System of transmission with constantly changing gear ratio

FIELD: mechanical engineering.

SUBSTANCE: proposed system of transmission with constantly changing gear ratio has input and output shafts, 16 and 24, respectively, transfer unit V with constantly changing gear ratio connected to input shaft 16, mixed epicyclical transfer mechanism E1 and second epicyclical transfer mechanism E2. Mechanism E1 has input sun gear S1 connected to output shaft of variable speed drive 18, carrier C1 connected to input shaft 16 and planetary gear P1 installed on carrier C1. Planetary gear P1 drives first intermediate output shaft 32 selectively connected to output shaft 24 of system through first clutch H at high speed of system. Planetary gear P1 provides also input power for second epicyclical transfer mechanism E2. Mechanism E2 has output C2 which is selectively connected to output shaft 24 of system through brake member L at low speeds of system.

EFFECT: minimization of engagement of gears, thus minimizing transmission losses, no backlash in mechanism E1, increased range of selection of sizes of gears, thus reducing speed of gears.

2 cl, 2 dwg

 

The present invention relates to systems and transmission (powertrain) with a constantly changing ratio.

It is known the existence of a transmission with continuously variable ratio, having coaxial input and output shafts of the system and block transmission with continuously variable ratio (known as the variable-speed drive)is attached coaxially to the input shaft of the system and having a coaxial output shaft of the variator. Mixed epicycle gear mechanism is driven by the input shaft of the system and the output shaft of the variator. Through the appropriate use of the clutch and other brake elements the system can operate at high speed or low gear. Examples of such transmission systems can be found in JP-A-6-174033 and JP-A-62-255655.

Small power loss is inevitable when the gear. Therefore, in order to maximize efficiency (efficiency) it is desirable to reduce the number of links of gear wheels, in particular, in the mixed epicycle gear mechanism, where losses can greatly increase during mode "recycling facilities". Thus, the present invention is the provision of "coaxial" transmission system with a continuously changing ratio of the above type with a decreased amount carried the conviction of gear wheels.

"Coaxial devices according to the prior art require relatively high speed gears, which in turn requires more expensive bearings and leads to increased wear. The objective of the invention is the reduction of these speed gears.

In accordance with the present invention results from the multimode transmission system with a continuously variable gear ratio, containing:

coaxial input and output shafts of the system;

its final drive unit continuously variable transmission (CVT), is coaxially attached to the input shaft of the system and having a coaxial output shaft of the variator; and

mixed epicycle gear mechanism having an input sun wheel with the drive attached to the output shaft of the variator, drove with the drive attached to the input shaft of the system and the first planetary gear (planetary gear)mounted on a drive rod and drive meshed with the input sun wheel;

and the first planetary gear causes the first intermediate output shaft, which is coaxial with the input shaft of the system, and the first planetary gear provides the supply power to the second epicycle, paradatec the WMD mechanism;

characterized in that the first intermediate output shaft selectively connected to the output shaft of the system through the first clutch when visokoprizemni functioning gear and the second gear has an output that is selectively connected to the output shaft of the system through the brake element when nishijima the operation of the transfer.

Using the above arrangement, when the output of the second epicycle gear mechanism attached to the output shaft system (which corresponds to operation at low modes), the number siteplease gears can be minimized, thereby minimized losses that arise in mixed epicycle gear mechanism, especially in the recirculation mode power. Moreover, mixed epicycle gear above arrangement does not require the ring or epicycle gears. This significantly reduces the physical size required for mixed epicycle gear mechanism and, consequently, allows for much greater flexibility in the selection of the relative sizes of the planetary gear and drove. This arrangement makes it possible to select gears that allow mixed epicycle gear mechanism to operate at lower speeds as compared with the devices of the prior art, thus reducing wear, minimizing losses and reducing requirements for other components, such as bearings.

The above arrangement also enables the implementation of recycling power on the high mode of the transmission system.

Preferably, the first intermediate output shaft is equipped with a sun wheel, which is the first planet carrier mixed epicycle gear mechanism. Preferably the solar wheel of the output shaft is the same size as the sun wheel input shaft.

