CN102444578A - Variable displacement vane pump - Google Patents
Variable displacement vane pump Download PDFInfo
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- CN102444578A CN102444578A CN2011103077980A CN201110307798A CN102444578A CN 102444578 A CN102444578 A CN 102444578A CN 2011103077980 A CN2011103077980 A CN 2011103077980A CN 201110307798 A CN201110307798 A CN 201110307798A CN 102444578 A CN102444578 A CN 102444578A
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Abstract
To restrain an abnormal sound when opening a relief valve, without making relief pressure of the relief valve unstable in a variable displacement vane pump. A seat surface 45 for seating a ball 35 when a valve is closed among the relief valve 33, is formed so that the center C of the ball 35 is offset to one side in the radial direction to the axis A1 of a valve hole 34. Thus, energizing force F of a relief valve spring 37 acts so as to strongly press the ball 35 to a wide part 45b on one side in the radial direction among the seat surface 45, and vibration of the ball 35 is restrained when the ball 35 abuts on the wide part 45b of the seat surface 45 even when opening the valve.
Description
Technical field
The present invention relates to for example be applicable to the variable capacity type vane pump of hydraulic pressure of motor vehicle power steering gear.
Background technique
At present, in the variable capacity type vane pump, be provided with the protection hydraulic equipment as everyone knows and avoid the safety valve that excessive pressure rises and damages.The ball valve that this safety valve utilizes helical spring to make to be kept by the valve body holding member leans on to the valve base part side presses, but above-mentioned valve body vibrates with the valve body holding member when this Investigation on safety valve, and the problem of generation noise is arranged.
So; In the technology of patent documentation 1 record; Make as the ball valve seat of above-mentioned valve body holding member, between the outer circumferential face of above-mentioned ball valve seat and valve opening, produce frictional force with accommodating the valve opening outer circumferential face butt of this ball valve seat, the inhibition noise through making the outer peripheral portion of accommodating this ball valve seat.
Patent documentation 1: TOHKEMY 2003-74725 communique
But in the technology of patent documentation 1 record; Because size error, assembly error and the hydraulic pressure of above-mentioned ball valve seat and valve opening have deviation to the frictional force that the situation of above-mentioned valve body effect etc. causes between the outer circumferential face of above-mentioned ball valve seat and valve opening, producing, and have the safety pressure problem of unstable of Investigation on safety valve.
Summary of the invention
The present invention makes in view of this problem, and purpose is to provide a kind of variable capacity type vane pump, and it is stable that safety is pressed, and produces noise when being suppressed at Investigation on safety valve.
Variable capacity type vane pump of the present invention possesses: rotor, and it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor; Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor; Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor; Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form; Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path; This variable capacity type vane pump is characterised in that said safety valve possesses: valve opening, and it is set in the said pump main body; The valve body of ball valve shape, it is configured in this valve opening; Valve base part, it is fixed on an axial side across said valve body in said valve opening, and is formed with the through hole that is communicated with said drain passageway, when closing valve and the ring valve seat surface of said valve body chimeric (seat) be formed on the valve body side opening portion of said through hole; Helical spring, it is set at opposite side across said valve body in said valve opening; The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with in said helical spring side and limit it with respect to the spring engagement portion of this helical spring in radially relative displacement, the recuperability of utilizing said helical spring compressive strain to be produced, said valve body to said valve base part side by pressing; Said valve seat surface forms: when closing valve, make in the said relatively helical spring in center of said valve body axle center with the end circle portion (seat volume portion) of valve seat surface opposition side in radial offset.
Specifically; The characteristic feature of an invention of first, second content of the present invention is; In said valve base part, when closing valve and the chimeric valve seat surface of said valve body be formed: the axle center that makes the end circle portion of valve seat surface opposition side in the said relatively helical spring in center of said valve body when closing valve is in radial offset.
The characteristic feature of an invention of the present invention's the 3rd content is; The axle center of this valve body holding part keeps said valve body in the position of radial offset to keep the valve body holding part of said valve body to be formed in relatively in the said valve body holding member; Thus, when closing valve in the said relatively helical spring of said valve body holding part the end circle portion of valve seat surface opposition side in radial offset.
The characteristic feature of an invention of the present invention's the 4th content is; Chimeric surface with valve body holding member opposition side in the said helical spring forms with respect to the imaginary plane with this helical spring axle center quadrature; Thus, the axle center of the said relatively valve opening in axle center of said valve body holding member is tilted.
The characteristic feature of an invention of the present invention's the 5th content is, forms said valve seat surface at said valve body and this valve seat surface chimericly and when closing valve, makes the axle center biasing of the valve body side end that valve body faces described in the said relatively valve base part through hole in center of said valve body.
According to the present invention, because the part of said valve body also can suppress the vibration of this valve body with said valve seat surface butt when driving valve, institute and prevents when driving valve, to produce noise so that safety is pressed stablely.
