CN213008688U

CN213008688U - Double-folding circumferential driver

Info

Publication number: CN213008688U
Application number: CN202020574583.XU
Authority: CN
Inventors: 罗灿
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-04-17
Filing date: 2020-04-17
Publication date: 2021-04-20
Anticipated expiration: 2030-04-17

Abstract

The utility model discloses two folding circumference transmission wares, including input shaft, one-way commutator, double-circuit book to the ware, thoughtlessly move the planet row, turn to support and output shaft. The input shaft is connected with a power device; the single-way commutator converts one rotation into two rotations with equal rotation speed and opposite directions; the double-path deflector is provided with two pairs of bevel gear pairs, and the unidirectional deflection torque automatically generated by the first driving bevel gear to the first driven bevel gear is the same as and opposite to the unidirectional deflection torque automatically generated by the second driving bevel gear to the second driven bevel gear; the mixed planet row enables two rotating speeds of the inner shaft of the sleeve shaft rotating together and the outer shaft of the sleeve shaft rotating together to be synthesized into the rotating speed of the output shaft; the steering support is controlled to revolve around the axis of the reversing sleeve shaft; the output shaft is connected with power using equipment, and the transmission torque is large. The control device drives the steering support to revolve, the control torque is small, the control device is small, and the rotation and the revolution of the output shaft are not interfered with each other.

Description

Double-folding circumferential driver

Technical Field

The utility model relates to a transmission structure of power consumer such as screw is folded to the ware, is thoughtlessly moved the planet row, is turned to support and output shaft by input shaft, one way commutator, double-circuit and is constituteed, and characteristics are when transmitting power from input shaft to output shaft, and transmission torque is big, and output shaft rotation and revolution are mutual noninterference, and control revolution's control torque is very little, and controlling means is very little. Referred to as a bi-folded circumferential driver.

Background

In a traditional fixed-axis propeller thruster, a propeller can rotate but a propeller shaft is fixed and cannot revolve. The traditional propeller with a moving shaft drives an output shaft to rotate by a bevel gear pair, and the output shaft is forced to revolve around the axis of an input shaft by driving an output shaft bearing. Because the bearing of the output shaft is driven to revolve to overcome the unidirectional deflection torque, and the control torque required by forward rotation and reverse rotation is different in size when the revolution is controlled, the rated control torque is very large, and the control device is very large. The transmission structure of the traditional propeller with a moving shaft has unidirectional rotation torque, so that the mutual interference of the rotation and the revolution of an output shaft cannot be decoupled, and a real circumferential driver cannot be calculated. The unidirectional deflection torque is torque which is automatically generated by the bevel gear pair when power is transmitted and enables the output shaft to revolve around the axis of the input shaft in a unidirectional mode, and is positively correlated with the input torque. The rotation of the output shaft around the axis of the output shaft is autorotation, and the rotation of the output shaft around the axis of the input shaft (or the axis of the reverse sleeve shaft) is revolution. The invention also discloses a hundred-direction driver, which does not generate unidirectional deflection torque when transmitting power, does not interfere rotation and revolution of an output shaft, has small control torque and small control device and is a real circumferential driver. But the drive torque of the hundred-direction driver is smaller. The aviation industry and the navigation industry need a transmission structure of a circumferential transmission device, wherein the rotation and the revolution of an output shaft do not interfere with each other, a control device is small, and transmission torque is large. The utility model provides a two-fold circumferential transmission ware of this kind of transmission structure promptly. The transmission structure can also be used for a cross-joint rotating part of a robot and a machine tool rotating part.

SUMMERY OF THE UTILITY MODEL

The utility model discloses two folding circumference transmission wares comprise input shaft, one way commutator, double-circuit book to the ware, thoughtlessly move the planet row, turn to support and output shaft.

The input shaft is connected with the power device for inputting power.

The one-way commutator is used for converting one rotation into two rotations with equal rotation speed and opposite rotation directions, and transmitting the two rotations in the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft respectively. The one-way commutator has four forms, the utility model discloses optional one of them: one way diverter in the form of a one way diverter includes a front bevel gear, a reversing bevel gear carrier, a rear bevel gear and a reversing sleeve shaft, see 2, 3, 4, 5 and 6 in fig. 1. The reverse sleeve shaft is two shafts which are nested with each other on the axial line of the reverse sleeve shaft and respectively is an inner shaft of the reverse sleeve shaft and an outer shaft of the reverse sleeve shaft. Fixing an input shaft bearing, and arranging a front bevel gear on the input shaft; a reversing bevel gear is meshed with the front bevel gear, the axis of the reversing bevel gear is perpendicular to the axis of the input shaft, and a support of the reversing bevel gear is fixed. The reversing sleeve shaft and the input shaft are arranged on the same axis, a bearing of the reversing sleeve shaft is fixed, and a rear bevel gear is arranged on the outer shaft of the reversing sleeve shaft and meshed with the reversing bevel gear. Directly connecting the input shaft with the inner shaft of the reverse sleeve shaft. The front bevel gear and the rear bevel gear form indirect connection through a reversing bevel gear. The number of the front bevel gear teeth is equal to that of the rear bevel gear teeth, so that the transmission ratio of the indirect connection is equal to-1.0. In the one-way commutator, two parts of the inner shaft of the reversing sleeve shaft and the outer shaft of the reversing sleeve shaft have the same rotating speed and opposite rotating directions. A form two one-way commutator comprising an inner driving bevel gear, an outer driving bevel gear, an inner driven bevel gear, an outer driven bevel gear and a reversing sleeve shaft, see 2, 3, 4, 5 and 6 in figure 2. The input shaft is fixed with a bearing, the input shaft is provided with an inner driving bevel gear and an outer driving bevel gear which are respectively arranged on two sides of the axis of the reverse sleeve shaft, the inner driving bevel gear is arranged after penetrating through the axis of the reverse sleeve shaft, and the outer driving bevel gear is arranged without penetrating through the axis of the reverse sleeve shaft. And fixing the reverse sleeve shaft bearing, and setting an included angle formed by intersecting the axis of the reverse sleeve shaft and the axis of the coaxial shaft, wherein the included angle is a transmission angle, and determining the value of the transmission angle according to actual needs. An inner driven bevel gear is arranged on an inner shaft of the reverse sleeve shaft, and the inner driven bevel gear is kept meshed with the inner driving bevel gear; and an outer driven bevel gear is arranged on an outer shaft of the reverse sleeve shaft, and the outer driven bevel gear is kept meshed with the outer driving bevel gear. The transmission ratio from the input shaft to the inner shaft of the reversing sleeve shaft is equal to the negative value of the transmission ratio from the input shaft to the outer shaft of the reversing sleeve shaft by setting the tooth number of the inner driving bevel gear, the tooth number of the outer driving bevel gear, the tooth number of the inner driven bevel gear and the tooth number of the outer driven bevel gear; for example: the number of teeth of the inner driving bevel gear is equal to the number of teeth of the inner driven bevel gear, and the number of teeth of the outer driving bevel gear is equal to the number of teeth of the outer driven bevel gear. In the two-way one-way commutator, two parts of a reverse sleeve shaft inner shaft and a reverse sleeve shaft outer shaft have the same rotating speed and opposite rotating directions. A form three one-way commutator comprising a front gear, an inner side gear, an outer side front gear, an outer side rear gear, a rear gear and a reversing sleeve shaft, see 2, 25, 3, 4, 5 and 6 in figure 3. The input shaft bearing is fixed, and the input shaft is provided with a front gear; an inner paraxial shaft and an outer paraxial shaft are arranged, the axes of the inner paraxial shaft and the outer paraxial shaft are respectively parallel to the axis of the coaxial shaft, and bearings of the inner paraxial shaft and the outer paraxial shaft are fixed; a rear gear is disposed on the reverse sleeve shaft outer shaft. The front gear is meshed with the front gear of the outer paraxial shaft, the rear gear of the outer paraxial shaft is meshed with the gear of the inner paraxial shaft, and the gear of the inner paraxial shaft is meshed with the rear gear. The reverse sleeve shaft and the input shaft are arranged on the same axis, a bearing of the reverse sleeve shaft is fixed, and the input shaft and the inner shaft of the reverse sleeve shaft are directly connected. The front gear and the rear gear form indirect connection through the outer paraxial front gear, the outer paraxial rear gear and the inner paraxial gear. By setting the number of internal paraxial gear teeth, the number of external paraxial front gear teeth, the number of external paraxial rear gear teeth, the number of front gear teeth, and the number of rear gear teeth, the transmission ratio of this indirect connection is made equal to-1.0, for example: the outer side shaft rear gear tooth number is equal to the inner side shaft gear tooth number which is equal to the rear gear tooth number which is equal to N, the front gear tooth number is equal to the outer side shaft front gear tooth number which is equal to 2 x N, and N is a natural number which is larger than or equal to 8. In the three-way commutator, two parts of a reverse sleeve shaft inner shaft and a reverse sleeve shaft outer shaft have the same rotating speed and opposite rotating directions. A form four one-way commutator comprising an inner driving bevel gear, an outer driving bevel gear, an inner driven bevel gear, an outer driven bevel gear and a reversing sleeve shaft, see 2, 3, 4, 5 and 6 in fig. 4. The input shaft is fixed with a bearing, the input shaft is provided with an inner driving bevel gear and an outer driving bevel gear which are respectively arranged on two sides of the axis of the reverse sleeve shaft, the inner driving bevel gear is arranged without passing through the axis of the reverse sleeve shaft, and the outer driving bevel gear is arranged after passing through the axis of the reverse sleeve shaft. And fixing the reverse sleeve shaft bearing, and setting an included angle formed by intersecting the axis of the reverse sleeve shaft and the axis of the input shaft, wherein the included angle is a transmission angle, and determining the value of the transmission angle according to actual needs. An inner driven bevel gear is arranged on an inner shaft of the reverse sleeve shaft, and the inner driven bevel gear is kept meshed with the inner driving bevel gear; and an outer driven bevel gear is arranged on an outer shaft of the reverse sleeve shaft, and the outer driven bevel gear is kept meshed with the outer driving bevel gear. The transmission ratio from the input shaft to the inner shaft of the reversing sleeve shaft is equal to the negative value of the transmission ratio from the input shaft to the outer shaft of the reversing sleeve shaft by setting the tooth number of the inner driving bevel gear, the tooth number of the outer driving bevel gear, the tooth number of the inner driven bevel gear and the tooth number of the outer driven bevel gear; for example: the number of teeth of the inner driving bevel gear is equal to the number of teeth of the inner driven bevel gear, and the number of teeth of the outer driving bevel gear is equal to the number of teeth of the outer driven bevel gear. In the four-way commutator, two parts of a reverse sleeve shaft inner shaft and a reverse sleeve shaft outer shaft have the same rotating speed and opposite rotating directions.

