EP0953764B1 - Volumetric pump - Google Patents
Volumetric pump Download PDFInfo
- Publication number
- EP0953764B1 EP0953764B1 EP99107763A EP99107763A EP0953764B1 EP 0953764 B1 EP0953764 B1 EP 0953764B1 EP 99107763 A EP99107763 A EP 99107763A EP 99107763 A EP99107763 A EP 99107763A EP 0953764 B1 EP0953764 B1 EP 0953764B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- duct
- volumetric pump
- valve
- seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000005086 pumping Methods 0.000 claims description 27
- 238000004891 communication Methods 0.000 claims description 9
- 230000005291 magnetic effect Effects 0.000 claims description 7
- 239000004020 conductor Substances 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 4
- 239000003302 ferromagnetic material Substances 0.000 claims description 3
- 230000000295 complement effect Effects 0.000 claims description 2
- 239000012530 fluid Substances 0.000 claims description 2
- 230000000284 resting effect Effects 0.000 claims description 2
- 238000001914 filtration Methods 0.000 claims 1
- 239000010687 lubricating oil Substances 0.000 description 15
- 238000002485 combustion reaction Methods 0.000 description 8
- 239000003921 oil Substances 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000005611 electricity Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 229920002457 flexible plastic Polymers 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- 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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0223—Electromagnetic pumps
Definitions
- the present invention relates to a volumetric pump.
- the present invention relates to a volumetric pump designed to ensure the circulation of lubricating oil in a two-stroke internal combustion engine of known type; the use to which the details as follow make explicit reference without loss of their general nature thereby.
- such pumps generally comprise a valve-like body of essentially cylindrical form, and a ferromagnetic material piston installed to slide axially within a cylindrical seat formed in the valve-like body.
- the two axial ends of the cylindrical seat are in communication with atmosphere by way of two connecting ducts which extend inside the valve-like body, coaxially with the longitudinal axis of the valve-like body; while the two variable-volume chambers in which the piston subdivides the cylindrical seat, are in communication together through an axial duct formed in the body of the piston.
- the electromagnetically-actuated volumetric pumps also comprise an opposition spring, which is located inside one of the two variable-volume chambers of which the piston subdivides the cylindrical seat, in such a manner as to minimise the volume of the chamber not occupied by the spring; and a coil of electrically conductor material, which when an electrical current passes through, is able to generate a magnetic field able to oppose the force of the opposing spring, and to axially move the piston in such a way as to maximise the volume of the variable-volume chamber not containing the spring.
- the said chamber defines the pumping chamber of the volumetric pump.
- the aforementioned electromagnetically-actuated volumetric pumps are finally provided with an intake valve located along the axial duct formed in the body of the piston, and with a supply valve located along the duct which connects the pumping chamber, or the variable-volume chamber not containing the opposition spring, directly to atmosphere.
- CH-675312 and FR-2465903 teach the use an intake valve which is not carried by the piston and is located inside the pumping chamber. More in details CH-675312 and FR-2465903 disclose an intake valve which comprises a plug axially moving inside the pumping chamber, and an opposing spring located inside the pumping chamber with a first end coming to bear against the plug and a second end coming to bear against the wall of the valve-like body, in such a manner as to maintain the plug bearing against the piston to engage the ingress of the passing duct formed within the piston.
- the purpose of the present invention is to provide an electro-magnetically actuated volumetric pump able to overcome the above cited drawbacks and to ensure an extremely precise control of the oil capacity throughout the whole range of use of an internal combustion engine, with relatively low production costs.
- a volumetric pump comprising a valve-like body, and at least a piston mounted axially sliding inside a seat formed within the valve-like body; the said seat being in communication with atmosphere by way if a supply duct and an intake duct, and the said piston defining inside the said seat at least a variable-volume pumping chamber; the volumetric pump also comprising flexible means able to retain the said piston in the resting position in which it minimises the volume of the said pumping chamber, a coil of electrically conductive material which when energised is able to provide a magnetic field allowing the axial movement of the piston inside the said seat to produce a variation in the volume of the said pumping chamber, and at least an intake valve and a discharge valve able to regulate respectively the incoming and outgoing flow of fluid from the said seat; the said intake valve being located inside the pumping chamber, not carried by the piston; the said volumetric pump being characterised in that it also comprises along the said intake duct a disc with a central calibrated hole.
