CN203114762U - Oil inlet adjusting and controlling valve used for oil pump of high pressure common rail system - Google Patents
Oil inlet adjusting and controlling valve used for oil pump of high pressure common rail system Download PDFInfo
- Publication number
- CN203114762U CN203114762U CN 201220645621 CN201220645621U CN203114762U CN 203114762 U CN203114762 U CN 203114762U CN 201220645621 CN201220645621 CN 201220645621 CN 201220645621 U CN201220645621 U CN 201220645621U CN 203114762 U CN203114762 U CN 203114762U
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- valve body
- spring
- valve
- high pressure
- spool
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Abstract
The utility model discloses an oil inlet quantity adjusting and controlling valve used for the oil pump of a high pressure common rail system, which comprises a ratio electromagnet, wherein a ball seat is arranged at the tail end of a ratio electromagnet push rod of the ratio electromagnet, a steel ball is arranged between the ball seat and a valve plug below the ball seat, one end of a spring is fixedly supported by the bottom of the valve plug, and the other end of the spring is fixedly supported at a spring seat; the valve plug is positioned in the cavity of a valve body; and the opening of a valve port is changed by adjusting the driving current of the ratio electromagnet so as to realize the flow adjusting. The oil inlet adjusting and controlling valve for the oil pump of the high pressure common rail system, disclosed by the utility model, has the effect of controlling the opening of the valve port by acting on the valve plug through both electromagnetic force and spring force and enabling the valve plug to be positioned at a relatively stable position, has a function of forcibly cooling the ratio electromagnet and can set the flow of a cooling fluid medium by changing the size of the diameter of an orifice.
Description
Technical field
The utility model relates to a kind of valve, is specifically related to a kind of oil pump oil inlet quantity adjusting control valve for high pressure co-rail system.
Background technique
Modulating valve generally adopts the single valve hole structure as a kind of common actuator, same spool travel, and the maximum flow ability is less than normal.This modulating valve, generally be that the maximum flow ability is non-adjustable and be fixed value or adjust the maximum flow ability by pad, the nonadjustable deficiency of maximum flow ability is to have limited regulating power and the scope of peak rate of flow, the deficiency of adjusting the maximum flow ability by pad shows as adjusting convenient, underaction inadequately, and perpendicularity manufacturing and the matching requirements of the part of this modulating valve are higher.
The model utility content
Technical problem to be solved in the utility model provides a kind of oil pump oil inlet quantity adjusting control valve for high pressure co-rail system, it can regulate the oil-feed flow of oil pump, and then the high-pressure oil feed amount of regulating oil pump, finally reach the pressure of regulating common rail pipe in the high pressure co-rail system.
For solving the problems of the technologies described above, the technical solution that the utility model is used for the oil pump oil inlet quantity adjusting control valve of high pressure co-rail system is:
Comprise proportion electro-magnet 1, proportion electro-magnet push rod 1.1 ends of proportion electro-magnet 1 are provided with ball seat 8, and the below of ball seat 8 is provided with spool 13, is provided with steel ball 9 between ball seat 8 and the spool 13; One end of the bottom fixed support spring 12 of spool 13, the other end of spring 12 is fixedly supported to spring seat 4; Ball seat 8, steel ball 9, spool 13, spring 12 are arranged in the cavity of valve body 3; The two ends of described spool 13 are thick, and are middle thin, spool 13 with the cavity of described valve body 3 be divided into epicoele V.2, active chamber V.3, cavity of resorption V.1; The epicoele that ball seat 8, steel ball 9 are in valve body 3 V.2 in, the cavity of resorption that spring 12 is in valve body 3 V.1 in; V.2, B.2 B.1 V.1 the epicoele of valve body 3 be interconnected with following inclined flow passage by last inclined flow passage with cavity of resorption.
One side of described valve body 3 is provided with oil inlet P, and the opposite side of valve body 3 is provided with oil outlet A; B.3, V.3 oil inlet P is communicated with active chamber by entrance channel; B.3, V.2 B.4 entrance channel be communicated with the epicoele of valve body 3 by the throttling runner; The throttle orifice R of throttling runner after B.4 is provided with impedance screw 14; B.7, V.3 oil outlet A directly is communicated with active chamber by the primary outlet runner; Oil outlet A also connect the front side outlet flow B.6, the rear side outlet flow B.8, V.3 B.5 B.8 B.6 the front side outlet flow be communicated with active chamber by balanced runner with the rear side outlet flow; V.3, B.7 C.3 active chamber lead to the primary outlet runner by first valve port, and B.6 B.5 C.2 V.3 active chamber lead to the front side outlet flow through balanced runner by second valve port, and B.8 B.5 C.1 V.3 active chamber lead to the rear side outlet flow through balanced runner by the 3rd valve port; V.1, the cavity of resorption of valve body 3 is communicated with oil return outlet T.
