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WO2019102486A1 - Pompe à huile à débit variable - Google Patents

Pompe à huile à débit variable Download PDF

Info

Publication number
WO2019102486A1
WO2019102486A1 PCT/IN2018/050213 IN2018050213W WO2019102486A1 WO 2019102486 A1 WO2019102486 A1 WO 2019102486A1 IN 2018050213 W IN2018050213 W IN 2018050213W WO 2019102486 A1 WO2019102486 A1 WO 2019102486A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
conduit
vdop
valve assembly
electronic control
Prior art date
Application number
PCT/IN2018/050213
Other languages
English (en)
Inventor
J. Suresh KUMAR
R. Sivanantham
Original Assignee
Ucal Fuel Systems Limited
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 Ucal Fuel Systems Limited filed Critical Ucal Fuel Systems Limited
Publication of WO2019102486A1 publication Critical patent/WO2019102486A1/fr

Links

Classifications

    • 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
    • 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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil

Definitions

  • the present invention generally relates to a variable delivery oil pump (VDOP) and more particularly, to a system for effective control of variable delivery oil pump (VDOP) which varies the oil quantity delivered to the engine according to specific engine operating conditions and speeds.
  • VDOP variable delivery oil pump
  • a lubrication unit such as an oil pump in engines and related systems are used for pressurizing the working fluid such as oil and delivering the fluid to lubrication circuits.
  • Conventional oil pumps for example, gerotor type oil pumps are used to deliver oil quantity linearly proportional to engine speeds. However, at higher engine speeds, such pumps deliver excess amount of oil and leads to an engine power loss.
  • the variable delivery oil pumps were developed, which were configured to deliver the required quantity of oil according to engine requirements both at low and high speeds.
  • a variable delivery oil pump consists of a main pump area having internal cavities for oil flow, a sliding ring placed inside the cavity and a rotor seated inside the sliding ring.
  • the rotor has radial slots, where plurality of vanes are aligned inside the slots, such that when the engine runs at high speeds and the pressure of the system increases, the sliding ring moves from its position to predetermined position, also called as minimum eccentricity position, against the spring biasing force to reduce the eccentricity of the pump.
  • predetermined position also called as minimum eccentricity position
  • the sliding ring moves towards the maximum eccentric position by means of spring force and consequently more quantity of oil delivery is achieved.
  • the movement of sliding ring determines the output volume of the pump and hence determines the quantity of oil delivered to the engine.
  • an oil delivery system does not provide an effective control on the movement of the sliding ring when the pressure inside the system fluctuates suddenly and also if there is an electronic failure, the whole pumps system fails to do its intended function.
  • the present invention aims to make the effective control of the variable delivery oil pump and also to run the pump system continuously even if the electronic failure occurs.
  • the electronic control setup used in the present invention need not to be operated on all conditions which reduces the power consumption of the VDOP system.
  • the present invention has been devised to mitigate the above mentioned drawbacks.
  • the present invention discloses a system to address the above mentioned problems and to effectively control oil quantity delivered to engine for specific operating condition and speeds.
  • a Variable Delivery Oil Pump (VDOP) system comprising a pumping unit and an internal cavity for oil flow, a sliding ring, at least one rotor housed inside the sliding ring, at least one hydraulically controlled dual valve assembly for regulating and relieving the pressure developed in the delivery line, a first return conduit connected to the hydraulic dual valve assembly for returning the oil back to an inlet side through a conduit and a second return conduit for returning the oil back to the inlet side, a relief conduit for reliving the pressure developed in a delivery conduit during shutoff conditions and an electronic control setup actuated by an electronic control unit at predetermined operating conditions for reducing the pressure in a spring chamber.
  • VDOP Variable Delivery Oil Pump
  • the hydraulic dual valve assembly further comprises a primary valve and a secondary valve.
  • the primary valve floats with respect to the secondary valve member.
  • the electronic control setup directly drains the oil from the spring chamber to reduce the pressure inside the spring chamber at predetermined operating conditions.
  • the hydraulic dual valve assembly has four modes of operation.
  • the hydraulic dual valve assembly during the first mode of operation regulates the oil going inside the spring chamber.
  • the hydraulic dual valve assembly during the second mode of operation returns the oil back to the inlet side through the first return conduit and the conduit.
  • the hydraulic dual valve assembly during the third mode of operation returns the oil back to the inlet side through the second return conduit .
  • the hydraulic dual valve assembly during the fourth mode of operation returns the oil directly to the sump through the relief conduit.
  • the oil is drained from the spring chamber through the first return conduit on failure of the electronic control setup.
  • FIG. 1 is a front view of a pumping unit of a variable delivery oil pump (VDOP) system in accordance with an embodiment of the present invention, in which the slider ring is at maximum eccentricity position.
  • VDOP variable delivery oil pump
  • Figure 2 illustrates schematic layout configuration of a pumping unit according to an embodiment of the present invention.
