WO2020207340A1 - 同种中心轮行星排变速器 - Google Patents

同种中心轮行星排变速器 Download PDF

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Publication number
WO2020207340A1
WO2020207340A1 PCT/CN2020/083140 CN2020083140W WO2020207340A1 WO 2020207340 A1 WO2020207340 A1 WO 2020207340A1 CN 2020083140 W CN2020083140 W CN 2020083140W WO 2020207340 A1 WO2020207340 A1 WO 2020207340A1
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WIPO (PCT)
Prior art keywords
planetary
gear
planetary row
transmission
row
Prior art date
Application number
PCT/CN2020/083140
Other languages
English (en)
French (fr)
Inventor
罗灿
Original Assignee
罗灿
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 罗灿 filed Critical 罗灿
Priority to EP20787312.6A priority Critical patent/EP3954924A4/en
Priority to KR1020217033861A priority patent/KR20210141632A/ko
Priority to CN202080006632.2A priority patent/CN113227612A/zh
Priority to US17/442,553 priority patent/US20220170533A1/en
Priority to JP2021557730A priority patent/JP2022527927A/ja
Publication of WO2020207340A1 publication Critical patent/WO2020207340A1/zh

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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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/18—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears with a plurality of planetary gear units
    • 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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36—Inputs being a function of speed
    • F16H59/38—Inputs being a function of speed of gearing elements
    • 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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/50—Inputs being a function of the status of the machine, e.g. position of doors or safety belts
    • F16H59/54—Inputs being a function of the status of the machine, e.g. position of doors or safety belts dependent on signals from the brakes, e.g. parking brakes
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

Definitions

  • the invention relates to a planetary gear transmission, in particular to a planetary gear transmission that adopts no less than three rows of the same type of center wheel planetary row structure to control the gears by controlling each brake.
  • the planetary gear transmission includes: the internal structure of each planetary row, namely the adopted planetary row, the structure formed by interconnecting the planetary rows, that is, the planetary row structure, the input and output lock ends, the controller of the transmission, etc.
  • Ordinary complete planetary row is composed of three parts: sun gear, inner gear ring and planet carrier with planetary gear.
  • the axes of sun gear and inner gear ring are the central axis of planetary row.
  • Sun gear is a kind of center wheel with inner teeth.
  • the circle is another center wheel.
  • Planetary rows are divided into single-layer stars and planetary rows and double-layer stars and planetary rows.
  • the single-layer planetary row has only single-layer planetary wheels, and the number of planetary wheels is equal to the number of planetary wheel sets. From the inside to the outside of the complete single-layer planetary row, the sun gear meshes with the single-layer planet gear, and the single-layer planet gear meshes with the inner ring gear.
  • each component of the planetary row is enlarged and reduced in proportion, and its motion law remains unchanged.
  • Multiple planetary rows are connected to each other to form a planetary row structure.
  • a component in the planetary row structure is a rotating component with a rotation speed, and several components are connected to each other and have the same rotation speed, which is the same rotating component.
  • the star-connected planetary row structure is: for multiple single-layer star planetary rows, the number of planetary wheel sets is the same, and the size of each planetary row is adjusted, and some are scaled up and some are scaled down.
  • the distance between the axis of the middle planetary gear and the central axis of the planetary row is equal; align each planetary gear of the planetary row with the planetary gear axes of the adjacent planetary row and connect them in groups.
  • This connection is called a star connection, and the star connection makes it participate in the connection.
  • Each planetary wheel of has the same speed, and each planet carrier participating in the connection has another same speed.
  • the planetary row structure formed by the star connection between the planetary rows is the star-connected planetary row structure. According to actual needs, each single-layer star planetary row in the star-connected planetary row structure can omit one of the two central wheels, the sun gear or the inner gear ring, to become an incomplete single-layer planetary planetary row.
  • An incomplete single-layer star planetary row has only two components: a central wheel and a planet carrier with planetary wheels.
  • the planetary rows used in the present invention are incomplete single-layer planetary planetary rows, and they are the same kind of center wheel planetary rows.
  • each planetary row omits the sun gear and is the same kind of center wheel (inner gear ring) planetary row. From the inside to the outside of the planetary row, a single-layer planetary gear meshes with the inner gear ring.
  • the present invention proposes the same kind of center wheel planetary gear transmission.
  • Features include the planetary row, planetary row structure, input and output locking ends, and various brakes. The characteristics are as follows:
  • the planetary row used is: the present invention uses no less than three rows of the same kind of center wheel planetary row.
  • Each row of planetary rows is an incomplete single-layer star planetary row, which has two components: a center wheel and a planet carrier with planetary gears; the center wheels in each planetary row are either all sun gears or all inner ring gears. All center wheels in a transmission are the same center wheel.
  • the same kind of center wheel planetary row includes the same kind of center wheel (sun gear) planetary row and the same kind of center wheel (inner gear ring) planetary row.
  • Each planetary row of the same kind of center wheel is a sun gear.
  • a planetary row of the same kind of center wheel (sun gear), and each planetary row in which the same kind of center wheel is an inner ring gear is called the same kind of center wheel (inner gear ring) planetary row.
  • one of the transmissions is selected and used to form the transmission, the same kind of center wheel (sun gear) planetary row is selected to form the same kind of center wheel (sun gear) planetary row transmission, and the same kind of center wheel (inner gear) is selected
  • the planetary row constitutes the same kind of center wheel (inner gear ring) planetary row transmission.
  • the concept of "planetary row” includes the components of the planetary row and the parts of the components, including the components, the meshing, transmission, support, arrangement and positional relationship between the components, including the components, the structure of each component, omission and parameter settings.
  • the planetary row structure is a star-connected planetary row structure.
  • the star-connected planetary row structure is: for multiple rows of single-layer star planetary rows, the number of planetary gear sets is the same, and the size of each planetary row is adjusted until the distance between the axis of the planetary gear in each planetary row and the central axis of the planetary row is all Equal; align each planetary wheel in the planetary row with the planetary wheel axis of the adjacent planetary row and connect them in groups.
  • This connection is called a star connection.
  • the planetary row structure formed by the star connection between the planetary rows is the star connection Planetary row structure.
  • planetary row structure is a specific term, and its concept includes the connection between the planetary rows, and also includes the planetary rows in connection and the components and parts of the planetary rows in connection, such as planetary rows, Such as rotating components, planetary gears participating in star connection, etc.
  • the input and output lock ends are: use the planet carrier as the input end to connect to the power device; any center wheel as the output end to connect to the power use equipment; the other center wheels are each used as a lock end and connected to a brake, which is controlled by the shift control device control. Control a brake to brake to lock the center wheel connected to it, and the rotation speed of the center wheel is zero; control a brake to stop the center wheel without braking.
  • Each brake is: the present invention adopts no less than two brakes as the controller of the transmission, and each is connected with a lock end.
  • Brakes are mature technologies, such as mechanical brakes, electromagnetic brakes, and power-assisted brakes.
  • the brake includes a stator and a mover, the stator is connected with a fixed object, and the mover is connected with a locking end, which can be controlled to be in a braking state, a half braking state and a non-braking state.
  • a clutch with one end connected to a fixed object such as a base is also a brake.
  • each rotating component serves as an input and output locking end, and no rotating component is redundant, which proves that the transmission structure of the present invention is simple.
  • Ordinary complete planetary row assembly can only be assembled axially, which has a certain contradiction with the structure of star-connected planetary row, and assembly is difficult.
  • the present invention adopts incomplete planetary row, each planet can be assembled radially without the axial assembly, and the assembly is simple; the overall planetary row structure can also be assembled radially, which expands the assembly method of the planetary row transmission.
  • Ordinary planetary gearboxes shift gears by controlling multi-disc clutches, brakes, and one-way clutches, and use hydraulic control mechanisms for actuation, with complex control structures. In the present invention, the gear position is controlled entirely by controlling the brake, the hydraulic control mechanism may not be used, and the control structure is simple.
  • the operating characteristics of the transmission of the present invention are: control a brake to brake to make the speed of the center wheel connected to it be zero; when the input speed is input, control a brake to brake, the output must form an output speed, and the input speed constitutes a certain
  • the transmission forms a transmission ratio corresponding to a gear; when the other brake is controlled, the output end must form another output speed, which forms another certain proportional relation with the input speed.
  • the transmission forms another transmission ratio, corresponding Another gear; and so on, the transmission of the present invention controls the gear by controlling the braking of each brake.
  • the transmission When one brake is controlled to brake in half, the transmission is semi-linked in the corresponding gear; when all brakes are controlled to not brake, the transmission is in neutral; when two or more brakes are controlled to brake, the transmission stops.