- reference number 1 indicates the whole of a volumetric pump assembly able to be used, preferably though not necessarily, to circulate the lubricating oil in a two-stroke internal combustion engine.
- the volumetric pump 1 comprises a valve-like body 2 of essentially cylindrical form, which extends coaxially with a longitudinal axis A, and has internally a seat 3 which extends preferably, though not necessarily, coaxially with axis A, and a pair of ducts 4 and 5 able to bring into communication the two axial ends of the seat 3 itself with atmosphere.
- the volumetric pump 1 also comprises a piston 6 made of ferromagnetic material, which is located axially mobile within the seat 3 formed in the valve-like body 2, and defines inside the seat 3 itself a variable volume pumping chamber 8. Obviously the connection between the piston 6 and the seat 3 has a fluid-proof seal.
- the duct 4 communicates directly with the chamber 8, and defines the volumetric pump supply duct 1, whereas duct 5 communicates with the seat 3 of the opposing part of the chamber 8 in relation to the piston 6, and defines the intake duct of the volumetric pump 1.
- ducts 4 and 5 extend coaxially with the axis A running in opposition to the seat 3 in such a way that each ends correspondingly in a respective end of the valve-like body 2.
- Such ends are designed in such a way as to allow coupling to pipework in which the lubricating oil circulates.
- the piston 6 has a passing hole 9, which extends coaxially with the axis A along the whole length of the piston 6 itself, in such a way as to ensure the communication of the chamber 8 with the duct 5.
- the volumetric pump 1 finally comprises a retaining spring 10 able to retain the piston 6 in a rest position in which, the piston 6 minimises the volume of the chamber 8, and a coil 11 made of electrically conducting material placed coaxially with axis A, on the outside of the valve-like body 2.
- the said coil 11 is able to generate when energised with electricity, a magnetic field and is located on the valve-like body 2 in such a manner that the magnetic field produced thereby causes an axial movement of the piston 6 so as to displace the piston 6 itself from the rest position, thus increasing the volume of chamber 8.
- the said displacement takes place against the action of spring 10.
- the seat 3 is sub-divided in two portions 3a and 3b of differing diameter, the piston 6 being mounted to slide within portion 3a of greater diameter, whereas the chamber 8 comprises the portion 3b of the seat 3 and as is more clearly explained below, part of the portion 3a when it reaches its maximum volume.
- the spring (70) on the other hand is located coaxially with the axis A inside the portion 3a of the part opposing the chamber 8 in relation to the piston 6 and presents a first end bearing against the piston 6 and a second end bearing against the bottom of the seat 3, in such a manner as to maintain the piston 6 bearing against the shoulder 7 connecting portions 3a and 3b of the seat 3 one to the other, or in the rest position.
- the volumetric pump 1 also has a disc 12 with a calibrated centre hole, which is located coaxially with the axis A in such a way as to present the calibrated hole aligned with the duct 5.
- the volumetric pump 1 also includes an intake valve 13 able to regulate the access of lubrication oil to the inside of the chamber 8, and a discharge valve 14 able to regulate the exit of the lubricating oil from the chamber 8.
- the intake valve 13 is located inside the chamber 8, to coincide with the passing hole 9 of the piston 6, whereas the discharge valve 14 is located in the duct 4 immediately downstream from the chamber 8.
- the valve 13 has a plug 15 located axially sliding inside the chamber 8, and an opposing spring 16 located inside the chamber 8 coaxially with axis A, with a first end bearing against the plug 15 and a second end bearing against the wall of the valve-like body 2, in such a manner as to maintain the plug 15 bearing on the piston 6 in such a way as to prevent with a fluid-sealing means the ingress from the passing hole 9.
- the valve 14 comprises instead a plug 17 located axially sliding inside the duct 4, and an opposing spring 18 located inside the duct 4 coaxially with the axis A, with a first end bearing against the plug 17 and a second end bearing against an annular shoulder 19 located inside the duct 5, in such a way as to keep the plug 17 bearing against a contraction 20 located at inlet of duct 5.
- both the plug 15 as well as the plug 17 consist of a metallic material spherically-formed body.
- volumetric pump 1 is preferably though not necessarily, fitted with a filter component 21 installed inside the duct 5.
