US3880051A - Pneumatic system including auxiliary output - Google Patents

Pneumatic system including auxiliary output Download PDF

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Publication number
US3880051A
US3880051A US490289A US49028974A US3880051A US 3880051 A US3880051 A US 3880051A US 490289 A US490289 A US 490289A US 49028974 A US49028974 A US 49028974A US 3880051 A US3880051 A US 3880051A
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US
United States
Prior art keywords
selectively
piston
pneumatic system
pneumatic
chamber
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
US490289A
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English (en)
Inventor
Daniel Eppler
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.)
ABB Installation Products Inc
Original Assignee
Thomas and Betts 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 US490289A priority Critical patent/US3880051A/en
Application filed by Thomas and Betts Corp filed Critical Thomas and Betts Corp
Priority to AR259291A priority patent/AR204867A1/es
Publication of US3880051A publication Critical patent/US3880051A/en
Application granted granted Critical
Priority to AU81430/75A priority patent/AU471223B2/en
Priority to CA227,984A priority patent/CA1022406A/en
Priority to ZA00753575A priority patent/ZA753575B/xx
Priority to FR7520944A priority patent/FR2279961A1/fr
Priority to IT50387/75A priority patent/IT1040845B/it
Priority to GB2853175A priority patent/GB1473789A/en
Priority to BR7504573*A priority patent/BR7504573A/pt
Priority to DE2532408A priority patent/DE2532408C3/de
Priority to DE7523120U priority patent/DE7523120U/de
Priority to NL7508701A priority patent/NL7508701A/xx
Priority to SE7508301A priority patent/SE412020B/xx
Priority to ES439651A priority patent/ES439651A1/es
Priority to BE158473A priority patent/BE831580A/xx
Priority to JP8894375A priority patent/JPS5621555B2/ja
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/16—Drives for riveting machines; Transmission means therefor
    • B21J15/18—Drives for riveting machines; Transmission means therefor operated by air pressure or other gas pressure, e.g. explosion pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25C—HAND-HELD NAILING OR STAPLING TOOLS; MANUALLY OPERATED PORTABLE STAPLING TOOLS
    • B25C1/00—Hand-held nailing tools; Nail feeding devices
    • B25C1/04—Hand-held nailing tools; Nail feeding devices operated by fluid pressure, e.g. by air pressure