  • the transmission ratio is the ratio of the input rotation speed to the output rotation speed.
  • the transmission ratio is a positive value, the input rotation speed and the output rotation speed have the same direction, and when the transmission ratio is a negative value, the input rotation speed and the output rotation speed are opposite.
  • connection generally refers to direct connection, and indirect connection will be specifically stated.
  • connection generally refers to direct connection, and indirect connection will be specifically stated.
  • connection In each planetary row, the relationship between the planet carrier and the planet wheel is: one is the shaft and the other is the bearing. The number of gear teeth of each component in each planetary row is determined according to actual needs, and the gear modulus of each component of the planetary row does not have to be the same as that of other planetary rows.
  • connection between the input end and the power unit There are two types of connection between the input end and the power unit: direct connection and indirect connection through the side shaft gear; the connection between the output end and the power use equipment includes direct connection and indirect connection through the side shaft gear; the direct connection transmission ratio is 1.0, The indirect transmission ratio is generally negative, such as -1.0.
  • the power plant adopts mature technology, such as an electric power plant, a steam power plant or a fuel power plant.
  • the shift control device adopts mature technology, such as an electric control mechanism, a mechanical control mechanism or a hydraulic control mechanism.
  • the multi-layer quill shaft is a mature technology, and the bearing and the shaft and the shafts of each layer can rotate relative to each other, but do not slide relative to each other in the axial direction.
  • Each bearing is a mature technology.
  • the bearing supports the shaft.
  • the bearing and the shaft can rotate relative to each other, but they do not slide relative to each other in the axial direction.
  • the brake is a mature technology.
  • the gear shift control device of the transmission of the present invention is actuated by the stator of the brake, and a hydraulic control mechanism may not be used.
  • the multi-plate clutch is a mature technology.
  • the multi-plate clutch in the traditional transmission contains two independent movers. Since the shift control device is actuated by the movers, a hydraulic control mechanism must be adopted.
  • the hydraulic control mechanism is a kind of shift control device and has a complicated structure.
  • Figures 1 to 5 use the same kind of center wheel (inner gear ring) planetary row.
  • Figure 1 and Figure 2 show three rows of planetary rows, Figure 3 shows four rows of planetary rows, Figure 4 shows five rows of planetary rows, and Figure 5 shows six rows of planetary rows.
  • the difference between Figure 1 and Figure 2 is that the planet carrier in Figure 1 is a bearing , The planet wheel is the shaft; the planet carrier in Figure 2 is the shaft, and the planet wheel is the bearing; the other difference between Figure 1 and Figure 2 is that the input end, output end, and locking end are arranged in a different order.
  • Figures 6 to 10 use the same kind of center wheel (sun wheel) planetary row.
  • Figure 6 and Figure 7 show three rows of planetary rows
  • Figure 8 shows four rows of planetary rows
  • Figure 9 shows five rows of planetary rows
  • Figure 10 shows six rows of planetary rows.
  • the difference between Figure 6 and Figure 7 is that the planet carrier in Figure 6 is a bearing
  • the planetary gear is the shaft
  • the planet carrier in Figure 7 is the shaft
  • the planetary gear is the bearing
  • another difference between Figure 6 and Figure 7 is that the input end, output end, and locking end are arranged in a different order.
  • the bearings in each figure only indicate the supporting principle, and do not reflect the actual number and actual size of the bearings.
  • the number of gears of the transmission of the present invention is equal to the number of brakes, which is equal to the number of planetary rows used minus one, so the number of planetary rows used is specifically set according to the actual required gears of the transmission.
  • the transmission ratio of each gear of the transmission of the present invention depends on the number of central gear teeth and planetary gear teeth of each planetary row used, so the number of central gear and planetary gear teeth of each planetary row is specifically set according to the actual required transmission ratio of each gear.
  • the number of planetary gear sets is specifically set according to the actual torque to be transmitted by the transmission and the number of teeth of each central gear. The transmission obtained through these specific settings does not change the characteristics of the present invention, and all belong to the protection scope of the present invention.
  • the structure diagrams of the transmission of the present invention with planetary rows not more than six rows are shown in Figs. 1 to 10, and the specific arrangement is demonstrated in each embodiment.
  • the structure diagram of the transmission of the present invention with more than six planetary rows can be deduced by analogy, and its specific settings can be deduced by analogy according to these embodiments, which will not be described in detail.
  • a transmission when keeping all other structures unchanged, only swaps its input end and output end, the new transmission formed is the reverse transmission of the original transmission.
  • the number of gears of the reverse transmission remains unchanged, and the new gear ratio of the reverse transmission is the reciprocal of the original gear ratio of the original transmission.
  • the planetary row is unchanged, the planetary row structure is unchanged, the brakes are unchanged, and the input and output lock ends are changed to: use the planet carrier as the output end to connect the power use equipment, and any center wheel can be used as The input end is connected to the power unit, and the remaining center wheels are each connected to a brake as a locking end; its operating characteristics remain unchanged.
  • the reverse transmission of the transmission of the present invention also belongs to the protection scope of the present invention.
  • the advantages of the same kind of center wheel planetary gearbox of the present invention are: it is proposed to use no less than three rows of the same kind of center wheel planetary row, the star-connected planetary row structure is proposed, and the input and output locking ends are proposed, which are better than the existing planetary row.
  • the transmission structure of the gearbox is simpler, and the assembly method of the planetary gearbox is expanded. It is proposed to control the gear position by controlling the braking of each brake, which is simpler than the control structure of the existing planetary gear transmission.
  • Fig. 1 is a schematic diagram of a transmission adopting three rows of planetary rows of the same kind of center wheel (inner gear ring) according to the present invention.
  • 1 is the No. 1 planetary row inner gear
  • 2 is the No. 2 planetary row inner gear
  • 3 is the No. 3 planetary row inner gear
  • 4 is the No. 1 planetary row planetary gear
  • 5 is the No. 2 planetary row planetary gear
  • 6 is the The number three planetary row of planet wheels
  • 7 is the planet carrier
  • 8 is the brake (there are 2)
  • 9 is the input arrow
  • 10 is the output arrow.
  • Figure 2 is a schematic diagram of a transmission using three rows of planetary rows of the same type of center wheel (inner gear ring) according to the present invention.
  • 1 is the No. 1 planetary row inner gear
  • 2 is the No. 2 planetary row inner gear
  • 3 is the No. 3 planetary row inner gear
  • 4 is the No. 1 planetary row planetary gear
  • 5 is the No. 2 planetary row planetary gear
  • 6 is the The number three planetary row of planet wheels
  • 7 is the planet carrier
  • 8 is the brake (there are 2)
  • 9 is the input arrow
  • 10 is the output arrow.
  • Fig. 3 is a schematic diagram of a transmission using four rows of planetary rows of the same kind of center wheel (inner gear ring) according to the present invention.
  • 1 is the inner gear ring of the first planetary row
  • 2 is the inner gear ring of the second planetary row
  • 3 is the inner gear ring of the third planetary row
  • 4 is the inner gear ring of the fourth planetary row
  • 5 is the planetary gear of the first planetary row
  • 7 is the third planetary row planetary gear
  • 8 is the fourth planetary row planetary gear
  • 9 is the planet carrier
  • 10 is the brake (there are 3)
  • 11 is the input arrow
  • 12 is the output arrow.
  • Fig. 4 is a schematic diagram of a transmission using five rows of planetary rows of the same kind of center wheel (inner gear ring) according to the present invention.
  • 1 is the inner gear ring of the first planetary row
  • 2 is the inner gear ring of the second planetary row
  • 3 is the inner gear ring of the third planetary row
  • 4 is the inner gear ring of the fourth planetary row
  • 5 is the inner gear ring of the fifth planetary row.
  • 6 is the No. 1 planetary row planetary gear
  • 7 is the No. 2 planetary row planetary gear
  • 8 is the No. 3 planetary row planetary gear
  • 9 is the No. 4 planetary row planetary gear
  • 10 is the No. 5 planetary row planetary gear
  • 11 is the planet carrier
  • 12 is the brake (there are 4)
  • 13 is the input arrow
  • 14 is the output arrow.
  • Fig. 5 is a schematic diagram of a transmission adopting six rows of planetary rows of the same kind of center wheel (inner gear ring) according to the present invention.
  • 1 is the inner gear ring of the first planetary row
  • 2 is the inner gear ring of the second planetary row
  • 3 is the inner gear ring of the third planetary row
  • 4 is the inner gear ring of the fourth planetary row
  • 5 is the inner gear ring of the fifth planetary row.
