Novel turbocharger

Abstract

The invention discloses a novel turbocharger, which relates to the technical field of turbochargers, and comprises a middle body, a rotor shaft, a rotor shaft, a rotor shaft sleeve and a rotor shaft sleeve, the gas compressor shell is connected with the middle body, and a gas compressor impeller connected with the rotor shaft is arranged in the gas compressor shell; the turbine shell is connected with the middle body, and a turbine connected with the rotor shaft is arranged in the turbine shell; wherein the gas compressor shell and the turbine shell are located on the two sides of the middle body, a turbine end floating bearing is arranged at the end, close to the turbine, of the rotor shaft, a pressing end sliding bearing is arranged at the end, close to the gas compressor impeller, of the rotor shaft, the middle body is further connected with an oil drainage guide thrust bearing, and the oil drainage guide thrust bearing and the pressing end sliding bearing form a single-layer oil film. According to the novel turbocharger, the bearing stress can be reduced by increasing the bearing span, and the shafting stability is improved. A single-layer oil film support is formed by the oil drainage guide thrust bearing and the pressure end sliding bearing, so that the friction efficiency loss of the bearing is reduced, and the mechanical efficiency of the supercharger is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of turbochargers, and in particular to a novel turbocharger. Background Art

[0002] As a critical engine subsystem, the turbocharger can improve engine power output and reduce fuel consumption and emissions. The compression-end plain bearing is the one closest to the compressor, while the turbine-end plain bearing is the one closest to the turbine. Due to the limited space constraints of the turbocharger, the distance between the two bearings (the bearing span) cannot be increased. A short bearing span design can lead to problems such as speed coupling, concentrated bearing loads, and reduced system damping. Furthermore, the turbine wheel of a turbocharger is typically slightly smaller than the compressor wheel. However, due to the high operating temperatures (above 600°C) of the turbine, the turbine wheel is typically made of a high-nickel alloy, while the compressor wheel is typically made of an aluminum alloy. The significant density difference between the two materials results in higher stresses on the turbine-end plain bearing, closer to the turbine, while lower stresses are experienced on the compression-end plain bearing, closer to the compressor. To accommodate the higher stresses on the turbine-end plain bearing, floating bearings are often used for both the turbine and compression-end bearings. However, although the floating bearing has greater damping force and better vibration resistance, its double-layer oil film will produce more friction loss.

[0003] Therefore, there are still shortcomings and deficiencies in the existing technology. How to provide a new turbocharger with high shaft stability and low friction loss is a technical problem that needs to be solved urgently by those skilled in the art. Summary of the Invention

[0004] The purpose of the present invention is to provide a novel turbocharger, which solves the technical problems of the existing turbocharger with short bearing span design, resulting in concentrated bearing load, poor shafting stability and high friction loss.

[0005] To achieve the above object, the present invention provides a novel turbocharger, comprising:

[0006] An intermediate body, internally provided with a rotor shaft for rotation;

[0007] A compressor casing connected to the intermediate body, and provided with a compressor impeller connected to the rotor shaft;

[0008] a turbine housing connected to the intermediate body and provided with a turbine connected to the rotor shaft;

[0009] Among them, the compressor housing and the turbine housing are located on both sides of the intermediate body, the rotor shaft is provided with a turbine end floating bearing at one end close to the turbine, and the rotor shaft is provided with a pressure end sliding bearing at one end close to the compressor impeller. The intermediate body is also connected to an oil leakage guide thrust bearing, and the oil leakage guide thrust bearing and the pressure end sliding bearing form a single layer of oil film.

[0010] Preferably, the intermediate body is provided with an oil inlet, a first oil guide channel is further provided inside the intermediate body, the oil leakage guide thrust bearing is provided with an oil inlet channel, and the oil inlet channel is connected with the oil inlet through the first oil guide channel.

[0011] Preferably, the rotor shaft is further provided with an oil leakage guide seal, and the oil leakage guide seal is located between the compressor impeller and the compression end sliding bearing.

[0012] Preferably, the end surface of the oil leakage guide shaft seal, the inner wall of the intermediate body, and the end surface of the oil leakage guide thrust bearing jointly define a first oil leakage chamber.

