WO1998046896A1 - Hydraulic clamp bushing having reduced sleeve thickness - Google Patents

Hydraulic clamp bushing having reduced sleeve thickness Download PDF

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Publication number
WO1998046896A1
WO1998046896A1 PCT/SE1998/000677 SE9800677W WO9846896A1 WO 1998046896 A1 WO1998046896 A1 WO 1998046896A1 SE 9800677 W SE9800677 W SE 9800677W WO 9846896 A1 WO9846896 A1 WO 9846896A1
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WO
WIPO (PCT)
Prior art keywords
sleeves
bushing
clamp bushing
pressure medium
value
Prior art date
Application number
PCT/SE1998/000677
Other languages
French (fr)
Inventor
Niclas Rosberg
Sven Lemon
Original Assignee
Etp Transmission 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 Etp Transmission Ab filed Critical Etp Transmission Ab
Publication of WO1998046896A1 publication Critical patent/WO1998046896A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
    • B23B31/30—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck
    • B23B31/305—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck the gripping means is a deformable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0805—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to deformation of a resilient body or a body of fluid

Definitions

  • the present invention relates to a hydraulic clamp bushing of the type comprising two expandable sleeves which are joined at one end or at both ends thereof, and which between the sleeves is formed with an all around extending chamber which is filled with a hydraulic pressure medium, and in which clamp bushing the sleeves, adjacent one end thereof are formed with means for internal or external pressurization of the pressure medium in the chamber between the two expandable sleeves.
  • Clamp bushings of the said type are arranged for forming a releasable joint between a shaft and a hub, for instance between a rotatable shaft and a rotatable tool having a hub part.
  • the clamp bushings also can be used for axially movable, reciprocatabie shafts and corresponding tools or any similar object formed with a hub.
  • the clamp bushings are formed for being slided onto the shaft with the inner sleeve thereof, and the hub is formed for being slided onto the outer sleeve of the clamp bushing.
  • Clamp bushings of the said type are known for instance from US patents US 3,861 ,815 (LANDAEUS) and US 4,093,052 (FALK).
  • the expandable sleeves have generally been formed with a relatively large width of material for the intended purpose of withstanding the high pressures which appear when the hydraulic pressure medium is pressurized, which pressure can be 1.000 bar or more, and also for having the sleeves regain their original shape when the pressure of the pressure medium is released.
  • the ⁇ -value generally has been between 1.12 and 1.15. Further, the ⁇ -values generally have been different for the inner sleeve and the outer sleeve of one and the same clamp bushing.
  • Such relatively high ⁇ -values may lead to the effect that the inner and outer sleeves become rather stiff, and that there is a need for a certain initial force for bringing said sleeves into contact with the shaft and the hub, respectively, which force is taken from the pressure of the pressure medium between the sleeves, and that the remaining part of the pressure of the pressure medium is used for clamp connecting the clamp bushing sleeves to the shaft and the hub. It has shown that as much as 50% of the pressure of the pressure medium, depending on the dimensions and the tolerances of the bushing, is needed for bringing the bushing sleeves into contact with the shaft and the hub, respectively, and that consequently only down to 50% of the pressure is available for creating the torque or moment transfer joint between shaft - clamp bushing - hub.
  • the inner sleeve and the outer sleeve are formed with the same nominal width, and this means that the ⁇ -value is different for the inner sleeve and the outer sleeve, respectively, and that there is a need for different amount of pressure of the hydraulic pressure medium for the inner sleeve and the outer sleeve, respectively, in order to provide a contact between the sleeves and the shaft and the hub, respectively.
  • the basis of the invention has been the idea of making it possible to reduce the width of the sleeves, especially so that the ⁇ -value will be between 1.08 and 1.12. This is quite sufficient for giving the bushing the desired strength.
  • Such a reduction of the ⁇ -value meaning reduced width of the inner and outer sleeves of the bushing as compared with what has been the case in priorly known techniques, presents several advantages: a) a reduced amount of the pressure of the pressure medium is consumed for over bridging the always existing play between shaft-bushing-hub, and this makes the bushing capable of providing an increased torque or moment transfer; b) there appear less bending stresses at the ends of the sleeves, that is at the weld joints between the inner and outer sleeves, when the sleeves bend outwards during the expansion thereof, and this leads to a reduced decorative of material fatigue and thereby to an increased working life of the bushing: c) the sleeves get a longer line of contact against the shaft and the hub, respectively, since the bending outwards at the ends of the sleeves follow along a reduced length of bending out
  • the ⁇ -value for the sleeves of a clamp bushing of the above mentioned type ought to be between 1.08 and 1.12, or more preferably between 1.09 and 1.11.
  • a ⁇ -value which is higher than 1.12 gives the bushing certain disadvantages of the type mentioned above in connection to the description of priorly known clamp bushings of the said type, in which the ⁇ -value generally is between 1.12 and 1.15.
  • the indicated ⁇ -values, and also the indicated tolerances relate both to the type of clamp bushing which is open at one end and which, at said one end is formed with a pressure piston for axial pressurization of the pressure medium between the sleeves and for the type of clamp bushing which is closed at both ends and which, at one end, is formed with a collar having means, like a pressurization screw, for pressurizing the pressure medium between the sleeves.
