The present invention is about infinitely variable U transformational transmission with high torque (hydraulic fluid converter) that is used in machinery sector. Known State of the Technology

Mathematical addition and subtraction transaction being used deferantially within existant mechanics undoubtedly has caused radical changes in the automotive sector.

The reason being, the ideal distribution of the engine power was not possible under straight conditions for turning on the wheels of the vehicle until then. Although it can be argued that the abacus mathematical addition is a mechanical counterpart, the situation is not so controversial for the axel gear.

Today, the axel gear is used in almost every wheeled vehicle. Another transport that is inevitably used in every vehicle, such as an axel gear, is gearbox or transmission. There is an important similarity between the transmission and the axel gear. This similarity is where axel gear machining is the perfect mechanical application of the mathematical addition and subtraction process, while the transmission is the mechanical application of the mathematical multiplication-division process. But even though the axel gear is a perfect fit, it is not the same when it comes to the transmission. The perfect transmission is possible with the perfect mechanical application of the mathematical multiplication- division process, which is still a matter of research from Leonardo Da Vinci to this day.

There are 3 terms in mathematical multiplication. Terms are multiplier, multiplicand and result or product. The multiplier and multiplicand are input and result or the product is an output term. The process has some basic features. These features are actually expected to be found in a transmission. 1- If the multiplier and the multiplicand numbers are fixed than the result is also fixed. At least one of the multiplier or multiplicand numbers must change for the product to change.

2- The input terms multiplier and multiplicand are the set of real numbers. There are infinite numbers of values between any two integers in the real number set.

3- An element that is an absorving element is the number "0” (zero). If multiplier or multiplicand is zero, than the result is also“0” (zero).

4- If only one of the terms as multiplier or multiplicand is a negative number, than the result would also be negative.

5- When this process is done, multipication would be done.

6- The multipication process could be done in reverse. This process will give the division.

As taking up the basic features above and considering the types of transmissions used today,;

Classic or Automatic Transmission;

The speed of the wheel axle is constant unless the engine revolutions or a gear is changed for constant engine revolutions while driving on a fixed gear. Whether classic or automatic, the neutral gear state in the transmission changes this regulation. In automatic transmission, the rule also changes when using the brake to stop while driving. The reason being, while the gear value is in neutral and the motor rotates, the wheel axle is not rotating. Even if there is no turning movement, some power is constantly transmitted to the wheel axle. Once the break is released, the vehicle tends to move. In the classic transmissions this case emerges as partial clutch situation at first movement.

“0” (zero) could be taken the multiplicand value“0” (zero) does not determined If you can get the multiplied value of "0" (the motor has stopped), a zero value for the multiplier is not defined. It is not a zero state for neutral gear shifting. Because the product (wheel shafts) can take any value while the gear is idle. This is just a disconnection and there is no such thing in mathematical multiplication. It is therefore not possible to use a swallowing element of zero in such gearboxes. The negative value of the multiplier is considered a reverse gear. Since the reversal of internal combustion engines, which has the most widespread use in automotive technology, there is no need to investigate whether the term can be negative. It is therefore not possible to use the feature of being a swallowing element of zero in such gearboxes. The negative value of the multiplier is considered as reverse gear. Since the reversal of internal combustion engines, which have the most widespread use in automotive technology, is not practical, there is no need to investigate whether the term can be negative.

The multiplicand can get“0” (zero) value (as the motor has stopped) multiplier is not determined as a zero. Neutral gear, is not in a zero position. Because the result, (wheel axel) can take any value while the gear is in neutral position. This is just a disconnection situation and there is no such thing in mathematical multiplication. It is therefore not possible to use the feature of being an absorving element as zero in such transmissions.

The negative value of the multiplier is considered as reverse gear. Since the reversal of internal combustion engines, which have the most widespread use in automotive technology, is not practical, there is no need to investigate whether the multiplier term can be negative.

CVT (Continuously Variable Transmission) Transmission

Since it is a more accurate expression for a constant gear or CVT transmission, the speed of the wheel axel is ideally fixed unless the engine revolutions or the transmission rate is changed while driving with a constant "transfer rate". Here, particularly the term “ideally" is used in particular. The situation is not real, but ideally fixed.

Because, the CVT transmission is powered by a friction-based transmission element, not by a gear mechanism. This is one of the most fundamental problems of known CVT transmissions and limits the transferable power to a great extent. In addition, the neutral state of the CVT transmission and the first move of the vehicle make the mutual stability rule out. The multiplicand (selected transfer rate) value cluster, as well as the multiplier (motor axel) value set, consists of real numbers. However, the transmission rate that can be selected in known CVT transmissions is defined from a certain distance from zero. The multiplier, that is, the transfer rate can never be zero, can not be close to zero. Again, a clutch mechanism works between this particular range and zero. Therefore, it is not possible to use absorvant element of zero in CVT transmission as well. It is not possible for the term multiplier to be directly negative as a transfer rate. For this reason, the reverse gear is achieved by an additional mechanism. Fluid-based transmission with propeller changing in line angle

This type of gearbox has been developed for applications where motor shaft speed is often kept high and where the performance is more important. Only in some racing cars, power transmission is provided through a fluid between the input and output shafts. It can not be said that the speed of the wheel shaft is constant unless the engine revolution is changed while traveling with a constant "transfer rate" or the transmission ratio is changed for a constant engine revolution. The shaft propellers loose fluid highly due to friction in contact with the fluid. For this reason, it can not be used in many applications where the system efficiency is more important.

The multiplicand (selected transfer rate) value cluster, as well as the multiplier (motor shaft) value set, consists of real numbers. The multiplying factor can be zero. However, since this situation does not allow the wheel speed to be zero, that is to say, it is not possible to use the feature that the zero number is an absorvent element in such transmissions. It is possible that the multiplier term is directly negative as a transfer rate. However, the system is not successful at power transmission at near zero and negative transmission ratios.

Piston and oil-based hydraulic transmission; This type of transmission has been developed for applications where the speed is less important than the performance of the motor shaft. Power transmission in the system, which is usually used on work machines, is provided by pumping a fluid between the inlet and outlet shafts. Hydraulic pumping with a rotational motion and producing a return motion from the pneumatic hydraulic pump are made by means of pistons. The transition function is not really a multiplication operation, but as the number of pistons it comes closer to a multiplication transaction.

The speed of the wheel shaft is constant unless the engine revolutions change while traveling with a constant "transmission rate" or the transmission rate is changed for a constant engine revolt. Fluid losses occur during the pumping of the fluid, along the pipes, and during the turning of the flow into a mechanical action, are high Increasing the operating speed greatly increases the losses. For this reason, it is not possible to use them where the system efficiency and certain operation speed more important.

The multiplier (selected transfer rate) value cluster, as well as the multiplicand (motor axel) value set, consists of real numbers. The multiplying factor can be zero. When the transfer rate reaches zero, the output shaft does not rotate and can not be rotated. This could be achived perfectly as the zero being the absorvent element. It is possible that the multiplier element tobe negative as a transfer rate. In this case, the output shaft rotates directly in the opposite direction.

