CN106594202B - Three-speed change gear - Google Patents
Three-speed change gear Download PDFInfo
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- CN106594202B CN106594202B CN201611207915.5A CN201611207915A CN106594202B CN 106594202 B CN106594202 B CN 106594202B CN 201611207915 A CN201611207915 A CN 201611207915A CN 106594202 B CN106594202 B CN 106594202B
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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
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
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- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
A three-speed transmission comprises a gear mechanism and C, B and D clutches which are arranged along the same axis; the gear mechanism comprises an input gear, a plurality of intermediate shaft gear assemblies, an output gear and a gear retainer assembly which is composed of a front retainer, a middle retainer and a rear retainer and is provided with two cavities; the input gear, the gear retainer assembly and the output gear are coaxially arranged and can rotate relatively; the middle part of the middle retainer is provided with a central output shaft as a first power output end; a central output shaft tube is coaxially sleeved outside the central output shaft and serves as a power output end II; a driving component of the clutch C is fixedly connected with the input shaft, and a 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 the shell of the speed change device; the D clutch is used for switching two outputs of the gear mechanism; B. the C clutch and the D clutch can only be selected to be locked. The invention has simple structure, low requirement on processing precision and convenient design and manufacture.
Description
Technical Field
The present invention relates to a gear change device applied to a vehicle transmission.
Background
There are two types of existing gear change mechanisms: fixed shaft type and planetary gear type.
As shown in FIGS. 1a and 1b, a schematic diagram of a prior art planetary gear type transmission is shown, which is composed of three planetary rows each including a gear P 1 Planet wheel P 2 Ring gear P 3 And a planetary carrier P 4 Three planetary rows combined together by three clutches C 1 、C 2 、C 3 And three braking bands B 1 、B 2 、B 3 In addition to the cooperation of the one-way clutch F, the gear P of each planetary row can be connected 1 Ring gear P 3 And a planet carrier P 4 The gear combination is respectively used as a driving part, a driven part or a fixing part, so that a plurality of gears can be combined. The hydraulic torque converter is often used in combination with the transmission in front of the transmission, so that the gear shifting can be carried out without cutting off the power of an engine, but the transmission efficiency is low; the related components of one planet row of the planetary gear transmission are mutually connected and nested with the related components of the other planet row, so that the whole transmission is very complex in structure and difficult to arrange, great difficulty is brought to manufacturing and maintenance, and particularly, a hobbing processing method cannot be adopted for processing a gear ring, so that the processing efficiency is low, the precision is poor, and the cost is high.
Disclosure of Invention
The invention provides a three-speed change device, aiming at solving the problems of complex structure and low processing efficiency of the existing gear speed change device.
The technical solution of the invention is as follows:
a three-speed transmission having an input and two outputs; it is characterized in that:
the three-speed change device comprises a gear mechanism T1, a C clutch T3, a B clutch T2 and a D clutch T4 which are arranged along the same axis;
the gear mechanism T1 comprises an input gear T11 fixedly arranged on an input shaft, a plurality of intermediate shaft gear assemblies consisting of an intermediate shaft T15, an intermediate shaft first gear T12 and an intermediate shaft second gear T13, an output gear T14 and a gear retainer assembly with two cavities, wherein the gear retainer assembly is formed by sequentially and fixedly connecting a front retainer T16, an intermediate retainer T18 and a rear retainer T17;
the input gear T11, the gear retainer assembly and the output gear T14 are coaxially arranged and can rotate relatively;
a central output shaft T19 is arranged in the middle of the middle retainer T18, one end of the central output shaft T19 is coaxially arranged side by side with the input shaft and can rotate relatively, and the other end of the central output shaft T19 is a power output end of the speed change device;
a central output shaft tube T20 capable of rotating relatively is coaxially sleeved outside the central output shaft T19, one end of the central output shaft tube T20 is fixedly connected with the output end of the output gear T14, and the other end of the central output shaft tube T20 is the other power output end of the speed change device;
the input gear T11 and the plurality of countershaft first gears T12 are engaged and are all located in a cavity between the front cage T16 and the middle cage T18, and the output gear T14 and the plurality of countershaft second gears T13 are engaged and are all located in a cavity between the rear cage T17 and the middle cage T18; the intermediate shaft first gear T12 and the intermediate shaft second gear T13 are coaxially fixed side by side and rotatably mounted in a cavity of the gear retainer assembly through the intermediate shaft T15, the intermediate shafts T15 penetrate through the intermediate retainer T18, and two ends of each intermediate shaft T15 are supported by the front retainer T16 and the rear retainer T17;
the C clutch T3 comprises a driving component T31 and a driven component T32; the driving component T31 is fixedly connected with the input shaft, and the driven component T32 is fixedly connected with the gear retainer assembly;
the B clutch T2 comprises a rotating component T21 and a fixed component T22; the rotating component T21 is fixedly connected with the gear retainer assembly, and the fixed component T22 is fixedly connected with a shell H containing the three-speed change device;
the D clutch T4 is arranged at the output end of the gear mechanism T1 and is used for switching the output of the gear mechanism T1; the D clutch T4 includes a second rotating component T41 and a second fixed component T42; the second rotating component T41 is fixedly connected with the central output shaft tube T20, and the second fixing component T42 is fixedly connected with a housing H containing the three-speed transmission;
the B clutch T2, the C clutch T3 and the D clutch T4 can be locked by one clutch.
Based on the basic technical scheme, the invention also optimizes and/or defines the following steps:
the housing H includes a front housing support and a rear housing support; the front housing supports an input end at the transmission; the rear housing support is located between the gear mechanism T1 and the B clutch T2, or between the B clutch T2 and the D clutch T4.
Types of the respective clutches in the three-speed transmission described above:
(1) The clutch B and the clutch C can adopt a multi-plate wet clutch.
(2) When the three-speed transmission device is a speed reduction device, the clutch B adopts 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; otherwise, the overrunning clutch is in a locking state; the C clutch adopts a multi-plate wet clutch.
