CN101287940B - Pressure control device - Google Patents
Pressure control device Download PDFInfo
- Publication number
- CN101287940B CN101287940B CN200680036718XA CN200680036718A CN101287940B CN 101287940 B CN101287940 B CN 101287940B CN 200680036718X A CN200680036718X A CN 200680036718XA CN 200680036718 A CN200680036718 A CN 200680036718A CN 101287940 B CN101287940 B CN 101287940B
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- China
- Prior art keywords
- spool
- sealed department
- fuel
- spring
- spheroid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
- F02M69/54—Arrangement of fuel pressure regulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/04—Check valves with guided rigid valve members shaped as balls
- F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0466—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with a special seating surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K2200/00—Details of valves
- F16K2200/30—Spring arrangements
- F16K2200/305—Constructional features of springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Control Of Fluid Pressure (AREA)
- Safety Valves (AREA)
- Valve Housings (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
A pressure control device in which pulsation is reduced and an occurrence of noise etc. is prevented. A pressure regulator (1) has a housing (11) having a fuel inlet (18), a fuel outlet (19), and a fuel path (14) for communicating the fuel inlet and fuel outlet, a ball (12) placed in the fuel path (14), a seal section (17) having an opening (22) communicating with the fuel inlet (18) and closing the fuel path (14) when an edge (22a) of the opening (22) is in contact with the ball (12), and a valve spring (13) for urging the ball (12) toward the seal section (17). The valve spring (13) is placed inclined relative to a line (N) normal to a cross-section of the opening (22), and valve body pressing force is different depending on a portion of the opening section (22). When the valve is opened, the ball (12) moves positioned to the right side in the figure, and the left side in the figure of the opening (22) is opened.
Description
Technical field
The present invention relates to carry out the pressure control device that hydrodynamic pressure is adjusted, particularly be used for the pressure control device of the fuel supply system of motor.
Background technique
In the fluid feed system of the fuel supply system of automobile or oil hydraulic circuit etc., in order to prevent that hydrodynamic pressure is excessive and use various pressure control devices.As such pressure control device, well-known have the pressure regulator that used diaphragm or one-way valve etc.The fuel supplying device of for example in Japanese kokai publication hei 9-166059 communique (patent documentation 1), having showed the pressure regulator that the one-way valve type is housed.In the pressure regulator of patent documentation 1, keeping spool (sleeve) by compression helical spring.And, by the switching of moving control valve of this spool, adjust from the pressure (fuel pressure) of the fuel of fuel supplying device discharge.In addition, showed to adopt to have spherical the spool and the pressure regulator of spring in the clear 48-46220 communique (patent documentation 3) real the opening of Japan.
Patent documentation 1: Japanese kokai publication hei 9-166059 communique
Patent documentation 2: Japanese kokai publication hei 6-117549 communique
Patent documentation 3: Japan opens clear 48-46220 communique in fact
The problem that invention will solve
, for for example having used,, there is spool to vibrate, in fluid, produce the situation of pulsation when the flow of fluid reaches a certain established amount when above as the spherical spool of patent documentation 3 and the pressure regulator of spring.Figure 15 (a) is the explanatory drawing of set condition that the pressure regulator of spherical spool and spring has been used in expression, the explanatory drawing of the state when Figure 15 (b) is the big flow that is illustrated in the pressure regulator of (a).Figure 16 is the explanatory drawing that is illustrated in the relation of fluid flow in the such pressure regulator of 15 (a) and hydrodynamic pressure.
The pressure regulator 351 of Figure 15 is the formations of having placed spheroid (spool) 353 and valve spring 354 and retainer 355 in shell 352.Valve spring 354 is kept by retainer 355.Spheroid 353 is crimped on the sealed department 356 by the active force of valve spring 354.When spheroid 353 and sealed department 356 butts, stream 357 is by locking.The pressure of fluid uprises the cracking pressure that becomes regulation when above, and the active force of spheroid 353 opposing valve springs 354 breaks away from from sealed department 356, becomes to open the valve state.
In such pressure regulator 351, when fluid flow increased above boundary value Q1, as shown in figure 16, spheroid 353 vibrated, the hydrodynamic pressure rapid change.In pressure regulator, generally the mobile meeting of the fluid around spheroid is set at equalization., in fact owing to mobile the departing from around the spheroid, spheroid 353 is slightly offset from the center of stream.At this moment, the direction that spheroid 353 departs from is not certain, and the position of spheroid 353 constantly changes, and has produced pulsation.Like this, when producing pulsation, can become different sound of generation or vibration, perhaps become the reason of dysfunctions such as pressure oscillation when the hydrodynamic pressure rapid change.
In general, what note in pressure regulator is, make spheroid 353 lift equalizations when driving valve, and fluid is flowed around spheroid equably.Therefore, in pressure regulator, get the central axle designs of each parts consistent as far as possible.And in the such pressure regulator of Figure 15, make central shaft more, the easy more state that floats fully that becomes of spheroid 353 when big flow then in Element Design or process segment.Shown in Figure 15 (b), under the state that spheroid floats fully, spheroid becomes can be along the state that vibrates on the sense of rotation up and down.Therefore, open the long-pending variation of valve face, it is unstable that pilot pressure becomes.Thereby central shaft is consistent more, even if also be easy to generate the pulsation of pressure more in low flow volume region.According to inventor's experiment, sphere diameter is the 4mm degree, makes when central shaft is critically consistent makes device, even the fluctuation of pressure also takes place the zone below 20 (l/h) easily.
; when such pressure regulator being used on the fuel supply system of for example cart or four-wheel wagon etc., for cart, the fuel of 60 (l/h) degree flows in pressure regulator; and for four-wheel wagon, the fuel of 200 (l/h) degree flows in pressure regulator.That is, in cart etc., can certainly imagine the use with down-off with 20 (l/h).Thereby the specification that pulsation might take place in the zone below 20 (l/h) still can't directly be used on actual vehicle, requires its improvement.
Summary of the invention
The object of the present invention is to provide and a kind ofly can lower pulsation, prevent the pressure control device that different sound etc. takes place.
Solve the method for problem
Pressure control device of the present invention has: the fluid outflow opening that shell, this shell have the fluid inflow entrance and be communicated with described fluid inflow entrance via stream; Sealed department, sealing portion forms in described shell, possesses the opening portion that is communicated with described fluid inflow entrance; Spool, this spool are configured in the described stream, can be provided with respect to described sealed department butt, disengaging ground; And spring, a distolateral and described spool butt of this spring, towards described sealed department to described spool reinforcing; It is characterized in that, be fixed with stopper, be formed with the intercommunicating pore that is communicated with between described fluid outflow opening and the described stream inside, the center O of this intercommunicating pore at the central part of described stopper at described fluid outflow opening
2Be configured on the central shaft of described opening portion, be concaved with another the distolateral spring holding part that keeps described spring at the upstream side of described stopper, and the center O of described spring holding part
1Be configured in center O with described intercommunicating pore
2On the position of departing from, when driving valve, described spool breaks away from from described sealed department, makes that the flowing of fluid around the described spool is partial to prescribed direction.Thus, even the mobile of fluid around described spool departs from, spool stably moves to a direction, and the action stabilization of the spool in the time of also can realizing out valve suppresses the vibration of spool.
