CA1049278A - Coupling assembly with narrow fluid slots - Google Patents
Coupling assembly with narrow fluid slotsInfo
- Publication number
- CA1049278A CA1049278A CA272,001A CA272001A CA1049278A CA 1049278 A CA1049278 A CA 1049278A CA 272001 A CA272001 A CA 272001A CA 1049278 A CA1049278 A CA 1049278A
- Authority
- CA
- Canada
- Prior art keywords
- recess
- pressure fluid
- pressure
- outer sleeve
- assembly according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- 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
- F16D25/00—Fluid-actuated clutches
- F16D25/04—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube
- F16D25/042—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch
- F16D25/046—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch and causing purely radial movement
-
- 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
Abstract
ABSTRACT OF THE DISCLOSURE
The present invention provides a fluid actuated coupling assembly for releasably coupling at least two elements together, comprising an outer sleeve, an inner sleeve concentric-ally mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the two sleeves which is closed at least at said one end of the sleeves, means for intro-ducing a pressure fluid in said recess and means for preventing exhaust of such pressure fluid, the radial dimension of the sleeve being variable by changing the pressure on the pressure fluid in the said recess, the volume of the recess in the non-pressurized state not exceeding a volume corresponding to a relationship between the width of the recess and the average diameter of the recess being 2 x 10-2.
The present invention provides a fluid actuated coupling assembly for releasably coupling at least two elements together, comprising an outer sleeve, an inner sleeve concentric-ally mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the two sleeves which is closed at least at said one end of the sleeves, means for intro-ducing a pressure fluid in said recess and means for preventing exhaust of such pressure fluid, the radial dimension of the sleeve being variable by changing the pressure on the pressure fluid in the said recess, the volume of the recess in the non-pressurized state not exceeding a volume corresponding to a relationship between the width of the recess and the average diameter of the recess being 2 x 10-2.
Description
The present invention relates to a fluid act~ated coupling assembly for releasably coupling at least two elements, preferably for transmitting of torque therebetween and comprising an outer sleeve, an inner sleeve concentrically mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the outer sleeve and the inner sleeve, and means for introducing a pressure fluid in said recess, the radial dimension of the sleeve walls being variable by changing the pressure on the pressure fluid in the said recess.
Fluid actuated coupling assemblies of the above kind are known in which the recess containing the pressure fluid is of relatively large volume. Such coupling assemblies are often used for releasably mounting of a wheel or the like on a shaft and for general purposes the priorly known coupling assemblies give a good result. These coupling assemblies are however disadvantage- ¦
ous in several respects when used in an environment which is subjected to large temperature changes. The pressure fluid which is generally an oil or fat product generally has a coefficient of expansion which is much higher than the coefficient of expansion for the inner sleeve and the outer sleeve which are normally made of steel. Generally the coefficient of expansion for the pressure fluid is a tenth power higher than that of steel.
When subjecting a coupling assembly of the above kind to high temperatures the pressure fluid expands much more than the steel sleeves and in case of large temperature differences this may cause a deformation of the coupling and it may even make the coupling burst. It is further difficult to obtain a good sealing at the very high pressures which result when raising the temperature to a high level. Further, when lowering the temper-ature the pressure fluid contracts much more than the steelsleeves and the torque transmitting ability is reduced accordingly, and it may even happen that one or both of the elements are ... .. _ i disconnected from the coupling assembly at extreme low tem~eratures. High temperatures are in this connection temper- ¦
atures of up to 100-125C of the pressure medium and with low temperatures, temperatures of -30C or lower.
Attempts have been made to overcome the above dis-advantages by using for the pressure fluid some pressure medium which has a lower coefficient of expansion that the above men-tioned liquid or fat, but no coupling known assemblies have eliminated or substantially reduced the said disadvantages so that the coupling can be used subiected to large temperature differences.
The present invention provides a fluid actuated cou~ling assembly for releasably coupling at least two elements together which can be used even subjected large temperature differences without being deformed due to extreme expansions or contractions of the pressure fluid, which does not loosen in case of lowering the temperature and in which there are no serious sealing problems depending on large pressure rise when subjecting the coupling to large temperature increases.