  • figure 1 shows a partially cut open clamp bushing of the type which is open at one end and which is arranged for being pressurized by means of an axially movable pressure piston.
  • Figure 2 correspondingly shows a clamp bushing which is closed at both ends and in which the pressurization of the pressure medium is made by means of a pressurization screw in a collar of the clamp bushing.
  • Figure 3 illustrates the method of manufacturing of a clamp bushing according to figure 2.
  • Figure 4 illustrates how the calculation is made of the ⁇ -values for the inner and outer sleeves in a clamp bushing of the type shown in figure 1
  • figure 5 correspondingly shows how the calculation is made of the ⁇ -value for a clamp bushing according to figure 2.
  • Figure 6 shows, in the right part thereof, a cross sectional through a clamp bushing of a priorly known type, as seen along line VII-VII of figure 3, and in the left part thereof the dimensions of the outer and inner sleeves.
  • Figure 7 correspondingly shows, in the right hand part thereof, a cross section through a clamp bushing according to the invention, and in the left part of the figure the dimensions of the outer and inner sleeves having the above described ⁇ -values.
  • the clamp bushing shown in figure 1 comprises, as known per se, an outer sleeve 1 and an inner sleeve 2, which are joined, for instance by welding, at one end 3, and the opposite end of which is open for pressurization of a pressure medium 4 which is enclosed in a pressure medium recess provided between the sleeves 1 and 2.
  • the pressurization is made by means of a pressure ring 5 acted on by several all around the sleeves distributed screws 6 which are threaded into a collar 7 which is integral with the outer sleeve 1.
  • the pressure ring acts on a piston 8 which, in turn, acts on a sealing 9 which is in direct contact with the pressure medium in the pressure medium recess.
  • the clamp bushing of figure 2 mainly differs from the bushing of figure 1 in that the outer and inner sleeves 1 and 2 are welded together at both ends 3a, 3b, and in that the pressure medium of the pressure medium recess is pressurized by means of a pressurization screw 10 which is threaded into a pressurization chamber 11 in the collar 7, which chamber over a passageway 12 (see figures 6 and 7) is connected to the pressure medium recess between the sleeves.
  • the manufacture of the clamp bushing as shown in figure 2 is normally made as indicated in figure 3 in that there are made, separately from each other, a outer sleeve 1 having a collar and an inner sleeve 2, both sleeves having a coring- out 13 adapted to form the pressure medium recess in the final clamp bushing; the inner sleeve 2 is pressed into the outer sleeve 1 , and the two sleeves are welded together at the two ends 3a and 3b thereof, for instance by electronic beam welding or laser welding; the pressure medium recess is filled with a hydraulic pressure medium, at the same time as the pressure medium slot is drained from air; and finally the pressurization screw 10 is mounted in the pressurization chamber 11 (see figures 6 and 7) of the collar 7.
  • both the outer sleeve and the inner sleeve have a width defined by the relationship between the outer diameter and the inner diameter of the sleeve, so that the quotient between the outer diameter and the inner diameter of the respective sleeve has a highest value of 1.12.
  • Said value is named the ⁇ -value and is, for the outer sleeve, the quotient between 0Y : 01, see designations in figure 4 and 5, and, for the inner sleeve the quotient between 0y : 0i.
  • the ⁇ -value is the same or nearly the same for the outer sleeve and the inner sleeve. Slight variations, however, may be allowed.
  • a too high ⁇ -value gives a stiff clamp bushing which is subjected to high bending stresses at the ends thereof upon pressurization. Also a relatively high portion of the pressure in the pressure medium is consumed for over bridging the play between the bushing and the shaft and hub, respectively. Further the bushing gets an outer diameter which is relatively large as compared with what has now been shown to be possible.
  • a too low ⁇ -value leads to a weak clamp bushing, in which there may appear a torsional rotation between the shaft and the hub upon application of a high torque or moment.
  • a torsional rotation between the shaft and the hub exceeding 0.4°-0.6° can not be recommended, and preferably a torsional rotation should not be allowed to exceed 0.3°.
  • the ⁇ -value should preferably be between 1.08 and 1.12, and most preferably between 1.09 and 1.11.
  • the ⁇ -value can be allowed to be slightly less than 1.08, but it should not be allowed to be lower than 1.05 for sleeves made of steel.
  • Figure 6 shows a clamp bushing of priorly known type, to the right in a cross section view through the collar, following VII-VII of figure 3, and to the left a cross section through the clamp bushing sleeves, and figure 7 correspondingly shows a clamp bushing according to the present invention. It is evident that it has been possible to reduce the outer diameter 0Y of the outer sleeve of the invention (figure 7) as compared with that of the priorly known clamp bushing (figure 6), in spite that it has been possible to maintain the inner diameter 0i of the inner sleeve unchanged. It has consequently been possible to reduce the dimensions and the overall diameter of the clamp bushing of the invention, at the same time as several other advantages have been obtained.
  • the preferred ⁇ -value for a clamp bushing of the described type is to some degree related to the tolerances between the shaft and the inner sleeve, and between the outer sleeve and the hub, respectively. At very narrow tolerances the ⁇ -value is of less importance, but for technical, practical and economical reasons the tolerances preferably should be of the 6th to the 8th degree according to adopted designation.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Gripping On Spindles (AREA)
  • Clamps And Clips (AREA)

