WO2019085880A1 - Transmission de freinage à rangées multiples et à montage en étoile - Google Patents

Transmission de freinage à rangées multiples et à montage en étoile Download PDF

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Publication number
WO2019085880A1
WO2019085880A1 PCT/CN2018/112601 CN2018112601W WO2019085880A1 WO 2019085880 A1 WO2019085880 A1 WO 2019085880A1 CN 2018112601 W CN2018112601 W CN 2018112601W WO 2019085880 A1 WO2019085880 A1 WO 2019085880A1
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WIPO (PCT)
Prior art keywords
planetary
connection
row
gear
star
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PCT/CN2018/112601
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English (en)
Chinese (zh)
Inventor
罗灿
Original Assignee
罗灿
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Publication date
Application filed by 罗灿 filed Critical 罗灿
Priority to CN201880003527.6A priority Critical patent/CN109874317B/zh
Publication of WO2019085880A1 publication Critical patent/WO2019085880A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms

Definitions

  • the invention relates to a planetary gear transmission, in particular to a transmission of a star-connected planetary row structure of a plurality of rows of planetary rows that controls a gear by controlling a brake.
  • Planetary platoons consist of three components: the sun gear, the inner ring gear and the planet carrier with planet gears.
  • the meshing arrangement of the three components determines the type of planetary row.
  • the existing planetary rows can be divided into single-layer star planetary rows, double-layer planetary planetary rows, and three-layer planetary planetary rows according to the single and double planetary wave level series on the planet carrier.
  • Zt be the number of teeth of the sun
  • Zq is the number of teeth of the inner ring gear
  • Nt is the speed of the sun gear
  • Nq is the speed of the inner ring gear
  • Nj is the speed of the carrier.
  • the single-layer planetary gears of the single-layer planetary planets are Zxd
  • the outer planetary gears of the double-layer planetary planetarys are Zxw
  • the inner planetary gears of the double-layer planetary planetarys are Zxn
  • the three-layer planetary planetarys The number of teeth of the layer planetary gear is Zxy
  • the number of teeth of the two-layer planetary gear of the three-layer planetary planetary row is Zxe
  • the number of teeth of the three-layer planetary gear of the three-layer planetary planetary row is Zxs.
  • the planetary row characteristic parameter a Zq/Zt.
  • the planetary row characteristic parameter a Zq/Zt, double-layer star planetary row
  • the planetary row characteristic parameter a Zq/Zt.
  • the planetary row characteristic parameters are the existing knowledge in the industry, and all the parameters of the Taixing and the circle are an extension of the existing knowledge, and are new knowledge that must be mastered in the industry.
  • the three planetary row motion characteristic equations are the existing knowledge in the industry.
  • the six Taixing equations and the six circle star equations are extensions of existing knowledge and are new knowledge that must be mastered in the industry.
  • the new knowledge is an essential tool for studying the structure of the star-connected planetary platoon.
  • the planetary equations of motion that include the equations of motion, the equations of the stars, and the equations of the circle are the complete mathematical language representations of the laws governing the motion of the planets.
  • the size of the planetary row is enlarged and reduced, and its various characteristic parameters are unchanged, and its motion equations are unchanged.
  • a plurality of planetary rows are connected to each other to form a planetary row structure.
  • Several components in the planetary row structure are connected and have the same determined rotational speed to form a rotating member, each rotating member having a rotational speed.
  • the two-way parallel connection or the star-connected planetary row structure between adjacent planetary rows is the planetary row structure of the two-degree-of-freedom determining system.
  • the two-degree-of-freedom determining system has a plurality of rotating members, wherein after the rotational speeds of the two rotating members are determined, the rotational speeds of all the rotating members are determined.
  • the star connection is in the connection between the planetary rows, so that the number of planetary wheels of each planetary row is the same, and the size of each planetary row is adjusted, and some ratios are Zoom in, and scale down until the distance between one of the planets in one of the planetary rows is equal to the axis of the planet's axis; one planet of a row of planets and one of the adjacent planets The axles are aligned and connected.
  • Such a connection necessarily causes the same number of planet wheels to participate in the connection to have the same speed, and each planet carrier participating in the connection has another identical speed.