According to the present invention therefore there is ~;
provided a 1uid actuated coupling assembly for releasably coupling at least two elements together, comprising an outer sleeve, an inner sleeve concentrically mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the two sleeves which is closed at least at said one end of the sleeves, means for introducing a pressure fluid in said recess and means for preventing exhaust of such pressure fluid, the radial dimension of the sleeve being variable by changing the pressure on the pressure fluid in the said recess, _ 30 the volume of the recess in the non-pressurized state not exceeding _ a volume corresponding to a relationship between the width of the recess and the average diameter of the recess being 2 x lO
~ temperature rise ~ T causes a pressure ri~e ~ P
within the recess of the coupling due to the fact that the Z
coefficient of expansion of the liquid y is higher than thàt of the inner sleeve and the outer sleeve. Mathematically the pressure rise may be expressed as follows:
Y ~ T
p =
~ . d2 L (1) B +
E (l-c2) . V
in which ~ P is the pressure change, a T is the temperature change, B is a constant of compressibility for the pressure fluid, d is the average diameter of the recess of the coupling, L is the length of said recess, E is the module of elasticity for the steel of the shaft and the hub to be connected by the coupling, c is the relation between the inner and the outer diameter of the hub to be connected and V is the pressure fluid F
volume in the recess of the coupling.
The present invention will be described with reference to the accompanying drawings, in which: ~
Fig. 1 is a graph of the pressure rise at two different p temperatures against the width of the recess between the inner ~i sleeve and the outer sleeve;
Fig. 2 is a corresponding graph of torque ratio at the point of slip between a hub and shaft connected by the coupling assembly at different widths of the recess and different original t pressures;
Fig. 3 is a cross section through a coupling assembly according to one embodiment of the invention; and Fig. 4 is a partial cross section through a further embodiment of the coupling of the present inventionO
It is evident from the above formula that a temperature rise causes a pressure rise and that a volume change may reduce 1~49Z78 the effect of such temperature rises. In order to inv~estigate the effect of different volume of the coupling recess at temper-ature rises tests have been made the results of which are illust-rated in Figures 1 and 2. In Figure 1 is shown a graph in which the pressure rise ~ P (horizontal shaft) at two different temper-ature rises of 50C and 100C respectively are plotted against a vertical axis showing the width t of the recess between the inner sleeve and the outer sleeve. The pressure rise A P is expressed in bar (1 bar = 0.1 MPa) and the width t of the recess in milli-meter. All tests were made with a coupling having an averagediameter d at the recess of 30 millimeters, the coefficient of expansion for the pressure fluid, which in this case was a fat product, was 7 x 10 4, the constant of compressibility B for the pressure fluid was 8 x 10 5 l/bar, the module of elasticity for the steel of the shaft and the hub to be connected was 21 x 1~5 kg/cm and the relation between the inner and the outer diameter of the hub to be connected was 0.5. ~, It is evident from the graph that there are relatively small changes of ~ P for increasing recesses from t = 0.5 to a . larger recess width whereas there are relatively large differences for decreasing recesses from t = 0.5 to a width of less than 0.5 mm. It is therefore evident, that if the volume of the pressure fluid in the recess of the coupling is reduced to a value corres-ponding to less than t = O.S mm for the coupling illustrated in Figure 1 it is possible to substantially reduce the pressure rise at temperature rises. To define the volume, the width t of the recess should be calculated considering the average.diameter d of the recess, and considering the said relationship it might be t stated, that the value of t:d should be less than about 2 x 10 2 It has been noted during the tests that the value of t:d does not give identical results for different sizes of the coupling, and it has been noted that the value is slightly decreasing for -- 4 -- ..
~049Z78 increasing diameters, depending on the fact that the tolerance of larqe diameter couplings may be made relatively smaller than of small size couplings, but generally the following relationship should be fulfilled in order to reduce the pressure rise at rising temperatures:
t = 2 10-2 (2) d In the ideal case the relationship t:d should be 0, but for well known reasons this is not possible, and considering the particular characteristics it has been found suitable to define the said relationship to be the same as or less than 2 x 10 2.
In Figure 2 is illustrated a corresponding graph showing r the torque ratio Ml/Mo at the point of slip between a hub and a shaft connected by the coupling assembly of the invention at different widths t of the coupling recess and at different orig-inal pressures. In the diagram M relates to torque at slip generally Mo is such torque in the original state and Ml is the torque at increased temperature. In all tests the temperature increase ~ T was +100C and there are plotted three different values corresponding to an original pressure of 900 bar, 600 bar and 300 bar respectively. The remaining values are the same as explained in connection to Figure 1.
The tests illustrated in Flgure 2 confirm the result found in connection with the tests illustrated in Figure 1, and it may be noted, that there are relatively small changes of the torque relation Ml/Mo for a width t of the recess larger than about 0.5 mm whereas there are large differences of Ml/rlo for widths t of the recess less than about 0.5 mm. The tests con- ~
sequently confirms that the relationship t/d should be less than F
3~ about 2 x 10 in order to substantially reduce the effects of the temperature rises and differences of Ml/Mo due to such temperature changes.
