CN203809109U - Supercharger connecting device - Google Patents
Supercharger connecting device Download PDFInfo
- Publication number
- CN203809109U CN203809109U CN201420134720.2U CN201420134720U CN203809109U CN 203809109 U CN203809109 U CN 203809109U CN 201420134720 U CN201420134720 U CN 201420134720U CN 203809109 U CN203809109 U CN 203809109U
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- China
- Prior art keywords
- output shaft
- timing gear
- clutch
- coupling arrangement
- tie
- 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 - Lifetime
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- 238000010168 coupling process Methods 0.000 claims abstract description 23
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- 229910000838 Al alloy Inorganic materials 0.000 claims description 2
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- 230000009347 mechanical transmission Effects 0.000 description 1
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Classifications
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- 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
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
- F02B33/38—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type of 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
- F04C18/126—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
- 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
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/122—Arrangements for supercharging the working space
-
- 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
- F02B39/04—Mechanical drives; Variable-gear-ratio drives
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
Abstract
The utility model provides a rotating part connecting device in a supercharger. The rotating part connecting device comprises a rotatable output shaft; the output shaft is provided with a conical male spline and an output shaft rotating axis. A coupling disc is provided with a disc rotating axis coaxial with the output shaft rotating axis, a conical female spline coaxial with the disc rotating axis so as to be joined with the conical male spline, and a plurality of disc holes formed in the coupling disc and parallel to the disc rotating axis. Each of a plurality of pins is provided with a disc end and a timing gear end far away from the disc end. The plurality of pins are coupled with the coupling disc at the disc ends of the pins by virtue of the coordination of a plurality of holes. A timing gear is fixed on a supercharger rotor and rotates along with the supercharger rotor. The timing gear is provided with a plurality of holes which are formed in the timing gear and matched and coupled with the timing gear ends of the plurality of pins.
Description
The cross reference of related application
The application is that it is incorporated by reference in their entirety to herein in the continuation-in-part application of the U.S. Patent Application Serial Number 12/856,121 of the common pending trial of submission on August 13rd, 2010.
Technical field
The utility model relates in general to pressurized machine clutch assembly and pressurized machine revolving part coupling arrangement.
Background technique
Pressurized machine can be used for increasing or " raisings " internal combustion (IC) thus the air pressure in the intake manifold of motor increases the horsepower of IC motor to be exported.Therefore, IC motor can have in the conventional air-breathing situation of ratio engine the stronger horsepower output capability that (for example,, during the aspirating stroke of piston, piston can be in air intake cylinder) occurs.Traditional pressurized machine is mainly to carry out mechanical type driving by motor, and therefore, when not needing and/or expect motor " supercharging ", pressurized machine can represent the consumption of engine horsepower.The pieceable clutch of selectivity for example can in series be arranged in, between pressurized machine input (bel-drivenn belt wheel) and supercharger rotor.Speed changer can in series be arranged between clutch and supercharger rotor.
Model utility content
Revolving part coupling arrangement in pressurized machine comprises rotatable output shaft, and this output shaft has taper external splines and output shaft spin axis.Tie-plate has the disc spins axis coaxial with output shaft spin axis, with disc spins axis coaxle to engage the inner splined hole of taper external splines and to be formed on a plurality of dishes hole that is parallel to disc spins axis in tie-plate.The timing gear end that a plurality of pins respectively have dish end and hold away from dish.Described a plurality of pin engages tie-plate at the dish end place of pin ordinatedly by described a plurality of holes.Timing gear are fixed on supercharger rotor with its rotation.Timing gear have a plurality of timing gear hole, and these holes are arranged in the timing gear end that engages in timing gear and ordinatedly described a plurality of pins.
Accompanying drawing explanation
With reference to following detailed description and accompanying drawing, the characteristics and advantages of an example of the present utility model will become apparent, and wherein, similar reference character is corresponding to similar, although component that may be not identical.For simplicity, having reference character or the feature of already described function above can or can not describe in other accompanying drawing of their appearance.