  • 6 is the inner gear ring of the sixth planetary row
  • 7 is the first planetary row planetary gear
  • 8 is the second planetary row planetary gear
  • 9 is the third planetary row planetary gear
  • 10 is the fourth planetary row planetary gear
  • 11 is the fifth planetary row.
  • 12 is the sixth planetary row planetary gear
  • 13 is the planet carrier
  • 14 is the brake (there are 5)
  • 15 is the input arrow
  • 16 is the output arrow.
  • Fig. 6 is a schematic diagram of a transmission adopting three rows of planetary rows of the same kind of center wheel (sun gear) according to the present invention.
  • 1 is the No. 1 planetary row of sun gear
  • 2 is the No. 2 planetary row of the sun gear
  • 3 is the No. 3 planetary row of the sun gear
  • 4 is the No. 1 planetary row of planetary gears
  • 5 is the No. 2 planetary row of planetary wheels
  • 6 is the No. 3 planetary gear
  • 7 is the planet carrier
  • 8 is the brake (there are 2)
  • 9 is the input arrow
  • 10 is the output arrow.
  • Fig. 7 is a schematic diagram of a transmission adopting three rows of planetary rows of the same kind of center wheel (sun gear) according to the present invention.
  • 1 is the No. 1 planetary row of sun gear
  • 2 is the No. 2 planetary row of the sun gear
  • 3 is the No. 3 planetary row of the sun gear
  • 4 is the No. 1 planetary row of planetary gears
  • 5 is the No. 2 planetary row of planetary wheels
  • 6 is the No. 3 planetary gear
  • 7 is the planet carrier
  • 8 is the brake (there are 2)
  • 9 is the input arrow
  • 10 is the output arrow.
  • Fig. 8 is a schematic diagram of a transmission adopting four rows of planetary rows of the same kind of center wheel (sun gear) according to the present invention.
  • 1 is the No. 1 planetary row sun gear
  • 2 is the No. 2 planetary row sun gear
  • 3 is the No. 3 planet row sun gear
  • 4 is the No. 4 planet row sun gear
  • 5 is the No. 1 planet row planetary wheel
  • 6 is the No. 2 planet Planetary gears
  • 7 is the third planetary planetary gear
  • 8 is the fourth planetary planetary gear
  • 9 is the planet carrier
  • 10 is the brake (there are 3)
  • 11 is the input arrow
  • 12 is the output arrow.
  • Fig. 9 is a schematic diagram of a transmission using five rows of planetary rows of the same kind of center wheel (sun gear) according to the present invention.
  • 1 is the No. 1 planetary row sun gear
  • 2 is the No. 2 planetary row sun gear
  • 3 is the No. 3 planet row sun gear
  • 4 is the No. 4 planet row sun gear
  • 5 is the No. 5 planet row sun gear
  • 6 is the No. 1 planet Planetary gears
  • 7 is the second planetary planetary gear
  • 8 is the third planetary planetary gear
  • 9 is the fourth planetary planetary gear
  • 10 is the fifth planetary planetary gear
  • 11 is the planet carrier
  • 12 is the brake (with 4)
  • 13 is the input arrow
  • 14 is the output arrow.
  • Fig. 10 is a schematic diagram of a transmission using six rows of planetary rows of the same kind of center wheel (sun gear) according to the present invention.
  • 1 is the No. 1 planetary sun gear
  • 2 is the No. 2 planetary sun gear
  • 3 is the No. 3 planetary sun gear
  • 4 is the No. 4 planetary sun gear
  • 5 is the No. 5 planetary sun gear
  • 6 is the No. 6 planet
  • the row of sun gears 7 is the No. 1 planetary row of planetary gears
  • 8 is the No. 2 planetary row of planetary gears
  • 9 is the No. 3 planetary row of planetary gears
  • 10 is the No. 4 planetary row of planetary gears
  • 11 is the No. 5 planetary row of planetary gears
  • 12 It is the sixth planetary row planetary gear
  • 13 is the planet carrier
  • 14 is the brake (there are 5)
  • 15 is the input arrow
  • 16 is the output arrow.
  • the planetary row is shown as a half-frame schematic diagram in accordance with industry practices, the input and output are shown by arrows, and the brake is shown by a diagram showing the stator grounding.
  • the brake is shown by a diagram showing the stator grounding.
  • Embodiment 1 An example of the transmission of the present invention using three rows of planetary rows of the same kind of center wheel (inner gear ring).
  • Features include the planetary row, planetary row structure, input and output locking ends and various brakes.
  • the planetary row adopted is: this embodiment adopts three rows of planetary rows of the same kind of center wheel (inner gear ring).
  • Each planetary row has two components: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all internal gear rings, which are the same kind of center wheel.
  • the number of planetary gear sets in the three rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing. Note: If you change the planetary gear to the bearing and the planet carrier to the shaft, see Figure 2.
  • the planetary row structure is a star-connected planetary row structure.
  • Zq1 is the number of ring gear teeth in the first planetary row
  • Zq2 is the number of ring gear teeth in the second planetary row
  • Zq3 is the number of ring gear teeth in the third planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary row two
  • X3 is the number of planetary gear teeth of the third planetary row.
  • the input and output locking end is: the planet carrier (7) is used as the input end to connect the power device.
  • the inner gear ring (1) of the No. 1 planetary row is used as the output end to connect to the power use equipment.
  • the second planetary row inner gear ring (2) and the third planetary row inner gear ring (3) each serve as a locking end connected to a brake (8). See Figure 1.
  • the brakes are: this embodiment uses two brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • Embodiment 2 Two examples of the transmission of the present invention using four rows of planetary rows of the same kind of center wheel (inner gear ring).
  • Features include the adopted planetary row, planetary row structure, input and output locking ends, and various brakes.
  • the planetary row used is: this embodiment uses four rows of planetary rows of the same kind of center wheel (inner gear ring). Each planetary row has two components: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all internal gear rings, which are the same kind of center wheel.
  • the number of planetary gear sets in the four rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zq1 is the number of ring gear teeth in the first planetary row
  • Zq2 is the number of ring gear teeth in the second planetary row
  • Zq3 is the number of ring gear teeth in the third planetary row
  • Zq4 is the number of ring gear teeth in the fourth planetary row
  • X1 is the number one planet
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is the number of planetary gear teeth in the fourth planetary row.
  • the input and output locking end is: the planet carrier (9) is used as the input end to connect the power device.
  • the inner gear ring (1) of the No. 1 planetary row is used as the output end to connect to the power use equipment.
  • the second planetary row inner gear ring (2), the third planetary row inner gear ring (3), and the fourth planetary row inner gear ring (4) are each connected to a brake (10) as a locking end. See Figure 3.
  • the brakes are: this embodiment adopts three brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • Embodiment 3 Three examples of the transmission of the present invention using five rows of planetary rows of the same kind of center wheel (inner gear ring).
  • the features include the adopted planetary row, the planetary row structure, the input and output locking ends, and the brakes.
  • the planetary row used is: this embodiment uses five rows of planetary rows of the same kind of center wheel (inner gear ring). Each planetary row has two components: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all internal gear rings, which are the same kind of center wheel.
  • the number of planetary gear sets in the five rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zq1 is the number of ring gear teeth in the first planetary row
  • Zq2 is the number of ring gear teeth in the second planetary row
  • Zq3 is the number of ring gear teeth in the third planetary row
  • Zq4 is the number of ring gear teeth in the fourth planetary row
  • Zq5 is the fifth planet
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is the number of planetary gear teeth in the fourth planetary row
  • X5 is the number five Number of teeth of planetary gear in planet row.
  • the input and output locking end is: the planet carrier (11) is used as the input end to connect the power device.
  • the inner gear ring (1) of the No. 1 planetary row is used as the output end to connect to the power use equipment.
  • the second planetary row inner gear (2), the third planetary row inner gear (3), the fourth planetary row inner gear (4), and the fifth planetary row inner gear (5) each serve as a locking end.
  • the brakes are: this embodiment adopts four brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the transmission When all four brakes are not applied, the transmission is in neutral.
  • the transmission controls the gear position by controlling the four brakes.
  • the gear ratios between adjacent gears of the forward three-speed and reverse one-speed transmission are approximately equal, and the deviation is less than 1.8%; the transmission structure is simple, and the control structure is simple, and can be used as an automobile transmission.
  • the transmission of the third embodiment in series with the transmission of embodiment 2, like the main transmission and the auxiliary transmission of a truck, to form a positive nine-speed and reverse three-speed transmission.
  • the transmission ratios from the positive first gear to the positive ninth gear are: -40.0/-30.67/-23.63/-18.29/-14.02/-10.80/-8.08/-6.19/-4.77, the transmission ratio range is 8.39, from the reverse first gear
  • the transmission ratios to the third reverse gear are: 40.0/30.67/23.63.
