RU2171930C2 - Automatic infinitely variable mechanical transmission - Google Patents

Abstract

FIELD: mechanical engineering; transport engineering; machine tool manufacture. SUBSTANCE: proposed transmission includes input shaft 1 and output shaft 2, carrier 5 with radial axles 6 on which locked internal wheels 7 and external wheels 8 of main satellites are located coaxially, auxiliary satellites 9 and additional satellites 19 which are thrown into engagement with drive central wheel 3 and driven central wheel 4 secured in transmission housing 10 by means of immovable bearing wheel 11 and movable bearing wheel 18; wheel 18 is linked with input shaft 1 by means of hollow intermediate shaft 17 and two pairs of gear wheels (15, 13 and 14, 16). Wheel 13 and 14 are secured on bearing shaft 12 mounted in transmission housing 10 in parallel with axis 0-0. Transfer and conversion of torque in wide ranges at any modes of operation are effected through braking rotation of carrier 5 with its radial axles 6 due to change in directions of vectors of moment of momentum and flywheels 20 connected with them at their simultaneous rotation around axis 0-0 and geometric axes O₁O₁ of radial axles 6 of carrier which is identical to their rotation about central point O¹ of intersection of these axes. EFFECT: extended range of variation of power gear ratio between drive and driven shafts in direct dependence on driven shaft load. 8 cl, 2 dwg

Description

 The invention relates to mechanical engineering and can be used in transport engineering, in particular in the automotive industry, and machine tool industry.

 An inertial automatic transmission is known, containing two neutral bevel gears mounted on coaxial shafts, a carrier with radial axles, located on the last satellites, carrying flywheels and interacting with the central bevel wheels, forming pairs of wheels with different gear ratios, the gears are engaged with different the central wheels are interlocked in pairs with each other and with the handwheels in at least two blocks and placed on the axles of the carrier symmetrically with respect to the transmission axis free rotation (RF patent N 2072208, IPC F H 33/10, 3/74, Bull. N 2).

 This inertial automatic transmission, capable of changing the speed of the output shaft depending on the load applied to it, has no external support (bearing on the housing) when transmitting torque, which limits the possibility of automatically changing the magnitude of the torque transmitted from the input shaft to the output shaft.

 The technical solution closest to the set of features to the claimed transmission is an inertial transmission containing a carrier with radial axles mounted with the possibility of rotation around the transmission axis, bevel gear central wheels mounted on different sides of the radial axes, mounted on coaxial drive and driven shafts, bevel gear satellites engaged with central wheels and forming pairs of wheels with the latter having different gear ratios, and the flywheels are set immersed on the radial axes drove. The transmission is equipped with a support conical gear central wheel fixed to the gear housing, mounted on the radial axles of the carrier, fixedly connected to the flywheels and engaged with the support wheel, and mounted on the carrier axes on two sides of the transmission axis, locked in two satellites, internal and external relative to the transmission axis, separately engaged with different central wheels, while the blocks of satellites and satellites with flywheels are placed independently imogo from each other around the rotation radial axes of the carrier (the Russian Federation patent N 2072715, IPC F 16 H 33/10, 3/74, 1997 YG).

 This inertial transmission reduces the efficiency and efficiency of using engine power while reducing the carrier’s rotational speed around the transmission axis, since the flywheel’s rotational speed decreases relative to the central point of intersection of the transmission and carrier axes. The transmission does not have a direct connection with the constant gear ratio of the output shaft to the input shaft if it is necessary to transfer the power flow and torque from the first of these shafts to the second shaft, which is necessary when braking the transport machine using the engine or when starting the engine by towing the transport machine.

 The present invention provides a range of automatic stepless changes in the power gear ratio between the drive and driven shafts in direct proportion to the load on the driven shaft and inversely to the speed of the driven shaft. The proposed transmission allows you to transmit torque with high efficiency in any operating mode, including when the carrier is stationary or at a minimum speed. At the same time, there is the possibility of power communication with a constant gear ratio of the driven shaft with the drive shaft in order to brake the transport machine using an engine, for example, when driving downhill or when stopping at a traffic light, as well as when starting the engine by towing the transport machine.