Abstract

A hydraulic clamp bushing formed for interconnecting a shaft and an object having a hub and being of the type comprising two expandable sleeves (1, 2) which are joined at least at one end thereof (3a, 3b) and which, in between said sleeves, define an all around extending recess forming a pressure medium recess which is filled with a hydraulic pressure medium (4), and which clamp bushing is formed with means (10) for internal or external pressurization of the pressure medium (4) in the pressure medium recess between said two expandable sleeves (1, 2), and in which the sleeves (1, 2) have a material width which, determined by the quotient between the outer diameter and the inner diameter of the respective sleeve, named λ-value (kappa value), does not exceed 1.12 or is preferably between 1.09 and 1.11. The clamp bushing is made of such material that the bushing is not allowed to be subjected to a torque rotation of more thant 0.4°-0.6° at maximum torque transmission. The tolerance between the shaft and the inner sleeve (2), and also between the outer sleeve (1) and the hub, should be of the 6th to the 8th degree.

Description

HYDRAULIC CLAMP BUSHING HAVING REDUCED SLEEVE THICKNESS
The present invention relates to a hydraulic clamp bushing of the type comprising two expandable sleeves which are joined at one end or at both ends thereof, and which between the sleeves is formed with an all around extending chamber which is filled with a hydraulic pressure medium, and in which clamp bushing the sleeves, adjacent one end thereof are formed with means for internal or external pressurization of the pressure medium in the chamber between the two expandable sleeves.
Clamp bushings of the said type are arranged for forming a releasable joint between a shaft and a hub, for instance between a rotatable shaft and a rotatable tool having a hub part. The clamp bushings also can be used for axially movable, reciprocatabie shafts and corresponding tools or any similar object formed with a hub. The clamp bushings are formed for being slided onto the shaft with the inner sleeve thereof, and the hub is formed for being slided onto the outer sleeve of the clamp bushing. When the hydraulic pressure medium in the clamp bushing is pressurized the inner sleeve expands radially inwards and the outer sleeve expands radially outwards, whereby the clamp bushing centers and interconnects the shaft and the tool having the hub. When the pressure of the pressure medium is released the expandable sleeves regain their original shape, whereby the shaft and the tool are released from the clamp bushing, so that the joint becomes completely released.
Clamp bushings of the said type are known for instance from US patents US 3,861 ,815 (LANDAEUS) and US 4,093,052 (FALK).
In said priorly known clamp bushings the expandable sleeves have generally been formed with a relatively large width of material for the intended purpose of withstanding the high pressures which appear when the hydraulic pressure medium is pressurized, which pressure can be 1.000 bar or more, and also for having the sleeves regain their original shape when the pressure of the pressure medium is released. The material width can be expressed as the quotient between the outer and the inner diameter of the respective sleeve, which value can be defined by the Greece letter "kappa", that is 0Y : 01 = K. In clamp bushings of the above mentioned type, known so far, the κ-value generally has been between 1.12 and 1.15. Further, the κ-values generally have been different for the inner sleeve and the outer sleeve of one and the same clamp bushing.
Such relatively high κ-values may lead to the effect that the inner and outer sleeves become rather stiff, and that there is a need for a certain initial force for bringing said sleeves into contact with the shaft and the hub, respectively, which force is taken from the pressure of the pressure medium between the sleeves, and that the remaining part of the pressure of the pressure medium is used for clamp connecting the clamp bushing sleeves to the shaft and the hub. It has shown that as much as 50% of the pressure of the pressure medium, depending on the dimensions and the tolerances of the bushing, is needed for bringing the bushing sleeves into contact with the shaft and the hub, respectively, and that consequently only down to 50% of the pressure is available for creating the torque or moment transfer joint between shaft - clamp bushing - hub.
For a good function of a clamp bushing also the tolerances between the shaft and the inner sleeve of the bushing and between the hub and the outer sleeve of the bushing, respectively, are of importance in combination with the above mentioned κ-value for the inner and outer sleeves of the bushing. Optimum tolerances ought to be of the 6th to the 8th tolerance degree, according to adopted designation.