Definitions

  • a pneumatic system applicable for pneumatically a la? 46 powered tools or the like comprises a pair of reciprocating slidable pistons arranged in tandem-like fashion within respective forward and rear chambers of a main cylinder.
  • a two position valve means is selectively operable to divert the incoming pneumatic fluid to either of the two chambers while simultaneously diverting the exhaust therefrom to an auxiliary output.
  • Pressurization of the forward chamber in the forward stroke is accomplished by providing a passageway through the rear piston for channeling the pressurized fluid into the forward chamber to employ the composite thrust of both pistons during the work cycle.
  • An auxiliary cylinder may be coupled to the auxiliary output for selective pressurization thereof whereby the auxiliary cylinder may further comprise a feed mechanism selectively sequenced by the pressure developed in the auxiliary output.
  • the system may also include a pressure reducer for further selectively pressurizing the auxiliary output to provide a selectively cycled low level pressure in the auxiliary cylinder.
  • the invention is directed to the field of pneumatic systems employable with pneumatically powered tools or the like.
  • the invention overcomes the difficulties and limitations noted above with respect to prior art devices by providing a pneumatic system comprising tandemly operated piston means operable in respective cylinders whereby the exhaust output therefrom is selectively diverted to an auxiliary output for the selective pressurization thereof to provide a composite system for pneumatically powered tools or the like which is simpler, cheaper, more reliable, and more trouble free than such prior art devices.
  • the main cylinder comprises a divider separating the interior thereof into a first chamber and a second chamber arranged in coaxial alignment.
  • a pair of pistons arranged in tandem-like fashion are slidably disposed within their respective chambers witha suitably orificed terminating end of the shank portion of the rear piston extending through a generally transverse aperture in the divider and into the front chamber when both pistons are in their fully retracted position.
  • the rear piston has a longitudinally extending bore therethrough to provide a passageway for pneumatic fluid entering the rear chamber so that upon selective pressurization of the rear chamber a portion of the pneumatic fluid flowing therethrough is directed into the front chamber to energize the front piston.
  • the front piston may supply the energizing force solely by virtue of the pressure exerted thereon or may be assisted by the force of the second piston bearing thereagainst during the forward stroke.
  • a manually controllable -valve means is operationally selective to divert the incoming pressurized fluid to either the front or rear chamber while diverting the exhaust fluid to an auxiliary output which may be coupled to an auxiliary cylinder which may comprise a feed mechanism selectively energized by the exhaust pressure to align and feed work pieces contained therein in accordance with a predetermined serially operative from a single pressurized source of pneumatic fluid.
  • FIG. 1 is a side elevational view, partly cut away and partly in section, of a pneumatically powered tool having a pneumatic system constructed in accordance with the concepts of the invention.
  • FIG. 2 is a fragmentary top plan view, partly cut away and partly in section, of a portion of the feed mechanism of the device of FIG. 1.
  • FIG. 3 is a diagrammatic view of the pneumatic system of FIG. 1 showing the respective elements in an initial or rest position.
  • FIG. 4 is a diagrammatic view of the system of FIG. 1 showing the direction of fluid flow when the valve means is operated from its first to its second position.
  • FIG. 5 is a diagrammatic view of the pneumatic system of FIG. 1 showing .the relative position of the respective elements therein after operation of the valve means from its first to its second position.
  • FIG. 6 is a diagrammatic view of the pneumatic system of FIG. 1 showing the pneumatic fluid flow when the valve means is moved from its second position to its first position.
  • FIG. 7 is a fragmentary perspective view showing a further embodiment of the shank portion of a first piston means of a pneumatic system constructed in accordance with the concepts of the invention.
  • FIG. 8 is a fragmentary side elevational view, in section, of a further embodiment of the shank portion of a first piston means of a pneumatic system constructed in accordance with the concepts of the invention.
  • FIG. 9 is a front sectional view of the device of FIG. 8.
  • FIG. 10 is a fragmentary side elevational view, in section, of yet another embodiment of the shank portion of a first piston means of a pneumatic system constructed in accordance with the concepts of .the invention.
  • FIG. 11 is a graphic representation showing the relationship between piston movement and auxiliary cylinder pressure of a pneumatic system constructed in accordance with the concepts of the invention.
  • FIGS. 1, 2, 3, 4, 5, and 6 there is shown a tool (FIG. 1) having a housing 22 within which is incorporated a pneumatic system 24 (FIG. 3) constructed in accordance with the concepts of the invention.
  • the housing 22 has a general pistol-like con figuration and includes a barrel portion 26 to which is attached a handle portion 28 suitably apertured as at 30 to receive a fitting 32 adapted to receive thereat a source of pneumatic pressure in a direction indicated by the arrow 34.