Description of drawings
Fig. 1 is an axial sectional view of representing the variable capacity type vane pump as the first embodiment of the present invention;
Fig. 2 is the A-A sectional view of Fig. 1;
Fig. 3 is the enlarged view of safety valve shown in Figure 2;
Fig. 4 is the enlarged view of expression valve seat surface details shown in Figure 3;
Fig. 5 is the figure of expression ball valve and valve seat surface chimeric status shown in Figure 4;
Fig. 6 is the explanatory drawing of ball valve action when representing Investigation on safety valve shown in Figure 3;
Fig. 7 is the figure of expression first embodiment's variation;
Fig. 8 is a sectional view of representing safety valve as the second embodiment of the present invention;
Fig. 9 is the major component enlarged view of safety valve shown in Figure 8;
Figure 10 is the figure of ball valve action when representing Investigation on safety valve shown in Figure 9;
Figure 11 is a sectional view of representing safety valve as the third embodiment of the present invention;
Figure 12 is an amplification view of representing retainer shown in Figure 8 separately;
Figure 13 is the figure that representes retainer as the 3rd embodiment's variation separately;
Figure 14 is a sectional view of representing safety valve as the fourth embodiment of the present invention;
Figure 15 is the figure that representes the safety valve spring of safety valve shown in Figure 14 separately;
Figure 16 is the figure of expression Investigation on safety valve state shown in Figure 14.
Description of reference numerals
1 variable capacity type vane pump, 4 pump main body 4a containing spaces, 6 live axles
7 rotors, the 8 cam ring 14a first fluid 14b of pressure chamber, second fluid pressure chamber
16 blades, 17 pump chambers 19 suck path 26 control valves (pressure control mechanism)
33 safety valves, 34 valve openings, 35 ball valves, 36 valve base parts
37 safety valve springs (helical spring) 37a, the first end circle portion
The 37b second end circle portion, 38 retainers (valve body holding member)
39 axial regions (spring engagement portion), 40 ball valve holding parts (valve body holding part)
44 through hole 45 valve seat surfaces, 46 ball valves (valve body) 47 ball valves (valve body)
48 safety valves, 49 valve base parts, 50 valve seat surfaces
51 retainers (valve body holding member), 52 ball valve holding parts (valve body holding part)
54 axial regions (spring engagement portion)
The axle center of A1 valve opening (axle center of the first end circle portion)
The center of C ball valve (center of valve body)
Embodiment
Fig. 1 and Fig. 2 are the figure that representes to be applicable to the variable capacity type vane pump of vehicle hydraulic power steering gear as suitable embodiment of the present invention, and Fig. 1 is its axial sectional view, and Fig. 2 is the A-A sectional view of Fig. 1.
Like Fig. 1, shown in Figure 2; In the variable capacity type vane pump 1, pump element 5 is housed in the containing space 4a in the pump main body 4, and 3 butt joints form this pump main body 4 with the back main body by preceding main body 2; Live axle 6 driven pump elements 5 rotations of containing space 4a are passed in utilization, realize the effect of pump.
Relative pump main body 4 is positioned in sense of rotation respectively bush ring 9 through locating stud 11 with pressure plate 10.Among Fig. 2; The 14a of the first fluid pressure chamber side of stating promptly in the clockwise direction side of locating stud 11 is provided with plate member 12; This plate member 12 has the function as the swing fulcrum of cam ring 8, and goes back the function of the sealed member of sealing between handlebar cam ring 8 and the bush ring 9.
In the inner peripheral surface of bush ring 9; Radially and plate member 12 relative positions be provided with this bush ring 9 and cam ring 8 between the sealing sealed member 13, utilize sealing parts 13 and plate member 12 between cam ring 8 and bush ring 9, to isolate a pair of 14a of fluid pressure chamber, 14b.Promptly be formed with the 14a of first fluid pressure chamber and second 14b of fluid pressure chamber respectively, utilize pressure official post cam ring 8 swings between these two 14a of fluid pressure chamber, the 14b, make the offset increase and decrease of cam ring 8 relative rotors 7 in the radially both sides of cam ring 8.In addition, cam ring 8 is reset spring 15 to leaning on pressure with the maximum direction of the offset of rotor 7 always.
Peripheral part at rotor 7 circumferentially is being provided with a plurality of elongated slot 7a that radially cut out equally spacedly.The blade 16 of substantially planar is accommodated by each elongated slot 7a respectively rotor 7 with radially freely haunting, forms a plurality of pump chambers 17 to the annulus between cam ring 8 and the rotor 7 circumferentially separating by these each blades 16.In Fig. 2, counterclockwise drive rotor 7 rotations through live axle 6, each pump chamber 17 increases and decreases its volume and turns round mobilely separately thus on one side, carries out pump and moves.Each blade 16 utilizes the pressure of the working oil among the back pressure chamber 7b that imports to the interior all sides that are formed on each elongated slot 7a and is pressed against on the inner peripheral surface of cam ring 8.
Facing the inner side surface 3a of containing space 4a in the main body 3 in the back, and in the part that is being equivalent to the suction zone that the volume of each pump chamber 17 enlarges gradually along with the rotation of rotor 7, cutting out and see it is first suction port 18 of crescent shape roughly along circumferential front.This first suction port 18 is communicated with the suction path 19a that the main body 3 in the back is provided with.Thus, importing to the working oil that sucks in the path 19a via the suction pipe 20 that is connected with not shown fuel tank utilizes the pump suction effect in above-mentioned suction zone and is inhaled into each pump chamber 17.
In pressure plate 10 on the face relative and cutting out second suction port 21 that is formed with these first suction port, 18 roughly the same shapes with first suction port, 18 relative positions with rotor 7.This second suction port 21 is communicated with the circulation flow path 22 that in preceding main body 2, forms.This circulation flow path 22 is communicated with recess in the preceding main body 2; This recess contains the sealed member of sealing between preceding main body 2 and the live axle 6; The residual oil of above-mentioned sealed member is supplied with to each pump chamber 17 owing to the pump suction effect in above-mentioned suction zone; Thus, can prevent that said residual oil from spilling to the outside.
