Transmission with helical synchronization

Abstract

The invention relates to transmissions. The present transmission comprises a housing, a splined shaft, a shaft with an axis orthogonal to the axis of the splined shaft, a plate-like element mounted perpendicularly on the axis of said shaft, a cylindrical toothed gear mounted on the splined shaft and rotating conjointly therewith, and a mechanism for locking and moving the cylindrical gear. The splined shaft is mounted parallel to the surface of the plate-like element and has engaging means extending along its length, which allow the cylindrical gear to rotate conjointly with the splined shaft. Formed on the surface of the plate-like element facing the splined shaft are circular toothed loops of a spiral, which are connected by counter-directional toothed spiral synchronizing tracks. The teeth of the cylindrical gear are in constant engagement with the teeth of the plate-like element. The cylindrical gear can be longitudinally locked so that its teeth remain in constant engagement with a selected circular toothed loop of the plate-like element, or the cylindrical gear can move longitudinally, travelling over the teeth of the toothed spiral synchronizing tracks in the case of a gear change. This makes it possible to change gears without power interruption.

Description

[0001] Helical Synchronization Transmission

[0002] Field of technology to which the invention relates

[0003] The invention relates to transmissions, namely gear transmissions with a continuously variable gear ratio between input and output without interruption of the power flow.

[0004] State of the art

[0005] Transmissions are devices known from the prior art—devices designed to match the speed and torque of a rotary source—usually an engine—with the speed and torque of a rotary consumer. Four common types of transmissions are available: manual, automatic, preselective, and continuously variable transmissions. Each has its well-known advantages and disadvantages, and their simultaneous existence confirms the niche nature of each. A solution that combines simplicity of design, engineering, and manufacturing with the other advantages of existing transmissions is currently lacking.

[0006] A transmission with spiral gear transitions is known (RU2595721C2, August 27, 2016). The first transmission shaft is a truncated cone with toothed elements. The second shaft is parallel to the cone's outer surface and contains a gear that can move freely along it, but is engaged with it, for example, by means of extended keys or splines along the shaft. At the beginning and end of the truncated cone are gears whose diameter is equal to the cone's diameter at their location, and the number of their teeth is proportional to the first and last transmission ratios. The tooth module of all gears and spiral gear transitions is identical. The cone gears are connected by two counter-wound spiral toothed raceways, which allow both increasing and decreasing the gear ratio without changing the direction of rotation of the first shaft by rolling the gear of the second shaft along them.At the intersections of counter-wound spiral gear transitions on the conical shaft, additional gears can be located, the number of teeth of which is proportional to the diameter of the cone at the intersection. A sufficient number of intermediate gears on the first shaft allows for fine-pitch adjustment of the transmission ratio, if necessary. To synchronize the position of the gear teeth on the second shaft with the position of the teeth on the spiral gear transitions and gears on the first shaft, an electronic or mechanical automatic control system must be used, moving the gear on the second shaft along the surface of the conical shaft so that the teeth are constantly engaged. The disadvantage of this solution is that it uses a truncated cone with toothed elements as a base, making its design and manufacture complex, expensive, and material-intensive.Furthermore, this solution has a narrow kinematic range, is up to twice as large as a manual transmission with equal load characteristics, and lacks precise, fast, and reliable shifting. It also uses an electronic, sensor-based automatic control system, which is expensive and complex and does not provide sufficient reliability when changing the gear ratio. According to automakers, this solution lacks industrial applicability.

[0007] The claimed invention eliminates the above mentioned disadvantages.

[0008] Disclosure of invention

[0009] The problem solved by the invention is the creation of a transmission that is structurally simple to manufacture and design, easy to maintain, repairable, capable of operating at high speeds, compact, efficient and reliable, providing a change in the transmission ratio without interrupting the flow of power with either mechanical, semi-automatic or automatic control, possessing reliability and high switching speed, high efficiency, and, in some extended applications, a large kinematic range, the number of gears in this range, as well as an increase in the transmitted torque up to two times in the same dimensions due to a small addition to the design.

