CN108730087A - Liquid pump for inhibiting cavitation - Google Patents
Liquid pump for inhibiting cavitation Download PDFInfo
- Publication number
- CN108730087A CN108730087A CN201810330906.8A CN201810330906A CN108730087A CN 108730087 A CN108730087 A CN 108730087A CN 201810330906 A CN201810330906 A CN 201810330906A CN 108730087 A CN108730087 A CN 108730087A
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- Prior art keywords
- valve
- outlet
- entrance
- pump
- group
- Prior art date
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- Granted
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- 239000007788 liquid Substances 0.000 title claims abstract description 41
- 230000002401 inhibitory effect Effects 0.000 title abstract 2
- 239000012530 fluid Substances 0.000 claims description 55
- 230000004087 circulation Effects 0.000 claims description 41
- 238000005086 pumping Methods 0.000 claims description 12
- 239000004744 fabric Substances 0.000 claims description 5
- 230000000750 progressive effect Effects 0.000 claims description 5
- 230000008859 change Effects 0.000 claims description 2
- 238000004891 communication Methods 0.000 claims description 2
- 239000000446 fuel Substances 0.000 abstract description 13
- 238000009826 distribution Methods 0.000 abstract description 5
- 238000013461 design Methods 0.000 description 10
- 230000000903 blocking effect Effects 0.000 description 7
- 230000001629 suppression Effects 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 230000003628 erosive effect Effects 0.000 description 3
- BVPWJMCABCPUQY-UHFFFAOYSA-N 4-amino-5-chloro-2-methoxy-N-[1-(phenylmethyl)-4-piperidinyl]benzamide Chemical compound COC1=CC(N)=C(Cl)C=C1C(=O)NC1CCN(CC=2C=CC=CC=2)CC1 BVPWJMCABCPUQY-UHFFFAOYSA-N 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000002829 reductive effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/022—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type having an accumulator storing pressurised fuel during pumping stroke of the piston for subsequent delivery to the injector
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/464—Inlet valves of the check valve type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0452—Distribution members, e.g. valves
- F04B1/0456—Cylindrical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
- F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
- F04B1/0538—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units located side-by-side
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
- F04B49/03—Stopping, starting, unloading or idling control by means of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/16—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps characterised by having multi-stage compression of fuel
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
A liquid pump usable with a fuel system, such as a common rail fuel system, includes a valve assembly having a valve block with an axial alignment member, a dead volume, and vapor distribution flow passages for inhibiting cavitation. The inlet valve meters the flow of liquid into the pump for pressurization by a plurality of reciprocating plungers operated by a rotating camshaft.
Description
Technical field
This invention relates generally to the entrance metering liquid pumps with the control output via entrance throttle, and more
More particularly to the entrance metering liquid pump with the valve group for being designed as suppression cavitation.
Background of invention
In a kind of pressure liquid pump, is throttled and controlled from the defeated of pump to entrance by using electric controlled metering valve
Go out.Therefore, when the output of pump, which is controlled below pump plunger, moves back and forth volume be discharged every time, it just will produce cavitation
Bubble.A kind of application of such pump is in fuel system, which adds guide rail using common rail and high pressure fuel pump
Pressure.In the particular instance, engine direct-driven pump, and controlled by changing entrance circulating area via throttle valve
Output from pump.
When circulating area is decreased to plunger cavity by entrance throttle, cavitation bubble may be generated near throttle valve, or
Cavitation bubble is potentially generated elsewhere, which advances to plunger cavity, occupies and is generated by the plunger for the pump that bounces back
Partial volume.When cavitation bubble ruptures near surface, it may occur however that cavitation corrasion.In some examples, cavitation corrasion can
Undesirable position can be happened at, near such as access road or valve seat.The position occurred according to cavitation damage and damage journey
Degree, the performance of pump can be damaged, and may more importantly be that eroded particles can find the way into fuel injector
Diameter, this may cause more serious problem.
