Axle electromagnetic disconnection system

FIELD: machine building.

SUBSTANCE: invention relates to vehicle axle disconnection system. Electromagnetic axle disconnection system disconnection plug comprises driven shaft housing, provided with driven shaft bearing and armature with winding rigidly attached to it. Pressure plate and sliding cam clutch are connected with driven shaft with possibility of sliding. During rotation driven shaft is in contact with driven shaft bearing. Said system also comprises drive shaft housing, rigidly attached to driven shaft housing. Drive shaft bearing is rigidly fixed in drive shaft housing.

EFFECT: electromagnetic disconnection system also comprises disconnecting spring and axially fixed cam clutch, rigidly attached to driving shaft end passing axially through opening in drive shaft housing.

12 cl, 8 dwg, 2 tbl

 



 

Same patents:

Braking assembly // 2416046

FIELD: transport.

SUBSTANCE: proposed braking assembly comprises electromagnet, brake spring and braking plates. One of the latter is rigidly fitted on the shaft while another one moves only axially. Braking and stop locking are performed by braking plates with their contact surfaces representing radially arranged teeth. Profile of teeth on one plate matches that of grooves on opposite plate.

EFFECT: reduced weight and sizes, higher reliability and longer life.

3 dwg

The invention relates to electric machines and can be used at elevated sprinkler machines

FIELD: transport.

SUBSTANCE: invention relates automotive industry and can be used in cars and trucks, starters of whatever carriers and other devices. This clutch consists of support (4a), butt parts (2a) at flywheel (3) and support (4a), dampers (14) arranged at axle of support (4f), doubling support, dampers (14) and butt parts (2a) antisymmetric relative to the plane extending through rotational axis centre perpendicular to support axis. Rotation is transmitted mechanically, by the force of normal pressure, from flywheel (3) to support (4a) applied tangentially to circumference of flywheel (3).

EFFECT: ruled out slippage, lower metal input, ease of maintenance.

4 cl, 4 dwg

Safety clutch // 2331803

FIELD: engines and pumps.

SUBSTANCE: invention can be used in the drives of heavy-load machines, assembly units and devices, e.g. mills, as a one-way transmission. The safety clutch has outer cage (2) made as a hollow cylinder with inner (1) cage making driving (12) and driven (13) sleeves coupled with driving (8) and driven (9) disks by means of splines. Flexible element (14) is arranged between the inner end face sections of driving (12) and driven (13) sleeves. Two pairs of ball-shaped wedging bodies (3) are arranged between outer end face surfaces (16) in recesses of sleeves (12 and 13) and mating cylindrical holes of driving (8) and driven (9) disks. Driving (20) and driven (21) half-couplings are arranged in the spaces of driving (12) and driven (13) sleeves and inner and outer teeth matching them. Every sleeve (12, 13) is furnished with a multi-start thread (26) with a great lead angle. Driving sleeve (12) has its threaded section (27) made on the outer cylindrical part above inner teeth (24). Driven sleeve (13) has its threaded section (28) made in the cylindrical space shifted from its inner teeth (25) towards drive sleeve (12). End face section (29) of the outer cylindrical part of driving sleeve (12) and end face section (30) of the cylindrical space of driven sleeve (13) have a cone-like joint face. The length of the said threaded sections (27 and 28) of driving (12) sleeve and driven (13) sleeve exceeds the width of outer teeth (22) of drive half-coupling (20).

EFFECT: transmission of higher torques, higher reliability and longer life.

6 dwg

Coupling // 2328634

FIELD: engines and pumps.

SUBSTANCE: invention can be used in highly loaded whatever machinery, for example, in rolling mills, as a one-way transmission. The coupling incorporates inner (1) casing, outer (2) casings, elastic rods and a wedging body arranged between the parts of inner (1) casing. Outer (2) casing is made in the form of a hollow cylinder with lock (5) and thrust (6) rings in its space at end sections. Inner (1) casing is made in the form of two barrels, i.e. extreme (7) and inner (8) and located in the space of outer (2) casing to rotate around the axis of symmetry of the coupling and axially move between thrust (6) rings. Extreme (7) and inner (8) barrels match with their end face sections (9 and 10). Equal-depth triangular recesses are made on the side of matching end face sections of extreme (7) and inner (8) barrels. The said recess longer side mates with matching end face section of the barrel, the other two sides are mutually matched along the circumference. In the formed holes in extreme (7) and inner (8) barrels a wedging body pair (4) is tangentially arranged at the angle to the matching plane of end face sections (9 and 10). Every body in the form of arc-like elastic steel band (4) with rounded off ends is orthogonally matched with short sides of recesses on the cylindrical outer surface of extreme (7) and inner (8) barrels. Driving (21) and driven (22) half-couplings are arranged in the space of extreme (7) and inner (8) barrels and match with them by outer teeth (23, 24) of driving (21) and driven (22) half-couplings and internal teeth (25, 26) of extreme (7) and inner (8) barrels. Extreme (7) barrel of inner (1) casing are located in the space of outer (2) casing and matches with thrust ring (6) and the teeth of driving (21) half-coupling. Inner (8) barrel of inner (1) casing is matched with ends (27, 28) of preloaded elastic rods (3) and with teeth of driven (22) half-coupling. Here elastic rods (3) match by local recesses (29, 30) with end face section of internal (8) barrel and thrust ring (6) arranged nearby second lock ring (5). The length of the aforesaid wedging body (4) exceeds the width of teeth (24) of driven (22) half-coupling.

EFFECT: transmission of high torques, higher reliability, longer life.

4 cl, 4 dwg

Coupling // 2328633

FIELD: engines and pumps.

SUBSTANCE: invention may be used in the drives of highly loaded whatever machinery, for example, in rolling mills as one-way transmission. The coupling incorporates inner (1) and outer (2) casings, a wedging body in the form of elastic rods (3) arranged at an angle to the casings. Outer (2) casing is made in the form of a hollow cylinder with lock rings (4 and 5) and thrust (6 and 7) rings in the cylinder space end parts. The space of outer (2) casing accommodates inner (1) casing rotating about the axis of symmetry of the clutch and moving axially between thrust (6 and 7) rings. Inner (1) casing is made in the form of two sleeves, i.e. extreme (8) and inner (9) matching by end face sections (12 and 13). Between end face sections (12 and 13) of extreme (8) and inner (9) barrels in cylindrical recesses (14) a pair of pushers (17) is tangentially mounted by means of rotary axles (15) with radial slots. End faces of every pusher (17) are made semi-spherical with the spheres radius equal to that of the sphere in the recess of radial slot of rotary axle (15). Here note, that the end faces of every pusher (17) match with the recesses in the slots of rotary axles (15) on end face sections (12 and 13) of extreme (8) and inner (9) barrels. driving (20) half-coupling is arranged in the space of extreme (8) barrel and matches with it by tooth engagement (22, 24). Driven (21) half-coupling is arranged in the space of inner (9) barrel and matches with it by tooth engagement (23, 25). Elastic rods (3) are fixed in inclined slots (26) of inner (9) barrel, the said rods ends match with thrust (7) ring located nearby second lock ring (5). Elastic rods (3) can get twisted in cylindrical space of outer (2) casing and get bent. The length of every aforesaid pusher (17) exceeds the width of teeth (23) of driven (21) half-coupling. Return travel of extreme (8) barrel is limited by the pin arranged in an auxiliary cylindrical recess on end face (13) section of inner (9) barrel.

EFFECT: transmission of high torques, higher reliability of the coupling, its longer life.

8 dwg

Clutch // 2299367

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner member (1), outer member (2), and wedging bodies made of rods (3) interposed between the members. Outer member (2) is made of a hollow cylinder and provided with locking rings (4) and (5) at its end, shaped groove (6) in its intermediate section, and key grooves made along generatrix of the inner side of outer member (2). Inner member (1) is mounted in the space of the outer member and is made of disk (8), end sleeve (9), and inner sleeve (10) that cooperate one with the other by means of faces (12) and (13). Disk (8) cooperates with hub (11) of inner sleeve (10) and inner space of outer race (2). End sleeve (9) is mounted for permitting rotation around the axis of symmetry of the clutch. Inner sleeve (10) is mounted for permitting axial movement from end sleeve (9) toward locking ring (5). End sleeve (9) cooperates with the inner surface of outer member (2) by means of centering collars and with bearing ring (15) by means of outer face. Bearing ring (15) is made in block with locking ring (4). End sleeve (9) and inner sleeve (10) are provided with oval recesses (16) and (21) that receive the ends of rods (3) by means of axles (18), ball pivots (19), and space bushings (20). Inner rings (22) and outer rims (23) limit the radial movements of axles (18), ball pivots (19), and space bushings (20). Inner sleeve (10) has cylindrical recesses, and disk (8) has hollows. The cylindrical recesses and the hollows are axially aligned and receive flexible members made of cylindrical compression springs. Disk (8) and space of the cylindrical compression spring receive telescopic rod mounted for permitting axial movement. One end of the rod cooperates with the hollow end sleeve (9), and the other end cooperates with bearing ring (36). Bearing ring (36) is made in block with the second locking ring (5) at the other end of the outer member. The ring groove in disk (8) receives segments (39) made of split parts of flat ring and mounted for permitting radial movement. The outer edge of segment (39) cooperates with longitudinal groove in the space of outer member (2). The inner edge of segment (39) abuts against the telescopic rod. Segments (45) and flexible members are interposed between outer rim (23) and inner sleeve (10) and set in its groves in pair for permitting radial movement. The peripheral sections of inner sleeve (10), segments (45), and disk (8) are provided with key grooves for receiving prismatic keys. The key is set in the key groove in the space of outer member (2). One of the ends of the key cooperates with bearing ring (36), and the other end cooperates with the inner face section of end sleeve (9). End sleeve (9) engages driving clutch member (51), and inner sleeve (10) engages driven clutch member (52).

EFFECT: enhanced reliability.

8 cl, 11 dwg

Clutch // 2299366

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner member (1), outer member (2), and wedging bodies made of rods (3) and interposed between the members. Outer member (2) is made of a hollow cylinder provided with locking rings (4) and (5) set in the ring grooves provided at the end sections of its space and ring collar (7) provided in the intermediate section of the space. Inner member (1) is made of end sleeve (8), inner sleeve (9), and floating disk (10) that is mounted for permitting movement along pin (11) of internal sleeve (9). End sleeve (8) and inner sleeve (9) are mounted in the space of outer member (2) by means of centering collars. Inner sleeve (9) is mounted for permitting axial movement between locking rings (4) and (5) of outer member (2) by means of prismatic keys. The faces of the sleeves interact one with the other by means of three rods (3) interposed between the faces and mounted in ring groove (14) provided in end sleeve (8) and oval recesses (15) provided in inner sleeve (9). Each of rods (3) is mounted in ring groove (14) of end sleeve (8) and oval recesses (15) of inner sleeve (9) by means of ball pivots (16), axles (17), and shaped threaded bushings (18). The outer face of end sleeve (8) is provided with ring (20) to define a slide bearing. Ring (20) cooperates with locking ring (4) of outer member (2) through stop ring (21). Inner sleeve (9) receives three spring-loaded rods mounted in through cylindrical openings. One end of the rod cooperates with the bottom of ring groove (14) in end sleeve (8) or the stop in ring groove (14). The other end of the rod is set in the opening of floating disk (10). The rod has a cylindrical hollow, and the end of the rod set in the opening in floating disk (10) has thinning and adapting chamfering. Each flexible member made of cylindrical compression spring cooperates with the bottom of the cylindrical recess in the rod and cylindrical hollow in the face of floating disk (10) by its end turns. The ring groove in floating disk (10) receive segments (32) to lock inner sleeve (9) in operation position. The end of the rod cooperates with the inner cylindrical surface of segment (32) or the chamfering of the thinning. The ring collar of inner sleeve (9) is provided with trapezoidal groves that receive the segments and flexible members. The groove of each segment embraces the prismatic key. The keys are set in key grooves provided in outer member (2) between centering collar (12) of end sleeve (8). The centering collar of inner sleeve (9) and floating disk (10) is provided with grooves oriented along the generatrix of the cylindrical surfaces. The grooves interact with the prismatic keys. End sleeve (8) engages driving clutch member (39), and inner sleeve engages driven clutch member (40). Inner sleeve (9) has a seat ring (52) that cooperates with pin (53) of driven clutch member (40).

EFFECT: enhanced reliability.

7 cl, 13 dwg

Clutch // 2299365

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner race (1) and outer race (2). Inner race (1) is made of two sleeves: end sleeve (6) and inner sleeve (7). The ends of rods (3) are interposed between the sleeves. The rods represent pushers and are mounted in U-shaped recesses (10) and (11) made in face sections of the sleeve by means of pivots (12) and (13) and axles (14) and (15). The face sections of the sleeves are mating. Outer race (2) is made of a hollow cylinder and provided with stop rings (4) and (5) mounted at the end sections. Inner sleeve (7) is mating to the inner space of outer race (2) by means of ring collar (16) and is provided with cylindrical hollows (17) that receive first pair of spring-loaded rods with flexible members. Each flexible member is made of a cylindrical compression spring and its end turns cooperate with the bottom of the cylindrical hollow and the head of the rod. One end of each rod cooperates with the face section of end sleeve (6). The other end of the rod cooperates with the stop ring (19). Stop ring (19) is set in the space of outer race (2). The outer face of end sleeve (6) whose ring collar (22) cooperates with the inner space of the outer race is provided with ring groove that receive slide bearings (23) and (24). Slide bearing (23) and (24) interacts with second stop ring (25) mounted in the space of outer race (2). Ring collar (16) of inner sleeve (7) is provided with groove (31) that receives segments of locator (32) and flexible member (33). The space of outer race (2) is provided with ring groove (34). The spaces of end sleeve (2) and inner sleeve (7) receive driving (35) and driven (36) clutch members, respectively. The clutch members cooperate with sleeves (6) and (7) by means of teeth (37), (38), (39), and (40). Inner sleeve (7) is mounted for permitting axial movement. Seat collar (41) of inner sleeve (7) is shifted with respect to its inner teeth (4) by a value equal to the length of pusher (3). Seat collar (41) also cooperates with ring projection (42) provided at the face of driven clutch member (36).

EFFECT: enhanced reliability.

7 cl, 8 dwg

Clutch // 2299364

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner clutch member (1), outer clutch member (2), and flexible rods (3) inclined to the clutch members. Ends (4) of rods (3) are secured inside race (2), and ends (5) are in a contact with inner race (1) through stop ring (26). Outer race (2) is made of a hollow cylinder with stop rings (6) and (7) at their end sections. Inner race (1) is mounted in the space of outer race (2) for permitting rotation with respect to the axis of symmetry of the clutch and axial movement between stop rings (6) and (7). Inner race (1) is made of two coaxial sleeves: end sleeve (11) and inner sleeve (12). The pair of pushers (16) is interposed between the faces of end sleeve (11) and inner sleeve (12) and is tangentially set in drop-shaped hollows (15). The faces of pushers (16) cooperates with the surfaces of drop-shaped hollows (15) made in the faces of end sleeve (11) and inner sleeve(12). The faces of pushers (16) are shaped into spheres. Driving clutch member (20) cooperates with end sleeve (1) by means of teeth (22) and (24). Driven clutch (21) cooperates with inner sleeve (12) by means of teeth (23) and (25). The length of each pusher (16) is larger than the width of teeth (23) of driven clutch member(21). End sleeve (11) of inner race (1) cooperates with locking ring (6). Inner sleeve (12) of inner race (1) cooperates with the free ends (5) of flexible rods (3) by means of stop ring (26). Each rod (3) is made of a plate made of sheet carbon steel. Second end (4) of the plate is set in the grooves provided in guiding ring (28) that is mounted in the space of outer race (2). The grooves are made at an angle to the generatrix of the cylindrical surface of the space of outer race (2).

EFFECT: enhanced reliability and expanded functional capabilities.

1 cl, 6 dwg

Clutch (versions) // 2255256

FIELD: mechanical engineering; drives of machines and mechanisms.

SUBSTANCE: proposed clutch includes two concentric clutch members. Novelty is that one clutch member has screw shaft with stop, and other clutch member has splined bushing. Clutch members are intercoupled by concentric slider in form of bushing whose inner surface is helical and outer surface is slotted. End face surfaces of slider are made in form of stops, and free travel of slider is found from expression where d is mean diameter of thread of screw shaft, m; ψ is angle of helix of thread line, deg; ψ>ϕ, where ϕ is reduced angle of friction in screw joint, deg; ω=f(t) is variable speed of drive shaft rotation at time of acceleration, rad/s; ti is acceleration time to get preset angular velocity of drive shaft, s. Flexible member can be installed between end face surfaces of corresponding clutch member and slider. According to second version, clutch contains bushing whose inner surface is splined, and outer surface is helical.

EFFECT: provision of reliable connection of driving and driven shafts, enlarged operating capabilities of clutch.

8 cl, 3 dwg

Clutch (versions) // 2255255

FIELD: mechanical engineering; drives of machines and mechanisms.

SUBSTANCE: proposed clutch contains two concentric clutch members. Novelty is that clutch members are united by slider connected with one of clutch members by splined joint and with other clutch member, by screw joint. Clutch members are provided with end face surfaces limiting displacement of slider. Bearing and helical spring are installed between end face surfaces of clutch member and slider connected by screw joint. Spring rate is determined by relationship where M is maximum torque transmitted by clutch, nm; x is maximum deformation of spring (slider stroke), m; dsp, db are respectively, mean diameters of splined and screw joints, m; dn is mean diameter of bearing, m; f1 is coefficient of friction in splined joint; f2 coefficient of friction in bearing; ψ is helix angle, deg; ϕ is reduced friction angle in screw joint, deg; k is spring rate, n/m. According to second design version, spring is installed between end face surfaces of clutch member and slider connected by splined joint. Spring rate is found with due account of parameters and characteristics of axial support bearing clutch member.

EFFECT: improved reliability of connection of driving and driven shafts, enlarged operating capabilities of clutch.

3 cl, 5 dwg

Clutch (versions) // 2255254

FIELD: mechanical engineering; drives of machines and mechanisms.

SUBSTANCE: proposed clutch includes two concentric clutch members. Novelty is than clutch is provided with slider coupling clutch members. Said slider is made in form of rigidly interconnected concentric screw and splined bushings. Clutch members contain, respectively, screw and splined shafts with stops. Free travel of slider is found from expression where d is mean diameter of thread of screw shaft, m; ψ is angle of helix of thread line, deg; ψ>ϕ where ϕ is reduced angle of friction in screw joint, deg; ω=f(t) is variable speed of drive shaft rotation at time of acceleration, rad/ s; ti is acceleration time to obtain preset angular velocity of drive shaft, s; L is free travel of slider, m. Flexible member can be installed between end face surfaces of corresponding clutch member and slider. According to other design version, clutches contain screw and splined shafts and corresponding bushings in different combinations.

EFFECT: improved reliability of connection of driving and driven shafts, enlarged operating capabilities of clutch.

16 cl, 6 dwg

Clutch (versions) // 2255255

FIELD: mechanical engineering; drives of machines and mechanisms.

SUBSTANCE: proposed clutch contains two concentric clutch members. Novelty is that clutch members are united by slider connected with one of clutch members by splined joint and with other clutch member, by screw joint. Clutch members are provided with end face surfaces limiting displacement of slider. Bearing and helical spring are installed between end face surfaces of clutch member and slider connected by screw joint. Spring rate is determined by relationship where M is maximum torque transmitted by clutch, nm; x is maximum deformation of spring (slider stroke), m; dsp, db are respectively, mean diameters of splined and screw joints, m; dn is mean diameter of bearing, m; f1 is coefficient of friction in splined joint; f2 coefficient of friction in bearing; ψ is helix angle, deg; ϕ is reduced friction angle in screw joint, deg; k is spring rate, n/m. According to second design version, spring is installed between end face surfaces of clutch member and slider connected by splined joint. Spring rate is found with due account of parameters and characteristics of axial support bearing clutch member.

EFFECT: improved reliability of connection of driving and driven shafts, enlarged operating capabilities of clutch.

3 cl, 5 dwg

Clutch (versions) // 2255256

FIELD: mechanical engineering; drives of machines and mechanisms.

SUBSTANCE: proposed clutch includes two concentric clutch members. Novelty is that one clutch member has screw shaft with stop, and other clutch member has splined bushing. Clutch members are intercoupled by concentric slider in form of bushing whose inner surface is helical and outer surface is slotted. End face surfaces of slider are made in form of stops, and free travel of slider is found from expression where d is mean diameter of thread of screw shaft, m; ψ is angle of helix of thread line, deg; ψ>ϕ, where ϕ is reduced angle of friction in screw joint, deg; ω=f(t) is variable speed of drive shaft rotation at time of acceleration, rad/s; ti is acceleration time to get preset angular velocity of drive shaft, s. Flexible member can be installed between end face surfaces of corresponding clutch member and slider. According to second version, clutch contains bushing whose inner surface is splined, and outer surface is helical.

EFFECT: provision of reliable connection of driving and driven shafts, enlarged operating capabilities of clutch.

8 cl, 3 dwg

Clutch // 2299364

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner clutch member (1), outer clutch member (2), and flexible rods (3) inclined to the clutch members. Ends (4) of rods (3) are secured inside race (2), and ends (5) are in a contact with inner race (1) through stop ring (26). Outer race (2) is made of a hollow cylinder with stop rings (6) and (7) at their end sections. Inner race (1) is mounted in the space of outer race (2) for permitting rotation with respect to the axis of symmetry of the clutch and axial movement between stop rings (6) and (7). Inner race (1) is made of two coaxial sleeves: end sleeve (11) and inner sleeve (12). The pair of pushers (16) is interposed between the faces of end sleeve (11) and inner sleeve (12) and is tangentially set in drop-shaped hollows (15). The faces of pushers (16) cooperates with the surfaces of drop-shaped hollows (15) made in the faces of end sleeve (11) and inner sleeve(12). The faces of pushers (16) are shaped into spheres. Driving clutch member (20) cooperates with end sleeve (1) by means of teeth (22) and (24). Driven clutch (21) cooperates with inner sleeve (12) by means of teeth (23) and (25). The length of each pusher (16) is larger than the width of teeth (23) of driven clutch member(21). End sleeve (11) of inner race (1) cooperates with locking ring (6). Inner sleeve (12) of inner race (1) cooperates with the free ends (5) of flexible rods (3) by means of stop ring (26). Each rod (3) is made of a plate made of sheet carbon steel. Second end (4) of the plate is set in the grooves provided in guiding ring (28) that is mounted in the space of outer race (2). The grooves are made at an angle to the generatrix of the cylindrical surface of the space of outer race (2).

EFFECT: enhanced reliability and expanded functional capabilities.

1 cl, 6 dwg

Clutch // 2299365

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner race (1) and outer race (2). Inner race (1) is made of two sleeves: end sleeve (6) and inner sleeve (7). The ends of rods (3) are interposed between the sleeves. The rods represent pushers and are mounted in U-shaped recesses (10) and (11) made in face sections of the sleeve by means of pivots (12) and (13) and axles (14) and (15). The face sections of the sleeves are mating. Outer race (2) is made of a hollow cylinder and provided with stop rings (4) and (5) mounted at the end sections. Inner sleeve (7) is mating to the inner space of outer race (2) by means of ring collar (16) and is provided with cylindrical hollows (17) that receive first pair of spring-loaded rods with flexible members. Each flexible member is made of a cylindrical compression spring and its end turns cooperate with the bottom of the cylindrical hollow and the head of the rod. One end of each rod cooperates with the face section of end sleeve (6). The other end of the rod cooperates with the stop ring (19). Stop ring (19) is set in the space of outer race (2). The outer face of end sleeve (6) whose ring collar (22) cooperates with the inner space of the outer race is provided with ring groove that receive slide bearings (23) and (24). Slide bearing (23) and (24) interacts with second stop ring (25) mounted in the space of outer race (2). Ring collar (16) of inner sleeve (7) is provided with groove (31) that receives segments of locator (32) and flexible member (33). The space of outer race (2) is provided with ring groove (34). The spaces of end sleeve (2) and inner sleeve (7) receive driving (35) and driven (36) clutch members, respectively. The clutch members cooperate with sleeves (6) and (7) by means of teeth (37), (38), (39), and (40). Inner sleeve (7) is mounted for permitting axial movement. Seat collar (41) of inner sleeve (7) is shifted with respect to its inner teeth (4) by a value equal to the length of pusher (3). Seat collar (41) also cooperates with ring projection (42) provided at the face of driven clutch member (36).

EFFECT: enhanced reliability.

7 cl, 8 dwg

Clutch // 2299366

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner member (1), outer member (2), and wedging bodies made of rods (3) and interposed between the members. Outer member (2) is made of a hollow cylinder provided with locking rings (4) and (5) set in the ring grooves provided at the end sections of its space and ring collar (7) provided in the intermediate section of the space. Inner member (1) is made of end sleeve (8), inner sleeve (9), and floating disk (10) that is mounted for permitting movement along pin (11) of internal sleeve (9). End sleeve (8) and inner sleeve (9) are mounted in the space of outer member (2) by means of centering collars. Inner sleeve (9) is mounted for permitting axial movement between locking rings (4) and (5) of outer member (2) by means of prismatic keys. The faces of the sleeves interact one with the other by means of three rods (3) interposed between the faces and mounted in ring groove (14) provided in end sleeve (8) and oval recesses (15) provided in inner sleeve (9). Each of rods (3) is mounted in ring groove (14) of end sleeve (8) and oval recesses (15) of inner sleeve (9) by means of ball pivots (16), axles (17), and shaped threaded bushings (18). The outer face of end sleeve (8) is provided with ring (20) to define a slide bearing. Ring (20) cooperates with locking ring (4) of outer member (2) through stop ring (21). Inner sleeve (9) receives three spring-loaded rods mounted in through cylindrical openings. One end of the rod cooperates with the bottom of ring groove (14) in end sleeve (8) or the stop in ring groove (14). The other end of the rod is set in the opening of floating disk (10). The rod has a cylindrical hollow, and the end of the rod set in the opening in floating disk (10) has thinning and adapting chamfering. Each flexible member made of cylindrical compression spring cooperates with the bottom of the cylindrical recess in the rod and cylindrical hollow in the face of floating disk (10) by its end turns. The ring groove in floating disk (10) receive segments (32) to lock inner sleeve (9) in operation position. The end of the rod cooperates with the inner cylindrical surface of segment (32) or the chamfering of the thinning. The ring collar of inner sleeve (9) is provided with trapezoidal groves that receive the segments and flexible members. The groove of each segment embraces the prismatic key. The keys are set in key grooves provided in outer member (2) between centering collar (12) of end sleeve (8). The centering collar of inner sleeve (9) and floating disk (10) is provided with grooves oriented along the generatrix of the cylindrical surfaces. The grooves interact with the prismatic keys. End sleeve (8) engages driving clutch member (39), and inner sleeve engages driven clutch member (40). Inner sleeve (9) has a seat ring (52) that cooperates with pin (53) of driven clutch member (40).

EFFECT: enhanced reliability.

7 cl, 13 dwg

Clutch // 2299367

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises inner member (1), outer member (2), and wedging bodies made of rods (3) interposed between the members. Outer member (2) is made of a hollow cylinder and provided with locking rings (4) and (5) at its end, shaped groove (6) in its intermediate section, and key grooves made along generatrix of the inner side of outer member (2). Inner member (1) is mounted in the space of the outer member and is made of disk (8), end sleeve (9), and inner sleeve (10) that cooperate one with the other by means of faces (12) and (13). Disk (8) cooperates with hub (11) of inner sleeve (10) and inner space of outer race (2). End sleeve (9) is mounted for permitting rotation around the axis of symmetry of the clutch. Inner sleeve (10) is mounted for permitting axial movement from end sleeve (9) toward locking ring (5). End sleeve (9) cooperates with the inner surface of outer member (2) by means of centering collars and with bearing ring (15) by means of outer face. Bearing ring (15) is made in block with locking ring (4). End sleeve (9) and inner sleeve (10) are provided with oval recesses (16) and (21) that receive the ends of rods (3) by means of axles (18), ball pivots (19), and space bushings (20). Inner rings (22) and outer rims (23) limit the radial movements of axles (18), ball pivots (19), and space bushings (20). Inner sleeve (10) has cylindrical recesses, and disk (8) has hollows. The cylindrical recesses and the hollows are axially aligned and receive flexible members made of cylindrical compression springs. Disk (8) and space of the cylindrical compression spring receive telescopic rod mounted for permitting axial movement. One end of the rod cooperates with the hollow end sleeve (9), and the other end cooperates with bearing ring (36). Bearing ring (36) is made in block with the second locking ring (5) at the other end of the outer member. The ring groove in disk (8) receives segments (39) made of split parts of flat ring and mounted for permitting radial movement. The outer edge of segment (39) cooperates with longitudinal groove in the space of outer member (2). The inner edge of segment (39) abuts against the telescopic rod. Segments (45) and flexible members are interposed between outer rim (23) and inner sleeve (10) and set in its groves in pair for permitting radial movement. The peripheral sections of inner sleeve (10), segments (45), and disk (8) are provided with key grooves for receiving prismatic keys. The key is set in the key groove in the space of outer member (2). One of the ends of the key cooperates with bearing ring (36), and the other end cooperates with the inner face section of end sleeve (9). End sleeve (9) engages driving clutch member (51), and inner sleeve (10) engages driven clutch member (52).

