CN102146916A - Variable displacement pump, oil jet and lublicating system using variable displacement pump - Google Patents

Abstract

The invention provides a variable displacement pump, which can inhibit the energy consumption in the initial period of the oil discharge. The variable displacement pump has a pump structure which allows discharge of the oil guided to a plurality of pump chambers 13 from an inlet 7 according to the volumn variation of the pump chamber from an outlet 8; when the discharge pressure supplied into a control oil chamber 16 reaches to a first discharge pressure Pf, a cam ring moves a prescribed distance to a direction and when the discharge pressure becomes a second discharge pressure Ps higher than the first discharge pressure Pf, the cam ring moves further to the direction, thereby changing the discharge pressure of the pump. The first discharge pressure is set to the pressure lower than that opening a ball valve 46 through compression deformation of a valve spring 50 of an oil nozzle 30, thereby preventing the energy consumption when the discharge pressure is low.

Description

Variable displacement pump, the lubrication system of using this variable displacement pump and oil nozzle

Technical field

The present invention relates to for example employed variable displacement pump of internal-combustion engine, the lubrication system of using this variable displacement pump and the oil nozzle of Motor Vehicle.

Background technique

As existing variable displacement pump, the known variable displacement pump that has following patent documentation 1 to be put down in writing.

This existing variable displacement pump possesses first spring that always elastic force acted on the cam ring and apply second spring of elastic force to the direction opposite with the elastic force of above-mentioned first spring when above-mentioned cam ring has moved that authorized pressure is above, rely on the relative elastic force of these two springs that the eccentric state of above-mentioned cam ring is changed to constitute two stage mode, thereby the discharge flow rate characteristic is changed to constitute two stage mode.

In addition, the elastic force that this variable displacement pump is resisted above-mentioned first spring according to above-mentioned cam ring moves first head pressure before, removes the locking states of valve timing control gear.

Patent documentation 1:(Japan) spy opens the 2009-97424 communique

But, supply with under the situation of oily this device above-mentioned existing variable displacement pump being applicable to the oil nozzle that cools off to the piston that is used for internal-combustion engine, if with above-mentioned this stage of first head pressure of variable displacement pump is that oil before above-mentioned cam ring moves is supplied with to oil nozzle, then might cause obtaining consuming unnecessary energy before the head pressure that is used to above-mentioned cam ring is moved.

Summary of the invention

The object of the present invention is to provide a kind of variable displacement pump that can suppress the energy consumption at oily discharge initial stage.

Variable displacement pump of the present invention possesses: the pump structure body, and it is driven by internal-combustion engine rotation, thereby will discharge from discharge portion according to the volume-variation of described working room from the oil that suction portion flows into a plurality of working rooms; Movable part, it makes from the flow minimizing of the oil of described discharge portion discharge by moving to a direction; And control gear, when the head pressure of described oil reaches first head pressure, described control gear makes described movable part move established amount to a direction, when the head pressure of described oil reaches than high second head pressure of described first head pressure, described control gear further moves described movable part to a direction, wherein, described first head pressure is set at the low pressure of pressure that begins to spray oil than described oil nozzle.

According to the present invention, can suppress the energy consumption at oily discharge initial stage.

Description of drawings

Fig. 1 is the exploded perspective view of the variable displacement pump of first mode of execution;

Fig. 2 is the plan view after the cover of the variable displacement pump of present embodiment is pulled down;

Fig. 3 is the A-A sectional drawing of Fig. 2;

Fig. 4 is the plan view of the expression pump case that present embodiment provided;

Fig. 5 is the Action Specification figure of present embodiment;

Fig. 6 is the Action Specification figure of present embodiment;

Fig. 7 is first, second helical spring spring displacement of expression present embodiment and the performance plot that spring is set the relation of load;

Fig. 8 is the performance plot of the relation of existing discharge hydraulic pressure of expression and engine speed;

Fig. 9 is a sectional arrangement drawing of having used the internal-combustion engine of the oil nozzle that present embodiment provided;

Figure 10 is the stereogram of same oil nozzle;

Figure 11 (A) is the sectional arrangement drawing that closes the valve state of expression oil nozzle, (B) is the sectional arrangement drawing of opening the valve state of the same oil nozzle of expression;

Figure 12 is that the valve timing control gear that present embodiment is provided is cut the overall diagram of representing open;

Figure 13 is the sectional drawing of the blade part of the same valve timing control gear of expression to the rotational position of retardation angle sideway swivel;

Figure 14 is the sectional drawing of the blade part of the same valve timing control gear of expression to the rotational position of advance side rotation;

Figure 15 is the sectional drawing of the locking mechanism of the same valve timing control gear of expression;

The effect of each mechanism when Figure 16 represents engine stoping operation is that Action Specification figure, (B) that the expression blade part is rotated the state that is controlled at retardation angle side are that Action Specification figure, (C) that expression locking piston is sticked in the state in locking hole is the Action Specification figure that the expression slide valve is maintained at the state of leftward position (A);

The effect of each mechanism when Figure 17 represents to rotate ignition key is that Action Specification figure, (B) that the expression blade part is rotated the state that is controlled at retardation angle side are that Action Specification figure, (C) of the state after expression locking piston is extracted from the locking hole is the Action Specification figure that the expression slide valve is maintained at the state of leftward position (A);

Figure 18 represents that motor forwards the effect of each mechanism in medium speed when zone to, (A) is that Action Specification figure, (B) that the expression blade part is rotated the state that is controlled at advance side are that Action Specification figure, (C) of the state after expression locking piston is extracted from the locking hole is the Action Specification figure that the expression slide valve is maintained at the state of right positions;

The effect of each mechanism when Figure 19 represents motor no-load running is that Action Specification figure, (B) that the expression blade part is rotated the state that is controlled at the retardation angle side are that Action Specification figure, (C) of the state extracted from the locking hole of expression locking piston is the Action Specification figure that the expression slide valve is maintained at the state of leftward position (A);

Figure 20 is the plan view of the state after the cover of the variable displacement pump of second mode of execution is pulled down in expression;

Figure 21 is the exploded perspective view of formation of the variable displacement pump of expression the 3rd mode of execution;

Figure 22 is for same variable displacement pump, and the plan view after cover is pulled down in expression is the figure of state of the offset maximum of expression cam ring;

Figure 23 is for same variable displacement pump, and the plan view after cover is pulled down in expression is the figure of state of the offset minimum of expression cam ring;

Figure 24 is the sectional arrangement drawing of the same variable displacement pump of expression;

Figure 25 is the plan view of the inside of the expression housing that present embodiment provided;

Figure 26 is the sectional arrangement drawing of the state of expression solenoid valve that present embodiment provided when not switching on;

The sectional arrangement drawing of the state when Figure 27 is the energising of the expression solenoid valve that present embodiment provided;

Figure 28 is the hydraulic circuit diagram of the variable displacement pump of present embodiment;

Figure 29 is that expression is about the engine speed of the variable displacement pump of present embodiment and the plotted curve of the relation between the hydraulic pressure;

Figure 30 is the sectional arrangement drawing of the state of the solenoid valve after the expression distortion when not switching on;

Figure 31 is the sectional arrangement drawing of state in solenoid valve when energising of the same variation of expression;

Figure 32 is the exploded perspective view of formation of the variable displacement pump of expression four embodiment of the invention;

Figure 33 is the plan view of the state after the cover of the variable displacement pump of same mode of execution is pulled down in expression, is the figure of state of the offset maximum of expression cam ring;

Figure 34 is the plan view of the state after the cover of the variable displacement pump of same mode of execution is pulled down in expression, is the figure of state of the offset minimum of expression cam ring;

Figure 35 is the plan view of the cover of same mode of execution;

Figure 36 is the rear view of the cover of same mode of execution;

Figure 37 is the sectional arrangement drawing of off working state of the hydraulic directio switching valve that variable displacement pump provided of fifth embodiment of the invention;

Figure 38 is the sectional arrangement drawing of working state of the hydraulic directio switching valve of the same mode of execution of expression;

Figure 39 is the hydraulic circuit diagram of the variable displacement pump of same mode of execution;

Figure 40 is the plotted curve of the relation of the engine speed of variable displacement pump of the same mode of execution of expression and hydraulic pressure.

Description of reference numerals

01 variable displacement pump

1,111 pump cases

The 1a bottom surface

2,112 covers

The 2a inner side surface

3,114 live axles

4,115 rotors

5,117 cam rings

5a cam ring inner peripheral surface

5b pivot protuberance

7,121 suction ports

8,122 exhaust ports

9 trunnions

11,116 blades

13,120 pump chambers

14 sealed members

15 elastic members

16 control grease chambeies

16a, 131 first control grease chambeies

16b, 132 second control grease chambeies

17,117b arm

19 first spring accommodation chambers

20 first helical springs

21 second spring accommodation chambers

22 second helical springs

30 oil nozzles

46 ball valve bodies (valve body)

50 valve spring (force application part)

Embodiment

Below, describe the mode of execution of variable displacement pump of the present invention in detail based on accompanying drawing.

The variable displacement pump 01 of each mode of execution is to each slide part supplying lubricating oil of motor vehicle internal combustion engine, and, via oil nozzle to the piston supplying lubricating oil, and then also to the locking mechanism supplying lubricating oil of valve timing control gear and this valve timing control gear.

[first mode of execution]

As Fig. 1～shown in Figure 3, variable displacement pump 01 possesses: be located at the front end of cylinder block of internal-combustion engine and the end opening pump case that the round-ended cylinder shape is arranged 1 by cover 2 sealings, connect the inside center portion of this pump case 1 and the live axle 3 that drives by the crankshaft rotating of motor, rotation is incorporated in the rotor 4 that the inside of above-mentioned pump case 1 and central part and above-mentioned live axle 3 combine freely, the movable part that swing is configured in the outer circumferential side of this rotor 4 freely is a cam ring 5, be configured in the less a pair of blade ring 6 of diameter of the bi-side of perimembranous side in the above-mentioned rotor 4 sliding freely, 6.

Above-mentioned pump case 1 is formed by aluminum alloy material, as shown in Figure 4, the bottom surface 1a of concavity slides thereon owing to cam ring 5 axial sides, therefore, the planeness of this bottom surface 1a or surface roughness etc. are processed accurately, and sliding scale forms by machining.

In addition, assigned position at pump case 1 inner peripheral surface, be formed with the pivot groove 1c that the hole of an end of the trunnion 9 of the pivot point that becomes above-mentioned cam ring 5 inserting and cross section are semi-circular shape, and, than the straight line M (hereinafter referred to as " cam ring reference line ") at the center (axle center of live axle 3) of axle center that connects trunnion 9 and pump case 1 more by the left side top position, among Fig. 2 in week, be formed with sealing surface 1s with the formation of circular arc concavity.

One end of described sealing surface 1s upper end side in the figure of control described later grease chamber 16 with sealed member described later 14 sliding contacts that are arranged on described cam ring 5, and seals jointly.Sealing face 1s forms the arc surface shape that forms with predetermined radius as shown in Figure 4.

In addition, as shown in Figure 4,, be formed with suction port 7, and roughly relatively be formed with exhaust port 8 respectively at the right half part of live axle 3 in the left side of live axle 3 at the bottom surface of pump case 1 1a.

As shown in Figure 4, the suction port 7a of the oil that above-mentioned suction port 7 is interior with sucking not shown food tray is communicated with, on the other hand, exhaust port 8 is communicated with via each slide part of not shown main oil gallery and internal-combustion engine and as for example valve timing control gear of variable valve gear from tap hole 8a.

Above-mentioned suction port 7 is made of the outside oral area 7c of circular-arc inboard oral area 7b and essentially rectangular, and on the other hand, exhaust port 8 constitutes by circular-arc inboard oral area 8b with outside oral area 8c that above-mentioned tap hole 8a directly is communicated with.

In addition, bearing hole 1f at the live axle 3 of the substantial middle that is formed at above-mentioned bottom surface 1a, so that the oil of discharging from above-mentioned exhaust port 8 forms via the mode that the front end groove 10a that forms the narrow roughly L shaped oil supply 10 of width supplies with, and, supply with oil from the opening of above-mentioned oil supply 10 to the bi-side of above-mentioned rotor 4 and the side of blade described later 11, to guarantee lubricity.

As Fig. 1, shown in Figure 3, above-mentioned cover 2 forms the heavy wall planar, forming the inner side surface 2a of general planar shape, similarly be formed with suction port 7 ' and the exhaust port 8 ' that is communicated with respectively with suction port 7 and exhaust port 8 with the bottom surface 1a of above-mentioned pump case 1, and, in the end of inner side surface 2a, connect the pin-and-hole 2b of the other end insertion that is formed with above-mentioned trunnion 9.In addition, in the substantial middle position of cover 2, connect and to be formed with above-mentioned live axle 3 and to penetrate and rotate the bearing hole 2c that is supported freely.

And this cover 2 carries out the location of circumferencial direction via a plurality of locating stud IP shown in Figure 1 to pump case 1, is installed on the pump case 1 with a plurality of bolt B simultaneously.

Above-mentioned live axle 3 relies on the rotating force that comes from the bent axle transmission to make rotor 4 along the rotation of the clockwise direction Fig. 2, becomes with left-half among this live axle 3 figure that is the center to suck the zone, and right half part becomes discharging area.

