Progressive transmission gear

FIELD: transport.

SUBSTANCE: invention may be used in trackless vehicles with engine (automobiles). Proposed transmission gear has at least one spur gear 1, 2 and at least toothed device to be engaged with said spur gear 1, 2. Spur gear 1, 2 has teeth 11 arranged along a curve. Said curve feature curvature radius increasing monotonically in angular range of said curve above 90°. Spiral, particularly logarithmic spiral, is a preferable shape of said curve.

EFFECT: compact and simple design, smooth run.

32 cl, 24 dwg

 

Technical area

The invention concerns a progressive gear in accordance with the restrictive part of the formula of the invention 1.

The level of technology

Progressive transmission is used, for example, in the steering of vehicles, primarily in trackless vehicles with engine (cars). Usually when turning the steering wheel rotational movement through the Pitman shaft steering wheel is transmitted to a gear wheel which is engaged with the gear rack. Gear wheel begins to shift the rack, which, in turn, affects the position of the wheels. Progressive steering (or progressive transmission) gear ratio when the steering wheel starts to decrease from its maximum in the middle position. This means that in straight-line motion, that is, when the average position of the steering wheel, a relatively large rotation of the steering wheel causes only a slight change of direction. Conversely, when performing maneuvers, when the wheel is strongly inverted, a relatively small turning movement of the steering wheel causes a significant change of direction. This ratio is necessary when Parking the car or on the corners (intersections).

the level of modern technology offers various solutions, with the help of which you can achieve a progressive attitude in the transmission mechanism. However, such transmission mechanisms have a fairly complex design, which leads to an increase in the value of their production and maintenance. The disadvantages of transmission mechanisms, which consist of many parts, include the following: frequent occurrence of undesirable gaps in the joints of the transfer mechanism. Such mechanisms should always take into account fluctuations in torque. Also early enough reached a dead point.

Patent DE-A-T 146769 describes the steering mechanism for trackless vehicles with engine (cars) with variable gear ratio, and the transmission mechanism includes a gear wheel and the rack. The toothed wheel has a non-circular shape and is installed eccentric.

Patent DE-A-39'13'809 offers a guiding device with a small angle and the two elliptical gears.

Description of the invention

The objective of the invention is the creation of a progressive transmission mechanism, intended primarily for steering control of the vehicle. This gear should be relatively small and compact.

This problem is solved by a gear mechanism with signs of formulas of the invention 1.

Progressive transmission mechanism according to the invention comprises at least one cylindrical gears and gear device (parts with teeth) or device with the toothed wheel. Cylindrical gear wheel engages with the device. The teeth of cylindrical wheels are located on a curve. The radius of curvature of the curve increases monotonically in the angular range of more than 90°.

Thus, the teeth of the cylindrical wheel may be located on a curve, the radius of curvature of which increases monotonically in the angular range of more than 90°, and the remaining parts of the circumference bevel gears can be made in a straight line. These sites circumference or at least a part can also be a curve, the radius of curvature of the latter may be either constant or decrease. The above described principle permits and other forms of execution of the sample.

The most preferred form of the sample implies that the curve monotonically with increasing radius of curvature, at least in certain areas will form a spiral, the center of which should coincide with the axis of rotation of the bevel gears.

In a preferred form, the spiral should be logarithmic, that is, with every turn, the distance to its goal is true or pole should increase with the same factor.

The timing device in the preferred form of execution represents at least one of the rack below the slope. The number of gear racks must match the number of cylindrical gears.

Depending on the form of cylindrical wheels gear racks have the form of straight or curved lines with a slope. On sections of the logarithmic curve of the cylindrical wheel, a corresponding portion of the rack must be in the form of a straight line with a slope. Rounded curve portions of the cylindrical wheel must comply with the toothed rack in the form of a straight line positioned horizontally, if the center of the rounded portion of the curve lies on the axis of rotation of the bevel gears. On other sections, depending on the curve of the cylindrical wheel corresponding sections of the rack must be either inclined or have a curved shape.

With the proper adjustment of cylindrical gear wheels or pinions device endpoint rotational motion is achieved only after 3/4 turn bevel gears or gear/shaft Pitman arm on the steering wheel. That is, between two endpoints on the Pitman shaft steering can make 11/2 turns. This ratio, first of all, istihaada when two gears and more. This gear must be at least two toothed rails, parallel displaced with respect to each other and at least partially installed one after the other. This arrangement avoids fluctuations of torque.

A special form of gear wheels and rails allows you to achieve progressive steering without the use of additional parts. The Pitman shaft steering mounted directly on the gear, so we can get the gear without a gap.

In other forms of execution of the timing device is a second cylindrical gear wheel. The teeth of this wheel are also located on a curve, the radius of curvature of which increases monotonically in the angular range of more than 90°. In the preferred form of the curve must be in the form of a logarithmic spiral. The first cylindrical gear wheel must be connected to the drive shaft (shaft Pitman arm steering). The second cylindrical gear wheel must be connected to a shaft which drives a conventional gear or gear racks. This design allows easily and with little cost to retool or additionally be installed on cars progressive transmission mechanism.

For progressive transmission according to the invention features the RNO smooth change of torque. Using a symmetric arrangement of the individual parts, as well as three line scanner gears with parallel offset is achieved by a symmetric path.

Progressive transmission mechanism according to the invention is primarily suitable for use in the steering control of the car. Such a mechanism can be installed as in normal cars, and sports.

Curve, along which are located the teeth must reach its minimum radius of curvature at the point where the cylindrical gear wheel comes in contact or is in engagement with a toothed device, if the steering mechanism is in the middle position. Then at small deviations from the average position - gear ratio will change relatively slowly. In this case, the toothed rack which engages a cylindrical gear wheel, are not required to have expressed a cycloidal shape with vertical side surfaces.

