CN106594191B - Two-speed device capable of providing large speed ratio - Google Patents

Two-speed device capable of providing large speed ratio Download PDF

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Publication number
CN106594191B
CN106594191B CN201611208725.5A CN201611208725A CN106594191B CN 106594191 B CN106594191 B CN 106594191B CN 201611208725 A CN201611208725 A CN 201611208725A CN 106594191 B CN106594191 B CN 106594191B
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clutch
gear
force transmission
fixedly connected
intermediate shaft
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CN106594191A (en
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韩文明
潘亚敏
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Shanxi Guoli Information Technology Co Ltd
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Shanxi Guoli Information Technology Co Ltd
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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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/04—Freewheels or freewheel clutches combined with a clutch for locking the driving and driven members
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

A two-speed device capable of providing a large speed ratio comprises an input shaft, an output shaft, a gear mechanism, a C clutch and a B clutch; the gear mechanism comprises an input gear, a middle shaft gear assembly, a transition gear assembly, an output gear and a gear retainer assembly which is formed by fixedly connecting a front retainer and a rear retainer and is provided with a cavity; the first intermediate shaft gear and the last intermediate shaft gear of the intermediate shaft gear assembly are respectively meshed with the input gear and the output gear, and the rest intermediate shaft gears are respectively meshed with corresponding transition gears; the driving component of the clutch C is fixedly connected with the input shaft, and the driven component is fixedly connected with the gear retainer assembly; the rotating component of the clutch B is fixedly connected with the gear retainer assembly, and the fixed component is fixedly connected with a shell containing the second-speed device; the B clutch and the C clutch are locked alternatively. Compared with the existing planetary gear transmission, the gear mechanism of the invention has the advantages of no gear ring, simple structure, low requirement on processing precision and capability of realizing large speed ratio under the condition of unchanged radial size.

Description

Two-speed device capable of providing large speed ratio
Technical Field
The present invention relates to a gear transmission applied to a vehicle, and more particularly to a two-speed device with more gears.
Background
There are two types of existing gear transmissions: fixed axis and planetary gear type.
As shown in fig. 1b, a schematic view of a planetary gear type transmission is provided, which is composed of three planetary rows, each including a gear P 1 Planetary gear P 2 Gear ring P 3 And a planet carrier P 4 (as shown in FIG. 1 a), three planetary rows are combined together, through three clutches C 1 、C 2 、C 3 Three brake bands B 1 、B 2 、B 3 In combination with engagement of the one-way clutch F, the gears P of each planetary row may be engaged 1 Gear ring P 3 And a planet carrier P 4 Respectively as an active part, a passive part or a fixed part, so that a plurality of gears can be combined. The hydraulic torque converter is often matched with the front part of the speed changer, and gear shifting can be carried out without cutting off the power of an engine, but the transmission efficiency is low; interconnecting, nesting of related components of one planetary row with related components of another planetary row of the planetary transmission results inThe whole transmission is very complex in structure and difficult to arrange, great difficulty is brought to manufacturing and maintenance, and particularly, a gear ring machining method cannot be adopted for machining a gear hobbing, so that machining efficiency is low, precision is poor, and cost is high.
Disclosure of Invention
In order to solve the problems of complex structure and low machining efficiency of the existing planetary gear transmission, the invention provides a two-speed device which has a simple structure and high machining efficiency and can provide a large speed ratio.
The technical scheme of the invention is as follows:
the utility model provides a can provide two speed devices of big velocity ratio which characterized in that: the second-speed device comprises a gear mechanism G1, a C clutch G3 and a B clutch G2 which are arranged along the same axis; the gear mechanism G1 comprises an input gear G11 fixedly arranged on an input shaft, a plurality of intermediate shaft gear assemblies, at least one transition gear assembly, an output gear G14 and a gear retainer assembly which is formed by fixedly connecting a front retainer G16 and a rear retainer G17 and is provided with a cavity; the intermediate shaft gear assembly comprises an intermediate shaft first gear G12, an intermediate shaft second gear G12a, an intermediate shaft third gear G13a, an intermediate shaft fourth gear G13 and … … which are coaxially arranged on an intermediate shaft G15 in parallel, and an intermediate shaft Nth gear; the first gear and the second gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft 1-2 gear assembly, the third gear and the fourth gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft 3-4 gear assembly, … …, the (N-1) th gear and the N gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft (N-1) -N gear assembly; the intermediate shaft 1-2 gear assembly, the intermediate shaft 3-4 gear assembly, the … … intermediate shaft (N-1) -N gear assembly are rotatably arranged in a cavity between the front retainer G16 and the rear retainer G17 through the intermediate shaft G15 and can rotate relatively; the two ends of the intermediate shaft G15 are supported by a front retainer G16 and a rear retainer G17; the transition gear assembly comprises a first transition gear G11a, a second transition gear G14a, … … and an Mth transition gear which are arranged between an input gear G11 and an output gear G14, wherein the first transition gear and the second transition gear are coaxially and fixedly connected to form a 1-2 transition gear assembly, the third transition gear and the fourth transition gear are coaxially and fixedly connected to form a 3-4 transition gear assembly, … …, and the (M-1) th transition gear and the M transition gear are coaxially and fixedly connected to form a (M-1) -M transition gear assembly; the input gear G11, the 1-2 transition gear assembly, the 3-4 transition gear assembly, the … …, (M-1) -M transition gear assembly and the output gear G14, and the gear retainer assembly are coaxially arranged and can rotate relative to each other; the input gear G11 is meshed with a plurality of intermediate shaft first gears G12; the output gear G14 is meshed with a plurality of intermediate shaft Nth gears; the first transition gear G11a, the second transition gears G14a, … … and the mth transition gear are respectively meshed with the plurality of intermediate shaft second gears G12a, the plurality of intermediate shaft third gears G13a, … … and the plurality of intermediate shaft (N-1) th gears; n=m+2, M being an even number; the C clutch G3 comprises a driving component G31 and a driven component G32; the driving component G31 is fixedly connected with the input shaft, and the driven component G32 is fixedly connected with the gear retainer assembly; the B clutch G2 comprises a rotating assembly G21 and a fixed assembly G22; the rotating component G21 is fixedly connected with the gear retainer assembly, and the fixing component G22 is fixedly connected with a shell H containing the two-speed device; the B clutch G2 and the C clutch G3 can only be locked.
Based on the above basic technical solution, the present invention also makes the following definitions and/or limitations:
m=2 and n=4.
Types of clutches in the above-described two-speed device:
(1) The B clutch and the C clutch can be multi-plate wet clutches.
(2) When the above-mentioned two-speed device is a speed reducing device, the B clutch is an overrunning clutch or a multi-plate wet clutch, and for the overrunning clutch: when the rotating direction of the rotating component relative to the fixed component is consistent with the rotating direction of the input gear, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state; the clutch C adopts a multi-plate wet clutch;
(3) When the second-speed device is a speed increasing device, the overrunning clutch or the multi-plate wet clutch is adopted as the C clutch, and the overrunning clutch is as follows: when the rotation direction of the driving component relative to the driven component is consistent with the rotation direction of the input gear, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state; the B clutch adopts a multi-plate wet clutch.