Depending on the stiffness of the sleeves there may appear great bending stresses at the ends of the sleeves, at which ends the bending outwards starts in connection to the radial expansion of the sleeves, and at which ends the sleeves are joined, generally by weld joints, whereby the sleeves, in particular at said ends, are subjected to high stresses. This may lead to fatigue of the material at and adjacent the ends of the sleeves after frequent and alternating external loads or internal loads, like in connection to frequent pressurizations and pressure releasings of the pressure medium in the pressure medium chamber. In many cases the inner sleeve and the outer sleeve are formed with the same nominal width, and this means that the κ-value is different for the inner sleeve and the outer sleeve, respectively, and that there is a need for different amount of pressure of the hydraulic pressure medium for the inner sleeve and the outer sleeve, respectively, in order to provide a contact between the sleeves and the shaft and the hub, respectively.
The basis of the invention has been the idea of making it possible to reduce the width of the sleeves, especially so that the κ-value will be between 1.08 and 1.12. This is quite sufficient for giving the bushing the desired strength. Such a reduction of the κ-value, meaning reduced width of the inner and outer sleeves of the bushing as compared with what has been the case in priorly known techniques, presents several advantages: a) a reduced amount of the pressure of the pressure medium is consumed for over bridging the always existing play between shaft-bushing-hub, and this makes the bushing capable of providing an increased torque or moment transfer; b) there appear less bending stresses at the ends of the sleeves, that is at the weld joints between the inner and outer sleeves, when the sleeves bend outwards during the expansion thereof, and this leads to a reduced risque of material fatigue and thereby to an increased working life of the bushing: c) the sleeves get a longer line of contact against the shaft and the hub, respectively, since the bending outwards at the ends of the sleeves follow along a reduced length of bending out; d) since the sleeve width is reduced both as concerns the inner sleeve and the outer sleeve the bushing, as a whole, will get a reduced outer diameter, and thereby a reduced overall radial dimension; e) by forming the inner sleeve and the outer sleeve with the same κ-value there is obtained a symmetric function of both sleeves and a more uniform centering and interconnection of shaft-bushing-hub.
Calculations and tests have proved that the κ-value for the sleeves of a clamp bushing of the above mentioned type ought to be between 1.08 and 1.12, or more preferably between 1.09 and 1.11. A κ-value which is higher than 1.12 gives the bushing certain disadvantages of the type mentioned above in connection to the description of priorly known clamp bushings of the said type, in which the κ-value generally is between 1.12 and 1.15.
There is also a lower limit for the optimum κ-value. A too low κ-value makes the bushing become a reduced torsion stiffness, and this means that the hub will be rotated in relation to the shaft when loaded. A bushing rotation of more than 0.3° can not be accepted considering the required accuracy of positioning.
The pressure P for different κ-values can be calculated by means of a formula which has been found empirically when the invention was made: P = E[(κ2 - 1)] : 2000 - D expressed in bar/μm in which formula E is the modulus of elasticity for the material of the bushing sleeves and D is the outer diameter of the respective sleeve.
The indicated κ-values, and also the indicated tolerances relate both to the type of clamp bushing which is open at one end and which, at said one end is formed with a pressure piston for axial pressurization of the pressure medium between the sleeves and for the type of clamp bushing which is closed at both ends and which, at one end, is formed with a collar having means, like a pressurization screw, for pressurizing the pressure medium between the sleeves.
Now the invention is to be described more in detail with reference to the accompanying drawings, in which figure 1 shows a partially cut open clamp bushing of the type which is open at one end and which is arranged for being pressurized by means of an axially movable pressure piston. Figure 2 correspondingly shows a clamp bushing which is closed at both ends and in which the pressurization of the pressure medium is made by means of a pressurization screw in a collar of the clamp bushing. Figure 3 illustrates the method of manufacturing of a clamp bushing according to figure 2. Figure 4 illustrates how the calculation is made of the κ-values for the inner and outer sleeves in a clamp bushing of the type shown in figure 1 , and figure 5 correspondingly shows how the calculation is made of the κ-value for a clamp bushing according to figure 2. Figure 6 shows, in the right part thereof, a cross sectional through a clamp bushing of a priorly known type, as seen along line VII-VII of figure 3, and in the left part thereof the dimensions of the outer and inner sleeves. Figure 7 correspondingly shows, in the right hand part thereof, a cross section through a clamp bushing according to the invention, and in the left part of the figure the dimensions of the outer and inner sleeves having the above described κ-values.