Proceeding from the minimum radius of curvature, the radius of the curve must monotonically increase in the angular range of more than 90°, especially in the range of more than 180°. This monotonic increase allows to achieve a smooth, uniform changes of gear ratio in this angular range.

In the middle position of the steering mechanics is the mA distance between the axis of rotation of the bevel gears and the point of contact of the wheel with the timing device should be minimal, so that the steering mechanism is very slow to respond to rotation of the steering wheel.

Other preferred forms of execution of the sample derived from the dependent claims.

Brief description of drawings

Below using preferred embodiments which are shown in the accompanying drawings, explains the subject invention. In the drawings shows:

figa: schematic side view of the transmission mechanism according to the invention with the gear wheels and racks in the first form of execution; figb: rack in accordance with figa (top view); figs: a graph of the progression of the transfer mechanism according figa; Figg: advanced image transmission mechanism in accordance with Figo with two racks;

figa: detailed image of the gear wheel and the first version of the rack in its highest elevation;

figb: item rack in accordance with figa (top view);

figa: schematic side view of the transmission mechanism according to the invention with the gear wheels and racks in the second form of execution; figb: rack in accordance with figa (top view);

figs: a graph of the progression of the transfer mechanism according figa;

figa: schematic side view of the transmission mechanism according invented the Yu with a toothed wheel and a toothed rack in the third form of implementation; figb: the toothed rack in accordance with figa (top view);

figs: a graph of the progression of the transfer mechanism according figa;

figa: schematic side view of the transmission mechanism according to the invention with the gear wheels and racks in the fourth form of execution; figb: rack in accordance with figa (top view);

figs: a graph of the progression of the transfer mechanism according figa;

figa: schematic side view of the transmission mechanism according to the invention with the gear wheels and racks in the fifth form of implementation; figb: rack in accordance with figa (top view);

figs: a graph of the progression of the transfer mechanism according figa;

figa: detailed image of the toothed wheel and the second variant of the rack in its highest elevation; figb: item rack in accordance with figa (top view);

figa: detailed image of the gear wheel and the third option the rack in its highest elevation; figb: item rack in accordance with figa (top view);

figa: advanced image transmission mechanism according to the invention in the sixth form run; figb: schematic diagram of the gear wheels in accordance with figa (top view).

Ways of carrying out the invention

On figa and 1b depicts the PE the first embodiment of progressive transmission mechanism according to the invention, when it is used in the car. Gear consists of at least two, and preferably three cylindrical gear wheels (1, 2), which have a common axis of rotation (12). Bevel gears (1, 2) connected to the shaft Pitman arm to the steering, which is not depicted in this drawing. The Pitman shaft is in the desired position by means of a steering wheel of the vehicle.

Each of cylindrical gear wheels (1, 2) is engaged with the gear device in the form of a toothed rack (3, 4, 5) and moves along the rails (3, 4, 5). Thus the axis of rotation (12) moves along a horizontal straight line or rack (3, 4, 5) are shifted in the longitudinal direction. Third toothed rack (5) variable. She is depicted on Fig lighter in color than the rails (3, 4).

On figa shows two (or three) bevel gears (1, 2) in different positions P1, P2, P3 and P4, while rotating along the gear racks(4, 5, 6).

Bevel gears (1, 2) have teeth (11), which are located along the curve (10) (see figa). Curve (10) has a radius of curvature r, which monotonically increases in the angular range of more than 90° curve and, accordingly, the bevel gears (1, 2).

In this embodiment, the teeth are located on the curve (10) in the angular range of more than 180° and less than 360°, when atamna the remaining section of the circumference of the cylindrical wheel (1, 2) the teeth are missing. In the form of execution according figa and 1b on the segment of a circle, which is approaching 270°, there are the teeth (11), whereas the remaining (13) the circumference of the cylindrical wheel has the shape of a straight line.

Thus, the center of the curve (10) retains its position relative to the cylindrical wheel (1, 2), moreover, it coincides with the axis of rotation (12) of the cylindrical wheel (1, 2).

In the depicted embodiment, the curve (10) is a spiral, but rather a logarithmic spiral. Its center should coincide with the axis of rotation (12) bevel gears (1, 2).

Two (or three) bevel gears (1, 2), which are used in this embodiment have the same number of teeth and the same shape of the curve. However, in other embodiments, they must be identical. However, the first and second cylindrical wheel (1, 2) are arranged in different positions and in mirror symmetry with respect to each other. Their circle with a maximum radius of curvature r must lie in opposite directions (180°) relative to each other, and the circle with the smallest radius of curvature r in the same direction. Figa contains more visual image (position P1 and P4). The third cylindrical wheel is located parallel offset relation to the first toothed wheel 1 and on the same level. It is not visible on figa, since it is superimposed on the image of the first cylindrical gear (1).

Side surfaces of individual teeth of cylindrical gears (1, 2) and the gear rails (3, 4, 5) are optimized for each other. This ensures maximum noiseless and free from friction interaction between the individual gear wheels (1, 2) racks (3, 4, 5). Because these principles are known in the art, they will not be considered in detail.

