EP0676260B1 - Hydraulische Drehmomentimpulserzeugung - Google Patents

Hydraulische Drehmomentimpulserzeugung Download PDF

Info

Publication number
EP0676260B1
EP0676260B1 EP95302273A EP95302273A EP0676260B1 EP 0676260 B1 EP0676260 B1 EP 0676260B1 EP 95302273 A EP95302273 A EP 95302273A EP 95302273 A EP95302273 A EP 95302273A EP 0676260 B1 EP0676260 B1 EP 0676260B1
Authority
EP
European Patent Office
Prior art keywords
liner
impulse
revolution
driving blades
main shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95302273A
Other languages
English (en)
French (fr)
Other versions
EP0676260A1 (de
Inventor
Koji C/O Uryu Seisaku Ltd Tatsuno
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.)
Uryu Seisaku Ltd
Original Assignee
Uryu Seisaku Ltd
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 Uryu Seisaku Ltd filed Critical Uryu Seisaku Ltd
Publication of EP0676260A1 publication Critical patent/EP0676260A1/de
Application granted granted Critical
Publication of EP0676260B1 publication Critical patent/EP0676260B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

Definitions

  • the invention relates to a hydraulic impulse torque generator for a power driven torque wrench.
  • Figure 21 indicates an example of this type of hydraulic impulse wrench which comprises a main valve 2 for starting and stopping a supply or compressed air, and a direction switch valve 3 for selecting the direction of revolution and a rotor 4 which is driven by compressed air supplied through the main and switch valves 2, 3.
  • An impulse torque generator 5 which converts rotational output torque into an impulse torque is mounted inside a front case 6 which projects from the main body of the hydraulic impulse torque wrench 1.
  • the impulse torque generator 5 comprises a liner 8 disposed inside a liner case 7, a main valve 2, a main shaft 9 having one or more slots on its surface which are coaxially mounted within the liner 8, and blades B disposed along the slots of the main shaft 9.
  • the blades B are radially urged outwardly by springs S into contact with the inner surface of the liner 8 thereby forming a seal between the liner 8 and the main shaft 9.
  • the liner 8 has an output adjusting mechanism 10 for adjusting the strength of impact torque.
  • An impact torque is generated on the main shaft 9 when the blades reach the seal points inside the liner 8 while the liner is driven by the rotor 4.
  • the diameter of the main shaft 9 must be designed relatively large in order to obtain sufficient strength. Therefore, it is difficult to manufacture a compact impulse torque wrench because of the slots for mounting the blades on the main shaft 9 and the holes for mounting the springs. In addition, the structure of the tool becomes complex and the durability of the tool is insufficient because the springs are likely to be damaged or destroyed.
  • An objective of this invention is to provide an impulse torque generator which is more energy efficient by decreasing the energy lost due to frictional resistance between the blades and the inner surface of the liner.
  • the impulse torque generator of the present invention results in little rise of working fluid temperature, and is a compact construction with excellent durability.
  • the blade biasing springs, which are essential in a conventional impulse torque generator, are not necessary in the present invention.
  • an impulse torque generator for a hydraulic power driven wrench, said impulse torque generator comprising: a rotor; a liner, operatively connected to said rotor which liner defines a hydraulic fluid cavity and has at least n pairs of seal surfaces spaced about an inner peripheral surface of said liner; and a main shaft rotatably and coaxially mounted within said liner, and having at least two projections; characterised in that at least n driving blades are mounted within said liner in the plane of the cross section of the liner, each driving blade having two edge portions which form sealing surfaces, the distance between said edge portions of each driving blade being such that upon mating with one of said pair of seal surfaces on said liner each driving blade forms a sealed chamber with the inner wall of the liner, such that the relative pressure generated in said formed chambers can alternate between high and low, and impulse torque being imparted to the main shaft by the rotational power of the liner through the driving blades when the relative pressure in said chamber is low.
  • n is an integer greater than or equal to 2
  • n pairs of seal surfaces of the liner are symmetrically arranged with respect to the center of the revolution at an angle of 360/n degree thereby generating n impulses on the main shaft at one revolution of the liner.
  • the n pairs of seal surfaces of the liner are symmetrically arranged with respect to the center of the revolution at an angle of 360/n degree, and further grooves for releasing the hydraulic oil pressure are disposed at the surface of the liner in portions which define the longitudinal end walls of the hydraulic fluid cavity and the side of the driving blades thereby generating one impulse at one revolution of the liner.
  • the impulse generator includes n pairs of seal surfaces which are unsymmetrically arranged with respect to the center of the revolution at an angle of 360/n degree thereby generating one impulse at one revolution of the liner.
