US3159099A - Fluid pulsing means for print hammers - Google Patents

Fluid pulsing means for print hammers Download PDF

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Publication number
US3159099A
US3159099A US131911A US13191161A US3159099A US 3159099 A US3159099 A US 3159099A US 131911 A US131911 A US 131911A US 13191161 A US13191161 A US 13191161A US 3159099 A US3159099 A US 3159099A
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United States
Prior art keywords
chamber
fluid
volume
piston
pressure
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Expired - Lifetime
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US131911A
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English (en)
Inventor
Wadey Walter Geoffrey
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Unisys Corp
Original Assignee
Sperry Rand Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to BE620847D priority Critical patent/BE620847A/xx
Priority to NL282126D priority patent/NL282126A/xx
Application filed by Sperry Rand Corp filed Critical Sperry Rand Corp
Priority to US131911A priority patent/US3159099A/en
Priority to GB28535/62A priority patent/GB944687A/en
Priority to CH934362A priority patent/CH400200A/de
Application granted granted Critical
Publication of US3159099A publication Critical patent/US3159099A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41J—TYPEWRITERS; SELECTIVE PRINTING MECHANISMS, i.e. MECHANISMS PRINTING OTHERWISE THAN FROM A FORME; CORRECTION OF TYPOGRAPHICAL ERRORS
    • B41J23/00—Power drives for actions or mechanisms
    • B41J23/20—Fluid-pressure power drives
    • B41J23/24—Fluid-pressure power drives for impression mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41J—TYPEWRITERS; SELECTIVE PRINTING MECHANISMS, i.e. MECHANISMS PRINTING OTHERWISE THAN FROM A FORME; CORRECTION OF TYPOGRAPHICAL ERRORS
    • B41J9/00—Hammer-impression mechanisms
    • B41J9/16—Means for cocking or resetting hammers
    • B41J9/22—Fluid-pressure means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41J—TYPEWRITERS; SELECTIVE PRINTING MECHANISMS, i.e. MECHANISMS PRINTING OTHERWISE THAN FROM A FORME; CORRECTION OF TYPOGRAPHICAL ERRORS
    • B41J9/00—Hammer-impression mechanisms
    • B41J9/26—Means for operating hammers to effect impression
    • B41J9/34—Fluid-pressure means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
    • F15B2211/8855—Compressible fluids, e.g. specific to pneumatics

