EP0600381A1 - A hydraulic actuating unit, in particular for controlling a valve of an internal-combustion engine - Google Patents
A hydraulic actuating unit, in particular for controlling a valve of an internal-combustion engine Download PDFInfo
- Publication number
- EP0600381A1 EP0600381A1 EP93119034A EP93119034A EP0600381A1 EP 0600381 A1 EP0600381 A1 EP 0600381A1 EP 93119034 A EP93119034 A EP 93119034A EP 93119034 A EP93119034 A EP 93119034A EP 0600381 A1 EP0600381 A1 EP 0600381A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- valve
- cavity
- unit according
- outlet opening
- 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.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
Definitions
- the present invention relates to a hydraulic actuating unit; advantageously, said unit can be used in a valve control assembly for an internal-combustion engine, in particular for the actuation of an auxiliary decompression valve.
- hydroaulic tappets which essentially comprise two members which are telescopically interconnected and which define a chamber connected with a supply of pressurised operating fluid through a non-return valve; the operating fluid, which is substantially incompressible, transmits the actuating forces from one member to the other. Any possible loosening between the two members, caused by an increase in play, is automatically compensated for by the admission of fresh fluid into said chamber through the non-return valve.
- the aforementioned devices can transmit actuating forces between a driving member, for example a rocker arm of a valve control assembly, and a driven member for example, a valve stem, thus taking up the relevant play in the manner described above.
- a driving member for example a rocker arm of a valve control assembly
- a driven member for example, a valve stem
- These devices essentially behave like rigid elements and do not enable the transmission of actuating forces between the driving member and the driven member to be eliminated, in the event of this function being required; therefore, the known devices can be effectively used, for example, for controlling the inlet and exhaust valves of an engine, which have to be actuated in all operating conditions, but not for controlling an auxiliary decompression valve which has to be actuated only in particular operating conditions.
- the object of the present invention is to devise a hydraulic actuating unit which does not have the drawbacks associated with the above-described known devices.
- the unit comprises a rocker arm having one end attached to the second member, the other end attached to the valve and a central portion adapted to co-operate with a respective cam of a camshaft.
- the reference numeral 1 generally designates an internal-combustion engine, only part of which is shown, comprising a crankcase 2 and a head 3.
- the crankcase defines a plurality of cylinders 4, only one of which is partly illustrated; each cylinder is associated with respective inlet and exhaust valves 4', only one of which is partly illustrated in dashed line in Figure 1.
- the valves 4' are controlled by a camshaft 5 accommodated in the head 3.
- Each cylinder 4 is additionally associated with an auxiliary decompression valve 6 normally co-operating in a fluidtight manner, under the action of a spring 6a, with a decompression port 7 connecting a combustion chamber 8 of the cylinder itself to an auxiliary exhaust duct 9.
- the valve 6 is adapted to be opened at the end of the compression stroke of the associated cylinder 4, when required by the operating conditions of the vehicle, so as to dissipate the compression energy before the subsequent expansion (working) stroke and, therefore, to provide a braking action.
- the auxiliary valve 6 is controlled by the camshaft 5, to which it can be selectively connected by means of an hydraulic actuating unit 10 which will be described in detail below.
- the unit 10 essentially comprises a control member 11 and a rocker 12, one end 13 of which is attached to a movable member 14 of the control member 11 and the opposite end 15 of which co-operates with a stem 16 of the valve 6.
- An intermediate part 17 of the rocker arm 12 is maintained in contact with a respective cam 18 of the camshaft 5 and is of arcuate shape, with its convexity facing the shaft 5.
- control member 11 is illustrated in Figures 2 and 3, to which reference will be made in the following.
- Said member 11 comprises a fixed outer casing 19 accommodated in a seating 20 provided in the head 3.