As shown in Figures 1 and 2, above-mentioned rotor 4 outwards is to slide in seven slit 4a of radial formation at central side internally respectively free to advance or retreatly and maintains seven blades 11, and, at the base end part of above-mentioned each slit 4a, be formed with the back pressure chamber 12 of the cross section circular that imports the discharge hydraulic pressure that above-mentioned exhaust port 8 discharged respectively.In addition, be formed with circular groove 4b, the 4b that keeps above-mentioned two blade rings 6,6 in interior all lateral deviation heart rotations freely at the axial two end part of rotor 4.

As shown in Figure 2, each the cardinal extremity edge of the inboard of above-mentioned each blade 11 and the outer circumferential face of above-mentioned a pair of blade ring 6,6 slip, and the inner peripheral surface 5a of each front-end edge and above-mentioned cam ring 5 freely slips.

In addition, between the inner side surface 2a of the bottom surface 1a of the outer circumferential face of the inner peripheral surface 5a of 11 in each blade and cam ring 5 and rotor 4, pump case 1, cover 2, being divided into a plurality of working rooms with fluid-tight fashion is fan-shaped pump chamber 13.Above-mentioned each blade ring 6 constitutes and above-mentioned each blade 11 is radially outward extrudes.

Above-mentioned cam ring 5 is formed integrally as roughly cylindric by the sintering metal of easy processing, in Fig. 2, right outer fix on the above-mentioned cam ring reference line X of outer circumferential face is formed with pivot protuberance 5b, at the central outer side surface of this pivot protuberance 5b, be formed with vertically with above-mentioned pivot channel 1c and jointly make trunnion 9 intercalations and prop up groove 5k as the semicircular pivot in the cross section of eccentric swing fulcrum.

In addition, the position of cam ring 5 above more leaning on than above-mentioned cam ring reference line X is the position, upper left side among Fig. 2, form the roughly lug boss 5c of inverted U-shaped shape, be formed with the arc surface 5d of the circular arc convex relative with above-mentioned sealing surface 1s in the outside of this lug boss 5c, and, be formed with the maintenance groove 5e that cross section is a rectangle at this arc surface 5d.Setting-in is fixed with the distolateral above-mentioned sealed member 14 that seals to above-mentioned control grease chamber 16 in this maintenance groove 5e.In addition, utilize the pivot of the above-mentioned pivot protuberance 5b of cam ring 5 to prop up groove 5k and trunnion 9, with the other end side sealing of above-mentioned control grease chamber 16.In addition, above-mentioned its radius of curvature of arc surface 5d roughly is set comparably according to the degree that forms certain micro-gap with above-mentioned sealing surface 1s.

Above-mentioned sealed member 14 is for example with the axially slenderly formation of the synthetic resin material that hangs down abrasiveness along cam ring 5, and the elastic force that dependence is fixed in the rubber system elastic member 15 of above-mentioned maintenance groove 5e bottom side is compressed on the sealing surface 1s.Thus, always guarantee the close property of good liquid of control described later grease chamber 16.

In addition, as shown in Figures 1 and 2, above-mentioned cam ring 5 is formed with a pair of suction side undercut groove 18a, the 18b that makes each pump chamber 13 of oil inflow in the suction zone in the axial both ends of the surface of suction port 7 sides, and, in the axial both ends of the surface of exhaust port 8 sides, respectively along the discharge side undercut groove 18c, the 18d that circumferentially are formed with the oil inflow exhaust port 8 in this discharging area makes each pump chamber 13.

Be divided into roughly circular-arc between above-mentioned control grease chamber 16 outer circumferential faces, above-mentioned pivot protuberance 5b and the sealed member 14 at above-mentioned cam ring 5, and, the discharge hydraulic pressure that imports from exhaust port 8 acts on the compression face 5f of cam ring outer circumferential face, making cam ring 5 is the counter clockwise direction swing of fulcrum to Fig. 2 with trunnion 9, thus, cam ring 5 is moved to the direction that the offset relative to rotor 4 reduces.

In addition, above-mentioned cam ring 5 is in the cylindrical body outer circumferential face and position above-mentioned pivot protuberance 5b opposition side, and being wholely set the outstanding extension of oriented radial outside is arm 17.This arm 17 has from the cylindrical body outer circumferential face of above-mentioned cam ring 5 and radially extends the arm main body 17a of rectangular plate shape of setting and the protuberance 17b that forms at the end face of the front end side of this arm main body 17a as shown in Figures 1 and 2.

Above-mentioned arm main body 17a is provided with the projection 17c of circular arc camber shape integratedly in the bottom surface with raised part 17b opposition side, on the other hand, raised part 17b is provided with along extending with respect to the roughly rectangular direction of arm main body 17a, and its end face 17d forms the little curved surface shape of radius of curvature.

In addition, above-mentioned pump case 1 with position above-mentioned pivot channel 1c opposition side, be the upper-lower position of above-mentioned arm 17, in Fig. 2, first spring accommodation chamber 19 of downside and the second spring accommodation chamber 21 of upside form on same axle.

The first spring accommodation chamber 19 forms the axially extended general plane rectangle along pump case 1, and the second spring accommodation chamber, 21 its length settings must be shorter than the first spring accommodation chamber 19, and similarly form axially extended general plane rectangle along pump case 1 with the first spring accommodation chamber 19.

In addition, the second spring accommodation chamber 21 relatively is provided with a pair of hooking part 23,23 of the elongated rectangular plate shape of extending to the inside each other as shown in Figure 5 integratedly at interior ora terminalis from the width direction of the 21a of its lower ending opening portion.Via the opening portion 21a between these two hooking parts 23,23, the protuberance 17b of above-mentioned arm 17 forms can enter in the above-mentioned spring accommodation chamber 21 or from it and retreats.The maximum elongation distortion of above-mentioned two hooking parts, 23,23 restrictions second helical spring 22 described later.

Inside at the above-mentioned first spring accommodation chamber 19, take in and dispose first helical spring 20, this first helical spring 20 is via the clockwise direction application of force of 17 pairs of above-mentioned cam rings 5 of above-mentioned arm in Fig. 1, the direction that promptly increases to the offset at the center of the rotating center of rotor 4 and above-mentioned cam ring 5 inner peripheral surfaces, to above-mentioned cam ring 5 application of forces.

Above-mentioned first helical spring 20 is applied in the spring load W3 of regulation, the bottom surface 19a Elastic Contact of the following ora terminalis and the first spring accommodation chamber 19, and, the circular-arc projection 17c butt that last ora terminalis always has with bottom surface at above-mentioned arm main body 17a, the direction application of force that increases to the offset at the center of the rotating center of the above-mentioned rotor 4 of above-mentioned cam ring 5 and above-mentioned cam ring 5 inner peripheral surfaces simultaneously.That is, to the clockwise direction application of force of cam ring 5 in Fig. 2.

In the above-mentioned second spring accommodation chamber 21, take in second helical spring 22 that disposes via the counter clockwise direction application of force of 17 pairs of above-mentioned cam rings 5 of above-mentioned arm in Fig. 2.

This second helical spring 22, the upper wall surface 21b Elastic Contact of ora terminalis and spring accommodation chamber 21 on it, and, following ora terminalis along the clockwise direction of cam ring shown in Figure 25 from the maximum eccentric mobile position to being limited to above-mentioned two hooking parts 23,23 during this, with the protuberance 17b Elastic Contact of above-mentioned arm 17, and the counter clockwise direction of cam ring 5 in Fig. 2 applied elastic force.

Promptly, the spring that also is applied with the regulation relative with first helical spring 20 on second helical spring 22 is set load, but this spring set load to set load W3 than the spring that puts on above-mentioned first helical spring 20 little, utilizing the difference of first helical spring 20 and second helical spring 22 setting load separately is load W1, and cam ring 5 is set at initial position (maximum eccentric position).

Specifically, by above-mentioned first helical spring 20 and second helical spring 22,, be the direction application of force of the volume increase of pump chamber 13 to making the eccentric upward direction of cam ring 5 always via arm 17 to be applied with the state of spring load W1.Above-mentioned spring load W1 is to be the required hydraulic pressure P1 of valve timing control gear when above at hydraulic pressure, the load that cam ring 5 begins to move.

On the other hand, offset at the inner peripheral surface center of the rotating center of rotor 4 above-mentioned cam ring 5, above-mentioned and above-mentioned cam ring 5 reaches specified value when above, second helical spring 22 and above-mentioned arm 17 butts, but as shown in Figure 5, when the offset deficiency at the center of the inner peripheral surface 5a of the rotating center of above-mentioned rotor 4 and above-mentioned cam ring 5 (less than) during established amount, with keep by the state of above-mentioned hooking part 23,23 compressions blocked end and with the roughly non-contact of above-mentioned arm 17.In addition, second helical spring 22 is limited to each hooking part 23,23 and makes the spring load W2 of above-mentioned first helical spring 20 in the oscillating quantity of the cam ring 5 of the spring load vanishing that arm 17 applies, during required hydraulic pressure P3 when referring to required hydraulic pressure P2 that hydraulic pressure is piston, oil nozzle etc. or bent axle maximum speed, the load that cam ring 5 begins to move.

In addition, above-mentioned cam ring 5 as shown in Figure 2, the elastic force that relies on above-mentioned first helical spring 20 when clockwise direction rotates, above-mentioned arm main body 17a's and cylindrical body between root end face 17d, with the bottom surface butt of a hooking part 23, thereby restriction is further rotated to clockwise direction.That is, rely on the elastic force of first helical spring 20, swing position is limited in initial, set position (maximum eccentric position).

Below, the elemental motion of the variable displacement pump 01 of present embodiment is described.Before this, according to Fig. 8 relation between the required hydraulic pressure of the oil nozzle that the cooling of the control hydraulic pressure of common variable displacement pump and internal-combustion engine slide part or valve timing control gear and piston is required is described.

Using under the situation of valve timing control gear described later as the countermeasure that reduces oil consumption and toxic emission, the required hydraulic pressure of internal-combustion engine uses the action source of the hydraulic pressure of above-mentioned variable displacement pump as this device, therefore, in order to improve the action response of this device, from the moment of engine low rotation speed, the high hydraulic pressure P1 shown in the dotted line b of working hydraulic pressure requirement Fig. 8.

In addition, when using oil nozzle 30 grades described later, require high hydraulic pressure P2 in the moment of motor medium speed, the required hydraulic pressure under maximum speed is mainly determined by the lubricated needed hydraulic pressure P3 of the bearing portion of bent axle.Therefore, the needed hydraulic pressure of whole internal-combustion engine forms the characteristic of the dotted line integral body that links dotted line b, c.

At this, the medium speed zone of internal-combustion engine requires the hydraulic pressure P3 that requires of hydraulic pressure P2 and high rotary speed area to be roughly the relation of P2＜P3, requires hydraulic pressure P2 and P3 more approaching mostly.Thereby, being preferably, Fig. 8 (D) zone i.e. the hydraulic pressure between the paramount rotary speed area of rotary speed area therefrom, even rotating speed rises, hydraulic pressure can not rise yet.

In the present embodiment, shown in the solid line among Fig. 8, at first, during from the starting of internal-combustion engine to the low rotation speed area that comprises idle running, because pump discharge head does not reach P1, therefore, the arm of cam ring 17 relies on spring load poor of first helical springs 20 and second helical spring 22, makes hooking part 23 butts of the arm main body 17a of cam ring 5 and pump case 1 and is in the state of quitting work (with reference to Fig. 2).

At this moment, the offset maximum of cam ring 5 and pump capacity are maximum, follow the rising of engine speed, discharge hydraulic pressure and sharply rise, and become the characteristic shown in (A) on the solid line of Fig. 8.

Then, follow the further rising of engine speed, the pump released liquor is pressed further and is risen, when reaching Pf shown in Figure 8, importing hydraulic pressure in the control grease chamber 16 increases, cam ring 5 begins to make first helical spring, 20 compressive strains that act on arm 17, and is that fulcrum is to the counter clockwise direction eccentric swing with trunnion 9.Above-mentioned Pf is i.e. first head pressure of cam action pressure that makes cam ring 5 action, be set at compare the valve timing control gear require hydraulic pressure P1 enough high.

Thus, because of pump capacity reduces, also shown in (B) zone of Fig. 8, reduce so discharge the rising characteristic of hydraulic pressure.Then, as shown in Figure 5, second helical spring 22 keeps being ended by card by the state of above-mentioned hooking part 23,23 compressions, and cam ring 5 is to swing counterclockwise, the state that does not apply to the end face 17d of arm protuberance 17b up to the load of second helical spring 22.

Under this state shown in Figure 5, from this moment, because the load of second helical spring 22 does not act on the cam ring 5, therefore, before discharge hydraulic pressure reached P2 (the hydraulic pressure P2 in the control grease chamber 16) and overcomes the spring load W2 of second helical spring 22, cam ring 5 becomes can not swingingly maintained state.Thereby along with the rotating speed of motor rises, released liquor presses to the rising characteristic shown in (C) of Fig. 8, still, because the offset of cam ring 5 diminishes and pump capacity reduces, therefore, can not become such rapid rising characteristic shown in above-mentioned (A) of Fig. 8.