In order to realize the smooth transition of torque in the gear shifting process, the overrunning clutch can be a friction plate type peripheral helical surface pressing overrunning clutch, and the overrunning clutch mainly has the following forms:
the 1 st:
the overrunning clutch is a friction plate type circumferentially distributed helical surface internal compression overrunning clutch and comprises a clutch limiting device, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly T22 comprises a first force transfer drum T221 and a plurality of first friction plates T222 arranged in the first force transfer drum, the first friction plates being axially slidable relative to the first force transfer drum and being circumferentially rotatable in synchronism;
the rotating assembly T21 comprises a second force transmission hub T211 and a plurality of second friction plates T212 arranged outside the second force transmission hub, and the second friction plates can slide relatively to the second force transmission hub along the axial direction and rotate synchronously along the circumferential direction;
the first force transfer drum T221 is sleeved outside the second force transfer hub T211;
the plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction;
the clutch limiting device comprises a support body T271 fixedly connected with an input shaft of the speed change device and a retainer ring T272 arranged on the support body;
the self-locking/overrunning control device is used for controlling the opening and closing of the first friction plate and the second friction plate and comprises a first spiral surface coupling part T23 and a second spiral surface coupling part T24;
a first helicoid T231 is arranged on the first helicoid matching part T23; a second helicoid T241 matched with the first helicoid is arranged on the second helicoid matching part T24;
the first helicoid couple T23 is fixedly connected with the support main body, and the second helicoid couple T24 is fixedly connected with the second force transmission hub T211; the second helicoidal couple is located between the support body and the first helicoidal couple T23, and the second helicoidal couple can make spiral slip relatively to said first helicoidal couple;
the support main body is of a circular ring structure with a neck, the neck of the support main body is a hollow cylinder, and the bottom of the support main body is an outward extending circular ring; a stop ring groove and a limit step are arranged on the outer side surface of the neck of the support main body; the retainer ring is arranged in the retainer ring groove; the retainer ring and the limiting step are used for fixing the axial position of the first helical surface coupling part T23; the annular ring of the support body serves to limit the axial positions of the first and second friction plates T222 and T212;
the additional clutch control device comprises an annular control oil cylinder arranged on the first force transmission drum T221; the annular control oil cylinder comprises a cylinder body T29, a connecting main body T30 and a pressure plate T28 arranged between the cylinder body T29 and the connecting main body T30; the connecting main body T30 is fixedly connected with the shell H; the cross section of the platen T28 is approximately U-shaped; a plurality of springs T25 are arranged between the bottom end surface of the pressure plate T28 and the connecting main body T30; one top of the pressure plate T28 is accommodated in a cylinder T29, a piston T26 of an annular control oil cylinder is formed, and a sealing oil chamber CYL is formed between the piston T26 and the cylinder T29; the other top end surface of the pressure plate T28 is used for pressing friction plates;
the support body and the first force transmission drum are respectively used as two force transmission ends of the clutch.
The 2 nd:
the overrunning clutch is a friction plate type circumferentially distributed helicoid external-pressing overrunning clutch and comprises a clutch limiting device, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly T22 comprises a first force transfer drum T221 and a plurality of first friction plates T222 arranged in the first force transfer drum, the first friction plates being axially slidable relative to the first force transfer drum and being circumferentially rotatable in synchronism;
the rotating assembly T21 comprises a second force transmission hub T211 and a plurality of second friction plates T212 arranged outside the second force transmission hub, and the second friction plates can slide relatively to the second force transmission hub along the axial direction and rotate synchronously along the circumferential direction;
the first force transmission drum T221 is sleeved outside the second force transmission hub T211;
the plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body fixedly connected with the shell H; the supporting main 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 opening and closing of the first friction plate and the second friction plate and comprises a first helical surface coupling part T23 and a second helical surface coupling part T24;
a first helicoid T231 is arranged on the first helicoid matching part T23; a second helicoid T241 matched with the first helicoid is arranged on the second helicoid matching part T24;
the first helicoid couple T23 is fixedly connected with the support main body, and the second helicoid couple T24 is fixedly connected with the first power transmission drum T221; the second helicoidal couple is located between the support body and the first helicoidal couple T23, and it slides spirally with respect to said first helicoidal couple;
the additional clutch control device comprises an annular cylinder arranged on the shell H, a piston T26 arranged in the annular cylinder, and a plurality of springs T25 arranged between the second helical surface coupling piece T24 and the piston T26; the end face of the piston provided with a plurality of springs simultaneously faces the first friction plate T222; a sealed 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 transmission hub are respectively used as two force transmission ends of the clutch.
And (3) type:
the overrunning clutch is a friction plate type circumferentially distributed helical surface internal compression overrunning clutch and comprises a clutch limiting device, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly T22 comprises a first force transfer drum T221 and a plurality of first friction plates T222 arranged in the first force transfer drum, the first friction plates being axially slidable relative to the first force transfer drum and being circumferentially rotatable in synchronism;
the rotating assembly T21 comprises a second force transmission hub T211 and a plurality of second friction plates T212 arranged outside the second force transmission hub, and the second friction plates can slide relatively to the second force transmission hub along the axial direction and rotate synchronously along the circumferential direction;
the first force transfer drum T221 is sleeved on the inner side of the second force transfer hub T211;
the plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction;
the clutch limiting device comprises a support body T271 fixedly connected with an input shaft of the speed change device and a retainer ring T272 arranged on the support body;
the self-locking/overrunning control device is used for controlling the opening and closing of the first friction plate and the second friction plate and comprises a first helical surface coupling part T23 and a second helical surface coupling part T24;
a first helicoid T231 is arranged on the first helicoid matching part T23; a second helicoid T241 matched with the first helicoid is arranged on the second helicoid matching part T24;
the first helicoid couple T23 is fixedly connected with the support main body, and the second helicoid couple T24 is fixedly connected with the first power transmission drum T221; the second helicoidal couple is located between the support body and the first helicoidal couple T23, and it slides spirally with respect to said first helicoidal couple;
the support main body is of a neck-provided circular ring structure, the neck of the support main body is a hollow cylinder, and the bottom of the support main body is an outward extending circular ring; a retainer groove and a limiting step are arranged on the outer side surface of the neck of the support main body; the retainer ring is arranged in the retainer ring groove; the retainer ring and the limiting step are used for fixing the axial position of the first helical surface coupling part T23; the annular ring of the support body serves to limit the axial positions of the first and second friction plates T222 and T212;
the additional clutch control device comprises an annular control oil cylinder arranged on the first force transmission drum T221; the annular control oil cylinder comprises a cylinder body T29, a connecting main body T30 and a pressure plate T28 arranged between the cylinder body T29 and the connecting main body T30; the connecting main body T30 is fixedly connected with the shell H; the cross section of the platen T28 is approximately U-shaped; a plurality of springs T25 are arranged between the bottom end surface of the pressure plate T28 and the connecting main body T30; one top of the pressure plate T28 is accommodated in a cylinder T29, a piston T26 of an annular control oil cylinder is formed, and a sealing oil chamber CYL is formed between the piston T26 and the cylinder T29; the other top end surface of the pressure plate T28 is used for pressing friction plates;
the support body and the second force transmission hub are respectively used as two force transmission ends of the clutch.
