CN102686847A - Supercharger with two intermeshing rotors and disc clutch - Google Patents
Supercharger with two intermeshing rotors and disc clutch Download PDFInfo
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- CN102686847A CN102686847A CN201080043970XA CN201080043970A CN102686847A CN 102686847 A CN102686847 A CN 102686847A CN 201080043970X A CN201080043970X A CN 201080043970XA CN 201080043970 A CN201080043970 A CN 201080043970A CN 102686847 A CN102686847 A CN 102686847A
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- Prior art keywords
- clutch
- stop ring
- stopping device
- compress
- anchor clamps
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- 230000007246 mechanism Effects 0.000 claims description 20
- 238000009527 percussion Methods 0.000 claims description 19
- 230000003213 activating effect Effects 0.000 claims description 7
- 230000003116 impacting effect Effects 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 230000033001 locomotion Effects 0.000 abstract description 8
- 230000008901 benefit Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000004913 activation Effects 0.000 description 3
- 239000002360 explosive Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 239000012141 concentrate Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005056 compaction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
- Supercharger (AREA)
Abstract
The invention concerns a supercharger that has two rotors engaging into each other and is provided with a disc clutch. The disc clutch has driving (9) and driven (12) clutches connected with a drive shaft (7) and with one of the rotors, respectively. Furthermore, there is an axially displaceable pressing body (15) as well as actuation device (13) for the same and a deactuation spring (17). According to the invention, the disc clutch comprises a stop device (18, 19) that limits the axial movement of the pressing body (15) in the deactuation direction. The stop device (18, 19) consists of an impact means (18) on the pressing body (15) or on the driven clutch holder (11) and a stop means (19) on the other component. The impact means (18) is axially fixed while the stop means (19) is attached by a friction joint.
Description
Technical field
The present invention relates to a kind of pressurized machine that has two intermeshing rotors and be provided with plate clutch, said plate clutch comprises:
-have a driving clutch of the driving clutch anchor clamps that are connected with live axle,
-have with rotor in one be connected from the dynamic clutch anchor clamps from dynamic clutch,
-be arranged to when activating, to compress clutch can axially movablely compress body,
-be used to activate the said actuation device that compresses body, and
-be used to make the said body that compresses to remove the spring assembly that activates.
Background technique
Through SE511761, can formerly know the pressurized machine of the above-mentioned type.When needs are supplied air to explosive motor with positive pressure-for example when quickening, through plate clutch joint pressurized machine.
When the joint of pressurized machine is implemented, before pressurized machine is activated, for example through accelerator pedal or start bonding operation through automatically controlled joint and can cause delay to a certain degree.Except other aspects, said delay comprises that the piston of operating plate clutch moves up to said clutch from initial position and is engaged to the used each other time fully.On the one hand; The said body that compresses should make up corresponding to being pressed against each other with clutch that moves arrives the distance that moves before the clutch pack; And this distance is the necessary result that manufacturing tolerances caused; On the other hand, said mobile should making up is pressed to together and meshes fully each other necessary distance with clutch.In non-actuated condition, drive and must relative to each other have gap to a certain degree certainly from dynamic clutch.
The time that reduces mentioned delay as much as possible is important.
Through US5749451, can formerly know a kind of plate clutch in addition, in said plate clutch, be provided with the restriction clutch plate along going the moving of direction of actuation with travel limit length and thereby the device of restriction engaging time.Said device comprises and the crew-served spring-loaded ball of camming surface.Therefore, therefore its complex design also causes manufacture cost expensive.
In addition, such device can be easy to take place the operation disorder.Known plate clutch is not the particular condition in the operation that is intended to engage pressurized machine and therefore be not suitable for this pressurized machine.
As far as being used to engage the plate clutch of pressurized machine, lay special stress on is to the demand of quick joint.During pressurized machine in relating to automobile, pressurized machine in starting its engage-for example when overtaking other vehicles, as far as possible promptly to respond be important.
The objective of the invention is to reduce the engaging time of the pressurized machine that is used for explosive motor with simple and reliable mode.
Summary of the invention
According to the present invention; Said purpose realizes through the following fact; That is, the sort of pressurized machine of mentioning through background introduction has following special characteristic: this plate clutch comprises being used to limit and compresses body along removing the axially movable stopping device of direction of actuation that said stopping device comprises percussion mechanism and stopping device; In said percussion mechanism and the said stopping device one be connected from the dynamic clutch anchor clamps; And in said percussion mechanism and the stopping device another with compress body and be connected, the connection of said percussion mechanism is axially fixed, and the connection of said stopping device connects through friction and provides.
