CN103857908A - Pump with centralized spring forces - Google Patents
Pump with centralized spring forces Download PDFInfo
- Publication number
- CN103857908A CN103857908A CN201280048988.8A CN201280048988A CN103857908A CN 103857908 A CN103857908 A CN 103857908A CN 201280048988 A CN201280048988 A CN 201280048988A CN 103857908 A CN103857908 A CN 103857908A
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- China
- Prior art keywords
- tappet
- returnning spring
- piston head
- piston
- moment
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/025—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by a single piston
- F02M59/027—Unit-pumps, i.e. single piston and cylinder pump-units, e.g. for cooperating with a camshaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0413—Cams
Abstract
A pump including a tappet biased into contact with a camshaft by a return spring is provided. The pump includes a torque transfer reduction interface mechanically interposed between the return spring and the tappet. The torque transfer reduction interface is configured to prevent spring wind-up generated by compressing and expanding the return spring from being transferred to the tappet to prevent the torque from causing the tappet to rotate relative to the camshaft about an axis extending perpendicular to the rotational axis of the camshaft.
Description
Technical field
Relate generally to fluid pumping apparatus of the present invention, and relate more specifically to the fluid pumping apparatus that one comprises the Returnning spring that keeps the contact between roller and tappet (roller and tappet) assembly, this roller and tappet assembly are followed (follow) camshaft with respect to pump barrel (pumping barrel) driven plunger, thus pumping fluid.
Background technique
Rail pump is used to especially fuel of motor pumping fluid altogether.Pump comprises the camshaft with roller tappet.Roller tappet is retained as the salient angle (lobe) against camshaft, so that the rotational motion of camshaft is converted into straight line motion, so that with respect to pump barrel rising (lift) pumping piston.The loopy moving of piston in pump barrel makes pressurized with fluid with pumping fluid.
Returnning spring is used for towards camshaft bias voltage roller tappet.When the salient angle that rotates to camshaft when camshaft has the position of little radius, roller tappet is pushed back beginning (start) position with respect to camshaft by Returnning spring, for rotation next time and the pumping campaign of camshaft are prepared.
In some pumps, Returnning spring is helical spring (coil spring), and it extends around piston and between pump barrel and tappet.Unfortunately, compressed and while stretching during reciprocal pump action when helical spring, small size rotation is attempted in helical spring end, and this is known as elasticity and rolls (wind up).In many application, this is not that problem or spring end will utilize limited kinetic force of friction coordinating slip on (mate) surface.But if can not suitably slide in the end of spring on matching surface, moment of torsion applies on the surface that (impart) press in helical spring end.This makes pumping environment existing problems.
In pump, but helical spring rolls while attempting to rotate because of elasticity, and consequent moment of torsion is passed (transfer) to roller tappet, causes roller tappet to rotate around pumping axis (piston moves back and forth along it).This causes roller displacement (shift), so that the spin axis of roller is no longer parallel to the spin axis of camshaft.In the mutual angled situation of axis, roller can not advance in correct path (true path) on camshaft (run).This cause roller in tappet along spin axis axial motion.The axial motion of roller cause the axial end of roller rub vertically (rub) be formed on the end retainer (end stop) in tappet, produce less desirable wearing and tearing.
The present invention relates to improvements over the prior art, this improvement is substantially eliminated or is reduced elasticity and rolls the moment of torsion of generation and be delivered to tappet.
Summary of the invention
Embodiments of the invention prevent that helical spring elasticity from rolling to the tappet of pump and apply moment of torsion, and this moment of torsion can cause tappet not line up with corresponding rotating cam.
In a specific embodiment, provide a kind of and comprise that tappet, roller, pump barrel, piston, Returnning spring and moment of torsion transmission reduce the pump at interface.Roller is rotatably carried by tappet.Pump barrel limits pumping chamber.Piston is carried in pumping chamber slidably, for along pumping axial-movement.Piston is operationally connected to tappet, for moving substantially synergistically along pumping axis and tappet.Returnning spring operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet.The axial bias power of described Returnning spring is not mechanically delivered to tappet by piston.Returnning spring is cardinal principle tubulose, and it has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis.Moment of torsion transmission reduces interface to be provided by the first and second axial abutment surface at least in part, and when Returnning spring is during in compressive state, the first and second surfaces limit contact area betwixt.Described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, arrives tappet so that the compressive force that Returnning spring produces reduces interface by moment of torsion transmission.Contact area between the first and second surfaces has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring.
In one embodiment, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, is operationally delivered to tappet to make its axial compressive force away from pump barrel reduce interface from Returnning spring by moment of torsion transmission along pumping axis bias voltage tappet.
In one embodiment, at least one in described first surface and second surface is convex surface.At one, more specifically in embodiment, the convex surface in described first surface and described second surface is spherical bending substantially.
In one embodiment, the contact area that described moment of torsion transmission reduces interface is configured in the time that Maximum Torque is created in the Returnning spring side that moment of torsion transmission reduces interface, allows sliding aspect angle around the spin axis that is basically parallel to pumping axis between described first surface and second surface.Described Maximum Torque is to reduce in the non-existent situation in interface even as big as making tappet carry out the moment of torsion of angle rotation with respect to pump barrel in moment of torsion transmission.。
Another embodiment comprises and the latch plate of the far-end axial engagement of Returnning spring, and the far-end of described Returnning spring rotates freely around pumping axis with respect to tappet.The load button of one in first surface and the second surface that provides moment of torsion transmission to reduce interface is also provided embodiment.Described load button is mechanically placed between latch plate and tappet, and the axial compressive force being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button.