  • the gear ratio spacing between adjacent gears is approximately equal, with a deviation of less than 2.7%. It is a rare constant ratio transmission. It is controlled by controlling seven brakes. Gear position can be used as a car transmission.
  • Embodiment 4 Four examples of the transmission of the present invention using six rows of planetary rows of the same type of center wheel (inner gear ring).
  • the features include the adopted planetary row, the planetary row structure, the input and output locking ends, and the brakes.
  • the planetary row used is: this embodiment uses six rows of planetary rows of the same kind of center wheel (inner gear ring). Each planetary row has two components: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all internal gear rings, which are the same kind of center wheel.
  • the number of planetary gear sets in the six rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zq1 is the number of ring gear teeth in the first planetary row
  • Zq2 is the number of ring gear teeth in the second planetary row
  • Zq3 is the number of ring gear teeth in the third planetary row
  • Zq4 is the number of ring gear teeth in the fourth planetary row
  • Zq5 is the fifth planet
  • Zt6 is the number of ring gear teeth in the sixth planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is four
  • X5 is the number of planetary gear teeth in the fifth planetary row
  • X6 is the number of planetary gear teeth in the sixth planetary row.
  • the input and output locking end is: the planet carrier (13) is used as the input end to connect to the power device.
  • the inner gear ring (1) of the No. 1 planetary row is used as the output end to connect to the power use equipment.
  • the rings (6) each serve as a locking end and are connected to a brake (14). See Figure 5.
  • the brakes are: this embodiment uses five brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the transmission ratio is -2.602, which corresponds to the second gear.
  • the transmission ratio is -3.392, which corresponds to the first gear.
  • the transmission controls the gear position by controlling the five brakes.
  • the gear ratio spacing between adjacent gears of the five-speed transmission of this embodiment is approximately equal, and the deviation is less than 0.3%; the transmission structure is simple, the control structure is simple, and it can be used as a bicycle transmission.
  • Embodiment 5 Five examples of the transmission of the present invention using three rows of planetary rows of the same type of center wheel (sun gear). Features include the adopted planetary row, planetary row structure, input and output locking ends, and various brakes.
  • the planetary row used is: this embodiment adopts three rows of the same kind of center wheel (sun gear) planetary row.
  • Each planetary row has two parts: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all sun wheels, which are the same kind of center wheel.
  • the number of planetary gear sets in the three rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing. Note: If you change the planetary gear to the bearing and the planet carrier to the shaft, see Figure 7.
  • the planetary row structure is a star-connected planetary row structure.
  • Zt1 is the number of sun gear teeth in the first planetary row
  • Zt2 is the number of sun gear teeth in the second planetary row
  • Zt3 is the number of sun gear teeth in the third planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of teeth of the planetary gear on the third planetary row.
  • the input and output locking end is: the planet carrier (7) is used as the input end to connect the power device.
  • the No. 1 planetary row sun gear (1) is used as an output terminal to connect to power use equipment.
  • the second planetary row sun gear (2) and the third planetary row sun gear (3) each serve as a locking end and are connected to a brake (8). These connections are achieved through a multilayer quill, see Figure 6.
  • the brakes are: this embodiment uses two brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the transmission ratio is 77.5, which corresponds to the second gear.
  • the transmission ratio is 120.0, which corresponds to the first gear.
  • the transmission controls the gear position by controlling the two brakes.
  • the transmission ratio of the two gears of this embodiment is large, the transmission structure is simple, the control structure is simple, and it can be used as a helicopter main reducer and transmission.
  • Embodiment 6 Six examples of the transmission of the present invention using four rows of planetary rows of the same type of center wheel (sun gear). The features include the planetary row, the structure of the planetary row, the input and output locking ends, and the brakes.
  • the planetary row used is: this embodiment uses four rows of the same kind of center wheel (sun gear) planetary row.
  • Each planetary row has two parts: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all sun wheels, which are the same kind of center wheel.
  • the number of planetary gear sets in the four rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zt1 is the number of sun gear teeth in the first planetary row
  • Zt2 is the number of sun gear teeth in the second planetary row
  • Zt3 is the number of sun gear teeth in the third planetary row
  • Zt4 is the number of sun gear teeth in the fourth planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is the number of planetary gear teeth in the fourth planetary row.
  • the input and output locking end is: the planet carrier (9) is used as the input end to connect the power device.
  • the No. 1 planetary row sun gear (1) is used as an output terminal to connect to power use equipment.
  • the second planetary row sun gear (2), the third planetary row sun gear (3), and the fourth planetary row sun gear (4) each serve as a locking end and are connected to a brake (10). These connections are achieved through multilayer quill shafts, see Figure 8.
  • the brakes are: this embodiment adopts three brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the gear ratio spacing between adjacent gears of the transmission in this embodiment is approximately equal, and the deviation is less than 0.24%; the transmission structure is simple, the control structure is simple, and it can be used as an electric vehicle transmission. Each gear is easy to form a large transmission ratio, and all gears are decelerated transmission, which is a major advantage of the transmission of the present invention.
  • Embodiment 7 Seven examples of the transmission of the present invention using five rows of planetary rows of the same type of center wheel (sun gear).
  • the features include the adopted planetary row, planetary row structure, input and output locking ends, and various brakes.
  • the planetary row used is: this embodiment uses five rows of planetary rows of the same kind of center wheel (sun gear). Each planetary row has two parts: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all sun wheels, which are the same kind of center wheel.
  • the number of planetary gear sets in the five rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zt1 is the number of sun gear teeth in the first planetary row
  • Zt2 is the number of sun gear teeth in the second planetary row
  • Zt3 is the number of sun gear teeth in the third planetary row
  • Zt4 is the number of sun gear teeth in the fourth planetary row
  • Zt5 is the number of sun gear teeth in the fifth planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is the number of planetary gear teeth in the fourth planetary row
  • X5 is the number of planetary gear teeth in the fifth planetary row .
  • the input and output locking end is: the planet carrier (11) is used as the input end to connect the power device.
  • the No. 1 planetary row sun gear (1) is used as an output terminal to connect to power use equipment.
  • the second planetary row sun gear (2), the third planetary row sun gear (3), the fourth planetary row sun gear (4), and the fifth planetary row sun gear (5) are each used as a locking end and connected to a brake ( 12). These connections are achieved through a multi-layer quill, see Figure 9.
  • the brakes are: this embodiment adopts four brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the transmission When all four brakes are not applied, the transmission is in neutral.
  • the transmission controls the gear position by controlling the four brakes.
  • the gear ratio spacing between adjacent gears of the transmission of this embodiment is approximately equal, and the deviation is less than 0.7%; the transmission structure is simple, the control structure is simple, and it can be used as a motor vehicle transmission.
  • Embodiment 8 Eight examples of the transmission of the present invention using six rows of planetary rows of the same kind of center wheel (sun gear).
  • the features include the adopted planetary row, the structure of the planetary row, the input and output locking ends, and the brakes.
  • the planetary row used is: this embodiment uses six rows of the same kind of center wheel (sun gear) planetary row.
  • Each planetary row has two parts: a center wheel and a planet carrier with planetary wheels; the center wheels in each planetary row are all sun wheels, which are the same kind of center wheel.
  • the number of planetary gear sets in the six rows of planetary rows is 4.
  • the planet wheel is the shaft, and the planet carrier is the bearing.
  • the planetary row structure is a star-connected planetary row structure.
  • Zt1 is the number of sun gear teeth in the first planetary row
  • Zt2 is the number of sun gear teeth in the second planetary row
  • Zt3 is the number of sun gear teeth in the third planetary row
  • Zt4 is the number of sun gear teeth in the fourth planetary row
  • Zt5 is the number of sun gear teeth in the fifth planetary row
  • Zt6 is the number of sun gear teeth in the sixth planetary row
  • X1 is the number of planetary gear teeth in the first planetary row
  • X2 is the number of planetary gear teeth in the second planetary row
  • X3 is the number of planetary gear teeth in the third planetary row
  • X4 is the number of planetary gear teeth in the fourth planetary row
  • X5 is the number of planetary gear teeth in the fifth planetary row
  • X6 is the number of planetary gear teeth in the sixth planetary row.
  • the input and output locking end is: the planet carrier (13) is used as the input end to connect to the power device.
  • the No. 1 planetary row sun gear (1) is used as an output terminal to connect to power use equipment.
  • the second planetary row sun gear (2), the third planetary row sun gear (3), the fourth planetary row sun gear (4), the fifth planetary row sun gear (5), the sixth planetary row sun gear (6) each Connect a brake (14) each as a locking end.
