Planet mechanism for gear box

FIELD: mechanical engineering.

SUBSTANCE: planet mechanism comprises solar pinion (43), carrier (41) with satellites (42), and crown gear wheel (39) with synchronizers. Carrier (41) has a bearing in outer wall (10) of the housing of the gear box which is defined by ball roller bearing (13) whose outer race is secured between the lid of the housing and reactive gear clutch member (38) which is set on the bearing. In front of bearing (13) are projections with transverse grooves. The projections are provided on the face of the bearing rods of satellites (42) and carrier (41). The grooves receive the split stop ring that embraces the step washer secured to carrier (41).

EFFECT: enhanced reliability and reduced sizes.

5 cl, 11 dwg

 

The technical solution relates to gears with variable speed used in vehicles.

On trucks, large capacity with the aim of obtaining a large range of gear ratios can be used gearbox combined kinematic diagram containing several pairs of the engagement between the gears arranged on parallel shafts with fixed axes of rotation, and the gear that represents blocked three planetary gear (Nedyalkov A.P. manual synchromesh transmission /collection of scientific work: Improvement of technical and economic indicators of motor vehicles. - US, 1993, s-85).

There are various schemes and designs of the combined transmissions (see, for example, the description of the utility model to the testimony of the Russian Federation No. 16717, IPC 60 To 17/06; international application WO 89/06194, IPC 60 To 20/10; the description given in the Federal Republic of Germany patent No. 1198213, NCI 63, 10/02; laid out in the Federal Republic of Germany application No. 3840403, IPC 60 To 17/08). Known also numerous examples that are used in planetary mechanisms (see, for example, laid out in the Federal Republic of Germany application patent No. 4216394, 4216397-4216400, 4439976, IPC F 16 N 57/08).

In such a combined gearbox to facilitate locking and unlocking of the planetary is about mechanism can be used various synchronizers (see.. for example, descriptions of inventions to the author certificates issued in the USSR, No. 1208377, IPC F 16 H 3/78, No. 1291751, IPC F 16 D 23/06, No. 1493834, IPC F 16 H 3/44, No. 1835889, IPC F 16 H 3/78; accepted proposal published in great Britain, No. 1249289, IPC F 23/06 16 D, F 16 H 3/78; the description of the patent granted in the USA, No. 4667538, NCI 74-785, IPC F 16 H 3/44; EPO published application No. 132023, IPC F 16 H 3/54 No. 536230, IPC F 16 H 3/78; international application WO 90/10806, 99/36712, IPC F 16 H 37/04 WO 00/37831, IPC F 16 H 57/08; laid out in the Federal Republic of Germany application No. 4121757, IPC 60 To 17/08, No. 19604824, IPC F 16 H 57/08; documents of title issued in Sweden, No. 504063, 504070, 514231, IPC F 16 H 3/78). When this locking and unlocking of the planetary mechanism can be accomplished by axial movement of the crown gear, which is shown in the security documents issued in Sweden, No. 453379, IPC 60 To 17/08 (EPO application No. 239555, IPC F 16 H 3/44), No. 463477, IPC F 16 D 23/06 (EPO application No. 423863, IPC F 16 H 3/78, U.S. patent No. 5083993, NCI 475-299), No. 512731, IPC F 16 H 3/78.

As a prototype adopted planetary gear transmission comprising a solar gear, drove with satellites located on the supporting rods, the crown gear with synchronizer, with the possibility of axial movement for alternate engagement with the blocking and reactive toothed coupling (see application WO 01/01016, IPC F 16 H 3/78). In this planetary mechanism carrier has a bearing in the cover of the transmission housing, the reactive toothed coupling half connected with plate spacer, placed between the gearbox housing and said cover. This increases the axial size of the transmission. Supporting rods satellites are forging a connection with the planet carrier, which complicates the disassembly of the mechanism when replacing bearings that have satellites.

Task - ensuring portability and maintainability planetary gear transmission.

