CN1807871A - High pressure pump having downsized structure - Google Patents
High pressure pump having downsized structure Download PDFInfo
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- CN1807871A CN1807871A CN 200610005465 CN200610005465A CN1807871A CN 1807871 A CN1807871 A CN 1807871A CN 200610005465 CN200610005465 CN 200610005465 CN 200610005465 A CN200610005465 A CN 200610005465A CN 1807871 A CN1807871 A CN 1807871A
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Abstract
A high pressure pump has a fuel passage and a pump chamber. Fuel flows into the pump chamber through the fuel passage. The high pressure pump includes a valve member and a plunger. The valve member is movable along a movable axis in a substantially axial direction of the valve member for controlling an amount of fuel flowing into the pump chamber through the fuel passage. The plunger is movable substantially along a movable axis in a substantially axial direction of the plunger. The plunger is capable of pressurizing fuel in the pump chamber to discharge fuel in the pump chamber. The movable axis of the valve member is displaced from the movable axis of the plunger substantially in parallel with each other.
Description
Technical field
The present invention relates to use the high-pressure service pump of plunger with pressurized with fluid.
Background technique
Traditionally, high-pressure service pump has by oil-engine driven plunger.High-pressure service pump uses plunger the fuel in the pump chamber to be discharged to the outside of high-pressure service pump.Valve member control flows into the fuel quantity of pump chamber by fuel channel.
According to WO00/06895 (JP-A-2002-521616, US6345608), high-pressure service pump has movable plunger and movable valve member.The axis of movement of plunger and the axis of movement of valve member are roughly coaxial.According to WO00/47888 (US6631706, US20040055580A1), the axis of movement approximate vertical of the axis of movement of plunger and valve member.
Consider the installability on motor, above-mentioned high-pressure service pump with plunger is preferably very little.But in the high-pressure service pump according to WO00/06895, plunger and valve member are roughly coaxial.Therefore, high-pressure service pump can be big along the axial change of plunger.In addition, in the high-pressure service pump according to WO00/06895, the coiler part of mobile valve member, the part of fuel channel etc. is arranged in a side opposite with plunger with respect to valve member.What therefore, high-pressure service pump can be along plunger is axially further elongated.
By contrast, in high-pressure service pump according to WO00/47888, the axis of valve member along plunger radially with respect to the axis of plunger and depart from.In this structure, roughly along the radially extension of plunger, therefore, even high-pressure service pump can be along the axial minification of plunger, high-pressure service pump also can be big along the radially change of plunger for valve member.In addition, in the high-pressure service pump according to WO00/47888, the part of coiler part, fuel channel etc. is arranged in a side opposite with plunger with respect to valve member.What therefore, high-pressure service pump can be along plunger is radially further elongated.
In addition, according to JP-A-2003-254191 (US20030164161A1), high-pressure service pump has the plunger that moves around, thus plunger with fuel from introduce chamber suction compression chamber, and in compression chamber, fuel is pressurizeed.In this high-pressure service pump, various parts, for example intake, control valve and escape cock are installed on the pump case.
But, being decided by the position that parts are set, parts can radially or along the axial of high-pressure service pump giving prominence to along high-pressure service pump.When parts were excessively outstanding from high-pressure service pump, high-pressure service pump was variable big.In addition, when parts excessively were projected into the outside of high-pressure service pump, parts just can be when installing high-pressure service pump and high-pressure service pump other parts interference on every side.Therefore, the installation of high-pressure service pump just may become very difficult.
Summary of the invention
Consider above-mentioned and other problem, an object of the present invention is to make a kind of high-pressure service pump with plunger, this high-pressure service pump along plunger axially and its radially all have a very little size.
According to an aspect of the present invention, high-pressure service pump has fuel channel and pump chamber (pump chamber).Fuel flows into pump chamber by fuel channel.High-pressure service pump comprises valve member and plunger.Valve member can be used to control the fuel quantity that flows into pump chamber by fuel channel along roughly axial axis of movement (mobile axis) motion (moving) that is positioned at valve member.Plunger can be roughly along roughly axial axis of movement (mobile axis) motion (moving) that is positioned at plunger.Plunger can be with the pressurization of the fuel in the pump chamber to discharge the fuel in the pump chamber.The axis of movement of valve member departs from the axis of movement of plunger and roughly is parallel to each other.
Alternatively, high-pressure service pump has the chamber of introducing and pump chamber.High-pressure service pump comprises plunger and valve member.Plunger partly limits pump chamber.Plunger can be roughly along the axial motion of plunger.Valve member can be roughly along the axial motion of valve member.Valve member can be communicated with pump chamber introducing the chamber, and will introduce chamber and pump chamber blocking-up.Valve member axially depart from axially and roughly being parallel to each other of plunger.
High-pressure service pump comprises introduces parts, pump case, discharge parts and plunger.Pump case has the chamber of introducing and compression chamber.Fluid is drawn into compression chamber by introducing the chamber from introducing parts.Fluid is pressurized in compression chamber.Fluid flows out from compression chamber by discharging parts.Plunger can move in pump case, is used for the pressurized with fluid with compression chamber.
In high-pressure service pump, to introduce the chamber and have the peripheral edge, it comprises the discontinuous part with respect to the circumferential setting of peripheral edge.Pump case has the space with respect to the outside that circumferentially is positioned at discontinuous part of peripheral edge.High-pressure service pump also comprises at least one parts that is contained at least in part in this space.
Alternatively, in high-pressure service pump, introduce the chamber and have recessed portion.Pump case has the space in the outside that is positioned at recessed portion.Described at least one parts are contained in this space at least in part.
Alternatively, in high-pressure service pump, introduce the chamber and have the peripheral edge, this peripheral edge comprises the circumferential straight section with respect to the peripheral edge.Pump case has the week space laterally that is positioned at straight section.Described at least one parts are contained in this space at least in part.
High-pressure service pump comprises introduces parts, pump case, discharge parts and plunger.Pump case has the chamber of introducing and compression chamber.Introducing parts is communicated with the introducing chamber.Introducing the chamber can be communicated with compression chamber.Discharging parts can be communicated with compression chamber with the outside of pump case.Plunger can move in pump case.Plunger partly limits compression chamber.
In high-pressure service pump, to introduce the chamber and have the peripheral edge, this peripheral edge extends to the second end of peripheral edge from the first end of peripheral edge.First end extends to the second end to be formed on the qualifying part that limits a space in the pump case.This space is positioned at the outside with respect to the circumferential described qualifying part of peripheral edge.High-pressure service pump also comprises at least one parts that is contained at least in part in this space.
Alternatively, in high-pressure service pump, introduce the chamber and have a plurality of peripheral edges.Each peripheral edge in described a plurality of peripheral edge has first end and the second end.In each peripheral edge in described a plurality of peripheral edges, first end extends to the second end.The first end of a peripheral edge in described a plurality of peripheral edge extends to the second end of another peripheral edge of described a plurality of peripheral edges to form qualifying part.A peripheral edge of described a plurality of peripheral edges and another peripheral edge in described a plurality of peripheral edge are along circumferentially adjacent.Qualifying part forms the space in the pump case.This space is with respect to the outside that circumferentially is positioned at qualifying part of peripheral edge.Described at least one parts are contained in this space at least in part.
Described at least one parts can comprise at least one valve in control valve and the safety valve.
Description of drawings
Reading can more be expressly understood above-mentioned and other purpose, feature and advantage of the present invention below with reference to the detailed description of accompanying drawing.Among the figure:
Fig. 1 is a side view in partial cross-section, has shown the high-pressure service pump according to first embodiment of the invention;
Fig. 2 is a side view in partial cross-section, has shown the valve portion according to first embodiment's high-pressure service pump, and this valve portion has the valve member that rests against on the valve seat member;
Fig. 3 is a side view in partial cross-section, has shown the valve portion according to first embodiment, and wherein valve member is lifted by using coiler part;
Fig. 4 is a side view in partial cross-section, has shown the high-pressure service pump according to second embodiment of the invention;
Fig. 5 is a side view in partial cross-section, has shown the high-pressure service pump according to third embodiment of the invention;
Fig. 6 is the sectional view along the line VI-VI among Fig. 5;
Fig. 7 is the sectional view along the line VII-VII among Fig. 5;
Fig. 8 is a side view in partial cross-section, has shown the safety valve according to the 3rd embodiment's high-pressure service pump;
Fig. 9 is a sectional view, has shown the high-pressure service pump according to fourth embodiment of the invention;
Figure 10 is a sectional view, has shown the high-pressure service pump according to fifth embodiment of the invention; With
Figure 11 is a side view in partial cross-section, has shown the high-pressure service pump according to sixth embodiment of the invention.
