CN109707856B - Valve body connecting system and exhaust gas recirculation system - Google Patents
Valve body connecting system and exhaust gas recirculation system Download PDFInfo
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- CN109707856B CN109707856B CN201910107561.4A CN201910107561A CN109707856B CN 109707856 B CN109707856 B CN 109707856B CN 201910107561 A CN201910107561 A CN 201910107561A CN 109707856 B CN109707856 B CN 109707856B
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Abstract
The invention relates to a valve body connecting system, which limits the length of a fastener to a set length, and embeds the top of the fastener into a valve shaft to fixedly connect a valve plate and the valve shaft, thereby shortening the length of the fastener to the maximum extent on the premise of ensuring that the effective screwing length of the fastener is not reduced, reducing the resistance loss in an air passage of a valve body and increasing the effective application range of a low-pressure waste gas circulating system. Simultaneously, the countersunk head design can make the logical groove region of valve shaft warp more easily when receiving the clamp force for can obtain the same effect with the crew cut fastener through exerting less installation moment of torsion.
Description
Technical Field
The invention relates to the technical field of exhaust gas circulation, in particular to a valve body connecting system on a low-pressure exhaust gas circulating valve and an exhaust gas recirculation system.
Background
Exhaust gas recirculation is a technology for redirecting a part of exhaust gas generated by gasoline or diesel engine operation back to the intake side and participating in combustion again, which can delay the combustion process in the engine cylinder, reduce combustion, pressure release rate and pumping loss, and also reduce the combustion temperature and oxygen concentration in the engine cylinder, thereby suppressing the generation of nitrogen oxides during the combustion process and improving the fuel economy of the automobile. The exhaust gas circulation system is divided into a low-pressure exhaust gas circulation system and a high-pressure exhaust gas circulation system according to the difference of the positions of gas taking and gas introducing in the exhaust gas circulation system. Compared with a high-pressure Exhaust Gas circulation system, the low-pressure Exhaust Gas circulation system has the advantages of large effective working range of Exhaust Gas circulation, high EGR rate (Exhaust Gas recirculation) and capability of inhibiting engine knocking at low speed and high load, so that the whole vehicle with the system has good fuel economy and environmental protection, can meet the emission requirements of relevant regulations, and is favored by many host manufacturers at home and abroad.
The low-pressure exhaust gas circulating valve is a key part in charge of controlling the exhaust gas air inflow in the low-pressure exhaust gas circulating system, the structure of the low-pressure exhaust gas circulating valve mainly comprises a motor, a transmission system, a sensor, a butterfly valve connecting system and the like, and a fastener (screw) in the butterfly valve system is used as a pivot for connecting the parts, so that the low-pressure exhaust gas circulating valve plays a role in fixedly connecting a valve shaft and a valve plate. In conventional butterfly valve designs, in order to ensure sufficient thread engagement length for better strength and anti-loosening characteristics, the screw, after being mounted on the valve shaft, emerges partially from the valve shaft with the head of the screw in the form of a flat head. In the low-pressure exhaust gas recirculation valve, since the diameter of the gas passage is small, the effective flow rate of exhaust gas is reduced by the shielding area due to the exposed portions of the valve shaft and the screw. In order to achieve the same EGR rate, a product with a larger gas passage diameter is needed, so that the volume of the product is further increased, more engine space is occupied, the use of the whole EGR system is limited by the design space of the engine, and the problems of difficult exhaust gas reintroduction and the like are also caused.
Disclosure of Invention
The invention aims to provide a valve body connecting system and an exhaust gas recirculation system, which can shorten the length of a fastener to the maximum extent on the premise of ensuring that the effective screwing length of the fastener is not reduced, so as to solve the problems that the low-pressure exhaust gas recirculation valve is difficult to introduce exhaust gas, is limited by the design space of an engine and the like, and reduce the resistance loss in an air passage of a valve body.
In order to achieve the above object, the present invention provides a valve body connection system, including a valve shaft, a valve plate and a plurality of fasteners, wherein the valve shaft is provided with a through groove penetrating through a shaft body of the valve shaft, the valve plate is inserted into the through groove, the plurality of fasteners penetrate through the valve plate from one side of the valve shaft to fix the valve plate, and the length of the fasteners is limited to a set length to fixedly connect the valve plate and the valve shaft.
Optionally, the top of the fastener is embedded in the valve shaft.
Optionally, the fastener is a countersunk head fastener, and the countersunk head fastener includes a countersunk head screw.
