US3107911A

US3107911A - Postage meter

Info

Publication number: US3107911A
Authority: US
Publication date: 1963-10-22
Anticipated expiration: 1980-10-22

Description

Oct. 22, 1963 Filed ma 11,' 1962 I. H. LUNDQUIST ETAL POSTAGE METER 4 Sheets-Sheet 1 IE'IE l Oct. 22, 1963 l. H. LUNDQUIST ETAL 3,107,911

' POSTAGE METER- Filed May 11, 1962 4 Sheets-Sheet 2 1953 l. H. LUNDQUIST ETAL' .POSTAGE METER 4 Sheets-sheaf. 3

Filed May 11, 1962 United States Patent 3,107,911 POSTAGE METER Ingemar H. Lundquist, Oakland, and Willy Schaerer and Charles S. Balaz, Hayward, Califl, assignors to Friden, Inc., a corporation of California Filed May 11, 1962, Ser. No. 194,124 14 Claims. (Cl. 271-3) This invention relates to mail treating machines and more particularly to the envelope feed mechanism therefor. y

In the use of a mail treating machine, mail matter such as envelopes are conveyed past a printing station for a metered postmark impression to be applied thereon. Where a considerable number of envelopes are to be processed, a stack of such envelopes is placed in a hopper on the machine and one-by-one the envelopes are separated from the stack for delivery to the printing station. Such machines must be adaptable to handle envelopes of various lengths and since those now in use are geared to separate and convey the short envelopes in an expeditious manner, the processing of the longer envelopes is much slower due to the additional time required to separate each of the longer envelopes from the stack. It is, therefore, an object of the present invention to provide a mail treating machine with an improved envelope feed mechanism whereby the speed of separation of each of the long envelopes is equivalent to that of each of the short envelopes.

Another object of the present invention is to provide an improved envelope feed mechanism for a mail treating machine by means of which the rate of separation of each envelope from a stack may be selectively controlled in accordance with the length of the envelope.

Another object of the present invention is to provide a mail treating machine with means for automatically controlling the rate of separation of each envelope from a stack as determined by the length of the envelopes.

A further object of the present invention is to provide a mail treating machine with an automatic speed control for the feeding of envelopes of various lengths regulated by the length of the envelopes.

Other objects and advantages will be apparent from the following description of a preferred embodiment as illustrated in the accompanying drawings in which:

FIG. 1 is a fragmentary elevational view of the front of the mail treating machine.

FIG. 2 is a fragmentary elevational view of the front of the mail treating machine complementary to FIG. 1 and having certain sections of the base portion broken away to show the speed control mechanism for the envelope feed device.

FIG. 3 is a fragmentary sectional plan view of the base portion of the machine showing the envelope feed mechanism and the speed control drive means therefor with the drive means adjusted for the slower speed, the view being taken on the plane indicated by line 33 in FIG. 2.

FIG. 4 is a fragmentary sectional end elevational View of the base portion of the machine showing the drive speed control mechanism for the envelope feed mechanism, the view being taken on the planes indicated by the lines 4-4 in FIG. 2.

FIG. 5 is a fragmentary sectional frontal elevational view of the base portion of the machine showing the adjustable device for controlling the speed of the envelope feed mechanism, the view being taken on the plane indicated by the line 5-5 in FIG. 4.

FIG. 6 is an enlarged plan view of the speed control mechanism and the adjustable means for enabling its operation, the view being taken on the planes indicated by the lines 6-6 in FIG. 2.

FIG. 7 is an enlarged sectional elevational view showing Patented Oct. 22, 1961s the pins associated with the larger of the driving pulleys and the spider selectively engageable therewith for controlling its operation, the view being taken on the planes indicated by the lines 7-7 in FIG. 6.

The invention is shown as being embodied in a mail treating, or postage metering, machine of the type disclosed in the application of Ingemar H. Lundquist, Serial No. 801,594, filed March 24, 1959, utilizing the workpiece feed mechanism of the type disclosed in Patent No. 3,074,532 issued to Charles S. Balaz, January 22, 1963.