  • the brakes are: this embodiment uses five brakes, each connected to a locking end.
  • the brake is an electromagnetic brake, which is controlled by the shift control device.
  • the transmission ratio is -30.875, which corresponds to the reverse gear.
  • the transmission controls the gear position by controlling the five brakes.
  • the gear ratio spacing between adjacent gears of the forward four-speed reverse gear transmission of this embodiment is approximately equal, and the deviation is less than 0.7%; the transmission structure is simple, the control structure is simple, and it can be used as a motor vehicle transmission.

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Abstract

一种同种中心轮行星排变速器，包括行星排、行星排结构、输入输出锁止端和各制动器（8）；该变速器采用不少于三排的同种中心轮（太阳轮）行星排或同种中心轮（内齿圈）行星排组成星连接行星排结构；输入输出锁止端以行星架（7）作为输入端，任取一个中心轮（1）作为输出端，其余中心轮（2、3）各作为一个锁止端；该变速器采用不少于二个制动器（8），制动器（8）各与一个锁止端连接；制动器（8）受换档控制装置控制处于制动状态、半制动状态和非制动状态；该变速器通过控制各制动器（8）制动来控制档位。

Description

同种中心轮行星排变速器 技术领域
本发明涉及一种行星排变速器，具体为采用不少于三排同种中心轮行星排的星连接行星排结构的全通过控制各制动器制动来控制档位的行星排变速器。
背景技术
为了变换转矩和转速，很多传动系统都配置了行星排变速器。不同行星排变速器采用的行星排、行星排结构、输入输出锁止端、控制器各有技术特征。现有行星排变速器传动结构复杂，通过控制多片离合器、制动器、单向离合器来换档，控制结构复杂。此前本人发明申报了全通过控制各制动器制动来控制档位的行星排变速器，控制结构简单，采用普通行星排，星连接行星排结构，传动结构比较简单。机械行业需要传动结构更简单的，全通过控制各制动器制动来控制档位的控制结构简单的行星排变速器。本发明就是提出这样的行星排变速器。
行星排变速器包括：各行星排的内部构造即采用的行星排，各行星排相互连接形成的结构即行星排结构，输入输出锁止端，变速器的控制器等。
普通完整行星排由太阳轮、内齿圈与带行星轮的行星架三种部件组成，其中太阳轮与内齿圈的轴线都是行星排的中心轴线，太阳轮是一种中心轮，内齿圈是另一种中心轮。行星排分为单层星行星排与双层星行星排，各有运动规律。单层星行星排只有单层行星轮，其行星轮个数等于其行星轮组数目。完整单层星行星排从内向外是太阳轮与单层行星轮啮合、单层行星轮与内齿圈啮合。行星排各部件尺寸等比放大缩小，其运动规律不变。多个行星排相互连接组成行星排结构。行星排结构中的一个部件拥有一个转速是一个旋转构件，几个部件相互连接拥有同一个转速就同是一个旋转构件。所述星连接行星排结构即：对多排单层星行星排，设置它们的行星轮组数目相同，调整各行星排尺寸大小，有的等比放大、有的等比缩小，直至各行星排中行星轮轴线到行星排中心轴线的距离都相等；把行星排的每个行星轮与相邻行星排的行星轮轴线对齐并分组相连接，这样的连接称为星连接，星连接使参与连接的各行星轮拥有一个相同的转速，参与连接的各个行星架拥有另一个相同的转速。各行星排之间以星连接方式组成的行星排结构就是星连接行星排结构。根据实际需要，星连接行星排结构中的各单层星行星排可以省略太阳轮或内齿圈这两种中心轮的其中之一，成为不完整单层星行星排。不完整单层星行星排只有一个中心轮、一个带行星轮的行星架这两个部件。本发明采用的各行星排是不完整单层星行星排，且是同种中心轮行星排，有两种：第一种，各行星排均省略了内齿圈，是同种中心轮(太阳轮)行星排，行星排从内向外是太阳轮与单层行星轮啮合。第二种，各行星排均省略了太阳轮，是同种中心轮(内齿圈)行星排，行星排从内向外是单层行星轮与内齿圈啮合。
发明内容
为设计制造传动结构更简单的，全通过控制各制动器制动来控制档位的控制结构简单的行星排变速器，本发明提出同种中心轮行星排变速器。特征包括采用的行星排、行星排结构、输入输出锁止端、各制动器等几个方面。各方面特征如下：
采用的行星排是：本发明采用不少于三排的同种中心轮行星排。每排行星排是不完整单层星行星排，有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮要么全是太阳轮、要么全是内齿圈，一个变速器中所有中心轮是同一种中心轮。所述同种中心轮行星排包括同种中心轮(太阳轮)行星排、同种中心轮(内齿圈)行星排这两种，同一种中心轮均是太阳轮的各行星排称为同种中心轮(太阳轮)行星排，同一种中心轮均是内齿圈的各行星排称为同种中心轮(内齿圈)行星排。本发明在一个变速器中选取采用其中一种来组成变速器，选取同种中心轮(太阳轮)行星排就组成同种中心轮(太阳轮)行星排变速器，选取同种中心轮(内齿圈)行星排就组成同种中心轮(内齿圈)行星排变速器。本发明中，“行星排”概念包括行星排的部件以及部件的零件，包括各部件、各零件之间的啮合、传动、支撑、排列及位置关系，包括各部件、各零件的构造、省略与参数设置。
行星排结构是星连接行星排结构。所述星连接行星排结构即：对多排单层星行星排，设置它们的行星轮组数目相同，调整各行星排尺寸大小，直至各行星排中行星轮轴线到行星排中心轴线的距离都相等；把行星排中每个行星轮与相邻行星排的行星轮轴线对齐并分组相连接，这样的连接称为星连接，各行星排之间以星连接方式形成的行星排结构就是星连接行星排结构。星连接行星排结构中各行星排的行星架共同成为一个旋转构件，各行星排的中心轮各是一个旋转构件。本发明中“行星排结构”是专用名词，其概念包括各行星排之间的连接，还包括处于连接中的各行星排和处于连接中的行星排各部件以及各零件，比如各行星排，比如旋转构件、参与星连接的行星轮等。
输入输出锁止端是：以行星架作为输入端连接动力装置；任取一个中心轮作为输出端连接动力使用设备；其余中心轮各作为一个锁止端各连接一个制动器，制动器受换档控制装置控制。控制一个制动器制动就锁止与之连接的中心轮，该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。
各制动器是：本发明采用不少于二个制动器作为变速器的控制器，各与一个锁止端连接。制动器为成熟技术，例如机械制动器、电磁制动器、助力制动器等。制动器含定子与动子，定子与固定物连接，动子与锁止端连接，可受控制处于制动状态、半制动状态和非制动状态。按机械原理，一端与机座等固定物连接的离合器也属于制动器。
本发明的星连接行星排结构，每一个旋转构件都作为输入输出锁止端，没有任何旋转构 件是冗余，这证明本发明变速器传动结构简单。普通完整行星排的装配方式只能轴向装配，这与星连接行星排结构有一定矛盾，装配较难。由于本发明采用不完整行星排，各行星排除了轴向装配还可以径向装配，装配简单；总的行星排结构也可以径向装配，这就拓展了行星排变速器的装配方式。普通行星排变速器通过控制多片离合器、制动器、单向离合器来换档，采用液压控制机构作动，控制结构复杂。本发明全通过控制制动器制动来控制档位，可以不采用液压控制机构，控制结构简单。
本发明变速器的运作特征是：控制一个制动器制动使与之连接的中心轮转速为零；输入端输入转速时，控制一个制动器制动，输出端必然形成一个输出转速，与输入转速构成一个确定的比例关系，变速器形成一个传动比，对应一个档位；控制另一个制动器制动，输出端必然形成另一个输出转速，与输入转速构成另一个确定的比例关系，变速器形成另一个传动比，对应另一个档位；依此类推，本发明变速器通过控制各制动器制动来控制档位。当控制一个制动器半制动时，变速器在相应的这个档位半联动；当控制各制动器均不制动时，变速器为空档；当控制两个以上制动器制动时，变速器停转。所述传动比即输入转速与输出转速的比值，传动比为正值时输入转速与输出转速方向相同，传动比为负值时输入转速与输出转速方向相反。