....
5 _ , .
For certain applications it is very essential to form the coupling as temperature independent as possible, and as mentioned above this can be made by making the recess for the pressure fluid very thin so as to maintain the width of the recess below the above stated value. At the same time the temperature dependency of the coupling can be further reduced by mixing the pressure medium with particles of a material having a thermal coefficient of expansion which is less than that of the pressure fluid or substantially the same as that of the outer sleeve and the inner sleeve of the coupling.
Referring now to Figure 3 there is shown a fluid actuated coupling assembly 10 which may be used e.g. for interconnecting a hub 25 and a shaft 26. The coupling assembly comprises an outer sleeve 11 and an inner sleeve 12 mounted concentrically within the outer sleeve 11 and secured thereto by means of annular welds 13 and 14 respectively. Alternatively to welding the concentrical sleeves 11 and 12 may be connected by other means such as soldering, ~
fusion, glueing, screwing or rivetting. Both sleeves 11 and 12 ,_ are radially resilient, i.e. inter alia , have relatively thin walls and are made of a material which is sufficiently resilient ~;
to permit the sleeves to be bowed in opposing radial directions under the pressure actions of a pneumatic or preferably hydraulic ~' pressure medium introduced to a zone or a gap 15 defined between the two sleeves 11 and 12. As will be evident from the Figure bowing of respective sleeves will cause the outer sleeve ll to be brought into frictional engagement with the hub or wheel 25 and F
the inner sleeve 12 to be brought into frictional engagement with the shaft 26 so that the two elements are coupled together by the coupling assembly.
For the sake of clearness the gap 15 between the inner sleeve and the outer sleeve is illustrated relatively wide, but in order to be able to reduce the effect of the pressure change in .. . ..
.
the pressure medium depending on temperature changes the width t of the recess for the gap 15 as considered in relation to the average diameter d should fulfillthe above relationship:
t~d = 2 x 10 2.
As will be seen from Figure 3 one end of the outer sleeve 11 is formed with a flange-like collar 16 in which there is a bore 18 which communicates with the gap 15. In the bore there is a sealed piston 27 which can be forced radially inwards by means of a screw 30. In order to eliminate the risk of splitt-ing the outer sleeve 11 and the inner sleeve 12 apart the ends ofthe gap lSa and 15b are formed as flutes, and in the said flutes 15a and 15b there are mounted angular filling elements 15c, 15d so as to reduce the volume of the gap 15. The filler elements 15c and 15d may be of any suitable material preferably having the same coefficient of expansion as the sleeves 11 and 12.
In Figure 4 there is shown a modified embodiment of the coupling assembly according to Figure 3 likewise comprising an outer sleeve 11 and an inner sleeve 12 provided concentrically within the outer sleeve 11 and defining between the two sleeves a recess or gap 15. At one end the two sleeves are connected to each other by means of a weld 14, and at the opposite end the gap 15 opens in an axial angular recess 18' which is sealed by a sealing piston 27'. A collar like pressure ring 27" is provided axially outside the piston ring 27 , and the said collar pressure ring 27" may be forced against the piston ring 27' and inside the recess 18' by means of several screws 30' provided round the coupling assembly and co-operating with the collar 16 of the outer sleeve 11.
. The means for providing a pressurization of the pressure fluid in the gap 15 may be of any suitable kind and it may by a separate external means for introducing pressurized fluid in the gap, and in such an embodiment of the invention the sealing piston . .
27 or 27 is exchanged for a one-way valve permitting introduction of pressurized fluid but preventing exhaust of such pressure fluid.
In order to further reduce the amount of pressure fluid in the gap 15 the said pressure fluid may contain small particles of a material having a coefficient of expansion which is the same Or nearly the same as that of the inner sleeve and the outer sleeve. By mixing the pressure fluid with such particles the E
amount of pressure fluid is correspondingly reduced.
The gap 15 defined between the sleeves 11 and 12 may have any suitable form, e.g. as illustràted in Figure 4, in which the reduced sections, e.g. the sections 11' of the outer sleeve 11 and 12 of the inner sleeve 12 give a slightly larger bowing than the wider parts 11", 12".
In order to reduce the amount of pressure fluid in the gap 15 the outer sleeve or the inner sleeve may be formed with radial extensions normally engaging the inner sleeve or outer sleeve respectively but which, when introducing pressure fluid in the gap thereby slightly moving the sleeves 11 and 12 apart, provide a passageway for the pressure fluid. Alternatively there may be provided~separate rings or similar elements in the gap which reduce the necessary amount of pressure fluid.