When engine speed further rises and makes and discharge hydraulic pressure and reach Ps (P2) when above, cam ring 5 as shown in Figure 6, elastic force via the spring load W2 of arm 17 opposing first helical spring 20 makes its distortion, swings while this cam ring 5 compresses this first helical spring 20.Follow the swing of this cam ring 5, pump capacity further reduces, and the rising of discharging hydraulic pressure reduces, and reaches the maximum speed of the state of characteristic shown in (D) that keeps Fig. 8.

Thereby the discharge hydraulic pressure (solid line) in the time of can making the high rotating speed of said pump fully near requiring hydraulic pressure (dotted line), therefore, can suppress power loss effectively.

Fig. 7 represents displacement or the angle of oscillation of cam ring 5 and the relation of spring load W1, W2 of each helical spring 20,22.That is, from engine starting under slow-revving original state, be applied with the elastic force of the setting load W1 of first helical spring 20, therefore, before surpassing spring load W1, can not carry out displacement.When surpassing this spring load W1, first helical spring 20 is compressed and displacement, thereby its load is increased, and on the other hand, second helical spring 22 reduces its load near free length, and consequently, spring load increases.This gradient is a spring constant.

Position shown in Figure 5 at above-mentioned cam ring 5, become the spring load W2 of first helical spring 20, and increase discontinuously, but when discharging hydraulic pressure when surpassing spring load W2, in the displacement, load increases by first helical spring 20 being compressed, but because of the helical spring that works becomes one, so spring constant reduces, changes in pitch.

As mentioned above, when engine speed rising and discharge hydraulic pressure have just reached P1, cam ring 5 suppresses to discharge the rising of hydraulic pressure with regard to beginning to move, but when cam ring 5 when counter clockwise direction shown in Figure 5 has just reached the amount of movement of regulation, the elastic force of second helical spring 22 no longer acts on, spring constant reduces, in addition, the spring load W2 of first helical spring 20 increases discontinuously, therefore, released liquor press be upgraded to P2 after, cam ring 5 begin once more the swing (with reference to Fig. 6).That is, the relative spring load of first, second helical spring 20,22 works, and spring performance becomes non-linear state, and therefore, cam ring 5 constitutes special swing to be changed.

Like this, according to the non-linear property of the elastic force of two helical springs 20,22, the characteristic of discharging hydraulic pressure becomes the characteristic shown in (A)～(D) of Fig. 8, can make above-mentioned control hydraulic pressure (solid line) fully near required hydraulic pressure (dotted line).Consequently, can fully reduce the power loss that rises and cause because of unwanted hydraulic pressure.

Then, the oil nozzle 30 that present embodiment provided is described.

That is, as shown in Figure 9, above-mentioned oil nozzle 30 is located on the internal-combustion engine 31, and above-mentioned internal-combustion engine 31 utilizes not shown bearing rotation to be supported with bent axle 34 freely in the inside by the crankshaft room that crankcase was divided into 33 of cylinder block 32.In addition, in the inside of the cylindric cylinder wall 37 that is formed at crankcase top, be provided with the piston 36 that links via connecting rod 35 and above-mentioned bent axle 34 sliding freely.

In the wall of said cylinder wall 37, be formed with cooling water and carry out circuit water jacket 37a, and, the inside in the next door 38 between above-mentioned crankcase and cylinder wall 37 is formed with the main oil gallery 39 of each slide part that will supply to each internal-combustion engine from the oil (lubricant oil) that above-mentioned variable displacement pump 01 is discharged etc.

In the bottom in above-mentioned next door 38, shown in Figure 11 A, B, be formed with the communication path 38a that is communicated with above-mentioned main oil gallery 39 along the vertical direction, and, be formed with the mounting hole that is formed with internal thread part 38b at inner peripheral surface in the bottom of this communication path 38a.

And, the bottom in above-mentioned next door 38, be equipped with between the inner peripheral surface of above-mentioned cylinder wall 37 and piston 36 etc. spray cooling with and the oil nozzle 30 of the oil of lubricated usefulness.

Shown in Figure 10 and Figure 11 A, B, this oil nozzle 30 mainly comprises: the cylindric holding member 40 that is formed by aluminum alloy material, penetrate the air door body 41 of the drum of the through hole 40a that is had in this holding member 40 inside from the below, be arranged at the location of lateral part of above-mentioned holding member 40 with the nozzle 43 of the lateral part of jut 42 and the side opposite with above-mentioned jut 42 that be arranged at holding member 40 integratedly.

Above-mentioned holding member 40 is formed with circular passage portion 44 between the outer circumferential face of above-mentioned through hole 40a and air door body 41, and, be formed with the telescoping groove 40b of the base end part 43a of chimeric fixedly said nozzle 43 in above-mentioned lateral part.

Above-mentioned air door body 41 is formed by Ferrious materials such as sintered alloies, outer circumferential face in the upper end portion is formed with the external thread part 41a that screws togather with above-mentioned internal thread part 38b, and, be oil supply hole 45 to being formed with the fuel feeding portion that is communicated with above-mentioned communication path 38a along the inner shaft of upper end portion.In addition, be formed with the oil guiding hole 47 that keeps ball valve body 46 movably continuously in the bottom of this oil supply hole 45.Stepped part between above-mentioned oil supply hole 45 and oil guiding hole 47 is formed with the circular attachment face 45a of mounting ball valve body 46.

In addition, on the perisporium of the underpart of air door body 41, be formed with the radial hole 48 of above-mentioned oil guiding hole 47 of a plurality of connections and passage portion 44 along diametric(al), and, lip part 41b be provided with integratedly in lower, outer perimeter.With air door body 41 via above-mentioned external thread part 41a and interior threaded hole 38b when next door 38 screws in fixedly, this lip part 41b pushes the base end part 43a of said nozzle 43 and is fixed on the next door 38 with holding member 40.

When via above-mentioned air door body 41 holding member 40 being fixed in next door 38, above-mentioned jut 42 embeds the positioning hole 38c that is opened in next door 38, carries out the location and the spline of holding member 40.

Said nozzle 43 erects obliquely from the base end part 43a of holding member 40 sides, front end 43b is positioned at the bottom of said cylinder wall 37 inside, along inner shaft to being formed with the elongated oilhole 43c of an end to above-mentioned passage portion 44 openings, and the spray nozzle part 43d that forms at this front end points to the bottom of above-mentioned piston 36.

And, it is the active force (elastic force) of helical valve spring 50 that above-mentioned ball valve body 46 utilizes the plug shape retainer 49 flexibly mounted force application parts that are pressed into oil guiding hole 47 underparts, to the direction that is installed to above-mentioned attachment face 45a, promptly seal the direction of lower ending opening of oil supply hole 45 by the application of force.

Above-mentioned valve spring 50, its spring load is that the cracking pressure of ball valve body 46 is set to, and the above-mentioned first head pressure Pf that compares above-mentioned variable displacement pump 01 is enough high and than the i.e. low slightly above-mentioned pressure P 2 (with reference to Fig. 8) of the second head pressure Ps of the working hydraulic pressure of cam ring 5.

Below, the action of above-mentioned oil nozzle 30 is described.At first, follow the starting of internal-combustion engine, the live axle 3 of above-mentioned variable displacement pump 01 be rotated the action and to main oil gallery 39 pressure oils, so that each slide part to internal-combustion engine is lubricated, but in preliminary stage, because pump discharge head such as the above-mentioned first head pressure Pf that reaches shown in Figure 8, therefore, above-mentioned ball valve body 46 utilizes the elastic force of valve spring 50 to be installed in attachment face 45a and goes up and keep the valve state that closes shown in Figure 11 A.

Thereafter, when the hydraulic pressure in pump discharge head rising, the oil supply hole 45 reached more than the P2 and overcomes the spring load of valve spring 50, shown in Figure 11 B, valve spring 50 was compressed and is out of shape, thereby ball valve body 46 is opened.Thus, oil supply hole 45 and oil guiding hole 47 is communicated with, supplies to the oil of oil supply hole 45 via communication path 38, flow into passage portion 44 by radial hole 48 from oil guiding hole 47 from main oil gallery 39.And since then, as shown in Figure 9, by the oilhole 43c of nozzle 43, from the lower direction internal spray of spray nozzle part 43d from piston 36.

Like this, the oil from above-mentioned variable displacement pump 01 is discharged is more than the first head pressure Pf and does not reach the low slightly P2 than the second head pressure Ps as if its head pressure, then can not spray to piston 36 from oil nozzle.Therefore, can suppress variable displacement pump 01 is discharged the initial stage at pump energy loss effectively.

In addition, as mentioned above, the above-mentioned first head pressure Pf is set at lower than the cracking pressure of the ball valve body 46 of oil nozzle 30, therefore, the engine speed region of when normal vehicle operation, using (general regions), can flow bean 30 spray oil, excessively discharge oil so can suppress pump, meanwhile the fuel delivery to the slide part of internal-combustion engine increases.Consequently, can reduce the frictional force of pump or internal-combustion engine, and reduce oil consumption.

In addition, at internal-combustion engine 31 cold machine (Leng Machine) time, can suppress the oily this unfavorable condition that oil nozzle 30 sprays low temperature to piston 36, so, warming-up (Nuan Machine) performance improves and can reduce toxic emission.

In addition, as the structure of above-mentioned oil nozzle 30, be not limited to the structure of above-mentioned mode of execution, also can constitute and holding member 40 and nozzle 43 are formed as one or nozzle 43 is fixed on the air door body 41 by soldering, and, as valve body, except that ball valve body, also can be made as plunger.

Then, above-mentioned valve timing control gear is described.

This valve timing control gear is applied to the air inlet side, as Figure 12～shown in Figure 15, possesses: the rotary driving body that the not shown bent axle by internal-combustion engine is driven in rotation via timing chain is a timing sprocket 51; The camshaft 52 that relative this timing sprocket 51 can be provided with the relative rotation; Being fixed on the end of this camshaft 52 and rotating the driven solid of rotation that are incorporated in freely in the timing sprocket 51 is blade part 53; Make this blade part 53 give row mechanism 54 according to the hydraulic pressure that hydraulic pressure carries out the Direct/Reverse rotation.

Above-mentioned timing sprocket 51 comprises: the bonnet 57 of the open rearward end of the shell 55 of above-mentioned blade part 53, the protecgulum 56 that seals the front opening of this shell 55, closed casing 55 is taken in the 55a of tooth portion and the rotation that are provided with timing chain engagement outside week integratedly freely, these shells 55 and protecgulum 56, bonnet 57 by four path bolts 58 from cam shaft to fastening being fixed together integratedly.

Above-mentioned shell 55 is cylindric that the rear and front end opening forms, and in the circumferential about 90 ° of positions of inner peripheral surface, being provided with four boots portions to the inside highlightedly is wall part 60.Each wall part 60 cross section is roughly trapezoidal, along the axial setting of shell 55, two ora terminalis that it is axial and two ora terminalis of shell 55 constitute with one side respectively, and, the substantial middle position of next door portion 60, perforation vertically is formed with four bolt through holes 61 that above-mentioned each bolt 58 penetrates.In addition, the interior edge face of each wall part 60 forms circular-arc along the profile of the aftermentioned vane rotor 64 of above-mentioned blade part 53, and in opening vertically is formed at the maintenance groove that the high bit position of interior edge face puts, the sealed member 62 of the chimeric コ of maintaining shape and push the not shown leaf spring of sealing parts 62 to the inside.

Above-mentioned protecgulum 56 offers the bigger bolt through hole 56a in aperture in central authorities, and offers four bolts hole of each the bolt through hole 61 that penetrates above-mentioned shell 55 at peripheral part.

Above-mentioned bonnet 57 is formed with the bearing hole 57a that the front end 52a of above-mentioned camshaft 52 is supported in rotation freely in substantial middle, and is formed with four interior threaded holes that above-mentioned each bolt 58 is threaded at peripheral part.

Above-mentioned camshaft 52 is supported in the upper end portion of cylinder head freely via the rotation of not shown camshaft bearing, is provided with integratedly via valve tappet at the assigned position of outer circumferential face to make not shown suction valve carry out the cam of breakdown action.

Above-mentioned sealed member 53 usefulness sintered alloy materials are integrally formed, possess: be fixed on the circular vane rotor 64 of camshaft 52 front ends with cam bolt 63 and be arranged on four blades 65 of circumferential 90 ° of positions of these vane rotor 64 outer circumferential faces integratedly in central authorities.Vane rotor 64 has penetrated above-mentioned cam bolt 63 in the axial bore 64a of central authorities, and the front end 52a that is formed with camshaft 52 penetrates chimeric telescoping groove 64b, with above-mentioned cam bolt 63 from being axially fixed in the front end 52a of camshaft 52.

In above-mentioned four blades 65 one forms wide roughly trapezoidal of the width of circumferencial direction roughly, other three are elongated rectangular shape respectively, these blades are arranged on the predetermined angular position of circumferencial direction, keep the weight balancing of blade part 53 integral body thus.In addition, each blade 65 is disposed between each wall part 60, and the central opening at separately outer circumferential face is formed with not shown maintenance groove, in each keeps groove, embed respectively and maintain コ shape sealed member 66 that the inner peripheral surface with above-mentioned shell 55 slips and to the leaf spring 66a of the inner peripheral surface direction pushing sealing parts 66 of shell 55.

In addition, between the bi-side of the both sides of each blade 65 and each wall part 60, four advance angle chambers 67 and retardation angle chamber 68 have been divided into respectively.

