WO2007106028A1 - An electric motor driven tool - Google Patents

An electric motor driven tool Download PDF

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Publication number
WO2007106028A1
WO2007106028A1 PCT/SE2007/050138 SE2007050138W WO2007106028A1 WO 2007106028 A1 WO2007106028 A1 WO 2007106028A1 SE 2007050138 W SE2007050138 W SE 2007050138W WO 2007106028 A1 WO2007106028 A1 WO 2007106028A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
tool
tool according
fluid
axial
Prior art date
Application number
PCT/SE2007/050138
Other languages
French (fr)
Inventor
Lind Björn
Original Assignee
Lind Finance & Development Ab
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 Lind Finance & Development Ab filed Critical Lind Finance & Development Ab
Publication of WO2007106028A1 publication Critical patent/WO2007106028A1/en

Links

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23BTURNING; BORING
    • B23B31/00Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/005Cylindrical shanks of tools
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23QDETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q1/00Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
    • B23Q1/70Stationary or movable members for carrying working-spindles for attachment of tools or work
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23QDETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/02Driving main working members
    • B23Q5/04Driving main working members rotary shafts, e.g. working-spindles
    • B23Q5/10Driving main working members rotary shafts, e.g. working-spindles driven essentially by electrical means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00Bearings not otherwise provided for
    • F16C32/06Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0685Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23BTURNING; BORING
    • B23B2220/00Details of turning, boring or drilling processes
    • B23B2220/36Turning, boring or drilling at high speeds
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23BTURNING; BORING
    • B23B2260/00Details of constructional elements
    • B23B2260/008Bearings
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23BTURNING; BORING
    • B23B2260/00Details of constructional elements
    • B23B2260/062Electric motors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00Apparatus used in shaping articles
    • F16C2322/39General build up of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a tool designed for high speeds and with a structure according to the preamble of Patent Claim 1.
  • the tool according to the invention is designed for speeds of up to 500,000 revolutions per minute and higher, for which reason the tool has a unique design. It is also possible for the tool to be made small, for example with a shaft diameter of as little as 2 mm or less.
  • the tool is especially suitable for use in nanotechnology, for example for grinding, drilling, milling, engraving, etc.
  • the tool has a novel design, and the special features that distinguish it from the prior art in this field are set forth in the characterizing parts of the patent claims.
  • Figure 1 is a schematic view of the tool in one position
  • Figure 2 is a schematic view of the tool in a position different than the first position
  • Figures IA and 2 A show alternative embodiments of the tool according to Figures 1 and 2
  • Figures IB and 2B show further variations of the tool according to Figures 1 and 2
  • Figure 3 shows a cross section along the line III-III in Figure 4 with pressure distribution around the radial fluid bearing
  • Figure 4 shows a longitudinal section through the tool according to a variant
  • Figure 5 is a schematic view of a cross section along the line V-V in Figure 6 with the pressure distribution around the radial fluid bearing
  • Figure 6 shows a longitudinal section through the tool according to the invention
  • Figures 7 and 8 show alternative embodiments of the invention.
  • reference number 1 designates a shaft of a rotatably driven tool, whose machining tool end is designated by reference number 2.
  • the machining tool 2 can be integrated in or releasably connected to the shaft 1.
  • the tool is mounted with its shaft in a radial fluid bearing 3 formed by an axial bore 4 in a housing 5.
  • Adjacent to the machining end 2 of the shaft 1, the latter is provided with a rotor 6 driven by a rotating magnetic field generated by a stator 6', which rotor is received freely in the stator 6' in the housing 5, as is shown.
  • the stator 6' can of course be arranged instead in a separate part, fastened to the housing.
  • an axial bearing 8 Adjacent to the rotor 6, an axial bearing 8 is arranged for cooperation with a bottom end surface 9 of a cavity 7 receiving the stator 6'.
  • the axial bearing 8 is fed with the same bearing fluid as the radial bearing.
  • Figures IB and 2B show how the tool according to the invention is also provided with an axial bearing 30, for example in the form of a ceramic ball, acting against the inner end surfaces of the shaft 1 and movable in the axial direction.
