EP0009814B1 - Extensible weight balancing device for a tool, particularly an assembling tool - Google Patents

Extensible weight balancing device for a tool, particularly an assembling tool Download PDF

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Publication number
EP0009814B1
EP0009814B1 EP79103795A EP79103795A EP0009814B1 EP 0009814 B1 EP0009814 B1 EP 0009814B1 EP 79103795 A EP79103795 A EP 79103795A EP 79103795 A EP79103795 A EP 79103795A EP 0009814 B1 EP0009814 B1 EP 0009814B1
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EP
European Patent Office
Prior art keywords
piston
tool
weight
cylinder
means according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP79103795A
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German (de)
French (fr)
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EP0009814A2 (en
EP0009814A3 (en
Inventor
Günter Otto
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Willy Traub & Co GmbH
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Willy Traub & Co GmbH
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Publication date
Application filed by Willy Traub & Co GmbH filed Critical Willy Traub & Co GmbH
Priority to AT79103795T priority Critical patent/ATE395T1/en
Publication of EP0009814A2 publication Critical patent/EP0009814A2/en
Publication of EP0009814A3 publication Critical patent/EP0009814A3/en
Application granted granted Critical
Publication of EP0009814B1 publication Critical patent/EP0009814B1/en
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25H—WORKSHOP EQUIPMENT, e.g. FOR MARKING-OUT WORK; STORAGE MEANS FOR WORKSHOPS
    • B25H1/00—Work benches; Portable stands or supports for positioning portable tools or work to be operated on thereby
    • B25H1/0021—Stands, supports or guiding devices for positioning portable tools or for securing them to the work

Definitions

  • the invention relates to an extendable weight compensation device according to the preamble of claim 1.
  • Such a pull-out weight compensation device is known from DE-C-728 400.
  • it is possible to absorb reaction torques at a specific position of the tool axis of rotation, but a constant height adjustment cannot be achieved during operation of the tool, since the parts of the suspension remain telescopically displaceable relative to one another even during tool operation.
  • the object of the invention is to improve the known weight compensation device with regard to its height adjustment during operation in such a way that the tool can be locked at an arbitrarily selectable height.
  • the configuration of claim 4 gives a piston-cylinder arrangement in which the piston rod can be replaced.
  • piston rods with different diameters can be used in constant piston-cylinder arrangements.
  • the ratio of the inner cylinder diameter to the piston diameter and thus the load-bearing capacity of the weight balancer can be adjusted with simple means. This also ensures easy maintenance.
  • From US-PS 33 26 546 a similar hydropneumatic piston cylinder arrangement with inner cylinder and outer cylinder is known, but in the known arrangement the interchangeability of the piston rod and thus the possibility of adjusting the load capacity of the weight balancer is not available.
  • the setting option is supported by the configurations of subclaims 5 to 7.
  • the configuration of claim 9 provides a compact arrangement of the individual components of the weight balancer.
  • the configuration of claim 21 results in control of the commissioning of the tool in such a way that the tool itself is only put into operation when all the operating conditions necessary to absorb the forces exerted by the tool have been created.
  • the weight balancer according to the invention can be used practically wherever hand-operated tools are used.
  • the invention largely avoids physical exertion which must be expended by the operating personnel in conventional devices.
  • Fig. 1 shows an embodiment of the invention, in which a tension tube 1 with a circular cross section ver as rigid support is used, which can be positively connected with the help of a collet 3 with an outer cylinder 4 of a piston-cylinder arrangement.
  • the tensioning tube 1 is fastened to a holding device designed as a trolley 5a, for example by screwing, which in turn has a locking device in the form of clamping jaws 6 with which the trolley 5a can be moved on a rail 7 on the ceiling.
  • a filling head 5 At the lower end of the extendable outer cylinder 4 of the piston-cylinder arrangement there is a filling head 5, the individual parts of which will be explained in connection with FIGS. 4 and 5.
  • the tool 9 Via a fastening rod 8, the tool 9 is rigidly fastened to the outer cylinder 4 of the piston-cylinder arrangement with the aid of a fixed connection 10.
  • the outer cylinder 4 of the piston-cylinder arrangement arranged in the clamping tube 1 is pulled downwards or raised upwards.
  • the effective load capacities or spring forces remain essentially constant over the entire extension length or lifting height.
  • the collet 3 is tightened by corresponding actuation of a valve 11, which is connected to a pressure source via a port P, so that the clamping tube 1 is rigid with the outer cylinder 4 is connected.
  • the height setting of the tool 9 is thus fixed.
  • the pressure medium is introduced through the valve 11, which also has the pressure medium outlet A, into the collet via a pressure line 12.
  • Pressure medium is also conveyed through the pressure line 12 to the pneumatically actuated locking device 6 of the trolley 5, so that the clamping jaws are placed on the rail 7 and the trolley 5 is blocked.
  • the tool 9 is then put into operation by further actuation of the valve 11 in the same direction.
  • a hand lever 13 is used, through which a valve piston 14, which will be explained in more detail in connection with FIGS. 6 and 7, is inserted into the valve for actuating the collet 3 and the clamping device 6 and the tool 9.
  • the devices mentioned are then operated in the order described above.
  • FIG. 2 An exemplary embodiment is described in FIG. 2, in which the weight compensation device is arranged on a carriage 30 which can be moved on the floor. This is mounted over the tensioning tube 1 "in such a way that it can be pivoted through 360 °.
  • a lockable cylinder arrangement 22 serves as storage, by means of which the weight balancer can be pivoted together with the tool into the corresponding operating position.
  • the guide shafts 23 are fastened to the cross plate 25, while the guide shafts 24 are fastened to the carriage, for example to the frame 27.
  • the cross plate 25 is guided on the guide shafts 24 so as to be displaceable in the vertical direction.
  • the guide shafts 23 are also attached, which are used for the horizontal guidance of the weight balance with the tool 9.
  • the tension tube 1 is supported on the guide shafts 24 via a carrier plate 26.
  • the hydropneumatic piston-cylinder arrangement is arranged in the tensioning tube 1.
  • the tensioning tube 1 and the hydropneumatic piston-cylinder arrangement arranged therein can have the same embodiment as the exemplary embodiment in FIG. 1.
  • the bearing block 31 can be rigidly connected via a rigid connecting rod 32 to the outer cylinder of the piston-cylinder arrangement which is arranged in the tension tube 1 '.
  • a collet 3 or 3' is provided in order to establish a frictional connection between the tensioning tube 1 or 1 'and the outer cylinder of the piston cylinder arrangement in the tensioning tube.
  • the control for blocking the cylinder 22 for actuating the collets 3 and 3 'and lifting devices 28, with which the carriage 30 can be supported on the floor by means of stamps 29, takes place via the valve 11.
  • This valve 11 can, as in the exemplary embodiment in FIG Fig. 1 can be operated.
  • the cylinder bearing 22 is blocked and the collets 3 and 3 'are tightened.
  • the lifting device 28 raises the carriage 30 so that it is supported on the ground by the punches 29.
  • the pneumatically operated tool 9 which can be a drill, is then put into operation by further pushing the valve piston 14 into the valve housing. This ensures that forces exerted by the tool from the device shown in FIG. 3 are reliably introduced into the ground.
  • FIG. 3 shows an exemplary embodiment of the hydropneumatic piston-cylinder arrangement which can be used in the invention.
  • This hydropneumatic piston-cylinder arrangement has the outer cylinder 4 and an inner cylinder 33.
  • an inner cylinder piston 34 is slidably arranged in the inner cylinder Linder 33.
  • a piston rod 35 is connected to the inner cylinder piston 34, for example, by screwing.
  • the piston rod 35 is guided in a piston rod guide 36 which is provided with a seal 37.
  • the piston rod guide 36 is inserted into a connecting piece 38 with the outer cylinder 4 and screwed, for example.
  • a thread 39 is provided. In this way, the piston rod can be removed from the inner cylinder 33 together with the piston rod guide.
  • piston rods with different diameters can be used in cylinder arrangements in which the inner cylinder and the outer cylinder have the same dimensions, in particular the same diameter. In this way, the ratio between the inner diameter of the inner cylinder 33 and the diameter of the piston rod 35 can be varied.
  • a stop neck 40 which is at a certain distance from the piston rod. The space between the stop neck 40 and the piston rod 35 forms an overflow channel which connects the interior above the piston 34 in the inner cylinder with the space between the inner cylinder 33 and the outer cylinder 4 above a separating or compensating piston 41.
  • the overflow channel 42 continues between the seal 37 and the upper part of the stop neck in a horizontal direction and has another vertically extending channel part between the connecting piece 38 and the stop neck 40, which opens into the space between the inner cylinder 33 and the outer cylinder 4.
  • the space above the piston 34 in the inner cylinder 33 and the space above the separating piston 41 between the inner cylinder 33 and the outer cylinder 4, which are connected to one another by the overflow channel 42, are filled with a hydraulic fluid, for example oil.
  • the space below the compensating piston 41 between the inner cylinder 33 and the outer cylinder 4 is filled with compressed gas.
  • This compressed gas can be filled in via a valve 45.
  • the inner cylinder 33 is supported against a base piece 44, which seals the space between the inner cylinder 33 and the outer cylinder 4.
  • Atmospheric pressure prevails in the space below the inner cylinder piston 34.
  • a ventilation hole 48 is provided in the base piece 44.
  • a stop neck 49 is also attached to the upper part of the outer cylinder. The stroke distance of the outer cylinder in the tensioning tube 1 is limited by this.
  • the piston rod 35 can be connected at its upper end via a ball joint 50 to a stationary articulation point or to the trolley 5. Forces emanating from the tool, however, are not transmitted to the trolley 5a via this ball joint, but, as has already been explained in connection with the exemplary embodiments in FIGS. 1 to 3, via the tensioning tube 1, which bridges this ball joint. In this respect, no forces act on this ball joint during the operation of the tool.
  • the collet 3 which is fastened to the clamping tube 1, essentially has a collet head 51 which can be displaced in the radial direction by axially displacing a pneumatically actuated slide 52.
  • the collet head and the slider have two contacting conical surfaces which are aligned with one another in such a way that when a pressure medium is introduced through the pressure line 12, the slider 52 is displaced upward in FIG. 5, so that the collet head 51 is pressed against the outer cylinder 4 .
  • a retaining ring 53 is also provided in the collet for guiding the slide 52. The sliding parts are sealed against each other by appropriate seals.
  • the filling head 5 is configured differently in the exemplary embodiment in FIG. 4 than in the exemplary embodiment in FIG. 3, but pressure gas between the outer cylinder 4 and the inner cylinder 33 below the separating piston (not shown in more detail) is also introduced via an adjusting valve 45 ' can. Furthermore, in the base piece 44 there is the ventilation hole 48 ', through which atmospheric pressure 33 can be set in the inner cylinder below the inner cylinder piston. The base piece 44 is screwed into a block 54, on which the tool 9 is pivoted. The swivel axis is horizontal.
  • the supply of compressed air into the tool 9 is controlled in this embodiment via a switch 55 which can be actuated by the valve 11 as soon as the valve piston 14 has been inserted into the valve by a certain distance by means of the handle 13; however, the locking device 6 for the trolley 5 and the collet 3 have been actuated beforehand.
  • FIGS. 5A to 5C show the valve alone, with the rest position in FIG. 5A tion of the valve is shown.
  • FIG. 5B shows a view of the valve from above
  • FIG. 5A shows a sectional illustration along the section line BB.
  • 5C shows a sectional representation along the section line CC.
  • the valve has a channel P which is connected to the compressed air source. At the lower end of this channel, a drain valve 56 for condensed water is provided.
  • three valve chambers 57, 58, 59 are arranged one above the other in the axial direction.
  • the valve piston 14 is guided in these valve chambers.
  • the valve piston has valve beads 60, 61, 62.
  • Valve grooves 63 and 64 are located between the valve beads.
  • the groove width is dimensioned such that when the compressed air is introduced, there is no nozzle effect, but that the compressed air can pass through smoothly. This means that sufficiently wide passage gaps are formed between the valve grooves and the valve chamber walls.
  • a compressed air outlet channel P is also provided in the valve body. This is located diametrically to the compressed air inlet channel P with respect to the valve chambers 57, 58, 59 or the piston 14 arranged one above the other in the middle. As can be seen from FIG. 5C, the valve also has a ventilation channel 65 which is connected via a cross connection is connected to a vent hole R. Furthermore, a further compressed gas outlet channel A is provided in the valve body. This is located diametrically with respect to the piston 14 to the ventilation channel.
  • valve or the valve piston 14 the rest position of the valve or the valve piston 14 is shown.
  • the valve piston is pushed into its lowest position by a compression spring 66.
  • the compressed air supply from the compressed air duct P is blocked in relation to the two compressed air outlet ducts P and A by the corresponding position of the valve beads, in particular the valve bead 61.
  • the compressed air outlet channel P is connected to the lower valve chamber 59.
  • the compressed air outlet channel A is connected to the upper valve chamber 57.
  • the compressed air inlet channel P is connected to the central valve chamber 58.
  • the compressed air supply to the lower chamber 59 is blocked by the valve bead 61, while the compressed air supply to the upper chamber 57 is blocked by the valve bead 60.
  • valve piston 14 If the valve piston 14 is pushed into the valve block by a certain amount, as shown in FIG. 5C, a connection between the central valve chamber 58 and the upper valve chamber 57 results via the valve groove 63. Compressed air can then be drawn from the compressed air channel P, which is connected to the compressed air source, flows into the compressed air outlet channel A via the upper valve chamber 57.
  • This compressed air outlet duct A is, as can be seen from the exemplary embodiments in FIGS. 1 and 2, connected to the locking device 6 of the trolley 5, the collet 3 or 3 ', the lockable cylinder 22 and the lifting devices 28. 5C, these devices are therefore actuated.
  • FIGS. 6A and 7C The second operating position of the valve is shown in FIGS. 6A and 7C.
  • the valve piston 14 is displaced a further distance into the valve block, so that a connection is also established between the central valve chamber 58 and the lower valve chamber 59 via the valve groove 64.
  • the compressed air can then also flow via this lower valve chamber 59 into the compressed air outlet channel P, which, as can be seen in particular from FIG. 6A, is connected to the pneumatically actuated tool 9.
  • the compressed air outlet channel is connected via a bore 68 provided in a holding plate 67 to a corresponding compressed air channel in the tool 9.
  • FIG. 6A is a sectional illustration along the section line D-D in FIG. 6B, which shows a top view of the valve with the holding plate 67.
  • FIG. 6C shows a sectional illustration along the section line E-E in FIG. 6B.
  • annular spaces 71 and 72 which are connected to the vent hole R.
  • the annular space 72 is connected to the ventilation bore R via the ventilation channel 65, as can be seen from FIGS. 5C and 6C. Damage to the seals cannot have an adverse effect, since the compressed air can then escape through these ventilation channels and bores. In this way, the pneumatic control is additionally secured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Actuator (AREA)
  • Earth Drilling (AREA)
  • Testing Of Balance (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Machine Tool Units (AREA)
  • Golf Clubs (AREA)
  • Jigs For Machine Tools (AREA)