Toothed rack (3, 4, 5) in this example have a rectangular shape and sloped. The tilt allows, inter alia, the movement of cylindrical gears toothed rails at a constant height of the axes of rotation of the cylindrical wheels. The rack should be parallel offset relation to each other and at least partially one over the other. The first and third rails (3, 5) are located near and parallel offset relation to each other. They should be identical in shape and have the same slope. Between them is a second toothed rack (4), the initial phase coincides with the end sections of the first and third rails (3, 5). The level of inclination of the second rail should be the same, but its direction is opposite to the inclination of the first and third rails (3, 5). The greatest rise timing of the rails (3, 4, 5) is in the transition region U. Cf is dnee position of the steering wheel and, accordingly, the gear wheels (1, 2) should correspond to the position P4, that is, when the gear wheel (1, 2) are the largest lifting gear racks (3, 4, 5). When turning the steering wheel to the left will be passed to the position P3, P2 and P1. If this is the first (and third, if there is one) gear (1) engages with a corresponding toothed rails (3, 5). Depending on your position when you turn the toothed wheel (1) begin to come into contact with the racks in the lines or points of contact, which is correlated with a monotonically increasing radius of curvature of the curve (10). This means that at position P4 tooth wheel, which engages with the rack meets the minimum radius of curvature, and at position P1 is maximum. The second gear wheel (2), located in the middle of rotating in free space without engagement with the rack. This rotation without catching most clearly seen in Figg.

The radius of curvature r of the curve will be minimal in the place where they come in contact gears (1, 2) and the rack (3, 4, 5) at the middle position of the steering wheel, that is, at the position P4. The minimum radius of curvature of the curve must be greater than the minimum distance between the curve (or teeth) and the axis of rotation (12)to its final drive ratio when the deviation of the steering wheel from Radnevo position became less.

When turning the steering wheel to the right first and third toothed wheel (1) will rotate without catching, and the second gear wheel (2) engages with a corresponding toothed rack (4). And in this case, the wheel will rotate from middle position P4 from the smallest radius of curvature to the largest. On Figg clearly seen as the one gear wheel rotates in mesh with the rack, and the other (or others) is idle.

The rise, which is achieved when moving from position P4 to the position P1 shown in figs. As can be seen from the drawing, an incremental rise is achieved in the angular range of 270°. This means that the steering wheel can be rotated up to 270°before it reaches the end point of the transmission mechanism. Because the steering wheel with the same result rotates in both directions, before it has reached its end point, you can make 11/2 turn.

On figaś3D shows a second form of execution of the transfer mechanism according to the invention. This example uses two bevel gears (1, 2) and two toothed racks (3, 4). On figa depicted both gears in the middle position P4, and in extreme position P1. The teeth of cylindrical gears (1, 2) are located along a logarithmic spiral in the angular range a, which approaches 180°. In primasius the m angular range slightly more than 90°, the radius of curvature of the curve is still monotonically increase, but the curve does not correspond to a logarithmic spiral. The segment of a circle in the remaining angular range again has the form of a straight line. This bevel gears (1, 2) are set in relation to its axis of rotation (12) in such a way that in the initial position of the steering wheel, i.e. in the area of greatest growth toothed rails (3, 4), the motion starts on that site which has the shape of a logarithmic spiral.

Toothed rack (3, 4), fitted to the cylindrical wheels (1, 2), first, in the place of its greatest growth, have the shape of a straight line with a slope, and then take the form of curved curve, it is also tilted.

On figs again depicted rise depending on the rotation angle of the steering wheel. In comparison with the first form of execution according figa-1c graphic line in the angular range between 180° and 270° are less curved.

In the form of execution according figa-4C there is only one cylindrical gear wheel (1) and only one toothed rack (3). A gear wheel (1) is depicted in the middle position P4 and in one of its extreme positions P1. The teeth (11) of the cylindrical wheel (1) are located on the curve is symmetric with respect to positive and negative rotation of the toothed wheel (1)from its mean position. The teeth (11) can be combined into two groups (14, 15). each group (14, 15) corresponds one curve (10), while both curves (10) pass through an angular range of 180°. They are arranged in mirror symmetry to a plane in which lies the axis of rotation (12). The curves one centre, it must coincide with the axis of rotation (12). When the wheels rotate in opposite directions. Thus the "egg-shaped" oval gear wheel, in which one curve constantly skips to another so that the maximum and minimum radii of curvature are the same. If the two curves toothed wheels (1) are logarithmic spirals, the toothed rack (3) has the form of a straight line. It has a tilt in both directions, starting from the middle position as the highest point. As can be seen from figs deviation on each of the sides is 180°. Due to this gear consists of a minimum number of parts, its design is compact and does not occupy much space. In addition, the production of such a mechanism does not require large expenditures.

In the form of execution according figa-5s again use two bevel gears (1, 6) and three toothed rack (3, 7, 8). Rack equipped with a parallel offset with respect to each other and at least partially one over the other. Gears (1, 6) is depicted in three positions. The first gear wheel (1) corresponds to the form of execution is uncatego wheel figa. The toothed rack (3), which relates to a toothed wheel (1)has the shape of a straight line with a slope in two directions. The teeth of the second wheel (6) arranged in a circle or ellipse. This toothed wheel (6) moves in two toothed rails (7, 8). The teeth of these rails (7, 8) are located along a horizontal straight line. Installed gears rotate to the left or right of the middle position P4. On figa depicts a single position during the rotation of the left. Helical gear (1) first engages with a corresponding toothed rack (3)installed at an angle. Round toothed wheel (6) rotates idle. After achieving the position of rotation is 180°, the toothed rack (3) with a slope ends, and a spiral gear wheel (1) starts to rotate idle. Due to the overlap zone of the two gear racks (3, 7) the force is transferred round toothed wheel (6), which moves along the first straight toothed rail (7) in the following angle range (not less than 90°). When turning right round toothed wheel (6) is engaged with the second straight gear rack (8). This rake is a direct continuation of the first toothed rack (7) - a continuation of the straight, but at the same time shifted longitudinally. As can be seen from figs, the endpoint with this arrangement is reached after a rotation of 270° ineach direction of rotation. In the zone of the rotation angle of the steering wheel between 180° and 270° rise in a straight line. For large deviations of the direction of lifting you can choose, because instead of round gears and straight toothed rack can be used in the curves, which were described in examples according figa-3D, with a corresponding adjustment. Additionally, to increase the number of revolutions can be arbitrarily extend the horizontal part of gear racks. Longer horizontal sections should be considered as a variant of the above-described arrangement of the construction details. This design is primarily suitable for trucks.