[0013] Preferably, the oil drain guide shaft seal outer shell is provided with a wear-resistant seal, one side of the wear-resistant seal is interference fit with the oil drain guide shaft seal, and the other side is used to partially seal the first oil drain chamber.

[0014] Preferably, the wear-resistant seal is a wear-resistant rubber sleeve.

[0015] Preferably, a sealing ring sleeve is further provided in the intermediate body, and the sealing ring sleeve is located between the compressor impeller and the oil drain guide shaft seal.

[0016] Preferably, the end surface of the sealing ring seat, the inner wall of the intermediate body, and the end surface of the oil leakage guide shaft seal jointly define a second oil leakage chamber.

[0017] Preferably, a sealing ring is provided between the oil drain guide shaft seal and the sealing ring seat.

[0018] Preferably, a second oil guiding channel is further provided inside the intermediate body, one end of the second oil guiding channel is communicated with the oil inlet, and an outlet at the other end is arranged toward one side of the vortex end floating bearing.

[0019] Compared to the aforementioned background technology, the novel turbocharger provided by the present invention features a turbine-end floating bearing and a compression-end sliding bearing, respectively, located at the rotor shaft end near the turbine and the compressor impeller. The oil-drain guide thrust bearing is directly integrated into the intermediate body, replacing the traditional dedicated thrust bearing located at one end of the turbine. This effectively avoids occupying axial space, freeing up axial space and increasing the span between the compression-end sliding bearing and the turbine-end floating bearing, thereby reducing bearing stress and improving shaft system stability. The oil-drain guide thrust bearing and the compression-end sliding bearing form a single-layer oil film support, which, compared to the double-layer oil film used when floating bearings are used, reduces bearing friction efficiency losses, avoids excessive friction losses, and improves the mechanical efficiency of the turbocharger. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0021] Figure 1 A schematic cross-sectional view of a novel turbocharger provided by an embodiment of the present invention;

[0022] Figure 2 for Figure 1 An enlarged view of the part A in the new turbocharger shown.

[0023] Figures 1 to 2 Reference numerals in the accompanying drawings: 1. intermediate body; 101. oil inlet; 102. oil return port; 103. first oil guide channel; 104. second oil guide channel; 2. compressor casing; 201. compressor impeller; 3. turbine casing; 301. turbine; 4. rotor shaft; 401. turbine end floating bearing; 402. compression end sliding bearing; 5. oil leakage guide thrust bearing; 501. oil inlet channel; 6. oil leakage guide shaft seal; 601. first oil leakage chamber; 602. second oil leakage chamber; 603. wear-resistant seal; 604. first protrusion; 7. sealing ring sleeve; 701. sealing ring; 702. second protrusion. DETAILED DESCRIPTION

[0024] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0025] In order to enable those skilled in the art to better understand the solutions of the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0026] The present invention provides a novel turbocharger with strong shaft system stability and low bearing friction loss, and can solve the problem of easy oil leakage of the turbocharger when the engine is idling for a long time, running without load or at low temperature.

[0027] Please refer to Figures 1 to 2 The novel turbocharger provided by the present invention comprises:

[0028] The intermediate body 1 has a rotor shaft 4 rotating inside;

[0029] The compressor housing 2 is connected to the intermediate body 1 and has a compressor impeller 201 connected to the rotor shaft 4 inside;

[0030] The turbine housing 3 is connected to the intermediate body 1 and has a turbine 301 connected to the rotor shaft 4 inside;

[0031] Among them, the compressor housing 2 and the turbine housing 3 are located on both sides of the intermediate body 1. The end of the rotor shaft 4 close to the turbine 301 is provided with a turbine end floating bearing 401, and the end of the rotor shaft 4 close to the compressor impeller 201 is provided with a pressure end sliding bearing 402. The intermediate body 1 is also connected to an oil leakage guide thrust bearing 5, and the oil leakage guide thrust bearing 5 and the pressure end sliding bearing 402 form a single layer of oil film.