At one, more specifically in embodiment, described load button freely carries out angle rotation around pumping axis with respect to tappet.
At one, more specifically in embodiment, described Returnning spring and latch plate directly do not press tappet vertically.This contributes to reduce the moment of torsion transmission between tappet and Returnning spring or latch plate.
In one embodiment, described piston has piston head, and latch plate comprises the piston head butt flange around piston receiver mouth.Piston extends past vertically piston receiver mouth and piston head is axially placed in and constrains between piston head butt flange and load button.
At one, more specifically in embodiment, described latch plate comprises: the spring butt flange extending radially outwardly, and it has the upper surface in the face of pump barrel, this upper surface of far-end against of Returnning spring; The first lower surface, it is provided by piston head butt flange and deviates from vertically pump barrel, and piston head is against the first lower surface; And second lower surface, it deviates from pump barrel vertically, and and described the first lower surface and described upper surface separates vertically and between described the first lower surface and described upper surface, described the second lower surface engages with load button vertically.
In one embodiment, described latch plate is axially fixed to tappet, and described Returnning spring is helical spring.
An embodiment further comprises the piston head cavity being formed on vertically between load button and piston head butt flange, and piston head is accommodated in piston head cavity.Described piston head cavity has axial dimension, and described axial dimension is configured to make piston head between piston head butt flange and load button, to carry out vertically limited axial motion.In the time that Returnning spring is compressed, piston head is by against load button, and in the time that Returnning spring stretches (extending), piston head will engage with piston head butt flange.This will prevent that piston head is clamped, clamped especially vertically.Clamping piston head can stop piston rotatablely moving and existing the piston producing in piston cylinder small not lining up may bound problem in system with respect to pumping axis undesirably.In addition, reduced the possibility that loads piston due to the little lateral movement of tappet along undesirable lateral/radial direction.
In one embodiment, described piston head has the axial end surface that deviates from vertically pump barrel.In the compressed situation of Returnning spring when the axial end surface upper surface of against load button vertically of piston head described in tappet is in the time that pump barrel is advanced.Preferably, at least one in the axial end surface of piston head and the upper surface of load button is convex surface.Convex shape contributes to make the loading of Returnning spring in center.
In one embodiment, the maximum radius size of described contact area be less than Returnning spring least radius size 25%.
In one embodiment, the direct butt tappet of described load button vertically facing to the abutment surface of pump barrel.Moment of torsion transmission reduces interface and is positioned to vertically compare the more close pump barrel of far-end of Returnning spring.The abutment surface of tappet is formed the far-end of axially extended projection.At least a portion of latch plate is around at least a portion of described axially extended projection.
Another embodiment of pump comprises that tappet, roller, pump barrel, piston, Returnning spring, latch plate, load button and moment of torsion transmission reduce interface.Roller is rotatably carried by tappet.Pump barrel limits pumping chamber.Piston is carried in pumping chamber slidably, for along pumping axial-movement.Described piston is operationally connected to tappet, for moving substantially synergistically along pumping axis and tappet.Described piston has piston head.
Returnning spring operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet.The axial bias power of described Returnning spring is not mechanically delivered to tappet by piston.Returnning spring is cardinal principle tubulose, and described Returnning spring has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis.
Latch plate operationally engages vertically with the far-end of Returnning spring.Piston extends past the piston ports in latch plate, and piston head is placed between tappet and latch plate vertically.Piston head is greater than piston ports.Latch plate is mechanically operationally fixed to tappet, for along pumping axis in the contrary direction of circulation with tappet axial motion substantially synergistically.
Load button is axially placed between tappet and piston head.Described load button is mechanically placed between latch plate and tappet, and the axial compressive force that can be operatively delivered to tappet being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button.
Moment of torsion transmission reduces interface to be provided by first surface and second surface at least in part, when Returnning spring is during in compressive state, and axially butt be limited to contact area therebetween of described first surface and second surface.Described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet.Contact area between the first and second surfaces has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring.Load button provides in first surface that moment of torsion transmission reduces interface and second surface.
In one embodiment, described latch plate comprises the piston head butt flange around piston ports.The size of piston ports can be formed as making piston to can't help latch plate or locate closely/radial clamping of tappet.Piston head is axially placed in and is constrained between piston head butt flange and load button.Piston head cavity is formed between load button and piston head butt flange vertically, and piston head is accommodated in piston head cavity.The axial dimension of described piston head cavity, less times greater than the axial dimension of piston head, is configured to provide piston head between piston head butt flange and load button, to carry out vertically limited axial motion so that piston head cavity has.This size prevents axial grip piston head.Described piston head has the axial end surface that deviates from vertically pump barrel.In the compressed situation of Returnning spring when the axial end surface upper surface of against load button vertically of piston head described in tappet is in the time that pump barrel is advanced.At least one in the axial end surface of piston head and the upper surface of load button is convex surface.When tappet deviates from pump barrel while advancing along pumping axis, piston head is against piston head butt flange vertically.By preventing axially or radial clamping/positioning piston closely, especially piston head, reduce the possibility that loads piston due to the little lateral movement of tappet along undesirable lateral/radial direction.