On the axis of the planetary gears mixed epicycle gear mechanism preferably has a second planetary gear that rotates together with the first planetary gear and causes the first intermediate output shaft. Conveniently, the second planetary gear has the same size as the first planetary gear.

On the axis of the first planetary gear mixed epicycle gear mechanism may also be third planetary gear that rotates together with the first planetary gear and passes the input power of the second epicycle gear mechanism.

The second epicycle gear mechanism preferably includes a second input Sol is acnee wheel, given the mixed epicycle gear mechanism, the planetary gear, the second input driven sun wheel, and drove forming the output power of the second epicycle gear mechanism.

Preferably the system also includes an intermediate gear, then connecting mixed epicycle gear with the second input sun wheel.

Preferably the second epicycle gear mechanism includes a second sun wheel meshed with the planetary gears of the second epicycle gear mechanism.

In one example embodiment, the system includes means for selectively braking the second sun gear. This can be done using a clutch located between the second sun wheel and the housing of the transmission system.

In another example embodiment of the solar wheel remains stationary relative to the housing of the transmission system, and the braking element includes clamping means for selectively attaching the second epicycle gear mechanism to the output shaft of the system.

Only in the form of example, will now be described some examples of embodiments of the present invention with reference to the accompanying drawings, on which:

figure 1 - diagram of the first example waples is of the transmission system with a continuously variable gear ratio in accordance with the present invention; and

2 is a diagram of a second example embodiment of the transmission system with a continuously variable gear ratio in accordance with the present invention as a modification of the example embodiment of figure 1.

Referring first to figure 1, the transmission system with a continuously variable gear ratio includes the variator V is known gearing with a toroidal groove rolling with two disk 10 with toroidal cavity, located one at each end of the block, and a pair of identical output disks 12, each of which is rotated to a corresponding input disk 10 and rotates with the other. The rows of rollers 14 mounted between the opposing surfaces of the input and output disks 10, 12 for the transmission of motion from the input disks 10 to the output disks 12 with gear ratio, which is changed by tilting the rollers 14.

The input disks 10 are attached to the input shaft 16 of the system, and gives from him. The CVT provides output power 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 sun wheel S1 of the first mixed epicycle gear mechanism E1. Drove transmitting mechanism C1 E1 is attached to the input shaft 16 and is driven by it and it is attached to the inside the C two input disks 10 a variator. Drove C1 carries the input planetary gears P1, which engage with a sun wheel S1, and gives from him. Each planetary gear set P1 on C1 driver using the attached shaft 20, which additionally supports the first and second output planetary gears PX1 and PY1. The output of the planetary gear PX1 identical planetary gear wheel P1 and transmits the total output of the transmission mechanism of E1 through the output sun wheel S2 (the same size as the input sun wheel S1) on the intermediate output shaft 22 that is located coaxially with the input shaft 16 of the system. The movement from the intermediate output shaft can be selectively transmitted through the clutch N high mode on the output shaft 24 of the system.

The output of the planetary gear PY1 has a smaller diameter than the planetary gears P1 and RH, and engages with the gear 26 located at one end of the tubular intermediate output shaft 28, which is located coaxially with the input shaft 16. The opposite end of the intermediate output shaft is also provided with a gear 30 of a smaller diameter than the gear 26. The gear 30 engages with the planetary gears of larger diameter P2 of the second, a simple reversing gear mechanism D2. Planetary gears P2 is settled and the driver C2, which is attached to the second tubular intermediate output shaft 32 that is located coaxially with the input shaft 16 of the system, and which in turn is attached to the output shaft 24 of the system.

Each of the planetary gears P2 of the second transmission mechanism of E2 is located at one end of the corresponding shaft 34, mounted in the driver C2. The opposite end of each shaft 34 is equipped with an additional, smaller planetary gear R, which engages with a sun wheel 36 located at one end of the tubular gear shaft 38, which is located coaxially with the input shaft 16 of the system. The other end of the countershaft 38 is attached to one side of the brake element in the form of a clutch low mode L, the other end of which is attached to the gearbox housing 40.

Transmission can operate in one of three modes, namely high mode, low mode and synchronous mode.

