US2318422A - Ironer - Google Patents

Description

L. RINGER May 4, 1943.

IRONER F'led Sept. 23, 1940 6 sheets-sneet 1 .nl/En Lur i Luz'hef Rincgefi IRONER Filed Sept. 23, 1940 6 SheetS-Shee'b 2 /HVEH L'UI-1 uheyRJJt/ger:

May 4, 1943.

JELEYFAEE Luther flygel).

May 4, 1943. r

.L. RINGER IRONER 2-,31s,4zz v Filed Sept. 23, 1940 fig-.8

6 Shee'cS-Shee*l 4 Luther Ringen/ L. RINGER 2,318,4 22.

Holumv Filed sept. 23. 1940 e sheets-sheet s May 4, 1943.

L. RINGER May 4,' 1943.

IRONER Filed Sept. 23, 1940 :6 Sheets-Sheet 6 i w 4 I x 4 w i nl' :I ii

;` h I r I rv: T'-

loz 5 v .Hz/En zur" Luther Ringer Patented May 4, 1943 r z,31s,422 I IRONEE Luther Ringer, Berrien Springs, Mich., assignor to Nineteen Hundred Corporation, St. Joseph, Mich., a corporation of New York Application September 23, 1940, Serial No. 357,932

Claims.

This invention relates to -ironing machines, and more particularly to ironing machines of the domestic or home laundry type. p

One common form of home laundry ironer comprises a power-driven padded roll and a heated shoe, which are moved relative to each other to carry them into and out of pressing engagement. As machines of this type are ordinarily constructed, the roll is mounted on a stationary axis, while the shoe is rocked or otherwise shifted toward and away from the roll. Provision is usually made for rocking or shifting the shoe by power derived from the same source that drives the roll. For this purpose a clutch is provided in the train of mechanism from the power source to the shoe-Shifting member, and this clutch is generally arranged to be engaged under manual control and disengaged automatically upon-completion of the shoe-releasing Operation. In this way the clutch is thrown out whenever the shoe reaches either extreme of its movements toward and away from the roll.

While the common practice is to rotate the roll at a constant speed, usually about six revolutions per minute, it has been found desirable to provide more than one speed of Operation for the roll due to the fact that clothes and other articles to be ironed vary greatly in texture, dampness, etc.

Ironing machines of the type hereinabove referred to are also provided with a safety release mechanism for disengaging the shoe from the roll very rapidly in the event of an emergency. This safety release mechanism is usually provided with an operating lever which projects up a substantial distance above the uppermost part ofthe heated shoe. It has been found that a safety release operating lever of this character prevents a compact cover construction to be used with the ironing machine. One of the features of the present invention is to provide an improved safety release operating member which may be retracted to a position below the uppermost part of the heated roll when the machine is not in use and when it is desired to cover the roll and shoe. v

One of theprincipal objects of the present in'- vention is to provide a novel speed-changing mechanism.

-A further object of the present invention is to provide a novel ironing machine embodying the above-referred-to highly desirable characteristics.

A further object of the present invention is to provide a novel ironing machine which is economical to manufacture, simple to operate, and rugged and reliable in use.

Another and further object of the present invention is to provide a novel clutch mechanism for effecting rocking movement of the shoe when desired. e

Another and still further object of the present invention is to provide a novel safety release member and mounting therefor for disengaging the shoe 'from the roll.

Still another object of the present invention is to provide a novel ball clutch speed-changing mechanism.

The novel features which I believe to be characteristic of my invention are set forth with particularity in the appended claims. My invention itself, however, both as to-ts method of operation and manner of construction, together'with further objects and advantages thereof, may best be understood by reference to the following description taken in connection with the accompanying drawings, in which:

Figure 1 is a front elevational view of a domestic ironing machine embodying the teachlngs 4 -of the present invention;

Figure 2 is a plan view of the ironing machine shown in Figure 1;

Figure 3 is a vertical sectional view throughv the ironing machine showing the shoe-release lever. in elevation;

Figure 4 is a front elevation of the shoe-release lever and associated mechanism, with the heated shoe removed;

Figure 5 is an enlarged fragmentary view of the shoe-release member and mounting as taken Figure 9 is a. view similar to Figur'e s, but with v fthe driving mechanism set to operate at a different speed and the eccentric arm in an "up position with the clutch disengaged;

Figure 10 is a fragmentary sectional view showing the driven gears in a neutral position;

Fgure 11 is -a sectional view through the smaller of the two driven gears as taken -along the line XI-XI of Figure 9; i

fingers 36 and 31 and Figure 12 is a fragmentary view of the trip lever and mechanism as taken along the line XII-XII of Figure 7;

Fgures 13, 14, and are fragmentary sectional views of a modified form of the gear shift shown in Figures 8 to 11, inclusive;

Figures 16 and 1'1 are fragmentary sectional views similar to Figures 13 and 14 but illustrating a third embodiment of the presentI invention insofar as the gear-Shifting mechanism is concerned.

Figure 18 is a sectional view of the emergency release lever assembly taken along` the line XVIII--XVIII of Figure 5; and

Figure 19 is a Vertical sectional view through the right-hand plunger shown in Figure 13.

The domestic or household ironing machine shown in Figures 1 to 12 of the drawings illustrates one embodiment of the present invention and includes, in general, a Supporting stand 2l, on which is mounted a rotatable padded roll 22 and a heated shoe 23 which is arranged to be moved into engagement with the padded roll 224 to perform the pressing or ironing Operation.

X Power for driving the padded roll 22 is obtained from an electric motor 24, which is mounted on the underside of the table top 25 of the support- -ing stand 21.