The United States Patent (USP) 8,202,064B2 for authorizing Tian et al. is related to the entrance section with the feature for avoiding cavitation from damaging
Flow control liquid valve.A kind of what Tian et al. proposed that valve member from passive inlet non-return valve extends have special shape and
The cavitation circulation adjuster of size.By encourage cavitation bubble far from skin breakage in a manner of, one kind significantly being formd by valve
Circulation pattern can lead to the unacceptable cavitation damage to pump.Although Tian et al. seems to provide to the prior art
It improves, other research and development for being related to suppression cavitation in the field of business are also popular.
Invention content
In one aspect, include valve body for the valve module of liquid pump, fluid inlet and fluid are formed in valve body
Outlet.Valve body includes forming the valve group of entrance valve seat and outlet valve seat, and entrance valve seat and outlet valve seat each fluid
Ground is located between fluid inlet and fluid outlet.Inlet non-return valve is positioned as being at least partially situated in valve group, and can be with
It is moved between the closed position and open position of blocking entrance valve seat.Outlet non-return valve is positioned as being at least partially situated at valve
In group, and it can be moved between the closed position and open position of blocking outlet valve seat.Plunger can in retracted position and
It is moved in valve body between progressive position.Inlet non-return valve, outlet non-return valve and plunger are limited to be shared by what valve group extended
Axis, and inlet non-return valve is axially located between outlet non-return valve and plunger.Valve body further reception formed therein that
The outlet plenum in entrance cavity and valve group in the pump chamber of plunger, valve group.Each center in pump chamber, entrance cavity and outlet plenum
On shared axis.Valve module further comprises the stream for the shifting pump liquor charging body between fluid inlet and fluid outlet
Circulation passage.Multiple circulation passages are disposed in the first parallel group extended between entrance cavity and pump chamber and with around altogether
There is the first circumferentially distributed of axis, and in the second parallel group extended between entrance cavity and outlet plenum and with surrounding
The second of shared axis is circumferentially distributed.
On the other hand, include entrance member for the valve group of liquid pump, it is formed therein that have entrance valve seat, fluid inlet
And extend between fluid inlet and entrance valve seat multiple into fluid channel.Valve group further comprises being positioned at entrance member
The first side on outlet member and fluid outlet, be formed with outlet valve seat in the outlet member.Valve seat further comprises positioning
Pump in the second side of entrance member, makes entrance member be clipped between pump and outlet member, and includes being positioned as at least
Part is located at the inlet non-return valve in entrance member.Inlet non-return valve can be in the closed position of blocking entrance valve seat and open position
It is moved between setting.Valve group further comprises being positioned as being at least partially disposed at the outlet non-return valve in outlet member, and can be
It is moved between the closed position and open position of blocking outlet valve seat.Entrance member, outlet member and pump, which limit, shares axis.Enter
It can be moved along the shared axis between corresponded closed positions and open position each of in mouth check-valves and outlet non-return valve
It is dynamic.Valve seat be further formed outlet plenum between the entrance cavity between entrance member and pump, entrance member and outlet member, pump chamber and
Multiple circulation passages.Multiple circulation passages are disposed in the first parallel group extended between entrance cavity and pump chamber and have
First around shared axis is circumferentially distributed, and in the second parallel group extended between entrance cavity and outlet plenum and has
Have circumferentially distributed around share axis second.
In another aspect, liquid pump includes pump case and entrance metering valve, pump intake and pump are formed in pump case
Outlet.Valve module is positioned in pump case, and includes the valve body with the valve group for forming entrance valve seat and outlet valve seat.
Liquid pump further comprises inlet non-return valve, which is positioned as being at least partially disposed in valve group and can hindering
It is moved between the closed position and open position of gear entrance valve seat.Outlet non-return valve is positioned as being at least partially disposed in valve group simultaneously
And it can be moved between the closed position and open position of blocking outlet valve seat.Plunger can be in retracted position and advanced potential
It is moved in valve body between setting.Inlet non-return valve, outlet non-return valve and plunger limit the shared axis extended through valve group,
And inlet non-return valve is axially located between outlet non-return valve and plunger.The further reception plunger formed therein that of valve body
Pump chamber, the outlet plenum in entrance cavity and valve group in valve group, and the center of pump chamber, entrance cavity and outlet plenum is all shared
On axis.Liquid pump further comprises for multiple circulation passages by valve group shifting pump liquor charging body, multiple circulation passage
It is disposed in the first parallel group extended between entrance cavity and pump chamber and with around share axis first circumferential point
In cloth, and the second parallel group for extending between entrance cavity and outlet plenum and with around the second circumferential of shared axis
Distribution.