- the casing 19 comprises an outer tubular body 24 and a cup-shaped body 25 provided with a base wall 26 and with a cylindrical wall 27 defining an inner cavity 28 and having an end opening 29; the cup-shaped body 25, the axial length of which is smaller than that of the body 24, is securely accommodated inside the body 24 so that the base wall 26 defines an intermediate transverse wall of the casing 19 and so that an end section of the wall 27 is coplanar with an end section of the body 24 itself.
- the wall 26 axially separates the cavity 28 from a cavity 33 defined by the portion of the body 24 not occupied by the body 25.
- the above-mentioned movable element 14 is slidably mounted inside the cavity 33 and essentially comprises a hollow piston 30 provided with a spherical head 31 integral therewith and extending axially to project towards the outside of the cylindrical body 24; said spherical head engages a corresponding seating 32 provided in the end 13 of the rocker arm 12 and forms a ball joint therewith.
- the piston 30 axially delimits with the wall 26 of the body 25 a chamber 34 and is urged towards the end of the body 24 by a helical spring 35 accommodated in the chamber 34 itself, the stiffness of which is much lower than the spring 6a of the valve 6; a resilient ring 36 mounted inside the body 24 serves as an axial stop for the movable member 14.
- the position of the movable member 14 is indicated in solid line in the absence of external loads or constraints, whereas there is indicated in dashed line the position effectively assumed in operation, when the head 31 is connected with the rocker arm 12.
- Two radial holes 37, 38 are provided in the cylindrical wall 27 of the body 25 and are respectively disposed a lesser and greater distance from the end opening 29 in the body 25 itself.
- the hole 37 communicates with a corresponding outlet hole 39 provided in the cylindrical body 24; an outer longitudinal slot 40 extends from the hole 39 and is extended to the outside of the seating 20.
- the hole 38 communicates through an outer longitudinal slot 41 of the body 25 with the above-mentioned chamber 34.
- the interior of the cavity 28 of the body 25 accommodates a cylindrical member 43 so that it can slide axially therein; said cylindrical member is urged by a spring 44 compressed between itself and the wall 26 of the body 25 towards the end opening 29 of the cavity 38; a resilient ring 45 mounted inside the wall 27 in the vicinity of the opening 29 forms an axial stop for the member 43.
- Said member 43 has an axial cavity 46 communicating with the opening 29 through a non-return valve 47, and an intermediate circumferential slot 48 which communicates with the axial cavity 46 by means of a plurality of radial holes 49.
- the cavity 46 has two sections 46a, 46b of different diameter, of which the section of larger diameter (46b) opens towards the wall 26, and forming between them an axial shoulder 51, the sections 46a, 46b of the cavity are separated from one another by a disc 52 clamped against the shoulder 51 and forming a support for the above-mentioned spring 44.
- the section 46a is connected with the slot 40 by a radial through-hole 50 of the casing 19.
- the non-return valve 47 comprises a ball 53 urged by a spring 56 into contact with a conical seating 54 provided between the cavity 46 and an axial hole 55 of the member 43 communicating with the opening 29; the spring 56 is compressed between the ball 53 and said disc 52.
- the member 43 is movable under the pressure of a hydraulic fluid, as will be described below, and against the action of the spring 44 from a first rest position, shown in Figure 2, in which it is in contact with the ring 45, and a second position, shown in Figure 3, in which it is contact with the wall 26.
- the circumferential slot 48 of the member 43 communicates with both the holes 37 and 38 and, therefore, the chamber 34 and the cavity 46a are connected with the outlet hole 39; in the second position, the slot 48 communicates with the hole 38 but not with the hole 37.
- the opening 29 of the body 25 of the member 11 communicates with a duct 60 provided in the engine head 3 and connected to a lubricating circuit of the engine itself by a solenoid valve, which is normally closed. Therefore, the engine oil constitutes the operating fluid for the control member 11.
- the mode of operation of the actuating unit 10 is the following.
- the member 43 When the duct 60 is not pressurised, the member 43 is situated in the rest position shown in Figure 2, under the action of the spring 44.