On high mode, when the transmission operates at its final respects from the ratio of the synchronous mode to extreme shocks, clutch high mode N is engaged and clutch low mode L out of engagement. This allows power generated mixed epicycle gear mechanism E1, which receives input power from the input disk is 10, and output disks 12 of the variator V, to be transmitted to the output shaft 24 of the system from the output planetary gears RH of the first epicycle gear mechanism E1, the output sun gear S2, the intermediate output shaft 22 and the coupling of high N. Power output from the other output of the planetary gears RU1 first mixed epicycle gear mechanism E1 is also passed to the second epicycle gear mechanism of E2, but because of the low coupling regime L raceplane, output power (output) is not transmitted to the carrier C2 and actually drove C2 simply rotates with the output shaft 24 of the system to which it is attached. If the sun gear S1 and S2 have the same diameter, the intermediate shaft 22 will rotate with the same speed as the output shaft 18 of the variator. However, changing the relative sizes of the wheels S1 and S2 will create the second epicycle functioning largely as a low transmission mode. Therefore, this arrangement simply lets recycle power to be exercised through the variator V at high mode. Synchronous switching point can then be determined independently of the range of the transmission ratio of the variator.

On low mode when the transmission is working on its final drive ratios from fully what about the reverse through neutral to synchronous mode, coupling high mode H out of engagement and the low coupling regime L is engaged. The disengagement of the high clutch mode N isolates the output shaft 24 of the system from the output planetary gears RH mixed epicycle gear mechanism E1. Moreover, the engagement of the clutch low mode L allows to transmit the output power from the first mixed epicycle gear mechanism E1 to the second epicycle gear mechanism of E2 on carrier C2 of the second epicycle gear mechanism of E2 by providing reactive power from the housing 40 of the transmission. Then the motion is transmitted to the second tubular intermediate output shaft 32 and thence to the output shaft 24 of the system.

The transition from high mode to low or Vice versa can be carried out on the so-called "synchronous mode", in which the gearbox works when the intermediate output shaft 22 running from the mixed epicycle gear mechanism E1, and the second tubular intermediate output shaft 32, coming from the second mixed epicycle gear mechanism E2, rotate with the same (or virtually the same) speed. In order to change the mode engages the clutch of the new regime, resulting in both clutches simultaneously engage for a short time, the click coupling of the old regime out of the engagement.

It should be noted that at the low mode, the only gears that actively engage in mixed epicycle gearing E1 will be the planetary gears P1 and PN1, thus minimizing losses that arise in mixed epicycle gearing E1, in particular, on the recirculation mode power. When working at high gearing not more than transmissions according to the prior art. However, it should also be noted that the present invention allows the use of mixed epicycle gear E1, which has no ring or epicycle gears. This not only reduces the weight of the gearbox, but also provides the best flexibility in the selection of the relative sizes of the planetary gears P1, RH and RU1. This, in turn, reduces the velocity components and to reduce the number of links to a minimum.

The example embodiment of figure 2 is very similar to the example of figure 1, the only significant difference is the location of the brake element low mode. The elements of the example embodiment of figure 2, corresponding elements of the example embodiment of figure 1 indicated by the same reference numbers, and will be described only the differences in construction.

The differences relate to the second epicyclical the mu transmission mechanism, denoted E2' in figure 2. Planetary gears P2 and R identical to the corresponding elements of the first example embodiment, but the sun wheel 36' is attached to the housing 40 of the transmission. The drive from the second tubular intermediate output shaft 32' is continuously taken from the carrier C2 and selectively attaches to the output shaft 24 of the system through the low coupling regime L'.

The example embodiment of figure 2 has the advantage that, when the low coupling regime L' unlinked, the second epicycle gear E2' down completely from the output shaft 24 of the system (in contrast to the first example embodiment, where the intermediate output shaft 32 is always coupled with the output shaft 24 of the system and, therefore, any problem that arises in the second epicycle gear mechanism during operation at high mode is not transmitted to the output shaft 24 of the system.