Description of the drawings
Fig. 1 is the side cross-sectional view of liquid pump in the liquid system according to one embodiment；
Fig. 2 is the end cross-section by liquid pump shown in Fig. 1；
Fig. 3 is the side cross-sectional view by a part for the liquid pump of Fig. 1 and 2；
Fig. 4 is the sectional view on multiple sectional planes by a part for the liquid pump of Fig. 1-3；
Fig. 5 is the sectional view on a sectional plane similar with Fig. 4；
Fig. 6 is the axial end view of entrance member in the valve group according to one embodiment；And
Fig. 7 is the axial, cross-sectional view by entrance member.
Specific implementation mode
Referring to Fig.1, liquid system 10 is shown, such as the fuel system of internal combustion engine.Liquid system 10 is (hereinafter referred to as
" system 10 ") may include reservoir 12 to contain pressurized fluid, such as it is configured to contain pressurized fluid and to multiple streams
Body transmitting device or fuel injector 13 supply (hereinafter referred to as " common rails 12 ") such as the common rails of pressurized fluid.Liquid system 10 can
It to include fuel system, is configured to directly spray compression ignition diesel engine, for example, each wherein in fuel injector 13
All it is positioned as being at least partially situated in cylinder.For example, common rail 12 may include single hole, elongated pressure vessel,
Or the multiple individual fluid accumulators being linked together with so-called daisy chain arrangement or other configurations.System 10 further includes liquid
Body supplies, such as fuel tank 14, and connection has the low-voltage transmission pump 16 of fuel tank 14, and is configured to through inlet valve 18
By fuel transmission to pressure liquid pump 20.Inlet valve 18 may include that can adjust to change the circulating area to liquid pump 20
Entrance throttle.The variation of circulating area is metered into the The fuel stream of pump 20, so that pump 20 is only to required fuel quantity
Pressurization, to keep or realize desired Fluid pressure in common rail 12.
Those skilled in the art will be familiar with the concept of entrance metering pump under current context.Inlet valve 18 can be pump 20
A part is simultaneously pumping in 20, or is potentially fluidly located at the upstream of the pump case 22 of pump 20.Altogether from above-mentioned Tian et al.
With known a kind of for the appropriately designed of inlet valve 18 in the United States Patent (USP) 8,202,064B2 that possesses, although the present invention not because
This is restricted.Those skilled in the art will also be familiar with and the relevant cavitation phenomenon of entrance metering pump.It will in the following description
It is more obvious, the structure of pump 20 can be designed with suppression cavitation according to multiple design concepts, multiple design
Concept can be used together or be used independently of each other.Design concept includes but not limited to firm symmetrical Machine Design, group
Divide positioning and arrangement, distribution of steam, the hydraulic pressure hardness of reduction and the tendency of production and/or damages relative insensitivity towards cavitation
Liquid pump inner region vapor bubbles rupture.
Pump 20 includes the rotatable camshaft 24 for being positioned as being at least partially disposed in pump case 22, and is configured to one
As conventional mode rotated by engine drive mechanism (not shown).The rotation of camshaft 24 leads to multiple pumping mechanisms 26
Reciprocating motion, each in generally conventional manner be equipped with for plunger 78 cam follower 28.Multiple pump machanisms 26
In each to shared Fluid pressure space 30 (hereinafter referred to " space 30 ") supply pressurized fluid, and thereafter by pumping
The pump discharge 34 formed on shell 22 supplies pressurized fluid to common rail 12.Pump discharge 32 can be formed in pump case 22, and
And fuel is supplied with the flow velocity determined according to the circulating area of inlet valve 18 described herein.
