CN211422764U

CN211422764U - Balance valve body structure for supercharger application

Info

Publication number: CN211422764U
Application number: CN201922253625.XU
Authority: CN
Inventors: 马仙龙; 金建交; 彭巍巍
Original assignee: Wuxi Cummins Turbo Technologies Co Ltd
Current assignee: Wuxi Cummins Turbo Technologies Co Ltd
Priority date: 2019-12-16
Filing date: 2019-12-16
Publication date: 2020-09-04
Anticipated expiration: 2029-12-16

Abstract

The utility model belongs to the technical field of turbo charger, a balanced valve body structure that booster was used is related to, including the volute, be equipped with balanced chamber, its characterized in that in the runner of volute: a first bushing and a second bushing are respectively fixed on two axial sides of the inner wall of the balance cavity, a shaft is arranged in the first bushing and the second bushing in a rotating fit mode, and an integrated valve is arranged in the balance cavity and fixedly connected with the shaft; two ends of the shaft extend out of the outer side of the volute, one end of the shaft extending out of the volute is connected with the connecting rod assembly, and the other end of the shaft extending out of the volute is sleeved with the check ring; the retainer ring can limit the movement of the valve body and eliminate the axial abrasion of the valve body caused by the self gravity. When the integrated valve works, the integrated valve acts integrally. The valve body structure effectively eliminates the abrasion or breakage of the valve body connecting piece caused by the rotation of the valve plate or the shaking of the valve plate due to the exhaust pulse of the engine.

Description

Balance valve body structure for supercharger application

Technical Field

The utility model belongs to the technical field of turbo charger, a balanced valve body structure that booster used is related to.

Background

Turbochargers are known which utilize the inertial momentum of exhaust gases from the engine to propel a turbine within a turbine housing to rotate at high speed, thereby driving a coaxial impeller which forces more air into the engine combustion chamber and mixes the fuel for combustion to increase the power generated by the engine. Typically to maximize the power generated by the combustion process, the engine is equipped with a branched exhaust manifold in communication with a turbocharged air induction system. The bifurcated exhaust manifold system is desirable to minimize engine exhaust emissions, in addition to helping to conserve the energy of the exhaust gases produced by the engine cylinders to increase engine power.

With the increasing air pollution and global warming, legislation on automobile emissions is becoming more and more stringent, especially in the control of nitrogen oxides (NOx), Particulate Matter (PM), and carbon monoxide (CO), and carbon dioxide, among others. In the prior art, engines using waste recirculation (EGR) systems, including diesel engines, natural gas engines, methanol engines, etc., need to be matched with corresponding superchargers.

Engines employing EGR systems recirculate a portion of the exhaust gas produced by the combustion of the engine back and forth into the engine cylinders to participate in combustion. By reducing the content of oxygen in the combustion chamber of the engine, the combustion temperature is reduced, thereby reducing harmful substances such as nitrogen oxides (NOx), carbon monoxide and the like in the exhaust gas of the engine.

To realize EGR driving, it is necessary to satisfy: the inlet pressure of the volute is larger than the boost pressure in the engine intake manifold, so that the high-pressure waste gas at the front part of the volute can be driven to automatically enter the intake side, and the EGR driving is realized. The prior art comprises a variable turbine section technology, a fixed section symmetrical flow passage technology, an asymmetric double flow passage technology and the like; where variable turbine section technology is costly and poorly reliable. The technology of the fixed section symmetrical flow channel needs the pressure of two flow channels to be simultaneously greater than the pressure of an air inlet manifold in order to meet the requirement of EGR driving, so that the engine is often caused to generate high pumping loss, and the oil consumption, the power and the emission of the engine during the middle and high-speed running are deteriorated. The asymmetrical double-flow-channel balance valve type supercharger is provided with two different flow channels, wherein the small flow channel is connected with the EGR loop, the high pressure in the small flow channel can effectively drive the EGR, and the large flow channel has lower exhaust gas pressure of the small flow channel, so that the pumping loss of the engine can be effectively reduced. In the middle and high speed running area of the engine, the pressure in the small flow passage is often surplus when being used for driving EGR, and at the moment, the balance valve device is opened to enable part of exhaust gas in the small flow passage to enter the large flow passage, so that the exhaust gas pressure in the two flow passages is closer, and the high speed pumping loss in the engine can be effectively reduced. On the basis of meeting the emission, the fuel oil and the economical efficiency of the engine can be greatly improved.

