EP3087275B1 - Variable displacement pump for fluids with modulated regulation, and method for regulating its displacement - Google Patents
Variable displacement pump for fluids with modulated regulation, and method for regulating its displacement Download PDFInfo
- Publication number
- EP3087275B1 EP3087275B1 EP14830721.8A EP14830721A EP3087275B1 EP 3087275 B1 EP3087275 B1 EP 3087275B1 EP 14830721 A EP14830721 A EP 14830721A EP 3087275 B1 EP3087275 B1 EP 3087275B1
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- European Patent Office
- Prior art keywords
- pump
- pressure
- spring
- regulation ring
- stage
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- 238000006073 displacement reaction Methods 0.000 title claims description 49
- 230000033228 biological regulation Effects 0.000 title claims description 41
- 239000012530 fluid Substances 0.000 title claims description 25
- 230000001105 regulatory effect Effects 0.000 title claims description 9
- 238000000034 method Methods 0.000 title claims description 7
- 230000009471 action Effects 0.000 claims description 9
- 238000005461 lubrication Methods 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 3
- 230000003247 decreasing effect Effects 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 21
- 238000006243 chemical reaction Methods 0.000 description 6
- 230000003042 antagnostic effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 238000013507 mapping Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Images
Classifications
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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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
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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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
Definitions
- the present invention relates to variable displacement pumps, and more particularly it concerns a pump of this kind with modulated regulation and a method of regulating its displacement.
- the invention is applied in a pump for the lubrication oil of the engine and/or the drive system of a motor vehicle, and particular reference will be made to such a preferred application in the description below.
- WO 2013/140304 discloses a positive displacement rotary pump with variable displacement in which the regulation exploits the variation of the relative position between an external regulation ring and the rotor eccentrically rotating within the same ring.
- the variation is obtained through a rotation of the ring.
- the latter is configured as a multistage rotary piston directly driven by the pressure of the pumped fluid, where at least one stage is permanently exposed to the action of the fluid and at least another stage intervenes, in addition to the first stage, upon command of an electrically controlled valve with on-off operation.
- the spring rotation is opposed by a spring guided on a tappet coupled with the ring by means of a spherical joint.
- WO2012/149929 discloses a variable displacement pump having actuation stages for regulating the displacement.
- One of the stages is configured as permanently exposed to the action of the fluid and at least another stage intervenes, in addition to the first stage, upon command of an electrically controlled valve with on-off operation in addition with a spool valve for modulating the applied pressure.
- No details of the construction of the pump are disclosed, i.e. neither of the ring ("Hubring" in this document) and its arrangement in the housing, nor of the spring and its mechanical and kinematic interaction with the other pump parts.
- modulation members are connected between the second stage and the driving members and are arranged to modulate a regulation pressure acting on the second stage depending on a control signal supplied by the driving members and on the pressure conditions.
- the modulating members include a distributor arranged to: take, depending on the control signal, at least a first and a second extreme configuration in correspondence of the maximum displacement and the minimum displacement of the pump, respectively; expose the second stage to the same pressure conditions as those acting on the first stage in the first extreme configuration, and to atmospheric pressure conditions in the second extreme configuration; and modulate the pressure acting on the second stage when the pressure of the pumped fluid reaches, while increasing or decreasing, respectively, a threshold pressure set for the intervention of members opposing a movement of a movable element of the distributor.
- the invention also concerns a method of regulating the displacement of a variable displacement pump for fluids as defined in independent claim 8, wherein movable regulation members are provided, which include at least a pair of actuation stages, of which a first stage is permanently exposed to the pressure conditions of the pumped fluid and is arranged to make the regulation members move against the action of opposing members, and a second stage is arranged to act concordantly with the opposing members in a manner controlled by external control members, and wherein a step of making the regulation members move comprises the step of modulating the driving pressure to which the second stage is exposed depending on the control signal and the pressure conditions of the pumped fluid.
- a pump 1 of the above kind comprises a body (schematised by dotted-and-dashed line 10), having a cavity within which regulation ring 11 (hereinafter also referred to simply as stator) is mounted so as to be freely rotatable along an arc of circumference about an axis 18 internal to the stator itself.
- Stator 11 has a chamber 12 accommodating rotor 13, keyed on a shaft 14 parallel to the rotation axis of stator 11. In the Figures, it is assumed that the rotor rotates in counterclockwise direction.
- stator 11 causes a variation of the relative eccentricity between stator 11 and rotor 13, and hence a variation of the displacement, between a condition of maximum eccentricity and displacement ( Fig. 1 ), which is taken also in rest conditions of the pump, and a condition of minimum eccentricity and displacement ( Fig. 2 ).
- a chamber 15 balancing the radial thrusts exerted on stator 11 because of the hydraulic pressure acting on the arc of the wall of chamber 12 corresponding to the balancing chamber.
- Balancing chamber 15 is defined by gaskets 16, 17 and it communicates with the devices utilising the pumped fluid, in particular with the lubrication circuit of the engine or the drive system of a motor vehicle.