Embodiment
(first embodiment)
As shown in fig. 1, high-pressure service pump 10 is installed on the internal-combustion engine 2.For example, high-pressure service pump 10 is high voltage supply pumps.High-pressure service pump 10 will use low pressure pump supplied fuel pressurization from low pressure pump, supply fuel to thus in the sparger of motor 2.For example, motor 2 can be petrol engine or diesel engine.
High-pressure service pump (Injection Pump) 10 comprises shell 12, compression member 30, valve portion 50 and solenoid portion (electromagnet portion) 70.
For example, shell 12 comprises shell body 14, and cap 16, fuel inlet 18 and fuel outlet (not shown) are screwed on the shell body 14.Shell body 14 is formed by the magnetic material such as Ferritic Stainless Steel.Shell body 14 has the passage 20 of introducing, valve passage 22, pump chamber 24, connecting passage 25 and discharge route 26.Form path (introducing chamber) 28 between shell body 14 and the cap 16.Introducing passage 20 is gone into 18 with fuel and is communicated with.Low pressure oil is supplied to from fuel tank by fuel inlet 18 and introduces the passage 20.Path 28 will be introduced passage 20 and be communicated with valve passage 22, thus fuel be introduced the valve passage 22 from introducing passage 20.Valve passage 22 is formed on motor 2 one sides with respect to path 28.Valve passage 22 is communicated with pump chamber 24 by connecting passage 25.When valve portion 50 was opened, valve passage 22 was introduced fuel the pump chamber 24 from path 28 by connecting passage 25.Valve portion 50 is to be provided with for valve passage 22.Discharge route 26 is communicated with pump chamber 24 with the fuel outlet (not shown).Fuel pressurized in pump chamber 24 (compression), and it is discharged to sparger by discharge route 26.Fuel outlet has safety check, and when the fuel pressure in pump chamber 24 became and is equal to or greater than threshold value and is predetermined pressure, this safety check was opened.
Compression member 30 is by cylinder body 32, plunger 34, spring seat 36, piston spring 38, oil seal 40,42, tappet 44 formations such as grade.Cylinder body 32 is by high hardness material, and for example Martensitic Stain Less Steel forms.Cylinder body 32 is essentially cylindrical.For example, cylinder body 32 is fixed on the shell body 14 in the mode of drive fit (interference fit).Plunger 34 is supported by the inner circle wall of cylinder body 32, to such an extent as to roughly coaxial with cylinder body 32, axial motion back and forth when sliding thus with respect to cylinder body 32.Plunger 34 has an end face 34a who is exposed to pump chamber 24, can push the fuel that flows into pump chamber 24 thus.Plunger 34 has the other end that is positioned at a side opposite with pump chamber 24.The other end of plunger 34 is fixed on the spring seat 36.Piston spring 38 is folded between spring seat 36 and the shell body 14.Spring seat 36 elastic force by means of piston spring 38 in motor 2 is urged on cam 4 via tappet 44.Cam 4 is used as driver element.In this structure, cam 4 is converted into reciprocating force around the rotating force of spin axis R, and is passed to plunger 34 via tappet 44, to such an extent as to plunger 34 axial motion back and forth.Oil seal 40 seals between cylinder body 32 and plunger 34, stops the inside of fuel from the internal leakage of motor 2 to cylinder body 32 thus.Oil seal 42 seals between cylinder body 32 and plunger 34, stops the inside of fuel from the internal leakage of cylinder body 32 to motor 2 thus.
As shown in Fig. 1, Fig. 2, valve portion 50 is by formations such as valve seat member 52, valve guiding element 54, valve member (valve plug) 56, valve springs 58.Valve portion 50 is arranged in the valve passage 22.Valve seat member 52 is essentially cylindrical, and is screwed togather the conduit wall that enters into valve passage 22.Valve seat member 52 has an end face that is positioned at a side opposite with path 28.That is to say that this end face of valve seat member 52 is disposed in tappet 44 1 sides in the motor 2.This end face of valve seat member 52 forms seat abutment surface 60.Valve guiding element 54 is essentially cylindrical.Valve guiding element 54 engages with the conduit wall of valve passage 22 in tappet 44 1 sides with respect to valve seat member 52.The inwall of valve guiding element 54 has the otch 62 that is positioned at predetermined circumferential position.For example, valve member 56 is formed by magnetic material.Valve member 56 is for having the general cylindrical shape of bottom.Valve member 56 is arranged between stop core 64 and the valve seat member 52.Stop core 64 is parts of shell body 14.Valve member 56 is supported to coaxial basically with respect to valve guiding element 54 by the inner circle wall of valve guiding element 54, to such an extent as to valve member 56 axial motion back and forth when sliding with respect to valve guiding element 54.In this embodiment, valve member 56 has the axis of movement O that almost parallel ground departs from respect to the axis of movement P of plunger 34, to such an extent as to valve member 56 radially overlapping with pump chamber 24 (partly) along plunger 34.Spring 58 is folded between the endoporus and stop core 64 of valve member 56.Spring 58 has the elastic force that valve member 56 is pressed to a thruster opposite with stop core 64.That is to say that the elastic force of spring 58 is pressed valve member 56 to seat abutment surface 60 1 lateral deviations.
Valve seat member 52 has the inner space, as shown in Figure 2, be lifted away from downwards under the situation of an abutment surface 60 at the bottom end 56a of valve member 56, the bottom end 56a of the inner space of described valve seat member 52 by valve member 56 is communicated with the inner space of otch 62 with gap between the abutment surface 60.Therefore, from path 28 flow to the gap between the bottom end 56a of the seat abutment surface 60 of inner space by valve seat member 52 of fuel the valve passage 22, valve seat member 52 and valve member 56, the inner space and the connecting passage 25 of otch 62 is introduced in the pump chamber 24.Valve member 56 has the open side end face 56b that is resisted against on the stop core 64, to such an extent as to stop valve member 56 further to move along the direction that valve member 56 is lifted away from an abutment surface 60.Rest against at the bottom end 56a of valve member 56 under the situation on the seat abutment surface 60 of valve seat member 52, the inner space of the inner space of valve seat member 52 and otch 62 is blocked.Therefore, the fuel that flows into valve passage 22 from path 28 is blocked and flows into pump chamber 24.
In this structure of high-pressure service pump 10, the fuel quantity that flows into pump chamber 24 can be controlled by the aforesaid operations of valve member 56.
Solenoid portion 70 is made of stator core 72, Bobbin 74, coil 76, connector 78, terminal 80 etc.Stator core 72, Bobbin 74, coil 76 and connector 78 parts are arranged in the receiving bore 82 of shell body 14.In shell body 14, receiving bore 82 is formed on tappet 44 1 sides with respect to valve portion 50 and stop core 64.Receiving bore 82 is arranged in radial outside with respect to plunger 34 in shell body 14.Stator core 72 forms roughly cylindricality by the magnetic material such as iron.Stator core 72 engages the inwall of receiving bore 82 via the two ends of stator core 72.For example, Bobbin 74 becomes substantial cylindrical by resin-shaped.Bobbin 74 is engaged and is fixed on the outer wall of stator core 72.Coil 76 is made of the line such as copper cash, to such an extent as to described line twines around the periphery of described Bobbin 74.
