Stepless gear ratio variation transmission

FIELD: transport.

SUBSTANCE: stepless gear ratio variation transmission incorporates an input shat (I), output shat (O) and gear ratio variator coupled with the aforesaid output shaft and furnished with its own output shaft. The 1st gear of the planetary reduction gear with input shafts coupled with the variator (V) output shaft and the transmission input shaft via the first coupling (H) and gear of the second planetary reduction gear with input shafts coupled with the variator output shafts and transmission input shaft come in mesh with the third planetary reduction that comes into mesh with the transmission output shaft via the first braking element (L). The second braking element (B) is arranged to lock the output shaft of the second planetary reduction gear in static state.

EFFECT: reduced rpm of parts and number of gearings.

8 cl, 2 dwg

 

The present invention relates to systems transmission with stepless change gear ratio.

Known systems transmission with stepless change gear ratio, containing the input and output shafts and the node stepless change gear ratio (known as the variable-speed drive)connected to the drive shaft of the system and having an output shaft of the variator. Combining planetary gear is driven by the input shaft system and the input shaft of the variator. Through the use of couplings or other braking elements the system can operate in high gear or low gear ratio. Examples of such transmissions, revealing design with coaxial input and output shafts of the system can be found in patent publications JP-A-6-174033 and JP-A-62-255655.

When the gearing will inevitably have a small power loss. Thus, to achieve maximum efficiency, it is desirable to reduce the amount of gearing gears, especially in combining planetary gear, where the losses are, in essence, can be increased when the mode is "recycling facilities".

In our parallel patent application UK 0212186,1 this problem is solved by creating a combining planetary gear unit, which will gain the input of the Central toothed wheel, United with the drive capability of the output shaft of the variator, drove planetary series, coupled with the opportunity to drive the input shaft of the system, and the first satellite is mounted on the drive rod and tazapsidis with the opportunity to drive the input of the Central toothed wheel. The first satellite, results in the first intermediate output shaft located coaxially with the input shaft of the system, and is configured to selectively connect the output shaft of the system through the first clutch. Additionally, the first satellite transmits a rotation of the second planetary gear, the output of which is configured to selectively connect the output shaft of the brake system through the element.

In this transmission, the variator is a component with the lowest performance, but it allows you to optimize the performance of the engine due to the coordination ratio that increases the General efficiency. However, when maximum power is impossible, because it occurs only at one engine speed. If the power loss is an important factor, it may make sense to sacrifice the stepless change gear ratio for best efficiency by eliminating the influence of the variator and its operation at a fixed ratio.

p> The overall result is the potential exclusion of small reducing the maximum speed of the vehicle on which the such transmission.

According to the first object of the present invention, the set of multi-mode transmission system with stepless change gear ratio, containing the input shaft of the system and the output shaft; a transmission node with a stepless change gear ratio (CVT)connected to the input shaft of the system and having an output shaft of the variator; the output shaft of the variator, which is made with selective connection with the output shaft system via the first clutch; combining planetary gear having inputs connected to the drive capability of the output shaft of the variator and the input shaft of the system, and the output is made with the possibility for selective connection with the output shaft of the system through the first brake element; and the second brake element is arranged to lock the output of the combining planetary gear in a stationary position.

Preferably, the input shaft of the system, the output shaft system and the variator are aligned with each other and with the second planetary gear containing the second input of the Central gear wheel, a driven output shaft combining planetary gear unit, being the m second brake element is designed with the ability to selectively locking the input of the Central gear of the second planetary gear in a stationary position.

Preferably, the transmission system includes an intermediate gear connecting the combining planetary gear and the input of the Central gear of the second planetary gear.

Preferably, the second planetary gear includes a second Central gear, siteplease with satellite.

Preferably, the Central gear wheel is held stationary relative to the transmission casing, and the first brake element includes a tool coupling for selectively connecting an output shaft of the second planetary gear with the output shaft system.

According to the second object of the present invention created a method of operation of the powertrain according to the present invention, in which

determine the state in which the output of the variator is connected with the output shaft of the system through the first clutch, and wherein the output of the combining planetary gear essentially stationary; and

include a second brake element for locking the output of the combining planetary gear in a stationary position.

The following description, only as an example, a specific variant of the present invention with reference to the accompanying drawings, on which:

figure 1 is a General illustration of the present invention and

2 is a diagram of a variant embodiment of transm the hurt in accordance with the present invention.

