CN102383920B - Turbocharger with lubricating oil control valve - Google Patents
Turbocharger with lubricating oil control valve Download PDFInfo
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- CN102383920B CN102383920B CN 201110312221 CN201110312221A CN102383920B CN 102383920 B CN102383920 B CN 102383920B CN 201110312221 CN201110312221 CN 201110312221 CN 201110312221 A CN201110312221 A CN 201110312221A CN 102383920 B CN102383920 B CN 102383920B
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Abstract
The invention relates to a valve used for a turbocharger and an operating method thereof. The valve comprises valve bodies between a fluid inlet and a throttled fluid outlet as well as a bypass outlet, wherein the valve bodies are divided into a throttling component for regulating the speed of the fluid through a throttle valve body and a bypass valve body part used for bypassing the throttled fluid part subjected to pressure reduction by the throttling component, namely further reducing the pressure of the throttled fluid; and the throttle valve body part and the bypass valve body part are coordinated with each other to operate, so that the pressure of the fluid flowing out of the throttled fluid outlet of the valve meets the requirement of the subsequent component operation. The valve and the operating method have the following beneficial effects: the defects during independent action of the throttle valve and the bypass valve are overcome; the pressure of the fluid accessed to the oil circuit can be effectively reduced by combining the advantages of the two valves and sufficient fluid flow is ensured to meet the requirement of the subsequent component operation; and the valve has a simple structure and a small volume and is convenient to install.
Description
Technical field
The present invention relates to the technical field of turbosupercharger, be specifically related to a kind of turbosupercharger with lubricating oil control valve.
Background technique
Turbosupercharger is used for diesel engine at first, and the motor after the use turbosupercharger has the advantages that power per liter is high, rate of fuel consumption is low, blowdown is less.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 sufficient lubrication and cooling.Therefore, giving sufficient lubricant oil is absolutely necessary.Will do sealing configuration in the very limited middle shell-space of turbosupercharger, 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 turbocharger for diesel engine is assemblied on the petrol engine in the prior art and uses, but because petrolic lubricant oil input pressure is generally 0.7-0.8MPa, so when petrolic lubricant oil oil pipe is 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, external series gap is 0.07-0.08mm, have simultaneously the sealing mechanism with the slit, 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, the lubricant oil that flows to pressurized machine is carried out step-down just necessary, make 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: namely unnecessary lubricant oil is flowed back to fuel tank by bypass valve.Its shortcoming be a large amount of lubricant oil by bypass, will reduce the consumption of lubricating oil of motor itself, can cause motor for want of lubricant oil cause the damage of moving link.Flow limit method: namely dwindle the oil inlet hole area, allow lubricant oil lose to reach hypotensive effect by the aperture pressure drag.As calculated and experiment showed, when oil inlet hole is reduced to φ 0.6mm from φ 4mm, just can make oil pressure drop to 0.4MPa from 0.7MPa.Although this structure is simple, also brings side effect, unavoidably has booty because keeping away in the lubricant oil.Some booty particle diameters are 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.
Summary of the invention
The technical problem to be solved in the present invention provides a kind of turbosupercharger leakage of oil defective that both overcome, and can guarantee again the turbosupercharger with lubricating oil control valve that the lubricant oil of motor and turbosupercharger is supplied with.
For solving the technical problem of above-mentioned primary solution, the invention provides a kind of turbosupercharger with lubricating oil control valve, be characterized in: lubricating oil control valve comprises: throttle valve body and bypass valve body, and the output stream of throttle valve body is connected with the bypass entrance of bypass valve body; 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.The entrance of described throttle valve body is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet of this throttle valve body links to each other with the lubricating oil inlet of turbosupercharger, the shell wall adjacent with the lubricating oil outlet of described turbosupercharger is provided with the bypassing reflux stream mouth, the bypass outlet of described bypass valve body links to each other with this bypassing reflux stream mouth, and the lubricating oil outlet of turbosupercharger links to each other with petrolic lubricating oil return pipeline.
Described throttle valve body also comprises: input, output stream, described 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 described input, output stream; The entrance of described input stream is connected with the entrance of throttle valve body, and the outlet of described output stream is the outlet of throttle valve body; Described bypass valve body comprises: the bypass flow path that is connected with described bypass entrance is provided with mangetic core assembly for the fluid flow of regulating this bypass flow path in this bypass flow path.