Optionally, the valve shaft is provided with a plurality of positioning holes, the positioning holes radially penetrate through the valve shaft, and the plurality of fasteners respectively penetrate into the valve shaft from the plurality of positioning holes.
Optionally, the through slot divides each positioning hole into a first part and a second part, the first part is closer to the end of the fastener than the second part, and the part of the fastener contacting with the first part is a threaded part.
Optionally, the top of the second section is provided with a tapered portion, and the top of the fastener compresses the tapered portion.
Optionally, the set length is obtained according to a boundary condition of the external thread shear failure of the fastener and a boundary condition of the internal thread shear failure of the valve shaft.
Optionally, the set length L is obtained according to the following formulan：
Ln＝L-(1/λ)·M
Wherein, lambda is a safety factor, and M is a reducible quantity.
Optionally, the reducible amount M is obtained according to the following formula:
M＝(L-L0-Q)-(N-H)；
if M is<0, then set M ═ L-L0-Q; if M is>0, then M ═ L (L-L)0-Q)-(N-H)；
Wherein L is the initial length of the fastener, L0The length of the clamping part of the fastener and the valve shaft is defined as Q, the length of the incomplete external thread at the tail end of the fastener is defined as N, the actual effective screwing length is defined as N, and the minimum effective screwing length is defined as H.
The invention also provides a waste gas recirculation system which comprises an air passage and the valve body connecting system, wherein the valve body connecting system is arranged in the air passage, and the inlet and outlet amount of waste gas is controlled by adjusting the position of the valve plate.
According to the invention, the length of the fastener is limited to be a set length, so that the valve plate is fixedly connected with the valve shaft, and therefore, the length of the fastener can be shortened to the maximum extent on the premise of not reducing the performance of the fastener, so that the resistance loss in the air passage of the valve body is reduced, and the effective application range of the low-pressure waste gas circulating system is enlarged. Meanwhile, the countersunk head design can enable the through groove area in the center of the valve shaft to be easier to deform when being subjected to clamping force, so that the same effect as that of a flat head fastener can be obtained by applying smaller mounting torque.
Drawings
FIG. 1a is a schematic diagram of the overall construction of a low pressure exhaust gas recirculation valve;
FIG. 1b is a schematic block diagram of a low pressure exhaust gas recirculation valve;
FIG. 2a is a schematic cross-sectional view of a fastener designed for a flat head;
FIG. 2b is a schematic cross-sectional view of the fastener when it is a countersunk head design;
FIG. 3 is a schematic structural view of a valve body attachment system in an embodiment of the present invention;
FIG. 4 is a cross-sectional view of an embodiment of the present invention after installation;
in the figure: 101-a motor; 102-a transmission system; 103-a sensor; 104-butterfly valve connection system; 3 a-grub screws; 3 b-countersunk head screws; 1-a valve shaft; 2-a valve plate; 3-a fastener; 4-through groove; 5-positioning holes; 51-tapered portion.
Detailed Description
The following describes in more detail embodiments of the present invention with reference to the schematic drawings. The advantages and features of the present invention will become more apparent from the following description. It is to be noted that the drawings are in a very simplified form and are not to precise scale, which is merely for the purpose of facilitating and distinctly claiming the embodiments of the present invention.
The low-pressure exhaust gas circulating valve is a key part in the low-pressure exhaust gas circulating system for controlling the exhaust gas intake, and has a structure as shown in fig. 1a and 1b, and the structure mainly comprises a motor 101, a transmission system 102, a sensor 103, a butterfly valve connecting system 104 and the like. The butterfly valve connection system 104 is a direct mechanical actuator responsible for controlling the amount of exhaust gas flow, and is composed of a valve shaft, a valve plate, and two fasteners. The butterfly valve connecting system and the air passage simultaneously form an exhaust gas flow passage of the low-pressure exhaust gas circulating valve, and the effective flow cross section of the passage directly determines the capacity of the low-pressure exhaust gas circulating valve for passing exhaust gas. And the fastener in the butterfly valve connecting system is used as a pivot for connecting parts, so that the valve shaft and the valve plate are fixedly connected. One end of the valve shaft is arranged on the shell in an interference fit mode through a bearing, the valve plate penetrates through the through groove of the valve shaft, and the valve plate and the valve shaft are screwed and fixed through a fastener with certain torque; the return torsion spring is preassembled on the sector gear and then welded with the valve shaft to restore the valve shaft. The torque output by the motor 101 is transmitted to the butterfly valve connecting system 104 through the transmission system 102, and the purpose of controlling the inlet and outlet amount of the waste gas is achieved by adjusting the actual position of the valve plate.