In pressure plate 10 on the face relative and, cut out to be formed with to see it is first exhaust port 23 of crescent shape roughly along circumferential front in the part that is equivalent to the diminishing discharging area of volume of each pump chamber 17 along with the rotation of rotor 7 with rotor 7.This first exhaust port 23 is via in preceding main body 2, being communicated with drain passageway 19b from pressure chamber 24 that the inner bottom surface 2a depression relative with pressure plate 10 is provided with.Thus, utilize the pump discharge effect of above-mentioned discharging area and make the working oil of discharging from each pump chamber 17 through pressure chamber 24 with drain passageway 19b and discharge to pump main body 4 outside is seen off to the hydraulic power oil hydraulic cylinder of not shown power steering gear.Pressure plate 10 is pushed to rotor 7 sides owing to the pressure in the pressure chamber 24.
The position relative with first exhaust port 23 in the inner side surface 3a of back main body 3 cuts out second exhaust port 25 that is formed with these first exhaust port, 23 roughly the same shapes.Through being arranged in axial symmetry to first, second suction port 18,21 and first, second exhaust port 23,25 across each pump chamber 17 respectively like this, can keep said each pump chamber 17 in the axially pressure balance of both sides.
The inside of upper end side in preceding main body 2 is provided with control pump in the direction (left and right directions of Fig. 2) with live axle 6 quadratures and discharges the control valve 26 as pressure control mechanism of pressing.On the main body 2, comprising before this control valve 26 left side from Fig. 2 is arranged on to the right: the opening portion in left side among Fig. 2 with the valve opening 28 of embolism 27 sealings, in being housed in this valve opening 28 with axially being free to slide the sleeve that the round-ended cylinder shape is roughly arranged 29, with this sleeve 29 to the control valve spring 30 of embolism 27 sides by pressure.
Be isolated into respectively by sleeve 29 in the valve opening 28: hyperbaric chamber 28a; It is formed between embolism 27 and the sleeve 29, is that the hydraulic pressure of pressure chamber 24 imports with the upstream side hydraulic pressure of the not shown metering orifice that is formed on drain passageway 19b (ャ one タ リ Application グ オ リ Off ィ ス); The middle chamber 28b that presses, it is accommodated control valve spring 30 and imports the downstream side hydraulic pressure of said metering orifice; Low pressure chamber 28c, it is formed on the outer circumferential side of sleeve 29, imports pump suction pressure via low-pressure passage 31 from sucking path 19a.Sleeve 29 is moving axially based on the pressure difference of middle pressure chamber 28b and hyperbaric chamber 28a.
Be exactly specifically; When the smaller and sleeve 29 of the pressure difference of middle pressure chamber 28b and hyperbaric chamber 28a is positioned at embolism 27 sides; The access 32 that the 14a of first fluid pressure chamber is communicated with valve opening 28 is to low pressure chamber 28c opening, and the lower hydraulic pressure of low pressure chamber 28c is imported into the 14a of first fluid pressure chamber.On the other hand; In the middle of press the pressure difference of chamber 28b and hyperbaric chamber 28a to increase and sleeve 29 resist control valve springs 30 depended on pressure and when moving axially; Low pressure chamber 28c was cut off with being communicated with gradually of the 14a of first fluid pressure chamber, was communicated with the 14a of first fluid pressure chamber via access 32 as hyperbaric chamber 28a.Thus, the higher hydraulic pressure of ratio of hyperbaric chamber 28a is imported into the 14a of first fluid pressure chamber.Promptly can import the 14a of first fluid pressure chamber to the hydraulic pressure of low pressure chamber 28c or hyperbaric chamber 28a selectively.
And; Import pump to second 14b of fluid pressure chamber always and suck pressure; When importing the hydraulic pressure of low pressure chamber 28c to the 14a of first fluid pressure chamber, because the depended on pressure of Returnning spring 15 and cam ring 8 is arranged in and the offset of rotor 7 is maximum position (leftward position of Fig. 2), pump delivery is maximum.On the other hand; When the 14a of first fluid pressure chamber imports the hydraulic pressure of hyperbaric chamber 28a; Utilize the 14a of this first fluid pressure chamber pressure and cam ring 8 opposing Returnning springs 15 depended on pressure and swing; The volume of second 14b of fluid pressure chamber is diminished, and this cam ring 8 reduces with the offset of rotor 7, and pump delivery reduces.
Be formed with safety valve 33 in the inside of sleeve 29.This safety valve 33 becomes authorized pressure when above at the pressure of middle pressure chamber 28b; Be that the pressure of power steering gear side (load side) becomes authorized pressure when above; Carry out releasing action, working oil is also flowed to sucking path 19a via low pressure chamber 28c and low-pressure passage 31.In other words, can utilize safety valve 33 to open and close the oily path between drain passageway 19b and the suction path 19a.
Fig. 3 is the enlarged view of expression safety valve 33 details.
As shown in Figure 3, safety valve 33 possesses: valve opening 34, and it is formed on interior all sides of sleeve 29 and is roughly cylindric; Release aperture 29a, it is set in the sleeve 29 and is communicated with this valve opening 34 with low pressure chamber 28c; As the ball valve 35 of ball valve, it is configured in the valve opening 34; Valve base part 36, it is fixed on an axial side across ball valve 35 by setting-in in valve opening 34; Safety valve spring 37, it is a helical spring, in valve opening 34, is arranged on opposite side across ball valve 35 by the state with compressive strain; As the retainer 38 of valve body holding member, it is set between ball valve 35 and the safety valve spring 37, utilize safety valve spring 37 compressive strains recuperability and ball valve 35 to valve base part 36 sides by pressing.