Described bypass flow path comprises: first, second bypass flow path that intersection is communicated with, and the first bypass flow path is a funnel shape path, and the bottom port of this funnel shape path is described bypass entrance, and the end port of the second bypass flow path is the bypass outlet of described bypass valve body; Described mangetic core assembly comprises: be located at the ball at the horn mouth place of described funnel shape path, be positioned at the pressure spring that is used for regulating fluid flow of this ball outboard end, the outboard end of this pressure spring is provided with the adjusting screw be used to the pressure of regulating described pressure spring; During use, regulate ball and described bell-mouthed gap by the pressure of regulating described pressure spring, with the control flow.
The method of work of the lubricating oil control valve of above-mentioned turbosupercharger comprises: pressure be the lubricant oil of 0.7-0.8MPa after the throttling of throttle valve body, adopt the logical step-down of by-pass valve body radical, so that be lower than 0.4-0.5Mpa from the lubricating oil pressure of throttle valve body output; The internal diameter of the throttling passage in the throttle valve body is 0.8-1.2mm.
As another kind of scheme, the entrance of described throttle valve body is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet of this throttle valve body links to each other with the lubricating oil inlet of turbosupercharger, the lubricating oil outlet of turbosupercharger links to each other with the first input end of a tee union, the bypass outlet of described bypass valve body links to each other with the second input end of described tee union, and the output terminal of described tee union is used for linking to each other with petrolic lubricating oil return pipeline.
The technique effect that the present invention has: (1) is assemblied in use and oil tight purpose on the petrol engine for realizing with turbocharger for diesel engine, and the present invention has increased a restrictor by-pass valve in the lubricating oil inlet of turbosupercharger, i.e. lubricating oil control valve; Throttle valve body wherein is used for throttling, to guarantee simultaneously the lubricant oil supply to petrol engine and turbosupercharger; The bypass valve body is used for step-down, and when making the lubricating oil pressure of inputting 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 turbocharger for diesel engine 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 described bypass valve body is sent into turbosupercharger by described 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.Lubricating oil control valve of the present invention is applied to 3360, on the turbosupercharger of the models such as K03, K04, played the effect of step-down leakproof.
Description of drawings
For content of the present invention is more likely to be clearly understood, below the specific embodiment and by reference to the accompanying drawings of basis, the present invention is further detailed explanation, wherein
The structural representation of the lubricating oil control valve of Fig. 1 turbosupercharger of the present invention.
The turbosupercharger of the described valve of Fig. 2 application of the present invention, mark 23 are the intermediate assembly of turbosupercharger 19.
The another kind of turbosupercharger of the described valve of Fig. 3 application of the present invention.
Embodiment
The present invention is described in detail below in conjunction with drawings and Examples:
(embodiment 1)
Such as Fig. 1, the lubricating oil control valve of the turbosupercharger of the 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 entrance 10 of bypass valve body 5; 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.
Described throttle valve body 4 also comprises: input, output stream 7,8, described 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 described input, output stream 7,8 sectional area; The entrance of described input stream 7 is connected with the entrance 1 of throttle valve body 4, and the outlet of described output stream 8 is the outlet 2 of throttle valve body 4; Described bypass valve body 5 comprises: the bypass flow path that is connected with described bypass entrance 10 is provided with mangetic core assembly 9 for the fluid flow of regulating this bypass flow path in this bypass flow path.
Described bypass flow path comprises: first, second bypass flow path 11,12 that intersection is communicated with, the first bypass flow path 11 is a funnel shape path, the bottom port of this funnel shape path is that the end port of described bypass entrance 10, the second bypass flow path 12 is the bypass outlet 3 of described bypass valve body 5; Described mangetic core assembly 9 comprises: the ball 13 of being located at the horn mouth place of described funnel shape path, be positioned at the pressure spring 14 that is used for regulating fluid flow of these ball 13 outboard ends, the outboard end of this pressure spring is provided with the adjusting screw 15 be used to the pressure of regulating described pressure spring 14; During use, regulate ball 13 and described bell-mouthed gap by the pressure of regulating described pressure spring 14, with the control flow.