The solution to this problem is provided by the fact that in a planetary transmission mechanism comprising a solar gear, drove with satellites located on the supporting rods, the crown gear with synchronizer, with the possibility of axial movement for alternate engagement with the blocking and reactive toothed coupling sleeve, a carrier has a foothold in the outer wall of the transmission housing, formed by a ball bearing, the outer ring which is fixed between the cover and reactive gear coupling, which is attached on the bearing, while the opposite of the bearing on the end face of the support rods of the satellites and the driver made the tabs with transverse grooves, in which installed split retaining ring covering the stepped washer attached to the cage.

When the pole was taken on a bearing fixed in the housing wall between wearing on him reactive the second toothed coupling half and lid, and fixing the supporting rods of the satellites specified retaining ring located in the groove made in these rods and a drive rod opposite the above-mentioned bearing, is compact and correspondingly decrease of metal planetary gear and the opportunity it convenient Assembly and disassembly for maintenance and repair.

Between the planet carrier and the shaft on which there is a sun gear, posted by tapered roller bearings.

In the support rods satellites made oblique hole, intersecting with their lateral surface and with a radial slot in the drive rod between the satellite and the washer opposite the mentioned shaft having a longitudinal bore for lubricating fluid.

In Valais, where there is a sun gear, made the cross hole, the axis of which is located in the plane between the satellites and the washer.

Around the conical bearing in the driver installed slinger. The slinger has a profile of the area.

1 shows a transmission for vehicles, in particular for trucks, longitudinal section.

Figure 2 shows separately the gearbox housing, a longitudinal section.

Figure 3 presents planetary gear transmission, a longitudinal section.

Figure 4 shows the crown gear kolesoprokatnogo mechanism, longitudinal section.

Figure 5 shows the plot of the crown gears, longitudinal section.

Figure 6 shows the synchronizer, longitudinal section.

7 given type And 6.

On Fig depicts the blocking toothed coupling, longitudinal section.

Figure 9 is given type B Fig.

Figure 10 shows the interaction of the teeth of the crown gears and synchronizer.

Figure 11 shows a fragment of the planetary mechanism.

Transmission (figure 1) includes a housing 1 consisting of front and rear Cup-shaped parts 2 and 3 (figure 2), the longitudinal walls of which are articulated together in the transverse plane 4. In the front wall 5 of the casing, which in this case is external, there are holes 11, 12 (figure 2) to accommodate the bearings 13, 14 (figure 1). Inside the transmission housing between the front 5 and rear walls 10 is a single continuous space 15 (2), free from any walls or intermediate walls. This single continuous space 15 between the front and rear outer walls 5 and 10 posted by the input shaft 16 (figure 1)mounted on the bearing 8, the side shaft 17, supported in bearings 9 and 14, the output shaft 18, mounted on ball bearing 13, the intermediate shaft 19 located between the input and output shafts 16 and 18 are coaxially therewith and supported on a tapered needle bearing is nick 20, located inside the input shaft 16, and the cylindrical bearing 21, is placed inside the output shaft 18.

On the input shaft 16 and the bearing mounted gear 22, having constant mesh with the gear 23 attached to the side shaft 17. Next to the gear 23 on the shaft 17 are connected gears 24 and 25, having constant mesh with gears 26 and 27, respectively, loosely mounted on the intermediate shaft 19. In addition, the shaft 17 is made sprockets 28 and 29, role playing gears, which have a constant mesh with the gears 30 and 31, respectively, freely arranged on the shaft 19.

Gears 22 and 26 may be alternately connected to the shaft 16 of the gear clutch 32. In addition, the gear 26 may be connected with the shaft 19 of the gear coupling 33. This coupling 33 may be connected with the shaft 19, the gear 27. The gears 30 and 31 can be alternately connected with the shaft 19 of the gear coupling 34. All these gear couplings are equipped with synchronizers.

About gear 31 on the shaft 19 is freely gear 35 connected to the shaft 19 of conventional toothed coupling 36 for inclusion in the gearbox reverse stroke by torque transmission from the shaft 17 of the ring gear 29 through the intermediate (parasitic) gear to the gear 35 and forth on the shaft 19.