In the conventional butterfly valve design, the inventor finds that in order to ensure enough screwing length and obtain better strength and anti-loosening characteristic, after the screw is installed on the valve shaft 1, the bottom of the valve shaft 1 is provided with a section of exposed part of the screw; while the screw head is in the form of a flat head, as shown in fig. 2a, the head of the flat head screw 3a protrudes from the surface of the valve shaft 1. For the low-pressure exhaust gas circulation valve, because the diameter of the gas passage is small, the shielding area caused by the exposed part of the grub screw 3a has a great influence on the effective flow rate of the exhaust gas, and in view of this, the inventor further finds that if a countersunk head design mode of the screw is adopted, as shown in fig. 2b, the head of the countersunk head screw 3b is embedded into the valve shaft 1, and the length of the countersunk head screw 3b can be maximally shortened on the premise of ensuring that the effective screwing length of the countersunk head screw 3b is not reduced.
As shown in fig. 3, the present embodiment provides a valve body connecting system, which includes a valve shaft 1, a valve plate 2 and a plurality of fasteners 3, wherein a through slot 4 is formed on the valve shaft 1, the valve plate 2 is inserted into the through slot 4, the plurality of fasteners 3 penetrate the valve plate 2 from one side of the valve shaft 1 to fix the valve plate 2, and the length of the fasteners 3 is limited to a set length to fixedly connect the valve plate 2 and the valve shaft 1.
Specifically, the through groove 4 penetrates through the side wall of the valve shaft 1, the valve plate 2 is circular, and the length of the through groove 4 is greater than the diameter of the valve plate 2, so that the valve plate 2 penetrates through the through groove 4. In addition, in this embodiment, the number of the fasteners 3 is 2, the top of the fastener 3 is partially embedded in the valve shaft 1, and the limited length enables the bottom of the fastener 3 to slightly protrude out of the valve shaft 1, so that the fastener 3 is not excessively exposed out of the valve shaft 1, the shielding area is reduced, and the influence on the effective flow rate of the exhaust gas is reduced.
Further, the fastener is a countersunk head fastener, and the countersunk head fastener comprises a countersunk head screw. In particular embodiments, the fastener may be any metal threaded fastener in the form of a head, including flush head fasteners.
Further, referring to fig. 4, a plurality of positioning holes 5 are formed in the valve shaft 1, the positioning holes radially penetrate through the valve shaft, and a plurality of fasteners 3 respectively penetrate into the valve shaft 1 from the plurality of positioning holes 5. In this embodiment, the number of the positioning holes 5 is 2, and the centers of the positioning holes 5 are located on the same straight line.
Further, the through-groove 4 divides each positioning hole 5 into a first part and a second part, the first part is closer to the end of the fastening member 3 than the second part, and the part of the fastening member 3 contacting the first part is a threaded part. Specifically, an internal thread is formed in a first part of the positioning hole 5, so that the fastening piece 3 is screwed into the positioning hole 5, and the external thread of the fastening piece 3 is matched with the internal thread of the positioning hole 5, thereby ensuring that the fastening piece 3 connects the valve plate 2 and the valve shaft 1 in a threaded manner.
Further, the top of the second section is provided with a tapered portion 51, and the top of the fastener 3 presses the tapered portion 51. In specific implementation, the fastening member 3 is screwed into the positioning hole 5, and the top conical surface of the fastening member 3 is matched with the conical portion 51 of the second sub-portion, so that the top of the fastening member 3 presses the conical portion 51. This allows the region of the channel 4 to be more easily deformed by the clamping forces applied, and the same clamping effect as a flat head fastener can be achieved by applying a lower mounting torque.
Further, a plurality of through holes are formed in the valve plate 2, the diameter of each through hole is larger than that of the corresponding fastening piece 3, and the fastening pieces 3 penetrate through the valve plate 2 from the through holes. Thus, the fastener 3 can smoothly pass through the valve plate 2 and connect the valve plate 2 and the valve shaft 1.
To ensure the compressive force of the fastener 3 and to shorten the length of the fastener 3, the inventors considered to shorten the length of the fastener 3 to the maximum extent without reducing the effective screw-in length of the fastener 3.
Specifically, the set length of the fastener 3 is mainly related to the boundary condition of the external thread shear failure of the fastener and the boundary condition of the internal thread shear failure of the valve shaft.
