RU2171931C2 - Sutomatic infinitely variabe 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 in which coaxial locked internal wheels 7 and external wheels 8 of main satellites 9 and additional satellites 18 which are thrown into engagement with drive central wheel 3 and driven central wheel 4 located on one side from carrier 5 secured in housing 10 of transmission by means of immovable bearing heel 11 and movable bearing ring 17 which is linked with input shaft 1 by means of hollow intermediate shaft 16 mounted coaxially relative to input shaft 1 and three gear wheels 15, 13, 14 for rotation relative to input shaft in opposite direction. Wheel 13 is secured on bearing shaft 12 in transmission housing 10 in parallel with axis 0-0. Transmission and conversion of torque in wide ranges and at any modes of operation are effected through braking rotation of carrier 5 with its radial axles 6 due to change in direction of vector of moment of moment of all satellites and flywheels 19 connected with them at their simultaneous rotation around axis 0-0 of transmission and geometric axes 0₁-0₁ of radial axles 6 of carrier which is identical to rotation relative to central point 0¹ of intersection of these axes. EFFECT: extended range of gear ratio between input and output shafts in direct dependence on output shaft load. 9 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 transmission is known, comprising a carrier with radial axles, mounted on them and interlocked by two satellites made of bevel wheels, and carrying flywheels, central conical wheels located on one side of the radial axes, each of which interacts with the corresponding satellite to form the latter conical pairs with different gear ratios. In this transmission, the driven and driving shafts are connected by a freewheeling mechanism, the driving element of which is mounted on the driven shaft, and the driven element on the driving shaft. The flywheel functions are also performed by satellite blocks, for which they are massive (RF patent N 2072717, IPC 6 F 16 H 33/10, 3/74, 01.27.97, Bull. N 3).

 This inertial 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 amount of torque transmitted from the drive shaft to the driven shaft.

 The technical solution closest to the set of features to the claimed transmission is an inertial transmission, comprising a housing, coaxial drive and driven shafts mounted on the latter drive and driven central bevel gears, mounted with the possibility of rotation around the transmission axis of the carrier with radial axes, on which rotation set satellites with flywheels. The gear is equipped with a support gear rigidly connected to the housing, engaged with gears carrying flywheels, and locked in two gears, internal and external relative to the gear axis, for gearing with different central bevel gears and constituent pairs of bevel wheels having different largest gear ratios. The drive and driven bevel gears are located on one side of the carrier’s radial axes, and the satellite blocks and satellites with flywheels are located on the carrier’s radial axes with the possibility of independent rotation.

 The driving and driven shafts are connected by a free-wheeling mechanism, the driving clip of which is connected with the driven shaft, and the driven shaft is connected with the driving shaft (RF patent N 2072716, IPC 6 F 16 H 33/10, 3/74, 01.27.97, Bull. N 3 )

 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 present invention provides a widening range of automatic stepless changes in the power gear ratio between input and output shafts in direct proportion to the load on the output shaft and inversely to the speed of the output 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.

 The indicated technical result is achieved in that the automatic stepless mechanical transmission comprises coaxial input and output shafts, the leading and driven central bevel gears mounted on these shafts, mounted with the possibility of rotation around the transmission axis of the carrier with radial axes, on which the axes are mounted symmetrically with rotation satellite transmissions - main and auxiliary, the main satellites are made in the form of interlocked two bevel gears - internal and external relative to the transmission axis, engaged with different central bevel gears and constituting pairs of bevel wheels having different gear ratios, a gear conical central fixed support wheel rigidly connected to the gear housing, engaged and engaged with auxiliary satellites, leading and driven the central bevel gears are located on one side of the carrier’s radial axes, and the blocks of the main satellites and auxiliary satellites are placed on axes drove with the possibility of independent rotation from each other. According to the invention, in the transmission housing, in the plane aligned with the transmission axis, a support shaft is placed on which a gear is fixed, engaged in engagement with two gears, one of which is fixed to the input shaft, and the other wheel is fixed to the hollow intermediate shaft, which is mounted coaxially with the input shaft and on it a gear conical central movable support wheel is fixed, which is meshed with additional satellites located on the carrier’s radial axes, while ensuring Maintaining input and intermediate shafts in opposite directions.

 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 with the flywheels placed on the radial axes of the carrier.

 As a special case of execution, the transmission contains two radial axes of the carrier located on the same diametrical 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, main or additional, or auxiliary satellites, respectively, are rotated independently of each other.

 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 input and output shafts are connected by a freewheeling mechanism, the leading element of which is connected to the output shaft, and the driven element is connected to the input shaft.