The double-path deflector is used for arranging two pairs of bevel gear pairs, a shaft where the first driving bevel gear is located and a shaft where the second driving bevel gear is located form a reverse sleeve shaft, and a shaft where the second driven bevel gear is located form a same-rotation sleeve shaft. Compared with the unidirectional deflection torque automatically generated by the second driving bevel gear pair and the second driven bevel gear, the unidirectional deflection torque automatically generated by the first driving bevel gear pair and the first driven bevel gear pair is the same in magnitude and opposite in direction. The two unidirectional yawing moments cancel each other out by being transmitted through the co-rotating sleeve shaft. The bevel gear pair is a mature technology, the bevel gear pair is a pair of bevel gears which are meshed with each other and used for transmission, the axis of an input shaft of the bevel gear pair is intersected with the axis of an output shaft of the bevel gear pair, and the intersected included angle is called a deflecting angle. The two bevel gear pairs are bevel gear pairs consisting of a first driving bevel gear and a first driven bevel gear, and also are bevel gear pairs consisting of a second driving bevel gear and a second driven bevel gear. The co-rotating sleeve shaft is two shafts which are mutually nested on the co-rotating sleeve shaft axis and respectively is a co-rotating sleeve shaft inner shaft and a co-rotating sleeve shaft outer shaft. The axis of the same rotating sleeve shaft is intersected with the axis of the reverse rotating sleeve shaft, and the intersection angle is a turning angle. The two-way deflector comprises a first driving bevel gear, a first driven bevel gear, a second driving bevel gear, a second driven bevel gear and a sleeve shaft rotating in the same direction. The double-circuit is rolled over to the ware and is had two kinds of forms, and the part sets up the meshing different, the utility model discloses optional one of them: the dual-path deflector is characterized in that a first driving bevel gear is arranged on an inner shaft of a reverse sleeve shaft, a second driving bevel gear is arranged on an outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft penetrates through the axial line of a same-rotation sleeve shaft, and the outer shaft of the reverse sleeve shaft does not penetrate through the axial line of the same-rotation sleeve shaft; a first driven bevel gear is arranged on an inner shaft of the co-rotating sleeve shaft, and a second driven bevel gear is arranged on an outer shaft of the co-rotating sleeve shaft; keeping the first driving bevel gear meshed with the first driven bevel gear and keeping the second driving bevel gear meshed with the second driven bevel gear. See 7, 8, 9, 10 and 11 in fig. 1. The dual-path deflector is characterized in that a first driving bevel gear is arranged in an inner shaft of a reverse sleeve shaft, a second driving bevel gear is arranged on an outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft penetrates through the axis of a co-rotating sleeve shaft, and the outer shaft of the reverse sleeve shaft does not penetrate through the axis of the co-rotating sleeve shaft; a first driven bevel gear is arranged on an outer shaft of the co-rotating sleeve shaft, and a second driven bevel gear is arranged on an inner shaft of the co-rotating sleeve shaft; keeping the first driving bevel gear meshed with the first driven bevel gear and keeping the second driving bevel gear meshed with the second driven bevel gear. See 7, 8, 9, 10 and 11 in fig. 2. The two-way direction folding device in the two forms ensures that the transmission ratio from the first driving bevel gear to the first driven bevel gear is equal to the negative value of the transmission ratio from the second driving bevel gear to the second driven bevel gear by setting the number of the first driving bevel gear teeth, the number of the second driving bevel gear teeth, the number of the first driven bevel gear teeth and the number of the second driven bevel gear teeth; for example: set up first initiative bevel gear number of teeth ═ second passive bevel gear number of teeth, and second initiative bevel gear number of teeth ═ second passive bevel gear number of teeth.

The function of the mixed-rotation planetary row is to synthesize the rotation speed of the output shaft by using two rotation speed components with the same rotation speed and the same rotation direction in two rotation speeds of the inner shaft of the same-rotation sleeve shaft and the outer shaft of the same-rotation sleeve shaft, and two rotation speed components with the same rotation speed and the same rotation speed in the opposite rotation directions in the two rotation speeds of the inner shaft of the same-rotation sleeve shaft and the outer shaft of the same-rotation sleeve shaft do not interfere with the rotation speed of the output shaft, so that the rotation and revolution of. The mixed-moving planet row has five forms, and the utility model can select one of the five forms: the first mixing row uses a bevel gear row comprising a left bevel gear, a planet carrier with bevel gear planets and a right bevel gear, see 12, 21, 14 and 13 in fig. 1. The left bevel gear is meshed with the bevel gear planet wheel, and the bevel gear planet wheel is meshed with the right bevel gear. When the left bevel gear tooth number is equal to the right bevel gear tooth number, the planet row is used as a mixed motion planet row. The right bevel gear and the left bevel gear are respectively connected with an inner shaft of a sleeve shaft rotating together and an outer shaft of the sleeve shaft rotating together, and the planet carrier is connected with an output shaft. The second hybrid planet row adopts a double-sun-wheel variable-linear-speed planet row which comprises a small sun wheel, a planet carrier with left and right planet wheels and a large sun wheel, and is shown as 12, 23, 24, 14 and 13 in fig. 2. The small sun wheel is meshed with the left planet wheel, the right planet wheel is meshed with the large sun wheel, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. Through setting up little sun gear tooth number, big sun gear tooth number, left side planet wheel tooth number and right side planet wheel tooth number, when making its planet row characteristic parameter a become 2.0, as thoughtlessly moving the planet row. The small sun gear and the planet carrier are respectively connected with the outer shaft of the same-rotation sleeve shaft and the inner shaft of the same-rotation sleeve shaft, and the large sun gear is connected with the output shaft. For example, when the small sun gear tooth number is 20, the right planet gear tooth number is 18, the large sun gear tooth number is 24, and the left planet gear tooth number is 30, the characteristic parameter a of the planet row is 2.0. The third mixed-action planetary row adopts a double-inner-gear-ring variable-linear-speed planetary row which comprises a large inner gear ring, a planet carrier with left and right planet gears and a small inner gear ring, and is shown as 12, 23, 24, 14 and 13 in fig. 3. The large inner gear ring is meshed with the left planet wheel, the right planet wheel is meshed with the small inner gear ring, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. The characteristic parameter a of the planet row is 2.0 by setting the tooth number of the large inner gear ring, the tooth number of the small inner gear ring, the tooth number of the left planet wheel and the tooth number of the right planet wheel, and the planet row is used as a mixed-motion planet row. The large inner gear ring and the planet carrier are respectively connected with the outer shaft of the sleeve shaft rotating together and the inner shaft of the sleeve shaft rotating together, and the small inner gear ring is connected with the output shaft. For example, when the large ring gear tooth number is 60, the left planet gear tooth number is 20, the right planet gear tooth number is 16, and the small ring gear tooth number is 96, the characteristic parameter a of the planet row is 2.0. The four-hybrid-action planetary row adopts a double-sun-wheel inner and outer planet variable linear speed planetary row which comprises a small sun wheel, a planet carrier with an inner-layer planet wheel left planet wheel and a right planet wheel and a large sun wheel, and is shown as 12, 25, 23, 24, 14 and 13 in fig. 4. The small sun wheel is meshed with the inner planet wheel, the inner planet wheel is meshed with the left planet wheel, the right planet wheel is meshed with the large sun wheel, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. Through setting up little sun gear tooth number, big sun gear tooth number, left side planet gear tooth number, right side planet gear tooth number and inlayer planet gear tooth number, when making its planet row characteristic parameter a become 1.0, as thoughtlessly moving the planet row. The small sun gear and the large sun gear are respectively connected with the outer shaft of the same-rotation sleeve shaft and the inner shaft of the same-rotation sleeve shaft, and the planet carrier is connected with the output shaft. For example, when the number of small sun gear teeth is equal to the number of left planet gears, 18, and the number of large sun gear teeth is equal to the number of right planet gears, 22, the characteristic parameter a of the planet row is equal to 1.0. The form five mixed-action planetary row adopts a common double-layer planetary row which comprises a sun gear, a planetary carrier with inner planetary gears and outer planetary gears and an inner gear ring, and is shown as 12, 21, 22, 14 and 13 in fig. 5. The sun wheel is meshed with the inner planet wheel, the inner planet wheel is meshed with the outer planet wheel, and the outer planet wheel is meshed with the inner gear ring. And when the number of teeth of the inner gear ring is equal to the number of teeth of the sun gear x 2, the inner gear ring is used as a mixed-motion planetary row. The sun gear and the planet carrier are respectively connected with the inner shaft of the same-rotation sleeve shaft and the outer shaft of the same-rotation sleeve shaft, and the inner gear ring is connected with the output shaft. The double-sun-wheel variable-linear-speed planetary row, the double-inner-gear-ring variable-linear-speed planetary row and the double-sun-wheel inner and outer-planet variable-linear-speed planetary row are all variable-linear-speed planetary rows which adopt mature technologies, and the double-sun-wheel variable-linear-speed planetary row is called as a double-row external-engagement planetary gear train in some textbooks. The variable linear speed planetary gear is a special planetary gear, a certain layer of planetary gears are used as variable linear speed planetary gears, a left planetary gear and a corresponding right planetary gear are arranged on each variable linear speed planetary gear shaft, the left planetary gear and the corresponding right planetary gear are coaxial and rotate at the same speed but have unequal reference circle linear speeds, namely 'variable linear speed', the left planetary gear and the right planetary gear are not simultaneously meshed with the same sun gear (or the same inner gear ring), and parameters such as the tooth number, the gear modulus and the like of the left planetary gear and the right planetary gear are not completely equal; the two central wheels of the variable-speed planetary gear are respectively a sun gear and an inner gear ring, and the two central wheels of the variable-speed planetary gear are both two sun gears or both two inner gear rings; the characteristic parameter a of the variable-speed planetary row with the two sun gears is equal to the tooth number of the large sun gear, the tooth number of the left planetary gear/(the tooth number of the small sun gear, the tooth number of the right planetary gear), and the characteristic parameter a of the variable-speed planetary row with the two inner gear rings is equal to the tooth number of the small inner gear ring, the tooth number of the left planetary gear/(the tooth number of the large inner gear ring, the tooth number of the right planetary gear). Compare to the concentrated transmission power of planet wheel with hundred to the driver adoption, the utility model discloses mix and move the planet row and adopt a plurality of planet wheels reposition of redundant personnel transmission power, transmission torque is big. The large transmission torque means that: under the condition of the same parameters of materials and the like, the transmission mechanism can transmit larger torque when the volume is the same, or the transmission mechanism can transmit the same torque by depending on smaller volume. The selection of the numbers of the bevel gear planet wheels, the left planet wheel, the right planet wheel, the inner planet wheel, the outer planet wheel and the like adopts a mature technology, one of the numbers of the five planet wheels, namely two, three, four, five and six, is selected, the numbers of various planet wheels in the same planet row are the same, and the selection is carried out according to the actual requirement by combining the assembly conditions of the planet row; the utility model discloses these several kinds of planet wheel numbers all select to be four in embodiment 1-embodiment 5.

