CN201241775Y

CN201241775Y - Ultra-high pressure diesel oil jetting pump

Info

Publication number: CN201241775Y
Application number: CNU2008200419903U
Authority: CN
Inventors: 汤燮铭
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-07-21
Filing date: 2008-07-21
Publication date: 2009-05-20
Anticipated expiration: 2018-07-21

Abstract

The utility model provides an ultra-high pressure diesel engine fuel injection pump, which can output the pressure of 160MPa at most, having compact structure, small occupied space, suitable precision requirement, simple manufacture and low production cost. The ultra-high pressure diesel engine fuel injection pump comprises a case, an eccentric shaft, a plunger, a pump head, an oil inlet and an oil outlet, which is characterized in that a ball-end sliding shoe at one end of the plunger is fit with an arc face at the eccentric part of the eccentric shaft, the another end of the plunger and the pump head adopt an elastic seal structure to form a plunger chamber therebetween, the blind end of the plunger chamber is connected with a cross chamber, the cross chamber and two vertical ends of the plunger chamber are connected with the oil inlet and the oil outlet via a spherical valve component respectively.

Description

A kind of super high-pressure diesel fuel injection pump

(1) technical field

The utility model relates to ultrahigh pressure oil spout technical field, is specially a kind of super high-pressure diesel fuel injection pump.

(2) background technique

Diesel engine is as the major impetus source that obtains extensive use, and its general structure is close, and the main distinction is at oil-fired system and automatical control system, that is employing in-line arrangement mechanical pump and electric-controlled co-rail system.What at present represent international most advanced level is German BOSCH company, the emission standard of its common rail fuel combustion system is in Europe III (state III), it adopts traditional bent axle, connecting rod, cross head design, its pump pressure rests on below the 130Mpa, and will on the 130Mpa basis, improve, difficulty is bigger, at first, the plunger idol is joined the required precision height, be difficult to processing, and adopt spring to return force contact force transferring structure, the problem that therefore how to solve Europe IV (state IV) standard is extremely urgent, reach international emission standard, distance is still arranged.

(3) summary of the invention

At the problems referred to above, the utility model provides a kind of super high-pressure diesel fuel injection pump, and its pressure that can export reaches 160Mpa, compact structure, and it is little to take up room, and required precision is moderate, and is easy to process, and manufacture cost is lower.

Its technological scheme is such: it comprises housing, eccentric shaft, and plunger, pump head, filler opening and oil outlet is characterized in that: the ball head sliding shoe of described plunger one end cooperates with the arc surface at the eccentric position of described eccentric shaft; Adopt elastic sealing structure to form described plunger cavity between the other end of described plunger and the described pump head, the cecum of plunger cavity connects the cross chamber, and the two ends that cross chamber and described plunger cavity are vertical are connected filler opening and oil outlet by the ball valve modular construction respectively.

It is further characterized in that: described elastic sealing structure comprises guide sleeve, described guide sleeve is set in an end of plunger, inboard at described guide sleeve, the end face of described plunger is pressed with blowout prevention ring, elastic piston successively, and connect by screw, described guide sleeve is pressed with blowout prevention ring, Sealing, pressure pad, reed successively away from the end face of an end in cross chamber, nut press mounting in described reed and described plunger with being threaded; Described plunger is frustoconic shape respectively with the position that described blowout prevention ring combines; The axis at described round platform position and the angle α between the round platform bus are 16 °～18 °; The end-beveling at described frustoconic shape position, the bus of chamfering rearward end and the angle β between central axis are 31 °～35 °; Described valve member structure comprises the oil transportation joint, the outer cover of described oil transportation joint is equipped with expansion piece, and connect by nut, described oil transportation joint and outside expansion piece thereof are plugged in oil transportation channel, in the described oil transportation joint valve seat is housed, the both ends of the surface of described valve seat are pressed with positioning ring respectively, and the ring step wall in the described positioning ring of an end and the oil transportation joint contacts, and the described positioning ring of the other end contacts with the ring step wall of pump head; In the oil transportation channel of described valve seat inside ball valve is set; Described ball valve has twice, and along the last side that pressure oil flows to, described ball valve lateral part is pressed with guide pin bushing, is pressed with spring between the positioning ring of described guide pin bushing and this side.