As shown in figure 1, the powertrain system with stepless change gear ratio includes input shaft I and the output shaft Of the system. Between the input shaft I and the output shaft Of the system is the variator V, preferably of a known type, such as a toroidal CVT with the working surface of the wheel with the friction rollers, and the clutch H high gear ratio. The input shaft I of the transmission and the output shaft of the variator V is also connected to the backplane planetary gear E output shaft which is configured to selectively connect the output shaft Of the transmission through the clutch L low gear ratio.

However, it should also be noted that the output shaft of the planetary gear also can be locked relative to the housing 40 of the transmission through one of the brake element in the form of a clutch Century

One sign of the output shaft combining planetary gear E is that at a certain transmission ratio of the variator output shaft of the planetary gear E is stationary (a condition that, when the transmission is in low gear ratio, known in the industry as "geared neutral"). The General principle of the present invention is that when you enable the coupling of H-mode high gear ratio and is iklyuchenie clutch L low gear ratio (i.e. when the transmission is in high gear ratio) of the output shaft of the planetary gear E is directly monitored, and when the speed of the output shaft of the planetary gear E is zero or close to zero, turns on additional clutch that locks the output shaft of the planetary gear, not allowing it to rotate. Locking coupler To prevent the departure of the variable from the predetermined gear ratio, which would lead to the state of the geared neutral, if the coupling mode low gear ratio is enabled.

The design, shown in figure 2, illustrates in more detail one of the variants of the present invention.

The powertrain system with stepless change gear ratio contains variable V related to a known type of variable-speed drives with toroidal working surface of the wheel with the friction rollers having two disk 10 with a toroidal working surfaces, which are mounted one at each end of the device, and a pair of similar output disks 12, each of which is converted to a corresponding input disk 10, and rotating one with the other. Between the facing to each other working surfaces of the input and output disks 10, 12 has a series of rollers 14 for transmitting rotation from the input disks 10 to the output disks 12 with gear ratio, which is diversified by changing the inclination of the rollers 14.

The input disks 10 are connected with the input shaft 16 of the system, and gives from him. The output of the variator through the tubular output shaft 18 of the variator, which is located coaxially with the input shaft 16. The end of the shaft 18, remote from the variator V, causes the Central gear S1 of the first combining planetary gear unit E1. Carrier C1 of the planetary gear unit E1 is connected with the input shaft 16 and is provided to them, and also connected to the inner of the two input disks 10 a variator. On the driver C1 is the input satellites P1, which are in engagement with the Central gear S1 and provides them. Each of the satellites P1 is installed on the driver C1 on the corresponding shaft 20 on which are installed first and second output satellites RH and PY1. Output satellite RH identical to the satellite P1 and transmits the summed output of the gearbox E1 through Central output gear S2 (the same size as the input of the Central gear S1) on the intermediate output shaft 22, mounted coaxially with the input shaft 16 of the system. The rotation of the intermediate output shaft can be selectively transmitted through the coupling to H-mode high gear ratio to the output shaft 24 of the system.

Output satellite PY1 has a smaller diameter than the satellites P1 and RH, and is in mesh with the gear 26 formed on the cut end of the tubular intermediate output shaft 28, installed coaxially with the output shaft 16. The opposite ends of this intermediate output shaft is also provided with a gear 30, which has a diameter less than the diameter of the gear 26. The gear 30 is in mesh with a larger diameter satellites P2 of the second simple reversing planetary gear D2. Satellites P2 is installed on a drive rod C2, which is connected with the second tubular intermediate output shaft 32, mounted coaxially with the output shaft 16 of the system and, in turn, connected to output shaft 24 of the system.

Each satellite P2 of the second planetary gear is located at one end of the corresponding shaft 34, mounted on a drive rod S2. At the opposite end of each shaft 34 is another satellite RH smaller diameter, which is in mesh with the Central gear 36 rigidly connected to the housing 40 of the transmission. The rotation of the second tubular intermediate output shaft 32 is continuously withdrawn from the carrier C2, and selectively transmitted to the output shaft 24 of the system through the coupling to L-mode low gear ratio.

In addition, it should be noted that the tubular intermediate output shaft 28 can be selectively inhibit relative to the housing 40 of the transmission, the above-mentioned additional coupling Century

The transmission can operate in one of three modes, and the property named is in the mode with a high gear ratio, in the regime with low gear ratio and in synchronous mode.