An embodiment according figa-6s in General corresponds to the form of execution shown on figa-5C. Only in this embodiment, two straight toothed racks are not separate devices. As a whole they are placed on a rack with tilt or at least connected with it. This results in a single toothed rack with one (at least), as in our example with two large sections (7', 8') and one narrow area (3'), located in the middle. Depending on the position of the steering wheel by rotation and, accordingly, the gear wheels (1, 6) or spiral gear wheel (1) engages in a narrow area (3', or round the wheel (6') is engaged with one of the wide sections (7', 8'). On figb can be seen that the toothed rack is extended on both sides. This form is recommended if instead of one round toothed wheels (6) are two round wheels, which are located on each side of the spiral gears (1). Thus again provides a symmetrical contour.

The area of greatest growth toothed rack may have a different design. On figa and 7b shows the first option. Here in the place of greatest growth is intermediate tooth (30). It should be noted that in this example both, and in the case of three - all three racks have such intermediate tooth (30). This arrangement provides a smooth ride.

On figa and 2B depicts another variant greatest lifting gear racks. There are no intermediate tooth. Each toothed rack ends with a tooth (31), established under the slope. The angle and distance to the next tooth of this Reiki fully correspond to the location of the remaining teeth. That is, one toothed rack ends before another begins. This means that the design has no teeth that overlap each other. In the production of this design is quite simple.

In the construction of the largest recovery under figa and 8b rack them which have the form, as in the above example - the upper teeth (31) sloped and meet the rest of the teeth. But in this case they are superimposed on top of the tooth (31) adjacent the rack. This variant has the following advantages: easy production and a smoother movement of the gears in contrast to the variant according figa and 2B.

The form of execution according figa and 9b differs from the previous one in the first place because here as a timing device is not toothed rack, and another cylindrical gear wheel, follower wheel (9). Cylindrical gear wheel 1 through the drive shaft or the Pitman shaft steering L is connected with a steering wheel and is driven wheel. This wheel through the drive shaft And connected with the gear R, and a toothed rack Z normal gear/rack and pinion.

Slave gear wheel (9) must have the same shape as the gear wheel according figa, and therefore details will not be described. Their teeth (10) it is engaged with a driven wheel (9)which has the same shape as the gear wheel according figa. That is the same shape of the curve and the same number of teeth as follower wheel (1). Ideally, two bevel gears (1, 9) must be identical. Both wheels can be in the form of a logarithmic spiral, but also another fo the mu curve, if the radii of curvature of the two curves monotonically increase in the angular range of 90° and complement each other. The centers of the curves in the above example again coincide with the axes of rotation of the gear wheels. However, figa and 9b are depicted in positions of rotation, which corresponds to the average position and steering wheel position, rotated 180°.

In the above-described examples, the centers of the curves coincide with the axes of rotation of the gear wheels. The axis of rotation, in addition, are bearing axis gears. These are the preferred forms of execution. Gears can be set differently, and the axis of rotation to position outside of the centers of curves. As mentioned above, the logarithmic spiral is the preferred shape of the curve. However, there are other curves if their radii of curvature monotonously increase in the angular range of 90°, and the shape of the toothed rack or the driven wheel, which engages with the toothed wheel, adapted and adjusted accordingly. Also it should be emphasized that various combinations of those principles, which describe different forms of execution. They are part of the explanation.

A list of reference designations

1 - the first cylindrical gear wheel

10 - curve

11 - tooth

12 - the axis of rotation

13 - residual plot

14 - the first groups of the teeth

15 - the second group of teeth

2 - the second cylindrical gear

3 - the first toothed rack

3' - a narrow stretch

30 - intermediate tooth

31 - teeth

4 - the second toothed rack

5 - third toothed rack

6 - round-gear

7 - first straight toothed rack

7' wide area

8 - the second straight toothed rack

8' - a narrow stretch

9 - follower wheel

A - drive shaft

L - the Pitman shaft steering

R - gear

Z - toothed rake, r is the radius of curvature

P1, P2, P3, P4 - position rotation

U - area (zone) overlap

K - curved line

1. Progressive mechanism for driving at least one cylindrical gear wheel (1, 2) and one timing device(3, 4, 5, 7, 8), with which engages a cylindrical gear wheel (1,2), the timing device consists of at least one Reiki(3, 4, 5, 7, 8), moreover, the cylindrical gear wheel (1, 2) has teeth (11)on the curve (10), having a radius of curvature (r)that is monotonically increasing in the angular range of the curve (10) more than 90°, while in the middle position of the mechanism for controlling the distance between the axis of rotation (12) bevel gears (1, 2) and the place of contact of spur gears (1, 2) with the timing device(3, 4, 5, 7, 8) is minimum is determined as being.

2. The mechanism according to claim 1, in which in the middle position (P4) bevel gears (1, 2) is the radius of curvature (r) is minimal.

3. The mechanism according to claim 1, in which curve (10) bevel gears (1, 2) is a spiral.

4. The mechanism according to claim 1, in which at least one curve (10) coincides with the axis of rotation (12) bevel gears (1, 2).

5. The mechanism according to claim 4, in which curve, at least in some areas is a spiral.

6. The mechanism according to claim 5, in which curve, at least in some areas, at least in one angular range of 90°, is the logarithmic spiral.