- Stator 11 is configured as a multistage rotary piston for displacement regulation, directly driven by pressurised fluid coming for instance from the devices utilising the pumped fluid (for instance, from a point of the lubrication circuit located downstream the oil filter).
- the rotary piston has a pair of actuation stages (or surfaces) formed by portions 19, 20 of the external surface of stator 11. Said stages are exposed to the action of the pressurised fluid introduced into chambers 21, 22, where portions of the stator surface adjacent to actuation surfaces 19, 20 move in fluid-tight manner.
- Reference numerals 33, 34 denote ducts through which the regulation pressures act on stages 19, 20. Possible further stages can be formed in lightening chambers formed in stator 11, as disclosed in WO 2013/140304 .
- stages 19, 20 are formed so that the pressure applied to stage 19 generates a force F1 in turn arranged to generate a torque causing stator rotation towards the minimum displacement position against the action of an opposing member 23 (in particular a helical spring), and so that the pressure applied to stage 20 generates a force F2 generating an antagonistic torque concordant with the torque generated by a force F3 due to the reaction of spring 23.
- an opposing member 23 in particular a helical spring
- the torques generated by F1, F2, F3 will also be referred to hereinafter as torque 1, torque 2 and torque 3.
- Spring 23 is preloaded so as to prevent the rotation of stator 11 - and hence to keep it in the position shown in Fig. 1 - as long as the resultant of the pressures applied to stages 19, 20 is lower than a predetermined threshold, and to subsequently keep the pump displacement at the value corresponding to the pressure threshold. Such a condition is attained when an equilibrium is established between torques 1, 2 and 3.
- Spring 23 has a longitudinal axis 28 ( Figs. 3, 4 ) which does not cross rotation axis 18 of stator 11, and is located in a seat 24 formed in body 10. Its end loops 23A, 23B, suitably arranged close to one another and preferably tapered, abut against flat end surface 24A of seat 24 and on a flat portion 25 of the external surface of stator 11, respectively.
- Planes 24A, 25 have formed thereon centring projections 26, 27 engaging end loops 23A, 23B of spring 23.
- Such projections are aimed at maintaining end loops 23A, 23B univocally positioned and at preventing the spring from "sliding" over planes 24A, 25 because of the radial and/or axial components of the applied forces, should the friction coefficients of the materials of spring 23, body 10 and stator 11 allow such a sliding.
- recesses surrounding loops 23A, 23B might be provided, or a projection might be provided on one side and a recess on the other side. The projections or the recesses may even have non-circular shape.
- planes 24A, 25 are formed so that they are mutually parallel when the displacement is minimum, and so that they define a certain angle under all other conditions, said angle being maximum in the maximum displacement condition.
- Spring 23 will have therefore a minimum (substantially zero) deformation and a substantially rectilinear axis in the minimum displacement condition, and will attain the maximum deformation in the maximum displacement condition.
- the behaviour of the spring axis can be defined by a polynomial of third degree.
- centring elements 26, 27 are the only elements retaining spring 23 and that, since they cooperate only with the end loops, they have no guiding function. The remaining portion of the spring therefore can freely deform itself during the rotation of stator 11.
- force vector F3 applied to plane 25 at the centre of element 27 creates a non-linear counter-motive torque since, as clearly shown in Figs. 3 and 4 , the force and its application arm b3 (distance from rotation axis 18 of stator 11) change as stator 11 is rotates.
- force F3 is the resultant of the components of the whole of the radial and tangential forces acting on plane 25 and has smaller intensity and arm than in the minimum displacement condition ( Fig. 4 ), where the vector is perpendicular to plane 25.
- spring 23 will depend on the pump displacement, on the difference between the maximum and the minimum displacement, on the regulating pressure, and, in case of a rotary pump, on the driving geometry of rotor 13.
- chamber 21 is directly supplied with pressurised oil through a branch 33A of outlet duct 33 of oil filter 32, whereas chamber 22 is supplied through a spool valve 40 modulating the displacement regulation pressure, said valve communicating with chamber 22 through a duct 34.
- spool 41 In spool valve 40, spool 41, movable against the action of an opposing spring 46, defines a first annular chamber 42, it too connected to duct 33 (branch 33B), and a second annular chamber 43, where duct 33 ends and which communicates, depending on the position of spool 41, either with the first annular chamber 42 or a third annular chamber 44. The latter in turn may communicate with a non-pressurised portion of circuit 30, in particular with oil sump 35.
- a fourth annular chamber 45 is also supplied with pressurised oil from duct 33 (branch 33C).
- Spool 41 further has a first end portion 41A onto which spring 46 is guided, whereas the opposite end portion 41B slides in fluid-tight manner within a further chamber 47.
- spool 41 may be positioned so as to let pressurised oil from branch 33D of duct 33 ( Fig. 2 ) pass into chamber 47, or to intercept such oil, making chamber 47 discharge towards oil sump 35 ( Fig. 1 ).
- the pressurised oil arrives also to chamber 22 in the pump through branch 33B of duct 33, chambers 42, 43 of valve 30 communicating with each other and duct 34, and, by acting on surface 20, generates, due to force F2, the antagonistic torque (torque 2) concordant with torque 3.