As illustrated, the mail treating machine comprises base portion 10, portable meter unit 12, super-structure 14 and workpiece separating mechanism 16 (FIGS. 1 and 2). Within the base portion 10 is the power-drive means in the form of an electric motor (not shown) which serves to impart continuous movement to conveyer belt 20, as well as to provide motivity to all the operational mechanisms of the machine. The portable meter unit 12 is detachably mounted on the base portion 10 and includes the postage indicia printing drum 21 rotatably supported therein, which, upon securing meter unit 12 in position on base portion 10, is maintained in operative relation to conveyer belt 20. Following the securing of the meter unit 12 on the base portion 10, the operation of the meter unit, as well as the rotation of the indicia printing drum 21, is efiected in a well-known manner by a cyclically operable drive mechanism within the housing of superstructure 14. Also driven by the cyclically operable drive means is the auxiliary, or town circle, printing drum, generally indicated at 22, the rotation of which is in synchronism with that of the indicia printing drum 21 and in timed relation to the surface speed of the conveyer belt 20.

structurally, base portion 10 includes base plate 26, cover 27 and longitudinally extending

frame members

28, 29, 30 and 31 (FIGS. 2 and 3). Each of the

frame members

28, 30 and 31 is secured in position in any convenient manner between base plate 26 and the under side of the top surface of cover 27, while frame member 29 is secured to the base plate 26 and extends upwardly through a suitable aperture in cover 27. The extension of the frame member 29 above the cover is suificient to provide a support for the separator device 16 and to serve as a guide against which one edge of the envelopes 32 is maintained during the separation and feeding operation thereof. Edgewise uniformity of a stack of the envelopes 32 in hopper 33 is maintained by the laterally adjustable plate 34 which is adaptable to maintain one edge of the envelopes against guide plate 29.

In order to process the envelopes 32, they are removed one at a time from the hopper 33 and are fed in end-to-end fashion to conveyor belt 29' for a simultaneous impression by each of the printing drums 21 and 22. The removal of the envelopes from the stack is accomplished by means of the feed mechanism, generally indicated at 38 (FIGS. 2 and 3), in co-operation with the separator device 16. Thereafter, each envelope is moved into frictional engagement with the roller 39 of the auxiliary feed mechanism 40 (FIGS. 1 and 2), which is effective to continue the movement of the envelope into engagement with conveyer belt 20. Roller 39' is driven by endless belt 41 and roller 42, which roller 42 is driven frictionally by conveyer belt 20. The speed at which roller 39 is driven is greater than the surface speed of the similar spaced parallel belts 45 of the feed mechanism 38 and is less than the surface speed of conveyer belt 20. Thus, as each envelope is frictionally engaged by the roller 39, its movement is immediately accelerated until it becomes frictionally engaged with conveyer belt 20, whereupon its movement is accelerated still more, thereby effecting a spaced relationship between the trailing end of one envelope and the leading end of the adjacent envelope.

Upon placing the stack of envelopes 32 into the hopper 33 (FIG. 2), the forward, or leading, edge of each envelope in the upper portion of the stack abuts the cover of the conventional separator unit 16, while the leading edge of each envelope in the lower portion of the stack abuts the frictional wheels 46 of the separator 16. The leading edge of the lowermost envelope abutting the frictional wheels 46 is also in contact with the frictional surface of the pair of feed belts 45, which belts are continuously driven to successively effect a separation of the lowermost envelope from the stack of envelopes 32 and to feed the envelopes in end-to-end fashion along the top surface of the cover 27 of base portion 10. In order to ensure sufficient frictional contact of the leading edge of the lowermost envelope with the top surface of the belts 45, the stack of envelopes is positioned in the hopper 33 in angular relationship to the top surface of the cover 27. The degree of angularity of the stack of envelopes 32 relative to the top of the cover 27 is determined by the inclined plate 48 of the gauge 47, adjustably secured by means of the knurled nut and bolt 49 on the lateral extension of the substantially vertically disposed hand grip 50 secured at its lower end on the slide 51. Slide 51 is in a form substantially that of a channel having each flange thereof formed angular-1y inwardly in conformity with the chamfered edge of the corresponding one of a pair of similar bars 52 (FIGS. 3 and 4), upon which the slide 51 is slidably mounted. Bars 52 are preferably made of a thermoplastic material and are supported in parallel spaced relationship on the horizontally disposed plate 54 by any suitable means, such as a plurality of screws 53, plate 54 being suitably supported in any convenient manner between frame members 36 and 31 in parallel relationship to the top of cover 27. Thus, it can be seen that the plate 48 may be adjusted relative to separator unit 16 by moving slide 51 to the left or right (FIG. 2) on bars 52 to attain the required degree of angularity of the envelopes 32 in accordance with the variation in the lengths of the envelopes to be processed.