7. The mechanism according to any one of claims 1 to 6, in which the teeth (11) in the angular range of more than 180° and less than 360° are arranged along the curve (10), and the remaining segment of a circle bevel gears (1, 2) teeth are missing.

8. The mechanism according to claim 7, in which the teeth (11) in the angular range close to 270°, are located along the curve (10), and the remaining segment of a circle bevel gears (1, 2) teeth are missing.

9. The mechanism according to any one of claims 1 to 6, in which a cylindrical gear wheel (1, 2) has a first and a second group of teeth (14, 15), and the first and second group of teeth (14, 15) are located along the first or second curve (10), respectively, and first and second curve (10) pass through from the power range of 180° bevel gears (1, 2), both curves (10) are arranged in mirror symmetry.

10. The mechanism according to any one of claims 1 to 6, in which the transmission mechanism has at least one additional cylindrical gear wheel (6), the teeth of which are arranged in a circle.

11. The mechanism according to any one of claims 1 to 6, in which at least one rail (3, 4, 5) sloped.

12. The mechanism according to claim 11, in which at least one rail (3, 4, 5) has the largest lifting the intermediate tooth.

13. The mechanism according to any one of claims 1 to 6, in which at least two rails (3, 4, 5) are located in relation to each other with parallel offset and at least partially one over the other, and the transmission mechanism has at least two bevel gears (1, 2), and one cylindrical gear wheel (1, 2) is in engagement with one rail(3, 4, 5).

14. The mechanism 13, in which at least two rails (3, 4, 5), at least partially arranged one after the other, have a slope in opposite directions, and the highest rise on the same contiguous area.

15. The mechanism according to any one of claims 1 to 6, in which at least one rail has one wide area (7', 8') and one narrow area (3'), and depending on the position of the bevel gears (1) it is engaged in the narrow section (3'), or other cylindrical gear is olaso (6) engages in a wide area (7', 8').

16. The mechanism according to any one of claims 1 to 6, in which at least one rail (3, 4, 5) has teeth that are located on a straight line.

17. The mechanism according to any one of claims 1 to 6, in which at least one rail (3, 4, 5) has teeth located along a curved line (K).

18. The mechanism according to any one of claims 1 to 6, in which the average position of the steering mechanism of the curve (10) at the intersection of cylindrical gears (1, 2) with the timing device(3, 4, 5, 7, 8) has a minimum radius of curvature.

19. The mechanism p, in which the radius of curvature (r) of the curve (10), since the minimum radius of curvature increases monotonically in the angular range of not less than 90°.

20. The mechanism p, in which the radius of curvature (r) of the curve (10), since the minimum radius of curvature increases monotonically in the angular range of not less than 180°.

21. Mechanism of claim 1, wherein the mechanism includes at least two bevel gears (1, 2), rotating around a common axis of rotation (12).

22. The mechanism according to item 21, which is in the middle position of the steering mechanism of the curve (10), at least one of the cylindrical gear wheels (1, 2) has an increasing radius of curvature (r) at the intersection of cylindrical gear wheels (1, 2) and a gear device(3, 4, 5, 7, 8).

23. The mechanism according to item 21, in which the first cylindrical gear wheel (1) and the second cylindricus the e gear wheel (2), at least two cylindrical gears (1, 2), each of which consists of teeth located on the corresponding curve (10), in which each of the curves (10) has a radius of curvature (r)that increases monotonically in the angular range of the curve (10) more than 90°.

24. The mechanism according to item 21, in which the first cylindrical gear wheel (1) and a second cylindrical gear wheel (2) are arranged mirror-symmetrically.

25. The mechanism according to paragraph 24, in which the region of the first cylindrical gear wheel (1)having a minimum radius of curvature (r), and the area of the second cylindrical gear wheel (2)having the minimum radius of curvature (r)are in the same direction.

26. The mechanism according to any one of p-25, in which the third cylindrical gear wheel is located on the common axis of rotation (12) so that the first cylindrical gear wheel (1) and the third cylindrical gear wheel arranged on one level and are parallel offset each other.

27. The mechanism p, in which the timing device consists of a first rail (3), which is coupling with the first cylindrical gear wheel (1), second rail (4), a member of the clutch with the second cylindrical gear wheel (2), and third rail (5), which is coupling with the third cylindrical toothed wheel.

28. The mechanism by which the yubom one of claims 1 to 6, where:
the mechanism includes first, second and third cylindrical gear wheel (1, 2), which rotate around a common axis of rotation (12), where the third cylindrical gear wheel is parallel offset relation to the first cylindrical gear wheel (1) and in the same direction as the first cylindrical gear wheel (1), and
- the timing device consists of a first rail (3), which is coupling with the first cylindrical gear wheel (1), second rail (4), a member of the clutch with the second cylindrical gear wheel (2), and third rail (5), which is coupling with the third cylindrical toothed wheel.

29. Progressive mechanism to control the vehicle, consisting of:
- first, second and third cylindrical gear wheels (1, 2), which rotate around a common axis of rotation (12), where the second cylindrical gear wheel (2) is located between the first cylindrical gear wheel (1) and the third cylindrical gear wheel, and
the first rail (3), second rail (4) and third rail (5), which are located relative to each other with parallel offset and at least partially one over the other, which
at least one cylindrical gear wheel (1,2) includes many of the teeth (11)located under the curve (10), characterized in, Thu the curve (10) has a radius of curvature (r), monotonically increasing in the angular range of the curve (10) more than 90°,
the first cylindrical gear wheel (1) is adapted for insertion into engagement with the first rail (3), the second cylindrical gear wheel (2) adapted for introduction into engagement with the second rail (4) and the third cylindrical gear wheel (2) adapted for introduction into engagement with the third rail (5),
the third cylindrical gear wheel is located on the common axis of rotation (12) parallel offset and coincides with the first cylindrical gear wheel (1), and
the first rail (3) and the third rail (5) is identical in form.