In pressure control device of the present invention, also can make described spool and described sealed department crimping by the pushing force that specific direction is partial in described spring utilization.
By described spring, can apply according to the active force different and different described spool with the butt position of described sealed department.When using such spring, the pushing force of spool changes according to the butt position of spool and sealed department.Therefore, when the hydrodynamic pressure increase, when the active force of spool antagonistic spring rose, spool relatively moved to a direction.Thus, the relatively direction of regulation that flows of the fluid around the side's side opening of opening portion, spool.
In addition, by described spring, can apply active force to described spool with respect to the direction of the open profile normal slope of described opening portion.When using such spring, spool is crimped on sealed department by the active force of true dip direction, and the spool pushing force changes according to the position of opening portion.Therefore, when the active force of hydrodynamic pressure increase, spool antagonistic spring rose, spool relatively moved to a direction.Thus, the relatively direction of regulation that flows of the fluid around the side's side opening of opening portion, spool.
Can described spring be configured in the described shell by state with respect to the open profile normal slope predetermined angular of described opening portion.In addition, as described spring, can use the conical helical spring of inclined.
On the other hand, other pressure control device of the present invention has: the fluid outflow opening that shell, this shell have the fluid inflow entrance and be communicated with described fluid inflow entrance via stream; Sealed department, sealing portion forms in described shell, possesses the opening portion that is communicated with described fluid inflow entrance; And spool, this spool is configured in the described stream, can be provided with respect to described sealed department butt, disengaging ground; It is characterized in that having opening structure, in this opening structure, when driving valve, described spool and the gap between the described sealed department on the regulation position of described sealed department are bigger than the described gap at other position of described sealed department; As described opening structure, be provided with and form non-circular described opening portion and elastic member; This elastic member, is crimped on described spool in the edge portion of described opening portion described spool reinforcing towards described sealed department; When driving valve, described spool breaks away from from described sealed department, makes that the flowing of fluid around the described spool is partial to prescribed direction.
In such pressure control device, because will be non-circular, become the regulation form so near the fluid of the sealed department when driving valve is mobile by the sealed department opening portion of stream locking being made with the spool butt, become the form of the mobile deflection prescribed direction side of fluid.Therefore, near the fluid the sealed department flows stable, departs from even the fluid around spool flows, and also is difficult to be subjected to its influence, and spool stably moves to prescribed direction.Thereby the action stabilization of the spool in the time of can realizing out valve can suppress the vibration of spool.At this moment, can make described opening portion form ellipse, its minor axis portion side apex configuration than length-diameter part side summit more on the position by the upstream side of described stream.
The invention effect
According to pressure control device of the present invention, because the mode with the mobile deflection prescribed direction of the fluid around the spool makes spool break away from from sealed department when driving valve, so when driving valve, can make spool preferentially to a direction side shifting.Thereby, even flowing, departs from the fluid around spool, spool also can stably move to a direction, makes the action stabilization of spool when can be implemented in out valve, can suppress the vibration of spool.Thus, can suppress the generation of fuel pulsation, can prevent that different sound from taking place and the function variation, simultaneously, also enlarged use probable discharge scope.
In addition, in pressure control device of the present invention, by adopting described spool and the gap between the described sealed department on the regulation position that when driving valve, makes described sealed department to become, can make flowing of spool fluid on every side be partial to prescribed direction effectively than the big opening structure in described gap on other position of described sealed department.In addition, by adopting the opening portion of sealed department is made non-circular opening structure, near mobile the becoming of the fluid the sealed department in the time of can making out valve is the regulation form.
Description of drawings
Fig. 1 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 1.
Fig. 2 is near the planimetric map of the structure the sealed department of pressure regulator of presentation graphs 1.
Fig. 3 is the sectional drawing of major component of structure of the pressure regulator of the expression embodiment of the invention 2.
Fig. 4 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 3, the state when (a) valve is closed in expression, the state when (b) valve is driven in expression.
Fig. 5 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 4.
Fig. 6 is the figure of structure of the pressure regulator of the expression embodiment of the invention 5, (a) is its sectional drawing, (b) is profile.
Fig. 7 is the figure of structure of the pressure regulator of the expression embodiment of the invention 6, (a) is its sectional drawing, (b) is planimetric map.
Fig. 8 is the figure of structure of the pressure regulator of the expression embodiment of the invention 7, (a) is its sectional drawing, (b) is ground plan.
Fig. 9 is the figure of structure of the pressure regulator of the expression embodiment of the invention 8, (a) is its sectional drawing, (b) is ground plan.
Figure 10 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 9.
Figure 11 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 10.
Figure 12 is the sectional drawing of structure of the pressure regulator of the expression embodiment of the invention 11.
Figure 13 is near the explanatory drawing of the structure the sealed department in the pressure regulator of expression Figure 12, (a) is its planimetric map, (b) is its amplification profile.
Figure 14 is near the explanatory drawing of the structure the sealed department of pressure regulator of the expression embodiment of the invention 12, (a) is its planimetric map, (b) is its amplification profile.
Figure 15 (a) is the explanatory drawing of set condition that the pressure regulator of spherical spool and spring has been used in expression, the explanatory drawing of the state when (b) being the big flow in the pressure regulator of expression (a).
Figure 16 is the explanatory drawing of the relation of fluid flow in the such pressure regulator of expression Figure 15 and hydrodynamic pressure.