- the valve body 2 consists of three cylindrical portions, respectively referenced 2a, 2b, 2c, in line along axis A, and made integral with each other by an external shell 22 which extends coaxially to axis A to protect the coil 11.
- the duct 5 is achieved inside the cylindrical portion 2a
- the seat 3 is achieved inside the cylindrical portion 2b
- the duct 4 is achieved inside the cylindrical portion 2c.
- volumetric pump 1 Operation of the volumetric pump 1 is now described assuming that the pump is located along a lubricating oil circulation duct.
- the opposing spring 16 nevertheless does not manage to keep the plug 15 bearing against piston 6, owing either to the inertia of the plug 15 or to the discharging lubricating oil forced through the passing hole (9).
- the lubricating oil occupying the portion 3a of the seat 3 together with the piston 6, in fact will discharge more easily through the passing hole (9) formed in the piston 6 than through the calibrated hole in the disc 12, also facilitated in this by the depression which occurs inside the chamber 8 owing to the rapid increase in volume.
- the opposing spring 18 ensures the return of the plug 17 to bear against the throttle 20 produced at the point of inlet of the duct 5.
- the capacity of the volumetric pump 1 is a function of the frequency with which the piston 6 is displaced inside the seat 3, that is to say of the frequency with which an electric current is made to pass through the coil 11.
- the piston 6 is made of permanent magnet material.
- the piston 6 is double acting, and defines inside its seat two variable volume pumping chambers 9 complementary to each other.
- Each chamber 8 is connected with atmosphere through a supply duct 4 which extends coaxial with the axis A, and has an intake valve 13 and a discharge valve 14, whereas the intake duct 5 is in common communication with both chambers 9, and extends inside the valve-like body 2 perpendicularly to the axis A, along an appendix of the valve body 2 which in turn extends perpendicularly to axis A.
- the duct 5 faces a branch 9a of the passing hole 9 which extends in the piston 6 perpendicularly to axis A, and the disc 12 is located along the duct 5, immediately upstream from the seat 3.
- valve body 2 presents two seats 3 each of which is actuated in a sliding manner by a respective piston 6, which defines a pumping chamber 8.
- each chamber 8 is is connected to atmosphere through a supply duct 4 which extends coaxial to the axis A, and is provided with its own intake valve 13 and its own discharge valve 14.
- the intake duct 5 is in communication with both seats 3, and a terminal portion thereof extends into the valve body 2 coaxially to the axis A, along an appendix in the valve body 2 which extends in turn, perpendicularly to axis A.
- volumetric pump 1 The advantages of the volumetric pump 1 described above are evident: the presence of the disc 12 with the central calibrated hole along the intake duct 5 avoids any undesired flow back of liquid in the intake duct 5 during the axial movement of the piston 6, thus allowing an optimal filling of the pumping chamber 8 at high speeds.
- a further advantage derives from the fact that the plug 15 for valve 13 cannot be deformed so that the volume of the chamber 8 is constant in whatsoever operating condition.
- the volumetric pump 1 can thus be transformed into a metering arrangement always able to provide the same volume of oil under pressure on each electrical current impulse.
- volumetric pump 1 has extremely simple construction, with a limited number of component parts in relative movement, and the fact that it allows direct piloting from an electronic central unit which, by varying the frequency of the supply to the coil 11, it is possible to control in real time and with extreme precision the capacity thus provided.
- volumetric pump 1 described and illustrated herein without thereby exceeding the scope of the present invention.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Reciprocating Pumps (AREA)
Description
- The present invention relates to a volumetric pump.
- In particular, the present invention relates to a volumetric pump designed to ensure the circulation of lubricating oil in a two-stroke internal combustion engine of known type; the use to which the details as follow make explicit reference without loss of their general nature thereby.
- As it is known, in two-stroke internal combustion engines the supply of lubricating oil to the engine intake manifold, and to any other part of the engine requiring continuous lubrication, is effectively achieved by volumetric pumps with gears and pistons actuated by the engine shaft.
- Normally such pumps provide a supply proportional to the engine rotation rate, and are frequently able to adjust the supply according to the throttle setting in the engine intake, in such a manner as to maintain at a given level the ratio between lubricating oil sent to the engine intake distributor and the air drawn through the intake distributor itself.