About ball valve holding part 40; In this ball valve holding part 40; Be provided with as valve body with the sunken end face of axial region 39 opposition sides and keep the ball valve of recess to keep recess 41 to keep ball valve 35; On the other hand, step-like 42 between this ball valve holding part 40 and the axial region 39 is chimeric with the second end circle 37b of portion of safety valve spring 37.It is that the center is formed rotational symmetric general flat mortar shape with the axle center A2 of retainer 38 that ball valve keeps recess 41; Through making ball valve 35 and this ball valve keep chimeric this ball valve 35 and the retainer 38 of limiting of recess 41, the center C of this ball valve 35 is positioned on the axle center A2 of retainer 38 in radially relative displacement.
On the other hand, be formed with the spring embedding part 43 of circular depressed in the bottom of valve opening 34.It is consistent with the axle center A1 of valve opening 34 that this spring embedding part 43 is formed its axle center; The first end circle 37a of portion and this spring embedding part 43 of valve base part 36 opposition sides through making safety valve spring 37 are chimeric, make the axle center of this first end circle 37a of portion consistent with the axle center A1 of valve opening 34.
Form valve seat surface 45: when safety valve 33 closes valve, the axle center A1 of the valve opening 34 that the center C that makes ball valve 35 when promptly ball valve 35 and valve seat surface 45 are chimeric is common with respect to the first end circle 37a of portion and through hole 44 and the Offset G3 (with reference to Fig. 5) that stipulates to biasing radially.The axle center A1 of the ball valve holding part 40 relative valve openings 34 of retainer 38 and radially be biased the axle center A1 tilt angle theta 1 of the relative valve opening 34 of axle center A2 of this retainer 38 consequently.
Fig. 4, Fig. 5 are the enlarged views of expression valve seat surface 45 details, and wherein Fig. 4 is an amplification view of representing valve base part 36 major components separately, Fig. 5 amplification view of closing valve state chimeric with valve seat surface 45 that be expression ball valve 35.
Details is then like Fig. 4, shown in Figure 5; Valve seat surface 45 is to have the part of the sphere of Offset G3 to form by the axle center A1 biasing with ball valve 35 footpath together and the relative valve opening 34 in center; Demonstrating surface with ball valve 35, to have the curved cross section of same curvature circular-arc, and gradually change at the width dimensions that circumferentially is formed of this valve seat surface 45.
Be exactly specifically; Radially mutual relative position is formed with respectively in valve seat surface 45: narrow width part 45a that the width dimensions of valve seat surface 45 is minimum and the maximum wide width part 45b of the width dimensions of valve seat surface 45; Valve seat surface 45 radially tilts towards the private side of wide width part 45b side direction through hole 44 (direction of leaving from the first end circle 37a of portion) this valve seat surface 45, and circumferentially from wide width part 45b to narrow width part 45a width change width dimensions gradually with narrowing down.In other words, valve seat surface 45 be formed in valve opening 34 axially in relative distance circumferentially the changing of the relative first end circle 37a of portion at this valve seat surface 45.
Say more in detail and be exactly; The opening side edge 45c of portion of valve seat surface 45 tilts to the direction near the first end circle 37a of portion in the axial of valve opening 34 towards narrow width part 45a side from wide width part 45b, and the private side edge 45d of portion of valve seat surface 45 tilts greatly in the axial of valve opening 34 to the direction ratio opening side edge 45c of portion near the first end circle 37a of portion towards narrow width part 45a side from wide width part 45b.In other words; The private side edge 45d of portion of wide width part 45b is than the private side edge 45d of portion of the narrow width part 45a Offset G1 to the first end circle 37a of portion opposition side biasing regulation; And the opening side edge 45c of portion of wide width part 45b is than the opening side edge 45c of portion of the narrow width part 45a Offset G2 to the first end circle 37a of portion opposition side biasing regulation, and the Offset G2 of the Offset G1 ratio open lateral edge portion 45c of the private side edge 45d of portion is big.The wide width part side opening angle θ that axle center A1 became 2 of imaginary line and valve opening 34 of the 45c of two edges portion, 45d that links wide width part 45b is bigger than the 45c of two edges portion that links narrow width part 45a, narrow width part side opening angle θ 3 that the imaginary line of 45d is become with the axle center A1 of valve opening 34.
In the variable capacity type vane pump 1 of above structure; When safety valve shown in Figure 3 33 closes valve; The axle center A1 of the relative valve opening 34 of the center C of ball valve 35 puts to wide width part 45b lateral deviation, and as above-mentioned, the axle center A1 of the relative valve opening 34 of axle center A2 of retainer 38 is towards wide width part 45b tilt.Thus, the depended on pressure F of safety valve spring 37 is to the axle center of retainer 38 A2 directive effect, and ball valve 35 is forced the part by the wide width part 45b side that is pressed in valve seat surface 45.In other words, retainer 38 had both utilized the axial composition F1 of depended on pressure F to resist with through hole 44 interior hydraulic pressure, utilized the radially composition F2 of depended on pressure F to come the part of ball valve 35 by the wide width part 45b side that is pressed in valve seat surface 45 again.