The continuously operable workpiece, or letter, feed mechanism for devices of the type described herein comprises the pair of similar endless belts 45, one of which is carried by a. pair of similar grooved pulleys 58 and 59 and the other of which is carried by a pair of similar grooved pulleys 60 and 61 (FIGS. 2 and 3). Pulleys 58 and 60 are coaxial and are secured in spaced relation on shaft 62 journalled in suitable bearings in

frame members

30 and 31. Similarly, pulleys 59 and 61, having a diameter equivalent to pulleys 58 and 60*, are secured in spaced relation on the inner end portion of shaft 63 which is suitably journalled in bearings in each of

frame members

30 and 31 in axial parallelism with shaft 62. The spacing between the pulleys 58 and 60 is equal to the spacing between pulleys 59 and 61, thereby providing a parallel relationship between the belts 4-5. As viewed from the right in FIG. 3, plleys 58 and 60 are axially displaced slightly to the right on shaft 62 out of alignment with the respective pulleys 59 and 61, thereby causing the parallel running belts 45 to run angularly inwardly toward the vertically disposed guide plate 29. Thus, it can be seen that upon clockwise rotation of the pulleys 59 and 61, as viewed from below in FIG. 3, and upon the frictional engagement of the lowermost envelope of the stack of envelopes 32 with the belts 45, the one edge of the lowermost envelope will be retained in engagement with the vertical wall of guide plate 29, thereby ensuring true alignment of the envelopes as they move in the feed path toward the printing station.

In addition to supplying power to the conveyer belt 20 and the cyclically operable drive mechanism for the indicia printing drum 21 and auxiliary printing drum 2-2, the electric motor (not shown) also serves to selectively drive the endless feed belts 45 at either of two selective speeds. Power is transmitted from the motor to the endless belts 45 by means of drive shaft 68 (FiG. 3) and intermediate drive shaft 69, which serves to selectively impart rotation to shaft 63 (FIGS. 2, 3, 4 and 6) by means of either toothed pulley 7t), timing belt 71 and toothed pulley 72,

or by means. of toothed pulley 73, timing belt 74 and toothed pulley 75. Drive shaft 68 is journalled along its length in suitable hearings in brackets 76 and 77 supported between

frame members

28 and 29 and, adjacent its end, is adequately supported in spaced parallel cars 78 of a bracket 79 secured on plate 80 supported between brackets 77 and 81. Shaft 69 is suitably journalled, adiacent one end, in a bearing in frame member 3 1 and, adjacent its other end, in a bushing in bracket 79', the shaft rotating freely in enlarged openings in

frame members

29 and 30 and plate 80. Continuous rotation of shaft 68 is transmitted to shaft 69 by means of the worm and worm 7 gear unit, generally indicated at 82, the worm being secured on shaft 68 between cars 78 of bracket 79, and the worm gear, enmeshed therewith, being secured on the end of shaft 69. Each of the

toothed pulleys

70 and 73 is freely mounted in spaced relationship on the other end of shaft 69, while the corresponding toothed pulleys 72. and

'75 are secured in a similar spaced relationship on the outer end of shaft 63. Normally, therefore, continuous rotation of shaft 69 is not imparted to shaft 63, but may be selectively utilized to eifect operation of the endless belts 45, as will now be described. 7

In mail treating machines now in use and of the type in which the present invention is embodied, the workpiece, or envelope, feed mechanism operates at one speed, the maximum speed which is most satisfactory for the expeditious handling of short envelopes. When envelopes of a longer dimension are to be processed, the time involved in the separation of the envelopes from the stack becomes proportionately greater with the length of the envelope. In order to efiiciently handle the separation of envelopes, irrespective of the length of the envelopes to be processed, the speed of the endless feed belts 45 is selectively controlled.

