EP2483541A1 - A supercharger with two intermeshing rotors and disc clutch - Google Patents
A supercharger with two intermeshing rotors and disc clutchInfo
- Publication number
- EP2483541A1 EP2483541A1 EP10820908A EP10820908A EP2483541A1 EP 2483541 A1 EP2483541 A1 EP 2483541A1 EP 10820908 A EP10820908 A EP 10820908A EP 10820908 A EP10820908 A EP 10820908A EP 2483541 A1 EP2483541 A1 EP 2483541A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stop
- pressing body
- stop ring
- disc clutch
- supercharger
- 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.)
- Withdrawn
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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- 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
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
-
- 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
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
-
- 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
- F16D25/12—Details not specific to one of the before-mentioned types
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/12—Drives characterised by use of couplings or clutches therein
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Definitions
- the present invention relates to a supercharger that has two intermeshing rotors and is provided with a disc clutch, which disc clutch comprises
- SE 51 1 761 a supercharger of the above-mentioned kind is previously known.
- the supercharger is engaged by the disc clutch when there is a need to supply air at positive pressure to the internal combustion engine, e.g., upon acceleration.
- the delay comprises, among other things, the time it takes for the piston that manoeuvres the disc clutch to move from the initial position until the clutches are fully meshed into each other.
- the move should bridge, on one hand, the distance that corresponds to the movement until the pressing body that presses the clutches, and that is a consequence of necessary manufacturing tolerances, against each other reaches the clutch pack, and on the other hand the distance that is required to press together the clutches into complete meshing with each other.
- the driving and driven clutches In a non-actuated state, the driving and driven clutches must of course have a certain clearance in relation to each other. It is important to reduce the time for the mentioned delay as much as possible.
- a disc clutch is furthermore previously known, in which there is a device to limit the movement of the clutch plate in the deactuation direction with the purpose of limiting the stroke length and thereby the engaging time.
- the device comprises spring-loaded balls that co-operate with cam surfaces. It is therefore complicated in its design and thereby costly to manufacture.
- a device of this type is susceptible to operational disturbances.
- the known disc clutch is not intended for engagement of a supercharger and is thereby not adapted to the special conditions in the manoeuvring of such a one.
- the need of a quick engagement is particularly accentuated. It is important that the supercharger as promptly as possible responds on initiation of its engagement, e.g., upon overtaking, when a supercharger in a car is concerned.
- the object of the present invention is to reduce the engaging time for a
- the object set forth is attained by the fact that a supercharger of the kind mentioned by way of introduction has the special features that the disc clutch comprises a stop device for the limitation of the axial movement of the pressing body in the deactuation direction, which stop device comprises impact means and stop means, one of the impact means and the stop means being connected with the driven clutch holder and the other one of the impact means and the stop means being connected with the pressing body, the connection of the impact means being axially fixing and the connection of the stop means being provided by a friction joint.
- the stop device limits the axial movement of the pressing body, an optimized axial positioning of the impact means and the stop means can be accomplished so that the axial movement is limited to what is required to bridge the clearance of the clutches.
- the part of the stroke length that is required to bridge the requisite manufacturing tolerances is thus eliminated. Furthermore, the clearance of the clutches can be kept at a minimum. Since there are several, usually about fifteen, co-operating components, tolerance elimination and clearance reduction lead to considerable shortening of the stroke length upon engagement. Thanks to the fact that the connection of the stop means is provided by a friction joint, it is easy to axially adjust the positioning of the stop means to a situation corresponding to said optimal positioning. Thereby, the distance that the pressing body needs to be displaced before it begins to press together the clutches is eliminated. Accordingly, the stroke length of the pressing body corresponds only to the clearance of the clutches. The stroke length of the manoeuvring means becomes limited to a corresponding degree. The engaging time can thereby be reduced from approx. 0,5 s down to 0,2 s, i.e., about half the value.
- the advantages of the invention primarily are interesting to use by reducing the engaging time, these advantages may alternatively be utilized by accepting a maintained engaging time but instead use a manoeuvring device that is dimensionally reduced.
- a manoeuvring device that is dimensionally reduced.
- the stop means comprises at least one stop ring.