Description of reference numerals
1 pressure regulator (pressure control device); 11 shells; 12 spheroids (spool); 13 valve springs (elastic member); The 13a terminal part; The 13b main body portion; 14 fuel flow paths; 15 big footpath streams; 16 path streams; 17 sealed departments; 18 fuel inflow entrances; 19 fuel outflow openings; 21 stoppers; 22 opening portions; 22a edge portion; 23 intercommunicating pores; 24 spring holding parts; 31 pressure regulators (pressure control device); 32 pressure regulators (pressure control device); 33 pressure regulators (pressure control device); 34 valve springs; O
1The center of spring holding part; O
2The center of intercommunicating pore; The e offset; N opening section normal; The central shaft of Os valve spring; θ
1The angle of inclination of valve spring central shaft; θ
2The angle of inclination of valve spring end; F
1Active force; Fa component; F
2Active force; Fb component; F
3Active force; The Ff fuel pressure; The screw diameter of D1 valve spring terminal part; The screw diameter of D2 valve spring main body portion; 101 pressure regulators (pressure control device); 102 shells; 102a sidewall (side wall portion); The 102b bottom surface; 103 spheroids (spool); 104 valve springs (elastic member); 105 valve chambers (stream); 105a upper opening edge; 106 fuel inflow entrances (fluid inflow entrance); 107 sealed departments; 108 fuel outflow openings (fluid outflow opening); 109 retainers; 111 spring holding parts; 121 pressure regulators; 122 fuel outflow openings; 131 pressure regulators; 132 fuel outflow openings; 133 path streams; 134 fuel inflow entrances; 141 pressure regulators; 142 fuel inflow entrances; 151 pressure regulators; 152 fuel outflow openings; 153 spring holding parts; 154 valve springs; 161 pressure regulators; 162 valve springs; 163 fuel outflow openings; 164 spring holding parts; O
3Central shaft; Os valve spring end central shaft; O
4Fuel outflow opening central shaft; O
5Fuel inflow entrance central shaft; O
6Fuel inflow entrance central shaft; θ fuel inflow entrance angle of inclination; 201 pressure regulators (pressure control device); 211 shells; 212 spheroids (spool); The 212a sealing surface; 213 valve springs (elastic member); 214 fuel flow paths; 215 big footpath streams; The 215a internal face; 216 path streams; 217 sealed departments; 218 fuel inflow entrances; 219 fuel outflow openings; 221 retainers; 222 opening portions; 222a edge portion; 231 pressure regulators (pressure control device); 232 walls; The 232a inner peripheral surface; The 232b upper end portion; D3 major diameter size; D4 minor axis size; P minor axis side summit; Q major diameter side summit; Gap between t1 wall portion's inner peripheral surface and the ball valve; Gap between the big footpath of t2 stream internal face and the ball valve; 351 pressure regulators; 352 shells; 353 spheroids; 354 valve springs; 355 retainers; 356 sealed departments; 357 streams.
Embodiment
Below, with reference to the accompanying drawings embodiments of the invention are elaborated.
Embodiment 1
Fig. 1 is the sectional drawing of expression as the structure of the pressure regulator (pressure control device) of embodiments of the invention 1, and Fig. 2 is the planimetric map of the pressure regulator of Fig. 1.The pressure regulator 1 of Fig. 1 for example with the patent documentation 1 the same exhaust port that is configured in fuel supplying device, the pressure of the fuel of giving motor is adjusted to the level of regulation.
Pressure regulator 1 forms the formation of the valve spring (elastic member) 13 of having accommodated the spheroid (spherical spool) 12 that is made of steel ball and being made of compression helical spring in metal shell 11.In shell 11, connect and form fuel flow path 14.Form big footpath stream 15 in the fuel downstream side of fuel flow path 14 (upper side among the figure), form path stream 16 at upstream side (lower side among the figure).In the stream 15 of big footpath, contain spheroid 12 and valve spring 13.On the boundary portion of big footpath stream 15 and path stream 16, form sealed department 17.The end of path stream 16 becomes fuel inflow entrance (fluid inflow entrance) 18.On sealed department 17, be provided with the opening portion 22 that is communicated with fuel inflow entrance 18.When the 22a of the edge portion butt of spheroid 12 and opening portion 22, opening portion 22 is stopped up by spheroid 12, and fuel flow path 14 is by locking.
The end of downstream side of big footpath stream 15 forms fuel outflow opening (fluid outflow opening) 19.The fixing stopper 21 of ring-type on fuel outflow opening 19.Central part at stopper 21 forms the intercommunicating pore 23 that is communicated with between fuel outflow opening 19 and stream 15 inside, big footpath.Upstream side (lower end surface) fovea superior at stopper 21 has spring holding part 24.The center O of spring holding part 24
1Be configured in center O with intercommunicating pore 23
2(consistent at this center with big footpath stream 15) departs from the position of size e.One distolateral and spring holding part 24 butts of valve spring 13.Valve spring 13 is made of compression helical spring, its another distolateral and spheroid 12 butts.Spheroid 12 is crimped on the sealed department 17 often by the active force of valve spring 13.
As shown in Figure 1, valve spring 13 is configured in the big footpath stream 15 under the state that tilts.The center O of spring holding part 24
1Be in center O with intercommunicating pore 23
2The position of departing from.Therefore, the center of the fixed side of valve spring 13 (stopper 21 sides) becomes eccentric state with respect to the center of sealed department 17.That is, the central shaft Os of valve spring 13 as shown in Figure 1, with respect to the open profile normal N of opening portion 22 (at this, consistent with the central shaft that stream bearing of trend along opening portion 22 prolongs, pass through O
2) tilt angle theta
1Thus, supplied with angle θ by 13 pairs of spheroids of valve spring 12
1Active force.Afterwards, spheroid 12 utilizes this active force to be crimped on the 22a of edge portion of opening portion 22.
When spheroid 12 was applied oblique active force, spheroid 12 was applied power F
1Component Fa push among the figure right-hand.Therefore, in pressure regulator 1, the power that spheroid 12 is crimped on the opening portion 22 changes according to the position of opening portion 22.In the pressure regulator 1 of Fig. 1, the crimp force of the 22a of 12 pairs of edge portions of spheroid, since component Fa, right side Fang Bianda in Fig. 1, and left side side diminishes.Therefore, shown in dotted line when applying fuel pressure Ff from the below, left part preferentially breaks away from from sealed department 17 among the figure of spheroid 12.That is, valve spring 13 preferentially plays a role from the preferential releasing mechanism that sealed department 17 breaks away from than other position as the regulation position that makes spheroid 12.
In such pressure regulator 1, when from fuel inflow entrance 18 fuelings, when its pressure uprises, the active force of spheroid 12 opposing valve springs 13 and side shifting (rising) downstream.Thus, spheroid 12 breaks away from from sealed department 17, and path stream 16 and big footpath stream 15 are communicated with.At this moment, pressure regulator 1 becomes out the valve state, and fuel flow path 14 is open-minded.At this, in this pressure regulator 1, spheroid 12 is when sealed department 17 is in place, and sealed department 17 is consistent with the center of spheroid 12.In contrast, fuel flows, when spheroid 12 rises, and spheroid 12 moves under the state that sealed department 17 departs from the center.
That is, in pressure regulator 1, because the crimp force of left part is had a mind to set lessly among the figure of spheroid 12, so when fuel pressure rose, at first being that the spheroid left side is preferential promoted, left side opening among the figure of opening portion 22.That is, when driving valve, spheroid 12 as shown in phantom in Figure 1, the inclined right direction moves, side's side opening of opening portion 22.Like this, so that the mode of the direction (left part among the figure) of deflection regulation wittingly of flowing of the fluid around the spheroid, make spheroid 12 when sealed department 17 breaks away from, even the mobile of fluid around the spheroid departs from, spheroid 12 also stably moves to a direction.Thereby the action of spool is stablized when driving valve, can suppress the vibration of spool.Thus, can suppress to take place the pulsation of fuel, prevent that different sound from taking place and the function variation, simultaneously,, also enlarge spendable range of flow because the whole flow that promotes of valve is increased.
Embodiment 2
Secondly, the pressure regulator (pressure control device) 31 to embodiments of the invention 2 describes.Fig. 3 is the sectional drawing of its major component.The pressure regulator of following examples also with the above-mentioned the same fuel supplying device that is used for.In addition, in embodiment 2～4, to giving identical reference character and omit its explanation with embodiment's 1 same parts, part.
