Sealing structure for turbocharger

Abstract

The utility model discloses a sealing structure for a turbocharger. The sealing structure comprises a shaft sleeve, a sealing ring and an air sealing ring, wherein the shaft sleeve is arranged on a rotor shaft of the turbocharger in a sleeving manner; the shaft sleeve is detachably and fixedly installed on the rotor shaft, a first ring groove is formed in the shaft sleeve, an inner ring of the sealing ring is located in the first ring groove, and an outer ring of the sealing ring is matched with the air sealing ring; an inner ring of the sealing ring comprises a first reducing pipe face, the large-diameter end of the first reducing pipe face is connected to the end face, facing an oil cavity of the turbocharger, of the sealing ring, the small-diameter end of the first reducing pipe face is far away from the oil cavity, and the end face, facing the oil cavity of the turbocharger, of the sealing ring abuts against the edge of the inner wall, facing the oil cavity, of a notch of the first ring groove. The first reducing pipe face is arranged, so that the end face, facing the oil cavity of the turbocharger, of the sealing ring only abuts against the inner wall edge, facing the oil cavity, of the notch of the first ring groove, the contact area is reduced, the reliability of the sealing structure can be improved, the service life of the sealing ring is prolonged, and the maintenance cost is reduced.

Description

TECHNICAL FIELD

[0001] The utility model relates to turbocharger technical field especially relates to a sealing structure for turbocharger. BACKGROUND

[0002] The turbocharger oil gas seal is very important to the reliability of turbocharger, and the sealing form is usually labyrinth and sealing ring contact type sealing. The radial flow turbocharger is limited by the compact structure, and the diesel engine manufacturers have strict requirements on the pressure in the crankcase when designing the diesel engine. In order to avoid the pressure in the crankcase exceeding the limit, the turbocharger usually adopts the sealing ring type sealing structure. The side end face of the existing structure sealing ring is a plane, and the thickness of the sealing ring becomes thinner with the increase of the wear amount. The sealing ring needs to be replaced when the wear is greater than 0.5mm, and the service life is short, which cannot meet the requirements of modern diesel engine strengthening, power improvement and long period maintenance life. SUMMARY

[0003] The utility model provides a sealing structure for turbocharger to solve above -mentioned technical problem.

[0004] In order to realize the above purpose, the technical scheme of the utility model is:

[0005] A sealing structure for turbocharger, comprising: a shaft sleeve sleeved on the rotor shaft of the turbocharger, a sealing ring and a gas seal ring;The shaft sleeve is detachably fixedly installed on the rotor shaft, a first ring groove is formed in the shaft sleeve, the inner ring of the sealing ring is located in the first ring groove, and the outer ring of the sealing ring is matched with the gas seal ring;The inner ring of the sealing ring comprises a first reducing pipe face, the large diameter end of the first reducing pipe face is connected to the end face of the sealing ring facing the oil cavity of the turbocharger, and the small diameter end of the first reducing pipe face is away from the oil cavity, and the end face of the sealing ring facing the oil cavity of the turbocharger is abutted against the inner wall edge of the slot opening of the first ring groove facing the oil cavity.

[0006] Preferably, along the radial direction of the first ring groove: the size of the part, where the end face of the sealing ring facing the oil cavity of the turbocharger is abutted against the inner wall edge of the slot opening of the first ring groove facing the oil cavity, is 0.2-0.4mm.

[0007] Preferably, the size of the first reducing pipe face along the axis direction of the rotor shaft is greater than or equal to 1.0mm.

[0008] Preferably, the inner ring of the sealing ring further comprises a second reducing pipe face, the large diameter end of the second reducing pipe face is connected to the end face of the sealing ring away from the oil cavity of the turbocharger, and the small diameter end of the second reducing pipe face faces the oil cavity.

[0009] Preferably, the first reducing pipe face and the second reducing pipe face are symmetrically arranged.

[0010] Preferably, the average of the sum of the sizes of the first and second reducers along the axial direction of the rotor shaft is greater than or equal to 1.0 mm.

[0011] Preferably, the shaft sleeve is interference fitted on the rotor shaft, and the interference fit of the rotor shaft with the shaft sleeve is controlled in the range of 0.05-0.08 mm for the rotor shaft with a diameter in the range of 30-50 mm.

[0012] Preferably, the shaft sleeve and the rotor shaft are made of the same material.

[0013] Preferably, the inner ring of the gas seal ring comprises a locating section and a fitting section, the locating section is located on the side of the first reducer facing the oil cavity of the turbocharger, and the inner diameter of the locating section is smaller than that of the fitting section; the end face of the sealing ring facing the oil cavity of the turbocharger abuts against the stepped surface formed by the locating section and the fitting section, and the outer periphery of the sealing ring cooperates with the inner wall of the fitting section.