In the said structure of the present utility model, being provided with of elastic sealing structure and ball valve modular construction guarantees pump housing high security and sealing, the pressure that the pump housing can be exported is higher, thereby avoided existing diesel injection pump, it is very high that its plunger idol is joined required precision, is difficult to processing, and adopt spring to return force contact force transferring structure, appearance is stuck easily, the jiggly shortcoming of transmission.

(4) description of drawings

Fig. 1 is the sectional view of the utility model plan view;

Fig. 2 be among Fig. 1 K to the sectional view of half-twist;

Fig. 3 is the enlarged view (being in artesian condition) at I place among Fig. 1;

Fig. 4 is the enlarged view (being in passive state) at I place among Fig. 1.

(5) embodiment

See Fig. 1, the utility model comprises housing 1, eccentric shaft 15, plunger 7, pump head 12, filler opening 39 and oil outlet 33, and the ball head sliding shoe of plunger 7 one ends cooperates with the arc surface at eccentric shaft 15 eccentric positions; The other end of plunger 7 forms plunger cavity 8 by elastic sealing structure and pump head 12.The cecum of plunger cavity 8 connects cross chamber 9, and cross chamber 9 and plunger cavity 8 vertical two ends are connected filler opening 39 and oil outlet 33 by the ball valve modular construction respectively; Elastic sealing structure comprises guide sleeve 11, guide sleeve 11 is set in an end of plunger 7, inboard at guide sleeve 11, the end face of plunger 7 is pressed with blowout prevention ring 14, elastic piston 13 successively, and by screw 10 connections, guide sleeve 11 is pressed with blowout prevention ring 6, Sealing 5, pressure pad 4, reed 3 successively away from the end face of an end in cross chamber 9, and nut 2 press-fits in reed 3 and is threaded with plunger 7 usefulness; Plunger 7 is frustoconic shape with the position that blowout prevention ring 6 combines; Angle α between the axis at round platform position and round platform bus is 16 °～18 °; The end-beveling at frustoconic shape position, the bus of chamfering rearward end and the angle β between central axis are 31 °～35 ° (see figure 3)s; The valve member structure comprises oil transportation joint 34,40 respectively, the outer cover of oil transportation joint 34 is equipped with expansion piece 24, and by nut 23 connections, oil transportation joint 34 and outside expansion piece 24 thereof are plugged in oil transportation channel, valve seat 25 is housed in the oil transportation joint, the both ends of the surface of valve seat 25 are pressed with the positioning ring of

positioning ring

26,32, one ends respectively, and (to be positioning ring 32 among Fig. 2 contact with ring step wall in the oil transportation joint 34, and positioning ring 26 contacts with the ring step wall of pump head 12; Twice

ball valve

28,29 is set in the oil transportation channel of valve seat 25 inside, and along the last side that pressure oil flows to, ball valve 29 lateral parts are pressed with guide pin bushing 30, are pressed with spring 31 between guide pin bushing 30 and the positioning ring 32.The inside and outside mounting structure of oil transportation joint 40 is identical with oil transportation joint 34.