  • Such a planetary row connection we call the planetary connection of the planetary row, a planetary row structure composed of a plurality of planetary rows connected by a star connection method is called a star-connected planetary row structure.
  • the description of the structure of the planetary slewing gears includes textual language expressions, as well as mathematical or linguistic expressions of numbers or algebraic expressions.
  • the structure of the planetary transmission includes a planetary row structure and an input/output lock connection.
  • the planetary row structure includes the order of the planetary row types, the order of the planetary wheel types, the various characteristic parameters of each planetary row, and the connection between the planetary rows.
  • the order of the planetary row types is an arrangement of different types of planetary rows, which are generally expressed in written language.
  • the characteristic parameters of each planetary row are generally expressed in mathematical language. Each characteristic parameter is a structure of each planetary row expressed in a mathematical language.
  • Planetary inter-row connections include series connections, parallel connections, star connections, etc., including textual expressions as well as mathematical language representations.
  • the word language means "the connection is to make the connection object's rotation speed equal”
  • the input-output lock connection is an important structure of the planetary transmission, and its external relationship includes input, output and lock, and its connection form includes constant connection and variable connection.
  • the gear ratio includes the gear ratio digital value and the gear ratio formula.
  • the transmission ratio equation is an algebraic equation, which is a mathematical language to represent the transmission process and action mechanism from input to output.
  • the present invention proposes a transmission of a multi-row planetary row star-connected planetary row structure that controls a gear by controlling a brake, which is called a star-connected multi-row brake transmission.
  • the star-connected multi-row brake transmission of the present invention is connected with an input end and an output end, and includes a planetary row structure, an input/output lock connection and a brake.
  • the present invention has the characteristics of a planetary row structure and an input/output lock connection feature. . among them:
  • the feature of the planetary row structure is that the planetary row structure of the present invention is a star-connected planetary row structure, and is a two-degree-of-freedom determining system planetary row structure.
  • the planetary row structure includes at least two planetary rows, each of which has the same number of planetary gear sets (the number of planetary gear sets is generally 2, 3, 4 or 5), adjusting the size of each planetary row, and some equal magnification Some ratios are reduced until the distance between the axis of one of the planets in the planetary rows is equal to the axis of the planetary row; a certain planetary gear of a row of planetary rows and a certain planetary axle of an adjacent planetary row
  • the heart is aligned, such a connection must have the same speed of the planets participating in the connection, and each planet carrier participating in the connection has another identical speed; such a planetary row connection, we call the planetary row
  • a planetary connection structure in which a plurality of planetary rows are connected by a star connection method is called
  • the star-connected multi-row brake transmission of the present invention is connected with a power source and a power-using device, and includes a star-connected planetary row structure and an input-output lock connection, wherein:
  • the star-connected planetary row structure includes at least two planet wheels, each of which includes a center wheel and a planet carrier equipped with planet wheels, wherein the center wheel includes an internal ring gear or a sun gear, and adjacent planet rows have the same planet gear
  • the number of layers is at least two layers, and the relationship between the two planetary rows is proportionally enlarged or reduced.
  • the planetary wheels of one of the two planetary rows correspond one-to-one, and are coaxially connected by the planet carrier to form a planetary row.
  • the star connection structure; the center wheel of each planetary row is a rotating member, the planetary wheels connected to each other between the two planetary rows are one rotating member, and the other planetary gears are respectively a rotating member;
  • the input/output lock connection is connected to the power source by one of the rotating members as the constant input connection end, and the power supply device is connected with the other rotating member as the constant output connection end, and the remaining rotating members serve as the variable lock connection ends. Connect to the brake.
  • each planetary row includes a sun gear, an inner ring gear and a planet carrier equipped with planet wheels, and the planetary row types include a single-layer star planetary row, a double-layer star planetary row, and a three-layer star planetary.
  • the planetary row structure consisting of four rows of planetary rows has eighty-one array combinations; in the star-connected planetary row structure of the present invention, the planetary row connections are all star connections, and the planetary wheel types participating in the star connection in each planetary row
  • a single-layer planetary gear consisting of a single-layered planetary planet, an outer planetary gear of a double-layered planetary row, an inner planetary gear of a double-layered planetary row, a planetary gear of a three-layered planetary row, and a three-layer planetary planetary row.
