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EP0735935A1 - Impulse drive system, especially for an impulse screwdriver - Google Patents

Impulse drive system, especially for an impulse screwdriver

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)
French (fr)
Other versions
EP0735935B1 (en
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/en
Application granted granted Critical
Publication of EP0735935B1 publication Critical patent/EP0735935B1/en
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.

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

Abstract

The impulse drive system (12) has a rotating body (13) connected to a drive spindle (14) in which there is an aperture (16) for a core component (17) concentric with the axis of rotation (15). The core component (17) is fitted to rotate with an output shaft (25). In addition, the rotating body (13) has a radial drilling (18) perpendicular to the axis of rotation (15) in which a piston (19) can move radially. The piston (19) has a through aperture (20) through which the core component (17) can be engaged. With its inner surface facing the core component (17), the piston forms a control surface (36) which co-operates with a control path (37) with control cams (38) formed on the core component (17). During relative rotation of the rotating body (13) and the core component (17), the piston (19) makes a radial stroke. A pressure medium in a pressure chamber (40) is thereby pressurised so that a rotary pulse is transmitted via the control surface (36) and the control path (37) to the output shaft (25).

Description

ImpulsSchlagwerk, insbesondere für ImpulsschrauberImpact mechanism, especially for pulse screwdrivers
Stand der TechnikState of the art
Die Erfindung geht aus von einem Impulsschlagwerk nach der Gattung des Anspruchs 1. Es ist schon ein Impulsschlagwerk bekannt (EP 460 592 AI), bei dem die Drehimpulserzeugung mittels radial nach außen gerichteter, in radialer Richtung beweglicher, federbelasteter Lamellen erfolgt, die zumindest zeitweise Hochdruckräume und benach¬ barte Niederdruckräume dichtend voneinander trennen. Die Lamellen weisen auf ihrer Außenseite speziell geformte Dichtflächen auf, die zur Vermeidung von Leckageverlusten möglichst genau herzustellen sind, was einen relativ hohen fertigungstechnischen Aufwand erfor¬ dert.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.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Impulsschlagwerk mit den kennzeichnenden Merk¬ malen des Anspruchs 1 hat demgegenüber den Vorteil, wesentlich ein¬ facher und genauer herstellbare rotationssymmetrische Dichtflächen aufzuweisen, wodurch fertigungsbedingte Maß- und/oder Formabweichun¬ gen und damit einhergehende Leckageverluste reduzierbar sind. Durch Ausbildung des Impulsschlagwerks mit wenigstens einem in radialer Richtung wirkenden Hubkolben läßt sich eine kompakte Bauweise in axialer Richtung erzielen. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vor¬ teilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 ange¬ gebenen Impulsschlagwerks möglich.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.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt eines ersten Ausführungsbeispiels eines erfindungsgemäß ausgebildeten Impulsschlagwerks, Figur 2 einen Quer¬ schnitt gemäß Linie II-II in Figur 1, die Figuren 3 und 4 jeweils Querschnitte durch zwei weitere Ausführungsbeispiele eines Impuls¬ schlagwerks, die Figuren 5, 6 und 7 ein viertes Ausführungsbeispiel, Figur 8 einen Querschnitt durch ein fünftes Ausführungsbeispiel, Figur 9 einen Längsschnitt durch ein sechstes Ausf hrungsbeispiel und Figur 10 einen Querschnitt gemäß Linie X-X in Figur 9.Embodiments of the invention are shown in the drawing and explained in more detail in the following description. 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 and FIG. 10 shows a cross section along line XX in FIG. 9.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Das in Figur 1 dargestellte Impulsschlagwerk weist einen zylindri¬ schen Rotationskörper 13 auf, der über eine Antriebswelle 14 mit Hilfe eines nicht näher dargestellten Antriebsmotors um eine Dreh¬ achse 15 beispielsweise in Richtung eines Pfeiles 15a drehend an¬ treibbar ist. Der Rotationskörper 13 hat an seinem der Antriebwelle 14 abgewandten Ende eine den Rotationskörper 13 fast vollständig durchziehende zentrale Aufnahmeöffnung 16, in der ein zylindrisches Kernteil 17 konzentrisch angeordnet ist. Senkrecht zur Drehachse 15 befindet sich etwa mittig im Rotationskörper 13 eine Radialbohrung 18, in der ein Hubkolben 19 radial verschiebbar aufgenommen ist. Im Hubkolben 19 befindet sich eine Durchgangsöffnung 20, die sich quer zur Hubrichtung des Hubkolbens 19 in axialer Richtung erstreckt und in der das Kernteil 17 mit Spiel den Hubkolben 19 durchragt. Die Radialbohrung 18 ist durch einen Deckel 21 verschließbar und mittels geeigneter Dichtmittel 22 nach außen hin abgedichtet.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. 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. Perpendicular to the axis of rotation 15, there is a radial bore 18 approximately in the center of the rotating body 13, in which a reciprocating piston 19 is received in a radially displaceable manner. In 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.