所述直接连接即通过机械相连使被连接的对象转速相同，所述间接连接即通过机械传动使两个被传动对象的转速确定性地相关。单独的“连接”一般指直接连接，间接连接会专门明示。各行星排中，行星架与行星轮这两者的相互关系为：一者为轴，另一者为轴承。各行星排中各部件齿轮齿数根据实际需要确定，行星排各部件的齿轮模数与其他行星排各部件的齿轮模数不必须相同。所述输入端与动力装置的连接有直接连接和通过旁轴齿轮间接连接两种；输出端与动力使用设备的连接有直接连接和通过旁轴齿轮间接连接两种；直接连接传动比为1.0，间接连接传动比一般为负值，例如-1.0。所述动力装置采用成熟技术，比如电动力装置、汽动力装置或燃油动力装置。所述换档控制装置采用成熟技术，比如电动控制机构、机械控制机构或液压控制机构。所述多层套筒轴为成熟技术，轴承与轴之间、各层轴之间可以相对转动，但沿轴向不相对滑移。各轴承为成熟技术，轴承承托着轴，轴承与轴之间可以相对转动，但沿轴向不相对滑移。所述制动器为成熟技术，本发明变速器的换档控制装置通过制动器的定子作动，可以不采用液压控制机构。所述多片离合器为成熟技术，传统变速器中多片离合器含两个独立的动子，由于换档控制装置通过动子作动，必须采用液压控制机构。所述液压控制机构是换档控制装置的一种，结构很复杂。
图1至图5采用同种中心轮(内齿圈)行星排。图1、图2为三排行星排，图3为四排行星排，图4为五排行星排，图5为六排行星排，图1与图2的区别是图1中行星架为轴承， 行星轮为轴；图2中行星架为轴，行星轮为轴承；图1与图2的另一个区别是输入端、输出端、锁止端的排列顺序不一样。图6至图10采用同种中心轮(太阳轮)行星排。图6、图7为三排行星排，图8为四排行星排，图9为五排行星排，图10为六排行星排，图6与图7的区别是图6中行星架为轴承，行星轮为轴；图7中行星架为轴，行星轮为轴承；图6与图7的另一个区别是输入端、输出端、锁止端的排列顺序不一样。各图中的轴承只示意支撑原理，不反映轴承的实际数量、实际尺寸。
本发明变速器的档位数等于制动器数，等于采用的行星排排数减一，所以根据实际需要的变速器档位数具体设置采用的行星排排数。本发明变速器各档位传动比取决于所采用各行星排的中心轮齿数、行星轮齿数，所以根据实际需要的各档位传动比具体设置各行星排中心轮齿数、行星轮齿数。行星轮轮组数目主要根据变速器实际需要传递的扭矩、结合各中心轮齿数来具体设置。通过这些具体设置得出的变速器不改变本发明的特征，均属于本发明的保护范围。采用行星排排数不多于六排的本发明变速器的结构简图在图1至图10有展示，其具体设置在各实施例中有示范。采用行星排排数多于六排的本发明变速器的结构简图可以类推，其具体设置可根据这些实施例类推，就不详述了。
一个变速器，当保持其他所有结构不变，只对换其输入端与输出端，形成的新变速器就是原变速器的逆变速器。逆变速器的档位数保持不变，逆变速器新的各档位传动比为原变速器对应原档位传动比的倒数。本发明变速器的逆变速器，采用的行星排不变，行星排结构不变，各制动器不变，输入输出锁止端改为：以行星架作为输出端连接动力使用设备，任取一个中心轮作为输入端连接动力装置，其余中心轮各作为一个锁止端各连接一个制动器；其运作特征不变。本发明变速器的逆变速器也属于本发明的保护范围。
上述采用的行星排、行星排结构、输入输出锁止端和各制动器的特征，以及运作特征、逆变速器特征，是本发明的创新。在本发明之前，业内没有相同特征的行星排变速器。
本发明同种中心轮行星排变速器的有益之处在于：提出了采用不少于三排同种中心轮行星排，提出了星连接行星排结构，提出了输入输出锁止端，比现有行星排变速器的传动结构更简单，且拓展了行星排变速器的装配方式。提出了全通过控制各制动器制动来控制档位，比现有行星排变速器控制结构简单。
附图说明
图1为本发明采用三排同种中心轮(内齿圈)行星排的变速器示意图。1为一号行星排内齿圈，2为二号行星排内齿圈，3为三号行星排内齿圈，4为一号行星排行星轮，5为二号行星排行星轮，6为三号行星排行星轮，7为行星架，8为制动器(有2个)，9为输入箭头，10为输出箭头。
图2为本发明采用三排同种中心轮(内齿圈)行星排的变速器示意图。1为一号行星排内齿圈，2为二号行星排内齿圈，3为三号行星排内齿圈，4为一号行星排行星轮，5为二号行星排行星轮，6为三号行星排行星轮，7为行星架，8为制动器(有2个)，9为输入箭头，10为输出箭头。
图3为本发明采用四排同种中心轮(内齿圈)行星排的变速器示意图。1为一号行星排内齿圈，2为二号行星排内齿圈，3为三号行星排内齿圈，4为四号行星排内齿圈，5为一号行星排行星轮，6为二号行星排行星轮，7为三号行星排行星轮，8为四号行星排行星轮，9为行星架，10为制动器(有3个)，11为输入箭头，12为输出箭头。
图4为本发明采用五排同种中心轮(内齿圈)行星排的变速器示意图。1为一号行星排内齿圈，2为二号行星排内齿圈，3为三号行星排内齿圈，4为四号行星排内齿圈，5为五号行星排内齿圈，6为一号行星排行星轮，7为二号行星排行星轮，8为三号行星排行星轮，9为四号行星排行星轮，10为五号行星排行星轮，11为行星架，12为制动器(有4个)，13为输入箭头，14为输出箭头。
图5为本发明采用六排同种中心轮(内齿圈)行星排的变速器示意图。1为一号行星排内齿圈，2为二号行星排内齿圈，3为三号行星排内齿圈，4为四号行星排内齿圈，5为五号行星排内齿圈，6为六号行星排内齿圈，7为一号行星排行星轮，8为二号行星排行星轮，9为三号行星排行星轮，10为四号行星排行星轮，11为五号行星排行星轮，12为六号行星排行星轮，13为行星架，14为制动器(有5个)，15为输入箭头，16为输出箭头。
图6为本发明采用三排同种中心轮(太阳轮)行星排的变速器示意图。1为一号行星排太阳轮，2为二号行星排太阳轮，3为三号行星排太阳轮，4为一号行星排行星轮，5为二号行星排行星轮，6为三号行星排行星轮，7为行星架，8为制动器(有2个)，9为输入箭头，10为输出箭头。
图7为本发明采用三排同种中心轮(太阳轮)行星排的变速器示意图。1为一号行星排太阳轮，2为二号行星排太阳轮，3为三号行星排太阳轮，4为一号行星排行星轮，5为二号行星排行星轮，6为三号行星排行星轮，7为行星架，8为制动器(有2个)，9为输入箭头，10为输出箭头。
图8为本发明采用四排同种中心轮(太阳轮)行星排的变速器示意图。1为一号行星排太阳轮，2为二号行星排太阳轮，3为三号行星排太阳轮，4为四号行星排太阳轮，5为一号行星排行星轮，6为二号行星排行星轮，7为三号行星排行星轮，8为四号行星排行星轮，9为行星架，10为制动器(有3个)，11为输入箭头，12为输出箭头。
图9为本发明采用五排同种中心轮(太阳轮)行星排的变速器示意图。1为一号行星排 太阳轮，2为二号行星排太阳轮，3为三号行星排太阳轮，4为四号行星排太阳轮，5为五号行星排太阳轮，6为一号行星排行星轮，7为二号行星排行星轮，8为三号行星排行星轮，9为四号行星排行星轮，10为五号行星排行星轮，11为行星架，12为制动器(有4个)，13为输入箭头，14为输出箭头。
图10为本发明采用六排同种中心轮(太阳轮)行星排的变速器示意图。1为一号行星排太阳轮，2为二号行星排太阳轮，3为三号行星排太阳轮，4为四号行星排太阳轮，5为五号行星排太阳轮，6为六号行星排太阳轮，7为一号行星排行星轮，8为二号行星排行星轮，9为三号行星排行星轮，10为四号行星排行星轮，11为五号行星排行星轮，12为六号行星排行星轮，13为行星架，14为制动器(有5个)，15为输入箭头，16为输出箭头。
各图中行星排均按业内惯例以半幅结构简图示意，输入、输出以箭头示意，制动器以定子接地的简图示意。各图中各部件只示意结构关系，未反映真实尺寸。
具体实施方式
实施例1：采用三排同种中心轮(内齿圈)行星排的本发明变速器一例。特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用三排同种中心轮(内齿圈)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是内齿圈，是同一种中心轮。使三排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。注：如果改行星轮为轴承，行星架为轴，可参见图2。
行星排结构是星连接行星排结构。设Zq1为一号行星排内齿圈齿数，Zq2为二号行星排内齿圈齿数，Zq3为三号行星排内齿圈齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zq1＝70，Zq2＝62，Zq3＝58，X1＝19，X2＝17，X3＝16。
输入输出锁止端是：以行星架(7)作为输入端连接动力装置。一号行星排内齿圈(1)作为输出端连接动力使用设备。二号行星排内齿圈(2)、三号行星排内齿圈(3)各作为一个锁止端各连接一个制动器(8)。参见图1。
各制动器是：本实施例采用二个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接三号行星排内齿圈(3)的制动器(8)制动时，传动比为62.222,对应二档档位。连接二号行星排内齿圈(2)的制动器(8)制动时，传动比为99.167,对应一档档位。两个制动器均不制动时，变速器为空档。本实施例变速器两个档 位传动比均很大，传动结构简单，控制结构简单，通过控制两个制动器制动来控制档位。作直升机主减速器兼变速器，可开辟直升机换档功能。
