CN102644589A

CN102644589A - Oil pump

Info

Publication number: CN102644589A
Application number: CN2011104005320A
Authority: CN
Inventors: 大西秀明; 佐贺浩二; 渡边靖
Original assignee: Hitachi Automotive Systems Ltd
Current assignee: Hitachi Astemo Ltd
Priority date: 2011-02-17
Filing date: 2011-12-06
Publication date: 2012-08-22
Also published as: US20120213655A1; JP5564450B2; JP2012172516A

Abstract

An oil pump includes: a valve receiving hole including; a first port connected with the suction port, a second port connected with the switching port, a third port connected with the discharge port, and a discharge pressure introduction port arranged to receive the discharge pressure, a valve element arranged to switch a first state in which the second port and the third port are connected, and a second state in which the first port and the second port are connected; and an urging member arranged to urge the valve element toward the first end side, the pressure receiving area of the valve element and the urging force of the urging member being set so that the oil pump is switched from the first state to the second state when the pressure within the hydraulic fluid chambers to which the switching port is opened is a negative pressure.

Description

Oil pump

Technical field

The present invention relates to oil pump, it is applicable to the hydraulic power to supply action oil such as each slide parts of for example motor vehicle internal combustion engine.

Background technique

As the existing oil pump that is applicable to the internal-combustion engine of Motor Vehicle, known have a disclosed technology in the for example following patent documentation 1.

Put it briefly; This oil pump is so-called variable displacement vane pump; Through spring cam ring is applied and to make it keep eccentric active force, and control the offset of this cam ring, thereby make discharge capacity variable based on the head pressure that is imported into by the control grease chamber that marks off between housing and the cam ring with respect to rotating center of rotor; Reduce the driving torque of pump, realize energy-conservationization.

Patent documentation 1: (Japan) spy opens the 2008-309049 communique

In recent years, expectation can increase discharge capacity and realize the miniaturization of pump through making existing said oil pump to be higher than the rotating speed high-speed driving of internal-combustion engine.

But if make the such high-speed driving of existing said oil pump, then intake does not catch up with, and cavitation occurs, thereby can not guarantee enough discharge capacitys.

Summary of the invention

Therefore, in view of the technical problem of above existing oil pump, even the object of the present invention is to provide a kind of oil pump that when high speed rotating, also can suppress the generation of cavitation and can guarantee enough discharge capacitys.

A kind of oil pump of the present invention is characterized in that having: the pump structure body, and it is driven by the internal-combustion engine rotation, so that the volume of a plurality of actions grease chamber increases and decreases continuously; The duct body, it comprises: switching duct, the volume in said action grease chamber of upstream side opening that the suction passage of the volume enlarged area opening in said action grease chamber, the volume in said action grease chamber dwindle the zone dwindles the discharge duct of the downstream side opening in zone; The valve accepting hole; The inner circumferential surface opening be formed with first duct that is communicated with said suction passage, with second duct of said switching hole link, with the 3rd duct of said discharge hole link, and be provided with the hydraulic pressure that is used to import in the said discharge duct in an end of said valve accepting hole be that the head pressure of head pressure imports the duct; Spool, it is housed in the said valve accepting hole sliding freely, can switch on following two states; First state; Limit being communicated with between said first duct and said second duct, make said second duct and said the 3rd hole link, second state; Make said first duct and said second hole link, limit being communicated with of said second duct and said the 3rd duct; Force application part, it is arranged on the other end side of said valve accepting hole, and said spool is applied towards one of said valve accepting hole distolateral active force; One of the said spool of the said head pressure effect distolateral compression area and the active force of said force application part are set, switched to said second state from said first state when becoming negative pressure with the pressure in the said action grease chamber that is formed with said switching duct at opening.

Another kind of oil pump of the present invention is characterized in that having: the pump structure body, and it is driven by the internal-combustion engine rotation, so that the volume of a plurality of actions grease chamber increases and decreases continuously; The duct body, it comprises: switching duct, the volume in said action grease chamber of upstream side opening that the suction passage of the volume enlarged area opening in said action grease chamber, the volume in said action grease chamber dwindle the zone dwindles the discharge duct of the downstream side opening in zone; Control mechanism; When the pressure in opening is formed with the said action grease chamber in said switching duct becomes the low speed rotation of positive pressure; Said switching duct and said discharge duct together will be moved oil and be expelled to the outside; When the pressure in opening is formed with the said action grease chamber in said switching duct becomes the high speed rotating of negative pressure, action oil is supplied to said switching duct from the low voltage section that is communicated with said suction passage.

Another kind of oil pump of the present invention is characterized in that having: the pump structure body, and it is driven by the internal-combustion engine rotation, so that the volume of a plurality of actions grease chamber increases and decreases continuously; The duct body, it comprises at least: the suction passage of the volume enlarged area opening in said action grease chamber, the volume in said action grease chamber dwindle the discharge duct of regional opening; Control mechanism, when the rotating speed of pump is to make when being positioned at the pressure of said action grease chamber that volume dwindles the upstream side in zone and becoming the rotating speed of negative pressure, action oil flows into this from low voltage section becomes the said action grease chamber of negative pressure.

Particularly, the invention is characterized in, when rotating speed becomes the pressure that makes in internal capacity dwindles the said action grease chamber of upstream side opening in zone and becomes the rotating speed of negative pressure, control, become the action grease chamber of negative pressure so that action oil flows into this from low voltage section.

According to the present invention; When the pressure in the said action grease chamber of the upstream side opening in the zone that portion's volume within it dwindles becomes the high speed rotating of negative pressure,, therefore can increase intake owing to supply with action oil to this action grease chamber that becomes negative pressure from low voltage section; Thereby; Even when high speed rotating, still can suppress the generation of cavitation, guarantee enough discharge capacitys.

Description of drawings

Fig. 1 is the plan view that constitutes the Equilibrator of oil pump of the present invention integratedly.

Fig. 2 is the sectional view through the A-A line of Fig. 1.

Fig. 3 is the plan view of Equilibrator shown in Figure 1.

Fig. 4 is the worm's eye view of Equilibrator shown in Figure 1.

Fig. 5 is the exploded perspective view of the oil pump structure of expression first embodiment of the invention.

Fig. 6 is the longitudinal section of oil pump shown in Figure 5.

Fig. 7 is the sectional view through the B-B line of Fig. 5.

Fig. 8 is the figure from looking sideways with the involutory surface of case member of pump housing monomer shown in Figure 5.

Fig. 9 is the figure from looking sideways with the involutory surface of the pump housing of case member monomer shown in Figure 5.

Figure 10 is the plotted curve of relation of spring load and the cam ring angle of oscillation of expression two springs shown in Figure 7.

Figure 11 is the rear view of oil pump shown in Figure 5.

Figure 12 is the sectional view through the C-C line of Figure 11.

Figure 13 is the figure from looking sideways with the involutory surface of case member of control valve (valve body) shown in Figure 12.

Figure 14 (a) and (b) be the hydraulic circuit diagram of the oil pump of first mode of execution, (a) expression first state of the present invention, (b) expression second state of the present invention.

Figure 15 is the plotted curve of hydraulic characteristic of the oil pump of expression first mode of execution.

Figure 16 (a)～(d) is the figure of state of phase place and the oil hydraulic circuit of expression each interval reaction ring shown in Figure 15, (a) representes interval a, (b) representes interval b, (c) representes interval c, (d) representes interval d, (e) representes interval e.

Figure 17 (a) and (b) be the hydraulic circuit diagram of the oil pump of second mode of execution, (a) expression first state of the present invention, (b) expression second state of the present invention.

Figure 18 (a) and (b) be the hydraulic circuit diagram of the oil pump of the 3rd mode of execution, (a) expression first state of the present invention, (b) expression second state of the present invention.

