Driving pulley for steplessly adjustable drive

FIELD: transport engineering.

SUBSTANCE: invention can be used in wide range of vehicles, for instance, in minicars or trucks, snow movers, carts used when playing golf, cross country cars and scooters. Proposed driving pulley contains two centrifugal mechanisms, namely, positive unit and negative unit. Both units contains corresponding group of flyweights exposed to action of centrifugal force at rotation of driving pulley. Positive unit is used as standard speed governor which shifts one of two flanges of driving pulley towards other flange to increase diameter of running-over-over of driving pulley when speed rises. Negative unit is used to apply opposite force of positive unit when speed of rotation exceeds threshold value to delay rise of ratio of steplessly adjustable drive to higher ratio under action of positive unit. It provides maintenance of high speed of rotation at intensive acceleration and slow speed of rotation at slow speeds of vehicle.

EFFECT: provision of additional control over entire range of change of ratio of steplessly adjustable drive to decrease force created by centrifugal system of driving pulley.

12 cl, 6 dwg

 

Infinitely-adjustable gear (PDU) is a mechanical device, in which the gear ratio is continuously variable-adjustable over the operating range as opposed to the conventional transmission with a limited number of selectable gear ratios. PDU automatically changes the gear ratio when the required load and speed, providing increased torque at high loads and low speeds and even adjusting the rotational speed of the engine during acceleration of the vehicle. It is usually used in a wide range of vehicles, such as small cars or trucks, snowmobiles, transfer for use when playing Golf, ATV's and scooters. BRP is usually connected to the engine, as the internal combustion engine or an electric motor.

Conventional PDU contains a drive pulley mechanically connected to the engine, a driven pulley mechanically connected to the wheels or caterpillar, and keystone drive belt transmitting torque between a drive pulley and a driven pulley. On each pulley drive belt lateral sides is caught between two opposing flanges, which are coaxially installed on the main shaft. One of the wheels can move in the direction of the axis about which relative to the other flange. Each flange directly or indirectly, is in the transmitting torque of engagement with the respective main shaft.

Initially, for example, at the stop or at low speeds, the diameter of the circumference of the cover driving pulley is minimal, and the diameter of the circle cover secondary pulley. This corresponds to the minimum transmission number, since each full rotation of a driving pulley has the minimum number of revolutions or part of the turnover of the secondary pulley.

Drive pulley usually contains a centrifugal mechanism, which is designed to increase the gear ratio when increasing his speed. This centrifugal mechanism is able to apply force to the movable flange of the driving pulley of its movement closer to the fixed flange, thereby causing the drive belt turn the circumference of larger diameter around the driving pulley. At the same time, the shift in position of the belt toward the drive pulley causes the movable flange of the slave pulley to move away from the fixed flange.

Driven pulley PDU is sensitive to torque. This allows the slave pulley to balance the force created by the centrifugal mechanism of the driving pulley so as to allow the engine speed is visits to the optimum level before as BRP will begin to increase the gear ratio during acceleration. In addition, the driven pulley allows PDUs to reduce the gear ratio, if the load increases. In accordance with this driven pulley includes a Cam system, forcing a movable flange to move toward the fixed flange secondary pulley, when increased torque, thereby pulling back the drive belt and the opposing force created by the centrifugal mechanism driving pulley. Conventional Cam system includes a Cam disk having a lot symmetrically inclined beveled surfaces which interact with corresponding elements, driven by a Cam. These elements usually are floaters or spots. Cam disk or set of elements, driven by a Cam, mounted on the rear side of the fixed flange and the other of them is usually rigidly connected to the main shaft.

When using PDU its moving parts are constantly striving to change his position until equilibrium is reached or until they reach the maximum gear ratio. The gear ratio at which stabilizes PDU is a balance between the forces applied to the drive belt master and the slave pulley. When the maximum is often the first rotation gear ratio is maximum, since there is a maximum number of revolutions or part of the turnover of the secondary pulley on each full rotation of a driving pulley. In this case, the decrease in the engine speed also decreases the force created by the centrifugal mechanism. A return spring located in the master and slave pulleys allow the respective rolling wheels to move back to their original position or close to this position, corresponding to small transmission number.