  • Figure 3 illustrates first mode of operation of a hydraulic dual valve assembly according to an embodiment of the present invention.
  • Figure 4 illustrates schematic layout configuration of the VDOP system when electronic control setup is activated according to an embodiment of the present invention.
  • FIG. 5 illustrates second mode of operation of the VDOP system according to an embodiment of the present invention.
  • Figure 6 illustrates third mode of operation of the VDOP system according to an embodiment of the present invention.
  • Figure 7 illustrates fourth mode of operation of the VDOP system according to an embodiment of the present invention.
  • FIG. 1 illustrates a front view of a pumping unit of a variable delivery oil pump (VDOP) system in accordance with an embodiment of the present invention.
  • the pumping unit (20) includes a housing (21) having an internal cavity (22) for fluid flow.
  • the pumping unit (20) is mounted on an engine (not shown) with a suitable gasket and the pumping unit (20) supplies pressurized working fluid to the engine.
  • the pumping unit (20) also includes a sliding ring
  • each radial slot (24a) accommodates a vane (25) of suitable size.
  • the outer faces of the vane (25) are engaged with the inner surface (30) of the sliding ring (23) and slides radially in the radial slot (24a) when the rotor (24) rotates around its central axis.
  • a cam ring (26) is aligned on top of the rotor (24) where the inside faces of the vanes (25) rest.
  • Two successive vanes (25) and the inner surface (30) of the sliding ring (23) forms a working volume which when multiplied with number of the vanes (25) gives the total delivery volume of the pump during one revolution.
  • the volume of working fluid such as oil changes as pump rotates, in which, the working volumes become smaller when the vanes (25) are approaching at a delivery side (29) and the working volume becomes larger when the vanes (25) are approaching at the inlet side (28).
  • This change of volume creates pump action allowing fluid to be sucked from the inlet side (28) and delivers the working fluid through delivery side (29).
  • a main pressure chamber (33) is formed in the housing (21) at one end of the sliding ring (23) and a spring chamber (34) is formed at other end of the sliding ring (23).
  • a spring member (27) is accommodated in the spring chamber (34) which produces returning force on the sliding ring (23) to return back to maximum eccentricity position.
  • the pressure difference between the main pressure chamber (33) and the spring chamber (34) creates a driving force on the sliding ring (23), which moves to vary the eccentricity of the VDOP .
  • the oil is delivered to an engine related systems (100) through a delivery line (80) and after lubrication, oil is drained to a sump (102) through a conduit (87).
  • FIG. 2 illustrates schematic layout configuration of a pumping unit (20) according to an embodiment of the present invention.
  • the pumping unit (20) is shown therein having a hydraulic dual valve assembly (50) and an electronic control setup (51) incorporated in the pumping unit (20).
  • oil is sucked from the sump (102) through an inlet conduit (31) and delivers the oil to the engine through a delivery conduit (32).
  • a portion of oil delivered to the engine (100) is diverted through a conduit (81) to the main pressure chamber (33).
  • Another portion of the oil is diverted through a conduit (82) to the hydraulic dual valve assembly (50), which will be described below.
  • the hydraulic dual valve assembly (50) has a primary valve (53) seated against a primary spring member (55).
  • the delivery conduit (32) is connected to the hydraulic dual valve assembly (50) through the conduit (82) and a port (63).
  • delivery pressure (pi) reaches first controlled pressure (PI*)
  • PI* first controlled pressure
  • the primary valve (53) moves against the primary spring member (55) force and opens the port (57) made in the cylinder (52).
  • the primary valve (53) is seated on a secondary valve (54) through the primary spring member (55).
  • One end of a secondary spring member (56) is connected to the secondary valve (54) and the other end of the secondary spring member (56) is seated on a retainer member (64) which is placed at one end of the hydraulic dual valve assembly (50).
  • the secondary valve (54) opens the port (58) in the cylinder (52) when the pressure in the delivery line (80) reaches a second control pressure (P2*) and opens a port (59) in the cylinder (52) when the pressure (Pl) in the delivery line (80) attains high pressure (P3*).
  • a port (60) is opened when the delivery line (80) pressure (Pl) attains shutoff pressure (P4*).
  • the primary valve (53) and secondary valve (54) can be of any other shape than the ones shown in the figures.
  • the VDOP system along with the inlet conduit (31) and the delivery conduit (32) further comprises a first return conduit (88) which returns the oil back to the inlet side (28) through a conduit (89) during medium pressure conditions and also during electronic control setup (51) failure conditions.
  • the electronic control setup (51) drains the oil through a conduit (86).
  • a second return conduit (84) is provided for returning the oil back to the inlet side (28) at high pressure conditions and a relief conduit (85) is provided for relieving the oil pressure during shutoff conditions.
  • the hydraulic dual valve assembly (50) comprises a first port (57), which directs the fluid entering from conduit (82) to the spring chamber (34) through a conduit (83) and has a second port (58), which directs the oil entering from the conduit (82) to the inlet side (28) through the first return conduit (88).
  • the ports (58, 61, 62) are connected to create the first return conduit (88) which returns the oil back to the inlet side (28) through the conduit (89).
  • the hydraulic dual valve assembly (50) further includes a third port (59) that connects the conduit (82) to the inlet side (28) through the conduit (84) and a shutoff port (60) that relieves the pressure in the delivery line (80) when the pressure exceeds the shutoff pressure.