Fig. 1 is according to the sectional view of the pressurized machine of an example of the present utility model;
Fig. 2 is according to the sectional view of the clutch assembly of an example of the present utility model;
Fig. 3 is according to the perspective view of the clutch assembly that Fig. 2 paints of an example of the present utility model;
Fig. 4 is according to the perspective exploded view of clutch armature, clutch rotor and the clutch coil of the clutch assembly of an example of the present utility model;
Fig. 5 is according to the partial, exploded perspective view of the clutch assembly of an example of the present utility model;
Fig. 6 describes according to the sectional view of the pressurized machine joiner of an example of the present utility model;
Fig. 7 is the flow chart of describing according to method of the present utility model example;
Fig. 8 is according to the perspective view of tie-plate of the present utility model example;
Fig. 9 is the sectional view of an example of tie-plate shown in Fig. 8;
Figure 10 illustrates the amplification profile being arranged according to the interior involute splines in the inner splined hole in tie-plate of the present utility model example; With
Figure 11 shows the output shaft in an example of the present utility model.
Embodiment
The utility model relates in general to pressurized machine clutch assembly and pressurized machine revolving part coupling arrangement.
Clutch assembly 10 according to an example of the present utility model has been shown in Fig. 1.According to an example of the present utility model, clutch assembly 10 is configured to for pressurized machine 12.Pressurized machine 12 can be a part for the intake manifold assembly of motor (not shown).Motor can comprise a plurality of cylinders and be arranged in the reciprocating piston in each cylinder, form thus expandable firing chamber.Motor can comprise air inlet and exhaust manifold assembly, for guiding combustible fluid to enter and leave firing chamber via intake valve and exhaust valve respectively.
The pressurized machine 12 of intake manifold assembly can be any positive displacement pump, comprise U. S. Patent 5,078,583 and 5,893, shown in 355, with the root's blower pressurized machine of describing, these patents are that assignee of the present utility model has and their full content is incorporated by reference herein, but whether must be restricted to these.Pressurized machine 12 also can comprise the positive displacement pump of screw compressor or any other type.According to an example of the present utility model, pressurized machine 12 can comprise a plurality of (for example a pair of) rotor 14, each has a plurality of porose salient angles.These rotors can be arranged in the cylindrical chamber of a plurality of parallel lateral overlaps, and can be delivered to the engine crankshaft torque actuated on it by (for example,, by drivign belt).Pressurized machine 12 can comprise main casing 16, and it limits described a plurality of cylindrical chamber.Main casing 16 also can be called rotor housing.The mechanical transmission mechanism that comprises axle 18 of pressurized machine 12 can make rotor 14 rotate with the fixed ratio with respect to speed of crankshaft, thereby makes the discharge capacity of pressurized machine 12 be greater than engine displacement, makes thus the supercharging air in inflow engine firing chamber.Pressurized machine 12 can comprise and is configured to receive the entrance of fluid and be configured to pressurized air to guide into via outlet pipe the outlet of intake valve from suction tude or passage.Suction tude or passage and outlet pipe can pass through bypass via interconnects.Bypass valve can be arranged within bypass path and can be configured to move between open position and closed position by actuator assembly.
Pressurized machine 12 can be connected to clutch assembly 10 in any suitable manner.Pressurized machine 12 may further include input housing, and it is as the clutch housing 20 of clutch assembly 10.Clutch assembly 10 comprises clutch housing 20, axle 22, belt wheel 24, clutch rotor 26, clutch armature 28 and clutch coil 30.Clutch housing 20 can be configured to hold other parts of clutch assembly 10.Clutch housing 20 is less at the diameter at first end 32 places, larger at the diameter at the second end 34 places.First end 32 is belt wheel 24 immediately.The second end 34 is the main casing 16 of pressurized machine 12 immediately.
Axle 22 also can be called belt wheel transmission axle.Axle 22 can have longitudinal axis 36, and axle 22 can be around this axis rotation.Axle 22 can be bearing in clutch housing 20 by least one bearing 38.For example and without limitation, axle 22 can for example, be bearing in clutch housing 12 by a plurality of (a pair of) bearing 38,40.Bearing 38,40 can be arranged between clutch housing 20 and axle 22.Referring now to Fig. 2-3, totally show another example of clutch assembly 110.As overall, shown in Fig. 2-3, at least a portion of belt wheel 24 can be along circumferential hoop around at least one bearing 38.By belt wheel 24 is placed at least one bearing 38 directly over, another bearing 40 can be configured to the radial load that applied by belt wheel 22 of supporting.According to an example of the present utility model, each bearing 38,40 can comprise inner ring and outer ring.When clutch assembly 10,110 engages, between the inner ring of bearing 38,40 and outer ring, substantially do not have relative movement.