Das Kernteil 17 ist drehschlüssig mit einer Abtriebswelle 25 gekop¬ pelt, die endseitig mit einer Befestigungseinrichtung für ein Schraubwerkzeug, beispielsweise für ein Schrauberbit, versehen ist. Kernteil 17 und Abtriebswelle 25 sind im Beispielsfall einstückig miteinander verbunden. Das Kernteil 17 ist endseitig an der Ab¬ triebswelle 25 ausgebildet. Kernteil 17 bzw. Abtriebswelle 25 sind in der Aufnah eöffnung 16 in Umf ngsrichtung gegenüber dem Rota¬ tionskörper 13 verdrehbar gelagert. Im Ausführungsbeispiel erfolgt die Lagerung in Gleitsitzen 27 und 28 jeweils seitlich der Radial¬ bohrung 18. Ein näher zur Befestigungseinrichtung 26 gelegener Gleitsitz 28 wird durch zwei axial versetzt zueinander angeordnete Ringbünde 29 und 30 des Kernteils 17 gebildet, zwischen denen ein Dichtring 31 in einer Ringnut 32 sitzt, der die Aufnahmeöffnung 16 nach außen hin abgedichtet. Das Kernteil 17 ist innerhalb des Rota¬ tionskörpers 13 durch einen Sicherungsring 33 in axialer Richtung festgelegt.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. In the exemplary embodiment, 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.
Der Hubkolben 19 wird mittels einer Rückstellfeder 35 in Richtung auf den Deckel 21 mit Federkraft beaufschlagt und gegen einen am Deckel 21 nach radial innen verspringenden Anschlag 34 gedrückt ge¬ halten. Der Hubkolben 19 bildet innerhalb der Durchgangsöffnung 20 eine als Steuermittel wirkende umlaufende Steuerfläche 36, die mit einer am Kernteil 17 im Bereich der Radialbohrung 18 angeordneten Steuerbahn 37 zusammenwirkt. Im Ausführungsbeispiel hat die Steuer¬ bahn 37 einen nahezu zylindrischen Querschnitt mit einem radial vor¬ stehenden, leistenförmigen Steuemocken 38.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. In the exemplary embodiment, the control track 37 has an almost cylindrical cross section with a radially projecting, strip-shaped control cam 38.
Innerhalb des Rotationskörpers 13 verbleibende Hohlräume sind nahezu vollständig mit einem im wesentlichen inko pressiblen Druckmedium, beispielsweise einem Hydrauliköl, gefüllt. Der Hubkolben 19 trennt eine am Grund der Radialbohrung 18 liegende Druckkammer 40 von einem Niederdruckraum 41. Der Niederdruckraum 41 erstreckt sich im wesentlichen über zwei Teilbereiche, innerhalb der Durchgangsöff¬ nung 20 zwischen Kernteil 17 und Rotationskörper 13, sowie zwischen dem Hubkolben 19 und dem Deckel 21. Beide Teilbereiche stehen über eine Ausgleichsleitung 24 miteinander in Verbindung. Die der Druck¬ kammer 40 zugewandte Kolbenfläche des Hubkolbens 19 bildet eine Ar¬ beitsfläche 39.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.
Die Druckkammer 40 ist über eine im Rotationskörper 13 verlaufende erste Verbindungsleitung 42 mit dem Niederdruckraum 41 verbunden. In der ersten Verbindungsleitung 42 ist ein einstellbares Steuerventil 43 angeordnet, mit dessen Hilfe ein Uberströmguerschnitt 44 zur er¬ sten Verbindungsleitung 42 steuerbar ist. Das Steuerventil 43 wird beispielsweise von einem axial verschiebbaren Gewindestift 45 mit Kegelspitze gebildet. Eine am Außenumfang des Gewindestiftes 45 an¬ geordnete Dichtung 46 verhindert, daß Druckmedium am Gewindestift 45 vorbei nach außen gelangt.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.
Eine zweite Verbindungsleitung 47 ist im Hubkolben 19 zwischen Nie¬ derdruckraum 41 und Druckkammer 40 ausgebildet. Die zweite Verbin¬ dungsleitung 47 erstreckt sich radial von der Steuerfläche 36 zur Arbeitsfläche 39 des Hubkolbens 19. In der zweiten Verbindungslei¬ tung 50 ist ein Rückströmventil 48 angeordnet, das bei Druck in der Druckkammer 40 in Richtung zum Niederdruckraum 41 sperrt und in um¬ gekehrter Richtung bei entsprechendem Unterdruck in der Druckkammer 40 ein Rückströmen von Druckmedium zuläßt. Aus Figur 2 ist erkenn¬ bar, daß das Rückströmventil 48 als Rückschlagventil ausgebildet ist und einen kugelförmigen Ventilschließkörper 49 aufweist, der von ei¬ ner Ventilschließfeder 50 mit Federkraft in Richtung auf den Nieder¬ druckraum 41 beaufschlagt ist. Die Ventilschließfeder 50 stützt sich dabei an einem fest mit dem Hubkolben verbundenen Stützring 51 ab. In Figur 2 ist der zylindrische Aufbau des Rotationskörpers 13 er¬ kennbar. In der Radialbohrung 18 ist der ebenfalls rotationssymme¬ trische Hubkolben 19 angeordnet. Im Hubkolben 19 befindet sich zen¬ tral die Durchgangsöffnung 20, die vom Kernteil 17 durchragt wird. In Figur 2 ist das Kernteil 17 gegenüber der in Figur 1 gezeigten Lage um ca. 30° entgegen der Pfeilrichtung 15a gedreht. Die Steuer¬ fläche 36 ist aus zwei jeweils etwa halbkreisförmigen Teilflächen 36a, 36b zusammengesetzt. Die näher zum Deckel 21 gelegene erste Teilfläche 36a weist einen größeren radialen Abstand zur Drehachse 15 auf, als die ihr gegenüberliegende, näher zur Druckkammer 40 ge¬ legene zweite Teilfläche 36b. Der radiale Abstand der zweiten Teil¬ fläche 36b zur Drehachse 15 ist dabei geringer, als der radiale Ab¬ stand des Steuernockens 38. Etwa senkrecht zur Drehachse 15 und zur Eubrichtung des Hubkolbens 19 sind die Teilflächen 36a und 36b durch etwa radial verlaufende Absatzflächen 54 und 55 miteinander verbun¬ den.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. In the second connecting line 50, 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. From Figure 2 is recognizable ¬ bar, that the return valve 48 is formed as a check valve and having a spherical valve closing body 49, the pressure chamber of egg ¬ ner valve closing spring 50 with spring force in the direction of the Nieder¬ is acted 41st The valve closing spring 50 is supported on a support ring 51 fixedly connected to the reciprocating piston. The cylindrical structure of the rotating body 13 can be seen in FIG. The likewise rotationally symmetrical reciprocating piston 19 is arranged in the radial bore 18. The through opening 20, which is penetrated by the core part 17, is located centrally in the reciprocating piston 19. In FIG. 2, the core part 17 is rotated by approximately 30 ° against the direction of the arrow 15a compared to the position shown in FIG. 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.