实施例2：采用四排同种中心轮(内齿圈)行星排的本发明变速器二例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用四排同种中心轮(内齿圈)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是内齿圈，是同一种中心轮。使四排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zq1为一号行星排内齿圈齿数，Zq2为二号行星排内齿圈齿数，Zq3为三号行星排内齿圈齿数，Zq4为四号行星排内齿圈齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zq1＝82，Zq2＝82，Zq3＝78，Zq4＝78，X1＝33，X2＝22，X3＝19，X4＝17。
输入输出锁止端是：以行星架(9)作为输入端连接动力装置。一号行星排内齿圈(1)作为输出端连接动力使用设备。二号行星排内齿圈(2)、三号行星排内齿圈(3)、四号行星排内齿圈(4)各作为一个锁止端各连接一个制动器(10)。参见图3。
各制动器是：本实施例采用三个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接四号行星排内齿圈(4)的制动器(10)制动时，传动比为-1.181，对应三档档位。连接三号行星排内齿圈(3)的制动器(10)制动时，传动比为-1.533,对应二档档位。连接二号行星排内齿圈(2)的制动器(10)制动时，传动比为-2.0,对应一档档位。三个制动器均不制动时，变速器为空档。变速器通过控制三个制动器制动来控制档位。本实施例变速器相邻档位的齿比间距近似相等，偏差小于0.3％；传动结构简单，控制结构简单，可作自行车变速器。
实施例3：采用五排同种中心轮(内齿圈)行星排的本发明变速器三例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用五排同种中心轮(内齿圈)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是内齿圈，是同一种中心轮。使五排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zq1为一号行星排内齿圈齿数，Zq2为二号行星排内齿圈齿数，Zq3为三号行星排内齿圈齿数，Zq4为四号行星排内齿圈齿数，Zq5为五号行星 排内齿圈齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数，X5为五号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zq1＝80，Zq2＝84，Zq3＝68，Zq4＝60，Zq5＝76，X1＝19，X2＝19，X3＝17，X4＝16，X5＝24。
输入输出锁止端是：以行星架(11)作为输入端连接动力装置。一号行星排内齿圈(1)作为输出端连接动力使用设备。二号行星排内齿圈(2)、三号行星排内齿圈(3)、四号行星排内齿圈(4)、五号行星排内齿圈(5)各作为一个锁止端各连接一个制动器(12)。参见图4。
各制动器是：本实施例采用四个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接五号行星排内齿圈(5)的制动器(12)制动时，传动比为4.034，对应三档档位。连接四号行星排内齿圈(4)的制动器(12)制动时，传动比为9.143，对应二档档位。连接三号行星排内齿圈(3)的制动器(12)制动时，传动比为20.0对应一档档位。连接二号行星排内齿圈(2)的制动器(12)制动时，传动比为-20.0,对应倒档档位。四个制动器均不制动时，变速器为空档。变速器通过控制四个制动器制动来控制档位。本实施例正三档倒一档变速器相邻档位之间的齿比间距近似相等，偏差小于1.8％；传动结构简单，控制结构简单，可作汽车变速器。
把本实施例3变速器与实施例2变速器串联，像货车的主变速器与副变速器串联，就形成正九档倒三档变速器。从正一档至正九档的传动比分别为：-40.0/-30.67/-23.63/-18.29/-14.02/-10.80/-8.08/-6.19/-4.77，传动比范围8.39，从倒一档至倒三档的传动比分别为：40.0/30.67/23.63，相邻档位之间的齿比间距近似相等，偏差小于2.7％，是难得的等比变速器，通过控制七个制动器制动来控制档位，可作汽车变速器。
实施例4：采用六排同种中心轮(内齿圈)行星排的本发明变速器四例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用六排同种中心轮(内齿圈)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是内齿圈，是同一种中心轮。使六排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zq1为一号行星排内齿圈齿数，Zq2为二号行星排内齿圈齿数，Zq3为三号行星排内齿圈齿数，Zq4为四号行星排内齿圈齿数，Zq5为五号行星排内齿圈齿数，Zt6为六号行星排内齿圈齿数，X1为一号行星排行星轮齿数，X2为二号行星 排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数，X5为五号行星排行星轮齿数，X6为六号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zq1＝82，Zq2＝74，Zq3＝86，Zq4＝82，Zq5＝78，Zq6＝78，X1＝33，X2＝23，X3＝25，X4＝22，X5＝19，X6＝17。
输入输出锁止端是：以行星架(13)作为输入端连接动力装置。一号行星排内齿圈(1)作为输出端连接动力使用设备。二号行星排内齿圈(2)、三号行星排内齿圈(3)、四号行星排内齿圈(4)、五号行星排内齿圈(5)、六号行星排内齿圈(6)各作为一个锁止端各连接一个制动器(14)。参见图5。
各制动器是：本实施例采用五个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接六号行星排内齿圈(6)的制动器(14)制动时，传动比为-1.181，对应五档档位。连接五号行星排内齿圈(5)的制动器(14)制动时，传动比为-1.533，对应四档档位。连接四号行星排内齿圈(4)的制动器(14)制动时，传动比为-2.0，对应三档档位。连接三号行星排内齿圈(3)的制动器(14)制动时，传动比为-2.602，对应二档档位。连接二号行星排内齿圈(2)的制动器(14)制动时，传动比为-3.392,对应一档档位。五个制动器均不制动时，变速器为空档。变速器通过控制五个制动器制动来控制档位。本实施例五档变速器相邻档位之间的齿比间距近似相等，偏差小于0.3％；传动结构简单，控制结构简单，可作自行车变速器。
实施例5：采用三排同种中心轮(太阳轮)行星排的本发明变速器五例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用三排同种中心轮(太阳轮)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是太阳轮，是同一种中心轮。使三排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。注：如果改行星轮为轴承，行星架为轴，可参见图7。
行星排结构是星连接行星排结构。设Zt1为一号行星排太阳轮齿数，Zt2为二号行星排太阳轮齿数，Zt3为三号行星排太阳轮齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zt1＝20，Zt2＝28，Zt3＝36，X1＝17，X2＝24，X3＝31。
输入输出锁止端是：以行星架(7)作为输入端连接动力装置。一号行星排太阳轮(1)作为输出端连接动力使用设备。二号行星排太阳轮(2)、三号行星排太阳轮(3)各作为一个锁止端各连接一个制动器(8)。这些连接是通过多层套筒轴实现的，参见图6。
各制动器是：本实施例采用二个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接三号行星排太阳轮(3)的制动器(8)制动时，传动比为77.5,对应二档档位。连接二号行星排太阳轮(2)的制动器(8)制动时，传动比为120.0,对应一档档位。两个制动器均不制动时，变速器为空档。变速器通过控制两个制动器制动来控制档位。本实施例变速器两个档位传动比均很大，传动结构简单，控制结构简单，可作直升机主减速器兼变速器。
实施例6：采用四排同种中心轮(太阳轮)行星排的本发明变速器六例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用四排同种中心轮(太阳轮)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是太阳轮，是同一种中心轮。使四排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zt1为一号行星排太阳轮齿数，Zt2为二号行星排太阳轮齿数，Zt3为三号行星排太阳轮齿数，Zt4为四号行星排太阳轮齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zt1＝26，Zt2＝34，Zt3＝34，Zt4＝50，X1＝17，X2＝23，X3＝24，X4＝39。