Referring now to Fig. 1-3 and 5, belt wheel 24 can be configured between the joint aging time of clutch assembly 10 from engine crankshaft (not shown) transmitting torque to axle 22.Belt wheel 24 can be connected to axle 22.According to an example of the present utility model, belt wheel 24 can be arranged in the outside of axle 22.Belt wheel 24 can be arranged in axle 22 one end and can be along circumferential threaded shaft 22.According to an example of the present utility model, belt wheel 24 can be arranged in the outside of clutch housing 20.Belt wheel 24 along the longitudinal axis 36 is axially spaced with clutch housing 20.According to an example of the present utility model, be arranged in immediately belt wheel 22 of at least one bearing 38 between clutch housing 20 and axle 22.Another bearing 40 can be arranged between clutch housing 20 and axle 22, the main casing 16 of more close pressurized machine 12.Belt wheel 24 can separate with other parts of clutch assembly 10 (not that is being, one).For example, belt wheel 24 can separate with clutch armature 28 (not that is being, one).
Belt wheel 24 can have the diameter irrelevant with the diameter of clutch rotor 26, clutch armature 28 and clutch coil 30.Belt wheel 24, in comprising its structure and being configured in, all irrelevant with the torque capacity of clutch rotor 26, clutch armature 28 and clutch coil 30.According to an example of the present utility model, according to a certain torque capacity of pressurized machine 12, the diameter of belt wheel 24 can be less than about 85mm.According to an example of the present utility model, the diameter of belt wheel 24 can be for about 45mm be to about 85mm.According to the diameter of belt wheel 24, belt wheel 24 can usually be regarded small pulley as.According to an example of the present utility model, belt wheel 24 can have the diameter less than the diameter of clutch coil 30, because according to an example of the present utility model, belt wheel 24 can not surround clutch coil 30.According to an example of the present utility model, belt wheel 24 can not made one with clutch rotor 26 yet.
Clutch rotor 26 can be configured to be magnetized and set up the magnetic loop that attracts clutch armature 28.According to an example of the present utility model, clutch rotor 26 can be connected to axle 22 and/or belt wheel 24.Clutch rotor 26 can be around longitudinal axis 36 rotations of axle 22.As common in small pulley structure, clutch rotor 26 is free of attachment to the axle 18 of pressurized machine.According to an example of the present utility model, clutch rotor 26 can consist of steel.Although at length mention steel as an example of the present utility model,, according to other example of the present utility model, clutch rotor 26 can consist of other material of any number.In an example of the present utility model, clutch rotor 26 can rotate with at least identical with belt wheel 24 rotating speed, and can be with the rotating speed rotation larger than the revolvable speed of clutch armature 28.According to an example of the present utility model, because clutch rotor 26 can be connected to axle 22 and/or belt wheel 24, so clutch rotor 26 can always maintain the rotating speed identical with belt wheel 24.In other words, even when clutch assembly 10 is disengaged, the rotating speed rotation that clutch rotor 26 also can be substantially the same with the rotating speed with axle 22.Clutch rotor 26 can be more stable conventionally under than the higher speed of clutch armature 28 time.Clutch rotor 26 can be arranged between clutch armature 28 and clutch coil 30 along the longitudinal axis 36 of axle 22.Clutch rotor 26 can have the first end face 42, and this edge face structure becomes at least partly around clutch coil 30.Clutch rotor 26 can have the second end face 44 (that is, contrary with the first end face 42), and this edge face structure becomes towards clutch armature 28.