Through the following fact, i.e. stopping device restriction compresses moving axially of body, can realize the best axially locating of percussion mechanism and stopping device, makes said moving axially be restricted to required the moving in gap of making clutch up.
Thus, exempted and made the required that part of running length of necessary manufacturing tolerances up.In addition, the gap of clutch can remain on minimum.Because have a plurality of-be typically about 15 concurrent operation parts, so eliminate tolerance and reduce the gap and cause that running length significantly shortens when engaging.Owing to connect the fact of the connection that stopping device is provided, so easily the position of stopping device is adjusted to the situation corresponding to said optimum position vertically through friction.Thereby, exempted compressing body compressing the distance that body need move before beginning clutch is pressed onto together.Correspondingly, the running length that compresses body is only corresponding to the gap of clutch.The running length of operation equipment becomes and is limited to corresponding degree.Thereby engaging time can reduce to 0.2s from about 0.5s, and promptly about initial value is half the.
The special scheme that friction between stopping device and the associated components thereof connects becomes stopping device and is very easy to produce and regulate.In addition, this design makes reliability become very high.
Though advantage of the present invention mainly concentrates on through reducing engaging time and uses, the operated device that can alternatively use size to reduce through the engaging time of accepting to remain unchanged utilizes these advantages.In the operation of for example hydraulic piston, wherein the oil pressure of motor is used as hydraulic power, and oily stream can be thus by throttling.Alternatively, if by oil pump feed, can select to have the pump of lower pressure and/or low volume.
According to preferred implementation, stopping device comprises at least one stop ring.
This device is formed ring have structural advantage, and be convenient to form friction and connect with mode easily.Suitably, said ring is coaxial with the main axis of plate clutch.In addition, percussion mechanism is ring-type and preferably coaxial suitably.Stop ring can be alternatively laterally moves along the direction of the main axis that is parallel to plate clutch, and wherein said plate clutch can be suitable for having a plurality of stop rings, said a plurality of stop rings preferably be arranged in the concentric round wire of the main axis of plate clutch on.
According to extra preferred implementation, the friction of each stop ring connect the radial outside all be formed on stop ring or inboard and be connected to said stop ring from the dynamic clutch anchor clamps and compress between one the corresponding radially inner side or the outside the body.
Thereby, under not to the situation of the unnecessary high request of accuracy of manufacturing, can the frictional force that fully is suitable for be provided relatively easy mode.
According to extra preferred implementation; Stop ring is provided with the device that is used for providing along different axial directions different powerful frictional force, prevents when activating that wherein power that stop ring moves along the moving direction that compresses body is less than the frictional force that prevents that stop ring from moving in opposite direction.
Thereby, through the following fact, promptly having very little moving resistance along compaction direction, stop ring can easily be adjusted to best axially situation, makes that the stop ring restriction compresses body during going actuation motion only can move to the position corresponding to the gap of clutch.Bigger frictional force is in opposite direction impacted in going actuation motion and is guaranteed to realize stop action when ring impacts on stop ring.
According to extra preferred implementation, the radial side of each stop ring of the part that constituting rubs connects is asymmetric, so that said different powerful frictional force is provided.
It is simple relatively and solution easily that design through stop ring provides the lack of uniformity of frictional force.
According to extra preferred implementation, the radial side of each stop ring of the part that constituting rubs connects is provided with the projection of inclined orientation, and said projection tilts along the moving direction that compresses body when going to activate.
The projection that tilts inwardly compresses against from the dynamic clutch anchor clamps or compress the barb of the material of body as a kind of, thereby forms opposing along the powerful frictional force of going direction of actuation to move.Along other direction, projection can slide with pulling thereby produce the less frictional force of the location that allows said projection.Wherein towards compress body outwards the alternate embodiment of directed projection be particularly advantageous can process by the aluminium that good grasping condition is provided because compress body.
According to the alternate embodiment of above-mentioned mode of execution, it is the connection that compresses that has greater than the impacting force of the maximum axial force of spring assembly that this friction connects.