Moving from the comparison made; piston and oil-based hydraulic transmission are somewhat closer to mathematical multiplication among others. Without the disadvantages already explained, the automotive sector would have shifted directly to this direction. CVT designs have been used by several companies in some models, but have not been able to make a difference as an axel gear due to the reasons that will be explained below.

The systems referred to as IVT (Infinitely Variable Transmission) are not mentioned above because they have not yet found any field of use where high powers are transmitted. The only difference between IVT and CVT is; a negative value to a positive value, can work in a range including the zero state. In this sense, there are quite a number of designs available (disc, bulk, strap, etc.). In practice, an IVT can also be produced using 2 CVT and an axel gear. The IVT carries almost all the properties described above for the multiplication process. For this reason, the system which is subject to this patent study (UIVT) is also called IVT. In addition to carrying the above features of mathematical multiplication, it is still a continuing effort to produce system that efficiently would work with high power transfer and componants would stand to attrition and be a long-lasting, low-cost, system that can operate efficiently over a wide range of operating speeds. When such a system is produced; using a car will be much simpler and easier, much more economical and would have more performance. Systems that generate electricity from wind energy would be more efficient, and industrial machinery will work more effectively.

The most basic difficulty of loading the ideal properties of a mathematical multiplication process into a mechanical system is the fact that the properties expected from the system do not quite match the solid state structure of the material. Mathematical multiplication on real numbers is analog (seamless) and ideal. To achieve this, it is necessary to place a multiplier element which provides analog control between the speed of an input shaft and the output shaft speed. Thus, the velocity of the input shaft (A) will be multiplied by the control arm setting (B), and the velocity of the output shaft will also be represented by the product term (C). When the control arm is moved to a positive position, the output will rotate at the same rate as the control shaft and at the same speed as the control arm, when the arm is moved in the negative direction, the output shaft will rotate in the reverse direction with the input shaft and again at the speed ratio of the control arm, when the arm is moved to exactly to the zero point input shaft will rotate at any desired speed without encountering any force, the output shaft will not rotate and will not be rotated (even when an external force is used). In the mechanical system, the increasing or decreasing output ramp rate, according to the control arm setting, will follow the basic physics law as decreasing and increasing force is gain. As it is known, the easiest and most efficient method of transferring mechanical power from one place to another is to use of a shaft. In this case, the power transmitted is in one ratio and in the same direction. However, if there is a change in rate or even direction, it is inevitable that the system to be designed will be more complicated and the losses will be more. For example; a multiplication operation can be performed using two gears having different diameters. But in this case, the multiplier term "transfer rate" can not be changed. The method of replacing the gears that use more gears in duplicate (the method used in classic and automatic gearboxes) convicts the multiplier term to a certain number of values. If the diameter of the running gear could be changed analogue, then the entire problem would have been solved. Unfortunately, this is not yet possible in state of solid physics.

This can be achieved by making contact with a point at a certain distance from a dicentric center, as compared to the case where the mechanical change in the mechanical systems provided by contact with each other provides the diameter change of the product. However, in this case, it is not possible that the structure is geared. In order for gear to be ratable, gear spacing of the side gear must be equal and the gear must be aligned. In this case, when the diameter changes, the range of the gear or the number of gear also changes.

Due to the reasons described above, CVT transmissions are not gears or chain structures, but belt, smooth surface transmission elements that do not have gear on the wheel are used. In a set of CVT designs, the transmission belt can be designed to accommodate the thread spacing or the metal chain structure, which can be stretched to change the length of the belt. These systems are not very common due to difficulties in production, high production costs, durability, reliability and transferable power limitations, while there are also systems that force the fit of gear using flexible gear elements. There is a major unsolvable problem with CVT transmissions. This problem is caused by limitations of transferable structural strength. Systems that increase durability in applications that require high power transfer are either too costly or inefficient. Systems, that are operated under high power without increased durability are worn out and malfunctioning in a short time. In a simple search on the internet, it can be seen that large number of vehicle owners with malfunctioning CVT transmissions have complained of high repair costs. The reason for this is hidden in the structure of the CVT. As you draw power from different diameters of a disc or a cone you can touch it along a line that is only constant in diameter. As the thickness of this contact line increases, you will approach the stmctural boundaries and you will not be able to deliver power at the desired amount. If you thicken this contact line so that it can work at higher powers, the speed will be different on both sides of the middle line, friction will occur, heat will emerge and your transmission elements will be worn out again.

This can be expressed as a boundary value problem. When a line is tangent to a circle, the size of the region it touches is expressed as "point". The point is a non-dimensional element and for this reason a sufficient amount of power can not be transferred from a point size. The area where a thick, dull surface touches a surface is referred to as a "line". The line is one-dimensional and power transfer is limited. For example, this is how the wheels of the train locomotives interact with the rail. Metal wheels roll on the track during acceleration; although they are superimposed on each other with incredible forces once the speed is increased the wheels start to wheel spin. In situation when the contact member is elastic, it makes the contact area a surface, in which case high power transfer is possible. In this case, however, losses are high, wear occurs and slippage is still possible. For example, this is the way the wheels of the car interact. Friction losses are high. A car (within its current weight) could be pushed with a touch of a human finger on a straight road, if it is put on a rail with metal wheels like a train. In addition, the tire wheel in road vehicles is an inevitable solution for different reasons. No one would want to have a car with engines and gears that had to be changed everytime between 40-50 thousand kilometers. The most efficient systems that transmit power by contacting one another are the system with gears. They can work effectively while transmitting very high forces. However, as mentioned above, IVTs with gears can not be produced by conventional methods.

An example where the contact area is a surface, and at the same times the transfer organs not using elastic material is the pressure-clutch system. The properties of the lining materials and the force of the pressure allow operation without loss and produce no-slip transmission elements. Unless the special condition known as half-clutch or mesh is occuring (for example, the clutch is never pressed or it’s not fully pressed), the pressure-clutch systems operate without loss and there is no material life problem. However, since the contact surfaces in the press-clutch systems are equally centric, there is no way or power is the reason why pressure-lined IVT can not be considered.

The problem of not speeding up to the speed of sound of propeller aircraft (because the propeller efficiency greatly decreased when the speed of the blades increased), could not be solved by making better propellers. In the supersonic airplane, a working source (reactive motor-side jet engine) is used that is completely different from the working principle propeller. It seems; making improvements in the current features of CVT and similar systems has not made the desired progress for about 50 years.

U.S. Patent No. 54409458 discloses“Hard gear infinitely variable transmission”. The rotating transmission is provided with a fixed infinitely variable transmission (IVT) in which the input shaft is driven by at least one quick return mechanism. The quick return mechanisms convert the rotational movement of the input shaft of the transmission to a variable action consisting of a close constant linear velocity section and a fast return section for each input rotation cycle. The near fixed linear velocity portion of the motion of each quick return mechanism is selectively connected to a conversion device that translates the motion into an output rotation. The input / output speed ratio is set by selectively changing the amount and direction of the fast turn mechanism motion that is applied to the conversion device. According to the input rotation, an infinite speed ratio can be generated as well as an output rotation in both forward and reverse directions.