Description of reference numerals

10 oil pumps

11 pump housings (duct body)

12 housing parts (duct body)

15 rotors (pump structure body)

16 impellers (pump structure body)

17 cam rings (pump structure body)

18 ring portions (pump structure body)

21,31 suction passages

22,32 discharge ducts

23,33 switching ducts

40 control valves

41 valve bodies (valve accepting hole)

43 spools

44 valve springs (force application part)

45 back pressure ducts (head pressure importing duct)

46 first ducts

47 second ducts

48 the 3rd ducts

PR pump chamber (action grease chamber)

Embodiment

Below, be elaborated with reference to accompanying drawing each mode of execution to oil pump of the present invention.In addition, in following explanation,, describe to be example as the oil pump of the lubricant oil of the valve arrangement for controlling timing IC engine supply that opens and closes the time to the slide part of motor vehicle internal combustion engine and controller valve with this oil pump.

Fig. 1～Figure 16 shows first mode of execution of oil pump of the present invention, and this oil pump 10 is arranged on the Equilibrator 1 integratedly, and is driven by this Equilibrator 1.Said bascule 1 is arranged on the bottom of internal combustion engine, is used to reduce the secondary vibration (2 vibrations) of internal combustion engine.

Therefore, before said oil pump 10 is described, at first said Equilibrator 1 is carried out schematic illustration; Like Fig. 1～shown in Figure 4; It is inner that this Equilibrator 1 is contained in the not shown food tray that is arranged on the internal-combustion engine bottom, mainly comprises: upper shell 2, and it is integrally formed in said food tray; Lower shell body 3, it is installed in the bottom of said upper shell 2; A pair of trunnion shaft is the live axle 4 of driving side and the driven shaft 5 of the slave end driven with it, and it is rotatably freely supported on two housings 2, between 3 and along the fore-and-aft direction of internal-combustion engine be axially disposing side by side of bent axle 6; Spiral actuation gear 4a and driven gear 5a, it is separately fixed at the end (right-hand end in Fig. 2) of two said axles 4,5 on axially, the counterrotating each other through intermeshing.The power of the bent axle 6 that transmits via chain 7 drives said live axle 4 with two times of rotating speeds of this bent axle 6, and on the other hand, and oppositely driven with live axle 4, rotating speed is identical with this live axle 4 via said gear 4a, 5a for said driven shaft 5.

And said oil pump 10 is installed in the front end of said Equilibrator 1, and its live axle 14 is linked to driven shaft 5 the other end on axially, is driven in rotation through the power that transmits from this driven shaft 5.And, in lower shell body 3, be provided with the oil purifier 8 that is used to suck the action oil that is stored in the said food tray, the action oil that is picked up by this oil purifier 8 through be arranged on these lower shell body 3 inner not shown suction paths be imported into oil pump 10 after state suction port 21a.On the other hand; In upper shell 2, be provided with and be used for the tap hole 2a of action oil pressure to (importing) not shown cylinder body (シリ Application ダ Block ロッ Network); State the action oil that exhaust port 22a discharges behind the oil pump 10 and be imported into said tap hole 2a, be discharged to said cylinder body via this tap hole 2a through being formed at two said

housing

2,3 inner not shown drain passageways.

Like this; Through making said oil pump 10 be integrally formed in Equilibrator 1; Can make the action oil of discharging be supplied to internal-combustion engine, make pipe arrangement that oil pump 10 is connected with internal-combustion engine etc., make the simplification of internal-combustion engine peripheral structure thereby need not to be provided with in addition through Equilibrator from this oil pump 10.

Below, said oil pump 10 of the present invention is specified, shown in Fig. 5～7; This oil pump 10 has: pump case (duct of the present invention body (Port one ト Block ロッ Network)); It is made up of the pump housing 11 and housing parts 12, and a distolateral opening of the said pump housing 11 has the pump containing room 13 of stating the pump structure body after inside contains; The cross section is roughly " コ " shape, and 12 sealings of said housing parts are positioned at the distolateral opening of this pump housing 11 1; Live axle 14, it is rotatably freely supported on said pump case, connects the approximate centre portion of said pump containing room 13, is driven by said Equilibrator 1 rotation; The pump structure body, it is housed in the said pump containing room 13, is driven by live axle 14, and along the rotation of the counter clockwise direction among Fig. 7, being formed at its inner a plurality of actions grease chamber with increase and decrease is the volume of pump chamber PR, realizes pumping action.

Wherein, said pump structure body has: rotor 15, and its rotation is housed in the pump containing room 13 freely, and central part is incorporated on live axle 14 peripheries; Impeller 16, it is housed in radial cutting free to advance or retreatly respectively and forms (Japanese: cut and owe to form) in a plurality of otch 15a of said rotor 15 peripheral parts; Cam ring 17, it can be configured in the outer circumferential side of said rotor 15 prejudicially with respect to the rotating center of rotor 15, together marks off each said pump chamber PR with two

impellers

16,16 of said pump case, rotor 15 and adjacency; A pair of

ring portion

18,18, its diameter are configured in the both sides of all sides in this rotor 15 sliding freely less than said rotor 15.

The said pump housing 11 is one-body molded by aluminum alloy material, and like Fig. 5～shown in Figure 8, the substantial middle position at the end wall 11a of this pump housing 11 of an end wall that forms pump containing room 13 connects to be formed with and rotates a bearing at end hole 11b of supporting driving shaft 14 freely.And, the assigned position on pump containing room 13 inner circle walls, cutting is formed with cross section and is the support slot 11c of semicircle shape roughly, and cam ring 17 is swung via pivot pin 19 and is supported on said support slot 11c freely.And; Be formed with on the inner circle wall of pump containing room 13 with after state the sealing sliding contact surface 11d of sealed member 20 sliding contacts; Sealing sliding contact surface 11d is configured on the peripheral part of cam ring 17; M is positioned at the Y axle negative direction side of Fig. 7 with respect to the straight line at the center of center that links bearing hole 11b and support slot 11b (below, be called " cam ring reference line ").Sealing sliding contact surface 11d is planar so that to be the center of circle form circular arc by the radius R 1 of regulation the center of support slot 11c; Length on its circumferencial direction is set in the eccentric swing scope of cam ring 17 can keep the length of sliding contact with said sealed member 20; When cam ring 17 eccentric swings; Along sealing sliding contact surface 11d cam ring 17 is carried out sliding guidance, carry out so that the action of this cam ring 17 (eccentric swing) is smooth and easy.

And; Like Fig. 7, shown in 8, on the inner side surface of the end wall 11a of the said pump housing 11, the outer regions of bearing hole 11b particularly; With zone that each said pump chamber PR volume is enlarged (below; Be called " volume enlarged area ") mode of upper shed, cutting is formed with the roughly suction passage 21 of circular arc concavity, the action oil that comes self balancing device 1 side via after state suction port 21a and be imported into this suction passage 21.On the other hand; Dwindle the downstream side in zone (below, be called " volume dwindles the zone ") at the volume of each said pump chamber PR, cutting is formed with the roughly discharge duct 22 of circular arc concavity; It will state exhaust port 22a after will importing from the action oil that each said pump chamber PR discharges; And dwindle the upstream side in zone (below, be called " volume dwindles the zone ") at the volume of said pump chamber PR, cutting is formed with the roughly switching duct 23 of circular arc concavity; It can be that head pressure is switched said suction passage 21 or discharged duct 22 according to the action oil pressure of internal-combustion engine, discharges duct 22 and switches duct 23 respectively across bearing hole 11b and relative with suction passage 21.