- the movable member 14 maintains the rocker arm 12 in contact with the camshaft 5 under the action of the spring 35, with a suitably reduced contact load defined by the low stiffness of the spring itself.
- the movable member 14 is free to oscillate along the tubular body 24 under the pressure of the rocker arm 12, since the chamber 34 communicates, as indicated above, with the outlet hole 39.
- the valve 6 remains closed, since the stiffness of the associated spring is much greater than that of the spring 35.
- the cam 18 is timed so that the opening of the valve 6 takes place at the end of the compression stroke in the cylinder, so as to discharge the air compressed during said stroke and thus prevent the compression energy from being returned during the expansion stroke, thus producing engine work.
- FIG 4 illustrates schematically an actuating unit 10 used in an engine 1' provided with a camshaft 5' in the crankcase.
- the unit 10 is substantially equal to that described but is mounted inverted and the end 15 of the rocker arm actuates a transmission rod 61 which controls in known manner a rocker arm 62 of conventional type which, in turn, actuates the valve 6.
- the mode of operation of the unit 10 is entirely analogous to that described.
- control member 11 not only performs all the controlled of a conventional hydraulic tappet, in particular the automatic take-up of play, but can also be operated hydraulically in such a way so to activate or deactivate selectively the actuation of the valve; moreover, the use of a rocker arm 12, the member 11 of which, when activated, constitutes a rigid fulcrum, enables the actuating loads to be transmitted mechanically and, therefore, to obtain an optimum dynamic response, particularly in an embodiment using an overhead camshaft.
- rocker arm 12 may be omitted or replaced with another suitable transmission member and the control member can be interposed directly between a driving member and a driven member.
- the unit 10 and, in particular, the control member 11 can be used not only to control a valve of an engine but also in any other engineering application, in which there is the requirement of interconnecting a driving member and a driven member in a selective manner and of automatically taking up the play between said members.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
- The present invention relates to a hydraulic actuating unit; advantageously, said unit can be used in a valve control assembly for an internal-combustion engine, in particular for the actuation of an auxiliary decompression valve.
- Devices are known, normally termed "hydraulic tappets", which essentially comprise two members which are telescopically interconnected and which define a chamber connected with a supply of pressurised operating fluid through a non-return valve; the operating fluid, which is substantially incompressible, transmits the actuating forces from one member to the other. Any possible loosening between the two members, caused by an increase in play, is automatically compensated for by the admission of fresh fluid into said chamber through the non-return valve.
- The aforementioned devices can transmit actuating forces between a driving member, for example a rocker arm of a valve control assembly, and a driven member for example, a valve stem, thus taking up the relevant play in the manner described above. These devices essentially behave like rigid elements and do not enable the transmission of actuating forces between the driving member and the driven member to be eliminated, in the event of this function being required; therefore, the known devices can be effectively used, for example, for controlling the inlet and exhaust valves of an engine, which have to be actuated in all operating conditions, but not for controlling an auxiliary decompression valve which has to be actuated only in particular operating conditions.
- The object of the present invention is to devise a hydraulic actuating unit which does not have the drawbacks associated with the above-described known devices.
- This object is achieved by the present invention in that it relates to a hydraulic actuating unit of the type comprising:
- a first member and a second member which are telescopically interconnected and which define a chamber adapted to contain a hydraulic fluid; and
- a non-return valve communicating with said chamber and adapted to be connected with a supply duct for said hydraulic fluid so as to allow said fluid to flow towards said chamber but to prevent it from flowing back towards said supply duct;
characterised by comprising a third member telescopically connected to said first member and provided with hydraulic connecting means, said first member defining an outer casing in which are accommodated said second member and said third member and being provided with an outlet opening, said third member being movable under the pressure of said hydraulic fluid and against the action of first resilient means from a first rest position, in which said hydraulic connecting means connect said chamber with said outlet opening, into a second operating position in which said chamber is isolated from said outlet opening. - According to a preferred embodiment of the present invention, which is particularly suitable for controlling an auxiliary decompression valve of an internal-combustion engine, the unit comprises a rocker arm having one end attached to the second member, the other end attached to the valve and a central portion adapted to co-operate with a respective cam of a camshaft.