In the above-mentioned patent application, two quick return mechanisms work one behind the other to transmit power to the output. On the output shaft, parts called sprags that provide one-way operation are used to create absolute value for the direction of movement. Sprags are problematic parts in terms of load carrying capacity.

The problem of using the friction element in the system described above as CVT has been tried to be solved by using another friction element of the same restraint. Sprags disrupt the direct connection between input and output as it provides one-way operation For this reason, it can not be said that the speed of the wheel shaft is constant unless the engine revolution is changed while traveling with a constant "transmission rate" or the transmission rate is changed for a constant engine revolution For example, if the transfer rate is zero (multiplier = zero), the output shaft will not rotate if it is tried to rotate only one direction, and the opposite direction will be easily rotatable In the operation of Patent No., US5440945, as it is shown in Fig.2, structure is again is a kind of sprag. As it is shown in Fig. 3 and Fig. 4, the structures diminishes the possibility of working with a cluster of real numbers since the gear have to sit together. In the operation of the Patent No., US 5440945, elliptical gears used at the input side of the movement are used to linearly approximate the speed function of the movement during the process of movement of the structure referred to as the quick return mechanism. The transmission function is not a complete multiplication operation during the whole process in which the motion is transmitted, particularly at the points where the quick return mechanisms mutually synchronize the motion transmission task. In the operation of Patent No., US5440945, the output motion structure is an IVT operation expressed as “near straight”. For this reason, there is no assertion that the multiplication process is a complete application.

As a result, it can be said that the full mechanical application of the impacting process from the above mentioned disadvantages, which is able to work in a wide range of working speeds, based on a completely mechanical working principle, capable of working in a range including a negative value to zero, there is a need for a new technology that does not require the use of space-age materials that transmit power to the gear, which transmit power to each other at the working limits, that do not wear and tear, frequent maintenance and parts replacement, and has low manufacturing and maintenance costs.

Description of Invention

The present invention is a U transmutable, infinitely variable transmission that can overcome the above-mentioned disadvantages, operation of a full mechanical application of the impact process which can work in a range that includes a negative value to zero as well as a positive value and which can work in a wide working speed range and based on a completely mechanical working principle and which can transmit very high forces with power transmission which is a new technology that does not require the use of space-age materials that transmit power to each other at the limit values, does not wear and tear, maintenance and parts change, and manufacturing and maintenance costs are low.

The subject matter of the invention is capable of delivering high power within the design that the product has. The subject matter of the invention does not require space- age materials to transfer of high powers with the design of the product. The subject matter of the invention does not require frequent maintenance of the parts. The present inventive article has a long-lasting structure with the design of the owner. The subject matter of the invention is a low production cost system.

By trying to apply the mathematical multiplication process with a perfect or close to perfection, the mechanical system has a way to be followed is quite different from the conventional approaches. The inventive subject matter uses a type of mathematical transformation in order to overcome the problems described in the known state of the art, and the multiplication is performed in a different space. Theory; the input terms (the multiplier and the multiplicand) are intended to be subjected to a conversion process before A and B are processed. In this transformational resultantial space, we can express the angular velocity A, which is expressed as Rad/ Sn, in a trigonometric and periodic space; we can multiply by B parameter which is a distance unit. Of course, this transformation must also be an inverse transform operation, since transformations are meaningful when it is possible to go back to the same space again. With the Inverse Transformation process, it will return to Linear Space again from the trigonometric and periodic distance and a rotation motion with the rotation speed AB Rad / Sn will be obtained. The complexity of the realization of these transformations in the mechanical system will be solved by using special transformations that can be performed with only one addition (a axel gear operation) and the inverse transform. Reverse conversion is very important. For this reason, it will be explained further more and will be explained with a sample.

Let's imagine a machine with a shaft that rotates at a linear velocity of a Rad/sn. Let this machine do the Sin ² t transformation to the input motion. The shaft at the exit of the machine will periodically rotate in the same direction, then rotate, then slow down, and repeat it all the time. If the machine's operation is defined as mathematical, it will correspond to subjecting the A parameter in the angle-time space to the Sin ² t Transformation. If this transformation is simply defined as multiplying A by Sin ² t , then the transformation will result in A Sin ² t, a trigonometric and periodic function.

By doing a reverse conversion, we take a different path instead of making a complex dividing machine to get back the A-speed. If we produce a second machine that converts the Sin ² t Secondary Signal and we translate this second machine's that makes motion in a different phase of p/2. While the first machine generates the Sin ² t and the second machine generates Sin ² (t + p/2). Now, if we think of doing a reverse conversion. The inverse transform operation is simply reduced to an addition process and the perfect addition process is already exists in the machine (Axel gear). . When A Sin ² t + A Sin ² (t + p/2), Sin ² (t + p/2) = Cos ² t and A(Sin ² t + Cos ² t) = A ,

And according to the Pisagor theorem Sin ² t + Cos ² t = 1 would be,

as can be seen, a trigonometric and periodic function of A Sin ² t would be transformed back into a linear A parameter. U Transaction:

The above example is given to illustrate the approach in a general manner. The conversion function we will use in reality will not have Sin ² t effect for different reasons. The trigonometric conversion function /u used in the UTVT Machine can be used as a special function that can solve both the mechanical design problems together with the basic feature explained above with examples and at the same time does not create mechanical problems in itself; It would be as;

Let's first examine some of these functions, which can be done with a simple addition function for inverse transformation. The conversion function we will use as specified will carry this property.

From the Pisagor theorem Sin ² t + Cos ² t = 1 ,

Ή

Sin ² t + Sin ² ( t + 2 ) = 1

JT L

Sin ² ( t - 4 ) + Sin ² ( t + 4 ) = 1

JT .. JT 7L

A Sin ² ( t - 4 ) + A Sin ² ( t + 4 ) = A (Sin ² ( t - 4 ) + Sin ² ( t + 4 )) = A

In Table-l at Figure-22, it shows graphs of functions for A = 1 value. The mathematical sum of these two functions equals 1, which is A.

7G 7L

If the functions are examined as Sin ² ( t - 4 ) + Sin ² ( t + 4 ) the properties would be;

1. Both of these functions have a positive value that is non zero in average.

2. When one of the functions is shifted by half the period, then is the same as the other function.

3. The slope of the function values with maximum or zero (at the point where they touch the top point or the horizontal axis) is zero.