[0010] The technical result consists of changing the transmission ratio without interrupting the power flow, increasing the reliability of switching, preventing jamming and breakdowns, reducing the overall dimensions and weight while maintaining the power characteristics.

[0011] The technical result is achieved due to the fact that the transmission includes a housing containing places for fastening shafts, at least one splined shaft and one shaft, the axis of which is orthogonal to the axis of the said at least one splined shaft, at least one plate element mounted perpendicularly to the axis of the said shaft, orthogonal to the axis of the at least one splined shaft, a cylindrical gear with teeth mounted on each of the at least one splined shaft, and made with the possibility of rotation together with the splined shaft and positioning along it using a locking and movement mechanism, wherein at least one splined shaft is mounted parallel to the surface of the plate element at a distance from it and is provided with engagement means extended along it, allowing the cylindrical gear to rotate together with it, but to be longitudinally located at any place of the splined shaft, while on the surface of the plate element,facing the splined shaft, at least two annular toothed turns are formed, connected by counter-wound spiral toothed synchronizer tracks, wherein the teeth of the cylindrical gear are in constant engagement with the teeth of the plate element, wherein the module of the teeth of the cylindrical gear and all the toothed elements of the plate element is the same, and the shape of the teeth of the plate element is not the same, depends on the radius of the tooth location, and is an imprint of the changing spatial position of the teeth of the cylindrical gear when it rolls along the pitch circles and pitch arcs of the spiral toothed synchronizer tracks, wherein each of at least one splined shaft and its cylindrical gear is provided with its own locking and movement mechanism, and each such locking and movement mechanism is designed with the possibility of linear positioning of the cylindrical gear along the splined shaft in such a way,that the cylindrical gear is either longitudinally fixed, and its teeth are in constant engagement with the selected ring gear of the plate element, or moves longitudinally, rolling strictly along the teeth of the spiral gear tracks-synchronizers when the transmission ratio changes.

[0012] In addition, the step of changing the diameters of the ring gear turns is made equal or variable.

[0013] In addition, the projection of the spline shaft axis onto the plane of the plate element is generally a chord.

[0014] In addition, the number of pairs of spiral toothed synchronizer tracks connecting adjacent toothed turns may be greater than one.

[0015] In addition, the locking and movement mechanism is a discrete action mechanism with mechanical or electronic control.

[0016] In addition, in the case of several splined shafts, the plate element can be summing or intermediate, while the cylindrical gear of each of the splined shafts is the input or output, and the number of combinations of positions of the input and output cylindrical gears of the splined shafts minus the matching ones determines the number of transmission coefficients.

[0017] In addition, if there are several splined shaft gears and their diameters are the same, the transmission may additionally contain a second plate element, installed in mirror image to the first one, to transmit up to twice the torque while maintaining the same dimensions.

[0018] In addition, the shape of the spiral toothed synchronizer track is made dependent on the selected control law in the locking and movement mechanism, but in such a way that the teeth of the cylindrical gear have constant engagement with the spiral toothed synchronizer tracks of the plate element.

[0019] Brief description of the drawings

[0020] Fig. 1 shows one of the embodiments of a transmission with control through the connection of a rod connected to a splined shaft gear to a rocker oscillating around the center of a plate element;

[0021] Fig. 2 shows a variant of the implementation of a transmission for bicycles and motorcycles with control through the connection of the carriage to the rocker, implemented on a half-gear and two toothed racks;

[0022] In Fig. 3a, b, a variant of the implementation of a transmission for bicycles and motorcycles with independent drives from pedals and an electric motor is shown; the movement of the splined shaft gears is controlled by connecting the carriages associated with them to a spiral groove on the back side of the plate element by snapping the carriage rod into it;

[0023] Fig. 4 shows a variant of the implementation of a transmission for bicycles and motor vehicles, where a plate element with spiral synchronizers is installed in place of a standard bicycle cassette, and two groups of spiral grooves are transferred to a control drum rotating synchronously with the plate element;

[0024] Fig. 5a, b shows a variant of the implementation of a transmission with input and output splined shafts, and two mirror-image plate elements are intermediate, control is carried out by connecting the carriages with spring-loaded rods controlled by electromagnets to spiral grooves on the reverse side of one of the plate elements;

[0025] Fig. 6 shows a variant of the implementation of a transmission for automobile automatic transmissions with control of the position of the carriages through the connection of a Maltese mechanism (ATM) associated with them.