- the pressures in both chambers 21, 22 are equivalent and the direction of action of resultant F1 - F2 will depend on the difference between the areas of surfaces 19, 20. In the illustrated example, taking into account that surface 19 has a greater area than surface 20, F1 > F2 and resultant F1 - F2 will act in counterclockwise direction.
- pressurised oil is supplied to chamber 45 of valve 40 thereby applying, onto an annular surface 41C of spool 41 defining such a chamber, a force opposing the force generated by spring 46.
- spool 41 begins moving to the left, thereby progressively shutting communication between chambers 42, 43 and progressively establishing communication between chambers 43, 44, and hence with oil sump 35, until a condition of equilibrium between the forces acting on the spool itself and the reaction of spring 46 is attained.
- a certain reduction in the pressure applied to stage 20, and hence of torque 2 takes place.
- stator 11 When the oil pressure is such that torque 1 - torque 2 > torque 3, stator 11 will rotate counterclockwise thereby reducing its eccentricity relative to rotor 13, and consequently the pump displacement.
- maximum regulated pressure value Such a pressure value, referred to as “maximum regulated pressure value", will be substantially maintained even as the rotation speed of the pump and the permeability of the engine (intended as the amount of oil used by the engine) vary.
- valve 50 When a suitable command arrives from the electronic control unit (not shown) of the vehicle, electrically-controlled valve 50 passes to the position shown in Fig. 2 , where it supplies chamber 47 with pressurised oil.
- Torque 2 becomes therefore 0 and the only torque opposing torque 3 is torque 1.
- Such a condition is referred to as "minimum regulated pressure value”.
- spool 41 will take an equilibrium position depending on the oil pressure conditions in duct 33 and on the reaction force of spring 46.
- the invention actually attains the desired aims. Thanks to the provision of the torque generated by F2, that adds to the torque generated by force F3 due to opposing spring 23, the force exerted by the latter to keep the equilibrium pressure can actually be reduced and, in the minimum pressure condition, actuation will be due only to the pressure applied to the first stage 19. Moreover, modulating the pressure applied to the second stage 20 by means of spool valve 40 makes actuation simple and stable. Lastly, the provision of non-guided opposing spring 23 reduces friction and hysteresis between the two directions of displacement regulation.
- electrically-controlled valve 50 is an on-off valve
- a proportional electrically-controlled valve could however be used for modulating the decrease and/or the increase of the driving pressure supplied by spool valve 40 (an hence the decrease or the increase of the pressure in chamber 22), thereby allowing a possible electronic management resulting from the engine "mapping".
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Description
- The present invention relates to variable displacement pumps, and more particularly it concerns a pump of this kind with modulated regulation and a method of regulating its displacement.
- Preferably, but not exclusively, the invention is applied in a pump for the lubrication oil of the engine and/or the drive system of a motor vehicle, and particular reference will be made to such a preferred application in the description below.
- It is known that, in pumps for making lubricating oil under pressure circulate in engines and/or drive systems in motor vehicles, the capacity, and hence the oil delivery rate, depends on the rotation speed of the engine. Hence, the pumps are designed so as to provide a sufficient delivery rate at low speeds, in order to ensure lubrication also under such conditions. If the pump has fixed geometry, at high rotation speed the delivery rate exceeds the necessary rate, whereby high power absorption, with a consequently higher fuel consumption, and a higher stress of the components occur due to the high pressures generated in the circuit.
- In order to obviate this drawback, it is known to provide the pumps with systems allowing a delivery rate regulation at the different operating conditions of the vehicle, in particular through a displacement regulation.
- The solutions for displacement regulation are specific for the particular type of pumping elements (vanes, external or internal gears, pistons...), but an element common to all solutions is the provision of movable regulation members driven by the pressure of the pumped fluid and of members, generally springs, opposing the movement of the regulation members and having the function of:
- ensuring that the pump is kept in the maximum displacement condition when starting and under low speed conditions;
- enabling a quick return of the pump to the maximum displacement during vehicle deceleration and/or when the operating conditions of the engine change.
- Generally, in such pumps, the problem exists of keeping the radial thrusts generated by the spring force and by the actuation pressures limited, thereby consequently reducing frictions and thus pressure hysteresis between the phases of increase and the phases of decrease of the same pressure (e.g., between the pressure values during engine acceleration and the values during engine deceleration), and of making actuation of the regulating members simple and stable.