In the same free space 15, in which are located ogeny mentioned shafts 17 and 19 with the gear wheels, at the rear of the outer wall 10 of the body is a two-speed single-row three planetary gear 37. This planetary mechanism to work as a reducer (demultiplier) provided with reactive toothed coupling 38, which is connected with the housing 1, namely with its Cup-shaped part 3. With reactive toothed coupling 38 has the ability to engage the crown gear wheel 39 at its axial movement toward the inner surface 40 (2) of the rear wall 10 of the housing 1, where the reactive coupling 38. Drove 41 (1) of the planetary mechanism, carrying satellites 42, made in one piece with the output shaft 18 of the transmission. With satellites 42 have a permanent engages the crown gear wheel 39 and a sun gear 43, which is located on the shaft 19 and represents the crown gear is made on this shaft. With the teeth of the sun gear 43 is splined connection blocking toothed coupling half 44 mounted on the shaft 19.

Jet gear coupling 38 mounted on ball bearing 13 located at the rear of the outer wall 10 of the transmission housing, and a drive rod 41, forming his support. The outer ring of the bearing 13 is fixed in the axial direction between wears his jet toothed coupling 38 and the cover 45, adjacent to the external surface of the rear wall 10. aktivna gear coupling 38 has from satellites 42 tapering towards the annular protrusion 46 with a tapered outer surface. Inside the protrusion 46 is threaded single threaded fasteners 47, in particular screws reactive toothed coupling 38 and the cover 45 is connected with the rear outer wall 10 of the body.

The internal teeth 48 of the crown gear wheel 39 having teeth located on the driver satellites 42, have the ability to mesh alternately with external teeth 49 on the locking teeth, the coupling 44 and the teeth on the gear reactive the coupling 38.

The teeth 48 of the crown wheel 39 near its ends are longitudinally tapering sections 50 and 51. The teeth 49 of each coupling is made extending to the crown wheel 39 to ensure proper engagement with its teeth, excluding spontaneous release of their gear. At the ends of the crown wheel 39 on his teeth 48 are made bevels 52, and at the end of each half opposite the satellites 42 teeth 49 are made bevels 53 to facilitate entry of the teeth into engagement with each other.

The planetary mechanism includes a synchronizer 54 and 55 (figure 3)placed on opposite sides of satellites 42 the jet 38 and the locking gear 44 of the coupling. Synchronizers are a ring with an inner conical surface 56 with the outer teeth 57 and 58, arranged in two rows. That is, each referred to the synchronizer has two of the ring gear. The teeth 57 which each synchronizer constant engagement with the teeth 48 of the crown gear wheel 39. The teeth 58 is made larger than the teeth 57. Large teeth 58 on the part of small teeth 57 are made bevel, i.e. large teeth 58 are oblique end face 59. The synchronizer 55 internal conical surface 56 is located opposite the outer conical surface 60, made for locking the gear coupling 44. The synchronizer 54 of the inner conical surface is located opposite the outer conical surface on the annular ledge 46 on reactive teeth, the coupling 38. Between the synchronizer 54, located in reactive coupling 38, and satellites 42 posted by a spring-loaded plunger 61, made in the form of a split ring with flat end faces, interacting with the teeth 48 of the crown wheel 39. In the zone of interaction of the pusher 61 with teeth 48 in these teeth made three transverse grooves of different profile with inclined lateral sides, namely the average groove 62 and the outer grooves 63 and 64. The sides 65 of the secondary grooves 62 steeper nearest lateral sides 66 and 67 of extreme grooves 63 and 64. That is, the sides 66 and 67 of extreme grooves made flatter than the sides 65 of the secondary grooves.

Between the plunger 61 and the synchronizer 55 located at the blocking toothed coupling 44, a drive rod 41 are rods 68, 69. These rods 68, 69 are placed in pairs coaxially with each other. And they have a disk head 70, to the second they come into contact with the plunger 61 and the synchronizer 55.

Satellites 42 are located in a drive rod 41 on the supporting rods 71 (11). At the end of the supporting rod 71 is made of the tabs 72, and a drive rod 41 is made of the protrusions 73, located opposite the bearing 13. The protrusions 72 and 73 made of transverse grooves in which are installed spring split lock ring 74 covering the stepped washer 75, attached to the cage with screws 76. The retaining ring 74 provides a reliable axial and circumferential fixation rods 71, preventing inadvertent them cranking and axial displacement. And stepped washer 75 provides reliable fixation of the stopper ring 74 in proper position.