In another embodiment, provide a kind of and comprise that rotating cam axle, tappet, roller, pump barrel, piston, Returnning spring, latch plate and moment of torsion transmission reduce the pump at interface.
Rotating cam axle is configured to around the rotation of camshaft spin axis, and described rotating cam axle comprises at least one cam lobe.
Roller is carried by tappet to rotate and follow cam lobe.Tappet and roller are converted into the straight-line displacement of tappet along pumping axis by camshaft around rotatablely moving of camshaft spin axis.
Pump barrel limits pumping chamber.Piston is carried in pumping chamber slidably, for the rotation because of camshaft along pumping axial-movement.Described piston is operationally connected to tappet, for moving substantially synergistically along pumping axis and tappet.
Returnning spring operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet.The axial bias power of described Returnning spring is not mechanically delivered to tappet by piston.
Moment of torsion transmission reduces interface to be provided by first surface and second surface at least in part, when Returnning spring is during in compressive state, and axially butt be limited to contact area therebetween of described first surface and second surface.Described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet.The contact area that moment of torsion transmission reduces interface is configured in the time that minimal torque appears in the Returnning spring side that moment of torsion transmission reduces interface, allow sliding aspect angle around the spin axis that is basically parallel to pumping axis between described first surface and second surface, instead of minimal torque is delivered to tappet so that tappet rotates with respect to camshaft around the axis that is basically parallel to pumping axis.
At one more specifically in embodiment, described Returnning spring is cardinal principle tubulose, described Returnning spring has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis, and contact area between described first surface and second surface has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring.
In one embodiment, described minimal torque be at least even as big as make tappet with respect to camshaft around moment of torsion that substantially axis perpendicular to the spin axis of camshaft carries out angle rotation.
In one embodiment, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, to make it away from pump barrel and reduce interface from Returnning spring by moment of torsion transmission towards the axial compressive force of camshaft to be operationally delivered to tappet along pumping axis bias voltage tappet.
In one embodiment, at least one in described first surface and second surface is convex surface.
In one embodiment, the convex surface in described first surface and described second surface is spherical bending substantially.
In one embodiment, the far-end axial engagement of latch plate and Returnning spring.In addition, load button provides in first surface that moment of torsion transmission reduces interface and second surface.Described load button is mechanically placed between latch plate and tappet, and the axial compressive force that is operationally delivered to tappet being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button.
When by reference to the accompanying drawings, according to detailed description below, other features of the present invention, object and advantage will become more apparent.
Brief description of the drawings
The accompanying drawing that is included in specification and form a part for specification illustrates some aspects of the present invention, together with the description for explaining principle of the present invention.In the accompanying drawings:
Fig. 1 is the phantom of pumping installations according to an embodiment of the invention; And
Fig. 2 is the phantom that the moment of torsion transmission of the pump of Fig. 1 reduces the amplification at interface (interface).
Although will describe the present invention with respect to certain preferred embodiment, do not expect the present invention to be limited to those embodiments.On the contrary, the invention is intended to contain all replacement schemes, amendment and the equivalent that are included in the spirit and scope of the present invention as defined by the appended claims.
Embodiment
Fig. 1 is the phantom of the simplification of pump 100 according to an embodiment of the invention.Pump 100 is for by making pressurized with fluid carry out pumping fluid.Pump 100 comprises entrance 102 and outlet 104.The fluid entering by entrance 102 is pressurized, is then pumped out from exporting 104.
In order to carry out pumping operation, pump comprises around camshaft axis 108 and rotating with driven plunger 110 along the reciprocating camshaft 106 of pumping axis 112.The to-and-fro motion of piston 110 causes fluid pressurized and be pumped by pump 100.
Piston 110 is carried in the pumping chamber 128 in the pump barrel 130 that is formed on pump 100 slidably.Pumping chamber 128 and entrance 102 and outlet 104 fluids are communicated with, so that the axial motion of piston 110 in pumping chamber 128 operationally causes fluid pressurized and be pumped out from exporting 104.
Piston 110 is operationally connected to tappet 118, to move substantially synergistically along pumping axis 112 and tappet 118.Therefore, when camshaft 106 rotates and forces tappet 118 along pumping axis 112 during towards pump barrel 130 axial motion, piston 110 together with tappet 118 along the advance displacement of (travel) basic identical amount of essentially identical direction.
Returnning spring 132(is also known as " helical spring 132 " at this) operationally between pump barrel 130 and tappet 118, make it away from pump barrel 130 with axial bias tappet 118.The biasing force producing when Returnning spring 132 is compressed is for making tappet 118 to returning with respect to the initial position of camshaft 106.The initial position of camshaft 106 is positions that salient angle 116 has its least radius.In other words, Returnning spring 132 forces tappet 118 to move to camshaft 106, to keep the radially butt contact between the outer surface of roller 120 and the outer surface of salient angle 116.