For this purpose, the normal speed of the feed belts 45, i.e., the speed required for the efiicient separation of the short envelopes from the stack, is controlled by the selective connection of the toothed pulley 70 with shaft 69, the pitch diameter of the pulley 70 being equivalent to that of the corresponding toothed pulley 72 (FIGS. 2, 4 and 6). For the separation of each envelope from a stack of longer envelopes, the speed of the endless belts 45 is increased under the control of toothed pulley 73, the pitch diameter of which is greater than that of the corresponding toothed pulley 75. The pitch diameter of

pulleys

70, 72 and 75 is identical. It becomes apparent, therefore, that shaft 63, when driven by pulley 70, belt 71 and pulley 72, will rotate at the same speed as shaft 69. However, if the rotation of the shaft 63 is under the control of pulley 73, belt 74 and pulley 75, its speed will be greater than that of drive shaft 69.

As stated hereinbefore, the toothed pulleys 70 and 73 are freely mounted on shaft 69 and each is provided with a pair of

disks

90, 91 and 92, 93, respectively, one for each side of, and secured on, the corresponding pulley. The diameter of each pair of

disks

90, 91 and 92, 93 is sufficiently greater than the outside diameter of the corresponding pulley to maintain the associated

belts

71 and 74 in driving position on the pulleys. Pulley 73 is positioned on shaft 69 adjacent the face of frame member 31 and is held against axial displacement by means of an E ring, or clip, engaged in an annular groove in the shaft. Similarly, pulley 70 is positioned on shaft 69, in spaced relationship to pulley 73, and is held against axial dis,- placement on shaft 69 by means of a pair of similar E rings, or clips engaged in corresponding annular grooves in the shaft.

Either pulley 70' or 73 (FIGS. 4, 6 and 7) may be of three equiangularly spaced pins 94 carried by disk 91 and projecting axially parallel to the shaft 69. Similarly, toothed pulley 73 is provided with a series of three equiangularly spaced pins 95 carried by disk 92 and project ing axially parallel to shaft 69 and in opposition to the series of pins 94 on pulley 70. Each series of pins 94 and 95 is disposed on the same radius and is adaptable, respectively, for selective engagement by a clutch, generally indicated at 96, axially slidable upon shaft 69 between toothed

pulleys

70 and 73. Clutch 96 comprises a hub 100 on one end of which a spider 101 is secured and on the other end of which a similar spider -2 is secured in parallel relationship to spider 101 (FIGS. 3, 4, 6 and 7). The three radially disposed arms of each

spider

101 and 102 are equiangularly spaced and are adapted for engagement with the corresponding pins 94 on pulley 70 or pins 95 on pulley 73, upon axial movement of clutch 96 to the right or left, as viewed in FIG. 4. In order to efifect rotation of either

pulley

70 or 73, following the engagement of the arms of

spiders

101 or 102 with the respective pins 94 or 95, hub 100 is provided with a pair of diametrically opposed axially parallel keyways which are slida'bly engaged with the respective extended ends of a diametrically disposed pin 103 in shaft 69.

The overall width, or axial length, of clutch 96 is less than the distance between the opposed ends of the series of pins 94 and 95 so that, when the clutch is positioned in the area between the pins 94 and 95 (FIG. 6), rotation of shaft 69 is ineffective to drive either

pulley

70 or 73. Normally, clutch 96 is maintained in this, the inactive position, by means of a manually controlled button 106 (FIGS. 2, 3, 6 and 7) rockable about a vertically disposed pin 107 carried by a boss 108 integrally for-med on base plate 26. The face of the control button 106 projects through a suitable aperture in cover 27 so that it may be easily rocked from the active position shown in FIG. 6 to the inactive position shown in FIG. 3. Button 106 is resiliently retained in either of its two positions by means of a toggle spring 109.