- the ring is coaxial with the principal axis of the disc clutch.
- the impact means is suitably ring-shaped and preferably coaxial.
- the stop ring may alternatively be laterally displaced in parallel to the principal axis of the disc clutch, wherein it may be suitable to have a plurality of stop rings, preferably arranged on a circular line that is concentric with the principal axis of the disc clutch.
- the friction joint of each stop ring is formed between a radial outside or inside of the stop ring and a radial inside or outside, respectively, of the one of the driven clutch holder and the pressing body with which the stop ring is connected.
- the stop ring is provided with means for the provision of differently strong frictional force in different axial directions, where the force that keeps the stop ring from being displaced in the motion direction of the pressing body upon actuation is smaller than the frictional force that keeps the stop ring from being displaced in the opposite direction.
- the stop ring can easily be adjusted to an optimal axial situation by the fact that there is very little resistance to being displaced in the pressing direction so that the stop ring limits the displacement of the pressing body during the deactuation movement to what corresponds to only the clearance of the clutches.
- the greater frictional force in the opposite direction entails that stop action is guaranteed when the impact ring impacts on the stop ring in the deactuation movement.
- each stop ring that constitutes one part of the friction joint is asymmetrical for the provision of said differently great frictional force.
- each stop ring that constitutes one part of the friction joint is provided with obliquely directed projections, which are inclined in the motion direction of the pressing body upon deactuation.
- the inclined projections function as a kind of barbs that are pressed inward against the material of the driven clutch holder or the pressing body, thereby creating a strong frictional force that counteracts movement in the deactuation direction. In the other direction, the projections will be able to draggingly slide with ensuing low frictional force, which allows the positioning thereof.
- the alternative wherein the projections are directed outward toward the pressing body is particularly advantageous, since the pressing body can be made from aluminium, which gives good gripping conditions.
- the friction joint is a compression joint having a pressing force that is greater than the maximum axial force of the spring means.
- the stop ring can thereby be formed as a plain ring that is fixedly shrunk to the one of the driven clutch holder and the pressing body with which it is connected. While the stop ring in the embodiments mentioned right above had different resistance to movement in different axial directions, here the frictional force counteracting movement is instead the same in both directions.
- the manoeuvring means comprises a hydraulic piston.
- the supercharger comprises a screw compressor.
- the invention is per se applicable to other kinds of supercharger types in the form of, e.g., a Roots blower, but is particularly suited to be applied to a screw compressor, thereby utilizing the general advantages that such a one entails.
- the invention also concerns a disc clutch of a corresponding design as the disc clutch included in the invented supercharger, particularly according to anyone of the preferred embodiments of the same.
- the invented disc clutch and the preferred embodiments of the same have advantages of the corresponding kind as the invented supercharger and which have been accounted for above.
- Fig. 1 is a perspective view of a supercharger of the type the invention relates to.
- Fig. 2 is an axial section through the disc clutch of the supercharger in Fig. 1 in the disengaged position.
- Fig. 3 is a detailed enlargement in Fig. 2
- Fig. 4 is an axial section corresponding to the one in Fig. 2 in the engaged
- Fig. 5 is a partial enlargement in Fig. 4.
- Fig. 6 is an end view of a part of a detail of the disc clutch in Figs. 2-5.
- Fig. 7 is a side view of the detail in Fig. 6.
- Figs. 8 and 9 are axial sections corresponding to the ones in Fig. 3 and Fig. 4, respectively, illustrating alternative embodiment examples.
- Figs. 10 and 11 are axial sections corresponding to the ones in Figs. 3 and 4, respectively, illustrating an additional embodiment example.
- Figs. 12 and 13 are an end view and a side view, respectively, of a detail of the disc clutch in Figs. 10-11.
- Figs. 14 and 15 are axial sections corresponding to the ones in Figs. 3 and 4, respectively, illustrating an additional embodiment example.
- the supercharger illustrated in a perspective view in Fig. 1 comprises a screw compressor arranged in a compressor housing 1 and a disc clutch provided with driving connection 6 and arranged in a clutch housing 2, which housings are joined to each other.
- the screw compressor has two screw rotors 4, 5 engaging into each other, one of which being a male rotor, the other one a female rotor.