The steering support is controlled by the control device to drive the co-rotating sleeve shaft and the output shaft to revolve around the axis of the counter-rotating sleeve shaft. The steering support comprises a fixed shaft component, a support, a movable shaft bearing and an output bearing. The dead axle part is the machinery that rotates around reverse sleeve axle axis, and the dead axle part has two kinds of forms, the utility model discloses optional one of them: in one form, a bearing-type fixed shaft member is selected to hold a shaft on the axis of the reversing sleeve shaft, and a bearing is provided around the shaft to support the shaft, and serves as the fixed shaft member. Referring to fig. 2, the fixed shaft member is 16, the one shaft held on the axis of the counter rotating quill is a fixed shaft 17, and the fixed shaft member is a bearing disposed outside the fixed shaft; referring again to fig. 4, the fixed shaft member is 16, the one shaft that remains on the reverse quill axis is the reverse quill 6, and the fixed shaft member is the bearing on the right side disposed outside of the reverse quill. The second type of fixed shaft member is a shaft-type fixed shaft member, the shaft is a shaft provided on the axis of the reverse sleeve shaft, the bearing thereof is a fixed bearing, and the shaft serves as the fixed shaft member. Referring to fig. 1, the fixed shaft member is 16, which is a shaft disposed on the axis of the reverse sleeve shaft, and its bearing is a fixed bearing 17. A moving shaft bearing is arranged outside the co-rotating sleeve shaft to support the co-rotating sleeve shaft, and an output bearing is arranged outside the output shaft to support the output shaft. The support is a connecting machine directly connecting the fixed shaft part, the movable shaft bearing and the output bearing, adopts a mature technology and has the function of implementing direct connection without conflict with other parts. The fixed shaft part, the movable shaft bearing and the output bearing are directly connected by the bracket, and the whole steering support can revolve around the axis of the reversing sleeve shaft to rotate. The connection between the steering support and the control device is one of direct connection and indirect connection, and the steering support is driven by the control device to revolve and rotate. The circumferential transmission means that power using equipment such as propellers revolves around the axis of the reversing sleeve shaft in the forward direction and the reverse direction while rotating around the axis of the output shaft, and the revolution angle range is infinite under the condition of no other mechanical limitation.

The output shaft is connected with power utilization equipment such as a propeller and the like to output power. The propeller (or rotor) is a mature technology and comprises a blade, a variable pitch device and the like.

The control device drives the steering support to rotate around the axis of the reverse sleeve shaft, and the output shaft revolves and rotates. When the control device is not driven, the output shaft does not revolve. The control torque required by the forward rotation and the reverse rotation is the same during revolution rotation, the control torque is very small, the control device is very small, and the rotation and the revolution of the output shaft are not interfered with each other.

The power plant employs mature technologies such as electric power plants, steam power plants, fuel power plants. The power-using equipment employs mature technologies such as propellers, rotors, trans-articular rotating parts of robots, machine tool rotating parts, and the like. The control device adopts the mature technology, such as an electric mechanism, a mechanical mechanism or a hydraulic mechanism, and the base of the control device is fixed. The shaft fixing, the bearing fixing, the support fixing or the base fixing are mature technologies, namely, the shaft, the bearing, the support or the base are directly connected with a ship body or a machine body through a connecting machine, and the rotating speed of the shaft, the bearing, the support or the base is enabled to be zero through the fixing shaft. The sleeve shaft is a mature technology, each bearing supports each layer of shaft, and the bearings can rotate relative to the shafts and can not slide relative to each other along the axial direction. The bearing is a mature technology, the bearing supports the shaft, and the bearing and the shaft can rotate relatively but do not slide relatively along the axial direction. The direct connection adopts a mature technology, namely, the rotation speed of the connected objects is enabled to be the same through mechanical connection, for example, the rotation speed of the connected objects is enabled to be the same through casting, bonding, welding, bolt connection, riveting and the like of a connecting piece. The indirect connection adopts a mature technology, namely the rotation speed determinacy of two driven objects is related through mechanical transmission, for example, the indirect connection is formed through a gear pair, a bevel gear pair, a worm gear, a gear rack, a connecting rod mechanism and chain belt transmission. The maintaining synchronization is directly connecting the connected objects, the connection is usually a direct connection, and an indirect connection is specifically and explicitly shown. A gear and a bevel gear are arranged on a certain shaft, and the arranged gear and the bevel gear are kept synchronous with the shaft. The gear ratio is equal to the rotational speed of the input member divided by the rotational speed of the output member. The symbol is a multiplication symbol,/a division symbol, and an equal symbol.

The utility model discloses two books circumference drivers, its useful part lies in: the transmission structure of the circumferential transmission device is provided, the output shaft can be controlled to revolve around the axis of the reversing sleeve shaft to rotate when power is transmitted, the control torque is small, the control device is small, and the rotation and revolution of the output shaft are not interfered with each other. The function of the propeller far exceeds that of the traditional propeller with a moving shaft. The transmission structure is completely different from that of the hundred-direction driver, and the transmission moment of the transmission structure is larger than that of the hundred-direction driver. The self-rotation transmission and revolution control of power using equipment such as a propeller and the like can be improved, and the self-rotation transmission and revolution control device can also be used for a joint-spanning rotating part of a robot and a machine tool rotating part.

Drawings

Fig. 1 is an example of a double-folded circumferential transmission, which is also a schematic diagram of embodiment 1 of the present invention. In the figure, 1 is an input shaft, 2 is a front bevel gear, 3 is a reversing bevel gear, 4 is a reversing bevel gear support, 5 is a rear bevel gear, 6 is a reversing sleeve shaft, 7 is a first driving bevel gear, 8 is a second driving bevel gear, 9 is a first driven bevel gear, 10 is a second driven bevel gear, 11 is a co-rotating sleeve shaft, 12 is a left bevel gear, 13 is a right bevel gear, 14 is a planet carrier, 15 is an output shaft, 16 is a fixed shaft component, 17 is a fixed bearing, 18 is a support, 19 is a moving shaft bearing, 20 is an output bearing, and 21 is a bevel planet gear.