Clutch armature 28 can be around longitudinal axis 36 rotations of axle 22.Clutch armature 28 can be configured to be drawn lean against on clutch rotor 26 and in contacting point and apply frictional force.Therefore load that can lifting clutch armature 28 is with the rotating speed of coupling clutch rotor 26.Clutch armature 28 can be arranged between clutch rotor 18 and pressurized machine 12 along the longitudinal axis 36 of axle 22.Clutch armature 28 can have the first end face 46, and this edge face structure becomes towards the second end face 44 of clutch rotor 26 and can comprise friction material.Clutch armature 28 can have the second end face 48 (that is, contrary with the first end face 44), and this edge face structure becomes towards pressurized machine 12.Clutch armature 28 can be connected to by spline and bolt the axle 18 of pressurized machine 12.According to an example of the present utility model, clutch armature 28 can comprise speed sensitive parts (for example friction material and spring).When clutch assembly 10,110 is disengaged, the rotating speed of clutch armature 28 can be less than the rotating speed of axle 22.Therefore, according to an example of the present utility model, when clutch assembly 10,110 is disengaged, clutch armature 28 can be configured to coast until stop, rather than must keep the rotating speed identical with belt wheel 24 always.According to an example of the present utility model, clutch armature 28 can be free of attachment to axle 22 and/or belt wheel 24.As an alternative, according to an example of the present utility model, clutch armature 28 can separate with belt wheel 24.Clutch armature 20 can be connected to the axle 18 of pressurized machine 12.Axle 18 can be called speedup input shaft 18.When clutch assembly 10,110 engages, the rotating speed of clutch armature 28 can be substantially identical with the rotating speed of axle 22.Because due to the speed sensitive material comprising as friction material, when fair speed, may more be difficult to keep the stability of clutch armature 28, clutch armature 28 can be free of attachment to axle 22 and/or belt wheel 24.Clutch armature 28 can separate with belt wheel 24, and therefore, clutch armature 28 can not affect size and/or the scope of belt wheel 24.By clutch armature 28 and belt wheel 24 are separated, can reduce the size of clutch housing 20 in belt wheel 24 peripheral regions.In addition, the size of belt wheel 24 and configuration can be irrelevant with size and/or the torque capacity of armature 28.
Clutch coil 30 can comprise flux source.Electric current and/or voltage can impose on clutch coil 30 with near generation magnetic field clutch coil 30 and produce the flux magnetic line of force.The intensity in magnetic field can be proportional with provided current level.Then magnetic flux can pass through the little working gas gap between clutch coil 30 and clutch rotor 26.Therefore clutch rotor 26 can become and be magnetized and set up magnetic loop to attract clutch armature 28.Then clutch armature 28 can be drawn and come on clutch rotor 26 and can apply frictional force in contacting point, and the load on clutch armature 28 can be promoted to the speed of coupling clutch rotor 26.When removing electric currents and/or voltage from clutch assembly 10,110, clutch armature 28 can be freely along with the axle 18 of pressurized machine 12 rotates.Clutch coil 30 can not surrounded by belt wheel 24.As an alternative, clutch coil 30 can be arranged in clutch rotor 26 and housing 16 that can more close pressurized machine 12.Clutch coil 30 can be arranged between clutch rotor 26 and clutch housing 20 along the direction of the longitudinal axis 36 of axle 22.Clutch coil 30 can be spaced apart with belt wheel 24 along the longitudinal axis 36 of axle 22.Clutch coil 30 can separate with belt wheel 24, and therefore, clutch coil 30 can not affect size and/or the scope of belt wheel 24.By clutch coil 30 and belt wheel 24 are separated, can reduce the size of clutch housing 20 in belt wheel 24 peripheral regions.In addition, the size of belt wheel 24 and configuration can be irrelevant with size and/or the torque capacity of clutch coil 30.
Clutch coil 30 can be controlled by electronic control unit (ECU) (not shown), and this electronic control unit (for example,, by electric wire 52) provides electrical signal to clutch coil 30.ECU can process input, and for example (but being not limited to), the sensor reading corresponding with vehicle parameter, and according to logic rules, process this and input to determine the suitable electrical signal that offers clutch coil 30.ECU can comprise microprocessor, and this microprocessor has for example, with the stored logic rule form of computer program (with) operation for solenoidoperated cluthes assembly 10,110 of enough internal memories.
According to an example of the present utility model, comprise that the pressurized machine 12 of clutch assembly 10,110 may further include the input overdrive gear 50 of the axle 18 that is connected to pressurized machine 12.Therefore, at least one in these rotors 14 of pressurized machine 12 can adopt input transmission configuration, comprise such as but not limited to, axle 18 and overdrive gear 50, by using these, pressurized machine 12 can receive input driving torque.According to an example of the present utility model, pressurized machine 12 can comprise clutch assembly 10,110; Housing 16; Be arranged in a plurality of rotors 14 in housing 16; Be configured to drive the axle 18 of the rotation of a plurality of rotors 14; And the input overdrive gear 50 that is connected to axle 18.Overdrive gear 50 and associated components are below more completely being described.