Conventional centrifugal mechanism driving pulley, in General, contains a group of centrifugal weights, making its way through a pair of opposite inclined rails converging toward the periphery of the driving pulley. Each of these weights is subjected to centrifugal force F according to the following equation:

,

where m is the mass of the weight, r is the radius from the center of the main shaft, ω - speed and θ - the angle of inclined rails relative to the main shaft. As can be seen from this equation, the force is a function of the square of the speed, which means that the centrifugal force increases faster than increases in proportion to the frequency itself of rotation. In addition, the weights move away from the center of the main shaft, when increasing the centrifugal force, which, is turn, also increases strength, as the latter depends on the radius r. From this it follows that the centrifugal system driving pulley soon becomes proportionally stronger than the Cam system of the driven pulley, thereby shifting the position of the belt toward the drive pulley. As a result of this regular PDU committed too early to raise the gear ratio in the direction of maximum transmission number, when increasing the rotation speed of the driving pulley. This part is controlled by changing the angle of inclined guides as a function of the position of the weights thus, as a function of the gear ratio. The angle of inclined rails relative to the axis of rotation is smaller with a larger gear.

Thus, one of the drawbacks of the conventional driving pulley is the lack of direct control over the force created by the centrifugal mechanism. Change settings, such as the mass of the weights or profile of inclined rails to allow higher engine speed during acceleration, is not always appropriate or possible solution because of the impacts that it has on the overall behavior of a PDU. For example, if the PDU is designed for assumptions of low engine speed when the average operating speed in order to reduce supplies is Yes fuel consumption and noise, then during heavy acceleration, the engine speed, as is most likely too small. Conversely, if the PDU is designed to allow high engine speed during intense acceleration with the aim of obtaining maximum power from it, then the speed will probably be too high when the average operating speed.

The purpose of this invention is the provision of additional control across the range of change of the gear ratio PDU in order to reduce the force generated by the centrifugal driving pulley system when certain conditions are satisfied. Thus, the position of the driving pulley is normally controlled in a known manner by means of the first group of weights, which are part of the site called “positive node. Then, starting at the specified speed, begins to come into effect in the second group of weights, which are part of the site called “negative node. The main purpose of the negative node is the creation of axial force opposite to the force generated by the positive node to the second flange. However, this opposite force is essentially no effect if there is no contact between the negative node positive node. In the construction account is by the mass of the weights, the angles of inclined guides, the presence and length of the stoppers, the stiffness of the springs and their pre-loading, as well as all other parameters, so that the contact between the negative and positive nodes occurs only when the proper conditions are satisfied.

More specifically, according to the present invention offers a driving pulley for a continuously variable-variable transmission, which is made coaxially mounted around the main shaft and driven at a variable speed and contains:

the first flange having opposite first and second sides, the first side is provided with a tapered wall,

a second flange, coaxial with the first flange and having a conical wall facing the conical wall of the first flange to form a groove for the reception of the belt, around which runs around the belt, while the second flange is configured to move in the direction of the axis relative to the first flange,

first means for connecting the first flange to the main shaft when the transmitting torque of the engagement,

second means for connecting the second flange to the main shaft when the transmitting torque of the engagement,

positive site that contains:

positive carriage, coaxial with the first flange and rigidly connected with the second rebar is Oh,

third means for connecting the positive carriage to the main shaft when the transmitting torque of the engagement,

- at least two symmetrically located pairs of radially-converging in mutually opposite first inclined guide rails, each pair has one inclined guide connected with the positive carriage, and another angled guideline connected with the second side of the first flange, and

- radially-movable weights, each of which is located between the respective pair of the first inclined guides

fourth means for creating a return force that causes the second flange to move away from the first flange,

this drive pulley is different in that he also has a negative site that contains:

negative carriage, coaxial with the first flange and movable relative to its axis direction, and is designed and located with the opportunity to interact with positive slide

fifth means for connecting the negative carriage to the main shaft when the transmitting torque of the interaction,

- at least two symmetrically located pairs of radially converging and vzaimopoleznyh second inclined guide rails, each pair has one inclined guide connected to the denier, the second carriage, and another inclined guide connected to the front wall, fixed with respect to the first flange,

sixth means for connecting the end wall to the main shaft when the transmitting torque of the interaction,

- radially-movable weights, each of which is located between the respective pair of second inclined guides, and

seventh means for creating a return force which makes negative the carriage to move away from the first flange.