Abstract

A tool balancing apparatus comprises a spring arrangement for balancing the weight of a tool such as an assembly tool. The spring arrangement is a hydro-pneumatic piston-cylinder unit whose one end is connected to a suitable mounting means and whose other end, being extensible, carries the tool. The apparatus further includes a bracing means such as a tube or a torsion bar assembly to form a rigid connection between the tool and the mounting means, thereby to carry any forces produced by the tool during operation thereof and to transmit such forces to the mounting means.

Description

Die Erfindung befasst sich mit einer ausziehbaren Gewichtsausgleichseinrichtung nach dem Oberbegriff des Anspruchs 1.The invention relates to an extendable weight compensation device according to the preamble of claim 1.

Eine derartige ausziehbare Gewichtsausgleichseinrichtung ist aus der DE-C-728 400 bekannt. Bei der bekannten ausziehbaren Gewichtsausgleichseinrichtung ist es zwar möglich, Reaktionsdrehmomente bei bestimmter Lage der Werkzeugdrehachse aufzufangen, jedoch lässt sich eine konstante Höheneinstellung beim Betrieb des Werkzeugs nicht erzielen, da die Teile der Aufhängung auch während des Werkzeugbetriebs teleskopartig zueinander verschiebbar bleiben.Such a pull-out weight compensation device is known from DE-C-728 400. In the known pull-out weight compensation device, it is possible to absorb reaction torques at a specific position of the tool axis of rotation, but a constant height adjustment cannot be achieved during operation of the tool, since the parts of the suspension remain telescopically displaceable relative to one another even during tool operation.