In the middle of press the pressure of chamber 28b to rise and the release that surpasses regulation when pressing; As shown in Figure 6; Ball valve 35 keeps the butt with the wide width part 45b side sections of valve seat surface 45 on one side, move and from the part of the narrow width part 45a side of valve seat surface 45 leave on one side, working oil is such flowing shown in Fig. 6 arrow.Promptly when valve left by safety valve 33, while ball valve 35 is held the part butt of wide width part 45b side in device 38 supports and the valve seat surface 45 and by stable support, the vibration of this ball valve 35 is suppressed.And as shown in Figure 3, in retainer 38 between the outer circumferential face of the outer circumferential face of ball valve holding part 40 and valve opening 34, both interfere and are provided with sufficient gap when preventing that safety valve 33 from leaving valve.
Therefore, according to present embodiment, the release of safety valve 33 is pressed and can be stablized, and the vibration of ball valve 35 prevents when valve left by safety valve 33, to have noise to produce in the time of can suppressing safety valve 33 and drive valve.
In the present embodiment, the valve seat surface 45 of valve base part 36 form be and ball valve 35 with the part of the spheres in footpath, but the sphere that constitutes valve seat surface 45 need be a same diameter with ball valve not necessarily also.
Fig. 7 be expression make as the variation of present embodiment with the sphere that constitutes valve seat surface 45 be the figure that the ball valve of different-diameter is entrenched in the state of valve seat surface 45; The big ball valve 46 usefulness solid lines of spherical diameter than constituting valve seat surface 45 are represented; On the other hand, dotting than the little ball valve 47 of spherical diameter that constitutes valve seat surface 45.
Variation specifically then as shown in Figure 7 is such; Use with the sphere that constitutes valve seat surface 45 be under the situation of ball valve 46,47 of different-diameter; When safety valve closes valve because the center of ball valve 46,47 also is the axle center A1 of relative valve opening 34 and putting to wide width part 45b lateral deviation, so can access roughly same effect with above-mentioned first embodiment.
In above-mentioned first embodiment; Form the axle center A1 of the through hole 44 of valve base part 36 on the one hand along valve opening 34; Setover the relative valve opening 34 of the sphere centre of the valve seat surface 45 that constitutes valve base part 34 with through hole 44 common axle center A1 on the one hand, but the axle center of through hole 44 also not necessarily must biasing with the sphere centre that constitutes valve seat surface 45.For example, even in radial offset, also can access roughly same effect to the axle center A1 of the through hole that forms on coaxial and the two relative valve opening 34 of valve seat surface with above-mentioned first embodiment.
Fig. 8～Figure 10 is the figure of expression second embodiment of the invention, and Fig. 8 is the safety valve sectional view vertically that the valve state is closed in expression, and Fig. 9 is the major component enlarged view of Fig. 8, and Figure 10 is the figure of Investigation on safety valve state in the presentation graphs 9.And among Fig. 8～Figure 10 for Fig. 1～identical or suitable part of first embodiment shown in Figure 7 then use with the same reference character of Fig. 1～Fig. 7.
Among second embodiment of Fig. 8～shown in Figure 10; The valve seat surface 65 of the valve base part 64 of safety valve 63 is at Fig. 8, shown in Figure 9 when closing valve; The center C of ball valve 35 forms on the axle center A1 that is positioned at valve opening 34; On the other hand, as the through hole 66 of valve base part 64 make the axle center A1 biasing of the relative valve opening 34 of axle center A6 that is the large-diameter portion 66a of circular to the cross section of ball valve 35 side openings towards the end of valve body side, other parts are then identical with above-mentioned first embodiment.
Specifically then as shown in Figure 9; Second embodiment's valve seat surface 65 is to form ring-type with the piece with ball valve 35 same diameter; Axle center A6 biasing for the relative large-diameter portion 66a of center C of this ball valve 35 when making ball valve 35 and this valve seat surface 65 chimeric likewise makes width dimensions circumferentially gradually change with above-mentioned first embodiment.Promptly form valve seat surface 65 part of sphere of axle center A6 and the center-biased of relative large-diameter portion 66a.The mark 65a of Fig. 8～Figure 10 representes the maximum wide width part of width dimensions in the valve seat surface 65, and the mark 65b of Fig. 8～Figure 10 representes the narrow width part that valve seat surface 65 width dimensions are minimum.
Therefore; Among this second embodiment; Shown in Figure 9 closing under the valve state; Although the depended on pressure F3 of safety valve spring 37 is to the axle center A1 directive effect along valve opening 34, because the axle center A6 biasing of the large-diameter portion 66a that the center C of ball valve 35 is faced with respect to the part of ball valve 35 outer surfaces, the pressing force F4 that pushes ball valve 35 to valve opening position so utilize the hydraulic pressure p in the large-diameter portion 66a is towards wide width part 65a tilt.Be that the ball valve 35 power F4 radially composition F5 wide width part 65a side sections in valve seat surface 65 with axle center large-diameter portion 66a A6 orthogonal direction that decomposite that is pressed is on one side pushed, Yi Bian the axial composition F6 along the axle center A6 direction of large-diameter portion 66a that the power F4 of being pressed decomposites pushes to valve opening position.
