetary carrier and is sequentially mounted from front to back. a first rear stage sun gear and a second rear stage sun gear disposed in the rear stage planet carrier and coaxially distributed in parallel with each other, and the rear stage planet carrier is provided with a plurality of inner circumferences in the axial direction a rear stage planetary coaxial shaft in which the stage sun gear and the second rear stage sun gear are evenly distributed, and each of the rear stage planetary coaxial shafts is provided with a first mesh for meshing with the first rear stage sun gear a rear stage planetary gear and a second rear stage planetary gear for meshing with the second rear stage sun gear;所述第三动力马达置于后级行星支架的前方侧并与后级行星支架同轴分布,且所述第三动力马达的动力输出轴与第一后级太阳齿轮相连;所述第二动力连接轴杆与第二后级太阳齿轮相连,所述动力输出齿轮套装于后级行星支架上。The third power motor is disposed on a front side of the rear stage planetary carrier and coaxially distributed with the rear stage planetary carrier, and the power output shaft of the third power motor is connected to the first rear stage sun gear; the second power The connecting shaft is coupled to the second rear stage sun gear, and the power output gear is fitted to the rear stage planet carrier.
- 如权利要求5所述的一种多档多动力行星齿轮变速装置,其特征在于:所述后级行星支架包括两块呈前后相对分布的支架板,所述第一后级太阳齿 轮和第二后级太阳齿轮由前至后顺序地夹持于两块支架板之间,所述后级行星同轴轴杆的前后两端分别与相对应的支架板轴转连接,所述动力输出齿轮与其中一块支架板装配为一体,所述第二动力连接轴杆穿过位于后方侧的支架板后与第二后级太阳齿轮相连。A multi-speed multi-power planetary gear shifting device according to claim 5, wherein said rear stage planetary bracket comprises two bracket plates which are arranged in front and rear relative to each other, said first rear stage sun gear The wheel and the second rear stage sun gear are sequentially clamped between the two bracket plates from front to back, and the front and rear ends of the rear stage planetary coaxial shaft are respectively pivotally connected with the corresponding bracket plates, The power output gear is integrally assembled with one of the bracket plates, and the second power connection shaft is connected to the second rear stage sun gear through the bracket plate on the rear side.
- 如权利要求6所述的一种多档多动力行星齿轮变速装置,其特征在于:每相邻的两根所述后级行星同轴轴杆之间还设置有一根联轴杆,所述联轴杆的前后两端分别与对应的支架板作固定连接。A multi-speed multi-power planetary gear shifting device according to claim 6, wherein a coupling shaft is disposed between each adjacent two of said rear stage planetary coaxial shafts, said joint The front and rear ends of the shaft are respectively fixedly connected with the corresponding bracket plates.
- 如权利要求6所述的一种多档多动力行星齿轮变速装置,其特征在于:所述第一后级太阳齿轮的前端面中心区域沿轴向方向向前延伸后形成有一贯穿于位于前方侧的支架板分布以用于与第三动力马达的动力输出轴相连的后级动力连接轴杆,且所述后级动力连接轴杆上套装有一用于将后级动力连接轴杆与位于前方侧的支架板作转动接触的第四轴承,所述第一后级太阳齿轮与第二后级太阳齿轮之间通过一第五轴承转动接触,所述第二动力连接轴杆上套装有一用于将第二动力连接轴杆与位于后方侧的支架板作转动接触的第六轴承。A multi-speed multi-power planetary gear shifting device according to claim 6, wherein a central portion of the front end surface of the first rear stage sun gear extends forward in the axial direction and is formed to penetrate through the front side. The bracket plate is distributed for the rear stage power connection shaft connected to the power output shaft of the third power motor, and the rear stage power connection shaft is provided with a rear power connection shaft and a front side a fourth bearing of the bracket plate for rotational contact, the first rear stage sun gear and the second rear stage sun gear are in rotational contact by a fifth bearing, and the second power connecting shaft is provided with a cover for The second power connecting shaft is a sixth bearing in rotational contact with the bracket plate on the rear side.
- 如权利要求5所述的一种多档多动力行星齿轮变速装置,其特征在于:它还包括一变速齿轮机构,所述变速齿轮机构包括一变速轴以及沿变速轴的轴向方向顺序地套装于变速轴上的第一变速齿轮和第二变速齿轮,所述第一变速齿轮与动力输出齿轮相啮合,所述第一变速齿轮通过变速轴带动第二变速齿轮作同步转动。A multi-speed multi-power planetary gear shifting device according to claim 5, further comprising a shifting gear mechanism including a shifting shaft and sequentially sleeved along an axial direction of the shifting shaft a first shifting gear and a second shifting gear on the shifting shaft, the first shifting gear meshes with the power output gear, and the first shifting gear drives the second shifting gear to rotate synchronously through the shifting shaft.
- 如权利要求9所述的一种多档多动力行星齿轮变速装置,其特征在于:它还包括一与第二变速齿轮相啮合的差速齿轮,所述差速齿轮套接于一动力输出轴上。 A multi-speed multi-power planetary gear shifting device according to claim 9, further comprising: a differential gear meshing with the second shifting gear, said differential gear being sleeved on a power output shaft on.
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CN201721042159.5U CN207297763U (en) | 2017-08-18 | 2017-08-18 | A kind of non-double dynamical planetary speed variator of Ravigneaux formula |
CN201721042159.5 | 2017-08-18 |
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2017
- 2017-08-18 CN CN201721042159.5U patent/CN207297763U/en active Active
- 2017-09-29 WO PCT/CN2017/098133 patent/WO2019033420A1/en active Application Filing
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DE102008011338A1 (en) * | 2007-02-27 | 2008-08-28 | Getrag Driveline Systems Gmbh | Automatic transmission e.g. differential transmission, for motor vehicle, has braking device for applying brake force causing brake torque, and planetary unit with effective surfaces disposed to part laterally adjacent to planetary wheel |
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