Stop ring can thereby form flat ring, said flat ring be retracted to regularly connected from the dynamic clutch anchor clamps with compress the body.Though the stop ring in the above-mentioned mode of execution has the different resistances that move on the different axial directions, the mobile frictional force of opposing is identical on both direction herein.
At this, alternatively, the direction in edge moves and provides through frictional force is adapted to along the different powerful external force of directive effect on ring of correspondence along the possibility that the other direction opposing is moved.
According to extra preferred implementation, operation equipment comprises hydraulic piston.
Hydraulic piston is the operation equipment type of the most often using in the plate clutch of pressurized machine, and therefore the present invention specifically concentrates on and adopts this operation equipment.As point out that at first the present invention allows to compare the hydraulic medium feeding mechanism that uses low performance under the littler situation with routine techniques in that engaging time is become in this embodiment.
According to extra preferred implementation, pressurized machine comprises screw compressor.
The present invention itself is applicable to-the pressurized machine of other kinds of Roots type supercharger form for example, but the present invention is particularly suitable for being applied to screw compressor, thus the common advantage of utilizing this compressor to possess.
Above-mentioned preferred implementation is limited in the claim that is subordinated to claim 1.What should stress is that extra preferred implementation can comprise all feasible combinations of above-mentioned preferred implementation naturally.
In second aspect, the invention still further relates to the plate clutch that is designed to be included in the plate clutch in the pressurized machine of the present invention accordingly, specifically according to the plate clutch in any the described pressurized machine in the preferred implementation of the present invention.
Plate clutch of the present invention and preferred implementation of the present invention have corresponding to advantage of the present invention and the top intensifier type of having explained.
Through the detailed description of embodiments of the invention being set forth in more detail the present invention consulting under the situation of accompanying drawing subsequently.
Description of drawings
Fig. 1 is the stereogram of the pressurized machine of the type that the present invention relates to.
Fig. 2 is the axial section through the plate clutch of the pressurized machine of the Fig. 1 that is in a disengaged position.
Fig. 3 is the partial enlarged drawing of Fig. 2.
Fig. 4 is the axial section corresponding to the plate clutch of Fig. 2 that is in engagement positio.
Fig. 5 is the partial enlarged drawing of Fig. 4.
Fig. 6 is the end elevation of a part of details of the plate clutch of Fig. 2-5.
Fig. 7 is the side view of the details of Fig. 6.
Fig. 8 and 9 is the axial sections that correspond respectively to the plate clutch of Fig. 3 and Fig. 4, and alternative has been shown among the figure.
Figure 10 and 11 is the axial sections that correspond respectively to the plate clutch of Fig. 3 and 4, and extra embodiment has been shown among the figure.
Figure 12 and 13 is respectively the end elevation and the side view of details of the plate clutch of Figure 10-11.
Figure 14 and 15 is the axial sections that correspond respectively to the plate clutch of Fig. 3 and 4, and extra embodiment has been shown among the figure.
Embodiment
In the stereogram of Fig. 1 pressurized machine has been shown, said pressurized machine comprises being arranged in the screw compressor in the compressor housing 1 and being provided with and drives link 6 and be arranged in the plate clutch in the clutch housing 2 that said housing 1 and 2 is bonded to each other.Screw compressor has two helical rotors 4,5 that are bonded to each other to the other side, and one in the said helical rotor 4,5 is the convex rotor, and another is recessed formula rotor.Be transmitted through compressor outlet 3 by the chamber air compressed that between the compressor housing of rotor 4,5 and explosive motor, forms.The other end of rotor is furnished with the inlet (not shown) so that air gets into.The present invention also can be applicable to similar rotor, for example roots rotor.
In normal running, pressurized machine is not worked.When power needs temporary transient increasing, activate plate clutch to drive pressurized machine.
Illustrate in greater detail plate clutch among Fig. 2 and 3, it has driver part and driven member.Driver part comprises through driving the live axle 7 that link 6 (see figure 1)s are connected with input drive shaft.Through driving clutch anchor clamps 8, live axle 7 is connected with driving clutch 9 splines.
Driven member comprises driven hub 10, this driven hub 10 through from the dynamic clutch anchor clamps be connected from dynamic clutch 12 splines.Driven hub 10 is connected with the driven shaft transmission ground of one (suitable is female rotor) in comprising helical rotor.For the sake of clarity, omitted being connected of driven hub 10 and rotor shaft among the figure, but said connection can be general type.