Upon rocking control button 106 counter-clockwise to the position shown in FIG. 6, a hook portion 110, integrally formed on button 106, engages a roller 111 secured on the free end of one horizontally disposed arm 112 of a bellcrank 115 pivotally mounted on a shoulder screw 116 threaded into a boss 117 integrally formed on base plate 26 (FIG. 7). In this position of the button 106, a distention 118 (FIGS. 6 and 7), arcuately formed on each edge of the arm 112 intermediate its length and lying between the

spiders

101 and 102 of the clutch 96 adjacent the peripheral surface of the hub 100, enables bellcrank 115 to maintain the clutch in its normally inactive position. To ensure positive adjustment of the clutch 96, an arm 119 extends horizontally in spaced parallel relationship to arm 112 integrally connected by web portion 120 to bellcrank 115. At its extremity, the arm 119 is provided with a substantially circular end portion 121 lying between

spiders

101 and 102 adjacent the peripheral surface of the hub 100 of clutch 96 and in diametrical opposition to the distention 118 of arm 112.

The adjustment of the clutch 96 to either of its two active positions becomes automatic upon adjustment of the adjustable gauge 47 for the proper angular disposition of a stack of envelopes 32 within hopper 33, as determined by the length of the envelopes. It will be recalled that such angular disposition of the envelopes in the hopper 33 is necessary for the separation of the envelopes one-by-one from the stack, upon operation of endless feed belts 45. For what is preferably to be considered the normal speed of operation of the endless feed belts 45, i.e., for the separation and feeding of short envelopes, the gauge 47 is adjusted to the position shown in FIG. 2, adjusting slide 51 to the position indicated in H6. 5, whereupon clutch 96 is moved to the active position shown in FIG. 4 to effect engagement of the arms 6 of spider 101 with pins 94 on toothed pulley 70. An angle member, or actuator, 125 is welded or otherwise secured on the lower surface and along substantially the longitudinal center line of the channel slide 51, movable with the adjustment of the slide in the space between the parallel bars 52 (FIGS. 4 and 5).

Upon adjustment of the gauge 47, the angle member, or actuator, 125 serves to control the selective adjustment of the clutch 96. For this purpose, a 'bellcrank 126 (FIGS. 4, 5 and 6) is rockably mounted on a shaft 127 which is supported at its ends in

frame members

30 and 31. At its extremity, one arm of bellcrank 126 carries a roller 128 adapted for rolling contact with the lower edge of the vertically disposed leg of angle member 125, while the other arm of bellcrank 126, at its free end, pivotally supports one end of a link 129 at 130. Link 129 extends horizontally and, at its other end, is pivotally supported on a pin 131 secured on the depending arm 132 of a bellcrank 133 roc-kably mounted on a shaft 134 supported at its respective ends in

frame members

30 and 31 axially parallel with shaft 127. An aperture in the other arm of ibellcrank 133', adjacent the end thereof, provides support for one end of a relatively strong spring 135 which is secured at its other end on a pin 136 on auxiliary transverse frame member 137 secured in any convenient manner between

frame members

30 and 31. spring 135 serves to urge bellcranks 133 and 126 in a clockwise direction to maintain roller 128 in contact with the lower edge of the vertical leg of angle member 125.

The rocking movement of the

bellcranks

126 and 133, under control of the actuator 125, normally serves to control the rocking movement of the bellcrank 115 and the active adjustment of clutch 96 (FIGS. 5, 6 and 7). To this end, arm 132 of bellcrank 133 is provided, at its lower extremity, with a pair of opposed arcuately formed lateral projections normally, respectively, engaged with the laterally extended

ears

138 and 139, of the respective depending arms and 141 of a scissors-type actuator, generally indicated at 1 42.

Arms

140 and 141 are rockably mounted upon shaft 134, contiguous with each other and with bellcrank 133, serving, upon rocking movement of bellcrank 133, to control the rocking movement of bellcrank 115 and the adjustment of clutch 96. For this purpose, a relatively light spring 145, secured at its respective ends on

ears

138 and 139 of respective arms 149 and 141, normally serves to maintain the

ears

138 and 139 in engagement with the respective projections on the lower end of arm 132 of bellcrank 133. At the same time, the inner parallel edge surfaces 147 and 148 of

respective arms

140 and 141 are maintained in'engagement with the parallel edge surfaces of the end portion of the horizontally disposed arm 146 formed at a right angle to am 112 of bellcrank 115. It is to be noted that spring 145 provides a yieldable connection betwee

arms

140 and 141 and bellcrank 115.