  • the two-layer planetary wheel, the three-layer planetary wheel of the three-layered planetary row, and the planetary wheels that participate in the star connection form a planetary wheel type sequence.
  • each characteristic parameter of each planetary row is combined with each other and determined according to actual needs.
  • the input/output lock connection is characterized in that: in the planetary row structure, one of the rotating members is used as a constant input connection end, and one input end is connected; a rotating member is used as a constant output connection end, and one output end is connected; The rotating members each serve as a variable lock connection end, each of which is connected to a brake.
  • the plurality of rotating members of the planetary row structure of the present invention are arranged as the constant input connection end, the constant output connection end, and the variable lock connection ends according to the above-mentioned input and output lock connection features, and are arranged to form an input/output lock connection arrangement. combination.
  • Each of the variable lock connection ends is connected to the brake, and the brake brake locks the variable lock connection end, and the variable lock connection end is not locked without braking.
  • the present invention controls the transmission gear position by controlling the brakes, one for each gear.
  • the input end is a power source, an engine or a transmission shaft, a transmission gear, a clutch, etc. located behind the engine, and the connection of the constant input connection end and the input end is directly connected coaxially or indirectly through a side shaft mechanical connection.
  • the output end is a power-using device, a wheel, a propeller or a transmission shaft, a transmission gear, a differential, etc. before the power-using device, and the connection of the constant-output connection end and the output end is directly connected coaxially or indirectly through the bypass shaft. connection.
  • the brake includes a brake clutch, a boost brake, and the like.
  • the present invention is characterized by the above-described planetary row structure feature and input/output lock connection feature.
  • the arrangement of the planetary row types, the arrangement of the planetary wheel types, and the combination of the various characteristic parameters of each planetary row change the application properties of the present invention, but do not change the features of the present invention.
  • Prior to the present invention there was no planetary transmission in the transmission industry that had the same features.
  • determining the rotational speed of any two rotating members determines the rotational speed of all rotating members.
  • the constant input connection speed is determined, a variable lock connection brake speed is determined to be zero, all rotating member speed is determined as a set of speed, the constant output connection has a speed, and the transmission is a gear.
  • the constant input connection speed is determined, the other variable lock connection brake speed is determined to be zero, all component speeds are determined to be another set of speeds, the constant output connection has another speed, the transmission is another Gear position.
  • the invention locks different variable locking connection ends by braking, and the rotation speed thereof is zero, the rotation speed of the constant output connection end is different, and the transmission ratio of the constant input connection end to the constant output connection end is different.
  • the process of replacing the brake locks with different variable lock connections is the process of shifting.
  • the transmission of the present invention is half-linked in this gear position.
  • the transmission of the present invention does not transmit power between the constant input connection end and the constant output connection end, and is in neutral.
  • the two-row star-connected planetary row structure of the present invention has five rotating members, namely, a first planetary sun gear, a first planetary inner ring gear, a second planetary sun gear, a second planetary inner ring gear and a planet.
  • the carrier, the planet carrier is a common planet carrier of each planetary row, and has left and right ends for external connection.
  • Two of the rotating members serve as constant input terminals and constant output terminals, and the remaining three rotating members serve as variable lock connections.
  • There are 20 combinations of input and output lock connections and 20 arrangement combinations are in accordance with the input/output lock connection feature of the present invention.
  • Figure 1 shows the outer-plane planetary gear of the No.
  • the planet carrier is a constant input connection end, connected to the input end; the first planetary gear inner ring gear q1 is a constant output connection end, connected to the output end; the first planetary row sun gear t1, the second planet row sun gear t2 and the second
  • the inner ring gear ring q2 of the planetary row is a variable locking connection end, and each is connected to a brake.
  • Part of the connection in Figure 1 is in the form of a sleeve shaft, which is a common practice in the transmission industry to address the arrangement of multiple parallel connections.
  • Figure 2 is a single-layer planetary wheel of the single-layered star-planetary row and a single-layer planetary wheel of the second-single-planetary planetary row, which is referred to as a single-row two-row star connection.