In this embodiment, the initial length L, the minimum effective screwing length H, the actual effective screwing length N, and the length L of the clamping portion of the fastener are defined0And the length Q of the incomplete external thread obtains a reducible quantity M; the set length of the fastener 3 is obtained by shortening the length of the threaded portion of the fastener in accordance with the shortfall M.
Firstly, respectively acquiring first screwing lengths H meeting boundary conditions of external thread shearing damage of the fastenersiObtaining a second screwing length H satisfying a boundary condition of the shearing failure of the internal thread of the valve shaft 1e。
The minimum effective screwing length H can be calculated according to the boundary condition of shearing damage of the thread, if H<HeOr HiThe thread is sheared and damaged, so that H is selected to be the first screwing length HiAnd a second twist length HeThe larger of these.
Acquiring the first screwing length H according to the boundary condition of the external thread shearing damage of the fasteneriSpecifically, it is calculated according to the following formula:
acquiring the second screwing length H according to the boundary condition of the shearing damage of the internal thread of the valve shaft 1eSpecifically, it is calculated according to the following formula:
wherein A issThe cross-sectional area at risk is calculated as follows:
wherein P is the thread pitch of the fastener, α is the thread profile half angle or profile flank angle of the thread, d is the dimension of the external thread outside diameter of the fastener, d is the thread pitch of the fastener2Is the dimension of the pitch diameter of the external thread of the fastener, d3Is the dimension of the external thread root diameter of the fastener, D1In order to obtain the dimension of the bottom diameter of the internal thread of the valve shaft 1, ρ is a friction angle, and the friction angle ρ is related to the friction coefficient μ, and is calculated according to the following formula:
μ＝tanρ；
σBBfor the tensile strength of the fastener, τBBIs the external thread shear strength of the fastener, tauBNIs the internal thread shear strength of the valve shaft 1. The strength parameter is obtained by using an estimated strength parameter of a standard fastener (screw) finished product, specifically, the strength parameter can be obtained through a strength test according to materials, heat treatment and processing technologies, for example, a hardness test is performed on screws with similar specifications made of the same materials to obtain Vickers hardness, and then the Vickers hardness is converted into tensile strength, so that the strength parameter is obtained.
Further, the actual effective screwing length N is obtained by using the following formula:
N＝V-t；
where V is the actual running-in length of the fastener measured directly and t is the length of the incomplete internal thread of the valve shaft (not shown in FIG. 4). The length t of the incomplete internal thread of the valve shaft can be specifically estimated according to a machining process for machining the internal thread when the valve shaft is manufactured and a chamfer value.
Further, calculating a difference U between the actual effective screwing length N and the minimum effective screwing length H, that is:
U＝N-H；
if the obtained U after calculation is less than 0, the initial design is proved to be unqualified and is not considered.
Furthermore, the actual shortenable maximum limit I is calculated according to the following formula:
I＝L-L0-Q；
wherein L is the initial length of the fastener, L0Q is the length of the clamping portion of the fastener to the valve shaft 1, and Q is the length of the incomplete external thread at the end of the fastener.
The reducible amount M is the difference between the maximum limit I and the difference U, that is:
M＝I-U；
namely, the reducible amount M is obtained by using the following equation:
M＝(L-L0-Q)-(N-H)；
if M is<0, then M ═ I is set, i.e., M ═ L-L0-Q; if M is>0, then M ═ I-U, i.e., M ═ L (L-L)0-Q)-(N-H)。
Further, the set length L of the fastener 3nCalculated according to the following formula:
Ln＝L-(1/λ)M；
in the embodiment, calculation errors, environment and manufacturing factors are considered at the same time, the designed safety factor lambda is set to be 1-1.5, the design safety factor lambda can be confirmed according to the difference between theoretical and actual conditions in the past design experience, and the minimum and maximum limit sizes of the sizes in the calculation formula need to be determined according to the general design rule. From the above description, the set length range of the fastener 3 should then be:
Ln_min＝L-(1/λmin) M to Ln_max＝L-(1/λmax)M；
Wherein λ isminTo minimize a factor of safety, lambdamaxThe maximum safety factor.
Furthermore, the invention also provides an exhaust gas recirculation system which comprises an air passage and the valve body connecting system, wherein the valve body connecting system is arranged in the air passage and is used for controlling the inlet and outlet amount of exhaust gas by adjusting the position of the valve plate.