[0014] Preferably, a second ring groove is formed on the fitting section, the groove bottom of the second ring groove is arc-shaped and tangent to the stepped surface formed by the locating section and the fitting section on one side, and the other side of the groove bottom of the second ring groove is connected with a slope extending to the inner wall of the fitting section and tangent to the slope.

[0015] Advantages:

[0016] The sealing structure for turbocharger disclosed in the present application greatly reduces the contact area by setting the first reducer so that the end face of the sealing ring facing the oil cavity of the turbocharger only abuts against the inner wall edge of the groove opening of the first ring groove, compared with the original structure in which the entire end face of the sealing ring contacts with the inner wall of the ring groove, the sealing pressure of the sealing surface is improved, the high oil pressure and high temperature lubricating oil are better sealed, and the contact area gradually increases to the conventional contact sealing after the sealing ring is worn during operation, which can improve the reliability of the sealing structure, prolong the service life of the sealing ring, and reduce the maintenance cost. BRIEF DESCRIPTION OF DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed in the following embodiment or prior art description will be briefly introduced. Obviously, the drawings in the following description are some embodiments of the present application, and those skilled in the art can also obtain other drawings according to these drawings without creative labor.

[0018] Figure 1 The structure diagram of the sealing structure for turbocharger disclosed in the present application is shown in the figure.

[0019] Figure 2 The structure diagram of the sealing structure for turbocharger disclosed in the present application is shown in the figure. Figure 1 The local enlarged view of A in the figure.

[0020] Figure 3 It is the first kind of sealing ring structure schematic view of the sealing structure of a turbocharger.

[0021] Figure 4 It is the second kind of sealing ring structure schematic view of the sealing structure of a turbocharger.

[0022] 1, shaft sleeve; 11, first ring groove; 2, sealing ring; 21, first reducing pipe surface; 22, second reducing pipe surface; 3, gas seal ring; 31, positioning section; 32, matching section; 321, second ring groove; 4, rotor shaft; 5, turbine. DETAILED DESCRIPTION

[0023] In order to make the purpose, technical scheme and advantages of the embodiments of the utility model clearer, the technical scheme in the embodiments of the utility model will be clearly and completely described below in combination with the drawings in the embodiments of the utility model. Obviously, the described embodiments are part of the embodiments of the utility model, rather than all the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by those skilled in the art without creative labor fall within the protection scope of the utility model.

[0024] A sealing structure of a turbocharger, in combination with Figure 1 , Figure 2 , Figure 3 and Figure 4 , comprises a shaft sleeve 1, a sealing ring 2 and a gas seal ring 3 sleeved on a rotor shaft 4 of a turbocharger; the shaft sleeve 1 is detachably fixedly installed on the rotor shaft 4, the shaft sleeve 1 is provided with a first ring groove 11, the inner ring of the sealing ring 2 is located in the first ring groove 11, and the outer ring of the sealing ring 2 cooperates with the gas seal ring 3; the inner ring of the sealing ring 2 comprises a first reducing pipe surface 21, the large-diameter end of the first reducing pipe surface 21 is connected to the end surface of the sealing ring 2 facing the oil cavity of the turbocharger, the small-diameter end of the first reducing pipe surface 21 is away from the oil cavity, and the end surface of the sealing ring 2 facing the oil cavity of the turbocharger abuts against the inner wall edge of the slot opening of the first ring groove 11 facing the oil cavity. The application avoids the direct contact between the whole end surface of the original sealing ring with a rectangular cross section and the inner wall of the ring groove, greatly reduces the contact area, improves the sealing pressure of the sealing surface, has a better sealing effect on high-pressure and high-temperature lubricating oil, and gradually increases the contact area of the sealing ring 2 after running and wearing to become a conventional contact sealing, so that the reliability of the sealing structure is improved, the service life of the sealing ring 2 is prolonged, and the maintenance cost is reduced.

[0025] Meanwhile, the sleeve 1 avoids the sealing ring 2 being directly installed on the rotor shaft 4, so that the contact surface of the sealing ring 2 and the rotor shaft 4 is worn and deformed, thereby avoiding large cost waste caused by the rotor shaft 4 being unable to be repaired.

[0026] Preferably, in the radial direction of the first ring groove 11: the size of the end surface of the sealing ring 2 towards the oil cavity of the turbocharger and the abutting part of the inner wall edge of the groove opening of the first ring groove 11 towards the oil cavity is 0.2-0.4 mm. That is, in the initial installation state, the width of the contact surface of the end surface of the sealing ring 2 towards the oil cavity of the turbocharger and the inner wall edge of the groove opening of the first ring groove 11 is ensured to be within the range of 0.2-0.4 mm. In the rotating process, under the action of the high-temperature gas, the end surface of the sealing ring 2 towards the oil cavity of the turbocharger is kept pressed against the inner wall edge of the groove opening of the first ring groove 11 and a smaller contact area is ensured, so that the sealing pressure is ensured and a better sealing effect is achieved.