In the regime with high gear ratio clutch H-mode with high gear ratio is switched on and the clutch L-mode with a low gear ratio is off. This sends the output of the first combining planetary gear unit formed by gears R and S2 and the planet carrier C1, which receives at the input rotation from the input disk 10, and the output disk 12 of the variator V, the output shaft 24 of the system from the output of satellites R of the first planetary gear unit E1, through a Central output gear S2, the intermediate output shaft 22 and the clutch H-mode with high gear ratio.

The output of the other output satellite PY1 first combining planetary gear unit E1 is also transmitted to the second planetary gear E2. This output is not transmitted to the carrier C2 in the regime with high gear ratio, because the coupling L-mode with a low gear ratio is off.

However, as described above, a status transmission (known as "geared neutral") tubular intermediate output shaft 28 (i.e. the second output of the combining planetary gear unit E1) does not rotate. The present invention takes advantage of this situation by detecting the state of the geared neutral and the connecting sleeves for locking the intermediate shaft 28 relative to the housing 40 of the transmission in the state, in which the second output of the combining planetary gear unit formed by gears S1, P1, PY1 and 26 and planet carrier C1 is fixed.

As a result, the variator effectively locked at a fixed transmission ratio corresponding to the geared neutral. Then, from the input shaft 16 of the power is transmitted with a fixed gear ratio through the first combining planetary gear formed by the planet carrier C1 and pairs of gears S2/PX1 and 26/PY1.

In the regime with low gear ratio clutch H-mode with high gear ratio is switched off and the clutch L-mode with a low gear ratio is enabled. Off clutch H-mode with high gear ratio isolates the output shaft 24 of the system from the output of a satellite RH combining planetary gear unit E1. In addition, the inclusion of the coupling L-mode low-gear ratio allows the rotation of an output of the first combining planetary gear unit E1 is supplied to the second planetary gear E2, transmit on carrier C2 of the second planetary gear E2 due to the reactive force from the housing 40 of the transmission. Then the rotation is transmitted to the second tubular intermediate output shaft 32 and from there to the output shaft 24 of the system.

The transition from low gear ratio mode with a high gear ratio, and the turnover can be performed in the so-called "synchronous mode", in which, the transmission operates in a state in which the intermediate output shaft 22, leading from the combining planetary gear unit E1, and the second tubular intermediate output shaft 32, leading from the second planetary gear unit E2, rotate with the same (or very close) frequency. To change the mode, include the coupling of the new regime, resulting in a short time coupling of both modes are enabled, and the clutch of the old regime and then shut down.

It should be noted that in the regime with low gear ratio the only gears that are in active engagement in combining planetary gear E1 are satellites P1 and PY1, thereby minimizing losses that arise in combining planetary gear, especially in the recirculation mode power. In the regime with high gear ratio, the number of links does not exceed the number of transmissions according to the prior art. However, it should also be noted that the present invention allows the use of the combining planetary gear E1, which has no ring gear or gear rims. This not only reduces the weight of the transmission, but also provides greater flexibility when selecting the relative sizes of the satellites P1, RH and PY1. This, in turn, reduces castorena parts and to reduce the number of links to a minimum.

It should be noted that the present invention is not limited to the details of the above options.

1. Multi-mode transmission system with stepless change gear ratio, containing the input shaft of the system and the output system, the transmission node with a stepless change gear ratio (CVT)connected to the input shaft of the system and having an output shaft of the variator, which is made with selective connection with the output shaft of the system through the first clutch, combining planetary gear having inputs connected to the drive capability of the output shaft of the variator and the input shaft of the system, and the output is made with the possibility for selective connection with the output shaft of the system through the first brake element, and a second brake element is arranged to lock the output of the combining planetary gear in a stationary position.

2. The system according to claim 1, in which the input shaft of the system, the output shaft system and the variator are aligned with each other and with the second planetary gear containing the second input of the Central gear wheel, a driven output shaft combining planetary gear unit, and the second brake element is designed with the ability to selectively locking the second Central gear of the second plan is ary gear in a stationary position.

3. The system according to claim 2, in which the second planetary gear includes a second Central gear, siteplease with satellite.

4. The system according to claim 3, in which the second Central gear wheel is held stationary relative to the transmission casing, and the first brake element includes a tool coupling for selectively connecting the output of the second planetary gear with the output shaft system.

5. The system according to claim 2, comprising the intermediate gears connecting the combining planetary gear and the input of the Central gear of the second planetary gear.

6. The system according to claim 5, in which the second planetary gear includes a second Central gear, siteplease with satellite.

7. The system according to claim 6, in which the second Central gear wheel is held stationary relative to the transmission casing, and the first brake element includes a tool coupling for selectively connecting the output of the second planetary gear with the output shaft system.