  • the first planetary row sun gear t1 is a constant input connection end, connected to the input end;
  • the first planetary row inner ring gear q1 is a constant output connection end, connected to the output end;
  • the ring gear q2 and the planet carrier are variable lock connection ends, and each is connected to a brake.
  • connection between the constant output connecting end and the output end is indirectly connected by the side shaft mechanical, and the side shaft with the paraxial gear (7) is set as the output end, and the paraxial gear is arranged on the inner ring gear of the first planetary row (7).
  • the meshed external gear (6) forms an indirect connection.
  • the three-row star-connected planetary row structure of the present invention has seven rotating members, namely, a first planetary row sun gear, a first planetary row inner ring gear, a second planetary row sun gear, a second planetary row inner ring gear, and three
  • the planets are the sun gear, the third planet's inner ring gear and the planet carrier, and the planet carrier is the common planet carrier of the planets.
  • Two of the rotating members serve as constant input terminals and constant output terminals, and the remaining five rotating members serve as variable lock connections.
  • the types of planetary wheels participating in the star connection in Figure 3 are in turn the inner planets of the first two-layered planetary planet and the inner planets of the second two-layer planetary row and the three-layer double-planetary planetary row.
  • the layer of planets referred to as the outer three inner rows of stars.
  • the first planetary row sun gear t1 is a constant input connection end, connected to the input end;
  • the planet carrier is a constant output connection end, connected to the output end;
  • the first planetary row inner ring gear q1, the second planetary row sun gear t2, the second The planetary row inner ring gear q2, the third planetary row sun gear t3 and the third planetary row inner ring gear q3 are variable locking connection ends, each of which is connected to the brake.
  • the four-row star-connected planetary row structure of the present invention has nine rotating members, namely, a first planetary row sun gear, a first planetary row inner ring gear, a second planetary row sun gear, a second planetary row inner ring gear, and three
  • the planetary sun gear, the third planetary inner ring gear, the fourth planetary sun gear, the fourth planetary inner ring gear and the planet carrier, the planet carrier is the common planet carrier of each planetary row.
  • Two of the rotating members serve as constant input terminals and constant output terminals, and the remaining seven rotating members serve as variable lock connections.
  • There are 72 combinations of input and output lock connections and 72 arrangement combinations are in accordance with the input/output lock connection feature of the present invention.
  • the types of planetary wheels participating in the star connection in Figure 4 are in the order of single-plane planetary gears of the single-layered single-planetary planetary row and single-plane planetary wheels of the single-layered single-planetary planetary row and the single-layer planetary carrier of the third-order single-planetary planetary row.
  • the single-plane planetary gear of the layer planetary gear and the single-layer planetary star of the fourth layer is referred to as a single four-row star.
  • the planet carrier is a constant input connection end, connected to the input end;
  • the first planetary row inner ring gear q1 is a constant output connection end, connected to the output end;
  • the first planetary row sun gear t1, the second planet row sun gear t2, the second Planetary gear ring gear q2, No. 3 planet row sun gear t3, No. 3 planet row ring gear q3, No. 4 planet row sun gear t4 and No. 4 planet row ring gear ring q4 is a variable locking connection, each connection Brake.
  • the five-row star-connected planetary row structure of the present invention has eleven rotating members.
  • the order of the planetary row type, the order of the planetary wheel types, and the combination or arrangement of the various characteristic parameters of each planetary row do not change the name and number of rotating members of each planetary connecting planetary row structure, and the number of rotating members in the star connecting planetary row structure is equal to (2*). n+1), where n is the number of planet rows in the star-connected planetary row structure.
  • n is the number of planet rows in the star-connected planetary row structure.
  • one rotating member acts as a constant input connection and one rotating member acts as a constant output connection, so there are at most (2*n-1) variable locking connections, connections (2* N-1) brakes, the transmission of the present invention controls the gear position by controlling the brakes, and the transmission of the present invention has (2*n-1) gear positions.
  • the transmission of the present invention can employ less than (2*n-1) gear positions as needed.
  • a clutch is used in a conventional planetary transmission to shift gears.
  • the control object of the clutch is the separation and combination of the moving part and the moving part.
  • the action of the clutch is completed by the hydraulic control system pushing the action actuator, and the structure of the oil supply pipe for pushing the clutch action actuator on the moving part is extremely complicated.