Adjust the driving current size of described proportion electro-magnet 1, change valve port C.1, C.2, aperture C.3, realize the adjusting of flow; Described proportion electro-magnet 1 no electric circuit, spool 13 is positioned at uppermost position in fig-ure under the spring force effect of spring 12, this moment valve port C.1, C.2, aperture maximum C.3; 1 energising of described proportion electro-magnet, the electromagnetic force that produces when proportion electro-magnet 1 is greater than the spring force of spring 12, and the proportion electro-magnet push rod 1.1 of proportion electro-magnet 1 promotes spools 13 by ball seat 8, steel ball 9 and moves downward, and makes spring 12 compressions, and spring force increases; When spring force increases to when equating with electromagnetic force, 1.1 stop motions of proportion electro-magnet push rod, this moment, C.1, C.2, C.3 valve port formed stable aperture; Flowing medium enters from oil inlet P, B.3, V.3 one road flowing medium enters active chamber through entrance channel, again respectively through valve port C.1, C.2, C.3, by the primary outlet runner B.7, balanced runner B.5, the front side outlet flow B.6, B.8 the rear side outlet flow arrive oil outlet A; Another road flowing medium through the throttling runner B.4, V.2 throttle orifice R force to cool off proportion electro-magnet 1 to epicoele, this road flowing medium take away heat again through last inclined flow passage B.1, down inclined flow passage B.2 to cavity of resorption V.1, flow out from oil return outlet T at last.
Described valve port C.1, C.2, C.3 maximum opening is determined by the diameter of steel ball 9, increases the diameter of steel ball 9, the initial position of spool 13 moves down, make valve port C.1, C.2, maximum opening C.3 reduces; Reduce the diameter of steel ball 9, move on the initial position of spool 13, make valve port C.1, C.2, maximum opening C.3 increases.
The diameter of the throttle orifice R of described throttling runner after B.4 determines salband to walk the ability of heat, makes the maximum temperature of cooled proportion electro-magnet 1 be no more than the serviceability temperature limit value.
Described ball seat 8 is the conical surface with the fitting surface of steel ball 9.Described spool 13 is the conical surface with the fitting surface of steel ball 9.
Be provided with compression spring 11 between described spring 12 and the spring seat 4, the length of installation of spring 12 is realized regulating by compression spring 11.
Described spring seat 4 is fixedlyed connected with valve body 3 by screw thread; Be provided with seal ring 5 between spring seat 4 and the valve body 3.
Described valve body 3 is arranged at the below of proportion electro-magnet 1, and proportion electro-magnet 1 is fixedlyed connected with valve body 3 by bolt; Produce sealing effect by seal ring 2 between valve body 3 and the proportion electro-magnet 1.
Described balanced runner end B.5 is provided with plug 6; Fastening by being threaded between plug 6 and the valve body 3; Be provided with seal ring 7 between plug 6 and the valve body 3.
The technique effect that the utility model can reach is:
The utility model jointly to the spool effect, makes spool be in a metastable position by electromagnetic force and spring force, thereby reaches the effect of valve port opening control, and the valve port of a plurality of symmetries is set, and the negotiability of valve control is obviously promoted.
The utility model changes the maximum opening that the maximum flow ability is valve port by the diameter that changes steel ball, can convenient, flexible increase or reduce the Flow-rate adjustment control range of valve, the maximum opening adjustment realizes by the steel ball standard piece, universal standardization height, with low cost.
Push rod of the present utility model and valve core chamber transmit power by bipyramid face steel ball cooperating structure, the conical surface-steel ball-conical surface assembly structure can make ball seat rotate in the certain limit self adaption, namely realize locating with self adaption, impel the contact of proportion electro-magnet push rod, ball seat, steel ball, core member good, and the perpendicularity that has reduced correlated parts makes requirement, also reduced matching requirements.
The utility model adopts the diclinic hole structure, need not the auxiliary hole plug, and is simple in structure; The diclinic hole structure is communicated with the upper and lower cavity of valve body, and each pressure constantly of valve body upper and lower cavity is all identical, makes the suffered pressure in the upper and lower end face of spool identical, and the influence that valve core movement is stressed is little.