The example of revolving part coupling arrangement disclosed herein and method can provide to be corrected out-of-alignment advantage and can lower or substantially eliminate the backlash in pressurized machine.The example that it being understood that revolving part coupling arrangement disclosed herein and method can prevent the destruction to some types of bearing, and these destructions may occur between the erecting stage of some pressurized machines.
With further reference to Fig. 1, pressurized machine 12 comprises pressurized machine speed changer 54.Pressurized machine speed changer 54 comprises that input overdrive gear 50 and output overdrive gear 51 are to provide the velocity ratio from speedup input shaft 18 to output shaft 56.Belt wheel 24 drive belt wheel transmission axle 22 in pressurized machines 12 with transmitting torque to inputting overdrive gear 50.Belt wheel 24 can be driven by the engine crankshaft belt wheel (not shown) that is connected to belt wheel 24 with (not shown) via front end helper drive (FEAD).Clutch assembly 10 can be arranged between belt wheel transmission axle 22 and input overdrive gear 50 speedup input shaft 18 is optionally connected to input overdrive gear 50.Input overdrive gear 50 engages output overdrive gear 51 engagingly, and this output overdrive gear is fixed on output shaft 56 with rotation therewith.
Overdrive gear 50 and 51 velocity ratio provide the speed discrepancy between speedup input shaft 18 and output shaft 56.According to an example of the present utility model, the scope of operable velocity ratio is approximately 1: 1 to approximately 3: 1.For example,, if use the velocity ratio of 2: 1, so, when speedup input shaft 18 is with 1,000 rpm of (rpm) time rotational, rotor 14 can be with 2000rpm rotation, this is that this will below be explained in more detail because rotor 14 rotates with output shaft 56.
Output shaft 56 can be configured and is indirectly connected to transmission timing gear 58 by dumb bell shaft, and this will below describe in more detail.Transmission timing gear 58 engage transmission timing gear 60 engagingly.Transmission timing gear 58 are connected to rotor 14.Transmission timing gear 60 be connected to rotor 14 '.These timing gear 58,60 can comprise identical tooth number, spaced apart with relatively high tooth pitch.For example, timing gear 58,60 can respectively have intermeshing 30 teeth; Therefore, timing gear 58,60 are with substantially equal angular velocity rotation.Thereby timing gear 58,60 make rotor 14,14 ' synchronous substantially, facilitated thus rotor 14,14 ' low wear rate and the high efficiency of pressurized machine 12.
Dumb bell shaft used herein configuration is commonly referred to as has the axle that separated by least one parts and its energy source, and the transmission system energy flow with indirect connection configures.For example, in direct axle configuration, use an axle from input direct transmitting rotary power to output in the situation that, according to an example of the present utility model, dumb bell shaft configuration uses the auxiliary axis being connected in series with joiner to carry out transmitting rotary power.In the example of directly axle configuration, output shaft can directly be installed on supercharger rotor, and output shaft also will be as rotor shaft.
, also with reference to Fig. 6, obtain the more details of pressurized machine 12 now, revolving part coupling arrangement 62 comprises output shaft 56 and transmission timing gear 58, has operability with transmitting rotary power between them.Output shaft 56 has taper external splines 64 and output shaft spin axis 66.The tie-plate 68 of coupling arrangement 62 has the disc spins axis 70 coaxial with output shaft spin axis 66.Tie-plate 68 has the taper inner splined hole 72 coaxial with disc spins axis 70 to engage the taper external splines 64 of output shaft 56.Inner splined hole 72 is tapered along disc spins axis 70.
Fig. 8 is the perspective view illustrating according to tie-plate 68 of the present utility model example.Fig. 8 shows described a plurality of dishes hole 74 and has three holes 75.In other example, the number in the dish hole 75 in described a plurality of dishes hole 74 can be greater than 3 or be less than 3.