 The indicated technical result is achieved in that the automatic stepless mechanical transmission comprises coaxial input and output shafts, gear conical drive and driven central wheels mounted on them, and a carrier in the form of axes radial relative to the geometric axis of the transmission, on which, on different sides of the transmission axis, are arranged gear conical satellites - main and auxiliary rotations, the first of which are engaged with the central wheels, and the second - with gear conical fixed central support wheel, while the carrier is placed between the Central wheels with the possibility of free rotation on the input or output shaft, and the mass of satellites is increased, including through the use of flywheels coaxially connected to the satellites.

 According to the invention, a support shaft is arranged parallel to the transmission axis in the transmission housing, on which two gear wheels are fixed, one of which is engaged with a gear fixed to the input shaft, and the other wheel with a gear fixed to the hollow intermediate shaft, which is mounted coaxially with the input shaft and is rigidly connected to the gear conical central movable support wheel, which is meshed with additional satellites placed on the carrier’s radial axes, while ensuring POSSIBILITY rotation of the intermediate shaft and the movable support wheels in the same direction as the input shaft.

 Satellites are made with massive rims and simultaneously with the transmission of torques and rotational movements also perform the functions of flywheels.

 As a special case of execution, the satellites are rigidly coaxially connected to the flywheels placed on the radial axes of the carrier.

 Each of the main satellites is made in the form of two bevel gears rigidly coaxially connected into a single block - internal and external with respect to the transmission axis, located at different distances from the geometric axis of the transmission and engaged with different central wheels, while the gear ratios of these gearing pairs of wheels are different.

 As a special case of execution, the transmission contains two radial axes of the carrier placed on the same line, on each of which, with the possibility of independent rotation from each other, the main, additional and auxiliary satellites are placed.

 As a special case of execution, the carrier contains two pairs of radial axes perpendicular to each other and, on each of these pairs of radial axes, the main, or additional, or auxiliary satellites are placed, respectively.

 The geometric axes of the carrier’s radial axes and the geometric axis of the transmission intersect at a central point aligned with these axes.

 The transmission is equipped with a freewheel mechanism, one of the clips of which is fixed in the transmission housing, and the other clip is connected to the carrier with the possibility of rotation of the carrier only in the direction of rotation of the input shaft.

 In FIG. 1 is a general view of an automatic stepless mechanical transmission (hereinafter referred to as transmission) with a display of its elements and distinguishing features characterizing the invention. In FIG. Figure 2 shows the transmission device in the particular case of its execution with the image of only those elements that fall into the section plane perpendicular to the geometric axis of the transmission and combined with the radial axes of the carrier. In this case, a variant of the device without the use of flywheels is shown.

 The transmission contains coaxial input 1 and output 2 shafts, gear wheels mounted on them, bevel driving 3 and driven 4 central wheels, and carrier 5 with axles 6 radial relative to the geometric axis of the O-O transmission, on which axles are placed on different sides from the O-O axis of the transmission rotary gear conical satellites - the main satellites, consisting of interlocked internal 7 and external 8 relative to the O-O axis of the wheel transmission, and auxiliary satellites 9. The main satellites 7, 8 are engaged respectively with the leading 3 and driven with 4 central wheels. Auxiliary satellites 9 are in engagement with a fixed fixed gear wheel 11. The carrier 6 with its radial axles 6 is placed between the central drive 3 and the driven 4 wheels with the possibility of free rotation on the input 1 or output 2 shaft, for which one of of these shafts, the carrier carrier lengthens accordingly.