  • FIGS 3-7 illustrate different modes of operation of the VDOP system according to an embodiment of present invention.
  • the oil flows to the main pressure chamber (33) through the conduit (81) so that the main pressure chamber (33) maintains delivery line pressure (Pl).
  • the sliding ring (23) at this condition maintains the maximum eccentricity position because of the spring member (27) accommodated in the spring chamber (34).
  • the pressure (Pl) in the delivery line (80) reaches the first control pressure (Pl*)
  • the primary valve (53) moves from its initial position against the primary spring member (55) and opens the port (57).
  • a portion of working fluid flows from the delivery side (29) to the spring chamber (34) through the conduit (83), resulting in pressure increase in the spring chamber (34).
  • the slider ring (23) is at maximum eccentricity condition. This will continue for the predetermined intermediate pressure (Pi*) which is illustrated in Figure 3.
  • FIG. 4 illustrates schematic layout configuration of the VDOP system when electronic control setup (51) is activated according to an embodiment of the present invention.
  • the working of the hydraulic dual valve assembly (50) in minimum eccentricity position of the sliding ring (23) is shown therein.
  • the electronic control unit (101) sends a signal to the electronic control setup (51) and actuates the electronic control setup (51).
  • the electronic control setup (51) drains the fluid from the spring chamber (34) through the conduit (86) to the sump (102) and hence the pressure in the spring chamber (34) will be lower than the pressure in the main pressure chamber (33).
  • This pressure difference creates a driving force for the sliding ring (23) to move from its initial position to the minimum eccentricity position.
  • the working volume of the pump is reduced and the quantity of fluid is controlled according to engine demand.
  • Figure 5 illustrates the second mode of operation of the VDOP system when the pumping unit (20) reaches the second controlled pressure (P2*) according to an embodiment of the present invention.
  • the secondary valve (54) begins to move against the secondary spring member (56) and the port (58) begins to open.
  • a portion of fluid diverted from the delivery side (29) is fed back to the inlet side (28) through the first return conduit (88) to relieve the pressure in the delivery line (80).
  • the secondary valve (54) acts like a pressure relief valve of the VDOP system.
  • Figure 6 illustrates the third mode of working of the VDOP system, wherein when the pressure in the delivery line (80) reaches the high pressure (P3*), the secondary valve (54) of the hydraulic dual valve assembly (50) begins to move against the secondary spring member (56) to open the port (59) in the cylinder (52). Thus, a portion of fluid diverted from the delivery side (29) is fed back to the inlet side (28) through the second return conduit (84) to relieve the pressure in the delivery line (80). During this operational mode, the secondary valve (54) closes the port (61) to block the first return conduit (88). Thus, the secondary valve (54) acts like a pressure relief valve of the VDOP system.
  • Figure 7 illustrates the fourth mode of operation of the VDOP system when the pumping unit (20) reaches the shutoff pressure (P4*) according to an embodiment of the present invention.
  • the secondary valve (54) moves further against the secondary spring member (56) to open the port (60).
  • the fluid flows from the port (60) to the sump (102) through the conduit (85).
  • the secondary valve (54) also acts like a shutoff valve in the VDOP system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne un système de pompe à huile à débit variable (VDOP) pour fournir une quantité requise d'huile à un moteur sur la base des conditions de fonctionnement du moteur et des vitesses du moteur. Le système de VDOP comprend une unité de pompage (20) comprenant un ensemble soupape double de commande hydraulique (50) et une configuration de commande électronique (51) pour commander efficacement la quantité d'huile délivrée au moteur (100). Le système de VDOP, conjointement avec un conduit d'entrée (31) et un conduit de distribution (32), comprend deux conduits de retour (84, 88) pour permettre un retour d'huile vers un côté d'entrée (28) et un conduit de décharge (85) pour permettre le retour de l'huile vers un carter d'huile (102). La configuration de commande électronique (51) peut être actionnée sous certaines conditions de fonctionnement ou, si la configuration de commande électronique (51) tombe en panne, le système de VDOP peut toujours fonctionner par l'intermédiaire des conduits de retour (84, 88) prévus dans le système de VDOP. Ainsi, la VDOP fonctionne en continu avec son fonctionnement prévu même après une panne électronique.
PCT/IN2018/050213 2017-11-21 2018-04-13 Pompe à huile à débit variable WO2019102486A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN201741041682 2017-11-21
IN201741041682 2017-11-21

Publications (1)

Publication Number Publication Date
WO2019102486A1 true WO2019102486A1 (fr) 2019-05-31

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IN2018/050213 WO2019102486A1 (fr) 2017-11-21 2018-04-13 Pompe à huile à débit variable

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WO (1) WO2019102486A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6896489B2 (en) * 2000-12-12 2005-05-24 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US9097251B2 (en) * 2009-06-16 2015-08-04 Pierburg Pump Technology Gmbh Variable-displacement lubricant pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6896489B2 (en) * 2000-12-12 2005-05-24 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US9097251B2 (en) * 2009-06-16 2015-08-04 Pierburg Pump Technology Gmbh Variable-displacement lubricant pump

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