Roughly neutral position on the circumferencial direction of said suction passage 21; Be provided with integratedly and state the importing portion 24 that the first spring containing room, 28 sides expand backwards, near the boundary portion of importing portion 24 and suction passage 21, promptly; The starting point position of this suction passage 21; Perforation is formed with suction port 21a, and the end wall 11a of this suction port 21a perforation pump housing 11 is also open facing outward, to be connected with Equilibrator 1 interior said suction path.Thus; Be imported into suction port 21a by the action oil that from said food tray, picked up through said suction path via oil purifier 8, the negative pressure that the pumping action through said pump structure body produces and will move and oilyly be supplied to each the pump chamber PR that is positioned at the capacity enlarged area via importing portion 24 and suction passage 21.And, said suction port 21a and importing portion 24 and be formed at cam ring 17 outer regions after state low pressure chamber 36 and be communicated with, thereby the low pressure action oil that pressure arrives said suction pressure also is imported into this low pressure chamber 36.Wherein, low voltage section of the present invention be comprise 21 that be communicated with the suction passage, make the notion of pressure at the four corner of said suction pressure, mainly comprise said suction passage 21, be adjacent importing portion 24 and low pressure chamber 36 of setting etc.

End side in said discharge duct 22, perforation is formed with exhaust port 22a, and the end wall 11a of this exhaust port 22a perforation pump housing 11 is also open facing outward, to be connected with Equilibrator 1 interior said drain passageway.Thus; Pressurized action oil is pressed towards and discharges duct 22 through the pumping action of said pump structure body, this action oily from exhaust port 22a through said drain passageway etc. and via being arranged on each slide part or the valve arrangement for controlling timing etc. that not shown working connection (オイ Le メイ Application ギャラリ) in the said cylinder body is supplied to internal-combustion engine.Wherein, Said exhaust port 22a expands towards radial outside with respect to the two ends on the circumferencial direction of discharging duct 22, said exhaust port 22a outer half side via be formed at cam ring 17 inner after state first access 38 and be arranged on housing parts 12 sides after state and discharge duct 32 (the second intercommunicating pore 32a) and be communicated with.

And; Near the starting point in said discharge duct 22; Cutting is formed with the connectivity slot 25 that is communicated with said discharge duct 22 and bearing hole 11b; Supply with action oil via this connectivity slot 25 to bearing hole 11b, and supply with action oil, thereby can guarantee each sliding position good lubricating property to the sidepiece of rotor 15 and each impeller 16.In addition, the advance and retreat direction of this connectivity slot and each impeller 16 is inconsistent, thereby can suppress to drop to when each said impeller 16 is advanced and retreat said connectivity slot 25.In addition; On the initial end in said discharge duct 22; Opening is formed with an end of internal path 26; It is inner that this internal path 26 is arranged on the end wall 11a of the pump housing 11, make said discharge duct 22 with after state control grease chamber 37 and be communicated with, state after the oily part of action that is pressed towards said discharge duct 22 through this internal path 26 is imported into and control grease chamber 37.

Terminal part position in said switching duct 23; Be provided with the interconnecting part 27 that expands towards radial outside integratedly, said switching duct 23 via this interconnecting part 27 and be formed at cam ring 17 inner after state second access 39 and be communicated with the switching duct 33 (third connecting hole 33a) of housing parts 12 sides.

Like Fig. 5, shown in Figure 9; Said housing parts 12 is roughly tabular; Be installed on the open end of the pump housing 11 through a plurality of bolt B 1,, connect to be formed with and rotate another distolateral bearing hole 12a of supporting driving shaft 14 freely in the position relative with the bearing hole 11b of the pump housing 11.And; On the inner side surface of the housing parts 12 of another end wall that constitutes pump containing room 13; In the position relative with being arranged on the said duct of on the pump housing 11 each 21～23, cutting is formed with the identical suction passage 31 in structure and each said duct 21～23, discharges duct 32 and switching duct 33 respectively.And, the terminal part in this suction passage 31, connect be formed with after state the first intercommunicating pore 31a that first duct 46 of control valve 40 is connected; And; Discharging the intermediate portion in duct 32, connect be formed with after state the second intercommunicating pore 32a that second duct 47 of control valve 40 is connected, in addition; Switching the terminal part in duct 33, connect be formed with after state the third connecting hole 33a that the 3rd duct 48 of control valve 40 is connected.

As shown in Figure 2; The end 14a of said live axle 14 on axially connects the end wall 11a of the pump housing 11 and towards the outside; But the driven shaft 5 that one is linked to Equilibrator 1 rotatably the other end on axially, the rotating force that transmits from said driven shaft 5 makes the counter clockwise direction rotation of rotor 15 along Fig. 6.Wherein, As shown in Figure 7, the center through said live axle 14 and with the straight line of said straight line M quadrature (below, be called " cam ring eccentric direction line ") N be the separatrix that volume enlarged area and volume dwindle the zone; Under common state; When stating control valve 40 promptly and being in first state, the X axle negative direction side of said straight line N is for sucking the zone, and the postive direction side is a discharging area.

Like Fig. 5～shown in Figure 7; Cutting is formed with radial a plurality of said otch 15a from its central side towards radial outside on said rotor 15; And,, be respectively arranged with and be used to import the back pressure chamber 15b that the cross section of discharging oil is the circular shape at the inboard base end part of each said otch 15a; Centrifugal force that produces through the rotation with said rotor 15 and the pressure in the back pressure chamber 15b are pressed to the outside with each said impeller 16.

When rotor 15 rotations, each front-end face of each said impeller 16 and the inner peripheral surface sliding contact of cam ring 17, and, each the cardinal extremity face of each said impeller 16 and the outer circumferential face sliding contact of each said ring portion 18,18.Promptly; Each said impeller 16 pressed to the radial outside of rotor 15 through each said

ring portion

18,18; Even under the little situation of the pressure of internal-combustion engine rotational speed low perhaps said centrifugal force, back pressure chamber 15b; Still can make each front end respectively with the inner peripheral surface sliding contact of cam ring 17, liquid thickly forms each said pump chamber PR.

The cam ring 17 has a substantially cylindrical shape, the so-called sintered metal integrally formed in said outer peripheral portion of the cam ring 17 on the predetermined position in the axial grooves formed by cutting a substantially circular arc-shaped pivot portion 17a, The pivot portion 17a is fitted with the pivot pin 19 to constitute an eccentric swing fulcrum, the cam ring 17 via a center of the shaft portion 17a opposite to the side opposite to the position in the radial direction is provided with each of the latter projecting said spring 34,35 linked (linked) arm 17b.And, on the both sides on the said arm 17b sense of rotation, relatively dispose first spring 34 with regulation elasticity coefficient, elasticity coefficient second spring 35 less than said first spring 34.Wherein, on a sidepiece on the said arm 17b sense of rotation, extend be provided be circular arc convex roughly push protuberance 17c; On the other hand; On another sidepiece on the said arm 17b sense of rotation, outstanding be provided with length greater than after state the push projection 17d of limitation part 30 thickness, the said front end maintenance butt of pushing protuberance 17c and first spring 34; The front end of the said push projection 17d and second spring 35 keeps butt, so that arm 17b and each said spring 34,35 interlock.

And; According to this structure; As shown in Figures 7 and 8, in the inside of the said pump housing 11, with the relative position of said support slot 11b; First, second spring reception room 28,29 of accommodating and keeping first, second spring 28,29 along the Y direction among Fig. 7 and pump reception room 13 in abutting connection with being provided with; In the first spring reception room 28, first spring 34 keeps regulation load W1 being set and elasticity is installed between the end wall and arm 17b (pushing teat 17c) of the first spring reception room 28, on the other hand; In the second spring reception room 29, line footpath (line footpath) elasticity is installed between the end wall and arm 17b (push projection 17d) of the second spring reception room 29 less than second spring, 35 maintenance regulation load W2 being set of said first spring 34.And; At said first, second spring reception room 28, between 29, be provided with the restrictions 30 that diameter is step-like and dwindles (section difference undergauge), sidepiece of this restrictions 30 and another sidepiece butt of arm 17b; Thereby limited the slewing area on the said arm 17b counter clockwise direction; On the other hand, the front end butt of another sidepiece of said restrictions 30 and second spring 35, thus limited the maximum elongation amount of said second spring 35.