  • the n pairs of seal surfaces of the liner are symmetrically arranged with respect to the center of the revolution at an angle of 360/n degree, and further guide grooves are eccentrically disposed on the surface of the liner in portions which define the longitudinal end walls of the hydraulic fluid cavity, and guide pins introduced into the guide grooves are disposed at the end of the driving blades, such that, said driving blades are guided by the pins and guide grooves so that sealed chambers of relatively low pressure are formed between the inner wall of the liner and the driving blade, once every revolution of the liner thereby generating one impulse per revolution of the liner.
  • the n pairs of seal surfaces disposed inside the liner at an angle of 360/n degrees, and the seal surface at both ends of the driving blades meet n times during one revolution of the liner, and therefore n impulses are generated with each revolution of the liner.
  • the n pairs of seal surfaces which are not symmetrically disposed inside the liner at an angle of 360/n degrees, and the sealing surfaces at both ends of the driving blades meet one time during one revolution of the liner. Therefore, only one large impulse is generated with each revolution of the liner.
  • the n pairs of sealing surfaces, disposed inside the liner at an angle of 360/n degrees, and sealing surfaces at both ends of the driving blades meet one time during one revolution of the liner by constraining the movement of the driving blades with pins on an end of the driving blades disposed in guide grooves on the liner covers. Therefore, only one impulse is generated with each revolution of the liner.
  • Figures 1 to 6 illustrate the first embodiment of a hydraulic impulse torque generator.
  • the basic structure of the impulse torque generator of the present invention is the same as that of the prior art impulse torque generator shown in Figure 21.
  • the impulse torque wrench of the present invention includes a main valve 2 for starting and stopping a supply of compressed air, and a direction switch valve 3 for selecting the direction of the rotation.
  • a rotor 4 is driven by compressed air supplied through the valves 2, 3.
  • An impulse torque generator, which converts rotational output torque into impulse torque is mounted inside a front case 6 which projects from a main body of the hydraulic impulse torque wrench 1.
  • An impulse torque generator 5 of the first embodiment includes a liner 11 filled with hydraulic oil and disposed inside a liner case 7, and a main shaft 9 coaxially mounted within the liner 11.
  • the liner 11 has an oval profile internal cavity section and is provided with at least two pairs of sealing surfaces 11a, 11b which gradually project from the inner surface of the liner and are arranged symmetrically with respect to a center of revolution at an angle of 180 degrees.
  • the liner 11 is inserted inside the liner case 7 and both ends of the liner case 7 are closed with an upper cover 12 and a lower cover 13.
  • the covers are secured to the liner 11 with knock-pins 17 which are inserted into pin holes 12a, 13a.
  • the liner 11 and the covers 12, 13 are thereby rotatable as one solid body.
  • the upper cover 12 is covered with liner case cover 7a to fix the cover in an axial direction and to seal the hydraulic oil inside of liner 11.
  • the main shaft 9 is mounted inside the liner 11 and has two smooth shaped projections 15a, 15b symmetrically disposed with respect to the revolution center at an angle of 180 degrees.
  • a radial length and an axial length of the two projections 15a, 15b are smaller than that of the liner thereby forming hydraulic oil passages at both ends of the liner and between the top of the projections and the inner surface of the liner.
  • Two driving blades 14a, 14b which have a smoothly contoured triangle shape, are inserted inside the liner cavity and are separated by the projections 15a, 15b of the main shaft.
  • each driving blade is the same as that of inner cavity of the liner so that the driving blades contact the upper cover and the lower cover at both ends.
  • sealing surfaces 11a, 11b are designed so that they contact sealing surfaces of the driving blades 14a, 14b and form seals two times with each revolution of the liner 11.
  • a passage 16 is disposed in an outer surface of the liner for communicating with low pressure chambers L which are formed inside the liner cavity by the driving blades 14a, 14b.
  • An output adjusting mechanism is disposed in the liner parallel to the axis of the liner. This mechanism is a well known mechanism which may include for example ports 10a, 10b connecting high pressure chambers H, which are formed inside the liner cavity by the driving blades 14a, 14b, and an output adjusting valve 10c which is screwed into a screw hole 13b disposed in the lower cover 13.
  • the impulse torque generator has four sealing surfaces which are two pairs of sealing surfaces disposed on an internal peripheral surface of the liner, two radially extending projections 15a, 15b, and two driving blades 14a, 14b.
