Patent Application
20230265914
The present application relates generally to transmissions, and more particularly, to a variable diameter shaft continuously variable transmission (VDS. CVT) for producing high torque output, high power transmission and efficiency of the transmission.
Transmissions are used in transportation, agricultural and construction equipment to transmit power from power sources, such as internal combustion engines to equipment for accomplishing a desired task. For example, transmissions are used to properly transmit power to the wheels of a vehicle, or to a vehicle implement. Various industries use gear mechanisms for transmission and conversion of engine power. Continuously variable transmission (CVT) can be used to overcome the above mentioned disadvantages of gearboxes. A continuously variable transmission (CVT) is a transmission that can change through an infinite number of effective gear ratios between a minimum and a maximum range. In contrast, non-CVT transmissions offer a fixed number of gear ratios. Specifically, hydrostatic CVTs may use a variable displacement pump and a hydraulic motor and transmit power using hydraulic fluid. A swash plate may be used within the variable displacement pump to vary the output of the hydrostatic CVT by adjusting the fluid flowing into the hydraulic motor. Thus, the swash plate may enable the hydrostatic CVT to be continuously variable. Some hydrostatic CVTs may be combined with gear assemblies, drive shafts, and clutches to create a hydro-mechanical CVT. It may be appreciated that in certain applications, such as in construction equipment, a high torque output may be utilized by implements of the construction equipment. Further, a high torque output may be beneficial for low speed movement of vehicles, such as construction vehicles or agricultural vehicles.
In CVTs, transmission rate between an input shaft and an output shaft can be changed continuously in a linear manner such that infinite number of transmission rates is available between predefined lower and upper limits. In a CVT, transmission is provided by friction between parts of the CVT. in this mechanism the highest power is transmitted through hydraulic fluid. For example, in a belt driven CVT, friction between a belt and a pulley and in a toroidal CVT, friction between a toroid and disks of the CVT cause the transmission. In the both mechanisms, the friction between driver and driven and also between V belt and pulley is very low.
However, using the friction mechanism in CVTs cause problems such as limited transmission capability, high depreciation, low efficiency, and lack of stability in the selected revolution. Hence there is a need for a VDS. CVT to produce efficient transmission with continuous/linear variation and high friction surface and high torque output and high-power transmission.
The disclosed subject matter relates to a variable diameter shaft continuously variable transmission (VDP·CVT) This invention is based on the power transfer (torque-rotation speed) from the input shaft set to the output shaft by an endless flat belt and a secondary shaft set and a set of sun gear. One part of sun gear set connected with input shaft set and second part of sun gear set connected with secondary shaft set and third part of sun gear set connected with output shaft. Devised sets of main and secondary movable parts on the circumference of the input shaft and secondary shaft, by moving those movable parts on the main and secondary guide rods and along the radii of the input and output shafts. The diameter sizes of the shaft changes, and with the change in the diameters size of the input shaft set and second shaft set, the conversion ratio of rotation speed between of the two input and secondary shafts changes. Because the diameter changes in the shaft sets are continuously, therefor the changes in the rotation speed conversion ratio between the of rotation speed between the input shaft set and secondary shafts will be continuous. Because one part of sun gear set is connected with input shaft and second part of sun gear set connected with secondary shaft set and third part of sun gear set connected with output shaft, therefor the changes in the rotation speed conversion ratio between input shaft and output shaft will be continuous. In this mechanism, can achieve from negative ratio of rotation to positive ratio of rotation.
Devised sets of main and secondary movable parts on the circumference of the input shaft and secondary shaft, by moving those movable parts on the main and secondary guide rods and along the radii of the input and output shafts. The diameter sizes of the shaft changes, and with the change in the diameters size of the input shaft set and second shaft set, the conversion ratio of rotation speed between of the two input and secondary shafts changes. There are some plate parts placed on the main movable sets, the duty of these plate parts is to cover the distance between the two adjacent sets of movable sets. Six mechanisms are used to control the movement of main and secondary movable sets as follows.
The first control mechanism has a number of the main guide rods that are mounted on the environments of the input and output shafts and in radii direction of input and output shafts. Each main movable set (with cover plate parts) placed on each pair of main guide rods and these movable sets have liner motion on the main guide rods.
The second control mechanism has a number of the secondary guide rods that are mounted on the input and output shafts and in radii direction of input and output shafts and have. Each secondary movable set placed on each pair of secondary guide rods and have liner motion on the secondary guide rods, the duty of secondary movable set is to control the motion of the cover plates that installed in the main movable set.