Normally the coupling is made with such thin recess that the outer sleeve and the inner sleeve at ambient temperature and before pressure is applied in the recess engage each other, and the diameter of the pressure medium bore 18, 18' and the stroke of the piston 27, 27' are formed with such dimensions that as far as possible almost all pressure medium at ready connection of the coupling is forced out of the pressure medium bore 18, 18 and into the recess 15. Further the diameter and the stroke of the pressure piston 27, 27', respectively should be adapted so that it it possible to quickly provide the intended connection force using relatively moderate force when drawing the screw or the screws 30.
8 - ~t 1049;~78 A friction coupling assembly of the ty~e illustrated in the drawings has been tested in hot rolling mills for mounting of roll sleeves on roll shafts in which the coupling was subjected to very high temperatures, and in which the pressure fluid, in spite of cooling of the mill rolls, had a temperature of Up to 150C. No change Of thC relationship Ml/~o was discovered between the roll shaft and the roll sleeve, and no deformation was discovered of the coupling. Thus the coupling according to the invention is useful in many applications where previously known couplings Of the kind in question are disadvantageous due to the high volume of presSure medium in the gap or recess. The invention may be used both in appliCations where the coupling is subjected to very high temperature and where the coupling iS sub-jected to very low temperature, and jUSt by adapting the pressure of the pressure flUid to the circumstances the coupling may be pr~par d for the different purposes. F
r ~ ,
Fluid actuated coupling assemblies of the above kind are known in which the recess containing the pressure fluid is of relatively large volume. Such coupling assemblies are often used for releasably mounting of a wheel or the like on a shaft and for general purposes the priorly known coupling assemblies give a good result. These coupling assemblies are however disadvantage- ¦
ous in several respects when used in an environment which is subjected to large temperature changes. The pressure fluid which is generally an oil or fat product generally has a coefficient of expansion which is much higher than the coefficient of expansion for the inner sleeve and the outer sleeve which are normally made of steel. Generally the coefficient of expansion for the pressure fluid is a tenth power higher than that of steel.
When subjecting a coupling assembly of the above kind to high temperatures the pressure fluid expands much more than the steel sleeves and in case of large temperature differences this may cause a deformation of the coupling and it may even make the coupling burst. It is further difficult to obtain a good sealing at the very high pressures which result when raising the temperature to a high level. Further, when lowering the temper-ature the pressure fluid contracts much more than the steelsleeves and the torque transmitting ability is reduced accordingly, and it may even happen that one or both of the elements are ... .. _ i disconnected from the coupling assembly at extreme low tem~eratures. High temperatures are in this connection temper- ¦
atures of up to 100-125C of the pressure medium and with low temperatures, temperatures of -30C or lower.
Attempts have been made to overcome the above dis-advantages by using for the pressure fluid some pressure medium which has a lower coefficient of expansion that the above men-tioned liquid or fat, but no coupling known assemblies have eliminated or substantially reduced the said disadvantages so that the coupling can be used subiected to large temperature differences.
The present invention provides a fluid actuated cou~ling assembly for releasably coupling at least two elements together which can be used even subjected large temperature differences without being deformed due to extreme expansions or contractions of the pressure fluid, which does not loosen in case of lowering the temperature and in which there are no serious sealing problems depending on large pressure rise when subjecting the coupling to large temperature increases.
According to the present invention therefore there is ~;
provided a 1uid actuated coupling assembly for releasably coupling at least two elements together, comprising an outer sleeve, an inner sleeve concentrically mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the two sleeves which is closed at least at said one end of the sleeves, means for introducing a pressure fluid in said recess and means for preventing exhaust of such pressure fluid, the radial dimension of the sleeve being variable by changing the pressure on the pressure fluid in the said recess, _ 30 the volume of the recess in the non-pressurized state not exceeding _ a volume corresponding to a relationship between the width of the recess and the average diameter of the recess being 2 x lO
~ temperature rise ~ T causes a pressure ri~e ~ P
within the recess of the coupling due to the fact that the Z
coefficient of expansion of the liquid y is higher than thàt of the inner sleeve and the outer sleeve. Mathematically the pressure rise may be expressed as follows:
Y ~ T
p =
~ . d2 L (1) B +
E (l-c2) . V
in which ~ P is the pressure change, a T is the temperature change, B is a constant of compressibility for the pressure fluid, d is the average diameter of the recess of the coupling, L is the length of said recess, E is the module of elasticity for the steel of the shaft and the hub to be connected by the coupling, c is the relation between the inner and the outer diameter of the hub to be connected and V is the pressure fluid F
volume in the recess of the coupling.