  • the number of sealing surfaces is selected depending on the desired number of impulses generated during each revolution of the liner. For instance, if n impulses are desired during one revolution of the liner, then the number of the seal surfaces inside the liner will be 2n (n pairs), and there will be n projections radially projecting from the main shaft and n driving blades.
  • the rotor 4 is rotated by introducing compressed air into the rotor 4 of the main body by opening the main valve and the switch valve.
  • the revolution power is transmitted to the liner 11.
  • Figure 6(a) indicates the position where no impulse is generated on the main shaft.
  • Figures 6(b),(c),(d) indicates the positions where the liner 11 rotates through an angle of 90 degrees respectively.
  • An impulse is generated, as indicated in Figure 6(b) and Figure 6(d), when the seal surfaces 11a, 11b and the seal surfaces of the driving blades meet together and the inner cavity of the liner 11 is divided into four chambers.
  • the instant an impulse torque is generated on the main shaft the volume of high pressure chamber H decreases and the volume of low pressure chamber L increases because of the shape of the inner surface of the liner.
  • the high pressure chamber is changed to a low pressure chamber and vise versa. That is, as the rotor drives the liner 11, seal surfaces 11a, 11b of the liner meet the sealing surfaces of the driving blades 14a, 14b.
  • Each chamber becomes a high pressure chamber or a low pressure chamber
  • the driving blades 14a, 14b are pushed toward the low pressure chamber, then,the rotational power of the liner 11 is exerted on projections 15a, 15b of the main shaft 9 through the driving blades 14a, 14b and provides an impulse on the main shaft 9, which is two impulses generated during each revolution of the liner.
  • each chamber becomes high pressure or low pressure chamber for an instant.
  • the driving blades are pushed toward the low pressure chamber, then the seals at the sealing surfaces are broken and hydraulic compressed oil in the high pressure chamber will flow out through gaps between the seal surfaces into the low pressure chamber, and therefore no impulse is generated on the main shaft 9.
  • a second embodiment of the present invention is shown in Figures 7 to 12.
  • the basic structure of the second embodiment is the same as the first embodiment explained before.
  • An impulse generator filled with hydraulic oil, is disposed inside a liner case 7, and a main shaft 9 is coaxially mounted within the center of a liner 21.
  • the liner 21 has an oval profile internal cavity section and two pairs of sealing surfaces 21a, 21b project from the inner surface of the liner and are spaced symmetrically with respect to the center of the revolution by an angle of 180 degrees.
  • the cylindrical liner 21 is inserted inside the liner case 7 and both ends of the liner case 7 are covered with an upper cover 22 and a lower cover 23.
  • the covers 22, 23 are secured to the liner 21 by means of knock-pins 27 inserted into pin holes 22a, 23a.
  • the covers 22, 23 and the liner 21 are thereby rotatable as a solid body.
  • the upper cover 22 is covered with liner case cover 7a to fix the cover along an axial direction and to seal the hydraulic oil inside of the liner 21.
  • Grooves 28a, 28b are provided in the surfaces of the upper cover 22 and the lower cover 23 for releasing the pressure of the hydraulic oil.
  • a main shaft 9 is mounted inside the liner 21 and has two projections 25a, 25b.
  • the projections have smooth contours and are symmetrically disposed with respect to the center of revolution by an angle of 180 degrees.
  • the radial length and the axial length of the two projections 25a, 25b are smaller than that of the liner and thereby form hydraulic oil passages at both ends of the liner and between the top of the projections and the inner surface of the liner.
  • Two driving blades 24a, 24b are inserted inside the liner 21 cavity and are separated by projections 25a, 25b of the main shaft.
  • the blades 24a, 24b have a smoothly contoured triangle shape.
  • the axial length of the driving blades is same as that of the inner cavity of the liner so that the driving blades contact the upper cover and the lower cover at both ends.
  • Grooves 29a, 29b are provided in the surfaces of the driving blades 24a, 24b for releasing the pressure of the hydraulic oil.
  • the sealing surfaces 21a, 21b and the sealing surfaces of the driving blades 24a, 24b meet and contact each other to form seals two times during each revolution of the liner 21.
  • the grooves 28a, 28b are disposed on both of the upper and the lower cover, but a groove in only one of the covers will suffice.
  • a groove for releasing the hydraulic oil pressure would be disposed on the corresponding side of the driving blades 24a, 24b.
  • a passage 26 is disposed in an outer surface of the liner 21 and communicates with low pressure chambers L which are formed inside the liner cavity by the driving blades 24a, 24b.
  • An output adjusting mechanism is disposed in the liner parallel to the axis of the liner 21. This mechanism is well known and, for example, may comprise ports 10a, 10b which connect high pressure chambers H formed inside the liner cavity by the driving blades 24a, 24b and an output adjusting valve 10c screwed into a screw hole 23b disposed in the lower cover 23.