And 4, the method comprises the following steps:
the overrunning clutch is a friction plate type peripheral helical surface external pressing overrunning clutch and comprises a clutch limiting device, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing assembly T22 comprises a first force transfer drum T221 and a plurality of first friction plates T222 arranged in the first force transfer drum, the first friction plates being axially slidable relative to the first force transfer drum and being circumferentially rotatable in synchronism;
the rotating assembly T21 comprises a second force transmission hub T211 and a plurality of second friction plates T212 arranged outside the second force transmission hub, and the second friction plates can slide relatively to the second force transmission hub along the axial direction and rotate synchronously along the circumferential direction;
the first force transfer drum T221 is sleeved on the inner side of the second force transfer hub T211;
the plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction;
the clutch limiting device comprises a support main body fixedly connected with the shell H; the supporting main 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 opening and closing of the first friction plate and the second friction plate and comprises a first spiral surface coupling part T23 and a second spiral surface coupling part T24;
a first helicoid T231 is arranged on the first helicoid matching part T23; a second helicoid T241 matched with the first helicoid is arranged on the second helicoid matching part T24;
the first helicoid couple T23 is fixedly connected with the support main body, and the second helicoid couple T24 is fixedly connected with the second force transmission hub T211; the second helicoidal couple is located between the support body and the first helicoidal couple T23, and it slides spirally with respect to said first helicoidal couple;
the additional clutch control device comprises an annular cylinder arranged on the shell H, a piston T26 arranged in the annular cylinder, and a plurality of springs T25 arranged between the second helical surface coupling piece T24 and the piston T26; the end face of the piston provided with a plurality of springs simultaneously faces the first friction plate T222; 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 respectively serve as two force transfer ends of the clutch.
In order to enable the helical surface coupling part of the friction plate type peripheral cloth helical surface pressing overrunning clutch to be self-locked and automatically unlocked, the first helical surface coupling part, the second helical surface coupling part, the first friction plate and the second friction plate meet the following conditions:
wherein β is the average helix angle of the helicoidal effective contact portions of the two helicoidal couples;
mu is the friction coefficient between the first friction plate and the second friction plate;
mu' is the friction coefficient between the spiral surfaces of the two spiral surface coupling parts;
n is the small value in the effective number of the first friction plate and the second friction plate.
The invention has the advantages that:
1. the gear mechanism in the speed change device adopts the common cylindrical gear, and compared with the existing planetary gear speed changer, the gear ring is cancelled, so that the complex nesting between the planetary gear and the related components of the planetary gear is avoided, the defects of complex structure and difficult processing of the related components of the planetary gear mechanism are overcome, the structure is simple, the requirement on processing precision is low, and the design and the manufacture are convenient; in addition, compared with the existing fixed shaft type gear speed change device, the gear shift control mechanism is easier to arrange and more gears are easier to realize.
2. The invention adopts the cooperation of the common clutch and the overrunning clutch, only the common clutch needs to be controlled when the gear shifting device is used, the overrunning clutch can change along with the state change of the common clutch, when one clutch is loosened, the other clutch is jointed, thereby realizing the uninterrupted power during the gear shifting.
3. The overrunning clutch adopts the friction plate type peripheral helical surface to press the overrunning clutch, so that the output torque of the previous gear is gradually changed to the output torque of the next gear during gear shifting, namely, the smooth transition of the output torque in the gear shifting process can be realized.
4. Compared with the traditional speed change module and a speed changer, the speed change module does not need to calibrate the control of an engine and strictly control the output of the torque of the engine.
Drawings
FIG. 1a is a schematic diagram of a basic structure of a prior art planetary gear mechanism;
FIG. 1b is a schematic illustration of a prior art planetary transmission;
FIG. 2 is a schematic structural view of the three speed transmission of the present invention;
FIG. 3 is a schematic structural diagram of an embodiment of the three speed transmission of the present invention;
FIG. 3a is an assembled cross-sectional view of a first embodiment of the clutch B (overrunning clutch) of FIG. 3;
FIG. 3B is an assembled cross-sectional view of the second embodiment of the clutch (overrunning clutch) B of FIG. 3;
FIG. 4 is a schematic diagram of the relationship between helicoid formation and helicoid assembly of a helicoid assembly of an overrunning clutch embodying the present invention;
FIG. 5 is a simplified schematic diagram of the structural principle of a friction plate type circumferentially distributed helicoid compression overrunning clutch;
FIG. 6 is a force analysis diagram of the overrunning clutch employed in the present invention.
Detailed Description
As shown in fig. 2, the three-speed transmission according to the present invention includes an input shaft, a gear mechanism T1, a B clutch T2, a C clutch T3, a D clutch T4, an output shaft T19, and an output shaft tube T20.
1. Gear mechanism
The gear mechanism T1 comprises an input gear T11, a plurality of groups of intermediate shaft gear assemblies (respectively composed of an intermediate shaft first gear T12, an intermediate shaft second gear T13 and an intermediate shaft T15) which are uniformly distributed along the circumference, an output gear T14 and a gear retainer assembly (composed of a front retainer component T16, an intermediate retainer component T18 and a rear retainer component T17 which are sequentially and fixedly connected) with two cavities.
The input gear T11, the gear cage assembly and the output gear T14 have coincident rotational axes and are capable of relative rotation therebetween.
A central output shaft T19 is arranged in the middle of the middle retainer T18, one end of the central output shaft T19 is coaxially arranged side by side with the input shaft and can rotate relatively, and the other end of the central output shaft T19 is connected with the adapter DR; the central output shaft T19 serves as a second power output of the gear mechanism T1, i.e., a second output of the three-speed transmission;
the central output shaft T19 is coaxially sleeved with a central output shaft tube T20 capable of rotating relatively, one end of the central output shaft tube T20 is fixedly connected with the output end of the output gear T14, and the other end is a first power output end of the gear mechanism T1, i.e., a first output end of the three-speed transmission.