The utlity model has and force cooling proportion electro-magnet function, and set the flow of cooling fluid medium by the size that changes the throttle orifice diameter, and then make cooled proportion electro-magnet 1 maximum temperature be no more than the serviceability temperature limit value.
The utility model is provided with the descending limit function that spring seat possesses spool, by this function minimum aperture can be set, and the length by changing spring seat push rod part is adjusting the position, upper-end surface, thus the downstream position of restriction spool.
Description of drawings
Below in conjunction with the drawings and specific embodiments the utility model is described in further detail:
Fig. 1 is the schematic representation that the utility model is used for the oil pump oil inlet quantity adjusting control valve of high pressure co-rail system;
Fig. 2 is the sectional drawing of S1-S1 among Fig. 1;
Fig. 3 is the sectional drawing of S2-S2 among Fig. 2.
Description of reference numerals among the figure:
1 is proportion electro-magnet, and 1.1 is the proportion electro-magnet push rod,
2 is O-ring seals, and 3 is valve body,
4 is spring seat, and 5 is O-ring seals,
6 is plug, and 7 is O-ring seals,
8 is ball seat, and 9 is steel ball,
11 is compression spring, and 12 is spring,
13 is spool, and 14 is impedance screw,
15 is pad,
P is filler opening, and A is oil outlet,
T is the oil return outlet, and R is throttle orifice,
C.1, C.2, C.3 be valve port,
B.1 be last inclined flow passage, B.2 be following inclined flow passage,
B.3 be entrance channel, B.4 be the throttling runner,
B.5 B.6 be balanced runner, be the front side outlet flow,
B.7 B.8 be the primary outlet runner, be the rear side outlet flow,
V.1 V.2 be cavity of resorption, be epicoele,
V.3 be active chamber.
Embodiment
As shown in Figure 1 to Figure 3, the utility model is used for the oil pump oil inlet quantity adjusting control valve of high pressure co-rail system, comprise proportion electro-magnet 1, proportion electro-magnet push rod 1.1 ends of proportion electro-magnet 1 are provided with ball seat 8, the below of ball seat 8 is provided with spool 13, is provided with steel ball 9 between ball seat 8 and the spool 13;
The two ends of spool 13 are thick, and are middle thin;
One end of the bottom fixed support spring 12 of spool 13, the other end of spring 12 is fixedly supported to spring seat 4; Spring 12 connects spring seat 4 by compression spring 11, and the length of installation of spring 12 is realized regulating by compression spring 11;
One side of valve body 3 is provided with oil inlet P, and the opposite side of valve body 3 is provided with oil outlet A;
B.3, V.3 oil inlet P is communicated with active chamber by entrance channel; B.3, V.2 B.4 entrance channel be communicated with the epicoele of valve body 3 by the throttling runner; The throttle orifice R of throttling runner in B.4 is provided with impedance screw 14, and by being threaded, impedance screw 14 is realized sealing by pad 15 with valve body 3 between impedance screw 14 and the valve body 3; By changing the pore size of throttle orifice (R), can adjust from entrance channel and B.3 flow to valve body epicoele flow size V.2;
B.7, V.3 oil outlet A directly is communicated with active chamber by the primary outlet runner;
Oil outlet A also connect the front side outlet flow B.6, the rear side outlet flow B.8, V.3 B.5 B.8 B.6 the front side outlet flow be communicated with active chamber by balanced runner with the rear side outlet flow;
V.3, B.7 C.3 active chamber lead to the primary outlet runner by first valve port, and B.6 B.5 C.2 V.3 active chamber lead to the front side outlet flow through balanced runner by second valve port, and B.8 B.5 C.1 V.3 active chamber lead to the rear side outlet flow through balanced runner by the 3rd valve port;
Balanced runner end B.5 is provided with plug 6; Fastening by being threaded between plug 6 and the valve body 3, be provided with O-ring seals 7 between plug 6 and the valve body 3;
V.2, B.2 B.1 V.1 the epicoele of valve body 3 be interconnected with following inclined flow passage by last inclined flow passage with cavity of resorption; V.1, the cavity of resorption of valve body 3 is communicated with oil return outlet T.