In the invention patent publication No. 200880022691.8 and utility model patent No. 201721524025.7, both of these patents describe shell structures corresponding to asymmetric double flow channels, and utility model patent 201820861464.5 describes a balance valve device for asymmetric double flow channel application, and the valve sheet schemes they adopt are all common bypass valve structures. The common bypass valve structure (as shown in figures 1 and 2) comprises a rocker arm 1, a pin shaft 2, a shaft 3, a gasket 4 and a valve plate 5, wherein the valve plate 5 is connected with an inner hole 1 of the rocker arm through the pin shaft 2, an axial gap and a radial gap exist, and the valve plate 5 can rotate around the pin shaft 2 and deflect under the action of external force. The asymmetrical double-flow-passage balance valve type supercharger is provided with a large flow passage and a small flow passage, and the large flow passage and the small flow passage are converged in a balance cavity. The pressure of the waste gas in the balance cavity is high-pressure gas which comes from high-frequency pulse change in an engine exhaust manifold, and after the valve plate receives the high-frequency pulse pressure, the front surface and the back surface of the valve plate can generate high-frequency alternating pressure difference, so that the valve plate is driven to rotate and shake in an accelerating mode. Therefore, the end faces of the upper gasket of the valve plate and the end face of the rocker arm, the end face of the rocker arm and the end face of the pin shaft, and the outer diameter of the pin shaft and the inner hole of the rocker arm are greatly abraded. Although some bypass valve plates (shown in fig. 3 and 4) adopt the anti-rotation feature 6 to enable the rotation angle of the valve plates to be smaller, under the action of pulse force, the valve plates can still rotate within a small-angle range to cause the anti-rotation structure to collide back and forth, so that the anti-rotation feature 6 is subjected to fatigue fracture, in addition, the valve plates 5 can still frequently deflect, and larger abrasion is generated between the end surfaces of the valve plates and the end surfaces of the rocker arms, between the end surfaces of the rocker arms and the end surfaces of the gaskets, and between the outer diameters of; the effective service life of the valve system is greatly shortened due to the abrasion of each part of the balance valve or the breakage of the anti-rotation feature, and the requirement of practical application cannot be met.

Similarly, for a turbine with a bypass valve in a symmetrical double-flow channel or an asymmetrical double-flow channel, high-frequency pulsating high-pressure turbine front exhaust gas causes great pressure difference between two surfaces of the bypass valve plate, so that great abrasion is generated between the end surface of the gasket and the end surface of the rocker arm, between the end surface of the rocker arm and the end surface of the pin shaft, and between the outer diameter of the pin shaft and the inner hole of the rocker arm.

In the application of the asymmetric double-flow-channel balance valve, the pressure and the temperature of exhaust gas in a balance cavity are high, one end of a shaft is in contact with outside air, the other end of the shaft is under high pressure in the cavity, the shaft generates high axial force to enable a rocker arm to be in contact with a bush, and when the balance valve is frequently opened and closed or is subjected to pulse impact to shake the valve plate, the shaft is driven to slightly move at high frequency to generate high axial abrasion. Although patent 201820861464.5 proposes a device (as shown in fig. 5) using a double bushing to balance the axial force, the balance valve rocker arm 1 is disposed between the first bushing 8 and the second bushing 10, the two ends of the balance valve shaft 3 are connected with the outside air, and the pressures and areas on the two sides of the shaft end are equal, so that no axial force is generated on the balance valve shaft 3 due to the large pressure difference inside and outside the balance cavity. But still does not eliminate the wear of the rocker arm in the axial direction, which occurs during the frequent opening and closing of the valve plate, due to the fact that the shaft is vertically downwards affected by the weight of its own parts in certain arrangements of the engine.

Usually, the valve plate rocker arm 1 and the shaft 3 are connected at a 9-slot position in a welding mode, and the defects of welding hot cracks, non-fusion and the like generated in a fusion area of the rocker arm and the shaft exist in the welding process. These defects subject the balancing or bypass valve to large impulse forces during use, greatly reducing the life of the welded connection due to the presence of the initial defect.

Disclosure of Invention

To the above problem, the utility model provides a balanced valve body structure that booster was used, this valve body structure has effectively eliminated because the valve block self that the engine exhaust pulse arouses rotation or the valve block connecting piece wearing and tearing or the fracture that the valve block shake leads to.

