CN202250266U - Lubricant control valve of turbocharger - Google Patents

Abstract

The utility model relates to a valve for a turbocharger. The valve comprises valve bodies between a liquid inlet, a throttle outlet and a bypass outlet, wherein the valve body is divided into a throttling component that is mounted in a throttling valve body to adjust the flow speed of the liquid, and a bypass valve body for distributing the throttle liquid of the throttling component with pressure released and further releasing the pressure of the throttle liquid; the throttling valve body is matched with the bypass valve body, thus the pressure of the liquid from the liquid outlet of the throttling valve can meet the requirement in the work of following components. The lubricant control valve provided by the utility model solves the problems due to single operation on the throttling valve and the bypass valve, and combines the advantages of the two valves to effectively reduces the liquid pressure in the oil channel, as well as providing enough flow rate of the liquid to meet the requirement in the work of following components; the valve has simple structure, small volume, and is convenient to mount.

Description

A kind of lubricant oil control valve of turbosupercharger

Technical field

The utility model relates to the technical field of turbosupercharger, is specifically related to a kind of lubricant oil control valve of turbosupercharger, relates in particular to the valve that is positioned at the turbosupercharger filler opening that is used on the petrol engine.

Background technique

Turbosupercharger is used for diesel engine at first, uses motor after the turbosupercharger to have power per liter height, rate of fuel consumption is low, blowdown is less characteristics.Be in high rotating speed, the condition of high temperature during in view of turbocharger operation, floating bearing or rolling bearing structure that turbosupercharger adopts must give lubricated fully and cooling.Therefore, giving sufficient lubricant oil is absolutely necessary.In the limited middle shell-space of the ten minutes of turbosupercharger, will do sealing configuration, prevent leakage of oil, except the reliability of reinforcement sealing structure, the restriction input pressure often plays conclusive effect to its leakproof.The lubricant oil input pressure of diesel engine generally is lower than 0.4-0.5Mpa, so the lubricant oil of diesel engine can directly send into turbosupercharger and be lubricated, and can ensure that turbosupercharger is oil-proof.

Be save design or purchase cost; Often above-mentioned use for diesel engine turbosupercharger is assemblied on the petrol engine in the existing technology and uses, but because petrolic lubricant oil input pressure is generally 0.7-0.8MPa, so when petrolic lubricant oil oil pipe directly linked to each other with turbosupercharger; When 0.7-0.8MPa the lubricant oil of pressure just flow into turbosupercharger; Because the pressure of this lubricant oil is excessive, general pressurized machine bearing internal clearance is 0.03-0.04mm, and external series gap is 0.07-0.08mm; The sealing mechanism that has slotted simultaneously, this just causes oil leakage phenomenon multiple.Especially the coking phenomenon that causes in the leakage of oil of turbine temperature end is more general, and this has shortened the working life of turbosupercharger.Therefore, it is just necessary that the lubricant oil that flows to pressurized machine is carried out step-down, makes the input pressure of lubricant oil be lower than the generation that 0.4-0.5Mpa just can effectively stop oil leakage phenomenon.

With regard to present technical specifications, prevent the pressurized machine leakage of oil, the simplest method is the restriction input pressure.By-pass method: promptly flow back to fuel tank to unnecessary lubricant oil through bypass valve.Its shortcoming be a large amount of lubricant oil by bypass, with the lubricant oil consumption that reduces motor itself, can cause motor for want of lubricant oil cause the damage of moving link.Flow limit method: promptly dwindle the oil inlet hole area, let lubricant oil lose to reach hypotensive effect through the aperture pressure drag.Through calculate and experiment showed, when oil inlet hole when φ 4mm is reduced to φ 0.6mm, just can make oil pressure drop to 0.4MPa from 0.7MPa.Though this structure is simple, also brings side effect, unavoidably has booty because of keeping away in the lubricant oil.The booty particle diameter that has is greater than 0.6mm, and oil inlet hole φ 0.6mm is easy to blocked like this.In case the pressurized machine oil starvation, bearing is quick-wearing very, and its consequence is very serious, thus throttling pore can not open too little.

The model utility content

The technical problem that the utility model solves provides a kind of use for diesel engine turbosupercharger being assemblied in when using on the petrol engine; Be suitable for overcoming the leakage of oil defective of turbosupercharger, and the lubricant oil control valve of the turbosupercharger that can guarantee simultaneously the lubricant oil of petrol engine and turbosupercharger is supplied with.

For solving the technical problem of above-mentioned solution, the utility model provides a kind of lubricant oil control valve of turbosupercharger, and it comprises: throttle valve body and bypass valve body, and the output stream of throttle valve body is connected with the bypass of bypass valve body inlet; The internal diameter of the throttling passage in the throttle valve body is 0.8-1.2mm; When the lubricating oil pressure of input throttle valve body was 0.7-0.8MPa, the lubricating oil pressure of exporting from the throttle valve body was lower than 0.4-0.5Mpa.