When the electric current of external control devices control coil 76 was supplied, coil 76 produced magnetic force, thereby stator core 72 and stop core 64 are magnetized.So the end face 56b of stop core 64 and valve member 56 produces magnetic attracting force between them.This magnetic attracting force is applied on the valve member 56 as the magnetic drive power that axially moves valve member 56 towards stop core 64.
Next the operation of high-pressure service pump 10 is described.
In valve portion 50, be applied on the end face 56a of valve member 56 as the pressure of lifting power, this lifting power is lifted away from valve member 56 the seat abutment surface 60 of valve seat member 52.In addition, be applied on the end face 56b of valve member 56 as the pressure of seat by power, this rests against on the seat abutment surface 60 of valve seat member 52 valve member 56 by power.Along with cam 4 rotations, plunger 34 is to tappet 44 1 lateral movements, thereby the pressure in the pump chamber 24 reduces.In this case, lifting power and seat change by the difference of power.As a result, the seat that puts on the end face 56b leans on the summation of the elastic force of power and spring 58 to reduce with respect to the lifting power on the end face 56a that puts on valve member 56.In this case, as shown in Figure 3, valve member 56 is lifted away from an abutment surface 60 along direction downward among Fig. 3, and is resisted against on the stop core 64, to such an extent as to fuel flows into valve passage 22 from path 28.After valve member 56 is resisted against on the stop core 64, move at plunger 34 before the extreme sport position of tappet 44 1 sides, the electric current supply of coil 76 begins.So valve member 56 and stop core 64 produce magnetic attracting force between them, to such an extent as to valve member 56 is held against on the stop core 64.In this case, fuel keeps flowing into pump chamber 24.
Plunger 34 arrives the extreme sport position of tappets 44 1 sides, and subsequently, plunger 34 beginnings 24 are moved along the direction that makes progress among Fig. 1 towards pump chamber.Coil 76 keeps supply of current until a certain scheduled time, and plunger 34 is in the 24 extreme sport positions that arrive pump chamber 24 1 sides when moving along the direction that makes progress among Fig. 1 towards pump chamber therebetween.Safety valve in the fuel outlet stops fuel to be discharged in the sparger in the time period below, and promptly 24 1 lateral movements stop up to the electric current supply of coil 76 basically along the direction that makes progress Fig. 1 towards pump chamber from plunger 34 beginnings.In this case, the gap between the end face 56a of the seat abutment surface 60 of the inner space of the fuel in the pump chamber 24 by connecting passage 25, otch 62, valve seat member 52 and valve member 56, the inner space and the valve passage 22 of valve seat member 52 are discharged in the path 28.
When the electric current supply of coil 76 stopped, valve member 56 and stop core 64 stopped at and produce magnetic attracting force between them.In this case, seat is by power, and the pressure that promptly puts on the end face 56b of valve member 56 is consistent basically with fuel pressure in the pump chamber 24.This summation by the elastic force of power and spring 58 that puts on the end face 56b of valve member 56 becomes greater than lifting power, promptly puts on the pressure on the end face 56a of valve member 56.So referring to Fig. 1, valve member 56 is lifted away from stop core 64, and rests against on the abutment surface 60, to such an extent as to stop the fuel in the pump chamber 24 to be drained in the path 28.
The direction that makes progress in Fig. 1 after valve member 56 rests against on the abutment surface 60 when plunger 34 is further moved when arriving the limit of sports record position of pump chamber 24 1 sides, the fuel in the plunger 34 compression pump chambers 24.In this case, when the fuel pressure in the pump chamber 24 becomes when being equal to or greater than the setting pressure of the safety check in the fuel outlet, safety check is opened, to such an extent as to the pressurized fuel in the pump chamber 24 is discharged in the sparger.Therefore, the time period that the fuel quantity of discharge can stop by the electric current supply of regulating winding 76 from high-pressure service pump 10 is controlled.
In this embodiment, the axis of movement O of valve member 56 departs from the axis of movement P of plunger 34 substantially parallelly, to such an extent as to valve member 56 is with respect to the radial offset of plunger 34 along it.So the length of high-pressure service pump 10 can axially reducing with respect to plunger 34.In addition, the axis of movement O of valve member 56 departs from the axis of movement P of plunger 34 substantially parallelly.In this structure, valve member 56 is extending axially along plunger 34 roughly.Therefore, be approximately perpendicular to the structure that the axis of movement P of plunger 34 extends with valve member 56 therein and compare, the length of high-pressure service pump 10 radially becomes very little with respect to plunger 34.
In this embodiment, coiler part 84 is along the projection image of the axial overlapping at least valve member 56 of valve member 56.Coiler part 84 is at the projection image of the overlapping valve member 56 of the radial outside of plunger 34.In this structure, even when plunger 34 and valve portion 50 form idle space (dead space) in high-pressure service pump 10, but coiler part 84 also efficient arrangement in this idle space.Therefore, coiler part 84 can be arranged in the high-pressure service pump 10, stops high-pressure service pump 10 along the axial of plunger 34 and big along the size change radially of plunger 34 simultaneously.
In addition, plunger 34 is arranged in tappet 44 1 sides with respect to pump chamber 24.Coiler part 84 is arranged in the radial outside of plunger 34.Coiler part 84 is arranged in tappet 44 1 sides with respect to valve portion 50.In this structure, the connecting passage 25 that valve passage 22 is communicated with pump chamber 24 needn't be arranged between plunger 34 and the coiler part 84, to such an extent as to can stop high-pressure service pump 10 big along the radially change of plunger 34.In addition, coiler part 84 can be arranged in the shell body 14 with respect to the axial bias mode of valve member 56.That is to say, in shell body 14, coiler part 84 axially can axially departing from respect to valve member 56.
The terminal 80 that coiler part 84 is electrically connected with external control devices is arranged on the outer circumferential side of shell body 14 at the radial outside of plunger 34.Terminal 80 can be roughly along the radially extension of shell body 14.Therefore, terminal 80 can be removed shell body 14, stops high-pressure service pump 10 axially elongated along plunger 34 simultaneously.
In addition, in this embodiment, the central axis Q of coiler part 84 is arranged to roughly coaxial with respect to the axis of movement O of valve member 56, circumferentially roughly produces magnetic attracting force equably to such an extent as to coiler part 84 can be along valve member 56.So valve member 56 can axial motion smoothly in valve guiding element 54.
In addition, in this embodiment, valve portion 50 is arranged in the valve passage 22 in tappet 44 1 sides with respect to path 28.Coiler part 84 is arranged in tappet 44 1 sides with respect to valve passage 22 and valve portion 50.In brief, coiler part 84 is arranged in a side roughly opposite with path 28 with respect to valve passage 22 and valve portion 50.In this structure, coiler part 84 can seal with respect to path 28 and valve passage 22 very like a cork by means of the stop core 64 of shell body 14.Therefore, the manufacture cost of high-pressure service pump 10 can be reduced.
In said structure, path 28, valve passage 22 and connecting passage 25 are as fuel channel.Path 28 is as upstream passageway.
(second embodiment)
Second embodiment is first embodiment's a remodeling.As shown in Figure 4, valve member 110 has axis of movement O, and its almost parallel ground in high-pressure service pump 100 departs from the central axis Q of coiler part 120.In this structure, the projection image axial overlap coiler part 120 and the cylinder body 32 of valve member 110.Therefore, compare with the structure of high-pressure service pump 10 among first embodiment, high-pressure service pump 100 is along the radially reduced size of plunger 34.
In above-mentioned first and second embodiment, valve member 56,110 can be arranged in tappet 44 1 sides with respect to coiler part 84,120.In this structure, connecting passage 25 can be arranged between plunger 34 and the coiler part 84,120, to such an extent as to connecting passage 25 is communicated with valve passage 22 with pump chamber 24.
(the 3rd embodiment)
As shown in Fig. 5 to Fig. 8, for example, high-pressure service pump 510 is the oil pumps that supply fuel to such as in the sparger of diesel engine and petrolic internal-combustion engine.
High-pressure service pump 510 comprises housing structure (shell body) 512, cap 516, plunger 520, pipe coupling 530, control valve 540, escape cock 560, safety valve (relief valve) 570 etc.