The clamp bushing shown in figure 1 comprises, as known per se, an outer sleeve 1 and an inner sleeve 2, which are joined, for instance by welding, at one end 3, and the opposite end of which is open for pressurization of a pressure medium 4 which is enclosed in a pressure medium recess provided between the sleeves 1 and 2. In this case the pressurization is made by means of a pressure ring 5 acted on by several all around the sleeves distributed screws 6 which are threaded into a collar 7 which is integral with the outer sleeve 1. The pressure ring acts on a piston 8 which, in turn, acts on a sealing 9 which is in direct contact with the pressure medium in the pressure medium recess.
The clamp bushing of figure 2 mainly differs from the bushing of figure 1 in that the outer and inner sleeves 1 and 2 are welded together at both ends 3a, 3b, and in that the pressure medium of the pressure medium recess is pressurized by means of a pressurization screw 10 which is threaded into a pressurization chamber 11 in the collar 7, which chamber over a passageway 12 (see figures 6 and 7) is connected to the pressure medium recess between the sleeves.
The manufacture of the clamp bushing as shown in figure 2 is normally made as indicated in figure 3 in that there are made, separately from each other, a outer sleeve 1 having a collar and an inner sleeve 2, both sleeves having a coring- out 13 adapted to form the pressure medium recess in the final clamp bushing; the inner sleeve 2 is pressed into the outer sleeve 1 , and the two sleeves are welded together at the two ends 3a and 3b thereof, for instance by electronic beam welding or laser welding; the pressure medium recess is filled with a hydraulic pressure medium, at the same time as the pressure medium slot is drained from air; and finally the pressurization screw 10 is mounted in the pressurization chamber 11 (see figures 6 and 7) of the collar 7.
For obtaining the advantages a) - e) mentioned above it is important to the invention that both the outer sleeve and the inner sleeve have a width defined by the relationship between the outer diameter and the inner diameter of the sleeve, so that the quotient between the outer diameter and the inner diameter of the respective sleeve has a highest value of 1.12. Said value is named the κ-value and is, for the outer sleeve, the quotient between 0Y : 01, see designations in figure 4 and 5, and, for the inner sleeve the quotient between 0y : 0i. For most applications it is preferred that the κ-value is the same or nearly the same for the outer sleeve and the inner sleeve. Slight variations, however, may be allowed. A too high κ-value gives a stiff clamp bushing which is subjected to high bending stresses at the ends thereof upon pressurization. Also a relatively high portion of the pressure in the pressure medium is consumed for over bridging the play between the bushing and the shaft and hub, respectively. Further the bushing gets an outer diameter which is relatively large as compared with what has now been shown to be possible.
A too low κ-value, in turn, leads to a weak clamp bushing, in which there may appear a torsional rotation between the shaft and the hub upon application of a high torque or moment. A torsional rotation between the shaft and the hub exceeding 0.4°-0.6° can not be recommended, and preferably a torsional rotation should not be allowed to exceed 0.3°.
Extensive tests have shown that the κ-value should preferably be between 1.08 and 1.12, and most preferably between 1.09 and 1.11. For certain applications the κ-value can be allowed to be slightly less than 1.08, but it should not be allowed to be lower than 1.05 for sleeves made of steel.
Figure 6 shows a clamp bushing of priorly known type, to the right in a cross section view through the collar, following VII-VII of figure 3, and to the left a cross section through the clamp bushing sleeves, and figure 7 correspondingly shows a clamp bushing according to the present invention. It is evident that it has been possible to reduce the outer diameter 0Y of the outer sleeve of the invention (figure 7) as compared with that of the priorly known clamp bushing (figure 6), in spite that it has been possible to maintain the inner diameter 0i of the inner sleeve unchanged. It has consequently been possible to reduce the dimensions and the overall diameter of the clamp bushing of the invention, at the same time as several other advantages have been obtained.
The preferred κ-value for a clamp bushing of the described type is to some degree related to the tolerances between the shaft and the inner sleeve, and between the outer sleeve and the hub, respectively. At very narrow tolerances the κ-value is of less importance, but for technical, practical and economical reasons the tolerances preferably should be of the 6th to the 8th degree according to adopted designation.
REFERENCE NUMERALS
1 outer sleeve
2 inner sleeve
3 end (3a, 3b)
4 pressure medium
5 pressure ring
6 screw
7 collar
8 piston
9 sealing
10 pressurization screw
11 pressurization chamber
12 passageway
13 coring out