[0026] The following elements are indicated by numbers on the figures:

[0027] 1 - Body;

[0028] 2,3 - Spline shaft bearings;

[0029] 4 - Splined shaft;

[0030] 5 - Plate element; 6,7,8 - Ring toothed turns (gears);

[0031] 9a, 96 - A pair of counter-wound spiral gear synchronizers;

[0032] 10a, 106 - Second pair of counter-wound spiral gear synchronizers; 11 - Cylindrical gear with teeth;

[0033] 12 - T-shaped rod of the movement mechanism;

[0034] 13 - Screws;

[0035] 14 - Retainer;

[0036] 15 - Oscillating mechanism;

[0037] 16 - Protrusion of plate element;

[0038] 17 - Element of the fixation and movement mechanism;

[0039] 18 - Rod of the movement mechanism in the form of a carriage;

[0040] 19 - Half gear;

[0041] 20 - Bicycle rear wheel hub;

[0042] 21 - Carriage;

[0043] 22 - A spring-loaded rod, by releasing which the carriage is caught in a groove on the plate element;

[0044] 23 - groove for increasing the transmission coefficient;

[0045] 24 - groove for reducing the transmission coefficient.

[0046] Implementation of the invention

[0047] The proposed transmission includes a housing containing places for fastening shafts, at least one splined shaft and one shaft, the axis of which is orthogonal to the axis of said at least one splined shaft, at least one plate element mounted perpendicularly to the axis of said shaft, orthogonal to the axis of at least one splined shaft, a cylindrical gear with teeth mounted on each of at least one splined shaft, and configured to rotate together with the splined shaft and be positioned along it using a locking and movement mechanism.

[0048] At least one splined shaft is mounted parallel to the surface of the plate element at a distance from it and is equipped with engagement means extending along it, allowing the cylindrical gear to rotate with it but be longitudinally positioned anywhere on the splined shaft. The cylindrical gear, in turn, may contain a ball bushing for longitudinal movement with reduced resistance.

[0049] On the surface of the plate element facing the splined shaft, at least two annular toothed turns are formed, connected by counter-wound spiral toothed synchronizer tracks. The teeth of the cylindrical gear are formed to be in constant engagement with the teeth of the plate element, wherein the module of the teeth of the cylindrical gear and all toothed elements of the plate element is the same, and the shape of each tooth of the plate element depends on the radius of its location, and is an imprint of the changing spatial position of the teeth of the cylindrical gear as it rolls along the pitch circles and pitch arcs of the spiral toothed synchronizer tracks.

[0050] There may be one, two or more shafts, similar to a splined shaft with cylindrical gears with the required number of teeth, working together with a plate element, as well as the associated locking and movement mechanisms, i.e. each shaft and its cylindrical gear are provided with their own single locking and movement mechanism, and each such locking and movement mechanism is designed with the possibility of linear positioning of the cylindrical gear along the splined shaft in such a way that the cylindrical gear is either longitudinally fixed, and its teeth are in constant engagement with the selected annular toothed thread of the plate element, or moves longitudinally, rolling strictly along the teeth of the spiral toothed synchronizer tracks when the transmission ratio changes.

[0051] In the case of several splined shafts, the plate element can be summing or intermediate, with the cylindrical gear of each of the splined shafts being the input or output, and the number of combinations of positions of the input and output cylindrical gears of the splined shafts minus the coinciding ones determines the number of transmission coefficients, which will be three for two ring gear turns on the plate element, seven for three, thirteen for four, twenty-one for five, thirty-one for six, forty-three for seven, etc.