In Fig. 2, plate clutch is gone to activate, promptly do not drive power from drive clutch 9 be sent to from dynamic clutch 12 and thus pressurized machine be not activated.
In order to engage pressurized machine, be provided with hydraulic piston 13 with the seal space 14 that is used for the sap pressure supply medium.On the 13a of the shell-like extension of hydraulic piston 13, compress body 15 and supported by axle journal through ball bearing 16.Spring 17 is disposed in and compresses body 15 and between the dynamic clutch anchor clamps 11 and spacing movement is provided between them.
In the time will engaging pressurized machine, hydraulic medium is introduced into seal space 14, and piston 13 is moved into the right side among the figure in the resistance that overcomes from spring 17, and therefore also will compress body 15 moves to the right side among the figure.When clutch pack was compressed, driving torque was transferred into driven hub 10 and further is sent to pressurized machine.Figure 4 and 5 show this state.
When throwing off, the pressure in the seal space 14 is released, and compresses body 15 and is pushed back the left side to the figure by spring, and therefore make hydraulic piston 13 also be pushed back the left side.
That describes up to now is actually the setting identical with the conventional plate clutch of pressurized machine that the present invention has.
Specialization of the present invention is stopping device, and said stopping device restriction plate clutch goes to activate-compress when promptly throwing off moving of body.Said stopping device comprises impact ring 18 and stop ring 19.
Impact in the groove 20 on flange 21 inboards that ring 18 is fixed on the axial protrusion that compresses body 15.Stop ring 19 is attached at from the outside of dynamic clutch anchor clamps 11.In Fig. 3 and 5, can be clear that the effect of stopping device.
When plate clutch will be thrown off from the position shown in the Figure 4 and 5, compress that body 15 is moved to the left and therefore make under the effect of spring 17 and impact ring 18 and also be moved to the left.Shown in Fig. 2 and 3, when the impact ring in this connection 18 arrives stop rings 19, continue mobile being prevented from, and compress body 15 axial position that 13 acquisitions are limited stopping device 18,19 with hydraulic piston.Under the situation that does not have stop ring 19, compress body 15 and will in the scope of the running length permission of hydraulic piston, continue to be moved to the left by power from spring 17 with hydraulic piston 13.
Because the following fact, promptly since stopping device 18,19 therefore to limit returning of hydraulic piston mobile, thereby make plate clutch will be when activating once more the required running length stroke that will become than have under the situation of stopping device 18,19 short.Thereby engaging time shortens accordingly.
In order to allow this adjusting and to guarantee the stopping function of stop ring 19 simultaneously, stop ring 19 is designed such that it and from being connected of dynamic clutch anchor clamps 11 allowing stop ring to move axially and can not move axially along other direction along a direction.
Like what see in Fig. 6 and 7, this realizes that through the following fact promptly stop ring 19 has the inside projection of a plurality of directions 22, and said projection 22 is obliquely to interior orientation.
Like what see in Fig. 3 and 5, stop ring 19 is by with from the outside with see that wherein the direction that is tilted to the left is applied to from dynamic clutch anchor clamps 11.Said true dip direction must push against the outside of clutch anchor clamps 11 inside edge of corresponding projection 22 with similar barb mode, thereby causes big resistance that stop ring is moved to the left.Along another direction, mobile resistance obviously reduces, because projection 22 can slide against the outside of clutch anchor clamps 11 at that time.The outside of stop ring 19 is against the inboard of the flange that compresses body 15 21, makes this ring be clamped at flange 21 and between the dynamic clutch anchor clamps 11.
The adjusting of the axial position of stop ring 19 realizes by stop ring 19, when plate clutch is installed, said stop ring 19 initial placement be from dynamic clutch anchor clamps 11 than shown in the figure out to left distant place more.During in this connects and at the initial activation plate clutch, make by power to compress body 15 and also be positioned at, and hydraulic piston 13 begins to moving left to total travel length substantially from the position of correspondence location than the place, the more left side shown in the figure from spring 17.When this initial engagement moves, when pressurized and hydraulic piston 13 is moved right when chamber 14, the shoulder 24 on the inboard of flange 23 will make stop ring 19 move along the direction that equidirectional moves-promptly can move easily along stop ring.Impact ring 18 also nature moves right with compressing body 15.Moving to when engaging fully, arriving the position shown in the Figure 4 and 5.