Definitions

  • the present invention relates to apparatus for,converting energy of relatively long duration into impulse energy of relatively short duration, and more particularly, to a fluid variable linkage mechanism for actuating the print hammer in a print in a mechanism.
  • variable mechanical linkage there are several types of variable mechanical linkage in existence which, by uncoupling, convert the energy of a moving mass to an impact force.
  • One familiar example is the typical piano or typewriter linkage whereby, after pressing the key for a certain distance, momentum is thereby imparted to the linkage which is eventually transferred to the hammer.
  • the wear and tear upon the moving contact surfaces therein causes the relatively early deterioration of the component parts.
  • the present invention obviates the above diiculties by providing means of imparting ever increasing momentum to a mass over a relatively long period of time, after which the mechanical advantage of the system changes to uncouple the mass in motion from its source of momentum and allow it to transfer its energy by an impulse force.
  • the invention is particularly adapted for use in the newly developing iield of pneumatic data processing systems where it finds direct application in printing mechanisms and the like.
  • Another object of the present invention is to provide apparatus whereby the momentum or a moving mass may be imparted to another movable mass as an impulse force without the need of a mechanical linkage therebetween.
  • Another object of the present invention is to provide apparatus whereby the energy in a low pressure pulse of relatively long duration may be converted into a high pressure pulse of relatively short duration.
  • a further object of the present invention is to provide a printing mechanism having a print hammer actuated by momentum exchange in which only one moving part is ⁇ required.
  • Another object of the present invention is to provide printing mechanism whereby a low pressure i'luid pulse of relatively long duration may be used to rapidly impart momentum to a print hammer therein.
  • FIGURE l discloses the invention in a printing mechanism environment.
  • FIGURE 2a discloses a pictorial cross-sectional View of the present invention.
  • FIGURE 2b discloses a cross-sectional elevation view of the present invention.
  • FIGURE 3 is a graph showing volume and pressure relationships in the present invention.
  • FIGURE 4 discloses the sequence of operations occurring in the present invention.
  • FIGURE 1 shows the invention being employed in a printing mechanism for actuating the print hammer, wherein pulses of fluid energy are utilized to impart momentum to only one moving part other than said hammer.
  • the numeral 10 generally indicates a housing having a number of passageways 141 through 14N in which are slidably disposed respective plungers 121 through 12N. Connected to one end of each plunger and exterior to housing 1G is a print hammer 161 through 16N. Each plunger 12 is normally retracted into housing 10 within its associated passageway 14 unless it is desired to print a character in the associated column on a print receiving member 18.
  • the type font for each print column may be placed around the periphery of a rotating print drum 2e journaled on spindle 22 such as is shown in FEGURE l. Alternatively, each type font may be positioned on an individual type wheel.
  • each type character is moved in succession adjacent to the print receiving member 18.
  • a plunger 12 is forced outwardly from housing 1G at high speed such that its print hammer 16 drives print receiving member 18 against the type character to leave an impression thereon.
  • the print hammer 16 rebounds from the impact with the type character and is repositioned within passageway 14.
  • T he means for actuating plunger 12 comprises the invention disclosed herein.
  • housingl Within housingl are disposed a plurality of chambers 261 through 26N, each having one end connected with an associated passageway 141 through 14N.
  • a piston member 2S Slidably disposed within a chamber 26 is a piston member 2S having end limits of travel between the two ends of the chamber.
  • a port 32 At the opposite end of chamber 26 from passageway 14 is a port 32 connected exterior to housing 19 with a conduit 34.
  • Each conduit is connected toa control pressure source 36, whereby a uid pulse of relatively long duration may be applied therethrough tolchamber 26.
  • Each piston member 28 may be fitted with an elastomer O-ring 30 or some other suitable seal, which prevents the leakage of iiuid from port 32 into the charnber volume ahead of said piston.
  • chamber 26 can be considered as divided into two regions 38 and 49 respectively forward and aft of seal 3Q, whose volumes vary as piston 28 moves.
  • FIGURES 2a and 2b respectively show pictorial and side elevation views in section of the invention.
  • chamber 26 is elongated and in the preferred embodiment has a circular cross section.
  • Piston 2S fits snugly within chamber 26 and may be provided with the O-seal 3i) in order to isolate the two volumes 38 and 4t) one from another.
  • the front of piston 28 may be streamlined by'shaping it in the form of an ogive 29. It the piston is so streamlined, then the lfront end 27 of chamber 26 should be complementarily shaped such that the piston front end and the chamber front end will t snugly together to a substantial degree.
  • Passageway 14 opens into the front end 27 of chamber 26 such that the pressure existing in volume 3S can be applied against one end of plunger 12 slidably disposed therein.
  • FIGURE 2b and FIGURE 3 the general principle behind the operation of the invention will be described.
  • the volume of chamber 26 is divided into two regions 38 and 40 which are respectively in front of and behind piston 2%. These two volumes are sealed from each other by means of the O-ring 30 or the like.
  • volume 38 is relatively large compared with volume 46.