- Unfortunately the oil pumps at present in use are not able to satisfy the requirements contained in the anti-pollution standards shortly to be introduced. In order to come within the limits established for such standards, the two-stroke internal combustion engines must in fact ensure a markedly lower consumption of lubricating oil than at present, and this may only be achieved by the use of oil pumps allowing an extremely accurate setting of the lubricating oil supply circulating within the engine. In the present volumetric pumps such a control would only be achieved by reducing to a few microns the coupling tolerances of the various pistons of the pump; such a reduction would only be achieved by means of complex production processes which would greatly increase the final production costs.
- A possible solution to the problem of anti-pollution standards about to be introduced, could be provided by the use of electro-magnetically operated volumetric pumps now widely used elsewhere in manufacture.
- Referring to U.S.3250219, such pumps generally comprise a valve-like body of essentially cylindrical form, and a ferromagnetic material piston installed to slide axially within a cylindrical seat formed in the valve-like body. The two axial ends of the cylindrical seat are in communication with atmosphere by way of two connecting ducts which extend inside the valve-like body, coaxially with the longitudinal axis of the valve-like body; while the two variable-volume chambers in which the piston subdivides the cylindrical seat, are in communication together through an axial duct formed in the body of the piston.
- The electromagnetically-actuated volumetric pumps also comprise an opposition spring, which is located inside one of the two variable-volume chambers of which the piston subdivides the cylindrical seat, in such a manner as to minimise the volume of the chamber not occupied by the spring; and a coil of electrically conductor material, which when an electrical current passes through, is able to generate a magnetic field able to oppose the force of the opposing spring, and to axially move the piston in such a way as to maximise the volume of the variable-volume chamber not containing the spring. The said chamber defines the pumping chamber of the volumetric pump.
- The aforementioned electromagnetically-actuated volumetric pumps are finally provided with an intake valve located along the axial duct formed in the body of the piston, and with a supply valve located along the duct which connects the pumping chamber, or the variable-volume chamber not containing the opposition spring, directly to atmosphere.
- Unfortunately, the electromagnetically-actuated volumetric pumps described above have the great disadvantage that their scope of utilisation is insufficiently extensive to allow justifiable use in two-stroke internal combustion engines.
- In particular, such pumps do not provide on discharge a sufficiently high capacity to satisfy the oil requirements of the internal combustion engine running at high speeds. This is mainly due to the fact that the overall piston weight is too great to allow axial movements sufficiently allowing hourly capacities compatible with those required for two-stroke internal combustion engines.
- Furthermore, for the electromagnetically-actuated volumetric pumps described above (please see U.S.
patent 3 250 219) the intake and supply valves are normally made of flexible plastic material, which owing to distortion, are unable to ensure the constant volume of the pumping chamber throughout the whole range of use of the pump. - To overcame this disadvantage CH-675312 and FR-2465903 teach the use an intake valve which is not carried by the piston and is located inside the pumping chamber. More in details CH-675312 and FR-2465903 disclose an intake valve which comprises a plug axially moving inside the pumping chamber, and an opposing spring located inside the pumping chamber with a first end coming to bear against the plug and a second end coming to bear against the wall of the valve-like body, in such a manner as to maintain the plug bearing against the piston to engage the ingress of the passing duct formed within the piston.
- However this solution has the major drawback of suffering of an undesired flow back of liquid in the intake duct during the axial movement of the piston which compromises the optimal filling of the pumping chamber at high speeds.
- The purpose of the present invention is to provide an electro-magnetically actuated volumetric pump able to overcome the above cited drawbacks and to ensure an extremely precise control of the oil capacity throughout the whole range of use of an internal combustion engine, with relatively low production costs.
- According to the present invention a volumetric pump is designed comprising a valve-like body, and at least a piston mounted axially sliding inside a seat formed within the valve-like body; the said seat being in communication with atmosphere by way if a supply duct and an intake duct, and the said piston defining inside the said seat at least a variable-volume pumping chamber; the volumetric pump also comprising flexible means able to retain the said piston in the resting position in which it minimises the volume of the said pumping chamber, a coil of electrically conductive material which when energised is able to provide a magnetic field allowing the axial movement of the piston inside the said seat to produce a variation in the volume of the said pumping chamber, and at least an intake valve and a discharge valve able to regulate respectively the incoming and outgoing flow of fluid from the said seat; the said intake valve being located inside the pumping chamber, not carried by the piston; the said volumetric pump being characterised in that it also comprises along the said intake duct a disc with a central calibrated hole.