In the shown embodiment, pump case 22 includes multiple housing components, that is, limits the first shell in space 30 and pump discharge 34
Body part 36, second shell part 38 and the third housing component 39 for wherein placing multiple pump machanisms 26.It should be appreciated that including multiple shells
The various different housings structures in the path of the quantity and design of body part, the quantity of pump machanism and various pipeline features can with it is shown
It is different.In addition it is possible to use 34 He of check valve and/or pump discharge between additional valve, such as transmission pump 16 and inlet valve 18
Check valve between common rail 12, but omitted in Fig. 1 for clarity of illustration.Fig. 2 shows relative to camshaft 24
Axial end view, it can thus be seen that the rotation of camshaft 24 causes shown pump machanism 26 to pump, by liquid
Suction pump 20 and space 30 is filled with to 12 supply pressurized fluid body of common rail.In illustrated embodiment two pump machanisms 26 it is usual that
This is out of phase moved back and forth, such as poor with the out-phase of 180 degree.
Pump 20 further comprises valve module associated with each pump machanism 26 40.It should be appreciated that any odd number herein
Component or component explanation, such as valve module 40 or pump machanism 26, it is intended that similarly censure for pumping 20 or imagining herein
Any other such component of other embodiment.Valve module 40 includes the valve body 42 being positioned in pump case 22.Referring again to
Fig. 3, valve body 42 has the fluid inlet 44 formed in it, with another fluid formed by the valve group 60 of valve body 42
Entrance 46 is connected to.Valve body 42 further comprises the fluid outlet 48 equally formed by valve group 60.In the described embodiment, valve
Group 60 further includes entrance member 62, formed therein that have entrance valve seat 64, fluid inlet 46 and in fluid inlet 46 and entrance valve seat
What is extended between 64 is multiple into fluid channel 66.Valve group 60 further includes the outlet member being positioned on the first side of entrance member 62
68.Valve seat 70 and fluid outlet 48 are formed in outlet member 68.Pump 72 is positioned in the second side of entrance member 62, to
So that entrance member 62 is clipped between pump 72 and outlet member 68.
Connection has the inlet non-return valve 74 of bias spring 75 to be positioned as being at least partially situated in valve 60 and at least partly
Ground is located in entrance member 62.Inlet non-return valve 74 can overcome the biasing force of bias spring 75 in blocking entrance valve seat 64
Closed position and the open position for not stopping entrance valve seat 64 between move.Outlet associated with bias spring 77 non-return
Valve 76 is positioned as being at least partially disposed in outlet member 68, and in the closed position of blocking outlet valve seat 70 and can not stop
It is moved between the open position of outlet valve seat 70.Plunger 78 can be moved in valve body 42 between retracted position and progressive position
It is dynamic, to by various other fluid channels of fluid inlet 46 and pump 20 with connect liquid from the sucking valve group of pump intake 32
60, and to liquid pressing and space 30 is transmitted it to be sprayed to common rail transmission 12 to cylinder.
It should be appreciated that in the case where inlet valve 18 is restricted to the entrance circulating area of pump 20, inhaled by retraction plunger 78
Entering liquid will tend to cause the fluid pressure drop of liquid to the pressure and hereinafter, these gas of liquid formation vapor bubbles
Bubble is bound to rupture to pressurize.The rupture of these bubbles can be associated with the generation of high speed micro jet flow of liquid,
The high speed micro jet flow can impinge upon on the surface in pump to cause the cavitation for substantially corroding the material for forming surface to damage
Evil.According to the present invention, although cavitation phenomenon still can occur during the operation of pump 20, the serious of cavitation phenomenon is damaged
Degree expection can reduce, and will tend to the region of pump in terms of position, and the region is far from the table sensitive to erosion damage
Face.
Entrance member 62, outlet member 68 and pump 72, which limit, shares axis 80.Inlet non-return valve 74,76 and of outlet non-return valve
In plunger 78 each can along between corresponded closed positions and open position or in the example of plunger 78 in retracted position and
It is moved between shared axis 80 between progressive position.It has been found that will substantially axisymmetric zero as in valve group 60
Part, which is arranged as almost coaxial, can have multiple advantageous effects, including the improved symmetry and consistency of liquid flow, matching connect
Touch part hardness to avoid relative motion thus reduce or avoid ability that fine motion during use damages and part at any time
Between the relative uniformity that deforms.For example, " seat is driven into " phenomenon known in the art can be expected to compared to it is optional design and
It says and occurs in relatively uniform pattern.It is further noted that being axially sandwiched between outlet member 68 and pump 72
Inlet non-return valve 74 can be axially positioned between plunger 78 and outlet non-return valve 76 by entrance member 62.Moreover, cloth as shown
Setting valve can make outlet non-return valve 76 or near it quantity of steam reduce, and specifically, wherein inlet non-return valve 74 is in sky
Between and hydraulic pressure on it is arranged in sequence, and outlet non-return valve 76 is in the axial direction far from plunger 78.In the shown embodiment, enter
Mouth valve seat 64 includes flat seat, and outlet valve seat 70 includes cone seat, and the center of each of which is all on shared axis 20.Under
Text further discusses relationship and cavitation phenomenon between above and other design feature.
