JPS6128077Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention provides a single-stage centrifugal turbocharger compressor having a compressor wheel rotated by a drive shaft, a cover surrounding the wheel, and an intake passage aligned with the axis of the shaft. , the compressor wheel includes radially extending vanes for moving air axially through the intake passage and for forcing air radially outwardly across the axis of the shaft, each vane having a having a front portion extending radially beyond the adjacent vane portions to form two concentric separate collection chambers surrounding the wheel with walls in the cover extending and radially extending; A circular common border is provided between the two chambers in close proximity to the junction of the front part and the adjacent part of the vane, so that the radially extending front part of the vane allows air to be moved into one of the chambers and the adjacent part of the vane To provide a compressor in which air is moved to the other side of the chamber.

It is well known that it is desirable to reduce the temperature of supercharged air before it is introduced into the intake passage of an internal combustion engine. U.S. Pat. No. 3,143,103 discloses a multi-stage turbocharger compressor with separate axial stages to provide cooling air to an external heat exchanger through which high pressure, high temperature air is passed to charge the engine. Maintaining a maximum oxygen content per unit volume of charge air is an important benefit for charge air cooling, as pointed out in the above-mentioned patent, but also because it reduces undesirable exhaust emissions from the engine. Recently, the above-described treatment of engine charge air has become of increasing interest to motor vehicle and industrial diesel engine users and manufacturers. Generally, if the combustion temperature is low,
The emission of toxic nitrogen oxide exhaust gas is small, and cooling the engine charge air lowers the combustion temperature and makes it more compact.
Assembly is urgently needed and its importance is great.

The object of the present invention is to provide a compact and efficient charge air cooled single stage centrifugal turbocharger compressor. According to the present invention, a uniquely constructed vane is carried on a compressor wheel, and two concentric separate collection chambers are installed in the compressor cover to extend in the radial direction of the vane when the compressor wheel is operated. The front blade part allows low temperature, low pressure air to enter one collection chamber, and the adjacent blade part allows high temperature, high pressure air to enter the other collection chamber, and the back surface of the hub, the front blade part, and the trailing edge are hollowed out. The above object is achieved by a turbocharger compressor having a double collection chamber with a conical cutout so that the front vane section applies a vibration damping force to each of the adjacent vane sections. Ru. According to the present invention, both the high-temperature, high-pressure air and the cooling air used for heat exchange are supplied by a compact single-stage turbocharger compressor,
The advantage is that the turbocharge and heat exchanger can be housed within the engine structure itself.

More specifically, the present invention includes a compressor wheel 46 rotated by drive shaft 14;
In a single stage centrifugal turbocharger compressor having a cover 38 surrounding the wheel and having an intake passage 58 cocentric with the shaft axis, the compressor wheel carries radially extending vanes 47 and the intake passage 58 to direct the air radially and outwardly transversely to the shaft axis, the vanes each having a front vane portion 47a.
and an adjacent vane portion 48, the front vane portion having:
Extending radially beyond adjacent vane sections,
Inside the cover a wall 39 with two concentric separate collection chambers 41, 42 surrounds the wheel, the wall having a radially extending front vane section 47a and an adjacent vane section 48. a front vane portion 47a which extends in proximity to the junction of the two chambers to provide a common circular boundary between the two chambers, thereby extending in the radial direction of the vane during operation of the compressor wheel 46; are adapted to move low temperature, low pressure air into the collection chamber 41, and adjacent vane sections 48 move high temperature, high pressure air into the collection chamber 42, each of which has a front vane section 47a. , separated from, but engaged at the edges, the corresponding adjacent vane portion 47a, the front vane portion 47a being separate from the drive shaft 14, but engaged at the edges;
The hub 5 is mounted in surface contact relation to a compressor wheel portion 52 supporting the hub 5.
1, and the back surface of the hub, the front blade portion 47a, and the trailing edge are hollowed out, and the hollowing is formed by the back surface of the hub 51 and the adjacent trailing edge of the front blade portion 47a. The locking nut 53 is formed to have a predetermined conical shape.
is tightened to the shaft and engages the hub 51, pressing the hub 51 against the compressor wheel section, thereby causing the front vane section 47a to apply a vibration damping force to each of the adjacent vane sections 48. A turbocharger compressor having dual collection chambers, characterized in that:

The concept of the invention is embodied in a compact single-stage centrifugal compressor, i.e. the compressor wheel vanes are formed in such a way that a fairly cool air flow is obtained at a relatively low temperature, and this flow is The high temperature and high pressure air flow induced by the part is maintained separately. The separate air flows induced by the two parts of the wheel vane are usually placed in heat exchange with each other in an external heat exchanger. However, heat exchange begins immediately within the compressor wheel cover, so
The size of the external heat exchanger can be reduced.
The front section of the vane is separated from adjacent vane sections to provide a flow of cooling air thereto, and is carried on a separate hub from that carrying the adjacent vane sections. The two hubs are mounted coaxially on the drive shaft, and the front vane sections and the back surfaces of their hubs are conically undercut, so that the vibration damping force is applied to each adjacent vane section by its corresponding front surface. Added by the vane section.