[0032] The intermediate body 1 is located between the compressor housing 2 and the turbine housing 3. The rotor shaft 4 rotates within the intermediate body 1. The turbine floating bearing 401 and the compressor sliding bearing 402 are located at the ends of the rotor shaft 4 near the turbine 301 and the compressor impeller 201, respectively. The oil leakage guide thrust bearing 5 is directly integrated into the intermediate body 1, replacing the dedicated thrust bearing traditionally located at one end of the turbine 301. This effectively avoids occupying axial space, freeing up axial space, and increasing the span between the compressor sliding bearing 402 and the turbine floating bearing 401, reducing bearing stress and improving shaft system stability. Furthermore, the oil leakage guide thrust bearing 5 and the compressor sliding bearing 402 form a single-layer oil film support, reducing bearing friction efficiency losses and improving the mechanical efficiency of the supercharger.

[0033] With such an arrangement, while retaining the turbine end floating bearing 401 to provide higher load-bearing capacity and damping force to maintain the stability of the shaft system, the span between the pressure end sliding bearing 402 and the turbine end floating bearing 401 is increased, thereby avoiding the problems of bearing stress concentration and bearing instability caused by a short span; the oil leakage guide thrust bearing 5 and the pressure end sliding bearing 402 are used to form a single-layer oil film support, thereby reducing the loss of bearing friction efficiency and avoiding the generation of more friction losses.

[0034] In some embodiments, please refer to Figures 1 to 2 The intermediate body 1 is provided with an oil inlet 101 , and a first oil guide channel 103 is also provided inside the intermediate body 1 . The oil leakage guide thrust bearing 5 is provided with an oil inlet channel 501 , and the oil inlet channel 501 is connected to the oil inlet 101 through the first oil guide channel 103 .

[0035] In addition, the intermediate body 1 is further provided with an oil return port 102 , which is located on a side of the intermediate body 1 away from the oil inlet 101 .

[0036] During lubrication, engine oil is added to the interior of the intermediate body 1 through the oil inlet 101. The engine oil enters the oil inlet channel 501 provided in the oil leakage guide thrust bearing 5 through the first oil guide channel 103. The engine oil enters between the oil leakage guide thrust bearing 5 and the pressure end sliding bearing 402 through the above-mentioned oil inlet channel 501. The oil leakage guide thrust bearing 5 and the pressure end sliding bearing 402 form a single-layer oil film. Compared with the double-layer oil film when using a floating bearing, it can reduce friction loss and improve the mechanical efficiency of the supercharger.

[0037] In some embodiments, please refer to Figures 1 to 2 The rotor shaft 4 is further provided with an oil leakage guide seal 6 , which is located between the compressor impeller 201 and the compression end sliding bearing 402 .

[0038] Attach Figure 2 When the up, down, left and right directions in FIG. 1 are used as an example for explanation, the oil leakage guide shaft seal 6 and the pressure end sliding bearing 402 are respectively located on the left and right sides of the oil leakage guide thrust bearing 5 .

[0039] In some embodiments, please refer to Figures 1 to 2 The end surface of the oil leakage guide shaft seal 6 , the inner wall of the intermediate body 1 , and the end surface of the oil leakage guide thrust bearing 5 jointly define a first oil leakage chamber 601 .

[0040] When the turbocharger is idling, unloaded, or running at low temperature for a long time, the end face of the oil drain guide seal 6, the inner wall of the intermediate body 1, and the end face of the oil drain guide thrust bearing 5 form a first oil drain chamber 601 away from the compressor impeller 201, guiding the oil in the return direction to prevent oil leakage.

[0041] In some embodiments, please refer to Figures 1 to 2 The outer shell of the oil leakage guide shaft seal 6 is provided with a wear-resistant seal 603. One side of the wear-resistant seal 603 is interference fit with the oil leakage guide shaft seal 6, and the other side is used to partially seal the first oil leakage chamber 601.

[0042] One side of the wear-resistant seal 603 is sleeved on the oil leakage guide shaft seal 6 and has an interference fit with the oil leakage guide shaft seal 6. The other side of the wear-resistant seal 603 is a free section. When the engine runs at high speed, the above-mentioned free section will expand outward due to the centrifugal effect at high speed. The free section of the wear-resistant seal 603 fits with the inner end surface of the intermediate body 1, so that a relative seal is formed between the free section of the wear-resistant seal 603 and the inner end surface of the intermediate body 1, thereby partially closing the first oil leakage chamber 601 and preventing oil from leaking to the side of the compressor impeller 201.