4. Aggregation speed change (acceleration) in the period is minimum.

Let's give the name "Super Symmetrical Character" for the two signals that provide these conditions. Super Symmetric Character is the most basic feature of the transformation function of UIVT Machine. In the production of super-symmetric character movements to be used as transformation functions in real UIVT machines; a method of taking the absolute value of the trigonometric functions that are symmetrical with respect to the horizontal coordinate axis to the positive directional variation of the property value zero and the negative directional variation will be used. Use of this method will add an absolute value operation to our conversion function, naturally there will also be an absolute value section in our UIVT machine. Absolute value taking can be performed mechanically under certain conditions. The most important point at this point is the time interval when the speed value is zero, which in the known continuous trigonometric functions is an minuscule moment with a limit of zero. It makes the sprags to work by making the direct use of simple and continuous trigonometric functions such as ^f which makes it produce the machine. Another issue is the inevitable inertia effect of mechanical systems. It is not possible to make big speed changes in a short period of time with this effect. Otherwise, excessive forces that would push the structural limits of the mechanical system or it would be excessive loud vibrating may occur, and it would make it inefficient for the usage in a practical sense. For this reason, a special conversion function has been produced in the continuous, but fragmented structure in which the speed change in the period, namely the function ^t is included to minimize in total.

For a machine that can be practically applicable and efficient, the movement at the end of the U transformation carries the following characteristics;

The two motions produced carry a super-symmetrical character (to each other).

In this scope;

- The movement has a positive average value.

- When one of the movements is shifted in phase by half of the period, it is the same as the other movements.

- The slopes at which motion velocities are at maximum or zero (at the point where they touch the top or horizontal axis) are also zero.

1. The time that the movement speed is zero (the movement stops) is different from zero.

2. Addition speed change (acceleration) in the system in which movements are produced is at a minimum level. Now let's examine by drawing a graph of the fragmented conversion function that we will use in our system, which carries all of these properties. The /u function can be expressed in terms of time or Q angle, which is the instantaneous angle of rotation of the input shaft. If Q expressed in terms of angle; the value of the /u(0) function corresponds to the magnitude of 1 tothe angular velocity of the output shaft. In other words, it is /u(t) = A/u(0).

The invention product consists of 4 sub-divisions or sub-machines It is seen in Table-2 is seen at Figure-23;

We can begin to explain how to make the mechanical realization according to the nature of the / s(0) function. The mechanical implementation of sub-machines #1 and #2 will be carried out in completely different ways. Sub-machine #3 performs the absolute value taking operation in relation to the input shaft direction. Sub Machine # 4 is a differentiation. It takes the sum of the rotational movements at the two entrances and transmits it to the exit. In the subject matter of the invention, 2 pieces of lower machines #1, #2 and #3 and 1 piece of lower machine #4 are used.

It is seen in Table-3 iat Figure-24; As shown in Table 3, the machines #1 and #2 will work in succession one after the other. In the drawing, it can be seen that if the machine group at the top of the drawing is 0 channeled and the bottom group B is channeled, the workings of the channels are exactly the same, but the only difference is that A is directly connected to the 0 channel of the input shaft but is connected to the B channel by a p radian phase difference.

The sub-machines #1 and #2 are structurally completely different from each other. As it has already been explained, the sub-machine number #1 will modulate the speed in terms of the speed of a motion generated by the function / s(0) with the speed of the rotation motion from the input shaft. The sub-machine #2, which receives this modulated motion, will be multiplied by the B parameter and take its absolute value when it takes the sine component of the integral of the angle of the / s(0) function. These processes, which are seen as complex in the mathematical model, are actually quite simple when they are in a mechanical machine The absolute value subtractor in the present invention actually performs an absolute value operation indexed to the input direction, which is slightly more complicated than the mathematical absolute value operation. This aspect differs from sprags. The main reason why the absolute value sub-machine is regarded as an invention; brake discs and brake pads, do not low torque limitations like sprags and offers the possibility to work without friction. In the production of the disclosed lower machine, constant rotation of ½ of the rotation period of the entry shaft of the product and the period of movement of the P gear is used.

In accordance with the invention, the brake changes are carried out in a superimposed manner. This overrunning sequence, which does not allow the movement to remain idle even during a small period of time, is described as follows:

1. Before the change is made, the structure of the brake disc /u(t) which is fully open, comes to a stop zone and stops

2. The brake disc, which does not turn before the other brake is released and is fully tightened

3. Then the other brake is opened. During this time, the opened up brake does not rotate

4. The opened up brake is starting to rotate after a while.

Therefore, the special structure provided by #1 Sub-Machine, where the velocity of the /u(t) function provided by the U transformation is zero and at a certain time interval other than zero, at a certain time interval other than zero, has a key role in the operation of the absolute value mechanism defined here. The fact that the movement is already stopped when the direction of travel is changed (when the brake is being changed) reduces the loss of the brake mechanism, which can be regarded as a friction element, to almost zero, allowing it to operate without friction. More specifically, there are only two situations in the mechanics: the brake is tight, the disc never rotates, or the brake is on, the disc rotates freely. The fact that the disc does not rotate during braking and releasing of the brake disc means that the friction is not realized. This system would be easy to install because of the parts forming the invention are easily connected to each other and costs are low due to the short installation time. Furthermore, the invention has a solid structure. §ekillerin A^iklanmasi:

The invention will be further described in the appended drawings so that the features of the invention will be more clearly understood and appreciated, but it is not intended to limit the invention to those particular embodiments. On the contrary, it is intended to cover all alternatives, modifications and equivalents that may be included within the scope of the invention defined by the appended claims. It should be understood that the details shown are only provided for the purpose of describing preferred embodiments of the present invention and are provided to both form the methods as well as to provide the most convenient and straightforward definition of the principles and conceptual features of the invention. In these drawings;

Figure 1 is a perspective view of the system.

Figure 2 is the the top view of the system.

Figure 3 is the rear view of the system.

Figure 4 is a perspective view of the system.

Figure 5 is a view of the view.

Figure 6 is a perspective view of the system.

Fig. 7 is a view of B view.

Fig. 8 is a front view of the rear gear group.

Figure 9 is a perspective view of the rear gear group.

Figure 10 is an exploded view of the rear gear group.

Figure 11 is the frontal view of the kidney-corresponding gear

Figure 12 is a perspective view of the system.

Figure 13 is the view of the C view.

Figure 14 is a perspective view of the system.

Fig. 15 is a view of D view.

Figure 16 is a cross-sectional view of the system. Figure 17 is a cross-sectional view of the system

Figure 18 is a perspective view of the system

Figure 19 is the view of E view

Figure 20 is a perspective view of the system

Figure 21 is a view of F view

Figure 22 is a view of Table- 1.

Figure 23 is a view of Table-2

Figure 24 is a view of Table 3.

The figures to aid in the understanding of this invention are numbered as indicated in the accompanying figure and are given below along with their names.