The clutch B can be a friction plate type cloth spiral surface compaction overrunning clutch, and mainly comprises the following modes:
1 st:
the overrun clutch is a friction plate type circumferential cloth spiral surface compression overrun clutch and comprises a clutch limiting device, a fixed component G22, a rotating component G21, a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating shaft line; the fixing assembly G22 comprises a first force transmission drum G221 and a plurality of first friction plates G222 arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction; the rotating assembly G21 comprises a second force transmission hub G211 and a plurality of second friction plates G212 arranged outside the second force transmission hub, wherein the second friction plates can slide relatively relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction; the first force transmission drum G221 is sleeved outside the second force transmission hub G211; the plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction; the clutch limiting device comprises a supporting main body G271 fixedly connected with an input shaft of the two-speed device and a retainer ring G272 arranged on the supporting main body; the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece G23 and a second spiral surface matching piece G24; the first helicoid coupling piece G23 is provided with a first helicoid G231; the second helicoid mating part G24 is provided with a second helicoid G241 matched with the first helicoid; the first screw surface mating part G23 is fixedly connected with the supporting main body, and the second screw surface mating part G24 is fixedly connected with the second force transmission hub G211; the second screw surface mating part is positioned between the supporting main body and the first screw surface mating part G23, and the second screw surface mating part can perform screw sliding relative to the first screw surface mating part; the supporting main body G271 is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom of the supporting main body G is an overhanging circular ring; the outer side surface of the neck of the support main body is provided with a check ring groove G273 and a limit step G274; the retainer G272 is disposed in the retainer groove G273; the retainer ring and the limiting step are used for fixing the axial position of the first spiral surface matching piece G23; the annular ring of the supporting body is used for limiting the axial positions of the first friction plate G222 and the second friction plate G212; the additional clutch control device comprises an annular control cylinder arranged on the first force transmission drum G221; the annular control oil cylinder comprises a cylinder body G29 and a connecting main body G30, and a pressure plate G28 arranged between the cylinder body G29 and the connecting main body G30; the connecting main body G30 is fixedly connected with the shell H; the cross section of the platen G28 is approximately U-shaped; a plurality of springs G25 are arranged between the bottom end surface of the pressure plate G28 and the connecting main body G30; one top of the pressure plate G28 is accommodated in a cylinder body G29, a piston G26 forming an annular control oil cylinder is arranged, and a sealing oil chamber CYL is formed between the piston G26 and the cylinder body G29; the other top end surface of the pressure plate G28 is used for pressing the friction plate; the support body and the first force transfer drum serve as two force transfer ends of the overrunning clutch, respectively.
2 nd:
the overrun clutch is a friction plate type cloth spiral surface external compaction overrun clutch and comprises a clutch limiting device, a fixed component G22, a rotating component G21, a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating axis; the fixing assembly G22 comprises a first force transmission drum G221 and a plurality of first friction plates G222 arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction; the rotating assembly G21 comprises a second force transmission hub G211 and a plurality of second friction plates G212 arranged outside the second force transmission hub, wherein the second friction plates can slide relatively relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction; the first force transmission drum G221 is sleeved outside the second force transmission hub G211; the plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction; the clutch limiting device comprises a supporting main body G271 fixedly connected with the shell H; the supporting body is of a circular ring structure and is used for limiting the axial positions of the first friction plate and the second friction plate; the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece G23 and a second spiral surface matching piece G24; the first helicoid coupling piece G23 is provided with a first helicoid G231; the second helicoid mating part G24 is provided with a second helicoid G241 matched with the first helicoid; the first spiral surface mating part G23 is fixedly connected with the supporting main body, and the second spiral surface mating part G24 is fixedly connected with the first force transmission drum G221; the second helicoidal mating piece is positioned between the supporting main body and the first helicoidal mating piece G23, and the second helicoidal mating piece slides spirally relative to the first helicoidal mating piece; the additional clutch control device comprises an annular cylinder body arranged on the shell H, a piston G26 arranged in the annular cylinder body, and a plurality of springs G25 arranged between the second spiral surface matching piece G24 and the piston G26; the end surfaces of the springs are arranged on the pistons and face the first friction plate G222 at the same time; a sealing oil chamber CYL is formed between the other end surface of the piston and the annular cylinder body; the support body and the second force transfer hub serve as two force transfer ends of the overrunning clutch, respectively.
3 rd:
the overrun clutch is a friction plate type circumferential cloth spiral surface compression overrun clutch and comprises a clutch limiting device, a fixed component G22, a rotating component G21, a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating axis; the fixing assembly G22 comprises a first force transmission drum G221 and a plurality of first friction plates G222 arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction; the rotating assembly G21 comprises a second force transmission hub G211 and a plurality of second friction plates G212 arranged outside the second force transmission hub, wherein the second friction plates can slide relatively relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction; the first force transmission drum G221 is sleeved on the inner side of the second force transmission hub G211; the plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction; the clutch limiting device comprises a supporting main body G271 fixedly connected with an input shaft of the second-speed device and a retainer ring G272 arranged on the supporting main body; the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece G23 and a second spiral surface matching piece G24; the first helicoid coupling piece G23 is provided with a first helicoid G231; the second helicoid mating part G24 is provided with a second helicoid G241 matched with the first helicoid; the first spiral surface mating part G23 is fixedly connected with the supporting main body, and the second spiral surface mating part G24 is fixedly connected with the first force transmission drum G221; the second helicoidal mating piece is positioned between the supporting main body and the first helicoidal mating piece G23, and the second helicoidal mating piece slides spirally relative to the first helicoidal mating piece; the supporting main body G271 is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom of the supporting main body G is an overhanging circular ring; the outer side surface of the neck of the support main body is provided with a check ring groove G273 and a limit step G274; the retainer G272 is disposed in the retainer groove G273; the retainer ring G13 and the limiting step G274 are used for fixing the axial position of the first screw face matching piece G23; the annular ring of the supporting body is used for limiting the axial positions of the first friction plate G222 and the second friction plate G212; the additional clutch control device comprises an annular control cylinder arranged on the first force transmission drum G221; the annular control oil cylinder comprises a cylinder body G29 and a connecting main body G30, and a pressure plate G28 arranged between the cylinder body G29 and the connecting main body G30; the connecting main body G30 is fixedly connected with the shell H; the cross section of the platen G28 is approximately U-shaped; a plurality of springs G25 are arranged between the bottom end surface of the pressure plate G28 and the connecting main body G30; one top of the pressure plate G28 is accommodated in a cylinder body G29, a piston G26 forming an annular control oil cylinder is arranged, and a sealing oil chamber CYL is formed between the piston G26 and the cylinder body G29; the other top end surface of the pressure plate G28 is used for pressing the friction plate; the support body and the second force transfer hub serve as two force transfer ends of the overrunning clutch, respectively.
