EP0908626A1 - Steuerungssystem verwendbar in einer Dosierpumpe - Google Patents

Steuerungssystem verwendbar in einer Dosierpumpe Download PDF

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Publication number
EP0908626A1
EP0908626A1 EP98202169A EP98202169A EP0908626A1 EP 0908626 A1 EP0908626 A1 EP 0908626A1 EP 98202169 A EP98202169 A EP 98202169A EP 98202169 A EP98202169 A EP 98202169A EP 0908626 A1 EP0908626 A1 EP 0908626A1
Authority
EP
European Patent Office
Prior art keywords
shaft
output
output regulator
coupling
regulator according
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.)
Withdrawn
Application number
EP98202169A
Other languages
English (en)
French (fr)
Inventor
Sergio Bellei
Andrea Bellei
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sabi Pompe e Impianti Srl
Original Assignee
Sabi Pompe e Impianti Srl
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Sabi Pompe e Impianti Srl filed Critical Sabi Pompe e Impianti Srl
Publication of EP0908626A1 publication Critical patent/EP0908626A1/de
Withdrawn legal-status Critical Current

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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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element

Definitions

  • This invention refers to an output regulator applicable to metering pumps.
  • the known output regulators comprise a mechanical body interposed between the motor of the pump and the pump itself.
  • a first and a second kinematic mechanism is essentially fitted inside said body.
  • the first kinematic mechanism is of a connecting rod and crank type and suitable for converting the rotary motion of the motor into a rectilinear alternating motion with a pre-established stroke, depending on the output of the pump.
  • the second kinematic mechanism has a structure suitable for selecting the stroke of said rectilinear alternating motion depending on the desired output.
  • the purpose of this invention is to provide a solution for the mentioned problem.
  • This means producing an output regulator applicable to alternating pumps capable of providing the best compromise between the virtues of economy, reliability and space saving as well as a capability of operating in observance of the mentioned tolerances.
  • the connecting rod provided at the end of the grooved shaft allows to define the diameter of the crank only as a function of the actual load, without for example having to take into account any other regulating organs. This circumstance allows to minimize the space required for a full rotation of the connecting rod.
  • the body housing this kinematic mechanism is consequently less bulky than that of equivalent regulators having the same potential; in other words, it offers a greater capability and reliability than that offered by known regulator types.
  • the change of output is obtained by a helical device which guarantees precision and linear action.
  • the output regulator is of a type applicable to metering pumps. It basically comprises a body 2 housing a first kinematic mechanism 3 and a second one 4. The body 2 can mechanically be interposed between the pump motor (not shown) and the pump itself (not shown).
  • the first kinematic mechanism 3 is of a type suitable for converting the motor rotary motion to a rectilinear alternating motion supplied to the pump depending on the desired output. It basically comprises a connecting rod 5 and a crank 6. The foot of the connecting rod 7 is connected by a pin 8 to a guide shoe 9 sliding in a guide 10 fitted to the body 2 of the regulator 1 along the axis D of the same connecting rod 5. The guide shoe 9 carries means 11 to provide a kinematic connection with the pump.
  • the guide 10 fitted to the body 2 of the regulator 1 can be separated from the same.
  • the body 1 is sealed in order to contain the lubricating oil of the kinematic mechanisms.
  • the connection between the connecting rod 5 and the crank 6 is left without a bearing.
  • the second kinematic mechanism 4 is suitable for selecting the stroke length of the foot 7 of the connecting rod 5, which moves with an alternating linear motion along the axis D.
  • the desired output depends on the length of this motion.
  • the second kinematic mechanism 4 comprises a gear 12 to transmit the power from the motor to the output regulator 1.
  • the gear 12 consists of a worm screw 13 and a sprocket 14.
  • the worm screw 13 is keyed to a shaft 15 passing through both said worm screw 13 and the body 2 of the regulator 1.
  • the extremities of said shaft 15 can be connected to a motor (not shown) or to an identical shaft 15 together with the body 2 of the regulator 1, so as to form a set of regulators 1 (see Figure 3, which exemplifies the case of two regulators), capable of regulating several pumps arranged in parallel and driven by a single motor.
  • the sprocket 14 of said gear 12 is keyed to a hollow shaft 16 rotating with respect to a main axis A parallel to the rotary axis C of the crank 6 of the first kinematic mechanism 3.
  • the inside of said hollow shaft on opposite sections of said main axis A holds a sliding shaft 17 and a contoured shaft 18.
  • the axis B of the contoured shaft 18 is parallel to the main axis A, which is perpendicular to the axis D of the connecting rod 5.
  • the sliding shaft 17 has a first extremity 19 coaxial with the main axis A, and a second extremity 20 fitted with a first coupling 21 and a second coupling 22 that engage it while allowing it to slide parallel to the main axis A with respect to both said hollow shaft 16 and said contoured shaft 18.
  • the contoured shaft 18 has a first section 23 that carries a helical projection 24 constituting the male portion of said second coupling 22.
  • the second section 25 of the contoured shaft 18 is connected to the button of the crank 6 of the first kinematic mechanism 3 by a third coupling 26.
  • the second coupling 22 is formed by a cavity 27, as shown in Figure 4 (or female portion of the second coupling 22) provided on the sliding shaft 17, which is complementary to the helical projection 24 (or male portion of the second coupling 22) fitted on the contoured shaft 18.
  • the cavity 27 provided on the sliding shaft 17 and the helical projection 24 fitted on the contoured shaft 18 have a triangular cross section.
  • the first coupling 21 comprises a key 28 on the sliding shaft 17 and a groove 29 on the hollow shaft 16.
  • the first extremity 19 of the sliding shaft 17 is connected, with the possibility of rotating around its axis B, to a regulating hand-wheel 31, which comprises a first outer section 32 screwable into the body 2 of the regulator 1 and a second inner section 33 slidable inside the body 2 of the regulator 1.
  • This inner section 33 is connected to the first extremity 19 (fitted with a bearing 34), as seen in Figure 1, of said sliding shaft 17, which is therefore telescopically arranged with respect to the body 2 .
  • the hand-wheel 31 slides with respect to the body 2, so that its lower rim 35 can be taken as an indicator of the selected output.
  • the regulating hand-wheel 31 can be locked in a pre-established position by a stop 36, preferably formed by a screw.
  • the power flows from the regulator through the shaft 15, which transmits it to the sprocket 14 that passes it on to the hollow shaft 16.
  • the hollow shaft 16 rotates around the main axis A and by its first coupling 21 induces the sliding shaft 17 to rotate around itself with respect to the axis A.
  • the sliding shaft 17 impresses a rotary motion on itself with respect to the axis B, and a revolution around the main axis A of the contoured shaft 18.
  • the contoured shaft 18 induces a rotation around the axis C of the crank 6, which moves the connecting rod 5 and alternatively the shoe 9 connected to an alternative pump.
  • the stroke of the shoe 9 is always equal to the distance between the main axis A and the rotary axis of the crank C with respect to the axis D of the connecting rod 5.
  • the stroke is always equal to the distance existing between the projection of the axis A on the axis D and the projection of the axis C on the same axis D.
  • Figure 5 is a simplified view of the position of the axes A-D when the regulator is set to the maximum stroke or output. This distance may be varied by acting on the hand-wheel 31, which can only rotate. The rotation of the hand-wheel 31 provokes the rectilinear sliding along the main axis A of the sliding shaft 17, which engages the helical projection 24 of the contoured shaft 18 by the cavity 2, inducing the rotation of said contoured shaft around its axis B and consequently changing the position of the axis C with respect to the axis D and therefore its stroke. This change can be appreciated by comparing Figure 5 with Figure 6.
  • a further rotation of the hand-wheel can cause the projection of the axis C on the axis D and the projection of the axis A on the axis D to coincide (Figure 7).
  • the stroke and therefore the output equal zero, even if the device is in operation.
  • the change of the stroke from zero to the maximum value can be achieved continuously and without any jumps in output, which may preclude certain values.
  • the operation of the device for any given output is smooth and free of any jumping or knocking action.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
  • Infusion, Injection, And Reservoir Apparatuses (AREA)
  • Devices For Dispensing Beverages (AREA)
EP98202169A 1997-10-06 1998-06-26 Steuerungssystem verwendbar in einer Dosierpumpe Withdrawn EP0908626A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT97MI002267A IT1295283B1 (it) 1997-10-06 1997-10-06 Regolatore di portata applicabile a pompe dosatrici
ITMI972267 1997-10-06