Preferably, piston 110 connects with operating of tappet 118 and makes the axial bias power of Returnning spring 132 can mechanically not be delivered to tappet 118 by piston 110.In other words the tappet 118 that forces producing when, Compress Spring 132 is compressed is passed to when tappet 118 contacts with camshaft 106 with maintenance roller 120 and does not shift by piston 110 at them away from the axial bias power of pump barrel 130.
Returnning spring 132 in illustrated embodiment is cardinal principle tubular coil spring.Tubular coil spring centers substantially on pumping axis 112.
As indicated in background technique part, in the time of helical spring (such as the helical spring using in the present invention) compression and stretching, extension, the end of spiral is wanted to extend or shorten.This motion of spring can apply moment of torsion to the surface of spring effect.Therefore may be, just disadvantageous if this power is applied to tappet 118, because power can be around the axis generation moment of torsion that is in substantially parallel relationship to pumping axis 112 in tappet 118 for this reason.This moment of torsion can cause tappet 118 around pumping axis 112 or the axis that is parallel to pumping axis 112, angle rotation to occur with respect to camshaft 106, so that pin axis 124 and camshaft axis 108 are no longer substantially parallel to each other.In addition, this layout can cause roller 120 to be subject to along the axial force of pin axis 124 directions, so as the end face axial of roller 120 be forced to enter axial stop 126, cause the end face of roller 120 to form sizable friction and wear.
The pump 100 of embodiment shown in Fig. 1 comprises that moment of torsion transmission reduces interface 134, and it significantly reduces because helical spring this feature (being indicated as being elasticity above rolls) moment of torsion producing is passed to the ability of tappet 118.Moment of torsion transmission reduces interface 134 and is configured to allow to roll by elasticity cause exercisable between helical spring 132 and tappet 118 and relatively moves.Therefore, any moment of torsion of generation can not led no longer parallel with camshaft axis 108 tappet 118 of pin axis 124 is rotated.
Provide at least in part the moment of torsion transmission of illustrated embodiment to reduce interface 134 by the upper surface 140 of the lower surface 136 of load button 138 and a part for tappet 118.When Returnning spring 132 is during in compressive state, these axial butts in surface 136,140, limit contact area 142 betwixt.This moment of torsion transmission reduce interface 134 operationally machinery be placed between Returnning spring 132 and tappet 118.Therefore, the axial compressive force of Returnning spring 132 is operationally delivered to tappet 118 from Returnning spring 132 by this contact area (substantially being illustrated by arrow 142) vertically.
The use that this moment of torsion transmission reduces interface 134 has changed because the elasticity of Returnning spring 132 is rolled the power pattern processed with respect to tappet 118 producing.First, because elasticity is rolled any moment of torsion that is applied to tappet 118 and is acted directly on the far-end 148 than Returnning spring 132 radius significantly reducing on the surface of tappet 118 and be passed to tappet 118.The embodiment of some prior aries adopts latch plate, and this latch plate is for example placed in, between coil spring and the tappet of joint piston crown (see latch plate 144, it is not the latch plate of prior art but shows interaction).But, in the embodiment of prior art, the spring butt flange extending radially outwardly of end bias voltage of spring of being reset (is for example shown in the flange 146 of the present embodiment, flange 146 is different from the structure of prior art) will directly axially press tappet (different with the flange 146 of the present embodiment, flange 146 and the tappet of the present embodiment separate vertically).In this configuration, elasticity is rolled and will be acted on tappet with Radius by latch plate, and this radius substantially equals Returnning spring and acts directly on the radius on tappet.
Another kind of prior art design is to press latch plate, and latch plate is pressed piston head and piston head is pressed into tappet and is directly contacted.Therefore,, in this arranges, piston head is clamped against tappet vertically.Piston can cause loading undesirably piston due to the little lateral movement of tappet along undesirable lateral/radial direction with respect to this clamping of tappet.
In addition, moment of torsion transmission reduces interface 134, and its contact area 142 has especially been configured to reduce moment of torsion and can be passed to the surface area of tappet 118 by it.By reducing size and the maximum radius of contact area 142 with respect to pumping axis 112, moment of torsion transmission reduces interface 134 and starts to be similar to a contact.Therefore the spin friction, overcoming between two surfaces 136,140 by very little moment of torsion engages.Therefore,, in the time that moment of torsion is rolled caused power generation by the elasticity of Returnning spring 132, allow two surfaces 136,140 relative to each other to carry out angle rotation along pumping axis 112, instead of cause moment of torsion to be delivered to tappet 118.
In addition, contact area 142, especially its radius between two surfaces 136,140, preferably change no-radius into or approach no-radius.Therefore, produce and normally act on surface 136,140 spin friction power by being that zero torque arm works substantially.This has significantly reduced to be delivered to the torque capacity of tappet 118, because moment of torsion is directly proportional to the torque arm of the frictional force being applied in.
With reference to Fig. 2, Fig. 2 is the enlarged view that moment of torsion transmission reduces interface 134 in addition, and the lower surface 136 of load button 138 is spherical bendings substantially.The upper surface 140 that the transmission of formation moment of torsion reduces the tappet 118 of the another part at interface 134 is substantitally planars.Therefore, the approximate some contact in the time of their axial butts of the contact area 142 between these two surfaces 136,140.But due to some distortion, contact area 142 is less times greater than a contact.As mentioned above, this causes the radius of contact area 142 to approach zero.The spherical curved surface profile of lower surface 136 has also been guaranteed center loaded.