The padded roll 22 is mounted for rotation on a stationary stub shaft 26, which projects approximately half way through the roll 22. While only a portion of this stub shaft 26 is shown (Figure 8), it is to be understood that the padded roll is suitably journaled on this stationary stub shaft 28 for rotation therearound. As will also be clear from an inspection of Figure 8, the stationary stub shaft 26'is carried on the housing 21, which encloses the speed-changing and clutch mechanism presently to be described.

Figures 3, 4, and 5'of the drawings illustrate one manner in which the heated shoe 23 may be carried on the Supporting stand 2l. A rotatable actuating shaft 28 is mounted below the table top 25 of the support-.ing stand 2| .and extends from a point below and immediately behind the casing 21 to approximately the middle of the supporting stand 2I. Shaft 28 extends through a housing 28, which is carried by a pair of brackets 38 (only one of which is shown in Figure 4) A rocker arm 3l is journaled for free movement on the shaft 28 and is held in place against the end of the housing 28 by an end plate or washer 32 and a nut 33, which is threaded onto the end of the shaft 28. The rocker arm 3l is of U-shaped cross section with the opening portion thereof facing forward. As may be seen best in Figures 3 and 4, the rocker arm 3| projects upwardly through the table top 25 to a position behind and slightly above the padded roll 22.

Rigidly secured to the shaft 28 and disposed inside the lower portion of the U-shaped rocker 1 arm 31 is a casting 35. The upper end of the casting 35 has two short fingers 38 and 31, finger 31 being somewhat longer than the finger 38. A pawl-engaging pin 33 extends between the is arranged to be engaged which is pivotallyV carried on a pin 4l mounted in the rocker arm 3l. The pawl 40 is normallybiased downwardly by a suitable spring 42. When the shoe-operating shaft 28 is rotated in a counterclockwise direction, as viewed in Figure 3 of the drawings, the pin 39 on the casting 35 engages the shoulder 43 on the pawl 48 and forces-the rocker arm 31 forwardly.

by a pawl member 40,

A relatively heavy col spring 44, which is under compression, extends between the casting 35 and the rear wall of the rocker arm 3l, it being held in place by a protuberance 45 in the wall of the .1 -arm 3! at one end and by a recessed portion 48 in the casting 35 at the other end. When the operating shaft 28 is rotated in a' clockwise direction, as viewed in Figure 3, the casting 35 is carried with it and forces the rocker arm 3l along with it through the medium of the coil spring 44.

The heated shoe 23 is provided with a bracket 41, which projects rearwardly therefrom through the rear wall 48 of the shoe 23 into pivoted engagement with the rocker arm 3l. The pivoted engagement is provided by a pin 49, which is carried by the rocker arm 3| and held in place by spring rings 50 at each end carried in grooves in the pin 48. An upper casting member 5l is journaled on the pin 48 and includes a cylindrical socket portion 52, through which an operating rod 53 extends and a tail portion 54. A connecting link 55 extends from the tail portion 54 of the casting 5l down into engagement with a slot 56 in the pawl 40. It will-be understood that when the casting 52 is rocked in a clockwise direction, as viewed in Figure 3 of the drawings, the connecting link 55 raises the pawl 40 to disengage the shoulder 43 from the pin 38. The heavy coil spring 44 thereupon forces the rocker arm 3! rapidly rearwardly (in a clockwise direction as viewed in Figure 3) and causes the heated shoe 23 to swing back from the roll 22.

The operating rod 53 loosely extends through a cylindrical Vbore 51 in the upper portion of the casting 52, as may be seen best in Figure 5. The lower end of the rod 53 is provided with a collar 58, which limits the upward movement thereon. The rod 53 is also provided with a pin 59, which is arranged to engage a shoulder 68 provided by counterboring the Opening 51 in the casting 51. A longitudinally extending slot BI is provided which permits the pin 43 to pass through the upper portion -52 of the casting 5l when the rod 53 is rotated to properly position the pin'53. The upper end of the rod 53 is provided with a knob 82 which enables it to be quickly grasped or engaged by the hand of the person operating the ironing machine.

The above-described type of emergency release mechanism, and particularly with regard to the manner in which the operating rod or handle is telescoped through the casting 5l, enables this operating handle 53 to be retracted to the position as shown by the dotted' lines in Figure 4 when the ironing machine is not in use. This' enables this particular type of release mechanism to-be used with an ironing machine having a cover which fits closely and compactly over the roll 22 and the heated shoe 23. InFigure 6 of the drawings I have shown an ironing machine with a cover 83 hingedly mounted on the supporting stand 2| by suitable hinges 54. It will be noted that the operating rod is in a retracted position so that the knob 82 is in a position which enables the cover 83 to be closed. In all the other figures of the drawings the cover 53 has been removed for purposes of clarity in illustration.

The mechanism for driving the roll and operating the shoe is substantially all contained within the housing 21, which is carried on the supporting stand 2l. Turning first to Figure 6, it 'will be observed that' the motor 24 is carried by a bracket 85 on the under side of the table to'p 25 of the Supporting stand 2I. The rotor shaft 66 of the motor 24 is provided'with a drive pulley 61 and connects through a belt-drive 68 to a driven pulley 69. The driven pulley 69 is mounted on a protruding end portion 18 of a worm 1I. The worm 1I is journaled in shoulder portions 12 and 13 formed in the casting which constitutes the 'housing 21.

The worm 1I is in constant mesh with`a worm Wheel 14, which is loosely mounted on a hollow shaft 15. The worm Wheel 14 has secured thereto, a toothed clutch disc or star wheel 16 which forms an integralpart of 'the worm 'Wheel 14. This clutch disc 16 is continuously rotated so long as the worm 1I is being driven.