Like this, the W0 that makes a concerted effort that load W1, W2 are set of two said

springs

34,35 promptly produces 34 pairs of said cam ring 17 application of forces of first spring of relatively large spring load; Thereby, keep said cam ring 17 is applied towards the active force that makes its offset augment direction (counter clockwise direction among Fig. 7) via arm 17b, thereby; As shown in Figure 7; Under said cam ring 17 non-action status, the push projection 17d of arm 17b gets in the second spring containing room 29 and makes 35 compressions of second spring, and another sidepiece of this arm 17b is pressed to a sidepiece of limitation part 30; Therefore, said cam ring 17 is limited in the offset maximum position.

And; As shown in Figure 7, at the peripheral part of said cam ring 17, give prominence to being provided with the 17e of sealing configuration portion that cross section is the general triangular shape; Sealing structural portion 17e has the relative and circular-arc sealing surface 17f concentric with sealing sliding contact surface 11d of sealing sliding contact surface 11d with the pump housing 11; And on the sealing surface 17f of sealing structural portion 17e, the sealing that cutting vertically is formed with the rectangular shape of cross section keeps groove 17g; In sealing keeps groove 17g, accommodate and maintain when cam ring 17 eccentric swings sealed member 20 with sealing sliding contact surface 11d sliding contact.Wherein, said sealing surface 17f between sealing sliding contact surface 11d and sealing surface 17f, is formed with the micro-gap of regulation with than the radius R 1 slightly little predetermined radius R2 of said sealing sliding contact surface 11d and constitute.

In addition; Said sealed member 20 is by the fluorine resin material that for example has low frictional behavior; Form axial elongated straight line shape along cam ring 17; Be pressed against on the sealing sliding contact surface 11d through being arranged on the elastic force that seals the rubber system elastic member 20a that keeps groove 17g bottom, keep the close state of liquid between said sealing sliding contact surface 11d and the sealing surface 17f thereby make.

In addition; Two said

spring containing rooms

28,29 are particularly via said importing portion 24, suction passage 21 and be communicated with low pressure chamber 36 and constitute; Through the action oil pressure in this low pressure chamber 36 cam ring 17 is kept by the state of pushing to pivot pin 19; Through pivot pin 19 and sealed member 20, and mark off the control grease chamber 37 of the eccentric swing that is used to control cam ring 17 in the outer regions of the cam ring 17 of the outer regions that is equivalent to switch duct 23.

The action oil of discharging in the duct 22 is constantly imported said control grease chamber 37 through internal path 26; Pump discharge head acts on the compression face 17h that is made up of the side in the face of the 17e of sealing configuration portion of this control grease chamber 37, thereby cam ring 17 is applied the oscillatory forces (locomotivity) towards the direction (clockwise direction among Fig. 7) that makes its offset minimizing.That is, this control grease chamber 37 constantly applies towards making its center be tending towards the active force with the concentric direction of the rotating center of rotor 15 cam ring 17 through said compression face 17h, carries out the amount of movement control of the concentric direction of this cam ring 17.

According to above structure; In said oil pump 10; The living active force towards concentric direction of in the spring load of the active force of eccentric direction and second spring 35 and control grease chamber 37, cutting down output that the spring load of first spring 34 produces has the power relation and the maintenance balance of regulation; In control grease chamber 37, cut down output living active force less than first spring 34 the load W1 and second spring 35 be set the poor of load W2 be set; That is, the W0 that makes a concerted effort that load is set of two said springs 34,35 (=W1-W2) time, cam ring 17 reaches maximum eccentric states shown in Figure 7; When what the rising of living active force with head pressure of cutting down output in the said control grease chamber 37 surpassed two said

springs

34,35 the making a concerted effort during W0 of load be set, cam ring 17 moves towards said concentric direction according to this head pressure.

Below; Relation to angle of oscillation (amount of movement) X of the spring load W of two said springs 34,35 and cam ring 17 specifies; Shown in figure 10, reach the position X1 of maximum eccentric states at cam ring 17, state after the living active force of in control grease chamber 37, cutting down output reaches and is equivalent to the active force that the first action oil pressure Pf produces two said springs 34,35 the making a concerted effort during W0 of load W1, W2 be set; First spring 34 shrinks; And second spring 35 begins elongation, and said cam ring 17 moves towards said concentric direction.Soon; Because of the increase of pump discharge head make control grease chamber 37 in cut down output active force living and increase and make second spring 35 and limitation part 30 butts; Thereby the support effect of second spring 35 is disappeared, and therefore said cam ring 17 is towards mobile the stopping (the position X2 among the figure) of concentric direction.And; Head pressure further increase and make control grease chamber 37 in cut down output living active force when reaching the spring load Wx of first spring 34 of stating the active force that the second action oil pressure Ps produces after being equivalent to; 34 beginnings of first spring are further shunk, and make said cam ring 17 further move (the position X3 among the figure) towards said concentric direction.

And; Particularly like Fig. 5, Figure 11～shown in Figure 13; In said oil pump 10; Be provided with control valve 40 (being equivalent to control mechanism of the present invention) at the back of housing parts 12, this control valve 40 comes the function of said switching valve 23 is carried out switching controls according to spool 43 position in the axial direction of control valve 40 by from being arranged on the head pressure control that the cam ring 17 first inner access 38 import.

Particularly shown in figure 12, said control valve 40 has: valve body 41, and it forms roughly tubular, a distolateral opening, the other end side seal closes; Plunger 42, it seals the opening portion of said valve body 41 1 ends; Spool 43, it is housed in the interior week of said valve body 41 vertically sliding freely, on each end of this spool 43, is formed with first 43a of back-up ring portion and second 43b of back-up ring portion with the inner peripheral surface sliding contact of valve body 41; Valve spring 44, its keep with after state that the duct switches that regulation that hydraulic pressure Pk equates is provided with load Wk and elasticity is installed between said valve body 41 1 plunger 42 and spool 43 in distolateral interior week, lasting to spool 43 another distolateral application of force to valve body 41.

The said back-up ring 43a of portion of each of the diameter of said valve body 41 and spool 43,43b are roughly the same, and said valve body 41 has: spool accommodation section 41a, and it accommodates said spool 43; Back pressure chamber structural portion 41b, it is step-like the other end that is arranged on said valve body 41 via stepped part 41c with respect to said spool accommodation section 41a with dwindling, the division of second 43b of back-up ring portion through spool 43 and form back pressure chamber 45 in inside; Said valve body 41 is fixed on the back side of housing parts 12 through a plurality of bolt B 2.And perforation is formed with respectively on the perisporium of said valve body accommodation section 41a: first duct 46, and it is connected with the first intercommunicating pore 31a via being arranged on the suction pressure lead-in groove 46a on valve body 41 inner side surfaces; Second duct 47, it is connected with the second intercommunicating pore 32a via being arranged on the head pressure lead-in groove 47a on valve body 41 inner side surfaces; The 3rd duct 48, it is connected with this third connecting hole 33a through direct opening on the 33a of third connecting hole.And; On the perisporium of said back pressure chamber structural portion 41b, connect and be formed with back pressure duct 49 (head pressure importing of the present invention duct); It keeps being connected with second duct 47 via being arranged on the connectivity slot 49a on valve body 41 inner side surfaces, and the action oil (head pressure) that is discharged to each said discharge duct 22,32 through the second intercommunicating pore 32a is constantly imported said back pressure duct 49.

The reduced of the intermediate portion of said spool 43 on axially; Between said spool 43 and valve body 41, form annulus 50 through two said back-up ring 43a of portion, 43b, the 3rd duct 48 is communicated with first duct 46 or second duct 47 via this annulus 50.

According to this structure; Shown in Figure 14 (a); Head pressure in being imported into back pressure chamber 45 lower and make this back pressure chamber 45 in cut down output under the state that load Wk is set of living active force less than valve spring 44, spool 43 (second 43b of back-up ring portion) pressed to the stepped part 41c of valve body 41 through the active force of this valve spring 44.Thus, first duct 46 is blocked by first 43a of back-up ring portion, via annulus 50 second duct 47 is communicated with the 3rd duct 48, thereby the effect (first state of the present invention) of discharging the duct is played in each said switching

duct

23,33.