Shown in figure 10; When the pressure in the large-diameter portion 66a presses the pressure of chamber 28b to press above the release of regulation promptly; Radially composition F5 wide width part 65a side sections in valve seat surface 65 of power F4 is pushed because ball valve 35 is pressed; So keep on one side with valve seat surface 65 in the part butt of wide width part 65a side, on one side action and from valve seat surface 65 part of narrow width part 65b side leave, working oil is such flowing shown in Figure 10 arrow.Therefore, this second embodiment also likewise can suppress the vibration of ball valve 35 when valve left by safety valve 63 with above-mentioned first embodiment, can access the roughly same effect with above-mentioned first embodiment.
Figure 11 is a sectional view of representing the safety valve 48 of variable capacity type vane pump as the third embodiment of the present invention.Figure 12 is a sectional view of representing the retainer 51 of safety valve 48 separately.
Among the 3rd embodiment shown in Figure 11; The valve seat surface 50 of valve base part 49 forms the sphere centre that constitutes this valve seat surface 50 and is positioned on the axle center A1 of valve opening 34, and in the retainer 51 as the valve body that is formed on ball valve holding part 52 keep the ball valve of recess keep recess 53 form the relative retainer 51 of the center C that makes ball valve 35 axle center A3 and in radial offset.Retainer 51 is except likewise having the axial region 54 with above-mentioned first embodiment, and other parts are also identical with above-mentioned first embodiment.
Specifically then shown in figure 12; Ball valve keeps recess 53 from being positioned at the roughly mortar shape of distortion that deep 55 on the retainer 51 axle center A3 demonstrates sectional shape towards opening side ground to enlarge gradually, radius circumferentially the gradually changing in this edge of opening portion 56 from the axle center A3 of retainer 51 to the edge of opening portion 56 of ball valve maintenance recess 53.Say in detail and be exactly; There is the maximum radius portion 58 of maximum radius R2 to be formed on relative position radially respectively in the least radius portion 57 that least radius R1 arranged in the edge of opening portion 56 and the edge of opening portion 56, circumferentially increasing gradually towards the radius of 58 ground edge of opening portions 56 of maximum radius portion from least radius portion 57.In other words; Ball valve keeps the open angle of axle center A3 of recess 53 relative retainers 51; Being minimum angles θ 4 at the circumferential position that is equivalent to least radius portion 57 on the one hand, is that maximum angle θ 5 ground are circumferentially gradually changing at the circumferential position that is equivalent to maximum radius portion 58 on the one hand.Thus, shown in figure 11, the axle center A2 of the relative retainer 51 of the center C of ball valve 35 and putting to maximum radius portion 58 lateral deviations.
Therefore; The 3rd embodiment also with above-mentioned first embodiment likewise make retainer 51 ball valve holding part 52 comparatively safe valve springs 37 the first end circle 37a of portion and in radial offset; Make the axle center A1 tilt angle theta 6 only of the relative valve opening 34 of axle center A3 of this retainer 51, so can access roughly same effect with above-mentioned first embodiment.
Figure 13 is a sectional view of representing retainer 59 as above-mentioned the 3rd embodiment's variation separately.
In the variation shown in Figure 13; Keep recess 61 to form keeping the ball valve that is formed on ball valve holding part 60 in the retainer 59 the axle center A4 of recess 61 with this ball valve is center rotational symmetric roughly mortar shape, and the axle center A5 of the relative retainer 59 of axle center A4 of this ball valve maintenance recess 61 is in radial offset.Retainer 59 is except likewise having the axial region 62 with above-mentioned the 3rd embodiment, and other parts are also identical with above-mentioned the 3rd embodiment.
Therefore, because the axle center A5 of the relative retainer 59 of center C that this variation also likewise makes ball valve 35 with above-mentioned the 3rd embodiment and in radial offset, so have the advantage that can access with above-mentioned the 3rd embodiment's effect same.
As the fourth embodiment of the present invention; Like Figure 14～shown in Figure 16; Replacing among above-mentioned the 3rd embodiment using the structure of retainer 51, is the shape that the axle center A1 of the safety valve spring 68 relative valve opening 34 of axle center A2 that also can use retainer 38 tilts as helical spring of the present invention.Among Figure 14～Figure 16 for the part identical or suitable then use and Figure 11, the same mark of Figure 12 with Figure 11, the 3rd embodiment shown in Figure 12.
Be exactly in the 4th embodiment's the safety valve 67 specifically; Retainer 38 likewise remains on ball valve 35 on the axle center A2 of this retainer 38 with above-mentioned first embodiment, and forming under safety valve spring shown in Figure 15 68 free states relatively and the imaginary plane P of the axle center A7 quadrature of this safety valve spring 68 inclination with the chimeric chimeric surface 68a of the inner bottom surface 34a of valve opening 34 in the safety valve spring 68.The angle of inclination of the relative imaginary plane P of mark θ 7 expression chimeric surface 68a shown in Figure 15.Parallel with imaginary plane P in the safety valve spring 68 as making under step-like the 42 chimeric free state that is formed in safety valve spring 68 by chimeric surface 68b of retainer 38.Other parts are identical with above-mentioned the 3rd embodiment.
Shown in figure 14; When between the inner bottom surface 34a that is installed in the safety valve spring 68 that forms like this valve opening 34 and retainer 38 step-like 42, while then safety valve spring 68 make its axle center agley compressive strain utilize this compressive strain recuperability and retainer 39 to valve base part 49 sides by pressure.Be the axle center A1 tilt angle theta 1 that safety valve spring 68 makes the relative valve opening 34 of axle center A2 of retainer 39 on one side, utilize along the depended on pressure F of the axle center A2 direction of this retainer 39 and retainer 39 to valve base part 49 sides by pressure on one side.
