Transmission

FIELD: transport.

SUBSTANCE: transmission comprises gear shift element (51) displacing towards gear shift and gear shift selection directions, gear shift lever (40) having a pair of fork parts (41) spaced apart in gear shift direction and gear shift fork (20-23) linked with gear shift lever via gear shifter (30). Aforesaid element (51) is moved to displace one of aforesaid fork parts to wards gear shifting to selectively move gear shift lever to make gear shifting with the help of gear shift fork and gear shifter rod. Aforesaid pair of fork parts (41) is arranged spaced apart towards gear shifting direction.

EFFECT: fast and efficient gear shifting.

4 cl, 7 dwg

 

The level of technology

The present invention relates to mechanical transmissions and, more specifically, to the design of the transmission unit of transmission, which includes the twin clutch.

Known mechanical automatic transmission using a torque Converter as transmissions for vehicles. These mechanical automatic transmission operation (gear selection and shift) transmission reported manually switching and coupling and uncoupling of the clutch is carried by the actuator, which does not require a torque Converter automatic gearshift. The transmission includes a shaft gear, is arranged to move in the direction of shift in the direction of the gear selection by means of sliding and rotation, many of the change-over lever (switch brackets), which are located in the direction of the gear selection, and switching rods (rods), which connect the switching levers and switching plugs, respectively. In addition, the switching element (switching mechanism), which is made in the form of dogs, is located on the shaft of the gear so that it stands out, and a pair of fork portions located at each change-over lever in such a way that they re the Seine from each other in the direction of the switch. In addition, the shaft gear is moved by the actuator in a mechanical automatic transmission, whereby the clevis part of the change-over lever selectively starts to move in the direction of switching of the switching element so that the switching fork works with the electoral move.

In addition, in the field of mechanical automatic transmissions were developed automatic transmission with clutches coupled with two couplings. Automatic transmission with dual clutch from a state in which one gear is engaged through one of the couplings, the desired gear is engaged through the other clutch, and when the rotational speed of a given gear is synchronized with the rotational speed of a gear meshing through one clutch, one clutch output gear, whereby when the disconnection does not occur neutral condition, and can switch gears when virtually no interruption of the flow of power when shifting gears.

Thus, in the automatic transmission with dual clutch, since the switch operation for the two transmissions are carried out sequentially during a gear change, moving the switching element becomes complex is mi, and as a result this causes a risk that the switching time becomes long. To solve this problem was proposed mechanical automatic transmission, in which the space between the two forked parts located at each change-over lever is increased in the direction of the switch so that the switching element may include between two forked parts of the change-over lever to activate a given transmission, which is in the neutral position, only by moving the switching element from a position between the two forked parts of the switching lever, which is biased condition in the direction of the gear selection, while moving the switching element, thereby simplified (see document JP-A-2001-304411).

However, according to the document JP-A-2001-304411 to the switching element included between two forked parts, when the switching element is moved in the direction of the gear selection, a pair of fork parts should be located so that the space between the two forked parts was relatively wide. Therefore, when the transmission is engaged, since the distance over which the switching element is moved from its neutral position in the clevis part of the DL the rest, becomes relatively large, there is a risk that fast switching is not achieved.

In addition, when a pair of fork parts is such that the space between them is relatively widely increased, the force transmitted from the switching element of the forked portion becomes small, and the efficiency deteriorates. Further, the deterioration of efficiency will be described with reference to Fig.7. 7 schematically shows the structure of the switching mechanism of the switching lever, the relevant prior art document JP-A-2001-304411).