With reference to Fig. 9, further describe the taper inner splined hole 72 of tie-plate 68.Inner splined hole 72 has larger diameter end 88 and smaller diameter end 90.Tie-plate 68 can have the hub 79 forming around inner splined hole 72.As shown in Figure 9, hub 79 can extend beyond the end face 83 of tie-plate 68, in hub side 81, than a relative side, obviously exceeds more.Hub 79 can be the structure that is easy to detect (for example, vision is detectable, or, detectable by process mistake proofing (poke-yoke) technology) so that checking, when output shaft 56 is seated in tie-plate 68, the free end 86 (seeing Fig. 1) of output shaft 56 passes larger diameter end 88 towards smaller diameter end 90.Taper inner splined hole 72 has formation taper involute splines thereon for engaging the taper external splines 64 of output shaft 56.Taper external splines 64 is also involute splines.Taper external splines 64 engages the tooth flank of the taper involute splines of taper inner splined hole 72 in the mode of side engage.Because interior involute splines and outer involute splines are side engage, so these splines are determined and focused on the axis between output shaft 56 and tie-plate 68.The tapering of spline allows the interference fit between external splines in less power one-tenth in place for these splines, and output shaft 56 is located in tie-plate 68.
But each comfortable each sides of the taper external splines 64 of taper inner splined hole 72 and output shaft 56 respectively with respect to disc spins axis 70 and output shaft spin axis 66 into about 0.5 degree the taperings to approximately 2.5 degree, to realize the interference fit between output shaft 56 and inner splined hole 72.
Figure 10 is amplification profile, and the interior involute splines 73 of arranging in inner splined hole 72 is shown.
In an example of the present utility model, for the power that makes output shaft 56 be located in tie-plate 68, in approximately 5 newton, between approximately 44 newton, change.Be not bound by any theory, it is believed that, the tapering of spline allows to obtain the tight interference fit between spline in the situation that not measuring one's own ability greatly.This tight interference fit can stop the relative movement between output shaft 56 and tie-plate, prevents thus the backlash of the joint between output shaft 56 and tie-plate 68.
Tie-plate 68 comprises a plurality of dishes hole 74 parallel with disc spins axis 70 being formed in tie-plate 68.Although it being understood that one that in Fig. 2, only illustrates typically in this plurality of dishes hole 74,, as shown in Figure 8, these a plurality of dishes hole 74 drum spin axis 70 radial arrangement.
Tie-plate 68 can be formed by any suitable material.For the example of the material of tie-plate 68, comprise for example polyether-ether-ketone (PEEK) and comprise Steel Alloy and the metal of aluminum alloy of polymer.The example of suitable Steel Alloy is SAE (Society of Automotive Engineers)/AISI (AISI) 1144.
Coupling arrangement 62 comprises a plurality of pins 76 further, and each pin has dish end 78 and away from dish, holds 78 timing gear end 80.Described a plurality of pin 76 can hold 78 places along 74, to engage ordinatedly tie-plate 68 by a plurality of dishes hole at the dish of pin 76.It being understood that described a plurality of pin 76 can be formed from steel.Described a plurality of pin 76 can be three pins, and can be in the corresponding dish hole in described a plurality of dishes hole 74 along circular-mode substantially equi-spaced apart open.In addition, the diameter of described a plurality of pins 76 can change between about 10mm at about 6mm, and length scale can change between about 25mm at about 20mm.
Transmission timing gear 58 are fixed on rotor 14 with rotation therewith.Transmission timing gear 58 have timing gear spin axis 82 and a plurality of timing gear hole 84.Although it being understood that one that in Fig. 6, only illustrates typically in this plurality of timing gear hole 84,, described a plurality of timing gear hole 84 is around timing gear spin axis 82 radial arrangement.Described a plurality of pin 76 can engage transmission timing gear 58 by a plurality of timing gear hole 84 ordinatedly at timing gear end 80 places of pin 76.
In an example, coupling arrangement 62 can regulation output axle spin axis 66 and timing gear spin axis 82 between approximately 0.05mm (millimeter) to the parallel misalignment of about 0.1mm.Deviation between output shaft spin axis 66 and timing gear spin axis 82 by the adaptability of pressurized machine 12 rather than in counterpart fixedly tolerance clearance regulate.This has eliminated the backlash of the joint between output shaft 56 and tie-plate 68.Figure 11 shows according to the example of output shaft 56 of the present utility model.Show the taper external splines 64 at free end 86 places of output shaft 56.External splines 64 is tapers, thus the free end output shaft diameter 77 at free end 86 places ' be less than output shaft diameters that record in the splined end away from free end 86, that indicate with reference character 77.