In the support rods 71 satellites 42 is made oblique hole 77, intersecting with their lateral surface and with a radial bore 78 made in the drive rod 41 between the satellite and the washer 75 opposite the shaft 19 having an axial bore 79 for lubricating fluid. With the shaft 19 a radial hole 80 for supplying lubricating fluid to the bearings of the satellites 42, the axis of which is located in the plane between the satellites and the washer 75. To limit the amount of lubricant supplied to the satellites, approximately conical bearing 21 in the drive rod 41 is installed slinger 81, which has the profile of the area.

When connecting gear clutch gear 32 22 or gear 26 with the input shaft 16 and when you connect the AI any gear coupling with the intermediate shaft 19 located thereon gear torque from the input shaft 16 is transmitted to the side of the shaft 17, and with him through any pair of the engagement between the gears mounted on parallel shafts 17 and 19, the torque is transmitted to the intermediate shaft 19 to the sun gear 43 of the planetary mechanism. When the work of the planetary gear as the gear teeth of his crown gear 39 meshed with the teeth of gear reactive coupling 38. In this case, the satellites 42 under the action of forces arising in their engagement with a sun gear 43, rolling stopped on the crown gear wheel 39, to create a drive rod 41 increased torque coming on the output shaft 18. When this jet turning point, reactive loading gear element 38, is perceived through the threaded fasteners 47 rear outer wall 10 of the casing, in which are bearings 13 and 14 for support shafts 18 and 17.

During operation of the planetary gear lubricating fluid to the bearings of the satellites 42 is supplied in the right quantity from the axial bore 79 in the shaft 19 through a radial hole 80 and then through the radial hole 78 in the drive rod 41 and the oblique holes 77 in the support rods 71 satellites. While fixing the support rod 71 at the position at which lubrication holes 77 and 78 intersect, is reliably provided retaining ring 74, is placed in the free space at the under the of ipnii 13. Prevent the discharge of excessive amounts of lubricating fluid conical bearing 21 to the satellites 42 is carried out by the slinger 81.

If you need to reduce torque on the output shaft 18 of the planetary mechanism 37 to lock. This crown gear wheel 39 is removed from engagement with reactive toothed coupling 38 by moving it from the back wall 10 of the body towards the locking coupling 44 together with the plunger 61. When moving the crown gear wheel 39, the plunger 61 is located at the transverse groove 64 in the teeth 48 of this gear, push the cylinder rod 68, which moves the rod 69, the pressure head 70 on the synchronizer 55. Due to friction between the conical surfaces 56 and 60 of the synchronizer 55 and the locking coupling 44 synchronizer 55 rotates relative to the crown gear wheels 39 and occupies such a position in which the teeth 48 in the event of axial movement of the crown wheel butt against the oblique end face 59 of large teeth 58. When the plunger 61 in the event of axial movement of the crown wheel 39 out of the end of the groove 64 in his teeth 48 and into the Central groove 62. Given the emphasis of the teeth 48 teeth 58 synchronizer 55 increases the strength of the interaction of the tapered surfaces 56 and 60 of the synchronizer 55 and the locking coupling 44. Under the action of the friction of these surfaces is the slow rotation of the shaft 19 and starts the rotation of the crown gear wheel 39. After rotation frequency locking coupling 44 and the crown wheel 39 are the same, the synchronizer 55 rotates relative to the crown wheel 39 within the lateral gaps between their teeth 57 and 48, and the teeth 48 are moving away from large teeth 58 of the blocking coupling 44, preventing axial movement of the crown gear wheel 39. Then the crown gear wheel 39, overcoming the resistance of the plunger 61 by compression in the radial direction, is moved further in the direction of the locking coupling 44, and his teeth 48 engages with its teeth 49, contacting with them their tapering sections 51. Consequently, the planetary mechanism is locked, then all of its parts rotate as a unit. After engagement of the teeth 48 and 49 on the output shaft 18 to the shaft 19 through the jointly rotating parts of the planetary mechanism receives torque equal to the torque on the shaft 19.