Described flow entrance adopts threaded coupling or flange-interface.
By fluid mechanics as can be known, the scope basis of described throttling passage 6 internal diameter values: two laws of fluid mass conservation (equation of continuity) and energy conservation (Bernoulli's equation) are in conjunction with obtaining 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, equal density):
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 for pressure and the flow velocity of fluid in the closed conduct that throttling passage 6 is installed following relation is arranged with Bernoulli's equation:
P
0Be the hydrodynamic pressure of the input stream 7 of throttling passage 6 upstreams, P
1Be the hydrodynamic pressure of the output stream 8 in throttling passage 6 downstreams, ρ is fluid density.In actual test process, the hydrodynamic pressure of throttling passage 6 internal diameters because of internal diameter is too small can't Measurement accuracy, 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.
Obtained the pressure loss formula in fluid process throttling passage 6 downstreams by above-mentioned fluid mass conservation (equation of continuity) and two laws combinations of energy conservation (Bernoulli's equation):
In the formula: the pressure drop Δ P=P of Δ P fluid after small holes
0-P
1d
0Be the diameter of described input stream 7, d
1Be the internal diameter of throttling passage 6, K is 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 by described pressure loss formula.
According to described 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, although but the pressure drop that throttling passage 6 hole internal diameter 0.6mm produce is maximum, but easily stopped up by booty because internal diameter is too small, so this shortcoming that easily is blocked in order to overcome throttling passage 6, so inside diameter ranges is selected in 0.8-1.2mm, the first-selected 1.0mm of the present embodiment.
Table 1 connects the lubricating oil control valve of the present embodiment with the lubricant oil filler opening of 3360 turbosupercharger, lubrication pressure test record (30 ℃ of oil temperatures)
Can find out from above-mentioned table 1 test data:
A, along with P
0Height, throttling reducing effect are larger, and P is at 0.05-0.12Mpa for the pressure drop range delta;
B, be throttling passage 6 step-downs of 1.0mm with internal diameter, 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 described 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 reduce to 0.5Mpa from 0.7Mpa and avoid turbosupercharger 19 oil pressure is excessive to cause leakage of oil because flowing into.
D, from bulk flow, the bypass recirculating oil quantity sum of the 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, so the not extra motor that links to each other with turbosupercharger 19 of giving causes the fuel feeding burden, and turbosupercharger 19 oil inlet quantities can be kept the normal operation of the floating bearing in the turbosupercharger 19 fully.
(embodiment 2):
On the basis of above-described embodiment 1, the method of work of the lubricating oil control valve of the turbosupercharger of the present embodiment, comprise: pressure is that the lubricant oil of 0.7-0.8MPa is after 4 throttlings of throttle valve body, adopt the 5 bypass step-downs of bypass valve body, so that be lower than 0.4-0.5Mpa from the lubricating oil pressure of throttle valve body 4 outputs; The internal diameter of the throttling passage 6 in the throttle valve body 4 is 0.8-1.2mm, preferred 1mm.
About the internal diameter value of described throttling passage 6, its hydrodynamic pressure calculating method comprises:
Fluid mass conservation (equation of continuity) and two laws of energy conservation (Bernoulli's equation) in the closed conduct.
Obtain fluid process throttling passage 6 holes pressure loss formula afterwards by above-mentioned fluid mass conservation (equation of continuity) and two laws combinations of energy conservation (Bernoulli's equation):
In the formula: the pressure drop of Δ P fluid after small holes; Δ P=P
0-P
1d
0Be the diameter of described input stream 7, d
1Be throttling passage 6 internal diameters, K is throttling passage 6 shrinkage coefficients and K=0.12-0.13, and K gets intermediate value 0.125.
Voltage drop value corresponding to internal diameter that calculates corresponding throttling passage 6 by described pressure loss formula.
