EP0631851A1 - Accouplement à impulsion, notamment pour clé à impulsion - Google Patents

Accouplement à impulsion, notamment pour clé à impulsion Download PDF

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Publication number
EP0631851A1
EP0631851A1 EP94108187A EP94108187A EP0631851A1 EP 0631851 A1 EP0631851 A1 EP 0631851A1 EP 94108187 A EP94108187 A EP 94108187A EP 94108187 A EP94108187 A EP 94108187A EP 0631851 A1 EP0631851 A1 EP 0631851A1
Authority
EP
European Patent Office
Prior art keywords
pressure chamber
mechanism according
housing part
pulse
core part
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.)
Ceased
Application number
EP94108187A
Other languages
German (de)
English (en)
Inventor
W. prof. Dr.-Ing. Backé
Egbert Dipl.-Ing. Schneider
Frank Wolter
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 EP0631851A1 publication Critical patent/EP0631851A1/fr
Ceased legal-status Critical Current

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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 type of the main claim.
  • a pulse percussion mechanism is already known (EP 460 592 A1), in which the angular momentum is generated by means of spring-loaded lamellae which are directed radially outwards and are movable in the radial direction and at least temporarily seal off high-pressure spaces and adjacent low-pressure spaces.
  • the outside of the lamellae has specially shaped sealing surfaces, which are to be manufactured as precisely as possible to avoid leakage losses, which requires a relatively high level of manufacturing complexity.
  • the pulse hammer mechanism according to the invention with the characterizing features of the main claim has the advantage, in contrast, to have rotationally symmetrical sealing surfaces that are much easier and more precisely to produce, which means that manufacturing-related dimensional and / or shape deviations and the associated leakage losses can be reduced. This is achieved by designing the pulse hammer mechanism with at least one axial piston which has cylindrically shaped sealing surfaces.
  • 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 partial section through the pulse hammer mechanism according to FIG. 1
  • FIG. 3 shows a partial section through a positive control device of the pulse hammer mechanism
  • FIG. 4 shows a cross section according to line IV-IV in FIG. 1
  • FIG. 5 6 shows a longitudinal section through a third exemplary embodiment
  • FIG. 7 shows a cross section along line VII-VII in FIG. 6.
  • the pulse percussion mechanism 10 shown in FIG. 1 has a cup-shaped cylindrical housing part 11 which can be driven in rotation by a drive shaft 12, for example in the direction of rotation of an arrow 13, about a rotation axis 14 common to the components 11, 12.
  • the drive shaft 12 is coupled to a known rotary drive, for example a drive motor of a pulse screwdriver, and has a torsionally rigid connection to the housing part 11 at its end facing away from the drive motor.
  • a stepped, cylindrical receiving opening 15 extends in the axial direction, which is closed on the one hand by a cup base 16 and on the other hand by a cover 17 in a pressure-tight manner.
  • the receiving opening 15 has a smaller inner diameter in an inner section 18 closer to the bowl bottom 16 and a larger inner diameter in an outer section 19 closer to the cover 17.
  • a predominantly cylindrical core part 20 Arranged inside the receiving opening 15 is a predominantly cylindrical core part 20, which at its end facing the cover 17 is coupled in a rotationally fixed manner to an output shaft 21 via a driving device 53 (see also FIG. 2).
  • the core part 20 is designed as a cylindrical reciprocating piston 22 at its end facing the drive shaft 12.
  • the reciprocating piston 22 projects partially into the inner section 18 of the receiving opening 15 and delimits a pressure chamber 24 with its end face 23 facing the cup bottom 16.
  • the reciprocating piston 22 is axially guided in the inner section 18 and is rotatable in the circumferential direction relative to the housing part 11.
  • a suitable sealing device for example a number of sealing grooves 25, is provided between the housing part 11 and the reciprocating piston 22 and seals the pressure chamber 24 to the outer section 19.
  • the sealing device is located between cylindrical components (18, 22), whereby a particularly good sealing effect can be achieved with simple manufacture.
  • Housing part 11 and core part 20 are coupled to one another via a positive control device 28.
  • the forced control device 28 comprises a circumferential annular groove 30 arranged on the outer circumference of the core part 20 as well as a counter body 31 which engages in the housing and is fixed to the housing Project core part 20 and axially limit the annular groove 30.
  • two diametrically opposed counter bodies 31 are provided which are rigidly connected to the housing part 11, for example by means of cylindrical pins 32.
  • the collars 29 carry control tracks 33a, 33b on their opposing collar surfaces, on which the counter-bodies 31 slide in relation to the core part 20 in the circumferential direction when the housing part 11 is rotated.
  • the control path 33a which is closer to the drive shaft 12, has two opposite one another, in the axial direction to the output shaft 21 projecting control cam 34.