Cooperating with the toothedclutch disc 16 is a clutch pawl assembly which includes a casting 11 mounted on and rigidly secured to the shaft 15, a clutch pawl 18, and a clutch pawl lever arm 19. The clutch pawl 18 and the clutch pawl lever arm 19 are both pivotally mounted on the casting 11 by means ofva common pin 88. They are held in place on the pin 88 by means of a washer assembly including a spring washer I98 and a rigid 'washer I9I, the washer's being held in place by the end I92 of a spring 83 which is hooked through a hole in the end of the pin 88. As will presently be referredl to again, the springwasher assembly I98 and I9I applies friction on the pawl 18 to prevent undesired ratcheting or contacting of the clutch disc or ratchet Wheel 16. The clutch pawl lever` arm 19 is shaped tostraddle the toothed clutch disc 16. The clutch pawl ward movement of theclutch `pawl 18. Due to v the fact that the clutch pawl lever 19 straddles the clutch disc 16, outward 'movement of the clutch pawl 18 would be limited by the engagement o'f the 'left-hand portion of the lever 19 against the clutch disc 16, if the edge of the opening 85 were not employed asr a stop. A spring 83 is hooked into the inner end of the pin 88 and extends down into engagement with a pin 84 on the lever arm 19. This spring 83 normally biases the lever arm 19 in a clockwise direction with respect to the casting 11 and the hollow shaft 15, as viewed in Figure '1 of the drawings. The' lever arm, in turn, bears against the ear 82 on the pawl 18 and causes it to fall into one of the cut-out portions of the toothed clutch disc 16. 82 of the clutch pawl is in engagement with the toothed portions of the clutch disc-16,.the casting 11 and theshaft 15 are rotated with.the worm wheel 14.4 If, however, the clutch pawl ear 82 is disengaged from 'the clutch disc 16, the casting 11 and the shaft 15 will no longer rotate with'the worm wheel 18.

As will presently appear. the clutch pawl lever arm assembly is employed to control the movement of the heated shoe 23 toward and away from the padded roll 22 and is also employed to start and stop the rotational movement of the padded roll 22. This control function is brought about by controlling the position of an eccentric 86 rigidly secured on the end of the hollow shaft 15 (see Figures 6, 8, and 9).

The particular eccentric construction shown It will thus be understood that when' the ear in the various flgures of the' drawings is-vin the form of a circular'metal disc having a hole 81 for -fitting over the shaft 15 which is disposed in an eccentric position thereon. Two pockets 88 on opposite sides of the diameter including the hole 81 are provided for the reception of felt or other fibrous oil packings 89. Lubricating passageways 98 are provided through the side wall of the circular disc from the pockets 88 to 'the peripheral surface of the disc forming the eccentric 86. As is clearlyshown in Figure 9, for example, the eccentric 88 may be looked to the shaft 15 by means of a set screw 9l.V The -set screw 9I is contained in a well 92, the lower portion of which is threaded as at 93. The upper portion of the well 92 is designed to receive a felt or fibrous oil packin'g 94, which-further serves to lubricate the peripheral surface of the eccentric 86.

Surrounding the eccentric 86 is a strap member 95, which is in the form of a casting having an upper portion machined to fit around the eccentric 86. This upper portion of the` strap member 95 is slit. as at 96. The slit portions of the member 95 are connected together by a long bolt 91 which has a coil spring 98 slipped thereover between the head of the bolt and the ad'lacent portion of the strap member 95. The vbolt 96 is held in place by a suitable nut 99.

The lower end of the strap member 95 carries a long threaded connecting rod I88 having a shoulder I8I thereon which Bears lagainst a sheet metal arm I82 of U-shaped cross section Which is rotatably mounted on the end of the rotatable actuating shaft 28. A coil spring I83 'is disposed' over the end of the connecting rodI I88.on the lower side of the sheet metal arm 'I82 and is held in place by av suitable nut I 84.

Tightly mounted on the end of the rotatable actuating shaft 28 and movable therewith is a crank arm I85. This crank arm I85'is disposed to lie between the side walls of the arm I82. A

I long bolt `I86. which passes freely through the arm I82. is threaded into the end of the crank arm I82. A cap or other suitable washer I81 is carried by the bolt adjacent its head, and a heavy coil spring I88 is mounted between this cap member I81 and the arm I82. This heavy coil spring I88 tends to force the arm I82 tight.- ly against the crank arm I85. When the eccentric 86 is rotated to the position shown in Fig- -ures 6 and 8, the connecting rod l88 is forced downwardly. Downward movement of the connecting rod I88 rocks-the arm I82 in a counterclockwise direction. as viewed in Flgureof the drawings. Since the heavy coil spring I88 tends to' keep the crank arm I against the arm I82, the crank arm I 85 is also rocked in a counterclockwise direction, as viewed in Figure 6 of the drawings. This carries the heated shoe 23 toward the padded roll 22 until it is stopped thereby. Continual downward movement of the connecting rod I88 now tends to separate the arm I82 from the crank arm I85 and thereby load' the coil spring. I88. This creates the desired Pressure between' the heated shoe 23 and the padded roll 22 for effecting the -ironing operation. When the cam 86 is in its lowermost position. as shown in Figure 6. the spring I88 is loaded and the heated shoe 23 i's performing its pressing function. 'The degree of pressure exerted by the heated shoe 23 against the padded roll 22 may be conveniently adjusted by screwing the bolt I86 more or less into the crank arm 185, thereby varying the extent. to which the spring 108 will be loaded by the downward movement of the connecting rod 100 when driven by the eccentric 86.