Referanslann A^iklanmasi:

A. Front gear group

1. Zero guidance

2. Kidney gear

3. Center shaft

4. Central shaft

5. Reciprocating gear

6. Zero piece

7. End bearing

B. Speed setting group

8. Stepping motor

8.1. Step motor shaft

8.2. Step motor pulley

Stepper motor fixing device

10. The first geared foot

11. Second threaded foot

12. Fixed side part

13. Step motor transmission gear set

14. The first rail 15. Speed change cam

15.1. Worm screw slot

16. Motion transfer roller

17. First bevel gear

18. Second bevel gear

19. Bevel spindle

20. First spur gear

21. Second spur gear

22. Worm screw shaft

C. Motion transfer group

23. Motion apportionment

24. Vertical rail

25. Fixed rail bed

26. Second rail

27. Racking gear

D. Rear thread group

28. Main gear set

28.1. Main exterior sun gear

28.2. Main interior sun gear

28.3. Main internal planetary gear 4.28. Main inner planet carrier

29. The first disk

30. Absolute value team

30.1. External sun gear

30.2. Internal sun gear

30.3. Internal planetary gear

30.4. Internal planet carrier

30.5. External sun gear fixing piece

31. Second disk

32. Left outer shaft

32.1. Left shaft fixing piece

33. Movement gear set 33.1. Collection of external sun gear

33.2. Collecting interior sun gear

33.3. Collection internal planetary gear

33.4. Collection internal planet carrier

33.5. Collection of external sun gear fixing piece

34. Right outer shaft

34.1. Right shaft fixing piece

35. Movement output shaft

36. Motion input shaft

36.1. Input shaft fixing piece

E. Brake group

37. Brake synchronization first gear

38. Brake synchronization second gear

38.1. Brake synchronization second gear shaft

39. The first cam

39.1. First cam path

40. Second cam

40.1. Second cam path

41. First brake synchronization shaft

41.1. First cam path tracker

42. The second disk fixing shaft

42.1 Second cam path tracker

43. First brake lining

44. First lining

45. Motion transmission gear

46. Second shrinking device

47. Second lining

K. belt

R. Bearing

S. Fixed block Description of Invention

The invention is characterized in that the motion transfer group (C) comprising the motion apportionment (23), the vertical rail (24), the fixed rail bed (25), the second rail (26) and the racking gear (27), the zero guide(l), kidney gear (2) comprises a front gear, group (A Consisting of a center shaft (3), a central shaft(4), a reciprocating gear (5), a zero piece (6), an end bearing (7) and a movement input gear (36), comprises a speed setting group (B) consisting of a stepper motor (8), the stepper motor fixing device (9), the stepper motor drive transmission gear set (13), the first rail (14), the speed change cam (15), the first bevel gear (17), the second bevel gear (18), consisting of the bevel spindle (19), the first spur gear (20), the second spur gear (21) and the endless screw shaft (22), comprises Rear thread group, (D) (hereinafter referred to simply as "D"), consisting of main gear set (28), the first disk (29), the absolute value set (30) consisting of a second disk (31), a left outer shaft(32), a motion collecting gear (33), a right outer gear (34), a motion output shaft (35) , comprises Brake group (E) consisting of a the brake synchronization first gear (37), the freewheel the first cam (39), the second cam (40), the first brake synchronizing shaft (41), the second brake synchronizing shaft (42), the first brake lining device (43), the first lining brake (44), the brake group (E) consisting of the Second brake synchronizing device (46) and the second brake lining (47) comprises two firstgeared feet (10) of first and second, positioned opposite to each other, a rear gear group (D) and a frontgear group (A), the second threadedbfoot (11) and the fixed rail bed (25) form the fixed fixed side piece (12). (Figure-l, Figure-2, Figure-3, Figure-4, Figure-5, Figure-6, Figure-7, Figure-8, Figure-l6, Figure-l8, Figure-l9).

The movement input shaft 36 which the movement from the product movement source enters into the system is constituted by the center shaft 3 fixed to the movement input shaft 36, the associated kidney gear 2 centered on the center shaft 3, the zero guide 1 associated with the zero guide 1 on the left and right sides is associated with the zero guide 6 associated with the zero guide 1 and the end bearing 7 associated with the end guide 7, and the zero part (6) is located in correspondence with the positioned gear (5) (Figure-4, Figure-5, Figure-l6). The product of the present invention is super symmetrical with respect to the movements of the left outer shaft 32 and the right outer shaft 34. The inventive product has a zero guide (1), a zero piece (6) and a tip (6) which allow the speed of movement of the kidney tooth (2) during the rotation of the recipient tooth (5) and the corresponding tooth bearing (7). In the present invention, the instantaneous speed changes of the motions of the system associated with the left-hand counter gear (5) and the right hand counter gear (5) and the corresponding gears (5) are minimized. In the present invention, the main gear set (28) includes the first disc (29), the second disc (31), the brake synchronizing first gear (37), the brake synchronizing second gear (38), the first cam (39), the second cam (40), first brake synchronization shaft (41), the second brake synchronizing shaft (42), first brake lining device (43), the first lining brake (44), the motion transmission gear (45), Second brake synchronizing device (46) and the second brake lining (47), has a positive value which is different from zero in terms of the direction of both the left outer shaft (32) and the right outer shaft (34). In the present invention, the left kidney gear (2) and the right kidney gear (2) are placed at an angle of 180° with respect to each other to form a phase difference of half the period between the movements of the right outer shaft (34) and the left outer shaft (32)Figure-4, Figure-5, Figure-8, Figure-l6, Figure-l8).

A first bevel gear (17) of the present invention comprises a second bevel gear (18) associated with the first bevel gear (17) perpendicular to the center line of the first bevel gear (17), a bearing (R) extending through the center of the second bevel gear (18), the first spur gear (20) centered on the end portion of the bevel gearshaft (19), the second bevel gear (21) associated with the first bevel gear (20), the endless screw shaft (22) positioned in the center of the second bevel gear (2l)two speed-change cams (15) associated with the first rail (14), and the endless screw shaft (22) positioned in parallel to the surface of the counter gear (5), the speed change cam (15) the stepper motor fixing device (9) comprises two stepper motors (8) fixed to the right and left of the stepper motor fixing device (9) and a stepper motor (12) centered on the left and right corresponding gears (5) (Fig. 5, Fig. 6, Fig. 19, Fig. 20, Fig. 21 ).