As shown in Fig.7, mechanical automatic transmission described in document JP-A-2001-304411, adopted a construction in which the switching element 71 wobbles during rotation of the shaft 70 of the control so that it pushes the fork portion 73 of the switching lever 72 in the direction of the switch. In this design, when the space L1 between the two forked parts 73 is increased, the switching element 71 pushes the fork part 73, when the switching element 71 is heavily tilted in the direction of the switch. Assuming that the power supplied to the forked part 73 torque T of the shaft 70 of the control, in this case, represents the tangential force F, the distance from the first point of contact between the switching ele is entom 71 and a forked part 73 to the axial center of the shaft 70 management represents the distance L2, and the slope of the line that connects the first point of contact with the axial center in the direction of the switch represents the angle α, a component of the tangential force F in the direction of switching, that is, the component force P1, which is the force that switches the change-over lever 72 in the direction of the shift obtained by the following equation (1).

According to equation (1) in the case when the distance L2 is essentially constantly regardless of the angle α, found that when the angle α increases from 0 to 90°, the component force P1 is reduced. Therefore, when the space L1 between the two forked parts 73 is increased according to the document JP-A-2001-304411, the force pushing the clevis portion 73 in the direction of switching is reduced, and therefore, it becomes difficult to move the switching lever 72 in the direction of the switch with good efficiency.

The invention

Thus, the aim of the invention is to provide a drive system which provides fast and efficient gear shifting by facilitating movements of the switching element without significantly increasing the space between the two forked parts arranged on a switching lever.

To achieve this goal according to the invention proposed transmission, the soda is containing:

the switching element is arranged to move in the direction of the switch and the direction of the gear selection;

the change-over lever having a pair of fork parts related to each other in the direction of the switch;

switching the plug connected to the switching lever through the switching rod, while

a switching element configured to move the actuator for pushing one of the forked portions in the direction of the switch to selectively move the switching lever in the direction of the switch to perform gear switching the fork by means of the change-over stock, and

a pair of fork portions is positioned in such a manner that it is shifted from each other in the direction of the gear selection.

Many of the change-over levers can be placed in the direction of the gear selection, and a lot of switching plugs can be connected with many switching levers, respectively.

The transmission may further comprise: a shaft running in the direction of the gear selection and configured to move in the direction of the gear selection and rotation of the actuator. The switching element may protrude from the outer periphery of the shaft.

Many switching element may be positioned on the shaft and unicentro from each other in the direction of the switch.

Brief description of drawings

Figure 1 is a typical diagram of an automatic transmission with dual clutch with six forward gears and one reverse gear, in which the invention applied.

Figure 2 is a perspective view showing the construction of the operating mechanism of the switching forks.

Figure 3 is a top view showing the configuration of the switching lever.

4 is an explanatory diagram showing the switching finger control when shifting, according to a variant embodiment of the invention.

5 is an explanatory diagram showing the switching finger control when shifting gears for transmission of the prior art.

6 is a schematic view showing the construction of the switching mechanism of the switching lever, the respective variant embodiment of the invention.

7 is a schematic view showing the construction of the switching mechanism of the change-over lever for the transmission of the prior art.

Detailed description of preferred embodiments of the invention

Next, on the basis of the attached drawings will be described variant embodiment of the invention.

Figure 1 shows and lustration diagram of the transmission node 1 transmission with dual clutch with six forward gears and one reverse gear, in which you applied the invention.

As shown in figure 1, the transmission node 1 includes two clutches 2, 3, the two main shaft 4, and 5, which are concentric, and two of the intermediate shaft 6, 7. The configuration provides for the transfer of power to the first main shaft 4 from the output shaft 9 of the engine through the first clutch 2, this configuration provides for the transfer of power to the second main shaft 5 to the output shaft 9 via the second clutch 3.

The first intermediate shaft 6 and the second intermediate shaft 7 are reflected from each other so that their axes parallel to the axes of the first main shaft 4 and the second main shaft 5, and is arranged to transfer power to the differential gear 10, which is in the final stages of the transmission unit 1. The gear 11 of the first transmission gear 12 of the second transmission gear 13 of the third gear and the gear 14 sixth gear supported rotatably on the first intermediate shaft 6 in such a way that they can rotate on it. The gear 15 of the fourth transmission gear 16 fifth gear and the gear 17 reverse gear supported rotatably on the second intermediate shaft 7 in such a way that they can rotate on it, and the gear 18 Parking transfer recorded on the second intermediate shaft 7.