  • the present invention uses a brake to shift gear positions.
  • the control object of the variable lock connection end brake is the separation and combination of the moving part and the fixed part, and the action actuator on the push piece is pushed to complete the braking action.
  • the power for controlling the action uses direct power, electric power, vacuum boost, etc., and the structure is simple. Even if the hydraulic actuator is used to push the action actuator to complete the action, pushing the fuel supply line structure of the clutch actuator on the fixture is simple. Therefore, the present invention achieves the purpose of simplifying the control system of the planetary transmission.
  • the planetary row structure of the present invention is unchanged, and the input/output lock connection feature is changed to the second feature: a rotating member is used as a constant input connection end, and an input end is connected; and a plurality of output ends are arranged.
  • Each of the plurality of rotating members is used as a constant output connecting end, and each of the constant output connecting ends is respectively connected with one output end, and the rotational speeds of the respective output ends are different; and the remaining rotating members are respectively used as the variable locking connecting ends, and one brake is respectively connected .
  • each time a rotating member is added as the constant output connecting end it is reduced to provide a rotating member as the variable locking connecting end, correspondingly reducing one brake and reducing one gear position.
  • the transmission of the present invention having a plurality of constant output connections and a plurality of outputs is suitable for situations where multiple output shifts are required and the shift position does not require much.
  • Such a star-connected multi-row brake transmission is also within the scope of the present invention.
  • the advantage of the star-connected multi-row brake transmission of the present invention is that the planetary row structure feature is proposed, the input and output lock connection characteristics are proposed, and the variable lock connection end is controlled by the brake to control the gear position.
  • the present invention simplifies the control system of the planetary transmission.
  • 1 is an example of a star-connected multi-row brake transmission of the present invention employing two rows of planetary rows, and is also a schematic view of Embodiment 1 of the present invention.
  • 1 is the number one planetary row
  • 2 is the second planetary row
  • 3 is the brake
  • 4 is the input end
  • 5 is the output end.
  • 2 is a schematic view showing another example of the star-connected multi-row brake transmission of the present invention using two rows of planetary rows.
  • 1 is the first planetary row
  • 2 is the second planetary row
  • 3 is the brake
  • 4 is the input end
  • 5 is the output end
  • 6 is the external gear on the inner ring gear of the first planetary row
  • 7 is the paraxial gear.
  • Fig. 3 is a view showing an example of the star-connected multi-row brake transmission of the present invention using three rows of planetary rows, and is also a schematic view of Embodiment 2 of the present invention.
  • 1 is the number one planetary row
  • 2 is the second planetary row
  • 3 is the third planetary row
  • 4 is the brake
  • 5 is the input end
  • 6 is the output end.
  • FIG. 4 is a schematic view showing an example of a star-connected multi-row brake transmission of the present invention using four rows of planetary rows.
  • 1 is the number one planetary row
  • 2 is the second planetary row
  • 3 is the third planetary row
  • 4 is the fourth planetary row
  • 5 is the brake
  • 6 is the input end
  • 7 is the output end.
  • Fig. 5 is a block diagram showing the structure of a new proportional twelve-speed reverse gear transmission in the second embodiment.
  • 1 is the number one planetary row
  • 2 is the second planetary row
  • 3 is the third planetary row
  • 4 is the fourth planetary row
  • 5 is the fifth planetary row
  • 6 is the brake
  • 7 is the front sub-transmission input
  • 8 For the front sub-transmission output
  • 9 is the rear sub-transmission input
  • 10 is the rear sub-transmission output.
  • the planetary row and the external gear are shown in the half-frame structure diagram according to the industry practice.
  • the sideshaft, the paraxial gear, etc. are shown in full-frame structure diagram, the input end is indicated by the input arrow, the output end is indicated by the output arrow, and the brake is grounded.
  • the clutch symbol is indicated.
  • the components in each figure are only schematic structural relationships and do not reflect the true dimensions.
  • Embodiment 1 An example of the star-connected multi-row brake transmission of the present invention employing two rows of planetary rows, see Fig. 1, including a planetary row structure, an input-output lock connection, and three brakes.
  • Its planetary row structure is a two-row star connected planetary row structure.
