EP0735935A1 - Systeme a impulsions operant par choc, en particulier pour un tournevis a impulsions - Google Patents

Systeme a impulsions operant par choc, en particulier pour un tournevis a impulsions

Info

Publication number
EP0735935A1
EP0735935A1 EP95902761A EP95902761A EP0735935A1 EP 0735935 A1 EP0735935 A1 EP 0735935A1 EP 95902761 A EP95902761 A EP 95902761A EP 95902761 A EP95902761 A EP 95902761A EP 0735935 A1 EP0735935 A1 EP 0735935A1
Authority
EP
European Patent Office
Prior art keywords
core part
control
pressure chamber
mechanism according
rotation
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.)
Granted
Application number
EP95902761A
Other languages
German (de)
English (en)
Other versions
EP0735935B1 (fr
Inventor
Horst Weidner
Robert Klenk
Wolfgang Backe
Egbert Schneider
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0735935A1 publication Critical patent/EP0735935A1/fr
Application granted granted Critical
Publication of EP0735935B1 publication Critical patent/EP0735935B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers
    • B25B23/1453—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers for impact wrenches or screwdrivers

Definitions

  • the invention is based on a pulse hammer mechanism according to the preamble of claim 1.
  • a pulse hammer mechanism is already known (EP 460 592 AI), in which the angular momentum is generated by means of radially outwardly directed, spring-loaded slats which are movable in the radial direction and which at least temporarily have high-pressure spaces and sealingly separate adjacent low-pressure rooms.
  • the outside of the lamellae has specially shaped sealing surfaces which can be produced as precisely as possible in order to avoid leakage losses, which requires a relatively high outlay in terms of production technology.
  • the pulse hammer mechanism according to the invention with the characterizing features of claim 1 has the advantage, in contrast, of having rotationally symmetrical sealing surfaces that are much simpler and more precisely producible, as a result of which manufacturing-related dimensional and / or shape deviations and the associated leakage losses can be reduced.
  • By designing the pulse hammer mechanism with at least one reciprocating piston acting in the radial direction a compact design in the axial direction can be achieved.
  • the measures listed in the subclaims allow advantageous further developments and improvements of the pulse hammer mechanism specified in claim 1.
  • FIG. 1 shows a longitudinal section of a first exemplary embodiment of a pulse hammer mechanism designed according to the invention
  • FIG. 2 shows a cross section along line II-II in FIG. 1
  • FIGS. 3 and 4 each show cross sections through two further exemplary embodiments of a pulse hammer mechanism
  • FIGS. 5, 6 and FIG. 7 shows a fourth exemplary embodiment
  • FIG. 8 shows a cross section through a fifth exemplary embodiment
  • FIG. 9 shows a longitudinal section through a sixth exemplary embodiment
  • FIG. 10 shows a cross section along line XX in FIG. 9.
  • the pulse percussion mechanism shown in FIG. 1 has a cylindrical rotary body 13 which can be driven via a drive shaft 14 with the aid of a drive motor, not shown in more detail, about a rotation axis 15, for example in the direction of an arrow 15a.
  • the rotary body 13 At its end facing away from the drive shaft 14, the rotary body 13 has a central receiving opening 16 which almost completely penetrates the rotary body 13 and in which a cylindrical core part 17 is arranged concentrically.
  • the reciprocating piston 19 there is a through opening 20 which extends transversely to the lifting direction of the reciprocating piston 19 in the axial direction and in which the core part 17 extends through the reciprocating piston 19 with play.
  • the radial bore 18 can be closed by a cover 21 and sealed to the outside by means of suitable sealing means 22.
  • the core part 17 is rotatably coupled to an output shaft 25 which is provided at the end with a fastening device for a screwing tool, for example for a screwdriver bit.
  • Core part 17 and output shaft 25 are integrally connected to one another in the example.
  • the end of the core part 17 is formed on the output shaft 25.
  • Core part 17 or output shaft 25 are rotatably mounted in the receiving opening 16 in the circumferential direction with respect to the rotary body 13.
  • the bearings are placed in sliding seats 27 and 28, each to the side of the radial bore 18.
  • a sliding seat 28 located closer to the fastening device 26 is formed by two annular collars 29 and 30 of the core part 17 which are axially offset from one another, between which a sealing ring 31 in an annular groove 32 sits, which seals the receiving opening 16 to the outside.
  • the core part 17 is fixed in the axial direction within the rotary body 13 by a locking ring 33.
  • the reciprocating piston 19 is acted upon by spring force by means of a return spring 35 in the direction of the cover 21 and is pressed against a stop 34 projecting radially inwards on the cover 21.
  • the reciprocating piston 19 forms within the through opening 20 a peripheral control surface 36 which acts as a control means and which interacts with a control track 37 arranged on the core part 17 in the region of the radial bore 18.