 As a special case of execution, the support shaft is placed parallel to the transmission axis, a cylindrical gear is fixed on it, engaged in gearing with gears, one of which has internal gearing, and the other wheel is external gearing.

 As a special case of execution, the support shaft is placed at an angle to the transmission axis, for example at a right angle, and a bevel gear is fixed on it, engaged with bevel gears, one of which is fixed to the input shaft, and the other wheel is fixed to the intermediate hollow shaft.

 In FIG. 1 is a general view of an automatic stepless mechanical transmission (hereinafter referred to as “transmission”) showing its elements and distinctive 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, the central 3 bevel gears driven and the driven 4 driven by them, and the carrier 5 mounted with the possibility of rotation around the transmission axis OO, carrier 5 with radial axes 6, on which the satellite transmission axis are symmetrically rotated, the main 7, 8 and auxiliary 9. The main satellites are made in the form of interlocked two bevel gears - internal 7 and external 8 relative to the axis OO transmission. The inner wheels 7 of the main satellites are engaged with the driving central wheel 3, and the outer wheels 8 of the main satellites are meshed with the driven central wheel 4, and these pairs of bevel wheels have different gear ratios. The gear conical central fixed support wheel 11 is rigidly connected to the gear housing 10 and is engaged with the auxiliary satellites 9. The driving 3 and driven 4 central wheels are located on one side of the radial axes 6 of the carrier 5, facing the output shaft 2. Blocks of the main satellites 7 , 8 and auxiliary satellites 9 are placed on the radial axes 6 of the carrier with the possibility of independent rotation from each other.

 In the transmission housing 10, in a plane aligned with the transmission axis OO, a support shaft 12 is placed on which a gear 13 is fixed, engaged in engagement with two gears 14 and 15, one of which 14 is fixed to the input shaft 1, and the other wheel 15 fixed on the hollow intermediate shaft 16, which is installed coaxially with the input shaft 1. At the other end of the intermediate shaft 16, facing the carrier 5, a gear conical central movable support wheel 17 is fixed, which is engaged with radial axles 6 yl additional satellites 18. This ensures rotation of the input shaft 1 and the intermediate shaft 16 in opposite directions.

 Satellites 7, 8, 9 and 18 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 9 and 18 are rigidly coaxially connected to the flywheels 19 placed on the radial axes 6 of the carrier.

As a special case of execution, the transmission contains two radial axles 6 of the carrier located on the same axial axial line O ₁ -O ₁ , on each of which, with the possibility of independent rotation, the main 7, 8, additional 18 and auxiliary 9 satellites are placed.

 As a particular embodiment shown in 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 additional 18, or auxiliary 9 satellites are rotated independently of each other, respectively.

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

 The input 1 and output 2 shafts are connected by a freewheel 20, the leading element of which is connected with the output 2, and the driven element is connected to the input shaft 1.

 As a particular embodiment shown in FIG. 1, the support shaft 12 is arranged parallel to the axis OO of the transmission and a cylindrical gear 13 is fixed thereon, engaged with gears 14, 15, one of which 14, mounted on the input shaft 1, has internal gearing, and the other wheel 15, fixed on the intermediate shaft 16 - external gearing.

 As a special case of execution, the support shaft is placed at an angle, for example, at a right angle, to the transmission axis OO, and a bevel gear is fixed thereon, engaged with bevel gears, one of which is fixed to the input shaft 1, and the other wheel is fixed on the hollow countershaft 16.

 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 three gears 13, 14, 15 in engagement provide rotation of the input shaft 1 and the intermediate shaft 16 in opposite directions.

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 the stationary position, each outer wheel 8 of the main satellite is coaxial associated with the corresponding inner wheel 7 of the main satellite rotating around a radial geometric axis O ₁ -O ₁ , it rolls around the stationary driven central wheel 4 and the entire block of each main satellite 7, 8 drives carrier 5 with its radial axes 6 about the axis OO of transmission. The carrier 5 thus rotates with a maximum frequency in the opposite direction with respect to the rotation of the input shaft 1.

 Together with carrier 5 and its radial axes 6, auxiliary 9 and additional 18 satellites rotate around the O-O axis of the transmission and the locked flywheels 19 coaxially with them.

Auxiliary satellites 9 are run around on a fixed support wheel 11 fixed in the transmission housing 10 and rotate together with the flywheels 19 simultaneously around the transmission axis OO and the axis O ₁ -O _{1 of the} carrier radial axes 6, which is equivalent to their rotation relative to the central point O ^{1 of the} intersection of these axes. Moreover, the speed of the auxiliary satellites 9 around the axes OO and O ₁ -O ₁ and relative to the central point O ¹ is maximum.