In summary, in the valve body connecting system according to the embodiment of the present invention, the top of the fastening member is inserted into the valve shaft, and the fastening member is used to fixedly connect the valve plate and the valve shaft by a predetermined length, so that the length of the fastening member can be shortened to the maximum extent without reducing the performance of the fastening member, the resistance loss in the valve body air passage can be reduced, and the effective application range of the low-pressure exhaust gas circulation system can be increased. Meanwhile, the countersunk head design can enable the through groove area in the center of the valve shaft to be easier to deform when being subjected to clamping force, so that the same effect as that of a flat head fastener can be obtained by applying smaller mounting torque.
The above description is only a preferred embodiment of the present invention, and does not limit the present invention in any way. It will be understood by those skilled in the art that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (8)
1. A valve body connecting system is characterized by comprising a valve shaft, a valve plate and a plurality of fasteners, wherein a through groove penetrating through a shaft body of the valve shaft is formed in the valve shaft, the valve plate is inserted into the through groove, the fasteners penetrate through the valve plate from one side of the valve shaft to fix the valve plate, the length of each fastener is limited to be a set length so as to fixedly connect the valve plate and the valve shaft, and the set length L is obtained according to the following formulan：
Ln＝L-(1/λ)·M
Wherein L is the initial length of the fastener, lambda is a safety factor, and M is a reducible quantity;
the reducible amount M is obtained according to the following formula:
M＝(L-L0-Q)-(N-H)；
if M is<0, then set M ═ L-L0-Q; if M is>0, then M ═ L (L-L)0-Q)-(N-H)；
Wherein L is the initial length of the fastener, L0The length of the clamping part of the fastener and the valve shaft is defined as Q, the length of the incomplete external thread at the tail end of the fastener is defined as N, the actual effective screwing length is defined as N, and the minimum effective screwing length is defined as H.
2. The valve body coupling system of claim 1, wherein a top portion of the fastener is embedded in the valve shaft.
3. A valve body coupling system as claimed in claim 1 or claim 2, wherein the fastener is a countersunk fastener including a countersunk screw.
4. The valve body coupling system of claim 1, wherein said valve shaft defines a plurality of alignment holes extending radially therethrough, and wherein a plurality of said fasteners extend through said valve shaft from said plurality of alignment holes, respectively.
5. The valve body coupling system of claim 4, wherein the through slot divides each of the positioning holes into a first section and a second section, the first section being closer to a distal end of the fastener than the second section, a portion of the fastener in contact with the first section being a threaded portion.
6. A valve body coupling system as in claim 5 wherein the top of the second section is provided with a taper against which the top of the fastener compresses.
7. The valve body coupling system of claim 1, wherein the set length is obtained based on a boundary condition of external thread shear failure of the fastener and a boundary condition of internal thread shear failure of the valve shaft.
8. An exhaust gas recirculation system comprising an air passage and a valve body connecting system according to any one of claims 1 to 7, wherein the valve body connecting system is disposed in the air passage to control the amount of exhaust gas flowing in and out by adjusting the position of a valve plate.
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| CN201910107561.4A CN109707856B (en) | 2019-02-02 | 2019-02-02 | Valve body connecting system and exhaust gas recirculation system |
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| CN201910107561.4A CN109707856B (en) | 2019-02-02 | 2019-02-02 | Valve body connecting system and exhaust gas recirculation system |
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| CN109707856B true CN109707856B (en) | 2021-07-16 |
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Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2698793B2 (en) * | 1987-03-20 | 1998-01-19 | 株式会社 日本気化器製作所 | Engine intake throttle valve |
| JP2004169614A (en) * | 2002-11-20 | 2004-06-17 | Denso Corp | Exhaust gas recirculation controlling device |
| CN203515820U (en) * | 2013-08-12 | 2014-04-02 | 四川红光汽车机电有限公司 | Electronic injection throttle body |
| JP2015059463A (en) * | 2013-09-18 | 2015-03-30 | 株式会社デンソー | Fluid control valve |
| CN204344291U (en) * | 2014-12-19 | 2015-05-20 | 宁波高发汽车控制系统股份有限公司 | A kind of closure being applicable to electronic control air throttle |
| CN205714447U (en) * | 2016-04-26 | 2016-11-23 | 上汽通用汽车有限公司 | Throttle valve device |
| CN206386190U (en) * | 2016-12-21 | 2017-08-08 | 宝沃汽车（中国）有限公司 | Air-throttle assemble, engine and vehicle |
| WO2018163912A1 (en) * | 2017-03-10 | 2018-09-13 | 本田技研工業株式会社 | Air intake structure for internal combustion engine |
| CN208294658U (en) * | 2018-05-29 | 2018-12-28 | 瑞安市阳宇机动车零部件有限公司 | reliable throttle body |
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