On the other hand; Shown in Figure 14 (b); Head pressure in being imported into back pressure chamber 45 is that the rising of oil pump 10 rotating speeds raises with internal-combustion engine rotational speed; Cut down output in this back pressure chamber 45 under the state that load Wk is set of living active force greater than valve spring 44, under the effect of the active force that this head pressure produces, spool 43 overcomes the active force of valve spring 44 and moves towards one distolateral (plunger 42 sides) of valve body 41.Thus, first duct 46 is communicated with the 3rd duct 48 via annulus 50, and second duct 47 is communicated with back pressure duct 49, thereby the effect (second state of the present invention) of suction passage is played in each said switching

duct

23,33.

Wherein, When carrying out the duct switching controls of this control valve 40; The compression area of said spool 43 (second 43b of back-up ring portion) and the size that load Wk is set of valve spring 44 are set to, make each said switching

duct

23,33 in press to the active force balance roughly of active force and the valve spring 44 of the back pressure chamber 45 that the head pressure before the negative pressure produces, under first state; When pressing to negative pressure in each said switching

duct

23,33, switch to second state from first state.

Below, based on Figure 15, Figure 16 the characteristic action of the oil pump 10 of this mode of execution is described.

At first; Before the effect to said oil pump 10 describes; Based on Figure 15 the necessary hydraulic pressure as the internal-combustion engine of the head pressure of this oil pump 10 control benchmark is described, the P1 among the figure representes that first internal-combustion engine requires hydraulic pressure, the desired hydraulic pressure of this device when it for example is equivalent to adopt the valve arrangement for controlling timing in order to improve burnup performance etc.; P2 representes the second internal-combustion engine requirement hydraulic pressure among the figure; The desired hydraulic pressure of this device when it is equivalent to adopt oil sprayer for cooling piston, P3 representes the 3rd internal-combustion engine requirement hydraulic pressure among the figure, it is the lubricated desired hydraulic pressure of bearing portion of said bent axle when the internal-combustion engine high speed rotating.Curve E (double dot dash line) expression desirable necessary hydraulic pressure (head pressure) P corresponding that links said some P1～P3 among the figure with internal-combustion engine rotational speed R.And; Pf representes the first action oil pressure that begins to swing through the W0 that makes a concerted effort that the living active force of cutting down output in the control grease chamber 37 makes cam ring 17 overcome two said springs 34,35 among the figure, and Ps representes the second action oil pressure that makes cam ring 17 overcome the spring load W1 of first spring and begin to swing through the living active force of cutting down output in the control grease chamber 37 among the figure.Pk is set between two said action oil pressure Pf, the Ps, and hydraulic pressure is switched in the duct that expression is used to switch the connection in each said switching duct 23,33.

Promptly; In said oil pump 10; In the interval a of the Figure 15 that is equivalent to idling of IC engine operation, the W0 that makes a concerted effort through two said

springs

34,35 is the active force that the spring load of relatively large first spring 34 produces, and makes the offset of cam ring 17 remain on the maximum rating shown in Figure 16 (a).Thus; In a of this interval; Head pressure (hydraulic pressure in the internal-combustion engine) P fully switches hydraulic pressure Pk less than said duct; The spool 43 of control valve 40 is positioned near a side of back pressure chamber 45, and each said switching

duct

23,33 is in the state that is connected with each said

discharge duct

22,32 respectively, so that head pressure P and internal-combustion engine rotational speed R roughly increase pro rata.

Thereafter; Internal-combustion engine rotational speed R rises; When head pressure P reaches the first action oil pressure Pf that is higher than the said first internal-combustion engine requirement hydraulic pressure P1 and sets; Shown in Figure 16 (b),, make cam ring 17 overcome the active force of first spring 34 and begin the said concentric direction of court and move through the active force of living active force and second spring 35 of cutting down output in the control grease chamber 37.Afterwards, because the offset of cam ring 17 reduces gradually, and the increase of discharge capacity is limited, and increases (the interval b among Figure 15) thereby suppressed head pressure P with the rising of internal-combustion engine rotational speed R.Soon; Second spring 35 extends with moving of said cam ring 17; Shown in Figure 16 (c), at the front end and limitation part 30 butts of said second spring 35, then the support effect of this second spring 35 disappears; The mobile of said cam ring 17 stops, and head pressure P roughly increases (the interval c among Figure 15) with the rising of internal-combustion engine rotational speed R with this internal-combustion engine rotational speed R once more pro rata.

In this mode of execution; Said oil pump 10 is not to drive with existing internal-combustion engine (bent axle) rotating speed, but with the rotating speed of Equilibrator 1 (driven shaft 5) promptly two times of rotating speeds of existing rotating speed drive, therefore; In this oil pump 10; In the zone that surpasses regulation rotating speed Rk of internal-combustion engine rotational speed R, the generation of cavitation must appear, cause head pressure P can not with the proportional increase of the rising of internal-combustion engine rotational speed R.Promptly; Under two times of rotating speeds of existing rotating speed, the rotating speed of rotor 15 is too fast, and it is too short to cause pump chamber PR to be positioned at time in each 21,31 zone, said suction passage (volume enlarged area); Can not enough action oil be sucked in the said pump chamber PR and moves to each 23,33 zone, said switching duct (volume dwindles regional upstream side) that is communicated with each said discharge duct 22,32; Thereby,, also still be negative pressure state in the pump chamber PR relative with this zone even move to each 22,23 zone, said switching duct; Can not discharge capacity be increased with the rising of internal-combustion engine rotational speed R to each said switching duct 23,33 discharging operations oil.

And; This technical problem is particularly particularly remarkable in the impeller pump as said oil pump 10; In trochoid formula pump for example, because discharge capacity still increases with the rising of internal-combustion engine rotational speed after the generation of cavitation occurring, therefore the not enough situation of discharge capacity can appear hardly.

Therefore; In said oil pump 10; Head pressure P reach with the rising of internal-combustion engine rotational speed R the generation that causes cavitation be equivalent to said internal-combustion engine rotational speed Rk the time the said duct of head pressure when switching hydraulic pressure Pk; Shown in Figure 16 (d), in control valve 40, what the living active force of cutting down output in the back pressure chamber 45 surpassed valve spring 44 is provided with load Wk; Spool 43 overcomes said valve spring 44 load Wk being set and towards plunger 42 side shiftings, thereby makes control valve 40 switch to second state from first state.Consequently; Via annulus 50 first duct 46 is communicated with the 3rd duct 48; From the action oil of each said

suction passage

21,31 via third connecting hole 33a or second access 39 and be imported into each said switching

duct

23,33; Except that each said

suction passage

21,31, the effect of suction passage is also played in each said switching

duct

23,33.

Like this; Because the effect of suction passage is played in each said switching

duct

23,33; Add each said

suction passage

21,31; (sucking the zone) between the suction area that adds up to enlarges; Prolonged pump chamber PR and be positioned at the time in this suction zone, thereby can not supply with enough action oil and make volume dwindle the pump chamber PR supply enough action oil of upstream side (respectively switching the zone in duct 23,33) to becoming negative pressure in zone, suppressed the generation of cavitation to the above-mentioned zone of each said

suction passage

21,31 that only depends on.

And; During said control valve 40 switches to second state from first state; Because first duct 46 in this control valve 40 dwindles with the amount of connection in second duct 47 gradually; Intrinsic discharge capacity (discharge capacity that pump whenever rotates a circle) reduces, even cause internal-combustion engine rotational speed R to rise, the increasing amount of head pressure P still changes in a period of time hardly; But after completion was switched in said duct, head pressure P roughly increased (the interval d among Figure 15) with the rising of internal-combustion engine rotational speed R with this internal-combustion engine rotational speed R once more pro rata.