As shown in figure 12, the first oily path 69 that it is working hydraulic pressure that above-mentioned hydraulic pressure has to above-mentioned each advance angle chamber 67 row's of giving lubricant oil for row mechanism 54 and to the oily path of the second oily path, 70 these two systems of each retardation angle chamber 68 row's of giving working hydraulic pressure, it is supply passage 71 and oil outlet passage 72 that these two oily paths 69,70 are connected with the main oil gallery that is used for IC engine supply lubricant oil via flow channel switching valve 73.Be provided with the unidirectional variable displacement pump 01 of the oil in the force feed food tray 74 in the above-mentioned supply passage 71.In addition, the downstream of above-mentioned oil outlet passage 72 is communicated with food tray 74.

Also as Figure 12 and shown in Figure 13, the above-mentioned first oily path 69 is formed between above-mentioned flow channel switching valve 73 and each the advance angle chamber 67, and it comprises: in the cylinder head in camshaft bearing and the inner shaft of camshaft 52 to and the first passage portion 69a that forms, be four tributary circuit 69b that general radial ground branch formed and be communicated with the first passage portion 69a and each advance angle chamber 67 to the inside of vane rotor 64 from the groove of camshaft 52 forward end.

On the other hand, the second oily path 70 forms between above-mentioned flow channel switching valve 73 and each retardation angle chamber 68, and it comprises: in the cylinder head towards the inner shaft of camshaft bearing and camshaft 52 to and the 70a of alternate path portion that forms; Be branch's formation radially and be communicated with the above-mentioned alternate path 70a of portion and four second tributary circuit 70b of each retardation angle chamber 68 to the inside of vane rotor 64 from the radial hole of camshaft front end 52a.

In addition, by above-mentioned blade part 53 or shell 55, and advance angle chamber 67, retardation angle chamber 68, hydraulic pressure constitute phase place change mechanism for row mechanism 54 etc.

As shown in figure 12, above-mentioned flow channel switching valve 73 is four-hole two bit-type solenoid valves, possesses: be fixed on the slide valve 79 that round-ended cylinder shape air door body 77 is arranged, be fixed in the solenoid 78 of these air door body 77 1 ends and be arranged on air door body 77 inside sliding freely integratedly in the valve opening 76 that is formed at cylinder head inside.

Above-mentioned air door body 77 is formed with the supplying mouth 80 that is communicated with supply passage 71 and air door body 77 inside in axial substantial middle position, and, radially be formed with each end of connection above-mentioned first oily path 69, the second oily path 70 and first, second mouthful 81,82 in the air door body 77 in the axial both sides of this supplying mouth 80.In addition, each outside at above-mentioned first, second mouthful 81,82 offers the inside of connection air door body 77 and first, second oil drain out 83,84 of oil outlet passage 72 respectively.

Above-mentioned solenoid 78 main compositions are for having: be located at helical shroud 78a inside electromagnetic coil 78b, by to this electromagnetic coil 78b energising by excitatory fixed core 78c, slide and push the movable plunger 78d of above-mentioned slide valve 79 to move it by this fixed core 78c excitatory.Described electromagnetic coil 78b is connected with electric control device 86 via not shown wire harness.

Above-mentioned slide valve 79 possesses: first 79a of back-up ring portion that is positioned at substantial middle that opens and closes above-mentioned supplying mouth 80 according to axial sliding position; The axial both sides of being located at this first back-up ring 79a of portion also relatively open and close the 79b of second, third back-up ring portion, the 79c of above-mentioned each first, second mouthful 81,82 and each oil drain out 83,84.In addition, this slide valve 79 utilizes the elastic force that is the Returnning spring of flexibly installing 85 between the exterior edge face that is arranged at air door body 77 another distolateral spring retainer 77a and above-mentioned the 3rd 79c of back-up ring portion, to left, the position that promptly is communicated with supplying mouth 80 and second mouthful 82 and is communicated with first mouthful 81 and oil drain out 83 is by the application of force, on the other hand, be used to the control electric current from above-mentioned electric control device 86, this slide valve 79 is controlled as the elastic force of opposing Returnning spring 85 and moves to neutral position the most right-hand or regulation.

Above-mentioned electric control device 86 is used to the various sensors such as cooling-water temperature sensor from the not shown CKP that detects engine speed, the signal that detects the Air flow meter that sucks air quantity and engine load sensor, detection of engine water temperature, detects current operational situation.

In addition, this electric control device 86 maybe blocks energising to the electromagnetic coil 78a of above-mentioned flow channel switching valve 73 conducting pulse control electric current according to above-mentioned engine operation condition, thereby carries out the switching controls of stream.

In addition, between the blade 65 and shell 55 of above-mentioned Extreme breadth, be provided with limit blade parts 53 with respect to the rotation of this shell 55 or the locking mechanism 87 that lifts restrictions.

This locking mechanism 87 comprises as Figure 12 and shown in Figure 15: slide with hole 88, it is located between above-mentioned the width wide blade 65 and bonnet 58, axially forms along the camshaft 52 of above-mentioned blade 65 inside; Locking piston 89, it is arranged on this slip sliding freely with 88 inside, hole, and is and has lid cylindric; Locking hole 90a, it is located at the card complex hole formation portion 90 that cross section is a cup-shaped, this locking hole 90a is for the coniform front end 89a engaging of above-mentioned locking piston 89 and break away from and as abutting part, and described card complex hole formation portion 90 is fixed in the fixed hole that is formed at above-mentioned bonnet 58; Helical spring 92, it keeps by being fixed in the above-mentioned slip spring retainer 91 with hole 88 underside sides, to locking piston 89 to the locking hole 90a direction application of force and as the 3rd force application part.

Above-mentioned locking piston 89 is at the integrally formed big footpath flange 89b that accepts pressure that is useful on of rear end side periphery, and, rotate to the position of retardation angle side at above-mentioned blade part 53, front end 89a utilizes the elastic force of above-mentioned helical spring 92 to engage with locking hole 90a, thus the relative rotation of locking timing sprocket 51 and camshaft 52.

In addition, above-mentioned locking piston 89 as shown in figure 15, utilization supplies to the hydraulic pressure in the above-mentioned locking hole 90a via the first oilhole 93a that is formed on above-mentioned blade part 53 or supplies to above-mentioned big footpath lip part 89a from above-mentioned retardation angle chamber 68 and slide with the arbitrary hydraulic pressure in the compression chamber 89c between the stepped part in hole 88 via the second oilhole 93b that is formed on blade part 53 equally from above-mentioned advance angle chamber 67, the elastic force of resisting above-mentioned helical spring 92 is then retired moving, thereby removes itself and the engaging of locking hole 90a.

Above-mentioned helical spring 92 is kept mechanism as locking states and is worked, it is set at the elastic force of following degree, this pressure that the i.e. working hydraulic pressure compression that can not come from above-mentioned variable displacement pump 01 force feed because of the air that is trapped in when the engine start in above-mentioned each retardation angle chamber 68 forms, and cause helical spring 92 compressive strain significantly, and above-mentioned helical spring 92 is set in the moment that the above-mentioned working hydraulic pressure that is discharged from reaches lifting hydraulic pressure Px at the initial stage shown in (A) of Fig. 8 and carries out compressive strain.

Below, the effect of above-mentioned valve timing control gear is described based on Figure 16～Figure 19.At first, when motor stops, the action of above-mentioned variable displacement pump 01 stops, stop thus supplying with working hydraulic pressure to advance angle chamber 67 and retardation angle chamber 68, and, after motor just stops, by the alternate torque that produces in advance at camshaft 52, blade part 53 is positioned at retardation angle side to the rotation of sense of rotation (direction of arrow) opposition side of camshaft 52 shown in Figure 13 and Figure 16 A.

In addition, at this constantly, shown in Figure 16 B, the locking piston 89 of above-mentioned locking mechanism 87 is according to the elastic force of helical spring 92, and front end 89a is sticked in the 90a of locking hole, the rotating freely of limit blade parts 53.

And then, also blocked to the energising of flow channel switching valve 73 from electric control device 86, therefore, slide valve 79 is according to the elastic force of Returnning spring 85, shown in Figure 16 C, to left position by the application of force.

Then, when the rotation ignition key makes engine start, begin between the several seconds from this turning crankshaft, can be from the control electric current of electric controller 86 to above-mentioned electromagnetic coil 78b output.Thereby, shown in Figure 17 C, slide valve 79 become utilize Returnning spring 85 elastic force to left by the state of the application of force.Therefore, supplying mouth 80 and second mouthful of 82 connection, meanwhile second 69b of back-up ring portion closes second oil drain out 84.Simultaneously, the first, the 3rd 69a of back-up ring portion, 69c make first mouthful 71 and 73 connections of first oil drain out.

Thereby, the working hydraulic pressure (head pressure) of discharging from variable displacement pump 01 is shown in the arrow of Figure 17 C, flow in the air door body 77 via supplying mouth 80 from supply passage 61, and directly flow in the second oily path 60 from second mouthful 82, since then, be fed into each retardation angle chamber 68 by each second tributary circuit 60b.

Therefore, shown in Figure 17 A, blade part 53 utilization is fed into the low working hydraulic pressure in above-mentioned each retardation angle chamber 68, keeps the state that is positioned at retardation angle side.Therefore, engine start raising.

At this moment, be trapped in air in each retardation angle chamber 68, carry out pressing the work of blade part 53 to retardation angle thruster with this low hydraulic pressure by above-mentioned low hydraulic pressure extruding.

On the other hand, shown in Figure 17 B, follow above-mentioned each retardation angle chamber 68 in press liter, this hydraulic pressure is fed into compression chamber 79c and acts on the compression face of big footpath flange 79b from the second oilhole 93b, the elastic force of locking piston 89 opposing helical springs 92, and retreat from locking hole 90a and to move and to extract out.Thus, the locking states of blade part 53 is disengaged and allows to rotate freely, but because the hydraulic pressure height in each retardation angle chamber 68, the maximum retardation angle position when therefore keeping above-mentioned motor and stopping.

As the front end 89a that makes this locking piston 89 from opportunity that locking hole 90a extracts out, the discharge hydraulic characteristic of above-mentioned variable displacement pump 01 become Fig. 8 lower than the first head pressure Pf (A) zone press rapid rising discharge hydraulic pressure Px constantly before first helical spring 70, aspect the time for rotate ignition key approximately through 2～3 seconds after.

When for example motor medium speed when reach beginning turning crankshaft after regional, from electric control device 86 to the electromagnetic coil 73b of flow channel switching valve 73 energising, to fixed core 78c carry out excitatory thereafter.So slide valve 79 moves to right-hand from the position shown in Figure 17 C via movable plunger 78d, moves to the most right-hand position in the position shown in Figure 18 C.So slide valve 79 cuts off the connection of first mouthful 81 and first oil drain out 83, and be communicated with supplying mouth 80 and first mouthful 81.Simultaneously, be communicated with second mouthful 82 and second oil drain out 84.

Therefore, shown in Figure 18 C, the discharge hydraulic pressure of variable displacement pump 01 flows in supplying mouth 80 and the air door body 77 from supply passage 71, again in the first passage portion 69a of first mouthful of 81 inflow first oily path 69, and be fed into each advance angle chamber 67 by each tributary circuit 69b since then, and make each 67 inside, advance angle chamber become high pressure, on the other hand, the working oil in each retardation angle chamber 68 is returned in the food tray 74 and is become low pressure from second oil drain out 84 via second oily path 60 grades.

Thereby, though the hydraulic pressure of the compression chamber 89b of locking piston 89 reduces, but shown in Figure 18 B, this follows the hydraulic pressure of above-mentioned each advance angle chamber 67 to rise, utilization supplies to high hydraulic pressure in the 90a of locking hole from the first oilhole 93a, the elastic force of locking piston 89 opposing helical springs 92 and keep the state of extracting out from locking hole 90a.Thus, blade part 53 utilizes the high hydraulic pressure of above-mentioned each advance angle chamber 67, right-hand rotation to figure shown in Figure 18 A is promptly rotated in the same way with the sense of rotation of camshaft 52 from position shown in Figure 13, and the relative rotatable phase of bent axle and camshaft 52 is changed to advance side rapidly.

Thus, the valve overlap of suction valve and outlet valve increases slightly, according to the effect of internal EGR, as described later, can reduce the discharge capacity of the HC in the waste gas.

In addition, when motor for example is transferred to high rotary speed area, keep, supply with hydraulic pressure to each advance angle chamber 67 continuously from the energising of electric control device 86 to electromagnetic coil 73b.Therefore, blade part 53 is further rotated to equidirectional, is maintained at maximum rotational position as shown in figure 14, makes the relative rotatable phase of bent axle and camshaft 52 be altered to advance side.Thus, valve overlap increases, and motor output improves.

In addition, engine running is transferred to when for example dallying, blocked to the control electric current that electromagnetic coil 78b flows from above-mentioned electric control device 86, thereby, slide valve 79 utilizes the elastic force of Returnning spring 85 to move to left, therefore shown in Figure 19 C, supplying mouth 80 and second mouthful of 82 connection, meanwhile second 69b of back-up ring portion closes second oil drain out 84.Simultaneously, the first, the 3rd 79a of back-up ring portion, 79c make first mouthful 81 and 83 connections of first oil drain out.