Fig. 2 is a schematic diagram of a two-fold circumferential transmission according to a second embodiment, which is also a schematic diagram of embodiment 2 of the present invention. In the figure, 1 is an input shaft, 2 is an inner driving bevel gear, 3 is an outer driving bevel gear, 4 is an inner driven bevel gear, 5 is an outer driven bevel gear, 6 is a reverse sleeve shaft, 7 is a first driving bevel gear, 8 is a second driving bevel gear, 9 is a first driven bevel gear, 10 is a second driven bevel gear, 11 is a same-rotation sleeve shaft, 12 is a small sun gear, 13 is a large sun gear, 14 is a planet carrier, 15 is an output shaft, 16 is a fixed shaft component, 17 is a fixed shaft, 18 is a support, 19 is a moving shaft bearing, 20 is an output bearing, 21 is a worm wheel, 22 is a worm, 23 is a left planetary wheel, and 24 is a right planetary wheel.

Fig. 3 is a schematic diagram of three examples of a double-folded circumferential transmission, which is also a schematic diagram of embodiment 3 of the present invention. In the figure, 1 is an input shaft, 2 is a front gear, 3 is an outer paraxial front gear, 4 is an outer paraxial rear gear, 5 is a rear gear, 6 is a reverse sleeve shaft, 7 is a first driving bevel gear, 8 is a second driving bevel gear, 9 is a first driven bevel gear, 10 is a second driven bevel gear, 11 is a same-rotation sleeve shaft, 12 is a large inner gear ring, 13 is a small inner gear ring, 14 is a planet carrier, 15 is an output shaft, 16 is a fixed shaft part, 17 is a fixed bearing, 18 is a support, 19 is a movable shaft bearing, 20 is an output bearing, 21 is a worm wheel, 22 is a worm, 23 is a left planetary wheel, 24 is a right planetary wheel, and 25 is an inner paraxial gear.

Fig. 4 is a schematic diagram of four examples of the double-folded circumferential transmission, which is also a schematic diagram of embodiment 4 of the present invention. In the figure, 1 is an input shaft, 2 is an inner driving bevel gear, 3 is an outer driving bevel gear, 4 is an inner driven bevel gear, 5 is an outer driven bevel gear, 6 is a reverse sleeve shaft, 7 is a first driving bevel gear, 8 is a second driving bevel gear, 9 is a first driven bevel gear, 10 is a second driven bevel gear, 11 is a same-rotation sleeve shaft, 12 is a small sun gear, 13 is a large sun gear, 14 is a planet carrier, 15 is an output shaft, 16 is a fixed shaft part, 17 is a fixed reverse sleeve shaft bearing, 18 is a support, 19 is a moving shaft bearing, 20 is an output bearing, 21 is a worm gear, 22 is a worm, 23 is a left planetary gear, 24 is a right planetary gear, and 25 is an inner planetary gear.

Fig. 5 is a schematic diagram of five examples of the double-folded circumferential transmission, which is also a schematic diagram of embodiment 5 of the present invention. In the figure, 1 is an input shaft, 2 is a front bevel gear, 3 is two reversing bevel gears, 4 is two reversing bevel gear supports, 5 is a rear bevel gear, 6 is a reversing sleeve shaft, 7 is a first driving bevel gear, 8 is a second driving bevel gear, 9 is two first driven bevel gears, 10 is two second driven bevel gears, 11 is two co-rotating sleeve shafts, 12 is two sun gears, 13 is two inner gear rings, 14 is two planet carriers, 15 is two output shafts, 16 is a fixed shaft component, 17 is a fixed bearing, 18 is a support, 19 is two moving shaft bearings, 20 is two output bearings, 21 is an inner planet gear, and 22 is an outer planet gear.

In the figures, parts of the bearings are not shown. The ground symbol indicates that the shaft, bearing, mount, or base is fixed. The components are only schematic in relation to each other and do not reflect actual dimensions.

Detailed Description

Example 1: the utility model discloses embodiment 1 of two books circumference transmission for the transmission of boats and ships screw comprises input shaft 1, single way commutator, double-circuit book to the ware, thoughtlessly move the planet row, turn to support and output shaft 15. See fig. 1.

The input shaft 1 is connected with the power device for inputting power.

The one-way commutator is in a form of one-way commutator and comprises a front bevel gear 2, a reversing bevel gear 3, a reversing bevel gear support 4, a rear bevel gear 5 and a reversing sleeve shaft 6. An input shaft bearing is fixed, and a front bevel gear 2 is arranged on an input shaft 1; a reversing bevel gear 3 fixed by a support is meshed with the front bevel gear 2, and the axis of the reversing bevel gear is vertical to the axis of the input shaft. The reversing bevel gear is connected with a shaft, and a bearing of the reversing bevel gear is used as a fixed support. The reverse sleeve shaft 6 and the input shaft 1 are arranged on the same axis, a bearing of the reverse sleeve shaft is fixed, and a rear bevel gear 5 is arranged on the outer shaft of the reverse sleeve shaft and meshed with the reversing bevel gear 3. Directly connecting the input shaft 1 with the inner shaft of the reversing quill. The front bevel gear 2 and the rear bevel gear 5 form indirect connection through a reversing bevel gear 3. The number of the front bevel gear teeth is equal to that of the rear bevel gear teeth, so that the indirectly connected transmission ratio is equal to-1.0, and the actual transmission ratio is as follows: the tooth number of the front bevel gear is equal to that of the reversing bevel gear and is equal to that of the rear bevel gear, which is equal to 17. The two components, the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft, have the same rotating speed and opposite rotating directions.

The two-way deflector comprises a first driving bevel gear 7, a first driven bevel gear 9, a second driving bevel gear 8, a second driven bevel gear 10 and a same-rotation sleeve shaft 11. A form of a double-path deflector is adopted, the axis of the same rotating sleeve shaft is intersected with the axis of the reverse rotating sleeve shaft, the intersection angle is a deflecting angle, and the deflecting angle is 90 degrees in the embodiment. A first drive bevel gear 7 is arranged on the inner shaft of the reverse sleeve shaft, a second drive bevel gear 8 is arranged on the outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft passes through the axial line of the same-rotation sleeve shaft, and the outer shaft of the reverse sleeve shaft does not pass through the axial line of the same-rotation sleeve shaft; a first driven bevel gear 9 is arranged on the inner shaft of the co-rotating sleeve shaft, and a second driven bevel gear 10 is arranged on the outer shaft of the co-rotating sleeve shaft; keeping the first driving bevel gear meshed with the first driven bevel gear and keeping the second driving bevel gear meshed with the second driven bevel gear. Through setting up first initiative bevel gear number of teeth, second initiative bevel gear number of teeth, first passive bevel gear number of teeth and the passive bevel gear number of teeth of second, make the first transmission ratio of initiative bevel gear to first passive bevel gear equal the negative value of the transmission ratio of second initiative bevel gear to second passive bevel gear. Actually taking: the first driving bevel gear tooth number is 17, the first driven bevel gear tooth number is 19, and the second driving bevel gear tooth number is 19.

The mixed-motion planetary row adopts a form of a mixed-motion planetary row which is a bevel gear planetary row and comprises a left bevel gear 12, a planet carrier 14 with four bevel gear planetary wheels 21 and a right bevel gear 13. The left bevel gear 12 is meshed with the bevel planet gear 21, and the bevel planet gear 21 is meshed with the right bevel gear 13. Actually taking: the left bevel gear tooth number is equal to the right bevel gear tooth number is equal to 17. The right bevel gear 13 and the left bevel gear 12 are respectively connected with an inner shaft of a sleeve shaft rotating together and an outer shaft of the sleeve shaft rotating together, and the planet carrier 14 is connected with an output shaft 15.

The steering mount includes a fixed shaft member 16, a bracket 18, a moving shaft bearing 19 and an output bearing 20. The fixed shaft part adopts a form of two fixed shaft parts, the fixed shaft part 16 is a shaft type fixed shaft part and is a shaft arranged on the axis of a reverse sleeve shaft, and a bearing of the shaft is a fixed bearing 17. A moving shaft bearing 19 is provided outside the co-rotating sleeve shaft to support the co-rotating sleeve shaft 11, and an output bearing 20 is provided outside the output shaft to support the output shaft 15. The entire steering mount is rotatable about the reverse quill axis by directly connecting the fixed shaft member 16, the moving shaft bearing 19 and the output bearing 20 by the bracket 18. The fixed shaft member 16 is directly connected to the control device and revolves under the drive of the control device. The control device adopts an electric mechanism.

The output shaft 15 is connected with a ship propeller to output power.

In the embodiment, the reverse sleeve shaft is arranged in the vertical direction of the ship, the control device drives the steering support to rotate around the axis of the reverse sleeve shaft, the output shaft revolves and rotates, the propeller revolves and rotates, and the ship realizes circumferential transmission propulsion. When the control device is not driven, the output shaft does not revolve. The control torque required by the forward rotation and the reverse rotation is the same during revolution rotation, the control torque is very small, the control device is very small, and the rotation and the revolution of the output shaft are not interfered with each other.