When the cam 86 is rotated 180 degrees, or, in other words, moved to its uppermost position,

as shown in Figure 9 of the drawings, the heated lever arm 19 are also rotated in a clockwise (ii-- rection. If something is placed in the path of the clutch pawl lever arm 19 as it rotates in a clockwise direction, this lever arm 19 moves over against the ear 81 of the clutch pawl 18 and lifts the ear 82 out of engagement with the clutch disc 16. The clutch disc 16 then continues to rotate, but motion of the clutch pawl assembly, including the casting 11, has ceased. Since the eccentric 86 moves in unison with the casting 11 (both being connected to a common shaft), it will at once be apparent that the angular position of the eccentric 86 may be controlled by placing an obstace in the path of movement of the clutch pawl lever arm 19 so as to cause it to rock about its Supporting pin 80 to engage the clutch pawl 18 and lift it out of engagement with the clutch disc 16.

This is provided by mounting a finger 161 on the casing 21 and providing the finger 161 with a bent end portion 162, which projects into the path of movement of the clutch pawl lever arm 19. As is clearly shown in Figures 7 and 12, the control flnger 161 is mounted on and locked against movement of a short shaft 163, which extends through the casing 21 and which has a suitable control knob 168 on its outer end. A spring 165 biases the finger 161 to a position in which the bent end portion 1621 lies directly in the path of movement of the end portions 166 and 161 of the clutch pawl lever arm 19 and in which the bent end portion 162 also lies against a stop member 190'. The stop member 190' is bolted to the hou'sing as at 191'. The finger 116 is mounted for rocking movement by a manual depression of the projecting finger-tipl portion 168 of the knob 166 (see Figures: 1 and 7). The end portions 166 and 161 are so designed that their leading edges 169 and 110 lle in an imaginary line passing through the center of rotation of the casting 11 and are 180 degrees apart.

The Operation of the control mechanism for the clutch pawl lever assembly will be apparent from a careful inspection of Figure 7. Assuming that the worm Wheel 14 and the clutch disc 16 are being driven in a clockwise direction from the worm 11, we find the leading edge 189 of the end portion 166 of the clutch pawl lever arm 19 in engagement with the bent end portion 182 of the control finger 161. In this position the 'clutch pawl lever arm 19 is holding the clutch pawl 18 out of engagement with the clutch disc 16. and the casting 11 remains stationary. In this position the eccentric 06 is in a "down" P- ition, as shown in Figures 6 and 8 of the drawings, and the heated shoe 28 is in tight pressing engagement with the padded roll 22.

If the finger-tip control lever 168 is now momentarily depressed, the bent end portion 162 of the finger 161 moves `out of engagement with the clutch paw1 lever arm 19, and the biasing spring 83 causes the clutch pawl lever arm 19 to bear against the ear 82 of the clutch pawl 18. This causes this ear 82 to drop down in the first slot which passes beneath it, and the clutch pawl assembly is now looked for rotation with the clutch disc 16 and the worm 14. When the pawl 18, the pawl lever arm 19 and the casting 11 are rotating with the clutch disc or ratchet Wheel 16, the left-hand portion of the pawl lever arm 19 (as viewed in Figure '1) is in its maximum angular position away from the casting 11 and the ear 82 of the pawl 18 is in one of the slots of the clutch disc 16. Rotation of the clutch pawl assembly, including the casting 11, continues until the leading edge '110 of the next end portion 161 of the clutch pawl lever arm 19 Vadvances into engagement with the bent end portion 162 of the control finger 161. At the moment of time when the pawl lever arm first strikes the stop or finger portion 162 the pawl is still in engagement with the clutch disc, and hence the casting 11 continues to rotate causing a counterclockwise movement of the pawl lever arm 19 about the pin on the casting 11. This 'relative movement of the pawl lever arm 19 with respect to the casting 18 causes the pawl ear 82 to be lifted out of the clutch disc slot in which it has been seated. The spring washer assembly 190 and 191 creates enough friction to hold the pawl up in its kick-up position to prevent it from contacting the clutch disc or ratchet wheel 16 and thus prevents any undesired clutching or ratcheting on the clutch disc 16.

The above described clutch mechanism and assembly' for selectively connecting the worm wheel 14 to the hollow shaft 15 and particularly the pawl mounting is one of the important novel features of the present invention.

A control lever 169', which is arranged to be engaged by the knee of the operator of the ironing machine, may be employed, if desired, for controlling movement of the finger 161. This knee-operated lever 169f is mechanically cou pled to the shaft 163, on which the control knob 168 is mounted in any suitable manner (not shown).

As has previously been pointed out, it is desirable to stop the rotation of the padded roll 22 whenever the heated shoe 23 is withdrawn from pressing engagement therewith. Since the starting and stopping of the padded roll 22' is a function of the 'position of the heated shoe 23, the control therefor may be conveniently provided to act in response to the positionof the cam 66. Before reference is made to the details of this control mechanism, which operates in response to position of the eccentric 86, the general construction by which the padded roll 22 is driven from the worm wheel 14 will be described.

The padded roll 22 is driven through a large gear 109, which is bolted to the end of the roll frame, as at 110. The large gear 109 is constantly in mesh with a pinion gear 111 keyed or otherwise rigidly secured on the reduced end portion 112 of adrive shaft 113. The drive shaft 118 is Journalen in a sleeve bearing 114` which, in turn, is heldlin an opening 115 in the housing 21. Rotatably mounted on the opposite end of the shaft 113 from the end on which the pinion trip 111 is mounted are a pair of gears 116 and 111. Each of the gears 116 and 111 is shown as being provided with separate hub portions 118 and 119, respectlvely, upon which the outer portions of each of the gears are sweated or otherwise rigidly secured. These gears 116 and 111 may be selectively placed in driving cooperation with the drive shaft 113 by a ball clutch mechanism presently to be described.