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WO 2013/140304 discloses a positive displacement rotary pump with variable displacement in which the regulation exploits the variation of the relative position between an external regulation ring and the rotor eccentrically rotating within the same ring. The variation is obtained through a rotation of the ring. The latter is configured as a multistage rotary piston directly driven by the pressure of the pumped fluid, where at least one stage is permanently exposed to the action of the fluid and at least another stage intervenes, in addition to the first stage, upon command of an electrically controlled valve with on-off operation. The spring rotation is opposed by a spring guided on a tappet coupled with the ring by means of a spherical joint. The on-off actuation of the second stage does not ensure regulation stability, and the provision of the guide tappet and of its articulation on the ring gives rise to frictions causing hysteresis in the pump reaction.WO2012/149929 discloses a variable displacement pump having actuation stages for regulating the displacement. One of the stages is configured as permanently exposed to the action of the fluid and at least another stage intervenes, in addition to the first stage, upon command of an electrically controlled valve with on-off operation in addition with a spool valve for modulating the applied pressure. No details of the construction of the pump are disclosed, i.e. neither of the ring ("Hubring" in this document) and its arrangement in the housing, nor of the spring and its mechanical and kinematic interaction with the other pump parts. - It is an object of the present invention to provide a pump obviating the drawbacks of the prior art.
- According to the invention, in a pump of the above kind and as defined in
independent claim 1, modulation members are connected between the second stage and the driving members and are arranged to modulate a regulation pressure acting on the second stage depending on a control signal supplied by the driving members and on the pressure conditions. - Advantageously, the modulating members include a distributor arranged to: take, depending on the control signal, at least a first and a second extreme configuration in correspondence of the maximum displacement and the minimum displacement of the pump, respectively; expose the second stage to the same pressure conditions as those acting on the first stage in the first extreme configuration, and to atmospheric pressure conditions in the second extreme configuration; and modulate the pressure acting on the second stage when the pressure of the pumped fluid reaches, while increasing or decreasing, respectively, a threshold pressure set for the intervention of members opposing a movement of a movable element of the distributor.
- The invention also concerns a method of regulating the displacement of a variable displacement pump for fluids as defined in independent claim 8, wherein movable regulation members are provided, which include at least a pair of actuation stages, of which a first stage is permanently exposed to the pressure conditions of the pumped fluid and is arranged to make the regulation members move against the action of opposing members, and a second stage is arranged to act concordantly with the opposing members in a manner controlled by external control members, and wherein a step of making the regulation members move comprises the step of modulating the driving pressure to which the second stage is exposed depending on the control signal and the pressure conditions of the pumped fluid.
- The above and other features and advantages of the invention will become apparent from the following description of preferred embodiments, made by way of non limiting example with reference to the accompanying drawings, in which:
-
Fig. 1 is a front view of a pump according to the invention, without the cover, in the maximum displacement position; -
Fig. 2 is a view similar toFig. 1 , showing the pump in the minimum displacement position; and -
Figs. 3 and 4 are simplified diagrams showing the opposing force and its arm in the maximum and minimum displacement conditions; - The Figures show, by way of example only, a variable displacement rotary pump with vanes, the general structure of which is as disclosed in
WO 2013/140304 . Thus, that structure will be described here only to the extent necessary for the understanding of the invention and, for further details, reference is to be made to that document. - Referring to
Figs. 1 and2 , apump 1 of the above kind comprises a body (schematised by dotted-and-dashed line 10), having a cavity within which regulation ring 11 (hereinafter also referred to simply as stator) is mounted so as to be freely rotatable along an arc of circumference about anaxis 18 internal to the stator itself.Stator 11 has achamber 12 accommodatingrotor 13, keyed on ashaft 14 parallel to the rotation axis ofstator 11. In the Figures, it is assumed that the rotor rotates in counterclockwise direction. As known to the skilled in the art, the rotation ofstator 11 causes a variation of the relative eccentricity betweenstator 11 androtor 13, and hence a variation of the displacement, between a condition of maximum eccentricity and displacement (Fig. 1 ), which is taken also in rest conditions of the pump, and a condition of minimum eccentricity and displacement (Fig. 2 ). Betweenstator 11 andbody 10 there is formed achamber 15 balancing the radial thrusts exerted onstator 11 because of the hydraulic pressure acting on the arc of the wall ofchamber 12 corresponding to the balancing chamber.Balancing chamber 15 is defined bygaskets -
Stator 11 is configured as a multistage rotary piston for displacement regulation, directly driven by pressurised fluid coming for instance from the devices utilising the pumped fluid (for instance, from a point of the lubrication circuit located downstream the oil filter). In the illustrated embodiment, the rotary piston has a pair of actuation stages (or surfaces) formed byportions stator 11. Said stages are exposed to the action of the pressurised fluid introduced intochambers actuation surfaces Reference numerals stages stator 11, as disclosed inWO 2013/140304 . - In the illustrated example,
stages stage 19 generates a force F1 in turn arranged to generate a torque causing stator rotation towards the minimum displacement position against the action of an opposing member 23 (in particular a helical spring), and so that the pressure applied tostage 20 generates a force F2 generating an antagonistic torque concordant with the torque generated by a force F3 due to the reaction ofspring 23. For the sake of easiness of description, the torques generated by F1, F2, F3 will also be referred to hereinafter astorque 1, torque 2 and torque 3. -
Spring 23 is preloaded so as to prevent the rotation of stator 11 - and hence to keep it in the position shown inFig. 1 - as long as the resultant of the pressures applied tostages torques 1, 2 and 3. -
Spring 23 has a longitudinal axis 28 (Figs. 3, 4 ) which does not crossrotation axis 18 ofstator 11, and is located in aseat 24 formed inbody 10. Itsend loops flat end surface 24A ofseat 24 and on aflat portion 25 of the external surface ofstator 11, respectively. -
Planes centring projections engaging end loops spring 23. Such projections are aimed at maintainingend loops planes spring 23,body 10 andstator 11 allow such a sliding. In place of the projections, alsorecesses surrounding loops - In the configuration shown by way of example,
planes Spring 23 will have therefore a minimum (substantially zero) deformation and a substantially rectilinear axis in the minimum displacement condition, and will attain the maximum deformation in the maximum displacement condition. Advantageously, in the deformed condition, the behaviour of the spring axis can be defined by a polynomial of third degree. - It will be appreciated that
centring elements elements retaining spring 23 and that, since they cooperate only with the end loops, they have no guiding function. The remaining portion of the spring therefore can freely deform itself during the rotation ofstator 11. In this way, force vector F3 applied toplane 25 at the centre ofelement 27 creates a non-linear counter-motive torque since, as clearly shown inFigs. 3 and 4 , the force and its application arm b3 (distance fromrotation axis 18 of stator 11) change asstator 11 is rotates. In particular, in the maximum displacement condition (Fig. 3 ), force F3 is the resultant of the components of the whole of the radial and tangential forces acting onplane 25 and has smaller intensity and arm than in the minimum displacement condition (Fig. 4 ), where the vector is perpendicular to plane 25. - Such conditions are gradually attained, without any friction due to the spring.