  • the pneumatic system described hereafter may be employed with a variety of types and shapes of pneumatic tools, for the sake of convenience the sytem will be described in detail with respect to the pistol-like tool configuration shown herein merely as a matter of illustration and not as a limitation of the type and shape of tool applicable therewith.
  • the source of pressurized pneumatic fluid 34 is coupled through the fitting 32 to both a pressure regulating means 36 and a valve means 38 located within the handle portion 28 of the tool 20.
  • the valve means 38 comprises a plunger means 40 selectively operable to cause selective diversion of the pneumatic fluid in a manner to be described in more detail hereafter.
  • the fitting 32 comprises a threaded connection 41 having a projection 42 to which is coupled a conduit 44 which has a first branch 46 coupled to the pressure regulating means 36 and a second branch 48 coupled to the valve means 38, as at 50.
  • the branch 46 of the conduit 44 is coupled to an inlet port 52 of the pressure regulating means 36 which . also comprises an outlet port 54 providing a regulated source of pressurized fluid to an auxiliary output line 56 which feeds an auxiliary cylinder means 58 comprising a feed tube 60 which may be loaded with a plurality of workpieces 62 for advancement into a work chamber 64 for engagement with the tool plunger 66 as further illustrated in detail in FIG. 2.
  • the feed tube 62 has coupled thereto at a forward end 68 a pair of retainers 70 formed preferably from resilient spring material.
  • Each retainer 70 is suitably formed so as to provide an inturned end 72 at the termination thereof wherein the spacing between the inturned ends 72 is somewhat less than the 'width of the workpieces 62. Accordingly, the workpieces 62 are prevented from advancing beyond the ends 72 of the retainer 70 until urged forwardly by an external force.
  • the means by which the workpieces 62 are selectively advanced into the work chamber 64 will be described in greater detail hereafter.
  • the valve means 38 is coupled to a main cylinder means 74 by way of conduits 76 and 78 to provide selective pressurization thereof. As shown in detail in FIG.
  • the main cylinder means 74 comprises a housing 80 having a first or rear chamber 82 and a second or front chamber 84, the front and rear chambers 84 and 82, respectively, being isolated from one another by a divider means such as an annular ring 86 having a transverse aperture 88 extending therethrough.
  • the ring 86 is provided with both an inner seal I00 extending circumferentially about the aperture 88 and an outer seal 102 extending between the external surface of the ring 86 and the inner wall of the main cylinder means 74.
  • a shank portion 104 of a first or rear piston means 106 extends partially through the aperture 88 of the ring 86 in a rest position substantially as shown in FIG.
  • the piston means 106 further comprises a head portion 108 having circumferentially disposed thereabout a seal 110 for sliding engagement with the inner surface of the main cylinder means 74.
  • Extending through the first or rear piston means 106 is a passageway 112 selectively bored to provide a conduit for pneumatic fluid in a manner to be described in greater detail hereafter. As shown in detail in FIG.
  • the rear piston means shank portion 104 is provided with a terminating end 114 having grooves 116 which extend from the passageway 112 radially outwardly to the outer surface of the terminating end 114 of the shank portion 104 to at least partially divert the pneumatic fluid flowing through the passageway 112 for pressurization of the second or front chamber 84.
  • the grooved portions 116 may be replaced by radially extending bores 118 which are disposed slightly rearwardly of the end face of the shank portion of the rear piston means to similarly divert the pneumatic fluid flowing through the passageway 112.
  • the radially extending bores 118 are shown as extending in a symmetrical pattern outwardly from the passageway 112 to provide a spoke-like configuration essentially as shown. It will of course be clear that the arrangement illustrated may be varied to comprise either one or more such bores 118 in either symmetrical or unsymmetrical patterns as necessary or desirable. Furthermore, although each of the bores 118 is shown as extending generally normal to the longitudinal axis of the shank portion 104, obliquely angled bores 120, as illustrated, for example, in FIG. 10 may be employed to provide a further embodiment in accordance with the concepts of the invention.
  • a combination of grooves and bores such as 116, 118, and 120 may be employed in any suitable arrangement at the terminating end of the first piston means shank portion without departing from the spirit of the invention and within the concepts herein disclosed.
  • Slidably disposed within the front or second chamber 84 (FIG. 3) is a front or second piston means 122 having a shank portion 124 extending through an orifice 126 in the main cylinder means 74 tdprovide an extension 128 either coupled to or formed soas to provide the plunger 66 described hereinabove with respect to the embodiment V I A Y.
  • the front or second piston means 122 further comprises a head portion 130 similar to the head portion 108 of the first or rear piston means 106 and preferably of equal diameter.
  • a seal 132 is disposed about the head portion 130 of the second or front piston means 122 and suitably proportioned to provide a sliding fit between the head portion 132 and the inner surface of the main cylinder means 74.
  • the pressure regulating means 36 comprises a housing 134 having an inner chamber in which is disposed a biased ball member 136 selectively seated at the inlet portion 52 and resiliently biased thereagainst by a spring 138 to selectively control the flow of pressurized fluid therethrough.