Im Leerlauf des ImpulsSchlagwerks 12 dreht das Kernteil 17 aufgrund von Reibungseinflüssen mit dem Rotationskörper 13 mit. Übersteigt das beim Einschrauben an der Befestigungseinrichtung 26 wirkende Drehmoment das Reibmoment, so wird sich der Rotationskörper 13 ge¬ genüber dem Kernteil 17 verdrehen. Das Kernteil 17 dreht dann lang¬ samer als der Rotationskörper 13.When the pulse hammer mechanism 12 is idling, 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.
Kommt es aus der gezeigten Position zu einer Relativverdrehung von Rotationskörper 13 und Kernteil 17, beispielsweise indem der Rota¬ tionskörper 13 gegenüber dem Kernteil 17 in Pfeilrichtung 15a wei¬ terdreht, so gelangt der Steuernocken 38 des Kernteils 17 schlie߬ lich zur Anlage an die Absatzflache 55. Je nach Größe des wirksamen Drehmoments wird sich dann der Hubkolben 19 entgegen der Kraft der Rückstellfeder 35 unter Verkleinerung des Volumens der Druckkammer 40 verschieben und dabei einen Drehimpuls auf die Befestigungsein¬ richtung 26 ausüben. Nach Überwindung der Absatzfläche 55 kann der Steuernocken 38 entlang der zweiten Teilfläche 36b gleiten, bis er nach einer weiteren halben Relatiwerdrehung nach Durchlaufen der zweiten Teilfläche 36b den Hubkolben 19 wieder freigibt. Der Hubkol¬ ben 19 wird dann von der Rückstellfeder 35 aus seiner Hubstellung wieder zur Anlage an den Anschlag 34 gebracht. Nach Durchlaufen der weiteren halben Relatiwerschiebung gelangt der Steuernocken 38 zur Erzeugung eines weiteren Drehimpulses erneut zur Anlage an die Ab¬ satzfläche 55. Aufgrund der symmetrischen Ausbildung der Steuerflä¬ che 36 und der Steuerbahn 37 ist das ImpulsSchlagwerk 12 auch in um¬ gekehrter Antriebsrichtung betreibbar.If there is a relative rotation of the rotary body 13 and the core part 17 from the position shown, for example in that the rotary body 13 rotates further in the direction of the arrow 15a relative to the core part 17, the control cam 38 of the core part 17 finally comes to rest against the sales surface 55. Depending on the size of the effective torque, the reciprocating piston 19 will then move against the force of the return spring 35 while reducing the volume of the pressure chamber 40 and in doing so exert an angular momentum on the fastening device 26. After overcoming the sales area 55 the control cam 38 slide along the second partial surface 36b until after another half a relative rotation after passing through the second partial surface 36b it releases the reciprocating piston 19 again. The reciprocating piston 19 is then brought from the stroke position back into abutment against the stop 34 by the return spring 35. After passing through the further half of the relative shift, 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.
Während der Volumenverkleinerung der Druckkammer 40 wird von der Ar¬ beitsfläche 39 ein Druck auf das Druckmedium ausgeübt. Über an der Außenfläche des Hubkolbens 19 angeordnete Überströmnuter. 56 und über entsprechende, diesen gegenüberliegende Aussparungen im Rotations¬ körper 13 im Bereich der Radialbohrung 18 kann zunächst Druckmedium zum Niederdruckraum 41 gelangen. Die Uberströmnut 56 und die Aus¬ sparung 57 bilden zusammen einen Uberströmkanal von der Druckkammer 40 zum Niederdruckraum 41. In der Uberströmnut 56 und innerhalb der Aussparung 57 sind sich axial erstreckende Dichtleisten 53, 59 an¬ geordnet, die bei zunehmender Hubbewegung des Hubkolbens 19 mitein¬ ander in Deckung kommen. Ist dies der Fall, so wird die Druckkammer 40 schlagartig abgedichtet. Je nach Größe des einstellbaren Über¬ strömquerschnitts am Steuerventil 43 wirkt dann auf den Kubkolben 19 ein mehr oder weniger großer Druckwiderstand. Das Rückschlagventil 48 ist dabei gesperrt. Der Überströmquerschnitt muß so gewählt wer¬ den, daß ein Blockieren des ImpulsSchlagwerkes 12 vermieden wird. Wirkt in der Druckkammer 40 ein erhöhter Druckwiderstand, so wird über die Steuerfläche 36 und den Steuernocken 38 ein entsprechend starker Drehimpuls auf das Kernteil 13 übertragen. Aufgrund der relativ großen Schwungmasse des Rotationskörpers 13 und des mit diesem gekoppelten Antriebsstranges können relativ große Drehimpulse erzielt werden, ohne daß das Impulsschlagwerk 12 blockiert. Bei der anschließenden Volumenvergrößerung der Druckkam¬ mer 40 nach Durchlaufen der Teilfläche 36b kann Druckmedium infolge des damit einhergehenden Unterdrucks in der Druckkammer 40 über das Rückströmventil 48 nachströmen.During the volume reduction of the pressure chamber 40, a pressure is exerted on the pressure medium by the working surface 39. 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. Depending on the size of the adjustable overflow cross section on the control valve 43, 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. When the volume of the pressure chamber 40 subsequently increases after passing through the sub-area 36b, pressure medium can flow in via the backflow valve 48 as a result of the associated negative pressure in the pressure chamber 40.