Introduce chamber 5110 and axially be formed on a side roughly opposite with compression chamber 5120 with respect to plunger 520.Introduce the radially outward expansion of chamber 5110 along compression chamber 5120.Introduce chamber 5110 and have the peripheral edge 5112 that is positioned at a side opposite with compression chamber 5120.It is circular that peripheral edge 5112 is essentially.Introduce chamber 5110 and have the peripheral edge 5114 that is positioned at compression chamber 5,120 one sides.
As shown in Figure 6, recess 5115 is formed at the radially both sides of peripheral edge 5114.Except that recess 5115, peripheral edge 5114 is essentially arc.Recess 5115 is arranged in the radially inner side of the curved portion that the extending circumferentially of the peripheral edge 5114 except recess 5115 partly limits.That is to say that recess 5115 forms the discontinuous part (qualifying part) that these parts with respect to peripheral edge 5114 are provided with respectively with arcuate shape.Introduce chamber 5110 and have, introduce in the chamber 5110 to such an extent as to recess 5115 is formed at along its axial step 5116 (Fig. 5, Fig. 8).Recess 5115 and step 5116 are formed on introduces the recessed portion that inwardly concaves in the chamber 5110.
More particularly, referring to Fig. 6, introduce chamber 5110 and have two peripheral edges 5114.Each peripheral edge 5114 has first end 5114a and the second end 5114b.In each peripheral edge 5114, first end 5114a extends to the second end 5114b.The first end 5114a of a peripheral edge 5114 extends to the second end 5114b of another peripheral edge 5114 to limit qualifying part (discontinuous part) 5115.A peripheral edge 5114 is circumferentially adjacent with another 5114 edges, peripheral edge.Each qualifying part 5115 limits residual space 5200 in pump case 512,516.Residual space 5200 is with respect to the outside that circumferentially is positioned at qualifying part 5115 of described peripheral edge 5114.
Each recess 5115 has in shell body 512 with respect to the residual space 5200 that radially is positioned at the outside of introducing chamber 5110.Control valve 540 and safety valve 570 are arranged in the residual space 5200 in the shell body 512.Pipe coupling 530 and escape cock 560 are arranged on the place, space of shell body 512.These spaces of shell body 512 are formed at peripheral edge one side of compression chamber 5120.These spaces of shell body 512 are formed on compression chamber 5,120 one sides with respect to introducing chamber 5110.Pipe coupling 530 is as introducing parts.Escape cock 560 is as discharging parts.Safety valve 570 is arranged on along introducing circumferentially being formed in the space between pipe coupling 530 and the escape cock 560 of chamber 5110.As shown in Fig. 6, Fig. 7, pipe coupling 530, escape cock 560 and safety valve 570 are arranged in a side opposite with control valve 540 with respect to the imaginary plane 5210 of the central axis that comprises plunger 520.
Next the parts of high-pressure service pump 510 are described.High-pressure service pump 510 is installed on the shell body 512.Referring to Fig. 5, plunger 520 can to-and-fro motion in the cylinder body 514 of shell body 512.Compression chamber 5120 along the moving direction of plunger 520 be formed at one distolateral on.Plunger 520 has another the distolateral head 522 that is positioned at plunger 520 along direction downward among Fig. 5.Head 522 links to each other with spring valve seat member 524.Spring valve seat member 524 and shell body 512 insert and put spring 526 between them.The elastic force of spring 526 presses against spring valve seat member 524 on the bottom interior wall of tappet (not shown).Tappet has bottom outer wall, and it is along with cam (not shown) rotation and with respect to cam slide, to such an extent as to plunger 520 moves back and forth.
The peripheral edge that plunger 520 is positioned at head 522 1 sides seals via the inner periphery of oil seal 528 for the shell body 512 that holds plunger 520.Oil seal 528 stops fuel to infiltrate pressurizing chamber 5120 from the inside of motor.In addition, oil seal 528 stops fuel to leak in the motor from pressurizing chamber 5120.
The fuel that sliding parts between plunger 520 and cylinder body 514 leaks into oil seal 528 1 sides turns back to the introducing passage 5102 that is arranged in low voltage side by unloading channel 5122.In this structure, can stop oil seal 528 to bear the pressure of fuel under high pressure.
The solenoid 550 of control valve 540 is formed and makes central core 554 and coil 556 be embedded into to be formed in the resin part 552.The part of central core 554 and coil 556 engages with the recess 518 of shell body 512.Recess 518 centers on the peripheral edge of compression chamber 5120 and forms.Recess 518 is arranged in a side opposite with introducing chamber 5110 with respect to valve member 542.When coil 556 was supplied electric current, shell body 512 and valve member 542 produced magnetic attracting force between them.Shell body 512 is positioned at a side roughly opposite with valve seat member 548 with respect to valve member 542.
Referring to Fig. 7, escape cock 560 has body 562, and this body is screwed on the shell body 512, to such an extent as to escape cock 560 is fitted into to discharge route 5130.The body 562 of escape cock 560 has the fuel channel 5132 that holds valve member 564, spring 566 and valve seat member 568.Valve seat member 568 is arranged in compression chamber 5,120 one sides with respect to valve member 564.Spring 566 pushes valve member 564 to valve seat member 568.When the fuel pressure in the compression chamber 5120 becomes when being equal to, or greater than predetermined pressure, valve member 564 is lifted away from valve seat member 568 against the elastic force of spring 566.So the fuel in the compression chamber 5120 is discharged from from high-pressure service pump 510 after by discharge route 5130 and fuel channel 5132.The fuel of discharging from high-pressure service pump 510 is supplied in the fuel rail such as common rail of accumulating pressurized fuel therein.The fuel that is accumulated in the fuel rail is supplied in the sparger.
Referring to Fig. 6, Fig. 7, safety valve 570 is arranged in along circumferentially being formed between pipe coupling 530 and the escape cock 560 and comprising in the space in residual space 5200.In this structure, safety valve 570 is generally housed in the shell body 512.Referring to Fig. 8, the body 572 and the shell body 512 of safety valve 570 screw togather, to such an extent as to the body 572 of safety valve 570 and shell body 512 insert and put valve seat member 578 between them, thereby safety valve 570 is assembled to shell body 512.Ball 574 and spring seat 575 constitute the valve member of safety valve 570.Spring 576 pushes spring seat 575 and ball 574 to valve seat member 578.Discharge route 5134 is communicated with the downstream of the valve member 564 of escape cock 560 (Fig. 7), to such an extent as to the fuel pressure in the discharge route 5134 is applied along the direction that ball 574 is lifted away from valve seat member 578.When the fuel pressure in the downstream of valve member 564 becomes when being equal to or greater than predetermined pressure, ball 574 is lifted away from valve seat member 578 against the elastic force of spring 576, introduces in the chamber 5110 to such an extent as to fuel is discharged into from discharge route 5134.Setting pressure when the setting pressure when safety valve 570 is opened is redefined for and opens greater than escape cock 560.
Next the operation of high-pressure service pump 510 is described.
Suction stroke at first is described.The pressure in introducing chamber 5110 that is arranged in the upstream of valve member 542 is applied thereto from the upstream of valve member 542.The pressure that is arranged in the compression chamber 5120 in valve member 542 downstreams is applied thereto from the downstream of valve member 542.When plunger 520 downward pumping direction in Fig. 5 move and compression chamber 5120 in pressure when reducing, change from introducing the pressure reduction that chamber 5110 and compression chamber 5120 put on the valve member 542.In this case, seat is produced by the fuel pressure in the compression chamber 5120 by power, and the direction that rests against on the valve seat member 548 along valve member 542 is applied on the valve member 542.In addition, lifting power is lifted away from valve seat member 548 along valve member 542 direction is produced by the fuel pressure of introducing chamber 5,110 one sides.When the seat of valve member 542 became lifting power less than valve member 542 by the summation of the elastic force of power and spring 546, valve member 542 was lifted away from valve seat member 548, and abutted against the shell body 512 that is positioned at a side opposite with valve seat member 548 for valve member 542.So fuel is flowing into compression chamber 5120 after introducing chamber 5110 and introducing passage 5118.