- The counter-reaction to the forces generated by
spring 23 in turn is discharged at the centre of centring element 26 (Figs. 1 ,2 ), orthogonally to plane 24A. - It is to be taken into account that, in
order spring 23 correctly operates, it is necessary to prevent unwanted side "drifts" making the spring strike against the axial sides ofseat 24. In other words, the deformation must be such that, in the deformed condition, the curve described by the axis remains in a plane transversal toaxis 28. This is obtained through a suitable choice of the ratio between the diameter and the free length ofspring 23 and of the angle betweenplanes spring 23 must be in therange 1 to 5, and preferably in therange 1 to 3.8, and that the angle between the planes must be in the range from about 10° to about 30°, and preferably of the order of 20°. Also the diameter of the wire cooperates to the definition of such a ratio. - Provided that such general indications are to be met, for a given application the characteristics of
spring 23 will depend on the pump displacement, on the difference between the maximum and the minimum displacement, on the regulating pressure, and, in case of a rotary pump, on the driving geometry ofrotor 13. - Turning back to displacement regulation stages 19, 20,
chamber 21 is directly supplied with pressurised oil through abranch 33A ofoutlet duct 33 ofoil filter 32, whereaschamber 22 is supplied through aspool valve 40 modulating the displacement regulation pressure, said valve communicating withchamber 22 through aduct 34. - In
spool valve 40,spool 41, movable against the action of an opposingspring 46, defines a firstannular chamber 42, it too connected to duct 33 (branch 33B), and a secondannular chamber 43, whereduct 33 ends and which communicates, depending on the position ofspool 41, either with the firstannular chamber 42 or a thirdannular chamber 44. The latter in turn may communicate with a non-pressurised portion ofcircuit 30, in particular withoil sump 35. A fourthannular chamber 45 is also supplied with pressurised oil from duct 33 (branch 33C).Spool 41 further has afirst end portion 41A onto which spring 46 is guided, whereas theopposite end portion 41B slides in fluid-tight manner within afurther chamber 47. Depending on the command provided by an electrically-controlled valve 50 (which, in this example, is an on-off valve),spool 41 may be positioned so as to let pressurised oil frombranch 33D of duct 33 (Fig. 2 ) pass intochamber 47, or to intercept such oil, makingchamber 47 discharge towards oil sump 35 (Fig. 1 ). - The operation of the described pump is as follows.