[0052] Parallel to the plate element, it is possible to arrange an additional second plate element in a mirror image to it, rotated by the same cylindrical gears, located on the same shaft axis (including if the diameters of the cylindrical gears of several splined shafts are the same), orthogonal to the axis of at least one splined shaft, which will increase the transmitted torque up to two times while maintaining the dimensions and suppress the bending of the splined shafts at the loading points.

[0053] The projection of the axis of the splined shaft onto the plane of the plate element is generally a chord, and in particular passes through the center, while the teeth of the plate element will also have the shape of the imprint of the rolling teeth of the cylindrical gear of the splined shaft.

[0054] The pitch of the annular tooth thread diameters may be equal or variable. In the figures shown, the pitch of the number of teeth on the annular tooth threads is equal; for example, in Fig. 1, the plate element contains 24-48-72 (a pitch of 24 teeth), and in Fig. 3, 24-40-56-72-88 (a pitch of 16 teeth). The numbers of teeth on the annular tooth threads and the spiral synchronizer tracks must be integers and multiples of the tooth module. These initial values ​​are presented in Table 1 as an example, where you can see the essence of filling the table in length and width, where the first column (for the compactness of the table, values ​​up to 16 are given, in the general case they are not limited) is the step between the numbers of teeth in a row such that an integer number of tooth modules fit into the spiral toothed track-synchronizer, the second column is the number of teeth on the initial ring gear, and then columns with the values ​​​​of the numbers of teeth on subsequent ring toothed tracks.The first ring gear turn and the pitch to the second are selected, then the pitch from the second to the third can be different—from a different row, and so on. Accordingly, there can be thousands of possible designs for a plate element.

[0055] Table 1 4 0 4 8 12 16 20 24 28

[0056] 4 2 6 10 14 18 22 26 30

[0057] 8 0 8 16 24 32 40 48 56

[0058] 8 2 10 18 26 34 42 50 58

[0059] 8 4 12 20 28 36 44 52 60

[0060] 8 6 14 22 30 38 46 54 62

[0061] 12 0 12 24 36 48 60 72 84

[0062] 12 2 14 26 38 50 62 74 86

[0063] 12 4 16 28 40 52 64 76 88

[0064] 12 6 18 30 42 54 66 78 90

[0065] 12 8 20 32 44 56 68 80 92

[0066] 12 10 22 34 46 58 70 82 94

[0067] 16 0 16 32 48 64 80 96 112 16 2 18 34 50 66 82 98 114 16 4 20 36 52 68 84 100 116 16 6 22 38 54 70 86 102 118 16 8 24 40 56 72 88 104 120 16 10 26 42 58 74 90 106 122 16 12 28 44 60 76 92 108 124 16

[0068]

[0069] 14 30 46 62 78 94 110 126

[0070] The shape of a spiral synchronizer track generally does not exhibit a linear change in radius with angle. Instead, it depends on the selected control type of the locking and movement mechanism, ensuring that the cylindrical gear teeth maintain reliable engagement with the spiral synchronizer tracks of the plate element. The spiral equation is a linear function of angle, a special case. However, such spiral synchronizer tracks cannot be used when the locking and movement mechanism is, for example, a harmonic oscillator (or, for example, a Maltese cross-coil mechanism). With such a law of linear movement of the cylindrical gear, there will be points where it will disengage from the spiral synchronizer tracks. Therefore, the shape of the spiral synchronizer track is adjusted based on the selected type of locking and movement mechanism.

[0071] The number of pairs of spiral toothed synchronizer tracks connecting adjacent toothed turns may be more than one.

[0072] The functions of the locking and movement mechanism can be implemented using known mechanically or electromagnetically connected mechanisms with optional microcontroller control, discrete action mechanisms - Maltese, ratchet, mechanisms for converting rotation into reciprocating motion, snap-in mechanisms, mechanisms for moving the connected rod along rotating grooves of a special shape, including in combination with these mechanisms together with gearboxes that reduce their operating speed to ensure reliable switching in high-speed transmissions, etc.