  • the impulse torque generator has 4 sealing surfaces 21a, 21b, which are two pairs of sealing surfaces disposed on the internal peripheral surface of the liner 21, two projections 25a, 25b radially projecting from the main shaft 9, and two driving blades 24a, 24b.
  • the number of sealing surfaces is not restricted to this number. The number of sealing surfaces may be selected depending on the desired strength of the impulse generated during each revolution of the liner. For instance, if more than n (n is greater than 3) pairs of seal surfaces are provided on the inner surface of the liner, then n projections will radially project from the main shaft, and n driving blades are necessary, and consequently a greater impulse is generated.
  • the rotor 4 is rotated by introducing compressed air into the rotor 4 of the main body by opening the main valve 2 and the switch valve 3.
  • the revolution power is transmitted to the liner 31.
  • Figure 12(a) indicates the position where no impulse is generated on the main shaft 9.
  • Figures 12(b), (c), and (d) indicates the liner 31 rotated through an angle of 90 degrees, respectively.
  • An impulse is generated as indicated in Figure 12(b) when the sealing surfaces 21a, 21b and the sealing surfaces of the driving blades 24a, 24b meet, and the inner cavity of the liner 21 is divided into four chambers.
  • the instant an impulse torque is generated on the main shaft 9 the volume of a high pressure chamber H decreases and a volume of a low pressure chamber L increases because of the shape of the inner cavity of the liner, and then the high pressure chamber changes to a low pressure chamber and vise versa. That is, as the rotor 4 drives the liner 21, seal surfaces 21a, 21b of the liner meet the sealing surfaces of the driving blade 24a, 24b and each chamber alternately becomes a high pressure chamber or a low pressure chamber.
  • the driving blades 24a, 24b are pushed toward the lower pressure chamber, the sealing surfaces have formed a sealed chamber and the rotational power of the liner 21 is exerted on projections 25a, 25b of the main shaft 9 through the driving blades 24a, 24b.
  • An impulse is intermittently provided on the main shaft 9, which represents one impulse with each revolution of the liner for tightening or loosening bolts or nuts.
  • each chamber becomes a high pressure or a low pressure chamber for an instant, and the driving blades are pushed toward the low pressure chamber and thus seals formed between the sealing surfaces are broken and hydraulic compressed oil in the high pressure chamber will flow out through gaps between the seal surfaces into a low pressure chamber, and therefore no impulse is generated.
  • the basic structure of the third embodiment is the same as the first embodiment described above.
  • An impulse generator filled with hydraulic oil, is disposed inside a liner case 7, and a main shaft 9 is coaxially mounted in the liner 31.
  • the liner 31 has an oval profile internal cavity section and two pairs of sealing surfaces 31a, 31b are provided on an internal peripheral surface of the liner 31.
  • the sealing surfaces 31a, 31b are smoothly contoured and are not arranged symmetrically with respect to the center of the revolution at an angle of 180 degrees.
  • the cylindrical liner 31 is inserted inside the liner case 7 and the ends of the liner 31 are covered with an upper cover 32 and a lower cover 33 which are secured to the liner 31 with knock-pins 37 inserted into pin holes 32a, 33a.
  • the assembled liner and covers are thereby rotatable as a solid body.
  • the upper cover 32 is covered with a liner case cover 7a for fixing the cover in the axial direction and for sealing the hydraulic oil inside of the liner 31.
  • a main shaft 9, mounted inside of the liner 31, has two smoothly contoured projections 35a, 35b symmetrically disposed with respect to the revolution center by an angle of 180 degrees.
  • the radial length and the axial length of the two projections 35a, 35b are smaller than that of the liner, thereby forming hydraulic oil passages between the driving blades and both ends of the liner 31, and between the top of the projections 35a ⁇ ,35b and the inner surface of the liner 31.
  • Two driving blades 34a, 34b having a triangle shape with smooth contours and of different size, are inserted inside the liner cavity and are separated by projections 35a, 35b of the main shaft 9.
  • the driving blade 34a is larger than the other driving blade 34b.
  • the axial length of the driving blades 34a, 34b are the same as the axial length of the inner cavity of the liner so that the driving blades contact the upper cover and the lower cover at both ends.
  • Sealing surfaces 34a, 34b are provided at both ends of the driving blades. The sealing surfaces of the driving blades 34a, 34b meet and contact with the sealing surfaces 31a, 31b of the liner to form a seal one time with each revolution of the liner 31.
  • two pairs of 4 sealing surfaces 31a, 31b are not disposed symmetrically with respect to the center of revolution around the inner surface of the liner 31 at an angle of 180 degrees and driving blades of different size are inserted in the liner 31.