The explanation is that, curve groove direction on the surfaces of pair disks is placed on the input or output shafts, they are symmetrical and when assembled they will have the same direction of grooves. Has been created a hole at the center of each of the disks and also two other holes at the specified points for coupling two guide disks to each other and four holes for mounted two interface sets (on a disk of each pair disk).
The third control mechanism is two guide disks for each of the input and output shafts, on the surface of each guide disks, has been created a number of tow kind curve grooves (or linear) and the number of each kind (first kind and second kind) of grooves are equal with the number of main movable sets or number of secondary movable sets.
The explanation is that, curve groove direction on the surfaces of pair disks is placed on the input or output shafts, they are symmetrical and when assembled they will have the same direction of grooves. Has been created a hole at the center of each of the disks and also two other holes at the specified points for coupling two guide disks to each other and four holes for mounted two interface sets (on a disk of each pair disk).
Two interface sets are mounted on one of a pair disk. Two disks are placed on each shaft (input and secondary) so that one of them placed on left side of the pairs of guide rod and other of them placed on the right side of the pairs of guide rod and also the groove surfaces of the disks are aligned. Each pair of disks are placed on their input and secondary shafts can have a rotary motion relative to their shaft.
In each shaft, one end of the main movable set is placed into the one first kind curve (or linear) groove of a disk that placed on left side of guide rod pairs and other end of the main movable set is placed into the one first kind curve (or linear) groove of a disk that placed on right side of guide rod pairs.
Also in each shaft, one end of the secondary movable set is placed into the one second kind curve (or linear) groove of a disk that placed on left side of guide rod pairs and other end of the secondary movable set is placed into the one second kind curve (or linear) groove of a disk that placed on right side of guide rod pairs.
All the ends of the main movable sets and all the ends of the secondary movable sets in this way are placed in the next curve grooves. Two interface sets for each pair of guide disks, mounted on the one of the guide disks (on the side that has not grooves). One pair guide disk that placed on each shaft (input and secondary) coupled together by two small shafts.
The main guide rods which are mounted on the shafts (input and secondary) with curve grooves (first kind) on the disk surfaces, control the place position of the main movable sets (each pair main guide rods with two first kind curve grooves from two face to face disks, they control a main movable set).
The secondary guide rods which are mounted on the shafts (input and secondary) with two curve grooves (second kind) on the disk surfaces, control the place position of the secondary movable sets (each pair of secondary guide rods with two second kind curve grooves from tow face to face disks, they control a secondary movable set).
By displacement of the main movable sets on the main guide rods and secondary movable sets on the secondary guide rods, diameters sizes of two shafts will be changed (input and secondary), by this method, the diameters of the shaft sets can be changed and variable diameters on input and secondary shaft sets will be achieved. The secondary movable sets help to control the cover plates that placed on the main movable set.
The fourth mechanism is a slider set for each input and secondary shaft. Each slider set consists of a cylindrical slider part and a bearing and a retainer part. The cylindrical part has a hole in the axis and in direction of length and has groove on the inner surface of the hole and also two helical and symmetrical grooves on the outer surface of the cylindrical, each of these two cylindrical parts is connected to a retaining part through a bearing.
These set of sliders are placed on the input and secondary shafts in some way the place of the inside groove of the hole is fitted to the parallel key that mounted on the input and output shafts (the rotational speed of the cylindrical part is same with his shaft). In each shaft (input and secondary) two small shafts of two interface sets (two interface sets are mounted on the guide disk) are placed inside the two outer helical grooves of the cylindrical part.
These cylindrical slider sets can have liner motion on the shafts (Input and secondary) in axis direction. With linear motion of cylindrical slider sets on the shafts and in the direction of the axis of the shafts (input and secondary), causing, rotation the pair of guide disks relative to their shafts, and this rotation of the disks causing the regular movement of movable sets (main and secondary) on their guide rods in direction of their guide rods axis.
In this way, the variable diameters of input and secondary shafts will be changed. As previously explained, because the direction of curved grooves of guide disks of the input shaft is different with direction of curved grooves of guide disks of the output shaft. Therefore, by moving both cylindrical slider sets in one direction (forward or backward), the variation in the diameters of the two input and secondary shafts will be inverse.