 Parallel to the O-O axis of the transmission, a support shaft 12 is placed in the transmission housing 10, on which two gears 13 and 14 are fixed, one of which 13 is engaged with the gear 15 mounted on the input shaft 1, and the other wheel 14 is engaged with a gear wheel 16 mounted on a hollow intermediate shaft 17, which is mounted coaxially with the input shaft 1 and is rigidly connected to the gear conical central movable support wheel 18, which is meshed with additional conical additional axles 6 of the carrier 5 satellites 19. In this case, it is possible to rotate the intermediate shaft 17 and the movable support wheel 18 in one direction with the input shaft 1.

 Satellites 7, 8, as well as 9 and 19 are made with massive rims, providing them with the ability to perform flywheel functions simultaneously with the transmission of torques and rotational movements.

 As a special case of execution, the auxiliary 9 and additional 19 satellites are rigidly coaxially connected with the flywheels placed on the radial axes 6 of the carrier.

 Each of the main satellites is made in the form of two bevel gears rigidly coaxially connected into a single block - internal 7 and external 8 relative to the transmission axis O-O, located at different distances from the geometric axis O-O of the transmission and correspondingly engaged with different central wheels - leading 3 and driven 4. At the same time, the gear ratios of these engaging pairs of wheels 3, 7 and 8, 4 are different.

 As a special case of execution, each of the main satellites is a single bevel wheel, which is meshed simultaneously with the driving 3 and driven 4 central wheels. This simplifies the transmission device, but at the same time reduces the possibility of changing the magnitude of the transmitted torque.

Referring to FIG. 1 transmission contains two radial axes 6 of carrier 5, placed on one line O ₁ -O ₁ diametrical with respect to the axis O-O of transmission. On each radial axis 6, with the possibility of independent rotation from each other, the main 7, 8, additional 19 and auxiliary 9 satellites are placed.

 As a special case of execution, shown in the image of FIG. 2, carrier 5 contains two pairs of radial axes 6 perpendicular to each other and on each of these pairs of radial axes the main 7, 8, or auxiliary 9, or an additional 19 satellites are placed. The relationship of these satellites with other transmission elements does not differ from the main version of the transmission device.

The geometric axis O-O transmission and the geometric axis O ₁ -O _{1 of the} radial axes 6 of carrier 5 intersect at a central point O ¹ combined with these axes.

 The transmission is equipped with a freewheel 21, one of the cages of which is fixed in the transmission housing 10, and the other cage is connected by means of a connecting element 22 with the radial axles 6 of the carrier 5 to allow the carrier to rotate freely in the direction of rotation of the input shaft 1 and prevent rotation in the direction of rotation output shaft 2.

 Automatic stepless mechanical transmission operates as follows.

 For the initial position it is assumed that the input shaft 1 rotates at a constant frequency and transmits an unchanged torque. The gear ratios of the pairs of gears 15, 13 and 14, 16 provide the rotation of the intermediate shaft 17 and the movable support wheel 18 with a higher frequency compared to the input shaft 1.

When the input shaft 1 is rotated together with the driving central wheel 3 mounted on it and the stationary output shaft 2 with the driven central wheel 4 mounted on it in connection with the load applied to this shaft or the beginning of rotation from a fixed position, the outer wheel 8 of the main satellite is coaxially connected with the inner wheel 7 of the main satellite rotating around the axis O ₁ -O ₁ with a maximum frequency, it rolls around the stationary driven central wheel 4 and the entire block of each main satellite 7, 8 drives the water silt 5 with its radial axes 6 around the axis O-O transmission. The carrier rotates in the direction of rotation of the input shaft 1 with the maximum frequency.

 Together with the radial axes 6 of the carrier, auxiliary 9 and additional 19 satellites and flywheels 20 coaxially interlocked with them rotate around the O-O axis of the transmission.

Auxiliary satellites 9 run around on a fixed support wheel 11 and rotate together with the flywheels simultaneously around the transmission axis O-O and the axis O ₁ -O _{1 of the} radial axles 6 of the carrier, which is equivalent to their rotation relative to the central point O ^{1 of the} intersection of these axes. In this case, the rotation frequency of the auxiliary satellites 9 around the O-O and O ₁ -O ₁ axes and relative to the central point O ¹ is maximum.