Aufgabe der Erfindung ist es demgegenüber, die bekannte Gewichtsausgleichseinrichtung bezüglich ihrer Höheneinstellung im Betrieb dahingehend zu verbessern, dass das Werkzeug in einer beliebig wählbaren Höhe feststellbar ist.In contrast, the object of the invention is to improve the known weight compensation device with regard to its height adjustment during operation in such a way that the tool can be locked at an arbitrarily selectable height.

Diese Aufgabe wird durch die im Anspruch 1 angegebene Erfindung gelöst.This object is achieved by the invention specified in claim 1.

Bei der Erfindung wird ferner in vorteilhafter Weise die Tatsache ausgenützt, dass die Federeigenschaften einer hydropneumatischen Kolbenzylinderanordnung praktisch über den gesamten Hubweg des Kolbens konstant gehalten werden können. Man gewinnt auf diese Weise trotz eines langen Auszugswegs des Gewichtsausgleichers über die gesamte Auszugsstrecke hin einen gleichbleibenden Gewichtsausgleich. Ferner lassen sich durch die kraftschlüssig mit dem Aussenzylinder der Kolbenzylinderanordnung verbundenen starren Abstützung vom Werkzeug ausgehende Kräfte, welche beispielsweise in Form von Drehmomenten wirksam werden, einwandfrei auffangen, so dass die Handhabung des Werkzeugs, abgesehen vom Gewichtsausgleich, für die Bedienungsperson noch wesentlich verbessert wird. Es ist zwar bekannt, auf dem Gebiet der Schrauber durch Verwendung von Schlagschraubern beim Anziehen von Schrauben das Anzugsmoment zu verringern, jedoch erzeugen diese Schlagschrauber erhebliche Geräusche, welche die Arbeitsbedingungen erheblich beeinträchtigen.The fact that the spring properties of a hydropneumatic piston-cylinder arrangement can be kept practically constant over the entire stroke of the piston is also advantageously used in the invention. In this way, despite a long extension path of the weight balancer, a constant weight balance is obtained over the entire extension distance. Furthermore, due to the rigid support connected to the outer cylinder of the piston cylinder arrangement, forces exerted by the tool, which are effective, for example, in the form of torques, can be absorbed perfectly, so that the handling of the tool, apart from the weight compensation, is still significantly improved for the operator. Although it is known in the field of screwdrivers to reduce the tightening torque by using impact wrenches when tightening screws, these impact wrenches produce considerable noises which have a considerable adverse effect on the working conditions.

Bei der Erfindung ist ausserdem dafür Sorge getragen, dass die Stelle, welche beim Auffangen von Kräften, die vom Werkzeug ausgehen, am ehesten brechen könnte, nämlich die Befestigungsstelle der Kolbenstange am Werkzeug oder an der Anlenk- oder Befestigungsvorrichtung nicht belastet wird. Dies wird durch die starre Abstützung erzielt, welche diesen Teil der Gewichtsausgleichseinrichtung überbrückt.In the case of the invention, care is also taken to ensure that the point which could break most easily when absorbing forces arising from the tool, namely the fastening point of the piston rod on the tool or on the articulation or fastening device, is not stressed. This is achieved by the rigid support which bridges this part of the weight compensation device.

In den Unteransprüchen sind vorteilhafte Weiterbildungen der Erfindung angegeben.Advantageous developments of the invention are specified in the subclaims.

Durch die Ausgestaltung des Anspruchs 4 gewinnt man eine Kolbenzylinderanordnung, bei der die Kolbenstange auswechselbar ist. Es lassen sich auf diese Weise in gleichbleibenden Kolbenzylinderanordnungen Kolbenstangen mit unterschiedlichem Durchmesser einsetzen. Auf diese Weise lässt sich das Verhältnis von Zylinderinnendurchmesser zu Kolbendurchmesser und damit die Tragkraft des Gewichtsausgleichers mit einfachen Mitteln einstellen. Zudem wird eine einfache Wartung auf diese Weise gewährleistet. Aus der US-PS 33 26 546 ist zwar eine ähnliche hydropneumatische Kolbenzylinderanordnung mit Innenzylinder und Aussenzylinder bekannt, jedoch ist bei der bekannten Anordnung die Auswechselbarkeit der Kolbenstange und damit die Einstellmöglichkeit der Tragkraft des Gewichtsausgleichers nicht vorhanden. Durch die Ausgestaltungen der Unteransprüche 5 bis 7 wird die Einstellmöglichkeit noch unterstützt.The configuration of claim 4 gives a piston-cylinder arrangement in which the piston rod can be replaced. In this way, piston rods with different diameters can be used in constant piston-cylinder arrangements. In this way, the ratio of the inner cylinder diameter to the piston diameter and thus the load-bearing capacity of the weight balancer can be adjusted with simple means. This also ensures easy maintenance. From US-PS 33 26 546 a similar hydropneumatic piston cylinder arrangement with inner cylinder and outer cylinder is known, but in the known arrangement the interchangeability of the piston rod and thus the possibility of adjusting the load capacity of the weight balancer is not available. The setting option is supported by the configurations of subclaims 5 to 7.

Durch die Ausgestaltung des Anspruchs 9 gewinnt man eine kompakte Anordnung der einzelnen Bauteile des Gewichtsausgleichers.The configuration of claim 9 provides a compact arrangement of the individual components of the weight balancer.

Durch die Ausgestaltung des Anspruchs 14 und der darauf zurückbezogenen Ansprüche gewinnt man eine universelle Einsatzmöglichkeit des Werkzeugs. Das Werkzeug ist dann nicht mehr an eine Schienenführung an der Decke gebunden, sondern kann an jeden beliebigen Ort in einer Montage- bzw. Fertigungshalle gebracht werden.Through the design of claim 14 and the claims related to it, one gains a universal application of the tool. The tool is then no longer tied to a rail guide on the ceiling, but can be brought to any location in an assembly or production hall.

Durch die Ausgestaltung des Anspruchs 21 erzielt man eine Steuerung der Inbetriebsetzung des Werkzeugs derart, dass erst dann, wenn alle zum Auffangen der vom Werkzeug ausgehenden Kräfte notwendigen Betriebsbedingungen geschaffen sind, das Werkzeug selbst in Betrieb gesetzt wird.The configuration of claim 21 results in control of the commissioning of the tool in such a way that the tool itself is only put into operation when all the operating conditions necessary to absorb the forces exerted by the tool have been created.

Der Gewichtsausgleicher nach der Erfindung lässt sich praktisch überall dort, wo handbetätigte Werkzeuge zum Einsatz kommen, zur Anwendung bringen. Durch die Erfindung werden körperliche Anstrengungen, welche durch das Bedienungspersonal bei herkömmlichen Einrichtungen aufgewendet werden müssen, weitgehendstvermieden.The weight balancer according to the invention can be used practically wherever hand-operated tools are used. The invention largely avoids physical exertion which must be expended by the operating personnel in conventional devices.

Ausführungsbeispiele der Erfindung sind anhand der beiliegenden Figuren nachstehend noch näher erläutert. Es zeigen:

  • Fig. 1 ein Ausführungsbeispiel, bei dem ein Spannrohr mit kreisrundem Mantel zur Anwendung kommt;
  • Fig.2 ein Ausführungsbeispiel, das am Boden mit Hilfe eines Wagens fahrbar und mit Hilfe einer Hubvorrichtung am Boden abstützbar ist;
  • Fig.3 eine hydropneumatische Kolbenzylinderanordnung, welche bei den Ausführungsbeispielen zurAnwendung kommen kann;
  • Fig.4 ein Ausführungsbeispiel, bei dem Einzelheiten zur Erzielung des Kraftschlusses zwischen dem Aussenzylinder der Kolbenzylinderanordnung und dem Spannrohr dargestellt sind, und
  • Fig.5A-C sowie 6A-C eine Ventilsteuerung für die pneumatisch zu betätigenden Bauteile des Gewichtsausgleichers.
Embodiments of the invention are explained in more detail below with reference to the accompanying figures. Show it:
  • Figure 1 shows an embodiment in which a tension tube with a circular jacket is used.
  • 2 shows an embodiment that can be moved on the ground with the help of a trolley and can be supported on the ground with the aid of a lifting device;
  • 3 shows a hydropneumatic piston-cylinder arrangement which can be used in the exemplary embodiments;
  • 4 shows an embodiment in which details for achieving the frictional connection between the outer cylinder of the piston cylinder arrangement and the tensioning tube are shown, and
  • 5A-C and 6A-C a valve control for the pneumatically actuated components of the weight balancer.