Gears 116 and 111 are constantly in mesh with a cooperating set of gears 120 and 121, which are .rotatably mounted on a sliding sleeve bearing or bushing 122. As is clearly shown in Figures 8 and 9 of the drawings, the gears 120 and 121 are prefj erablyformed integral with each other from a single piece .of metal to form a single one-piece unit. The sleeve bearing or bushing 122 is mounted -on the hollow shaft and arranged forlimited axial movement thereon. i The face of the gear unit 120, 121 which lies opposite the worm Wheel 14 is provided with jaw clutch teeth 123, Which cooperate with a complementary set of jaw clutch teeth 124 formed on 'the worm wheel 14.v It will thus be understood that whenever the jaw clutch sleeves 123 and 124 are 'in engagement with each other, the gears 120 and .hollow shaft 15 and is provided with a semispherical end 121, which bears against a cam plate 128. The cam plate 128 is mounted on the outer face of Vthe eccentric strap 95 by means of a plurality of 'bolts- 129. Oil rings 130 are preferably provided in the head portion 131 of the control shaft 125 and cooperating lubricating ports 132, '133 and` 134 are provided through the hollow shaft 15, the sleeve 135, in which the hollow shaft is mounted, and the end plate 136 of the housing 21, respectively. 4

The sleeve bearing or bushng 122, upon which the gears 120, 121 are rotatably mounted, is keyed or pinned to the control shaft 125 as at 131. It Will thus be understood that bylongitudinally or axially shifted the control shaft 125 the jaw clutch teeth 123 may be engaged and disengaged from the jaw clutch teeth 124 of the worm Wheel 14. The cam plate 128 is so constructed that When the eocentric 86 is in its lowermost position, as shown in Figures 6 and 8,-

the control clutch shaft 120 is in its extreme right-hand position (as viewed in Figure 8), and the jaw clutch teeth 123 are in locking engagement with the complementary jaw clutch teeth 124 of the worm Wheel 14. When the eccentric 86 is rotated through 180 degrees, or to its upv clutch teeth on the worm Wheel 14. In this position the gears 120 and 121 come to rest, and rotation of the padded roll 22 stops, since it is no longer being driven from the worm Wheel 14. i

The gear unit 120, 121 is retained 'in desired position on the sleeve bearing or bushing 122 by providing a shoulder 138 at one end of the sleeve bearing 122 and by a-washer and lock ring 138 and 140, respectively, at the other end. v

AS win at once be understood by those skineo in the art, the transmission formed by gears .1,16, 111, 120, and 121 provides a two-speed drive i tated at a different speed due to the different gear ratio between mating gears 116 and, 120 and the other set of gears4 111and 121.

A novel ball clutch mechanism is provided for I selectively connecting either gear 116 or gear 111 to the drive shaft 113. One detailed embodiment of this construction -will now be described. f

In Figures 8 to 11 of the drawings, it will be observed that a ball clutch control shaft 141 is slidably mounted in an axial bore or'recess 142 formed in the end of the drive shaft 113. This ball clutch control shaft has an intermediate deep-cut flat shoulderI 143 and two fiat end shoulders 144 and 145. Openings 146 and 141 are provided through the drive shaft 113 under the hubs 118 and 11-9, respectively, of gears 116 and 111. The ball clutch control shaft 141 is keyed to the drive shaft 113, as at 148, so as' to 'prevent relative vrotation between the ball clutch control shaft 141 and the drive shaft 113. The key 148 may be held in place in any suit- :ligge manner such as by means of a set screw A shallow, circumferentially disposed channel is formed on the radial inner faces of thehubs 118 and 119, as at 150 and 151. Mounted within each channel 150 and 151 are a -plurality of partitions 'or walls 152, which make a smooth running flt with the drive shaft 113 (see Figure 11).'

A pair of balls 153 and '154 are carried in the assembly'in the openings 146 and 141. When one of these balls is pushed up throughgone of the openings 146 and 141, the ball is engaged by one of the walls or partitions 152, and thereafter the drive shaft 113 will be driven by the gear carry-` ing the projection engaging the ball. When the ball is dropped down so that no portion'thereof projects out through the drive shaft 113. the

gear will rotete froely around the drive shaft 13 without driving the same. The shoulders 143, 144, and on the ball clutch control shaft 141 provide a convenient mechanism for forcing the balls 153 and 154 upwardly through the openingsl 146 and 141 when desired. When the control'141 is in' the position as shown in Figure 10, both of the balls 146 and 141 are seated on the Intermediate deep-cut shoulder 143. For that reason, both of the gears 116 and 111 are free to rotate on the drive shaft 113 and will not drive the same. This represents the neutral position of the ball clutch control shaft 141. It will be observed from an inspection of Figure 11 that since the balls 153 and forced back into the openings 146 and 141 by the partitions 152 unless positions by one of the shoulders 144 or 145.

When -the ball clutch control shaft 141 is moved to the right to the position as shown in Figure 8, the 'ball 153-rides up off the shoulder 143 and onto the shoulder 144. In this. position,'the gear 116 Will -be connected to the drive shaft 1 13 through one of its partitions 152, the ball 153, and the wall of the' Opening 146. The ball 154 is still seated on the deep-cut intermediate shoulder 143, and for that reason gear from that of 116, will not be connected in driving engagement with the drive shaft 113. This represents the lowspeed connection for the roll drive.

When the ball clutch control shaft 141 is movedto the position as shown in VFigure 9 of the drawings,,the ball 153 moves down onto the deep-cut Intermediate shoulderl143, but the ball 154 rides up onto the shoulder 145 and causes a driving 154 never come quite half wayl out of the openings 146 and 141, they will be positively held in their outer 111, which is being roi connection between the gear 111 and the drive shaft 113. This provides the high-speed drive for the roll 22.