  • Fluid, liquid or gas (for example water or air), for the fluid bearing of the tool shaft 1 is introduced into an inlet 11, as is indicated by an arrow 12, and distributes itself in the radial bearing 3 on the one hand towards the axial bearing 8 and on the other hand towards the inner end of the shaft located in the housing.
  • the introduced bearing fluid is conveyed away via outlet channels 13 and 14.
  • a counter- force acting against the axial bearing is generated by means of the bearing fluid being exposed to underpressure, i.e. forced out with underpressure via the outlet channels 13 and 14.
  • the bearing fluid that reaches the axial bearing 8, 9 is prevented from leaking out in the turbine wheel end on account of an underpressure prevailing in the space round the axial bearing.
  • the rotor 6 can be dimensioned, or the material thereof chosen, such that its mass inertia increases the rotation energy and thereby increases the machining capacity of the tool.
  • the housing 5, with the tool located therein in the position shown in Figure 1 can be displaced to and away from the workpiece.
  • This can be done (see Figure 1) by a liquid column 15 being formed between the end of the shaft 1 in the housing 5 and a piston 16 that is displaceable axially in the bore 4.
  • the liquid column which is located between the end of the shaft 1 and the piston 16, and which (when the bearing medium is a liquid) is formed by the bearing fluid flowing from the inlet 11 to the outlet 14, is at all times fully developed, this by virtue of the fact that the piston 16 in the starting position keeps the outlet line 14 open.
  • the piston 16 is quickly forced in by the desired distance, which means that the shaft 1 and thus the tool are displaced by said distance.
  • the piston 16 is drawn back to the starting position, the tool naturally follows it. It must be understood that these displacements of the tool backwards and forwards in the housing 1 take place within a very short time, for which reason the liquid column is not influenced to any appreciable degree by the bearing fluid that flows towards the end of the shaft and the liquid column.
  • the bearing medium is instead composed of a gas (air) (see Figures IA and 2A)
  • a liquid is delivered without any appreciable pressure via a channel 28 in order to ensure the liquid column 15.
  • the action of the stator 6', and thus of the rotating magnetic field, on the rotor 6 can remain essentially the same, even when the tool is displaced outwards from the housing 5.
  • Figures 3-6 show schematic views of a tool according to the invention, which differs from the tool described in connection with Figures 1 and 2 only in that the radial fluid bearings have been given a special design.
  • Figure 4 thus shows two radial fluid bearings 17 and 18.
  • the non-bearing outer side of each bearing is provided with three axial channels 19 (see Fig. 3) which at one end comprise a radial channel 20 in the bearing, opening into the bearing surface, and which at the other end open into a space 21 present between the two bearings.
  • the space 21 is filled with bearing fluid, which flows on the one hand into the gap between the shaft 1 and the bearing surface and on the other hand via the channels 19 and the radial channels 20 to the bearing gap.
  • the supply of bearing fluid also through the channels 20 means that a pressure distribution curve is formed in the bearing gap between each radial bearing 17 and 18 and the shaft 1, as shown in Figure 3.
  • Figure 5 shows another embodiment for solving the problems mentioned earlier.
  • the arrangement differs from Figures 3 and 4 in that the bearing surface of each bearing 17 and 18 supporting the shaft 1 has regular radial formations deviating from the purely circular shape.
  • the bearing surface has three radially widened, axial parts 22, which means that the bearing fluid flowing between the fluid bearing and the shaft is compressed in the "narrower" areas during rotation of the shaft, for which reason a pressure curve is also obtained corresponding to the one in Figure 5.
  • the preferred embodiment of the invention described above can be modified in accordance with what is shown in Figures 7 and 8.
  • this force can, as shown in Figure 7, instead be generated by applying an external force component generated, for example, by an air stream 25 directed more or less axially towards the rotor 6 (see Figure 7).
  • Figure 8 shows the axially inwardly directed force generated by a magnet 27, attracting the rotor 6.
  • this magnet 27 can be replaced by or supplemented with a magnet 27 placed at the inner end of the shaft 1 and attracting the axle 1.
  • the above-described tool according to the invention can of course be combined to form a tool with several rotating shafts provided with machining tools and operating, if necessary, at different speeds.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Turning (AREA)