Die Fig. 1 zeigt ein Ausführungsbeispiel der Erfindung, bei dem als starre Abstützung ein Spannrohr 1 mit kreisrundem Querschnitt verwendet wird, das mit Hilfe einer Spannzange 3 mit einem Aussenzylinder 4 einer Kolbenzylinderanordnung kraftschlüssig in Verbindung gebracht werden kann. Das Spannrohr 1 ist an einer als Rollwagen 5a ausgebildeten Haltevorrichtung, beispielsweise durch Verschrauben, befestigt, die ihrerseits in Form von Klemmbacken 6 eine Feststelleinrichtung aufweist, mit der der Rollwagen 5a an einer Schiene 7 an der Decke verfahrbar ist. Am unteren Ende des ausziehbaren Aussenzylinders 4 der Kolbenzylinderanordnung befindet sich ein Füllkopf 5, dessen Einzelteile im Zusammenhang mit den Fig. 4 und 5 noch erläutert werden. Übere eine Befestigungsstange 8 ist das Werkzeug 9 mit Hilfe einer festen Verbindung 10 am Aussenzylinder 4 der Kolbenzylinderanordnung starr befestigt.Fig. 1 shows an embodiment of the invention, in which a tension tube 1 with a circular cross section ver as rigid support is used, which can be positively connected with the help of a collet 3 with an outer cylinder 4 of a piston-cylinder arrangement. The tensioning tube 1 is fastened to a holding device designed as a trolley 5a, for example by screwing, which in turn has a locking device in the form of clamping jaws 6 with which the trolley 5a can be moved on a rail 7 on the ceiling. At the lower end of the extendable outer cylinder 4 of the piston-cylinder arrangement there is a filling head 5, the individual parts of which will be explained in connection with FIGS. 4 and 5. Via a fastening rod 8, the tool 9 is rigidly fastened to the outer cylinder 4 of the piston-cylinder arrangement with the aid of a fixed connection 10.

Um das Werkzeug, welches im dargestellten Ausführungsbeispiel ein Bohrer, insbesondere ein pneumatisch betätigter Bohrer ist, in seine Arbeitsstellung zu bringen, wird der Aussenzylinder 4 der im Spannrohr 1 angeordneten Kolbenzylinderanordnung nach unten gezogen oder nach oben angehoben. Die dabei wirksamen Tragkräfte bzw. Federkräfte bleiben über die gesamte Auszugslänge bzw. Hubhöhe hin im wesentlichen konstant.In order to bring the tool, which in the exemplary embodiment shown is a drill, in particular a pneumatically operated drill, into its working position, the outer cylinder 4 of the piston-cylinder arrangement arranged in the clamping tube 1 is pulled downwards or raised upwards. The effective load capacities or spring forces remain essentially constant over the entire extension length or lifting height.

Vor Inbetriebnahme des Werkzeugs 9, das beim dargestellten Ausführungsbeispiel ein pneumatisch angetriebenes Werkzeug ist, wird die Spannzange 3 durch entsprechende Betätigung eines Ventils 11, das über einen Anschluss P an eine Druckquelle angeschlossen ist, angezogen, so dass das Spannrohr 1 starr mit dem Aussenzylinder 4 verbunden wird. Die Höheneinstellung des Werkzeugs 9 ist somit festgelegt. Das Druckmedium wird dabei über das Ventil 11, das ausserdem den Druckmediumsauslass A aufweist, in die Spannzange über eine Druckleitung 12 eingebracht. Durch die Druckleitung 12 wird ausserdem Druckmedium zur pneumatisch betätigten Feststelleinrichtung 6 des Rollwagens 5 gefördert, so dass die Klemmbacken an die Schiene 7 angelegt werden und der Rollwagen 5 blockiert ist. Nach Betätigung der Spannzange 3 und der Feststelleinrichtung 6 wird durch weitere Betätigung des Ventils 11 in der gleichen Richtung anschliessend das Werkzeug 9 in Betrieb gesetzt.Before the tool 9, which is a pneumatically driven tool in the exemplary embodiment shown, is put into operation, the collet 3 is tightened by corresponding actuation of a valve 11, which is connected to a pressure source via a port P, so that the clamping tube 1 is rigid with the outer cylinder 4 is connected. The height setting of the tool 9 is thus fixed. The pressure medium is introduced through the valve 11, which also has the pressure medium outlet A, into the collet via a pressure line 12. Pressure medium is also conveyed through the pressure line 12 to the pneumatically actuated locking device 6 of the trolley 5, so that the clamping jaws are placed on the rail 7 and the trolley 5 is blocked. After the collet 3 and the locking device 6 have been actuated, the tool 9 is then put into operation by further actuation of the valve 11 in the same direction.

Zur Bedienung des Ventils 11 dient ein Handhebel 13, durch welchen ein Ventilkolben 14, der im einzelnen noch im Zusammenhang mit den Figuren 6 und 7 erläutert wird, zur Betätigung der Spannzange 3 und der Klemmvorrichtung 6 sowie des Werkzeugs 9 in das Ventil eingeschoben. Die genannten Vorrichtungen werden dann in der vorstehend beschriebenen Reihenfolge betätigt.To operate the valve 11, a hand lever 13 is used, through which a valve piston 14, which will be explained in more detail in connection with FIGS. 6 and 7, is inserted into the valve for actuating the collet 3 and the clamping device 6 and the tool 9. The devices mentioned are then operated in the order described above.

In der Fig. 2 ist ein Ausführungsbeispiel beschrieben, bei welchem die Gewichtsausgleichseinrichtung an einem am Boden verfahrbaren Wagen 30 angeordnet ist. Diese ist über das Spannrohr 1" derart gelagert, dass sie um 360° verschwenkt werden kann.An exemplary embodiment is described in FIG. 2, in which the weight compensation device is arranged on a carriage 30 which can be moved on the floor. This is mounted over the tensioning tube 1 "in such a way that it can be pivoted through 360 °.

Als Lagerung dient eine blockierbare Zylinderanordnung 22, durch welche der Gewichtsausgleicher zusammen mit dem Werkzeug in die entsprechende Betriebslage verschwenkt werden kann.A lockable cylinder arrangement 22 serves as storage, by means of which the weight balancer can be pivoted together with the tool into the corresponding operating position.

Mit Hilfe von Führungswellen 23, die an einer Kreuzplatte befestigt sind und Führungswellen 24, auf denen die Kreuzplatte 25 geführt wird, lässt sich eine vertikale und eine horizontale Verschiebung des Gewichtsausgleichs zusammen mit dem Werkzeug erzielen.With the help of guide shafts 23, which are attached to a cross plate and guide shafts 24, on which the cross plate 25 is guided, a vertical and a horizontal displacement of the weight balance can be achieved together with the tool.

Die Führungswellen 23 sind an der Kreuzplatte 25 befestigt, während die Führungswellen 24 am Wagen, beispielsweise am Rahmen 27, befestigt sind. Die Kreuzplatte 25 ist an den Führungswellen 24 in vertikaler Richtung verschiebbar geführt. An der Kreuzplatte 25 sind ausserdem die Führungswellen 23 befestigt, die zur horizontalen Führung des Gewichtsausgleiches mit dem Werkzeug 9 dienen. An den Führungswellen 24 ist über eine Trägerplatte 26 das Spannrohr 1 abgestützt. Im Spannrohr 1 ist die hydropneumatische Kolbenzylinderanordnung angeordnet. Das Spannrohr 1 und die darin angeordnete hydropneumatische Kolbenzylinderanordnung können die gleiche Ausführungsform besitzen wie das Ausführungsbeispiel in der Fig. 1. Dies gilt auch für das Spannrohr l' und die darin angeordnete Kolbenzylinderanordnung, welche zur horizontalen Führung des Befestigungsblockes 31 und damit des Gewichtsausgleichers und des Werkzeugs 9 dienen. Der Lagerblock 31 kann dabei über einen starren Verbindungsstab 32 mit dem Aussenzylinder der Kolbenzylinderanordnung, die im Spannrohr l' angeordnet ist, starr verbunden sein. Um einen Kraftschluss zwischen dem Spannrohr 1 bzw. 1' und dem Aussenzylinder der Kolbenzylinderanordnung im Spannrohr herzustellen, ist eine Spannzange 3 bzw. 3' vorgesehen.The guide shafts 23 are fastened to the cross plate 25, while the guide shafts 24 are fastened to the carriage, for example to the frame 27. The cross plate 25 is guided on the guide shafts 24 so as to be displaceable in the vertical direction. On the cross plate 25, the guide shafts 23 are also attached, which are used for the horizontal guidance of the weight balance with the tool 9. The tension tube 1 is supported on the guide shafts 24 via a carrier plate 26. The hydropneumatic piston-cylinder arrangement is arranged in the tensioning tube 1. The tensioning tube 1 and the hydropneumatic piston-cylinder arrangement arranged therein can have the same embodiment as the exemplary embodiment in FIG. 1. This also applies to the tensioning tube 1 'and the piston-cylinder arrangement arranged therein, which are used for the horizontal guidance of the fastening block 31 and thus the weight balancer and the Tool 9 serve. The bearing block 31 can be rigidly connected via a rigid connecting rod 32 to the outer cylinder of the piston-cylinder arrangement which is arranged in the tension tube 1 '. In order to establish a frictional connection between the tensioning tube 1 or 1 'and the outer cylinder of the piston cylinder arrangement in the tensioning tube, a collet 3 or 3' is provided.