If necessary to increase the torque on the output shaft 18 of the planetary mechanism 37 you want to unlock and enable it to work as a reducer. This crown gear wheel 39 is moved in the direction of the rear wall 10 of the body together with located at the groove 63 in his teeth 48 spring plunger 61 which presses the synchronizer 54. The synchronizer 54 is pressed their internal is her conical surface to the outer conical surface, available on the annular ledge 46 on a jet gear element 38. Due to friction between the conical surfaces of the synchronizer 54 and reactive coupling 38 synchronizer 54 is rotated relative to the crown gear 39 in the position in which the teeth 48 at their axial displacement butt against the oblique end face of the large teeth of the synchronizer 54. When the plunger 61 in the event of axial movement of the crown wheel 39 out of extreme grooves 63 in his teeth 48 and into the Central groove 62. Given the emphasis of the teeth 48 in the teeth of the synchronizer 54 increases the strength of the interaction of the tapered surfaces of the synchronizer 54 and reactive coupling 38. Under the action of friction of these surfaces there is an acceleration of the rotation of the shaft 19 and the slow rotation of the crown gear wheel 39. After stopping the crown wheel 39 synchronizer 54 is rotated relative to it within the lateral gaps between their teeth in the position in which the teeth 48 are moving away from large teeth reactive coupling 38, preventing axial movement of the crown gear wheel 39. Then the crown gear wheel 39, overcoming the resistance of the plunger 61 by compression in the radial direction, is moved further in the direction of the reactive coupling 38, and his teeth 48 engages with its teeth. Is the entry of the planetary what about the mechanism at work as a reducer.

Presents planetary gear transmission comprising a solar gear, drove with satellites located on the supporting rods, the crown gear with synchronizer, with the possibility of axial movement for alternate engagement with the blocking and reactive toothed coupling sleeve, has a compact and robust design, since the bearing carrier in the outer wall of the transmission housing is formed by a rolling bearing, the outer ring which is fixed between the cover and reactive toothed coupling half mounted on this bearing, and in front of the bearing on the end face of the support rods of the satellites and the driver made the tabs with transverse grooves which have a split retaining ring covering attached to the cage stepped washer for reliable fixation of the locking ring and, consequently, the supporting rods satellites. Transmission of such planetary gear has a relatively small axial dimension, allowing the shaft with gear transmission and a planetary mechanism are accommodated in a single space between the front and rear outer walls of the casing, forming bearings all shafts.

1. Planetary gear transmission comprising a solar gear, drove with satellites, spaced supports on the s terminals, crown gear with synchronizer, with the possibility of axial movement for alternate engagement with the blocking and reactive toothed coupling sleeve, wherein the carrier has a bearing in the outer wall of the transmission housing, formed by a ball bearing, the outer ring which is fixed between the cover and reactive gear coupling, which is attached on the bearing, while the opposite of the bearing on the end face of the support rods of the satellites and the driver made the tabs with transverse grooves which have a split retaining ring, covering the stepped washer attached to the cage.

2. The planetary mechanism according to claim 1, characterized in that between the planet carrier and the shaft on which there is a sun gear, posted by tapered roller bearings.

3. The planetary mechanism according to claim 2, characterized in that the supporting rods satellites made oblique hole, intersecting with their lateral surface and with a radial slot in the drive rod between the satellite and the washer opposite the mentioned shaft having a longitudinal bore for lubricating fluid.

4. The planetary mechanism according to claim 3, characterized in that a radial shaft hole, the axis of which is located in the plane between the satellites and the washer.

5. Against the initial mechanism according to claim 4, characterized in that the approximately conical bearing in the driver installed slinger.

6. The planetary mechanism according to claim 5, characterized in that the slinger has a profile of the area.



 

Same patents:

Breather // 2262020

FIELD: mechanical engineering; removal of excessive pressure from reservoirs of reduction gears, gear-boxes and other mechanisms.