Arrive at plunger 520 before its bottom dead center, coil 556 is supplied electric current under valve member 542 and situation that shell body 512 contacts.Therefore, the magnetic attracting force that is produced by means of coil 556 can be very little, is used to keep valve member 542 to contact to open control valve 540 with shell body 512.
Next return stroke is described.When even the compression aspect that begins to make progress along Fig. 5 from its bottom dead center when plunger 520 moves to its top dead, the also electric current supply of hold-in winding 556.In this case, magnetive attraction is applied between shell body 512 and the valve member 542, to such an extent as to valve member 542 continues to abut against shell body 512, retentive control valve 540 is opened thus.So the fuel of pressurization turns back to the introducing chamber 5110 from control valve 540 after by introducing passage 5118 in compression chamber 5120 because plunger 520 moves upward.
Next pressure stroke is described.When the electric current supply of coil 556 stopped in return stroke, coil 556 stopped to produce the magnetive attraction that puts between valve member 542 and the shell body 512.In this case, lean on the summation of the elastic force of power and spring 546 to become from compression chamber 5120 towards the seat that valve seat member 548 puts on valve member 542 greater than the lifting power that puts on from introducing chamber 5110 on the valve member 542.So valve member 542 rests against on the valve seat member 548, to such an extent as to will introduce chamber 5110 and introduce passage 5118 blocking-up.In this case, the compression aspect that makes progress in Fig. 5 when plunger 520 is when its top dead is further moved, and the fuel in the compression chamber 5120 is pressurized, thus boost pressure.When the fuel pressure in the compression chamber 5120 became greater than predetermined pressure, the valve member 564 in the escape cock 560 was lifted away from valve seat member 568 against the elastic force of the spring in escape cock 560 566, to such an extent as to escape cock 560 is opened.So the fuel of pressurization is discharged from from escape cock 560 by means of discharge route 5130 in compression chamber 5120.The fuel of discharging from escape cock 560 is supplied to the fuel rail (not shown), and is accumulated.The fuel of accumulating is supplied in the sparger.Fuel pressure in being accumulated in fuel rail becomes when being equal to or higher than predetermined pressure, and the ball 574 of safety valve 570 is lifted away from valve seat member 578.Therefore, the fuel of the fuel channel 5132 (Fig. 7) by escape cock 560 turns back to by means of discharge route 5134 (Fig. 8) and safety valve 570 and introduces in the chamber 5110.
Above-mentioned suction stroke, return stroke and pressure stroke repeat, thus high-pressure service pump 510 pump fuel.The electric current supply time of the coil 556 of control valve 540 is controlled, to such an extent as to the fuel quantity that restriction is discharged from high-pressure service pump 510.
In this embodiment, introducing chamber 5110 is recessed into to compression chamber 5,120 one sides.Be formed at a residual space 5200 in the shell body 512 and hold the valve member 542 of control valve 540.
The coil 556 of control valve 540 is disposed in the space that is positioned at a side opposite with introducing chamber 5110 for valve member 542.Coil 556 is arranged in the space of peripheral edge one side of compression chamber 5120.Control valve 540 comprises solenoid 550, so control valve 540 needs very big holding space.But in this structure, control valve 540 can be efficiently be arranged in the shell body 512 by means of the space of shell body 512.
In addition, pipe coupling 530, escape cock 560 and safety valve 570 are arranged in a side for the imaginary plane 5210 that comprises plunger 520 central axis.Control valve 540 is arranged in for imaginary plane 5210 side opposite with pipe coupling 530, escape cock 560 and safety valve 570.Each pipe coupling 530, escape cock 560 and safety valve 570 have simple structure, and therefore the installing space that needs is littler than control valve 540 needed installing spaces.In this structure, pipe coupling 530, escape cock 560 and safety valve 570 are by a unified side that is arranged on for imaginary plane 5210.Need the control valve 540 of very big installing space for imaginary plane 5210, to be arranged in opposite side because having solenoid 550.
In said structure, the space in the shell body 512 is efficiently utilized, to such an extent as to the parts of restriction high-pressure service pump 510 are outwards excessively outstanding from high-pressure service pump 510.As a result, high-pressure service pump 510 reduced sizes.
In addition, can reduce from the high-pressure service pump 510 outside excessively overhangs of outstanding parts.When high-pressure service pump 510 is installed, can stop these parts and high-pressure service pump 510 other parts on every side to be interfered mutually.Therefore, high-pressure service pump 510 can easily be installed.
(the 4th and the 5th embodiment)
Sectional view shown in Fig. 9 be along with Fig. 5 in the identical view that line obtained of line VI-VI.As shown in Figure 9, in the 4th embodiment, straight section 5117 is formed in the peripheral edge 5114 of introducing chamber 5110.This straight section 5117 is used as discontinuous part (qualifying part).Control valve 540 is arranged in the outer circumferential side of straight section 5117.
More particularly, referring to Fig. 9, introduce chamber 5110 and have the peripheral edge 5114 that extends to its second end 5114b from its first end 5114a.First end 5114a extends to the second end 5114b to form the qualifying part (discontinuous part) 5117 that limits residual space 5200.Residual space 5200 is with respect to the outside that circumferentially is positioned at qualifying part 5117 of peripheral edge 5114.
Sectional view shown in Figure 10 be along with Fig. 5 in the identical view that line obtained of line VII-VII.As shown in Figure 10, in the 5th embodiment, two straight sectioies 5117 are formed on the both sides with respect to the circumferential introducing chamber 5110 of peripheral edge 5114.Control valve 540 and safety valve 570 are arranged in the outer circumferential side of straight section 5117.
In above-mentioned the 4th and the 5th embodiment, except each straight section 5117, peripheral edge 5114 is essentially arc.Straight section 5117 is positioned at the radially inner side of curved portion, and this curved portion is by being defined along extending circumferentially peripheral edge 5114 except straight section 5117.In this structure, straight section 5117 limits the discontinuous part that is provided with respect to peripheral edge 5114.Straight section 5117 limits the recessed portion that inwardly concaves in introducing chamber 5110.
(the 6th embodiment)
As shown in Figure 11, shell body 582, cylinder body 584 and cap 516 constitute the pump case of high-pressure service pump 580.Shell body 582, cylinder body 584 and cap 516 are mutually independent.Shell body 582 is formed by Ferritic Stainless Steel.Cylinder body 584 is formed by Martensitic Stain Less Steel.
(other embodiment)
The 3rd to the 6th embodiment, control valve 540 is disposed in the residual space 5200 that is formed in the shell body as the parts of high-pressure service pump.Alternatively, in control valve 540 and safety valve 570 the residual space 5200 of arrangements of components in being formed at the shell body as high-pressure service pump.But except control valve 540 and safety valve 570, pipe coupling 530 and escape cock 560 can be arranged at least one residual space 5200.Alternatively, pipe coupling 530 and escape cock 560, rather than control valve 540 and safety valve 570 can be arranged at least one residual space 5200.
Recess can be formed at the upside of introducing the chamber or the downside of introducing the chamber, rather than is formed at the cross side of introducing the chamber.Residual space can be formed at the outside of this recess.The shape of introducing the discontinuous part in the peripheral edge in chamber can be roughly arc, when the curvature of this arc is roughly arc at least in part in the peripheral edge of discontinuous part, less than the curvature of the peripheral edge part of discontinuous part.When discontinuous part is positioned at the radially inner side of the part from the peripheral edge except discontinuous part along extending circumferentially, can produce similar effect.
The peripheral edge of introducing the chamber can be formed by straight section fully, and straight section can be defined as discontinuous part.In this case, the peripheral edge is a polygonal.
Use high-pressure service pump and the fluid of pumping is not limited to fuel.But the fluid of high-pressure service pump pumping any kind of, for example two-phase fluid of gas, steam and liquid and liquid.
Each embodiment's said structure can suitably make up.