Now will be given non-restrictive description of a preferred variant of the invention with reference to the accompanying drawings, in which:

figure 1 is a view in longitudinal section of a driving pulley according to a preferred variant implementation of the present invention, showing two possible positions of the negative node, when the driving pulley is in the position of small reduction ratio,

figure 2 is a view in longitudinal section, similar to the view in figure 1 and showing two possible positions of the negative node, when the driving pulley is in high gear,

figure 3 is a view in radial section along the line III-III in figure 1,

4 is a view in radial section along the line IV-IV in figure 2,

5 is a view in longitudinal section along the line V-V in figure 4,

6 is a graph showing three typical experiment the global curves (1, 2, 3) frequency of rotation of the driving pulley as a function of vehicle speed during continuous and intensive acceleration from low speed and a typical curve (5) for continuous and intensive acceleration from average speed (4).

In further provides a list of reference numbers along with the names of the parts that are used in the accompanying drawings and the description:

10 - drive pulley,

12 - groove to accept the strap,

14 - keystone drive belt,

16 - main shaft,

18 is a hollow drum,

20 - end element (drum),

22 is a cylindrical body (drum),

24 - coupling,

28 - the first flange,

30 - conical wall (first flange),

36 - the second flange,

38 - conical wall (second flange),

40 - Bush (second flange),

42 - liners (second flange),

44 - hole (first flange),

46 - liner (in the hole of the first flange),

50 - positive node

52 - positive carriage,

54 - liners (positive return),

56 - Cam tracking elements (positive node)

58 - axis (positive node)

60 - slot (in the drum),

62 - weights (positive node)

64 - the first inclined guides (positive node)

66 - second inclined rails (LPO is positive node),

70 - spring (positive node)

72 - spring (negative node)

74 - intermediate part (cylindrical body),

78 - stoppers,

80 - negative node

82 is negative,the carriage

84 - liners (negative return),

86 - Cam tracking elements (negative node)

88 - axis (negative node)

90 - slots (in the drum),

92 - weights (negative node)

94 - the first inclined guides (negative node)

96 - the second inclined guides (negative node).

The driving pulley (10) is primarily intended for use in the infinitely-variable transmission (PDU) of the vehicle, as, for example, a subcompact car or truck, snowmobile, mikroavtobus for use when playing Golf, ATV or scooter. However, it may find application in other cases or in other environments where it may be useful to use a driving pulley (10), as, for example, in stationary commercial or industrial machines.

Figure 1-5 shows the driving pulley (10) according to the possible and preferred variant implementation of the present invention. It should be noted that the parts shown in figure 2-5 and marked by the reference numbers correspond to similar parts shown in figure 1. Within this is the first invention can be also created other options for its implementation.

The driving pulley (10) coaxially mounted around the main shaft (16), which is mechanically connected with the output shaft of the engine (not shown), such as an internal combustion engine of the vehicle. The main shaft (16) can be performed as part of a driving pulley (10) or may be a continuation of the shaft, around which is mounted the driving pulley (10). The advantage of using the main shaft (16) as part of the driving pulley (10) is that the latter can be pre-assembled and installed directly on the vehicle.

It should be noted that the term “axial”as used in the description and the claims, means that the corresponding elements have a common Central axis, and does not mean that the elements have a circular cross-section. In addition, since the driving pulley (10) must be driven with a high rotational speed, as is obvious to a person skilled in the art, all parts are balanced relative to the main shaft (16).

The driving pulley (10) comprises a first flange (28) and second flange (36), which are both facing each other and have opposite tapered walls (30, 38), forming between them a groove (12) for reception of the belt. Keystone drive belt (14) runs around in an arc around the greater part of the conical walls (30, 38). Almost half of the cool is a corresponding point, the transmitted drive belt (14)falls on the first flange (28), while the other half on the second flange (36).

The first flange (28) is preferably supported by means of a hollow drum (18). The drum (18) includes a radially directed end element (20) and a cylindrical housing (22). Cylindrical body (22) is attached to the periphery of the end member (20). End element (20) is in the transmitting torque of the interaction with the main shaft (16). To this end the element (20) may be rigidly connected to the main shaft corresponding tool, such as a slot or a cone, which is pressed into a corresponding mating part. It can also be connected by fasteners, welding, pressing, etc.