Claims

C L A I M S
1. A hydraulic clamp bushing formed for interconnecting a shaft and an object having a hub and being of the type comprising two expandable sleeves (1 , 2) which are joined at least at one end thereof (3; 3a, 3b) and which in between said sleeves (1 , 2) define an all around extending recess forming a closed pressure medium recess which is filled with a hydraulic pressure medium (4), and which clamp bushing, at one end thereof, is formed with means (5; 10) for internal or external pressurization of the pressure medium (4) in the pressure medium recess between said two expandable sleeves (1 , 2) characterized in that the sleeves (1 , 2) have a material width which, determined by the quotient between the outer diameter and the inner diameter of the respective sleeve, named ╬║-value (kappa value), does not exceed 1.12.
2. A hydraulic clamp bushing according to claim 1 , characterized in that the κ-value for each of the sleeves (1 , 2) is of such magnitude that the torsional rotation of the clamp bushing, at maximum transferred torque, does not exceed between 0.4° and 0.6°, or preferably does not exceed 0.3ς.
3. A hydraulic clamp bushing according to claim 1 or 2, characterized in that the ╬║-value for sleeves made of steel is higher than 1.05.
4. A hydraulic clamp bushing according to claim 1 , 2 or 3, characterized in that the ╬║-value preferably is between 1.08 and 1.12, more preferably between 1.09 and 1.11.
5. A hydraulic clamp bushing according to any of the preceding claims, characterized in that the ╬║-value is the same or nearly the same for each of the sleeves of the clamp bushing.
6. A hydraulic clamp bushing according to any of the preceding claims, characterized in that the tolerance between a shaft and the inner sleeve (2), and also between the object having the hub and the outer sleeve (1), for a bushing having the said ╬║-value is of the 6th to the 8th degree according to adopted designation.
PCT/SE1998/000677 1997-04-11 1998-04-14 Hydraulic clamp bushing having reduced sleeve thickness WO1998046896A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9701354A SE512052C2 (en) 1997-04-11 1997-04-11 Hydraulic clamp bushing
SE9701354-4 1997-04-11

Publications (1)

Publication Number Publication Date
WO1998046896A1 true WO1998046896A1 (en) 1998-10-22