  • the seal surfaces 31a, 31b and the seal surfaces of the driving blades 34a, 34b meet only one time with each revolution of the liner 31 and one impulse is generated on the main shaft 9.
  • it is possible to generate one impulse during one revolution by adapting a symmetrically disposed crank-like shaped sealing surface along the driving blade, an inclined sealing surface along the driving blade, or a V-shaped seal surface.
  • a passage 36 is disposed in an outer surface of the liner 31, and communicates with low pressure chambers L which are formed inside the liner cavity by the driving blades 34a, 34b.
  • An output adjusting mechanism is disposed in the liner parallel to the axis of the liner 31. This mechanism is a well known mechanism and may comprise ports 10a, 10b which connect high pressure chambers H and an output adjusting valve 10c screwed into a screw hole 33b in the lower cover 33.
  • the impulse torque generator includes sealing surfaces 31a, 31b, which are two pairs of sealing surfaces disposed on the internal peripheral surface of the liner 31, two projections 35a, 35b radially projecting from the main shaft 9, and two driving blades 34a, 34b.
  • the number of the sealing surfaces is not restricted to this number.
  • the number of the seal surfaces are selected depending on the desired strength of the impulse generated during each revolution of the liner. For instance, if there is provided more than n (n is greater than 3) pairs of sealing surfaces around the inner surface of the liner, then it will be necessary to provide n projections radially projecting from the main shaft and n driving blades, and consequently, a greater impulse is generated.
  • the rotor 4 is actuated by introducing compressed air into the rotor 4 of the main body by opening the main valve 2 and the switch valve 3.
  • the revolution power is transmitted to the liner 21.
  • Figure 14(a) shows the position in which no impulse is generated on the main shaft 9.
  • Figures 14(b), (c), (d) indicate positions of the liner 31 rotated about an angle of 90 degrees respectively.
  • An impulse is generated, as shown in Figure 14(b), when the sealing surfaces 31a, 31b and the sealing surfaces of the driving blades 34a, 34b meet together and the inner cavity of the liner 31 is divided into four chambers.
  • the instant an impulse torque is generated on the main shaft 9, the volume of a high pressure chamber H decreases and the volume of a low pressure chamber L increases because of the shape of the inner surface of the liner.
  • the high pressure chambers are then changed to low pressure chambers and vise versa. That is, as the rotor drives the liner 31, sealing surfaces 31a, 31b of the liner meet the sealing surfaces of the driving blades 34a, 34b, and each chamber becomes a high pressure chamber or a low pressure chamber.
  • each chamber becomes a high pressure chamber H or a low pressure chamber L for a very short period, and then the driving blades are pushed toward the low pressure chamber.
  • the seal between the sealing surfaces of the liner and the driving blades are broken, and hydraulic oil starts to flow from the high pressure chamber to the low pressure chamber through the broken seal and no impulse is generated on the main.shaft 9 at this stage.
  • the basic structure of the fourth embodiment is same as the first embodiment explained before.
  • An impulse generator filled with hydraulic oil, is disposed inside a liner case 7, and a main shaft 9 is coaxially mounted through the center of liner 41.
  • the liner 41 has an oval profile internal cavity section and two pairs or four sealing surfaces, 41a, 41b are provided.
  • the sealing surfaces project from the inner surface of the liner and are arranged symmetrically with respect to a center of the revolution at an angle of 180 degrees.
  • the cylindrical liner 41 is inserted inside the liner case 7 and the ends of the liner case 7 are covered with an upper cover 42 and a lower cover 43 which are secured to the liner 41 with knock-pins (not shown) inserted into pin holes 42a, 43a.
  • the assembled body is thereby rotatable as a solid body.
  • the upper cover 42 is covered with liner case cover 7a for fixing the cover in the axial direction and to seal the hydraulic oil inside the liner 41.
  • Guide grooves 42c, 43c are provided on the surface of the upper cover 42 and the lower cover 43. As shown in Figure 18 and Figure 19, the guide grooves 42c, 43c are eccentrically disposed with respect to the revolution center of the liner, and the direction of the eccentricity of the two guide grooves is in a 180 degree opposite direction.
  • a hole 43e and an oil inlet 43f are provided in the lower cover 43.
  • a pin 48 is inserted in the hole 43e for fixing the cover to the liner cover and to prevent rotation of the lower cover 43 with respect to the liner case 7. This construction is also applicable to the previously described embodiments of the present invention.
  • a main shaft 9 is mounted inside the liner 41 and has two smooth shaped projections 45a, 45b symmetrically disposed with respect to the revolution center by an angle of 180 degrees.
  • the radial length and the axial length of the two projections 45a, 45b are smaller than that of the liner thereby forming hydraulic oil passages at both ends of the liner and between the top of the projections and the inner surface of the liner.