The present invention will be described with reference to the accompanying drawings, in which: ~
Fig. 1 is a graph of the pressure rise at two different p temperatures against the width of the recess between the inner ~i sleeve and the outer sleeve;
Fig. 2 is a corresponding graph of torque ratio at the point of slip between a hub and shaft connected by the coupling assembly at different widths of the recess and different original t pressures;
Fig. 3 is a cross section through a coupling assembly according to one embodiment of the invention; and Fig. 4 is a partial cross section through a further embodiment of the coupling of the present inventionO
It is evident from the above formula that a temperature rise causes a pressure rise and that a volume change may reduce 1~49Z78 the effect of such temperature rises. In order to inv~estigate the effect of different volume of the coupling recess at temper-ature rises tests have been made the results of which are illust-rated in Figures 1 and 2. In Figure 1 is shown a graph in which the pressure rise ~ P (horizontal shaft) at two different temper-ature rises of 50C and 100C respectively are plotted against a vertical axis showing the width t of the recess between the inner sleeve and the outer sleeve. The pressure rise A P is expressed in bar (1 bar = 0.1 MPa) and the width t of the recess in milli-meter. All tests were made with a coupling having an averagediameter d at the recess of 30 millimeters, the coefficient of expansion for the pressure fluid, which in this case was a fat product, was 7 x 10 4, the constant of compressibility B for the pressure fluid was 8 x 10 5 l/bar, the module of elasticity for the steel of the shaft and the hub to be connected was 21 x 1~5 kg/cm and the relation between the inner and the outer diameter of the hub to be connected was 0.5. ~, It is evident from the graph that there are relatively small changes of ~ P for increasing recesses from t = 0.5 to a . larger recess width whereas there are relatively large differences for decreasing recesses from t = 0.5 to a width of less than 0.5 mm. It is therefore evident, that if the volume of the pressure fluid in the recess of the coupling is reduced to a value corres-ponding to less than t = O.S mm for the coupling illustrated in Figure 1 it is possible to substantially reduce the pressure rise at temperature rises. To define the volume, the width t of the recess should be calculated considering the average.diameter d of the recess, and considering the said relationship it might be t stated, that the value of t:d should be less than about 2 x 10 2 It has been noted during the tests that the value of t:d does not give identical results for different sizes of the coupling, and it has been noted that the value is slightly decreasing for -- 4 -- ..
~049Z78 increasing diameters, depending on the fact that the tolerance of larqe diameter couplings may be made relatively smaller than of small size couplings, but generally the following relationship should be fulfilled in order to reduce the pressure rise at rising temperatures:
t = 2 10-2 (2) d In the ideal case the relationship t:d should be 0, but for well known reasons this is not possible, and considering the particular characteristics it has been found suitable to define the said relationship to be the same as or less than 2 x 10 2.
In Figure 2 is illustrated a corresponding graph showing r the torque ratio Ml/Mo at the point of slip between a hub and a shaft connected by the coupling assembly of the invention at different widths t of the coupling recess and at different orig-inal pressures. In the diagram M relates to torque at slip generally Mo is such torque in the original state and Ml is the torque at increased temperature. In all tests the temperature increase ~ T was +100C and there are plotted three different values corresponding to an original pressure of 900 bar, 600 bar and 300 bar respectively. The remaining values are the same as explained in connection to Figure 1.
The tests illustrated in Flgure 2 confirm the result found in connection with the tests illustrated in Figure 1, and it may be noted, that there are relatively small changes of the torque relation Ml/Mo for a width t of the recess larger than about 0.5 mm whereas there are large differences of Ml/rlo for widths t of the recess less than about 0.5 mm. The tests con- ~
sequently confirms that the relationship t/d should be less than F
3~ about 2 x 10 in order to substantially reduce the effects of the temperature rises and differences of Ml/Mo due to such temperature changes.
....
5 _ , .
For certain applications it is very essential to form the coupling as temperature independent as possible, and as mentioned above this can be made by making the recess for the pressure fluid very thin so as to maintain the width of the recess below the above stated value. At the same time the temperature dependency of the coupling can be further reduced by mixing the pressure medium with particles of a material having a thermal coefficient of expansion which is less than that of the pressure fluid or substantially the same as that of the outer sleeve and the inner sleeve of the coupling.