4 th:
the overrun clutch is a friction plate type cloth spiral surface external compaction overrun clutch and comprises a clutch limiting device, a fixed component G22, a rotating component G21, a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating axis; the fixing assembly G22 comprises a first force transmission drum G221 and a plurality of first friction plates G222 arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction; the rotating assembly G21 comprises a second force transmission hub G211 and a plurality of second friction plates G212 arranged outside the second force transmission hub, wherein the second friction plates can slide relatively relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction; the first force transmission drum G221 is sleeved on the inner side of the second force transmission hub G211; the plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction; the clutch limiting device comprises a supporting main body G271 fixedly connected with the shell H; the supporting body is of a circular ring structure and is used for limiting the axial positions of the first friction plate and the second friction plate; the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece G23 and a second spiral surface matching piece G24; the first helicoid coupling piece G23 is provided with a first helicoid G231; the second helicoid mating part G24 is provided with a second helicoid G241 matched with the first helicoid; the first screw surface mating part G23 is fixedly connected with the supporting main body, and the second screw surface mating part G24 is fixedly connected with the second force transmission hub G211; the second helicoidal mating piece is positioned between the supporting main body and the first helicoidal mating piece G23, and the second helicoidal mating piece slides spirally relative to the first helicoidal mating piece; the additional clutch control device comprises an annular cylinder body arranged on the shell H, a piston G26 arranged in the annular cylinder body, and a plurality of springs G25 arranged between the second spiral surface matching piece G24 and the piston G26; the end surfaces of the springs are arranged on the pistons and face the first friction plate G222 at the same time; a sealing oil chamber CYL is formed between the other end surface of the piston and the annular cylinder body; the support body and the first force transfer drum serve as two force transfer ends of the overrunning clutch, respectively.
In order to enable the spiral surface matching parts of the friction plate type cloth spiral surface compaction overrunning clutch to be self-locking and automatically unlocking, the first spiral surface matching parts, the second spiral surface matching parts, the first friction plate and the second friction plate meet the following conditions:
Figure BDA0001190533040000071
wherein, beta is the average helix angle of the effective contact part of the helicoids of the two helicoids of the matching parts;
mu is the friction coefficient between the friction pair of the first friction plate and the second friction plate;
μ' is the coefficient of friction between the two helicoidal mating parts;
n is a small value in the effective number of the first friction plate and the second friction plate.
The invention has the advantages that:
1. compared with the existing planetary gear transmission, the gear mechanism provided by the invention omits a gear ring, avoids complex nesting between planetary rows and planetary row related components, overcomes the defects of complex structure and difficult processing of the planetary gear mechanism related components, has a simple structure and low processing precision requirement, and is convenient to design and manufacture; in addition, the transition gear assembly is arranged, so that a large speed ratio can be realized under the condition that the radial size is unchanged.
2. The invention adopts the cooperation of the common clutch and the overrunning clutch, when in use, the common clutch is only controlled, the overrunning clutch can be changed along with the state change of the common clutch, and when one clutch is released, the other clutch is engaged, so that the power can not be interrupted during gear shifting.
3. The overrun clutch adopted by the invention is a friction plate type cloth spiral surface compaction overrun clutch, so that the gradual change of the output torque from the former gear to the output torque of the latter gear can be realized during gear shifting, and the smooth transition of the output torque in the gear shifting process can be realized.
4. When the gear shifting device is used for gear shifting, only the common clutch is required to be controlled, the state of the overrunning clutch can be changed along with the common clutch, and compared with the existing speed changing module and speed changer, the gear shifting device does not need to calibrate the control of a motor and does not need to strictly control the output of the torque of the motor.
Drawings
FIG. 1a is a schematic diagram of a basic structure of a planetary gear mechanism according to the prior art;
FIG. 1b is a schematic diagram of a prior art planetary gear transmission;
FIG. 2 is a schematic diagram of a second-speed device according to the present invention;
FIG. 3 is a schematic diagram of a second embodiment of the present invention;
FIG. 3a is an assembled cross-sectional view of a first embodiment of the B clutch (overrunning clutch) of FIG. 3;
FIG. 3B is an assembled cross-sectional view of a second embodiment of the B clutch (overrunning clutch) of FIG. 3;
FIG. 4 is a schematic diagram of the relationship between helicoidal surface formation and helicoidal surface mating parts;
FIG. 5 is a simplified schematic diagram of the structural principle of a friction plate type cloth spiral surface compression overrunning clutch;
FIG. 6 (a) is a schematic diagram illustrating the force analysis of an overrunning clutch according to the present invention;
FIG. 6 (b) is a force-bearing schematic diagram of wedges when the overrunning clutch is locked;
FIG. 6 (c) is a force diagram of the wedges during an overrunning clutch unlock condition.
Detailed Description
As shown in fig. 2, the second-speed device provided by the present invention includes: an input shaft, a gear mechanism G1, a B clutch G2, a C clutch G3, and an output shaft.
1. Gear mechanism
The gear mechanism G1 comprises an input gear G11, a plurality of groups of intermediate shaft gear assemblies uniformly distributed along the circumference (each group of intermediate shaft gear assemblies consists of 1 intermediate shaft first gear G12, 1 intermediate shaft second gear G12a, 1 intermediate shaft third gear G13a, 1 intermediate shaft fourth gear G13 and 1 intermediate shaft G15), wherein the gears G12 and G12a are fixedly connected into a whole and synchronously rotate, the gears G13a and G13 are fixedly connected into a whole and synchronously rotate), a transition gear assembly (consisting of a first transition gear G11a and a transition gear G14 which are fixedly connected into a whole), an output gear G14 and a gear retainer assembly with a cavity (consisting of a front retainer G16 and a rear retainer G17 which are fixedly connected).
The input gear G11, the gear cage assembly, the transition gear assembly and the output gear G14 have coincident axes of rotation and are rotatable relative to each other.
The input gear G11 is meshed with a plurality of intermediate shaft first gears G12 and is located in a cavity between the front cage G16 and the intermediate cage G18; a plurality of intermediate shaft second gears G12a mesh with the first transition gear G11a, a plurality of intermediate shaft third gears G13a mesh with the second transition gear G14a, and a plurality of intermediate shaft fourth gears G13 mesh with the output gear G14, all located in the cavity between the intermediate holder G18 and the rear holder G17.
2. B, C clutch
The B clutch G2 comprises a rotating assembly G21 and a fixed assembly G22; the rotating component G21 is fixedly connected with the gear retainer assembly, and the fixing component G22 is fixedly connected with the shell H. The C clutch G3 comprises a driving component G31 and a driven component G32; the driving component G31 is fixedly connected with the input shaft, and the driven component G32 is fixedly connected with the gear retainer assembly. The B clutch G2 and the C clutch G3 can be locked only alternatively.
3. Working process
The working process of the invention is divided into two working conditions:
(1) when the B clutch G2 is engaged, the C clutch G3 is disengaged, the power transmission route is: input end, input gear g11, intermediate shaft first gear g12, intermediate shaft second gear g12a, first transition gear g11a, second transition gear g14a, intermediate shaft third gear g13a, intermediate shaft fourth gear g13, output gear g14 and output end. The transmission ratio is i G The output steering is in the same direction as the input torque.