- Under rest conditions, the pump is in the condition shown in
Fig. 1 .Rotor 13 is off axis relative tocavity 12 ofstator 11 and is located close to the wall ofcavity 12. Electrically-controlledvalve 50 is not actuated, so that no pressure exists inchamber 47 andspring 46 ofspool valve 40 pushes spool 41 completely to the right. Thus,chambers chamber 22 ofpump 1.Chamber 44 is isolated and permanently communicates with the drain (oil sump 35). - When
pump 1 is started, the rotation ofrotor 13 will give rise, in wholly conventional manner, to a flow of pressurised oil towards balancingchamber 15 andlubrication system 30 ofengine 31. As the rotation speed and the flow rate increase,lubrication system 30 of the engine, by opposing an increasing resistance to the flow, will make the pressure induct 33 increase. - Such a pressure, brought to
chamber 21 throughbranch 33A, acts on thefirst stage 19, thereby creating a hydraulic thrust onstator ring 11 and generating, by means of force F1,torque 1 opposed by torque 3 generated by reaction force F3 ofspring 23. The pressurised oil arrives also tochamber 22 in the pump throughbranch 33B ofduct 33,chambers valve 30 communicating with each other andduct 34, and, by acting onsurface 20, generates, due to force F2, the antagonistic torque (torque 2) concordant with torque 3. Under these conditions, the pressures in bothchambers surfaces surface 20, F1 > F2 and resultant F1 - F2 will act in counterclockwise direction. - Moreover, through
branch 33C, pressurised oil is supplied tochamber 45 ofvalve 40 thereby applying, onto anannular surface 41C ofspool 41 defining such a chamber, a force opposing the force generated byspring 46. When this opposing force exceeds the preload ofspring 46,spool 41 begins moving to the left, thereby progressively shutting communication betweenchambers chambers oil sump 35, until a condition of equilibrium between the forces acting on the spool itself and the reaction ofspring 46 is attained. Thus, a certain reduction in the pressure applied to stage 20, and hence of torque 2, takes place. - When the oil pressure is such that torque 1 - torque 2 > torque 3,
stator 11 will rotate counterclockwise thereby reducing its eccentricity relative torotor 13, and consequently the pump displacement. Such a pressure value, referred to as "maximum regulated pressure value", will be substantially maintained even as the rotation speed of the pump and the permeability of the engine (intended as the amount of oil used by the engine) vary. - When a suitable command arrives from the electronic control unit (not shown) of the vehicle, electrically-controlled
valve 50 passes to the position shown inFig. 2 , where it supplieschamber 47 with pressurised oil. When the force due to the joint pressure of the oil introduced intochambers spring 46, it causesspool 41 to move completely to the left, wherebypump chamber 22 discharges oil tosump 35 throughchambers valve 40 and thus passes to atmospheric pressure. Torque 2 becomes therefore 0 and the only torque opposing torque 3 istorque 1. Such a condition is referred to as "minimum regulated pressure value". Also in thiscase spool 41 will take an equilibrium position depending on the oil pressure conditions induct 33 and on the reaction force ofspring 46. - The invention actually attains the desired aims. Thanks to the provision of the torque generated by F2, that adds to the torque generated by force F3 due to opposing
spring 23, the force exerted by the latter to keep the equilibrium pressure can actually be reduced and, in the minimum pressure condition, actuation will be due only to the pressure applied to thefirst stage 19. Moreover, modulating the pressure applied to thesecond stage 20 by means ofspool valve 40 makes actuation simple and stable. Lastly, the provision of non-guided opposingspring 23 reduces friction and hysteresis between the two directions of displacement regulation. - It is clear that the above description is given only by way of non-limiting example and that changes and modifications are possible without departing from the scope of the claims.
- For instance, even if it has been assumed that electrically-controlled
valve 50 is an on-off valve, a proportional electrically-controlled valve could however be used for modulating the decrease and/or the increase of the driving pressure supplied by spool valve 40 (an hence the decrease or the increase of the pressure in chamber 22), thereby allowing a possible electronic management resulting from the engine "mapping".
Claims (10)
- A variable displacement pump for fluids, comprising:- a pump body (10) having a cavity;- a regulation ring or stator (11) mounted within said cavity and arranged to move, in response to operating conditions of the pump (1), between two extreme positions corresponding to a maximum displacement and a minimum displacement, respectively, of the pump;- a rotor (13) accomodated in a chamber (12) of the regulation ring (11); and- a spring (23) opposing the movement of the regulation ring (11);wherein the regulation ring (11) has at least a pair of actuation stages (19, 20) having mutually differing surfaces, a first of said actuation stages (19) being permanently exposed to pressure conditions of the pumped fluid and being arranged to make the regulation ring (11) move against the action of the spring (23), and a second of said actuation stages (20) being arranged to act concordantly with the spring (23) in a manner controlled by an electrically-controlled valve (50);wherein:- a spool valve (40) is connected between the second stage (20) and the electrically-controlled valve (50) and is arranged to modulate a regulation pressure acting on the second stage (20) depending on a control signal supplied by the electrically-controlled valve (50) and on the pressure conditions of the pumped fluid,characterised in that the pump (1) is a pump for a lubrication circuit (30) of an engine (31),in that said movement of the regulation ring (11) is a rotation about a rotation axis (18) internal to the regulation ring (11),in that the spring (23) is a helical spring having a longitudinal axis (28) which does not cross the rotation axis (18) of the regulation ring (11), is located in a seat (24) formed in the pump body (10) and has end loops (23A, 23B) which abut against a flat end surface (24A) of the seat (24) and on a flat portion (25) of an external surface of regulation ring (11), andin that said flat end surface (24A) and said flat portion (25) have formed thereon centring projections or recesses (26, 27) engaging end loops (23A, 23B) of the spring (23) and configured for maintaining said end loops (23A, 23B) univocally positioned and preventing the spring (23) from sliding over said flat end surface (24A) and flat end portion (25), said centring projections or recesses (26, 27) have no guiding function so that the spring (23) has an intermediate portion freely deformable during the rotation of the regulation ring (11).