[0073] Fig. 1 shows one embodiment of a transmission that comprises a housing 1 (fastening means) with fastening points for two shafts at 90 degrees to each other, and points for installing bearings of the two shafts. Bearings 2 and 3 are mounted in the housing 1 on a splined shaft 4, other bearings (not shown) are mounted on the shaft axis of a plate element 5 in the form of a disk. The plate element 5 contains on its surface annular toothed turns (gears) 6, 7, 8, the number of which may be any, starting from two. Adjacent annular turns / gears 6, 7, 8 are connected by counter-wound spiral toothed synchronizers 9a, 96 and 10a, 106, which makes it possible to change the transmission gear ratio, both up and down, without changing the direction of rotation of the plate element 5.

[0074] The shape of the plate element may differ from the shape of the disk, for example, it can be square, oval or other round or polygonal shape, including with cutouts, but it must contain the toothed elements necessary for operation.

[0075] The splined shaft 4 is located parallel to the surface of the plate element 5 at some distance from it, contains a cylindrical gear 11 of the splined shaft with teeth, which can move freely along the splined shaft 4, but is in engagement with it and rotates together with it. The splined shaft 4 can be provided with keys, splines, and other engagement means extended along it, which allow the gear 11 of the splined shaft, which in turn can contain a ball bushing for longitudinal movement with less resistance, to rotate together with it, but have the possibility of longitudinal movement so that the teeth of the gear 11 of the splined shaft are in constant engagement with the teeth of the plate element 5. The movement and fixation of the gear 11 of the splined shaft along the shaft 4 can be carried out using a locking and movement mechanism, for example, using carriages (Fig.2 - 5) or, as in this case, by means of a T-shaped rod 12 (inside the splined shaft, while the shaft has slots through which the rod is connected to the movable gear), loosely connected to the gear 11 of the splined shaft by means of two screws 13 (Fig. 1). The carriage or rod has a connectable rigid connection to the control mechanisms, which in Fig. 1 is realized by connecting the rod through a spring latch to a linear oscillating mechanism in the center. In Fig. 1, one can see the T-shaped rod 12, which is fixed for reliability by a spring-loaded ball with a housing 1 in three positions - when the gear 11 of the splined shaft works with one of the ring gears 6, 7 or 8. The longitudinal movement of the T-shaped rod 12 is carried out by engaging it with the lock 14. The lock 14 rotates around its axis in the oscillator 15, has three positions - for movement to the right, left and neutral.The oscillator 15 swings left and right along the T-shaped rod due to the movement of the projection 16 of the plate element 5 in its slot. The lock 14 has a cut, and depending on the preliminary rotation of the lock in one of the two directions and its pressing, it hooks the T-shaped rod 12 when the positions of the lock 14 and one of the two grooves on the T-shaped rod 12 are aligned, and during the reverse movement of the oscillator 15 after switching, the lock 14 snaps off due to the oblique cut.

[0076] Optionally, the locking and movement mechanism can be supplemented with solenoids that control the position and pressing of the lock 14. The solenoids can be connected to a microcontroller, which in turn, to improve the quality of operation, can use information from various sensors that inform it about the state of the transmission elements - rotation speed, angle of rotation of the plate element, selected gear sensor, lock position sensor, and optimal control algorithms, etc.

[0077] The counter-wound spiral toothed synchronizer tracks 9a, 96 and 10a, 106 are the key elements of the connection of adjacent ring gears, there is at least one pair of them between adjacent ring gears, they allow both increasing and decreasing the gear ratio by rolling the gear 11 of the splined shaft from one ring gear of the plate element to another, without changing the direction of rotation of the first shaft, and perform the synchronization function when switching in a “tooth in tooth” transmission, that is, it is performed not by angular velocity, as with friction synchronizers, but by angle.