According to the technical scheme of the utility model: the utility model provides a balanced valve body structure that booster was used, includes the volute, is equipped with balanced chamber in the runner of volute, its characterized in that: a first bushing and a second bushing are respectively fixed on two axial sides of the inner wall of the balance cavity, a shaft is arranged in the first bushing and the second bushing in a rotating fit mode, and an integrated valve is arranged in the balance cavity and fixedly connected with the shaft;

two ends of the shaft extend out of the outer side of the volute, one end of the shaft extending out of the volute is connected with the connecting rod assembly, and the other end of the shaft extending out of the volute is sleeved with the check ring;

when the integrated valve works, the integrated valve acts integrally.

As a further improvement of the utility model, integrative valve is the whole, and integrative valve forms the circular shape valve body portion through the hole and the axle fixed connection that set up on keeping away from the valve body that sets up the hole part on the integrative valve, and on vertical projection face, the valve body position is in the radial outside of inner bore portion.

As a further improvement, the integrated valve is provided with a through groove, and the integrated valve and the shaft are welded and connected at the through groove.

As a further improvement of the present invention, ribs are provided on the integrated valve respectively corresponding to both sides of the through groove.

As a further improvement of the utility model, a logical groove is arranged on the integrated valve or a logical groove is arranged on both sides of the surface of the integrated valve in the radial direction.

As a further improvement of the utility model, the radial one end of an axial side end face of integrative valve sets up the groove.

As a further improvement of the utility model, the radial both ends of an axial side end face of integrative valve set up the groove respectively.

As a further improvement of the utility model, the integrated valve adopts an integrally-acting valve body structure and comprises a rocker arm, a valve block and a gasket, an inner hole of the rocker arm is welded with a shaft at a through groove, and the end surfaces at two sides of the rocker arm are respectively in tight fit with the valve block and the gasket; the valve plate is provided with an integrally connected valve plate shaft, the valve plate shaft penetrates through holes in the rocker arm and the gasket, and the gasket is arranged on the upper portion of the inner hole of the rocker arm.

As a further improvement of the utility model, welded connection or riveting fixed between the valve plate shaft and the gasket.

The technical effects of the utility model reside in that: the utility model discloses simple structure, it is compact reasonable, integrative valve structure can eliminate because the valve block self that the engine exhaust pulse arouses rotation or the valve body connecting piece wearing and tearing or the fracture that the valve block shake leads to. Because when the integrated valve and the shaft move axially, the integrated valve can not be axially contacted with the first bush and the second bush all the time, even in certain special arrangement that the shaft vertically faces downwards, the abrasion of the axial end part of the valve plate in the valve cavity can be effectively eliminated. The check ring or the connecting rod assembly outside the shaft bears the self gravity of the valve body system, and the working temperature is lower due to the fact that the check ring or the connecting rod assembly is arranged outside the valve cavity, so that the abrasion of the check ring or the connecting rod assembly is effectively reduced. The groove of integrative valve groove makes the welding heat more concentrate on the position of valve block hole tank bottom and axle, is favorable to the material to fuse and reduces the heat affected zone, and the muscle next to the groove has can effectively prevent to overweld or weld through. The welding quality and consistency are effectively improved, so that the strength of the welding part is improved, and the service life of the balance valve or the bypass valve system is prolonged.

Drawings

Fig. 1 is a schematic diagram of a common bypass valve.

Fig. 2 is a top view of fig. 1.

FIG. 3 is a schematic view of a bypass valve with anti-rotation features.

Fig. 4 is a top view of fig. 3.

FIG. 5 is a schematic view of a balanced valve assembly with a double liner.

Fig. 6 is a schematic structural diagram of a first embodiment of the present invention.

Fig. 7 is a schematic view of the single-side welding of the integrated valve of the present invention.

Fig. 8 is a right side view of fig. 7.

Fig. 9 is a schematic diagram of the integrated valve double-side welding of the present invention.

Fig. 10 is a right side view of fig. 9.

Fig. 11 is a schematic structural view of a second embodiment of the present invention.

Fig. 12 is a schematic view of a welding structure of the middle integrated valve of the present invention.

Fig. 13 is a schematic view of a riveted structure of the middle integrated valve of the present invention.

Fig. 14 is the interference fit welding schematic diagram of the middle integrated valve of the present invention.

Fig. 15 is the interference fit riveting schematic diagram of the middle integrated valve of the present invention.

Detailed Description

The following description will further describe embodiments of the present invention with reference to the accompanying drawings.