  • the control track 37 has an almost cylindrical cross section with a radially projecting, strip-shaped control cam 38.
  • Cavities remaining within the rotating body 13 are almost completely filled with an essentially incompressible pressure medium, for example a hydraulic oil.
  • the reciprocating piston 19 separates a pressure chamber 40 located at the base of the radial bore 18 from a low-pressure chamber 41.
  • the low-pressure chamber 41 extends essentially over two partial areas, within the through-opening 20 between the core part 17 and the rotating body 13, and between the reciprocating piston 19 and the cover 21. Both Subregions are connected to one another via a compensating line 24.
  • the piston surface of the reciprocating piston 19 facing the pressure chamber 40 forms a working surface 39.
  • the pressure chamber 40 is connected to the low-pressure chamber 41 via a first connecting line 42 running in the rotating body 13.
  • An adjustable control valve 43 is arranged in the first connecting line 42, with the aid of which an overflow cross-section 44 to the first connecting line 42 can be controlled.
  • the control valve 43 is formed, for example, by an axially displaceable threaded pin 45 with a conical tip.
  • a seal 46 arranged on the outer circumference of the threaded pin 45 prevents pressure medium from passing the threaded pin 45 to the outside.
  • a second connecting line 47 is formed in the reciprocating piston 19 between the low pressure chamber 41 and the pressure chamber 40.
  • the second connecting line 47 extends radially from the control surface 36 to the working surface 39 of the reciprocating piston 19.
  • a backflow valve 48 is arranged which blocks pressure in the pressure chamber 40 in the direction of the low pressure chamber 41 and in um ⁇ reverse direction with a corresponding negative pressure in the pressure chamber 40 allows a backflow of pressure medium.
  • the control surface 36 is composed of two approximately semicircular partial surfaces 36a, 36b.
  • the first partial surface 36a which is closer to the cover 21, is at a greater radial distance from the axis of rotation 15 than the second partial surface 36b lying opposite it and closer to the pressure chamber 40.
  • the radial distance of the second partial surface 36b from the axis of rotation 15 is less than the radial distance of the control cam 38.
  • the partial surfaces 36a and 36b are approximately perpendicular to the axis of rotation 15 and to the direction of the piston 19 by approximately radially extending shoulder surfaces 54 and 55 connected to each other.
  • the core part 17 rotates with the rotating body 13 due to the effects of friction. If the torque acting on the fastening device 26 when screwing in exceeds the friction torque, the rotating body 13 will rotate relative to the core part 17. The core part 17 then rotates more slowly than the rotary body 13.
  • the reciprocating piston 19 is then brought from the stroke position back into abutment against the stop 34 by the return spring 35.
  • the control cam 38 again comes into contact with the shoulder surface 55 to generate a further angular momentum. Due to the symmetrical design of the control surface 36 and the control path 37, the pulse hammer mechanism 12 can also be operated in the reverse drive direction.
  • a pressure is exerted on the pressure medium by the working surface 39.
  • pressure medium Via overflow grooves arranged on the outer surface of the reciprocating piston 19. 56 and via corresponding recesses in the rotary body 13 opposite these in the region of the radial bore 18, pressure medium can initially reach the low-pressure chamber 41.
  • the overflow groove 56 and the recess 57 together form an overflow channel from the pressure chamber 40 to the low-pressure space 41.
  • Axially extending sealing strips 53, 59 are arranged in the overflow groove 56 and within the recess 57, which are included with the increasing stroke movement of the reciprocating piston 19 ⁇ take cover. If this is the case, the pressure chamber 40 is sealed suddenly.
  • a more or less high pressure resistance acts on the piston 19.
  • the check valve 48 is blocked.
  • the overflow cross section must be selected such that blocking of the pulse hammer mechanism 12 is avoided. If an increased pressure resistance acts in the pressure chamber 40, a correspondingly strong angular momentum is transmitted to the core part 13 via the control surface 36 and the control cam 38. Due to the relatively large flywheel mass of the rotating body 13 and the drive train coupled to it, relatively large angular momentum can be achieved without the impulse mechanism 12 blocking.
  • pressure medium can flow in via the backflow valve 48 as a result of the associated negative pressure in the pressure chamber 40.
  • FIG. 3 shows a second exemplary embodiment of the pulse hammer 12.
  • a single reciprocating piston 19 is received in the radial bore 18.
  • the main difference from the first exemplary embodiment is the arrangement of a damping spring 60 between the reciprocating piston 19 and the cover 21.