  • the valve means 38 comprises an inner chamber 140 in which are slidably disposed a first diverter means 142 situated at one end of the plunger means 40 and a second diverter means 144 spaced rearwardly from the first diverter means 142, said diverter means 142 and 144 being arranged to selectively divert the pneumatic fluid flowing within the inner chamber 140 of the valve means 38.
  • the first and second diverters 142 and 144 are formed preferably as annular rings each comprising a seal I46, 148, respectively, extending circumferentially thereabout to provide a sealed sliding fit with the inner surface of the chamber 140.
  • the plunger means 40 is biased towards the right in FIG.
  • valve means 38 is coupled to the outlet port 54 of the pressure regulating means 36 by a conduit 152 which also joins the valve means 38 with the auxiliary output line 56 at the junction 154.
  • a further conduit 156 couples the auxiliary output line to the valve means 38 just behind or to the right, as viewed in FIG. 3, of the second diverter means 144. Accordingly, in the operational state illustrated in FIG.
  • the incoming pressurized fluid is directed through the conduit 48 into the inner chamber 140 of the valve means 38 and then out through the line 78 to the second or front chamber 84 of the main cylinder means 74 to apply a force against the underside of the head portion 130 of the front or second piston means 122 in a direction to urge it rearwardly or towards the left, as viewed in FIG. 3, thereby causing the rear or first piston means 106 to be moved in the same direction upon the contact of its shank portion 104 with the head portion 130 of the front piston means 122.
  • the second or front chamber 84 of the main cylinder means 74 is maintained under continuous pressure so that the front and rear piston means 122 and 106, respectively, are held in their retracted position, substantially as shown.
  • the output of the pressure regulating means 36 is coupled by way of the conduit 152 to the auxiliary output line 56 to provide a constant low pressure thereat when the system is in the rest position indicated in FIG. 3, whereby the low pressure pneumatic fluid in the auxiliary output line 56 is applied against an auxiliary piston means 158 slidably disposed within the interior of the auxiliary cylinder means 58.
  • an enlarged head portion 160 at one end of the plunger means 40, the head portion 160 protruding outwardly from the valve means 38 for selective engagement by the user.
  • the plunger means 40 is shown displaced to a second position by applying a force to the head portion 160 in a direction indicated by the arrow 162.
  • the pneumatic fluid is now diverted from the second or front chamber 84 to the first or rear chamber 82 via the conduit 76, the pressurized fluid entering the first or rear chamber 82 by way of a port 164 extending through the main cylinder housing 74 substantially as shown in FIG. 4.
  • the fluid is thus caused to enter the space behind the head portion 108 of the first or rear piston means 106 to apply a force to the piston means 106 urging it towards the right, as viewed in FIG. 4.
  • a portion of the fluid entering through the port 164 is diverted through the piston shank passageway 112 into the front or second chamber 84 to impinge against the head portion 130 of the second or front piston means 122, thereby causing the second piston means 122 to similarly be urged towards the right, as viewed in FIG. 4, in a direction indicated by the arrow 166.
  • the static fluid previously occupying the front chamber 84 is caused to exit therefrom by way of the conduit 78 and is conducted through the valve means 38 into the conduit 156 and then into the auxiliary output line 56 to the auxiliary cylinder means 58.
  • FIG. 11 there is shown a graph depicting the pressure variation in the auxiliary cylinder means 58. The interval indicated in FIG.
  • the first piston 106 being unobstructed in its movement, will be accelerated somewhat above the speed of the second piston 122 so that the terminating end of the shank portion 104 of the first piston means 106 will be caused to abut the head portion 130 of the second piston means 122 whereby the force exerted by both the first piston means 106 and the second piston means 122 will be applied to the extending portion of the shank portion 124 of the second piston means 122 for operation on a workpiece situated at the terminating end of the plunger means 66 shown in FIG. 1.
  • the work to be done by the plunger means 66 is thus accomplished by the total driving force available from both the first piston means 106 and the second piston means 122, both cooperating to produce a total force equal to the sum of the forces exerted on each of the piston head portions 108 and 130, respectively, of the first and second piston means 106 and 122.
  • the pressure built up in the auxiliary output line 56, and consequently in the auxiliary cylinder 58 reaches a maximum before the end of the forward stroke of the second piston means 122 and is arranged to provide a force sufficient to eject a workpiece 62 from between the terminating ends 72 of the retainers shown in FIG. 2 and into the work chamber 64.
  • a vertical line 172 extending from the bottom to the top of FIG. 11 indicates the point in the operating cycle where each of the piston means 106 and 122 reached the end of their forward travel causing the auxiliary cylinder pressure to drop to the low pressure level indicated as 167 despite continued depression of the plunger means 40.
  • the biasing means 150 operate to return the first and second diverter means 146, and 148, respectively, to their initial or rest position substantially as shown in FIG. 6.