Die Steuerung zur Blockierung des Zylinders 22 zur Betätigung der Spannzangen 3 und 3' sowie von Hubeinrichtungen 28, mit denen der Wagen 30 über Stempel 29 am Boden abgestützt werden kann, erfolgt über das Ventil 11. Dieses Ventil 11 kann, wie beim Ausführungsbeispiel in der Fig. 1 dargestellt, betätigt werden. Auch beim in der Fig. 3 dargestellten Ausführungsbeispiel werden zunächst beim Einschieben des Ventilkolbens 14 in das Ventil die Zylinderlagerung 22 blockiert und die Spannzangen 3 und 3' angezogen. Ausserdem wird durch die Hubeinrichtungen 28 der Wagen 30 angehoben, so dass er über die Stempel 29 am Boden abgestützt ist. Durch weiteres Einschieben des Ventilkolbens 14 in das Ventilgehäuse wird dann das pneumatisch betriebene Werkzeug 9, welches ein Bohrer sein kann, in Betrieb gesetzt. Dadurch wird sichergestellt, dass von der in der Fig. 3 dargestellten Vorrichtung vom Werkzeug ausgehende Kräfte sicher in den Boden eingeleitet werden.The control for blocking the cylinder 22 for actuating the collets 3 and 3 'and lifting devices 28, with which the carriage 30 can be supported on the floor by means of stamps 29, takes place via the valve 11. This valve 11 can, as in the exemplary embodiment in FIG Fig. 1 can be operated. Also in the embodiment shown in FIG. 3, when the valve piston 14 is inserted into the valve, the cylinder bearing 22 is blocked and the collets 3 and 3 'are tightened. In addition, the lifting device 28 raises the carriage 30 so that it is supported on the ground by the punches 29. The pneumatically operated tool 9, which can be a drill, is then put into operation by further pushing the valve piston 14 into the valve housing. This ensures that forces exerted by the tool from the device shown in FIG. 3 are reliably introduced into the ground.

In der Fig. 3 ist ein Ausführungsbeispiel für die hydropneumatische Kolbenzylinderanordnung, welche bei der Erfindung zur Anwendung kommen kann, dargestellt. Diese hydropneumatische Kolbenzylinderanordnung besitzt den Aussenzylinder 4 sowie einen Innenzylinder 33. Im Innenzylinder 33 ist ein Innenzylinderkolben 34 verschiebbar angeordnet. Mit dem Innenzylinderkolben 34 ist beispielsweise durch Verschrauben eine Kolbenstange 35 verbunden. Die Kolbenstange 35 wird in einer Kolbenstangenführung 36, die mit einer Dichtung 37 versehen ist, geführt. Die Kolbenstangenführung 36 ist in ein Verbindungsstück 38 mit dem Aussenzylinder 4 eingesetzt und beispielsweise verschraubt. Hierzu ist ein Gewinde 39 vorgesehen. Auf diese Weise lässt sich die Kolbenstange zusammen mit der Kolbenstangenführung aus dem Innenzylinder 33 entnehmen. Da die Kolbenstange mit dem Innenzylinderkolben 34 verschraubbar ist, kann der Kolben im Zylinder verbleiben. Es lassen sich auf diese Weise in Zylinderanordnungen, bei denen der Innenzylinder und der Aussenzylinder gleiche Abmessungen, insbesondere gleiche Durchmesser besitzen, Kolbenstangen mit unterschiedlichen Durchmessern einsetzen. Auf diese Weise lässt sich das Verhältnis zwischen Innendurchmesser des Innenzylinders 33 zum Durchmesser der Kolbenstange 35 variieren. Ausserdem befindet sich zwischen der Kolbenstangenführung 36 und dem oberen Ende des Innenzylinders 33 ein Anschlaghals 40, der zur Kolbenstange einen bestimmten Abstand aufweist. Der Zwischenraum zwischen dem Anschlaghals 40 und der Kolbenstange 35 bildet einen Überströmkanal, welcher den Innenraum oberhalb des Kolbens 34 im Innenzylinder mit dem Raum zwischen dem Innenzylinder 33 und dem Aussenzylinder 4 oberhalb eines Trenn- bzw. Ausgleichskolbens 41 verbindet. Der Überströmkanal 42 setzt sich zwischen der Dichtung 37 und dem oberen Teil des Anschlaghalses in waagrechter Richtung fort und besitzt zwischen dem Verbindungsstück 38 und dem Anschlaghals 40 einen weiteren sich vertikal erstreckenden Kanalteil, der in den Raum zwischen dem Innenzylinder 33 und dem Aussenzylinder 4 mündet. Der Raum oberhalb des Kolbens 34 im Innenzylinder 33 und der Zwischenraum oberhalb des Trennkolbens 41 zwischen dem Innenzylinder 33 und dem Aussenzylinder 4, welche durch den Überströmkanal 42 miteinander verbunden sind, sind mit einer Hydraulikflüssigkeit, beispielsweise ÖI, angefüllt.FIG. 3 shows an exemplary embodiment of the hydropneumatic piston-cylinder arrangement which can be used in the invention. This hydropneumatic piston-cylinder arrangement has the outer cylinder 4 and an inner cylinder 33. In the inner cylinder Linder 33, an inner cylinder piston 34 is slidably arranged. A piston rod 35 is connected to the inner cylinder piston 34, for example, by screwing. The piston rod 35 is guided in a piston rod guide 36 which is provided with a seal 37. The piston rod guide 36 is inserted into a connecting piece 38 with the outer cylinder 4 and screwed, for example. For this purpose, a thread 39 is provided. In this way, the piston rod can be removed from the inner cylinder 33 together with the piston rod guide. Since the piston rod can be screwed to the inner cylinder piston 34, the piston can remain in the cylinder. In this way, piston rods with different diameters can be used in cylinder arrangements in which the inner cylinder and the outer cylinder have the same dimensions, in particular the same diameter. In this way, the ratio between the inner diameter of the inner cylinder 33 and the diameter of the piston rod 35 can be varied. In addition, between the piston rod guide 36 and the upper end of the inner cylinder 33 there is a stop neck 40 which is at a certain distance from the piston rod. The space between the stop neck 40 and the piston rod 35 forms an overflow channel which connects the interior above the piston 34 in the inner cylinder with the space between the inner cylinder 33 and the outer cylinder 4 above a separating or compensating piston 41. The overflow channel 42 continues between the seal 37 and the upper part of the stop neck in a horizontal direction and has another vertically extending channel part between the connecting piece 38 and the stop neck 40, which opens into the space between the inner cylinder 33 and the outer cylinder 4. The space above the piston 34 in the inner cylinder 33 and the space above the separating piston 41 between the inner cylinder 33 and the outer cylinder 4, which are connected to one another by the overflow channel 42, are filled with a hydraulic fluid, for example oil.

Der Raum unterhalb des Ausgleichskolbens 41 zwischen dem Innenzylinder 33 und dem Aussenzylinder 4 ist mit Druckgas angefüllt. Dieses Druckgas kann über ein Ventil 45 eingefüllt werden.The space below the compensating piston 41 between the inner cylinder 33 and the outer cylinder 4 is filled with compressed gas. This compressed gas can be filled in via a valve 45.

Der Innenzylinder 33 ist gegen ein Bodenstück 44, das den Raum zwischen dem Innenzylinder 33 und dem Aussenzylinder 4 abdichtet, abgestützt. Auf diesem Bodenstück 44 befindet sich ein Hilfsring 43, der eine Bohrung aufweist, die etwa zur Hälfte als zylindrische Bohrung 46 und zur anderen Hälfte als konische Bohrung 47 ausgebildet ist. Hierdurch wird das Einsetzen des Innenzylinders 33 erleichtert.The inner cylinder 33 is supported against a base piece 44, which seals the space between the inner cylinder 33 and the outer cylinder 4. On this base piece 44 there is an auxiliary ring 43 which has a bore which is approximately half designed as a cylindrical bore 46 and the other half as a conical bore 47. This facilitates the insertion of the inner cylinder 33.