In embodiment 2 pressure regulator 31, the end tilts of sealed department 17 sides of valve spring 13 forms.That is, as shown in Figure 3, the part of terminal about two circle degree is with respect to the central shaft Os tilt angle theta of valve spring 13
2Twine.When using such valve spring 13, spheroid 12 is applied from open profile normal N (at this, Os is consistent with central shaft) tilt angle theta
2Directed force F
2Thus, spheroid 12 has utilized angle θ
2Crimp force be crimped on the sealed department 17.With above-mentioned the same, at this moment, spheroid 12 is applied power F
2Component Fb right-hand reinforcing in figure, the spool crimp force changes according to the position of opening portion 22.Therefore, when applying fuel pressure Ff from the below, with respect to sealed department 17, left part preferentially breaks away from from sealed department 17 among the figure of spheroid 12.
Like this, also when spheroid 12 was in place on sealed department 17, the center of spheroid 12 was consistent with the center of sealed department 17 for pressure regulator 31.And fuel flows, when spheroid 12 rises, the relative sealed department 17 in the center of spheroid 12 departs from, left side opening among the figure of opening portion 22.Thus, the direction of the mobile deflection regulation around the spheroid, with above-mentioned the same, the action of spool is stablized when driving valve, can suppress the vibration of spool.Thereby, also can suppress to take place the pulsation of fuel with embodiment 2 pressure regulator 31, prevent that different sound from taking place and the function variation, simultaneously, also enlarged spendable range of flow.
Embodiment 3
Fig. 4 is the sectional drawing of major component of the pressure regulator (pressure control device) 32 of the expression embodiment of the invention 3, the state when (a) valve is closed in expression, the state when valve is driven in (b) expression.In embodiment 3 pressure regulator 32, the end of sealed department 17 sides of valve spring 13 forms draws line end shape, forms the diameter littler than other position of valve spring 13.That is, the screw diameter D1 of the terminal part 13a of valve spring 13 is wound in the diameter littler than the screw diameter D2 of the 13b of valve body portion (D1＜D2).
In general, for compression helical spring, because the cube of spring modulus k and coil average diameter is inversely proportional to, so when coil average diameter changed, the pushing force of valve spring 13 is significantly variation also.Thereby at the end of valve spring 13, the spring modulus k at the position (position on right side among Fig. 4) of big footpath side diminishes, to the active force of spheroid 12 since the position of opening portion 22 cause changing.That is, when amount of bow is identical, because at the position of the little side of spring modulus k, spring-load diminishes, so right side side's active force of valve spring 13 diminishes in Fig. 4.Therefore, in embodiment 3 pressure regulator 32, spheroid 12 also forms by the pushing force of relative open profile normal N inclination and the form of sealed department 17 crimping.
Like this, in pressure regulator 32, because the active force of valve spring 13 is different and different according to the position of opening portion 22, so when when the below applies fuel pressure, the right side part is preferentially from sealed department 17 disengagings among the figure of the spheroid 12 that crimp force is little.At this moment, also be spheroid 12 on sealed department 17 when in place, sealed department 17 is consistent with the center of spheroid 12, and when fuel flows, when spheroid 12 rises, the relative sealed department 17 in the center of spheroid 12 departs from, right openings among the figure of opening portion 22.Thus, the direction of the mobile deflection regulation around the spheroid, with above-mentioned the same, the action of spool is stablized when driving valve, can suppress the vibration of spool.Thereby, can suppress to take place the pulsation of fuel, prevent that different sound from taking place or the function variation, simultaneously, also enlarged spendable range of flow.
In addition, for compression helical spring, because spring modulus k is inversely proportional to the volume number, so the active force difference that causes because of spiral external diameter variation becomes remarkable more more less along with the volume number of valve spring 13.Thereby the volume number of lead-in wire end (external diameter change section) is few more, and then the difference of active force (variation) is big more.In addition, in embodiment 3, cause active force to change, but the line of spring is directly changed and active force is changed by the variation of spiral external diameter.That is, because the biquadratic of spring modulus k and gauge or diameter of wire is proportional, so the line of valve spring 13 that side of a side of thin part institute butt directly, the crimp force of spheroid 12 diminishes.
Embodiment 4
Fig. 5 is the sectional drawing of the pressure regulator (pressure control device) 33 of embodiments of the invention 4.Also the pressure regulator 1 with embodiment 1 is the same in embodiment 4 pressure regulator 33, the center O of spring holding part 24
1Be in center O with intercommunicating pore 23
2The position of departing from.Intercommunicating pore 23 forms and sealed department 17 coaxial shapes the center O of intercommunicating pore 23
2Consistent with the open profile normal N of opening portion 22.Thereby the center of the relative sealed department 17 in center of the fixed side of valve spring 34 (stopper 21 sides) becomes eccentric state.
On the other hand, different with pressure regulator 1 in pressure regulator 33, as valve spring, use the conical helical spring (taper spring) of inclined.Using above the spiral outer radial taper spring of hole enlargement gradually on the valve spring 34, at this, the helical spring of the type of opening is greatly expanded in the spiral outer end in left side among the employing figure than the spiral outer end on right side.
When using such valve spring 34, spheroid 12 is applied with respect to open profile normal N tilt angle theta
3Directed force F
3, by this active force, spheroid 12 is crimped on the 22a of edge portion of opening portion 22.When spheroid 12 was applied oblique active force, spheroid 12 was pushed among the figure right-hand by the component of active force, and the power that spheroid 12 is crimped on the opening portion 22 changes according to the change in location of opening portion 22.In the pressure regulator 33 of Fig. 5, the side that the crimp force of the 22a of 12 pairs of edge portions of spheroid forms right side among the figure is big, and a side in left side is little.Therefore, when the below applied fuel pressure, left part preferentially broke away from from sealed department 17 among the figure of spheroid 12.That is, in embodiment 4, valve spring 34 also is preferentially to play a role from the preferential releasing mechanism that sealed department 17 breaks away from than other position as the regulation position that makes spheroid 12.
In pressure regulator 33, also the same with the above embodiments, fuel flows, when spheroid 12 rises, and depart from respect to sealed department 17 at the center of spheroid 12, left side opening among the figure of opening portion 22.Thus, the direction of the mobile deflection regulation around the spheroid, with above-mentioned the same, the action of spool is stablized when driving valve, can suppress the vibration of spool.Thereby, can suppress to take place the pulsation of fuel, prevent that different sound from taking place and the function variation, simultaneously, also enlarged spendable range of flow.In addition, in embodiment 1～4, only, just can become structure of the present invention to existing pressure regulator by changing stopper 21 or valve spring 13,34, can be simply and suppress the vibration of spool economically.