Thereby, the working hydraulic pressure of discharging from variable displacement pump 01 is shown in the arrow of Figure 19 C, flow in the air door bodies 77 via supplying mouth 80 from supply passage 71, directly flow in the second oily path 79 from second mouthful 82 then, and supply to each retardation angle chamber 68 by each second tributary circuit 70b since then.On the other hand, by first mouthful 81, be discharged to by first oil drain out 83, oil outlet passage 72 becomes low pressure to the hydraulic pressure of each advance angle chamber 67 again in the food tray 74 from the first oily path 69.

At this moment, locking piston 39 is shown in Figure 19 B, utilization has been imported into the hydraulic pressure of the compression chamber 89c of the high hydraulic pressure in the retardation angle chamber 68, keep the state that self-locking closed pore 90a extracts out, thereby allow freely rotating of blade part 53, therefore, this blade part 53 utilizes the high hydraulic pressure be fed in above-mentioned each retardation angle chamber 68 to rotate to retardation angle side shown in Figure 19 A.Thus, flammability improves, and the stability of the race of engine improves.

As previously discussed, in the present embodiment, according to the special construction of first, second helical spring 20,22 that uses above-mentioned variable displacement pump 01, the action response of the valve timing control gear in the time of can improving engine start.

Promptly, variable displacement pump 01 except that the lubricant oil that will discharge from tap hole via above-mentioned exhaust port 8 to the internal-combustion engine slide part is supplied with, also be used as the action source of valve timing control gear, as mentioned above, the rising of the initial discharge hydraulic pressure of putting down in writing among Fig. 8 (a-quadrant) becomes good, therefore, can improve the action response of the relative rotatable phase of for example timing sprocket 51 after the motor starting just and camshaft 52 to the retardation angle side.

[second mode of execution]

Figure 20 represents second mode of execution, and basic structures such as pump structure body are the same with first mode of execution, but with above-mentioned trunnion 9 be the center in the drawings the modes that increase with offset of two of upper and lower settings push the control grease chamber 16 of above-mentioned cam ring 5.

That is, the control grease chamber of first mode of execution is made as the first control 16a of grease chamber, in the bottom of trunnion 9 sides of pump case 1, is formed with roughly L shaped groove 24, constitute the second control 16b of grease chamber by this groove 24.In addition, be formed with secondary sealing area 24a in the bottom of above-mentioned groove 24, it is the arc surface shape at center with the axle center of above-mentioned trunnion 9 that this secondary sealing area 24a forms radius.

On the other hand, the position in the above-mentioned groove 24 at cam ring 5, be integrally formed with the protuberance 25 of general triangular, and being formed with radius is the second arc surface 25a at center at the position relative with above-mentioned secondary sealing area 24a of this protuberance 25 with the axle center of above-mentioned trunnion 9.Forward end at this second arc surface 25a is formed with the maintenance groove that cross section is a rectangle, takes in the inside of this maintenance groove to dispose the sealed member 26 that slips with above-mentioned sealing surface 24a and be the elastic member 27 of rectangle to the cross section that sealing surface 24a direction is pushed sealing parts 26.

Above-mentioned sealing surface 24a is set at following arc length, even promptly cam ring 5 swings to minimum offset shown in Figure 14 with respect to the offset at rotor 4 centers from maximum eccentric position shown in Figure 2, above-mentioned sealed member 26 also can slip.

In addition, the above-mentioned second control 16b of grease chamber is communicated with exhaust port 8 via the connectivity slot 1g that forms at the bottom surface of pump case 1 1a, thereby, with the identical head pressure of the first compression face 5f of the head pressure of accepting the first control 16a of grease chamber, act on the second compression face 5g towards the second control 16b of grease chamber of cam ring 5 peripheries.

In addition, the radius of curvature of the above-mentioned second arc surface 25a is set forr a short time than the radius of curvature of the first arc surface 5d of first sealed member 14 sides.Thereby, the surface area of the surface area ratio first compression face 5f of the second compression face 5g is little, therefore, when the head pressure in first, second control 16a of grease chamber, 16b acts on two compression face 5f, 5g respectively, for cam ring 5, similarly produce anticlockwise swing torque among the figure with first mode of execution.But, be clockwise direction owing to only act on the hydraulic torque of the above-mentioned second compression face 5g from the second control 16b of grease chamber, therefore, a part is cancelled.Therefore, under the identical situation of head pressure, the swing torque of cam ring 5 is littler than the swing torque of first mode of execution.

Therefore, can set the elastic force of above-mentioned two helical springs 20,22 little, so, the coil diameter of each helical spring 20,22 can be reduced.Consequently, can seek the miniaturization of vane pump integral body.

[the 3rd mode of execution]

The 3rd mode of execution of Figure 21～29 expression variable displacement pumps 01 though have part difference with the structure of the variable displacement pump 01 of first, second mode of execution, also has common place, so, for this common local detailed.

That is, this variable displacement pump 01 possesses: the cross section with pump accommodation chamber 113 is the pump case 111 of コ shape; Seal the cover 112 of an end opening of this pump case 111; Connect the approximate centre portion of pump accommodation chamber 113 and the live axle 114 that drives by the crankshaft rotating of motor; The rotor 115 that rotation is incorporated in the pump accommodation chamber 113 freely and central part combines with live axle 114; Be configured to from being seven slit 115a, seven blades 116 free to advance or retreat that opening radially is formed at these rotor 115 peripheral parts; The cam ring 117 that can eccentric dispose at the rotating center of the relative rotor 115 in the inside of pump case 111 (can swing); Be accommodated in the pump case 111, always the direction that increases to the offset of cam ring 117 relative rotor 115 rotating centers is single helical spring 118 to the force application part of these cam ring 117 application of forces; Be configured in the blade ring 119,119 of the both sides of all sides in the rotor 115 sliding freely.Above-mentioned live axle 114, rotor 115, blade 116, cam ring 117 become the pump structure body.

Also as Figure 24 and shown in Figure 25, above-mentioned pump case 111 connects to be formed with and rotates a bearing at end hole 111a of supporting driving shaft 114 freely in the substantial middle position of the bottom surface of pump accommodation chamber 113 113a.In addition, at the assigned position of pump accommodation chamber 113 inner circle walls that become pump case 111 inner side surfaces, as shown in figure 25, opening is formed with the roughly semicircular support slot 111b in cross section that cam ring 117 is supported in swing freely.

In addition, inner circle wall at pump accommodation chamber 113,, be formed with first, second sealing that the aftermentioned sealed member 130,130 that is equipped on cam ring 117 peripheral parts slips respectively and slip face 111c, 111d in both sides across the cam ring reference line M at the center of center that links bearing hole 111a and support slot 111b.These sealings are slipped face 111c, 111d and are formed by the center of distance support slot 111b and be respectively the radius R 1 of regulation, the arc surface shape that R2 constitutes, and these sealings circumferencial direction length of slipping face 111c, 111d is set to, and above-mentioned each sealed member 130,130 can always slip in the eccentric swing scope of cam ring 117.Thus, during cam ring 117 eccentric swings, slip face 111c, 111d and be directed and slide, so this cam ring 117 can move (eccentric swing) swimmingly along above-mentioned each sealing.

In addition, at the bottom surface of said pump accommodation chamber 113 13a, as Figure 22 and shown in Figure 25, outer regions at bearing hole 111a, with across the roughly relative mode of bearing hole 111a, opening is formed with respectively: suction port 121, and its conduct is the suction portion of circular arc concavity roughly, makes zone (the sucking the zone) opening of the internal capacity increase of pump chamber 120 to following pumping action; Exhaust port 122, it is as the discharge portion of circular arc concavity roughly, zone (discharging area) opening that the internal capacity of pump chamber 120 is reduced.

Above-mentioned suction port 121 is connected with the importing path 124 that extends setting to spring accommodation chamber 128 sides described later from the substantial middle position of this suction port 121, import path 124 midway at this, perforation is formed with the inlet hole 121a of the diapire of perforation pump case 111 to outside opening.Thus, as shown in figure 28, be stored in the lubricant oil in the food tray 152 of motor, the negative pressure that produces based on the pumping action of following the said pump structure is inhaled into each pump chamber 120 in above-mentioned suction zone via inlet hole 121a and suction port 121.

In addition, above-mentioned inlet hole 121a constitute with above-mentioned importing path 124 jointly towards the outer regions of the cam ring 117 of pump suction side, suction pressure is imported the outer regions of the pump suction side of this cam ring 117.Thus, become suction pressure or barometric pressure with the outer regions of the cam ring 117 of the pump suction side of each pump chamber 120 adjacency in above-mentioned suction zone, therefore, helping to suppress lubricant oil spills to the outer regions of the cam ring 117 of this pump suction side from each pump chamber 120 that sucks the zone.At this, the said pump suction side is meant the zone in the left side of the aftermentioned cam ring eccentric direction line N among Figure 22.

Above-mentioned exhaust port 122 with extend the importing path of being arranged to towards the aftermentioned first control grease chamber 131 that the outer circumferential side at cam ring 117 is divided into 125 from the top portion of this exhaust port 122 and be connected, be formed with the tap hole 122a of the diapire of perforation pump case 111 in the terminal part perforation of this importings path 125 to outside opening.

And this tap hole 122a is communicated with via each slide part in main oil gallery 39 and the internal-combustion engine and above-mentioned valve timing control gear and then with oil nozzle 30.

According to such structure, utilize the pumping action of said pump structure lubricant oil pressurized and that discharge from each pump chamber 120 of above-mentioned discharging area, be fed into each slide part and valve timing control gear in the internal-combustion engine via exhaust port 122 and tap hole 122a.

In addition, above-mentioned tap hole 122a constitutes the outer regions of discharging the cam ring 117 of side with above-mentioned importing path 125 jointly towards pump, head pressure is imported the outer regions of the pump discharge side of this cam ring 117.At this, said pump is discharged the zone that side is meant the right side of the aftermentioned cam ring eccentric direction line N among Figure 22.

In addition, near the top of above-mentioned exhaust port 122 one, opening is formed with the connectivity slot 123 that is communicated with this exhaust port 122 and bearing hole 111a, via this connectivity slot 123 to bearing hole 111a supplying lubricating oil, and also to the sidepiece supplying lubricating oil of rotor 115 or blade 116, to guarantee the lubricity of each sliding position.

In addition, this connectivity slot 123 forms with the direction of haunting of above-mentioned each blade 116 inconsistent, thereby comes off to this connectivity slot 123 when suppressing these blades 116 and haunting.

Above-mentioned cover 112 is roughly tabular, forms heavy wall a little with the corresponding position of bearing hole 111a of the pump case 111 of lateral part, and, at this thick wall part, connect to be formed with and rotates another distolateral bearing hole 112a of supporting driving shaft 114 freely.The inner side surface of this cover 112 is the general planar shape.And a plurality of bolts 126 of these cover 112 usefulness are installed in the open end of pump case 111.

Above-mentioned live axle 114 constitutes by the rotating force that comes from the bent axle transmission and makes the clockwise direction rotation of rotor 115 to Figure 22, center at this live axle 114 is the boundary with straight line (hereinafter referred to as " cam eccentric direction the line ") N with above-mentioned cam ring reference line M quadrature, left side among Figure 22 becomes the said pump suction side, and right-hand part becomes said pump and discharges side.

Above-mentioned rotor 115 is as Figure 21 and shown in Figure 22, opening is formed with internally, and central side is the above-mentioned a plurality of slit 115a that form radially to radial outside, and, be formed with the back pressure chamber 115b of the cross section circular shape of the discharge oil importing that will be discharged to above-mentioned exhaust port 122 respectively at the inboard base end part of each slit 115a.Thus, above-mentioned each blade 116 utilizes the centrifugal force following the rotation of rotor 115 and produce and the hydraulic pressure of back pressure chamber 115b to be pushed out laterally.

Each front-end face of above-mentioned each blade 116 slips with the inner peripheral surface of cam ring 117 respectively, and slip with the outside slip surface of each blade ring 119,119 respectively the side of each cardinal extremity face.Thus, even the hydraulic pressure of low, above-mentioned centrifugal force of engine speed or back pressure chamber 115b hour, each inner side surface of the outer circumferential face of rotor 115, the blade of adjacency 116,116 and the inner peripheral surface of cam ring 117, with as the bottom surface 113a of the pump accommodation chamber 113 of the pump case 111 of sidewall and the inner side surface of cover 112, also divide above-mentioned each pump chamber 120 with fluid-tight fashion.

Above-mentioned cam ring 117 is integrally formed as roughly cylindric by so-called sintering metal, be provided with the support slot 111b of pump case 111 chimeric and constitute the hinge portion 117a of the roughly circular arc convex of eccentric swing fulcrum vertically highlightedly at the assigned position of peripheral part, and, be positioned at the position of opposition side across the center of cam ring 117 at relative this hinge portion 117a, be provided with the arm 117b that gets in touch with helical spring 118 vertically highlightedly.

At this, in above-mentioned pump case 111, with the position of above-mentioned support slot 111b opposition side, be provided with the spring accommodation chamber 128 that is communicated with pump accommodation chamber 113 via the interconnecting part 127 that is set at Rack L, taken in helical spring 118 in this spring accommodation chamber 128.

This helical spring 118 is flexibly in the mode of setting load W with regulation and is held between the bottom surface of bottom surface that extends to the above-mentioned arm 117b front end in the spring accommodation chamber 128 by above-mentioned interconnecting part 127 and spring accommodation chamber 128.In addition, in the bottom surface of above-mentioned arm 117b front end, be provided with highlightedly and engage with interior all sides of helical spring 118 and form roughly circular-arc support projection 117i, an end of helical spring 118 is supported by this support projection 117i.