In Figur 3 ist ein zweites Ausführungsbeispiel des Impulsschlagwer¬ kes 12 dargestellt. Gegenüber dem ersten Ausführungsbeispiel nach den Figuren 1 und 2 gleiche und gleichwirkende Teile sind durch gleiche Bezugszeichen gekennzeichnet. Auch hier ist ein einzelner Hubkolben 19 in der Radialbohrung 18 aufgenommen. Hauptunterschied zum ersten Ausf hrungsbeispiel ist die Anordnung einer Dämpfungsfe¬ der 60 zwischen Hubkolben 19 und Deckel 21. Die Dämpfungsfeder 60 ist als Druckfeder ausgebildet. Die Dämpfungsfeder 60 hat die Aufga¬ be, beim Rückhub des Kubkolbens 19 einen Aufprall des Hubkolbens 19 gegen den Absatz 34 zu verhindern bzw. zu dämpfen. Außerdem unter- . stützt die Dämpfungsfeder 60 einen klemmfreien Durchlauf des Steuer¬ nockens 38 an der Teilfläche 36b. Der Radius der ersten Teilfläche 36a der Steuerfläche 36 enspricht etwa dem des Steuernockens 38. Die Dämpfungsfeder 60 beaufschlagt den Hubkolben 19 in Richtung auf die Druckkammer 40 und bewirkt, daß Steuernocken 38 und erste Teilfläche 36a aneinander anliegen.FIG. 3 shows a second exemplary embodiment of the pulse hammer 12. Compared to the first exemplary embodiment according to FIGS. 1 and 2, parts that are the same and have the same effect are identified by the same reference numerals. Here, too, 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.
Die Rückstellung des Hubkolbens 19 aus der Hubstellung in die ge¬ zeigte Ausgangsstellung erfolgt in diesem Fall selbsttätig durch das unter Druck stehende Druckmedium in der Druckkammer 40 und wird un¬ terstützt durch das Durchlaufen des Steuernocken 38 an der ersten Teilfläche 36a. Auf die Rückstellfeder kann daher verzichtet werden. Die Ventilschließfeder 50 des Rückströmventils 48 stützt sich bei dieser Ausführung am Grund der Radialbohrung 18 ab. Die Dichtleisten 58, 59 haben in der gezeigten Grundstellung einen geringen Abstand voneinander, so daß ein geringer Hub zum Schließen der Druckkammer 40 ausreicht. In Figur 4 ist ein drittes Ausführungsbeispiel des Impulsschlagwerks 12 dargestellt. Gegenüber dem ersten bzw. dem zweiten Ausführungs¬ beispiel gleiche und gleichwirkende Teile sind ebenfalls durch glei¬ che Bezugszeichen gekennzeichnet. Auch hier ist keine zusätzliche Rückstellfeder 35 für den Hubkolben 19 vorhanden, da die Rückstel¬ lung über die erste Teilfläche 36a erfolgt. Im Gegensatz zu den vor¬ hergehenden Ausführungsbeispielen ist die Steuerfläche 36 ohne Ab¬ satzflächen ausgebildet. Während die erste Teilfläche 36a etwa den gleichen Radius wie der Steuernocken 38 hat, verläuft die zweite Teilfläche 36b mit unterschiedlichem Radius, der in Umlaufrichtung des Steuernockens 38 ausgehend vom Radius des Steuernockens 38 in einen dem Radius des Kernteils 17 entsprechenden Radius und an¬ schließend wieder in den Radius des Steuernockens 38 übergeht. Die zweite Teilfläche 36b hat dabei einen bogenförmigen Verlauf, der an den Außenumfang des Kernteils 17 stark angepaßt ist, so daß der Kub¬ kolben 19 in der gezeigten Grundstellung großflächig an der Steuer¬ bahn 37 anliegt.In this case, the return of the lifting piston 19 from the lifting position into the shown starting position takes place automatically through the pressurized pressure medium in the pressure chamber 40 and is supported by the passage of the control cam 38 on the first partial surface 36a. The return spring can therefore be dispensed with. In this embodiment, the valve closing spring 50 of the backflow valve 48 is supported on the bottom of the radial bore 18. In the basic position shown, the sealing strips 58, 59 are at a short distance from one another, so that a short stroke is sufficient to close the pressure chamber 40. 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. Here, too, there is no additional return spring 35 for the reciprocating piston 19, since the reset takes place via the first partial surface 36a. In contrast to the previous exemplary embodiments, 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.
Die Steuerbahn 37 bildet demnach einen Anschlag für die zweite Teil¬ fläche 36b beim Rückhub des Hubkolbens 19. Zwischen Hubkolben 19 und Deckel 21 ist in der Grundstellung ein Spalt 61 vorhanden, so daß auf eine den Rückschlag gegen den Deckel 21 abfedernde Dämpfungsfe¬ der verzichtet werden kann. Auch eine Ventilschließfeder wird hier nicht benötigt, da der Ventilschließkörper 49 vom Druck des Druck¬ mediums in der Druckkammer 40 geschlossen wird. Ein Sicherungsring 52 verhindert das Herauswandern des Ventilschließkörpers 49 in die Druckkammer 40.The control track 37 accordingly forms a stop for the second partial surface 36b during the return stroke of the reciprocating piston 19. In the basic position, 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.