输入输出锁止端是：以行星架(9)作为输入端连接动力装置。一号行星排太阳轮(1)作为输出端连接动力使用设备。二号行星排太阳轮(2)、三号行星排太阳轮(3)、四号行星排太阳轮(4)各作为一个锁止端各连接一个制动器(10)。这些连接是通过多层套筒轴实现的，参见图8。
各制动器是：本实施例采用三个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接四号行星排太阳轮(4)的制动器(10)制动时，传动比为6.183,对应三档档位。连接三号行星排太阳轮(3)的制动器(10)制动时，传动比为13.565,对应二档档位。连接二号行星排太阳轮(2)的制动器(10)制动时，传动比为29.90,对应一档档位。三个制动器均不制动时，变速器为空档。变速器通过控制三个制动器制动来控制档位。本实施例变速器相邻档位之间的齿比间距近似相等，偏差小于0.24％；传动结构简单，控制结构简单，可作电动车变速器。各档位均容易形成大传动比，全是减速传动，这 是本发明变速器的一大优点。
实施例7：采用五排同种中心轮(太阳轮)行星排的本发明变速器七例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用五排同种中心轮(太阳轮)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是太阳轮，是同一种中心轮。使五排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zt1为一号行星排太阳轮齿数，Zt2为二号行星排太阳轮齿数，Zt3为三号行星排太阳轮齿数，Zt4为四号行星排太阳轮齿数，Zt5为五号行星排太阳轮齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数，X5为五号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zt1＝26，Zt2＝34，Zt3＝34，Zt4＝50，Zt5＝50，X1＝17，X2＝23，X3＝24，X4＝39，X5＝51。
输入输出锁止端是：以行星架(11)作为输入端连接动力装置。一号行星排太阳轮(1)作为输出端连接动力使用设备。二号行星排太阳轮(2)、三号行星排太阳轮(3)、四号行星排太阳轮(4)、五号行星排太阳轮(5)各作为一个锁止端各连接一个制动器(12)。这些连接是通过多层套筒轴实现的，参见图9。
各制动器是：本实施例采用四个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接五号行星排太阳轮(5)的制动器(12)制动时，传动比为2.786,对应四档档位。连接四号行星排太阳轮(4)的制动器(12)制动时，传动比为6.183,对应三档档位。连接三号行星排太阳轮(3)的制动器(12)制动时，传动比为13.565,对应二档档位。连接二号行星排太阳轮(2)的制动器(12)制动时，传动比为29.90,对应一档档位。四个制动器均不制动时，变速器为空档。变速器通过控制四个制动器制动来控制档位。本实施例变速器相邻档位之间的齿比间距近似相等，偏差小于0.7％；传动结构简单，控制结构简单，可作机动车变速器。
实施例8：采用六排同种中心轮(太阳轮)行星排的本发明变速器八例，特征包括采用的行星排、行星排结构、输入输出锁止端和各制动器等。
采用的行星排是：本实施例采用六排同种中心轮(太阳轮)行星排。每排行星排有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮全是太阳轮，是同一种中心轮。使六排行星排的行星轮组数目均为4。行星轮为轴，行星架为轴承。
行星排结构是星连接行星排结构。设Zt1为一号行星排太阳轮齿数，Zt2为二号行星排太阳轮齿数，Zt3为三号行星排太阳轮齿数，Zt4为四号行星排太阳轮齿数，Zt5为五号行星排太阳轮齿数，Zt6为六号行星排太阳轮齿数，X1为一号行星排行星轮齿数，X2为二号行星排行星轮齿数，X3为三号行星排行星轮齿数，X4为四号行星排行星轮齿数，X5为五号行星排行星轮齿数，X6为六号行星排行星轮齿数。本实施例中各部件齿轮齿数确定为：Zt1＝26，Zt2＝30，Zt3＝34，Zt4＝34，Zt5＝50，Zt6＝50，X1＝17，X2＝19，X3＝23，X4＝24，X5＝39，X6＝51。
输入输出锁止端是：以行星架(13)作为输入端连接动力装置。一号行星排太阳轮(1)作为输出端连接动力使用设备。二号行星排太阳轮(2)、三号行星排太阳轮(3)、四号行星排太阳轮(4)、五号行星排太阳轮(5)、六号行星排太阳轮(6)各作为一个锁止端各连接一个制动器(14)。这些连接是通过多层套筒轴实现的，参见图10。
各制动器是：本实施例采用五个制动器，各与一个锁止端连接。制动器为电磁制动器，受换档控制装置控制。
控制一个制动器制动就锁止与之连接的中心轮，使该中心轮转速为零；控制一个制动器不制动就不锁止与之连接的中心轮。连接六号行星排太阳轮(6)的制动器(14)制动时，传动比为2.786,对应四档档位。连接五号行星排太阳轮(5)的制动器(14)制动时，传动比为6.183,对应三档档位。连接四号行星排太阳轮(4)的制动器(14)制动时，传动比为13.565,对应二档档位。连接三号行星排太阳轮(3)的制动器(14)制动时，传动比为29.90,对应一档档位。连接二号行星排太阳轮(2)的制动器(14)制动时，传动比为-30.875,对应倒档档位。五个制动器均不制动时，变速器为空档。变速器通过控制五个制动器制动来控制档位。本实施例正四档倒一档变速器相邻档位之间的齿比间距近似相等，偏差小于0.7％；传动结构简单，控制结构简单，可作机动车变速器。
以上显示和描述了本发明的基本原理、主要特征和优点。本行业的技术人员应该了解，本发明不受上述实施例的限制，在不脱离本发明精神和范围的前提下本发明还会有各种变化与改进，这些变化和改进都落入要求保护的本发明范围内。本发明要求保护范围由所附的权利要求及同等物界定。

Claims (3)

  1. 同种中心轮行星排变速器，特征包括采用的行星排、行星排结构、输入输出锁止端、各制动器等几个方面，各方面特征如下：采用的行星排是：本发明采用不少于三排的同种中心轮行星排，每排行星排是不完整单层星行星排，有一个中心轮、一个带行星轮的行星架这两个部件；各行星排中的中心轮要么全是太阳轮、要么全是内齿圈，一个变速器中所有中心轮是同一种中心轮，所述同种中心轮行星排包括同种中心轮(太阳轮)行星排、同种中心轮(内齿圈)行星排这两种，同一种中心轮均是太阳轮的各行星排称为同种中心轮(太阳轮)行星排，同一种中心轮均是内齿圈的各行星排称为同种中心轮(内齿圈)行星排，本发明在一个变速器中选取采用其中一种来组成变速器，选取同种中心轮(太阳轮)行星排就组成同种中心轮(太阳轮)行星排变速器，选取同种中心轮(内齿圈)行星排就组成同种中心轮(内齿圈)行星排变速器；
    行星排结构是星连接行星排结构，所述星连接行星排结构即：对多排单层星行星排，设置它们的行星轮组数目相同，调整各行星排尺寸大小，直至各行星排中行星轮轴线到行星排中心轴线的距离都相等，把行星排中每个行星轮与相邻行星排的行星轮轴线对齐并分组相连接，这样的连接称为星连接，这样的行星排结构就是星连接行星排结构；
    输入输出锁止端是：以行星架作为输入端连接动力装置，任取一个中心轮作为输出端连接动力使用设备，其余中心轮各作为一个锁止端各连接一个制动器，制动器受换档控制装置控制；
    各制动器是：本发明采用不少于二个制动器作为变速器的控制器，各与一个锁止端连接，制动器可受控制处于制动状态、半制动状态和非制动状态。
  2. 如权利要求1所述的同种中心轮行星排变速器，其运作特征是：控制一个制动器制动使与之连接的中心轮转速为零；输入端输入转速时，控制一个制动器制动，输出端必然形成一个输出转速，与输入转速构成一个确定的比例关系，变速器形成一个传动比，对应一个档位；控制另一个制动器制动，输出端必然形成另一个输出转速，与输入转速构成另一个确定的比例关系，变速器形成另一个传动比，对应另一个档位；依此类推，本发明变速器通过控制各制动器制动来控制档位；当控制一个制动器半制动时，变速器在相应的这个档位半联动；当控制各制动器均不制动时，变速器为空档；当控制两个以上制动器制动时，变速器停转。
  3. 如权利要求1所述的同种中心轮行星排变速器，其特征还在于：本发明变速器的逆变速器，采用的行星排不变，行星排结构不变，各制动器不变，输入输出锁止端改为：以行星架作为输出端连接动力使用设备，任取一个中心轮作为输入端连接动力装置，其余中心轮各作为一个锁止端各连接一个制动器；其运作特征不变；本发明变速器的逆变速器也属于本发明的保护范围。
    行星排作为变速器，不与任何动力、制动设备连接。已解释
PCT/CN2020/083140 2019-04-07 2020-04-03 同种中心轮行星排变速器 WO2020207340A1 (zh)

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