However, the movable support wheel 18 by means of two pairs of gears 15, 13 and 14, 16 connected to the input shaft 1 is rotated in the same direction as the input shaft 1. The gear ratios of the two gear pairs 15, 13 connected to the support shaft 12 and 14, 16 provide rotation of the intermediate shaft 17 and the movable support wheel 18 with a higher frequency compared to the carrier 5. In this case, additional satellites 19 and the associated flywheels 20 rotate around the radial axes 6 of the carrier 5, and therefore relative to the central point O ¹ .

From the foregoing, it follows that with a fixed output shaft 2 and a maximum speed of carrier 5, the block of wheels 7, 8 of the main satellites and auxiliary satellites 9 with their flywheels 20 rotate with respect to the central point O ¹ with a maximum frequency. At the same time, under the indicated conditions, additional satellites 19 with their flywheels 20 rotate with respect to the central point O ¹ with a minimum frequency.

It is known that a rotating body has a certain moment of momentum, which manifests itself in compliance with the fundamental universal physical conservation law, according to which the moment of momentum can only be changed under the influence of external forces. It is also known that the angular momentum during rotation of the body relative to the point is a vector quantity and the direction of the vector coincides with the direction of the axis of rotation of the body itself, in this case, with the direction of the axis O ₁ -O ₁ carrier, perpendicular to the axis O-O transmission. But since the axis O ₁ –O _{1 of the} carrier rotates around the O – O axis of transmission and relative to the central point O ^{1 of the} intersection of these axes, the direction of the moment vectors of the momentum of the satellites and flywheels is constantly changing.

 It is known that actions on vectors are a reflection of the corresponding actions on vector quantities, and vector quantities are equal if their numerical values and directions coincide. Based on this, under the above conditions of rotation of the satellites and flywheels relative to two axes at the same time, their angular momenta are forced to change under the influence ultimately from the torque transmitted by the input shaft 1 and the moment of resistance applied to the output shaft 2. The manifestation of the law conservation counteracts the rotation of the axles 6 of the carrier 5 around the axis O-O transmission, which tend to maintain their stable position. In this regard, the axles 6 of the carrier are supports for transmitting torque from the driving Central wheel 3 to the driven Central wheel 4 and then to the output shaft 2. The magnitude of the transmitted torque depends on the amount of braking torque applied to the carrier 5, and also from the gear ratios of two pairs of engaging wheels - the leading Central wheel 3, the inner wheel 7 of the main satellite and the outer wheel 8 of the main satellite, the driven Central wheel 4.

Based on the above nature of the mechanical interaction of the transmission elements, it follows that with the beginning of rotation of the output shaft 2 and with an increase in the frequency of its rotation, the rotation of the main satellites 7, 8 and auxiliary satellites 9 with their flywheels 20 relative to the central point O ¹ with a corresponding decrease in created them braking torque applied to the carrier 5. At the same time, the rotation frequency of additional satellites 19 with their flywheels relative to the center point O ¹ increases, respectively a twofold increase in the braking torque created by them, applied to the carrier 5.

 With a stationary carrier 5 with its radial axles 6, the driven central wheel 4 will rotate with a maximum frequency depending on the gear ratios of the engaging pairs of wheels 3, 7 and 8, 4. The locked wheels 7, 8 of the main satellites and auxiliary satellites 9 with their flywheels 20 will be at the same time create the minimum braking torque, and the additional satellites 19 with their flywheels 20 - the maximum braking torque, applied to the carrier 5 with its radial axes 6.

 Therefore, the described transmission will reliably transmit torque at any ratio in the rotational speeds of input 1 and output 2 shafts. This automatically converts the transmitted torque and changes the speed of the output shaft 2 depending on the load applied to it due to the fact that the rotational speed of the carrier 5 with its radial axes 6 around the transmission axis O-O are inversely related to the rotational speed output shaft 2.