  • the order of the planetary row types the first planetary row (1) is a double-layered planetary row, and the second planetary row (2) is a single-layered planetary row.
  • the order of the planetary gears the outer planets of the first two-layer planetary planets and the single-plane planetarys of the second single-plane planetary planets participate in the star connection, referred to as the outer two-row star connection.
  • a1, bw1, and cw1 be the first planetary row characteristic parameter, the outer star parameter, and the outer ring star parameter, respectively, a2, bd2, and cd2 are the second planetary row characteristic parameter, the single too star parameter, the single circle star parameter, Nxw1.
  • Nxd2 is the single-plane planetary gear speed of the No. 2 planet
  • Nj1 is the number one planetary carrier speed
  • Nj2 is the second planetary carrier speed
  • the input/output lock connection includes: the first planetary row planet carrier j1 is a constant input connection end, and is connected to one input end (3); the first planetary row inner ring gear q1 is a constant output connection end, and one output end is connected (4 ); No. 1 planet row sun gear t1, No. 2 planet row sun gear t2, No. 2 planet row inner ring gear q2 is a variable lock connection end, each connected to a brake (5).
  • the connection of the first planetary row carrier j1 and the connection of the first planetary sun gear t1 pass through the inside of the connection of the second planetary sun gear t2 in the form of a multi-layered sleeve shaft.
  • the planetary row structure feature and the input/output lock connection feature of the first embodiment are in accordance with the features of the present invention.
  • the transmission ratio is cw1/(cw1+bd2), and the transmission ratio formula and its corresponding transmission path are used as the third gear position.
  • the gear transmission paths of the first embodiment are difficult to distinguish by the word language, and it is easy to distinguish the nature of the gear path of each gear by mathematical language, that is, the gear ratio formula of each gear position is expressed.
  • the transmission ratio formula is obtained by solving the equations of the transmission path, and the two moving speeds of cw1 and cd2 in the transmission path are It is impossible to express which of the gear ratios is the main language.
  • this transmission ratio depends on the values of cw1 and cd2. According to the different values of cw1 and cd2, it can be the positive transmission ratio or the negative transmission ratio. It is better to express in text language than to be complete and valid in mathematical language.
  • each planetary row of the present invention is combined with each other to form a specific application property of the transmission.
  • the k1 values are specifically different depending on the needs.
  • the two-row planetary row of the transmission of the present invention is often applied as a three-gear transmission, a two-speed reverse gear transmission.
  • the ratio is 4.19773883, the second gear ratio is 1.833333, and the third gear ratio is 0.801023.
  • the ratio between adjacent gear ratios is approximately equal, and the transmission between first gear and second gear
  • the number of teeth of the No. 1 planet row is 85
  • the number of inner planetary gear teeth is 48
  • the outer planetary gear teeth are 48
  • the inner ring gear teeth number is 187.
  • the transmission controls the gear position via three brakes (5).
  • the gear ratio of the gear is 5.444444.
  • the gear ratio of the second gear is 2.0
  • the gear ratio of the third gear is 0.734332.
  • the ratio between the gear ratios of the adjacent gears is approximately equal.
  • the ratio of the gear ratio between the first gear and the second gear is 2.722222
  • the number of teeth of the No. 1 planet row is 88
  • the number of inner planetary gear teeth is 40
  • the number of inner ring gear teeth is 176.
  • the first embodiment is a type of proportional transmission having a plurality of equal ratios, and not just a transmission having only one equal ratio.
  • Embodiment 2 An example of the star-connected multi-row brake transmission of the present invention using three rows of planetary rows, see Fig. 3, including a planetary row structure, an input-output lock connection, and five brakes.
  • Its planetary row structure is a three-row star connected planetary row structure.
  • the order of the planetary row types the first planetary row (1), the second planetary row (2), and the third planetary row (3) are double-layered planetary rows.
  • the order of the planetary gears the outer planets of the first two-layer planetary planets and the inner planetary planets of the second two-layer planetary planets and the inner planetarys of the third-layer double-planetary planetarys.
  • the outer three inner rows are connected by stars.