In the above-described embodiments, sealing configuration is used in the flowmeter.But sealing configuration is not limited to be used for flowmeter.Sealing configuration can be used for any other contained structure.
Without departing from the spirit of the present invention, can change diversely various remodeling and change to the foregoing description.
Claims (56)
1, a kind of high-pressure service pump (10,100), it has fuel channel (22,25,28) and pump chamber (24), and fuel flows in the described pump chamber (24) by described fuel channel (22,25,28), and described high-pressure service pump (10,100) is characterised in that and comprises:
Valve member (56,110), it can be used for control flows into described pump chamber (24) by described fuel channel (22,25,28) fuel quantity roughly along being positioned at the axial axis of movement motion of valve member (56,110); With
Plunger (34), it can be roughly along being positioned at the axial axis of movement motion of plunger (34), and plunger (34) can be with the pressurization of the fuel in the described pump chamber (24) to discharge the fuel in the described pump chamber (24);
Wherein, the axis of movement of described valve member (56,110) departs from the axis of movement of described plunger (34) and roughly is parallel to each other.
2, high-pressure service pump according to claim 1 (10,100) is characterized in that also comprising:
Coiler part (84,120), its in shell (12) roughly along coiler part (84,120) axially depart from described valve member (56,110), described coiler part (84,120) can be handled described valve member (56,110); With
Terminal (80), it can be electrically connected described coiler part (84,120) with external control devices, and described external control devices is controlled the electric current supply of described coiler part (84,120);
Wherein, described terminal (80) is arranged in the outer circumferential side of described shell (12).
3, high-pressure service pump according to claim 1 (10,100), it is characterized in that, the projection image of the overlapping at least in part described valve member of described coiler part (84,120) (56,110), projection image the extending axially of described valve member (56,110) along described valve member (56,110); And
Coiler part (84,120) can be roughly moves axially described valve member (56,110) along described valve member (56,110).
According to claim 2 or 3 described high-pressure service pumps (10,100), it is characterized in that 4, described coiler part (84,120) is along the radial arrangement of described plunger (34) outside in plunger (34).
5, according to claim 2 or 3 described high-pressure service pumps (10,100), it is characterized in that also comprising:
Tappet (44), its driving force with internal-combustion engine (2) is delivered to plunger (34);
Wherein said plunger (34) is arranged in tappet (44) one sides with respect to described pump chamber (24); And
Described coiler part (84,120) is arranged in tappet (44) one sides with respect to valve member (56,110).
According to claim 2 or 3 described high-pressure service pumps (10,100), it is characterized in that 6, described coiler part (84,120) has the central axis (Q) roughly coaxial with respect to the axis of movement (O) of described valve member (56,110).
According to claim 2 or 3 described high-pressure service pumps (10,100), it is characterized in that 7, described coiler part (84,120) has the central axis (Q) of the axis of movement (O) that departs from described valve member (56,110).
According to claim 2 or 3 described high-pressure service pumps (10,100), it is characterized in that 8, described fuel channel (22,25,28) has the upstream passageway (28) of the upstream side that is positioned at described valve member (56,110); And
Described coiler part (84,120) is arranged in a side opposite with described upstream passageway (28) with respect to described valve member (56,110).
9, a kind of high-pressure service pump (10,100), it has introducing chamber (28) and pump chamber (24), and described high-pressure service pump (10,100) is characterised in that and comprises:
Plunger (34), it partly limits described pump chamber (24), described plunger (34) can be roughly along the axial motion of plunger (34); With
Valve member (56,110), it can be roughly along the axial motion of valve member (56,110), and described valve member (56,110) can be communicated with described introducing chamber (28) with described pump chamber (24), and can be with described introducing chamber (28) and described pump chamber (24) blocking-up;
Wherein, described valve member (56,110) axially departs from axially and roughly being parallel to each other of described plunger (34).
According to arbitrary described high-pressure service pump (10,100) in claim 1 to 3 and the claim 9, it is characterized in that 10, described valve member (56,110) is extending axially along described plunger (34) roughly.
11, a kind of high-pressure service pump (510) is characterized in that comprising:
Introduce parts (530);
Have the pump case (512,516) of introducing chamber (5110) and compression chamber (5120), fluid is drawn into the described compression chamber (5120) from described introducing parts (530) by described introducing chamber (5110), and fluid is pressurized in described compression chamber (5120);
Discharge parts (560), fluid flows out from described compression chamber (5120) by described discharge parts; With
Plunger (520), it can move in described pump case (512,516), is used for the pressurized with fluid with described compression chamber (5120);
Wherein, described introducing chamber (5110) has peripheral edge (5114), and described peripheral edge (5114) comprise with respect to the discontinuous part of the circumferential setting of described peripheral edge (5115,5117); And
Described pump case (512,516) has the space (5200) with respect to the outside of the described discontinuous part of circumferentially being positioned at of described peripheral edge (5114) (5115,5117);
Described high-pressure service pump (510) also comprises:
Be contained at least one parts (540,570) in the described space (5200) at least in part.
12, high-pressure service pump according to claim 11 (510) is characterized in that, described discontinuous part (5115,5117) is straight section (5117).
13, high-pressure service pump according to claim 12 (510) is characterized in that, described straight section (5117) roughly extends to another end of described peripheral edge (5114) point-blank from an end of described peripheral edge (5114).
According to arbitrary described high-pressure service pump (510) in the claim 11 to 13, it is characterized in that 14, described introducing chamber (5110) is arranged in a side roughly opposite with described plunger (520) with respect to described compression chamber (5120); And
Described introducing chamber (5110) is along the radially outward expansion of described compression chamber (5120).
15, high-pressure service pump according to claim 14 (510) is characterized in that, described space (5200) are arranged in described compression chamber (5120) one sides with respect to described introducing chamber (5110).
16, according to arbitrary described high-pressure service pump (510) in the claim 11 to 13, it is characterized in that, described at least one parts (540) comprise control valve (540), it can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560).
17, high-pressure service pump according to claim 16 (510) is characterized in that, described control valve (540) comprises valve member (542) and coil (556);
Described valve member (542) is contained in the described space (5200) at least in part;
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and can be with described introducing chamber (5110) and described compression chamber (5120) blocking-up;
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542);
Described coil (556) is arranged in a side roughly opposite with described introducing chamber (5110) with respect to described valve member (542); And
Described coil (556) is with respect to the outside that radially is arranged on described compression chamber (5120) of described compression chamber (5120).
According to arbitrary described high-pressure service pump (510) in the claim 11 to 13, it is characterized in that 18, described at least one parts (570) comprise safety valve (570), this safety valve is controlled the fluid downstream pressure of described discharge parts (560).
According to claim 14 or 15 described high-pressure service pumps (510), it is characterized in that 19, described introducing parts (530) and described discharge parts (560) are arranged in compression chamber (5120) one sides with respect to described introducing chamber (5110).
20, high-pressure service pump according to claim 19 (510) is characterized in that, described at least one parts (570) comprise safety valve (570), and this safety valve is controlled the fluid downstream pressure of described discharge parts (560); And
Described safety valve (570) along circumferential arrangement between described introducing parts (530) and described discharge parts (560).
21, high-pressure service pump according to claim 20 (510) is characterized in that, described at least one parts (540) comprise control valve (540), and this control valve comprises valve member (542) and coil (556);
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560);
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542); And
Described control valve (540) is arranged in described introducing parts (530), discharges parts (a 560) side roughly opposite with safety valve (570) with respect to the imaginary plane (210) of the central axis that comprises described plunger (520).
According to arbitrary described high-pressure service pump (510) in the claim 11 to 13, it is characterized in that 22, described space (5200) are with respect to the outside that radially is positioned at described discontinuous part (5115,5117) of described pump case (512,516).
According to arbitrary described high-pressure service pump (510) in the claim 11 to 13, it is characterized in that 23, the peripheral edge (5114) in described introducing chamber (5110) is roughly along the extending circumferentially except the peripheral edge part of described discontinuous part (5115,5117).