  • the source of pneumatic pressure is now caused to be conducted through the conduit 48 through the valve means 38 and the conduit 78 into the second or forward chamber 84 of the main cylinder means 74 and impinges against the undersurface of the head portion 130 of the second piston means 122, driving the second piston means 122 to its retracted position or to the left, as viewed in FIG. 6, in the direction indicated by the arrow 174.
  • the head portion 130 of the second piston means 122 will thus be caused to abut the terminating end of the first piston means shaft portion 104 thereby urging the first piston means 106 towards its retracted position in response to the movement of the second piston means 122.
  • the pneumatic fluid within the chamber 82 is forced out of the chamber 82 through the conduit 76, thence into the valve means 38 and into the auxiliary output line 56 where it is conducted into the auxiliary cylinder means 58.
  • the rate of rearward movement of both the first and second piston means 106 and 122 is indicated by the sloping line 176 in FIG. 11 (a) which illustrates a slower rate of travel than occurs in the forward stroke illustrated by the sloping line 178 in FIG. 11 (a).
  • the retainers are arranged to insure that the workpieces 62 are retained in position against the lower pressure level indicated by the line in FIG. 11 (b).
  • the exhaust pressure from the rear or first chamber 82 is also directed into pressure regulating means 36 through the conduit 152 to internally pressurize the inner chamber 138 of the pressure regulating means 38 sufficiently to cause the ball means 136 to be urged against the seat 52 of the pressure regulating means 36 thereby disrupting the source of low pressure emanating therefrom so that the pressure in the auxiliary output line 56 is supplied solely from the rear or first chamber 82.
  • a pneumatic system for a pneumatically powered tool or the like comprising: a source of pneumatic pressure; main cylinder means having a first chamber and a second chamber, said first and said second chambers being arranged in generally coaxial alignment; selectively apertured divider means disposed within said main cylinder means for selectively isolating said first chamber from said second chamber; first piston means having a head portion and a shank portion and slidably disposed within said main cylinder means first chamber so that its shank portion extends through said divider aperture, there being a passageway extending through the length of said first piston means for permitting the passage of pneumatic fluid therethrough; second piston means having a head portion and a shank portion and slidably disposed within said main cylinder means second chamber in generally coaxial alignment with said first piston means, said second piston means having an extension at the terminating end of its shank portion protruding coaxially outwardly from said main cylinder means for operation on a workpiece, said first piston means passageway communicating at one end with said main cylinder means
  • first and said second piston means being arranged for tandem-like operation upon the selective pressurization of said main cylinder means first and second chambers.
  • said first and said second piston means being independently selectively advanced upon the operation of said valve means from said first position to said second position.
  • said first and said second piston means being selectively retracted upon the operation of said valve means from said second position to said first position, movement of said first and said second piston means between said retracted and said extended positions causing selective pressurization of said auxiliary output.
  • valve means comprises biasing means for normally biasing said valve means in said first position.
  • a pneumatic system as defined in claim 1 further comprising auxiliary cylinder means coupled to said auxiliary output for selective pressurization therefrom in response to the movement of said first and said second piston means.
  • a pneumatic system as defined in claim 3 further comprising auxiliary piston means disposed within said auxiliary cylinder means for slidable movement therewithin.
  • a pneumatic system as defined in claim 1 further comprising pressure regulating means coupled between said pneumatic pressure source and said auxiliary output for further selectively pressurizing said auxiliary output.
  • a pneumatic system as defined in claim 5 wherein said pressure regulating means comprises a housing having an inlet port coupled to said pneumatic pressure source. the interior of said housing including means selectively biased towards said inlet port to control the flow of pneumatic fluid therethrough.
  • valve means comprises a generally elongate inner chamber, said valve means further including plunger means axially slidable in said inner chamber and having diverter means operable by said plunger means for selectively directing pneumatic fluid passing through said valve means inner chamber.
  • a pneumatic system as defined in claim 13 further comprising pressure regulating means coupled between said pneumatic pressure source and said auxiliary output for further selectively pressurizing said auxiliary output.
  • a pneumatic system as defined in claim 20 wherein said pressure regulating means comprises a housing having an inlet coupled to pressure source, the interior of said housing including means selectively biased towards said inlet port to control the flow of pneumatic fluid therethrough.
US490289A 1974-07-22 1974-07-22 Pneumatic system including auxiliary output Expired - Lifetime US3880051A (en)