(2) When the B clutch G2 is disengaged and the C clutch G3 is engaged, the power transmission route is: input end→whole gear mechanism (as one rigid body) →output end. The transmission ratio is 1, and the output steering direction is the same as the input torque direction.
4. Selection of B, C clutch design
The B, C clutch design of the present invention is selected from several preferred embodiments:
(1) the clutch B is a multi-plate wet clutch, and the clutch C is a multi-plate wet clutch.
(2) When the second speed device is a speed reducing device, the clutch B is an overrunning clutch, and when the rotation direction of the rotating assembly relative to the fixed assembly is consistent with the rotation direction of the input gear, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state; the C clutch is a multi-plate wet clutch.
(3) When the two-speed device is a speed increasing device, the clutch B is a multi-plate wet clutch, the clutch C is an overrunning clutch, and when the rotation direction of the driving component relative to the driven component is consistent with the rotation direction of the input gear, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locked state.
(4) When the second speed device is a speed reducing device, the B clutch is a combination of an overrunning clutch and a plurality of wet clutches, and when the plurality of wet clutches in the B clutch are engaged, the B clutch can also transmit torque in the overrunning direction of the overrunning clutch (when the rotation direction of the rotating assembly relative to the fixed assembly is consistent with the rotation direction of the input gear, the overrunning clutch is in an overrunning state; otherwise, the overrunning clutch is in a locking state); the C clutch is a multi-plate wet clutch.
(5) When the second speed device is a speed increasing device, the B clutch is a multi-plate wet clutch, the C clutch is a combination of an overrunning clutch and the multi-plate wet clutch, when the multi-plate wet clutch in the C clutch is connected, the C clutch can also transmit torque in the overrunning direction of the overrunning clutch (when the rotation direction of the driving component relative to the driven component is consistent with the rotation direction of the input gear, the overrunning clutch is in an overrunning state, otherwise, the overrunning clutch is in a locking state).
As shown in fig. 3, the B clutch uses a friction plate type spiral surface to compress the overrunning clutch, and the C clutch uses a multi-plate wet clutch (a conventional friction plate type clutch). The B clutch is described in detail below with several specific embodiments.
Example 1:
as shown in fig. 3a, the clutch B is a friction plate type spiral surface external compression overrun clutch, and comprises a clutch limiting device G27, a fixed component G22, a rotating component G21, a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotation axis.
The fixing assembly G22 includes a first force transfer drum G221 and a plurality of first friction plates G222 disposed on the first force transfer drum G221, the first friction plates G222 being axially slidable relative to the first force transfer drum G221, the first friction plates G222 being rotated in synchronization with the first force transfer drum G221 in the circumferential direction.
The rotating assembly G21 includes a second force transmission hub G211 and a plurality of second friction plates G212 disposed outside the second force transmission hub G211, the second friction plates G212 being axially slidable relative to the second force transmission hub G211, the second friction plates G212 rotating in synchronization with the second force transmission hub G211 in the circumferential direction.
The first force transmission drum G221 is sleeved outside the second force transmission hub G211; a step G223 and a baffle G224 for limiting the axial position of the first friction plate G222 are also arranged on one end face of the first force transfer drum G221; the step G223 blocks the blocking piece G224, limiting it from sliding out of the end of the first force transfer drum G221; the stop G224 serves to limit the axial position of the first and second friction plates G222, G212, preventing the friction plates from sliding out of the first force transfer drum G221.
The plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction.
The clutch limiting device G27 comprises a supporting main body G271 fixedly connected with the shell H; the supporting body G271 has a circular ring structure for restricting axial positions of the first friction plate G222 and the second friction plate G212;
the self-locking/overrunning control device is used for controlling the engagement of the first friction plate G222 and the second friction plate G212 to comprise a first screw surface mating part G23 and a second screw surface mating part G24. A plurality of first helicoids G231 are arranged on the matching surface of the first helicoid matching piece G23; a plurality of second helicoids G241 matched with the first helicoids G231 are arranged on the matching surface of the second helicoid matching piece G24; the direction of rotation of the first helicoid G231 and the second helicoid G241 is related to the direction in which the clutch transfers torque:
Referring to fig. 3a, a torsion moment is applied to the second force transmission hub G211, when the second force transmission hub G211 has a clockwise rotation tendency relative to the support body G271 under the action of the torsion moment, as seen from left to right in the illustrated position, if the first helicoids G231 and the second helicoids G241 are right-handed, the overrunning clutch is in an overrunning state under the action of the moment; if the first helicoid G231 and the second helicoid G241 are left-handed, the overrunning clutch is in a locked state under the action of the torque, and the torque on the second force transmission hub G211 is transmitted to the support body through the second friction plate G212, the first friction plate G222, the first force transmission drum G221 and the first helicoid coupling G23, which are fixedly connected with the second helicoid coupling G24.
The first helicoidal mating part G23 is fixedly connected with the supporting main body G271, and the second helicoidal mating part G24 is fixedly connected with the first force transmission drum G221; the second helicoid partner G24 is located in a space formed by the first force transmission drum G221, the support body G271 and the first helicoid partner G23, and the second helicoid partner G24 can spirally slide with respect to the first helicoid partner G23.
The support body G271 and the second force transfer hub G211 serve as the two force transfer ends of the overrunning clutch, respectively.
The additional clutch control device comprises an annular cylinder body arranged on the shell H, a piston G26 arranged in the annular cylinder body, and a plurality of springs G25 arranged between the second spiral surface matching piece G24 and the piston G26; the end surfaces of the springs are arranged on the pistons and face the first friction plate G222 at the same time; and a sealing oil chamber CYL is formed between the other end surface of the piston and the annular cylinder body.
Working principle:
when the sealed oil chamber CYL is filled with oil, the hydraulic thrust force overcomes the spring force of the spring G25 to press the piston G26 against the friction plate, and the B2 clutch is an overrunning clutch and a multi-plate wet clutch in an engaged state: when the overrun condition is met, the clutch enters an overrun condition, and torque is transmitted even if the overrun condition is met, and the transmitted torque is the same as the multi-plate wet clutch, wherein the transmitted torque is=positive pressure on a friction surface multiplied by an equivalent friction coefficient; when the clutch enters a locking working condition and the transmitted torque is large enough, friction force between friction plates forms friction torque to drive the second spiral surface matching piece G24 to further rotate towards the locking direction, even the piston G26 can be pressed back to the cylinder CYL pressure release position, at the moment, even if the cylinder is depressurized, the spring G25 can not press back the second spiral surface matching piece G24, and the limit value of the transmitted torque is the strength limit of the part.
When the sealing oil chamber CYL is depressurized, the first spiral surface mating part G23 and the second spiral surface mating part G24 are in an unlocking state, the spring force of the spring G25 returns the piston G26, namely, the piston G26 moves in a direction away from the friction plate, at the moment, the B2 clutch is in a separating state, and no torque is transmitted in both rotation directions.
Example 2:
as shown in fig. 3B, the B clutch is a friction plate type spiral surface compression overrunning clutch, and comprises a clutch limiting device G27, a fixed component G22, a rotating component G21, a self-locking/overrunning control device and an additional clutch control device, which are arranged on the same rotation axis.