  • a1, bw1, and cw1 be the first planetary row characteristic parameter, the outer star parameter, and the outer ring star parameter, respectively, a2, bn2, and cn2 are the second planetary row characteristic parameter, the inner star parameter, the inner circle star parameter, a3 , bn3, cn3 are the three-plane planetary row characteristic parameter, the inner star parameter, the inner circle star parameter, Nxw1 is the outer planet wheel speed of the No. 1 planet, Nxn2 is the inner planetary wheel speed of the No. 2 planet, and Nxn3 is No. 3.
  • Nj1 is the number of planetary carrier speed of the first planet
  • Nj2 is the planetary carrier speed of the second planet
  • Nj3 is the planetary carrier speed of the third.
  • 1 planet row planet carrier j1 is a constant output connection end, connected to an output end (5);
  • No.1 planetary row inner ring gear q1, second planet row sun gear t2, second planet row inner ring gear q2, third planet row sun gear t3 and third planet row inner ring gear q3 is a variable locking connection end, Connect one brake (6) to each.
  • the connection of the first planetary row sun gear t1 and the second planetary row sun gear t2 are connected in the form of a multi-layered sleeve shaft from the inside of the connection of the third planetary sun gear t3.
  • the planetary row structure feature and the input/output lock connection feature of the second embodiment are in accordance with the features of the present invention.
  • the transmission ratio is (bw1+cn2)/bw1, and the transmission ratio formula and its corresponding transmission path are used as the second gear position.
  • the transmission ratio is (bw1+bn3)/bw1, and the transmission ratio formula and its corresponding transmission path are used as the third gear position.
  • the transmission ratio is (bw1+bn2)/bw1, and the transmission ratio formula and its corresponding transmission path are used as the fourth gear position.
  • each planetary row of the present invention is combined with each other to form a specific application property of the transmission.
  • /(bw1+bn2) k2
  • the ratio of the transmission ratio is equal to the ratio of the third gear ratio to the fourth gear ratio is equal to k2, so that the absolute value of the reverse gear ratio is equal to the one gear ratio.
  • the transmission is a proportional four-speed reverse transmission.
  • the k2 values are specifically different depending on the needs.
  • the three-row planetary row of the inventive transmission is often applied as a proportional five-gear transmission, a four-speed reverse gear transmission.
  • the four-row planetary row of the inventive transmission is often used as a proportional seven-speed transmission, a six-speed reverse gear transmission.
  • the reverse gear ratio is -3.722222
  • the fourth gear ratio is 2.0
  • the third gear ratio is 2.945496
  • the second gear ratio is 3.029412
  • the first gear ratio is 3.729730.
  • the ratio between the transmission and the gear ratio of the adjacent gears is approximately equal.
  • the actual ratio of the gear ratio between the first gear and the second gear is 1.231173.
  • the actual ratio of the gear ratio between the second gear and the third gear is 1.231739, the third gear.
  • 1 planet is 36, the number of inner planet teeth is 49, the number of outer planet teeth is 18, the number of inner ring teeth is 170; the number of sun gears on the second planet is 68, the number of inner planet teeth, the outer planet
  • the number of teeth is 34, the number of teeth of the inner ring gear is 138; the number of teeth of the third row of planetary gears is 108, the number of inner planetary gear teeth, the number of outer planetary gear teeth are 37, and the number of inner ring gear teeth is 202.
  • the transmission controls the gear position via five brakes (6).
  • the transmission of Embodiment 1 of the present invention is connected in series with the transmission of Embodiment 2 of the present invention as a sub-transmission, see FIG.
  • the output (8) of the transmission of the embodiment 1 is connected to the input (9) of the transmission of the embodiment 2, the two sub-transmissions constitute a new transmission having five planetary rows, the new transmission having an input (7), an output End (10), which is a new transmission with a ratio of positive 12-speed reverse gear.
  • the first planetary row and the second planetary row in the first embodiment respectively serve as the first planetary row (1) and the second planetary row (2) of the new transmission; the first planetary row in the second embodiment
  • the No. 2 planetary platoon and the No. 3 planetary platoon are respectively the No.
  • This equal ratio positive 12-speed reverse gear has five planetary rows.
  • the gears are controlled.
  • Each gear has two brakes (6) for braking at the same time.