24, a kind of high-pressure service pump (510) is characterized in that comprising:
Introduce parts (530);
Have the pump case (512,516) of introducing chamber (5110) and compression chamber (5120), fluid is drawn into the described compression chamber (5120) from described introducing parts (530) by described introducing chamber (5110), and fluid is pressurized in described compression chamber (5120);
Discharge parts (560), fluid is discharged parts by this and is flowed out from described compression chamber (5120); With
Plunger (520), it can move in described pump case (512,516), is used for the pressurized with fluid with described compression chamber (5120);
Wherein, described introducing chamber (5110) has recessed portion (5115,5116); And
Described pump case (512,516) has the space (5200) in the outside that is positioned at the female part (5115,5116);
Described high-pressure service pump (510) also comprises:
Be contained at least one parts (540,570) in the described space (5200) at least in part.
25, high-pressure service pump according to claim 24 (510);
Wherein, described introducing chamber (5110) is arranged in a side roughly opposite with described plunger (520) with respect to described compression chamber (5120); And
Described introducing chamber (5110) is along the radially outward expansion of described compression chamber (5120).
26, high-pressure service pump according to claim 25 (510) is characterized in that, described space (5200) are arranged in described compression chamber (5120) one sides with respect to described introducing chamber (5110).
27, according to arbitrary described high-pressure service pump (510) in the claim 24 to 26, it is characterized in that, described at least one parts (540) comprise control valve (540), this control valve can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560).
28, high-pressure service pump according to claim 27 (510) is characterized in that, described control valve (540) comprises valve member (542) and coil (556);
Described valve member (542) is contained in the described space (5200) at least in part;
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and can be with described introducing chamber (5110) and described compression chamber (5120) blocking-up;
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542);
Described coil (556) is arranged in a side roughly opposite with described introducing chamber (5110) with respect to described valve member (542); And
Described coil (556) is with respect to the radial arrangement of described compression chamber (5120) outside in described compression chamber (5120).
According to arbitrary described high-pressure service pump (510) in the claim 24 to 26, it is characterized in that 29, described at least one parts (570) comprise safety valve (570), this safety valve is controlled the fluid downstream pressure of described discharge parts (560).
According to claim 25 or 26 described high-pressure service pumps (510), it is characterized in that 30, described introducing parts (530) and described discharge parts (560) are arranged in described compression chamber (5120) one sides with respect to described introducing chamber (5110).
31, high-pressure service pump according to claim 30 (510) is characterized in that, described at least one parts (570) comprise safety valve (570), and this safety valve is controlled the fluid downstream pressure of described discharge parts (560); And
Described safety valve (570) along circumferential arrangement between described introducing parts (530) and described discharge parts (560).
32, high-pressure service pump according to claim 31 (510) is characterized in that, described at least one parts (540) comprise control valve (540), and this control valve comprises valve member (542) and coil (556);
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560);
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542); And
Described control valve (540) is arranged in described introducing parts (530), discharges parts (a 560) side roughly opposite with safety valve (570) with respect to the imaginary plane (210) of the central axis that comprises described plunger (520).
33, according to arbitrary described high-pressure service pump (510) in the claim 24 to 26, it is characterized in that, described introducing chamber (5110) has peripheral edge (5114), and this peripheral edge comprises the discontinuous part (5115,5117) that is provided with respect to described peripheral edge (5114); And
Described space (5200) is with respect to the outside of the described discontinuous part of circumferentially being positioned at of described peripheral edge (5114) (5115,5117).
34, high-pressure service pump according to claim 33 (510) is characterized in that, described space (5200) are with respect to the outside that radially is positioned at described discontinuous part (5115,5117) of described pump case (512,516).
35, high-pressure service pump according to claim 33 (510) is characterized in that, the peripheral edge (5114) in described introducing chamber (5110) is roughly along the extending circumferentially of the peripheral edge part except described discontinuous part (5115,5117).
36, high-pressure service pump according to claim 33 (510), it is characterized in that, described discontinuous part (5117) is straight section (5117), and this straight section roughly extends to another end of described peripheral edge (5114) point-blank from an end of described peripheral edge (5114).
37, a kind of high-pressure service pump (510) is characterized in that comprising:
Introduce parts (530);
Have the pump case (512,516) of introducing chamber (5110) and compression chamber (5120), fluid is drawn into the described compression chamber (5120) from described introducing parts (530) by described introducing chamber (5110), and fluid is pressurized in described compression chamber (5120);
Discharge parts (560), fluid is discharged parts by this and is flowed out from described compression chamber (5120); With
Plunger (520), it can move in pump case (512,516), is used for the pressurized with fluid with described compression chamber (5120);
Wherein, described introducing chamber (5110) has peripheral edge (5114), and this peripheral edge comprises the straight section (5117) with respect to the circumferential setting of described peripheral edge (5114); And
Described pump case (512,516) has the week space (5200) laterally that is positioned at straight section (5117);
Described high-pressure service pump (510) also comprises:
Be contained at least one parts (540,570) in the described space (5200) at least in part.
According to the described high-pressure service pump of claim 37 (510), it is characterized in that 38, described introducing chamber (5110) is arranged in a side roughly opposite with described plunger (520) with respect to described compression chamber (5120); And
Described introducing chamber (5110) is along the radially outward expansion of described compression chamber (5120).
According to the described high-pressure service pump of claim 38 (510), it is characterized in that 39, described space (5200) are arranged in described compression chamber (5120) one sides with respect to described introducing chamber (5110).
40, according to arbitrary described high-pressure service pump (510) in the claim 37 to 39, it is characterized in that, described at least one parts (540) comprise control valve (540), this control valve can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560).
According to the described high-pressure service pump of claim 40 (510), it is characterized in that 41, described control valve (540) comprises valve member (542) and coil (556);
Described valve member (542) is contained in the described space (5200) at least in part;
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and can be with described introducing chamber (5110) and described compression chamber (5120) blocking-up;
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542);
Described coil (556) is arranged in a side roughly opposite with described introducing chamber (5110) with respect to described valve member (542); And
Described coil (556) is with respect to the radial arrangement of described compression chamber (5120) outside in described compression chamber (5120).
According to arbitrary described high-pressure service pump (510) in the claim 37 to 39, it is characterized in that 42, described at least one parts (570) comprise safety valve (570), this safety valve is controlled the fluid downstream pressure of described discharge parts (560).
According to claim 38 or 39 described high-pressure service pumps (510), it is characterized in that 43, described introducing parts (530) and described discharge parts (560) are arranged in described compression chamber (5120) one sides with respect to described introducing chamber (5110).
According to the described high-pressure service pump of claim 43 (510), it is characterized in that 44, at least one parts (570) comprise safety valve (570), parts (560) fluid downstream pressure is discharged in this safety valve control; And
Described safety valve (570) is along circumferentially being arranged between described introducing parts (530) and the described discharge parts (560).
According to the described high-pressure service pump of claim 44 (510), it is characterized in that 45, described at least one parts (540) comprise control valve (540), this control valve comprises valve member (542) and coil (556);
Described valve member (542) can be communicated with described introducing chamber (5110) with described compression chamber (5120), and described introducing chamber (5110) and described compression chamber (5120) blocking-up can be used for the Fluid Volume that control is flowed out from described discharge parts (560);
Described coil (556) can produce the magnetic attracting force that is used to handle described valve member (542); And
Described control valve (540) is arranged in described introducing parts (530), discharges parts (a 560) side roughly opposite with safety valve (570) with respect to the imaginary plane (210) of the central axis that comprises described plunger (520).
According to arbitrary described high-pressure service pump (510) in the claim 37 to 39, it is characterized in that 46, described space (5200) are with respect to the radial arrangement of described pump case (512, the 516) outside in described discontinuous part (5115,5117).
According to arbitrary described high-pressure service pump (510) in the claim 37 to 39, it is characterized in that 47, the peripheral edge (5114) in described introducing chamber (5110) is roughly along the extending circumferentially of the peripheral edge part except described straight section (5117).
According to arbitrary described high-pressure service pump (510) in the claim 37 to 39, it is characterized in that 48, described straight section (5117) roughly extends to another end of described peripheral edge (5114) point-blank from an end of described peripheral edge (5114).