[0043] In some embodiments, please refer to Figures 1 to 2 , the wear-resistant seal 603 is a wear-resistant rubber sleeve.

[0044] In some embodiments, please refer to Figures 1 to 2 A sealing ring sleeve seat 7 is also provided in the intermediate body 1 , and the sealing ring sleeve seat 7 is located between the compressor impeller 201 and the oil drain guide shaft seal 6 .

[0045] In some embodiments, please refer to Figures 1 to 2 The end surface of the sealing ring seat 7, the inner wall of the intermediate body 1, and the end surface of the oil leakage guide shaft seal 6 jointly define a second oil leakage chamber 602.

[0046] The end face of the sealing ring sleeve 7, the inner wall of the intermediate body 1 and the end face of the oil drain guide shaft seal 6 form a second oil drain chamber 602. By setting up the second oil drain chamber 602, the residual oil that breaks through the first oil drain chamber 601 can be intercepted. The second oil drain chamber 602 and the first oil drain chamber 601 form a stepped sealing defense line, effectively preventing oil leakage.

[0047] In addition, the oil leakage guide shaft seal 6 is provided with a first protrusion 604 facing the side of the sealing ring sleeve 7, and the sealing ring sleeve 7 is provided with a second protrusion 702 facing the side of the first protrusion 604. The first protrusion 604 and the second protrusion 702 are located in the second oil leakage chamber 602, and a maze structure is formed in the second oil leakage chamber 602 through the first protrusion 604 and the second protrusion 702.

[0048] In this way, the labyrinth structure can extend the leakage path, achieve the effect of non-contact sealing, and further avoid oil leakage.

[0049] In some embodiments, please refer to Figures 1 to 2 A sealing ring 701 is provided between the oil drain guide seal 6 and the sealing ring seat 7. Specifically, the sealing ring 701 can be mounted on and fixed to the oil drain guide seal 6. The provision of the sealing ring 701 creates a relative seal between the oil drain guide seal 6 and the sealing ring seat 7, preventing the oil in the second oil drain chamber 602 from leaking toward the compressor impeller 201.

[0050] In some embodiments, please refer to Figures 1 to 2 A second oil guide channel 104 is further provided inside the intermediate body 1 . One end of the second oil guide channel 104 is connected to the oil inlet 101 , and the outlet of the other end is arranged toward the side of the vortex end floating bearing 401 .

[0051] During lubrication, engine oil is added into the intermediate body 1 through the oil inlet 101 , and the engine oil flows to the vortex end floating bearing 401 through the outlet end of the second oil guide channel 104 , thereby lubricating the vortex end floating bearing 401 .

[0052] In the novel turbocharger provided by the present invention, the turbine end floating bearing 401 and the pressure end sliding bearing 402 are respectively arranged at one end of the rotor shaft 4 close to the turbine 301 and the end of the rotor shaft 4 close to the compressor impeller 201, and the oil leakage guide thrust bearing 5 is directly integrated on the intermediate body 1, replacing the dedicated thrust bearing traditionally arranged at one end of the turbine 301, thereby effectively avoiding occupying axial space, freeing up axial space, and increasing the span of the pressure end sliding bearing 402 and the turbine end floating bearing 401, which can reduce bearing stress and improve shaft system stability.

[0053] The oil leakage guide thrust bearing 5 and the pressure end sliding bearing 402 form a single-layer oil film support. Compared with the double-layer oil film when using a floating bearing, this reduces the loss of bearing friction efficiency, avoids generating too much friction loss, and improves the mechanical efficiency of the supercharger.

[0054] The provision of a first oil drain chamber 601 and a second oil drain chamber 602 addresses the problem of turbocharger oil leakage during prolonged engine idling, no-load operation, or low-temperature operation. The first oil drain chamber 601 directs leaking oil back into the engine, minimizing leakage. The second oil drain chamber 602 intercepts residual oil that escapes the first oil drain chamber 601. Together, the second oil drain chamber 602 and the first oil drain chamber 601 form a stepped seal, effectively preventing oil leakage.