  • the total ideal ratio of the transmission is 1.23, the deviation between the actual value of the gear ratio and the ideal value is less than 0.4%, and the range of the positive gear ratio is 9.773.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission de freinage à rangées multiples et à montage en étoile comprenant une structure de trains d'engrenages planétaires, des raccords de verrouillage d'entrée/sortie et des freins. La structure de trains d'engrenages planétaires est une structure de trains d'engrenages planétaires à montage en étoile d'un système de détermination à deux degrés de liberté, qui comprend au moins deux rangées de trains d'engrenages planétaires. Les trains d'engrenages planétaires comprennent des trains d'engrenages planétaires à une couche, des trains d'engrenages planétaires à deux couches et des trains d'engrenages planétaires à trois couches qui sont agencés et combinés les uns aux autres. Des engrenages planétaires participant au montage en étoile comprennent des engrenages planétaires à une couche, des engrenages planétaires à couche externe, des engrenages planétaires à couche interne, des engrenages planétaires à première couche, des engrenages planétaires à deuxième couche et des engrenages planétaires à troisième couche qui sont agencés et combinés les uns aux autres. Des paramètres caractéristiques des trains d'engrenages planétaires sont combinés les uns aux autres. Les raccords de verrouillage d'entrée/sortie sont connectés à une extrémité d'entrée (4) au moyen d'un élément rotatif servant d'extrémité de connexion d'entrée inchangée (j1), sont connectés à une extrémité de sortie (5) au moyen d'un élément rotatif servant d'extrémité de connexion de sortie inchangée (q1) et sont connectés de manière correspondante aux freins (3) au moyen d'autres éléments rotatifs servant d'extrémités de connexion à verrouillage variable (t1, t2, t3). Les intervalles sont commandés en commandant les freins.
PCT/CN2018/112601 2017-10-31 2018-10-30 Transmission de freinage à rangées multiples et à montage en étoile WO2019085880A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201880003527.6A CN109874317B (zh) 2017-10-31 2018-10-30 星连接多排制动变速器

Applications Claiming Priority (2)

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CN201711046492.8 2017-10-31
CN201711046492.8A CN109723771A (zh) 2017-10-31 2017-10-31 星连接多排制动变速器

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WO2019085880A1 true WO2019085880A1 (fr) 2019-05-09

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109723792A (zh) * 2017-10-31 2019-05-07 罗灿 非锥齿轮差速器
DE102022133638A1 (de) * 2022-12-16 2024-06-27 Zf Friedrichshafen Ag Schaltbares Planetengetriebe und Verfahren zum Schalten des Planetengetriebes

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000145901A (ja) * 1998-11-12 2000-05-26 Exedy Corp 自動変速装置
CN101446332A (zh) * 2008-12-18 2009-06-03 潍坊盛瑞动力机械科技有限公司 一种多挡位动力换挡行星变速箱
CN105673783A (zh) * 2016-04-21 2016-06-15 中国北方车辆研究所 一种大传动比的两挡行星变速器
CN205383229U (zh) * 2016-03-21 2016-07-13 岭南师范学院 新型九档自动变速器传动机构
CN205401620U (zh) * 2016-03-02 2016-07-27 岭南师范学院 一种新型高效八档自动变速器传动机构
WO2016193286A1 (fr) * 2015-06-04 2016-12-08 Swepart Transmission Ab Train planétaire

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000145901A (ja) * 1998-11-12 2000-05-26 Exedy Corp 自動変速装置
CN101446332A (zh) * 2008-12-18 2009-06-03 潍坊盛瑞动力机械科技有限公司 一种多挡位动力换挡行星变速箱
WO2016193286A1 (fr) * 2015-06-04 2016-12-08 Swepart Transmission Ab Train planétaire
CN205401620U (zh) * 2016-03-02 2016-07-27 岭南师范学院 一种新型高效八档自动变速器传动机构
CN205383229U (zh) * 2016-03-21 2016-07-13 岭南师范学院 新型九档自动变速器传动机构
CN105673783A (zh) * 2016-04-21 2016-06-15 中国北方车辆研究所 一种大传动比的两挡行星变速器

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CN109874317A (zh) 2019-06-11
CN109874317B (zh) 2021-10-15

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