In addition, the transmission node raspolojeny four switching fork 20-23. The first switching plug 20 and the second switching fork 21 are located so that they are slidable to move along the axis of the first intermediate shaft 6, and the third switching the plug 22 and the fourth switching fork 23 are arranged so that they are slidable to move along the axis of the second intermediate shaft 7. Due to the sliding movement of these switching forks 20-23 gear 12 of the second gear and the gear 14 sixth gear can be selectively engage and out of engagement with the first intermediate shaft 6 (operations shift) by means of a first switch of the plug 20 and the gear 11 of the first gear and the gear 13 of the third transmission can be selectively engage and out of engagement with the first intermediate shaft 6 (operations shift) using the second switching fork 21. In addition, the gear 15 of the fourth gear and the pinion gear 17 in the rear of the transmission can be selectively engage and out of engagement with the second intermediate shaft 7 (operations shift) using the third switch plug 22, and the gear 16 fifth gear and the gear 18 Parking transmission can be selectively engage and out of engagement with the second intermediate shaft 7 (the switch operation before the Sabbath.) using a fourth switching the fork 23. The gear 11 of the first transmission gear 13 of the third gear and the gear 16 fifth gear connected with the first main shaft 4, while the gear 12 of the second transmission gear 15 of the fourth transmission gear 14 sixth gear and the pinion gear 17 in the rear of the transmission is connected to the second main shaft 5.

Namely, the transmission node 1 transmission with dual clutch gear switch to first gear, third gear and fifth gear and they can be selectively carried out by means of a first clutch 2, whereas switching to second gear, fourth gear, sixth gear and rear gear and they can be selectively carried out by means of the second clutch 3.

Figure 2 shows a view in perspective showing the construction of the operating mechanism of the switching forks 20-23.

As shown in figure 2, the switching fork 20-23 installed, respectively, on four switching rods 30, which are arranged in such a way that they allow them to move forward and backward (in the direction of the shift), and, in addition, switching the rods 30 are, respectively, the switching levers 40. The change-over lever 40 is a sheet material, which is made U-shaped, open up, and located so that the forked portion 41 located at the upper end h of the STI, aligned in the direction of progressive movement forward and backward. Switching levers 40 are located so that the center line of their holes in the direction of progressive movement forward and back combined with each other in such position that they are open (or are in neutral positions).

The shaft 50 of the gear is supported on the switching lever 40 so that it passes above the center lines of holes in the direction of progressive movement forward and backward in such a way that it can rotate and move in the axial direction (the direction of the gear selection). The fingers 51 of the control dog (switching elements) are arranged on the shaft 50 of the gear so that they are held him down. Two fingers 51 are such that they are related to each other in the axial direction, and the fingers 51 are such that one finger 51 is located in the hole of one of the switching levers 40.

When the shaft 50 of the gear slides in the axial direction so that the finger 51 is located in the hole of the change-over lever 40 for a given transmission, and shaft 50 of the gear then rotates to push on the fork part 41 of the change-over lever 40 by means of the finger 51 of control is, switching fork 20-23 may move in the direction of progressive movement forward and backward through the change-over rod 30 so that the transmission of the corresponding switching plugs 20-23, can engage or withdraw from the engagement to perform operations gear.