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WO2005097383A1 (en) * 2004-04-03 2005-10-20 Kennametal Inc. Hydraulic expanding chuck
DE102005058156B3 (en) * 2005-12-05 2007-02-01 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Hydraulic clamping device for tools in machine tool has clamping screw with central threaded through boring into which pre-setting screw is screwed
US7467566B2 (en) 2003-11-25 2008-12-23 Bobst S.A. Anti-backlash device in a gear
EP2093169A1 (en) 2008-02-23 2009-08-26 Krones AG Star wheel transporter
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ITUB20154811A1 (en) * 2015-10-16 2017-04-16 Danieli Off Mecc LAMINATION CAGE FOR METAL PRODUCTS
CN106872170A (en) * 2017-03-27 2017-06-20 江西洪都航空工业集团有限责任公司 Fixture is simulated for the magnitude of interference that bearing is installed
CN112122638A (en) * 2019-06-25 2020-12-25 肯纳金属公司 Sealing piston for a hydraulic expansion clamping device and expansion clamping device
EP3827917A1 (en) * 2019-11-28 2021-06-02 Schunk GmbH & Co. KG Spann- und Greiftechnik Expansion clamping device and method for the production thereof
CN113790218A (en) * 2021-09-28 2021-12-14 李宏亮 Hydraulic adjustable expansion connecting sleeve and assembling method

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WO2002070177A2 (en) * 2001-02-14 2002-09-12 Command Tooling Systems, Llc Hydraulically actuated holder
WO2002070177A3 (en) * 2001-02-14 2007-11-15 Command Tooling Systems Llc Hydraulically actuated holder
EP1340930A1 (en) 2002-02-28 2003-09-03 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Transmission shift control with hydraulic wedging bodies
WO2004038246A2 (en) 2002-10-22 2004-05-06 Sequa Can Machinery, Inc. Plate cylinder locking mechanism
US7467566B2 (en) 2003-11-25 2008-12-23 Bobst S.A. Anti-backlash device in a gear
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US7914010B2 (en) 2004-04-03 2011-03-29 Kennametal Inc. Hydraulic expansion chuck for chucking a tool, such as a boring tool, milling cutter, or other cutting tool
DE102005058156B3 (en) * 2005-12-05 2007-02-01 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Hydraulic clamping device for tools in machine tool has clamping screw with central threaded through boring into which pre-setting screw is screwed
EP1792679A2 (en) * 2005-12-05 2007-06-06 Schunk GmbH & Co. KG Spann- und Greiftechnik Hydraulic clamping device
EP1792679A3 (en) * 2005-12-05 2007-12-26 Schunk GmbH & Co. KG Spann- und Greiftechnik Hydraulic clamping device
EP2093169A1 (en) 2008-02-23 2009-08-26 Krones AG Star wheel transporter
DE102008010894A1 (en) 2008-02-23 2009-08-27 Krones Ag star wheel
CN102905793A (en) * 2010-03-31 2013-01-30 阿尔法拉瓦尔股份有限公司 Centrifugal separator and rotor
EP2552592A4 (en) * 2010-03-31 2017-08-23 Alfa Laval Corporate AB Centrifugal separator and rotor
ITUB20154811A1 (en) * 2015-10-16 2017-04-16 Danieli Off Mecc LAMINATION CAGE FOR METAL PRODUCTS
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CN106393652A (en) * 2016-11-28 2017-02-15 江苏新美星液体包装工程技术研究中心有限公司 Mounting structure of swing arm and swing shaft of rotary bottle blowing machine
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CN106872170B (en) * 2017-03-27 2019-07-09 江西洪都航空工业集团有限责任公司 Magnitude of interference for bearing installation simulates fixture
CN112122638A (en) * 2019-06-25 2020-12-25 肯纳金属公司 Sealing piston for a hydraulic expansion clamping device and expansion clamping device
US11577326B2 (en) * 2019-06-25 2023-02-14 Kennametal Inc. Sealing piston for a hydraulic expansion chucking device and expansion chucking device
CN112122638B (en) * 2019-06-25 2024-04-23 肯纳金属公司 Sealing piston for a hydraulic expansion clamping device and expansion clamping device
EP3827917A1 (en) * 2019-11-28 2021-06-02 Schunk GmbH & Co. KG Spann- und Greiftechnik Expansion clamping device and method for the production thereof
WO2021105436A1 (en) * 2019-11-28 2021-06-03 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Expansion chucking device and method for production thereof
CN113790218A (en) * 2021-09-28 2021-12-14 李宏亮 Hydraulic adjustable expansion connecting sleeve and assembling method

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SE9701354D0 (en) 1997-04-11
SE9701354L (en) 1998-10-12

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