Movement of the ball clutch control shaft 141 is obtained by providing a plurality of circumferentially extending ribs or ring fianges 155,

which mesh with a small pinion 156. The pinion 156 is mounted on a shaft 151, which passes through a wall of the casing 21 and carries a speed-selection control knob 158 (see Figure 7). The shaft 151 is conveniently mounted in a boss 159 carried by the casing 21, and a pin 166 is provided on the shaft 151 for limiting the turning movement of the shaft 151.

It will, of course, be understood that whenever the drive shaft 113 is rotated the ball clutch control shaft 141 is also rotated so that the ribs or ring fianges are rotating between the teeth of the pinion gear 156 (without, of course, turning the pinlon) The manner in which the shoe 23 is heated forms no part of the present'inventlon, and for that reason details of its construction are not shown. It will, of course, be understood that this shoe is heated preferably by suitable electric heating coils mounted therein and energized through a cable 116, which is connected through a switch 111 to a source of electric energy. A separate switch 112 is preferably provided for the motor 24.

The Operation of the lroning machine above described is relatively simple. The ironer is started by switching on the motor control switch 112 and the coil heating switch 111. The heated shoe 23 is in a position away from the padded roll 22. With the heated shoe 23 in this position, the eccentric 86 is in the position as shown in Figure 9. Assuming that the clothes or articles to be ironed are only moderately damp and that a high speed is desired, the control shaft 141 is moved to its innermost position by the knob 158. This forces the ball 154 up into the channel 151 of the gear 1 11. as shown in Figure 9, and thereby places the gear 111 in driving connection with the drive shaft 113, which is directly geared to the padded 'roll 22.

. Since the eccentric 86 is in its uppermost position, the control shaft 125 has been forced to 'its innermost position in the hollow shaft 15, and the jaw clutch teeth 123 are out of engagement with the :law clutch teeth 124. This, of course, means that the gear 121 is stationary, and the padded roll 22 is idle.

The article to be pressed is now laid on top of the padded roll 22, with a portion thereof slightly below the heated shoe 23. The finger-tip control lever 168 is depressed momentarily. This causes the eccentric 86 to be rotated 180 degrees in the manner previously described in detail. Rotation of the eccentric 86 causes theheated shoe 23 to be rocked forwardly into tight pressing engagement with the padded roll 22. It also causes the bulged-out portion of the cam plate 128 to be moved opposite the semi-spherical end 121 of the control shaft 125. Under the action of the spring 26, the sleeve bearing or bushing 122 r`is shifted axially along the hollow shaft 15, which causes engagement of the jaw clutch teeth 123 with the jaw clutch teeth 124. This causes a driving connection from the worm Wheel 14 through the transmission to the padded roll 22.

If it is desired to stop the rotation of the padded roll 22 `while the shoe 23 is still in tight engagement therewith, the control knob 158 .is'

moved to a position to cause the control shaft 141 to assume the position shown in Figure 10 of the drawings. In this position the ball clutch is in its neutral position, and both of the gears 116 and 111 are rotating idly on the drive shaft 113.

If it is desired to change from a high speed to a low speed of rotation of the padded roll 22, the control knob 158 is moved to a position to cause the control shaft 141 to assume the position shown in Figure 8 of the drawings. This causes the gear 116 to be operatively connected to the drive shaft 113.

Whenever it is desired to lift the heated shoe 23 from the padded roll 22, the finger-tip control lever 168 is momentarily depressed, and this causes the pawl clutch assembly to rotate 180 degrees, or until one of the end portions 166 or 161 of the clutch pawl lever arm 19 strikes the bent end portion 162 of the control finger 161. It will, of course, be remembered that every time the clutch pawl lever assembly rotates 180 degrees, the ecoentric 86 also rotates 180 degrees.

In Figures 13, 14, and 15 I have illustrated a modification of the gear-Shifting ball clutch assembly which is described in connection with the preferred embodiment of this invention. More specifieally, a .pair of plungers 113 and 114 are employed in place of the balls 153 and 154. The central portion of the control shaft 141 is cut back to form a flat bar portion 115. An intermediate shoulder 116 is cut into the bar portion in the same manner as the intermediate shoulder 143 is formed in the preferred embodiment of the invention. Two end shoulders 111 and 118 are provided by the upper edge of the bar portion 115 on either side of the intermediate shoulder 116. shoulders 111 and 118 are connected to shoulder 116 by a sloping side portion.

The plungers 113 and 114 are slotted out to enable them to be seated in straddling engagement over the bar portion 115 of the control shaft 141. The inner end of the slot formed in each of the plungers 113 and 114 has a fiat shoulder portion 119 and an inclined shoulder portion 186. A sectional view through plunger 114 is shown in Figure 19. The plunger 113 is the same as plunger 114, but With the inclined portion reversed with respect to the flat portion 119.

The flat portions 119 of each of the plungers 113 and 114 are arranged to be seated on one of the shoulders 116, 111, or 118, depending upon thel position of the control shaft 141 in the axial bore of the drive shaft 113. The inclined portions 1811 of the plungers 113 and 114 form a cam surface Which causes the plungers 113 and 114 to ride up and down the sloping connecting surfaces between shoulders 111 and 116, and 118 and 1 16. The ends of the plungers 113 and 114 are slightly tapered as at 181 to enable the partitions 152 to force the plungers tightly against the bar portion 115 of the control shaft 141.

Figure 14 ofthe drawings illustrates the speedchanging mechanism in its neutral position with both of the plungers 113 and 114 out of engagementwith the gears 116 and 111. Figure 13 of the drawings illustrates the low-speed gear in driving connection with the drive shaft 113. To place the high-speed gear 111 in driving connection with the drive shaft, the control shaft 141 is moved to its extreme inner position in the end of the drive shaft 113, thereby causing the plunger 114 to ride up onto shoulder 118 and plunger 113 to fall down onto the intermediate shoulder 116.