Referring to FIGS. 3 and 5, with the control button 106 rocked clockwise to the inactive position shown in FIG. 3 and upon adjustment of the gauge 47 for the processing of short envelopes, slide 51 will be adjusted to the position shown in FIG. 5, wherein spring 135 urges bellcrank 126 clockwise as the roller 128 moves upwardly along the beveled end surface of the vertically disposed leg of the angle 125 Accordingly, bellcra'nk 133 is effective to rock depending arm 140 clockwise which, through spring 145, causes depending arm 141 to follow, thereby rocking bellcrank 1'15 (counter-clockwise in FIG. 3) to engage spider 101 of clutch 96 with pins 94 on toothed pulley 70. Thus, the endless belts 45 will be driven at a speed suitable for the eflicient separation and feeding 7 7, whereupon bellcrank 1 15 is cammed in a clockwise direction to position clutch 96 intermediate pins 94 and 95. 'Ihereupon, arm 141 of the scissors-type actuator 142 will be rocked counter-clockwise (FIGS. and 7) causing spring 145 to yield, spring 135 overcoming spring 145.

For the separation and feeding of the longer envelopes, gauge 47 and, therefore, slide 51 (FIGS. 2 and 5) are moved to the left, whereupon angle member 125 becomes efiective to rock :

bellcranks

126 and 133 counter-clockwise against the urgency of the spring 135. As bellcrank 133 is rocked counter-clockwise, a similar rocking movement is imparted to the depending arm 141 which, through spring 145, causes a similar rocking movement of the arm 140 of the scissors-type actuator 142, when control button 106 is in the inactive position shown in FIG. 3. Such movement of

arms

141 and 140 causes bellcrank 115 to be rocked clockwise (FIG. 3) to engage the spider 102 of the clutch 96 with pins 95 on the larger toothed pulley 73. Thereafter, the rotation of drive shaft 69 causes feed belts 45 to be driven at an accelerated speed. The termination of the processing operation for the longer envelopes is similar to that for the short envelopes except that, upon rocking movement of the control button 106 to the active position shown in FIG. 6, the depending arm 140 (-FIG. 5) is rocked clockwise, .tensioning spring 145. If, after the termination of an operation it becomes desirable to again initiate processing of the long or short envelopes, control button 106 is rocked clockwise from the position shown in FIG. 6 to the inactive position, whereupon spring 145 becomes effective to restore either the yieldable arm 140 or arm 141 to its active position, thereby adjusting clutch 96 in accordance with the setting of the adjustable gauge 47. If, upon initiation of a separating and feeding operation for the short or long envelopes, clutch 96 should be out of phase with either pins 94 on pulley 70 or pins 95 on pulley 73, the radial arms of spider 10 1 or 10-2 will engage the ends of the corresponding pins 94 or 95 and spring 145 on the scissors-type actuator 142 will yield. However, following a sufficient rotation of drive shaft 69 and clutch 96, tensioned spring 145 will cause the radial arms of either

spider

101 or 102 to be moved into active engagement with the corresponding pins 94 or 95.

We claim:

1. In a workpiece separating and forwarding mechanism, a hopper for the storage of a stack of workpieces, means for feeding the workpieces singly from said hopper, a pair of normally inactive driving means selectively operable to drive said feeding means at either of two rates of speed, a power driven means adjustable for selec tive engagement with either of said pair of driving means to control the operation thereof, a manually controlled means settable to bias said power driven means into engagement with one or the other of said driving means, and a manipulable means operable to effect a disengagement of said power driven means from either of said driving means irrespective of the setting of said settable means thereby terminating operation of said feeding means.