- The pump as claimed in claim 1, characterised in that between the regulation ring (11) and the pump body (10) there is formed a balancing chamber (15) defined by gaskets (16, 17) and configured for balancing a radial thrusts exerted on the regulation ring (11) because of the hydraulic pressure acting on an arc of the wall of the chamber (12) corresponding to the balancing chamber (15), wherein the pumped fluid delivered by the pump passes through said balancing chamber (15).
- The pump as claimed in any one of preceding claims, characterised in that the spool valve (40) includes a distributor arranged to:- take, depending on the control signal, at least a first and a second extreme configuration in correspondence of the maximum displacement and the minimum displacement of the pump, respectively;- expose the second stage (20) to the same pressure conditions as those acting on the first stage (19) in the first extreme configuration, and to atmospheric pressure conditions in the second extreme configuration, and to modulate the pressure acting on the second stage when the pressure of the pumped fluid reaches, while increasing or decreasing, respectively, a threshold pressure set for the intervention of members (46) opposing a movement of a movable element (41) of the distributor.
- The pump as claimed in claim 3, characterised in that the electrically-controlled valve (50) is an electrically-controlled valve with on-off operation.
- The pump as claimed in claim 3, characterised in that the electrically-controlled valve (50) is an electrically-controlled valve with proportional operation and the distributor is arranged to take, depending on the control signal, also a plurality of intermediate configurations in each of which it is arranged to modulate the pressure acting on the second stage when the pumped fluid reaches the threshold pressure.
- The pump as claimed in any one of claims 3 to 5, characterised in that the spool valve (40) is configured so that the spool (41) is arranged to define:- a first chamber (42) permanently communicating with a duct (33) in which the pumped fluid is present;- a second chamber (43) permanently communicating with a chamber (22) of the pump (1) in which the second actuation stage (20) moves, and also communicating with the first chamber (42) in the first extreme configuration;- a third chamber (44) arranged to communicate only with a region at atmospheric pressure (35) in the second extreme configuration, and to simultaneously communicate with the second chamber (43) and the region at atmospheric pressure (35), in a manner depending on the position of the spool (41), in valve configurations other than the extreme configurations;- a fourth chamber (45), also permanently communicating with said duct (33); and- a fifth chamber (47), arranged to be put in communication by the electrically-controlled valve (50) either with said duct (33), in the first extreme configuration, or with the region at atmospheric pressure (35), in the second extreme configuration.
- The pump as claimed in claim 6, characterised in that said duct (33) is the outlet duct of a filter (32).
- A method of regulating the displacement of a variable displacement pump for fluids (1) for a lubrication circuit (30) of an engine (31), the method comprising the steps of:- providing, within a cavity of a pump body (10), a regulation ring or stator (11) arranged to rotate about an axis (18) internal to the regulation ring (11), in response to pressure conditions of a pumped fluid (1) and against the action of a spring (23), between two extreme positions corresponding to a maximum displacement and a minimum displacement of the pump, respectively, wherein said spring (23) is a helical spring having a longitudinal axis (28) which does not cross the rotation axis (18) of regulation ring (11), is located in a seat (24) formed in the pump body (10) and has end loops (23A, 23B) which abut against a flat end surface (24A) of the seat (24) and on a flat portion (25) of an external surface of regulation ring (11);- providing a rotor (13) accomodated in a chamber (12) of the regulation ring (11);- providing in the regulation ring (11) at least a pair of actuation stages (19, 20) having mutually differing surfaces, a first of said actuation stages (19) being arranged to act oppositely to the spring (23), and a second of said actuation stages (20) being arranged to act concordantly with the spring (23);- making said regulation ring (11) move by permanently exposing the first stage (19) to said pressure conditions and by applying a control pressure to the second stage (20) in a manner depending on a control signal and modulating the control pressure to which the second stage (20) is exposed depending on the control signal and the pressure conditions of the pumped fluid; and- providing projections or recesses (26, 27) on said flat end surface (24A) and said flat portion (25), said projections or recesses (26, 27) engaging end loops (23A, 23B) of the spring (23), maintaining said end loops (23A, 23B) univocally positioned and preventing the spring (23) from sliding over said flat end surface (24A) and flat end portion (25), said centring projections or recesses (26, 27) have no guiding function so that the spring (23) has an intermediate portion which freely deforms during the rotation of the regulation ring (11).
- The method as claimed in claim 8, characterised in that the step of modulating the control pressure comprises the steps of:- interposing, between the second stage (20) and an electrically-controlled valve (50) supplying the control signal, a spool valve (40) responsive to the control signal and the pressure conditions of the pumped fluid;- making, by means of the control signal, the spool valve (40) take at least a first and a second extreme configuration in correspondence of the maximum displacement and the minimum displacement of the pump, respectively;- exposing the second stage (20) to the same pressure conditions as those acting on the first stage (19) in the first extreme configuration, and to atmospheric pressure conditions in the second extreme configuration, and modulating the pressure acting on the second stage when the pressure of the pumped fluid reaches a threshold pressure while increasing or decreasing, respectively.