Embodiment 5
Fig. 6 is the figure of structure of the pressure regulator (pressure control device) of expression embodiments of the invention 5, (a) is its sectional drawing, (b) is profile.Pressure regulator 101 is also accommodated the spheroid (spool) 103 made by steel ball and the valve spring (elastic member) 104 made by compression helical spring and constituting in metal shell 102.In shell 102, form the valve chamber (stream) 105 of cylinder hole shape.The diameter fuel inflow entrance (fluid inflow entrance) 106 littler than valve chamber 105 formed at bottom in the figure of valve chamber 105.Boundary portion at valve chamber 105 and fuel inflow entrance 106 forms sealed department 107.Valve chamber 105 and sealed department 107, fuel inflow entrance 106 are along central shaft O
3Be configured to coaxial shape.
At sidewall (side wall portion) 102a of shell 102 last formation fuel outflow opening (fluid outflow opening) 108.Fuel outflow opening 108 is to connect the form setting of sidewall 102a, at the position on the top that faces spheroid 103 opening.At this, the center configuration of fuel outflow opening 108 is on than the center height of the spheroid 103 that is crimped on the state on the sealed department 107, than low position, the upper end of the spheroid 103 of this state.On sidewall 102a, only fuel outflow opening 108 is set at a place.Fuel in the valve chamber 105 flows out outside pressure regulator 101 from fuel outflow opening 108.
One distolateral and spheroid 103 butts of valve spring 104.Usually, spheroid 103 is crimped on the sealed department 107 by the active force of valve spring 104.The end of spheroid 103 sides of valve spring 104 as shown in Figure 6, the relative central shaft O of its central shaft Os
3To tilting with fuel outflow opening 108 opposition sides.Thereby spheroid 103 is crimped on the position with fuel outflow opening 108 opposition sides more firmly in sealed department 107.In the figure middle and upper part of valve chamber 105, be pressed into the retainer 109 of fixing short size cylindrical shape.In addition, also can suitably forge the upper opening edge 105a of valve chamber 105, retainer 109 riveted fixing are got off at internal side diameter.Side below retainer 109 is concaved with spring holding part 111.Another of valve spring 104 is distolateral to be connected on the spring holding part 111.
In pressure regulator 101, when from fuel inflow entrance 106 fuelings, when its pressure raises, spheroid 103 is also resisted the active force of valve spring 104 and side shifting (rising) downstream.Thus, spheroid 103 breaks away from from sealed department 107, and fuel inflow entrance 106 and valve chamber 105 are communicated with, and become out the valve state.At this, in this pressure regulator 101, as previously mentioned, on the sidewall 102a of valve chamber 105, be provided with fuel outflow opening 108.Therefore, in sealed department 107, fuel outflow opening 108 side fuel flow easily, and fuel outflow opening 108 plays a role as the fluid guiding mechanism.Thus, spheroid 103 preferentially rises from the mode that sealed department 107 breaks away from the position of fuel outflow opening 108 sides.
Thus, as shown in Figure 6, in the fuel outflow opening 108 sides formation gap of sealed department 107, fuel flows from this gap to fuel outflow opening 108.In addition, in this pressure regulator 101, by the end tilts of valve spring 104, the crimp force of the spheroid 103 of fuel outflow opening 108 sides dies down slightly.Therefore, the position of fuel outflow opening 108 sides of the spheroid 103 easier rising that becomes.
Like this, in embodiment 5 pressure regulator 101, near the fuel flow rate sealed department 107 becomes bigger than the position beyond it at the position near fuel outflow opening 108.That is, right-hand member effluent amount is maximum among the figure, and along with the distance with fuel outflow opening 108 becomes far away, flow diminishes.Thereby in pressure regulator 101, the fuel flow rate when driving valve is not that complete cycle is all impartial, but forms the form that is against fuel outflow opening 108 sides partially.Like this, when be provided with on the valve chamber 105 cross-drilled hole, wittingly make around the spheroid flow to prescribed direction (right side part among the figure) partially by the time, depart from even the fuel around spheroid flows, also be difficult to be subjected to its influence, spheroid 103 is stayed assigned position easily.Therefore, the action of spool is stablized when driving valve, can suppress the vibration of spool.Thereby, can suppress to take place the pulsation of fuel, prevent that different sound from taking place and the function variation, simultaneously,, also enlarged spendable range of flow because the flow that valve rises overally required increases.
Embodiment 6
Fig. 7 is the figure of structure of the pressure regulator 121 of the expression embodiment of the invention 6, is that its sectional drawing, (b) are planimetric maps (a).And in embodiment 6～10, the parts the same with embodiment 5, part are given identical reference character and omitted its explanation.
In the pressure regulator 121 of Fig. 7, on retainer 109, be provided with fuel outflow opening 122.At this, on sidewall 102a, do not establish the fuel outflow opening, the side of shell 102 is by locking.Fuel outflow opening 122, one is distolateral to valve chamber 105 inner openings, and the outside opening of the other end side direction shell 102 is with the form setting of joining with retainer 109.The center of fuel outflow opening 122 (central shaft O
4) be configured in from the center of retainer 109 (central shaft O
3) eccentric e
1The position on.
In pressure regulator 121, because in spheroid 103 risings, when becoming out the valve state, fuel outflow opening 122 flows so fuel outflow opening 122 sides one side's at sealed department 107 places fuel becomes easily to the eccentric setting of the outer circumferential side of retainer 109.Therefore, spheroid 103 preferentially rises from the mode that sealed department 107 breaks away from the position of fuel outflow opening 122 sides as shown in Figure 7, the form of fuel flow rate deflection fuel outflow opening 122 sides when forming out valve.That is, in embodiment 6, the fuel outflow opening 122 of eccentric configuration plays a role as the fluid guiding mechanism.
Like this, in embodiment 6 pressure regulator 121, position deflection that can based on fuel outflow opening 122 makes flowing around the spheroid depart to prescribed direction wittingly, and the action of spool is stable when driving valve.Therefore, can suppress the vibration of spool, suppress to take place the pulsation of fuel, prevent that different sound from taking place or the function variation, simultaneously, also enlarged spendable range of flow.
Embodiment 7
Fig. 8 is the figure of structure of the pressure regulator 131 of the expression embodiment of the invention 7, is that its sectional drawing, (b) are ground plans (a).In the pressure regulator 131 of Fig. 8, the same with existing pressure regulator, be provided with fuel outflow opening 132 in the central authorities of retainer 109.On the other hand, in this pressure regulator 131, below sealed department 107, form path stream 133 with valve chamber 105 coaxial shape ground.Fuel inflow entrance 134 is to be communicated with in the path stream 133 and the form setting of the outside of shell 102.Fuel inflow entrance 134 one distolateral to path stream 133 inner openings, the outside opening of the other end side direction shell 102.Fuel inflow entrance 134 forms the diameter littler than path stream 133.The center of fuel inflow entrance 134 (central shaft O
5) be configured in center (central shaft O from path stream 133
3) eccentric e
2The position on.