The shaft 50 of the gear is driven by a motor 60 gear and is driven to slide in the axial direction by an electric motor 61 of the gear selection by means of the actuator 63 with ball screw pair. The motor 60 of the gear and the motor 61 of the gear selection controlled by an electronic unit 62 of the control on the basis of a shift lever, not shown, and working conditions of the engine 8 is regulated so that the shift takes place sequentially, for example, when switching is carried out on a given transmission. The electronic unit 62 of the control also controls the action of the clutches 2, 3, occur when shifting. In particular, when the gear electronic unit 62 controls the other clutch 3 or 2 for entering into engagement with the next gear transmission from a state obtained before occurred gear when one of the clutches 2 or 3 engages when the maintenance is alinia gear, which engages with one of the clutches 2 or 3. In this case, at the time when the rotational speed of the gear that engages, is synchronized with the rotational speed of the previous gear, the final gear output gear thereby to perform switching of the transmission so that almost without interrupting the flow of power when shifting gears.

Figure 3 shows a top view showing the configuration of the change-over lever 40.

As shown in figure 3, the change-over lever 40 in this embodiment of the invention is made with a bend so that a pair of opposed fork parts 41 are offset from each other in the axial direction. That is the opposite forked portion 41 are displaced from each other in the axial direction (the direction of the gear selection).

Figure 4 shows an explanatory diagram which illustrates the displacement of the fingers 51 of the control when shifting gears. In this drawing, for example, shows the stages of the shift fingers 51 management from complete shift to the fourth transfer by withdrawing from the engagement or previous gear third gear until completion of switching to another gear.

In this drawing, the vertical direction shows the direction of the gear, and the horizontal direction indicates the direction of the gear selection. The Central position of the vertical line indicates the neutral position. Each pair of forked portions 41 is moved by one unit vertical in the drawing, and when moving vertically to the outside is shifting in the transmission, which corresponds to such movement of the clevis part. In addition, the fingers 51 of the control is moved vertically by one unit from the vertical center of the drawing, when the rotating shaft 50 of the gear.

(Beznagruzochnyh state) Is beznagruzochnyh state is a state in which switching to the fourth transfer just completed. In beznagruzochnyh state right finger 51A management moved the internal side of the forked portion 41f of the fourth transmission so as to shift it to the outside, whereby engages the gear of the fourth gear. In this state, the fork portion 41p third gear also moves outward.

(Phase 1) Fingers 51A, 51b of the control is moved to the upper position shift, as seen in the drawing.

(Phase 2) Fingers 51A, 51b of the control is moved to the left in the drawing so that the left finger 51b management moved to the same horizontal position (the same position in the direction of the gear selection), as the forked portion 41d of the first pass.

(Stage 3) Fingers 51A, 51b management moved down in the neutral position in the drawing, whereby the left finger 51b management pushes the inner side of the forked portion 41d of the first transmission so that it moves it down. As a result, the clevis portion 41p third gear is moved to the neutral position, whereby the third transmission comes out of gear (complete removal of the mesh of the previous gear).

(Step 4) Fingers 51A, 51b of the control is moved to the right in the drawing so that the right finger 51A management rests on the left side of the fork part a reverse gear.

(Step 5) Fingers 51A, 51b of the control is moved downward in the drawing so that the right finger 51A control rests in the inner side of the forked portion 41f of the fourth transfer.

(Step 6) Fingers 51A, 51b of the control is moved to the right in the drawing so that the right finger 51A management rests on the left side of the forked portion 41h of the Parking gear.

(Step 7) Fingers 51A, 51b of the control is moved upward in the drawing so that the right finger 51A management pushes the inner side of the forked portion 41g fifth gear so that it moves the forked portion 41g fifth gear position switch, resulting in the completed switching to another gear.

Thus the m in this embodiment of the invention, shifting from complete engagement of the fourth transmission until completion of engagement of the fifth transmission is completed in the course of seven steps.

Next, as a comparative example will be described stages of switching fingers 51 of the control by the transmission node, the relevant prior art.

Figure 5 shows an explanatory diagram which illustrates the switching of the fingers 51 of the control when shifting, and the switching stages of the fingers 51 of the control shown from the completion of switching to the fourth transfer by withdrawing from the engagement or previous gear third gear until completion of switching to another gear.