The fixing assembly G22 includes a first force transfer drum G221 and a plurality of first friction plates G222 disposed on the first force transfer drum G221, the first friction plates G222 being axially slidable relative to the first force transfer drum G221, the first friction plates G222 being rotated in synchronization with the first force transfer drum G221 in the circumferential direction.
The rotating assembly G21 includes a second force transmission hub G211 and a plurality of second friction plates G212 disposed outside the second force transmission hub G211, the second friction plates G212 being axially slidable relative to the second force transmission hub G211, the second friction plates G212 rotating in synchronization with the second force transmission hub G211 in the circumferential direction.
The first force transmission drum G221 is sleeved outside the second force transmission hub G211; the plurality of first friction plates G222 and the plurality of second friction plates G212 are alternately arranged in the axial direction.
The self-locking/overrunning control device is used for controlling the engagement of the first friction plate G222 and the second friction plate G212 to comprise a first screw surface mating part G23 and a second screw surface mating part G24. A plurality of first helicoids G231 are arranged on the matching surface of the first helicoid matching piece G23; a plurality of second helicoids G241 matched with the first helicoids G231 are arranged on the matching surface of the second helicoid matching piece G24; the direction of rotation of the first helicoid G231 and the second helicoid G241 is related to the direction in which the clutch transfers torque:
Referring to fig. 3b, a torsional moment is applied to the supporting body G271, when the supporting body G271 has a clockwise rotation tendency relative to the first force transfer drum G221 (which is an outer drum) under the action of the torsional moment, when the first spiral surface G231 and the second spiral surface G241 are rotated right, the overrunning clutch is in an overrunning state under the action of the moment, as seen from left to right in the illustrated position; if the first spiral surface G231 and the second spiral surface G241 are left-handed, the overrunning clutch is in a locked state under the action of the torque, and the torque on the supporting body G271 is transmitted outwards through the first spiral surface coupling member G23, the second force transmission hub G211 (inner hub) fixedly connected with the second spiral surface coupling member G24, the second friction plate G212, the first friction plate G222 and the first force transmission drum G221 (outer drum).
The clutch limiting device comprises a supporting main body G271 and a retainer ring G272; the supporting main body G271 is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom of the supporting main body G is an overhanging circular ring; the outer side surface of the neck of the support main body is provided with a check ring groove G273 and a limit step G274; the retainer G272 is disposed in the retainer groove G273; the retainer ring G272 and the limiting step G274 are used for fixing the axial position of the first screw face coupling piece G23; the annular ring of the support body serves to limit the axial positions of the first friction plate G222 and the second friction plate G212.
The second helicoidal mating part G24 is fixedly connected with a second force transmission hub G211; the second helicoidal mating piece G24 is located in the space formed by the second force transmission hub G211, the support body G271 and the first helicoidal mating piece G23.
The support body G271 and the first force transfer drum G221 serve as the two force transfer ends of the overrunning clutch, respectively.
The additional clutch control device comprises an annular control cylinder arranged on the first force transmission drum G221;
the annular control oil cylinder comprises a cylinder body G29 and a connecting main body G30, and a pressure plate G28 arranged between the cylinder body G29 and the connecting main body G30; the connecting main body G30 is fixedly connected with the shell H; the cross section of the platen G28 is approximately U-shaped;
a plurality of springs G25 are arranged between the bottom end surface of the pressure plate G28 and the connecting main body G30;
one top of the pressure plate G28 is accommodated in a cylinder body G29, a piston G26 forming an annular control oil cylinder is arranged, and a sealing oil chamber is formed between the piston G26 and the cylinder body G29;
the other top end face of the pressing plate G28 is used for pressing the friction plate.
Working principle:
when the sealed oil chamber CYL is filled with oil, the hydraulic thrust overcomes the spring force of the plurality of springs G25 to separate the pressure plate G28 from the friction plate, and the B clutch is an overrunning clutch: the clutch will enter the overrun condition when the overrun condition is met, and the clutch will enter the locking condition when the locking condition is met.
When the sealed oil chamber CYL is depressurized, the spring force of the spring G25 returns the piston G26, and the pressure plate G28 is pressed against the friction plate, and at this time, the B clutch respectively plays roles of an overrunning clutch and a normal clutch according to the torque transmission direction: when the direction of the transmission torque accords with the condition of entering the overrunning state, the B clutch acts as a common clutch, and the transmission torque is dependent on the total spring force of the spring G25; when the direction of the transmitted torque accords with the condition of entering the locking state, the B clutch enters the locking working condition, and the B clutch plays a role of an overrunning clutch.
Example 3:
the B clutch is a friction plate type spiral surface external compression overrunning clutch, which is similar to the B clutch in embodiment 1 in structure, and differs in that:
the first force transmission drum G221 is sleeved on the inner side of the second force transmission hub G211;
the second helicoidal mating part G24 is fixedly connected with a second force transmission hub G211; the second helicoidal mating piece G24 is located in the space formed by the second force transfer hub G211, the support body and the first helicoidal mating piece G23.
The support body and the first force transfer drum G221 act as the two force transfer ends of the overrunning clutch, respectively.
Example 4:
the B clutch is a friction plate type helical surface compression overrunning clutch, similar to the B clutch in embodiment 2 in structure, except that:
The first force transmission drum G221 is sleeved on the inner side of the second force transmission hub G211;
the second helicoidal mating part G24 is fixedly connected with the first force transmission drum G221; the second helicoidal partner G24 is located in the space formed by the first force transfer drum G221, the support body and the first helicoidal partner G23.
The support body and the second force transfer hub G211 serve as the two force transfer ends of the overrunning clutch, respectively.
FIG. 4 is a schematic diagram showing the assembly relationship between the formation of the helicoids and the two helicoidal mating members in the overrunning clutch according to embodiments 1 to 4; fig. 5 is a simplified schematic diagram of the structure principle of the overrunning clutch in the above embodiments 1 to 4, in which a pair of inclined planes are taken to represent the helicoid mating parts for illustration, in which the wedge block corresponds to the second helicoid mating part G24, in which the inclined planes correspond to the first helicoid mating part G23, and the direction of the acting force F is the circumferential direction. By modifying the structure of fig. 5, all the components are changed into a structure which is uniformly distributed along the circumference, and the combination of the overrunning clutch and the multi-plate wet clutch shown in fig. 3a and 3b (namely, the friction plate type circumferential spiral surface outer/inner compression overrunning clutch) is changed.