In such pressure regulator 131, rise, when becoming out the valve state, spheroid 103 applied the last thrust of being partial to fuel inflow entrance 134 sides at spheroid 103.That is, because fuel inflow entrance 134 relative path stream 133 eccentric settings, so the fuel by flowing into from fuel inflow entrance 134, a side of spheroid 103 pushes away on consumingly.Therefore, spheroid 103 preferentially rises from the mode that sealed department 107 breaks away from the position of fuel inflow entrance 134 sides as shown in Figure 8, and the fuel flow rate when driving valve becomes the form of deflection fuel inflow entrance 134 sides.That is, in embodiment 7, path stream 133 plays a role as the fluid guiding mechanism with the fuel inflow entrance 134 of relative path stream 133 eccentric configurations.
Like this, in embodiment 7 pressure regulator 131, biasing that can based on fuel inflow entrance 134 makes flowing around the spheroid lean on partially to prescribed direction wittingly, and the action of spool is stable when driving valve.Therefore, can suppress the vibration of spool, suppress to take place the pulsation of fuel, prevent that different sound from taking place or the function variation, simultaneously, also enlarged spendable range of flow.
Embodiment 8
Fig. 9 is the figure of structure of the pressure regulator 141 of the expression embodiment of the invention 8, is that its sectional drawing, (b) are ground plans (a).In the pressure regulator 141 of Fig. 9, also the same with existing pressure regulator, be provided with fuel outflow opening 132 in the central authorities of retainer 109.On the other hand, in this pressure regulator 141, fuel inflow entrance 142 is with respect to central shaft O
3Diagonal.That is the central shaft O of fuel inflow entrance 142,
6With respect to central shaft O
3Tilt angle theta r.And fuel inflow entrance 142 bottom surface 102b from shell 102 under heeling condition extends to sealed department 107.
In such pressure regulator 141, in spheroid 103 risings, when becoming out the valve state, because fuel inflow entrance 142 is with relative central shaft O
3The form setting of tilting is so meeting with fuel below tiltedly on the spheroid 103.Therefore, it is along inclined direction mobile that fuel is tending towards, and becomes the form that fuel concentrates on the right side among Fig. 9.Thus, spheroid 103 preferentially rises from the mode that sealed department 107 breaks away from the position of true dip direction forward end, and the fuel flow rate when becoming out valve becomes the form on right side among the deflection figure.That is, in embodiment 8, the fuel inflow entrance 142 of tilted configuration plays a role as the fluid guiding mechanism.
Like this, in embodiment 8 pressure regulator 141, inclination that can based on fuel inflow entrance 142 makes flowing around the spheroid lean on partially to prescribed direction wittingly, and the action of spool is stable when driving valve.Therefore, can suppress the vibration of spool, suppress to take place the pulsation of fuel, prevent that different sound from taking place and the function variation, simultaneously, also enlarged spendable range of flow.
In addition, in described embodiment 5～8, make the end tilts ground and spheroid 103 butts of valve spring 104, but any one embodiment can both force depart from and the one-sided lifting of Forced Valve by making to flow, not need spring end to tilt.Promptly.As shown in figure 15, also can adopt make valve spring 104 terminal non-obliquely with the structure of spheroid 103 butts.
Embodiment 9
Figure 10 is the sectional drawing of structure of the pressure regulator 151 of the expression embodiment of the invention 9.In the pressure regulator 151 of Figure 10, the center configuration of fuel outflow opening 152 is on the position with respect to the center off-centre of retainer 109.And the spring holding part 153 that side forms below retainer 109 is with respect to central shaft O
3Be eccentrically set on the direction the same with fuel outflow opening 152.Between retainer 109 and spheroid 103, tilted configuration is used the valve spring 154 of compression helical spring.That is, this embodiment 9 becomes the structure that has made up the above embodiments 1 and embodiment 6.
In such pressure regulator 151, because eccentric configuration fuel outflow opening 152, so side's fuel of fuel outflow opening 152 sides flows easily in sealed department 107.And then, because the also eccentric configuration of spring holding part 153, so the crimp force of spheroid 103 relative sealed departments 107 also is offset.That is, because the configuration of the off-centre of fuel outflow opening 152 and spring holding part 153, make that left part breaks away from from sealed department 107 easily among the figure of spheroid 103.
Therefore, in sealed department 107, in spheroid 103 risings, when becoming out the valve state, fuel outflow opening 152 side fuel flow easily, and little at fuel outflow opening 152 side spheroid crimp forces.That is, in embodiment 9, the fuel outflow opening 152 of eccentric configuration plays a role as the fluid guiding mechanism.Therefore, when spheroid 103 rose, the center of spheroid 103 was offset with respect to sealed department 107, the preferential opening in left side among the figure of sealed department 107.Thereby, with above-mentioned the same, flowing around the spheroid leaned on partially to prescribed direction, when driving valve, can make the action of spool stable.
Embodiment 10
Figure 11 is the sectional drawing of structure of the pressure regulator 161 of the expression embodiment of the invention 10.In the pressure regulator 161 of Figure 11, replace Figure 10 pressure regulator 151 valve spring 154 and use the valve spring 162 of volute spring.That is, this embodiment 10 becomes the structure that has made up the foregoing description 4 and embodiment 6.
In such pressure regulator 161, because the also eccentric configuration of fuel outflow opening 163, so the same with the pressure regulator 151 of Figure 10, in sealed department 107, the fuel of fuel outflow opening 163 sides flows easily.And then, owing in the 164 eccentric configurations of spring holding part, use volute spring as valve spring 162, so the crimp force of spheroid 103 relative sealed departments 107 also further is offset.That is, in embodiment 10, the fuel outflow opening 163 of eccentric configuration plays a role as the fluid guiding mechanism, and valve spring 162 also has the function as preferential releasing mechanism.
Like this, in embodiment 10 pressure regulator 161, because the off-centre setting of fuel outflow opening 163 and spring holding part 164 and the double effects that uses volute spring, left part is easier among the figure of spheroid 103 breaks away from from sealed department 107.Thereby, with above-mentioned the same, flowing around the spheroid leaned on partially to prescribed direction, when driving valve, can make the action of spool stable.
Figure 12 is the sectional drawing of structure of the pressure regulator (pressure control device) of the expression embodiment of the invention 11.Pressure regulator 201 is also accommodated the spheroid 212 (spherical spool) that is made of steel ball and the valve spring (elastic member) 213 that is made of compression helical spring and constituting in metal shell 211.In shell 211, connect and form fuel flow path 214.Form big footpath stream 215 in the fuel downstream side of fuel flow path 214 (upper side among the figure), and form path stream 216 at upstream side (lower side among the figure).In the stream 215 of big footpath, deposit spheroid 212 and valve spring 213.Boundary portion at big footpath stream 215 and path stream 216 forms sealed department 217.The end of path stream 216 becomes fuel inflow entrance (fluid inflow entrance) 218.
The end of downstream side of big footpath stream 215 becomes fuel outflow opening (fluid outflow opening) 219, and stopper 221 is fixed in this.Stopper 221 forms ring-type, distolateral and its upstream side (lower end surface) butt of valve spring 213.Valve spring 213 is made up of conical helical spring, its another distolateral and spheroid 212 butts.Spheroid 212 is by the active force of valve spring 213 and be crimped on usually on the sealed department 217.On sealed department 217, be provided with the opening portion 222 that is communicated with fuel inflow entrance 218.The diameter of opening portion 222 is littler than the diameter of spheroid 212.During the 222a of the edge portion butt of the sealing surface 212a of spheroid 212 and opening portion 222, opening portion 222 is clogged by spheroid 212, and fuel flow path 214 is by locking.