2. In a workpiece separating and forwarding mechanism, a feeding means for the workpieces, a separating abutment means associated with said feeding means for co-operation therewith to restrict the feeding to single workpieces from a stack of workpieces, a plurality of driving means for said feeding means selectively operable to control the rate of speed of said feeding means, a continuously operable power driven means including a clutch adjustable for selective engagement with each of said plurality of driving means to control the speed of operation of said feeding means, and means settable to each of a plurality of positions to control the selective adjustment of said clutch.

3. In a workpiece separating and forwarding mechanism, a hopper for the storage of a stack of workpieces of one of each of a plurality of lengths, means for feeding the workpieces from said hopper, a separating abutment means associated with said feeding means for cooperation therewith to restrict the feeding to single workpieces from the stack of workpieces, means adjustable in accordance with the length of the workpieces to maintain a uniform stack of workpieces in said hopper, a plurality of normally inactive means selectively operable to control the speed of operation of said feeding means, a continuously operable drive means, a clutch driven by said drive means engageable selectively with one of each of said plurality of control means to drive said feeding means, means controlled by said adjustable means upon adjustment thereof for effecting engagement of said clutch, and a manually settable means for controlling operation of said controlled means to effect disengagement of said clutch irrespective of the adjustment of said adjustable means thereby terminating operation of said feeding means.

4. In a workpiece separating and forwarding mechanism, a hopper for the storage of a stack of workpieces, means for feeding the workpieces from said hopper, a separating abutment means associated with said feeding means for co-operation therewith to restrict the feeding to single workpieces from the stack of workpieces, means adjustable relative to said separating abutment means for maintaining a uniform stack of workpieces in said hopper and for maintaining the lowermost workpiece in the stack in feed relationship to said feeding means, a plurality of driving means, each operable selectively to control the speed of operation of said feeding means, a source of power, and means driven by said source of power adjustable by said adjustable means for engagement selectively with one of each of said driving means to control the rate of feed of said feeding means.

5. In a workpiece separating and forwarding mechanism, a hopper for the storage of a stack of workpieces of one of each of a plurality of lengths, a variable speed means for feeding the workpieces from said hopper, a

separating abutment means associated with said feed means for cooperation therewith to restrict the feeding to the successive lowermost workpiece from the stack of workpieces, means settable in each of a plurality of positions relative to said separating abutment means and in accordance with the length of the workpieces in said hopper to maintain the lowermost workpiece in the stack in feed relationship to said :feed means, a plurality of driving means for said feed means, each of said driving means being selectively operable to control a different speed of operation of said feed means, a power operated means, means driven by said power operated means adjustable to selectively control the operation of each of said driving means, and means actuated by said settable means upon movement to each set position thereof to control the adjustment of said adjustable means.

6. In a mail treating machine having a hopper for the storage of a stack of envelopes of one of each of various lengths, means for feeding the envelopes from said hopper, a separating abutment means associated with said feeding means for co-operation therewith to restrict the feeding to single envelopes from the stack of envelopes, means manually adjustable relative to said separating means in acordance with the length of the envelopes in said hopper to maintain each successive envelope to be fed in frictional engagement with said feeding means, a power driven means, and a variable speed drive mechanism for controlling a selective rate of speed of said feeding means in accordance with the length of the en- .velopes in said hopper, the combination comprising a plurality of independent drive means for said feeding means, each of said drive means being connectable selectively with said power driven means and operable upon operation thereof to effect a different rate of speed of operation of said feeding means, and means settable by said manually adjustable means for effecting a con- 9 nection between said power driven means and each of said drive means to enable operation of a selected one of said plurality of drive means as determined by the adjustment of said adjustable means.

7. In a mail treating machine having means for controlling the successive feeding of envelopes, a power driven means, and a variable speed control mechanism interposed between said power driven means and said feeding means to regulate the speed of operation of said feeding means, the combination comprising a plurality of selective drive means, each operable upon selection thereof to drive said feeding means at a dilferent rate of speed, means driven by said power driven means connectable selectively with one of said drive means, a manually adjustable means, means controlled by said manually adjustable means operable to bias said connectable means into operative relation with a selected one of said drive means, and a manually settable means adjustable from an inactive to an active position to disable said biasing means disconnecting said connectable means thereby terminating operation of said feeding means.