Referring now to Figure 3 there is shown a fluid actuated coupling assembly 10 which may be used e.g. for interconnecting a hub 25 and a shaft 26. The coupling assembly comprises an outer sleeve 11 and an inner sleeve 12 mounted concentrically within the outer sleeve 11 and secured thereto by means of annular welds 13 and 14 respectively. Alternatively to welding the concentrical sleeves 11 and 12 may be connected by other means such as soldering, ~
fusion, glueing, screwing or rivetting. Both sleeves 11 and 12 ,_ are radially resilient, i.e. inter alia , have relatively thin walls and are made of a material which is sufficiently resilient ~;
to permit the sleeves to be bowed in opposing radial directions under the pressure actions of a pneumatic or preferably hydraulic ~' pressure medium introduced to a zone or a gap 15 defined between the two sleeves 11 and 12. As will be evident from the Figure bowing of respective sleeves will cause the outer sleeve ll to be brought into frictional engagement with the hub or wheel 25 and F
the inner sleeve 12 to be brought into frictional engagement with the shaft 26 so that the two elements are coupled together by the coupling assembly.
For the sake of clearness the gap 15 between the inner sleeve and the outer sleeve is illustrated relatively wide, but in order to be able to reduce the effect of the pressure change in .. . ..
.
the pressure medium depending on temperature changes the width t of the recess for the gap 15 as considered in relation to the average diameter d should fulfillthe above relationship:
t~d = 2 x 10 2.
As will be seen from Figure 3 one end of the outer sleeve 11 is formed with a flange-like collar 16 in which there is a bore 18 which communicates with the gap 15. In the bore there is a sealed piston 27 which can be forced radially inwards by means of a screw 30. In order to eliminate the risk of splitt-ing the outer sleeve 11 and the inner sleeve 12 apart the ends ofthe gap lSa and 15b are formed as flutes, and in the said flutes 15a and 15b there are mounted angular filling elements 15c, 15d so as to reduce the volume of the gap 15. The filler elements 15c and 15d may be of any suitable material preferably having the same coefficient of expansion as the sleeves 11 and 12.
In Figure 4 there is shown a modified embodiment of the coupling assembly according to Figure 3 likewise comprising an outer sleeve 11 and an inner sleeve 12 provided concentrically within the outer sleeve 11 and defining between the two sleeves a recess or gap 15. At one end the two sleeves are connected to each other by means of a weld 14, and at the opposite end the gap 15 opens in an axial angular recess 18' which is sealed by a sealing piston 27'. A collar like pressure ring 27" is provided axially outside the piston ring 27 , and the said collar pressure ring 27" may be forced against the piston ring 27' and inside the recess 18' by means of several screws 30' provided round the coupling assembly and co-operating with the collar 16 of the outer sleeve 11.
. The means for providing a pressurization of the pressure fluid in the gap 15 may be of any suitable kind and it may by a separate external means for introducing pressurized fluid in the gap, and in such an embodiment of the invention the sealing piston . .
27 or 27 is exchanged for a one-way valve permitting introduction of pressurized fluid but preventing exhaust of such pressure fluid.
In order to further reduce the amount of pressure fluid in the gap 15 the said pressure fluid may contain small particles of a material having a coefficient of expansion which is the same Or nearly the same as that of the inner sleeve and the outer sleeve. By mixing the pressure fluid with such particles the E
amount of pressure fluid is correspondingly reduced.
The gap 15 defined between the sleeves 11 and 12 may have any suitable form, e.g. as illustràted in Figure 4, in which the reduced sections, e.g. the sections 11' of the outer sleeve 11 and 12 of the inner sleeve 12 give a slightly larger bowing than the wider parts 11", 12".
In order to reduce the amount of pressure fluid in the gap 15 the outer sleeve or the inner sleeve may be formed with radial extensions normally engaging the inner sleeve or outer sleeve respectively but which, when introducing pressure fluid in the gap thereby slightly moving the sleeves 11 and 12 apart, provide a passageway for the pressure fluid. Alternatively there may be provided~separate rings or similar elements in the gap which reduce the necessary amount of pressure fluid.
Normally the coupling is made with such thin recess that the outer sleeve and the inner sleeve at ambient temperature and before pressure is applied in the recess engage each other, and the diameter of the pressure medium bore 18, 18' and the stroke of the piston 27, 27' are formed with such dimensions that as far as possible almost all pressure medium at ready connection of the coupling is forced out of the pressure medium bore 18, 18 and into the recess 15. Further the diameter and the stroke of the pressure piston 27, 27', respectively should be adapted so that it it possible to quickly provide the intended connection force using relatively moderate force when drawing the screw or the screws 30.