The fifth control mechanism is a mover mechanism for moving cylindrical slider sets, mover mechanism consisting of an actuator (mechanical, electrical, hydraulic, etc.), a connector plate, two guide shafts for connector plate.
The sixth control mechanism is first part of sun gear set connected with input shaft 2 and second part of it connected with secondary shaft set 21 and the third part of it connected with output part 30, for example, carrier is fixed with input shaft 2, ring gear involved with secondary shaft set 21 by three interface gears and sun gear fixed on output shaft.
In this mechanism, in order to further increase of the friction between the main movable sets and the carrier belt, it results in better efficiency, is used one incremental set.
With the sets and parts described, the invention is completed. Since the movement created by the actuator (mechanical, electrical, hydraulic) is continuous, the movement of the cylindrical slider sets will be also continuous and follow it, the rotation of the pair guide disk and the diameters changes will be continuous. As a result, changes in the conversion rate (output to input) will be continuous.
As indicated above, the parts and sets that installed and assemblies on the two input shaft set 2 and secondary shaft set 21 are same, but the direction curve grooves of guide disks are different (they are inversely in the direction of the curve grooves in the corresponding disks). Therefore, to avoid repeating the threads, only one shaft sets is described, for example the input shaft set is described.
And for a better understanding of the mechanism, for the components and assemblies 3, 4, 5, 6 that they can be selected numerous, we select a certain number, for example, for each of the input and output shaft set, twenty-four numbers of main guide rods 3 and twelve sets of main movable 6 and the twenty-four numbers secondary guide rods 4 and twelve sets of secondary movable 5 are selected.
For more clarity and better depicting the performance of the parts in most figures, instead of showing all of the twenty-four numbers main guide rods and twelve sets main movable, only four numbers main guide rods and two sets main movable are shown.
And twenty-four numbers other holes (small size) for the secondary guide rods 4 are considered (the two-row holes are one-to-one along the axis of the shaft). A pair of main guide rods 3 and a pair of secondary guide rods 4 are shown on the figure. There are also two symmetrical holes (inside a part of the shaft having a larger diameter) and created along the shaft axis (section A-A).
A) Two parts 61 having holes of equal diameter (with a further tolerance) with diameter of main guide rod 4, and on one side of each these parts 61 is fitted a small shaft, these small shafts will be placed in the curve grooves (first kind) of the guide disks;
B) Nine numbers (or more) of cover plates 63 these have hole and that are placed on the shaft 62 in the free mode, the outer surface of the part 63 in the form of a section of the environment of the circle, radius of the circle is the same size of the largest variable diameter of the input shaft and secondary shaft. Inside of the cover plates is formed a special curve groove; and
C) A shaft 62 with nine numbers of cover plates 63, arranged between two parts 62 that fixes these two parts in such a manner that the axial distance of the two holes of two parts 62 is same with the axial distance of the two guide rods 3, which will be placed on the input shaft, as shown in the figure, the two guide rods 3 will be placed within the holes of the set 6, and the set 6 can have linear motion along the axis on a pair guide rods 3.
This is the maximum diameter of the input shaft 2. As can be seen, two adjacent sets of cover plates 63 overlap each other, The shaft 52 from set 5 is placed inside the curved grooves in the cover plats 63 from two adjacent sets 6 and duty of shaft 52 is maintaining and matching the outer arc centers of the covering parts 63 belongs to the two adjacent sets 6. (Next, the circle created from main movable sets 6 will be variable diameter of the input shaft and secondary shaft).
On the top of this figure, in the medium diameter, the interaction between the two cover parts 63 and the shaft function 52 in maintaining the center of the arcs of the outer surface can be seen, which means that the two external arcs of the cover parts 63 from two adjacent main movable sets 6 will be matches together, and this will continue in all of the diameters.
The twelve curve grooves (first kind) for the main movable sets 6 and the twelve curve grooves (second kind) for the secondary movable sets 5, the width of the curve grooves of the secondary movable sets 5 is less than the width of the curve grooves of the main movable sets 6. It needs to be explained that the direction of the curve grooves in the two disks on the one shaft is not a same direction, but when the assembling two guide disks on the input or output shafts, direction of curve grooves of two disks will be the same direction.