Although it is spherical bending that lower surface 136 is shown as, in alternate embodiment, upper surface 140 can be spherical curved surface extraly or alternatively.In addition, alternate embodiment can be used the surface except spherical curved surface.For example, surface can be taper shape or the only removed truncated cone shape of fraction of cone tip substantially.Equally, target is to reduce contact area, especially the size of the maximum radius of contact area.
As mentioned above, moment of torsion transmission reduces interface 134 and has significantly reduced torque arm, because elasticity is rolled any power producing and is delivered to tappet 118 by torque arm.For example, in the prior art design of the direct against tappet of helical spring, torque arm is at least equally large with respect to the inside radius R1 of pumping axis 112 with helical spring 132, and inside radius R1 is also known as the smallest radial size in week in helical spring.Similarly, in the embodiment of the spring butt flange extending radially outwardly with direct compression tappet, torque arm at least with the spring butt flange extending radially outwardly (its with respect to its pumping axis vertically with tappet butt) the inside radius of a part equally large.But the new torque arm of utilizing moment of torsion transmission to reduce interface 134 is at most the size of the maximum radius of contact area 142.This maximum radius size is significantly less than the least radius size R1 of Returnning spring 132 and approaches as described above zero.
Interface between load button 138 and tappet 118 makes load button rotate with respect to the free ditch of tappet 118 around pumping axis 112.In other words, unique resistance of the rotation between two parts is the frictional force producing therebetween.
The contact area 142 that moment of torsion transmission reduces interface 134 is configured to reduce moment of torsion that the Returnning spring side at interface produces when maximum when moment of torsion transmission, allows two surfaces around pumping axis 112 in slip aspect angle.Maximum Torque is to reduce the moment of torsion even as big as making tappet 118 carry out angle rotation with respect to pump barrel 130 in the non-existent situation in interface 134 in moment of torsion transmission.In other words, Maximum Torque is to be enough to make tappet 118 to overcome the internal force between camshaft 106 and tappet gear 114, thus the moment of torsion that tappet 118 is rotated with respect to camshaft 106.
In one embodiment, the overall dimensions of contact area 142 is less than 75% of least radius R1, is more preferably 50%, is more preferably 25%.
Because latch plate 144 is with respect to the specific arrangements of load button 138 and tappet 118, make its axial compressive force away from pump barrel 130 operationally not be delivered to tappet by piston 110 for bias voltage tappet 118.In view of the following fact, this is especially correct, that is, the axial dimension of piston head 158 is less than the axial dimension of piston head cavity 170, to allow carrying out limited axial displacement between load button 138 and piston head butt flange 152.
When camshaft 106 makes upwards driven plunger 110 while causing pump action of tappet gear 114, the power that is delivered to piston 110 is transmitted by load button 138.In a preferred embodiment, the lower surface 174 of piston head 158 is spherical bendings, and the upper surface 168 of load button 138 is substantitally planars.Equally, this pass ties up to contact is substantially provided between two contact surfaces 168,174.When tappet 118 is in the time that pump barrel is advanced, this layout allows to make piston 110 center loaded.Should be noted that these spherical curved surfaces 174 and 136 are nonreentrant surfaces.This configuration allows to contact with matching surface point.
Except frictional force, latch plate 144, piston 110, tappet 118 and load button 138 are with respect to pumping axis 112 or axis whole 360 ° within the scope of the freely relative to each other rotation parallel with pumping axis 112.Therefore,, except friction, do not have mechanical structure that moment of torsion is delivered to the angular motion between tappet 118 or restraining spring plate and tappet from latch plate 144.
In the embodiment shown, the upper surface 140 of tappet 118 is formed on the axially extended projection 178 of tappet 118, the axial butt upper surface 140 of load button 138.The spring butt flange 146 extending radially outwardly separates with a part for axially extended projection (landportion) 178 radially outwardly and surrounds this part.Therefore, moment of torsion transmission reduces between far-end 148 and pump barrel 130 that interface is axially placed in Returnning spring 132.
In the embodiment shown, latch plate 144 and Returnning spring 132 directly axially do not press tappet 118.This configuration reduces interface 134 guiding by moment of torsion transmission and is applied to the axial compressive force of the Returnning spring 132 on tappet 118, instead of directly guides described axial compressive force from the spring butt flange 146 extending radially outwardly of Returnning spring 132 or annular.
All reference materials, comprise publication, patent application and the patent of quoting herein, are incorporated herein by reference, and the degree of quoting is that each reference material is merged separately and particularly by reference and its full content is stated.
In the time that description is of the present invention (while especially describing following claim), represent that term " " and the similar terms of english article is interpreted as comprising odd number and plural number, unless be otherwise noted or obvious and contradicted by context herein.Term " comprises ", " having " and " containing " is interpreted as open-ended term (that is, representing " including but not limited to "), unless otherwise noted.The number range of enumerating herein is only intended to as relating separately to the simple method of the each independent numerical value in the scope of dropping on, and unless otherwise indicated herein, and each independent numerical value is incorporated in specification, is set forth in individually herein as it.Can carry out all methods described herein with any suitable order, unless be otherwise noted or obvious and contradicted by context herein.For example, use to any and all examples or exemplary language (, " such as ") provided herein is only intended to illustrate better the present invention and does not limit the scope of the invention, unless otherwise stated.Any language in specification should not be interpreted as indicating any element of not advocating be put into practice essential to the invention.