  • the damping spring 60 is designed as a compression spring.
  • the damping spring 60 has the task of preventing or dampening an impact of the lifting piston 19 against the shoulder 34 during the return stroke of the piston 19. Also under-.
  • the damping spring 60 supports a jam-free passage of the control cam 38 on the partial surface 36b.
  • the radius of the first partial surface 36a of the control surface 36 corresponds approximately to that of the control cam 38.
  • the damping spring 60 acts on the reciprocating piston 19 in the direction of the pressure chamber 40 and causes the control cam 38 and the first partial surface 36a to bear against one another.
  • FIG. 4 shows a third embodiment of the pulse hammer mechanism 12. Parts that are the same and have the same effect as the first or second exemplary embodiment are likewise identified by the same reference numerals.
  • the control surface 36 is designed without shoulder surfaces. While the first partial surface 36a has approximately the same radius as the control cam 38, the second partial surface 36b runs with a different radius, which in the circumferential direction of the control cam 38 starts from the radius of the control cam 38 into a radius corresponding to the radius of the core part 17 and then again passes into the radius of the control cam 38.
  • the second partial surface 36b has an arcuate course, which is strongly adapted to the outer circumference of the core part 17, so that the piston 19 in the basic position shown abuts the control track 37 over a large area.
  • the control track 37 accordingly forms a stop for the second partial surface 36b during the return stroke of the reciprocating piston 19.
  • a gap 61 is present between the reciprocating piston 19 and the cover 21, so that there is no damping spring which cushions the return against the cover 21 can be.
  • a valve closing spring is also not required here, since the valve closing body 49 is closed by the pressure of the pressure medium in the pressure chamber 40.
  • a locking ring 52 prevents the valve closing body 49 from migrating out into the pressure chamber 40.
  • a fourth exemplary embodiment is shown in FIGS. 5, 6 and 7.
  • two lifting pistons are arranged in the radial bore in this and in the two following embodiments. Parts which are the same and have the same effect as in the preceding exemplary embodiments are identified in all the following embodiments with two pistons by a reference symbol increased by 100.
  • a cylindrical rotary body 113 can be driven to rotate about an axis of rotation 115 via a drive shaft 114.
  • a core part 117 is arranged within an axial receiving opening 116 and is connected in a rotationally locking and axially aligned manner to an output shaft 125.
  • the output shaft 125 carries at the end a fastening device 126 for attaching a turning tool.
  • a continuous radial bore 118 is formed in the rotating body 113.
  • Two reciprocating pistons 119a, 119b are accommodated in the radial bore 118.
  • the radial bore 118 is closed on both sides by a pot-shaped housing part 170.
  • Sealing means 171, 172 are provided between the rotating body 113 and the housing part 170.
  • Housing part 170 and rotary body are connected to one another in a rotationally fixed manner.
  • the reciprocating pistons 119 separate a radially outer pressure chamber 140 from a low-pressure chamber 141.
  • the low-pressure chamber 141 is expanded by an encircling annular chamber 181 axially offset from the radial bore 118 in the rotating body 113.
  • the core part 117 has an approximately double-arched, mirror-symmetrical cross section.
  • Each arc section of the control path 137 has a continuous transition from a large radial distance to the axis of rotation 115 over a small radial distance to a correspondingly large radial distance.
  • Control surfaces 136a, 136b formed on the reciprocating piston 119 which correspond to the control path 138 and act as control means, are flat.
  • the reciprocating pistons are each shown in the stroke position in the radially outer reversal point.
  • the reciprocating pistons 119 can move back radially inward along the control path 137.
  • the pulse hammer mechanism 112 from FIG. 5 was rotated through 90 ° into the drawing plane. It can be seen that between the housing part 170 and the rotating body 113 on the outer casing of the rotating body 113 there is a circumferential annular groove 173 which connects the high-pressure chambers 140 delimited by the reciprocating pistons 119 to one another.
  • the pressure medium which is pressurized radially outwards during the stroke movement can flow to the annular chamber 181 of the low-pressure chamber 141 via a first connecting line 142 with a control valve 143 arranged therein.
  • the control valve 143 is arranged in an axial threaded bore in the rotary body 113.
  • the first connecting line 142 first extends in the radial direction inwards out of the annular groove 173 to the control valve 143 and then axially to the annular chamber 181.
  • a bore 174 runs radially inwards and obliquely to the shaft bearing 127.
  • the bore 174 is cut by an axial bore 175 which completely penetrates the rotating body 113.