In den Figuren 5, 6 und 7 ist ein viertes Ausführungsbeispiel darge¬ stellt. Im Gegensatz zu den vorhergehenden Ausführungsbeispielen sind bei diesem und bei den beiden folgenden Ausführungen zwei Hub¬ kolben in der Radialbohrung angeordnet. Gegenüber den vorhergehenden Ausführungsbeispielen gleiche und gleichwirkende Teile sind bei al¬ len folgenden Ausführungen mit zwei Kolben durch ein um 100 erhöhtes Bezugszeichen gekennzeichnet. Ein zylindrischer Rotationskörper 113 ist über eine Antriebswelle 114 um eine Drehachse 115 drehend antreibbar. Innerhalb einer axia¬ len Aufnahmeöffnung 116 ist ein Kernteil 117 angeordnet, das dreh¬ schlüssig und axial fluchtend mit einer Abtriebswelle 125 verbunden ist. Die Abtriebswelle 125 trägt endseitig eine Befestigungseinrich¬ tung 126 zum Aufstecken eines Drehwerkzeugs. Im Rotationskörper 113 ist eine durchgehende Radialbohrung 118 ausgebildet. In der Radial- bohrung 118 sind zwei Hubkolben 119a, 119b aufgenommen. Nach außen hin wird die Radialbohrung 118 von einem topfartig geformten Gehäu¬ seteil 170 beidseitig abgeschlossen. Zwischen Rotationskörper 113 und Gehäuseteil 170 sind Dichtmittel 171, 172 vorgesehen. Gehäuse¬ teil 170 und Rotationskörper sind drehfest miteinander verbunden. Die Hubkolben 119 trennen eine radial außen liegende Druckkammer 140 von einer Niederdruckkammer 141. Der Niederdruckraum 141 ist um eine axial versetzt zur Radialbohrung 118 im Rotationskörper 113 angeord¬ nete, umlaufende Ringkammer 181 erweitert.A fourth exemplary embodiment is shown in FIGS. 5, 6 and 7. In contrast to the previous exemplary embodiments, 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. To the outside, 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.
Wie aus der Figur 6 entnehmbar ist, hat das Kernteil 117 einen etwa doppelbogenförmigen spiegelsymmetrischen Querschnitt. Jeder Boge ab- schnitt der Steuerbahn 137 hat einen kontinuierlichen Übergang von einem großen radialen Abstand zur Drehachse 115 über einen kleinen radialen Abstand zu einem entsprechend großen radialen Abstand. Am Hubkolben 119 ausgebildete, mit der Steuerbahn 138 korrespondieren¬ de, als Steuermittel wirkende Steuerflächen 136a, 136b sind eben ausgebildet. An radial außen liegenden Arbeitsflächen 139a, 139b der Hubkolben 119a, 119b befinden sich Aufnahmebohrungen 169 für Rück¬ stellfedern 135, die sich einerseits an den Hubkolben 119 und ande¬ rerseits am Gehäuseteil 170 abstützen. In Figur 6 sind die Hubkolben jeweils in Hubstellung im radial äußeren Umkehrpunkt dargestellt. Bei einer weiteren Verdrehung des Rotationskörpers 113 gegenüber dem Kernteil 117 können die Hubkolben 119 entlang der Steuerbahn 137 nach radial innen zurückwandern. In Figur 7 wurde das ImpulsSchlagwerk 112 aus Figur 5 um 90° in die Zeichenebene verdreht. Dabei ist erkennbar, daß zwischen Gehäuseteil 170 und Rotationskörper 113 am Außenmantel des Rotationskörpers 113 eine in Umfangsrichtung umlaufende Ringnut 173 angeordnet ist, die die von den Hubkolben 119 begrenzte Hochdruckräume 140 miteinander verbindet. Das bei der Hubbewegung nach radial außen unter Druck stehende Druckmedium kann über eine erste Verbindungsleitung 142 mit darin angeordnetem Steuerventil 143 zur Ringkammer 181 des Nieder¬ druckraums 141 strömen. Das Steuerventil 143 ist dabei in einer axialen Gewindebohrung im Rotationskörper 113 angeordnet. Die erste Verbindungsleitung 142 erstreckt sich zunächst in radialer Richtung nach innen aus der Ringnut 173 heraus zum Steuerventil 143 und an¬ schließend axial zur Ringkammer 181.As can be seen from FIG. 6, 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. On radially outer working surfaces 139a, 139b of the reciprocating pistons 119a, 119b there are receiving bores 169 for return springs 135 which are supported on the one hand on the reciprocating pistons 119 and on the other hand on the housing part 170. In Figure 6, the reciprocating pistons are each shown in the stroke position in the radially outer reversal point. When the rotary body 113 is rotated further relative to the core part 117, the reciprocating pistons 119 can move back radially inward along the control path 137. In FIG. 7, 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.
In der um 180° zum Steuerventil 143 versetzten Schnitthälfte ver¬ läuft eine radial nach schräg innen zum Wellenlager 127 verlaufende Bohrung 174. Die Bohrung 174 wird von einer Axialbohrung 175 ge¬ schnitten, die den Rotationskörper 113 vollständig durchdringt. Das abtriebsseitige Ende der Axialbohrung 175 ist mittels eines Gewin¬ destopfens 176 und zugehöriger Dichtmittel 177 abgedichtet. Der an- triebsseitige Teil der Zusatzbohrung 175 mündet in die Ringkammer 181 des Niederdruckraums 141. Der axiale Bereich zwischen Eohrung 174 und Niederdruckraum 141 der Zusatzbohrung 175 bildet eine zweite Verbindungsleitung 147, in der ein Rückströmventil 148 angeordnet ist. Eine zugehörige Ventilschließfeder 149 des Rückströmventils 148 stützt sich einerseits am Gewindstopfen 176, andererseits am Ventil¬ schließkörper 149 ab.In the half of the cut offset by 180 ° to the control valve 143, 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.