  • Two same-size driving blades 44a, 44b of triangle shape with smooth contours are inserted inside of the liner cavity and are separated by projections 45a, 45b of the main shaft.
  • the axial length of the driving blades is the same as that of the inner cavity of the liner so that the driving blades contact both the upper cover and the lower cover at their ends.
  • Both radial ends of the driving blades 44a, 44b are formed with sealing surfaces for contacting the sealing surfaces of the liner 41.
  • guide pins 47a, 47b are inserted in the guide grooves 42c, 43c at either one of the longitudinal ends of the driving blades 44a, 44b. More specifically, the guide pin 47b is inserted in the guide groove 42c and guide pin 47a in the guide groove 43c.
  • the sealing surfaces of the liner and driving blades meet two times during each revolution of the liner, but the motion of the driving blade is limited by the guide grooves, and therefore an impulse is generated at every other meeting. Therefore, only one impulse is generated with each revolution of the liner.
  • a passage 46 is disposed in an outer surface of the liner 41.
  • the passage ditch 46 connects low pressure chambers L which are formed inside the liner cavity by the driving blades 44a, 44b.
  • An output adjusting mechanism is disposed in the liner parallel to the axis of the liner 41. This mechanism is a well known mechanism, and may include ports 10a, 10b which communicate with high pressure chambers H, formed inside the liner cavity by the driving blades 44a, 44b, and an output adjusting valve 10c which is screwed into a screw hole 43b disposed in the lower cover 43.
  • An accumulator 49 for absorbing the heat expansion of the hydraulic oil is disposed parallel to the axis of the liner 41.
  • the accumulator 49 includes a piston 49a, and an air permeable member 49b in which one end of the accumulator 49 is connected to the inner cavity of the liner 41 via a small passage 43d disposed in the lower cover 43 of the liner. The other end is connected to the open air through the air permeable member 49b.
  • a small hole 42b is disposed in the upper cover 43 and a gap is provided between the upper cover 42 and the liner case 7a.
  • the impulse torque generator includes four sealing surfaces 41a, 41b, which are two pairs of sealing surfaces disposed inside the liner 41, two projections 45a, 45b radially projecting from the main shaft 9, and two driving blades 44a, 44b.
  • the number of sealing surfaces is not restricted to this number.
  • the number of the seal surfaces is selected depending on the desired strength of the impulse generated during one revolution of the liner. For instance, if there is provided more than n (n is greater than 3) pairs of sealing surfaces around the inner surface of the liner, then n projections radially projecting from the main shaft and n driving blades are necessary and will result in the generation of a greater impulse.
  • the rotor 4 is actuated by introducing compressed air into the rotor 4 of the main body by opening the main valve 2 and the switch valve 3.
  • the revolution power is transmitted to the liner 41.
  • Figure 20(a) shows the state where no impulse is generated on the main shaft 9.
  • Figures 20(b), (c), (d) show the liner 41 rotated about an angle of 90 degrees respectively.
  • An impulse is generated as indicated in Figure 20(b) when the sealing surfaces 41a, 41b and the sealing surfaces of the driving blades 44a, 44b meet together and the inner cavity of the liner 41 is divided into four chambers.
  • the instant an impulse torque is generated on the main shaft 9, the volume of a high pressure chamber H decreases and the volume of a low pressure chamber L increases because of the shape of the inner cavity of the liner 41.
  • the high pressure chamber changes to a low pressure chamber and vise versa. That is, as the rotor 4 drives the liner 41, sealing surfaces 41a, 41b of the liner meet the sealing surfaces of the driving blades 44a, 44b, and each chamber becomes a high pressure chamber or a low pressure chamber.
  • the driving blades 44a, 44b are pushed toward the low pressure chamber, and the sealing surfaces have completely sealed and thereby the rotational power of the liner 41 is exerted on projections 45a, 45b of the main shaft 9 through the driving blade 44a, 44b.
  • An impulse is provided on the main shaft 9 intermittently, which is one impulse with one revolution of the liner for tightening or loosening of bolts or nuts.
  • each chamber becomes a high pressure or a low pressure chamber, and the driving blades are pushed toward the low pressure chamber. Then the seals formed between the sealing surfaces are broken and the hydraulic compressed oil in the high pressure chambers flows out through gaps between the sealing surfaces into a low pressure chamber, and therefore no impulse is generated on the main shaft.
  • the liner case 7 will change in the reverse direction of Figure 20, that is, the orientation of the inside of the liner changes as shown in Figures 20(d)-(c)-(b)-(a)-(d), and a reverse direction impulse on the main shaft 9 is generated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Actuator (AREA)