 It is known that the magnitude of the angular momentum of a rotating body depends on its mass, the distance of this mass from the axis or point of rotation and the speed of rotation. This determines the ability to create gears with various specified parameters by using satellites 7, 8, 9, 19 and flywheels 20 differing in size and mass and using various gear ratios used in the transmission of gear pairs.

 In the particular case of the transmission shown in FIG. 2, when carrier 5 contains two pairs of radial axes 6 perpendicular to each other, the interaction of the satellites 7, 8, 9, 19 included in the transmission with other transmission elements does not differ from the above description, since all power and kinematic connections of the transmission elements remain without changes.

 When transmitting with massive satellites and without using the flywheels, the nature of its operation does not change compared to the above, since the satellites perform the functions of the flywheels.

 Given in the description and claims, other special cases of its implementation allow to specify the device taking into account the specified design features. However, the above nature of the transmission does not change.

 If necessary, the transmission of torque and rotation from the output shaft 2 to the input shaft 1 in order to brake the working machine, the engine stops. In this case, under the influence of the torque transmitted from the output shaft to the input shaft, the free-wheeling mechanism 21 is closed, which, by means of the connecting element 22 and if there is support on the transmission housing 10, does not allow the carrier 5 to rotate in the direction of rotation of the output shaft 2, which ensures reliable transmission of power flow with a constant power transmission ratio using the driven central wheel 4, the main satellites 8, 7 and the driving central wheel 3 on the input shaft 1 and e - to the engine, the forced rotation of the shaft of which leads to braking of the working machine. In the same way, the engine is started using towing a working machine.

Claims (8)

 1. An automatic stepless mechanical transmission containing coaxial input and output shafts, gear conical drive and driven central wheels mounted on them, and a carrier in the form of axes radial relative to the transmission geometry axis, on which gear conical gears are rotatably mounted on different sides of the transmission axis - main and auxiliary, the first of which are engaged with the central wheels, and the second with a conical fixed central gear fixed in the transmission housing with a support wheel, while the carrier is placed between the central wheels with the possibility of free rotation on the input or output shaft, and the mass of satellites is increased, including through the use of flywheels coaxially connected to the satellites, characterized in that the support shaft is parallel to the transmission axis in the transmission housing on which two gears are fixed, one of which is engaged with a gear mounted on the input shaft, and the other with a gear mounted on the floor of the intermediate shaft, ing mounted coaxially with the input shaft and is rigidly connected with a toothed conical central movable support wheel being in engagement with the axes arranged on radial carrier additional satellites, thus it is possible rotation of the intermediate shaft and the movable support wheels in the same direction as the input shaft.  2. The transmission according to claim 1, characterized in that the satellites are made with massive rims and simultaneously with the transmission of torques and rotational movements also perform the functions of flywheels.  3. The transmission according to claim 1, characterized in that, as a special case of execution, the satellites are rigidly coaxially connected to the flywheels placed on the radial axes of the carrier.  4. The transmission according to claim 1, characterized in that each of the main satellites is made in the form of two bevel gears rigidly coaxially connected into a single block - internal and external with respect to the transmission axis, located at different distances from the geometric axis of the transmission and engaged with different central wheels, while the gear ratios of these engaging pairs of wheels are different.  5. The transmission according to claim 1, characterized in that, as a special case of execution, the transmission contains two radial axes of the carrier located on the same line, on each of which, with the possibility of independent rotation from each other, the main, additional and auxiliary satellites are placed.  6. The transmission according to claim 1, characterized in that, as a special case of execution, the carrier contains two pairs of radial axes perpendicular to each other and, on each of these pairs of radial axes, the main, or additional, or auxiliary satellites are respectively placed.  7. The transmission according to claim 1, characterized in that the geometric axes of the carrier’s radial axes and the geometric axis of the transmission intersect at a central point aligned with these axes.  8. The transmission according to claim 1, characterized in that it is equipped with a freewheel mechanism, one of the clips of which is fixed in the transmission housing, and the other clip is connected to the carrier with the possibility of rotation of the carrier only in the direction of rotation of the input shaft.

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