It is further noted that in the shown embodiment, valve body 42 is including between outer valve body 50 and is positioned at
Plug-in unit 52 in 50 between outer valve body.Plug-in unit 52 limits centre bore 54 with part 50 and forms the annular sky of fluid inlet 44 together
Between.Herein, term " fluid inlet " and " inlet annular space " can be replaced mutually.Plug-in unit 52 further comprises
Formation with its in multiple ingates 56, extend between fluid inlet or inlet annular space 44 and centre bore 54.Enter
Oral pore 56 is generally radially extending, and is supplying access road 58 axially extending in entrance member 62.During valve seat 60 is located at
In heart hole 54, so that inlet annular space 44 is in fluid communication with the fluid inlet 46 in ingate 56 and entrance member 62.
Multiple fluid channels 66 that enter in entrance member 62 extend radially inwardly to access road 58 from fluid inlet 46.
As it appears from the above, liquid pump 20 and particularly valve group 60 are configured to the hydraulic pressure hardness reduced, following article is into one
Step description, the rate of pressure rise of relative time or " dp/dt " during pumping or pressurization stroke can be reduced.For this purpose, valve group 60
It is further formed at the entrance cavity 82 between entrance member 62 and pump 72, the outlet plenum between entrance member 62 and outlet member 68
84 and the pump chamber 86 between pump 72 and plug-in unit 52.As shown in figure 3, plunger 78 can be in the traveling for limiting swept volume
It is moved in distance 100.In one embodiment, plunger 78 limits swept volume, and described along multiple circulations
Entrance cavity 82, outlet plenum 84 and the pump chamber 86 in channel 90 limit the combined volume more than swept volume.Combined volume can be work
Make the about twice of volume to about three times, and more specifically can be about 2.1 times of swept volume.Because dead volume can lead to
Crossing certain measures reduces the efficiency of pumps, so in described range, efficiency and flattening pressure rise with suppression cavitation and only
Degree reaches balance between sacrificing efficiency, although the present invention is not limited thereto.
Valve group 60 also forms multiple circulation passages 90.It is round each of in circulation passage 90, is disposed in entrance cavity 82
In the first parallel group 92 extended between pump chamber 86 and with the first circumferentially distributed, Yi Ji around shared axis 80
In the second parallel group 94 extended between entrance 82 and outlet plenum 86 and with around share axis 80 second circumferential point
Cloth.The circulating area formed by the first parallel group 92 can be less than the circulating area formed by inlet check valve seat 64.At one
In embodiment, circulating area can reduce about 50% coefficient.It has been observed that providing the downstream of bigger during filling
Circulating area can make the generation of vapor bubbles be biased to pump chamber 82 rather than be biased to valve seat or other regions, so that steam
The rupture of bubble is less intractable or more manageability.
Referring once again to Fig. 4,5,6 and 7, in one embodiment, circulation passage 90 in the first parallel group 92 it is total
Number is equal to the sum of circulation passage 90 in the second parallel group 94.As can be seen that every in the first parallel group 92 and the second parallel group 94
A circulation passage 90 has the distribution of consistent size, shape and rule.Each circulation passage 90 is also positioned as distance and shares axis
The consistent radial distance of line 80.Circulation passage 90 may be located on entrance cavity 82, outlet plenum 84 and pump chamber in group 92 and group 94
In 86 space envelopes limited.Circulation passage 90 in first group 92 can have with the circulation passage 90 of group 94 around shared
The interlaced arrangement of axis 20.The sum of each circulation passage 90 can be eight in group 92 and group 94.