  • volume E58 becomes progressively smaller while volume l increases in magnitude.
  • Volume 38 decreases in linear fashion as piston 28 travels toward end 27 of chamber 26 which is illustrated in FIGURE 3 by dotted line A under the assumption that the shapes of the piston front end 29 and chamber end 27 are such that volume 38 is substantially equal to Zero when piston 28 is in its extreme right hand position.
  • Boyles law the volume occupied by an ideal compressible fluid varies inversely as its absolute pressure assuming that its temperature remains constant, Boyles law may be expressed as follows:
  • volume 38 has a value substantially equal to zero when piston 28 is in its extreme right hand position, i.e., adjacent end 27 of chamber 26, it will be seen from FIGURE 3 that the piston travels three-fourths of its total travel, beginning at point I with the volume 38 pressure only being increased by a multiple of four. At this time, piston 28 is in a position indicated by III. Upon piston 28 moving from position III to position IV, which yis but one-eighth the total distance between its limits of travel, the volume 38 pressure becomes eight times its value at position I. Upon piston 28 reaching point V from point IV, which is one-sixteenth the total travel, the volume 38 pressure becomes sixteen times its value at position I. Therefore, the rate of change in the pressure of volume 38 increases as piston 28 moves to reduce said volume, although the rate of change of volume 38 remains constant with respect to piston position.
  • volume 38 As Volume 38 is reduced its pressure increases which thus diminishes the value of the unbalanced force acting on piston 28 and consequently reduces its acceleration.
  • the pressure of volume 38 When the pressure of volume 38 is finally equal to the pressure in volume 40, neglecting any effects of friction, there is no unbalanced force acting on piston 28 and thus no change in its velocity or momentum.
  • piston 28 Because it now possesses momentum, piston 28 continues to move towards its right-most position thus reducing volume 38 even further and consequently increasing the pressure therein. Since this pressure now rises above the pressure in volume 40, an unbalanced force is applied to piston 28 in a direction opposing its motion, which thereby produces a deacceleration effect. At this time, thevelocity and momentum of piston 28 begins to decrease until eventually the piston is stopped.
  • FIGURE 3 The above described action is illustrated in FIGURE 3.
  • the pressure existing in volume 38 is that represented by curve C. This pressure may be made as small as desired.
  • the pressure of the uid applied to volume 40 is represented by line B which is considered to apply a force to piston 28 in a direction opposite to the force applied by pressure C. It the input pressure B is higher than pressure C existing in volume 38 at position I, the resultant unbalanced pressure acting on piston 28 has a value indicated by curve D in FIGURE 3. This unbalanced pressure D creates an unbalanced force which causes piston 28 to move from its left most position I towards its right most position.
  • piston 28 no longer accelerates but instead maintains the velocity and momentum imparted to it by this time. However, because of this momentum the piston continues to move toward its right most position which consequently reduces volume 38 even more ⁇ and further increases pressure C. The resultant pressure thereby becomes negative and acts as an ever increasing unbalanced force on piston 28 in a direction to oppose its motion. Piston 28 isthereby brought to a rapid halt near or at the end of its right most travel at the time when volume 38 becomes quite small and its pressure quite large.
  • plunger 12 In order to impart velocity and consequently momentum to plunger 12 in a direction away from chamber 26, there must be an unbalanced force acting thereon. Normally, plunger 12 may be maintained in its retracted position by'using either the external environmental pressure or by physical restraining means such as spring tension, etc. When the force exerted by the pressure C upon plunger 12 is less than this restraining force, plunger 12 will remain in its retracted position. However, upon pressure C becoming large enough, the resulting unbalanced force on plunger 12 causes it to accelerate in a direction away from end 27 of chamber 26. This acceleration depends upon the magnitude of the unbalanced force and thus upon the magnitude of pressure C in reduced volume 38.
  • the energy contained in a relatively low pressure fluid pulse of long duration is imparted to a mass in the form of a relatively high energy pulse of short duration without need for any mechanical linkage.
  • This invention is therefore particularly adapted for use with data processing equipment where information is transmitted by means of fluid pulses.
  • the pressure of the input fluid pulse during its duration can remain relatively constant or may instead commence to decrease due to the expanding volume 40 if a constant pressure source 36 is not available. Although a decreasing input pressure would result in a more rapid change of the resultant pressure D, this does not affect the operation of the invention as long as the pressure in reduced volume 38 can build up to a point sufficient to impart relatively high velocity to plunger 12 within a short period of time.
  • the absolute values of the input pressure, the initial low pressure in volume 38, and the final pressure of volume 38 may be varied according to the teachings and relationships here disclosed.
  • a fluid pulse is here utilized to impart momentum to piston 28, itis obvious that other means may be employed for this purpose without changing the relationships between piston 28, volume ⁇ 38, and plunger 12.
  • plunger 12 normally rebounds from the impact and is repositioned in passageway 14.
  • plunger 12 may be caused to have sufficient rebound energy so as to cause the production of a back pressure Wave.
  • This back pressure helps to reposition piston 28 in its left most position in readiness for the next fluid pulse.