Im Raum unterhalb des Innenzylinderkolbens 34 herrscht Atmosphärendruck. Hierzu ist eine Belüftungsbohrung 48 im Bodenstück 44 vorgesehen.Atmospheric pressure prevails in the space below the inner cylinder piston 34. For this purpose, a ventilation hole 48 is provided in the base piece 44.

Am oberen Teil des Aussenzylinders ist ausserdem ein Anschlaghals 49 befestigt. Durch diesen wird die Hubstrecke des Aussenzylinders im Spannrohr 1 begrenzt.A stop neck 49 is also attached to the upper part of the outer cylinder. The stroke distance of the outer cylinder in the tensioning tube 1 is limited by this.

Die Kolbenstange 35 kann an ihrem oberen Ende über ein Kugelgelenk 50 mit einer stationären Anlenkstelle oder mit dem Rollwagen 5 verbunden werden. Kräfte, die vom Werkzeug ausgehen, werden jedoch nicht über dieses Kugelgelenk auf den Rollwagen 5a übertragen, sondern, wie im Zusammenhang mit den Ausführungsbeispielen in den Fig. 1 bis 3 schon erläutert wurde, über das Spannrohr 1, welches dieses Kugelgelenk überbrückt. Es wirken insofern keinerlei Kräfte auf dieses Kugelgelenk während des Betriebes des Werkzeugs.The piston rod 35 can be connected at its upper end via a ball joint 50 to a stationary articulation point or to the trolley 5. Forces emanating from the tool, however, are not transmitted to the trolley 5a via this ball joint, but, as has already been explained in connection with the exemplary embodiments in FIGS. 1 to 3, via the tensioning tube 1, which bridges this ball joint. In this respect, no forces act on this ball joint during the operation of the tool.

Aus der Fig. 4 ist zu ersehen, wie sich im einzelnen mit Hilfe der Spannzange 3 der Aussenzylinder 4 der Kolbenzylinderanordnung mit dem Spannrohr 1 kraftschlüssig verbinden lässt. Die Spannzange 3, welche am Spannrohr 1 befestigt ist, besitzt hierzu im wesentlichen einen Spannzangenkopf 51, der in radialer Richtung durch axiale Verschiebung eines pneumatisch betätigbaren Schiebers 52 verschoben werden kann. Der Spannzangenkopf und der Schieber besitzen zwei sich berührende Kegelflächen, die derart zueinander ausgerichtet sind, dass beim Einleiten eines Druckmediums durch die Druckleitung 12 der Schieber 52 in der Fig. 5 nach oben verschoben wird, so dass der Spannzangenkopf 51 gegen den Aussenzylinder 4 angedrückt wird. Auf diese Weise wird der Kraftschluss zwischen dem Aussenzylinder 4 und dem Spannrohr 1 hergestellt. Zur Führung des Schiebers 52 ist in der Spannzange noch ein Haltering 53 vorgesehen. Die verschiebbaren Teile sind gegeneinander durch entsprechende Dichtungen abgedichtet.From FIG. 4 it can be seen how the outer cylinder 4 of the piston-cylinder arrangement can be connected to the tensioning tube 1 in a force-locking manner with the aid of the collet 3. For this purpose, the collet 3, which is fastened to the clamping tube 1, essentially has a collet head 51 which can be displaced in the radial direction by axially displacing a pneumatically actuated slide 52. The collet head and the slider have two contacting conical surfaces which are aligned with one another in such a way that when a pressure medium is introduced through the pressure line 12, the slider 52 is displaced upward in FIG. 5, so that the collet head 51 is pressed against the outer cylinder 4 . In this way, the frictional connection between the outer cylinder 4 and the tension tube 1 is established. A retaining ring 53 is also provided in the collet for guiding the slide 52. The sliding parts are sealed against each other by appropriate seals.

Der Füllkopf 5 ist beim Ausführungsbeispiel in der Fig. 4 anders ausgebildet als beim Ausführungsbeispiel in der Fig. 3, wobei jedoch ebenfalls über ein Einstellventil 45' Druckgas zwischen dem Aussenzylinder 4 und dem Innenzylinder 33 unterhalb des nicht näher dargestellten Trennkolbens in einstellbarer Menge eingeleitet werden kann. Ferner befindet sich im Bodenstück 44 die Belüftungsbohrung 48', durch die im Innenzylinder unterhalb des Innenzylinderkolbens 33 Atmosphärendruck eingestellt werden kann. Das Bodenstück 44 ist in einem Block 54 eingeschraubt, an welchem das Werkzeug 9 schwenkbar angelenkt ist. Die Schwenkachse liegt dabei horizontal.The filling head 5 is configured differently in the exemplary embodiment in FIG. 4 than in the exemplary embodiment in FIG. 3, but pressure gas between the outer cylinder 4 and the inner cylinder 33 below the separating piston (not shown in more detail) is also introduced via an adjusting valve 45 ' can. Furthermore, in the base piece 44 there is the ventilation hole 48 ', through which atmospheric pressure 33 can be set in the inner cylinder below the inner cylinder piston. The base piece 44 is screwed into a block 54, on which the tool 9 is pivoted. The swivel axis is horizontal.

Die Zufuhr der Druckluft in das Werkzeug 9 wird bei diesem Ausführungsbeispiel über einen Schalter 55 gesteuert, der durch das Ventil 11 betätigt werden kann, sobald der Ventilkolben 14 um eine bestimmte Strecke in das Ventil mit Hilfe des Handgriffs 13 eingeschoben worden ist; vorher sind jedoch die Feststelleinrichtung 6 für den Rollwagen 5 und die Spannzange 3 betätigt worden.The supply of compressed air into the tool 9 is controlled in this embodiment via a switch 55 which can be actuated by the valve 11 as soon as the valve piston 14 has been inserted into the valve by a certain distance by means of the handle 13; however, the locking device 6 for the trolley 5 and the collet 3 have been actuated beforehand.

In den Fig. 5 und 6 ist im einzelnen das Ventil 11 dargestellt. In den Fig. 5A bis 5C ist das Ventil allein dargestellt, wobei in der Fig. 5A die Ruhestellung des Ventils gezeigt ist. Die Fig. 5B zeigt eine Ansicht des Ventils von oben, wobei die Fig. 5A eine schnittbildliche Darstellung entlang der Schnittlinie B-B zeigt. Die Fig. 5C zeigt eine schnittbildliche Darstellung entlang der Schnittlinie C-C. Das Ventil besitzt einen Kanal P, der an die Druckluftquelle angeschlossen ist. Am unteren Ende dieses Kanals ist ein Entwässerungsventil 56 für Kondenswasser vorgesehen. Im Ventil sind in axialer Richtung übereinander drei Ventilkammern 57, 58, 59 angeordnet. In diesen Ventilkammern ist der Ventilkolben 14 geführt. Der Ventilkolben weist Ventilwülste 60, 61, 62 auf. Zwischen den Ventilwülsten befinden sich Ventilnuten 63 und 64. Die Nutenbreite ist so bemessen, dass beim Einleiten der Druckluft keine Düsenwirkung auftritt, sondern ein glatter Durchtritt der Druckluft erfolgen kann. Das heisst, zwischen den Ventilnuten und den Ventilkammerwänden werden ausreichend breite Durchtrittsspalte gebildet.5 and 6, the valve 11 is shown in detail. FIGS. 5A to 5C show the valve alone, with the rest position in FIG. 5A tion of the valve is shown. FIG. 5B shows a view of the valve from above, FIG. 5A shows a sectional illustration along the section line BB. 5C shows a sectional representation along the section line CC. The valve has a channel P which is connected to the compressed air source. At the lower end of this channel, a drain valve 56 for condensed water is provided. In the valve, three valve chambers 57, 58, 59 are arranged one above the other in the axial direction. The valve piston 14 is guided in these valve chambers. The valve piston has valve beads 60, 61, 62. Valve grooves 63 and 64 are located between the valve beads. The groove width is dimensioned such that when the compressed air is introduced, there is no nozzle effect, but that the compressed air can pass through smoothly. This means that sufficiently wide passage gaps are formed between the valve grooves and the valve chamber walls.