The inventive product comprising a stepper motor (8) which comprises a stepper motor shaft (8.1) which supplies the stepper motor drive transmission gear set(l3) with the aid of the obtained motion by means of a stepper motor shaft (8.1). The subject invention comprises a main gear set (28) comprising a main exterior sun gear (28.1), a main interior sun gear (28.2), a main inner planetary gear (28.3) and a main inner planetary carrier (28.4), an absulate value set (30) including an external sun gear (30.1), an external sun gear (30.2), an internal planet gear (30.3), an internal planet carrier (30.4) and an outer sun planetary gear fixing member (30.5) comprises a left outer shaft (32) a collection outer sun gear (33.1), a collection inner sun gear (33.2) centered on the outer sun planetary gear fixture (30.5) comprises a motion collecting gear set, (33) including the picking inner planetary gear (33.3), the picking inner planetary carrier (33.4) and the picking outer sun gear fixing piece (33.5), comprises the right outer shaft (34) centered on the inner sun gear (30.2) and total a internal sun gear (33.2) centered motion output shaft (35). The invention product has a left outer mile (32) comprising a left shaft fixing piece (32.1). In the present invention, the right outer shaft (34) including the right shaft fixing member (34.1) is provided. (Fig. 8, Fig. 9, Fig. 10, Fig. 17) The invention product consists of an absolute value assembly (30) comprising an inner planet carrier (30.4) fixed to the main outer sun gear (28.1). The invention has a left outer mile (32) comprising a left shaft fixing part (32.1) fixedly centered on the product collecting inner planet carrier (33.4). In the present invention, there is a right outer shaft (34) which includes the right shaft fixing member (34.1) centered and fixed to the outer sun gear fixing member (33.5). The invention product consists of a motion collecting gear (33) which collects two different motions from the right outer shaft (34) and the left outer milder (32) and extracts them as a single motion. The invention comprises a first disk (29), a second disk (31), a main gear set (28) and an absolute value set (30) providing absolute positive value by applying absolute value processing to the positive and negative directional movements transmitted by the rack (27) (Figure-8, Figure-9, Figure-lO, Figure-l7).

Brake synchronization second gear (38) including the brake synchronizing first gear (37), the brake synchronizing second gear shaft (38.1) positioned centrally on the product motion input shaft (36) according to the present invention comprises a first cam (39) fixedly centered on the brake synchronizing second gear shaft (38.1), and the second cam (40) are connected to first brake synchronization shaft (41) associated with the first cam (39) and the second brake disk synchronizing shaft (42) associated with the second cam (40) are connected to first brake synchronization shaft (41) associated with the first brake lining device (43) which is associated with the second brake disk synchronizing shaft (42) comprises a second brake synchronizing device (46) associated with the first lining brake (44) associated with the first lining device (43) and first lining brake (47) associated with the second synchronizing device (46) (Figure -5, Figure-l6). The product of the invention has a first cam (39) comprising a first cam path (39.1). The invention has a second cam (40) comprising a second cam path (40.1). The inventive product comprises a first brake synchronizing shaft (41) comprising a first cam path monitoring element (41.1). The invention product has a second brake synchronization shaft (42) comprising a second cam tracker (42.1). The present invention relates to the brake synchronizing second gear (38) which includes the first cam (39) and the second cam (40) on the left side and the first cam (39) on the right side and the brake synchronizing second gear shaft (38.1). The invention product comprises a first brake synchronizing shaft (41) comprising a first cam track track (41.1) associated with a first cam path (39.1). The invention product has a second brake synchronization shaft (42) comprising a second cam path track (42.1) associated with the second cam path (40.1). In the present invention, there is a second cam (40) comprising a second cam path (40.1 located int the first cam path (39.1) to be at an angle of 180°. ( (Fig. 14, Fig. 15, Fig. 16)

In the present invention, there is a ratio of 1/2 in size between the brake synchronizing first gear (37) and the brake synchronizing second gear (38). The invention has a first lining brake (44) and a second brake (47) which engage and disengage the first disk (29) and the second disk (31) when they are stationary, in order to avoid product wear and component wear (the disks are not already rotating during tightening and releasing) . In accordance with the invention, the positive direction movement of the rack (27) with the second disk (31) of the second brake lining (47) is transmitted in the positive direction to the left outer mile (32). In accordance with the invention, the negative direction movement of the rack (27) is transmitted by the first disk (29) of the first lining brake (44) to the left external shaft (32) in the positive direction. The subject product is the full mechanical application of the mathematical multiplication process (Figure-7, Figure-8, Figure-l5). Detailed Description of Invention

The inventive parts essentially consist of; a zero guidance (1), the kidney gear (2), the central shaft (3), the central shaft (4), the reciprocating gear (5), the zero piece (6), the end bearing (7) a fixed part (12), a Step motor transmission gear set (13), a first rail (14), a speed change cam (15), a second gear wheel the first spur gear 21 and the second spur gear (21) and the endless screw shaft (22) and the first bevel gear (20) are moved in the direction of the axis the motion apportionment (23), the vertical rail (24), the fixed rail bed (25), the second rail (26), the rack gear (27), the main gear set (28), the first disc (29), the absolute value set (30), the right external shaft (34), the motion output shaft (35), the motion input shaft (36), the brake synchronization first gear (37), the second disk (31), the left outer shaft (32), the motion collection gear set (33), the brake synchronization second shaft (38), the first cam (39), the second cam (40), the first brake synchronization shaft (41), the second brake synchronization shaft (42), the first brake lining device (43), the first lining brake (44), the motion transmission gear (45), the second synchronizing device (46) and the second brake lining (47., (Figure-l, Figure-3, Figure-5, Figure-6, Figure-7, Figure-8, Figure-l8, Figure-l9, Figure-20, Figure-21).

In the present invention, there is provided a motion transmission group (C) comprising a motion transmission device (23), a vertical rail (24), a fixed rail seat (25), a second rail

(26) and a rack (27) The present invention relates to an apparatus and a method for manufacturing a product which comprises a zero guide (1), a kidney gear (2), a center gear (3), a central shaft (4), a counter gear (5), a zero piece (6) (A). According to the product comprises a stepper motor (8), a stepper motor fixing device (9), a stepper motor transmission gear set (13), a first bevel gear (17), a second bevel gear (18), a bevel gear shaft (19) consisting of first bevel gear (20), the second bevel gear (21) and endless screw shaft (22) under the speed setting group (B). (Fig. 1, Fig. 6, Fig. 7, Fig. 12, Fig. 13 and Fig. 18) Figure-l9) In the present invention, there is provided a motion transmission group (D) is characterized in that the product main gear set (28) comprises the first disc (29), the absolute value set (30), the second disc (31), the left outer spindle (32), Motion collecting gear set (33), the right outer shaft (34), forming the motion output shaft (35) and the motion transmission gear (45). In particular, the brake synchronization first gear (37), the brake synchronizing second gear (38), the first cam (39), the second cam (40), the first brake synchronizing shaft (41), the second brake synchronizing shaft (42), which is composed of the first brake (43), the first brake (44), the second brake synchronizing device (46) and the second brake lining (47). (Fig.4, Fig. 5, Fig. 8, Fig. 16),