The drum (18) forms a shroud that covers and protects most of the other parts of the driving pulley (10). It should be noted that it is possible to manufacture a different drum (18)than that shown in figures 1 and 2. For example, a mechanical element (20) and the cylindrical body (22) can be divided into strips spaced from each other (not shown), or may be formed from a rigid grid (not shown).

The second flange (36) is preferably supported around the main shaft (16) through the elongated sleeve (40). The sleeve (40) coaxially mounted around the main shaft (16) which slides freely relative to the main shaft (16). Inserts (42) are used to separate the sleeve (40) from main shaft (16) and facilitate sliding. The sleeve (40) passes through the Central hole (44)made in the middle of the first flange (28). The hole (44) covers the insert (46)and the outer surface of the sleeve (40) is connected with the slide with the inner surface of the insert (46). Inserts (42) can be replaced by a linear guide (not shown), etc.

Figures 1 and 2, also shows a positive node (50), which adjusts the relative distance between the first flange (28) and second flange (36) depending on the frequency of rotation of the driving pulley (10). The distance between the flanges (28, 36) is also a function of the resultant axial force drive belt (14) to their conical walls (30, 38). Positive node (50) includes a carriage (52) positive node, coaxially and movably mounted on the main shaft (16), preferably by means of inserts (54). Carriage (52) positive node preferably rigidly connected to the sleeve (40) and is supported by it.

As best shown in figure 3, the carriage (52) positive node is functionally connected to the drum (18) through a set of Cam tracking elements (56), which are symmetrically located relative to the main shaft (16). Jaw tracking elements (56) preferably are the two who are the rollers in the amount of three rollers. On the other hand, Cam servo elements (56) can be floaters (not shown). Each roller (56) is preferably fitted around the liner or bearing. Each roller (56) coaxially located around the corresponding radially directed axis (58) and is directed longitudinally directed groove (60), located in the drum (18). The grooves (60) have a width slightly larger than the outer diameter of the rollers (56). In this case, the rollers (56) can freely and longitudinally move within the corresponding groove (60), the length of the slots (60) essentially corresponds to the amount of movement of the second flange (36).

When using the PDU portion of the torque from the engine is transmitted to the second flange (36)passes through the main shaft (16), the drum (18), the carriage (52) positive node through rollers (56) and grooves (60), a sleeve (40) and then, finally, reaches the second flange (36). Torque can also be transmitted in the other direction, for example, during deceleration. On the other hand, you can think of other ways to achieve torque transmission, one of which is the use of a linear guide (not shown) between the sleeve (40) and main shaft (16).

As shown in figures 1 and 2, the positive node (50) contains many weights (62), symmetrically located relative to the main shaft (16). Predpochtitel what about there are three sinker (62). Each sinker (62) located between the respective pair of inclined guides (64, 66) for weights. The number of weights (62) is equal to the number of pairs of inclined guides (64, 66). Both inclined guides (64, 66) of each pair are radially converging relative to the main shaft (16). In the shown embodiment of the invention, the first inclined guides (64) located on the carriage (52) positive node, and the second inclined guides (66) made in one piece with the rear side of the first flange (28).

As shown in figure 4, each sinker (62) preferably made of three parts, namely a Central cylindrical section and two identical cylindrical lateral parts.

The Central part has a diameter different from the diameter of the two lateral parts. The liner or bearing (not shown) allows the separate rotation of the Central part relative to the two side parts. One of the inclined guides (64, 66) is made of two parts, each of which is in engagement with the respective side parts and the other of the inclined guides (64, 66) is in interaction with the Central part. The angle of inclined guides (64, 66) relative to the longitudinal axis of the driving pulley preferably decreases outwards. In addition, part of the weights can be the ü is covered with a cushioning material, for example, a plastic composite material to avoid deformation of the inclined rails. For example, they can be made to slide on inclined guides (64, 66) instead of rolling over them.