Said throttle valve body also comprises: input, output stream, said throttling passage are serially connected with between this input, the output stream; The sectional area of this throttling passage is less than the sectional area of said input, output stream; The inlet of said input stream is connected with the inlet of throttle valve body, and the outlet of said output stream is the outlet of throttle valve body; Said bypass valve body comprises: with the bypass flow path that said bypass inlet is connected, on this bypass flow path, be provided with the mangetic core assembly of the fluid flow that is used to regulate this bypass flow path.

Said bypass flow path comprises: first, second bypass flow path that intersection is communicated with, and first bypass flow path is a funnel shape path, and the bottom port of this funnel shape path is said bypass inlet, and the end port of second bypass flow path is the bypass outlet of said bypass valve body; Said mangetic core assembly comprises: be located at the ball at the horn mouth place of said funnel shape path, be positioned at the pressure spring that is used for the regulated fluid flow of this ball outboard end, the outboard end of this pressure spring is provided with the adjusting screw of the pressure that is used to regulate said pressure spring; During use, regulate ball and said bell-mouthed gap through the pressure of regulating said pressure spring, with control flow rate.

The technique effect that the utlity model has: (1) is assemblied in use and oil tight purpose on the petrol engine for realizing with the use for diesel engine turbosupercharger; The utility model has increased a restrictor by-pass valve, i.e. lubricant oil control valve on the lubricating oil inlet of turbosupercharger; Throttle valve body wherein is used for throttling, to guarantee the lubricant oil supply to petrol engine and turbosupercharger simultaneously; The bypass valve body is used for step-down, and when making the lubricating oil pressure of importing the throttle valve body be 0.7-0.8MPa, the lubricating oil pressure of exporting from the throttle valve body is lower than 0.4-0.5Mpa; Thereby realized the use for diesel engine turbosupercharger is assemblied in use and oil tight purpose on the petrol engine; Wherein, the internal diameter of the throttling passage in the throttle valve body is 0.8-1.2mm, when can guarantee appropriate flow, prevents its obstruction; (2) the bypass oil spilling of said bypass valve body is sent into turbosupercharger through said bypassing reflux stream mouth, with the cooling turbine pressurized machine, so alternative cooling water; This valve arrangement is simple, and volume is little, is convenient to install.On the turbosupercharger of models such as the lubricant oil control valve of the utility model is applied to 3360, K03, K04, played the effect of step-down leakproof.

Description of drawings

For the content that makes the utility model is more clearly understood, below basis specific embodiment and combine accompanying drawing, the utility model is done further detailed explanation, wherein

The structural representation of the lubricant oil control valve of the turbosupercharger of Fig. 1 the utility model.

The turbosupercharger of the said valve of application of Fig. 2 the utility model, mark 23 are the intermediate assembly of turbosupercharger 19.

The another kind of turbosupercharger of the said valve of application of Fig. 3 the utility model.

Embodiment

Below in conjunction with accompanying drawing and embodiment the utility model is elaborated:

(embodiment 1)

Like Fig. 1, the lubricant oil control valve of the turbosupercharger of present embodiment comprises: throttle valve body 4 and bypass valve body 5, and the output stream 8 of throttle valve body 4 is connected with the bypass of bypass valve body 5 inlet 10; The internal diameter of the throttling passage 6 in the throttle valve body 4 is 0.8-1.2mm, preferred 1mm; When the lubricating oil pressure of input throttle valve body 4 was 0.7-0.8MPa, under throttle valve body 4 and 5 actings in conjunction of bypass valve body, the lubricating oil pressure of exporting from throttle valve body 4 was lower than 0.4-0.5Mpa.

Said throttle valve body 4 also comprises: the input, output stream 7,8, said throttling passage 6 be serially connected with this input, output stream 7, between 8; The sectional area of this throttling passage 6 is less than the sectional area of said input, output stream 7,8; The inlet of said input stream 7 is connected with the inlet 1 of throttle valve body 4, and the outlet of said output stream 8 is the outlet 2 of throttle valve body 4; Said bypass valve body 5 comprises: with the bypass flow path that said bypass inlet 10 is connected, on this bypass flow path, be provided with the mangetic core assembly 9 of the fluid flow that is used to regulate this bypass flow path.