  • the control track 33b which is closer to the output shaft 21, has a corresponding course with depressions 35 running parallel to the control cams 34.
  • the counter bodies 31 and the control tracks 33a, 33b have conical jacket-shaped contact surfaces.
  • the cavity located in the outer section 19 between the core part 20 or the output shaft 21 and the housing part 11 forms a low-pressure chamber 36 of the pulse hammer mechanism 10.
  • the low-pressure chamber 36 like the pressure chamber 24, is almost completely filled with a pressure medium.
  • a suitable seal is provided between housing part 11 and output shaft 21, for example by means of a sealing ring 38 seated in a circumferential groove 37.
  • the pressure chamber 24 is connected to the low-pressure chamber 36 via a first connecting line 40 running in the wall of the housing part 11.
  • the first connecting line 40 has a radial outlet piece 41 from the pressure chamber 24 and an axial connecting piece 42 to the low pressure chamber 36.
  • the outlet piece 41 forms a flow opening 43 to the connecting piece 42, which can be more or less closed by means of an aperture 44.
  • the diaphragm 44 can be designed, for example, as a threaded pin which can be adjusted from the outside more or less close to the flow opening 43 using a suitable tool.
  • Flow opening 43 and orifice 44 thus form a control valve 45 with an adjustable valve opening cross section, through which the pressure resistance acting on the reciprocating piston 22 from the pressure medium during the stroke movement can be adjusted.
  • the pressure chamber 24 is connected to the low pressure chamber 36 via a second connecting line 48.
  • the second connecting line 48 likewise runs in the housing part 11 first radially away from the pressure chamber 24 and then axially towards the low-pressure space 36.
  • Check valve 49 arranged so that a backflow of the pressure medium from the pressure chamber 24 into the low pressure chamber 36 is prevented during the pressurization in the pressure chamber 24, on the other hand an inflow of pressure medium from the low pressure chamber 36 into the pressure chamber 24 is possible during the return stroke of the reciprocating piston 22.
  • the check valve 49 comprises, for example, a spherical valve closing body 50, which is acted upon by a closing spring 51 in the direction of the low pressure chamber 36 with a closing force and is pressed against a valve seat 52.
  • FIG. 2 the coupling of the core part 20 to the output shaft 21 by means of the driving device 53 is shown in more detail.
  • the output shaft 21 has at its end facing the core part 20 radially outwardly projecting driving pins 54 which engage in a radially continuous driving groove 55 formed in the core part 20.
  • the driving pins 54 can be formed by means of a transverse rod 56 which is arranged in a radial through-bore of the output shaft 21 and which carries driving sleeves 57 at the end.
  • the driving groove 55 has a sufficiently large one axial length, so that the stroke movement of the core part 20, which is explained below and is forced by the force control device 28, is not transmitted to the output shaft 21 in the axial direction and the rotational entrainment is retained even during this stroke movement.
  • the output shaft 21 carries a known turning tool, for example a screwdriver bit, at its end (not shown in the drawing) which faces away from the pulse hammer mechanism 10. Now the drive shaft 12 and thus the housing part 11 from the rotary drive driven in rotation, when the output shaft 21 is unloaded or only slightly loaded, the core part 20 is driven in rotation as a result of frictional forces. This rotary movement is transmitted to the output shaft 21 via the driving device 53. If the screw-in torque to be tapped at the output shaft 21 exceeds the torque transmitted from the housing part 11 to the core part 20 as a result of the frictional forces, the housing part 11 rotates relative to the core part 20.
  • a known turning tool for example a screwdriver bit
  • the counter bodies 31 slide along the control tracks 33a, 33b until they hit the control cams 34 accrue, which then force the axial lifting movement of the core part 20 and thus of the lifting piston 22 in the direction of the pressure chamber 24.
  • the chamber volume of the pressure chamber 24 is reduced, which results in pressurization of the pressure medium located in the pressure chamber 24, which brings about a corresponding pressure resistance on the lifting piston 22 or the core part 20.
  • a more or less incomplete pressure compensation between the pressure chamber 24 and the low-pressure chamber 36 is possible during the pressurization.
  • FIG. 3 shows a section through a control cam 34 of the control track 33a.
  • the impact force F acting between the counter body 31 and the control cam 34 during the lifting movement can be broken down into an axial force component F ax and a force component in the circumferential direction F U.
  • the force component F ax causes the stroke movement of the core part 20. It counteracts the pressure resistance of the pressure medium described above.