Weights (62) can radially move between their respective pair of inclined guides (64, 66). Weights (62) under the action of centrifugal force is forced radially outward, thus acting on the inclined guides (64, 66) and creating a first force, displacing the second flange (36) toward the first flange (28) and the frequency-dependent rotation of a driving pulley (10). The first force tends to increase the diameter of the circumference of the cover groove (12) for reception of the belt and thereby the gear ratio of a PDU. The axial reaction force of the weights (62) is balanced by the force exerted by the first spring, which is preferably a cylindrical helical spring (70), coaxially installed around the main shaft (16) and pre-loaded in compression. In figure 1, 2 and 5, the spring (70) is installed between the carriage (52) positive node and a negative node (80), as it will be explained later. The first spring (70) may also be conical spring (not shown)located between the positive carriage (52) and a stationary location, such as, for example, the intermediate part (74). As is obvious to a specialist in this region is among the it is also possible other devices.

When using PDU in the case of constant speed, a balance is achieved between the forces tending to close the driving pulley (10) and the resulting weights (62) positive node (50), and by seeking to uncover the driving pulley (10) and resulting from the spring (70) and the axial reaction force of the belt (14) in the flanges (28, 36) of a driving pulley (10).

The present invention differs in that the driving pulley (10) further includes a negative node (80). The appointment of a negative unit (80) is the second force opposing the first force generated by the positive node (50). The second power will actually increase the speed at which changes the gear ratio compared to the ratio using similar driving pulley (10) without negative node (80). The second force acts against the first force, mainly during acceleration. However, depending on the design it may be useful in other situations.

The design of the negative node (80) is similar to the design of positive node (50). Negative node (80) contains the negative carriage (82), which is movably mounted around the main shaft (16), preferably by means of liners (84) or linear bearing (not shown). In addition, the negative is a recreational site (80) contains many pairs of inclined guides (94, 96) for the weights, symmetrically located relative to the main shaft (16). Both inclined guides (94, 96) one pair of radially converge relative to the main shaft (16). The first inclined guides (94) located on the end wall (20), and the second inclined guides (96) - on the negative carriage (82). Weights (92), preferably manufactured as weights (62) positive node (50)located between each pair of naklonnykh guides (94, 96) for weights. Each sinker (92) of the negative node (80) can essentially radially to move between the respective pair of inclined guides (94, 96).

When using PDU weights (92) is forced radially outward by centrifugal force and effect on the inclined guides (94, 96), creating an axial reaction force that tends to move the negative carriage (82) toward the positive carriage (52). The second spring (72), which preferably is conical spring, heavily loaded in compression, is used to release negative carriage (82) from the back side of the flange (28). The second spring (72) one party relies on the ring part (74), rigidly connected with the inner side of the cylindrical body (22) of the drum (18). In this case, the negative carriage (80) will start to move from its original is the provisions, only if the axial reaction force generated during extrusion of weights (92) under the action of centrifugal force will be greater than the initial force pre-load of the second spring (72). This occurs at a given frequency of rotation of the driving pulley (10). In the shown embodiment of the invention, the first spring (70) also exerts a force which is directed against axial reaction forces generated by the weights (92).

As best shown in figure 4 and 5, the negative carriage (82) like the positive carriage (52) is functionally connected to the drum (18) through a set of Cam tracking elements (86), symmetrically located relative to the main shaft (16). Jaw tracking elements (86) are preferably rollers, three in number, or, alternatively, sliders (not shown). Each roller (86) is preferably a liner or bearing is mounted around a respective axis (88) and is directed longitudinally directed groove (90)located in the drum (18). Rollers (86) can freely and longitudinally move within their respective slots (90), the length of the slots (90) essentially corresponds to the amount of movement of the negative carriage (82). Rollers (86) and the grooves (90) allow the negative carriage (82) to follow the movement of the drum (18). It should be noted that the number of rollers 86) may be less especially due to the fact that there is no torque. It should also be noted that the rollers (86) or Cam followers elements of any other type may be replaced by a linear guide (not shown)installed between the negative carriage (82) and main shaft (16).

The behavior of the driving pulley (10) is not completely dependent on speed. In fact, in the preferred embodiment of the invention indirectly used driven pulley PDU to control special features of a driving pulley (10). As mentioned above, conventional driven pulley is a mechanical device sensitive to torque. If will increase the load, as, for example, increasing the torque from the engine, then the distance between the flanges of the driven pulley will tend to decrease in order to reduce the gear ratio of a PDU. The reduction gear ratio occurs when the axial reaction force of the belt (14) on the secondary pulley flange is greater than the axial reaction force of the weights (62) positive node (50). If it's going to take place, the driven pulley is slipping drive belt (14), when the gear ratio is above the minimum reduction ratio, thereby forcing people to increase the distance between the flanges of the driving pulley (10). If the PDU will be on m is the minimum transfer number, then the belt (14) do not shift, but the tension in him will be very large.