Example 2: the utility model discloses two embodiment 2 of folding circumference transmission ware for the transmission of boats and ships screw comprises input shaft 1, single way commutator, double-circuit book to the ware, thoughtlessly move the planet row, turn to support and output shaft 15. See fig. 2.

The input shaft 1 is connected with the power device for inputting power.

The one-way commutator adopts a form of a two-way commutator and comprises an inner driving bevel gear 2, an outer driving bevel gear 3, an inner driven bevel gear 4, an outer driven bevel gear 5 and a reverse sleeve shaft 6. The input shaft bearing is fixed, an inner driving bevel gear 2 and an outer driving bevel gear 3 are arranged on the input shaft 1 and are respectively arranged on two sides of the axis of the reverse sleeve shaft, the inner driving bevel gear 2 is arranged after penetrating through the axis of the reverse sleeve shaft, and the outer driving bevel gear 3 is arranged without penetrating through the axis of the reverse sleeve shaft. The fixed reverse sleeve shaft bearing sets up the crossing contained angle that forms of reverse sleeve shaft axis and syntropy axle axis, and this contained angle is exactly the drive angle, and this embodiment drive angle is 90 degrees. An inner driven bevel gear 4 is arranged on the inner shaft of the reverse sleeve shaft, and the inner driven bevel gear 4 is kept meshed with the inner driving bevel gear 2; an outer driven bevel gear 5 is provided on the outer shaft of the reverse sleeve shaft, keeping the outer driven bevel gear 5 in mesh with the outer driving bevel gear 3. Through setting up interior initiative bevel gear number of teeth, outer initiative bevel gear number of teeth, interior passive bevel gear number of teeth and outer passive bevel gear number of teeth, make input shaft 1 to the negative value of the transmission ratio of the outer axle of reverse sleeve axle of input shaft 1 to reverse sleeve axle. Actually taking: the number of teeth of the inner driving bevel gear is equal to 17 that of the inner driven bevel gear, and the number of teeth of the outer driving bevel gear is equal to 19 that of the outer driven bevel gear. The two components, the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft, have the same rotating speed and opposite rotating directions.

The two-way deflector comprises a first driving bevel gear 7, a first driven bevel gear 9, a second driving bevel gear 8, a second driven bevel gear 10 and a same-rotation sleeve shaft 11. Adopt form two way deflector, set up with the sleeve axle axis of rotation and the crossing of reverse sleeve axle axis, the angle of intersection is the dog-ear angle, and this embodiment dog-ear angle is 90 degrees. A first drive bevel gear 7 is arranged on the inner shaft of the reverse sleeve shaft, a second drive bevel gear 8 is arranged on the outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft passes through the axial line of the same-rotation sleeve shaft, and the outer shaft of the reverse sleeve shaft does not pass through the axial line of the same-rotation sleeve shaft; a first driven bevel gear 9 is arranged on the outer shaft of the same-rotation sleeve shaft, and a second driven bevel gear 10 is arranged on the inner shaft of the same-rotation sleeve shaft; keeping the first drive bevel gear 7 meshed with the first driven bevel gear 9 and keeping the second drive bevel gear 8 meshed with the second driven bevel gear 10. By setting the number of the first driving bevel gear teeth, the number of the second driving bevel gear teeth, the number of the first driven bevel gear teeth and the number of the second driven bevel gear teeth, the transmission ratio of the first driving bevel gear 7 to the first driven bevel gear 9 is equal to the negative value of the transmission ratio of the second driving bevel gear 8 to the second driven bevel gear 10. Actually taking: the first driving bevel gear tooth number is 19, the second driving bevel gear tooth number is 17.

The hybrid planet row adopts a form two hybrid planet row, is a double-sun-wheel variable-speed planet row, and comprises a small sun wheel 12, a planet carrier 14 with four left planet wheels 23 and four right planet wheels 24, and a large sun wheel 13. The small sun wheel 12 is meshed with the left planet wheel 23, the right planet wheel 24 is meshed with the large sun wheel 13, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. Actually taking: the number of teeth of the small sun gear is 20, the number of teeth of the right planet gear is 18, the number of teeth of the large sun gear is 24, the number of teeth of the left planet gear is 30, and the characteristic parameter a of the planet row is 2.0. The small sun gear 12 and the planet carrier 14 are respectively connected with a sleeve shaft outer shaft and a sleeve shaft inner shaft which rotate together, and the large sun gear 13 is connected with an output shaft 15.

The steering mount includes a fixed shaft member 16, a bracket 18, a moving shaft bearing 19 and an output bearing 20. The fixed shaft member is a fixed shaft member in the form of a bearing, the fixed shaft member 16 is a fixed shaft member 17 as a shaft held on the axis of the reverse sleeve shaft, and the fixed shaft member is a bearing provided outside the fixed shaft. A moving shaft bearing 19 is provided outside the co-rotating sleeve shaft to support the co-rotating sleeve shaft 11, and an output bearing 20 is provided outside the output shaft to support the output shaft 15. The entire steering mount is rotatable about the reverse quill axis by directly connecting the fixed shaft member 16, the moving shaft bearing 19 and the output bearing 20 by the bracket 18. The steering support and the control device form indirect connection through a worm gear and a worm, and are driven by the control device to revolve. The worm wheel 21 is provided on the fixed shaft member, and the worm wheel 21 and the fixed shaft member 16 are synchronized with each other, and the number of teeth of the worm wheel is 30. The worm 22 connected with the control device is arranged, the number of the heads of the worms is 2, and the supports of the worms are fixed. The worm wheel 21 meshes with the worm 22. The control device adopts an electric mechanism.

The output shaft 15 is connected with a ship propeller to output power.

In the embodiment, the reverse sleeve shaft is arranged in the vertical direction of the ship, the control device drives the steering support to rotate around the axis of the reverse sleeve shaft through the worm gear, the output shaft revolves and rotates, the propeller revolves and rotates, and the ship realizes circumferential transmission propulsion. When the control device is not driven, the output shaft does not revolve. The control torque required by the forward rotation and the reverse rotation is the same during revolution rotation, the control torque is very small, the control device is very small, and the rotation and the revolution of the output shaft are not interfered with each other.

Example 3: the utility model discloses embodiment 3 of two books circumference transmission ware for the transmission of helicopter tail rotor is folded to the ware, is thoughtlessly moved the planet row, is turned to support and output shaft 15 and constitutes by input shaft 1, one way commutator, double-circuit. See fig. 3.

The input shaft 1 is connected with the power device for inputting power.

The one-way commutator adopts a form of three one-way commutators, and comprises a front gear 2, an inner paraxial gear 25, an outer paraxial front gear 3, an outer paraxial rear gear 4, a rear gear 5 and a reverse sleeve shaft 6. An input shaft bearing is fixed, and a front gear 2 is arranged on an input shaft 1; an inner paraxial shaft and an outer paraxial shaft are arranged, the axes of the inner paraxial shaft and the outer paraxial shaft are respectively parallel to the axis of the same directional shaft, and bearings of the inner paraxial shaft and the outer paraxial shaft are fixed, an inner paraxial gear 25 is arranged on the inner paraxial shaft, and an outer paraxial front gear 3 and an outer paraxial rear gear 4 are sequentially arranged on the outer paraxial shaft; a rear gear 5 is provided outside the reverse sleeve shaft. The front gear 2 is meshed with the outer side shaft front gear 3, the outer side shaft rear gear 4 is meshed with the inner side shaft gear 25, and the inner side shaft gear 25 is meshed with the rear gear 5. The reverse sleeve shaft 6 and the input shaft 1 are arranged on the same axis, a bearing of the reverse sleeve shaft is fixed, and the input shaft 1 and the inner shaft of the reverse sleeve shaft are directly connected. The front gear 2 and the rear gear 5 form indirect connection through an outer side shaft front gear 3, an outer side shaft rear gear 4 and an inner side shaft gear 25. Making the transmission ratio of this indirect connection equal to-1.0, the following is taken: the outer and rear paraxial gear teeth count is 18 for the inner and rear paraxial gear teeth count and 36 for the outer and front paraxial gear teeth count. The two components, the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft, have the same rotating speed and opposite rotating directions.

The hybrid planet row adopts a form of three hybrid planet rows, is a double-inner-gear-ring variable linear speed planet row, and comprises a large inner gear ring 12, a planet carrier 14 with four left planet wheels 23 and four right planet wheels 24, and a small inner gear ring 13. The large inner gear ring 12 is meshed with the left planet wheel 23, the right planet wheel 24 is meshed with the small inner gear ring 13, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. Actually taking: the number of teeth of the big inner ring gear is 60, the number of teeth of the left planet gear is 20, the number of teeth of the right planet gear is 16, the number of teeth of the small inner ring gear is 96, and the characteristic parameter a of the planet row is 2.0. The large inner gear ring 12 and the planet carrier 14 are respectively connected with a sleeve shaft outer shaft and a sleeve shaft inner shaft which rotate together, and the small inner gear ring 13 is connected with an output shaft 15.