SUBSTANCE: proposed breather has stepped housing 1 with air escape hole, cap 6 and hemispherical dampening element 5. Rod 2 is fitted in air escape hole. Upper part of rod 2 is provided with circular groove. Lower part of rod 2 which is taper in shape extends beyond housing. Dampening element 5 is received by circular groove of rod 2. Cap 6 mounted immovably on housing 1 is provided with slots 7 in its lower part. Clearance is formed in between bottom of cap 6 and end face of rod 2. As soon as pressure reaches its excessive level, rod moves upward letting the air outside through clearance formed between dampening element 5 and through hole of housing 1, flat and slots 7.

EFFECT: enhanced operational reliability; avoidance of water penetration inside mechanism at immersion of breather in aqua medium.

4 dwg

FIELD: mechanical engineering.

SUBSTANCE: breather comprises flexible vessel (1), which is in communication with crankcase (8) of the reduction gear through pipeline (6), and pressure gauge (10). Flexible vessel (1) is made of corrugation provided with frame (3) and compression springs (4) which arrest the flexible vessel against free lowering and define a space for compensating air rarefaction in the crankcase of the reduction gear at initial moment of operation.

EFFECT: enhanced reliability.

1 dwg

FIELD: mechanical engineering; vertical gear reducers.

SUBSTANCE: proposed vertical gear reducer has housing 1, three stages assembled from cylindrical gear wheels 3, 5, 7 which are rigidly connected with shafts mounted rotatably in bearings 9-12 in housing. Lubricating fluid 13 is located in lower part of housing. Third-stage wheel 7 is partially immersed in lubricating fluid. Fitted on shaft of second-stage wheel 5 is washer 15 which rotates together with pinion stem 6 performing axial and angular motion. End faces 16 and 17 of gear wheels 3 and 7 of first and third stages directed towards second-stage wheel 5 are located in one plane. Washer 15 is pressed to end faces of gear wheels 16 and 17.

EFFECT: enhanced reliability due to reliable delivery of lubricant to teeth of wheels of higher stage.

3 dwg

The invention relates to transport machinery, can be used in transmissions, vehicles, and is intended to improve lubrication

The invention relates to the transport industry, in particular for lubrication systems, axles, and can be used in the automotive industry

The invention relates to the transport industry, in particular to high-speed gearboxes with lubrication oil for indoor traction drive rail vehicles

The invention relates to transport machinery and can be used in transmissions for wheeled vehicle

Roller device // 2226631
The invention relates to rollers and cooling during use, in particular to the rollers used in variable-speed drives with toroidal raceway

The invention relates to the field of engineering

The invention relates to mechanical engineering and can be used in internal combustion engines

Gear box // 2267675

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing (1), shafts (16), (17), (18), and (19) with pinions, and three-sprocket planet mechanism (37) provided with a device for its locking. Crown wheel (39) of the planet mechanism is connected with the reaction gearing member (38) mounted on the inner surface of back outer wall (10) of the housing.

EFFECT: reduced sizes.

5 cl, 4 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet mechanism comprises solar pinion (43), carrier (41) with satellites (42), gear wheel (39) with synchronizers (54) and (55), and ring spring pusher (61) of the synchronizer that cooperates with teeth (48) of wheel (39). Pusher (61) is interposed between satellites (42) and synchronizer (54). Teeth (48) of wheel (39) in the zone of cooperation with pusher (61) are provided with transverse grooves (62-64).

EFFECT: reduced axial size.

6 cl, 10 dwg

Gear box // 2254507

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing (1) made of the front and rear cap-shaped parts whose longitudinal walls are mating in the transverse plane. The housing receives input shaft (16) with pinion (22), side shaft (17) with pinions (23)-(25), intermediate shaft (19), output shaft (18), and three-link planet mechanism (37) with the device for its locking and connecting its link with the reactive gear member (38) connected with housing (1). Shafts (16)-(19) with pinions and planet mechanism (37) are arranged in the single space between front (5) and rear (10) outer walls of housing (1) which define supports for the shafts.

EFFECT: decreased sizes and reduced metal consumption.