2. B, C, D clutch
The B clutch T2 comprises a rotating component T21 and a fixed component T22; the rotating component T21 is fixedly connected with the gear retainer assembly, and the fixed component T22 is fixedly connected with the shell H.
The C clutch T3 comprises a driving component T31 and a driven component T32; the driving component T31 is fixedly connected with the input shaft, and the driven component T32 is fixedly connected with the gear retainer assembly.
The D clutch T4 is arranged at the output end of the gear mechanism T1 and is used for switching the output of the gear mechanism T1; the D clutch T4 includes a second rotating component T41 and a second fixed component T42; the second rotating assembly T41 is fixedly connected with the central output shaft tube T20, and the second fixing assembly T42 is fixedly connected with the housing H.
The B clutch T2, the C clutch T3 and the D clutch T4 can only be locked alternatively.
3. Working process
The working process of the invention is divided into three working conditions:
(1) when the B clutch T2 is engaged, the C clutch T3 is disengaged, and the D clutch T4 is disengaged, the power transmission route is: input → input gear T11 → intermediate shaftFirst gear T12 → intermediate shaft second gear T13 → output gear T14 → first output end. The transmission ratio is i T The rotation direction of the output end is the same as that of the input end.
(2) When the B clutch T2 is disengaged, the C clutch T3 is engaged, and the D clutch T4 is disengaged, the power transmission route is: input → entire gear mechanism (as a rigid body) → first output. The transmission ratio is 1, and the rotation direction of the output end is the same as that of the input end.
(3) When the clutch B T2 is disengaged, the clutch C T3 is disengaged, and the clutch D T4 is engaged, the power transmission route is: input → input gear T11 → intermediate shaft assembly (gears T12, T13) → intermediate shaft T15 → gear cage assembly (T16, T17, T18) → central output shaft T19 → second output. The transmission ratio is (1-i) T ) The symbol is "+" indicating that the direction of rotation is the same as the direction of rotation of the input end; the symbol "-" indicates that the direction of rotation is opposite to that of the input.
4. Selection of the design of a clutch in a transmission
As shown in fig. 3, the clutch B adopts a friction plate type helical surface pressing overrunning clutch, and the clutch C adopts a multi-plate wet clutch (a conventional common 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 helicoidal external pressing overrunning clutch and comprises a clutch limiting device T27, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis.
The fixing assembly T22 includes a first force transfer drum T221 and a plurality of first friction plates T222 provided on the first force transfer drum T221, the first friction plates T222 being relatively slidable in the axial direction with respect to the first force transfer drum T221, the first friction plates T222 rotating in the circumferential direction in synchronization with the first force transfer drum T221.
The rotating assembly T21 includes a second force transmission hub T211 and a plurality of second friction plates T212 disposed outside the second force transmission hub T211, the second friction plates T212 can slide relative to the second force transmission hub T211 in the axial direction, and the second friction plates T212 and the second force transmission hub T211 rotate synchronously in the circumferential direction.
The first force transmission drum T221 is sleeved outside the second force transmission hub T211; a step T223 and a baffle T224 which limit the axial position of the first friction plate T222 are also arranged on one end surface of the first force transmission drum T221; the step T223 blocks the stopper T224 to restrict it from sliding out of the end of the first transfer drum T221; the stopper plate T224 serves to limit the axial position of the first friction plate T222 and prevent the first friction plate T222 from slipping out of the first force-transmitting drum T221.
The plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction.
The clutch limiting device comprises a supporting main body T271 fixedly connected with the shell H; the support body T271 has a circular ring structure for limiting the axial positions of the first friction plate T222 and the second friction plate T212;
the self-locking/overrunning control device is used for controlling the engagement and the disengagement of the first friction plate T222 and the second friction plate T212 and comprises a first helical surface coupling part T23 and a second helical surface coupling part T24. A plurality of first helicoids T231 are arranged on the matching surface of the first helicoid matching part T23; a plurality of second helicoids T241 matched with the first helicoids T231 are arranged on the matching surface of the second helicoid matching part T24; the direction of rotation of the first and second helical surfaces T231, T241 is related to the direction in which the clutch transmits torque:
referring to fig. 3a, when a torque is applied to the second force transmission hub T211, and the second force transmission hub T211 tends to rotate clockwise relative to the support body T271 under the action of the torque, when the first helical surface T231 and the second helical surface T241 rotate clockwise, the overrunning clutch is in an overrunning state under the action of the torque; if the first and second spiral surfaces T231 and T241 are rotated left, the overrunning clutch is in a locked state under the action of the torque, and the torque on the second force transmission hub T211 is transmitted to the support main body through the second friction plate T212, the first friction plate T222, the first force transmission drum T221 fixedly connected with the second spiral surface coupling member T24, and the first spiral surface coupling member T23.
The first helicoid couple T23 is fixedly connected with the support main body T271, and the second helicoid couple T24 is fixedly connected with the first transmission drum T221; the second helicoidal couple T24 is located in the space formed by the first transfer drum T221, the support body T271 and the first helicoidal couple T23, and the second helicoidal couple T24 is capable of sliding spirally with respect to the first helicoidal couple T23.
The support body T271 and the second force transmitting hub T211 act as the two force transmitting ends of the clutch, respectively.
The additional clutch control device comprises an annular cylinder arranged on the shell H, a piston T26 arranged in the annular cylinder, and a plurality of springs T25 arranged between the second helical surface coupling piece T24 and the piston T26; the end face of the piston provided with a plurality of springs is simultaneously opposite to the first friction plate T222; and a sealing oil chamber CYL is formed between the other end surface of the piston and the annular cylinder body.
The working principle is as follows:
when the sealed oil chamber CYL is filled with oil, the hydraulic thrust overcomes the spring force of the spring T25 to press the piston T26 to the friction plate, and the clutch B is an overrunning clutch and a multi-plate wet clutch in an engaging state: when the clutch accords with the overrunning condition, the clutch enters the overrunning working condition, and transmits torque even under the overrunning working condition, the magnitude of the transmitted torque is the same as that of a multi-plate wet clutch, and the transmitted torque = positive pressure on a friction surface multiplied by an equivalent friction coefficient; when the clutch is in line with the locking condition, the clutch enters the locking working condition, when the transmitted torque is large enough, the friction force between the friction plates forms friction torque to drive the second spiral surface coupling piece T24 to further rotate towards the locking direction, even if the piston T26 is pressed back to the pressure relief position of the oil cylinder CYL, at the moment, even if the oil cylinder is depressurized, the spring T25 cannot press back the second spiral surface coupling piece T24, and the limit value of the transmitted torque is the strength limit of the part.