- The present invention is now described with reference to the appended drawings, which illustrate a non-restrictive operating example thereof wherein:
- Figure 1 is a sectional view of a volumetric pump designed according to the terms of the present invention;
- Figures 2 and 3 are sectional views of a number of variations of the volumetric pump illustrated in Figure 1.
-
- With reference to Figure 1, reference number 1 indicates the whole of a volumetric pump assembly able to be used, preferably though not necessarily, to circulate the lubricating oil in a two-stroke internal combustion engine.
- The volumetric pump 1 comprises a valve-
like body 2 of essentially cylindrical form, which extends coaxially with a longitudinal axis A, and has internally aseat 3 which extends preferably, though not necessarily, coaxially with axis A, and a pair ofducts seat 3 itself with atmosphere. The volumetric pump 1 also comprises apiston 6 made of ferromagnetic material, which is located axially mobile within theseat 3 formed in the valve-like body 2, and defines inside theseat 3 itself a variablevolume pumping chamber 8. Obviously the connection between thepiston 6 and theseat 3 has a fluid-proof seal. - The
duct 4 communicates directly with thechamber 8, and defines the volumetric pump supply duct 1, whereasduct 5 communicates with theseat 3 of the opposing part of thechamber 8 in relation to thepiston 6, and defines the intake duct of the volumetric pump 1. - In the example illustrated here, in
particular ducts seat 3 in such a way that each ends correspondingly in a respective end of the valve-like body 2. Such ends are designed in such a way as to allow coupling to pipework in which the lubricating oil circulates. - However the
piston 6 has apassing hole 9, which extends coaxially with the axis A along the whole length of thepiston 6 itself, in such a way as to ensure the communication of thechamber 8 with theduct 5. - The volumetric pump 1 finally comprises a
retaining spring 10 able to retain thepiston 6 in a rest position in which, thepiston 6 minimises the volume of thechamber 8, and acoil 11 made of electrically conducting material placed coaxially with axis A, on the outside of the valve-like body 2. Thesaid coil 11 is able to generate when energised with electricity, a magnetic field and is located on the valve-like body 2 in such a manner that the magnetic field produced thereby causes an axial movement of thepiston 6 so as to displace thepiston 6 itself from the rest position, thus increasing the volume ofchamber 8. Obviously, the said displacement takes place against the action ofspring 10. - In the example as illustrated, in particular the
seat 3 is sub-divided in twoportions 3a and 3b of differing diameter, thepiston 6 being mounted to slide within portion 3a of greater diameter, whereas thechamber 8 comprises theportion 3b of theseat 3 and as is more clearly explained below, part of the portion 3a when it reaches its maximum volume. The spring (70) on the other hand is located coaxially with the axis A inside the portion 3a of the part opposing thechamber 8 in relation to thepiston 6 and presents a first end bearing against thepiston 6 and a second end bearing against the bottom of theseat 3, in such a manner as to maintain thepiston 6 bearing against the shoulder 7 connectingportions 3a and 3b of theseat 3 one to the other, or in the rest position. - Meeting the axial end of the
seat 3 where thespring 10 is bearing, or meets the inlet toduct 5, the volumetric pump 1 also has adisc 12 with a calibrated centre hole, which is located coaxially with the axis A in such a way as to present the calibrated hole aligned with theduct 5. - The volumetric pump 1 also includes an
intake valve 13 able to regulate the access of lubrication oil to the inside of thechamber 8, and adischarge valve 14 able to regulate the exit of the lubricating oil from thechamber 8. Theintake valve 13 is located inside thechamber 8, to coincide with thepassing hole 9 of thepiston 6, whereas thedischarge valve 14 is located in theduct 4 immediately downstream from thechamber 8. - In the example illustrated here, in particular, the
valve 13 has aplug 15 located axially sliding inside thechamber 8, and anopposing spring 16 located inside thechamber 8 coaxially with axis A, with a first end bearing against theplug 15 and a second end bearing against the wall of the valve-like body 2, in such a manner as to maintain theplug 15 bearing on thepiston 6 in such a way as to prevent with a fluid-sealing means the ingress from thepassing hole 9. - The
valve 14 comprises instead aplug 17 located axially sliding inside theduct 4, and anopposing spring 18 located inside theduct 4 coaxially with the axis A, with a first end bearing against theplug 17 and a second end bearing against anannular shoulder 19 located inside theduct 5, in such a way as to keep theplug 17 bearing against acontraction 20 located at inlet ofduct 5. - In the example shown here, both the
plug 15 as well as theplug 17 consist of a metallic material spherically-formed body. - Finally the volumetric pump 1 is preferably though not necessarily, fitted with a
filter component 21 installed inside theduct 5. - With reference to Figure 1, to facilitate the assembly of the volumetric pump 1, the
valve body 2 consists of three cylindrical portions, respectively referenced 2a, 2b, 2c, in line along axis A, and made integral with each other by anexternal shell 22 which extends coaxially to axis A to protect thecoil 11. In the case in point, theduct 5 is achieved inside thecylindrical portion 2a, theseat 3 is achieved inside thecylindrical portion 2b, whereas theduct 4 is achieved inside thecylindrical portion 2c. - Other structural solutions are obviously possible to facilitate the assembly of the
tubular body 2. - Operation of the volumetric pump 1 is now described assuming that the pump is located along a lubricating oil circulation duct.