Above-mentioned helical spring 118 has the elastic force based on above-mentioned setting load W, direction (clockwise direction among Figure 22) application of force that cam ring 117 is always increased to its offset via above-mentioned arm 117b.Thus, under the off working state of cam ring shown in Figure 22 117, this cam ring 117 becomes the state that limitation part 128a that end face that the active force that utilizes above-mentioned helical spring 118 makes arm 117b is arranged at spring accommodation chamber 128 caps with being highlighted pushes, thus, this cam ring 117 is restricted to the position of its offset maximum.

Like this, by the opposition side extension that constitutes at hinge portion 117a arm 117b is set, and by the front end application of force of 118 pairs of these arms of helical spring 117b, thereby, can produce moment of torsion to greatest extent to cam ring 117, therefore, can realize the miniaturization of this helical spring 118, consequently can seek the miniaturization of pump self.

In addition, peripheral part at above-mentioned cam ring 117, be provided with cross section vertically respectively highlightedly and be a pair of first, second sealing formation 117c of portion, the 117d of general triangular, this first, second sealing formation 117c of portion, 117d has respectively that the relative mode of face 111c, 111d forms and slip first, second sealing surface 117g, the 117h that face 111c, 111d are the concentric circle arc plane shape with each sealing to slip with above-mentioned first, second sealing.In addition, on sealing surface 117g, the 117h of each the sealing formation 117c of portion, 117d, to be formed with cross section be that first, second sealing of essentially rectangular keeps groove 117e, 117f to opening vertically, keeps taking in respectively among groove 117e, 117f when maintaining at cam ring 117 eccentric swings and a pair of sealed member 130,130 that face 111c, 111d slip is slipped in each sealing in each sealing.

At this, above-mentioned each sealing surface 117g, 117h are made of than constituting corresponding with it above-mentioned slightly little predetermined radius R3, the R4 of radius R 1, R2 that slips face 111c, 111d that respectively seal the center apart from above-mentioned hinge portion 117a respectively, slip between face 111c, the 111d at each sealing surface 117g, 117h and above-mentioned each sealing, be formed with small clearance C respectively.

Above-mentioned each sealed member 130,130 for example forms elongated straight line shape by the fluorine-type resin material with low frictional behavior along cam ring 117 axial, utilization is provided in the elastic force that each sealing keeps the rubber system elastic member 29,29 of groove 117e, 117f bottom, and above-mentioned each sealed member 130,130 is crushed on each sealing and slips on face 111c, the 111d.The close property of good liquid that can always keep thus, each pressure chamber 31,32 of aftermentioned.

And, off working state at cam ring 117, be positioned at the outer regions of the cam ring 117 of hinge portion 117a side becoming said pump discharge the comparing cam ring eccentric direction line N of side, between the inner side surface of the outer circumferential face of this cam ring 117 and pump case 111, utilize the inner side surface of outer circumferential face, hinge portion 117a, above-mentioned each sealed member 130,130 and the pump case 111 of cam ring 117, across the both sides of hinge portion 117a, mark off the first control grease chamber 131 and the second control grease chamber 132 respectively.

In addition, in the present embodiment, constitute outer regions at cam ring 117, in the scope of said pump discharge side, above-mentioned first, second control grease chamber 131,132 integral body are taken in, being preferably to be accommodated in the footpath upwards becomes the zone that the above-mentioned discharging area of pressurised zone overlaps, promptly in the perisporium of cam ring 117 zone relative with the pump chamber 120 that always becomes malleation.

In the above-mentioned first control grease chamber 131, always be imported into the head pressure that exhaust port 122 is discharged via importing path 125, make head pressure act on first compression face 133, thus, provide oscillatory forces (locomotivity) to cam ring 117 to the direction (counter clockwise direction among Figure 22) that its offset is reduced, wherein, described first compression face 133 is made of the outer circumferential face of cam ring 117 in the face of this first control grease chamber 131 and accepts power with the mode effect of the active force that hinders helical spring 118.

Promptly, this first control grease chamber 131 is via the rotating center with one heart approaching direction of above-mentioned first compression face 133 to center that makes cam ring 117 and rotor 115, always, thus, be used for the amount of movement control of the concentric direction of this cam ring 117 to these cam ring 117 application of forces.

On the other hand, in the above-mentioned second control grease chamber 132, the introduction hole 135 that forms by the diapire that connects pump case 111 suitably is imported into head pressure, and wherein said introduction hole 135 is via according to engine operation condition and controlled aftermentioned solenoid valve 140 is connected with tap hole 122a.By making head pressure act on second compression face 134, thereby, provide oscillatory forces to cam ring 117 to the direction (clockwise direction among Figure 22) that its offset is increased, wherein said second compression face 134 is made of the outer circumferential face in the face of the cam ring 117 of this second control grease chamber 132 and accepts power to the direction effect of the active force of supporting helical spring 118.

At this, as shown in figure 22, the compression area S2 of above-mentioned second compression face 134 sets forr a short time than the compression area S1 of above-mentioned first compression face 133, and the power that constitutes according to the rules concerns, make the active force and the force balance of bringing by the first control grease chamber 131 of cam ring 117 eccentric directions that produce by active force, the active force of the auxiliary helical spring 118 of active force that produces by this second control grease chamber 132 based on active forces of pressing in the second control grease chamber 132 and helical spring 118.

That is, the above-mentioned second control grease chamber 132 makes the head pressure of supplying with as required via above-mentioned solenoid valve 140 act on second compression face 134, suitably supports the active force of helical spring 118, thereby, be used for the amount of movement control of the eccentric direction of cam ring 117.

In addition, on the above-mentioned variable displacement pump 01, as shown in figure 28, based on from the exciting curent of vehicle-mounted ECU 151 and the solenoid valve 140 and this variable displacement pump 01 split setting that move according to the operational situation of motor, connect tap hole 122a and introduction hole 135 via this solenoid valve 140, when opening solenoid valve 140, the first control grease chamber 131 and the second control grease chamber 132 are communicated with thus.

Above-mentioned solenoid valve 140 mainly comprises as Figure 26 and shown in Figure 27: cylindric air door body 141, and the distolateral formation opening of one, the other end side seal closes; Valve body 142, it is accommodated in this air door body 141 vertically sliding freely, is formed with the 142a of first, second back-up ring portion, 142b that the inner peripheral surface with air door body 141 slips at two end part; Spring 143, it is incorporated in another distolateral back pressure chamber that marks off 145 at air door body 141 by second 142b of back-up ring portion of this valve body 142, to the distolateral application of force of valve body 142 to air door body 141; Electromagnetic unit 144, it is installed in the open end of air door body 141, following energising to make connecting rod 144b pass in and out the active force of antagonistic spring 143, so that valve body 142 is to another distolateral moving axially of air door body 141.

The oil drain out 141c that above-mentioned air door body 141 is formed with the IN mouth 141a that is connected with tap hole 22a, the OUT mouth 141b that is connected with introduction hole 135 respectively with connecting, is connected with suction port 121 or outside at its perisporium, and, be formed with and suction port 121 or the outside back pressure mouth 141d that always is connected also to back pressure chamber 145 openings at the sidewall of the other end with connecting.

Above-mentioned valve body 142 forms at axial intermediate portion undergauge, mark off annulus 146 by above-mentioned two 142a of back-up ring portion, 142b between itself and the air door body 141, be communicated with OUT mouth 141b with IN mouth 141a or be communicated with OUT mouth 141b and oil drain out 141c via this annulus 146.

Above-mentioned electromagnetic unit 144 is well-known formation, mainly comprises: coil unit 144a, its on bobbin the coiling coil and thereon outside the embedding yoke form; Armature, it can be arranged on the interior all sides of this coil unit 144a vertically with advancing and retreat and be made of magnetic material, and this armature is not shown; Connecting rod 144b, it combines with this armature and to follow the advance and retreat of armature to advance and retreat according to "on" position mobile.

At this, above-mentioned solenoid valve 140 constitutes so-called normal-open electromagnetic valve as shown in figure 26, under non-power status, is communicated with IN mouth 141a and OUT mouth 141b via annulus 146, and head pressure is imported the second control grease chamber 132.At this moment, oil drain out 141c becomes the state to back pressure chamber 145 openings.

On the other hand, as shown in figure 27, when coil unit 144a conducting exciting curent, utilize the active force of the pushing force antagonistic spring 143 of connecting rod 144b, it is distolateral that valve body 142 is pushed back another of air door body 141.Thus, IN mouth 141a is cut off by first 142a of back-up ring portion of valve body 142, and OUT mouth 141b is communicated with oil drain out 141c via annulus 146, and the second control grease chamber 132 is opened wide towards suction pressure or barometric pressure.

According to above structure, above-mentioned variable displacement pump 01 is controlled the offset of this cam ring 117 by the relative power relation interior pressure, that act on cam ring 117 of the interior pressure of controlling the above-mentioned first control grease chamber 131 and the second control grease chamber 132 that is controlled by the active force and the solenoid valve 140 of helical spring 118.And, make the variable quantity of above-mentioned each pump chamber 120 internal capacity of time spent by controlling this offset with control pump, thereby control the head pressure characteristic of this variable displacement pump 01.

Below, based on Figure 22, Figure 23 and Figure 29 the characteristic effect of the variable displacement pump 01 of present embodiment, i.e. head pressure control based on the pump of the offset control of cam ring 117 are described.

At first, as mentioned above, under the situation that makes the action of above-mentioned valve timing control gear, the hydraulic pressure that requires of the head pressure of above-mentioned variable displacement pump 01 is P1 among the figure.That is, the low hydraulic pressure P1 that is set at after the valve timing control gear has just started with motor moves.

In addition, as the hydraulic pressure that requires of the crankshaft bearing liner under the high rotating speed of internal-combustion engine, if when for example being in low-load or low oil temperature, then the P2 among the figure becomes requirement hydraulic pressure, if when being in high load or high oil temperature, then the P4 among the figure becomes requirement hydraulic pressure.

In addition, when motor was in high load, for piston being cooled off and use above-mentioned oil nozzle 30, but the cracking pressure of the above-mentioned ball valve body 46 of this oil nozzle 30 was set to the hydraulic pressure P3 among the figure under the regulation rotation speed n when medium speed.

So, above-mentioned variable displacement pump 01 is set to when low-load or low oil temperature, constituting the P1 satisfy among Figure 29 or the either party among the P2 or P1 and P2 both sides' the first head pressure characteristic that requires hydraulic pressure is low pressure characteristic X, and, be set to when high load or high oil temperature, constituting the P3 that satisfies among Figure 29 or the either party among the P4 or P3 and P4 both sides' the second head pressure characteristic that requires hydraulic pressure is high pressure characteristics Y.

And, by the switching (ON-OFF) of switching above-mentioned solenoid valve 140, the acting characteristic of change cam ring 117, be that the needed discharge hydraulic pressure of action of cam ring 117 is first, second working hydraulic pressure Px, Py, and select only hydraulic characteristic among above-mentioned two hydraulic characteristic X, the Y according to the operational situation of motor, respectively require hydraulic pressure with what satisfy above-mentioned motor.

In the present embodiment, as shown in figure 29, for above-mentioned low pressure characteristic X, be set at link the valve timing control gear require hydraulic pressure P1 and be in low-load or low oily temperature state under the high rotating speed of motor the time the hydraulic characteristic represented of the dotted line that requires hydraulic pressure P2, and for above-mentioned high pressure characteristics Y, the hydraulic characteristic that the solid line that requires hydraulic pressure P4 the when cracking pressure that is set at the above-mentioned oil nozzle 30 when linking the motor medium speed be in high load or high oily temperature state under requires the high rotating speed of motor under hydraulic pressure P3 and this state is represented.

Promptly, for above-mentioned variable displacement pump 01, the spring load W of helical spring 118 is set to the above-mentioned first working hydraulic pressure Px, when being in low-load or low oil temperature, from ECU151 to solenoid valve 140 conducting exciting curents, thus, IN mouth 141a is cut off, and only imports head pressure in the first control grease chamber 131.

Thus, before the interior pressure of the first control grease chamber 131 reached the first working hydraulic pressure Px, the offset of cam ring 117 was maintained at maximum rating (with reference to Figure 22), followed the rotating speed of motor to rise, and head pressure rises sharp.

Then, when the rising according to head pressure made the interior pressure of the first control grease chamber 131 reach the first working hydraulic pressure Px, cam ring 117 was the direction swing (with reference to Figure 23) of fulcrum to the offset minimizing of above-mentioned cam ring eccentric direction line N below with hinge portion 117a.Thus, the volume-variation amount of above-mentioned each pump chamber 120 during pumping action reduces, and consequently, follows the rising of engine speed and the head pressure that rises slowly rises, and therefore, obtains low pressure characteristic X shown in Figure 29.

Then, when above-mentioned low-load or low oily temperature state are transferred to high load or high oily temperature state, blocked to the exciting curent of solenoid valve 140 conductings from ECU151, IN mouth 141a and OUT mouth 141b are communicated with, head pressure not only imports the first control grease chamber 131, and is imported into the second control grease chamber 132.