  • the force component in the circumferential direction F U causes a torque on the core part 20 and on the driving device 53 on the output shaft 21.
  • the amount of the impact force F which can be transmitted to the control cams 34 when the counter body 3 runs up depends on the pressure resistance of the pressure medium on the reciprocating piston 22.
  • the print media in the pressure chamber 24 has only a slight pressure resistance on the reciprocating piston 22, so only a small impact force F can be transmitted between the counter body 31 and the control cam 34, as a result of which only a small force component F U acts on the reciprocating piston 22.
  • a large pressure resistance on the reciprocating piston 22 and a sufficiently large momentum of the housing part 11 a large impact force F acts, which causes a correspondingly large force component in the circumferential direction F U (angular momentum).
  • an essentially incompressible fluid for example a hydraulic oil
  • the counter body 31 running with great momentum against the control cams 34 then cause an abrupt angular momentum in the circumferential direction on the output shaft 21. It must be prevented that the piston 22 completely blocks during its stroke movement, which can be achieved by a corresponding adjustment of the control valve 45.
  • the latter After the top dead center of the lifting piston 22 is reached, the latter carries out a return movement forced by the control path 33b. A quantity of pressure medium displaced from the pressure chamber 24 during the pressurization is replaced during the return movement of the reciprocating piston 22 via the second connecting line 48.
  • the chamber volume of the pressure chamber 24 increases, as a result of which negative pressure and thus a suction effect arise in the pressure chamber 24.
  • the check valve 49 Depending on the size of the negative pressure, the check valve 49 then assumes a valve opening position that is dependent on the pretension of the closing spring 51, pressure medium being able to reach the pressure chamber 24 from the low-pressure chamber 36 via the second connecting line 48.
  • FIG. 4 shows a cross section of the pulse hammer mechanism 10 according to line IV-IV in FIG. 1.
  • the hollow cylindrical housing part 11 surrounds the reciprocating piston 22, which towards the pressure chamber 24 (FIG. 1) is designed as a hollow piston with a hollow cylindrical recess 60. Except in the wall of the reciprocating piston 22 is a radially continuous control opening 61 which, with a corresponding opening 62 running radially inward from the first connecting line 40 to the reciprocating piston 22, coincides once per relative rotation of the housing part 11 with the reciprocating piston 22 by 360 ° .
  • the pressure chamber 24 is then connected to the low-pressure chamber 36 via the control opening 61, the opening 62 and the first connecting line 40.
  • FIG. 1 shows a cross section of the pulse hammer mechanism 10 according to line IV-IV in FIG. 1.
  • two further radially continuous compensation openings 63 are arranged approximately opposite the control opening 61.
  • the compensation openings 63 each enclose an angle of approximately 45 ° to a longitudinal axis of the control opening 61 and cause that when pressure builds up in the pressure chamber 24, ie when the control opening 61 is blocked, the housing part 11 acts through the control opening 61 and the compensation openings 63 Media is loaded approximately evenly.
  • FIG. 5 shows a second exemplary embodiment of a pulse hammer mechanism 10 according to the invention.
  • the parts that are the same and have the same effect as the first exemplary embodiment according to FIGS. 1 to 4 are identified by the same reference numerals.
  • the main difference from the first embodiment is that the output shaft 21 and the core part 20 are clamped together in the axial direction by means of the force of a spring 66.
  • a holding tube 67 is rigidly attached in the transverse direction and receives the transverse rod 56.
  • the driving sleeves 57 are arranged, which are rotatably carried along by the tabs 58 in the circumferential direction of the core part 20.
  • the spring 66 is supported on the one hand on the holding tube 67 and on the other hand on an axial locking ring 69 which is seated in an inner groove 68 arranged therein close to the free end of the tabs 58.
  • the bracing causes the driving sleeve 57 to be held in the groove bottom 59 of the driving groove 55. Since the housing part 11 is coupled to the output shaft 21 via an axial support (not shown in FIG. 5) and is therefore not axially displaceable relative to the output shaft 21, the control path 33a facing the reciprocating piston 22 is in constant contact with the counter bodies 31.
  • the control track 33 b facing the output shaft 21 from FIG. 1 can therefore be dispensed with.
  • the bias of the spring 66 is selected so that the stroke movements of the core part 20 are not transmitted to the output shaft 21.
  • the spring 66 can be formed, for example, by slotted disc springs which have a spring stiffness which is matched to the desired pretension.
  • the counter bodies 31 can also be designed as rolling bodies, as a result of which the frictional resistance between the counter bodies 31 and the control track 33 a can be reduced.