- An inlet (not shown) is arranged in the other end of the rotors for the intake of the air.
- the invention is also applicable to similar rotors, e.g., of the Roots type.
- the supercharger does not work.
- the disc clutch is actuated to drive the supercharger.
- the disc clutch shown in more detail in Figs. 2 and 3 has a driving part and a driven part.
- the driving part comprises a driving shaft 7 that, via driving connection 6 (see Fig. 1 ), is connected with an input drive shaft.
- driving clutch holder 8 By a driving clutch holder 8, the driving shaft 7 is spline-connected with the driving clutches 9.
- the driven part comprises a driven hub 10 that, by a driven clutch holder, is spline- connected with the driven clutches 12.
- the driven hub 10 is drivingly connected with a driven shaft that consists of one of the screw rotors, suitably the female rotor.
- connection of the driven hub 10 with rotor shaft is omitted in the figure, but may be of conventional kind.
- the disc clutch is deactuated, i.e., no driving power is transferred from the driving clutches 9 to the driven clutches 12 and the supercharger is thus not active.
- a hydraulic piston 13 having a sealed space 14 for the supply of hydraulic medium.
- a pressing body 15 is journalled via a ball bearing 16.
- a spring 17 is arranged between the pressing body 15 and the driven clutch holder 11 and provides a distancing action between these.
- the special with the present invention is a stop device that limits the movement of the pressing body upon deactuation, i.e., disengagement of the disc clutch.
- the stop device consists of an impact ring 18 and a stop ring 19.
- the impact ring 18 is fixed in a groove 20 on the inside of an axially projecting flange 21 of the pressing body 15.
- the stop ring 19 is attached on the outside of the driven clutch holder 11. The function of the stop device is most clearly seen in Figs. 3 and 5.
- the distance between the impact ring 18 and the stop ring 19 in the engaged state (Figs. 4 and 5) is adjusted so that it corresponds to the distance required to bridge the clearance of the clutch pack.
- the adjustment of the distance is provided by adjustment of the axial position of the stop ring 19 on the driven clutch holder 11.
- the stop ring is 19 designed so that its connection with the driven clutch holder 11 allows axial displacement in one direction but not in the other one. This is provided by the fact that the stop ring 19, as is seen in Figs. 6 and 7, has a number of inwardly directed projections 22, which are directed obliquely inward.
- the stop ring is 19 applied to the driven clutch holder 11 with the oblique direction to the left as seen from the outside and in.
- the oblique direction entails that the inner edge of the respective projection 22 in a barb-like way is pressed against the outside of the clutch holder 11 , which results in great resistance to leftward movement of the stop ring.
- the resistance to movement is considerably lower since the projections 22 then can slide against the outside of the clutch holder 11.
- the outside of the stop ring 19 abuts against the inside of the flange 21 of the pressing body 15 so that the ring is clamped between the flange 21 and the driven clutch holder 11.
- Adjustment of the axial position of the stop ring 19 is effected by the stop ring 19, upon mounting of the disc clutch, being preliminary placed further out to the left on the driven clutch holder 11 than what is shown in the figures.
- the pressing body 15 by virtue of the force from the spring 17, is situated further to the left than what is shown in the figures, and the hydraulic piston 13 starts from a position situated correspondingly further to the left at a principally full stroke length.
- the device entails furthermore an automatic readjustment as the clutches are wearing down. This is due to the fact that increased wearing down of the clutches causes the stroke movement to proceed somewhat further rightward and thereby displace the stop ring 19 correspondingly in this direction.
- FIG. 8 An alternative embodiment of the stop ring 19 is illustrated in Figs. 8 and 9.
- the stop ring is formed as a shrink ring 19a.
- the shrink ring 19a forms a
- the compression joint is adapted so that the frictional force becomes greater than what can be overcome by the force from the spring 17, but sufficiently limited to be possible to be overcome by the manoeuvring force from the hydraulic piston 13.
- the stop ring 19a will stop the leftward movement of the impact ring 18 and thereby limit the return stroke length.
- the stop ring 19a obtains an axial position that limits the stroke length to what is necessary.