- With a view to a better understanding of the present invention, a preferred embodiment thereof will be described below, non-restrictively by way of example, with reference to the accompanying drawings, wherein:
- Figure 1 is a partial section through an internal-combustion engine provided with a hydraulic actuating unit designed in accordance with the present invention;
- Figure 2 and Figure 3 are axial sections, on an enlarged scale, of a control member of the unit in Figure 1, in two different operating positions, and
- Figure 4 illustrates schematically an internal-combustion engine of different type, provided with an actuating unit analogous to that in Figure 1.
- Referring now to Figure 1, the reference numeral 1 generally designates an internal-combustion engine, only part of which is shown, comprising a
crankcase 2 and a head 3. The crankcase defines a plurality of cylinders 4, only one of which is partly illustrated; each cylinder is associated with respective inlet and exhaust valves 4', only one of which is partly illustrated in dashed line in Figure 1. The valves 4' are controlled by acamshaft 5 accommodated in the head 3. - Each cylinder 4 is additionally associated with an
auxiliary decompression valve 6 normally co-operating in a fluidtight manner, under the action of aspring 6a, with a decompression port 7 connecting a combustion chamber 8 of the cylinder itself to an auxiliary exhaust duct 9. Thevalve 6 is adapted to be opened at the end of the compression stroke of the associated cylinder 4, when required by the operating conditions of the vehicle, so as to dissipate the compression energy before the subsequent expansion (working) stroke and, therefore, to provide a braking action. - The
auxiliary valve 6 is controlled by thecamshaft 5, to which it can be selectively connected by means of an hydraulic actuatingunit 10 which will be described in detail below. - The
unit 10 essentially comprises acontrol member 11 and a rocker 12, oneend 13 of which is attached to amovable member 14 of thecontrol member 11 and the opposite end 15 of which co-operates with astem 16 of thevalve 6. An intermediate part 17 of the rocker arm 12 is maintained in contact with arespective cam 18 of thecamshaft 5 and is of arcuate shape, with its convexity facing theshaft 5. - The
control member 11 is illustrated in Figures 2 and 3, to which reference will be made in the following. - Said
member 11 comprises a fixedouter casing 19 accommodated in a seating 20 provided in the head 3. Thecasing 19 comprises an outertubular body 24 and a cup-shaped body 25 provided with abase wall 26 and with acylindrical wall 27 defining aninner cavity 28 and having an end opening 29; the cup-shaped body 25, the axial length of which is smaller than that of thebody 24, is securely accommodated inside thebody 24 so that thebase wall 26 defines an intermediate transverse wall of thecasing 19 and so that an end section of thewall 27 is coplanar with an end section of thebody 24 itself. - Therefore, the
wall 26 axially separates thecavity 28 from acavity 33 defined by the portion of thebody 24 not occupied by thebody 25. The above-mentionedmovable element 14 is slidably mounted inside thecavity 33 and essentially comprises ahollow piston 30 provided with aspherical head 31 integral therewith and extending axially to project towards the outside of thecylindrical body 24; said spherical head engages acorresponding seating 32 provided in theend 13 of the rocker arm 12 and forms a ball joint therewith. - The
piston 30 axially delimits with thewall 26 of the body 25 achamber 34 and is urged towards the end of thebody 24 by ahelical spring 35 accommodated in thechamber 34 itself, the stiffness of which is much lower than thespring 6a of thevalve 6; aresilient ring 36 mounted inside thebody 24 serves as an axial stop for themovable member 14. In Figure 2 the position of themovable member 14 is indicated in solid line in the absence of external loads or constraints, whereas there is indicated in dashed line the position effectively assumed in operation, when thehead 31 is connected with the rocker arm 12. - Two
radial holes cylindrical wall 27 of thebody 25 and are respectively disposed a lesser and greater distance from the end opening 29 in thebody 25 itself. Thehole 37 communicates with acorresponding outlet hole 39 provided in thecylindrical body 24; an outerlongitudinal slot 40 extends from thehole 39 and is extended to the outside of the seating 20. Thehole 38 communicates through an outerlongitudinal slot 41 of thebody 25 with the above-mentionedchamber 34. - The interior of the