This cylindrical slider set 11,12,13 is somehow placed on the shaft 2, inner groove of the part 11 fitted to the parallel key 14 that is mounted on the shaft 2, and two shafts 10 that is mounted on two parts 9, is placed inside of two helical grooves of cylindrical slider part 11, the cylindrical slider 11 has a rotational speed equal to the shaft 2 rotational speed. Cylindrical slider 11 can have a linear motion along the input shaft 2 axis.
and also illustrate the main movable sets 60 on the main guide rods 3 in the maximum diameter and also in the middle diameter. By using this type of main movable sets 60, the second control mechanism will be eliminated from two main shaft sets (input and output).
It means from each main shafts (input and secondary shafts), twelve pairs of secondary guide rods 4, as well as twenty-four numbers holes on each shaft and twelve sets secondary movable 5, as well as twelve numbers curve grooves (second kind) on the guide disks are eliminated (only twelve numbers curve grooves are required to control the main movable sets 60 on each guide disks).
Because the main movable sets 6 are controlled by two non-parallel guides (the main guide rods 3 and disks curve grooves 7), and because the main guide rods 3 are in line with the radii of the shaft 2 and they are also arranged by equal degrees (thirty degrees), as well as the regularity and uniformity of the curve grooves on the guide disks 7.
If a pair guide disks 7 on the input shaft 2 do not rotate relative to the shaft 2, the main movable sets 6 will be in steady state on the main guide rods 3 and all of them have equal distance from the axis of the shaft 2 and created a specified diameter.
By rotating the pair guide disk 7 relative to the shaft 2, the main movable sets 6 changes location on the main guide rods 3 and along rods axis (in line with the radii of the input shaft), and value of this change in location on the main guide rods 3 are equal in all of the main movable sets 6 and always all of the main movable sets 6 distance from the center of the shaft 2 are the same.
Meaning that by rotating the guide disk 7 relative to the shaft 2 the diameter of the input shaft 2 will be changed, as well as secondary movable sets 5 change location on the secondary guide rods 4 and along rods axis (in line with the radii of the input shaft), and value of this change location are equal in all of the secondary movable sets 5 and always all of the secondary movable sets distance from the center of the shaft 2 is the same.
The cylindrical slider set 11, 12, 13 can have linear motion on the shaft 2 and along its axis. The bearing 12 between the cylindrical slider 11 and the retainer part 13 of the cylindrical slider set 11, 12, 13 causes the retainer part 13 does not following the rotation movement of the cylindrical slider part 11, and also by the parallel key 14 between the cylindrical slider part 11 and the input shaft 2, the rotational movement of cylindrical slider part 11 is the same with the rotational movement of the shaft 2.
As described in the
When the cylindrical slider 11 has linear motion along the axis of the input shaft 2, parts 10, 9 and pair guide disk 7 have rotational movement relative to the cylindrical slider 11 and also input shaft 2.
By rotational movement of pair guide disk 7, all of main movable sets 6 and secondary movable sets 5, Change location on the main guide rods 3 and secondary guide rods 4, as a result, the variable diameter of the input shaft 2 will change.
As explained above, all parts and sets mounted on the input shaft 2 and the secondary shaft 21 are same (other than the curve grooves direction of corresponding pairs disk at the two input 2 and secondary shaft 21 are inverse to one another).
In this mechanism, when actuator 16 move part 15 (forward or backward), two cylindrical slider sets (11, 12, 13) will have linear motion on the two shaft 2 and shaft 21 and the two pair guide disks 7 have rotational motion relative to his shaft 2 and shaft 21 and change location of all main movable sets 6 on the main guide rods 3 and secondary movable sets 5 on the secondary guide rods 4, as a result, the variable diameters of shaft 2 and shaft 21 will change.
Because the curve grooves direction of a pair guide disk 7 that placed on the shaft 2 are inverted with curve grooves direction of a pair guide disks 7 that placed on the shaft 21, so the diameters variations of the input shaft 2 and the secondary shaft 21 will be inverted, that means when the diameter of the one shaft increases, the diameter of the other shaft will decrease.
An endless flat belt 22 (made of metal or rigid metal or) on the assembly of variable diameter on both shafts 2 and 21 and therefore the power transfer (torque-rotation) from the input shaft 2 to the secondary shaft 21 is carried out through the flat belt.
Because movement of actuator 16 is continuous movement, so the movement of the part 15 and the associated two cylindrical slider sets (11, 12, 13) will be continuous. as a result, the rotation motion of the two pairs guide disk 7 will be continuous, and finally the diameters variations of the input shaft 2 and secondary shaft 21 will be continuous. And with continuous of the diameter's variation, the conversion ratios of the input shaft 2 and secondary shaft 21 also will be continuous.