Abstract

Tool in the form of a rotating driven shaft (1) with a tooled (2) end and provided with at least one drive part (6, 6') for driving the tool, which shaft is mounted in a housing (5) with at least one radial fluid bearing (3, 17, 18). The tool is characterized in that at least one drive part (6, 6') is arranged on the shaft (1) between said at least one radial fluid bearing (3, 17) and the tooled end.

Description

AN ELECTRIC MOTOR DRIVEN TOOL
The present invention relates to a tool designed for high speeds and with a structure according to the preamble of Patent Claim 1.
The tool according to the invention is designed for speeds of up to 500,000 revolutions per minute and higher, for which reason the tool has a unique design. It is also possible for the tool to be made small, for example with a shaft diameter of as little as 2 mm or less.
By virtue of its high speeds but relatively low torques, the tool is especially suitable for use in nanotechnology, for example for grinding, drilling, milling, engraving, etc.
The tool has a novel design, and the special features that distinguish it from the prior art in this field are set forth in the characterizing parts of the patent claims.
The invention will be described below on the basis of examples and with reference to the drawing, in which Figure 1 is a schematic view of the tool in one position, and Figure 2 is a schematic view of the tool in a position different than the first position, Figures IA and 2 A show alternative embodiments of the tool according to Figures 1 and 2, Figures IB and 2B show further variations of the tool according to Figures 1 and 2, Figure 3 shows a cross section along the line III-III in Figure 4 with pressure distribution around the radial fluid bearing, Figure 4 shows a longitudinal section through the tool according to a variant, Figure 5 is a schematic view of a cross section along the line V-V in Figure 6 with the pressure distribution around the radial fluid bearing, Figure 6 shows a longitudinal section through the tool according to the invention and Figures 7 and 8 show alternative embodiments of the invention.
In the figures, reference number 1 designates a shaft of a rotatably driven tool, whose machining tool end is designated by reference number 2. The machining tool 2 can be integrated in or releasably connected to the shaft 1. In a first embodiment according to Figures 1 and 2, the tool is mounted with its shaft in a radial fluid bearing 3 formed by an axial bore 4 in a housing 5. Adjacent to the machining end 2 of the shaft 1, the latter is provided with a rotor 6 driven by a rotating magnetic field generated by a stator 6', which rotor is received freely in the stator 6' in the housing 5, as is shown. The stator 6' can of course be arranged instead in a separate part, fastened to the housing. Adjacent to the rotor 6, an axial bearing 8 is arranged for cooperation with a bottom end surface 9 of a cavity 7 receiving the stator 6'. The axial bearing 8 is fed with the same bearing fluid as the radial bearing. Figures IB and 2B show how the tool according to the invention is also provided with an axial bearing 30, for example in the form of a ceramic ball, acting against the inner end surfaces of the shaft 1 and movable in the axial direction. Within the scope of the invention, it is of course possible to exclude the axial fluid bearing 8 and to only use the axial bearing 30 for the axial displacement of the shaft 1 and of the tool. With the tool fully inserted, the axial fluid bearing 8 can take up the axial forces and the axial bearing 30 can be unloaded.
Fluid, liquid or gas (for example water or air), for the fluid bearing of the tool shaft 1 is introduced into an inlet 11, as is indicated by an arrow 12, and distributes itself in the radial bearing 3 on the one hand towards the axial bearing 8 and on the other hand towards the inner end of the shaft located in the housing. The introduced bearing fluid is conveyed away via outlet channels 13 and 14. To secure the axial position of the tool in the housing with the axial bearing 8 cooperating with the end surface 9, or when the axle according to Fig. 2B rests against the ball 30, a counter- force acting against the axial bearing is generated by means of the bearing fluid being exposed to underpressure, i.e. forced out with underpressure via the outlet channels 13 and 14. The bearing fluid that reaches the axial bearing 8, 9 is prevented from leaking out in the turbine wheel end on account of an underpressure prevailing in the space round the axial bearing.
In order to increase the mass inertia of the tool, the rotor 6 can be dimensioned, or the material thereof chosen, such that its mass inertia increases the rotation energy and thereby increases the machining capacity of the tool.