[0078] The outer and inner diameters of the ring gear are selected based on the pitch diameter, and the number of teeth is chosen so that the number of teeth on the counter-wound spiral synchronizer gears allows for shifting to the adjacent ring gear without jamming. Additional ring gears can be located at the intersections of the counter-wound spiral synchronizer gear tracks on the plate element, with the number of teeth proportional to the pitch diameter at the intersection on the plate element.To ensure an extended contact patch between the meshing teeth of a splined shaft gear (in this case, a spur gear) and the plate element, the shape of the teeth on the plate element is imprinted by the spatial position of the teeth of the first shaft gear, which change during rotation as they roll along the pitch circles of the ring gears and the pitch lines of the spiral synchronizers, as seen in the shape of the teeth in Fig. 1. In other words, the shape of the tooth on the plate element is non-standard, and the tooth profile is variable. A variable tooth profile can result in varying tooth deformations under load along its length, so this must be taken into account when designing a transmission. Materials that reduce this effect, such as polyamide, rimamide, caprolon, and others, can be used to manufacture the plate element with spiral synchronizer raceways.To prevent jamming at the junctions of the ring gears and the spiral synchronizer toothed raceways at acute angles, they must be connected with solid teeth, taking into account the change in radius, so that the diverging gap between them becomes greater than the protrusion of the splined shaft gear beyond the outer boundary of the ring gear or the spiral synchronizer toothed raceway, which is implemented and can be seen in Fig. 1. The transmission may contain one or more additional splined shafts with their own splined shaft gears moving along them and locking and moving mechanisms, operating independently of each other. In this case, the plate element becomes summing or intermediate, and then the number of transmission ratios is determined by the number of combinations of splined shaft gear positions at the input and output, without identical ones - N(N-1)+1, where N is the number of ring gears of the plate element.If there are input and output splined shafts, and the plate element is intermediate, then with two ring gears there are three transmission ratios, with three ring gears there are seven transmission ratios, with four ring gears there are thirteen transmission ratios, with five ring gears there are twenty-one possible transmission ratios, etc.

[0079] If the plate element is used as an intermediate one, then the input and output shafts can be located either on the same axis or at an angle to each other, but their axes belong to planes parallel to the plane of the plate element, and there can also be several output shafts, each with its own locking and movement mechanism.

[0080] In the case where the diameters of the splined shaft gears at the input and output are equal, the transmission can be supplemented with a second plate element that works in mirror image to the first, as in Fig. 5a, 5b, 6, which will further increase the transmitted torque up to two times without increasing the dimensions.

[0081] The locking and movement mechanism may have various design options based on mechanically or electromagnetically connected mechanisms with optional microcontroller control, discrete action mechanisms - Maltese, ratchet, mechanisms for converting rotation into reciprocating motion, snap-on mechanisms, mechanisms for moving the connected rod along rotating grooves of a special shape, including a combination of these mechanisms together with gearboxes that reduce the speed of their operation to ensure reliable switching in high-speed transmissions, etc., and in addition, it may also have microcontroller control via solenoids.For high-speed applications, a Maltese-type locking and shifting mechanism can be used. Its use allows for a reduction in operating speed by 3-20 times compared to the speed of plate elements, which additionally ensures switching reliability and allows for an increase in the operating speed of the transmission and the transmitted power, but requires higher manufacturing precision.

[0082] Fig. 2 shows another embodiment of a transmission for bicycles and motorcycles.

[0083] The design is similar to that described for Fig. 1 and is located on the rear wheel axle in place of the bicycle freewheel and sprockets, or in place of the bicycle's drive sprocket. The connection between the rotation source and the rotation consumer is via a shaft drive. A distinctive feature of the solution is the use of a linear-oscillating mechanism consisting of two toothed racks and a half-pinion on the axis of a plate element with spiral synchronizers, so that the rear wheel's supporting axle can pass through the center. The longitudinal movement of the splined shaft pinion or its rigid fixation is achieved by a carriage connected to a rod with projections. When the rod is pressed upward, it is rigidly fixed by the housing. When pressed downward, it disengages from the housing and engages the linear-oscillating mechanism at the desired moment. It moves until it locks into place with the housing in a different position if it is spring-loaded upward during movement.