Subsequently, body 15 is moved to the left and when throwing off, impact ring 18 travelling backwards thereupon when causing compressing along with chamber 14 release pressures and spring 17, and not travelling backwards thereupon of stop ring 19.When impacting ring 18 arrival and contact stop ring 19, the continuation of impact ring 18 is moved to get clogged and therefore the continuation that compresses body is moved also and is got clogged.This be because, can not overcome 19 pairs of powerful resistances that move in the direction of above-described stop ring from the spring force of spring 17.Plate clutch is in a disengaged position (Fig. 2 and 3) now.
Running length when the position of regulating thus of stop ring 19 defines further the joint.The trip length will be restricted to the gap of clutch pack subsequently.
Along with the wearing and tearing of clutch, said device makes it possible to further regulate automatically.This is that i.e. clutch abrasion increase causes stroke motion more or less further to advance to the right owing to the following fact, and stop ring 19 is moved accordingly in the direction.
Fig. 8 and 9 shows the alternate embodiment of stop ring 19.Here, stop ring forms contractile ring 19a.Contractile ring 19a forms with compression from dynamic clutch anchor clamps 11 and is connected.Said compression connects and is arranged such that frictional force becomes and can not can be overcome by the steering force from hydraulic piston 13 but fully be limited to by the bigger power that power overcame from spring 17.
Thus, when disengagement is moved, thereby stop ring 19a will make impact ring 18 stop to be moved to the left and limit backhaul length.
It only is that the gap of clutch pack is needed that the initial axially locating of stop ring 19a is arranged to running length is restricted to.In this connected, stop ring 19a was applied to from dynamic clutch anchor clamps 11 and through extruding is installed and pushes the appropriate location.The joint situation has been shown among Fig. 9.
Alternatively, when initial engagement, can stop ring be pushed suitable position through operated piston.This presupposes, and the pressure of connection is less than passing through the power that operated piston obtains.
When throwing off, impacting ring will be moved to the left, and be prevented from being moved further up to it, and this moment, it was against stop ring 19a.Because it is bigger than spring force stop ring to be remained on the surface friction drag of appropriate location, be moved to the left thereby hinder stop ring.Said disengaged position has been shown among Fig. 8.
In this way, stop ring 19a obtains running length is limited in the axial position in the necessary scope.
Figure 10 and 11 shows other alternate embodiment, and wherein Figure 10 shows the plate clutch that is in a disengaged position, and Figure 11 shows the plate clutch that is in engagement positio.
In this example, the stop ring 19b that in Figure 12 and 13, is shown in further detail has the directed inclination projection 22b of radially outward and against the inboard of the axial orientation flange 21 that compresses body 15.Impacting ring 18b here, forms from the annular radial flange of dynamic clutch anchor clamps 11.Disengaged position in Figure 10, stop ring 19b against the impact ring 18b from dynamic clutch anchor clamps 11 and thus restriction to compress returning of body 15 mobile.
Like what see in Figure 10 and 11, stop ring 19b is applied to the inboard of the flange 21 that compresses body 15 with the direction that is tilted to the right from inboard and outside projection 22b.Said true dip direction must push against the inboard of flange 21 inside edge of corresponding projection 22b with the mode of similar barb, thereby causes big resistance that stop ring is moved right.Along another direction, mobile resistance obviously reduces, because projection 22b at that time can be against the inner slide of flange 21.The inboard of stop ring 19b is against the outside from dynamic clutch anchor clamps 11, makes this ring be clamped at flange 21 and between the dynamic clutch anchor clamps 11.
The adjusting of the axial position of stop ring 19b realizes by stop ring 19b, and when plate clutch was installed, stop ring 19b initial placement be than outside distant place more, the right side shown in the figure in flange 21.When the initial activation plate clutch, by the power from spring 17 make compress body 15 be positioned at than shown in the figure left more at a distance, and hydraulic piston 13 begins further to move on to the left side of total travel length substantially from the position of correspondence location.When this initial engagement moves; When pressurized and hydraulic piston 13 moves right when chamber 14; Supporter ring 24b from the dynamic clutch anchor clamps will limit moving of stop ring 19b; That is, make the relative movement between flange 21 and the stop ring 19b carry out along the direction that stop ring 19b can move easily.Moving to when engaging fully, arrive position shown in Figure 11.