- In service, when the
coil 11 is energised with electricity, the magnetic field produced thereby causes the axial displacement of thepiston 6 and consequent increase in the volume ofchamber 8. - During the displacement of the
piston 6, theopposing spring 16 nevertheless does not manage to keep theplug 15 bearing againstpiston 6, owing either to the inertia of theplug 15 or to the discharging lubricating oil forced through the passing hole (9). The lubricating oil occupying the portion 3a of theseat 3 together with thepiston 6, in fact will discharge more easily through the passing hole (9) formed in thepiston 6 than through the calibrated hole in thedisc 12, also facilitated in this by the depression which occurs inside thechamber 8 owing to the rapid increase in volume. - In view of the whole of the displacement and the volumes involved, when the
opposing spring 16 manages to displace theplug 15 to close the entrance to thepassing hole 9 of thepiston 6, the lubricating oil has already completely filled thechamber 8 which in addition toportion 3b of theseat 3 now also comprises part of portion 3a of theseat 3 itself - When the magnetic field ceases, that is when no more electricity passes into the
coil 11, theretaining spring 10 returns thepiston 6 into the rest position, thus rapidly reducing the volume of thechamber 8. Nevertheless since the lubricating oil is incompressible, the excess part of the lubricating oil discharges from thechamber 8 through theduct 4, thereby displacing theplug 17. - When all the excess lubricating oil has discharged, the
opposing spring 18 ensures the return of theplug 17 to bear against thethrottle 20 produced at the point of inlet of theduct 5. - It will be obvious that the capacity of the volumetric pump 1 is a function of the frequency with which the
piston 6 is displaced inside theseat 3, that is to say of the frequency with which an electric current is made to pass through thecoil 11. - According to a variation not shown here, the
piston 6 is made of permanent magnet material. - According to the variation illustrated in Figure 2, the
piston 6 is double acting, and defines inside its seat two variablevolume pumping chambers 9 complementary to each other. Eachchamber 8 is connected with atmosphere through asupply duct 4 which extends coaxial with the axis A, and has anintake valve 13 and adischarge valve 14, whereas theintake duct 5 is in common communication with bothchambers 9, and extends inside the valve-like body 2 perpendicularly to the axis A, along an appendix of thevalve body 2 which in turn extends perpendicularly to axis A. In that case theduct 5 faces a branch 9a of thepassing hole 9 which extends in thepiston 6 perpendicularly to axis A, and thedisc 12 is located along theduct 5, immediately upstream from theseat 3. - According to the variation illustrated in Figure 3, the
valve body 2 presents twoseats 3 each of which is actuated in a sliding manner by arespective piston 6, which defines apumping chamber 8. In a similar way as the previous variation, eachchamber 8 is is connected to atmosphere through asupply duct 4 which extends coaxial to the axis A, and is provided with itsown intake valve 13 and itsown discharge valve 14. In that case theintake duct 5 is in communication with bothseats 3, and a terminal portion thereof extends into thevalve body 2 coaxially to the axis A, along an appendix in thevalve body 2 which extends in turn, perpendicularly to axis A. - The advantages of the volumetric pump 1 described above are evident: the presence of the
disc 12 with the central calibrated hole along theintake duct 5 avoids any undesired flow back of liquid in theintake duct 5 during the axial movement of thepiston 6, thus allowing an optimal filling of thepumping chamber 8 at high speeds. - A further advantage derives from the fact that the
plug 15 forvalve 13 cannot be deformed so that the volume of thechamber 8 is constant in whatsoever operating condition. The volumetric pump 1 can thus be transformed into a metering arrangement always able to provide the same volume of oil under pressure on each electrical current impulse. - Other advantages of the volumetric pump 1 are its extremely simple construction, with a limited number of component parts in relative movement, and the fact that it allows direct piloting from an electronic central unit which, by varying the frequency of the supply to the
coil 11, it is possible to control in real time and with extreme precision the capacity thus provided. - Finally it is clear that modifications and variations may be made to the volumetric pump 1 described and illustrated herein without thereby exceeding the scope of the present invention.