  • the already mentioned recess 60 in the reciprocating piston 22 can be clearly seen.
  • the reciprocating piston 22 is shown rotated by 90 ° with respect to the control cam 34, so that the control opening 61 and the two compensation openings 63 are shown in section.
  • the compensation openings 63 are arranged radially opposite and axially offset from the control opening 61.
  • the shown cover position of the control opening 61 and opening 62 is also reached once per relative rotation of the housing part 11 relative to the core part 20 by 360 °, precisely when the counter body 31 runs onto the control cam 34.
  • a control valve 45 and / or check valve 48 can be provided between the pressure chamber 24 and the low pressure chamber 36.
  • FIG. 6 shows a third exemplary embodiment of a pulse hammer mechanism 10 according to the invention.
  • the parts which are the same and have the same effect as the exemplary embodiments according to FIGS. 1 to 4 or FIGS. 5 and 6 are identified by the same reference symbols.
  • the drive shaft 12 drives the housing part 11 to rotate about its axis of rotation 14, for example in the direction of the arrow 13.
  • the housing part 11 encloses a core part 20 'which is rotatable relative to the housing part 11, which is arranged in a receiving opening 15' arranged in the housing part 11 and is integrally formed on the end of the output shaft 21.
  • the receiving opening 15 ' is closed at the end by a cover 17' fixed to the housing.
  • a shaft sealing ring 38 is also provided between the cover 17 'and the output shaft 21.
  • the core part 20 ' there are two diametrically opposite, axial through openings 75, in each of which two reciprocating pistons 22' are inserted.
  • the through openings 75 are connected to one another via a radial bore 76.
  • the reciprocating pistons 22 ' in each case axially pressed away from one another by a compression spring 78 arranged centrally in the through openings 75 and thereby prevented from falling out of the through openings 75 by control tracks 33 ', which are arranged on the housing part 11 or cover 17' opposite the axial end faces of the core part 20 '.
  • Rolling elements 77 which are designed as balls and which reduce the frictional resistance of the positive control device 28 'are preferably arranged between the reciprocating pistons 22' and the control tracks 33 '.
  • the control tracks 33 'and the rolling elements 77 each form a positive control device 28'.
  • the reciprocating pistons 22 ' are axially displaceable and arranged in a sealing manner in the through openings 75 with respect to the core part 20' and delimit a pressure chamber 24 'filled with pressure medium.
  • the rolling elements 77 also roll in the circumferential direction on the control tracks 33'.
  • the control cams 34 ' are arranged with respect to one another in such a way that all the rolling elements 77 run onto the control cams 34' at the same time and in the process move the reciprocating pistons 22 'axially against one another.
  • a pressure resistance is then exerted on the reciprocating pistons 22', which causes a force comparable to the impact force F from FIG. 3 to act on the individual reciprocating pistons 22 ', the circumferential component of which is added to the circumferential force F U which causes the Angular momentum on the output shaft 21 causes.
  • FIG. 7 shows a cross section through the pulse hammer mechanism 10 according to line VII-VII in FIG. 6.
  • the cavity between the core part 20 'and the housing part 11 forms a low-pressure space 36' filled with pressure medium.
  • a cylinder tube 80 is arranged which is rigidly connected to the housing part 11' and therefore rotates with it.
  • the cylinder tube 80 has an opening 62 'which can be seen in FIG. 6 and which is aligned once per revolution with a control opening 61' arranged in the core part 20 '. Since the pressure chamber 24 'extends into the cylinder tube 80, pressure compensation between the pressure chamber 24' and the low-pressure chamber 36 'is then possible via the control opening 61'. In this way it is achieved that, analogously to the previous exemplary embodiments, pressure build-up occurs only once per relative rotation of the housing part 11 relative to the core part 22 'by 360 °.
  • a control valve and / or a check valve can also be arranged between the pressure chamber 24 'and the low pressure chamber 36', which is then formed either in the core part 22 'or in the housing part 11'.
  • the assignment of drive shaft 12 to housing part 11 and output shaft 21 to core part 20 described in the exemplary embodiments according to FIGS. 1 to 4, 5, and 6 and 7; 20 ' is not absolutely necessary, but is advantageous because of the higher moment of inertia and the higher flywheel mass of the housing part 11.
  • the housing part 11 can of course also be completely hollow cylindrical, the receiving opening 15; 15 'then of two opposing covers 17; 17 'is completed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP94108187A 1993-06-24 1994-05-27 Accouplement à impulsion, notamment pour clé à impulsion Ceased EP0631851A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4320903 1993-06-24
DE19934320903 DE4320903A1 (de) 1993-06-24 1993-06-24 Impulsschlagwerk, vorzugsweise für Impulsschrauber