Figure 13 is near the explanatory drawing of the structure the expression sealed department 217, (a) is that near planimetric map, (b) the sealed department is its amplification profile.As shown in figure 13, in pressure regulator 201 of the present invention, opening portion 222 forms ellipse.Opening portion 222 dimension D 3 of left and right directions (major diameter) is in the drawings set than the long (D3＞D4) of the dimension D 4 of above-below direction (minor axis).The 222a of edge portion of opening portion 222 becomes descend some shape of (upstream side) curve ground, minor axis side direction below, so that spheroid 212 can closely contact, minor axis side summit P is configured in than major diameter side summit Q and more leans on the position of stream upstream side (with reference to Figure 13 (b)).In addition, handle to improve precision by implement punching on sealed department 217, spheroid 212 is crimped on the sealed department 217, both are butt seamlessly.
In such pressure regulator 201, from fuel inflow entrance 218 fuelings, when its pressure uprises, the active force of spheroid 212 opposing valve springs 213 is side shifting (rising) downstream.Thus, spheroid 212 breaks away from from sealed department 217, and path stream 216 and big footpath stream 215 are communicated with, and become out the valve state, and fuel flow path 214 is open-minded.At this, in this pressure regulator 201, as described above, opening portion 222 becomes the ellipse that minor axis side direction updrift side descends.Thereby when rising with these shaped aperture portion 222 tight spheroids that contact 212, as the gap that produces between spheroid 212 and the 222a of edge portion, one side is bigger than minor axis side for its major diameter side.That is, oval-shaped opening portion 222 has the gap opening structure bigger than the gap at other position between the spheroid on the regulation position 212 and sealed department 217 when driving valve.Therefore, in pressure regulator 201, the fuel flow rate when driving valve is not the complete cycle equalization, and fuel flow rate becomes the form of representing with the thickness of arrow among Figure 13 (a).
Promptly, in pressure regulator 201 of the present invention, near the sealed department 217 fuel flow rate is bigger than minor axis side in opening portion major diameter side, and the fuel that imports from fuel inflow entrance 218 becomes the form that left and right directions is shunted to figure by spheroid 212 and oval-shaped sealed department 217.When the mobile shunting that makes wittingly around the spool, even the mobile generation of the fuel around the spool is leaned on partially, also be difficult to be subjected to it to influence like this, spheroid 212 is stayed the position of regulation easily.Therefore, the vibration that when driving valve, can make the action of spool stable, can suppress spool.Thereby, can suppress to take place the pulsation of fuel, prevent that different sound from taking place and dysfunction, simultaneously, also enlarged spendable range of flow.
Secondly, the pressure regulator (pressure control device) 231 to embodiments of the invention 12 describes.Figure 14 is near the explanatory drawing of the structure of the sealed department of expression pressure regulator 231, is that its planimetric map, (b) are its amplification profiles (a).In addition, similarly to Example 11 parts, part are given identical reference character and omitted its explanation.
In embodiment 12 pressure regulator 231, as shown in figure 14, form wall portion (special-shaped portion) 232 in the sealed department downstream side of big footpath stream 215.Wall portion 232 becomes that to the side-prominent shape of internal diameter, inner peripheral surface 232a forms spherical shape along a part of internal face 215a (is the amount of half cycle at this) that circumferentially makes big footpath stream 215.Gap between inner peripheral surface 232a of wall portion and the spheroid 212 enlarges towards the stream downstream side, and 232b becomes t1 in the upper end portion of wall portion 232.Clearance t 1 diminishes significantly than internal face 215a on the part that does not form wall portion 232 (special-shaped portion non-formation position) and the clearance t 2 between the spheroid 212.
When the downstream side at sealed department 217 forms such wall portion 232, when rising, spool hindered and very difficult side flow downstream by wall portion 232 at wall portion 232 existing positions from the fuel that flows out between spheroid 212 and the 222a of edge portion.That is, in embodiment 12, in the direction of setting the fuel flow difficulties, in prescribed direction fuel is flowed on this point easily, wall portion 232 plays a role as the fluid guiding mechanism.Therefore, the fuel flow rate when driving valve is not the complete cycle equalization, becomes the form of representing with the thickness of arrow among Figure 14 (a).That is, in embodiment 12 pressure regulator 231, do not exist that side of wall portion 232 bigger than wall portion's 232 these side fuel flow rates, clearance t 1 is that the right-hand member side is minimum among the minimum figure, increases along with the gap enlargement of wall portion-valve core chamber.
Like this, during the direction (left part among the figure) of the mobile deflection regulation when make spool wittingly under the work of wall portion 232 around, even the mobile of fuel around the spool is offset, also be difficult to be subjected to it to influence, spheroid 212 is stayed the position of regulation easily.Therefore, the action of spool is stablized when driving valve, can suppress the vibration of spool.Thereby, can suppress to take place the pulsation of fuel, prevent that different sound from taking place or dysfunction, simultaneously, also enlarged spendable range of flow.
In addition, in this embodiment, form wall portion 232 along the mode that circumferentially slowly enlarges, but also can make clearance t 1 wall portion 232 is set in mode with the identical value of predetermined angular (for example 60 °, 90 °, 180 ° etc.) with clearance t 1 right part from figure.
The invention is not restricted to the foregoing description, obviously in the scope that does not break away from its design, can carry out various changes.
For example, be that example is illustrated with the pressure regulator as pressure control device in the above-described embodiment, but the present invention also is suitable for the pressure control device of other kinds such as safety check, therefore also can enlarge the whole scope of adjustable in pressure, suppresses the generation of different sound.In addition, the present invention can not only be used for the pressure regulator of check valve-type, also can be used for the pressure regulator of valve formula etc.
And then, be that example is illustrated with the pressure regulator that is used for the engine fuel supply system in said embodiment, but its purposes is not limited to motor, can be used for various oil hydraulic circuits.In addition, become the fluid of pressure regulation object, be not limited to motor fuels such as gasoline or light oil, also can be applicable to the work wet goods of water or air, oil hydraulic circuit.
In addition, in described embodiment to used the pressure regulator of spherical steel ball to set forth as spool, but the parts etc. that also underpart can be made hemispheric sleeve shape are made spool and are used, and the structure of pressure regulator self also is not limited to the above embodiments.In addition, also can adopt the structure that the foregoing description is combined except that embodiment 9,10.