Claims (14)
- Volumetric pump (1) comprising a valve-like body (2), and at least a piston (6) mounted axially sliding inside a seat (3) formed within the valve-like body (2); the said seat (3) being in communication with atmosphere by way if a supply duct (4) and an intake duct (5), and the said piston (6) defining inside the said seat (3) at least a variable-volume pumping chamber (8); the volumetric pump (1) also comprising flexible means (10) able to retain the said piston (6) in the resting position in which it minimises the volume of the said pumping chamber (8), a coil (11) of electrically conductive material which when energised is able to provide a magnetic field allowing the axial movement of the piston (6) inside the said seat (3) to produce a variation in the volume of the said pumping chamber (8), and at least an intake valve (13) and a discharge valve (14) able to regulate respectively the incoming and outgoing flow of fluid from the said seat (3); the said intake valve (13) being located inside the pumping chamber (8), not carried by the piston (6); the said volumetric pump (1) being characterised in that it also comprises along the said intake duct (5) a disc (12) with a central calibrated hole.
- Volumetric pump according to claim 1, characterised in that the said supply duct (4) directly connects the said pumping chamber (8) with atmosphere; the said piston (6) being provided instead with a passing duct (9) able to ensure communication of the pumping chamber (8) with the said intake duct (5).
- Volumetric pump according to claim 2, characterised in that the said piston (6) subdivides the seat (3) inside the valve-like body (2) into two portions which are connected with atmosphere respectively by means of the supply duct (4) and by means of the intake duct (5); the passing duct (9) in the piston (6) being able to connect together the two portions of the said seat (3).
- Volumetric pump according to claim 3, characterised in that the said supply duct (4) and intake duct (5) connect with atmosphere the two axial ends of the sat (3) formed inside the said valve-like body.
- Volumetric pump according to any one of claims 2 to 4, characterised by the fact that the said intake valve (13) comprises a plug (15) axially moving inside the pumping chamber (8), and an opposing spring (16) located inside the pumping chamber (8) with a first end coming to bear against the plug (15) and a second end coming to bear against the wall of the valve-like body (2), in such a manner as to maintain the plug (15) bearing against the piston (6) in such a manner as to engage while maintaining engaged under fluid-sealed conditions the passing duct (9) under fluid-seal conditions the ingress of the passing duct (9) formed within the said piston (6).
- Volumetric pump according to any one of the previous claims, characterised by the fact that the said supply duct (4) has immediately downstream from the said pumping chamber (8) a choke means (20), and the said discharge valve (14) comprises a moving plug (17) inside the said supply duct (4), and an opposing spring (18) able to maintain the said plug (17) bearing against the said choke means (20), engaging it under fluid-sealed conditions.
- Volumetric pump according to any one of the previous claims, characterised in that the said disc (12) is located along the said intake duct (5) in such a way as to present its calibrated hole coaxial with the axis (A) of the duct.
- Volumetric pump according to any one of the previous claims, characterised in that it comprises a filtering component (21) located along the said intake duct (5).
- Volumetric pump according to any one of the previous claims, characterised in that the said seat (3), the said supply duct (4), the said piston (6) and its passing hole (9), are extended coaxially with a same longitudinal axis (A).
- Volumetric pump according to claim 9, characterised in that the said valve-like body (2) is of essentially cylindrical shape and extends coaxially with the said longitudinal axis (A).