  • the creation of this plunger rebound energy is itself a direct function of the initiating pulse pressure, since the momentum originally imparted to piston 28 is a direct consequence of said initiating pulse pressure.
  • the advantages of such an ernbodirnent is that a faster cycle time results from this forceful repositioning of the piston and plunger.
  • the front end of piston 28 can be streamlined if desired by giving it the shape of a ogive. Such streamlining reduces friction loss in the uid such that piston 28 gains momentum much more quickly. Other streamlined shapes may be employed to perform this function.
  • FIGURE 4 is a graphical timewise representation of the operation of the invention in FIGURE 2b and shows one complete cycle from the initiation of a fluid input pulse to the repositioning of piston 28 in its left most position.l Parts a, b, c, and d of FIGURE 4 respectively show the input pressure pulse, the chamber 38 volume, piston 28 momentum, and plunger 12 momentum as plotted against the cycle time. Piston momentum and plunger momentum are shown as having both positive and negative values to indicate the direction of motion.
  • piston 28 If piston 28 is initially positioned adjacent to port 32, a uid input pulse applied thereto creates an unbalanced force in a direction toward plunger 12. Assume for purposes of this description that the input pulse pressure remains constant with the ever increasing volume 4t) until the pulse is terminated. If the initial pressure in volume 38 is quite low as compared with the input pressure, this unbalanced force is substantially constant until volume 38 is reduced by at least one-half. Therefore, the initial acceleration of piston 28 is substantially constant until position II is reached, and its velocity increases in linear fashion. This is illustrated in FIGURE 4c wherein the piston momentum is seen to also increase in linear fashion during the rst part of the cycle. However, this constant rate of change in piston velocity results in an ever increasing rate of change in volume 38.
  • volume 38 decreases at ever increasing rate. Eventually, volume 38 decreases to such an extent that the pressure therein begins to substantially oppose the input pressure until at last there is no unbalanced force acting on piston 28 so that its velocity at this instant is unchanging. This is indicated in FIGURE 4c by the maximum positive value of the piston momentum. Thereafter this momentum curve rapidly falls to zero with a relatively high pressure being created in the reduced volume 38 sufficient to create an unbalanced force on plunger 12 and impart momentum thereto as indicated by FIGURE'4d. The high unbalanced force on plunger 12 results in a rapid increase of its momentum from a value of zero. Y
  • the input pulse in FIGURE 4a may be terminated either prior to, at, or subsequent to the time when momentum is imparted to plunger 12. Thereafter, the high pressure in reduced volume 38 causes an unbalanced force to be applied to piston 28 in a direction such that piston 28 quickly stops and reverses its direction of travel. This action is illustrated in FIGURE 4c by the negative portion of the curve. Because of the high pressure in reduced volume 38, to' which is coupled the rebound energy of plunger 12, a large acceleration is imparted to piston 28. As shown in FIGURE 4d, plunger 12 upon making impact with its print receiving member rebounds in the opposite direction. This is indicated by the change of polarity of the curve, wherein it is seen that the repositioning time of plunger 12 is quite'rapid.
  • piston 28 is repositioned and awaits a subsequent fiuid actuating input pulse.
  • Apparatus for converting fluid energy of relatively long duration into impulse energy of relatively short duration which comprises in combination: an elongated fluid impervious chamber having a wall at at least one end thereof for preventing the escape of fluid therefrom; a piston member of predetermined mass and having first and second opposed end surfaces which is slidably disposed within said chamber with its said first end surface facing said chamber one end wall so that there is substantially no uid leakage between said chamber and said piston member, said piston member being movable between predetermined maximum and minimum distances with respect to said chamber one end wall so as to vary the chamber volume between it and said chamber one end wall between predetermined maximum and minimum volume values; a pressurized body of compressible uid occupying said chamber volume; a movable mechanical force transmitting member extending through said chamber at said one end so as to be in fluid communication with said chamber volume without permitting any substantial escape of fluid therefrom, and which is normally biased to a rest position but movable therefrom in respouse to compressible fluid pressure only when below a first chamber
  • Printing mechanism comprising: a type face, a print hammer spaced apart from said type face a distance to permit insertion of a print receiving member therebetween; an elongated uid impervious hamber having a wali at at least one end thereof for preventing the escape of uid therefrom; a pistonvmember of predetermined mass and having first and second opposed end ⁇ surfaces which is slidably disposed Within said chamber with its said first end surface Afacing said chamber one end Wall so that there is substantially no uid leakage between said chamber and said piston member, said piston member being movable between predetermined maximum and minimum distances with respect to said chamber one end wall so as to vary the chamber volume between it and said chamber one end wall between predetermined maximum and minimum volume values; a pressurized body of compressible'fluid oecupying said chamber volume; a movable mechanical force transmitting member corineeted at one end thereof to said print hammer for moving same to force a said inserted print receiving member against said type