When the sealed oil chamber CYL releases the pressure, the first spiral surface coupling piece T23 and the second spiral surface coupling piece T24 are in an unlocking state, the piston T26 returns by the spring force of the spring T25, namely, the piston T26 moves towards the direction far away from the friction plate, the clutch B is in a separation state at the moment, and the torques are not transmitted in two rotation directions.
Example 2:
as shown in fig. 3B, the clutch B is a friction plate type helical surface pressing overrunning clutch, and includes a clutch limiting device T27, a fixed component T22, a rotating component T21, a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotation axis.
The fixing assembly T22 includes a first force-transmitting drum T221 and a plurality of first friction plates T222 provided on the first force-transmitting drum T221, the first friction plates T222 being relatively slidable in the axial direction with respect to the first force-transmitting drum T221, and the first friction plates T222 being rotatable in the circumferential direction in synchronism with the first force-transmitting drum T221.
The rotating assembly T21 includes a second force transmission hub T211 and a plurality of second friction plates T212 disposed outside the second force transmission hub T211, the second friction plates T212 can slide relative to the second force transmission hub T211 in the axial direction, and the second friction plates T212 and the second force transmission hub T211 rotate synchronously in the circumferential direction.
The first force transmission drum T221 is sleeved outside the second force transmission hub T211; the plurality of first friction plates T222 and the plurality of second friction plates T212 are alternately arranged in the axial direction.
The self-locking/overrunning control device is used for controlling the engagement and the disengagement of the first friction plate T222 and the second friction plate T212 and comprises a first helical surface coupling part T23 and a second helical surface coupling part T24. A plurality of first helicoids T231 are arranged on the matching surface of the first helicoid matching part T23; a plurality of second helicoids T241 matched with the first helicoids T231 are arranged on the matching surface of the second helicoid matching piece T24; the direction of rotation of the first and second helical surfaces T231, T241 is related to the direction in which the clutch transmits torque:
referring to fig. 3b, when a torque is applied to the support body T271, and the support body T271 tends to rotate clockwise with respect to the first power transfer drum T221 (which is an outer drum) when viewed from left to right in the illustrated position, if the first helical surface T231 and the second helical surface T241 rotate rightwards, the overrunning clutch is in an overrunning state under the torque; if the first and second spiral surfaces T231 and T241 are rotated to the left, the overrunning clutch is in a locked state under the action of the torque, and the torque on the support body T271 is transmitted to the outside through the first spiral surface coupling T23, the second force transmission hub T211 (inner hub) fixedly connected to the second spiral surface coupling T24, the second friction plate T212, the first friction plate T222, and the first force transmission drum T221 (outer drum).
The clutch limiting device comprises a support body T271 and a check ring T272 which are fixedly connected with an input shaft of the speed change device; the support body T271 is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom is an outward extending circular ring; a retainer groove T273 and a limit step T274 are formed in the outer side face of the neck of the support main body; the retainer ring T272 is arranged in the retainer ring groove T273; the retainer ring T272 and the limit step T274 are used for fixing the axial position of the first helical surface coupling piece T23; the annular ring of the support body serves to limit the axial position of the first and second friction plates T222 and T212.
The second helicoid matching part T24 is fixedly connected with a second force transmission hub T211; the second helicoidal couple T24 is located in the space formed by the second force-transmitting hub T211, the support body T271 and the first helicoidal couple T23.
The support body T271 and the first power transmission drum T221 serve as two power transmission ends of the clutch, respectively.
The additional clutch control device comprises an annular control oil cylinder arranged on the first force transmission drum T221;
the annular control oil cylinder comprises a cylinder body T29, a connecting main body T30 and a pressure plate T28 arranged between the cylinder body T29 and the connecting main body T30; the connecting main body T30 is fixedly connected with the shell H; the cross section of the platen T28 is approximately U-shaped;
a plurality of springs T25 are arranged between the bottom end face of the pressure plate T28 and the connecting main body T30;
one top of the pressure plate T28 is accommodated in a cylinder T29 to form a piston T26 of an annular control oil cylinder, and a sealing oil chamber is formed between the piston T26 and the cylinder T29;
the other top end surface of the pressure plate T28 is used for pressing the friction plates.
The working principle is as follows:
when the seal oil chamber CYL is filled with oil, the hydraulic thrust overcomes the spring force of a plurality of springs T25 to enable the pressure plate T28 to be separated from the friction plate, and the clutch B is an overrunning clutch: when the overrunning condition is met, the clutch enters the overrunning working condition, and when the locking condition is met, the clutch enters the locking working condition.
When the sealed oil chamber CYL releases the pressure, the spring force of the spring T25 returns the piston T26, the pressure plate T28 presses to the friction plate, and the clutch B plays the roles of an overrunning clutch and a common clutch according to the torque transmission direction: when the direction of the transmission torque meets the condition of entering an overrunning state, the clutch B acts as a common clutch, and the transmission torque of the clutch B depends on the total spring force of the spring T25; when the direction of the transmitted torque accords with the condition of entering a locking state, the clutch B enters a locking working condition and plays the role of an overrunning clutch.
Example 3:
the clutch B is a friction plate type helicoid external pressing overrunning clutch, has a similar structure with the clutch B in the embodiment 1, and is different from the structure in that:
the first force transfer drum T221 is sleeved on the inner side of the second force transfer hub T211;
the second helicoid coupling T24 is fixedly connected with a second force transmission hub T211; the second helicoidal couple T24 is located in the space formed by the second force-transmitting hub T211, the support body and the first helicoidal couple T23.
The support body and the first power transmission drum T221 respectively serve as two power transmission ends of the clutch.
Example 4:
the clutch B is a friction plate type helical surface internal compression overrunning clutch, and is similar to the clutch B in the embodiment 2 in structure, and the difference is that:
the first force transfer drum T221 is sleeved inside the second force transfer hub T211;
the second helicoid coupling T24 is fixedly connected with the first transmission drum T221; the second helicoidal couple T24 is located in the space formed by the first transfer drum T221, the support body and the first helicoidal couple T23.
The support body and the second force transmitting hub T211 act as the two force transmitting ends of the clutch, respectively.