A further modifioation of the speed-changing mechanism is shown in Figures 16 and 1'1 of the asiaeaa drawings. In this case, a rocker arm |82 is empioyed having 'rounded or ball-likevends l83 and 184. This rocker arm l82 is preferably pivotally seated on a snap ring l93 which retains it l n desired position with respect to shaft MI. The rounded or ball-like'ends l83 and l8l correspond to the balls 153 and i54 of the first embodiment of the invention and to the plungers |`I3 and Ill of the second embodiment of the invention. The

-central portion of the control shaft MI includes a deep-cut portion IB5, two intermediate shoulders l86 and 181, which are connected to the deep-cut portion 185 by 'sloping surfaces, and two outer shoulder portions I 88 and i89, which are formed'by the outer surface of the control shaft Ill.

It will be noted that in this form of the invention an extra deep-cut central portion is necessary which does not appear in the form of the construction shown in Figure 6. This becomes necessary due to the fact that when one ball-like ure 16 of the drawings has the ban-uke end las on the upper shoulder l88, which places the low speed gear HG in driving connection with the drive shaft ll3. The opposite end of the rocker arm l82, namely, the ball-like end l84, is down in the.deep-cut central portion 185. In Figure 17 of the drawings, rocker arm l82 is in its neutral position, and bothof the gears HG and l.| 'I are free on the drive shaft il3. The highspeed gear Ill is placed in connection with the drive shaft ll3 by moving the control shaft to its innermost position in the end of the drive shaft li3, which cause'snthe ball-like end -IBI to ride up on the top shoulder l89.

While I have shown particular embodiments of my invention, it will, of course, be understood that I do not wish to be limited thereto, since many modifications may be made, and I therefore contemplate by the appended claims to cover all such modifications as fall within the true spirit and scope of my invention.

I claim as my invention:

rotatable roll, a heated shoe movable into ironing engagement'therewith, and driving means rotating said roll; a two-speed transmission comprising a support, a drive .shaft mounted on said `support and driven by said drivingV means, a

driven shaft mounted on said support and connected to drive said roll, a countershaft carried by said support, a set of of gears rotatably mounted on said driven shaft, a second set of gears integral with each other and rotatably and slid- .ably mounted on said countershaft complemenof gears andsaid worm wheel having mating jaw clutch teeth on opposed faces and disengageable upon sliding movement of said 'second set of gears on said countershaft, and ball clutch means between each of said first gears and said driven shaft for connecting one of said first gears in driving relation therewith, and means for selectively actuating said ball clutch means.

i 1. In an ironing machine of the type having a rotatable roll, a heated shoe movable into iron- 'ing engagement therewith, and driving means for rotating said roll; a two-speed transmissionl with each other and slidably mounted on said countershaft complementary to and meshed with said first set of gears, a worm Wheel rotatably mounted on said countershaft, said drive shaft including a worm meshed with said worm wheel, said second set of gears and said worm wheel having mating jaw clutch teeth on opposed faces and disengageable upon sliding movement of said second set of gears on -said countershaft, and means for selectively eonnecting one of said first set of gears to said driven shaft, thereby to drive said roll from said driving means at a selected speed depending upon which of said first gears is connected to said driven shaft. I

2. In an ironing machine of the type having a 3. A driving 'mechanlsxn for an .ironing vmachine which includesa support, a hollow shaft journaied in said support, a driving member rotatably mounted on saidshaft, a sleeve bearing axially movable on said shaft. a driven member mounted for rotation only on'said sleeve bearing, clutch means between said driving and driven members, a control shaft slidably carried in said hollow shaft and connected to said sleeve bearing, whereby upon` axialmovement of said control shaft said clutch means is disengaged, spring means on said hollow shaft-acting against said control shaft to urge said clutch means in operative engage'ment between said driving and driven members, and an eccentric mounted on said hollow shaft and secured thereto a cani plate secured to said eccentric and bearingV against the' free end'of `said .control shaft, said cam plate being shaped to force said control shaft to one extreme axial position when said eccentric is in one-position, and to fpermit said control shaft to be moved by saidvspring to its other extreme axial position upon rotation of said eccentric through .substantially 180 degrees, and clutch means for connecting said eccentric to said driv- 'ing member.

4. A' clutch assembly comprising. a shaft to be driven, -a ratchetwheel rotatably mounted on` said shaft, means for rotating said ratchet- Wheel, a pawl Supporting member mounted on and secured to said shaft, a pawl, a pin carried by said support substantially parallel to said shaft, said pawl being angularly movable on said pin into and out of ratchet engagement with said ratchet wheel, a pawl lever armV mounted on said pin and movable angularly ratchet wheel, and friction means for holding said pawl out of ratchet engagement with said i ratchet Wheel when said pawl lever arm has a pawl supporting member mounted on and se-' cured to said shaft, a pawl, a pin carried by said support substantially parallel to said shaft, said pawl being angularly movable on said pin into and out of ratchet engagement with said'ratchet Q wheel, a pawl level arm mounted on said pin and movable angularly thereon, said pawl 'havratchet engagement With said ratchet Wheel and upon engagement with the other of said spaced portions causing movement of said pawl out of ratchet engagement with said ratchet Wheel, and friction means for holding said pawl out of ratchet engagement With said ratchet Wheel when said pawl lever arm has moved said pawl to an unclutched position.

6. A clutch assembly comprising a shaft to be driven, a ratchet Wheel rotatably mounted on said shaft, means for rotating said ratchet Wheel, a pawl Supporting member mounted on and secured to said shaft, 'a pawl having a pair of spaced ears proiecting substantially parallel to said shaft, a pin carried by said support substantially parallel to said shaft, said pawl being mounted for limited rotational movement on said pin, a pawl lever arm extending between said ears, said lever arm being mounted on said pin for limited rotational movement, a spring normally urging said lever arm into engagement with one of said ears to move said pawl into ratchet engagement with said ratchet Wheel, said lever arm being movable against the action of said spring to engage the other of said ears and lift said pawl out of ratchet engagement.