With reference to Fig. 7, with flow process Figure 100, show an example of the manufacture method of pressurized machine 12.Frame 101 representatives are arranged in the method step in pressurized machine housing 11 by rotatable output shaft 56.Rotatable output shaft 56 can be supported by bearing.Rotatable output shaft 56 also can have external splines 64 and output shaft spin axis 66.Pressurized machine housing 11 can comprise a plurality of parts of pressurized machine 12, the supporting structure that it provides the outer surface of pressurized machine 12 and is formed for the inner member of pressurized machine 12.For example, pressurized machine housing 11 can comprise the housing parts for rotor assembly 27 and pressurized machine speed changer 54, and suitable joint, lid, mounting points, Sealing and fastening piece.
Frame 102 represents tie-plate 68 is pressed on output shaft 56.Tie-plate 68 can have the disc spins axis 70 coaxial with output shaft spin axis 66, to engage the inner splined hole 72 of external splines 64 and to be parallel to disc spins axis 70, be formed on a plurality of dishes hole 74 in dish 68 with disc spins axis 70 is coaxial.
At frame 103 places, the method is further included in the step of arranging the rotor assembly 27 that comprises rotor shaft 29 in pressurized machine housing 11.
At frame 104 places, the method is further included in the step of arranging timing gear 58 on rotor shaft 29, and these timing gear have timing gear spin axis 82 and are arranged in a plurality of timing gear hole 84 in timing gear 58.
At frame 105 places, the step that the method further comprises is by a plurality of pins 76, timing gear 58 to be connected on tie-plate 68.Described a plurality of pin 76 respectively has dish end 78 and away from dish, holds 78 timing gear end 80.This connection be by described a plurality of pins 76 and tie-plate 68 the dish of pin 76 hold 78 places by a plurality of dishes hole 74 engage ordinatedly and described a plurality of pin 76 and timing gear 58 at timing gear end 80 places of described a plurality of pins 76 by a plurality of timing gear hole 84 engage ordinatedly realize.
It is believed that, example of the present utility model allows, between erecting stage greatly to reduce the assembling that bearing damage possibility is realized to pressurized machine 12.Especially, in an example of the present utility model, the bearing of supporting output shaft 56 is still less subject to impression and damages, because the axial output shaft load between erecting stage is lower.
It being understood that in this article, term " connects/is connected/joint " and/or similar term, has wide in range definition to contain multiple different connection configuration and mounting technology.These configure and technology includes but not limited to, contacting directly between (1) parts and another parts, does not have intermediate member between them; Contacting between (2) parts and another parts, between them, there are one or more parts, as long as these parts of " being connected to " these another parts are to operate in some way contact these another parts (although having one or more optional features between them).
Describe and claimed example disclosed herein in, singulative " " and " being somebody's turn to do " comprise plural object, unless context is otherwise obviously really stipulated.
It being understood that scope provided herein comprises the scope of regulation and any numerical value or the subinterval within the scope of defined.For example, the about 6mm extremely scope of about 10mm should be construed to, and not only comprises that the about 6mm of the limit value of clearly enumerating, to about 10mm, also comprises independently numerical value, for example, 7mm, 8.2mm, 9.1mm etc., and subinterval, for example about 6mm is to about 7.5mm etc.In addition,, when using " approximately " to describe numerical value, this means the little variation (reaching +/-10%) of containing stated numerical value.
Although described a plurality of examples in detail,, it will be apparent for a person skilled in the art that disclosed example can retrofit.Therefore, aforementioned description will be thought unrestriced.
Claims (8)
1. the revolving part coupling arrangement in pressurized machine, is characterized in that, comprising:
Rotatable output shaft, it has taper external splines and output shaft spin axis;
Tie-plate, it has:
The disc spins axis coaxial with described output shaft spin axis;
With described disc spins axis coaxle to engage the taper inner splined hole of described taper external splines; With
Be formed on a plurality of dishes hole that is parallel to described disc spins axis in described tie-plate;
A plurality of pins, described in each, pin has dish end and away from the timing gear end of described dish end, described a plurality of pins engage with described tie-plate by described a plurality of dishes hole ordinatedly at the described dish end of described pin; With
Timing gear, it is fixed to supercharger rotor to rotate with it, and described timing gear have:
Timing gear spin axis; With
A plurality of timing gear hole, it is arranged in described timing gear and with the described timing gear end of described a plurality of pins and engages ordinatedly.