- Volumetric pump according to any one of the previous claims, characterised in that the said piston (6) defines on the inside of the said seat (3) two variable-volume pumping chambers (9) complementary to each other; both the said pumping chambers (8) being each directly connected to a respective supply duct (4), and both communicating with a same said intake duct (5) through a passing hole (9) formed in the said piston (6).
- Volumetric pump according to one or other of claims 1 to 10, characterised in that it comprises two pistons (6) mounted axially sliding each inside a respective seat (3) formed in the said valve-like body (2); the pistons (6) defining respective variable-volume pumping chambers (8) inside the corresponding seats (3).
- Pump according to one or other of the previous claims, characterised by the fact that the said piston (6) is made of ferromagnetic material.
- Pump according to one or other of the claims 1 to 12, characterised by the fact that the said piston (6) is made of permanent magnet material.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT98BO000263A IT1299987B1 (en) | 1998-04-27 | 1998-04-27 | VOLUMETRIC PUMP. |
ITBO980263 | 1998-04-27 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0953764A1 EP0953764A1 (en) | 1999-11-03 |
EP0953764B1 true EP0953764B1 (en) | 2004-09-29 |
Family
ID=11343135
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99107763A Expired - Lifetime EP0953764B1 (en) | 1998-04-27 | 1999-04-19 | Volumetric pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0953764B1 (en) |
DE (1) | DE69920566T2 (en) |
ES (1) | ES2229574T3 (en) |
IT (1) | IT1299987B1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4203160B2 (en) * | 1998-11-13 | 2008-12-24 | 株式会社ミクニ | Electromagnetic pump |
DE60126056T2 (en) * | 2001-01-24 | 2007-07-12 | Mikuni Corp. | Fuel supply system |
ITMI20010420A1 (en) * | 2001-03-01 | 2002-09-01 | Inc Dell Orto S P A | PUMP CONTROLLED BY ELECTROMAGNET |
ITMI20010419A1 (en) * | 2001-03-01 | 2002-09-01 | Inc Dell Orto S P A | PUMP CONTROLLED BY ELECTROMAGNET |
ITMI20012647A1 (en) * | 2001-12-13 | 2003-06-13 | Dellorto Spa | PUMP CONTROLLED BY ELECTROMAGNET |
ITMI20050688A1 (en) * | 2005-04-18 | 2006-10-19 | Dellorto Spa | FUEL SUPPLY SYSTEM FOR INTERNAL COMBUSTION ENGINES AND PUMP-INJECTOR UNIT WITH ELECTROMAGNETIC DRIVE USED IN SUCH A SYSTEM |
DK179750B1 (en) | 2017-12-13 | 2019-05-07 | Hans Jensen Lubricators A/S | Large slow-running two-stroke engine and method of lubri-cating such engine, as well as an injector with an electric pumping system for such engine and method |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES252076Y (en) * | 1979-07-16 | 1981-11-01 | ALTERNATING ELECTROMAGNETIC PUMP FOR LIQUIDS | |
GB8709082D0 (en) * | 1987-04-15 | 1987-05-20 | Eaton Sa Monaco | Electrical fluid pump |
CH675312A5 (en) * | 1988-06-13 | 1990-09-14 | Rueck & Meier Ag | Fluid dosing device using timed pump operation - compensates set time for detected variation in pump flow |
US5567131A (en) * | 1995-04-20 | 1996-10-22 | Gorman-Rupp Industries | Spring biased check valve for an electromagnetically driven oscillating pump |
-
1998
- 1998-04-27 IT IT98BO000263A patent/IT1299987B1/en active IP Right Grant
-
1999
- 1999-04-19 EP EP99107763A patent/EP0953764B1/en not_active Expired - Lifetime
- 1999-04-19 ES ES99107763T patent/ES2229574T3/en not_active Expired - Lifetime
- 1999-04-19 DE DE69920566T patent/DE69920566T2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE69920566T2 (en) | 2005-12-08 |
ITBO980263A0 (en) | 1998-04-27 |
ES2229574T3 (en) | 2005-04-16 |
DE69920566D1 (en) | 2004-11-04 |
ITBO980263A1 (en) | 1999-10-27 |
EP0953764A1 (en) | 1999-11-03 |
IT1299987B1 (en) | 2000-04-04 |
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