In a transmission node corresponding to the prior art, a pair of fork portions 41 of each of the change-over lever 40 is deflected in the direction of the switch, and is in the same position in the direction of the switch.

(Beznagruzochnyh state) As in the embodiment of the invention, the right finger 51A management pushes the inner side of the forked portion 41f' so to move it outward, whereby engages the gear of the fourth gear. In this state, the fork portion 41p' third gear also moves outward.

(Phase 1) is alcy 51A, 51b control is moved to the left in the drawing so that the left finger 51b management rests on the right side of the forked portion 41d' first pass.

(Phase 2) Fingers 51A, 51b of the control is moved to the upper position of the switch in the drawing.

(Stage 3) Fingers 51A, 51b of the control is moved to the left in the drawing so that the left finger 51b management moved to the same horizontal position, as and a forked portion 41d' first pass.

(Step 4) Fingers 51A, 51b management moved down in the neutral position in the drawing, whereby the left finger 51b management pushes the inner side of the forked portion 41d' first gear to move it down. In the forked portion 41p' third gear is moved to the neutral position, whereby the third gear of the transmission is derived from the mesh (complete removal of the mesh of the previous gear).

(Step 5) Fingers 51A, 51b of the control is moved to the right in the drawing so that the right finger 51A management rests on the left side of the fork part a' reverse gear.

(Step 6) Fingers 51A, 51b of the control is moved downward in the drawing so that they are moved to the lower position of the switch in the drawing.

(Step 7) Fingers 51A, 51b of the control is moved to the right in the drawing so that the right finger 51A controls peretse in the left side of the forked portion 41h' Parking gear.

(Step 8) Fingers 51A, 51b management moved up to the neutral position in the drawing.

(Step 9) Fingers 51A, 51b of the control is moved to the right in the drawing so that the right finger 51A management moved to the same horizontal position, as and a forked portion 41g' fifth gear.

(Step 10) Fingers 51A, 51b of the control is moved upward in the drawing so that the right finger 51A management pushes the inner side of the forked portion 41g' fifth gear so that it moves the forked portion 41g' fifth gear position switch, whereby the switch to the fifth transmission is completed.

As described above, the transmission node corresponding to the prior art, requires ten stages from completion of switching to the fourth transfer until completion of switching to another gear.

As a pair of fork portions 41 of each of the change-over lever 40 is designed so that it is deflected in the direction of switching, switching fingers 51 of the control, which is located between two forked parts 41 of the change-over lever 40 in the direction of the neutral position while maintaining engagement of the gear transmission requires two stages (from binarypackage state to stage 2), whereas in the embodiment of the invention the switch is dynatup (binarypackage state to stage 1). In addition, when switching finger 51 of control that rests against the side of one of the forked portions 41 of the change-over lever 40, which is in the neutral position, to the other forked portion 41 to push it outward to thereby switching the change-over lever 40, the transmission node corresponding to the prior art, requires three steps (from step 7 to step 10), whereas in the embodiment of the invention, the switching is completed during one stage (from stage 6 to stage 7).

Thus, in the embodiment of the invention, since the number of stages of switching fingers 51 of the control can be significantly reduced when the gear shift can be achieved by reducing the switching time. In addition, also when shifting to other programs the number of stages of switching fingers 51 control may be reduced.

In the embodiment of the invention, which eliminates the need for a considerable increase in the space between the two forked parts of the change-over lever 40 relative to the finger 51 of the control, as it has occurred in a transmission node corresponding to the prior art, when it is moved, the finger 51 of the control may rest against a forked portion 41 immediately, thus, provide the traveler a quick gear changes.

Figure 6 schematically shows the structure of the switching mechanism of the switching lever, the respective variant embodiment of the invention.