- FIG. 10 shows the disc clutch in the disengaged position and Fig. 11 in the engaged position.
- the stop ring 19b shown in more detail in Figs. 12 and 13 has, in this example, the inclined projections 22b thereof directed radially outward and abuts against the inside of the axially directed flange 21 of the pressing body 15.
- the impact ring 18b is formed as a ring-shaped radial flange of the driven clutch holder 11. In the disengaged position in Fig. 10, the stop ring 19b abuts against the impact ring 18b on the driven clutch holder 11 and thus limits the return movement of the pressing body 15.
- the stop ring 19b is applied to the inside of the flange 21 of the pressing body 15 with the oblique direction of the projections 22b to the right as seen from the inside and out.
- the oblique direction entails that the inner edge of the respective projection 22b in a barb-like way is pressed against the inside of the flange 21 , which results in great resistance to rightward
- the pressing body 15 Upon initial actuation of the disc clutch, the pressing body 15, by virtue of the force from the spring 17, is situated further to the left than what is shown in the figures, and the hydraulic piston 13 starts from a position situated correspondingly further to the left at a principally full stroke length.
- the position shown in Fig. 11 Upon completed engagement movement, the position shown in Fig. 11 is reached.
- FIG. 14 shows the disc clutch in the disengaged position and Fig. 15 in the engaged position.
- the stop means has a plurality of stop rings 19c, e.g., eight, arranged along a circle concentric with the principal axis of the disc clutch.
- Each stop ring 19c is attached to a cylindrical pin 25 by a friction joint of the similar kind as the one described in connection with Figs. 3 and 5, and the stop ring 19c has the corresponding inwardly directed projections as the stop ring 19 of Figs. 3 and 5 that is illustrated in more detail in Figs. 6 and 7.
- the stop ring 19c has a considerably smaller diameter than the stop ring 19 in Figs. 6 and 7.
- each stop ring 19c The oblique direction of the projections on each stop ring 19c is such that the resistance to relative motion of the stop ring 19c to the left in the figures in relation to the pin 25 is considerably greater than such a relative motion to the right, thanks to the previously described barb action.
- Each pin 25 is fixedly connected with the driven clutch holder 11 and can thereby be regarded as a part of the same.
- the pins 25 extend through openings 26 in the pressing body 15.
- the pressing body 15 has a radial circumferential groove 27 on the side turned away from the clutch pack, whereby a radial flange 24c is formed, and in which flange each opening 26 has a continuation 28. Accordingly, in one direction, the groove 27 is limited by the flange 24c and in the other one by an opposite wall 18c of the pressing body.
- the ring-shaped wall 18c constitutes impact means 18c for the co-operation with the stop rings 19c.
- the pressing body 15 When the disc clutch is to be disengaged from the situation illustrated in Fig. 15, the pressing body 15 is moved leftward by the spring 17 and thereby also the impact means 18c. When the impact means 18c in that connection has reached up to the stop ring 19c, as is shown in Fig. 14, continued movement is prevented and the pressing body 15 and the hydraulic piston 13 assume an axial position defined by the stop device 18c, 19c. Without the stop ring 19c, the pressing body 15 and the hydraulic piston 13 would have, because of the force from the spring 17, continued to be displaced leftward as far as allowed by the stroke length of the hydraulic piston.
- the distance between the impact means 18c and each stop ring 19c in the engaged state (Fig. 15) is adjusted so that it corresponds to the distance required to bridge the clearance of the clutch pack.
- the adjustment of the distance is provided by adjustment of the axial position of each stop ring 19c on the pins 25 of the driven clutch holder 11.
- Adjustment of the axial position of each stop ring 19c is effected by each stop ring 19c, upon mounting of the disc clutch, being preliminary placed further out to the left on the respective pin 25 than what is shown in the figures.
- the pressing body 15 by virtue of the force from the spring 17, is situated further to the left than what is shown in the figures, and the hydraulic piston 13 starts from a position situated correspondingly further to the left at a principally full stroke length.
- the chamber 14 upon this initial engagement movement, is pressurized and the hydraulic piston 13 is displaced rightward, the flange 24c will displace each stop ring 19c in the same direction, i.e., the direction in which the stop ring is easily displaceable.