In addition, at this moment, because said control valve 40 switches to second state; Discharging area dwindles, and the volume that is positioned at the pump chamber PR of this discharging area dwindles, and action oil is discharged to each said

discharge duct

22,32 under this state; Therefore, compare when being positioned at first state, though theoretic discharge capacity reduces with this control valve 40; But owing to the generation of cavitation do not occur, actual discharge capacity increases.

Thereafter; Internal-combustion engine rotational speed R further rises; When head pressure P reaches the second action oil pressure Ps that is higher than said the 3rd internal-combustion engine requirement hydraulic pressure P3 and sets; Shown in Figure 16 (e), the living active force of cutting down output in the control grease chamber 37 makes cam ring 17 overcome the spring load Wx of first spring 34 and begins further to move towards said concentric direction.So with reducing of cam ring 17 offsets, the increase of discharge capacity is limited, thus, can suppresses head pressure P and increase (the interval e among Figure 15) with the rising of internal-combustion engine rotational speed R.

Like this; In said oil pump 10; Through two said

springs

34,35 and control valve 40 and cam ring 17 is swung control; So that therefore the multistage increase of head pressure P can not make said head pressure P invalidly increase, thereby can access the characteristic (with reference to Figure 15) that very meets internal-combustion engine requirement hydraulic pressure (curve E).

And, in said oil pump 10, when carrying out head pressure P when surpassing said duct and switching the high speed rotating of hydraulic pressure Pk; And the said

suction passage

21,31 of each said switching

duct

23,33 and each is connected; Also, when this high speed rotating, suck more action oil, guarantee suitable discharge capacity from the angle of the generation that suppresses cavitation; Thereby can make this oil pump 10 make idle work hardly, can not cause the burnup mis-behave.

As stated; According to the oil pump 10 of this mode of execution, make when carrying out high speed rotating when being positioned at pump chamber PR that said volume dwindles the upstream side (each 23,33 zone, said switching duct) in zone and reaching negative pressure, through switching control valve 40; Can supply with action oil from each said switching

duct

23,33; Thereby intake is increased, therefore can solve the technical problem the generation that promptly when high speed rotating, suppresses cavitation, guarantee enough discharge capacitys.

In other words; In said oil pump 10, when it carries out said high speed rotating, because can be from each said switching

duct

23,33 suction actions oil; Therefore the zone (sucking the zone) of suction action oil enlarges during high speed rotating; The time (respiratory time) that pump chamber PR is positioned at this suction zone prolongs, thereby can guarantee enough intakes, suppresses the generation of cavitation.

And; In said oil pump 10, during cam ring 17 moved towards said concentric direction, the part owing to each side of the arm 17b that passes through cam ring 17 with each said

suction passage

21,31 covered; Therefore it becomes the resistance when sucking, thereby effectively suppresses the generation of said cavitation.

In addition, be two times of existing rotating speed (rotating speed of bent axle) owing to make the driving rotating speed of said oil pump 10, so can realize and existing identical discharge ability, thereby can make pump housing miniaturization significantly through half pump capacity of existing oil pump.

In addition, in this mode of execution,, therefore need not new driving source, suppressed the increase of cost owing to utilize the Equilibrator of both having deposited 1 that is attached to internal-combustion engine to obtain two times of rotary driving forces of existing oil pump.

Figure 17 shows second mode of execution of oil pump of the present invention; Its at the said excavationg pump of the back pressure duct 49 of the control valve 40 of said first mode of execution and each 22, be provided with normally closed solenoid valve SV between 32; It comes electrically to carry out said duct switching controls through this solenoid valve SV according to the running state of internal-combustion engine and move based on the field current from vehicle-mounted ECU 60.In addition, it is first state of the present invention that Figure 17 (a) shows the state that field current do not flow into solenoid valve SV, and it is second state of the present invention that Figure 17 (b) shows the state that field current flows into behind the solenoid valve SV.

Promptly; Basically; Detected internal-combustion engine rotational speed R such as sensor according to by regulation control said solenoid valve SV, are lower than at this internal-combustion engine rotational speed R under the state of said regulation rotating speed Rk (with reference to Figure 15), do not flow into solenoid valve SV from the field current of ECU60; The action oil that is imported into back pressure duct 49 is discharged from, and head pressure is imported in the back pressure chamber 45.Consequently, the active force of valve spring 44 is pressed to the stepped part 41c of valve body 41 with spool 43, and this control valve 40 is maintained at said first state (with reference to Figure 17 (a)).

On the other hand, reach said regulation rotating speed Rk when above at internal-combustion engine rotational speed R, flow into solenoid valve SV and make it drive valve from the field current of ECU60, the head pressure P more than hydraulic pressure Pk is switched in said duct is imported in the back pressure chamber 45.Consequently, spool 43 overcomes the active force of valve spring 44 through this importing pressure, moves towards one distolateral (plunger 42 sides) of valve body 41, and this control valve 40 switches to said second state (with reference to Figure 17 (b)).

As stated; In this mode of execution; Utilize solenoid valve SV to come electrically to carry out the duct switching controls of said control valve 40, therefore carry out said duct switching controls and compare, do not receive to plant the influence etc. of the hydraulic pressure variation that change produces because of the wearing and tearing of pump 10 each several parts or oil with the head pressure (action oil pressure) of pass through of said first mode of execution; Thereby can continue to carry out suitable duct switching controls, suppress the generation of cavitation reliably.

In addition; In this mode of execution, through back pressure duct 49 and each the said discharge duct 22 that said solenoid valve SV is arranged on said control valve 40, the importing pressure of controlling the back pressure chamber 45 that imports control valve 40 between 32, still; Except that this structure; Also can in the case, can function as described above effect equally through the spool 43 of the direct drive control valve 40 of said solenoid valve SV.

Figure 18 shows the 3rd mode of execution of oil pump of the present invention; Its solenoid valve SV with said second mode of execution changes to line style solenoid valve RSV; And; In line style solenoid valve RSV and each said discharge duct 22, be provided with throttle orifice 61 between 32, control the drainage discharge capacity through said line style solenoid valve RSV, and then control action is in the importing pressure of back pressure chamber 45.In addition, it is first state of the present invention that Figure 18 (a) shows the maximum state of line style solenoid valve RSV drainage discharge capacity, and it is that zero state is second state of the present invention that Figure 18 (a) shows line style solenoid valve RSV drainage discharge capacity.

That is, said line style solenoid valve RSV mainly has: valve body 51, and it forms roughly tubular, a distolateral opening, the other end side seal closes; Spool 52, it is housed in the interior week of said valve body 51 vertically sliding freely, on each end of this spool 52, is formed with first 52a of back-up ring portion and second 52b of back-up ring portion with the inner peripheral surface sliding contact of valve body 51; Valve spring 53, its second 52b of back-up ring portion that is housed in through said valve body 52 is formed in another distolateral back pressure chamber 55 of valve body 51, and spool 52 is applied towards the distolateral active force of valve body 51 1; Electromagnetic unit 54, it is installed on the opening portion of valve body 51 1 ends, after the energising, overcomes the active force of valve spring 53 through making bar 54b advance and retreat, makes spool 52 vertically towards the other end side shifting of valve body 51.

On the perisporium of said valve body 51, connect and be formed with: IN duct 51a, it is communicated with each said switching

duct

23,33; OUT duct 51b, it is connected with back pressure duct 49; Discharge duct 51c, it is connected with each said

suction passage

21,31 or outside, be used for after state the action oil discharge in the annulus 56.

Its intermediate portion reduced on axially of said spool 52, formation annulus 56 through two said back-up ring 52a of portion, 52b and between said spool 52 and valve body 51 interconnects each said duct 51a～51c via this annulus 56.And second 52b of back-up ring portion through this spool 52 makes and discharges duct 51c and open and close, thereby the action oil pressure that imports back pressure duct 49 from annulus 56 via OUT duct 51b is controlled.