8. In a mail treating machine having a hopper for the storage of a stack of envelopes of one of each of various lengths, endless belt means for feeding the envelopes from said hopper, a separating abutment means associated with said endless belt means for co-operation therewith to restrict the feeding to single envelopes from the stack of envelopes, a gauge adjustable relative to said separating means in accordance with the length of the envelopes in said hopper to maintain each successive envelope to be fed in frictional engagement with said endless belt means a continuously operable drive means for said endless belt means, and a variable speed mechanism interposed between said drive means and said endless belt means for regualting the speed of operation of said endless belt means, the combination comprising a plurality of power transmission means, each operable selectively to drive said endlessbelt means at a different rate of speed in accordance with the length of the envelopes in said hopper, means driven by said drive means adjustable for driving engagement selectively with each of said power transmission means, engaging means for effecting the engagement of said driven means with one of said power transmission means, and means settable by said gauge for controlling the operation of said engaging means in accordance with the adjustment of said gauge.

9. In a mail treating machine having a hopper for the storage of a stack of envelopes of either of two lengths, an endless feed belt for feeding the envelopes from said hopper, a separating abutment means associated with said endless belt for co-operation therewith to restrict the feeding to single envelopes from a stack of envelopes, a gauge manually adjustable relative to said separating means in accordance with the length of the envelopes in said hopper to maintain each successive envelope to be fed in frictional engagement with said endless belt, a continuously operable drive means including a shaft, and a variable speed control mechanism for controlling operation of said endless belt, the combination comprising a pair of power transmission means, each selectively operable to drive said endless belt at a different rate of speed, a clutch means supported on said shaft and adjustable for driving engagement with either of said power transmission means to effect operation thereof by said drive means, means associated with said clutch means rockable to either of two positions to control the adjustment of said clutch means, and means settable by said gauge upon each adjustment thereof effective to control the positioning of said rockable means.

10. In a device of the character described in claim 9', said power transmission means comprising a pair of similar driven means associated with said endless belt in spaced relationship for enabling the operation of said belt and a pair of driving means freely mounted for in dependent actuation on said shaft and spaced thereon in accordance with the spacing between said driven means for controlling operation of said driven means, one of said driving means being operable upon engagement of said clutch means therewith to drive the corresponding one of said driven means at a given speed and the other of said driving means being operable upon engagement of said clutch means therewith to drive the other of said driven means at a greater speed.

'11. In a device of the character described in claim 10, wherein each of said driving means includes a similar series of pins secured in eq-uiangularly spaced relationship thereon axially parallel to said shaft'and in opposition, one series to the other for selective driving engagement by said clutch means.

12. In a device of the character described in claim 11, said clutch means comprising a member keyed for axial sliding movement on said shaft between each of said i riving means, and a pair of spiders secured in space-d relationship on said member for sliding movement therewith and positionable between the opposed ends of said pins on each of said driving means, each of said spiders including a series of radially disposed arms adapted for engagement with the series of pins on the corresponding one of said driving means upon adjustment of said memher by said rockable means.

13. In a device of the character described in claim 12, including a manually operable means selectively adjust,- able from an inactive to an active position to rock the rockable means for controlling the sliding movement of said member and the inactive positioning of said spiders relative to the series of pins on each of said driving means irrespective of the setting of said settable means by said gauge, thereby terminating operation of said driving means.

14. In a device ofthe character described in claim 13,

means to the active position to enable the inactive positioning of said member in either adjusted position of said gauge.

No references cited.

Claims

1. IN A WORKPIECE SEPARATING AND FORWARDING MECHANISM, A HOPPER FOR THE STORAGE OF A STACK OF WORKPIECES, MEANS FOR FEEDING THE WORKPIECES SINGLY FROM SAID HOPPER, A PAIR OF NORMALLY INACTIVE DRIVING MEANS SELECTIVELY OPERABLE TO DRIVE SAID FEEDING MEANS AT EITHER OF TWO RATES OF SPEED, A POWER DRIVEN MEANS ADJUSTABLE FOR SELECTIVE ENGAGEMENT WITH EITHER OF SAID PAIR OF DRIVING MEANS TO CONTROL THE OPERATION THEREOF, A MANUALLY CONTROLLED