cavity 28 of thebody 25 accommodates acylindrical member 43 so that it can slide axially therein; said cylindrical member is urged by aspring 44 compressed between itself and thewall 26 of thebody 25 towards the end opening 29 of thecavity 38; aresilient ring 45 mounted inside thewall 27 in the vicinity of the opening 29 forms an axial stop for themember 43. - Said
member 43 has anaxial cavity 46 communicating with the opening 29 through anon-return valve 47, and an intermediatecircumferential slot 48 which communicates with theaxial cavity 46 by means of a plurality ofradial holes 49. In particular, thecavity 46 has twosections 46a, 46b of different diameter, of which the section of larger diameter (46b) opens towards thewall 26, and forming between them anaxial shoulder 51, thesections 46a, 46b of the cavity are separated from one another by adisc 52 clamped against theshoulder 51 and forming a support for the above-mentionedspring 44. The section 46a is connected with theslot 40 by a radial through-hole 50 of thecasing 19. - The
non-return valve 47 comprises aball 53 urged by aspring 56 into contact with aconical seating 54 provided between thecavity 46 and anaxial hole 55 of themember 43 communicating with theopening 29; thespring 56 is compressed between theball 53 and saiddisc 52. Themember 43 is movable under the pressure of a hydraulic fluid, as will be described below, and against the action of thespring 44 from a first rest position, shown in Figure 2, in which it is in contact with thering 45, and a second position, shown in Figure 3, in which it is contact with thewall 26. - In said first position, the
circumferential slot 48 of themember 43 communicates with both theholes chamber 34 and the cavity 46a are connected with theoutlet hole 39; in the second position, theslot 48 communicates with thehole 38 but not with thehole 37. - Referring still to Figure 1, the
opening 29 of thebody 25 of themember 11 communicates with aduct 60 provided in the engine head 3 and connected to a lubricating circuit of the engine itself by a solenoid valve, which is normally closed. Therefore, the engine oil constitutes the operating fluid for thecontrol member 11. - The mode of operation of the actuating
unit 10 is the following. - When the
duct 60 is not pressurised, themember 43 is situated in the rest position shown in Figure 2, under the action of thespring 44. Themovable member 14 maintains the rocker arm 12 in contact with thecamshaft 5 under the action of thespring 35, with a suitably reduced contact load defined by the low stiffness of the spring itself. During the rotation of thecamshaft 5, themovable member 14 is free to oscillate along thetubular body 24 under the pressure of the rocker arm 12, since thechamber 34 communicates, as indicated above, with theoutlet hole 39. Thevalve 6 remains closed, since the stiffness of the associated spring is much greater than that of thespring 35. - When the
duct 60 is pressurised, thus opening the associated solenoid valve, themembrane 43 is displaced under the hydraulic pressure from the first position to the second position (Figure 3) and the oil contained in themember 11 is isolated from theoutlet hole 39. At this point, the oil flows from theduct 60 through thenon-return valve 47 until it completely fills the cavity 46a and thechamber 34, after which, because of the incompressibility of oil, themovable member 14 constitutes a rigid restraint for the rocker arm 12. Consequently, the actuating force exerted by thecam 18 induces rotation of the rocker arm 12 about thehead 31 of themember 14 and, therefore, the opening of thevalve 6 under the pressure of the end 15 of the rocker arm 12. - The
cam 18 is timed so that the opening of thevalve 6 takes place at the end of the compression stroke in the cylinder, so as to discharge the air compressed during said stroke and thus prevent the compression energy from being returned during the expansion stroke, thus producing engine work. - The control of the
unit 10 and any subsequent utilisation of the compressed air are not described, since they do not form part of the subject-matter of the present invention. - Figure 4 illustrates schematically an actuating