During machining operations, the housing 5, with the tool located therein in the position shown in Figure 1, can be displaced to and away from the workpiece. However, it is also possible to only displace the tool in the axial bore 4 instead. This can be done (see Figure 1) by a liquid column 15 being formed between the end of the shaft 1 in the housing 5 and a piston 16 that is displaceable axially in the bore 4. In the fully inserted position of the tool, the liquid column which is located between the end of the shaft 1 and the piston 16, and which (when the bearing medium is a liquid) is formed by the bearing fluid flowing from the inlet 11 to the outlet 14, is at all times fully developed, this by virtue of the fact that the piston 16 in the starting position keeps the outlet line 14 open. If the tool is to be displaced axially outwards, the piston 16 is quickly forced in by the desired distance, which means that the shaft 1 and thus the tool are displaced by said distance. When the piston 16 is drawn back to the starting position, the tool naturally follows it. It must be understood that these displacements of the tool backwards and forwards in the housing 1 take place within a very short time, for which reason the liquid column is not influenced to any appreciable degree by the bearing fluid that flows towards the end of the shaft and the liquid column. When the bearing medium is instead composed of a gas (air) (see Figures IA and 2A), a liquid is delivered without any appreciable pressure via a channel 28 in order to ensure the liquid column 15. In the case (see Figures IB and 2B) where the axle 1 only rests against the axial bearing, the ball 30, which acts against the end surface of the shaft 1, the ball constitutes the only axial bearing (not shown), and the axial displacement of the tool takes place by means of the part 16', on which the ball is arranged, being displaced axially. In the case shown in Figures IB and 2B, where the axial fluid bearing 8 is combined with the axial bearing 30 (ball), the shaft 1 in the inserted end position will bear against the axial fluid bearing 8, and the bearing 30 can be relieved, which bearing has a bearing function only during outward displacement of the shaft 1 by means of the part 16'.
By designing the rotor 6 with a certain axial extent, the action of the stator 6', and thus of the rotating magnetic field, on the rotor 6 can remain essentially the same, even when the tool is displaced outwards from the housing 5.
When the tool is to be removed from the housing, for example for replacement, an overpressure is applied in the outlet channel 13 instead of an underpressure, and this overpressure directly "pushes" the tool out of the housing 5. During tool replacement, the turbine wheel is removed from the shaft and is mounted on a new shaft with a new machining tool end.
To achieve the high speeds intended for the invention and to generate a stable movement of the tool, an aim is to eliminate pressure variations in the bearings. Figures 3-6 show schematic views of a tool according to the invention, which differs from the tool described in connection with Figures 1 and 2 only in that the radial fluid bearings have been given a special design. Figure 4 thus shows two radial fluid bearings 17 and 18. In the example shown, the non-bearing outer side of each bearing is provided with three axial channels 19 (see Fig. 3) which at one end comprise a radial channel 20 in the bearing, opening into the bearing surface, and which at the other end open into a space 21 present between the two bearings. As will be appreciated, the space 21 is filled with bearing fluid, which flows on the one hand into the gap between the shaft 1 and the bearing surface and on the other hand via the channels 19 and the radial channels 20 to the bearing gap. The supply of bearing fluid also through the channels 20 means that a pressure distribution curve is formed in the bearing gap between each radial bearing 17 and 18 and the shaft 1, as shown in Figure 3. By delivering bearing fluid through the channels 20, a controlled pressure distribution (according to the arrows in Figure 3) is obtained in the bearing, which effectively prevents incorrect functioning of the bearing at high speeds.
Figure 5 shows another embodiment for solving the problems mentioned earlier. Here, the arrangement differs from Figures 3 and 4 in that the bearing surface of each bearing 17 and 18 supporting the shaft 1 has regular radial formations deviating from the purely circular shape. In the example shown in Figure 5, the bearing surface has three radially widened, axial parts 22, which means that the bearing fluid flowing between the fluid bearing and the shaft is compressed in the "narrower" areas during rotation of the shaft, for which reason a pressure curve is also obtained corresponding to the one in Figure 5. The preferred embodiment of the invention described above can be modified in accordance with what is shown in Figures 7 and 8.
Instead of operating with underpressure in the bearing fluid in order to use a force to maintain the position of the axial bearing 8; 30 with respect to the end surface 9, this force can, as shown in Figure 7, instead be generated by applying an external force component generated, for example, by an air stream 25 directed more or less axially towards the rotor 6 (see Figure 7).
Finally, Figure 8 shows the axially inwardly directed force generated by a magnet 27, attracting the rotor 6. Alternatively, this magnet 27 can be replaced by or supplemented with a magnet 27 placed at the inner end of the shaft 1 and attracting the axle 1.
The modifications described above in connection with Figures 7 and 8 thus presuppose the same tools as shown in and described with reference to Figures 1-6, except that an underpressure is not necessary in the outlet channels 13, 14, since the tool's axial movement controlled by the piston 16 and the liquid column 15 is generated in the manner described earlier.
The above-described tool according to the invention can of course be combined to form a tool with several rotating shafts provided with machining tools and operating, if necessary, at different speeds.