The steering mount includes a fixed shaft member 16, a bracket 18, a moving shaft bearing 19 and an output bearing 20. The fixed shaft part adopts a form of two fixed shaft parts, the fixed shaft part 16 is a shaft type fixed shaft part and is a shaft arranged on the axis of a reverse sleeve shaft, and a bearing of the shaft is a fixed bearing 17. A moving shaft bearing 19 is provided outside the co-rotating sleeve shaft to support the co-rotating sleeve shaft 11, and an output bearing 20 is provided outside the output shaft to support the output shaft 15. The entire steering mount is rotatable about the reverse quill axis by directly connecting the fixed shaft member 16, the moving shaft bearing 19 and the output bearing 20 by the bracket 18. The steering support and the control device form indirect connection through a worm gear and a worm, and are driven by the control device to revolve. The worm wheel 21 is provided on the fixed shaft member 16, and the worm wheel 21 and the fixed shaft member 16 are synchronized with each other, and the number of teeth of the worm wheel is 30. A worm 22 connected with the control device is arranged, the number of the worm heads is 2, and the worm support is fixed. The worm wheel 21 meshes with the worm 22. The control device adopts an electric mechanism.

The output shaft 15 is connected with a tail rotor of the helicopter to output power.

In the embodiment, the reversing sleeve shaft is arranged in the vertical direction of the helicopter, the control device drives the steering support to rotate around the axis of the reversing sleeve shaft through the worm gear, the output shaft revolves and rotates, the tail rotor revolves and rotates, and the tail rotor of the helicopter realizes circumferential transmission propulsion. When the control device is not driven, the output shaft does not revolve. The control torque required by the forward rotation and the reverse rotation is the same during revolution rotation, the control torque is very small, the control device is very small, and the rotation and the revolution of the output shaft are not interfered with each other.

Example 4: the utility model discloses embodiment 4 of two books circumference transmission for the transmission of boats and ships screw comprises input shaft 1, single way commutator, double-circuit book to the ware, thoughtlessly move the planet row, turn to support and output shaft 15. See fig. 4.

The input shaft 1 is connected with the power device for inputting power.

The one-way commutator adopts a four-way commutator, and comprises an inner driving bevel gear 2, an outer driving bevel gear 3, an inner driven bevel gear 4, an outer driven bevel gear 5 and a reverse sleeve shaft 6. The input shaft bearing is fixed, an inner driving bevel gear 2 and an outer driving bevel gear 3 are arranged on the input shaft 1 and symmetrically distributed on two sides of the axis of the reverse sleeve shaft respectively, the inner driving bevel gear 2 does not penetrate through the axis of the reverse sleeve shaft and is arranged, and the outer driving bevel gear 3 penetrates through the axis of the reverse sleeve shaft and is arranged. The fixed reverse sleeve shaft bearing sets up the crossing contained angle that forms of reverse sleeve shaft axis and input shaft axis, and this contained angle is exactly the transmission angle, and this embodiment transmission angle is 90 degrees. An inner driven bevel gear 4 is arranged on the inner shaft of the reverse sleeve shaft, and the inner driven bevel gear 4 is kept meshed with the inner driving bevel gear 2; an outer driven bevel gear 5 is provided on the outer shaft of the reverse sleeve shaft, keeping the outer driven bevel gear 5 in mesh with the outer driving bevel gear 3. Actually taking: the number of teeth of the inner driving bevel gear is equal to 17 that of the inner driven bevel gear, the number of teeth of the outer driving bevel gear is equal to 19 that of the outer driven bevel gear, and the transmission ratio from the input shaft 1 to the inner shaft of the reversing sleeve shaft is equal to the negative value of the transmission ratio from the input shaft 1 to the outer shaft of the reversing sleeve shaft. The two components, the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft, have the same rotating speed and opposite rotating directions.

The two-way deflector comprises a first driving bevel gear 7, a first driven bevel gear 9, a second driving bevel gear 8, a second driven bevel gear 10 and a same-rotation sleeve shaft 11. Adopt form two way deflector, set up with the sleeve axle axis of rotation and the crossing of reverse sleeve axle axis, the angle of intersection is the dog-ear angle, and this embodiment dog-ear angle is 90 degrees. A first drive bevel gear 7 is arranged on the inner shaft of the reverse sleeve shaft, a second drive bevel gear 8 is arranged on the outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft passes through the axial line of the same-rotation sleeve shaft, and the outer shaft of the reverse sleeve shaft does not pass through the axial line of the same-rotation sleeve shaft; a first driven bevel gear 9 is arranged on the outer shaft of the same-rotation sleeve shaft, and a second driven bevel gear 10 is arranged on the inner shaft of the same-rotation sleeve shaft; keeping the first drive bevel gear 7 meshed with the first driven bevel gear 9 and keeping the second drive bevel gear 8 meshed with the second driven bevel gear 10. Actually taking: the first driving bevel gear tooth number is 19, the second driving bevel gear tooth number is 17, and the transmission ratio of the first driving bevel gear 7 to the first driven bevel gear 9 is equal to the negative value of the transmission ratio of the second driving bevel gear 8 to the second driven bevel gear 10.

The mixed-motion planetary line adopts a four-mixed-motion planetary line, is a double-sun-wheel inner and outer planetary variable linear speed planetary line, and comprises a small sun wheel 12, a planetary carrier 14 with four inner planetary wheels 25, four left planetary wheels 23 and four right planetary wheels 24, and a large sun wheel 13. The small sun wheel 12 is meshed with the inner planet wheel 25, the inner planet wheel 25 is meshed with the left planet wheel 23, the right planet wheel 24 is meshed with the large sun wheel 13, and the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed. Actually taking: when the number of teeth of the small sun gear is equal to that of the inner-layer planet gear, the number of teeth of the left planet gear is equal to 18, and the number of teeth of the large sun gear is equal to that of the right planet gear, the number of teeth of the large sun gear is equal to 22, and a characteristic parameter a of the planet row is equal to 1.0. The small sun gear 12 and the large sun gear 13 are connected to the sleeve shaft rotating shaft outer shaft and the sleeve shaft rotating shaft inner shaft, respectively, and the planet carrier 14 is connected to the output shaft 15.

The steering mount includes a fixed shaft member 16, a bracket 18, a moving shaft bearing 19 and an output bearing 20. The fixed shaft part is a fixed shaft part in a form, the fixed shaft part 16 is a bearing type fixed shaft part, the shaft which is kept on the axis of the reversing sleeve shaft is the reversing sleeve shaft, the bearing of the shaft is a fixed bearing 17, and the fixed shaft part 16 is a bearing which is arranged outside the reversing sleeve shaft on the right side in the drawing and can rotate. A moving shaft bearing 19 is provided outside the co-rotating sleeve shaft to support the co-rotating sleeve shaft 11, and an output bearing 20 is provided outside the output shaft to support the output shaft 15. The entire steering mount is rotatable about the reverse quill axis by directly connecting the fixed shaft member 16, the moving shaft bearing 19 and the output bearing 20 by the bracket 18. The steering support and the control device form indirect connection through a worm gear and a worm, and are driven by the control device to revolve. The worm wheel 21 is provided on the fixed shaft member, and the worm wheel 21 and the fixed shaft member 16 are synchronized with each other, and the number of teeth of the worm wheel is 30. The worm 22 connected with the control device is arranged, the number of the heads of the worms is 2, and the supports of the worms are fixed. The worm wheel 21 meshes with the worm 22. The control device adopts an electric mechanism.

The output shaft 15 is connected with a ship propeller to output power.

Example 5: the utility model discloses embodiment 5 of two books circumference transmission for the transmission of boats and ships double screw is folded to the ware, is mixed to move the planet row, is turned to support and output shaft 15 and constitutes by input shaft 1, one way commutator, double-circuit. In contrast to embodiment 1, one input shaft is shared; sharing a single commutator; the two pairs of double-path folding devices share a first driving bevel gear and a second driving bevel gear; the mixed-action planet row and the output shaft are respectively provided with two pairs; the two sub-steering brackets share a fixed shaft member and the two brackets are connected so as to be incorporated as a single body. See fig. 5.

The input shaft 1 is connected with the power device for inputting power.

The one-way commutator is in a form of one-way commutator and comprises a front bevel gear 2, two reversing bevel gears 3, two reversing bevel gear supports 4, a rear bevel gear 5 and a reverse sleeve shaft 6. Two reversing bevel gears and two reversing bevel gear supports are adopted to strengthen the rated torque of the one-way reverser. An input shaft bearing is fixed, and a front bevel gear 2 is arranged on an input shaft 1; two reversing bevel gears 3 are meshed with the front bevel gear 2, the axes of the reversing bevel gears are perpendicular to the axis of the input shaft, and two reversing bevel gear supports 4 are fixed. The reverse sleeve shaft 6 and the input shaft 1 are arranged on the same axis, a bearing of the reverse sleeve shaft is fixed, and the rear bevel gear 5 is arranged on the outer shaft of the reverse sleeve shaft and meshed with the two reversing bevel gears 3. Directly connecting the input shaft 1 with the inner shaft of the reversing quill. The front bevel gear 2 and the rear bevel gear 5 form an indirect connection through two reversing bevel gears 3. Actually taking: the tooth number of the front bevel gear is equal to that of the reversing bevel gear and is equal to that of the rear bevel gear, which is equal to 17, and the indirectly connected transmission ratio is equal to-1.0. The two components, the inner shaft of the reverse sleeve shaft and the outer shaft of the reverse sleeve shaft, have the same rotating speed and opposite rotating directions.