Describe the preferred embodiments of the present invention here, comprised best mode known to the inventors for carrying out the invention.By reading above description, for a person skilled in the art apparent of the modification of those preferred embodiments.Inventor wishes that technician can suitably adopt this class modification, and inventor expects to be different from here other modes that describe in detail and puts into practice the present invention.Therefore, the institute that the present invention includes the theme of recording in claims changes and equivalent, as applicable law allows.In addition, any combination that the present invention comprises said elements (with its all possible variations), unless be here otherwise noted or obvious and contradicted by context.
Claims (24)
1. a pump, comprising:
Tappet;
The roller being carried revolvably by tappet;
Limit the pump barrel in pumping chamber;
Piston, it is carried in pumping chamber slidably, and for along pumping axial-movement, described piston is operationally connected to tappet, for moving substantially synergistically along pumping axis and tappet;
Returnning spring, it operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet, the axial bias power of described Returnning spring is not mechanically delivered to tappet by piston, Returnning spring is cardinal principle tubulose, and described Returnning spring has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis; And
Moment of torsion transmission reduces interface, it is provided by first surface and second surface at least in part, when Returnning spring is during in compressive state, axially butt be limited to contact area therebetween of described first surface and second surface, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, and the contact area between described first surface and second surface has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring.
2. pump according to claim 1, wherein, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, is operationally delivered to tappet to make its axial compressive force away from pump barrel reduce interface from Returnning spring by moment of torsion transmission along pumping axis bias voltage tappet.
3. pump according to claim 1, wherein, at least one in described first surface and second surface is convex surface.
4. pump according to claim 3, wherein, the convex surface in described first surface and described second surface is spherical bending substantially.
5. pump according to claim 1, wherein, the contact area that described moment of torsion transmission reduces interface is configured in the time that Maximum Torque is created in the Returnning spring side that moment of torsion transmission reduces interface, allow sliding aspect angle around the spin axis that is basically parallel to pumping axis between described first surface and second surface, described Maximum Torque is to reduce in the non-existent situation in interface even as big as making tappet carry out the moment of torsion of angle rotation with respect to pump barrel in moment of torsion transmission.
6. pump according to claim 1, further comprises:
Latch plate, the far-end axial engagement of itself and Returnning spring, the far-end of described Returnning spring rotates freely around pumping axis with respect to tappet;
Load button, it provides in first surface that moment of torsion transmission reduces interface and second surface, described load button is mechanically placed between latch plate and tappet, and the axial compressive force being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button.
7. pump according to claim 6, wherein, described load button freely carries out angle rotation around pumping axis with respect to tappet.
8. pump according to claim 6, wherein, described Returnning spring and latch plate directly do not press tappet vertically.
9. pump according to claim 6, wherein, described piston has piston head, and described latch plate comprises the piston head butt flange around piston receiver mouth, piston extends past vertically piston receiver mouth and piston head is axially placed in and constrains between piston head butt flange and load button.
10. pump according to claim 9, wherein, described latch plate comprises:
The spring butt flange extending radially outwardly, it has the upper surface in the face of pump barrel, this upper surface of far-end against of Returnning spring;
The first lower surface, it is provided by piston head butt flange and deviates from vertically pump barrel, and piston head is against the first lower surface; And
The second lower surface, it deviates from pump barrel vertically, and and described the first lower surface and described upper surface separates vertically and between described the first lower surface and described upper surface, described the second lower surface engages with load button vertically.
11. pumps according to claim 10, wherein, described latch plate is axially fixed to tappet, and described Returnning spring is helical spring.
12. pumps according to claim 10, further comprise the piston head cavity being formed on vertically between load button and piston head butt flange, piston head is accommodated in piston head cavity, described piston head cavity has axial dimension, and described axial dimension is configured to make piston head between piston head butt flange and load button, to carry out vertically limited axial motion.
13. pumps according to claim 12, wherein, described piston head has the axial end surface that deviates from vertically pump barrel, in the compressed situation of Returnning spring, when the axial end surface upper surface of against load button vertically of piston head described in tappet is in the time that pump barrel is advanced, at least one in the axial end surface of piston head and the upper surface of load button is convex surface.
14. pumps according to claim 1, wherein, the maximum radius size of described contact area be less than Returnning spring least radius size 25%.
15. pumps according to claim 6, wherein, the abutment surface of facing vertically pump barrel of the direct butt tappet of described load button, moment of torsion transmission reduces interface and is positioned to vertically compare the more close pump barrel of far-end of Returnning spring, the abutment surface of tappet is formed the far-end of axially extended projection, and at least a portion of latch plate is around at least a portion of described axially extended projection.