The present invention will be explained below with reference to the drawings.

Referring first to FIGS. 1 and 2, an exhaust gas powered turbocharger is shown.
This turbocharger has turbine housing 1
0 and houses therein a conventional bladed turbine wheel (not shown) for driving a shaft 14. The turbine housing includes a flanged inlet passage 18 for transmitting engine exhaust gases to the turbine wheel. The turbine components themselves are of conventional type construction. High pressure gas entering the turbine expands through the turbine wheel causing shaft 14 to rotate at high speed. The spent gas is discharged through the turbine outlet passage 19.

An intermediate cast length 21 is attached to the turbine housing cast length 10 , and the cast length 21 and the turbine housing 10 are tightly held together by a tightening ring 22 . The cast length (casting) 21 is asymmetrical in shape, and the central portion 2
4 and an outwardly flanged portion 27. The shaft 14 is located in the center portion 24 of the cast length 21.
There is a central opening 34 extending into the interior. Within this opening, the central portion 24 supports a rotational and thrust bearing, generally designated 36, to permit free rotation of the shaft.

A compressor cover caster, designated 38, is secured to the flanged portion 27 by a tightening ring 37. A curved wall 39 is provided which extends into and is integral with this cover cast. This curved wall has extensions 39a by means of which a circular, common boundary 39b is formed between the two chambers 41 and 42.

As will now be described in detail, chamber 41 surrounds the compressor wheel and defines a generally annular collection area, the outlet of which is formed as a tangentially extending outlet passage 43 (FIG. 2). As shown in FIG. 2, the chamber 42 has a spiral shape,
It forms a diffusion path. Extension 39 of wall 39
c includes a narrow diffusion passage 43 extending generally radially from the tip of the compressor wheel vane, as described next. The spiral chamber or passageway 42 has its outlet in a tangentially extending outlet passageway 44 (FIG. 2).

An extended, reduced diameter portion of the shaft 14 carries a plurality of radially extending vanes, generally designated 46.
It supports a centrifugal compressor wheel shown in . As best shown in FIGS. 1 and 3, each vane has a front portion 47 in front of an adjacent vane portion 48. As best shown in FIGS. Front part 47 of each blade
has a radially extending portion 47a extending radially beyond the adjacent vane portion 48, and a circular common boundary portion between chambers 41 and 42 is adjacent to the radially extending front portion 47a. It is located adjacent to the junction with the vane portion 48 . The front vane section 47 carries a hub section 51 which is supported on the shaft 14 and is pressed adjacent to a hub member 52 which carries an adjacent vane section 48 . The hub 51 and the hub member 52 are connected to the shaft 1
It is held in place by tightening a lock nut 53 on the threaded end of 4. Front part of the blade 4
The edges of 7 engage the edges of adjacent vane sections 48 and, as shown in FIG.
and the adjacent vane portion 48 in a continuous and smooth manner.

As shown by the broken line 56 in FIG. When the hub portion 52 is compressed by tightening, the front vane portion 47 applies a vibratory damping force to the corresponding adjacent vane portion 48 which is concentrated adjacent the outer periphery of the adjacent vane 48 . The dashed line 56 shows the underside of the hub 51 and the front vane section 47 in front of the hub is clamped to the hub section 52. When the nut 53 is tightened to the hub portion and the blade is slightly deformed, the edge engages the adjacent blade portion and the hub 51 engages the hub portion 52, causing the blade deformation to cause the outer edge of the adjacent blade portion 48 to engage. Produces additional braking force.

The operation will be explained. Rotating the compressor wheel 46 at high speed moves air through the compressor inlet passage 58. The gas flow induced by the radially extending front portion 47a passes through the circular boundary 39b and enters the collection chamber 41. The remaining gas flow induced by the front vane portion 47 that mates with the adjacent portion 48 flows through the narrow diffusion passage 4.
3 into a spiral diffusion passageway or chamber 42 . The air moving into chamber 41 is at a lower temperature and pressure than the air moving through chamber 42, and as shown in FIG.
1 to a conventional type of air-to-air heat exchanger. The high temperature, high pressure air passing through the spiral passage 42 exits through the outlet 44 and is introduced into the heat exchanger 61 . 2
Because the two separate air streams are heat exchanged, the temperature of the air from chamber 42 drops before it is introduced into the internal combustion engine intake manifold 62, indicated at 63.

Referring to FIG. 5, a variation of the turbocharger compressor arrangement is shown. The configuration of FIG. 5 differs from the configuration described above in that chamber 41 includes a member extending wall surface 68 corresponding to wall 39 of FIG. 1. This member includes integral fins 69 to aid in heat transfer across wall 68.