Below in conjunction with accompanying drawing working procedure of the present utility model is described: when eccentric shaft 15 rotates, the ball head sliding shoe of plunger 7 is slided along the circular arc groove face on eccentric shaft 15 surfaces, when eccentric position is positioned at the right side, plunger 7 right laterals, plunger cavity 8 internal pressures raise, the blowout prevention ring 14 that is in passive state slides backward under the effect of the crack pressure that rises, the crack H that rises is 0.8 millimeter～1 a millimeter (see figure 3), to be distributed in area than on the little blowout prevention ring 14 of elastic piston 13 by plunger 7 front end elastic pistons 13 formed pressure, the stress that is produced of blowout prevention ring 14 will be greater than working stress, in like manner, blowout prevention ring 14 effectively stops the leakage by guide sleeve 11 outer end pressures.When the pressure in the pump housing does not drop to the limit of calculating sealing when following as yet, will keep this pressure reduction automatically always.And plunger cavity 8 internal pressures are pushed

ball valve

28,29 open when rising to certain value, and high pressure oil is discharged from oil transportation mouth 33; When eccentric shaft 15 eccentric positions go back to, plunger 7 backhauls, plunger cavity 8 strengthens, and forms negative pressure in the chamber 8, and

ball valve

36,37 is opened under negative pressure state, and the oil of external pipe enters the pump housing.Twice fuel inlet

ball check valve

38,37, fuel-displaced

ball valve

28,29 are respectively two seals, and the upset of

ball valve

38,37,28,29 on the nest seat sword of

valve seat

25,27, there is not fixedly impression, therefore not easy to wear, the stroke of

ball valve

38,37,28,29 is subjected to the control of guide pin bushing 30,36, spring 35,31.16 is that reinforced seal, 17 is that flat key, 18 is that gland, 19 is that back-up ring, 20 is that packing ring, 21 is that nut, 22 is a ball ring.

Claims

1, a kind of super high-pressure diesel fuel injection pump, it comprises housing, eccentric shaft, plunger, pump head, filler opening and oil outlet is characterized in that: the ball head sliding shoe of described plunger one end cooperates with the arc surface at the eccentric position of described eccentric shaft; Adopt elastic sealing structure to form described plunger cavity between the other end of described plunger and the described pump head, the cecum of plunger cavity connects the cross chamber, and the two ends that cross chamber and described plunger cavity are vertical are connected filler opening and oil outlet by the ball valve modular construction respectively.

2, according to the described a kind of super high-pressure diesel fuel injection pump of claim 1, it is characterized in that: described elastic sealing structure comprises guide sleeve, described guide sleeve is set in an end of plunger, inboard at described guide sleeve, the end face of described plunger is pressed with blowout prevention ring, elastic piston successively, and connect by screw, described guide sleeve is pressed with blowout prevention ring, Sealing, pressure pad, reed successively away from the end face of an end in cross chamber, nut press mounting in described reed and described plunger with being threaded.

3, according to the described a kind of super high-pressure diesel fuel injection pump of claim 2, it is characterized in that: described plunger and described guide sleeve are frustoconic shape respectively with the position that described blowout prevention ring combines.

4, according to the described a kind of super high-pressure diesel fuel injection pump of claim 3, it is characterized in that: the axis at described round platform position and the angle α between the round platform bus are 16 °～18 °.

5, according to the described a kind of super high-pressure diesel fuel injection pump of claim 4, it is characterized in that: the end-beveling at described frustoconic shape position, the bus of chamfering rearward end and the angle β between central axis are 31 °～35 °.

6, according to the described a kind of super high-pressure diesel fuel injection pump of claim 4, it is characterized in that: described valve member structure comprises the oil transportation joint, the outer cover of described oil transportation joint is equipped with expansion piece, and connect by nut, described oil transportation joint and outside expansion piece thereof are plugged in oil transportation channel, in the described oil transportation joint valve seat is housed, the both ends of the surface of described valve seat are pressed with positioning ring respectively, ring step wall in the described positioning ring of one end and the oil transportation joint contacts, and the described positioning ring of the other end contacts with the ring step wall of pump head; In the oil transportation channel of described valve seat inside ball valve is set; Described ball valve has twice, and along the last side that pressure oil flows to, described ball valve lateral part is pressed with guide pin bushing, is pressed with spring between the positioning ring of described guide pin bushing and this side.