Therefore; When the pressure in the through hole 44 of valve base part 49 presses the pressure of chamber 28b to press above the release of regulation promptly; That kind then shown in figure 16; Ball valve 35 keep on one side with valve seat surface 50 in the butt of a side sections radially, on one side from valve seat surface 50 radially the other side move Investigation on safety valve with separating.Thus, the 4th embodiment also can suppress the vibration of ball valve 35 when valve left by safety valve 37, can access the roughly same effect with above-mentioned the 3rd embodiment.
At this,, and be not have the content of record to put down in writing as follows in the claim with its effect the technological thought of grasping from above-mentioned each embodiment.
(1) characteristics of the variable capacity type vane pump of content 2 records of the present invention are that the relative distance of the said first end circle portion that the said relatively valve opening of said valve seat surface is axial is formed in the circumferential variation of this valve seat surface.
In the technological thought of (1) record, said valve body gets into said valve base part dearly in the part of leaving from the said helical spring first end circle portion of said valve seat surface, so the axle center of the said relatively valve opening in the center of said valve body and in radial offset.
(2) like the variable capacity type vane pump of (1) record, be characterized in said valve seat surface said valve opening axially towards this valve seat surface radially a side and above-mentioned valve opening axially on tilt to the direction of leaving from the said first end circle portion.
In the technological thought of (2) record; Since in the said valve seat surface radially the part of a side than in the said valve seat surface radially the part of opposite side leave from the said first end circle portion; So get into dearly to said valve base part at the said valve body of this part, put to a lateral deviation radially in the axle center of the said relatively valve opening in the center of this valve body.
(3) the variable capacity type vane pump of putting down in writing like (2); Be characterized in that said valve seat surface is through forming drift to the extruding of said valve base part, and realize at least in the said drift that forming face that said valve seat surface is shaped is formed the part with the sphere of said valve body same diameter.
In the technological thought of (3) record, because the said relatively valve seat surface of said valve body is face contact, so the close property of liquid can improve said safety valve and close valve the time.
(4) the variable capacity type vane pump of putting down in writing like content of the present invention (3); Be characterized in that said valve body holding part has the valve body that keeps said valve body and keeps recess; And this valve body keeps recess to demonstrate the mortar shape of hole enlargement gradually towards opening side ground from deep, this valve body keep recess the said relatively valve body holding member in deep the axle center and in radial offset.
In the technological thought of (4) record, through make said valve body keep recess the said relatively valve body holding member in deep the axle center and in radial offset, the axle center of the said relatively valve body holding member in center that can make said valve body is in radial offset.
Claims (5)
1. variable capacity type vane pump possesses:
Rotor, it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor;
Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor;
Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor;
Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form;
Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path;
This variable capacity type vane pump is characterised in that,
Said safety valve possesses:
Valve opening, it is set in the said pump main body;
The valve body of ball valve shape, it is configured in this valve opening;
Valve base part, it is fixed on an axial side across said valve body in said valve opening, and is formed with the through hole that is communicated with said drain passageway, when closing valve and the chimeric ring valve seat surface of said valve body be formed on the valve body side opening portion of said through hole;
Helical spring, it is set at opposite side across said valve body in said valve opening;
The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with in said helical spring side and limit it with respect to the spring engagement portion of this helical spring in radially relative displacement, the recuperability of utilizing said helical spring compressive strain to be produced, said valve body to said valve base part side by pressing;
Said valve seat surface forms: when closing valve, make in the said relatively helical spring in center of said valve body axle center with the end circle portion of valve seat surface opposition side in radial offset.
2. variable capacity type vane pump possesses:
Rotor, it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor;
Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor;
Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor;
Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form;
Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path;
This variable capacity type vane pump is characterised in that,
Said safety valve possesses:
Valve opening, it is set in the said pump main body;
The valve body of ball valve shape, it is configured in this valve opening;
Valve base part; It is fixed on an axial side across said valve body in said valve opening; And be formed with the through hole that is communicated with said drain passageway coaxially with said valve opening, and, when closing valve and the chimeric ring valve seat surface of said valve body be formed on the valve body side opening portion of said through hole;
Helical spring, it is arranged on opposite side across said valve body in said valve opening, and the first end circle portion and the said valve opening of an axial side are chimeric with the bottom of this valve opening coaxially;
The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with the spring engagement portion in said helical spring side; The restriction of this spring engagement portion with respect in this helical spring axially the second end circle portion of the other end side in radially relative displacement, the recuperability of utilizing said helical spring compressive strain said valve body to said valve base part side by pressure;
Said valve seat surface forms: when closing valve, make said valve body the said relatively valve opening in center the axle center and in radial offset.
3. variable capacity type vane pump possesses:
Rotor, it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor;
Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor;
Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor;
Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form;
Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path;
This variable capacity type vane pump is characterised in that,
Said safety valve possesses:
Valve opening, it is set in the said pump main body;
The valve body of ball valve shape, it is configured in this valve opening;
Valve base part, it is fixed on an axial side across said valve body in said valve opening, and is formed with the through hole that is communicated with said drain passageway, when closing valve and the chimeric ring valve seat surface of said valve body be formed on the valve body side opening portion of said through hole;
Helical spring, it is set at opposite side across said valve body in said valve opening;
The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with in said helical spring side and limit it with respect to the spring engagement portion of this helical spring in radially relative displacement, the recuperability of utilizing said helical spring compressive strain to be produced, said valve body to said valve base part side by pressing;
The axle center that said valve body holding part is formed in respect to this valve body holding part keeps said valve body in the position of radial offset, and thus, the end circle portion that when closing valve, makes valve seat surface opposition side in the said relatively helical spring of said valve body holding part is in radial offset.