[0084] Fig. 3a, b shows a variant of the transmission for bicycles and motorcycles with independent drives from the pedals and electric motor. Plate element 5 with five ring gears and spiral synchronizer tracks is installed in place of a standard bicycle cassette. The locking and movement mechanism operates by snapping the spring-loaded rod 22 of each carriage 21 into spiral grooves 23, 24 located on the second side of the plate element (Fig. 3b), and subsequent longitudinal movement of the carriage along the splined shaft such that the splined shaft gear rolls along the spiral synchronizer tracks during shifting. Features of the solution include the ability to use different distances between adjacent ring gears, and separate independent control of several incoming power flows, as well as the irreversibility of the solution.The spring-loaded rod must snap into the groove at the correct moment, which can be easily monitored by closing a microswitch at the desired angular position of the disc. The rod can be released by actuating the movable axis of the solenoid holding it while holding the control button. At the end of the switching groove, there is a raised section; when raised, the rod returns to its cocked position in the carriage, completing the switching process. The carriages are secured to the housing in stationary positions by spring-loaded locking pins.

[0085] Fig. 4 shows a variant of a transmission for a bicycle / motorcycle, where the spiral grooves on the reverse side of the plate element are transferred to the control drum, rotating synchronously with it. Thus, snapping the spring-loaded control rod of the carriage into the spiral grooves of the control drum allows for longitudinal movement of the carriage and the splined shaft gear, allowing the entire assembly to be positioned on one side of the plate element.The snapping of the spring-loaded rod is carried out by the operation of the solenoid, which holds it with its tongue, and the solenoid is activated in two cases: if the switch button (control buttons can be replaced by a microcontroller) for the upper gear is held down and the corresponding microswitch has been activated, indicating the desired angle of rotation of the control drum, such that the beginning of the control groove for the upper gear is under the rod, or if the button for switching to the lower gear is held down and the second microswitch has been activated, indicating the desired angle of rotation of the control drum, such that the beginning of the control groove for the lower gear is under the rod.

[0086] At the end of the control grooves, there are raised projections along which the piston rod is lifted out of the groove at the end of the shifting procedure and then snaps back into place with the solenoid's spring-loaded tongue. A spring-loaded protrusion secures the carriage to the housing in stationary positions.

[0087] Fig. 5a and b show a thirteen-speed transmission. The input and output splined shaft gears engage the splined shafts via ball bushings. Each splined shaft has four possible positions—both input and output. This results in sixteen possible combinations of the resulting transmission ratio, with no three identical combinations. With equal input and output gear diameters, the power flow can be transmitted by two intermediate plate elements, resulting in up to twice the transmitted power flow while maintaining the same overall dimensions. The carriages, which control the longitudinal position of the splined shaft gears, slide along guides using linear bearings and are controlled by connecting their rods to the control grooves of one of the plate elements.The snapping of the spring-loaded rod of each of the carriages is carried out by the actuation of the solenoid, which holds it with its tongue, and the solenoid is actuated in two cases: if the switch button (control buttons can be replaced by a microcontroller) for the upper gear is held down and the corresponding microswitch has been actuated, indicating the desired angle of rotation of the plate element, such that the beginning of the control groove for the upper gear is under the rod, or if the button for switching to the lower gear is held down and the second microswitch has been actuated, indicating the desired angle of rotation of the plate element, such that the beginning of the control groove for the lower gear is under the rod.

[0088] At the end of the control grooves, there are raised protrusions along which the piston rod of each carriage is lifted out of the groove at the end of the shifting procedure and then re-engaged by the spring-loaded solenoid tongue. The carriages are secured to the housing in stationary positions by a spring-loaded protrusion. This design can be supplemented with two more splined shafts, the positions of the gears on these splined shafts can be controlled from a second plate element.