In the present invention, there is, the first geared foot (10), the second geared foot (11) and the fixed side part (12) form the chassis. The motion input shaft (36) provided in the subject of the invention; are concentric with the center shaft (3) and the central shaft (4) fixed to each other. Movement through the motion input shaft (36) rotates the brake synchro nization first gear (37) and the kidney gears (2) positioned on the center shaft (3). The kidney gears (2) are placed on the central shaft (3) at an angle of 180 degrees relative to each other. The kidney gear (2) is in contact with the corresponding gear (5) and transmits the movement to the gear (5). The counter gear (5) moves along the contact of the kidney tooth (2). The kidney stops without moving in the zero position during the period that the tooth (2) does not contact the corresponding tooth (5). There is a 180 degree difference between the right kidney gear (2) and the left kidney gear (2). The kidney gears (2) rotate the corresponding gear (5) with a certain speed function as required by the geometrical structures. The end bearing (7) is positioned on both ends of the zero part (6) of the invention. The zero pieces (6) are secured by centering the corresponding gear (5). In the present invention, there is a zero guide (1) fixedly centered on the kidney gear (2). The tip bearing (7) contacts the zero guide (1) (Fig. 1, Fig. 4, Fig. 6, Fig. 7, Fig. 16) to ensure that the counter gear remains in the zero position when the thread stopper (5) remains stationary. The time during which the reciprocating tooth (5) remains stationary at zero corresponds to 25% of the full diameter of the kidney tooth (2), which is part of the speed function of the reciprocating tooth (5). Two first rails (14) are fixed to the front face of the counter gear (5) so as to be parallel to each other. The first rails (14) are equally spaced relative to the center of the gear (5). The speed change cam (15) is positioned on the first rails (14). The first rails (14) form a movement reference on the counter gear (5) for the speed change cam (15). The speed change cam 15 can move on this first reference rail (14). The motion transfer roller (16) is positioned on the speed change cam (15). With the return of the counter gear (5); the motion transferring roller (16) and the speed changing cam (15) make a rotational movement about a circle whose radius is changed with respect to the distance to the center of the gear (5). The movement of the speed change cam (15) on the reference provides the worm shaft (22). The speed change cam (15) includes a worm screw slot (15.1). The endless screw shaft (22) is sandwiched between the two fixed blocks (S) by means of bearings (R). The bearing worm screw shaft (22) is associated with the worm screw housing (15.1). The motion transfer roller (16) is positioned on the speed change cam (15). With the return of the counter gear (5), the motion transferring roller 16 and the speed changing cam 15 make a rotational movement about a circle whose radius is changed with respect to the center of the gear 5. The movement of the speed change cam worm shaft (22). The speed change cam (15) includes a worm screw slot (15.1). The endless screw shaft (22) is sandwiched between two fixed blocks (S) by means of bearings (R). The bearing worm screw shaft (22) is associated with the worm screw housing (15.1). The first spur gear (20) is centered on the bevel gear spindle (19). The bevel gear shaft (19) is sandwiched between the two blocks by means of bearings (R). The second bevel gear (18) is centered on the center of the bevel gear shaft (19). The first bevel gear (17) is associated with a second bevel gear (18) perpendicular to the axis of the second bevel gear (18). The first bevel gear (17) is associated with the stepper motor drive transmission gear group (13). The rotational movement of the worm shaft (22) is associated only with the rotation of the stepper motors (8) by means of the motion transmission gear group (13) and is independent of the rotation of the corresponding gear (5). The stepper motor drive transmission gear group (13) is associated with the stepper motor (8) by means of the belt K. It consists of step motor (8), step motor shaft (8.1) and step motor pulley (8.2). The stepper motor (8) takes action with the command it receives. The stepping motor (8) which is in motion transmits the motion to the stepping motor transmission gear group (13) with the help of the belt (K). The stepper motor drive transmission group (13) rotates the first bevel gear (17) about its own axis. The second bevel gear (18), which is associated with rotation of the first bevel gear (17), also rotates. The first plain gear (20) on the same shaft as the second bevel gear (18) rotates together with the second bevel gear (18) to rotate the second plain gear (21). With the rotation of the second plain gear (21), the worm shaft (22) rotates about its own axis and provides the movement of the speed change cam (15) and the motion transferring bearing (16) on the reference (Fig. 5, Fig. 17, Fig. 19).

The motion transferring roller (16) is associated with the motion transferring apparatus (23). In the present invention, the fixed rail seat (25) is positioned on the fixed side member (12). The second rail (26) is associated with the fixed rail tracks (25). The second rail (26) has two pieces parallel to each other. The vertical rail (24) is fixed so that the second rails (26) are positioned perpendicular to each other. The movement transfer device 23 is associated with the vertical rail 24 so as to be able to move up and down freely. The motion transferring device (23) and the motion transferring bearing (16) move in relation to each other. In this regard, the rotation of the gear (5) and the other parts connected to the second rail (26) and the second rail (26) move only in the horizontal axis. The depth of this movement is also related to the distance from the center of the counter gear (5) on the reference of the speed change cam (15). When the speed change cam 15 is positioned on the reference to the precise center of the reciprocating gear (5,) the second rail (26) and the other connected parts do not move, even if reciprocating gear (5) is rotating. As the speed change cam (15) moves away from the center of the reciprocating gear (5), the speed of movement is increased. If the speed change cam (15) is positioned at a distance from the center of the counter gear (5) in the positive direction, the final movement is positive. If the speed change cam (15) is positioned at a distance from the center of the counter gear (5) in the negative direction, the final movement is negative direction. The position on the reference of the speed change cam (15) determines the speed and direction of the final movement. The motion transfer roller (16) facilitates the movement of motion between the speed change cam 15 and the motion transfer ap- paratus 23 (Fig. 1, Fig. 4, Fig. 5).

The second rail (26), which moves right to left (horizontal) in the fixed rail bed (25), is fixed to the rack (27). The rack (27) is associated with the movement transmission gear (45). The rack (27) rotates the associated transmission gear (45) clockwise or counter clockwise. The main transmission sun gear (28.1) is fixed to the transmission transmission gear (45). The motion transmission tooth (45) and the main outside sun gear (28.1) move together in a clockwise counterclockwise direction. The first disk (29) and the second disk (3 l)are fixed or released to make the movement of the main extemalsun gear (28.1) change directionally. In the present invention, the motion input shaft (36) is fixed by centering the brake synchronizing first gear (37). The brake synchronization first gear (37) moves together with the movement input shaft (36). The brake synchronizing first gear (37) is associated with the brake synchronizing second gear (38). The ratio between the brake synchronizing first gear (37) and the brake synchronizing second gear (38) is ½. Brake synchronization rotates two revolutions of the first gear (37) one revolution of the brake synchronizing second gear (38). The brake synchronization second gear (38) includes the brake synchronization second gear shaft 38.1 (Figure 1, Figure 5, Figure 7, Figure 8, Figure 13).