In fig. 1 to 15, the anti-rotation valve comprises a rocker arm 1, a pin shaft 2, a shaft 3, a gasket 4, a valve plate 5, an anti-rotation feature 6, a connecting rod assembly 7, a first bushing 8, a through groove 9, a second bushing 10, a volute 11, a balance valve cavity 12, an integrated valve 13, a check ring 14, a groove 15, ribs 16, a valve body structure 17 of integral action, a valve plate shaft 18 and the like.

As shown in fig. 6, the utility model relates to a balance valve body structure for a supercharger, which comprises a volute 11, a balance cavity 12 is arranged in a flow channel of the volute 11, a first bush 8 and a second bush 10 are respectively fixed on two sides of the inner wall of the balance cavity 12 in the axial direction, a shaft 3 is arranged in the first bush 8 and the second bush 10 in a rotating fit manner, and an integrated valve 13 is arranged in the balance cavity 12 and is fixedly connected with the shaft 3;

two ends of the shaft 3 extend out of the outer side of the volute 11 and are in contact with the atmosphere, one end of the shaft 3 extending out of the volute 11 is connected with the connecting rod assembly 7, and the other end of the shaft 3 extending out of the volute 11 is sleeved with a retaining ring 14; the integrated valve 13 is axially moved toward the retainer ring 14 side and is retained by the connecting rod assembly 7, and the integrated valve 13 is axially moved toward the connecting rod assembly 7 side and is retained by the retainer ring 14.

The integrated valve 13 operates as a whole when operating.

Since the clearance between both sides of the integrated valve 13 and the first and

second bushes

8, 10 is larger than the amount of the integrated valve 13 that moves in the two-axis direction, the integrated valve 13 cannot contact with the first or

second bush

8, 10, and therefore the integrated valve 13 cannot contact with the first or

second bush

8, 10 even when the shaft 3 is vertically downward in some special arrangements of the engine. The weight force on the shaft 3, the integrated valve 13, the check ring 14 and the connecting-rod assembly 7 thus all falls on the end face of the check ring 14 in contact with the second bush 10 or on the end face of the connecting-rod assembly 7 in contact with the first bush 8. Therefore, the two ends of the integrated valve cannot generate axial abrasion, the original axial abrasion is transferred to the retainer ring 14 or the connecting rod assembly 7, and the temperature of the components is greatly lower than that of the balance cavity 12 due to the fact that the retainer ring 14 and the connecting rod assembly 7 are arranged outside the volute 11, and therefore the abrasion loss is greatly reduced in the same rotating displacement.

As shown in fig. 7 and 8, the integrated valve 13 is compared with a common bypass valve or a bypass valve with anti-rotation feature (as shown in fig. 1 and 2): the integrated valve 13 is an integral piece, the integrated valve 13 is fixedly connected with the shaft 3 through a set inner hole, a circular valve body part is formed on the valve body which is far away from the inner hole part on the integrated valve 13, and on a vertical projection plane, the valve body part is positioned on the radial outer side of the inner hole part. The integrated valve 13 is streamlined, a circular hole which is the same as the rocker arm 1 is formed in one end at the high position of the waterfall and is used for being connected with the shaft 3, a through groove 9 used for welding is formed in the side wall of the circular hole, the shaft 3 and the integrated valve 13 are fixedly welded at the position, and one end at the low position of the waterfall is provided with a circular characteristic which is the same as that of the valve block 5, namely a valve body part.

The integrated valve 13 is provided with a through groove 9, and the integrated valve 13 is connected with the shaft 3 at the through groove 9 in a welding mode.

The two sides of the integrated valve 13 corresponding to the through groove 9 are respectively provided with a rib 16, and the ribs 16 can effectively prevent the materials at the two end parts of the groove from being welded through.

As shown in fig. 7 and 8, a through groove 9 is formed in the integrated valve 13, a groove 15 is formed at one radial end of an end face of the integrated valve 13 on one axial side, the groove 15 can be formed by a straight line or a straight line and a slant line or a slant line, and the groove can make welding heat more concentrated on the valve body part and the shaft 3, which is beneficial to the fusion of the valve material and the shaft material and reduces the heat affected zone.

As shown in fig. 9 and 10, a through groove 9 is respectively provided on two sides of the surface of the integrated valve 13 in the radial direction, and another embodiment of the integrated valve 13 is different from the integrated valve 13 shown in fig. 7 and 8 in that: the radial two ends of the axial end surface of the integrated valve 13 are respectively provided with a groove 15. The integrated valve 13 is only composed of one part and is in a waterfall streamline shape, one end at the high position of the waterfall is provided with a circular hole which is the same as the rocker arm 1 and is used for being connected with the shaft 3, the side wall of the circular hole is provided with two through grooves 9 used for welding, and the shaft 3 and the integrated valve 13 are welded and fixed at the position; one end of the lower part of the waterfall has the same circular characteristic as the valve plate 5, and has the function of a valve.