Claims (8)
1. pressure control device has:
The fluid outflow opening that shell, this shell have the fluid inflow entrance and be communicated with described fluid inflow entrance via stream;
Sealed department, sealing portion forms in described shell, possesses the opening portion that is communicated with described fluid inflow entrance;
Spool, this spool are configured in the described stream, can be provided with respect to described sealed department butt, disengaging ground; And
Spring, a distolateral and described spool butt of this spring, towards described sealed department to described spool reinforcing; It is characterized in that,
Be fixed with stopper at described fluid outflow opening,
Central part at described stopper is formed with the intercommunicating pore that is communicated with between described fluid outflow opening and the described stream inside, the center (O of this intercommunicating pore
2) be configured on the central shaft of described opening portion,
Upstream side at described stopper is concaved with another the distolateral spring holding part that keeps described spring, and
Center (the O of described spring holding part
1) be configured in the center (O with described intercommunicating pore
2) on the position of departing from,
When driving valve, described spool breaks away from from described sealed department, makes that the flowing of fluid around the described spool is partial to prescribed direction.
2. pressure control device as claimed in claim 1 is characterized in that, the pushing force that specific direction is partial in described spring utilization makes described spool and described sealed department crimping.
3. pressure control device as claimed in claim 2 is characterized in that described spring applies active force to described spool, and this active force is according to different with the butt position of described sealed department butt.
4. pressure control device as claimed in claim 2 is characterized in that, described spring applies active force with respect to the direction of the open profile normal slope of described opening portion to described spool.
5. as claim 3 or 4 described pressure control devices, it is characterized in that, described spring with respect to the state configuration of the open profile normal slope predetermined angular of described opening portion in described shell.
6. as claim 3 or 4 described pressure control devices, it is characterized in that described spring is the conical helical spring of inclined.
7. pressure control device has:
The fluid outflow opening that shell, this shell have the fluid inflow entrance and be communicated with described fluid inflow entrance via stream;
Sealed department, sealing portion forms in described shell, possesses the opening portion that is communicated with described fluid inflow entrance; And
Spool, this spool are configured in the described stream, can be provided with respect to described sealed department butt, disengaging ground; It is characterized in that,
Have opening structure, in this opening structure, when driving valve, described spool and the gap between the described sealed department on the regulation position of described sealed department are bigger than the described gap at other position of described sealed department;
As described opening structure, be provided with and form non-circular described opening portion and elastic member; This elastic member, is crimped on described spool in the edge portion of described opening portion described spool reinforcing towards described sealed department;
When driving valve, described spool breaks away from from described sealed department, makes that the flowing of fluid around the described spool is partial to prescribed direction.
8. pressure control device as claimed in claim 7 is characterized in that described opening portion forms ellipse, and its minor axis portion side apex configuration is more being leaned on the position of described stream upstream side than length-diameter part side summit.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005289588 | 2005-10-03 | ||
| JP289588/2005 | 2005-10-03 | ||
| JP289589/2005 | 2005-10-03 | ||
| JP289587/2005 | 2005-10-03 | ||
| JP2005289589 | 2005-10-03 | ||
| JP2005289587 | 2005-10-03 | ||
| PCT/JP2006/319433 WO2007040169A1 (en) | 2005-10-03 | 2006-09-29 | Pressure control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101287940A CN101287940A (en) | 2008-10-15 |
| CN101287940B true CN101287940B (en) | 2010-09-08 |
Family
ID=37906211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680036718XA Expired - Fee Related CN101287940B (en) | 2005-10-03 | 2006-09-29 | Pressure control device |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5149624B2 (en) |
| CN (1) | CN101287940B (en) |
| BR (1) | BRPI0616483B8 (en) |
| WO (1) | WO2007040169A1 (en) |
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| JP5023141B2 (en) * | 2009-12-15 | 2012-09-12 | 日立オートモティブシステムズ株式会社 | Variable displacement vane pump |
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| JP5198511B2 (en) * | 2010-06-29 | 2013-05-15 | 株式会社デンソー | Constant residual pressure valve |
| JP5913510B1 (en) * | 2014-09-26 | 2016-04-27 | 株式会社小金井精機製作所 | Diesel pump |
| JP6474996B2 (en) * | 2014-11-13 | 2019-02-27 | トヨタ自動車株式会社 | Pressure reducing valve and gas supply device |
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| CN104929019B (en) * | 2015-06-05 | 2017-08-11 | 柳工无锡路面机械有限公司 | A kind of rubber-tyred roller tire tread injection system |
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| JP6950356B2 (en) * | 2017-08-24 | 2021-10-13 | 株式会社デンソー | Pressure regulator |
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| JP2520510Y2 (en) * | 1990-03-14 | 1996-12-18 | 東芝精機株式会社 | Pressure regulating valve |
| JPH0725500Y2 (en) * | 1990-07-20 | 1995-06-07 | 東芝精機株式会社 | Pressure control valve |
| JPH0463874U (en) * | 1990-10-12 | 1992-05-29 | ||
| JPH0625673U (en) * | 1992-09-03 | 1994-04-08 | 新電元工業株式会社 | Ball valve |
| JP3364116B2 (en) * | 1997-08-05 | 2003-01-08 | 株式会社山武 | Valve device |
| JP4066721B2 (en) * | 2002-06-17 | 2008-03-26 | 株式会社アドヴィックス | Check valve and brake actuator using the check valve |
| JP4731999B2 (en) * | 2005-05-24 | 2011-07-27 | 株式会社パイオラックス | Pressure on / off valve |
-
2006
- 2006-09-29 BR BRPI0616483A patent/BRPI0616483B8/en not_active IP Right Cessation
- 2006-09-29 JP JP2007538743A patent/JP5149624B2/en active Active
- 2006-09-29 WO PCT/JP2006/319433 patent/WO2007040169A1/en active Application Filing
- 2006-09-29 CN CN200680036718XA patent/CN101287940B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3473443A (en) * | 1966-03-26 | 1969-10-21 | Danfoss As | Safety valve for hydraulic system |
| US3465787A (en) * | 1967-04-12 | 1969-09-09 | Gen Electric | Spring-biased valve with anti-chattering feature |
| US3437082A (en) * | 1967-06-23 | 1969-04-08 | Standard Screw | Flow metering device |
| CN2158477Y (en) * | 1993-02-09 | 1994-03-09 | 中国水利水电基础工程局科研所 | Valve for high pressure injecting concrete mud |
| US5960822A (en) * | 1995-07-17 | 1999-10-05 | INA Wazlager Schaeffler OHG | Step valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101287940A (en) | 2008-10-15 |
| JPWO2007040169A1 (en) | 2009-04-16 |
| BRPI0616483B8 (en) | 2020-05-19 |
| WO2007040169A1 (en) | 2007-04-12 |
| JP5149624B2 (en) | 2013-02-20 |
| BRPI0616483B1 (en) | 2020-05-05 |
| BRPI0616483A2 (en) | 2012-12-25 |
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Effective date of registration: 20211123 Address after: Gunma Patentee after: MITSUBA Corp. Patentee after: HONDA MOTOR Co.,Ltd. Patentee after: Hitachi astemo Co.,Ltd. Address before: Gunma Patentee before: MITSUBA Corp. Patentee before: HONDA MOTOR Co.,Ltd. Patentee before: KEIHIN Corp. |
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