In this embodiment of the invention, since the space L3 between the two forked parts 41 may be set relatively narrow, finger 51 management can push the clevis portion 41 with a small tilt in the direction of the switch. Assuming that the power supplied to the forked part 41 torque T from the shaft 50 of the gear shift is in this case, the tangential force F, the distance from the first point of contact between the finger 51 management and a forked part 41 to the axial center of the shaft 50 of the gear is the distance L4, and the slope of the line that connects the first point of contact with the axial center of the shaft 50 of the gear in the direction of the offset direction is the angle β, the component of the tangential force F in the direction of displacement, i.e. the component force P2, which is the force that moves the fork part 41 in the direction of the switch, obtained using the following equation (2).

Therefore, in this embodiment of the invention, since the space L3 between the two forked parts 41 are relatively narrow, and therefore, the angle β is reduced to a smaller angle, as long as the ANO in equation (2), component power of 2 not significantly reduced relative to the tangential force F. in Addition, since the distance L4 remains essentially constant regardless of the angle β, the torque T of the shaft 50 of the gear is transmitted with good efficiency, as a force that pushes the fork portion 41 in the direction of the switch, thus ensuring the movement of the switching lever 40 in the direction of the switch with good efficiency.

In addition, because they use more than one finger 51 control, even in the case when you need to switch a lot of gear, each finger 51 perform control so that it activates a part of the change-over levers, whereby the offset distance of each finger control in the direction of switching can be reduced. Therefore, the switching mechanism for the fingers 51 of the control can be compact in size relative to the direction of the switch.

In addition, the direction in which rejected the clevis portion 41 may be set appropriately for each of the switching levers depending on the quantity and location of gear. In addition, the invention can be applied to a transmission unit with a different number of gears compared to the embodiment of the invention, the number of fingers 51 of the control mo is et to be set accordingly depending on the number of used gear.

According to the object of the invention, by properly setting the direction of deviation of fork parts in accordance with the location of the change-over rod, when the switching element is moved in the direction of the slide so that it rests against the side of one of the forked parts for the gearshift, in the case when the switching element is moved in the direction of the switch, the switching element may abut the inner side of the other fork parts. Consequently, since the movement of the switching element when the switching gear simplified without significantly increasing the space between the two forked parts, can be achieved fast and efficient shifting.

According to the object of the invention the switching element can be moved in the direction of the switch and the direction of the gear selection by means of the rotation and displacement of the shaft in the direction of the gear selection by means of the actuator. Therefore, the switching mechanism for the displacement of the switching element in the direction of the switch and the direction of the gear selection can be made simple.

According to the object of the present invention, since the switching elements are arranged on the shaft in the amount of more than one so that they are related to each other in the direction of the selection of the transmission, even in the case when there is a lot of gear that you want to switch, and therefore requires a lot of switching rods, each switching element may be designed to work with a part of the switching rods for gear, whereby the displacement of each switching element in the direction of the gear selection can be reduced. Therefore, a switching mechanism for switching element may have a compact size relative to the direction of the gear selection.

1. Transmission containing a switching element configured to move in the direction of the switch and the direction of the gear selection; a switching lever having a pair of fork parts related to each other in the direction of the switch; and a switching plug, connected to the switching lever through the switching rod, while the switching element is configured to move the actuator for pushing one of the forked portions in the direction of the switch to selectively move the switching lever in the direction of the switch to perform a gear change-over with a fork by means of the change-over rod, and a pair of fork portions is positioned in such a manner that it is shifted from each other in the direction gear selection.

2. Tran the mission according to claim 1, in which many of the change-over lever is in the direction of the gear selection, and many switching forks connected with many switching levers, respectively.

3. Transmission according to claim 1, additionally containing a shaft running in the direction of the gear selection, and is arranged to move in the direction of the gear selection and rotation of the actuator, while the switching element protrudes from the outer periphery of the shaft.

4. Transmission according to claim 3, in which many switching element is located on the shaft and related to each other in the direction of the switch.



 

Same patents:

FIELD: transport.