According to described formula:
Work as d
1During=1.2mm, known P
0=0.7Mpa, d
0=4mm then calculates pressure drop Δ P=0.10Mpa;
Work as d
1During=1.0mm, known P
0=0.7Mpa, d
0=4mm then calculates pressure drop Δ P=0.11Mpa;
Work as d
1During=0.8mm, known P
0=0.7Mpa, d
0=4mm then calculates pressure drop Δ P=0.13Mpa;
Work as d
1During=0.6mm, known P
0=0.7Mpa, d
0=4mm then calculates pressure drop Δ P=0.15Mpa;
Can obtain from calculated data, when the internal diameter of throttling passage 6 is selected 1.0mm, known P
0=0.7Mpa, d
0=4mm, pressure drop Δ P=0.11Mpa is by Δ P=P
0-P
1Calculate P
1=0.59Mpa because subsequent parts work fluid pressure requires can carry out dividing potential drop by bypass valve section 5 for 0.5Mpa, reduces the hydrodynamic pressure of the outlet 2 of throttle valve body 4.
(embodiment 3):
Such as Fig. 2, a kind of turbosupercharger of using the lubricating oil control valve of above-described embodiment 1 and 2, comprise: the entrance 1 of described throttle valve body 4 is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet 2 of this throttle valve body 4 links to each other with the lubricating oil inlet 20 of turbosupercharger 19, the shell wall adjacent with the lubricating oil outlet 21 of described turbosupercharger 19 is provided with the bypassing reflux stream mouth, the bypass of described bypass valve body 5 outlet 3 links to each other with this bypassing reflux stream mouth, and the lubricating oil outlet 21 of turbosupercharger 19 links to each other with petrolic lubricating oil return pipeline.
(embodiment 4):
Such as Fig. 3, a kind of turbosupercharger of using the lubricating oil control valve of above-described embodiment 1 and 2, comprise: the entrance 1 of described throttle valve body 4 is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet 2 of this throttle valve body 4 links to each other with the lubricating oil inlet 20 of turbosupercharger 19, the lubricating oil outlet 21 of turbosupercharger 19 links to each other with the first input end of a tee union 22, the bypass of described bypass valve body 5 outlet 3 links to each other with the second input end of described tee union 22, and the output terminal of described tee union 22 is for linking to each other with petrolic lubricating oil return pipeline.
Obviously, above-described embodiment only is for example of the present invention clearly is described, and is not to be restriction to embodiments of the present invention.For those of ordinary skill in the field, can also make other changes in different forms on the basis of the above description.Here need not also can't give all mode of executions exhaustive.And these belong to apparent variation or the change that spirit of the present invention extended out and still are among protection scope of the present invention.
Claims (6)
1. turbosupercharger with lubricating oil control valve is characterized in that:
Described lubricating oil control valve 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 entrance (10) of bypass valve body (5); 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;
The entrance (1) of described throttle valve body (4) is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet (2) of this throttle valve body (4) links to each other with the lubricating oil inlet (20) of turbosupercharger (19), the shell wall adjacent with the lubricating oil outlet (21) of described turbosupercharger (19) is provided with the bypassing reflux stream mouth, the bypass outlet (3) of described bypass valve body (5) links to each other with this bypassing reflux stream mouth, and the lubricating oil outlet (21) of turbosupercharger (19) links to each other with petrolic lubricating oil return pipeline.
2. the turbosupercharger with lubricating oil control valve according to claim 1, it is characterized in that: described throttle valve body (4) also comprises: input, output stream (7,8), described 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 described input, output stream (7,8); The entrance of described input stream (7) is connected with the entrance (1) of throttle valve body (4), and the outlet of described output stream (8) is the outlet (2) of throttle valve body (4);
Described bypass valve body (5) comprising: the bypass flow path that is connected with described bypass entrance (10) is provided with mangetic core assembly (9) for the fluid flow of regulating this bypass flow path in this bypass flow path.
3. the turbosupercharger with lubricating oil control valve according to claim 2, it is characterized in that: described bypass flow path comprises: first, second bypass flow path (11,12) that intersection is communicated with, the first bypass flow path (11) is a funnel shape path, the bottom port of this funnel shape path is described bypass entrance (10), and the end port of the second bypass flow path (12) is the bypass outlet (3) of described bypass valve body (5);
Described mangetic core assembly (9) comprising: the ball (13) of being located at the horn mouth place of described funnel shape path, be positioned at the pressure spring (14) that is used for regulating fluid flow of this ball (13) outboard end, the outboard end of this pressure spring is provided with the adjusting screw (15) be used to the pressure of regulating described pressure spring (14); During use, regulate ball (13) and described bell-mouthed gap by the pressure of regulating described pressure spring (14), with the control flow.