So, the pressure that acts on second compression face 134 of the second control grease chamber 132 does work in the mode of the active force of support helical spring 118, therefore, even the interior pressure of the first control grease chamber 131 reaches the first working hydraulic pressure Px among Figure 29, cam ring 117 can not move yet, before the difference that the interior pressure and the second interior pressure of controlling grease chamber 132 according to the first control grease chamber 131 act on the hydraulic coupling of first compression face 133 and second compression face 134 reached the active force of helical spring 118, cam ring 117 all was maintained at the state (with reference to Figure 22) of the offset maximum of this cam ring 117.

Promptly, when this high load or high oil temperature, as shown in figure 29, when head pressure reaches difference that the interior pressure according to the interior pressure of the first control grease chamber 131 and the second control grease chamber 132 acts on the hydraulic coupling of first compression face 133 and second compression face 134 and equates with the active force of helical spring 118 before such second working hydraulic pressure Py, maintain the state of the offset maximum of cam ring 117, follow the rotating speed of motor to rise, head pressure significantly rises.

Then, when the interior pressure of the first control grease chamber 131 reaches the second working hydraulic pressure Py, the direction swing (with reference to Figure 23) that cam ring 117 reduces to offset.Thus, the volume-variation amount of above-mentioned each pump chamber 120 during pump work reduces, and follows the rising of engine speed and the head pressure that rises slowly rises, and therefore, obtains high pressure characteristics Y as shown in figure 29.

Like this, above-mentioned variable displacement pump 01 as principle, is a benchmark with rotating speed or load, the oily temperature etc. of motor, is judged as by ECU151 under the situation that needs high pressure, and the pump discharge head characteristic is transferred to high pressure characteristics Y.

So, usually under the load or the warm contour situation of oil of motor, transfer to above-mentioned high pressure characteristics Y, so, in the above description, situation as this high pressure characteristics of performance Y, load or the high state of oil temperature with motor are that example is illustrated, but for example in the valve timing control gear, also need high hydraulic pressure sometimes, in this case than above-mentioned requirements hydraulic pressure P1, correspondingly carry out the switching of solenoid valve 140 by the actuating signal of ECU151 and valve timing control gear, therefore, even be in low states such as the load of motor or oily temperature, also the pump discharge head characteristic is transferred to above-mentioned high pressure characteristics Y.

In other words, in the present embodiment, represented above-mentioned requirements hydraulic pressure P1 is set at the common situation that requires hydraulic pressure of valve timing control gear, but also can above-mentioned requirements hydraulic pressure P1 have been set as the MIN hydraulic pressure that requires of valve timing control gear according to the specification of the vehicle that carries present embodiment etc.

In addition, transferring to once more under the situation of above-mentioned low-load or low oily temperature state from above-mentioned high load or high oily temperature state, from ECU151 conducting exciting curent once more, solenoid valve 140 becomes "on" position shown in Figure 7, and the second control grease chamber 132 is opened wide towards barometric pressure or suction pressure.Thus, the action of cam ring 117 depends on the power relation between the active force of the first control interior pressure of grease chamber 131 and helical spring 118, and the head pressure characteristic of pump changes to low pressure characteristic X.Consequently, can reduce because of shifting unwanted head pressure, thereby can suppress the power loss of motor to low-load or low oily temperature state.

Like this, in the above-mentioned variable displacement pump 01, ECU151 comes switching solenoid valve 140 based on the rotating speed or the various operation informations such as load, oily temperature of motor, thereby can change the acting characteristic of cam ring 117, and selects and the rotating speed of this motor or the head pressure characteristic of couplings such as load, oily temperature.Thus, can reduce waste, the power loss of motor is suppressed at inferior limit as the merit of pump.

And, in this variable displacement pump 01, action control for aforesaid cam ring 117, by based on the simple control of the ON-OFF of solenoid valve 140 and complicated controls such as the controls that do not need to load, and do not need the precision machining of the degree of lip-rounding shape etc. in this solenoid valve 140 by using general solenoid valve 140 or open the simple structure of the adjustment of valve characteristic etc., just can easily realize.Therefore, also can seek cheapization of the manufacture cost of pump.

In addition, in the above-mentioned variable displacement pump 01, as using among Figure 23 shown in the heavy line arrow, the interior pressure of above-mentioned each pump chamber 120 of discharging area acts on the inner peripheral surface of the hinge portion 117a side of cam ring 117, therefore, this cam ring 117 is right-hand in figure along above-mentioned cam ring reference line M to be that above-mentioned support slot 111b side is urged, and hinge portion 117a is crushed among this support slot 111b.

But, in the variable displacement pump 01 of present embodiment, discharge the outer regions of the cam ring 117 of side in said pump, promptly with above-mentioned each pump chamber 120 of above-mentioned relatively discharging area, across the relative mode of the perisporium of cam ring 117 and these pump chambers 120, dispose above-mentioned two control grease chambeies 131,132, therefore shown in the thick dashed line arrow among Figure 23, the interior pressure of these two control grease chambeies 131,132 acts on cam ring 117 so that the opposition side of cam ring 117 to support slot 117b rolled back respectively, thereby alleviates the crimping of hinge portion 117a to support slot 111b.Thus, the friction of hinge portion 117a and support slot 111b in the time of can reducing cam ring 117 eccentric swings.

Consequently, can suppress the abrasion of this hinge portion 117a or support slot 111b, especially can suppress abrasion by the support slot 111b that constitutes than the low material of cam ring 117 hardness.

In addition, according to above-mentioned effect, though act on the power of outer circumferential side in the cam ring 117 roughly offsets in said pump discharge side, but,, barometric pressure or suction pressure are arranged via importing path 124 effects in the outer regions of the cam ring 117 of the said pump suction side that is positioned at above-mentioned support slot 111b opposition side, by this barometric pressure or suction pressure, hinge portion 117a is pressed in the support slot 11b morely, therefore, can not cause this hinge portion 117a to leave the inner face of support slot 111b.Thus, can obtain the suitable action of the cam ring 117 that hinge portion 117a and support slot 111b moderately slip.

In addition, as mentioned above, discharge the zone of side in said pump, dispose above-mentioned two pressure chambers 31,32 in the mode relative with above-mentioned each pump chamber 120 of discharging area, therefore, in this zone, the pressure that acts on the pressure of all sides in the cam ring 117 and act on outer circumferential side all be head pressure also about equally, therefore, the pressure difference of periphery in the cam ring 117 of this discharging area can be suppressed at inferior limit.Thus, spill (seepage) of the lubricant oil of the micro-gap that forms can be suppressed at inferior limit between the inner side surface of above-mentioned discharging area via the diapire 113a of the bi-side of cam ring 117 and pump accommodation chamber 113 and cover 112.Consequently, can greatly reduce the waste of the merit of variable displacement pump 01, and the high efficiency that can seek this variable displacement pump 01.

As previously discussed, variable displacement pump 01 according to present embodiment, by dispose first, second pressure chamber 31,32 in both sides across hinge portion 117a, the interior pressure of the second control grease chamber 132 is with the mode effect of the active force of support helical spring 118, therefore, can set the active force of this helical spring 118 very little.

Specifically, by disposing the above-mentioned second control grease chamber 132, as long as helical spring 118 has the active force that can guarantee above-mentioned low pressure characteristic X, promptly the active force with the first working hydraulic pressure Px equilibrium gets final product, therefore, the helical spring that can use the little low load of spring constant compared with the past.Thus, the required space of configuration helical spring 118 be can dwindle in the pump case 111, miniaturization, the lightweight of this variable displacement pump 01 realized.Consequently, variable displacement pump 01 is enhanced to the lift-launch of motor.

And the compression area of above-mentioned second compression face 134 is set to littler than above-mentioned first compression face 133, therefore, can utilize the second control grease chamber 132 that the working hydraulic pressure of cam ring 117 is set at two-stage.Thus, also can improve the degrees of freedom of the head pressure characteristic of pump.

In addition, the action of valve timing control gear and the locking of locking mechanism are removed hydraulic pressure and are set to P1 among the low pressure characteristic X, therefore and the respective embodiments described above similarly, can realize the improvement of the action response of valve timing control gear.

In addition, the above-mentioned first head pressure X sets lowlyer than the cracking pressure P3 of above-mentioned oil nozzle 30, therefore in the employed engine speed region of normal vehicle operation, can not spray oil from oil nozzle 30.

Therefore and the respective embodiments described above similarly, can suppress the discharge capacity of variable displacement pump 01, the friction that reduces each several part also reduces oil consumption.

In addition, when cold machine, oil nozzle 30 can not spray the oil of low temperature, so the warming-up performance is improved.

In addition, the variable displacement pumps that power steering gear is used etc., the differential pressure of utilizing two pressure chambers are swung control to cam ring and the pump that constitutes, provide multiple at present, produce the structure of differential pressure but this existing pump all has based on the pressure loss that is caused by throttling arrangement etc., this pressure loss can reduce pump efficiency.Relative therewith, the variable displacement pump 01 of present embodiment, it constitutes importing head pressure and can be with the pressure loss in the first control grease chamber 131 and the second control grease chamber 132, the compression face product moment that utilizes these two pressure chambers 31,32 is the action moment of torsion that the area difference of first compression face 133 and second compression face 134 produces cam ring 117, so, can not produce the unfavorable condition that the such pump efficiency of above-mentioned existing variable displacement pump reduces.Thus, compare, and do not produce the above-mentioned pressure loss correspondingly, help to improve pump efficiency with above-mentioned existing variable displacement pump.

In addition; for the variable displacement pump 01 of present embodiment; when solenoid valve 140 non-energisings; it is set to becomes above-mentioned high pressure characteristics; therefore; also possesses function, even i.e. these solenoid valve 140 out of order situations use the whole zone in zone also can guarantee the head pressure that needs at motor as following failure protecting device.

Figure 30 and Figure 31 represent the variation of above-mentioned the 3rd mode of execution, are the examples that the solenoid valve 140 of the 3rd mode of execution is constituted so-called normal close type solenoid valve.

That is, the solenoid valve 140 of this variation is to constitute the so-called normal close type solenoid valve with characteristic opposite with the solenoid valve of above-mentioned the 3rd mode of execution.It constitutes as shown in figure 30, and when non-energising, IN mouth 151a is cut off, and OUT mouth 151b is communicated with oil drain out 151c; As shown in figure 31, when energising, IN mouth 151a and OUT mouth 151b are communicated with.Thus, when variable displacement pump 01 is non-energising at solenoid valve 140, become low pressure characteristic X, this solenoid valve 140 becomes high pressure characteristics Y when being energized.

According to this formation, for the head pressure characteristic of the desired variable displacement pump 01 of motor, when the frequency of high pressure characteristics Y hangs down than the frequency with low pressure characteristic X, can shorten current"on"time to solenoid valve 140, therefore, help to suppress this solenoid valve 140 through the time deterioration.

[the 4th mode of execution]

Figure 32～Figure 36 represents the 4th mode of execution, is the configuration of the sealed member 130,130 of above-mentioned the 3rd mode of execution of change, and with the structure of solenoid valve 140 with shell one formation.

Promptly, in the present embodiment, cancel above-mentioned each sealing that respectively seals the 117c of formation portion, 117d that is arranged on cam ring 117 in the 3rd mode of execution and keep groove 117e, 117f, replace and slip on face 111c, the 111d in above-mentioned each sealing, keep groove 117e, position that 117f is relative in each sealing that is cancelled with above-mentioned, being formed with each sealing keeps the same sealing of groove 117e, 117f to keep groove 111e, 111f, in sealing keeps groove 111e, 111f, take in together and dispose above-mentioned each elastic member 129,129 and above-mentioned each sealed member 130,130.

In addition, in the present embodiment, as Figure 32, Figure 35 and shown in Figure 36, at the outer side surface 112b of cover 112, be formed with the air door body 141 of solenoid valve 140 abreast with above-mentioned cam ring eccentric direction line N, this solenoid valve 140 and shell one constitute.

In addition, for the structure of solenoid valve 140, the same with above-mentioned the 3rd mode of execution, in the air door body 141 that is integrally formed at above-mentioned cover 112, taken in valve body 142 sliding freely, the upper end portion in Figure 35 of this air door body 141 i.e. an end opening portion, and electromagnetic unit 144 is installed.

In addition, follow the change of this structure, inner side surface 112c at above-mentioned cover 112, as shown in figure 36 and pump case 111 similarly be respectively equipped with suction port 121, exhaust port 122, be communicated with exhaust port 122 and bearing hole 112a connectivity slot 123, and begin to extend the importing path 125 of setting from exhaust port 122.

In addition, on this cover 112, to be communicated with the mode of above-mentioned pump case 111 inside (pump accommodation chamber 113) and air door body 141 inside, offer IN mouth 141a at the assigned position that imports path 124, and at the OUT mouth 141b that offers double as introduction hole 135 with respect to this IN mouth 141a across the roughly symmetrical assigned position of above-mentioned cam ring reference line M, and, at the perisporium of the air door body 111 that is integrally formed at this cover 112 and each assigned position of diapire, perforation is formed with oil drain out 141c and back pressure mouth 141d respectively.

Thereby, according to this mode of execution, when cam ring 117 eccentric swings, above-mentioned each sealed member 130,130 and the pump case that is made of aluminum alloy material hardness ratio 111 high iron are that above-mentioned each sealing surface 117g, 117h of the cam ring 117 that constitutes of agglomerated material slips, therefore, can suppress to cause each sealing surface 117g, 117h abrasion because of each sealed member 130,130.Thus, compare with above-mentioned the 3rd mode of execution, the durability of variable displacement pump 01 improves.