SUBSTANCE: vehicle transmission comprises multiple drive gears, input shaft, output shaft fitted in parallel with input shaft, driven gear and synch mechanism. Parking gear is made integral with synch mechanism bush. Packing gear and bearing on shaft extension overlap each other radially.

EFFECT: compact and simple design.

4 cl, 3 dwg

FIELD: transport.

SUBSTANCE: invention relates to automotive transmissions. Proposed transmission comprises parking gear lock (14) with locking part (26) to get in mesh with parking gear (12), parking rod (16) with thick part (15) to initiate parking gear lock (14), and bracket with rod rest element (34) to hold packing rod (16). Gear wheel lock (14) also has rest element. When thick part (15) goes out of contact with the ledge, rest element gets suspended on thick part (15) and locking gear lock (14) is held in position whereat locking part (26) is out of mesh with parking gear (12).

EFFECT: ruling out improper operation.

10 cl, 6 dwg

FIELD: motor car construction.

SUBSTANCE: synchronised automatic transmission contains blocking section of lever (88a-88c), brought into engagement with switching lever (65a-65d) separately from switching claw (70a-70c) and providing control of switching socket adjuster (64a-64c) with its transferring into neutral position. Selection mechanism (67) of switching is implemented with ability of activation of specified gear by means of brought into engagement of switching claw with switching lever of switching socket adjuster, corresponding specified gear and shifting of switching socket adjuster in direction of switching. Lock engine (80) is implemented with ability of control by switching socket adjuster, which is not a switching socket adjuster of specified gear, and provides its transferring into neutral position by means movement of blocking section of lever, after movement of switching claw, in the selected direction, and it brought this blocking section of lever into engagement with switching lever of switching socket adjuster, which is not a switching socket adjuster of specified gear.

EFFECT: invention can be used in vehicle (car), using synchroniser.

9 cl, 17 dwg

FIELD: transport.

SUBSTANCE: invention relates to thrown-in gear indicators incorporated with mechanical automotive transmissions. The proposed device comprises indicator (6) and, at least one acceleration pickup (7) arranged on gearshift lever (1) to vary car inclination.

EFFECT: reducing emergent situations.

19 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: invention is related to the field of motor transport machine building. System of automatic transmission control comprises pump, hydraulic distributor of modes having three positions, slide type pressure controller, hydraulic distributors of transmissions, pump filter, distributor filter, lubricating throttle, heat exchanger. In the first position hydraulic distributor of modes connects forward manifold and backward manifold to drain cavity. In the second position hydraulic distributor of modes connects forward manifold to the main manifold, and backward manifold to drain cavity. In the third position hydraulic distributor of modes connects forward manifold and backward manifold to the main manifold. Hydraulic distributors of transmissions are arranged as electromagnetic, and supply power fluid via control manifold to hydraulic cylinders of transmission control elements. Slide type pressure controller comprises stem with two pistons - left and right - that separate the stem into three sections. Pump filter is installed in supply channel between drain and controller drain channel. Distributor filter is installed in main manifold between pump and hydraulic distributor of modes. Lubricating throttle is installed in lubricating manifold, through which liquid is supplied to lubrication system. Heat exchanger is installed between lubricating system and lubricating throttle.

EFFECT: higher reliability of automatic transmission.

2 cl, 2 dwg

Gearbox // 2278793

FIELD: automotive industry.