FIG. 4 is a schematic view showing the assembly relationship between the helical surface formation and the two helical surface coupling parts in the overrunning clutches according to embodiments 1 to 4; fig. 5 is a simplified schematic diagram of the structure of the overrunning clutch according to embodiments 1-4, in which a pair of inclined surfaces represents a helical surface coupling member, the wedge corresponds to the second helical surface coupling member T24, the inclined surface corresponds to the first helical surface coupling member T23, and the direction of the force F is the circumferential direction. By modifying the structure of fig. 5, all the components are changed into a structure uniformly arranged along the circumference, and the combination of the overrunning clutch and the multi-plate wet clutch (i.e. the friction-plate peripheral helical surface outer/inner pressing overrunning clutch) shown in fig. 3 is changed.
Fig. 6 (a) is a schematic diagram of force analysis of the overrunning clutch according to embodiments 1 to 4, in which a pair of helical surfaces represents a helical surface coupling member, a wedge in the diagram corresponds to the second helical surface coupling member T24, an inclined surface in the diagram corresponds to the first helical surface coupling member T23, an inclination angle β of the inclined surface is an average helical angle of a helical surface effective contact portion of the two helical surface coupling members, F is a force applied to a circumference where a torque transmitted by the overrunning clutch is converted to the "average helical angle β", and a direction of F is a tangential direction of a force application point on the circumference. Fig. 6 (b) is a schematic force diagram of wedges when the overrunning clutch is locked, fig. 6 (c) is a schematic force diagram of wedges when the overrunning clutch is unlocked, f is a friction force of the friction torque between the second friction plate T212 of the rotating part and the first friction plate T222 of the fixed part which are arranged at intervals converted to the circumference of the average helical angle beta, and the friction coefficient between friction pairs of the friction plates is mu; f 'is the friction force converted from the friction torque between the spiral surface coupling parts to the circumference of the average spiral angle beta, and the friction coefficient between the spiral surface coupling parts is mu'; n is the small value of the effective number of the first friction plate and the second friction plate, N is the positive pressure applied to the friction plates arranged at intervals, and S is the positive pressure between the matching surfaces of the spiral surface coupling parts.
For the lockup regime, 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-Ssinβ＝0
N-f'sinβ-Scosβ＝0
for the unlocked condition, the "average pitch angle β" for the critical state is determined using the following equation:
f＝μ×N
f'＝μ'×S
f+f'cosβ-Ssinβ＝0
N-f'sinβ-Scosβ＝0
therefore, not only the spiral surface coupling parts of the friction plate type peripheral cloth spiral surface external/internal pressing overrunning clutch are enabled to generate self locking, but also the automatic unlocking of the spiral surface coupling parts can be ensured, and the following conditions are met:
the following description of the present invention will be given by way of example to enable smooth torque transition during shifting.
The embodiment is as follows: the structure and parameters of the transmission are as follows:
For convenience of description, the initial operating conditions are firstly set as follows: the clutch B is in a locking state, the clutch C is in a releasing state, and the transmitted friction torque M C =0, with a transmission ratio i, the torque relationship is:
M input device ＝M 11
M Output of ＝i*M 11
M Output of ＝M Input device +M B
In the formula
M Input device -torque transmitted by the input;
M output of -torque delivered by the output;
M 11 torque transmitted on the input gear T11;
M B torque transmitted by the B clutch (overrunning clutch);
M C torque transmitted by the C clutch (multi-plate wet clutch);
when gear shifting is required, the C clutch begins 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 the output ＝M Input device +M B
First, when M C When the value is not less than 0, the reaction time is not less than 0,
M output the output ＝i*M Input device ，
M B ＝(i-1)*M Input device
Namely the initial working condition;
II, as M C When maximum torque is transmitted, i.e.
M B ＝0；
M Output of ＝M Input device ，
At the moment, M is solved according to the torque relation in the gear shifting process C The maximum torque transmitted is:
M C ＝(1-1/i)M input the method
Therefore, when M is C By
M Input the method When changed, the output torque is changed>
On change, a gear is selected from the gear having the gear ratio i>
The gear with the transmission ratio of 1 is adopted, so that smooth transition of the gear shifting process is realized.
In addition, the double-clutch structure is adopted, so that one clutch is separated while the other clutch is synchronously engaged during gear shifting, and uninterrupted power can be realized in the gear shifting process. When one of the double clutches is an overrunning clutch and the other one is a common clutch, only the common clutch needs to be controlled, the state of the overrunning clutch can change along with the common clutch, and the control is simple and convenient.
Claims (9)
1. A three-speed transmission having an input and two outputs; the method is characterized in that:
the three-speed transmission device comprises a gear mechanism (T1), a C clutch (T3), a B clutch (T2) and a D clutch (T4) which are arranged along the same axis;
the gear mechanism (T1) comprises an input gear (T11) fixedly arranged on an input shaft of the speed changing device, a plurality of intermediate shaft gear assemblies consisting of an intermediate shaft (T15), an intermediate shaft first gear (T12) and an intermediate shaft second gear (T13), an output gear (T14) and a gear retainer assembly with two cavities, wherein the gear retainer assembly is formed by sequentially and fixedly connecting a front retainer (T16), an intermediate retainer (T18) and a rear retainer (T17);
the input gear (T11), the gear retainer assembly and the output gear (T14) are coaxially arranged and can rotate relatively;
a central output shaft (T19) is arranged in the middle of the middle retainer (T18), one end of the central output shaft (T19) is coaxial with an input shaft of the speed change device and can rotate relatively, and the other end of the central output shaft (T19) is a power output end;
a central output shaft tube (T20) capable of rotating relatively is coaxially sleeved outside the central output shaft (T19), one end of the central output shaft tube (T20) is fixedly connected with the output end of the output gear (T14), and the other end of the central output shaft tube (T20) is a power output end;
the input gear (T11) and the plurality of jackshaft first gears (T12) are in mesh and are all located in the cavity between the front cage (T16) and the middle cage (T18), the output gear (T14) and the plurality of jackshaft second gears (T13) are in mesh and are all located in the cavity between the rear cage (T17) and the middle cage (T18); the first intermediate shaft gear (T12) and the second intermediate shaft gear (T13) are coaxially fixed side by side and rotatably arranged in a cavity of the gear retainer assembly through the intermediate shafts (T15), the intermediate shafts (T15) penetrate through the intermediate retainer (T18), and two ends of each intermediate shaft are supported by the front retainer (T16) and the rear retainer (T17);
the C clutch (T3) comprises a driving component (T31) and a driven component (T32); the driving component (T31) is fixedly connected with the input shaft, and the driven component (T32) is fixedly connected with the gear retainer assembly;
the B clutch (T2) comprises a rotating component (T21) and a fixed component (T22); the rotating component (T21) is fixedly connected with the gear retainer assembly, and the fixed component (T22) is fixedly connected with a shell (H) containing the three-speed change device;
the D clutch (T4) is arranged at the output end of the gear mechanism (T1); the D clutch (T4) comprises a second rotating assembly (T41) and a second fixed assembly (T42); the second rotating component (T41) is fixedly connected with the central output shaft tube (T20), and the second fixing component (T42) is fixedly connected with a shell (H) containing the three-speed change device;
the clutch B (T2), the clutch C (T3) and the clutch D (T4) can be locked by only one clutch.