4. variable capacity type vane pump possesses:
Rotor, it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor;
Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor;
Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor;
Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form;
Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path;
This variable capacity type vane pump is characterised in that,
Said safety valve possesses:
Valve opening, it is set in the said pump main body;
The valve body of ball valve shape, it is configured in this valve opening;
Valve base part, it is fixed on an axial side across said valve body in said valve opening, and is formed with the through hole that is communicated with said drain passageway, when closing valve and the chimeric ring valve seat surface of said valve body be formed on the valve body side opening portion of said through hole;
Helical spring, it is set at opposite side across said valve body in said valve opening;
The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with in said helical spring side and limit it with respect to the spring engagement portion of this helical spring in radially relative displacement, the recuperability of utilizing said helical spring compressive strain to be produced, said valve body to said valve base part side by pressing;
The chimeric surface of valve body holding member opposition side forms with respect to the imaginary plane with this helical spring axle center quadrature in the said helical spring, thus, the axle center of the said relatively valve opening in axle center of said valve body holding member is tilted.
5. variable capacity type vane pump possesses:
Rotor, it is configured in the containing space in the pump main body, and has a plurality of blades that freely are provided with to radially, this rotor driven shaft rotary driving with haunting;
Cam ring, it can be configured in this rotor movably on the direction that the offset of this rotor changes relatively outer circumferential side forms a plurality of pump chambers with each said blade and rotor;
Suck path, its with said containing space in the suction regional connectivity of the volume increase of each said pump chamber along with the rotation of said rotor;
Drain passageway, its with said containing space in the discharging area of the volume reducing of each said pump chamber is communicated with along with the rotation of said rotor;
Pressure control mechanism, at least one side's pressure is controlled the offset of the said relatively rotor of said cam ring with this in a pair of fluid pressure chamber that its radially both sides that are controlled at said cam ring form;
Safety valve, it is set in the said pump main body, opens and closes the oily path between said drain passageway and the said suction path;
This variable capacity type vane pump is characterised in that,
Said safety valve possesses:
Valve opening, it is set in the said pump main body;
The valve body of ball valve shape, it is configured in this valve opening;
Valve base part, it is fixed on an axial side across said valve body in said valve opening, and is formed with the through hole that is communicated with said drain passageway, when closing valve and the chimeric ring valve seat surface of said valve body be formed on the valve body side opening portion of said through hole;
Helical spring, it is set at opposite side across said valve body in said valve opening;
The valve body holding member; It is set between said valve body and the helical spring; Said valve body side be formed with not only limit with respect to this valve body in radially relative displacement but also keep the valve body holding part of this valve body; And be formed with in said helical spring side and limit it with respect to the spring engagement portion of this helical spring in radially relative displacement, the recuperability of utilizing said helical spring compressive strain to be produced, said valve body to said valve base part side by pressing;
Said valve seat surface forms: at said valve body and this valve seat surface is chimeric when promptly closing valve, make the axle center biasing of the valve body side end that valve body faces described in the through hole of the said relatively valve base part in center of said valve body.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010230133A JP5396364B2 (en) | 2010-10-13 | 2010-10-13 | Variable displacement vane pump |
| JP2010-230133 | 2010-10-13 |
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| Publication Number | Publication Date |
|---|---|
| CN102444578A true CN102444578A (en) | 2012-05-09 |
| CN102444578B CN102444578B (en) | 2016-01-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110307798.0A Active CN102444578B (en) | 2010-10-13 | 2011-10-12 | Variable displacement vane pump |
Country Status (2)
| Country | Link |
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| JP (1) | JP5396364B2 (en) |
| CN (1) | CN102444578B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103470503A (en) * | 2013-10-08 | 2013-12-25 | 天津商业大学 | Sliding-vane refrigerating compressor for axial by-pass capacity adjustment |
| CN107202008A (en) * | 2016-03-18 | 2017-09-26 | 日立汽车系统株式会社 | Pump installation |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6025206B2 (en) * | 2013-03-22 | 2016-11-16 | 日立オートモティブシステムズ株式会社 | Variable displacement vane pump |
| JP6652238B2 (en) | 2016-11-01 | 2020-02-19 | 日立オートモティブシステムズ株式会社 | Vehicle-mounted equipment having a biasing structure using a coil spring |
| JP6711528B2 (en) * | 2017-02-10 | 2020-06-17 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
| JP7077779B2 (en) | 2018-05-25 | 2022-05-31 | 株式会社アドヴィックス | valve |
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| CN107202008A (en) * | 2016-03-18 | 2017-09-26 | 日立汽车系统株式会社 | Pump installation |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012082762A (en) | 2012-04-26 |
| JP5396364B2 (en) | 2014-01-22 |
| CN102444578B (en) | 2016-01-20 |
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Effective date of registration: 20210804 Address after: Ibaraki Patentee after: Hitachi astemo Co.,Ltd. Address before: Ibaraki Patentee before: HITACHI AUTOMOTIVE SYSTEMS, Ltd. Effective date of registration: 20210804 Address after: Ibaraki Patentee after: HITACHI AUTOMOTIVE SYSTEMS, Ltd. Address before: Kanagawa Prefecture, Japan Patentee before: HITACHI AUTOMOTIVE SYSTEMS STEERING, Ltd. |