The two pairs of two-way direction deflectors comprise a first driving bevel gear 7, a first driven bevel gear 9, two second driving bevel gears 8, two second driven bevel gears 10 and two sleeve shafts 11 rotating in the same direction. The double-circuit book turns to the ware all adopts form double-circuit book to the ware, sets up and intersects with reverse sleeve axle axis with the sleeve axle axis that changes, and the angle of intersection is the angle of turning over promptly, and two are respectively symmetric distribution in the both sides of reverse sleeve axle axis with the sleeve axle that changes, and this embodiment angle of turning over is 90 degrees. A first drive bevel gear 7 is arranged on the inner shaft of the reverse sleeve shaft, a second drive bevel gear 8 is arranged on the outer shaft of the reverse sleeve shaft after the inner shaft of the reverse sleeve shaft passes through the axial line of the same-rotation sleeve shaft, and the outer shaft of the reverse sleeve shaft does not pass through the axial line of the same-rotation sleeve shaft; a first driven bevel gear 9 is respectively arranged on the inner shafts of the two same-rotation sleeve shafts, and a second driven bevel gear 10 is respectively arranged on the outer shafts of the two same-rotation sleeve shafts; and keeping the first driving bevel gear meshed with the two first driven bevel gears respectively, and keeping the second driving bevel gear meshed with the two second driven bevel gears respectively. Through setting up first initiative bevel gear number of teeth, second initiative bevel gear number of teeth, first passive bevel gear number of teeth and the passive bevel gear number of teeth of second, make the first transmission ratio of initiative bevel gear to first passive bevel gear equal the negative value of the transmission ratio of second initiative bevel gear to second passive bevel gear. Actually taking: the first driving bevel gear tooth number is 17, the first driven bevel gear tooth number is 19, and the second driving bevel gear tooth number is 19.

The two pairs of mixed-motion planetary rows adopt five mixed-motion planetary rows which are common double-layer planetary rows, and each mixed-motion planetary row comprises a sun gear 12, a planetary carrier 14 with four inner planetary gears 21 and four outer planetary gears 22, and an inner gear ring 13. The sun gear 12 is meshed with the inner planet gears 21, the inner planet gears 21 are meshed with the outer planet gears 22, and the outer planet gears 22 are meshed with the inner gear ring 13. Actually taking: the number of teeth of the ring gear is 68 and the number of teeth of the sun gear is 34. The sun gear 12 and the carrier 14 are connected to a sleeve shaft inner shaft and a sleeve shaft outer shaft, respectively, and the carrier 14 is connected to two output shafts 15, respectively.

The steering mounts each include a fixed shaft member 16, a bracket 18, a moving shaft bearing 19 and an output bearing 20. The two pairs of steering supports share one fixed shaft component, the steering supports adopt two fixed shaft components, the fixed shaft component 16 is a shaft type fixed shaft component, and is a shaft arranged on the axis of a reverse sleeve shaft, and a bearing of the shaft is a fixed bearing 17. A moving shaft bearing 19 and an output bearing 20 are respectively arranged outside the two co-rotating sleeve shafts and respectively support the co-rotating sleeve shaft 11 and the output shaft 15. The fixed shaft part 16, the two movable shaft bearings 19 and the two output bearings 20 are directly connected by a bracket 18, and the two steering supports are combined into a whole and can rotate around the axis of the reverse sleeve shaft. The fixed shaft member 16 is directly connected to the control device and revolves under the drive of the control device. The control device adopts an electric mechanism.

The two output shafts 15 are respectively connected with double propellers of the ship to output power. The two propellers rotate in opposite directions.

The two-way reversing transmission device is essentially two double-folded circumferential transmission devices, an input shaft, a one-way reversing device, a first driving bevel gear, a second driving bevel gear and a fixed shaft component are shared, and two supports are connected into a whole; the steering support and the two output shafts are driven by the same control device to rotate around the axis of the reverse sleeve shaft. A reverse sleeve shaft is arranged in the vertical direction of the ship, the control device drives the steering support to rotate around the axis of the reverse sleeve shaft, the output shaft revolves to rotate, the double propellers revolve to rotate, and the ship realizes circumferential transmission propulsion. When the control device is not driven, the output shaft does not revolve. The control torque required by the forward rotation and the reverse rotation is the same during revolution rotation, the control torque is very small, the control device is very small, and the rotation and the revolution of the output shaft are not interfered with each other.

The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It should be understood by those skilled in the art that the present invention is not limited by the foregoing embodiments, and can be modified without departing from the spirit and scope of the present invention, which falls into the scope of the present invention. The scope of the invention is defined by the appended claims and equivalents.

Claims

1. The double-folding circumferential transmission device consists of an input shaft, a single-way reverser, a double-way deflector, a steering support and an output shaft, and is characterized in that:

the input shaft inputs power from the power device;

the one-way commutator adopts a form of one-way commutator, and comprises a front bevel gear, a reversing bevel gear support, a rear bevel gear and a reversing sleeve shaft, wherein an input shaft bearing is fixed, the input shaft is provided with the front bevel gear, the reversing bevel gear is meshed with the front bevel gear, the axis of the reversing bevel gear is vertical to the axis of the input shaft, the support of the reversing bevel gear is fixed, the reversing sleeve shaft and the input shaft are positioned on the same axis, a bearing of the reversing sleeve shaft is fixed, the rear bevel gear is meshed with the reversing bevel gear and is arranged on the outer shaft of the reversing sleeve shaft, the input shaft is directly connected with the inner shaft of the reversing sleeve shaft, the front bevel gear and the rear bevel gear form indirect connection through the reversing bevel gear, the transmission ratio of the indirect connection is equal to-1.0 by setting the number of front bevel gear teeth equal to the number of rear bevel gear teeth, and the rotating speeds of the two parts of, The rotating directions are opposite;

the double-path deflector comprises a first driving bevel gear, a first driven bevel gear, a second driving bevel gear, a second driven bevel gear and a co-rotating sleeve shaft, the double-path deflector is in a form of a double-path deflector, the first driving bevel gear is arranged in the inner shaft of the counter-rotating sleeve shaft, the second driving bevel gear is arranged on the outer shaft of the counter-rotating sleeve shaft after the inner shaft of the counter-rotating sleeve shaft passes through the axis of the co-rotating sleeve shaft, the outer shaft of the counter-rotating sleeve shaft does not pass through the axis of the co-rotating sleeve shaft, the first driven bevel gear is arranged in the inner shaft of the co-rotating sleeve shaft, the second driven bevel gear is arranged in the outer shaft of the co-rotating sleeve shaft, the first driving bevel gear is meshed with the first driven bevel gear, the second driving bevel gear is meshed with the second driven bevel gear, and the number of teeth of the first driving bevel gear, the second driving bevel gear, the number of, the transmission ratio from the first driving bevel gear to the first driven bevel gear is equal to the negative value of the transmission ratio from the second driving bevel gear to the second driven bevel gear;

the mixed-motion planetary row adopts a first mixed-motion planetary row, and is a bevel gear planetary row, the bevel gear planetary row comprises a left bevel gear, a planet carrier with bevel gear planet wheels and a right bevel gear, the left bevel gear is meshed with the bevel gear planet wheels, the bevel gear planet carriers are meshed with the right bevel gear, when the number of teeth of the left bevel gear is equal to the number of teeth of the right bevel gear, the mixed-motion planetary row is used as a mixed-motion planetary row, the right bevel gear and the left bevel gear are respectively connected with an inner shaft of a co-rotating sleeve shaft and an outer shaft of the co-rotating sleeve shaft;

the steering support comprises a fixed shaft part, a support, a movable shaft bearing and an output bearing, wherein the fixed shaft part is a machine rotating around the axis of the reverse sleeve shaft, the fixed shaft part adopts a form fixed shaft part, the form fixed shaft part is a bearing type fixed shaft part, one shaft kept at the axis of the reverse sleeve shaft is selected, a bearing is arranged at the periphery of the shaft to support the shaft, the bearing is used as the fixed shaft part, the movable shaft bearing is arranged outside the same-rotation sleeve shaft to support the same-rotation sleeve shaft, the output bearing is arranged outside the output shaft to support the output shaft, the support is directly connected with the fixed shaft part, the movable shaft bearing and the output bearing, the whole steering support can rotate around the axis of the reverse sleeve shaft in a revolving way, the connection of the steering support and the control device is one of direct connection and indirect connection, and the steering support is driven;

the output shaft is connected with power utilization equipment such as a propeller and the like to output power;

the control device drives the steering support to rotate around the axis of the reverse sleeve shaft, the output shaft revolves and rotates, when the control device is not driven, the output shaft does not revolve and rotate, the control torque required by forward rotation and reverse rotation is the same during revolution and rotation, the control torque is small, the control device is small, and the rotation and revolution of the output shaft do not interfere with each other.