Said bypass flow path comprises: first, second bypass flow path 11,12 that intersection is communicated with; First bypass flow path 11 is a funnel shape path; The bottom port of this funnel shape path is that the end port of said bypass inlet 10, the second bypass flow path 12 is the bypass outlet 3 of said bypass valve body 5; Said mangetic core assembly 9 comprises: the ball 13 of being located at the horn mouth place of said funnel shape path; Be positioned at the pressure spring that is used for the regulated fluid flow 14 of these ball 13 outboard ends, the outboard end of this pressure spring is provided with the adjusting screw 15 of the pressure that is used to regulate said pressure spring 14; During use, regulate ball 13 and said bell-mouthed gap through the pressure of regulating said pressure spring 14, with control flow rate.

Throttling passage 6 is suitable for the flow velocity of regulated fluid, and convection cell carries out step-down; Bypass valve body 5 and throttle valve body 4 cooperatings carry out the part shunting through 9 pairs of mangetic core assemblies in this bypass valve body 5 through the fluid after throttling passage 6 throttlings, with to the further step-down of this fluid.

Said fluid inflow entrance adopts threaded coupling or flange-interface.

Can be known the scope basis of said throttling passage 6 internal diameter values by fluid mechanics: two laws of fluid mass conservation (equation of continuity) and energy conservation (Bernoulli's equation) combine to obtain in the closed conduct;

The conservation of mass: fluid flows in the pipeline of a sealing, and when running into throttling element, its quality is constant before and after throttling element, is expressed as with equation of continuity:

V ₀×A ₀×ρ＝V ₁×A ₁×ρ

Fluid is perfect liquid (liquid is incompressible, and density equates):

V ₀×A ₀＝V ₁×A ₁

V ₀Be the rate of flow of fluid of the input stream 7 before the throttling passage 6, V ₁Be the rate of flow of fluid in the throttling passage 6, A ₀Be sectional area in the pipe of input stream 7, A ₁Sectional area in the pipe of throttling passage 6.

Energy conservation: represent following relation is arranged for the pressure and the flow velocity of fluid in the closed conduct that throttling passage 6 is installed with Bernoulli's equation:

$\frac{P_0}{\mathrm{\&rho;}}+\frac{{V_0}^2}{2}=\frac{{\mathrm{<figure-callout\; id="1"\; label="P"\; filenames="HDA0000098904540000011.png,HDA0000098904540000021.png"\; state="\{\{state\}\}">P</figure-callout>}}_1}{\mathrm{\&rho;}}+\frac{{{\mathrm{<figure-callout\; id="1"\; label="V"\; filenames="HDA0000098904540000011.png,HDA0000098904540000021.png"\; state="\{\{state\}\}">V</figure-callout>}}_1}^2}{2}$

P ₀Be the hydrodynamic pressure of the input stream 7 at throttling passage 6 upper reaches, P ₁Be the hydrodynamic pressure of the output stream 8 in throttling passage 6 downstream, ρ is a fluid density.In actual test process; The hydrodynamic pressure of throttling passage 6 internal diameters can't accurately be measured because of internal diameter is too small; The hydrodynamic pressure that can judge output stream 8 according to fluid mass conservation (equation of continuity) and energy conservation (Bernoulli's equation) is very approaching with the hydrodynamic pressure of throttling passage 6 internal diameters, so here with the hydrodynamic pressure of hydrodynamic pressure replacement throttling passage 6 internal diameters of output stream 8.

Combine to obtain the pressure loss formula of fluid by above-mentioned fluid mass conservation (equation of continuity) and two laws of energy conservation (Bernoulli's equation) through throttling passage 6 downstream:

$\mathrm{\&Delta;P}=P_0[1-{\left(\frac{d_1}{d_0}\right)}^K]$

In the formula: the pressure drop of Δ P fluid after small holes; Δ P=P ₀-P ₁d ₀Be the diameter of said input stream 7, d ₁Be the internal diameter of throttling passage 6, K is the shrinkage coefficient and the K=0.12-0.13 of throttling passage 6, and K gets intermediate value 0.125.

Calculate the internal diameter of throttling passage 6 or be arranged in the pressure of exporting stream 8 throttling fluids through said pressure loss formula.

According to said formula:

When pressure drop Δ P=0.10Mpa, known P ₀=0.7Mpa, d ₀=4mm then calculates d ₁=1.2mm;

When pressure drop Δ P=0.11Mpa, known P ₀=0.7Mpa, d ₀=4mm then calculates d ₁=1.0mm;

When pressure drop Δ P=0.13Mpa, known P ₀=0.7Mpa, d ₀=4mm then calculates d ₁=0.8mm;

When pressure drop Δ P=0.15Mpa, known P ₀=0.7Mpa, d ₀=4mm then calculates d ₁=0.6mm;

Can obtain from calculated data, as the known P of input stream pressure ₀=0.7Mpa, d ₀=4mm; The inside diameter ranges 0.6mm-1.2mm of throttling passage 6 all can produce pressure drop, and the internal diameter of pressure drop size and throttling passage 6 is inversely prroportional relationship, though the pressure drop that throttling passage 6 hole internal diameter 0.6mm produce maximum; But stopped up by booty easily because internal diameter is too small; So in order to overcome this shortcoming that throttling passage 6 is blocked easily, so be selected in 0.8-1.2mm to inside diameter ranges, the first-selected 1.0mm of present embodiment.