SUBSTANCE: proposed gearbox contains great number of gears forming step up and down stages. Each set is formed by transmission gear fixed on shaft and installed for connection with shaft through sliding gear. Each end outlet mechanism is firmed by end outlet member (101, 102, 103, 104 - which are clutches) and connected with it by shifter fork (105, 106, 107, 108). Shifter forks (105, 106, 107, 108) are arranged on shaft 109 for axial travel. Transmission stages are engaged by connecting sliding gear with carrying shaft by means of end outlet member (101, 102, 103, 104). End outlet mechanism is set into action by end actuating mechanism. Sequence of speed changing is not set in end actuating mechanism. End actuating mechanism contains at least one main actuating member III - shifter pin, which comes into active engagement with end outlet members 101, 102, 103, 104. Possibility of engagement of one transfer stage by means of first end outlet mechanism is provided. And then at least one main actuating member can come into active engagement with other end mechanism without disengagement of stage preliminarily shifted in. Each actuating mechanism contains at least one auxiliary actuating member (113, 116, -thin cams). Description of automobile with such gearbox is provided. Proposed invention provides gearbox in which sequence of speed changing in end actuating mechanism is not set, time of speed changing is considerably reduced and safety is increased.

EFFECT: simple design of gearbox with minimum possible number of parts, ease of control without additional safety precautions.

68 cl, 44 dwg

The invention relates to an improved composite mechanical design of transmission transmission gears with spiral teeth, it is preferable to transport the compound transmissions with multiple essentially identical to the intermediate shaft

The invention relates to the transport industry, in particular to the management of pyatikonechnoi transmission vehicle

The derailleur // 2025627
The invention relates to the field of engineering, more specifically to mechanisms with differential and freewheel, and can be used in instrumentation

FIELD: machine building.

SUBSTANCE: invention is related to the field of motor transport machine building. System of automatic transmission control comprises pump, hydraulic distributor of modes having three positions, slide type pressure controller, hydraulic distributors of transmissions, pump filter, distributor filter, lubricating throttle, heat exchanger. In the first position hydraulic distributor of modes connects forward manifold and backward manifold to drain cavity. In the second position hydraulic distributor of modes connects forward manifold to the main manifold, and backward manifold to drain cavity. In the third position hydraulic distributor of modes connects forward manifold and backward manifold to the main manifold. Hydraulic distributors of transmissions are arranged as electromagnetic, and supply power fluid via control manifold to hydraulic cylinders of transmission control elements. Slide type pressure controller comprises stem with two pistons - left and right - that separate the stem into three sections. Pump filter is installed in supply channel between drain and controller drain channel. Distributor filter is installed in main manifold between pump and hydraulic distributor of modes. Lubricating throttle is installed in lubricating manifold, through which liquid is supplied to lubrication system. Heat exchanger is installed between lubricating system and lubricating throttle.

EFFECT: higher reliability of automatic transmission.

2 cl, 2 dwg

FIELD: machine engineering, namely stable-speed drives of subsidiary aggregates.

SUBSTANCE: drive includes planetary ball gearing 1000 with gradual variation of gear ratio; step motor, worm gearing. Planetary ball gearing includes planetary members having rolling contact with inner and outer raceways and it may gradually vary gear ratio in range 0.3 - 1.0. Inlet shaft of said gearing is joined with primary propeller such as crankshaft of transport vehicle engine through driving belt B1. Gearing includes at least one outlet shaft coaxial to inlet shaft. Processor analyzes revolution number of crankshaft and respectively varies gear ratio with use of step motor joined with worm gearing for keeping stable revolution number at outlet regardless of revolution number of crankshaft.

EFFECT: possibility for keeping stable revolution number of gearing regardless of revolution number of crankshaft of primary propeller.

21 cl, 18 dwg, 3 tbl

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable gear box comprises a number of velocity governors. Driving disk (34), driven disk, and cylindrical bearing member (18) are in contact with the first, second, and third points on each of the velocity governors. Disk (60) of the thrust bearing transmits rotation to the driving disk. At least two generators of axial loading are interposed between the driven and driving disks and disk of the thrust bearing and can apply the axial loading to the driven disk.

EFFECT: improved structure.

62 cl, 27 dwg

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

8 dwg

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

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

The invention relates to continuously variable transmissions of the type band - gutter knock wheel

The invention relates to a mechanical transmission with a continuously variable change speed of the driven shaft and can be used in the automotive industry

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

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

8 dwg

Up!