Negative node (80) is designed for more effective response PDU. This is because the negative carriage (82) of the negative node (80) can move in the range of provisions, which covers the range of provisions positive carriage (52). When the rotation speed of the driving pulley (10) is above the threshold value, dictated by pre-loading the second spring (72) and, optionally, pre-loading of the first spring (70), depends on the relative position between the positive carriage (52) and the negative carriage (82), the negative carriage (82) is moved closer to the positive carriage (52). There is an interaction between the positive carriage (52) and the negative carriage (82), if the rotational speed of the driving pulley (10) is quite high, depending on the gear ratio. If the gear ratio is small, the communication speed must be quite high. However, if the gear ratio is high, the positive carriage (52) is close to the negative node (82). During the interaction of the axial reaction force of the weights (62) positive carriage (52) is reduced by the axial reaction force of the weights (92) of the negative node (80) minus the force of the second spring (72), to ora increasingly as further compression of the spring. Of course, the threshold speed at which the negative carriage (82) begins to move, below the speed at which the positive node was usually begin to increase the gear ratio PDU.

In the future, is an example of a vehicle that has mechanical characteristics in a typical application of the vehicle engine and which is used for experiments on the master pulley embodying the present invention.

Some of the results of these experiments are shown in Fig.6 for a better illustration of the advantages of the present invention.

Example

Engine: 55 HP, about 5000 rpm

The maximum estimated vehicle speed: 160 km/h.

The outer diameter of the driving pulley: 164 mm

The distance between the centers of the drive and driven pulleys: 170 mm

The calculated belt length: 710 mm

Minimum gear ratio (underdrive): 0,4.

Maximum gear ratio (Overdrive)is 2.0.

Weights (positive node): 3×320,

Weights (negative node): 3×175,

The angles of inclined guides (relative to the longitudinal axis of the main shaft):

Gear ratio0,41,0 2,0
Inclined guides (positive node)80°60°55°
Inclined guides (negative node)-55°70°

Design:

Pre-loadSpring stiffness
The first spring (70)35 kg10 kg/cm
The second spring (72)135 kg30 kg/cm

In the normal host pulley steady increase in torque from the engine eventually increases its rotational speed, thus increases the frequency of rotation of the driving pulley (10)and the axial force-response weights (62) positive node (50). As mentioned above, the conventional centrifugal system soon becomes proportionally stronger than the Cam system secondary pulley, and usually too early increases the gear ratio in the direction of maximum transmission number. It is clear from the experimental curve 1 of figure 6, where the drive pulley had no negative node. In this example, the transition occurred near 2500 rpm and vehicle speed of about 20 km/h. Within a few seconds povertyeradication number increased load on the engine and held the rotational speed of the driving pulley (10) to about 3000 rpm The vehicle continued to accelerate, but the gear ratio PDU proportionally until it reaches a maximum value at 110 km/h. Then BRP was a single-speed transfer up to the maximum speed slightly below 140 km/h.

The experimental curve 2 figure 6 shows an example relationship between the speed of the vehicle and the rotational speed of the driving pulley (10), which is provided with a negative node (80) according to the present invention. In this case, the rotational speed was increased to about 3250 rpm before the change gear ratio of a PDU. In this example, the action of the negative carriage (82) begins with minimal gear. Because it reduces the influence of positive carriage (80), it seeks to create the overshoot in the rotation speed. In this case, with a transmission number of about 0.8 correlation between the speed of the vehicle and the rotational speed of the driving pulley (10) is essentially linear. The change in the curve occurred mainly because the corners in groups of inclined rails decreases towards the periphery of the driving pulley (10). The interaction between the positive carriage (52) and the negative carriage (82) continued all the way to the maximum speed of the vehicle 160 cmcas. This maximum speed was 20 km/h higher than in the previous example, as the internal combustion engine was allowed to give more power at higher speeds. In the experiment, the engine was allowed to reach such high speeds, since the gear ratio was lower than in the example illustrated in curve 1. For example, at 110 km/h ratio reached 2.0 by curve 1, while it was equal to 1.2 on the curve 2. When the maximum speed on curve 1, which is about 137 km/h, the speed was around 3500 rpm and speed was such that the engine could not create sufficient capacity under these conditions to achieve higher speed. On the curve 2 at 137 km/h, the engine speed was about 4750 rpm Increased power, exhaust from the engine, allowing the vehicle to reach speeds of 160 km/h and the engine to reach speeds above 5000 rpm/min