30. The mechanism by clause 29, in which:
- when in the first position of the steering mechanism of the first cylindrical gear wheel (1) is engaged with the first rail (3) and the third cylindrical gear wheel is engaged with the third rail (5) and a second cylindrical gear wheel (2) is rotated in free space without gearing where:
- when in the second position of the steering mechanism of the second cylindrical gear wheel (2) is engaged with the second rail (4), and the first and third cylindrical gear wheel (1) rotate without catching.

31. The mechanism in clause 29 or 30 in which the first cylindrical gear wheel (1) and a second cylindrical gear wheel (2) are arranged in mirror C is metry with respect to each other on a common axis of rotation (12).

32. The mechanism according to any one of PP and 30, in which the first and third rail (3, 5) have the same slope and in which the second rail (4) is inclined in the opposite direction relative to the slope of the first and third rails.



 

Same patents:

FIELD: machine building.

SUBSTANCE: converter of gear ratio of transmission consists of planetary differential with driving carrier (2) and two central gears (5, 6) different in diametre. One of central gears (5) transfers rotation to output shaft (7). Second central gear (6) transfers rotation via reducer (8) shifting direction of rotation and friction clutch (9), driven disk of which is rigidly coupled with the output shaft, also to output shaft (7). Both central gears rotate the output shaft in one direction, but have different speed of rotation. Difference of rotation speed is compensated with the friction clutch also distributing load between arms of the differential.

EFFECT: decreased losses and simplification of design.

3 cl, 1 dwg

FIELD: transportation.

SUBSTANCE: device for spatial control comprises disc element, which is installed inside and in the same plane with internal frame element and is connected movably to its pair of opposite sides by two axes. The first actuator located under disc element is immovably fixed on internal frame element and via hollow axis it is connected to the second actuator. The second pair of opposite sides of internal frame element is movably fixed by two axes with external frame element, which is movably fixed by hollow axis to electric drive installed on base. On specified base bellows bottom is immovably fixed, and outlet of it is immovably fixed on the second actuator. Hollow central axis with its direct section passes inside hollow axis along normal line to base and provides for movable connection of disc element to base and electric drive, and from the side of local bend it passes through center of disc element along normal to its plane.

EFFECT: improved efficiency of device, possibility to transform circular rotation of axis into angular motion in single plane.

1 dwg

Pulse drive // 2328640

FIELD: engines and pumps.

SUBSTANCE: invention relates to pulsed drives designed to vary output shaft r.p.m. and can be used in various machinery. The drive incorporates a post, a motor, a driving shaft with a cam, a driven ratchet wheel with a pawl provided with a tooth to interact with the said ratchet wheel and a hole to interact with the cam. Note that the drive is furnished with the pawl position control system. The control system consists of an electrical magnet mounted onto the post nearby the pawl tooth and designed to hold out of contact with the ratchet wheel, and another electrical magnet arranged opposite the pawl medium part and designed to press it against the ratchet wheel.

EFFECT: automatically controlled gear ratio.

3 dwg

FIELD: mechanical engineering.

SUBSTANCE: gear ratio converter comprises planet differential provided with the driving carrier and central gear wheels of different diameters. One of the gear wheels is secured to the output shaft for permitting power transmission to the output shaft. The second gear wheel loads the friction device with a given sliding force. The driven part of the friction device is rigidly connected with the third central gear wheel that freely rotates on the output shaft and transmits rotation to the fourth central gear wheel through the reduction gear. The fourth central gear wheel is rigidly connected with the output shaft.

EFFECT: simplified design.

1 dwg

The invention relates to a work site, in particular to the node to move the products in the machines for the processing of tobacco products

The invention relates to mechanical engineering and can be used as a transformative mechanism when creating device of the rotary type, variable-speed drives, actuators, mechanisms of intermittent rotation, etc

The invention relates to the field of engineering, and in particular to mechanisms for converting rotary motion with constant frequency in the rotation with variable speed of rotation of the driven link and can be used in various fields of technology

FIELD: engines and pumps.

SUBSTANCE: internal combustion engine (ICE) comprises cylinders (1, 11), pistons (2, 10), an output shaft (12), systems of cooling, lubrication, supply, ignition, pistons (2, 10). The pistons (2, 10) are connected in pairs, via rods (3, 9) with a frame (5). The frame (5) is arranged with upper (6) and lower (7) geared racks. Longitudinal axes of upper (6) and lower (7) racks are displaced relative to each other and relative to the axis of pistons (2, 10). There are wheels (15, 16) are installed at the output shaft (12). Geared racks (6,7) engage with geared sectors (17, 18) of wheels (15, 16). If one piston (10) is in the upper dead point, then the other one (2) - in the lower one. Conversion of reciprocal motion of pistons (2, 10) into rotary motion of the output shaft (12) takes place as a result of displacement of the frame (5) with geared racks (6, 7). Also an ICE is represented in the invention, where the geared racks (6, 7) and geared sectors (17, 18) of the wheels (15, 16) are magnetised. Also one of the geared pair elements may be magnetised.

EFFECT: reduced friction between geared sectors of wheels and geared racks.