Industrial applicibility
It will be understood by those skilled in the art that according to definition, all entrance metering pumps will have steam to generate, and steam
Necessarily rupture is so that pressure rises and begins pumping liquid.In general, minimum in order to be obtained in entrance metering pump
Or zero corrode, bubble must rupture under sufficiently low energy level, be high enough to so that bubbles burst does not generate energy
To the hurtful injection stream in surface.When regional breakdown of the bubble in elevated ambient pressures, bubbles burst energy tends to partially
It is high.Pressure comparatively quickly rises under steam pressure can cause bubble to be trapped in high environment far above steam pressure
The region of pressure.Therefore, when these vapor bubbles rupture, there may be problem and cavitation damage is generated.At least exist
When pumping starts, comparatively faster pump rate and relatively large plunger can be associated with relatively large dp/dt.
As noted previously, as reducing the fluid modulus of dp/dt, dead volume can lead to smaller system hardness.This
Outside, circulation passage 90 uniform and it is consistent be distributed, identical shape and identical size lead to stream by circulation passage 90
Body pumping minimally generates recirculation zone, whirlpool or can other uneven or non-laminar flow streams associated with cavitation.Stream
The sum of circulation passage is eight, round, and distance shares the radial distance of axis 80 unanimously and surrounds shared axis 80 uniformly circumferentially
Distribution, these are considered so that liquid is intended as the whole row relatively consistently moved during the pumping action of pump 20
It is dynamic.In addition, circulation passage be distributed, that size is consistent, arrangement is uniform and shape is consistent is distributed steam, so that without one
The special damage that a some areas have been broken by bubble.The smaller stream for opening entrance valve seat 64 of circulation passage 90
Logical region can also the deviation of position that generates of auxiliary steam and/or rupture towards pump chamber 86, and thus avoid crucial valve
Rupture on seat or structure hot spot.These and other methods described herein can maximize the potential life-span of pump, even if certain
The erosion of a little background levels is inevitable.
Moreover, as it appears from the above, substantially axisymmetric part axially stacked is so that hardness is matched, thus is minimized
The relative motion on the sealing surface of matching component and reduce or eliminate fretting wear.In the high pressure and high circulation ring of pump 20
In border, symmetrical centre valve tends to unevenly deform around 360 degree of seat, ensures even related in small break-in or clast
Stabilized seal is also kept after abrasion.It has been observed that ensureing stabilized seal, especially going out in such as outlet non-return valve 76
In mouth valve or delivery valve, limitation is contributed to corrode.Seat leakage between pumping events can generate it is altitude it is several under high speed
Stream, and vapor bubbles cause these streams to be ruptured when next pumping events start and cause erosion to damage near leakage seat
Evil.
Inlet non-return valve 74 is axially located provided between the top of pump chamber 86 and outlet non-return valve component 76 into
The circulation path of one step suppression cavitation.In certain being related to earlier, the vapor bubbles of formation can be tracked to from prime mover
Farthest position, the prime mover are usually delivery valve.In the case where no this paper carries the design code of the known phenomenon,
Vapor bubbles may rupture in the position.It is contemplated that entrance valve seat 64 may include flat seat, for intended size
The generation of valve minimizes circulating area.Such design can cause or reinforce the downstream limitation to target valve seat, and not
It realizes and seals dependent on knife-edge, this so that the design is more elastic for clast damage.
The purpose that this specification is merely to illustrate, is not construed in any way as limiting the scope of the present invention.Cause
This, it will be appreciated by those skilled in the art that can be right without departing substantially from whole and zone of reasonableness and spirit of the invention
Disclosed embodiment makes various modifications.When examining attached drawing and attached claims, other aspect, feature and
Advantage will be apparent.As used herein, article "an" intention includes one or more objects, and can be with " one
Or multiple " be used interchangeably.When being intended to censure only one object, term "one" or similar language are used.Similarly,
As used herein, the intentions such as term " having " are construed to open-ended term.In addition, unless clearly otherwise indicated, otherwise " base
In " word expression " being based at least partially on ".