Fig. 6 is a schematic diagram of stress analysis of the overrun clutch in the above embodiments 1 to 4, in which a pair of helicoids are used to represent helicoids, the wedge block in the figure corresponds to the second helicoids G24, the inclined plane in the figure corresponds to the first helicoids G23, the inclined angle β of the inclined plane is the average helix angle of the effective contact portions of the helicoids of the two helicoids, F is the acting force of the overrun clutch in which the transmission torque of the overrun clutch is converted to the "average helix angle β", and the direction of F is the tangential direction of the acting point on the circumference. Fig. 6 (b) shows a force-bearing schematic diagram of a wedge block when the overrun clutch is locked, fig. 6 (c) shows a force-bearing schematic diagram of the wedge block when the overrun clutch is unlocked, f is a friction force obtained by converting friction torque between a second friction plate G212 of a rotating part and a first friction plate G222 of a fixed part which are alternately arranged to a circumference where an average helix angle beta is located, and a friction coefficient between friction pairs of the friction plates is mu; f 'is the friction force on the circumference where the friction torque between the screw-face mating parts is converted to the average helix angle beta, and the friction coefficient between the screw-face mating parts is mu'; n is a small value in the effective number of the first friction plate and the second friction plate, N is a positive pressure applied between the alternately arranged friction plates, and S is a positive pressure between mating surfaces of the helicoidal mating members.
For the lockup condition, the "average helix angle β" for the critical state is found using the following equation:
f＝μ×N
f'＝μ'×S
2(n-1)f+f-f'cosβ-S sinβ＝0
N-f'sinβ-S cosβ＝0
for the unlock condition, the "average helix angle β" for the critical state is found using the following equation:
f＝μ×N
f'＝μ'×S
f+f'cosβ-S sinβ＝0
N-f'sinβ-S cosβ＝0
therefore, the friction plate type circumferential cloth screw surface external/internal compression overrunning clutch screw surface matching part is self-locked, the screw surface matching part can be automatically unlocked, and the following conditions are satisfied:
Figure BDA0001190533040000151
in the following, a specific embodiment is used to explain that the torque can realize smooth transition in the gear shifting process.
Embodiment one: the structure and parameters of the second-speed device are as follows:
Figure BDA0001190533040000152
i 1 >1, a speed reducer;
Figure BDA0001190533040000153
the rotation direction of the input end and the input gear is clockwise (seen from the input end to the output end);
Figure BDA0001190533040000154
the clutch B adopts an overrunning clutch, the locking direction is anticlockwise, and the overrunning direction is clockwise;
Figure BDA0001190533040000155
the C clutch needs to adopt a plurality of wet clutches (the arrangement position is close to the input end), a driving component and a friction plate of the C clutch are connected with the input shaft to integrally and synchronously rotate, and a driven component and the friction plate of the C clutch are connected with the gear mechanism retainer assembly to integrally and synchronously rotate.
For convenience of explanation, the initial conditions are set first: the clutch B is in a locking state, the clutch C is in a separating state, and the transmitted friction torque M C =0, at which time the gear ratio is iThe torque relationship is:
M input device ＝M 11
M Output of ＝i*M 11
M Output of ＝M Input device +M B
In the middle of
M Input device -torque transmitted at the input;
M output of -torque transmitted at the output;
M 11 -torque transmitted on the input gear G11;
M B torque transmitted by the clutch (overrunning clutch);
M C torque transmitted by a-C clutch (multi-plate wet clutch);
when gear shifting is required, the C clutch starts to be slowly engaged, and the transmitted friction torque M C From small to maximum, the torque relationship during engagement is:
M input device -M C ＝M 11
M Output of ＝i*M 11
M Output of ＝M Input device +M B
Work as M C When the value of the sum is =0,
M output of ＝i*M Input device ，
M B ＝(i-1)*M Input device
Namely the initial working condition;
second part as M C When transmitted to maximum torque, i.e.
M B ＝0；
M Output of ＝M Input device ，
At the moment, according to the torque relation in the gear switching process, M is solved C The maximum torque transmitted is:
M C ＝(1-1/i)M input device
Thus, when M C From the following components
Figure BDA0001190533040000161
When the torque is changed, the output torque is increased by +.>
Figure BDA0001190533040000167
Figure BDA0001190533040000168
The gear is changed by the +.>
Figure BDA0001190533040000162
The gear ratio is 1, thereby realizing smooth transition of the gear shifting process.
Embodiment two:
the structure and parameters of the second gear transmission are as follows:
Figure BDA0001190533040000163
i<1, a speed increaser;
Figure BDA0001190533040000164
the direction of rotation of the input of the variator is clockwise (as viewed from the input to the output of the variator);
Figure BDA0001190533040000165
The clutch G2 adopts a common clutch;
Figure BDA0001190533040000166
the overrunning clutch G3 is adopted, the locking direction is clockwise, and the overrunning direction is anticlockwise, namely, when the driving component rotates clockwise relative to the driven component, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state;
for convenience of explanation, the initial conditions are set first: the B clutch G2 is in a disengaged state, the C clutch G3 is in a locked state, and at this time, the friction torque M transmitted by the B clutch G2 B =0, a transmission ratio of1, torque relationship is:
M input device ＝M Output of
When the gear is shifted, the B clutch G2 starts to be gradually engaged, and the friction torque M transmitted by the B clutch G2 B From small to maximum, the torque relationship during the switching process is:
M input device +M C ＝M 11
M Output of ＝i*M 11
M Output of ＝M Input device -M B
Work as M B When the value of the sum is =0,
M output of ＝M Input device ，
Namely, a gear with a transmission ratio of 1, namely, the initial working condition;
second part as M B When transmitting to maximum torque, i.e. M C =0, at this time, according to the torque relationship during gear shift, M is solved B The maximum torque transmitted is:
M B ＝(1-i)M input device
M Output of ＝i*M Input device
Thus, when M B From (1-i) M Input device When changing, the output torque is changed
Figure BDA0001190533040000171
The gear is changed by +.1 of the transmission ratio >
Figure BDA0001190533040000172
The gear with the ratio of i realizes smooth transition of the gear shifting process.
In addition, the invention adopts the double clutch structure, one clutch is separated during gear shifting, and the other clutch is synchronously engaged, so that the power is not interrupted in the gear shifting process. When one of the double clutches is an overrunning clutch and the other is a common clutch, only the common clutch is required to be controlled, the state of the overrunning clutch can be changed along with the common clutch, and the control is simple and convenient.