2 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: friction bearing (7) consists of bushing (17) out of synthetic plastic with at least one circular groove (16) made on external periphery surface (15) of bushing, of circular-shaped elastic element (18) inserted in circular groove (16) and of couple of periphery, axially symmetrical and turned inside surfaces (21, 22). Bushing (17) also has two pairs of slots (23, 24) and (25, 26) each positioned so, that surfaces (21, 22) run between them along circumference; the slots facilitate corresponding surfaces (21, 22) travelling in radial direction inside/outside. Further, the bushing has at least one pair of internal periphery surfaces (27, 28) turned outside and passing from outside into radial direction relative to pair of surfaces (21, 22). Each surface (27, 28) forms a gap with corresponding external periphery surface from the side of teeth and from opposite to it side of a shaft of steer rack; the shaft is inserted and fixed in a through orifice formed with pairs of surfaces (21, 22) and (27, 28). The section of each surface (21, 22) comes into a sliding contact with a corresponding external periphery surface of the shaft of the steer rack, except for external periphery surfaces from the side of teeth and for opposite to it side of the shaft of the steer rack. There is also disclosed the rack-and-pinion steer including the above said friction bearing.

EFFECT: facilitating specified rigidity for shaft of steer rack in its radial direction and in axial direction of drive gear; also facilitation of movable support with low friction resistance in axial direction of shaft; reduced effect of relaxation of stresses due to creep strain and heat prehistory.

9 cl, 10 dwg

FIELD: machine building.

SUBSTANCE: profiles of gears (1,2) are composed of similar turned one relative to another crowns. Crowns of gear (1) have one tooth and correspond to eccentric setoff circumferences (3). Crowns of gear (2) have crowns (8, 8', 8") of cycloidal profile. Each crown of one tooth gear (1) is formed with external sleeve (4) of bearing (5) set on eccentric set off section (6) of common shaft (7).

EFFECT: reduced skidding of engaged profiles.

5 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to tooth rack gear, transforming rotary motion into forward motion and on the contrary. It can be used instead of usual involute gear of rack-and-gear mechanisms in linear drives of stands, in devices of auto steering control, and also in load-lifting technology (rack-and-gear jack and suchlike). Rack toothing for linear drive contains wheel (1) and rack (2). Wheel is implemented with one tooth with profile in transverse section of wheel in the form of circumference (3), off-centre displaced from pivot pin of wheel (1). Skew tooth is formed by successive and continuous turn of transverse sections around wheel's axis with formation of helical surface. Rack (2) allows helical teeth (4) of cycloidal profile, conjugated to helical surface of wheel (1). In the second option wheel (1) allows also one tooth and composed from certain crowns, each of which allows profile in the form of off-centre shifted circumference. Teeth of rack (2) are composed also from several cycloidal crowns. Adjacent wheel crowns and racks are phase shifted relative to each other for pitch of corresponding crown, divided for number of crowns.

EFFECT: invention provides creation of small-capacity rack toothing and increasing of its load-carrying capacity.

4 cl, 6 dwg

FIELD: transportation.

SUBSTANCE: invention is related to steering mechanisms of wheel transport and traction machines, and may also find application in motor industry, tractor construction, machine-tool construction, instrument making, production of weight-lifting machines, where mechanisms are required with preset patterns of their separate work members movement. Steering mechanism comprises tooth gear with master gear (1) and tooth rack (6). Tooth rack (6) is made in the form of two parallel parts that move one along each other. Teeth (7) of racks are installed with the possibility of alternate engagement with gear in radiuses of its dividing circumferences, which makes it possible to obtain an alternation transmission ratio.

EFFECT: makes it possible to improve controllability of transport vehicle due to provision of optimal pattern for variation of transmission ratio of rack steering mechanism, and also to increase traffic safety.

4 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention can be used in systems with piston, slider and other units. Proposed mechanism has housing, guides 2, slider 3, output shaft 4 with circumferential section 5 of gear rim alternately engaging with two sections 6, 7 of rim (racks) arranged from side of slider 3 with teeth orientated in opposite direction. End working teeth of edges of rim sections 5-7 are made with body truncation surface having at least one bend and orientated with tilting at acute angle by one extremity to surface of point and by other extremity, square to one of end faces. Surface of truncation of tooth body together with cut of top surface on opposite sections 5 and 6 or 5 and 7 of rim is orientated so that corresponding pairs of working teeth are aligned with ridges at insignificant clearance at opposite relative displacement.

EFFECT: reduced level of vibrations, eliminated possibility of wedging.

6 cl, 21 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to lever-tooth mechanisms with rack and it can be used to drive mechanisms of slotting machine, automobile windshield wiper, brush cleaner of screens of grain-cleaning machines, in automatic machines, etc. Proposed mechanism contains base, toothed wheel and crank hinge-mounted on base for rotation, and toothed rack engaging with toothed wheel. Lever with guide member is hinge-mounted on axle of toothed wheel. Guide member engages with rear side of toothed rack forming translational pair. Guide member is made in form of roller hinge-mounted for rotation on axle installed on free end of lever provided with thread. Axle of roller is provided with through cross hole to pass threaded end of lever. Roller is held on lever by nuts arranged from outer and inner sides of roller to adjust and fix radial clearance in meshing between rack and toothed wheels.

EFFECT: improved operating characteristics of mechanism.

2 dwg

Motion converter // 2308603

FIELD: mechanical engineering, particularly combustion engines, pumps and positive displacement compressors, namely mechanisms, which covert reciprocal movement into rotation and vice versa.

SUBSTANCE: motion converter comprises four cylinders grouped in pairs. Pistons of opposite cylinders are connected with each other through fixed bar. The converter has the first and the second pair of fixedly connected parallel toothed racks brought into engagement with corresponding segmental gear-wheels fixedly connected to one output shaft. In each segmented gear-wheel teeth extend for less than half of 180° pitch circle. Segmented gear-wheels cooperating with corresponding toothed racks are shifted through predetermined angle, preferably 90° angle, one relatively another.