8 - ~t 1049;~78 A friction coupling assembly of the ty~e illustrated in the drawings has been tested in hot rolling mills for mounting of roll sleeves on roll shafts in which the coupling was subjected to very high temperatures, and in which the pressure fluid, in spite of cooling of the mill rolls, had a temperature of Up to 150C. No change Of thC relationship Ml/~o was discovered between the roll shaft and the roll sleeve, and no deformation was discovered of the coupling. Thus the coupling according to the invention is useful in many applications where previously known couplings Of the kind in question are disadvantageous due to the high volume of presSure medium in the gap or recess. The invention may be used both in appliCations where the coupling is subjected to very high temperature and where the coupling iS sub-jected to very low temperature, and jUSt by adapting the pressure of the pressure flUid to the circumstances the coupling may be pr~par d for the different purposes. F
r ~ ,
Claims (10)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A fluid actuated coupling assembly for releasably coupling at least two elements together, comprising an outer sleeve, an inner sleeve concentrically mounted within the outer sleeve and secured thereto at least at one end and defining a recess between the two sleeves which is closed at least at said one end of the sleeves, means for introducing a pressure fluid in said recess and means for preventing exhaust of such pressure fluid, the radial dimension of the sleeve being variable by chang-ing the pressure on the pressure fluid in the said recess, the volume of the recess in the non-pressurized state not exceeding a volume corresponding to a relationship between the width of the recess and the average diameter of the recess being 2 x 10-2.
2. An assembly according to claim 1, in which each end of the recess is flute-formed to avoid splitting apart of the outer sleeve and the inner sleeve.
3. An assembly according to claim 2, in which each of the recess flutes is partly filled with an element or substantially the same coefficient of expansion as the inner sleeve and the outer sleeve.
4. An assembly according to claim 2, in which the recess flutes are partly filled up with a separate element re-ducing the size thereof to a size corresponding to the width of the recess at the maximum.
5. An assembly according to claim 1, in which the means for introducing pressure fluid into the recess comprises a bore communicating the recess with the exterior, a sealing piston being provided in said bore and a screw means for forcing the sealing piston into the bore.
6. An assembly according to claim 1, in which the means for introducing pressure fluid into the recess comprises an axial groove, a sealing ring piston provided in said groove and a collar pressure ring engaging the ring piston and forcing same into the groove by means of screw means connecting the collar pressure ring with the outer sleeve.
7. An assembly according to claim 1, in which the means for introducing pressurized fluid into the recess comprises an external pressure supply, a one way valve communicating the recess with the pressure fluid supply thereby permitting the introduction of pressure fluid in the recess and preventing exhaust of pressure fluid therefrom.
8. An assembly according to claim 1, in which the pressure fluid is mixed up with particles having a coefficient of expansion which is less than that of the pressure fluid.
9. An assembly as claimed in claim 8, in which the particles have a coefficient of expansion which is the same as that of the outer sleeve and the inner sleeve.
10. An assembly according to claim 1, in which at least one of the outer sleeve and the inner sleeve are formed with radial extensions reducing the required amount of pressure fluid in the recess.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/660,682 US4093052A (en) | 1974-01-23 | 1976-02-23 | Fluid actuated coupling assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1049278A true CA1049278A (en) | 1979-02-27 |
Family
ID=24650539
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA272,001A Expired CA1049278A (en) | 1976-02-23 | 1977-02-17 | Coupling assembly with narrow fluid slots |
Country Status (14)
| Country | Link |
|---|---|
| JP (1) | JPS52102956A (en) |