4. turbosupercharger with lubricating oil control valve, it is characterized in that: described lubricating oil control valve 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 entrance (10) of bypass valve body (5); 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;
The entrance (1) of described throttle valve body (4) is used for linking to each other with petrolic lubricant oil feeding pipe road, the outlet (2) of this throttle valve body (4) links to each other with the lubricating oil inlet (20) of turbosupercharger (19), the lubricating oil outlet (21) of turbosupercharger (19) links to each other with the first input end of a tee union (22), the bypass outlet (3) of described bypass valve body (5) links to each other with the second input end of described tee union (22), and the output terminal of described tee union (22) is used for linking to each other with petrolic lubricating oil return pipeline.
5. the turbosupercharger with lubricating oil control valve according to claim 4, it is characterized in that: described throttle valve body (4) also comprises: input, output stream (7,8), described 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 described input, output stream (7,8); The entrance of described input stream (7) is connected with the entrance (1) of throttle valve body (4), and the outlet of described output stream (8) is the outlet (2) of throttle valve body (4);
Described bypass valve body (5) comprising: the bypass flow path that is connected with described bypass entrance (10) is provided with mangetic core assembly (9) for the fluid flow of regulating this bypass flow path in this bypass flow path.
6. the turbosupercharger with lubricating oil control valve according to claim 5, it is characterized in that: described bypass flow path comprises: first, second bypass flow path (11,12) that intersection is communicated with, the first bypass flow path (11) is a funnel shape path, the bottom port of this funnel shape path is described bypass entrance (10), and the end port of the second bypass flow path (12) is the bypass outlet (3) of described bypass valve body (5);
Described mangetic core assembly (9) comprising: the ball (13) of being located at the horn mouth place of described funnel shape path, be positioned at the pressure spring (14) that is used for regulating fluid flow of this ball (13) outboard end, the outboard end of this pressure spring is provided with the adjusting screw (15) be used to the pressure of regulating described pressure spring (14); During use, regulate ball (13) and described bell-mouthed gap by the pressure of regulating described pressure spring (14), with the control flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110312221 CN102383920B (en) | 2011-10-14 | 2011-10-14 | Turbocharger with lubricating oil control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110312221 CN102383920B (en) | 2011-10-14 | 2011-10-14 | Turbocharger with lubricating oil control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102383920A CN102383920A (en) | 2012-03-21 |
| CN102383920B true CN102383920B (en) | 2013-04-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110312221 Expired - Fee Related CN102383920B (en) | 2011-10-14 | 2011-10-14 | Turbocharger with lubricating oil control valve |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201635831U (en) * | 2010-03-16 | 2010-11-17 | 奇瑞汽车股份有限公司 | Oil return device of turbocharger |
| CN201650398U (en) * | 2010-03-01 | 2010-11-24 | 江苏林海动力机械集团公司 | Pressure relief device of engine pressure lubricating system |
| CN202250372U (en) * | 2011-10-14 | 2012-05-30 | 常州新瑞汽车配件制造有限公司 | Turbocharger with lubricating oil control valve |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0893490A (en) * | 1994-09-21 | 1996-04-09 | Nissan Diesel Motor Co Ltd | Lubricating device of turbocharger |
-
2011
- 2011-10-14 CN CN 201110312221 patent/CN102383920B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201650398U (en) * | 2010-03-01 | 2010-11-24 | 江苏林海动力机械集团公司 | Pressure relief device of engine pressure lubricating system |
| CN201635831U (en) * | 2010-03-16 | 2010-11-17 | 奇瑞汽车股份有限公司 | Oil return device of turbocharger |
| CN202250372U (en) * | 2011-10-14 | 2012-05-30 | 常州新瑞汽车配件制造有限公司 | Turbocharger with lubricating oil control valve |
Non-Patent Citations (1)
| Title |
|---|
| JP特开平8-93490A 1996.04.09 |
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|---|---|
| CN102383920A (en) | 2012-03-21 |
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