Claims (9)

1. A two speed device for providing a high speed ratio, comprising:
the second-speed device comprises an input shaft, an output shaft, a gear mechanism (G1), a C clutch (G3) and a B clutch (G2) which are arranged along the same axis;
the gear mechanism (G1) comprises an input gear (G11) fixedly arranged on an input shaft, a plurality of intermediate shaft gear assemblies, at least one transition gear assembly, an output gear (G14) and a gear retainer assembly which is formed by fixedly connecting a front retainer (G16) and a rear retainer (G17) and is provided with a cavity;
the intermediate shaft gear assembly comprises an intermediate shaft first gear (G12), an intermediate shaft second gear (G12 a), an intermediate shaft third gear (G13 a), an intermediate shaft fourth gear (G13), … … and an intermediate shaft Nth gear which are coaxially arranged on the intermediate shaft (G15) in parallel; the first gear and the second gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft 1-2 gear assembly, the third gear and the fourth gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft 3-4 gear assembly, … …, the (N-1) th gear and the N gear of the intermediate shaft are coaxially and fixedly connected to form an intermediate shaft (N-1) -N gear assembly; the intermediate shaft 1-2 gear assembly, the intermediate shaft 3-4 gear assembly, the … … and the intermediate shaft (N-1) -N gear assembly are rotatably arranged in a cavity between the front retainer (G16) and the rear retainer (G17) through the intermediate shaft (G15) and can rotate relatively; both ends of the intermediate shaft (G15) are supported by a front retainer (G16) and a rear retainer (G17);
The transition gear assembly comprises a first transition gear (G11 a), a second transition gear (G14 a), a … … and an M-th transition gear which are arranged between an input gear (G11) and an output gear (G14), wherein the first transition gear and the second transition gear are coaxially and fixedly connected to form a 1-2 transition gear assembly, the third transition gear and the fourth transition gear are coaxially and fixedly connected to form a 3-4 transition gear assembly, … …, an (M-1) th transition gear and an M transition gear are coaxially and fixedly connected to form an (M-1) -M transition gear assembly; an input gear (G11), a 1-2 transition gear assembly, a 3-4 transition gear assembly, … …, a (M-1) -M transition gear assembly and an output gear (G14), and a gear retainer assembly are coaxially arranged and can rotate relative to each other;
the input gear (G11) meshes with a plurality of intermediate shaft first gears (G12); the output gear (G14) is meshed with a plurality of intermediate shaft nth gears;
the first transition gear (G11 a), the second transition gear (G14 a), the … … and the M transition gear are respectively meshed with the plurality of intermediate shaft second gears (G12 a), the plurality of intermediate shaft third gears (G13 a), the … … and the plurality of intermediate shaft (N-1) th gears;
n=m+2, M being an even number;
the C clutch (G3) comprises a driving component (G31) and a driven component (G32); the driving component (G31) is fixedly connected with the input shaft, and the driven component (G32) is fixedly connected with the gear retainer assembly;
The B clutch (G2) comprises a rotating component (G21) and a fixed component (G22); the rotating component (G21) is fixedly connected with the gear retainer assembly, and the fixing component (G22) is fixedly connected with a shell (H) containing the second-speed device;
the B clutch (G2) and the C clutch (G3) can only be locked alternatively.
2. A two-speed apparatus according to claim 1, wherein: the m=2.
3. A secondary device as claimed in claim 1 or claim 2, wherein: the B clutch and the C clutch are all multi-plate wet clutches.
4. A secondary device as claimed in claim 1 or claim 2, wherein:
when the second speed device is a speed reducing device, the B clutch is an overrunning clutch or a multi-plate wet clutch, and for the overrunning clutch: when the rotating direction of the rotating component relative to the fixed component is consistent with the rotating direction of the input end of the second-speed device, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state; the C clutch is a multi-plate wet clutch;
when the second speed device is a speed increasing device, the C clutch is an overrunning clutch or a multi-plate wet clutch, and for the overrunning clutch: when the rotation direction of the driving component relative to the driven component is consistent with the rotation direction of the input end of the second-speed device, the overrunning clutch is in an overrunning state; conversely, the overrunning clutch is in a locking state; the B clutch is a multi-plate wet clutch.
5. A two-speed apparatus according to claim 1, wherein:
the clutch B is a friction plate type circumferential cloth spiral surface compression overrunning clutch and comprises a clutch limiting device, a fixed component (G22), a rotating component (G21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating shaft line;
the fixing assembly (G22) comprises a first force transmission drum (G221) and a plurality of first friction plates (G222) arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction;
the rotating assembly (G21) comprises a second force transmission hub (G211) and a plurality of second friction plates (G212) arranged outside the second force transmission hub, wherein the second friction plates can slide relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction;
the first force transmission drum (G221) is sleeved outside the second force transmission hub (G211);
a plurality of first friction plates (G222) and a plurality of second friction plates (G212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (G271) fixedly connected with an input shaft of the two-speed device and a check ring (G272) arranged on the supporting main body;
the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece (G23) and a second spiral surface matching piece (G24);
The first spiral surface matching piece (G23) is provided with a first spiral surface (G231); a second helicoidal surface (G241) matched with the first helicoidal surface is arranged on the second helicoidal surface matching piece (G24);
the first spiral surface matching piece (G23) is fixedly connected with the supporting main body, and the second spiral surface matching piece (G24) is fixedly connected with the second force transmission hub (G211); the second screw surface mating part is positioned between the supporting main body and the first screw surface mating part (G23), and the second screw surface mating part can perform screw sliding relative to the first screw surface mating part;
the supporting main body (G271) is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom of the supporting main body is an overhanging circular ring; the outer side surface of the neck of the support main body is provided with a check ring groove (G273) and a limit step (G274); the retainer ring (G272) is arranged in the retainer ring groove (G273); the retainer ring and the limit step are used for fixing the axial position of the first spiral surface matching piece (G23); the annular ring of the supporting body is used for limiting the axial positions of the first friction plate (G222) and the second friction plate (G212);
the additional clutch control device comprises an annular control cylinder arranged on the first force transmission drum (G221); the annular control oil cylinder comprises a cylinder body (G29) and a connecting main body (G30), and a pressure plate (G28) arranged between the cylinder body (G29) and the connecting main body (G30); the connecting main body (G30) is fixedly connected with the shell (H); the cross section of the pressure plate (G28) is approximately U-shaped; a plurality of springs (G25) are arranged between the bottom end surface of the pressure plate (G28) and the connecting main body (G30); one top of the pressure plate (G28) is accommodated in a cylinder body (G29), a piston (G26) forming an annular control oil cylinder is arranged, and a sealing oil Chamber (CYL) is formed between the piston (G26) and the cylinder body (G29); the other top end surface of the pressure plate (G28) is used for pressing the friction plate; the support body and the first force transfer drum serve as two force transfer ends of the overrunning clutch, respectively.
6. A two-speed apparatus according to claim 1, wherein: the clutch B is a friction plate type cloth spiral surface external compaction overrunning clutch and comprises a clutch limiting device, a fixed component (G22), a rotating component (G21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly (G22) comprises a first force transmission drum (G221) and a plurality of first friction plates (G222) arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction;
the rotating assembly (G21) comprises a second force transmission hub (G211) and a plurality of second friction plates (G212) arranged outside the second force transmission hub, wherein the second friction plates can slide relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction;
the first force transmission drum (G221) is sleeved outside the second force transmission hub (G211);
a plurality of first friction plates (G222) and a plurality of second friction plates (G212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (G271) fixedly connected with the shell (H); the supporting body is of a circular ring structure and is used for limiting the axial positions of the first friction plate and the second friction plate;
The self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece (G23) and a second spiral surface matching piece (G24);
a plurality of first helicoids (G231) are arranged on the matching surface of the first helicoid matching piece (G23); a plurality of second helicoids (G241) matched with the first helicoids are arranged on the matching surface of the second helicoid matching piece (G24);
the first spiral surface matching piece (G23) is fixedly connected with the supporting main body, and the second spiral surface matching piece (G24) is fixedly connected with the first force transmission drum (G221); the second helicoidal piece is positioned between the supporting body and the first helicoidal piece (G23), and the second helicoidal piece slides helically with respect to the first helicoidal piece;
the additional clutch control device comprises an annular cylinder body arranged on the shell (H), a piston (G26) arranged in the annular cylinder body, and a plurality of springs (G25) arranged between the second spiral surface matching part (G24) and the piston (G26); the end surfaces of the springs are arranged on the pistons and face the first friction plate (G222) at the same time; a sealing oil Chamber (CYL) is formed between the other end surface of the piston and the annular cylinder body; the support body and the second force transfer hub serve as two force transfer ends of the overrunning clutch, respectively.