49, a kind of high-pressure service pump (510) is characterized in that comprising:
Introduce parts (530);
Have the pump case (512,516) of introducing chamber (5110) and compression chamber (5120), described introducing parts (530) are communicated with described introducing chamber (5110), and described introducing chamber (5110) can be communicated with compression chamber (5120);
Discharge parts (560), it can be communicated with the outside of described compression chamber (5120) with described pump case (512,516); With
Plunger (520), it can move in described pump case (512,516), and described plunger (520) partly limits described compression chamber (5120);
Wherein, described introducing chamber (5110) has peripheral edge (5114), and this peripheral edge extends to the second end (5114b) of described peripheral edge (5114) from the first end (5114a) of described peripheral edge (5114);
Described first end (5114a) extends to described the second end (5114b) to be formed on the qualifying part (5115,5117) that limits space (5200) in the described pump case (512,516), and described space (5200) are with respect to the outside that circumferentially is positioned at described qualifying part (5115,5117) of described peripheral edge (5114);
Described high-pressure service pump (510) also comprises:
Be contained at least one parts (540,570) in the described space (5200) at least in part.
50, according to the described high-pressure service pump of claim 49 (510), it is characterized in that, described qualifying part (5115,5117) is straight section (5117), and this straight section roughly extends to the second end (5114b) of described peripheral edge (5114) point-blank from the first end (5114a) of described peripheral edge (5114).
According to the described high-pressure service pump of claim 49 (510), it is characterized in that 51, described qualifying part (5115,5117) is the discontinuous part (5115) of extending along the track that is roughly arc.
According to arbitrary described high-pressure service pump (510) in the claim 49 to 51, it is characterized in that 52, described at least one parts (540,570) comprise at least one valve in control valve (540) and the safety valve (570).
53, a kind of high-pressure service pump (510) is characterized in that comprising:
Introduce parts (530);
Have the pump case (512,516) of introducing chamber (5110) and compression chamber (5120), described introducing parts (530) are communicated with described introducing chamber (5110), and described introducing chamber (5110) can be communicated with described compression chamber (5120);
Discharge parts (560), it can be communicated with the outside of described compression chamber (5120) with described pump case (512,516); With
Plunger (520), it can move in described pump case (512,516), and described plunger (520) partly limits described compression chamber (5120);
Wherein, described introducing chamber (5110) has a plurality of peripheral edges (5114), each peripheral edge in described a plurality of peripheral edge (5114) has first end (5114a) and the second end (5114b), in each peripheral edge of described a plurality of peripheral edges (5114), described first end (5114a) extends to described the second end (5114b);
The second end (5114b) that the first end (5114a) of a peripheral edge in described a plurality of peripheral edge (5114) extends to another peripheral edge in described a plurality of peripheral edge (5114) is to form qualifying part (5115,5117), and a peripheral edge in described a plurality of peripheral edges (5114) is circumferentially adjacent with another edge, peripheral edge in described a plurality of peripheral edge (5114);
Described qualifying part (5115,5117) limits the space (5200) in the described pump case (512,516), and this space (5200) are with respect to the outside that circumferentially is positioned at described qualifying part (5115,5117) of described peripheral edge (5114);
Described high-pressure service pump (510) also comprises:
Be contained at least one parts (540,570) in the described space (5200) at least in part.
54, according to the described high-pressure service pump of claim 53 (510), it is characterized in that, described qualifying part (5115,5117) is straight section (5117), and this straight section roughly extends to the second end (5114b) of described peripheral edge (5114) point-blank from the first end (5114a) of described peripheral edge (5114).
According to the described high-pressure service pump of claim 53 (510), it is characterized in that 55, qualifying part (5115,5117) is the discontinuous part (5115) of extending along the track that is roughly arc.
According to arbitrary described high-pressure service pump (510) in the claim 53 to 55, it is characterized in that 56, described at least one parts (540,570) comprise at least one valve in control valve (540) and the safety valve (570).
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP009020/2005 | 2005-01-17 | ||
| JP2005009020A JP4221760B2 (en) | 2005-01-17 | 2005-01-17 | High pressure fuel pump |
| JP020925/2005 | 2005-01-28 | ||
| JP2005020925A JP4453015B2 (en) | 2005-01-28 | 2005-01-28 | High pressure fuel pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1807871A true CN1807871A (en) | 2006-07-26 |
| CN100425823C CN100425823C (en) | 2008-10-15 |
Family
ID=36800485
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100054651A Active CN100425823C (en) | 2005-01-17 | 2006-01-17 | High pressure pump having downsized structure |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4221760B2 (en) |
| CN (1) | CN100425823C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105492756A (en) * | 2013-08-30 | 2016-04-13 | 罗伯特·博世有限公司 | Pump, in particular a high-pressure fuel pump |
| CN105888906A (en) * | 2008-10-28 | 2016-08-24 | 罗伯特·博世有限公司 | Fuel high-pressure pump for internal combustion engine |
| CN107850027A (en) * | 2015-08-10 | 2018-03-27 | 大陆汽车有限公司 | High-pressure fuel pump |
| CN109196212A (en) * | 2017-01-20 | 2019-01-11 | 斯坦蒂内有限责任公司 | Direct magnetic control inlet valve for fuel pump |
| CN112334647A (en) * | 2018-07-27 | 2021-02-05 | 日立汽车系统株式会社 | Fuel pump |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5178676B2 (en) * | 2009-09-29 | 2013-04-10 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
| JP2012158990A (en) * | 2011-01-28 | 2012-08-23 | Denso Corp | High-pressure pump |
| JP6221410B2 (en) | 2013-06-27 | 2017-11-01 | トヨタ自動車株式会社 | High pressure fuel pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6027312A (en) * | 1997-10-29 | 2000-02-22 | Stanadyne Automotive Corp. | Hydraulic pressure supply pump with simultaneous directly actuated plungers |
| DE19834121A1 (en) * | 1998-07-29 | 2000-02-03 | Bosch Gmbh Robert | Fuel supply system of an internal combustion engine |
| JP3465641B2 (en) * | 1999-07-28 | 2003-11-10 | トヨタ自動車株式会社 | Fuel pump control device |
| JP2001041128A (en) * | 1999-07-28 | 2001-02-13 | Toyota Motor Corp | High pressure fuel pump |
-
2005
- 2005-01-17 JP JP2005009020A patent/JP4221760B2/en not_active Expired - Fee Related
-
2006
- 2006-01-17 CN CNB2006100054651A patent/CN100425823C/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105888906A (en) * | 2008-10-28 | 2016-08-24 | 罗伯特·博世有限公司 | Fuel high-pressure pump for internal combustion engine |
| CN105492756A (en) * | 2013-08-30 | 2016-04-13 | 罗伯特·博世有限公司 | Pump, in particular a high-pressure fuel pump |
| CN105492756B (en) * | 2013-08-30 | 2019-03-08 | 罗伯特·博世有限公司 | Pump, especially high-pressure fuel pump |
| CN107850027A (en) * | 2015-08-10 | 2018-03-27 | 大陆汽车有限公司 | High-pressure fuel pump |
| CN107850027B (en) * | 2015-08-10 | 2020-09-15 | 大陆汽车有限公司 | High-pressure fuel pump |
| US10900451B2 (en) | 2015-08-10 | 2021-01-26 | Vitesco Technologies GmbH | High-pressure fuel pump |
| CN109196212A (en) * | 2017-01-20 | 2019-01-11 | 斯坦蒂内有限责任公司 | Direct magnetic control inlet valve for fuel pump |
| CN109196212B (en) * | 2017-01-20 | 2021-02-09 | 斯坦蒂内有限责任公司 | Direct magnetically controlled inlet valve for fuel pump |
| CN112334647A (en) * | 2018-07-27 | 2021-02-05 | 日立汽车系统株式会社 | Fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006194218A (en) | 2006-07-27 |
| CN100425823C (en) | 2008-10-15 |
| JP4221760B2 (en) | 2009-02-12 |
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