[0089] Fig. 6 shows a variant of the transmission design for an automobile gearbox (AT). A seven-speed AT for a front-wheel drive vehicle is shown. A standard clutch is used to select the operating mode—forward, neutral, and reverse—using a switch with a typical inertial synchronizer. This mode is more conveniently implemented through an idler gear. Once selected, gear shifting occurs automatically from first to last. The design shown in Fig. 5 or Fig. 6 can be used as an innovative gearbox component. Torque from the clutch disc passes through a hollow output shaft to the splined shaft gear furthest from the clutch disc, which can have three fixed positions on a plate element. The torque diverges between the two plate elements and converges on the splined shaft gear closest to the clutch disc, which also has three fixed positions.Thus, the automatic transmission has seven (9 - 2 = 7) possible combinations of gear ratios. From the output gear, rotation is transmitted via a splined shaft to the drive gear of the final drive, which is engaged via an inertial synchronizer when the drive mode is selected. The locking and shifting mechanism is based on two Maltese cross mechanisms, each connected to its own splined shaft gear. The rotation speed of the Maltese cross mechanism shafts is four times slower than the rotation speed of the plate elements, ensuring reliable and unambiguous connection of the Maltese cross to the two counter-rotating shafts with pinions. The longitudinal position of the two Maltese cross mechanisms and their connection to the shafts with pinions are controlled by two three-position solenoids, controlled by a microcontroller.

[0090] The embodiment of the invention demonstrates that the device solves the problems posed for transmissions. Since various changes and modifications are possible in implementing the invention without exceeding the scope of protection, this description and the solutions presented in Figs. 1-6 are illustrative examples and are not limiting.

Claims

CLAUSES OF THE INVENTION 1. A transmission characterized in that it includes a housing containing places for fastening shafts, at least one splined shaft and one shaft whose axis is orthogonal to the axis of said at least one splined shaft, at least one plate element mounted perpendicularly to the axis of said shaft, orthogonal to the axis of at least one splined shaft, a cylindrical gear with teeth mounted on each of the at least one splined shaft and configured to rotate together with the splined shaft and be positioned along it using a locking and moving mechanism, wherein at least one splined shaft is mounted parallel to the surface of the plate element at a distance from it and is provided with engagement means extending along it, allowing the cylindrical gear to rotate together with it, but to be longitudinally located at any point on the splined shaft, while on the surface of the plate element facing the splined shaft,at least two annular toothed turns are formed, connected by counter-wound spiral toothed synchronizer tracks, wherein the teeth of the cylindrical gear are in constant engagement with the teeth of the plate element, wherein the module of the teeth of the cylindrical gear and all the toothed elements of the plate element is the same, and the shape of the teeth of the plate element is not the same, depends on the radius of the tooth location, and is an imprint of the teeth of the cylindrical gear changing the spatial position when it rolls along the pitch circles and pitch arcs of the spiral toothed synchronizer tracks, wherein each of at least one splined shaft and its cylindrical gear are provided with their own one locking and movement mechanism, and each such locking and movement mechanism is designed with the possibility of linear positioning of the cylindrical gear along the splined shaft in such a way that the cylindrical gear is either longitudinally fixed,and its teeth are in constant engagement with the selected ring gear of the plate element, or moves longitudinally, rolling strictly along the teeth of the spiral gear tracks-synchronizers when the transmission ratio changes.

2. A transmission according to paragraph 1, characterized in that the step of changing the diameters of the ring gear turns is made equal or variable.

3. The transmission according to paragraph 1, characterized in that the projection of the axis of the splined shaft onto the plane of the plate element is a chord.

4. The transmission according to claim 1, characterized in that the number of pairs of spiral toothed synchronizer tracks connecting adjacent toothed turns may be greater than one.

5. The transmission according to claim 1, characterized in that the locking and movement mechanism is a discrete action mechanism with mechanical or electronic control.

6. A transmission according to paragraph 1, characterized in that, in the presence of several splined shafts, the plate element is summing or intermediate, wherein the cylindrical gear of each of the splined shafts is input or output, and the number of combinations of positions of the input and output cylindrical gears of the splined shafts minus the coinciding ones determines the number of transmission ratios.

7. The transmission according to paragraph 1, characterized in that if there are several splined shaft gears and their diameters are the same, the transmission additionally contains a second plate element installed in mirror image of the first one to transmit up to twice as much torque while maintaining the same dimensions.

8. A transmission according to paragraph 1, characterized in that the shape of the spiral toothed synchronizer track is made dependent on the selected type of control in the locking and movement mechanism, but in such a way that the teeth of the spline shaft gear have constant engagement with the spiral toothed synchronizer tracks of the plate element.

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