[0027] Preferably, the size of the first reducing pipe surface 21 in the axial direction of the rotor shaft 4 is greater than or equal to 1.0 mm, that is, H1-H2≥1.0 mm, H1 represents the axial size of the sealing ring 2, and H2 represents the axial size of the center hole of the sealing ring 2; it is ensured that after the end surface of the sealing ring 2 is worn to gradually increase the contact area, the conventional contact sealing can still be achieved, so that it can still work reliably after the wear is greater than 0.5 mm.

[0028] Preferably, the inner ring of the sealing ring 2 further comprises a second reducing pipe surface 22, the large-diameter end of the second reducing pipe surface 22 is connected to the end surface of the sealing ring 2 away from the oil cavity of the turbocharger, and the small-diameter end of the second reducing pipe surface 22 is towards the oil cavity. When the end surface of the sealing ring 2 corresponding to the first reducing pipe surface 21 is worn too much, the sealing ring 2 can be adjusted, and the end surface of the sealing ring 2 away from the oil cavity of the turbocharger (that is, the end surface of the sealing ring 2 corresponding to the second reducing pipe surface 22) is abutted against the inner wall edge of the groove opening of the first ring groove 11 towards the oil cavity.

[0029] Preferably, the first reducing pipe surface 21 and the second reducing pipe surface 22 are symmetrically arranged, so that the sealing ring 2 does not need to be distinguished as front and back during installation, facilitating installation and debugging; and facilitating replacement during maintenance.

[0030] Preferably, the average value of the sum of the sizes of the first reducing pipe surface 21 and the second reducing pipe surface 22 in the axial direction of the rotor shaft 4 is greater than or equal to 1.0 mm, that is, (H3-H4) / 2≥1.0 mm, H3 represents the axial size of the sealing ring 2, and H4 represents the axial size of the center hole of the sealing ring 2; it is ensured that after the end surface of the sealing ring 2 is worn to gradually increase the contact area, the conventional contact sealing can still be achieved, so that it can still work reliably after the wear is greater than 0.5 mm.

[0031] Specifically, the first and second reducers 21 and 22 can be selected from a ring segment of a quadratic cone, an elliptical paraboloid, a double-leaf hyperboloid, a single-leaf hyperboloid, an ellipsoid, and a spherical surface, such that the contact area of the end face of the sealing ring 2 gradually increases after wear.

[0032] Preferably, the shaft sleeve 1 is interference-fitted on the rotor shaft 4, and the interference amount is controlled within the range of 0.05-0.08 mm for the rotor shaft 4 with a diameter within the range of 30-50 mm and the shaft sleeve 1. After long-term use, the deformed shaft sleeve 1 due to wear can be removed and replaced with a new one, thereby ensuring the sealing effect and prolonging the service life of the rotor shaft 4.

[0033] Preferably, the shaft sleeve 1 and the rotor shaft 4 are made of the same material, so that they have the same expansion coefficient and avoid loosening after being heated.

[0034] Specifically, the rotor shaft 4 is butted against the mandrel of the turbine 5 and fixedly connected through friction welding, and the shaft sleeve 1 is sleeved on the connection between the rotor shaft 4 and the mandrel of the turbine 5, and a step is machined on the mandrel of the turbine 5 to position the shaft sleeve 1. This structure design reduces the diameter of the position where the rotor shaft 4 and the mandrel of the turbine 5 need to be welded, which is beneficial to improve the reliability of friction welding.

[0035] Specifically, the outer diameter of the shaft sleeve 1 is less than or equal to the outer diameter of the step on the mandrel of the turbine 5, which avoids the shaft sleeve 1 protruding from the step on the mandrel and being directly affected by high-temperature gas to expand, thereby avoiding the shaft sleeve 1 loosening due to the increased temperature difference with the rotor shaft 4.

[0036] Preferably, the inner ring of the gas seal ring 3 includes a positioning segment 31 and a matching segment 32, the positioning segment 31 is located on the side of the first reducer 21 facing the oil cavity of the turbocharger, and the inner diameter of the positioning segment 31 is smaller than that of the matching segment 32; the end face of the sealing ring 2 facing the oil cavity of the turbocharger abuts against the stepped surface formed by the positioning segment 31 and the matching segment 32, and the outer periphery of the sealing ring 2 matches the inner wall of the matching segment 32; the position of the sealing ring 2 is ensured, and the end face of the sealing ring 2 facing the oil cavity of the turbocharger and the inner wall edge of the slot opening of the first ring groove 11 facing the oil cavity, and the stepped surface formed by the end face of the sealing ring 2 facing the oil cavity of the turbocharger and the positioning segment 31 and the matching segment 32 are reliably contacted.