Claims

Patent Claims
1. Tool in the form of a rotating driven shaft (1) with a tooled (2) end and provided with at least one drive part (6, 6') for driving the tool, which shaft is mounted in a housing (5) with at least one radial fluid bearing
(3, 17, 18), characterized in that at least one drive part (6, 6') is arranged on the shaft (1) between said at least one radial fluid bearing (3, 17) and the tooled end.
2. Tool according to Claim 1, characterized in that the driven shaft is mounted with at least one axial bearing (8), the axial position of the tool in the housing (5) being determined by the axial bearing (8) and a force directed counter thereto.
3. Tool according to Claim 2, characterized in that the counter-directed force is generated by a pressure difference.
4. Tool according to Claim 2, characterized in that the counter-directed force is generated by a magnetic field.
5. Tool according to Claim 2, characterized in that the counter-directed force is generated by a mass flow oriented in the direction towards the axial fluid bearing (8).
6. Tool according to Claim 3, characterized in that the bearing fluid delivered for the fluid bearing of the shaft is conveyed away from the housing by means of underpressure generating the counter-directed force.
7. Tool according to any of the preceding claims, characterized in that the drive part is in the form of a rotor (6) driven by a rotating magnetic field (6')-
8. Tool according to any of Claims 2-7, characterized in that the axial bearing (8) is arranged such that it limits the axial movement of the tool directed into the housing (5).
9. Tool according to any of the preceding claims, characterized in that the bearing fluid is a liquid or gas (water or air).
10. Tool according to any of the preceding claims, characterized in that the radial fluid bearing is provided with subsections (22) that deviate from the cylindrical shape, such that a pressure distribution varying 360 degrees around the axle is created in the bearing gap.
11. Tool according to any of the preceding claims, characterized in that the radial fluid bearing that supports the rotatable axle is designed such that a pressure distribution varying 360 degrees around the axle is created in the bearing gap, by means of bearing fluid being delivered to the bearing surface via separate radial channels (20) formed in the bearing.
12. Tool according to any of preceding Claims 2-11, characterized in that the part of the shaft (1) located in the housing can be acted upon by a liquid column, acting in the direction opposite to the counter-force, for axial displacement of the shaft and therefore of the tool in the direction away from the axial bearing (8).
13. Tool according to Claim 12, characterized in that the liquid column acts on the end of the shaft in the housing and is formed by the bearing fluid and is in communication with a discharge channel (14) for the bearing fluid when the shaft is located in its completely inserted position in the housing, which communication is interrupted when the axial displacement of the tool takes place.
14. Tool according to any of preceding Claims 6-13, characterized in that, when the underpressure is replaced by an overpressure, the tool is forced to leave the housing.
15. Tool according to any of preceding Claims 2-14, characterized in that the axial bearing (8) is arranged in the form of a fluid bearing which is connected to the drive part (6), and whose bearing fluid consists of some of the fluid delivered to the radial bearing.
16. Tool according to any of Claims 2-14, characterized in that the axial bearing (30) is arranged to be axially displaceable, acting on the shaft's end face located in the housing.
17. Tool according to Claims 2-15, characterized in that it is provided with an axial bearing according to Claim 15 in combination with an axial bearing according to Claim 16.
PCT/SE2007/050138 2006-03-10 2007-03-09 An electric motor driven tool WO2007106028A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0600535A SE530269C2 (en) 2006-03-10 2006-03-10 Tool with a drive part arranged between a fluid bearing and the tool part
SE0600535-9 2006-03-10