4 cl, 4 dwg

Gear box // 2253781

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises shafts (3)-(5) with gear wheels (6)-(9), housing (18) provided with load-bearing wall (19) with supports (20) and (21), shafts (4) and (5), three-link differential mechanism (15) whose one link is connected with the secondary shaft (5), mechanism for shifting gears, and device for control of the differential mechanism. Wall (19) is made of detachable lid which encloses the differential mechanism (15) and mates the longitudinal wall of housing (18).

EFFECT: enhanced reliability.

9 cl, 11 dwg

The invention relates to the oil industry, namely technological equipment pumper setup

Gear motor // 2008545
The invention relates to mechanical engineering and can be used in various industries, for example in the service devices of the vehicle or aircraft that require compact geared motors

FIELD: transport engineering.

SUBSTANCE: proposed multiple=speed gearbox contains housing 1, drive shaft 2, mainshaft 3 and countershaft 4. Drive shaft 2 and mainshaft 3 are installed coaxially. Countershaft 4 is arranged in parallel with said shafts. Gears 8-12 of countershaft 4 are meshed in pairs with gears 14-18 freely fitted on mainshaft 3. Three low-speed gears and reverse gear are secured on countershaft 4. Reverse gear 20 is fitted on axle 5 between countershaft 4 and mainshaft 3. Two three-position shifter sleeves D(23) and E(24) are arranged on hubs of mainshaft 3 between two pairs of low-speed gears 16 and 17, and reverse gears 21 and 18, respectively. Three-position shifter sleeve A(22) is arranged on hub of drive shaft. Two two-position twin shifter sleeves B and C are arranged between second, third and fourth rows of gears. They consist, each, of two two-position sleeve members 25 and 26, 28 and 29 respectively, intercoupled by shifter forks 27 and 30. One of sleeve members is installed on gear rim of mainshaft 3 and the other is installed opposite to first one on gear of countershaft 4.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of forward speeds up to 24 and reverse speeds up to 8.

1 tbl, 2 dwg

FIELD: transport engineering.

SUBSTANCE: proposed multiple-speed gearbox contains housing 1, drive shaft 2, main shaft 3 and countershaft 4. Drive shaft 2 and main shaft 3 are installed coaxially. Countershaft 4 is arranged in parallel with shafts stated above. Gear 6 of drive shaft 2 is in meshing with gear 7 of countershaft 4. Gears 8-12 of countershaft 4 engage in pairs with gears 13-17 freely fitted on main shaft 3. Low-speed gears 11, 12 and reverse speed gear 18 are secured on countershaft 4. Three-position shifter speed E is fitted on hub of main shaft 3 between rows of low speed gears. Four two-position twin shifter sleeves A - D are arranged between first five rows of gears. Said twin shifter sleeves consist, each, of two two-position sleeve members arranged on gears of adjacent parallel shafts interacted by shifter forks 23, 26, 29, 32, respectively. One of shifter sleeve members is fitted on rim of gear freely fitted relative to countershaft 4, and other shifter sleeve member is installed opposite to first one on rim of gear of main shaft or drive shaft.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of forward speeds up to 32 and reverse speeds up to 16.

3 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to conventional gearboxes of transport and traction vehicles. Each speed in multiple-shaped gearbox contains drive and driven shafts with fitted-on gears and intermediate gears freely fitted on curvilinear axle for rotation and equipped with stop. Curvilinear axle is secured in gearbox for turning around axis of drive or driven shaft. Intermediate gears are installed on axle with angular shift, being in constant meshing either with gears of drive shaft or gears of driven shaft. At gear-shifting, common axle of intermediate gears of shifted-in and shifted-out speeds is unlocked and rotated around axis of gearbox shaft with gear of which intermediate gears are in constant meshing. Intermediate gear of shifted-out speed is brought out of meshing with gear of other shaft, and gear of shifted-in speed is brought synchronously into meshing with gear of other shaft for complete engagement of corresponding speed, after which axle of intermediate gears is locked. To select direction of change-over, engine of vehicle is changed over for traction or braking conditions.

EFFECT: provision of gear-shifting practically without breaking of power flow and without synchronization of gear speeds.

3 cl, 4 dwg

Up!