The invention is not limited to the details above described examples of embodiment. In particular, can be used with other types of variable-speed drives, which differs from the described type. Moreover, the size of the gears can be modified for specific circumstances. For example, in the described embodiments the sun wheel S1 epicycle gear mechanism has the same size as the output sun wheel S2. However, instead of t the th, to have one size, S1 may be greater or less than S2, if necessary.

1. Multimode transmission system with a continuously variable gear ratio, containing coaxial input and output shafts of the system, the transmitting unit continuously variable transmission (CVT), is coaxially attached to the input shaft of the system and having a coaxial output shaft of the variator, and mixed epicycle gear mechanism having an input sun wheel with the drive attached to the output shaft of the variator, drove with the drive attached to the input shaft of the system and the first planetary gear (planetary gear)mounted on a drive rod and drive meshed with the input sun wheel, and the first planetary gear causes the first the intermediate output shaft, which is coaxial with the input shaft of the system, and the first planetary gear provides the supply power to the second epicycle gear mechanism, wherein the first intermediate output shaft selectively connected to the output shaft of the system through the first clutch when a highly sensitive operation of the transmission, and the second gear has an output that is selectively connected to the output shaft of the system is s through the braking element when nishijima the operation of the transfer.

2. The transmission system according to claim 1, characterized in that the first intermediate output shaft includes a sun wheel, which is provided in the first planetary gear mixed epicycle gear mechanism.

3. The transmission system according to claim 2, characterized in that the sun wheel on the output shaft is the same size as that of the input sun wheel.

4. The transmission system according to claim 1, characterized in that the axis of the planetary gears mixed epicycle gear mechanism carries a second planetary gear that rotates together with the first planetary gear and causes the first intermediate output shaft.

5. The transmission system according to claim 2, characterized in that the axis of the planetary gears mixed epicycle gear mechanism carries a second planetary gear that rotates together with the first planetary gear and causes the first intermediate output shaft.

6. The transmission system according to claim 3, characterized in that the axis of the planetary gears mixed epicycle gear mechanism carries a second planetary gear that rotates together with the first planetary gear and causes the first intermediate output shaft.

7. The transmission system according to claim 4, characterized in that the second planetary is update wheel is the same size, as the first planetary gear.

8. The transmission system according to claim 5, characterized in that the second planetary gear has the same size as the first planetary gear.

9. The transmission system according to claim 6, characterized in that the second planetary gear has the same size as the first planetary gear.

10. The transmission system according to claim 4, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input power to the second epicycle gear mechanism.

11. The transmission system according to claim 5, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input power to the second epicycle gear mechanism.

12. The transmission system according to claim 6, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input powerfully the TB for the second epicycle gear mechanism.

13. The transmission system according to claim 7, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input power to the second epicycle gear mechanism.

14. The transmission system of claim 8, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input power to the second epicycle gear mechanism.

15. The transmission system according to claim 9, characterized in that the axis of the first planetary gear mixed epicycle gear mechanism carries the third planetary gear that rotates together with the first planetary gear and provides input power to the second epicycle gear mechanism.

16. The transmission system according to any one of the preceding paragraphs, characterized in that the second epicycle gear mechanism includes a second input sun wheel driven mixed epicycle gear mechanism, the planetary gear, the driven second input the output sun wheel, and drove forming the output power of the second epicycle gear mechanism.

17. The transmission system according to item 16, characterized in that it contains an intermediate gear connecting the mixed epicycle gear mechanism and the second input sun wheel.

18. The transmission system according to item 16, wherein the second epicycle gear mechanism includes a second sun wheel meshed with the planetary gears of the second epicycle gear mechanism.

19. The transmission system according p, characterized in that it includes means for selectively braking the second sun gear.

20. The transmission system according to claim 19, characterized in that the brake element includes a clutch disposed between the second sun wheel and the housing of the transmission system.

21. The transmission system according p, characterized in that the sun wheel remains stationary relative to the housing of the transmission system, and the braking element includes clamping means for selectively attaching the second epicycle gear mechanism to the output shaft of the system.



 

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Drive (versions) // 2278309

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FIELD: transport engineering; vehicle transmissions.

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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.

EFFECT: perfected design owing to reduction of metal usage and complexity.

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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