7. A clutch assembly comprising la shaft to be driven, a ratchet Wheel rotatably mounted on said shaft, means for rotating said ratchet 0,,

Wheel, a pawl Supporting member mounted on and secured to said shaft, a pawl having a pair of spaced ears projecting substantially parallel to said shaft, a pin carried by said support substantially parallel to said shaft, said pawl being mounted for limited rotational movement on said pin, a pawl lever arm straddling said ratchet Wheel and extending between said ears, 'said lever arm being mounted on said pin and having relative movement with respect to said pawl between said ears, a spring normally urging said lever arm into engagement With one of said ears to move said pawl into ratchet engagement With said ratchet Wheel, said support, said lever arm, said pawl and said shaft beingr rotated with said ratchet Wheel when said pawl is in clutched engagement therewith, and a member movable into the path of movement of said lever arm as it rotates with said shaft, said member causing relative angular movement between said lever arm and said support, and Which movement of said lever arm with respect to said support lifts said pawl out of clutched engagement With said ratchet Wheel.

8. A clutch assembly comprising a shaft to be driven, a ratchet Wheel rotatably mounted on said shaft, means for rotating said ratchet Wheel, a pawl Supporting member mounted on and secured to said shaft, a pawl having a pair of spaced ears projecting substantially parallel to said shaft, a pin carried by said support substantially parallel to said shaft, said pawl being mounted for limited rotational movement on said pin, a pawl lever arm straddling said ratchet Wheel and extending between said ears, said levei` arm being mounted on said pin and having relative movement with respect to said pawl between said ears, a spring normally urgng said lever arm into engagement with one of said ears to move said pawl into ratchet engagement With said ratchet Wheel, said support, said lever arm, said pawl and said shaft being rotated with said ratchet Wheel When said pawl is in clutched engagement therewith, a member movable into the path of movement of said lever arm as it rotates with said shaft, said member causing relative langular movement between said lever arm and said support and Which movement of said lever arm with respect to said support lifts said pawl out of clutch/:d engagement With said ratchet Wheel, a spring washer mounted on said pin and holding said pawl and said 'lever arm frictionally against said support and against each other, and retaining means on said pin for holding said spring washer in desired position, the friction created by said spring washer being such as to hold said pawl out of ratchet engagement with said ratchet Wheel When said pawl lever arm has moved said pawl to an unclutched position.

i 9. A driving mechanism for an ironing machine which includes a support, a hollow shaft journaled in said support, a driving member rotatably mounted on said shaft, a sleeve bearing axiallymovable on said shaft, a driven member mounted for rotation only on said sleeve bearing, clutch means between said driving and driven members, acontrol shaft slidablycarried in said hollow shaft and connected to said sleeve bearing, Whereby upon axial movement of said control shaft said clutch means is disengaged, a ratchet Wheel connected to said driving mem'.;er for rotation therewith, a pawl Supporting member mounted on and secured to said hollow shaftv a pawl pivotally mounted on said support for angular movement into and out of ratchet engagement with said ratchet Wheel in a plane substantially perpendicular to said shaft, a pawl lever arm pivotally mounted on said support, said pawl having spaced portions engageable by said lever arm, said lever arm having relative movement with respect to said pawl between said spaced portions and upon engagement of one of said spaced portions causing movement of said pawl into ratchet engagement with said ratchet' Wheel and upon engagement with the other of said spaced portions causing movement of said pawl out of ratchet engagement with said ratchet Wheel, control means movable into the path of rotation of said lever arm as said lever arm rotates With 'said shaft, thereby causing angular movement of said lever arm With respect to said support to lift said pawl out of ratchet engagement With said ratchet Wheel, and cam means secured to said hollow shaft and engageable With said control shaft upon rotation of said hollow shaft to move said control shaft axially inwardly, thereby causing said clutch means between said driving and driven member to be disengaged.

10. A driving mechanism for an ironing machine which includes a support, a hollow shaft journaled in said support, a driving member rotatably mounted on said shaft, a sleeve bearing axially movable on said shaft, a driven member mounted for rotation only on said sleeve bearing, clutch means between said driving and driven members, a control shaft slidably carried in said hollow shaft and connected to said sleeve bearing, whereby upon axial movement of said conr`trol shaft said clutch means is disengaged, spring means on said hcllow'shaft acting against said control shaft to urge said clutch means into operative engagement between said driving and driven members, an eccentric mounted on said hollow shaft and secured thereto, a cam plate secured to said eccentric and bearing against the free end of said control shaft, said cam plate being shaped 'to force said control shaft to one extreme axial position when said eccentric is in one position and to permit said control shaft to be moved by said spring to its other extreme axial position upon rotation of said eccentrc through substantially 180 degrees, a ratchet Wheel connected to said driving member for rotation therewith, a pawl Supporting member mounted on and\secured to said hollow shaft, a pawl having a pair of spaced ears projecting substantially parallel to said Ihollow shaft, and pivotally mounted on said support for angular movement in a plane substantially perpendicular to said hollow shaft, a pawl lever arm pivotally mounted on said support extending between said ears, a spring extending between said lever arm and said support for normally urging said lever arm into engagement with one of said ears to move said pawl into ratchet engagement with said ratchet whel, and control means for causing said lever-farm to be moved against the action of said spring into engagement with the other of said ears to lift said pawl out of ratchet engagement, said cam plate being intermittently advanced through steps of 180 degrees, thereby to shift said clutch means into and out of driving connection between said driving and driven members.

LUTI-IER. RINGER.

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