| AT (1) | ATA110777A (en) |
| BR (1) | BR7700996A (en) |
| CA (1) | CA1049278A (en) |
| CH (1) | CH606853A5 (en) |
| DE (2) | DE2707530A1 (en) |
| ES (1) | ES456151A1 (en) |
| FI (1) | FI64984C (en) |
| FR (1) | FR2341778A1 (en) |
| GB (1) | GB1546699A (en) |
| IT (1) | IT1064344B (en) |
| NL (1) | NL7701906A (en) |
| NO (1) | NO141381C (en) |
| SE (1) | SE422232B (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4188142A (en) * | 1977-11-09 | 1980-02-12 | Olsson Hans O | Lockable swivel coupling |
| SE422426B (en) * | 1978-02-24 | 1982-03-08 | Foerenade Fabriksverken | METHOD AND APPARATUS FOR MOUNTING TOOLS, WORK PIECES AND LIKE A ROTATING SPINDLE |
| SE425515B (en) * | 1978-06-15 | 1982-10-04 | Metalform Safeset Ab | PRESSURE-POWERED COUPLING |
| SE7812703L (en) * | 1978-12-11 | 1980-06-12 | Hans Otto Olsson | DEVICE FOR HYDRAULIC CLUTCHES |
| EP0129633A1 (en) * | 1983-06-27 | 1985-01-02 | Centro-Morgardshammar Ab | A mounting for a roll unit, particularly in a wire rod mill |
| DE3543672A1 (en) * | 1985-12-11 | 1987-06-19 | Voith Gmbh J M | CLUTCH BETWEEN A SHAFT AND A HUB |
| JPH01299465A (en) * | 1988-05-27 | 1989-12-04 | Nippon Denso Co Ltd | Vehicle speedometer that is also used as accelerometer |
| JPH0419424A (en) * | 1990-05-14 | 1992-01-23 | Japan Steel Works Ltd:The | Friction type clamp device |
| JPH04348805A (en) * | 1990-12-06 | 1992-12-03 | Mitsubishi Materials Corp | Rotary machining tool |
| DE4326150C2 (en) * | 1993-08-04 | 1998-12-17 | Voith Gmbh J M | Device for the axial fixing of components |
| SE505609C2 (en) * | 1995-12-04 | 1997-09-22 | Voith Safeset Ab | COUPLING |
| DE29711184U1 (en) * | 1997-06-26 | 1997-08-21 | Leitz Geb Gmbh & Co | Hydro clamping element |
| JP6070175B2 (en) | 2012-12-27 | 2017-02-01 | トヨタ自動車株式会社 | Transmission test apparatus and transmission test method |
| US10619657B2 (en) * | 2015-04-04 | 2020-04-14 | Esm Energie-Und Schwingungstechnik Mitsch Gmbh | Reversible connecting of machine components |
| EP3208478B1 (en) * | 2016-02-18 | 2021-01-20 | Voith Patent GmbH | Method and system for digital optimization of torque limiters and connection couplings |
| DE102019106503A1 (en) * | 2019-03-14 | 2020-09-17 | Voith Patent Gmbh | Safety coupling with pressure regulation |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE356105B (en) * | 1971-12-14 | 1973-05-14 | K Landaeus | |
| SE423566B (en) * | 1973-01-25 | 1982-05-10 | Foerenade Fabriksverken | PRESSURE SUPPORT SUPPORT FRICTION FOR CONNECTING ATMINSTONE TWO DETAILS PREFERRED FOR Torque Transfer |
-
1976
- 1976-11-19 IT IT7629575A patent/IT1064344B/en active
- 1976-12-16 GB GB52621/76A patent/GB1546699A/en not_active Expired
-
1977
- 1977-01-28 SE SE7700924A patent/SE422232B/en not_active IP Right Cessation
- 1977-01-31 FI FI770328A patent/FI64984C/en not_active IP Right Cessation
- 1977-02-17 BR BR7700996A patent/BR7700996A/en unknown
- 1977-02-17 CA CA272,001A patent/CA1049278A/en not_active Expired
- 1977-02-18 AT AT0110777A patent/ATA110777A/en not_active IP Right Cessation
- 1977-02-21 JP JP1722677A patent/JPS52102956A/en active Granted
- 1977-02-21 NO NO770565A patent/NO141381C/en unknown
- 1977-02-22 FR FR7705090A patent/FR2341778A1/en active Granted
- 1977-02-22 ES ES456151A patent/ES456151A1/en not_active Expired
- 1977-02-22 NL NL7701906A patent/NL7701906A/en not_active Application Discontinuation
- 1977-02-22 DE DE19772707530 patent/DE2707530A1/en active Pending
- 1977-02-22 DE DE19777705310U patent/DE7705310U1/en not_active Expired
- 1977-02-23 CH CH222577A patent/CH606853A5/xx not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| NO141381C (en) | 1980-02-27 |
| FR2341778A1 (en) | 1977-09-16 |
| ES456151A1 (en) | 1978-01-16 |
| IT1064344B (en) | 1985-02-18 |
| BR7700996A (en) | 1977-12-06 |
| ATA110777A (en) | 1982-05-15 |
| GB1546699A (en) | 1979-05-31 |
| DE7705310U1 (en) | 1979-06-07 |
| SE422232B (en) | 1982-02-22 |
| CH606853A5 (en) | 1978-11-15 |
| FR2341778B1 (en) | 1983-11-10 |
| JPS52102956A (en) | 1977-08-29 |
| FI770328A (en) | 1977-08-24 |
| NO141381B (en) | 1979-11-19 |
| FI64984C (en) | 1984-02-10 |
| JPS6240567B2 (en) | 1987-08-28 |
| DE2707530A1 (en) | 1977-08-25 |
| NO770565L (en) | 1977-08-24 |
| SE7700924L (en) | 1977-08-24 |
| NL7701906A (en) | 1977-08-25 |
| FI64984B (en) | 1983-10-31 |
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