As everyone knows, said electromagnetic unit 54 mainly has: coil unit 54a, and it is wound with coil on bobbin, be embedded in yoke portion outward; Armature, it is processed by magnetic material, can be arranged on interior all sides of said coil unit 54a with advancing and retreat vertically, and is not shown; Bar 54b, it combines with armature, moves with the armature advance and retreat according to the "on" position of coil.

According to this structure, be lower than at internal-combustion engine rotational speed R under the state of said regulation rotating speed Rk, flow into said line style solenoid valve RSV from the maximum field current of ECU60, bar 54b reaches maximum advance and retreat state, and the discharge capacity of discharging duct 51c reaches maximum.Consequently; Spool 43 is not overcome the active force of valve spring 44 and the required enough action oil pressures that move import the back pressure chamber of said control valve 40; Become through the active force of valve spring 44 state of spool 43 being pressed to the stepped part 41c of valve body 41, this control valve 40 is maintained at said first state (with reference to Figure 18 (a)).

On the other hand, rise and reach the regulation rotating speed Rf that is equivalent to the said first action oil pressure Pf when above at internal-combustion engine rotational speed R, with the rising of internal-combustion engine rotational speed R; Field current from ECU60 reduces gradually; The opening area of discharging duct 51c reduces gradually, thereby the interior pressure of said back pressure chamber 45 is increased gradually, when the interior pressure of this back pressure chamber 45 reaches said duct and switches hydraulic pressure Pk; Spool 43 beginnings are moved towards one distolateral (plunger 42 sides) of valve body 41, begin to carry out said duct switching controls.Soon, when the field current from ECU60 reaches minimum and makes when discharging duct 51c complete closed, this control valve 40 switches to said second state (with reference to Figure 18 (b)) fully from said first state.

As stated; In this mode of execution; Owing to utilize line style solenoid valve RSV that the back pressure chamber 45 of said control valve 40 is imported pressure control, therefore can play and the identical action effect of said second mode of execution, this line style solenoid valve RSV is different with the said solenoid valve SV that only can carry out ON-OFF control; Switch owing to can carry out said duct gradually, the discharge capacity that therefore can suppress when switching because of this duct changes the head pressure change that causes.

In addition; In this mode of execution, through back pressure duct 49 and each the said discharge duct 22 that said line style solenoid valve RSV is arranged on said control valve 40, the importing pressure of controlling the back pressure chamber 45 that imports control valve 40 between 32, still; Except that this structure; Also can in the case, can function as described above effect equally through the spool 43 of the direct drive control valve 40 of said line style solenoid valve RSV.

The present invention is not limited to the structure of each said mode of execution; For example, can freely change said internal-combustion engine according to the specification of the internal-combustion engine of the vehicle that said oil pump 10 is installed or valve arrangement for controlling timing etc. requires hydraulic pressure P1～P3, said first, second to move oil pressure Pf, Ps and said duct switching hydraulic pressure Pk.

And the driving source of said oil pump 10 also is not limited to use Equilibrator 1, so long as can get final product with the rotating speed device driven that is higher than internal-combustion engine rotational speed, can use other devices.And these other devices are not limited to both be stored in the device on the car body, also append the device of setting.

In addition; In each said mode of execution; Via said control valve 40 the said

suction passage

21,31 of each said switching

duct

23,33 and each is connected; Thereby enlarge to suck the zone, but also can not suck the zone through incompatible unified expansion of each subset of cell channels that will cut apart, and through making the said zone that sucks enlarge the pump intake when guaranteeing high speed rotating continuously.

Promptly; Each said

discharge duct

22,32 and each said switching

duct

23,33 are set to a succession of discharge duct respectively; And (for example will make in the separate a pair of partition wall in the said suction passage of this a succession of discharge duct and each 21,31 partition wall relative with the bigger pump chamber PR of internal capacity; The partition wall of downside among Fig. 7); Form partition member independent mutually and that can move with respect to these two

parts

11,12, suck the zone and change continuously, can make said suctions zone expansion with the distribution of discharging area through this partition member along the circumferential direction being moved respectively and making with two said

parts

11,12.

As stated; Because can make the distribution that sucks zone and discharging area changes continuously; Therefore the intake in the time of not only can guaranteeing the internal-combustion engine high speed rotating; And can suppress because of the expansion of suction/discharging area or dwindle the unexpected variation of the pump delivery that causes, thereby discharge capacity stably that can control pump 10.And, in said structure, because only through partition member being moved just can easily control the expansion of suctions/discharging area or dwindle, so can improve the response performance of pump 10.

In addition; In said second, third mode of execution; Control Parameter as said solenoid valve SV and line style solenoid valve RSV; With basic internal-combustion engine rotational speed is that example is illustrated; But except this internal-combustion engine rotational speed, also can be shared, control through the pressure that is arranged in detected each the said

switching ducts

23,33 such as pressure transducer or pressure switch in each said switching

duct

23,33 according to the temperature of the temperature of the cooling water that for example in internal-combustion engine, flows or action oil or the two.

That is because the influence of oil viscosity is also moved in the generation of cavitation, therefore, through with the temperature of the temperature of said cooling water or action oil, preferably the combination of the two is set at Control Parameter, can further suitably suppress the generation of cavitation.And; As stated; If the interior pressure in each said switching

duct

23,33 reaches negative pressure, cavitation then takes place, therefore carry out the generation that said duct switching controls can suitably suppress cavitation too based on the interior pressure in each said switching

duct

23,33.

Below, the technological thought of the invention beyond the above-mentioned mode of execution is described.

(a) according to the oil pump of first invention, it is characterized in that,

The discharge capacity of said pump structure body can change according to said head pressure,

Head pressure when the head pressure that makes said spool switch to said second state from said first state is set at and is lower than discharge capacity that pump whenever rotates a circle and reaches minimum.

Because the head pressure that appears at pump of cavitation arrives before the head pressure of the intrinsic discharge capacity of pump when minimum, therefore the head pressure when making switch pressure be lower than this intrinsic discharge capacity to reach minimum can effectively suppress the generation of cavitation.

(b) according to (a) described oil pump, it is characterized in that,

Said valve arrangement body has: rotor, and it is driven by the internal-combustion engine rotation, and outer circumferential side has a plurality of radial grooves; Cam ring, it is configured in the outer circumferential side of said rotor, and the center of this cam ring inner peripheral surface can be eccentric with respect to the rotating center of said rotor; Impeller, it is housed in respectively free to advance or retreatly in a plurality of said grooves, the inner peripheral surface sliding contact of each front end and said cam ring;

Owing to dispose said duct body on two sides on said cam ring is axial, therefore mark off each said action grease chamber through said duct body, said rotor, said cam ring and each said impeller.

(c) according to (b) described oil pump, it is characterized in that,

When said head pressure reaches first pressure; The center of said cam ring inner peripheral surface reduces with respect to the offset of the rotating center of said rotor; When said head pressure reaches second pressure that is higher than said first pressure; The center of said cam ring inner peripheral surface further reduces with respect to the offset of the rotating center of said rotor

The head pressure that said spool switches to said second state from said first state is higher than said first pressure and is lower than said second pressure.

Through said structure, can guarantee the function of capacity-variable type pump, bring into play action effect of the present invention.That is, owing to second state that switches to reduces discharge capacity from first state, the cam duration of oscillation lags behind, and consequently, causes pump to do idle work.Therefore, under the state that cavitation does not take place, carry out aforesaid switching, not only can not play the effect of the generation that reduces cavitation, and wasted the function of the capacity-variable type pump that can reduce the pump driving torque on the contrary.

(d) according to (c) described oil pump, it is characterized in that,

On said cam ring, effect has the active force of two kinds of different springs of spring load respectively,

When said head pressure reaches said first pressure; Said cam ring overcomes the active force of the less spring of two said spring medi-spring loads and the direction that reduces with respect to the offset of the rotating center of said rotor towards the center that makes said cam ring inner peripheral surface moves

When said head pressure reached said second pressure, said cam ring overcame the active force of the bigger spring of two said spring medi-spring loads and the direction that further reduces with respect to the offset of the rotating center of said rotor towards the center that makes said cam ring inner peripheral surface moves.