Priority Applications (16)

Application Number Priority Date Filing Date Title
US490289A US3880051A (en) 1974-07-22 1974-07-22 Pneumatic system including auxiliary output
AR259291A AR204867A1 (es) 1974-07-22 1975-01-01 Disposicion neumatica
AU81430/75A AU471223B2 (en) 1974-07-22 1975-05-22 Pneumatic system including auxiliary output
CA227,984A CA1022406A (en) 1974-07-22 1975-05-28 Pneumatic system including auxiliary output
ZA00753575A ZA753575B (en) 1974-07-22 1975-06-03 Pneumatic system including auxiliary output
FR7520944A FR2279961A1 (fr) 1974-07-22 1975-07-03 Systeme pneumatique comprenant une sortie d'echappement auxiliaire
IT50387/75A IT1040845B (it) 1974-07-22 1975-07-07 Impianto pneumatico per utensili a motore pneumatico
GB2853175A GB1473789A (en) 1974-07-22 1975-07-07 Pneumatic system including auxiliary output
BR7504573*A BR7504573A (pt) 1974-07-22 1975-07-18 Sistema pneumatico para uma ferramenta pneumaticamente acionada ou semelhante
DE7523120U DE7523120U (de) 1974-07-22 1975-07-19 Pneumatisch betriebene antriebsvorrichtung
DE2532408A DE2532408C3 (de) 1974-07-22 1975-07-19 Druckluftantrieb für Werkzeuge
NL7508701A NL7508701A (nl) 1974-07-22 1975-07-21 Pneumatisch handgereedschap met hulpdrukleiding.
SE7508301A SE412020B (sv) 1974-07-22 1975-07-21 Pneumatisk anordning for ett pneumatiskt drivet verktyg
ES439651A ES439651A1 (es) 1974-07-22 1975-07-22 Un sistema neumatico para una herramienta o similar acciona-da neumaticamente.
BE158473A BE831580A (fr) 1974-07-22 1975-07-22 Systeme pneumatique comprenant une sortie d'echappement auxiliaire
JP8894375A JPS5621555B2 (ja) 1974-07-22 1975-07-22