Table 1 connects the lubricant oil control valve of present embodiment with the lubricant oil filler opening of 3360 turbosupercharger, lubrication pressure test record (30 ℃ of oil temperature)

Can find out from above-mentioned table 1 test data:

A, along with P ₀Raising, throttling reduction effect is bigger, P is at 0.05-0.12Mpa for the pressure drop range delta;

B, use throttling passage 6 step-downs of internal diameter as 1.0mm, the maximum 0.12Mpa that can descend.According to the calculating of above-mentioned pressure loss formula, internal diameter is 1.0mm, P ₀=0.7Mpa, d ₀During=4mm, pressure drop Δ P=0.11Mpa, error is within the range of permission; This shows; The calculated data that the span 0.12-0.13 of the shrinkage coefficient K of throttling passage 6, K get intermediate value 0.125 is consistent with experimental result, has also proved the correctness of said pressure loss formula.

C, when the pressure of bypass valve body 5 transfers to 0.4Mpa; Can further reduce oil pressure; The pressure that makes the outlet 2 of throttling valve body 4 is 0.5Mpa; This outlet 2 links to each other with the lubricating oil inlet 20 of turbosupercharger 19, so this turbosupercharger 19 is worked under the pressure of 0.5Mpa, like this can hydrodynamic pressure reduces to 0.5Mpa from 0.7Mpa and avoids turbosupercharger 19 to cause leakage of oil because of the inflow oil pressure is excessive.

D, from bulk flow; The bypass recirculating oil quantity sum of oil inlet quantity of turbosupercharger 19 (flow of lubricating oil inlet 20) and bypass valve body 5 equals total recirculating oil quantity of turbosupercharger 19; Do not cause the fuel feeding burden so have the extra motor that links to each other with turbosupercharger 19 of giving, and turbosupercharger 19 oil inlet quantities can be kept the proper functioning of the floating bearing in the turbosupercharger 19 fully.

Obviously, the foregoing description only be for explain clearly that the utility model does for example, and be not to be qualification to the mode of execution of the utility model.For the those of ordinary skill in affiliated field, on the basis of above-mentioned explanation, can also make other multi-form variation or change.Here need not also can't give exhaustive to all mode of executions.And conspicuous variation that these spirit that belong to the utility model are extended out or change still are among the protection domain of the utility model.

Claims (3)

1. the lubricant oil control valve of a turbosupercharger is characterized in that comprising: throttle valve body (4) and bypass valve body (5), and the output stream (8) of throttle valve body (4) is connected with the bypass of bypass valve body (5) inlet (10);

The internal diameter of the throttling passage (6) in the throttle valve body (4) is 0.8-1.2mm;

When the lubricating oil pressure of input throttle valve body (4) was 0.7-0.8MPa, the lubricating oil pressure of exporting from throttle valve body (4) was lower than 0.4-0.5Mpa.

2. the lubricant oil control valve of turbosupercharger according to claim 1, it is characterized in that: said throttle valve body (4) also comprises: input, output stream (7,8), said throttling passage (6) are serially connected with between this input, the output stream (7,8); The sectional area of this throttling passage (6) is less than the sectional area of said input, output stream (7,8); The inlet of said input stream (7) is connected with the inlet (1) of throttle valve body (4), and the outlet of said output stream (8) is the outlet (2) of throttle valve body (4);

Said bypass valve body (5) comprising: with the bypass flow path that said bypass inlet (10) is connected, on this bypass flow path, be provided with the mangetic core assembly (9) of the fluid flow that is used to regulate this bypass flow path.

3. the lubricant oil control valve of turbosupercharger according to claim 2; It is characterized in that: said bypass flow path comprises: first, second bypass flow path (11,12) that intersection is communicated with; First bypass flow path (11) is a funnel shape path; The bottom port of this funnel shape path is a said bypass inlet (10), and the end port of second bypass flow path (12) is the bypass outlet (3) of said bypass valve body (5);

Said mangetic core assembly (9) comprising: the ball (13) of being located at the horn mouth place of said funnel shape path; Be positioned at the pressure spring that is used for the regulated fluid flow (14) of this ball (13) outboard end, the outboard end of this pressure spring is provided with the adjusting screw (15) of the pressure that is used to regulate said pressure spring (14); During use, regulate ball (13) and said bell-mouthed gap through the pressure of regulating said pressure spring (14), with control flow rate.

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