2. The bi-fold circumferential driver of claim 1, further characterized in that the one-way commutator is replaced with a two-way commutator, comprising an inner driving bevel gear, an outer driving bevel gear, an inner driven bevel gear, an outer driven bevel gear, and a reverse sleeve shaft, a fixed input shaft bearing, the inner driving bevel gear and the outer driving bevel gear provided on the input shaft are respectively provided on both sides of the axis of the reverse sleeve shaft, the inner driving bevel gear is provided after passing through the axis of the reverse sleeve shaft, the outer driving bevel gear is provided without passing through the axis of the reverse sleeve shaft, the fixed reverse sleeve shaft bearing is provided with an angle formed by intersecting the axis of the reverse sleeve shaft and the axis of the same shaft, the angle is a driving angle, the inner driven bevel gear provided on the inner shaft of the reverse sleeve shaft is engaged with the inner driving bevel gear, the outer driven bevel gear provided on the outer shaft of the reverse sleeve shaft, the outer driven bevel gear is engaged with the outer driving bevel gear, through setting up interior initiative bevel gear number of teeth, outer initiative bevel gear number of teeth, interior passive bevel gear number of teeth and outer passive bevel gear number of teeth, make the transmission ratio of input shaft to the internal shaft of reverse sleeve axle equal the negative value of the transmission ratio of input shaft to the external shaft of reverse sleeve axle, the rotational speed of the internal shaft of reverse sleeve axle in the two way commutators of form, these two parts of reverse sleeve axle external shaft equals, the rotation direction is opposite.

3. The double-folding peripheral driver of claim 1, wherein the one-way commutator is replaced with a three-way commutator of a type including a front gear, an inner bypass gear, an outer bypass front gear, an outer bypass rear gear, a rear gear and a reverse sleeve, a bearing of the input shaft is fixed, the front gear is provided on the input shaft, the inner bypass and the outer bypass are provided with bearings which are parallel to the axis of the same shaft, respectively, the inner bypass gear is provided on the inner bypass, the outer bypass front gear and the outer bypass rear gear are provided in order on the outer bypass, the rear gear is provided on the outer shaft of the reverse sleeve, the front gear is engaged with the outer bypass front gear, the outer bypass rear gear is engaged with the inner bypass gear, the inner bypass gear is engaged with the rear gear, the reverse sleeve and the input shaft are provided on the same axis, the bearing of the reverse sleeve is fixed, the input shaft and the reverse sleeve are directly connected, the front gear and the rear gear are indirectly connected through an outer paraxial front gear, an outer paraxial rear gear and an inner paraxial gear, and the transmission ratio of the indirect connection is equal to-1.0 by setting the gear number of the inner paraxial front gear, the gear number of the outer paraxial rear gear, the gear number of the front gear and the gear number of the rear gear, and the rotating speeds of the two parts, namely an inner shaft of a reversing sleeve shaft and an outer shaft of the reversing sleeve shaft, in the three-way commutator are equal and the rotating directions are opposite.

4. The bi-fold circumferential driver of claim 1, further characterized in that the one-way commutator is replaced with a four-way commutator comprising an inner driving bevel gear, an outer driving bevel gear, an inner driven bevel gear, an outer driven bevel gear and a reverse sleeve shaft, a fixed input shaft bearing is provided on the input shaft, the inner driving bevel gear and the outer driving bevel gear are respectively provided on both sides of the axis of the reverse sleeve shaft, the inner driving bevel gear is provided without passing through the axis of the reverse sleeve shaft, the outer driving bevel gear is provided after passing through the axis of the reverse sleeve shaft, a fixed reverse sleeve shaft bearing is provided on the reverse sleeve shaft with the axis of the reverse sleeve shaft intersecting the axis of the input shaft to form an included angle which is a driving angle, the inner driven bevel gear is provided on the inner shaft of the reverse sleeve shaft to keep the inner driven bevel gear engaged with the inner driving bevel gear, the outer driven bevel gear is provided on the outer shaft of the reverse sleeve shaft to keep the outer driven bevel gear engaged with the outer driving bevel gear, through setting up interior initiative bevel gear number of teeth, outer initiative bevel gear number of teeth, interior passive bevel gear number of teeth and outer passive bevel gear number of teeth, make the transmission ratio of input shaft to the internal shaft of reverse sleeve axle equal the negative value of the transmission ratio of input shaft to the external shaft of reverse sleeve axle, the rotational speed of the internal shaft of reverse sleeve axle in the four single-way commutators of form, the external shaft of reverse sleeve axle these two parts equals, the rotation direction is opposite.

5. The bi-folded circumferential driver of claim 1, further characterized by: wherein the two-way direction-folding device is used in a form of a two-way direction-folding device, a first drive bevel gear is arranged in the inner shaft of the reversing sleeve shaft, the first drive bevel gear is arranged after the inner shaft of the reversing sleeve shaft passes through the axis of the same-rotation sleeve shaft, a second driving bevel gear is arranged on the outer shaft of the reverse sleeve shaft, the outer shaft of the reverse sleeve shaft does not penetrate through the axial line of the sleeve shaft rotating together, a first driven bevel gear is arranged on the outer shaft of the same-rotation sleeve shaft, a second driven bevel gear is arranged on the inner shaft of the same-rotation sleeve shaft, the first driving bevel gear is kept meshed with the first driven bevel gear, the second driving bevel gear is kept meshed with the second driven bevel gear, through setting up first initiative bevel gear number of teeth, second initiative bevel gear number of teeth, first passive bevel gear number of teeth and the passive bevel gear number of teeth of second, make the first transmission ratio of initiative bevel gear to first passive bevel gear equal the negative value of the transmission ratio of second initiative bevel gear to second passive bevel gear.

6. The double-folding circumferential driver according to claim 1, wherein the double-mixing planetary row is a double-sun-wheel variable-speed planetary row, and comprises a small sun wheel, a planet carrier with a left planet wheel and a right planet wheel, and a large sun wheel, wherein the small sun wheel is meshed with the left planet wheel, the right planet wheel is meshed with the large sun wheel, the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed, and when the characteristic parameter a of the planetary row is 2.0 by setting the number of the small sun wheel teeth, the number of the large sun wheel teeth, the number of the left planet wheel teeth and the number of the right planet wheel teeth, the small sun wheel and the planet carrier are respectively connected with an outer shaft of a rotating sleeve shaft and an inner shaft of the rotating sleeve shaft, and the large sun wheel is connected with an output shaft.

7. The double-folding circumferential driver according to claim 1, wherein the hybrid planetary gear is a three-hybrid planetary gear in a form of a double-inner-ring gear variable linear speed planetary gear, which comprises a large inner ring gear, a planet carrier with left and right planet gears and a small inner ring gear, the large inner ring gear is meshed with the left planet gears, the right planet gears are meshed with the small inner ring gear, the left planet gears and the corresponding right planet gears are coaxial and rotate at the same speed, and when the characteristic parameter a of the planetary gear is 2.0, the large inner ring gear and the planet carrier are respectively connected with an outer shaft of a same-rotation sleeve shaft, an inner shaft of the same-rotation sleeve shaft, and the small inner ring gear is connected with an output shaft.

8. The double-folding circumferential driver of claim 1, wherein the hybrid planetary gear is a four-hybrid planetary gear in a form of a double-sun-wheel inner-outer-planet variable linear speed planetary gear, and comprises a small sun wheel, a planet carrier with an inner-layer planet wheel, a left planet wheel and a right planet wheel, and a large sun wheel, wherein the small sun wheel is meshed with the inner-layer planet wheel, the inner-layer planet wheel is meshed with the left planet wheel, the right planet wheel is meshed with the large sun wheel, the left planet wheel and the corresponding right planet wheel are coaxial and rotate at the same speed, and when the characteristic parameter a of the planetary gear is 1.0 by setting the number of the small sun wheel, the number of the large sun wheel, the number of the left planet wheel, the number of the right planet wheel, and the number of the inner-layer planet wheel, the small sun wheel and the large sun wheel are respectively connected with an outer shaft of a same rotating sleeve and an inner shaft of a same rotating sleeve, and.

9. The double-folding circumferential driver of claim 1, wherein the hybrid planetary row is a five-hybrid planetary row, which is a common double-layer planetary row, comprising a sun gear, a planetary carrier with inner planet gears and outer planet gears, and an inner gear ring, wherein the sun gear is engaged with the inner planet gears, the inner planet gears are engaged with the outer planet gears, the outer planet gears are engaged with the inner gear ring, and when the number of teeth of the inner gear ring is 2, the sun gear and the planetary carrier are respectively connected with an inner shaft of a co-rotating sleeve shaft and an outer shaft of the co-rotating sleeve shaft, and the inner gear ring is connected with an output shaft.

10. The bi-folding peripheral driver of claim 1 further characterized in that the fixed shaft member in the steering mount is replaced with a form two fixed shaft member, the form two fixed shaft member is a shaft type fixed shaft member, the shaft is a shaft disposed on the axis of the reverse sleeve shaft, the bearing is a fixed bearing, the shaft is a fixed shaft member, a moving shaft bearing is disposed outside the rotating sleeve shaft to support the same sleeve shaft, an output bearing is disposed outside the output shaft to support the output shaft, the fixed shaft member, the moving shaft bearing and the output bearing are directly connected by a bracket, the entire steering mount is capable of revolving around the axis of the reverse sleeve shaft, the connection between the steering mount and the control device is one of a direct connection and an indirect connection, and the steering mount is capable of revolving by the control device.