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US490289A US3880051A (en) 1974-07-22 1974-07-22 Pneumatic system including auxiliary output

Publications (1)

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US3880051A true US3880051A (en) 1975-04-29

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ID=23947422

Family Applications (1)

Application Number Title Priority Date Filing Date
US490289A Expired - Lifetime US3880051A (en) 1974-07-22 1974-07-22 Pneumatic system including auxiliary output

Country Status (15)

Country Link
US (1) US3880051A (ja)
JP (1) JPS5621555B2 (ja)
AR (1) AR204867A1 (ja)
AU (1) AU471223B2 (ja)
BE (1) BE831580A (ja)
BR (1) BR7504573A (ja)
CA (1) CA1022406A (ja)
DE (2) DE2532408C3 (ja)
ES (1) ES439651A1 (ja)
FR (1) FR2279961A1 (ja)
GB (1) GB1473789A (ja)
IT (1) IT1040845B (ja)
NL (1) NL7508701A (ja)
SE (1) SE412020B (ja)
ZA (1) ZA753575B (ja)

Cited By (17)

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US4811963A (en) * 1986-07-04 1989-03-14 Autoblok S.P.A. Automatic indexing chuck for angular step-by-step movement of jaws
US5007328A (en) * 1989-07-24 1991-04-16 Otteman John H Linear actuator
US5016522A (en) * 1988-07-04 1991-05-21 Allardin Jean A Multi-stage air pressure cylinder
US5031402A (en) * 1990-08-02 1991-07-16 Klaeger Joseph H Pneumatic pump actuator for oil wells
US5058384A (en) * 1990-09-20 1991-10-22 University Of British Columbia Digital actuator
US5066191A (en) * 1987-11-30 1991-11-19 Sulzer Brothers Limited Turbine with control system
US6314862B1 (en) 2000-01-24 2001-11-13 Retterer Manufacturing Co., Inc. Combination cylinder and pistons
US6386508B1 (en) 2000-06-05 2002-05-14 D-M-E Company Actuator having dual piston surfaces
KR20030017281A (ko) * 2001-09-21 2003-03-03 신구성 자동 못박음 장치
US6719263B1 (en) 2002-09-20 2004-04-13 D-M-E Company Multi-piston valve actuator
US20040144229A1 (en) * 2002-12-26 2004-07-29 Savoy Mark A. Adjustable work support
EP1625916A1 (en) * 2004-07-30 2006-02-15 BLACK & DECKER INC. Integrated air tool and pressure regulator
US8869916B2 (en) 2010-09-09 2014-10-28 National Oilwell Varco, L.P. Rotary steerable push-the-bit drilling apparatus with self-cleaning fluid filter
US9016400B2 (en) 2010-09-09 2015-04-28 National Oilwell Varco, L.P. Downhole rotary drilling apparatus with formation-interfacing members and control system
WO2016178587A1 (en) * 2015-05-05 2016-11-10 S-Gun Limited A pneumatic or hydraulic mechanism
CN106541367A (zh) * 2015-09-21 2017-03-29 苏州科维新型包装有限公司 一种气动钉枪的扳机装置及气动钉枪
WO2018070881A1 (en) * 2016-10-11 2018-04-19 S-Gun Limited A pneumatic or hydraulic mechanism

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JPS5519046A (en) * 1978-07-26 1980-02-09 Motomura Seisakusho:Kk Method of making koji and equipment therefor
JPS5574787A (en) * 1978-12-02 1980-06-05 Fujiwara Jiyouki Sangyo Kk Air conditioner for automatic malting device
DE9109312U1 (ja) * 1991-07-27 1991-09-26 J.M. Voith Gmbh, 7920 Heidenheim, De
DE4340570C2 (de) * 1993-11-29 2003-04-10 Hilti Ag Eintreibvorrichtung zum Setzen von Befestigungselementen in Aufnahmematerialien
JP4714629B2 (ja) * 2006-04-20 2011-06-29 株式会社生方製作所 感熱スイッチ