FIG. 6 shows a variation in vane design for a compressor wheel. In this design, all bucket-shaped curved sections extend across the radially extending front section 71 of the vane, and the adjacent vane section 72 is uncurved. Since the non-curved adjacent vane section 72 and the extended hub section are formed separately from the curved front vane section 71, simple casting and manufacturing methods can be used to produce said curved section of the wheel. .

The compressor wheel and cover or housing structure of the present invention facilitates heat exchange between hot air and cold, low pressure air in the compressor.
Can be started within the housing itself. In FIG. 4, an external heat exchanger is shown for use in reducing the charge air temperature within the engine, with means for extending the heat exchange surface into the compressor housing (e.g., by fins 69 in FIG. 5). The size and capacity of the external heat exchanger can be reduced by using If the need for cooling by charging air is relatively small, the structure of the present invention can be used to
There is no need to use a separate external heat exchanger. Typically, each adjacent vane section has a wheel output of a single-stage centrifugal air compressor, with a primarily circular wall edge 3
The high temperature, high pressure charge air and cooling air used for heat exchange, which exerts the vibration damping force on each vane adjacent to 9b, are both supplied by a compact single stage turbocharger compressor. In this way, the turbocharger and heat exchanger can be housed within the engine structure itself, and when it is necessary to use air from the engine's radiator fan as a coolant for the charge air produced by the turbocharger, the core of the heat exchanger can be placed inside the engine. There is no need to install it on a radiator. Compared to installing a heat exchanger adjacent to the engine radiator using radiator fan air for cooling, the use of the turbocharger of the present invention in conjunction with the smallest heat exchanger reduces the This is particularly advantageous for power vehicle machinery and the like, which are widely used in the field of motor vehicles. Under such operating conditions, the air flow passages of the radiator fan can become clogged with dust, leaves, and other debris, preventing the required cooling of the air charge. In the arrangement shown in FIG. 5, clean air is supplied to both flow channels via heat exchange, so that no disturbances occur.

[Brief explanation of the drawing]

Fig. 1 is a side view of a turbocharger embodying the present invention showing the compressor components in cross section, Fig. 2 is an end view of the turbocharger shown in Fig. 1, and Fig. 3 is the compressor wheel shown in Fig. 1. Figure 4 is a schematic diagram of the turbocharger shown in Figure 1, which is incorporated into a system that turbocharges an internal combustion engine using a heat exchanger, and Figure 5 is the same as that shown in Figure 2. FIG. 6 is a top view showing a partially modified compressor wheel and cover. DESCRIPTION OF SYMBOLS 10... Turbine housing, 14... Shaft, 19... Gas passage, 21... Casting, 22... Tightening ring, 24... Center portion, 27...
...Flange portion, 34...Central opening, 36...Thrust bearing, 37...Tightening ring, 39...Curved wall, 4
1, 42...Chyamba, 43...Exit, 44...
Exit passageway, 46...Compressor wheel, 4
7...Front surface of the blade, 48...Blade, 51, 52...
...Hub, 53...Lock nut, 58...Entrance passage,
61...Heat exchanger, 62...Intake manifold, 6
3...Internal combustion engine, 68...Wall surface, 69...Fin, 71, 72...Blade.

Claims (1)

[Scope of utility model registration request] In a single-stage centrifugal turbocharger compressor having a compressor wheel 46 rotated by a drive shaft 14 and a cover 38 surrounding the wheel and having an intake passage 58 cocentric with the shaft axis, the compressor wheel is , carrying radially extending vanes 47 to move air radially through the intake passage 58 and directing the air radially and outwardly transversely to the shaft axis; The feather is
Each has a front vane portion 47a and an adjacent vane portion 48, the front vane portion extending radially beyond the adjacent vane portion to form two concentric separate collection chambers within the cover. A wall 39 having 41, 42 surrounds the wheel, which wall extends adjacent the juncture of the radially extending front vane section 47a and the adjacent vane section 48 between the two chambers. is extended to provide a circular boundary such that during operation of the compressor wheel 46, the radially extending front vane portion 47a of the vane moves cold, low pressure air into the collection chamber 41. The front vane section 47a of each vane is separated from the corresponding adjacent vane section 48, and the adjacent vane sections 48 are adapted to move hot, high pressure air into the collection chamber 42. , and the front vane section 47a is separate from the drive shaft 14 but mounted in surface contact relation to a compressor wheel section 52 that supports the adjacent vane section 48. It extends in the radial direction from the hub 51 in a state in which the rear surface of the hub and the front blade portion 4
7a and the rear edge are hollowed out, and the hollow is formed so that the ring defined by the back surface of the hub 51 and the adjacent rear edge of the front blade portion 47a is shaped like a cone. 53 is tightened to the shaft and engages the hub 51, forcing the hub 51 against the compressor wheel section, thereby causing the front vane section 47a to apply a vibration damping force to each of the adjacent vane sections 48. A turbocharger compressor having a double collection chamber characterized by: