US2865232A - Multi-speed drive device - Google Patents

Description

Dec. 23, 1958 R. M. NARDONE MULTI-SPEED DRIVE DEVICE 3 Sheets-Sheet 1 Filed Oct. 26, 1954 R m m m RoTroeoM Narozowe BY Dec. 23, 1958 R. M. NARDONE 2,865,232

MULTI-SPEED DRIVE DEVICE Filed Oct. 26, 1954 3 Sheets-Sheet 2 w ROTTLGOM iwxrdbne Dec. 23, 1958 R. M. NARDONE 2,865,232

MULTI-SPEED DRIVE DEVICE Filed Oct. 26, 1954 5 Sheets-Sheet 3 INVENTOR.

ROMEO M NARDONE ATTORNEY United States Patent MULTI SPEED DRIVE DEVICE Romeo M. Nardoue, Teanec k, N. J., assignor. to Breeze Corporations, Inc., Union,N. J., a corporation of New Jersey Application October 26, 1954, Serial No. 464,866 1 Claim. ci. 74-785 This invention relates to winches and more particu larly to power driven winches employed to'slide a' load across asubstantially level surface.

Presently known' winches of the aforesaid type are only capable of operating at one speed,which speed may vary slightly depending upon' the load to whichlit is slibjeeted. With'present day mass production methods,

where work may required upon an article as it is being moved; the inability to slow the o erating speed A further undesirable characteristic of present winches" is the uncoiling of the cablefrom the take up drum when slack in the winch cable occurs. This condition produces an uneven pull upon the winch load;

Accordingly, it is one of the objectsof this iavenfiea- Another feature of the present invention is the use of aball screw and nut assembly which permits high fleet angles between the cable and the take up drum; and'in addition facilitates side loadings. I A

A further feature of this invention is the adjustable pressure roller assembly which prevents uncoilirig or' springing away of the cable wound about the take up drum when slack develops in the caue' set'weemhe drum and a load afiixed to the free end of the cablel' The invention cd nsists" or the arranties, cornbina-. tion and arrangement of parts, as herein illustrated, described and claimed. 4

the accompanying drawings, forming a part hereof isillust ratjed one form of embodiment at the" invention, and in which:

Figure 1' is a substantially longitudinal cross section taken through the winch mechanism according to this invention; with certain parts shown in elevation.

Figure 2 is an enlargedfragmentary sectional'view of the two speed assembly according tothis" invention;

Figure 3 is a fragmentary view inlongitudinal section;

' therefrom to a point short of the vertical wall 17 of the recess 14 The end'of the shaft 41 is sp'lined as shown somewhat enlarged, of the multi-speed structure shown" in Figure 1.

Referring to the drawings and specifically to Figure l, 10 designates a winch housing comprising abase 11, topwall 12, end Walls 13 and 14, andfront. and rear walls 15. End wall 13 is recessed inwardly of the ends of the base 11 and the top wall 12 and is normaltheretor End wall 14 is dished inwardly to form a'frusto-conical recess indicated at 14. The bottom recess 14 com municates with an inwardly extending cylindrical portion 16 having at the end thereofa wall 17. A single speed electric motor 18is supported by endwall 14." A speed change assembly 19 and reduction gear assembly 70, are" coupledto the motor 18,the construction and function thereof will be hereinafter more fully discussed.

Within the winch housing 10 and overlying the speed change assembly 19 and gear reductionassembly 70,'is

a cable take up drum 20. The drum 20 is hollow,

open at one end which open end overlies the dishedwith similar holes 26 in the drum wall 21: The holes 25' and 26 are adapted to receive'pins 27 by which the sleeve 23 is secured to the drum 20; The portion of the sleeve 23 extending from the drum 20" projects through an opening 28 in the housing end wall 13' and is journaled therein upon a' ball bearing 29. Since the sleeve 23 is connected to the" drum 20, the drum is supported by the sleeve bearing 29 of the end wall 13. The motor end of the drum 20 is journaled upon the outside of the reduction gear assembly by a ball bearing 31'. The bearing 31 is carried within an internal flange 30 formed in the drum20.

A level wind assembly 32 is disposed adjacent the drum 20. The assembly 32 comprises a ball screw 33 and nut 34. To the nut 34 is threaded a funnel member 35 which guides a cable 36 into the nut 34 of the level wind'assembly 32. The ball screw 33 is' journaledat its ends to housing end walls 13 and 14 by ball bearings c'hored to the drum end wall 21" by means of ah'olding plate 21- boltedthereto by bolts 21". The free end ofthe' cable 36 is fed through the level wind assembly 32 by passingthe cable 36through a' transverse bore34 in the The drum 20 iscaused to rotate by the electric motor 18 through the two speed assembly 19 and the gear redu'ction assembly 70.

The electric motor 18 is secured to the end wall14' within the recess 14a by bolts 40. As best shown in Figure 2, the drive shaft 41 of the motor 18' extends at 46. Centrally carried by a bearing assembly 73 within an opening in the wall 17 and in axial alignment with the shaft 41, is a spider plate 42. Axle members 43, fixedly carried by the plate 42, support planet gears 44 mounted upon ball bearing members 45. The gears 44 are'so positioned that' they are in mesh with the'splined end 46 ofthe shaft 41:

Adjacent the gears 44is disposed a clutch plate assent:

.. My 47 consisting of washer likepl'ates 48" and' 49 al- Parented 'Dec. 23, 1958- 3 ternately and slidably carried by the splines 46 of the shaft 41 and the stud members 43, respectively.

On the motor side of the first clutch assembly 47 is a first face type solenoid 50, hereinafter referred to as the low speed solenoid-The lowspeed solenoid is supported by a bracket member 51 which is secured to the end wall 14 by bolts 40. A metal ring member 52, which serves as the solenoid armature has attached thereto a pressure ring 52 which bears against the clutch plate 49, thereby maintaining the successive alternate plates in clutching contact. Slidably mounted upon the shaft 41, adjacent the splined end 46, is a bearing 53. The bearing 53 is held against a shoulder of the pressure ring 52 by acoil spring 54. Upon energization of the low speed solenoid 50 the armature 52 is drawn, to the right of the position shown in Figures 1 and 2, against the tension .of a spring 54. The movement of the armature releases the pressure on the clutch plates 48 and 49 which were squeezed between pressure ring 52 and the ring member 52'. The release of the pressure unlocks the axle members 43 from the drive shaft 41 and prevents direct transmittal of the rotary movement of'shaft 41 to the gear plate 42. The planet gears 44 nevertheless remain in mesh with the shaft 41.

A second solenoid 55, hereinafter referred to as the high speed solenoid, is securd by bolts 56 to the bracket member 51. The high speed solenoid 55 is of the face type. A second ring member or armature 57 is positioned between the solenoid 55 and a brake plate assembly 58.

The brake plate assembly 58 comprising a plurality of washer- like plates 59 and 60 is disposed adjacent the armature 57. The brake plates 59 and 60 are alternately in mesh with the planet gears 44 and slidably carried by slotted ring member 61, respectively. Slotted ring member 61 is attached to the outer extension wall 16 by bolts 62. Plates 59, 60, when locked, form an internal ring gear in mesh with the planet gears 44.

A coil spring 63 is disposed between the bracket member 51 and the armature 57 so that when the high speed solenoid 55 is de-energized, the spring 63, bears against the armature 57 and pressure ring member 64 thereby forcing together the plates 59 and 60 of the brake assembly 58.

The operation of the high and low speed solenoids 55 and 50 is effected through an electrical circuit (not shown) independent of the motor 18. A pair of leads 65 and 66 (shown in Figure 1) conduct electric current to the respective solenoid windings 67 and 68 from a source of electrical potential and through a switch (not shown). Since the solenoids are controlled through a circuit independent of the motor 18, speed change can be effected without stopping the winch.

A four stage reduction gear assembly 70 is disposed adjacent the side of the wall 17 opposite the motor drive shaft 41. Power is supplied to the reduction gear assembly 70 by way of a sun pinion 71 which is secured to the hub of the spider 42 by means of a bolt 72. The pinion 71 and the spider 42 are journaled in a central opening 72 in the wall 17 by the bearing assembly 73. The cylindrical housing 7 of the gear reduction assembly 70 is secured to the recess end wall 17 by bolts 74. The housing 70 is internally splined at 75 and performs as a ring gear.

As shown in Figure l, the sun pinion 71 of the gear reduction assembly engages planetary gears 76, which are also in mesh with the internal splines 75 of the housing 70 The sun pinion 71 and the planetary gears 76 comprise the first stage of the reduction gear assembly 70. The planetary gears 76 are rotatably mounted upon studs 80 which are secured to a sun pinion gear 78. Rotary motion is transmitted by the gear 78 through a second stage reduction gear train comprising a second set of planetary gears 77 which mesh with the sun gear 78 and the splines 75. The second set of planetary gears 77 are rotatably supported upon studs 81 carried by a second sun pinion 78 A'third set of planetary gears 77 mesh.

4 with the second sun gear 78 and the splines 75. The gears 77 and the gear 78 comprise a third stage reduction gear train to effect a further reduction in speed of rotation. The planetary gears 77 are rotatably mounted upon studs 82 which are carried by a third sun pinion 78 The third sun gear 78 is in mesh with a fourth set of planetary gears 77 which are also in mesh with the splines 75 to form the fourth stage reduction gear train. The fourth set of planetary gears 78 are rotatably mounted upon studs 83 which are secured to the end wall 84 of the member 90. The sun pinions 78, 78 and 78 are rotatably and successively mounted upon a shaft 88. The shaft 88 is secured to the end wall 84 of the member 90.

The cylindrical support member 90 is rotatably carried within the housing 70a by a ring member 91. Internal splines 92 complete the structure of the support member 90, the purpose of which will be hereinafter discussed.

Within the cylindrical member 90 there is supported a torque overload clutch assembly indicated at 93. This assembly comprises a tubular clutch member 94 supported centrally of the member 90 by an adjustable ring nut 95 threadably received by member 90, and a pressure ring member 96. The end of the tubular member 94 is provided with teeth 94 In addition, member 94 has external splines 97, opposite the splines 92 of the support member 90. Interposed between the tubular clutch member 94 and the support member 90 is a clutch pack 101 consisting of a plurality of plates 98 and 99 alternately slidably carried by splines 92 and 97. Pressure is exerted upon the clutch plates 99 by a wavy washer 100 disposed between the ring nut 95 and the pressure ring member 96. By adjustment of the nut 95, the pressure upon the plates 98 and 99 may be preset.

The rotary motion of the support member 90 is passed through the clutch pack 101 to the clutch member 94.

From the clutch member 94 rotation is transmitted to' an output clutch member 102 through the teeth 94 and complementary teeth 103 of the clutch member 102. The driven clutch member 102 has external splines 104 which engage internal splines 105 of the sleeve 23. Since the sleeve 23 is secured to the drum 20, in the above described manner, the drum 20 is thereby rotated.

The clutch members 94 and 102 are held in engagement by a coil spring 106 which is disposed within sleeve 23 and bears against a shoulder 143 on the sleeve 23 and the clutch member 102. A clutch release rod 108 is yieldably journaled within the clutch member 102 by a bearing 109. The release rod 108 is provided with a shoulder 110 and terminates at its inner end in a flange 111. Interposed between the flange 111 and the hearing 109 is a return coil spring 112. The release rod 108 permits manual disengagement of the clutch members 94 and 102. A pull upon the rod 108, to the left in Figure 1, compresses return coil spring 112 until the rod shoulder 110 bears against the bearing 109. When the shoulder 110 strikes the bearing 109, the clutch member 102 is moved to the left in Figure 1, thereby disengaging the clutch teeth 103 from the complementary teeth 94 When the rod 108 is released, the spring 112 returns the clutch member 102 into engagement with the clutch member 94.

n The two speed operation of the winch is accomplished 1n the following manner: To secure low speed, the low speed solenoid 50 is energized and at the same time high speed solenoid 55 is de-energized. To effect high speed operation of the winch, the low speed solenoid 50is de-energized and the high speed solenoid 55 is energized.

In low speed operation, the activated solenoid 50 moves armature 52 against the tension of spring 54, thereby releasing the clutch plates 48 and 49. The release of the brake plates 48 and 49, uncouples the sp1der plate 42, through the planet gear axles 43, from the motor shaft 41. At the same time solenoid 55 is de energlzed permitting spring 63 to compress brake discs 59 and 60, whereupon discs 59, locked together as a unit, operate as a ring gear. With the componentparts of the speed .change assembly 19 in the positions as aforesaid, the planet gears 44 and the brake plates 59 form a gear reduction train which transmits rotation of shaft 41, to planet gears 44, through the plate 42, thence to the drive pinion 71, at a reduction in R. P. M. Rotation is then transmitted fromthe drive pinion 71, through the speed reduction assembly 70, through the cylindrical support member 90, to the overload clutch pack 101, thence through the clutch members 94 and 102 and sleeve 23, to the drum 20, in the manner previously described.

For high speed operation, a switch (not shown) is thrown which de-energizes the low speed solenoid and simultaneously energizes the high speed solenoid 55. Upon de-energiza'tion of the low speed solenoid 50, the clutch plates 48 and 49 are compressed by armature 52 under the urging of spring 54 as shown in Figure 2. At the same moment, the high speed solenoid 55 is energized, drawing the armature 57 against the spring 63 thereby releasing brake plates 59 and 60. This release of the brake plates 59 and 60 permits plates 59, with which the gears 44 mesh, to slip upon rotation of the gears 44. Since the planet gear axles 43 are now coupled to the motor drive shaft 41, the spider 42 is rotated by the planet gears 44 in a substantially 1:1 ratio to the motor drive shaft 41. The rotation of the sun pinion 71, which is secured to the spider 42, will drive the drum 20 through the reduction gear assembly 70, the clutch members 94 and 102 and the sleeve 23, in the manner previously described.

When low speed operation is again desired a switch (not shown) is thrown to energize the low speed solenoid 50 and simultaneously de-energize the high speed solenoid 55.

The level wind assembly 32 and its gear train drive mechanism can best be seen by referring to Figure l. The sleeve 23 extends beyond the winch housing 10, at which end it is provided with gear teeth 114. Gear teeth 114 mesh with a larger gear 115 which is journaled in the housing and wall 13. The gear 115 engages a driven gear 116 which is keyed to the end of the ball screw 33. A nut 117 is threaded upon the end of the ball screw 33. The nut 117 holds the ball screw 33 within the winch housing 10 and prevents end play of the screw 33 therein. The ratio of the gears 114, 115 and 116 is such that for every complete revolution of the drum 20, the ball screw nut 34 is indexed the thickness of the cable 36. This synchronized feeding of the cable 36, as the drum rotates to retract the cable, prevents the windings of the cable from cries-crossing. That is, the cable will be wound about the drum so that the coils thereof lie in side by side relationship.

To automatically stop the winding or unwinding of the cable 36 about the drum 20 when it reaches the end of its travel, a limit switch assembly 120 is mounted upon the outside face of the end wall 13. The limit switch assembly 120 is secured to the wall 13 by screws 121 so as to overlie the hub of the gear 115.

The limit switch assembly 120 comprises a switch support plate 122 upon which are mounted spaced microswitch members 123 and 124. One switch member 123 controls the electrical circuit to the motor 18 for winding, the other switch member 124 controlling the circuit for the unwinding operation. Interposed between the micro-switches 123 and 124, is a switch actuating means in the form of a screw 125. The screw 125 is slidably keyed within two upstanding members or ears 122 of the plate 122. To the end of a stud shaft 126, axially carried by the gear 115, is attached a worm screw 127. In mesh with the worm screw 127 is a worm gear 128. The worm gear 128 is positioned between the two ears 122 and is internally threaded to receive the switch actuating screw 125. Since the stud shaft 126 is fixed to the gear 115 by means of a pin 129, the rotation of gear 115 rotates worm 127. Worm 127 drives gear 128 which in turn feeds screw 125 axially in the direction of one of the switch members 123 or 124, depending upon the direction of rotation of the gear 115. When the contact screw 125 strikes the contact member 130 or 131 of the switch members 123 and 124, respectively, the

electrical circuit of the motor 18 is opened, thereby stopping rotation of the drum 20 in that direction. As the opposite circuit (either for unwinding or winding of the cable) is closed through its micro-switch, the motor 18 will operate to rotate the drum 20 in the opposite direction.

Again referring to Figure l, a tubular rail member 142 is supported above the ball screw 33 by end walls 13 and 14. The rail member 142 is receivable within a U-shaped groove 143 in the top of the nut 34. The purpose of the rail member 142 is to guide the nut 34 in its travel along the ball screw 33. In addition, the rail member 142 serves to resist the torsional stress applied to the nut 34 when the fleet angle between the cable and the drum 20 is great. Another function of the rail member 142 is to support therein the electrical leads which run from the limit switches 123 and 124 to an electrical junction box, partially shown at 150.

From the foregoing description of the speed change assembly 19, it can be readily seen that a simultaneous energization of the high and low speed solenoids 50 and S5 prevents the rotary motion of the motor drive shaft 41 from being transmitted through the planet gears 44 to the reduction gear assembly 70. Therefore, in initially starting the winch, the solenoids 50 and 55 may be first energized and then the motor 18 started. Once the motor 18 has been started, solenoid 55 may be de-energized thereby effecting an initial low speed operation. If it is desired to elfect initial high speed operation the solenoid 50 is de-energized while the other solenoid 55 remains activated. Thereafter, a change of speed from the initial speed of operation may be accomplished in the manner previously described.

The starting procedure outlined above represents a safety feature, which will prevent damage to the reduction gear assembly '70 and/or the speed change assembly 19.

It is apparent from the foregoing description that a winch mechanism has been provided which can be selectively operated at two speeds without stopping the de' vice. it is a compact unit in which the speed change means and the drive means are an integral part of the winch. Further, it is a winch which is provided with a level wind assembly that permits of operation under high fleet angles between the cable and the take-up drum. The level wind assembly, comprising a ball screw and nut member, enables the winch to operate under greater side loadings than presently known structures.

Having thus fully described the invention, what is claimed as new and desired to be secured by Letters Patent of the United States, is:

A multi-speed drive means comprising a rotary drive shaft having a splined portion thereof, a first series of shaft driven plates slidably carried upon the splined portion of the shaft and in engagement therewith, a series of washer shaped plates alternately disposed between the driven plates, a planetary carrier in the form of a spider plate spaced from the plates, stud members carried by the spider and extending therefrom in the direction of the plates, planet gears rotatably carried upon a portion of the said studs, and washer shaped plates carried by the other portion of the studs, a first solenoid adjacent the plates, a washer shaped armature for said solenoid engageable with the plates, a spring around the splined shaft in engagement with the armature to normally urge it against the plates to produce frictional engagement of said plates thereby locking the studs with said shaft, a second series of driven plates disposed about but spaced from the splined shaft and in mesh with the planet gears, 21 second set of washer shaped plates alternately disposed between the second set of driven plates, a fixed ring member coupled to the second set of washer shaped plates, a second solenoid adjacent the second set of plates, an armature between the second solenoid and second set of plates, a second spring normally urging the second set of plates together, output means coupled to the planetary carrier and a source of electrical potential selectively connected to the solenoids whereby the armatures may be pulled away from the plates against the pressure of the springs to vary the transmission of power from the power source through the plates to the output means.

Jones et al. Dec. 23, 1913 Hale July 17, 1928 8 Winther '1 Dec. 15,

Havill Feb. 27,

Nardone July 3,

Wilsing June 4, Arnold Oct. 8,

Arnold Nov. '11,

Bridwell Jan. 2,

Russell Nov. 14,

Nardone May 15,

Durston July 21,

Carr Nov. 17,

Brown Dec. 15,

FOREIGN PATENTS Germany Oct. 3, Germany Oct. 22,

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