16. 1 kinds of pumps, comprising:
Tappet;
The roller rotatably being carried by tappet;
Limit the pump barrel in pumping chamber;
Piston, it is carried in pumping chamber slidably, and for along pumping axial-movement, described piston is operationally connected to tappet, and for moving substantially synergistically along pumping axis and tappet, described piston has piston head;
Returnning spring, it operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet, the axial bias power of described Returnning spring is not mechanically delivered to tappet by piston, Returnning spring is cardinal principle tubulose, and described Returnning spring has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis; And
Latch plate, the far-end axial engagement of itself and Returnning spring, piston extends past the piston ports in latch plate, and piston head is placed between tappet and latch plate vertically, piston head is greater than piston ports, and latch plate is mechanically secured to tappet to carry out substantially synergistically axial motion with tappet in the opposite direction along pumping axis;
Load button, it is axially placed between tappet and piston head, described load button is mechanically placed between latch plate and tappet, and the axial compressive force being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button; And
Moment of torsion transmission reduces interface, it is provided by first surface and second surface at least in part, when Returnning spring is during in compressive state, axially butt be limited to contact area therebetween of described first surface and second surface, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, contact area between described first surface and second surface has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring, and load button provides in first surface that moment of torsion transmission reduces interface and second surface.
17. pumps according to claim 16, wherein, described latch plate comprises the piston head butt flange around piston ports, piston head is axially placed in and is constrained between piston head butt flange and load button; And
Piston head cavity is formed between load button and piston head butt flange vertically, piston head is accommodated in piston head cavity, described piston head cavity has axial dimension, and described axial dimension is configured to make piston head between piston head butt flange and load button, to carry out vertically limited axial motion; And
Wherein, described piston head has the axial end surface that deviates from vertically pump barrel, in the compressed situation of Returnning spring, when the axial end surface upper surface of against load button vertically of piston head described in tappet is in the time that pump barrel is advanced, at least one in the axial end surface of piston head and the upper surface of load button is convex surface; And
Wherein, when tappet deviates from pump barrel while advancing along pumping axis, piston head is against piston head butt flange vertically.
18. 1 kinds of pumps, comprising:
Rotating cam axle, it is configured to around the rotation of camshaft spin axis, and described rotating cam axle comprises at least one cam lobe;
Tappet,
Roller, it is carried by tappet to rotate and follow cam lobe, and tappet and roller are converted into the straight-line displacement of tappet along pumping axis by camshaft around rotatablely moving of camshaft spin axis;
Limit the pump barrel in pumping chamber;
Piston, it is carried in pumping chamber slidably, and for the rotation because of camshaft, along pumping axial-movement, described piston is operationally connected to tappet, for moving substantially synergistically along pumping axis and tappet;
Returnning spring, it operationally makes it away from pump barrel with bias voltage tappet axially between pump barrel and tappet, and the axial bias power of described Returnning spring is not mechanically delivered to tappet by piston; And
Moment of torsion transmission reduces interface, it is provided by first surface and second surface at least in part, when Returnning spring is during in compressive state, axially butt be limited to contact area therebetween of described first surface and second surface, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, the contact area that moment of torsion transmission reduces interface is configured in the time that minimal torque appears in the Returnning spring side that moment of torsion transmission reduces interface, allow sliding aspect angle around the spin axis that is basically parallel to pumping axis between described first surface and second surface, instead of minimal torque is delivered to tappet so that tappet rotates around the axis that is basically parallel to pumping axis.
19. pumps according to claim 18, wherein, described Returnning spring is cardinal principle tubulose, described Returnning spring has the inwardly week of footpath limiting with respect to the smallest radial size of pumping axis, and contact area between described first surface and second surface has the maximum radial dimension with respect to pumping axis of the smallest radial size that is less than Returnning spring.
20. pumps according to claim 18, wherein, described minimal torque be at least even as big as make tappet with respect to camshaft around moment of torsion that substantially axis perpendicular to the spin axis of camshaft carries out angle rotation.
21. pumps according to claim 20, wherein, described moment of torsion transmission reduces interface and is mechanically placed between Returnning spring and tappet, to make it away from pump barrel and reduce interface from Returnning spring by moment of torsion transmission towards the axial compressive force of camshaft to be operationally delivered to tappet along pumping axis bias voltage tappet.
22. pumps according to claim 21, wherein, at least one in described first surface and second surface is convex surface.
23. pumps according to claim 22, wherein, the convex surface in described first surface and described second surface is spherical bending substantially.