Subsequently, body 15 is moved to the left and when throwing off when causing compressing along with chamber 14 release pressures and spring 17, stop ring 19b travelling backwards thereupon.When stop ring 19b arrival and contact impact ring 18b, the continuation campaign of stop ring 19b gets clogged and therefore the continuation campaign that compresses body is also got clogged.This is the powerful resistance to being moved to the left with respect to flange 21 owing to above-described stop ring 19, and this resistance can not be overcome by the spring force from spring 17.Plate clutch is in a disengaged position (Figure 10) now.
Figure 14 and 15 shows another alternative, and wherein Figure 14 shows the plate clutch that is in a disengaged position, and Figure 15 shows the plate clutch that is in engagement positio.
In this example, stopping device has a plurality of stop ring 19c, for example 8 stop rings arranging of edge and the concentric circle of the main axis of plate clutch.Each stop ring 19c is connected and is attached to cylindrical pin 25 through being similar to a kind of friction that combines Fig. 3 and 5 to describe, and shown in Fig. 3 and 5 and the stop ring 19 that in Fig. 6 and 7, is shown in further detail, and stop ring 19c has accordingly the projection to interior orientation.Yet, should be understood that stop ring 19c has than the 19 obvious littler diameters of the stop ring in Fig. 6 and 7.Since the barb effect that the front is described, the true dip direction of the projection on each stop ring 19c make stop ring 19c with respect to the resistance of pin 25 relative movement in left side in figure obviously greater than the resistance of to the right this type of relative movement.
Each pin 25 all with therefore be permanently connected from dynamic clutch anchor clamps 11 and can be considered to from the part of dynamic clutch anchor clamps 11.Pin 25 extends through the opening 26 that compresses in the body 15.In addition, compress body 15 and have footpath groove 27 towards periphery in the side of leaving from clutch pack, form radial flange 24c thus, and each opening 26 all has extension 28 in said flange.
Therefore, along a direction, groove 27 is limited by flange 24c, and is limited by the counter wall 18c that compresses body along other direction.Annular wall 18c is configured for the crew-served percussion mechanism 18c with stop ring 19c.
Will be when situation shown in Figure 15 be thrown off when plate clutch, compress that body 15 is moved to the left and therefore percussion mechanism 18c also is moved to the left under the effect of spring 17.Shown in figure 14, when the percussion mechanism 18c in this connection arrives stop ring 19c, continue mobile being prevented from, and compress body 15 axial position that 13 acquisitions are limited stopping device 18c, 19c with hydraulic piston.Under the situation that does not have stop ring 19c, compressing body 15 and hydraulic piston 13 will be because of continuing to be moved to the left in the scope that the running length of hydraulic piston allows from the power of spring 17.
Through the following fact, i.e. returning of stopping device 18c, 19c restriction hydraulic piston is mobile, plate clutch will be when activating once more the needed running length stroke that will become than have under the situation of stopping device 18c, 19c short.Thereby engaging time shortens accordingly.
Distance between percussion mechanism 18c under the jointing state (Figure 15) and each the stop ring 19c is adjusted so that it is corresponding to the needed distance in the gap of making clutch pack up.The adjusting of said distance is provided through the axial position of regulating each the stop ring 19c from the pin 25 of dynamic clutch anchor clamps 11.
The adjusting of the axial position of each stop ring 19c realizes by each stop ring 19c, when plate clutch is installed, stop ring 19c initial placement be on the pin 25 of correspondence than shown in the figure outwards with distant place more left.During in this connects and at the initial activation plate clutch; By power from spring 17; Make to compress body 15 and also be positioned at, and hydraulic piston 13 begins further to move on to the left side of total travel length substantially from the position that correspondence is located than the place that more keeps left shown in the figure.When this initial engagement moves, when pressurized and hydraulic piston 13 moves right when chamber 14, flange 24c will make each stop ring 19c move along the direction that equidirectional moves-promptly can move easily along stop ring.Moving to when engaging fully, arrive position shown in Figure 15.