The experimental curve 3 figure 6 refers to the example of drive pulley (10)containing a negative node (80), in which the range of positions of the negative carriage (82) was limited group of blocks (78), shown in figure 1. The stoppers (78) is installed on the negative carriage (82) and rested in the intermediate part (74). Typically, and depending on to the reconstruction of the outer part of the negative carriage (82) can be used to limit the range of positions, when she rests in an intermediate portion (74) or some other part attached to the drum (18). The stoppers (78) reduce the movement of the negative carriage (82) at a distance of d1. This allows you to keep the initial action of the negative node (80) (to reduce the effect of overshoot) and allow BRP to increase the gear ratio from a lower speed, thereby maintaining low engine speed at a relatively low speed of the vehicle. Increasing the gear ratio has led to the displacement of the positive carriage (52) towards the negative carriage (82). Negative node (80) became applicable for the rest of acceleration as soon as there was an interaction between the positive carriage (52) and the negative carriage (82). After the end of acceleration and achieve a constant speed of the vehicle PDU finds a new equilibrium and the engine speed tends to decrease, due to changes in torque applied to the follower pulley.

Graph 6 reference number 4 marked the point when the vehicle speed was constant and equal to 70 km/h. At this point, the gear ratio is 1.5, and the frequency of rotation of the driving pulley (10) is about 2200 rpm In this case, continuous and intense at the root of this vehicle speed dependence between the speed of the vehicle and the rotational speed of the driving pulley (10) followed the experimental curve 5. First, the speed proportionally increased faster than the increased speed of the vehicle. This is due to the fact that a PDU within a few seconds reduced gear ratio to about 1, 2. The reduction ratio of the reduction occurred because a higher torque on the driven pulley reduced gear ratio. When this happened, the engine speed had the opportunity to grow. This increase in speed allowed the negative carriage (82) to move towards the positive carriage (52) and, in the end, to achieve, to contribute to the reduction gear ratio. The second part of this acceleration was the same as the second part of the acceleration on the experimental curve 3.

It should be noted that in this example, the driving pulley (10) is directly connected with the output shaft of the engine, as is the case in many applications. On the other hand, you can use the gear or similar device between the output shaft of the motor and drive pulley (10). Furthermore, the presence of the first spring (70) between the positive carriage (52) and the negative carriage (82) allows the negative node (80) can have a direct impact on positive node (50), even when they do not interact among themselves.

Depending to the regulations and conditions may not be an interaction between the positive carriage (52) and the negative carriage (82), if the vehicle is accelerating from a slow speed. For example, if the slave pulley attached only a small torque, the positive node (50) is almost free to move as soon as you change speed. Speed can be maintained lower than the threshold value, when in effect a negative node (80).

The present invention is not limited to the described variants of its implementation and covers any other alternatives within the limits defined by the claims.

1. The driving pulley (10) for infinitely-adjustable, made with coaxially installed around the main shaft (16) and for rotation with variable speed, containing:

the first flange (28)having opposite first and second sides, the first side is provided with a conical wall (30),

the second flange (36), coaxial with the first flange (28) and having a conical wall (38)facing the conical wall (30) of the first flange (28) for the formation of the groove (12) for reception of the belt, around which runs around the drive belt (14), while the second flange (36) is arranged to move in the direction of the axis relative to the first flange (28),

first means for connecting the first the flange (28) to the main shaft (16) when the transmitting torque of the interaction,

second means for connecting the second flange (36) to the main shaft (16) when the transmitting torque of the interaction,

positive node (50)containing:

- positive carriage (52), coaxial with the first flange (28) and is rigidly connected with the second flange (36),

third means for connecting the positive carriage (52) to the main shaft (16) when the transmitting torque of the interaction,