Claims (10)
1. a kind of valve module for liquid pump, including：
Valve body has fluid inlet and fluid outlet formed therein that, and includes forming entrance valve seat and outlet valve seat
Valve group, the entrance valve seat and the outlet valve seat be respectively fluidly located in the fluid inlet and the fluid outlet it
Between；
Inlet non-return valve, is positioned as being at least partially disposed in the valve group and can be in the close stance for stopping the entrance valve seat
It sets and is moved between open position；
Outlet non-return valve, is positioned as being at least partially disposed in the valve group and can be in the close stance for stopping the outlet valve seat
It sets and is moved between open position；
Plunger moves in the valve body that can be between retracted position and progressive position；
The inlet non-return valve, the outlet non-return valve and the plunger limit the shared axis extended through the valve group, and
And the inlet non-return valve is axially located between the outlet non-return valve and the plunger；
Valve body, it is further formed therein that have the pump chamber, the entrance cavity in the valve group and the valve group for receiving the plunger
Interior outlet plenum, and center each in the pump chamber, the entrance cavity and the outlet plenum is on the shared axis；
And
Multiple circulation passages are disposed in institute for transfer pumping fluid between said fluid inlet and said fluid outlet
It states in the first parallel group extended between entrance cavity and the pump chamber and with surround the shared axis first circumferential point
In cloth, and the second parallel group for extending between the entrance cavity and the outlet plenum and with surrounding the shared axis
It is second circumferentially distributed.
2. valve module according to claim 1, wherein the sum of circulation passage described in first parallel group is equal to institute
State the sum of circulation passage described in the second parallel group, and it is wherein described first it is circumferentially distributed with described second it is circumferentially distributed not
Together, so that first parallel group and second parallel group have the interlaced arrangement around the shared axis；And
The circulating area wherein formed by first parallel group is less than the circulating area formed by the inlet check valve seat.
3. valve module according to claim 2, wherein the plunger limits swept volume, and it is the entrance cavity, described
Outlet plenum, the pump chamber and the multiple circulation passage limit the combined volume more than the swept volume；
The wherein described combined volume is about 2 times to about 3 times of the swept volume；And
The sum of each circulation passage is eight in wherein described first parallel group and second parallel group, and wherein basis
Correspondence first apart from the consistent radial distance of the shared axis is circumferentially distributed or second is circumferentially distributed, is evenly distributed described
It is each in one parallel group and second parallel group.
4. valve module according to claim 1, wherein the valve body further comprises Outer casing member and limits centre bore
Plug-in unit, and the plug-in unit forms inlet annular space and with being formed in multiple entrances in it together with the outer housing
Hole, and the multiple ingate extends between the inlet annular space and the centre bore, and the wherein described valve seat
So that the fluid inlet is in fluid communication with the multiple ingate in the centre bore；And
The wherein described valve seat includes entrance member, outlet member and pump, and the entrance member has from the fluid inlet radially-inwardly
What is extended is multiple into fluid channel, wherein the entrance cavity is partly limited by the entrance member and partly by the pump
It limits, the outlet plenum is partly limited by the entrance member and partly limited by the outlet member, and the pump chamber portion
Ground is divided to be limited by the pump and partly limited by the plug-in unit.
5. a kind of valve group for liquid pump, including：
Entrance member, it is formed therein that have entrance valve seat, fluid inlet and prolong between the fluid inlet and the entrance valve seat
That stretches is multiple into fluid channel；
Outlet member is positioned on the first side of the entrance member, and the outlet member is formed therein that have outlet valve seat and fluid to go out
Mouthful；
Pump is positioned in the second side of the entrance member, so that the entrance member is clipped in the pump and the outlet
Between part；
Inlet non-return valve, is positioned as being at least partially disposed in the entrance member and can be in the closing for stopping the entrance valve seat
It is moved between position and open position；
Outlet non-return valve, is positioned as being at least partially disposed in the outlet member and can be in the closing for stopping the outlet valve seat
It is moved between position and open position；
The entrance member, the outlet member and the pump limit and share axis, and the inlet non-return valve and the outlet
It can each be moved between the corresponded closed positions and open position along the shared axis in check-valves；
The valve seat is further formed entrance cavity, the entrance member and the outlet between the entrance member and the pump
Outlet plenum, pump chamber between part and multiple circulation passages；And
The multiple circulation passage is disposed in the first parallel group extended between the entrance cavity and the pump chamber and has
Have flat around the first circumferentially distributed of the shared axis, and second extended between the entrance cavity and the outlet plenum
It is in row group and circumferentially distributed with surround the shared axis second.