As shown in fig. 11, the valve body structure 17 for realizing the integral action of the integral valve comprises a rocker arm 1, a valve plate 5 and a gasket 4, wherein the rocker arm 1, the valve plate 5 and the gasket 4 form an integral piece, and when in use, the integral action is realized; an inner hole of the rocker arm 1 is welded with the shaft 3 at the through groove 9, and the end surfaces of two sides of the rocker arm 1 are respectively in tight fit with the valve plate 5 and the gasket 4; the valve plate 5 is provided with a valve plate shaft 18 which is integrally connected, the valve plate shaft 18 penetrates through holes in the rocker arm 1 and the gasket 4, and the gasket 4 is arranged at the upper part of an inner hole of the rocker arm 1.

As shown in fig. 12 and 13, the valve plate shaft 18 and the spacer 4 are welded or riveted, so that the valve plate 5 loses the rotation and swing functions.

As shown in fig. 14 and 15, the valve plate shaft 18 passes through the holes of the rocker arm 1 and the gasket 4, the gasket 4 is arranged at the upper part of the rocker arm 1, the valve plate shaft 18 is in interference connection with the hole of the rocker arm 1, and the gasket 4 is fixed with the valve plate shaft 18 into a whole by welding or riveting, so that the valve plate 5 also loses the rotating and swinging functions.

Claims

1. The utility model provides a balanced valve body structure that booster was used, includes volute (11), is equipped with balanced chamber (12) in the runner of volute (11), its characterized in that: a first bush (8) and a second bush (10) are respectively fixed on two axial sides of the inner wall of the balance cavity (12), a shaft (3) is arranged in the first bush (8) and the second bush (10) in a rotating fit manner, and an integrated valve (13) is arranged in the balance cavity (12) and is fixedly connected with the shaft (3);

two ends of the shaft (3) extend out of the outer side of the volute (11), one end of the shaft (3) extending out of the volute (11) is connected with the connecting rod assembly (7), and the other end of the shaft (3) extending out of the volute (11) is sleeved with the retainer ring (14);

the integrated valve (13) integrally acts when working.

2. The balance valve body structure for supercharger application according to claim 1, wherein: integrative valve (13) are the one-piece, integrative valve (13) through the hole and axle (3) fixed connection that set up, form circular shape valve body portion on keeping away from the valve body that sets up the hole part on integrative valve (13), on vertical projection face, valve body position is in the radial outside of inner bore portion.

3. The balance valve body structure for supercharger application according to claim 2, wherein: the integrated valve (13) is provided with a through groove (9), and the integrated valve (13) is connected with the shaft (3) in a welding mode at the through groove (9).

4. A balance valve body structure for supercharger applications according to claim 3, wherein: ribs (16) are respectively arranged on the two sides of the integrated valve (13) corresponding to the through grooves (9).

5. A balance valve body structure for supercharger applications according to claim 3, wherein: the integrated valve (13) is provided with a through groove (9) or the two radial sides of the surface of the integrated valve (13) are respectively provided with a through groove (9).

6. The balance valve body structure for supercharger application according to claim 1, wherein: and a groove (15) is arranged at one radial end of the end face of one axial side of the integrated valve (13).

7. The balance valve body structure for supercharger application according to claim 1, wherein: and bevels (15) are respectively arranged at the radial two ends of the end face of one axial side of the integrated valve (13).

8. The balance valve body structure for supercharger application according to claim 1, wherein: the integrated valve (13) adopts an integrally-acting valve body structure (17) and comprises a rocker arm (1), a valve plate (5) and a gasket (4), an inner hole of the rocker arm (1) is welded with a shaft (3) at a through groove (9), and the end surfaces of two sides of the rocker arm (1) are respectively in tight fit with the valve plate (5) and the gasket (4); the valve plate (5) is provided with a valve plate shaft (18) which is integrally connected, the valve plate shaft (18) penetrates through holes in the rocker arm (1) and the gasket (4), and the gasket (4) is arranged on the upper portion of an inner hole of the rocker arm (1).

9. The balance valve body structure for supercharger applications according to claim 8, wherein: the valve plate shaft (18) and the gasket (4) are welded or riveted.