Claims (5)

  1. Impulsdrehmomenterzeuger für einen mit hydraulischer Kraft angetriebenen Schraubenschlüssel, wobei der genannte Impulsdrehmomenterzeuger folgendes umfasst:
    einen Läufer (4);
    eine Büchse (11; 21; 31; 41), die funktionsmäßig mit dem genannten Läufer verbunden ist, wobei die genannte Büchse einen Hydraulikfluidhohlraum definiert und wenigstens n Paar Dichtflächen (11a, 11b) hat, die um eine innere Umfangsfläche der genannten Büchse herum beabstandet angeordnet sind; und
    eine Hauptwelle (9), die rotierbar und koaxial in der genannten Büchse montiert ist und wenigstens zwei Vorsprünge (15a, 15b) hat;
    dadurch gekennzeichnet, dass in der genannten Büchse in der Ebene des Querschnitts der Büchse wenigstens n Azltriebsblätter (14a; 14b; 24a; 24b; 34a; 34b; 44a; 44b) montiert sind, wobei jedes Ahtriebsblatt zwei Randteile hat, die Dichtflächen bilden, wobei der Abstand zwischen den genannten Randteilen jedes Antriebsblatts so ist, dass jedes Antriebsblatt beim Zusammenlaufen mit einer der Dichtflächen des genannten Paars an der genannten Büchse mit der inneren Wand der Büchse eine abgedichtete Kammer bildet, so dass der in den genannten gebildeten Kammern erzeugte relative Druck zwischen hoch und niedrig wechseln kann, und wobei der Hauptwelle von der Rotationskraft der Büchse durch die Antriebsblätter Impulsdrehmoment verliehen wird, wenn der relative Druck in der genannten Kammer niedrig ist,
    wobei n eine Ganzzahl ist, die größer oder gleich 2 ist.
  2. Impulsdrehmomenterzeuger für einen mit hydraulischer Kraft angetriebenen Schraubenschlüssel gemäß Anspruch 1, wobei die n Paare Dichtflächen der Büchse (11) in Bezug auf die Mitte der Umdrehung in einem Winkel von 360/n Grad symmetrisch angeordnet sind, wodurch an der Hauptwelle (9) bei einer Umdrehung der Büchse n Impulse erzeugt werden.
  3. Impulsdrehmomenterzeuger für einen mit hydraulischer Kraft angetriebenen Schraubenschlüssel gemäß Anspruch 1, wobei die n Paare Dichtflächen der Büchse (21) in Bezug auf die Mitte der Umdrehung in einem Winkel von 360/n Grad symmetrisch angeordnet sind und an der Oberfläche der Büchse (22, 23) in Teilen, die die Längsendwände des Hydraulikfluidhohlraums und die Seite der Antriebsblätter (24a, 24b) definieren, weitere Rillen (28a, 28b, 29a, 29b) zum Freisetzen des Hydrauliköldrucks angeordnet sind, wodurch bei einer Umdrehung der Büchse ein Impuls erzeugt wird.
  4. Impulsdrehmomenterzeuger für einen mit hydraulischer Kraft angetriebenen Schraubenschlüssel gemäß Anspruch 1, wobei die n Paare Dichtflächen der Büchse (31) in Bezug auf die Mitte der Umdrehung in einem Winkel von 360/n Grad unsymmetrisch angeordnet sind, wodurch bei einer Umdrehung der Büchse ein Impuls erzeugt wird.
  5. Impulsdrehmomenterzeuger für einen mit hydraulischer Kraft angetriebenen Schraubenschlüssel gemäß Anspruch 1, wobei die n Paare Dichtflächen der Büchse (41) in Bezug auf die Mitte der Umdrehung in einem Winkel von 360/n Grad symmetrisch angeordnet sind und an der Oberfläche der Büchse in Teilen, die die Längsendwände des Hydraulikfluidhohlraums definieren, weitere Rillen (42c, 43c) exzentrisch angeordnet sind und in die Führungsrillen eingeführte Führungsstifte (47a, 47b) am Ende der Antriebsblätter (44a, 44b) angeordnet sind, so dass die genannten Antriebsblätter von den Stiften und Führungsrillen geführt werden, so dass zwischen der inneren Wand der Büchse und dem Antriebsblatt bei jeder Umdrehung der Büchse einmal abgedichtete Kammern relativ niedrigen Drucks gebildet werden, wodurch pro Umdrehung der Büchse ein Impuls erzeugt wird.
EP95302273A 1994-04-08 1995-04-05 Hydraulische Drehmomentimpulserzeugung Expired - Lifetime EP0676260B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP95753/94 1994-04-08
JP9575394 1994-04-08
JP7086393A JP2804904B2 (ja) 1994-04-08 1995-03-17 油圧式トルクレンチの打撃トルク発生装置
JP86393/95 1995-03-17