Im Kernteil 117 befindet sich ein axialer Kanal 178, der über einen durchgehenden Radialkanal 179 mit dem sich zwischen den Steuerflä¬ chen 136 und der Steuerbahn 137 befindlichen Teil des Niederdruck- raums 141 in Verbindung steht. In axialer Richtung durchzieht der Kanal 178 das Kernteil 117 bis zu dessen antriebsseitigen Ende. Dort steht er über einen im Rotationskörper 113 radial durchgehenden Querkanal 180 mit der Ringkammer 181 in Verbindung. Im Bereich des Wellenlagers 127 befindet sich im Kernteil 117 eine einseitig offene Steuerbohrung 182 zum Kanal 178, die einmal pro vollständiger Rela¬ tivverdrehung von Kernteil 117 zu Rotationskörper 113 mit der Mün¬ dung der Bohrung 174 in Deckung kommt. Dann ist die Druckkammer 140 über die Bohrung 174, die Steuerbohrung 182 und den Kanal 178 mit dem Niederdruckraum 141 verbunden, so daß sich in der Druckkammer 140 kein nennenswerter Druck aufbaut. Bei einer weiteren Verdrehung um 180°, bei der die Hubkolben 119a, 119b ebenfalls in ihrer äußeren Hubstellung stehen, ist die Verbindung zwischen Bohrung 174 und Steuerbohrung 182 unterbrochen, so daß sich dann in der Druckkammer 140 Druck aufbauen kann. Auf diese Weise wird erreicht, daß jeweils nur einmal pro Relativverdrehung von Rotationskörper 113 und Kern¬ teil 117 ein Impuls entsteht, wodurch eine größere Schwungenergie zwischen den einzelnen Impulsen aufgebaut werden kann.In 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. Then 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. With a further rotation through 180 °, in which the reciprocating pistons 119a, 119b are also in their outer stroke position, 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.
In Figur 8 ist ein fünftes Ausführungsbeispiel gezeigt, mit gegen¬ über dem Ausführungsbeispiel gemäß den Figuren 5, 6 und 7 geänderten Berührungsflächen von Hubkolben 119a, 119b mit der Steuerbahn 137. Die Steuerbahn 137 des Kernteils 117 ist hier überwiegend zylin¬ drisch ausgebildet. Am Außenumfang des Kernteils 117 sind nicht dar¬ gestellt um 180° zueinander versetzt zwei Steuernocken 138 angeord¬ net. Die Steuernocken 138 werden beispielsweise durch Wälzkörper 184 gebildet, die am Kernteil 117 in U fangsrichtung fest, jedoch um ihre Längsachse verdrehbar gehaltert sind. Die Steuernocken 138 ar¬ beiten zusammen mit entsprechend um 180° versetzten, in den Steuer¬ flächen 136 der Hubkolben 119 gelagerten Walzen 183, die anstelle der Steuerflächen 136 als Steuermittel wirken. Auf diese Weise kön¬ nen die Reibkräfte zwischen der Steuerbahn 137 und der Steuerfläche 136 verringert werden. In der oberen Bildhälfte der Figur 8 ist das Impulsschlagwerk 112 in der Grundstellung und in der unteren Bildhälfte in seiner äußeren Hubstellung dargestellt. Auch bei den anderen Ausführungsformen des Impulsschlagwerkes 12, 112 können in den Steuerflächen 36, 136 und/oder den Steuerbahnen 37, 137 Wälzkör¬ per 183, 184 zur Verringerung des Reibwiderstandes vorgesehen wer¬ den. Insbesondere kann der Steuernocken 38 des Impulsschlagwrekes 12 als Wälzkörper ausgebildet sein.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. On the outer circumference of the core part 117, 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. In this way, the frictional forces between the control track 137 and the control surface 136 can be reduced. In the upper half of FIG. 8, 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. Also in the other embodiments of the pulse hammer mechanism 12, 112, 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. In particular, the control cam 38 of the impulse impact wrench 12 can be designed as a rolling element.
In Figur 9 und 10 ist ein weiteres Ausführungsbeispiel des Impuls¬ schlagwerks 112 dargestellt, bei dem die Hubkolben 119a, 119b über eine Zwangssteuerung 185 in Hubrichtung verstellt werden. In der ab- triebsseitigen Seitenwand der Hubkolben 119 sind Zylinderstifte 186a, 186b gehaltert, die in eine mit dem Kerteil 117 umlaufende Steuernut 187 greifen. Die Steuernut 187 hat in Umlaufrichtung des Kernteils 117 einen veränderlichen radialen Abstand zur Drehachse 115, so daß je nach Drehwinkelstellung zwischen Rotationskörper 113 und Kernteil 117 die Hubstellung der Kubkolben 119a, 119b verändert wird. Die Steuernut 187 hat einen symmetrischen Verlauf, so daß die beiden Hubkolben 119 jeweils gleichzeitig ihre äußere bzw. innere Hubstellung erreichen. In der -oberen Bildhälfte der Figur 9 ist die radial äußere Hubstellung des Hubkolbens 119a gezeigt, in der unte¬ ren Bildhälfte die um 90° versetzt dazu erreichbare radial innere Hubstellung des Hubkolbens 119b.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.
In Figur 10 ist die Steuernut 187 im Schnitt dargestellt. Sie hat, einen etwa doppelbogenförmigen Verlauf, entsprechend der Steuerbahn 137 in Figur 6. In die Steuernut 187 greifen die beiden Zylinder¬ stifte 186 ein. Über die radial weiter außen liegende Nutwand 187a werden die Hubkolben aus ihrer radial äußeren Position nach innen gestellt. Mittels der inneren Seitenwand 187b werden sie entspre¬ chend nach außen verstellt. Bei der Ausführung mit Zwangssteuerein¬ richtung 185 sind Rückstellfedern für die Hubkolben 119a, 119b nicht erforderlich. Hochdruckraum bzw. Druckkammer sowie Niederdruckraum und Ringkammer als Erweiterung sind in den Ausführungsbeispielen nach den Figuren 8 bis 10 prinzipiell entsprechend dem Beispiel nach den Figuren 5 bis 7 ausgebildet. Die in den Ausführungsbeispielen beschriebene Zuord¬ nung von Antriebswelle 14 zum Rotationskörper 13 und von der Ab¬ triebswelle 25 zum Kernteil 17 ist nicht zwingend, wegen des höheren Flächenträgheitsmomentes des Rotationskörpers 13 und der somit höhe¬ ren Schwungmasse des Antriebs jedoch vorteilhaft. In Figure 10, the control groove 187 is shown in section. She has an approximately double-curved shape, according to the control path 137 in Figure 6. 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. In the version with positive control device 185, 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.