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Impact Printers (AREA)
US131911A 1961-08-16 1961-08-16 Fluid pulsing means for print hammers Expired - Lifetime US3159099A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
BE620847D BE620847A (en)van) 1961-08-16
NL282126D NL282126A (en)van) 1961-08-16
US131911A US3159099A (en) 1961-08-16 1961-08-16 Fluid pulsing means for print hammers
GB28535/62A GB944687A (en) 1961-08-16 1962-07-25 Fluid pressure operation of devices such as printing hammers
CH934362A CH400200A (de) 1961-08-16 1962-08-06 Vorrichtung zur Umwandlung von Druckimpulsen von relativ kleinem Druck und relativ langer Dauer in Druckimpulse von relativ hohem Druck und relativ kurzer Dauer

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Application Number Priority Date Filing Date Title
US131911A US3159099A (en) 1961-08-16 1961-08-16 Fluid pulsing means for print hammers

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Publication Number Publication Date
US3159099A true US3159099A (en) 1964-12-01

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Application Number Title Priority Date Filing Date
US131911A Expired - Lifetime US3159099A (en) 1961-08-16 1961-08-16 Fluid pulsing means for print hammers

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US (1) US3159099A (en)van)
BE (1) BE620847A (en)van)
CH (1) CH400200A (en)van)
GB (1) GB944687A (en)van)
NL (1) NL282126A (en)van)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3263607A (en) * 1964-07-29 1966-08-02 Sperry Rand Corp Fluid hammer impression actuating means
US3282206A (en) * 1964-12-21 1966-11-01 Sperry Rand Corp Hydraulically actuated print hammer for high speed printers
US4027762A (en) * 1973-11-10 1977-06-07 Kokusai Gijutsu Kaihatsu Kabushiki Kaisha Dot printer
US4046073A (en) * 1976-01-28 1977-09-06 International Business Machines Corporation Ultrasonic transfer printing with multi-copy, color and low audible noise capability
US4290357A (en) * 1979-10-09 1981-09-22 Natmar, Inc. Independently operable multihead endless band printer
US20210379727A1 (en) * 2018-10-22 2021-12-09 Schaeffler Technologies AG & Co. KG Tool and method for mechanical surface treatment

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1031526A (en) * 1912-03-05 1912-07-02 Newton Heston Cloud Jr Gun.
US1055857A (en) * 1911-11-22 1913-03-11 Hans Charles Behr Process of operating percussive apparatus.
US1555655A (en) * 1923-11-01 1925-09-29 Bryant Service Inc Explosive marking device
US1691170A (en) * 1926-11-29 1928-11-13 All Metal Products Company Toy machine gun
US2546114A (en) * 1944-08-28 1951-03-20 Triplett & Barton Inc Pneumatic die stamping machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1055857A (en) * 1911-11-22 1913-03-11 Hans Charles Behr Process of operating percussive apparatus.
US1031526A (en) * 1912-03-05 1912-07-02 Newton Heston Cloud Jr Gun.
US1555655A (en) * 1923-11-01 1925-09-29 Bryant Service Inc Explosive marking device
US1691170A (en) * 1926-11-29 1928-11-13 All Metal Products Company Toy machine gun
US2546114A (en) * 1944-08-28 1951-03-20 Triplett & Barton Inc Pneumatic die stamping machine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3263607A (en) * 1964-07-29 1966-08-02 Sperry Rand Corp Fluid hammer impression actuating means
US3282206A (en) * 1964-12-21 1966-11-01 Sperry Rand Corp Hydraulically actuated print hammer for high speed printers
US4027762A (en) * 1973-11-10 1977-06-07 Kokusai Gijutsu Kaihatsu Kabushiki Kaisha Dot printer
US4046073A (en) * 1976-01-28 1977-09-06 International Business Machines Corporation Ultrasonic transfer printing with multi-copy, color and low audible noise capability
US4290357A (en) * 1979-10-09 1981-09-22 Natmar, Inc. Independently operable multihead endless band printer
US20210379727A1 (en) * 2018-10-22 2021-12-09 Schaeffler Technologies AG & Co. KG Tool and method for mechanical surface treatment

Also Published As

Publication number Publication date
NL282126A (en)van)
GB944687A (en) 1963-12-18
CH400200A (de) 1965-10-15
BE620847A (en)van)

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