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US2844978A (en) * 1956-10-08 1958-07-29 Boeing Co Rivet squeezer
US2931340A (en) * 1955-05-11 1960-04-05 Electraulic Presses Control mechanism for hydraulic presses
US3554088A (en) * 1968-11-06 1971-01-12 James Henry Bruyn Air tool

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US2931340A (en) * 1955-05-11 1960-04-05 Electraulic Presses Control mechanism for hydraulic presses
US2844978A (en) * 1956-10-08 1958-07-29 Boeing Co Rivet squeezer
US3554088A (en) * 1968-11-06 1971-01-12 James Henry Bruyn Air tool

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4811963A (en) * 1986-07-04 1989-03-14 Autoblok S.P.A. Automatic indexing chuck for angular step-by-step movement of jaws
US5066191A (en) * 1987-11-30 1991-11-19 Sulzer Brothers Limited Turbine with control system
US5016522A (en) * 1988-07-04 1991-05-21 Allardin Jean A Multi-stage air pressure cylinder
US5007328A (en) * 1989-07-24 1991-04-16 Otteman John H Linear actuator
US5031402A (en) * 1990-08-02 1991-07-16 Klaeger Joseph H Pneumatic pump actuator for oil wells
US5058384A (en) * 1990-09-20 1991-10-22 University Of British Columbia Digital actuator
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US8869916B2 (en) 2010-09-09 2014-10-28 National Oilwell Varco, L.P. Rotary steerable push-the-bit drilling apparatus with self-cleaning fluid filter
US9016400B2 (en) 2010-09-09 2015-04-28 National Oilwell Varco, L.P. Downhole rotary drilling apparatus with formation-interfacing members and control system
US9476263B2 (en) 2010-09-09 2016-10-25 National Oilwell Varco, L.P. Rotary steerable push-the-bit drilling apparatus with self-cleaning fluid filter
WO2016178587A1 (en) * 2015-05-05 2016-11-10 S-Gun Limited A pneumatic or hydraulic mechanism
CN106541367A (zh) * 2015-09-21 2017-03-29 苏州科维新型包装有限公司 一种气动钉枪的扳机装置及气动钉枪
CN106541367B (zh) * 2015-09-21 2018-12-28 苏州科维新型包装有限公司 一种气动钉枪的扳机装置及气动钉枪
WO2018070881A1 (en) * 2016-10-11 2018-04-19 S-Gun Limited A pneumatic or hydraulic mechanism
US11242873B2 (en) 2016-10-11 2022-02-08 S-Gun Limited Pneumatic or hydraulic mechanism

Also Published As

Publication number Publication date
DE7523120U (de) 1976-12-23
BE831580A (fr) 1976-01-22
IT1040845B (it) 1979-12-20
SE412020B (sv) 1980-02-18
BR7504573A (pt) 1976-07-06
JPS5621555B2 (ja) 1981-05-20
JPS5134479A (ja) 1976-03-24
AR204867A1 (es) 1976-03-05
SE7508301L (sv) 1976-01-23
FR2279961A1 (fr) 1976-02-20
DE2532408A1 (de) 1976-02-12
AU8143075A (en) 1976-04-15
DE2532408C3 (de) 1980-08-21
CA1022406A (en) 1977-12-13
ES439651A1 (es) 1977-03-01
GB1473789A (en) 1977-05-18
ZA753575B (en) 1976-04-28
AU471223B2 (en) 1976-04-15
FR2279961B1 (ja) 1979-01-12
NL7508701A (nl) 1976-01-26
DE2532408B2 (de) 1979-12-13

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