Publications (1)

Publication Number Publication Date
EP0908626A1 true EP0908626A1 (de) 1999-04-14

Family

ID=11377994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98202169A Withdrawn EP0908626A1 (de) 1997-10-06 1998-06-26 Steuerungssystem verwendbar in einer Dosierpumpe

Country Status (2)

Country Link
EP (1) EP0908626A1 (de)
IT (1) IT1295283B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102261329A (zh) * 2010-05-26 2011-11-30 上海工程技术大学 一种计量泵行程调节机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR526897A (fr) * 1920-11-05 1921-10-15 Louis Renault Dispositif permettant à un moteur à air comprimé de fonctionner comme compresseur
GB538320A (en) * 1940-03-02 1941-07-29 Rotherham & Sons Ltd Improvements relating to time-lag devices such as incorporate gearing
US2257854A (en) * 1938-07-12 1941-10-07 Joseph A Peterson Pressure regulator for fluids
EP0106808A2 (de) * 1982-06-30 1984-04-25 Gualtiero Maurer Radialkolbenmaschine mit variabler Verdrängung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR526897A (fr) * 1920-11-05 1921-10-15 Louis Renault Dispositif permettant à un moteur à air comprimé de fonctionner comme compresseur
US2257854A (en) * 1938-07-12 1941-10-07 Joseph A Peterson Pressure regulator for fluids
GB538320A (en) * 1940-03-02 1941-07-29 Rotherham & Sons Ltd Improvements relating to time-lag devices such as incorporate gearing
EP0106808A2 (de) * 1982-06-30 1984-04-25 Gualtiero Maurer Radialkolbenmaschine mit variabler Verdrängung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102261329A (zh) * 2010-05-26 2011-11-30 上海工程技术大学 一种计量泵行程调节机构
CN102261329B (zh) * 2010-05-26 2014-04-02 上海工程技术大学 一种计量泵行程调节机构

Also Published As

Publication number Publication date
ITMI972267A1 (it) 1999-04-06
IT1295283B1 (it) 1999-05-04

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