In the present invention, the brake synchronization is secured by centering the second toothed shaft (38.1), the first cam (39) and the second cam (40). The first cam (39) includes the first cam path (39.1). The second cam (40) contains the second cam path (40.1). The first brake synchronization shaft (41) provided in the subject matter comprises a first cam track track (41.1). The second brake synchronization shaft (42) comprises the second cam path tracker (42.1). The first cam path (39.1) and the second cam path (40.1) are uneven. The first cam track track (41.1) and the second cam track track (42.1) associated with the first cam path (39.1) and the second cam path (40.1) follow this non-uniform path so that the first brake synchronizing shaft (41) and the second brake synchronizing shaft (42) movement. The first cam (39) and the second cam 40 are generally positioned such that the first brake synchronization shaft (41) moves forward while the second brake synchronization shaft (42) moves backward. The first brake synchronization shaft (41) is associated with the first brake squeezing device (43). The second brake synchronization shaft (42) is associated with the second brake squeeze device (46). The first lining (44) is attached to the first lining apparatus (43) and the second lining (47) is attached to the second lining apparatus (46). The first cam track tracker (41.1) tracks the first cam tracker (39.1). Thus, the first brake synchronization shaf (41) moves back and forth. With the forward movement of the first brake synchronization shaft (41), the first brake shrink device (43) provides for the first brakes 44 to compress the first disk (29). With the backward movement of the first brake synchronization shaft (41), the first brake lining (43) allows the first lining (44) to release the first disk (29). The second cam track track (42.1 follows the second cam track 40.1. Thus, the second brake synchronization (42) moves back and forth. With the forward motion of the second brake synchronization shaft (42), the second lining clamp (46) provides the second pads (47) to compress the second disk (31). With the backward movement of the first brake synchronization shaft (41), the first pivoting device (43) allows the first pivots (44) to release the first disk (29). The second cam track (42.1) follows the second cam track (40.1). Thus, the second brake synchronization shaft (42) moves back and forth. With the forward motion of the second brake synchronization shaft (42), the second lining clamp (46) provides the second lining (47) to compress the second disk (31). The second brake is tight when the first brake continues to squeeze (both brake squeezes). He then leaves the first lining. In the following time, the first lining is tightened while the second lining is tightened, and then the second lining is left. Briefly, there is a situation in which both ends are tight during transitions, but there is no situation in which both ends release (Figure-5, Figure-l5, Figure-l6).

The main gear set (28), which is present in the subject of the invention, (28.1), main inner sun gear (28.2), main inner planetary gear (28.3) and main inner planetary carrier (28.4). In the present invention, the absolute value set (30) comprises an external sun gear (30.1), an internal sun gear (30.2), an internal planet gear (30.3), an internal planet carrier (30.4) and an external sun gear fixing piece (30.5). The motion gathering gear assembly (33) is provided in the subject matter; collecting internal sun gear (33.1), collecting interior sun gear (33.2) collecting internal planet gear (33.3) collecting internal planet carrier (33.4) and collecting external sun gear fixing piece (33.5). In the present invention, the main inner planetary carrier (28.4), the first disc (29) is fixed. The main internal planetary gears (28.3) are associated with the main internal planetary carrier (28.4) from the center points. The main external sun gear (28.1) is fixed to the external planetary carrier (30.4). The internal planet carrier (30.4) is associated with the central points of the internal planetary gears (30.3). The outer sun gear (30.1) is fixed to the outer sun gear fixing member (30.5). The external sun gear fixing member (30.5) is fixed by being associated with the second disc (31). The left external shaft 32 is fixed by being associated with the main internal sun gear (28.2) and the internal sun gear (30.2). The left external shaft (32) includes the left shaft fixing piece (32.1). The right external shaft (34) is fixed by being associated with the main internal sun gear (28.2) and the internal sun gear (30.2) on the right side. The right external shaft (34) includes the right shaft fixing piece (34.1). The left shaft fixing member 32.1 is fixed to the collection internal planet carrier 33.4. The right shaft fixing member (34.1) is fixed to the outer sun gear fixing member (33.5). The collection internal planet carrier (33.4) is associated with the collection internal planet gears (33.3) from the center points. The outer sun gear fixing piece (33.5) is fixed to the collection outer sun gear (33.1) (Figure- 8, Figure-9, Figure-lO). In the present invention, the motion transmission roller (16) first moves in the forward direction of the drive rack gear (27), which is guided by the removal of the counter gear (5) in the positive direction. The forward motion of the rack gear (27) rotates the main outdoor sun gear (28.1) clockwise. During rotation, the second disc (31) remains stationary due to being tightened by the second boot (47). The first disk (29) is in the free state. The clockwise movement of the main external sun gear (28.1) is transmitted as the left outer mile (32) is clockwise. The movement of the speed change cam (15) in the positive direction on the reference from the center of the counter gear (5) causes the movement of the racking gear (27) to move backward. The backward movement of the racking gear (27) turns the main drive transmission gear 45 clockwise. During this rotation, the first disk (29) remains stationary due to being tightened by the first boot (44). The second disk (31) is in a free state. The motion transmission gear (45) and the main external sun gear (28.1) rotate together as they are fixed to each other. The clockwise movement of the main externalsun gear (28.1) is transmitted in such a way that the left outer mile (32) is clockwise. A forward and backward movement of the racking gear (27) causes the main external sun gear (28.1) to rotate counterclockwise one clockwise. The first lining (44) compresses and disengages the second disk (31) in the second linig (47), so that the first lining (44) is synchronized with the continuous directional movement of the rack (27). Thus, the movements of the main external sun gear (28.1) clockwise and counterclockwise are transmitted so that the left external mile (32) is clockwise (Figure-5, Figure-7, Figure-8). In the present invention, the movement of the speed change cam (15) in the negative direction on the reference from the center of the counter gear (5) causes the movement of the rack (27) in the forward direction. The forward motion of the rack gear (27) rotates the main external sun gear (28.1) clockwise. During rotation, the first disc (29) remains stationary due to being tightened by the first lining (44).

The second disk (31) is in a free state. The clockwise counterclockwise movement of the main external sun gear (28.1) is transmitted as the left external mile (32) is clockwise reversed. A forward and backward movement of the rack gear (27) causes the main external sun gear (28.1) to rotate counterclockwise one clockwise. The first lining (44) compresses and disengages the second disk (31) in the second lining (47), so that the first lining (44) is synchronized with the continuous directional movement of the rack (27). Thus, the movements of the main external sun gear (28.1) clockwise and counterclockwise are transmitted in such a way that the left outer mile (32) is clockwise reversed (Figure-5, Figure-9, Figure-lO).

In the present invention, the first disk (29) and the second disk (31) are compressed and released in the following order; the first disc (29) is clamped-the second disc (31) is free, the first disc (29) is clamped-the second disc (31) is clamped, the first disc (29) is free from the free-second disc (31), the disk (31) is tight, the first disk (29) is in a state in which the second disk (31) is repeatedly jammed repeatedly. In the present invention, there is no situation in which the first disc (29) and the second disc (31) are free at the same time when the first disc (29) and the second disc (31) are tightened at the same time.

In the present invention, the movement output shaft (35) is fixed by being associated with the collection inner sun gear (33.2). In the present invention, the motion of the right outer shaft (34) and the left outer shaft (32) are collected by the mechanism of the movement collecting gear (33) and transmitted to the movement output shaft (35). The right outer shaft (34) and the left outer shaft (32) rotate in the same direction but in a one-to-one rotation. The stopping and rotating movements are super symmetrical relative to each other. These two motions which are super symmetric with respect to each other are transmitted to the motion output shaft (35) by forming a continuous output motion in the same direction as the collection by the motion collecting gear assembly (33). (Fig. 8, Fig. 10).