unit 10 used in an engine 1' provided with a camshaft 5' in the crankcase. Theunit 10 is substantially equal to that described but is mounted inverted and the end 15 of the rocker arm actuates atransmission rod 61 which controls in known manner arocker arm 62 of conventional type which, in turn, actuates thevalve 6. The mode of operation of theunit 10 is entirely analogous to that described. - The advantages which can be obtained by the present invention are evident from a study of the features of the
unit 10 designed in accordance therewith. Above all, thecontrol member 11 not only performs all the controlled of a conventional hydraulic tappet, in particular the automatic take-up of play, but can also be operated hydraulically in such a way so to activate or deactivate selectively the actuation of the valve; moreover, the use of a rocker arm 12, themember 11 of which, when activated, constitutes a rigid fulcrum, enables the actuating loads to be transmitted mechanically and, therefore, to obtain an optimum dynamic response, particularly in an embodiment using an overhead camshaft. - Finally, it is evident that modifications and variations can be made to the
unit 10, without thereby departing from the scope of protection of the present invention. In particular, the rocker arm 12 may be omitted or replaced with another suitable transmission member and the control member can be interposed directly between a driving member and a driven member. - Additionally, the
unit 10 and, in particular, thecontrol member 11 can be used not only to control a valve of an engine but also in any other engineering application, in which there is the requirement of interconnecting a driving member and a driven member in a selective manner and of automatically taking up the play between said members.
Claims (9)
- A hydraulic actuating unit (10) of the type comprising:- a first member (19) and a second member (14) which are telescopically interconnected and which define a chamber (34) adapted to contain a hydraulic fluid; and- a non-return valve (47) communicating with said chamber (34) and adapted to be connected with a supply duct (60) for said hydraulic fluid so as to allow said fluid to flow towards said chamber (34) but to prevent it from flowing back towards said supply duct (60);
characterised by comprising a third member (43) telescopically connected to said first member (19) and provided with hydraulic connecting means (46a, 48, 49), said first member (19) defining an outer casing in which are accommodated said second member (14) and said third member (43) and being provided with an outlet opening (37, 39), said third member (43) being movable under the pressure of said hydraulic fluid and against the action of first resilient means (44) from a first rest position, in which said connecting means (46a, 48, 49) connect said chamber with said outlet opening (37 39), into a second operating position in which said chamber (34) is isolated from said outlet opening (37, 39). - A unit according to Claim 1, characterised in that said non-return valve (47) is provided inside said third member (43).
- A unit according to Claim 1 or 2, characterised in that said outer casing (19) has an intermediate transverse wall (26) interposed between said chamber (34) and a first cavity (28) accommodating said third member (43) and adapted to be connected with said supply duct (60).
- A unit according to Claim 3, characterised in that said first resilient means (44) are interposed between said transverse wall (26) and said third member (43).
- A unit according to Claim 3 or 4, characterised in that said hydraulic connecting means for said third member (43) comprise a second cavity (46a) communicating with said first cavity (28) of said casing (19) through said non-return valve (47), an outer circumferential slot (48) and at least one radial hole (49) communicating with said second cavity (46a) and with said slot (48); said outer casing having a passage (38, 41) connecting said first cavity with said chamber (34) and axially spaced apart along said first cavity (28) with respect to said outlet opening (37, 39), so that said slot (48) communicates with said passage (38) and with said outlet opening (37) in said first position of said third member (43) and only with said passage (38) in said second position of said third member (43).
- A unit according to any one of the preceding Claims, characterised by comprising second resilient means (35) urging said second member (14) in the opposite direction to said third member (43), and axial stop means (36) for said second member (14).