  • the output end of the axial bore 175 is sealed by means of a threaded plug 176 and associated sealing means 177.
  • the part of the additional bore 175 on the drive side opens into the annular chamber 181 of the low-pressure chamber 141.
  • the axial region between the bore 174 and the low-pressure chamber 141 of the additional bore 175 forms a second connecting line 147, in which a backflow valve 148 is arranged.
  • An associated valve closing spring 149 of the backflow valve 148 is supported on the one hand on the threaded plug 176 and on the other hand on the valve closing body 149.
  • the core part 117 there is an axial channel 178, which is connected via a continuous radial channel 179 to the part of the low-pressure space 141 located between the control surfaces 136 and the control path 137. Pulls through in the axial direction the channel 178 the core part 117 up to its drive end. There it is connected to the annular chamber 181 via a transverse channel 180 which is radially continuous in the rotating body 113. In the area of the shaft bearing 127 there is in the core part 117 a control bore 182 to the channel 178 which is open on one side and which coincides with the opening of the bore 174 once per complete relative rotation from the core part 117 to the rotary body 113.
  • the pressure chamber 140 is connected via the bore 174, the control bore 182 and the channel 178 to the low-pressure chamber 141, so that no appreciable pressure builds up in the pressure chamber 140.
  • the connection between the bore 174 and the control bore 182 is interrupted, so that pressure can then build up in the pressure chamber 140. In this way it is achieved that a pulse occurs only once per relative rotation of the rotating body 113 and the core part 117, as a result of which a greater swing energy can be built up between the individual pulses.
  • a fifth exemplary embodiment is shown in FIG. 8, with the contact surfaces of reciprocating pistons 119a, 119b with the control path 137 that have been changed compared to the exemplary embodiment according to FIGS. 5, 6 and 7.
  • the control path 137 of the core part 117 is here predominantly cylindrical.
  • two control cams 138 are not shown, offset by 180 ° to one another.
  • the control cams 138 are formed, for example, by rolling elements 184, which are fixed to the core part 117 in the U direction, but are rotatable about their longitudinal axis.
  • the control cams 138 work together with correspondingly offset rollers 180, which are mounted in the control surfaces 136 of the reciprocating pistons 119 and act as control means instead of the control surfaces 136.
  • the pulse hammer mechanism 112 is in the basic position and in the lower position Half of the picture shown in its outer stroke position.
  • rolling elements 183, 184 can be provided in the control surfaces 36, 136 and / or the control tracks 37, 137 to reduce the frictional resistance.
  • the control cam 38 of the impulse impact wrench 12 can be designed as a rolling element.
  • FIGS. 9 and 10 show a further exemplary embodiment of the pulse hammer mechanism 112, in which the reciprocating pistons 119a, 119b are adjusted in the stroke direction via a positive control 185.
  • Cylinder pins 186a, 186b are held in the output-side wall of the reciprocating pistons 119 and engage in a control groove 187 which runs around the core part 117.
  • the control groove 187 has a variable radial distance from the axis of rotation 115 in the circumferential direction of the core part 117, so that the stroke position of the piston pistons 119a, 119b is changed depending on the rotational angle position between the rotating body 113 and the core part 117.
  • the control groove 187 has a symmetrical course, so that the two reciprocating pistons 119 each reach their outer or inner stroke position simultaneously.
  • the radially outer stroke position of the lifting piston 119a is shown in the upper half of FIG. 9, and the radially inner stroke position of the lifting piston 119b, which can be reached offset by 90 °, is shown in the lower half of the figure.
  • control groove 187 is shown in section. She has an approximately double-curved shape, according to the control path 137 in Figure 6.
  • the two Zylinder ⁇ access pins 186 a In the control groove 187, the two Zylinder ⁇ access pins 186 a.
  • the reciprocating pistons are moved inward from their radially outer position via the groove wall 187a lying radially further outward. They are adjusted outwards accordingly by means of the inner side wall 187b.
  • return springs for the reciprocating pistons 119a, 119b are not required.
  • High-pressure chamber or pressure chamber as well as low-pressure chamber and annular chamber as an extension are in the exemplary embodiments according to FIGS. 8 to 10 basically designed in accordance with the example according to FIGS. 5 to 7.
  • the assignment of the drive shaft 14 to the rotary body 13 and from the output shaft 25 to the core part 17 described in the exemplary embodiments is not mandatory, but is advantageous because of the higher moment of inertia of the rotary body 13 and the higher flywheel mass of the drive.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Actuator (AREA)