2. The three-speed transmission according to claim 1, characterized in that: the housing (H) comprises a front housing support and a rear housing support; the rear housing support is located between the gear mechanism (T1) and the B clutch (T2), or between the B clutch (T2) and the D clutch (T4).
3. The three-speed transmission according to claim 1 or 2, characterized in that: and the clutch B and the clutch C are both multi-plate wet clutches.
4. Three-speed transmission according to claim 1 or 2, characterized in that:
when the speed changer is a speed reducer, the clutch B is an overrunning clutch or a multi-plate wet clutch; for an 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; otherwise, the overrunning clutch is in a locking state; the C clutch is a multi-plate wet clutch.
5. The three-speed transmission according to claim 1, wherein:
the clutch B is a friction plate type circumferential cloth helical surface internal compression overrunning clutch and comprises a clutch limiting device, a fixed component (T22), a rotating component (T21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing component (T22) comprises a first force transmission drum (T221) and a plurality of first friction plates (T222) arranged in the first force transmission drum, wherein the first friction plates can relatively slide along the axial direction relative to the first force transmission drum and synchronously rotate along the circumferential direction;
the rotating assembly (T21) comprises a second force transmission hub (T211) and a plurality of second friction plates (T212) arranged outside the second force transmission hub, and the second friction plates can slide relative to the second force transmission hub along the axial direction and synchronously rotate along the circumferential direction;
the first force transmission drum (T221) is sleeved outside the second force transmission hub (T211);
a plurality of first friction plates (T222) and a plurality of second friction plates (T212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (T271) fixedly connected with an input shaft of the speed change device and a retainer ring (T272) arranged on the supporting main body;
the self-locking/overrunning control device is used for controlling the opening and closing of the first friction plate and the second friction plate and comprises a first spiral surface coupling part (T23) and a second spiral surface coupling part (T24);
a first helicoid (T231) is arranged on the first helicoid matching part (T23); a second helicoid (T241) matched with the first helicoid is arranged on the second helicoid matching part (T24);
the first helicoid couple (T23) is fixedly connected with the support main body (T271), and the second helicoid couple (T24) is fixedly connected with the second force transmission hub (T211); the second helicoidal couple is located between the support body and the first helicoidal couple (T23), and it is able to make a spiral slip with respect to said first helicoidal couple;
the support body (T271) is of a circular ring structure with a neck, the neck is a hollow cylinder, and the bottom is an outward extending circular ring; a retainer groove (T273) and a limit step (T274) are arranged on the outer side surface of the neck of the support main body; the retainer ring is arranged in the retainer ring groove; the retainer ring and the limiting step are used for fixing the axial position of the first spiral surface matching part (T23); the annular ring of the support body is used for limiting the axial position of the first friction plate (T222) and the second friction plate (T212);
the additional clutch control device comprises an annular control oil cylinder arranged on the first force transmission drum (T221); the annular control oil cylinder comprises a cylinder body (T29), a connecting main body (T30) and a pressure plate (T28) arranged between the cylinder body (T29) and the connecting main body (T30); the connecting main body (T30) is fixedly connected with the shell (H); the cross section of the pressure plate (T28) is approximately U-shaped; a plurality of springs (T25) are arranged between the bottom end surface of the pressure plate (T28) and the connecting body (T30); one top of the pressure plate (T28) is accommodated in a cylinder body (T29), a piston (T26) of an annular control oil cylinder is formed, and a sealed oil Chamber (CYL) is formed between the piston (T26) and the cylinder body (T29); the other top end surface of the pressure plate (T28) is used for pressing friction plates;
the support body and the first force transfer drum respectively serve as two force transfer ends of the clutch.
6. The three-speed transmission according to claim 1, wherein:
the clutch B is a friction plate type peripheral helical surface external pressing overrunning clutch and comprises a clutch limiting device, a fixed component (T22), a rotating component (T21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing component (T22) comprises a first force transmission drum (T221) and a plurality of first friction plates (T222) arranged in the first force transmission drum, wherein the first friction plates can relatively slide along the axial direction relative to the first force transmission drum and synchronously rotate along the circumferential direction;
the rotating assembly (T21) comprises a second force transmission hub (T211) and a plurality of second friction plates (T212) arranged outside the second force transmission hub, and the second friction plates can relatively slide along the axial direction relative to the second force transmission hub and synchronously rotate along the circumferential direction;
the first force transmission drum (T221) is sleeved outside the second force transmission hub (T211);
a plurality of first friction plates (T222) and a plurality of second friction plates (T212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (T271) fixedly connected with the shell (H); the supporting main 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 opening and closing of the first friction plate and the second friction plate and comprises a first helical surface coupling part (T23) and a second helical surface coupling part (T24);
a first helicoid (T231) is arranged on the first helicoid matching part (T23); a second helicoid (T241) matched with the first helicoid is arranged on the second helicoid matching part (T24);
the first helicoidal couple (T23) is fixedly connected with the support main body, and the second helicoidal couple (T24) is fixedly connected with the first transmission drum (T221); the second helicoidal couple is located between the support body (T271) and the first helicoidal couple (T23), and it slides helically with respect to said first helicoidal couple;
the additional clutch control device comprises an annular cylinder arranged on the shell (H), a piston (T26) arranged in the annular cylinder, and a plurality of springs (T25) arranged between the second spiral surface coupling part (T24) and the piston (T26); the end surface of the piston provided with a plurality of springs simultaneously faces the first friction plate (T222); a sealed 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 transmission hub are respectively used as two force transmission ends of the clutch.