8. The method of operation of a powertrain according to any one of the preceding paragraphs, which determine the state in which the output of the variator is connected with the output shaft of the system through the first clutch, and wherein the output of the combining planetary gear essentially stationary and include a second brake ele is UNT for locking the output of the combining planetary gear in a stationary position.



 

Same patents:

FIELD: engines and pumps.

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1 dwg

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18 cl, 8 dwg

FIELD: transport engineering; vehicle transmissions.

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FIELD: transport engineering; vehicle transmissions.

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1 dwg

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39 cl, 15 dwg

Drive (versions) // 2278309

FIELD: mechanical engineering; devices for control of rotational speed of working member shaft.

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5 cl, 3 dwg

FIELD: mechanical engineering.

SUBSTANCE: mechanical amplifier comprises power differential (1), comparing differential (30), adjusting differential (2), control differential (36), and two self-braking mechanisms (3) and (4). The input of the power differential (1) is connected with the drive and input of control differential (2). Central wheels (17) and (18) of the power differential are secured to driven links (15) and (16) of the self-braking mechanisms and connected with central wheels (32) and (33) of the comparing differential so that the central wheels of the comparing differential rotate in opposite directions. Driving links (13) and (14) of the self-braking mechanisms are connected with central wheels (19) and (20) of the adjusting differential and central wheels (42) and (43) of the control differential so that the central wheels of the control differential rotate in opposite directions.

EFFECT: enhanced reliability and expanded functional capabilities.

1 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: in proposed coaxial shaft-and-planetary transmission gear 10 on primary shaft 2 is secured and is in meshing with gear 7 provided with rim of increased width and freely fitted on intermediate shaft 6. Gear 11 of secondary shaft 3 has also rim of increased width near gear rim of gear 10 of primary shaft 2. shifter sleeve member 24 fitted on said gear rims is coupled with other sleeve member 25 by shifter fork 26, sleeve member 25 being installed on gear rims of gears 7 and 8 of intermediate shaft 6. Gear rim 19 of output shaft of carrier 15 is two-position one. Gear rim 20 of output shaft of set 5 is three-position one, and shifter sleeve 28 on said rim is provided with three internal gear rims. Gear rim 31 with internal and external meshing is teeth rigidly secured on slider 30 of shifter sleeve 28, external meshing teeth being coupled with three-position gear rim 23 of housing of set 1.

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2 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: according to invention, gear 14 is secured on primary shaft 3, and gear 13 is secured on first tubular shaft 9 freely fitted on primary shaft 3. Gear rims 21 and 22 are fitted on shafts 3 and 9. Input shaft 2 with hub of three-position shifter sleeve 23 and additional driving shaft 4 are installed coaxially to shaft 3. Two gears 17 and 18 in meshing with gears 19 and 20 of secondary shaft 5 are secured on shaft 4. Gear 19 is fitted on shaft 5. Gear 20 is secured on second tubular shaft 10 freely installed on shaft 5. Gear rims 24 and 25 are secured on shafts 5 and 10. Shaft 6 with hub of two-position shifter sleeve 26 and sun gear 27 of planetary mechanism is installed coaxially to shaft 5. Gear 27 engages through planet pinions 31 with epicyclic wheel 32. Planet pinions 31 are freely fitted on axles of carrier 33. Two gear rims 34 and 35 are arranged on periphery of housing of carrier 33. Shaft 7 of carrier 33 with two position gear rim is arranged coaxially to shaft 5 and shaft 6. Third tubular shaft 11 of housing of epicyclic wheel with gear rim 38 is freely fitted on shaft 7. Output shaft 8 with hub of three-position shifter sleeve 40 is arranged coaxially to shaft 7. Sleeve 40 is movably coupled by guide 41 with two-rim shifter sleeve 42 arranged between gear rim 37 of housing 36 of epicyclic wheel 32 and gear rim 43 of gearbox case provided with two inner gear rims and one outer gear rim.

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2 dwg

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet friction variator comprises shaft (1), solar wheel (2), corona wheel (6), carrier (4) with satellites (3), and secondary shaft (5). Corona wheel (6) that is used as a control member is connected with variator housing (11) and primary shaft (1) through friction mechanisms. Secondary shaft (5) is made in block with carrier (4) for permitting control of velocity and direction of rotation of the corona wheel by means of friction mechanisms and control electric motor (9) connected with the corona wheel.

EFFECT: simplified structure, reduced sizes, and enhanced reliability.

1 dwg

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