EFFECT: enhanced reliability.

8 cl, 11 dwg

Coupling // 2328633

FIELD: engines and pumps.

SUBSTANCE: invention may be used in the drives of highly loaded whatever machinery, for example, in rolling mills as one-way transmission. The coupling incorporates inner (1) and outer (2) casings, a wedging body in the form of elastic rods (3) arranged at an angle to the casings. Outer (2) casing is made in the form of a hollow cylinder with lock rings (4 and 5) and thrust (6 and 7) rings in the cylinder space end parts. The space of outer (2) casing accommodates inner (1) casing rotating about the axis of symmetry of the clutch and moving axially between thrust (6 and 7) rings. Inner (1) casing is made in the form of two sleeves, i.e. extreme (8) and inner (9) matching by end face sections (12 and 13). Between end face sections (12 and 13) of extreme (8) and inner (9) barrels in cylindrical recesses (14) a pair of pushers (17) is tangentially mounted by means of rotary axles (15) with radial slots. End faces of every pusher (17) are made semi-spherical with the spheres radius equal to that of the sphere in the recess of radial slot of rotary axle (15). Here note, that the end faces of every pusher (17) match with the recesses in the slots of rotary axles (15) on end face sections (12 and 13) of extreme (8) and inner (9) barrels. driving (20) half-coupling is arranged in the space of extreme (8) barrel and matches with it by tooth engagement (22, 24). Driven (21) half-coupling is arranged in the space of inner (9) barrel and matches with it by tooth engagement (23, 25). Elastic rods (3) are fixed in inclined slots (26) of inner (9) barrel, the said rods ends match with thrust (7) ring located nearby second lock ring (5). Elastic rods (3) can get twisted in cylindrical space of outer (2) casing and get bent. The length of every aforesaid pusher (17) exceeds the width of teeth (23) of driven (21) half-coupling. Return travel of extreme (8) barrel is limited by the pin arranged in an auxiliary cylindrical recess on end face (13) section of inner (9) barrel.

EFFECT: transmission of high torques, higher reliability of the coupling, its longer life.

8 dwg

Coupling // 2328634

FIELD: engines and pumps.

SUBSTANCE: invention can be used in highly loaded whatever machinery, for example, in rolling mills, as a one-way transmission. The coupling incorporates inner (1) casing, outer (2) casings, elastic rods and a wedging body arranged between the parts of inner (1) casing. Outer (2) casing is made in the form of a hollow cylinder with lock (5) and thrust (6) rings in its space at end sections. Inner (1) casing is made in the form of two barrels, i.e. extreme (7) and inner (8) and located in the space of outer (2) casing to rotate around the axis of symmetry of the coupling and axially move between thrust (6) rings. Extreme (7) and inner (8) barrels match with their end face sections (9 and 10). Equal-depth triangular recesses are made on the side of matching end face sections of extreme (7) and inner (8) barrels. The said recess longer side mates with matching end face section of the barrel, the other two sides are mutually matched along the circumference. In the formed holes in extreme (7) and inner (8) barrels a wedging body pair (4) is tangentially arranged at the angle to the matching plane of end face sections (9 and 10). Every body in the form of arc-like elastic steel band (4) with rounded off ends is orthogonally matched with short sides of recesses on the cylindrical outer surface of extreme (7) and inner (8) barrels. Driving (21) and driven (22) half-couplings are arranged in the space of extreme (7) and inner (8) barrels and match with them by outer teeth (23, 24) of driving (21) and driven (22) half-couplings and internal teeth (25, 26) of extreme (7) and inner (8) barrels. Extreme (7) barrel of inner (1) casing are located in the space of outer (2) casing and matches with thrust ring (6) and the teeth of driving (21) half-coupling. Inner (8) barrel of inner (1) casing is matched with ends (27, 28) of preloaded elastic rods (3) and with teeth of driven (22) half-coupling. Here elastic rods (3) match by local recesses (29, 30) with end face section of internal (8) barrel and thrust ring (6) arranged nearby second lock ring (5). The length of the aforesaid wedging body (4) exceeds the width of teeth (24) of driven (22) half-coupling.

EFFECT: transmission of high torques, higher reliability, longer life.

4 cl, 4 dwg

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