EFFECT: increased performance.

3 cl, 5 dwg, 1 tbl

FIELD: the invention refers to the field of machine building namely to transformers of alternate/reciprocal motion into rotary and vice-versa and may be used in piston engines, pumps, compressors and other gears.

SUBSTANCE: the transformer is a planetary toothed mechanism consisting of a non-rotating central pinion with inner toothed gearing making alternate/reciprocal motion relatively to the axle rotating together with firmly connected with it from one side and interacting with the central pinion-satellite. The length of the toothed rim of the satellite is two times smaller then the length of the toothed rim of the central pinion, of the link or of the mechanism providing continuous engagement of the teeth of the central pinion and the satellite. The link and the mechanism are fulfilled in such a manner that install marginally allowable distance between the positions of their joining with the central pinion and with the satellite not installing the maximum allowable value of this distance. The central pinion and the satellite have figured different profile according to their toothed rims.

EFFECT: increases the coefficient of efficiency of transformation of the alternate/reciprocal motion into rotary and vice-versa and simplifies the construction of the toothed transformer.

10 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: according to invention, body 10 forms prismatic chamber 12 whose cross section is oval of odd order formed from arcs 34, 36, 38 with first smaller radius of curvature and arcs 40, 42, 44 with second, larger radius of curvature changing continuously and differentially one into the other. Thus, corresponding cylindrical parts of inner surface of chamber are formed. Chamber 12 accommodates rotating piston 60 whose cross section forms oval of the order smaller by 1 than order of chamber 12. Opposite parts of side surface are formed on rotating piston 60, one of which rotates in part of inner surface of radius of curvature equal to said part and the other adjoins opposite part of inner surface to slide along surface. rotating piston 60 divides chamber 12 in any position into two working spaces 78, 80. Instantaneous axes of rotation 112, 114 of rotating piston 60 are determined on middle plane of piston being fixed for a short time. Working agent to set rotating piston 60 into motion is periodically introduced into working spaces. Rotating piston 60 rotates in each phase of its motion in one of opposite parts of its side surface 70 in corresponding part of inner side surface 62 of chamber around corresponding instantaneous axis of rotation 112 and slides by opposite part of its surface 72 along corresponding opposite part of inner side surface 54 of chamber 12 to stop, i.e. until it comes into extreme position. Then, to execute following phase of movement, instantaneous axis of rotation jumps from previous position into second possible position 114 relative to piston and is fixed in this position for a short rime. Driven or driving shaft 102 is in engagement with rotating piston 60. To prevent kinematic ambiguity of instantaneous axis of rotation in extreme position, instantaneous axis of rotation is mechanically fixed in each extreme position for a time (Fig.1).

EFFECT: improved efficiency of machine in operation.

20 cl, 79 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building, namely, to rack-type steering mechanisms. Proposed mechanism comprises case, gear, moving rack engaging with said gear, rack guide and elastic appliance arranged between said case and rack guide. Rack guide comprises cylindrical body with wide annular recess on outer surface and at least one annular narrow grooves on bottom surface of wide annular recess, its width being smaller than that of wide annular recess section. Rack guide comprises sliding support, endless annular flexible element and cylindrical sleeve with cutout. Said cylindrical sleeve is press-fitted in case bore while sleeve edge comes in contact with case inner edge surface that defines case limit bore.

EFFECT: longer life.

7 cl, 15 dwg

FIELD: machine building.

SUBSTANCE: friction bearing (7) consists of bushing (17) out of synthetic plastic with at least one circular groove (16) made on external periphery surface (15) of bushing, of circular-shaped elastic element (18) inserted in circular groove (16) and of couple of periphery, axially symmetrical and turned inside surfaces (21, 22). Bushing (17) also has two pairs of slots (23, 24) and (25, 26) each positioned so, that surfaces (21, 22) run between them along circumference; the slots facilitate corresponding surfaces (21, 22) travelling in radial direction inside/outside. Further, the bushing has at least one pair of internal periphery surfaces (27, 28) turned outside and passing from outside into radial direction relative to pair of surfaces (21, 22). Each surface (27, 28) forms a gap with corresponding external periphery surface from the side of teeth and from opposite to it side of a shaft of steer rack; the shaft is inserted and fixed in a through orifice formed with pairs of surfaces (21, 22) and (27, 28). The section of each surface (21, 22) comes into a sliding contact with a corresponding external periphery surface of the shaft of the steer rack, except for external periphery surfaces from the side of teeth and for opposite to it side of the shaft of the steer rack. There is also disclosed the rack-and-pinion steer including the above said friction bearing.

EFFECT: facilitating specified rigidity for shaft of steer rack in its radial direction and in axial direction of drive gear; also facilitation of movable support with low friction resistance in axial direction of shaft; reduced effect of relaxation of stresses due to creep strain and heat prehistory.

9 cl, 10 dwg

FIELD: transport.

SUBSTANCE: invention relates to automotive industry. Proposed hinged system comprises hinge 7 arranged partially in sealing bellows, rod with hollow space 6 linked with hinge 7, sealing bellows that constricts inner space and gastight joint 13. Hinge 7 has case 8 and hinge pin 9 arranged to move relative to said case. Gastight joint 13 communicates hollow space 6 of rod 4 with inner space of sealing bellows and has one groove 15. Groove 15 is made in the hinge face side that faces rod 4, terminates in sealing bellows inner space and has radial outer end. Said radial outer end of hinge 15 terminates at a distance from hinge face side outer perimetre.

EFFECT: perfected gastight joint.

13 cl, 14 dwg

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