- A unit according to any one of the preceding Claims for controlling a valve (6) of an internal-combustion engine (1), characterised by comprising a rocker arm (12) having a first end portion (13) connected to said second member (14), a second end portion (15) connected to said valve (6) and an intermediate portion adapted to co-operate with a cam (18) of a camshaft (5) of said engine (1).
- A unit according to Claim 7, characterised in that said first end portion (13) of said rocker arm (12) and said second member are connected to one another by means of ball-joint means (31, 32).
- An internal-combustion engine comprising a plurality of cylinders (4) provided with respective inlet and exhaust valves (4') and with an auxiliary decompression valve (6), and with a camshaft (5) for operating at least said inlet and exhaust valves (4'), characterised in that said auxiliary valve (6) is connected with a respective cam (18) of said shaft (5) by means of a hydraulic actuating unit (10) according to any one or the preceding Claims.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITTO920972A IT1257926B (en) | 1992-11-30 | 1992-11-30 | HYDRAULIC DRIVE UNIT, IN PARTICULAR FOR THE CONTROL OF A VALVE OF AN INTERNAL COMBUSTION ENGINE. |
ITTO920972 | 1992-11-30 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0600381A1 true EP0600381A1 (en) | 1994-06-08 |
EP0600381B1 EP0600381B1 (en) | 1997-03-26 |
Family
ID=11410895
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93119034A Expired - Lifetime EP0600381B1 (en) | 1992-11-30 | 1993-11-25 | A hydraulic actuating unit, in particular for controlling a valve of an internal-combustion engine |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0600381B1 (en) |
DE (1) | DE69309229T2 (en) |
ES (1) | ES2100428T3 (en) |
IT (1) | IT1257926B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1612376A1 (en) * | 2004-06-29 | 2006-01-04 | Eaton S.R.L. | Open ended mini lash adjuster |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4050435A (en) * | 1975-12-02 | 1977-09-27 | Harold L. Fuller, Jr. | Valve control for cylinder cutout system |
US4337739A (en) * | 1980-03-24 | 1982-07-06 | Jordan Edgar R | Valve control mechanism for internal combustion engines |
DE4000531A1 (en) * | 1990-01-10 | 1990-06-13 | Roland Schmidt | Adjusting engine valve stroke - involves hydraulic cylinder-piston closure device |
-
1992
- 1992-11-30 IT ITTO920972A patent/IT1257926B/en active IP Right Grant
-
1993
- 1993-11-25 EP EP93119034A patent/EP0600381B1/en not_active Expired - Lifetime
- 1993-11-25 ES ES93119034T patent/ES2100428T3/en not_active Expired - Lifetime
- 1993-11-25 DE DE69309229T patent/DE69309229T2/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4050435A (en) * | 1975-12-02 | 1977-09-27 | Harold L. Fuller, Jr. | Valve control for cylinder cutout system |
US4337739A (en) * | 1980-03-24 | 1982-07-06 | Jordan Edgar R | Valve control mechanism for internal combustion engines |
DE4000531A1 (en) * | 1990-01-10 | 1990-06-13 | Roland Schmidt | Adjusting engine valve stroke - involves hydraulic cylinder-piston closure device |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1612376A1 (en) * | 2004-06-29 | 2006-01-04 | Eaton S.R.L. | Open ended mini lash adjuster |
WO2006003514A1 (en) * | 2004-06-29 | 2006-01-12 | Eaton Corporation | Open ended mini lash adjuster |
US7644693B2 (en) | 2004-06-29 | 2010-01-12 | Eaton Corporation | Open ended mini lash adjuster |
Also Published As
Publication number | Publication date |
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EP0600381B1 (en) | 1997-03-26 |
ES2100428T3 (en) | 1997-06-16 |
ITTO920972A0 (en) | 1992-11-30 |
ITTO920972A1 (en) | 1994-05-30 |
DE69309229D1 (en) | 1997-04-30 |
IT1257926B (en) | 1996-02-19 |
DE69309229T2 (en) | 1997-07-31 |
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