Abstract

Le système à impulsions opérant par choc (12) présente un corps rotatif (13), accouplé à un arbre moteur (14) et dans lequel est pratiquée une ouverture (16) destinée à loger un noyau (17) de façon concentrique par rapport à l'axe de rotation (15). Le noyau (17) est accouplé de façon solidaire à un arbre de sortie (25) rotatif . Le corps rotatif (13) présente en outre un alésage radial (18), s'étendant perpendiculairement à l'axe de rotation (15), et dans lequel est logé un piston alternatif (19) à mouvement radial. Ledit piston (19) présente un passage (20) permettant l'accès au noyau (17). Le piston forme, avec ses surfaces internes tournées vers le noyau (17), une surface de commande (36) qui agit conjointement avec une piste de commande (37) formée sur le noyau (17) et munie de cames (38). Chaque rotation relative du corps rotatif (13) et du noyau (17) est accompagnée d'une course radiale du piston (19). Un fluide de pression logé dans une chambre de compression (40) est soumis à une pression, ce qui entraîne la transmission d'une impulsion rotative à l'arbre de sortie (25) par l'intermédiaire de la surface de commande (36) et de la piste de commande (37).
EP95902761A 1993-12-21 1994-12-14 Systeme a impulsions operant par choc, en particulier pour un tournevis a impulsions Expired - Lifetime EP0735935B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4343582A DE4343582A1 (de) 1993-12-21 1993-12-21 Impulsschlagwerk, insbesondere für Impulsschrauber
DE4343582 1993-12-21
PCT/DE1994/001484 WO1995017281A1 (fr) 1993-12-21 1994-12-14 Systeme a impulsions operant par choc, en particulier pour un tournevis a impulsions