V.2, B.2 B.1 V.1 the epicoele of valve body of the present utility model be interconnected with following inclined flow passage by last inclined flow passage with cavity of resorption, make epicoele V.2 identical with cavity of resorption pressure V.1, the suffered pressure in spool 13 upper and lower end faces is identical, thereby can eliminate spool 13 upper and lower end face pressure surges and difference to the influence of spool 13 stability.
Working principle of the present utility model is as follows:
Proportion electro-magnet 1 no electric circuit, spool 13 is positioned at uppermost position in fig-ure under the spring force effect of spring 12, this moment valve port C.1, C.2, aperture maximum C.3;
Proportion electro-magnet 1 energising, the electromagnetic force that produces when proportion electro-magnet 1 is greater than the spring force of spring 12, and the proportion electro-magnet push rod 1.1 of proportion electro-magnet 1 promotes spools 13 by ball seat 8, steel ball 9 and moves downward, and makes spring 12 compressions, and spring force increases; When spring force increases to when equating with electromagnetic force, 1.1 stop motions of proportion electro-magnet push rod, this moment, C.1, C.2, C.3 valve port formed stable aperture;
Flowing medium enters from oil inlet P, B.3, V.3 one road flowing medium enters active chamber through entrance channel, again respectively through valve port C.1, C.2, C.3, by the primary outlet runner B.7, balanced runner B.5, the front side outlet flow B.6, B.8 the rear side outlet flow arrive oil outlet A; The driving current size of resize ratio electromagnet 1, change valve port C.1, C.2, aperture C.3, namely change the area of flow area, thereby realize the adjusting of flow; When the driving current of proportion electro-magnet 1 is 0, valve port C.1, C.2, flow area area maximum C.3, valve port opening maximum, the flow maximum of valve; Along with the increase of proportion electro-magnet 1 driving current, spool 13 is descending, valve port C.1, C.2, flow area area C.3 reduces, valve port opening reduces, the flow of valve reduces;
Another road flowing medium through the throttling runner B.4, V.2 throttle orifice R force to cool off proportion electro-magnet 1 to epicoele, this road flowing medium take away heat again through last inclined flow passage B.1, down inclined flow passage B.2 to cavity of resorption V.1, flow out from oil return outlet T at last; Set the diameter of the throttle orifice R of impedance screw 14 according to the heat taken away of cooling needs, make the maximum temperature of cooled proportion electro-magnet 1 be no more than the serviceability temperature limit value.
Thereby the size of current that changes proportion electro-magnet 1 changes the suffered electromagnetic force size of proportion electro-magnet push rod 1.1, electromagnetic force and spring force balance, thereby can change valve port C.1, C.2, aperture size C.3; Electrical current is more big, and electromagnetic force is more big, valve port C.1, C.2, aperture C.3 is more little; When electric current increases to certain value, the upper end of spool 13 fully with runner B.5, B.7 cover, valve port C.1, C.2, aperture C.3 is zero; Continue to increase electric current, spool 13 continues to move downward, and contacts with the upper-end surface of spring seat 4 until spool 13 lower end surfaces.Length by changing spring seat 4 push rods part to be adjusting the position, upper-end surface, thereby changes the downstream position of spool 13, arrives the restriction minimum discharge, and the minimum stream value can not be 0.
Change the diameter of steel ball 9, can change valve port C.1, C.2, maximum opening C.3, thereby adjust the maximum flow control ability of valve; Increase the diameter of steel ball 9, the initial position of spool 13 moves down, thus make valve port C.1, C.2, maximum opening C.3 reduces; Reduce the diameter of steel ball 9, move on the initial position of spool 13, thus make valve port C.1, C.2, maximum opening C.3 increases.
Claims (10)
1. oil pump oil inlet quantity adjusting control valve that is used for high pressure co-rail system, it is characterized in that: comprise proportion electro-magnet (1), proportion electro-magnet push rod (1.1) end of proportion electro-magnet (1) is provided with ball seat (8), the below of ball seat (8) is provided with spool (13), is provided with steel ball (9) between ball seat (8) and the spool (13); One end of the bottom fixed support spring (12) of spool (13), the other end of spring (12) is fixedly supported to spring seat (4); Ball seat (8), steel ball (9), spool (13), spring (12) are arranged in the cavity of valve body (3); The two ends of described spool (13) are thick, and middle thin, spool (13) is divided into epicoele (V.2), active chamber (V.3), cavity of resorption (V.1) with the cavity of described valve body (3); Ball seat (8), steel ball (9) are in the epicoele (V.2) of valve body (3), and spring (12) is in the cavity of resorption (V.1) of valve body (3); The epicoele (V.2) of valve body (3) and cavity of resorption (V.1) are interconnected by last inclined flow passage (B.1) and following inclined flow passage (B.2).
2. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 1, it is characterized in that: a side of described valve body (3) is provided with filler opening (P), and the opposite side of valve body (3) is provided with oil outlet (A); Filler opening (P) is communicated with active chamber (V.3) by entrance channel (B.3); Entrance channel (B.3) is communicated with the epicoele (V.2) of valve body (3) by throttling runner (B.4); Throttle orifice (R) behind the throttling runner (B.4) is provided with impedance screw (14);
Oil outlet (A) directly is communicated with active chamber (V.3) by primary outlet runner (B.7); Oil outlet (A) also connects front side outlet flow (B.6), rear side outlet flow (B.8), and front side outlet flow (B.6) and rear side outlet flow (B.8) are communicated with active chamber (V.3) by balanced runner (B.5);
Active chamber (V.3) leads to primary outlet runner (B.7) by first valve port (C.3), active chamber (V.3) leads to front side outlet flow (B.6) by second valve port (C.2) through balanced runner (B.5), and active chamber (V.3) leads to rear side outlet flow (B.8) by the 3rd valve port (C.1) through balanced runner (B.5);
The cavity of resorption (V.1) of valve body (3) is communicated with oil return outlet (T).
3. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 2, it is characterized in that: described valve port (C.1, C.2, C.3) maximum opening is determined by the diameter of steel ball (9), increase the diameter of steel ball (9), the initial position of spool (13) moves down, and (C.1, C.2, C.3) maximum opening reduces to make valve port; Reduce the diameter of steel ball (9), move on the initial position of spool (13), the maximum opening of valve port (C.1, C.2, C.3) is increased.
4. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 2, it is characterized in that: the diameter of the throttle orifice (R) behind the described throttling runner (B.4) determines salband to walk the ability of heat, makes the maximum temperature of cooled proportion electro-magnet (1) be no more than the serviceability temperature limit value.
5. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 1 is characterized in that: described ball seat (8) is the conical surface with the fitting surface of steel ball (9).
6. be used for the oil pump oil inlet quantity adjusting control valve of high pressure co-rail system according to claim 1 or 5, it is characterized in that: described spool (13) is the conical surface with the fitting surface of steel ball (9).
7. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 1, it is characterized in that: be provided with compression spring (11) between described spring (12) and the spring seat (4), the length of installation of spring (12) is realized regulating by compression spring (11).
8. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 1, it is characterized in that: described spring seat (4) is fixedlyed connected with valve body (3) by screw thread; Be provided with seal ring (5) between spring seat (4) and the valve body (3).
9. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 1, it is characterized in that: described valve body (3) is arranged at the below of proportion electro-magnet (1), and proportion electro-magnet (1) is fixedlyed connected with valve body (3) by bolt; Produce sealing effect by seal ring (2) between valve body (3) and the proportion electro-magnet (1).
10. the oil pump oil inlet quantity adjusting control valve for high pressure co-rail system according to claim 2, it is characterized in that: the end of described balanced runner (B.5) is provided with plug (6); Fastening by being threaded between plug (6) and the valve body (3); Be provided with seal ring (7) between plug (6) and the valve body (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220645621 CN203114762U (en) | 2012-11-29 | 2012-11-29 | Oil inlet adjusting and controlling valve used for oil pump of high pressure common rail system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220645621 CN203114762U (en) | 2012-11-29 | 2012-11-29 | Oil inlet adjusting and controlling valve used for oil pump of high pressure common rail system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203114762U true CN203114762U (en) | 2013-08-07 |
Family
ID=48895112
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220645621 Withdrawn - After Issue CN203114762U (en) | 2012-11-29 | 2012-11-29 | Oil inlet adjusting and controlling valve used for oil pump of high pressure common rail system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203114762U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103850999A (en) * | 2012-11-29 | 2014-06-11 | 中国船舶重工集团公司第七一一研究所 | Oil pump oil inlet quantity adjusting control valve used for high pressure common rail system |
-
2012
- 2012-11-29 CN CN 201220645621 patent/CN203114762U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103850999A (en) * | 2012-11-29 | 2014-06-11 | 中国船舶重工集团公司第七一一研究所 | Oil pump oil inlet quantity adjusting control valve used for high pressure common rail system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130807 Effective date of abandoning: 20170329 |
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| AV01 | Patent right actively abandoned |