Publications (1)

Publication Number Publication Date
EP0631851A1 true EP0631851A1 (fr) 1995-01-04

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ID=6491054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94108187A Ceased EP0631851A1 (fr) 1993-06-24 1994-05-27 Accouplement à impulsion, notamment pour clé à impulsion

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EP (1) EP0631851A1 (fr)
DE (1) DE4320903A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730947A1 (fr) * 1995-02-25 1996-08-30 Bosch Gmbh Robert Visseuse a impulsion
EP1179395A2 (fr) 2000-08-11 2002-02-13 Uryu Seisaku Limited Générateur d'impulsions de couple pour une clé hydraulique
EP1454715A2 (fr) * 2003-03-07 2004-09-08 Ingersoll-Rand Company Système de commande à clapet inertiel
US11213934B2 (en) 2018-07-18 2022-01-04 Milwaukee Electric Tool Corporation Impulse driver
US11724368B2 (en) 2020-09-28 2023-08-15 Milwaukee Electric Tool Corporation Impulse driver

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3210959A (en) * 1963-05-17 1965-10-12 Ingersoll Rand Co Torque device
EP0186316A1 (fr) * 1984-12-13 1986-07-02 Chicago Pneumatic Tool Company Outil portable à force motrice de type à impulsion
EP0321594A1 (fr) * 1987-12-21 1989-06-28 van Laere, Christiaan G.M. Outil électrorotatif utilisable manuellement en cours de travail, kit comprenant cet outil et interrupteur pour cet outil

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3210959A (en) * 1963-05-17 1965-10-12 Ingersoll Rand Co Torque device
EP0186316A1 (fr) * 1984-12-13 1986-07-02 Chicago Pneumatic Tool Company Outil portable à force motrice de type à impulsion
EP0321594A1 (fr) * 1987-12-21 1989-06-28 van Laere, Christiaan G.M. Outil électrorotatif utilisable manuellement en cours de travail, kit comprenant cet outil et interrupteur pour cet outil

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730947A1 (fr) * 1995-02-25 1996-08-30 Bosch Gmbh Robert Visseuse a impulsion
DE19506663C2 (de) * 1995-02-25 2003-03-06 Bosch Gmbh Robert Impulsschrauber
EP1179395A2 (fr) 2000-08-11 2002-02-13 Uryu Seisaku Limited Générateur d'impulsions de couple pour une clé hydraulique
EP1179395A3 (fr) * 2000-08-11 2003-07-23 Uryu Seisaku Limited Générateur d'impulsions de couple pour une clé hydraulique
EP1454715A2 (fr) * 2003-03-07 2004-09-08 Ingersoll-Rand Company Système de commande à clapet inertiel
EP1454715A3 (fr) * 2003-03-07 2006-01-18 Ingersoll-Rand Company Système de commande à clapet inertiel
US11213934B2 (en) 2018-07-18 2022-01-04 Milwaukee Electric Tool Corporation Impulse driver
US11890726B2 (en) 2018-07-18 2024-02-06 Milwaukee Electric Tool Corporation Impulse driver
US11724368B2 (en) 2020-09-28 2023-08-15 Milwaukee Electric Tool Corporation Impulse driver

Also Published As

Publication number Publication date
DE4320903A1 (de) 1995-01-05

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