6. valve group according to claim 5, wherein by the circulating area that first parallel group is formed be less than by it is described enter
The circulating area that mouth non-return valve seat is formed；
The sum of the circulation passage in wherein described first parallel group is equal to the circulation passage in second parallel group
Sum；And
Each it is positioned as the radial distance consistent from the shared axis in wherein the multiple circulation passage, by the entrance
In the space envelope that chamber, the outlet plenum and the pump chamber limit, and the circulation wherein in first parallel group
Channel is in interlaced arrangement around the shared axis with the circulation passage in second parallel group.
7. valve group according to claim 5, wherein the inlet valve seat includes flat seat, and residing outlet valve seat includes circle
Conical seat, and center each in the entrance valve seat and the outlet valve seat is on the shared axis.
8. a kind of liquid pump, including：
Pump case has pump intake and pump discharge formed therein that；
Entrance metering valve is configured to change the circulating area of the pump intake；
Valve module in the pump case, and includes the valve body with the valve group for forming entrance valve seat and outlet valve seat；
Inlet non-return valve, is positioned as being at least partially disposed in the valve group and can be in the close stance for stopping the entrance valve seat
It sets and is moved between open position；
Outlet non-return valve, is positioned as being at least partially disposed in the valve group and can be in the close stance for stopping the outlet valve seat
It sets and is moved between open position；
Plunger moves in the valve body that can be between retracted position and progressive position；
The inlet non-return valve, the outlet non-return valve and the plunger limit the shared axis extended through the valve group, and
And the inlet non-return valve is axially located between the outlet non-return valve and the plunger；
The valve body, it is further formed therein that have the pump chamber for receiving the plunger, the entrance cavity in the valve group and described
Outlet plenum in valve group, and the center of the pump chamber, the entrance cavity and the outlet plenum is all on the shared axis；With
And
Multiple circulation passages, for by the valve group shifting pump liquor charging body, be disposed in the entrance cavity and the pump chamber it
Between in the first parallel group for extending and with around the first circumferentially distributed of the shared axis, and in the entrance cavity and
It is in the second parallel group extended between the outlet plenum and circumferentially distributed with surround the shared axis second.
9. liquid pump according to claim 8 further comprises second valve group essentially identical with first valve module
Part, and further comprise that connection has the first cam follower of the plunger of first valve module and connection to have described the
Second cam follower of the plunger of two valve modules；
The wherein described pump case shared Fluid pressure space formed therein that, in first valve module and second valve module
Each is fluidly located between the shared Fluid pressure space and the pump intake；And
The wherein described plunger limits swept volume, and the entrance cavity, the outlet plenum, the pump chamber and the multiple circulation
Channel limits about 2 times to about 3 times of combined volume of the swept volume.
10. liquid pump according to claim 5, wherein stream each in first parallel group and second parallel group
The sum of circulation passage is eight, and wherein according to circumferential point of the correspondence first apart from the consistent radial distance of the shared axis
Cloth is second circumferentially distributed, is evenly distributed in first parallel group and second parallel group each；And
The circulating area wherein formed by first parallel group is less than the circulating area formed by the inlet check valve seat.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201762488975P | 2017-04-24 | 2017-04-24 | |
| US62/488975 | 2017-04-24 | ||
| US15/642300 | 2017-07-05 | ||
| US15/642,300 US10557446B2 (en) | 2017-04-24 | 2017-07-05 | Liquid pump with cavitation mitigation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108730087A true CN108730087A (en) | 2018-11-02 |
| CN108730087B CN108730087B (en) | 2022-05-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810330906.8A Active CN108730087B (en) | 2017-04-24 | 2018-04-13 | Liquid pump for inhibiting cavitation |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN108730087B (en) |
| DE (1) | DE102018109618A1 (en) |
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| Publication number | Publication date |
|---|---|
| DE102018109618A1 (en) | 2018-10-25 |
| CN108730087B (en) | 2022-05-27 |
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