- at least two symmetrically located pairs of radially converging and vzaimopoleznyh inclined guides (64, 66), each pair has one inclined guide (64)connected to the positive carriage (52), and another inclined guide (66)connected with the second side of the first flange (28), and

- radially-movable weights (62), each located between a respective pair of the first inclined guides (64, 66),

fourth means for creating a return force that causes the second flange (36) to move from the first flange (28),

when the driving pulley (10) characterized in that it further contains a negative node (80)containing:

- the negative carriage (82), coaxial with the first flange (28) and movable relative to its axis direction, and is designed and located with the opportunity to interact with positive what Aretai (52),

fifth means for connecting the negative carriage (82) to the main shaft (16) when the transmitting torque of the interaction,

- at least two symmetrically located pairs of radially converging and vzaimopoleznyh second inclined guides (94, 96), with each pair has one inclined guide (96)connected with the negative carriage (82), and another inclined guide (94)connected to an end wall (20), fixed relative to the first flange (28),

sixth means for connecting the end wall (20) to the main shaft (16) when the transmitting torque of the interactions, and

- radially movable weights (92), each of which is located between the respective pair of second inclined guides (94, 96), and

seventh means for creating a return force which makes the negative carriage (82) to move from the first flange (36).

2. The driving pulley (10) under item 1, characterized in that the first means includes a hollow drum (18), coaxially located around the main shaft (16) and having one end (20)rigidly connected to the main shaft (16), and a second end rigidly connected to the second side of the first flange (28).

3. The driving pulley (10) p. 2, characterized in that the third means includes a multitude of pairs of radially protruding Cam witness ale is now (56) and the corresponding directed along the axis of the grooves (60), in each pair one of the Cam followers of the element (56) and groove (60) is located on the positive carriage (52)and the other on the drum (18).

4. The driving pulley (10) under item 3, characterized in that the Cam servo elements (56) are rollers.

5. The driving pulley (10) according to any one of paragraphs. 1-4, characterized in that the second means includes moving in the direction of the axis of the sleeve (40), coaxially mounted around the main shaft (16) and rigidly connecting together the second flange (36) and a positive carriage (52).

6. The driving pulley (10) according to any one of paragraphs. 1-5, characterized in that the fourth means includes a spring installed between the positive carriage (52) and the negative carriage (82).

7. The driving pulley (10) according to any one of paragraphs. 1-6, characterized in that the fifth means includes a multitude of pairs of radially protruding Cam tracking elements (86) and the corresponding directed along the axis of the grooves (90), and in each pair one of the Cam followers of the element (86) and groove (90) is located on the negative carriage (82), and the other on the drum (18).

8. The driving pulley (10) p. 7, characterized in that the Cam servo elements (86) are rollers.

9. The driving pulley (10) p. 2, characterized in that the end wall (20) is part of the drum (18).

10. The driving pulley (10) p. 9, wherein the seventh means includes a spring, Odie the end of which is connected to the drum (18), and the other end to the negative node (82).

11. The driving pulley (10) according to any one of paragraphs. 1-10, characterized in that it further includes means for restraining the negative carriage (82) relative to the positive carriage (52).

12. The driving pulley (10) under item 1, characterized in that the means for restraining the negative carriage (82) contains at least one stopper (78), installed between the upper part of the negative carriage (82) and place fixed relative to the first flange (28).



 

Same patents:

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FIELD: transport mechanical engineering.

SUBSTANCE: hydraulic vehicle comprises at lest one hydraulic pump (10) which is actuated by engine, one hydraulic motor for actuating wheel (31), hydraulic circuit (50) for connecting hydraulic pump (10) with hydraulic motor (30), and valve (60) for control of flow. The input shaft of hydraulic pump (10) is directly connected with the crankshaft of the engine. Valve (60) returns oil, which is supplied from hydraulic pump (10) to valve (60), to hydraulic pump (10) in the first position. In the second position, valve (60) supplies oil, which is supplied from hydraulic pump (10) to the valve, to hydraulic motor (30). In the third position, valve (60) supplies oil, which is supplied from hydraulic motor (10) to the valve, to the drain branch pipe of hydraulic motor (3).

EFFECT: simplified design and reduced weight.

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EFFECT: prolonged service life and enhanced reliability.

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FIELD: mechanical engineering.

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EFFECT: reduced sizes and weight.

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