7. The three-speed transmission according to claim 1, characterized in that:
the clutch B is a friction plate type circumferentially distributed helical surface internal compression overrunning clutch and comprises a clutch limiting device, a fixed component (T22), a rotating component (T21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing component (T22) comprises a first force transmission drum (T221) and a plurality of first friction plates (T222) arranged in the first force transmission drum, wherein the first friction plates can relatively slide along the axial direction relative to the first force transmission drum and synchronously rotate along the circumferential direction;
the rotating assembly (T21) comprises a second force transmission hub (T211) and a plurality of second friction plates (T212) arranged outside the second force transmission hub, and the second friction plates can relatively slide along the axial direction relative to the second force transmission hub and synchronously rotate along the circumferential direction;
the first force transmission drum (T221) is sleeved on the inner side of the second force transmission hub (T211);
a plurality of first friction plates (T222) and a plurality of second friction plates (T212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (T271) fixedly connected with an input shaft of the speed change device and a retainer ring (T272) arranged on the supporting main body;
the self-locking/overrunning control device is used for controlling the opening and closing of the first friction plate and the second friction plate and comprises a first helical surface coupling part (T23) and a second helical surface coupling part (T24);
a first helicoid (T231) is arranged on the first helicoid matching part (T23); a second helicoid (T241) matched with the first helicoid is arranged on the second helicoid matching part (T24);
the first helicoidal couple (T23) is fixedly connected with the support main body, and the second helicoidal couple (T24) is fixedly connected with the first transmission drum (T221); the second helicoidal couple is located between the support body and the first helicoidal couple (T23), and it slides helically with respect to said first helicoidal couple;
the support main body is of a neck-provided circular ring structure, the neck of the support main body is a hollow cylinder, and the bottom of the support main body is an outward extending circular ring; a retainer groove (T273) and a limit step (T274) are arranged on the outer side surface of the neck of the support body; the retainer ring (T272) is arranged in the retainer ring groove; the retainer ring and the limiting step are used for fixing the axial position of the first helical surface coupling part (T23); the annular ring of the support body is used for limiting the axial position of the first friction plate (T222) and the second friction plate (T212);
the additional clutch control device comprises an annular control oil cylinder arranged on the first force transmission drum (T221); the annular control oil cylinder comprises a cylinder body (T29), a connecting main body (T30) and a pressure plate (T28) arranged between the cylinder body (T29) and the connecting main body (T30); the connecting main body (T30) is fixedly connected with the shell (H); the cross section of the pressure plate (T28) is approximately U-shaped; a plurality of springs (T25) are arranged between the bottom end surface of the pressure plate (T28) and the connecting body (T30); one top of the pressure plate (T28) is accommodated in a cylinder body (T29), a piston (T26) of an annular control oil cylinder is formed, and a sealed oil Chamber (CYL) is formed between the piston (T26) and the cylinder body (T29); the other top end surface of the pressure plate (T28) is used for pressing friction plates;
the support body and the second force transmission hub are respectively used as two force transmission ends of the clutch.
8. The three-speed transmission according to claim 1, characterized in that:
the clutch B is a friction plate type peripheral helical surface external pressing overrunning clutch and comprises a clutch limiting device, a fixed component (T22), a rotating component (T21), a self-locking/overrunning control device and an additional clutch control device which are arranged on the same rotating axis;
the fixing component (T22) comprises a first force transmission drum (T221) and a plurality of first friction plates (T222) 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 synchronously rotate along the circumferential direction;
the rotating assembly (T21) comprises a second force transmission hub (T211) and a plurality of second friction plates (T212) arranged outside the second force transmission hub, and the second friction plates can slide relative to the second force transmission hub along the axial direction and synchronously rotate along the circumferential direction;
the first force transmission drum (T221) is sleeved on the inner side of the second force transmission hub (T211);
a plurality of first friction plates (T222) and a plurality of second friction plates (T212) are alternately arranged in the axial direction;
the clutch limiting device comprises a supporting main body (T271) fixedly connected with the shell (H); the supporting main 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 opening and closing of the first friction plate and the second friction plate and comprises a first helical surface coupling part (T23) and a second helical surface coupling part (T24);
a first helicoid (T231) is arranged on the first helicoid matching part (T23); a second helicoid (T241) matched with the first helicoid is arranged on the second helicoid matching part (T24);
the first helicoid couple (T23) is fixedly connected with the support main body, and the second helicoid couple (T24) is fixedly connected with the second force transmission hub (T211); the second helicoidal couple is located between the support body and the first helicoidal couple (T23), and it slides spirally with respect to said first helicoidal couple;
the additional clutch control device comprises an annular cylinder arranged on the shell (H), a piston (T26) arranged in the annular cylinder, and a plurality of springs (T25) arranged between the second spiral surface coupling part (T24) and the piston (T26); the end surface of the piston provided with a plurality of springs simultaneously faces the first friction plate (T222); a sealed 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 respectively serve as two force transfer ends of the clutch.
9. The three-speed transmission according to claim 5, 6, 7 or 8, characterized in that: the first helicoid matching part, the second helicoid matching part, the first friction plate and the second friction plate meet the following conditions:
wherein β is the average helix angle of the helicoidal effective contact portions of the two helicoidal couples;
mu is the friction coefficient between the first friction plate and the second friction plate;
mu' is the friction coefficient between two spiral surface coupling parts;
n is the small value in the effective number of the first friction plate and the second friction plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611207915.5A CN106594202B (en) | 2016-12-23 | 2016-12-23 | Three-speed change gear |
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| CN201611207915.5A CN106594202B (en) | 2016-12-23 | 2016-12-23 | Three-speed change gear |
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| CN106594202A CN106594202A (en) | 2017-04-26 |
| CN106594202B true CN106594202B (en) | 2023-04-07 |
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| CN111677822A (en) * | 2019-12-24 | 2020-09-18 | 熵零技术逻辑工程院集团股份有限公司 | Driving mechanism |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1148674A (en) * | 1995-09-07 | 1997-04-30 | 丰田自动车株式会社 | Automatic speed variator |
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| WO2015080090A1 (en) * | 2013-11-29 | 2015-06-04 | アイシン・エィ・ダブリュ株式会社 | Multistage transmission |
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Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1148674A (en) * | 1995-09-07 | 1997-04-30 | 丰田自动车株式会社 | Automatic speed variator |
Non-Patent Citations (1)
| Title |
|---|
| 张海涛 ; 王恰锋 ; 刘晓光 ; .浅谈自动变速器发展简史.科技信息(学术研究).2008,(04),全文. * |
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