[0055] When the engine is running at high speed, the free section on the other side of the wear-resistant seal 603 expands outward due to the centrifugal effect at high speed and fits against the inner wall of the intermediate body 1, so that a relative seal is formed between the free section of the wear-resistant seal 603 and the inner wall of the intermediate body 1, thereby partially closing the first oil drain chamber 601 and preventing oil from leaking to the side of the compressor impeller 201.

[0056] It should be noted that, in this specification, relational terms such as first and second are merely used to distinguish one entity from other entities, but do not necessarily require or imply any actual relationship or order between these entities.

[0057] The principles and implementation methods of the present invention are described herein using specific examples. The description of the above examples is only intended to help understand the method and core concept of the present invention. It should be noted that those skilled in the art may make various improvements and modifications to the present invention without departing from the principles of the present invention, and such improvements and modifications also fall within the scope of protection of the present invention.

Claims

1. A new type of turbocharger, characterized in that: include: An intermediate body (1) having a rotor shaft (4) rotating therein; A compressor housing (2) connected to the intermediate body (1) and provided with a compressor impeller (201) connected to the rotor shaft (4); a turbine housing (3), connected to the intermediate body (1), and provided with a turbine (301) connected to the rotor shaft (4); The compressor housing (2) and the turbine housing (3) are located on both sides of the intermediate body (1); a turbine end floating bearing (401) is provided at one end of the rotor shaft (4) close to the turbine (301); a pressure end sliding bearing (402) is provided at one end of the rotor shaft (4) close to the compressor impeller (201); and an oil leakage guide thrust bearing (5) is further connected to the intermediate body (1); the oil leakage guide thrust bearing (5) and the pressure end sliding bearing (402) form a single layer of oil film.

2. The novel turbocharger according to claim 1, characterized in that: The intermediate body (1) is provided with an oil inlet (101), a first oil guide channel (103) is further provided inside the intermediate body (1), the oil leakage guide thrust bearing (5) is provided with an oil inlet channel (501), and the oil inlet channel (501) is communicated with the oil inlet (101) through the first oil guide channel (103).

3. The novel turbocharger according to claim 2, characterized in that: The rotor shaft (4) is further provided with an oil leakage guide shaft seal (6), and the oil leakage guide shaft seal (6) is located between the compressor impeller (201) and the compression end sliding bearing (402).

4. The novel turbocharger according to claim 3, characterized in that: The end surface of the oil leakage guide shaft seal (6), the inner wall of the intermediate body (1), and the end surface of the oil leakage guide thrust bearing (5) jointly define a first oil leakage chamber (601).

5. The novel turbocharger according to claim 4, characterized in that: The outer shell of the oil drain guide shaft seal (6) is provided with a wear-resistant seal (603), one side of the wear-resistant seal (603) is interference-fitted with the oil drain guide shaft seal (6), and the other side is used to partially seal the first oil drain chamber (601).

6. The novel turbocharger according to claim 5, characterized in that: The wear-resistant sealing element (603) is a wear-resistant rubber sleeve.

7. The novel turbocharger according to claim 5, characterized in that: A sealing ring seat (7) is also provided in the intermediate body (1), and the sealing ring seat (7) is located between the compressor impeller (201) and the oil drain guide shaft seal (6).

8. The novel turbocharger according to claim 7, characterized in that: The end surface of the sealing ring seat (7), the inner wall of the intermediate body (1), and the end surface of the oil leakage guide shaft seal (6) jointly define a second oil leakage chamber (602).

9. The novel turbocharger according to claim 7, characterized in that: A sealing ring (701) is provided between the oil drain guide shaft seal (6) and the sealing ring sleeve (7).

10. The novel turbocharger according to claim 2, characterized in that: A second oil guide channel (104) is further provided inside the intermediate body (1), one end of the second oil guide channel (104) is connected to the oil inlet (101), and the outlet at the other end is arranged toward the side of the vortex end floating bearing (401).

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