(e) according to (c) described oil pump, it is characterized in that,

The center of said cam ring inner peripheral surface reduces with respect to the offset of the rotating center of said rotor, then covers the part of said suction passage through the side of said cam ring.

Through said structure, can reduce the intake of suction passage, suppress the generation of cavitation.

(f) according to the oil pump of first invention, it is characterized in that,

The driving rotating speed of said pump structure body is higher than the speed of crankshaft of internal-combustion engine.

Because the rotating speed of pump is higher than existing rotating speed, therefore under the identical situation of pump capacity, can make the pump miniaturization.

(g) according to (f) described oil pump, it is characterized in that,

The driving rotating speed of said pump structure body is two times of speed of crankshaft.

Because the rotating speed of pump is two times of existing rotating speed, therefore under the identical situation of pump capacity, capacity is merely existing half the getting final product, and can make pump miniaturization significantly.

(h) according to (g) described oil pump, it is characterized in that,

Said pump structure body is by the Equilibrator driving that is used to reduce the internal-combustion engine secondary vibration.

Owing to utilize the attached both cryopreservation devices of internal-combustion engine, therefore need not new driving source and just can make rotary driving force reach existing two times, increase thereby suppress cost.

(i) according to (h) described oil pump, it is characterized in that,

Said pump structure body is installed in the said Equilibrator.

Owing to make pump and Equilibrator integrated, so compare, can pump be installed in the vehicle etc. compactly with pump independently is set.

(j) according to the oil pump of second invention, it is characterized in that,

Said control mechanism is carried out electrical control.

Through said structure, and utilize head pressure to carry out said switching controls to compare, do not receive to plant the influence of the hydraulic pressure variation that change produces, thereby can continue suitably to carry out said switching controls because of the wearing and tearing of pump or oil.

(k) according to (j) described oil pump, it is characterized in that,

Said control mechanism is controlled according to the rotating speed of detected internal-combustion engine.

Because therefore the rotating speed that exists with ... pump of cavitation is controlled through the rotating speed of the basis internal-combustion engine relevant with the rotating speed of pump, can suitably suppress the generation of cavitation.

(l) according to (k) described oil pump, it is characterized in that,

Said control mechanism is controlled with reference to the temperature of detected internal-combustion engine.

Because the influence of oil viscosity is also moved in the generation of cavitation, therefore, through this structure, can further suitably suppress the generation of cavitation.

(m) according to (j) described oil pump, it is characterized in that,

Said control mechanism is controlled according to the pressure in detected said switching duct.

If the pressure in volume dwindles the switching duct of upstream side opening in zone becomes negative pressure, cavitation then takes place, therefore carry out said switching controls through pressure based on said switching duct, can suitably suppress the generation of cavitation.

(n) according to the oil pump of the 3rd invention, it is characterized in that,

When rotating speed is to make to be positioned at the said action of upstream side grease chamber that volume dwindles the zone when becoming the rotating speed of negative pressure, the zone of suction action oil enlarges, and on the contrary, the zone of discharging operation oil dwindles.

Through said structure, can during sucking, guarantee enough intakes, suppress the generation of cavitation.

(o) according to (n) described oil pump, it is characterized in that,

The zone of suction action oil enlarges according to said rotating speed continuously.

Through said structure, can suppress because of the expansion of suction/discharging area or dwindle the unexpected variation of the pump delivery that causes, thereby can control pump reposefully.

(p) according to (o) described oil pump, it is characterized in that,

Said duct body is provided with the partition member with said suction passage and the separation of said discharge duct, and this partition member moves according to said rotating speed, thereby the suction zone of said action oil is enlarged.

Through said structure, with will suck/existing pump that discharging area is separated regularly compares, and can easily realize sucking/expansion of discharging area or dwindle, and improves the response performance of pump.

Claims

1. oil pump is characterized in that having:

The pump structure body, it is driven by the internal-combustion engine rotation, so that the volume of a plurality of actions grease chamber increases and decreases continuously;

The duct body, it comprises: switching duct, the volume in said action grease chamber of upstream side opening that the suction passage of the volume enlarged area opening in said action grease chamber, the volume in said action grease chamber dwindle the zone dwindles the discharge duct of the downstream side opening in zone;

The valve accepting hole; The inner circumferential surface opening be formed with first duct that is communicated with said suction passage, with second duct of said switching hole link, with the 3rd duct of said discharge hole link, and be provided with the hydraulic pressure that is used to import in the said discharge duct in an end of said valve accepting hole be that the head pressure of head pressure imports the duct;

Spool, it is housed in the said valve accepting hole sliding freely, can switch on following two states,

First state limits being communicated with between said first duct and said second duct, makes said second duct and said the 3rd hole link,

Second state makes said first duct and said second hole link, limits being communicated with of said second duct and said the 3rd duct;

Force application part, it is arranged on the other end side of said valve accepting hole, and said spool is applied towards one of said valve accepting hole distolateral active force;

One of the said spool of the said head pressure effect distolateral compression area and the active force of said force application part are set, switched to said second state from said first state when becoming negative pressure with the pressure in the said action grease chamber that is formed with said switching duct at opening.

2. oil pump according to claim 1 is characterized in that,

The head pressure that makes said spool switch to said second state from said first state is set at and is lower than discharge capacity that pump whenever rotates a circle and becomes the head pressure when minimum.

3. oil pump according to claim 2 is characterized in that,

Said valve arrangement body has: rotor, and it is driven by the internal-combustion engine rotation, and its outer circumferential side has a plurality of radial grooves; Cam ring, it is configured in the outer circumferential side of said rotor, and the center of this cam ring inner peripheral surface can be eccentric with respect to the rotating center of said rotor; Impeller, it is housed in respectively free to advance or retreatly in a plurality of said grooves, each front end of this impeller and the inner peripheral surface sliding contact of said cam ring;

Said duct body is configured in two axial sides of said cam ring, to mark off each said action grease chamber through said duct body, said rotor, said cam ring and each said impeller.

4. oil pump according to claim 3 is characterized in that,

The head pressure that makes said spool switch to said second state from said first state is set at and is higher than said first pressure and is lower than said second pressure.

5. oil pump according to claim 4 is characterized in that,

When said head pressure reaches said first pressure; Said cam ring overcomes the active force of the less spring of two said spring medi-spring loads and the direction that reduces with respect to the offset of the rotating center of said rotor towards the center of said cam ring inner peripheral surface moves

When said head pressure reached said second pressure, said cam ring overcame the active force of the bigger spring of two said spring medi-spring loads and the direction that further reduces with respect to the offset of the rotating center of said rotor towards the center of said cam ring inner peripheral surface moves.

6. oil pump according to claim 4 is characterized in that,

The center of said cam ring inner peripheral surface reduces with respect to the offset of the rotating center of said rotor, and then the part of said suction passage is covered by the side of said cam ring.

7. oil pump according to claim 1 is characterized in that,

8. oil pump according to claim 7 is characterized in that,

Said pump structure body is installed in the said Equilibrator.

9. oil pump is characterized in that having:

Control mechanism; When the pressure in opening is formed with the said action grease chamber in said switching duct becomes the low speed rotation of positive pressure; Said switching duct and said discharge duct together will be moved oil and be expelled to the outside; When the pressure in opening is formed with the said action grease chamber in said switching duct becomes the high speed rotating of negative pressure, action oil is supplied to said switching duct from the low voltage section that is communicated with said suction passage.

10. oil pump is characterized in that having:

The duct body, it comprises: the volume in the suction passage of volume enlarged area opening, in said action grease chamber dwindles the discharge duct of regional opening at least in said action grease chamber;

Control mechanism, when the rotating speed of pump is to make when being positioned at the pressure of said action grease chamber that volume dwindles the upstream side in zone and becoming the rotating speed of negative pressure, action oil flows into this from low voltage section becomes the said action grease chamber of negative pressure.