7. The secondary device of claim 4 wherein: the overrun clutch is a friction plate type circumferential cloth spiral surface compression overrun clutch and comprises a clutch limiting device, a fixed component (G22) and a rotating component (G21), a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating shaft line;
the fixing assembly (G22) comprises a first force transmission drum (G221) and a plurality of first friction plates (G222) arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction;
the rotating assembly (G21) comprises a second force transmission hub (G211) and a plurality of second friction plates (G212) arranged outside the second force transmission hub, wherein the second friction plates can slide relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction;
the first force transmission drum (G221) is sleeved on the inner side of the second force transmission hub (G211);
a plurality of first friction plates (G222) and a plurality of second friction plates (G212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (G271) fixedly connected with the input shaft of the second-speed device and a check ring (G272) arranged on the supporting main body;
the self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece (G23) and a second spiral surface matching piece (G24);
The first spiral surface matching piece (G23) is provided with a first spiral surface (G231); a second spiral surface (G241) matched with the first spiral surface is arranged on the second spiral surface matching part (G24);
the first spiral surface matching piece (G23) is fixedly connected with the supporting main body, and the second spiral surface matching piece (G24) is fixedly connected with the first force transmission drum (G221); the second helicoidal piece is positioned between the supporting body and the first helicoidal piece (G23), and the second helicoidal piece slides helically with respect to the first helicoidal piece;
the supporting main body (G271) is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom of the supporting main body is an overhanging circular ring; the outer side surface of the neck of the support main body is provided with a check ring groove (G273) and a limit step (G274); the retainer ring (G272) is arranged in the retainer ring groove (G273); the retainer ring (G272) and the limiting step (G274) are used for fixing the axial position of the first spiral surface matching piece (G23); the annular ring of the supporting body is used for limiting the axial positions of the first friction plate (G222) and the second friction plate (G212);
the additional clutch control device comprises an annular control cylinder arranged on the first force transmission drum (G221); the annular control oil cylinder comprises a cylinder body (G29) and a connecting main body (G30), and a pressure plate (G28) arranged between the cylinder body (G29) and the connecting main body (G30); the connecting main body (G30) is fixedly connected with the shell (H); the cross section of the pressure plate (G28) is approximately U-shaped; a plurality of springs (G25) are arranged between the bottom end surface of the pressure plate (G28) and the connecting main body (G30); one top of the pressure plate (G28) is accommodated in a cylinder body (G29), a piston (G26) forming an annular control oil cylinder is arranged, and a sealing oil Chamber (CYL) is formed between the piston (G26) and the cylinder body (G29); the other top end surface of the pressure plate (G28) is used for pressing the friction plate; the support body and the second force transfer hub serve as two force transfer ends of the overrunning clutch, respectively.
8. The secondary device of claim 4 wherein: the overrun clutch is a friction plate type cloth spiral surface external compaction overrun clutch and comprises a clutch limiting device, a fixed component (G22), a rotating component (G21), a self-locking/overrun control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly (G22) comprises a first force transmission drum (G221) and a plurality of first friction plates (G222) arranged in the first force transmission drum, wherein the first friction plates can slide relative to the first force transmission drum along the axial direction and rotate synchronously with the first force transmission drum along the circumferential direction;
the rotating assembly (G21) comprises a second force transmission hub (G211) and a plurality of second friction plates (G212) arranged outside the second force transmission hub, wherein the second friction plates can slide relative to the second force transmission hub along the axial direction and rotate synchronously with the second force transmission hub along the circumferential direction;
the first force transmission drum (G221) is sleeved on the inner side of the second force transmission hub (G211);
a plurality of first friction plates (G222) and a plurality of second friction plates (G212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (G271) fixedly connected with the shell (H); the supporting body is of a circular ring structure and is used for limiting the axial positions of the first friction plate and the second friction plate;
The self-locking/overrunning control device is used for controlling the engagement and disengagement of the first friction plate and the second friction plate and comprises a first spiral surface matching piece (G23) and a second spiral surface matching piece (G24);
the first spiral surface matching piece (G23) is provided with a first spiral surface (G231); a second helicoidal surface (G241) matched with the first helicoidal surface is arranged on the second helicoidal surface matching piece (G24);
the first spiral surface matching piece (G23) is fixedly connected with the supporting main body, and the second spiral surface matching piece (G24) is fixedly connected with the second force transmission hub (G211); the second helicoidal piece is positioned between the supporting body and the first helicoidal piece (G23), and the second helicoidal piece slides helically with respect to the first helicoidal piece;
the additional clutch control device comprises an annular cylinder body arranged on the shell (H), a piston (G26) arranged in the annular cylinder body, and a plurality of springs (G25) arranged between the second spiral surface matching part (G24) and the piston (G26); the end surfaces of the springs are arranged on the pistons and face the first friction plate (G222) at the same time; a sealing oil Chamber (CYL) is formed between the other end surface of the piston and the annular cylinder body; the support body and the first force transfer drum serve as two force transfer ends of the overrunning clutch, respectively.
9. A secondary device as claimed in claim 5, 6, 7 or 8, wherein: the first spiral surface matching piece, the second spiral surface matching piece, the first friction plate and the second friction plate meet the following conditions:
Figure FDA0004027527090000071
Wherein, beta is the average helix angle of the effective contact part of the helicoids of the two helicoids of the matching parts;
mu is the friction coefficient between the friction pair of the first friction plate and the second friction plate;
μ' is the coefficient of friction between the two helicoidal mating parts;
n is a small value in the effective number of the first friction plate and the second friction plate.
CN201611208725.5A 2016-12-23 2016-12-23 Two-speed device capable of providing large speed ratio Active CN106594191B (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1749602A (en) * 2004-09-18 2006-03-22 杨斌彬 Uniterrupted power gear box
CN102155521A (en) * 2010-02-11 2011-08-17 宁波宏协离合器有限公司 Planetary gear mechanism and mechanical speed changer comprising same
CN104019208A (en) * 2014-05-12 2014-09-03 韩文明 Speed change device with hydraulic control mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1749602A (en) * 2004-09-18 2006-03-22 杨斌彬 Uniterrupted power gear box
CN102155521A (en) * 2010-02-11 2011-08-17 宁波宏协离合器有限公司 Planetary gear mechanism and mechanical speed changer comprising same
CN104019208A (en) * 2014-05-12 2014-09-03 韩文明 Speed change device with hydraulic control mechanism
WO2015172655A1 (en) * 2014-05-12 2015-11-19 韩文明 Speed change device with hydraulic manipulation mechanism

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