[0037] Preferably, the matching segment 32 is provided with a second ring groove 321, the groove bottom of the second ring groove 321 is arc-shaped and one side is tangent to the stepped surface formed by the positioning segment 31 and the matching segment 32, and the other side of the groove bottom of the second ring groove 321 is connected with an inclined surface extending to the inner wall of the matching segment 32 and tangent to the inclined surface. The second ring groove 321 clears the root of the stepped surface formed by the positioning segment 31 and the matching segment 32, and ensures that the end face of the sealing ring 2 facing the oil cavity of the turbocharger and the stepped surface formed by the positioning segment 31 and the matching segment 32 can be tightly contacted.

[0038] Finally, it should be noted that the above examples are intended to illustrate the technical solutions of the present application, but not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that they can still modify the technical solutions recorded in the foregoing embodiments, or make equivalent substitutions for part or all of the technical features; and these modifications or substitutions do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application.

Claims

1. A seal structure for a turbocharger, characterized by, The application relates to a turbocharger rotor shaft sleeve (1), a sealing ring (2) and an air seal ring (3) which are arranged on a turbocharger rotor shaft (4); the sleeve (1) is detachably fixed on the rotor shaft (4), a first ring groove (11) is formed in the sleeve (1), the inner ring of the sealing ring (2) is located in the first ring groove (11), and the outer ring of the sealing ring (2) is matched with the air seal ring (3); the inner ring of the sealing ring (2) comprises a first reducing pipe face (21), the large-diameter end of the first reducing pipe face (21) is connected to the end face of the sealing ring (2) facing the oil cavity of the turbocharger, the small-diameter end of the first reducing pipe face (21) is away from the oil cavity, and the end face of the sealing ring (2) facing the oil cavity of the turbocharger is abutted against the inner wall edge of the slot opening of the first ring groove (11) facing the oil cavity. In the radial direction of the first ring groove (11), the abutting part of the end face of the sealing ring (2) facing the oil cavity of the turbocharger and the inner wall edge of the slot opening of the first ring groove (11) facing the oil cavity has a size of 0.2-0.4 mm.

2. The seal arrangement for a turbocharger as set forth in claim 1, wherein The size of the first reducing pipe face (21) in the axial direction of the rotor shaft (4) is greater than or equal to 1.0 mm.

3. The seal arrangement for a turbocharger as set forth in claim 1, wherein, The inner ring of the sealing ring (2) further comprises a second reducing pipe face (22), the large-diameter end of the second reducing pipe face (22) is connected to the end face of the sealing ring (2) away from the oil cavity of the turbocharger, and the small-diameter end of the second reducing pipe face (22) faces the oil cavity.

4. The seal arrangement for a turbocharger as set forth in claim 1, wherein, The first reducing pipe face (21) and the second reducing pipe face (22) are symmetrically arranged.

5. The seal arrangement for a turbocharger as set forth in claim 4, wherein The average value of the sum of the sizes of the first reducing pipe face (21) and the second reducing pipe face (22) in the axial direction of the rotor shaft (4) is greater than or equal to 1.0 mm.

6. A seal arrangement for a turbocharger according to claim 4 or 5, characterised in that The sleeve (1) is interference-fitted on the rotor shaft (4), and for the rotor shaft (4) with a diameter in the range of 30-50 mm, the interference amount of the cooperation between the rotor shaft (4) and the sleeve (1) is controlled in the range of 0.05-0.08 mm.

7. The seal arrangement for a turbocharger as set forth in claim 1, wherein, The sleeve (1) and the rotor shaft (4) are made of the same material.

8. The seal arrangement for a turbocharger as set forth in claim 1, wherein, The inner ring of the air seal ring (3) comprises a positioning section (31) and a cooperation section (32), the positioning section (31) is located on the side of the first reducing pipe face (21) facing the oil cavity of the turbocharger, the inner diameter of the positioning section (31) is smaller than that of the cooperation section (32), the end face of the sealing ring (2) facing the oil cavity of the turbocharger is abutted against the stepped face formed by the positioning section (31) and the cooperation section (32), and the outer periphery of the sealing ring (2) is matched with the inner wall of the cooperation section (32).

9. The seal arrangement for a turbocharger as set forth in claim 1, wherein, A second ring groove (321) is formed in the cooperation section (32), the groove bottom of the second ring groove (321) is arc-shaped, one side of the groove bottom is tangent to the stepped face formed by the positioning section (31) and the cooperation section (32), and the other side of the groove bottom is connected with an inclined surface extending to the inner wall of the cooperation section (32) and tangent to the inclined surface.

10. The seal arrangement for a turbocharger as set forth in claim 9, wherein, ​

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