- the position shown in Fig. 15 is reached.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE0950723A SE534205C2 (en) | 2009-10-02 | 2009-10-02 | Overloader with two interlocking rotors and slat coupling |
PCT/SE2010/051037 WO2011040869A1 (en) | 2009-10-02 | 2010-09-28 | A supercharger with two intermeshing rotors and disc clutch |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2483541A1 true EP2483541A1 (en) | 2012-08-08 |
EP2483541A4 EP2483541A4 (en) | 2017-09-27 |
Family
ID=43826518
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10820908.1A Withdrawn EP2483541A4 (en) | 2009-10-02 | 2010-09-28 | A supercharger with two intermeshing rotors and disc clutch |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP2483541A4 (en) |
JP (1) | JP2013506784A (en) |
KR (1) | KR20120092620A (en) |
CN (1) | CN102686847A (en) |
AU (1) | AU2010301163A1 (en) |
BR (1) | BR112012007287A2 (en) |
RU (1) | RU2012117758A (en) |
SE (1) | SE534205C2 (en) |
WO (1) | WO2011040869A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112014006523A5 (en) | 2014-03-27 | 2016-12-15 | Schaeffler Technologies AG & Co. KG | Sheet metal press plate and pressure pot as a common component |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3596537A (en) * | 1969-06-11 | 1971-08-03 | Gen Motors Corp | Clutch piston and retraction spring subassembly and method of transmission assembly |
US3815716A (en) * | 1973-03-19 | 1974-06-11 | Gen Motors Corp | Automatic piston adjuster |
JPS56135534U (en) * | 1980-03-17 | 1981-10-14 | ||
SE506513C2 (en) * | 1995-10-23 | 1997-12-22 | Lysholm Techn Ab | Transmission with a two-piece connector |
US5749451A (en) * | 1996-09-27 | 1998-05-12 | General Motors Corporation | Clutch assembly with a piston stroke adjuster |
SE511761C2 (en) * | 1996-10-09 | 1999-11-22 | Lysholm Techn Ab | Oil cooled slat coupling |
DE10004179C5 (en) * | 1999-09-30 | 2017-06-29 | Volkswagen Ag | Multiple clutch device |
JP3943950B2 (en) * | 2002-02-18 | 2007-07-11 | 株式会社エクセディ | Clutch cover assembly |
BRPI0710286B1 (en) * | 2006-04-26 | 2019-05-07 | Litens Automotive Partnership | UNIDIRECTIONAL INSULATOR TO TRANSFER TORQUE BETWEEN A FLEXIBLE DRIVE AND A DIPOSITIVE |
-
2009
- 2009-10-02 SE SE0950723A patent/SE534205C2/en unknown
-
2010
- 2010-09-28 RU RU2012117758/06A patent/RU2012117758A/en not_active Application Discontinuation
- 2010-09-28 AU AU2010301163A patent/AU2010301163A1/en not_active Abandoned
- 2010-09-28 EP EP10820908.1A patent/EP2483541A4/en not_active Withdrawn
- 2010-09-28 WO PCT/SE2010/051037 patent/WO2011040869A1/en active Application Filing
- 2010-09-28 KR KR1020127011466A patent/KR20120092620A/en not_active Application Discontinuation
- 2010-09-28 BR BR112012007287A patent/BR112012007287A2/en not_active IP Right Cessation
- 2010-09-28 CN CN201080043970XA patent/CN102686847A/en active Pending
- 2010-09-28 JP JP2012532047A patent/JP2013506784A/en active Pending
Non-Patent Citations (1)
Title |
---|
See references of WO2011040869A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2011040869A1 (en) | 2011-04-07 |
BR112012007287A2 (en) | 2016-04-19 |
CN102686847A (en) | 2012-09-19 |
SE534205C2 (en) | 2011-05-31 |
EP2483541A4 (en) | 2017-09-27 |
RU2012117758A (en) | 2013-11-10 |
KR20120092620A (en) | 2012-08-21 |
JP2013506784A (en) | 2013-02-28 |
AU2010301163A1 (en) | 2012-04-19 |
SE0950723A1 (en) | 2011-04-03 |
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