Publications (2)

Publication Number Publication Date
EP0676260A1 EP0676260A1 (de) 1995-10-11
EP0676260B1 true EP0676260B1 (de) 1999-02-17

Family

ID=26427527

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95302273A Expired - Lifetime EP0676260B1 (de) 1994-04-08 1995-04-05 Hydraulische Drehmomentimpulserzeugung

Country Status (4)

Country Link
EP (1) EP0676260B1 (de)
JP (1) JP2804904B2 (de)
KR (1) KR100334211B1 (de)
DE (1) DE69507845T2 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6708778B2 (en) 2001-01-12 2004-03-23 Makita Corporation Hydraulic unit with increased torque
JP5547004B2 (ja) * 2010-09-07 2014-07-09 瓜生製作株式会社 油圧式トルクレンチの打撃トルク調節装置
KR102431500B1 (ko) 2017-08-31 2022-08-11 우류세이사쿠 가부시키가이샤 유압식 토크 렌치의 타격 토크 발생 장치
JP6762572B2 (ja) * 2017-08-31 2020-09-30 瓜生製作株式会社 油圧式トルクレンチの打撃トルク発生装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1074078A (en) * 1965-08-17 1967-06-28 Ingersoll Rand Co Rotary impulse tools
SE460713B (sv) * 1986-04-22 1989-11-13 Atlas Copco Ab Hydrauliskt momentimpulsverk
SE450222B (sv) * 1986-07-24 1987-06-15 Atlas Copco Ab Hydraulisk momentimpulsgenerator
GB2240500B (en) * 1990-02-06 1993-09-22 Desoutter Ltd Hydraulic torque impulse generator
SE469322B (sv) * 1992-05-05 1993-06-21 Atlas Copco Tools Ab Hydraulisk momentimpulsgenerator

Also Published As

Publication number Publication date
KR100334211B1 (ko) 2002-11-18
DE69507845T2 (de) 1999-06-17
DE69507845D1 (de) 1999-03-25
JP2804904B2 (ja) 1998-09-30
EP0676260A1 (de) 1995-10-11
JPH07328944A (ja) 1995-12-19

Similar Documents

Publication Publication Date Title
US4553948A (en) Oil pressure type pneumatic torque wrench
US5544710A (en) Pulse tool
US4547137A (en) Scroll type fluid compressor with thickened spiral elements
JP3746482B2 (ja) 空気式ロータリツール
US4867000A (en) Linear motion power cylinder
KR920004045A (ko) 진동발생장치
US5741186A (en) Impulse torque generator for a hydraulic power wrench
EP0353106B1 (de) Hydraulischer Drehimpuls-Generator für Schraubenschlüssel
CA1222987A (en) Scroll type fluid displacement apparatus
EP0676260B1 (de) Hydraulische Drehmomentimpulserzeugung
WO2004007968A1 (en) Volume screw machine of rotary type
US6230823B1 (en) Downhole motor
US6079386A (en) Rotary machine
EP3450106B1 (de) Schlagdrehmomenterzeuger für hydraulischen kraftschrauber
JP6762572B2 (ja) 油圧式トルクレンチの打撃トルク発生装置
US5517960A (en) Rotating internal combustion engine
US4925378A (en) Rotary vane compressor with valve controlled pressure biased sealing means
JP2007501354A (ja) 主及びサテライト・ロータを有するロータリーマシーン
JP4121616B2 (ja) 油圧式トルクレンチの打撃トルク発生装置
JP2023177373A (ja) 油圧式トルクレンチの打撃トルク発生装置
JP4329029B2 (ja) 油圧パルス発生装置
JP2779749B2 (ja) 油圧式トルクレンチの打撃トルク発生装置
JP2024101590A (ja) 油圧式トルクレンチの打撃トルク発生装置
KR200239970Y1 (ko) 에어콘용 밀폐형 콤프레샤
JPS62246481A (ja) ２ブレ−ド式インパルスレンチ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19960308

17Q First examination report despatched

Effective date: 19970407

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

ITF It: translation for a ep patent filed
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 69507845

Country of ref document: DE

Date of ref document: 19990325

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140203

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140416

Year of fee payment: 20

Ref country code: SE

Payment date: 20140417

Year of fee payment: 20

Ref country code: DE

Payment date: 20140419

Year of fee payment: 20

Ref country code: IT

Payment date: 20140408

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 69507845

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20150404

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20150404