In Table 1, N is the rotation speed of the shafts, D is variable diameter of shafts. An index shows the component number. For example, N2 is the rotation speed of shaft 2 and D2 is variable diameter of shaft 2. N21 is the rotation speed of shaft 21 and D21 is variable diameter of shaft 21.
As explained above, the carrier 26 fixed on the input shaft 2 and sun gear 29 fixed on the output shaft 30, and secondary shaft 21 involved with the ring gear 28 (can be gears, chain with gear and etc.), for example, by three gears (22, 23, 24), as a result, by changing the speed of the secondary shaft 21 rotation, the rotational speed of the output shaft 30 will also change. Because changing the speed of the secondary shaft 21 rotation is continuous, so, changes the rotational speed of the output shaft 30 will also continuous.
In Table 2, N26 is rotational speed of carrier that equal with rotational speed of output shaft 2, that is mean N2, N27 is rotational speed of ring gear and G27 is teeth number of ring gear, N28 is rotational speed of sun gear and G28 is teeth number of sun gear, N30 is rotational speed of sun gear 29 or output shaft 30, R is the conversion rate in the mechanism.
In the
The strap stiffening set shown in
By installing the number of sensors on the mechanism and controlling the actuator through the sensors, this invention will be automatic.
Because the parts used in this invention are simple, therefor, production of this mechanism with the simple facilities is possible.
This invention useable in all industries that need to be converted the rotation speed to the torque, including, automotive, shipbuilding, machine tools.
The separation of various system components in the examples described above should not be understood as requiring such separation in all examples, and it should be understood that the described components and systems can generally be integrated together in a single packaged into multiple systems.
While the foregoing has described what are considered to be the best mode and/or other examples, it is understood that various modifications may be made therein and that the subject matter disclosed herein may be implemented in various forms and examples, and that the teachings may be applied in numerous applications, only some of which have been described herein. It is intended by the following claims to claim any and all applications, modifications and variations that fall within the true scope of the present teachings.
Unless otherwise stated, all measurements, values, ratings, positions, magnitudes, sizes, and other specifications that are set forth in this specification, including in the claims that follow, are approximate, not exact. They are intended to have a reasonable range that is consistent with the functions to which they relate and with what is customary in the art to which they pertain.
The scope of protection is limited solely by the claims that now follow. That scope is intended and should be interpreted to be as broad as is consistent with the ordinary meaning of the language that is used in the claims when interpreted in light of this specification and the prosecution history that follows and to encompass all structural and functional equivalents. Notwithstanding, none of the claims are intended to embrace subject matter that fails to satisfy the requirement of Sections 101, 102, or 103 of the Patent Act, nor should they be interpreted in such a way. Any unintended embracement of such subject matter is hereby disclaimed.
Except as stated immediately above, nothing that has been stated or illustrated is intended or should be interpreted to cause a dedication of any component, step, feature, object, benefit, advantage, or equivalent to the public, regardless of whether it is or is not recited in the claims.
It will be understood that the terms and expressions used herein have the ordinary meaning as is accorded to such terms and expressions with respect to their corresponding respective areas of inquiry and study except where specific meanings have otherwise been set forth herein. Relational terms such as first and second and the like may be used solely to distinguish one entity or action from another without necessarily requiring or implying any actual such relationship or order between such entities or actions. The terms “comprises,” “comprising,” or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. An element proceeded by “a” or “an” does not, without further constraints, preclude the existence of additional identical elements in the process, method, article, or apparatus that comprises the element.
The Abstract of the Disclosure is provided to allow the reader to quickly ascertain the nature of the technical disclosure. It is submitted with the understanding that it will not be used to interpret or limit the scope or meaning of the claims. In addition, in the foregoing Detailed Description, it can be seen that various features are grouped together in various implementations for the purpose of streamlining the disclosure. This method of disclosure is not to be interpreted as reflecting an intention that the claimed implementations require more features than are expressly recited in each claim. Rather, as the following claims reflect, inventive subject matter lies in less than all features of a single disclosed implementation. Thus the following claims are hereby incorporated into the Detailed Description, with each claim standing on its own as a separately claimed subject matter.
This application claims the benefit of priority to PCT/2019/056281 filed on Jul. 23, 2019, all of which are incorporated by reference herein in their entireties.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/IB2019/056281 | 7/23/2019 | WO |