In addition, in the present embodiment,, therefore the oil hydraulic circuit of variable displacement pump 01 is finished in this variable displacement pump 01 owing to being that shell is integrally formed with cover 112 with solenoid valve 140.Therefore, helping with variable displacement pump 01 is the miniaturization of the hydraulic feed system at center.

[the 5th mode of execution]

Figure 37～Figure 39 represents the 5th mode of execution, it constitutes: with the basic comprising that constitutes of above-mentioned the 4th mode of execution, replace the solenoid valve 140 of the 4th mode of execution and have the hydraulic directio switching valve 150 that the head pressure utilized is moved, and change the head pressure characteristic of pump in view of the above.

That is, in the present embodiment, as the alternative part of above-mentioned solenoid valve 140, use well-known slide column type hydraulic directio switching valve 150, this hydraulic directio switching valve 150 possesses as Figure 37, shown in Figure 38: air door body 151 cylindraceous, and the distolateral formation opening of one, the other end side seal close; Stopper 152, it seals an end opening portion of this air door body 151; Valve body 153, it is accommodated in the air door body 151 vertically sliding freely, and the 153a of first, second back-up ring portion, the 153b that are had by two end part mark off pressure chamber 155 and back pressure chamber 156 in this air door body 151; Spring 154, its be accommodated in the back pressure chamber 156 and to valve body 153 to pressure chamber's 155 side application of forces.This hydraulic directio switching valve 150 is set to: when the interior pressure of pressure chamber 154 surpass be set to higher and during than above-mentioned requirements hydraulic pressure P1 than the low regulation setting pressure Pz of above-mentioned requirements hydraulic pressure P2, as shown in figure 38, the elastic force of valve body 153 antagonistic springs 154 is to back pressure chamber 156 side shiftings.

Above-mentioned air door body 151 is at the axial assigned position of its perisporium, connect the oil drain out 151c that is formed with the IN mouth 151a that is connected with tap hole 122a, the OUT mouth 151b that is connected with introduction hole 135, is connected respectively with suction port 121 or outside, and, at the sidewall of back pressure chamber 155 sides, connect be formed with suction port 121 or outside is connected and with back pressure chamber 145 always towards suction pressure or the unlimited back pressure mouth 151d of barometric pressure.

The internal thread part scyewed joint of the open end inner peripheral surface that above-mentioned stopper 152 is distolateral with being located at above-mentioned air door body 151 1 connects along the axle center and to be formed with introducing port 152a, always imports head pressure by this introduction hole 152a in pressure chamber 155.

Above-mentioned valve body 153 forms at axial intermediate portion undergauge, mark off annulus 157 by above-mentioned two 153a of back-up ring portion, 153b between itself and the air door body 151, be communicated with OUT mouth 151b and IN mouth 151a or be communicated with OUT mouth 151b and oil drain out 151c via this annulus 157.

Promptly, when valve body 153 is in off working state, cut off IN mouth 151a by first 153a of back-up ring portion, OUT mouth 151b and oil drain out 151c are communicated with via annulus 157, and valve body 153 is when moving, cut off oil drain out 151c by second 153b of back-up ring portion, IN mouth 151a and OUT mouth 151b are communicated with via annulus 157.

Thereby, the variable displacement pump 01 of present embodiment, under the low state of engine speed, the IN mouth 151a of hydraulic directio switching valve 150 is cut off, head pressure only acts on the first control grease chamber 131, so, as shown in figure 40, when head pressure reached the first working hydraulic pressure Px, performance made cam ring 117 reduce the direction swing and make the slowly so described low pressure characteristic X (the T1 interval among Figure 40) of rising of head pressure to offset.

And, when head pressure rises and when making the interior pressure of pressure chamber 155 reach above-mentioned setting pressure Pz, valve body 153 is based on the active force that compresses anti-spring 154 in this pressure chamber 155, beginning moves axially to back pressure chamber 155 sides, follow moving axially of this valve body 153, oil drain out 151c is sealed by second 153b of back-up ring portion, and IN mouth 151a opens wide gradually to annulus 157.Thus, IN mouth 151a and OUT mouth 151b are communicated with gradually via annulus 157, and head pressure imports in the second control grease chamber 132 gradually.Consequently, press liter in the second control grease chamber 132, accompany with it, cam ring 117 is to the swing of offset augment direction, and therefore, the performance head pressure further increases so described high pressure characteristics Y (the T2 interval among Figure 40) significantly.

Like this, according to present embodiment, can obtain possessing the oil pump of the head pressure characteristic that the rotating speed with motor is complementary with cheaper manufacture cost.

In addition, the operating pressure of valve timing control gear is set at the P1 among the above-mentioned low pressure characteristic X, the cracking pressure of oil nozzle 30 is set at the P3 of high pressure characteristics Y, the above-mentioned first working hydraulic pressure Px is set at the hydraulic pressure that fully is lower than above-mentioned P3, therefore, the action effects same such as energy consumption that can be reduced with the respective embodiments described above.

In addition, in the respective embodiments described above, the interior pressure of controlling the relative first control grease chamber 131 of interior pressure of grease chamber 132 by the active force and second that makes helical spring 118 averages out, control the action of cam ring 117, but also can be according to pump size, the compression area of first compression face 133 is set at bigger than the compression area of second compression face 134, thereby cancellation helical spring 118 is only controlled the action of cam ring 117 by the interior pressure (differential pressure) of above-mentioned two pressure chambers 31,32.

In addition, in the respective embodiments described above, though the compression area of above-mentioned second compression face 134 is set at littler than the compression area of first compression face 133, the requirement according to internal-combustion engine etc. also can be set at above-mentioned two compression faces 133,134 equal.

In addition, for the tightness of guaranteeing above-mentioned control grease chamber is provided with sealed member, as long as but can satisfy the hydraulic characteristic that requires of internal-combustion engine, for reducing cost, also can cut down sealed member.

Also can further change the configuration of above-mentioned spring accommodation chamber, in addition, two helical spring setting load can freely be set according to pump size or size respectively, and its coil diameter or length also can freely change.

In addition,, be not limited to the valve timing control gear as variable valve gear, also go for hydraulic pressure be the action source, for example can change mechanical valve (Machine Seki man's cap used in ancient times) the operating angle and the lift amount variable mechanism of lifting capacity etc.

In addition, also this variable displacement pump can be applied to internal-combustion engine hydraulic equipment class in addition etc.

Below, the technological thought of the invention of the above-mentioned requirements protection grasped from above-mentioned mode of execution is described.

[a] invents described variable displacement pump as first aspect, it is characterized in that,

Described second head pressure is set at the high pressure of pressure that begins to discharge oil than above-mentioned oil nozzle.

According to the present invention, except that the action effect of first aspect invention, by second head pressure being set, can be more reliably spray and be not subjected to about the state of cooling unequal of the rising of oil temperature or internal-combustion engine to piston from oil nozzle than the pressure height that sprays from oil nozzle.

[b] invents described variable displacement pump as first aspect, it is characterized in that,

Above-mentioned oil nozzle possesses: main body, and it has the Oil Guide portion of the oil importing that is supplied to oily fuel feeding portion, will be fed into this fuel feeding portion, the valve seat that forms between this fuel feeding portion and Oil Guide portion;

Valve body, it is according to the pressure of the oil that is fed into described fuel feeding portion, leaves or is installed in described valve seat and open and close described fuel feeding portion;

Force application part, its to described valve body to closing the valve direction application of force, and, the cracking pressure of described valve body is set at than the high pressure of described first head pressure;

Nozzle, its downstream side with described Oil Guide portion is connected, and sprays oil from jetburner towards described piston.

[c] invents described variable displacement pump as first aspect, it is characterized in that,

Described movable part is the cam ring that is formed with camming surface at inner peripheral surface,

Described pump structure body possesses: rotor, and it is driven by the internal-combustion engine rotation; Blade, it is arranged to from the outer circumferential side of this rotor free to advance or retreat, and is divided into described a plurality of working room by the inner peripheral surface direction turnover to described cam ring,

By described cam ring is moved, change the offset of cam ring with respect to described centre of rotor.

[d] invents described variable displacement pump as the c aspect, it is characterized in that,

The described oil that is discharged from is used for the slide part of internal-combustion engine is lubricated.

[e] invents described oil nozzle as the third aspect, it is characterized in that,

Described oil nozzle is begun to spray oily pressure to be set at lower than described second head pressure.

[f] invents described variable displacement pump as first aspect, it is characterized in that,

The described oil that is discharged from also is used to make the locking mechanism of valve timing control gear and this valve timing control gear to move, and wherein said valve timing control gear can change the rotary driving body of internal-combustion engine and the relative rotatable phase of camshaft,

The pressure of removing the locking of described locking mechanism is set to than the low pressure of described first head pressure.

Claims (9)

1. variable displacement pump reaches authorized pressure when above at the pressure of the oil that is supplied to, and this variable displacement pump is supplied with oil to the oil nozzle that the piston to internal-combustion engine sprays oil, and this variable displacement pump is characterised in that to possess:

The pump structure body, it is driven by the rotation of described internal-combustion engine, thereby will discharge from discharge portion according to the volume-variation of described working room from the oil that suction portion flows into a plurality of working rooms;

Movable part, it makes from the flow minimizing of the oil of described discharge portion discharge by moving to a direction; And

Control gear, when the head pressure of described oil reaches first head pressure, described control gear makes described movable part move established amount to a direction, when the head pressure of described oil reaches than high second head pressure of described first head pressure, described control gear further moves described movable part to a direction

Described first head pressure is set at the low pressure of pressure that begins to spray oil than described oil nozzle.

2. variable displacement pump as claimed in claim 1 is characterized in that, described second head pressure is set at the high pressure of pressure that begins to discharge oil than described oil nozzle.

3. variable displacement pump as claimed in claim 1 is characterized in that,

Described oil nozzle possesses:

Main body, it has the Oil Guide portion of the oil importing that is supplied to oily fuel feeding portion, will be fed into this fuel feeding portion, the valve seat that forms between this fuel feeding portion and Oil Guide portion;

Valve body, it is according to the pressure of the oil that is fed into described fuel feeding portion, leaves or is installed in described valve seat and open and close described fuel feeding portion;

Force application part, its to described valve body to closing the valve direction application of force, and, the cracking pressure of described valve body is set at than the high pressure of described first head pressure;

Nozzle, its downstream side with described Oil Guide portion is connected, and sprays oil from jetburner towards described piston.

4. variable displacement pump as claimed in claim 1 is characterized in that,

Described movable part is the cam ring that is formed with camming surface at inner peripheral surface,

Described pump structure body possesses: rotor, and it is driven by the internal-combustion engine rotation; Blade, it is arranged to from the outer circumferential side of this rotor free to advance or retreat, and is divided into described a plurality of working room by the inner peripheral surface direction turnover to described cam ring,

By described cam ring is moved, change the offset of cam ring with respect to described centre of rotor.

5. variable displacement pump as claimed in claim 4 is characterized in that, the described oil that is discharged from is the oil that is used for the slide part of lubricated internal-combustion engine.

6. variable displacement pump as claimed in claim 1 is characterized in that,

The described oil that is discharged from also is used to make the locking mechanism of valve timing control gear and this valve timing control gear to move, and wherein said valve timing control gear can change the rotary driving body of internal-combustion engine and the relative rotatable phase of camshaft,

The pressure of removing the locking of described locking mechanism is set to than the low pressure of described first head pressure.

7. lubrication system of using variable displacement pump is characterized in that possessing:

Oil nozzle, its pressure at the oil that is supplied to reach authorized pressure when above, spray oil to the piston of internal-combustion engine;

Variable displacement pump, it possesses: the pump structure body, it is driven by the rotation of described internal-combustion engine, thereby will discharge from discharge portion according to the volume-variation of described working room from the oil that suction portion flows into a plurality of working rooms; Movable part, it makes from the flow minimizing of the oil of described discharge portion discharge by moving to a direction; And control gear, when the head pressure of described oil reaches first head pressure, described control gear makes described movable part move established amount to a direction, when the head pressure of described oil reaches than high second head pressure of described first head pressure, described control gear further moves described movable part to a direction

Described first head pressure is set at the low pressure of pressure that begins to spray oil than described oil nozzle.

8. oil nozzle reaches authorized pressure when above at the pressure of the oil of supplying with from variable displacement pump, and described oil nozzle is discharged oil to the piston of internal-combustion engine, wherein,

Described variable displacement pump possesses: the pump structure body, and it is driven by the rotation of described internal-combustion engine, thereby will discharge from discharge portion according to the volume-variation of described working room from the oil that suction portion flows into a plurality of working rooms; Movable part, it makes from the flow minimizing of the oil of described discharge portion discharge by moving to a direction; And control gear, when the head pressure of described oil reaches first head pressure, described control gear makes described movable part move established amount to a direction, when the head pressure of described oil reaches than high second head pressure of described first head pressure, described control gear further moves described movable part to a direction

Beginning to spray oily pressure from described oil nozzle is set at than the high pressure of described first head pressure.

9. the oil nozzle shown in claim 8 is characterized in that, described oil nozzle is begun to spray oily pressure be set at lower than described second head pressure.

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