Claims

Ansprüche Expectations
1. Impulsschlagwerk insbesondere für Impulsschrauber, mit einem an- oder abgetriebenen, um eine Drehachse (15, 115) des Impuls- εchlagwerks (12, 112) drehbaren Rotationskörper (13, 113), der eine sich axial erstreckende, zentrale Aufnahme ffnung (16, 116) auf¬ weist, und mit einem zum Abtrieb oder Antrieb führenden Kernteil (17, 117), das innerhalb der Aufnahmeöffnung (16, 116) relativ zum Rotationskörper (13, 113) verdrehbar angeordnet ist, dadurch gekenn¬ zeichnet, daß im Rotationskörper (13, 113) wenigstens eine senkrecht zur Drehachse (15, 115) verlaufende Radialbohrung (18, 118) vorge¬ sehen ist, in der wenigstens ein Hubkolben (19, 119a, 119b) radial verschiebbar aufgenommen ist, welcher Hubkolben (19, 119a, 119b) stirnseitig eine Arbeitsfläche (39, 139) und im Bereich des Kerntei¬ les (17, 117) liegende Steuermittel (36, 136) hat, wobei die Steuer¬ mittel (36, 136) mit wenigstens einer mit dem Kernteil (17, 117) • verbundenen umlaufenden Steuerbahn (37, 137) zusammenwirken, welche in Umlaufrichtung des Kernteils (17, 117) einen wechselnden radialen Abstand zur Drehachse (15, 115) zur Erzeugung einer Radialverschie¬ bung des Hubkolbens (19, 119a, 119b) aufweist, durch die über die Arbeitsfläche (39, 139) ein in einer Druckkammer (40, 140) befindli¬ ches Druckmedium mit Druck beaufschlagbar ist. 1. Impulse percussion mechanism, in particular for impulse screwdrivers, with a driven or driven rotary body (13, 113) rotatable about an axis of rotation (15, 115) of the pulse percussion mechanism (12, 112), which has an axially extending, central receiving opening (16 , 116) and with a core part (17, 117) leading to the output or drive, which is rotatably arranged within the receiving opening (16, 116) relative to the rotary body (13, 113), characterized in that in Rotary body (13, 113) at least one radial bore (18, 118) running perpendicular to the axis of rotation (15, 115) is provided, in which at least one reciprocating piston (19, 119a, 119b) is received, which reciprocating piston (19, 119a, 119b) has a working surface (39, 139) on the end face and control means (36, 136) located in the area of the core part (17, 117), the control means (36, 136) being connected to the core part ( 17, 117) • connected orbiting control track (37, 137) together acting in the direction of rotation of the core part (17, 117) at an alternating radial distance from the axis of rotation (15, 115) to produce a radial displacement of the reciprocating piston (19, 119a, 119b), through which the working surface (39, 139) a pressure medium located in a pressure chamber (40, 140) can be pressurized.
2. Impulsschlagwerk nach Anspruch 1, dadurch gekennzeichnet, daß der Rotationskörper (13, 113) mit einer Antriebswelle (14, 114) und das Kernteil (17, 117) mit einer Abtriebswelle (25, 125) des Impuls¬ schlagwerks (12, 112) drehschlüssig verbunden sind.2. Pulse hammer mechanism according to claim 1, characterized in that the rotary body (13, 113) with an input shaft (14, 114) and the core part (17, 117) with an output shaft (25, 125) of the pulse hammer mechanism (12, 112 ) are rotationally connected.
3. Impulsschlagwerk nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Druckkammer (40, 140) über eine erste Verbindungsleitung (42, 142) mit einem Niederdruckraum (41, 141) verbunden ist, wobei in der ersten Verbindungsleitung (42, 142) ein Steuerventil (43,3. Impact mechanism according to claim 1 or 2, characterized in that the pressure chamber (40, 140) via a first connecting line (42, 142) with a low pressure chamber (41, 141) is connected, wherein in the first connecting line (42, 142) a control valve (43,
143) angeordnet ist, mittels dessen ein Uberströmquerschnitt (44,143) is arranged, by means of which an overflow cross section (44,
144) in der ersten Verbindungsleitung (42, 142) einstellbar ist.144) can be set in the first connecting line (42, 142).
4. Impulsschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Druckkammer (40, 140) über eine zweite Ver¬ bindungsleitung (47, 147) mit einem Niederdruckraum (41, 141) ver¬ bunden ist, wobei in der zweiten Verbindungsleitung (47, 147) ein Rückströmventil (41, 141) angeordnet ist.4. Impulse hammer mechanism according to one of the preceding claims, characterized in that the pressure chamber (40, 140) via a second connecting line (47, 147) with a low-pressure chamber (41, 141) is connected, wherein in the second connecting line ( 47, 147) a backflow valve (41, 141) is arranged.
5. Impulsschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß als Steuermittel (36, 136) in einer Steuerfläche des Hubkolbens (19, 119a, 119b) wenigstens ein Wälzkörper (183) und/oder in der Steuerbahn (37, 137) des Kernteiles (17, 117) we¬ nigstens ein ggf. damit zusammenwirkender weiterer Wälzkörper (184) angeordnet ist.5. Impulse hammer mechanism according to one of the preceding claims, characterized in that as control means (36, 136) in a control surface of the reciprocating piston (19, 119a, 119b) at least one rolling element (183) and / or in the control path (37, 137) of the Core part (17, 117) at least one further rolling element (184) which may interact with it is arranged.
6. ImpulsSchlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der wenigstens eine Hubkolben (19, 119a, 119b) bei einer Relatiwerdrehung des Kernteils (17, 117) zum Rotations¬ körper (13, 113) in radialer Richtung zwangsgesteuert ist.6. Impact mechanism according to one of the preceding claims, characterized in that the at least one reciprocating piston (19, 119a, 119b) is positively controlled in the radial direction in the case of a relative rotation of the core part (17, 117) to the rotary body (13, 113).
7. Impulsschlagwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Rotationskörper (13) eine einseitig offene und mittels eines Deckels (21) verschließbare Radialbohrung (18) aufweist, in der ein einzelner Hubkolben (19) radial verschiebbar angeordnet ist. 7. Impact mechanism according to one of the preceding claims, characterized in that the rotary body (13) has a radial bore (18) which is open on one side and can be closed by means of a cover (21) and in which a single lifting piston (19) is arranged so as to be radially displaceable.
8. Impulsschlagwerk nach einem der Ansprüche 1 bis 6, dadurch ge¬ kennzeichnet, daß der Rotationskörper (113) eine durchgehende und mittels eines hohlzylindrischen Gehäuseteiles (170) abgeschlossene Radialbohrung (118) aufweist, in der zwei Hubkolben (119a, 119b) radial verschiebbar geführt sind.8. Impact mechanism according to one of claims 1 to 6, characterized ge indicates that the rotary body (113) has a continuous and by means of a hollow cylindrical housing part (170) closed radial bore (118) in which two piston pistons (119a, 119b) are radially displaceable are led.
9. Impulsschlagwerk nach Anspruch 8, dadurch gekennzeichnet, daß die Steuerbahn (137) zwei einander gegenüberliegende radiale Erhebungen (138) aufweist, die über einen bogenförmigen Abschnitt mit geringe¬ rem radialem Abstand von der Drehachse (115) mit der jeweils anderen Erhebung (138) verbunden ist.9. Impulse hammer mechanism according to claim 8, characterized in that the control track (137) has two opposite radial elevations (138) which, over an arcuate section with a small radial distance from the axis of rotation (115) with the respective other elevation (138 ) connected is.
10. Impulsschlagwerk nach Anspruch 8 oder 9, dadurch gekennzeichnet, daß im Kernteil (117) ein mit dem Niederdruckraum (141) in Verbin¬ dung stehender Kanal (178) mit Steuerbohrung (182) angeordnet ist, der einmal pro vollständiger Relativverdrehung von Kernteil (117) und Rotationskörper (113) mit einer mit der Druckkammer (141) ver¬ bundenen Bohrung (174) in Deckung kommt. 10. Impact mechanism according to claim 8 or 9, characterized in that in the core part (117) with the low-pressure chamber (141) in connec tion channel (178) with control bore (182) is arranged, once per complete relative rotation of the core part ( 117) and rotating body (113) with a bore (174) connected to the pressure chamber (141).
EP95902761A 1993-12-21 1994-12-14 Impulse drive system, especially for an impulse screwdriver Expired - Lifetime EP0735935B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4343582 1993-12-21
DE4343582A DE4343582A1 (en) 1993-12-21 1993-12-21 Impact mechanism, especially for pulse screwdrivers
PCT/DE1994/001484 WO1995017281A1 (en) 1993-12-21 1994-12-14 Impulse drive system, especially for an impulse screwdriver

Publications (2)

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

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

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Title
See also references of WO9517281A1

Also Published As

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

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