Im Ventilkörper ist ausserdem ein Druckluftaustrittskanal P, vorgesehen. Dieser befindet sich diametral zum Drucklufteinlasskanal P in bezug auf die in der Mitte übereinander angeordneten Ventilkammern 57, 58, 59 bzw. den Kolben 14. Wie aus der Fig. 5C zu entnehmen ist, besitzt das Ventil noch einen Entlüftungskanal 65, der über eine Querverbindung mit einer Entlüftungsbohrung R verbunden ist. Ferner ist im Ventilkörper ein weiterer Druckgasaustrittskanal A vorgesehen. Dieser befindet sich bezüglich des Kolbens 14 diametral zum Entlüftungskanal.A compressed air outlet channel P is also provided in the valve body. This is located diametrically to the compressed air inlet channel P with respect to the valve chambers 57, 58, 59 or the piston 14 arranged one above the other in the middle. As can be seen from FIG. 5C, the valve also has a ventilation channel 65 which is connected via a cross connection is connected to a vent hole R. Furthermore, a further compressed gas outlet channel A is provided in the valve body. This is located diametrically with respect to the piston 14 to the ventilation channel.

In der Fig. 5A ist die Ruhestellung des Ventils bzw. des Ventilkolbens 14 dargestellt. Der Ventilkolben ist dabei durch eine Druckfeder 66 in seine unterste Stellung geschoben. Die Druckluftzufuhr aus dem Druckluftkanal P ist gegenüber den beiden Druckluftauslasskanälen P, und A durch die entsprechende Stellung der Ventilwülste, insbesondere des Ventilwulstes 61, gesperrt. Wie aus der Fig. 5A zu ersehen ist, ist der Druckluftauslasskanal P, mit der unteren Ventilkammer 59 verbunden. Der Druckluftauslasskanal A ist mit der oberen Ventilkammer 57 verbunden. Der Drucklufteinlasskanal P ist mit der mittleren Ventilkammer 58 verbunden. Durch den Ventilwulst 61 wird die Druckluftzufuhr in die untere Kammer 59 gesperrt, während die Druckluftzufuhr in die obere Kammer 57 durch den Ventilwulst 60 gesperrt ist. Wenn der Ventilkolben 14 um einen bestimmten Betrag in den Ventilblock eingeschoben wird, wie das in der Fig. 5C dargestellt ist, ergibt sich über die Ventilnut 63 eine Verbindung zwischen der mittleren Ventilkammer 58 und der oberen Ventilkammer 57. Es kann dann Druckluft aus dem Druckluftkanal P, welcher an die Druckluftquelle angeschlossen ist, über die obere Ventilkammer 57 in den Druckluftauslasskanal A einströmen. Dieser Druckluftauslasskanal A ist, wie aus den Ausführungsbeispielen der Fig. 1 und 2 zu ersehen ist, mit der Feststellvorrichtung 6 des Rollwagens 5, der Spannzange 3 bzw. 3', dem blockierbaren Zylinder 22 und den Hubeinrichtungen 28 verbunden. In der Stellung des Ventils der Fig. 5C werden daher diese Einrichtungen betätigt.5A the rest position of the valve or the valve piston 14 is shown. The valve piston is pushed into its lowest position by a compression spring 66. The compressed air supply from the compressed air duct P is blocked in relation to the two compressed air outlet ducts P and A by the corresponding position of the valve beads, in particular the valve bead 61. As can be seen from FIG. 5A, the compressed air outlet channel P is connected to the lower valve chamber 59. The compressed air outlet channel A is connected to the upper valve chamber 57. The compressed air inlet channel P is connected to the central valve chamber 58. The compressed air supply to the lower chamber 59 is blocked by the valve bead 61, while the compressed air supply to the upper chamber 57 is blocked by the valve bead 60. If the valve piston 14 is pushed into the valve block by a certain amount, as shown in FIG. 5C, a connection between the central valve chamber 58 and the upper valve chamber 57 results via the valve groove 63. Compressed air can then be drawn from the compressed air channel P, which is connected to the compressed air source, flows into the compressed air outlet channel A via the upper valve chamber 57. This compressed air outlet duct A is, as can be seen from the exemplary embodiments in FIGS. 1 and 2, connected to the locking device 6 of the trolley 5, the collet 3 or 3 ', the lockable cylinder 22 and the lifting devices 28. 5C, these devices are therefore actuated.

Die zweite Betriebsstellung des Ventils ist in den Fig. 6A und 7C dargestellt. In diesen Stellungen ist der Ventilkolben 14 um ein weiteres Stück in den Ventilblock hinein verschoben, so dass über die Ventilnut 64 eine Verbindung auch zwischen der mittleren Ventilkammer 58 zur unteren Ventilkammer 59 hergestellt ist. Es kann dann die Druckluft über diese untere Ventilkammer 59 auch in den Druckluftauslasskanal P, einströmen, welcher, wie insbesondere aus der Fig. 6A zu ersehen ist, mit dem pneumatisch betätigbaren Werkzeug 9 verbunden ist. Auf diese Weise wird gewährleistet, dass erst durch den Druckluftauslasskanal A die Druckluft in die Druckluftleitung 12 eingebracht wird und anschliessend die Druckluft, welche zum Werkzeug 9 geleitet wird, in den zweiten Druckluftauslasskanal P, eingebracht wird. Der Druckluftauslasskanal ist über eine in einer Halteplatte 67 vorgesehene Bohrung 68 mit einem entsprechenden Druckluftkanal im Werkzeug 9 verbunden.The second operating position of the valve is shown in FIGS. 6A and 7C. In these positions, the valve piston 14 is displaced a further distance into the valve block, so that a connection is also established between the central valve chamber 58 and the lower valve chamber 59 via the valve groove 64. The compressed air can then also flow via this lower valve chamber 59 into the compressed air outlet channel P, which, as can be seen in particular from FIG. 6A, is connected to the pneumatically actuated tool 9. In this way it is ensured that the compressed air is introduced into the compressed air line 12 only through the compressed air outlet channel A and then the compressed air which is directed to the tool 9 is introduced into the second compressed air outlet channel P. The compressed air outlet channel is connected via a bore 68 provided in a holding plate 67 to a corresponding compressed air channel in the tool 9.

Die Fig. 6A ist eine schnittbildliche Darstellung längs der Schnittlinie D-D in der Fig. 6B, welche eine Draufsicht des Ventils mit der Halteplatte 67 zeigt. Die Fig. 6C zeigt eine schnittbildliche Darstellung entlang der Schnittlinie E-E in der Fig. 6B.FIG. 6A is a sectional illustration along the section line D-D in FIG. 6B, which shows a top view of the valve with the holding plate 67. FIG. 6C shows a sectional illustration along the section line E-E in FIG. 6B.

Wie aus den Fig. 5 und 6 zu ersehen ist, befinden sich ausserhalb der Dichtungen 69 und 70 zur Abdichtung der Ventilräume 57 und 59 Ringräume 71 und 72, welche mit der Entlüftungsbohrung R in Verbindung stehen. Der Ringraum 72 steht über dem Entlüftungskanal 65, wie aus den Fig. 5C und 6C zu ersehen ist, mit der Entlüftungsbohrung R in Verbindung. Eine Beschädigung der Dichtungen kann sich insofern nicht nachteilig auswirken, da dann die Druckluft über diese Entlüftungskanäle und Bohrungen entweichen kann. Auf diese Weise ergibt sich eine zusätzliche Sicherung der pneumatischen Steuerung.As can be seen from FIGS. 5 and 6, outside of the seals 69 and 70 for sealing the valve spaces 57 and 59 there are annular spaces 71 and 72 which are connected to the vent hole R. The annular space 72 is connected to the ventilation bore R via the ventilation channel 65, as can be seen from FIGS. 5C and 6C. Damage to the seals cannot have an adverse effect, since the compressed air can then escape through these ventilation channels and bores. In this way, the pneumatic control is additionally secured.