Publications (1)

Publication Number Publication Date
WO2007106028A1 true WO2007106028A1 (en) 2007-09-20

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ID=38509766

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2007/050138 WO2007106028A1 (en) 2006-03-10 2007-03-09 An electric motor driven tool

Country Status (2)

Country Link
SE (1) SE530269C2 (en)
WO (1) WO2007106028A1 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU585041A1 (en) * 1976-05-03 1977-12-25 Предприятие П/Я М-5886 Tool holder
DE3819799A1 (en) * 1987-08-04 1989-02-16 Fortuna Werke Maschf Ag Machine tool
FR2688731A1 (en) * 1992-03-20 1993-09-24 Martinez Armand Rotational drive of a tool by a motor rotating at high or very high speed
DE19621773A1 (en) * 1995-05-31 1996-12-05 Ntn Toyo Bearing Co Ltd External compressed air bearing spindle
US5674032A (en) * 1995-10-12 1997-10-07 Aesop, Inc. Tooling system and method with integral hydrostatic bearings and turbine power source
DE19917693A1 (en) * 1999-04-20 2000-10-26 Benjamin Blumenschein High speed rotary drive device for tool, with tubular casing having through air channel between induction inlet and outlet opposite it

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU585041A1 (en) * 1976-05-03 1977-12-25 Предприятие П/Я М-5886 Tool holder
DE3819799A1 (en) * 1987-08-04 1989-02-16 Fortuna Werke Maschf Ag Machine tool
FR2688731A1 (en) * 1992-03-20 1993-09-24 Martinez Armand Rotational drive of a tool by a motor rotating at high or very high speed
DE19621773A1 (en) * 1995-05-31 1996-12-05 Ntn Toyo Bearing Co Ltd External compressed air bearing spindle
US5674032A (en) * 1995-10-12 1997-10-07 Aesop, Inc. Tooling system and method with integral hydrostatic bearings and turbine power source
DE19917693A1 (en) * 1999-04-20 2000-10-26 Benjamin Blumenschein High speed rotary drive device for tool, with tubular casing having through air channel between induction inlet and outlet opposite it

Also Published As

Publication number Publication date
SE0600535L (en) 2007-09-11
SE530269C2 (en) 2008-04-15

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