- The method as claimed in claim 8, characterised in that the step of modulating the control pressure further comprises the steps of making the spool valve (40) take, depending on the control signal, also a plurality of intermediate positions between the extreme positions, and of modulating the pressure applied to the second stage also in each intermediate position, when the threshold pressure is reached.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT001063A ITTO20131063A1 (en) | 2013-12-23 | 2013-12-23 | ADJUSTABLE DISPLACEMENT PUMP FOR FLUIDS WITH ADJUSTMENT MODULATION, AND METHOD FOR ADJUSTING ITS DISPLACEMENT |
IT001072A ITTO20131072A1 (en) | 2013-12-24 | 2013-12-24 | ADJUSTABLE DISPLACEMENT PUMP AND METHOD FOR ADJUSTING THE PUMP DISPLACEMENT |
PCT/IB2014/067211 WO2015097637A1 (en) | 2013-12-23 | 2014-12-22 | Variable displacement pump for fluids with modulated regulation, and method for regulating its displacement |
Publications (2)
Publication Number | Publication Date |
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EP3087275A1 EP3087275A1 (en) | 2016-11-02 |
EP3087275B1 true EP3087275B1 (en) | 2022-08-03 |
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Family Applications (2)
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EP14830721.8A Active EP3087275B1 (en) | 2013-12-23 | 2014-12-22 | Variable displacement pump for fluids with modulated regulation, and method for regulating its displacement |
EP14830722.6A Active EP3087276B1 (en) | 2013-12-23 | 2014-12-22 | Variable displacement pump and method for regulating the displacement of the pump |
Family Applications After (1)
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EP14830722.6A Active EP3087276B1 (en) | 2013-12-23 | 2014-12-22 | Variable displacement pump and method for regulating the displacement of the pump |
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EP (2) | EP3087275B1 (en) |
WO (2) | WO2015097637A1 (en) |
Families Citing this family (6)
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JP6260778B2 (en) * | 2014-03-14 | 2018-01-17 | 日立オートモティブシステムズ株式会社 | Variable displacement vane pump |
DE102015117433B4 (en) * | 2015-10-13 | 2019-01-03 | Schwäbische Hüttenwerke Automotive GmbH | rotary pump |
CN105351188B (en) * | 2015-11-04 | 2017-05-31 | 湖南机油泵股份有限公司 | A kind of two grades of variable displacement vane pump control systems of combination valve type |
JP6709135B2 (en) * | 2016-09-16 | 2020-06-10 | Kyb株式会社 | Variable displacement vane pump |
JP2018044535A (en) * | 2016-09-16 | 2018-03-22 | Kyb株式会社 | Variable capacity type vane pump |
CN107605720B (en) * | 2017-10-27 | 2019-06-28 | 湖南机油泵股份有限公司 | A kind of three-level or level Four displacement-variable oil pump based on biswitch solenoid valve |
Citations (1)
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WO2013140304A1 (en) * | 2012-03-19 | 2013-09-26 | Vhit Spa | Variable displacement rotary pump and displacement regulation method |
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US2669189A (en) * | 1947-09-05 | 1954-02-16 | Houdaille Hershey Corp | Adjustable fluid pump |
DE3001673C2 (en) * | 1980-01-18 | 1984-06-28 | Audi Nsu Auto Union Ag, 7107 Neckarsulm | Adjustable vane pump |
DE102005033293A1 (en) * | 2005-07-16 | 2007-01-25 | Zf Lenksysteme Gmbh | Displacement pump with variable delivery volumes, particularly single stroke vane cell pump, produced pressure medium flow for user and has rotor in housing |
AT502189B1 (en) * | 2005-07-29 | 2007-02-15 | Miba Sinter Holding Gmbh & Co | VANE PUMP |
US7959171B2 (en) | 2007-11-26 | 2011-06-14 | Nissan Motor Co., Ltd. | Lower spring seat mounting structure for vehicle suspension |
DE102010022677B4 (en) * | 2010-06-04 | 2016-06-30 | Nidec Gpm Gmbh | Vane pump |
DE102010055141A1 (en) | 2010-12-18 | 2012-08-02 | Audi Ag | Spring pad for a freestanding suspension spring of a motor vehicle |
DE112012001982A5 (en) * | 2011-05-05 | 2014-01-30 | Ixetic Bad Homburg Gmbh | variable |
-
2014
- 2014-12-22 EP EP14830721.8A patent/EP3087275B1/en active Active
- 2014-12-22 WO PCT/IB2014/067211 patent/WO2015097637A1/en active Application Filing
- 2014-12-22 EP EP14830722.6A patent/EP3087276B1/en active Active
- 2014-12-22 WO PCT/IB2014/067217 patent/WO2015097639A1/en active Application Filing
Patent Citations (1)
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WO2013140304A1 (en) * | 2012-03-19 | 2013-09-26 | Vhit Spa | Variable displacement rotary pump and displacement regulation method |
Also Published As
Publication number | Publication date |
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EP3087276A1 (en) | 2016-11-02 |
WO2015097637A1 (en) | 2015-07-02 |
EP3087275A1 (en) | 2016-11-02 |
EP3087276B1 (en) | 2020-03-11 |
WO2015097639A1 (en) | 2015-07-02 |
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