2. coupling arrangement as claimed in claim 1, is characterized in that, described tie-plate is constituted by aluminum alloy, Steel Alloy or polyether-ether-ketone (PEEK) or they.
3. coupling arrangement as claimed in claim 1, is characterized in that, described a plurality of pins consist of steel.
4. coupling arrangement as claimed in claim 1, it is characterized in that, the described taper external splines of described taper inner splined hole and described output shaft respectively with respect to described disc spins axis and described output shaft spin axis into about 0.5 degree to the taperings of approximately 2.5 degree to realize the interference fit between described output shaft and described splined hole.
5. coupling arrangement as claimed in claim 1, is characterized in that, for the power that makes described output shaft be located in described tie-plate, is that approximately 5 newton are to approximately 44 newton.
6. coupling arrangement as claimed in claim 1, is characterized in that, described taper inner splined hole has tapered side matching spline to connect with the described taper external splines with complementary splines profile.
7. coupling arrangement as claimed in claim 1, is characterized in that, the parallel misalignment of 0.05mm to about 0.1mm of having an appointment between described output shaft spin axis and described timing gear spin axis.
8. coupling arrangement as claimed in claim 1, is characterized in that, described a plurality of pins along circular array substantially equi-spaced apart open.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/768,656 | 2013-02-15 | ||
| US13/768,656 US9086012B2 (en) | 2010-08-13 | 2013-02-15 | Supercharger coupling |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203809109U true CN203809109U (en) | 2014-09-03 |
Family
ID=50112765
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420134720.2U Expired - Lifetime CN203809109U (en) | 2013-02-15 | 2014-02-14 | Supercharger connecting device |
| CN201410111339.9A Pending CN103993953A (en) | 2013-02-15 | 2014-02-14 | Supercharger coupling |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410111339.9A Pending CN103993953A (en) | 2013-02-15 | 2014-02-14 | Supercharger coupling |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP2767718B1 (en) |
| CN (2) | CN203809109U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103993953A (en) * | 2013-02-15 | 2014-08-20 | 伊顿公司 | Supercharger coupling |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112016006204T5 (en) | 2016-02-08 | 2018-09-27 | Eaton Intelligent Power Limited | COUPLING DAMPERS FOR CHARGERS FROM THE ELASTOMER SERIES |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4953517A (en) * | 1989-04-14 | 1990-09-04 | Eaton Corporation | Torsion damping mechanism for a supercharger |
| US5078583A (en) | 1990-05-25 | 1992-01-07 | Eaton Corporation | Inlet port opening for a roots-type blower |
| US5281116A (en) * | 1993-01-29 | 1994-01-25 | Eaton Corporation | Supercharger vent |
| US5893355A (en) | 1996-12-26 | 1999-04-13 | Eaton Corporation | Supercharger pulley isolator |
| CN201246400Y (en) * | 2008-07-24 | 2009-05-27 | 杭州星光机械有限公司 | Prick bottom spline shaft |
| CN201650449U (en) * | 2010-03-02 | 2010-11-24 | 中国重汽集团济南动力有限公司 | Diesel engine |
| US8464697B2 (en) * | 2010-08-13 | 2013-06-18 | Eaton Corporation | Integrated clutch supercharger |
| AU2011100997A4 (en) * | 2011-08-09 | 2011-11-17 | Hengdian Group Linix Motor Co., Ltd. | Transmission Structure Between Planet Carrier and Output Shaft |
| CN203809109U (en) * | 2013-02-15 | 2014-09-03 | 伊顿公司 | Supercharger connecting device |
-
2014
- 2014-02-14 CN CN201420134720.2U patent/CN203809109U/en not_active Expired - Lifetime
- 2014-02-14 CN CN201410111339.9A patent/CN103993953A/en active Pending
- 2014-02-14 EP EP14155147.3A patent/EP2767718B1/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103993953A (en) * | 2013-02-15 | 2014-08-20 | 伊顿公司 | Supercharger coupling |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2767718B1 (en) | 2018-04-11 |
| CN103993953A (en) | 2014-08-20 |
| EP2767718A1 (en) | 2014-08-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190627 Address after: Dublin, Ireland Patentee after: Eaton Intelligent Power Co.,Ltd. Address before: Ohio, USA Patentee before: Eaton Corp. |
|
| TR01 | Transfer of patent right | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140903 |
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| CX01 | Expiry of patent term |