However, the movable support wheel 17 through the gears 13, 14, 15 connected to the input shaft 1 and the intermediate shaft 16 is rotated in the opposite direction with respect to the rotation of the input shaft 1. The gears 14, 13, 15 together provide the gear ratios rotation of the intermediate shaft 16 and the movable support wheel 17 with a higher frequency compared to the rotation frequency of the carrier 5 with its radial axes 6 about the transmission axis OO under these conditions, i.e. with the fixed driven wheel 4 and the output shaft 2. In this case, additional satellites 18 and the associated flywheels 19 rotate around the radial axes 6 of the carrier, and therefore, relative to the central point O ¹ , with a minimum frequency, since carrier 5 with its radial axes 6 rotates with maximum frequency in one direction with a movable support wheel 17.

From the foregoing, it follows that with a fixed output shaft 2 and maximum speed of carrier 5, the block of wheels 7, 8 of the main satellites and auxiliary satellites 9 with their flywheels 19 rotate with respect to the central point O ¹ with a maximum frequency. At the same time, under the indicated conditions, additional satellites 18 with their flywheels 19 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, the direction of the axis O ₁ -O ₁ drove, perpendicular to the axis OO transmission. But since the axis O ₁ -O _{1 of the} carrier rotates around the axis OO of the 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 OO transmission, which tend to maintain their stable stationary 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 from the gear ratios of two pairs of engaging wheels - the driving 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 19 relative to the central point O ¹ with a corresponding decrease in the the braking moment of the force applied to the carrier 5. Simultaneously, the rotation frequency of the additional satellites 18 with their flywheels relative to the central point O ¹ increases, respectively the increasing 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 19 will be at the same time create a minimum braking torque, and additional satellites 18 with their flywheels 19 - 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 speeds of the carrier 5 with its radial axes 6 around the transmission axis OO are inversely dependent on the speed of the 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, 18 and flywheels 19 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, 18 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, a free-wheeling mechanism 20 is closed, which ensures the transmission of power flow from the output shaft 2 to the input shaft 1 and further to the engine, the forced rotation of the shaft of which leads to braking of the working machine. The engine is started in the same way by towing a transport vehicle.

Claims (9)

 1. An automatic stepless mechanical transmission containing coaxial input and output shafts, drive and driven central bevel gears mounted on these shafts, mounted with the possibility of rotation around the transmission axis of the carrier with radial axes on which satellites are mounted symmetrically with rotation axis, the main and auxiliary, main satellites are made in the form of interlocked two bevel gears, internal and external, relative to the transmission axis, engaged with different central bevel wheels and constituent pairs of bevel gears having different gear ratios, a gear conical central fixed support wheel is rigidly connected to the gear housing, engaged with auxiliary satellites, the driving and driven central bevel gears are placed one at a time side of the carrier’s radial axes, and the blocks of the main satellites and auxiliary satellites are placed on the carrier’s radial axes with the possibility of independent g rotation from each other, characterized in that in the transmission housing in a plane aligned with the transmission axis, a support shaft is placed on which a gear is fixed, engaged in engagement with two gears, one of which is fixed to the input shaft, and the other to hollow intermediate shaft, which is installed coaxially with the input shaft and fixed to it a gear conical central movable support wheel, which is meshed with additional satellites placed on the radial axes of the carrier, while ensuring rotation of the input and intermediate shafts in opposite directions.  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, as a special case of execution, it contains two radial axes of the carrier located on the same diametrical line, on each of which, with the possibility of independent rotation from each other, main, additional and auxiliary satellites are placed.  5. 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 rotations are independently independent of each other, or auxiliary satellites.  6. 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.  7. The transmission according to claim 1, characterized in that the input and output shafts are connected by a freewheeling mechanism, the driving element of which is connected to the output shaft, and the driven element is connected to the input shaft.  8. The transmission according to claim 1, characterized in that, as a special case of execution, the support shaft is parallel to the transmission axis, a cylindrical gear is fixed thereon, engaged in engagement with the gears, one of which has internal gearing, and the other wheel external gearing.  9. The transmission according to claim 1, characterized in that, as a special case of execution, the support shaft is placed at an angle to the transmission axis, for example at a right angle, and a bevel gear is engaged on it, engaged with bevel gears, one of which are fixed on the input shaft, and the other on the hollow intermediate shaft.

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