Subsequently, when throwing off along with chamber 14 release pressures, spring 17 causes compressing body 15 and is moved to the left.When percussion mechanism 18c arrives and during contact stop ring 19c, the continuation that compresses body 15 is moved and is got clogged.This is because due to 19 pairs of above-described each stop rings powerful resistances that move in the direction, can not overcome this resistance from the spring force of spring 17.Plate clutch is in a disengaged position (Figure 14) now.
Claims (11)
1. pressurized machine that has two rotors that are engaged with each other (4,5) and be provided with plate clutch, said plate clutch comprises:
-have a driving clutch (9) of the driving clutch anchor clamps (8) that are connected with live axle (7);
-have with said rotor (4,5) in a connection from dynamic clutch anchor clamps (11) from dynamic clutch (12);
-be arranged to when activating, to compress said clutch (9,12) can axially movablely compress body (15);
-be used to activate the said actuation device (13) that compresses body (15); And
-be used to make the said body (15) that compresses to remove the spring assembly (17) that activates,
It is characterized in that, said plate clutch comprise be used to limit said compress body (15) along go the axially movable stopping device of direction of actuation (18,18b, 18c, 19; 19a, 19b, 19c), said stopping device (18,18b; 18c, 19,19a, 19b 19c) comprises percussion mechanism (18; 18b, 18c) and stopping device (19,19a, 19b, 19c); In said percussion mechanism and the said stopping device one be connected from said dynamic clutch anchor clamps (11), and in said percussion mechanism and the said stopping device another be connected with the said body (15) that compresses, said percussion mechanism (18,18b, connection 18c) is axially fixed; And said stopping device (19,19a, 19b, connection 19c) connects through friction to be provided.
2. pressurized machine as claimed in claim 1 is characterized in that, said stopping device (19,19a, 19b, 19c) comprise at least one stop ring (19,19a, 19b, 19c).
3. pressurized machine as claimed in claim 2 is characterized in that, each stop ring (19; 19a, 19b, friction 19c) connects all at stop ring (19; 19a, 19b, radial outside 19c) or inboard and be connected to said stop ring (19; 19a, 19b, 19c) from dynamic clutch anchor clamps (11) and compress between one corresponding radially inner side or the outside the body (15) and form.
4. like claim 2 or 3 described pressurized machines, it is characterized in that said stop ring (19; 19b, 19c) be provided be used for along different axial directions provide different powerful frictional force device (22,22b); Wherein when activating, prevent stop ring (19,19b, the frictional force that 19c) moves along the moving direction that compresses body (15) is less than preventing stop ring (19; 19b, the frictional force that 19c) moves in opposite direction.
5. pressurized machine as claimed in claim 4 is characterized in that, constitute the part that said friction connects each stop ring (19,19b, radial side 19c) is asymmetric, so that said different powerful frictional force is provided.
6. pressurized machine as claimed in claim 5; It is characterized in that, constitute the part that said friction connects each stop ring (19,19b; Radial side 19c) is provided with the projection (22 of inclined orientation; 22b), and the projection of said inclined orientation when going to activate (22,22b) tilt along the moving direction that compresses body (15).
7. like claim 2 or 3 described pressurized machines, it is characterized in that it is that the compression that has greater than the impacting force of the maximum axial force of spring assembly (17) connects that said friction connects.
8. like each described pressurized machine among the claim 1-7, it is characterized in that said actuation device (13) comprises hydraulic piston (13).
9. like each described pressurized machine among the claim 1-8, it is characterized in that said pressurized machine comprises screw compressor.
10. plate clutch comprises:
-have a driving clutch (9) that drives clutch anchor clamps (8);
-have from dynamic clutch anchor clamps (11) from dynamic clutch (12);
-be arranged to when activating, to compress clutch (9,12) can axially movablely compress body (15);
-be used to activate the said actuation device (13) that compresses body (15); And
-be used to make compress body (15) and remove the spring assembly (17) that activates,
It is characterized in that, said plate clutch comprise be used for the restriction compress body (15) along go the axially movable stopping device of direction of actuation (18,18b, 18c, 19; 19a, 19b, 19c), said stopping device (18,18b; 18c, 19,19a, 19b 19c) comprises percussion mechanism (18; 18b, 18c) and stopping device (19,19a, 19b, 19c); In said percussion mechanism and the said stopping device one be connected from dynamic clutch anchor clamps (11), and in said percussion mechanism and the said stopping device another with compress body (15) and be connected, said percussion mechanism (18,18b, connection 18c) is axially fixed; And said stopping device (19,19a, 19b, connection 19c) connects through friction to be provided.