24. pumps according to claim 18, further comprise:
Latch plate, the far-end axial engagement of itself and Returnning spring;
Load button, it provides in first surface that moment of torsion transmission reduces interface and second surface, described load button is mechanically placed between latch plate and tappet, and the axial compressive force that is operationally delivered to tappet being applied on latch plate with convenient Returnning spring Returnning spring when the compressive state is substantially fully operationally delivered to tappet by load button.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/252,544 | 2011-10-04 | ||
| US13/252,544 US20130084198A1 (en) | 2011-10-04 | 2011-10-04 | Pump with centralized spring forces |
| PCT/US2012/058464 WO2013052486A1 (en) | 2011-10-04 | 2012-10-02 | Pump with centralized spring forces |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103857908A true CN103857908A (en) | 2014-06-11 |
Family
ID=47049370
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280048988.8A Pending CN103857908A (en) | 2011-10-04 | 2012-10-02 | Pump with centralized spring forces |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20130084198A1 (en) |
| CN (1) | CN103857908A (en) |
| DE (1) | DE112012004121T5 (en) |
| WO (1) | WO2013052486A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3012345B1 (en) | 2013-10-29 | 2017-07-28 | Commissariat Energie Atomique | DEVICE FOR ENCAPSULATING A SENSITIVE DEVICE AND METHOD OF MAKING SAID DEVICE |
| GB201416001D0 (en) * | 2014-09-10 | 2014-10-22 | Delphi International Operations Luxembourg S.�.R.L. | Pumping mechanism |
| US10273920B2 (en) * | 2015-09-25 | 2019-04-30 | Stanadyne Llc | Single piston pump with reduced piston side loads |
| CN105973589B (en) * | 2016-07-21 | 2018-09-25 | 北京科技大学 | A kind of safe axis pin high speed torsion detecting device of automotive seat |
| US10006424B1 (en) * | 2016-12-22 | 2018-06-26 | GM Global Technology Operations LLC | Pump assembly and a propulsion system |
| JP7058505B2 (en) * | 2018-01-09 | 2022-04-22 | ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング | Fuel supply pump |
| DE102020104313B3 (en) * | 2020-02-19 | 2021-01-28 | Schaeffler Technologies AG & Co. KG | Plunger for acting on a pump piston of a high-pressure fuel pump |
| WO2022108578A1 (en) * | 2020-11-18 | 2022-05-27 | Cummins Inc. | Fuel pump assembly |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE601034C (en) * | 1933-02-24 | 1934-08-07 | Rene Plasseraud | Device for regulating the delivery rate of a pump, in particular a fuel injection pump |
| US1976151A (en) * | 1931-06-19 | 1934-10-09 | Guiberson Diesel Engine Compan | Fuel pump for internal combustion engine |
| US5404855A (en) * | 1993-05-06 | 1995-04-11 | Cummins Engine Company, Inc. | Variable displacement high pressure pump for fuel injection systems |
| CN1111065A (en) * | 1993-05-06 | 1995-11-01 | 卡明斯发动机公司 | Compact high performance fuel syste with accumulator |
| US5464330A (en) * | 1993-03-09 | 1995-11-07 | Applied Power Inc. | Cyclic hydraulic pump improvements |
| US5775203A (en) * | 1997-01-28 | 1998-07-07 | Cummins Engine Company, Inc. | High pressure fuel pump assembly |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3225433A1 (en) * | 1981-07-09 | 1983-03-10 | Lucas Industries P.L.C., Birmingham, West Midlands | FUEL INJECTION PUMP |
| DE19809315A1 (en) * | 1998-03-05 | 1999-09-09 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel generation |
| JP4016237B2 (en) * | 1999-04-16 | 2007-12-05 | 株式会社デンソー | Fuel injection pump |
| DE10115168C1 (en) * | 2001-03-27 | 2002-08-22 | Orange Gmbh | High-pressure fuel pump, in particular for injection systems of internal combustion engines |
| JP2003074439A (en) * | 2001-06-19 | 2003-03-12 | Denso Corp | Fuel injection pump |
| DE10212492B4 (en) * | 2002-03-21 | 2012-02-02 | Daimler Ag | piston pump |
| DE102006045933A1 (en) * | 2006-09-28 | 2008-04-03 | Robert Bosch Gmbh | Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly |
| DE102008001871A1 (en) * | 2008-05-20 | 2009-11-26 | Robert Bosch Gmbh | High-pressure fuel pump |
| GB2484889B (en) * | 2010-08-17 | 2013-09-04 | Artemis Intelligent Power Ltd | Ring cam and fluid-working machine including ring cam |
-
2011
- 2011-10-04 US US13/252,544 patent/US20130084198A1/en not_active Abandoned
-
2012
- 2012-10-02 CN CN201280048988.8A patent/CN103857908A/en active Pending
- 2012-10-02 WO PCT/US2012/058464 patent/WO2013052486A1/en active Application Filing
- 2012-10-02 DE DE112012004121.6T patent/DE112012004121T5/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1976151A (en) * | 1931-06-19 | 1934-10-09 | Guiberson Diesel Engine Compan | Fuel pump for internal combustion engine |
| DE601034C (en) * | 1933-02-24 | 1934-08-07 | Rene Plasseraud | Device for regulating the delivery rate of a pump, in particular a fuel injection pump |
| US5464330A (en) * | 1993-03-09 | 1995-11-07 | Applied Power Inc. | Cyclic hydraulic pump improvements |
| US5404855A (en) * | 1993-05-06 | 1995-04-11 | Cummins Engine Company, Inc. | Variable displacement high pressure pump for fuel injection systems |
| CN1111065A (en) * | 1993-05-06 | 1995-11-01 | 卡明斯发动机公司 | Compact high performance fuel syste with accumulator |
| US5775203A (en) * | 1997-01-28 | 1998-07-07 | Cummins Engine Company, Inc. | High pressure fuel pump assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112012004121T5 (en) | 2014-06-26 |
| WO2013052486A1 (en) | 2013-04-11 |
| US20130084198A1 (en) | 2013-04-04 |
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