Claims (24)

1. Extensible weight-balancing means (balancer) for a tool (9), in particular an assembly tool, in which weight balancing is achieved by spring means, said spring means being supported at one end thereof at a travelling supporting assembly (5a) and the tool (9) being disposed at the other, extensible end of said spring means, wherein forces originating at the tool (9) during manipulation are taken up through a support (1) bridging said spring means and are transmitted into the movable supporting assembly (5a, 30), characterised in that the support (1) bridging said spring means is provided with controllable clamping means (3) adapted to establish a rigid link between the tool (9) and the supporting assembly (5a, 30) said supporting assembly being locked during operation of the tool.
2. Weight-balancing means according to claim 1, characterised in that the tool (9) is secured to an outer cylinder (4) of a piston and cylinder assembly, the piston (34) thereof being supported through the piston-rod (35) by the supporting assembly (5a), and that during force-locked engagement, achieved by the clamping means (3), between the tool (9) and the outer cylinder (4), the clamping means (3) bridging the piston (34) and the piston-rod (35) are supported in force-locked relationship by the travelling supporting assembly (5a).
3. Weight-balancing means according to claim 1 or 2, characterised in that the hydropneumatic piston and cylinder assembly has a linear characteristic.
4. Weight-balancing means according to anyone of claims 1 to 3, characterised in that the piston and cylinder assembly includes an inner cylinder (33) in which the piston (34) and the piston-rod (35) are guided, that a balancing piston (41) movable in axial direction, is disposed between the inner cylinder (34) and the outer cylinder (4), said balancing piston dividing the space between the inner cylinder (34) and the outer cylinder (4) into two outer cylinder chambers, one of said outer cylinder chambers being filled with a hydraulic fluid and communicating through an overflow channel (42) with a cylinder chamber also filled with oil and bounded by the inner cylinder piston (34), that the other outer cylinder chamber is filled with a pressurized gas and that atmospheric pressure prevails in the other inner cylinder chamber bounded by the inner cylinder piston (34).
5. Weight-balancing means according to anyone of claims 1 to 4, characterised in that the piston-rod (35) is adapted to be removable from the piston and cylinder assembly.
6. Weight-balancing means according to anyone of claims 1 to 5, characterised in that the piston-rod (35) is adapted to be removable together with a piston-rod guide (36) from the piston and cylinder assembly.
7. Weight-balancing means according to anyone of claims 1 to 6, characterised in that the ratio of the diameter of the piston-rod (35) to the inner diameter of the inner cylinder (33) is adjustable.
8. Weight-balancing means according to anyone of claims 1 to 7, characterised in that a stop (49) is fixed to the outer cylinder (4) to limitthe axial extensibility of the outer cylinder.
9. Weight-balancing means according to anyone of claims 1 to 8, characterised in that the rigid support is designed to be a draw-in tube (1) surrounding the outer cylinder (4) of said piston and cylinder assembly, and in that the outer cylinder (4) is slideable in axial direction within the draw-in tube (1).
10. Weight-balancing means according to claim 9, characterised in that the draw-in tube (1) has a circular outer jacket adapted to be brought into force-locked engagement with the outer jacket (4) of the piston and cylinder assembly by means of a draw-in collet.
11. Weight-balancing means according to claim 10, characterised in that the draw-in collet (3) is pneumatically actuable.
12. Weight-balancing means according to anyone of claims 1 to 11, characterised in that the supporting assembly (5a) is designed as a carriage adapted to travel along the ceiling and having pneumatically actuable locking means (6).
13. Weight-balancing means according to anyone of claims 1 to 11, characterised in that the supporting assembly is designed as a carriage (30) adapted to travel along the ground and supportable on the ground by means of a pneumatically actuable jack (28).
14. Weight-balancing means according to claim 13, characterised in that the tool (9) of the carriage (30) adapted to travel along the ground is movable in vertical and horizontal direction and may be swivelled through 360°.
15. Weight-balancing means according to claim 13 or 14, characterised in that the tool (9) is mounted on a plate (25) adapted for cross-directional movement and guided along guide shafts (23, 24) attached to the carriage (30), to guide the tool in vertical and horizontal direction.
16. Weight-balancing means according to anyone of claims 13 to 15, characterised in that two hydropneumatic piston and cylinder assemblies, each disposed in a draw-in tube (1, 1') are provided for the vertical and horizontal movement of the tool (9), the outer cyliners (4) of said piston and cylinder assemblies to which the tool (9) is attached, being each adapted to be connected under pneumatic control in form-locked relationship with the associated draw-in tube (1 or 1').
17. Weight-balancing means according to claim 15 or 16, characterised in that the plate (25) adapted for cross-directional movement is attached to the outer cylinders (4) of said piston and cylinder assemblies.
18. Weight-balancing means according to anyone of claims 13 to 17, characterised in that the tool (9) is pivotably supported in a pneumatically lockable cylinder (22).
19. Weight-balancing means according to anyone of claims 1 to 18, characterised in that the tool (9) is pneumatically actuable.
20. Weight-balancing means according to claim 19, characterised in that the tool (9) is designed to be a pneumatically actuable screwdriver.
21. Weight-balancing means according to anyone of claims 1 to 20, characterised in that the draw-in in collet (3) and the clamping jaws (6) of the carriage (5a) adapted to travel along the ceiling or the jack (28) of the carriage (30) adapted to travel along and be supported on the ground are actuated by a pneumatic control device (11, 13, 14) before actuation of the tool (9).
22. Weight-balancing means according to anyone of claims 1 to 21, characterised in that the pneumatic control means (11, 13, 14) includes a valve (11) with a valve plunger (14), said valve plunger having bulb rings (60, 61, 62) and ring grooves (63, 64) disposed therebetween and being slide able in axial direction within three valves chambers (57,58,59) arranged in series along the axial direction of the valve plunger (11), that a pressure medium inlet (P) and two pressure medium outlets (PI, A) are disposed within the valve body, one of said pressure medium outlets leading to the tool (9) and the other to the draw-in collet (3, 3') and the locking or clamping means (6) or the jack (28), and that the pressure medium inlet (P) is connected into the middle valve chamber (58) and the pressure medium outlets (PI, A) are each connected to one of the two other valve chambers (57,59).
23. Weight-balancing means according to claim 21 or 22, characterised in that the zones located outside the seals (69, 70) of the two outer valve chambers (57, 59) are connected to a vent (R).
24. Weight-balancing means according to claim 22, characterised in that the valve plunger (14) is adapted to be actuated by hand.
EP79103795A 1978-10-06 1979-10-04 Extensible weight balancing device for a tool, particularly an assembling tool Expired EP0009814B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79103795T ATE395T1 (en) 1978-10-06 1979-10-04 EXTENSIBLE WEIGHT COMPENSATION DEVICE FOR A TOOL, IN PARTICULAR ASSEMBLY TOOL.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2843727 1978-10-06
DE2843727A DE2843727C2 (en) 1978-10-06 1978-10-06 Extendable holding device for a tool, in particular an assembly tool

Publications (3)

Publication Number Publication Date
EP0009814A2 EP0009814A2 (en) 1980-04-16
EP0009814A3 EP0009814A3 (en) 1980-04-30
EP0009814B1 true EP0009814B1 (en) 1981-10-28

Family

ID=6051621

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79103795A Expired EP0009814B1 (en) 1978-10-06 1979-10-04 Extensible weight balancing device for a tool, particularly an assembling tool

Country Status (4)

Country Link
US (1) US4274495A (en)
EP (1) EP0009814B1 (en)
AT (1) ATE395T1 (en)
DE (1) DE2843727C2 (en)

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JPS60502148A (en) * 1983-08-26 1985-12-12 セ−　オ−　デ−　アンテ−ル　テクニ−ク　エスア− Assembly robot consisting of assembly transfer device for transferring assembled parts, assembly method and its application
DE3331975A1 (en) * 1983-09-05 1985-03-28 Deutsche Gesellschaft für Wiederaufarbeitung von Kernbrennstoffen mbH, 3000 Hannover IMPACT SCREW DEVICE FOR REMOTE HANDLING IN SHIELDED CELLS
DE9402241U1 (en) * 1994-02-10 1995-06-14 LIKRATEC Drucklufttechnik GmbH, 80636 München Screwdriver guide with brake
DE19500320A1 (en) * 1995-01-07 1996-07-11 Hilti Ag Powder-operated stud setting tool
US5779216A (en) * 1995-11-16 1998-07-14 Ohio Tool Systems, Inc Power tool torque and weight balancing apparatus
FR2986452B1 (en) * 2012-02-06 2015-01-16 Asbe Eng SYSTEM FOR COMPENSATING A REACTION EFFORT PRODUCED BY A MOBILE TOOL
CN109682927A (en) * 2017-10-19 2019-04-26 江苏骆驼环保科技有限公司 A kind of stationary source monitoring device protection mounting device
FR3095361B1 (en) * 2019-04-25 2021-07-23 Commissariat Energie Atomique Load carrying and effort amplification rod

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Also Published As

Publication number Publication date
DE2843727C2 (en) 1986-02-06
DE2843727A1 (en) 1980-04-10
ATE395T1 (en) 1981-11-15
EP0009814A2 (en) 1980-04-16
EP0009814A3 (en) 1980-04-30
US4274495A (en) 1981-06-23

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