Publications (2)

Publication Number Publication Date
EP0735935A1 true EP0735935A1 (fr) 1996-10-09
EP0735935B1 EP0735935B1 (fr) 2000-04-05

Family

ID=6505597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95902761A Expired - Lifetime EP0735935B1 (fr) 1993-12-21 1994-12-14 Systeme a impulsions operant par choc, en particulier pour un tournevis a impulsions

Country Status (5)

Country Link
US (1) US5735354A (fr)
EP (1) EP0735935B1 (fr)
JP (1) JPH10501180A (fr)
DE (2) DE4343582A1 (fr)
WO (1) WO1995017281A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19506663C2 (de) * 1995-02-25 2003-03-06 Bosch Gmbh Robert Impulsschrauber
CA2421024C (fr) * 2002-07-19 2011-04-26 Marcellin Bruneau Barre de purgeage
HK1049571A2 (en) * 2003-02-05 2003-04-25 Wing Wide Hk Ltd Electric wrench for vehicle repairing
ATE452731T1 (de) * 2006-11-13 2010-01-15 Cooper Power Tools Gmbh & Co Werkzeug mit einem hydraulikschlagwerk
DE102010063080A1 (de) * 2010-12-14 2012-06-14 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Schlagwerk
TWM414304U (en) * 2011-05-20 2011-10-21 Hyphone Machine Ind Co Ltd Pneumatic tool
US9878435B2 (en) 2013-06-12 2018-01-30 Makita Corporation Power rotary tool and impact power tool
TWM562747U (zh) 2016-08-25 2018-07-01 米沃奇電子工具公司 衝擊工具
AT521254B1 (de) 2019-01-17 2019-12-15 Cutpack Com Gmbh Spannvorrichtung
AT523492B1 (de) 2020-01-31 2022-04-15 Cutpack Com Gmbh Spannvorrichtung zum Einspannen eines Werkstücks

Citations (2)

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Publication number Priority date Publication date Assignee Title
JPS4914839A (fr) 1972-06-02 1974-02-08
US4533337A (en) 1982-09-24 1985-08-06 Atlas Copco Aktiebolag Hydraulic torque impulse tool

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2850128A (en) * 1952-08-01 1958-09-02 Rotor Tool Company Rotary impact clutch
US2940566A (en) * 1958-02-17 1960-06-14 Master Pneumatic Tool Company Impact clutch
US3210959A (en) * 1963-05-17 1965-10-12 Ingersoll Rand Co Torque device
US3561543A (en) * 1969-02-07 1971-02-09 Ingersoll Rand Co Rotary impact wrench mechanism
JPS6033628B2 (ja) * 1981-01-27 1985-08-03 株式会社 空研 インパクトレンチにおける打撃回転装置
US4635731A (en) * 1984-12-13 1987-01-13 Chicago Pneumatic Tool Company Impulse tool
US5092410A (en) * 1990-03-29 1992-03-03 Chicago Pneumatic Tool Company Adjustable pressure dual piston impulse clutch

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4914839A (fr) 1972-06-02 1974-02-08
US4533337A (en) 1982-09-24 1985-08-06 Atlas Copco Aktiebolag Hydraulic torque impulse tool

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO9517281A1

Also Published As

Publication number Publication date
JPH10501180A (ja) 1998-02-03
DE4343582A1 (de) 1995-06-22
US5735354A (en) 1998-04-07
DE59409278D1 (de) 2000-05-11
EP0735935B1 (fr) 2000-04-05
WO1995017281A1 (fr) 1995-06-29

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