11. plate clutch as claimed in claim 10 is characterized in that, said plate clutch comprises and is used for limiting the characteristic according to each described plate clutch of claim 2-8.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE0950723-7 | 2009-10-02 | ||
| 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 (1)
| Publication Number | Publication Date |
|---|---|
| CN102686847A true CN102686847A (en) | 2012-09-19 |
Family
ID=43826518
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080043970XA Pending CN102686847A (en) | 2009-10-02 | 2010-09-28 | 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) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106164517A (en) * | 2014-03-27 | 2016-11-23 | 舍弗勒技术股份两合公司 | Pressurized tank and metal platen as common component |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109236887B (en) * | 2018-09-30 | 2024-04-19 | 厦门南超机械有限公司 | Clutch |
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|---|---|---|---|---|
| WO1997015759A1 (en) * | 1995-10-23 | 1997-05-01 | Lysholm Technologies Ab | Transmission including a two-part clutch arrangement |
| WO1998015748A1 (en) * | 1996-10-09 | 1998-04-16 | Lysholm Technologies Ab | Oil-cooled disc clutch |
| US5749451A (en) * | 1996-09-27 | 1998-05-12 | General Motors Corporation | Clutch assembly with a piston stroke adjuster |
| US6464059B1 (en) * | 1999-09-30 | 2002-10-15 | Mannesmann Sachs Ag | Multiple-clutch device |
| CN101432541A (en) * | 2006-04-26 | 2009-05-13 | 利滕斯汽车合伙公司 | One-way isolator for high torque devices |
Family Cites Families (4)
| 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 | ||
| JP3943950B2 (en) * | 2002-02-18 | 2007-07-11 | 株式会社エクセディ | Clutch cover assembly |
-
2009
- 2009-10-02 SE SE0950723A patent/SE534205C2/en unknown
-
2010
- 2010-09-28 WO PCT/SE2010/051037 patent/WO2011040869A1/en active Application Filing
- 2010-09-28 BR BR112012007287A patent/BR112012007287A2/en not_active IP Right Cessation
- 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 JP JP2012532047A patent/JP2013506784A/en active Pending
- 2010-09-28 RU RU2012117758/06A patent/RU2012117758A/en not_active Application Discontinuation
- 2010-09-28 KR KR1020127011466A patent/KR20120092620A/en not_active Application Discontinuation
- 2010-09-28 CN CN201080043970XA patent/CN102686847A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1997015759A1 (en) * | 1995-10-23 | 1997-05-01 | Lysholm Technologies Ab | Transmission including a two-part clutch arrangement |
| US5749451A (en) * | 1996-09-27 | 1998-05-12 | General Motors Corporation | Clutch assembly with a piston stroke adjuster |
| WO1998015748A1 (en) * | 1996-10-09 | 1998-04-16 | Lysholm Technologies Ab | Oil-cooled disc clutch |
| US6464059B1 (en) * | 1999-09-30 | 2002-10-15 | Mannesmann Sachs Ag | Multiple-clutch device |
| CN101432541A (en) * | 2006-04-26 | 2009-05-13 | 利滕斯汽车合伙公司 | One-way isolator for high torque devices |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106164517A (en) * | 2014-03-27 | 2016-11-23 | 舍弗勒技术股份两合公司 | Pressurized tank and metal platen as common component |
| US10167903B2 (en) | 2014-03-27 | 2019-01-01 | Schaeffler Technologies AG & Co. KG | Dual clutch |
| CN106164517B (en) * | 2014-03-27 | 2019-04-12 | 舍弗勒技术股份两合公司 | Pressurized tank and metal platen as common component |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2012117758A (en) | 2013-11-10 |
| AU2010301163A1 (en) | 2012-04-19 |
| EP2483541A1 (en) | 2012-08-08 |
| EP2483541A4 (en) | 2017-09-27 |
| JP2013506784A (en) | 2013-02-28 |
| SE0950723A1 (en) | 2011-04-03 |
| BR112012007287A2 (en) | 2016-04-19 |
| SE534205C2 (en) | 2011-05-31 |
| KR20120092620A (en) | 2012-08-21 |
| WO2011040869A1 (en) | 2011-04-07 |
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Application publication date: 20120919 |